CN209672488U - Fin-tube type heat exchanger, air-conditioner outdoor unit and air conditioner - Google Patents
Fin-tube type heat exchanger, air-conditioner outdoor unit and air conditioner Download PDFInfo
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- CN209672488U CN209672488U CN201920334399.5U CN201920334399U CN209672488U CN 209672488 U CN209672488 U CN 209672488U CN 201920334399 U CN201920334399 U CN 201920334399U CN 209672488 U CN209672488 U CN 209672488U
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Abstract
It includes the air-conditioner outdoor unit that the utility model, which discloses a kind of fin-tube type heat exchanger, air-conditioner outdoor unit and air conditioner, the air conditioner,.The air-conditioner outdoor unit includes fin-tube type heat exchanger.The fin-tube type heat exchanger includes multiple fins and the more refrigerant pipes through multiple fins, in which: the caliber D of the refrigerant pipe meets 4mm≤D≤6mm；The total pipe range Z of the refrigerant pipe of the fin-tube type heat exchangerLWith the nominal capacity Q of fin-tube type heat exchanger, meet ZLmin≤ZL≤ZLmax, ZLmin=6.39m/kW*Q-4.10m/mm*D+28.8m, ZLmax=10.9m/kW*Q-6.42m/mm*D+45.2m；Wherein: total pipe range ZLUnit be m；The unit of nominal capacity Q is kW.The fin-tube type heat exchanger of the utility model can standardize and choose total refrigerant pipe pipe range, and then improve the heat exchange efficiency and Energy Efficiency Ratio of heat exchanger.
Description
Technical field
The utility model relates to technical field of heat exchangers, in particular to a kind of fin-tube type heat exchanger, air-conditioner outdoor unit and sky
Adjust device.
Background technique
The caliber of the refrigerant pipe of usual heat exchanger is larger (usually 7mm~9.5mm), heat exchange of the refrigerant inside refrigerant pipe
Efficiency is lower, causes the heat transfer effect of heat exchanger poor.Research finds the caliber of reduction refrigerant pipe, can improve changing for heat exchanger
Thermal effect.But if directly using heat exchanger instead caliber lesser refrigerant pipe, the refrigerant pipe of this small diameter tube flows refrigerant
Resistance it is larger, if the overall length of refrigerant pipe is longer, be easy to cause the biggish pressure loss, and then lead to the heat exchange efficiency of heat exchanger
Decline.
Utility model content
The main purpose of the utility model is to propose a kind of fin-tube type heat exchanger, it is intended to specification chooses total refrigerant pipe pipe range,
Improve the heat exchange efficiency and Energy Efficiency Ratio of heat exchanger.
To achieve the above object, the utility model proposes a kind of fin-tube type heat exchanger, the fin-tube type heat exchanger includes more
A fin and more refrigerant pipes through multiple fins, in which: the caliber D of the refrigerant pipe meets 4mm≤D≤6mm；Institute
State the total pipe range Z of the refrigerant pipe of fin-tube type heat exchangerLWith the nominal capacity Q of fin-tube type heat exchanger, meet ZLmin≤ZL≤
ZLmax, ZLmin=6.39m/kW*Q-4.10m/mm*D+28.8m, ZLmax=10.9m/kW*Q-6.42m/mm*D+45.2m；Wherein:
Total pipe range ZLUnit be m；The unit of nominal capacity Q is kW.
In one embodiment, the nominal capacity Q meets 2kW≤Q≤12kW, the total pipe range Z of the refrigerant pipeLMeet
20.72m≤ZL≤150m。
In one embodiment, the nominal capacity Q meets 2kW≤Q≤2.6kW, the total pipe range Z of the refrigerant pipeLSymbol
Close 21.73m≤ZL≤26.81m。
In one embodiment, the nominal capacity Q meets 2.6kW < Q≤3.5kW, the total pipe range Z of the refrigerant pipeL
Meet 39.32m~61.78m.
In one embodiment, the nominal capacity Q meets 3.5kW < Q≤5.1kW, the total pipe range Z of the refrigerant pipeL
Meet 40.52m≤ZL≤62.39m。
In one embodiment, the nominal capacity Q meets 5.1kW < Q≤7.2kW, the total pipe range Z of the refrigerant pipeL
Meet 63.50m≤ZL≤87.15m。
In one embodiment, the nominal capacity Q meets 7.2kW < Q≤12kW, the total pipe range Z of the refrigerant pipeLSymbol
Close 95.5m≤ZL≤123.56m。
In one embodiment, the width P of the finrMeet 10mm≤Pr≤ 26mm, between the two neighboring refrigerant pipe
Tube spacing PtMeet 10mm≤Pt≤23mm。
In one embodiment, the spacing of fin P between the two neighboring finfMeet 1.1mm≤Pf≤1.6mm。
In one embodiment, the fin be sheet type fin perhaps corrugated fin perhaps fenestration fin or
Bridge shape fin.
In one embodiment, the surface of the fin is provided with hydrophilic layer.
