EP1046809B1 - Fluid metering device - Google Patents

Fluid metering device Download PDF

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Publication number
EP1046809B1
EP1046809B1 EP00107401A EP00107401A EP1046809B1 EP 1046809 B1 EP1046809 B1 EP 1046809B1 EP 00107401 A EP00107401 A EP 00107401A EP 00107401 A EP00107401 A EP 00107401A EP 1046809 B1 EP1046809 B1 EP 1046809B1
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EP
European Patent Office
Prior art keywords
valve needle
metal bellows
fluid metering
pressure
valve
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
EP00107401A
Other languages
German (de)
French (fr)
Other versions
EP1046809A3 (en
EP1046809A2 (en
Inventor
Eric Chemisky
Bernhard Fischer
Bernhard Dr. Gottlieb
Andreas Dr. Kappel
Hans Prof. Meixner
Randolf Dr. Mock
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Siemens AG
Original Assignee
Siemens AG
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Filing date
Publication date
Priority to DE19917839 priority Critical
Priority to DE19917839 priority
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP1046809A2 publication Critical patent/EP1046809A2/en
Publication of EP1046809A3 publication Critical patent/EP1046809A3/en
Application granted granted Critical
Publication of EP1046809B1 publication Critical patent/EP1046809B1/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664Injectors 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
    • F02M51/0671Injectors 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603Injectors peculiar thereto with means directly operating the valve needle using piezo-electric or magnetostrictive operating means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08Fuel-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167Means for compensating clearance or thermal expansion
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0057Means for avoiding fuel contact with valve actuator, e.g. isolating actuators by using bellows or diaphragms
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/16Sealing of fuel injection apparatus not otherwise provided for

Description

The invention relates to a Fluiddosiervorrichtung with the an in-housing, pressurized 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 of the housing is mechanically operated on the one hand and on the other hand represents an element of a valve.

In the prior art are various sealing or Implementation elements known. For the application of the dosage of pressurized fuels with a Pressure up to, for example, 300 bar and a working temperature range from -40 ° C to +150 ° C, however, special requirements placed on a product suitable for serial production. Generally requirements for embrittlement, the Wear and reliability are met.

The fatigue life of previously used O-ring seals does not meet the above requirements. Instead of O-rings and membrane seals such as metal beads o. Ä. Can be used. However, these have the disadvantage of a very high pressure-loaded surface, which has a corresponding force introduction into the valve needle result. If a pressure area of 1 mm 2 is considered at a one-sided overpressure of, for example, 300 bar, then a force of 30 N results. The use of diaphragms as lead-through element of a valve needle by a pressurized chamber can therefore meet the requirements for high axial compliance at the same time do not satisfy sufficient compressive strength. A high compressive strength inevitably leads to a correspondingly dimensioned membrane thickness, which in turn requires a high axial rigidity. Due to the large membrane area and thereby also acting on the valve needle very high pressure forces no pressure-independent function of a fluid metering is possible. However, this is necessary for example for an engine start or for specific map areas. A compensation of the pressure forces when using a membrane, for example by a mechanical spring, is therefore possible at the pronounced pressure dependence of the forces acting on the valve needle forces at best in a single operating point.

The valve needle feedthrough can be similar to diesel injectors also by a clearance of the needle in a cylindrical Housing bore done. The disadvantage here is the unavoidable leakage, along the needle feedthrough, the one Return line into the tank or to the low pressure connection of the Fuel pump required. Due to the higher hydraulic Losses will also increase the overall efficiency of the engine reduced.

A fluid metering device with a metal bag as leadthrough element is known for example from the publications JP 07 158534 A, DE 591 559 A and DE 41 41 274 A.

The object of the invention is a fluid metering device to make such that a hermetically sealed Carrying out a valve needle by one with a lower Pressure-filled fluid-filled chamber is ensured, wherein a feedthrough element to be used is not essential exerts pressure-dependent forces on the valve needle.

The solution of this task is done by the feature combination of claim 1.

By using a metal bellows as a lead-through element for a valve needle through a chamber containing the dosing Containing fluid, many existing problems can be solved. The invention is based on the exact understanding the behavior of a pressurized metal bellows. In this case, in particular by the pressure on the metal bellows and related deformations triggered forces, the metal bellows on the two-sided attachment to the outside be transmitted. It is on by high pressure differences Both sides of the metal bladder go out, with the higher Pressure inside or outside the metal bellows can be. The basic insight is, in particular, that the wall of the metal bellows even at low axial spring constant at a pressurization only small force changes at the ends of a bellows fastened on both sides leads. The axial deformations of the bellows shafts are quite not small, but stand out just like those on the individual Balbwellen acting forces in their total over the entire length of the metal bellows almost on. Thus, with little pressure-related forces, the metal bellows axially on the valve needle be transferred.

