US3647177A - Alternating current solenoids - Google Patents

Alternating current solenoids Download PDF

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Publication number
US3647177A
US3647177A US830342A US3647177DA US3647177A US 3647177 A US3647177 A US 3647177A US 830342 A US830342 A US 830342A US 3647177D A US3647177D A US 3647177DA US 3647177 A US3647177 A US 3647177A
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armature
housing
core
portions
fluid
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Gregor L Lang
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—Lift valves
    • F16K31/0658—Armature and valve member being one single element

Definitions

  • FIGIS INVENTOR. GREGOR L. LANG ALTERNATING CURRENT SOLENOIDS BACKGROUND This invention relates to alternating current electromagnets useful in solenoid devices such as relays, actuators, and particularly in magnetic fluid control valves of the type used to control the flow of gases or liquids under pressure in a closed system.
  • solenoid fluid control valves In the design of solenoid fluid control valves it has been the practice to provide a cylindrical plunger guide or cap member of nonmagnetic material to serve as a housing for the movable valve plunger and a return biasing spring.
  • the housing with appropriate gasketed assembly to the valve body, confines within. the cup whatever fluid is controlled by the valve.
  • Such constructions are often referred to as wet armature" valves.
  • the exciting coil is provided with a magnetic shell and cylindrical pole members, designed to conduct the flux to the vicinity of the plunger housing with a minimum of gaps or magnetic discontinuities, to thereby attain a relatively high magnetic efficiency.
  • the coil is commonly assembled about the housing, such that when energized, the magnetic flux path is through the wall of the nonmagnetic housing and the plunger-armature.
  • U.S. Pat. Nos. 2,627,544 and 2,936,790 illustrate typical examples of solenoid valves constructed as described.
  • the wall, thickness of the cup forms a gap across which. the flux must pass twice, on entering and leaving the armature.
  • the plunger cup be of appreciable wall thickness, a typical value for a brass or bronze housing being 0.026 inch for a fluid pressure of 125 p.s.i.
  • the wall thickness represents an equivalent gap of 0.052 inch in an otherwise closed magnetic circuit.
  • the cup or guide housing the armature may be constructed of thin ferromagnetic material such as A.I.S.I. type 430 stainless steel, chosen from the group known as straight chrome ferritic.
  • armature housings can be constructed with thin wall sections of adequate strength to withstand the fluid pressures encountered in such valves.
  • the use of a magnetic material has the effect of essentially eliminating the magnetic gap invariably encountered in previous wet armature valves.
  • Another object is to provide for a. magnetic fluid valve of the above type, a construction wherein for a. given fluid load on the annature, the required electrical power is reduced whereby the amount of copper in the solenoid winding can be greatly reduced.
  • a further object is to provide for a magnetic fluid valve of the above type, a solenoid and magnetic circuit construction of such new and novel character that the required electrical input power per unit of fluid pressure or fluid flow is decreased, whereby the heat dissipation and time rate of temperature rise of said solenoid is reduced over-prior constructions.
  • Another object is to provide for a magnetic fluid valve of the immersed armature type, a solenoid and magnetic circuit of new and novel character enabling increased armature forces, and increased fluid loads, pressures, and flowrates, for a given value of electrical input power.
  • a still further object is to provide for a magnetic fluid control valve, an armature housing constructed of ferromagnetic material having the property of hysteresis, to coact with a phase splitting core of the type described in my copendingapplication Ser. No. 783,035, filed Dec. 1 l, 1968, now U.S. Pat. No. 3,553,618.
  • the phase-shifting effectiveness is further improved with resulting further improvement of the solenoid magnetic efficiency.
  • Another important object is to provide an electromagnetic construction of high efficiency for use in hermetically sealed devices commonly used in vacuum or explosionproof systems wherein complete isolation by an impermeable barrier is requisite between the electrical energizing and magnetically actuated elements of said devices.
  • An additional object is to provide a solenoid construction wherein a housing or guide for the armature is constructed of ferromagnetic material, whereby'the distribution of'magnetic flux in and around said armature is controlled to yield an improved force-versus-distance characteristic, to thereby increase the wide gap pull value attained by said solenoid.
  • Yet another object is the provision in a flow control valve, of an armature and a closely fitting magnetic housing which is characterized by a motion-inhibiting piston or dashpot effect, serving to reduce the tendency of the valve to produce hydraulic noise or water hammer effects.
  • FIG. I is a cross-sectional view of a fluid valve embodying a solenoid according to this invention.
  • FIG. 2 is a sectioned partial view showing an alternative solenoid construction according to my copending application Ser. No. 783,035 for Phase Splitting Core, in combination herewith.
  • FIG. 3 is an enlarged partially sectioned view of the assembly of the magnetic core of FIG. 2.