The utility model also provides a kind of air-conditioner outdoor unit and air conditioner, and the air conditioner includes air conditioner indoor unit and described
Air-conditioner outdoor unit.The air-conditioner outdoor unit is connect with the air conditioner indoor unit by refrigerant pipe.The air-conditioner outdoor unit includes pipe
Fin heat exchanger.The fin-tube type heat exchanger includes multiple fins and the more refrigerant pipes through multiple fins, in which: institute
The caliber D for stating refrigerant pipe meets 4mm≤D≤6mm；The total pipe range Z of the refrigerant pipe of the fin-tube type heat exchangerLWith tube fin type heat exchange
The nominal capacity Q of device, meets ZLmin≤ZL≤ZLmax, ZLmin=6.39m/kW*Q-4.10m/mm*D+28.8m, ZLmax=
10.9m/kW*Q-6.42m/mm*D+45.2m；Wherein: total pipe range ZLUnit be m；The unit of the nominal capacity Q is kW.
The technical solution of the utility model, the caliber D by limiting refrigerant pipe meet 4mm≤D≤6mm, the fin-tube type
The total pipe range Z of the refrigerant pipe of heat exchangerLWith the nominal capacity Q of fin-tube type heat exchanger, meet ZLmin≤ZL≤ZLmax, ZLmin=
6.39m/kW*Q-4.10m/mm*D+28.8m ZLmax=10.9m/kW*Q-6.42m/mm*D+45.2m；Wherein: total pipe range ZL's
Unit is m；The unit of the nominal capacity Q is kW, with the selection of the total refrigerant pipe pipe range of specification, it is ensured that fin-tube type heat exchanger energy
While enough refrigerant pipes used compared with small diameter tube (4mm~6mm), total tube side resistance of the fin-tube type heat exchanger is smaller, reduces it
The pressure loss obtains preferable heat exchange property.
Detailed description of the invention
In order to illustrate the embodiment of the utility model or the technical proposal in the existing technology more clearly, below will be to embodiment
Or attached drawing needed to be used in the description of the prior art is briefly described, it should be apparent that, the accompanying drawings in the following description is only
It is some embodiments of the utility model, for those of ordinary skill in the art, in the premise not made the creative labor
Under, the structure that can also be shown according to these attached drawings obtains other attached drawings.
Fig. 1 is the top view of the utility model fin-tube type heat exchanger (single) embodiment；
Fig. 2 is the top view of fin-tube type heat exchanger in Fig. 1；
Fig. 3 is top view of the fin-tube type heat exchanger before bending in Fig. 2；
Fig. 4 is the partial schematic diagram of the fin of fin-tube type heat exchanger in Fig. 1；
Fig. 5 is the top view of the utility model fin-tube type heat exchanger (double) embodiment；
Fig. 6 is the top view of fin-tube type heat exchanger in Fig. 5；
Fig. 7 is top view of the fin-tube type heat exchanger before bending in Fig. 6.
Drawing reference numeral explanation:
| Label | Title | Label | Title |
| 100 | Fin-tube type heat exchanger | 120 | Refrigerant pipe |
| 110 | Fin |
The utility model aim is realized, the embodiments will be further described with reference to the accompanying drawings for functional characteristics and advantage.
Specific embodiment
The following will be combined with the drawings in the embodiments of the present invention, carries out the technical scheme in the embodiment of the utility model
Clearly and completely describing, it is clear that described embodiment is only a part of the embodiment of the utility model, rather than all
Embodiment.Based on the embodiments of the present invention, those of ordinary skill in the art are not making creative work premise
Under every other embodiment obtained, fall within the protection scope of the utility model.
It is to be appreciated that if related in the utility model embodiment directionality instruction (such as upper and lower, left and right, it is preceding,
Afterwards ...), then directionality instruction is only used for explaining opposite between each component under a certain particular pose (as shown in the picture)
Positional relationship, motion conditions etc., if the particular pose changes, directionality instruction is also correspondingly changed correspondingly.
In addition, if relating to the description of " first ", " second " etc. in the utility model embodiment, " first ", " the
Two " etc. description is used for description purposes only, and is not understood to indicate or imply its relative importance or is implicitly indicated meaning
The quantity of the technical characteristic shown." first " is defined as a result, the feature of " second " can explicitly or implicitly include at least one
A this feature.It in addition, the technical solution between each embodiment can be combined with each other, but must be with ordinary skill
Based on personnel can be realized, this technical side will be understood that when the combination of technical solution appearance is conflicting or cannot achieve
The combination of case is not present, also not within the protection scope of the requires of the utility model.
The utility model discloses a kind of fin-tube type heat exchanger and air-conditioner outdoor unit.The air-conditioner outdoor unit includes the pipe wing
Formula heat exchanger.The air-conditioner outdoor unit includes shell, is mounted on the intracorporal wind wheel component of the shell and fin-tube type heat exchanger.
Such as, but not limited to, the wind wheel component includes axial-flow windwheel.The fin-tube type heat exchanger can be the straight of in line shape setting
Row pipe fin type heat exchanger is also possible to the bending fin-tube type heat exchanger of substantially L-shaped bending setting.
