EP1210516B1 - Einspritzsystem und verfahren zum betreiben eines einspritzsystems - Google Patents
Einspritzsystem und verfahren zum betreiben eines einspritzsystems Download PDFInfo
- Publication number
- EP1210516B1 EP1210516B1 EP00956132A EP00956132A EP1210516B1 EP 1210516 B1 EP1210516 B1 EP 1210516B1 EP 00956132 A EP00956132 A EP 00956132A EP 00956132 A EP00956132 A EP 00956132A EP 1210516 B1 EP1210516 B1 EP 1210516B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- control valve
- hydraulic
- injection system
- transformer
- piezoactuator
- 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.)
- Expired - Lifetime
Links
- 238000002347 injection Methods 0.000 title claims abstract description 36
- 239000007924 injection Substances 0.000 title claims abstract description 36
- 238000000034 method Methods 0.000 title claims abstract description 12
- 230000005540 biological transmission Effects 0.000 claims description 11
- 230000009365 direct transmission Effects 0.000 claims description 7
- 239000000446 fuel Substances 0.000 description 12
- 230000008859 change Effects 0.000 description 8
- 230000000694 effects Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000007613 environmental effect Effects 0.000 description 3
- 230000003213 activating effect Effects 0.000 description 2
- 230000003993 interaction Effects 0.000 description 2
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
Images
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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
-
- 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
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/20—Output circuits, e.g. for controlling currents in command coils
- F02D41/2096—Output circuits, e.g. for controlling currents in command coils for controlling piezoelectric 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
- 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
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
-
- 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
- F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
- F02M2200/701—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical
-
- 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
- F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
- F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
Definitions
- the invention relates to an injection system with a piezo actuator, a hydraulic translator and a control valve, being in the continuous operation of the injection system the stroke of the piezo actuator via a hydraulic medium transferable to the control valve in the hydraulic translator is.
- the invention further relates to a method for Operating an injection system.
- An injection system also referred to below as a piezo injector, according to the genus specified above, in particular application in diesel accumulator injection systems.
- at memory injection or "common rail injection” pressure generation and injection are decoupled.
- the injection pressure from approx. 120 to 1600 bar becomes independent of the Engine speed and the injection quantity generated and is in the "Rail” - the fuel storage - ready for injection.
- Injection timing and injection quantity are in the electronic Control unit calculated and by the injector on each Engine cylinder implemented.
- the injector has the job Start spraying and injection quantity.
- FIG 3 is a control valve of the prior art for shown a piezo actuator.
- the stroke of one not shown Piezo element is opened via a hydraulic translator a control valve 110 transmitted.
- a Valve stroke 112 is provided, which is sufficient to the control valve 110 between a first valve seat 114 and a second valve seat 116 to reciprocate.
- Below of the control valve 110 is the valve control space 118 arranged.
- At this valve control chamber 118 closes via a Inlet throttle 120 on a fuel inlet 122.
- the control room 118 via an outlet throttle-124 the control valve 110 connected. Reaches into the control room 118 a push rod 126 through which the force to not injector shown is transmitted.
- the inlet throttle 120 and the outlet throttle 124 serve on the one hand the opening behavior via their relative flow rates to determine the nozzle needle.
- the flow restrictor 124 also serves to return a leakage amount of Fuel from valve timing 118 in the overlying ones Cavity and over the fuel return 128 to one Fuel tank.
- the inlet throttle 120 prevents the pressure in the control room 118 immediately completely compensates and adapts to the high pressure in the common rail, because only a decrease in pressure enables the opening of the nozzle needle by pulling back the push rod 126.
- valve 110 In the present special case according to the state of the art Figure 3 is a control valve 110 with two valve seats 114, 116.
- the general principles of valve control can also be used with just one valve seat realize.
- the piezo element then, for example, double with voltage pulses Frequency can be excited.
- the prior art systems one of which is shown in FIG 3 is shown, is common that both during the starting process as well as during operation a system pressure in the injector must be present. This places demands on the performance of the High-pressure pump of the common rail system, since the leakage quantity is Ensuring the system pressure supply from the high pressure pump must be provided. There are further disadvantages itself in connection with the occurring leakage quantities, because these have to be removed from the system under high pressure. Furthermore, the prior art systems are environmental depending, for example, at high temperatures engine turned off the fuel from the coupler compartment the control valve evaporates; this represents additional Pressure supply requirements when restarting the System.
