EP1073840B1 - Sequence valve in a fuel injection system for internal combustion engines - Google Patents

Sequence valve in a fuel injection system for internal combustion engines Download PDF

Info

Publication number
EP1073840B1
EP1073840B1 EP98966770A EP98966770A EP1073840B1 EP 1073840 B1 EP1073840 B1 EP 1073840B1 EP 98966770 A EP98966770 A EP 98966770A EP 98966770 A EP98966770 A EP 98966770A EP 1073840 B1 EP1073840 B1 EP 1073840B1
Authority
EP
European Patent Office
Prior art keywords
bore
valve
pressure pump
housing
pump
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.)
Expired - Lifetime
Application number
EP98966770A
Other languages
German (de)
French (fr)
Other versions
EP1073840A1 (en
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/en
Application granted granted Critical
Publication of EP1073840B1 publication Critical patent/EP1073840B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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 Genus of claim 1.
  • valve piston is driven by the pressure of the Low pressure pump fuel delivered against the force the compression spring can be moved. If one is exceeded Pressure threshold gives the valve piston a line connection to pump elements of the high pressure pump free.
  • connection valve has several functions: on the one hand it can the low-pressure part of the fuel injection system on the way through the throttle bore and the camshaft space be vented. The other is through the throttle bore the camshaft chamber with lubricant Fuel supplied.
  • connection valve should in the event of a defect in the high-pressure system part as Shut-off valve serve to protect the internal combustion engine.
  • a disadvantage of this known embodiment is that the one not removed from the high pressure pump Fuel flow an uneconomical mode of operation Low pressure pump.
  • connection valve according to the invention with the features of Compared to claim 1 has the advantage that outside the direct line connection between the Low pressure pump and the high pressure pump lying next to the Venting 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 shutdown of the not by the high pressure pump decreased fuel volume flow immediately to Ensures the suction side of the low pressure pump. It controls the connection valve two fuel circuits, namely the the lubrication and cooling of the high pressure pump and the Serve the return of the de-fueled fuel, whereby the first-mentioned circuit when switching on the second Circulation remains largely unaffected. Furthermore is by returning the de-fueled fuel directly to the suction side of the low pressure pump Conveying capacity increased, because a for filtering the Bypassed the system's fuel pre-filter can be.
  • valve is advantageous because with a single movable valve member several Valve functions are exercised.
  • the valve is also completely pre-assembled and testable. by virtue of its arrangement in the housing of the high pressure pump is the Installation of the valve in the system with little effort connected, in particular only a seal after required on the outside because the screw thread Connections of the pump housing to the camshaft space and Adequate suction side of the low pressure pump hydraulically separated. This is the connection valve can be manufactured with a relatively short valve housing.
  • FIG. 1 shows a Hydraulic circuit diagram of a schematically reproduced Fuel injection system with a high pressure pump assigned connection valve and Figure 2, the connection valve in longitudinal section.
  • Fuel storage injection system 10 for Internal combustion engines that is direct injection Diesel engines, has as essential elements Low pressure pump 11, a high pressure pump 12, a High-pressure fuel accumulator (common rail) 13, injection solenoid valves (Injectors) 14, a flow control valve 15 as well as a connecting valve 16.
  • the low pressure pump 11 is with a suction line 17 to a fuel tank 18 and with a low pressure line 19 to the high pressure pump 12 connected.
  • In the low pressure line 19 is the flow control valve 15.
  • the low pressure pump 11 fed high pressure pump 12 is in turn on the outlet side through a high pressure line 20 to the high pressure fuel accumulator 13 in connection to which the injection solenoid valves 14 are connected.
  • the high-pressure pump 12 is a radial piston pump by design with several pump elements 23, of which in FIG. 1 only one element is shown.
  • To drive the Pump elements 23 serve a camshaft 24 (or a Eccentric shaft or crankshaft).
  • the camshaft 24 is located itself in a camshaft space 25 of a pump housing 26. From the cut-in valve 16, which on the inflow side to the Low pressure line 19 is connected, leads Supply line 27 in the camshaft space 25 and one Return line 28 to suction line 17 of the low pressure pump 11.
  • the camshaft chamber 25 is in turn on the exhaust side Tank drain line 21 connected.
  • Connection valve 16 shows a hollow cylindrical one Screw-in part designed, mainly in one Blind hole 31 of the pump housing 26 of the high pressure pump 25 received valve housing 32, in its stepped Through bore 33 a longitudinally movable valve piston 34, an axially arranged one behind the other Helical compression spring 35 and a through hole 33 outwardly sealed ball 36 are.
  • the valve housing 32 has an externally threaded section 37 on which it is under attack on one hexagon 38 on the valve housing into the blind hole 31 is screwed in. In the drawn position of the Valve housing 32 engages in the drawing below located end face 39 at the bottom 40 of the hole Blind hole 31 on. On the part of the mouth 41 of the Blind hole 31 is the valve housing 32 with a Sealing ring 42 sealed.
  • the valve housing 32 is between the sealing ring 42 and the Bore bottom 40 with two through holes 33 crossing cross holes 45 and 46 provided.
  • the Sealing ring-side cross bore 45 is with a first Outflow bore 47 of the pump housing 26 in connection.
  • the first outflow bore 47 is part of the feed line 27 to Camshaft chamber 25 of the high pressure pump 12 (see Figure 1).
  • the second transverse bore 46 of the valve housing remote from the sealing ring 32 stands with a second outflow bore 48 Pump housing 26 in connection.
  • the second drain hole 48 is part of the suction side of the low pressure pump 11 leading return line 28.
  • Face of the valve housing 32 there is an inflow bore 49 with the through bore 33 in connection.
  • the inflow bore 49 is to that of the Low pressure pump 11 leading to high pressure pump 12 Low pressure line 19 connected.
  • the second Outflow bore 48 is due to the dense attack of the Valve housing 32 on the bottom 40 of the hole completely Inflow bore 49 separated. Adequate hydraulic Sealing is between the first outflow bore 47 and the second outflow bore 48 through the screw connection (Male thread section 37) between the valve housing 32 and achieved the pump housing 26.
  • the sleeve-shaped valve piston 34 is suitable in the through hole 33 of the valve housing 32 is added.
  • the Valve piston 34 In the rest position of the connecting valve 16 is the Valve piston 34 with a circumferentially arranged Snap ring 51 on a step 52 of the through hole 33 due to the spring force of those acting on the valve piston Helical compression spring 35 supported. Their bias is by correspondingly deeply pressing the ball 36 into the Through hole 33 set.
  • the valve piston 34 has in its spring-side piston head 53 has a throttle bore 54, through which the spring section of the Through hole 33 with the interior 55 of the valve piston 34 communicates.
  • the valve piston has a circumference 34 an annular groove 56, which by one or more Throttle bores 57 is connected to the interior 55.
  • the Annular groove 56 of the valve piston 34 forms a first Control edge 58, the level 52 of the Through hole 33 is a hollow cone-shaped first Control contour 59 of the valve housing 32 is assigned.
  • the Valve piston 34 has on its end facing away from the spring a second control edge 60, which with the second Control contour 61 forming transverse bore 46 of the valve housing 32 cooperates.
  • valve piston 34 blocks 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 second outflow bore 48.
  • the inflow hole 49 is however, constantly through the throttle bore 54 in the piston crown 53 connected to the camshaft chamber 25 of the high pressure pump 12.
  • the low pressure system Air located through the throttle bore 54 in the piston crown 56 of the valve piston 34 through the first outflow bore 47 in the camshaft space 25 and from this through the Drain the tank drain line 21. This is a vent of the low pressure system effectively achieved.
  • the fuel supplied to the switching valve 16 becomes the Valve piston 34 from its rest position against the Spring force of the compression spring 35 shifted. If exceeded the first control edge 58 reaches a first pressure threshold of the valve piston 34 in the area of the control contour 59, so that a fuel 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 space 25 of the High pressure pump 12 can flow.
  • the connecting valve 16 acts with a small stroke of the valve piston 34 as a flow control valve, with the one for lubricating and cooling the high pressure pump 12 sufficient fuel volume flow is set. To this is due to the parallel to the throttle bore 57 throttle bore 54 extending in the piston crown 53 Add partial fuel quantity.

