US3880476A - Electromagnetic valve - Google Patents

Electromagnetic valve Download PDF

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Publication number
US3880476A
US3880476A US419846A US41984673A US3880476A US 3880476 A US3880476 A US 3880476A US 419846 A US419846 A US 419846A US 41984673 A US41984673 A US 41984673A US 3880476 A US3880476 A US 3880476A
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United States
Prior art keywords
valve
pressure
chamber
housing
pistons
Prior art date
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Expired - Lifetime
Application number
US419846A
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English (en)
Inventor
Juan Belart
Werner Fink
Dieter Kircher
Grunberg Hubertus Von
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TDK Micronas GmbH
ITT Inc
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Deutsche ITT Industries GmbH
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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
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F16K31/0613—Sliding valves with cylindrical slides
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
    • B60T8/3635—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems switching between more than two connections, e.g. 3/2-valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3655—Continuously controlled electromagnetic valves
    • B60T8/366—Valve details
    • B60T8/3665—Sliding valves
    • 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
    • F16K31/0603—Multiple-way valves
    • F16K31/0624—Lift valves
    • 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
    • F16K31/0603—Multiple-way valves
    • F16K31/0624—Lift valves
    • F16K31/0627—Lift valves with movable valve member positioned between seats
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated

Definitions

  • the valve body of the valve is connected with the magnetic armature to control the cross-sectional area of pressure medium flow through the valve in a continuous sequence proportional to the magnetic force resulting from the energizing current produced by the electronic circuitry of the antiskid system.
  • the energizing current By changing the energizing current, it is possible to change the pressure difference between the pressure medium source and the pressure-operated brake.
  • the hydraulic antiskid control is more accurate and smoother than is achieved with previously employed open/close antiskid hydraulic control valves.
  • This invention relates to an electromagnetic valve for use in antiskid systems, the valve body thereof being mechanically connected with the magnetic armature such that the valve body blocks, opens or diverts the passage of pressure medium flow through the valve when the magnet winding is energized.
  • the switching times are determined, among other things, by the mass of the magnetic armature and by the amount of friction to be overcome when the armature is accelerated, as well as by the magnetic resistance in the closed magnetic circuit.
  • the plunger-type armature represents a relatively large mass.
  • valve control orifice changes continuously and in proportion to the magnetic force in order to achieve a control more accurate and smooth than could be achieved with the open/close valves known to date.
  • a feature of the present invention is the provision of an electromagnetic valve for use in an antiskid brake system comprising a magnet housing having a first longitudinal axis, a magnet winding disposed in the housing coaxial of the axis, a magnetic return path disposed in the magnet housing magnetically coupled to the winding, a sleeve of non-magnetic material disposed in the return path coaxial of the first axis, a first chamber disposed in the magnet housing adjacent the sleeve and the return path, a valve body disposed coaxial of the first axis, at least a portion of the valve body projecting into the first chamber, at least one armature plate disposed in the first chamber in an engaged relationship with the portion of the valve body projecting into the first chamber, and a spring disposed in the first chamber in an engaged relationship with the valve body and the armature plate to bias the valve body and the armature plate in a rest position, the valve body controlling the flow of a brake pressure medium through the valve between at least a brake pressure medium inlet and
  • Another feature of the present invention is the provision of armature plates arranged to leave a free space for a central opening and having their inner edges grip the under surface of'a collar provided directly on the valve body or on the movable supporting member of the valve body.
  • the armature plates are slightly inclined with their outer edges abutting the magnetic return path.
  • a further feature of the present invention is the provision of a diaphragm spring provided with openings and including a central aperture.
  • This spring has its inner edge engaged in a groove provided on the valve body or on the valve body support and its outer edge firmly connected to the housing. This spring biases both the valve body and the armature platesin their rest positions.
  • Still another feature of the present invention is the provision of a star-shaped diaphragm spring having its inner edge in engagement with a groove in an annular element mounted on the valve body or on the valve body support.
  • Still a further feature of the present invention is the provision that the characteristic curve of the diaphragm spring is adapted to the characteristic curve of the electromagnet.
  • the valve body is a valve slide controlling in a known manner the flow of pressure medium between the connectors of the pressure-medium source of the pressureoperated device and of a pressure medium reservoir, and that the valve slide is pressure-balanced in rest position, i.e., when there is flow of pressure medium between the pressure-medium source and the pressureoperated device.
  • Still a further feature of this invention is the provision of a duct interconnecting the chambers accommodating the ends of the valve slide.
  • Still another feature of this invention is that the duct interconnecting the chambers accommodating the ends of the valve slide also communicates with the pressureoperated device in one embodiment and with the pressure medium source in another embodiment.
  • valve slide is divided to form two pistons.
  • these pistons are mechanically connected and pressure-balanced in rest position at their outer and inner ends by the pressure of the pressure-operated device and by the source pressure, respectively.
