EP0941400A1 - Soupape de commande de liquides - Google Patents

Soupape de commande de liquides

Info

Publication number
EP0941400A1
EP0941400A1 EP98941236A EP98941236A EP0941400A1 EP 0941400 A1 EP0941400 A1 EP 0941400A1 EP 98941236 A EP98941236 A EP 98941236A EP 98941236 A EP98941236 A EP 98941236A EP 0941400 A1 EP0941400 A1 EP 0941400A1
Authority
EP
European Patent Office
Prior art keywords
pressure
piston
coupling space
valve
low
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
EP98941236A
Other languages
German (de)
English (en)
Other versions
EP0941400B1 (fr
Inventor
Rudolf Heinz
Dieter Kienzler
Roger Potschin
Klaus-Peter Schmoll
Friedrich Boecking
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 EP0941400A1 publication Critical patent/EP0941400A1/fr
Application granted granted Critical
Publication of EP0941400B1 publication Critical patent/EP0941400B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • 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
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way 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
    • F02M63/0057—Means for avoiding fuel contact with valve actuator, e.g. isolating actuators by using bellows or diaphragms
    • 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
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions
    • 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
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the invention relates to a valve for controlling liquids according to the preamble of claim 1.
  • EP 0 477 400 discloses such a valve.
  • the actuating piston of the valve member is arranged so as to be tightly displaceable in a part of a stepped bore that is smaller in diameter, whereas a piston with a larger diameter that is moved with the piezo actuator is arranged in a part of the stepped bore that is larger in diameter.
  • a hydraulic space is clamped between the two pistons, such that when the larger piston is moved by the actuator by a certain distance, the actuating piston of the valve member is moved by a distance increased by the transmission ratio of the stepped bore cross-sectional areas.
  • the valve member, the actuating piston, the piston with the larger diameter and the piezo actuator lie one behind the other on a common axis.
  • a volume which is thus increased leads to a compressibility which reduces the transmission rigidity of the hydraulic column formed by the coupling space.
  • the known device essentially provides for leakage from the coupling space in order to achieve tolerance compensation during the working stroke.
  • it is provided to add stabilizing material to the liquid in the coupling space, which has a compressibility-reducing effect. Rubber parts or metal parts that are added to the liquid are also used for this purpose.
  • the valve according to the invention with the characterizing features of claim 1 has the advantage over the fact that the coupling space always remains sufficiently filled by coupling fluid can flow in the direction of the coupling space from the adjacent low-pressure spaces in the times that lie between the working strokes of the piezo actuator. A possible change in length of the entire facility is continuously corrected in this way.
  • the coupling space can be refilled or refilled easily via the col- guided tours. This also applies if the piezo actuator, the valve, the enclosed pressure chamber liquid or the housing should change its length, for example when heated, because such a change in length in the coupling chamber is compensated for by leaks.
  • the device works reliably reliably, has a simple structure and ensures a safe and reliable seal.
  • the filling is favored by the increase in volume during the return stroke of the actuator piston together with the piezo actuator and the pressure drop that arises in this way.
  • This pressure drop is advantageously also supported according to claim 3 by a spring loading the actuator piston toward the piezo actuator.
  • the invention is substantially improved in that defined gaps are provided according to claim 4, which are designed with regard to their task for refilling the coupling space. There is a very essential requirement with regard to this dimensioning in the dimensioning rule according to claim 5.
  • the design of the piston actuating the valve and the actuator piston can be designed according to claim 6, according to which only part of the length of the piston determines the criteria defining the connection between the low-pressure chamber and the coupling chamber for refilling, and a remaining part of the piston each provides the length that is required to ensure exact guidance of the pistons.
  • the piston being provided with only a short gap length l w close to the coupling space and according to claim 8, where the liquid from the low-pressure space is unthrottled the pressure medium channel can be brought up very close to the gap l w
  • An essential improvement of the refilling according to the invention results from claim 11 in that a certain pressure which is higher than the ambient pressure is set in the low-pressure rooms. This results in an increase in the pressure gradient favoring the refilling of the coupling space towards the coupling space, this pressure being provided in accordance with patent claim 12.
  • FIG. 1 shows a fuel injector in section
  • FIG. 2 shows a first embodiment of a piston arrangement on a coupling space with liquid make-up
  • FIG. 3 shows another type of piston
  • FIG. 4 shows a modification of the piston type according to FIG. 3
  • FIG. 5 shows another modification of a Piston type according to FIG. 3
  • FIG. 6 a diagram of the refilling time
  • FIG. 7 a type with three pistons
  • FIG. 8 an injection system with the fuel injection valve according to the invention.
  • the valve according to the invention is used in a fuel injection valve, which is mainly in the
