CN1432123A - Device for heat/moist exchange - Google Patents

Device for heat/moist exchange Download PDF

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Publication number
CN1432123A
CN1432123A CN01810548A CN01810548A CN1432123A CN 1432123 A CN1432123 A CN 1432123A CN 01810548 A CN01810548 A CN 01810548A CN 01810548 A CN01810548 A CN 01810548A CN 1432123 A CN1432123 A CN 1432123A
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CN
China
Prior art keywords
turbulent
ratio
pipeline
heat
generator
Prior art date
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Granted
Application number
CN01810548A
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Chinese (zh)
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CN1237321C (en
Inventor
斯万·梅尔克·尼尔松
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Individual
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Individual
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Publication of CN1432123A publication Critical patent/CN1432123A/en
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Publication of CN1237321C publication Critical patent/CN1237321C/en
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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

Landscapes

  • 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 (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 Dh and Reynolds number being in the range of 0.01-0.04, that the angle theta which indicates the inclination of the rear edge sides (5) of the turbulence generators is in the range of 30 DEG -60 DEG , that the ratio of the height e of the upper side 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 between the turbulence generators to the height e is in the range of 8-30, that the ratio of the length B of the upper side 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 of the turbulence generators to the hydraulic diameter is in the range of 0.01-0.2.

