WO2014139698A1 - Pompe à carburant à haute pression avec clapet de sortie disposé entre une chambre d'alimentation et une sortie - Google Patents

Pompe à carburant à haute pression avec clapet de sortie disposé entre une chambre d'alimentation et une sortie Download PDF

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Publication number
WO2014139698A1
WO2014139698A1 PCT/EP2014/050538 EP2014050538W WO2014139698A1 WO 2014139698 A1 WO2014139698 A1 WO 2014139698A1 EP 2014050538 W EP2014050538 W EP 2014050538W WO 2014139698 A1 WO2014139698 A1 WO 2014139698A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
outlet
fuel pump
spring
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/EP2014/050538
Other languages
German (de)
English (en)
Inventor
Michael Kleindl
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
Priority to KR1020157025157A priority Critical patent/KR102122709B1/ko
Priority to CN201480013958.2A priority patent/CN105190017A/zh
Publication of WO2014139698A1 publication Critical patent/WO2014139698A1/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
    • 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
    • F02M59/462—Delivery 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
    • F02M63/005—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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F02M59/367—Pump inlet valves of the check valve type being open when actuated

Definitions

  • High-pressure fuel pump with an outlet valve arranged between a delivery chamber and an outlet
  • the invention relates to a high-pressure fuel pump according to the preamble of claim 1.
  • Fuel distributor can be promoted with a particular desired pressure.
  • the high-pressure fuel pump generally has a plurality of valves.
  • such high-pressure fuel pumps are designed as piston plug-in pumps.
  • Pressure relief valve of a high-pressure fuel pump combined in one common housing are arranged.
  • a required number of elements can be reduced, whereby costs can be reduced.
  • the outlet valve and the pressure relief valve may optionally be designed with only 6 elements.
  • valve assembly Pressure relief valve
  • Valve seat body may be arranged. Valve elements or valve body of
  • Valve arrangement can be guided radially in a simple manner in the common housing.
  • elements of the combined exhaust valve and pressure relief valve according to the invention can be carried out by comparatively simple stamped and deep-drawn parts. This allows valve elements
  • valve assembly may be designed with a comparatively low mass.
  • Valve assembly requires a relatively small installation space, which may result in improved flexibility in the construction of the high-pressure fuel pump.
  • the valve assembly can be designed with a particularly short axial length ("installation length").
  • a limit value for a maximum allowable fuel pressure for the pressure relief valve in an at least partially assembled state of the valve assembly during assembly can be set "externally", ie even before the final assembly of the pressure relief valve in the fuel pump.
  • Combined pressure relief valve in a - can be produced as a separate part - outlet of the high-pressure fuel pump are arranged.
  • valve arrangement according to the invention has a comparatively small dead space volume, as a result of which a delivery rate ("delivery rate") of the high-pressure fuel pump can be increased.
  • delivery rate delivery rate
  • An assembly or a final assembly of the combined exhaust valve and pressure relief valve is relatively easy and inexpensive possible.
  • the Valve assembly according to the invention be carried out without the use of cohesive connections.
  • the invention relates to a high-pressure fuel pump, with an outlet valve arranged between a delivery chamber and an outlet, and with one arranged between the outlet and the delivery chamber
  • the outlet valve and the pressure limiting valve have a common valve seat body.
  • the fuel high pressure pump according to the invention can be made comparatively small, simple and inexpensive.
  • the common valve seat body particularly few and simple elements are needed.
  • the valve seat body is arranged centrally between the outlet valve and the pressure relief valve and comprises two
  • a hydraulic flow for the exhaust valve may be through a single centrally located through bore
  • a hydraulic flow for the pressure relief valve may be through one or more through bores disposed in a radially outer region of the valve seat body.
  • a particularly space-saving arrangement results when the outlet valve and the pressure limiting valve are arranged substantially coaxially to each other.
  • the outlet valve and the pressure limiting valve are arranged substantially coaxially to each other.
  • Exhaust valve and the pressure relief valve and a discharge valve and the pressure relief valve enclosing housing designed substantially rotationally symmetric or radially symmetrical.
  • the outlet valve and the pressure relief valve together can be made particularly small, simple and inexpensive.
  • the function of the pressure relief valve can be improved if the pressure relief valve has an annular valve element. As a result, the pressure relief valve can be particularly powerful and yet simple.
  • the pressure relief valve has a leaf spring as a valve spring.
  • a leaf spring is relatively easy to produce - for example, as a sheet metal spring - and also has a small space, while still a comparatively large force for biasing the pressure relief valve can be generated.
  • the fuel high-pressure pump has the
  • leaf spring is formed as a curved or corrugated annular spring. It can be
  • the pressure relief valve can be made particularly simple and inexpensive, and it has very few items.
  • a first spring support is arranged, on which a spring of the outlet valve is supported, and in that a second spring support is arranged in the housing, on which the spring of the pressure limiting valve is supported, wherein the first and the second spring support are made substantially annular.
