EP2102486A1 - Injector with an axial pressure-compensating control valve - Google Patents
Injector with an axial pressure-compensating control valveInfo
- Publication number
- EP2102486A1 EP2102486A1 EP07802985A EP07802985A EP2102486A1 EP 2102486 A1 EP2102486 A1 EP 2102486A1 EP 07802985 A EP07802985 A EP 07802985A EP 07802985 A EP07802985 A EP 07802985A EP 2102486 A1 EP2102486 A1 EP 2102486A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- chamber
- sleeve
- pressure
- valve piston
- 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
- 239000000446 fuel Substances 0.000 claims description 39
- 238000002485 combustion reaction Methods 0.000 claims description 6
- 238000011161 development Methods 0.000 description 3
- 230000018109 developmental process Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000007789 sealing Methods 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
- 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
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
-
- 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
- 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
-
- 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
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
-
- 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
- F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
-
- 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
- F02M63/0043—Two-way valves
Definitions
- the invention relates to an injector according to the preamble of claim 1.
- DE 103 53 169 A1 describes a common rail injector with a control valve for blocking and opening a fuel drain path from a control chamber.
- a piezoelectric actuator is provided, which acts via a translation piston in the axial direction on a valve piston adjusting.
- the fuel pressure within a control chamber can be influenced by means of the control valve embodied as a 3/2 directional valve, the control chamber being supplied with fuel from a high-pressure fuel accumulator via a pressure channel with inlet throttle and an additional channel with fuel.
- a nozzle needle is moved between an open position and a closed position, wherein the nozzle needle in its open position releases the fuel flow into the combustion chamber of an internal combustion engine. Since the known control valve is not pressure balanced in the axial direction, high actuating forces for opening the control valve are required.
- a common rail injector with a pressure-balanced control valve in the axial direction is known.
- the known control valve has as an adjustable valve element on an axially displaceable sleeve, the Ie- is acted upon in the radial direction with fuel pressure from a high pressure area. Due to the use of a pressure balanced control valve only small actuating forces for opening the control valve are required, so that the setting task is performed in the known injector of an electromagnetic drive. If the control valve known from EP 1 612 403 A1 were transferred to the injector known from DE 103 53 169 A1, the overall configuration of the injector would have to be changed. In particular, in the case of the piezo-actuated injector, the low-pressure space would have to be moved substantially further in the direction of the control chamber.
- the invention is therefore based on the object of proposing an injector with an alternatively configured axially-pressure compensated valve, which is particularly suitable for the use of an electromagnetic actuator.
- the invention is based on the idea that, instead of an axially adjustable sleeve, an axial direction is used. to provide adjustable valve piston for opening and closing the control valve.
- the valve piston (bolt) is arranged within a valve chamber which is hydraulically connected to the control chamber, so that when the control valve is open, fuel can flow out through a fuel drain path from the control chamber via the valve chamber to a low-pressure chamber. When the control valve is closed, the fuel drain path is blocked.
- the valve piston is not guided according to the invention directly in a throttle plate, but in a sleeve which in the
- Valve chamber is added. To the valve piston in
- a spring is provided which on the one hand on the valve piston, in particular on the underside of a valve head and on the other hand on the sleeve, in particular on the end face of the sleeve, is supported. So that on the valve piston in the axial direction no or only minimal pressure forces act, so it is a pressure balanced in the axial direction control valve, it is provided that low pressure is applied to both end faces of the valve piston and that in the axial direction acted upon by low pressure (projection) Areas of the valve piston are equal on both sides. Since the valve seat facing the end face of the valve piston limits the low-pressure chamber or is directly connected hydraulically with this, is automatically low pressure on the end face.
- the application of the (lower) end face opposite this (upper) end face with low pressure can be realized, for example, by providing a connecting channel to the end face of the valve piston facing away from the valve seat, which connecting channel is directly adjacent to this end face. hydraulically connected to the low pressure area of the injector.
- fuel pressures in a range between approximately 0 and 10 bar prevail, whereas the fuel flowing from a high-pressure fuel reservoir into the injector is under a pressure in a range between approximately 1800 and 2000 bar.
- the inventive design of the injector can be easily transferred to the known from DE 103 53 169 Al injector, in which case, preferably instead of an additional fuel supply to the valve chamber, a low-pressure connection line can be provided to the nozzle needle facing the end face of the valve body with low pressure to supply.
