GB2391057A - Magnetic flow restrictor - Google Patents
Magnetic flow restrictor Download PDFInfo
- Publication number
- GB2391057A GB2391057A GB0216924A GB0216924A GB2391057A GB 2391057 A GB2391057 A GB 2391057A GB 0216924 A GB0216924 A GB 0216924A GB 0216924 A GB0216924 A GB 0216924A GB 2391057 A GB2391057 A GB 2391057A
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- GB
- United Kingdom
- Prior art keywords
- shuttle
- upstream
- downstream
- adjustment
- enclosure
- Prior art date
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- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 101
- 239000012530 fluid Substances 0.000 claims abstract description 35
- 238000003491 array Methods 0.000 claims abstract description 17
- 230000008878 coupling Effects 0.000 claims description 11
- 238000010168 coupling process Methods 0.000 claims description 11
- 238000005859 coupling reaction Methods 0.000 claims description 11
- 239000000696 magnetic material Substances 0.000 claims description 11
- 230000033001 locomotion Effects 0.000 claims description 9
- 241000252067 Megalops atlanticus Species 0.000 claims description 5
- 230000006835 compression Effects 0.000 claims description 5
- 238000007906 compression Methods 0.000 claims description 5
- 238000012423 maintenance Methods 0.000 claims description 5
- 239000007787 solid Substances 0.000 claims description 5
- 230000000452 restraining effect Effects 0.000 claims description 2
- 230000003247 decreasing effect Effects 0.000 claims 2
- 230000001737 promoting effect Effects 0.000 claims 2
- 230000035945 sensitivity Effects 0.000 claims 2
- 230000013011 mating Effects 0.000 abstract 1
- 239000000463 material Substances 0.000 description 21
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 13
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 8
- 238000005260 corrosion Methods 0.000 description 7
- 230000007797 corrosion Effects 0.000 description 7
- 238000005299 abrasion Methods 0.000 description 5
- 239000004033 plastic Substances 0.000 description 5
- 229920003023 plastic Polymers 0.000 description 5
- 229910052742 iron Inorganic materials 0.000 description 4
- 239000004800 polyvinyl chloride Substances 0.000 description 4
- 229920000915 polyvinyl chloride Polymers 0.000 description 4
- 239000004593 Epoxy Substances 0.000 description 3
- 239000003651 drinking water Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 229910001369 Brass Inorganic materials 0.000 description 2
- 229910000906 Bronze Inorganic materials 0.000 description 2
- 229910000760 Hardened steel Inorganic materials 0.000 description 2
- 235000012206 bottled water Nutrition 0.000 description 2
- 239000010951 brass Substances 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 238000010137 moulding (plastic) Methods 0.000 description 2
- 230000009972 noncorrosive effect Effects 0.000 description 2
- 239000006223 plastic coating Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 239000010935 stainless steel Substances 0.000 description 2
- 229910001220 stainless steel Inorganic materials 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- VEXZGXHMUGYJMC-UHFFFAOYSA-M Chloride anion Chemical compound [Cl-] VEXZGXHMUGYJMC-UHFFFAOYSA-M 0.000 description 1
- 229910000881 Cu alloy Inorganic materials 0.000 description 1
- 229910001335 Galvanized steel Inorganic materials 0.000 description 1
- 241000543375 Sideroxylon Species 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 235000020188 drinking water Nutrition 0.000 description 1
- 239000013536 elastomeric material Substances 0.000 description 1
- 239000000835 fiber Substances 0.000 description 1
- 239000008397 galvanized steel Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000007373 indentation Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 229910000679 solder Inorganic materials 0.000 description 1
- 229920003051 synthetic elastomer Polymers 0.000 description 1
- 239000005061 synthetic rubber Substances 0.000 description 1
- 238000005406 washing Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/08—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid using a permanent magnet
- F16K31/084—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid using a permanent magnet the magnet being used only as a holding element to maintain the valve in a specific position, e.g. check valves
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D7/00—Control of flow
- G05D7/01—Control of flow without auxiliary power
- G05D7/0126—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs
- G05D7/0133—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs within the flow-path
- G05D7/014—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs within the flow-path using sliding elements
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Automation & Control Theory (AREA)
- Mechanical Engineering (AREA)
- Measuring Volume Flow (AREA)
Abstract
A magnetic flow restrictor comprises straight main pipe 1 attached upstream to bend pipe 3, and fitted with downstream and upstream magnetic arrays 6-9 and 10-13 respectively, concentrically supporting internally mobile shuttle 15, comprising main cylinder 18, with downstream support magnet 16 and conical downstream shield 20 and rear cylinder 19 with frustrum shield 21 and upstream support magnet 17. Fluid entering upstream pipe 5 passes around shuttle 15 causing it to move downstream closing space between shield 20 and constriction 14 of main pipe 1 with reduced fluid pressure and flow. However shuttle 15 is prevented from closing completely by forces exerted between magnet 17 and shuttle locator magnet 24 fixed to end of shaft 23 which passes though magnet 17 and wall of pipe 3, with screw thread 27 of mounting 26 mating with threaded end 28 of shaft 23, allowing adjustment of said shaft position and flow rate. A coil spring 39 (50, Fig 9) may be employed to assist the magnetic force between magnets 17, 24. The cylinder 18 may have external, curved guide vanes (36, Fig 5).
Description
MAGNETIC FLOW RESTRICTOR
This invention relates to a magnetic flow restrictor, which would be suitable for regulating flow in fluid control and drinking water supply systems.
With increasing population and growing demand for potable water, water supply companies and related government agencies are finding it harder to satisfy supply requirements within the available budget. This is partly because water resources are scarcer and located increasingly far from the supply center and partly because many existing water sources are becoming polluted and require expensive treatment before use. There is also an ongoing attempt to supply larger percentage of the population with potable water, but this additional served area and population may frequently be located further from the sources.
Much of the cost of developing supply systems lies in the cost of main transmission and distribution pipework. There is also a substantial cost component in many systems related to water storage, which is provided in part to allow for fluctuation in water demand throughout the day. Thus at some times during the day when demand is high, such as when most people are getting up in the morning and washing before they go to work, water is drained from the full reservoirs. At other times such as in the late night and early morning hours, the demand from users is low, so that extra available water can be used to refill the empty reservoirs.
For smaller towns with served populations of 10,000 persons or less, the peak hour demand from users may be as much as, or more than twice the average hourly demand for the day.
loo meet this demand it is usually necessary to provide pipework of adequate flow capacity, so that the diameter of pipes laid must be greater than that necessary to provide flow at the average hourly rate. The additional size frequently results in a unit cost difference per length laid of more than 50%. Although this additional cost of pipe network can often be met by supply operators for larger and richer towns, it can represent an unacceptable financial burden for smaller and less developed towns. The added costs of pipe and reservoirs to satisfy the peak demand requirements will result in an unacceptably high capital investment and unacceptably high water tariffs.
