GB2044541A - Movable plunger type electromagnetic valve - Google Patents
Movable plunger type electromagnetic valve Download PDFInfo
- Publication number
- GB2044541A GB2044541A GB8005140A GB8005140A GB2044541A GB 2044541 A GB2044541 A GB 2044541A GB 8005140 A GB8005140 A GB 8005140A GB 8005140 A GB8005140 A GB 8005140A GB 2044541 A GB2044541 A GB 2044541A
- Authority
- GB
- United Kingdom
- Prior art keywords
- plunger
- core
- electromagnetic valve
- stroke
- type electromagnetic
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0644—One-way valve
- F16K31/0655—Lift valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D31/00—Use of speed-sensing governors to control combustion engines, not otherwise provided for
- F02D31/001—Electric control of rotation speed
- F02D31/002—Electric control of rotation speed controlling air supply
- F02D31/003—Electric control of rotation speed controlling air supply for idle speed control
- F02D31/005—Electric control of rotation speed controlling air supply for idle speed control by controlling a throttle by-pass
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M3/00—Idling devices for carburettors
- F02M3/06—Increasing idling speed
- F02M3/07—Increasing idling speed by positioning the throttle flap stop, or by changing the fuel flow cross-sectional area, by electrical, electromechanical or electropneumatic means, according to engine speed
- F02M3/075—Increasing idling speed by positioning the throttle flap stop, or by changing the fuel flow cross-sectional area, by electrical, electromechanical or electropneumatic means, according to engine speed the valve altering the fuel conduit cross-section being a slidable valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D11/00—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated
- F02D11/06—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance
- F02D11/10—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the electric type
- F02D2011/101—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the electric type characterised by the means for actuating the throttles
- F02D2011/102—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the electric type characterised by the means for actuating the throttles at least one throttle being moved only by an electric actuator
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Magnetically Actuated Valves (AREA)
- Electromagnets (AREA)
Abstract
A plunger electromagnetic actuator for an air regulator valve in a throttle chamber bypass in an electronic engine control device comprises a cylindrical coil 5, a core 2 and a plunger 10 disposed in the axial direction of the coil in a central portion thereof and in which parts of the facing ends of the plunger and core have substantially a frustoconical form. The cone angle of the conical parts of the core and plunger is made small as the maximum stroke of the plunger is greater, in order to obtain a proportional relation between the quantity of electricity supplied to the cylindrical coil and the stroke of the plunger. Examples of cone angle ranges for different maximum stroke lengths are given. <IMAGE>
Description
SPECIFICATION
Movable plunger type electromagnetic valve
The present invention relates to a movable plunger type electromagnetic valve for controlling the flow rate of air or fluid in proportion to an inputted quantity of electricity.
The prior art and the present invention and the advantages of the latter will be described with reference to the accompanying drawings, in which:
Figures la and ib show a relation between the stroke of plunger and the attractive force, plotted for various magnetomotive forces, in a typical example of conventional movable plunger type electromagnetic valves;
Figure 2 shows an ideal proportional characteristic between the stroke of plunger and the attractive force;
Figure 3 is a transverse sectional view showing a preferred embodiment of a movable plunger type electromagnetic valve according to the present invention;
Figure 4 is an enlarged view showing a part of the embodiment shown in Fig. 3;;
Figures 5 to 7 show relations between the stroke of plunger and the attractive force, in movable plunger type electromagnetic valves according to the present invention;
Figure 8 is a block diagram showing an example of devices which employ a movable plunger type electromagnetic valve according to the present invention.
Prior to the explanation of embodiments of the present invention, typical examples of the conventional movable plunger type electromagnetic valve will be described below.
The conventional movable plunger type electromagnetic valves have such a relation between the displacement or the stroke of plunger and the attractive force as shown in Fig. 1 a. In more detail, the above relation plotted for a magnetomotive force of x1AT (ampere-turn) is indicated by a curve a, the relation for a magnetomotive force of x2AT, which is greater than x, by a predetermined value, is indicated by a curve b, and the latter relation is shifted to curves C and d every time the magnetomotive force is increased by the predetermined value. Further, when the magnetomotive force is kept constant, the attractive force is increased as the stroke of plunger is shorter. While the characteristic of a spring biasing the plunger is given by a straight line e in Fig. 1 a.The intersecting points of the characteristic line of the spring and the characteristic curves of the plunger, namely, the points where the plunger stands still due to the fact that the attractive force and the biasing force of the spring are well balanced, are spaced apart from each other by different distances f, g, h and i, as is shown in Fig. 1 b which is an enlarged view of a part indicated by a broken line in Fig. 1 a. In other words, the displacement of the plunger is not proportional to the input current.
