JPH057591B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to proportionally actuated solenoid valves.

More particularly, the present invention is useful in electromagnetic solenoid valves operable to provide fluid control in conjunction with diaphragm operated valves.

BACKGROUND OF THE INVENTION Solenoid valves, such as those described above, are known and utilized to control the flow of liquid or air. Conventional valves of this type use two on-off valves connected in sequence to approximate proportional control and linear response action; Therefore, it has the disadvantage of inherently slow response speed due to the large mass of the armature and the large operating stroke, and also has the disadvantage of an inherently slow response speed due to the large mass of the armature and the large operating stroke. This has the disadvantage that output changes due to source pressure and wear.

Also, for example, US Pat. No. 4,005,733, US Pat.
No. 3529620 and No. 3982554, such valve combination devices are often spring-loaded and operated in conjunction with connecting rods or ball valves, or special It is a complex assembly with a flexible diaphragm made of materials.
These devices enable fluid flow through the valve as a function of changes in current and/or voltage across the solenoid. Some of these valves operate in steady state (i.e. direct current flow at a given voltage);
Acting forces such as mechanical spring bias, electromagnetic fields, and/or fluid pressure are balanced or calibrated to permit operation of the valve in a given mode. However, these valves are generally not electrically adjustable. In at least one case there is also an adjusting device, such as a screw, adapted to vary the fluid flow and pressure acting against the biasing spring, thereby varying the operating state of the valve. The biasing spring of such devices can vary, as can the number of turns of the solenoid coil, the materials of construction, and the dimensions of the assembly. These devices suffer from the drawbacks of being somewhat complex and relatively expensive to assemble.

The solenoid valve as described above is equipped with various small processing units or microprocessors that accept input signals indicative of physical parameters such as the oxygen content of the exhaust gas, vehicle speed, engine speed, engine temperature, etc. It is especially applied to new models of automobiles. Such a microprocessor accepts these input data signals and determines the amount of fuel delivered,
The data is evaluated and/or compared to produce signals that control spark advance or other operating parameters.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a simple valve assembly, in particular electromagnetically adjustable and responsive to changing input electrical signals, which eliminates the drawbacks of the prior art in electromechanical solenoid valves. It is an object of the present invention to provide a valve assembly that can be operated in accordance with the present invention.

Yet another object of the invention is to provide a valve assembly of the type described above which has an adjustable feature that allows a substantially linear relationship between pressure difference and current by means of only one valve. That's true.

SUMMARY OF THE INVENTION The above objects are solved according to the invention by providing an electromechanical solenoid valve arrangement as defined in the claims.

Operation The solenoid valve of the present invention is capable of providing a substantially linear relationship between the output pressure differential and the current input to the valve, thus providing a Such a modified condition of the current input enables a corresponding control of the pressure differential and thus of pressure responsive devices such as exhaust gas recirculation valves.

Features of this valve include an adjustable or movable portion that allows for calibration of the valve to a set point that defines the desired slope of the pressure differential versus current input curve as described below during manufacture of the valve. That's true.

That is, adjustment of such portions of the valve allows adjustment of the set point and adjustment of the slope of the pressure differential versus input current curve to change the reluctance of the flux circuit and to modify the various operating characteristics of the valve. It can be given.

In this way, the output of the valve is set to the customer's desired operation.

Additionally, a flow restriction, such as an orifice, may be provided within the fluid passageway to reduce flow through the valve and allow operation to occur with minimal vacuum, as described below. .

Such small flow conditions require only a very limited amount of flow to operate a solenoid valve, such as the valve of the present invention, especially when considering many devices driven by vacuum obtained from the engine manifold. This is extremely important in the conditions of modern automobiles, where only vacuum is available.

Such small flow characteristics also make it possible to use a sensitive responsive valve with a movable small mass armature or magnetic closure member to control the state of the flux circuit by controlling the input current, as described below. It makes it possible. The closure member moves only a very small distance to provide flow control and allows the closure member to be actuated to fully open, fully closed, or intermediate positions to provide fully open, fully closed, or proportional control of the valve. .

Therefore, using large armatures of mass that have to move over large distances as in the prior art, proportional control and linear response have the disadvantage of inherently slow response speeds due to large actuation strokes. Compared to approximations of the action, the present invention is characterized by superior adjustability, allowing a substantially linear relationship between pressure difference and current with only one valve. Thus, not only does the cost of additional valves as in the prior art be eliminated, but the low flow feature provides a valve that is less sensitive to variations in the vacuum source.

