CN1991284A - Highly effective air-cooled tube wing-type heat exchanger - Google Patents
Highly effective air-cooled tube wing-type heat exchanger Download PDFInfo
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- CN1991284A CN1991284A CN 200510121470 CN200510121470A CN1991284A CN 1991284 A CN1991284 A CN 1991284A CN 200510121470 CN200510121470 CN 200510121470 CN 200510121470 A CN200510121470 A CN 200510121470A CN 1991284 A CN1991284 A CN 1991284A
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Abstract
The invention discloses a fined tube heat exchanger with wind cooling of high efficiency. It adopts different combinations of heat exchanger. Front row tube at windward side is smooth tube and back row tube at leeward side is inner screw tube; or front row fin at windward side is flat plate and back row fin at leeward side is ripple plate or punching gap plate; or front row fins at windward side have bigger distance between fins and back row fins at leeward side have smaller distance between fins. In general, the heat transfer coefficient at back row pipe is larger than the one at front row pipe, or the heat transfer area at back row pipe is larger than the one at front row pipe, or the heat transfer coefficient and area at back row pipe are larger than the one at front row pipe. The structure makes the heat transfer coefficient or area of front row of heat exchanger at windward side relative smaller and the one of back row of heat exchanger at leeward side relative larger. It can improve the uniformity of temperature difference field, decrease the average heat conduction temperature difference of heat exchanger and improve the heat exchanging efficiency of heat exchanger.
Description
Technical field
The present invention relates to a kind of air-cooled tube wing-type heat exchanger, belong to the technical field that heat-exchange apparatus is made.
Background technology
Finned heat exchanger in the market has various ways, and as fin-tube type, dividing wall type, two-sided honeycomb fashion, swinging, wherein the fin-tube type finned heat exchanger is a heat exchanger structure form the most frequently used in the operation of air conditioning systems.Air-cooled tube wing-type heat exchanger, gas phase or liquid phase cold (heat) fluid be in the pipe flows inside, air under the effect of blower fan from pipe outside nature or forced flow be cooled (heat radiation).In order to increase heat transfer area, pipe is outer generally to be equipped with fin (nest plate or around sheet) more, and adopts mode double or that arrange comb more.The thermal resistance regularity of distribution of fin-tube type finned heat exchanger is: the ratio of the thermal resistance of the thermal contact resistance of pipe internal thermal resistance, heat exchanger fin and pipe outer air side is approximately 2: 1: 7.Double or to arrange the cooling grid cast identical with the sheet type more, its heat transfer coefficient is also roughly the same.
Cold and hot two kinds of fluids carry out heat exchange along heat-transfer area, and its temperature longshore current is to continuous variation, and its heat transfer temperature difference Δ T also constantly changes.From air-flow direction (rather than pipeline is along journey), pipe outer air side temperature longshore current is bigger to changing, and it is less to changing to manage inboard fluid temperature (F.T.) longshore current.Therefore, the heat transfer temperature difference of heat exchanger windward side is bigger, and the front-seat heat exchanger heat exchange efficiency of windward side is also higher.Air reduces with the inboard fluid heat transferring temperature difference of pipe after by front-seat heat exchanger, thereby the heat exchange efficiency of back row's heat exchanger of intermediate layer and leeward side is very low.
With double in the operation of air conditioning systems or the air-cooled tube wing-type evaporimeter of arranging comb is example more, because caliber (is generally Φ 4～12mm) greatly, the pressure loss of cold-producing medium by evaporimeter the time is also less (to be generally 10～100kPa), the evaporating temperature of the cold-producing medium of one-component in whole evaporimeter changes less (being generally 0.5～3 ℃), can be similar to think that the inboard cold-producing medium evaporating temperature of pipe does not become T
R
The air intake in the pipe outside is the higher room temperature (T of temperature
0), with the inside and outside heat transfer temperature difference Δ T of pipe during the comb heat exchange before the evaporimeter of windward side
F=T
0-T
R, air is flowed through before the evaporimeter, and temperature is reduced to T behind the comb
1＜T
0During again with the evaporimeter rear of tube heat exchange of leeward side, also be reduced to Δ T with the outer heat transfer temperature difference of pipe in the pipe
B=T
1-T
R＜Δ T
F(Q is a heat output in the formula according to thermal conduction study formula Q=KA Δ T, K is a heat transfer coefficient, A is a heat transfer area, Δ T is a heat transfer temperature difference) as can be known, if usable floor area, the dual-row evaporator that structure is identical, leeward evaporimeter rear of tube exchange capability of heat will be significantly less than the exchange capability of heat of the preceding comb of evaporimeter that facings the wind.Test and Computer simulation results all show.Advance the single channel stringing mode that discharge the back according to the cold-producing medium front row, under the standard condition of GB/T7725 defined, the heat exchange amount of comb is about 60～75% of total heat exchange amount before the evaporimeter, and the heat exchange amount of evaporimeter rear of tube is about total heat exchange amount 25～40%.Equally, for the evaporimeter of many rows comb, comb heat exchange efficiency the best before the evaporimeter, the central evaporator heat exchange efficiency reduces, and evaporimeter rear of tube heat exchange efficiency is the poorest.The total exchange capability of heat of heat exchanger is lower.
