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Cited by 99Refrigeration and Air Conditioning TechnologiesHeat Transfer and OptimizationAdsorption and Cooling Systems

Effect of fin types of outdoor fan-supplied finned-tube heat exchanger on periodic frosting and defrosting performance of a residential air-source heat pump

Huang, Dong, Ri-Jing, Zhao, Liu, Yun, Yi, De-Bo·2014·Applied Thermal Engineering
DOI 10.1016/j.applthermaleng.2013.11.052
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AI snapshot

Written from the paper’s full text.

TL;DR

This experimental study compared flat, wavy, and louver fins on the outdoor finned-tube heat exchanger of a residential air-source heat pump over repeated frosting/defrosting cycles. Flat fins gave the best overall thermal performance, followed by wavy and louver fins, and the differences were linked to how frost accumulation interacted with the outdoor axial fan’s characteristic curve.

Key findings

  • Six consecutive frosting/defrosting cycles were run for each fin type; frosting and defrosting durations were almost equal, about 46.6 min and 3.9 min, respectively, because the same defrosting control schemes were used.
  • During frosting, time-average heating capacity, COP, and input power for flat fin were greater by 17.1%, 9.0%, and 7.6%, respectively, than for louver fin; wavy fin values were greater by 7.4%, 4.3%, and 2.7% than louver fin.
  • Time-average values from the third, fourth, and fifth cycles: flat fin had COP 2.30, heating capacity 5894.33 W, input power 2573.46 W; wavy fin had 2.20, 5410.38 W, 2455.29 W; louver fin had 2.11, 5035.40 W, 2390.45 W.
  • The heating-capacity curve began descending earliest for louver fin at 17.83 min, versus 24.33 min for wavy and 24.58 min for flat; peak heating capacities were 6121.90 W, 6438.71 W, and 6591.13 W, respectively. The paper attributes rapid drops for wavy and louver fins to the outdoor axial fan entering its stall zone, while flat fin did not experience the stall zone during the 46.6 min frosting duration.

Methods

  • A split-type residential air-source heat pump with nominal 7200 W cooling capacity was tested with R22; three outdoor finned-tube heat exchangers with equal geometrical parameters but flat, wavy, or louver fins were compared.
  • Tests used two environmental simulation rooms and a data acquisition system, with heating capacity measured by the indoor air enthalpy difference method based on Chinese Standard GB/T 7725-2004; indoor conditions were 20 °C dry-bulb/12 °C wet-bulb and outdoor conditions were 2 °C dry-bulb/1 °C wet-bulb for frosting/defrosting cycles.
  • Defrosting was initiated when the defrosting sensor was below −2 °C and frosting time exceeded 45 min, and terminated when defrosting time exceeded 10 min or the sensor reached 12 °C; time-average values from the third, fourth, and fifth cycles were used for overall comparison, and real-time data from the fourth cycle were used for dynamic comparison.

Limitations

  • The paper states that experimental measurements of frost thickness and air pressure drop were not included; the dashed lines in Fig. 13 only schematically present air pressure drops under different frost thickness and are not experimental test results.
  • Evident from the text: the study is limited to one residential air-source heat pump, R22, and fixed standard test conditions, so generalization to other systems, refrigerants, or operating conditions is not established.
  • Evident from the text: the fan-stall explanation is inferred from performance curves and a schematic fan/pressure-drop combination rather than from measured airflow or pressure-drop data.

Model-written summary. Check it against the paper before relying on it.

Integrity signals

Registry

Crossref · 10.1016/j.applthermaleng.2013.11.052

Cites

25 of 25 references verified0 citation errors · 0 not checkable

Statistics

Nothing to recompute.

Claims the paper makes

3 of 14 cited sources checked · 0 supported · 0 flagged · accuracy not yet measured

  • Premisecitation
    § Introduction

    In most experimental researches, the airflow rate across the finned-tube heat exchanger was maintained constant throughout the frosting test, although frost grows continuously.

