EP2035686A1 - Fuel injector - Google Patents
Fuel injectorInfo
- Publication number
- EP2035686A1 EP2035686A1 EP07728615A EP07728615A EP2035686A1 EP 2035686 A1 EP2035686 A1 EP 2035686A1 EP 07728615 A EP07728615 A EP 07728615A EP 07728615 A EP07728615 A EP 07728615A EP 2035686 A1 EP2035686 A1 EP 2035686A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- membrane
- fuel injector
- return
- recess
- 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.)
- Granted
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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
-
- 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
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
-
- 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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/002—Arrangement of leakage or drain conduits in or from injectors
-
- 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
- F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
- F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
Definitions
- the present invention relates to a fuel injector according to the preamble of
- Fuel injectors of the type of interest serve to control the fuel which is injected into the combustion chamber in an internal combustion engine. They are essentially composed of a solenoid valve and a miniservovalve, and actuate a nozzle needle whose opening and closing position is controlled by the solenoid valve, so that injection holes are opened and closed in the injector for injecting the fuel.
- Such a fuel injector is known from DE 101 59 003 Al. Here is one
- Force injector which is designed with a solenoid valve for controlling the miniservoval valve with an anchor which can be applied to a valve seat in the lower armature space.
- the lower armature space is in fluid communication via bores with a control pressure chamber, whereby leakage quantities occurring via at least one return borehole can be returned to a tank above the lower armature space.
- means for reducing these pressure oscillations in the lower armature space are provided.
- the means for reducing pressure fluctuations comprise in the lower armature space incorporated
- An essential disadvantage of the known designs of fuel injectors are those pressure oscillations that lead to different opening behavior of the Miniservoventils and thus can lead to volume fluctuations of the injected fuel.
- Pressure oscillations that propagate through communicating holes in the adjacent solenoid valve space and the magnetic spring space cause a quantity map ripple, which also can not be satisfactorily reduced or avoided by means of the increased fluid volumes.
- DE 102 21 383 A1 discloses pressure limiting devices for limiting occurring peak pressure values in the fluidic system of a fuel injector. These relate to a fuel injector which has a high-pressure fuel pump with a pump piston driven in a stroke movement, which delimits a pump working chamber which is connected to at least one fuel injector, through which fuel is injected into the combustion chamber of the internal combustion engine. In this case, at least one connection of the pump working space with a discharge region is controlled by an electrically actuated control valve.
- Pressure limiting device is opened when a predetermined pressure in the pump working space, a connection of the pump working space with a discharge area.
- the pressure limiting device has an elastically deformable membrane, which is acted upon by the pressure prevailing in the pump working chamber and the pressure when exceeding the predetermined pressure
- a disadvantage of the proposed pressure limiting device is the outflow of the fuel into a discharge area, which forms the formation of a closed Systems, ie the integration of the pressure relief device in the closed fluidic system of the return bores without leakage current not possible.
- the invention includes the technical teaching that the means for reducing pressure oscillations comprise at least one diaphragm can, which is accommodated in a recess which is fluidically connected to the at least one return bore.
- the return bores extend from the lower region of the flat seat into the region of the solenoid valve, wherein the portion of the return bore in the direction of the solenoid valve serves as a connecting line into the magnetic spring chamber. Due to the reduced pressure oscillations, the bounce behavior of the armature of the miniservovalve can be reduced or avoided, which enables an improved metering of the amount of fuel injected into the combustion chamber, and the closing behavior of the fuel injector in the final phase of the injection cycle is optimized. Due to the thus achieved improved quantification of the injected fuel quantity due to the minimized or avoided bounce behavior improved combustion of the fuel due to the optimized atomization of the fuel is reachable in the combustion chamber, resulting in a reduction of pollutant emissions.
- An advantageous embodiment of the present invention provides that the recess is introduced in the injector body, so that the diaphragm cell can be integrated into the injector body.
- the recess for receiving the diaphragm can is circular
- a connecting channel allows fluid communication between the return bore and the recess to provide fluid communication between the recess and the return bore.
- the recess is pressure-tightly sealed by means of a closure element, wherein in the recess adjacent to the diaphragm cell a biasing element is arranged, which mechanically clamps the diaphragm box on the joint circumference of the membrane shells against the closure element.
