EP1553286B1 - Soupape de dosage avec une unité de compensation de longueur - Google Patents

Soupape de dosage avec une unité de compensation de longueur Download PDF

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Publication number
EP1553286B1
EP1553286B1 EP04106517A EP04106517A EP1553286B1 EP 1553286 B1 EP1553286 B1 EP 1553286B1 EP 04106517 A EP04106517 A EP 04106517A EP 04106517 A EP04106517 A EP 04106517A EP 1553286 B1 EP1553286 B1 EP 1553286B1
Authority
EP
European Patent Office
Prior art keywords
metering valve
valve
unit
fluid
valve according
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.)
Expired - Fee Related
Application number
EP04106517A
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German (de)
English (en)
Other versions
EP1553286A1 (fr
Inventor
Bernhard Gottlieb
Oliver Hennig
Andreas Kappel
Tim Schwebel
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.)
Siemens AG
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Siemens AG
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Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP1553286A1 publication Critical patent/EP1553286A1/fr
Application granted granted Critical
Publication of EP1553286B1 publication Critical patent/EP1553286B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion

Definitions

  • the invention relates to a metering valve with actuator unit, valve unit, fluid supply and length compensation unit.
  • PMA P iezoelektrischen M ultilayer ktors A
  • the coefficient of thermal expansion strongly depends on the polarization state and the mechanical and electrical stress history of the PMA, as well as on the temperature itself in nonlinear dependence, and can have values in the range of -5 ⁇ 10 -6 l / 1 for one and the same PMA. K up to + 7 ⁇ 10 -6 l / K.
  • the hydraulic compensation element consists of an oil-filled hydraulic chamber, which is bounded on the one hand by a cylinder housing and on the other hand by a fitted in the form of a tight clearance hydraulic piston. About the tight clearance and / or a throttle bore, the hydraulic chamber communicates with a storage volume.
  • the storage volume serves on the one hand as a surge tank into which or from the oil flows when the height of the hydraulic chamber changes and on the other hand as a compensator for the thermal volume change of the oil volume itself.
  • the storage space must a previously adjustable basic pressure on the compensation path and the full temperature range as constant as possible hold.
  • the entire oil volume must be hermetically sealed and must not contain any gas bubbles.
  • the compensation path in a hydraulic compensation element is limited, inter alia, by the height of the hydraulic chamber in the axial direction and is in typical applications max. ⁇ 200 ⁇ m.
  • the mechanical rigidity c of the hydraulic chamber drops so sharply that the dynamic properties of the piezo drive are unacceptably impaired. An exact adjustment of a HK is therefore essential.
  • the invention has for its object to provide a length compensation unit with increased compared to the prior art compensation path and much simpler structure.
  • the invention is based on the finding that a friction-based compensation element (FK) can be used as a length compensation element for the integration of maximum functionality under given installation space conditions.
  • FK friction-based compensation element
  • the invention riktionsbasteilettilement (FK) is superior to the known concepts H ydraulic K ompensatoren (HK) in the following properties:
  • the installation space, in particular the length of an actuator, is significantly reduced when using a FK compared to actuator with HK, as the HK must always connect to the actuator in length, while the FK only an additional pipe of small wall thickness is necessary, which is the actuator includes. Therefore, only a small additional space requirement arises in the diameter.
  • the safe return of the metering valve in the closed state or in the idle state by means of a return spring is done by a corresponding force which is introduced into the valve unit.
  • the introduction can be done directly on the valve unit or very beneficial on the FK on the valve unit.
  • the closing force can be applied mechanically or hydraulically (by the FK), with both parts adding up to the closing force.
  • the mechanical portion, which is applied by the return spring, is used to secure closure of the valve in the pressureless state of the injector. Leakage of fluid from the injector can thus be reliably prevented even when parked engine.
  • the formation of a jacket-flow cooling system is particularly advantageous for the uniform formation of the cooling flow and for the complete cooling of the actuator unit.
  • an inert fluid which does not have a corrosive effect, is used. This encloses the actuator and binds this thermally to the outside.
  • a metal bellows serves to separate the area of the valve unit under increased fluid pressure from the area of the actuator unit subjected to lower pressure and as a feedthrough element for the valve needle from the actuator unit to the valve unit. Furthermore, to protect the metal bellows before pressure waves formed between metal bellows and pressurized with fluid pressure region of the valve unit positioned clearance fit.
  • a fluid with dilatant properties can be interposed.
  • the advantages in this case lie in the increase of the compensation path, which is essentially based on the mechanical construction method.
  • the use of a dilatant fluid is associated with other particular advantages.
