EP1073840A1 - Soupape supplementaire d'un systeme d'injection du carburant d'un moteur a combustion interne - Google Patents

Soupape supplementaire d'un systeme d'injection du carburant d'un moteur a combustion interne

Info

Publication number
EP1073840A1
EP1073840A1 EP98966770A EP98966770A EP1073840A1 EP 1073840 A1 EP1073840 A1 EP 1073840A1 EP 98966770 A EP98966770 A EP 98966770A EP 98966770 A EP98966770 A EP 98966770A EP 1073840 A1 EP1073840 A1 EP 1073840A1
Authority
EP
European Patent Office
Prior art keywords
bore
valve
pressure pump
pump
pressure
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.)
Granted
Application number
EP98966770A
Other languages
German (de)
English (en)
Other versions
EP1073840B1 (fr
Inventor
Erhard Faix
Helmut Clauss
Rainer Lorenz
Gerd Loesch
Markus Rueckle
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 EP1073840A1 publication Critical patent/EP1073840A1/fr
Application granted granted Critical
Publication of EP1073840B1 publication Critical patent/EP1073840B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7908—Weight biased
    • Y10T137/7909—Valve body is the weight
    • Y10T137/791—Ball valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7922—Spring biased
    • Y10T137/7927—Ball valves

Definitions

  • the invention relates to a connecting valve according to the preamble of patent claim 1.
  • Low pressure pump known (DE 44 01 074 AI).
  • a connecting valve with a sleeve-shaped valve piston loaded by a compression spring.
  • This has a throttle bore in its base, through which the low-pressure pump is constantly connected to a camshaft chamber of the high-pressure pump designed as a radial piston pump.
  • the camshaft chamber is in turn connected to the fuel tank.
  • valve piston is displaceable against the force of the compression spring by the pressure of the fuel delivered by the low-pressure pump. If a pressure threshold is exceeded, the valve piston releases a line connection to pump elements of the high-pressure pump. - 2 -
  • connection valve has several functions: on the one hand, the part of the fuel injection system on the low-pressure side can be vented on the way via the throttle bore and the camshaft chamber.
  • the throttle bore supplies the camshaft chamber with fuel that serves as a lubricant.
  • the cut-in valve should serve as a shut-off valve in the event of a defect in the high-pressure system part in order to protect the internal combustion engine.
  • a disadvantage of this known embodiment is that the fuel flow which is not drawn off by the high-pressure pump results in an uneconomical mode of operation of the low-pressure pump.
  • the connecting valve according to the invention with the features of claim 1 has the advantage that it is located outside the direct line connection between the low pressure pump and the high pressure pump, in addition to the venting of the low pressure side
  • Fuel injection system part and the dimensioning of the lubricant flow to the camshaft of the high-pressure pump also the control of the fuel volume flow not taken off by the high-pressure pump directly
  • connection valve controls two fuel circuits, namely the one used for the lubrication and cooling of the high-pressure pump and the return of the deactivated fuel, the first-mentioned circuit when the second is switched on
  • Circulation remains largely unaffected.
  • the return flow of the deactivated fuel directly to the suction side of the low-pressure pump increases its delivery rate, since it is used to filter the Fuel required system pre-filter can be bypassed.
  • valve is advantageous because several valve functions can be performed with a single movable valve member.
  • the valve can also be completely pre-assembled and tested as a structural unit. Due to its arrangement in the housing of the high-pressure pump, the installation of the valve in the system is associated with little effort, in particular only a seal to the outside is required, since the screw thread
  • the connecting valve can thus be manufactured with a relatively short valve housing.
  • FIG. 1 shows a hydraulic circuit diagram of a schematically reproduced fuel injection system with a cut-in valve assigned to a high-pressure pump
  • FIG. 2 shows the cut-in valve in longitudinal section.
  • a fuel storage injection system 10 for internal combustion engines which is shown in a highly simplified manner in FIG. 1, that is to say direct injection - 4 -
  • Diesel engines has as essential elements a low-pressure pump 11, a high-pressure pump 12, a high-pressure fuel reservoir (common rail) 13, injection solenoid valves (injectors) 14, a quantity control valve 15 and a cut-in valve 16.
  • the low pressure pump 11 is connected to a fuel tank (tank) 18 with a suction line 17 and to the high pressure pump 12 with a low pressure line 19.
  • the volume control valve 15 is located in the low-pressure line 19.
  • the high-pressure pump 12, which is fed by the low-pressure pump 11, is in turn connected on the outlet side by a high-pressure line 20 to the high-pressure fuel reservoir 13, to which the injection solenoid valves 14 are connected.
  • a tank drain line 21 leads from these to the fuel tank 18.
  • the mode of operation of the fuel storage injection system 10 is known, so that only the arrangement of the connection valve 16 in the system, the structure and function of the connection valve 16 will be discussed below.
  • the high-pressure pump 12 is, by design, a radial piston pump with a plurality of pump elements 23, of which only one element is shown in FIG. 1.
  • a camshaft 24 (or an eccentric shaft or crankshaft) is used to drive the pump elements 23.
  • the camshaft 24 is located in a camshaft chamber 25 of a pump housing 26. From the connecting valve 16, which is connected to the low pressure line 19 on the inflow side, a feed line 27 leads into the camshaft chamber 25 and a return line 28 to the suction line 17 of the low pressure pump 11.
