EP3034858B1 - Relief valve for a fuel pump - Google Patents

Relief valve for a fuel pump Download PDF

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Publication number
EP3034858B1
EP3034858B1 EP15194022.8A EP15194022A EP3034858B1 EP 3034858 B1 EP3034858 B1 EP 3034858B1 EP 15194022 A EP15194022 A EP 15194022A EP 3034858 B1 EP3034858 B1 EP 3034858B1
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EP
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Prior art keywords
valve
section
piston
valve piston
fuel
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EP15194022.8A
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German (de)
French (fr)
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EP3034858A1 (en
Inventor
Achim Koehler
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0023—Valves in the fuel supply and return system
    • F02M37/0029—Pressure regulator in the low pressure fuel system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves

Definitions

  • overflow valves For controlling a fuel quantity supplied to the high-pressure pump, overflow valves are known in which a piston is arranged in a housing and an increase in pressure in the inlet causes a displacement of the piston, wherein a return opening on the housing of the overflow valve is released by the displacement of the piston and so the pressure and the amount in the inlet of the high-pressure fuel pump can be reduced.
  • WO 01/40656 A1 discloses a device for supplying fuel to an injection engine with a pressure relief valve.
  • DE 10 2010 063398 A1 discloses a fuel delivery device for a fuel injection device of an internal combustion engine, wherein in a low-pressure region, a pressure reduction device in the form of a Venturi tube is provided.
  • EP 2 159 406 A1 discloses a fuel pressure control system with a fuel pressure regulator.
  • an overflow valve in which a valve piston is slidably disposed in the valve housing and is supported on the valve housing via a spring.
  • a spring chamber is formed between the valve piston and the valve housing, wherein the spring chamber is connected via a throttle with a return of the low-pressure circuit to the fuel tank. If the valve piston is displaced by the valve spring from the valve housing in the direction of an inlet opening of the overflow valve, fuel from the low pressure circuit via the throttle can not flow fast enough into the spring chamber, so that a negative pressure forms, which leads to a vapor bubble in the spring chamber.
  • This vapor bubble is desirable because it facilitates the displacement of the valve piston in the direction of the spring chamber in the further operation of the spill valve and acts as a hydraulic damping element, so that little or no pressure fluctuations in the return of the low pressure circuit through the valve piston via the throttle displaced fuel quantity to be induced.
  • a disadvantage of such a solution is that the vapor bubble is relatively unstable and weak, so that sufficient damping can not be ensured in all operating conditions with increasing demands in terms of pressure and injection quantity tolerances.
  • the object of the invention is to develop an overflow valve such that the movement of the valve piston and a hydraulic damping in the spring chamber can be improved.
  • the object is achieved with an overflow valve having the features of claim 1.
  • the solution according to the invention has the advantage over the prior art that the valve piston has a radial bore in the form of a Venturi nozzle, comprising a first section with a tapering cross section, a second section with a smallest cross section and a third section with a widening one Cross-section, wherein the second portion is connected via a channel hydraulically connected to the spring chamber.
  • the fuel flowing through the venturi nozzle generates a negative pressure in the second section of the nozzle, whereby the negative pressure causes fuel to escape from the spring chamber is sucked through the channel, so that a negative pressure is generated in the spring chamber, which favors the formation of a vapor volume.
  • the hydraulic damping of the overflow valve is improved and the mobility of the valve body is increased, so that a more accurate and better control of the inlet pressure and the feed rate to the high-pressure pump is possible.
  • an at least partially circumferential groove is formed on the valve piston.
  • the at least partially circumferential groove always has an overlap with at least one of the at least one diversion bore. This further facilitates the outflow of the fuel exiting the venturi nozzle and further increases the flow velocity in the venturi nozzle.
  • the negative pressure in the second section of the Venturi nozzle and the associated suction power from the spring chamber are further increased.
  • valve piston has an inlet opening of the valve housing facing end face, wherein the end face hydraulically via an inlet bore to the first portion of Venturi nozzle is connected.
  • the first portion is directly connected to the region of highest pressure in the spill valve, so that the amount of fuel entering the venturi nozzle is increased.
  • This step increases the flow rate through the Venturi nozzle and thus the negative pressure in the second region of the nozzle, whereby the extraction of the fuel from the spring chamber is favored.
  • a further advantageous development consists in that a plurality of diversion bores distributed over the circumference are formed on the valve housing. As a result, with a slight displacement of the valve piston, a comparatively large hydraulic cross section can be opened to the return, whereby the pressure regulation of the pressure regulating valve is improved. Particularly advantageous are four evenly distributed over the circumference of the valve housing Ab Kunststoffbohrept, which are located on a common bolt circle. As a bolt circle is to be understood a connection line which connects the centers of Abêtbohronne together.
  • the at least partially circumferential groove comprises an angular range of at least 100 °.
  • a further advantageous development is that on an outer surface of the valve piston, an inlet opening for the first portion of the Venturi nozzle is formed, wherein the inlet opening is partially or completely blocked by a cover. This prevents that the fuel supplied via the end face of the valve piston at least partially exits laterally from the inlet opening of the first section of the Venturi nozzle. Thereby, a main flow direction from the first portion of the Venturi nozzle is ensured in the direction of the third portion, so that the negative pressure in the second portion is increased and thus the suction of fuel from the spring chamber is improved.
