EP1664525A1 - Dispositif de dosage - Google Patents

Dispositif de dosage

Info

Publication number
EP1664525A1
EP1664525A1 EP04787126A EP04787126A EP1664525A1 EP 1664525 A1 EP1664525 A1 EP 1664525A1 EP 04787126 A EP04787126 A EP 04787126A EP 04787126 A EP04787126 A EP 04787126A EP 1664525 A1 EP1664525 A1 EP 1664525A1
Authority
EP
European Patent Office
Prior art keywords
end cap
actuator
housing
dosing device
stop
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
Application number
EP04787126A
Other languages
German (de)
English (en)
Other versions
EP1664525B1 (fr
Inventor
Georg Bachmaier
Bernhard Fischer
Bernhard Gottlieb
Andreas Kappel
Tim Schwebel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP1664525A1 publication Critical patent/EP1664525A1/fr
Application granted granted Critical
Publication of EP1664525B1 publication Critical patent/EP1664525B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting

Definitions

  • the invention relates to a metering device, in particular with an actuator unit as a drive for a valve in a common rail diesel injector.
  • piezo actuator piezoelectric multilayer actuator
  • Conventional methods for compensating the temperature-related change in length of the piezo actuator using suitable material combinations pose serious stability and manufacturing problems.
  • the elongation ratio of the piezo actuator that can be achieved by the inverse piezoelectric effect in high-performance ceramics due to the application of a maximum field strength of approx. 2KV / mm permissible for continuous operation is only 1.2-1.4 per thousand (i.e. 1.2-1.4 ⁇ m elongation each) 1 mm length of the piezo actuator).
  • the inverse piezoelectric effect leads to an elongation of maximum 56 ⁇ m. So if there is only a minimal relative deviation in the effective temperature expansion coefficient of approx.
  • the coefficient of thermal expansion depends strongly on the polarization state and the mechanical and electrical load history of the piezo actuator.
  • the temperature dependence of the length of the piezo actuator is non-linear.
  • the temperature expansion coefficient can have values in the range of -5 * 10 ⁇ 6 for the same piezo actuator
  • the positive change in length of the piezo actuator generated by the electrical charging of the piezo actuator is used in current common-rail diesel injectors to push open a sealing element.
  • a thermal gap ie a safety distance, between the freely movable end of a piezoelectric actuator unit (PAU), which is designed as a plunger or to which a plunger is coupled in a mechanically rigid manner and to the sealing element of typically 3-5 ⁇ m.
  • the PAU consists of an upper end cap that is mechanically stiff and that contains at least one hole through which electrical connections of the piezo actuator can be led to the outside, a lower end cap that is designed as a plunger or to which a plunger is mechanically stiffly coupled, the piezo actuator and a Bourdon tube into which the piezo actuator is welded between the two end caps under a prestress of approx. 600N-800N.
  • Thermal coordination between the actuator housing and the PAU is not ideal.
  • the safety distance is used to ensure that, in the event of a greater thermal expansion of the PAU relative to the actuator housing, the sealing element is opened and there is therefore permanent leakage through the servo valve.
  • the listed fluctuations in the PMA temperature coefficient clearly that even such a distance is not always sufficient.
  • the units of the injector are at a high temperature. Due to the associated temperature expansion of the piezo actuator relative to the housing, which cannot be perfectly tuned, the thermal distance can be overcome and the sealing element can be opened despite the lack of piezo control, especially since in the shutdown state no counterforce F 0 caused by the fluid pressure acts on the sealing element. The sealing element is therefore still open when the engine is switched off.
  • the fluid pressure which presses on the sealing element from the other direction, can subsequently reach up to 2000 bar when the injector is switched on and can cause forces or counterforces of up to 600 N.
  • these forces ensure that the sealing element closes in a defined manner, despite the actuator being overstretched.
  • an internal high-pressure pump in the motor vehicle is no longer able to build up the pressure required to close the sealing element when the engine and thus the injector is started again, provided the injector is still hot, so that the injector malfunctions.
  • FIG. 1 An actuator unit A customary in accordance with the prior art is shown in FIG. 1. It consists of a housing 1, a piezo actuator 2 with a tubular spring 8, a first and a second end cap 3, 7, the first end cap 3 being provided with a tappet 4.
  • the piezo actuator 2 is welded into the tubular spring 8 under a prestress of approximately 600 to 800 N in order to avoid harmful tensile stresses during operation.
  • a membrane 5, typically made of metal, enables the piezo actuator to be sealed off from the fuel.
  • the second end cap 7 is supported against the housing 1, while the first end cap 3 together with the control Tappet 4 presses against the sealing element 6 of the seat valve 12.
  • the sealing element 6 which is realized as a ball, is held in the seat 12 by means of a weak return spring (not shown) with approximately 5N.
  • a weak return spring (not shown) with approximately 5N.
  • thermal changes are not short-term processes in the range of less than 10 ms, but rather are in the seconds to minutes range.
  • a slow expansion of the actuator 2 can, however, be intercepted by a hydraulic compensation element X, as shown in FIG.