Description

Heat/device for heat/moist exchange
Invention field
The present invention relates to a kind of heat/device for heat/moist exchange of optimizing the wet conversion ratio separately of heat with respect to the ratio that passes air-flow differential wherein.Consider this purpose, this switching equipment is provided with a turbulent generator that extends perpendicular to pipeline, after this turbulent generator has one along the side, a upper side and side, a forward position.
Background technology
Foregoing air-air heat/device for heat/moist exchange constitutes by being assembled into the plane and the wavy band that form triangle or trapezoidal pipeline together usually.In the heat/device for heat/moist exchange of the type, cross-section of pipeline is less and air flow velocity in facility environment is very fast, and air is along duct orientation laminar flow relatively in an orderly manner.Therefore, air-flow comes down to stratiform.Only in the short distance of entrance, there is certain air-flow to flow perpendicular to duct wall.The so-called Reynolds number of scope between 100-600 is as airflow characteristic in this article.In case Reynolds number is less than about 2000, air-flow will remain stratiform.
Those skilled in the art know, in the laminar flow near duct wall, form the boundary layer, and the air velocity here is essentially zero.This boundary layer has reduced heat and wet exchange coefficient considerably, particularly relevant with the so-called extended flow heat exchange coefficient that wets.In order to strengthen the wet exchange of heat, air is flowed towards the direction of pipe surface as follows, promptly reduce the exchange between boundary layer and increase layer and the layer.This can be produced by so-called turbulent flow.In level and smooth pipeline uniformly, when Reynolds number surpassed 2000, laminar flow can change turbulent flow into.Obtain so high Reynolds number in the pipeline of heat/device for heat/moist exchange discussed herein if be desirably in, then need in fact than higher air velocity usually.When Reynolds number in the above-mentioned switching equipment is low, so just must use the manual type turbulization in pipeline for example by a special turbulent generator is installed.
Known such turbulent generator has many forms.The turbulent generator that a transverse fold shape is arranged in the heat exchange cylinder in SE-B-444071.These folds at first are used for keeping jointly making it not by intussusception, and having the effect of turbulization simultaneously around the band of central tube, and this turbulence effect makes the efficiency of damp and hot exchanging in the switching equipment with above-mentioned fully level and smooth pipeline obtain to a certain degree raising.
Therefore the turbulent generator of the type has improved hot wet exchange to a certain extent.Yet also increased pressure reduction tempestuously.The increase that is higher than efficiency of damp and hot exchanging is it seems in the increase of pressure reduction.Yet it is very important to have a small pressure difference in the air-air switching equipment.Because pressure reduction has determined to drive size and the power supply requirement that air communication is crossed the fan of switching equipment.Furthermore, this pressure reduction depends on design, size and the geometry of turbulent generator.
Goal of the invention
Therefore the purpose of this invention is to provide a hot device for heat/moist exchange, its turbulent generator makes it can obtain the optimal proportion of air-flow differential with respect to the wet conversion ratio of heat in ducted position of this switching equipment and design.
Summary of the invention
According to the present invention, above-mentioned purpose can realize that its pipeline is formed and must be finished by the condition of following provisions by a heat/device for heat/moist exchange:
Spacing between the center of entrance and nearest turbulent generator is determined by the long-pending ratio of spacing and turbulent flow diameter and Reynolds number and Reynolds number must be between the 0.01-0.04 scope, show turbulent generator back angle θ with respect to the inclined degree of the vertical plane by duct bottom should be at 30-60 ° along the side, the turbulent generator upper side is higher than the ratio of the height e of duct bottom and pipeline turbulent flow diameter should be in the scope of 0.30-1.1, the ratio of spacing in the pipeline between the turbulent generator and above-mentioned height e should be in the scope of 8-30, the length of each turbulent generator upper side is higher than the ratio of the height e of duct bottom with it should be in the scope of 1.0-4.0, and the ratio of turbulent generator edge radius and turbulent flow diameter should be in the scope of 0.01-0.2.
In order to optimize the ratio of pressure reduction and heat/wet exchange rate, the transverse wave of turbulization, so-called turbulent generator not only needs to be placed on apart from the suitable distance of pipeline tapping, and will be placed on each other correct distance place apart.Furthermore, they should be by correct design, and has certain extension on the vertical and horizontal direction in pipeline.
At the entrance place of heat/device for heat/moist exchange, because the very thin so hot wet conversion coefficient height in boundary layer.The boundary layer is along the principal direction thickening of air-flow and the wet transfer ratio of heat reduces then.In order to improve the wet conversion efficiency of heat, the turbulent generator in the duct wall should be too near import, and this is because the wet conversion efficiency of the heat in this zone is very high.In fact turbulent generator can cause and the increase of undesirable pressure reduction like this.Therefore preferably first turbulent generator is placed on the distance that natural import turbulent flow disappears in the pipeline.
When air arrives first turbulent generator, having produced orderly turbulence air-flow and air will flow towards duct wall.Therefore, heat/wet conversion ratio is significantly improved.When the turbulence air-flow that produces during away from turbulent generator, turbulent flow will reduce gradually.When disappearing, turbulent flow is the optimum position of laying second turbulent generator.
By a large amount of experiments and research, found the geometric profile of the turbulent generator that makes heat/wet conversion efficiency and pressure reduction optimal proportion and in ducted riding position.
Used the statement of turbulent flow diameter in this article, the ratio of its expression fluid line cross-sectional area and cross-section of pipeline girth.The characteristic of air-flow is expressed by so-called Reynolds number (Reynolds number) and Schmidt number (Schmidt ' s number).
Accompanying drawing is described
Below contrast figure is carried out more detailed description to the present invention, wherein
Fig. 1 is the perspective view of the pipeline of heat of the present invention with turbulent generator/wet switch,
Fig. 2 is the side schematic view of pipeline among Fig. 1,
Fig. 3 be among Fig. 1 and Fig. 2 pipeline along the sectional view of I-I line.
The specific embodiment
Fig. 1 and Fig. 2 illustrate import 1 and a part of pipeline 2 of heat/device for heat/moist exchange of the present invention.In the drawings, only illustrate and be placed in import 1 first turbulent generator 3 and second turbulent generator 4 the most nearby.The height of pipeline 2 is h.Open import and the spacing A between first turbulent generator 3 centers are determined by the ratio that amasss of spacing A and turbulent flow diameter and Reynolds number that must be between 0.01-0.04.Here the turbulent flow diameter is represented the ratio of fluid line cross-sectional area relative duct size section girth, and Reynolds number is determined by air-flow.
By mentioned earlier equally as can be known, A depends on Reynolds number, and depends on air velocity thus.Therefore the best riding position of first turbulent generator depends on operating environment at that time.
Can find fairly obviously that by Fig. 2 turbulent generator 3,4 has special geometric form.They are formed with the back along side 5, smooth upper side 6 and the forward position side 7 that tilts of inclination.
According to the present invention, also can use following condition: show turbulent generator 3,4 back be in 30-60 ° the scope along side 5 with respect to the angle θ of the inclined degree of pipeline 2 bottoms 8, the height e and the pipeline 2 turbulent flow diameter D of upper side 6 relative duct size bottom 8 hRatio should be in the scope of 0.30-1.1.Furthermore, the length B that the ratio range of first turbulent generator 3 and 4 centre-to-centre spacing P of second turbulent generator and height e should be 8-30 and each turbulent generator 3,4 upper sides 6 ratio range of 8 height e bottom the upper side relative duct size should be 1.0-4.0.
Like this, turbulent generator 3,4 of the present invention have special geometric shape and be positioned at each other at a distance of and the import 1 of distance (suitable have triangle or/and trapezoidal cross-section) pipeline 2 certain for the calculated distance place, thereby increased efficiency of damp and hot exchanging considerably, but just improved pressure reduction within bounds.When air-flow during near turbulent generator 3, flow velocity depends on the cross section that reduces and increases partly, as shown in Figure 3.Subsequently, when air by turbulent generator 3 and when leaving sharp edges in the transition portion from upper side 6 to side, forward position 7 because the cross section that obviously separates, and produced violent turbulent flow behavior.This method has very improved efficiency of damp and hot exchanging effectively.
Turbulent generator 4 is placed on as follows apart from the position of first turbulent generator 3 through calculated distance P, thereby the turbulent flow that is produced is utilized as much as possible fully, after this, before air arrives second turbulent generator 4, form a what is called of in Fig. 1, representing contact zone again with O.This has just been avoided can not significantly increasing pressure reduction increase unnecessary under the situation of efficiency of damp and hot exchanging under the existing turbulent flow.At contact zone O again, air-flow can touch flat surfaces to a certain extent again before arriving next turbulent generator.
Importantly, make the edge part of turbulent generator 3,4 enough sharp keen so that place's (decompression place) is cut apart in generation.Edge radius r should satisfy r/D as shown in Figure 2 hRatio within the 0.01-0.2 scope.
In order further to reduce pressure reduction when keeping heat transfer rate, as shown in Figure 2, the height e that starts at from the bottom 8 of turbulent generator should be greater than the height f that starts at from the pipeline upper side.This design has been avoided in the unnecessary turbulent flow of this outburst area place generation.Easily, this appropriate designs of ledge just cooperates it with pipeline downside wall part 5,6 and 7 corresponding recesses that limited, thereby is used for obtaining when pipe layers is set stable joint, for example can avoid overlapping.
The designed turbulent generator of the present invention is effective equally to the high flow rate air-flow, and this moment, turbulent flow also produced in level and smooth pipeline.Naturally the turbulent flow of Xing Chenging is by being used to separate and the converging of ingress of air/separating effect and mechanism are improved again.