  • This injection valve has a valve housing 1, in which a valve needle 3 is guided in a longitudinal bore 2, which can also be preloaded in the known direction by a closing spring in a known manner (not shown here).
  • the valve needle is provided with a conical sealing surface 4, which cooperates with a seat 6 at the tip 5 of the valve housing projecting into the combustion chamber, from which injection openings lead out into the interior of the injection valve, here the valve needle 3 surrounding it below Connect the fuel pressure-filled annular space 7 to the combustion chamber in order to carry out an injection when the valve needle has lifted from its seat.
  • the annular space is connected to a further pressure space 8, which is constantly connected to a pressure line 10, via which fuel under injection pressure is fed to the fuel injection valve from a high-pressure fuel reservoir 9.
  • This high Kraf material pressure also acts in the pressure chamber 8, and there on a pressure shoulder 11, via which the nozzle needle can be lifted from its valve seat under suitable conditions in a known manner.
  • valve needle At the other end of the valve needle, it is guided in a cylinder bore 12 and includes with its end face 14 a control pressure chamber 15 which is constantly connected via a throttle connection 16 to an annular chamber 17 which, like the pressure chamber 8, is always connected to the high-pressure fuel accumulator stands. Axially from the control pressure chamber 15, a bore having a throttle 19 leads off to a valve seat 20 of a control valve 21. A valve member 22 of the control valve interacts with the valve seat, which in the raised state establishes a connection between the control pressure chamber 15 and a low-pressure chamber 18, which is constantly connected a relief room is connected.
  • a compression spring 24 which loads the valve member 22 in the closing direction and acts on the valve member 22 towards the valve seat 20, so that this connection of the control pressure chamber 15 is closed in the normal position of the control valve. Since the end face of the valve needle 3 is larger in the area of the control pressure chamber. ßer than the area of the pressure shoulder 11, the same fuel pressure in the control pressure chamber, which also prevails in the pressure chamber 8 now holds the valve needle 3 in the closed position. If the valve member 22 is lifted off, however, the pressure is decoupled via the throttle connection 16
  • Control pressure chamber 15 relieved. If the closing force is now missing or reduced, the valve needle 3 opens quickly against the force of a closing spring and, on the other hand, can be brought into the closed position as soon as the valve member 22 comes back into the closed position, since from this point on the throttle connection 16 is the original high fuel pressure then quickly rebuilds in the control pressure chamber 15.
  • the control valve according to the invention has a piston 25 intended for its actuation, which acts on the valve member 22 and can be actuated by a piezo actuator 32 (not shown in detail).
  • the piston 25 is tightly guided in a guide bore 28 arranged in a housing part 26 of the fuel injection valve and limits how the
  • FIG. 2 shows, with its end face 29, a coupling space 30, which on its opposite wall is closed off by a larger diameter piston 65 in a bore 65, which is part of the piezo actuator 32 and which is also arranged in the coupling space 30
  • Spring washer 66 can be non-positively coupled to the piezo actuator 32.
  • the actuator piston can be returned together with the piezo actuator 32 in another suitable manner.
  • Both pistons 25 and 31 are tightly guided in their bores. Due to the different piston surfaces of the two pistons 25 and 31, the coupling space 30 serves as a translator space by translating a design-related small stroke of the piezo actuator piston 31 into a larger stroke of the piston 25 actuating the control valve 21.
  • the piezo actuator 32 When the piezo actuator 32 is excited, the piston 25 is displaced provides that the valve member 22 lifts from its seat 20. This results in a relief of the control pressure chamber 15, which in turn causes the valve needle 3 to open.
  • FIG. 2 shows the coupling space 30 and the two pistons 25 and 31 detached from the valve housing 1.
  • the cylinder bores for the pistons 25 and 31 have gaps 35 and 36 of a width s 1 and s 2 , via which the low-pressure spaces 33 and 18 are connected to the coupling space 30.
  • the length of the gap 35 is denoted by 1 and that of the gap 36 by 1 2 and the diameter of the piston 31 is d and that of the piston 25 is d 2 -
  • the piezo actuator 32 is energized and the actuator piston 31 is subsequently adjusted. This leads to an increase in pressure in the coupling space 30, which in turn results in an adjustment of the piston 25 together with the valve member 22. Because of the different diameters of the pistons, the piston 25 moves further than the actuator piston 31.
  • the pressure increase in the coupling space leads to leakage losses in the coupling space fluid via the leakage gaps between the pistons 25 and 31 and their guidance in the bores.
  • the time in which there is a high pressure in the coupling space for actuating the valve member is short in comparison to the times, the load pauses which lie in between.
  • the coupling space 30 is not pumped empty over the gaps 35 and 36 over time when a high pressure in the coupling space arises during the work of the valve, according to the invention it is possible, in the load pauses, to achieve a rapid refilling of the coupling space 30 in order to compensate for any loss of fluid, even at relatively low pressures in the low-pressure spaces 18 and 33. This is favored by the fact that the actuator piston with the piezo actuator
  • the two pistons 25 and 31 and their guides have to be designed geometrically in a special way in order to achieve an optimal working ability of the arrangement and a repeated production of the filling volume of the coupling space 30.