  • Such a hydraulic compensation element X is preferably located between the end cap 7 of the actuator 2 and the upper end of the housing 1 and is fastened to the housing. Using such a hydraulic compensation element, the thermal expansion of the actuator now takes place in the direction of the end cap 7 and does not necessarily lead to a change in the distance between the
  • the hydraulic compensation element X has a stiffness that is comparable to that of a solid body in comparison to short-term application of force. Despite this stiffness, the hydraulic compensation element or a component of the hydraulic compensation element that is indirectly or directly connected to the piezo actuator yields by a negligible path. However, these negligible paths add up when the piezo actuator is actuated several times, so that the hydraulic compensation tion element or the component of the hydraulic compensation element is shifted upward by the maximum deflection of the piezo actuator and the distance between the plunger 4 and sealing element 6 is increased such that the plunger no longer reaches the sealing element when the piezo actuator is actuated repeatedly. In this case, opening of the sealing element 6 is no longer possible.
  • the invention is therefore based on the object of specifying a device and / or a method by which a predeterminable distance between a sealing element and an actuator unit can always be maintained.
  • the solution consists in a metering device, comprising: an actuator unit comprising a housing with an actuator inserted into the housing, a hydraulic compensation element which is connected to the actuator, a first end of the actuator being provided with a first end cap, a stop in the form a seat is arranged on the housing, which lies opposite the first end cap and for the first end cap an abutment position, the stop defines a maximum distance between a sealing element of a valve unit and the end cap, the distance being smaller than the deflection length caused by the actuator and the deflection length over the end cap for opening the valve is sufficient when the first end cap moves in the direction of the hydraulic compensation element, the end cap hits the stop and this movement is blocked.
  • This metering device has the advantage that the smallest possible distance between the sealing element and the actuator is maintained even with fluctuating working temperatures. An opening of the sealing element by the actuator is thus always guaranteed, the Raulische compensation element achievable compensation of the temperature expansion of the actuator is maintained.
  • the first end cap is guided past the stop and, by means of a subsequent second rotation, the end cap and the stop face each other such that when the end cap moves in the direction of the hydraulic compensation element, the end cap hits the stop and this one - movement is blocked.
  • the procedure corresponds to a simple key-lock relationship between the end cap and the stop. It is particularly suitable and safe for simple manufacture of the metering device.
  • the key-lock relationship is preferably a bayonet lock.
  • the actuator is preferably a piezo actuator.
  • FIG. 2 shows a metering device with a stop arrangement and a hydraulic compensation element
  • FIG. 3 examples of a geometry of an end cap
  • FIG. 4 the end cap guided through a housing and presented in FIG. 3,
  • Figure 5 is a three-dimensional view of the end cap passed through the housing
  • FIG. 2 shows a dosing device with the known features from FIG. 1, a hydraulic compensation element 13 already mentioned, modified end caps 7, 3 and a stop 1.
  • the hydraulic compensation element 13 can be installed in the metering device in a simple manner between one end of the housing 1 and the piezo actuator 2, which advantageously simplifies the integration into or modification of existing injectors.
  • the hydraulic compensation element is preferably fixedly attached to the inner wall of the housing 1.
  • the hydraulic compensation element 13 is fundamentally stiff with respect to a brief application of force and, at the same time, yields in the event of a thermally induced change in the length of the actuator.
  • the hydraulic compensation element 13 preferably has at least one hydraulic chamber 13c, a hollow cylindrical housing 13a and a piston 13b, the piston 13b or the housing 13a being connected to the second end cap 7 of the actuator 2.
  • the hydraulic chamber 13c lies between axially pressure-effective surfaces of the piston and the housing and between at least two clearance fits 13g, which are formed between the piston and the housing.
  • the axially pressure-effective surfaces are essentially axially aligned.
  • “Axial” is understood to mean the direction of the force effects and transmissions of the piezo actuator or the hydraulic compensation element. However, “axially” is also understood to mean “essentially axially”.
  • the game fits 13g basically have a strongly fluid-restricting effect.
  • the hydraulic compensation element can be filled under pressure with a fluid, preferably silicone oil. It is preferred that the hydraulic compensation element has an axial bore 13d through the feed lines 17 can be guided to the piezo actuator 2. In particular, the piston 13b is provided with this through hole 13d.
  • the piston 13b and the housing 13a can be displaced relative to one another in a forceless manner in the event of a slow thermally induced change in length of the actuator, so that the hydraulic compensation element yields during this time.
  • the piston In the event of a brief impact, the piston only moves a negligible distance relative to the housing, so that the hydraulic compensation element can be regarded as stiff.
  • the hydraulic compensation element has several, in particular two, hydraulic chambers for increased rigidity.
