WO2005057004A1 - Ventilanordnung, insbesondere einlassventil einer hochdruck-kraftstoffpumpe - Google Patents
Ventilanordnung, insbesondere einlassventil einer hochdruck-kraftstoffpumpe Download PDFInfo
- Publication number
- WO2005057004A1 WO2005057004A1 PCT/DE2004/002343 DE2004002343W WO2005057004A1 WO 2005057004 A1 WO2005057004 A1 WO 2005057004A1 DE 2004002343 W DE2004002343 W DE 2004002343W WO 2005057004 A1 WO2005057004 A1 WO 2005057004A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- channel section
- valve
- channel
- valve arrangement
- longitudinal axis
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of 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
- F02M59/02—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
- F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
- F02M59/06—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
-
- 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
- F02M59/44—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
-
- 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
- F02M63/02—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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0452—Distribution members, e.g. valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/001—Noise damping
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/06—Venting
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
-
- 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
- F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/206—Flow affected by fluid contact, energy field or coanda effect [e.g., pure fluid device or system]
- Y10T137/2087—Means to cause rotational flow of fluid [e.g., vortex generator]
Definitions
- Valve arrangement in particular inlet valve of a high-pressure fuel pump
- the invention relates to a valve arrangement, in particular an inlet valve arrangement of a high-pressure fuel pump, with a valve element arranged in a valve chamber and a fluid channel adjoining the valve chamber upstream.
- a valve arrangement of the type mentioned is known from the market. It is used, for example, in a high-pressure fuel pump of a common rail injection system. Such high pressure fuel umpe is designed as a piston pump. A ball check valve is provided as an inlet valve to a delivery chamber. The ball of the
- Check valve is arranged in a valve chamber into which an inlet bore opens.
- the inlet bore comprises a first channel section which is essentially perpendicular to the longitudinal axis of a piston of the piston pump, and a second channel section which is coaxial to the longitudinal axis of the piston of the piston pump.
- the longitudinal axes of the two channel sections intersect in an intersection area. In this intersection area, there is a sharp-edged deflection of the fuel flowing to the inlet valve during operation of the piston pump.
- the object of the present invention is a valve arrangement of the type mentioned to further develop that it works with as little loss as possible and, as a result, the efficiency, for example of a high-pressure fuel pump, in which the valve arrangement is used, is improved.
- Opening time of the valve element leads to a greater throughput.
- the length of the fluid channel can also be shorter, which overall reduces the size of the valve arrangement and, for example, a fuel pump in which it is used. Due to the swirling flow otherwise existing highly unsteady turbulent flow processes (pulse-like speed profile) is reduced or completely prevented, which reduces the load on the fluid channel and a region located further upstream. For example, a feed pump that supplies the fluid to the valve arrangement is also protected.
- valve element Due to the even flow in the fluid channel, the valve element itself is evenly flowed around and remains in the center even in the open state of suspension, which means that there is no transverse force on the valve due to a fluid flowing past on one side. This also leads to an improvement in the efficiency of the valve arrangement and to a reduction in wear on the valve element.
- the fluid channel comprises a first channel section and a second channel section adjoining it, the longitudinal axes of the channel sections being at an angle of ⁇ 180 ° to one another, and the longitudinal axis of the first channel section being laterally offset from the longitudinal axis of the second channel section.
- the rotation of the flow in the second channel section is caused in a simple manner by the lateral offset. Turbulence generated due to the kink between the two channel sections is effectively smoothed out, or such turbulence cannot arise at all.
- the rotation is particularly clear when the longitudinal axes of the two channel sections are at least approximately at right angles to one another. In this case, the swirl imparted to the flow in the second channel section is strongest, and therefore those with the Advantages achievable valve assembly according to the invention greatest.
- valve arrangement comprises a ball or a cone element as a valve element.
- these rotationally symmetrical valve elements Due to the rotational movement of the fluid flowing to the valve chamber, these rotationally symmetrical valve elements are also set in rotation. This prevents one-sided wear on these valve elements and increases the durability of a valve seat assigned to the valve element.
- a particularly preferred embodiment of the valve arrangement according to the invention is characterized in that the two channel sections have at least approximately the same radius in cross section and that the lateral offset of the longitudinal axes is greater than the radius. This simplifies the manufacture of the valve arrangement according to the invention and thus lowers the manufacturing costs, since the same drilling tool can be used for both channel sections.