  • a geometric ratio according to the following equation is to be aimed for as a leak rate characteristic:
  • V Formula From such a ratio, the fastest possible refilling takes place without tolerances, in particular in columns 35 and 36, having a greater influence on the duration of the refilling. It follows from the above relationship that the gap and the piston diameter tend to be large and the initial volume and the length of the sealing gaps are to be chosen small. However, this leak rate characteristic value of> 8 should not be chosen too large, since otherwise the leak rate will become too large and the coupling function, ie the hydraulic rigidity of the coupling space filling volume and thus the stroke, will decrease. In order to keep the stiffness of the coupling space 30 necessary for switching the valve as large as possible, the output volume V 0 of the coupling space must be as small as possible.
  • the gaps 35 and 36 should not be too large and the piston lengths Z and 1 2 should not be too small for the two pistons 25 and 31, and nevertheless the n • d • s 3 “characteristic value > 4, then for the pistons 25 and
  • a piston 37 is shown in FIG. 3, the length dimension 1 of which is interrupted twice by annular grooves 38 and 39 in order to obtain guide parts which are far apart with a short sealing gap length, as a result of which the guide accuracy is increased.
  • the gap lengths lying between the annular groove 39 and 38, the low pressure chamber 18 or 43 and the coupling chamber 30 are shorter than the original total length of the piston. This results in a more favorable geometric ratio for filling according to the above formula for the leakage rate value with very good guidance accuracy.
  • a piston 40 has an annular groove 41 which is arranged close to the coupling space 30 and thus defines a short effective gap length l w there .
  • This short gap length is only included in the result value according to the above formula.
  • the piston part following this effective gap length serves as a necessary guide part, but it has no influence on the value resulting from the above formula. In this way, the favorable value for refilling during the rest periods can be achieved in a simple and safe manner.
  • FIG. 5 shows a piston 42 which, based on the embodiment according to FIG. 4, has a short length
  • the sealing gap length according to the piston 40 is modified in that one or more lateral flats 44 lead away from the annular groove 43, which corresponds to the annular groove 41 in FIG. 4, towards the piston end.
  • the gap width formed by the annular groove 43 and the lateral flats 44 is hydraulically so large that it is ineffective for a sealing function, and the piston part determined by its length only acts as a piston guide and is not included in the result of the leak rate characteristic value.
  • the flattened area 44 is to be regarded as a pressure medium channel through which the annular groove 43 is supplied with pressure medium from the adjacent low-pressure space. However, this flattening can also be realized in a different form, for example also as a bore or another type of channel between the annular groove 43 and the low-pressure space.
  • FIG. 6 shows a diagram which, on the basis of three curves 45, 46 and 47, shows the different duration of the refilling in relation to the duration of the working pressure in the coupling space and at different ambient pressures.
  • a time ratio is plotted on the ordinate, which is determined by the time required to couple the coupling space to a certain pressure, for example 90% of the ambient pressure and the values of the leakage rate parameter, which arise from different parameters and two columns, ie two pistons, the pistons 25 and 31, from the above formula.
  • the leakage rate is ⁇ 4 times, the infinite.
  • the pressure that prevails in the low-pressure chamber is also important. With increasing pressure there is a faster refilling.
  • FIG. 7 shows a design with 3 pistons, namely with the actuator piston 31 already described and with the coupling space 30.
  • a control valve is a control valve
  • the refilling according to the invention can also be used for such a type. It can also be used for devices with more than three pistons.
  • one injection valve 51 is used per engine cylinder, as has already been dealt with on the basis of FIG.
  • the injection valve 51 is on the one hand via a supply line 52 to a high-pressure accumulator 53 and on the other hand via a return line 54 to a low-pressure container 55
  • the injection system also includes a fuel pump 56, a high-pressure pump 57, an overflow valve 58, a pressure control valve 59, a pressure limiter 60, a flow limiter 61 and an electronic control device 62.
  • a pressure-maintaining valve 63 is now inserted into the return line 54, which is led from the injection valve 51 to the container 55 and is set to a pressure of 10 to 20 bar.
  • the return line 54 must then be made correspondingly stable.
  • the two low-pressure chambers 18 and 34 which lie on the two sides of the actuator piston 31 facing away from the coupling chamber 30 and of the piston 25 actuating the valve member 22, are connected to the low pressure, and this low pressure is connected now held by the pressure-maintaining valve 63 at an elevated level of, for example, 10 to 20 bar.
  • a retention valve 63 is particularly recommended if the pressure difference between the pressure in the coupling chamber 30 which has dropped to about 0 bar after the actuator stroke and the ambient pressure of 1 bar until the next injection process of the internal combustion engine (for example 25 ms at an engine speed of 4800 rpm). is not sufficient for refilling the coupling space 30. With the differential pressure increased to 10 to 20 bar, the coupling space 30 can be refilled with certainty in the short time available.
  • the advantage here is that only a single pressure control valve 63 is required per motor.