  • the necessary manufacturing accuracy for the components involved or for the filling with the lubricant make high demands on the production of such a bearing.
  • the design of a friction-based bearing is characterized by small gaps and by lengthy filling with a lubricant and very expensive.
  • a specific solution to the problem involves the use of a dilatant fluid between the corresponding cooperating components of the friction-based compensation element.
  • a dilatant fluid For a dilatant fluid, an increase in shear rate causes the viscosity to increase to solid-like properties.
  • the behavior of a dilatant substance corresponds to the requirements of the FK that slow processes such as the compensation of changes in length or component tolerances occur at a low shear rate.
  • slow processes such as the compensation of changes in length or component tolerances occur at a low shear rate.
  • the friction-based compensation element (FK) described in detail below represents a further development and optimization of the cited prior art with regard to the integration of maximum functionality under given installation space conditions, such as prescribed overall height, outside diameter and simple construction as a modular unit. This can be set up separately, tested and installed.
  • the FK according to the invention is superior to the known concepts of hydraulic compensators (HK) in the following properties:
  • the space, in particular the length of the piezo drive, is significantly reduced when using a FK compared to a piezo drive with HK, since the HK always has to connect in length to the piezo drive, while in FK only an additional tube of small wall thickness, which includes the actuator unit, is required. Therefore, only a small additional space requirement arises in the diameter.
  • the FK only requires a tight cylinder fit.
  • the volume filled with a high-viscosity oil need not be filled free of gas bubbles.
  • An air inclusion serves just to absorb the thermal expansion of the oil volume.
  • the valve unit consists of a valve needle 1, whose lower end is formed according to the orientation in the figures in the form of a valve plate 2 and from a cartridge / sleeve 3, in the lower end of a valve seat 4 is ground, which together with the valve plate 2, a cone jet valve forms, wherein the jet cone angle of the exiting fuel by the geometric configuration of the valve plate 2 and the valve seat 4 are set.
  • the valve needle 1 is axially guided in the sleeve 3 by two very tight clearance fits 5.6.
  • the cross section of the valve needle 1 in the region of the lower fitting 5 has an or a plurality of flats, so that the fuel in the space between the valve needle and sleeve inner wall of the at least one inlet bore 7 during the injection process can flow freely to the open cone jet valve.
  • a metal bellows 8 is hermetically sealed at its lower end with the valve needle 1 and at its upper end hermetically sealed to the valve body 9 by welding.
  • BalganBankInstitutes causes the high-pressure fuel from the outside acts on the bellows.
  • the installation of metal bellows under external pressure loading is recommended by the bellows manufacturers as the more stable variant.
  • the metal bellows 8 serves as a high pressure resistant hermetically sealed, but axially soft feedthrough element that does not hinder the required movement of the valve needle 1 for fast opening and closing of the cone jet valve.
  • d 1 and d 2 an opening, closing or vanishing pressure-dependent force on the valve needle.
  • a path-independent closing force F R is introduced into the valve needle.
  • the valve body 9 is connected to the sleeve 3 hermetically sealed and pressure-stable, preferably by welding.
  • the valve unit is mountable as a separate unit up to the state described so far and can be tested in its function by means of suitable devices, e.g. on tightness of the welds, tightness of the cone jet valve, training and properties of the cone jet, which saves costs, as defective valve groups can be immediately discarded and errors are not detected on a complete injector, whereby the entire injector would have to be discarded.
  • suitable devices e.g. on tightness of the welds, tightness of the cone jet valve, training and properties of the cone jet, which saves costs, as defective valve groups can be immediately discarded and errors are not detected on a complete injector, whereby the entire injector would have to be discarded.
  • the actuator unit consists of the piezoelectric multilayer actuator, PMA 12, which is welded under pressure bias between a bottom plate 13 and a top plate 14 in a tube spring 15.
  • the compressive prestressing protects the PMA from damaging tensile stresses in highly dynamic operation.
  • the piezoceramic behaves stable against compressive stresses, tensile stresses, however, can lead to the destruction of the piezoceramic.
  • the effect of the gap suspension between the end faces of the PMA and the corresponding mating surfaces of the top plate 14 and bottom plate 13 is avoided by applying a strong compressive bias, typically from about 500 N - 1000 N, which leads to a soft, mechanical coupling of the top plate 14 and bottom plate 13 leads and therefore be the cause of losses in the deflection of the actuator can.
  • a strong compressive bias typically from about 500 N - 1000 N
  • causes of the occurrence of gap suspension are geometric deviations from the ideal plane-parallel geometry of the PMA end faces.
  • the faces are typically made with a tolerance in the parallelism of about ⁇ 50 ⁇ m.