- the closure element seals in
- Shape of a lid from the recess to the outside in the injector body wherein the closure element may be formed as a circular disc-shaped lid, which is mechanically secured by means of a shaft securing ring in the injector body and fluidly pressure sealed by means of a ring seal.
- the biasing member may be made of a thin sheet metal material as an elastic, plate spring-like, circular disk-shaped element, so that the pressure cell is clamped in the region of its circumference by the biasing member against the inside of the closure element.
- the diaphragm cell is constructed from two circular membrane shells, which are pressure-tight radially circumferentially joined together.
- the joint connection can advantageously be designed as a welded joint, wherein the membrane box is radially radially positioned and biased in the region of the weld seam of the two membrane shells between the biasing member and the inside of the closure element.
- Membrane shells of the diaphragm can relieve pressure.
- Another embodiment of the invention provides that the recess for receiving the diaphragm cell is accommodated in a separate damper housing, wherein the damper housing disposed on the injector and fluidly with the
- the execution of the means for reducing pressure oscillations in a separate damper housing offers the possibility to arrange the diaphragm can outside the injector body, and the recess in which the diaphragm cell is added to fluidly connect to the system of return bores.
- the damper housing comprises an interior which is formed by means of a closure element to a closed recess for receiving the diaphragm cell, wherein stops are provided which receive the diaphragm can on the circumference of the weld and center radially.
- the biasing element is designed to be adjustable in the embodiment of the damper housing, so that the stop, which on
- Preload element is formed, is adjustable.
- the circular membrane shells have a concentric wave structure to increase the compliance. Due to the wave structure, the value of membrane cup deflection may be increased due to the lower compliance and thus the extended elastic range to maximize the maximum volume difference between a maximum pressure and a minimum pressure within the recess.
- the volume difference relates to the maximum or minimum volume of the interior of the diaphragm cell.
- the wave structure runs concentrically around the central axis of the circular membrane can and can For example, four wave peaks or troughs include. Concerning the arrangement of the membrane shells to form the membrane can each other on the one hand the opportunity is offered to arrange the two circular membrane shells mirror images of each other, so that the wave structure of the membrane shells against each other and the membrane cell has a symmetrical design.
- the two circular membrane shells to form the diaphragm cell are arranged parallel, ie in the same direction to each other, so that the wave structure of the membrane shell is rectilinear and the diaphragm cell has an asymmetrical design.
- the membrane shells can be formed equal to each other, so that a small parts variance can be achieved.
- the membrane shells can be welded in the mutually facing arrangement, so that the membrane box does not require a preferred installation direction due to their symmetry.
- a minimum distance results which leads to a minimum thickness of the membrane can and comprises a relatively large volume within the membrane can.
- the contour of the membranes in the entire spring region have a small distance, which is made possible by an asymmetrical arrangement of the membrane shells. Due to the low output volume in the diaphragm cell and the resulting steeper pressure volume characteristic, the pressure force which the diaphragm can expands when the external pressure is reduced is reduced bulges, very quickly, whereby a lower load on the membrane shells and the weld in the uninstalled state or outside of the operation of the diaphragm cell is given.
- Diaphragm box is filled with helium and has a gas pressure which is greater than the return pressure in the return line or in the recess connected to the return line. If helium is selected as the gas which fills the membrane can, the sealing of the membrane shells is reliably possible and at the same time leads to more favorable properties of the gas state change. Helium has a high adiabatic exponent, with a steeper pressure rise characteristic compared to the isothermal basic design in highly dynamic processes.
- the diaphragm cell on a stroke limitation which is introduced inside the diaphragm cell.
- the stroke limiter in this case comprises stirrup elements, which are arranged interlocking, so that this limits both the membrane shells merging membrane shell deflection and the membrane shells divergent Membranschalen vombiegung.
- the stirrup elements can be welded into the membrane shells on the inside, and have a C-shaped profile structure, which in each case engage one another in opposite directions.
- stirrup elements in the respective membrane shell can be formed equal to one another in order to minimize the parts variance in this case as well, whereby an asymmetrical design of the elements of the stroke limitation within the membrane shells is also possible.