One possible solution to this problem is to limit the supply at each faucet to the average hourly rate. in this way, consumers will theoretically still be able to receive the same quantity of water in one day as they would receive with the more expensive peak hour system. However in order to benefit fully from this average supply, each consumer family should provide their own small storage tank, which would allow stored water to be used during peak hours.
in the case of most newly constructed water supply systems it is common to provide flow meters at each service connection that would measure the flow of water received by each consumer family. In the case of average hour systems, it would also be necessary to provide flow restrictors that would only allow a flow rate of a preset amount to be passed to the consumer outlet.
In early systems designed for average hourly flow rates, flow restrictors commonly consisted of short lengths of pipes with reduced diameter fixed orifice plates inserted. These orifices quickly became clogged which resulted in modified movable orifice types such as that described in British Patent No. GB19900023043/19901023 (EP0482904). However, due to widely varying pressures in different parts of the system this was found to be inequitable.
Later systems designed for average hourly flow rates included more sophisticated manually adjustable orifice devices which could be set to provide the average hourly flow rate over the whole day by reference to the metered amount. An example of an adjustable type is given in French Patent No. FR19950002589119950306 (EP0736635). However these devices have always been difficult to adjust fairly, as the flow rate passing is still dependent on system pressures, which could vary substantially with a small change in network configuration. In parallel with these developments, attempts have been made to design flow restrictors which automatically self-adjust to provide a steady preset flow rate for a range of pressures.
An example of these devices can be found by reference to Patent No. US5209265. These types of device rely on flexible diaphragms of soft elastomeric material, which are often noisy due to the abrupt change in cross section at the discharge of the orifice. The automatic flow rate adjustment with varying pressure is open not accurate over a wide enough pressure range. Many diaphragm configurations have been developed to beat the noise problem such as Patent No. US4976283. These restrictors also require regular maintenance and replacement of the diaphragm (usually of synthetic rubber material).
An object of the present invention is to provide a simple low cost solution, which will constitute a compact in line device requiring little or no maintenance over a long period of time. The device will be suitable for automatically controlling flow rates over a wide range of pressures. Adjustment and fine-tuning of the device will be possible with the device already installed. This device will not only be suitable for use with water supply, but in any type of hydraulic or fluid transport system where controlled flow rates under varying pressure conditions may be required, such as in hydraulically powered tools or in medical apparatus. As the device does not depend on a flexible diaphragm, it will not be adversely effected by high or low temperature operation.
According to the present invention, there is provided a magnetic flow restrictor comprising a hollow open ended cylindrical tubular enclosure made of substantially non-magnetic material such as uPVC and a conjoined upstream bend pipe, which may be inserted between two pipes or other fluid containing and transporting apparatus by use of commonly used pipe coupling joints at each end, said enclosure being provided internally with a free moving mainly cylindrical but streamlined shuttle made of substantially non-magnetic material, being supported with its longitudinal alignment coaxial with that of said enclosure by means of internally fixed upstream and downstream support magnets located within its body interacting with magnets rigidly and firmly affixed or detachably affixed in symmetrical magnetic arrays to said enclosure, which is provided at its downstream end with a concentric
internal constriction with clear passage of smaller diameter than said enclosure but larger diameter than said shuttle external diameter into which the downstream tapered end of said shuttle is free to penetrate except for the longitudinal restraining force on said shuttle upstream support magnet exerted by a central shuttle locator magnet located near the upstream end of said shuttle but downstream of the upstream rear shuttle support magnet, said locator magnet being directly and rigidly attached or indirectly attached via an internal helical coil spring to the downstream end of a longitudinally aligned tie or adjustment shah coaxial with said shuttle, which shaft has its upstream (outer) end firmly held in a lateral sense within a mounting attached to or integral with the upstream bend pipe of similar internal and external diameter to said enclosure, the location of said tie or adjustment shah being longitudinally and manually adjustable and fixable by means of screw thread adjustment and lock nut respectively and/or automatically adjustable by means of a spring mounted externally to said mounting and coaxial with said shaft in combination with manual fixable adjustment by means of screw thread adjustment and lock nut respectively, whereby the movement of said shuttle is restricted to a narrow range in a longitudinal direction so that it will not move outside the area of support offered by said magnetic arrays and will offer resistance to the flow of fluid past said shuttle which will vary according to the pressure differential from the upstream end to the downstream end of said shuttle, according to the strength of the magnets used, according to the compression characteristics of said springs if any, and according to the manually set longitudinal adjustment of said shaft;
Specific embodiments of the invention will now be described by way of examples with reference to the accompanying drawings in which: Sheet 1/6 Figure 1 shows a longitudinal section view of a simple magnetic flow restrictor, with inset cross-section W-W; Sheet 2/6 Figure 2 shows a longitudinal section view of a typical in-pipe mounting arrangement for a magnetic flow restrictor; Sheet 2/6 Figure 3 shows a vertical section view of a magnetic flow restrictor shuttle in downstream (restricted flow) position; Shect 2/6 Figure 4 shows a vertical section view of a magnetic flow restrictor shuttle in upstream (open flow) position; Sheet 3/6 Figure 5 shows a longitudinal section view of a shuttle with external guide vanes for a simple magnetic flow restrictor; Sheet 3/6 Figure 6 shows vertical cross-section views Z-' and Y-Y of a shuttle with external guide vanes for the simple magnetic flow restrictor; Sheet 4/6 Figure 7 shows a longitudinal section view ol a magnetic flow restrictor with internally sprung shuttle; Sheet 4/6 Figure 8 shows a vertical section detail of internal shuttle spring and adjustment shaft end plate for a magnetic flow restrictor with internally sprung shuttle; Sheet 5/6 Figure 9 shows a longitudinal section view of a magnetic flow restrictor with external spring adjustment; Sheet 6/6 Figure 10 shows a longitudinal section view of a magnetic flow restrictor with indented support magnets, with inset cross-section V-V.
Referring to Sheet 1/6 Figure I and Sheet 2/6 Figures 3 and 4, the magnetic flow restrictor in its simplest form comprises a substantially straight and horizontally aligned hollow open ended cylindrical tubular enclosure, or main pipe I made of substantially non-magnetic material, such as unplasticized Poly-Vinyl-Chloride (uPVC), with pipe wall thickness and material strength sufficient to resist the internal pressure of contained fluid, the upstream end of said main pipe 1 being attached via main coupling 2, which may typically be a bolted flanged, bayonet or screw type joint, to bend pipe 3, of similar materials, and similar internal and external diameter to main pipe 1, said 90 degree bend pipe 3 being in turn provided at its upstream end with a further inlet coupling 4, also typically similar to main coupling 2, linking said bend pipe 3 to upstream pipe 5. In the following description, all magnets
referred to are industrial strength permanent magnets. Main pipe 1 is fitted with two magnetic arrays comprising magnets 6, 7, 8, 9 and 10,1 1, 12 and 13 respectively, which are fixed to the outer parts of said main pipe, each array typically consisting of three or more rectangular magnets (in this case four magnets each), each magnet with length slightly less than half the diameter of said main pipe 1, located equidistantly around the circumference of said main pipe, said magnets being aligned with their longer axes parallel to the longitudinal axis X- X of said main pipe 1. In each array, said magnets are also aligned with their similar magnetic poles facing radially inward, the approximate spacing of said arrays longitudinally may be in the order of twice the external main pipe diameter, with the downstream array 6,7,8,9 being typically located just upstream of internal pipe constriction 14, which is of
s streamlined profile typically of Venturi form with its downstream end tapering to meet the internal pipe face at a narrow angle. Said constriction 14 may be a molding monolithic with and of the same material as main pipe 1, or a separate component securely fixed internally within main pipe 1. The upstream array 10,11,12 and 13 is typically located at about half of main pipe diameter downstream from coupling 2, which will allow sufficient space for adjustment of flange bolts, but at the same time at a short distance from the bend pipe 3 to allow use of a short restrictor adjustment shaft 23.
The function of said magnetic arrays is to substantially locate and support mobile flow restrictor shuttle 15 internally within main pipe 1, said shuttle 15 comprising main substantially straight hollow cylindrical tubular enclosure, or main shuttle cylinder 18, which has external diameter of between 60% and 80% of internal diameter of main pipe 1 and length about twice its external diameter, made of thin but rigid substantially non-
magnetic material, such as unplasticized Poly-Vinyl-Chloride (uPVC), supported with its longitudinal central axis substantially in line with the longitudinal central axis X-X of main pipe I by virtue of balanced thrust from said magnetic arrays acting on downstream shuttle support magnet 16 and upstream shuttle support magnet 17. Magnet 16 fixed inside the downstream end of main shuttle cylinder 18 by means of epoxy or plastic molding, etc., is typically of soft iron solid cylindrical form encased in a thin layer of plastic or other suitable material for protection against corrosion and abrasion with its diameter slightly less than the inner diameter of main shuttle cylinder 18 and its width between one third and one quarter of its diameter, being oriented with its central axis substantially coincident with the central longitudinal axis of said shuttle 15 and with the magnetic pole of its circumference similarly aligned to the poles of the inward faces of downstream array magnets 6,7,X and 9 thus causing a repulsive force to act between said array magnets and said downstream shuttle support magnet 16 when the upstream half of said array magnets is adjacent to or just downstream of magnet 16. Magnet 17 fixed inside the upstream end of rear shuttle cylinder 19 by means of epoxy or plastic molding is typically of soft iron cylindrical ring form encased in a thin layer of plastic or other suitable material for protection against corrosion and abrasion with its outer diameter slightly less than the inner diameter of rear shuttle cylinder 19 and its width between one third and one quarter of its outer diameter, being oriented with its central axis substantially coincident with the central longitudinal axis of said shuttle 15 and with the magnetic pole of its circumference similarly aligned to the poles of the inward faces of upstream array magnets 10,11,12 and 13 thus causing a repulsive force to act between said array magnets and said upstream shuttle support magnet 17 when the downstream half of said array magnets is adjacent to or just upstream of magnet 17.
Rear shuttle cylinder 19 which has internal diameter slightly smaller than external diameter of main shuttle cylinder 18 and length about equal to its diameter, made of thin but rigid substantially non-magnetic material, such as unplasticized Poly-Vinyl-Chloride (uPVC), supported with its longitudinal central axis substantially in line with the longitudinal central axis X-X of main pipe I is attached to the upstream end of main shuttle cylinder 18 via a screw thread or similarly detachable arrangement. The downstream end of main shuttle cylinder 18 is fitted with a hollow conical downstream nose shield 20, which has its
longitudinal axis coincident with that of cylinder 18, thus causing the downstream end of shuttle 15 to be closed. The upstream end of rear shuttle cylinder 19 is fitted with a hollow conical frustrum shaped upstream nose shield 21, which has its longitudinal axis coincident with that of cylinder 19, thus causing the upstream end of shuttle 15 to be open with circular aperture 22 of slightly larger diameter than that of restrictor adjustment shun 23. Both shields 20 and 21 may be constructed of similar material to the shuttle main and rear cylinders 18 and 19 and may typically have apex angles of from 40 to 50 degrees. The exact apex angle may be designed to be optimized for the particular main pipe and restrictor shuttle diameter and to suit the particular form of internal constriction 14. The downstream conical shield may if desired be replaced with a shield of more complex profile, which has varying surface angle with distance from the apex, and would be more suitable where high pressures are common. However in all cases shields would be designed to be symmetrical about the central longitudinal axis.
Restrictor adjustment shaft 23, typically straight and of solid cylindrical or tubular construction from strong non-corrosive material, such as stainless steel, brass or carbon fibre, extends horizontally along axis X-X from the downstream side of shuttle central locator magnet 24 to which it is rigidly and centrally affixed passing freely through the central opening of upstream shuttle magnet 17 and through sealing bush 25, typically of brass or copper alloy set into the wall of bend pipe 3 and surrounded and stabilized by adjuster support mounting 26, possibly monolithic with and of the same uPVC material as bend pipe 3 or of other suitable leak-proof and durable construction, said support mounting 26 being provided internally with screw thread 27 which mates with threaded end 28 of shad 23, allowing longitudinal adjustment of said shaft position, which may be secured by screwed lock nut 29 at end of shaft 23. Magnet 24, located inside the upstream end of main shuttle cylinder 18 but not attached thereto, is typically of soft iron solid cylindrical form encased in a thin layer of plastic or other suitable material for protection against corrosion and abrasion with its diameter slightly less than that of downstream shuttle magnet 16 and having width between one third and one quarter of its diameter, being oriented with its central axis substantially coincident with the central longitudinal axis X-X of said shuttle 15 and with the magnetic pole at the perimeter of its upstream circular face with the same magnetic potential as the downstream peripheral pole of upstream shuttle magnet 17, thus causing a repulsive force to act between said magnet 17 and said shuttle central locator magnet 24.