Landscapes

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

Description

Die Erfindung geht aus von einem Zuschaltventil nach der Gattung des Patentanspruchs 1.The invention relates to a connecting valve according to the Genus of claim 1.

Es ist schon ein Kraftstoffeinspritzsystem für Brennkraftmaschinen mit einer Kraftstoff aus einem Tank saugenden und an eine Hochdruckpumpe fördernden Niederdruckpumpe bekannt (DE 44 01 074 A1). In der Verbindungsleitung zwischen den beiden Pumpen ist ein Zuschaltventil mit einem druckfederbelasteten hülsenförmigen Ventilkolben angeordnet. Dieser weist in seinem Boden eine Drosselbohrung auf, durch welche die Niederdruckpumpe ständig mit einem Nockenwellenraum der als Radialkolbenpumpe ausgebildeten Hochdruckpumpe in Verbindung steht. Der Nockenwellenraum wiederum ist an den Kraftstofftank angeschlossen.It's already a fuel injection system for Internal combustion engines with a fuel from a tank sucking and conveying to a high pressure pump Low pressure pump known (DE 44 01 074 A1). In the Connection line between the two pumps is a Connecting valve with a sleeve-shaped, spring loaded Valve piston arranged. This has one in its bottom Throttle bore through which the low pressure pump constantly with a camshaft chamber as a radial piston pump trained high pressure pump is connected. The The camshaft space is in turn attached to the fuel tank connected.

Der Ventilkolben ist durch den Druck des von der Niederdruckpumpe geförderten Kraftstoffs entgegen der Kraft der Druckfeder verschiebbar. Bei Überschreiten einer Druckschwelle gibt der Ventilkolben eine Leitungsverbindung zu Pumpenelementen der Hochdruckpumpe frei. The valve piston is driven by the pressure of the Low pressure pump fuel delivered against the force the compression spring can be moved. If one is exceeded Pressure threshold gives the valve piston a line connection to pump elements of the high pressure pump free.

