EP1370750A2 - Mecanisme de reglage hydraulique permettant de commander une soupape d'echange de gaz d'un moteur a combustion interne - Google Patents

Mecanisme de reglage hydraulique permettant de commander une soupape d'echange de gaz d'un moteur a combustion interne

Info

Publication number
EP1370750A2
EP1370750A2 EP02729795A EP02729795A EP1370750A2 EP 1370750 A2 EP1370750 A2 EP 1370750A2 EP 02729795 A EP02729795 A EP 02729795A EP 02729795 A EP02729795 A EP 02729795A EP 1370750 A2 EP1370750 A2 EP 1370750A2
Authority
EP
European Patent Office
Prior art keywords
gas exchange
valve
hydraulic
feed pump
exchange valve
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
EP02729795A
Other languages
German (de)
English (en)
Other versions
EP1370750B1 (fr
Inventor
Diogenes Perez Cuadro
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.)
Mahle Ventiltrieb GmbH
Original Assignee
Mahle Ventiltrieb 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 Mahle Ventiltrieb GmbH filed Critical Mahle Ventiltrieb GmbH
Publication of EP1370750A2 publication Critical patent/EP1370750A2/fr
Application granted granted Critical
Publication of EP1370750B1 publication Critical patent/EP1370750B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F01L9/24—Piezoelectric actuators

