EP3274583A1 - Control valve arrangement - Google Patents

Control valve arrangement

Info

Publication number
EP3274583A1
EP3274583A1 EP16702730.9A EP16702730A EP3274583A1 EP 3274583 A1 EP3274583 A1 EP 3274583A1 EP 16702730 A EP16702730 A EP 16702730A EP 3274583 A1 EP3274583 A1 EP 3274583A1
Authority
EP
European Patent Office
Prior art keywords
control valve
armature
seat
face
valve member
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
EP16702730.9A
Other languages
German (de)
French (fr)
Other versions
EP3274583B1 (en
Inventor
Michael Peter Cooke
David MENU
Richar Denis Jacques Alain ENTERS
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.)
Delphi Technologies IP Ltd
Original Assignee
Delphi International Operations Luxembourg SARL
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 Delphi International Operations Luxembourg SARL filed Critical Delphi International Operations Luxembourg SARL
Publication of EP3274583A1 publication Critical patent/EP3274583A1/en
Application granted granted Critical
Publication of EP3274583B1 publication Critical patent/EP3274583B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic 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
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves
    • 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
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • 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
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • 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
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8076—Fuel injection apparatus manufacture, repair or assembly involving threaded members

Definitions

  • the present invention relates generally to a fuel injector and more particularly to a control valve arrangement.
  • a control valve indirectly controls the displacements of a valve member, or needle, in order to enable or forbid fuel injection through the nozzle.
  • the control valve generally comprises a body in which is arranged an electromagnetic solenoid provided with a central bore, a compression spring arranged in said bore and, an armature and spool assembly slidably guided along a valve axis in a hydraulic distribution bore provided in the body.
  • the armature and spool assembly comprises a magnetic armature that is a thick disc-like member having an upper face and an under face and a central through orifice and also, a spool stem inserted an crimped in the central orifice, the spool being a cylindrical shaft having a top end flush with the upper surface of the armature, the spool protruding from the under face and extending in the hydraulic bore toward a distal bottom end.
  • the spring In operation, the spring is compressed between the bottom of the solenoid's central bore and the top end of the stem, so that it permanently pushes the armature and spool assembly away from the solenoid and when the solenoid is electrically energized, a magnetic field attracting the armature and spool assembly toward the solenoid is generated, the armature and spool assembly spool moving to an open position and further compressing the spring.
  • the spool must be guided with minimal clearance inside the hydraulic bore and also with very precise alignment to the solenoid to avoid friction from sideloads caused by concentricity or parallelism errors between the solenoid and the armature. Such accuracy is costly and even with the most accurate machining possible, these effects can still generate shot-shot variation of fuelling. Another problem is that as fuel pressures increase, so does the fuel temperature, which can cause fuel lacquer to form on the valve guide, adding a further source of friction.
  • the control valve member is guided in translation along a valve axis between a closed position forbidding fuel to exit a spill orifice and an open position enabling fuel to exit said spill orifice.
  • the control valve member comprises a magnetic armature to which is fixed a seat member and, the armature is adapted to cooperate with an electromagnetic solenoid in order for the seat member be move between the closed position wherein it is in sealing abutment against a fixed seating face, and the open position wherein said seat member is lifted away from said fixed seating face.
  • the control valve member further comprises a spring member adapted to guide in translation along the valve axis the seat member in the control valve chamber.
  • the armature is a thick disc-like member axially extending between an upper face and an opposed lower face and, the seat member comprises a connecting portion fixed to the armature and, a head portion having a sealing face adapted to abut the fixed seating face in closed position, the head portion being on the side of the lower face of the armature.
  • the seat member may a screw which male threaded member is tightened in a threaded orifice centrally provided in the armature, the head portion of the screw being of a larger cross section than the connecting male threaded member.
  • the spring member is a spider spring provided with a plurality of resilient limbs radially extending from a common core to a distal end adapted to be fixed in the control valve chamber.
  • the core of the spring member is centrally holed so that the connecting portion of the seat member can be inserted in said hole prior to be tightened in the armature so that, the spring member is fixedly trapped between the lower face of the armature and the head of the control valve member.
  • the resilient limbs further comprise a peripheral portion erecting from the distal end of each resilient limb, perpendicularly to the limbs, the peripheral portions surrounding the armature and being adapted to be press fitted against the inner peripheral wall of the valve member chamber.
  • the spring member is integral to the seat member forming an integral seat-spring member.
  • Said integral seat-spring member has a central core portion having upwardly extending a threaded connecting member fixedly tightened in the central threaded orifice of the armature and, a flat external face adapted to seal the spill orifice.
  • the integral seat-spring member further comprises a peripheral annular ring and a plurality of arms extending from the core to the ring.
  • the arms have resilient properties enabling the core to move axially relative to the peripheral ring and to return to a rest position.
  • each arm is curved partially circumventing the core prior to merging into a peripheral ring.
  • the seat-spring member is provided with an annular recess thinning the thickness of the arms, the under face of the peripheral ring and the flat face of the core being co-planar faces.
  • the invention further extends to a control valve assembly of a fuel injector comprising a body in which is arranged an electric solenoid adapted to generate a magnetic field when energized in order to move, between an open position and a closed position, a control valve member as set in anyone of the preceding paragraphs.