  • valve solenoid having an armature housing constructed of ferromagnetic material of relatively thin wall section, behaves in an unexpectedly opposite manner to that previously postulated.
  • the pulling force per unit of input power is greatly in excess of the values obtained with the use of nonmagnetic material in said housing.
  • FIG. 1 is a median sectional view of a solenoid flow control valve according to the present invention in which cylindrical armature 1, and bias spring 2, are enclosed by armature housing 3, said housing being constructed of ferromagnetic material, and so dimensioned as to permit free axially slidable motion therein by plunger-armature l.
  • Armature l is formed with a projecting valve stem portion 4, having atits lower end an integrally formed conical valve portion designed to enter and seal fluid orifice 6 under the influence of bias spring 2, when the valve is deenergized or closed.
  • Bias spring 2 is of the conical compression type having its large diameter upper end supported by annular shoulder portion 11 formed in housing member 3, and having its small diameter end engaged with valve stem 4 by snapring 7, or other suitable means. Compression spring 2 thus biases armature 1 in a downward direction such as to seal fluid orifice 6 when the valve is deenergized. When so biased the upper surface of armature l is separated from the inner abutting surface of magnetic cup 3, thus forming working gap 8 which allows upward motion of armature 1, when the solenoid is energized.
  • Valve body 9 is formed of plastic or metal, and is provided with inlet pipefitting l4, and outlet fitting 22, which are connected by integrally formed fluid passages with the appropriate sides of the valve means.
  • Inlet 14 is provided with an annular recess 16, adapted to receive wire mesh inlet strainer 15 which serves to prevent fluid-home particulate matter from entering the valve.
  • Inlet 14 is connected by fluid duct 17 to annular fluid channel 18, whereby the incoming fluid is conducted to thepressure chamber formed by the inside of the conical portion 12 of plunger housing 3.
  • the peripheral flange portion 13. of housing 3 is pressed into sealing contact with elastic sealing ring 20, by the downward force exerted on annular pressure plate 19, by a number of appropriately spaced assembly screws, not shown.
  • Fluid seal ring 20, formed of an elastomer is seated in annular channel 21 formed in valve body 9. Elastic ring 20 thus forms a compressibly deformed seal which confines the pressurized incoming fluid to the inside of said conical pressure chamber.
  • Outlet fitting 22 is formed by a downward projecting portion of valve body 9, generally tubular in form, and positioned coaxial with armature plunger 1.
  • Outlet fluid duct 23 extends upward to connect with fluid passage 24 which passes vertically through annular valve seat member 25.
  • Valve member 25 is molded of elastomeric material and is dimensioned to fit snugly inannular recess 26 formed in valve body 9, coaxial with fluid duct 23, and forming the upper extremity thereof.
  • Fluid orifice 6 forms the valve seat proper, being normally sealed by the engagement thereagainst of valve cone 5, when the solenoid is deenergized.
  • Fluid passage 24 forms a flow limiting restriction, the diameter being appropriate to the fluid pressure, viscosity, and flow rate desired.
  • the magnetic solenoid is assembled over the cylinder cup portion of housing 3, coaxial therewith.
  • the solenoid is comprised of copper winding 27, on insulating spool 28, and is connected to the external power source by terminals or leads 29.
  • the winding encloses soft iron core piece 30, and is enclosed by mild steel magnetic outer shell 31, to which pole piece 30 is attached at top center 32.
  • Magnetic shell 31 has in its lower surface a bore or hole dimensioned to fit snugly over the cylindrical cup portion of housing 3 which extends into winding spool 28 to abut the lower end of core piece 30, thus completing the magnetic circuit linking solenoid 27 in an effectively closed manner.
  • a dimensional length of core 30 equal to 75 percent of the length of solenoid winding 27 has yielded good results in tests.
  • FIG. 1 depicts the valve in deenergized state, with armature l in the downward position thus forming axial gap 8 separating armature 1 from the diaphragm portion 33 of housing 3.
  • the magnetomotive force deriving from the current flowing in solenoid 27 gives rise to a concentration of flux flowing axially in the thin cylindrical wall of housing 3, with a resulting saturation of the wall.
  • the excess of available flux lines beyond the saturation level is thus diverted radially through the wall of housing 3, thence axially through armature 1, across gap 8 and through diaphragm 33 to core 30, thus developing a pulling force which raises armature 1, compressing spring 2, and opening passage 24 to allow the flow of fluid therethrough.
  • the housing wall operates in two difi'ering and sequential magnetic states, varied by the motion or position of armature 1.
  • the housing wall becomes saturated by the high inrush current at energization, followed by a transition into a less saturated state as armature 1 reaches the full stroke or zero gap position, with coil current dropping to the lower steady-state value.
  • Both states result in the transfer of major values of flux into and through armature 1, thereby causing said armature to develop useful values of mechanical pulling force.
