WO2001096803A1 - Device for heat/moist exchange - Google Patents

Device for heat/moist exchange Download PDF

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Publication number
WO2001096803A1
WO2001096803A1 PCT/SE2001/001041 SE0101041W WO0196803A1 WO 2001096803 A1 WO2001096803 A1 WO 2001096803A1 SE 0101041 W SE0101041 W SE 0101041W WO 0196803 A1 WO0196803 A1 WO 0196803A1
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WO
WIPO (PCT)
Prior art keywords
ratio
range
turbulence
ducts
duct
Prior art date
Application number
PCT/SE2001/001041
Other languages
French (fr)
Inventor
Sven Melker Nilsson
Original Assignee
Sven Melker Nilsson
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 Sven Melker Nilsson filed Critical Sven Melker Nilsson
Priority to DE10196335.1T priority Critical patent/DE10196335B3/en
Priority to KR1020027015608A priority patent/KR100709233B1/en
Priority to AU2001256930A priority patent/AU2001256930A1/en
Priority to JP2002510887A priority patent/JP3939648B2/en
Priority to PL358923A priority patent/PL197437B1/en
Publication of WO2001096803A1 publication Critical patent/WO2001096803A1/en
Priority to FI20022196A priority patent/FI112880B/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/02—Ducting arrangements
    • F24F13/04—Air-mixing units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2221/00—Details or features not otherwise provided for
    • F24F2221/46—Air flow forming a vortex

