WO2006040274A1 - Vorrichtung zum fördern von kraftstoff - Google Patents
Vorrichtung zum fördern von kraftstoff Download PDFInfo
- Publication number
- WO2006040274A1 WO2006040274A1 PCT/EP2005/054977 EP2005054977W WO2006040274A1 WO 2006040274 A1 WO2006040274 A1 WO 2006040274A1 EP 2005054977 W EP2005054977 W EP 2005054977W WO 2006040274 A1 WO2006040274 A1 WO 2006040274A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve
- pressure
- control
- shut
- valve seat
- Prior art date
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 38
- 238000002485 combustion reaction Methods 0.000 claims abstract description 19
- 238000011144 upstream manufacturing Methods 0.000 claims description 16
- 238000010079 rubber tapping Methods 0.000 claims description 7
- 238000004519 manufacturing process Methods 0.000 abstract description 2
- 239000002828 fuel tank Substances 0.000 description 3
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 230000001419 dependent effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000003502 gasoline Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
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
- 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
-
- 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
- F02M37/0047—Layout or arrangement of systems for feeding fuel
- F02M37/0052—Details on the fuel return circuit; Arrangement of pressure regulators
- F02M37/0058—Returnless fuel systems, i.e. the fuel return lines are not entering the fuel tank
-
- 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
- F02M37/0076—Details of the fuel feeding system related to the fuel tank
- F02M37/0088—Multiple separate fuel tanks or tanks being at least partially partitioned
- F02M37/0094—Saddle tanks; Tanks having partition walls
-
- 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
- F02M37/02—Feeding by means of suction apparatus, e.g. by air flow through carburettors
- F02M37/025—Feeding by means of a liquid fuel-driven jet pump
-
- 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
- F02M37/04—Feeding by means of driven pumps
- F02M37/08—Feeding by means of driven pumps electrically driven
- F02M37/10—Feeding by means of driven pumps electrically driven submerged in fuel, e.g. in reservoir
- F02M37/106—Feeding by means of driven pumps electrically driven submerged in fuel, e.g. in reservoir the pump being installed in a sub-tank
-
- 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
- F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
- F02M69/46—Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
- F02M69/54—Arrangement of fuel pressure regulators
-
- 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
- Y10T137/8593—Systems
- Y10T137/85978—With pump
- Y10T137/85986—Pumped fluid control
- Y10T137/86002—Fluid pressure responsive
- Y10T137/86019—Direct response valve
Definitions
- the invention relates to a device for conveying fuel according to the preamble of the main claim. It is already known a device for conveying fuel from DE 199 36287 C2, with a suction jet pump and the suction jet pump with fuel supply tapping line, which branches off from a leading to an internal combustion engine pressure line and can be shut off by means of a shut-off valve.
- a shut-off valve By means of the electrically switchable shut-off valve, it is possible regardless of the pressure downstream of a feed pump and independent of the operating conditions of an internal combustion engine to turn off the ejector.
- the disadvantage is that the electrically switchable shut-off valve is relatively expensive.
- the inventive device for conveying fuel with the characterizing features of the main claim has the advantage that in a simple way an improvement is achieved in that the manufacturing costs are reduced by the pressure of the pressure line acts on the shut-off valve, that this automatically at a pressure greater than or equal to a predetermined closing pressure closes. In this way, an electrically switchable actuator is saved.
- the measures listed in the dependent claims advantageous refinements and improvements of the main claim device are possible.
- the shut-off valve as a diaphragm valve or as
- Piston valve formed as these are particularly simple and inexpensive embodiments.
- shut-off valve has an input connection and control connection which is flow-connected upstream with the pressure line and an output connection which leads downstream to the at least one suction jet pump, since in this way it can be achieved that the pressure of the pressure line causes closure of the shut-off valve.
- the first closing body in the shape of a piston with a first piston section and / or a second piston section.
- the pressure of the pressure line in the first valve seat facing direction acts on the first closing body, and a return spring is provided, which presses the first closing body in the direction away from the first valve seat, as on the first closing body in this way a balance of power between the force acting on the first closing body pressure force of the pressure line and the spring force of the return spring results.
