Boiling heat transfer and critical heat flux in helical coils
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Suzuki et al.: Application of Boiling Heat Transfer (1/7)
[Tutorial Paper]
Application of Boiling Heat Transfer to High-Heat-Flux Cooling
Technology in Power ElectronicsKoichi Suzuki*, Kazuhisa Yuki*, and Masataka Mochizuki**
*Tokyo University of Science, Yamaguchi, 1-1-1, Daigaku-dori, Sanyo-Onoda-shi, Yamaguchi 756-0884, Japan
**Thermal Tech. Div., Fujikura Corp., 1-5-1, Kiba, Koto-ku, Tokyo 135-8512, Japan
(Received August 16, 2011; accepted September 12, 2011)
Abstract
Boiling heat transfer is a superior heat transfer technology using the latent heat transport with phase-change. However,
it has been difficult to employ as a cooling technology for electronics because the unstable transition boiling and film
boiling with excessive high temperature are impossible to control. In highly subcooled boiling, the coalescing bubbles
formed on the heating surface collapse to many fine bubbles at the beginning of transition boiling and the heat flux
exceeds the critical heat flux. This boiling regime has been called Microbubble Emission Boiling (MEB). Two models of
cooling device are introduced using subcooled flow boiling with MEB for power electronics, where the maximum heat
flux is 500 W/cm2 (5 MW/m2).
Keywords: MEB (Microbubble Emission Boiling), High Heat Flux, Cooling Technology, Power Electronics
NomenclaturehB ; Heat transfer coefficient in boiling, kJ/m2K
hMEB ; Heat transfer coefficient in MEB, kJ/m2K
q ; Heat flux, W/m2
Tl ; Bulk temperature of liquid, K
Tsat ; Saturation temperature of liquid, K
Tw ; Temperature of heating surface, K
ΔTsub ; Liquid subcooling, K
ΔTsat ; Superheat of heating surface, K
1. IntroductionSince the end of the last century, we have serious prob-
lems with the natural environment, energy resources, and
global warming. In particular, the reduction of CO2 emis-
sions is an important problem to be resolved urgently.
In order to reduce CO2 emission and save fossil fuels,
the development of electric vehicles (EVs) has recently
been accelerated. In the near future, automobiles driven
by petrol or oil will be replaced by EVs or fuel cell vehicles
(FCVs). In the EV power control system, an IC package is
employed for electronic power equipment such as an
inverter. These IC inverters produce large amount of heat
and the maximum heat flux has been predicted at higher
than 300 W/cm2.
Recently, Silicon Carbide, SiC, has attracted interest as
a new power semiconductor material in place of the con-
ventional Silicon. The maximum operating temperature of
SiC is said to be 400~450°C. However, the actual operating
temperature should be lower than 200°C in order to
decrease power loss and to protect circuit parts from high
temperatures. Of course, it is impossible to remove such
high heat flux from the new power IC devices by conven-
tional cooling technologies, namely air cooling or liquid
cooling.
Boiling heat transfer is well known as a superior heat
transfer technology to remove large amounts of heat from
a hot body using the transport of latent heat with a phase-
change. However, there are some difficulties with applying
this cooling method to electronics. The heating surface
becomes covered with coalescing bubbles at the critical
heat flux (CHF), the maximum of nucleate boiling where
the liquid is not fully in contact with the heating surface.
The remaining liquid layer or microlayer below the
coalescing bubbles evaporates rapidly and the surface
begins to dry. The boiling then turns rapidly to film boiling
with the instantaneous temperatures rising through transi-
tion boiling. Finally, the surface is seriously damaged by
the high temperature burnout. Generally, it is impossible
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to control the transition boiling. So it has been difficult to
apply boiling heat transfer to the cooling technology in
electronics.
In highly subcooled boiling, many microbubbles are
emitted from coalescing bubbles formed on the heating
surface at the beginning of transition boiling and the heat
flux exceeds CHF considerably, as CHF shown in Fig. 1
and 2.[1] This boiling regime has been called Microbubble
Emission Boiling (MEB). The investigation of MEB was
started by Shigeaki Inada, Professor of Gunma National
University, in 1981.[2–5] More recently, MEB research
has been conducted by a group led by Satoshi Kumagai,
Professor of Tohoku National University, for subcooled
flow boiling[6–8] and by Kin-ichi Torikai and Koichi
Suzuki for channel flow boiling.[9, 10] For example, the
maximum heat flux is higher than 1000 W/cm2 in sub-
cooled flow boiling of water with heating surfaces smaller
than 10 mm × 10 mm.[8, 11] According to the investiga-
tions of MEB, the authors proposed two models for cool-
ing devices in power electronics. The maximum cooling
heat flux was 500 W/cm2 in subcooled flow boiling of
water with microbubble emissions under atmospheric con-
ditions. The present paper introduces Microbubble Emis-
sion Boiling and its application to cooling technology in
power electronics.
2. Outline of Microbubble Emission Boiling (MEB)Bubble behaviors in subcooled pool boiling are shown
in Fig. 2 as a typical example of MEB.[1] A copper heating
surface 10 mm in diameter is placed facing upward on the
bottom of the boiling vessel. The surface is polished with
#500 sand-paper. The boiling liquid is a mixture of water,
an aqueous solution of 10 wt% Ethanol and an aqueous
solution of 7.5 wt% Propanol. The boiling is performed in
subcooled quasi-pool boiling under atmospheric condi-
tions. Large coalescing bubbles formed on the heating sur-
face at CHF collapse to many fine bubbles at the beginning
of transition boiling. The liquid is supplied to the heating
surface as the bubbles collapse. The supplied liquid then
evaporates and the boiling bubbles again expand to large
coalescing bubbles at CHF. The process is repeated rap-
idly and the heat flux exceeds the critical heat flux.[9, 10]
Microbubble emission boiling occurs significantly in
highly subcooled flow boiling. Boiling curves with MEB
are shown in Fig. 3 as an example of subcooled flow boil-
ing in a horizontal rectangular channel.[10] As an exam-
ple, a test section for channel flow boiling is shown in Fig.
4. The channel is 17 mm in height, 12 mm in width and 150
mm in length and is set horizontally. The 10 mm × 10 mm
heating surface is the upper surface of a copper heating
block placed at the bottom of the horizontal rectangular
channel. The heating block consists of a straight section
and a base block. A number of cartridge heaters are
Fig. 1 Typical Boiling curve including MEB.
Fig. 2 Video pictures of microbubbles emitted from coalesc-ing bubbles formed on heating surface (10 mm in diameter) in subcooled quasi-pool boiling with MEB at liquid subcooling of 40 K.
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inserted in the base section. Three K-type sheathed ther-
mocouples 0.5 mm in diameter are fitted in the axis of the
straight section with 1 mm, 3 mm and 5 mm from the heat-
ing surface. The surface temperature is estimated by
extrapolating the measured temperature distribution and
the heat flux is calculated by the temperature gradient
using Fourier’s thermal conduction equation in steady
state. The heating surface is polished with #500 sandpaper
prior to the boiling test. The heating block is enveloped
with thermal insulations and the heat loss is estimated at
less than 5% of the axial heat flow in the straight section
according to a number of previous experiments by the
authors.
Distilled water is used for the boiling liquid and the
mean pressure in the channel is maintained near atmo-
spheric pressure. The mass flow rate is 500 kg/m2s (0.5
m/s). Bubble behaviors on the heating surface are
observed using a high-speed video camera through a
transparent glass window assembled in the side housing of
the channel. Pressure fluctuations are measured by an
electronic pressure transducer installed over the heating
surface.
Subcooled boiling was tested for liquid subcooling at 20
K, 30 K, 40 K, 50 K and 60 K.[10] At the beginning of tran-
sition boiling, MEB occurs and the heat fluxes exceed the
CHFs, as shown in Fig. 3. The maximum heat flux reaches
10 MW/m2 at the higher liquid subcooling of 40 K. How-
ever, no MEB occurs at the 20 K liquid subcooling or the
boiling turns instantaneously to transition boiling without
increasing heat flux even if MEB occurs. Therefore, the
liquid subcooling is an important factor for MEB genera-
tion.
The liquid subcooling ΔTsub is defined as the difference
between the saturation temperature of the liquid Tsat and
the bulk liquid temperature, Tl , as indicated in equation
(1). The superheating of the heating surface, ΔTsat , is
defined as the difference between the temperature of the
heating surface, Tw , and the saturation temperature of the
liquid, Tsat , as indicated in equation (2).
ΔTsub = Tsat - Tl (1)
ΔTsat = Tw - Tsat (2)
The heat transfer coefficient is given by the boiling
curves shown in Fig. 3. The heat transfer coefficient in
boiling is based on the superheating of the heating surface
as in equation (3).
hB, hMEB = q/ΔTsat (3)
For example, the heat transfer coefficient hB in nucleate
boiling is about 80,000 W/m2K and hMEB in MEB is
140,000~200,000 W/m2K given by the experimental result
shown in Fig. 3. Those heat transfer coefficients are con-
siderably higher than those in single phase flow heat trans-
fer.
3. Applications of MEB for Cooling TechnologyGenerally, an inverter used for an EV is composed of IC
packages and the cooling surface is considered large, 10
cm × 20 cm for example. The thermal emission rate is pre-
dicted to be higher than 100 W/cm2 (1 MW/m2), because
the thermal emission issued from an inverter is generally
estimated to be at least 20 percent of the maximum power
output of an electric vehicle, which is assumed to be 100
kW. For cooling an inverter with a single channel, it is dif-
ficult to remove the heat from the down-stream section of
cooling surface as shown in Fig. 5. The maximum heat
flux and CHF are indicated for the length of the surface in
Fig. 6 in our experimental results on the subcooled flow
boiling of water in a horizontal rectangular channel. The
heating surfaces are placed at the bottom of a horizontal
Fig. 3 An example of subcooled flow boiling of water with MEB at liquid velocity of 0.5 m/s (500 kg/m2s).
Fig. 4 An example of subcooled flow boiling of water with MEB at liquid velocity of 0.5 m/s (500 kg/m2s).
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rectangular channel 5 mm in height. The temperature of
the distilled water is 40 K of liquid subcooling at the inlet
of the channel and the mean flow velocity is 0.5 m/s (500
kg/m2s). The maximum heat flux and CHF decrease with
the length of the heating surface. The critical heat flux
agrees roughly with the correlation proposed by
Haramura-Katto[12] and Ivey-Morris.[13] For a long heat-
ing surface, the maximum heat flux decreases as shown in
Fig. 6. The experimental data indicate that the limit of cool-
ing length in MEB is less than 50 mm.
According to the experimental results on subcooled flow
boiling of water in a horizontal rectangular channel, the
authors have proposed two models of high-heat-flux cool-
ing device for power electronics.
3.1 Compact High-Heat-Flux Cooling Device (CHCD) [11, 14, 15]
Subcooled flow boiling was conducted for a horizontal
rectangular channel with a flat heating surface placed at
the bottom of the channel.[14] The channel is 5 mm in
height, 24 mm in width, and 300 mm in length for a single
unit. The heating surface is made of copper and is 20 mm
in width and 50 mm in length. The boiling curves at liquid
subcooling of 40 K and liquid velocity of 0.5 m/s (500
kg/m2s) are shown in Fig. 7.[14] Significant microbubble
emission boiling occurs and the heat flux exceeds the
CHF. The maximum heat flux obtained is 500 W/cm2 (5
MW/m2) and the maximum heat removal is 5 kW.
The test section is useful for a high-heat-flux cooling
device where the length of the cooling surface is shorter
than 50 mm. The proposed simple cooling device is named
CHCD (Compact High-Heat-Flux Cooling Device).
A concept of the composite type of CHCD is shown in
Fig. 8.[11] The maximum heat removed from the power
component is 120 kW. However, high pressure fluctuations
are generated in MEB as shown in Fig. 9.[14] MEB is
extremely vigorous reaching a maximum pressure of
700~800 kPa.
In order to reduce the excessive instantaneous pressure
fluctuations, many needle rods 0.5 mm in diameter and 4~4.5
mm in length are assembled in a lattice with 3~5 mm sepa-
ration just above the heating surface from the upper hous-
ing of the rectangular channel, as shown in Fig. 10.[14, 15]
Fig. 6 Maximum heat flux and CHF with length of heating surface in subcooled flow boiling of water in horizontal rectan-gular channel at liquid subcooling of 40 K and liquid velocity of 0.5 m/s (500 kg/m2s).
Fig. 7 Subcooled flow boiling of water at liquid subcooling of 40 K and liquid velocity of 0.5 m/s (500 kg/m2s) under atmo-spheric condition. Heating surface = 50 mmL × 20 mmW.
Fig. 8 A concept of integrated CHCD of 24 CH. Max. cooling heat = 120 kW.
Fig. 5 Surface temperature in subcooled flow boiling with long sized heating surface.
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In microbubble emission boiling, large coalescing bubbles
divide into small ones. The pressure fluctuations decrease
dramatically and the peak pressures are lower than 200
kPa, as shown in Fig. 11.[14] According to the experiment,
a low noise and high-heat-flux cooling device can be pro-
duced by the pressure reduction needles.
3.2 Passive-Active High-Heat-Flux Cooling Device (PHCD) [11, 16, 17]
For a heating surface longer than 50 mm, it is difficult to
remove the high heat flux from a high-powered electronics
device with a single cooling channel. The liquid subcooling
decreases as it flows along the heating surface and large
coalescing bubbles form on the down-stream section as
shown in Fig. 5. Microbubble emission boiling is gener-
ated on the up-stream section but dry-out can easily occur
in the down-stream section.
An inverter with an IC package is employed for an elec-
tric vehicle. The size of the cooling surface will be 20 cm ×
20 cm for more than 100 kW of poweroutput. In order to
prevent the long heating surface from dry-out, a model of
cooling device with two channels and multi-needle nozzles
is proposed and shown in Fig. 12.[11, 16, 17]
The subcooled liquid is separated into the main channel
and the sub-channel assembled over the head of the main
channel. The subcooled fluid in the sub-channel flows
counter to the main channel flow. The tips of the nozzles
have four small slits and are placed within 1 mm of the
heating surface.
The performance of the cooling device is shown in Fig.
13. In the experiments, the cooling device was tested for a
single unit with a heating surface 100 mm in length × 10
mm in width. The main channel is 5 mm high and the sub-
channel is 10 mm high. Nine nozzles, each 1 mm in diame-
ter and 4.5 mm in length, are aligned on the centerline of
heating surface at 10 mm intervals.
Distilled water is used and the liquid subcooling is 40 K
under atmospheric conditions. With a low thermal load,
the cooling is performed in Passive Mode, where the mean
velocity of the liquid is 0.03~0.05 m/s (30~50 kg/m2s) in
the main channel, as shown in Fig. 13. The maximum cool-
ing heat flux is 500 kW/m2 (50 W/cm2) in the passive
mode. With increasing thermal emission, the flow rate of
Fig. 9 Pressure fluctuations in cooling channel at bubble col-lapse in MEB. Liquid subcooling ΔTsub = 40 K, Liquid veloc-ity = 0.5 m/s (500 kg/m2s), Superheat of heating surface ΔTsat = 43 K.
Fig. 10 Illustration of cooling device with needles assembled overhead of cooling Surface.
Fig. 11 Pressure damping in the channel with the number of needle in MEB. Heating surface = 50 mmL × 20 mmW. Liquid subcooling ΔTsub = 40 K, Liquid velocity = 0.5 m/s.
Fig. 12 Cutting view of Passive-Active High Heat Flux Cool-ing Device (PHCD).
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the subcooled liquid in the main channel is increased to
0.5 m/s (500 kg/m2s) and the cooling is performed mainly
by the main channel flow until the thermal emission
reaches 2 MW/m2 (200 W/cm2).
In the higher thermal emission region, the subcooled
liquid is supplied into the heating surface directly from the
sub-channel through the multi-needle nozzle. The strong
subcooled jet removes the thin vapor film from the sur-
face. This is Active Cooling Mode. The active mode
removes up to 5 MW/m2 (500 W/cm2). So the dual chan-
nel cooling device was named PHCD (Passive-Active High-
Heat-Flux Cooling Device). The maximum heat flux of 500
W/cm2 is sufficient to cover the cooling limit of future
power electronics for motor vehicles. PHCD is flexible in
terms of the size of cooling surface using multiple-units or
multiple-channels and can adapt to cool variable thermal
loads by continuously changing the cooling mode.
4. ConclusionIn subcooled boiling of water, microbubble emission
boiling (MEB) is generated at liquid subcooling above 20
K under atmospheric conditions and the heat flux exceeds
critical heat flux (CHF). The maximum heat flux is 10
MW/m2 (1 kW/cm2) at liquid subcooling higher than 40 K
and liquid velocity of 0.5 m/s (a mass flow flux of 500
kg/m2s) for a small heating surface of 10 mm × 10 mm
with a cm-sized rectangular channel. The cooling heat flux
decreases with the length of the heating surface. For a
long heating surface with a single flow channel, it is diffi-
cult to remove high heat flux in the down-stream section of
the heating surface.
Two models of compact high-heat-flux cooling devices
using MEB have been proposed for high thermal-emission
electronic devices such as IC packaged inverters used for
electric vehicles or power electronics. They are a CHCD
(Compact High-Heat-Flux Cooling Device) with a single
rectangular channel and a PHCD (Passive-Active High-
Heat-Flux Cooling Device) with two channels and a multi-
needle nozzle.
The maximum length of the heating surface is 50 mm
for CHCD. The maximum cooling heat flux is 5 MW/cm2
(500 W/cm2) at liquid subcooling of 40 K and 0.5 m/s (500
kg/m2s), however, considerable high pressure fluctuation
is induced at the collapse of large coalescing bubbles in
MEB. The strong pressure fluctuations are successfully
reduced by a multi-needle rod placed in lattice-wise above
the heating surface.
PHCD has been proposed for heating surfaces longer
than 50 mm. In the experiments, the test was conducted
for a device with a heating surface 100 mm in length and
10 mm in width. The maximum cooling heat flux of 5
MW/m2 (500 W/cm2) was obtained in active mode with
impinging jets in addition to the main channel flow. The
maximum heat flux is sufficiently higher than the pre-
dicted heat flux of 3 MW/m2 (300 W/cm2) emitted from
the power IC package used for electric vehicles or a com-
pact electric power generator.
Acknowledgement The fundamental study on microbubble emission boil-
ing was supported financially by a Grant-in-Aid for Scien-
tific Research promoted by the JSPS (Japan Society for the
Promotion of Science) in 2002–2005.
The research and development for high-heat-flux cool-
ing technology was carried out as part of the “Project of
Fundamental Technology Development for Energy Con-
servation” promoted by NEDO (New Energy and Indus-
trial Technology Development Organization of Japan) in
2002–2005.
The further experiments with the PHCD cooling device
were conducted in the “Project to develop innovative
seeds” promoted by the JST (Japan Science and Technol-
ogy Agency) in 2006. The authors express our gratitude to
NEDO, JSPS, and JST for their support of the experimen-
tal research and development. Furthermore, the authors
also wish to express their sincere appreciation to Prof.
Hiroshi Kawamura of Tokyo University of Science, Prof.
Haruhiko Ohta of Kyushu University, Dr. Yoshiyuki Abe of
AIST, Dr. Hideo Iwasaki of Toshiba Corp., Prof. Masaru
Ishizuka of Toyoma prefectural University, Dr. Masataka
Mochizuki of Fujikura Corp. and Prof. Johannes Straub of
Fig. 13 An example of cooling performance of PHCD, Liquid subcooling Tsub = 40 K.
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Technical University of Muenchen for their great coopera-
tion in the experimental research and development.
References[1] K. Suzuki, “Microbubble Emission Boiling of Alco-
hol-Water Mixtures,” IASME Transactions, Issue 7,
Vol. 2, pp. 1106–1111, 2005.
[2] S. Inada, Y. Miyasaka, R. Izumi, and Y. Owase, “A
study on Boiling Curves in Subcooled Pool Boiling
(1st Report, An effect of liquid subcooling on local
heat transfer),” Transaction of JSME, Vol. 47, No.
417, pp. 852–861, 1981 (in Japanese).
[3] S. Inada, Y. Miyasaka, S. Sakamoto, and R. Izumi, “A
study on Boiling Curves in Subcooled Pool Boling
(2nd Report, An effect of liquid subcooling on local
heat transfer),” Transaction of JSME, Vol. 47, No.
422, pp. 2021–2029, 1981 (in Japanese).
[4] S. Inada, Y. Miyasaka, and R. Izumi, “A study on Boil-
ing Curves in Subcooled Pool Boiling (3rd Report,
Behaviors of bubble cluster and temperature fluctua-
tions of heating surface),” Transaction of JSME, Vol.
47, No. 422, pp. 2030–2041, 1981 (in Japanese).
[5] S. Inada, Y. Miyasaka, R. Izumi, and M. Kobayashi,
“A study on Boling Curves in Subcooled Pool Boling
(4th Report; Heat transfer mechanism in transition
boiling),” Transaction of JSME, Vol. 47, No. 423, pp.
2199–2208, 1981 (in Japanese).
[6] A. Fujibayashi, S. Kumagai, and T. Takeyama,
“Effects of Surface Orientation on Heat Transfer in
Highly Subcooled Convection Boiling,” Transaction
of JSME, Vol. 51, No. 463, pp. 919–927, 1985 (in
Japanese).
[7] R. Kubo and S. Kumagai, “Occurrence and Stability of
Microbubble Emission Boiling,” Transaction of JSME,
Vol. 58, No. 546, pp. 497–502, 1992 (in Japanese).
[8] S. Kumagai, M. Murata, M. Izumi, and R. Shimada,
“Heat Transfer Mechanism Based on Temperature
Profiles and Bubble Motion in Microbubble Emis-
sion Boiling,” Proc. 6 the ASME-JSME thermal Engi-
neering Joint Conf., CD-ROM C6-219, 2003.
[9] K. Suzuki, K. Torikai, H. Satoh, J. Ishimaru, and Y.
Tanaka, “Boiling Heat transfer of Subcooled Water in
a Horizontal Rectangular Channel (Observation of
MEB and MEB generation),” Transaction of JSME,
Vol. 65, No. 637, pp. 3097–3104, 1999 (in Japanese).
[10] K. Suzuki and R. Inagaki, “A Fundamental Study on
High Heat Flux Cooling using Subcooled Flow Boil-
ing with Microbubble Emission,” Proc. 5th Interna-
tional Conference on Enhanced, Compact and Ultra-
compact Heat Exchangers: Science, Engineering and
Technology, CD-ROM, CHE2005-37, 2005.
[11] K. Suzuki, “Microbubble Emission Boiling for
Advanced Compact Heat Exchanger,” Proc. 7th
International Conference on Enhanced, Compact
and Ultra-compact Heat Exchangers: Science, Engi-
neering and Technology, CD-ROM, CHE2009-31,
2009.
[12] Y. Haramura and Y. Katto, “A New Hydrodynamic
Model of Critical Heat Flux, Applicable Widely to
Both Pool and Forced Convection Boiling on Sub-
merged and Bodies in Saturated Liquid,” Interna-
tional Journal of Heat and Mass Transfer, Vol. 26,
No. 3, pp. 389–399, 1983.
[13] H. J. Ivey and D. J. Morris, “On the Relevance of
Vapor Liquid Exchange Mechanism for Subcooled
Boiling Heat Transfer at Higher Pressure,” Rep.
AEEW-R-137, UKAEA, Winfrith, 1962.
[14] K. Suzuki, Y. Goto, and Y. Tanabe, “High Heat Flux
Cooling for Power Electronics using Subcooled Flow
Boiling with Microbubble Emission,” Proceedings of
the 17 th International Symposium on Transport
Phenomena, CR-ROM No. 3-B-I-1, 2006.
[15] Tokyo University of Science, PCT: WO2007/102498,
2007.
[16] K. Suzuki, H. Kawamura, S. Tamura, and H. Maki,
“Subcooled Flow Boiling with Microbubble Emis-
sion; Development for High Heat Flux Cooling Tech-
nology in Power Electronics”, Proceedings of the
13th International Heat Transfer Conference,
CD-RM BOI-28, 2006.
[17] Tokyo University of Science, Japanese Patent, No.
4766427, No. 4766428, 2011.