Definitions

  • the invention relates to a device for heat/moisture exchange for optimising the ratio of transfer rate of heat and moisture, respectively, to pressure drop of an air flow flowing through the exchanger.
  • the exchanger is provided with turbulence generators extending transversely to the ducts and having a rear edge side, an upper side and a front edge side.
  • An air-to-air heat/moisture exchanger of the type described above is usually made of plane and corrugated bands, alternately, which when putting them together form triangular or trapezoid-shaped ducts.
  • heat/moisture exchangers of the type mentioned above with ducts having relatively small cross-sections and with air-flow rates that are frequent in these contexts the air flows in relatively ordered layers in the direction of the ducts.
  • the flow is essentially laminar. Only along a short distance at the inlet of the ducts, a certain flow occurs transversely to the duct walls.
  • the so-called Reynolds number which in this context is in the range of 100-600 is used as characteristic of the air flow. As long as the Reynolds number is smaller than about 2000, the flow remains laminar.
  • turbulence thus has to be generated in an artificial manner, for instance by arranging special turbulence generators in the ducts.
  • turbulence generators are known in many different forms. From SE-B-444 071 a roller is known for heat transfer, having turbulence generators in the form of transverse corrugations.
  • the object of the invention is thus to provide a heat/moisture exchanger, in which the turbulence generators should have such a location and design in the ducts of the exchanger that an optimal ratio of the pressure drop of the air flow to the transfer rate of heat and moisture is obtained.
  • the objects described above are achieved by a device for heat/moisture exchange, in which the composition of the ducts has to fulfil the conditions stated below: that the distance between the inlet of the ducts and the centre of the nearest turbulence generator is determined by the ratio of the distance to the product of the hydraulic diameter and Reynolds number having to be in the range of 0.01-0.04, that the angle ⁇ which indicates the inclination of the rear edge sides of the turbulence generators relative to a vertical plane through the bottom of the ducts is to be in the range of 30°-60°, that the ratio of the height e of the upper side above the bottom of the duct to the hydraulic diameter of the duct is to be in the range of 0.30-1.1, that the ratio of the distance between the turbulence generators in the duct to the height e mentioned above is to be in the range of 8-30, that the ratio of the length of the upper side of each turbulence generator to its height e above the bottom of the duct is to be in the range of
  • the transverse waves that cause turbulence have to be placed, on the one hand, at the correct distance from the duct opening and, on the other, at the correct distance from each other. Furthermore, they have to be correctly designed and have a certain extension both vertically and horizontally in the duct.
  • the coefficient of heat and moisture transfer is high since the boundary layer is very thin. The thickness of the boundary layer then increases in the main direction of the flow and the transmission coefficient of heat and moisture is reduced.
  • the turbulence generators in the duct walls should not be arranged too near the inlet since the transfer of heat and moisture already is high in this area. Thus, a turbulence generator would essentially only cause an increased pressure drop, which is not desirable. Consequently, it is optimal to place the first turbulence generator in the duct at such a distance that the natural inlet turbulence has faded.
  • the air reaches the first turbulence generator an ordered turbulent air flow is generated and the air is made to flow towards the duct walls.
  • a marked increase of the transfer rate of heat/moisture is obtained.
  • the thus turbulent air flow then leaves the turbulence generator, the turbulence is reduced gradually.
  • the turbulence has faded, it is optimal to place the next turbulence generator.
  • hydraulic diameter is used, which is an expression of the ratio of the cross-sectional area of a flow duct to the circumference of the cross-section of the duct.
  • the air flow is characterised by the so-called Reynolds number and Schmidt ' s number .
  • Fig. 1 is a perspective view of a duct of a heat/moisture exchanger which has turbulence generators according to the invention
  • Fig. 2 is a schematic side view of the duct in Fig . 1 .
  • Fig. 3 is a cross-sectional view of the duct in Figs 1 and 2 along the line I -I in Fig. 2.
  • Figs 1 and 2 show the inlet 1 and part of a duct 2 for a heat/moisture exchanger according to the invention.
  • a first turbulence generator 3 which is located nearest the inlet 1 and a second turbulence generator 4 are shown.
  • the duct 2 has a height h.
  • the distance A between the opening of the inlet and the centre of the first turbulence generator 3 is determined by the ratio of the distance A to the product of the hydraulic diameter and Reynolds number having to be in the range of 0.01-0.04.
  • the hydraulic diameter is an expression of the ratio of the cross-sectional area of a flow duct to the circumference of the duct, and Reynolds number depends on the air flow.
  • the turbulence generators 3, 4 have a particular geometry. They are thus formed with an oblique rear edge side 5, a flat upper side 6 and an oblique front edge side 7.
  • the angle ⁇ which indicates the inclination of the rear edge side 5 of the turbulence generators 3 , 4 in relation to the bottom 8 of the duct 2 is to be in the range of 30°-60° and the ratio of the height e of the upper side 6 above the bottom 8 to the hydraulic diameter D h of the duct 2 is to be 0.30-1.1.
  • the ratio of the distance P between the centre of the first 3 and the second 4 turbulence generator to said height e is to be in the range of 8-30 and the ratio of the length B of the upper side 6 of each turbulence generator 3 , 4 to the height e of the upper side above the bottom 8 is to be in the range of 1.0-4.0.
  • turbulence generators 3,4 with a special geometry and at a calculated distance from one another and from the inlet 1 in ducts 2 suitably of a triangular and/or a trapezoid- shaped cross-section, a considerably increased transfer rate of heat and moisture is achieved, but only a moderate increase of pressure drop.
  • the flow rate increases locally depending on a reduced cross-sectional surface, which Fig. 3 intends to illustrate.
  • the turbulence generator 4 is arranged at a calculated distance P from the first turbulence generator 3 in such a manner that the generated turbulence can be used as completely as possible and, after this, a so- called re-engaging area, designated O in Fig. 1, is to be formed before the air passes the second turbulence generator 4. This prevents an unnecessary additional pressure drop without a significant increase of the transfer rate of heat and moisture in the already turbulent air flow. In the re-engaging area 0, it is achieved that once again the air engages, to a large extent, the smooth surface, before it reaches the next turbulence generator.
  • edge radius r should be such that the ratio r/D h is in the range of 0.01-0.2.
  • the height e from the bottom 8 of the turbulence generator can be made higher than the corresponding height f from the upper side of the duct, see Fig. 2.
  • This design eliminates unnecessary turbulence in this protruding space.
  • this protruding part has such a design as to fit well in the corresponding recess defined by the wall portions 5, 6 and 7 on the underside of the duct with the aim of obtaining a stable joint when arranging layers of ducts on one another and, for instance, avoiding telescoping.
  • the turbulence generators are also made efficient at a high air flow rate, where a turbulent flow would be formed also in a smooth duct.
  • the turbulence which is formed naturally is improved by the convergent/divergent effect and mechanisms for separation and re-engagement of the air.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

