EP1360407A2 - Soupape de regulation de liquides - Google Patents

Soupape de regulation de liquides

Info

Publication number
EP1360407A2
EP1360407A2 EP02712735A EP02712735A EP1360407A2 EP 1360407 A2 EP1360407 A2 EP 1360407A2 EP 02712735 A EP02712735 A EP 02712735A EP 02712735 A EP02712735 A EP 02712735A EP 1360407 A2 EP1360407 A2 EP 1360407A2
Authority
EP
European Patent Office
Prior art keywords
valve
closing member
piston
valve closing
filling device
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Withdrawn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
EP02712735A
Other languages
German (de)
English (en)
Inventor
Wolfgang Stoecklein
Dietmar Schmieder
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 EP1360407A2 publication Critical patent/EP1360407A2/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Withdrawn legal-status Critical Current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
    • 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
    • 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
    • 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 the preamble of claim 1.
  • Valves for controlling liquids of the type mentioned at the outset are known from practice and are used, for example, in a fuel injection valve, in particular a common rail injector, in an internal combustion engine of a motor vehicle.
  • Such a valve is described for example in the • EP 0477400 Al.
  • This valve has a piezoelectric actuator for actuation.
  • the valve has a hydraulic chamber which acts as a hydraulic ratio or coupling and tolerance compensation element. ment works.
  • the hydraulic chamber encloses a common compensation volume between two pistons delimiting it, one piston of which has a smaller diameter and is connected to the valve-closing element to be controlled and the other piston has a larger diameter and is connected to the piezoelectric actuator.
  • the piston of smaller diameter makes a stroke increased by the ratio of the piston diameters when the piston of larger diameter, the so-called actuating piston, experiences a certain deflection by means of the piezoelectric actuator.
  • tolerances based on temperature gradients or different coefficients of thermal expansion of the materials used, as well as any setting effects can be compensated for by means of a compensation volume of the hydraulic chamber without the position of the valve closing element to be controlled being changed.
  • the fluid pressure in the hydraulic coupler always drops when the valve is operated due to leakage. For this reason, it is necessary to constantly refill the hydraulic coupler with appropriate amounts of hydraulic fluid.
  • the coupler In the case of an injection valve, the coupler is usually refilled with fluid which is fed to the injection valve under high pressure and on the one hand represents the fluid to be injected into the internal combustion engine by means of the injection valve and on the other hand serves to control the injection valve.
  • the fluid is tapped via a leakage point, which, for example, in order to avoid high pressure in the coupler, has a small hydraulic cross-section, ie a throttle point.
  • valve according to the invention with the features according to the preamble of claim 1, in which the valve closing member has a piston-like, cylinder-shaped area, which forms at least one filter gap for the fluid to be supplied with the valve body and in the height of which a feed channel of the filling device branches, in contrast, has the advantage that the risk of clogging a throttle point of the filling device, for example a throttle pin or a throttle bore, is low, since the valve closing member in combination with the valve body forms a dirt filter for the fluid flowing through the throttle point to fill the hydraulic coupler.
  • the valve according to the invention has the advantage that the dirt filter formed from the valve body and valve closing member is a more or less self-cleaning dirt filter, since contaminants that may accumulate in the area of the filter gap dissolve again due to the movement of the valve closing member.
  • the invention is easy to implement in that the filter gap is realized by tightly guiding the piston-like valve closing member on the valve body, for example in an essentially correspondingly designed bore thereof.
  • the supply duct branches off downstream of at least one filter gap. Otherwise a sufficient filter effect could not be achieved.
  • the piston-like region of the valve closing element is guided on at least one annular valve body projection which surrounds the valve closing element and which forms the filter gap with the piston-like region of the valve closing element.
  • the feed channel of the filling device can branch off from an annular space surrounding the piston-like area of the valve closing member. This annular space is then expediently downstream of the filter gap.
  • the valve preferably has a control channel which establishes a connection between a space which is formed on the side of the valve closing member facing away from the actuating piston and the control space.
