EP1135602A1 - Soupape pour commander le passage de liquides - Google Patents

Soupape pour commander le passage de liquides

Info

Publication number
EP1135602A1
EP1135602A1 EP00965829A EP00965829A EP1135602A1 EP 1135602 A1 EP1135602 A1 EP 1135602A1 EP 00965829 A EP00965829 A EP 00965829A EP 00965829 A EP00965829 A EP 00965829A EP 1135602 A1 EP1135602 A1 EP 1135602A1
Authority
EP
European Patent Office
Prior art keywords
valve
actuating piston
cross
sectional area
chamber
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.)
Withdrawn
Application number
EP00965829A
Other languages
German (de)
English (en)
Inventor
Wolfgang Stoecklein
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 EP1135602A1 publication Critical patent/EP1135602A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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 is based on a valve for controlling liquids in accordance with the type defined in more detail in patent claim 1.
  • a valve which can be actuated via a piezoelectric actuator is already known.
  • This known valve has an arrangement for an adaptive, mechanical tolerance compensation acting in the stroke direction for a displacement transformer of the piezoelectric actuator, in which the deflection of the piezoelectric actuator is transmitted via a hydraulic chamber.
  • the hydraulic chamber which works as a so-called hydraulic ratio, closes between two pistons delimiting it, of which one piston is designed with a smaller diameter and is connected to a valve member to be controlled and the other piston is designed with a larger diameter and connected to the piezoelectric actuator, a common compensation volume. This can be used to compensate for tolerances due to temperature gradients in the component as well as any setting effects, without this resulting in a change in the position of the valve element to be controlled.
  • the hydraulic chamber is clamped between the two pistons in such a way that the actuating piston of the valve member makes a stroke which is increased by the transmission ratio of the piston diameter when the larger piston is moved by a certain distance by the piezoelectric actuator.
  • the valve member, the pistons and the piezoelectric actuator lie one behind the other on a common axis.
  • the piezoelectric actuator supplies a large power reserve as long as the actuator stroke is small, but that the maximum stroke of such piezoelectric actuators is also small.
  • the stroke of the actuating piston of a valve closing element can be increased compared to the actuator stroke by means of a hydraulic or mechanical transmission ratio. However, this reduces the maximum force that the actuator exerts on the valve closing element. This is a major disadvantage, particularly in the case of valves which are not force-balanced. Above all, this applies to servo valves for controlling fuel injection valves designed as common rail injectors, in which on the one hand a high force for opening the valve and on the other hand a large valve lift is desired.
  • the invention has for its object to provide a valve for controlling liquids with a piezoelectric unit as an actuator, with which both a large lifting force and a large valve lift can be realized.
  • valve according to the invention for controlling liquid with a step ratio advantageously enables a large force to be exerted on the valve closing member for a first partial length of the maximum stroke, since the transmission ratio compared to the actuating piston is 1: 1.
  • the valve closing member can thus also be opened against a very high pressure.
  • a large remaining stroke can then be overcome with less force in the sleeve surrounding the actuating piston.
  • the valve is particularly suitable as a servo valve for controlling a fuel injection valve for internal combustion engines, in particular a common rail injector, in which the servo valve has to be opened against a high rail pressure and one specified by an injection needle Flow through the valve seat of the valve closing member must be realized with a corresponding valve lift.
  • the piezoelectric actuator can also be reduced in size, since the maximum actuator force is only required for a short stroke path in order to carry out the required stroke path. Since the dimensioning of the piezoelectric actuator is an important cost factor, the manufacturing costs can additionally be reduced in this way with the valve according to the invention.
  • FIG. 1 shows a schematic, partial representation of a first exemplary embodiment of the invention in a fuel injection valve for internal combustion engines in longitudinal section
  • FIG. 2 shows a schematic illustration of a second exemplary embodiment with an actuating piston that is alternative to that of FIG. 3 shows a diagram with which the valve stroke h over time t is shown in the valve according to the invention in comparison with a conventional valve without step ratio
  • FIG. 4 shows a diagram in which a valve-side actuator force F in relation to the valve stroke h in the invention -
  • the valve according to the invention is shown in comparison to conventional valves without a stepped ratio.
  • FIG. 1 shows a use of the valve according to the invention in a fuel injection valve 1 for internal combustion engines of motor vehicles.