Summary of the invention
The technical problem to be solved in the present invention is to overcome the deficiencies in the prior art, a kind of highly effective air-cooled tube wing-type heat exchanger that reduces heat transfer temperature difference is provided, make the heat transfer coefficient of back row's leeward side of heat exchanger or heat transfer area heat transfer coefficient or heat transfer area greater than front-seat windward side, improve the uniformity of temperature difference field, improve total heat exchange efficiency of heat exchanger.
Collaborative theoretical according to the field in the augmentation of heat transfer, by making up different heat exchanger forms, make the heat transfer coefficient of the front-seat windward side of heat exchanger less relatively, the heat transfer coefficient of back row's leeward side is relatively large, or the heat transfer area of front-seat windward side is less relatively, the heat transfer area of back row's leeward side is relatively large, then can improve the uniformity of temperature difference field, reduce the mean temperature difference of heat exchanger, improve the heat exchange amount of back row's leeward side and in total heat exchange amount shared ratio, improve total exchange capability of heat of heat exchanger.
Technical scheme of the present invention is: a kind of air-cooled tube wing-type heat exchanger, at least comprise the preceding comb of being located at the heat exchanger windward side and the rear of tube of being located at the heat exchanger leeward side, it is characterized in that: the heat transfer coefficient of described rear of tube is greater than the heat transfer coefficient of preceding comb, and/or the heat transfer area of rear of tube is greater than the heat transfer area of preceding comb.That is to say, this heat exchanger is by the combination of different copper pipes and fin form, arrange the heat transfer coefficient of the heat transfer coefficient of leeward side, or afterwards arrange the heat transfer area of the heat transfer area of leeward side, or adopt the combination of the two greater than front-seat windward side greater than front-seat windward side thereafter.
Comb and rear of tube are copper pipe before described, and front-seat copper pipe heat transfer coefficient is less than the heat transfer coefficient of rear copper pipe.That is to say that this heat exchanger uses the combination of dissimilar copper pipes: the preceding comb of windward side uses the less copper pipe of heat transfer coefficient, and the rear of tube of leeward side uses the bigger copper pipe of heat transfer coefficient.Use the naked body copper pipe as preceding comb, rear of tube uses riffled tube.
Perhaps, the heat transfer coefficient of the described preceding set fin of comb is less than the heat transfer coefficient of the set fin of rear of tube.That is to say that this heat exchanger uses the combination of different sheet shape fins: the front-seat fin of windward side uses the less sheet type of heat transfer coefficient, and back row's fin of leeward side uses the bigger sheet type of heat transfer coefficient.Use plain film as front-seat fin, rear of tube uses back row's fin to use corrugated plate or calking sheet.
Perhaps, the spacing of the described preceding set fin of comb is greater than the spacing of the set fin of rear of tube.That is to say that this heat exchanger uses the combination of different pitch of fins: the front-seat fin of windward side uses bigger sheet spacing, and its heat transfer area is less; Back row's fin of leeward side uses less sheet spacing, and its heat transfer area is bigger.
Perhaps, this heat exchanger also can adopt the combination of two or more implementations of above-mentioned copper pipe or fin simultaneously.
Compared with prior art, the heat transfer coefficient of the front and rear row heat exchanger in the highly effective air-cooled tube wing-type heat exchanger provided by the present invention or heat transfer area difference, can improve the uniformity of temperature difference field, reduce the mean temperature difference of heat exchanger, improve the heat exchange efficiency of heat exchanger.What specify is, the flow direction that the front and rear row of heat exchanger of the present invention is relative air by heat exchanger, windward side is called the front row, and leeward side becomes back row, rather than the front and back on the physical significance.
Description of drawings
Below in conjunction with the drawings and the specific embodiments heat exchanger of the present invention is further described:
Accompanying drawing 1 is for using the side view of detachable wall hanging type air conditioner indoor unit of the present invention;
Accompanying drawing 2 is for using the side view that the present invention is used for window air conditioner;
Accompanying drawing 3 is the vertical view of Fig. 2.
