EP1046809A2 - Dispositif de dosage d'un fluide - Google Patents

Dispositif de dosage d'un fluide Download PDF

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Publication number
EP1046809A2
EP1046809A2 EP00107401A EP00107401A EP1046809A2 EP 1046809 A2 EP1046809 A2 EP 1046809A2 EP 00107401 A EP00107401 A EP 00107401A EP 00107401 A EP00107401 A EP 00107401A EP 1046809 A2 EP1046809 A2 EP 1046809A2
Authority
EP
European Patent Office
Prior art keywords
metering device
valve needle
fluid metering
metal bellows
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.)
Granted
Application number
EP00107401A
Other languages
German (de)
English (en)
Other versions
EP1046809A3 (fr
EP1046809B1 (fr
Inventor
Andreas Dr. Kappel
Bernhard Fischer
Bernhard Dr. Gottlieb
Randolf Dr. Mock
Eric Chemisky
Hans Prof. Meixner
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
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP1046809A2 publication Critical patent/EP1046809A2/fr
Publication of EP1046809A3 publication Critical patent/EP1046809A3/fr
Application granted granted Critical
Publication of EP1046809B1 publication Critical patent/EP1046809B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0671—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto
    • 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • 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
    • 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
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for

Definitions

  • the invention relates to a fluid metering device with the a pressurized one in a housing Fluid, either a liquid or a gas, in predetermined Quantities can be dispensed or injected. It is passed through the housing a valve needle, the outside the housing is mechanically operated on the one hand and on the other hand represents an element of a valve.
  • valve needle feedthrough can be similar to diesel injectors also by a clearance fit of the needle in a cylindrical Drill the housing.
  • the disadvantage here is that unavoidable leakage along the needle passage, one Return line in the tank or to the low pressure connection of the Fuel delivery pump required. Due to the higher hydraulic Losses will also affect the overall efficiency of the engine reduced.
  • the object of the invention is a fluid metering device to be designed so that a hermetically sealed Carrying a valve needle through one with one under Pressurized fluid-filled chamber is ensured, whereby a lead-through element to be used is not essential exerts pressure-dependent forces on the valve needle.
  • the invention is based on precise understanding the behavior of a pressurized metal bellows. This is particularly due to the pressure on the metal bellows and related deformations triggered forces that of the metal bellows with two-sided attachment to the outside be transmitted. It is characterized by high pressure differences go out on both sides of the metal bellows, the higher Pressure can be inside or outside the metal bellows.
  • the basic finding is in particular that the wall of the metal bellows even with a low axial spring constant only slight changes in force when pressurized at the ends of a bellows attached on both sides leads.
  • the radial is a particularly advantageous embodiment Fixation of the valve needle through the firm connection of the metal bellows with the valve needle on the one hand and with the housing on the other hand.
  • the insert ensures a compression spring between the housing and valve needle for a reliable closing force that acts on the valve.
  • the valve needle or a a guide for the outer sleeve placed over the metal bellows represent this.
  • the metal bellows can under certain circumstances are concerned with his leadership in some areas. A residual risk of a Buckling is further reduced.
  • the special advantages of the metal bellows are achieved both with internal pressure as well as with external pressure.
  • the dimensioning of the edge thickness of the metal bellows in the area from 25 to 500 ⁇ m shows that small wall thicknesses at large pressures, such as 300 bar, are sufficient.
  • connection points For mounting the valve needle and the metal bellows in the housing, for example in one Injector with several nested Elements, connection points must be freely accessible. This can advantageously be done by welding connections, for example laser welding.
  • the fluid metering device can be designed with valves be that open inwards or outwards.
  • the Construction of the metal bellows in relation to the rest Elements, in particular for the stroke-generating actuator, are corresponding adapt.
  • Electromagnets can be used as actuators. It is advantageous to use piezo actuators, for example are biased in a Bourdon tube.
  • the high pressure injectors considered here are used with fuel pressures PFUEL operated up to 500 bar, for example.
  • a stroke of the valve needle is extremely short and is in the range from 10 to 100 ⁇ m.
  • the housing 1 is divided into the chamber 13, which is connected by means of a line bore 7, via the the fluid is supplied under pressure.
  • Such a fluid metering device or a hydraulic valve for dosing the Fluid therefore separates a high pressure room from a room, which can have, for example, ambient pressure.
  • the implementation the valve needle 3 through the housing 1, in particular through the chamber 13 and the actuator chamber 14 represents the core of the Invention is a metal bellows 17 used.
  • the high-pressure injector shown in FIG. 1 has in the injector housing 1 a valve seat 2.
  • the valve seat 2 is in the Basic state by the second end 23 of the valve needle 3 connected valve plate 4 kept closed.
  • the closed state by the valve seat 2 and the valve plate 4 injector formed by the cocked Compression spring 5 ensures that with the valve needle 3 over a snap ring 6 is connected.
  • the fuel is supplied through the line bore 7 in the housing 1.
  • the drive unit is located in the upper part of the injector housing 1, formed from a piezoelectric multilayer actuator (PMA) 8 in low voltage technology, combined with one Bourdon tube 9, a head plate 10 and a foot plate 11. Die Bourdon tube 9 is with the top plate 10 and the bottom plate 11 welded that the PMA 8 under a mechanical pressure preload stands.
  • PMA piezoelectric multilayer actuator
  • the housing 1 and the base plate 1 are also connected to each other as stiffly as possible via a weld.
  • a gap 12 Between the head plate 10 and the first end 22 of the valve needle 3 there is a gap 12, the height of which is considerable is smaller than the stroke of the PMA 8.
  • the gap 12 serves on the one hand for setting defined force relationships in the valve seat and on the other hand to catch small differences in thermal length changes.
  • the injector components consist of materials with low thermal expansion coefficients or made of different materials with regard to their thermal Coefficients of linear expansion are thus coordinated are that the constancy of the gap height is approximately is guaranteed.
