EP1276985A1 - Vanne de commande de liquides - Google Patents

Vanne de commande de liquides

Info

Publication number
EP1276985A1
EP1276985A1 EP01916927A EP01916927A EP1276985A1 EP 1276985 A1 EP1276985 A1 EP 1276985A1 EP 01916927 A EP01916927 A EP 01916927A EP 01916927 A EP01916927 A EP 01916927A EP 1276985 A1 EP1276985 A1 EP 1276985A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
piston
throttle body
system pressure
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Withdrawn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
EP01916927A
Other languages
German (de)
English (en)
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 EP1276985A1 publication Critical patent/EP1276985A1/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Withdrawn legal-status Critical Current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
    • F02M63/0031—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
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • 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
    • F02M63/0014—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
    • 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
    • F02M63/0045—Three-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
    • 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

Definitions

  • the invention is based on a valve for controlling liquids according to the type defined in more detail in claim 1.
  • the actuating piston thus 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.
  • This known valve is provided for separating a low-pressure area from a high-pressure area and can be used, for example, in fuel injectors, in particular common-rail injectors, or in pumps of motor vehicles, where different types of such valves are also known in practice.
  • the hydraulic system in the low-pressure range in particular in the hydraulic coupler, requires a system pressure which, however, drops due to leakage if there is insufficient refilling with hydraulic fluid.
  • a filling device is therefore generally provided, with which pressure medium can be fed from the high pressure area into the system pressure area.
  • a system pressure in the hydraulic chamber which is essentially constant and is at least largely independent of the prevailing high pressure in the high-pressure range, creates the problem that, at high pressure values, a large actuator force is required to open the valve closing member against the high-pressure direction, which requires the use of a large one and correspondingly expensive actuator. Furthermore, at high pressure in the high pressure range, the displacement of hydraulic volume from the hydraulic chamber via the gaps surrounding the adjacent pistons is correspondingly increased, whereby the refilling time for building up and maintaining the system pressure on the low pressure side may be extended in such a way that there is a lack of complete refilling shortly thereafter subsequent actuation of the valve, a shorter valve lift is carried out, which may have a negative influence on the opening behavior of the entire valve.
  • the valve according to the invention for controlling liquids with the features of claim 1 has the advantage that the system pressure can be varied in a structurally simple manner depending on the pressure prevailing in the high pressure range. Due to the high-pressure-dependent refilling, an increase in the system pressure in the hydraulic chamber is possible at a high pressure level in the high-pressure range, as a result of which the actuating piston is supported to open the valve closing member against the high pressure that is present. In front- In some cases, a reduced control voltage of the actuator unit compared to a valve with constant system pressure is required, which is why the valve according to the invention can be equipped with a smaller and less expensive actuator unit. In addition, the valve according to the invention enables a defined filling of the low pressure area, in particular the hydraulic chamber. With increasing pressure in the high pressure range, the refilling time can be shortened with the variable system pressure.
  • the solution according to the invention is characterized by its simple nature, which allows the variable system pressure in the hydraulic chamber to be defined by easily adjustable geometric variables such as the diameter and lengths of the throttle body and the piston, along which the system pressure is reduced towards the low-pressure region.
  • the robustness of the system pressure supply against particles or dirt in the hydraulic fluid is particularly advantageous, which is due to the configuration of the refilling device with a quasi-bypass flow. This ensures the reliable provision of the required system pressure in the entire engine map.
  • the at least one throttle body is arranged axially adjustable in the cavity, wherein it is preferably movable in such a way that it branches off the system pressure line when the system pressure drops. pressure at least partially overlaps. This shortens the length of the gap around the throttle body, which results in a higher flow and an increase in the system pressure.
  • the valve according to the invention is particularly suitable for controlling fuel injection valves, but in principle it can also be implemented in all hydraulically translated systems with a piezoelectric actuator or a magnetic actuator, such as in pumps.