The specific embodiment
Embodiment one:
As shown in Figure 1, adopt to comprise the refrigerating circuit of being made of sealing compressor, condenser, capillary, evaporimeter in the air-conditioner of the present invention, wherein compressor, condenser and capillary are installed in (not shown) in the air-conditioner outdoor unit.The grid of room air on outer cover 109, panel 110 enters indoor set and evaporimeter carries out heat exchange.Comb 103,104 is positioned at the windward side, the outside of evaporimeter rear of tube 105,106 before the evaporimeter.Comb 103,104 and evaporimeter rear of tube 105,106 all are air-cooled tube wing-type heat exchangers before the evaporimeter, are installed on the indoor set base 111, and are furnished with indoor motor 112, axial-flow fan 113.The inboard high pressure feed tube 101 of cold-producing medium inlet chamber behind capillary-compensated, being divided into two-way up and down by three-way pipe 102 enters and is positioned at the outside comb 103,104 before the evaporimeter of layer that facings the wind, enter the evaporimeter rear of tube 105,106 that is positioned at the inboard then, last two-way cold-producing medium is combined into the compressor return air mouth that a route low pressure muffler 108 returns off-premises station through threeway 107.
Comb 103,104 used copper pipes are light pipe before the evaporimeter, and its heat transfer coefficient is less; Evaporimeter rear of tube 105,106 used copper pipes are riffled tube, and its heat transfer coefficient is bigger.Comb 103,104 and evaporimeter rear of tube 105,106 can be made up of two row's evaporimeters of one before the evaporimeter, also can by two independently evaporimeter form, or form by the combination of the two.Need to prove that the position of the preceding comb of evaporimeter, rear of tube is the flow direction of inevitable corresponding cold-producing medium not, in order to make full use of the exchange capability of heat of evaporimeter, the existence that in whole evaporimeter stream, can have shunting and conflux.Different shunting modes, it can be the shunting in comb 103,104 or the evaporimeter rear of tube 105,106 before evaporimeter respectively, also can be the shunting between comb 103,104 and the evaporimeter rear of tube 105,106 before evaporimeter, promptly between double effect evaporator, exist stream to intersect.But no matter how refrigerant flow path is arranged, is in the copper pipe of front-seat windward side and the heat transfer temperature difference Δ T of air side
FBigger, and the Coefficient K of light pipe
FLess; Be in the copper pipe of row windward side, back and the heat transfer temperature difference Δ T of air side
BLess, and the Coefficient K of riffled tube
BBigger.Adopt the copper pipe of identical heat transfer coefficient to compare with front and rear row, this moment front and rear row the heat-transfer capability relative equilibrium of copper pipe, the temperature difference field of whole heat exchanger is comparatively even.
Result of the test shows, evaporimeter rear of tube 105,106 uses a kind of low flute profile inner screw thread copper pipe, all use light pipe to compare with comb, rear of tube before the evaporimeter, after front and rear row used light pipe and riffled tube respectively in the present embodiment, the refrigerating capacity of air-conditioner had increased 13.2%; All use internal thread to compare with comb, rear of tube before the evaporimeter, after front and rear row used light pipe and riffled tube respectively in the present embodiment, the refrigerating capacity of air-conditioner had increased 3.9%.
Embodiment two:
As accompanying drawing 2, shown in Figure 3, use window air conditioner of the present invention and comprise that the air entry by comb 205, evaporimeter rear of tube 206 and compressor 201 before comb 202, condenser rear of tube 203, capillary 204, the evaporimeter before the exhaust outlet of compressor 201, the condenser is communicated with the refrigerating circuit that forms sealing successively.
The forward and backward comb of evaporimeter and the forward and backward comb of condenser all are the air-flow direction of relative and flow through evaporimeter and condenser, and be inevitable corresponding with its physical location.Comb 202 is positioned at the windward side of condenser rear of tube 203 before the condenser, and comb 202 and condenser rear of tube 203 all are air-cooled tube wing-type heat exchangers before the condenser, and are furnished with back air channel 210 and aerofoil fan 211.Comb 205 is positioned at the windward side of evaporimeter rear of tube 206 before the evaporimeter, and comb 205 and evaporimeter rear of tube 206 all are air-cooled tube wing-type heat exchangers before the evaporimeter, and is furnished with primary air separating duct 208 and centrifugal fan 209.The electric system 212 that air-conditioner casing 207 is used to that the parts of above-mentioned refrigeration system are installed and is used to control the air-conditioner operation.
Comb 205 used copper pipes are light pipe before the evaporimeter, and its heat transfer coefficient is less; Evaporimeter rear of tube 206 used copper pipes are a kind of low flute profile riffled tube, and its heat transfer coefficient is bigger.Comb 205 and evaporimeter rear of tube 206 can be made up of two row's evaporimeters of one before the evaporimeter, also can by two independently evaporimeter form, or form by the combination of the two.Be in the copper pipe of front-seat windward side and the heat transfer temperature difference Δ T of air side
FBigger, and the Coefficient K of light pipe
FLess; Be in the copper pipe of row windward side, back and the heat transfer temperature difference Δ T of air side
BLess, and the Coefficient K of riffled tube
BBigger.Adopt the copper pipe of identical heat transfer coefficient to compare with front and rear row, this moment front and rear row the heat-transfer capability relative equilibrium of copper pipe, the temperature difference field of whole heat exchanger is comparatively even.