  • the perforated plate 15 To pass the valve needle 3 out of the fuel chamber 13 in the unpressurized actuator space 14 is the perforated plate 15, which is welded to an inner bore 16 of the housing 1. The perforated plate 15 can also be machined out of the housing 1 his. Between the first end 22 of the valve needle 3 and the perforated plate 15 is the cylindrical metal bellows 17th welded on, for hermetic sealing of the fuel chamber 13 compared to the actuator chamber 14 with a large size axial compliance. In the shown in Figure 1 Configuration is the metal bellows 17 by the fuel pressure acted on inside. However, it is also possible that Metal bellows 17 directed downwards between valve needle 3 (no longer at the end of the needle) and the perforated plate 15, whereby this is acted upon by the fuel pressure on the outside would be, as shown in Figure 2.
  • the actuator 8 in in this case a piezo actuator, via the electrical leads 18 charged, whereupon the PMA 8 expands and the valve plate 4 the valve needle 3 lifts off the valve sealing seat 2 and Fluid or fuel emerges from the injection valve.
  • the PMA 8 becomes electrical unload.
  • the PMA 8 contracts again its original length and the valve needle 3 is through the biased strong return spring 5 is moved back so far that the valve plate 4 lies sealingly in the valve seat 2 and the annular injection opening is closed.
  • a metal bellows complies with a suitably selected one Geometry in full all on one bushing or sealing element requirements. These include, that the metal bellows is a perfect, durable and reliable Represents sealing.
  • the metal bellows 17 holds what calculations and tests have shown, despite the thin walls from, for example, 50 to 500 ⁇ m due to its high radial Rigidity was very high without being irreversible to be deformed.
  • the specification of a wall thickness range is to be interpreted so that a metal bellows 17 is not a variable one, but a constant wall thickness for the individual case having.
  • the metal bellows can with a sufficient number the required high axial flexibility of shafts, i.e. a possibly required low axial spring constant exhibit.
  • the diameter of the metal bellows 17 can be adjusted accordingly. This will make of the pressurized fluid with the valve needle 3 Valve plate 4 acting pressure forces and those from the end surface of the metal bellows introduced into the valve needle 3 due to pressure Compensate forces so mutually that no resulting Compression force component acts on the valve needle 3. As a result, such an injector shows a fuel pressure almost completely independent switching behavior, since the piezoelectric actuator is the only one for the opening and closing forces 8 and the force of the prestressed return spring 5 is decisive are.
  • the metal bellows 17 has a wide range due to the metallic material Working temperature range with constant functions. Thermal changes in length of the bellows itself result the low axial spring constant of the metal bellows only negligible changes in force on the valve needle 3 seen in the axial direction.
  • the metal bellows can be due to its mechanical spring action in the axial direction Return spring, the compression spring 5, partially or completely replace.
  • the metal bellows 17 is on both sides fastened with elements to which in the metal bellows by external Transmit forces generated in the axial direction become.
  • a valve needle be designed in such a way that there is a predeterminable balance of forces. This realization could by simulation calculations and by trials be proven.
  • the high-pressure injector according to FIGS. 2 and 3 has the following dimensions, for example:
  • the diameter DN of the valve needle 3 is 3 mm and the diameter DS of the valve seat 2 is 4 mm.
  • the resulting annular differential area AD of 5.5 mm 2 acts on the valve needle 3 with an opening force FU downward in the opening direction of 137.5 N. Since the wall of the metal bellows 17 subjected to external pressure has almost no forces on it Valve needle 3 transmits, the size of the upward compensation pressure forces and thus the upward compensation pressure force FO can be adjusted by the diameter of the metal bellows 17, ie by the diameter DP of the end plate 19, which represents the connection between the metal bellows wall and the valve needle 3.
  • valve seat force is completely independent of pressure and is only determined by the amount of the pre-tensioning force FR set for the return spring.
  • the diameter of the valve needle in the area of the metal bellows can be reduced if necessary.
  • An adaptation of the pressure-effective surfaces is not only limited to cylindrical metal bellows, but can also be done with a corresponding construction in the case of non-cylindrical designs.
  • the metal bellows 17 after the introduction of Valve needle 3 into the housing of the injector subsequently Laser welding 20 on the perforated plate 15 of the valve housing 1 and attached to the valve needle 3.
  • FIG. 3 shows the arrangement complementary to FIG oriented metal bellows 17 cheaper embodiment results from the respective location of the welds, which are preferred for reliability reasons with mechanical compressive stresses should.
  • a certain advantage is in the embodiment according to the figure 2 the shorter length of the by the (compensation force FO) and acting downwards (opening force FU) Compressed forces under load on the area of the valve needle Figure 3 is stretched a little less.
  • the metal bellows 17 in the case of FIGS 3 shows the return spring 5 replace partially or completely. This results in a considerable simplification of construction and cost savings. Is on an additional return spring (compression spring 5) not waived, this can reduce the overall height also housed inside or outside of the metal bellows 17 his.
  • cylindrical metal bellows 17 come other designs, e.g. conical bellows or bellows with cross-sectional geometry deviating from the circular shape in question.
  • FIG. 4 is an injector with an inwardly opening injection nozzle shown. Again, the detail is below Fluid pressure standing chamber 13 shown against the actuator space 14 should be hermetically sealed.
  • the metal bellows 17 is pressurized.
  • the actuator will represented by an electromagnet 21.
  • the storage of the Electromagnet 21 also happens according to FIG. 1 through a base plate 11, the electrical leads 18 are led to the outside. Weldings 20 happen also preferably by laser processing.
  • the Valve needle 3 is in turn in Figure 4 with its second end 23 Part of the shown in connection with the housing Valves and with their first end 22 in turn formed that the coil 21 a stroke movement on the Valve needle 3 can transmit.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
EP00107401A 1999-04-20 2000-04-05 Dispositif de dosage d'un fluide Expired - Lifetime EP1046809B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19917839 1999-04-20
DE19917839 1999-04-20