The present invention is useful in an electromagnetic solenoid valve assembly having a central hole terminating in a non-magnetic sheet member within a central interior chamber having an outlet port. A flat disc armature or closure member is provided operable within the central chamber to contact the non-magnetic sheet member and seal fluid flow between the central aperture and the outlet port. The magnetically induced force required to actuate the magnetic closure member is made dependent on the mass of the magnetic closure member and the diameter of the non-magnetic sheet member. the magnetic closure member is perforated;
It may be serrated or otherwise stamped to permit fluid communication to permit communication between the central hole and the outlet port.

The invention can be operated in conjunction with known valve systems. Additionally, the solenoid is operable where fluid pressure is used to control a vacuum-actuated or pressure-actuated device.

EXAMPLES Modes of carrying out the invention will now be described with reference to the accompanying drawings.

Like numerals in the drawings indicate like members.

A solenoid valve assembly 10 constructed in accordance with the present invention is shown in FIG. It is shown in cooperation with assembly 12. This actuation combination 11 is connected between a vacuum source 300 and a vacuum motor 301. A vacuum in the sense indicated here is a pressure below atmospheric pressure. The solenoid valve assembly 10 has a top portion 13 and a bottom portion 15 shown in FIGS. 2, 5A and 5B.
a magnetic outer member or mounting bracket 14 having a hollow cylindrical magnetic core pole piece or central member 16; an electrical winding 18 mounted around the central member 16; It includes a sheet member 20 of material, an annular magnetic closure member 22 (FIG. 3), and a base member 23 defining at least one aperture 129. FIG. 1 shows an electrical connection system 150 with a pair of terminals connectable to a suitable current source 152 by a pair of conductors 154.
The current source 152 can be a direct current source, a rectangular generator, a variable resistor, a pulse width modification or modulation circuit, or an on-board computer serving as a signal source.

Central member 16 defines a cylindrical central bore 24 having an inlet port 26 and an outlet port 28 . Disposed about the central member 16 is a cylindrical sleeve or reference member 30, which is preferably made of a magnetic material to enhance magnetic flux density. The electrical winding 18 is mounted on a bobbin 3 whose upper, lower and inner diameter surfaces are made of plastic material.
2, the bobbin 32 surrounds and engages the reference member 30, thereby encircling almost the entire length of the central member 16. A subassembly consisting of central member 16, reference member 30, bobbin 32 and electrical winding 18 is formed by outer member or bracket 14 (FIG. 5A) and is connected by slot 35 and bobbin 32 which are open on one side. It is rigidly held in place by being attached to a flange 36 formed therein. Although not required, an enclosure 38 surrounds the outer diameter of the electrical winding 18 in this embodiment. A washer retainer or top member 40, preferably of magnetic material, is attached to the top of the enclosure 38 in FIG. 2 and defines an opening 42. Central member 1
6 and reference member 30 project through the aperture 42. Outer member 14 has a tab 43 formed at its upper end above top member 40 for securing top member 40 and subassembly within outer member 14.

As shown in FIG. 6, the center member 16 is formed with a seal slot 46 near its lower end, and the center member 16 terminates in a flange right angle foot 44 having an outer diameter 47 and a lower surface 45. Reference member 30
The lower end of defines a flange 48 having a counterbore 50 having an outer diameter 49 and a wall 51. The non-magnetic sheet member 20 has a shoulder 52, a wall 54 having an opening 53 and an inner surface 58,
It forms the diameter shown. Flanges 44 and 48 have equal outer diameters 47 and 49, respectively, and contact inner surface 58 of sheet member 20.
The flange 48 of the reference member 30 is held in contact with the shoulder portion 52 and press-fitted into the opening 53. The central member 16 is adjustable in position along a vertical axis relative to the reference member 30 and the sheet member 20 to which it is press-fitted, and is
8 and the flange 44, or the lower surface 45 of the central member 16 may be brought into close contact with the lower surface 21 of the seat member 20 and the closing member 22. In this manner, the central member 16 is adjustable to meet specific force requirements as a function of distance relative to the closure member 22.

Examples of modified forms of the central member 16, sheet member 20 and reference member 30 are shown in FIGS. 11 and 12.
As shown in the figure. FIG. 11 shows the reference member 30 and the non-magnetic sheet member 20 as a non-magnetic member 231 formed into a single drawn thin-walled tube. The thickness of this tube material is approximately 0.3 mm (0.01 inch) to allow the wall thickness of the central member 16 to be increased to improve magnetic flux density.
Non-magnetic member 231 includes a sheet 233 and a tubular extension 235 of cylindrical shape. sheet 2
The outer and inner diameters of 33 are greater than the outer and inner diameter dimensions of tubular extension 235, and seat 233 is
The flange or intermediate foot 44 of the central member 16 defines a shoulder 237 that allows upward movement to be restricted. The sheet 233 further includes the closure member 2
2, forming a lower surface 21 that comes into contact with the lower surface 21. Central member 16 is adjustable as a function of distance relative to closure member 22 to meet specific force requirements.

FIG. 12 shows a second modified example of the non-magnetic sheet member 20, in which the sheet member 20 and the bobbin 32 are
is formed as an integral member 240 from a non-magnetic material by casting, molding or other methods. This member 240 of FIG. 12 defines a cylindrical passageway 242 and has a wall 246 similar to the reference member 30 of FIGS.
a flange 48 extending outwardly beyond the thickness of 46;
The reference member 244 is adapted to receive a reference member 244 that does not have a flange, such as. The central member 16 is slidable within the reference member 244 and is restricted from upward movement beyond the contact of the flange 44 with the wall 246. The central member 16 is slidable to vary the function between the flange 44 and the lower surface 21 of the seat member 20, thus meeting specific force requirements as a function of distance from the closure member 22. Adjustable. In this embodiment, reference member 244 is made from a magnetic material and can be thin or thick walled. This is because this material is not integral with the nonmagnetic sheet member 20 and can be used to increase magnetic flux density.

In FIG. 2, bobbin 32 forms a shoulder 59. In FIG. In FIG. 6, the outer wall 5 of the sheet member 20
6 and the shoulder 52 abut against the shoulder 59 of the bobbin 32, thereby being rigidly held. 6th
As shown in the figure, the lower surface 21 of the sheet member 20
and the lower surface 45 of the central member 16 is "x"
It is shown by. Gasket 55 for sealing
is located within the seal slot 46 of the central member 16 and contacts the counterbore wall 51 to provide a seal therebetween. Setting the proper height, i.e., properly setting the distance "x", is performed by attaching the central member 16 to the top surface 60 of the reference member 30 by a known method such as welding.
This is done by fixing the Filter 6
2 is placed on top of the central member 16 to prevent particles from entering the solenoid valve. This filter 62 may be of cellulosic material.

The diaphragm operating valve 12 is a vacuum motor 301
is used to operate the solenoid valve assembly 10 to limit the supply of vacuum source 300 to the vacuum source 300 . Diaphragm operated valve 12 has a bottom cover 102 secured to the lower end of base member 23 by shell 104 . The bottom cover 102 defines a port 106 and a passageway 108 that communicate with a vacuum source 300 . The base member 23 is the neck portion 1
10 and a flange 112 having a seal slot 114 for receiving a seal gasket 116. Flanges 36 and 112 abut each other with sealing gasket 116 providing a tight seal therebetween. Neck 110 is disposed within slot 35 of outer member 14 to maintain diaphragm actuated valve 12 in communication with solenoid valve assembly 10. The flange 112 of the base member 23 and the bobbin 32 cooperate to form an annular chamber 118 and the annular magnetic closure member 22 is operable to engage the seat member 20 . As shown in FIG.
20 and has a diameter "z". The closure member 22 defines openings 122, and these openings form the closure member 2.
Allows fluid to flow through 2. As shown in FIG.
is maintained in a reference position held close to the lower surface 21 (with spacing on the order of 0.038 mm (0.0015 in)). Generally, the seat member 20 is made of a soft material such as brass, and the closure member 22 is made of a hard material such as iron or steel, with the combination of soft material contacting the hard material when the two members come into contact. is giving. This hard-soft material contact provides minimal deformation to the inner top surface of the closure member 22.
20 is actuated into contact with the lower surface 21 of the sheet member 20 to provide better seating and a tighter seal, thereby sealing the hole or passageway 24.
and chamber 118.
Sheet member 20 may also be made of a hard material such as non-magnetic stainless steel or plastic. During normal operation, the closure member 22 is maintained in close proximity to the seat member 20 by a spring 124 attached to the base member 23. Base member 23 includes an upright cylindrical portion 128 terminating in a generally planar flat surface 127 . Spring 1
24 are arranged around this cylindrical portion 128,
Surface 127 aids in positioning magnetic closure member 22. A cylindrical portion 128 extends into the chamber 118 and its flat surface 127 limits downward movement of the closure member 22. The welding of cylindrical portion 128 also serves to limit the welding of chamber 118;
This allows the fluid pressure within chamber 118 and the weld to change more quickly.

The illustrated valve 12 is a dual diaphragm operated valve in which diaphragms 200 and 202 are arranged parallel to each other to form an opening 208 in the middle of which an atmospheric chamber 20 communicates with the atmosphere through a plug 206.
4, and the plug 206 itself is connected to the base member 23.
and the cover 102 . Opening 208 communicates with the atmosphere through a port 211 formed by shell 104. An open port 21 is located above the passage 108.
A connecting sleeve 214 having 5 and 217 is arranged. Valve 12 includes a sealing device 212, shown in its home position in FIG. 2, seated on coupling sleeve 214 to seal port 215. Movable plates 218, 219 are fixed to diaphragms 200 and 202, respectively.
Plate 219 defines an annular opening 220, an annular contact ridge 222 and an annular chamber 224 into which a cap member 225 is inserted.
24 is sealed. A spring 216 is seated in cap member 225 and is adapted to force sealing device 212 into a home position and into contact with sleeve 214. A sealing device 212 contacts the sleeve 214 to remove the opening 22 from the sleeve 214 and the vacuum source 300.
0 to seal the communication to the chamber 226 formed between the plate 219 and the cover 102. Chamber 226 is connected to port 228 formed by cover 102 and coupling device 23
0 to the vacuum motor 301.

Cover 102 defines passageways 130 and 132 and orifice 134. Base member 2
3 and plate 218 cooperate to form a vacuum chamber 136 therebetween. Vacuum state is vacuum source 300
From passages 130, 132 and orifice 134
The vacuum is communicated from chamber 136 to chamber 118 through opening 129 .

FIG. 13 shows a modified embodiment of the assembly 10 shown in FIG. The bobbin 32 of the assembly 10 defines a lower surface 404 open to the chamber 118 and the biasing spring 402 is positioned against the lower surface 404 and in contact with the magnetic closure member 22 . The biasing spring 402 provides a force that acts to maintain the aforementioned closure member 22 in a normally open relationship with the lower surface 21 of the non-magnetic sheet member 20. Furthermore, this biasing spring 402
hole 24 as shown in FIGS. 2 and 13.
It is maintained at a reference position perpendicular to the vertical axis of. It has been found that the act of maintaining the closure member 22 in a reference position in this manner prevents angular displacement of the closure member 22 from its perpendicular relationship to the vertical axis.

Closing member 22, shown in FIG. 2 in a reference position proximate seat member 20 during operation, is driven by a current passed through electrical winding 18 to generate magnetic flux in valve assembly 10 at a given voltage. respond quickly to the magnetic flux induced by A magnetic circuit is created through the outer member 14, the closure member 22, the center member 16, the reference member 30, the top member or washer retainer 40, and the air gap between the outlet port 28 of the center member 16 and the closure member 22. Under steady state conditions, when direct current is being passed through the electrical winding 18, the closure member 22 is pulled towards the sheet member 20 and held in this position until the magnetic flux is interrupted. When the current is interrupted, i.e. when the magnetic flux is interrupted, the closing member 22 is caused by gravity and pressure difference to spring 1 as shown in FIG.
24, which spring 124 serves as a means for pushing the closure member 22 into the reference position.

A pressure lower than atmospheric pressure or vacuum is provided at port 106.
When a vacuum condition is applied to the passages 108, 13
0,132 and chamber 1 through orifice 134.
36 and 118. If the vacuum in chamber 136 is large enough to deflect diaphragms 200 and 202 against atmospheric pressure;
Valve plates 218, 219 move vertically upward from the reference position shown in FIG. As the raised lip 222 moves upward, it lifts the sealing device 212 and closes the opening 21.
7 and port 215 to provide vacuum communication between passageway 108 and chamber 226.

In the combined system of valves 10 and 12 shown in FIG.
4, communicates with chamber 118 of solenoid valve assembly 10 through chamber 136 and opening 129. Central member 1
6 introduces atmospheric air into chamber 1 through inlet port 26, passageway or hole 24 and outlet port 28 as shown.
It is connected to 18.

When electrical winding 18 is energized by power supply 152 , a magnetic flux is induced that attracts closure member 22 toward central member 16 . Seat member 20 contacts surface 120 of closure member 22, thus blocking communication between chamber 118 and passageway 24. The force (magnetic flux) required to move the closure member 22 depends on the mass of the closure member 22, the pressure difference between the chamber 118 and the passage or hole 24, and the seat member 2.
It is related to the diameter "y" of 0. The diameter "y" of the seat member 20 and the mass of the closure member 22 are determined at the time of assembly. The operating variables that influence the movement of the closure member 22 are therefore the pressure difference and the magnetic force, the latter being proportional to the current through the winding 18 at a given voltage.

The force of the magnetic field in a solenoid valve is proportional to the input power to the electrical winding, as shown in Figure 7 (Harvard Rotters, "Electromagnetic Devices", 1st edition, 10th printing).
1967 (New York City Willie & Size Incorporated, 1941, no.
232 pages). In this example, when the hole 24 is at atmospheric pressure and a vacuum (pressure lower than atmospheric pressure) is introduced into the chamber 118, the pressure difference acting on the face 120 of the closure member 22 is applied to keep the closure member 22 open. It happens. The attractive force of the magnetic flux is the mass of the closing member 22 (approximately 1.4gr), gravity, and the force of the closing member 22 due to the force of the spring 1.
The force of the downward pressure exerted on surface 120 must be overcome to seat it on surface 24 and hold it in the reference position. Since the mass of closure member 22 is constant, the magnetic force required to move closure member 22 is a function of the pressure difference. This magnetic force has been found to be proportional to the current (in amperes) passing through the electrical winding 18 under ideal conditions, as shown in FIG. In the present invention, the pressure difference (mercury column (2.54 cm i.e.
An empirical illustration of the variation of vacuum) with in) is shown in FIG. Although the linear functions of FIG. 9 show the shape of the hysteresis loops, a straight line function is superimposed between these loops as an approximation to the ideal case of FIG. This function in FIG. 9 is for a solenoid having a resistance of 43 ohms, an electrical input of 160 hertz, and acting against a vacuum input of 14 inches of mercury. Similar curves have been determined for various resistances, frequencies and pressure differences.

Movement of the set point to provide a significant change in vacuum input level from a vacuum of 12.7 cm (4 in) of mercury to a vacuum of 50.8 cm (20 in) for a square wave input signal at a low frequency such as approximately 80 hertz It has been found that there is. For such low frequency operation, the orifice 134 may form a laminar to the jet flow structure and improve fluid flow characteristics to alleviate the set point movement problems discussed above. has been found.

Any given point along this linear function can be selected and designated as a set point. At this set point, the corresponding amperage value for a solenoid with the characteristics that created this curve is
4 and chamber 118, a magnetic field strong enough to attract closure member 22 to sheet member 20 against the subatmospheric vacuum is induced.

Therefore, the closure member 2 in contact with the sheet member 20
The operation of chamber 2 is constant or related to a given amperage value, and when the pressure difference between chamber 118 and hole 24 is at or below the set point along the curve, chamber 1
18 and hole 24.

It is also noted that the vacuum within chamber 118 is communicated through orifice 134. There are significant differences in the diameters of holes 24 and orifices 134 and sheet members 20. As an example, in some applications, orifice 134 has a diameter of approximately 0.51 mm (0.020 in), hole 24 has a diameter of approximately 1.52 mm (0.060 in), and seat member 20 has a diameter of approximately 7.62 mm (0.300 in). in). however,
The pressure difference between the chamber 118 and the hole 24 is a function of the magnetic force acting on the closure member 22 because the spacing between the surface 120 of the sheet member 20 and the closure member 22 is very small. The fact that orifice 134 is shown within valve 12 does not affect the operation of solenoid valve assembly 10. This is because a similar communication orifice can be disposed integrally with the communication means or opening 129 or the solenoid valve assembly 10.

The operation of the device described above is shown as being proportional to a given power, amperage or voltage input to the electrical winding 18. The curves of the Lotters reference cited above are shown in FIG. 7 as a family of curves on Cartesian coordinate axes. As noted, the horizontal or horizontal axis is the armature (in this example, the closure member 2
2) is the length of the stroke, and the vertical axis represents the force. In this example, the armature stroke has very small increments, about 0.038 mm (about 0.0015 inches). However, since there is a constant distance "x" from the central member 16 to the lower surface 21 of the seat member 20, the length of the stroke over which this force must act is x (mm
)+0.038mm (xin+0.0015in). Therefore, the actual movement of the closure member 22 has been kept to a minimum in order to provide a more rapid response and better control. If a pair of vertical lines extend along the horizontal axis shown in Figure 7 at distances x and x+0.038mm
If drawn at (x+0.0015in), these vertical lines intersect a family of curves at various amperage values. Therefore, this solenoid valve operates within a very narrow range of these variables, thereby causing the chamber 118 to
and provides better control of the actuation for regulating fluid flow between the holes 24.

The solenoid valve assembly described above will open and close at either set point. That is, the opening/closing operation is performed at any point along the linear function shown in FIG. In this case the pressure difference can be selected to be responsive to a given input current, or the input current (8
(shown on the horizontal axis of the figure) can be selected to move the closure member 22 at a given pressure difference. In either case, the solenoid valve assembly 110
has been found to be temperature insensitive at a given peak amperage value over the normal operating temperature range of an automobile engine compartment. This state is
The signal source is a square wave and the control is based on the duty cycle, i.e. the current flow time % within a given total time.
This is often the case when a car's on-board computer is used as such a signal source. At higher temperatures, this duty cycle is increased to compensate for these changed high temperature conditions. This is illustrated in FIG. 10, where the output curves are constructed at two temperatures: 23.3°C (74°F) and 121°C (250°F). The results show only significant changes in the position of the curves.

Dimension “y” of sheet member 20 shown in FIG.
is relatively large compared to the diameter of the hole 24. Such dimensional differences accommodate operation by vacuum actuated devices such as diaphragm actuated valve 12. If a high pressure (above atmospheric) pressure source is attached to the inlet port 26 of the central member 16, the restriction 303 of FIG. The pressure actuating device 304 is connected thereto.
The non-magnetic sheet member 20 for high pressure operation is generally constructed with a diameter based on empirical testing to determine the mode of operation consistent with the slave motor 304 and surrounding operating conditions. However, the dimensions of the sheet member for operation at such high pressures will be much closer to the holes 24 than for vacuum operation.

With the present invention constructed as described above, the actuating combination 11 comprising the solenoid valve assembly 10 and the diaphragm actuated valve assembly 12 can operate as follows. That is, the vacuum supplied to the assembly 10 from the vacuum source 300 through the orifice 134 in the assembly 12 is applied to the fixed magnetic central member within the annular chamber 118 with its position adjusted relative to the reference member 30. 16 fluid passages 24 with the interposition of a non-magnetic sheet member 20 within the annular chamber 118 and a magnetic closure member 22 cooperating with these central member 16 and sheet member 20. electrical winding 1
8, the closure member 22 is magnetically actuated and drawn toward the seat member 20 to close the opening formed between the seat member 20 and the closure member 22. passing through the chamber 118
movement into a given position according to the fluid flow induced by the vacuum within, creating the desired pressure difference, which is transmitted to the assembly 12 through the communication opening 129, so that the desired pressure difference is , sealing device 212
The vacuum motor 301 is supplied by the operation of the diaphragms 200 and 202 which actuate the vacuum motor 301.

This actuating assembly device 11 is a modern motor vehicle equipped with a microprocessor that receives input signals indicative of physical parameters such as the oxygen content of the exhaust gas, the speed of the vehicle, engine speed, ejector temperature, etc. It is particularly suitable for use in

While one particular embodiment of the invention has been illustrated and described, it will be obvious that various modifications and variations may be made therein. It is therefore to be understood that the appended claims broadly cover all modifications and variations that fall within the spirit and scope of the invention.

Effects of the Invention Since the present invention is constructed as described above, the present invention has an inexpensive structure, maintains a linear relationship between the output pressure difference and the input current of the valve during manufacturing, and adjusts the slope as desired. Adjustment of the input current allows adjustment of the set point so that the current input, such as from an on-board computer in a vehicle, can be varied by adjusting the input current to a pressure differential or corresponding pressure-responsive device such as an exhaust gas recirculation valve. This provides an excellent solenoid valve assembly that enables control.

[Brief explanation of the drawing]

FIG. 1 is a side view of the solenoid valve assembly of the present invention showing its connection to a power supply source and a vacuum source. FIG. 2 is a vertical cross-sectional view of the proportionally actuated solenoid valve assembly of the present invention, shown on a larger scale than in FIG. 1; FIG. 3 is a plan view of the closure member shown in FIG. 1; 4 is a partial cross-sectional view of a modified embodiment of the valve assembly of FIG. 2; FIG. FIG. 5A is a plan view of the outer member or mounting bracket. FIG. 5B is a side view of FIG. 5A. FIG. 6 is a partially enlarged sectional view of the nonmagnetic sheet member and magnetic control member assembly. FIG. 7 is a diagram showing force versus stroke in a solenoid valve device. FIG. 8 is a diagram showing the linear output of the present invention. FIG. 9 is a diagram plotting empirical data of pressure difference as a function of current. FIG. 10 is a diagram showing the effect of temperature on the operation of the present invention. 1st
FIG. 1 is an enlarged sectional view showing a modified example of a sleeve made of a single member, that is, a combination of a reference member and a non-magnetic sheet member. FIG. 12 is an enlarged sectional view showing a modified example of a combination of a single non-magnetic sheet member and a bobbin. FIG. 13 is a vertical cross-sectional view of a modified embodiment of the proportionally actuated solenoid valve assembly of the present invention. 10...Solenoid valve assembly, 12...Diaphragm actuated valve, 14...Outer member or mounting bracket, 15...Bottom, 16...Central member or magnetic core pole piece, 18...Electrical winding, 2
0... Non-magnetic sheet member, 22... Magnetic closing member, 23... Base member, 24... Hole or passage, 26... Inlet port, 28... Outlet port,
30,244...Reference member or sleeve, 3
2...Bobbin, 40...Top member or washer retainer, 152...Power supply source, 20
0,202...Diaphragm, 300...Vacuum source, 301...Vacuum motor or vacuum operating device, 304...Pressure operating device.