  • a respective radially externa ßerer region of the first and the second spring support is pressed against an associated radially inner region of the housing.
  • Spring support each separate from the housing elements and can be particularly simple, for example, designed as an annular perforated discs.
  • first and the second spring support can be pressed in each case with a defined axial dimension, whereby, for example, the respective spring forces can be adjusted during assembly.
  • the spring of the outlet valve is a helical spring.
  • a coil spring has a higher compared to a leaf spring number of springs and can be designed to be durable.
  • the high-pressure fuel pump is a
  • Valve body of the exhaust valve cup-shaped executed, wherein the spring of the exhaust valve radially within the valve body, a bottom of the valve body subjected to a compressive force.
  • high-pressure fuel pump is a radially externa ßerer portion of the valve body in a portion of
  • Valve seat body guided radially.
  • a coaxial arrangement of these elements of the exhaust valve is effected in a particularly simple manner, and au for a safe and tight fit of the valve body provided on the valve seat.
  • the radially externa ßere portion of the valve body is guided radially in a separate from the valve seat body arranged guide element. This allows the valve seat body to be designed with a simpler geometry, which costs can be reduced.
  • the separately arranged guide element extends the design possibilities in the design of the exhaust valve.
  • the high-pressure fuel pump according to the invention is particularly simple when the combined exhaust valve and pressure relief valve is integrated in an outlet of the high-pressure fuel pump.
  • the outlet valve and the pressure limiting valve are arranged in a particularly space-saving manner. Also, from a functional point of view, the location of the outlet valve and the pressure relief valve near the outlet is
  • Figure 1 is a schematic sectional view of a substantially executed according to the prior art fuel high-pressure pump for a fuel system for an internal combustion engine;
  • Figure 2 is an axial sectional view of an outlet of a
  • Figure 3 is an enlarged sectional view of the combined exhaust valve and pressure relief valve similar to Figure 2;
  • Figure 4 is a sectional view of an alternative to the Figure 3 embodiment of the combined exhaust valve and pressure relief valve.
  • Figure 5 is a perspective view of an integrally formed with a leaf spring valve element of the pressure relief valve together with a portion of a valve seat body.
  • FIG. 1 shows a high pressure fuel pump 10 for a fuel system for an internal combustion engine (not shown) in a schematic
  • FIG. 1 Sectional view.
  • the high-pressure fuel pump 10 of Figure 1 substantially corresponds to the prior art, but some elements of the invention in the figure 1 are shown at least symbolically.
  • Figures 2 to 5 describe the invention in detail.
  • the high-pressure fuel pump 10 has a pump housing 12, in whose left portion in the drawing, an electromagnet 14 with a coil 16, an armature 18 and an armature spring 20 is arranged. Furthermore, the high pressure fuel pump 10 includes one with a low pressure line 22
  • High pressure line 28 connected to outlet 30 with an outlet valve 32.
  • the outlet valve 32 includes a valve body 33 and a present as Coil spring executed spring 35.
  • an outlet 34 is arranged at the outlet 30.
  • the high-pressure fuel pump 10 in an upper right area of FIG. 1 comprises a symbol represented by a switching symbol
  • Pressure limiting valve 54 which will be explained in more detail in the following figures 2 to 5.
  • the pressure-limiting valve 54 can open against a conveying direction of the high-pressure fuel pump 10 determined by the outlet valve 32 to a delivery chamber 42.
  • the inlet valve 26 comprises a valve spring 36 and a valve body 38.
  • the valve body 38 can be horizontal by means of a in the drawing
  • a piston 44 is arranged vertically movable in the drawing. The piston 44 can be moved by means of a roller 46 of a - in this case elliptical - cam 48 in a cylinder 50.
  • the cylinder 50 is formed in a portion of the pump housing 12.
  • the inlet valve 26 is hydraulically connected via an opening 52 to the delivery chamber 42.
  • this fuel delivers from the inlet 24 to the outlet 30, the outlet valve 32 depending on a respective hydraulic pressure difference between the delivery chamber 42 and the outlet 30 and depending on the force of the spring 35 opens or closes ,
  • the inlet valve 26 is acted upon by a respective pressure difference between the inlet 24 and the delivery chamber 42 at full delivery, but also by the valve needle 40 and the
  • Electromagnets 14 14.
  • Figure 2 shows an axial sectional view of the outlet nozzle 34 of the high-pressure fuel pump 10, wherein the exhaust valve 32 and the
  • Pressure relief valve 54 integrated into the outlet port 34 and arranged in combination.
  • Pressure relief valve 54 to each other arranged substantially coaxially.
  • Generalizing the outlet pipe 34 is also referred to below as the housing 56.
  • FIG. 2 the elements shown in FIG. 2 are essentially rotationally symmetrical or radially symmetrical with respect to a longitudinal axis
  • the outlet valve 32 and the pressure limiting valve 54 have a common valve seat body 58, which in the drawing approximately axially in the middle between the pressure relief valve 54 (left) and the outlet valve 32nd
  • the valve seat body 58 has a substantially cylindrical basic shape and is preferably non-positively in the housing
  • valve seat body 58 may also be arranged cohesively or positively in the housing 56.
  • a cylindrical bore 59 is arranged, which in a right in the drawing area has a portion with a sudden increase in diameter, so that a stepped bore is formed.
  • a cup-shaped valve body 33 of the outlet valve 32 is arranged, wherein a radially outer portion of the valve body 33 from a radially inner wall the section of the diameter of the valve seat body 58 is radially guided.
  • a helical spring spring 35 of the exhaust valve 32 Radially within the cup-shaped valve body 33 is designed as a helical spring spring 35 of the exhaust valve 32 is arranged concentrically with the other elements.
