EP3339628A1 - Ventilanordnung für ein einspritzventil und einspritzventil - Google Patents

Ventilanordnung für ein einspritzventil und einspritzventil Download PDF

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Publication number
EP3339628A1
EP3339628A1 EP17159254.6A EP17159254A EP3339628A1 EP 3339628 A1 EP3339628 A1 EP 3339628A1 EP 17159254 A EP17159254 A EP 17159254A EP 3339628 A1 EP3339628 A1 EP 3339628A1
Authority
EP
European Patent Office
Prior art keywords
armature
valve
pole piece
gap
valve assembly
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Withdrawn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
EP17159254.6A
Other languages
English (en)
French (fr)
Inventor
Stefano Filippi
Mauro Grandi
Francesco Lenzi
Valerio Polidori
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.)
Continental Automotive GmbH
Original Assignee
Continental Automotive 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 Continental Automotive GmbH filed Critical Continental Automotive GmbH
Priority to PCT/EP2017/083946 priority Critical patent/WO2018115197A1/en
Publication of EP3339628A1 publication Critical patent/EP3339628A1/de
Withdrawn legal-status Critical Current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
    • F02M51/0614—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of electromagnets or fixed armature
    • 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
    • F02M51/061—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
    • F02M51/0685—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 and the valve being allowed to move relatively to each other or not being attached to each other
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0075—Stop members in valves, e.g. plates or disks limiting the movement of armature, valve or spring
    • 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
    • F02M2200/02—Fuel-injection apparatus having means for reducing wear
    • 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
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/90—Selection of particular materials
    • F02M2200/9038—Coatings
    • 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
    • F02M2200/90—Selection of particular materials
    • F02M2200/9053—Metals
    • F02M2200/9061—Special treatments for modifying the properties of metals used for fuel injection apparatus, e.g. modifying mechanical or electromagnetic properties

