JP5901191B2 - Turbo chiller performance evaluation apparatus and method - Google Patents

Description

  The present invention relates to a turbo chiller performance evaluation apparatus and method.

  Conventionally, a method disclosed in Patent Document 1 is known as a method for evaluating the performance of a turbo refrigerator. Patent Document 1 focuses on the point that the COP characteristic in an ideal environment without loss approximates to the inverse Carnot cycle, and adds a correction coefficient representing the compressor characteristic to the expression representing the inverse Carnot cycle and turbo A method of calculating the maximum COP that can be exhibited by the refrigerator (hereinafter referred to as “target COP”) is disclosed.

JP 2011-106792 A

The calculation method of the target COP disclosed in Patent Document 1 uses a device loss amount actually generated as a correction term with respect to the COP characteristic in an ideal environment having no loss represented by the inverse Carnot cycle equation. Based on the technical idea of giving.
In the method disclosed in Patent Document 1, the device loss due to the compressor is given as a correction coefficient Cf using the relative load factor as a parameter, but devices other than the compressor constituting the turbo refrigerator, for example, an evaporator or a condenser The loss of the heat exchanger such as a heat exchanger is given as a constant value in the term of loss equivalent temperature difference Td.

  According to the present invention, when a target COP is calculated by giving a device loss amount actually generated as a correction term to a COP characteristic under an ideal environment without loss, the loss corresponding to the performance of the condenser is calculated. An object of the present invention is to provide a turbo chiller performance evaluation apparatus and method for improving the calculation accuracy of a target COP by giving a temperature difference.

In order to solve the above problems, the present invention employs the following means.
The present invention is an apparatus for evaluating the performance of a turbo chiller including a compressor and a condenser as a heat exchanger, and an actual loss of equipment is expressed in an expression representing COP characteristics under an ideal environment without loss. Using an arithmetic expression given as a correction term, a calculation means for calculating a target COP that is the maximum COP that can be exhibited by the refrigerator is provided, wherein the heat exchange loss of the condenser is the correction term. The heat exchange loss of the condenser is calculated using a load factor, a cooling water outlet temperature, and a function of the centrifugal chiller calculated using a function with a difference between the cooling water outlet temperature and the cooling water outlet temperature as a parameter. A performance evaluation apparatus is provided.

  According to the present invention, the maximum COP that can be exhibited by the refrigerator using an arithmetic expression in which an actual device loss is given as a correction term in an expression representing the COP characteristic in an ideal environment without loss. A certain target COP is calculated. In this case, the arithmetic expression includes the heat exchange loss of the condenser as a correction term, and the heat exchange loss of the condenser includes the load factor, the cooling water outlet, and the cold water outlet temperature and the cooling water outlet temperature. The heat exchange loss of the condenser depends on the load factor, the cooling water outlet temperature, and the difference between the cooling water outlet temperature and the cooling water outlet temperature to calculate the target COP. Can be reflected. Thereby, the calculation accuracy of the target COP can be improved.

  In the turbo chiller performance evaluation apparatus, the calculation formula for calculating the heat exchange loss of the condenser obtains the relationship between the cooling water outlet temperature and the heat exchange loss of the condenser for each load factor, and the relationship Is preferably derived from

  In this way, the relationship between the cooling water outlet temperature and the heat exchange loss of the condenser is obtained for each load factor, and the heat exchange loss of the condenser is calculated using a function derived from this relationship, so the reliability is high. The heat exchange loss of the condenser can be obtained.

In the turbo chiller performance evaluation apparatus, the heat exchange loss of the condenser is, for example, due to an influence of an air volume of the refrigerant gas having a change in a specific volume of the refrigerant gas represented by a load factor and a cooling water outlet temperature as a parameter. It is represented by the sum of a loss-corresponding temperature difference and a loss-corresponding temperature difference due to the influence of superheated steam with the difference between the cold water outlet temperature and the cooling water outlet temperature as a parameter.
For example, the loss-corresponding temperature difference due to the effect of the air volume of the refrigerant gas has a characteristic of showing a higher value as the cooling water outlet temperature is lower, and the loss-corresponding temperature difference due to the influence of the superheated steam is The higher the temperature, the higher the numerical value.

  In the turbo chiller performance evaluation apparatus, the COP characteristic in an ideal environment without loss may be represented by an equation representing an inverse Carnot cycle.