Claims (1)

Claims: 1. An electromechanical valve arrangement comprising: an electrical winding 18 defining a central magnetic flux axis; and a substantially cylindrical central axial member defining a fluid passageway 24 aligned with the magnetic flux axis. 16. A magnetic flux circuit forming a magnetic flux path including a plurality of adjacent axial members including an axial outer member 14 and an axial top member 40 adjacent to one end 26 of the fluid passageway 24, wherein the plurality of adjacent axial members an axial member that includes one physically movable member, the physically movable member being movable relative to an adjacent member and within the magnetic flux path of the movable member; said magnetic flux circuit adapted to adjust a portion thereof and to adjust the size of the air gap between said movable member and said adjacent member; an annular non-magnetic sheet member 20 having a central opening disposed near the lever; and a magnetic closure member 22 extending from the non-magnetic sheet member 20.
is positioned adjacent to and forms a portion of the magnetic flux passageway and is pushed through the fluid passageway 24 and the central opening of the sheet member 20 into abutment against the closure member 22 by a predetermined pressure difference. Fluid flow is regulated by varying the energization level of the electrical winding 18, and the closure member 22 has a circular closure surface 120 substantially perpendicular to the axis of the fluid passageway 24. , and a change in the size of the air gap caused by movement of the movable member along the magnetic flux path changes the reluctance of the magnetic flux circuit and correspondingly changes the magnetic resistance of the electrical winding 18. adjusting the response of said valve arrangement to a given energization level to produce a given pressure differential; the non-magnetic sheet forming a cylindrical chamber 118 constraining the annular sheet member 20 to be substantially parallel to the longitudinal axis of the fluid passageway 24 between abutting and spaced apart from the annular sheet member 20; an electromechanical valve arrangement comprising: a position adjacent member 20; 2, the fluid passageway 24 of the central member 16 has a predetermined cross-sectional area, and the magnetic closure member 2
2 is arranged adjacent to said non-magnetic sheet member 20 to form a fluid opening that is substantially smaller than said predetermined cross-sectional area that provides the operative position of said closure member 22. The electromechanical valve device according to item 1. 3 the seat member 20 is disposed proximate an outlet end 28 of the fluid passageway 24 and the central member 16 is physically movable within the valve arrangement;
Adjusting the portion of the central member 16 within the magnetic flux path and controlling the central member 16 or the outlet end 2
8. An electromechanical valve arrangement according to claim 1, adapted to adjust the size of the air gap between the magnetic closure member 8 and the magnetic closure member 22. 4 said closure member 2 adapted to communicate with said fluid passageway 24 through a fluid opening that is substantially smaller than a predetermined cross-sectional area of said fluid passageway 24;
3. The electromechanical valve system of claim 2, further comprising a device forming a fluid chamber 118 surrounding a fluid chamber 118, the fluid conduit device having a first end extending from the fluid chamber 118. a fluid conduit arrangement adapted to allow a fluid pressure differential to be provided between an outlet end 28 of the fluid passageway 24 and a second end of the fluid conduit arrangement; and within the fluid chamber 118. 129. An electromechanical valve device comprising: a device 129 that utilizes the relative pressures of; 5. The electrical system of claim 4, wherein the fluid passageway 24, the fluid opening formed by the closure member 22, the fluid chamber 118 and the fluid conduit device form one fluid path. a restriction device 134 in the fluid path for restricting the flow of fluid through the fluid path, the restriction device 134 for providing different operative positions of the closure member 22; An electromechanical valve device having an effective cross-sectional area smaller than a cross-sectional area of the fluid passageway 24 and the fluid conduit device and smaller than a cross-sectional area of the fluid opening. 6. An electromechanical valve assembly comprising: an electrical winding 18; and a magnetic flux circuit magnetically coupled to the winding 18 to form a magnetic flux path, the magnetic flux circuit comprising a substantially cylindrical magnetic Central member 16, magnetic outer member 1
4 and a magnetic top member 40 adjacent the inlet end 26 of the fluid passageway 24;
6 is physically movable along the magnetic flux path within the valve arrangement to adjust the portion of the central member 16 within the magnetic flux path and the size of the air gap adjacent the central member 16. the magnetic flux circuit having a central opening aligned with and disposed adjacent the outlet end 28 of the fluid passageway 24, the central opening having a cross-sectional area larger than the cross-sectional area of the fluid passageway 24; a non-magnetic sheet member 20 adapted to form a larger pressure-applying cross-sectional area; and a non-magnetic sheet member 20 disposed adjacent to said non-magnetic sheet member 20 and adapted to substantially cover said central opening and said magnetic flux. A magnetic closure member 22 that completes the passageway allows the flow of fluid forced through the fluid passageway 24 and the central opening of the sheet member 20 by a predetermined pressure difference to the electrical winding 18 .