  • the housing 13a is expanded by a part in order to form a further hydraulic chamber, analogous to the first hydraulic chamber 13c, between the piston 13b and the housing 13a, as mentioned above.
  • the hydraulic compensation element would act bidirectionally.
  • the hydraulic compensation element 13 is provided on its two end faces with membranes 13f, which are preferably each attached to the piston 13b and to the housing 13a.
  • Storage volumes 13e are formed by the membrane between the housing, the membranes and the piston.
  • the membranes can bulge even at elevated temperatures, so that they can compensate for a thermal change in volume of the fluid in the hydraulic compensation element. They preferably each have thermal expansion coefficients that differ from those of the housing and / or the piston.
  • the membrane is preferably designed as an annular flat membrane.
  • the hydraulic compensation element is hydraulically provided with a compensation accumulator via a bore in the housing 13a is connected in order to be able to intercept an increasing volume change of the fluid in the hydraulic compensation element even better at elevated temperature than only with the aforementioned membranes 13f and storage volumes 13e.
  • the compensating accumulator preferably has a membrane, which can be realized as an elastic sleeve, and a storage volume enclosed underneath.
  • the elastic sleeve of the compensation memory is preferably arranged on the outer surface of the housing 13a. When the temperature of the fluid rises, the membrane expands so that a larger volume is available to the fluid in the hydraulic compensation element and therefore there is no disruptive net force effect between the piston and the housing.
  • the housing 13a of the hydraulic compensation element by means of a spacer with the inner wall of the housing 1 of the metering device is mechanically connected.
  • the compensating accumulator can also be implemented in the form of an external hydraulic accumulator.
  • the piston 13b or the housing 13a is provided with axial bores which connect the storage volumes 13e to the hydraulic chambers 13c in order to facilitate a return flow of the fluid into the hydraulic chambers and into the storage volumes during the blanking gap of the piezo actuator.
  • the openings of the holes are provided with check valves, so-called flapper valves, so that the openings of the holes close when the piezo actuator is briefly deflected, and the hydraulic compensation element is still stiff when the force is briefly applied.
  • the check valves open due to a drop in pressure in the hydraulic chambers 13c.
  • a low-friction movement of the piston 13b relative to the housing 13a of the hydraulic compensation element can be guaranteed, since otherwise its desired compensation function would not be given or would only be given to a limited extent.
  • the fit dimensions and tolerances of the piston and housing must be selected so that there is positive play.
  • a sufficient surface quality of the outside of the piston and / or the inner wall of the housing, in particular a low surface roughness, such as can be produced by grinding, for example, and to avoid tilting, is sufficient for a low-friction and jerky movement between the piston and the housing Guide length, advantageous.
  • Adherence to the fit dimensions of the piston and cylinder is ensured in such a way that not only in the assembled state, but also in the stationary and transient operation of the hydraulic compensation element, there is no jamming or sliding (stick-slip) of the piston in the housing, for example by a greater thermal expansion of the piston with respect to the housing or a greater thermal contraction of the housing with respect to the piston.
  • radial temperature gradients occur due to the high and time-changing heat release of the piezo actuator with simultaneous cooling by the fuel, which can lead to different thermal expansion of the piston and cylinder and, if not properly designed, to pinches. This can be prevented by the following measures:
  • the piston and the housing consist of the same material or materials with the same thermal expansion coefficient.
  • the temperature influence on the gap flow between the clearance fits 13g in the state of the hydraulic system loaded by an actuator can be in wide ranges be compensated if the piston has a suitably chosen higher thermal expansion than the housing.
  • the explanation is that the viscosity of the hydraulic fluid decreases with temperature according to an exponential law and the volume flow of the hydraulic fluid increases exponentially along the clearances.
  • the volume flow is proportional to the 3rd power of the width of the fit, which can also be referred to as the fit.
  • the fit diminishes linearly with the temperature and thus the temperature effects on the fit and on the viscosity are opposite.
  • the housing 1 of the metering device is extended compared to the original structure according to FIG. 1 in order to be able to accommodate the hydraulic compensation element 13.
  • the second end cap 7 ⁇ is welded to the piston 13b of the hydraulic compensation element.
  • the housing 1 is closed at the top by a closing element 15, preferably a fixed bearing. Nevertheless, the relatively small space requirement of the hydraulic compensation element 13 with maximum rigidity for the metering device for installation in an injector of a motor vehicle under the strict space conditions customary there is particularly advantageous.