  • the invention further extends to a fuel injector comprising a control valve assembly as set in the preceding paragraph.
  • Figure 1 is a side view of a fuel injector having a partial section enabling to show the internal control valve assembly.
  • Figure 2 is a magnified view of the partial section of figure 1 showing a first embodiment of the control valve assembly as per the invention.
  • Figure 3 is an isometric bottom view of the valve member of figure 2.
  • Figure 4 is an isometric top view of the valve member of figure 2.
  • Figure 5 is a magnified view of the partial section of figure 1 showing a second embodiment of the control valve assembly as per the invention.
  • Figure 6 is an isometric bottom view of the valve member of figure 5.
  • Figure 7 is an isometric top view of the valve member of figure 5.
  • a fuel injector 10 having an elongated shape erecting along a main axis XI .
  • the injector 10 comprises from top to bottom the stack of an actuator assembly 12, a control valve assembly 14, a filling valve assembly 16 and a nozzle assembly 18.
  • the actuator assembly 12 comprises a cylindrical actuator body 20 axially XI extending from a top extremity 22, where is arranged an electrical connector 24, to a lower face 26 having a mirror surface finish in order to be in in sealing facial abutment against the upper face 28 of the body 30 of the filling valve assembly 16.
  • a bore 32, provided in the actuator body 20, opens in said lower face 26, said bore 32 upwardly extends along a valve axis X2 toward an upward bottom 34. From said bottom 34 upwardly extends a conduit for electrical cables to connect to the pins of the connector 24.
  • the control valve assembly 14 Inside the bore 32 is arranged the control valve assembly 14 now described.
  • the control valve assembly 14, magnified on figure 2 comprises a cylindrical solenoid 36 having its lower face 38 deep inside the bore 32, the lift being maintained by an annular spacer 40 press fitted in the bore 32, or adjusted in position between the lower face 38 of the solenoid and the upper face 28 of the body of the filling valve assembly.
  • a control valve chamber 42 is defined inside the spacer 40 and between the lower face 38 of the solenoid and the upper face 28 of the body of the filling valve assembly.
  • a control valve member 44 described afterward.
  • a first spring 46 is arranged compressed in a second bore 48 extending axially X2 inside the solenoid 36, the first spring 46 permanently axially X2 pushing the control valve member 44 away from the solenoid 36.
  • valve axis X2 is parallel and slightly offset from the main axis XI .
  • This characteristic introduced in EP0740068 presents multiple advantages. Nevertheless, although the injector illustrating the present invention is provided with offset axes, other injectors with aligned axes can also benefit from the invention.
  • the filling valve assembly 16 now described, has its body 30 extending from its upper face 28 to a distant lower face 50 that is in sealing facial abutment against the upper face 52 of the nozzle assembly 18.
  • a poppet valve member 54 axially X2 slidably guided in another bore 56 that largely opens in the lower face 50 of the filling valve and, from the upper end of said another bore 50 a small spill orifice 58 upwardly extends and opens in the upper face 28 of the body 30 in the centre of the control chamber 42, the opening of said spill orifice 58 being surrounded by a fixed valve seating surface 60.
  • the poppet valve member 54 is also provided with an axial X2 inner conduit 62 extending throughout the poppet valve member 54, the cross section of the conduit 62 being restricted its top end, just prior to opening right in front of the small spill orifice 58.
  • the poppet valve member 54 is permanently biased by a second spring 64 arranged compressed in an enlarged portion 66 of the bore 56.
  • the nozzle assembly 18 comprises an upper guide member 72 concentrically arranged on the top of a nozzle body 74, said nozzle body 74 defining, in the vicinity of the spray holes 70, a lower guide 76 that is axially XI aligned with a bore 78 provided in the upper guide member 72 so that, a needle valve member 80 is slidably guided between said bore 78 and the lower guide 76.
  • the needle valve 80 is permanently biased by a third spring 82 that is arranged around the needle 80 and compressed between a face of the upper guide member 72 and a shoulder face 84 of the needle 80.
  • the needle 80 axially XI extends from a head 86 slidably adjusted in the bore 78 to a pointy tip 88 that cooperates with an inner face of the nozzle body 74 in order to open or close the spray holes 70.
  • the portion of the bore 78 that is above the head 86 of the needle defines a control chamber 90 opening in the upper face 52 of the nozzle assembly, which is also the upper face of the upper guide member.
  • the poppet valve 54 and its inner conduit 62 largely open in the control chamber 90.
  • the constituents of the body of the injector 10 are maintained fixed together by an external injector capnut 92 that is inserted around the nozzle body 74, in abutment against an external shoulder face of said body 74, the capnut 92 upwardly extending around the upper guide member 72 and the filling valve assembly 16 to be screwed and tightened on the outer face of the actuator body 20.
  • the injector 10 is also provided with a high pressure fuel inlet circuit 94 and a fuel return circuit 96.
  • the inlet circuit 94 comprises a main conduit 98 having a series of aligned portions extending through the different bodies of the injector 10 from an inlet at the top end down to the spray holes 70.
  • Said inlet circuit 94 also comprises a secondary conduit 100 leading from the main conduit 98 to the enlarged portion 66 of the bore 56 that is in the filling valve assembly.
  • the return circuit 98 comprises the inner conduit 62 inside the poppet valve, the spill orifice 58 at the top of the filling body, the control valve chamber 42 and another conduit, not represented, extending to an outlet connectable to a low pressure reservoir.
  • a first embodiment of the control valve member 44 now described in detail in reference to figures 3 and 4, comprises a magnetic armature 102, a seat member 104 and a spring member 106 all fixedly attached together.
  • the armature 102 is made of magnetic material and, is a thick disc- like member axially X2 extending between an upper face 108 that faces the lower face 38 of the solenoid, and an opposed lower face 110.
  • the armature 102 is further provided with a central threaded orifice 112 extending throughout the axial thickness of the disc-like member.
  • the seat member 104 can be described as a hexagonal head screw having a male threaded connecting member 114 complementary tightened in the threaded orifice 112 of the armature, the head portion 116 of the screw being under the armature 102, the head portion 116 having an under annular face 118 facing the armature and, a flat external face 120 facing the fixed valve seating surface 60.