Claims (1)

1. heat/device for heat/moist exchange that the wet conversion ratio separately of heat is optimized with respect to the ratio that passes air-flow differential wherein, this switching equipment has a pipeline (1), this pipeline is provided with perpendicular to pipeline and extends and have after one a turbulent generator (3 of (5), a upper side (6) and side, a forward position (7) along the side, 4), it is characterized in that
Its pipeline is formed and must be met the following conditions:
Spacing (A) between the center of pipeline (1) inlet and nearest turbulent generator (3) is by spacing (A) and turbulent flow diameter (D h) and the long-pending ratio of Reynolds number determines and this Reynolds number must be between the 0.01-0.04 scope,
Show turbulent generator (3,4) back (5) should be at 30-60 ° with respect to the angle θ of the inclined degree of the vertical plane by pipeline (1) bottom (8) along the side,
Turbulent generator (3,4) upper side (6) is higher than the height e and the turbulent flow diameter (D of duct bottom (8) h) ratio should be in the scope of 0.3-1.1,
Spacing in the pipeline between first and second turbulent generators (3,4) and the ratio of above-mentioned height e should be in the scopes of 8-30,
The length B of each turbulent generator (3,4) upper side (6) is higher than the ratio of the height e of duct bottom (8) with it should be in the scope of 1.0-4.0,
The ratio of turbulent generator edge radius and turbulent flow diameter should be in the scope of 0.01-0.2.
CNB018105483A 2000-06-15 2001-05-14 Device for heat/moist exchange Expired - Lifetime CN1237321C (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE00022228 2000-06-15
SE0002222A SE515132C2 (en) 2000-06-15 2000-06-15 Device for heat / moisture exchanger with turbulence generators