  • the pistons forming the valve slide are pressure-balanced in rest position at their outer ends by the source pressure and at their inner adjacent ends by the pressure of the pressureoperated device.
  • valve slide when the electromagnet is energized, can be actuated by source pressure in a direction opposite to that of the magnetic force, and by pressure of the pressure-operated device in the direction of the magnetic force, the actuating surfaces for both pressures being of equal size.
  • the energizing current of the electromagnet and consequently the pressure difference between the pressure medium source and the pressure-operated device are continuously variable.
  • FIG. 1 is a longitudinal cross-sectional view of a first embodiment of an electromagnetic valve in accordance with the principles of the present invention showing a seat valve which is closed when the magnet coil is deenergized;
  • FIG. 2 is a transverse cross-sectional view of the seat valve taken along line A-B of FIG. 1;
  • FIG. 3 is a longitudinal cross-sectional view of a second embodiment of an electromagnetic valve in accordance with the principles of the present invention showing a seat valve which is opened when the magnet coil is deenergized;
  • FIG. 4 is a longitudinal cross-sectional view of a third embodiment of an electromagnetic valve in accordance with the principles of the present invention showing a 3/2 directional control valve;
  • FIG. 5 and 6 are further embodiments of an electromagnetic valve in accordance with the principles of the present invention showing 3/2 directional control valves.
  • FIG. 1 there is located in a housing 2 made of magnetizable material the magnet coil 3 in an insulated relationship with housing 2.
  • Housing 2 together with the magnet core 9 surrounded by coil 3, forms a magnetic return path 10 into which there is embedded a sleeve 4 made of non-magnetic material.
  • armature plates 1 held by means of retaining clips 6.
  • Armature plates 1 have an annular central opening. It can be seen from FIG. 2 that there are two trapezoidal armature plates resting against each other at their bases and that a semicircular aperphragm spring 5, so that the valve-closing member will be lifted from its seat and the valve will be opened.
  • FIG. 3 shows an embodiment of a seat valve constructed in accordance with this invention which is opened with the electromagnet being deenergized.
  • a substantial number of parts of FIG. 3 are identical to those of the seat valve of FIG. 1 and, therefore, like parts have been assigned like reference numerals in both FIGS.
  • a blind-end bore 20 extends into magnet core 9, the outlet 21 extending later.- ally from bore 20 through magnetic return path 10.
  • a valve seat 22 is disposed on a stepped portion of blind-end bore 20.
  • the closing member of valve body 7' projects into blind-end bore 20 of magnet core 9, thus lying opposite valve seat 22.
  • the inner edges of armature plates 1 grip the under surface of collar 12 and are kept in position by means of retaining clips 6 in the manner described with respect to FIG. 1.
  • diaphragm spring ture With one end of diaphragm spring 5 engaging annular element 16 at collar 15' of supporting member 13' and with the other end of diaphragm spring 5 engaging a groove in housing chamber- 11, the diaphragm spring ture is cut into each base. At the circular opening, the
  • armature plates 1 grip the under surface of a collar 12 of the supporting member 13 for the vvalve body 7.
  • Supporting member 13 is provided with clearance for motion by virtue of a centric recess 14 in the magnet core 9 into which supporting member 13 is projecting.
  • a U-shaped cross-sectional annular element 16 is located on the top surface of a collar l5.
  • Retaining clips 6 each have one end gripped by one arm of annular element 16, while the other ends of clips 6 engage a groove in armature plates 1.
  • the inner edge of a star-shaped diaphragm spring 5 includes a v 'closing member'resting against the valve seat of the outlet 17 provided in the adjacent housing wall.
  • the same housing wall also includes the inlet 18 terminating in housing chamber 11.
  • lnlet 18 is covered with a filter 8 to provide a protection against dirt.
  • a thread 19 provided at housing 2 permits the valve to be screwed into a cooperating device such as a pressure medium conduit. If current flows through coil 3 of the electromagnet, the induced magnetic field will cause armature plates 1 to be attracted by magnet core 9 and magnetic return path 10, respectively, armature plates 1 thus causing supporting member 13 and the associated valve body 7 to follow against the force of dia- 5 via supporting member 13' keeps valve body .7 spaced apart from valve seat 22 and armature plates 1 apart from magnetic return path 10.
  • This embodiment also provides for a protective filter 8 covering inlet 23 terminating in housing chamber 11.
  • the magnetic leakage field is reduced by virtue of magnetic return path 10, thus permitting more efficient use to be made of the magnetic forces and consequently allowing utilization of a smaller electromagnet.
  • the non-magnetic sleeve 4 embedded in magnetic return path 10 avoids the occurrence of a magnetic short circuit and induces the lines of magnetic flux to run through armature plates 1.
  • a non-adhesive plate (not shown) made of non-magnetic material has been provided between magnet core 9 and armature plates 1.
  • the non-adhesive plate, while resting on armature plates 1 may be clamped under collar 12 of supporting member 13, or, in the shape of an expanding cap, be squeezed into centric recess 14 of magnet core 9.
  • armature plates I enjoy the advantage of moving under extremely low friction during switching and of having less mass.
  • there is only one air gap in the magnetic circuit namely, theworking air gap.
  • the radial air gap necessary in frictionless suspended plunge r-type armatures in not required.
  • the flat design of the armature also enables diaphragm springs to be mounted in a preferable manner. The diaphragm springs permit high forces to be controlled more readily than is the case with spiral springs.
  • valves constructed in accordance with the present invention have very short switching times even if no special magnetic materials are used.
  • FIG. 4 shows the arrangement of the magnetic armature already described together with a slide valve incorporating, in the embodiment shown, further decisive advantages particularly for use in antiskid control systems.