  • the spring member 106 is a spider spring made by stamping a metal sheet. It has a central annular core 122 from which three resilient limbs members 124 radially outwardly extend toward a distal end 126 where each limb 124 is bent upwardly forming a peripheral cylindrical portion 128, the three peripheral portions 128 surrounding the armature 102. As shown on the figures, the three limbs are equally distributed at 120° from each other. Alternatively, the spring member 106 could have two, four or more limbs, a preferred parameter being that they are arranged at equal angle from each other so that, when deflecting each limb generates the same force as the other limbs and the combined forces is axially X2 oriented. The spring member 106 is fixed to the armature as the central annular core 122 forms a washer compressed between the under annular face 118 of the head and the lower face 110 of the armature.
  • the spring member can be a thin disk- like leaf spring provided with a peripheral wall.
  • the peripheral wall as will be seen below, aiming at fixing the control valve member 44 in the control valve chamber 42 can get any desired shape fulfilling said purpose.
  • the seat member is described as threaded and tightened in the armature. In non-represented alternatives, any other type of fixation is also possible, such as welding, brazing, press fitting, crimping...
  • control valve member 44 is fixedly arranged in the control valve chamber 42, the external face of the peripheral portions 128 of the spring member being press fitted in the spacer 40.
  • the flat external face 120 of the head portion control valve member 44 is right above the fixed valve seating surface 60 and thanks to the resilient property of the limbs 124 and the axial X2 combined forces generated by said limbs 124, the spring member 106 axially X2 guides the valve member 44 in axial X2 translation.
  • a first phase the injection of fuel is prohibited as the needle 80 is in a downward closed position in complementary abutment against a seating face of the nozzle body 74, closing the access to the spray hole 70.
  • the solenoid 36 is not electrically energized and therefor the control valve member 44 is biased by the first spring 46 in a closed position where the flat under face 120 of the seat member 104 seals the fixed valve seating 60.
  • the poppet valve 54 is pushed in a downward open position by the second spring 64 and also under the influence of the fuel pressure filling the enlarged portion 66 of the bore 56.
  • a continuous fluid communication is open between the inlet circuit 94 and the control chamber 90 wherein pressure raises and maintains the needle 80 in the downward closed position.
  • an injection event is initiated by energizing the solenoid 36 which generates a magnetic field upwardly attracting the armature 102 toward the solenoid and therefore opening the spill orifice 58. It is to be noted that during its displacement the valve member 44 is guided by the spring member 106, all the limbs resiliently deflecting together. The high pressure fuel inside the control chamber 90 immediately flows out into the control valve chamber 42 wherefrom it continues in the return circuit 96 toward a low pressure reservoir.
  • the opening of the spill orifice 58 creates a sudden depressurisation upwardly aspiring the poppet valve 54 that moves in a closed position forbidding the entry of high pressure fuel in the control chamber 90.
  • a third phase the injection event started above is ended by stopping to energize the solenoid 36.
  • the first spring 46 downwardly pushes the control valve member 44 toward closing the spill orifice 58.
  • the valve member 44 is once again perfectly guided along the valve axis X2 by the spring member 106 which limbs 124 deflect together.
  • the pressure rises again in the control chamber 90 forcing the needle 80 toward the closed position.
  • the first spring 46 is no longer necessary and is removed.
  • the spring member 106 is arranged so that it permanently generates on the seat member 104 and the armature 102 an axial X2 downward force strong enough to force the seat member 104 back to closing the spill orifice 58 when the solenoid is no longer energized.
  • a second embodiment of the control valve member 44 is now described in reference to figures 5, 6 and 7 and, in limiting the description to the differences with the first embodiment, the features having similar function keeping the same numeral references.
  • the second embodiment comprises the magnetic armature 102 and an integral seat-spring member 140.
  • This integral seat-spring member 140 has a central core portion 142, having upwardly extending a threaded connecting member 144 fixedly tightened in the central threaded orifice 112 of the armature and, opposite the connecting member 144, a flat external face 146 is adapted to seal the fixed valve seating surface 60 of the spill orifice 58.
  • the integral seat- spring member 140 further comprises a peripheral annular ring 148 and three resilient arms 150 extending from the core 142 to the ring 148. Each arm 150 is curved in a transverse plan partially circumventing the core 142 prior to merging into a peripheral ring 148. Furthermore, the arms 150 are all identical and equally angularly distributed about the core 142.
  • the seat spring member could comprise two, or four, or any other number of resilient arms 150.
  • the seat spring member 140 radially extends throughout the control valve chamber 42, the outer face of peripheral ring 148 being in close vicinity to the inner face of the bore 32. Furthermore, the seat- spring member 140 is provided with an annular recess 152 arranged on its lower face facing the upper face 28 of the body of the filling valve assembly. Said recess 152 thins the thickness of the arms 150 while the flat face 146 and the under face of the peripheral ring 148 are coplanar.
  • the peripheral ring 148 is maintained in abutment against the upper face 28 of the body of the filling valve assembly by a ring spacer 154 arranged between the peripheral ring 148 and the lower face 38 of the solenoid.
  • the three arms are equally distributed at 120° from each other.
  • the spring member 106 could have two, four or more arms, a preferred parameter being that they are arranged at equal angle from each other so that, when deflecting each arm generates the same force as the other arms and the combined forces is axially X2 oriented to guide the core in its axial translations.
  • the solenoid When the solenoid is no longer energized, the first spring 46 pushes the core 142 downward in the closing position of the spill orifice 58 and the arms 150 return to a rest position.
  • the first spring 46 is no longer necessary and is removed and, when being deflected, the combined resiliency of the arms 150 is strong enough so that they generate a downward force that is sufficient to force the core 142 back to closing the spill orifice 58 when the solenoid is no longer energized.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

