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WO2018054628A1 - Pompe à carburant à haute pression - Google Patents

Pompe à carburant à haute pression Download PDF

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Publication number
WO2018054628A1
WO2018054628A1 PCT/EP2017/071012 EP2017071012W WO2018054628A1 WO 2018054628 A1 WO2018054628 A1 WO 2018054628A1 EP 2017071012 W EP2017071012 W EP 2017071012W WO 2018054628 A1 WO2018054628 A1 WO 2018054628A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
valve element
fuel pump
pressure fuel
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.)
Ceased
Application number
PCT/EP2017/071012
Other languages
German (de)
English (en)
Inventor
Michael Kleindl
Markus Hilligardt
Rainer Kornhaas
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 WO2018054628A1 publication Critical patent/WO2018054628A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/005—Pressure relief valves
    • 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
    • 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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • 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
    • F02M63/0205—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 for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
    • F02M63/0215—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 for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits
    • 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
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/0245—Means for varying pressure in common rails by bleeding fuel pressure between the high pressure pump and the common rail
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/025—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side and remaining open after return of the normal pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0406—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded in the form of balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/042—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with locking or disconnecting arrangements

Definitions

  • the invention relates to a high-pressure fuel pump according to the preamble of claim 1.
  • High-pressure fuel pumps for fuel systems of internal combustion engines for example for a gasoline direct injection, are known from the market.
  • fuel is conveyed from a fuel tank by means of a prefeed pump and the mechanically driven high-pressure pump under high pressure into a high-pressure accumulator ("rail").
  • Such fuel systems typically include a pressure relief valve that prevents a pressure in the high pressure accumulator from increasing too much. If the pressure in the high-pressure accumulator reaches too high a value, the pressure-limiting valve opens in the intake stroke of the high-pressure pump
  • High-pressure accumulator sucked into the delivery chamber.
  • the pressure limiting valve opens when the pressure in the high pressure accumulator is so great that a pressure difference that occurs between the high pressure accumulator and the delivery chamber in the intake stroke of the high pressure pump, an opening pressure of
  • the invention has the advantage that in the so-called "error case
  • a FFVF can occur, for example, with a defective quantity control valve
  • High-pressure accumulator again completely dissipate conveyed amount of fuel into the delivery chamber, so that the pressure in the high-pressure accumulator increases uncontrollably. Due to the permanent leakage after entering the hundred percent
  • the hydraulic variable can in particular a delivery rate and / or a delivery pressure through the
  • control means comprises a loading device, which exerts a force component orthogonal to an opening direction of the valve element on the valve element with the pressure relief valve open.
  • a loading device which exerts a force component orthogonal to an opening direction of the valve element on the valve element with the pressure relief valve open.
  • the loading device comprises a flow path in a valve body, the upstream of the valve element is arranged. Consequently, the fluid flow passing through the pressure limiting valve can itself exert an orthogonal force on the valve element, the force component thus exerted when the second limit is exceeded such that the valve element is transferred to a position in which the pressure limiting valve is permanently open.
  • Pressure relief valve flowing fuel can thus the valve element from its central position, from which it could reversibly return to the closed position, in an eccentric position from which it can not return to the closed position, push out.
  • the fuel thus exerts a resulting and in the longitudinal axis of the
  • control means comprise a geometric configuration on a spring receptacle arranged between a valve spring and the valve element.
  • a spring receiver normally ensures a defined position of the valve element relative to the valve spring. Consequently, the spring receiver can be designed geometrically such that the
  • Valve element is controllable when exceeding the second threshold in an irreversibly open position.
  • the spring receptacle is deflected in the opening direction of the pressure limiting valve when the second threshold value is exceeded, for example tilted and / or pushed to the side, that the valve element when exceeding the second limit in