  As described above, by using an expression representing the inverse Carnot cycle as an expression representing the COP characteristic under an ideal environment without loss, the arithmetic expression of the target COP can be simplified, and the calculation of the target COP can be performed. The time required and the processing burden can be reduced.

  In the turbo chiller performance evaluation apparatus, a mechanical loss due to the performance of the compressor may be given as the correction term in the arithmetic expression.

  Since the mechanical loss due to the performance of the compressor is given as a correction term in the arithmetic expression for calculating the target COP, the mechanical loss due to the compressor can be reflected in the target COP. Thereby, the calculation accuracy of the target COP can be further improved.

  The present invention is a method for evaluating the performance of a turbo chiller including a compressor and a condenser as a heat exchanger, and an actually generated equipment loss is expressed in an expression representing COP characteristics under an ideal environment without loss. A calculation step of calculating a target COP that is the maximum COP that can be exhibited by the refrigerator using the calculation formula given as the correction term is provided, and the calculation formula includes the heat exchange loss of the condenser as the correction term. The heat exchange loss of the condenser is calculated using a load factor, a cooling water outlet temperature, and a function of the centrifugal chiller calculated using a function with a difference between the cooling water outlet temperature and the cooling water outlet temperature as a parameter. A performance evaluation method is provided.

  According to the present invention, there is an effect that the calculation accuracy of the target COP can be improved.

It is the figure which showed schematic structure of the inverter turbo refrigerator which concerns on one Embodiment of this invention. It is the functional block diagram which expanded and showed the function with which the performance evaluation apparatus of the inverter turbo refrigerator which concerns on one Embodiment of this invention is provided. It is the figure which showed the heat-transfer state in a shell and tube condenser. It is the figure which showed the relationship between the cooling water exit temperature when changing a load factor, and the heat exchange performance of a condenser. It is the figure which showed roughly the state of the refrigerant | coolant liquid and refrigerant gas in a shell and tube condenser. FIGS. 6A and 6B are diagrams illustrating a difference in superheat degree depending on the heat insulating head. FIG. 6A illustrates a case where the heat insulating head is high, and FIG. 6B illustrates a case where the heat insulating head is low. The loss equivalent temperature difference of the condenser is the loss equivalent temperature difference due to the influence of the air volume of the refrigerant gas with the change in the specific volume of the refrigerant gas represented by the load factor and the cooling water outlet temperature as the parameter, the cold water outlet temperature and the cooling It is a figure showing that it becomes the sum of temperature difference equivalent to loss by the influence of superheated steam which makes a difference with water outlet temperature a parameter.

  Hereinafter, an embodiment of a performance evaluation device for a centrifugal chiller according to the present invention will be described with reference to the drawings. In the present embodiment, a case will be described in which the performance evaluation device for a centrifugal chiller is provided in a control device that controls the centrifugal chiller. In the following description, an inverter turbo chiller will be described as an example. However, the performance evaluation device for a turbo chiller according to the present invention is not limited to an inverter turbo chiller, but a fixed speed turbo chiller. Is applicable.

  FIG. 1 is a diagram showing a schematic configuration of an inverter turbo refrigerator 1. The inverter turbo refrigerator 1 includes a turbo compressor 11 that compresses refrigerant, a condenser 12 that condenses high-temperature and high-pressure gas refrigerant compressed by the turbo compressor 11, and an evaporator that evaporates liquid refrigerant that passes through the condenser 12. 13, The control apparatus 14 which controls the inverter turbo refrigerator 1 is provided as a main structure.

  Further, the inverter turbo chiller 1 measures a temperature sensor 30 that measures the chilled water inlet temperature Tr1, a temperature sensor 31 that measures the chilled water outlet temperature Tr2, a flow rate sensor 32 that measures the chilled water flow rate F1, and a cooling water inlet temperature Tw1. A temperature sensor 33, a temperature sensor 34 for measuring the cooling water outlet temperature Tw2, a flow rate sensor 35 for measuring the cooling water flow rate F2, and the like are provided. The measurement values of these sensors 30 to 35 are transmitted to the control device 14.

  In addition, the structure of the inverter turbo refrigerator 1 shown in FIG. 1 is an example, and is not limited to this structure. Moreover, the inverter turbo refrigerator 1 is not limited to the case where it has only a cooling function, For example, you may have only a heating function or both a cooling function and a heating function.

