WO1999066197A1 - Ventil zum steuern von flüssigkeiten - Google Patents
Ventil zum steuern von flüssigkeiten Download PDFInfo
- Publication number
- WO1999066197A1 WO1999066197A1 PCT/DE1999/000662 DE9900662W WO9966197A1 WO 1999066197 A1 WO1999066197 A1 WO 1999066197A1 DE 9900662 W DE9900662 W DE 9900662W WO 9966197 A1 WO9966197 A1 WO 9966197A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piezo
- housing
- valve
- actuator
- piezo actuator
- Prior art date
Links
- 239000007788 liquid Substances 0.000 title claims abstract description 10
- 239000000463 material Substances 0.000 claims description 7
- 230000008859 change Effects 0.000 claims description 3
- 230000000694 effects Effects 0.000 claims 1
- 230000002093 peripheral effect Effects 0.000 claims 1
- 238000002347 injection Methods 0.000 description 31
- 239000007924 injection Substances 0.000 description 31
- 239000000446 fuel Substances 0.000 description 29
- 238000010438 heat treatment Methods 0.000 description 8
- 238000001816 cooling Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 230000001276 controlling effect Effects 0.000 description 6
- 238000007789 sealing Methods 0.000 description 6
- 230000008901 benefit Effects 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 2
- 239000012528 membrane Substances 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 239000004065 semiconductor Substances 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 238000011144 upstream manufacturing 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
- 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
- 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
- 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
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/004—Actuating devices; Operating means; Releasing devices actuated by piezoelectric means
- F16K31/007—Piezo-electric stacks
-
- H—ELECTRICITY
- H10—SEMICONDUCTOR DEVICES; ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
- H10N—ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
- H10N30/00—Piezoelectric or electrostrictive devices
- H10N30/80—Constructional details
Definitions
- the invention is based on a valve for controlling liquids according to the preamble of patent claim 1.
- a valve which is known from EP-A-0 371 469
- the valve member is actuated by a piezo actuator, in that a hydraulic space is provided between the piezo actuator and the valve member, via which it is possible to have tolerances balance.
- Such valves have the disadvantage that care must be taken to ensure that the hydraulic space is always sufficiently filled with control fluid.
- the provision of a hydraulic room also means a great deal of effort in terms of sealing the same. If, on the other hand, the valve for controlling liquids is to be actuated directly by a piezo actuator, difficulties arise when working with a piezo actuator due to its energization.
- the heating leads to changes in length of the piezo actuator itself and also to thermal expansion of the heating housing surrounding the piezo actuator. Thus, in the course of the operation of such a valve, it can happen that, due to the different thermal expansions, the valve can no longer get into its closed position or into a defined position.
- the valve according to the invention for controlling liquids with the characterizing features of claim 1 has the advantage that a simple valve can be provided which is actuated directly by the piezo actuator, with temperature-related changes in length of the piezo actuator compared to that of the provided compensating element this receiving housing can be substantially compensated.
- Peltier element can, in a known manner, bring about cooling or heating at the intended installation location and thus counteract undesirable changes in length, in particular changes in length in the direction of actuation of the piezo actuator, by either supplying heat or dissipating heat depending on the operating state or design specification becomes.
- Compensation advantageously takes place in that a compensating element is used, the material of which has a different coefficient of thermal expansion than the surrounding materials.
- a material with a high coefficient of thermal expansion has the advantage that by means of heating and / or cooling by the Peltier element, relatively large compensating changes in length can be achieved in the direction of actuation of the piezo actuator, which can accommodate the large changes in length that occur in the area of heat generation of the working pezo stack , and thus a compensation tion of these changes in length compared to the smaller changes in length in the surrounding housing due to the lower heat flux density.
- the heating or cooling of the compensating element can be carried out by an axially or radially adjoining Peltier element.
- the latter solution offers a smaller axial installation space and a larger contacting surface between the compensating element, the Peltier element and the heat-absorbing housing, which provides a heat sink.
