CN204514132U - A kind of non-homogeneous fin radiator for Heller type indirect air cooling system - Google Patents
A kind of non-homogeneous fin radiator for Heller type indirect air cooling system Download PDFInfo
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- CN204514132U CN204514132U CN201520227703.8U CN201520227703U CN204514132U CN 204514132 U CN204514132 U CN 204514132U CN 201520227703 U CN201520227703 U CN 201520227703U CN 204514132 U CN204514132 U CN 204514132U
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Abstract
The utility model discloses a kind of non-homogeneous fin radiator for Heller type indirect air cooling system, described non-homogeneous fin radiator is divided into top, middle part and bottom along short transverse, and this trizonal height is respectively h
1, h
2and h
3, the radiating fin distribute spacing of top, middle part and bottom is respectively d
1, d
2and d
3; As 0.02H≤h
1≤ 0.25H, 0.5H≤h
2≤ 0.96H, 0.02H≤h
3during≤0.25H, 1.1d≤d
1≤ 3.5d, d
2=d, 1.1d≤d
3≤ 3.5d, wherein H is the radiator length comprising radiating fin, and d is the spacing of fin of radiating fin when being evenly arranged.The utility model optimizes the distribution of fin, reduces bottom radiator and the flowing resistance at top, has slackened the whirlpool of radiator dorsal area, enhanced the overall heat exchange performance of radiator, simultaneously due to the minimizing of fin number, also saves a small amount of bauxite resource.
Description
Technical field
The utility model relates to a kind of non-homogeneous fin radiator for Heller type indirect air cooling system.
Background technology
Dry cooling tower or direct air cooling system are compared with the fired power generating unit of employing wet cooling tower, and can economize on water 65%-90%, and this sustainable development for rich coal water-deficient area power industry has great importance.Dry cooling systems can be divided into direct air cooled system to unify indirect air cooling system (calling a cooling system in the following text), and according to the pattern of condenser and the difference of radiator position, a cooling system can be divided into again Hai Leshi, Harmon formula, SCAL type.Between cooling system due to air water two white heat be contactless heat transfer, therefore cooling the limit be the dry-bulb temperature of surrounding air, make average coal consumption comparatively wet type cooling unit coal consumption height 3.3%-6.2%.In addition, the quality of cooling system service behaviour directly has influence on vacuum and the net coal consumption rate of condenser.Data show: cooling tower outlet water temperature often reduces by 1 DEG C, and condenser vacuum change 0.4KPa, affects net coal consumption rate about 1g/kwh.
Between Hai Leshi, the core component of cooling system is the outer vertically arranged good fortune brother type aluminum pipe aluminum fin-stock radiator of injection type condenser, indirect cool tower and tower, the type radiator is also referred to as Hungary's good fortune brother (Forgo) type radiator, be made up of pipe type finned-tube bundle, structure is the large fin of round tube overcoat of full aluminum, water effluent journey is double-flow, and the broad form being applied to engineering reality at present has the 5th Dai Haile-Fu Ge (Heller-Forgo) T60 type 6 comb and the 6th Dai Fuge type 4 comb.
It is the process that a heat absorption heats up that air flows through spreader region, the good fortune brother type radiator that this fin is evenly arranged is in actual moving process, for bottom radiator and top area, Local Heat Transfer area is identical with central region, but due to the impact of ground and top closing plate, make air velocity lower, this region Local Heat Transfer ability certainly will be caused lower than radiator central region, based on the optimum air force field theory of cooling tower, aerodynamic field everywhere, temperature field and the alternate heat transfer driving force of air water two more balanced, overall heat exchange ability is stronger, therefore the radiator air aerodynamic field that is evenly arranged of fin and Local Heat Transfer area are not best matching relationship, simultaneously due to the difference along short transverse air velocity, easily there is longitudinal whirlpool in radiator back face, produce local resistance, be unfavorable for the circulation of air, on the whole and be unfavorable for the heat radiation of radiator, cause the cooling effectiveness of air cooling tower to reduce.
Utility model content
In order to solve the shortcoming of prior art, the utility model provides a kind of non-homogeneous fin radiator for Heller type indirect air cooling system.
The utility model is by the following technical solutions:
For a non-homogeneous fin radiator for Heller type indirect air cooling system, comprise some cooling elements, described cooling element comprises four cooling tube bundles in parallel, and cooling tube bundle two ends in parallel are provided with tube sheet, and described tube sheet is fixed on connecting plate; Described cooling tube bundle, comprises pipe, radiating fin and stiffener, and described radiating fin and stiffener are equipped with preformed hole, and described pipe passes the preformed hole of radiating fin and stiffener; Some described cooling elements are cascaded to be fixed on connecting plate and form cooling stud; The top of described cooling stud is provided with top hydroecium, and the bottom of cooling stud is provided with bottom hydroecium; Described tube sheet bolt and connecting plate are fixed.Described radiating fin is aluminium matter radiating fin, and radiating fin is shaping by pressing.Described pipe and radiating fin and stiffener adopt expanding joint method to fix.Described pipe is for comprising aluminum pipe.The material of described stiffener is aluminium alloy.The outer likeness in form I-steel of described stiffener.