  • Part area of the spring receiving surface is formed, and that the
  • geoemetric embodiment comprises a chamfer at least partially formed at an edge region of this portion, the extent seen in the opening direction of the valve element is less than 0.2 mm, in particular at most 0.17 mm.
  • the chamfer can have an angle of 40-50 °, in particular 45 °.
  • Outside diameter of the spring receiving comprises, which has a diameter of less than 4.5 mm.
  • the spring receptacle is arranged in a recess, and that the recess has a diameter of 5 mm.
  • the recess has a diameter of 5 mm.
  • Recess may apply the ratio of the outer diameter of the spring receiver to the diameter of the recess in a corresponding manner.
  • Pressure limiting valve is a possibility that the position and / or orientation of the spring receptacle when the second threshold is exceeded unstable and so a permanent leakage of the pressure relief valve is made possible by irreversible deflection of the valve element.
  • the geometric configuration is a recess which is preferably lateral relative to a longitudinal axis of the pressure-limiting valve and which engages on a region of the valve element which faces the valve element
  • Spring receptacle has, in which recess the
  • Valve element is at least partially included when it is in the irreversibly open position.
  • the valve element can be kept irreversibly safe in the event of a fault, so that when the second limit value is exceeded, a permanent open position is reliably ensured.
  • valve element is clamped or clamped in the irreversibly open position between the spring receptacle and the valve body. This is a particularly simple way to allow a permanent open position of the pressure relief valve.
  • valve body has the geometric design.
  • valve body could have a groove.
  • Figure 1 shows a longitudinal section through a first embodiment of a high-pressure fuel pump with a pressure relief valve
  • FIG. 2 is an enlarged detail view of the pressure relief valve of Figure 1;
  • Figure 3 is a schematic representation of the pressure relief valve of Figure 1 in the irreversible position
  • FIG. 4 shows a flowchart for illustrating the mode of operation of the
  • a high-pressure fuel pump for an internal combustion engine not shown in detail bears the reference numeral 10.
  • the high-pressure fuel pump 10 has an overall substantially cylindrical pump housing 12 in or on which the essential components of the high-pressure fuel pump 10 are arranged.
  • the high-pressure fuel pump 10 has an intake / quantity control valve 14, one in one
  • Delivery chamber 16 arranged, displaceable by a drive shaft, not shown in a reciprocating motion delivery piston 18, an exhaust valve 20 and a pressure relief valve 22.
  • a first channel 24 is present, which extends coaxially to the delivery chamber 16 and the delivery piston 18 and which leads from the delivery chamber 16 to a second and formed by a recess channel 26 at an angle of 90 ° to the first channel 24th is arranged and in which the pressure relief valve 22 is received.
  • a longitudinal axis of the first channel 24 is present, which extends coaxially to the delivery chamber 16 and the delivery piston 18 and which leads from the delivery chamber 16 to a second and formed by a recess channel 26 at an angle of 90 ° to the first channel 24th is arranged and in which the pressure relief valve 22 is received.
  • Pump housing 12 carries in Figure 1 a total of reference numeral 28, a longitudinal axis or longitudinal direction of the pressure relief valve 22 the Reference numeral 29.
  • Figure 1 above is in the pump housing 12 a
  • Pressure damper 30 is arranged.
  • Delivery stroke of the fuel located in the delivery chamber 16 is compressed and via the outlet valve 20, for example, in a high-pressure region 32,
  • the high pressure area 32 is connected to the high pressure fuel pump 10 via an outlet port 34
  • Amount of fuel discharged in a delivery stroke is adjusted by the solenoid-operated intake and quantity control valve 14. With an impermissible pressure in the high-pressure area, this opens
  • Pressure limiting valve 22 whereby fuel from the high-pressure region can flow into the delivery chamber 16.
  • Pressure relief valve 22 first includes a sleeve-like valve body 38 which is pressed into the recess 26 and in which a in the longitudinal direction 29 of the Druckbegerzungsventils 22 and the valve body 38 extending channel 40 is present. At the right in Figure 2 end of the channel 40 is at the
  • Valve body 38 a valve seat 42 in the form of a conical extension
  • valve element 44 in the form of a valve ball.
  • Valve element 44 is a spring receiving 46 is arranged, in which a
  • Passage opening 48 is present, which in the longitudinal direction of the spring receiving 46, that is in turn parallel to the longitudinal axis 29, runs.
  • the spring receptacle 46 On the side facing away from the valve element 44 side of the spring receptacle 46, the spring receptacle 46 has a pin-like extension 50.
  • first end portion 52 formed as a spiral spring
  • Valve spring 54 postponed.
  • a right in Figure 2 right end portion 56 of the valve spring 54 of the pressure relief valve 22 is disposed in a cylindrical end portion 58 of the recess 26 and is supported against a