Computer simulation results shows, evaporimeter rear of tube 206 uses a kind of low flute profile inner screw thread copper pipe, according to identical heat exchanger shunting stringing mode, under the standard condition of GB/T7725 defined, the heat exchange amount of comb reaches 56% of total heat exchange amount before the evaporimeter, and the heat exchange amount of evaporimeter rear of tube reaches total heat exchange amount 44%.When the forward and backward comb of evaporimeter all used light pipe, the heat exchange amount of comb accounted for total heat exchange amount 69% before the evaporimeter, and the heat exchange amount of evaporimeter rear of tube only accounts for 31%.Test shows, all uses light pipe, the forward and backward comb of condenser all to use the plain film of 1.8 millimeters of pitch of fins to compare with the forward and backward comb of evaporimeter, adopts the refrigerating capacity of the air-conditioner of the described technical scheme of present embodiment to increase 18.7%; With comb before and after the forward and backward comb of evaporimeter all uses riffled tube, condenser all single bridge of 1.5 millimeters of pitch of fins sheet of charging compare, adopt the refrigerating capacity of the air-conditioner of the described technical scheme of present embodiment to increase 6.3%.
Claims (7)
1. air-cooled tube wing-type heat exchanger, at least comprise the preceding comb of being located at the heat exchanger windward side and the rear of tube of being located at the heat exchanger leeward side, it is characterized in that: the heat transfer coefficient of described rear of tube is greater than the heat transfer coefficient of preceding comb, and/or the heat transfer area of rear of tube is greater than the heat transfer area of preceding comb.
2. air-cooled tube wing-type heat exchanger according to claim 1 is characterized in that: comb and rear of tube are copper pipe before described, and the heat transfer coefficient of front-seat copper pipe is less than the heat transfer coefficient of rear copper pipe.
3. air-cooled tube wing-type heat exchanger according to claim 2 is characterized in that: comb is the naked body copper pipe before described, and rear of tube is a riffled tube.
4. according to each described air-cooled tube wing-type heat exchanger of claim 1 to 3, it is characterized in that: the heat transfer coefficient of the set fin of comb is less than the heat transfer coefficient of the set fin of rear of tube before described.
5. air-cooled tube wing-type heat exchanger according to claim 4 is characterized in that: described front-seat fin is a plain film, and back row's fin is corrugated plate or calking sheet.
6. according to each described air-cooled tube wing-type heat exchanger of claim 1 to 3, it is characterized in that: the spacing of the set fin of comb is greater than the spacing of the set fin of rear of tube before described.
7. air-cooled tube wing-type heat exchanger according to claim 4 is characterized in that: the spacing of the set fin of comb is greater than the spacing of the set fin of rear of tube before described.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200510121470 CN1991284A (en) | 2005-12-31 | 2005-12-31 | Highly effective air-cooled tube wing-type heat exchanger |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200510121470 CN1991284A (en) | 2005-12-31 | 2005-12-31 | Highly effective air-cooled tube wing-type heat exchanger |
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| Publication Number | Publication Date |
|---|---|
| CN1991284A true CN1991284A (en) | 2007-07-04 |
Family
ID=38213712
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200510121470 Pending CN1991284A (en) | 2005-12-31 | 2005-12-31 | Highly effective air-cooled tube wing-type heat exchanger |
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| Country | Link |
|---|---|
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101963418A (en) * | 2009-07-21 | 2011-02-02 | 江森自控楼宇设备科技(无锡)有限公司 | Micro channel heat exchanger for air-conditioner heat pump |
| CN101793424B (en) * | 2010-02-09 | 2012-06-13 | 董祥顺 | High-powered energy-saving radiator |
| CN105020878A (en) * | 2014-04-17 | 2015-11-04 | 广东美的集团芜湖制冷设备有限公司 | Multi-row heat exchanger and air conditioner |
-
2005
- 2005-12-31 CN CN 200510121470 patent/CN1991284A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101963418A (en) * | 2009-07-21 | 2011-02-02 | 江森自控楼宇设备科技(无锡)有限公司 | Micro channel heat exchanger for air-conditioner heat pump |
| CN101963418B (en) * | 2009-07-21 | 2012-09-05 | 约克（无锡）空调冷冻设备有限公司 | Micro channel heat exchanger for air-conditioner heat pump |
| CN101793424B (en) * | 2010-02-09 | 2012-06-13 | 董祥顺 | High-powered energy-saving radiator |
| CN105020878A (en) * | 2014-04-17 | 2015-11-04 | 广东美的集团芜湖制冷设备有限公司 | Multi-row heat exchanger and air conditioner |
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