  • the housing of the slide valve contains a cylinder bore 30 enlarging at its one end to form a chamber 32 via a stepped portion 31. In its middle area, cylinder bore 30 enlarges once more into a wide groove 33. Groove 33 connects in its whole width with a port 34 of the slide valve. Cylinder bore 30 contains two slidably mounted pistons 36 and 37 coupled to each other via a mechanical connection 35. The diameter of piston 37 is smaller than the diameter of piston 36. Piston 36 is sealed to the inner wall of cylinder bore 30 and projects into enlarged chamber 31. Piston 36 is secured against sliding out by means of a circlip 38.
  • annular chamber 39 is created permanently communicating with a second port 40 of the slide valve. That end of piston 36 which is connected with the second piston 37 is reduced to the diameter of piston 37, thus producing within the area of groove 33 a collar 41 on piston 36. Collar 41 corresponding in length to the width of groove 33. The other end of piston 37 is tightly confined within cylinder bore 30 reduced to the diameter of piston 37. This diameter reduction of bore 30 creates annular chamber 42 communicating with the third port 43 of the 3/2 directional control valve.
  • Housing 2 of the electromagnet is screwed into a recess of the valve casing in which cylinder bore 30 terminates.
  • the armature plates 1 with their inner edges grip the upper surface of collar 47 on the end of piston 37 and are secured by means of retaining clips 6 which are fixed to annular element 16.
  • the inner edge of diaphragm spring 5 also engages annular element 16 resting against collar 46 while the outer edges of spring 5 engage a groove of housing wall 2 of the electromagnet.
  • Diaphragm spring 5 keeps both armature plates 1 and pistons 36 and 37 in their illustrated home or rest positions.
  • this valve is to be use preferably for antiskid control systems.
  • port 43 connects with the brake actuation system, i.e., with the master cylinder, while port 34 connects with the wheel brake cylinder and port 40 with the reservoir.
  • the electronic control system will transmit a current pulse to the electromagnet. This pulse is continuously variable in accordance with the variation of the output variable relative to its rated value.
  • the brake In the illustrated valve position, wherein the electromagnet is deenergized, the brake can be operated as usual.
  • the brake pressure is transmitted through port 43, annular chamber 42 and the port 34 to the wheel brake cylinder.
  • Pressure P, in the master cylinder is equal to pressure P, in the wheel brake cylinder. Since pressure P via duct 48, also acts on the outer front surfaces of pistons 36 and 37, these pistons are hydraulically balanced. If the electronic control unit of the antiskid system detects danger of wheel lock, current will flow through coil 3 of the electromagnet and cause armature plates 1 to be attracted towards magnetic return path 10, thereby also moving the mechanically connected pistons 36 and 37 in the same direction. In this process, leading edges 44 first interrupt the pressure-medium connection between the master cylinder and the wheel brake cylinder, whereupon the leading edges 45 open the connection from port 34 of the wheel brake cylinder through annular chamber 39 to port 40 leading to the reservoir, thus permitting pressure in the wheel brake to drop.
  • Pressure P, of the master cylinder exerts the force P, X A on the annular surface A of collar 41 at piston 36, whereas, caused by the flow conditions, pressure P, in the wheel brake cylinder exerts the opposing force P 2 X A.
  • Pressure P in the wheel brake cylinder is now continuously decreasing until the resulting hydraulic force (P, P X A acting on pistons 36 and 37 is equal to the magnetic force determined by the coil current, disregarding the friction and spring forces.
  • Variation of the coil current which as mentioned above is continuously variable dependent on the output variable, involves a change of the pressure difference P, P
  • the characteristic curve of the diaphragm spring 5 is preferably adapted to that of the electromagnet in order to achieve independence of the resulting force from the stroke and to obtain an improved controller action.
  • the pressure difference between the brake control valve or the master cylinder and the wheel brake cylinder is adjusted in proportion to the magnetic force.
  • the control pressure thus represents a further item for the electronic control unit.
  • FIG. 5 shows a further improved embodiment of the slide valve constructed in accordance with the present invention.
  • This embodiment also has one end of the cylinder bore 50 enlarged to form a chamber 51 into which projects the tightly confined smaller piston 52.
  • Piston 53 which is of larger diameter than piston 52, is confined within that area of cylinder bore 50 enlarged by a stepped portion and rests against the adjacent surface of piston 52, around which end an annular chamber 54 is formed.
  • an annular chamber 55 is created permanently communicating with one port 56 which, when used in an antiskid control system. leads to the reservoir.
  • a further recess provided in bore creates anannular chamber 57.
  • a collar 58 is provided on piston 53 having a width to the width of a groove 59.
  • This groove 59 connects with the second port 60 of the valve,.which port leads to the wheel brake cylinder.
  • the annular chamber 57 communicates with chamber 11 via recesses 63 provided in the valve housing. Chamber 11 receives piston 53 which is connected with the electromagnetic control system in the manner described with reference to FIG. 4. Via one of these recesses 63, the annular chamber 57 and chamber 11 communicate by means of a duct 64 with chamber 51 and the port 65 leading to themaster cylinder, in order to achieve pressure balance.
  • the groove 59 connects with the annular chamber 54 at the piston 52 via a longitudinal bore 66 and a cross bore 67 provided in piston 53.
  • the mode of operation of the embodiment of FIG. 5 is the same as that described with reference I to FIG. 4.
  • the embodiment of FIG. 5 has the following advantages.
  • FIG. 6 represents a slide valve operating according to the same principles as described above but showing a further simplified embodiment provided with an integrally formed valve slide.
  • the valve casing 70 there is accommodated the cylinder 71 with the cylinder bore 72.
  • the valve slide is tightly and slidably received in cylinder bore 72 terminating in the housing chamber 74 which communicates with the master cylinder via a port 73.
  • a recess 76 provided in the wall of cylinder 71 connects cylinder bore 72 with a further housing chamber 77 which communicates with the wheel brake cylinder via a port 78.
  • the collar 79 is produced by a recess in valve slide 75.
  • the width of collar 79 corresponds to the width of recess 76 provided in the cylinder wall.