  • the control chamber is arranged, for example so 'as to surround the area of the valve closing member, the SST and the cooperating with the valve seat valve ch dividedbau UMF.
  • a throttle can advantageously be formed in the control channel.
  • this throttle should have a larger cross section than the upstream discharge throttle. Because of the throttle arranged in the control channel, forces then arise on the valve closing element which cause the valve closing element to close quickly. This in turn ensures small and stable injection quantities with an injection valve.
  • the control channel can either be formed in the valve closing member or, at the discretion of the person skilled in the art, also in the valve body.
  • the valve closing member is formed at least in two parts.
  • the valve closing member comprises a substantially hemispherical component which interacts with the valve seat, and an essentially cylindrical component which is guided on the valve body and forms the filter gap with it.
  • DIE se embodiment allows greater tolerances in the manufacture of the valve body, because when the semi-spherical member and the cylindrically shaped component 'radially relative to one another. ⁇ are formed, the guide for the cylindrical component does not have to be formed concentrically with the valve seat.
  • the setting of a stroke of the valve closing element when the actuating piston is actuated can be carried out by means of a stroke setting element, which is preferably disc-shaped and is arranged on the free end face of the valve closing element.
  • FIG. 1 shows a partial schematic illustration of an injection valve for injecting fuel into an internal combustion engine in a longitudinal section
  • FIG. 2 shows a schematic representation of a second embodiment of an injection valve in a representation corresponding to FIG. 1; and FIG. 3 shows a third embodiment of an injection valve, likewise in a representation corresponding to FIG. 1.
  • FIG. 1 shows a fuel injection valve 1 which is provided for installation in an internal combustion engine of a motor vehicle which is known per se and is designed here as a common rail injector for injecting preferably diesel fuel.
  • the fuel injection valve 1 comprises, as essential structural units, a valve control module 2 and a nozzle module 3.
  • the nozzle module 3 comprises a valve control piston 4, which is arranged in a nozzle body 5 and is in operative connection with a nozzle needle, not shown, which controls an opening of the fuel injection valve 1 leading to a combustion chamber of the internal combustion engine, or forms a structural unit with the latter.
  • valve control chamber 6 borders on the free end face of the valve control piston 4 shown in FIG. 1.
  • the position of the valve control piston 4 and thus that of the nozzle needle is set via the pressure level prevailing in the valve control chamber 6.
  • the valve control chamber 6 is connected via an inlet throttle 7 to a fuel supply area 8, which contains fuel intended for injection, and via an outlet throttle 9 to the valve control module 2.
  • the high-pressure supply area 8 is connected to a high-pressure accumulator, not shown here, which is common to several injection valves, a so-called common rail.
  • the fuel contained in the high-pressure supply area 8 can thus be under a pressure of, for example, up to 1.5 kbar.
  • an injection time and an injection quantity of the injection valve 1 includes the valve control module 2 with ⁇ a valve body 22, chem in WEL 5 is a valve member 10 is guided, the piezoelectric means of a not shown actuator unit of conventional design is operable.
  • the actuator unit is arranged on that side of the valve member 10 10 which faces away from the valve control piston 4 and thus the combustion chamber of the internal combustion engine.
  • the piezoelectric actuator acts on a first piston 11, which is assigned to the valve member 10 and forms the so-called control piston.
  • the actuating piston 11 is operatively connected to a second piston 13, the so-called actuating piston, via a hydraulic coupler 12.
  • the hydraulic coupler 12 is designed as a hydraulic chamber and transmits the axial deflection of the actuating piston moved by means of the piezoelectric actuator unit
  • the hydraulic transmission causes the actuating piston 13 to make a stroke which is increased by the transmission ratio of the piston diameters when the actuating piston 11, which is in the present case
  • the actuating piston 13 is used to actuate a valve 10 closing member 14, which cooperates with a valve seat 15, which is designed here as a ball seat.
  • the valve- Closing member 14 has on its side facing the actuating piston 13 a substantially hemispherical region 16 which interacts with the correspondingly shaped valve seat 15.
  • the hemispherical region 16 is adjoined in the direction of the valve control piston 4 by an essentially piston-like, cylindrical region 17, which in turn is adjoined by an adjusting disc 18 for limiting the stroke of the valve closing member 14.