Publications (3)

Publication Number Publication Date
EP1046809A2 true EP1046809A2 (fr) 2000-10-25
EP1046809A3 EP1046809A3 (fr) 2003-06-18
EP1046809B1 EP1046809B1 (fr) 2005-08-10

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Application Number Title Priority Date Filing Date
EP00107401A Expired - Lifetime EP1046809B1 (fr) 1999-04-20 2000-04-05 Dispositif de dosage d'un fluide

Country Status (3)

Country Link
US (1) US6311950B1 (fr)
EP (1) EP1046809B1 (fr)
DE (1) DE50010902D1 (fr)

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EP2239793A1 (fr) 2009-04-11 2010-10-13 Bayer MaterialScience AG Montage de film polymère électrique commutable et son utilisation
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EP1985388A1 (fr) 2008-08-06 2008-10-29 Witzenmann GmbH Poutre métallique résistant aux hautes pressions et son procédé de fabrication
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EP2568155A1 (fr) * 2011-09-09 2013-03-13 Continental Automotive GmbH Ensemble de soupape et soupape d'injection
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US9574532B2 (en) 2011-09-09 2017-02-21 Continental Automotive Gmbh Valve assembly and injection valve
US9377114B2 (en) 2012-04-25 2016-06-28 Nordson Corporation Pressure control valve for reactive adhesives
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DE102012223212B4 (de) * 2012-12-14 2020-10-01 Robert Bosch Gmbh Aktor zur Betätigung eines Kraftstoffinjektors

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US6311950B1 (en) 2001-11-06
DE50010902D1 (de) 2005-09-15

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