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WO2011062958A2 - Échangeur de chaleur ayant un tube à vortex pour applications à écoulement d'air commandé - Google Patents

Échangeur de chaleur ayant un tube à vortex pour applications à écoulement d'air commandé Download PDF

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Publication number
WO2011062958A2
WO2011062958A2 PCT/US2010/056980 US2010056980W WO2011062958A2 WO 2011062958 A2 WO2011062958 A2 WO 2011062958A2 US 2010056980 W US2010056980 W US 2010056980W WO 2011062958 A2 WO2011062958 A2 WO 2011062958A2
Authority
WO
WIPO (PCT)
Prior art keywords
tube
fluid
stream
inner tube
backpressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US2010/056980
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English (en)
Other versions
WO2011062958A3 (fr
Inventor
Hieyoung William Oh
Steven Edward Broerman
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Illinois Tool Works Inc
Original Assignee
Illinois Tool Works Inc
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 Illinois Tool Works Inc filed Critical Illinois Tool Works Inc
Priority to EP10782140A priority Critical patent/EP2504638A2/fr
Priority to CN201080052974.4A priority patent/CN102667369B/zh
Publication of WO2011062958A2 publication Critical patent/WO2011062958A2/fr
Publication of WO2011062958A3 publication Critical patent/WO2011062958A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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