- Figure 1 a cross section of a fuel injector with means for limiting the pressure, wherein the means are designed as a diaphragm cell, which are integrated within the injector body;
- FIG. 2 shows a cross-section of a detail of the membrane cell of FIG. 1, which is integrated within the injector body;
- FIG. 2a shows a cross section of a section of the damper assembly according to another embodiment
- FIG. 3 shows a cross-section of a fuel injector with means for limiting the pressure, wherein the means are designed as a membrane can, which are integrated in a damper housing arranged outside the injector body;
- FIG. 4 shows a membrane can according to the present invention, which has a symmetrical stroke limiter inserted on the inside;
- FIG. 5 shows a further exemplary embodiment of the membrane can with the stroke limiter inserted on the inside, wherein the stroke limiter is of asymmetrical design
- FIG. 6 a shows a first exemplary embodiment of the membrane can, which is a symmetrical one
- FIG. 6b shows a further exemplary embodiment of the membrane can, which has an asymmetrical arrangement of the membrane shells.
- the fuel injector shown in Figure 1 comprises a solenoid valve 1 and a miniservovalve 2.
- the solenoid valve 1 comprises an armature 3 and a valve seat 4, which separates an armature space 5 from a control chamber of the miniservovalve 2.
- the armature 3 moves upward in the vertical direction, so that the valve seat 4 in the lower armature space 5 opens.
- This valve seat 4 is in turn via one or more holes in fluid communication with a control pressure chamber of the miniservovalve 2.
- the pressure in the control pressure chamber of the miniservoval valve decreases, fluid via the holes in the direction of the valve seat 4 from there into the lower Anchor space 5 flows.
- the injector on the flat seat 6 of the miniservovalve 2 now relieves the control line from rail pressure to return pressure, a high volume flow within the return bore 8 initially arises. This is forwarded to the recess 10, so that the diaphragm can 9 is pressurized and the membrane shells are arched inwards , This reduces the inner volume of the diaphragm cell 9, and occurring pressure peaks within return bores 8 are reduced. If, on the other hand, the pressure within the return bore 8 drops, the membrane shells of the membrane can 9 expand again, so that overall the pressure fluctuations are smoothed out.
- the diaphragm cell 9 is arranged between the closure element 12 and a biasing element 13, which the
- FIG. 2 shows an enlarged section of the recess 10 within the injector body 7.
- the recess 10 is connected to the area below the flat seat (see FIG. 1).
- the membrane box 9 is arranged, which is formed from a first membrane shell 14 and a second membrane shell 15. If the fuel then flows through the return bore 8 into the recess 10, it first passes into a first space 21, which passes through recesses 29 and 30 within the injector body 7 or the Closure element 12 is possible.
- a second space 22 is also pressurized with fuel pressure, which is directly connected to the return bore 8. Now increases the pressure within the spaces 21, 22, so the membrane shells 14 and 15 directed towards each other inwardly, so that the volume decreases within the diaphragm cell 9.
- a stroke limiter 16 which consists of a first bracket member 17 and a second bracket member 18.
- the ironing elements have a C-shaped profile, so that they each abut against the inside of the membrane shells 14, 15 and thereby limit the lifting movement.
- the bracket elements 17 and 18 engage each other when the pressure in the spaces 21, 22 decreases, and the
- Biasing element 13 shown in a flying and unbiased condition.
- the closure element 12 is sealed by means of a sealing element 20 with respect to the outside of the injector body 7, which consists for example of an O-ring.
- stops 23 and 24 are provided both in the injector body 7 and in the closure element 12, to which the membrane shells 14 and 15 abut outwardly at a curvature of the membrane shells 14, 15.
- the inner stroke limiter 16 and the outer stroke limiter with the stops 23 and 24 are both shown in the figure 2 for simultaneous presentation, wherein one of the two stroke limits is sufficient for a technical implementation of the arrangement.
- the stops are optionally formed by the housing 7 and the closure element 12 or by the biasing element 13 and the receiving element 28 (see Figure 3).
- Figure 2a shows another embodiment for receiving, limiting and biasing the diaphragm cell 9.
- the biasing member 13a has at least three exhibitions 32, which relieve the weld seam 19 by elastic bias and at the same time hold the diaphragm cell 9 in position.
- Through the exhibitions 32 forms in the enclosure 31 a recess, whereby the space 22 directly and the Room 21 communicates with the return bore 8 via the recess 29a.
- a latching 33 is formed, which preferably engages in the sealing ring groove of the closure element 12a and produces a positive connection.
- a stop 24a is formed, which cooperates with the closing element 12a formed on the stop 23a and can be used both for Loslaufdruckvorschreib and for stroke limitation.