As is well known, when the attractive force is kept nearly constant in a moving range of plunger under a constant magnetomotive force, and when the attractive force, as shown in Fig.
2, is increased by a constant value with a constant increase in input current, that is, curves a, b, C and dare arranged at regular intervals, a proportional relation is established between the displacement of plunger and the input current. However, many unknown problems have to be solved in order to obtain such a proportional relation.
There is known the following countermeasure for producing the above proportional relation.
That is, facing parts of a plunger and a core are made substantially in a conical form. In other words, the facing part of the plunger and that of the core are formed respectively in a convex cone and a concave cone, which are complementary to each other. Thus, the change of permeance due to the change of stroke is made small. Furthermore, the overlapping length, between a yoke and the plunger which is a function of ineffective magnetomotive force, is varied in accordance with the stroke of the plunger, in order to obtain the magnetomotive force having a flat characteristic. For the above countermeasure, however, the fact how the cone angle of the cone portion affects the relation between the stroke and the inputted current is not yet known very well. Therefore, it is not possible to produce the proportional relation in a satisfactory manner by the above countermeasure.
The electromagnet employed in the movable plunger type electromagnetic valve becomes economical as the ratio of the weight of electromagnet to the unit (effective) work is smaller.
In general, the size of electromagnet in the axial direction becomes large as the maximum stroke of plunger is longer, and the diameter of electromagnet becomes large as the attractive force is stronger, since the number of turns of the winding is increased.
When the maximum stroke of a plunger, the magnetomotive force, the cross section of that part of the plunger which faces the core, and through which magnetic flux passes, and the permeability of air are expressed by x(m), U(AT), S(m2), and 1l, respectively, the attractive force
F(N) (newton) is given by the following equation:
Since F is proportional to the diameter and x is proportional to the size in the axial direction, the index number for determining the cone angle a (of the conical part) capable of producing a maximum electromagnetic efficiency is given by +/F/x.
Although a rough value of the angle a is obtained from the index number, the angle a is, in fact, dependent upon the diameter of the plunger, the maximum stroke x, the material and construction of the magnetic circuit, and so on. Further, since the angle a obtained from the index number is determined from the viewpoint of electromagnetic efficiency (namely, the amount of the displacement of the plunger for a magnetomotive force), the above angle cannot provide an electromagnetic valve having an excellent proportional characteristic.
The inventor has paid attention to the relation between the cone angle and the maximum stroke of the plunger which has an effect upon the proportional characteristic, and has studied the optimum cone angle in accordance with the maximum stroke in order to obtain an excellent proportional characteristic.
An object of the present invention is to provide a movable plunger type electromagnetic valve having an excellent proportional characteristic between the stroke of the plunger and an inputted current.
In order to attain the above and other objects, according to one aspect of the present invention, there is provided a movable plunger type electromagnetic valve comprising a cylindrical coil; a core and a plunger disposed in the axial direction of the cylindrical core in a central portion thereof, a part of the plunger facing the core having substantially a conical form, a part of the core facing the plunger having substantially a conical form, the conical form of the plunger and the conical form of the core being complementary to each other; and input terminals connected to both ends of the cylindrical coil for supplying the cylindrical coil with a supply current: wherein the cone angle of the conical parts of the core and the plunger is made small as the maximum stroke of the plunger is greater, in order to obtain a proportional relation between the quantity of electricity supplied to the cylindrical coil and the stroke of the plunger.
Now, the present invention will be explained below in detail, on the basis of embodiments shown in the drawings. Fig. 3 is a transverse sectional view showing an embodiment of a movable plunger type electromagnetic valve according to the present invention. Referring to Fig.
3, a casing 1 includes in the central portion thereof a core 2. That part of the core 2 which faces a plunger, has the form of a concave cone (strictly speaking, a frustum of a concave cone), and the core 2 includes therein a bearing 3. One side surface of a bobbin 4 has the form of a bag, and a coil 5 is wound on the outer periphery of the bobbin 4. Both ends of the coil 5 are connected respectively to supply terminals 6 and 7. A yoke made of a magnetic material is mounted on the outer periphery having the form of a bag. A member 9 made of a resin units the bobbin 4, the coil 5, the terminals 6 and 7, and the yoke 8, in a body. A plunger 10 is disposed in the inner cylindrical portion of the bobbin 4 through a plunger guide 11, in such a manner that one end of the plunger 10 faces one end of the core 2.The part of the plunger 10 facing the core 2 has the form of a convex cone (strictly speaking, a frustum of a convex cone), which has an appropriate cone angle to be complementary to the concave cone of the core 2.