  • annular chamber 82 is created by the above-mentioned recess in valve slide 75 and communicates with the housing port 84 via a cross bore 83 in the cylinder wall. Port 84 leads to the reservoir.
  • Cylinder 71 projects into a housing chamber 85 into which is screwed housing 86 of the electromagnet.
  • Valve slide 75 connects with the pressure-balanced magnetic armature 87 and is biased in rest position by means of a spring 88.
  • housing chamber 77 is connected with housing chamber 85 containing the valve-slide front surface facing the electromagnet.
  • valve slide 75 is pressure-balanced'in rest position. Brake pressure is thus free to be transmitted from the master cylinder through housing chamber 74, cylinder bore 72, recess 76 in the cylinder wall, and housing chamber 77, to the wheel brake cylinder. If the electromagnet receives a current pulse in the event of wheel locking danger, magnetic armature 87 will be attracted towards the magnet core 90, with the valve slide 75 being displaced. Leading edges 80 first interrupt the pressure-medium connection between the master cylinder and the wheel brake cylinder, whereupon leading edges 81 will open up the connection between wheel brake cylinder and reservoir.
  • the master cylinder pressure P acts on the front surface of collar 79 of the valve slide 75, while, via duct 89, the wheel brake cylinder pressure P acts on the front surface of valve slide 75 facing the electromagnet. As described above, a pressure difference is then produced at valve slide 75 which is proportional to the continuously variable coil current. With the magnet force being of the same magnitude, the crosssectional area of the valve slide in FIG. 6 is bound to be approximately the same as the annular surface A in FIG. 4.
  • FIG. 6 shows an embodiment of the invention incorporating a plunger-type armature.
  • the valve constructed in accordance with this invention provides for more freedom in selecting the most expedient control method and is, among other things, the prerequisite for a continuous control system no longer producing sharply defined phases for pressure decrease, pressure stabilization and pressure increase, but producing a pressure curve smoothly swinging near its ideal value. This is achieved by permanently interrogating the output variable in a timing screen and by modifying the coil current of the electromagnet according to the variation exceeding the permissible deviation with a downward or upward tendency.
  • the invention relates to an analog valve instead of a digital valve, i.e., control is via the current intensity and not via the duration of voltage application.
  • the slide valves combine the advantage of low resistance to flow with accurate control possibilities. thus enabling the valves to be installed directly in the brake line.
  • An electromagnetic valve for use in an antiskid brake system comprising:
  • a magnet housing having a first longitudinal axis
  • valve body disposed coaxial of said first axis, at least a portion of said valve body projecting into said first chamber;
  • armature plates disposed in said first chamber, said armature plates having a central opening coaxial of said axis, the outer edges of said armature plates abutting said return path and being slightly'inclined away from said return path, and the inner edges of said armature plates engaging said portion of said valve body projecting into said first chamber to move said valve body when said winding is energized and said armature plates adjacent said inner edges are attracted toward said return path;
  • a spring disposed in said first chamber in an engaged relationship with said valve body and said armature plates to bias said valve body and said armature plates in a rest position;
  • valve body controlling the flow of a brake pressure medium through said valve between at least a brake pressure medium inlet and a brake pressure medium outlet when said winding is energized and said armature plates are attracted toward said return path;
  • said spring including a diaphragm spring having openings therethrough and a central aperture coaxial of said first axis,
  • a valve according to claim 1 wherein said groove is provided by a U-shaped crosssectioned annular element mounted on said portion of said valve body projecting into said first chamber.
  • said diaphragm spring is star shaped.
  • the characteristic curve of said diaphragm spring is adapted to the characteristic curve of an electromag ne t including said winding, said return path, said sleeve and said armature plates.
  • a valve according to claim 4 further including a valve housing connected to said magnet housing,
  • valve housing havig a second longitudinal axis which is an extension of said first axis; a pressure medium source inlet connection extending through the wall of said valve-housing; a pressure medium reservoir outlet connection extending through the wall of said valve housing; and a pressure medium wheel brake cylinder outlet connection extending through the wall of said valve housing; and wherein said valve body includes a valve slide extending from said first chamber into said valve housing coaxial of said second axis, said valve slide being disposed in a cooperative relationship with said source inlet connection, said reservoir outlet connection and said wheel brake cylinder outlet connection to control the flow of pressure medium between these three connections, said valve slide being pressure balanced in its rest position when the flow of pressure medium is between said source inlet connection and said wheel brake cylinder outlet connection.
  • a valve according to claim 5 further including a second chamber disposed in said valve housing embracing the end of said valve slide remote from said first chamber; and a duct disposed in said valve housing to interconnect said first and second chambers.
  • said duct is connected to said wheel brake cylinder outlet connection.
  • said duct is connected to said source inlet connection.
  • said valve slide is formed by two pistons in tandem relationship. 10.
  • said two pistons can move freely with respect to each other, said two pistons being pressure-balanced in their rest position by the pressure at said source inlet connection being applied to the remote ends of said two pistons and by the pressure at said wheel brake cylinder outlet connection being applied to the adjacent ends of said two pistons.
  • a v alv e according to claim 12 wherein D said first and second. actuating surfaces are equal in connection are comlnuously Variablesize I i the pressure difference between said source inlet connection and said wheel brake cylinder outlet