- the heat flow from the piezo element to the heat sink can advantageously be improved by interposing the cup-shaped housing according to claim 7, in order to achieve the lowest possible temperature dependence of the actuation stroke of the piezo actuator.
- FIG. 1 shows a schematic illustration of a fuel injection valve in which the valve according to the invention can be used to control liquids
- FIG. 2 shows a simplified illustration of a first embodiment of the valve according to the invention
- FIG. 3 shows a second embodiment of the invention using a compensating element
- FIG 4 shows a third exemplary embodiment of the invention with a Peltier element lying on the circumferential side of the compensating element according to FIG. 3
- FIG. 5 shows a fourth exemplary embodiment of the invention with a piezo actuator mounted in a cup-shaped housing part.
- FIG. 1 shows a fuel injection valve 1 in a simplified representation, which has an injection valve housing 2, with a stepped bore 3, in which an injection valve member 5 is guided.
- This has a conical sealing surface 6 at one end, which cooperates with a conical valve seat 7 at the end of the stepped bore 3.
- Fuel injection openings 8 are arranged downstream of the valve seat and are separated from a pressure chamber 9 when the sealing surface 6 is placed on the valve seat 7.
- the pressure chamber extends over an annular space 10, which is formed around the part 13 of the injection valve member 5 which is connected to the sealing surface 6 and is connected upstream, to the valve seat 7.
- the pressure chamber 9 is connected via a pressure line 12 to a high-pressure fuel source in the form of a high-pressure fuel reservoir 14, which is supplied, for example, by a high-pressure pump 4, which delivers a variable delivery rate, from a reservoir 11 with fuel which is brought to injection pressure.
- the high-pressure fuel reservoir supplies several of the injection valves shown.
- the part 13 of the injection valve member with a smaller diameter merges with a pressure shoulder 16 facing the valve seat 7 into a part 18 of the injection valve member with a larger diameter. This is tightly guided in the stepped bore 3 and continues on the side facing away from the pressure shoulder 16 in an intermediate part 19, up to a piston-shaped end 20 of the injection valve member.
- this has a spring plate 22, between which and the housing 2 of the fuel injection valve a compression spring 21 is clamped, which acts on the fuel injection valve member in the closed position.
- the piston-like end 20 delimits an end face 24, the area of which is larger than that of the pressure shoulder 16, in the housing 2 of the fuel injection valve, a control chamber 25 which is in constant communication with the high-pressure fuel accumulator 14 via a first throttle 26 and via a second, in a discharge channel 28 arranged throttle 27 is connected to a relief chamber 29.
- the passage of the drain channel 28 is controlled by a control valve 31, which is designed as a 2/2-way valve, so that the drain channel is either open or closed.
- control valve 31 is used to control the injection quantity and injection timing of fuel into the combustion chambers of an associated internal combustion engine, in particular a diesel internal combustion engine. When closed
- Control valve is because of the constant connection of the control chamber 25 with the high-pressure fuel reservoir, the pressure prevailing there at a high level. Because the area of the end face 24 is larger than the area of the pressure shoulder 16 and the pressure acting on both areas is the same at the moment, the result is a force, supported by the compression spring 21, which holds the fuel injection valve member 5 in the closed position . If the control valve 31 is opened to trigger an injection, the control chamber 25 can be relieved to the relief chamber 29, so that, decoupled from the high-pressure fuel reservoir by the first throttle 26, a pressure of lower levels is established in the control chamber 25. In this case, the pressure forces acting on the pressure shoulder 16 in the opening direction predominate and the fuel injection valve is opened for injection, whereby the injection timing and the start of injection are defined. By reclosing the control valve 31, the original high fuel pressure is restored very quickly in the control chamber 25, since the fuel continues to flow via the first throttle 26 can. As a result, the fuel injection valve member 5 returns to its initial position or closed position to end the high-pressure injection.