- the injection system according to the invention is based on the prior art Technology in an advantageous manner in that the piezo actuator and the components of the hydraulic translator are arranged with respect to the control valve so that at least part of the stroke of the piezo actuator directly on the Control valve is transferable.
- the control valve can thus open due to the stroke of the piezo element without there was a system pressure in the first place.
- the system can therefore be independent of Environmental influences, such as excessive heat or long periods of inactivity of the engine, ensure a system pressure supply at all times. It is surprising that a direct, i.e.
- the lifting capacity of the Piezo element on what with a suitable choice-any other Boundary parameters to compensate for the length reduction can lead. So at low temperatures could be almost the entire stroke of the piezo element in one stroke of Control valve are implemented when the great length of the Piezo element causes a direct or almost direct Contact of the elements within the hydraulic Translator is available. At higher temperature when the piezo element a shorter length is generally a There is a distance between elements of the path translation. There in this case, however, the lifting capacity is greater, the stroke of the piezo element initially run empty and from a certain point Actuate the control valve with power directly at the time and therefore open.
- the hydraulic translator preferably has a first one Translator piston on which stops from a piezo actuator can be acted upon with force. In this way finds a direct power transmission from the piezo actuator in the hydraulic translator, which then, depending on the operating state, hydraulically or directly on the control valve is transferable.
- the hydraulic. Translator one has second booster piston, which is of the first Translator piston can be acted upon by force.
- the invention a hydraulic translator with at least two translation pistons on both via a hydraulic medium as well as interact directly.
- the basic idea of the invention is realized in an elegant way.
- Hydraulic medium between the first and the second Booster piston available. This ensures that the stroke of the piezo actuator by mediating the hydraulic translator in a sufficient stroke of the Control valve is translated. This stroke has to be so big that a sufficient pressure drop is generated in the control room and can open the injector.
- at which transmit the actuating force via a hydraulic medium becomes direct in the direct transmission of power Contact between the hydraulic booster pistons Translator used.
- This direct contact is through one wide temperature range feasible because of the special temperature behavior immediate effects of the piezo element to the relative positions of the booster pistons.
- a slight opening of the Control valve is due to the direct power transmission sufficient to fill the system area with Ensure fuel. Consequently lies after this filling the prerequisite for hydraulic operation of the control valve.
- the stroke of the piezo actuator on the control valve this releases a gap in the range of about 3 - 5 ⁇ m.
- a Gap is sufficient to fill the coupler space of the translator.
- a pressure control valve is preferably used to set a desired system pressure provided. This is able after filling the system area with fuel, which can be done in a few milliseconds System pressure.
- the invention advantageously provides a method to operate a piezo injector with a piezo actuator, a hydraulic translator and a control valve for Available in which the piezo actuator is electrically excited and is caused to a stroke, the stroke in a first phase is transferred directly to a control valve, the stroke in one second phase hydraulically transferred to a control valve and the control valve is opened by the stroke.
- the method thus uses two in a useful manner fundamentally different principles for opening the Control valve. Even when the coupler space is empty, i.e. with a coupler room in which there is no hydraulic medium, can the control valve by the excitation of the piezo actuator of the piezo injector opened by direct mechanical contact become.
- Such direct mechanical contact can over a wide temperature range due to the special Temperature behavior of the piezo element in view on the temperature coefficient and the temperature dependence of the hub can be realized.
- By opening the Control valve which by direct mechanical contact system area with hydraulic medium be filled so that subsequently, in a second phase, hydraulic power transmission can take place.
- By the hydraulic power transmission takes place, so that the stroke of the piezo actuator is converted into a stroke which is sufficient to open the injector.
- control valve in the first phase in the range of about 3 - 5 ⁇ m opens. This opening is enough to quickly fill the system area with Fuel out; at the same time becomes a useful throttling made available. Overall, the leakage rate of the system compared to the use of a constant choke, resulting in an advantageously lower power requirement the high pressure pump leads.
- the method according to the invention is then particularly advantageous if the first phase is the start phase and the second Phase is the phase of continuous operation.
