US20140096854A1 - Fluid flow control device - Google Patents
Fluid flow control device Download PDFInfo
- Publication number
- US20140096854A1 US20140096854A1 US14/103,593 US201314103593A US2014096854A1 US 20140096854 A1 US20140096854 A1 US 20140096854A1 US 201314103593 A US201314103593 A US 201314103593A US 2014096854 A1 US2014096854 A1 US 2014096854A1
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- United States
- Prior art keywords
- fluid flow
- control device
- flow control
- fluid
- twist
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- 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.)
- Abandoned
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- 239000012530 fluid Substances 0.000 title claims abstract description 95
- 241000237852 Mollusca Species 0.000 claims description 6
- 230000001133 acceleration Effects 0.000 claims 1
- 230000037361 pathway Effects 0.000 abstract description 16
- 230000008901 benefit Effects 0.000 description 6
- 241000238366 Cephalopoda Species 0.000 description 4
- 241000237858 Gastropoda Species 0.000 description 4
- 230000003247 decreasing effect Effects 0.000 description 3
- 241000881665 Argonauta Species 0.000 description 2
- 241001481166 Nautilus Species 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007717 exclusion Effects 0.000 description 1
- 230000001902 propagating effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
- F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
- F04F5/02—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid
- F04F5/04—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid displacing elastic fluids
- F04F5/06—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid displacing elastic fluids of rotary type
-
- 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
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
- F16L55/02—Energy absorbers; Noise absorbers
- F16L55/027—Throttle passages
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
- B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
- B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
- B05B1/34—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl
- B05B1/3405—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl
- B05B1/341—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15D—FLUID DYNAMICS, i.e. METHODS OR MEANS FOR INFLUENCING THE FLOW OF GASES OR LIQUIDS
- F15D1/00—Influencing flow of fluids
- F15D1/02—Influencing flow of fluids in pipes or conduits
- F15D1/04—Arrangements of guide vanes in pipe elbows or duct bends; Construction of pipe conduit elements for elbows with respect to flow, e.g. for reducing losses of flow
-
- 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
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L9/00—Rigid pipes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
-
- 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
- G05D7/0186—Control of flow without auxiliary power without moving parts
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/0318—Processes
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/206—Flow affected by fluid contact, energy field or coanda effect [e.g., pure fluid device or system]
- Y10T137/2087—Means to cause rotational flow of fluid [e.g., vortex generator]
Definitions
- Nozzles, diffusers and venturis are specific types of ducts used in relation to the flow of fluid.
- a nozzle is intended to mean a duct of varying cross-sectional area which is designed so that fluid flow is accelerated by a pressure differentiated between the inlet and the outlet.
- a diffuser is intended to mean a duct of varying cross-sectional area which is designed so that fluid flow is decelerated by an increase of pressure between the inlet and the outlet.
- a venturi can be seen as a duct comprising a nozzle section and diffuser section abutted in tandem.
- Nozzles are widely used in the field of fluid flow as a means to provide an accelerated stream of fluid and have many applications.
- Diffusers are used to decelerate fluid flow and again have many applications.
- Venturis are used to cause a short region of accelerated flow in a duct. It is a well known law of thermodynamics that the accelerated fluid flow is accompanied by a reduced pressure, and that many applications of venturis are directed to utilising the reduced pressure.
- an exemplary embodiment of the present invention provides a flow controller adapted to control a flow of fluid within the controller, the flow controller having a flow path adapted to convey said fluid, wherein the cross-sectional area of the flow path varies along the flow path and wherein in at least a portion of its length the flow controller comprises an active surface capable of influencing the fluid flow through the flow path.
- the active surface is adapted to cause vortical motion of fluid within the fluid pathway about the axis of flow of the fluid.
- the configuration of the active surface conforms to at least one logarithmic curve conforming to the Golden Section.
- the curvature of the active surface is uni-dimensional.
- the curvature of the active surface is bi-dimensional.
- the curvature of the active surface varies in accordance with the Golden Section.
- the curvature of the active surface conforms to an equiangular spiral.
- the curvature of the active surface is transverse to the central axis of the fluid pathway.
- the curvature of the active surface can be in a direction parallel to the central axis.
- the curvature of the active surface is both transverse to the central axis and is parallel to the direction of the central axis to define a three-dimensional surface conforming substantially or in the greater part to the Golden Section.
- the fluid pathway has a spiral configuration.
- the configuration takes the form of a logarithmic helix or a volute or a whorl.
- the cross-sectional area of the flow path varies logarithmically substantially or in greater part in conformity to the Golden Section.
- the cross-sectional area of the flow path varies to cause the incremental volume of the flow path to vary logarithmically.
- the incremental volume is caused to vary in conformity with the Golden Ratio.
- the active surface has the configuration conforming to the external configuration of a shell of the phylum Mollusca, class Gastropoda or Cephalopoda.
- the active surface conforms to the external configuration of shells selected from the genera Volutidea, Argonauta, Nautilus, Conidea or Turbinidea.
- the active surface has the configuration of the interior of shells of the phylum Mollusca; classes Gastropoda or Cephalopoda.
- the active surface has the configuration of the interior of shells selected from the genera Volutidea, Conidea, Turbinidea, Argonauta, or Nautilus.
- the configuration of the flow controller promotes substantially radially laminar fluid flow.
- the flow controller comprises a nozzle.
- the flow controller comprises a diffuser.
- the flow controller comprises a venturi.
- FIG. 1 is a chart of the Golden Section or Fibonacci Progression
- FIG. 2 is an isometric view of a nozzle according to a first embodiment
- FIG. 3 is an isometric view of a nozzle according to a second embodiment
- FIG. 4 is an isometric view of a nozzle according to a third embodiment
- FIG. 5 is an isometric view of a diffuser according to a fourth embodiment
- FIG. 6 is a sectional elevation of a conventional venturi tube
- FIG. 7 is an isometric view of a venturi according to a fifth embodiment
- FIG. 8 is an isometric view of a venturi according to a sixth embodiment.
- An embodiment of the invention is directed to a flow controller, the structure of which is configured to cause the rate of a fluid flow to be altered during passage through the controller.
- Each of the embodiments is directed to a flow controller adapted to alter the rate of flow of a fluid.
- Each of the embodiments serves, in the greater part, to enable fluids to move in their naturally preferred way, thereby reducing inefficiencies created through turbulence and friction which are normally found in apparatus commonly used for propagating fluid flow.
- Previously developed technologies have generally been less compliant with natural fluid flow tendencies.
- the greater percentage of the surfaces of the flow controller of each of the embodiments described herein are generally designed in the greater part, in accordance with the Golden Section or Ratio or are designed to ensure the volume of fluid flowing through the flow controller expands or contracts in the greater part in accordance with the Golden Section and therefore it is a characteristic of each of the embodiments that the flow controller provides a fluid pathway which is of a spiralling configuration and which conforms at least in greater part to the characteristics of the Golden Section or Ratio.
- FIG. 1 illustrates the unfolding of the spiral curve according to the Golden Section or Ratio.
- the order of growth of the radius of the curve which is measured at equiangular radii e.g., E, F, G, H, I and J
- equiangular radii e.g., E, F, G, H, I and J
- This can be illustrated from the triangular representation of each radius between each sequence which corresponds to the formula of a:b b:a+b which conforms to the ratio of 1:0.618 approximately and which is consistent throughout the curve.
- the curvature of the surfaces which form the flow controller takes a two dimensional or three dimensional shape equivalent to the lines of vorticity or streak lines found in a naturally occurring vortex.
- the curvature of the surfaces substantially or in the greater part conform to the characteristics of the Golden Section or Ratio and that any variation in cross-sectional area of the flow controller also substantially or in greater part conforms to the characteristics of the Golden Section or Ratio.