- the first piston section is arranged in the valve chamber and extends into the control chamber and the second piston section is provided in the control chamber. Furthermore, it is advantageous that the treble line branches off from the pressure line upstream of a check valve arranged in the pressure line, since in this way it is achieved that the shut-off valve opens when the feed pump is switched off.
- the brake line upstream or downstream of the shut-off valve has a throttle element, since in this way the volume flow from the pressure line to the at least one suction jet pump is limited.
- Control terminal and the control chamber of the shut-off valve to arrange a control valve, which is connected for example in one piece with the shut-off valve.
- control valve has a second closing body cooperating with a second valve seat and a third valve seat.
- Embodiment provides that the second closing body is piston-shaped and axially movable between the second valve seat and the third valve seat.
- control chamber is fluidly connected to the second valve seat at the second valve seat with a leakage connection, since the control chamber is depressurized in this way and can be emptied via a leakage line.
- control chamber is fluidly connected to the control port upon application of the second closing body to the third valve seat, since the
- Control chamber is pressurized in this way with the pressure of the pressure line.
- FIG. 1 shows a view of a device for conveying fuel
- FIG. 2 shows a first exemplary embodiment of a shut-off valve according to the invention
- FIG. 3 shows a second exemplary embodiment
- FIG. 4 shows a third exemplary embodiment of the shut-off valve according to the invention.
- Fig.l shows a device for conveying fuel from a reservoir to an internal combustion engine, in which an inventive shut-off valve could be used.
- the device serves to provide an internal combustion engine with sufficient fuel for combustion in a combustion chamber.
- the device has a delivery module 2 arranged in a storage container 1 with a cylindrical swirl pot 3, in which, for example, a feed pump 4 and a main filter 5 are arranged.
- the feed pump 4 is for example an electric fuel pump.
- the feed pump 4 sucks, for example, fuel via an input channel 8 from the swirl pot 3 and delivers the fuel under pressure via an output channel 9 of the feed pump 4 in a pressure line 11, which leads, for example, to a fuel rail 14 of an internal combustion engine 15.
- the fuel rail 14 is connected to a plurality of injectors 16 which inject the fuel into cylinders, not shown, of the internal combustion engine.
- the pressure line 11 can downstream but also with a high pressure pump of a so-called gasoline direct injection or a
- Be connected diesel injection system which injects the fuel under high pressure in a fuel rail and injection valves in cylinders of the internal combustion engine.
- the storage container 1 is, for example, a so-called saddle tank with a saddle 6 which divides the storage container 1 into at least two separate regions, for example a first region 1.1 and a second region 1.2.
- the delivery module 2 is arranged, for example, in the first region 1.1.
- a known tank level sensor 17 for measuring a level 18 in the reservoir 1 is provided.
- the pressure line 11 of the Kleinf ⁇ lter 5 has upstream or downstream, for example, upstream of the Hauptf ⁇ lters 5 a check valve
- a pressure relief valve 20 may be provided which opens at a pressure in the pressure line 11 downstream of the check valve 19 equal to a predetermined opening pressure and fuel from the pressure line 11 from downstream of the check valve 19 to pressure relief after the upstream of the check valve 19 flows back.
- the pressure relief valve 20 opens in the opposite direction to the check valve 19.
- the pressure line 11 downstream of the check valve 19 facing connection of the pressure relief valve 20 is, for example, with the pressure line 11 upstream of the Hauptf ⁇ lters 5, as shown in Fig.l, or with the pressure line 11 downstream of the Hauptf ⁇ lters 5, as shown for example in Figure 2, fluidly connected.
- a pressure increase in the pressure line 11 with a resulting opening of the pressure relief valve 20 may be caused, for example, by an increase in the temperature after switching off the internal combustion engine 15.
- the tether 21 branches in a saddle tank, for example in a first Treb effetsabêt 21.1 and a second Treb effet 21.2, the first Treb effetsabêt 21.1 with a first suction jet pump 22 and the second Treb effet 21.2 with a second suction jet pump 23 is fluidly connected.
- the first suction jet pump 22 is arranged, for example, on the delivery module 2 and promotes fuel during operation fuel from the first region 1.1 of the fuel tank 1 in the surge chamber 3 of the conveyor module 2.