- the first phase is the start phase and the second Phase is the phase of continuous operation.
- a system pressure is preferably provided after the start phase set by a pressure maintaining valve. In this way can take advantage of the common rail system, at which the pressure generation and the injection are decoupled from one another are used in connection with the invention.
- the invention is based on the surprising finding that by taking advantage of the temperature behavior of a piezo element an integrated system supply can be implemented is.
- the system pressure range is filled each time the system is started, so that effects of environmental influences, such as the Temperature at which starting behavior can be avoided. simultaneously is the amount of leakage compared to a control valve with a constant choke significantly reduced, whereby the high-pressure pump of the common rail system has a lower one Has power requirements. Because of the possibility of a unpressurized discharge of the leakage amount in the injector is the Use of conventional leak hoses possible.
- Figure 1a shows a section of a piezo injector with a piezo actuator 10, a hydraulic translator 12 and a control valve 14.
- a stop on the piezo actuator 10 16 provided which has a first booster piston 18 acted upon when the piezo actuator 10 is activated.
- the first booster piston 18 interacts a second booster piston 20, so that this Control valve 14 can be opened.
- FIG 1b shows another state of the invention Device, the same elements with identical reference numerals Marked are.
- the control valve 14 is shown in the same state as in Figure 1a.
- the first booster piston 18 and the second booster piston 20 of the hydraulic booster 12 there is a free space, resulting from the difference in length ⁇ l of the piezo actuator 10 from FIG. 1b in comparison to FIG 1a results.
- This length difference ⁇ l is based on the fact that 1b shows a state at a higher temperature, for example at 120 ° C, is shown as in Figure 1a.
- the negative mentioned Temperature coefficient of the piezo element consequently leads to Retraction of the first booster piston 18.
- the lifting capacity of the piezo actuator 10 at the high temperature larger than at the low temperature.
- the piezo actuator is one Has expanded amount, which for example slightly is smaller than 25 ⁇ m.
- the lifting capacity of the piezo actuator is about 25 ⁇ m in comparison about 50 ⁇ m at 120 ° C.
- the reduced lifting capacity is still sufficient to the control valve 14 by a sufficient amount ⁇ h from the Lift out the valve seat.
- ⁇ l 0, ensures the increased lifting capacity of about 50 microns sufficient opening of the control valve 14.
- the diagram according to FIG. 2 shows the interplay between Stroke h and temperature expansion ⁇ l only schematically.
- the actual changes in length ⁇ l and the stroke h can sometimes be finely coordinated.
- the opening ⁇ h of the control valve 14 is always large enough to be quick Allow the system to be filled with fuel.
- the opening ⁇ h must not be too large either the control valve 14 advantageously a throttling effect Has. This throttling effect may be due to the throttling effect an inlet throttle (see FIG. 3 for the prior art) vote.
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- 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)
- Control And Safety Of Cranes (AREA)
Description
Claims (13)
- Einspritzsystem mit einem Piezosteller (10), einem hydraulischen Übersetzer (12) und einem Steuerventil (14), wobei im kontinuierlichen Betrieb des Einspritzsystems der Hub des Piezostellers (10) über ein Hydraulikmedium in dem hydraulischen übersetzer (12) auf das Steuerventil (14) übertragbar ist, dadurch gekennzeichnet, daß der Piezosteller und die Komponenten des hydraulischen Übersetzers bezüglich des Steuerventils so angeordnet sind, daß durch die Komponenten des hydraulishen Übersetzers bis zum Aufbau eines Systemdrucks im hydraulischen Übersetzer (12) wenigstens ein Teil des Hubs des Piezostellers (10) direkt mechanisch auf das Steuerventil (14) übertragbar ist.
- Einspritzsystem nach Anspruch 1, dadurch gekennzeichnet, daß der hydraulische Übersetzer (12) einen ersten Übersetzerkolben (18) aufweist, welcher von einem Anschlag (16) des Piezostellers (10) mit Kraft beaufschlagbar ist.
- Einspritzsystem nach Anspruch 2, dadurch gekennzeichnet, daß der hydraulische Übersetzer (12) einen zweiten Übersetzerkolben (20) aufweist, welcher von dem ersten Übersetzerkolben (18) mit Kraft beaufschlagbar ist.