Non-homogeneous fin radiator of the present utility model is divided into top, middle part and region, three, bottom along short transverse, and the height of described top, middle part and bottom is respectively h
1, h
2and h
3, the trizonal radiating fin distribute spacing in described top, middle part and bottom is respectively d
1, d
2and d
3; As 0.02H≤h
1≤ 0.25H, 0.5H≤h
2≤ 0.96H, 0.02H≤h
3during≤0.25H, 1.1d≤d
1≤ 3.5d, d
2=d, 1.1d≤d
3≤ 3.5d, wherein, H is the radiator length comprising radiating fin, and d is the spacing of fin of radiating fin when being evenly arranged.
Height when the top of non-homogeneous fin radiator, middle part and bottom meets: 0.02H≤h
1=h
3≤ 0.25H, and 0.5H≤h
2during≤0.96H, 1.1d≤d
1=d
3≤ 3.5d, d
2=d.
Described non-homogeneous fin radiator is divided into top, middle part and bottom along short transverse, when the ratio that described top, middle part and bottom account for non-homogeneous fin radiator total height is respectively 5%, 85% and 10%, and d
1=2d, d
2=d, d
3=1.8d.
Described non-homogeneous fin radiator is divided into top, middle part and bottom along short transverse, when the ratio that described top, middle part and bottom account for non-homogeneous fin radiator total height is respectively 10%, 80% and 10%, and d
1=d
3=1.8d, d
2=d.
Described non-homogeneous fin radiator is divided into top, middle part and bottom along short transverse, when the ratio that described top, middle part and bottom account for non-homogeneous fin radiator total height is respectively 15%, 70% and 15%, and d
1=d
3=1.6d, d
2=d.
Described non-homogeneous fin radiator is divided into top, middle part and bottom along short transverse, when the ratio that described top, middle part and bottom account for non-homogeneous fin radiator total height is respectively 20%, 60% and 20%, and d
1=d
3=1.6d, d
2=d.
The beneficial effects of the utility model are:
(1) fin of the present utility model is according to the outer actual wind speed regularity of distribution of Hai Leshi dry Cooling heat radiator, based on the optimum air force field theory of cooling tower, optimize the distribution of fin, reduce bottom radiator and the flowing resistance at top, slacken the whirlpool of radiator dorsal area, enhance bottom radiator and the heat exchange at top, radiator is more balanced along short transverse heat exchange, thus enhance the overall heat exchange performance of radiator, simultaneously due to the minimizing of fin number, also save a small amount of bauxite resource;
(2) the utility model not only can be used for the 5th Dai Haile-Fu Ge (Heller-Forgo) T60 type 6 comb, also can be used for the 6th Dai Fuge type 4 comb.
Accompanying drawing explanation
Fig. 1 (a) is Heller-Forgo T60 type aluminium circular tube structure schematic diagram;
Fig. 1 (b) is Heller-Forgo T60 type aluminum fin-stock structural representation;
Fig. 2 is cooling tube bundle structural representation;
Fig. 3 is cooling element structural representation;
Fig. 4 is the heat spreader structures schematic diagram of embodiment one, two, three, four;
Wherein, 1, aluminium pipe; 2, radiating fin; 3, aluminium circular hole; 4, turbulent flow reinforced structure; 5, stiffener; 6, tube sheet; 7, connecting plate; 8, top hydroecium; 9, bottom hydroecium.
Detailed description of the invention
Below in conjunction with accompanying drawing and embodiment, the utility model is described further:
Based on the above analysis to good fortune brother type radiator shortcoming in actual moving process that fin is evenly arranged, following optimization is done to the fin of good fortune brother type radiator: for the 5th Dai Haile-Fu Ge (Heller-Forgo) T60 type 6 comb, the structure composition of non-homogeneous fin radiator is described, the utility model does not change the size of original fin radiator, material, manufacturing process and connected mode, only makes the appropriate adjustments the distribution mode of radiating fin.
Non-homogeneous fin radiator of the present utility model is divided into top, middle part and region, three, bottom along short transverse, and the height of described top, middle part and bottom is respectively h
1, h
2and h
3, the trizonal radiating fin distribute spacing in described top, middle part and bottom is distributed as d
1, d
2and d
3; As 0.02H≤h
1≤ 0.25H, 0.5H≤h
2≤ 0.96H, 0.02H≤h
3during≤0.25H, 1.1d≤d
1≤ 3.5d, d
2=d, 1.1d≤d
3≤ 3.5d, wherein, H is the radiator length comprising radiating fin, and d is the spacing of fin of radiating fin when being evenly arranged.