Definitions

  • Hydraulic actuator for actuating a gas exchange valve of an internal combustion engine
  • the invention relates to a hydraulic actuator according to the preamble of claim 1 and a method for operating this actuator according to claim 13.
  • the feed pump delivers continuously during the entire engine operation. So that a periodic closing and opening of the gas exchange valves is possible, the hydraulic delivery flow from the delivery pump to the gas exchange valve must be interrupted to open or close the valve. For this interruption, a correspondingly switchable check valve is required within the hydraulic circuit upstream and downstream of the gas exchange valve.
  • a high-pressure accumulator is also required, into which the feed pump delivers closed shut-off valve when the gas exchange valve is upstream. When the shut-off valve is opened upstream of the gas exchange valve, this high-pressure accumulator is connected directly to the gas exchange valve via the circuit line into which the feed pump delivers hydraulic fluid.
  • the invention is concerned with the problem of simplifying the construction of a generic actuator and, moreover, of designing it in such a way that variable, that is to say different, stroke lengths can be achieved when the gas exchange valve is opened.
  • a piezoelectric-hydraulic actuating device for gas exchange valves of internal combustion engines with which, among other things, different stroke lengths can basically be reached when opening a gas exchange valve, is already known from DE 198 39 732 AI.
  • piezo elements act as displacement actuators on a hydraulic transmission system, i.e. a constant amount of hydraulic fluid is moved to actuate the valve.
  • a piezo actuator according to JP 5-20 27 08 A2 works in the same way.
  • the design according to the invention is based on the idea of not shifting a constant volume of hydraulic fluid, but of conveying hydraulic fluid with a high-frequency pump and using the amount of hydraulic fluid delivered or, depending on the volume flow delivered, the Operate gas exchange valves.
  • the embodiment according to the invention compared to those previously known drives, there is already the advantage of a small-scale, camshaft-independent device for actuating the gas exchange valves of an internal combustion engine.
  • an advantage of the invention also consists in the one without a high-pressure accumulator and one switch-off valve located upstream of the gas exchange valve and, secondly, to be able to achieve a variable stroke adjustment of the gas exchange valve.
  • the device according to the invention operates in an energy-saving manner, since the feed pump cannot work continuously, but only intermittently to open or close the valve.
  • the feed pump usually works to open the gas exchange valve, the closing movement of which takes place under the force of a return spring.
  • the gas exchange valve could also close hydraulically and open under the force of a return spring.
  • the valve can also be operated according to the principle of a hydraulic pendulum.
  • a high-frequency, precisely controllable or controllable feed pump is used.
  • feed pumps of this type are those with piezoelectric, magnetostrictive and / or electrochemical actuators as feed elements.
  • the displacer volume of hydraulic fluid that is required to open or close a gas exchange valve against a counterforce can be generated in the circuit in that the circuit flow during the hydraulically effected opening or closing process is completely prevented downstream of the gas exchange valve or is at least accumulated in such a way that downstream there is such a large flow resistance that opening or closing the gas exchange valve by overcoming it Opposing force can take place.
  • the accumulation can be caused by a restricted flow cross-section.
  • This cross section can be varied according to the respective function for opening and closing the gas exchange valve. However, it is also possible to leave the throttle cross-section unchanged and only to vary the delivery volume of the hydraulic fluid in a function-appropriate manner for closing and / or opening the gas exchange valves.
  • the hydraulic force, which acts on a gas exchange valve to be actuated, is thus dependent on the difference in the volume flow flowing upstream and downstream of the gas exchange valve within the hydraulic fluid circuit during a same time.
  • the device according to the invention in particular also enables the gas exchange valves to be actuated when an internal combustion engine is braking.
  • Feed pumps with piezoelectric, magnetostrictive and / or electrochemical actuators as feed elements and possibly similarly operated pump valves, which can be used expediently and advantageously for the present invention, are also particularly suitable in the same way as injection pumps for internal combustion engines.
  • 1b shows a diagram with crankshaft angles KW of an internal combustion engine entered on the abscissa and opening stroke H of the gas exchange valve entered on the coordinate to illustrate different opening stroke lengths achievable with the device according to the invention
  • FIG. 2 shows an actuating device according to FIG. 1 with a feed pump designed as a piezo pump
  • FIG. 3 shows a device according to FIG. 2 with a control valve instead of a 2/2 switching valve
  • Fig. 4 shows a device according to Fig. 2 with a constructively shown 2/2 switching valve and a displacement sensor on the gas exchange valve to be actuated in a first embodiment of the displacement sensor
  • FIG. 5 shows a device according to FIG. 4 with a second embodiment of the displacement sensor
