GB2388177A - Resiliently biased motor-driven valve - Google Patents
Resiliently biased motor-driven valve Download PDFInfo
- Publication number
- GB2388177A GB2388177A GB0301507A GB0301507A GB2388177A GB 2388177 A GB2388177 A GB 2388177A GB 0301507 A GB0301507 A GB 0301507A GB 0301507 A GB0301507 A GB 0301507A GB 2388177 A GB2388177 A GB 2388177A
- Authority
- GB
- United Kingdom
- Prior art keywords
- valve
- drive shaft
- motor
- valve member
- spring
- 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.)
- Withdrawn
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
- F16K31/44—Mechanical actuating means
- F16K31/56—Mechanical actuating means without stable intermediate position, e.g. with snap action
- F16K31/563—Mechanical actuating means without stable intermediate position, e.g. with snap action for rotating or pivoting 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
- F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
- F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
- F16K31/043—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
-
- 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
- F16K31/44—Mechanical actuating means
- F16K31/53—Mechanical actuating means with toothed gearing
- F16K31/535—Mechanical actuating means with toothed gearing for rotating valves
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Taps Or Cocks (AREA)
- Electrically Driven Valve-Operating Means (AREA)
Abstract
A valve 10 comprising a rotatable valve member 12, and a motor 14 adapted to rotate the valve member 12 towards either a closed position or an open position. The valve having resilient biasing means 16 adapted to return the valve member 12 to the open position or the closed position respectively when the motor 14 is switched oft wherein the resilient biasing means 16 exerts an approximately constant biasing force on the valve member 12 over the range of rotational movement of the valve member 12 between the open and closed positions. The resilient biasing means 16 is preferably a pre-curled spring strip (figs 2 & 3) made of spring steel. The valve may be a ball valve used in the cooling of an automotive engine.
Description
Title: Valve Description of Invention
The present invention relates to a valve, particularly to a valve with a rotational valve member, such as a ball valve member, for example, which is driven by an electric motor and returned to a rest position by means of a spring.
Electric ball valves are known in which to close or open the valve, the valve member is driven by an electric motor, and when the motor is switched off, the valve member is returned to a rest position by means of a spring. In known such valves the spring is a torsion spring which coils up as the motor drives the valve member e.g. towards the closed position. Thus, when the motor is switched off, and hence the restraining force of the motor is removed, the torsion spring uncoils and drives the valve member back to its rest position.
Disadvantages of valves of this kind are that the electrical power consumption required to drive the valve member to the closed or open position against the force of the spring, the restoring force of which increases as the spring coils up, is relatively high, and, in a valve where the valve member is driven to the closed position, there can be leakage across the valve member if the motor cannot provide sufficient torque to overcome the maximum torque provided by the torsion spring.
According to the invention we provide a valve comprising a rotatable valve member, and a motor, the motor being adapted to rotate the valve member towards either a closed position or an open position, and there being resilient biasing means adapted to return the valve member to the open position or the closed position respectively when the motor is switched off, characterized in that the resilient biasing means exerts an approximately constant biasing force on the valve member over the range of rotational movement of the valve member between the closed and open positions.
( In a valve with a torsion spring, the torque exerted by the motor in order to coil the torsion spring until the valve head is in the closed position, for example, increases as the spring coils up, and similarly, the torque driving the valve head to the open position decreases as the spring uncoils. In order to provide sufficient power to drive the valve head back to the open position, the torsion spring must be relatively tightly coiled when the valve head is in the closed position, and thus the motor must be sufficiently powerful to exert the necessary force to overcome the resistance of the spring as it becomes tightly coiled. By virtue of the provision of a constant force biasing means, less power is required to move the valve, as there is no need for the motor to be capable of overcoming the resistance of an increasingly tightly wound torsion spring in order to close the valve. Thus a smaller motor may be used to operate the valve. There is also less risk of leakage across the valve when the valve is of the kind in which the valve member is driven to the closed position, because the motor only has to exert a relatively lower torque to maintain the valve in the closed position.