Definitions

  • the present invention relates generally to controlled airflow devices and, more particularly, to a heat exchanger device having a vortex tube for controlled airflow applications.
  • Certain applications require a small amount of cold or hot air that must be delivered through small diameter restrictive tubing or hose, (e.g. tubing with an inner diameter of less than 10 millimeters, and preferably, less than 3 millimeters), sometimes because of the constricted space that the tubing must be routed through.
  • small diameter restrictive tubing or hose e.g. tubing with an inner diameter of less than 10 millimeters, and preferably, less than 3 millimeters
  • These applications are widespread and can vary from aerospace to electronics to medical uses as well as others.
  • These applications normally may only require a small amount of cooling or heating capacity, normally no greater than 150 BTUH (44 watts).
  • refrigeration-based air conditioning systems One conventional method to deliver cold airflows is refrigeration-based air conditioning systems.
  • these refrigeration-based units are designed to deliver relatively large airflows through large ducts or passages. Because of this, they are designed so that the cold airflow can be moved with a fan or blower; the fan or blower can overcome the low ducting resistances of the relatively large passages.
  • Application of these conventional refrigeration systems for providing cold airflows through small sized passages or tubing is not ideal because the fans and blowers used to convey the cold air cannot overcome the resistance of the small passages.
  • the refrigeration system can be designed or retrofitted with higher pressure blowers or fans to overcome the ducting resistance, but these blowers are intended for delivering large volume airflows, not airflows on the order of less than 2 or 3 cubic feet per minute (0.000944 m 3 /s or 0.00142 m 3 /s).
  • these conventional refrigeration systems typically range from 350 to 12,000 BTUH (102.57 Watts to 3,516.85 Watts) cooling capacity, even the smallest known units are considered oversized for most applications.
  • a heat exchanger device includes, but is not limited to, a vortex tube and a hollow tube.
  • the vortex tube includes, but is not limited to, a fluid supply tube connected with a swirl chamber, an inlet of a first inner tube connected with an outlet of the swirl chamber and an inlet of a second inner tube connected with the outlet of the swirl chamber, an internal heat exchanger, wherein an inlet of the internal heat exchanger is connected with an outlet of the first inner tube, and a nozzle connected with the outlet of the first inner tube and the inlet of the internal heat exchanger.
  • the hollow tube is connected with an inlet of the nozzle.
  • a method for heating or cooling includes, but is not limited to, supplying fluid into a vortex tube, the vortex tube having a first inner tube connected with a swirl chamber and an outer backpressure tube surrounding the first inner tube.
  • the method further includes, but is not limited to, dividing the fluid into first and second streams of fluid, flowing the first stream of fluid through the first inner tube, and flowing a first portion of the first stream of fluid through a nozzle connected with the first inner tube.
  • the method further includes, but is not limited to, flowing a second portion of the first stream of fluid through the outer backpressure tube.
  • a device for heating or cooling a site includes, but is not limited to, a swirl chamber for receiving and separating a fluid into first and second streams, a first inner tube connected with an outlet of the swirl chamber, a backpressure tube, and a nozzle.
  • the backpressure tube has an inlet.
  • the inlet of the outer backpressure tube is connected with an outlet of the first inner tube.
  • the nozzle is connected with the outlet of the first inner tube and the inlet of the backpressure tube.
  • FIG. 1 A depicts a side view of a heat exchanger including a vortex tube connected with a small diameter tube having an adjustment valve at the vortex tube, in accordance with one preferred embodiment.
  • FIG. IB depicts an end view taken along line A- A of the vortex tube for the heat exchanger shown in FIG. 1A, in accordance with one preferred embodiment.
  • FIG. 2A depicts an insulating sleeve assembly of the vortex tube for the heat exchanger shown in FIG. 1A, in accordance with one preferred embodiment.
  • the insulating sleeve assembly is made of a thermally insulating material (plastic, ceramic, etc.) whose purpose is to insulate an external sleeve 112 from cold or hot exhaust flow 154.
  • FIG. 2B depicts an exploded top view of the insulating sleeve assembly of the vortex tube for the heat exchanger shown in FIG. 2A, in accordance with one preferred embodiment.
  • Insulating sleeves 113 and 115 fit together to form a continuous insulating sleeve inside external sleeve 112.
  • FIG. 2C depicts a partial cross-sectional side view taken along line G-G of the heat exchanger shown in FIG. IB, in accordance with one preferred embodiment.
  • FIG. 2D depicts a first end view taken along line B-B of the vortex tube for the heat exchanger shown in FIG. 1A, in accordance with one preferred embodiment.
  • FIG. 2E depicts a cross-sectional view taken along line J-J of the vortex tube for the heat exchanger shown in FIG. 2C, in accordance with one preferred embodiment.
  • FIG. 2F depicts a cross-sectional view taken along line C-C of the vortex tube for the heat exchanger shown in FIG. 2C, in accordance with one preferred embodiment.
  • FIG. 2G depicts a cross-sectional view taken along line D-D of the vortex tube for the heat exchanger shown in FIG. 2C, in accordance with one preferred embodiment.
  • FIG. 2H depicts a cross-sectional view taken along line K-K of the vortex tube for the heat exchanger shown in FIG. 2C, in accordance with one preferred embodiment.