  The control device 14 has a function of controlling the number of revolutions of the turbo compressor 11 based on measured values received from each sensor and a load factor sent from the host system, and a function of evaluating the performance of the refrigerator. Have.

  The control device 14 includes, for example, a CPU (Central Processing Unit) (not shown), a RAM (Random Access Memory), a computer-readable recording medium, and the like. A series of processing steps for realizing various functions to be described later are recorded in a recording medium or the like in the form of a program, and the CPU reads the program into a RAM or the like to execute information processing / arithmetic processing. Thus, various functions described later are realized.

  FIG. 2 is a functional block diagram showing expanded functions related to performance evaluation among the functions of the control device 14. As illustrated in FIG. 2, the control device 14 includes a data acquisition unit 101, a storage unit 102, and a calculation unit 103.

  The data acquisition unit 101 acquires operation data of the inverter turbo chiller 1 as input data. As the operation data, for example, the cold water inlet temperature Tr1 measured by the temperature sensor 30, the cold water outlet temperature Tr2 measured by the temperature sensor 31, the cooling water inlet temperature Tw1 measured by the temperature sensor 33, and the temperature sensor 34 are measured. The cooling water outlet temperature Tw2, the current load factor, and the like.

  The storage unit 102 stores an arithmetic expression for calculating a target COP, which is the maximum COP that the inverter turbo chiller 1 can achieve in terms of performance at each operating point. Hereinafter, the arithmetic expressions stored in the storage unit 102 will be described.

COP _ct = {(Tr2 + 273.15) / (Tw2-Tr2 + Td)} / Cf (1)

The above equation (1) shows the actual device loss for the COP characteristic in an ideal environment without loss represented by the inverse Carnot cycle equation (hereinafter referred to as “actual machine ideal COP”). This is an arithmetic expression given as correction terms Cf and Td. By using this equation (1), the target COP _ct is calculated.
In the equation (1), the correction term Cf is a correction term for reflecting the device loss due to the device characteristics of the turbo compressor 11 in the actual ideal COP, and Td is the loss equivalent temperature difference between the evaporator and the condenser. This is a correction term to be reflected in. Further, Tr2 is a cold water outlet temperature, Tw2 is a cooling water outlet temperature, and the measured values of the temperature sensors 31 and 34 are substituted.

Specifically, the correction term Cf is obtained by the following equation (2).
Cf = f (Qfr) (2)

  Here, Qfr is expressed by the following equation (3).

  Qfr = Qf / Qr (3)

The above expression (3) is an arithmetic expression derived based on the device characteristics of the turbo compressor 11, and is a predetermined value in the difference between the predetermined cooling water outlet temperature set as the operation reference point and the predetermined cold water outlet temperature. It is an arithmetic expression for calculating a relative load factor Qfr representing a current load factor in a difference between a current cooling water outlet temperature and a current cold water outlet temperature with respect to a load factor. (3) In the equation, Qf the current load ratio, _{Q r} is given by the following equation (4).

Qr = φ / μad ^1/2 (Had / k ₁₀₀ ) ^1/2 = 0.1 * (Had / 19.4) ^1/2 (4)

  Had in the equation (4) is given by the following equation (5) from the thermodynamic characteristics.

Had = (-2.7254 * 10 ^-4 Tr2 ² -9.0244 * 10 ^-3 Tr2 + 47.941) * {log ₁₀ Pc-log ₁₀ Pe} * 1000 / 9.8067 (5)

  In the above equation (5), Pc is the saturation pressure [MPa] of the condenser, Pe is the saturation pressure [MPa] of the evaporator, and Tr2 is the cold water outlet temperature [° C.].

Further, the correction term Td is specifically obtained by the following equation (6).
Td = Tde + Tdc (6)

  In equation (6), Tde is a loss-corresponding temperature difference considering the heat exchange loss of the evaporator, and Tdc is a loss-corresponding temperature difference considering the heat exchange loss of the condenser. Here, the loss equivalent temperature difference Tdc considering the heat exchange loss of the condenser is one of the main features of the present invention, and the derivation method will be described in detail later. Further, the loss-corresponding temperature difference considering the heat exchange loss of the evaporator may be calculated using a predetermined function having the load factor as a parameter, or may be a constant value.