Definitions

  • the present invention relates to a valve assembly for an injection valve and to an injection valve, e.g. a fuel injection valve of a vehicle. It particularly relates to solenoid injection valves.
  • Conventional solenoid injection valves have a stationary pole piece and a moveable armature which is accelerated towards the pole piece for opening the valve.
  • the armature hits the pole piece at the end of the opening transient for stopping the armature motion in a fully open configuration of the valve.
  • Modern combustion engines often require high fuel pressure and fast opening transients so that the armature and the pole piece experience a large impulse when the armature hits the pole piece.
  • the armature therefore usually has a chrome plating on surfaces of the armature contacting the pole piece to improve wear resistance.
  • the chrome plating is costly and should be avoided for environmental reasons.
  • Advantageous embodiments and developments of the valve assembly and the injection valve are specified in the dependent claims, the following description and the drawings.
  • a valve assembly for an injection valve is specified.
  • an injection valve comprising the valve assembly is specified.
  • the injection valve may in particular be a fuel injection valve of a vehicle.
  • the injection valve is in particular a fuel injection valve which is configured for injecting fuel directly into a combustion chamber of an internal combustion engine.
  • the valve assembly comprises a valve body with a central longitudinal axis.
  • the valve body has a cavity with a fluid inlet portion and a fluid outlet portion.
  • the cavity in particular extends through the valve body in axial direction from the fluid inlet portion to the fluid outlet portion.
  • valve assembly comprises a valve needle.
  • the valve needle is received in the cavity. It is configured and arranged to prevent a fluid flow through the fluid outlet portion in a closing position and is axially displaceable relative to the valve body away from the closing position for releasing the fluid flow through the fluid outlet portion.
  • the valve assembly further comprises a calibration spring.
  • the valve needle is biased by the calibration spring towards the closing position.
  • the calibration spring may in particular be preloaded in the valve assembly for biasing the valve needle axially into the closing position.
  • the calibration spring has a spring rate k with k ⁇ 300 N/mm.
  • the valve assembly further comprises a pole piece and an armature.
  • the pole piece and the armature are also parts of an electro-magnetic actuator unit which is configured to actuate the valve needle.
  • the electro-magnetic actuator unit preferably further comprises a solenoid and in particular also a magnetic yoke which may also function as a housing for the solenoid.
  • the injection valve comprises the actuator unit.
  • the pole piece is stationary, i.e. it is positionally fix with respect to the valve body.
  • the armature is arranged in the cavity. It is axially movable with respect to the valve body and the pole piece in reciprocating fashion.
  • the armature is operable to move the valve needle away from the closing position, in particular against the bias of the calibration spring, when it travels towards the pole piece.
  • the armature is operable to take the valve needle with it in axial direction towards the pole piece when the armature is displaced axially towards the pole piece.
  • the armature is axially displaced towards the pole piece by the magnetic force on the armature which is generated by the actuator unit when the solenoid is energized for actuating the valve needle.
  • the armature is in one piece with the valve needle.
  • the armature comprises a central through-hole through which a shaft of the valve needle extends.
  • the armature is fixed to the shaft, e.g. by welding.
  • the armature has an axial play with respect to the valve needle. In particular, it is in sliding mechanical contact with the shaft of the valve needle.
  • the valve needle preferably comprises a retaining element which is in one piece with the shaft or fixed to the shaft. The retaining element is arranged and positioned to limit axial displaceability of the armature relative to the valve needle in direction towards the pole piece. In this way, the armature is operable to engage in form-fit connection with the retaining element for taking the valve needle with it in direction towards the pole piece.
  • the pole piece has a central axial opening.
  • the pole piece may be in one piece with the valve body or may be fluid-tightly fixed to the valve body so that fluid flowing through the cavity from the fluid inlet portion and the fluid outlet portion has to flow through the central axial opening.
  • the pole piece and the valve body are shaped and arranged such that, in the region of the valve assembly from one axial end of the pole piece to the other axial end of the pole piece, the central axial opening of the pole piece is the only fluid flow path enabling fluid flow from the fluid inlet portion to the fluid outlet portion.
  • That the pole piece is fluid-tightly fixed to the valve body means in particular that the pole piece is joined to the valve body in such fashion that an external circumferential surface of the valve body interfaces with an internal circumferential surface of the valve body such that fluid flow along the pole piece is blocked by the joint between the external circumferential surface of the pole piece and the internal circumferential surface of the valve body.
  • the internal circumferential surface of the valve body also denoted as "inner surface" herein - in particular defines the cavity.
  • the armature and the valve body shape a radial gap between the inner surface of the valve body and an outer surface of the armature, the radial gap defining an axial fluid channel along the outer surface of the armature.
  • the outer surface of the armature is in particular an external circumferential surface of the armature.
  • the radial gap may extend completely circumferentially around the armature.
  • sections with the radial gap between the inner surface of the valve body and the outer surface of the armature may alternate with sections in which the outer surface of the armature is in sliding mechanical contact with the inner surface of the valve body.
  • an axial gap is shaped between - and in particular by - a lower surface of the pole piece and a top surface of the armature, in particular in embodiments in which the top surface of the armature overlaps the central axial opening of the pole piece.