  • valve piston has an end face facing away from an inlet opening in the valve housing, the opposite end face having a cup-shaped recess for receiving the valve spring.
  • a further advantageous development is that a throttle is formed on the valve housing in the region of the spring chamber.
  • Fig. 1 is an inventive overflow valve 10 includes a valve housing 12 and a valve piston 14 which is slidably disposed in the valve housing 12.
  • the valve housing 12 has at least one inlet opening 31, with which the overflow valve 10 can be connected to a fuel supply and at least one, preferably at least two, more preferably four evenly distributed over the circumference of the valve housing 12, Abêtbohrung (s) 17, with which the fuel from the spill valve 10 can flow back into a low-pressure circuit of a fuel injection system.
  • the valve piston 14 is supported via a valve spring 16 on the valve housing 12, so that between the valve piston 14 and the valve housing 12, a spring chamber 15 is formed.
  • a throttle 37 is formed in the region of the spring chamber 15, which is also connected to the low-pressure circuit of the fuel injection system is formed.
  • a radial bore 18 in the form of a Venturi nozzle 19 is formed on the valve piston 14, a radial bore 18 in the form of a Venturi nozzle 19 is formed.
  • the Venturi nozzle 19 has a first portion 21, in which the cross section of the radial bore 18 tapers in the flow direction, a second portion 22, in which the radial bore 18 has the smallest flow cross-section, and a third portion 23, in which the cross section of the radial bore 18 is expanded in the flow direction. From the second section 22, a channel 24 leads into the spring chamber 15, so that the Venturi nozzle 19 and the spring chamber 15 are hydraulically connected.
  • the valve piston 14 has, on its end face 28 facing the inlet opening 31, an inlet bore 25 which connects the end face 28 hydraulically to the first section 21 of the venturi nozzle 19.
  • a leakage gap 11 is formed, can flow through the fuel from the inlet opening 31 into the spring chamber 15. Since the leakage gap 11 is formed narrow, the spring chamber 15 inflowing amount of fuel is limited.
  • a cup-shaped recess 39 for receiving the valve spring 16 is provided on the valve piston 14, from its end face 38 remote from the inlet opening 31.
  • a circumferential groove 27 is further formed on a lateral surface 33, which revolves around the valve piston 14 at the level of an inlet opening 34 or an outlet opening 44, thus freeing the inlet opening 34 and the outlet opening 44 from the leakage gap 11.
  • a cover element 35 which partially or completely blocks the inlet opening 34 is inserted into the groove 27 or into the inlet opening 34.
  • Fig. 1a shows the inlet opening 31 of the valve housing 12 facing end face 28 of the valve piston 14.
  • the inlet bore 25 is shown, which opens into the first portion 21 of the Venturi nozzle 19.
  • the Venturi nozzle 19, with the first portion 21, the second portion 22 and the third portion 23 is shown, and the channel 24, which connects the second portion 22 of the Venturi nozzle 19 with the spring chamber 15.
  • the groove 27 is shown as a completely circumferential groove 27, as already described in the previous section and a partially circumferential groove 27 is possible.
  • the valve piston 14 of the overflow valve 12 is arranged displaceably in the valve housing 12.
  • the pressure in the spring chamber 15 first of all largely corresponds to the pressure in the inlet opening 31 of the valve housing 12. If an increase in pressure occurs in the region of the inlet opening 31, the pressure pushes the valve piston 14 against the valve spring 16 and thereby releases the diversion bores 17 that there is a rapid pressure reduction in the region of the inlet opening 31. Due to an increased pressure in the region of the inlet opening 31, an increased pressure on the end face 28 of the valve piston 14 occurs in parallel so that fuel flows through the inlet bore 25 into the first region 21 of the venturi nozzle 19. When flowing through the Venturi nozzle 19 is formed in the second region 22, a negative pressure, so that fuel is sucked out of the spring chamber 15 via the channel 24.
  • the valve piston 14 displaces the fuel through the throttle 17 from the spring chamber 15.
  • the valve spring 15 is designed such that it can push the valve piston 14 even with a partially empty spring chamber 15 in the starting position, so that in the spring chamber 15, in particular in the area cup-shaped Recess 39 creates a negative pressure. Due to the negative pressure in the spring chamber 15, there is a partial evaporation of the fuel, whereby a compressible vapor bubble is formed, which on the one hand increases the mobility of the valve piston 14. As a result, on the one hand, the mobility of the valve piston 14 is facilitated, which is able to compensate for volume changes or swelling volume waves and to dampen a pressure pulsation. In this case, the valve piston 14 can escape at pressure increases in the region of the inlet opening 31 by a compression of the vapor bubble, without the fuel from the spring chamber 15 must be displaced.
  • the leakage gap 11 is kept as narrow as possible in order to limit the amount of inflowing fuel.
  • the throttle 37 on the valve housing 12 can be omitted if sufficient fuel is sucked out of the spring chamber 15 via the negative pressure in the second section 22 of the Venturi nozzle 19 through the channel 24.
  • FIG. 2 is a schematic representation of a low-pressure circuit 50 of a fuel injection system with a high pressure pump 100 according to the invention with an overflow control valve 10 according to the invention.
  • a fuel tank 1 is connected via a line 3 to a prefeed pump 2, which in turn is connected via a further line 4 to the high-pressure pump 100.
  • a low-pressure region 5 and a high-pressure region 6 are formed on the high-pressure pump 100, the fuel being conveyed from the prefeed pump into the low-pressure region 5 of the high-pressure pump 100 where it is compressed and conveyed from the high-pressure region 6 into a high-pressure line 7 and further into a high-pressure fuel accumulator, not shown ,
  • the overflow valve 10 is arranged on the low-pressure region 5 of the high-pressure pump 100 and allows the fuel to flow back into the fuel tank 8 via a return line 8.