- the fuel injection valve is controlled via a control unit 36, which controls the control valves 31 of the individual fuel injection valves as a function of operating parameters, further detects the pressure in the high-pressure fuel reservoir with a pressure sensor 37 and controls the variably delivering high-pressure fuel pump 4 in accordance with the deviation from a desired setpoint.
- a pressure relief valve 38 can be provided, which can also be controlled as a pressure control valve depending on operating parameters, depending on the design of the high-pressure fuel supply.
- the force - high-pressure material pump can also deliver the same amount at all times and the pressure in the high-pressure fuel accumulator 14 can be regulated via the pressure relief valve, which is to be regarded here explicitly as a pressure control valve.
- FIG. 2 shows part of the fuel injection valve according to FIG. 1 with the injection valve housing 2, in which the control valve 31 is also integrated and the control chamber 25, which is enclosed in the housing by the end face 24 of the piston-shaped end 20.
- the inflow to the control chamber 25 takes place via the first throttle 26 and the outflow via the outflow channel 28 in which the second throttle 27 is seated.
- the control valve has a valve member 40 with a stem 41 and a valve head 42 which projects into a valve chamber 43.
- a spring plate 44 is provided, against which a compression spring 45 rests, which on the other hand is supported on the housing and strives to keep the valve member in the closed position. This is done by contacting a sealing surface 47 provided on the valve head against a conical seat 46, which is located at the transition between the valve chamber 43 and a guide bore 48 of the adjoining stem 41.
- the shaft Adjacent to the sealing surface 47, the shaft has an annular recess 49, which makes it possible, when the valve head 42 is lifted from the valve seat 46, to connect the valve chamber 43 to a part of the drain channel 128 branching off from the guide bore 48.
- This channel opens into a spring chamber 51 which receives the compression spring 45 and the end of the shaft 41 with the spring plate 46 which projects from the guide bore 48 and from which a line 228 leads to the relief chamber 29.
- the compression spring 45 By the compression spring 45, the valve member 40 is normally held in the closed position, so that the valve chamber 43 and
- Control chamber 25 are closed towards the outflow side and the high pressure of the high-pressure fuel accumulator can build up in the control chamber 25 to close the fuel injection valve member.
- the valve member 40 is actuated in the opening direction by means of the aforementioned piezo actuator 53.
- This consists of a piezo element in the form of a piezo stack 56, which is enclosed axially as seen by a base plate 57 and a cover plate 58, the base plate 57 being an actuating part with a piston-shaped element End 59 can be brought into contact with the shaft 41. Since piezo components can only be stressed permanently and reliably under pressure, the piezo stack is prestressed by spring elements 60. The fresh electrical lead to the piezo stack is not shown in the drawing and is carried out in the usual way.
- the actuator thus formed from the piezo stack, base plate 57, cover plate 58 and spring elements 60 is sealed by an elastic membrane element 61 in an actuator space 54.
- the membrane element 61 closes the actuator space 54 Above the spring chamber 51 and also holds the actuator with its cover plate 58 in contact with a Peltier element 62.
- the temperature in the region of the piezo actuator which has a high heat flow load as the heat source, will become greater during operation of the fuel injector than the temperature of the housing surrounding the actuator space 54, which has a lower heat flow load.
- the piezo actuator would thus increase in comparison to the predetermined length of the housing in which it is installed and could influence the position of the valve member 40. So that the valve member 40 can regularly return to the closed position, a preliminary stroke hv is provided here, which the piston-shaped end 59 has to cover in order to come into contact with the valve member. This forward stroke can partially absorb the temperature-related differences in length, so that the operation of the control valve is not affected.
- the Peltier element provides a further possibility of compensating for length differences by actively influencing the temperature of the piezo actuator.
- a Peltier element can be used to lower the temperature (cooling) or supply it in a known manner.
- These elements are therefore also referred to as electrical semiconductor heat pumps.
- the temperature of the piezo actuator can be regulated in a controlled manner with a regulated supply of heat and / or discharge.
- the distance of the piezo actuator to the valve can be kept constant by heating or cooling.