  • the spring 35 is supported at its left in the drawing axial end portion to a bottom 64 of the cup-shaped valve body 33 and therefore can act on the bottom 64 with a compressive force in the drawing to the left.
  • valve seat body 58 comprises an annular web
  • annular valve element 70 of the pressure limiting valve 54 bears against a sealing seat 78.
  • the annular valve element 70 is designed substantially as a centrally perforated cylindrical disc.
  • An outer diameter of the annular valve element 70 corresponds approximately to a radially inner diameter of the housing 56. In this case, an at least small radial gap is present between the annular valve element 70 and the housing 56, so that the annular
  • Valve element 70 in the housing 56 according to a function of
  • Pressure relief valve 54 is axially movable.
  • a valve spring of the pressure limiting valve 54 is arranged in the form of a leaf spring 72.
  • the leaf spring 72 is designed substantially as a curved cylindrical and centrally perforated disc. In the drawing to the left of the leaf spring 72, a second spring support 74 is arranged. Accordingly, the
  • Leaf spring 72 between the second spring support 74 and the annular valve member 70 build a compressive force by which the valve element 70 is acted upon against the sealing seat 78.
  • two axial fluid channels 80 which are arranged in a radially approximately central region of the valve seat body 58, are visible on the valve seat body 58. In the state of the arrangement shown in FIG. 2, the axial fluid channels 80 are closed on one side by the annular valve element 70.
  • the spring supports 68 and 74 are designed substantially "annular" in each case as a perforated cylindrical disc, wherein a respective radially outer portion of the spring supports 68 and 74 arranged on an associated radially inner portion of the housing 56, in the present case is compressed.
  • a respective centric hole allows a flow of fuel.
  • Exhaust valve 32 according to Figure 2 in a similar manner to Figure 1 way. If in a delivery stroke of the fuel high-pressure pump 10, a fuel pressure in the delivery chamber 42 is greater than a fuel pressure in the high pressure line 28 - plus the force of the spring 35 - so the cup-shaped valve body 33 of the sealing seat 66 on the valve seat body 58 in the drawing after lift off to the right, whereby the exhaust valve 32 opens.
  • a hydraulic connection between the delivery chamber 42 and the high-pressure line 28 and thereby a delivery of fuel as follows: Through the central opening of the second spring support 74, then through the central opening of the leaf spring 72, then through the central opening in the annular valve element 70, then through the central opening in the valve seat body 58, then through a radially au ßerraum the cup-shaped valve body 33 and a radial radially formed within the valve seat body 58 radial gap, then radially inwardly into a region of the spring 35, then axially through a central opening in the first spring support 68, then by an approximately nozzle-shaped, that is conical and cylindrical radially inner cavity of the
  • the fuel pressure in the high-pressure line 28 is greater than the pressure in the delivery chamber 42, plus the force exerted by the leaf spring 72 on the annular valve element 70 force, so that can
  • Fuel pressure does not exceed the maximum value, the pressure relief valve 54 is closed.
  • the valve body 33 is cup-shaped, and the annular valve element 70 disc-shaped, both elements have a comparatively low mass, whereby the outlet valve 32 and the pressure relief valve 54 can open or close relatively quickly.
  • Figure 3 shows a similar to the embodiment of Figure 2
  • Leaf spring 72 is supported in contrast to the figure 2 at an inner end face of the housing 56.
  • the housing 56 has a radially inner diameter step.
  • FIG. 3 Drawing to be mounted from the right.
  • the remaining arrangement and form of the elements of FIG. 3 essentially correspond to those of FIG. 2.
  • FIG. 4 shows, based on the representation of FIG. 3, a further one
  • valve seat body 58 has a simplified geometry with respect to FIGS. 2 and 3. In this case, a radially inner diameter jump of the central bore 59 in the valve seat body 58 is not present.
  • the sealing seat 66 of the outlet valve 32 which is also designed as an annular web in the embodiment according to FIG. 4, is arranged on the valve seat body 58 on a front end in the drawing.
  • Valve seat body 58 separately arranged guide member 76, wherein a radially externa ßerer portion of the valve body 33 is guided radially in the guide member 76.
  • the guide element 76 is shown only schematically. In particular, anchoring of the guide element 76 on the housing 56 is not shown for the sake of simplicity.
  • Pressure relief valve 54 correspond to those of Figures 2 and 3. Likewise, the function of the combined exhaust valve 32 and
  • FIG. 5 shows a perspective view of an integrally formed with the leaf spring 72 valve member 70 of the pressure relief valve 54 together with an axial portion of the valve seat body shown in simplified form 58.
  • the leaf spring 72 here additionally assumes the function of the annular Valve element 70 and thus is in relation to the valve function "direct acting".
  • the leaf spring 72 two approximately cylindrically executed sealing portions (in the figure 5 by the reference numeral "70")), which can close the present two axial fluid channels 80 in the valve seat body 58.
  • the leaf spring 72 In a closed state of the pressure limiting valve 54, the leaf spring 72 is substantially struck only with the cylindrical sealing portions on the sealing seat 78 of the valve seat body 58. If a fuel pressure in the high-pressure line 28 is greater than a fuel pressure in the delivery chamber 42 plus the axial force applied by the leaf spring 72, the two cylindrical sealing sections of the leaf spring 72 can lift off the sealing seat 78 and thus return fuel flow from the high-pressure line 28 back into the Allow delivery chamber 42.