An output shaft 14 is fixed to the plunger 10, and is supported by the bearing 3 provided in the core 2. A control valve 12 is coupled with the output shaft 11, and is supplied with a predetermined load by a spring 1 3.
In the above construction, when an input current is supplied from a d.c. power supply (not shown) to the coil 5 through the terminals 6 and 7, a magnetomotive force is generated in correspondence to the input current, and the plunger 10 is displaced to a position where the magnetomotive force and the reaction force of the spring 1 3 are well balanced. When a proportional relation is generated between the input current and the displacement of the plunger 10, the above embodiment is called a proportional control valve.
Fig. 4 is an enlarged view showing that part of the embodiment shown in Fig. 3 which includes the plunger 10 and the core 2.
In the structure shown in Fig. 4, when the diameter of the plunger 10, the gap between the yoke 8 and the plunger 10, the overlapping length between the yoke 8 and the plunger 10, the angle made between the bottom and the side of the conical part of the plunger 10, the mean radius of that part of the plunger 10 which is inserted in the core 2, the length of the conical part of the plunger 10, and the spacing between the plunger 10 and the core 2 (namely, the stroke of the plunger) are expressed by D, 8, h, ss, r, H, and x, respectively, the effective permeance Pg is given by the following equation:
Further, the ineffective permeance Ps is given by the following equation:
Thus, the attractive force F acting upon the plunger 10 is given bythe following equation::
The attractive force was set to a desired value on the basis of the above equation, the length and diameter of the electromagnetic valve and the maximum current flowing through the coil were set respectively to desired values, the size of the electromagnet was limited to a predetermined one, and then the optimum value of each of the cone angle a of the conical part of the plunger 10 and the cone angle a' of the conical part of the core 2 was studied by experiments in order to obtain the best proportional characteristic for various maximum strokes.
Thus, such relations as shown in Figs. 5 to 7 were obtained. In this case, the length and diameter of the electromagnetic valve and the maximum current were set equal to 50 mm, 30 mm and 1.3 A, respectively. In each of Figs. 5 to 7, a solid line shows target values.
Fig. 5 shows a relation between the stroke and the attractive force which is plotted in a range of magnetomotive force of 250 to 1000 AT in a case where the maximum stroke is less than 3 mm, and the cone angles a and a' are used as parameter in the above relation.
As is apparent from Fig. 5, the attractive force is increased as the cone angle is greater, when the magnetomotive force is kept constant. Further, the experimental facts shown in Fig. 5 indicate that a satisfactory proportional relation is obtained between the input current and the stroke within a range of cone angles a and a' of substantially 30 to 70 . In other words, in the above range of cone angles, the characteristic curves of the attractive force plotted against the stroke are arranged at regular intervals for input currents which differ from one another by a predetermined value.
In a case where the maximum stroke lies within a range of 3 to 7 mm, as is shown in Fig. 6, a satisfactory proportional relation is obtained between the input current and the stroke within a range of cone angles a and a' of substantially 20 to 50 .
Similarly, in a case where the maximum stroke is greater than 7 mm, as is shown in Fig. 7, a satisfactory proportional relation is obtained within a range of cone angles of substantially 10 to 30". That is, the cone angles have to be made small as the maximum stroke is longer. This fact is a novel one which cannot be derived from the conventional relation based upon the electromagnetic efficiency between the cone angle and the stroke.
As has been described hereinbefore, in a plunger type electromagnetic valve which is not ready to exhibit the proportional characteristic but structurally strong, the cone angles of the plunger and the core are studied on the basis of experiments to obtain an excellent proportional characteristic. As a result of the experiments, it is made possible to provide a proportional control valve which is high in electromagnetic efficiency, small in size, and light in weight.
Fig. 8 is a block diagram for showing a control device which employs a movable plunger type electromagnetic valve according to the present invention. That is, the movable plunger type electromagnetic valve is used as the air regulator which is provided on a bypass of a throttle chamber in an electronic engine control device.