wherein the closure member 22 defines a circular closure surface 120 substantially perpendicular to the axis of the fluid passageway 24 and the central area along the magnetic flux path. Movement of member 16 causes said central member 1 to move within said magnetic flux path.
6 and the size of the air gap, thereby varying the reluctance of the magnetic flux circuit of the valve assembly for a given energization level of the electrical winding 18. said magnetic closure member 22 adapted to correspondingly adjust the response actuation to provide a given pressure difference; and adjacent said non-magnetic sheet member 20 and receiving said magnetic closure member 22 to direct the movement of said magnetic closure member 22; a device for forming a cylindrical chamber 118 adapted to constrain the fluid passageway 24 substantially parallel to the longitudinal axis between a position abutting the annular sheet member 20 and a position spaced therefrom; Electro-mechanical valve assembly. 7. An electromechanical valve assembly comprising: an electrical winding 18 defining a central magnetic flux axis; and a substantially cylindrical magnetic center defining a fluid passageway 24 of predetermined cross-sectional area aligned with said magnetic flux axis. a magnetic flux circuit defining a magnetic flux path including a member 16, a magnetic outer member 14, and a magnetic top member 40 adjacent one end 26 of the fluid passageway 24; 24; The relative axial positions of the central member 16 and the axially extending portion of the seat member 20 are adjustable, such that the spacing between the other end 28 and the seating portion 21 is adjusted. a magnetic closure member 22 disposed adjacent to said non-magnetic sheet member 20 forming a fluid aperture, said fluid aperture providing various operative positions of said magnetic closure member 22; the magnetic closure member 22 being substantially smaller than the predetermined cross-sectional area for the purpose of the present invention; and forming a fluid chamber 118 that communicates with the fluid passageway 24 through the fluid opening and surrounds the closure member 22. means; a fluid conduit device having a first end extending from the fluid chamber 118 for providing a fluid pressure differential between the other end 28 of the fluid passageway 24 and the other end of the fluid conduit device; and the closure member 22 forms part of the magnetic flux circuit to allow the fluid to flow through the fluid passageway 24 and the central opening of the sheet member 20 by a predetermined pressure differential. The flow of fluid forced against the closure member 22 is adjusted by varying the energization level of the electrical winding 18, which extends in the axial direction of the non-magnetic sheet member 20. adjustment of the relative position of the center member 16 and the central member 16 changes the effective magnetic air gap;
thereby changing the reluctance of the valve assembly for a given energization level of the electrical winding 18 to produce a given pressure differential. Electro-mechanical valve assembly. 8. An electromechanical valve assembly comprising: an electrical winding 18 defining a central magnetic flux axis; a magnetic flux circuit including a substantially cylindrical magnetic central member 16, a magnetic outer member 14 and a magnetic top member 40; a non-magnetic annular sheet member 20 having a central opening defining a fluid passageway of a predetermined cross-sectional area aligned with the magnetic flux axis; and a magnetic closure disposed adjacent to the non-magnetic sheet member 20 defining a fluid opening. A member 22, wherein the fluid opening is substantially smaller than the predetermined cross-sectional area to provide various operative positions of the closure member 22, and the closure member 22 is a portion of the magnetic flux circuit. forming a fluid passageway of predetermined cross-sectional area and a central opening of the sheet member 20 through the closure member 22.
said magnetic closure member 22 such that the flow of fluid caused by a predetermined pressure difference can be adjusted by varying the energization level of said electrical winding 18; and is adjacent to the non-magnetic sheet member 20, receives the magnetic closure member 22, and directs the movement of the magnetic closure member 22 along the length of the fluid path between a position in contact with the non-magnetic annular sheet member 20 and a position away from the same. means forming a cylindrical guide 118 constraining substantially parallel to a directional axis; said guide 118 communicating with said fluid passageway 24 through said fluid opening and defining a fluid chamber 118 surrounding said closure member 22; The fluid chamber 1
the restriction device 1 having a first end extending from 18;
34 is provided, the restriction device 134 having an effective cross-sectional area substantially less than the cross-sectional area of the predetermined cross-sectional area of the fluid passageway 24. An electromechanical valve assembly comprising: a fluid conduit device; a device 129 for utilizing relative pressure within the fluid chamber 118; 9. The electromechanical valve assembly of claim 8, wherein the device 129 for utilizing the relative pressure within the fluid chamber 118 is an opening 129 in the fluid chamber 118. 10. An electromechanical valve assembly as claimed in claim 8 adapted for use with a pressure responsive device, wherein the device 129 utilizes relative pressure within the fluid chamber 118.
and a valve assembly in a conduit 129 for providing communication between said pressure responsive device 12.