  • the spring receptacle 46 has on a valve element 44 facing and seen in the direction of the longitudinal axis 29 in the present embodiment circular cross-section having portion 59 a planar
  • Embodiment wherein the planar portion 59 is chamfered at a radially outer edge region.
  • the chamfer 60 thus formed has a dimension, ie an extent in the opening direction of the valve element 44 or seen in the direction of the longitudinal axis 29 of the pressure relief valve 22, of less than 0.2 mm, in particular at most 0.17 mm.
  • the angle of the chamfer 60 with respect to the longitudinal axis 29 is between 40 ° to 50 °, in particular it is 45 °.
  • Spring receptacle 46 is less than 4.5 mm with a diameter of the recess 26 of 5 mm. For other diameters of the recess 26, the ratio of the diameter of the planar portion of the spring receptacle 46 to the diameter of the recess 26 applies in a corresponding manner. Furthermore, this flat region has a circumferential annular recess 62 in the radially middle and present to the valve member 44 directly
  • Pressure limiting valve 22 whereby fuel from the high-pressure accumulator 32 can flow into the delivery chamber 16.
  • the pressure limiting valve 22 opens when a pressure difference between the outlet side
  • High-pressure accumulator 32 and the delivery chamber 16 of the high-pressure fuel pump 10 exceeds a predetermined first limit. Will that be
  • Pressure relief valve 22 is opened, the valve element 44 lifts off from the valve seat 42. By the pressure limiting valve 22 is thus prevented that the pressure in the outlet-side high-pressure accumulator 32 is unacceptably high.
  • the pressure relief valve 22 is thus moved in a reversibly open position when the formed as overpressure in the high-pressure accumulator 32 hydraulic variable exceeds a first limit.
  • Reversible here means that the valve element 44 returns to the closed position, in which it rests against the valve seat 42, as soon as the pressure falls below the predetermined first limit again.
  • an orthogonal force component acts on the valve element 44 to be irreversibly deflected so that the pressure relief valve 22 is permanently open and even if the second or first Limit value is exceeded, no longer returns to the closed position.
  • High-pressure accumulator 32 and delivery chamber 16 are thus permanently fluidly connected to each other.
  • valve element 44 between the portion 59 of the
  • Pressure limiting valve 22 generates flowing fuel.
  • no symmetrical radial force acts on the valve element 44 after lifting off the valve seat 42, so that no orthogonal force component or no orthogonal force vector would result.
  • the fluid flows in a preferred direction assyemtrisch around the valve element, so that in a direction orthogonal, a force vector results, which drives the valve element 44 radially outward, that is orthogonal to the opening direction of the pressure relief valve 22.
  • the valve element 44 is thus acted upon in the irreversible position.
  • the loading device Since the valve element 22 is “controlled” when the predetermined second limit value is exceeded in the irreversibly opened position, the loading device may be referred to as “control means” or as part of a control means.
  • control means or as part of a control means.
  • a corresponding shaping of the flow path of the fuel for example by a corresponding shape of the immediately upstream of the valve seat 42 existing portion of the channel 40.
  • Conceivable for example, is a helical corrugation of the inner wall of this portion of the channel 40 through which a twist is forced by the flow, or a slight inclination of the longitudinal axis of this section relative to the longitudinal axis 29th
  • Spring receptacle 46 "slips” and clamped between the valve body 38 and spring receptacle 46 and secured in the clamped position by the recess 62 ( Figure 3).
  • the bevel 60 and the particular value of the diameter 66 of the portion 59 are thus part of the above-mentioned
  • the operation of the pressure relief valve is summarized again with reference to Figure 4 are shown: starting from a closed position 68 in which the valve member 44 tightly against the valve seat 42, the valve element 44 is lifted from the valve seat 42 when a hydraulic variable G is a first limit G1 exceeds. Hierbau the valve element 44 is deflected in a reversibly open position 70, whereby fuel from the high-pressure accumulator 32 can flow into the delivery chamber 16.
  • the hydraulic variable G may be formed in particular as a pressure in the high-pressure accumulator 32.
  • the valve member 44 moves back to the valve seat 42 so that the pressure relief valve 22 again assumes its closed position.
  • the pressure relief valve 22 thus assumes a permanent open position, so that fuel from the high-pressure accumulator 32 can flow permanently into the delivery chamber 16. Even if the hydraulic quantity G again the limits G2 and / or G1 falls below the pressure relief valve no closed position more. Exceeding the second limit value G2 occurs in particular in the so-called full-blown (FFVF) error case.
  • the hydraulic variable G can in particular as flow or discharge pressure or a
  • Pressure relief valve 22 may be formed through.
  • the hydraulic variable G associated with the first limit value G1 can thus be equal to or different from that of the hydraulic variable which is related to the limit value G2.