A control valve member (44) of a fuel injector control valve assembly (14) adapted to be arranged in a control valve chamber (42) wherein it is guided in translation along a valve axis (X2) between a closed position forbidding fuel to exit a spill orifice (58) and an open position enabling fuel to exit said spill orifice (58), the control valve member (44) comprising a magnetic armature (102) to which is fixed a seat member (104). The armature (102) is adapted to cooperate with an electromagnetic solenoid (36) in order for the seat member (104) be move between the closed position wherein it is in sealing abutment against a fixed seating face (60), and the open position wherein said seat member (104) is lifted away from said fixed seating face (60). The control valve member (44) further comprises a spring member adapted to guide in translation along the valve axis (X2) the seat member (104) in the control valve chamber (42).

Description

Control valve arrangement TECHNICAL FIELD
The present invention relates generally to a fuel injector and more particularly to a control valve arrangement.
BACKGROUND OF THE INVENTION
In a fuel injector, a control valve indirectly controls the displacements of a valve member, or needle, in order to enable or forbid fuel injection through the nozzle. The control valve generally comprises a body in which is arranged an electromagnetic solenoid provided with a central bore, a compression spring arranged in said bore and, an armature and spool assembly slidably guided along a valve axis in a hydraulic distribution bore provided in the body. The armature and spool assembly comprises a magnetic armature that is a thick disc-like member having an upper face and an under face and a central through orifice and also, a spool stem inserted an crimped in the central orifice, the spool being a cylindrical shaft having a top end flush with the upper surface of the armature, the spool protruding from the under face and extending in the hydraulic bore toward a distal bottom end.
In operation, the spring is compressed between the bottom of the solenoid's central bore and the top end of the stem, so that it permanently pushes the armature and spool assembly away from the solenoid and when the solenoid is electrically energized, a magnetic field attracting the armature and spool assembly toward the solenoid is generated, the armature and spool assembly spool moving to an open position and further compressing the spring.
The spool must be guided with minimal clearance inside the hydraulic bore and also with very precise alignment to the solenoid to avoid friction from sideloads caused by concentricity or parallelism errors between the solenoid and the armature. Such accuracy is costly and even with the most accurate machining possible, these effects can still generate shot-shot variation of fuelling. Another problem is that as fuel pressures increase, so does the fuel temperature, which can cause fuel lacquer to form on the valve guide, adding a further source of friction. SUMMARY OF THE INVENTION
It is an object of the invention to resolve or at least mitigate the above mentioned problem in proposing a control valve member of a fuel injector control valve assembly adapted to be arranged in a control valve chamber. The control valve member is guided in translation along a valve axis between a closed position forbidding fuel to exit a spill orifice and an open position enabling fuel to exit said spill orifice. The control valve member comprises a magnetic armature to which is fixed a seat member and, the armature is adapted to cooperate with an electromagnetic solenoid in order for the seat member be move between the closed position wherein it is in sealing abutment against a fixed seating face, and the open position wherein said seat member is lifted away from said fixed seating face.
The control valve member further comprises a spring member adapted to guide in translation along the valve axis the seat member in the control valve chamber.
The armature is a thick disc-like member axially extending between an upper face and an opposed lower face and, the seat member comprises a connecting portion fixed to the armature and, a head portion having a sealing face adapted to abut the fixed seating face in closed position, the head portion being on the side of the lower face of the armature.
More particularly, the seat member may a screw which male threaded member is tightened in a threaded orifice centrally provided in the armature, the head portion of the screw being of a larger cross section than the connecting male threaded member.
Also, the spring member is a spider spring provided with a plurality of resilient limbs radially extending from a common core to a distal end adapted to be fixed in the control valve chamber.
The core of the spring member is centrally holed so that the connecting portion of the seat member can be inserted in said hole prior to be tightened in the armature so that, the spring member is fixedly trapped between the lower face of the armature and the head of the control valve member.
Also, the resilient limbs further comprise a peripheral portion erecting from the distal end of each resilient limb, perpendicularly to the limbs, the peripheral portions surrounding the armature and being adapted to be press fitted against the inner peripheral wall of the valve member chamber.
In a second embodiment, the spring member is integral to the seat member forming an integral seat-spring member.
Said integral seat-spring member has a central core portion having upwardly extending a threaded connecting member fixedly tightened in the central threaded orifice of the armature and, a flat external face adapted to seal the spill orifice. The integral seat-spring member further comprises a peripheral annular ring and a plurality of arms extending from the core to the ring.
More particularly, the arms have resilient properties enabling the core to move axially relative to the peripheral ring and to return to a rest position.