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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)
  • Safety Valves (AREA)

Abstract

L'invention concerne une pompe à carburant à haute pression (10). Ladite pompe comporte un clapet de sortie (32) disposé entre une chambre d'alimentation (42) et une sortie (30), ainsi qu'un clapet limiteur de pression (54) disposé entre la sortie (30) et la chambre d'alimentation (42). Selon l'invention, le clapet de sortie (32) et le clapet limiteur de pression (54) possèdent un corps de siège de clapet commun (58).
PCT/EP2014/050538 2013-03-15 2014-01-14 Pompe à carburant à haute pression avec clapet de sortie disposé entre une chambre d'alimentation et une sortie Ceased WO2014139698A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
KR1020157025157A KR102122709B1 (ko) 2013-03-15 2014-01-14 송출 챔버와 배출부 사이에 배치된 배출 밸브를 구비한 고압 연료 펌프
CN201480013958.2A CN105190017A (zh) 2013-03-15 2014-01-14 具有布置在输送室和出口之间的出口阀的燃料高压泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013204563.8A DE102013204563A1 (de) 2013-03-15 2013-03-15 Kraftstoff-Hochdruckpumpe mit einem zwischen einem Förderraum und einem Auslass angeordneten Auslassventil
DE102013204563.8 2013-03-15

Publications (1)

Publication Number Publication Date
WO2014139698A1 true WO2014139698A1 (fr) 2014-09-18

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2014/050538 Ceased WO2014139698A1 (fr) 2013-03-15 2014-01-14 Pompe à carburant à haute pression avec clapet de sortie disposé entre une chambre d'alimentation et une sortie

Country Status (4)

Country Link
KR (1) KR102122709B1 (fr)
CN (1) CN105190017A (fr)
DE (1) DE102013204563A1 (fr)
WO (1) WO2014139698A1 (fr)

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JP2019173588A (ja) * 2018-03-27 2019-10-10 株式会社ケーヒン 弁ユニット固定構造