Landscapes

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

Abstract

L'invention concerne une pompe à carburant haute pression (10) pour un système d'injection de carburant d'un moteur à combustion interne, comprenant une soupape de limitation de pression (22) disposée de manière fluidique entre une chambre de refoulement (16) et un accumulateur haute pression (32) et s'ouvrant en direction de la chambre de refoulement (16), ladite soupape comprenant un élément soupape (44) qui peut être déplacé dans une position ouverte de manière réversible (70), lorsqu'au moins une grandeur hydraulique (G) dépasse une première valeur limite prédéfinie (G1), la soupape de limitation de pression (22) comprenant un moyen de commande (40, 60, 66) qui commande l'élément soupape (44) pour le faire passer dans une position ouverte de manière irréversible (72) lorsque la grandeur hydraulique (G) dépasse une deuxième valeur limite prédéfinie (G2).
PCT/EP2017/071012 2016-09-22 2017-08-21 Pompe à carburant à haute pression Ceased WO2018054628A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016218215.3 2016-09-22
DE102016218215.3A DE102016218215A1 (de) 2016-09-22 2016-09-22 Kraftstoff-Hochdruckpumpe

Publications (1)

Publication Number Publication Date
WO2018054628A1 true WO2018054628A1 (fr) 2018-03-29

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ID=59656082

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2017/071012 Ceased WO2018054628A1 (fr) 2016-09-22 2017-08-21 Pompe à carburant à haute pression

Country Status (2)

Country Link
DE (1) DE102016218215A1 (fr)
WO (1) WO2018054628A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018209596A1 (de) 2018-06-14 2019-12-19 Robert Bosch Gmbh Kraftstoffpumpe
CN113167202A (zh) * 2018-12-13 2021-07-23 罗伯特·博世有限公司 燃料高压泵
DE102020211324A1 (de) 2020-09-09 2022-03-10 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstoff-Hochdruckpumpe

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019216314A1 (de) * 2019-10-23 2021-04-29 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe
DE102020111372A1 (de) 2020-04-27 2021-10-28 Bayerische Motoren Werke Aktiengesellschaft Batteriegehäuse mit Ventilvorrichtung, Batterie sowie Kraftfahrzeug

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10288269A (ja) * 1997-04-14 1998-10-27 Toyota Motor Corp 蓄圧式燃料噴射装置
WO2008084768A1 (fr) * 2007-01-11 2008-07-17 Mitsuba Corporation Dispositif de commande de pression
US7806235B1 (en) * 2006-10-04 2010-10-05 Curtis Roys Environmental compressor protection assembly
DE102013220816A1 (de) * 2013-10-15 2015-04-16 Continental Automotive Gmbh Druckbegrenzungsventil für ein Kraftstoffeinspritzsystem und Kraftstoffeinspritzsystem

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10288269A (ja) * 1997-04-14 1998-10-27 Toyota Motor Corp 蓄圧式燃料噴射装置
US7806235B1 (en) * 2006-10-04 2010-10-05 Curtis Roys Environmental compressor protection assembly
WO2008084768A1 (fr) * 2007-01-11 2008-07-17 Mitsuba Corporation Dispositif de commande de pression
DE102013220816A1 (de) * 2013-10-15 2015-04-16 Continental Automotive Gmbh Druckbegrenzungsventil für ein Kraftstoffeinspritzsystem und Kraftstoffeinspritzsystem

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018209596A1 (de) 2018-06-14 2019-12-19 Robert Bosch Gmbh Kraftstoffpumpe
CN113167202A (zh) * 2018-12-13 2021-07-23 罗伯特·博世有限公司 燃料高压泵
DE102020211324A1 (de) 2020-09-09 2022-03-10 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstoff-Hochdruckpumpe
WO2022053328A1 (fr) 2020-09-09 2022-03-17 Robert Bosch Gmbh Pompe à carburant haute pression

Also Published As

Publication number Publication date
DE102016218215A1 (de) 2018-03-22

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