  • the camshaft chamber 25 is in turn connected on the outlet side to the tank drain line 21.
  • the embodiment of the connecting valve 16 shown in FIG. 2 shows a screw-in part designed as a hollow cylinder, predominantly in one - 5 -
  • valve housing 32 In the drawn position of the pump housing 26 of the high-pressure pump 25 accommodated valve housing 32, in the stepped through bore 33 of which a longitudinally movable valve piston 34, a helical compression spring 35 arranged axially one behind the other and a ball 36 which seals the through bore 33 to the outside are accommodated.
  • the valve housing 32 has an external thread section 37, with which it is screwed into the blind hole 31 under attack on a hexagon 38 on the valve housing side. In the drawn position of the
  • Valve housing 32 engages its end face 39 located in the drawing at the bottom of the bore 40 of the blind bore 31. On the side of the mouth 41 of the blind bore 31, the valve housing 32 is sealed with a sealing ring 42.
  • the valve housing 32 is provided between the sealing ring 42 and the bore base 40 with two transverse bores 45 and 46 crossing the through bore 33.
  • the cross-bore 45 on the sealing ring side has a first
  • the first outflow bore 47 is part of the feed line 27 to the camshaft chamber 25 of the high-pressure pump 12 (see FIG. 1).
  • the second transverse bore 46 of the valve housing 32 remote from the sealing ring is provided with a second outflow bore 48 of the
  • the second outflow bore 48 is part of the return line 28 leading to the suction side of the low-pressure pump 11.
  • an inflow bore 49 is connected to the through bore 33.
  • the inflow bore 49 is connected to the low pressure line 19 leading from the low pressure pump 11 to the high pressure pump 12.
  • the second outflow bore 48 is completely separated from the inflow bore 49 by the tight engagement of the valve housing 32 on the bottom 40 of the bore. Adequate hydraulic - 6 -
  • Sealing is achieved between the first outflow bore 47 and the second outflow bore 48 by means of the screw connection (external thread section 37) between the valve housing 32 and the pump housing 26.
  • the sleeve-shaped valve piston 34 is suitably received in the through bore 33 of the valve housing 32.
  • the valve piston 34 In the rest position of the connecting valve 16, the valve piston 34 is supported with a snap ring 51 arranged on the circumference on a step 52 of the through bore 33 due to the spring force of the helical compression spring 35 acting on the valve piston. Their pretension is adjusted by pressing the ball 36 deeply into the through hole 33.
  • the valve piston 34 has in its spring-side piston head 53 a throttle bore 54 through which the spring-side section of the
  • Through hole 33 communicates with the interior 55 of the valve piston 34.
  • the valve piston 34 On the circumferential side, the valve piston 34 has an annular groove 56, which is connected to the interior 55 by one or more throttle bores 57.
  • the annular groove 56 of the valve piston 34 forms a first control edge 58, which on the part of the step 52 of the through hole 33 is assigned a hollow cone-shaped first control contour 59 of the valve housing 32.
  • the valve piston 34 has a second control edge 60 on its end facing away from the spring, which cooperates with the transverse bore 46 of the valve housing 32 forming a second control contour 61.
  • the valve piston 34 closes off the connection between the inflow bore 49 through the throttle bore 57 to the first outflow bore 47 and from the inflow bore 49 to the second outflow bore 48.
  • the inflow bore 49 is constantly through the throttle bore 54 in the piston crown 53 connected to the camshaft chamber 25 of the high pressure pump 12.
  • air located in the low-pressure system can flow through the throttle bore 54 in the piston crown 56 of the valve piston 34 through the first outflow bore 47 into the camshaft chamber 25 and from there through the
  • the valve piston 34 As the delivery pressure of the fuel withdrawn from the tank 18 by the low-pressure pump 11 and supplied to the connection valve 16 through the inflow bore 49 increases, the valve piston 34 is displaced from its rest position against the spring force of the compression spring 35. When a first pressure threshold is exceeded, the first control edge 58 of the valve piston 34 reaches the area of the control contour 59, so that a fuel flow can flow from the inflow bore 49 through the throttle bore 57 of the valve piston 34 to the first outflow bore 47 and further into the camshaft chamber 25 of the high-pressure pump 12 . With a small stroke of the valve piston 34, the connecting valve 16 acts as a flow control valve with which a fuel volume flow sufficient for lubricating and cooling the high-pressure pump 12 is set. To this must be added the partial fuel quantity passing through the throttle bore 54 running parallel to the throttle bore 57 in the piston crown 53.
  • the valve piston 34 which is displaced longitudinally in the direction of the ball 36, releases the transverse bore 46 of the valve housing 32 with a second control edge 60 when a second pressure threshold, which is higher than the first pressure threshold, is exceeded.
  • Fuel that has not been drawn off by the high-pressure pump 12 is discharged through the second outflow bore 48 and the return line 28 directly to the suction side of the low-pressure pump 11.
  • the hold valve 16 acts now additionally as a pressure control valve with which the inflow-side pressure is kept largely free of fluctuations.
  • the pressure control has an advantageous effect on the quantity control valve 15 because a fuel supplied to this valve with little pressure fluctuation supports its operation.