- a transition area between the first channel section and the second channel section be machined by means of electrochemical material removal. This enables a largely edge-free transition from one channel section to the other channel section, which is also favorable for a uniform flow.
- the transition area comprises a wall curved from the first to the second channel section. This leads to a particularly smooth flow in which little turbulence occurs. It is also particularly preferred if the first channel section does not extend axially or not significantly beyond the second channel section. As a result, the dynamic pressure upstream of the deflection from the first channel section to the second channel section is reduced, which further reduces the flow resistance and improves the overall efficiency of the valve arrangement in terms of flow technology.
- the longitudinal axis of the first channel section and the longitudinal axis of the second channel section enclose an angle> 90 °. This leads to an additional reduction in resistance.
- Figure 1 is a schematic representation of an internal combustion engine with a high pressure fuel pump
- FIG. 2 shows a section through a housing of the high-pressure fuel pump from FIG. 1;
- Figure 4 shows a detail IV of Figure 2
- FIG. 5 shows a section along the line VV of Figure 4;
- Figure 6 is a section along the line VI-VI of Figure 4;
- FIG. 8 shows a representation similar to FIG. 3 of a modified embodiment of a housing of the high-pressure fuel pump from FIG. 1.
- An internal combustion engine bears the overall reference number 10 in FIG. 1. It comprises a fuel tank 12, from which a prefeed pump 14 converts the fuel to one
- High pressure fuel pump 16 promotes. This compresses the fuel to a very high pressure and delivers it to a fuel collecting line 18 (“rail”), in which the fuel is stored under high pressure. A plurality of injectors 20 are connected to these and inject the fuel directly into combustion chambers 22 assigned to them.
- a housing 24 of the high-pressure fuel pump 16 is shown in greater detail in FIGS. 2 and 3. It comprises three cylinders 26a, 2 ⁇ b, and 26c, which are constructed essentially identically. For the sake of simplicity, only the cylinder 26a is referred to below.
- a piston bore 28 is present in the cylinder 26a, in which a piston, not shown, is accommodated in a longitudinally displaceable manner.
- the piston bore 28 can be connected to a fuel inlet 32 via a fluid channel 30.
- the fuel inlet 32 is in turn connected to the prefeed pump 14.
- the fluid channel 28 is divided into two channel sections 34 and 36.
- the first duct section 34 extends at an angle from an inlet duct (without reference number), which in turn leads away from a fuel inlet 32. To the outside, the first channel section 34 is blocked by a ball that is not provided with reference symbols.
- Its longitudinal axis 38 runs perpendicular to the longitudinal axis 40 of the piston bore 28 and of the second channel section 36 (see FIG. 3). However, the two longitudinal axes 38 and 40 do not intersect. As especially from the
- the longitudinal axis 38 of the first channel section 34 is instead laterally offset with respect to the longitudinal axis 40 of the second channel section 36.
- the lateral offset is designated by V in FIGS. 6 and 7.
- the two channel sections 38 and 40 have the same radius, which is greater than the lateral offset V of the two longitudinal axes 38 and 40.
- a valve chamber 42 is present between the second channel section 36 of the fluid channel 30 and the piston bore 28. Between the valve chamber 42 and the second channel section 36, a shoulder is formed, which forms a valve seat 44 for a valve ball 46, which in the Valve chamber 42 is received (see Figures 4 and 5). The valve ball 46 is urged against the valve seat 44 by a spring, not shown in the drawing. A delivery chamber 47 connects to the valve chamber 42. As can also be seen in particular from FIG. 7, the first channel section 34 hardly extends beyond the second channel section 36. The fluid channel 30, the valve seat 44 and the valve ball 46 overall form a valve arrangement 47.
- the high-pressure fuel pump 16 operates as follows (again, only the cylinder 26a is referred to here):
- valve ball 46 lifts off the valve seat 44.
- the fuel passes from the first channel section 34 into the second channel section 36. It experiences a change in direction of 90 °. Due to the lateral movement component 48, however, the fluid flow in the second channel section 36 additionally results in a rotary movement about the longitudinal axis 40 of the second Channel section 36 a. This rotary movement is also referred to as "swirl" or “spin” and bears the reference symbol 50 in FIGS. 6 and 7.