Das Zuschaltventil hat mehrere Funktionen: zum einen kann der niederdruckseitige Teil des Kraftstoffeinspritzsystems auf dem Weg über die Drosselbohrung und den Nockenwellenraum entlüftet werden. Zum anderen wird durch die Drosselbohrung der Nockenwellenraum mit als Schmierstoff dienendem Kraftstoff versorgt. Darüber hinaus soll das Zuschaltventil bei einem Defekt des hochdruckseitigen Systemteils als Absperrventil dienen, um die Brennkraftmaschine zu schützen. Nachteilig ist jedoch bei dieser bekannten Ausführungsform, daß der nicht von der Hochdruckpumpe abgenommene Kraftstoffstrom eine unwirtschaftliche Betriebsweise der Niederdruckpumpe zur Folge hat.The connection valve has several functions: on the one hand it can the low-pressure part of the fuel injection system on the way through the throttle bore and the camshaft space be vented. The other is through the throttle bore the camshaft chamber with lubricant Fuel supplied. In addition, the connection valve should in the event of a defect in the high-pressure system part as Shut-off valve serve to protect the internal combustion engine. However, a disadvantage of this known embodiment is that the one not removed from the high pressure pump Fuel flow an uneconomical mode of operation Low pressure pump.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Zuschaltventil mit den Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß es, außerhalb der unmittelbaren Leitungsverbindung zwischen der Niederdruckpumpe und der Hochdruckpumpe liegend, neben der Entlüftung des niederdruckseitigen Kraftstoffeinspritzsystemteils und der Bemessung des Schmierstoffstromes zu der Nockenwelle der Hochdruckpumpe auch die Absteuerung des nicht von der Hochdruckpumpe abgenommenen Kraftstoff-Volumenstroms unmittelbar zur Saugseite der Niederdruckpumpe sicherstellt. Dabei steuert das Zuschaltventil zwei Kraftstoffkreisläufe, nämlich den der Schmierung sowie Kühlung der Hochdruckpumpe und den der Rückführung des abgesteuerten Kraftstoffs dienenden, wobei der erstgenannte Kreislauf beim Zuschalten des zweiten Kreislaufs weitgehend unbeeinflußt bleibt. Darüber hinaus wird durch die Rückführung des abgesteuerten Kraftstoffs unmittelbar zur Saugseite der Niederdruckpumpe deren Förderleistung gesteigert, da ein zum Filtern des Kraftstoffs erforderlicher Vorfilter des Systems umgangen werden kann.The connection valve according to the invention with the features of Compared to claim 1 has the advantage that outside the direct line connection between the Low pressure pump and the high pressure pump lying next to the Venting 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 shutdown of the not by the high pressure pump decreased fuel volume flow immediately to Ensures the suction side of the low pressure pump. It controls the connection valve two fuel circuits, namely the the lubrication and cooling of the high pressure pump and the Serve the return of the de-fueled fuel, whereby the first-mentioned circuit when switching on the second Circulation remains largely unaffected. Furthermore is by returning the de-fueled fuel directly to the suction side of the low pressure pump Conveying capacity increased, because a for filtering the Bypassed the system's fuel pre-filter can be.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Patentanspruch 1 angegebenen Zuschaltventils möglich.By the measures listed in the subclaims advantageous further developments and improvements of the Claim 1 specified connecting valve possible.

Die Ausgestaltung des Ventils ist von Vorteil, weil mit einem einzigen bewegbaren Ventilglied mehrere Ventilfunktionen ausgeübt werden. Das Ventil ist außerdem komplett als Baueinheit vormontierbar und prüfbar. Aufgrund seiner Anordnung im Gehäuse der Hochdruckpumpe ist der Einbau des Ventils in das System mit wenig Aufwand verbunden, insbesondere ist lediglich eine Abdichtung nach außen erforderlich, da das Einschraubgewinde die Verbindungen des Pumpengehäuses zum Nockenwellenraum und zur Saugseite der Niederdruckpumpe in ausreichendem Maß hydraulisch voneinander trennt. Damit ist das Zuschaltventil mit einem relativ kurz bauenden Ventilgehäuse herstellbar.The design of the valve is advantageous because with a single movable valve member several Valve functions are exercised. The valve is also completely pre-assembled and testable. by virtue of its arrangement in the housing of the high pressure pump is the Installation of the valve in the system with little effort connected, in particular only a seal after required on the outside because the screw thread Connections of the pump housing to the camshaft space and Adequate suction side of the low pressure pump hydraulically separated. This is the connection valve can be manufactured with a relatively short valve housing.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen Hydraulikschaltplan eines schematisch wiedergegebenen Kraftstoffeinspritzsystems mit einem einer Hochdruckpumpe zugeordneten Zuschaltventil und Figur 2 das Zuschaltventil im Längsschnitt.An embodiment of the invention is in the drawing shown in simplified form and in the following Description explained in more detail. 1 shows a Hydraulic circuit diagram of a schematically reproduced Fuel injection system with a high pressure pump assigned connection valve and Figure 2, the connection valve in longitudinal section.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Ein in Figur 1 stark vereinfacht wiedergegebenes Kraftstoffspeicher-Einspritzsystem 10 für Brennkraftmaschinen, das heißt direkteinspritzende Dieselmotoren, weist als wesentliche Elemente eine Niederdruckpumpe 11, eine Hochdruckpumpe 12, einen Kraftstoff-Hochdruckspeicher (Common Rail) 13, Einspritz-Magnetventile (Injektoren) 14, ein Mengen-Regelventil 15 sowie ein Zuschaltventil 16 auf. Die Niederdruckpumpe 11 ist mit einer Saugleitung 17 an einen Kraftstoffbehälter (Tank) 18 und mit einer Niederdruckleitung 19 an die Hochdruckpumpe 12 angeschlossen. In der Niederdruckleitung 19 befindet sich das Mengen-Regelventil 15. Die von der Niederdruckpumpe 11 gespeiste Hochdruckpumpe 12 wiederum steht auslaßseitig durch eine Hochdruckleitung 20 mit dem Kraftstoff-Hochdruckspeicher 13 in Verbindung, an den die Einspritz-Magnetventile 14 angeschlossen sind. Von diesen führt eine Tankablaufleitung 21 zum Kraftstoffbehälter 18. Die Arbeitsweise des Kraftstoffspeicher-Einspritzsystems 10 ist bekannt, so daß nachfolgend lediglich auf die Anordnung des Zuschaltventils 16 im System, der Aufbau und die Funktion des Zuschaltventils 16 eingegangen wird.A shown in a highly simplified manner in FIG. 1 Fuel storage injection system 10 for Internal combustion engines, that is direct injection Diesel engines, has as essential elements Low pressure pump 11, a high pressure pump 12, a High-pressure fuel accumulator (common rail) 13, injection solenoid valves (Injectors) 14, a flow control valve 15 as well as a connecting valve 16. The low pressure pump 11 is with a suction line 17 to a fuel tank 18 and with a low pressure line 19 to the high pressure pump 12 connected. In the low pressure line 19 is the flow control valve 15. The low pressure pump 11 fed high pressure pump 12 is in turn on the outlet side through a high pressure line 20 to the high pressure fuel accumulator 13 in connection to which the injection solenoid valves 14 are connected. One of these leads Tank drain line 21 to the fuel tank 18. Die 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 the function of the connecting valve 16 is received.