  • armature 1 with a closely fitted housing 3, as disclosed in FIG. 1 provides further functional benefits resulting from an inherent dashpot orfluid damping effect. Said damping effect serves to reduce the tendency of an AC solenoid to produce intermittent pull forces and buzzing sounds, when phase-splitting means are not employed, as in FIG. 1 where core piece is of the simple cylindrical type.
  • the diametral clearance between armature 1 and housing 3 may be varied to control the damping and rate of movement of armature l, as the controlled fluid enters and leaves gap area 8.
  • the force and rate of bias spring 2 becomes an important design factor, since spring force together with the above armature diametral clearance, are basic in determining the rate at which armature 1 moves downward after deenergization of solenoid 27.
  • the above damping effect may be further modified for fluids of varying viscosity by providing an axially aligned fluid passage through armature l, or by providing axially aligned leakage grooves in the periphery of said armature.
  • the fluid damping serves beneficially to reduce the tendency of the valve to produce hydraulic-hammer and other fluid surge or transient effects arising from rapid armature motion.
  • FIG. 2 depicts a solenoid construction in which a phase splitting core of a self-shading type described in my copending patent application Ser. No. 783,035 is used in lieu of the plain cylindrical core 30 of FIG. 1, yielding a further major improvement in magnetic efficiency and pull force, over the values obtainable with said cylindrical iron core.
  • the solenoid construction of FIG. 2 is directly usable with the valve construction of FIG. 1, the related valve description thus being applicable to FIG. 2.
  • the twopiece annular core 34 and 35 makes use of the discovered fact that hysteresis and eddy currents in flux carrying core members may be economically and efficiently used to obtain phase retardation and resultant phase splitting in AC devices in lieu of shading rings previously used for that purpose.
  • the core assembly including soft iron outer sleeve 34, and mild steel inner cylindrical member 35, is shown in section in FIG. 2, and also in an enlarged partially sectioned view in FIG. 3 which discloses the annular and peripheral gap means which contribute to the phase splitting function and high magnetic efficiency of said core assembly.
  • Outer cylindrical core member 34 is the leading phase flux path, being designed to introduce a minimum of phase retardation of the flux wave flowing therein. To that end it is constructed of a low hysteresis material such as silicon steel of annealed ingot iron. It is further provided with a longitudinal slot 36, which extends the full length of said sleeve thus interrupting the phase retarding circumferential circulating current which would otherwise flow therein.
  • the flux wave flowing in sleeve 34 is thus substantially in phase with the alternating magnetomotive force established by the current flowing in exciting coil 27.
  • Inner cylindrical core member 35 is the lagging phase or retardant flux path, being designed to obtain a substantial value of flux wave phase retardation by the combined-effects of hysteresis and internal circulating currents.
  • Member 35 is constructed of a milk steel such as cold-rolled A.I.S.I. C-lll7 which is characterized by a moderate degree of inherent hysteresis or remanence, such as to cause an effective phase retardation of the flux wave flowing therethrough.
  • member 35 is designed as an unbroken cylindrical body which is subject to the flow of circular induced eddy currents throughout its length.
  • Said eddy currents serve to oppose changes in the instantaneous flux value flowing in said member, thus retarding the phase of the resultant flux wave, in addition to the hysteretic phase retardation aforesaid.
  • the resultant angular phase shift is thus a composite value which may be considered as the vector sum of the two phase lag angles obtained separately from the retarding effects of magnetic hysteresisand eddy current flow.
  • An annular gap 37 provides for magnetic separation of the two core members 34 and 35, to avoid interphase shunting of fluxcomponentsdue to the proximity of the two members.
  • Gap'37 is indicated in FIG. 3, produced by forming member 35 with a step or shoulder 38 whereby the lower portion of core 35 is slightly smaller in diameter than the inside of sleeve 34.
  • a satisfactory dimension for-said gap has been found to be provided by forming shoulder 38 with a. radial dimension equal to 2% percent of the outside diameter of sleeve 34.
  • gap 37 may be between 70 and percent of the length of sleeve member 34. While the annular gap space 37 is shown in the drawing as an airgap, it will be apparent to those skilled in the art that the gap space may alternatively be filled with an appropriate nonmagnetic material such as plastic or cement, to maintain concentricity and secure adhesron.
  • a flow rate of 1.0 g.p.m. was chosen, with operation on 1 15 v. 60-cycle AC with a water gauge pressure of 60 p.s.i.
  • the diameter of fluid passage 24 was established as 0.072 inch, and an armature travel of 0.063 inch was chosen, thus setting the axial dimension of working gap 8 at 0.063 inch.
  • An armature open-gap (inrush) pull requirement of 10 oz. was established to allow a reserve over the maximum load values to be encountered.
  • Coil spool 28 length o.a., 0.820 inch, winding length 0.760
  • Coil 27 3,900 turns, No. 39 or 40 B&S ga. copper, weight 8 or ll gm.
  • Core sleeve 34 0.600 inch long, 0.437.dia, 0.062 wall, ingot iron.
  • Armature 1 dia. 0.395 inch to 0.400 inch,,plunger length 0.325 inch, 430 8.8.
  • a numerical performance .factor of merit P was devised as an expression of open gap pull in ounces attainable, per watt of steady state electrical. input.