- the latch 33 is secured by the boundary of the enclosure 31 in the recess 10.
- the diaphragm mount which is independent of the injector body 7, permits precise pretensioning and idling pressure adjustment and stroke limitation to the outside.
- the damper assembly 34 gives a high
- the damper assembly 34 consists of the closure member 12 a, the diaphragm box 9, the biasing member 13 a and the
- the circular disc-shaped biasing element 13a adopts both the preload to relieve the weld 29 and the function of the Loslauftikvorschreib and stroke limitation.
- the elastic bias is carried out by at least three flared areas, which lie close to the welding seam on the diaphragm cell.
- Figure 3 shows another embodiment of the means for reducing pressure oscillations, wherein these comprise a diaphragm cell 9, which within a
- Damper housing 11 is arranged.
- the damper housing 11 is in turn disposed on the injector body 7, and fluidly and mechanically connected thereto.
- the mechanical connection according to the present embodiment comprises a screw connection, wherein the fluidic connection via internal channels in the recess 10 within the damper housing 11 with the system of the return bore
- the diaphragm cell 9 is received within the damper housing 11 and arranged by means of a closure element 12 in this fixed.
- a receiving element 28 is provided, which is also formed circular disk-shaped and has a stop 25 in the center.
- a further biasing element 27 is provided, which end in the direction of the diaphragm cell 9 has an opposite stop 26.
- the closure element 12 is screwed inside the damper housing 11 and sealed pressure-tight by means of seals.
- the biasing member 27 is within the
- the centrally arranged stop 25 is formed on the receiving element 28 and acts counter to the abutment 26 of the biasing member 27.
- each different configurations of the stroke limiter 16 are shown in the diaphragm cell 9.
- the stroke limiter 16 has C-shaped stirrup members 17 and 18 which intermesh with each other such that both an inwardly directed membrane flexure and an outwardly directed one
- the stroke limiter in FIG. 5 is designed asymmetrically, which represents a further embodiment of the same. This comprises a T-shaped bracket member 17 and each bracket-shaped bracket elements 18, which also engage in such a manner and an inwardly directed and an outward deflection of the diaphragm shells 14 and
- the membrane shells 14 and 15 are joined together by a radially circumferential weld 19.
- FIGS. 6a and 6b each show a symmetrical as well as an asymmetrical design of the membrane can 9.
- the membrane shells 14 and 15 are formed equal to one another, so that they are arranged mirror-inverted by 180 ° relative to each other and are welded together.
- the membrane shells 14 and 15 according to FIG. 6b have an asymmetrical design, so that the wave structure within the membrane shells is uniform and the overall height in the membrane can 9 is reduced overall.
- the membrane shells 14 and 15 each have three shafts, which are formed concentrically around the central axis of the membrane boxes 9, wherein also a different number of waves can be introduced into the membrane shells, which depends on the diameter of the membrane box and the thickness of the sheet material of the membrane shells ,
- the wave structure enlarges the elastic region for bending the membrane shells 14 and 15, and substantially avoid damage or overloading of the membrane shells (14, 15) and the weld seam 19.
