WO1999063283A1 - Apparatus for cooling fluid - Google Patents

Apparatus for cooling fluid Download PDF

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Publication number
WO1999063283A1
WO1999063283A1 PCT/GB1999/001695 GB9901695W WO9963283A1 WO 1999063283 A1 WO1999063283 A1 WO 1999063283A1 GB 9901695 W GB9901695 W GB 9901695W WO 9963283 A1 WO9963283 A1 WO 9963283A1
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WO
WIPO (PCT)
Prior art keywords
flow line
fluid
vortex
rotation
outlet
Prior art date
Application number
PCT/GB1999/001695
Other languages
French (fr)
Inventor
Alistair Mitchell
Peter Scott
Fraser Innes
Original Assignee
The Secretary Of State For Defence
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by The Secretary Of State For Defence filed Critical The Secretary Of State For Defence
Priority to AU42735/99A priority Critical patent/AU4273599A/en
Publication of WO1999063283A1 publication Critical patent/WO1999063283A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/02—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using Joule-Thompson effect; using vortex effect
    • F25B9/04—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using Joule-Thompson effect; using vortex effect using vortex effect
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/02—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust
    • F01N3/037—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of inertial or centrifugal separators, e.g. of cyclone type, optionally combined or associated with agglomerators
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • This invention relates to a low pressure apparatus for cooling fluids, particularly gases and especially exhaust gases and also to a device for collecting particulates from a fluid.
  • One known method of cooling a gas is to use the vortex tube effect.
  • a longitudinal vortex is formed within a larger vortex encouraging fluid flow in the opposite direction.
  • the fluid in the smaller vortex loses energy and is cooled whereas the outer vortex experiences an increase in temperature.
  • the overall effect on the central vortex is to produce a cooling effect.
  • vortex tubes require the outer vortex to be produced having a relatively large angular momentum which conventionally requires high pressure drivers. This is not practicable in all situations, for instance in use with engine exhaust gases as increased back pressure can prevent the engine from operating correctly.
  • a vortex tube that requires the use of a high pressure driver is disclosed in GB 1539950 which uses a compressor to induce the formation of a vortex. It is therefore an object of the present invention to produce a low pressure device for cooling fluid which is simple, inexpensive and robust.
  • an apparatus for cooling fluid comprising a first flow line having an inlet, a second flow line connected to the first flow line and an outlet from the second flow line wherein the first flow line is adapted so as to cause rotation of the fluid passing therethrough and being such that the radius of rotation in the vicinity of the inlet is substantially greater than the radius of rotation of the fluid at the end of the first flow line and wherein the second flow line acts as a vortex tube with the fluid coming from the first flow line being introduced into the second flow line to form an outer vortex and reflected from the end of the second flow line to form an inner vortex, the fluid from the inner vortex being fed to the outlet.
  • the fluid is fed into the first flow line and may be moving in a generally linear manner.
  • the first flow line causes a rotational motion which imparts an angular momentum to the fluid.
  • the radius of rotation of the fluid is reduced between the inlet - and the end of the first flow line. This means, due to the conservation of angular momentum, that the angular velocity of the fluid flow increases.
  • the fluid can achieve the necessary angular velocity for the vortex tube effect in the second flow line.
  • the first flow line is formed between inner and outer conical walls and the inlet introduces fluid tangentially.
  • the term "conical” shall be taken to include flared bell shapes as well as straight sided cones. Having a conical shape forces the fluid to move in a generally circular manner and move along the flow line with the attendant reduction in radius of rotation.
  • the inner and outer conical walls of the first flow line may incorporate flow guide vane structures to encourage the fluid to achieve the necessary angular velocity for the vortex tube effect in the second flow line.
  • a structure may, for example, take the form of a corkscrew shaped vane located between the inner and outer conical walls.
  • the second flow line comprises a straight tube having a constriction at one end and an orifice at the other.
  • the constriction at the end of the second flow line e.g. by the means of a valve, the temperature of the cooled fluid can be altered.
  • the second flow line is conveniently situated along the axis of rotation of the fluid passing through the first flow line as this eases the transfer of the fluid exiting the first flow line into the second flow line with the preservation of the angular velocity.
  • the second flow line can be located in line with the first flow line or alternatively the second flow line can be at least partly located within the inner walls of the first flow line in order to minimise the volume of the device.
  • the fluid exiting the first flow line may conveniently be directed into the second flow line by an annular reflector located at the end of the first flow line.
  • the fluid may then be easily turned around and fed into the second flow line whilst preserving the angular velocity of the fluid.
  • the return stream of the inner vortex of cooler fluid from the second flow line can then pass through the centre of the annular reflector and on to the outlet. It has been found that some reduction in the efficiency of the device may result where this latter arrangement is used but this may be acceptable where - the volume available for the device is limited. Where no limitation on size is needed it may therefore be preferable to adopt the alternative, first mentioned arrangement.
  • the second flow line may be connected to a drainage means to allow for drainage of any condensed liquid, e.g. water.
  • the increase in angular velocity caused by the reduction in the radius of rotation of the fluid also causes any particulates in the fluid to move toward the edge of the flow because of the centrifuge effect. These particulates could therefore be bled from the fluid at the end or the outer surface of the first flow line.