  • valve closing element 14 In the area of the hemispherical area 16 of the valve closing element 14, the same is surrounded by a control chamber 19, which is separated from a so-called drainage space 20 in the blocking position of the valve closing element 14.
  • a return channel branches off from the L5 drainage space 20 and leads to a leakage connection of the injection valve 1, which is connected to a fuel storage tank, also not shown here.
  • valve closing member 14 in particular the cylindrical one
  • Area 17 of the valve closing member 14 is guided in a bore 21 of the valve body 22.
  • two annular, rib-like projections 23 and 24 are formed, which form the guide for the valve closing member 25 14 and each represent a filter gap with the same.
  • the cylindrical region 17 of the valve closing member 14 is guided so closely to the projections 23 and 24 that only a very narrow annular gap remains between the valve closing member 14 and the projection 23 and 24, one
  • a channel 26 branches off for filling the hydraulic chamber 12 with hydraulic fluid.
  • the channel 26 leads to a throttle pin 28 arranged in a bore 27 of the valve body 22, downstream of which a channel system 33 leads to the actuating piston 11, so that hydraulic fluid can be guided into the hydraulic chamber 12 via the annular gap delimiting the actuating piston 11.
  • the channel system 33 is also equipped with a pressure relief valve 29, so that the pressure set by means of this valve 29 is always present in the hydraulic chamber 12.
  • the valve closing member 14 also has a blind hole-like bore 30 which is introduced into the valve closing member 14 from the side facing the outlet throttle 9.
  • the bore 30 is aligned axially.
  • a channel 31 designed as a throttle branches off from the bore 30 and leads to the control chamber 19. Via the bore 30 and the throttle 31, which together form a so-called control channel, the control quantity required for actuating the injection valve 1 is guided from a space 32 downstream of the outlet throttle 9 into the control space 19.
  • the diameter of the throttle 31 is very much larger than that of the outlet throttle 9 connected upstream thereof.
  • the fuel injection valve 1 according to FIG. 1 operates in the manner described below.
  • valve closing member 14 In the closed state of the fuel injection valve 1, i.e. when there is no voltage on the piezoelectric actuator unit, the valve closing member 14 is located, i.e. whose hemispherical region 16 is formed on the valve seat 15 assigned to it. The valve closing member 14 is thus in the blocking position.
  • the actuating piston 11 is retracted in the direction of the actuator unit, as a result of which the pressure prevailing in the hydraulic chamber 12 is reduced and the valve closing member 14 and thus the actuating piston 13 likewise in the direction of the piezoelectric actuator unit are moved until the valve closing member 14 comes to rest in the valve seat 15. Then the rail pressure prevailing in the high-pressure supply region 8 can build up again in the valve control chamber 6. This is done via the inlet throttle 7. As a result, the valve control piston 4 is moved back into its closed position.
  • the filter gaps are also cleaned here during the closing movement of the valve closing member 14.
  • FIG. 2 differs from that of Figure 1 in that the valve closing member 14 is not constructed in one piece, but in several parts. For reasons of clarity, functionally the same Components the same reference numerals as used in Figure 1.
  • the valve closing member 14 consists of a substantially hemispherical component 42, to which a
  • Disc 43 connects a substantially cylindrical, bolt-like area 41.
  • a channel 44 is formed, which is arranged axially and in which a throttle 45 is formed.
  • the channel 44 ends in the area of the disk 43 and establishes a connection between a space 32 delimiting the valve closing member 14 on its free end face and the control space 19. Otherwise, the effect of the cylindrical region 41 corresponds to that of the valve closing element according to FIG. 1.
  • the valve closing member 14 thus has in connection with the projections 23 and 24 a filtering action for the fuel which is used for filling the hydraulic chamber 12 and via the channel 26 and from the throttle pin
  • the exemplary embodiment according to FIG. 3 differs from those according to FIGS. 1 and 2 in that here the valve closing member 14, which consists of a hemispherical region 52 and a cylindrical region 51, is formed in one piece and solidly. On the free end face adjoins the valve closing member 14, an adjusting disk 18 for adjusting the stroke of the valve closing member 14.
  • the injector 50 further includes a space 53 essentially adjoining the adjusting disk 18, into which fuel is fed via the outlet throttle 9, and from which a control duct 54 branches off, which leads to the control space 19.
  • a throttle 55 is arranged in the control channel 54.
  • the control channel 54 and the throttle 55 are formed in the valve body 22.
  • the mode of operation of the throttle 55 essentially corresponds to that of the throttle 31 of the injection valve shown in FIG. 1.