- Einspritzsystem nach Anspruch 3, dadurch gekennzeichnet, daß zumindest während des kontinuierlichen Betriebs Hydraulikmedium zwischen dem ersten Übersetzerkolben (18) und dem zweiten Übersetzerkolben (20) vorhanden ist.
- Einspritzsystem nach Anspruch 3 oder 4, dadurch gekennzeichnet, daß bei der direkten Übertragung des Hubs des Piezostellers (10) auf das Steuerventil (14) direkter Kontakt zwischen dem ersten Übersetzerkolben (18) und dem zweiten Übersetzerkolben (20) vorliegt.
- Einspritzsystem nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß bei der direkten Übertragung des Hubs des Piezostellers (10) auf das Steuerventil (14) dieses in einem geringeren Maß öffnet als bei der hydraulischen Übertragung während des kontinuierlichen Betriebs.
- Einspritzsystem nach Anspruch 6, dadurch gekennzeichnet, daß bei der direkten Übertragung des Hubs des Piezostellers (10) auf das Steuerventil (14) dieses einen Spalt im Bereich von etwa 3 - 5 µm freigibt.
- Einspritzsystem nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß ein Druckhalteventil zur Einstellung eines erwünschten Systemdruckes vorgesehen ist.
- Verfahren zum Betreiben eines Einspritzsystems mit einem Piezosteller (10), einem hydraulischen Übersetzer (12) und einem Steuerventil (14), bei dem der Piezosteller (10) elektrisch angeregt und zu einem Hub veranlaßt wird, der Hub bis zum Aufbau eines Systemdrucks im hydraulischen Übersetzer (12) von dessen Komponenten wenigstens zu einem Teil direkt mechanisch auf das Steuerventil (14) übertragen wird und das Steuer ventil (14) durch den Hub geöffnet wird.
- Verfahren nach Anspruch 9, dadurch gekennzeichnet, daß der Hub in der ersten Phase das Steuerventil (14) weniger öffnet als in der zweiten Phase.
- Verfahren nach Anspruch 9 oder 10, dadurch gekennzeichnet, daß der Hub in der ersten Phase das Steuerventil im Bereich von etwa 3 - 5 µm öffnet.
- Verfahren nach einem der Ansprüche 9 bis 11, dadurch gekennzeichnet, daß die erste Phase eine Startphase und die zweite Phase eine Phase des kontinuierlichen Betriebs ist.
- Verfahren nach Anspruch 12, dadurch gekennzeichnet, daß im Anschluß an die Startphase ein Systemdruck von einem Druckhalteventil eingestellt wird.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19939520A DE19939520C2 (de) | 1999-08-20 | 1999-08-20 | Einspritzsystem und Verfahren zum Betreiben eines Einspritzsystems |
DE19939520 | 1999-08-20 | ||
PCT/DE2000/002680 WO2001014734A1 (de) | 1999-08-20 | 2000-08-10 | Einspritzsystem und verfahren zum betreiben eines einspritzsystems |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1210516A1 EP1210516A1 (de) | 2002-06-05 |
EP1210516B1 true EP1210516B1 (de) | 2004-11-03 |
Family
ID=7919028
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00956132A Expired - Lifetime EP1210516B1 (de) | 1999-08-20 | 2000-08-10 | Einspritzsystem und verfahren zum betreiben eines einspritzsystems |
Country Status (8)
Country | Link |
---|---|
US (1) | US6588678B1 (de) |
EP (1) | EP1210516B1 (de) |
JP (1) | JP2003507654A (de) |
KR (1) | KR20020023422A (de) |
AT (1) | ATE281599T1 (de) |
CZ (1) | CZ2002609A3 (de) |
DE (2) | DE19939520C2 (de) |
WO (1) | WO2001014734A1 (de) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10213858A1 (de) * | 2002-03-27 | 2003-10-30 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
DE102004017303A1 (de) * | 2004-04-08 | 2005-10-27 | Robert Bosch Gmbh | Einspritzdüse |
DE102004027824A1 (de) * | 2004-06-08 | 2006-01-05 | Robert Bosch Gmbh | Kraftstoffinjektor mit variabler Aktorübersetzung |