  • Figure 1 is a schematic, partial representation of a first embodiment of the invention in a fuel injector in longitudinal section
  • FIG. 2 shows a schematic, partial illustration of a further exemplary embodiment of the invention in longitudinal section, in which case a throttle body of a filling device is mounted so as to be axially displaceable. Description of the embodiments
  • FIG. 1 shows a realization of a valve according to the invention in a fuel injection valve 1 for internal combustion engines of motor vehicles.
  • This fuel injection valve 1 is designed here as a common rail injector for the injection of preferably diesel fuel, the fuel injection being controlled via the pressure level in a valve control chamber 2, which is connected to a high pressure supply.
  • a valve member 3 is actuated via an actuator unit designed as a piezoelectric actuator 4, which is arranged on the side of the valve member 3 facing away from the valve control chamber 2 and is constructed in a manner known per se from several layers.
  • the piezoelectric actuator 4 has an actuator head 5 on its side facing the valve member 2 and an actuator foot ⁇ on its side facing away from the valve member 3, which is supported on a wall of a valve body 7.
  • the valve member 3 comprises a second piston 11, which is also displaceably arranged in a longitudinal bore 10 of the valve body 7 and which has a valve closing member 12 actuated and is therefore also referred to as an actuating piston.
  • the two pistons 9 and 11 delimit a hydraulic chamber 13, which serves as a hydraulic coupler and transmits the deflection of the piezoelectric actuator 4. Since the diameter AI of the second piston 11 is smaller than the diameter of the first piston 9, the second piston 11 makes a stroke which is increased by the transmission ratio of the piston diameter when the larger first piston 9 is moved by the piezoelectric actuator 4 by a certain distance.
  • the hydraulic chamber 13 also serves to compensate for tolerances due to temperature gradients in the component or different coefficients of thermal expansion of the materials used and any setting effects, so that these have no effect on the position of the valve closing element 12 to be controlled.
  • valve seats 14, 15 formed on the valve body 7 and thereby separates a low-pressure region 16 with the system pressure p_sys from a high-pressure region 17 with a high pressure or rail pressure p_R.
  • the valve seats 14, 15 are formed in a valve chamber 18 formed by the valve body 7, from which a leakage drain channel 19 leads away on the side of the valve seat 14 facing the piezoelectric actuator 4. Having high pressure the valve chamber 18 can be connected to the valve control chamber 2 of the high-pressure region 17 via the second valve seat 15 and an outlet throttle 20.
  • valve control chamber 2 which is not shown in any more detail, a movable valve control piston can be arranged in a manner known per se, by means of its axial movements in the valve control chamber 2, which is connected in the usual way to an injection line, which is connected to a high-pressure storage chamber (common for several fuel injection valves) -Rail) is connected and supplies an injection nozzle with fuel, the injection behavior of the fuel injection valve 1 is controlled.
  • a high-pressure storage chamber common for several fuel injection valves
  • a further valve pressure chamber 21 adjoins the piezo-side end of the bore 10 with the valve member 3 and is delimited by the valve body 7, the first piston 9 and a sealing element 22 connected to the first piston 9 and to the valve body 7.
  • a leakage line 23 leads out of this valve pressure chamber 21.
  • the sealing element 22 is designed as a bellows-like membrane and prevents the actuator 4 from coming into contact with the fuel contained in the low-pressure region 16.
  • a filling device 24 is provided. This has a channel-like cavity 25, in which a pin-like throttle body 26 is arranged with a gap 27 surrounding it.
  • a system pressure line 28 branches off, which leads to hydraulic chamber 13.
  • the system pressure line 28 opens into a gap 29 surrounding the first piston 9, via which the system pressure is reduced to the valve pressure chamber 21 and thus to the low pressure region 16.
  • system pressure line 28 opens into a gap 30 surrounding the second piston 11, as is indicated in FIG. 1 by the line 28 ⁇ , or that the system pressure line is direct opens into the hydraulic chamber 13.
  • the indirect filling of the hydraulic chamber 13 serves to improve the pressure holding capacity in the hydraulic chamber during the activation.
  • the arrangement shown in FIG. 1 thus represents a series connection of two separate pistons, namely the throttle body 26 and the first piston 9, via which the high pressure p_R is reduced to the low pressure region 16.
  • the high pressure p_R is reduced to the system pressure p_sys via the gap 27 of the throttle body 26 which is arranged essentially axially immovably in the cavity 25.
  • the pressure divider ratio is determined by the ratio of the lengths and diameters of the throttle body 26 and the piston connected downstream 9 set.
