Mitsubishi Heavy Industries Technical Review Vol. 49 No. 1 (March 2012)
56

Deployment of a New Series of Eco Turbo ETI Chillers

KENJI UEDA*1

YASUSHI HASEGAWA*2

KAZUKI WAJIMA*3

MASAHARU NITTA*2

YASUHIRO KAMADA*1

AKIMASA YOKOYAMA*2

The use of inverters in heat source equipment has expanded significantly since the release of
the eco Turbo ETI Series of centrifugal chillers, which are equipped with inverters (as standard
equipment) for energy savings and user-friendliness. In particular, application of inverters
contributes to energy savings in heat source systems subjected to widely varying operating
conditions such as cooling water temperature and load factor. Mitsubishi Heavy Industries, Ltd.
(MHI) is expanding the eco Turbo ETI Series in order to reduce the environmental burden of theseunits. This paper explains the possibility of further series expansion in terms of characteristics,
energy saving effects, and the usefulness of performance enhancements and functional
improvements, as well as technologies for reducing the environmental burden, including the
adoption of new refrigerants.

|1. Introduction
In response to increasing social concerns for energy savings and reduction of CO2 emissions,high-performance centrifugal chillers are currently being widely used in industrial facilities (suchas heat source systems) as well as for residential air conditioning systems. Although centrifugal
chillers are highly efficient heat pump machines, their energy consumption is greater because of
their high capacity. Thus, the development of technologies and products focusing on performanceenhancement is essential in terms of reduction of CO2 emissions. In addition, because centrifugal
chillers are now widely used in many heat source systems, simplicity of installation anduser-friendliness have become important customer needs.
This paper provides a background on the current trends and customer needs in heat source
equipment and describes the evolution and characteristics of the eco Turbo ETI Series ofcentrifugal chillers, which are equipped with inverters (as standard equipment) and were firstreleased in May 2008.1|2. Further Performance Enhancements
For the ETI series of centrifugal chillers, all technical factors for performance enhancement
have been proven in the field of large, high-performance centrifugal chillers, and downsizing andperformance enhancement have both been accomplished through review and refinement of thesetechnical factors. We have expanded the ETI series and achieved further performanceenhancements. The technologies required for these performance enhancements are described
below.

2.1

Performance enhancement for expansion of the series

The ETI-20 series and ETI-40 series, released in 2008, were designed in response to thecapacity range of the adsorption chillers to be replaced. However, the demand for general air
conditioning applications has continued to increase. In order to handle the primary demand for a*1 Manager, Centrifugal & Absorption Chiller Department, Air-Conditioning & Refrigeration Systems*2 Centrifugal & Absorption Chiller Department, Air-Conditioning & Refrigeration Systems*3 Engineering Manager, Centrifugal & Absorption Chiller Department, Air-Conditioning & Refrigeration Systems

Mitsubishi Heavy Industries Technical Review Vol. 49 No. 1 (March 2012)57

capacity zone of 700 USRt (1 USRt = 3.516 kW), and to improve the performance of the ETI-20
series and ETI-40 series in the capacity range of 250 to 350 USRt, in 2011 we added the ETI-30
series and the ETI-60 series, which attains a capacity of 300 USRt with a single compressor. At thesame time, the following technologies have been applied for overall performance enhancement.

Refinement of the shape of the impeller for performance enhancement
Refinement of the shape of the 2nd inlet guide vane for performance and controllability
enhancement
Further reduction of bearing loss
Reduction in the size, weight, and loss of gearOptimization of the suction and discharge flows of the compressor for further reductionof suction and discharge losses
Table 1 lists representative specifications for the ETI-30 series and the ETI-60 series, towhich the above technologies were applied. The rated COP (Coefficient of Performance) evaluatedfor electric power consumption including the inverter input power, oil pump power and control
power was increased to a maximum of 6.2, a performance enhancement of approximately 3% incomparison to the maximum COP of the previous ETI series. The refinements in the shape of theimpeller and the 2nd inlet vane enabled significant performance enhancement around the maximum
capacity. The rated COP around the maximum capacity of the new series exceeds 6.0, a
performance enhancement of approximately 5 % or more in comparison to the previous ETI series(the rated COP is 5.7). As with the previous ETI-20 series and ETI-40 series, the new series do not
require a separate panel because the inverter is installed on the chiller as standard equipment. As aresult, the footprints of these units decreased by approximately 45% in comparison to theequivalent-capacity models of the previous AART series, thus simplifying the installation
procedure.
Table 1

Representative specifications for the ETI series

Type
Cooling capacity
Chilled water temperature
Cooling water temperature
Electric power consumption
COP
Refrigerant

2.2

ETI-20200 USRt
703 kW
116.3 kW
6.0

ETI-40
ETI-30A
400 USRt
300 USRt
1,407 kW o
1,055
kW
o
Inlet 12o C/Outlet 7 oC
Inlet 32 C/Outlet 37 C
232.6 kW172.9 kW
6.0
6.1
HFC-134a

ETI-60A
600 USRt
2,110 kW340.2 kW
6.2

High-performance ES series

An improved high-performance centrifugal chiller, ETI-40ES, has been released.2 Based on
the ETI-40 series, the ETI-40ES uses a double cooling cycle, which was previously applied tolarge-capacity chillers (1,000 USRt or higher). This system has two series-connected refrigerant
cycles, as shown in Figure 1. Because the compression ratio of the compressor is shared, the power
required for compression decreases, and thus the performance is enhanced. In addition, the unit’s
capability for handling large temperature differences allows power reduction at the chilled water
pump. As a result, the rated COP has reached 7.0.2
Table 2 lists representative specifications of the ETI-40ES, and Figure 2 shows its part load
characteristic. The optimized fine inverter control of the two separate compressors for high and low
pressure side allows the maximum COP of 29.1 to be attained during part load operation, which isan improvement of approximately 22% compared with the existing ETI-40 series. Based on thisimprovement of the maximum COP, the IPLV (Integrated Part Load Value) increased to 11.7,
approximately 15% better than the ETI-40. As a result, improvements in both economic efficiency
and CO2 emissions are expected; specifically, yearly CO2 emissions and electricity costs will be
reduced by approximately 68 % in comparison to our previous model, the ART.
Although the standard load control range is 100 % to 10 %, 0 % load operation is alsoavailable as an optional function for enhanced convenience of operation. As with the ETI series,
ETI-40ES has a wide capacity control range. Its inverter is installed on the chiller as standard
equipment, in a manner similar to the ETI-40 series, thus providing a compact design.

Mitsubishi Heavy Industries Technical Review Vol. 49 No. 1 (March 2012)
58

Figure 1 Principle of the double cooling cycle
Table 2

Representative specifications for the ETI-40ES

Cooling capacity
Chilled water temperature
Cooling water temperature
Electric power consumption
COP
IPLV (ARI)

Figure 2 Part load characteristic of
ETI-40ES

400 USRt
1,407 kWoooo
Inlet 17 C/Outlet 7 Co
Inlet 12
C/Outlet 7 CoInlet 32 C/Outlet 37 C
202 kW
213 kW
7.0
6.6
11.7

|3. Further Functional Improvements
In the technical development of centrifugal chillers, we have focused on functional
improvement as well as performance enhancement, thereby allowing users to always make the bestuse of the high performance of their machines. Specifically, we provide 1) indication of real-time
COP and the target COP, 2) indication of the load zone in which optimal operation occurs, and 3) afunction that continuously responds to variations in load and temperature to maintain highperformance.

3.1

Real-time indication of target COP

It is important to be able to judge the appropriateness of current operations to ensure that thecentrifugal chiller operates at high performance. Under rated conditions, such a judgment can bemade by comparison with specifications. In actual operations, however, the load and cooling watertemperature differ from the rated specifications, so that the expected performance (COP) isdifferent from what is expected under rated conditions. Although it is possible to estimate theperformance (COP) accurately via a computer simulation based on actual measured operating data,
this technique is not always applicable due to the complexity. Thus, we have established aperformance estimation procedure, using simple formulas based on theoretical principles.3
Different performance estimation procedures are established for the inverter-driven
centrifugal chiller with variable speed control and the fixed-speed centrifugal chiller. The reason
for this is that the two differ in their capacity control methods: one uses a compressor speed
control, while the other does not. For the fixed-speed centrifugal chiller, part load performance isestimated based on the inlet vane control, taking control of the capacity and the loss characteristic,along with the hot gas bypass control. For the inverter-driven centrifugal chiller, a performance
estimation formula was created to reflect compressor characteristics for all chilling capabilities andchilled water and cooling water temperatures, using an index based on theoretical properties of thepneumatic equipment in the centrifugal compressor. This procedure is more general because losses
at the inlet vane and the hot gas bypass valve can be identified. For both centrifugal chiller control
types, the difference between the estimated and measured values was less than 3 % of the rated
power equivalent, and hence (in view of the measurement accuracy) the electric power
consumption of the chiller can be determined with adequate precision (Figure 3).

Mitsubishi Heavy Industries Technical Review Vol. 49 No. 1 (March 2012)59(a) Fixed-speed centrifugal chiller

Figure 3(b) Centrifugal chiller with variable-speed control

Comparison of estimated and measured values of part load COP

The performance estimation procedure can be installed on a microcomputer board (with lesscomputing power than a typical personal computer) mounted on the chiller and can indicate thetarget COP on the display screen of the chiller operation panel in real time for comparison with theactual measured COP. Comparison of the results should lead to improved chiller operation andearly detection of abnormalities.

3.2
(1)

Chilled water and cooling water flow rate detectors as standard equipment

Chilled water and cooling water flow rate detection
A very effective and widely used overall energy-saving technique for a heat source
system employs a variable flow control for the chilled water (or brine) and cooling water toreduce the electric power consumption of the respective pumps. A variable flow control usually
involves electromagnetic flow meters mounted on the water pipes to obtain flow rate signals forcontrolling the inverter frequencies of the motors driving the pumps. However, because acentrifugal chiller is a high-capacity heat source with large water pipes, and an electromagnetic
flow meter suitable for such a pipe size is expensive, realization of variable flow control ischallenging, and this stands in the way of energy conservation. Thus, the chiller is equippedwith a sensor instead of a flow meter, providing chilled water and cooling water signals that canbe used to control the pumps at moderate cost. Additionally, the expansion valve, the rotation
speed, and the hot gas bypass valve, excluding the inlet vane (which performs PID control of
the chilled water outlet temperature), are controlled on the basis of the chilled water inlet andoutlet temperatures, the chilled water flow rate, the pressure at each point, and the amount ofrefrigerant in circulation, calculated using the cooling capacity that optimizes control of thechiller. For variable flow control of the chilled water, very fine control (and the resulting highenergy-saving efficiency) can be attained using a chilled water flow rate signal to calculate thecooling capacity. Also, the relevant sensor can be used as a substitute for an electromagnetic
flow meter in the system. Moreover, for systems not using variable flow control, robustness is
ensured by allowing adjustable control through detection of departure or staggering bycontinuously monitoring the flow rate of the chilled water and cooling water, which affects theoperating conditions.
(2) Detection of chilled water and cooling water stoppage
A chiller must be equipped with water stoppage detectors in both the chilled water andcooling water systems, to prevent freezing in the heat exchanger tubes of the evaporator andrapid increases in condenser pressure. In the past, the differential pressure at the heat exchanger
for a specified flow rate of the chilled water (or brine) and cooling water was used as thedetection criterion, and a situation in which the differential pressure reached a value equivalent
to a certain flow rate was judged to be a water stoppage. However, this detection method

Mitsubishi Heavy Industries Technical Review Vol. 49 No. 1 (March 2012)60

requires an expensive fine differential pressure detector when the flow rate is low. Thus, weused the flow rate measuring function described above to detect water stoppages under a wide
range of conditions, regardless of the specified conditions. This enables a wider range ofcontrol for the heat source system. Although measurement of the flow rate and detection of awater stoppage involve the same sensor, separate arithmetical processing of each signal canensure a quick response to both, which is essential for water stoppage detection (a function that
protects the equipment) and the accuracy required for flow rate measurement.

|4. Application of a New Environmentally Friendly Refrigerant
In past years, possible ozone-depleting CFC and HCFC refrigerants in refrigeration and air
conditioning equipment were replaced with HFC refrigerants. However, in the wake of thisreplacement, there are growing concerns about the global warming effects of HFC refrigerants,
which have high GWP (Global Warming Potential). In Europe, the F gas regulation, which
includes restrictions on the use of HFC refrigerants in newly built automotive air conditioning
systems, has been in effect since 2011. The refrigerant used in existing centrifugal chillers is
HFC-134a, which has a high GWP of 1430.4 Therefore, we have proposed the application of a
low-GWP refrigerant and tested it on the ETI series.