- the second suction jet pump 23 is provided for example in the second region 1.2 of the fuel tank 1 and promotes fuel from the second area 1.2 via a return line 24 during operation also in the swirl pot 3 or in the first area 1.1 of the fuel tank 1.
- the first suction jet pump 22 is arranged, for example, on the delivery module 2 and promotes fuel during operation fuel from the first region 1.1 of the fuel tank 1 in the surge chamber 3 of the conveyor module 2.
- the second suction jet pump 23 is provided for example in the second region
- Suction jet pump 22 and the second suction jet pump 23 are each arranged near a tank bottom 25 of the storage container 1.
- the speed of the feed pump 4 is dependent on the pressure downstream of the feed pump 4, for example, depending on the pressure in the pressure line 11 or in the
- Fuel distributor 14 regulated.
- a pressure sensor 28 is provided, which determines the pressure, for example in the pressure line 11 or in the fuel rail 14 and passes as a controlled variable to an electronic control unit 29, which takes over the control of the feed pump 4.
- the fuel delivery with speed control of the feed pump 4 is also referred to as demand-controlled fuel delivery.
- a shut-off valve 30 is arranged in the third brake line 21, for example upstream of the treble line sections 21.1, 21.2.
- the shut-off valve 30 serves to take place via the haulage line 21 fuel supply of the suction jet pumps 22,23 at fuel pressures in the pressure line 11, which is greater than or equal to a predetermined
- the predetermined pressure in the pressure line 11 is achieved without a more powerful and expensive feed pump 4 in sufficient time.
- the pressure downstream of the feed pump 4 acts on the shut-off valve 30 such that it automatically closes at a pressure greater than or equal to a predetermined closing pressure.
- a flow cross section of the haulage line 21 is closed so that no more fuel passes from the pressure line 11 to the suction jet pumps 22, 23.
- the feed pump 4 is controlled at engine start so that the pressure in the pressure line 11 reaches a value which is greater than the closing pressure of the shut-off valve 30 and greater than the pressure in the pressure line 11 at full load operation.
- the erf ⁇ ndungsgemässe shut-off valve 30 is compared to an example, solenoid-operated shut-off valve 30 significantly cheaper to produce.
- FIG. 2 shows a section of a view of a first embodiment of the invention Abschaltventils.
- the inventive Abschaltventil 30 is formed according to the first embodiment as a diaphragm valve.
- the shut-off valve 30 has, for example, an input port 33, a
- the inlet connection 33 is connected to the section of the tapping line 21 leading to the pressure line 11 and the outlet connection 34 to the section of the tapping line 21 leading to the at least one suction jet pump 22, 23.
- the control port 35 is fluidly connected to the pressure line 11, for example indirectly via the tether line 21st
- a throttle element 40 is arranged, for example, in order to limit the volume flow flowing to the at least one suction jet pump 22, 23.
- the throttle element 40 may also be arranged in the drive line 21, 21.1, 21.2 downstream of the outlet connection 34 of the shut-off valve 30.
- valve chamber 36 is an axially with respect to a valve axis 39 movable first closing body 37 and one with the first Schliesspian 37 cooperating first valve seat 38 is provided.
- the first closing body 37 and the first valve seat 38 form for example a ball-cone, cone-ball, conical-cone, ball-ball seat or a flat seat.
- the output port 34 of the shut-off valve 30 opens into the valve chamber 36 via a valve seat opening 41 which can be closed by the first closing body 37.
- Schliessharmtage 37 is for example piston-shaped with a first piston portion 37.1 and / or a second piston portion 37.2, wherein the first piston portion 37.1 cooperates with the first valve seat 38 and from the valve chamber 36 via a valve passage 42 into an example cylindrical control chamber 43 of the shut-off valve 30th enough.
- the second piston portion 37.2 is arranged in the control chamber 43 and connected in one piece with the first piston portion 37.1.
- the second piston section 37.2 divides the control chamber 43, for example, into a pressure chamber 44 connected to the control port 35 and a spring chamber 45 connected to the atmosphere.