A particularly advantageous embodiment provides the radial Fixation of the valve needle by the firm connection of the metal bellows with the valve needle on the one hand and with the housing on the other hand.

In another embodiment of the invention provides the use a compression spring between the housing and valve needle for a reliable closing force acting on the valve.

Despite the great stability of the metal bellows in particular in the case of a cylindrical design, the valve needle or a over the metal bellows inverted outer sleeve a guide for represent this. The metal bellows may under certain circumstances partially rest on his leadership. A residual risk of a Buckling is thus reduced again.

The particular advantages of metal bellows are achieved both with internal pressure as well as external pressure. The dimensioning of the edge strength of the metal bellows in the area from 25 to 500 microns shows that small wall thickness at large pressures, such as 300 bar, are sufficient.

Experiments have shown that an education of the metal bellows in the form of longitudinally visible strung together Semicircular segments provides special advantages. These semicircle segments can each be through intervening straight Pieces are supplemented.

The metal bellows is advantageously fixed to the valve needle and connected to the housing. For mounting the valve needle and the metal bellows in the housing, for example at a Injection valve with several nested ones Elements, joints must be freely accessible. This can advantageously by welded joints, For example, laser welding done.

To the at high applied fluid pressures on the pressurized To selectively influence surfaces acting compressive forces, should have a certain balance, based on the Ventilnade acting in opposite directions fluid pressure forces are present. It is intended to achieve a total compensation of these forces so that the valve needle with respect to said forces is almost free of force or at the valve one with the pressure proportional rising closing force is applied. That that in Closing direction of the pressure-effective forces slightly larger are as those directed against the closing force. additionally the force of a closing spring can be advantageous.

In principle, the fluid metering device can be formed with valves be that open inward or outward. The Construction of the metal bellows in relation to the rest Elements in particular for the impact-generating actuator is corresponding adapt. As an actuator electromagnets come into question. It is advantageous to use piezoelectric actuators, for example are biased in a Bourdon tube.

Exemplary embodiments will be described below with reference to schematic figures which do not limit the scope of protection.

FIG. 1
shows a high-pressure injector with an actuator, a pressure-loaded metal bellows and an outward-opening valve,
FIG. 2
shows a high pressure injector with an externally pressurized metal bellows and an outwardly opening valve,
FIG. 3
shows a Hochdruckinjektor with an inner pressure-loaded metal bellows and an outwardly opening valve and
FIG. 4
shows a Hochdruckinjektor with an actuator, a druckbeauflaglagten metal bellows and an inwardly opening valve.

The high-pressure injectors considered here are fuel-injected PFUEL operated up to, for example, 500 bar. A stroke of the valve needle is extremely short and lies in the range from 10 to 100 μm. When looking at the housing 1 is between the fluidically pressurized area and the Area of the actuator with much lower pressure to distinguish. For this purpose, the housing is divided into the chamber 13, which is connected by means of a conduit bore 7, over the the fluid is supplied under pressure. Such a fluid metering device or a hydraulic valve for dosing the Fluids thus separates a high pressure room from a room for example, may have 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 Invention. As a lead-through element is a metal bellows 17 used.

In the construction of a high-pressure injection valve for direct-injection lean-burn engines, particularly when the injection valve has a piezoelectric actuator 8 as a drive, the following problems are to be solved:

  • The implementation of the valve needle 3 from the pressurized fuel chamber 13 in the drive part of the injector is to perform hermetically sealed;
  • the lead-through element, here the metal bellows 17, should have a high mechanical resilience (low spring rate) in the direction of movement of the valve needle 3 so as not to impair the deflection of the valve needle 3 and keep the forces introduced by the temperature-induced changes in length of the lead-through element into the valve needle 3 low ;
  • it should be ensured a sufficient compressive strength of the lead-through element at typical fuel pressures up to 500 bar;
  • pressure-related forces that act directly on the valve needle or that are introduced by connected with the valve needle mechanically connected elements, such as the lead-through element in the valve needle to be compensated appropriately;
  • Furthermore, a very high reliability of the lead-through element must be guaranteed in terms of leakage, ie the mechanical compressive / tensile stresses occurring in the lead-through element must be in a material-compatible range, in which the lead-through element is deformed only elastically reversible;
  • the function of the lead-through element must typically be ensured in a temperature range of -40 to + 150 ° C;
  • the lead-through element should continue to offer the opportunity to compensate for the forces acting on the valve needle 3 pressure-related forces suitable to make the valve needle total pressure-free. For example, due to the pressure-loaded surface of the valve disk 4 of an outwardly opening injector according to Figure 1 at high fuel pressure, a high pressure acting in the opening direction (opening force FU), which advantageously by a second pressure-loaded surface which generates a force acting in the opposite direction FO, is compensated. With such a possibility exist with respect to the valve seat diameter DS and the valve needle diameter DN no restrictions;
  • the lead-through element must be designed so that the mountability of the injector is ensured.