  • the axial gap may be shaped between - and in particular by - the lower surface of the pole piece and top surfaces of the armature and the valve needle, respectively.
  • the valve needle - in particular the retaining element - may contribute to shape a an inner portion of the axial gap.
  • the axial gap defines a radial fluid path from an aperture of the central axial opening of the pole piece to the radial gap between the inner surface of the valve body and the outer surface of the armature.
  • the aperture of the central axial opening in particular perforates the lower surface of the pole piece.
  • the lower surface of the pole piece in particular extends completely circumferentially around the aperture. An inner edge of the lower surface may expediently adjoin the aperture.
  • the lower surface of the pole piece and the top surface of the armature - or the top surfaces of the armature and the valve needle, respectively - may be unperforated so that fluid flowing through the cavity from the fluid inlet portion to the fluid outlet portion has to pass the axial gap.
  • fluid flowing from the fluid inlet portion to the fluid outlet portion in the subject valve assembly is forced to flow through the central axial opening of the pole piece, further through the axial gap in radial outward direction to the radial gap between the outer surface of the armature and the inner surface of the valve body and further along the outer surface of the armature.
  • the width of the axial gap is reduced as the armature approaches the pole piece so that the pressure gradient along the axial gap increases as the distance of the top surface of the armature from the lower surface of the pole piece decreases. In this way, a hydraulic force is generated which acts on the armature and increases as the distance of the top surface of the armature from the lower surface of the pole piece decreases.
  • That fluid “has to pass" the central axial opening of the armature, the axial gap and the fluid channel (s) along the outer surface of the armature, respectively, is in particular understood to mean that no other fluid channels are provided in parallel thereto.
  • This includes embodiments in which leakage channels are present, e.g. between the shaft of the valve needle and the armature, through which small amounts of fluid may flow from the fluid inlet portion to the fluid outlet portion without passing the central axial opening of the armature, the axial gap and/or the fluid channel (s) along the outer surface of the armature.
  • the leakage channels are dimensioned so small the fluid flow through the leakage channels is negligible for the generation of the pressure gradient.
  • the hydraulic diameter of the axial gap is smaller at its inflow end - i.e. adjacent to the central axial opening of the pole piece-than at its outflow end - i.e. adjacent to the radial gap between the outer surface of the armature and the inner surface of the valve body.
  • the lower surface of the pole piece and the top surface of the armature - or the top surfaces of the armature and the valve needle, respectively - each are planar surfaces.
  • the lower surface of the pole piece is coplanar to the top surface of the armature - or to the top surfaces of the armature and the valve needle, respectively.
  • the top surface of the armature and the lower surface of the pole piece are free from protrusions, i.e. in particular macroscopic protrusions.
  • the axial gap widens in radial outward direction.
  • the valve assembly is configured to retain a predefined minimum gap width of the axial gap throughout operation, in particular throughout operation of the electro-magnetic actuator unit, i.e. in particular while the solenoid is energized to actuate the valve needle.
  • the predefined minimum gap width has a value of at least 15 ⁇ m.
  • the valve assembly may expediently be configured to hold the gap width of the axial gap constant at said minimum gap width, in particular during a non-zero period of time after an opening transient of the armature and before a closing transient of the armature during one injection event.
  • the position of the valve needle when the axial gap has the minimum gap with is herein also denoted as "maximum opening position of the valve needle".
  • the minimum gap width of the axial gap is 50 ⁇ m or less, preferably 45 ⁇ m or less. In one embodiment, the minimum gap width has a value between 25 ⁇ m and 40 ⁇ m, the limits being included. It has been found, that a residual gap between the top surface of the armature and the lower surface of the pole piece of about 30 ⁇ m provides a good functionality.
  • the valve assembly may be configured to retain the predefined minimum gap with - i.e. the maximum opening position of the valve needle - by means of balancing, at the minimum gap width, a magnetic force of the actuator unit on the armature in a direction away from the fluid outlet portion by the sum of a hydraulic force generated by the radial pressure gradient along the axial gap and a spring force of the calibration spring both acting in a direction towards the fluid outlet portion.
  • the magnetic force of the actuator unit is balanced with the sum of the hydraulic force and the spring force by means the radial extension of the axial gap, the magnetic force of the actuator unit, and the spring rate k of the calibration spring being adapted to a nominal operating pressure of the valve assembly and/or to one another.
  • Adapting the radial extension of the axial gap is in particular achieved by selecting the radius of the axial opening of the pole piece and/or the outer radius R of the armature.
  • Surface regions of the pole piece, the armature and - as the case may be - the valve needle comprise said lower surface of the pole piece and said top surface of the armature or said top surfaces of the armature and the valve needle, respectively. Since there is no mechanical contact between these surfaces during operation of the valve assembly, all of the corresponding surface regions lack any hardening layers in one embodiment. In particular, the surface regions are free of a chrome plating layer. In particular, the material composition of the surface regions corresponds substantially to the bulk material of the respective part.
  • the armature may be suspended in a stable position when the magnetic force, the hydraulic force and the spring force are balanced. In this position, the armature may expediently be without contact to the pole piece. In this position, the energy of the armature has a minimum, so the equilibrium is stable.
  • the local minimum in the energy can be achieved by providing a suitable gradient of the hydraulic force exerted by fuel flow on the armature.
  • the suitable gradient is achieved by the design of the injector, especially by the design of the flow path, as explained above.