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

Description

Stand der TechnikState of the art

Es dem Stand der Technik sind Kraftstoff-Einspritzsysteme mit einer Hochdruckpumpe und einem Hochdruckspeicher bekannt, wobei der Kraftstoff mittels der Hochdruckpumpe verdichtet und dem Hochdruckspeicher zugeführt wird. Aus dem Hochdruckspeicher wird der Kraftstoff mittels Injektoren in die Brennräume eines Verbrennungsmotors eingespritzt. Es ist ferner bekannt, dass an dem Kraftstoff-Einspritzsystem ein Niederdruck-Kreislauf vorhanden ist, welcher den Kraftstofftank mit der Hochdruckpumpe verbindet. Zur Steuerung einer der Hochdruckpumpe zugeführten Kraftstoffmenge sind Überströmventile bekannt, bei denen ein Kolben in einem Gehäuse angeordnet ist und eine Druckerhöhung im Zulauf eine Verschiebung des Kolbens bewirkt, wobei durch die Verschiebung des Kolbens eine Rücklauföffnung am Gehäuse des Überströmventils freigegeben wird und so der Druck und die Menge im Zulauf der Kraftstoffhochdruckpumpe reduziert werden können.In the prior art, fuel injection systems with a high-pressure pump and a high-pressure accumulator are known, wherein the fuel is compressed by means of the high-pressure pump and supplied to the high-pressure accumulator. From the high-pressure accumulator, the fuel is injected by means of injectors into the combustion chambers of an internal combustion engine. It is also known that a low pressure circuit is present on the fuel injection system, which connects the fuel tank with the high pressure pump. For controlling a fuel quantity supplied to the high-pressure pump, overflow valves are known in which a piston is arranged in a housing and an increase in pressure in the inlet causes a displacement of the piston, wherein a return opening on the housing of the overflow valve is released by the displacement of the piston and so the pressure and the amount in the inlet of the high-pressure fuel pump can be reduced.

WO 01/40656 A1 offenbart eine Einrichtung für die Zufuhr von Kraftstoff zu einem Einspritzmotor mit einem Überdruckventil. WO 01/40656 A1 discloses a device for supplying fuel to an injection engine with a pressure relief valve.

DE 10 2010 063398 A1 offenbart eine Kraftstofffördereinrichtung für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine, wobei in einem Niederdruckbereich eine Druckreduzierungseinrichtung in Form eines Venturirohrs vorgesehen ist. DE 10 2010 063398 A1 discloses a fuel delivery device for a fuel injection device of an internal combustion engine, wherein in a low-pressure region, a pressure reduction device in the form of a Venturi tube is provided.

EP 2 159 406 A1 offenbart ein Kraftstoffdruckregelsystem mit einem Kraftstoffdruckregler. EP 2 159 406 A1 discloses a fuel pressure control system with a fuel pressure regulator.

Aus der DE10 2006 037 174A1 ist ein Überströmventil bekannt, bei der ein Ventilkolben im Ventilgehäuse verschiebbar angeordnet ist und über sich über eine Feder am Ventilgehäuse abstützt. Dabei ist zwischen dem Ventilkolben und dem Ventilgehäuse ein Federraum ausgebildet, wobei der Federraum über eine Drossel mit einem Rücklauf des Niederdruck-Kreislaufes zum Kraftstofftank verbunden ist. Wird der Ventilkolben durch die Ventilfeder vom Ventilgehäuse in Richtung einer Einlassöffnung des Überströmventils verschoben, so kann Kraftstoff aus dem Niederdruckkreislauf über die Drossel nicht schnell genug in den Federraum strömen, so dass sich ein Unterdruck ausbildet, welcher zu einer Dampfblase im Federraum führt. Diese Dampfblase ist erwünscht, da sie im weiteren Betrieb des Überströmventil zum einen die Verschiebung des Ventilkolbens in Richtung des Federraums erleichtert und zum anderen als ein hydraulischen Dämpfungselement wirkt, so dass keine oder nur geringe Druckschwankungen im Rücklauf des Niederdruckkreislaufes durch die vom Ventilkolben über die Drossel verdrängte Kraftstoffmenge induziert werden.From the DE10 2006 037 174A1 an overflow valve is known in which a valve piston is slidably disposed in the valve housing and is supported on the valve housing via a spring. In this case, a spring chamber is formed between the valve piston and the valve housing, wherein the spring chamber is connected via a throttle with a return of the low-pressure circuit to the fuel tank. If the valve piston is displaced by the valve spring from the valve housing in the direction of an inlet opening of the overflow valve, fuel from the low pressure circuit via the throttle can not flow fast enough into the spring chamber, so that a negative pressure forms, which leads to a vapor bubble in the spring chamber. This vapor bubble is desirable because it facilitates the displacement of the valve piston in the direction of the spring chamber in the further operation of the spill valve and acts as a hydraulic damping element, so that little or no pressure fluctuations in the return of the low pressure circuit through the valve piston via the throttle displaced fuel quantity to be induced.

Nachteilig an einer solchen Lösung ist jedoch, dass die Dampfblase relativ instabil und schwach ausgebildet ist, so dass eine hinreichende Dämpfung bei steigenden Anforderungen bezüglich Druck und Einspritzmengentoleranzen nicht in allen Betriebszuständen sichergestellt werden kann.A disadvantage of such a solution, however, is that the vapor bubble is relatively unstable and weak, so that sufficient damping can not be ensured in all operating conditions with increasing demands in terms of pressure and injection quantity tolerances.

Die Aufgabe der Erfindung besteht darin, ein Überströmventil derart weiterzubilden, dass die Bewegung des Ventilkolbens und eine hydraulisch Dämpfung im Federraum verbessert werden.The object of the invention is to develop an overflow valve such that the movement of the valve piston and a hydraulic damping in the spring chamber can be improved.

Offenbarung der ErfindungDisclosure of the invention

Die Aufgabe wird mit einem Überströmventil mit den Merkmalen des Anspruchs 1 gelöst. Die erfindungsgemäße Lösung bietet gegenüber dem Stand der Technik den Vorteil, dass der Ventilkolben eine radiale Bohrung in Form einer Venturi-Düse, umfassend einen ersten Abschnitt mit einem sich verjüngenden Querschnitt, einen zweiten Abschnitt mit einem kleinsten Querschnitt und einen dritten Abschnitt mit einem sich erweiternden Querschnitt aufweist, wobei der zweite Abschnitt über einen Kanal hydraulisch mit dem Federraum verbunden ist. Der durch die Venturi-Düse strömende Kraftstoff erzeugt im zweiten Abschnitt der Düse einen Unterdruck, wobei durch den Unterdruck Kraftstoff aus dem Federraum über den Kanal abgesaugt wird, so dass im Federraum ein Unterdruck erzeugt wird, welcher eine Entstehung eines Dampfvolumens begünstigt. Dadurch wird die hydraulische Dämpfung des Überströmventils verbessert und die Beweglichkeit des Ventilkörpers erhöht, so dass eine genauere und bessere Regelung des Zulaufdrucks und der Zulaufmenge zur Hochdruckpumpe möglich ist.The object is achieved with an overflow valve having the features of claim 1. The solution according to the invention has the advantage over the prior art that the valve piston has a radial bore in the form of a Venturi nozzle, comprising a first section with a tapering cross section, a second section with a smallest cross section and a third section with a widening one Cross-section, wherein the second portion is connected via a channel hydraulically connected to the spring chamber. The fuel flowing through the venturi nozzle generates a negative pressure in the second section of the nozzle, whereby the negative pressure causes fuel to escape from the spring chamber is sucked through the channel, so that a negative pressure is generated in the spring chamber, which favors the formation of a vapor volume. As a result, the hydraulic damping of the overflow valve is improved and the mobility of the valve body is increased, so that a more accurate and better control of the inlet pressure and the feed rate to the high-pressure pump is possible.