  • the setting of the system pressure p_sys by the separate piston-like components allows the length of the throttle body to be dimensioned very small, since the second half of the pressure divider is formed by the piston 9.
  • the short lengths or larger diameters allow a higher quality of the components with a simultaneous reduction in the costs of manufacture and, above all, when adjusting or assembling.
  • the system pressure p_sys which is reached after an injection after a certain refilling time, and the ratio of the diameters and leakage gap lengths on the throttle body 26 and the piston 9 is dependent on several parameters, to which the seat diameter A2 of the first valve seat 14 and the ratio of the diameter Count A0 of the first piston 9 to the diameter AI of the second piston 11.
  • the spring force F_F a further parameter for geometrically determining the throttle body 26 and the first piston 9.
  • the system pressure p_sys is set so that it is always less than a maximum permissible system pressure, which in turn corresponds to a pressure level at which occurs an automatic valve opening without actuation of the actuator unit 4.
  • FIG. 2 shows an embodiment variant of the exemplary embodiment shown in FIG. 1, in which, for reasons of clarity, functionally identical components are identified by the reference numerals used in FIG. 1.
  • the throttle body 26 is arranged essentially axially immovably in the cavity 25 of the filling device 24
  • the throttle body 26 is here arranged axially displaceably in the cavity 25 by means of a spring device 32.
  • the throttle body 26 is displaced in the cavity 25 by the spring force of the spring device 32 when the high-pressure region 17 is relieved to a stop 33 on the high-pressure side.
  • high pressure p_R is applied, the throttle body 26 is displaced against the spring force of the spring device 32 and the system pressure.
  • the spring force and the dimensioning of the throttle body 26 are designed such that the throttle body 26 with its end on the system pressure side, which forms a control edge 34, at least partially overlaps the branching of the system pressure line 28 when the system pressure p_sys drops inadmissibly.
  • the spring device 32 thus allows the system pressure p_sys to be automatically corrected as a function of the leakage via the pistons 9 and 11 as a result of temperature and position influences.
  • the overlap shortens the Control edge 34 with the branching of the system pressure line 28, the effective sealing length or leakage gap length along the throttle body 26, and the leaks are compensated. In this way, the system pressure p_sys in the hydraulic chamber can be kept constant.
  • the axial mobility of the throttle body 26 also advantageously ensures that the gap 27 is cleaned independently and is not clogged by dirt particles contained in the fuel.
  • the line 33 of the filling device 24 branching off from the high-pressure region 17 is connected to the valve chamber 18, in which the valve-closing member 12 can be moved between the valve seats 14 and 15, and which can also be integrated in a high-pressure line.
  • the line 33 leading away from the high-pressure region 17 is connected in terms of flow with a high-pressure inlet from a high-pressure pump to the valve control chamber 2 or with other regions in the high-pressure region 17, for example with the valve control chamber or the outlet throttle 20.
  • the fuel injection valve 1 according to FIGS. 1 and 2 operates in the manner described below.
  • the first piston 9 penetrates into the hydraulic chamber 13 with a temperature increase and withdraws from it when the temperature drops without this having any effect on the closed and open position of the valve closing element 12 and the fuel injector 1 in total.
  • the piezoelectric actuator 4 is acted on by voltage, so that it suddenly expands axially.
  • the piezoelectric actuator 4 is supported on the valve body 7 and builds up an opening pressure in the hydraulic chamber 13.
  • the second piston 11 moves the valve closing member 12 out of its upper valve seat 14 into a central position between the two valve seats 14, 15.
  • the piezo side is reached to achieve the equilibrium pressure a greater force is required. This is applied by the filling device 24 in that the pressure p_sys in the hydraulic chamber 13 is correspondingly increased at a high rail pressure p_R.
  • the piezo-side force on the valve closing member 12 is increased at the same voltage on the piezoelectric actuator 4, the increase in force resulting from the system pressure p_sys and the diameter AI of the second piston 11.
  • This increase in force corresponds to a substantially higher voltage which would have to be applied to the piezoelectric actuator, so that the force reserve obtained can be used, for example, for the smaller dimensioning of the piezoelectric actuator.
  • valve closing member 12 As soon as the valve closing member 12 has reached its lower valve seat 15 against the rail pressure p_R, the covering of the piezoelectric actuator 4 is interrupted, whereupon the valve member 12 moves back to its central position and fuel is injected again. At the same time, the hydraulic chamber 13 is refilled to the system pressure p_sys via the filling device 23.
  • the described embodiments each relate to a so-called double-seat valve, but the invention can of course also be applied to single-switching valves with only one valve seat.