  • the axial gap is shaped and dimensioned such that it effects a hydraulic gradient ⁇ hyd with ⁇ hyd ⁇ 250 N/mm when the gap width of the axial gap is the predefined minimum gap width - i.e. in particular when the valve needle is in the maximum opening position and the armature is in the stable suspended position.
  • the hydraulic force exerted by fuel flowing from the fluid inlet portion to the fluid outlet portion on the armature has a gradient ⁇ hyd in axial direction with ⁇ hyd ⁇ 250 N/mm.
  • ⁇ hyd ⁇ 300 N/mm applies to the hydraulic gradient.
  • the axial gap effects a pressure gradient having a value in the range between 3 bar and 5 bar, the limits being included, when the gap width of the axial gap is the predefined minimum gap width.
  • the pressure gradient may advantageously bring about the above mentioned hydraulic gradient.
  • the calibration spring can have a spring rate k with k ⁇ 100 N/mm, e.g. the spring rate k has a value between 1 N/mm and 100 N/mm, the limits being included.
  • a calibration spring is common and low-cost.
  • the valve assembly comprises a calibration tube which is received in the central axial opening of the pole piece and press-fitted with the pole piece, in particular with the circumferential internal surface of the pole piece which defines the central axial opening.
  • the calibration tube and the pole piece expediently are separate parts so that the calibration tube is axially moveable into the central axial opening for adjusting a preload of the calibration spring during manufacturing of the valve assembly.
  • the calibration tube is positionally fix relative to the pole piece and the valve body.
  • one axial end of the calibration spring is seated against the calibration tube and the opposite axial end of the calibration spring is seated against the valve needle.
  • the calibration spring can also be seated against the armature instead of or additionally to being seated against the valve needle.
  • the calibration spring can have a helicoidal shape. This, too, is a common design in calibration springs in contrast complex three-dimensional spring designs with a high stiffness.
  • the helicoidal spring may advantageously occupy a particularly small volume so that a particularly large volume remains void and available for the fluid flow through the central axial opening of the pole piece.
  • the armature does not comprise through holes, apart from one internal - i.e. central - through hole through which the valve needle extends.
  • the shaft of the valve needle extends through the only through hole which is comprised by the armature.
  • through holes are often formed in armatures to provide a fluid path in the direction of the fluid outlet portion. Such through holes are not necessary according to this embodiment. Moreover, they are undesired because they would reduce the pressure gradient which is achievable along the axial gap. Instead, the only flow path for fluid flow in the direction of the fluid outlet portion is through the central axial opening of the armature and further via the axial gap and the radial gap. Therefore, the dimensions of these gaps can be designed to control the hydraulic behavior of the fluid flow and to employ a suitable gradient of the hydraulic force.
  • a ratio r/R of an outer radius R of the armature and an inner radius r of the pole piece 1.5 ⁇ R/r ⁇ 3 applies.
  • the inner radius r of the pole piece is in particular the radius of the central axial opening, in particular at its aperture in the lower surface of the pole piece.
  • a ratio r/b of the inner radius r of the pole piece and the radial gap b 8 ⁇ r/b ⁇ 20 may apply in this or other embodiments in which the radial gap preferably extends completely circumferentially around the armature - in particular with a constant gap width.
  • 80 ⁇ m ⁇ b ⁇ 250 ⁇ m applies the radial gap b between the inner surface of the valve body and the outer surface of the armature.
  • the radius of the inner circumferential edge of the radial gap has a value between 2 mm and 6 mm, preferably between 3 mm and 5 mm, the limits being included in each case, in one embodiment.
  • the hydraulic gradient can be in the range of 280 - 400 N/mm.
  • a calibration spring with a spring rate k with 1 N/mm ⁇ k ⁇ 100 N/mm can be used.
  • a stable suspended stop position for the armature is reachable based only on dimensions of injector components.
  • Figure 1 shows an injection valve 1 that is in particular suitable for dosing fuel to an internal combustion engine.
  • An enlarged cutout II of figure 1 is shown in figure 2 .
  • the injection valve 1 comprises a valve assembly 3 and an actuator unit 19.
  • the valve assembly 3 comprises a valve body 4 with a central longitudinal axis L.
  • a housing 6 is partially arranged around the valve body 4.
  • the valve body 4 comprises a cavity 9.
  • the cavity 9 has a fluid outlet portion 7.
  • the fluid outlet portion 7 communicates with a fluid inlet portion 5 of the cavity 9.
  • the fluid inlet portion 5 and the fluid outlet portion 7 are in particular positioned at opposite axial ends of the valve body 4.
  • the cavity 9 takes in a valve needle 11.
  • the valve needle 11 comprises a needle shaft 13, a sealing ball 15 welded to the tip of the needle shaft 13, and an upper retaining element 24.
  • the upper retaining element 24 is fixedly coupled by welding to the needle shaft 13 adjacent to an axial end of the needle shaft 13 remote from the sealing ball 15.
  • valve needle 11 In a closing position, the valve needle 11 sealingly rests on a seat plate 8 having at least one injection nozzle.
  • the fluid outlet portion 7 is arranged near the seat plate.
  • a fluid flow through the at least one injection nozzle is prevented.
  • the injection nozzle may be, for example, an injection hole. However, it may also be of some other type suitable for dosing fluid.
  • the electro-magnetic actuator unit 19 comprises a coil 21, a stationary pole piece 25, a moveable armature 23, and a housing 6.
  • the housing 6 surrounds a portion of the valve body 4.
  • the coil 21 is preferably arranged inside the housing 6 and also extends circumferentially around the valve body 4.
  • the housing 6, parts of the valve body 4, the pole piece 25 and the armature 23 form a magnetic circuit.
  • the valve assembly 3 further comprises a calibration spring 18.
  • the calibration spring 18 is a helicoidal spring which is seated against a calibration tube 16 and against the upper retaining element 24 of the valve needle 11 at its opposite axial ends.
  • the calibration tube 16 is press-fitted into a central axial opening 26 of the pole piece 25 so that the calibration tube 16 is positionally fix relative to the pole piece 25.