In operation, fluid enters via upstream pipe 5 (marked "IN" on Figure 1) and flows within bend pipe 3 where pressure "P-1" is relatively high to meet the upstream end of flow restrictor shuttle 15 and passing through the annular space between the outside of shuttle 15 and the inside wall of main pipe I reaches the downstream end of shuttle 15, where it converges to exit from the restrictor through the narrow annular space between downstream conical shield 20 and constriction 14 with reduced pressure P-2. The fluid passing shuttle 15 causes drag and friction forces to be exerted on the outside of shuttle l 5 which tend to cause shuttle 15 to move downstream and close the annular space between conical shield 20 and constriction 14. However the shuttle 15 is prevented from closing completely by counter
forces exerted between shuttle locator magnet 24 and shuttle upstream magnet 17. With relatively low pressure differential between upstream and downstream ends of the restrictor, the fluid forces tending to close the annular exit space are relatively small so that the shuttle stays more or less in its upstream (open) position as shown in Figure 4 and allowing flow to pass quite freely. However with relatively high pressure differential between upstream and downstream ends of the restrictor, the fluid forces tending to close the annular exit space are relatively large so that the shuttle stays more or less in its downstream (closed) position as shown in Figure 3, thus restricting flow to the exit. By adjusting rotationally about its axis with a spanner the adjustment shaft 23, which can be provided with a squared outer end or recessed head (Phillips head, Allen key, elc.) for better purchase, the resistance of magnets 24 and 17 to flow forces can be raised or lowered according to most common prevailing pressure conditions.
Referring to Sheet 2/6 Figure 2, which shows a longitudinal section view of a typical in-pipe mounting arrangement for a magnetic flow restrictor, the upstream end of main pipe I and 90 degree bend pipe 3 which contain the components of the magnetic flow restrictor is attached via inlet coupling 4 to upstream pipe 5, which can typically be a 90 degree bend pipe made of any normally recognized pipe material, such as unplasticized Poly-Vinyl-
Chloride (uPVC), with pipe wall thickness and material strength sufficient to resist the internal pressure of contained fluid, said pipe 5 adjoining upstream main pipework 30 via its upstream end coupling 31 which may typically be a bolted flange, bayonet or screw type joint, said upstream main pipework 30 typically being laid horizontally and representing a service connection pipe being supplied from a main pipe distribution network. The downstream end of main pipe I is attached via 90 degree pipe bends 32 and 34, made of any normally recognized pipe material, such as unplasticized Poly-Vinyl-Chloride (uPVC), with pipe wall thickness and material strength suffieicnt to resist the internal pressure of contained fluid, to horizontal downstream pipework 35, via downstream pipe coupling 33 which may typically be a bolted flange, bayonet or screw type joint located at any suitable distance from the downstream end of internal pipe constriction 14, but preferably at least the same distance that separates upstream pipe coupling 2 from the downstream end of constriction 14, as this straight downstream portion of main pipe 1 will allow reduced turbulence, noise and cavitation effects, said downstream pipework 35 typically representing the consumer end of a service connection. The above mounting arrangement may either be arranged with pipe bends in the vertical plane or in the horizontal plane as the flow restrictor is not sensitive to its mounting attitude. The flow restrictor may also be mounted with its axis X-X in the vertical plane, but this would have some resultant effect on flow aperture due to gravity, which could nevertheless be compensated for by adjustment with a spanner of adjustment shaft 23.
Referring to Sheet 3/6 Figures 5 and 6 (including Sections Y-Y and Z-Z), stability of the flow restrictor shuttle 15 during operation can be enhanced by a minor modification in which the main shuttle cylinder 18 is fitted with external guide vanes 36, which may be of the same material as cylinder 18 and may be molded monolithically with said cylinder 18, but may also be of other substantially non-magnetic material and affixed to the outside of
cylinder 18 by internal studs or other suitable method, said guide vanes 36 being typically equidistantly spaced around the circular perimeter of cylinder 18 and running the externally exposed part length of cylinder 18 from its downstream end to the downstream end of rear cylinder 19, said guide vanes 36 having their upstream ends mainly longitudinal and parallel to axis X-X through the center of cylinder 18 and their downstream ends typically making an angle of from 30 to 40 degrees with said axis X-X, said guide vanes being typically of triangular or rectangular cross section with their attached bases less wide than their height above the perimeter of cylinder 18, said height being typically slightly more than sufficient to allow projection of the vanes beyond the outer perimeter of rear cylinder 19, but less than to cause interference with the internal surface of main pipe I (shown on Sheet 1/6 Figure 1).
In order to reduce turbulence, the guide vanes 36 would typically be provided with chamfers 37 and 38 at their upstream and downstream ends, said chamfers being typically angled at between 20 to 30 degrees to axis X-X. During operation, the effect of guide vanes 36 would be to cause rotation of shuttle 15 about axis X-X, which would improve lateral stability and reduce yawing of said shuttle. The fluid passing over the outside of the shuttle would be given a definite rotational component of motion which would aDow better organized and less noisy flow at the exit with resulting reduced cavitation in the region downstream of constriction 14 (shown on Sheet 1/6 Figure 1). The rotating fluid mass passing the constriction 14 would have a relativeb high velocity at the region close to the wall of main pipe I and this could be beneficially reduced by provision of a roughened internal surface for the downstream part of main pipe 1.