  • FIG. 21 depicts a cross-sectional view taken along line F-F of the vortex tube for the heat exchanger shown in FIG. 2C, in accordance with one preferred embodiment.
  • FIG. 2J depicts a second end view taken along line L-L of the vortex tube for the heat exchanger shown in FIG. 2C, in accordance with one preferred embodiment.
  • FIG. 3 depicts an enlarged partial cross-sectional side view taken along line G-G of the heat exchanger shown in FIG. IB, in accordance with one preferred embodiment.
  • Methods and devices consistent with the present invention overcome the disadvantages of conventional cooling and heating systems by using a vortex tube which has a means for reducing backpressure produced when fluid flows through small diameter restrictive tubing, maximizing the efficiency of the vortex tube heat exchanger.
  • FIGS. 1-3 there is shown various embodiments of a heat exchanger device 100 for cooling applications consistent with the present invention. Alternately a vortex tube 110 of the heat exchanger device 100 may be reversed for heating
  • heat exchanger device 100 includes a vortex tube 110 connected via with a small diameter restrictive tube 180 via a first inner tube 142.
  • Small diameter restrictive tube 180 is a hollow tube having a diameter D 2 preferably of less than 10 millimeters, and more preferably, less than 5 millimeters, and most preferably less than 3 millimeters.
  • the small diameter restrictive tube 180 has a diameter D 2 of approximately 2.413 millimeters +0.5 millimeters.
  • small diameter restrictive tube 180 is a cannula which is used for insertion into a mammalian subject. Methods and systems consistent with the present invention take all of the above concerns into account in order to maximize the efficiency of the vortex tube 110.
  • vortex tube 110 includes fluid supply tube 120 connected with inlet 123 of vortex tube 110, a swirl chamber 140 connected with the fluid supply tube 120, a first inner tube 142 and second inner tube 160, preferably for hot fluids, connected with the swirl chamber 140, a backpressure tube 150 connected with the first inner tube 142, and a nozzle 144 connected with an outlet 124 of the first inner tube 142.
  • Vortex tube 110 receives a fluid 104 through the fluid supply tube 120, and separates fluid 104 into first and second streams 106, 108 of fluid 104 traveling down first and second inner tubes 142, 160, respectively.
  • the fluid 104 is received at an ambient temperature from 15°C to 30°C, and more preferably about 21.1°C + 5°C.
  • the first stream 106 is a cold stream of fluid 104 and the second stream 108 is a hot stream of fluid 104.
  • the second stream 108 is a cold stream of fluid 104 and the first stream 106 is a hot stream of fluid 104.
  • a cold stream of fluid 104 has an average temperature of less than 5°C, more preferably less than 0°C, more preferably less than -5°C, and most preferably less than -10°C.
  • a hot stream of fluid 104 has an average temperature of more than 60°C, more preferably more than 65 °C, more preferably more than 70°C, and most preferably more than 80°C.
  • Fluid 104 is any material in gaseous form.
  • fluid 104 is a compressed gas, such as compressed air.
  • Vortex tube 110 may be used for controlled airflow applications.
  • vortex tube 110 can deliver cold airflows from zero to 100 cubic feet/minute (CFM) (zero to 2.832 cubic meters/minute), using only compressed air as a power source.
  • a smaller vortex tube 110 can create cooling capacities up to 400 BTUH (117 Watts) using no more than 8 standard cubic feet/minute (SCFM) (0.22656 cubic meters/minute) of compressed air.
  • Vortex tube 110 performs most efficiently when first fluid stream 106 is exhausted from the vortex tube 110 and into small diameter restrictive tube 180 at atmospheric pressure with no resistance to flow. Vortex tube 110 can still perform well with slight resistance or backpressure on the first fluid stream 106.
  • the resistances created by the small diameter restrictive tube 180 into which the first fluid stream 106 flows can create a backpressure which exceeds 19.7 psia (34.5 kPa) at an outlet 124 of the first inner tube 142 of the vortex tube 110, where the first fluid stream 106 flows into the tube 180.
  • vortex tube 110 Because the performance of vortex tube 110 is directly related to the absolute pressure differential between the pressure of the fluid 104 at an inlet 123 and the pressure of the fluid 104 in first stream 106 at the outlet 124, a 19.7 psia (34.5 kPa) resistance or backpressure can severely limit the performance of the vortex tube 110.
  • the pressure of the fluid 104 at the inlet 123 of the vortex tube 110 could be as little as 54.7 psia (377.1kPa) and the pressure of the fluid 104, and particularly first stream 106 of fluid 104, at the outlet 124 could be that of air directed to atmosphere, or 14.7 psia (101.325 kPa).
  • the desired pressure at the inlet 123 is 104.7 to 114.7 psia (721.9 kPa to 790.8 kPa) and desired pressure at the outlet 124 is 14.7 psia (101.325 kPa).
  • the pressure drop ratio becomes as little as
  • one object of this invention is to keep the pressure drop ratio as high as possible, and preferably greater than 4.00: 1, and more preferably, greater than 5.00: 1, and most preferably, greater than 7.00: 1.
  • Vortex tube 110 is most efficient when operated in a 60 to 70% cold/heat fraction range. This means that an 8 SCFM (0.22656 cubic meters/minute) vortex tube 110 is most efficient in creating the most cooling capacity (BTUH) when there is 60 to 70% of this 8 SCFM (0.22656 cubic meters/minute) of fluid 104 exiting out the outlet 124 of first inner tube 142. Even when operated in this cold/heat fraction range and at reasonable pressure drop ratios (e.g. pressure drop ratios of greater than greater than 4.00: 1), very cold or very hot air temperatures (e.g. less than -5°C or greater than 65 °C, respectively) are achievable.
  • pressure drop ratios e.g. pressure drop ratios of greater than greater than 4.00: 1