  • FIG. 6 shows a device according to FIG. 2 with a switching device for the mutual actuation of several gas exchange valves by means of a common piezo pump
  • FIG. 7 shows a device according to FIG. 2 with a camshaft-operated 2/2-way valve as a check valve
  • FIG. 8 shows a device according to FIG. 2 with an actuator which additionally engages in the adjustment hydraulic system for braking operation of the internal combustion engine having the gas exchange valves.
  • the hydraulic actuator device shown schematically in Fig. La is composed of the following elements.
  • a high-frequency feed pump 6 which can be operated intermittently or discontinuously conveys hydraulic fluid in a circuit.
  • hydraulic fluid is drawn in from a storage container 8 and is formed via lines 11 and 4 and a 2/2-way switching valve 7 Check valve fed back into the reservoir 8.
  • a gas exchange valve 1 is connected to the circuit line, specifically via a hydraulic chamber 2 of the gas exchange valve 1.
  • a change in the volume of the hydraulic chamber 2 results in a proportional stroke adjustment of the gas exchange valve 1.
  • the stroke distance is indicated by arrows H in FIG.
  • a mechanical spring 19 is provided for the backward movement of the gas exchange valve 1 against a hydraulically effected adjustment.
  • the gas exchange valve 1 is held in the closed position by the spring 19 when there is no hydraulic counterforce.
  • the feed pump 6 delivers hydraulic fluid with a volume flow Q v into the line 11 when the 2/2-way valve is closed.
  • the delivered hydraulic fluid thus penetrates into the hydraulic chamber 2 of the gas exchange valve 1 and thus causes the gas exchange valve 1 to open.
  • the delivery operation of the feed pump 8 ' is interrupted and the 2/2-way valve is switched to flow.
  • the delivery operation is preferably interrupted by switching off the delivery pump 6 in accordance with the valve closing time.
  • the delivery pump 6 must be a high-frequency pump which can be switched without delay and in the shortest possible time intervals.
  • a piezo pump is used as the feed pump 6.
  • An essential advantage of the invention described with reference to the schematic representation in FIG. 1 a is that neither a shut-off valve nor a pressure accumulator between such a shut-off valve and the feed pump are required between the hydraulic chamber 2 of the gas exchange valve 1 and the feed pump 6.
  • a shut-off valve must always be present in such a device, the feed pump delivering that shut-off valve into the high-pressure accumulator when the shut-off valve is in the closed position.
  • hydraulic fluid is essentially conveyed from this high-pressure accumulator into the hydraulic chamber of the gas exchange valve in order to achieve a quick response.
  • variable stroke adjustments of the gas exchange valve 1 can be achieved by means of different flow rates Q v of the feed pump 6. This can be achieved through different delivery times, delivery volumes and / or delivery frequencies of the pump. The variability that can be achieved in this way 11
  • FIG. 1c shows a device according to the invention with two gas exchange valves 1 and 1 in which both gas exchange valves operate according to the same principle described above. Functionally identical parts have the same reference numbers, which are only provided with an additional index line. In addition, only shut-off valves 28, 28 located upstream of the two gas exchange valves 1, l ⁇ are required in order to be able to act alternately on the gas exchange valves 1, l ⁇ .
  • the gas exchange valve 1 is actuated via an interposed lever 30 as a mechanical translation aid.
  • FIG. 2 An actuating device operating according to the schematic structure in FIG. 1 a is shown in FIG. 2 with reference to a piezo pump as feed pump 6.
  • the shaft of the gas exchange valve 1 of an internal combustion engine is designed at its end facing away from the engine combustion chamber as a displacer piston 3 which slidably engages in the hydraulic chamber 2.
  • the hydraulic chamber 2 is connected to the Hydraulic line 4 connected, which is connected on the one hand via a one-way valve 5 through which flow can flow in the direction of the hydraulic chamber 2, to a delivery chamber 9 of the feed pump 6 designed as a piezo pump, and on the other hand via the shut-off valve designed as a 2/2-way switching valve 7 to the reservoir 8 for hydraulic fluid.
  • the hydraulic line 4 is connected to the delivery chamber 9 of the piezo pump 6 via a one-way valve 10 through which the delivery chamber 9 can flow.
  • the connecting line 11 having the one-way valve 5 and starting from the hydraulic line 4 likewise leads into the delivery chamber 9 of the piezo pump 6.
  • the piezo pump 6 consists of a housing 12 in which some piezo elements 13 lying one on top of the other are mounted. In the direction of expansion, these piezo elements 13 act on a piston-shaped displacement element 14, which acts on the delivery chamber 9 of the piezo pump 6 and can be displaced in a driven manner by the piezo elements 13 for changing the volume within the delivery chamber 9.
  • the delivery chamber 9 is sealed with respect to the space of the piezo pump housing 12 via the displacement element 14.
  • the piezo elements 13, which are cut into a stack are prestressed by a spring 15 which is supported on the housing 12 of the piezo pump 6. Further pre-tensioning measures are possible.
  • the piezo elements 13 can be acted upon electrically in order to generate a linear expansion.