Fig. 1 and Fig. 2 are please referred to, the fin-tube type heat exchanger 100 of the utility model including multiple fins 110 and runs through multiple institutes
State more refrigerant pipes 120 of fin 110.On the thickness direction of the fin-tube type heat exchanger 100, the more refrigerant pipes 120
It in single setting (such as Fig. 2) or can be in multiple rows of setting (such as Fig. 6).Every row's refrigerant pipe 120 includes more and changes along the fin-tube type
The refrigerant pipe 120 that the short transverse of hot device 100 is intervally arranged.Here, the caliber D of refrigerant pipe 120 meets 4mm≤D≤6mm, it is cold
Matchmaker's pipe 120 belongs to small diameter tube refrigerant pipe, relative to conventional Large Diameter Pipeline refrigerant pipe (caliber usually in 7mm or more) for, the tubule
Diameter refrigerant pipe can improve the heating capacity of fin-tube type heat exchanger 100.
Particularly, the total pipe range Z of heat exchanging pipe 120LFor the sum of the pipe range of all U-tubes of fin-tube type heat exchanger 100.
For the U-tube, two adjacent refrigerant pipes connect to form the U-tube for the setting that is in U-shape.So, it is assumed that the number of U-tube
Amount is M, and the quantity of refrigerant pipe is m, and a height of L that rises of refrigerant pipe then has M=2m, ZL=ML=2mL.
For the high L that rises of refrigerant pipe, by taking the fin-tube type heat exchanger of bending as an example, the fin-tube type heat exchanger packet of the bending
Include the first in line part 101, the second in line part 102, and be located at the first in line part 101 and the second in line part 102 it
Between arch section 103.It is assumed that: one end further away from the second in line part 102 of the first in line part 101, it is in line to second
The distance of part 102 is L1；One end further away from the first in line part 101 of second in line part 102, it is in line to described first
The distance of part 101 is L2；The radius of the corresponding circle of arch section 103 is R, then its arc length is π R/2.So, the high L that rises
With L1、L2, there are following relationships by R: the high L=L that rises1+L2- 2R+ π R/2 ± 3%.
Since the caliber of the refrigerant pipe 120 reduces, the refrigerant pipe total pipe range ZLIt needs to rationally design again.If institute
State refrigerant pipe total pipe range ZLToo short, refrigerant exchanges heat insufficient in heat exchanger, and the exchange capability of heat of the fin-tube type heat exchanger 100 is also
Less than guarantee.And if the refrigerant pipe total pipe range ZLToo long, the cost of refrigerant pipe 120 is larger.Therefore, the refrigerant pipe general pipeline
Long ZLCertain selection standard should preferably be met.
In order to study the refrigerant pipe total pipe range Z of the fin-tube type heat exchanger 100LInfluence to its heat transfer effect, in refrigerant
The caliber D of pipe 120 meets within the scope of 4mm≤D≤6mm (such as 4mm, 5mm, 6mm), controls the name of fin-tube type heat exchanger 100
In the case that refrigerating capacity is certain, to total refrigerant pipe pipe range Z of fin-tube type heat exchanger 100LAnd cost performance (the ratio of Energy Efficiency Ratio and cost
Value) carrying out following multinomial experiment, (wherein: Q ' indicates actual refrigerating capacity；APF indicates Energy Efficiency Ratio；C indicates cost；CP cost performance):
Experiment acquisition table 1-1 to table 1-7 is carried out for the fin-tube type heat exchanger that refrigerant pipe caliber is 4mm:
When table 1-1.Q=2000W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(kW) | APF(W/W) | C (member) | CP |
| Experiment 1 | 18.20 | 1700 | 3.80 | 35.0 | 0.1086 |
| Experiment 2 | 20.72 | 2056 | 5.16 | 38.0 | 0.1358 |
| Experiment 3 | 26.64 | 2103 | 5.33 | 41.9 | 0.1273 |
| Experiment 4 | 32.56 | 2225 | 5.48 | 48.0 | 0.1142 |
| Experiment 5 | 35.56 | 2325 | 5.49 | 65.2 | 0.0842 |
When table 1-2.Q=2300W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(kW) | APF(W/W) | C (member) | CP |
| Experiment 1 | 18.20 | 2100 | 3.67 | 35.0 | 0.1049 |