Die Hochdruckpumpe 12 ist bauartgemäß eine Radialkolbenpumpe mit mehreren Pumpenelementen 23, von denen in Figur 1 lediglich ein Element dargestellt ist. Zum Antrieb der Pumpenelemente 23 dient eine Nockenwelle 24 (oder eine Exzenterwelle oder Kurbelwelle). Die Nockenwelle 24 befindet sich in einem Nockenwellenraum 25 eines Pumpengehäuses 26. Vom Zuschaltventil 16, welches zuströmseitig an die Niederdruckleitung 19 angeschlossen ist, führt eine Zuführleitung 27 in den Nockenwellenraum 25 und eine Rückführleitung 28 zur Saugleitung 17 der Niederdruckpumpe 11. Der Nockenwellenraum 25 wiederum ist auslaßseitig an die Tankablaufleitung 21 angeschlossen.The high-pressure pump 12 is a radial piston pump by design with several pump elements 23, of which in FIG. 1 only one element is shown. To drive the Pump elements 23 serve a camshaft 24 (or a Eccentric shaft or crankshaft). The camshaft 24 is located itself in a camshaft space 25 of a pump housing 26. From the cut-in valve 16, which on the inflow side to the Low pressure line 19 is connected, leads Supply line 27 in the camshaft space 25 and one Return line 28 to suction line 17 of the low pressure pump 11. The camshaft chamber 25 is in turn on the exhaust side Tank drain line 21 connected.

Das in Figur 2 dargestellte Ausführungsbeispiel des Zuschaltventils 16 zeigt ein als hohlzylindrisches Einschraubteil ausgebildetes, überwiegend in einer Sacklochbohrung 31 des Pumpengehäuses 26 der Hochdruckpumpe 25 aufgenommenes Ventilgehäuse 32, in dessen gestufter Durchgangsbohrung 33 ein längsbewegbarer Ventilkolben 34, eine achsgleich hintereinander angeordnete Schraubendruckfeder 35 und eine die Durchgangsbohrung 33 nach außen druckdicht abschließende Kugel 36 aufgenommen sind. Das Ventilgehäuse 32 weist einen Außengewindeabschnitt 37 auf, mit dem es unter Angriff an einem ventilgehäuseseitigen Sechskant 38 in die Sacklochbohrung 31 eingeschraubt ist. In der gezeichneten Stellung des Ventilgehäuses 32 greift dessen in der Zeichnung unten befindliche Stirnfläche 39 am Bohrungsgrund 40 der Sacklochbohrung 31 an. Seitens der Mündung 41 der Sacklochbohrung 31 ist das Ventilgehäuse 32 mit einem Dichtring 42 abgedichtet.The embodiment shown in Figure 2 Connection valve 16 shows a hollow cylindrical one Screw-in part designed, mainly in one Blind hole 31 of the pump housing 26 of the high pressure pump 25 received valve housing 32, in its stepped Through bore 33 a longitudinally movable valve piston 34, an axially arranged one behind the other Helical compression spring 35 and a through hole 33 outwardly sealed ball 36 are. The valve housing 32 has an externally threaded section 37 on which it is under attack on one hexagon 38 on the valve housing into the blind hole 31 is screwed in. In the drawn position of the Valve housing 32 engages in the drawing below located end face 39 at the bottom 40 of the hole Blind hole 31 on. On the part of the mouth 41 of the Blind hole 31 is the valve housing 32 with a Sealing ring 42 sealed.

Das Ventilgehäuse 32 ist zwischen dem Dichtring 42 und dem Bohrungsgrund 40 mit zwei die Durchgangsbohrung 33 kreuzenden Querbohrungen 45 und 46 versehen. Die dichtringseitige Querbohrung 45 steht mit einer ersten Abströmbohrung 47 des Pumpengehäuses 26 in Verbindung. Die erste Abströmbohrung 47 ist Teil der Zuführleitung 27 zum Nockenwellenraum 25 der Hochdruckpumpe 12 (siehe Figur 1). Die zweite, dichtringferne Querbohrung 46 des Ventilgehäuses 32 steht mit einer zweiten Abströmbohrung 48 des Pumpengehäuses 26 in Verbindung. Die zweite Abströmbohrung 48 ist Teil der zur Saugseite der Niederdruckpumpe 11 führenden Rückführleitung 28. Stirnseitig des Ventilgehäuses 32 steht eine Zuströmbohrung 49 mit der Durchgangsbohrung 33 in Verbindung. Die Zuströmbohrung 49 ist an die von der Niederdruckpumpe 11 zur Hochdruckpumpe 12 führende Niederdruckleitung 19 angeschlossen. Die zweite Abströmbohrung 48 ist durch den dichten Angriff des Ventilgehäuses 32 am Bohrungsgrund 40 völlig von der Zuströmbohrung 49 getrennt. Eine ausreichende hydraulische Abdichtung ist zwischen der ersten Abströmbohrung 47 und der zweiten Abströmbohrung 48 durch die Schraubverbindung (Außengewindeabschnitt 37) zwischen dem Ventilgehäuse 32 und dem Pumpengehäuse 26 erzielt.The valve housing 32 is between the sealing ring 42 and the Bore bottom 40 with two through holes 33 crossing cross holes 45 and 46 provided. The Sealing ring-side cross bore 45 is with a first Outflow bore 47 of the pump housing 26 in connection. The first outflow bore 47 is part of the feed line 27 to Camshaft chamber 25 of the high pressure pump 12 (see Figure 1). The second transverse bore 46 of the valve housing remote from the sealing ring 32 stands with a second outflow bore 48 Pump housing 26 in connection. The second drain hole 48 is part of the suction side of the low pressure pump 11 leading return line 28. Face of the valve housing 32 there is an inflow bore 49 with the through bore 33 in connection. The inflow bore 49 is to that of the Low pressure pump 11 leading to high pressure pump 12 Low pressure line 19 connected. The second Outflow bore 48 is due to the dense attack of the Valve housing 32 on the bottom 40 of the hole completely Inflow bore 49 separated. Adequate hydraulic Sealing is between the first outflow bore 47 and the second outflow bore 48 through the screw connection (Male thread section 37) between the valve housing 32 and achieved the pump housing 26.