  • the hydraulic chamber 2 with the displacement piston 3 of the shaft of the gas exchange valve 1 guided therein is connected in two ways to the hydraulic line 4.
  • one of these connections namely an opening 16, is used exclusively for filling the hydraulic chamber 2
  • a second opening 17 is mainly used for emptying the hydraulic chamber 2 and has a greater flow resistance than the opening 16.
  • the opening 17 is designed in such a way that its flow resistance can be changed by the displacement piston 3 passing over this opening, specifically in such a way that the flow resistance is increased as the hydraulic chamber 2 decreases.
  • the inflow opening 16 is designed as a one-way valve which can only flow through in the direction of the interior of the hydraulic chamber 2. This valve function is achieved by a ball 18 pressed spring-loaded onto the opening 16 from the inside of the hydraulic chamber 2.
  • the valve 1 is held in the closed position by a spring 19 when the valve actuating device is inactive.
  • the piezo pump 6 acts upon the electrical application of the individual piezo elements 13 as a high-frequency pump which, by an oscillating movement of the displacement element 14, hydraulic fluid from the reservoir 8 via the one-way valve 10 and the delivery chamber 9 and then that One-way valve 5 transported into the hydraulic chamber 2, thereby opening the valve 1.
  • a closed 2/2-way switching valve 7 is a prerequisite for opening valve 1.
  • the piezo pump 6 is switched electrically inactive while the 2/2-way switching valve 7 is opened at the same time.
  • the hydraulic fluid under pressure in the hydraulic chamber 2 can pass through the opening 17 and the opened 2/2-way switching valve 7 flow into the hydraulic reservoir 8, whereby the gas exchange valve 1 closes under the force of the spring 19.
  • the displacement speed of the valve stem when the gas exchange valve 1 is closed is reduced, thereby preventing the valve of the gas exchange valve 1 from striking the valve seat.
  • the 2/2-way switching valve 7 is controlled or regulated in combination with the electrical application of the piezo pump 6 such that periodic opening and closing of the gas exchange valve 1 can take place in a fully variable manner.
  • the embodiment of the device according to FIG. 3 differs from that according to FIG. 2 in that an electrical volume flow control valve 20 is used instead of a 2/2-way switching valve 7.
  • This volume flow control valve 20 allows when setting an electrical Stroms a delay in the emptying speed of the hydraulic chamber 2 when the gas exchange valve 1 approaches its closed position. This allows the hydraulic chamber
  • the stem of the valve 1 is connected to a displacement sensor 21 in FIG. 4. Furthermore, the 2/2-way switching valve 7 is shown there in a constructively specific embodiment.
  • the specific design of the 2/2-way switching valve 7 consists in an electromagnetically actuated valve switching device.
  • the displacement sensor 21 is designed as an inductive displacement sensor.
  • the 2/2-way valve switching valve 7 is actuated as a function of the travel signals of the travel sensor 21.
  • the route signals can NEN can also be used to control and regulate the feed pump 6.
  • the embodiment according to FIG. 5 differs from that according to FIG. 4 only in another type of displacement sensor, which is designed there as an eddy current displacement sensor 22.
  • a piezo pump 6 actuates a plurality of gas exchange valves 1 via a multi-way switching valve 23.
  • the switching valve 23 is actuated via electromagnetic actuators
  • This switching valve 23 designed as a slide valve can also be implemented piezoelectrically if the switching dynamics require it.
  • the hydraulic fluid can be kept under pressure in the hydraulic reservoir 8, for which purpose in FIG. 6 a hydraulic pump acting on the interior of the reservoir 8
  • FIG. 7 shows an embodiment in which a 2/2-way switching valve 27 serving as a blocking valve operates in a camshaft-actuated manner, for example by means of a special camshaft 29.
  • Such a camshaft-operated operation of the 2/2-way switching valve 27 can be expedient when actuating a gas exchange valve 1 of an internal combustion engine which acts as an exhaust valve and which is actuated more frequently in a known manner when the internal combustion engine is braking than in an engine drive mode.
  • an additional, for example camshaft-actuated, hydraulic actuator 26 can be provided for controlling the relevant outlet valves 1 in engine brake operation, as shown in FIG. 8.
  • This hydraulic actuator 26 is connected to the hydraulic chamber 2 in an area between the 2/2-way switching valve 7; 27 or the alternatively used control valve 20 and the access opening 16.
  • the piezo pump 6 can be actuated in such a way that it is switched inactive when the hydraulic actuator 26 is active for opening the valve 1.
  • An actuator operating according to the invention has the following advantages in particular. a: There is good system dynamics through a highly dynamic working, for example piezo pump and pressurization of the hydraulic fluid reservoir. A high pressure accumulator is not necessary. The suction behavior of the feed pump is only subject to minimal temperature influences. This makes it possible to use the actuator according to the invention over the entire speed range of the internal combustion engine.
  • a check valve located downstream of a gas exchange valve within the hydraulic fluid circuit is subject to reduced dynamic requirements. due to the variable, i.e. discontinuous piezo pump, so that this check valve can be actuated electromagnetically.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