  • -P becomes 10 (oz.),divided-by the measured input watts (w.) for the closed gap steady-state condition.
  • housing 3 servesbeneficially as a saturable magneticshunt, bypassing around armature l a portion of the residual flux originating in parts such as core 30, shell 31, or core 35.
  • the bypassing of residual flux is effective up to the saturationlevel of the cylindrical wall of housing 3, thus representing a further benefit accruing to the present invention.
  • a magnetomotive device having a coil with a core and an armature arranged to form a magnetic circuit
  • a housing for said armature said core including a composite flux conducting element comprising a plurality of ferromagnetic portions defining spaced magnetically parallel flux paths, said portions incorporating relative variations in at least one of the electromagnetic properties thereof including magnetic hysteresis and eddy current susceptibility, said portions being in fixed relative position and being magnetically separated over a substantial portion of their common length by substantially nonmagnetic gap means extending therebetween.
  • a magnetomotive device as set forth in claim 1 in which said housing is a fluid confining barrier interposed between said armature and said coil.
  • a substantially closed magnetic circuit including a tubular housing for said armature, said housing being of unitary construction having one and closed by a transverse diaphragm portion, said housing including said diaphragm portion being formed throughout of ferromagnetic material providing an uninterrupted flux path throughout the tubular wall and diaphragm portions thereof and in which at least the tubular wall portion thereof is substantially the same thickness throughout its entire length.
  • a magnetomotive device as set in claim 3 in which said housing is a fluid confining barrier interposed between said armature and said coil.
  • a magnetomotive device as set forth in claim 3 in which said housing is arranged as a fluid confining element of an associated fluid control valve, said armature being immersed in the fluid controlled by said valve.
  • a magnetomotive device having a coil with a core and an armature arranged to form a magnetic circuit
  • a housing for said armature said core including a composite flux conducting element comprising a plurality of ferromagnetic portions defining spaced magnetically parallel flux paths, said portions incorporating relative variations in at least one of the electromagnetic properties thereof including magnetic hysteresis and eddy-current susceptibility, said portions being magnetically separated over a substantial portion of their common length by substantially nonmagnetic gap means extending therebetween, said portions including an inner cylindrical member and an outer sleeve member arranged in an annular coaxial manner, said sleeve member having its circumferential electrical continuity substantially interrupted.
  • a magnetomotive device having a coil with a core and an armature arranged to form a magnetic circuit, a housing for said armature arranged as a fluid confining element of an associated fluid control valve, said core including a composite flux conducting element comprising a plurality of ferromagnetic portions defining spaced magnetically parallel flux paths, said portions incorporating relative variations in at least one of the electromagnetic properties thereof including magnetic hysteresis and eddy current susceptibility, said portions being magnetically separated over a substantial portion of their common length by substantially nonmagnetic gap means extending therebetween, said armature being immersed in the fluid controlled by said valve.
  • a housing for said armature said core including a composite flux conducting element comprising a plurality of ferromagnetic portions defining spaced magnetically parallel flux paths, said portions incorporating relative variations in at least one of the electromagnetic properties thereof including magnetic hysteresis and eddy current susceptibility, said portions being magnetically separated over a substantial portion of their common length by substantially nonmagnetic gap means extending therebetween, said housing being of tubular form and of integral construction having one end closed by a transverse diaphragm portion, said housing being fonned of ferromagnetic material of substantially uniform thickness, said core and said armature forming a substantially closed flux path including said housing.
  • a substantially closed magnetic circuit including a tubular housing for said armature, said housing being of integral construction having one end closed by a transverse diaphragm portion, said housing being formed of ferromagnetic material of substantially uniform thickness, said armature being disposed within said housing for operative movement and having fluid valving means in operative association therewith, said core including a composite flux conducting element comprising a plurality of ferromagnetic portions defining spaced magnetically parallel flux paths, said portions incorporating relative variations in at least one of the magnetic properties thereof including magnetic hysteresis and eddy current susceptibility, said portions being magnetically separated over a substantial portion of their common length by substantially nonmagnetic gap means extending therebetween.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetically Actuated Valves (AREA)
US830342A 1969-06-04 1969-06-04 Alternating current solenoids Expired - Lifetime US3647177A (en)

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Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3747893A (en) * 1972-01-17 1973-07-24 Westinghouse Electric Corp Fluid coupling with sink retainer
US3837618A (en) * 1973-04-26 1974-09-24 Co Des Freins Et Signaux Westi Electro-pneumatic valve
US3861643A (en) * 1973-10-05 1975-01-21 United Aircraft Corp Saturating magnetic control valve
US3982554A (en) * 1974-04-25 1976-09-28 Tekyo Keiki Company Limited Electromagnetic flapper valve
US4132194A (en) * 1975-05-30 1979-01-02 Nissan Motor Company, Limited Valve arrangement for use in mixture ratio control system of internal combustion engine
US4148340A (en) * 1970-08-03 1979-04-10 Process Systems, Inc. Digital fluid flow control system
US4501299A (en) * 1982-05-21 1985-02-26 Humphrey Products Company Plunger-type valve
US4836248A (en) * 1982-06-29 1989-06-06 Robert Bosch Gmbh Hydraulic electromagnetically actuated slide valve
DE3831196A1 (de) * 1988-09-14 1990-03-22 Bosch Gmbh Robert Elektromagnetisch betaetigbares ventil
EP0525377A1 (de) * 1991-07-30 1993-02-03 Robert Bosch Gmbh Ventil
FR2686387A1 (fr) * 1992-01-21 1993-07-23 Danfoss As Partie superieure d'une electrovanne.
US20020057154A1 (en) * 2000-10-28 2002-05-16 Volker Keck Electromagnetic actuator for operating a final control element
EP1217273A3 (de) * 2000-12-20 2003-06-11 WABCO GmbH & Co. OHG Elektromagnetventileinrichtung
US20060255892A1 (en) * 2005-05-16 2006-11-16 Adams Ross R Solenoid
EP1165960B1 (de) * 2000-02-04 2007-07-25 Robert Bosch Gmbh Brennstoffeinspritzventil
WO2012159688A1 (de) * 2011-05-20 2012-11-29 Faurecia Autositze Gmbh Fahrzeugsitz mit einer pneumatisch veränderbaren sitzkontur
WO2012159689A1 (de) * 2011-05-20 2012-11-29 Faurecia Autositze Gmbh Pneumatikventileinheit