  • the fuel injection valve 1 is designed as a common rail injector, the injection of diesel fuel being controlled via the pressure level in a valve control chamber 12 which is connected to a high pressure supply.
  • a multi-part valve member 2 is actuated via a piezoelectric unit designed as a piezoelectric actuator 3, the piezoelectric actuator 3 on the side facing away from the valve control chamber and combustion chamber of the valve member 2 is arranged.
  • the piezoelectric actuator 3, which is constructed in a manner known per se from several layers, has an actuator head 4 on its side facing the valve member 2 and an actuator foot 5 on the side facing away from the valve member, which is supported on a valve body 9.
  • An actuator piston 7 of the valve member 2 bears against the actuator head 4 via a support 6.
  • the valve member 2 is axially displaceable in a bore 8 of the valve body 9 and comprises, in addition to the actuating piston 7, an actuating piston 10 actuating a valve closing member 13, the actuating piston 7 and the actuating piston 10 being coupled to one another by means of a hydraulic transmission.
  • the hydraulic transmission is designed with a hydraulic chamber 11, via which the deflection of the piezoelectric actuator 3 is transmitted.
  • the hydraulic chamber 11 encloses a common compensation volume between the two pistons 7 and 10 delimiting it, of which the actuating piston 10 is designed with a smaller diameter and the actuating piston 7 with a larger diameter.
  • a stepped ratio for which purpose the actuating piston 10 is designed as a stepped piston which has an area 10A facing the hydraulic chamber 11 with a first cross-sectional area AI and an adjoining area 10B with a larger second cross-sectional area A2, the transition to the larger one two- th cross-sectional area A2 represents a stop 15 for a sleeve 14, by which the actuating piston 10 is surrounded in the bore 8, counter to the valve seat direction.
  • the first, smaller cross-sectional area AI of the actuating piston 10 and the cross-sectional area A3 of the sleeve 14 adjoining the hydraulic chamber 11, neglecting gap areas, correspond to the cross-sectional area A0 of the actuating piston 7 on the hydraulic chamber 11.
  • a stop 34 for the sleeve 14 provided in the valve seat direction until the actuation piston 10 is moved together with the sleeve 14 until it is reached, ie until a first partial length h_0 of a maximum stroke distance H is reached, and from which the actuation piston 10 executes a remaining stroke path h_r alone.
  • the stop 34 is preferably designed as a shoulder on a division surface 33 of the divided valve body 9 in the bore 8.
  • the length of the sleeve 14 is selected to be equal to the length of the region 10A of the actuating piston 10 with the first cross-sectional area AI.
  • the cross-section of the actuating piston 10 tapers from its area 10B with the second cross-sectional area A2 towards a contact surface 16 for the valve closing member 13.
  • valve closing member 13 which is spherical and is provided on the end of the valve member 2 on the valve control chamber side, interacts with valve seats 17, 18 formed on the valve body 9.
  • a spring 19 is assigned to the lower valve seat 18 and holds the valve closing member 13 on the upper valve seat 17 when the valve control chamber 12 is relieved.
  • the valve seats 17, 18 are formed in a first valve chamber 20 formed by the valve body 9, which is connected to a leakage drain channel 21 and to a compensation channel 23 of a filling device 24 leading to a valve system pressure chamber 22.
  • valve closing member 13 only interacts with one valve seat.
  • the valve closing member 13 separates a low-pressure area 25 with a system pressure from a high-pressure area 26 with a high pressure or rail pressure.
  • a (not visible) movable valve control piston is arranged in the high-pressure region 26, of which only the valve control chamber 12 is indicated. Axial movements of the valve control piston in the valve control chamber 12, which is connected in the usual way to an injection line, which is connected to a high-pressure storage chamber (common rail) common to several fuel injection valves and supplies an injection nozzle with fuel, the injection behavior of the Fuel injection valve 1 controlled in a manner known per se.
  • a second valve chamber 27 adjoins the bore 8, which is formed on the one hand by the valve body 9 and is limited on the one hand by a sealing element 28 connected to the actuating piston 7 and the valve body 9, the sealing element 28 shown only schematically in FIG. 1 being designed as a bellows-like membrane and preventing the piezoelectric actuator 3 from containing the fuel contained in the low-pressure region 25 comes into contact.
  • the filling device 24 which is only indicated in FIG. 1, is provided to compensate for a leakage quantity in the low-pressure region 25 by means of the hydraulic fluid from the high-pressure region 26 can be performed in the low pressure region 25.
  • the channel-like cavity 23 of the filling device 24 m flows into a gap 29 surrounding the actuating piston 7, the mouth area forming the system pressure chamber 22 with an annular groove 30.
  • the hydraulic chamber 11 is refilled with fuel from the annular groove 30 with appropriate leakage.