Pour commander une soupape d'échange de gaz (1) d'un moteur à combustion interne, cette soupape fermant sous l'action d'un ressort, on utilise comme mécanisme de réglage hydraulique une pompe d'alimentation (6) à refoulement intermittent et donc variable (6). Cette pompe d'alimentation (6) fonctionne à haute fréquence et peut, à cet effet, posséder comme éléments de refoulement des actionneurs piézo-électriques, magnétostrictifs et/ou électrochimiques. Le cas échéant, la pompe d'alimentation (6) peut fonctionner avec une soupape d'arrêt (7) qui est située en aval de la soupape d'échange de gaz (1) et qui est commandée ou réglée en fonction de cette pompe.
EP02729795A 2001-03-21 2002-03-16 Mecanisme de reglage hydraulique permettant de commander une soupape d'echange de gaz d'un moteur a combustion interne Expired - Fee Related EP1370750B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10113722 2001-03-21
DE10113722A DE10113722A1 (de) 2001-03-21 2001-03-21 Hydraulischer Stellantrieb zum Betätigen eines Gaswechselventils eines Verbrennungsmotors
PCT/DE2002/000947 WO2002077421A2 (fr) 2001-03-21 2002-03-16 Mecanisme de reglage hydraulique permettant de commander une soupape d'echange de gaz d'un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1370750A2 true EP1370750A2 (fr) 2003-12-17
EP1370750B1 EP1370750B1 (fr) 2005-05-18