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)
  • Electrically Driven Valve-Operating Means (AREA)

Abstract

La présente invention concerne une vanne de commande de liquides, comprenant une unité d'actionneur (4), qui permet d'actionner un élément de vanne (3) à mobilité axiale. Cet élément de vanne présente un premier piston (9) et un second piston (11), séparé du premier piston par une chambre hydraulique (13), et actionne un élément de fermeture de vanne (12), qui sépare une zone de basse pression (16), à la pression du système, d'une zone de haute pression (17). Afin de compenser les fuites, un dispositif de remplissage (24) pouvant être connecté à la zone de haute pression (17) est pourvu d'une cavité (25) dans laquelle un corps d'étranglement est monté de façon qu'une conduite (33) menant à la zone de haute pression (17) débouche dans la cavité (25), à une extrémité du corps d'étranglement (26), et qu'à l'autre extrémité, une conduite de pression du système (28) menant à la transmission hydraulique bifurque. La définition géométrique du corps d'étranglement (26), d'un espacement l'entourant (27) et des dimensions du piston (9), le long duquel la pression de système est réduite jusqu'à la zone de basse pression (16), permet d'assurer que la pression du système (p_sys) s'élève en fonction de la pression (p_R) dans la zone de haute pression (17).
EP01916927A 2000-04-20 2001-03-20 Vanne de commande de liquides Withdrawn EP1276985A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10019765A DE10019765B4 (de) 2000-04-20 2000-04-20 Ventil zum Steuern von Flüssigkeiten
DE10019765 2000-04-20
PCT/DE2001/001055 WO2001081754A1 (fr) 2000-04-20 2001-03-20 Vanne de commande de liquides

Publications (1)

Publication Number Publication Date
EP1276985A1 true EP1276985A1 (fr) 2003-01-22

Family

ID=7639566

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01916927A Withdrawn EP1276985A1 (fr) 2000-04-20 2001-03-20 Vanne de commande de liquides

Country Status (6)

Country Link
US (1) US6719264B2 (fr)
EP (1) EP1276985A1 (fr)
JP (1) JP2003532002A (fr)
CZ (1) CZ20014487A3 (fr)
DE (1) DE10019765B4 (fr)
WO (1) WO2001081754A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE10043625C2 (de) * 2000-09-05 2003-03-27 Bosch Gmbh Robert Hydraulisch übersetztes Ventil
DE10048933A1 (de) * 2000-10-04 2002-05-02 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10136186A1 (de) * 2001-07-25 2003-02-06 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10148594A1 (de) * 2001-10-02 2003-04-10 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10157419A1 (de) * 2001-11-23 2003-06-12 Bosch Gmbh Robert Leckagereduzierte Druckversorgung für Kraftstoffinjektoren
DE10333690A1 (de) * 2003-07-24 2005-02-17 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333696A1 (de) 2003-07-24 2005-02-24 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333698A1 (de) * 2003-07-24 2005-02-24 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333695A1 (de) * 2003-07-24 2005-03-03 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
CN100432415C (zh) * 2004-07-06 2008-11-12 株式会社电装 共轨喷油器
JP4325589B2 (ja) 2004-07-06 2009-09-02 株式会社デンソー コモンレール用インジェクタ
US7506825B2 (en) * 2006-05-31 2009-03-24 Caterpillar Inc. Fuel injector control system
JP2009287620A (ja) * 2008-05-28 2009-12-10 Ihi Aerospace Engineering Co Ltd バルブ装置
US8500036B2 (en) * 2010-05-07 2013-08-06 Caterpillar Inc. Hydraulically amplified mechanical coupling
DE102010027278B4 (de) * 2010-07-15 2020-07-02 Metismotion Gmbh Thermisch volumenneutraler Hubübertrager sowie Dosierventil mit einem solchen Hubübertrager und Verwendung des Dosierventils

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EP0192241B1 (fr) * 1985-02-19 1988-09-21 Nippondenso Co., Ltd. Soupape de commande pour régler le passage de fluide
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Also Published As

Publication number Publication date
DE10019765A1 (de) 2001-10-31
CZ20014487A3 (cs) 2003-03-12
WO2001081754A1 (fr) 2001-11-01
US6719264B2 (en) 2004-04-13
JP2003532002A (ja) 2003-10-28
DE10019765B4 (de) 2004-12-09
US20020104976A1 (en) 2002-08-08

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