Referring to Sheet 4/6 Figures 7 and 8, which show longitudinal and vertical section views of a magnetic flow restrictor with internally sprung shuttle in which more sensitive adjustment and a longer range of controlled shuttle travel may be achieved by introduction
of a helically wound internal coil spring 39 typically of hardened steel, bronze alloy of low corrosion potential, fitted coaxially with spring tie shad 43, between adjustment shaft circular end plate 40 and circular ring magnet 42, said end plate 40 of diameter slightly less than the internal diameter of shuttle main cylinder 18 and thickness of a few millimeters, being of substantially non-corrosive and strong material such as galvanized steel and generally flat but with some minor circular indentation 45 by which spring 39 may be located laterally, said spring 3g being secured radially at the end plate by means of short longitudinal projection 41 passing through a small hole in said end plate 40, said tie shaft 43 being substantially similar to and replacing adjustment shaft 23, but slightly longer and with its downstream end affixed to the center of end plate 40 by centrally located axial end bolt 44 with lock washer or other suitable securing device which will not become loosened accidentally through shaft rotation during adjustment, said ring magnet 42 located inside the upstream end of main shuttle cylinder 18 but not attached thereto by means of open ended location cylinder 46, typically of non-magnetic material such as uPVC being of the same external diameter as circular end plate 40 and affixed thereto on the upstream side by epoxy or screw thread applied to the outer circumference of end plate perimeter flange 47 which can be integral with end plate 40 and of the same material or attached by weld or solder thereto, said location cylinder 46 being of thin enough cross section to allow free movement of ring magnet 42 longitudinally in the direction of axis X-X, said ring magnet 42 being
typically of soft iron cylindrical ring form encased in a thin plastic coating 48 or other suitable material for protection against corrosion and abrasion with its diameter slightly less than that of downstream shuttle magnet]6 and having width between one third and one quarter of its diameter, being oriented with its central axis substantially coincident with the central longitudinal axis X-X of said shuttle 15 and with the magnetic pole at the perimeter of its upstream circular face with the same magnetic potential as the downstream peripheral pole of upstream shuttle magnet 17, thus causing a repulsive force to act between said magnet 17 and said shuttle central locator magnet 24, said ring magnet 42 being located laterally at the upstream end of spring 39 by means of peripheral guide 49, typically a cylindrical ring of rectangular cross section with similar width to spring 39 wire diameter having external diameter flush with external diameter of plastic coating 48 and possibly molded integrally with the same from the same plastic material.
In operation, fluid enters via upstream pipe 5 (marked "IN" on Figure 7) and flows within bend pipe 3 where pressure "P-l" is relatively high to meet the upstream end of flow restrictor shuttle 15 and passing through the annular space between the outside of shuttle 15 and the inside wall of main pipe 1 reaches the downstream end of shuttle 15, where it converges to exit from the restrictor through the narrow annular space between downstream conical shield 20 and constriction] 4 with reduced pressure P-2. The fluid passing shuttle 15 causes drag and friction forces to be exerted on the outside of shuttle 15 which tend to cause shuttle 15 to move downstream and close the annular space between conical shield 20 and constriction 14. However the shuttle 15 is prevented from closingcompletely by counter forces exerted between shuttle ring magnet 42 held in position by spring 39 and end plate 40, and shuttle upstream magnet 17. With relatively low pressure differential between upstream and downstream ends of the restrictor, the fluid forces tending to close the annular exit space are relatively small so that the shuttle stays more or less in its upstream (open) position as shown in Figure 4 and allowing flow to pass quite freely. However with relatively high pressure differential between upstream and downstream ends of the restrictor, the fluid forces tending to close the annular exit space are relatively large so that the shuttle stays more or less in its downstream (closed) position as shown in Figure 3, thus restricting flow to the exit. By adjusting rotationally about its axis with a spanner the tie shaft 43, which can be provided with a squared outer end or recessed head (Phillips head, Allen key, etc.) for better purchase, the resistance of magnets 42 and 17 and spring 39 to flow forces can be raised or lowered according to most common prevailing pressure conditions.
Referring to Sheet 516 Figures 9, which shows a longitudinal section view of a magnetic flow restrictor with external spring adjustment in which more sensitive adjustment and a longer range of controlled shuttle travel may alternatively be achieved by introduction of a
helically wound coil spring at the outer end of the adjustment shaft. This externally sprung alternative has the benefit that the spring operates in a dry envirorunent and that the shuttle assembly may be less bully than its internally sprung alternative. The general Features of this alternative are similar to those of the basic un-sprung version described for figures 1 to 4 above, but extended adjustment shad 51 replaces adjustment shad 23 being slightly longer with longer threaded end 52 and additional adjustment nut 54, while short support mounting
53 replaces adjuster support mounting 26 and is not fitted with internal screw thread 27, but still retains sealing bush 25, said short support mounting 53 being provided at its outer end with rectangular recess 55 in the circular perimeter of its end face, which allows positioning of helically wound external coil spring 50 typically made of hardened steel, bronze alloy of low corrosion potential, fitted coaxially with extended adjustment shaft 51, with its internal diameter slightly larger than the external diameter of shall 51 and the inner circular face of recess 55, said spring 50 being constrained longitudinally and laterally by stainless steel cup washer 56 on shaft 51, which is in turn held in place by adjustment nut 54 and lock nut 29.
In operation, fluid enters via upstream pipe 5 (marked AN" on Figure 9) and flows within bend pipe 3 where pressure "P-l" is relatively high to meet the upstream end of flow restrictor shuttle 15 and passing through the annular space between the outside of shuttle 15 and the inside wall of main pipe 1 reaches the downstream end of shuttle 15, where it converges to exit from the restrictor through the narrow annular space between downstream conical shield 20 and constriction 14 with reduced pressure P-2. The fluid passing shuttle l 5 causes drag and friction forces to be exerted on the outside of shuttle 1 S which tend to cause shuttle 15 to move downstream and close the annular space between conical shield 20 and constriction 14. However the shuttle 15 is prevented from closing completely by counter forces exerted between shuttle locator magnet 24 and shuttle upstream magnet 17, said locator magnet 24 being itself located according lo forces transmitted through spring 50.
With relatively low pressure differential between upstream and downstream ends of the restrictor, the fluid forces tending to close the annular exit space are relatively small so that the shuttle stays more or less in its upstream (open) position as shown in Figure 4 and allowing flow to pass quite freely. However with relatively high pressure differential between upstream and downstream ends of the restrictor, the fluid forces tending to close the annular exit space are relatively large so that the shuttle stays more or less in its downstream (closed) position as shown in Figure 3, thus restricting flow to the exit. By adjusting rotationally about as axis against adjustment nut 54 with a spanner the extended adjustment shaft 51, which can be provided with a squared outer end or recessed head (Phillips head, Allen key, etc.) for better purchase, the resistance of magnets 24 and 17 and spring 50 to now forces can be raised or lowered according to most common prevailing pressure conditions. Referring to Sheet 6/6 figure 10 which shows a longitudinal section view of a magnetic flow restrictor with indented support magnets, with inset cross-section V-V, a less restrictive alternative is presented which is basically similar to the simple magnetic flow restrictor of Figure 1 above, but with indented magnet arrays and streamlined shuttle as described below.