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3314900A1 (de) 1983-04-25 1984-10-25 Gerhard Dipl.-Ing. 4630 Bochum Mesenich Elektromagnet fuer ventile
GB2144201B (en) * 1983-07-28 1986-10-22 Lucas Ind Plc Fuel injector valve seat
GB2189010B (en) * 1986-03-07 1990-03-21 Alexander Controls Ltd Apparatus for controlling the flow of gas
GB2204381A (en) * 1987-04-23 1988-11-09 Teddington Controls Ltd Solenoids

Citations (4)

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Publication number Priority date Publication date Assignee Title
US989018A (en) * 1910-10-27 1911-04-11 Alonzo B See Alternating-current magnet.
US2013439A (en) * 1933-07-10 1935-09-03 Frank A Gauger Valve
US2853659A (en) * 1952-03-10 1958-09-23 Herion Erich Solenoid arrangements
US3166692A (en) * 1961-09-25 1965-01-19 Aero Flow Dynamics Inc Alternating current solenoid

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US989018A (en) * 1910-10-27 1911-04-11 Alonzo B See Alternating-current magnet.
US2013439A (en) * 1933-07-10 1935-09-03 Frank A Gauger Valve
US2853659A (en) * 1952-03-10 1958-09-23 Herion Erich Solenoid arrangements
US3166692A (en) * 1961-09-25 1965-01-19 Aero Flow Dynamics Inc Alternating current solenoid

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4148340A (en) * 1970-08-03 1979-04-10 Process Systems, Inc. Digital fluid flow control system
US3747893A (en) * 1972-01-17 1973-07-24 Westinghouse Electric Corp Fluid coupling with sink retainer
US3837618A (en) * 1973-04-26 1974-09-24 Co Des Freins Et Signaux Westi Electro-pneumatic valve
US3861643A (en) * 1973-10-05 1975-01-21 United Aircraft Corp Saturating magnetic control valve
US3982554A (en) * 1974-04-25 1976-09-28 Tekyo Keiki Company Limited Electromagnetic flapper valve
US4132194A (en) * 1975-05-30 1979-01-02 Nissan Motor Company, Limited Valve arrangement for use in mixture ratio control system of internal combustion engine
US4501299A (en) * 1982-05-21 1985-02-26 Humphrey Products Company Plunger-type valve
US4836248A (en) * 1982-06-29 1989-06-06 Robert Bosch Gmbh Hydraulic electromagnetically actuated slide valve
DE3831196A1 (de) * 1988-09-14 1990-03-22 Bosch Gmbh Robert Elektromagnetisch betaetigbares ventil
US5217204A (en) * 1991-07-30 1993-06-08 Robert Bosch Gmbh Valve
EP0525377A1 (de) * 1991-07-30 1993-02-03 Robert Bosch Gmbh Ventil
FR2686387A1 (fr) * 1992-01-21 1993-07-23 Danfoss As Partie superieure d'une electrovanne.
EP1165960B1 (de) * 2000-02-04 2007-07-25 Robert Bosch Gmbh Brennstoffeinspritzventil
US20020057154A1 (en) * 2000-10-28 2002-05-16 Volker Keck Electromagnetic actuator for operating a final control element
US7088209B2 (en) * 2000-10-28 2006-08-08 Daimlerchrysler Ag Electromagnetic actuator for operating a final control element
EP1217273A3 (de) * 2000-12-20 2003-06-11 WABCO GmbH & Co. OHG Elektromagnetventileinrichtung
US6712333B2 (en) 2000-12-20 2004-03-30 Wabco Gmbh & Co. Ohg Valve mechanism
US20060255892A1 (en) * 2005-05-16 2006-11-16 Adams Ross R Solenoid
US7196602B2 (en) 2005-05-16 2007-03-27 Macon Electric Coil Company Solenoid
WO2012159688A1 (de) * 2011-05-20 2012-11-29 Faurecia Autositze Gmbh Fahrzeugsitz mit einer pneumatisch veränderbaren sitzkontur
WO2012159689A1 (de) * 2011-05-20 2012-11-29 Faurecia Autositze Gmbh Pneumatikventileinheit

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CA937623A (en) 1973-11-27
GB1305774A (en, 2012) 1973-02-07

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