  • planar faces are formed spherical. Without or with only low compressive bias is only a fraction of the PMA end face on investment with the corresponding mating surface on the top or bottom plate and causes a mechanically soft coupling. A sufficiently high compressive force causes by elastic deformation, the closing of the column and thus a full-scale contact of the end faces of the corresponding mating surfaces and thus a mechanically rigid coupling.
  • the head plate 14 also contains holes 16 through which the electrical connections 17 of the PMA are led out centrally from the actuator unit.
  • the actuator unit can also be electrically and mechanically tested as a separate module before it is installed in an injector.
  • the length compensator is in a preferred embodiment for use in the described metering valve of two concentric tubes, the inner tube 18 and the outer tube 19, wherein the outer diameter of the inner tube 18 is only slightly smaller than the inner diameter of the outer tube 19, so that both tubes a tight clearance fit form.
  • a typical diameter difference is approx. 5 ⁇ m - 20 ⁇ m.
  • the inner tube 18 is rigidly connected to the top plate 14 of the actuator unit 32, for example, welded.
  • the outer tube 19 is connected at its lower end to the valve group rigid and high pressure tight.
  • the bottom plate 13 is rigidly connected to the upper end of the valve needle 1.
  • the interior space inside the outer tube 19 is largely filled with dilatant fluid to ensure the permanent filling of the gap between the inner tube 18 and the outer tube 19. Furthermore, the filling serves at the same time for optimum loss heat dissipation from the PMA to the outer tube 19.
  • the fuel supply consists of an inlet connector / inlet fitting 26 with an inlet opening 20, into which the fuel is fed from the high-pressure pump via a fuel line.
  • the inlet opening opens into an annular groove 21, through which the fuel is distributed uniformly over the circumference.
  • For fuel supply is the further a jacket tube 22.
  • the cylindrical annular gap between the outer tube 19 and the jacket tube 22 serves as a fuel line from the inlet fitting 26 to the valve group.
  • the inlet fitting (26) is high pressure resistant and hermetically sealed to the upper end of the outer tube and the jacket tube.
  • the lower end of the jacket tube is high pressure resistant and hermetically sealed to the sleeve 3.
  • This type of concentric fuel delivery allows for optimum loss heat removal from the PMA via the inner tube 18, the silicone oil and the outer tube 19 to the fuel.
  • the elasticity of the outer and jacket tube is an efficient, injector-internal pressure accumulator, which optimally damps the pressure waves caused by the rapid opening and closing of the cone jet valve.
  • the inlet fitting 26 may include a device for mechanical injector calibration, consisting of a hollow screw 23, and a soft spring 24, which is supported at the top of the hollow screw and the bottom of the actuator unit.
  • a device for mechanical injector calibration consisting of a hollow screw 23, and a soft spring 24, which is supported at the top of the hollow screw and the bottom of the actuator unit.
  • the function of the FK is based on the fact that it allows the coupling by viscous friction, briefly high forces at high transfer mechanical rigidity, wherein during the period of the force effect compared to the Aktorausschung only a negligible relative displacement between the tubes occurs.
  • the mechanical stiffness of the FK is determined by the mechanical stiffnesses of the two tubes. Very slow Relativverschiebungen between the tubes take place virtually free of forces. Therefore, the FK for use in short-term operating switching valves or periodically operating switching valves can be used, the phase of the power transmission compared to the Aktorausschung only leads to a negligible relative displacement between the tubes in the FK.
  • the PMA (12) is charged via the electrical connections (17), the PMA is extended and opens the cone jet valve, the closing force being taken over by the PMA.
  • the actuator unit is supported by the inner tube and the viscous friction on the outer tube.
  • the closing force via the viscous friction, causes the actuator unit to be pushed upwards at a constant speed relative to the outer tube during the opening period.
  • fuel in the form of a cone jet enters the combustion chamber through the opened cone jet valve.
  • the PMA is discharged again via the electrical connections 17, whereby the PMA is contracted again to the original length and the cone jet valve is closed by the closing force.
  • the return spring 10 supports the closing operation.
  • a dynamic equilibrium is established such that the drift of the inner tube 18 upwards, which occurs during the injection process, is reset during the rest phase of the injector.
  • This equilibrium position depends on the tactile rate, ie. H. from the ratio of the injection time to the period. Since the injection time for injectors for internal combustion engines is substantially less than the period, the dynamic equilibrium position of the FK corresponds almost to its rest position with arbitrarily long period duration. Therefore, the dynamic duty cycle effect is negligible for practical applications.
  • the application of the FK is not limited to piezoelectric drives. It is also advantageous for all types of solid state actuators such. B. in magnetostrictive or electrostrictive actuators.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (12)