Abstract

L'invention concerne un système d'injection de carburant présentant une pompe basse pression destinée à prélever du carburant d'un réservoir et une pompe haute pression alimentée par la pompe basse pression et dotée d'éléments pompe actionnés par un arbre à cames. Une soupape supplémentaire (16) est reliée, côté admission (orifice d'admission 49) au côté refoulement de la pompe basse pression et, côté évacuation, d'une part (orifice d'évacuation 47) au compartiment d'arbre à cames de la pompe haute pression et, d'autre part, (orifice d'évacuation 48) au côté aspiration de la pompe basse pression. Un piston à soupape (34) de la soupape supplémentaire (16), libère, sous l'action d'un ressort, la liaison entre la pompe basse pression et le compartiment d'arbre à cames dans le cas d'un premier seuil de pression et la liaison entre le côté refoulement et le côté aspiration de la pompe basse pression dans le cas d'un deuxième seuil de pression plus élevé que le premier. Un orifice d'étranglement (54) pratiqué dans le fond (53) du piston à soupape (34) sert à la ventilation du système basse pression. L'invention convient aux moteurs diesel à injection directe.
EP98966770A 1998-04-24 1998-12-10 Soupape supplementaire d'un systeme d'injection du carburant d'un moteur a combustion interne Expired - Lifetime EP1073840B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19818385 1998-04-24
DE19818385A DE19818385A1 (de) 1998-04-24 1998-04-24 Zuschaltventil in einem Kraftstoffeinspritzsystem für Brennkraftmaschinen
PCT/DE1998/003628 WO1999056016A1 (fr) 1998-04-24 1998-12-10 Soupape supplementaire d'un systeme d'injection du carburant d'un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1073840A1 true EP1073840A1 (fr) 2001-02-07
EP1073840B1 EP1073840B1 (fr) 2002-06-12

Family

ID=7865693

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98966770A Expired - Lifetime EP1073840B1 (fr) 1998-04-24 1998-12-10 Soupape supplementaire d'un systeme d'injection du carburant d'un moteur a combustion interne

Country Status (5)

Country Link
US (1) US6422212B1 (fr)
EP (1) EP1073840B1 (fr)
JP (1) JP4280419B2 (fr)
DE (2) DE19818385A1 (fr)
WO (1) WO1999056016A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
FR2863667A1 (fr) * 2003-12-16 2005-06-17 Volkswagen Ag Dispositif d'alimentation en carburant pour moteur a combustion interne ainsi que procede de mise en oeuvre

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IT1310755B1 (it) * 1999-11-30 2002-02-22 Elasis Sistema Ricerca Fiat Pompa idraulica ad alta pressione, in particolare pompa a pistoniradiali per il carburante di un motore a combustione interna.
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DE102010001834A1 (de) * 2010-02-11 2011-08-11 Robert Bosch GmbH, 70469 Verfahren zur Versorgung einer Hochdruckpumpe in einem Kraftstoffeinspritzsystem einer Brennkraftmaschine mit Kraftstoff sowie Kraftstoffeinspritzsystem
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FR2863667A1 (fr) * 2003-12-16 2005-06-17 Volkswagen Ag Dispositif d'alimentation en carburant pour moteur a combustion interne ainsi que procede de mise en oeuvre

Also Published As

Publication number Publication date
US6422212B1 (en) 2002-07-23
EP1073840B1 (fr) 2002-06-12
JP4280419B2 (ja) 2009-06-17
WO1999056016A1 (fr) 1999-11-04
JP2002513115A (ja) 2002-05-08
DE59804470D1 (de) 2002-07-18
DE19818385A1 (de) 1999-10-28

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