4.1

Selection of an alternative refrigerant

In the refrigeration and air conditioning industry, the application of low-GWP refrigerants
has mainly been considered for automotive and household air conditioning systems. For
large-capacity centrifugal chillers, which contain large quantities of refrigerant, the application of
low-GWP refrigerants has not been actively discussed because of availability issues.
HFO-1234ze(E), which was developed as an alternative to SF6, is manufactured domestically, andits availability is relatively high. Furthermore, it has thermophysical properties similar to those of
HFC-134a. We have therefore selected HFO-1234ze(E) as a possible low-GWP alternativerefrigerant for centrifugal chillers and have discussed its application.

4.2

Results of the compatibility test with materials

Compatibility assessments of HFO-1234ze(E) with materials used have already been
conducted.5 In a centrifugal chiller, however, the refrigerant exists as a mixture of lubricant andrefrigerant, and hence it is necessary to assess the compatibility of such a mixture with materials toensure that no deterioration occurs in the materials, refrigerant, or lubricant. If material
deterioration occurs, refrigerant leakage, operational problems, or mechanical breakdown may
result. In the lubricant compatibility assessment described above, steel, copper, and aluminummaterials used as catalysts have been verified to be compatible. We performed autoclave tests toassess the compatibility of a mixture of HFO-1234ze(E) and POE (Polyol Ester) with 29
high-polymer materials used as sealing or insulating materials in centrifugal chillers. For 27 of the
29 materials tested, no lubricant acid number increase, turbidity, or material mass decrease
occurred, and thus their compatibility was verified. On the other hand, as Table 3 indicates, two of
the materials (CR and asbestos-free sheet) experienced an acid number increase of 0.2 mgKOH/g
or more, significant turbidity, and deterioration, and hence their compatibility is dubious. However,
because there was no acid number increase or turbidity for the third sealing material (HNBR), CR
and asbestos-free sheet can be replaced with HNBR.
Table 3Compatibility test results for mixture of R1234ze(E) and lubricant

Test specimen
Material

O ringCR(chloroprene rubber)(L3.0) (×)

GasketAsbestos-free sheet(L5.0) (×)

O ring
HNBR(hydrogenated nitrile rubber)(L0.5) (○)

107.5 % (○)

106.5 % (○)

104.1 % (○)

0.98 (×)

1.36 (×)

0.00 (○)

Color (ASTM)

Percentage of mass change
Total acid number(mgKOH/g)

Mitsubishi Heavy Industries Technical Review Vol. 49 No. 1 (March 2012)61

4.3

note 1Results of drop-in test

We performed an operational assessment of an ETI-40 centrifugal chiller with the original
HFC-134a replaced by HFO-1234ze(E). Figure 4 shows an external view of the chiller. Because
HFO-1234ze(E) has a specific gravity at least 20% lower than that of HFC-134a, its cooling
capacity is 71% of the cooling capacity of HFC-134a, provided the volumetric inflow rate to thecompressor is the same for both refrigerant gases. In order to assess the refrigerant characteristics
of HFO-1234ze(E) in comparison to HFC-134a, the test was conducted under operating conditions
in which the HFO-1234ze(E) volumetric inflow rate to the compressor corresponded to 350 USRt,
400 USRt, and 500 USRt of operation with HFC-134a. In addition, the measurements were taken
under part load conditions, which is important for assessing the performance during actual
operation. Figure 5 shows the measurement results for rated performance, and Figure 6 compares
the test results under part load conditions.
The COP of HFO-1234ze(E) at rated performance is 94 % to 97 % of the COP of HFC-134a.
As the load decreases, so does the performance. This is thought to result from the fact that adecrease in the Re number increases the friction loss in the compressor, and the relative percentage
of mechanical loss and motor loss to cooling capacity increases because HFO-1234ze(E) has ahigher viscosity coefficient than HFC-134a. In this regard, if an exclusive design is employed for
optimization of compressor specifications such as impeller diameter or blade shape, performance
similar to that of HFC-134a will be obtained. Under part load conditions, the COP of
HFO-1234ze(E) surpasses that of HFC-134a at a load factor of 40% or lower because it shifts to asmaller load rate than HFC-134a, due to differences in compressor inlet gas density and latent heat.
Note 1: The HFO-1234ze(E) drop-in test with the centrifugal chiller was grant-aided by NEDO in 2010.