- the pressure chamber 44 is sealed off from the spring chamber 45, for example by means of a diaphragm 48 starting from the second piston section 37.2 extends radially outwardly to a housing wall 49 of the control chamber 43.
- the valve chamber 36 is sealed, for example, with respect to the spring chamber 45 of the control chamber 43.
- the spring chamber In the spring chamber
- a return spring 50 is arranged, which is supported at its one end to the housing wall 49 of the control chamber 43 and acts with its other end on the second piston portion 37.2.
- the return spring 50 presses the closing body 37 in the direction away from the first valve seat 38.
- the pressure of the pressure line 11 acts on the second piston section 37.2 of the first closing body 37 via the control connection 35 and presses it counter to the effective direction of the return spring 50 in the direction of the first valve seat 38.
- Control chamber 43 to the atmosphere without pressure. From the equilibrium of forces on the first closing body 37 consisting of the pressure force acting in the pressure chamber 44 and the spring force of the return spring 50, a resultant force therefore results on the first closing body 37 in the opening direction, so that the shut-off valve 30 is opened when the feed pump 4 is switched off. As soon as the feed pump 4 is switched on, it builds up a pressure in the pressure line 11, which propagates via the haulage line 21 and the control connection 35 into the pressure chamber 44 minus a pressure loss.
- the return spring 50 is designed such that the first closing body 37 at a pressure in the
- Pressure chamber 44 applies greater than or equal to a predetermined closing pressure to the first valve seat 38 and the shut-off valve 30 closes in this way.
- the predetermined closing pressure of the shut-off valve 30 is greater than the pressure in the pressure line 11 at full load operation of the internal combustion engine 15 or equal to this pressure.
- the predetermined closing pressure of the shut-off valve 30 is for example in
- the shut-off valve 30 is thus initially open at the engine start, closes as soon as the pressure of the pressure line 11 reaches or exceeds the predetermined closing pressure and opens again as soon as the pressure of the pressure line 11 falls below the predetermined closing pressure.
- FIG. 3 shows in section a view of a second embodiment of the inventive Abschaltventils.
- the shut-off valve according to Figure 3 differs from the shut-off valve according to Figure 2 in that the shut-off valve 30 is not designed as a diaphragm valve, but as a piston valve.
- the second piston portion 37.2 extends in its radial extent with respect to the valve axis 39 to the housing wall 49 of the control chamber 43 and divides in this way the control chamber 43 in the pressure chamber 44 and the spring chamber 45.
- the membrane 48 according to Figure 2 is therefore omitted.
- the second piston portion 37.2 for example, has a greater axial extent than in the first embodiment to a good seal between the pressure chamber 44th and to reach the spring chamber 45 and to avoid tilting of the second piston portion 37.2 with the housing wall 49 of the control chamber 43.
- FIG. 4 shows a sectional view of a third exemplary embodiment of the inventive shut-off valve.
- the shut-off valve according to Figure 4 differs from the shut-off valve according to Figure 3 essentially in that the first closing body 37 has only a first piston portion 37.1 and the control chamber 43 is a control valve 53 upstream in the flow direction.
- the control valve 53 is, for example, integrally connected to the shut-off valve 30, but may also be provided separately.
- the control valve 53 is, for example, integrally connected to the shut-off valve 30, but may also be provided separately.
- the control valve 53 is arranged, for example, in the shut-off valve 30 downstream of the control connection 35 and upstream of the control chamber 43.
- the control valve 53 has, for example, a second closing body 56, which cooperates with a second valve seat 54 and a third valve seat 55 and is, for example, piston-shaped and axially movable axially in a cylinder chamber 57 between the second valve seat 54 and the third valve seat 55.
- the control connection 35 opens into the cylinder chamber 57 via an inlet opening 58, wherein the second valve seat 54 is arranged at the inlet opening 58 and surrounds it annularly.
- the second valve seat 54 and the third valve seat 55 are formed for example as a flat seat, but may also be provided as a ball or conical seat.
- the control valve 53 has a
- Leakage connection 60 which opens into the cylinder chamber 57 via a leakage opening 61, wherein the third valve seat 55 is disposed on the leakage opening 61 and surrounds them annularly.
