EP1073840A1 - Sequence valve in a fuel injection system for internal combustion engines - Google Patents

Sequence valve in a fuel injection system for internal combustion engines

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)
French (fr)
Other versions
EP1073840B1 (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

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

The invention relates to a fuel injection system having a low pressure pump to extract fuel from a tank and a high pressure pump with pump elements actuated by a camshaft and fed by the low pressure pump. A sequence valve (16) is connected to the high pressure pump on the inlet side (inlet port 49) as well as to the camshaft area of the high pressure pump on the outlet side and to the suction side of the low pressure pump (outlet port 47). A spring-loaded valve piston (34) of the sequence valve (16) releases a connection between the low pressure pump and the camshaft area when a first pressure threshold is reached and a releases a connection between the pressure side and the suction side of the low pressure pump when a second pressure threshold is reached that is higher than the first pressure threshold. A throttle orifice (54) at the bottom (53) of the valve piston (34) serves to air bleed the low pressure system. The invention cab be used in direction-injection diesel engines.

Description

Zuschaltventil in einem Kraf stoffeinspritzsystem für BrennkraftmaschinenConnection valve in a fuel injection system for internal combustion engines
Stand der TechnikState of the art
Die Erfindung geht aus von einem Zuschaltventil nach der Gattung des Patentanspruchs 1.The invention relates to a connecting valve according to the preamble of patent claim 1.
Es ist schon ein Kraftstoffeinspritzsystem für Brennkraftmaschinen mit einer Kraftstoff aus einem Tank saugenden und an eine Hochdruckpumpe förderndenIt is already a fuel injection system for internal combustion engines with a fuel that sucks fuel from a tank and delivers it to a high-pressure pump
Niederdruckpumpe bekannt (DE 44 01 074 AI) . 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 .Low pressure pump known (DE 44 01 074 AI). In the connecting line between the two pumps there is 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.
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. - 2 -The 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 -
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 Kraftstoffström eine unwirtschaftliche Betriebsweise der Niederdruckpumpe zur Folge hat .The 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. On the other hand, the throttle bore supplies the camshaft chamber with fuel that serves as a lubricant. In addition, 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, however, 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.
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 niederdruckseitigenThe 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
Kraftstoffeinspritzsystemteils und der Bemessung des SchmierstoffStromes zu der Nockenwelle der Hochdruckpumpe auch die Absteuerung des nicht von der Hochdruckpumpe abgenommenen Kraftstoff-Volumenstroms unmittelbar zurFuel 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
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 zweitenEnsures the suction side of the low pressure pump. The 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
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.Circulation remains largely unaffected. In addition, 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.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Patentanspruch 1 angegebenen Zuschaltventils möglich.The measures listed in the subclaims allow advantageous developments and improvements of the connecting valve specified in claim 1.
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 dieThe design of the 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
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.Hydraulic connections between the pump housing and the camshaft chamber and the suction side of the low-pressure pump are sufficiently separated. The connecting valve can thus 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 shown in simplified form in the drawing and explained in more detail in the following description. 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, and FIG. 2 shows the cut-in 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 - 4 -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 -
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.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.
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, 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.
Das in Figur 2 dargestellte Ausführungsbeispiel des Zuschaltventils 16 zeigt ein als hohlzylindrisch.es Einschraubteil ausgebildetes, überwiegend in einer - 5 -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 -
Sacklochbohrung 31 des Pumpengehäuses 26 der Hochdruckpumpe 25 aufgenommenes Ventilgehause 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 ventilgehauseseitigen Sechskant 38 in die Sacklochbohrung 31 eingeschraubt ist. In der gezeichneten Stellung desBlind bore 31 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
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.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.
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 erstenThe 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
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 desOutflow bore 47 of the pump housing 26 in connection. 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
Pumpengehäuses 26 in Verbindung. Die zweite Abströmbohrung 48 ist Teil der zur Saugseite der Niederdruckpumpe 11 führenden Rückführleitung 28. Stirnseitig des Ventilgehauses 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 - 6 -Pump housing 26 in connection. The second outflow bore 48 is part of the return line 28 leading to the suction side of the low-pressure pump 11. At the front of the valve housing 32, 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 -
Abdichtung ist zwischen der ersten Abströmbohrung 47 und der zweiten Abströmbohrung 48 durch die Schraubverbindung (Außengewindeabschnitt 37) zwischen dem Ventilgehause 32 und dem Pumpengehäuse 26 erzielt.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.
Der hulsenförmig 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 derThe sleeve-shaped valve piston 34 is suitably received in the through bore 33 of the valve housing 32. 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
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 Ventilgehauses 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.Through hole 33 communicates with the interior 55 of 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.
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 dieIn the drawn rest position of the connecting valve 16, 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. However, 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. When the low-pressure pump 11 starts up, 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
Tankablaufleitung 21 abströmen. Hiermit wird eine Entlüftung des Niederdrucksystems wirkungsvoll erzielt.Drain the tank drain line 21. This effectively deaerates the low pressure system.
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 Kraftstoffström 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.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.
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 Zusehaltventil 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, 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.