Publications (2)

Publication Number Publication Date
CN1432123A true CN1432123A (en) 2003-07-23
CN1237321C CN1237321C (en) 2006-01-18

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CNB018105483A Expired - Lifetime CN1237321C (en) 2000-06-15 2001-05-14 Device for heat/moist exchange

Country Status (9)

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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) SE515132C2 (en)
WO (1) WO2001096803A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102119315A (en) * 2008-08-06 2011-07-06 S·M·尼尔松 Channel system
CN102980424A (en) * 2008-04-18 2013-03-20 S·M·尼尔松 Channel system
US9441523B2 (en) 2008-04-18 2016-09-13 Sven Melker Nilsson Channel system with internal flow director and turbulence generator

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5545260B2 (en) 2010-05-21 2014-07-09 株式会社デンソー Heat exchanger
FR2990151B1 (en) * 2012-05-02 2014-05-23 Michelin & Cie MEMBRANE FOR VULCANIZING THE INNER PART OF A TIRE IN WHICH CIRCULATES A PRESSURIZED GAS COMPRISING TURBULENCE GENERATORS
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
PL235069B1 (en) 2017-12-04 2020-05-18 Ts Group Spolka Z Ograniczona Odpowiedzialnoscia Coil for transmission of heat for the rotary, cylindrical heat exchanger
FR3082237B1 (en) * 2018-06-12 2020-10-30 Safran Aircraft Engines LOW PRESSURE DROP HEAT EXCHANGE DEVICE
KR102206263B1 (en) * 2019-05-13 2021-01-21 조영호 White Smoke(includiong hazardous substances)Removal System Using High-Efficiency Heat Exchanger
WO2023107618A1 (en) * 2021-12-08 2023-06-15 Worcester Polytechnic Institute Passive flow control for captive vortex

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DE2219130C2 (en) * 1972-04-19 1974-06-20 Ulrich Dr.-Ing. 5100 Aachen Regehr CONTACT BODY FOR HEAT AND / OR SUBSTANCE EXCHANGE
SE444071B (en) * 1980-11-14 1986-03-17 Sven Melker Nilsson ROTATING REGENERATIVE EXCHANGER, PROCEDURE FOR ITS MANUFACTURING AND MACHINE FOR IMPLEMENTATION OF THE PROCEDURE
FR2559575A1 (en) * 1984-02-14 1985-08-16 Gea Ahlborn Gmbh Co Kg Plate heat exchanger
SE458806B (en) 1987-04-21 1989-05-08 Alfa Laval Thermal Ab PLATE HEAT EXCHANGER WITH DIFFERENT FLOW RESISTANCE FOR MEDIA
US5573062A (en) * 1992-12-30 1996-11-12 The Furukawa Electric Co., Ltd. Heat transfer tube for absorption refrigerating machine

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102980424A (en) * 2008-04-18 2013-03-20 S·M·尼尔松 Channel system
US9441523B2 (en) 2008-04-18 2016-09-13 Sven Melker Nilsson Channel system with internal flow director and turbulence generator
CN102119315A (en) * 2008-08-06 2011-07-06 S·M·尼尔松 Channel system
CN102119315B (en) * 2008-08-06 2014-04-09 S·M·尼尔松 Channel system
US9410462B2 (en) 2008-08-06 2016-08-09 Sven Melker Nilsson Channel system

Also Published As

Publication number Publication date
SE0002222L (en) 2001-06-11
WO2001096803A1 (en) 2001-12-20
SE515132C2 (en) 2001-06-11
FI112880B (en) 2004-01-30
AU2001256930A1 (en) 2001-12-24
CN1237321C (en) 2006-01-18
SE0002222D0 (en) 2000-06-15
PL197437B1 (en) 2008-03-31
JP2004503739A (en) 2004-02-05
KR100709233B1 (en) 2007-04-19
KR20030010626A (en) 2003-02-05
JP3939648B2 (en) 2007-07-04
DE10196335B3 (en) 2016-10-06
DE10196335T1 (en) 2003-05-22
PL358923A1 (en) 2004-08-23
FI20022196A (en) 2002-12-13

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