  As described above, the storage unit 102 stores an arithmetic expression mainly functioning for calculating the target COP and an accompanying arithmetic expression for calculating various parameters used in these arithmetic expressions. .

  When the input data is acquired by the data acquisition unit 101, the calculation unit 103 reads various calculation formulas from the storage unit 102, and calculates a target COP at the current operating point using these calculation formulas. Specifically, the calculation unit 103 obtains a correction term Cf corresponding to the current operating point using the above equations (2) to (5), and corresponds to the current operating point using the equation (6). The correction term Td to be obtained is obtained. Then, by substituting the obtained correction terms Cf and Td into the equation (1), a target COP corresponding to the current operating point is obtained.

  Next, a method for deriving a loss-corresponding temperature difference in consideration of the heat exchange loss of the condenser in the above equation (6) will be described with reference to FIGS. Here, the condenser 12 according to the present embodiment is a shell-and-tube condenser, in which the refrigerant gas discharged from the turbo compressor 11 flows in, and heat is generated between the refrigerant gas and the cooling water passing through the tube. Exchange. The refrigerant gas is condensed by heat exchange, and the latent heat of condensation is cooled by cooling water passing through the tube.

  Here, a general equation for heat exchange in the condenser is shown in Equation (7).

  Q = K × A × ΔTm (7)

In the above equation (7), Q is the amount of heat exchange (kW), K is the average heat transmission rate (kW / m ² · K), A is the effective heat transfer area (m ² ), and ΔTm is the average temperature difference (K) And is given by the following equation (8).

ΔTm = (ΔT1 + ΔT2) / 2 (8)
ΔT1 = condensation temperature−cooling water inlet temperature = Tc−Tw1 (K)
ΔT2 = condensation temperature−cooling water outlet temperature = Tc−Tw2 (K)

  In the above equation (7), when the average heat passage rate K and the effective heat transfer area A are constant, if the cooling water inlet temperature Tw1 and the cooling water outlet temperature Tw2 are given, the condensing temperature Tc with respect to the exchange heat quantity Q is It can be seen that it is uniquely determined. Further, when the average heat passage rate K and the effective heat transfer area A are constant, the heat transfer driving force for heat exchange is the temperature difference between the refrigerant gas and the cooling water flowing in the tube. Therefore, as the exchange heat quantity Q is larger, the heat transfer driving force, in other words, the temperature difference is required.

  FIG. 3 is a view showing a heat transfer state in the shell and tube condenser. In FIG. 3, the condensation temperature is constant at a predetermined value Tc. The cooling water having a temperature Tw1 at the inlet of the condenser (point A in FIG. 3) is gradually heated by the heat exchange with the cold water in the condenser (region B in FIG. 3), and the outlet of the condenser It can be seen that the temperature is raised to the temperature Tw2 at (point C in FIG. 3). The smaller the temperature difference ΔT2 between the cooling water outlet temperature Tw2 and the condensation temperature Tc, the smaller the heat exchange loss of the condenser.

The inventors have empirically found that the temperature difference ΔT2 between the cooling water outlet temperature Tw2 and the condensation temperature Tc increases as the load factor increases. More specifically, the heat exchange loss of the condenser depends on the load factor. Therefore, the higher the load factor, the greater the heat exchange loss of the condenser, and the experiment was conducted to verify the relationship between the load factor and the heat exchange loss of the condenser.
In addition, in the condenser, the condensation temperature changes in addition to the load factor, and the specific volume of the refrigerant gas flowing in the condenser depends on the condensation temperature, so the condensation temperature (cooling water outlet temperature) and the heat exchange loss of the condenser The relationship was also verified.

  FIG. 4 is a diagram showing the relationship between the cooling water outlet temperature and the heat exchange loss of the condenser at each load factor. In FIG. 4, the horizontal axis represents the cooling water outlet temperature (° C.), and the vertical axis represents the heat exchange loss of the condenser, which is represented by the difference between the cooling water outlet temperature and the condensation temperature. FIG. 4 shows the respective relationships when the load factor is 100%, 80%, 60%, 40%, 30%, and 20%.

As shown in FIG. 4, it was verified that the heat exchange loss of the condenser increases as the load factor increases. Moreover, it turned out that heat exchange loss becomes large, so that the cooling water exit temperature falls in most area | regions.
This is because the specific volume of the refrigerant gas flowing into the condenser increases as the cooling water outlet temperature decreases, that is, the air volume increases and the effective heat transfer area decreases.
On the other hand, it was also found that the cooling water outlet temperature has an inflection point around 30 ° C. This will be described below with reference to FIG.