  • the device therefore preferably includes a means for separating the fluid at the periphery, such as a circumfrential slot leading to an outlet. Because of the pressure differential between the outlet, which may lead to the open air, and the end of the first flow line and the angular velocity of the fluid, the fluid around the periphery of the flowfield can be bled from the main flow.
  • a second aspect of the invention is therefore use of the device as a particulate trap and water condenser for exhaust gases.
  • a particulate trap and water condenser comprising a device according to the present invention will function at any temperature of exhaust gas as it relies on induced rotational velocity and not temperature. Further, the device will operate with any type of fuel and is robust, inexpensive and may be retro fittable. The device could be arranged to condense water from the exhaust gas ( by utilising the cold flow) which could then be simply drained away and also to capture the particulates in the exhaust. The particulates could be stored for periodic removal or alternatively could be fed back to the engine inlet manifold for re-combustion. The heated gas flow passed through the constriction could be circulated for some other use, say enhanced catalyst warm up.
  • Figure 1 shows a cross section of a device according to a first embodiment of the invention.
  • Figure 2 shows a cross section of a device according to a second embodiment of the invention.
  • Figure 1 shows a device suitable for use as a particulate trap and water condenser for an engine exhaust system.
  • the exhaust gases are introduced tangentially via an inlet 2 into a first flow line 4.
  • the first flow line 4 is formed between two flared bell shaped walls 6 & 8.
  • the exhaust gases are introduced tangentially to the first flow line where the generally linear motion is converted to circular motion. Due to the shape of the outer wall 6 and inner wall 8 the exhaust gases spiral away from the inlet 2.
  • the radius of rotation decreases, although the width of the flow line remains nominally the same, and therefore, due to conservation of angular momentum, the angular velocity of the rotating gas increases.
  • annular element 10 which has a shaped face to causes the exhaust gases to turn through 180° and into the tube 12, which provides the second flow line.
  • the annular element 10 directs the exhaust gases towards the periphery of tube 12 the flow causes a vortex to occur in that region of the tube.
  • Gases reflected from the end 14 of the tube form an inner vortex of gas travelling in the opposite direction and so a vortex tube arrangement is created, cooling the gas in the inner vortex and heating the gas in the outer vortex.
  • Valve 16, located at the end 14 of the tube 12 can be controlled to alter the degree of cooling of the inner vortex.
  • the cooling of the gas of the inner vortex can cause water vapour present in the exhaust gases to condense in the region of cap 18 by ducting cold gas to the surface of the first flowline 4.
  • a drain point 20 is located at the lowest point of the cap 18 to allow drainage of the condensed water.
  • the exhaust gases from the inner vortex of tube 12 then pass through the orifice formed by the annular element 10 and on through outlet 22. Not all the exhaust gases exiting the first flow line 4 are directed into tube 12.
  • the annular element extends slightly beyond the edges of outer wall 6 of the first flow line 4.
  • a pressure differential between the gases exiting the first flow line 4 and an outlet 24 causes the gases at the periphery of the flow field to be bled off through the cap 18 to outlet 24.
  • Outlet 24 may be provided with a valve (not shown) to control the extent of removal of gases from the periphery of the flow.
  • Figure 2 also shows a device suitable for use as a particulate trap and water condenser for an engine exhaust system. In Figure 2 like numerals are used to identify identical elements of the device to those shown in Figure 1.
  • the second flow line 42 is located in line with the first flow line 4.
  • the exhaust gases are once again introduced tangentially via an inlet 2 into a first flow line 4 which is formed between two bell shaped walls 6 and 8.
  • the shape of the walls causes the exhaust gases to spiral away from the inlet 2.
  • the process is enhanced by the presence of flow guide vanes 40 located between the outer wall 6 and the inner wall 8. As explained above the angular velocity of the rotating gas increases as the gases travel down the first flow line 4.
  • the rotating exhaust gases are then introduced into the peripheral region of the tube 42 (the second flow line) and a vortex tube arrangement is set up wherein an inner vortex of gas travelling in the opposite direction to the gases introduced into the peripheral region of the tube 42 is created (Note: the second flow line 42 and the first flow line 4 meet at the orifice 46 which is described hereinafter).
  • the vortex tube arrangement cools the gas in the inner vortex and heats the gas in the outer vortex.
  • Valve 116 located at the end 44 of the tube 42 can be controlled to alter the degree of cooling of the inner vortex.
  • the exhaust gases from the cool inner vortex of tube 42 then pass through an orifice 46 into a chamber 60 defined by a projection of inner wall 8 of the first flow line 4 (two such being shown in section in Figure 2) and on through to outlet 122.
  • Some of these gases are directed via a number of tubes 48 into a jacket 50 which cloaks the outer wall 6 of the first flow line 4.
  • the tubes 48 pass through the inner wall 8, across first flow line 4 and through the outer wall 6 and are streamlined to reduce the drag imposed on the gases in the first flow line 4.
  • the gases in the jacket 50 have the effect of cooling the incoming exhaust gases in the first flow line 4. This results in the condensation of water vapour present in the exhaust gases.
  • the jacket 50 contains a gas outlet 58.
  • the gases in the first flow line 4 have a relatively large angular velocity and so any condensed water vapour, particulates and the like are located in the gases at the periphery of the flow field, because of a centrifuge effect.
  • a small break 52 is incorporated in the wall 6 of the first flow line 4 so that the gases at the outer edges of the flow, and therefore most of the water vapour and/or particulates, can be extracted.
  • An extraction jacket 54 which contains an outlet 56, is placed around the break 52.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Processes For Solid Components From Exhaust (AREA)
  • Separating Particles In Gases By Inertia (AREA)