- the leakage connection 60 is, for example, via a leakage line
- the second closing body 56 is provided by a closing spring arranged in the cylinder chamber 57
- the closing spring 63 is designed such that the control valve 53 opens at a pressure in the pressure line 11 which is greater than or equal to a predetermined opening pressure.
- the predetermined opening pressure of the control valve 53 is greater than the pressure in the pressure line 11 at full load operation of the internal combustion engine and is for example between six and nine bar.
- the restoring spring 50 acting on the first closing body 37 is designed according to this exemplary embodiment such that the shut-off valve 30 closes as soon as the control valve 53 opens and the control chamber 43 is pressurized with fuel from the pressure line 11.
- the cylinder chamber 57 is connected both to a control channel 64 and a leakage channel 67 with the control chamber 43 of the shut-off valve 30.
- the control channel 64 opens with its one end, for example, in a second valve seat 54 with the control port 35 facing portion of the cylinder chamber 57 and the leakage channel 67 with its one end, for example, in a third
- the control channel 64 and the leakage channel 67 open at its other end, for example, with a common channel portion in the control chamber 43.
- Control chamber 43 is connected, wherein the second closing body 56 closes the cylinder chamber 57 facing the end of the leakage channel 67 and the leakage opening 61 tightly. As a result, the control chamber 43 is pressurized with the pressure of the pressure line 11.
- the control chamber 43 is fluidly connected to the leakage port 60, wherein the second closing body 56 closes the cylinder chamber 57 facing the end of the control channel 64 and the inlet opening 58. In this way, the control chamber 43 is depressurized to the atmosphere, since the reservoir 1 has atmospheric pressure.
- Control chamber 43 fluidly connected and the control chamber 43 in this way pressurized with the pressure of the pressure line 11.
- Control valve 53 falls short, the second closing body 57 moves back to the second valve seat 54, so that first the leakage opening 61 and the leakage channel 67 is opened to the cylinder chamber 57 and then the control channel 64 to the cylinder chamber 57 and the inlet port 58 are closed. Since the control chamber 43 is depressurized in this way, the first closing body 37 is moved by the return spring 50 in the direction away from the first valve seat 38. In this case, the first closing body 37 displaces liquid from the control chamber 43 via the leakage line 67, the cylinder chamber 57 and the leakage connection 60 into the leakage line 62.
- a further throttle element 68 may be arranged.
- valve chamber 36 and the control chamber 43 are separated according to the third embodiment only by the first closing body 37 from each other. to
- a hollow cylindrical stop 69 is provided in the control chamber 43, for example.
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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)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200550003138 DE502005003138D1 (de) | 2004-10-09 | 2005-10-04 | Vorrichtung zum fördern von kraftstoff |
US11/576,640 US7832379B2 (en) | 2004-10-09 | 2005-10-04 | Device for pumping fuel |
EP05789639A EP1799991B1 (de) | 2004-10-09 | 2005-10-04 | Vorrichtung zum fördern von kraftstoff |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200410049286 DE102004049286A1 (de) | 2004-10-09 | 2004-10-09 | Vorrichtung zum Fördern von Kraftstoff |
DE102004049286.7 | 2004-10-09 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006040274A1 true WO2006040274A1 (de) | 2006-04-20 |
Family
ID=35385828
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2005/054977 WO2006040274A1 (de) | 2004-10-09 | 2005-10-04 | Vorrichtung zum fördern von kraftstoff |