Der hülsenförmig ausgebildete Ventilkolben 34 ist passend in der Durchgangsbohrung 33 des Ventilgehäuses 32 aufgenommen. In der Ruhestellung des Zuschaltventils 16 ist der Ventilkolben 34 mit einem umfangsseitig angeordneten Sprengring 51 an einer Stufe 52 der Durchgangsbohrung 33 aufgrund der Federkraft der am Ventilkolben angreifenden Schraubendruckfeder 35 abgestützt. Deren Vorspannung ist durch entsprechend tiefes Einpressen der Kugel 36 in die Durchgangsbohrung 33 eingestellt. Der Ventilkolben 34 hat in seinem federseitigen Kolbenboden 53 eine Drosselbohrung 54, durch welche der federseitige Abschnitt der Durchgangsbohrung 33 mit dem Innenraum 55 des Ventilkolbens 34 in Verbindung steht. Umfangsseitig hat der Ventilkolben 34 eine Ringnut 56, welche durch eine oder mehrere Drosselbohrungen 57 mit dem Innenraum 55 verbunden ist. Die Ringnut 56 des Ventilkolbens 34 bildet eine erste Steuerkante 58, der seitens der Stufe 52 der Durchgangsbohrung 33 eine hohlkegelförmige erste Steuerkontur 59 des Ventilgehäuses 32 zugeordnet ist. Der Ventilkolben 34 hat an seiner federabgewandten Stirnseite eine zweite Steuerkante 60, welche mit der eine zweite Steuerkontur 61 bildenden Querbohrung 46 des Ventilgehäuses 32 zusammenwirkt.The sleeve-shaped valve piston 34 is suitable in the through hole 33 of the valve housing 32 is added. In the rest position of the connecting valve 16 is the Valve piston 34 with a circumferentially arranged Snap ring 51 on a step 52 of the through hole 33 due to the spring force of those acting on the valve piston Helical compression spring 35 supported. Their bias is by correspondingly deeply pressing the ball 36 into the Through hole 33 set. The valve piston 34 has in its spring-side piston head 53 has a throttle bore 54, through which the spring section of the Through hole 33 with the interior 55 of the valve piston 34 communicates. The valve piston has a circumference 34 an annular groove 56, which by one or more Throttle bores 57 is connected to the interior 55. The Annular groove 56 of the valve piston 34 forms a first Control edge 58, the level 52 of the Through hole 33 is a hollow cone-shaped first Control contour 59 of the valve housing 32 is assigned. The Valve piston 34 has on its end facing away from the spring a second control edge 60, which with the second Control contour 61 forming transverse bore 46 of the valve housing 32 cooperates.

In der gezeichneten Ruhestellung des Zuschaltventils 16 sperrt der Ventilkolben 34 die Verbindung zwischen der Zuströmbohrung 49 durch die Drosselbohrung 57 zur ersten Abströmbohrung 47 sowie von der Zuströmbohrung 49 zur zweiten Abströmbohrung 48 ab. Die Zuströmbohrung 49 ist jedoch ständig durch die Drosselbohrung 54 im Kolbenboden 53 mit dem Nockenwellenraum 25 der Hochdruckpumpe 12 verbunden. Bei Anlauf der Niederdruckpumpe 11 kann im Niederdrucksystem befindliche Luft durch die Drosselbohrung 54 im Kolbenboden 56 des Ventilkolbens 34 durch die erste Abströmbohrung 47 in den Nockenwellenraum 25 und von diesem durch die Tankablaufleitung 21 abströmen. Hiermit wird eine Entlüftung des Niederdrucksystems wirkungsvoll erzielt.In the drawn rest position of the connecting valve 16 the valve piston 34 blocks 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 second outflow bore 48. The inflow hole 49 is however, constantly through the throttle bore 54 in the piston crown 53 connected to the camshaft chamber 25 of the high pressure pump 12. When the low pressure pump 11 starts, the low pressure system Air located through the throttle bore 54 in the piston crown 56 of the valve piston 34 through the first outflow bore 47 in the camshaft space 25 and from this through the Drain the tank drain line 21. This is a vent of the low pressure system effectively achieved.

Mit ansteigendem Förderdruck des durch die Niederdruckpumpe 11 aus dem Tank 18 entnommenen und durch die Zuströmbohrung 49 dem Zuschaltventil 16 zugeführten Kraftstoffs wird der Ventilkolben 34 aus seiner Ruhestellung entgegen der Federkraft der Druckfeder 35 verschoben. Bei Überschreiten einer ersten Druckschwelle gelangt die erste Steuerkante 58 des Ventilkolbens 34 in den Bereich der Steuerkontur 59, so daß ein Kraftstoffstrom von der Zuströmbohrung 49 durch die Drosselbohrung 57 des Ventilkolbens 34 zur ersten Abströmbohrung 47 und weiter in den Nockenwellenraum 25 der Hochdruckpumpe 12 fließen kann. Das Zuschaltventil 16 wirkt bei kleinem Hub des Ventilkolbens 34 als Stromregelventil, mit dem ein zur Schmierung und Kühlung der Hochdruckpumpe 12 ausreichender Kraftstoff-Volumenstrom eingestellt wird. Zu diesem ist die durch die parallel zur Drosselbohrung 57 verlaufende Drosselbohrung 54 im Kolbenboden 53 gelangende Teilkraftstoffmenge hinzuzurechnen.With increasing delivery pressure of the low pressure pump 11 removed from the tank 18 and through the inflow hole The fuel supplied to the switching valve 16 becomes the Valve piston 34 from its rest position against the Spring force of the compression spring 35 shifted. If exceeded the first control edge 58 reaches a first pressure threshold of the valve piston 34 in the area of the control contour 59, so that a fuel 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 space 25 of the High pressure pump 12 can flow. The connecting valve 16 acts with a small stroke of the valve piston 34 as a flow control valve, with the one for lubricating and cooling the high pressure pump 12 sufficient fuel volume flow is set. To this is due to the parallel to the throttle bore 57 throttle bore 54 extending in the piston crown 53 Add partial fuel quantity.