  • the piezoelectric actuator unit PAU mentioned in the introduction to the description, hereinafter referred to as actuator unit A, comprises the arrangement of features that are directly or indirectly mechanically connected to the piezo actuator 2, in addition to the features known from FIG. 1, also has a first, lower and modified end cap 3 ⁇ , which is equipped with a plunger 4 directed towards a valve unit B.
  • the valve unit B is understood to be at least one arrangement which comprises the valve seat 12 and the sealing element 6.
  • the valve unit can also have supply and return lines 9, 10 for the fuel.
  • the end cap 3 ⁇ is preferably frustoconical, the outer surface of which has steps.
  • the end cap 3 * should have at least two ears 3 x a, the surfaces of which, aligned essentially axially and in the opposite direction to the sealing element 6, come into contact with the axially aligned surfaces 14a of the stop 14 when the actuator is withdrawn.
  • a membrane 5 seals the piezo actuator 2 against a fuel located in the metering device, which flows from the inlet 9 through the seat valve 12 to the return 10 when the sealing element 6 is opened.
  • the membrane 5 preferably connects the housing 1 to the end cap 3 ⁇ .
  • the piezo actuator 2 is preferably also provided with a second, upper end cap 7, which is connected to the hydraulic compensation element. It is preferred that the end cap 7 has an axial bore 16 for connecting wires 17 in order to simplify the contacting of the piezo actuator 2 with control electronics (not shown).
  • An essential element of the metering device is the stop 14, which acts against a change in the equilibrium position of the piston 13b of the hydraulic compensation element, and thus also the position of the end cap 3 ⁇ .
  • the stop 14 can be viewed as a taper of the inside diameter of the housing 1.
  • inner diameter or “diameter” is always understood to mean a transverse axial diameter that runs at right angles to the longitudinal axis of the actuator.
  • the stop is preferably broken through by two recesses. The stop allows the actuator to expand in the direction of the sealing element 6, but prevents the end cap 3 from being pulled back beyond a predefined distance from the sealing element 6. If the piston 3b of the hydraulic compensation element also wants to move away from its originally set equilibrium position, the elasticity of the piezo actuator results in a push-back force which, after the control voltage for the piezo actuator has been removed (the blanking gap), the originally set equilibrium position of the piston 13b forces.
  • the stop 14 can be designed in a large number of variants. It is essential in a specific embodiment to mount it below the piezo actuator in order to allow the actuator to expand upwards or in the opposite direction to the sealing element.
  • Figure 3 shows the lower end cap 3 ⁇ as a truncated cone shape with a lateral surface which is provided with steps.
  • the end cap has in particular two ears 3 a, on the transverse axial plane of which there is an outer diameter of the end cap which is larger than the minimum inner diameter of the stop or the taper 14 of the housing 1.
  • the ears 3 ⁇ a of the end cap 3 in particular are guided past the recesses 14 a of the stop 14. The end cap is then turned so that the ears 3 a can no longer be pushed past the stop by pulling back the end cap.
  • Figure 4 shows how the end cap 3 before the finished ⁇ hergestell- th state of the dosing device the stop 14 is opposite.
  • the cross-sectional view on the left shows how the outer diameter of the end cap 3 at the level of the ears 3 ⁇ a is larger than the minimum inner diameter of the stop.
  • the recesses of the stop are shown at 14a.
  • the right three-dimensional view clearly shows how that
  • Recess 14a and stop are each arranged together.
  • the position of the ears 3 ⁇ a of the end cap is such that the end cap 3 ⁇ can be passed straight ahead without rotating the stop by the ears 3 ⁇ a being passable through the recesses 14a.
  • End cap 3 V has been guided past the stop 14, it is rotated so that the ears 3 die a and the recesses 14a of the stop are no longer axially opposite one another and the ears 3 a would hit the stop 14 when the piezo actuator was withdrawn.
  • FIG. 5 shows a further three-dimensional view of the lower area of the metering device before it has been produced. As shown in FIG. 4, the ears 3 a lie opposite the recesses 14 a, so that the end cap 3 ⁇ can be guided past the stop 14.
  • a stop 14 is the direct connection between the tappet 4 and the sealing element 6 of the seat valve 12, so that the tappet also takes on the role of the sealing element.
  • the valve seat itself becomes the stop element, since the sealing element or the plunger has a diameter so that it or it cannot be guided past the valve seat.
  • the stop 14 can also be replaced by an additional spring between the piston 13b and the fixed bearing 15.
  • the bias of the spring in the manufacture of the metering device ensures an effective downward force which acts via the tappet 4 to the sealing element 6 of the valve unit B and counteracts a change in the equilibrium position of the piston.
  • the piston always experiences a restoring force to prevent the piston from shifting its equilibrium position and to ensure a defined contact between the tappet and the sealing element.
  • the elasticity of the membrane 5 is also suitable as a restoring element for a desired equilibrium position. Welding the membrane 5 to the end cap 3 ⁇ and to the housing 1 provides protection against rotation of the end cap in a position in which the recesses 14a and the ears 3 ⁇ a face each other in the finished state of the metering device, and the This accidentally pulls the end cap past the stop again.
  • the metering device according to the invention is used in a common rail diesel injector.
  • the following sources are included in this document:

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne un dispositif de dosage équipé d'une unité d'actionnement (A) comprenant un corps (1) dans lequel est logé un actionneur (2), ainsi qu'un élément de compensation hydraulique (13) qui peut être rempli d'un fluide sous pression et qui est relié à cet actionneur. Une première extrémité de l'actionneur (2) est pourvue d'un premier capuchon d'extrémité (3'). Une butée (14) sous forme de siège est placée sur le corps (1), cette butée étant située en vis-à-vis du premier capuchon d'extrémité (3') et définissant pour celui-ci une position de butée. Ladite butée (14) maintient une distance maximale entre un élément d'étanchéité (6) d'une unité soupape (B) et le capuchon d'extrémité (3'), cette distance étant inférieure à la course produite par l'actionneur (2) de sorte que la course de l'actionneur (2) soit suffisante pour permettre l'ouverture de la soupape par l'intermédiaire du capuchon d'extrémité (3'). Lorsque le premier capuchon d'extrémité (3') est déplacé en direction de l'élément de compensation hydraulique (13), il entre en contact avec la butée (14) et son mouvement est stoppé.
EP04787126A 2003-09-12 2004-09-10 Dispositif de dosage Expired - Fee Related EP1664525B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10342308 2003-09-12
PCT/EP2004/052130 WO2005026532A1 (fr) 2003-09-12 2004-09-10 Dispositif de dosage