Referring to Fig. 8 which shows a main structure of an electronic engine control device, the flow rate of air which is taken in through an air cleaner 22, is measured by an air flow meter 24, and the electric output indicating the flow rate of air is supplied from the air flow meter 24 to a control circuit 20. The air having passed through the air flow meter 24 is led to a throttle chamber 26, and is then introduced into a combustion chamber 44 of an engine 42 through an intake manifold 36 and a suction valve 38. The quantity of air introduced into the combustion chamber 44 is controlled by changing the opening of a throttle valve 28, which is provided within the throttle chamber 26 and is mechanically interlocked with an accelerator pedal (not shown). The throttle chamber 26 is further provided with a bypass 30 and an air regulator 32.
The air regulator 32 is formed of an air control valve 34 which is an example of movable plunger type electromagnetic valves according to the present invention, and controls the quantity of air passing through the bypass 30 in accordance with the output signal of the control circuit 20. That is, the air control valve 34 controls the speed of revolution of engine in warming-up period of the engine, and so on. The electromagnetic valve 34 shown in Fig. 8 is one of modifications of the embodiment shown in Fig. 3, and includes two valves.
When fuel is injected from a fuel injector 54 in response to an output of the control circuit 20, the suction valve 38 is made open in synchronism with the motion of a piston 46, and a mixed gas of air and fuel is introduced into the combustion chamber 44. The mixed gas is compressed, and then fired by an ignition plug (not shown) to be burnt. Thus, the combustion energy of the mixed gas is converted into the kinetic energy for moving the piston.
The mixed gas which has been burnt, is drawn off through an exhaust valve 40 and an exhaust pipe 56. The exhaust pipe 56 is provided with an exhaust gas recirculating valve (or
EGR valve) 58, through which a part of the exhaust gas is led to the intake manifold 36. That is, a part of the exhaust gas flows back to the suction side of the engine. The quantity of exhaust gas recirculated is controlled by the opening of the exhaust gas recirculating valve 58, and the above opening is controlled by an output of the control circuit 20. The control circuit 20 is provided with a positive supply terminal 60 and a negative supply terminal 62. A water temperature sensor 52 is provided in a water jacket 50 of the engine 42, detects the temperature of the cooling water, and applies a signal corresponding to the detected water temperature to the control circuit.Further, the engine 42 is equipped with an angle sensor 48 for detecting the rotary position of the engine, which generates a reference signal in synchronism with the rotation of engine, for example, at angular intervals at 120 and further generates an angle signal every time the engine is rotated by a predetermined angle (for example, 0.5"). These signals are applied to the control circuit 20 in order to obtain the speed of revolution of engine in the control circuit 20.
In the electronic engine control device having the above-mentioned construction, the air control valve 34 can conduct such four functions as mentioned below.
The first function is to compensate a change with the passage of time in the opening of the throttle valve 28 in idling of engine. When the opening of the valve 28 is varied with the passage of time in idling of engine, the number of rotations of engine in idling of engine is deviated from a desired value. In order to solve this problem, the control circuit 20 calculates the number of rotations in idling of engine on the basis of the output of the angle sensor 48, and supplies the air control valve 34 with a signal to control the opening of the control valve 34..Thus, the speed of revolution of engine in idling of engine is compensated, and the desired number of rotations is obtained.
The second function of the air control valve 34 is to control the speed of revolution of engine in starting time in accordance with the temperature of cooling water. In starting the engine, the temperature of cooling water is detected by the sensor 52, and the air control valve 34 is opened in accordance with the water temperature to increase the number of rotations of engine.
With the increase in the water temperature, the opening of the air control valve 34 is made small to reduce the speed of revolution of engine. When the water temperature is increased to a predetermined value, the air control valve 34 is closed to maintain the speed of revolution of engine at a predetermined value.
The third function is to temporarily increase the quantity of air to conduct the complete combustion in starting the engine. That is, in starting the engine, the air control valve 34 is temporarily opened to increase the quantity of air introduced into the engine. Thus, an optimum mixed gas is formed and the complete combustion is conducted.
The fourth function is to increase the number of rotations of engine when a cooler mounted to the engine is turned on. That is, when the cooler is turned on and therefore the load of engine is increased, the control circuit 20 opens the air control valve 34 by a predetermined value in response to the turning-on of the cooler to increase the number of rotations of engine.
Since the opening of a movable plunger type electromagnetic valve according to the present invention is controlled in proportion to the input current, the flow rate of air passing through the valve is also controlled in proportion to the input current. Therefore, the above valve according to the present invention is well suited for an air control valve in an electronic engine control device, and can appropriately control an engine under various conditions.
Claims (3)
1. A movable plunger type electromagnetic valve comprising a cylindrical coil; a core and a plunger disposed in the axial direction of said cylindrical coil in a central portion thereof, a part of said plunger facing said core having substantially a conical form, a part of said core facing said plunger having substantially a conical form, said conical form of said plunger and said conical form of said core being complementary to each other; and input terminals connected to both ends of said cylindrical coil for supplying said cylindrical coil with a supply current: wherein the cone angle of said conical parts of said core and said plunger is made small as the maximum stroke of said plunger is greater, in order to obtain a proportional relation between the quantity of electricity supplied to said cylindrical coil and the stroke of said plunger.
2. A movable plunger type electromagnetic valve according to claim 1, wherein said cone angle of said conical parts of said core and said plunger lies within an angular range of substantially 30 to 70 when said maximum stroke of said plunger is less than 3 mm, lies within an angular range of substantially 20 to 50 when said maximum stroke lies in a range of 3 to 7 mm, and lies within an angular range of substantially 10 to 30 when said maximum stroke is greater than 7 mm.
3. A movable plunger type electromagnetic valve substantially as herein before described with reference to Figs. 3 to 7 of Fig. 8 of the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1832979A JPS6016734B2 (en) | 1979-02-21 | 1979-02-21 | Movable plunger type electromagnetic flow control device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB2044541A true GB2044541A (en) | 1980-10-15 |
| GB2044541B GB2044541B (en) | 1984-01-11 |
Family
ID=11968578
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB8005140A Expired GB2044541B (en) | 1979-02-21 | 1980-02-15 | Movable plunger type electromagnetic valve |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS6016734B2 (en) |
| DE (1) | DE3006302A1 (en) |
| GB (1) | GB2044541B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2145879A (en) * | 1983-09-01 | 1985-04-03 | Michael Clift | Solenoid actuator with loose-fit armature |
| GB2154066A (en) * | 1984-02-06 | 1985-08-29 | Johnson Service Co | Solenoid actuator with linear force: stroke characteristic to reduce noise |
| EP0976957A2 (en) * | 1998-07-29 | 2000-02-02 | Karl Dungs GmbH & Co. | Servo pressure controller with stepped magnet armature |
| WO2012134277A1 (en) * | 2011-03-25 | 2012-10-04 | Daf Trucks N.V. | Suspension system for a driver's compartment of a vehicle |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IT1119231B (en) * | 1979-10-17 | 1986-03-03 | Fiat Auto Spa | ELECTRONIC CONTROL SYSTEM IN THE COLD STARTING PHASE IN COMBUSTION ENGINES |
| DE3332822A1 (en) * | 1983-09-12 | 1985-03-28 | Robert Bosch Gmbh, 7000 Stuttgart | Solenoid valve with inflexible valve seal |
| DE3416336C2 (en) * | 1984-05-03 | 1997-02-13 | Rexroth Pneumatik Mannesmann | magnetic valve |
| CA1293174C (en) * | 1986-07-24 | 1991-12-17 | General Motors Corporation | Solenoid operated fluid pressure regulator valve |
| DE19836648A1 (en) | 1998-08-13 | 2000-02-17 | Pierburg Ag | Fluid valve |
-
1979
- 1979-02-21 JP JP1832979A patent/JPS6016734B2/en not_active Expired
-
1980
- 1980-02-15 GB GB8005140A patent/GB2044541B/en not_active Expired
- 1980-02-20 DE DE19803006302 patent/DE3006302A1/en not_active Ceased
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2145879A (en) * | 1983-09-01 | 1985-04-03 | Michael Clift | Solenoid actuator with loose-fit armature |
| GB2154066A (en) * | 1984-02-06 | 1985-08-29 | Johnson Service Co | Solenoid actuator with linear force: stroke characteristic to reduce noise |
| EP0976957A2 (en) * | 1998-07-29 | 2000-02-02 | Karl Dungs GmbH & Co. | Servo pressure controller with stepped magnet armature |
| EP0976957A3 (en) * | 1998-07-29 | 2001-01-17 | Karl Dungs GmbH & Co. | Servo pressure controller with stepped magnet armature |
| WO2012134277A1 (en) * | 2011-03-25 | 2012-10-04 | Daf Trucks N.V. | Suspension system for a driver's compartment of a vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| DE3006302A1 (en) | 1980-09-04 |
| JPS6016734B2 (en) | 1985-04-27 |
| JPS55111107A (en) | 1980-08-27 |
| GB2044541B (en) | 1984-01-11 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PE20 | Patent expired after termination of 20 years |
Effective date: 20000214 |