Figure 5 Measurement results for rated
performance

Figure 6 Measurement results under part
load conditions

Figure 4 Centrifugal
chiller used in
the R1234ze(E)drop-in test
Figure 7

4.4

LCCP comparison of HFC-134a and HFO-1234ze(E)LCCP (Life Cycle Climate Potential) assessment

Based on the performance measurement results under part load conditions described in 4.3, acomparative assessment of LCCP (the environmental load index for the entire life cycle) was
conducted as shown in Figure 7.note 2 The calculations indicate that although HFO-1234ze(E) has
an indirect effect (CO2 emissions due to electric power consumption during refrigerant
manufacturing and chiller operation) approximately 3 % higher than that of HFC-134a, due to aslight performance decrement, its low GWP can reduce overall CO2 emissions, including a direct

Mitsubishi Heavy Industries Technical Review Vol. 49 No. 1 (March 2012)
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effect (CO2 leakage during operation and disposal), by approximately 30%.
Note 2: LCCP is calculated under the following conditions: 1) annual operating hours is 4,000, 2)
equipment life cycle is 15 years, 3) operational electric power consumption is calculated from the IPLV
load factor and the cooling water temperature, 4) the CO2 emission factor is 0.351 kg/kWh (actual 2009
performance value reported by the Federation of Electric Power Companies of Japan), 5) CO2 emission
during refrigerant manufacturing is 23 kg per 1 kg of manufactured refrigerant (LCCP calculation factorof the Japan Refrigeration and Air Conditioning Industry Association), 6) leakage during operation is
7 % per year, and 7) leakage during disposal is 2 %.

|5. Conclusion
The ETI series high-performance centrifugal chillers offer smaller capacity and compact size,reflecting market needs. The combination of an inverter installed as standard equipment, existinghigh-performance technologies, and a new design concept focused on small capacity achieves highreliability and brings significant energy savings and reduced CO2 emissions to conventional
industrial and commercial customers, as well as to customers desiring smaller capacity chillers for
air conditioning and other applications. In order to expand the ETI series of centrifugal chillers, wehave improved their performance, functionality, and environmental friendliness in response tomarket needs and have verified the results. Furthermore, we have applied a low-GWP refrigerant toadvance the prospect of long-term, continuous energy savings.
It is expected that inverter-equipped centrifugal chillers will be simpler to install, easy to use,and suitable for general purposes. We would like to continue to develop products that meet market
requirements, based on the technologies applied to the ETI series.

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Ueda, K. et al., The “eco Turbo ETI” Series of High-Performance Variable-Speed-Control Centrifugal
Chillers, Mitsubishi Heavy Industries Technical Review Vol. 46 (2009) pp. 51-54
Yokoyama, A. et al., Variable Speed Centrifugal Chiller with Optimal Control for Independent Two
Refrigerant Circuits, The International Symposium on New Refrigerants and Environmental Technology
2010, pp. 132-137
Ueda, K. et al., Development of Calculation Method of Partial Load Performance for Centrifugal Chillers
Part 1, An Outline and Practical Applications of a Method，Proceedings of SHASE (2010-9)，pp. 93-96
Preservation of the Layer of Ozone and of the Global Climatic System(http://www.ipcc.ch/pdf/special-reports/sroc/sroc_spmts_fr.pdf)
Koyama, S. et al., Basic Characteristics of HFO-1234ze(E) as a Next-Generation Low-GWP Refrigerant
Candidate, J. HTSJ, Vol. 49 (2010) p. 40-4