  • the filling device 24 has a suitable throttling in relation to the high-pressure region 26 and a suitable one May have device for releasing an excess pressure.
  • the fuel injection valve 1 according to FIG. 1 operates in the manner described below.
  • FIGS. 3 and 4 serve for further explanation, FIG. 3 showing the valve stroke h over time t and FIG. 4 purely schematically showing the relationship between valve-side actuator force F and valve stroke h in the valve according to the invention compared to conventional valves without a stepped ratio.
  • valve closing member 13 of the valve member 2 is held in contact with the upper valve seat 17 by the high pressure or rail pressure in the high pressure region 26, so that no fuel from the valve control chamber 12 connected to the high pressure storage chamber enters the valve chamber 20 and can then escape through the leakage drain channel 21.
  • the actuating piston 7 penetrates into the compensating volume of the hydraulic chamber 11 as the temperature rises and pulls out accordingly when the temperature drops without this having any effects the closing and Has the open position of the valve member 2 and the fuel valve 1 as a whole.
  • the valve closing member 13 For fuel injection through the fuel injection valve 1, the valve closing member 13 must be opened against the direction of flow and thus against the rail pressure in the high pressure region 26.
  • An actuator force F_mm required for opening results from the existing rail pressure and the diameter of the valve seat 17 or 18.
  • the actuator force F for opening the valve closing member 13, which is greater than the force F_mm required for this with a valve stroke h, is given by the Piezoelectric actuator 3 is generated, which suddenly expands axially when energized and builds up a certain pressure by moving the actuating piston n of the hydraulic chamber 11.
  • a hydraulic force is exerted via the hydraulic chamber 11 on the actuating piston 10 and in this phase on the stop 14 of the actuating piston 10, which is just as large as the force of the piezoelectric actuator 3. That is, it lies em Gear ratio 1: 1 before as long as the sleeve 14 abuts the stop 15.
  • the actuating piston 10 moves together with the sleeve 14 abutting the stop 15 in a time period from the time t_0 of the valve closing member 13 being lifted from the valve seat 17 to the point in time t 1 of striking the sleeve 14 at the stop 34 over a first partial length h_0 of its maximum stroke H.
  • valve movement over time t which is qualitatively represented by the line l_hl in FIG. 3 in the fuel injection valve 1 according to the invention, differs from the valve movement of a conventional valve with a hydraulic or mechanical 1: 1 coupling, which is represented by a line l_h2 is shown in that the valve speed is small in conventional valves, while the actuator force F is large. This can also be seen in FIG. 4 from a line 1_F2 standing for such conventional valves. In contrast, the valve speed in the valve according to the invention is relatively high until the maximum stroke H is reached at a time t_2.
  • the line 1_E3 in FIG. 4 shows the ratio of actuator force F to valve lift h in a conventional valve without a stepped ratio with a ratio of the cross-sectional areas of actuating piston to actuating piston of 2: 1. While a very large maximum valve lift H_3 can be achieved here, the initial actuator force F3 is so small that it is not sufficient to open a valve seat with a large diameter as in the valve according to the invention, which enables a large flow.
  • the valve closing member 13 is stabilized in a central position between the two valve seats 17, 18 and then moved to the lower valve seat 18 in a closed position, as a result of which no more fuel reaches the first valve chamber 20 from the valve control chamber 12 m , If the energization of the piezoelectric actuator 3 is interrupted, it shortens again, and the valve closing member 13 is brought into the middle position between the two valve seats 17, 18, with a renewed fuel injection taking place. Fuel can penetrate into the valve chamber 20 through the lower valve seat 18. After the pressure in the valve chamber 20 has been reduced by the leakage drain 21, the valve closing member 13 moves its closed position to the upper valve seat 17, the sleeve 14 being carried along by the stop 15 of the actuating piston 10.
  • the actuation piston 10 of a second exemplary embodiment of the fuel injection valve is shown in the general position.
  • the actuating piston 10 'shown here differs in that it is designed in two parts, the region 10A' with the first cross-sectional area AI representing a separate component.
  • a recess 32 is provided on an end face 31 of the actuating piston 10 facing this component.
  • the area 10B with the second cross-sectional area A2 and the subsequent tapering area IOC speak in their design to the actuating piston of FIG. 1.
  • the exemplary embodiments relate to m non-force-balanced fuel injection valves
  • the invention can of course also be used in force-balanced designed valves, where the rapid opening of the valve is advantageous.
  • the invention is also not limited to fuel injection valves, but is suitable for all valves with a piezoelectric actuator system in which a valve closing member separates a high pressure area from a low pressure area, such as e.g. in pumps.