  • very cold or very hot air temperatures e.g. less than -5°C or greater than 65 °C, respectively
  • length L 3 of small diameter restrictive tube 180 connected with outlet 124 of the vortex tube 110 can be quite long in length (for example, greater than 1 meter, and more preferably greater than two meters, and in one example up to up to 3.04 meters), for various reasons.
  • the application may require that cold or hot fluid 104 be present at an outlet 184 of the small diameter restrictive tube 180 in a short time period (e.g. no longer than 5 minutes).
  • the length L 3 , diameter D 2 , wall thickness, and material of small diameter restrictive tube 180 determines its thermal mass. Because the cooling capacity of the driving vortex tube 110 can be limited (e.g.
  • the thermal mass of the small diameter restrictive tube 180 must be kept to a minimum, to allow quick realization of the cold or hot temperature of the fluid 104 at the outlet 184 of the small diameter restrictive tube 180.
  • the small diameter restrictive tube 180 can be pre-cooled or cooled concurrently via a heat exchanger to allow un-delayed cold (or hot) temperatures of fluid 104 at the outlet 184 in order to minimize any "thermal lag".
  • Fluid supply tube 120 is connected with inlet 123 of vortex tube 110 and supplies fluid 104 to vortex tube 110 at inlet 123.
  • supply tube 120 is movably connected with inlet 123 using a swiveling elbow-shaped member 122, allowing for the fluid supply tube 120 to be rotated about inlet 123.
  • Inlet 123 is connected with an entry channel 118 which leads into the vortex tube 110, and specifically into the swirl chamber 140.
  • fluid supply tube 120 may be routed inside the external sleeve 112 and then out the back of the vortex tube 110 through exhaust cover 171.
  • Fluid 104 enters swirl chamber 140, and is separated by swirl chamber 140 into first and second streams 106, 108 of fluid 104 traveling down first and second inner tubes 142, 160, respectively.
  • first stream 106 is a cold stream of fluid 104 and the second stream 108 is a hot stream of fluid 104.
  • the second stream 108 is a cold stream of fluid 104 and the first stream 106 is a hot stream of fluid 104.
  • An inlet 141 of the first inner tube 142 is connected with a first outlet 139 of the swirl chamber 140, and an inlet 161 of the second inner tube 160 is connected with a second outlet 143 of the swirl chamber 140.
  • each stream 106, 108 is then guided down its respective inner tube 142, 160.
  • First inner tube 142 allows for the first stream 106 of fluid 104 to flow from the swirl chamber to nozzle 144.
  • Outlet 124 of first inner tube 142 is connected with nozzle 144 and backpressure tube 150.
  • Nozzle 144 is sized so as not to allow all of the first stream 106 of fluid 104 to flow through nozzle 144 without an increase in pressure, or without forming any backpressure in first stream 106.
  • an inlet of the nozzle 144 is smaller than outlet 124 of the first inner tube 142 and is capable of creating backpressure in the first stream 106.
  • the vortex tube 110 includes backpressure tube 150 which is designed to take in any excess fluid 104 which cannot freely flow through nozzle 144.
  • backpressure tube 150 is able to relieve backpressure in first stream 106 that may be caused as fluid 104 flows through nozzle 144, helping maximize the efficiency of the vortex tube 110.
  • the backpressure tube 150 in addition to relieving any backpressure in first stream 106, can be configured as an internal heat exchanger 148 to transfer cold/heat to the first inner tube 142 and/or the second inner tube 160.
  • backpressure tube 150 can take several forms, such as an outer backpressure tube which surrounds the inner tubes 142, 160, a coiled tube surrounding inner tubes 142, 160, a plate type device connected with inner tubes 142, 160, a shell and tube type, and a finned tube connected with inner tubes 142, 160.
  • a shell and tube type heat exchanger includes several small tubes enclosed in a larger shell.
  • the backpressure tube 150 is an outer backpressure tube which preferably surrounds at least a portion of the first inner tube 142.
  • the backpressure tube 150 comprises a material which has a thermal conductivity of less than 10 Watts per meter Kelvin and the inner tubes 142, 160 have a thermal conductivity of greater than 10 Watts per meter Kelvin.
  • the inner tubes 142, 160 have a thermal conductivity of greater than 10 Watts per meter Kelvin.
  • the backpressure tube 150 is an outer backpressure tube which comprises a material which has a thermal conductivity of less than 10 Watts per meter Kelvin and the inner tubes 142, 160 have a thermal conductivity of greater than 10 Watts per meter Kelvin.
  • Second inner tube 160 allows for the second stream 108 of fluid 104 to flow from the swirl chamber 140 to an exhaust chamber 170.
  • the second stream 108 of fluid 104 mixes with a second portion 154 of the first stream 106 of fluid 104.
  • the combined streams of fluid 104 are then exhausted from the vortex tube 110 through exhaust holes 172 formed in an exhaust cover 171 which caps the exhaust chamber 170.
  • the temperature of the combined streams of fluid 104 which are exhausted from the vortex tube 110 can be controlled by controlling the amount of the second portion 154 which enters the exhaust chamber 170, using means such as a flow control mechanism 130.
  • Second inner tube 160 allows for the second stream 108 of fluid 104 to flow from the swirl chamber 140 out through the vortex tube 110 via a valve or orifice 165.
  • the adjustable valve or fixed orifice 165 allows the vortex tube 110 to be adjusted, in the field with the case of the adjustable valve or at the factory in the case of the fixed orifice, to maintain an optimum cold fraction of 60% to 70%.
  • Flow control mechanism 130 is any device which can vary the flow of fluid 104 through a tube or channel, and includes things such as a valve.
  • the flow control mechanism 130 includes an inner flow control ring 132 having openings 133 through which second portion 154 of first stream 106 flows through, and an outer flow control ring 134 having openings 135 through which second portion 154 of first stream 106 flows through.
  • one of the rings 132, 134 is fixed while the other ring 132, 134 is movable, in order to create a configuration in which the size of the openings 133 can be varied and therefore the flow of the second portion 154 of first stream 106 can be varied as well.
  • the flow control mechanism 130 is for regulating an amount of fluid 104 allowed to flow through the backpressure tube 150, and in turn regulating an amount of fluid 104 able to flow through the nozzle 144 and into the small diameter restrictive tube 180.
  • a compression spring 137 can be placed between body 191 of the vortex tube 110 and the outer flow control ring 134. This compression spring 137 serves to prevent gaps and air leakage between outer flow control ring 134 and inner flow control ring 132.
  • fluid 104 such as compressed air
  • the vortex tube 110 is set at a fixed cold/heat fraction of preferably from 50% to 90%, and more preferably from 60% to 80%, and most preferably, from 60% to 70%.
  • cold/heat fraction refers to the percentage of the total flow of fluid 104 through the vortex tube 110 which exists from inner tube 142 as a cold/hot stream of fluid 104.
  • the vortex tube 110 divides the fluid 104 into first and second streams 106, 108 of fluid 104.
  • the first stream 106 is a fraction of fluid 104 equal to the fixed cold/heat fraction.
  • First stream 106 flows down the first inner tube 142 and exits outlet 124 of first inner tube 142.
  • a first portion 152 of the first stream 106 enters the nozzle 144, while a second portion 154 of the first stream 106 enters and flows down the backpressure tube 150.
  • the first inner tube 142 is ideally sized to not create a flow restriction of the first stream 106, but not so large as to add unnecessary thermal mass to the backpressure tube 150.
  • the first inner tube 142 is preferably constructed of a material that has a high thermal conductivity, for example, a thermal conductivity greater than 10 Watts per meter Kelvin.
  • Backpressure tube 150 is sized so as not to create a flow restriction to the second portion 154 but also not so large to prevent unnecessary thermal mass.
  • the backpressure tube 150 is constructed of a material that has a low thermal conductivity, for example, a thermal conductivity of less than 10 Watts per meter Kelvin.
  • the second portion 154 of the first stream 106 that passes back over the inner tube 142 and enters the backpressure tube 150 is also known as an exhaust flow.
  • the second portion 154 serves to keep the first stream 106 traveling through the first inner tube 142 either cool or warm, depending on the application and the configuration of the vortex tube 110.
  • This second portion 154 can either be adjusted by the user or fixed to create a certain heat exchange rate. If adjustable, the flow of the second portion 154 can be adjusted via flow control mechanism 130, such as a valve, at either end of the backpressure tube 150.
  • the first portion 152 which is not directed back through the backpressure tube 150 and which flows through the nozzle 144 may also be referred to as the application flow.
  • the first portion 152 is the portion of the first stream 106 that is directed to the point of use or application site 102.
  • adjustment of the flow of the second portion 154 through the backpressure tube 150 via flow control mechanism 130 also adjusts the flow of the first portion 152 flowing through the nozzle 144 to the application site 102.
  • This second portion 154 is the cold/hot exhaust flow and keeps the cold/hot fraction from gaining or losing heat in the first inner tube 142.
  • the remaining 0.53 CFM of fluid 104 is directed to the application site 102 and is called the application flow.
  • the cold/hot exhaust fraction in second stream 108 from the vortex tube 110 in this example is 3.23 CFM.
  • the second portion 154 of the first stream 106 of fluid 104 is routed in a counterflow direction (opposite that of the direction of flow of the first stream 106) back through the backpressure tube 150 to either keep the cold stream of fluid 104 in first inner tube 142 from gaining heat or keep the hot stream of fluid 104 in first inner tube 142 from losing heat, and the remaining portion 152 of the first stream 106 of fluid 104 is directed to the application site 102.
  • the first portion 152, the application flow is therefore kept as cold or hot as possible as it reaches the application site 102, prolonging its cooling or heating capacity.
  • Insulated exhaust chamber 190 is formed by two insulated plastic sleeves 113 and 115. Sleeves 113 and 115 fit tightly around body 191 of vortex tube 110 and insulate the exterior sleeve 112 from cold or hot flow in second portion 154. Insulating the exterior sleeve 112 is important as this allows vortex tube 110 to be a hand-held device and provides comfort to a user of the vortex tube 110 when held by a hand.
  • the hot/cold exhaust flow 108 passes through a muffler 199.
  • Muffler 199 serves to keep exhaust flow 108 quiet in order to reduce noise for a user handling the vortex tube 110.
  • Muffler 199 can be made of any porous noise reducing material, and preferably, a porous plastic material. Muffler 199 must be porous enough so as not to create a backpressure on exhaust flow 108.
  • exhaust flows 154 and 108 mix in chamber 200
  • the hot and cold temperatures of exhaust flows 154 and 108 tend to cancel each other out, resulting in an exhaust temperature preferably of about 21 °C +5°C.
  • the exhaust temperature is preferably not objectionable to a user of the vortex tube 110.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Jet Pumps And Other Pumps (AREA)