The invention relates to a device for heat/moisture exchange which has ducts (1) with turbulence generators (3, 4) extending transversely to the ducts and having a rear edge side (5), an upper side (6) and a front edge side (7). The device is characterised in that the ducts are such that the distance A between the inlet of the ducts and the centre of the nearest turbulence generator is determined by the ratio of the distance A to the product of the hydraulic diameter and Reynolds number being in the range of 0.01-0.04, that the angle υ which indicates the inclination of the rear edge sides (5) of the turbulence generators is in the range of 30°-60°, that the ratio of the height e of the upper side (6) above the bottom of the duct to the hydraulic diameter Dh is in the range of 0.3-1.1, that the ratio of the distance P between the turbulence generators (3, 4) to the height e is in the range of 8-30, that the ratio of the length B and the upper side (6) of each turbulence generator to the height e is in the range of 1.0-4.0, and that the ratio of the edge radius r of the turbulence generators to the hydraulic diameter Dh is in the range of 0.01-0.2.

Description

DEVICE FOR HEAT/MOIST EXCHANGE
Field of the Invention
The invention relates to a device for heat/moisture exchange for optimising the ratio of transfer rate of heat and moisture, respectively, to pressure drop of an air flow flowing through the exchanger. With this purpose in view, the exchanger is provided with turbulence generators extending transversely to the ducts and having a rear edge side, an upper side and a front edge side.
Background Art
An air-to-air heat/moisture exchanger of the type described above is usually made of plane and corrugated bands, alternately, which when putting them together form triangular or trapezoid-shaped ducts. In heat/moisture exchangers of the type mentioned above with ducts having relatively small cross-sections and with air-flow rates that are frequent in these contexts, the air flows in relatively ordered layers in the direction of the ducts. Thus, the flow is essentially laminar. Only along a short distance at the inlet of the ducts, a certain flow occurs transversely to the duct walls. The so-called Reynolds number which in this context is in the range of 100-600 is used as characteristic of the air flow. As long as the Reynolds number is smaller than about 2000, the flow remains laminar.
It is well known by those skilled in the art that, in a laminar air flow nearest the duct wall, a boundary layer is formed, where the speed of the air flow is essentially zero. This boundary layer considerably reduces the coefficient of heat and moisture transfer, above all in connection with so-called completely developed flow. In order to increase the coefficient of heat and moisture transfer, the air must be caused to flow in a direction towards the surface of the duct in such a manner that the boundary layer is reduced and the transfer from one layer to another is made greater. This may occur by so-called turbulent flow. In smooth, even ducts, the laminar flow changes into a turbulent flow when Reynolds number exceeds about 2000. If it is desirable to achieve such high Reynolds numbers in the ducts in the heat/moisture exchangers as are discussed here, essentially higher speeds of the air flow than usual in this context are required. In connection with low Reynolds numbers that apply to the exchanger described above, turbulence thus has to be generated in an artificial manner, for instance by arranging special turbulence generators in the ducts. Such turbulence generators are known in many different forms. From SE-B-444 071 a roller is known for heat transfer, having turbulence generators in the form of transverse corrugations. These corrugations serve above all to keep the bands which are wound on a centre tube together so that they do not telescope, but have at the same time a turbulence-generating effect that causes a certain degree of improvement of the transfer properties of heat and moisture in relation to exchangers with completely smooth ducts which are described above. This type of turbulence generators thus increases the transfer of heat and moisture to a considerable extent. However, also the pressure drop increases drastically. The increase of the pressure drop has appeared to be greater than the increase of the transfer of heat and moisture. However, in air-to-air exchangers it is essential having a low pressure drop since the pressure drop dimensions the size and the power requirement of the fans which are arranged to drive the air flow through the exchanger. Furthermore, this pressure drop has been found to be dependent on the design, dimension and geometry of the turbulence generators . Object of the Invention
The object of the invention is thus to provide a heat/moisture exchanger, in which the turbulence generators should have such a location and design in the ducts of the exchanger that an optimal ratio of the pressure drop of the air flow to the transfer rate of heat and moisture is obtained.
Summary of the Invention
According to the invention, the objects described above are achieved by a device for heat/moisture exchange, in which the composition of the ducts has to fulfil the conditions stated below: that the distance between the inlet of the ducts and the centre of the nearest turbulence generator is determined by the ratio of the distance to the product of the hydraulic diameter and Reynolds number having to be in the range of 0.01-0.04, that the angle θ which indicates the inclination of the rear edge sides of the turbulence generators relative to a vertical plane through the bottom of the ducts is to be in the range of 30°-60°, that the ratio of the height e of the upper side above the bottom of the duct to the hydraulic diameter of the duct is to be in the range of 0.30-1.1, that the ratio of the distance between the turbulence generators in the duct to the height e mentioned above is to be in the range of 8-30, that the ratio of the length of the upper side of each turbulence generator to its height e above the bottom of the duct is to be in the range of
1.0-4.0, and that the ratio of the edge radius of the turbulence generators to the hydraulic diameter is to be in the range of 0.01-0.2.