    “Second, the airflow rate across the finned-tube heat exchanger is maintained to be constant throughout the frosting test in most of the experimental researches [5,10,11,13,20], although frost grows continuously.”
    Quote in the paperSubstantial claim2 of 5 sources checked
    • cites [5] Kristian, 2009, Prediction of an effective cooling output of the fin-and-tube heat exchanger under frosting conditions, Appl. Therm. Eng. source
    • cites [10] Yan, 2005, Thermofluid characteristics of frosted finned-tube heat exchanger, Int. J. Heat Mass Transfer source

      The Experimental apparatus section (p. 2) explicitly says airflow was maintained constant throughout each test by adjusting fan speed. This confirms the cited study used that procedure during frosting, but the paper does not establish that most experimental studies did so. (LLM, conf=0.86)

      Experimental — accuracy not yet measured
    • cites [11] Kondepudi, 1990, The effects of different fin configurations on the performance of finned-tube heat exchangers under frosting conditions, ASHRAE Trans.
    • cites [13] Yan, 2003, Performance of fined tube heat exchanger operating under frosting conditions, Int. J. Heat Mass Transfer source
    • cites [20] Padhmanabhan, 2011, Modeling non-uniform frost growth on a fin-and-tube heat exchanger, Int. J. Refrigeration source

      The Model validation section (p. 6) says the fan's variable-frequency drive maintained airflow constant during frost growth in this paper's experiments. The paper does not establish that most experimental studies use this practice; it also reports that airflow redistributes locally across the coil as frost accumulates. (LLM, conf=0.88)

      Experimental — accuracy not yet measured
  • Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    The falling amplitudes of the heating capacity relative to the peak were 1244.40 W, 2048.29 W and 1999.92 W for flat, wavy and louver fins, respectively.

    “As a consequence, the falling amplitudes of the heating capacity relative to the peak valuedthe difference between the peak and the value at the defrosting initiationdwere 1244.40W, 2048.29Wand 1999.92W for flat, wavy and louver fins, respectively.”
    Quote in the paperSubstantial claim
  • Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    The flat fin had the greatest suction and discharge pressures at the moment of defrosting initiation, followed by the wavy and louver fin types.

    “Finally, the flat fin had the greatest suction and discharge pressures at the moment of defrosting initiation, and followed by wavy and louver fin types.”
    Quote in the paperNot a substantial claim
  • Findingown data
    § Abstract

    During the frosting cycle, the time-average input power for flat fin was 7.6% greater than that for louver fin.

    “The time-average heating capacity, COP and input power for flat fin during frosting cycle were more by 17.1%, 9.0% and 7.6%, respectively than those for louver fin.”
    Quote in the paperSubstantial claim
  • Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    The starting point of the descending segment of the input power curve for the wavy fin was later than that for the louver fin.

    “Despite the fact that the starting point of the descending segment of the input power curve for wavy finwas later than that for the louver fin, the input power at defrosting initiation was almost equal between wavy and louver fins.”
    Quote in the paperNot a substantial claim
  • Classified as probably not a substantial claim. 13
  • May combine two claims. 29

  • Probably not a substantial claim: may not pass S3 (load-bearing). May combine two claims.

    Premisecitation
    § 2780 2387.56 3.92 2000 1482.52

    The louver fin had the most frost accumulation amount and the greatest air pressure drop, followed by the wavy and flat fins.

    “Some experimental results showed the louver fin had the most frost accumulation amount and the greatest air pressure drop, followed the wavy and flat fins.”
    Quote in the paperNot a substantial claim1 of 3 sources checked
    • cites Silva and Hermes [1] da Silva, 2011, Experimental study of frost accumulation on fan-supplied tube-fin evaporators, Appl. Therm. Eng. source
    • cites Yan and Li [10] Yan, 2005, Thermofluid characteristics of frosted finned-tube heat exchanger, Int. J. Heat Mass Transfer source

      The Results and discussion (pp. 4–5) report the greatest frost accumulation and pressure drop for re-direction louver fins. The paper compares re-direction louver, one-sided louver, and flat plate fins—not wavy fins—so it does not support the claimed louver–wavy–flat ranking. (LLM, conf=0.88)

      Experimental — accuracy not yet measured
    • cites Kondepudi and O'Neal [11] Kondepudi, 1990, The effects of different fin configurations on the performance of finned-tube heat exchangers under frosting conditions, ASHRAE Trans.

  • May combine two claims.

    Findingown data

    The differences in time-average COP among the three fin types were greater, and the flat fin had the greatest COP, followed by wavy and louver fins respectively.

    “However, the differences in the time-average COP among three fin types were greater, and the flat fin had the greatest COP, followed by wavy and louver fins, respectively.”
    Quote in the paperSubstantial claim

  • May combine two claims.

    Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    The heating capacity curve for wavy fin started to drop at the 24.33rd minute with a peak value of 6438.71 W.

    “The heating capacity curve for wavy fin started to drop at the 24.33rd minute with the peak value of 6438.71 W.”
    Quote in the paperNot a substantial claim

  • May combine two claims.

    Findingown data

    The peak and time-average heating capacity for wavy fin were 6428.82 W and 5410.38 W, respectively, greater by 5.2% and 7.4% than those for louver fin.

    “Those for wavy fin were 6428.82Wand 5410.38W, respectively, which were greater by 5.2% and 7.4% than those for louver fin.”
    Quote in the paperSubstantial claim

  • May combine two claims.

    Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    The curves of the heat amount absorbed by the outdoor heat exchanger were similar in shape to the heating capacity and input power curves, but had greater amplitude of variation than the input power curves.

    “Obviously, the curves of the heat amount absorbed by outdoor heat exchanger in Fig. 7 were similar in the shapes to the curves of heating capacity in Fig. 5 and input power in Fig. 6, but had greater amplitude of variation than those of the input power in Fig. 6.”
    Quote in the paperSubstantial claim
    • The authors state this as an assumption: The frosting period can be regarded as a quasi-static process for computing the heat amount absorbed by the outdoor heat exchanger.

  • Probably not a substantial claim: may not pass S3 (load-bearing). May combine two claims.

    Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    Because the input power was almost zero at the moments of both defrosting initiation and termination, the corresponding COP was beyond the range of normal value.

    “In addition, because the input power in Fig. 6 was almost a zero at the moments of both the defrosting initiation and termination, accordingly the corresponding COP in Fig. 8 was beyond the range of normal value.”
    Quote in the paperNot a substantial claim

  • May combine two claims.

    Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    The points where the heating capacity curves started to descend and the peak values of heating capacity had great differences among the three fin types.

    “However, the points where the heating capacity curves started to descend and the peak values of the heating capacity had great differences among three fin types.”
    Quote in the paperSubstantial claim

  • May combine two claims.

    Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    The starting point was at the 24.58th minute for flat fin, the latest among the three fin types, and the corresponding maximum heating capacity was 6591.13 W.

    “The starting point was at the 24.58th minute for flat fin, the latest one among three fin types, and the corresponding maximum heating capacity was 6591.13 W.”
    Quote in the paperNot a substantial claim

  • May combine two claims.

    Findingown data

    The peak and time-average heating capacity for flat fin were 6590.61 W and 5894.33 W, respectively, greater by 7.8% and 17.1% than 6112.68 W and 5035.4 W for louver fin.

    “Meanwhile, the peak and time-average values of the heating capacity for flat fin were 6590.61 W and 5894.33 W, respectively, which were greater by 7.8% and 17.1% than those of 6112.68 W and 5035.4 for louver fin.”
    Quote in the paperSubstantial claim

  • Probably not a substantial claim: may not pass S3 (load-bearing).

    Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    The suction and discharge temperatures had similar curve shapes to the suction and discharge pressures.

    “Obviously, suction and discharge temperatures had the similar curve shapes as the suction and discharge pressures in Figs. 9 and 10.”
    Quote in the paperNot a substantial claim

  • Probably not a substantial claim: may not pass S1 (asserted), S3 (load-bearing), S4 (based).

    Findingnone given
    § 2780 2387.56 3.92 2000 1482.52

    The suction and discharge pressures for the wavy and louver fin types gradually increased at first, then decreased rapidly and gradually at last.

    “Similar to the heating capacity in Fig. 5 and the input power in Fig. 6, the suction and discharge pressures for flat fin increased at first, and then gradually decreased, while the input power for wavy and louver fin types gradually increased at first, then decreased rapidly and gradually at last.”
    Quote in the paperNot a substantial claim

  • May combine two claims.

    Findingown data
    § Abstract

    The flat fin had the best thermal performance of the air-source heat pump, followed by wavy and louver fins.

    “The experimental results showed the flat fin had the best thermal performance of the air-source heat pump, followed by wavy and louver fins.”
    Quote in the paperSubstantial claim

  • May combine two claims.

    Findingown data

    The peak and time-average COP for flat fin were 2.52 and 2.3, respectively, greater by 3.7% and 9.0% than 2.43 and 2.11 for louver fin.