- a compensating element 68 can be provided in the direction of change in length of the piezo actuator 53 or in the direction of actuation thereof, which compensates with its flat end faces 69, 70 flush with the piezo actuator 53 or Peltier element. Element 62 abuts so that a good heat flow is guaranteed.
- the compensating element has a coefficient of thermal expansion that is particularly large. By means of different heating or cooling via the Peltier element 62, a large change in length of the piezo actuator 53 can be compensated with this high coefficient of thermal expansion.
- the piezo actuator comes into an intended working position in relation to the shaft 41 of the valve element 40 when the operation is started.
- the compensation element 68 can then be cooled with increasing heating , which then leads to a loss of elongation which compensates for the increase in elongation of the piezo actuator.
- the compensating element 68 ' can also come into contact directly with the adjacent housing wall 63.
- the Peltier element 62 ' is arranged on the circumferential side of the compensating element 68', as a result of which a high thermal contact area is formed.
- the annular Peltier element is then in good thermal contact with the annular wall 71 of the housing. Because of the large heat-introducing cross-section, this wall offers the possibility of rapidly dissipating heat which must be passed on from the piezo actuator 53 to the surroundings.
- the wall is connected to corresponding heat sinks, which can either be cooling water or cooling surfaces.
- the position of the piezo actuator 53 can be geometrically fixed in a cup-shaped housing part 73.
- This offers a large heat-dissipating cross-section and it is connected on the circumference via a Peltier element 62 ′′ to the cooled housing or to special heat sinks 75.
- the piezo actuator is also precisely positioned here.
- the piezo actuator is already partially cooled by the heat flow through the pot-shaped housing part and it is compensated for length by the Peltier element 62 '.
- the cup-shaped housing part itself can also act as a compensating element analogous to the embodiment according to FIG. 4.
- the embodiment according to FIG. 5 offers an even better heat flow compared to that according to FIG. 4, since larger dissipative surfaces and larger thermal contact surfaces are available to the Peltier element 62 ′′.
- a piezo actuator can be used in a simple manner, which has the advantage of precisely controllable ren opening strokes both with respect to the opening path and the opening times. For this purpose, it offers the great advantage of being able to achieve high switching speeds that are able to control even small pre-injection quantities by briefly and / or slightly relieving the pressure on the control room.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/485,542 US6333586B1 (en) | 1998-06-12 | 1999-03-11 | Valve for controlling fluids |
EP99913115A EP1029174A1 (de) | 1998-06-12 | 1999-03-11 | Ventil zum steuern von flüssigkeiten |
JP2000554986A JP2002518640A (ja) | 1998-06-12 | 1999-03-11 | 流量制御弁 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19826339A DE19826339A1 (de) | 1998-06-12 | 1998-06-12 | Ventil zum Steuern von Flüssigkeiten |
DE19826339.2 | 1998-06-12 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1999066197A1 true WO1999066197A1 (de) | 1999-12-23 |
Family
ID=7870758