  1. Soupape de dosage avec unité de compensation de longueur, composée
    - d'un boîtier,
    - d'une unité de soupape (30) pour le dosage d'un fluide grâce à une course d'une aiguille de soupape (1),
    - d'une conduite d'amenée (31) d'un fluide sous pression,
    - d'une unité d'actionneur (32) pour créer une course de soupape,
    - d'une unité de compensation de longueur intercalée dans le flux de force entre l'unité d'actionneur (32) et le boîtier de la soupape de dosage,
    caractérisée en ce que l'unité de compensation de longueur est réalisée par un élément de compensation à base de friction (33) composé d'au moins deux tubes (18, 19) disposés parallèlement à l'unité d'actionneur (32) et entourant celle-ci, à savoir d'un tube interne (18) et d'un tube externe (19), ces tubes étant guidés l'un dans l'autre à l'aide d'un ajustement à jeu, un fluide ayant des propriétés de dilatation étant présent entre les tubes, la viscosité de ce fluide augmentant avec un degré croissant de cisaillement, de sorte que l'unité de compensation de longueur se comporte comme un palier rigide lors de mouvements relatifs rapides.
  2. Soupape de dosage selon la revendication 1, dans laquelle un ressort de rappel (10) précontraint est prévu pour pousser l'aiguille de soupape (1) en direction de fermeture.
  3. Soupape de dosage selon la revendication 2, dans laquelle le ressort de rappel (10) s'appuyant sur le boîtier s'engage de l'autre côté sur une tête de soupape (11) qui est directement reliée à l'aiguille de soupape (1).
  4. Soupape de dosage selon la revendication 1, dans laquelle le ressort de rappel (10) s'appuyant sur le boîtier s'engage de l'autre côté sur le tube interne (18).
  5. Soupape de dosage selon l'une des revendications précédentes, dans laquelle des connecteurs électriques (17) de l'unité d'actionneur (32) peuvent passer à l'extérieur à travers l'ouverture frontale du tube interne (18).
  6. Soupape de dosage selon l'une des revendications 1 à 5, dans laquelle un fluide à haute viscosité ayant une viscosité d'au moins 200 Ns/m2 est présent.
  7. Soupape de dosage selon l'une des revendications 1 à 5, dans laquelle une huile de silicone est employée comme fluide à haute viscosité.
  8. Soupape de dosage selon l'une des revendications précédentes, dans laquelle l'amenée de fluide (31) allant en direction axiale dans la partie radialement externe de la soupape de dosage est uniformément distribuée sur la périphérie et forme un refroidissement par flux double.
  9. Soupape de dosage selon l'une des revendications précédentes, dans laquelle l'unité d'actionneur (32) contient un fluide inerte pour la dissipation de la chaleur.
  10. Soupape de dosage selon l'une des revendications précédentes, dans laquelle un soufflet métallique (8) est prévu qui sépare la partie (30) de l'unité de soupape chargée d'une pression de fluide élevée de la partie (32) de l'unité d'actionneur chargée d'une pression moins élevée et sert d'élément de traversée de l'aiguille de soupape (1) depuis l'unité d'actionneur (32) vers l'unité de soupape (30).
  11. Soupape de dosage selon l'une des revendications précédentes, dans laquelle un ajustement à jeu (6) est positionné entre le soufflet métallique (8) et la partie de l'unité de soupape (30) chargée de la pression de fluide, afin de protéger le soufflet métallique (8).
  12. Soupape de dosage selon l'une des revendications précédentes, dans laquelle l'APM (12) peut être commandé par une tension de polarisation négative afin d'élargir la course de l'unité d'actionneur (32).
EP04106517A 2004-01-09 2004-12-13 Soupape de dosage avec une unité de compensation de longueur Expired - Fee Related EP1553286B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200410001505 DE102004001505B4 (de) 2004-01-09 2004-01-09 Dosierventil mit Längenkompensationseinheit
DE102004001505 2004-01-09