| Experiment 2 | 21.73 | 2280 | 5.03 | 38.0 | 0.1324 |
| Experiment 3 | 27.84 | 2293 | 5.24 | 41.9 | 0.1252 |
| Experiment 4 | 33.59 | 2340 | 5.36 | 48.0 | 0.1117 |
| Experiment 5 | 35.56 | 2450 | 5.38 | 65.2 | 0.0825 |
When table 1-3.Q=2600W, the experimental data of fin-tube type heat exchanger
When table 1-4.Q=3500W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(kW) | APF(W/W) | C (member) | CP |
| Experiment 1 | 40.20 | 2975 | 3.70 | 85.2 | 0.0434 |
| Experiment 2 | 47.75 | 3368 | 4.77 | 87.6 | 0.0545 |
| Experiment 3 | 61.39 | 3438 | 4.89 | 102.6 | 0.0477 |
| Experiment 4 | 75.03 | 3533 | 5.00 | 107.6 | 0.0465 |
| Experiment 5 | 80.32 | 3536 | 5.01 | 117.5 | 0.0426 |
When table 1-5.Q=5100W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(W) | APF(W/W) | C (member) | CP |
| Experiment 1 | 53.63 | 3562 | 3.45 | 160.2 | 0.0215 |
| Experiment 2 | 65.81 | 4998 | 4.27 | 171.6 | 0.0249 |
| Experiment 3 | 79.56 | 5050 | 4.39 | 188.6 | 0.0233 |
| Experiment 4 | 91.74 | 5123 | 4.70 | 195.3 | 0.0241 |
| Experiment 5 | 103.50 | 5135 | 4.71 | 217.5 | 0.0217 |
When table 1-6.Q=7200W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(W) | APF(W/W) | C (member) | CP |
| Experiment 1 | 61.39 | 7050 | 3.19 | 228.60 | 0.0140 |
| Experiment 2 | 68.04 | 7180 | 3.97 | 244.6 | 0.0162 |
| Experiment 3 | 86.94 | 7225 | 4.18 | 272.5 | 0.0153 |
| Experiment 4 | 105.84 | 7298 | 4.35 | 290.5 | 0.0150 |
| Experiment 5 | 135.84 | 7305 | 4.37 | 303.5 | 0.0144 |
When table 1-7.Q=12000W, the experimental data of fin-tube type heat exchanger
Experiment acquisition table 2-1 to table 2-7 is carried out for the fin-tube type heat exchanger that refrigerant pipe caliber is 5mm:
When table 2-1.Q=2000W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(W) | APF(W/W) | C (member) | CP |
| Experiment 1 | 17.89 | 1958 | 3.89 | 42.0 | 0.0926 |
| Experiment 2 | 19.34 | 2056 | 4.91 | 45.0 | 0.1091 |
| Experiment 3 | 24.86 | 2103 | 5.21 | 52.9 | 0.0985 |
| Experiment 4 | 30.39 | 2225 | 5.51 | 58.7 | 0.0938 |
| Experiment 5 | 32.50 | 2245 | 5.51 | 63.7 | 0.0864 |
When table 2-2.Q=2300W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(W) | APF(W/W) | C (member) | CP |
| Experiment 1 | 17.89 | 2058 | 3.49 | 42.0 | 0.0831 |
| Experiment 2 | 20.81 | 2280 | 4.96 | 45.0 | 0.1103 |
| Experiment 3 | 25.97 | 2293 | 5.17 | 52.9 | 0.0978 |
| Experiment 4 | 31.07 | 2340 | 5.32 | 60.7 | 0.0876 |
| Experiment 5 | 32.50 | 2245 | 5.41 | 63.7 | 0.0849 |
When table 2-3.Q=2600W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(W) | APF(W/W) | C (member) | CP |
| Experiment 1 | 19.34 | 2380 | 3.96 | 47.0 | 0.0843 |
| Experiment 2 | 22.73 | 2480 | 4.81 | 52.9 | 0.0909 |
| Experiment 3 | 29.23 | 2550 | 5.29 | 58.0 | 0.0911 |
| Experiment 4 | 35.72 | 2645 | 5.49 | 63.1 | 0.0869 |
| Experiment 5 | 44.56 | 3368 | 5.59 | 83.7 | 0.0668 |
When table 2-4.Q=3500W, the experimental data of fin-tube type heat exchanger
When table 2-5.Q=5100W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(W) | APF(W/W) | C (member) | CP |
| Experiment 1 | 35.72 | 4832 | 3.18 | 196.1 | 0.0162 |
| Experiment 2 | 46.57 | 4998 | 4.10 | 203.3 | 0.0202 |
| Experiment 3 | 58.37 | 5050 | 4.35 | 241.3 | 0.0180 |
| Experiment 4 | 72.45 | 5123 | 4.47 | 259.4 | 0.0172 |
| Experiment 5 | 81.13 | 5225 | 4.51 | 270.1 | 0.0167 |
When table 2-6.Q=7200W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(W) | APF(W/W) | C (member) | CP |
| Experiment 1 | 57.29 | 6850 | 2.95 | 261.3 | 0.0113 |
| Experiment 2 | 63.50 | 7180 | 3.96 | 289.6 | 0.0137 |
| Experiment 3 | 81.13 | 7225 | 4.01 | 320.1 | 0.0125 |
| Experiment 4 | 98.77 | 7298 | 4.32 | 350.5 | 0.0123 |
| Experiment 5 | 114.58 | 7385 | 4.52 | 522.6 | 0.0086 |
When table 2-7.Q=12000W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(W) | APF(W/W) | C (member) | CP |
| Experiment 1 | 81.13 | 9725 | 2.01 | 390.1 | 0.0051 |
| Experiment 2 | 89.12 | 11896 | 3.32 | 406.5 | 0.0082 |
| Experiment 3 | 114.58 | 12530 | 3.52 | 522.6 | 0.0067 |
| Experiment 4 | 140.04 | 13384 | 3.67 | 638.8 | 0.0057 |
| Experiment 5 | 150.01 | 14562 | 3.85 | 802 | 0.0048 |
Experiment acquisition table 3-1 to table 3-7 is carried out for the fin-tube type heat exchanger that refrigerant pipe caliber is 6mm:
When table 3-1.Q=2000W, the experimental data of fin-tube type heat exchanger
When table 3-2.Q=2300W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(W) | APF(W/W) | C (member) | CP |
| Experiment 1 | 15.00 | 2115 | 3.81 | 50.5 | 0.0754 |
| Experiment 2 | 18.43 | 2280 | 4.95 | 49.0 | 0.1011 |
| Experiment 3 | 22.75 | 2293 | 5.04 | 63.0 | 0.0800 |
| Experiment 4 | 27.28 | 2340 | 5.23 | 67.0 | 0.0780 |
| Experiment 5 | 28.00 | 2325 | 5.25 | 68.7 | 0.0764 |
When table 3-3.Q=2600W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(W) | APF(W/W) | C (member) | CP |
| Experiment 1 | 17.06 | 2380 | 3.60 | 49.0 | 0.0735 |
| Experiment 2 | 20.06 | 2480 | 4.83 | 50.1 | 0.0964 |
| Experiment 3 | 25.79 | 2550 | 4.92 | 54.0 | 0.0910 |
| Experiment 4 | 31.52 | 2645 | 5.13 | 66.0 | 0.0777 |
| Experiment 5 | 39.32 | 2708 | 5.58 | 98.3 | 0.0568 |
When table 3-4.Q=3500W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(kW) | APF(W/W) | C (member) | CP |
| Experiment 1 | 31.52 | 3245 | 3.55 | 76.0 | 0.0467 |
| Experiment 2 | 39.32 | 3368 | 4.58 | 82.3 | 0.0556 |
| Experiment 3 | 50.55 | 3438 | 4.71 | 88.0 | 0.0535 |
| Experiment 4 | 61.78 | 3533 | 4.78 | 92.0 | 0.0520 |
| Experiment 5 | 71.59 | 7225 | 4.76 | 106.6 | 0.0447 |
When table 3-5.Q=5100W, the experimental data of fin-tube type heat exchanger
When table 3-6.Q=7200W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(W) | APF(W/W) | C (member) | CP |
| Experiment 1 | 50.55 | 5050 | 3.37 | 115.0 | 0.0293 |
| Experiment 2 | 56.03 | 7180 | 3.91 | 122.4 | 0.0320 |
| Experiment 3 | 71.59 | 7225 | 4.16 | 136.0 | 0.0306 |
| Experiment 4 | 87.15 | 7298 | 4.34 | 145.0 | 0.0300 |
| Experiment 5 | 101.10 | 7353 | 4.35 | 168.2 | 0.0259 |
When table 3-7.Q=12000W, the experimental data of fin-tube type heat exchanger
| Experimental group | ZL(m) | Q’(W) | APF(W/W) | C (member) | CP |
| Experiment 1 | 71.59 | 7225 | 2.16 | 136.0 | 0.0159 |
| Experiment 2 | 78.64 | 11896 | 3.36 | 140.0 | 0.0240 |
| Experiment 3 | 101.10 | 12530 | 3.53 | 180.0 | 0.0196 |
| Experiment 4 | 123.56 | 13384 | 3.74 | 220.0 | 0.0170 |
| Experiment 5 | 143.56 | 14386 | 3.73 | 255.6 | 0.0146 |
From above-mentioned table 1-1 to table 3-7, choosing three relatively high experimental groups of sexual valence in each table is one preferred single
In member, such as table 1-1, preferred cell is to test 2 to experiment 4.Most short total pipe range successively is extracted from each preferred cell again
ZLminTable 4 is obtained, and extracts longest total pipe range ZLmaxCorresponding experimental group obtains table 5:
Most short total pipe range Z in each preferred cell of table 4.LminExperimental group summarizes
Longest total pipe range Z in each preferred cell of table 5.LmaxExperimental group experimental group summarize
According to the data in table 4, fit about most short total pipe range ZLminWith the caliber D of nominal capacity Q, refrigerant pipe
Fitting formula are as follows: ZLmin=6.39m/kW*Q-4.10m/mm*D+28.8m.The ZLminFitting formula in, relevant three coefficients
Respectively k1'=6.39, k2'=4.10, k3'=28.8.It is, ZLmin=k1’m/kW*Q-k2’m/mm*D+k3’m。
According to the data in table 5, fit about most short total pipe range ZLmaxWith the caliber D of nominal capacity Q, refrigerant pipe
Fitting formula are as follows: ZLmax=10.9m/kW*Q-6.42m/mm*D+45.2m.The ZLmaxFitting formula in, relevant three coefficients
Respectively k1'=10.9, k2"=6.42, k3"=45.2.It is, ZLmax=k1”m/kW*Q-k2”m/mm*D+k3”m。
Therefore, the total pipe range Z of the refrigerant pipe of the fin-tube type heat exchanger is limitedLWith the nominal capacity of fin-tube type heat exchanger
The relationship of Q, meets ZLmin≤ZL≤ZLmaxWhen, the total pipe range of the refrigerant pipe of the fin-tube type heat exchanger is in preferably single in cost performance
In more excellent range in member, that is to say, that the hot device of fin-tube type pipe can get higher cost performance.It is assumed that ZL=k1m/kW*Q-
k2m/mm*D+k3M, then then, there is ZLmin≤ZL≤ZLmax, and k1Meet k1’≤k1≤k1' (i.e. 6.39≤k1≤ 10.9), k2
Meet k2’≤k2≤k2' (i.e. 4.10≤k2≤ 6.42), k3Meet k3’≤k3≤k3' (i.e. 28.8≤k3≤45.2)。