Publications (2)

Publication Number Publication Date
EP1664525A1 true EP1664525A1 (fr) 2006-06-07
EP1664525B1 EP1664525B1 (fr) 2008-04-23

Family

ID=34305717

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04787126A Expired - Fee Related EP1664525B1 (fr) 2003-09-12 2004-09-10 Dispositif de dosage

Country Status (5)

Country Link
US (1) US8038119B2 (fr)
EP (1) EP1664525B1 (fr)
JP (1) JP4264449B2 (fr)
DE (1) DE502004006944D1 (fr)
WO (1) WO2005026532A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005024049A1 (de) * 2005-05-25 2006-11-30 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung, insbesondere für eine Brennkraftmaschine mit Kraftstoff-Direkteinspritzung
US20070007363A1 (en) * 2005-07-04 2007-01-11 Hitachi, Ltd. Fuel injection valve
GB201512350D0 (en) * 2015-07-15 2015-08-19 Delphi Int Operations Lux Srl Servo actuator for fuel injector
EP3139028A1 (fr) * 2015-09-03 2017-03-08 Delphi International Operations Luxembourg S.à r.l. Coupleur à double extrémité pour servocommande
EP3546808B1 (fr) 2018-03-29 2023-05-10 Hamilton Sundstrand Corporation Soupapes

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US2922614A (en) * 1956-06-18 1960-01-26 Honeywell Regulator Co Hum-free solenoid device
US3418980A (en) * 1965-09-01 1968-12-31 Physics Internat Company Fuel injector-ignitor system for internal combustion engines
JPS618462A (ja) * 1984-06-25 1986-01-16 Nippon Soken Inc 電歪式燃料噴射弁
DE3533085A1 (de) * 1985-09-17 1987-03-26 Bosch Gmbh Robert Zumessventil zur dosierung von fluessigkeiten oder gasen
JPH01187363A (ja) * 1988-01-21 1989-07-26 Toyota Motor Corp 内燃機関用燃料噴射弁
DE59811027D1 (de) * 1997-04-04 2004-04-29 Siemens Ag Einspritzventil mit Mitteln zur Kompensation der thermischen Längenänderung eines Piezoaktors
DE19826341A1 (de) * 1998-06-12 1999-12-16 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
AT2962U3 (de) * 1998-07-02 1999-11-25 Avl List Gmbh Einspritzeinrichtung für eine brennkraftmaschine
DE19950762A1 (de) * 1999-10-21 2001-04-26 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10019764B4 (de) 2000-04-20 2004-09-23 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten
EP1325226B1 (fr) * 2000-10-11 2006-12-20 Siemens VDO Automotive Corporation Ensemble compensateur muni d'un diaphragme souple et d'un tube de remplissage interne, destine a un injecteur de carburant et procede correspondant
US6766965B2 (en) 2001-08-31 2004-07-27 Siemens Automotive Corporation Twin tube hydraulic compensator for a fuel injector
DE10162250A1 (de) 2001-12-18 2003-07-03 Bosch Gmbh Robert Brennstoffeinspritzventil
US6749127B2 (en) 2002-02-11 2004-06-15 Siemens Vdo Automotive Corporation Method of filling fluid in a thermal compensator

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Title
See references of WO2005026532A1 *

Also Published As

Publication number Publication date
EP1664525B1 (fr) 2008-04-23
DE502004006944D1 (de) 2008-06-05
US20070131884A1 (en) 2007-06-14
US8038119B2 (en) 2011-10-18
JP2007505254A (ja) 2007-03-08
WO2005026532A1 (fr) 2005-03-24
JP4264449B2 (ja) 2009-05-20

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