Erfindungsgemäß ist an dem Ventilkolben eine zumindest abschnittsweise umlaufende Nut ausgebildet. Durch eine zumindest abschnittsweise umlaufende Nut kann der Austrittsbereich des dritten Abschnitts der Venturi-Düse freigespart werden, so dass der Kraftstoff leichter aus der Düse austreten kann und somit der Durchfluss durch die Düse erhöht wird. Damit erhöht sich die Strömungsgeschwindigkeit des Kraftstoffs durch die Venturi-Düse und somit der Unterdruck im zweiten Bereich. Dadurch kann eine verbesserte Absaugung des Kraftstoffs aus dem Federraum über den Kanal erreicht werden.According to the invention, an at least partially circumferential groove is formed on the valve piston. By an at least partially circumferential groove, the outlet region of the third section of the Venturi nozzle can be freed, so that the fuel can easily escape from the nozzle and thus the flow through the nozzle is increased. This increases the flow velocity of the fuel through the Venturi nozzle and thus the negative pressure in the second area. As a result, an improved extraction of the fuel from the spring chamber via the channel can be achieved.

Ferner weist die zumindest abschnittsweise umlaufende Nut stets eine Überdeckung mit zumindest einer der mindestens einen Absteuerbohrung auf. Dadurch wird der Abfluss des aus der Venturi-Düse austretenden Kraftstoffs weiter erleichtert und die Strömungsgeschwindigkeit in der Venturi-Düse weiter erhöht. Somit werden der Unterdruck im zweiten Abschnitt der Venturi-Düse und die damit verbundene Absaugleistung aus dem Federraum weiter erhöht.Furthermore, the at least partially circumferential groove always has an overlap with at least one of the at least one diversion bore. This further facilitates the outflow of the fuel exiting the venturi nozzle and further increases the flow velocity in the venturi nozzle. Thus, the negative pressure in the second section of the Venturi nozzle and the associated suction power from the spring chamber are further increased.

Durch die in den abhängigen Ansprüchen angeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im unabhängigen Anspruch angegebenen Überströmventils möglich.Advantageous refinements and improvements of the overflow valve specified in the independent claim are possible by the measures cited in the dependent claims.

Eine vorteilhafte Weiterbildung besteht darin, dass der Ventilkolben eine einer Zulauföffnung des Ventilgehäuses zugewandte Stirnfläche aufweist, wobei die Stirnfläche hydraulisch über eine Zulaufbohrung mit dem ersten Abschnitt der Venturi-Düse verbunden ist. Dadurch ist der erste Abschnitt direkt mit dem Bereich des höchsten Drucks im Überströmventil verbunden, so dass die Menge des in die Venturi-Düse einlaufenden Kraftstoffs erhöht wird. Dieser Schritt erhöht die Durchflussmenge durch die Venturi-Düse und somit den Unterdruck im zweiten Bereich der Düse, wodurch die Absaugung des Kraftstoffs aus dem Federraum begünstigt wird.An advantageous development is that the valve piston has an inlet opening of the valve housing facing end face, wherein the end face hydraulically via an inlet bore to the first portion of Venturi nozzle is connected. As a result, the first portion is directly connected to the region of highest pressure in the spill valve, so that the amount of fuel entering the venturi nozzle is increased. This step increases the flow rate through the Venturi nozzle and thus the negative pressure in the second region of the nozzle, whereby the extraction of the fuel from the spring chamber is favored.

Eine weitere vorteilhafte Weiterbildung besteht darin, dass an dem Ventilgehäuse mehrere über den Umfang verteilte Absteuerbohrungen ausgebildet sind. Dadurch kann bei einer geringen Verschiebung des Ventilkolbens ein vergleichsweise großer hydraulischer Querschnitt zum Rücklauf geöffnet werden, wodurch die Druckregelung des Druckregelventils verbessert wird. Besonders vorteilhaft sind dabei vier gleichmäßig über den Umfang des Ventilgehäuses verteilte Absteuerbohrungen, welche sich auf einem gemeinsamen Lochkreis befinden. Als Lochkreis ist dabei eine Verbindungslinie zu verstehen, welche die Mittelpunkte der Absteuerbohrungen miteinander verbindet.A further advantageous development consists in that a plurality of diversion bores distributed over the circumference are formed on the valve housing. As a result, with a slight displacement of the valve piston, a comparatively large hydraulic cross section can be opened to the return, whereby the pressure regulation of the pressure regulating valve is improved. Particularly advantageous are four evenly distributed over the circumference of the valve housing Absteuerbohrungen, which are located on a common bolt circle. As a bolt circle is to be understood a connection line which connects the centers of Absteuerbohrungen together.

Besonders vorteilhaft ist dabei, wenn die zumindest abschnittsweise umlaufende Nut einen Winkelbereich von mindestens 100° umfasst. So ist bei 4 gleichmäßig auf einem Lochkreis über den Umfang des Ventilgehäuses verteilten Absteuerbohrungen sichergestellt, dass die Austrittsöffnung des dritten Abschnitts der Venturi-Düse über die umlaufende Nut stets in Überdeckung mit mindestens einer der Absteuerbohrungen steht.It is particularly advantageous if the at least partially circumferential groove comprises an angular range of at least 100 °. Thus, in 4 evenly distributed on a bolt circle over the circumference of the valve housing Absteuerbohrungen ensures that the outlet opening of the third section of the Venturi nozzle on the circumferential groove is always in register with at least one of the Absteuerbohrungen.