The fin-tube type heat exchanger 100 of the utility model, the caliber D by limiting refrigerant pipe 120 meet 4mm≤D≤6mm,
The refrigerant pipe total pipe range Z of fin-tube type heat exchanger 100LMeet ZLmin≤ZL≤ZLmax, ZLmin=6.39m/kW*Q-4.10m/mm*D+
28.8m ZLmax=10.9m/kW*Q-6.42m/mm*D+45.2m, with refrigerant pipe total pipe range suitably total at Rational choice, it is ensured that
While fin-tube type heat exchanger 100 is capable of refrigerant pipe 120 of small diameter tube, total tube side resistance of the fin-tube type heat exchanger 100 is smaller,
Preferable heat exchange property is obtained, and then obtains higher Energy Efficiency Ratio and cost performance.
Based on the above embodiment, according to different nominal capacity Q, can also make rational planning for ZLValue range, with
Select more preferably refrigerant pipe total pipe range ZL.For this purpose, nominal capacity Q can be divided into 2kW≤Q≤2.6kW, 2.6kW < Q≤
3.5kW, 3.5kW < Q≤5.1kW, 5.1kW < Q≤7.2kW, five sections 7.2kW < Q≤12kW.For five sections,
Refrigerant pipe total pipe range Z is cooked up respectivelyLValue interval.
In one embodiment, for 2kW≤Q≤2.6kW, from table 1-1 to table 1-3, table 2-1 to table 2-3 and table 3-1
Corresponding total pipe range Z in preferred cell is selected to table 3-3L, it can get such as the following table 6:
6. 2kW of table≤Q≤2.6kW corresponds to the total pipe range Z in preferred cellLSummarize
By the data in above-mentioned table 6 as it can be seen that when meeting 2kW≤Q≤2.6kW for nominal capacity Q, the general pipeline of refrigerant pipe
Long ZLIn the range of 21.73m~26.81, it can be ensured that fin-tube type heat exchanger 100 is under any nominal capacity of the range
Obtain preferable exchange capability of heat and cost performance.For example, but be not limited to: the total pipe range Z of refrigerant pipeL21.73m, 21.94m,
22.75m、24.86m、25.97m、26.81m。
In another embodiment, for 2.6kW < Q≤3.5kW, from table 1-3 and table 1-4, table 2.-3 and table 2-4, and
Table 3-3 and table 3-4 selects corresponding total pipe range Z in preferred cellL, it can get such as the following table 7:
7. 2.6kW < Q≤3.5kW of table corresponds to the total pipe range Z in preferred cellLSummarize
By the data in above-mentioned table 7 as it can be seen that when meeting 2.6kW < Q≤3.5kW for nominal capacity Q, refrigerant pipe it is total
Pipe range ZLWithin the scope of 39.32m~61.78m, it can be ensured that fin-tube type heat exchanger 100 is under any nominal capacity of the range
It can get preferable exchange capability of heat and cost performance.For example, but be not limited to: the total pipe range Z of refrigerant pipeL44.56m,
47.75m、50.55m、57.29m、61.78m。
In another embodiment, for 3.5kW < Q≤5.1kW, from table 1-4 and table 1-5, table 2-4 and table 2-5 and table 3-
4 and table 3-5 selects corresponding total pipe range Z in preferred cellL(can refer to table 6 or table 7 in detail), no longer lists one by one herein.Together
Reason can get, when the nominal capacity Q meets 3.5kW < Q≤5.1kW, the total pipe range Z of refrigerant pipeL40.52m~
Within the scope of 62.39m, it can be ensured that fin-tube type heat exchanger 100 can get under any nominal capacity of the range and preferably change
Thermal energy power and cost performance.For example, but be not limited to: the total pipe range Z of refrigerant pipeL40.52m, 46.57m, 51.74m, 58.37m,
62.39m。
In another embodiment, for 5.1kW < Q≤7.2kW, from table 1-5 and table 1-6, table 2-5 and table 2-6, Yi Jibiao
3-5 and table 3-6 selects corresponding total pipe range Z in preferred cellL(can refer to table 6 or table 7 in detail), also no longer arranges one by one herein
Out.Similarly it can get, when the nominal capacity Q meets 5.1kW < Q≤7.2kW, refrigerant pipe total pipe range ZL63.50m~
Within the scope of 87.15m, it can be ensured that fin-tube type heat exchanger 100 can get under any nominal capacity of the range and preferably change
Thermal energy power and cost performance.For example, but be not limited to: refrigerant pipe total pipe range ZL68.04m, 71.59m, 81.13m, 86.94m,
87.15m。
In a further embodiment, for 7.2kW < Q≤12kW, from table 1-6 and table 1-7, table 2-6 and table 2-7, Yi Jibiao
3-6 and table 3-7 selects corresponding total pipe range Z in preferred cellL(can refer to table 6 or table 7 in detail), also no longer arranges one by one herein
Out.Similarly it can get, when the nominal capacity Q meets 7.2kW < Q≤12kW, refrigerant pipe total pipe range ZL95.5m~
Within the scope of 123.56m, it can be ensured that fin-tube type heat exchanger 100 can get under any nominal capacity of the range and preferably change
Thermal energy power and cost performance.For example, but be not limited to: the total pipe range Z of refrigerant pipeL101.10m, 114.58m, 122.78m,
123.56m。
Based on any of the above-described embodiment, the caliber D of refrigerant pipe 120 meets 4mm≤D≤6mm, limits the fin 110
Width PrMeet 16mm≤Pr≤ 26mm, the spacing of fin P between the two neighboring fin 110fMeet 1.1mm≤Pf≤
2.0mm.In D, the Pr、PfIn corresponding range, the fin-tube type heat exchanger 100 has biggish exchange capability of heat, relative in big
Pipe diameter heat exchanger can increase 3%.By rationally designing adjacent fins spacing, so as to accommodate more solidifying frost, it is stifled to reduce solidifying frost
The case where filling in fin 110 occurs.And then the defrost period can be extended, it avoids frequent defrost and heating capacity is caused to reduce, influence user
Comfort.
It particularly, is the width P of the fin 110 within the scope of 4mm~6mm in the caliber D of refrigerant pipe 120rIt should meet
Pr∈ [16mm, 26mm], and the spacing of fin P between two adjacent fins 110fP should be metf∈ [1.1mm, 2.0mm].Example
Such as: Pr=17mm, 18mm, 20mm, 22mm, 24mm, 25.5mm.Pf=1.2mm, 1.3mm, 1.4mm, 1.5mm, 1.6mm,
1.7mm、1.8mm、1.9mm。
It is additionally contemplates that if the spacing of fin between the two adjacent fins 110 of the fin-tube type heat exchanger 100 is smaller, when solidifying
When the height of dewdrops is more than the spacing of fin, the droplet between fin 110 will be connected, and form firm " water
Bridge ".Obviously, " water bridge " meeting occupied space, and then reduce " holding white volume ".It therefore, is the generation of reduction " water bridge ", optionally,
The spacing of fin PfMeet 1.1mm≤Pf≤1.6mm.Such as: Pf=1.15mm, 1.20mm, 1.25mm, 1.30mm,
1.35mm、1.40mm、1.45mm、1.50mm、1.55mm。
In addition, the quantity M in view of U-tube also is compliant with M=H/ (2*Pt), that is to say, that m=2*M=H/Pt(PtFor U-tube
Two refrigerant pipes 120 between tube spacing).Total refrigerant pipe pipe range Z of the fin-tube type heat exchanger 100L=ML=L* (H/
Pt).Therefore, in total refrigerant pipe pipe range Z of fin-tube type heat exchanger 100LAfter determination, the fin-tube type heat exchanger can be also determined substantially
100 tube spacing Pt。
Further, it is also possible to which hydrophilic layer is arranged on the surface of the fin 110.The hydrophilic layer can be hydrophilic aluminum foil painting
Layer.The hydrophilic layer has stronger affinity to water, and condensed water is spread comparatively fast on fin 110, it is not easy to be formed " water bridge ", be subtracted
Small ventilation resistance helps to improve the exchange capability of heat of fin-tube type heat exchanger 100 Yu air.
In addition, the fin 110 is chosen as sheet type fin or corrugated wing for the type of the fin 110
Piece perhaps fenestration fin or bridge shape fin.But, it is contemplated that corrugated fin perhaps fenestration fin or bridge shape
The shape of fin is more irregular, and when the overall dimensions of fin 110 are almost the same, the volume of this few class fin is typically larger than
Sheet type fin occupies biggish space, so the gap that will lead to inside fin-tube type heat exchanger 100 reduces, so that Rong Shuanliang
Reduce.In view of above-mentioned consideration, in the present embodiment, the fin 110 is preferably sheet type fin, can reduce fin 110 with this
Volume, reduce its occupied space, and then ensure to accommodate inside fin-tube type heat exchanger 100 with enough gaps more solidifying
Frost reduces the case where solidifying frost blocks fin 110 and occurs.And then the defrost period can be extended.
The utility model also provides a kind of air conditioner, and the air conditioner includes air conditioner indoor unit and air-conditioner outdoor unit, described
Air-conditioner outdoor unit is connect with the air conditioner indoor unit by refrigerant pipe.The specific structure of the air-conditioner outdoor unit is referring to above-mentioned implementation
Example, since this air conditioner uses whole technical solutions of above-mentioned all embodiments, the same skill with above-described embodiment
All beneficial effects brought by art scheme, this is no longer going to repeat them.
The above is only the preferred embodiment of the present invention, and therefore it does not limit the scope of the patent of the utility model,
It is all under the inventive concept of the utility model, equivalent structure made based on the specification and figures of the utility model becomes
It changes, or directly/be used in other related technical areas indirectly and be included in the scope of patent protection of the utility model.
Claims (13)
1. a kind of fin-tube type heat exchanger, which is characterized in that the fin-tube type heat exchanger includes multiple fins and runs through multiple described
More refrigerant pipes of fin, in which:
The caliber D of the refrigerant pipe meets 4mm≤D≤6mm；
The total pipe range Z of the refrigerant pipe of the fin-tube type heat exchangerLWith the nominal capacity Q of fin-tube type heat exchanger, meet ZLmin≤ZL
≤ZLmax, ZLmin=6.39m/kW*Q-4.10m/mm*D+28.8m, ZLmax=10.9m/kW*Q-6.42m/mm*D+45.2m；Its
In: total pipe range ZLUnit be m；The unit of nominal capacity Q is kW.
2. fin-tube type heat exchanger as described in claim 1, which is characterized in that the nominal capacity Q meet 2kW≤Q≤
12kW, the total pipe range Z of the refrigerant pipeLMeet 20.72m≤ZL≤150m。
3. fin-tube type heat exchanger as claimed in claim 2, which is characterized in that the nominal capacity Q meet 2kW≤Q≤
2.6kW, the total pipe range Z of the refrigerant pipeLMeet 21.73m≤ZL≤26.81m。
4. fin-tube type heat exchanger as claimed in claim 2, which is characterized in that the nominal capacity Q meet 2.6kW < Q≤
3.5kW, the total pipe range Z of the refrigerant pipeLMeet 39.32m~61.78m.
5. fin-tube type heat exchanger as claimed in claim 2, which is characterized in that the nominal capacity Q meet 3.5kW < Q≤
5.1kW, the total pipe range Z of the refrigerant pipeLMeet 40.52m≤ZL≤62.39m。
6. fin-tube type heat exchanger as claimed in claim 2, which is characterized in that the nominal capacity Q meet 5.1kW < Q≤
7.2kW, the total pipe range Z of the refrigerant pipeLMeet 63.50m≤ZL≤87.15m。
7. fin-tube type heat exchanger as claimed in claim 2, which is characterized in that the nominal capacity Q meet 7.2kW < Q≤
12kW, the total pipe range Z of the refrigerant pipeLMeet 95.5m≤ZL≤123.56m。
8. fin-tube type heat exchanger as claimed in any one of claims 1 to 7, which is characterized in that the width P of the finrMeet
10mm≤Pr≤ 26mm, the tube spacing P between the two neighboring refrigerant pipetMeet 10mm≤Pt≤23mm。
9. fin-tube type heat exchanger as claimed in any one of claims 1 to 7, which is characterized in that the two neighboring fin it
Between spacing of fin PfMeet 1.1mm≤Pf≤1.6mm。
10. fin-tube type heat exchanger as claimed in any one of claims 1 to 7, which is characterized in that the fin is sheet type wing
Piece perhaps corrugated fin perhaps fenestration fin or bridge shape fin.
11. fin-tube type heat exchanger as claimed in any one of claims 1 to 7, which is characterized in that the surface of the fin is arranged
There is hydrophilic layer.
12. a kind of air-conditioner outdoor unit, which is characterized in that the air-conditioner outdoor unit includes shell, and such as claim 1 to 11 times
Fin-tube type heat exchanger described in meaning one, the fin-tube type heat exchanger are mounted in the shell.
13. a kind of air conditioner, which is characterized in that the air conditioner includes air conditioner indoor unit, and as claimed in claim 12
Air-conditioner outdoor unit, the air-conditioner outdoor unit and the air conditioner indoor unit are connected by refrigerant pipe.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920334399.5U CN209672488U (en) | 2019-03-15 | 2019-03-15 | Fin-tube type heat exchanger, air-conditioner outdoor unit and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920334399.5U CN209672488U (en) | 2019-03-15 | 2019-03-15 | Fin-tube type heat exchanger, air-conditioner outdoor unit and air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN209672488U true CN209672488U (en) | 2019-11-22 |
Family
ID=68571799
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201920334399.5U Active CN209672488U (en) | 2019-03-15 | 2019-03-15 | Fin-tube type heat exchanger, air-conditioner outdoor unit and air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN209672488U (en) |
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2019
- 2019-03-15 CN CN201920334399.5U patent/CN209672488U/en active Active
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