Claims

Ansprüche Expectations
1. Zuschaltventil (16) in einem Kraftstoffeinspritzsystem (10) für Brennkraftmaschinen mit einer Niederdruckpumpe (11) zur Entnahme von Kraftstoff aus einem Tank (18) und einer von der Niederdruckpumpe (11) gespeisten Hochdruckpumpe (12) mit nockenwellenbetätigten Pumpenelementen (23), wobei das Zuschaltventil (16) einen hülsenförmigen, vom Druck der Niederdruckpumpe (11) längsbewegbaren Ventilkolben (34) hat, der von einer vorgespannten Schraubendruckfeder (35) belastet ist, eine Drosselbohrung (54) im Kolbenboden (53) aufweist und bei einer vorbestimmten Druckschwelle des von der Niederdruckpumpe (11) geförderten Kraftstoffs eine Abströmbohrung (48) in einem den Kolben (34) führenden Ventilgehäuse (32) freigibt, wobei die Drosselbohrung (54) abströmseitig ständig mit einem die Nockenwelle (24) enthaltenden Raum (25) eines Gehäuses (26) der Hochdruckpumpe (12) in Verbindung steht, der an den Kraftstofftank (18) angeschlossen ist, dadurch gekennzeichnet, daß der Ventilkolben (34) bei einer ersten Druckschwelle eine parallel zur Drosselbohrung (54) verlaufende Verbindung (49, 55, 57, 45, 47) zwischen der Niederdruckpumpe (11) und dem Nockenwellenraum (25) der Hochdruckpumpe (12) steuert und bei einer demgegenüber höheren zweiten Druckschwelle die - 10 -1. connecting valve (16) in a fuel injection system (10) for internal combustion engines with a low pressure pump (11) for taking fuel from a tank (18) and a high pressure pump (12) fed by the low pressure pump (11) with camshaft-operated pump elements (23), wherein the connecting valve (16) has a sleeve-shaped valve piston (34) which can be moved longitudinally by the pressure of the low-pressure pump (11) and which is loaded by a prestressed helical compression spring (35), has a throttle bore (54) in the piston crown (53) and at a predetermined pressure threshold of the fuel delivered by the low pressure pump (11) releases an outflow bore (48) in a valve housing (32) guiding the piston (34), the throttle bore (54) on the outflow side with a space (25) of a housing containing the camshaft (24) (26) of the high pressure pump (12) is connected, which is connected to the fuel tank (18), characterized in that the valve piston s (34) controls a connection (49, 55, 57, 45, 47) between the low-pressure pump (11) and the camshaft chamber (25) of the high-pressure pump (12) parallel to the throttle bore (54) at a first pressure threshold and, in contrast, controls one higher second pressure threshold - 10 -
Abströmbohrung (48) freigibt, die unmittelbar mit der Saugseite der Niederdruckpumpe (11) in Verbindung steht.Outflow bore (48) releases, which is directly connected to the suction side of the low pressure pump (11).
2. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß der Ventilkolben (34) mit Überschreiten der ersten Druckschwelle im Zusammenwirken mit einer ersten Steuerkontur (59) des Ventilgehäuses (32) als Stromregelventil arbeitet und mit Überschreiten der zweiten Druckschwelle im Zusammenwirken mit einer zweiten Steuerkontur (61) des Ventilgehäuses (32) eine Druckregelfunktion ausübt.2. Valve according to claim 1, characterized in that the valve piston (34) when the first pressure threshold is exceeded in cooperation with a first control contour (59) of the valve housing (32) works as a flow control valve and when the second pressure threshold is exceeded in cooperation with a second control contour (61) of the valve housing (32) exercises a pressure control function.
3. Ventil nach Anspruch 2, gekennzeichnet durch die weiteren Merkmale : das Ventilgehäuse (32) ist im Gehäuse (26) der Hochdruckpumpe (12) aufgenommen, das Ventilgeh use (32) ist ein hohlzylindrisch.es3. Valve according to claim 2, characterized by the further features: the valve housing (32) is accommodated in the housing (26) of the high-pressure pump (12), the Ventilgeh use (32) is a hohlzylindrisch.es
Einschraubteil , in seiner Durchgangsbohrung (33) sind der Ventilkolben (34) und die Druckfeder (35) achsgleich hintereinander aufgenommen, wobei die Drosselbohrung (54) des Kolbens (34) federseitig angeordnet ist, die Durchgangsbohrung (33) ist federabgewandt an eine mit der Druckseite der Niederdruckpumpe (11) in Verbindung stehende Zuströmbohrung (49) angeschlossen, die Durchgangsbohrung (33) steht federseitig durch eine erste Querbohrung (45) mit dem Nockenwellenraum (25) derScrew-in part, in its through-bore (33) the valve piston (34) and the compression spring (35) are accommodated one behind the other with the axis, the throttle bore (54) of the piston (34) being arranged on the spring side, the through-bore (33) is turned away from the spring with one The pressure side of the low pressure pump (11) is connected to the incoming flow bore (49), the through bore (33) is on the spring side through a first transverse bore (45) with the camshaft chamber (25)
