ＯＴＥＣ
アルミプレートを用いたプレート式熱交換器における水蒸気の凝縮熱伝達特性
Vol. 23 (2018)，17 〜 25

アルミプレートを用いたプレート式熱交換器における水蒸気の凝縮熱伝達特性
ĿȂ¾Ç*1ȉûłĉą*2
Characteristic of condensation heat transfer of water vapor on plate heat exchanger
using aluminum plate
Hirofumi ARIMA*1, Kohei YAMAMOTO
Institute of Ocean Energy, Saga University
1-48, Hirao, Kubara-aza, Yamashiro-cho, Imari-shi, Saga, 849-4256, Japan*2
Department of Mechanical Engineering, Saga University
1-Honjo, Saga-shi, Saga, 840-8502, Japan*1

Abstract
The spray flash seawater desalination is attracted attention as a multipurpose of OTEC technology. The system consists offlash chamber (evaporator), condenser, fresh water tank and vacuum pump. The hot surface seawater flows into the vacuumed
flash chamber and flash evaporated inside the very low-pressure environment. The evaporated water vapor flows into thecondenser. The condenser can be condensed the water vapor using the cold seawater. Then, the produced pure water are stored
into the fresh water tank. Incidentally, the flash chamber and condenser are important devices in this desalination system. If the
improvement of efficiency of this desalination system, it is important to improve the efficiency of these devices. The condenser
research in the desalination field, the condensation in the low pressure and water vapor have to be considered. In addition, inorder to improvement of the heat transfer performance of the condenser, the new material for condenser also have to beconsidered. The author proposed the usage the aluminum alloy for heat transfer surface. In our previous study, the condense
heat transfer of water vapor inside plate heat exchanger using aluminum plate which was installed into the spray flash seawater
desalination was measured. In addition, in this study, compared of condense heat transfer performance between the aluminumalloy and conventional titanium plate which have same thermal resistance of the plate. The result is that the heat transfer
performance of aluminum alloy is as well as that of the titanium one. However, the measurement of condensation was notconsidered the effect of the no condensable gas in the source water. The noncondensable gas becomes the thermal resistance inthe vapor condensation. Therefore, in this study, the measurement of the condense heat transfer of the water vapor without thenoncondensable gas on the aluminum alloy and titanium plates to understand the property of the pure water vapor. The result
is that the overall condense heat transfer without the gas is off course the larger than that of with the gas. In addition, it was
found that the condense heat transfer coefficients on the aluminum plate is derived at several source water temperature and cold
water flow rate and temperature condition under the pure water vapor. The result will be used for design the plate condenser
using aluminum plates.
Key words : Condenser, Aluminum alloy, Spray flash desalination, PEEK resin, WIN KOTE film,

1. 緒

言

Ż× OTEC (ȉƣý (Ŝ{, 2015) 3]u@ (Makai Ocean Engineering, 2015) &îǋdpvXǱǊ8ȉť
ř;ſ îǋîȃǣ158! 7ȊOTEC 'ŸĔ#!ȉƆǺâ&ŝ/{ťř;«²ſ7ǂÉ²ſÅƴ%#Ǝ58! 7ȊǂÉ²ſ'"2OdsxbpUMnƻƆ;ſ ťřŧř¼š(ȉƿúř;ƍ
ƜðÑª"ƻƆȉ'řƻŘ;¯ưÑª"Ũúř;ſ !¯ư7MOVj" 6ȉOTEC #ǅÐĘǻÁƙÃ 2018 Ć 08 ľ 10 ĵ
*1ǘãëťŢC[rHxƏƛQvRx ȇ849-4256 zǪāûƂÁéąø 1-48Ȉ
*2ǘãëżÿëǧŒŊMOVjÿëƔ ȇ840-8502 ǘāłćƂȋƄȈ
E-mail: arima@ioes.saga-u.ac.jp

17

18

有馬 博史 , 山本 康平

ă&ȅ Ȋ{Á5 ({Á5, 1999) ( OTEC #OdsxbpUMnƻƆĊťřŧř¼ǀƱ;Ʃ/É:ǂÉdpvX;@vVqNBvX]@cqUY OTEC #!Ĩŉ7#"ǡřKOX'ǍƟ;ƾ! 6ȉKOX"
ǡřÅƴ" 7#;Ɠ! 7ȊyĲȉ'ǂÉ²ſ'îǋƏƛ&!(ČQvRx" 2014 Ć5"&

ƾ:8! 6 (Ťƀ5, 2016)ȉƣý'ŞƯƌťŢŭĈĀƆǺîǋǊ£ (|ȉƣý OTEC) 5Ē587ťř;«²ſ!ȉČQvRx'ƣýLVp@X&ǊƱîǋǍȃſOdsxbpUMnƻƆĊťřŧř¼ǀƱ
&47ťřŧř¼;ǟĆ"ƾ:8ȉOTEC '°·á»3îťÚ'ťřŭ'á»&47»Ƈ%Ďǽ&!ǌ

ǣ158! 7Ȋ#9"ȉOdsxbpUMnƻƆĊťřŧř¼ǀƱ'ĘƴÌ{&(ȉťř;ƍƜ|"bpU
MnƻƆ7bpUMnTmv^x#řƻŘ;¯ư7dsxXĊ¯ưÑ'ĘƴÌ{}Åœ" 7ȊbpUMnTmv^x&!(bpUMnƻƆïª'\PrčŹ ({Á5, 1991) 3\PrÌ (Ŝ{5, 2005) &7 (Òţ'±Ăǡř&~ 7Ďǽǳ7Əƛ (Ł, 2006), (Sami et al., 2012)%$ƾ:8!ȊyĲȉ¯ưÑ(bpUMnƻƆÑ5'řƻŘ'¯ư 4)Ʀª;ă&ǕÖ; '&½±%ƴ·ǃś87ȉ'ĘƴÌ{&ǳ7Əƛ,#<$ƾ:8! % Ȋ.ȉ¯ưÑ'ŷǼŃį&(yƸ&TRvſ8!
7ȉŷǼŃį&ǳ7Əƛ2ǣ158!% #5ȉƞƳ5(ŷǼŃį#!>riÉǮ;Ĩŉȉ'²ſÅƴĘ&!Əƛ (ĿȂ5, 2017) ;ǣ1!Ȋ85'Əƛ"(ȉťř&ċ >ri&ŸŕKxV?
vJ;ĳŷdsxX#!dsxXĊŷĩÑ&Ʃ/ǝ/ȉ¯ưŷǦ3ǡřKOX&!ǌ;ƾ!
7Ȋ#9"'Əƛ&!(ȉÁř#!ƿúř':6&řǥřſ 58ȉ5&'řǥř(ƶŘ;ƾ! % 1}¯ưĘFO;Î<" Ȋ>riÉǮŷǼ& 7řƻŘ'¯ưŷǦź&!ǌ;ƾ ÝÉ&(ȉ}¯ưĘFO;Î.% ŽÞ"¯ưîȃ;ƾ +" 7Ȋ¯ư& 7}¯ưĘFO'Ďǽ&!(ȉSparrow-Lin 5 (Sparrow, et al., 1964) (ȉ¥Ĭ vol%'}¯ưĘFO'ũ§"¯ưŷǦź 50%Ŭ÷7#;Ǟ+! 6ȉ.ȉťřŧř¼& 7¯ư#ǿ'ŽÞ"'¯ưŻǔ#!ȉäǬ5 (äǬ5,2004) (DxdvL@Ir OTEC &!ȉ}¯ưFO;Î0ŭťř;ŬÖ|"ƻƆđ&¯ưÝÉȉ}¯ưFOŵĈ 0.1wt%" !2'ß¸& ȉ}¯ưFOÎ.8% ÝÉ'żǒŷĩǭ#îŮ8­řŷĩǭ'ŗ 90%5 20%&ėŴ&|ȉ .6¯ưŷǦź|7#;Ɠ! 7Ȋ85'#5ȉłƏƛ"(ĺĆĈ'îȃĲš (ĿȂ5, 2017) ;ǄƊȉ}¯ưĘFO;Î.% řƻŘ'¯ư;ęíƶŘ
8Ář;ſ !>riÉǮdsxX¯ưÑ& 7¯ưîȃ;ƾȊłÜ"('ƪň&
!ÜÏ;ƾ
Ȋ
2. 記

Ac
As
Cp
Deq
h
i
k
l
L
m
Nu
P
Q
Re
t
T

Ȍ ţǛİǼƚ     [m2]Ȍ ƮŷǼƚ     [m2]Ȍ íÖŗŷ      [J/kgK]Ȍ ř·ƋČƊĐ    [m]Ȍ ŷǦź      [W/m2K]
Ȍ ŗCvRrax   [J/kg]Ȍ ŷöź      [W/mK]Ȍ dsxXŷǼȅ [m]Ȍ ųŷ        [J/kg]Ȍ ǚǭţǭ      [kg/s]
Ȍ Nusselt Ĭ      [-]Ȍ Ö·        [Pa]Ȍ ŷĩǭ      [W]Ȍ Reynolds Ĭ     [-]Ȍ dsxXÀ    [m]Ȍ ŭĈ        []号U

Ȍ ŷǟǤź      [W/m2K]
Ȍ ţǠ        [m/s]VHqMmĮéȌ ƤĈ        [Paws]µ

nrȌ »ƤĈ       [m2/s]Ȍ ñĈ        [kg/m3]

Ūé
c
in
L
lm
out
P
sat
V, v

Ȍ ­ř
Ȍ §Ä
Ȍ ŦƋ
Ȍ ôĬąØȌ °Ä
Ȍ VOXdsxXȌ ȁÐȌ ŘƋȉƻŘ¢19

アルミプレートを用いたプレート式熱交換器における水蒸気の凝縮熱伝達特性

3. 実

験

Fig. 1 に実験装置の概略図を示す．実験装置はテストセクション (プレート式凝縮器) ，真空温水タンク，清水
タンク，真空ポンプ 1 および 2，冷凍機で構成されている．系内の圧力を真空に保つ 2 台の真空ポンプはそれぞれ，真空ポンプ 1 が ULVAC 製 DTC-22 (ダイアフラム式，到達圧力 1.0×103 Pa, 排気速度 24 L/min)，真空ポンプ
2 が ULVAC 製 DA-30D (ダイアフラム式，到達圧力 6.7×103 Pa, 排気速度 36 L/min) である．また，凝縮器での水蒸気の冷却には，深層水の代わりに冷凍機 (オリオン製: RKW1500B-V-G1，冷却能力 5.3kW) で作った冷水を用いた．温水タンク内に封入した原水は，ロッドヒーター (大阪魂製: CHC1404, 400W×2 本) を温調器 (オムロン
製: OMRON E5CN-QTD, SSR 制御) と組み合わせて温度調整を行った．真空温水タンクと清水タンクの真空圧力の測定には圧力変換器 (横河電機製: FP101A，測定範囲 0 ~ 50kPaA，測定精度 ± 0.06%)，冷水の体積流量測定
は電磁流量計 (キーエンス製: FD-M10AT，測定精度 ± 1.6% of F.S.), 系内の温度の測定には K 型熱電対 (林電工
製: ST6，クラス 1，誤差 ±1.5℃) を用いた．これらの測定値はデータロガー (GRAPHTEC 製: GL820) に集められ記録された．また，本実験では原水の脱気の状態を確認するために DO メーター (飯島電子工業製: ID-150, 測
定範囲 1.0~20.0mg/L, -5~50℃, 測定精度 ±0.1mg/L, ±0.2℃) を使用した．
実験において作動流体は系内を次のように流れる．真空ポンプで系内を 2 ~ 5kPa に減圧した状態で，原水を温水タンクで任意温度まで加熱沸騰させ水蒸気を発生させる．その水蒸気を凝縮器に流して冷水で凝縮させる．凝縮で得られた真水は最後に清水タンクに貯蔵される．

T

PHE

T

Inlet

Outlet

T
Inlet

Data
loggerP T
TP

Test section

Valve

T
T

T
Refrigerator

Pure
water
tank

VP
2

Vacuum pump
N2 Tank

Flowmeter

Vacuumed
Hot watertankOutletVP
1

P Pressuretransducer
T Thermocouple

Rod heaters
By-pass line

Volt slider

Water
tank

Discharged
valve
Measuring cylinder

Handheld
DO meterFig. 1 Schematic diagram of experimental apparatus.
Heat transfer area andflow channel

100

20.0

228.0

350
300
194

70

Front face

Back face

Photo

Fig. 2 Design of test plate.

TP-2

TP-1

TP-3

Fig. 3 Photos of test plates.

TP-4(TP-1: 25m-PEEK, TP-2: 100m-PEEK, TP-3: WIN KOTE, TP-4: Ti)

20

有馬 博史 , 山本 康平

3・2 テストプレート

Fig. 2 &>riÉǮǁVOXdsxX'ŌƃÕ#ŖŃ'¬ƍ;ƓȊŖŃ( A5052 >riZAjÉǮ" 7ȊVOXdsxX'óš(ȅ 350mmȉĄ 100mmȉÀ 3.5mm (ŷǼȉĽƽǧ) " 7Ȋ.VOXdsxX(ȉƺƳ5ĺĆÜÏ (ĿȂ5, 2017) OdsxbpUMnĊťřŧř¼& 7¯ưîȃ"ſVOXdsxX (Fig. 3) #Ëy'2';ſȊFig. 3 &ƓVOXdsxX(ȉŖŃ&ƷÀ 25µm ' PEEK őƵ"Kx
V?vJdsxX (|ȉTP-1) #ȉƷÀ 5µm ' WIN KOTE (|ȉTP-3) "KxV?vJ;ƾ 3 Ƙǿ'>riZAjÉǮǁdsxX" 7Ȋ% ȉTP-2 (ĺĆĈÜÏ'îȃ (ĿȂ5, 2017) "ſdsxX"7ȉÓ(ſ%1œƄ#Ȋ.ȉłîȃ&!2ȉĴĞ'TRvǁdsxX (|ȉTP-4);ŗǜſ#!ſ Ȋ% ȉTP-1 ~ 3 ( TP-4 'âč;ŏ2'" 7ȉŷǼ(ąŲǼ#%! 7Ȋ85'VOXdsxX(È 4 ŇĞ8ȉ4 Ň;yƩ#!¯ưîȃ&ſȊ.85'VOXdsxX(ȉĴĞ'dsxXĊŷĩÑ'bsxj (>rb=p^rǁ: T2-BFG) &Ʃ/ǝ0#"ȉVOXQIMov;ōĞȊVOXQIMov'ĿºƮŷǼƚȉƻŘ¢ţǛİǼƚȉdsxXÀ 4)ŷöź; Table 1 &ƓȊ
Table 1 Specification of plates
Plate type

TP-1

TP-3

TP-4

Material

PEEK
25

WIN KOTE
5

Titanium
-

4
3/2

4
3/2

4
3/2

Thickness of coating [µm]Number of plates on test section
Number of channel (Cold water/ Vapor)
Plate thickness t [mm]

3.5

3.5

0.5

6.7×10-2

6.7×10-2

8.0×10-2

2.10×10-4

2.10×10-4

2.99×10-4

Length of the heat transfer area of test
plate lch [m]2.33×10-1

2.33×10-1

2.78×10-1

Thermal conductivity kP [W/mK]

140

140

22

Total heat transfer area Ac [m2]Cross-sectional are of surface vapor
channel Acv [m2]3・3 実験方法

îȃ"(ȉµơ"Ɠ 3 Ƙǿ'VOXdsxX (TP-1, 2, 4) ;¯ưÑ&88Ʃ/ǝ/ȉÈ'VOXd
sxX& 7¯ưŷǦź'Ůí;ƾȊ3 Ƙǿ'VOXdsxX(88 4 ŇyƩ#!VOXQIM
ov" 7 PHE &Ʃǝ.8Ȋîȃ&Ʀª"Ůí8ŹĜǭ(¨!WxRtFx&Ǹ158ȉ5 ƕǲǶ" 3±ǲǉǯ8Ȋ.ȉWxRĭż&(88' ' 3 ±ǲ'ąØ ſ 58Ȋ«ŻĘƐǏ'1È'ń" 3 ÓŮí;ƾ%Ȋ.¯ưǠĈ'Ůí'1ȉūřRvI¢Ǽ&ŦǼȅ'Ůí'1'Ɖƈ6;Ǩ
! 10 ±ǲ& 7ŦǼ'ȅ'á¼;ǉǯȊŦǼȅ'ƥĈ;ß1&ȉWNRrEkp&4!ĪĎ
ǉǯ;ƾȊ.ȉłîȃ"(}¯ưĘFO;ĥǵřƻŘ;ſ !¯ưŷǦź'Ůí;ƾ Ȋ'1ŷǦź'Ů
íµ&Ář'ƶŘ;½±&ƾȊÁř'ƶŘ(ȉŭřRvIª;ƍƜgvd"ƍƜŹĜ&ȉ35~40" 1 ĻǲƗĈ¸ŷ!ƾȊƶŘ'ŹĜ(Ář 1L &Î.87űêǩƨ'ǚǭ [mg] (DO ) ;űêǩƨǈ (DO ǈ)"ƐǏȊƶŘ8Ář' DO 'ƐǏ(ȉDO ǈ'ŮíÁż{yĶãŘÖ|&ğĕǃ 7Ȋ'1ȉ
|'Ĳš"ãŘÖ|"'ŮíŰ£;ƾȊ.ƶŘđ'Ář 200ml ;ŭřRvI5^@_Op@v;
!ūřRvI&Ɩļ 7Ȋ'đȉƝƨFO;ūřRvI&ƬôÖ" 110kPa õ§!ĥ°^rc;Ǳīȉðǭ 300ml 'kOMqvSx&Ɩļ 7ȊĽđ&kOMqvSx& DO ǈ'dtxc;Ĥ§!ȉ±Ǡ 30cm "{|7#"Ůí;ƾ ȊƶŘđ' DO ( 1.9 ~ 3.3 mg/L Ē58Ȋ20, 1atm & 7ȁÐűêǩƨǭ
 8.84 mg/L " 7#5ȉÁř&ĽãÎ.8! űêǩƨǭ'ªȉƧ 60 ~ 80 wt%'ǩƨĥǵ8ȊÁ21

アルミプレートを用いたプレート式熱交換器における水蒸気の凝縮熱伝達特性

ř&Î.87}¯ưĘFO#!'&ƝƨFOģ587ȉãŘ'ƝƨÂ)ǩƨƩĞ#űǇĈ'ǳ
5Ɲƨ'űêǭ(ǩƨ' 2 #%7ȊËlrƩĞŗ"Ář'űê±ƶŘ8#í7#ȉƶŘđ'Ɲ
ƨ'űêǭ(Ƨ 3.3 ~ 5.8 mg/L #%7Ȋîȃ(ȉ{'ŵĈ'}¯ưĘFO;Î0Ář;ſ!ƾ! 7Ȋîȃń#!ȉTable 2 &Ɠ­řƚţǭȉŭřƚţǭȉ­řŭĈȉŭřŭĈȉȁÐÖ·;~ Ȋ
Table 2 Experimental conditions
Plate typeTP-1, TP-3, TP-4

Flow rate of cold water mc [L/min]

1, 2.5, 5, 10

Temperature of inlet cold water Tc, in [℃]
Temperature of inlet hot water Th, in [℃]5, 1035, 40

System pressure P [kPa] in hot water tank
System pressure P [kPa] in pure water tank
Dissolved oxygen value [mg/L]

3.9 ~ 6.2 (Tsat = 27.2 ~ 36.4℃)
1.8 ~ 4.6 (Tsat = 15.8 ~ 31.4℃)
1.9 ~ 3.3

3・4 データ整理łîȃ"(ȉ¯ưÑ'ŷǟǤź U [W/m2K] ;ś17#"¯ưŷĘƴ'ǌ;ƾȊŷǟǤź U (ŔĊ"ö°Ȋ
𝑈𝑈 = 𝑄𝑄% ⁄(𝐴𝐴( ∆𝑇𝑇,- )(1)

𝑄𝑄% = 𝑚𝑚% 𝐶𝐶𝐶𝐶% (𝑇𝑇%,456 − 𝑇𝑇%,89 )(2)

" QC [W] (­řŷĩǭȉAs [m2] (VOXdsxX'ƮŷǼƚȉDTlm [] (ôĬąØŭĈĀ" 7Ȋ.ȉQCȉDTlm (88ŔĊ"ś1Ȋ(?@AB C?D,EF )Δ𝑇𝑇;< = (𝑇𝑇%,456 − 𝑇𝑇%,89 )Iln (?

@AB C?D,GHB )(3)

" mc [kg/s] (­ř'ǚǭţǭȉCpc [J/kgK] (­ř'íÖŗŷȉTc,in, Tc,out [] (­ř¢'§Ä#°ÄŭĈ" 7Ȋ.ȉTsat [] (ƍƜŭřRvIª'Ö·;ȁÐÖ· Psat [Pa] ##'ř'ȁÐŭĈ" 7ȊȁÐŭĈ( PROPATH (Propath Group, 2016) "ś1ȊVOXdsxX& 7ąØ¯ưŷǦź hv [W/m2K] (ȉŷǟǤź U c [W/m2K]#­ř¢ŷǦź hc [W/m2K]
5Ē587ŷġĠȉVOXdsxX'ŷöź kP [W/mK]#VOXdsxXÀ t [m] 'ŗ5Ē587ds
xX'ŷġĠ;ſ !ȉ|'Ċ5ś1Ȋ
1

ℎL

1

6

1

(4)

= M − (N + ℎ )ODĊ(4)&ſ ­ř¢ŷǦź hc (ȉĺĆĈ'ÜÏ (ĿȂ5, 2017) #ËŎ&ťŢƿúř 4)Ũúř;ç#ŷĩÑîȃ"Ē58Ŕ'ħƟĊ;ſ Ȋ
𝑁𝑁𝑁𝑁% =SD TUV,D
ND

W/`= 𝐶𝐶W 𝑅𝑅𝑅𝑅%Z.\ 𝑃𝑃𝑃𝑃%(5)"ȉDeq [m](ř·ƋČƊĐȉkc [W/mK](­ř'ŷöź" 7Ȋ.Ċ(5)' Re Ĭ# Pr Ĭ(88 Rec= VcDeqc/nc, Prc = µcCpc/kc "íƲ87­ř& 7 " 7ȊĬ C1 (VOXdsxX'Ƙǿ&É:! Table
3 ' ;~ Ȋ

22

有馬 博史 , 山本 康平

Table 3 The value of coefficients C1 of Eq. (5)C1
TP-1
0.0169TP-30.0108TP-4
0.0625WxRĭż&ſ ­řţǠ Vc [m/s] (­ř'ǚǭţǭmc [kg/s], ­ř'ñĈ𝜌𝜌b [kg/m3] #ţǛİǼƚ Ac [m2];ſ !ŔĊ"ś1Ȋ𝑉𝑉b = 𝑚𝑚b ⁄𝜌𝜌b 𝐴𝐴b(6).ȉƻŘǚǭţǭ mv [kg/s] (ŔĊ"ś1Ȋ

𝑚𝑚d =

ef

(7)

8g,EF C8g,GHB

"ȉiV, in, iV, out [J/kg](ƻŘ§Äȉ°Ä& 7ŗCvRrax" 6ȉƻŘ§Äȉ°Ä& 7ŭĈÂ)Ö·5 PROPATH (Propath Group, 2016) "ś1 ;ſȊyĲȉƻŘ¢'ŷǦź'ĭż(ȉ|'dsxXŷǼǰ lch [m] ÛŰ' Nu Ĭ;ſ !ƾȊ

𝑁𝑁𝑁𝑁, =Sg,Dh

𝑅𝑅𝑅𝑅d =

-g Tij(8)Ng"ȉ kv [W/mK] (řƻŘ'ŷöź" 7Ȋ.ȉƻŘǚǭţǭ(Ŕ' Re Ĭ"ĭż;ƾȊ
(9)

kf lg

4. 結

果

4・1 冷水流量に対する熱交換量îȃ"Ē58¯ưÑ'­řǚǭţǭ mc &ô7ŷĩǭ Qc 'ǳ; Fig. 4 (a)-(c) &ƓȊŷĩǭ(Ċ(2)"ś1 ;Ȋ­ř'ǚǭţǭ(ȉ0 < mc < 0.2 kg/s 'ƢÔ"~ Ȋ'Ļȉ­ř§ÄŭĈ( 5 4)
10ȉƍƜŭřRvIª'ŭĈ( 35 4) 40;~ Ȋ¨!'ń&!ȉŷĩǭ( Qc = 500 ~ 1400 W

1000

1000

1000

500

0
0

Cold Hot
5℃ 35℃
5℃ 40℃
10℃ 35℃
10℃ 40℃

0.1

0.2
0.3
mC [kg/s](a) TP-1 plate

0.4

Cold Hot
5℃ 35℃
5℃ 40℃
10℃ 35℃
10℃ 40℃500

00

QC [W]

1500

QC [W]

1500

QC [W]

1500

0.1

0.2

mC [kg/s](b) TP-3 plate

0.3

0.4

500

0
0

Cold Hot
5℃ 35℃
5℃ 40℃
10℃ 35℃
10℃ 40℃

0.1

0.2
0.3
mC [kg/s](c) TP-4 plate

Fig. 4 The heat transfer rate of the cold-water side against cold-water mass flow rate

0.4

23

アルミプレートを用いたプレート式熱交換器における水蒸気の凝縮熱伝達特性'ƢÔ"Ē58Ȋ.ȉ 8'ń&!2­řǚǭţǭ'ß¸& ȉŷĩǭß¸! 7Ȋ!ȉ'á¼&45,-yí' ;Ɠ#±Ȋ.ȉǊíŭȉ­řǚǭţǭ mc > 0.1 kg/s &Ĉń&47ŗǜ"( 8'VOXdsxX&!2ȉ­ř§ÄŭĈ' Ĳ 4)ŭřRvIŭĈ'ȅ
Ĳŷĩǭȅ%7#:7Ȋ
4・2 冷水流速に対する熱通過率

îȃ"Ē58¯ưÑ'­řţǠ Vc &ô7ŷǟǤź U 'ǳ; Fig. 5 (a)-(c) &ƓȊ­řţǠ(­řǚǭţǭ mc ;Ċ(6)"ĩƟ2'" 7Ȋ.ȉĩƟ8­řţǠ&47ŮíƢÔ( 0 < Vc < 0.5 m/s " 7Ȋ­ř§ÄŭĈ 4)ƍƜŭřRvIª'ŭĈ&!( 4.2 ơ"Ǟ+ #Ëy" 7Ȋ.ȉŷǟǤź U ( U = 500~700 W/m2K ' ;ƓȊFig. 5 46 8'VOXdsxX&!2 1/U ' (ȉµǞ'­řţǠƢÔ"(1/Vc &ô!,-yí' ;Ɠ#±7Ȋ.ȉTP-1, 3 ' 1/U ' (,-Ë" ȉTP-4 ' 1/U '( TP1, 3 46ã;Ɠ! 7Ȋ .6 TP-4 'ŷǟǤź( TP-1, 3 '846 #±7Ȋ

10-2

10-3

10-2

Cold Hot
5℃ 35℃
5℃ 40℃
10℃ 35℃
10℃ 40℃

1/U

1/U

1/U

10-2

10-3

Cold Hot
5℃ 35℃
5℃ 40℃
10℃ 35℃
10℃ 40℃

10-3

Cold Hot
5℃ 35℃
5℃ 40℃
10℃ 35℃
10℃ 40℃

10-4 0
10

101
1/VC

10-4 010102(a) TP-1 plate

101
1/VC

10-4 010102(b) TP-3 plate

101
1/VC

102

(c) TP-4 plate

Fig. 5 The overall heat transfer coefficient against cold-water flow velocity.

4・3 蒸気質量流量に対する平均凝縮熱伝達率

îȃ"Ē58¯ưÑ'ƻŘǚǭţǭ mV &ô7ąØ¯ưŷǦź hv 'ǳ; Fig. 6 (a)-(c) &ƓȊąØ¯ưŷǦź hv (ŷǟǤź U #ÈVOXdsxXń& 7­ř¢ŷǦź hc ' ;Ċ(4)&§7#"ś
1Ȋ 8'VOXdsxX&!2ƻŘǚǭţǭ'ß¸& ¯ưŷǦźß¸ȊVOXdsxX'Ƙǿ&47ŗǜ"(ȉ 8'ŭřRvIw­ř§ÄŭĈȉƻŘǚǭţǭń&!2 TP-1, TP-3 'KxV?vJ>ridsxXŷǼ'ąØ¯ưŷǦź( TP-4 'TRvdsxX'846ã #±7Ȋ.
ȉTP-3 '¯ưŷǦź' Ľ2ȅ #:7ȊyĲȉËy'VOXdsxX& 7¯ưŷǦź'ŗ
ǜ"(ȉŭřRvIŭĈȅ Ĳ 7 (­ř§ÄŭĈȅ Ĳȉ¯ưŷǦźȅ%7¤ÌǄ58Ȋ

1000

1

2

3

mV [kg/s](a) TP-1 plate

456[´10-4]

Cold Hot
5℃ 35℃
5℃ 40℃
10℃ 35℃
10℃ 40℃

2000

hV [W/m2K]

hV [W/m2K]

hV [W/m2K]

Cold Hot
5℃ 35℃
5℃ 40℃
10℃ 35℃
10℃ 40℃

2000

0
0

3000

3000

3000

1000

0

0

1

2

3

mV [kg/s](b) TP-3 plate

456[´10-4]

Cold Hot
5℃ 35℃
5℃ 40℃
10℃ 35℃
10℃ 40℃

2000

1000

0
0

1

2

3
mV [kg/s](c) TP-4 plate

Fig. 6 The averaged condense heat transfer coefficient against vapor mass flow rate.

456[´10-4]

24

有馬 博史 , 山本 康平

4・4 不凝縮性ガスの有無による平均凝縮熱伝達率の比較

łîȃ"Ē58}¯ưĘFO;Î.% řƻŘ'ąØ¯ưŷǦź hv #ĺĆĈÜÏ;ƾ}¯ưĘFO;Î0řƻŘ'ąØ¯ưŷǦź'Ůíƪň (ĿȂ5, 2016) #'ŗǜ; Fig. 7 (a)-(c) &ƓȊFig. 7 (a)-(c) "(8'VOXdsxX&!2ƻŘǚǭţǭ mV 'ŮíƢÔƅ%! 71ƪň'íǭƇ%ŗǜ(ǹ ȉǫǂ! 7ţǭƢÔ"ŗǜ;ƾ #ȉTP-1 # TP- 3 "(ĸ5&}¯ưĘFO'¯ưŷǦź'Ĳȅ;Ɠ! 7#:7ȊyĲȉTP-4 'ÝÉ(,-Ë ;ƓȊă&ƍƜŹĜ;ťřŧř¼;ƾ bpUMnƻƆĊťřŧř¼ǀƱ&!2ȉ}¯ưĘFO&47¯ưŷǦź'Ďǽ 7#ĸ5

#%Ȋ.ȉ>riÉǮǁdsxX'¯ưŷǦź'ǌ&!2½±%ƶŘĕǃ" 7#ƐǏ

8Ȋ
3000

3000

3000
With noncondensable gas
Without noncondensable gas

1000

0
0

1

2

3

mV [kg/s]

4

2000

1000

0
0

5
6
[´10-4]

With noncondensable gas
Without noncondensable gas

hV [W/m2K]

2000

hV [W/m2K]

hV [W/m2K]

With noncondensable gas
Without noncondensable gas

1

2

3

4

mV [kg/s](a) TP-1 plate56[´10-4](b) TP-3 plate

2000

1000

0
0

1

2

3

4

mV [kg/s]

56[´10-4](c) TP-4 plate

Fig. 7 Compared of averaged heat transfer coefficient between with and without noncondensable gas.

4・5 平均凝縮熱伝達率の Nu 数による整理

îȃ"Ē58¯ưÑ'ąØ¯ưŷǦź hv &!ȉĊ(8), (9) "ś1 Nu ĬÂ) Re Ĭ&47ĭż;ƾȊ'ƪň; Fig. 8 &ƓȊFig. 8 46ȉRe Ĭ'ß¸& ȉNu Ĭß¸! 7#±7ȊVOXds
xX'Ƙǿ&47ŗǜ"(ȉTP-3 ' Nu ĬĽ2ȅ TP-1 Ľ2 #:7Ȋ'#5ȉťřŧř¼
ǀƱ& 7¯ư"(ȉĨŉ>riÉǮdsxX'ŷĘƴTRv46¦8! 7#ĸ5" 7Ȋ% ȉÓîȃ"ſ>riÉǮdsxX'ŖŃ'ŷǼ(ąŲǼ" 7ȉTP-4 &ĳ8! 74 %e
qvfxvčŹ'ŷǼ;ĦſÝÉŷǣ'ºňĒ58ȉ
5&ŷĘƴÌ{72'#ę87Ȋ

2000

TP-1 (PEEK 25µm)
TP-3 (WINKOTE)
TP-4 (Titanium)

Nul

1000

0
0

200 400 600 800 1000
ReV

Fig. 8 Relationship between Rev and Nul.

アルミプレートを用いたプレート式熱交換器における水蒸気の凝縮熱伝達特性

5. 結

言

łƏƛ"(ȉdsxXĊŷĩÑſ'ŷdsxX#!ı&Ĩŉ 2 Ƙǿ'>riZAjÉǮdsxX'¯ưŷĘƴ'ǌ'1ȉƶŘ;ƾřƻŘ;ç#¯ưŷǦź'Ůí;ƾȊŗǜ'1TRv'dsxX&47Ůí2!ƾȊ.ȉdsxXĊŷĩÑ(OdsxbpUMnƻƆĊťřŧř¼ǀ
Ʊ&Ʃ/ǝ<"ſ7#;ęí! 7#5ȉîȃ(ƍƜ|&!ƾȊ'ƪň;|&ǉȊ!(­řǚǭţǭ'ß¸&(1) ¨!'VOXdsxXłîȃ'­řǚǭţǭƢÔ"(ȉmc < 0.1 kg/s &!(ŷĩǭ,-yí#%7Ȋ
ŷĩǭ'ß¸ǆò8ȉmc > 0.1 kg/s &(2) TP-1, 3 'VOXdsxX&Řǚǭţǭ'Ďǽ( TP-3 dsxX&!ƻŘǚǭţǭ'ß¸& ¯ưŷǦź'ß¸ǆò8Ȋ.ȉƻ!Ǿƺ" ȊyĲȉTP-4 "(:%ŷǦź'á¼Ē58%Ȋ(3) ƍƜ|&!2}¯ưĘFO'ĿŶ&47¯ưŷǦź*'ĎǽǾƺ#%7#ĸ5#%Ȋ(4) Óŗǜ;ƾVOXdsxX'">riÉǮ; WIN KOTE "KxV?vJ TP-3 dsxXĽ
2¯ưŷĘƴȅ #ĸ5#%Ȋ謝辞łƏƛ( JSPS ƔƏǗ 15K00637 &46ǙǮ'yǧ'¹Ğ;Ã2'" 7Ȋ&ǉ!ěǓ7Ȋ
文

献

Ŝ{ĉ, «žÅƴC[rHx& 7ìíǺů'ď¶;ƉĢťŢŭĈĀƆǺ'ı ùǱ - ŞƯwƣý
5æ.ťŢŭĈĀƆǺ'ƦƫǢƦ, ĵłhqvCvNZ>qvJëǎ, Vol. 50, No. 1 (2015), pp. 5458.
Makai Ocean Engineering, “Makai Connects World’s Largest Ocean Thermal Plant to U.S. Grid”,
http://www.makai.com/makai-news/2015_08_29_makai_connects_otec/ (2015.8).
{ÁĹƁ, Ŝ{ĉ, “ťŢŭĈĀƆǺ#OdsxbpUMnƻƆĊťřŧř¼'ǱƆ#ùŀ”, ĵłťřëǎ,Vol. 53, No. 1, (1999), pp. 2-11.
ŤƀÐ, ìŚ¡, üþÍå, Ŝ{ĉ, ©ýƈÊ, “ƣý& 7ťŢŭĈĀC[rHx'ǂÉ²ſ&ǳ7Û
ƒƏƛ”, ťŢŨúřƏƛ, Vol. 17, (2016) p. 55.
{ÁĹƁ, Ŝ{ĉ, “ťŢŭĈĀƆǺ#OdsxbpUMnƻƆĊťřŧř¼'ǱƆ#ùŀ”, ĵłťřëǎ,Vol. 53, No. 1, (1999), pp. 2-11.
Ŝ{ĉ, Łã, ÉƀƎ , {ÁĹƁ, “OdsxbpUMnƻƆĊťřŧř¼&ǳ7îȃƇƏƛȇÒţĲÌ
'ĎǽȈ”, ĵłťřëǎ, Vol. 59, No. 1, (2005), pp.68-73.
Łã, ǘãëÿëƦƏƛƔ ¾àǒĮ, (2006).
Sami, M. and Y. Ikegami, “On the evaporation of superheated water drops formed by flashing of liquid jets”, International
Journal of Thermal Sciences, Vol. 57, (2012), pp. 37-44.
ĿȂ¾Ç, Ơĝ, Ņƀķy, “OdsxbpUMnƻƆĊťřŧř¼ſ>riZAjÉǮdsxXĊ¯ưÑ'ŷĘƴǌ”, OTEC, Vol. 22, (2017), pp. 27-35.
Sparrow, E. M., Lin, S.H., “Condensation heat transfer in the presence of a noncondensable gas”, Journal of Heat Transfer,
Transaction, ASME, (1964), pp. 430-436.
äǬǷƭ, ƀĖƹ, “ŧř¼Œƴ;Ŀ7DxdvL@IrťŢŭĈĀƆǺMOVj -¯ưÑ& 7}¯ưFO&47¯ưǭ*'Ďǽ-“, ǺŘëǒĮǎ B, Vol. 124, No. 8, (2004), pp. 1021-1026.
Propath Group, W-PROPATH, http://www2.mech.nagasaki-u.ac.jp/PROPATH/ (2016.3).

25