Mit weitersteigendem Förderdruck der Niederdruckpumpe 11 gibt der in Richtung auf die Kugel 36 längsverschobene Ventilkolben 34 mit Überschreiten einer gegenüber der ersten Druckschwelle höheren zweiten Druckschwelle mit seiner zweiten Steuerkante 60 die Querbohrung 46 des Ventilgehäuses 32 frei. Von der Hochdruckpumpe 12 nicht abgenommener Kraftstoff wird durch die zweite Abströmbohrung 48 und die Rückführleitung 28 unmittelbar zur Saugseite der Niederdruckpumpe 11 abgesteuert. Das Zuschaltventil 16 wirkt nun zusätzlich als Druckregelventil, mit dem der zuströmseitige Druck weitgehend schwankungsfrei gehalten wird. Die Druckregelung wirkt sich in vorteilhafter Weise auf das Mengen-Regelventil 15 aus, weil ein diesem Ventil druckschwankungsarm zugeführter Kraftstoff dessen Arbeitsweise unterstützt.As the delivery pressure of the low-pressure pump 11 increases there is the longitudinally displaced towards the ball 36 Valve piston 34 with one exceeding the first Pressure threshold higher second pressure threshold with its second control edge 60, the transverse bore 46 of the valve housing 32 free. Not removed from the high pressure pump 12 Fuel is through the second outflow bore 48 and Return line 28 directly to the suction side of the Low pressure pump 11 shut down. The connecting valve 16 acts now additionally as a pressure control valve with which the upstream pressure kept largely free of fluctuations becomes. The pressure control has an advantageous effect on the flow control valve 15 because of this valve Fuel supplied with little pressure fluctuation Working method supports.

Claims (5)

  1. Cut-in valve (16) in a fuel injection system (10) for internal combustion engines with a low-pressure pump (11) for extracting fuel from a tank (18) and with a high-pressure pump (12) fed by the low-pressure pump (11) and having camshaft-actuated pump elements (23), the cut-in valve (16) having a sleeve-shaped valve piston (34) which is longitudinally moveable by the pressure of the low-pressure pump (11) and is loaded by a prestressed helical compression spring (35), has a throttle bore (54) in the piston bottom (53) and, in the case of a predetermined pressure threshold of the fuel conveyed by the low-pressure pump (11), opens an outflow bore (48) in a valve housing (32) guiding the piston (54), the throttle bore (54) being constantly connected on the outflow side to a space (25) of a housing (26) of the high-pressure pump (12), said space containing the camshaft (24) and being connected to the fuel tank (18), characterized in that, in the case of a first pressure threshold, the valve piston (34) controls a connection (49, 55, 57, 45, 47), running parallel to the throttle bore (54), between the low-pressure pump (11) and the camshaft space (25) of the high-pressure pump (12) and, in the case of a second pressure threshold higher than the first, opens the outflow bore (48) which is connected directly to the suction side of the low-pressure pump (11).
  2. Valve according to Claim 1, characterized in that, when the first pressure threshold is exceeded, the valve piston (34) operates, in cooperation with a first controlled contour (59) of the valve housing (32), as a flow-regulating valve and, when the second pressure threshold is exceeded, said valve piston performs, in cooperation with a second controlled contour (61) of the valve housing (32), a pressure-regulating function.
  3. Valve according to Claim 2, characterized by the further features:
    the valve housing (32) is received in the housing (26) of the high-pressure pump (12);
    the valve housing (32) is a hollow-cylindrical screw-in part;
    the valve piston (34) and the compression spring (35) are received in its passenger bore (33)
    coaxially one behind the other, the throttle bore (54) of the piston (34) being arranged on the spring side;
    the passenger bore (33) is connected, facing away from the spring, to an inflow bore (49) connected to the delivery side of the low-pressure pump (11);
    the passenger bore (33) is connected on the spring side to the camshaft space (25) of the high-pressure pump (12) by means of a first transverse bore (45);
    the passenger bore (33) is crossed, facing away from the spring, by the second transverse bore (46) connected to the suction side of the low-pressure pump (11) and having the second control contour(61).
  4. Valve according to Claim 3, characterized in that the valve piston (34) is supported, under the prestressing force of the compression spring (35), on a step (52) of the passenger bore (33) of the valve housing (32), and the prestressing force of the compression spring (35) is set by means of a ball (36) pressed, pressure-tight, into the passenger bore (33).
  5. Valve according to Claim 3, characterized in that the valve housing (32) is arranged in a blind-hole bore (31) and, with its end face (39) engaging on the bottom (40) of the blind-hole bore (31), separates the inflow bore (49) from the outflow bore (48) continued in the pump housing (26), in that the valve housing (32) has an externally threaded portion (37) which extends between the first transverse bore (45) and the second transverse bore (46) and by means of which said valve housing is fastened in the pump housing (26), and in that the valve housing (32) is sealed off relative to the pump housing (26) by means of a sealing ring (42) between the first transverse bore (45) and the mouth (41) of the blind-hole bore (31).
EP98966770A 1998-04-24 1998-12-10 Sequence valve in a fuel injection system for internal combustion engines Expired - Lifetime EP1073840B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19818385 1998-04-24
DE19818385A DE19818385A1 (en) 1998-04-24 1998-04-24 Connecting valve for fuel injection system of internal combustion engine
PCT/DE1998/003628 WO1999056016A1 (en) 1998-04-24 1998-12-10 Sequence valve in a fuel injection system for internal combustion engines