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE1999/000662 WO1999066197A1 (de) | 1998-06-12 | 1999-03-11 | Ventil zum steuern von flüssigkeiten |
Country Status (5)
Country | Link |
---|---|
US (1) | US6333586B1 (de) |
EP (1) | EP1029174A1 (de) |
JP (1) | JP2002518640A (de) |
DE (1) | DE19826339A1 (de) |
WO (1) | WO1999066197A1 (de) |
Families Citing this family (33)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001512911A (ja) * | 1997-08-05 | 2001-08-28 | シーメンス アクチエンゲゼルシヤフト | 前圧縮された圧電アクチュエータ |
DE19939449A1 (de) | 1999-08-20 | 2001-03-01 | Bosch Gmbh Robert | Verfahren zum Steuern von Flüssigkeiten |
DE19939454A1 (de) | 1999-08-20 | 2001-03-01 | Bosch Gmbh Robert | Verfahren und Vorrichtung zum Steuern von Flüssigkeiten |
DE19946841A1 (de) * | 1999-09-30 | 2001-05-03 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19963920B4 (de) * | 1999-12-31 | 2005-01-13 | Robert Bosch Gmbh | Injektor für ein Common-Rail-Kraftstoffeinspritzsystem mit schiebergesteuertem Zulaufkanal und direkter Kopplung von Steuerkolben und Düsenkanal |
DE10002437A1 (de) * | 2000-01-21 | 2001-08-16 | Bosch Gmbh Robert | Piezoaktor |
DE10016247B4 (de) * | 2000-03-31 | 2009-10-22 | Continental Automotive Gmbh | Einspritzventil mit einer Dichtmembran |
DE10049285A1 (de) * | 2000-10-05 | 2002-04-18 | Bosch Gmbh Robert | Hochdruckleitung mit wechselndem Innendurchmesser |
EP1325225B1 (de) * | 2000-10-11 | 2007-08-08 | Siemens VDO Automotive Corporation | Ausgleichsvorrichtung für ein einspritzventil |
WO2002038948A1 (en) | 2000-11-13 | 2002-05-16 | Siemens Vdo Automotive Corporation | Magneto-hydraulic compensator for a fuel injector |
DE50206891D1 (de) * | 2001-02-22 | 2006-06-29 | Continental Teves Ag & Co Ohg | Ventil, insbesondere für hydraulische kraftfahrzeug-bremsanlagen |
DE10123172A1 (de) * | 2001-05-12 | 2002-11-14 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
JP2003097418A (ja) * | 2001-07-18 | 2003-04-03 | Denso Corp | 圧電体素子の変位伝達構造 |
US6582204B2 (en) * | 2001-09-06 | 2003-06-24 | The United States Of America As Represented By The Administrator Of The U.S. Enviromental Protection Agency | Fully-controlled, free-piston engine |
US6749127B2 (en) | 2002-02-11 | 2004-06-15 | Siemens Vdo Automotive Corporation | Method of filling fluid in a thermal compensator |
DE10233100A1 (de) * | 2002-07-20 | 2004-01-29 | Robert Bosch Gmbh | Piezoelektrisches Aktormodul und Verfahren zur Montage eines piezoelektrischen Aktormoduls |
DE10233906A1 (de) | 2002-07-25 | 2004-02-19 | Siemens Ag | Einspritzmodul |
DE10322672A1 (de) * | 2003-05-20 | 2004-12-09 | Robert Bosch Gmbh | Ventil zum Steuern von Flüssigkeiten |
DE10347774B4 (de) | 2003-10-14 | 2006-04-13 | Siemens Ag | Aufnahmehülse für einen Aktorkörper |
US7145282B2 (en) * | 2004-07-15 | 2006-12-05 | Delphi Technologies, Inc. | Actuator |
JP4539217B2 (ja) * | 2004-07-30 | 2010-09-08 | 日本精工株式会社 | 電動パワーステアリング装置 |
DE102004044153A1 (de) * | 2004-09-13 | 2006-03-30 | Siemens Ag | Hubvorrichtung und Einspritzventil |
DE102006026931A1 (de) * | 2006-06-09 | 2007-12-13 | Siemens Ag | Piezoaktuator |
US7429815B2 (en) * | 2006-06-23 | 2008-09-30 | Caterpillar Inc. | Fuel injector having encased piezo electric actuator |
DE102006043027A1 (de) * | 2006-09-13 | 2008-03-27 | Epcos Ag | Verspannelement und Piezoaktor mit dem Verspannelement |
US20090134240A1 (en) * | 2007-11-27 | 2009-05-28 | Caterpillar Inc. | Method of making piezoelectrically actuated device |