- the swirl 50 prevents the fluid flow in the transition region between the first channel section 34 and the second channel section 36 from changing Flow detaches, which would lead to increased flow resistance and the risk of cavitation and corresponding wear.
- the swirl 50 also causes the valve ball 46 to rotate in the open state, so that it wears evenly.
- their sealing effect and that of the valve seat 44 is retained over a very long period of time. Since separation of the fuel flow in the transition area between the two channel sections 34 and 36 and in particular in the second channel section 36 is prevented, there is also no constriction of the fluid flow with a correspondingly reduced hydraulic diameter, which would lead to increased throttling.
- FIG. 8 An alternative embodiment is shown in FIG. 8. Elements and areas which have functions equivalent to elements and areas of the previous figures have the same reference numerals. They are not explained in detail again.
- the longitudinal axis 38 of the first channel section 34 is not at an angle of 90 °, but at an angle of approximately 45 ° to the longitudinal axis 40 of the second channel section 36. less drag flow realized.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006543352A JP4373447B2 (ja) | 2003-12-10 | 2004-10-21 | 弁装置 |
EP04802632A EP1700028B1 (de) | 2003-12-10 | 2004-10-21 | Ventilanordnung, inbesondere einlassventil einer hochdruck-kraftstoffpumpe |
DE200450006447 DE502004006447D1 (de) | 2003-12-10 | 2004-10-21 | Ventilanordnung, inbesondere einlassventil einer hochdruck-kraftstoffpumpe |
US10/581,415 US20080190502A1 (en) | 2003-12-10 | 2004-10-21 | Valve Assembly, in Particular Inlet Valve of a High-Pressure Fuel Pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10357612.6 | 2003-12-10 | ||
DE2003157612 DE10357612A1 (de) | 2003-12-10 | 2003-12-10 | Ventilanordnung, insbesondere Einlassventil einer Hochdruck-Kraftstoffpumpe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005057004A1 true WO2005057004A1 (de) | 2005-06-23 |
Family
ID=34638560
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2004/002343 WO2005057004A1 (de) | 2003-12-10 | 2004-10-21 | Ventilanordnung, insbesondere einlassventil einer hochdruck-kraftstoffpumpe |
Country Status (6)
Country | Link |
---|---|
US (1) | US20080190502A1 (de) |
EP (1) | EP1700028B1 (de) |
JP (1) | JP4373447B2 (de) |
CN (1) | CN1894499A (de) |
DE (2) | DE10357612A1 (de) |
WO (1) | WO2005057004A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009103572A1 (en) * | 2008-02-22 | 2009-08-27 | Robert Bosch Gmbh | High-pressure pump for feeding high-pressure fuel to an internal-combustion engine |
WO2010094366A1 (de) * | 2009-02-18 | 2010-08-26 | Robert Bosch Gmbh | Brennstoffpumpe |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016220610A1 (de) * | 2016-10-20 | 2018-04-26 | Robert Bosch Gmbh | Hochdruckpumpe für ein Kraftstoffeinspritzsystem |
JP6988196B2 (ja) * | 2017-06-27 | 2022-01-05 | 株式会社Soken | 燃料噴射装置 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3804843A1 (de) * | 1988-02-17 | 1989-08-31 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE3937707A1 (de) * | 1988-12-24 | 1991-05-16 | Bosch Gmbh Robert | Druckventil |
DE19500690A1 (de) * | 1995-01-12 | 1996-07-18 | Bosch Gmbh Robert | Kraftstoffversorgungsanlage und Verfahren zum Betreiben einer Kraftstoffversorgungsanlage |
WO1997017538A1 (de) * | 1995-11-08 | 1997-05-15 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für brennkraftmaschinen |
WO2004109093A1 (de) * | 2003-05-22 | 2004-12-16 | Robert Bosch Gmbh | Rückschlagventil, insbesondere für eine hochdruckpumpe einer kraftstoffeinspritzeinrichtung für eine brennkraftmaschine |