By using a correspondingly designed metal bellows 17 as an implementing element can be all solve the problems listed above. With reference to the illustrated in Figure 1 Execution of an outwardly opening high-pressure fuel injection valve First, the function of the Injectors and then the various functions of the Metal bellows 17 explained.

The high-pressure injector shown in FIG. 1 has the injector housing 1 a valve seat 2 on. The valve seat 2 is in Basic state by the second end 23 of the valve needle 3 connected valve disc 4 kept closed. Of the closed state of the valve seat 2 and the valve disc 4 injection nozzle is formed by the tensioned Compression spring 5 ensures that with the valve needle 3 via a snap ring 6 is connected. The fuel supply takes place through the attached in the housing 1 bore 7th In the upper part of the injector housing 1 is the drive unit, formed from a piezoelectric multilayer actuator (PMA) 8 in low voltage technology, combined with a Bourdon tube 9, a top plate 10 and a base plate 11. Die Bourdon tube 9 is so with the top plate 10 and the base plate 11th welded, that the PMA 8 under a mechanical compression bias stands. The housing 1 and the base plate 1 are also as stiff as possible connected by a weld. Between top plate 10 and first end 22 of the valve needle 3 there is a gap 12 whose height is considerable 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 the thermal length changes. To compensate for different thermal length changes, i. to make sure a substantial temperature independence of the height of the gap 12, the injector components are made of materials with low thermal expansion coefficients or made of different materials, in terms of their thermal Linear expansion coefficients so matched are that the constancy of the gap height approximately is guaranteed.

To carry out the valve needle 3 from the fuel chamber 13 in the pressureless actuator chamber 14 is the perforated plate 15, which is welded to an inner bore 16 of the housing 1. Likewise, the perforated plate 15 also worked out of the housing 1 be. Between the first end 22 of the valve needle 3 and the perforated plate 15 is the cylindrical metal bellows 17th welded, which hermetically seals the fuel chamber 13 with respect to the actuator chamber 14 at the same time large axial compliance is used. In the one shown in FIG Configuration, the metal bellows 17 by the fuel pressure applied inside. However, it is also possible that Metal bellows 17 directed downwards between valve needle 3 (no longer at the needle end) and the perforated plate 15, this is applied externally by the fuel pressure would be as shown in Figure 2.

To initiate the injection process, the actuator 8, in In this case, a piezoelectric actuator, via the electrical leads 18 charged, whereupon the PMA 8 expands and the valve plate 4 of the valve needle 3 lifts off from the valve seat 2 and Fluid or fuel exiting the injection valve.

To complete the injection process, the PMA 8 becomes electrical discharged. The PMA 8 contracts again its original length and the valve needle 3 is through the biased strong return spring 5 moves back so far that the valve disk 4 rests sealingly in the valve seat 2 and the annular injection port is closed.

The use of a metal bellows fulfills suitably chosen Geometry in full all to a feedthrough element or sealing element requirements. These include, that the metal bellows a perfect, durable and reliable Sealing represents. The metal bellows 17 holds what calculations and tests have shown, despite low wall thicknesses for example, 50 to 500 microns due to its high radial Stiffness very high pressures without irreversible to be deformed. The specification of a wall thickness range is be interpreted that a metal bellows 17 not varying, but for the individual case a constant wall thickness having. The metal bellows can with a sufficient number of waves at the same time the required high axial compliance, i.e. a possibly required low axial spring constant exhibit.

To the pressure-effective surfaces of the valve needle 3 in total to influence specifically, so that ideally a state complete power compensation or a state with low Flow force is present, the diameter of the metal bellows 17 be coordinated accordingly. This will be different from the pressurized fluid on the valve needle 3 with Valve plate 4 acting compressive forces and those of the end face the metal bellows introduced into the valve needle 3 pressure-related Forces compensate each other so that no resulting Compressive force component acts on the valve needle 3. As a result, such an injector shows a fuel pressure almost completely independent switching behavior, since for the opening and closing forces only the piezoelectric actuator 8 and the force of the prestressed return spring 5 prevail are. Although this is not true to the same extent for dynamic Compressive forces (pressure waves) when opening and closing a high-pressure injector are unavoidable, but is one pressure balanced valve needle 3 against such effects naturally much less sensitive. The metal bellows 17 has a wide due to the metallic material Working temperature range with consistent functions. Thermal length changes of the bellows themselves lead due to the low axial spring constant of the metal bellows only too negligible small force changes to the valve needle. 3 seen in the axial direction. The metal bellows may be due its mechanical spring action in the axial direction the Return spring, the compression spring 5, partially or completely replace.

To understand the invention is the clarification of the behavior a pressurized metal bellows, in particular the deformations caused by the pressure and thereby triggered forces necessary. The metal bellows 17 is double-sided fastened with elements on which in the metal bellows by external Press transferred forces in the axial direction become. In conjunction with the targeted setting of this Forces through the diameter of the bellows at the smallest possible axial spring constant by the design of Metallbalgwandung a valve needle can be designed in such a way that a specifiable balance of forces is present. This realization could by simulation calculations and by experiments be proved ..

In particular, it has been found that with fluidic pressurization the change in the total length of the wall of a Metal bellows with multiple waves, with only the wall the metal bellows is considered pressurized extremely is low. At internal pressure is shortened the wall of the metal bellows 17 slightly, with external pressure it extends slightly. For example is at a pressure of 200 bar and a metal bellows geometry with twelve shafts, an inner diameter of 3.5 mm, one Outer diameter of 5.3 mm, a wall thickness of 100 microns and a wall length of 12.1 mm a typical change in length from 10 to 20 microns occur. Due to the low axial spring constant for example 0.2 / μm of the metal bellows wall This only leads to small force changes at the ends of a Both sides attached metal bellows 17. The axial deformations the bellows shafts are not small, stand out but just like the ones acting on the individual bellows shafts Forces in their total over the total length of the bellows almost on. Through this knowledge about the connections of the evoked Forces on a metal bellows by pressurization For example, such a metal bellows 17 may be in both orientations be incorporated, i. Internal or external pressurization. Despite the deformations of the bellows waves can be the mechanical stresses in the wall of the metal bellows 17 by controlling the wall thickness, for example 25 to 500 μm, easily hold in a material-compatible area, without that the axial compliance is substantially reduced.

As a particularly favorable form for the bellows has a from semicircle segments joined together in longitudinal section existing geometry proved. Opposite a sinusoidal Waveform shows the semicircle segments existing wall lower mechanical stresses in the axial Direction at higher axial compliance on.

Because of the bellows wall even at high pressures or pressure changes almost no resulting forces on the bellows can be transferred, such for the pressure balance the valve needle 3 required compensation forces targeted be adjusted by the bellows diameter. this will illustrated in detail by the representations of Figures 2 and 3. In Figures 2 and 3, one outwards opening injection valve shown. FIG. 2 shows a externally pressurized metal bellows within the system and FIG. 3 shows an internal pressure-loaded metal bellows 17.

The high-pressure injector according to FIGS. 2 and 3 has, for example, the following dimensions:
The diameter DN of the valve needle 3 is 3 mm and the diameter DS of the valve seat 2 is 4 mm. On the valve needle 3 thus acts at a fuel pressure of 250 bar due to the resulting annular differential area AD of 5.5 mm 2 directed downwardly in the opening direction opening force FU with 137.5 N. Since the wall of the externa pressurized metal bellows 17 almost no forces on the Valve needle 3 transmits, can be selectively adjusted by the diameter of the metal bellows 17, ie by the diameter DP of the end plate 19, which is the connection between Metallbalgwandung and valve needle 3, the size of the upward acting compensation pressure forces and thus the upward compensation pressure force FO. In order to fulfill the condition FO = FU (opening force = compensation force) in the example chosen, the diameter of the end plate 19 is given a value of DP = 4 mm. The valve seat force is completely drukkunabhängig under these conditions and is determined exclusively by the height of the set biasing force FR of the return spring. In order to avoid contact of the bellows shafts with the valve needle, if necessary, the diameter of the valve needle in the region of the metal bellows can be reduced. An adaptation of the pressure-effective surfaces is not limited to cylindrical metal bellows, but can be done with appropriate design even in non-cylindrical formations.

Montagetechnisch the metal bellows 17 after the introduction of Valve needle 3 in the housing of the injector subsequently by means Laser welding 20 on the perforated plate 15 of the valve housing 1 and attached to the valve needle 3.

Figure 3 shows the complementary to Figure 2 arrangement with top-oriented internal pressure-loaded metal bellows 17. Die cheaper embodiment results from the particular situation the welds, for reasons of reliability preferably be subjected to mechanical compressive stresses should. A certain advantage is in the embodiment of FIG 2 the shorter length of the upward through the (compensation force FO) and downward (opening force FU) acting Compressive forces loaded area of the valve needle opposite Figure 3 is thereby slightly less stretched.