- the curvature of the active surface conforms to an equiangular spiral.
- the characteristics of the Golden Section or Ratio are found in nature in the form of the external and internal configurations of shells of the phylum Mollusca, classes Gastropoda and Cephalopoda and it is a common characteristic of at least some of the embodiments that the fluid pathway defined by the flow controller corresponds generally to the external or internal configuration of shells of one or more of the genera of the phylum Mollusca, classes Gastropoda and Cephalopoda.
- the outer surfaces of the embodiments in the drawings are depicted in a way whereby they would correspond with the inner surfaces, such as would be the case if the walls of the embodiments are of constant thickness. In this way some concept of the helical/spiral configurations of the inner surfaces is conveyed.
- the configuration of the outer surface is not of significance to the embodiments and thus the outer surface could be configured as a simple surface such as a cone, leaving the inner surface complex as suggested in these drawings.
- the first embodiment takes the form of a nozzle as shown in FIG. 2 .
- the nozzle 11 has a nozzle body 21 , an outlet 22 and an inlet 23 which is adapted to be joined to a duct (not shown) such as a pipe, hose or similar providing a source of fluid under pressure.
- the nozzle body 21 has an internal surface 25 which reduces in cross-sectional area to the outlet 22 .
- the internal surface of the nozzle may be seen to twist in a combination helical manner and spiralling manner between the input and the output. As indicated above, this twist is in a configuration which provides an active surface which conforms at least in greater part to the characteristics of the Golden Section or Ratio. It will be seen that as a result of the twist, fluid flowing in the nozzle is caused to be given a rotational motion about the longitudinal axis of the nozzle to thereby induce vortical motion in the fluid.
- a second embodiment takes the form of a nozzle as shown in FIG. 3 .
- the second embodiment is of substantially similar construction to that of the first embodiment, and therefore in the drawings like parts are denoted with like numerals.
- the second embodiment differs from the first only in the particular design of the nozzle in that it is relatively longer and has greater twist.
- the formation of the vortical flow emitted from the nozzle outlet can be controlled. In certain applications, it will be desirable for the outlet to comprise a narrow vortical stream while in others, a diverging stream will be required to promote mixing of the output with the surrounding fluid.
- a third embodiment takes the form of a nozzle as shown in FIG. 4 .
- the twist in the flow surfaces causes the direction of flow to be diverted transversely to that of the incoming flow stream. This redirection is achieved without significant loss because the internal surface of the nozzle is still configured to conform at least in greater part to the characteristics of the Golden Section or Ratio. As a result, turbulence is substantially avoided.
- a fourth embodiment takes the form of a diffuser as shown in FIG. 5 .
- a diffuser may comprise a flow controller substantially identical to a nozzle but with direction of flow reversed.
- the diffuser of FIG. 5 corresponds with the nozzle of FIG. 2 but having an internal surface 25 which increases in cross-sectional area to the outlet 22 . Therefore, in the drawings like numerals are again used to depict like features.
- the precise characteristics of the output flow can be controlled by varying the design properties of the diffuser while maintaining the inner surface to conform at least in greater part to the characteristics of the Golden Section or Ratio.
- the cross-sectional area of the previous embodiments varies between the inlets to the outlets; for the nozzles, the area decreasing and for the diffusers, the area increasing.
- further embodiments of the fluid flow control devices as previously described are configured to conform with this constraint. As a result, the volume of fluid flowing through the flow controller expands or contracts in the greater part in accordance with the Golden Ratio.
- a fifth embodiment takes the form of a modified venturi tube as shown in FIG. 7 .
- the modified venturi tube is best appreciated by comparison with a conventional venturi tube which is depicted In FIG. 6 .
- a venturi 51 comprises an inlet 52 , an outlet 53 and a constricted region 54 .
- the constricted region 54 comprises an entry 55 , an exit 56 and a region of maximum constriction 57 .
- the flow is represented by flow lines 58 .
- the modified venturi 61 comprises an inlet 62 , an outlet 63 , a region of maximum constriction 64 , an entry 65 and an exit 66 . It will be readily perceived that these portions conform generally to corresponding portions of the conventional venturi tube of FIG. 6 .
- the entry 64 and exit 65 are specifically designed to induce the fluid to move in accordance with the laws of Nature.
- the flow controller is designed with a pathway having a curvature substantially or in greater part conforming to that of the Golden Section or Ratio. The fluid is thereby induced into vortical flow the greater part of which conforms to the Golden Section or Ratio. The energy losses caused as a result of this vortical flow are considerably lower than those which result from a conventional venturi.
- the apparatus may be used more effectively than previously has been possible. Firstly, it is possible to increase the ratio of the area of inlet relative to the area of maximum constriction. This increases the relative pressure difference that may be generated between the inlet and the region of maximum constriction. This broadens the scope of use of the device.
- a sixth embodiment takes the form of a modified venturi tube as shown in FIG. 8 .
- the sixth embodiment although somewhat different in appearance, operates in substantially the same manner as that of fifth embodiment and so, in the drawings, like parts are denoted with like numerals.
- the sixth embodiment again comprises a duct, the area of cross-section of which reduces from an inlet to a portion of maximum constriction, and then increase to the outlet.
- the difference between the sixth embodiment and the fifth is that in the fifth embodiment the flow induces a vortex which has an axis of rotation which is co-linearly aligned with the central axis of the inlet, whereas in the sixth embodiment, the axis of rotation of the vortex is disposed substantially transversely to the central the axis of the inlet.
- the cross-sectional area of the duct varies along the flow path, decreasing in the entry and increasing in the exit.
- further embodiments of the modified venturi tubes as previously described are configured to conform with this constraint. As a result, the volume of fluid flowing through the entry and exit of the venturi contracts or expands in the greater part in accordance with the Golden Ratio.
- the arrangements promote substantially radial laminar flow and it is believed that this assists the efficiency of the fluid flow within those arrangements
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- Engineering & Computer Science (AREA)
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- Physics & Mathematics (AREA)
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- General Physics & Mathematics (AREA)
- Automation & Control Theory (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Chemical & Material Sciences (AREA)
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Abstract
Description
- The present application is a continuation and claims the priority benefit of U.S. patent application Ser. No. 12/862,637 filed Aug. 24, 2010, which is a continuation and claims the priority benefit of U.S. patent application Ser. No. 11/323,137 filed Dec. 29, 2005, now U.S. Pat. No. 7,802,583, which is a continuation and claims the priority benefit of PCT patent application PCT/AU2004/000862 filed Jun. 29, 2004, which claims the priority benefit of Australian patent application 2003903386 filed Jul. 2, 2003. The disclosures of aforementioned applications are incorporated herein by reference.
- 1. Field of the Invention
- The present invention relates to nozzles, diffusers and venturis. It may be applied in any application in which nozzles, diffusers and venturis are used.
- 2. Description of the Related Art
- Nozzles, diffusers and venturis are specific types of ducts used in relation to the flow of fluid. For the purpose of this specification, a nozzle is intended to mean a duct of varying cross-sectional area which is designed so that fluid flow is accelerated by a pressure differentiated between the inlet and the outlet. A diffuser is intended to mean a duct of varying cross-sectional area which is designed so that fluid flow is decelerated by an increase of pressure between the inlet and the outlet. A venturi can be seen as a duct comprising a nozzle section and diffuser section abutted in tandem.
- Nozzles are widely used in the field of fluid flow as a means to provide an accelerated stream of fluid and have many applications. Diffusers are used to decelerate fluid flow and again have many applications. Venturis are used to cause a short region of accelerated flow in a duct. It is a well known law of thermodynamics that the accelerated fluid flow is accompanied by a reduced pressure, and that many applications of venturis are directed to utilising the reduced pressure.
- While nozzles, diffusers and venturis are widely used, it is also well known that their performance is affected considerably by turbulence and frictional losses. These factors significantly limit the uses to which such devices can be applied.
- Accordingly, an exemplary embodiment of the present invention provides a flow controller adapted to control a flow of fluid within the controller, the flow controller having a flow path adapted to convey said fluid, wherein the cross-sectional area of the flow path varies along the flow path and wherein in at least a portion of its length the flow controller comprises an active surface capable of influencing the fluid flow through the flow path.
- According to an exemplary embodiment of the invention, the active surface is adapted to cause rotational motion of fluid within the fluid pathway about the axis of flow of the fluid.
- According to an exemplary embodiment of the invention, the active surface is adapted to cause vortical motion of fluid within the fluid pathway about the axis of flow of the fluid.
- According to an exemplary embodiment of the invention, the configuration of the active surface conforms to at least one logarithmic curve conforming to the Golden Section.
- According to an exemplary embodiment of the invention the curvature of the active surface is uni-dimensional.
- According to an exemplary embodiment of the invention the curvature of the active surface is bi-dimensional.
- According to an exemplary embodiment of the invention, the curvature of the active surface varies in accordance with the Golden Section.
- According to an exemplary embodiment of the invention, the curvature of the active surface conforms to an equiangular spiral.
- According to an exemplary embodiment of the invention the curvature of the active surface is transverse to the central axis of the fluid pathway.
- According to an exemplary embodiment of the invention the curvature of the active surface can be in a direction parallel to the central axis.
- According to an exemplary embodiment of the invention the curvature of the active surface is both transverse to the central axis and is parallel to the direction of the central axis to define a three-dimensional surface conforming substantially or in the greater part to the Golden Section.
- According to an exemplary embodiment of the invention, the fluid pathway has a spiral configuration. According to a preferred embodiment the configuration takes the form of a logarithmic helix or a volute or a whorl.
- According to an exemplary embodiment of the invention, the cross-sectional area of the flow path varies logarithmically substantially or in greater part in conformity to the Golden Section.
- According to an exemplary embodiment of the invention, the cross-sectional area of the flow path varies to cause the incremental volume of the flow path to vary logarithmically.
- According to an exemplary embodiment of the invention, the incremental volume is caused to vary in conformity with the Golden Ratio.
- According to an exemplary embodiment of the invention, the active surface has the configuration conforming to the external configuration of a shell of the phylum Mollusca, class Gastropoda or Cephalopoda. According to exemplary forms of the invention the active surface conforms to the external configuration of shells selected from the genera Volutidea, Argonauta, Nautilus, Conidea or Turbinidea.
- According to an exemplary embodiment of the invention, the active surface has the configuration of the interior of shells of the phylum Mollusca; classes Gastropoda or Cephalopoda. In particular embodiments, the active surface has the configuration of the interior of shells selected from the genera Volutidea, Conidea, Turbinidea, Argonauta, or Nautilus.
- According to an exemplary embodiment of the invention, the configuration of the flow controller promotes substantially radially laminar fluid flow.
- According to an exemplary embodiment of the invention, the flow controller comprises a nozzle.
- According to an exemplary embodiment of the invention, the flow controller comprises a diffuser.
- According to an exemplary embodiment of the invention, the flow controller comprises a venturi.
-
FIG. 1 is a chart of the Golden Section or Fibonacci Progression; -
FIG. 2 is an isometric view of a nozzle according to a first embodiment; -
FIG. 3 is an isometric view of a nozzle according to a second embodiment; -
FIG. 4 is an isometric view of a nozzle according to a third embodiment; -
FIG. 5 is an isometric view of a diffuser according to a fourth embodiment; -
FIG. 6 is a sectional elevation of a conventional venturi tube; -
FIG. 7 is an isometric view of a venturi according to a fifth embodiment; -
FIG. 8 is an isometric view of a venturi according to a sixth embodiment. - An embodiment of the invention is directed to a flow controller, the structure of which is configured to cause the rate of a fluid flow to be altered during passage through the controller. Each of the embodiments is directed to a flow controller adapted to alter the rate of flow of a fluid.
- It has been found that all fluids when moving under the influence of the natural forces of Nature, tend to move in spirals or vortices. These spirals or vortices generally comply to a mathematical progression known as the Golden Ratio or a Fibonacci-like Progression.
- Each of the embodiments serves, in the greater part, to enable fluids to move in their naturally preferred way, thereby reducing inefficiencies created through turbulence and friction which are normally found in apparatus commonly used for propagating fluid flow. Previously developed technologies have generally been less compliant with natural fluid flow tendencies.
- The greater percentage of the surfaces of the flow controller of each of the embodiments described herein are generally designed in the greater part, in accordance with the Golden Section or Ratio or are designed to ensure the volume of fluid flowing through the flow controller expands or contracts in the greater part in accordance with the Golden Section and therefore it is a characteristic of each of the embodiments that the flow controller provides a fluid pathway which is of a spiralling configuration and which conforms at least in greater part to the characteristics of the Golden Section or Ratio.
- The characteristics of the Golden Section are illustrated in
FIG. 1 which illustrates the unfolding of the spiral curve according to the Golden Section or Ratio. As the spiral unfolds the order of growth of the radius of the curve which is measured at equiangular radii (e.g., E, F, G, H, I and J) is constant. This can be illustrated from the triangular representation of each radius between each sequence which corresponds to the formula of a:b=b:a+b which conforms to the ratio of 1:0.618 approximately and which is consistent throughout the curve. - It is a characteristic of each of the embodiments that the curvature of the surfaces which form the flow controller takes a two dimensional or three dimensional shape equivalent to the lines of vorticity or streak lines found in a naturally occurring vortex. In general, the curvature of the surfaces substantially or in the greater part conform to the characteristics of the Golden Section or Ratio and that any variation in cross-sectional area of the flow controller also substantially or in greater part conforms to the characteristics of the Golden Section or Ratio. In at least some of the embodiments, the curvature of the active surface conforms to an equiangular spiral. Furthermore it has been found that the characteristics of the Golden Section or Ratio are found in nature in the form of the external and internal configurations of shells of the phylum Mollusca, classes Gastropoda and Cephalopoda and it is a common characteristic of at least some of the embodiments that the fluid pathway defined by the flow controller corresponds generally to the external or internal configuration of shells of one or more of the genera of the phylum Mollusca, classes Gastropoda and Cephalopoda.
- It has been found that it is a characteristic of fluid flow that, when it is caused to undergo a fluid flow through a pathway having a curvature substantially or in greater part conforming to that of the Golden Section or Ratio that the fluid flow over the surfaces is substantially non-turbulent and as a result has a decreased tendency to cavitate. As a result, fluid flow over the surface is more efficient than has been encountered in previous instances where the pathway does not substantially or in greater part correspond to that of the Golden Section. As a result of the reduced degree of turbulence which is induced in the fluid in its passageway through such a pathway, the flow controllers according to the various embodiments can be used for conducting fluid with a greater efficiency than has previously been possible with conventional flow controllers of equivalent dimensional characteristics.
- To assist the reader's understanding of the embodiments, the outer surfaces of the embodiments in the drawings are depicted in a way whereby they would correspond with the inner surfaces, such as would be the case if the walls of the embodiments are of constant thickness. In this way some concept of the helical/spiral configurations of the inner surfaces is conveyed. In practical fluid flow control devices, the configuration of the outer surface is not of significance to the embodiments and thus the outer surface could be configured as a simple surface such as a cone, leaving the inner surface complex as suggested in these drawings.
- The first embodiment takes the form of a nozzle as shown in
FIG. 2 . Thenozzle 11 has anozzle body 21, anoutlet 22 and aninlet 23 which is adapted to be joined to a duct (not shown) such as a pipe, hose or similar providing a source of fluid under pressure. Thenozzle body 21 has aninternal surface 25 which reduces in cross-sectional area to theoutlet 22. In addition, the internal surface of the nozzle may be seen to twist in a combination helical manner and spiralling manner between the input and the output. As indicated above, this twist is in a configuration which provides an active surface which conforms at least in greater part to the characteristics of the Golden Section or Ratio. It will be seen that as a result of the twist, fluid flowing in the nozzle is caused to be given a rotational motion about the longitudinal axis of the nozzle to thereby induce vortical motion in the fluid. - As a result of the vortical motion, the turbulence and friction in the nozzle are reduced considerably from that observed in a conventional nozzle having a simple conical internal surface.
- A second embodiment takes the form of a nozzle as shown in
FIG. 3 . The second embodiment is of substantially similar construction to that of the first embodiment, and therefore in the drawings like parts are denoted with like numerals. The second embodiment differs from the first only in the particular design of the nozzle in that it is relatively longer and has greater twist. By varying the parameters of the nozzle, the formation of the vortical flow emitted from the nozzle outlet can be controlled. In certain applications, it will be desirable for the outlet to comprise a narrow vortical stream while in others, a diverging stream will be required to promote mixing of the output with the surrounding fluid. - A third embodiment takes the form of a nozzle as shown in
FIG. 4 . In this embodiment, the twist in the flow surfaces causes the direction of flow to be diverted transversely to that of the incoming flow stream. This redirection is achieved without significant loss because the internal surface of the nozzle is still configured to conform at least in greater part to the characteristics of the Golden Section or Ratio. As a result, turbulence is substantially avoided. - It will be appreciated that a whole class of embodiments are possible whereby the output flow is directed obliquely relative to the direction of the input flow stream.
- A fourth embodiment takes the form of a diffuser as shown in
FIG. 5 . It may be appreciated that a diffuser may comprise a flow controller substantially identical to a nozzle but with direction of flow reversed. In this regard, the diffuser ofFIG. 5 corresponds with the nozzle ofFIG. 2 but having aninternal surface 25 which increases in cross-sectional area to theoutlet 22. Therefore, in the drawings like numerals are again used to depict like features. As with the nozzle, while the diffuser ofFIG. 4 will induce vortical motion in the fluid flow, the precise characteristics of the output flow can be controlled by varying the design properties of the diffuser while maintaining the inner surface to conform at least in greater part to the characteristics of the Golden Section or Ratio. - It has been previously been noted that the cross-sectional area of the previous embodiments varies between the inlets to the outlets; for the nozzles, the area decreasing and for the diffusers, the area increasing. In a further development of the previous embodiments, it has been found advantageous, at least in certain circumstances to vary the incremental volume of the controller along the fluid pathway in a manner that conforms to the characteristics of the Golden Section or Ratio. To take advantage of this aspect, further embodiments of the fluid flow control devices as previously described are configured to conform with this constraint. As a result, the volume of fluid flowing through the flow controller expands or contracts in the greater part in accordance with the Golden Ratio.
- A fifth embodiment takes the form of a modified venturi tube as shown in
FIG. 7 . The modified venturi tube is best appreciated by comparison with a conventional venturi tube which is depicted InFIG. 6 . In the conventional venturi tube ofFIG. 6 , aventuri 51 comprises aninlet 52, anoutlet 53 and aconstricted region 54. The constrictedregion 54 comprises anentry 55, anexit 56 and a region ofmaximum constriction 57. In the drawings, the flow is represented byflow lines 58. - When fluid is caused to flow into the
inlet 52 ofventuri 21, it is affected by theentry 55 wherein the diameter of the fluid pathway is progressively reduced until the region ofmaximum constriction 57 is reached. This constriction within the fluid pathway causes the speed at which the fluid is travelling to be increased. In accordance with well known laws of thermodynamics, this increase in fluid speed is accompanied by a reduction in pressure of the fluid. Subsequent to the region ofmaximum constriction 57, the fluid flow is affected by theexit 56 wherein the diameter of the fluid pathway is progressively increased to theoutlet 53. In theexit 56, the fluid is progressively slowed. - It is known that the energy losses at a venturi are very significant. As mentioned above, these losses are caused both by friction and turbulence. In particular, it is well known that while the performance of a venturi can be increased by increasing the ratio of the inlet diameter relative to the diameter of
maximum constriction 57, it is also known that in practice that any gains achieved by so reducing the region of maximum constriction are rapidly cancelled by the increased losses which result. - As can be seen in
FIG. 7 , the modifiedventuri 61 comprises aninlet 62, anoutlet 63, a region ofmaximum constriction 64, anentry 65 and anexit 66. It will be readily perceived that these portions conform generally to corresponding portions of the conventional venturi tube ofFIG. 6 . In contrast however, theentry 64 andexit 65 are specifically designed to induce the fluid to move in accordance with the laws of Nature. As mentioned previously, the flow controller is designed with a pathway having a curvature substantially or in greater part conforming to that of the Golden Section or Ratio. The fluid is thereby induced into vortical flow the greater part of which conforms to the Golden Section or Ratio. The energy losses caused as a result of this vortical flow are considerably lower than those which result from a conventional venturi. - As a result of the considerably reduced energy losses caused by the modified venturi of the fifth embodiment, the apparatus may be used more effectively than previously has been possible. Firstly, it is possible to increase the ratio of the area of inlet relative to the area of maximum constriction. This increases the relative pressure difference that may be generated between the inlet and the region of maximum constriction. This broadens the scope of use of the device.
- A sixth embodiment takes the form of a modified venturi tube as shown in
FIG. 8 . The sixth embodiment, although somewhat different in appearance, operates in substantially the same manner as that of fifth embodiment and so, in the drawings, like parts are denoted with like numerals. The sixth embodiment again comprises a duct, the area of cross-section of which reduces from an inlet to a portion of maximum constriction, and then increase to the outlet. The difference between the sixth embodiment and the fifth is that in the fifth embodiment the flow induces a vortex which has an axis of rotation which is co-linearly aligned with the central axis of the inlet, whereas in the sixth embodiment, the axis of rotation of the vortex is disposed substantially transversely to the central the axis of the inlet. - It has been noted previously that in the embodiments of the modified venturi tube, the cross-sectional area of the duct varies along the flow path, decreasing in the entry and increasing in the exit. As in the examples of the nozzles and diffusers, it has been found advantageous, at least in certain circumstances to vary the incremental volume of the controller along the fluid pathway in a manner that conforms to the characteristics of the Golden Section or Ratio. To take advantage of this aspect, further embodiments of the modified venturi tubes as previously described are configured to conform with this constraint. As a result, the volume of fluid flowing through the entry and exit of the venturi contracts or expands in the greater part in accordance with the Golden Ratio.
- It has been found that, in at least certain configurations of the embodiments, the arrangements promote substantially radial laminar flow and it is believed that this assists the efficiency of the fluid flow within those arrangements
- It should be appreciated that the scope of the present invention need not be limited to the particular scope of the embodiments described above.
- Throughout the specification, unless the context requires otherwise, the word “comprise” or variations such as “comprises” or “comprising”, will be understood to imply the inclusion of a stated integer or group of integers but not the exclusion of any other integer or group of integers.
Claims (22)
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11359652B2 (en) * | 2020-03-10 | 2022-06-14 | Paul Van Buskirk | Orifice plates |
Families Citing this family (28)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AUPR982502A0 (en) * | 2002-01-03 | 2002-01-31 | Pax Fluid Systems Inc. | A heat exchanger |
AUPR982302A0 (en) | 2002-01-03 | 2002-01-31 | Pax Fluid Systems Inc. | A fluid flow controller |
EP1470338A4 (en) * | 2002-01-03 | 2012-01-11 | Pax Scient Inc | Vortex ring generator |
US6845523B2 (en) * | 2002-08-16 | 2005-01-25 | Roger M. Copp | Rescue vest with rollers |
AU2003903386A0 (en) * | 2003-07-02 | 2003-07-17 | Pax Scientific, Inc | Fluid flow control device |
KR101168098B1 (en) | 2003-11-04 | 2012-07-24 | 팍스 싸이언티픽 인코퍼레이션 | Fluid Circulation System |
WO2005073560A1 (en) * | 2004-01-30 | 2005-08-11 | Pax Scientific, Inc | A vortical flow rotor |
AU2005207983A1 (en) * | 2004-01-30 | 2005-08-11 | Pax Scientific, Inc | Housing for a centrifugal fan, pump or turbine |
KR101122723B1 (en) * | 2005-08-24 | 2012-03-23 | 엘아이지에이디피 주식회사 | Gas supply line and gas supply system |
US8328522B2 (en) | 2006-09-29 | 2012-12-11 | Pax Scientific, Inc. | Axial flow fan |
US20090308472A1 (en) * | 2008-06-15 | 2009-12-17 | Jayden David Harman | Swirl Inducer |
US20130221024A1 (en) * | 2010-10-08 | 2013-08-29 | Central Glass Company, Limited | Halogen-containing gas supply apparatus and halogen-containing gas supply method |
US20120152399A1 (en) * | 2010-12-20 | 2012-06-21 | Marc Gregory Allinson | F.U.N tunnel(s) |
US8887745B2 (en) * | 2011-08-22 | 2014-11-18 | Robert Krause | Midpoint reversed directionally coupled double chamber structure for the natural induction of a tornado |
US8794217B1 (en) | 2013-02-07 | 2014-08-05 | Thrival Tech, LLC | Coherent-structure fuel treatment systems and methods |
US9222403B2 (en) | 2013-02-07 | 2015-12-29 | Thrival Tech, LLC | Fuel treatment system and method |
US10252784B2 (en) | 2013-03-15 | 2019-04-09 | John Ioan Restea | Apparatus for propelling fluid, especially for propulsion of a floating vehicle |
US20160271519A1 (en) * | 2013-05-03 | 2016-09-22 | Jayden David Harman | Vacuum Condenser |
CN103482074B (en) * | 2013-09-28 | 2015-06-17 | 魏伯卿 | Volute cushion boosting propeller |
USD732655S1 (en) * | 2013-11-21 | 2015-06-23 | Sanyo Denki Co., Ltd. | Fan |
CN105934561B (en) | 2014-01-24 | 2019-06-07 | 卡梅伦技术有限公司 | The system and method reduced for polymer degradation |
NL2016590B1 (en) * | 2016-04-12 | 2017-11-01 | Van Langh Holding B V | Cooling system and machining device. |
CN106382413B (en) * | 2016-09-29 | 2018-11-16 | 裴学华 | Noise-eliminating tap |
CA3059049A1 (en) * | 2016-11-08 | 2018-05-17 | 1090690 B.C. Ltd. | Wave producing method and apparatus |
CN106593538B (en) * | 2017-01-24 | 2022-05-17 | 北京磐龙天地科技发展股份有限公司 | Vortex engine |
CN207715843U (en) * | 2017-12-22 | 2018-08-10 | 上海河图工程股份有限公司 | A kind of wear-resistant multilevel decompression mechanism |
CN108479236A (en) * | 2018-04-25 | 2018-09-04 | 广州绿竹环保科技有限公司 | A kind of water dust scrubber |
JP2020157823A (en) * | 2019-03-25 | 2020-10-01 | 本田技研工業株式会社 | Oil supply guide |
Family Cites Families (180)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11544A (en) * | 1854-08-22 | William | ||
US700785A (en) * | 1901-03-22 | 1902-05-27 | Albert L Kull | Muffler for explosive or other engines. |
US794926A (en) * | 1903-05-04 | 1905-07-18 | Benjamin Crawford | Exhaust-muffler. |
US825010A (en) | 1905-12-27 | 1906-07-03 | Benjamin W Snow | Muffler. |
US879583A (en) * | 1906-05-16 | 1908-02-18 | Arthur Pratt | Exhaust-muffler. |
US871825A (en) | 1906-09-07 | 1907-11-26 | Ludwig Schupmann | Projectile for rifled firearms. |
US965135A (en) * | 1908-12-30 | 1910-07-19 | Hugo C Gibson | Internal-combustion engine. |
US969101A (en) * | 1909-02-05 | 1910-08-30 | Hugo C Gibson | Muffler. |
US938101A (en) | 1909-02-05 | 1909-10-26 | Harry B Winters | Muffler. |
US943233A (en) | 1909-08-28 | 1909-12-14 | John Boyle | Exhaust-muffler. |
US1023225A (en) * | 1911-06-22 | 1912-04-16 | Mckenzie Cleland | Muffler for automobiles. |
US1272180A (en) * | 1917-06-26 | 1918-07-09 | Vacuum Muffler Corp | Muffler. |
US1356676A (en) | 1919-01-28 | 1920-10-26 | Automobile-radiator | |
US1353478A (en) * | 1919-09-09 | 1920-09-21 | George W Kirk | Muffler |
US1505893A (en) * | 1920-03-06 | 1924-08-19 | Hunter William | Silencer for internal-combustion engines |
US1396583A (en) | 1920-05-08 | 1921-11-08 | Krafve William | Muffler |
US1471697A (en) | 1922-09-09 | 1923-10-23 | Kubes Frantisek | Apparatus for making sugar fondant |
US1713047A (en) * | 1924-11-14 | 1929-05-14 | Maxim Silencer Co | Means for adjusting oscillation period of exhausts of internal-combustion engines |
US1785460A (en) | 1925-03-02 | 1930-12-16 | Robert Suczek | Pump or the like |
US1729018A (en) | 1925-11-05 | 1929-09-24 | Siders Wesley | Muffler for automobile engines |
US1658126A (en) * | 1926-07-05 | 1928-02-07 | Emanuel Hertz | Muffler for internal-combustion engines |
US1720918A (en) * | 1926-07-30 | 1929-07-16 | Harold H Nesbitt | Cooling tank |
US1756916A (en) * | 1927-01-24 | 1930-04-29 | Gen Motors Corp | Muffler |
US1667186A (en) * | 1927-05-31 | 1928-04-24 | William R Bluehdorn | Muzzle attachment for guns |
US1709217A (en) * | 1928-03-15 | 1929-04-16 | Francis F Hamilton | Exhaust muffler |
US1812413A (en) * | 1929-01-24 | 1931-06-30 | Maxim Silencer Co | Silencer |
US1872075A (en) * | 1929-01-24 | 1932-08-16 | Gen Motors Corp | Air cleaner and muffler |
US1816245A (en) * | 1929-04-06 | 1931-07-28 | Lester J Wolford | Exhaust silencer |
US1799039A (en) * | 1929-09-16 | 1931-03-31 | Conejos Anthony | Heat extractor |
US1891170A (en) | 1930-06-13 | 1932-12-13 | Nose Toichi | Aeroplane |
US1919250A (en) * | 1931-11-06 | 1933-07-25 | Joseph W Droll | Propeller wheel for fans |
US2068686A (en) * | 1934-11-27 | 1937-01-26 | Lascroux Joseph Louis | Apparatus for silencing the exhaust of internal combustion engines |
US2085796A (en) * | 1935-11-05 | 1937-07-06 | Tube Turns Inc | Method of making reducers |
US2210031A (en) * | 1936-08-28 | 1940-08-06 | Pfaudler Co Inc | Refrigerating apparatus and method |
US2139736A (en) | 1936-11-19 | 1938-12-13 | Kenneth P Durham | Vortical muffling device |
US2165808A (en) * | 1937-05-22 | 1939-07-11 | Murphy Daniel | Pump rotor |
US2359365A (en) | 1943-05-20 | 1944-10-03 | Katcher Morris | Muffler |
US2552615A (en) | 1948-05-29 | 1951-05-15 | Lawrence F Baltzer | Muffler with spiral conical insert |
US2912063A (en) | 1953-04-13 | 1959-11-10 | Barnes Ralph Glenn | Muffler |
US2784797A (en) | 1954-07-13 | 1957-03-12 | John H Bailey | Muffler |
GB873135A (en) | 1956-08-01 | 1961-07-19 | Marc Marie Paul Rene De La Fou | Improvements in or relating to engine exhaust systems |
US2879861A (en) * | 1956-11-16 | 1959-03-31 | Fred J Belsky | Flow control unit |
US2958390A (en) | 1957-03-18 | 1960-11-01 | Owens Illinois Glass Co | Sound muffling device |
US2908344A (en) | 1958-03-24 | 1959-10-13 | Maruo Hisao | Muffler |
US3071159A (en) * | 1958-04-19 | 1963-01-01 | Coraggioso Corrado Bono | Heat exchanger tube |
FR1231173A (en) * | 1959-04-09 | 1960-09-27 | Soc Lab Sarl | Improvements to the flow of fluids following non-rectilinear trajectories |
US3082695A (en) * | 1959-06-15 | 1963-03-26 | Klein Schanzlin & Becker Ag | Impellers, especially single vane impellers for rotary pumps |
GB893135A (en) | 1959-06-16 | 1962-04-04 | Union Carbide Corp | Conveying apparatus for removing roof falls during earth boring |
US3081826A (en) * | 1960-01-27 | 1963-03-19 | Loiseau Christophe | Ship propeller |
US3232341A (en) * | 1960-02-01 | 1966-02-01 | Garrett Corp | Condenser |
US3066755A (en) | 1960-04-21 | 1962-12-04 | Diehl William Carl | Muffler with spiral partition |
US3182748A (en) | 1961-08-15 | 1965-05-11 | Garrett Corp | Helical vane for sound absorbing device and method of making said vane |
US3215165A (en) | 1963-05-27 | 1965-11-02 | Cons Paper Bahamas Ltd | Method and device for the control of fluid flow |
US3371472A (en) * | 1965-12-08 | 1968-03-05 | John Krizman Jr. | Spark arrester |
US3339631A (en) * | 1966-07-13 | 1967-09-05 | James A Mcgurty | Heat exchanger utilizing vortex flow |
US3407995A (en) | 1966-10-12 | 1968-10-29 | Lau Blower Co | Blower assembly |
US3800951A (en) * | 1968-12-23 | 1974-04-02 | Bertin & Cie | Apparatus for removing a substance floating as a layer on the surface of a body of liquid |
US3584701A (en) * | 1970-04-07 | 1971-06-15 | Michael W Freeman | Sound and resonance control device |
US3636983A (en) * | 1970-08-14 | 1972-01-25 | Edwin J Keyser | Method and apparatus for increasing fluid flow |
US3692422A (en) * | 1971-01-18 | 1972-09-19 | Pierre Mengin Ets | Shearing pump |
US3688868A (en) | 1971-08-26 | 1972-09-05 | Stephen J Gibel | Expansion chambered, fail-safe muffler |
SU431850A1 (en) | 1972-07-03 | 1974-06-15 | Специальное Экспериментально-Конструкторское Бюро Промышленного Рыболовства | Submersible fish pump |
SU850104A1 (en) | 1973-12-24 | 1981-07-30 | Предприятие П/Я Р-6603 | Rotor-type film apparatus |
US3927731A (en) | 1974-04-10 | 1975-12-23 | Carter James B Ltd | Muffler with spiral duct and double inlets |
US3918829A (en) | 1974-06-19 | 1975-11-11 | Warren Pumps Inc | Low pressure-pulse kinetic pump |
US3940060A (en) * | 1974-08-23 | 1976-02-24 | Hermann Viets | Vortex ring generator |
US3964841A (en) * | 1974-09-18 | 1976-06-22 | Sigma Lutin, Narodni Podnik | Impeller blades |
US3970167A (en) | 1975-05-12 | 1976-07-20 | Irvin Joseph C | Rotary flow muffler |
US3957133A (en) * | 1975-09-10 | 1976-05-18 | Scovill Manufacturing Company | Muffler |
JPS5236219A (en) * | 1975-09-13 | 1977-03-19 | Teruo Kashiwara | Exhaust equipment for internal combustion engine |
DE2712443C3 (en) * | 1977-03-22 | 1981-08-20 | Brombach, Hansjörg, Dr.-Ing., 6990 Bad Mergentheim | Vortex chamber device |
US4323209A (en) * | 1977-07-18 | 1982-04-06 | Thompson Roger A | Counter-rotating vortices generator for an aircraft wing |
US4211183A (en) * | 1977-08-08 | 1980-07-08 | Hoult David P | Fish raising |
SU738566A1 (en) | 1978-01-23 | 1980-06-05 | Киевский Ордена Ленина Государственный Университет Им.Т.Г.Шевченко | Apparatus for keeping aquatic organisms |
US4182596A (en) * | 1978-02-16 | 1980-01-08 | Carrier Corporation | Discharge housing assembly for a vane axial fan |
JPS54129699U (en) | 1978-02-17 | 1979-09-08 | ||
SE415791B (en) | 1979-01-29 | 1980-10-27 | Gunnar Valdemar Eriksson | COMBINED SILENCER AND OIL OVELA for compressed air appliances |
US4225102A (en) * | 1979-03-12 | 1980-09-30 | The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration | Aerodynamic side-force alleviator means |
GB2057567A (en) | 1979-08-24 | 1981-04-01 | Borg Warner | Expanding scroll diffuser for radial flow impeller |
DE2940773C2 (en) | 1979-10-08 | 1986-08-14 | Punker GmbH, 2330 Eckernförde | High-performance centrifugal fan |
US4317502A (en) * | 1979-10-22 | 1982-03-02 | Harris Theodore R | Engine exhaust muffler |
US4299553A (en) | 1979-12-14 | 1981-11-10 | The Continental Group, Inc. | Hot runner manifold flow distributor plug |
SU858896A1 (en) | 1979-12-19 | 1981-08-30 | Предприятие П/Я Р-6956 | Rotor-type comminuting device |
US4331213A (en) * | 1980-01-28 | 1982-05-25 | Mitsuko Leith | Automobile exhaust control system |
SU1030631A1 (en) | 1980-05-26 | 1983-07-23 | Сибирский Научно-Исследовательский И Проектный Институт Цементной Промышленности,Научная Часть | Heat exchange device |
DE3238913C2 (en) | 1982-10-21 | 1985-10-03 | Werner Dr. 8972 Sonthofen Röhrs | Centrifugal fan housing |
IT1235222B (en) * | 1982-11-26 | 1992-06-26 | Secratary Of State For Defence | IMPROVEMENT IN MISSILE AND SIMILAR FUSELETS |
DE3365881D1 (en) * | 1982-12-22 | 1986-10-09 | Staehle Martin | Centrifugal pump of the open channel rotor type |
JPS59158308A (en) * | 1983-02-28 | 1984-09-07 | Hisao Kojima | Muffler |
IT1195502B (en) * | 1983-06-02 | 1988-10-19 | Giuseppe Nieri | SILENCER DEVICE PARTICULARLY FOR EXHAUST GAS AND GENERAL GAS IN QUICK MOVEMENT |
US4505297A (en) * | 1983-08-02 | 1985-03-19 | Shell California Production Inc. | Steam distribution manifold |
US4685534A (en) * | 1983-08-16 | 1987-08-11 | Burstein A Lincoln | Method and apparatus for control of fluids |
US4644135A (en) * | 1983-08-29 | 1987-02-17 | The Marley Company | Wall mounted forced air electric heater |
US4699340A (en) | 1983-11-07 | 1987-10-13 | Vehicle Research Corporation | Laminar vortex pump system |
DE3505789A1 (en) * | 1985-02-20 | 1986-08-21 | Grote, Paul, 2901 Friedrichsfehn | SPIRAL HEAT EXCHANGER |
US4996924A (en) * | 1987-08-11 | 1991-03-05 | Mcclain Harry T | Aerodynamic air foil surfaces for in-flight control for projectiles |
SE457121B (en) * | 1986-05-07 | 1988-11-28 | Mosbaeck Handelsbolag I Helsin | FLOEDESREGULATOR |
US4693339A (en) | 1986-10-16 | 1987-09-15 | Newport News Shipbuilding And Dry Dock Company | Muffler for gas inducting machinery generating low frequency noise |
US5100242A (en) * | 1987-03-20 | 1992-03-31 | Brian Latto | Vortex ring mixers |
US4823865A (en) * | 1988-02-18 | 1989-04-25 | A. O. Smith Corporation | Turbulator construction for a heat exchanger |
DK122788A (en) | 1988-03-08 | 1989-09-09 | Joergen Mosbaek Johannessen | DEVICE FOR REGULATING THE FLOW IN A CONTROL SYSTEM |
US4993487A (en) * | 1989-03-29 | 1991-02-19 | Sundstrand Corporation | Spiral heat exchanger |
US5058837A (en) | 1989-04-07 | 1991-10-22 | Wheeler Gary O | Low drag vortex generators |
GB8918446D0 (en) * | 1989-08-12 | 1989-09-20 | Stokes Keith H | Heat exchange apparatus |
US5181537A (en) * | 1989-12-12 | 1993-01-26 | Conoco Inc. | Outlet collectors that are rate insensitive |
US5010910A (en) * | 1990-05-21 | 1991-04-30 | Mobil Oil Corporation | Steam distribution manifold |
US5207397A (en) * | 1990-06-08 | 1993-05-04 | Eidetics International, Inc. | Rotatable nose and nose boom strakes and methods for aircraft stability and control |
FR2666031B1 (en) | 1990-08-27 | 1993-10-22 | Pierre Saget | PROCESS FOR THE CENTRIFUGAL SEPARATION OF THE PHASES OF A MIXTURE AND CENTRIFUGAL SEPARATOR WITH LONGITUDINAL BLADES USING THIS PROCESS. |
GB2249642B (en) * | 1990-10-29 | 1994-09-14 | Hydro Int Ltd | Vortex valves |
US5040558A (en) * | 1990-10-31 | 1991-08-20 | Mobil Oil Corporation | Low thermal stress steam distribution manifold |
US5249993A (en) | 1991-07-19 | 1993-10-05 | Martin Roland V R | Weed resistant boat propeller |
US5261745A (en) | 1992-04-13 | 1993-11-16 | Watkins James R | Mixing apparatus with frusto-conically shaped impeller for mixing a liquid and a particulate solid |
US5266755A (en) | 1992-11-02 | 1993-11-30 | Chien Kuo Feng | Car silencer for absorbing sound and exhaust pollutants |
JP2649131B2 (en) | 1992-11-18 | 1997-09-03 | 神鋼パンテツク株式会社 | Stirrer and bottom ribbon blade used for it |
US5320493A (en) | 1992-12-16 | 1994-06-14 | Industrial Technology Research Institute | Ultra-thin low noise axial flow fan for office automation machines |
US5312224A (en) * | 1993-03-12 | 1994-05-17 | International Business Machines Corporation | Conical logarithmic spiral viscosity pump |
DE4331606C1 (en) * | 1993-09-17 | 1994-10-06 | Gutehoffnungshuette Man | Spiral housing for turbo-engines (rotary engines, turbomachines) |
KR960703203A (en) * | 1994-04-28 | 1996-06-19 | 시게후치 마사토시 | MULTIVANE RADIAL FAN DESIGNING METHOD AND MULTIVANE RADIAL FAN |
AT407772B (en) | 1994-11-08 | 2001-06-25 | Habsburg Lothringen Leopold In | COMBINED RESONATOR AND MUFFLER SYSTEM |
US5787974A (en) * | 1995-06-07 | 1998-08-04 | Pennington; Robert L. | Spiral heat exchanger and method of manufacture |
WO1997003291A1 (en) * | 1995-07-10 | 1997-01-30 | Jayden David Harman | A rotor |
AU694679B2 (en) | 1995-07-10 | 1998-07-23 | Jayden David Harman | A rotor |
JP3632789B2 (en) * | 1995-08-28 | 2005-03-23 | 東陶機器株式会社 | Multiblade centrifugal fan design method and multiblade centrifugal fan |
US5661638A (en) * | 1995-11-03 | 1997-08-26 | Silicon Graphics, Inc. | High performance spiral heat sink |
FR2744661B1 (en) * | 1996-02-08 | 1998-04-03 | Deckner Andre Georges | REVERSE HELICOIDAL REAMER |
US6179218B1 (en) * | 1996-08-30 | 2001-01-30 | Christopher Gates | Solar powered water fountain |
JP3574727B2 (en) * | 1997-03-31 | 2004-10-06 | 国際技術開発株式会社 | Heat exchange equipment |
US5943877A (en) * | 1997-05-05 | 1999-08-31 | The Joseph Company | Space vehicle freezer including heat exchange unit space use |
US5824972A (en) | 1997-05-13 | 1998-10-20 | Butler; Boyd L. | Acoustic muffler |
GB2334791B (en) * | 1998-02-27 | 2002-07-17 | Hydro Int Plc | Vortex valves |
US5934612A (en) * | 1998-03-11 | 1999-08-10 | Northrop Grumman Corporation | Wingtip vortex device for induced drag reduction and vortex cancellation |
CA2263033A1 (en) * | 1998-05-21 | 1999-11-21 | Gary L. Wegner | Cyclonic liquid circulation system |
WO2000003859A1 (en) * | 1998-07-16 | 2000-01-27 | Idemitsu Petrochemical Co., Ltd. | Lightweight resin molded product and production method thereof |
GB9828696D0 (en) * | 1998-12-29 | 1999-02-17 | Houston J G | Blood-flow tubing |
JP2000257610A (en) | 1999-03-10 | 2000-09-19 | Tomotaka Marui | Turbulence restraining method by autogenous swirl flow using surface flow of fixed rotor, autogenous swirl flow generating device, autogenous swirl flow generating and maintaining control method and verifying method for turbulence restrain effect |
JP2001012658A (en) * | 1999-06-25 | 2001-01-16 | Fujita Corp | Drain pipe |
KR100337287B1 (en) * | 1999-07-28 | 2002-05-17 | 윤종용 | centrifugal fan |
US6252258B1 (en) * | 1999-08-10 | 2001-06-26 | Rockwell Science Center Llc | High power rectifier |
IL131590A0 (en) * | 1999-08-25 | 2001-01-28 | Technion Res & Dev Foundation | Self-adaptive segmented orifice device and method |
WO2001018476A1 (en) | 1999-09-10 | 2001-03-15 | Kasprzyk Martin R | Insert for a radiant tube |
US6089348A (en) | 1999-09-22 | 2000-07-18 | Bokor Manufacturing Inc. | Blower noise silencer |
US6152258A (en) | 1999-09-28 | 2000-11-28 | Brunswick Corporation | Exhaust system with silencing and water separation capability |
DK1238185T3 (en) * | 1999-11-25 | 2006-03-06 | Jayden David Harman | Single or multi-blade rotor |
US6385967B1 (en) * | 2000-05-31 | 2002-05-14 | Shun-Lai Chen | Exhaust pipe for motor vehicle muffler |
KR100378803B1 (en) * | 2000-06-12 | 2003-04-07 | 엘지전자 주식회사 | Muffler for compressor |
US20020000720A1 (en) | 2000-06-21 | 2002-01-03 | Knowles L. James | Washdown system |
ES2195689B1 (en) | 2000-07-26 | 2005-04-01 | Manuel Muñoz Saiz | SUSTAINING PROVISION FOR AIRPLANE SIDE SURFACES. |
JP4185654B2 (en) * | 2000-08-04 | 2008-11-26 | カルソニックカンセイ株式会社 | Centrifugal multi-blade blower |
US6596170B2 (en) | 2000-11-24 | 2003-07-22 | Wlodzimierz Jon Tuszko | Long free vortex cylindrical telescopic separation chamber cyclone apparatus |
US6632071B2 (en) | 2000-11-30 | 2003-10-14 | Lou Pauly | Blower impeller and method of lofting their blade shapes |
US6382348B1 (en) * | 2001-02-09 | 2002-05-07 | Shun-Lai Chen | Twin muffler |
FR2823541B1 (en) * | 2001-04-11 | 2003-05-23 | Christian Hugues | CYLINDRICAL WING END WITH HELICOID SLOT |
US6684633B2 (en) * | 2001-04-27 | 2004-02-03 | Marion Barney Jett | Exhaust device for two-stroke internal combustion engine |
US20030012649A1 (en) * | 2001-07-16 | 2003-01-16 | Masaharu Sakai | Centrifugal blower |
DE10163812A1 (en) | 2001-12-22 | 2003-07-03 | Mann & Hummel Filter | Device for sound absorption in a pipe duct |
EP1470338A4 (en) | 2002-01-03 | 2012-01-11 | Pax Scient Inc | Vortex ring generator |
AUPR982302A0 (en) | 2002-01-03 | 2002-01-31 | Pax Fluid Systems Inc. | A fluid flow controller |
AUPR982502A0 (en) | 2002-01-03 | 2002-01-31 | Pax Fluid Systems Inc. | A heat exchanger |
US6959782B2 (en) | 2002-03-22 | 2005-11-01 | Tecumseh Products Company | Tuned exhaust system for small engines |
JP3858744B2 (en) | 2002-04-09 | 2006-12-20 | 株式会社デンソー | Centrifugal blower |
DE10230044A1 (en) | 2002-07-04 | 2004-02-05 | 3W-Modellmotoren Gmbh | silencer |
US6817419B2 (en) | 2002-10-30 | 2004-11-16 | John A. Reid | Well production management and storage system controller |
USD510998S1 (en) * | 2003-03-27 | 2005-10-25 | Research Foundation Of The University Of Central Florida | High efficiency air conditioner condenser twisted fan blades and hub |
USD487800S1 (en) * | 2003-04-16 | 2004-03-23 | Delta Electronics Inc. | Fan |
AU2003903386A0 (en) | 2003-07-02 | 2003-07-17 | Pax Scientific, Inc | Fluid flow control device |
US7661509B2 (en) * | 2003-07-14 | 2010-02-16 | Dadd Paul M | Devices for regulating pressure and flow pulses |
US20050155916A1 (en) * | 2003-07-19 | 2005-07-21 | Tuszko Wlodzimierz J. | Cylindrical telescopic structure cyclone apparatus |
CN1279868C (en) * | 2003-08-26 | 2006-10-18 | 苏州金莱克清洁器具有限公司 | Dust-collector noise silencer |
USD509584S1 (en) * | 2003-10-08 | 2005-09-13 | Datech Technology Co., Ltd. | Fan wheel with hub fastener |
KR101168098B1 (en) | 2003-11-04 | 2012-07-24 | 팍스 싸이언티픽 인코퍼레이션 | Fluid Circulation System |
WO2005073560A1 (en) * | 2004-01-30 | 2005-08-11 | Pax Scientific, Inc | A vortical flow rotor |
AU2005207983A1 (en) * | 2004-01-30 | 2005-08-11 | Pax Scientific, Inc | Housing for a centrifugal fan, pump or turbine |
TWM252798U (en) | 2004-03-16 | 2004-12-11 | Huei-Fang Chen | Muffler structure |
US20060260869A1 (en) | 2005-05-18 | 2006-11-23 | Kim Jay S | Muffler having fluid swirling vanes |
US7331422B2 (en) | 2005-07-18 | 2008-02-19 | Alan Wall | Vortex muffler |
TWM287387U (en) | 2005-08-24 | 2006-02-11 | Delta Electronics Inc | Fan and fan housing with air-guiding static blades |
US8328522B2 (en) | 2006-09-29 | 2012-12-11 | Pax Scientific, Inc. | Axial flow fan |
US20090308472A1 (en) | 2008-06-15 | 2009-12-17 | Jayden David Harman | Swirl Inducer |
DE102009000645B3 (en) | 2009-02-05 | 2010-07-29 | Deutsches Zentrum für Luft- und Raumfahrt e.V. | Silencer with at least one Helmholtz resonator constructed by means of helical internals |
US8287422B2 (en) * | 2010-05-14 | 2012-10-16 | Shu-Mei Tseng | Model helicopter with epicyclic gearing based reduction gear mechanism |
-
2003
- 2003-07-02 AU AU2003903386A patent/AU2003903386A0/en not_active Abandoned
-
2004
- 2004-06-29 MX MXPA06000145A patent/MXPA06000145A/en not_active Application Discontinuation
- 2004-06-29 WO PCT/AU2004/000862 patent/WO2005003616A1/en active Application Filing
- 2004-06-29 KR KR1020057025416A patent/KR20060037285A/en not_active Application Discontinuation
- 2004-06-29 EP EP04737483A patent/EP1644657A4/en not_active Withdrawn
- 2004-06-29 EA EA200600136A patent/EA007421B1/en not_active IP Right Cessation
- 2004-06-29 JP JP2006517892A patent/JP2007538201A/en active Pending
- 2004-06-29 CN CNA2004800187633A patent/CN1816713A/en active Pending
- 2004-06-29 CA CA 2532090 patent/CA2532090A1/en not_active Abandoned
-
2005
- 2005-12-26 IL IL172815A patent/IL172815A/en not_active IP Right Cessation
- 2005-12-29 US US11/323,137 patent/US7802583B2/en not_active Expired - Fee Related
-
2010
- 2010-08-24 US US12/862,637 patent/US8631827B2/en active Active
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2013
- 2013-12-11 US US14/103,593 patent/US20140096854A1/en not_active Abandoned
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11359652B2 (en) * | 2020-03-10 | 2022-06-14 | Paul Van Buskirk | Orifice plates |
Also Published As
Publication number | Publication date |
---|---|
EA200600136A1 (en) | 2006-06-30 |
CA2532090A1 (en) | 2005-01-13 |
AU2003903386A0 (en) | 2003-07-17 |
JP2007538201A (en) | 2007-12-27 |
MXPA06000145A (en) | 2006-04-27 |
WO2005003616A1 (en) | 2005-01-13 |
IL172815A0 (en) | 2006-06-11 |
EP1644657A1 (en) | 2006-04-12 |
US8631827B2 (en) | 2014-01-21 |
US20100313982A1 (en) | 2010-12-16 |
EA007421B1 (en) | 2006-10-27 |
US20060102239A1 (en) | 2006-05-18 |
EP1644657A4 (en) | 2010-06-09 |
KR20060037285A (en) | 2006-05-03 |
IL172815A (en) | 2011-08-31 |
CN1816713A (en) | 2006-08-09 |
US7802583B2 (en) | 2010-09-28 |
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