EP1210516B1 - Einspritzsystem und verfahren zum betreiben eines einspritzsystems - Google Patents

Einspritzsystem und verfahren zum betreiben eines einspritzsystems Download PDF

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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
Application number
EP00956132A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1210516A1 (de
Inventor
Patrick Mattes
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1210516A1 publication Critical patent/EP1210516A1/de
Application granted granted Critical
Publication of EP1210516B1 publication Critical patent/EP1210516B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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)
EP00956132A 1999-08-20 2000-08-10 Einspritzsystem und verfahren zum betreiben eines einspritzsystems Expired - Lifetime EP1210516B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19939520 1999-08-20
DE19939520A DE19939520C2 (de) 1999-08-20 1999-08-20 Einspritzsystem und Verfahren zum Betreiben eines Einspritzsystems
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 (ko)
EP (1) EP1210516B1 (ko)
JP (1) JP2003507654A (ko)
KR (1) KR20020023422A (ko)
AT (1) ATE281599T1 (ko)
CZ (1) CZ2002609A3 (ko)
DE (2) DE19939520C2 (ko)
WO (1) WO2001014734A1 (ko)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
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)

* Cited by examiner, † Cited by third party
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
DE59010904D1 (de) * 1990-09-25 2000-05-31 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
EP1046809B1 (de) * 1999-04-20 2005-08-10 Siemens Aktiengesellschaft Fluiddosiervorrichtung
DE19940300A1 (de) * 1999-08-25 2001-03-01 Bosch Gmbh Robert Steuerventil für einen Injektor
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
DE19946841A1 (de) * 1999-09-30 2001-05-03 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten

Also Published As

Publication number Publication date
DE50008530D1 (de) 2004-12-09
KR20020023422A (ko) 2002-03-28
US6588678B1 (en) 2003-07-08
EP1210516A1 (de) 2002-06-05
ATE281599T1 (de) 2004-11-15
WO2001014734A1 (de) 2001-03-01
JP2003507654A (ja) 2003-02-25
CZ2002609A3 (cs) 2003-06-18
DE19939520C2 (de) 2001-06-07
DE19939520A1 (de) 2001-03-01

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