Publications (2)

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

Family

ID=7865693

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98966770A Expired - Lifetime EP1073840B1 (en) 1998-04-24 1998-12-10 Sequence valve in a fuel injection system for internal combustion engines

Country Status (5)

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

Families Citing this family (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19858084C1 (en) * 1998-12-16 2000-04-20 Siemens Ag Injection system with common rail high pressure pump, especially for vehicle internal combustion engine
IT1308780B1 (en) 1999-07-02 2002-01-10 Elasis Sistema Ricerca Fiat HIGH PRESSURE PUMP EQUIPPED WITH INTERCEPTION VALVE FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE.
DE19954695A1 (en) * 1999-11-13 2001-05-23 Bosch Gmbh Robert Fuel injection system
IT1310754B1 (en) * 1999-11-30 2002-02-22 Elasis Sistema Ricerca Fiat VALVE SYSTEM FOR INLET PRESSURE CONTROL OF A LIQUID IN A HIGH PRESSURE PUMP, AND RELATED VALVE
IT1310755B1 (en) * 1999-11-30 2002-02-22 Elasis Sistema Ricerca Fiat HIGH PRESSURE HYDRAULIC PUMP, IN PARTICULAR RUBBER PISTON PUMP FOR THE FUEL OF AN INTERNAL COMBUSTION ENGINE.
DE10009182C2 (en) * 2000-02-26 2003-12-18 Daimler Chrysler Ag Method for controlling or regulating the power of an internal combustion engine
DE10057786A1 (en) 2000-11-22 2002-06-06 Siemens Ag Injection system for an internal combustion engine and method for regulating and / or venting such an injection system
DE10061296A1 (en) * 2000-12-08 2002-06-27 Siemens Ag Injection system for internal combustion engine has second choke for venting injection system designed to pass volumetric fuel flow at specified rate
DE10153185A1 (en) * 2001-10-27 2003-05-15 Bosch Gmbh Robert Fuel injection system with improved delivery control
EP1321663A3 (en) * 2001-12-19 2003-07-02 Robert Bosch Gmbh Fuel injection device for an internal combustion engine
US20040101420A1 (en) * 2002-11-18 2004-05-27 Breeden Robert H. Solenoid regulated pump assembly
DE10260174A1 (en) * 2002-12-20 2004-07-08 Robert Bosch Gmbh Piston pump, in particular high-pressure fuel pump for internal combustion engines with direct injection
DE10358864A1 (en) * 2003-12-16 2005-07-14 Volkswagen Ag Fuel supply device for an internal combustion engine and method for operating this
US20070272217A1 (en) * 2004-02-06 2007-11-29 Bosch Corporation Fuel Supply Device
ATE468486T1 (en) * 2005-12-27 2010-06-15 Fiat Ricerche HIGH PRESSURE FUEL PUMP, WITH THE FUEL LINE IN CONNECTION WITH THE PUMP SUMP
SI22392B (en) * 2006-09-27 2013-04-30 Tajfun Planina Proizvodnja Strojev, D.O.O. Hydraulic aggregate for supply and control of smaller hydraulic consumers, particularly brake and clutch in forestry winch
JP2008169746A (en) * 2007-01-11 2008-07-24 Denso Corp Fuel supply device
DE102007052665A1 (en) * 2007-11-05 2009-05-07 Robert Bosch Gmbh Fuel overflow valve for a fuel injector and fuel injector with fuel spill valve
ITMI20072219A1 (en) * 2007-11-23 2009-05-24 Bosch Gmbh Robert OVERPRESSURE VALVE AND HIGH PRESSURE PUMP INCLUDING THIS PRESSURE VALVE
DE102008045193A1 (en) * 2008-08-30 2010-03-04 Man Diesel Se Fuel supply system i.e. common rail fuel supply system, for marine diesel internal combustion engine, has region maintaining emergency operating pressure through casing and separated from low pressure region by check valve
FR2935771B1 (en) * 2008-09-09 2010-10-08 Bontaz Centre Sa DEVICE FOR CONTROLLING THE SUPPLY OF A SYSTEM WITH A FLUID
DE102009001563A1 (en) * 2009-03-16 2010-09-23 Robert Bosch Gmbh high pressure pump
IT1395733B1 (en) * 2009-08-03 2012-10-19 Bosch Gmbh Robert OVERPRESSURE VALVE FOR A FUEL SUPPLY SYSTEM FROM A TANK TO AN INTERNAL COMBUSTION ENGINE, AND FUEL SUPPLY SYSTEM FROM A TANK TO AN INTERNAL COMBUSTION ENGINE PROVIDED WITH THIS OVERPRESSURE VALVE
DE102010001834A1 (en) * 2010-02-11 2011-08-11 Robert Bosch GmbH, 70469 Method for supplying a high-pressure pump in a fuel injection system of an internal combustion engine with fuel and fuel injection system
DK177283B1 (en) * 2010-02-24 2012-10-08 Man Diesel & Turbo Deutschland Valve arrangement
DE102011003362A1 (en) * 2011-01-31 2012-08-02 Robert Bosch Gmbh Overflow valve for a fuel injection system and fuel injection system with overflow valve
ITMI20110966A1 (en) * 2011-05-27 2012-11-28 Bosch Gmbh Robert PUMPING GROUP FOR FOOD FUEL, PREFERIBLY GASOIL, FROM A CONTAINMENT TANK TO AN INTERNAL COMBUSTION ENGINE
US20140234132A1 (en) * 2011-09-02 2014-08-21 Alfmeier Prazision Ag Baugruppen Und Systemlosungen Pump, In Particular Pneumatic Pump
DE102015208934A1 (en) 2014-05-13 2015-11-19 Robert Bosch Gmbh SPRING-LOADED COMPONENT MOUNTING WITHIN FUEL TANK
DE102016208427A1 (en) * 2016-05-17 2017-11-23 Robert Bosch Gmbh Overflow valve for a high-pressure pump, high-pressure pump and method for operating an overflow valve
IT201700080520A1 (en) * 2017-07-17 2019-01-17 Bosch Gmbh Robert PUMPING GROUP FOR FUEL SUPPLEMENTATION, PREFERABLY GASOIL, TO AN INTERNAL COMBUSTION ENGINE
CN117065489B (en) * 2023-10-17 2023-12-15 四川铸创安全科技有限公司 Spray type dust fall device