Abstract

A device for cooling fluid, for example exhaust gases, consisting of an inlet (2), two connected flow lines (4, 12) and an outlet (22). The first flow line (4) imparts a rotational motion to the fluid and gradually reduces the radius of rotation so as to generate enough rotational velocity to form a vortex tube arrangement in the second flow line (12) with inner and outer vortices being formed. The vortex tube arrangement in the second flow line (12) cools the fluid in the inner vortex which is then fed to the outlet (22).

Description

Apparatus for Cooling Fluid
This invention relates to a low pressure apparatus for cooling fluids, particularly gases and especially exhaust gases and also to a device for collecting particulates from a fluid.
It is sometimes wished to cool fluids, particularly exhaust gases or gases in turbines, for example to condense water etc. out of the gas or simply cool the gas to reduce overall temperature of an operating device.
One known method of cooling a gas is to use the vortex tube effect. Here a longitudinal vortex is formed within a larger vortex encouraging fluid flow in the opposite direction. The fluid in the smaller vortex loses energy and is cooled whereas the outer vortex experiences an increase in temperature. The overall effect on the central vortex is to produce a cooling effect.
However, vortex tubes require the outer vortex to be produced having a relatively large angular momentum which conventionally requires high pressure drivers. This is not practicable in all situations, for instance in use with engine exhaust gases as increased back pressure can prevent the engine from operating correctly. A vortex tube that requires the use of a high pressure driver is disclosed in GB 1539950 which uses a compressor to induce the formation of a vortex. It is therefore an object of the present invention to produce a low pressure device for cooling fluid which is simple, inexpensive and robust.
According to the present invention therefore is provided an apparatus for cooling fluid comprising a first flow line having an inlet, a second flow line connected to the first flow line and an outlet from the second flow line wherein the first flow line is adapted so as to cause rotation of the fluid passing therethrough and being such that the radius of rotation in the vicinity of the inlet is substantially greater than the radius of rotation of the fluid at the end of the first flow line and wherein the second flow line acts as a vortex tube with the fluid coming from the first flow line being introduced into the second flow line to form an outer vortex and reflected from the end of the second flow line to form an inner vortex, the fluid from the inner vortex being fed to the outlet.
The fluid is fed into the first flow line and may be moving in a generally linear manner. The first flow line causes a rotational motion which imparts an angular momentum to the fluid. The radius of rotation of the fluid is reduced between the inlet - and the end of the first flow line. This means, due to the conservation of angular momentum, that the angular velocity of the fluid flow increases. Thus, with a relatively small pressure at the inlet the fluid can achieve the necessary angular velocity for the vortex tube effect in the second flow line.
Preferably the first flow line is formed between inner and outer conical walls and the inlet introduces fluid tangentially. As used herein the term "conical" shall be taken to include flared bell shapes as well as straight sided cones. Having a conical shape forces the fluid to move in a generally circular manner and move along the flow line with the attendant reduction in radius of rotation.
Conveniently the inner and outer conical walls of the first flow line may incorporate flow guide vane structures to encourage the fluid to achieve the necessary angular velocity for the vortex tube effect in the second flow line. Such a structure may, for example, take the form of a corkscrew shaped vane located between the inner and outer conical walls.
Conveniently the second flow line comprises a straight tube having a constriction at one end and an orifice at the other. By adjusting the constriction at the end of the second flow line, e.g. by the means of a valve, the temperature of the cooled fluid can be altered. The second flow line is conveniently situated along the axis of rotation of the fluid passing through the first flow line as this eases the transfer of the fluid exiting the first flow line into the second flow line with the preservation of the angular velocity. Either the second flow line can be located in line with the first flow line or alternatively the second flow line can be at least partly located within the inner walls of the first flow line in order to minimise the volume of the device.