Eine weitere vorteilhafte Weiterbildung besteht darin, dass an einer Mantelfläche des Ventilkolbens eine Eintrittsöffnung für den ersten Abschnitt der Venturi-Düse ausgebildet ist, wobei die Eintrittsöffnung teilweise oder vollständig durch ein Abdeckelement versperrt ist. Dadurch wird verhindert, dass der über die Stirnseite des Ventilkolbens zugeführte Kraftstoff zumindest teilweise seitlich aus der Eintrittsöffnung des ersten Abschnitts der Venturi-Düse austritt. Dadurch wird eine Hauptströmungsrichtung aus dem ersten Abschnitt der Venturi-Düse in Richtung des dritten Abschnitts sichergestellt, so dass der Unterdruck im zweiten Abschnitt erhöht und somit die Absaugung von Kraftstoff aus dem Federraum verbessert wird.A further advantageous development is that on an outer surface of the valve piston, an inlet opening for the first portion of the Venturi nozzle is formed, wherein the inlet opening is partially or completely blocked by a cover. This prevents that the fuel supplied via the end face of the valve piston at least partially exits laterally from the inlet opening of the first section of the Venturi nozzle. Thereby, a main flow direction from the first portion of the Venturi nozzle is ensured in the direction of the third portion, so that the negative pressure in the second portion is increased and thus the suction of fuel from the spring chamber is improved.

Eine weitere vorteilhafte Weiterbildung besteht darin, dass der Ventilkolben eine einer Zulauföffnung im Ventilgehäuse abgewandte Stirnfläche aufweist, wobei die abgewandte Stirnfläche eine topfförmige Ausnehmung zur Aufnahme der Ventilfeder aufweist. Durch eine solche Ausnehmung kann zum einen die Befestigung der Ventilfeder am Ventilkolben erleichtert werden, zum anderen kann sich aber in der Ausnehmung besonders einfach und stabil ein Dampfvolumen ausbilden, da dieser Bereich eine besonders geringe Zuströmung von Kraftstoff über die Leckage entlang der Kolbenmantelfläche erfährt.A further advantageous development consists in that the valve piston has an end face facing away from an inlet opening in the valve housing, the opposite end face having a cup-shaped recess for receiving the valve spring. By such a recess, on the one hand, the attachment of the valve spring on the valve piston can be facilitated, on the other hand, but can form a particularly simple and stable vapor volume in the recess, as this area undergoes a particularly small inflow of fuel through the leakage along the piston skirt surface.

Eine weitere vorteilhafte Weiterbildung besteht darin, dass an dem Ventilgehäuse im Bereich des Federraums eine Drossel ausgebildet ist. Durch ein Zusammenwirken von Venturi-Düse und bekannter Federraumdrossel kann die Ausbildung eines Dampfvolumens gegenüber einer Lösung mit Federraumdrossel und ohne Venturi-Düse erhöht werden.A further advantageous development is that a throttle is formed on the valve housing in the region of the spring chamber. Through an interaction of Venturi nozzle and known spring chamber throttle, the formation of a vapor volume compared to a solution with spring chamber throttle and without Venturi nozzle can be increased.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Die Erfindung ist anhand von in den Zeichnungen dargestellten Ausführungsbeispielen in der nachfolgenden Beschreibung näher erläutert. Gleich Bauteile oder Bauteile mit gleicher Funktion sind dabei mit gleichen Bezugszeichen gekennzeichnet. Es zeigen:

Fig. 1
zeigt ein erfindungsgemäßes Überströmventil in einer Schnittdarstellung.
Fig. 1a
zeigt eine Draufsicht auf die Stirnfläche eines Ventilkolbens des erfindungsgemäßen Überströmventils aus Fig. 1.
Fig. 2
zeigt den Niederdruckkreislauf eines Kraftstoffeinspritzsystems mit einer Hochdruckpumpe mit einem erfindungsgemäßen Überströmventil.
The invention is explained in more detail in the following description with reference to exemplary embodiments illustrated in the drawings. Like components or components with the same function are identified by the same reference numerals. Show it:
Fig. 1
shows an inventive overflow valve in a sectional view.
Fig. 1a
shows a plan view of the end face of a valve piston of the overflow valve according to the invention Fig. 1 ,
Fig. 2
shows the low-pressure circuit of a fuel injection system with a high-pressure pump with an overflow valve according to the invention.

In Fig. 1 ist ein erfindungsgemäßes Überströmventil 10 umfasst ein Ventilgehäuse 12 und einen Ventilkolben 14, welcher im Ventilgehäuse 12 verschiebbar angeordnet ist. Das Ventilgehäuse 12 weist mindestens eine Zulauföffnung 31 auf, mit der das Überströmventil 10 an eine Kraftstoffversorgung anschließbar ist sowie mindestens eine, bevorzugt mindestens zwei, besonders bevorzugt vier gleichmäßig über den Umfang des Ventilgehäuses 12 verteilte, Absteuerbohrung(en) 17 auf, mit denen der Kraftstoff aus dem Überströmventil 10 in einen Niederdruckkreislauf eines Kraftstoffeinspritzsystems zurückströmen kann. Der Ventilkolben 14 ist über eine Ventilfeder 16 am Ventilgehäuse 12 abgestützt, so dass zwischen dem Ventilkolben 14 und dem Ventilgehäuse 12 ein Federraum 15 ausgebildet ist. An dem Ventilgehäuse 12 ist im Bereich des Federraums 15 eine Drossel 37 ausgebildet, welche ebenfalls an den Niederdruckkreislauf des Kraftstoffeinspritzsystems angeschlossen ist, ausgebildet.In Fig. 1 is an inventive overflow valve 10 includes a valve housing 12 and a valve piston 14 which is slidably disposed in the valve housing 12. The valve housing 12 has at least one inlet opening 31, with which the overflow valve 10 can be connected to a fuel supply and at least one, preferably at least two, more preferably four evenly distributed over the circumference of the valve housing 12, Absteuerbohrung (s) 17, with which the fuel from the spill valve 10 can flow back into a low-pressure circuit of a fuel injection system. The valve piston 14 is supported via a valve spring 16 on the valve housing 12, so that between the valve piston 14 and the valve housing 12, a spring chamber 15 is formed. On the valve housing 12, a throttle 37 is formed in the region of the spring chamber 15, which is also connected to the low-pressure circuit of the fuel injection system is formed.