  • the calibration spring 18 is compressed by and between the calibration tube 16 and the upper retaining element 24 so that it is preloaded and exerts a force on the needle 11 towards the closing position.
  • the armature 23 is axially movable in the cavity 9 relative to the valve needle 11 and relative to the valve body 4. In particular, it may slide on the needle 11. Axial dispaceability of the armature 23 relative to the needle is limited by the upper retaining element 24 in axial direction towards the pole piece 25 and by a lower retaining element 43 in axial direction away from the pole piece 25.
  • the lower retaining element 43 is fixed to the needle shaft 13 on the side of the armature 23 remote from the upper retaining element 24.
  • the distance between the upper and lower retaining elements 24, 43 is selected such that the armature 23 has an axial play with respect to the needle 11.
  • the upper retaining element 24 is arranged in the central axial opening 26 of the pole piece 25 and in sliding mechanical contact with an inner surface of the pole piece 25 which defines the central axial opening 26 for axially guiding the needle 11.
  • the armature 23 has a central through hole 28 through which the needle shaft 13 extends. An external circumferential surface of the needle shaft 13 is in sliding contact with an inner circumferential surface of the armature 23 which defines the central through hole 28 for axially guiding the armature 23.
  • a fluid path through the cavity 9 is roughly denoted with dashed arrows in figures 1 and 2 .
  • An outer circumferential surface of the pole piece 25 is fluid-tightly press-fitted into the valve body 4 so that it does not allow fluid to pass along the outer circumferential surface of the pole piece 25. Rather, fluid flowing from the fluid inlet portion 5 to the fluid outlet portion 7 is forced to flow through the calibration tube 16 and further through the central axial opening 26 of the pole piece.
  • a planar top surface 27 of the armature 23 is facing towards a planar lower surface 29 of the pole piece 25. In the present embodiments both surfaces are coplanar.
  • An outer radius R of the armature 23 is defined as the distance between the central longitudinal axis L and a cylindrical outer surface 31 of the armature 23.
  • An inner radius r of the pole piece 25 is defined as the distance between the central longitudinal axis L and the point from which on the lower surface 29 of pole piece 25 is substantially parallel and closest to the top surface 27 armature 23.
  • the inner radius r defines an aperture of the central axial opening 26. Absent a residual gap between the top surface 27 of the armature 23 and the lower surface 29 of the pole piece 25, the inner radius r would be the inner radius of an annular contact area 32 between the armature 23 and the pole piece 25.
  • r denotes the inner radius of the annular axial gap 32 where the armature 23 and the pole piece 25 have the smallest distance, corresponding to the gap width d of the axial gap 32.
  • a radial gap 34 is established which has a width b of 100 ⁇ m.
  • the radial gap 34 defines an annular flow channel along the armature 23.
  • the armature 23 is free from internal flow channels so that fluid flowing through the cavity 9 from the fluid inlet portion 5 to the fluid outlet portion 7 is forced to flow from the central axial opening 26 in radially outward direction through the axial gap 32 and further through the annular flow channel along the outer circumferential surface 31 of the armature 23.
  • the calibration spring 18 forces the valve needle 11 to move in axial direction into its closing position.
  • the valve needle 11 takes the armature 23 with it in direction away from the pole piece 25.
  • the armature 23 detaches from the upper retaining element 24 and travels downwards towards the disc-shaped element 43 against the bias of the armature return spring 38 which finally pushes the armature 23 back in contact with the upper retaining element 24.
  • the injection valve 1 has a stable fully open configuration, in which the needle 11 has travelled furthest upwards away from the fluid outlet portion 7 to a maximum opening position. In this position, the armature 23 does not contact the pole piece 25 but is suspended at a distance from the pole piece 25. A residual axial gap 32 between the top surface 27 of the armature 23 and the lower surface 29 of the pole piece 25 is retained throughout the injection event. Consequently, there is no hard stop for the armature 23 in the fully open configuration.
  • the armature 23 is suspended in the maximum opening position by an equilibrium of forces in a stable position.
  • a magnetic force acting in a direction away from the fluid outlet portion 7 is balanced by the sum of a hydraulic force and a spring force exerted by the calibration spring 18 both acting in a direction towards the fluid outlet portion 7.
  • a hydraulic gradient of 280 - 400 N/mm which is adjusted by choosing suitable dimensions of the injection valve 1, in particular a ratio r/R of 1.5 ⁇ R/r ⁇ 3, a ratio r/b of 8 ⁇ r/b ⁇ 20 and a radial gap 34 width b of 80 ⁇ m ⁇ b ⁇ 250 ⁇ m in the present embodiment.
  • a minimum residual gap width d of about 30 ⁇ m of the axial gap 32 can be achieved with an overall pressure drop over the armature in the range of a few bars, e.g. 3-5 bars. This pressure drop is sufficiently low not to cause problems with the spray generation.
  • the flow rate is dominated by the valve seat.
  • the static flow has no part-to-part effect and the dynamic flow can be controlled, for example, by any mechatronic approach using the electromagnetic injector closing behavior.
  • Figure 3 shows a cross section of the valve assembly 3 according to figures 1 and 2 in the plane A-A indicated in figure 2 .
  • the valve needle 11 In the maximum opening position of the valve needle 11, there is a residual gap with a width d across the axial gap 32 between the top surface of the armature 23 and the lower surface 29 of the pole piece 25. Fluid flow is directed by an axially symmetric pressure field through the residual gap along the area 32 to the outer radius R of the armature 23 and along the outer face 31 of the armature 23 through the radial gap 34 in the direction of the fluid outlet portion 7.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fuel-Injection Apparatus (AREA)
EP17159254.6A 2016-12-23 2017-03-03 Ventilanordnung für ein einspritzventil und einspritzventil Withdrawn EP3339628A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/EP2017/083946 WO2018115197A1 (en) 2016-12-23 2017-12-20 Valve assembly for an injection valve and injection valve