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

La présente invention porte sur une soupape de commande de liquides pourvue, pour son fonctionnement, d'un compartiment de liaison (30) rempli de liquide, placé entre un piston (21) d'actionneur piézo-électrique (32) et un piston (25) actionnant un élément de soupape. Pour compenser les pertes de liquides que subit le compartiment de liaison lorsqu'il est soumis pendant un court instant à une haute pression à chaque cycle de fonctionnement, le différentiel de pression existant dans des chambres de basse pression (18, 22) entre, d'une part, le compartiment de liaison (30) et, d'autre part, les faces du piston (31) de l'actionneur piézo-électrique (32) et celles du piston (25) actionnant le membre de soupape (22), orientées les unes et les autres du côté opposé au compartiment de liaison (30), est utilisé lors de la course de retour du piston actionneur (31) pour obtenir un nouveau remplissage le long de fentes (35, 36), sans utiliser de soupape. Ce type de soupape est conçu pour des systèmes d'injection de carburant dans des moteurs à combustion interne de véhicules.
EP98941236A 1997-10-02 1998-06-27 Soupape de commande de liquides Expired - Lifetime EP0941400B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19743668 1997-10-02
DE19743668A DE19743668A1 (de) 1997-10-02 1997-10-02 Ventil zum Steuern von Flüssigkeiten
PCT/DE1998/001763 WO1999018347A1 (fr) 1997-10-02 1998-06-27 Soupape de commande de liquides

Publications (2)

Publication Number Publication Date
EP0941400A1 true EP0941400A1 (fr) 1999-09-15
EP0941400B1 EP0941400B1 (fr) 2003-01-29

Family

ID=7844459

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98941236A Expired - Lifetime EP0941400B1 (fr) 1997-10-02 1998-06-27 Soupape de commande de liquides

Country Status (7)

Country Link
US (1) US6168133B1 (fr)
EP (1) EP0941400B1 (fr)
JP (1) JP2001512547A (fr)
KR (1) KR20000069205A (fr)
CN (1) CN1102996C (fr)
DE (2) DE19743668A1 (fr)
WO (1) WO1999018347A1 (fr)

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US6570474B2 (en) 2000-02-22 2003-05-27 Siemens Automotive Corporation Magnetostrictive electronic valve timing actuator
DE10043625C2 (de) * 2000-09-05 2003-03-27 Bosch Gmbh Robert Hydraulisch übersetztes Ventil
EP1325227B1 (fr) 2000-10-11 2006-07-05 Siemens VDO Automotive Corporation Ensemble compensateur a membrane souple pour injecteur de carburant et procede correspondant
DE10055272A1 (de) * 2000-11-08 2002-05-23 Bosch Gmbh Robert Druckgesteuerter Injektor mit in Reihe geschalteten Steuerventilen
US6991187B2 (en) * 2000-11-13 2006-01-31 Siemens Automotive Corporation Magneto-hydraulic compensator for a fuel injector
US6454238B1 (en) * 2001-06-08 2002-09-24 Hoerbiger Kompressortechnik Services Gmbh Valve
DE10155229B4 (de) * 2001-11-09 2004-07-15 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten
US6749127B2 (en) 2002-02-11 2004-06-15 Siemens Vdo Automotive Corporation Method of filling fluid in a thermal compensator
US6983894B2 (en) 2002-02-13 2006-01-10 Siemens Vdo Automotive Inc. Piezo-electrically actuated canister purge valve with a hydraulic amplifier
DE10330132A1 (de) * 2003-07-04 2005-01-20 Robert Bosch Gmbh Druckhalteventil, Werkzeug, Set und Kraftstoffeinspritzsystem
DE102004062006A1 (de) * 2004-12-23 2006-07-13 Robert Bosch Gmbh Kraftstoffinjektor mit direkt angesteuertem Einspritzventilglied
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KR20000069205A (ko) 2000-11-25
CN1241243A (zh) 2000-01-12
CN1102996C (zh) 2003-03-12
DE59807065D1 (de) 2003-03-06
WO1999018347A1 (fr) 1999-04-15
JP2001512547A (ja) 2001-08-21
DE19743668A1 (de) 1999-04-08
EP0941400B1 (fr) 2003-01-29
US6168133B1 (en) 2001-01-02

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