In the latter arrangement, the fluid exiting the first flow line may conveniently be directed into the second flow line by an annular reflector located at the end of the first flow line. The fluid may then be easily turned around and fed into the second flow line whilst preserving the angular velocity of the fluid. The return stream of the inner vortex of cooler fluid from the second flow line can then pass through the centre of the annular reflector and on to the outlet. It has been found that some reduction in the efficiency of the device may result where this latter arrangement is used but this may be acceptable where - the volume available for the device is limited. Where no limitation on size is needed it may therefore be preferable to adopt the alternative, first mentioned arrangement.
The second flow line may be connected to a drainage means to allow for drainage of any condensed liquid, e.g. water.
The increase in angular velocity caused by the reduction in the radius of rotation of the fluid also causes any particulates in the fluid to move toward the edge of the flow because of the centrifuge effect. These particulates could therefore be bled from the fluid at the end or the outer surface of the first flow line. The device therefore preferably includes a means for separating the fluid at the periphery, such as a circumfrential slot leading to an outlet. Because of the pressure differential between the outlet, which may lead to the open air, and the end of the first flow line and the angular velocity of the fluid, the fluid around the periphery of the flowfield can be bled from the main flow. A second aspect of the invention is therefore use of the device as a particulate trap and water condenser for exhaust gases.
It is desired to remove particulates from exhaust gases to reduce pollution. Usual methods rely on catalysts or traps, however at low speeds the lower exhaust gas temperatures may be too low to allow the devices to function correctly. Further, for military vehicles and the like, the fuel types used in a vehicle may contain elements which would destroy a catalytic converter.
Also in the military sphere reducing the particulates and water present in exhaust gases reduces the thermal signature of the vehicle.
A particulate trap and water condenser comprising a device according to the present invention will function at any temperature of exhaust gas as it relies on induced rotational velocity and not temperature. Further, the device will operate with any type of fuel and is robust, inexpensive and may be retro fittable. The device could be arranged to condense water from the exhaust gas ( by utilising the cold flow) which could then be simply drained away and also to capture the particulates in the exhaust. The particulates could be stored for periodic removal or alternatively could be fed back to the engine inlet manifold for re-combustion. The heated gas flow passed through the constriction could be circulated for some other use, say enhanced catalyst warm up.
The invention will now be described by way of example only with reference to the accompanying drawings of which; Figure 1 shows a cross section of a device according to a first embodiment of the invention.
Figure 2 shows a cross section of a device according to a second embodiment of the invention.
Figure 1 shows a device suitable for use as a particulate trap and water condenser for an engine exhaust system. The exhaust gases are introduced tangentially via an inlet 2 into a first flow line 4. The first flow line 4 is formed between two flared bell shaped walls 6 & 8. The exhaust gases are introduced tangentially to the first flow line where the generally linear motion is converted to circular motion. Due to the shape of the outer wall 6 and inner wall 8 the exhaust gases spiral away from the inlet 2. As the gases travel down first flow line 4 the radius of rotation decreases, although the width of the flow line remains nominally the same, and therefore, due to conservation of angular momentum, the angular velocity of the rotating gas increases.
At the end of the first flow line 4 is an annular element 10 which has a shaped face to causes the exhaust gases to turn through 180° and into the tube 12, which provides the second flow line. As the annular element 10 directs the exhaust gases towards the periphery of tube 12 the flow causes a vortex to occur in that region of the tube. Gases reflected from the end 14 of the tube form an inner vortex of gas travelling in the opposite direction and so a vortex tube arrangement is created, cooling the gas in the inner vortex and heating the gas in the outer vortex. Valve 16, located at the end 14 of the tube 12 can be controlled to alter the degree of cooling of the inner vortex.