  FIG. 5 is a diagram schematically showing the state of the refrigerant liquid and the refrigerant gas in the condenser. The refrigerant gas (superheated steam) discharged from the turbo compressor 11 is cooled to the condensation temperature, starts condensing on the tube tube surface, and then the condensate is supercooled. Since the sensible heat exchange is performed while the superheated steam is cooled to the condensation temperature, the heat transfer surface in contact with the superheated steam has a small amount of heat exchanged per unit heat transfer area, and the heat exchange loss as a whole becomes large.

  FIG. 6 shows the difference in the degree of superheat due to the heat insulating head. 6A shows a case where the heat insulating head is high, and FIG. 6B shows a case where the heat insulating head is low. As shown in FIGS. 6 (a) and 6 (b), when the chilled water outlet temperature Tr2 is constant, the higher the cooling water outlet temperature Tw2, the greater the degree of superheat, so the mixture ratio of superheated steam increases, Increased impact on heat exchange loss.

  From the above, the heat exchange loss of the condenser is, for example, the air flow rate of the refrigerant gas with the change in the specific volume of the refrigerant gas depending on the load factor and the coolant outlet temperature as a parameter as shown in the following equation (9) and FIG. And the effect of superheated steam with the difference between the cold water outlet temperature and the cooling water outlet temperature as a parameter.

  Tdc = Tdcv + Tdcs (9)

In equation (9), Tdcv is a loss-corresponding temperature difference due to the effect of the air flow rate of the refrigerant gas with the change in the specific volume of the refrigerant gas depending on the load factor and the cooling water outlet temperature as a parameter, and Tdcs is the cooling water outlet temperature and the cooling water outlet temperature. This is the loss equivalent temperature difference due to the effect of superheated steam with the difference as a parameter.
As shown in FIG. 7, the loss-corresponding temperature difference Tdcs due to the effect of the refrigerant gas flow rate has a characteristic that it shows a higher numerical value as the cooling water outlet temperature is lower, and the loss-corresponding temperature difference Tdcs due to the effect of superheated steam. Has a characteristic that the higher the cooling water outlet temperature, the higher the numerical value.

  For example, the influence of the air flow rate of the refrigerant gas with the change in the specific volume of the refrigerant gas depending on the load factor and the coolant outlet temperature as a parameter is expressed by the following equation (10).

Tdcv = f (Tw2) + av (10)
av = f (Qf) (11)

In Equation (10), Tw2 is a coolant outlet temperature, and av is a variable having the current load factor Qf as a parameter, and is given by Equation (11).
In the equation (10), although expressed as a polynomial with the cooling water outlet temperature as a parameter, it may be expressed by other functions such as an exponential function.

  The influence of superheated steam with the difference between the cooling water outlet temperature and the cold water outlet temperature as a parameter is expressed by the following equation (12).

Tdcs = f (Tw2-Tr2) + as (12)
as = f (Qf) (13)

In the equation (12), Tw2 is the cooling water outlet temperature, Tr2 is the cold water outlet temperature, and as is a variable having the current load factor Qf as a parameter, and is given by the equation (13).
In the equation (12), the difference between the cooling water outlet temperature and the cooling water outlet temperature is expressed as a polynomial, but may be expressed by other functions such as an exponential function.

Next, the operation of the turbo chiller performance evaluation apparatus according to the present embodiment will be described.
First, the data acquisition unit 101 acquires operation data of the inverter turbo chiller 1 as input data, and outputs the acquired input data to the calculation unit 103. The calculation unit 103 calculates the target COP at the current operating point using the above arithmetic expression stored in the storage unit 102 and the operation data input from the data acquisition unit 101.

Specifically, the correction term Cf corresponding to the current operating point is obtained using the equations (2) to (5), and the heat is calculated using the equations (6) and (9) to (13). The heat exchange loss Td of the exchanger is calculated. More specifically, by substituting the current cooling water outlet temperature into Tw2 of equation (10), the current cooling water outlet temperature into Tw2 of equation (12), and the current cooling water outlet temperature into Tr2, a condenser is obtained. Is calculated, and the loss equivalent temperature difference Td between the condenser and the evaporator is obtained by substituting the calculated loss equivalent temperature difference Tdc of the condenser into the equation (6).
When the correction terms Cf and Td are obtained, the target COP corresponding to the current operating point is calculated by substituting these correction terms into the equation (1).