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

L'invention concerne une soupape de régulation de liquides, comportant une unité actionneur piézo-électrique pour actionner un élément de soupape (10) disposé dans un corps de soupape (22) composé d'au moins une partie. Cet élément de soupape comprend au moins un piston de réglage (11) en liaison avec l'unité actionneur et au moins un piston de commande (13) en liaison active avec le piston de réglage (11) par l'intermédiaire d'un coupleur hydraulique (12). Ce piston de commande est relié à un élément de fermeture de soupape (14), qui coopère avec au moins un siège de soupape (15) et qui, en position de fermeture, sépare l'espace de commande (19) de l'espace d'évacuation (20), le coupleur hydraulique (12) étant pourvu d'un dispositif de remplissage. L'élément de fermeture de soupape (14) comporte une zone (17; 41; 51) cylindrique ayant la forme d'un piston, cette zone constituant avec le corps de soupape (22) au moins un interstice de filtre pour le fluide s'écoulant dans le dispositif de remplissage, à la hauteur duquel débouche un canal d'alimentation (26) du dispositif de remplissage.
EP02712735A 2001-02-02 2002-02-01 Soupape de regulation de liquides Withdrawn EP1360407A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10104618 2001-02-02
DE10104618A DE10104618A1 (de) 2001-02-02 2001-02-02 Ventil zum Steuern von Flüssigkeiten
PCT/DE2002/000369 WO2002061266A2 (fr) 2001-02-02 2002-02-01 Soupape de regulation de liquides

Publications (1)

Publication Number Publication Date
EP1360407A2 true EP1360407A2 (fr) 2003-11-12

Family

ID=7672555

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02712735A Withdrawn EP1360407A2 (fr) 2001-02-02 2002-02-01 Soupape de regulation de liquides

Country Status (5)

Country Link
US (1) US6811134B2 (fr)
EP (1) EP1360407A2 (fr)
JP (1) JP2004518064A (fr)
DE (1) DE10104618A1 (fr)
WO (1) WO2002061266A2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005059169A1 (de) * 2005-12-12 2007-06-14 Robert Bosch Gmbh Kraftstoffinjektor mit direkt betätigbarem Einspritzventilglied
DE102006027485A1 (de) * 2006-06-14 2007-12-20 Robert Bosch Gmbh Kraftstoffeinspritzventil mit Sicherheitssteuerventil
DE102009000181A1 (de) * 2009-01-13 2010-07-15 Robert Bosch Gmbh Kraftstoff-Injektor
DE102017207208A1 (de) * 2017-04-28 2018-10-31 Robert Bosch Gmbh Ventil zum Einstellen eines Fluidstroms

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59010904D1 (de) 1990-09-25 2000-05-31 Siemens Ag Anordnung für einen in Hubrichtung wirkenden adaptiven, mechanischen Toleranzausgleich für den Wegtransformator eines piezoelektrischen Aktors
US5779149A (en) * 1996-07-02 1998-07-14 Siemens Automotive Corporation Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke
DE19954288A1 (de) * 1999-11-11 2001-05-17 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
US6616064B2 (en) * 2000-06-29 2003-09-09 Robert Bosch Gmbh Injector with a control face on the outlet side

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO02061266A2 *

Also Published As

Publication number Publication date
JP2004518064A (ja) 2004-06-17
US20030155540A1 (en) 2003-08-21
WO2002061266A2 (fr) 2002-08-08
DE10104618A1 (de) 2002-08-08
US6811134B2 (en) 2004-11-02
WO2002061266A3 (fr) 2002-10-03

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