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2742054A (en) * 1954-02-05 1956-04-17 Consolidation Coal Co Spring biased safety valve with spring bias relieving means
DE4126640B4 (en) * 1991-08-12 2005-06-16 Robert Bosch Gmbh Pump arrangement with a prefeed pump and a radial piston pump
DE4401074B4 (en) 1994-01-15 2007-01-18 Robert Bosch Gmbh Pump arrangement, in particular for conveying fuel from a reservoir to an internal combustion engine
JP3842331B2 (en) * 1995-05-26 2006-11-08 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング FUEL SUPPLY DEVICE FOR FUEL SUPPLY FOR INTERNAL COMBUSTION ENGINE AND METHOD FOR OPERATING INTERNAL COMBUSTION ENGINE
DE19634899A1 (en) * 1996-08-29 1998-03-05 Bosch Gmbh Robert Low pressure regulating valve for diesel internal combustion engines
JP3237549B2 (en) * 1996-11-25 2001-12-10 トヨタ自動車株式会社 High pressure fuel supply system for internal combustion engine
JP3183203B2 (en) * 1996-12-18 2001-07-09 トヨタ自動車株式会社 High pressure fuel injection system for internal combustion engines
DE19746563A1 (en) * 1997-10-22 1999-04-29 Bosch Gmbh Robert Fuel injection system for IC engine
JPH11200990A (en) * 1998-01-07 1999-07-27 Unisia Jecs Corp Fuel injection controller
DE19834121A1 (en) * 1998-07-29 2000-02-03 Bosch Gmbh Robert Fuel supply system of an internal combustion engine
US5937896A (en) * 1998-08-07 1999-08-17 Mitsubishi Denki Kabushiki Kaisha Check valve and seating valve
JP3389863B2 (en) * 1998-08-11 2003-03-24 トヨタ自動車株式会社 Fuel injection control device for internal combustion engine
JP2000265926A (en) * 1999-03-12 2000-09-26 Bosch Automotive Systems Corp Fuel feed pump
JP2000291509A (en) * 1999-04-01 2000-10-17 Mitsubishi Electric Corp Fuel supply device for direct injection type gasoline engine
JP3633388B2 (en) * 1999-08-04 2005-03-30 トヨタ自動車株式会社 High pressure fuel pump control device for internal combustion engine
JP3539302B2 (en) * 1999-09-09 2004-07-07 トヨタ自動車株式会社 Fuel supply device for internal combustion engine

Also Published As

Publication number Publication date
DE59804470D1 (en) 2002-07-18
EP1073840A1 (en) 2001-02-07
JP2002513115A (en) 2002-05-08
DE19818385A1 (en) 1999-10-28
WO1999056016A1 (en) 1999-11-04
US6422212B1 (en) 2002-07-23
JP4280419B2 (en) 2009-06-17

Similar Documents

Publication Publication Date Title
EP1073840B1 (en) Sequence valve in a fuel injection system for internal combustion engines
DE4400213C2 (en) Fuel valve device
DE102004013307B4 (en) High-pressure fuel pump with a pressure relief valve
DE10103112B4 (en) Fuel pressure regulator
EP3059439B1 (en) Pump unit for a high-pressure pump
DE3732259A1 (en) METHOD AND DEVICE FOR INJECTING FUEL INTO AN INTERNAL COMBUSTION ENGINE
DE102005033638A1 (en) Fuel conveyor, in particular for an internal combustion engine
EP1141539B1 (en) Piston pump for high-pressure fuel generation
EP2798191A1 (en) Fuel overflow valve for a fuel injection device, and fuel injection device comprising fuel overflow valve
EP1357283B1 (en) Fuel injection system for internal combustion engine
EP2807365A1 (en) High-pressure fuel pump for an injection system
WO2011131448A1 (en) Pump assembly
EP1262658B1 (en) Fuel system for supplying fuel for an internal combustion engine
DE10139055A1 (en) Method, computer program, control and / or regulating device and fuel system for an internal combustion engine
EP1312791A2 (en) High pressure fuel pump with vented membrane accumulator
EP2835526B1 (en) Valve assembly for a fuel supply system and fuel supply system
WO2002103197A1 (en) Fuel injection device for an internal combustion engine
EP1537334B1 (en) Pump, especially for a fuel injection device for an internal combustion engine
WO2004027250A1 (en) Fuel injection unit for internal combustion engines
DE10108175C1 (en) High pressure fuel pump, for an internal combustion engine, has membrane of store controlling 2/2 path valve
EP1203882A2 (en) Injector
EP1275843A2 (en) Internal combustion engine for motor vehicle
EP1383999B1 (en) Fuel injection device for an internal combustion engine
EP1284360B1 (en) Fuel injection device for an internal combustion engine
DE10122242A1 (en) Accumulator injection system (common rail) for internal combustion engines

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20001124

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 20010919

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 59804470

Country of ref document: DE

Date of ref document: 20020718

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20020912

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20030313

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20121218

Year of fee payment: 15

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20131210

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131210

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20141218

Year of fee payment: 17

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 18

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 19

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20151210

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20171219

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20180223

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59804470

Country of ref document: DE