Also, each arm is curved partially circumventing the core prior to merging into a peripheral ring.
Also, the seat-spring member is provided with an annular recess thinning the thickness of the arms, the under face of the peripheral ring and the flat face of the core being co-planar faces.
The invention further extends to a control valve assembly of a fuel injector comprising a body in which is arranged an electric solenoid adapted to generate a magnetic field when energized in order to move, between an open position and a closed position, a control valve member as set in anyone of the preceding paragraphs.
The invention further extends to a fuel injector comprising a control valve assembly as set in the preceding paragraph. BRIEF DESCRIPTION OF THE DRAWINGS
The present invention is now described by way of example with reference to the accompanying drawings in which:
Figure 1 is a side view of a fuel injector having a partial section enabling to show the internal control valve assembly.
Figure 2 is a magnified view of the partial section of figure 1 showing a first embodiment of the control valve assembly as per the invention.
Figure 3 is an isometric bottom view of the valve member of figure 2.
Figure 4 is an isometric top view of the valve member of figure 2. Figure 5 is a magnified view of the partial section of figure 1 showing a second embodiment of the control valve assembly as per the invention.
Figure 6 is an isometric bottom view of the valve member of figure 5.
Figure 7 is an isometric top view of the valve member of figure 5.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
In reference to figure 1 is presented a fuel injector 10 having an elongated shape erecting along a main axis XI . According to the arbitrary and non-limiting orientation of the figure, the injector 10 comprises from top to bottom the stack of an actuator assembly 12, a control valve assembly 14, a filling valve assembly 16 and a nozzle assembly 18.
The actuator assembly 12 comprises a cylindrical actuator body 20 axially XI extending from a top extremity 22, where is arranged an electrical connector 24, to a lower face 26 having a mirror surface finish in order to be in in sealing facial abutment against the upper face 28 of the body 30 of the filling valve assembly 16. A bore 32, provided in the actuator body 20, opens in said lower face 26, said bore 32 upwardly extends along a valve axis X2 toward an upward bottom 34. From said bottom 34 upwardly extends a conduit for electrical cables to connect to the pins of the connector 24. Inside the bore 32 is arranged the control valve assembly 14 now described.
The control valve assembly 14, magnified on figure 2 comprises a cylindrical solenoid 36 having its lower face 38 deep inside the bore 32, the lift being maintained by an annular spacer 40 press fitted in the bore 32, or adjusted in position between the lower face 38 of the solenoid and the upper face 28 of the body of the filling valve assembly. As visible on figure 2, a control valve chamber 42 is defined inside the spacer 40 and between the lower face 38 of the solenoid and the upper face 28 of the body of the filling valve assembly. In said control valve chamber 42 is arranged a control valve member 44 described afterward. Furthermore, a first spring 46 is arranged compressed in a second bore 48 extending axially X2 inside the solenoid 36, the first spring 46 permanently axially X2 pushing the control valve member 44 away from the solenoid 36.
As visible on the figure, the valve axis X2 is parallel and slightly offset from the main axis XI . This characteristic introduced in EP0740068 presents multiple advantages. Nevertheless, although the injector illustrating the present invention is provided with offset axes, other injectors with aligned axes can also benefit from the invention.
The filling valve assembly 16, now described, has its body 30 extending from its upper face 28 to a distant lower face 50 that is in sealing facial abutment against the upper face 52 of the nozzle assembly 18. In said body 30 is arranged a poppet valve member 54 axially X2 slidably guided in another bore 56 that largely opens in the lower face 50 of the filling valve and, from the upper end of said another bore 50 a small spill orifice 58 upwardly extends and opens in the upper face 28 of the body 30 in the centre of the control chamber 42, the opening of said spill orifice 58 being surrounded by a fixed valve seating surface 60.
The poppet valve member 54 is also provided with an axial X2 inner conduit 62 extending throughout the poppet valve member 54, the cross section of the conduit 62 being restricted its top end, just prior to opening right in front of the small spill orifice 58. The poppet valve member 54 is permanently biased by a second spring 64 arranged compressed in an enlarged portion 66 of the bore 56.
The nozzle assembly 18, now described, axially XI extends from the upper face 52 previously introduced to a tip end 68 provided with spray holes 70. In the example described the nozzle assembly 18 comprises an upper guide member 72 concentrically arranged on the top of a nozzle body 74, said nozzle body 74 defining, in the vicinity of the spray holes 70, a lower guide 76 that is axially XI aligned with a bore 78 provided in the upper guide member 72 so that, a needle valve member 80 is slidably guided between said bore 78 and the lower guide 76. The needle valve 80 is permanently biased by a third spring 82 that is arranged around the needle 80 and compressed between a face of the upper guide member 72 and a shoulder face 84 of the needle 80.
The needle 80 axially XI extends from a head 86 slidably adjusted in the bore 78 to a pointy tip 88 that cooperates with an inner face of the nozzle body 74 in order to open or close the spray holes 70. The portion of the bore 78 that is above the head 86 of the needle defines a control chamber 90 opening in the upper face 52 of the nozzle assembly, which is also the upper face of the upper guide member. As visible on figure 2, the poppet valve 54 and its inner conduit 62 largely open in the control chamber 90.