- a piezoelectric actuator instead of a piezoelectric actuator, an electromagnetic drive can be used.
- the sleeve is received with radial play in the valve chamber, so that pressurized fuel in the valve chamber exerts a radially inwardly acting force on the sleeve, so that a widening of the guide clearance between the sleeve and the valve piston avoided during operation and thus leakage losses are minimized.
- the hydraulic connection between the control chamber and the valve chamber is realized via a drainage channel with outlet throttle, the cross sections of the outlet throttle and the inlet throttle arranged in the pressure chamber supplying the control chamber being matched to one another in such a way that when the valve is open Control valve has a net fuel flow into the low-pressure space results.
- the drainage channel opens into the valve chamber in a region between the sleeve and the valve chamber inner wall. This makes it possible to integrate the flow channel exclusively in a arranged between the control chamber and the valve chamber throttle plate.
- the injector is particularly suitable for the use of a solenoid actuator, since due to the axial pressure balance of the control valve comparatively low actuating forces must be applied.
- the electromagnetic drive has at least one electromagnet (coil) and at least one armature plate interacting therewith, the armature plate having to be operatively connected to the valve piston. Since there is no minimum pressure to act on a translation piston of a piezo actuator in an electromagnetic drive, the low pressure level can be lower, whereby the return system for the fuel can be designed more cost-effective overall.
- the anchor plate is operatively connected to a push rod, for example, integrally formed therewith, wherein the armature plate facing away from the free end of the push rod on the valve piston, in particular the valve piston head, is centered.
- the adjusting force of the electromagnetic drive via the armature plate and from this via the push rod on the valve piston are transferred to lift it from the valve seat and thus release the fuel discharge path to the low-pressure chamber, which in turn lifts the nozzle needle from its needle seat and the fuel flow in one Combustion chamber releases.
- the stroke of the electromagnetic drive can be adjusted via the variation of the length of the push rod.
- a weak biasing spring is preferably provided, which biases the armature plate and thus the push rod in the direction of the valve piston.
- the spring force must be such that it is less than the spring force of the spring within the valve chamber, which presses the valve piston in the opposite direction in its valve seat.
- the invention is provided in a further development that the push rod is guided within a stop sleeve, wherein the stop sleeve is received within the electromagnet of the solenoid drive and has a stop surface for the anchor plate.
- valve chamber is limited on its side facing the control chamber by a throttle plate, the throttle plate thus forms the bottom surface of the valve chamber on which the guide sleeve within the valve chamber off. supports.
- this throttle plate is advantageously also the Ab ⁇ running channel with outlet throttle from the control chamber introduced ⁇ introduced .
- connection channel which connects the nozzle needle ⁇ facing end face of the valve piston with the Niederbuchbe ⁇ rich of the injector, so preferably at least approximately the same (low) pressure prevails on both end faces of the valve piston ,
- Fig. 1 a sectional view of an injector with pressure-balanced in the axial direction
- FIG. 2 shows a detailed view of an injector, from which the hydraulic connection between the control chamber and the valve chamber can be seen
- FIG. 3 shows an enlarged detail view of the installation situation of an anchor plate of a Elect ⁇ romagnetantriebes of the injector
- Fig. 4 a one-piece assembly of anchor plate and push rod.
- a common rail injector 1 is shown.
- the injector 1 has an injector body 2, a nozzle body 3 shown only in sections, and a valve body 4 lying against the injector body 2 and a throttle plate 5 arranged between the valve body 4 and the nozzle body 3.
- a guide bore 7 is formed, in which an elongated nozzle needle 8 is guided axially movable.
- the nozzle needle has a closing surface 10 with which it can be brought into tight contact with a needle seat 11 formed inside the nozzle body 3.
- the nozzle needle 8 When the nozzle needle 8 abuts the needle seat 11, ie, is in a closed position, the fuel outlet from a nozzle hole arrangement 12 is blocked. If, on the other hand, it is lifted by the needle seat 11, fuel can flow from a pressure chamber 13 in the axial direction along the nozzle needle 8 past the needle seat 11 to the nozzle hole arrangement 12 and be sprayed there substantially under high pressure (rail pressure) into a combustion chamber.
- the nozzle needle 8 is biased by means of a biasing spring, not shown, in the direction of its closed position.