In this alternative, the magnetic arrays comprising magnets 6,7,8,9 and 10,1 l, 12, 13 which were located externally to main pipe 1 in Figure I have been transferred to the inner side of main pipe 1 and are encased in a thin layer of plastic or other suitable material for protection against corrosion and abrasion by the contained liquid, which encasement may take the form of an integral molding of main pipe 1, said encasement being provided at both upstream and downstream ends with tapered triangular shaped ends 57 of similar material to the encasement and of width and height similar to the end profile of said magnet encasement,
being intended to streamline the indented magnets. In this alternative, downstream shuttle support magnet 16 and upstream shuttle support magnet 17 have been replaced by reduced downstream shuttle support magnet 58 and reduced upstream shuttle support magnet 59 respectively together with their casings, which magnets 58 and 59 are similar to magnets 16 and 17, but of reduced diameter of about 80 percent of the latter simple type restrictor magnets, while Conner shuttle central locator magnet 24 is replaced by reduced shuttle central locator nugget 60, which is also similar to magnet 24 but of reduced diameter of about 80 percent of the latter simple type restrictor magnet, similarly reduced roan shuttle cylinder 61 and reduced rear shuttle cylinder 62 are similar to but have about 80 percent of the diameters of main shuttle cylinder 18 and rear shuttle cylinder 19 respectively which allows hollow conical downstream nose shield 20, which has its longitudinal axis coincident with that of cylinder 18, is tapered more acutely to said axis as is hollow conical fiustrum shaped upstream nose shield 21. This alternative therefore allows greater space between the inside of main pipe l and the outside of shuttle 1 S. which will in turn allow greater flow to pass said shuttle 15 with indented magnet supports for any given head differential than would be possible with the simple type flow restrictor of Figure 1.
The concept of the indented magnet arrangement described above is of course applicable to the internally sprung and externally sprung versions of the magnetic flow restrictor as shown in Figures 7 and 9 and to the shuttle with vanes as shown in Figure 5.
Claims (17)
1. A magnetic flow restrictor comprising a hollow open ended cylindrical tubular enclosure made of substantially non-magnetic material such as uPVC and a conjoined upstream bend pipe, which may be inserted between two pipes or other fluid containing and transporting apparatus by use of commonly used pipe coupling joints at each end, said enclosure being provided internally with a free moving mainly cylindrical but streamlined shuttle made of substantially non-magnetic material, being supported with its longitudinal alignment coaxial with that of said enclosure by means of internally fixed upstream and downstream support magnets located within its body interacting with magnets rigidly and thinly affixed or detachably affixed in symmetrical magnetic arrays to said enclosure, which is provided at its downstream end with a concentric internal constriction with clear passage of smaller diameter than said enclosure but larger diameter than said shuttle external diameter into which the downstream tapered end of said shuttle is free to penetrate except for the longitudinal restraimng force on said shuttle upstream support magnet exerted by a central shuttle locator magnet located near the upstream end of said shuttle but downstream of the upstream rear shuttle support magnet, said locator magnet being directly and rigidly attached or indirectly attached via an internal helical coil spring to the downstream end of a longitudinally aligned tie or adjustment shaft coaxial with said shuttle, which shaft has its upstream (outer) end firmly held in a lateral sense within a mounting attached to or integral with the upstream bend pipe of similar internal and external diameter to said enclosure, the location of said tie or adjustment shaft being longitudinally and manually adjustable and fixable by means of screw thread adjustment and lock nut respectiveb and/or automatically adjustable by means of a spring mounted externally to said mounting and coaxial with said shaft in combination with manual fixable adjustment by means of screw thread adjustment and lock nut respectively, whereby the movement of said shuttle is restricted to a narrow range in a longitudinal direction so that it will not move outside the area of support offered by said magnetic arrays and will offer resistance to the flow of fluid past said shuttle which will vary according to the pressure differential from the upstream end to the downstream end of said shuttle, according to the strength of the magnets used, according to the compression characteristics of said springs if any, and according to the manually set longitudinal adjustment of said shaft;
2. A magnetic flow restrictor as claimed in Claim I above wherein the downstream
constriction of said enclosure is in the form of a Venturi shape, which results in quieter operation;
3. A magnetic flow restrictor as claimed in any preceding claim above, wherein some or all of said magnetic arrays are affixed to the outside of said enclosure, which
allows easy replacement and maintenance and less resistance to fluid flow by fixed obstruction within said enclosure;
4. A magnetic flow restrictor as claimed in any preceding claim above, wherein some or all of said magnetic arrays are affixed to the inside of said enclosure, which allows use of smaller shuttle magnet diameter and overall dimensions with less resistance to fluid flow;
5. A magnetic flow restrictor as claimed in any preceding claim above, wherein the downstream shuttle support magnet fixed within the shuttle is of a cylindrical shape with its external diameter substantially larger than its longitudinal thickness;
6. A magnetic flow rcstrictor as claimed in any preceding claim above, wherein the upstream shuttle support magnet fixed within the shuttle is of a cylindrical ring shape with its external diameter substantially larger than its longitudinal thickness and with its internal diameter slightly larger than the tie or adjustment shaft diameter;
7. A magnetic flow restrictor as claimed in any preceding claim above, wherein the shuttle locator magnet fixed directly at the downstream end of the tie/ adjustment shaft is of a solid cylindrical shape with its diameter substantially larger than its longitudinal thickness and sufficiently smaller than the inside diameter of the main cylindrical shuttle body to allow free longitudinal movement relative to said body;
8. A magnetic flow restrictor as claimed in any preceding claim above, wherein the tie/ adjustment shalt is provided with an external screw thread which inter- reacts with an internal screw thread on the shaft mounting of the upstream bend pipe to allow manual longitudinal adjustment of fixed locator magnet position relative to the upstream bend pipe and enclosure with downstream constriction, so that the resistance to closure of the constriction passage by the downstream tapered shuttle end can be manually increased or decreased according to flow requirements;
9. A magnetic flow restrictor as claimed in any preceding claim above, wherein a shuttle locator magnet is fixed indirectly via internal coil spring to the downstream end of the tie/ adjustment shaft and is of a cylindrical ring shape with its external diameter substantially larger than its longitudinal thickness but sufficiently smaller than the inside diameter of the main cylindrical shuttle body to allow free longitudinal movement relative to said body and with its internal diameter slightly larger than the tie or adjustment shaft diuneter,, wherein said coil spring allows greater range of longitudinal travel of the shuttle, which in turn will allow automatic flow restriction over a greater range of pressure differential;