In order to optimise the ratio of pressure drop to the transfer rate of heat/moisture, the transverse waves that cause turbulence, the so-called turbulence generators, have to be placed, on the one hand, at the correct distance from the duct opening and, on the other, at the correct distance from each other. Furthermore, they have to be correctly designed and have a certain extension both vertically and horizontally in the duct. At the inlet of the ducts of a heat/moisture exchanger, the coefficient of heat and moisture transfer is high since the boundary layer is very thin. The thickness of the boundary layer then increases in the main direction of the flow and the transmission coefficient of heat and moisture is reduced. In order to increase transfer of heat and moisture, the turbulence generators in the duct walls should not be arranged too near the inlet since the transfer of heat and moisture already is high in this area. Thus, a turbulence generator would essentially only cause an increased pressure drop, which is not desirable. Consequently, it is optimal to place the first turbulence generator in the duct at such a distance that the natural inlet turbulence has faded. When the air reaches the first turbulence generator, an ordered turbulent air flow is generated and the air is made to flow towards the duct walls. Thus, a marked increase of the transfer rate of heat/moisture is obtained. When the thus turbulent air flow then leaves the turbulence generator, the turbulence is reduced gradually. When the turbulence has faded, it is optimal to place the next turbulence generator.
By extensive tests and research, the definitions of the geometry of the turbulence generators and their location in the duct have been found, which result in an optimal ratio of the transfer rate of heat/moisture to the pressure drop.
In this context, the expression hydraulic diameter is used, which is an expression of the ratio of the cross-sectional area of a flow duct to the circumference of the cross-section of the duct. The air flow is characterised by the so-called Reynolds number and Schmidt ' s number .
Brief Description of the Drawing In the following, the invention will be described in more detail with reference to the accompanying drawing, in which
Fig. 1 is a perspective view of a duct of a heat/moisture exchanger which has turbulence generators according to the invention,
Fig. 2 is a schematic side view of the duct in Fig . 1 , and
Fig. 3 is a cross-sectional view of the duct in Figs 1 and 2 along the line I -I in Fig. 2.
Description of Preferred Embodiments
Figs 1 and 2 show the inlet 1 and part of a duct 2 for a heat/moisture exchanger according to the invention. In the drawing, only a first turbulence generator 3 which is located nearest the inlet 1 and a second turbulence generator 4 are shown. The duct 2 has a height h. The distance A between the opening of the inlet and the centre of the first turbulence generator 3 is determined by the ratio of the distance A to the product of the hydraulic diameter and Reynolds number having to be in the range of 0.01-0.04. Here the hydraulic diameter is an expression of the ratio of the cross-sectional area of a flow duct to the circumference of the duct, and Reynolds number depends on the air flow. From that described above, it is also evident that A depends on Reynolds number and, thus, on the speed of the air flow. The optimal location of the first turbulence generator thus depends on the current operating conditions . As will be especially evident from Fig. 2, the turbulence generators 3, 4 have a particular geometry. They are thus formed with an oblique rear edge side 5, a flat upper side 6 and an oblique front edge side 7.
According to the invention, the following conditions are further applicable: the angle θ which indicates the inclination of the rear edge side 5 of the turbulence generators 3 , 4 in relation to the bottom 8 of the duct 2 is to be in the range of 30°-60° and the ratio of the height e of the upper side 6 above the bottom 8 to the hydraulic diameter Dh of the duct 2 is to be 0.30-1.1. Furthermore, the ratio of the distance P between the centre of the first 3 and the second 4 turbulence generator to said height e is to be in the range of 8-30 and the ratio of the length B of the upper side 6 of each turbulence generator 3 , 4 to the height e of the upper side above the bottom 8 is to be in the range of 1.0-4.0. By thus using according to the invention, turbulence generators 3,4 with a special geometry and at a calculated distance from one another and from the inlet 1 in ducts 2 suitably of a triangular and/or a trapezoid- shaped cross-section, a considerably increased transfer rate of heat and moisture is achieved, but only a moderate increase of pressure drop. When the air flow approaches the turbulence generator 3, the flow rate increases locally depending on a reduced cross-sectional surface, which Fig. 3 intends to illustrate.
Subsequently, when the air passes the turbulence generator 3 and leaves the sharp edge in the transition from the upper side 6 to the front edge side 7, an intensive turbulent movement arises due to the separation and the significantly divergent cross-section. This process is very efficient when it comes to increasing the transfer of heat and moisture.
The turbulence generator 4 is arranged at a calculated distance P from the first turbulence generator 3 in such a manner that the generated turbulence can be used as completely as possible and, after this, a so- called re-engaging area, designated O in Fig. 1, is to be formed before the air passes the second turbulence generator 4. This prevents an unnecessary additional pressure drop without a significant increase of the transfer rate of heat and moisture in the already turbulent air flow. In the re-engaging area 0, it is achieved that once again the air engages, to a large extent, the smooth surface, before it reaches the next turbulence generator.
It is important for the edges of the turbulence generators 3,4 to be sharp enough to produce the separation points (relieving points) . The edge radius r, see Fig. 2, should be such that the ratio r/Dh is in the range of 0.01-0.2.
In order to further reduce the pressure drop while maintaining the transfer rate of heat, the height e from the bottom 8 of the turbulence generator can be made higher than the corresponding height f from the upper side of the duct, see Fig. 2. This design eliminates unnecessary turbulence in this protruding space. Conveniently, this protruding part has such a design as to fit well in the corresponding recess defined by the wall portions 5, 6 and 7 on the underside of the duct with the aim of obtaining a stable joint when arranging layers of ducts on one another and, for instance, avoiding telescoping.
By designing the turbulence generators according to the invention, they are also made efficient at a high air flow rate, where a turbulent flow would be formed also in a smooth duct. The turbulence which is formed naturally is improved by the convergent/divergent effect and mechanisms for separation and re-engagement of the air.