The calculated COP is transmitted to a monitoring device (not shown) via a communication medium. In addition, in the control device 14, in parallel with the above-described target COP calculation process, for example, the output heat amount, the actually measured COP at the current operating point (the value obtained by dividing the output heat amount [kW] by the power consumption [kW]), and the like. The calculation results are also transmitted to the monitoring device via the communication medium.
In the monitoring device, the target COP, the actual measurement COP, the output heat amount, and the like received from the control device 14 are displayed on the monitor, and the information is provided to the user.

  As described above, according to the turbo chiller performance evaluation apparatus and method according to the present embodiment, the load factor, the cooling, and the heat exchange loss of the heat exchanger that are conventionally given as constants Since the condenser heat exchange loss considering the water outlet temperature and the difference between the cooling water outlet temperature and the cold water outlet temperature is adopted, the calculation accuracy of the target COP can be improved. Thereby, it becomes possible to improve the accuracy of performance evaluation of the turbo refrigerator.

  In the above-described embodiment, the case where the control device 14 has the function of the performance evaluation device of the centrifugal chiller has been described. However, the performance evaluation device of the centrifugal chiller may be established as a single system. Good. In this case, the performance evaluation device for the turbo chiller receives operation data related to the turbo chiller from the control device 14 via a predetermined communication medium, and calculates a target COP and the like using the information. Further, the performance evaluation device for a centrifugal chiller according to the present invention may have a built-in function in a monitoring device that monitors operation control of the centrifugal chiller.

DESCRIPTION OF SYMBOLS 1 Turbo refrigerator 11 Turbo compressor 12 Condenser 13 Evaporator 14 Control apparatus 101 Data acquisition part 102 Memory | storage part 103 Calculation part

Claims (6)

A turbo chiller performance evaluation device comprising a compressor and a condenser as a heat exchanger,
The target COP, which is the maximum COP that can be exhibited by the refrigerator, is calculated using an arithmetic expression in which the actual device loss is given as a correction term in an expression that expresses the COP characteristic in an ideal environment without loss. Computation means for calculating,
The arithmetic expression includes the heat exchange loss of the condenser as the correction term,
The heat exchanger loss of the condenser is a performance evaluation device for a turbo chiller, which is calculated using a load factor, a cooling water outlet temperature, and a function using a difference between the cooling water outlet temperature and the cooling water outlet temperature as a parameter.   2. The calculation formula for calculating the heat exchange loss of the condenser is derived from the relationship by obtaining a relationship between a cooling water outlet temperature and a heat exchange loss of the condenser for each load factor. Turbo refrigerator performance evaluation device.   The heat exchange loss of the condenser is a loss-corresponding temperature difference due to the effect of the air flow rate of the refrigerant gas with the change in the specific volume of the refrigerant gas as a parameter expressed by the load factor and the cooling water outlet temperature, and the cold water outlet temperature and the cooling water. The turbo chiller performance evaluation apparatus according to claim 1 or 2, represented by a sum of a loss-corresponding temperature difference due to the influence of superheated steam, the difference of which is the outlet temperature as a parameter.   4. The performance evaluation device for a turbo chiller according to claim 1, wherein the COP characteristic in an ideal environment without loss is represented by an expression representing an inverse Carnot cycle. 5.   The turbo chiller performance evaluation apparatus according to any one of claims 1 to 4, wherein a mechanical loss due to the performance of the compressor is given as the correction term in the arithmetic expression. A method for evaluating the performance of a turbo refrigerator equipped with a compressor and a condenser as a heat exchanger,
The target COP, which is the maximum COP that can be exhibited by the refrigerator, is calculated using an arithmetic expression in which the actual device loss is given as a correction term in an expression that expresses the COP characteristic in an ideal environment without loss. It has a calculation process to calculate,
The arithmetic expression includes the heat exchange loss of the condenser as the correction term,
The heat exchange loss of the condenser is a turbo chiller performance evaluation method calculated using a load factor, a cooling water outlet temperature, and a function having a difference between the cooling water outlet temperature and the cooling water outlet temperature as parameters.

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