An dem Ventilkolben 14 ist eine radiale Bohrung 18 in Form einer Venturi-Düse 19 ausgebildet. Die Venturi-Düse 19 weist einen ersten Abschnitt 21 auf, in dem sich der Querschnitt der radialen Bohrung 18 in Durchflussrichtung verjüngt, einen zweiten Abschnitt 22, in dem die radiale Bohrung 18 den geringsten Strömungsquerschnitt aufweist, sowie einen dritten Abschnitt 23, in dem sich der Querschnitt der radialen Bohrung 18 in Strömungsrichtung erweitert. Von dem zweiten Abschnitt 22 führt ein Kanal 24 in den Federraum 15, so dass die Venturi-Düse 19 und der Federraum 15 hydraulisch verbunden sind.On the valve piston 14, a radial bore 18 in the form of a Venturi nozzle 19 is formed. The Venturi nozzle 19 has a first portion 21, in which the cross section of the radial bore 18 tapers in the flow direction, a second portion 22, in which the radial bore 18 has the smallest flow cross-section, and a third portion 23, in which the cross section of the radial bore 18 is expanded in the flow direction. From the second section 22, a channel 24 leads into the spring chamber 15, so that the Venturi nozzle 19 and the spring chamber 15 are hydraulically connected.

Der Ventilkolben 14 weist auf seiner der Zulauföffnung 31 zugewandten Stirnfläche 28 eine Zulaufbohrung 25 auf, welche die Stirnfläche 28 hydraulisch mit dem ersten Abschnitt 21 der Venturi-Düse 19 verbindet. Zwischen dem Ventilkolben 14 und dem Ventilgehäuse 12 ist ein Leckagespalt 11 ausgebildet, über den Kraftstoff aus der Zulauföffnung 31 in den Federraum 15 strömen kann. Da der Leckagespalt 11 schmal ausgebildet ist, ist die dem Federraum 15 zuströmende Menge an Kraftstoff begrenzt. Um Platz für die Ventilfeder 16 zu schaffen und um ein Nachströmen von Kraftstoff über den Leckagespalt möglichst gering zu halten ist an dem Ventilkolben 14, ab seiner der Zulauföffnung 31 abgewandten Stirnfläche 38 ein topfförmige Ausnehmung 39 zur Aufnahme der Ventilfeder 16 vorgesehen.The valve piston 14 has, on its end face 28 facing the inlet opening 31, an inlet bore 25 which connects the end face 28 hydraulically to the first section 21 of the venturi nozzle 19. Between the valve piston 14 and the valve housing 12, a leakage gap 11 is formed, can flow through the fuel from the inlet opening 31 into the spring chamber 15. Since the leakage gap 11 is formed narrow, the spring chamber 15 inflowing amount of fuel is limited. In order to make room for the valve spring 16 and to keep a subsequent flow of fuel through the leakage gap as small as possible, a cup-shaped recess 39 for receiving the valve spring 16 is provided on the valve piston 14, from its end face 38 remote from the inlet opening 31.

An dem Ventilkolben 14 ist an einer Mantelfläche 33 ferner eine umlaufende Nut 27 ausgebildet, welche auf Höhe einer Eintrittsöffnung 34 bzw. einer Austrittsöffnung 44 um den Ventilkolben 14 umläuft, und somit die Eintrittsöffnung 34 bzw. die Austrittsöffnung 44 gegenüber dem Leckagespalt 11 freistellt. Alternativ kann auch eine Nut 27 vorgesehen werden, welche abschnittsweise umlaufend ausgebildet ist, und dabei mindestens einen Winkelbereich von 100° umfasst und zumindest die Austrittsöffnung 44 freistellt. Dies ist insbesondere dann möglich, wenn der Ventilkörper 12 vier gleichmäßig über den Umfang verteilte Absteuerbohrungen 17 aufweist, so dass stets eine Überdeckung der Nut 27 mit mindestens einer Absteuerbohrung 17 gewährleistet ist.On the valve piston 14, a circumferential groove 27 is further formed on a lateral surface 33, which revolves around the valve piston 14 at the level of an inlet opening 34 or an outlet opening 44, thus freeing the inlet opening 34 and the outlet opening 44 from the leakage gap 11. Alternatively, it is also possible to provide a groove 27, which is formed circumferentially in sections, thereby encompassing at least an angular range of 100 ° and freeing at least the outlet opening 44. This is especially possible when the valve body 12 has four evenly distributed over the circumference Absteuerbohrungen 17, so that always an overlap of the groove 27 is ensured with at least one Absteuerbohrung 17.

Um ein Ausströmen des durch die Zulaufbohrung 25 in den ersten Bereich 21 der Venturi-Düse 19 über die Eintrittsöffnung 34 zu vermeiden, wird in die Nut 27 oder in die Eintrittsöffnung 34 selbst ein Abdeckelement 35 eingesetzt, welches die Eintrittsöffnung 34 teilweise oder vollständig versperrt.In order to prevent the outflow through the inlet bore 25 into the first region 21 of the venturi nozzle 19 via the inlet opening 34, a cover element 35 which partially or completely blocks the inlet opening 34 is inserted into the groove 27 or into the inlet opening 34.