Claims

1. A device for heat/moisture exchange for optimising the ratio of transfer rate of heat and moisture, respectively, to pressure drop of an air flow flowing through the exchanger which, with this purpose in view, is provided with ducts (1) having turbulence generators (3, 4) extending transversely to the ducts and having a rear edge side (5) , an upper side (6) and a front edge side (7), c h a r a c t e r i s e d in that the composition of the ducts (1) , in order to achieve said purpose, has to fulfil the following conditions: that the distance A between the inlet of the ducts (1) and the centre of the nearest turbulence generator (3) is determined by the ratio of the distance A to the product of the hydraulic diameter D and Reynolds number having to be in the range of 0.01-0.04, that the angle θ which indicates the inclination of the rear edge sides (5) of the turbulence generators
(3, 4) relative to a vertical plane through the bottom (8) of the duct (1) is to be in the range of 30°-60°, that the ratio of the height e of the upper side (6) above the bottom (8) of the duct to the hydraulic diameter Dh is to be in the range of 0.3-1.1, that the ratio of the distance P between the centre of the first (3) and the second (4) turbulence generator in the duct, seen from the inlet, to the height e mentioned above is to be in the range of 8-30, that the ratio of the length B and the upper side
(6) of each turbulence generator (3, 4) to its height e above the bottom (8) of the duct is to be in the range of 1.0-4.0, and that the ratio of the edge radius r of the turbulence generators (3, 4) to the hydraulic diameter Dh is to be in the range of 0.01-0.2.
PCT/SE2001/001041 2000-06-15 2001-05-14 Device for heat/moist exchange WO2001096803A1 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
DE10196335.1T DE10196335B3 (en) 2000-06-15 2001-05-14 Device for the exchange of heat / moisture
KR1020027015608A KR100709233B1 (en) 2000-06-15 2001-05-14 Device for heat/moist exchange
AU2001256930A AU2001256930A1 (en) 2000-06-15 2001-05-14 Device for heat/moist exchange
JP2002510887A JP3939648B2 (en) 2000-06-15 2001-05-14 Equipment for heat / humidity exchange
PL358923A PL197437B1 (en) 2000-06-15 2001-05-14 Device for heat/moist exchange
FI20022196A FI112880B (en) 2000-06-15 2002-12-13 Device intended for heat / moisture exchange