The constituents of the body of the injector 10 are maintained fixed together by an external injector capnut 92 that is inserted around the nozzle body 74, in abutment against an external shoulder face of said body 74, the capnut 92 upwardly extending around the upper guide member 72 and the filling valve assembly 16 to be screwed and tightened on the outer face of the actuator body 20.
As visible on the figure, the injector 10 is also provided with a high pressure fuel inlet circuit 94 and a fuel return circuit 96. The inlet circuit 94 comprises a main conduit 98 having a series of aligned portions extending through the different bodies of the injector 10 from an inlet at the top end down to the spray holes 70. Said inlet circuit 94 also comprises a secondary conduit 100 leading from the main conduit 98 to the enlarged portion 66 of the bore 56 that is in the filling valve assembly. The return circuit 98 comprises the inner conduit 62 inside the poppet valve, the spill orifice 58 at the top of the filling body, the control valve chamber 42 and another conduit, not represented, extending to an outlet connectable to a low pressure reservoir.
A first embodiment of the control valve member 44, now described in detail in reference to figures 3 and 4, comprises a magnetic armature 102, a seat member 104 and a spring member 106 all fixedly attached together.
The armature 102 is made of magnetic material and, is a thick disc- like member axially X2 extending between an upper face 108 that faces the lower face 38 of the solenoid, and an opposed lower face 110. The armature 102 is further provided with a central threaded orifice 112 extending throughout the axial thickness of the disc-like member.
The seat member 104 can be described as a hexagonal head screw having a male threaded connecting member 114 complementary tightened in the threaded orifice 112 of the armature, the head portion 116 of the screw being under the armature 102, the head portion 116 having an under annular face 118 facing the armature and, a flat external face 120 facing the fixed valve seating surface 60.
The spring member 106 is a spider spring made by stamping a metal sheet. It has a central annular core 122 from which three resilient limbs members 124 radially outwardly extend toward a distal end 126 where each limb 124 is bent upwardly forming a peripheral cylindrical portion 128, the three peripheral portions 128 surrounding the armature 102. As shown on the figures, the three limbs are equally distributed at 120° from each other. Alternatively, the spring member 106 could have two, four or more limbs, a preferred parameter being that they are arranged at equal angle from each other so that, when deflecting each limb generates the same force as the other limbs and the combined forces is axially X2 oriented. The spring member 106 is fixed to the armature as the central annular core 122 forms a washer compressed between the under annular face 118 of the head and the lower face 110 of the armature.
In another alternative not represented the spring member can be a thin disk- like leaf spring provided with a peripheral wall. Furthermore, the peripheral wall, as will be seen below, aiming at fixing the control valve member 44 in the control valve chamber 42 can get any desired shape fulfilling said purpose. Also, the seat member is described as threaded and tightened in the armature. In non-represented alternatives, any other type of fixation is also possible, such as welding, brazing, press fitting, crimping...
In reference to figure 2, the control valve member 44 is fixedly arranged in the control valve chamber 42, the external face of the peripheral portions 128 of the spring member being press fitted in the spacer 40. In place, the flat external face 120 of the head portion control valve member 44 is right above the fixed valve seating surface 60 and thanks to the resilient property of the limbs 124 and the axial X2 combined forces generated by said limbs 124, the spring member 106 axially X2 guides the valve member 44 in axial X2 translation.
In operation, when arranged in fuel injection equipment, fuel at high pressure enters via the inlet and fills the inlet circuit 94. The principle of operation of the fuel injector 10 is similar to the description provided in application PCT/EP2014/063810. Said principle is briefly recalled here below.
In a first phase the injection of fuel is prohibited as the needle 80 is in a downward closed position in complementary abutment against a seating face of the nozzle body 74, closing the access to the spray hole 70. The solenoid 36 is not electrically energized and therefor the control valve member 44 is biased by the first spring 46 in a closed position where the flat under face 120 of the seat member 104 seals the fixed valve seating 60. Also, the poppet valve 54 is pushed in a downward open position by the second spring 64 and also under the influence of the fuel pressure filling the enlarged portion 66 of the bore 56. A continuous fluid communication is open between the inlet circuit 94 and the control chamber 90 wherein pressure raises and maintains the needle 80 in the downward closed position.
In a second phase an injection event is initiated by energizing the solenoid 36 which generates a magnetic field upwardly attracting the armature 102 toward the solenoid and therefore opening the spill orifice 58. It is to be noted that during its displacement the valve member 44 is guided by the spring member 106, all the limbs resiliently deflecting together. The high pressure fuel inside the control chamber 90 immediately flows out into the control valve chamber 42 wherefrom it continues in the return circuit 96 toward a low pressure reservoir. Thanks to the small volume that is in the bore 56 right above the poppet valve 54, the opening of the spill orifice 58 creates a sudden depressurisation upwardly aspiring the poppet valve 54 that moves in a closed position forbidding the entry of high pressure fuel in the control chamber 90.