Family

ID=7678373

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02729795A Expired - Fee Related EP1370750B1 (fr) 2001-03-21 2002-03-16 Mecanisme de reglage hydraulique permettant de commander une soupape d'echange de gaz d'un moteur a combustion interne

Country Status (4)

Country Link
US (1) US6886509B2 (fr)
EP (1) EP1370750B1 (fr)
DE (3) DE10113722A1 (fr)
WO (1) WO2002077421A2 (fr)

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7641181B2 (en) * 2003-01-24 2010-01-05 Liquid Spring Technologies, Inc. Distributed power suspension system
DE102004018359B4 (de) * 2003-04-12 2013-12-24 Mahle Ventiltrieb Gmbh Hydraulischer Stellantrieb von insbesondere Gaswechselventilen eines Verbrennungsmotors
US20060198742A1 (en) * 2005-03-07 2006-09-07 Baker Hughes, Incorporated Downhole uses of piezoelectric motors
US7559358B2 (en) * 2005-08-03 2009-07-14 Baker Hughes Incorporated Downhole uses of electroactive polymers
ITMI20060608A1 (it) * 2006-03-30 2007-09-30 Dellorto Spa Sistemi e dispositivo elettroidraulico di comando delle valvole di motori a combustione interna ad azionamento variabile con unica elettrovalvola a tre vie
ATE470054T1 (de) * 2006-07-04 2010-06-15 Renault Trucks Hydraulisch betätigtes ventilsteuersystem und verbrennungsmotor mit solch einem system
DE102006034242A1 (de) * 2006-07-21 2008-01-31 Ricardo Deutschland Gmbh Vorrichtung zum Einspritzen von Kraftstoff und zur Betätigung eines Gaswechselventils
SE530572C2 (sv) * 2006-11-16 2008-07-08 Atlas Copco Rock Drills Ab Pulsmaskin för en bergborrmaskin, metod för skapande av mekaniska pulser i pulsmaskinen, samt bergborrmaskin och borrigg innefattande sådan pulsmaskin
GB2455067B (en) * 2007-11-15 2010-02-24 Lotus Car A valve operating system for operating a poppet valve of an internal combustion engine
DE102008049181A1 (de) * 2008-09-26 2010-04-01 Schaeffler Kg Elektrohydraulische Ventilsteuerung
US20130343918A1 (en) * 2011-03-10 2013-12-26 Michael L. Fripp Hydraulic pump with solid-state actuator
CN103742217B (zh) * 2013-12-28 2015-11-18 大连理工大学 一种用于6缸内燃机的模块化多功能可变气门驱动系统
DE102014002309B4 (de) * 2014-02-19 2016-01-07 Hydac Electronic Gmbh Steuervorrichtung
CN105386810A (zh) * 2015-12-31 2016-03-09 潍柴动力股份有限公司 一种发动机制动系统
DE102016205910A1 (de) * 2016-04-08 2017-10-12 Mtu Friedrichshafen Gmbh Ventiltrieb zur variablen Ansteuerung eines Einlassventils und eines Auslassventils und Brennkraftmaschine mit einem solchen Ventiltrieb
CN107288699B (zh) * 2016-04-11 2023-08-29 浙江师范大学 一种压电驱动的无凸轮轴气门驱动机构
DE102016214760B4 (de) 2016-04-28 2018-03-01 Mtu Friedrichshafen Gmbh Verfahren zum Betrieb einer Brennkraftmaschine, Einrichtung zum Steuern und/oder Regeln einer Brennkraftmaschine, Einspritzsystem und Brennkraftmaschine
CN106949246B (zh) * 2017-03-01 2019-01-01 浙江大学 一种高速大流量气动先导式可变配气结构
GB2564100B (en) * 2017-05-15 2021-12-08 Hydro Int Ltd A wastewater treatment device
CN109770440B (zh) * 2019-03-25 2024-04-16 云南中烟工业有限责任公司 一种电子烟液压电泵送装置及其电子烟制品
CN110792746B (zh) * 2019-09-04 2023-07-14 鲁班嫡系机器人（深圳）有限公司 一种压电驱动装置及设备

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH536934A (de) 1969-08-30 1973-05-15 Bosch Gmbh Robert Steuerung von Ein- und Auslassventilen bei Brennkraftmaschinen durch Flüssigkeit
US4200067A (en) * 1978-05-01 1980-04-29 General Motors Corporation Hydraulic valve actuator and fuel injection system
US4206728A (en) * 1978-05-01 1980-06-10 General Motors Corporation Hydraulic valve actuator system
US4593658A (en) * 1984-05-01 1986-06-10 Moloney Paul J Valve operating mechanism for internal combustion and like-valved engines
DE3816165A1 (de) * 1988-05-11 1989-11-23 Bosch Gmbh Robert Steuersystem fuer eine dieselbrennkraftmaschine
JPH05202708A (ja) 1992-01-29 1993-08-10 Suzuki Motor Corp エンジンの動弁装置
JPH05202712A (ja) * 1992-01-30 1993-08-10 Toyota Motor Corp 内燃機関の油圧式弁駆動装置
JP3831778B2 (ja) 1996-06-13 2006-10-11 株式会社日本自動車部品総合研究所 多自由度動弁系制御システム
DE19826045A1 (de) * 1998-06-12 2000-01-13 Bosch Gmbh Robert Verfahren zur Steuerung eines Gaswechselventils für Brennkraftmaschinen
DE19839732C2 (de) 1998-09-01 2002-10-31 Iav Gmbh Piezoelektrisch-hydraulische Betätigungseinrichtung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO02077421A2 *

Also Published As

Publication number Publication date
DE50203141D1 (de) 2005-06-23
US20040094104A1 (en) 2004-05-20
EP1370750B1 (fr) 2005-05-18
DE10291247D2 (de) 2004-04-15
WO2002077421A2 (fr) 2002-10-03
WO2002077421A3 (fr) 2003-01-03
DE10113722A1 (de) 2002-09-26
US6886509B2 (en) 2005-05-03

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