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Magnetically Actuated Valves (AREA)
  • Regulating Braking Force (AREA)
  • Electromagnets (AREA)
US419846A 1972-12-20 1973-11-28 Electromagnetic valve Expired - Lifetime US3880476A (en)

Applications Claiming Priority (1)

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DE2262247A DE2262247A1 (de) 1972-12-20 1972-12-20 Elektromagnetisches ventil

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US (1) US3880476A (sv)
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BR (1) BR7309978D0 (sv)
DE (1) DE2262247A1 (sv)
FR (1) FR2255532B1 (sv)
GB (1) GB1454295A (sv)
IT (1) IT1050219B (sv)
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Cited By (50)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4048601A (en) * 1976-05-28 1977-09-13 Leach Corporation Switch mounting assembly for an electromagnetic relay
US4094553A (en) * 1977-07-28 1978-06-13 General Signal Corporation Brake control system having an electro-pneumatic pilot valve
US4114648A (en) * 1974-12-25 1978-09-19 Konan Electric Co., Ltd. Double acting electromagnetic valve
US4197518A (en) * 1976-11-19 1980-04-08 Lucas Industries Limited Electromagnetic actuating device employing lever means
US4250922A (en) * 1978-05-24 1981-02-17 Robert Bosch Gmbh Electromagnetically operated control valve
US4316599A (en) * 1979-03-26 1982-02-23 Regie Nationale Des Usines Renault Servo-control valve
EP0051702A1 (en) * 1980-11-06 1982-05-19 The Jacobs Manufacturing Company Improved solenoid
EP0110217A2 (de) * 1982-11-26 1984-06-13 Robert Bosch Gmbh Hydraulisches Fahrzeugbremssystem
EP0171998A1 (en) * 1984-08-15 1986-02-19 AlliedSignal Inc. Servo apparatus
US4579145A (en) * 1983-08-05 1986-04-01 Robert Bosch Gmbh Pressure control device
US4635683A (en) * 1985-10-03 1987-01-13 Ford Motor Company Variable force solenoid
US4662605A (en) * 1985-01-30 1987-05-05 G. W. Lisk Company, Inc. Spool drive for pressure regulating, proportional solenoid valve
DE3732445A1 (de) * 1987-09-25 1989-04-13 Rexroth Mannesmann Gmbh Druckregelventil
US4838313A (en) * 1987-05-28 1989-06-13 Aisin Aw Co., Ltd. Solenoid-operated pressure control valve
US4844559A (en) * 1987-11-20 1989-07-04 Lucas Industries Public Limited Company Electrically operated solenoid valve
US4891626A (en) * 1989-01-18 1990-01-02 Neuman Industries, Inc. Refrigerator door ajar detection system
US4900104A (en) * 1987-09-28 1990-02-13 Gary Clifford Pressure modulation valve
US4934762A (en) * 1988-03-14 1990-06-19 Honda Giken Kogyo Kabushiki Kaisha Hydraulic brake system
US4940291A (en) * 1988-01-07 1990-07-10 Honda Giken Kogyo Kabushiki Kaisha Method and apparatus for controlling hydraulic braking pressure for a vehicle
US4944331A (en) * 1989-06-22 1990-07-31 Allied-Signal Inc. Solenoid valve
US4971116A (en) * 1988-11-09 1990-11-20 Aisin Aw Kabushiki Kaisha Pressure control valve
US4971114A (en) * 1988-11-21 1990-11-20 Diesel Kiki Co., Ltd. Electromagnetic proportional pressure control valve
US5014747A (en) * 1988-11-09 1991-05-14 Aisin Aw Kabushiki Kaisha Pressure control valve
USRE33960E (en) * 1989-01-18 1992-06-16 Neuman Industries, Inc. Refrigerator door ajar detection system
US5186093A (en) * 1990-04-12 1993-02-16 Bendix Europe Services Techniques Electrically controlled pressure-regulating system for a hydraulic circuit
US5191827A (en) * 1990-04-12 1993-03-09 Bendix Europe Services Techniques Electrically controlled pressure-regulating system for a hydraulic circuit
US5244260A (en) * 1990-09-28 1993-09-14 Bendix Europe Services Techniques Automatic braking device for a vehicle