DE102013205273A1 (de) | 2012-04-17 | 2013-10-17 | Schaeffler Technologies AG & Co. KG | Ventileinrichtung |
DE102012014892A1 (de) | 2012-07-27 | 2014-01-30 | Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. | Stellantrieb und Verfahren zum Entwärmen eines in einem Stellantrieb mit einem Stellglied eingehausten Festkörperaktors |
US9951884B2 (en) * | 2014-12-02 | 2018-04-24 | Huo Jhih Co., Ltd. | Temperature control valve |
GB201501295D0 (en) * | 2015-01-27 | 2015-03-11 | Delphi International Operations Luxembourg S.�.R.L. | Servo injector |
US9945292B2 (en) * | 2015-03-10 | 2018-04-17 | Hamilton Sundstrand Corporation | Thermoelectric cooled torque motor |
JP6793026B2 (ja) * | 2016-12-13 | 2020-12-02 | 株式会社堀場エステック | バルブ装置及びバルブ制御装置 |
KR20210045157A (ko) * | 2019-10-16 | 2021-04-26 | 현대자동차주식회사 | 연료 전지 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5977181A (ja) * | 1982-10-25 | 1984-05-02 | Matsushita Electric Ind Co Ltd | 熱動弁 |
EP0371469A2 (de) | 1988-11-30 | 1990-06-06 | Toyota Jidosha Kabushiki Kaisha | Apparat zum Antreiben eines piezoelektrischen Elements zum Öffnen oder zum Schliessen eines Ventilteils |
DE19619319A1 (de) * | 1996-05-14 | 1997-11-20 | Ruediger Ufermann | Piezoelektrische-Kraftstoff- Einspritzvorrichtung |
DE19629589A1 (de) * | 1996-07-23 | 1998-01-29 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
DE19650900A1 (de) * | 1996-12-07 | 1998-06-10 | Bosch Gmbh Robert | Piezoelektrischer Aktuator |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2417450A1 (de) * | 1974-04-10 | 1975-10-23 | Nicolae L Dr Hamburger | Elektrohydraulischer signalumwandler mit umwandlung von stromwaermeunterschieden eines elektrischen steuerstromes in viskositaetsunterschiede einer arbeitsfluessigkeit |
US4933591A (en) * | 1988-01-06 | 1990-06-12 | Ford Aerospace Corporation | Double saggital pull stroke amplifier |
US5402159A (en) * | 1990-03-26 | 1995-03-28 | Brother Kogyo Kabushiki Kaisha | Piezoelectric ink jet printer using laminated piezoelectric actuator |
-
1998
- 1998-06-12 DE DE19826339A patent/DE19826339A1/de not_active Withdrawn
-
1999
- 1999-03-11 JP JP2000554986A patent/JP2002518640A/ja active Pending
- 1999-03-11 US US09/485,542 patent/US6333586B1/en not_active Expired - Fee Related
- 1999-03-11 EP EP99913115A patent/EP1029174A1/de not_active Withdrawn
- 1999-03-11 WO PCT/DE1999/000662 patent/WO1999066197A1/de not_active Application Discontinuation
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5977181A (ja) * | 1982-10-25 | 1984-05-02 | Matsushita Electric Ind Co Ltd | 熱動弁 |
EP0371469A2 (de) | 1988-11-30 | 1990-06-06 | Toyota Jidosha Kabushiki Kaisha | Apparat zum Antreiben eines piezoelektrischen Elements zum Öffnen oder zum Schliessen eines Ventilteils |
DE19619319A1 (de) * | 1996-05-14 | 1997-11-20 | Ruediger Ufermann | Piezoelektrische-Kraftstoff- Einspritzvorrichtung |
DE19629589A1 (de) * | 1996-07-23 | 1998-01-29 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
DE19650900A1 (de) * | 1996-12-07 | 1998-06-10 | Bosch Gmbh Robert | Piezoelektrischer Aktuator |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 008, no. 186 (M - 320) 25 August 1984 (1984-08-25) * |
Also Published As
Publication number | Publication date |
---|---|
DE19826339A1 (de) | 1999-12-16 |
US6333586B1 (en) | 2001-12-25 |
JP2002518640A (ja) | 2002-06-25 |
EP1029174A1 (de) | 2000-08-23 |
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