In a third phase the injection event started above is ended by stopping to energize the solenoid 36. The first spring 46 downwardly pushes the control valve member 44 toward closing the spill orifice 58. In this downward translation, the valve member 44 is once again perfectly guided along the valve axis X2 by the spring member 106 which limbs 124 deflect together. Similarly to the first phase, the pressure rises again in the control chamber 90 forcing the needle 80 toward the closed position.
In a non-represented alternative to this first embodiment, the first spring 46 is no longer necessary and is removed. The spring member 106 is arranged so that it permanently generates on the seat member 104 and the armature 102 an axial X2 downward force strong enough to force the seat member 104 back to closing the spill orifice 58 when the solenoid is no longer energized. A second embodiment of the control valve member 44 is now described in reference to figures 5, 6 and 7 and, in limiting the description to the differences with the first embodiment, the features having similar function keeping the same numeral references. The second embodiment comprises the magnetic armature 102 and an integral seat-spring member 140. This integral seat-spring member 140 has a central core portion 142, having upwardly extending a threaded connecting member 144 fixedly tightened in the central threaded orifice 112 of the armature and, opposite the connecting member 144, a flat external face 146 is adapted to seal the fixed valve seating surface 60 of the spill orifice 58. The integral seat- spring member 140 further comprises a peripheral annular ring 148 and three resilient arms 150 extending from the core 142 to the ring 148. Each arm 150 is curved in a transverse plan partially circumventing the core 142 prior to merging into a peripheral ring 148. Furthermore, the arms 150 are all identical and equally angularly distributed about the core 142. Alternatively, the seat spring member could comprise two, or four, or any other number of resilient arms 150.
As better visible on figure 5, the seat spring member 140 radially extends throughout the control valve chamber 42, the outer face of peripheral ring 148 being in close vicinity to the inner face of the bore 32. Furthermore, the seat- spring member 140 is provided with an annular recess 152 arranged on its lower face facing the upper face 28 of the body of the filling valve assembly. Said recess 152 thins the thickness of the arms 150 while the flat face 146 and the under face of the peripheral ring 148 are coplanar.
Also, in the control valve chamber 42, the peripheral ring 148 is maintained in abutment against the upper face 28 of the body of the filling valve assembly by a ring spacer 154 arranged between the peripheral ring 148 and the lower face 38 of the solenoid.
In operation, when the solenoid 36 is energized, the armature 102 is upwardly attracted, the spacer 154 maintains the peripheral ring 128 in place against the upper face 28 of the body of the filling valve, the arms 150 resiliently deflect together and, the core 142 upwardly moves along with the armature 102 therefor opening the spill orifice 58.
As shown on the figures, the three arms are equally distributed at 120° from each other. Alternatively, the spring member 106 could have two, four or more arms, a preferred parameter being that they are arranged at equal angle from each other so that, when deflecting each arm generates the same force as the other arms and the combined forces is axially X2 oriented to guide the core in its axial translations.
When the solenoid is no longer energized, the first spring 46 pushes the core 142 downward in the closing position of the spill orifice 58 and the arms 150 return to a rest position.
In a non-represented alternative, the first spring 46 is no longer necessary and is removed and, when being deflected, the combined resiliency of the arms 150 is strong enough so that they generate a downward force that is sufficient to force the core 142 back to closing the spill orifice 58 when the solenoid is no longer energized.
LIST OF REFERENCES
XI main axis
X2 valve axis
10 injector
12 actuator assembly
14 control valve assembly
16 filing valve assembly
18 nozzle assembly
20 actuator body
22 top extremity of the actuator body
24 electrical connector
26 lower face of the actuator body
28 upper face of the body of the filling valve assembly
30 body of the filling valve assembly
32 bore
34 upward bottom of the bore
36 solenoid
38 lower face of the solenoid
40 spacer
42 control valve chamber
44 control valve member
46 first spring
48 second bore inside the solenoid
50 lower face of the filling valve body 52 upper face of the nozzle assembly
54 poppet valve
56 bore of the poppet valve
58 spill orifice
60 fixed valve seating surface
62 inner conduit inside the poppet valve
64 second spring
66 enlarged portion of the bore
68 tip end of the nozzle
70 spray holes
72 upper guide member
74 nozzle body
76 lower guide
78 bore in the upper guide member
80 needle valve member
82 third spring
84 shoulder face
86 head of the needle
88 pointy tip of the needle
90 control chamber
92 capnut
94 inlet circuit
96 return circuit
98 main inlet conduit
100 secondary inlet conduit
102 magnetic armature
104 seat member
106 spring member
108 upper face of the armature
110 lower face of the armature
112 threaded orifice
114 threaded connecting member of the valve member
116 head portion
118 under annular face of the head
120 flat external face
122 central annular core of the spring member
124 limbs of the spring member
126 distal ends of a limb
128 peripheral portion
140 seat spring member
142 central core portion of the seat spring member
144 threaded connecting member of the seat spring member flat face of the seat spring member peripheral ring
resilient arm
annular recess
ring spacer