Fig. 1a zeigt die der Zulauföffnung 31 des Ventilgehäuses 12 zugewandte Stirnfläche 28 des Ventilkolbens 14. Auf der Stirnfläche 28 ist die Zulaufbohrung 25 dargestellt, welche in dem ersten Abschnitt 21 der Venturi-Düse 19 mündet. Ferner ist die Venturi-Düse 19, mit dem ersten Abschnitt 21, dem zweiten Abschnitt 22 und dem dritten Abschnitt 23 dargestellt, sowie der Kanal 24, der den zweiten Bereich 22 der Venturi-Düse 19 mit dem Federraum 15 verbindet. Ferner ist die Nut 27 als komplett umlaufende Nut 27 dargestellt, wie bereits im vorhergehenden Abschnitt beschrieben ist auch eine abschnittsweise umlaufende Nut 27 möglich. Fig. 1a shows the inlet opening 31 of the valve housing 12 facing end face 28 of the valve piston 14. On the end face 28, the inlet bore 25 is shown, which opens into the first portion 21 of the Venturi nozzle 19. Further, the Venturi nozzle 19, with the first portion 21, the second portion 22 and the third portion 23 is shown, and the channel 24, which connects the second portion 22 of the Venturi nozzle 19 with the spring chamber 15. Furthermore, the groove 27 is shown as a completely circumferential groove 27, as already described in the previous section and a partially circumferential groove 27 is possible.

Der Ventilkolben 14 des Überströmventils 12 ist verschiebbar in dem Ventilgehäuse 12 angeordnet. Dabei entspricht der Druck im Federraum 15 zunächst weitestgehend dem Druck in der Zulauföffnung 31 des Ventilgehäuses 12. Kommt es im Bereich der Zulauföffnung 31 zu einer Druckerhöhung, so schiebt der Druck den Ventilkolben 14 gegen die Ventilfeder 16 und gibt dabei die Absteuerbohrungen 17 frei, so dass es zu einem schnellen Druckabbau im Bereich der Zulauföffnung 31 kommt. Parallel kommt es durch einen erhöhten Druck im Bereich der Zulauföffnung 31 zu einem erhöhten Druck auf die Stirnfläche 28 des Ventilkolbens 14, so dass Kraftstoff durch die Zulaufbohrung 25 in den ersten Bereich 21 der Venturi-Düse 19 fließt. Bei Durchströmen der Venturi-Düse 19 entsteht im zweiten Bereich 22 ein Unterdruck, so dass Kraftstoff aus dem Federraum 15 über den Kanal 24 abgesaugt wird.The valve piston 14 of the overflow valve 12 is arranged displaceably in the valve housing 12. The pressure in the spring chamber 15 first of all largely corresponds to the pressure in the inlet opening 31 of the valve housing 12. If an increase in pressure occurs in the region of the inlet opening 31, the pressure pushes the valve piston 14 against the valve spring 16 and thereby releases the diversion bores 17 that there is a rapid pressure reduction in the region of the inlet opening 31. Due to an increased pressure in the region of the inlet opening 31, an increased pressure on the end face 28 of the valve piston 14 occurs in parallel so that fuel flows through the inlet bore 25 into the first region 21 of the venturi nozzle 19. When flowing through the Venturi nozzle 19 is formed in the second region 22, a negative pressure, so that fuel is sucked out of the spring chamber 15 via the channel 24.

Der Ventilkolben 14 verdrängt den Kraftstoff durch die Drossel 17 aus dem Federraum 15. Die Ventilfeder 15 ist derart ausgelegt, dass sie den Ventilkolben 14 auch bei einem teilweise entleerten Federraum 15 in die Ausgangslage zurückschieben kann, so dass im Federraum 15, insbesondere im Bereich der topfförmigen Ausnehmung 39 ein Unterdruck entsteht. Durch den Unterdruck im Federraum 15 kommt es zu einer teilweisen Verdampfung des Kraftstoffs, wodurch eine kompressible Dampfblase entsteht, welche zum einen die Beweglichkeit des Ventilkolbens 14 erhöht. Dadurch wird zum einen die Beweglichkeit des Ventilkolbens 14 erleichtert, welche in der Lage ist, Volumenänderungen bzw. schwellende Mengenwellen zu kompensieren und eine Druckpulsation zu dämpfen. Dabei kann der Ventilkolben 14 bei Druckerhöhungen im Bereich der Zulauföffnung 31 durch eine Verdichtung der Dampfblase ausweichen, ohne das Kraftstoff aus dem Federraum 15 verdrängt werden muss.The valve piston 14 displaces the fuel through the throttle 17 from the spring chamber 15. The valve spring 15 is designed such that it can push the valve piston 14 even with a partially empty spring chamber 15 in the starting position, so that in the spring chamber 15, in particular in the area cup-shaped Recess 39 creates a negative pressure. Due to the negative pressure in the spring chamber 15, there is a partial evaporation of the fuel, whereby a compressible vapor bubble is formed, which on the one hand increases the mobility of the valve piston 14. As a result, on the one hand, the mobility of the valve piston 14 is facilitated, which is able to compensate for volume changes or swelling volume waves and to dampen a pressure pulsation. In this case, the valve piston 14 can escape at pressure increases in the region of the inlet opening 31 by a compression of the vapor bubble, without the fuel from the spring chamber 15 must be displaced.

Entlang des Ventilkolbens 14 kann Kraftstoff entlang des Leckagespalts 11 in den Federraum 15 nachströmen, daher ist der Leckagespalt 11 möglichst eng gehalten, um die Menge des nachströmenden Kraftstoffs zu begrenzen.
In einer einfachen Ausführungsform kann die Drossel 37 am Ventilgehäuse 12 entfallen, wenn hinreichend viel Kraftstoff über den Unterdruck im zweiten Abschnitt 22 der Venturi-Düse 19 durch den Kanal 24 aus dem Federraum 15 abgesaugt wird.Along the valve piston 14 fuel can flow along the leakage gap 11 in the spring chamber 15, therefore, the leakage gap 11 is kept as narrow as possible in order to limit the amount of inflowing fuel.
In a simple embodiment, the throttle 37 on the valve housing 12 can be omitted if sufficient fuel is sucked out of the spring chamber 15 via the negative pressure in the second section 22 of the Venturi nozzle 19 through the channel 24.

In Fig. 2 ist eine schematisch ein Niederdruckkreislauf 50 eines Kraftstoffeinspritzsystems mit einer erfindungsgemäßen Hochdruckpumpe 100 mit einem erfindungsgemäßen Überströmregelventil 10 dargestellt. Ein Kraftstofftank 1 ist über eine Leitung 3 mit einer Vorförderpumpe 2 verbunden, welche ihrerseits über eine weitere Leitung 4 mit der Hochdruckpumpe 100 verbunden. An der Hochdruckpumpe 100 ist ein Niederdruckbereich 5 und ein Hochdruckbereich 6 ausgebildet, wobei der Kraftstoff von der Vorförderpumpe in den Niederdruckbereich 5 der Hochdruckpumpe 100 gefördert wird, dort verdichtet und aus dem Hochdruckbereich 6 in eine Hochdruckleitung 7 und weiter in einen nicht dargestellten Kraftstoffhochdruckspeicher gefördert wird. Das Überströmventil 10 ist am Niederdruckbereich 5 der Hochdruckpumpe 100 angeordnet und ermöglicht es, dass der Kraftstoff über eine Rücklaufleitung 8 zurück in den Kraftstofftank 8 strömt.In Fig. 2 is a schematic representation of a low-pressure circuit 50 of a fuel injection system with a high pressure pump 100 according to the invention with an overflow control valve 10 according to the invention. A fuel tank 1 is connected via a line 3 to a prefeed pump 2, which in turn is connected via a further line 4 to the high-pressure pump 100. A low-pressure region 5 and a high-pressure region 6 are formed on the high-pressure pump 100, the fuel being conveyed from the prefeed pump into the low-pressure region 5 of the high-pressure pump 100 where it is compressed and conveyed from the high-pressure region 6 into a high-pressure line 7 and further into a high-pressure fuel accumulator, not shown , The overflow valve 10 is arranged on the low-pressure region 5 of the high-pressure pump 100 and allows the fuel to flow back into the fuel tank 8 via a return line 8.

Claims (8)

  1. Overflow valve (10) for regulating a fuel volume flow in a low-pressure circuit of a fuel injection system, having a valve housing (12) and having a valve piston (14) which is displaceable in the valve housing (12), wherein a spring chamber (15) is formed between the valve piston (14) and the valve housing (12), and wherein, in the spring chamber (15), there is arranged a valve spring (16) by means of which the valve piston (14) is supported relative to the valve housing (12), wherein, on the valve housing (12), there is formed at least one spill bore (17) which, in a relaxed state of the valve spring (16), is at least substantially closed off by the valve piston (14), characterized in that the valve piston (14) has a radial bore (18) in the form of a Venturi nozzle (19) comprising a first section (21) with a narrowing cross section, a second section (22) with a smallest cross section and a third section (23) with a widening cross section, wherein the second section (22) is hydraulically connected via a duct (24) to the spring chamber (15), wherein, on the valve piston (14), there is formed a groove (27) which runs in encircling fashion at least in sections and which is always in overlap with at least one of the at least one spill bore(s) (17).
  2. Overflow valve (10) according to Claim 1, characterized in that the valve piston (14) has a face surface (28) facing toward an inflow opening (31) of the valve housing (12), wherein the face surface (28) is hydraulically connected via an inflow bore (25) to the first section (21) of the Venturi nozzle (19).
  3. Overflow valve (10) according to either of Claims 1 and 2, characterized in that, on the valve housing (12), there are formed multiple, in particular 4, spill bores (17) which are preferably distributed uniformly over the circumference.
  4. Overflow valve (10) according to Claim 1 and 3, characterized in that the groove (27) which runs in encircling fashion at least in sections covers an angle range of at least 100°.
  5. Overflow valve (10) according to one of Claims 1 to 4, characterized in that, on a shell surface (33) of the valve piston (14), there is formed an inlet opening (34) for the first section (21) of the Venturi nozzle (19), wherein the inlet opening (34) is partially or completely shut off by a cover element (35).
  6. Overflow valve (10) according to one of. Claims 1 to 5, characterized in that the valve piston (14) has a face surface (38) which is averted from an inflow opening (31) in the valve housing (12), wherein the averted face surface (38) has a pot-shaped recess (39) for receiving the valve spring (16).
  7. Overflow valve (10) according to one of Claims 1 to 6, characterized in that a throttle (37) is formed on the valve housing (12) in the region of the spring chamber (15).
  8. High-pressure pump (100) for a fuel injection system, having an overflow valve (10) according to one of Claims 1 to 7.
EP15194022.8A 2014-12-16 2015-11-11 Relief valve for a fuel pump Active EP3034858B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014226074.4A DE102014226074A1 (en) 2014-12-16 2014-12-16 Overflow valve for a fuel pump

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EP3034858B1 true EP3034858B1 (en) 2018-01-10

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DE102017212003A1 (en) * 2016-09-16 2018-03-22 Robert Bosch Gmbh Overflow valve, in particular for use in a fuel injection system, high-pressure pump and fuel injection system

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Publication number Priority date Publication date Assignee Title
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
DE102006037174A1 (en) 2006-08-09 2008-02-14 Robert Bosch Gmbh Apparatus and method for controlling a fuel flow rate in a low pressure circuit system for an internal combustion engine
ATE542994T1 (en) * 2008-08-29 2012-02-15 Delphi Tech Holding Sarl IMPROVED FUEL PRESSURE REGULATION SYSTEM AND IMPROVED FUEL PRESSURE REGULATOR FOR USE THEREIN
DE102010063398A1 (en) * 2010-12-17 2012-06-21 Robert Bosch Gmbh Fuel conveying device for fuel injector of internal combustion engine, has pressure reduction device provided in form of venturi tube in by-pass pipe, where venturi tube is formed in hollow screw screwed into housing portion

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