The cooling of the gas of the inner vortex can cause water vapour present in the exhaust gases to condense in the region of cap 18 by ducting cold gas to the surface of the first flowline 4. A drain point 20 is located at the lowest point of the cap 18 to allow drainage of the condensed water. The exhaust gases from the inner vortex of tube 12 then pass through the orifice formed by the annular element 10 and on through outlet 22. Not all the exhaust gases exiting the first flow line 4 are directed into tube 12. The annular element extends slightly beyond the edges of outer wall 6 of the first flow line 4. A pressure differential between the gases exiting the first flow line 4 and an outlet 24 causes the gases at the periphery of the flow field to be bled off through the cap 18 to outlet 24. Outlet 24 may be provided with a valve (not shown) to control the extent of removal of gases from the periphery of the flow.
As the gases will have a relatively large angular velocity when exiting the first flow line 4 any particulates and the like will be located in the gases at the periphery of the flow field, because of a centrifuge effect. Therefore, removing the gases at the outer edges of the flow removes most of the particulates from the exhaust. These separated gases could then be directed to deposit the particulates in a suitable container for periodic emptying or alternatively they could be returned to the engine inlet manifold for re-combustion. Figure 2 also shows a device suitable for use as a particulate trap and water condenser for an engine exhaust system. In Figure 2 like numerals are used to identify identical elements of the device to those shown in Figure 1. In this second embodiment of the invention the second flow line 42 is located in line with the first flow line 4. The exhaust gases are once again introduced tangentially via an inlet 2 into a first flow line 4 which is formed between two bell shaped walls 6 and 8. As described in the first embodiment, the shape of the walls causes the exhaust gases to spiral away from the inlet 2. However, in this embodiment the process is enhanced by the presence of flow guide vanes 40 located between the outer wall 6 and the inner wall 8. As explained above the angular velocity of the rotating gas increases as the gases travel down the first flow line 4.
The rotating exhaust gases are then introduced into the peripheral region of the tube 42 (the second flow line) and a vortex tube arrangement is set up wherein an inner vortex of gas travelling in the opposite direction to the gases introduced into the peripheral region of the tube 42 is created (Note: the second flow line 42 and the first flow line 4 meet at the orifice 46 which is described hereinafter). As before, the vortex tube arrangement cools the gas in the inner vortex and heats the gas in the outer vortex. Valve 116 located at the end 44 of the tube 42 can be controlled to alter the degree of cooling of the inner vortex. The exhaust gases from the cool inner vortex of tube 42 then pass through an orifice 46 into a chamber 60 defined by a projection of inner wall 8 of the first flow line 4 (two such being shown in section in Figure 2) and on through to outlet 122. However, not all the cool gases passing through the orifice 46 pass through to the outlet 122. Some of these gases are directed via a number of tubes 48 into a jacket 50 which cloaks the outer wall 6 of the first flow line 4. The tubes 48 pass through the inner wall 8, across first flow line 4 and through the outer wall 6 and are streamlined to reduce the drag imposed on the gases in the first flow line 4. The gases in the jacket 50 have the effect of cooling the incoming exhaust gases in the first flow line 4. This results in the condensation of water vapour present in the exhaust gases. The jacket 50 contains a gas outlet 58.
As described above, the gases in the first flow line 4 have a relatively large angular velocity and so any condensed water vapour, particulates and the like are located in the gases at the periphery of the flow field, because of a centrifuge effect. In this embodiment a small break 52 is incorporated in the wall 6 of the first flow line 4 so that the gases at the outer edges of the flow, and therefore most of the water vapour and/or particulates, can be extracted. An extraction jacket 54, which contains an outlet 56, is placed around the break 52.
Alternative arrangements for directing cooling gases and/or removing condensed water vapour and particulates or the like will be readily apparent to the skilled person and shall be understood as not being limited to the specific arrangements described herein.

Claims

1. An apparatus for cooling fluid comprising a first flow line having an inlet, a second flow line connected to the first flow line and an outlet from the second flow line wherein the first flow line is adapted so as to cause rotation of a fluid passing therethrough and being such that the radius of rotation of the fluid in the vicinity of the inlet is substantially greater than the radius of rotation of the fluid at the end of the first flow line and wherein the second flow line acts as a vortex tube with the fluid coming from the first flow line being introduced into the second flow line to form an outer vortex and reflected from the end of the second flow line to form an inner vortex, the fluid from the inner vortex being fed to the outlet.
2. An apparatus as claimed in claim 1 wherein the first flow line is bounded by inner and outer conical walls.
3. An apparatus as claimed in claim 2 wherein the first flow line incorporates structures to encourage the rotation of a fluid passing therethrough.
4. An apparatus as claimed in claim 3 wherein said structure comprises a corkscrew- shaped vane.
5. An apparatus as claimed in any preceding claim wherein the second flow line comprises a straight tube having a constriction at one end.
6. An apparatus as claimed in any preceding claim wherein the second flow line is situated along the axis of rotation of the fluid passing through the first flow line.
7. An apparatus as claimed in any preceding claim wherein the second flow line is in line with and outside of the first flow line.
8. An apparatus as claimed in claims 2 to 6 wherein the second flow line lies at least ~ partly within the inner walls of the first flow line.
9. An apparatus as claimed in claim 8 further comprising an annular reflector to direct fluid exiting the first flow line into the second flow line.
10. An apparatus as claimed in any preceding claim wherein the end of the second flow line in the vicinity of the outlet is connected to a drainage means for draining off water condensed in the apparatus.
11. An apparatus as claimed in any preceding claim further comprising a means for separating off the fluid at the periphery of the flowfield at the end of the first flow line.
12. A water condenser for an engine exhaust comprising an apparatus according to claim 10.
13. A particulate trap for an engine exhaust comprising an apparatus according to claim 11.
14. An apparatus as hereinbefore described with reference to the accompanying drawings.
PCT/GB1999/001695 1998-06-03 1999-05-27 Apparatus for cooling fluid WO1999063283A1 (en)

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Application Number Priority Date Filing Date Title
AU42735/99A AU4273599A (en) 1998-06-03 1999-05-27 Apparatus for cooling fluid

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GBGB9811882.1A GB9811882D0 (en) 1998-06-03 1998-06-03 Apparatus for cooling fluid
GB9811882.1 1998-06-03

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7665955B2 (en) 2006-08-17 2010-02-23 Siemens Energy, Inc. Vortex cooled turbine blade outer air seal for a turbine engine

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US2788647A (en) * 1949-11-14 1957-04-16 Garrett Corp Gaseous fluid cooling device
US2971342A (en) * 1958-01-06 1961-02-14 David W Pilcher Apparatus for simultaneously reducing the pressure, dehydrating and separating fluid flow
US3786643A (en) * 1973-01-02 1974-01-22 Owatonna Tool Co Vortex tube
US3815375A (en) * 1973-07-06 1974-06-11 Vortec Corp Pressure regulating refrigerative air dryer system
US3861142A (en) * 1973-02-05 1975-01-21 Ranendra K Bose Anti-pollution systems for automobiles
GB1539950A (en) 1976-06-25 1979-02-07 Sohre J Thermodynamic energy conversion device
US4235845A (en) * 1979-01-02 1980-11-25 Bose Ranendra K Anti-air pollution system for exhaust gas
GB2215645A (en) * 1988-03-17 1989-09-27 Ford Motor Co Separator for IC engine exhaust system
US5685143A (en) * 1992-10-30 1997-11-11 Kat-Tecnik Oy Catalytic exhaust gas purifier and catalytic method of purifying exhaust gas

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2788647A (en) * 1949-11-14 1957-04-16 Garrett Corp Gaseous fluid cooling device
DE858260C (en) * 1951-08-24 1952-12-04 Andreas Hofer Hochdruck Appbau Process for improving and applying the vortex tube effect
US2971342A (en) * 1958-01-06 1961-02-14 David W Pilcher Apparatus for simultaneously reducing the pressure, dehydrating and separating fluid flow
US3786643A (en) * 1973-01-02 1974-01-22 Owatonna Tool Co Vortex tube
US3861142A (en) * 1973-02-05 1975-01-21 Ranendra K Bose Anti-pollution systems for automobiles
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AU4273599A (en) 1999-12-20
GB9811882D0 (en) 1998-07-29

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