Preferably, the resilient biasing means includes a pre-curled spring strip, a first end of which is connected to a drive shaft and a central portion of which is engaged with and curled around a bearing part such that rotation of the drive shaft in a first direction causes the strip to uncurl about We bearing part. In this case, the resilient biasing means may include a plurality of pre-curled spring strips, the first ends of which may be connected to a drive shaft at positions i generally equally spaced around the drive shah.
Providing a plurality of spring ships reduces the force that each spring is required to exert on the drive shaft to achieve a specified total force, which may reduce the fatigue life of each spring. Moreover, arranging a plurality of spring strips at generally equal spacings around the drive shaft generally
balances the radial forces acting on the drive shah, and thus reduces wear on any bearings in which the drive shaft may be mounted.
Preferably the motor is connected to the drive shaft such that operation of the motor causes rotation of the drive shaft in the first direction.
Preferably the drive shaft is connected to the motor by at least one gear.
Preferably the drive shaft is generally cylindrical and has a radius greater than an equilibrium radius of curvature of the or each spring strip.
Preferably the drive shaft is provided with a rotation sensing device adapted to provide an indication of the angular position of the drive shaft.
Information from Me rotation sensing device may thus be used to control the motor to achieve a desired degree of opening or closing of the valve.
Preferably the resilient biasing means is made of spring steel.
In one example, when the valve is for a coolant system for an internal combustion or other engine, the motor is adapted to drive the valve member towards a closed position, and the resilient biasing means is adapted to return the valve member to the open position although the invention may be applied where the valve member is driven to an open position, for use for example in a heating system.
The valve member may be a ball valve.
The invention will now be described with reference to the accompanying drawings, of which, FIGURE 1 is an illustrative side view of a valve according to the invention in a closed position, FIGURE 2 is an illustrative top view of the valve shown in Figure 1 in the closed position, FIGURE 3 is an illustrative top view of the valve as shown in Figure 2, but with the valve in a fully open position FIGURE 4 is an illustrative top view of a portion of an alternative embodiment of the invention.
f Referring now to the figures, there is shown a valve 10 including a rotatable valve member 12, and a motor 14, the motor 14 being adapted in this case to rotate the valve member 12 to a closed position as illustrated in Figures 1 and 2. The valve 10 further includes resilient biasing means 16 which is adapted to return the valve member 12 to an open position, as shown in Figure 3, when the motor 14 is switched off.
The resilient biasing means 16 includes a spring 18 which exerts an approximately constant force on the valve member 12 over the entire range of rotational movement of the valve member 12. The spring 18 in this example, is a pre-curled metal e.g. spring steel strip which is connected at a first end 1 8a to a generally cylindrical drive shah 20.
The spring 18 is typically formed from flat stainless steel strip or high carbon texturised spring steel strip, which after pre-stressing and thermal processing is curled such that under rest conditions, i.e. when no external forces are exerted on the spring 18, the strip forms a tightly wound generally circular coil. When uncoiled, the spring exhibits a tendency to curl which is generally uniform regardless of the spring extension. Such springs are known, and typically used in applications such as cable, hose or cord retraction mechanisms, or as motors for wind- up mechanised toys or clocks.
The spring 18 extends from a drum 20a of the drive shaft 20 and is curled around a generally cylindrical bearing part 22. The radius of the drum 20a is greater than the equilibrium radius of curvature of the spring 18. A rotation sensing device 24, such as a potentiometer, is engaged with a first end portion 20b of the drive shaft 20, and is adapted to provide an indication of the angular position of the drive shaft 20 e.g. relative to a motor housing. This information may be used in controlling operation of the motor 14 to achieve a desired degree of opening of the valve 10. D The motor 14 is an electric motor, and has an output shaft 26 upon which is mounted a first gear wheel 28. The first gear wheel 28 meshes with a second
gear wheel 30, and a third gear wheel 32 is mounted on a common shah, coaxially, with the second gear wheel 30. The third gear wheel 32 meshes with a 90 gear segment 34 mounted on the first end portion 20b of the drive shaft 20. Thus, the motor 14 is connected to the drive shaft 20 through a series of gears 28, 30, 32, 34.