US5259414A (en) * 1988-11-09 1993-11-09 Aisin Aw Co., Ltd Pressure control valve
US5333947A (en) * 1991-06-27 1994-08-02 Bendix Europe Services Techniques Solenoid valve for a wheel antilockup system
US5410943A (en) * 1991-10-31 1995-05-02 Alliedsignal Europe Services Techniques Pressure regulation device for hydraulic system
US5431489A (en) * 1992-06-12 1995-07-11 Mando Machinery Corporation Hydraulic anti-skid braking systems for automobiles
US5778932A (en) * 1997-06-04 1998-07-14 Vickers, Incorporated Electrohydraulic proportional pressure reducing-relieving valve
US5878766A (en) * 1997-10-20 1999-03-09 Vickers, Incorporated Pressure compensated flow control valve
US5918635A (en) * 1997-10-08 1999-07-06 Vickers, Incorporated Low pressure solenoid valve
US6086164A (en) * 1994-10-27 2000-07-11 Robert Bosch Gmbh Magnet valve with pressure limitation for slip-controlled motor vehicle brake systems
US6148859A (en) * 1996-06-01 2000-11-21 Lucas Industries, Plc Hydraulic control valve assemblies for hydraulic braking systems
US6189984B1 (en) * 1997-03-13 2001-02-20 Robert Bosch Gmbh Hydraulically actuated stop valve and hydraulic brake system for a vehicle
US6213568B1 (en) * 1997-03-15 2001-04-10 Continental Teves Ag & Co., Ohg Hydraulic braking system operated by extraneous force
US6390129B2 (en) * 1999-12-15 2002-05-21 Jansen's Aircraft Systems Controls, Inc. Proportional solenoid-operated fluid metering device
US20080116406A1 (en) * 2003-10-09 2008-05-22 Emerson Electric Co. Valve Assembly
US20080156383A1 (en) * 2006-11-28 2008-07-03 Caterpillar Inc. Fluid-transfer system
US20090038697A1 (en) * 2005-04-27 2009-02-12 Ryosuke Cho Switching valve
US20100019567A1 (en) * 2006-09-15 2010-01-28 Siemens Aktiengesellschaft Self-energizing hydraulic brake
US20100132812A1 (en) * 2007-03-27 2010-06-03 Peter Henry Boughman Toilet cistern inlet valve
US20110024665A1 (en) * 2008-02-11 2011-02-03 MTA House, Level 1, 43-51 Brisbane Street Valve
CN102213330A (zh) * 2010-04-01 2011-10-12 株式会社电装 螺线管滑阀
JP2012122609A (ja) * 2010-11-19 2012-06-28 Denso Corp 油圧調整弁
EP2698574A1 (fr) 2012-08-16 2014-02-19 Patrice Mazigh Connecteur pour tuyaux de raccordement de système de climatisation et appareil de climatisation associé
US20170089370A1 (en) * 2014-05-16 2017-03-30 Audi Ag Electromagnet for a hydraulic system
US20170089371A1 (en) * 2014-05-16 2017-03-30 Audi Ag Electromagnet for a hydraulic system

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2435569C2 (de) * 1974-07-24 1985-06-27 Alfred Teves Gmbh, 6000 Frankfurt Elektromagnetisch betätigbares 3/2-Wegeventil
DE2731334A1 (de) * 1977-07-12 1979-01-25 Bosch Gmbh Robert Bremsblockierschutzeinrichtung
DE3143848A1 (de) * 1981-11-05 1983-05-11 Robert Bosch Gmbh, 7000 Stuttgart Elektromagnetisch betaetigbares ventil, insbesondere kraftstoffeinspritzventil
DE3240274A1 (de) * 1982-10-30 1984-05-03 Robert Bosch Gmbh, 7000 Stuttgart Mehrkreis-druckmittel-bremsanlage ii
DE3240276A1 (de) * 1982-10-30 1984-05-03 Robert Bosch Gmbh, 7000 Stuttgart Drucksteuerventil fuer eine bremsanlage
JPS59123769U (ja) * 1983-02-10 1984-08-20 太平洋工業株式会社 電磁弁
FR2559726B1 (fr) * 1984-02-22 1987-07-31 Fiat Auto Spa Electrovalve, notamment destinee a la commande des dispositifs antiderapage pour vehicules automobiles
JPH0788162B2 (ja) * 1985-10-18 1995-09-27 曙ブレーキ工業株式会社 車両の制動液圧封じ込め装置
GB8822713D0 (en) * 1988-09-28 1988-11-02 British Petroleum Co Plc Fail-safe valve
DE4020951A1 (de) * 1990-06-30 1992-01-02 Bosch Gmbh Robert Magnetventil
DE4134493A1 (de) * 1991-10-18 1993-04-22 Teves Gmbh Alfred Blockiergeschuetzte hydraulische bremsanlage
CN113581243B (zh) * 2021-07-22 2022-08-19 青岛自远机械有限公司 一种列车制动用防滑器排风阀