JP4079144B2 (ja) * | 2004-12-20 | 2008-04-23 | 株式会社豊田中央研究所 | 燃料噴射弁 |
US8500036B2 (en) * | 2010-05-07 | 2013-08-06 | Caterpillar Inc. | Hydraulically amplified mechanical coupling |
DE102014211334B3 (de) | 2014-06-13 | 2015-08-27 | Continental Automotive Gmbh | Verfahren zur Charakterisierung eines hydraulischen Koppelelementes eines Piezo-Injektors |
US11666944B1 (en) * | 2020-05-28 | 2023-06-06 | Amazon Technologies, Inc. | Detection of overfilled containers in sortation systems |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4995587A (en) * | 1989-11-03 | 1991-02-26 | Martin Marietta Corporation | Motion amplifier employing a dual piston arrangement |
ATE192263T1 (de) * | 1990-09-25 | 2000-05-15 | Siemens Ag | Anordnung für einen in hubrichtung wirkenden adaptiven, mechanischen toleranzausgleich für den wegtransformator eines piezoelektrischen aktors |
DE19500706C2 (de) * | 1995-01-12 | 2003-09-25 | Bosch Gmbh Robert | Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen |
US5779149A (en) * | 1996-07-02 | 1998-07-14 | Siemens Automotive Corporation | Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke |
DE19652801C1 (de) * | 1996-12-18 | 1998-04-23 | Siemens Ag | Verfahren und Vorrichtung zum Ansteuern wenigstens eines kapazitiven Stellgliedes |
DE19726481A1 (de) * | 1997-06-21 | 1998-12-24 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19732802A1 (de) * | 1997-07-30 | 1999-02-04 | Bosch Gmbh Robert | Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen |
DE19743669A1 (de) * | 1997-10-02 | 1999-04-08 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19746143A1 (de) * | 1997-10-18 | 1999-04-22 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19807903C2 (de) * | 1998-02-25 | 2001-11-29 | Siemens Ag | Vorrichtung und Verfahren zur Kraftübertragung |
DE19843534A1 (de) * | 1998-09-23 | 2000-03-30 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
DE50010902D1 (de) * | 1999-04-20 | 2005-09-15 | Siemens Ag | Fluiddosiervorrichtung |
DE19940300A1 (de) * | 1999-08-25 | 2001-03-01 | Bosch Gmbh Robert | Steuerventil für einen Injektor |
DE19946841A1 (de) * | 1999-09-30 | 2001-05-03 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19946827C1 (de) * | 1999-09-30 | 2001-06-21 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19946828C1 (de) * | 1999-09-30 | 2001-07-12 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
-
1999
- 1999-08-20 DE DE19939520A patent/DE19939520C2/de not_active Expired - Fee Related
-
2000
- 2000-08-10 DE DE50008530T patent/DE50008530D1/de not_active Expired - Lifetime
- 2000-08-10 WO PCT/DE2000/002680 patent/WO2001014734A1/de not_active Application Discontinuation
- 2000-08-10 US US10/049,943 patent/US6588678B1/en not_active Expired - Fee Related
- 2000-08-10 CZ CZ2002609A patent/CZ2002609A3/cs unknown
- 2000-08-10 KR KR1020027002131A patent/KR20020023422A/ko not_active Application Discontinuation
- 2000-08-10 EP EP00956132A patent/EP1210516B1/de not_active Expired - Lifetime
- 2000-08-10 JP JP2001518582A patent/JP2003507654A/ja active Pending
- 2000-08-10 AT AT00956132T patent/ATE281599T1/de not_active IP Right Cessation
Also Published As
Publication number | Publication date |
---|---|
JP2003507654A (ja) | 2003-02-25 |
ATE281599T1 (de) | 2004-11-15 |
CZ2002609A3 (cs) | 2003-06-18 |
DE19939520C2 (de) | 2001-06-07 |
DE19939520A1 (de) | 2001-03-01 |
WO2001014734A1 (de) | 2001-03-01 |
US6588678B1 (en) | 2003-07-08 |
EP1210516A1 (de) | 2002-06-05 |
DE50008530D1 (de) | 2004-12-09 |
KR20020023422A (ko) | 2002-03-28 |
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