Family Cites Families (16)
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US712929A (en) * | 1901-10-28 | 1902-11-04 | George M Hendee | Valve for internal-combustion engines. |
US1105134A (en) * | 1913-11-12 | 1914-07-28 | Engelbert Hanemann | Carbureter. |
US1517598A (en) * | 1921-09-01 | 1924-12-02 | Stevenson John William | Apparatus for spraying fluids and mixing the same |
NL299872A (de) * | 1962-10-30 | 1900-01-01 | ||
US3797510A (en) * | 1971-10-28 | 1974-03-19 | Purolator Inc | Crashworthy valve |
US3854468A (en) * | 1972-01-17 | 1974-12-17 | Rheem Mfg Co | Vortex humidifier for forced flow hot air furnace |
US3921656A (en) * | 1974-06-20 | 1975-11-25 | Spectrum Ass Inc | Self-closing breakaway valve assemblies |
US4131134A (en) * | 1977-05-04 | 1978-12-26 | Owen, Wickersham & Erickson | Fluid flow regulator |
US4157281A (en) * | 1977-07-14 | 1979-06-05 | Systems Technology Corp | Method and apparatus for reclaiming solvents from solvent-bearing sludge material |
US4574451A (en) * | 1982-12-22 | 1986-03-11 | General Electric Company | Method for producing an article with a fluid passage |
US4827961A (en) * | 1987-10-13 | 1989-05-09 | Helix Enterprises, Inc. | High velocity fluid swivel joint coupling |
DE3843819A1 (de) * | 1988-09-09 | 1990-03-22 | Bosch Gmbh Robert | Druckventil |
JP2001246216A (ja) * | 1999-12-28 | 2001-09-11 | Denso Corp | 気液分離装置 |
US7082955B2 (en) * | 2001-12-04 | 2006-08-01 | Ecotechnology, Ltd. | Axial input flow development chamber |
CA2364516C (en) * | 2001-12-04 | 2010-10-19 | Ecotech Systems International, Ltd. | Flow development chamber |
JP4260697B2 (ja) * | 2004-06-29 | 2009-04-30 | 三菱電機株式会社 | 電磁弁 |
-
2003
- 2003-12-10 DE DE2003157612 patent/DE10357612A1/de not_active Withdrawn
-
2004
- 2004-10-21 EP EP04802632A patent/EP1700028B1/de active Active
- 2004-10-21 JP JP2006543352A patent/JP4373447B2/ja not_active Expired - Fee Related
- 2004-10-21 DE DE200450006447 patent/DE502004006447D1/de active Active
- 2004-10-21 CN CNA2004800369928A patent/CN1894499A/zh active Pending
- 2004-10-21 US US10/581,415 patent/US20080190502A1/en not_active Abandoned
- 2004-10-21 WO PCT/DE2004/002343 patent/WO2005057004A1/de active IP Right Grant
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3804843A1 (de) * | 1988-02-17 | 1989-08-31 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE3937707A1 (de) * | 1988-12-24 | 1991-05-16 | Bosch Gmbh Robert | Druckventil |
DE19500690A1 (de) * | 1995-01-12 | 1996-07-18 | Bosch Gmbh Robert | Kraftstoffversorgungsanlage und Verfahren zum Betreiben einer Kraftstoffversorgungsanlage |
WO1997017538A1 (de) * | 1995-11-08 | 1997-05-15 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für brennkraftmaschinen |
WO2004109093A1 (de) * | 2003-05-22 | 2004-12-16 | Robert Bosch Gmbh | Rückschlagventil, insbesondere für eine hochdruckpumpe einer kraftstoffeinspritzeinrichtung für eine brennkraftmaschine |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009103572A1 (en) * | 2008-02-22 | 2009-08-27 | Robert Bosch Gmbh | High-pressure pump for feeding high-pressure fuel to an internal-combustion engine |
WO2010094366A1 (de) * | 2009-02-18 | 2010-08-26 | Robert Bosch Gmbh | Brennstoffpumpe |
CN102325997B (zh) * | 2009-02-18 | 2015-05-20 | 罗伯特·博世有限公司 | 燃料泵 |
Also Published As
Publication number | Publication date |
---|---|
DE10357612A1 (de) | 2005-07-07 |
CN1894499A (zh) | 2007-01-10 |
US20080190502A1 (en) | 2008-08-14 |
DE502004006447D1 (de) | 2008-04-17 |
JP2007513292A (ja) | 2007-05-24 |
EP1700028A1 (de) | 2006-09-13 |
EP1700028B1 (de) | 2008-03-05 |
JP4373447B2 (ja) | 2009-11-25 |
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