Publications (2)

Publication Number Publication Date
EP1553286A1 EP1553286A1 (fr) 2005-07-13
EP1553286B1 true EP1553286B1 (fr) 2007-10-31

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EP04106517A Expired - Fee Related EP1553286B1 (fr) 2004-01-09 2004-12-13 Soupape de dosage avec une unité de compensation de longueur

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Country Link
EP (1) EP1553286B1 (fr)
DE (2) DE102004001505B4 (fr)

Families Citing this family (8)

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Publication number Priority date Publication date Assignee Title
WO2006003042A1 (fr) 2004-07-07 2006-01-12 Siemens Aktiengesellschaft Frein de stationnement electronique et procede de commande d'un frein de ce type
DE102005036826B4 (de) * 2005-08-04 2007-04-26 Siemens Ag Kraftstoffinjektor zur Ermittlung des Brennraumdrucks in einer Brennkraftmaschine
DE102005037419A1 (de) * 2005-08-08 2007-02-22 Siemens Ag Injektor zur Direktinjektion von brennbaren Fluiden
DE602006021529D1 (de) * 2006-02-03 2011-06-09 Continental Automotive Gmbh Aktoreinheit für ein Einspritzventil und Einspritzventil
DE102011102170B4 (de) 2011-05-20 2024-06-06 Vitesco Technologies GmbH Einspritzvorrichtung zur Einspritzung eines Fluids
DE102019121679A1 (de) * 2019-08-12 2021-02-18 Vermes Microdispensing GmbH Dosiersystem mit justierbarem Aktor
DE102020120439A1 (de) 2020-08-03 2022-02-03 Focke & Co. (Gmbh & Co. Kg) Ventil für fließfähige Medien
BE1030754B1 (nl) * 2023-01-31 2024-02-27 Tatjana Yazgheche Hulpstukken bij het samenstellen van een doseerventiel

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Publication number Priority date Publication date Assignee Title
DE3614564A1 (de) * 1986-04-29 1987-11-05 Daimler Benz Ag Einspritzduese zur kraftstoffeinspritzung in den brennraum einer luftverdichtenden einspritzbrennkraftmaschine
DE19905340C2 (de) * 1999-02-09 2001-09-13 Siemens Ag Verfahren und Anordnung zur Voreinstellung und dynamischen Nachführung piezoelektrischer Aktoren
DE19940055C1 (de) * 1999-08-24 2001-04-05 Siemens Ag Dosierventil
US6584958B2 (en) * 1999-10-15 2003-07-01 Westport Research Inc. Directly actuated injection valve with a ferromagnetic needle
DE10035168A1 (de) * 2000-07-19 2002-02-07 Siemens Ag Stellantrieb, Ventil sowie Verfahren zum Herstellen eines Stellantriebs
DE10039424A1 (de) * 2000-08-11 2002-02-28 Siemens Ag Dosierventil mit einem hydraulischen Übertragungselement
EP1381772B1 (fr) * 2000-11-13 2004-08-11 Siemens VDO Automotive Corporation Compensateur magnetique-hydraulique pour injecteur de carburant
JP4288182B2 (ja) * 2002-04-22 2009-07-01 シーメンス アクチエンゲゼルシヤフト 流体のための調量装置、特に自動車用噴射弁
DE112004000221D2 (de) * 2003-03-26 2006-02-16 Siemens Ag Dosierventil mit Längenkompensationseinheit

Non-Patent Citations (1)

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Title
None *

Also Published As

Publication number Publication date
EP1553286A1 (fr) 2005-07-13
DE102004001505B4 (de) 2005-11-10
DE502004005355D1 (de) 2007-12-13
DE102004001505A1 (de) 2005-08-04

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