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16206538 2016-12-23

Publications (1)

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EP3339628A1 true EP3339628A1 (de) 2018-06-27

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110131084A (zh) * 2019-06-03 2019-08-16 无锡格林鲍尔科技有限公司 一种阀杆偶件化高压共轨喷油器
EP3875747A1 (de) * 2020-03-06 2021-09-08 Vitesco Technologies GmbH Ventilanordnung für ein einspritzventil sowie einspritzventil
CN114458508A (zh) * 2022-03-09 2022-05-10 哈尔滨工程大学 一种基于永磁实现高动态响应的电磁-永磁耦合的高速电磁阀

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114680274B (zh) * 2022-03-08 2024-05-28 宁夏昊王米业集团有限公司 一种熟化米的制备装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016116749A1 (en) * 2015-01-23 2016-07-28 Sentec Ltd Solenoid-based fuel injector
WO2017009103A1 (de) * 2015-07-15 2017-01-19 Robert Bosch Gmbh Ventil zum zumessen eines fluids
EP3156638A1 (de) * 2015-10-14 2017-04-19 Continental Automotive GmbH Kraftstoffeinspritzventil
WO2017097777A1 (fr) * 2015-12-11 2017-06-15 Delphi International Operations Luxembourg S.À R.L. Injecteur de carburant

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016116749A1 (en) * 2015-01-23 2016-07-28 Sentec Ltd Solenoid-based fuel injector
WO2017009103A1 (de) * 2015-07-15 2017-01-19 Robert Bosch Gmbh Ventil zum zumessen eines fluids
EP3156638A1 (de) * 2015-10-14 2017-04-19 Continental Automotive GmbH Kraftstoffeinspritzventil
WO2017097777A1 (fr) * 2015-12-11 2017-06-15 Delphi International Operations Luxembourg S.À R.L. Injecteur de carburant

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110131084A (zh) * 2019-06-03 2019-08-16 无锡格林鲍尔科技有限公司 一种阀杆偶件化高压共轨喷油器
CN110131084B (zh) * 2019-06-03 2024-05-28 无锡格林鲍尔科技有限公司 一种阀杆偶件化高压共轨喷油器
EP3875747A1 (de) * 2020-03-06 2021-09-08 Vitesco Technologies GmbH Ventilanordnung für ein einspritzventil sowie einspritzventil
CN114458508A (zh) * 2022-03-09 2022-05-10 哈尔滨工程大学 一种基于永磁实现高动态响应的电磁-永磁耦合的高速电磁阀

Also Published As

Publication number Publication date
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