    “The peak and time-average values of COP for flat fin were 2.52 and 2.3, respectively, and were greater by 3.7% and 9.0% than those of 2.43 and 2.11 for louver fin.”
    Quote in the paperSubstantial claim

  • May combine two claims.

    Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    The input power for the flat fin began to drop latest and most gently.

    “Input power for flat fin began to drop not only the latest but also most gently.”
    Quote in the paperNot a substantial claim

  • May combine two claims.

    Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    The flat fin had the best thermal performance of the residential heat pump in the periodic frosting/defrosting cycles, followed by the wavy and louver fins.

    “The experimental results the flat fin had the best thermal performance of the residential heat pump in the periodic frosting/defrosting cycles, followed by wavy and louver fins.”
    Quote in the paperSubstantial claim

  • May combine two claims.

    Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    The starting point of the descending segment was at the 17.83rd minute for louver fin, the earliest among the three fin types, and the heating capacity arrived at a peak value of 6121.90 W.

    “The starting point of the descending segment was at the 17.83rdminute for louver fin in Fig. 5, the earliest one among three fin types, and the heating capacity arrived at the peak value of 6121.90 W.”
    Quote in the paperNot a substantial claim

  • May combine two claims.

    Findingown data

    The peak and time-average COP for wavy fin were 2.5 and 2.2, respectively, greater by 2.9% and 4.3% than those for louver fin.

    “Those for wavy fin were 2.5 and 2.2, respectively, which were greater by 2.9% and 4.3% than those for louver fin.”
    Quote in the paperSubstantial claim

  • May combine two claims.

    Findingown data
    § 2780 2387.56 3.92 2000 1482.52

    Although the starting points of the descending segment were almost equal for flat and wavy fins, the peak heating capacity for flat fin was bigger by 2.37% or 152.51 W than that for wavy fin.

    “Regardless of the fact that the starting points of the descending segment were almost equal for flat and wavy fins, but the peak value of the heating capacity for flat fin was bigger by 2.37% or 152.51 W than that for wavy fin.”
    Quote in the paperNot a substantial claim

  • May combine two claims.

    Interpretationreasoning
    § 2780 2387.56 3.92 2000 1482.52

    The frosting curves for the wavy fin decreased rapidly when the axial fan experienced the stall zone, and decreased slightly at last after the stall zone was passed through.

    “Hence, frosting curves for wavy fin decreased rapidly when the axial fan experienced the stall zone, and decreased slightly at last after the stall zone was went through.”
    Quote in the paperSubstantial claim

  • Probably not a substantial claim: may not pass S4 (based). May combine two claims.

    Premisenone given
    § Introduction

    The real refrigerant temperature along the flowing path at the evaporating two-phase zone decreases owing to pressure drop, while the temperature of a single-phase working fluid always increases.

    “The real refrigerant temperature along the flowing path at the evaporating two-phase zone decreases owing to the pressure drop, while the temperature of a single-phaseworking fluid always increases.”
    Quote in the paperNot a substantial claim

  • May combine two claims.

    Interpretationreasoning
    § 2780 2387.56 3.92 2000 1482.52

    The wavy fin had less frost accumulation amount and smaller air pressure drop than the louver fin, and it experienced the stall zone of the axial fan later.

    “The wavy fin had less frost accumulation amount and smaller air pressure drop than the louver fin, and it experienced the stall zone of the axial fan later.”
    Quote in the paperSubstantial claim

  • May combine two claims.

    Interpretationreasoning
    § 2780 2387.56 3.92 2000 1482.52

    The axial fan experienced the stall zone from Point 3 to Point 4 and its airflow rate decreased faster, and accordingly the frosting curves for the louver fin decreased rapidly.

    “Therefore the axial fan experienced the stall zone from Point 3 to Point 4 and its airflow rate was faster decreased, and accordingly the frosting curves for louver fin in Figs. 5e12 decreased rapidly.”
    Quote in the paperSubstantial claim

  • Probably not a substantial claim: may not pass S4 (based). May combine two claims.

    Premisenone given
    § Introduction

    The real air-source heat pump is a closed-loop system and consists of four main components that interrelate with each other.

    “The real air-source heat pump is a closed-loop system, and consists of the four main components which interrelate with each other.”
    Quote in the paperNot a substantial claim

  • Probably not a substantial claim: may not pass S3 (load-bearing).

    Study design and conductnone given

    All temperature and pressure sensors on the residential heat pump were calibrated to reduce experimental uncertainties.

    “All temperature and pressure sensors on the residential heat pump were calibrated to reduce experimental uncertainties.”
    Quote in the paperNot a substantial claim

  • Probably not a substantial claim: may not pass S3 (load-bearing).

    Study design and conductnone given

    The relative error of pressure sensors over an effective measurement range of 0 to 25 bars was ±0.25%.

    “The relative error of pressure sensors over effective measurement range of 0e25 bars was �0.25%.”
    Quote in the paperNot a substantial claim

  • Probably not a substantial claim: may not pass S3 (load-bearing).

    Study design and conductnone given

    The temperature sensors were T-type thermocouples calibrated with a standard water bath over a temperature range of -30 to 120 °C and having an error of ±0.2 °C.

    “The temperature sensors were T-type thermocouples calibrated with a standard water bath over a temperature range of �30e120 �C and having an error of �0.2 �C.”
    Quote in the paperNot a substantial claim

  • Probably not a substantial claim: may not pass S3 (load-bearing).

    Study design and conductcitation

    Uncertainties reported in the present study were estimated following the single-sample method proposed by Moffat [25].

    “Uncertainties reported in the present study are estimated following the single-sample method proposed by Moffat [25].”
    Quote in the paperNot a substantial claim0 of 1 sources checked
    • cites Moffat [25] Moffat, 1988, Describing the uncertainties in experimental results, Exp. Therm. Fluid Sci. source

  • Probably not a substantial claim: may not pass S4 (based). May combine two claims.

    Premisenone given
    § Introduction

    The heat transfer coefficient of real two-phase refrigerant varies markedly along the flowing path due to quality variation, while that of a single-phase working fluid stays almost constant except for a shorter entrance effect.

    “The heat transfer coefficient of the real two-phase refrigerant varies along the flowing path markedly due to its quality variation, while that of a single-phase working fluid stays almost constant except the shorter entrance effect.”
    Quote in the paperNot a substantial claim

  • May combine two claims.

    Interpretationreasoning
    § 2780 2387.56 3.92 2000 1482.52

    The flat fin had the least frost accumulation amount and smallest air pressure drop, and it did not experience the stall zone of the axial fan during the frosting time of 46.6 min.

    “However, the flat fin had the least frost accumulation amount and smallest air pressure drop, and it did not experience the stall zone of the axial fan, during the frosting time of 46.6 min.”
    Quote in the paperSubstantial claim

  • Probably not a substantial claim: may not pass S4 (based). May combine two claims.

    Interpretationreasoning
    § Introduction

    The frosted evaporator will affect compressor performance by decreasing suction pressure and temperature, and will furthermore influence the performance of the condenser and the expansion valve.

    “The frosted evaporator will affect the compressor performance by the decrease in the suction pressure and temperature, and furthermore influence the performance of the condenser and the expansion valve.”
    Quote in the paperNot a substantial claim

  • Probably not a substantial claim: may not pass S4 (based).

    Interpretationnone given
    § 2780 2387.56 3.92 2000 1482.52

    There should be decisive effects of frost that resulted in the initial ascending segments of the performance parameter curves.

    “There should be the decisive effects of frost which resulted in the initial ascending segments of performance parameter curves.”
    Quote in the paperNot a substantial claim

  • May combine two claims.

    Interpretationreasoning
    § Abstract

    The frosting curves for wavy and louver fin types decreased rapidly because the outdoor axial fan experienced the stall zone caused by more frost accumulation and greater air pressure drop, and decreased slightly at last after the stall zone was passed through.

    “The frosting curves for wavy and louver fin types decreased rapidly because the outdoor axial fan experienced the stall zone caused by more frost accumulation and greater air pressure drop, and decreased slightly at last after the stall zone was went through.”
    Quote in the paperSubstantial claim

  • May combine two claims.

    Interpretationreasoning
    § Introduction

    The experimental results in this paper were widely dissimilar from those of Kondepudi and O'Neal [11], and even contrary to each other.

    “Hence, the experimental results in this paper were widely dissimilar from those of Kondepudi and O'Neal [11], and even contrary to each other.”
    Quote in the paperNot a substantial claim0 of 1 sources checked
    • cites Kondepudi and O'Neal [11] Kondepudi, 1990, The effects of different fin configurations on the performance of finned-tube heat exchangers under frosting conditions, ASHRAE Trans.

  • May combine two claims.

    Interpretationreasoning
    § 2780 2387.56 3.92 2000 1482.52

    The louver fin had the most frost accumulation amount and the greatest and fastest air pressure drop, resulting in the earliest occurrence of Point 3.

    “The louver fin had the most frost accumulation amount and the greatest and fastest air pressure drop, resulting in the earliest occurrence of Point 3.”
    Quote in the paperSubstantial claim

  • May combine two claims.

    Interpretationreasoning
    § 2780 2387.56 3.92 2000 1482.52

    The flat fin had the least frost accumulation amount and smallest air pressure drop, and the axial fan did not experience the stall zone during the frosting time of 46.6 min.

    “However, the flat fin had the least frost accumulation amount and smallest air pressure drop, and the axial fan did not experience the stall zone, during the frosting time of 46.6 min.”
    Quote in the paperSubstantial claim

  • May combine two claims.

    Interpretationreasoning
    § 2780 2387.56 3.92 2000 1482.52

    The frosting curves for the wavy and louver fin types decreased rapidly when the axial fan experienced the stall zone, and decreased slightly at last after the stall zone was passed through.

    “The frosting curves for wavy and louver fin types decreased rapidly when the axial fan experienced the stall zone, and decreased slightly at last after the stall zone was went through.”
    Quote in the paperSubstantial claim
36 of 36

  • The authors state this as an assumption.

    The frosting period can be regarded as a quasi-static process for computing the heat amount absorbed by the outdoor heat exchanger.

    “the heat amount absorbed by outdoor heat exchanger in Fig. 7 was obtained by subtracting the input power from the heating capacity if the frosting period was regarded as a quasi-static process.”
1 of 1

Claims other papers make about this one

Each is checked against this paper’s own text: does it say what the citing paper says it does?

Self-check

Percentages, sums and reported differences re-computed from the paper’s own numbers.

Each contradiction between two passages listed here was confirmed by an independent check.

  • Flat-fin defrosting time differs from abstract claim

    Major

    The abstract says defrosting lasted about 3.9 minutes for each fin type, but Table 4 gives 4.72 minutes for the flat fin.

  • Performance ranking names the flat fin twice

    Minor

    The text ranks flat first and then says the remaining fin types are wavy and flat, contradicting its stated ranking of flat, wavy and louver.

2 of 2

Cites

Flagged first, then by citations

Research works printed but not linked: 1

  1. Kondepudi, 1987, The effect of frost growth on extended surface heat exchanger performance: a review, ASHRAE Trans., 93, 258

Cited by

Sorted by citations

Related

Authors
Huang, D., Ri-Jing, Z., Liu, Y., & Yi, D.-B.
Affiliations
Xi'an Jiaotong University (CN)
Corresponding author
Huang, Dong
ORCID
Venue
Applied Thermal Engineering
Publisher
Elsevier BV
Published
2014-08
Volume
69
Issue
1-2
Pages
251-260
ISSN
1359-4311 (ISSN-L)
DOI
10.1016/j.applthermaleng.2013.11.052
OpenAlex
W2058672372
Semantic Scholar
e23b04cd5986b981e006a0527583c7cbc9aac6c1
Cited by
99
References
25
Citations by year
2026: 4 · 2025: 10 · 2024: 13 · 2023: 12 · 2022: 9 · 2021: 6 · 2020: 8 · 2019: 8 · 2018: 9 · 2017: 9 · 2016: 5 · 2015: 3 · 2014: 3
FWCI
4.87
Type
journal article
Language
en
Open access
closed
Licence
www.elsevier.com/tdm/userlicense/1.0/ (tdm)
Locations
Applied Thermal Engineering (publishedVersion)
Funders
National Natural Science Foundation of China (51006079)
Topics
  • Physical Sciences › Engineering › Mechanical Engineering › Refrigeration and Air Conditioning Technologies
  • Physical Sciences › Engineering › Mechanical Engineering › Heat Transfer and Optimization
  • Physical Sciences › Engineering › Mechanical Engineering › Adsorption and Cooling Systems
Keywords
finned tube heat exchanger, air-source heat pump, wavy fins, louver fins, flat fins, coefficient of performance, frost accumulation

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