- the invention is not limited in its execution to the above-mentioned preferred embodiment. Rather, a number of variants is conceivable, which makes use of the illustrated solution even with fundamentally different types of use.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006027780A DE102006027780A1 (en) | 2006-06-16 | 2006-06-16 | fuel injector |
PCT/EP2007/054160 WO2007144229A1 (en) | 2006-06-16 | 2007-04-27 | Fuel injector |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2035686A1 true EP2035686A1 (en) | 2009-03-18 |
EP2035686B1 EP2035686B1 (en) | 2010-12-15 |
Family
ID=38325218
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07728615A Not-in-force EP2035686B1 (en) | 2006-06-16 | 2007-04-27 | Fuel injector |
Country Status (6)
Country | Link |
---|---|
US (1) | US8038083B2 (en) |
EP (1) | EP2035686B1 (en) |
JP (1) | JP4878386B2 (en) |
AT (1) | ATE491884T1 (en) |
DE (2) | DE102006027780A1 (en) |
WO (1) | WO2007144229A1 (en) |
Families Citing this family (28)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4530053B2 (en) * | 2008-01-22 | 2010-08-25 | 株式会社デンソー | Fuel pump |
US7520268B1 (en) * | 2008-03-18 | 2009-04-21 | Robert Bosch Gmbh | Fuel rail damping assembly including an insert |
FR2929343A3 (en) * | 2008-03-31 | 2009-10-02 | Renault Sas | Fuel return circuit for fuel injecting device in internal combustion engine, has closure pipe made of deformable material and provided in parallel to part of collecting pipe length so that pressure waves are returned to downstream portion |
US7900886B2 (en) * | 2008-04-18 | 2011-03-08 | Caterpillar Inc. | Valve assembly having a washer |
EP2385241B1 (en) * | 2010-05-04 | 2013-07-17 | Continental Automotive GmbH | Pulsation damper |
DE102010029123A1 (en) * | 2010-05-19 | 2011-11-24 | Robert Bosch Gmbh | Fuel injector with hydraulic coupler unit |
DE102010030626A1 (en) * | 2010-06-29 | 2011-12-29 | Robert Bosch Gmbh | Pulsation damper element for a fluid pump and associated fluid pump |
US8727752B2 (en) * | 2010-10-06 | 2014-05-20 | Stanadyne Corporation | Three element diaphragm damper for fuel pump |
DE102011008467B4 (en) * | 2011-01-13 | 2014-01-02 | Continental Automotive Gmbh | Injector with pressure compensation |
DE102011100029C5 (en) | 2011-04-29 | 2016-10-13 | Horiba Europe Gmbh | Device for measuring a fuel flow and calibration device therefor |
DE102011120468A1 (en) * | 2011-12-07 | 2013-06-13 | Andreas Stihl Ag & Co. Kg | Internal combustion engine with fuel supply device |
JP5821769B2 (en) * | 2012-04-24 | 2015-11-24 | 株式会社デンソー | Damper device |
DE102013003104A1 (en) * | 2013-02-25 | 2014-08-28 | L'orange Gmbh | Fuel injector for use with diesel fuel in fuel injection device of fuel injection system, has pressure shock absorber that is arranged in leakage flow path to attenuate pressure waves, which run through leakage flow path to actuator chamber |
US20150017040A1 (en) * | 2013-07-12 | 2015-01-15 | Denso Corporation | Pulsation damper and high-pressure pump having the same |
JP5854006B2 (en) * | 2013-07-12 | 2016-02-09 | 株式会社デンソー | Pulsation damper and high-pressure pump equipped with the same |
JP5783431B2 (en) * | 2013-07-12 | 2015-09-24 | 株式会社デンソー | Pulsation damper and high-pressure pump equipped with the same |
FR3017905B1 (en) * | 2014-02-24 | 2018-12-07 | Delphi International Operations Luxembourg S.A R.L. | FUEL INJECTOR |
JP5892397B2 (en) * | 2014-10-30 | 2016-03-23 | 株式会社デンソー | Pulsation damper |
JP6527689B2 (en) * | 2014-12-12 | 2019-06-05 | 株式会社不二工機 | Diaphragm and pulsation damper using the same |
DE102015219768A1 (en) * | 2015-10-13 | 2017-04-13 | Continental Automotive Gmbh | High-pressure fuel pump for a fuel injection system of a motor vehicle |
DE102015226024A1 (en) * | 2015-12-18 | 2017-06-22 | Robert Bosch Gmbh | Fluid pump, in particular high-pressure fuel pump |
WO2017169960A1 (en) * | 2016-03-28 | 2017-10-05 | イーグル工業株式会社 | Metal diaphragm damper |
CN111356833B (en) * | 2017-11-24 | 2022-01-25 | 伊格尔工业股份有限公司 | Metal diaphragm damper and manufacturing method thereof |