Height when the top of non-homogeneous fin radiator, middle part and bottom meets: 0.02H≤h
1=h
3≤ 0.25H, and 0.5H≤h
2during≤0.96H, 1.1d≤d
1=d
3≤ 3.5d, d
2=d.
As shown in Fig. 1 (a), be the structural representation of Heller-Forgo T60 type aluminium pipe, the external diameter of aluminium pipe 1 is 17.75mm, and thickness is 0.75mm; Radiating fin 2, the large plate fin of aluminium, fin thickness is 0.33mm, and former spacing of fin is 2.88mm.
As shown in Fig. 1 (b), 4 is turbulent flow reinforced structure, aluminium pipe 1 Heterogeneous Permutation, longitudinal pitch is 30mm, and be laterally airflow direction, aluminium pipe 1 arranges six rows, centre-to-centre spacing is 25mm, radiating fin 2 is shaping by pressing, and aluminium pipe 1 through aluminium circular hole 3 reserved on radiating fin 2, and adopts expanding joint method to fix with radiating fin 2.
Fig. 2 is cooling tube bundle structural representation.In figure, the material of stiffener 5 is aluminium alloy, outer likeness in form I-steel, high 170mm, long 599mm, thick 6mm, and box out in centre, aluminium pipe 1 passes in hole; Each tube bank is by the aluminium pipe 1 of 60 long 4840mm.
Fig. 3 is cooling element structural representation.In figure, the material of tube sheet 6 is aluminium alloy, leaves pore and bolt hole; Four cooling tube bundles form a cooling element by tube sheet 6 parallel connection, and this element is the most elementary cell of radiator, is composed in series the cooling stud of various length, i.e. radiator by it.
Fig. 4 is heat spreader structures schematic diagram, and each cooling stud is in series by several cooling elements, and two ends tube sheet bolt and connecting plate 7 are fixed, and cooling stud top is connected with top hydroecium 8, and bottom is connected with bottom hydroecium 9, fixes between hydroecium and tube sheet with bolt.
Embodiment one:
Radiator is divided into three parts according to short transverse by the present embodiment, top, middle part, bottom, and the ratio that three parts account for total height is respectively 5%, 85% and 10%, top spacing of fin d
1=2d=5.76mm, bottom fin spacing is d
3=1.8d=5.184mm, other parameter constants of fin, wherein d is the spacing of fin of radiating fin when being evenly arranged, 2.88mm.
Embodiment two:
Radiator is divided into three parts according to short transverse by this embodiment, top, middle part, bottom, and the ratio that three parts account for total height is respectively 10%, 80% and 10%, and the spacing of fin of top and bottom is d
1=d
3=1.8d=5.184mm, other parameter constants of fin.
Embodiment three:
Radiator is divided into three parts according to short transverse by this embodiment, top, middle part, bottom, and the ratio that three parts account for total height is respectively 15%, 70% and 15%, and the spacing of fin of top and bottom is d
1=d
3=1.6d=4.608mm, other parameter constants of fin.
Embodiment four:
Radiator is divided into three parts according to short transverse by this embodiment, top, middle part, bottom, and the ratio that three parts account for total height is respectively 20%, 60% and 20%, and the spacing of fin of top and bottom is d
1=d
3=1.2d=4.032mm, other parameter constants of fin.
Radiating principle of the present utility model is:
(1) when heat radiator fin is evenly arranged along short transverse
Radiator inlet air flow velocity is as follows along the regularity of distribution of short transverse: owing to affecting by ground drag, at lower position place, wind speed is less, along with the increase of height, wind speed increases gradually, intermediate range wind speed greatly about radiator reaches maximum, radiator top area, due to the impact by top closing plate between radiator and tower edge, wind speed diminishes again, because local area of dissipation is identical, therefore cause along short transverse local heat dissipation capacity different, the heat-sinking capability of the radiator of top and bottom section does not maximize; Air enters air cooling tower after flowing through radiator, and along radiator short transverse, air velocity is different, easily produces longitudinal whirlpool, forms local resistance, is unfavorable for the circulation of air, is unfavorable for the heat radiation of radiator on the whole, cause the cooling effectiveness of air cooling tower to reduce.
(2) when heat radiator fin is along the uneven layout of short transverse
(2.1) when the radiating fin distribute spacing of radiator top and bottom and middle part unequal, owing to increasing the spacing of fin at top and bottom, reduce the local resistance of radiator, air velocity increases, the ventilation in this region increases, the local area of dissipation in this region is mated more with air velocity, and local heat-sinking capability is improved.Known based on the optimum aerodynamic field theory analysis of cooling tower, integral heat sink effect is better than the radiator that fin is evenly arranged.