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US2627007A (en) * 1950-06-20 1953-01-27 Westinghouse Electric Corp Pile regulator
US2892058A (en) * 1954-01-26 1959-06-23 W N Borg Corp Relay
US2938703A (en) * 1957-03-04 1960-05-31 Baso Inc Electromagnetic control device
US3231315A (en) * 1963-02-07 1966-01-25 Ford Motor Co Anti-skid braking system
US3690431A (en) * 1971-06-14 1972-09-12 Centronics Data Computer Print head assembly containing solenoids
US3749125A (en) * 1971-02-26 1973-07-31 Fiat Spa Solenoid-actuated pneumatic actuator for anti-skid vehicle braking systems

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Publication number Priority date Publication date Assignee Title
US2627007A (en) * 1950-06-20 1953-01-27 Westinghouse Electric Corp Pile regulator
US2892058A (en) * 1954-01-26 1959-06-23 W N Borg Corp Relay
US2938703A (en) * 1957-03-04 1960-05-31 Baso Inc Electromagnetic control device
US3231315A (en) * 1963-02-07 1966-01-25 Ford Motor Co Anti-skid braking system
US3749125A (en) * 1971-02-26 1973-07-31 Fiat Spa Solenoid-actuated pneumatic actuator for anti-skid vehicle braking systems
US3690431A (en) * 1971-06-14 1972-09-12 Centronics Data Computer Print head assembly containing solenoids

Cited By (60)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4114648A (en) * 1974-12-25 1978-09-19 Konan Electric Co., Ltd. Double acting electromagnetic valve
US4048601A (en) * 1976-05-28 1977-09-13 Leach Corporation Switch mounting assembly for an electromagnetic relay
US4197518A (en) * 1976-11-19 1980-04-08 Lucas Industries Limited Electromagnetic actuating device employing lever means
US4094553A (en) * 1977-07-28 1978-06-13 General Signal Corporation Brake control system having an electro-pneumatic pilot valve
US4250922A (en) * 1978-05-24 1981-02-17 Robert Bosch Gmbh Electromagnetically operated control valve
US4316599A (en) * 1979-03-26 1982-02-23 Regie Nationale Des Usines Renault Servo-control valve
EP0051702A1 (en) * 1980-11-06 1982-05-19 The Jacobs Manufacturing Company Improved solenoid
EP0110217A2 (de) * 1982-11-26 1984-06-13 Robert Bosch Gmbh Hydraulisches Fahrzeugbremssystem
EP0110217A3 (en) * 1982-11-26 1986-10-08 Robert Bosch Gmbh Hydraulic vehicle brake system
US4579145A (en) * 1983-08-05 1986-04-01 Robert Bosch Gmbh Pressure control device
EP0171998A1 (en) * 1984-08-15 1986-02-19 AlliedSignal Inc. Servo apparatus
US4662605A (en) * 1985-01-30 1987-05-05 G. W. Lisk Company, Inc. Spool drive for pressure regulating, proportional solenoid valve
US4635683A (en) * 1985-10-03 1987-01-13 Ford Motor Company Variable force solenoid
US4838313A (en) * 1987-05-28 1989-06-13 Aisin Aw Co., Ltd. Solenoid-operated pressure control valve
DE3732445A1 (de) * 1987-09-25 1989-04-13 Rexroth Mannesmann Gmbh Druckregelventil
US4900104A (en) * 1987-09-28 1990-02-13 Gary Clifford Pressure modulation valve
US4844559A (en) * 1987-11-20 1989-07-04 Lucas Industries Public Limited Company Electrically operated solenoid valve
US4940291A (en) * 1988-01-07 1990-07-10 Honda Giken Kogyo Kabushiki Kaisha Method and apparatus for controlling hydraulic braking pressure for a vehicle
US5042886A (en) * 1988-01-07 1991-08-27 Honda Giken Kogyo Kabushiki Kaisha Method for controlling hydraulic braking pressure for a vehicle
US4934762A (en) * 1988-03-14 1990-06-19 Honda Giken Kogyo Kabushiki Kaisha Hydraulic brake system
US4971116A (en) * 1988-11-09 1990-11-20 Aisin Aw Kabushiki Kaisha Pressure control valve
US5014747A (en) * 1988-11-09 1991-05-14 Aisin Aw Kabushiki Kaisha Pressure control valve
US5259414A (en) * 1988-11-09 1993-11-09 Aisin Aw Co., Ltd Pressure control valve
US4971114A (en) * 1988-11-21 1990-11-20 Diesel Kiki Co., Ltd. Electromagnetic proportional pressure control valve
US4891626A (en) * 1989-01-18 1990-01-02 Neuman Industries, Inc. Refrigerator door ajar detection system
USRE33960E (en) * 1989-01-18 1992-06-16 Neuman Industries, Inc. Refrigerator door ajar detection system
US4944331A (en) * 1989-06-22 1990-07-31 Allied-Signal Inc. Solenoid valve
US5186093A (en) * 1990-04-12 1993-02-16 Bendix Europe Services Techniques Electrically controlled pressure-regulating system for a hydraulic circuit
US5191827A (en) * 1990-04-12 1993-03-09 Bendix Europe Services Techniques Electrically controlled pressure-regulating system for a hydraulic circuit
US5244260A (en) * 1990-09-28 1993-09-14 Bendix Europe Services Techniques Automatic braking device for a vehicle
US5333947A (en) * 1991-06-27 1994-08-02 Bendix Europe Services Techniques Solenoid valve for a wheel antilockup system
US5410943A (en) * 1991-10-31 1995-05-02 Alliedsignal Europe Services Techniques Pressure regulation device for hydraulic system
US5431489A (en) * 1992-06-12 1995-07-11 Mando Machinery Corporation Hydraulic anti-skid braking systems for automobiles
US6086164A (en) * 1994-10-27 2000-07-11 Robert Bosch Gmbh Magnet valve with pressure limitation for slip-controlled motor vehicle brake systems
US6148859A (en) * 1996-06-01 2000-11-21 Lucas Industries, Plc Hydraulic control valve assemblies for hydraulic braking systems
US6189984B1 (en) * 1997-03-13 2001-02-20 Robert Bosch Gmbh Hydraulically actuated stop valve and hydraulic brake system for a vehicle
US6213568B1 (en) * 1997-03-15 2001-04-10 Continental Teves Ag & Co., Ohg Hydraulic braking system operated by extraneous force
US5778932A (en) * 1997-06-04 1998-07-14 Vickers, Incorporated Electrohydraulic proportional pressure reducing-relieving valve
US5918635A (en) * 1997-10-08 1999-07-06 Vickers, Incorporated Low pressure solenoid valve
US5878766A (en) * 1997-10-20 1999-03-09 Vickers, Incorporated Pressure compensated flow control valve
US6390129B2 (en) * 1999-12-15 2002-05-21 Jansen's Aircraft Systems Controls, Inc. Proportional solenoid-operated fluid metering device
US8100382B2 (en) * 2003-10-09 2012-01-24 Brooks Instrument, LLP Valve assembly
US20080116406A1 (en) * 2003-10-09 2008-05-22 Emerson Electric Co. Valve Assembly
US20090038697A1 (en) * 2005-04-27 2009-02-12 Ryosuke Cho Switching valve
US7987871B2 (en) * 2005-04-27 2011-08-02 Eagle Industry Co., Ltd. Switching valve
US20100019567A1 (en) * 2006-09-15 2010-01-28 Siemens Aktiengesellschaft Self-energizing hydraulic brake
US8201668B2 (en) * 2006-09-15 2012-06-19 Siemens Aktiengesellschaft Self-energizing hydraulic brake
US20080156383A1 (en) * 2006-11-28 2008-07-03 Caterpillar Inc. Fluid-transfer system
US20100132812A1 (en) * 2007-03-27 2010-06-03 Peter Henry Boughman Toilet cistern inlet valve
US8276610B2 (en) * 2007-03-27 2012-10-02 Super Star Toilet System Pty Ltd of RSM of Bird Cameron Toilet cistern inlet valve
US20110024665A1 (en) * 2008-02-11 2011-02-03 MTA House, Level 1, 43-51 Brisbane Street Valve
CN102213330A (zh) * 2010-04-01 2011-10-12 株式会社电装 螺线管滑阀
JP2012122609A (ja) * 2010-11-19 2012-06-28 Denso Corp 油圧調整弁
KR101328280B1 (ko) * 2010-11-19 2013-11-14 가부시키가이샤 덴소 유압 조정 밸브
US8925585B2 (en) 2010-11-19 2015-01-06 Denso Corporation Oil pressure regulation valve
EP2698574A1 (fr) 2012-08-16 2014-02-19 Patrice Mazigh Connecteur pour tuyaux de raccordement de système de climatisation et appareil de climatisation associé
US20170089370A1 (en) * 2014-05-16 2017-03-30 Audi Ag Electromagnet for a hydraulic system
US20170089371A1 (en) * 2014-05-16 2017-03-30 Audi Ag Electromagnet for a hydraulic system
US10662983B2 (en) * 2014-05-16 2020-05-26 Audi Ag Electromagnet for a hydraulic system
US10935056B2 (en) * 2014-05-16 2021-03-02 Audi Ag Electromagnet for a hydraulic system

Also Published As

Publication number Publication date
DE2262247A1 (de) 1974-06-27
IT1050219B (it) 1981-03-10
FR2255532B1 (sv) 1978-09-08
ZA739160B (en) 1974-10-30
SE398850B (sv) 1978-01-23
BR7309978D0 (pt) 1974-08-29
GB1454295A (en) 1976-11-03
FR2255532A1 (sv) 1975-07-18
JPS505928A (sv) 1975-01-22

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