Country Status (4)
Country | Link |
---|---|
US (1) | US7832379B2 (de) |
EP (1) | EP1799991B1 (de) |
DE (2) | DE102004049286A1 (de) |
WO (1) | WO2006040274A1 (de) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE502006003105D1 (de) * | 2005-06-21 | 2009-04-23 | Daimler Ag | Kraftstoffversorgungseinrichtung |
FR2890341B1 (fr) * | 2005-09-02 | 2008-10-24 | Inergy Automotive Systems Res | Systeme a carburant comprenant une reserve a carburant et un bac de retention |
DE102005049982A1 (de) * | 2005-10-19 | 2007-04-26 | Robert Bosch Gmbh | Vorrichtung zum Fördern von Kraftstoff |
DE102006024456A1 (de) * | 2006-05-24 | 2007-11-29 | Siemens Ag | Saugstrahlpumpe |
DE102007026671A1 (de) | 2007-06-08 | 2008-12-11 | Robert Bosch Gmbh | Kraftstofffördersystem |
JP4732429B2 (ja) * | 2007-12-18 | 2011-07-27 | 愛三工業株式会社 | 調圧弁及び燃料供給装置 |
DE102008059117B4 (de) | 2008-11-26 | 2011-07-28 | Continental Automotive GmbH, 30165 | Hochdruckpumpenanordnung |
US8459960B2 (en) * | 2009-02-09 | 2013-06-11 | Robert Bosch Gmbh | Jet pump assembly |
US8720485B2 (en) * | 2010-06-03 | 2014-05-13 | Robert Bosch Gmbh | Fuel system including dual fuel delivery modules for bifurcated fuel tanks |
DE102010039547B4 (de) | 2010-08-20 | 2023-02-02 | Robert Bosch Gmbh | Vorrichtung zum Fördern von Kraftstoff aus einem Vorratsbehälter zu einer Brennkraftmaschine |
DE102010062075A1 (de) | 2010-11-26 | 2012-05-31 | Robert Bosch Gmbh | Tankanordnung mit mechanischem Druckregler sowie Fahrzeug |
US9097217B2 (en) * | 2011-08-31 | 2015-08-04 | Gm Global Technology Operations. Llc | Propulsion systems and modules for vehicles |
US9809441B2 (en) * | 2015-12-21 | 2017-11-07 | Ford Global Technologies, Llc | Systems and methods for preventing fuel tank overfilling |
DE102016211944A1 (de) * | 2016-06-30 | 2018-01-04 | Bayerische Motoren Werke Aktiengesellschaft | Tankanordnung für ein Fahrzeug |
DE102016217800B4 (de) | 2016-09-16 | 2021-12-23 | Vitesco Technologies GmbH | Fluidfördervorrichtung |
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DE102004003113A1 (de) * | 2004-01-21 | 2005-08-11 | Siemens Ag | Vorrichtung zum Steuern eines Druckes in einer Kraftstoff-Vorlaufleitung |
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US7395818B2 (en) * | 2005-04-21 | 2008-07-08 | Walbro Engine Management, L.L.C. | Multi-gaseous fuel control device for a combustion engine with a carburetor |
-
2004
- 2004-10-09 DE DE200410049286 patent/DE102004049286A1/de not_active Withdrawn
-
2005
- 2005-10-04 WO PCT/EP2005/054977 patent/WO2006040274A1/de active IP Right Grant
- 2005-10-04 EP EP05789639A patent/EP1799991B1/de not_active Expired - Fee Related
- 2005-10-04 US US11/576,640 patent/US7832379B2/en not_active Expired - Fee Related
- 2005-10-04 DE DE200550003138 patent/DE502005003138D1/de active Active
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JPH02286865A (ja) * | 1989-04-27 | 1990-11-27 | Nippondenso Co Ltd | 車両用燃料供給装置 |
DE4224981A1 (de) * | 1992-07-29 | 1994-02-03 | Bosch Gmbh Robert | Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeuges |
DE4426946A1 (de) * | 1994-07-29 | 1996-02-01 | Bosch Gmbh Robert | Vorrichtung zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeugs |
DE19628580A1 (de) * | 1996-07-16 | 1998-01-22 | Mannesmann Vdo Ag | Strömungsventil |
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EP1126157A2 (de) * | 2000-02-15 | 2001-08-22 | Robert Bosch Gmbh | Kraftstoffversogungseinrichtung für eine Brennkraftmaschine eines Kraftfahrzeugs |
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Also Published As
Publication number | Publication date |
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US20080095642A1 (en) | 2008-04-24 |
DE102004049286A1 (de) | 2006-04-20 |
US7832379B2 (en) | 2010-11-16 |
DE502005003138D1 (de) | 2008-04-17 |
EP1799991B1 (de) | 2008-03-05 |
EP1799991A1 (de) | 2007-06-27 |
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