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0002222-8 2000-06-15
SE0002222A SE0002222L (en) 2000-06-15 2000-06-15 Device for heat / moisture exchanger with turbulence generators

Publications (1)

Publication Number Publication Date
WO2001096803A1 true WO2001096803A1 (en) 2001-12-20

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PCT/SE2001/001041 WO2001096803A1 (en) 2000-06-15 2001-05-14 Device for heat/moist exchange

Country Status (9)

Country Link
JP (1) JP3939648B2 (en)
KR (1) KR100709233B1 (en)
CN (1) CN1237321C (en)
AU (1) AU2001256930A1 (en)
DE (1) DE10196335B3 (en)
FI (1) FI112880B (en)
PL (1) PL197437B1 (en)
SE (1) SE0002222L (en)
WO (1) WO2001096803A1 (en)

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WO2009128750A1 (en) * 2008-04-18 2009-10-22 Sven Melker Nilsson Channel system
US20120279693A2 (en) * 2008-08-06 2012-11-08 Sven Nilsson Channel system
WO2013164283A1 (en) * 2012-05-02 2013-11-07 Compagnie Generale Des Etablissements Michelin Vulcanization membrane for the inner portion of a tire, in which a pressurized gas circulates and which includes turbulence generators
US9816762B2 (en) 2010-05-21 2017-11-14 Denso Corporation Heat exchanger having a passage pipe
FR3082237A1 (en) * 2018-06-12 2019-12-13 Safran Aircraft Engines LOW PRESSURE HEAT EXCHANGE DEVICE
US11340025B2 (en) 2017-12-04 2022-05-24 SWISS ROTORS Spolka z o.o. Heat transmission roll for a rotary cylindrical heat exchanger

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JP6121765B2 (en) * 2013-03-23 2017-04-26 京セラ株式会社 Sample holder
JP2014059139A (en) * 2013-10-23 2014-04-03 Melker Nilsson Sven Channel system
KR102206263B1 (en) * 2019-05-13 2021-01-21 조영호 White Smoke(includiong hazardous substances)Removal System Using High-Efficiency Heat Exchanger
US20230175793A1 (en) * 2021-12-08 2023-06-08 Worcester Polytechnic Institute Passive flow control for captive vortex

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US3887664A (en) * 1972-04-19 1975-06-03 Ulrich Regehr Contact body for the transfer of heat and/or substances
FR2559575A1 (en) * 1984-02-14 1985-08-16 Gea Ahlborn Gmbh Co Kg Plate heat exchanger
US4915165A (en) * 1987-04-21 1990-04-10 Alfa-Laval Thermal Ab Plate heat exchanger
US5573062A (en) * 1992-12-30 1996-11-12 The Furukawa Electric Co., Ltd. Heat transfer tube for absorption refrigerating machine

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Publication number Priority date Publication date Assignee Title
US3887664A (en) * 1972-04-19 1975-06-03 Ulrich Regehr Contact body for the transfer of heat and/or substances
FR2559575A1 (en) * 1984-02-14 1985-08-16 Gea Ahlborn Gmbh Co Kg Plate heat exchanger
US4915165A (en) * 1987-04-21 1990-04-10 Alfa-Laval Thermal Ab Plate heat exchanger
US5573062A (en) * 1992-12-30 1996-11-12 The Furukawa Electric Co., Ltd. Heat transfer tube for absorption refrigerating machine

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FI112880B (en) 2004-01-30
FI20022196A (en) 2002-12-13
JP3939648B2 (en) 2007-07-04
AU2001256930A1 (en) 2001-12-24
SE515132C2 (en) 2001-06-11
SE0002222L (en) 2001-06-11
JP2004503739A (en) 2004-02-05
DE10196335B3 (en) 2016-10-06
KR20030010626A (en) 2003-02-05
PL197437B1 (en) 2008-03-31
SE0002222D0 (en) 2000-06-15
CN1237321C (en) 2006-01-18
DE10196335T1 (en) 2003-05-22
PL358923A1 (en) 2004-08-23
KR100709233B1 (en) 2007-04-19
CN1432123A (en) 2003-07-23

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