By the mechanical spring action of the metal bellows 17 in axial direction, the metal bellows 17 in the in Figure 1, 2 and 3 shown embodiments, the return spring. 5 partly or completely replace. This results a considerable design simplification and cost savings. Is applied to an additional return spring (compression spring 5) not waived, this can reduce the height also housed inside or outside of the metal bellows 17 be.

In addition to the proposed cylindrical metal bellows 17 come also other types, e.g. conical bellows or bellows with of the circular shape deviating cross-sectional geometry in question.

Claims (19)

  1. Fluid metering device for a pressurized fluid, comprising:
    a chamber (13) in a housing (1), said chamber (13) containing the fluid subject to pressure,
    a valve needle (3) passed through the chamber (13), the first end (22) of which can be lifted outside the chamber (13) and the second end (23) of which together with a valve seat (2) positioned on the housing (1) forms a valve connected to the chamber (13), and
    metal bellows (17) as the passage element for the first end (22) of the valve needle (3) from outside into the chamber (13), the chamber (13) being connected in a hermetically sealed manner at the point of passage by means of the connection between the first end (22) of the valve needle (3) via the metal bellows (17) to the housing, characterised in that the resulting force acting as a pressure at the valve needle (3) and exerted on elements connected thereto is adjusted by means of selected areas acting as pressure at the metal bellows (17) and the valve needle (3), such that the forces acting as a pressure at the valve needle (3) are compensated for overall or a closing force that increases in proportion to the pressure is present at the valve.
  2. Fluid metering device according to Claim 1,
    the radial angle position of the valve needle (3) being fixed by connecting the metal bellows (17) to the valve needle (3) on the one hand and to the housing (1) on the other hand.
  3. Fluid metering device according to Claim 1,
    a compression spring (5) also being provided between the housing (1) and the valve needle (3) to apply a predefinable closing force.
  4. Fluid metering device according to one of the preceding claims, the metal bellows (17) being configured as cylindrical.
  5. Fluid metering device according to one of the preceding claims, the valve needle (3) or an outer sleeve representing a guide for the metal bellows (17).
  6. Fluid metering device according to one of the preceding claims, the metal bellows (17) being subject to internal or external pressure.
  7. Fluid metering device according to one of the preceding claims, the metal bellows having a wall thickness of 25 to 500 µm.
  8. Fluid metering device according to one of the preceding claims, the metal bellows (17) being made up of semicircular segments joined together side by side in the longitudinal cross-section.
  9. Fluid metering device according to Claim 8, straight parts being present between each of the semicircular segments.
  10. Fluid metering device according to one of the preceding claims, the metal bellows (17) being connected by weld seams (20) directly or indirectly to the housing (1) on the one hand and to the first end (22) of the valve needle (3) on the other hand.
  11. Fluid metering device according to Claim 10, the weld seams being laser weld seams.
  12. Fluid metering device according to one of the preceding claims, a face plate (19) being provided between the first end (22) of the valve needle (3) and the metal bellows (17).
  13. Fluid metering device according to one of Claims 11 or 12, the diameter of the metal bellows (17) being designed in conjunction with the diameter of the face plate (19) such that forces acting as a pressure at the valve needle (3) are compensated for overall or a closing force that increases in proportion to the pressure is present at the valve.
  14. Fluid metering device according to one of the preceding claims, the fuel pressure (PFUEL) being 1 to 500 bar.
  15. Fluid metering device according to one of the preceding claims for use with injectors that open outwards.
  16. Fluid metering device according to one of the preceding claims, the first end (22) of the valve needle (3) being such that it can be lifted by an actuator (8) connected permanently to the housing (1).
  17. Fluid metering device according to Claim 16, the actuator (8) being a piezo-actuator, which is pretensioned in a Bourdon spring and held at a distance from the first end (22) of the valve needle (3) by a gap (12) of predefined width in the idle state.
  18. Fluid metering device according to Claim 16, the actuator (8) being an electromagnet.
  19. Fluid metering device according to one of the preceding claims, the lift of the valve needle (3) being limited in a defined manner by stops.
EP00107401A 1999-04-20 2000-04-05 Fluid metering device Expired - Fee Related EP1046809B1 (en)

Priority Applications (2)

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

Publications (3)

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

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US (1) US6311950B1 (en)
EP (1) EP1046809B1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2308602A2 (en) 2009-10-06 2011-04-13 Nordson Corporation Liquid dispensing module

Families Citing this family (82)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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