A second end portion 20c of the drive shaft 20 is connected to the valve member 12. The valve member in this example is a ball valve of generally conventional design, and thus the valve member 12 is a generally spherical ball with a cylindrical passage 12a extending centrally through the ball. The diameter of the passage 12a generally corresponds to the internal diameter of the conduit 36 in which the valve 10 is located.
When the valve member 12 is in the open position, as shown in Figure 3, the passage 12a is aligned with a longitudinal axis parallel to a longitudinal axis of the conduit 36, such that fluid may flow along the conduit through the passage 12a of the valve member 12. When the valve member 12 is in the closed position, as shown in Figures 1 and 2, the longitudinal axis of the passage 12a extends generally perpendicular to the longitudinal axis of the conduit 36, and fluid is prevented from flowing along the conduit 36 by the valve member 12.
The valve member 12 is mounted for rotation within the conduit 36 about a longitudinal axis of the drive shaft 20 which extends generally perpendicular to the longitudinal axis of the conduit 36. The valve member 12 may thus be moved from the open position to the closed position by rotating the drive shaft 20 through 90 .
When the valve member 12 is in the open position, as shown in Figure 3, a first edge portion of the gear segment 34 meshes with the third gear wheel 32, and the valve 10 may be closed by operating the motor 14 to rotate the motor output shaft 26 anticlockwise as seen from above. This movement is
transmitted by means of the gears 28, 30, 32, 34 to cause anticlockwise rotation of the drive shaft 20.
The ratios of the gears 28, 30, 32, 34 are selected so that a desired number of revolutions of the motor output shaft 26 causes the drive shaft 20 to rotate through 90 , and thus the required sensitivity of valve member 12 movement may be achieved. If, for example, fine control over valve member 12 movement is required, the gear ratios should be selected such that a large number of rotations of the motor output shaft 26 are required to rotate the drive shaft through 90 .
It will, of course, be appreciated that it is not necessary to use the exact gear arrangement of this embodiment, and the number and arrangement of gears may be varied to achieve a similar result. It is also not necessary to use a series of meshing gears, and any other appropriate transmission arrangement, such as one or more friction couplings, for example, may be used to connect the motor 14 to the drive shaft 20. Altematively, it would be possible to use a stepper motor directly to drive the drive shaft 20, in which case, no gears may be required to connect the motor output shaft 26 to the drive shaft 20.
- Once the drive shaft 20 has been rotated 90 anticlockvvise, a second edge portion of the gear segment 34 is meshed with the third gear wheel 32, and the valve member 12 is in the closed position, as shown in Figures 1 and 2.
This rotation of the drive shah 20 also causes the first end 1 8a of the spring 18 to be pulled away from the bearing part 22, and bent around a 90 segment of the drain 20a. The spring 18 is arranged such that it is bent around the drwn 20a in an opposite direction to the direction in which the spring 18 has been pre-stressed to curl. The spring 18 thus forms an S-shape around the bearing part 22 and the drum 20a.
As the spring 18 is pulled away from the bearing part 22, the bearing part 22 forces the spring 18 to uncurl. This generates a restoring force tending
( to return the spring 18 to its curled state, and the restoring force is generally constant regardless of the degree of extension or uncurling. This restoring force thus tends to rotate the drive shaft 20 clockwise, but the motor 14 is adapted to overcome the restoring force of the spring 18.
As the restoring force of the spring 18 is generally constant regardless of its state of extension, a lower power, and hence smaller, motor 14 may be provided than would be necessary to overcome the resistance of a conventional torsion spring in the same application. In addition, as the resistance offered by the spring 18 does not increase to a maximum as the valve member 12 approaches the closed position, the likelihood of the motor 14 being unable to overcome the resistance of the spring 18 to bring the valve member to a fully closed position is reduced. Thus, the probability of leakage across the valve member 12 is diminished.
When the motor power is switched off, however, the motor 14 allows the restoring force of the spring 18, to cause the drive shaft 20 to rotate clockwise, and the valve member 12 to return to the open position.
Thus, in the event of motor power failure, the valve member 12 is, in this case, restored to the fully open position. It will be appreciated, however, that the valve 10 could, if desired, be arranged so that the motor 14 is used to drive the valve member 12 to the open position, with the spring 18 acting to restore the valve member 12 to the closed position.
Where the valve 10 is integrated win a control system, the rotation sensing potentiometer 24 may be adapted to provide the control system with an indication of the position of the valve member 12.
A valve 10 according to the invention may advantageously be used in a coolant system for an internal combustion or other engine or otherwise, in an application which requires a motor driven valve which fails safe in an open or closed position.
Whilst the embodiment described above incorporates a ball member 12, the invention may be used in conjunction with any other type of power operated valve with a rotatable valve member. Moreover, although the drive shaft 20 in this example rotates through around 90 in order to move the valve member 12 between the open and closed positions, the invention may also be applied to a valve in which rotation of the valve member 12 between the open and closed positions requires rotation of the drive shaft 20 through more or less than 90 , or for multi-port valves in which rotation of the valve member 12 between more than two positions is required. The length and degree of curvature of the spring 18, and the configuration of the gear segment 34 may be altered to accommodate deflections of the drive shaft 20 of more than 90 .
Moreover, whilst in the above example, the restoring force of the spring 18 causes the drive shaft 20 to rotate clockwise, the spring 18 may alternatively be arranged to cause the drive shaft 20 to rotate anticlockwise.
Whilst the embodiment described above incorporates a single spring 18, it is possible for the resilient biasing means to include a plurality of such springs 18, 18'. Figure 4 illustrates an alternative embodiment of the invention, in which two pre-curled spring steel strips 18, 18' are mounted on the drive shaft 20, the first end 18a, 1 8a' of each spring 18, 18' being connected to the drive shaft 20 at a position diametrically opposite the other. Two bearing parts 22, 22' are provided so that each spring 18 curls around a different bearing part 22, 22', the drive shaft 20 being positioned between the two bearings parts 22, 22', and the springs 22, 22' are arranged in a rotationally symmetrical array around the drive shaft. Thus, when the motor 14 is operated, both springs 22, 22' uncurl around the bearing parts 22, 22', and the restoring force tending to rotate the drive shaft 20 clockwise to its rest position is the sum of the restoring forces exerted by both springs 18, 18'.
( By virtue of the provision of two springs 18, 18', the restoring force exerted by each of the springs 18, 18' need only be half the total desired restoring force, which may increase the fatigue life of the springs 18, 18'.
Of course, an unlimited number of springs 18, 18' may be used in a similar fashion to further increase the total restoring force exerted by the springs 18, 18' without increasing the restoring force exerted by each individual spring 18, 18', the number of springs 18, 18' being restricted only by factors such as space and cost of the valve 10.
Preferably, the first ends 18a, 18a' of the springs 18, 18' are connected to the drive shaft 20 at diametrically opposite sides to one another, in a rotationally symmetrical array, in order to balance the radial forces acting on the drive shaft 20, and hence reduce wear on any bearings in which the drive shaft 20 may be mounted for rotation.
In order to achieve a similar result where more than two springs 18, 18' are used, the ends 1 8a, 1 8a' of all of the springs 18, 18' should be connected to the drive shaft 20 at positions which are generally equally spaced around the drive shaft 20, and the springs 18, 18' arranged in a generally rotationally symmetrical array around the drive shaft 20.