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DE102017209901A1 (de) 2017-06-13 2018-12-13 Robert Bosch Gmbh Gas-Druckbegrenzungsventil zum Steuern und Ablassen von einem gasförmigen Medium
DE102017209906A1 (de) 2017-06-13 2018-12-13 Robert Bosch Gmbh Gas-Druckbegrenzungsventil mit Ringspaltsitz zum Steuern und Ablassen von einem gasförmigen Medium
US10982633B2 (en) * 2017-07-03 2021-04-20 Continental Automotive Systems, Inc. Fuel pump solenoid assembly method
DE102017211981B3 (de) * 2017-07-13 2018-09-27 Continental Automotive Gmbh Kraftstoffeinspritzsystem für eine Brennkraftmaschine
CN109386635B (zh) * 2017-08-04 2019-12-06 大陆汽车电子(长春)有限公司 用于高压泵的双向阀和高压泵
CN107605632B (zh) * 2017-10-17 2020-02-07 奇瑞汽车股份有限公司 一种汽车发动机高压油泵
CN107859582B (zh) * 2017-10-17 2020-12-01 奇瑞汽车股份有限公司 一种汽车发动机油泵
DE102018201279B4 (de) * 2018-01-29 2019-11-28 Continental Automotive Gmbh Hochdruckanschluss für eine Kraftstoffhochdruckpumpe eines Kraftstoffeinspritzsystems sowie Kraftstoffhochdruckpumpe
DE102018206763A1 (de) * 2018-05-02 2019-11-07 Robert Bosch Gmbh Ventileinrichtung für eine Hochdruckpumpe
KR102107464B1 (ko) * 2018-12-20 2020-05-07 주식회사 현대케피코 고압펌프
US11352994B1 (en) * 2021-01-12 2022-06-07 Delphi Technologies Ip Limited Fuel pump and combination outlet and pressure relief valve thereof
KR102712960B1 (ko) * 2021-09-30 2024-10-07 (주)모토닉 엘피아이 연료펌프의 밸브구조

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EP0147591A2 (fr) * 1983-12-12 1985-07-10 Robert Bosch Gmbh Soupape d'alimentation pour pompes d'injection de carburant
JPH02132847U (fr) * 1989-04-10 1990-11-05
US20040177884A1 (en) * 2003-03-14 2004-09-16 Denso Corporation Simple structure of fuel pressure regulator designed to minimize pressure loss
WO2011048456A1 (fr) * 2009-10-22 2011-04-28 Toyota Jidosha Kabushiki Kaisha Pompe à carburant
KR20110051826A (ko) * 2009-11-11 2011-05-18 현대자동차주식회사 고압 연료 펌프의 토출 밸브와 압력 릴리프 밸브 일체형 구조
US20110126804A1 (en) * 2009-12-01 2011-06-02 Lucas Robert G Common rail fuel pump with combined discharge and overpressure relief valves
EP2497939A1 (fr) * 2011-03-08 2012-09-12 Hitachi Automotive Systems, Ltd. Pompe d'alimentation en carburant haute pression
US20120251365A1 (en) * 2011-03-30 2012-10-04 Denso Corporation High pressure fuel pump
WO2013027242A1 (fr) * 2011-08-24 2013-02-28 トヨタ自動車株式会社 Dispositif de régulation de fluide et système d'alimentation en combustible

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DE3843819A1 (de) * 1988-09-09 1990-03-22 Bosch Gmbh Robert Druckventil
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Publication number Priority date Publication date Assignee Title
EP0147591A2 (fr) * 1983-12-12 1985-07-10 Robert Bosch Gmbh Soupape d'alimentation pour pompes d'injection de carburant
JPH02132847U (fr) * 1989-04-10 1990-11-05
US20040177884A1 (en) * 2003-03-14 2004-09-16 Denso Corporation Simple structure of fuel pressure regulator designed to minimize pressure loss
WO2011048456A1 (fr) * 2009-10-22 2011-04-28 Toyota Jidosha Kabushiki Kaisha Pompe à carburant
KR20110051826A (ko) * 2009-11-11 2011-05-18 현대자동차주식회사 고압 연료 펌프의 토출 밸브와 압력 릴리프 밸브 일체형 구조
US20110126804A1 (en) * 2009-12-01 2011-06-02 Lucas Robert G Common rail fuel pump with combined discharge and overpressure relief valves
EP2497939A1 (fr) * 2011-03-08 2012-09-12 Hitachi Automotive Systems, Ltd. Pompe d'alimentation en carburant haute pression
US20120251365A1 (en) * 2011-03-30 2012-10-04 Denso Corporation High pressure fuel pump
WO2013027242A1 (fr) * 2011-08-24 2013-02-28 トヨタ自動車株式会社 Dispositif de régulation de fluide et système d'alimentation en combustible

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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