Landscapes

  • 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)

Abstract

L'invention concerne une soupape pour commander le passage de liquides, qui comporte une unité piézo-électrique (3) servant à l'actionnement d'un organe de soupape (2) pouvant se déplacer dans un alésage (8) d'un corps de soupape (9) et pourvu d'au moins un piston de commande (16) et d'au moins un piston d'actionnement (10) servant à actionner un organe de fermeture de soupape (13). Entre le piston de commande (7) et le piston d'actionnement (10) est formée une chambre hydraulique (11) jouant le rôle de coupleur hydraulique. Dans cette soupape, une transmission étagée est telle que le piston d'actionnement (10) peut être déplacé avec un manchon (14) qui l'entoure sur une première longueur partielle de sa course de levée maximale, une première surface de section (A1), respectivement adjacente à la chambre hydraulique (11), du piston d'actionnement (10), et une surface de section (A3) du manchon (14) correspondant ensemble, au maximum, à la surface de section (Ao) du piston de commande (7). En outre, dans l'alésage (8), en direction du siège de soupape, se trouve une butée (34) destinée au manchon (14), le piston d'actionnement (10) exécutant le reste de sa course de levée à partir du moment où ledit manchon atteint ladite butée.
EP00965829A 1999-09-30 2000-09-09 Soupape pour commander le passage de liquides Withdrawn EP1135602A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19946827 1999-09-30
DE19946827A DE19946827C1 (de) 1999-09-30 1999-09-30 Ventil zum Steuern von Flüssigkeiten
PCT/DE2000/003065 WO2001023754A1 (fr) 1999-09-30 2000-09-09 Soupape pour commander le passage de liquides

Publications (1)

Publication Number Publication Date
EP1135602A1 true EP1135602A1 (fr) 2001-09-26

Family

ID=7923810

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00965829A Withdrawn EP1135602A1 (fr) 1999-09-30 2000-09-09 Soupape pour commander le passage de liquides