(2.2) because the air velocity in top and bottom heat spreader region increases, make along short transverse, the air velocity of radiator dorsal area balances more, therefore the generative capacity reducing the longitudinal whirlpool in this region and the local resistance brought by whirlpool, advantageously in the heat radiation of radiator.
By reference to the accompanying drawings detailed description of the invention of the present utility model is described although above-mentioned; but the restriction not to the utility model protection domain; one of ordinary skill in the art should be understood that; on the basis of the technical solution of the utility model, those skilled in the art do not need to pay various amendment or distortion that creative work can make still within protection domain of the present utility model.
Claims (6)
1. for a non-homogeneous fin radiator for Heller type indirect air cooling system, it is characterized in that, described non-homogeneous fin radiator is divided into top, middle part and region, three, bottom along short transverse, and the height of described top, middle part and bottom is respectively h
1, h
2and h
3, the trizonal radiating fin distribute spacing in described top, middle part and bottom is respectively d
1, d
2and d
3; As 0.02H≤h
1≤ 0.25H, 0.5H≤h
2≤ 0.96H, 0.02H≤h
3during≤0.25H, 1.1d≤d
1≤ 3.5d, d
2=d, 1.1d≤d
3≤ 3.5d, wherein, H is the radiator length comprising radiating fin, and d is the spacing of fin of radiating fin when being evenly arranged.
2. a kind of non-homogeneous fin radiator for Heller type indirect air cooling system as claimed in claim 1, is characterized in that, the height when the top of described non-homogeneous fin radiator, middle part and bottom meets: 0.02H≤h
1=h
3≤ 0.25H, and 0.5H≤h
2during≤0.96H, 1.1d≤d
1=d
3≤ 3.5d, d
2=d.
3. a kind of non-homogeneous fin radiator for Heller type indirect air cooling system as claimed in claim 1, it is characterized in that, described non-homogeneous fin radiator is divided into top, middle part and bottom along short transverse, when the ratio that described top, middle part and bottom account for non-homogeneous fin radiator total height is respectively 5%, 85% and 10%, d
1=2d, d
2=d, d
3=1.8d.
4. a kind of non-homogeneous fin radiator for Heller type indirect air cooling system as claimed in claim 1, it is characterized in that, described non-homogeneous fin radiator is divided into top, middle part and bottom along short transverse, when the ratio that described top, middle part and bottom account for non-homogeneous fin radiator total height is respectively 10%, 80% and 10%, d
1=d
3=1.8d, d
2=d.
5. a kind of non-homogeneous fin radiator for Heller type indirect air cooling system as claimed in claim 1, it is characterized in that, described non-homogeneous fin radiator is divided into top, middle part and bottom along short transverse, when the ratio that described top, middle part and bottom account for non-homogeneous fin radiator total height is respectively 15%, 70% and 15%, d
1=d
3=1.6d, d
2=d.
6. a kind of non-homogeneous fin radiator for Heller type indirect air cooling system as claimed in claim 1, it is characterized in that, described non-homogeneous fin radiator is divided into top, middle part and bottom along short transverse, when the ratio that described top, middle part and bottom account for non-homogeneous fin radiator total height is respectively 20%, 60% and 20%, d
1=d
3=1.6d, d
2=d.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520227703.8U CN204514132U (en) | 2015-04-15 | 2015-04-15 | A kind of non-homogeneous fin radiator for Heller type indirect air cooling system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520227703.8U CN204514132U (en) | 2015-04-15 | 2015-04-15 | A kind of non-homogeneous fin radiator for Heller type indirect air cooling system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204514132U true CN204514132U (en) | 2015-07-29 |
Family
ID=53712101
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520227703.8U Withdrawn - After Issue CN204514132U (en) | 2015-04-15 | 2015-04-15 | A kind of non-homogeneous fin radiator for Heller type indirect air cooling system |
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|---|---|
| CN (1) | CN204514132U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104729329A (en) * | 2015-04-15 | 2015-06-24 | 山东大学 | Nonuniform finned radiator for Heller type indirect air cooling system |
| CN107305105A (en) * | 2016-04-25 | 2017-10-31 | 江苏科力普汽车部件有限公司 | A kind of circular pipe type radiator core body |
-
2015
- 2015-04-15 CN CN201520227703.8U patent/CN204514132U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104729329A (en) * | 2015-04-15 | 2015-06-24 | 山东大学 | Nonuniform finned radiator for Heller type indirect air cooling system |
| CN104729329B (en) * | 2015-04-15 | 2016-08-24 | 山东大学 | A kind of non-homogeneous fin radiator for Heller type indirect air cooling system |
| CN107305105A (en) * | 2016-04-25 | 2017-10-31 | 江苏科力普汽车部件有限公司 | A kind of circular pipe type radiator core body |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20150729 Effective date of abandoning: 20160824 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |