Day 1 Session III - 01 TJ Zhang.masdar

8/18/2019 Day 1 Session III - 01 TJ Zhang.masdar

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Hydrocarbon Refrigeration –

Status, Challenges & Opportunities

Tuesday, September 10, 2013

TieJun (TJ) Zhang

[email protected]


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A research‐driven graduate university in science and technologies

Focused on advanced energy, water and sustainability research

Over 80

professors

and

400

PhD/MSc

students

from

50

countries

1 PhD and 9 MSc programs covering various engineering fields

In collaboration with Massachusetts Institute of Technology (MIT)

Located in carbon‐neutral “Masdar City” in Abu Dhabi, UAE

MASDAR INSTITUTE OF SCIENCE AND TECHNOLOGY

PV Plant

Masdar

Institute

AD Airport


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Research Experience:

• 2011‐2012, Visiting Faculty at DRL, Massachusetts Institute of Technology (MIT), USA

• 2008‐2011, Postdoctoral Research Associate, Rensselaer Polytechnic Institute (RPI), USA

Honors and Awards

• Principal Investigator,

Masdar

Institute

– MIT

Flagship

Solar

Research

Project,

2013

• Alien of Extraordinary Ability in Science, U.S. Department of Homeland Security, 2012

Professional Activities

• K‐18 Technical Committee Member of ASME Heat Transfer Division

• Session

Organizer/Chair

of

many

ASME/IEEE

International

Conferences• Invited Reviewer for over 20 International Journals and Numerous Conferences

DR. TJ ZHANG – BIO & RESEARCH LAB

5 PhD & 6 MSc students

2 Postdoc Researchers

1

Visiting

Scientist


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Cooling Represents ~Half of UAE Electrical LoadADWEA 2008 daily loads for Abu Dhabi Island: Weather Sensitivity

COOLING DEMAND IN ABU DHABI, UAE

Provided by

Dr. Peter Armstrong


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J. Catano, T.J. Zhang, et al., “Vapor Compression Refrigeration Cycle for Electronics Cooling–Part I: Dynamic

Modeling and Experimental Validation & Part II: gain‐scheduling control for critical heat flux avoidance,”

International

Journal

of

Heat

and

Mass

Transfer ,

in

press.

VAPOR COMPRESSION REFRIGERATION COOLING CYCLE

Compact refrigeration

cooling

cycle

research

testbed

at RTRL – Masdar Institute (before insulation)

Diagram of

typical

refrigeration

cooling

cycle

with air‐cooled condenser

Thermo‐

Physical

Property

Heat

Transfer


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-20 0 20 40 60 80 100 120 140 160 1800

1000

2000

3000

4000

5000

6000

7000

8000

Temperature T (C)

P r e s s u r e

P ( k P a

)

R134a

R1234yf

R1234ze

R290 (Propane)

R600a (Isobutane)

R600 (Butane)

R601 (Pentane)

R744 (CO2)

-20 0 20 40 60 80 100 120 140 160 1800

0.5

1

1.5

2

2.5

3x 10

4

Temperature T (C)

V o

l u m

e t r i c C o o

l i n g

C a p a c

i t y

q v ( k J / m

3 )

R134a

R1234yf

R1234ze

R290 (Propane)

R600a (Isobutane)

R600 (Butane)

R601 (Pentane)

R744 (CO2)

Pressure level of different refrigerants Volumetric cooling capacity of different refrigerants

ENVIRONMENT-FRIENDLY ALTERNATIVE REFRIGERANTS

1) At certain operating temperature, the pressure of CO2 is much higher than other refrigerants

2) In a nominal operating temperature range (0‐80 C), the cooling capacity of Propane is higher

3) At high temperature (80‐120 C), the cooling capacity of isobutane/butane is comparable

4) At very high temperature (>120 C), the cooling capacity of pentane is also comparable

Conclusions

T.

J.

Zhang,

S.

Mohamed,

“Conceptual

Design

and

Analysis

of

Hydrocarbon‐

based

Solar

Thermal

Power

and Ejector Cooling Systems in Hot Climates,” ASME Journal of Solar Energy Engineering, under review.


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1 1.5 20

0.5

1

1.5

M a s

s F l o w R a t e ( g / s )

1 1.5 20

100

200

300

t / ts

C o o l i n g C a p a c i t y ( W )

R134a

R1234ze

R290 (Propane)

R600a (Isobutane)

LINEAR COMPRESSOR WITH ALTERNATIVE REFRIGERANTS

M. Alzoubi, T. J. Zhang, “Transient Thermal‐Fluid Modeling of a Linear Micro‐Compressor in Compact Refrigeration

Cooling Systems”

ASME

2013

International

Mechanical

Engineering

Congress

&

Exposition, San

Diego,

USA,

2013.

At the

same

inlet/exit

condition

&

piston

velocity

profile:

1) The cooling flowrate of R1234ze is higher

2) The cooling capacity of Propane is higher0 100 200 300 400 500 600 70050

100

150

200

250

300

350

400

450

500

Enthalpy (kJ/kg)

P r e s s u r e

( k P a

)

Propane (R290)

h

Sat. Vapor

Sat. Liquid

VCC Cycle


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HEAT TRANSFER ON NANOSTRUCTURED SURFACES

• Thin Liquid Film Evaporation on Superhydrophilic Nanostructured CuO Surfaces

• Jumping‐Drop Condensation on Superhydrophobic Nanostructured CuO Surfaces

Vapor condensation on superhydrophobic nanostructured copper surfaces

in Environmental Scanning Electron Microscopy (to be applied to hydrocarbon)


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-200 -100 0 100 200 300 400 500 600 700 800

0

200

400

600

800

1000

1200

1400

1600Pentane

Enthalpy h (kJ/Kg)

P r e s

s u r e P ( k P a )

c

p g

m

myx

d

f

v e

er

ey

power

cooling

sat.vap.

sat.liq.

-0.4 -0.2 0 0.2 0.4 0.6 0.8 1 1.2 1.4 1.60

20

40

60

80

100

120

140

160

180

Pentane

Entropy s [kJ/(kg*K)]

T e m p e r a t u r e T ( C )

cp

g

m

myx

d

f

v e

er

ey

power

cooling

sat.vap.

sat.liq.

amb.T

Hydrocarbon

Refrigerant asWorking Fluid

Ejectorvs.

Compressor

Stand-Alone

COMPACT SOLAR THERMAL POWER & EJECTOR COOLING

T. J. Zhang, S. Mohamed, “Conceptual Design and Analysis of Hydrocarbon‐based Solar Thermal Power

and Ejector

Cooling

Systems

in

Hot

Climates,”

ASME Journal of Solar Energy Engineering, under review.


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1 1.2 1.4 1.6 1.8 2 2.2 2.4 2.6

0

50

100

150

200

Entropy s [kJ/(kg*K)]


R134a

R1234yf

R1234ze

R290 (Propane)

R600a (Isobutane)

R600 (Butane)

R601 (Pentane)R744 (CO

2)

amb. T

10-3

10-2

10-1

100

0

500

1000

1500

2000

2500

3000

3500

4000

4500Pentane

Specific Volume v (m3/kg)

P r e s s u r e P ( k P a )

mt

n my xdf

spinodal

sat.vap.

sat.liq.

Tt=131C

Tn=110C

Isotherm T

MetastableSupersat.

Vapor Zone

Ejector Motive

Flow

Pressure‐specific volume spinodal lines and metalstable

region of pentane (‘o’: ejector motive flow P‐v diagram)

Temperature‐specific entropy lines of different

refrigerants (saturated vapor): ambient T=40 C



WORKING FLUID SELECTION IN EJECTOR COOLING CYCLE


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m t n(e) y x d f 0

200

400

P r

e s s u r e P ( k P a ) Pentane

Motive

Entrain

m t n(e) y x d f 0

50

100

150


Motive

Entrain

m t n y x d f0

1

2

3

M a c h N u m b e r M

Motive



HYDROCARBON REFRIGERANT GAS EJECTOR

Axial pressure/temperature/velocity

distributions

inside a pentane gas ejectorHydrocarbon

refrigerant

gas

ejector

(top: diagram; bottom: automatic ejector photo)

(S& K)


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COMBINED SUPERCRITICAL CO2 BRAYTON & ORC CYCLE

Supercritical‐CO2 Brayton Cycle under development

Organic

Rankine Cycle

Testbed under

development

(Infinity

S‐CO2

Turbine)


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Difference most pronounced at high ambient, high load conditions!

Annual energy savings wrt R410A (Zakula 2012)

w/night precooling Conventional plant

Propane versus R410A 2.4 % 7.8%

Ammonia versus R410A 8.7 % 14.0%

PROPANE VS. R410A IN VRF SPLIT SYSTEM – DR. ARMSTRONG

T. Zakula, P. Armstrong & L. Norford, “Optimal coordination of heat pump compressor and fan speeds and

subcooling over a wide

range

of

loads

and

conditions,”

HVAC&R

Research,

18(6),

pp.

1153

‐1167,

2012


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Applied Research in Cooling Efficiency and Advanced Control(Dr. Peter Armstrong)

1. A/C and Chiller component‐based model for optimal equipment design and control (MI‐MIT)

Air‐cooled,

water

cooled

chiller

and

DX

‐equipment

including

BPHX

Any compressor technology (recip, scroll, screw, centrifugal, economized)

Any refrigerant supported by REFPROP

2. GCC‐Chiller—optimal design & efficiency standard (AD Gov. – Executive Affairs Authority)

Oversize EXV,

combined

condenser

and

evaporator

circuits

Optimal coordination of fan and compressor speeds and SC

3. GCC‐Dehumidification—design & efficiency standard (AD Gov. – Executive Affairs Authority)

Enthalpy‐wheel, run‐around heat exchanger optimized for low SHR

DX coil, variable‐speed condensing unit, subcooling/reheat HX

4. District Cooling

VFD

retrofit

and

optimal

control

(National

Central

Cooling

Co.

– Tabreed)

Variable‐speed CW pump retrofits

Optimal coordination of pumps, CT‐fan, CT cells, and compressors

5. Hydrocarbon refrigeration system safety control system (Collaborating with Dr. TJ Zhang)

OTHER COOLING RESEARCH ACTIVITIES – DR. ARMSTRONG


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Thank You

Q & A


16/17

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3D IMAGE OF CUO NANO-NEEDLES FOR REFRIGERATION


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-20 0 20 40 60 80 100 120 140 160 1800

0.5

1

1.5

2

2.5

3

3.5

Temperature T (C)

K i n e m a t

i c V i s c o s

i t y

v ( c S t )

R134a

R1234yf

R1234zeR290 (Propane)

R600a (Isobutane)

R600 (Butane)

R601 (Pentane)

R744 (CO2)

Kinematic viscosity of different refrigerants (saturated vapor)

(Similar to Saturated liquid/vapor density ratio)

-20 0 20 40 60 80 100 120 140 160 1800

0.002

0.004

0.006

0.008

0.01

0.012

0.014

0.016

Temperature T (C)

S u r f a c e

T e n s

i o n (

N / m )

R134a

R1234yf

R1234ze

R290 (Propane)R600a (Isobutane)

R600 (Butane)

R601 (Pentane)

R744 (CO2)

Surface tension of different refrigerants

THERMOPHYSICAL PROPERTIES OF REFRIGERANTS

Documents

Day 1 Session III - 01 TJ Zhang.masdar