- the upper end face 14 of the nozzle needle 8 protrudes into a control chamber 15, which is bounded on the opposite side of the end face 14 of the throttle plate 14.
- the control chamber 15 is supplied via a pressure channel 16 with inlet throttle 17 and a connection pocket 20 in the valve body 4 with fuel under high pressure from a supply line 18, wherein the supply line 18 is connected to a fuel high-pressure accumulator, not shown, for example via a Ra- dialkolbenpumpe is pressurized.
- the supply channel 18 is simultaneously connected via a connecting bore 19 within the throttle plate 5 with the control chamber 15 radially enclosing the pressure chamber 13. Via an apparent from Fig.
- control chamber 15 is hydraulically connected to a valve chamber 23 of a control valve 24 within the valve body 4.
- the drainage channel 21 is part of a fuel drainage path from the control chamber to a low pressure chamber 25 arranged above the valve chamber 23 in the plane of the drawing. From there, the fuel can flow off via a return line (not shown).
- a closing force is exerted on the nozzle needle 8 by a biasing spring, not shown, at the same time is exercised by the pressure prevailing in the control chamber 15 fuel pressure on the end face 14 of the nozzle needle 8, a closing force on this.
- These closing forces act on the basis of the action of fuel pressure on a formed on the nozzle needle 8, not shown, step surface resulting opening force.
- the control valve 24 is in a closed position and the fuel drain from the control chamber 15 is locked in the low pressure chamber 25, the stationary force acting on the nozzle needle 8 closing force is greater than the opening force, which is why the nozzle needle 8 then assumes its closed position.
- the control valve 24 is then opened, fuel flows out of the control chamber and the nozzle needle 8 is lifted from its needle seat 11.
- the flow cross-sections of the inlet throttle 17 and the outlet throttle 21 are matched to one another such that the inflow through the pressure channel 16 is weaker than the outflow through the outlet channel 21 and accordingly when it is open
- Control valve 24 results in a net outflow of fuel.
- the consequent pressure drop in the control chamber 15 causes the amount of the closing force to drop below the magnitude of the opening force and the nozzle needle 8 to sink from the needle seat
- an axially displaceable valve piston 26 is arranged, which is guided in a sleeve 27 with the least possible backlash.
- the sleeve 27 is received with radial clearance within the valve chamber 23.
- a helical spring 29 is arranged, which is supported on the one hand on an upper end face 30 of the sleeve 27 and on the other hand on a lower annular shoulder 31 of the valve piston head 28 and so the valve piston 26 in the plane of the drawing in the direction of low pressure space 25 on biases a valve seat 32.
- the sleeve 27 is sealingly pressed on a bottom surface 33 of the valve chamber 23, the bottom surface 33 being formed by a surface of the throttle plate 5.
- the cross-sectional area of the valve piston 26 sealed off at the valve seat 32 corresponds to the cross-sectional area of the valve piston 26 guided inside the sleeve 27.
- the diameter of the valve seat 32 corresponds to the inner diameter of the sleeve 27.
- valve piston 26 Due to the at least approximate identity of the acted upon by low pressure surfaces of the valve piston, the valve piston is pressure balanced in the axial direction.
- the drain passage 21 from the control chamber 25 opens into a pocket 37 in the valve body 4.
- the pocket 37 is connected to an annular space 38 between the sleeve 27 and the valve chamber wall 39 so that fuel from the control chamber 15 into the valve chamber 23 can flow.
- the annular space 38 ensures that the guide clearance between valve piston 26 and sleeve 27 does not expand, so that leakage losses are minimized.
- the fuel pressure within the valve chamber 23 ensures for, in addition to the axial spring force of the coil spring 29, an axial force acts on the sleeve 27 in the direction of throttle plate 5, so that the sleeve 27 sealingly abuts the bottom surface 33. Any leakage losses are removed via the connecting line 35.
- an electromagnetic actuator 40 is arranged with an electromagnet 41.
- the electromagnet 41 is received in a bore 42, which guides the electromagnet 41 over its inner diameter.
- the electromagnet 41 is biased by a spring element 43 axially against the lower side in the drawing plane of the injector body 2.
- a stepped bore 44 is provided, the axis of symmetry of which corresponds to the axis of symmetry of the valve piston 26.
- a first shoulder 45 of the stepped bore 44 limits the axial mobility of an armature plate 46, which cooperates with the electromagnet 41.
- a push rod 47 Centrally supported on the armature plate 46 and in a receiving bore of the armature plate 46 is a push rod 47 which transmits a movement of the armature plate 45 to the valve piston 26 and thus controls the movement of the valve piston 26.
- the push rod 47 is centered with its convex free end 48 on the concave end face 34 of the valve piston 26.
- the push rod 47 is guided in a stop sleeve 49 near the anchor plate 46, wherein the stop sleeve 49 is received in a central passage opening of the electromagnet 41 ,
- the stop sleeve 49 has on its upper end face a stop surface 50 for abutment of the armature plate 46 upon energization of the electromagnet 41.
- the armature plate 46 is pressed via a weak biasing spring 51, which is supported on the valve body 2, via the push rod 47 against the valve piston 26, so that these parts are in contact.
- the contacting of the electromagnet 41 is guided via a housing part 52 in the injector body in the drawing plane in order to be able to lead the contacting to the plug, not shown, on the injector head (not shown).
- Fig. 3 the installation situation of the anchor plate 46 is shown.
- the armature plate 46 is received between the injector body 2 and the valve body 4.
- the distance a between the valve body 4 and the underside of the armature plate 46 is the armature stroke when the electromagnet 41 is energized.
- the distance b between the upper side of the armature plate 46 and the injector body 2 is the so-called overtravel. Since the push rod 47 and the anchor plate 46 at the closing time still have kinetic energy, they are moved in the direction of flight F until the anchor plate 46 abuts against the first shoulder 45 of the stepped bore 44. This additional route is referred to as overrunning b and should be designed as low as possible to spend the control valve as soon as possible after an operation in a state of rest.
- Fig. 4 shows a one-piece design between anchor plate 46 and push rod 47. In this case, the armature stroke can be adjusted by a targeted grinding in the length of the push rod 47.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006050163A DE102006050163A1 (en) | 2006-10-25 | 2006-10-25 | Injector i.e. common rail injector, for injecting fuel into combustion chamber of internal combustion engine, has spring pressing piston on seat and casing on surface, where piston diameter in casing corresponds to piston diameter at seat |
PCT/EP2007/058968 WO2008049669A1 (en) | 2006-10-25 | 2007-08-29 | Injector with an axial pressure-compensating control valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2102486A1 true EP2102486A1 (en) | 2009-09-23 |
EP2102486B1 EP2102486B1 (en) | 2010-11-10 |
Family
ID=38577461
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07802985A Active EP2102486B1 (en) | 2006-10-25 | 2007-08-29 | Injector with an axial pressure-compensating control valve |
Country Status (8)
Country | Link |
---|---|
US (1) | US8113176B2 (en) |
EP (1) | EP2102486B1 (en) |
JP (1) | JP2010507746A (en) |
CN (1) | CN101529081B (en) |
AT (1) | ATE487874T1 (en) |
BR (1) | BRPI0717354B1 (en) |
DE (2) | DE102006050163A1 (en) |
WO (1) | WO2008049669A1 (en) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8622475B2 (en) | 2008-12-15 | 2014-01-07 | Bae Industries, Inc. | Linear recliner assembly with threaded linear drive rod and rotatably engaged gear stop |
DE102009027709A1 (en) * | 2009-07-15 | 2011-01-20 | Robert Bosch Gmbh | Fuel injection valve |
DE102009028979A1 (en) * | 2009-08-28 | 2011-03-03 | Robert Bosch Gmbh | Fuel injector for an internal combustion engine |
DE102010031497A1 (en) * | 2010-07-19 | 2012-01-19 | Robert Bosch Gmbh | Fuel injector with hydraulic coupler unit |
AT510462B1 (en) * | 2010-09-22 | 2014-04-15 | Bosch Gmbh Robert | METHOD FOR CHECKING AND REPAIRING A FUEL INJECTOR |
DE102011075750B4 (en) * | 2011-05-12 | 2021-02-11 | Vitesco Technologies GmbH | Method for determining a position of a closure element of an injection valve for an internal combustion engine |
FR2988140B1 (en) * | 2012-03-15 | 2016-02-05 | Bosch Gmbh Robert | HIGH PRESSURE FUEL PRESSURE CONTROL VALVE OF INTERNAL COMBUSTION ENGINE FUEL |
US10077748B2 (en) | 2014-12-23 | 2018-09-18 | Cummins Inc. | Fuel injector for common rail |
CN106762289A (en) * | 2017-01-18 | 2017-05-31 | 哈尔滨工程大学 | Pressure accumulation orifice-plate type electric-controlled fuel injector |
CN109595108B (en) * | 2018-12-03 | 2023-09-01 | 成都威特电喷有限责任公司 | Compact high-pressure fuel injection device |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5779149A (en) * | 1996-07-02 | 1998-07-14 | Siemens Automotive Corporation | Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke |
DE19732802A1 (en) * | 1997-07-30 | 1999-02-04 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
DE19936668A1 (en) * | 1999-08-04 | 2001-02-22 | Bosch Gmbh Robert | Common rail injector |
US6293254B1 (en) * | 2000-01-07 | 2001-09-25 | Cummins Engine Company, Inc. | Fuel injector with floating sleeve control chamber |
DE10001099A1 (en) * | 2000-01-13 | 2001-08-02 | Bosch Gmbh Robert | Control valve for injector of fuel injection system for internal combustion engine; has regulator connected to pressure piston to separate control chamber from control valve and increase pressure |
JP3795724B2 (en) * | 2000-03-13 | 2006-07-12 | 株式会社デンソー | Fuel injection apparatus and injection characteristic adjusting method thereof |
JP4325110B2 (en) * | 2000-12-28 | 2009-09-02 | 株式会社デンソー | Piezoelectric actuator device and fuel injection valve |
DE10120157A1 (en) * | 2001-04-25 | 2002-11-07 | Bosch Gmbh Robert | Fuel injector with throttle element integrated in the control valve |
JP2003083202A (en) * | 2001-09-10 | 2003-03-19 | Nippon Soken Inc | Fuel injection valve |
JP3903927B2 (en) * | 2003-02-20 | 2007-04-11 | 株式会社デンソー | Injector |
DE10353169A1 (en) | 2003-11-14 | 2005-06-16 | Robert Bosch Gmbh | Injector for injecting fuel into combustion chambers of internal combustion engines, in particular piezo-controlled common rail injector |
ES2277229T3 (en) | 2004-06-30 | 2007-07-01 | C.R.F. Societa Consortile Per Azioni | SERVOVALVULA TO CONTROL THE FUEL INJECTOR OF AN INTERNAL COMBUSTION ENGINE. |
JP2006077666A (en) * | 2004-09-09 | 2006-03-23 | Denso Corp | Piezoactuator device |
DE102006021741A1 (en) * | 2006-05-10 | 2007-11-15 | Robert Bosch Gmbh | Fuel injector with pressure compensated control valve |
-
2006
- 2006-10-25 DE DE102006050163A patent/DE102006050163A1/en not_active Withdrawn
-
2007
- 2007-08-29 CN CN2007800400322A patent/CN101529081B/en active Active
- 2007-08-29 JP JP2009533762A patent/JP2010507746A/en active Pending
- 2007-08-29 WO PCT/EP2007/058968 patent/WO2008049669A1/en active Application Filing
- 2007-08-29 DE DE502007005634T patent/DE502007005634D1/en active Active
- 2007-08-29 BR BRPI0717354-7A patent/BRPI0717354B1/en active IP Right Grant
- 2007-08-29 EP EP07802985A patent/EP2102486B1/en active Active
- 2007-08-29 US US12/447,322 patent/US8113176B2/en active Active
- 2007-08-29 AT AT07802985T patent/ATE487874T1/en active
Non-Patent Citations (1)
Title |
---|
See references of WO2008049669A1 * |
Also Published As
Publication number | Publication date |
---|---|
BRPI0717354A2 (en) | 2014-01-21 |
ATE487874T1 (en) | 2010-11-15 |
JP2010507746A (en) | 2010-03-11 |
BRPI0717354B1 (en) | 2019-04-09 |
DE102006050163A1 (en) | 2008-04-30 |
US8113176B2 (en) | 2012-02-14 |
DE502007005634D1 (en) | 2010-12-23 |
CN101529081A (en) | 2009-09-09 |
CN101529081B (en) | 2011-09-07 |
WO2008049669A1 (en) | 2008-05-02 |
EP2102486B1 (en) | 2010-11-10 |
US20100071665A1 (en) | 2010-03-25 |
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