Country Status (7)

Country Link
US (1) US6457699B1 (fr)
EP (1) EP1135602A1 (fr)
JP (1) JP2003510517A (fr)
KR (1) KR20010080619A (fr)
CZ (1) CZ20011877A3 (fr)
DE (1) DE19946827C1 (fr)
WO (1) WO2001023754A1 (fr)

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DE19939520C2 (de) * 1999-08-20 2001-06-07 Bosch Gmbh Robert Einspritzsystem und Verfahren zum Betreiben eines Einspritzsystems
DE10004810A1 (de) * 2000-02-04 2001-08-16 Bosch Gmbh Robert Hydraulisches Hub-Übersetzungssystem
DE10019767A1 (de) * 2000-04-20 2001-10-31 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
FR2819021B1 (fr) 2000-12-28 2005-03-04 Denso Corp Soupape de commande hydraulique et injecteur de carburant utilisant une telle soupape
JP2004526617A (ja) * 2001-02-22 2004-09-02 コンチネンタル・テベス・アーゲー・ウント・コンパニー・オーハーゲー 液圧式自動車ブレーキシステム用バルブ
JP3527215B2 (ja) * 2001-04-26 2004-05-17 株式会社日本自動車部品総合研究所 燃料噴射弁
JP3527214B2 (ja) * 2001-04-26 2004-05-17 株式会社日本自動車部品総合研究所 燃料噴射弁
DE10131617A1 (de) * 2001-06-29 2003-01-23 Bosch Gmbh Robert Kraftstoffinjektor-Schaltventil zur Druckentlastung/Belastung eines Steuerraumes
DE10136186A1 (de) * 2001-07-25 2003-02-06 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10145620B4 (de) * 2001-09-15 2006-03-02 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten
DE10151688A1 (de) * 2001-10-19 2003-04-30 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
FR2836518B1 (fr) * 2002-02-22 2005-12-02 Peugeot Citroen Automobiles Sa Injecteur de carburant
DE10213858A1 (de) * 2002-03-27 2003-10-30 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10312712A1 (de) * 2003-03-21 2004-09-30 Robert Bosch Gmbh Steuergerät und Computerprogramm zum Ansteuern eines Kraftstoffventils einer Brennkraftmaschine
DE102004018927A1 (de) * 2004-04-20 2005-11-17 Robert Bosch Gmbh Common-Rail-Injektor
DE102004027824A1 (de) 2004-06-08 2006-01-05 Robert Bosch Gmbh Kraftstoffinjektor mit variabler Aktorübersetzung
ES2273197T3 (es) * 2004-06-30 2007-05-01 C.R.F. Societa Consortile Per Azioni Inyector de combustible con valvula de control por equilibrio de fuerzas.
DE102005020598A1 (de) * 2005-05-03 2006-11-09 Robert Bosch Gmbh Ventilanordnung einer Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE102007002282A1 (de) * 2007-01-16 2008-07-17 Robert Bosch Gmbh Kraftstoffinjektor mit Koppler
GB2574841A (en) * 2018-06-19 2019-12-25 Rklab Ag Injector apparatus
WO2021136022A1 (fr) * 2020-01-03 2021-07-08 浙江盾安人工环境股份有限公司 Électrovanne
FR3122053A1 (fr) * 2021-04-15 2022-10-21 Psa Automobiles Sa dispositif piézo-hydraulique pour démultiplier un effort à partir d’un élément piezoélectrique

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Also Published As

Publication number Publication date
JP2003510517A (ja) 2003-03-18
US6457699B1 (en) 2002-10-01
CZ20011877A3 (cs) 2002-03-13
WO2001023754A1 (fr) 2001-04-05
KR20010080619A (ko) 2001-08-22
DE19946827C1 (de) 2001-06-21

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