Claims

1. Control valve member (44) of a fuel injector control valve assembly (14) adapted to be arranged in a control valve chamber (42) wherein it is guided in translation along a valve axis (X2) between a closed position forbidding fuel to exit a spill orifice (58) and an open position enabling fuel to exit said spill orifice (58), the control valve member (44) comprising a magnetic armature (102) to which is fixed a seat member (104) wherein,
the armature (102) is adapted to cooperate with an electromagnetic solenoid (36) in order for the seat member (104) be move between the closed position wherein it is in sealing abutment against a fixed seating face (60), and the open position wherein said seat member (104) is lifted away from said fixed seating face (60), characterized in that
the control valve member (44) further comprises a spring member (106) adapted to guide in translation along the valve axis (X2) the seat member (104) in the control valve chamber (42) and wherein,
the armature (102) is a thick disc-like member axially (X2) extending between an upper face (108) and an opposed lower face (110), the seat member (104) comprising a connecting portion (114) fixed to the armature (102) and, a head portion (116) having a sealing face (120) adapted to abut the fixed seating face (60) in closed position, the head portion (116) being on the side of the lower face (110) of the armature and wherein,
the spring member (106) is a provided with a plurality of resilient limbs (124) extending from a common core (122) to a distal end adapted to be fixed in the control valve chamber (42) and wherein,
said core (122) is centrally holed so that the connecting portion (114) of the seat member (104) can be inserted in said hole prior to be tightened in the armature (102) so that, the spring member (106) is fixedly trapped between the lower face (110) of the armature and the head (116) of the control valve member.
2. Control valve member (44) as claimed in claim 1 wherein the seat member (104) is a screw which male threaded member is tightened in a threaded orifice (112) centrally provided in the armature (102), the head portion (116) of the screw being of a larger cross section than the connecting male threaded member.
3. Control valve member (44) as claimed in claim 2 wherein the spring member (106) is a spider spring, the resilient limbs (124) radially extending from the common core (122).
4. Control valve member (44) as claimed in any one of the preceding claims wherein the resilient limbs (124) further comprise a peripheral portion (128) erecting from the distal end of each resilient limb (124), perpendicularly to the limbs, the peripheral portions (128) surrounding the armature (102) and being adapted to be press fitted against the inner peripheral wall of the valve member chamber (42).
5. Control valve member (44) as claimed in claim 3, wherein the spring member is integral to the seat member forming an integral seat-spring member
(140).
6. Control valve member (44) as claimed in claim 5 wherein the integral seat- spring member (140) has a central core portion (142) having upwardly extending a threaded connecting member (144) fixedly tightened in the central threaded orifice (112) of the armature and, a flat external face (146) adapted to seal the spill orifice (58), the integral seat-spring member (140) further comprising a peripheral annular ring (148) and a plurality of arms (150) extending from the core (142) to the ring (148).
7. Control valve member (44) as claimed in claim 6 wherein the arms (150) have resilient properties enabling the core (142) to move axially (X2) relative to the peripheral ring (148) and to return to a rest position.
8. Control valve member (44) as claimed in claim 7 wherein each arm (150) is curved partially circumventing the core (142) prior to merging into a peripheral ring (148).
9. Control valve member (44) as claimed in any one of the claims 7 or 8 wherein the seat-spring member (140) is provided with an annular recess (152) thinning the thickness of the arms (150), the under face of the peripheral ring (148) and the flat face (146) of the core being co-planar faces.
10. Control valve assembly (14) of a fuel injector (10) comprising a body (20) in which is arranged an electric solenoid (36) adapted to generate a magnetic field when energized in order to move, between an open position and a closed position, a control valve member (44) as set in anyone of the preceding claims.
11. Fuel injector (10) comprising a control valve assembly (14) as set in claim 10.
EP16702730.9A 2015-03-25 2016-02-03 Control valve arrangement Active EP3274583B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB1505004.0A GB201505004D0 (en) 2015-03-25 2015-03-25 Control valve arrangement
PCT/EP2016/052304 WO2016150604A1 (en) 2015-03-25 2016-02-03 Control valve arrangement

Publications (2)

Publication Number Publication Date
EP3274583A1 true EP3274583A1 (en) 2018-01-31
EP3274583B1 EP3274583B1 (en) 2021-09-29

Family

ID=53052346

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16702730.9A Active EP3274583B1 (en) 2015-03-25 2016-02-03 Control valve arrangement

Country Status (3)

Country Link
EP (1) EP3274583B1 (en)
GB (1) GB201505004D0 (en)
WO (1) WO2016150604A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB201518923D0 (en) 2015-10-27 2015-12-09 Delphi Internat Operations Luxembourg S À R L Control valve arrangement of a fuel injector
CN107524551B (en) * 2017-08-31 2020-01-31 重庆红江机械有限责任公司 micro-injection electric control oil injector with pressure maintaining structure

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2550297A (en) * 1944-09-04 1951-04-24 Gen Controls Co Electromagnetically operated valve
US2911183A (en) * 1955-04-07 1959-11-03 Baso Inc Magnetic valves
DE2303450A1 (en) * 1973-01-25 1974-08-22 Kirchheim E Heinrich Dipl Kfm MAGNETIC VALVE
US4196751A (en) * 1976-01-15 1980-04-08 Johnson Controls, Inc. Electric to fluid signal valve unit
DE19851143B4 (en) * 1998-11-06 2009-03-12 Steuerungstechnik Staiger Gmbh & Co. Produktions-Vertriebs-Kg Valve
US6220569B1 (en) * 2000-01-07 2001-04-24 Clippard Instrument Laboratory, Inc. Electrically controlled proportional valve
JP4296081B2 (en) * 2003-12-09 2009-07-15 シーケーディ株式会社 solenoid valve
SE531951C2 (en) * 2007-06-20 2009-09-15 So Elektronik Ab Electromechanical valve

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GB201505004D0 (en) 2015-05-06
WO2016150604A1 (en) 2016-09-29
EP3274583B1 (en) 2021-09-29

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