10. A magnetic flow restrictor as claimed in any preceding claim above, wherein a coil spring is mounted coaxially with said adjuster shaft and externally between the bend pipe adjuster shaft mounting and a screw threaded adjustment nut, allowing manual
adjustment of spring compression which in turn results in adjustment of sensitivity to fluid flow rate and pressure differential in the flow restrictor' as well as greater range of longitudinal travel of the shuttle, which in turn will allow automatic flow restriction over a greater range of pressure differential; A magnetic flow restrictor as claimed in any preceding claim above, wherein a lock nut is provided on the tie/ adjustment shaft to prevent unsolicited loosening of the manually set adjustment condition' 12. A magnetic flow restrictor as claimed in any preceding claim above, wherein the cylindrical main body of the shuttle is provided with external guide vanes of height which would allow clearance between the shuttle and the internal surface of the main cylindrical enclosure and with alignment passing from longitudinal at the upstream end through about 30 to 40 degrees to that at the downstream end, thus promoting rotation of the shuttle about its longitudinal axis during operation, resulting in added flow stability and lower noise with greater pressure reduction at the downstream outlet; 13. A magnetic flow restrictor as claimed in any preceding claim above, wherein the shuttle body is comprised of upstream and downstream cylindrical compartments which are joined together by a screw thread which allows easy assembly and maintenance; 14. A magnetic flow reslrictor as claimed in any preceding claim above, wherein the upstream bend pipe shaft mounting is provided with an internal seal to prevent leakage of fluid under pressure along the tie/adjustment shah; 15. A magnetic flow rcstrictor as claimed in any preceding claim above, wherein the part of the enclosure downstream of the constriction passage is straight and of similar length to or longer than the part of the enclosure upstream of said constriction which allows lower noise and more stable operating characteristics; 16. A magnetic flow restrictor as claimed in any preceding claim above, which is arranged with its main enclosure mounted in offset but parallel alignment to the main upstream incoming supply pipe, being provided with an additional pipe bend upstream and two additional bends downstream of said flow restrictor; 17. A magnetic flow restrictor substantially as described herein with reference to Figures 1-10 of the accompanying drawings
t is %' It' t.: Amendments to the claims have been filed as follows 1 A magnetic flow restrictor comprising a hollow open ended cylindrical tubular enclosure made of substantially non-magnetic material such as uPVC and a conjoined upstream bend pipe, which may be inserted between two pipes or other fluid containing and transporting apparatus by use of commonly used pipe coupling joints at each end, said enclosure being provided internally with a free moving mainly cylindrical but streamlined shuttle made of substantially non-magnetic material, being supported with its longitudinal alignment coaxial with that of said enclosure by means of internally fixed upstream and downstream support magnets located within its body interacting with magnets rigidly and firmly affixed or detachably affixed in symmetrical magnetic arrays to said enclosure, which is provided at its downstream end with a concentric internal constriction with clear passage of smaller diameter than said enclosure into which the downstream tapered end of said shuttle is free to penetrate except for the longitudinal restraining force on said shuttle upstream support magnet exerted by a central shuttle locator magnet located near the upstream end of said shuttle but downstream of the upstream rear shuttle support magnet, said locator magnet being directly and rigidly attached or indirectly attached via an internal helical coil spring to the downstream end of a longitudinally aligned tie or adjustment shaft coaxial with said shuttle, which shaft has its upstream (outer) end firmly held in a lateral sense within a mounting attached to or integral with the upstream bend pipe of similar internal and external diameter to said enclosure, the location of said tie or adjustment shaft being longitudinally and manually adjustable and fixable by means of screw thread adjustment and lock nut respectively and/or automatically adjustable by means of a spring mounted externally to said mounting and coaxial with said shaft in combination with manual fixable adjustment by means of screw thread adjustment and lock nut respectively, whereby the movement of said shuttle is restricted to a narrow range in a longitudinal direction so that it will not move outside the area of support offered by said magnetic arrays and will offer resistance to the flow of fluid past said shuttle which will vary according to the pressure differential from the upstream end to the downstream end of said shuttle, according to the strength of the magnets used, according to the compression characteristics of said springs if any, and according to the manually set longitudinal adjustment of said shaft; 2. A magnetic flow restrictor as claimed in Claim I above wherein the downstream constriction of said enclosure is in the form of a Venturi shape, which results in quieter operation; 3. A magnetic flow restrictor as claimed in any preceding claim above, wherein some or all of said magnetic arrays are affixed to the outside of said enclosure, which
lo allows easy replacement and ma ntenance and less resistance to fluid flow by fixed obstruction within said enclosure; 4. A magnetic flow restrictor as claimed in any preceding claim above, wherein some or al! of said magnetic arrays Ore affixed to the inside of said enclosure, which allows use of smaller shuttle magnet diameter and overall din- Rnsions -with less resistance to fluid flow, 5. A magnetic flow restrctor as Darned in any preceding ciaiin above, wherein the downstream shuttle support magnet fixed within the shuttle is of a cylindrical shape with its external diameter substantially larger than its longitudinal thickness, 6. A magnetic flow restrictor as claimed in any preceding claim above, wherein the upstream shuttle support magnet fixed within the shuttle is of a cylindrical ring shape with its external diameter substantially larger than its longitudinal thickness and with its internal diameter slightly larger than the tie or adjustment shaft diameter; 7. A magnetic flow rcstrictor as claimed in any preceding claim above, wherein the shuttle locator magnet fixed directly at the downstream end of the tie/ adjustment shaft is of a solid cylindrical shape with its diameter substantially larger than its longitudinal thickness and sufficiently smaller than the inside diameter of the Grin cylindrical shuttle body to allow free longitudinal movement relative to said body; 8. A magnetic flow restrictor as claimed in any preceding claim above, wherein the tie/ adjustment shaft is provided with an external screw thread which inter-reacts with an internal screw thread on the shaft mounting of the upstream bend pipe to allow manual longitudinal adjustment of fixed locator magnet position relative to the upstream bend pipe and enclosure with downstream constriction, so that the resistance to closure of the constriction passage by the downstream tapered shuttle end can be manually increased or decreased according to flow requirements; 9. A magnetic flow restrictor as claimed in any preceding claim above, wherein a shuttle locator magnet is fixed indirectly via internal coil spring to the downstream end of the tie/ adjustment shad! and is of a cylindrical ring shape with its external diameter substantially larger than its longitudinal thickness but sufficiently smaller than the inside diameter of the main cylindrical shuttle body to allow tree longitudinal movement relative to said body and with its internal diameter slightly larger than the tie or adjustment shaft diameter, wherein said coil spring allows greater range of longitudinal travel of the shuttle, which in turn will allow automatic flow restriction over a greater range of pressure differential; 1 O. A magnetic Dow restrictor as claimed in any preceding claim above, wherein a coil spring is mounted coaxially with said adjuster shaft and externally between the bend pipe adjuster shah mounting and a screw threaded adjustment nut, allowing manual
adjustment of spring compression which in turn results in adjustment of sensitivity to fluid flow rate and pressure differential in the flow restrictor, as well as greater range of longitudinal travel of the shuttle, which in turn will allow automatic flow restriction over a greater range of pressure deferential;
11. A magnetic flow restrictor as claimed in any preceding claim above, wherein a lock nut is provided on the tie/ adjustment shall to prevent unsolicited loosening of the manually set adjustment condition;
12. A magnetic flow restrictor as claimed in any preceding claim above, wherein the cylindrical main body of the shuttle is provided with external guide vanes of height which would allow clearance between the shuttle and the internal surface of the main cylindrical enclosure and with alignment passing from longitudinal at the upstream end through about 30 to 40 degrees to that at the downstream end, thus promoting rotation of the shuttle about its longitudinal axis during operation, resulting in added flow stability and lower noise with greater pressure reduction at the downstream outlet;
13. A magnetic flow restrictor as claimed in any preceding claim above, wherein the shuttle body is comprised of upstream and downstream cylindrical compartments which are joined together by a screw thread which allows easy assembly and maintenance,
14. A magnetic flow restrictor as claimed in any preceding claim above, wherein the upstream bend pipe shaft mounting is provided with an internal seal to prevent leakage of fluid under pressure along the tie/adjustment shaft;
15. A magnetic flow restrictor as claimed in any preceding claim above, wherein the part of the enclosure downstream of the constriction passage is straight and of similar length to or longer than the part of the enclosure upstream of said constriction which allows lower noise and more stable operating characteristics;
16. A magnetic flow restrictor as claimed in any preceding claim above, which is arranged with its main enclosure mounted in offset but parallel alignment to the main upstream incoming supply pipe, being provided with an additional pipe bend upstream and two additional bends downstream of said flow restrictor;
17. A magnetic flow restrictor substantially as described herein with reference to Figures 1-10 ofthe accompanying drawings
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0216924A GB2391057B (en) | 2002-07-20 | 2002-07-20 | Magnetic flow restrictor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0216924A GB2391057B (en) | 2002-07-20 | 2002-07-20 | Magnetic flow restrictor |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB0216924D0 GB0216924D0 (en) | 2002-08-28 |
| GB2391057A true GB2391057A (en) | 2004-01-28 |
| GB2391057B GB2391057B (en) | 2004-06-02 |
Family
ID=9940856
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB0216924A Expired - Fee Related GB2391057B (en) | 2002-07-20 | 2002-07-20 | Magnetic flow restrictor |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2391057B (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2443427A (en) * | 2006-11-03 | 2008-05-07 | Fuel Savers Ltd | Delivery valve |
| GB2435487B (en) * | 2006-02-22 | 2011-03-16 | Weatherford Lamb | Adjustable venturi valve |
| GB2473616A (en) * | 2009-09-16 | 2011-03-23 | Ge Aviat Systems Ltd | Flow regulation in aircraft systems |
| CN103758776A (en) * | 2014-01-28 | 2014-04-30 | 长沙中粮机械有限公司 | Air volume control device and centrifugal fan |
| CN109386637A (en) * | 2017-08-07 | 2019-02-26 | 上海卓思智能科技股份有限公司 | A kind of venturi valve and its wind pressure adjusting method |
| CZ310100B6 (en) * | 2023-06-16 | 2024-08-07 | Západočeská Univerzita V Plzni | An electromagnetic coaxial valve |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111455624B (en) * | 2019-01-18 | 2022-04-05 | 青岛海尔洗涤电器有限公司 | Automatic additive feeding device and washing machine |
| CN120361323A (en) * | 2020-11-17 | 2025-07-25 | 科里福罗公司 | Device for clearing obstructions |
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| GB1398320A (en) * | 1971-11-12 | 1975-06-18 | Aerospatiale | Fluid flow control device |
| GB2021237A (en) * | 1978-05-17 | 1979-11-28 | Agfa Gevaert | Flow control valve |
| US4206781A (en) * | 1978-06-07 | 1980-06-10 | Salter Jack N | Self-actuated flow control valve |
| WO1987004765A1 (en) * | 1986-02-04 | 1987-08-13 | Eidsmore Paul G | Fluid pressure regulation and method |
| GB2358696A (en) * | 1998-11-03 | 2001-08-01 | John Henry May | Constant flow valve |
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2002
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1398320A (en) * | 1971-11-12 | 1975-06-18 | Aerospatiale | Fluid flow control device |
| GB2021237A (en) * | 1978-05-17 | 1979-11-28 | Agfa Gevaert | Flow control valve |
| US4206781A (en) * | 1978-06-07 | 1980-06-10 | Salter Jack N | Self-actuated flow control valve |
| WO1987004765A1 (en) * | 1986-02-04 | 1987-08-13 | Eidsmore Paul G | Fluid pressure regulation and method |
| GB2358696A (en) * | 1998-11-03 | 2001-08-01 | John Henry May | Constant flow valve |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2435487B (en) * | 2006-02-22 | 2011-03-16 | Weatherford Lamb | Adjustable venturi valve |
| US8689883B2 (en) | 2006-02-22 | 2014-04-08 | Weatherford/Lamb, Inc. | Adjustable venturi valve |
| GB2443427A (en) * | 2006-11-03 | 2008-05-07 | Fuel Savers Ltd | Delivery valve |
| GB2443427B (en) * | 2006-11-03 | 2011-03-30 | Fuel Savers Ltd | Valve |
| GB2473616A (en) * | 2009-09-16 | 2011-03-23 | Ge Aviat Systems Ltd | Flow regulation in aircraft systems |
| US9417634B2 (en) | 2009-09-16 | 2016-08-16 | Moog Wolverhampton Limited | Flow regulation in aircraft systems |
| CN103758776A (en) * | 2014-01-28 | 2014-04-30 | 长沙中粮机械有限公司 | Air volume control device and centrifugal fan |
| CN103758776B (en) * | 2014-01-28 | 2015-11-18 | 长沙中粮机械有限公司 | Air volume control device and centrifugal fan |
| CN109386637A (en) * | 2017-08-07 | 2019-02-26 | 上海卓思智能科技股份有限公司 | A kind of venturi valve and its wind pressure adjusting method |
| CN109386637B (en) * | 2017-08-07 | 2020-05-15 | 上海卓思智能科技股份有限公司 | Venturi valve and air pressure adjusting method thereof |
| CZ310100B6 (en) * | 2023-06-16 | 2024-08-07 | Západočeská Univerzita V Plzni | An electromagnetic coaxial valve |
Also Published As
| Publication number | Publication date |
|---|---|
| GB0216924D0 (en) | 2002-08-28 |
| GB2391057B (en) | 2004-06-02 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 20120720 |