Abstract

L'invention porte sur un dispositif échangeur de chaleur. Le dispositif comprend, entre autres, un tube à vortex et un tube creux. Le tube à vortex comprend, entre autres, un tube d'arrivée de fluide relié à une chambre à tourbillon, une entrée d'un premier tube intérieur reliée à une sortie de la chambre à tourbillon et une entrée d'un second tube intérieur reliée à la sortie de la chambre à tourillon, un échangeur de chaleur intérieur, une entrée de l'échangeur de chaleur intérieur étant reliée à une sortie du premier tube intérieur et une buse étant reliée à la sortie du premier tube intérieur et à l'entrée de l'échangeur de chaleur intérieur. Le tube creux est relié à une entrée de la buse.
PCT/US2010/056980 2009-11-23 2010-11-17 Échangeur de chaleur ayant un tube à vortex pour applications à écoulement d'air commandé Ceased WO2011062958A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP10782140A EP2504638A2 (fr) 2009-11-23 2010-11-17 Échangeur de chaleur ayant un tube à vortex pour applications à écoulement d'air commandé
CN201080052974.4A CN102667369B (zh) 2009-11-23 2010-11-17 具有用于受控气流应用的涡流管的热交换器

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US26381709P 2009-11-23 2009-11-23
US61/263,817 2009-11-23
US12/895,009 2010-09-30
US12/895,009 US20110120677A1 (en) 2009-11-23 2010-09-30 Heat exchanger having a vortex tube for controlled airflow applications

Publications (2)

Publication Number Publication Date
WO2011062958A2 true WO2011062958A2 (fr) 2011-05-26
WO2011062958A3 WO2011062958A3 (fr) 2011-12-08

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US (1) US20110120677A1 (fr)
EP (1) EP2504638A2 (fr)
CN (1) CN102667369B (fr)
WO (1) WO2011062958A2 (fr)

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JP5674129B2 (ja) * 2008-01-11 2015-02-25 オイ イーセ エコ クーリング エンジニアリング リミテッドＯｙ Ｅｃｅ Ｅｃｏ Ｃｏｏｌｉｎｇ Ｅｎｇｉｎｅｅｒｉｎｇ Ｌｔｄ 旋回流管処理に関連する方法および装置
FR2929382B1 (fr) * 2008-04-01 2010-04-30 S I R S E Procede de commande d'un dispositif comportant des tubes vortex de hilsch-ranque.

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9725754B2 (en) 2010-07-29 2017-08-08 Sean F. Boyle Generic sample preparation
WO2018033250A3 (fr) * 2016-08-19 2018-07-05 Sata Gmbh & Co. Kg Dispositif de thermorégulation servant à chauffer et/ou à refroidir des gaz ou des mélanges de gaz, de préférence pour l'utilisation dans le domaine de la protection respiratoire
US11400322B2 (en) 2016-08-19 2022-08-02 Sata Gmbh & Co. Kg Temperature-control device for heating and/or cooling gases or gas mixtures preferably for the use in the field of respiratory protection

Also Published As

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WO2011062958A3 (fr) 2011-12-08
CN102667369B (zh) 2015-08-12
CN102667369A (zh) 2012-09-12
EP2504638A2 (fr) 2012-10-03
US20110120677A1 (en) 2011-05-26

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