DE102018212090A1 (en) * | 2018-07-19 | 2020-01-23 | Robert Bosch Gmbh | Nozzle assembly for a fuel injection valve for injecting a gaseous and / or liquid fuel, fuel injection valve |
DE102018212229A1 (en) * | 2018-07-23 | 2020-01-23 | Continental Automotive Gmbh | Pump for a motor vehicle, holding device, assembly and method |
JP7041956B2 (en) * | 2018-09-20 | 2022-03-25 | 株式会社不二工機 | Pulsation damper |
JP7118183B2 (en) * | 2019-02-13 | 2022-08-15 | 日立Astemo株式会社 | Metal diaphragm, metal damper, and fuel pump with these |
CN116940782A (en) * | 2021-03-09 | 2023-10-24 | 日本发条株式会社 | Pulsation damping component |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2936425A1 (en) * | 1979-09-08 | 1981-04-02 | Robert Bosch Gmbh, 7000 Stuttgart | ELECTROMAGNETICALLY ACTUABLE FUEL INJECTION VALVE |
US5520215A (en) * | 1995-08-04 | 1996-05-28 | Handy & Harman Automotive Group, Inc. | Pressure regulator and dampener assembly |
DE29708369U1 (en) * | 1997-05-09 | 1997-07-10 | Fev Motorentech Gmbh & Co Kg | Controllable injection valve for fuel injection on internal combustion engines |
WO2000028205A1 (en) * | 1998-11-10 | 2000-05-18 | Ganser-Hydromag Ag | Fuel injection valve for internal combustion engines |
GB9906092D0 (en) * | 1999-03-18 | 1999-05-12 | Lucas France | Fuel injector |
US6360963B2 (en) * | 2000-01-12 | 2002-03-26 | Woodward Governor Company | Gaseous fuel injector having high heat tolerance |
DE60124332D1 (en) * | 2000-03-07 | 2006-12-21 | Matsushita Electric Ind Co Ltd | liquid dispenser |
US6321776B1 (en) * | 2000-04-24 | 2001-11-27 | Wayne L. Pratt | Double diaphragm precision throttling valve |
DE10159003A1 (en) | 2001-11-30 | 2003-06-18 | Bosch Gmbh Robert | Injector with a solenoid valve for controlling an injection valve |
JP3823060B2 (en) * | 2002-03-04 | 2006-09-20 | 株式会社日立製作所 | High pressure fuel supply pump |
EP1411236B1 (en) * | 2002-10-19 | 2012-10-10 | Robert Bosch Gmbh | Device for damping of pressure pulsations in a fluid system, especially in a fuel system of an internal combustion engine |
US7322488B2 (en) * | 2003-07-22 | 2008-01-29 | Flexcon Industries Trust | Expansion tank with double diaphragm |
JP4036153B2 (en) | 2003-07-22 | 2008-01-23 | 株式会社日立製作所 | Damper mechanism and high-pressure fuel supply pump |
US7303091B2 (en) * | 2003-07-22 | 2007-12-04 | Flexcon Industries | Expansion tank with double diaphragm |
JP2005076571A (en) * | 2003-09-02 | 2005-03-24 | Nippon Soken Inc | Injector |
US7165535B2 (en) * | 2004-05-27 | 2007-01-23 | Delphi Technologies, Inc. | Fuel rail pulse damper with improved end crimp |
DE102004034672A1 (en) | 2004-07-17 | 2006-02-16 | Robert Bosch Gmbh | Fuel injection device for an internal combustion engine |
JP4686501B2 (en) * | 2007-05-21 | 2011-05-25 | 日立オートモティブシステムズ株式会社 | Liquid pulsation damper mechanism and high-pressure fuel supply pump having liquid pulsation damper mechanism |
JP4530053B2 (en) * | 2008-01-22 | 2010-08-25 | 株式会社デンソー | Fuel pump |
-
2006
- 2006-06-16 DE DE102006027780A patent/DE102006027780A1/en not_active Withdrawn
-
2007
- 2007-04-27 DE DE502007005966T patent/DE502007005966D1/en active Active
- 2007-04-27 JP JP2009514725A patent/JP4878386B2/en not_active Expired - Fee Related
- 2007-04-27 AT AT07728615T patent/ATE491884T1/en active
- 2007-04-27 US US12/304,599 patent/US8038083B2/en not_active Expired - Fee Related
- 2007-04-27 WO PCT/EP2007/054160 patent/WO2007144229A1/en active Application Filing
- 2007-04-27 EP EP07728615A patent/EP2035686B1/en not_active Not-in-force
Non-Patent Citations (1)
Title |
---|
See references of WO2007144229A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE102006027780A1 (en) | 2007-12-20 |
WO2007144229A1 (en) | 2007-12-21 |
EP2035686B1 (en) | 2010-12-15 |
US20090127356A1 (en) | 2009-05-21 |
US8038083B2 (en) | 2011-10-18 |
DE502007005966D1 (en) | 2011-01-27 |
JP4878386B2 (en) | 2012-02-15 |
ATE491884T1 (en) | 2011-01-15 |
JP2009540206A (en) | 2009-11-19 |
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