Hochdruckpumpe (12) in Verbindung, die Durchgangsbohrung (33) ist federabgewandt von der mit der Saugseite der Niederdruckpumpe (11) in Verbindung stehenden, die zweite Steuerkontur (61) aufweisenden zweitenHigh-pressure pump (12) in connection, the through bore (33) is spring-facing away from the second control contour (61), which is connected to the suction side of the low-pressure pump (11)
Querbohrung (46) gekreuzt.Cross bore (46) crossed.
4. Ventil nach Anspruch 3, dadurch gekennzeichnet, daß der Ventilkolben (34) unter der Vorspannkraft der Druckfeder (35) an einer Stufe (52) der Durchgangsbohrung (33) des - 11 -4. Valve according to claim 3, characterized in that the valve piston (34) under the biasing force of the compression spring (35) at a step (52) of the through bore (33) of the - 11 -
Ventilgehäuses (32) abgestützt und die Vorspannkraft der Druckfeder (35) mit einer in die Durchgangsbohrung (33) druckdicht eingepreßten Kugel (36) eingestellt ist.Supported valve housing (32) and the biasing force of the compression spring (35) is adjusted with a ball (36) pressed into the through bore (33) in a pressure-tight manner.
5. Ventil nach Anspruch 3, dadurch gekennzeichnet, daß das Ventilgehäuse (32) in einer Sacklochbohrung (31) angeordnet ist und mit seiner am Grund (40) der Sacklochbohrung (31) angreifenden Stirnfläche (39) die Zuströmbohrung (49) von der im Pumpengehäuse (26) fortgeführten Abströmbohrung (48) trennt, daß das Ventilgehäuse (32) einen sich zwischen der ersten Querbohrung (45) und der zweiten Querbohrung (46) erstreckenden Außengewindeabschnitt (37) aufweist, mit dem es in dem Pumpengehäuse (26) befestigt ist, und daß das Ventilgehäuse (32) zwischen der ersten Querbohrung (45) und der Mündung (41) der Sacklochbohrung (31) mit einem Dichtring (42) gegen das Pumpengehäuse (26) abgedichtet ist. 5. Valve according to claim 3, characterized in that the valve housing (32) is arranged in a blind hole (31) and with its base (40) of the blind hole (31) engaging end face (39) the inflow bore (49) from the Pump housing (26) continued outflow bore (48) separates that the valve housing (32) has an external thread section (37) extending between the first transverse bore (45) and the second transverse bore (46), with which it is fastened in the pump housing (26) and that the valve housing (32) between the first transverse bore (45) and the mouth (41) of the blind bore (31) is sealed with a sealing ring (42) against the pump housing (26).
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)

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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

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

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JP (1) JP4280419B2 (en)
DE (2) DE19818385A1 (en)
WO (1) WO1999056016A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2863667A1 (en) * 2003-12-16 2005-06-17 Volkswagen Ag Fuel supply device for spark ignition engine with direct injection, has tubular duct with fuel return hole and pressure relief valve arranged on its one end, where valve acts as de-airing valve and drain valve of fuel distribution ramp

Families Citing this family (31)

* 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
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.
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
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
EP1712775A4 (en) * 2004-02-06 2010-01-20 Bosch Corp Fuel supply device
EP1803933B1 (en) * 2005-12-27 2010-05-19 C.R.F. Societa Consortile per Azioni High-pressure pump for a fuel, with sump in communication with the fuel inlet
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
CN103711682B (en) * 2011-09-02 2016-10-26 建筑组合及解决系统阿尔夫梅尔精密股份公司 Pump, particularly air driven 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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9956016A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2863667A1 (en) * 2003-12-16 2005-06-17 Volkswagen Ag Fuel supply device for spark ignition engine with direct injection, has tubular duct with fuel return hole and pressure relief valve arranged on its one end, where valve acts as de-airing valve and drain valve of fuel distribution ramp

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

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