The features disclosed in the foregoing description, or the following
claims, or the accompanying drawings, expressed in their specific forms or in terms of a means for performing the disclosed function, or a method or process for attaining the disclosed result, as appropriate, may, separately, or in any combination of such features, be utilised for realising the invention in diverse forms thereof.
Claims (14)
1. A valve comprising a rotatable valve member, and a motor, the motor being adapted to rotate the valve member towards either a closed position or an open position, and there being resilient biasing means adapted to return the valve member to the open position or the closed position respectively when the motor is switched off, characterized in that the resilient biasing means exerts an approximately constant biasing force on the valve member over the range of rotational movement of the valve member between the closed and open positions.
2. A valve according to claim 1 wherein the resilient biasing means includes a pre-curled spring strip, a first end of which is connected to a drive shaft and a central portion of which is engaged with and curled around a bearing part such that rotation of the drive shaft in a first direction causes the strip to uncurl about the bearing part.
3. A valve according to claim 2 wherein the resilient biasing means includes a plurality of pre-curled spring strips.
4. A valve according to claim 3 wherein the first ends of the spring strips are connected to the drive shaft at positions generally equally spaced around the drive shaft.
5. A valve according to claim 2, 3 or 4 wherein the motor is connected to the drive shaft such that operation of the motor causes rotation of the drive shaft in the first direction.
(
6. A valve according to claim 2, 3, 4 or 5 wherein the drive shaft is connected to the motor by at least one gear.
7. A valve according to claim any one of claims 2 to 6 wherein Me drive shaft is generally cylindrical and has a radius greater than an equilibrium radius of curvature of the or each spring strip.
8. A valve according to any one of claims 2 to 7 wherein the drive shaft is provided with a rotation sensing device adapted to provide an indication of the angular position of the drive shaft.
9. A valve according to any preceding claim wherein the resilient biasing means is made of spring steel.
10. A valve according to any preceding claim wherein the motor is adapted to drive the valve member towards the closed position, and the resilient biasing means is adapted to return the valve member to the open position.
11. A valve according to any preceding claim further including a ball valve.
12. A valve according to any preceding claim wherein the valve is a coolant fluid valve for use in an automotive engine.
13. A valve substantially as hereinbefore described with reference to and/or as shown in the accompanying drawings.
14. Any novel feature or novel combination of features hereinbefore described with reference to and/or as shown in the accompanying drawings.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP03009934A EP1359355A1 (en) | 2002-05-01 | 2003-04-30 | Valve |
| JP2003125482A JP2004003643A (en) | 2002-05-01 | 2003-04-30 | Valve |
| AU2003292398A AU2003292398A1 (en) | 2003-01-23 | 2003-12-10 | Valve |
| PCT/GB2003/005369 WO2004065833A1 (en) | 2003-01-23 | 2003-12-10 | Valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0209948A GB0209948D0 (en) | 2002-05-01 | 2002-05-01 | Valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB0301507D0 GB0301507D0 (en) | 2003-02-19 |
| GB2388177A true GB2388177A (en) | 2003-11-05 |
Family
ID=9935856
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB0209948A Ceased GB0209948D0 (en) | 2002-05-01 | 2002-05-01 | Valve |
| GB0301507A Withdrawn GB2388177A (en) | 2002-05-01 | 2003-01-23 | Resiliently biased motor-driven valve |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB0209948A Ceased GB0209948D0 (en) | 2002-05-01 | 2002-05-01 | Valve |
Country Status (1)
| Country | Link |
|---|---|
| GB (2) | GB0209948D0 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004065833A1 (en) * | 2003-01-23 | 2004-08-05 | Dana Automotive Limited | Valve |
| WO2014135274A2 (en) * | 2013-03-05 | 2014-09-12 | Auma Riester Gmbh & Co. Kg | Fitting closing device and fitting actuating assembly |
| DE102014005628A1 (en) * | 2014-04-16 | 2015-10-22 | Auma Riester Gmbh & Co. Kg | Valve switch device and valve actuator assembly |
| US9791027B2 (en) | 2015-09-08 | 2017-10-17 | Reikor Corporation | Apparatus utilizing planetary gearset coupled to a constant torsion spring |
| EP3569894A1 (en) * | 2018-05-14 | 2019-11-20 | Siemens Schweiz AG | Actuator |
| GB2596873A (en) * | 2020-07-10 | 2022-01-12 | Thompson Aero Seating Ltd | Actuation system |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3799190A (en) * | 1972-11-21 | 1974-03-26 | Controls Co Of America | Oil control |
| EP0202413A1 (en) * | 1985-04-03 | 1986-11-26 | Nordson Corporation | Remote control proportional flow adhesive dispensing gun |
| US6062534A (en) * | 1997-04-25 | 2000-05-16 | Fisher Controls International | Double acting rotary valve actuator |
| US6422530B1 (en) * | 2000-03-07 | 2002-07-23 | James W. Williams, III | Fail-safe fluid actuator |
-
2002
- 2002-05-01 GB GB0209948A patent/GB0209948D0/en not_active Ceased
-
2003
- 2003-01-23 GB GB0301507A patent/GB2388177A/en not_active Withdrawn
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3799190A (en) * | 1972-11-21 | 1974-03-26 | Controls Co Of America | Oil control |
| EP0202413A1 (en) * | 1985-04-03 | 1986-11-26 | Nordson Corporation | Remote control proportional flow adhesive dispensing gun |
| US6062534A (en) * | 1997-04-25 | 2000-05-16 | Fisher Controls International | Double acting rotary valve actuator |
| US6422530B1 (en) * | 2000-03-07 | 2002-07-23 | James W. Williams, III | Fail-safe fluid actuator |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004065833A1 (en) * | 2003-01-23 | 2004-08-05 | Dana Automotive Limited | Valve |
| US10215267B2 (en) | 2013-03-05 | 2019-02-26 | Auma Riester Gmbh & Co. Kg | Valve closing device and valve actuating assembly |
| WO2014135274A2 (en) * | 2013-03-05 | 2014-09-12 | Auma Riester Gmbh & Co. Kg | Fitting closing device and fitting actuating assembly |
| WO2014135274A3 (en) * | 2013-03-05 | 2015-01-08 | Auma Riester Gmbh & Co. Kg | Fitting closing device and fitting actuating assembly |
| CN105026812A (en) * | 2013-03-05 | 2015-11-04 | 欧玛里斯特有限责任两合公司 | Fitting closing device and fitting actuating assembly |
| DE102014005628A1 (en) * | 2014-04-16 | 2015-10-22 | Auma Riester Gmbh & Co. Kg | Valve switch device and valve actuator assembly |
| US9791027B2 (en) | 2015-09-08 | 2017-10-17 | Reikor Corporation | Apparatus utilizing planetary gearset coupled to a constant torsion spring |
| US10760657B2 (en) | 2015-09-08 | 2020-09-01 | Riekor Corporation | Apparatus utilizing planetary gearset coupled to a constant torsion spring |
| EP3569894A1 (en) * | 2018-05-14 | 2019-11-20 | Siemens Schweiz AG | Actuator |
| US11047591B2 (en) | 2018-05-14 | 2021-06-29 | Siemens Schweiz Ag | Actuator |
| GB2596873A (en) * | 2020-07-10 | 2022-01-12 | Thompson Aero Seating Ltd | Actuation system |
| EP3936436A1 (en) * | 2020-07-10 | 2022-01-12 | Thompson Aero Seating Limited | Actuation system |
| GB2596873B (en) * | 2020-07-10 | 2023-07-19 | Thompson Aero Seating Ltd | Actuation system |
| US11866981B2 (en) | 2020-07-10 | 2024-01-09 | Thompson Aero Seating Limited | Actuation system |
Also Published As
| Publication number | Publication date |
|---|---|
| GB0301507D0 (en) | 2003-02-19 |
| GB0209948D0 (en) | 2002-06-05 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |