WO2024046434A1 - 冷水机组空调系统及其控制方法 - Google Patents

冷水机组空调系统及其控制方法 Download PDF

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Publication number
WO2024046434A1
WO2024046434A1 PCT/CN2023/116258 CN2023116258W WO2024046434A1 WO 2024046434 A1 WO2024046434 A1 WO 2024046434A1 CN 2023116258 W CN2023116258 W CN 2023116258W WO 2024046434 A1 WO2024046434 A1 WO 2024046434A1
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Prior art keywords
chiller
temperature
head
load
conditioning system
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PCT/CN2023/116258
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English (en)
French (fr)
Inventor
矫晓龙
石靖峰
盛凯
Original Assignee
青岛海信日立空调系统有限公司
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Priority claimed from CN202211055081.6A external-priority patent/CN115453869A/zh
Priority claimed from CN202211081826.6A external-priority patent/CN115309056A/zh
Application filed by 青岛海信日立空调系统有限公司 filed Critical 青岛海信日立空调系统有限公司
Publication of WO2024046434A1 publication Critical patent/WO2024046434A1/zh

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    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05B—CONTROL OR REGULATING SYSTEMS IN GENERAL; FUNCTIONAL ELEMENTS OF SUCH SYSTEMS; MONITORING OR TESTING ARRANGEMENTS FOR SUCH SYSTEMS OR ELEMENTS
    • G05B13/00—Adaptive control systems, i.e. systems automatically adjusting themselves to have a performance which is optimum according to some preassigned criterion
    • G05B13/02—Adaptive control systems, i.e. systems automatically adjusting themselves to have a performance which is optimum according to some preassigned criterion electric
    • G05B13/04—Adaptive control systems, i.e. systems automatically adjusting themselves to have a performance which is optimum according to some preassigned criterion electric involving the use of models or simulators

Definitions

  • the present disclosure relates to the technical field of chillers, and in particular to a chiller air conditioning system and a control method thereof.
  • Chiller air conditioning systems can achieve cooling or heating to meet industrial needs and consumer needs.
  • a chiller air conditioning system includes multiple chillers and controllers.
  • the multiple chillers share water channels, and the refrigerant flow paths of the multiple chillers are independent of each other.
  • Each chiller in the multiple chillers includes at least one compressor, condenser, throttling member and evaporator. device.
  • the at least one compressor is configured to compress the refrigerant to compress the low-pressure refrigerant to form a high-pressure refrigerant;
  • the condenser is configured to condense the gaseous refrigerant into a liquid refrigerant and perform heat exchange with the cooling water.
  • the throttling member is configured to control the flow rate and pressure of the refrigerant flowing through the throttling member; and the evaporator is configured to evaporate liquid refrigerant into gaseous refrigerant and perform heat exchange with chilled water.
  • the compressor, the condenser, the throttling member and the evaporator are connected in sequence to form a refrigerant cycle; the controller is configured to: establish a performance model of the chiller; a performance model of the chiller Related to the operating data of the chiller; calculating the target parameters of each chiller in the multiple chillers under multiple working conditions; the multiple working conditions are different from each other, and under the multiple working conditions
  • the number of activations of the plurality of chillers described below is different; according to the performance model of the chiller and at least one of the target parameters of each chiller, the predicted energy efficiency ratio of each chiller is calculated; according to the The predicted energy efficiency ratio of each chiller is determined to determine the operating status of the multiple chillers; the operational status of the chiller refers
  • the chiller air conditioning system includes multiple chillers and controllers.
  • the multiple chillers share water channels, and the refrigerant flow paths of the multiple chillers are independent of each other.
  • Each chiller in the multiple chillers includes at least one compressor, condenser, throttling member and evaporator. device.
  • the condenser is configured to condense gaseous refrigerant into liquid refrigerant and perform heat exchange with cooling water.
  • the evaporator is configured to evaporate liquid refrigerant into gaseous refrigerant and perform heat exchange with chilled water.
  • the compressor, the condenser, the throttling member and the evaporator are connected in sequence to form a refrigerant cycle.
  • the method includes: calculating the average load rate of each chiller in the multiple chillers under multiple working conditions; the multiple working conditions are different from each other, and the multiple chillers under the multiple working conditions.
  • the number of turned-on chillers is different; calculate the evaporation temperature and condensation temperature of each chiller under the multiple working conditions; calculate the evaporation temperature and condensation temperature of each chiller according to the evaporation temperature and condensation temperature of each chiller.
  • the first weight corresponding to each chiller under working conditions is related to the temperature difference between the evaporation temperature and the condensation temperature; according to the preset performance model of the chiller, As well as the evaporation temperature and condensation temperature of each chiller under the multiple working conditions, the predicted energy efficiency ratio of each chiller under the multiple working conditions is calculated; the performance model represents the performance coefficient and The relationship between the average cooling load rate and the first weight; there is a preset relationship between the predicted energy efficiency ratio and the performance coefficient, the evaporation temperature and the condensation temperature; according to the multiple working conditions
  • the predicted energy efficiency ratio of each chiller under the condition is determined to determine the operating status of the multiple chillers; the operating status of the chiller refers to the on or off of the chiller; according to the determined operating status of the multiple chillers The operating status controls the operation of the multiple chillers.
  • Figure 1 is a block diagram of a chiller air conditioning system according to some embodiments
  • Figure 2 is a structural diagram of a chiller according to some embodiments.
  • Figure 3 is a block diagram of a chiller according to some embodiments.
  • Figure 4 is a flowchart of steps performed by a controller according to some embodiments.
  • Figure 5 is another flowchart of steps performed by a controller according to some embodiments.
  • Figure 6 is yet another flowchart of steps performed by a controller according to some embodiments.
  • Figure 7 is yet another flowchart of steps performed by a controller according to some embodiments.
  • Figure 8 is a line graph of actual energy efficiency ratio and predicted energy efficiency ratio of a multi-head water unit according to some embodiments
  • Figure 9 is a line chart of the relative error of the actual energy efficiency ratio and the predicted energy efficiency ratio of a multi-head water unit according to some embodiments.
  • Figure 10 is yet another flowchart of steps performed by a controller according to some embodiments.
  • Figure 11 is a statistical graph of demand cooling load at sample points of the chiller air conditioning system according to some embodiments.
  • Figure 12 is a statistical graph of chilled water supply temperature at sample points of a chiller air conditioning system according to some embodiments.
  • Figure 13 is a statistical graph of the cooling water return temperature at sample points of the chiller air conditioning system according to some embodiments.
  • Figure 14 is a statistical graph of the number of consoles at sample points of the chiller air conditioning system according to some embodiments.
  • Figure 15 is a statistical graph of predicted energy efficiency ratios for sample points of a chiller air conditioning system according to some embodiments.
  • first and second are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of indicated technical features. Therefore, features defined as “first” and “second” may explicitly or implicitly include one or more of these features. In the description of the embodiments of the present disclosure, unless otherwise specified, "plurality" means two or more.
  • connection should be understood in a broad sense.
  • connection can be a fixed connection, a detachable connection, or an integrated connection; it can be a direct connection or an indirect connection through an intermediate medium.
  • connection can be a fixed connection, a detachable connection, or an integrated connection; it can be a direct connection or an indirect connection through an intermediate medium.
  • connection can be a fixed connection, a detachable connection, or an integrated connection; it can be a direct connection or an indirect connection through an intermediate medium.
  • a chiller air-conditioning system includes at least one chiller.
  • a performance model needs to be established to control the chiller, so that the chiller air-conditioning system has good energy efficiency.
  • the model can be modeled based on the data of the equipment (such as thermodynamic parameters such as temperature, pressure, etc.), or modeled through machine learning.
  • the data of the equipment such as thermodynamic parameters such as temperature, pressure, etc.
  • the energy saving of the multi-head chiller will be reduced. The effect is poor, so the energy efficiency of the chiller air conditioning system is poor.
  • a large number of operational tests need to be done to try to improve the energy-saving effect of the chiller system, thereby affecting the product delivery time and wasting experimental resources.
  • the reason for the poor accuracy of the multi-head chiller performance model is that the multi-head chiller is usually treated as an overall system, by collecting the parameters of the single-head chiller corresponding to each compressor, and superimposing the collected parameters.
  • the model is modeled directly according to the modeling method of a single-head chiller.
  • the performance of a multi-head chiller is not a simple linear relationship with that of a single-head chiller, for example, multiple compressors may affect each other, the simulation in the performance model established by directly superimposing parameters
  • the combined parameters may not be accurate, and the actual energy efficiency ratio cannot be obtained.
  • a white box model is used to model a multi-head chiller. For example, a performance model is established based only on the theoretical data of the chiller.
  • a black box model (Black Box Model) is used to model multi-head chillers. For example, a performance model is established based only on the collected operating data of the chiller. In this way, due to limitations in the scope of the collected data, The accuracy of this model is poor.
  • the chiller air-conditioning system is controlled based on the performance model established in the above way, and the energy efficiency of the chiller air-conditioning system is relatively poor.
  • some embodiments of the present disclosure provide a chiller air conditioning system 100.
  • the controller establishes a performance model of a single chiller and a performance model of a multi-head chiller based on the Gray Box Model.
  • An energy model is constructed, and the established model is used to control the chiller air-conditioning system, so that the chiller air-conditioning system 100 has a higher energy efficiency ratio.
  • the gray box model here includes theoretical data for the chiller as well as collected data.
  • Figure 1 is a block diagram of a chiller air conditioning system according to some embodiments.
  • a chiller air-conditioning system 100 includes a plurality of chillers 101 .
  • the chiller air conditioning system 100 includes a first chiller 101, a second chiller 101... and an Nth chiller 101.
  • N is greater than 1 (N>1), and N is a natural number.
  • the chiller 101 may include one compressor 1, and the chiller 101 may be referred to as a single-head chiller.
  • the chiller 101 may also include multiple compressors 1, and the chiller 101 may be called a multi-head chiller.
  • the multi-head chiller can be understood as consisting of multiple single-head chillers.
  • the compressor 1 is configured to compress refrigerant such that low-pressure refrigerant is compressed to form high-pressure refrigerant.
  • the cooling capacities of common single-head chillers include 125 refrigeration tons (Ton of Refrigeration, RT), 150 refrigeration tons, 180 refrigeration tons and 200 refrigeration tons.
  • a 400-ton multi-head chiller can be composed of two 200-ton single-head chillers;
  • a 500-ton multi-head chiller can be composed of a 200-ton single-head chiller and two It consists of a 150-ton single-head chiller.
  • the single-head chillers in the multi-head chiller can share a water channel, and the multiple chillers 101 in the chiller air-conditioning system 100 can use one water channel, and the multiple chillers 101 can use one water channel.
  • the refrigerant flow paths e.g., fluorine paths
  • fluorine paths are independent of each other.
  • Figure 2 is a structural diagram of a chiller according to some embodiments.
  • the chiller 101 includes a compressor 1 and a condenser 2 .
  • the compressor 1 is configured to compress refrigerant so that low-pressure refrigerant is compressed to form high-pressure refrigerant.
  • the outlet of compressor 1 is connected with the inlet of condenser 2.
  • the condenser 2 is configured to condense the gaseous refrigerant into liquid refrigerant and perform heat exchange with the cooling water.
  • the chiller 101 further includes a throttling member 3 and an evaporator 4 .
  • the evaporator 4 is configured to evaporate the liquid refrigerant into a gaseous refrigerant and perform heat exchange with the chilled water.
  • the throttling member 3 is connected to the outlet of the condenser 2 and is configured to control the flow rate and pressure of the refrigerant flowing through the throttling member 3 to expand the liquid refrigerant into a low-pressure liquid refrigerant.
  • Compressor 1, condenser 2, throttle 3 and evaporator 4 are connected in sequence through pipelines to form a refrigerant cycle.
  • compressor 1 compresses low-temperature and low-pressure refrigerant gas into high-temperature and high-pressure refrigerant gas and discharges it to condenser 2.
  • the high-temperature and high-pressure refrigerant gas exchanges heat with the outdoor air flow in condenser 2.
  • the refrigerant releases heat, and the heat released Brought to the outdoor ambient air by the air flow, the refrigerant undergoes a phase change and condenses into a liquid or gas-liquid two-phase refrigerant.
  • the refrigerant flows out of the condenser 2 and enters the throttling member 3 to reduce the temperature and pressure and become a low-temperature and low-pressure refrigerant.
  • the low-temperature and low-pressure refrigerant enters the evaporator 4.
  • the refrigerant absorbs the heat of the chilled water in the evaporator 13 and evaporates, thereby lowering the temperature of the chilled water in the evaporator 4 to achieve a cooling effect.
  • the evaporated refrigerant turns into low-temperature and low-pressure refrigerant gas and flows back into the compressor 1 to realize recycling of the refrigerant.
  • the evaporator 4 is also connected to the user side. After the temperature of the chilled water in the evaporator 4 decreases, the chilled water enters the user side. Here, the chilled water in the evaporator 4 can be replenished from the user side.
  • the chilled water in the chiller 101 enters the evaporator 4, absorbs the cooling energy of the refrigerant evaporation, and its temperature decreases to become cold water. Then, the chilled water enters the water distributor and enters the surface cooler or cooling coil. After heat exchange with the user side (such as indoor air), it returns to the chiller 101 for circulation.
  • the chiller 101 also includes a cold water circuit in which cooling water (also called cooling liquid) circulates.
  • cooling water also called cooling liquid
  • the operation of each component will generate a large amount of heat. If the heat is not taken away in time, excessive temperature may easily cause damage to the components.
  • the cooling water can remove heat and cool the components.
  • the heat exchange of the chiller 101 includes four processes: 1 Heat exchange between chilled water and the fluid (such as air) in the cooling location. 2 Heat exchange between chilled water and refrigerant in evaporator 4. 3 Heat exchange between cooling water and refrigerant in condenser 2. 4 Heat exchange between cooling water and air in the cooling tower.
  • the compressor 1 may be a magnetically levitated centrifugal compressor.
  • the throttling member 3 may be an electronic expansion valve, a pressure reducer, or the like.
  • the chiller air conditioning system 100 further includes a controller 5 .
  • the controller 5 is configured to control the operation of each component in the chiller air-conditioning system 100 so that each component of the chiller air-conditioning system 100 operates to achieve predetermined functions of the chiller air-conditioning system 100 .
  • the controller 5 is a central processing unit (CPU), a general-purpose processor, a network processor (Network processor, NP), digital signal processor (Digital signal processing, DSP), microcontroller unit (Microcontroller unit, MCU) or any combination thereof.
  • CPU central processing unit
  • NP network processor
  • DSP digital signal processor
  • MCU microcontroller unit
  • FIG. 3 is a flowchart of steps performed by a controller in accordance with some embodiments.
  • the controller 5 is configured to perform steps 11 to 16 .
  • step 11 the average load rate PLR (i,j) of each chiller 101 among the multiple chillers 101 under multiple working conditions is calculated.
  • the multiple working conditions are different from each other, and the number of activations of the multiple chillers 101 under the multiple working conditions is different.
  • the chiller air-conditioning system 100 includes N chillers 101 .
  • the first working condition means turning on one chiller 101
  • the second working condition means turning on two chillers 101
  • the third working condition means turning on three chillers 101; and so on, the Nth working condition means turning on N chillers 101 101.
  • the controller 5 can calculate the average load rate PLR (i,j) of each chiller 101 under different working conditions according to formula (1).
  • i represents the i-th working condition
  • j represents the j-th chiller 101 that is turned on
  • Q f is the demand cooling load of the chiller air-conditioning system 100
  • Q ch(j) is the rated cooling load of the j-th chiller 101
  • n is the number of activated chillers 101 in the chiller air-conditioning system 100 .
  • controller 5 can calculate the demand cooling load Q f of the chiller air conditioning system 100 according to formula (2).
  • Q f Q p ⁇ C (2)
  • Q p refers to the water flow rate on the main pipe of the refrigeration machine room
  • ⁇ C refers to the temperature difference between the supply and return water.
  • the demand cooling load Q f can be calculated in other ways, and this disclosure does not limit this.
  • the main pipeline is the main pipeline formed after the chilled water pipeline and the cooling water pipeline are combined.
  • the temperature difference between supply and return water refers to the water supply temperature difference on the main pipeline.
  • the controller 5 can calculate the average load rate PLR (i,j) of each chiller 101 under multiple working conditions.
  • the chiller air conditioning system 100 includes two 200-ton chillers 101 as an example for description.
  • the first average load rate PLR (1,1) of the first chiller 101 and the second average load rate PLR (1,1) of the second chiller 101 are calculated according to formula (1).
  • Average load rate PLR (1,2) the calculation process of the first average load rate PLR (1,1) and the second average load rate PLR (1,2) can refer to the following formula (101) and formula (102).
  • PLR (1,1) (Q f /1)/Q ch(1) (101)
  • PLR (1,2) (Q f /1)/Q ch(2) (102)
  • the third average load rate PLR (2,1) of the first chiller 101 and the third average load rate PLR (2,1) of the second chiller 101 are calculated according to formula (1).
  • Four average load rate PLR (2,2) .
  • the calculation process of the third average load rate PLR (2,1) and the fourth average load rate PLR (2,2) can refer to the following formula (103) and formula (104).
  • PLR (2,1) (Q f /2)/Q ch(1) (103)
  • PLR (2,2) (Q f /2)/Q ch(2) (104)
  • the two chillers 101 are respectively 200-ton chillers 101, and the rated cooling load Q ch(1) of the first chiller 101 and the rated cooling load Q ch(2) of the second chiller 101
  • the chiller air conditioning system 100 includes a 200-ton chiller 101 and a 150-ton chiller 101 as an example for description.
  • the first average load rate PLR (1,1) of the first chiller 101 and the second average load rate PLR (1,1) of the second chiller 101 are calculated according to formula (1).
  • Average load rate PLR (1,2) the calculation process of the first average load rate PLR (1,1) and the second average load rate PLR (1,2) can refer to the following formula (105) and formula (106).
  • PLR (1,1) (Q f /1)/Q ch(1) (105)
  • PLR (1,2) (Q f /1)/Q ch(2) (106)
  • the third average load rate PLR (2,1) of the first chiller 101 and the third average load rate PLR (2,1) of the second chiller 101 are calculated according to formula (1).
  • Four average load rate PLR (2,2) .
  • the calculation process of the third average load rate PLR (2,1) and the fourth average load rate PLR (2,2) can refer to the following formula (107) and formula (108).
  • PLR (2,1) (Q f /2)/Q ch(1) (107)
  • PLR (2,2) (Q f1 /2)/Q ch(2) (108)
  • the two chillers 101 are respectively a 150-ton chiller 101 and a 200-ton chiller 101, and the rated cooling load Q ch (1) of a 200-ton chiller 101 is the same as that of a 150-ton chiller 101,
  • the rated cooling load Q ch(2) of the chiller 101 is different (Q ch(1) ⁇ Q ch(2) ). Therefore, the first average load rate PLR (1,1) and the second average load rate PLR (1,2) are not the same (PLR (1,1) ⁇ PLR (1,2) ), the third average load rate PLR (2,1) and the fourth average load rate PLR (2,2) are not the same (PLR (2,1) ⁇ PLR (2,2) ).
  • the average load rate PLR (i, j) corresponding to each of the three chillers 101 can be calculated, That is, the first average load rate PLR (1,1) , the second average load rate PLR (1,2) , and the fifth average load rate PLR (1,3) .
  • the average load rate corresponding to each of the three chillers 101 can be calculated, that is, the third average load rate PLR (2,1) , the fourth average load rate PLR (2,2) and Sixth average load rate PLR (2,3) .
  • the average load rate corresponding to each of the three chillers 101 can be calculated, that is, the seventh average load rate PLR (3,1) , the eighth average load rate PLR (3,2) and Ninth average load rate PLR (3,3) .
  • the controller 5 can calculate the average load rate PLR (i,j) of each chiller 101 under multiple working conditions.
  • step 12 the evaporation temperature Te(i,j) and condensation temperature Tc (i,j) of each chiller 101 under multiple working conditions are calculated.
  • the first relationship and the second relationship are preset to determine the evaporation temperature Te(i,j) and condensation temperature Tc (i,j) of each chiller 101 under multiple working conditions.
  • the first relationship represents the evaporation temperature and the average cooling load rate PLR, the chilled water supply temperature te, the corresponding cooling water supply and return temperature difference ⁇ T e,tem when the chiller 101 is operating at the rated load, and the chiller 101 is operating at the rated load.
  • the relationship between the corresponding condenser heat transfer temperature difference ⁇ T e,exc (such as formula (3)).
  • the second relationship represents the condensation temperature and the average cooling load rate PLR, the cooling water return temperature tc, the corresponding chilled water supply and return temperature difference ⁇ T c,tem when the chiller 101 is operating at the rated load, and the chiller 101 when the chiller 101 is operating at the rated load.
  • the relationship between the corresponding evaporator heat exchange temperature differences during operation ⁇ T c,exc (such as formula (4)).
  • the corresponding cooling water supply and return temperature difference ⁇ T e,tem when the chiller 101 is operating under rated load the corresponding evaporator heat exchange temperature difference ⁇ T c,exc when the chiller 101 is operating under rated load, and the cold water
  • the corresponding condenser heat exchange temperature difference ⁇ T e,exc when the unit 101 is operating under the rated load and the corresponding chilled water supply and return temperature difference ⁇ T c,tem when the chiller 101 is operating under the rated load can be respectively set to 5°C, so that Calculate the evaporation temperature Te and condensation temperature Tc.
  • the above four values can also be taken as other values according to requirements, and this disclosure does not limit this.
  • the controller 5 can calculate the evaporation temperature Te (i,j) of each chiller 101 under multiple working conditions based on the evaporation temperature model (first relationship) and the condensation temperature model (second relationship). ) and condensation temperature T c(i,j) .
  • the chiller air conditioning system 100 includes two 200-ton chillers 101 as an example for description.
  • the controller 5 controls the system according to the first average load rate PLR (1,1) , the first chilled water supply temperature te (1,1) , and the first cooling water supply and return temperature difference ⁇ Te ,1) , the heat exchange temperature difference of the first condenser ⁇ T e,exc(1,1) , and the evaporation temperature Te (1,1) of the first chiller is calculated through formula (3).
  • the controller 5 controls the first average load rate PLR (1,1) , the first cooling water supply temperature tc (1,1) , the first chilled water supply and return temperature difference ⁇ T c,tem (1,1) ,
  • the first evaporator heat exchange temperature difference ⁇ T c,exc(1,1) is used to calculate the condensation temperature Tc (1,1) of the first chiller 101 through formula (4).
  • the controller 5 controls the second average load rate PLR (1,2) , the second chilled water supply temperature te (1,2) , and the second cooling water supply and return temperature difference ⁇ T e,tem (1 ,2) , the second condenser heat exchange temperature difference ⁇ T e,exc(1,2) , calculate the evaporation temperature Te (1,2) of the second chiller through formula (3). Furthermore, the controller 5 controls the system according to the second average load rate PLR (1,2) , the second cooling water supply temperature tc (1,2) , and the first chilled water supply and return water temperature.
  • the difference ⁇ T c,tem(1,2) and the first evaporator heat exchange temperature difference ⁇ T c,exc(1,1) are used to calculate the condensing temperature Tc of the second 200-ton chiller unit through formula (4) ( 1,2) .
  • the first average load rate PLR (1,1) is the average load rate under the first working condition
  • the first chilled water supply temperature te (1,1) is the chilled water supply temperature under the first working condition
  • the first cooling water supply and return water temperature difference ⁇ T e,tem(1,1) is the cooling water supply and return water temperature difference under the first working condition
  • the first condenser heat exchange temperature difference ⁇ T e,exc(1,1) is The heat exchange temperature difference of the condenser under the first working condition.
  • the second average load rate PLR (1,2) is the average load rate under the second working condition
  • the second chilled water supply temperature te (1,2) is the chilled water supply temperature under the second working condition
  • the supply and return water temperature difference ⁇ T e, tem (1, 2) is the cooling water supply and return water temperature difference under the second working condition
  • the second condenser heat exchange temperature difference ⁇ T e, exc (1, 2) is the second working condition.
  • the chiller air conditioning system 100 includes a 200-ton chiller 101 and a 150-ton chiller 101 as an example for description.
  • the controller 5 controls the system according to the first average load rate PLR (1,1) , the first chilled water supply temperature te (1,1) , and the first cooling water supply and return temperature difference ⁇ Te ,1) , the first condenser heat exchange temperature difference ⁇ T e,exc(1,1) , the evaporation temperature Te (1,1) of the first chiller 101 is calculated through formula (3).
  • the controller 5 operates according to the first average load rate PLR (1,1) , the first cooling water supply temperature tc (1,1) , the first chilled water supply and return temperature difference ⁇ T c,tem (1,1), and the first cooling water supply temperature tc (1,1).
  • the evaporator heat exchange temperature difference ⁇ T c,exc(1,1) is used to calculate the condensing temperature Tc (1,1) of the first chiller 101 through formula (4).
  • the controller 5 controls the second average load rate PLR (1,2) , the second chilled water supply temperature te (1,2) , and the second cooling water supply and return temperature difference ⁇ T e,tem (1 ,2) , the second condenser heat exchange temperature difference ⁇ T e,exc(1,2) , calculate the evaporation temperature Te (1,2) of the second chiller 101 through formula (3).
  • the controller 5 operates according to the second average load rate PLR (1,2) , the second cooling water supply temperature tc (1,2) , the first chilled water supply and return temperature difference ⁇ T c,tem (1,2) , the first The evaporator heat exchange temperature difference ⁇ T c,exc(1,1) is used to calculate the condensation temperature Tc (1,2) of the second chiller 101 through formula (4).
  • the first average load rate PLR (1,1) is different from the second average load rate PLR (1,2) (PLR (1,1) ⁇ PLR (1,2) ), then the first chilled water supply
  • the temperature te (1,1) and the second chilled water supply temperature te (1,2) are the same, and the first cooling water return temperature tc (1,1) and the second cooling water return temperature tc (1,2)
  • the condensing temperature Tc (1,1) of a 200-ton chiller 101 is different from the condensing temperature Tc (1,2) of a 150-ton chiller 101 (Tc (1, 1) ⁇ Tc (1,2) ), the evaporation temperature Te (1,1) of a 200-ton chiller 101 is not the same as the evaporation temperature Te (1,2) of a 150-ton chiller 101 Same (Te (1,1) ⁇ Te (1,2) ).
  • the controller 5 can calculate the evaporation temperature Te (i,j) and condensation temperature Tc (i,j) of each chiller 101 under multiple working conditions.
  • step 13 according to the evaporation temperature Te (i,j) and condensation temperature Tc (i,j) of each chiller 101 under different working conditions, calculate the first weight corresponding to each chiller 101 under multiple working conditions. Value dT (i,j) .
  • the weight dT (i,j) is related to the temperature difference between the evaporation temperature Te (i,j) and the condensation temperature Tc (i,j) .
  • the controller 5 calculates the first weight dT (i, j) corresponding to each chiller 101 under multiple working conditions according to formula (5).
  • Tc represents the condensation temperature
  • Te represents the evaporation temperature
  • ⁇ Tmax represents the maximum temperature difference between the condensation temperature Tc and the evaporation temperature Te of the chiller 101
  • ⁇ Tmin represents the condensation temperature Tc and the evaporation temperature Te of the chiller 101 .
  • the minimum temperature difference between evaporation temperatures Te is the minimum temperature difference between evaporation temperatures Te .
  • the maximum temperature difference ⁇ T max between the condensation temperature T c and the evaporation temperature Te of the chiller 101 is preset to 45°C, and the condensation temperature T c and evaporation temperature Te of the chiller 101 are preset.
  • the minimum temperature difference ⁇ T min between them is 15°C, so that the controller 5 can calculate the first weight dT (i,j) using formula (5).
  • the minimum temperature difference ⁇ T min between the condensation temperature T c and the evaporation temperature Te of the chiller 101 and the maximum temperature difference ⁇ T max between the condensation temperature T c and the evaporation temperature Te of the chiller 101 can also be other values respectively. value, or other coefficients related to the temperature difference between the condensation temperature Tc and the evaporation temperature Te of the chiller 101 can also be set, and this disclosure is not limited.
  • the controller 5 can calculate the first weight dT (i,j) corresponding to each chiller 101 under various working conditions according to formula (5).
  • the chiller air conditioning system 100 includes two 200-ton chillers 101 as an example for description.
  • the controller 5 calculates the first evaporation temperature Te (1,1) of the first chiller 101 and the condensation temperature Tc (1,1) of the first chiller 101 through formula (5).
  • the controller 5 calculates the second chiller 101 through the formula (5) based on the evaporation temperature Te (1,2) of the second chiller 101 and the condensation temperature Tc (1,2) of the second chiller 101.
  • the first weight dT (1,2) of the chiller 101 is the first weight of the chiller 101.
  • the chiller air conditioning system 101 includes a 200-ton chiller and a 150-ton chiller.
  • the controller 5 calculates the first working condition according to the evaporation temperature Te (1,1) of the first chiller 101 and the condensation temperature Tc (1,1) of the first chiller 101 through formula (5).
  • the controller 5 calculates the second time by formula (5) based on the evaporation temperature Te (1,2) of the second chiller 101 and the condensation temperature Tc (1,2) of the second chiller 101.
  • the first weight value dT (1,2) of the chiller 101 is the first weight value of the chiller 101.
  • the condensing temperature Tc (1,1) of the first chiller 101 is different from the condensing temperature Tc (1,2) of the second chiller 101 (Tc (1,1) ⁇ Tc ( 1,2) ), therefore, the first weight dT (1,1) of the first chiller 101 and the first weight dT (1,2) of the second chiller 101 are different (dT (1,1 ) ⁇ dT (1,2) ).
  • step 13 the controller 5 can calculate the first weight dT (i,j) corresponding to each chiller 101 under multiple working conditions.
  • step 14 based on the preset performance model of the chiller 101 and the calculated evaporation temperature Te (i,j) and condensation temperature Tc (i,j) of each chiller 101 under multiple working conditions, Calculate the predicted energy efficiency ratio COP pre(i,j) of each chiller 101 under multiple operating conditions.
  • the performance model of the single-head chiller is the performance model of the chiller 101; when the chiller 101 is a multi-head chiller, the performance model of the single-head chiller can be based on the multi-head chiller.
  • the performance model of each single-head chiller unit in the chiller unit is used to obtain the performance model of the chiller unit 101. That is to say, the performance model of the chiller includes at least one of a performance model of a single-head chiller or a performance model of a multi-head chiller.
  • the performance model of a single-head chiller can be modeled using equipment-based data or machine learning.
  • the multi-head chiller can also be treated as a whole, and the data of the entire system can be collected and modeled according to the modeling method of a single-head chiller.
  • the following description takes the chiller 101 as a multi-head chiller as an example.
  • Figure 4 is another flowchart of steps performed by a controller in accordance with some embodiments.
  • controller 5 is further configured to perform steps 141 to 143.
  • step 141 the operation data of the chiller 101 is collected.
  • the collected operating data of the chiller 101 includes: the evaporation temperature Te k , the condensation temperature Tc k and the operating load L k of each single-head chiller in the chiller 101 .
  • k represents the k-th single-head chiller, and k is a natural number, and k is greater than or equal to 1 (1 ⁇ k).
  • the above evaporation temperature Tek , condensation temperature Tck and operating load Lk refer to the parameters of each single-head chiller in the chiller 101.
  • the above evaporation temperature Tek , condensation temperature Tck and operating load Lk refer to the parameters of the chiller 101.
  • m is greater than or equal to k (k ⁇ m).
  • k k ⁇ m
  • m is a natural number.
  • the collected operating data of the chiller 101 also includes: chilled water supply temperature Te -out , chilled water return temperature Te -in , chilled water flow Qe , cooling water inlet temperature T c- in , the cooling water outlet temperature T c-out , the cooling water flow rate Q c , and the operating power P i of each single-head chiller unit in the chiller unit 101 .
  • Figure 5 is yet another flowchart of steps performed by a controller according to some embodiments.
  • controller 5 is also configured to perform steps 1411 to 1416:
  • step 1411 the current cooling capacity Q chw of the chiller 101 is calculated based on the chilled water return temperature Te -in , the chilled water supply temperature Te -out , the chilled water flow Q e and the specific heat capacity c of water.
  • the controller 5 calculates the current cooling capacity Q chw of the chiller 101 according to formula (201).
  • Q chw c ⁇ Q e ⁇ (T e-in -T e-out ) (201)
  • step 1412 the current heat rejection Q cw of the chiller 101 is calculated based on the cooling water outlet temperature T c-out , the cooling water inlet temperature T c - in , the cooling water flow rate Q c and the specific heat capacity c of water.
  • the controller 5 calculates the heat rejection Q cw of the chiller 101 according to formula (202).
  • Q cw c ⁇ Q c ⁇ (T c-in -T c-out ) (202)
  • step 1413 the energy balance coefficient ⁇ is calculated based on the current cooling capacity Q chw of the chiller 101 , the current heat rejection Q cw of the chiller 101 , and the operating power Pi of each single-head chiller in the chiller 101 .
  • the controller 5 calculates the energy balance coefficient ⁇ of the chiller 101 according to formula (203).
  • m represents the number of single-head chillers, Indicates the sum of the operating power of all single-head chillers in the chiller 101.
  • step 1414 it is determined whether the energy balance coefficient ⁇ is greater than a preset value. If “Yes”, perform step 1415; if "No”, perform step 1416.
  • step 1415 it is determined that the collected operating data is an abnormal value.
  • step 1416 it is determined that the collected operating data is a normal value.
  • the preset value can be preset or changed according to needs.
  • the preset value is 10%. If the capacity balance coefficient ⁇ is greater than 10%, the controller 5 determines that the operation data corresponding to the capacity balance coefficient ⁇ is an abnormal value; if the capacity balance coefficient ⁇ is less than or equal to 10%, the controller 5 determines that the operation data corresponding to the capacity balance coefficient ⁇ is normal. value.
  • the operating data corresponding to the capacity balance coefficient ⁇ is: the evaporation temperature Te k , the condensation temperature Tc k and the operating load L k of each single-head chiller in the chiller 101 .
  • step 142 a performance model for each single-head chiller in chiller 101 is determined.
  • the performance model of the single-head chiller is determined. It should be noted that the data collected here are the operating data of a single-head chiller in order to establish a performance model.
  • Figure 6 is yet another flowchart of steps performed by a controller according to some embodiments.
  • controller 5 is configured to perform steps 1421 and 1422:
  • step 1421 based on the collected evaporation temperature Te k , condensation temperature Tc k and energy efficiency ratio COP k of each single-head chiller, calculate Calculate the performance coefficient DCOP k of each single-head chiller.
  • controller 5 calculates the performance coefficient DCOP k of each single-head chiller through formula (204).
  • step 1422 according to the performance coefficient DCOP k of each single-head chiller, the second weight dT k and the load rate PLR k , the relationship between the performance coefficient of each single-head chiller is fitted and determined.
  • the controller 5 calculates the load rate PLR k through formulas (205) and (206).
  • each single-head chiller represents the sum of the operating loads of all single-head chillers, and Q k represents the cooling capacity of each single-head chiller.
  • the cooling capacity Q k of each single-head chiller is related to the operating load L k of the single-head chiller and the current cooling capacity Q chw of the chiller.
  • the controller 5 can calculate the second weight value dT k corresponding to each single-head chiller according to formula (5). It should be noted that the second weight dT k is related to the collected evaporation temperature, the collected condensation temperature, and the temperature difference between the condensation temperature and the evaporation temperature of the single-head chiller.
  • the controller 5 fits the relationship between the performance coefficient DCOP k , the load rate PLR k and the second weight dT k (such as formula (207)).
  • DCOP k A k ⁇ PLR k 2 +B k ⁇ PLR k ⁇ dT k +C k ⁇ dT k 2 +D k ⁇ PLR k +E k ⁇ dT k +F k (207)
  • a k , B k , C k , D k , E k and F k are fitting coefficients.
  • Formula (207) is the relational expression of the performance coefficient of a single-head chiller, which is the performance model of a single-head chiller.
  • the fitting coefficients of a 200-ton single-head chiller are A 1 , B 1 , C 1 , D 1 , E 1 and F 1 respectively, and the cooling load rate is PLR 1 and the weight is dT 1 .
  • the fitting coefficients of a 150-ton single-head chiller are A 2 , B 2 , C 2 , D 2 , E 2 and F 2 respectively, and the cooling load rate is PLR 2 and the weight is dT 2 .
  • step 14 when the controller 5 calculates the performance coefficient of the chiller 101 based on the performance model of the single-head chiller, by adding the average load rate PLR (i,j) calculated in step 11, the first value calculated in step 13 The first weight value dT (i, j) is substituted into the load rate PLR k and the second weight value dT k respectively to obtain the performance coefficient.
  • step 143 the performance model of the multi-head chiller is determined based on the determined performance model of each single-head chiller.
  • Figure 7 is yet another flowchart of steps performed by a controller according to some embodiments.
  • controller 5 is configured to perform steps 1431 to 1433:
  • step 1431 the predicted energy efficiency ratio COP pre,k of each single-head chiller is calculated based on the determined performance model of the single-head chiller, the collected evaporation temperature Te k and the collected condensation temperature Tc k .
  • the controller 5 calculates the predicted energy efficiency ratio COP pre,k of each single-head chiller through formula (209).
  • COP pre,k DCOP k ⁇ Te k /(Tc k -Te k ) (209)
  • step 1432 the electric power P w of the chiller 101 is determined based on the predicted energy efficiency ratio COP pre,k and cooling capacity Q k of each single-head chiller.
  • the controller 5 calculates the electric power P w of the chiller 101 according to formula (210).
  • step 1433 the predicted energy efficiency ratio COP pre of the multi-head chiller is determined based on the electric power P w and the current cooling capacity Q chw of the chiller 101 .
  • the controller 5 determines the predicted energy efficiency ratio COP pre of the chiller 101 (multi-head chiller) through formula (210).
  • COP pre Q cw /P w (210)
  • the performance model (Formula 209 to Formula 210) of the multi-head chiller and the predicted energy efficiency ratio COP pre of the multi-head chiller can be determined.
  • the predicted energy efficiency ratio COP pre(i,j) of the chiller 101 in step 14 can be obtained by formula (209); when the chiller 101 is a multi-head chiller
  • the predicted energy efficiency ratio COP pre(i,j) of the chiller 101 in step 14 can be obtained through formula (210).
  • performance models of large-scale multi-head chillers with different combinations can be quickly established and optimized in combination with actual operating data. In this way, the accuracy of the performance model can be improved.
  • this modeling method reflects the operation of multi-head chillers based on the characteristics of multiple single-head chillers. Therefore, using this model to control the chiller 101 can achieve good energy-saving effects.
  • a performance model is established based on the operating data of a multi-head chiller, and the performance model is verified.
  • the cooling capacity of the multi-head chiller is 500 tons
  • the 500-ton multi-head chiller consists of a 200-ton single-head chiller and two 150-ton chillers. It consists of a single head chiller.
  • Table 1 shows the chilled water inlet temperature, chilled water outlet temperature, cooling water inlet temperature, cooling water inlet temperature, cooling water flow rate, total power, total cooling load and total load rate of the multi-head chiller.
  • Table 2 shows the operating data of the 200-ton single-head chiller among the 500-ton multi-head chiller.
  • Table 3 shows the operating data of a 150-ton single-head chiller in a 500-ton multi-head chiller.
  • Table 4 shows the operating data of another 150-ton single-head chiller in the 500-ton multi-head chiller.
  • the controller 5 calculates the predicted energy efficiency ratio COP pre of a 500-ton multi-head chiller .
  • Figure 8 is a line graph of actual energy efficiency ratio and predicted energy efficiency ratio of a multi-head water unit according to some embodiments.
  • Figure 9 is a line graph of the relative error of the actual energy efficiency ratio and the predicted energy efficiency ratio of a multi-head water unit according to some embodiments.
  • the broken line of the actual energy efficiency ratio and the predicted energy efficiency ratio of the 500-ton multi-head water unit mostly overlap.
  • the relative error between the actual energy efficiency ratio and the predicted energy efficiency ratio of the 500-ton multi-head water unit is small.
  • the predicted energy efficiency ratio COP pre of the multi-head chiller is basically the same as the actual energy efficiency ratio COP.
  • controller 5 can calculate the predicted energy efficiency ratio COP pre(i,j) of each chiller 101 under different working conditions according to formula (209) and formula (210).
  • the chiller air conditioning system 100 includes two 200-ton chillers 101 as an example.
  • the controller 5 controls the first cooling load rate PLR (1,1) , the first weight dT (1,1) , the first evaporation temperature Te (1,1) , and the first condensation temperature Tc ( 1,1) and formula (209) to calculate the first predicted energy efficiency ratio COP pre(1,1) of the first chiller 101.
  • the controller 5 controls the second cooling load rate PLR (1,2) , the second weight dT (1,2) , the second evaporation temperature Te (1,2) , and the second condensation temperature Tc ( 1,2) and formula (209) to calculate the second predicted energy efficiency ratio COP pre(1,2) of the second chiller 101.
  • the controller 5 controls the third cooling load rate PLR (2,1) , the third weight dT (2,1) , the third evaporation temperature Te (2,1) , and the third condensation temperature Tc ( 2,1) and formula (209) to calculate the third predicted energy efficiency ratio COP pre(2,1) of the first chiller 101.
  • the controller 5 is based on the fourth cooling load rate PLR (2,2) , the fourth weight dT (2,2) , the fourth evaporation temperature Te (2,2) , the fourth condensation temperature Tc (2,2) and the formula (209) Calculate the fourth predicted energy efficiency ratio COP pre(2,2) of the second chiller 101.
  • the chiller air-conditioning system 100 includes a 200-ton chiller 101 and a 150-ton chiller 101 as an example.
  • the controller 5 controls the first cooling load rate PLR (1,1) , the first weight dT (1,1) , the first evaporation temperature Te (1,1) , and the first condensation temperature Tc ( 1,1) and formula (209) to calculate the first predicted energy efficiency ratio COP pre(1,1) of the first chiller 101.
  • the controller 5 controls the second cooling load rate PLR (1,2) , the second weight dT (1,2) , the second evaporation temperature Te (1,2) , and the second condensation temperature Tc ( 1,2) and formula (209) to calculate the second predicted energy efficiency ratio COP pre(1,2) of the second chiller 101.
  • the first predicted energy efficiency ratio COP pre(1,1) and the second predicted energy efficiency ratio COP pre(1,2) are not necessarily the same.
  • the controller 5 controls the third cooling load rate PLR (2,1) , the third weight dT (2,1) , the third evaporation temperature Te (2,1) , and the third condensation temperature Tc ( 2,1) and formula (209) to calculate the third predicted energy efficiency ratio COP pre(2,1) of the first chiller 101.
  • the controller 5 is based on the fourth cooling load rate PLR (2,2) , the fourth weight dT (2,2) , the fourth evaporation temperature Te (2,2) , the fourth condensation temperature Tc (2,2) and the formula (209) Calculate the fourth predicted energy efficiency ratio COP pre(2,2) of the second chiller 101.
  • the third predicted energy efficiency ratio COP pre(2,1) and the fourth predicted energy efficiency ratio COP pre(2,2) are not necessarily the same.
  • step 15 the operating status of multiple chillers 101 in the chiller air conditioning system 100 is determined based on the predicted energy efficiency ratio COP pre(i,j) of each chiller under multiple working conditions.
  • the operating status of the chiller 101 refers to whether the chiller 101 is on or off.
  • step 16 the operation of the multiple chillers 101 is controlled according to the determined operating status of the multiple chillers 101.
  • the controller 5 compares the predicted energy efficiency ratio COP pre,(i,j) to determine whether to turn on or off the corresponding chiller 101 in the chiller air-conditioning system 100, so that the chiller air-conditioning system 100 operates in a relatively high energy efficiency working condition. Down.
  • the chiller air-conditioning system 100 includes two 200-ton chillers 101 .
  • the chiller air-conditioning system 100 includes a 200-ton chiller and a 150-ton chiller 101.
  • the first predicted energy efficiency ratio COP pre(1,1) corresponding to a 200-ton chiller 101 and the second predicted energy efficiency ratio COP pre( ) corresponding to a 150-ton chiller 101 1,2) are not necessarily the same.
  • the third predicted energy efficiency ratio COP pre(2,1) corresponding to a 200-ton chiller 101 is the fourth predicted energy efficiency ratio COP pre(2,1) corresponding to a 150-ton chiller 101 . 2,2) are not necessarily the same.
  • the chiller air conditioning system 100 can operate at a higher energy efficiency ratio.
  • the chiller air-conditioning system 100 includes two chillers 101
  • the controller 5 calculates that the energy efficiency of turning on the two chillers 101 is greater than the energy efficiency of turning on one chiller, then the chiller air-conditioning system 100 works under the condition of turning on two chillers 101. In this case, if one chiller 101 is currently running, it is determined that the second chiller 101 needs to be turned on.
  • the chiller air conditioning system 100 works under the condition of turning on one chiller 101. In this case, if two chillers are currently running, it is determined that one chiller 101 needs to be shut down.
  • Figure 10 is yet another flowchart of steps performed by a controller according to some embodiments.
  • step 16 includes steps 161 to 166 .
  • step 161 the load change rate ROC of the cooling load of the chiller air conditioning system 100 at the previous moment relative to the demand cooling load is calculated.
  • step 162 it is determined whether the load change rate ROC reaches the upper limit value ROC1 of the load change rate of the chiller 101 to be started. If “Yes”, execute step 163 and return to step 11; if "No”, execute step 166.
  • step 163 one chiller 101 in the chiller air conditioning system 100 is started.
  • step 164 it is determined whether the load change rate ROC reaches the upper limit value ROC2 of the load change rate of the chiller 101 to be shut down. If “Yes”, execute step 165 and return to step 11; if "No”, execute step 166.
  • step 165 one chiller 101 in the chiller air conditioning system 100 is shut down.
  • step 166 the chiller air conditioning system 100 is controlled to continue operating in the current operating state.
  • the controller 5 can determine whether the cooling load has changed sharply by calculating the load change rate of the cooling load of the chiller air conditioning system 100 at the previous moment relative to the demand cooling load.
  • the sudden change includes two types of changes: one is a small sudden change, which requires shutting down the chiller 101; the other is a sharp increase, which requires turning on the chiller 101.
  • the load change rate ROC reaches the upper limit ROC1 of the load change rate of the chiller 101 to be shut down, it indirectly indicates that the load has decreased sharply within the first preset time period. If the chiller 101 is not shut down, the load change rate ROC will The water temperature cannot be adjusted to the set value immediately within the set time. That is to say, the cooling capacity of the chiller air conditioning system 100 cannot be reduced to the required cooling load in time within the first preset time period, and the corresponding chiller 101 needs to be shut down.
  • the load change rate ROC reaches the upper limit ROC2 of the load change rate of the chiller 101 to be started, it indirectly indicates that the load has increased sharply within the first preset time period.
  • the water temperature cannot be adjusted to the set value immediately within the set time. That is to say, the cooling capacity of the chiller air-conditioning system 100 cannot be increased in time to the required cooling load within the first preset time period, and the chiller 101 needs to be turned on.
  • the load change rate does not reach the upper limit of the load change rate of the chiller 101 to be turned on or off, it indirectly indicates that there is a slight fluctuation in the load within the first preset time period (the fluctuation may also be caused by sensor measurement error). At this time, even if the corresponding chiller 101 is not turned on or off, the water temperature can be adjusted to the set value within the first preset time period.
  • the first preset time period may be a set time for periodically obtaining the cooling load of the chiller air conditioning system 100 .
  • the first preset time period T1 is 5 minutes.
  • the load change rate ROC is related to the demand cooling load of the chiller air conditioning system 100 , the cooling load of the chiller air conditioning system 100 and the first preset time period T1 .
  • the load change rate ROC, the demand cooling load of the chiller air-conditioning system 100, the cooling load of the chiller air-conditioning system 100 and the first preset time period T1 satisfy formula (301).
  • ROC (Q d -Q f )/T1 (301)
  • Q f is the demand cooling load of the chiller air conditioning system 100
  • Q d is the cooling load of the chiller air conditioning system 100
  • T1 is the first preset time length.
  • the appropriate start-stop time interval of the chiller 101 in the chiller air-conditioning system 100 is the second preset time period T2.
  • the second preset time period T2 is 30 minutes.
  • the controller 5 can obtain the rated cooling load Q ch of the chiller 101.
  • the controller 5 returns to step 11 until the load change rate ROC is less than the upper limit value ROC1 of the load change rate of the chiller 101 to be started (ROC ⁇ the upper limit value of ROC1).
  • the controller 5 can obtain the rated cooling load Q ch of the chiller 101.
  • the chiller air conditioning system 100 includes a 200-ton chiller 101 and a 150-ton chiller 101 In this case, if the controller 5 calculates that the energy efficiency of turning on two chillers 101 is greater than the energy efficiency of turning on one 200-ton chiller 101, then the chiller air conditioning system 100 needs to work when turning on the two chillers 101 under working conditions.
  • the controller 5 calculates the load change rate ROC1 of the chiller 101 to be started based on the rated cooling load Q ch of the 150-ton chiller 101 to be started through formula (302). If the load change rate ROC is greater than or equal to the upper limit value ROC1 of the load change rate of the chiller 101 to be started, the controller 5 determines to start the 150-ton chiller 101, otherwise, the current operation of a 200-ton chiller 101 is continued. Chiller 101.
  • the chiller air conditioning system 100 includes a 200-ton chiller and a 150-ton chiller 101
  • the controller 5 calculates that the energy efficiency ratio of turning on a 200-ton chiller 101 is to turn on two If the energy efficiency of the chiller 101 is high, the air conditioning system 101 of the chiller needs to work under the condition of turning on a 150-ton chiller 101.
  • the controller 5 calculates the load change rate ROC2 of the 150-ton chiller 101 to be shut down through formula (303) based on the rated cooling load Q ch of the 150-ton chiller 101 to be shut down.
  • the controller 5 determines to shut down the 150-ton chiller 101, otherwise, keep the two currently running. Chiller 101.
  • the chiller 101 with the longest running time in the chiller air-conditioning system 100 may be shut down first.
  • the chiller air-conditioning system 100 can be maintained to operate with high energy efficiency, and the chiller air-conditioning system 100 can also be adjusted in a timely manner based on the load change rate ROC. Load regulation to achieve energy savings.
  • the following uses a chiller air-conditioning system 100 composed of a 300-ton chiller and a 250-ton chiller as an example to verify the steps performed by the controller 5 provided in some embodiments of the present disclosure.
  • Figure 11 is a statistical graph of demand cooling load at sample points of a chiller air conditioning system according to some embodiments.
  • Figure 12 is a statistical graph of chilled water supply temperature at sample points of a chiller air conditioning system in accordance with some embodiments.
  • the abscissa represents the 559 sample points collected.
  • Figure 11 shows the demand cooling load Q f of the 559 sample points.
  • Figure 12 shows the chilled water supply temperature Te at 559 sample points.
  • Figure 13 is a statistical graph of cooling water return temperatures at sample points of the chiller air conditioning system according to some embodiments.
  • Figure 14 is a statistical graph of the number of consoles at a sample point of a chiller air conditioning system according to some embodiments.
  • Figure 15 is a statistical graph of predicted energy efficiency ratios for sample points of a chiller air conditioning system according to some embodiments.
  • the abscissa represents the 559 sample points collected.
  • Figure 13 shows the cooling water return temperature Tc of the 559 sample points.
  • Figure 14 shows the number of consoles for 559 sample points.
  • Figure 15 shows the predicted energy efficiency ratio COP pre for 559 sample points. 14 and 15 , the chiller air-conditioning system 100 is controlled through the steps executed by the controller 5. The control is efficient and accurate, and the stability of the chiller air-conditioning system 100 is high.
  • step numbers in some embodiments of the present disclosure are only for convenience in describing some embodiments of the present disclosure and cannot be understood as limiting the order of the steps.
  • the execution order of the steps can be specifically determined according to actual needs and is not limited to the order of steps in some embodiments of the present disclosure.
  • Some embodiments of the present disclosure also provide a control method for a chiller air-conditioning system, which has a similar structure to the chiller air-conditioning system 100 .
  • the chiller air conditioning system includes multiple chillers 101 and a controller 5 , and the method can be executed by the controller 5 .
  • the method includes: calculating the average load rate of each chiller in the multiple chillers under multiple working conditions; the multiple working conditions are different from each other, and the multiple chillers under the multiple working conditions The number of activated chillers is different; calculate the evaporation temperature and condensation temperature of each chiller under the multiple working conditions; calculate the evaporation temperature and condensing temperature of each chiller under the multiple working conditions.
  • the first weight corresponding to each chiller is related to the temperature difference between the evaporation temperature and the condensation temperature; according to the preset performance model of the chiller, and Based on the evaporation temperature and condensation temperature of each chiller under the multiple working conditions, calculate the predicted energy efficiency ratio of each chiller under the multiple working conditions; the performance model represents the relationship between the performance coefficient and the The relationship between the average cooling load rate and the first weight; there is a preset relationship between the predicted energy efficiency ratio and the performance coefficient, the evaporation temperature and the condensation temperature; according to the multiple working conditions
  • the predicted energy efficiency ratio of each chiller described below is used to determine the operating status of the multiple chillers; so The operating status of the chiller refers to the on or off of the chiller; the operation of the multiple chillers is controlled according to the determined operational status of the multiple chillers.
  • the method further includes: after determining the operating status of the multiple chillers, calculating the load change rate of the cooling load of the air conditioning system of the chiller at the previous moment relative to the demand cooling load; if When the load change rate reaches the upper limit of the load change rate of the chiller to be turned on or off, the air conditioning system of the chiller is controlled to operate in a determined operating state; if the load change rate is less than the chilled water chiller to be turned on or off. The upper limit of the load change rate of the unit controls the air conditioning system of the chiller to continue operating under the current operating state.
  • the method further includes: if the load change rate reaches an upper limit of the load change rate of the chiller to be started, controlling the chiller to be started to start; if the load change rate When the upper limit of the load change rate of the chiller to be shut down is reached, the chiller to be shut down is controlled to be shut down; the chiller to be shut down is the chiller with the longest running time among the running chillers.
  • the method further includes: calculating based on the demand cooling load of the chiller air conditioning system, the number of activated chillers in the chiller air conditioning system, and the rated cooling loads of the multiple chillers. The average cooling load rate of each chiller under the multiple working conditions.
  • the method further includes: obtaining the chilled water supply temperature, the cooling water return temperature, the corresponding cooling water supply and return temperature difference when the chiller is operating under rated load, and the corresponding cooling water temperature difference when the chiller is operating under rated load.
  • the evaporator heat exchange temperature difference, the corresponding condenser heat exchange temperature difference when the chiller is operating at rated load, and the corresponding chilled water supply and return water temperature difference when the chiller is operating at rated load according to the preset first relationship, calculate The evaporation temperature of each chiller under the multiple working conditions; the first relationship represents the evaporation temperature, the average cooling load rate, the chilled water supply temperature, and the time when the chiller is operating at rated load.
  • the condensation temperature of the chiller; the second relationship represents the condensation temperature and the average cooling load rate, the cooling water return temperature, the corresponding chilled water supply and return temperature difference when the chiller is operating under rated load, And the relationship between the corresponding evaporator heat transfer temperature difference when the chiller is operating at rated load.
  • the method further includes: based on the maximum temperature difference between the condensation temperature and the evaporation temperature of the chiller, the minimum temperature difference between the condensation temperature and the evaporation temperature of the chiller, the calculated evaporation temperature and Condensing temperature, calculate the first weight corresponding to each chiller unit.
  • the method further includes: collecting operating data of the chiller; the operating data includes the evaporation temperature, condensing temperature, and operating load of each single-head chiller in the chiller; according to the collected The evaporation temperature, condensation temperature, operating load, and the rated cooling capacity and energy efficiency ratio of each single-head chiller are used to determine the performance model of each single-head chiller; based on the determined performance of each single-head chiller model to determine the performance model of the multi-head chiller; the performance model of the chiller includes at least one of the performance model of the single-head chiller or the performance model of the multi-head chiller.
  • the method further includes: calculating the performance coefficient of the single-head chiller based on the collected evaporation temperature, condensation temperature and energy efficiency ratio; based on the performance coefficient of the single-head chiller, the second weight value and load rate, fit and determine the relationship expression of the performance coefficient of the single-head chiller.
  • the relational expression of the performance coefficient of the single-head chiller is the performance model of the single-head chiller, and the second weight value is related to the collected evaporation temperature, the collected condensation temperature, and the condensation temperature of the single-head chiller. The temperature difference between the temperature and the evaporation temperature is related.
  • the method further includes: calculating the load rate based on the operating load and rated cooling capacity of the single-head chiller and the current cooling capacity of the chiller.
  • the method further includes: calculating the predicted energy efficiency ratio of each single-head chiller based on the determined performance model of each single-head chiller and the collected evaporation temperature and condensation temperature; Describe the predicted energy efficiency ratio and cooling capacity of each single-head chiller, and determine the electrical power of the chiller; the cooling capacity of each single-head chiller is related to the operating load of the single-head chiller and the operating load of the chiller. The current cooling capacity is related; according to the electric power and the current cooling capacity of the chiller, the predicted energy efficiency ratio of the multi-head chiller is determined.
  • the method further includes: deleting outliers in the collected operating data.
  • deleting abnormal values in the collected operating data includes: calculating the chilled water unit based on the chilled water return temperature, the chilled water supply temperature, the chilled water flow rate, and the specific heat capacity of the water. the current cooling capacity of the chiller; calculate the current heat rejection of the chiller according to the cooling water outlet temperature, the cooling water inlet temperature, the cooling water flow rate and the specific heat capacity of the water; calculate the current cooling capacity of the chiller , the current heat rejection of the chiller and the operating power of each single-head chiller, calculated Calculate the energy balance coefficient; if the energy balance coefficient is greater than the preset value, determine the collected operating data to be abnormal values; delete the operating data determined to be abnormal values.

Abstract

提供一种冷水机组空调系统及其控制方法。所述冷水机组空调系统包括多台冷水机组和控制器。所述控制器被配置为：建立所述冷水机组的性能模型；计算在多个工况下所述多台冷水机组中每台冷水机组的目标参数；所述多个工况互不相同，且在所述多个工况下所述多台冷水机组的开启数量不同；根据所述冷水机组的性能模型、以及所述每台冷水机组的目标参数中的至少一个，计算所述每台冷水机组的预测能效比；根据所述每台冷水机组的所述预测能效比，确定所述多台冷水机组的运行状态。

Description

冷水机组空调系统及其控制方法
本申请要求于2022年08月31日提交的、申请号为202211055081.6的中国专利申请的优先权、于2022年09月05日提交的、申请号为202211081826.6的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本公开涉及冷水机组技术领域，尤其涉及一种冷水机组空调系统及其控制方法。
背景技术
随着工业水平的不断提高，冷水机组空调系统逐渐应用在了各行各业。冷水机组空调系统可以实现制冷或者制热，以满足工业需求以及消费者需求。
发明内容
一方面，提供一种冷水机组空调系统。所述冷水机组空调系统包括多台冷水机组和控制器。所述多台冷水机组共用水路，且所述多台冷水机组的制冷剂流路互相独立，所述多台冷水机组中的每台冷水机组包括至少一个压缩机、冷凝器、节流件以及蒸发器。所述至少一个压缩机被配置为压缩冷媒以使低压冷媒受压缩形成高压冷媒；所述冷凝器被配置为将气态冷媒冷凝为液态冷媒，并与冷却水进行热交换。所述节流件且被配置为控制流经所述节流件的所述冷媒的流量和压力；以及所述蒸发器被配置为将液态冷媒蒸发为气态冷媒，并与冷冻水进行热交换。所述压缩机、所述冷凝器、所述节流件和所述蒸发器依次连接形成冷媒循环；所述控制器被配置为：建立所述冷水机组的性能模型；所述冷水机组的性能模型与所述冷水机组的运行数据相关；计算在多个工况下所述多台冷水机组中每台冷水机组的目标参数；所述多个工况互不相同，且在所述多个工况下所述多台冷水机组的开启数量不同；根据所述冷水机组的性能模型、以及所述每台冷水机组的目标参数中的至少一个，计算所述每台冷水机组的预测能效比；根据所述每台冷水机组的所述预测能效比，确定所述多台冷水机组的运行状态；所述冷水机组的运行状态指所述冷水机组开启或关闭；根据确定的所述多台冷水机组的运行状态，控制所述多台冷水机组的运行。
另一方面，提供一种冷水机组空调系统的控制方法。所述冷水机组空调系统包括多台冷水机组和控制器。所述多台冷水机组共用水路，且所述多台冷水机组的制冷剂流路互相独立，所述多台冷水机组中的每台冷水机组包括至少一个压缩机、冷凝器、节流件和蒸发器。所述冷凝器被配置为将气态冷媒冷凝为液态冷媒，并与冷却水进行热交换。所述蒸发器被配置为将液态冷媒蒸发为气态冷媒，并与冷冻水进行热交换。所述压缩机、所述冷凝器、所述节流件和所述蒸发器依次连接形成冷媒循环。被配置为控制所述多台冷水机组的运行。所述方法包括：计算在多个工况下所述多台冷水机组中每台冷水机组的平均负荷率；所述多个工况互不相同，且在所述多个工况下所述多台冷水机组的开启数量不同；计算在所述多个工况下所述每台冷水机组的蒸发温度和冷凝温度；根据所述每台冷水机组的蒸发温度和冷凝温度，计算在所述多个工况下所述每台冷水机组对应的第一权值；所述第一权值与所述蒸发温度和所述冷凝温度之间的温差相关；根据预设的所述冷水机组的性能模型、以及在所述多个工况下所述每台冷水机组的蒸发温度和冷凝温度，计算在所述多个工况下所述每台冷水机组的预测能效比；所述性能模型表征性能系数与所述平均冷负荷率和所述第一权值的关系；所述预测能效比与所述性能系数、所述蒸发温度和所述冷凝温度之间存在预设关系；根据在所述多个工况下所述每台冷水机组的预测能效比，确定所述多台冷水机组的运行状态；所述冷水机组的运行状态指所述冷水机组开启或关闭；根据确定的所述多台冷水机组的运行状态，控制所述多台冷水机组的运行。
附图说明
图1为根据一些实施例的冷水机组空调系统的框图；
图2为根据一些实施例的冷水机组的结构图；
图3为根据一些实施例的冷水机组的框图；
图4为根据一些实施例的控制器执行步骤的流程图；
图5为根据一些实施例的控制器执行步骤的另一种流程图；
图6为根据一些实施例的控制器执行步骤的又一种流程图；
图7为根据一些实施例的控制器执行步骤的又一种流程图；
图8为根据一些实施例的一种多机头水机组的实际能效比和预测能效比的折线图；
图9为根据一些实施例的一种多机头水机组的实际能效比和预测能效比的相对误差的折线图；
图10为根据一些实施例的控制器执行步骤的又一种流程图；
图11为根据一些实施例的冷水机组空调系统的样本点的需求冷负荷的统计图；
图12为根据一些实施例的冷水机组空调系统的样本点的冷冻水供水温度的统计图；
图13为根据一些实施例的冷水机组空调系统的样本点的冷却水回水温度的统计图；
图14为根据一些实施例的冷水机组空调系统的样本点的控制台数的统计图；
图15为根据一些实施例的冷水机组空调系统的样本点的预测能效比的统计图。
具体实施方式
下面将结合附图，对本公开一些实施例进行清楚、完整地描述，显然，所描述的实施例仅仅是本公开一部分实施例，而不是全部的实施例。基于本公开所提供的实施例，本领域普通技术人员所获得的所有其他实施例，都属于本公开保护的范围。
除非上下文另有要求，否则，在整个说明书和权利要求书中，术语“包括(comprise)”及其其他形式例如第三人称单数形式“包括(comprises)”和现在分词形式“包括(comprising)”被解释为开放、包含的意思，即为“包含，但不限于”。在说明书的描述中，术语“一个实施例(one embodiment)”、“一些实施例(some embodiments)”、“示例性实施例(exemplary embodiments)”、“示例(example)”、“特定示例(specific example)”或“一些示例(some examples)”等旨在表明与该实施例或示例相关的特定特征、结构、材料或特性包括在本公开的至少一个实施例或示例中。上述术语的示意性表示不一定是指同一实施例或示例。此外，所述的特定特征、结构、材料或特点可以以任何适当方式包括在任何一个或多个实施例或示例中。
以下，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本公开实施例的描述中，除非另有说明，“多个”的含义是两个或两个以上。
在描述一些实施例时，可能使用了“连接”及其衍伸的表达。术语“连接”应做广义理解，例如，“连接”可以是固定连接，也可以是可拆卸连接，或成一体；可以是直接相连，也可以通过中间媒介间接相连。这里所公开的实施例并不必然限制于本文内容。
本文中“适用于”或“被配置为”的使用意味着开放和包容性的语言，其不排除适用于或被配置为执行额外任务或步骤的设备。
通常，冷水机组空调系统包括至少一台冷水机组，为了对冷水机组空调系统的能效进行控制，需要建立性能模型，以对冷水机组进行控制，从而使冷水机组空调系统具有良好的能效。
对于包括一台压缩机的冷水机组的性能模型，可以根据设备的数据(如，温度、压力等热力学参数)进行建模，或者，通过机器学习进行建模。然而，对于具有多台压缩机的多机头冷水机组，由于建立的性能模型的精度较差，这样，当利用建立的性能模型对多机头冷水机组进行控制时，多机头冷水机组的节能效果较差，从而冷水机组空调系统的能效较差。另外，在冷水机组系统交付之前，需要做大量的运行测试试验，以尝试改善冷水机组系统的节能效果，从而影响产品的交付时间，浪费实验资源。
多机头冷水机组性能模型的精度较差的原因在于：通常将多机头冷水机组作为一个整体系统，通过采集每台压缩机对应的单机头冷水机组的参数，并将采集的参数进行叠加，直接按照单机头冷水机组的建模方法进行建模。然而，由于多机头冷水机组的性能与单机头冷水机组的性能之间并非简单的线性关系，例如，多台压缩机之间可能会相互影响，利用直接叠加的参数建立的性能模型中的拟合参数可能并不准确，无法得到与实际相符的能效比。在一些方案中，采用白箱模型(White Box Model)对多机头冷水机组进行建模，例如，仅根据冷水机组的理论数据建立性能模型，这样，难以得到与实际相符的能效比；在另一些方案中，采用黑箱模型(Black Box Model)对多机头冷水机组进行建模，例如，仅根据采集的冷水机组的运行数据建立性能模型，这样，由于采集的数据的范围存在限制，这样，该模型的精度较差。
在此情况下，根据以上方式建立的性能模型对冷水机组空调系统进行控制，冷水机组空调系统的能效比较差。
为了解决上述问题，本公开一些实施例提供了一种冷水机组空调系统100。在该冷水机组空调系统100中，控制器根据灰盒模型(Gray Box Model)建立单机冷水机组的性能模型以及多机头冷水机组的性 能模型，并利用所建立的模型对冷水机组空调系统进行控制，以使得冷水机组空调系统100具有较高的能效比。可以理解的是，此处的灰盒模型包括冷水机组的理论数据以及采集的数据。
图1为根据一些实施例的冷水机组空调系统的框图。
如图1所示，冷水机组空调系统100包括多台冷水机组101。例如，冷水机组空调系统100包括第一台冷水机组101、第二台冷水机组101…以及第N台冷水机组101。这里，N大于1(N＞1)，且N为自然数。冷水机组101可以包括一个压缩机1，该冷水机组101可以被称为单机头冷水机组。冷水机组101也可以包括多个压缩机1，该冷水机组101可以被称为多机头冷水机组。这里，多机头冷水机组可以理解为由多个单机头冷水机组构成。压缩机1配置为压缩冷媒以使低压冷媒受压缩形成高压冷媒。
例如，常见的单机头冷水机组的制冷量包括125冷吨(Ton of Refrigeration，RT)、150冷吨、180冷吨和200冷吨。一台400冷吨的多机头冷水机组可以由两台200冷吨的单机头冷水机组构成；一台500冷吨的多机头冷水机组可以由一台200冷吨的单机头冷水机组和两台150冷吨的单机头冷水机组组成。
需要说明的是，多机头冷水机组中的各单机头冷水机组之间可以共用水流路，且冷水机组空调系统100中的多台冷水机组101可以用一个水流路，而多台冷水机组101的制冷剂流路(如，氟路)相互独立。
图2为根据一些实施例的冷水机组的结构图。
如图2所示，冷水机组101包括压缩机1和冷凝器2。压缩机1被配置为压缩冷媒以使低压冷媒受压缩形成高压冷媒。压缩机1的出口与冷凝器2的进口相连。冷凝器2被配置为将气态冷媒冷凝为液态冷媒，并与冷却水进行热交换。
在一些实施例中，如图2所示，冷水机组101还包括节流件3和蒸发器4。蒸发器4被配置为将液态冷媒蒸发为气态冷媒，并与冷冻水进行热交换。节流件3与冷凝器2的出口相连，且被配置为控制流经所节流件3的所述冷媒的流量和压力，以将液态冷媒膨胀为低压的液态冷媒。压缩机1、冷凝器2、节流件3和蒸发器4通过管路依次连通形成冷媒循环。
在制冷时，压缩机1将低温低压的冷媒气体压缩成高温高压的冷媒气体并排至冷凝器2，高温高压的冷媒气体在冷凝器2中与室外空气流换热，冷媒释放热量，释放的热量被空气流带到室外环境空气中，冷媒则发生相变而冷凝成液态或气液两相冷媒。冷媒流出冷凝器2，进入节流件3降温降压变成低温低压的冷媒。低温低压的冷媒进入蒸发器4，冷媒吸收蒸发器13内的冷冻水的热量而蒸发，使蒸发器4内的冷冻水的温度降低，实现制冷效果。蒸发后的冷媒变成低温低压的冷媒气体，回流入压缩机1，实现冷媒的循环利用。蒸发器4还与用户端侧相连，蒸发器4内的冷冻水的温度降低后，该冷冻水进入用户侧。这里，蒸发器4内的冷冻水可由用户侧补充。
冷水机组101中的冷冻水进入蒸发器4内，吸收了制冷剂蒸发的冷量，其温度降低成为冷水。然后，冷冻水进入分水器后进入表冷器或冷却盘管内，与用户侧的(如室内空气)进行热交换后，再回到冷水机组101进行循环。
在一些实施例中，冷水机组101还包括冷水水路，冷却水(又称冷却液)在该冷却水路中循环流动。在冷水机组101的运行过程中，各部件运转会产生大量热量，若不及时将热量带走，温度过高易导致部件损坏。通过设置冷水水路并使冷却水流经冷水机组101中的部件，可以将部件产生的热量传导进冷却水。这样，冷却水可以带走热量，使部件降温。
在一些实施例中，冷水机组101的热交换包括4个过程：①冷冻水与用冷场合的流体(如空气)的热交换。②冷冻水与蒸发器4内制冷剂的热交换。③冷却水与冷凝器2内制冷剂的热交换。④冷却水在冷却塔与空气的热交换。
在一些实施例中，压缩机1可以是磁悬浮离心压缩机。
在一些实施例中，节流件3可以是电子膨胀阀、减压器等。
在一些实施例中，如图1所示，冷水机组空调系统100还包括控制器5。控制器5被配置为控制冷水机组空调系统100中各部件工作，以使得冷水机组空调系统100的各部件运行实现冷水机组空调系统100的预定功能。
例如，控制器5为中央处理器(Central processing unit，CPU)、通用处理器网络处理器(Network  processor，NP)、数字信号处理器(Digital signal processing，DSP)、微控制单元(Microcontroller unit，MCU)或它们的任意组合。
图3为根据一些实施例的控制器执行步骤的流程图。
在一些实施例中，如图3所示，控制器5被配置为执行步骤11至步骤16。
在步骤11中，计算在多个工况下多台冷水机组101中每台冷水机组101的平均负荷率PLR(i,j)。
所述多个工况互不相同，且在多个工况下多台冷水机组101的开启数量不同。
按照冷水机组空调系统100中开启的冷水机组101的数量，分为多种不同的工况。例如，如图1所示，冷水机组空调系统100包括N台冷水机组101。第一工况表示开启一台冷水机组101，第二工况表示开启两台冷水机组101，第三工况表示开启三台冷水机组101；以此类推，第N工况表示开启N台冷水机组101。
控制器5可以根据公式(1)计算不同工况下的每台冷水机组101的平均负荷率PLR(i,j)。
这里，i表示第i工况，j表示开启的第j台冷水机组101，Qf为冷水机组空调系统100的需求冷负荷，Qch(j)为第j台冷水机组101的额定冷负荷，n为冷水机组空调系统100中开启的冷水机组101的数量。
需要说明的是，控制器5可以根据公式(2)计算冷水机组空调系统100的需求冷负荷Qf。
Qf＝Qp×△C        (2)
这里，Qp是指制冷机房的主管路上的水流量，△C是指供回水的温差。当然，可以通过其他方式计算需求冷负荷Qf，本公开对此不作限制。这里，主管路为冷冻水管路和冷却水管路回合之后形成的主要管路。该供回水的温差指的是该主要管路上的供水温差。
这样，控制器5可以计算多个工况下的每台冷水机组101的平均负荷率PLR(i,j)。
在一些实施例中，以冷水机组空调系统100包括两台200冷吨的冷水机组101为例进行说明。
在第一工况下(即一台冷水机组101开启)，根据公式(1)计算第一台冷水机组101的第一平均负荷率PLR(1,1)和第二台冷水机组101的第二平均负荷率PLR(1,2)。这里，第一平均负荷率PLR(1,1)和第二平均负荷率PLR(1,2)的计算过程可参照如下公式(101)和公式(102)。
PLR(1,1)＝(Qf/1)/Qch(1)       (101)
PLR(1,2)＝(Qf/1)/Qch(2)        (102)
在第二工况下(即，两台冷水机组101开启)，根据公式(1)计算第一台冷水机组101的第三平均负荷率PLR(2,1)和第二台冷水机组101的第四平均负荷率PLR(2,2)。这里，第三平均负荷率PLR(2,1)和第四平均负荷率PLR(2,2)的计算过程可参照如下公式(103)和公式(104)。
PLR(2,1)＝(Qf/2)/Qch(1)      (103)
PLR(2,2)＝(Qf/2)/Qch(2)      (104)
这里，由于两台冷水机组101分别为200冷吨的冷水机组101，且第一台冷水机组101的额定冷负荷Qch(1)与第二台冷水机组101的额定冷负荷Qch(2)相同(Qch(1)＝Qch(2))，因此，第一平均负荷率PLR(1,1)与第二平均负荷率PLR(1,2)相同(PLR(1,1)＝PLR(1,2))，第三平均负荷率PLR(2,1)与第四平均负荷率PLR(2,2)相同(PLR(2,1)＝PLR(2,2))。
在另一些实施例中，以冷水机组空调系统100包括一台200冷吨的冷水机组101和一台150冷吨的冷水机组101的为例进行说明。
在第一工况下(即一台冷水机组101开启)，根据公式(1)计算第一台冷水机组101的第一平均负荷率PLR(1,1)和第二台冷水机组101的第二平均负荷率PLR(1,2)。这里，第一平均负荷率PLR(1,1)和第二平均负荷率PLR(1,2)的计算过程可参照如下公式(105)和公式(106)。
PLR(1,1)＝(Qf/1)/Qch(1)       (105)
PLR(1,2)＝(Qf/1)/Qch(2)        (106)
在第二工况下(即，两台冷水机组101开启)，根据公式(1)计算第一台冷水机组101的第三平均负荷率PLR(2,1)和第二台冷水机组101的第四平均负荷率PLR(2,2)。这里，第三平均负荷率PLR(2,1)和第四平均负荷率PLR(2,2)的计算过程可参照如下公式(107)和公式(108)。
PLR(2,1)＝(Qf/2)/Qch(1)       (107)
PLR(2,2)＝(Qf1/2)/Qch(2)      (108)
这里，由于两台冷水机组101分别为150冷吨的冷水机组101和200冷吨的冷水机组101，且一台200冷吨的冷水机组101的额定冷负荷Qch(1)与一台150冷吨的冷水机组101的额定冷负荷Qch(2)不相同(Qch(1)≠Qch(2))，因此，第一平均负荷率PLR(1,1)与第二平均负荷率PLR(1,2)不相同(PLR(1,1)≠PLR(1,2))，第三平均负荷率PLR(2,1)与第四平均负荷率PLR(2,2)不相同(PLR(2,1)≠PLR(2,2))。
类似的，在冷水机组空调系统100包括三台冷水机组101的情况下，对于第一工况，可以计算对应三台冷水机组101中每台冷水机组101的平均负荷率PLR(i,j)，即，第一平均负荷率PLR(1,1)、第二平均负荷率PLR(1,2)和第五平均负荷率PLR(1,3)。对于第二工况，可以计算对应三台冷水机组101中每台冷水机组101的平均负荷率，即第三平均负荷率PLR(2,1)、第四平均负荷率PLR(2,2)和第六平均负荷率PLR(2,3)。对于第三工况，可以计算对应三台冷水机组101中每台冷水机组101的平均负荷率，即第七平均负荷率PLR(3,1)、第八平均负荷率PLR(3,2)和第九平均负荷率PLR(3,3)。
这样，通过步骤11，控制器5可以计算出多个工况下的每台冷水机组101的平均负荷率PLR(i,j)。
在步骤12中，计算多个工况下每台冷水机组101的蒸发温度Te(i,j)和冷凝温度Tc(i,j)。
预先设置第一关系、第二关系，以确定多个工况下每台冷水机组101的的蒸发温度Te(i,j)和冷凝温度Tc(i,j)。
第一关系表征蒸发温度与平均冷负荷率PLR、冷冻水供水温度te、冷水机组101在额定负荷下运行时对应的冷却水供回水温差ΔTe,tem、以及冷水机组101在额定负荷下运行时对应的冷凝器换热温差之间的关系ΔTe,exc(如公式(3))。第二关系表征冷凝温度与平均冷负荷率PLR、冷却水回水温度tc、冷水机组101在额定负荷下运行时对应的冷冻水供回水温差ΔTc,tem、以及冷水机组101在额定负荷下运行时对应的蒸发器换热温差之间的关系ΔTc,exc(如公式(4))。

需要说明的是，在计算蒸发温度Te(i,j)和冷凝温度Tc(i,j)过程中，需要获取上述参数。
在一些实施例中，冷水机组101在额定负荷下运行时对应的冷却水供回水温差ΔTe,tem、冷水机组101在额定负荷下运行时对应的蒸发器换热温差ΔTc,exc、冷水机组101在额定负荷下运行时对应的冷凝器换热温差ΔTe,exc、冷水机组101在额定负荷下运行时对应的冷冻水供回水温差ΔTc,tem可以分别取值为5℃，以便计算蒸发温度Te和冷凝温度Tc。当然，以上四个值也可以根据需求取为其他值，本公开对此不作限定。
这样，控制器5可以根据蒸发温度的模型(第一关系)和冷凝温度的模型(第二关系)，计算出在多个工况下的每台冷水机组101的蒸发温度Te(i,j)和冷凝温度Tc(i,j)。
在一些实施例中，以冷水机组空调系统100包括两台200冷吨的冷水机组101为例进行说明。
在第一工况下，控制器5根据第一平均负荷率PLR(1,1)、第一冷冻水供水温度te(1,1)、第一冷却水供回水温差ΔTe,tem(1,1)、第一冷凝器换热温差△Te,exc(1,1)，通过公式(3)计算出第一台冷水机组的蒸发温度Te(1,1)。并且，控制器5根据第一平均负荷率PLR(1,1)、第一冷却水水供水温度tc(1,1)、第一冷冻水供回水温差ΔTc,tem(1,1)、第一蒸发器换热温差△Tc,exc(1,1)，通过公式(4)计算出第一台冷水机组101的冷凝温度Tc(1,1)。
在第一工况下，控制器5根据第二平均负荷率PLR(1,2)、第二冷冻水供水温度te(1,2)、第二冷却水供回水温差ΔTe,tem(1,2)、第二冷凝器换热温差△Te,exc(1,2)，通过公式(3)计算出第二台冷水机组的蒸发温度Te(1,2)。并且，控制器5根据第二平均负荷率PLR(1,2)、第二冷却水水供水温度tc(1,2)、第一冷冻水供回水温 差ΔTc,tem(1,2)、第一蒸发器换热温差△Tc,exc(1,1)，通过公式(4)计算出第二台200冷吨的冷水机组的冷凝温度Tc(1,2)。
需要说明的是，第一平均负荷率PLR(1,1)为第一工况下的平均负荷率，第一冷冻水供水温度te(1,1)为第一工况下的冷冻水供水温度，第一冷却水供回水温差ΔTe,tem(1,1)为第一工况下的冷却水供回水温差，第一冷凝器换热温差△Te,exc(1,1)为第一工况下的冷凝器换热温差。第二平均负荷率PLR(1,2)为第二工况下的平均负荷率，第二冷冻水供水温度te(1,2)为第二工况下的冷冻水供水温度，第二冷却水供回水温差ΔTe,tem(1,2)为第二工况下的冷却水供回水温差，第二冷凝器换热温差△Te,exc(1,2)为第二工况下的冷凝器换热温差。
由于第一平均负荷率PLR(1,1)与第二平均负荷率PLR(1,2)相同(PLR(1,1)＝PLR(1,2))，因此，在第一冷冻水供水温度te(1,1)和第二冷冻水供水温度te(1,2)相同，且第一冷却水回水温度tc(1,1)和第二冷却水回水温度tc(1,2)相同的情况下，第一台冷水机组101的冷凝温度Tc(1,1)与第二台冷水机组101的冷凝温度Tc(1,2)相同(Tc(1,1)＝Tc(1,2))。第一台冷水机组101的蒸发温度Te(1,1)与第二台冷水机组101的蒸发温度Te(1,2)相同(Te(1,1)＝Te(1,2))。
在另一些实施例中，以冷水机组空调系统100包括一台200冷吨的冷水机组101和一台150冷吨的冷水机组101为例进行说明。
在第一工况下，控制器5根据第一平均负荷率PLR(1,1)、第一冷冻水供水温度te(1,1)、第一冷却水供回水温差ΔTe,tem(1,1)、第一冷凝器换热温差△Te,exc(1,1)，通过公式(3)计算出第一台冷水机组101的蒸发温度Te(1,1)。
控制器5根据第一平均负荷率PLR(1,1)、第一冷却水水供水温度tc(1,1)、第一冷冻水供回水温差ΔTc,tem (1,1)、第一蒸发器换热温差△Tc,exc(1,1)，通过公式(4)计算出第一台冷水机组101的冷凝温度Tc(1,1)。
在第一工况下，控制器5根据第二平均负荷率PLR(1,2)、第二冷冻水供水温度te(1,2)、第二冷却水供回水温差ΔTe,tem(1,2)、第二冷凝器换热温差△Te,exc(1,2)，通过公式(3)计算出第二台冷水机组101的蒸发温度Te(1,2)。
控制器5根据第二平均负荷率PLR(1,2)、第二冷却水水供水温度tc(1,2)、第一冷冻水供回水温差ΔTc,tem(1,2)、第一蒸发器换热温差△Tc,exc(1,1)，通过公式(4)计算出第二台冷水机组101的冷凝温度Tc(1,2)。
这样，第一平均负荷率PLR(1,1)与第二平均负荷率PLR(1,2)不相同(PLR(1,1)≠PLR(1,2))，则在第一冷冻水供水温度te(1,1)和第二冷冻水供水温度te(1,2)相同，且第一冷却水回水温度tc(1,1)和第二冷却水回水温度tc(1,2)相同的情况下，一台200冷吨的冷水机组101的冷凝温度Tc(1,1)与一台150冷吨的冷水机组101的冷凝温度Tc(1,2)也不相同(Tc(1,1)≠Tc(1,2))，一台200冷吨的冷水机组101的蒸发温度Te(1,1)与一台150冷吨的冷水机组101的蒸发温度Te(1,2)也不相同(Te(1,1)≠Te(1,2))。
其他工况下的每台冷水机组101的蒸发温度Te(i,j)和冷凝温度Tc(i,j)的计算过程与上文类似，在此不再叙述。
这样，通过步骤12，控制器5可以计算出多个工况下的每台冷水机组101的蒸发温度Te(i,j)和冷凝温度Tc(i,j)。
在步骤13中，根据不同工况下每台冷水机组101的蒸发温度Te(i,j)以及冷凝温度Tc(i,j)，计算多个工况下每台冷水机组101对应的第一权值dT(i,j)。
权值dT(i,j)与蒸发温度Te(i,j)和冷凝温度Tc(i,j)之间的温差相关。
例如，控制器5根据公式(5)计算与多个工况下每台冷水机组101对应的第一权值dT(i,j)。
这里，Tc表示冷凝温度，Te表示蒸发温度，△Tmax表示冷水机组101的冷凝温度Tc和蒸发温度Te之间的最大温差，△Tmin表示冷水机组101的冷凝温度Tc和蒸发温度Te之间的最小温差。
在一些实施例中，预先设定冷水机组101的冷凝温度Tc和蒸发温度Te之间的最大温差△Tmax为45℃，预先设定冷水机组101的冷凝温度Tc和蒸发温度Te之间的最小温差△Tmin为15℃，以便控制器5利用公式(5)计算第一权值dT(i,j)。
当然，冷水机组101的冷凝温度Tc和蒸发温度Te之间的最小温差△Tmin、冷水机组101的冷凝温度Tc和蒸发温度Te之间的最大温差△Tmax也可以分别为其他值，或者也可以设定与冷水机组101的冷凝温度Tc和蒸发温度Te之间温差相关的其他系数，本公开对此不作限定。
在此情况下，控制器5可以根据公式(5)，计算多种工况下每台冷水机组101对应的第一权值dT(i,j)。
在一些实施例中，以冷水机组空调系统100包括两台200冷吨的冷水机组101为例进行描述。
对于第一工况，控制器5根据第一台冷水机组101的蒸发温度Te(1,1)、第一台冷水机组101的冷凝温度Tc(1,1)，通过公式(5)计算出第一台冷水机组101的第一权值dT(1,1)。
对于第一工况，控制器5根据第二台冷水机组101蒸发温度Te(1,2)、第二台冷水机组101冷凝温度Tc(1,2)，通过公式(5)计算出第二台冷水机组101的第一权值dT(1,2)。
在第一工况下，由于第一台冷水机组101的蒸发温度Te(1,1)等于第二台冷水机组101蒸发温度Te(1,2)(Te(1,1)＝Te(1,2))，第一台冷水机组101的冷凝温度Tc(1,1)等于第二台冷水机组101的冷凝温度Tc(1,2)(Tc(1,1)＝Tc(1,2))，因此，第一台冷水机组101的第一权值dT(1,1)和第二台冷水机组101的第一权值dT(1,2)相同(dT(1,1)＝dT(1,2))。
又如，以冷水机组空调系统101包括一台200冷吨的冷水机组和一台150冷吨的冷水机组为例进行描述。
对于第一工况，控制器5根据第一台冷水机组101的蒸发温度Te(1,1)、第一台冷水机组101的冷凝温度Tc(1,1)，通过公式(5)计算第一台冷水机组101的第一权值dT(1,1)。
对于第一工况，控制器5根据第二台冷水机组101的蒸发温度Te(1,2)、第二台冷水机组101的冷凝温度Tc(1,2)，通过公式(5)计算第二台冷水机组101的第一权值dT(1,2)。
在第一工况下，由于第一台冷水机组101的蒸发温度Te(1,1)与第二台冷水机组101的蒸发温度Te(1,2)不相同(Te(1,1)≠Te(1,2))，第一台冷水机组101的冷凝温度Tc(1,1)与第二台冷水机组101的冷凝温度Tc(1,2)不相同(Tc(1,1)≠Tc(1,2))，因此，第一台冷水机组101的第一权值dT(1,1)和第二台冷水机组101的第一权值dT(1,2)不同(dT(1,1)≠dT(1,2))。
其他工况下的第一权值dT(i,j)的计算过程与上文类似，在此不再叙述。
这样，通过步骤13，控制器5可以计算出与多个工况下每台冷水机组101对应的第一权值dT(i,j)。
在步骤14中，根据预设的冷水机组101的性能模型、以及计算出的在多个工况下每台冷水机组101的蒸发温度Te(i,j)以及冷凝温度Tc(i,j)，计算在多个工况下的每台冷水机组101的预测能效比COPpre(i,j)。
在一冷水机组101为单机头冷水机组的情况下，单机头冷水机组的性能模型为该冷水机组101的性能模型；在一冷水机组101为多机头冷水机组的情况下，可以根据多机头冷水机组中各单机头冷水机组的性能模型，获取该冷水机组101的性能模型。也就是说，冷水机组的性能模型包括单机头冷水机组的性能模型或多机头冷水机组的性能模型中的至少一个。
需要说明的是，对于单机头冷水机组的性能模型可以采用基于设备的数据进行建模、或者采用机器学习进行建模。当然，对于多机头冷水机组的性能模型，也可以将该多机头冷水机组作为一个整体，通过采集整个系统的数据并按照单机头冷水机组的建模方法进行建模。
下文以冷水机组101为多机头冷水机组为例进行说明。
图4为根据一些实施例的控制器执行步骤的另一种流程图。
在一些实施例中，如图4所示，控制器5还被配置为执行步骤141至步骤143。
在步骤141中，采集冷水机组101的运行数据。
采集的冷水机组101的运行数据包括：冷水机组101中的每台单机头冷水机组的蒸发温度Tek、冷凝温度Tck以及运行负载Lk。这里，k表示第k台单机头冷水机组，且k为自然数，k大于或等于1(1≤k)。需要说明的是，在冷水机组101为多机头冷水机组的情况下，上述蒸发温度Tek、冷凝温度Tck以及运行负载Lk指的是该冷水机组101中每台单机头冷水机组的参数。在冷水机组101为单机头冷水机组的情况下，上述蒸发温度Tek、冷凝温度Tck以及运行负载Lk指的是该冷水机组101的参数。
在该多机头冷水机组包括m台单机头冷水机组的情况下，则m大于或等于k(k≤m)。这里，m＞1，且m为自然数。
另外，还需要采集冷水机组101中单机头冷水机组的其他运行数据，以剔除所采集的数据(蒸发温度Tek、冷凝温度Tck以及运行负载Lk)中的异常值，从而提高采集的数据的可靠性，也有利于准确建立冷水机组101的性能模型。
在一些实施例中，采集的冷水机组101的运行数据还包括：冷冻水供水温度Te-out、冷冻水回水温度Te-in、冷冻水流量Qe、冷却水进水温度Tc-in、冷却水出水温度Tc-out、冷却水流量Qc、冷水机组101内各单机头冷水机组的运行功率Pi。
图5为根据一些实施例的控制器执行步骤的又一种流程图。
在此情况下，如图5所示，控制器5还被配置执行步骤1411至步骤1416：
在步骤1411中，根据冷冻水回水温度Te-in、冷冻水供水温度Te-out、冷冻水流量Qe以及水的比热容c，计算冷水机组101的当前制冷量Qchw。
例如，控制器5根据公式(201)计算冷水机组101的当前制冷量Qchw。
Qchw＝c×Qe×(Te-in-Te-out)       (201)
需要说明的是，也可以采用其他方式计算冷水机组101的当前的制冷量Qchw。
在步骤1412中，根据冷却水出水温度Tc-out、冷却水进水温度Tc-in、冷却水流量Qc以及水的比热容c，计算冷水机组101的当前排热量Qcw。
例如，控制器5根据公式(202)计算冷水机组101的排热量Qcw。
Qcw＝c×Qc×(Tc-in-Tc-out)       (202)
在步骤1413中，根据冷水机组101的当前制冷量Qchw、冷水机组101的当前排热量Qcw以及冷水机组101中每台单机头冷水机组的运行功率Pi，计算能量平衡系数γ。
例如，控制器5根据公式(203)计算冷水机组101的能量平衡系数γ。
这里，m表示单机头冷水机组的数量，表示冷水机组101中所有单机头冷水机组的运行功率之和。
在步骤1414中，判断能量平衡系数γ是否大于预设值。若“是”，则执行步骤1415，若“否”，则执行步骤1416。
在步骤1415中，确定所采集的运行数据为异常值。
在步骤1416中，确定所采集的运行数据为正常值。
这里，所述预设值可根据需求预设或改变。例如，所述预设值为10％。若能力平衡系数γ大于10％，控制器5确定能力平衡系数γ对应的运行数据为异常值；若能力平衡系数γ小于或等于10％，控制器5确定能力平衡系数γ对应的运行数据为正常值。
需要说明的是，能力平衡系数γ对应的运行数据为：冷水机组101中的每台单机头冷水机组的蒸发温度Tek、冷凝温度Tck以及运行负载Lk。
在步骤142中，确定冷水机组101中每台单机头冷水机组的性能模型。
根据采集的单机头冷水机组的蒸发温度Tek、冷凝温度Tck、运行负载Lk、额定制冷量Qdes,k和能效比COPk，确定单机头冷水机组的性能模型。需要说明的是，此处采集的数据为单机头冷水机组的运行数据，以便建立性能模型。
这里，引入用于表征单机头冷水机组的性能模型的性能系数DCOPk。
图6为根据一些实施例的控制器执行步骤的又一种流程图。
在一些实施例中，如图6所示，控制器5被配置为执行步骤1421和步骤1422：
在步骤1421中，根据采集的每台单机头冷水机组的蒸发温度Tek、冷凝温度Tck和能效比COPk，计 算每台单机头冷水机组的性能系数DCOPk。
例如，控制器5通过公式(204)计算每台单机头冷水机组的性能系数DCOPk。
在步骤1422中，根据每台单机头冷水机组的性能系数DCOPk、第二权值dTk和负荷率PLRk，拟合并确定每台单机头冷水机组的性能系数的关系式。
例如，控制器5通过公式(205)和(206)计算负荷率PLRk。

这里，表示所有单机头冷水机组的运行负载之和，Qk表示每台单机头冷水机组的制冷量。每台单机头冷水机组的制冷量Qk与所述单机头冷水机组的运行负载Lk以及所述冷水机组的当前制冷量Qchw相关。
并且，控制器5可以根据公式(5)计算出每台单机头冷水机组对应的第二权值dTk。需要说明的是，第二权值dTk与采集的蒸发温度、采集的冷凝温度以及所述单机头冷水机组的冷凝温度和蒸发温度之间的温差相关。
控制器5拟合性能系数DCOPk与负荷率PLRk以及第二权值dTk之间的关系式(如公式(207))。
DCOPk＝Ak×PLRk 2+Bk×PLRk×dTk+Ck×dTk 2+Dk×PLRk+Ek×dTk+Fk     (207)
这里，Ak、Bk、Ck、Dk、Ek和Fk为拟合系数。公式(207)为单机头冷水机组的性能系数的关系式，也就是单机头冷水机组的性能模型。
例如，200冷吨的单机头冷水机组的拟合系数分别为A1、B1、C1、D1、E1和F1，且冷负荷率为PLR1，权值为dT1。则200冷吨单机头冷水机组的性能模型为：
DCOP1＝A1×PLR1 2+B1*PLR1×dT1+C1×dT1 2+D1×PLR1+E1×dT1+F1。
又如，150冷吨的单机头冷水机组的拟合系数分别为A2、B2、C2、D2、E2和F2，且冷负荷率为PLR2，权值为dT2。则150冷吨单机头冷水机组的性能模型为：
DCOP2＝A2×PLR2 2+B2×PLR2×dT2+C2*dT2 2+D2×PLR2+E2×dT2+F2。
需要说明的是，不同冷吨的单机头冷水机组，其拟合系数不同。另外，在步骤14中，当控制器5根据单机头冷水机组的性能模型计算冷水机组101的性能系数时，通过将步骤11中计算平均负荷率PLR(i,j)，步骤13中计算的第一权值dT(i,j)分别代入负荷率PLRk和第二权值dTk得到该性能系数。
在步骤143中，根据确定的每台单机头冷水机组的性能模型，确定多机头冷水机组的性能模型。
图7为根据一些实施例的控制器执行步骤的又一种流程图。
在一些实施例中，如图7所示，控制器5被配置为执行步骤1431至步骤1433：
在步骤1431中，根据确定的单机头冷水机组的性能模型、采集的蒸发温度Tek和采集的冷凝温度Tck，计算每台单机头冷水机组的预测能效比COPpre,k。
例如，控制器5通过公式(209)计算每台单机头冷水机组的预测能效比COPpre,k。
COPpre,k＝DCOPk×Tek/(Tck-Tek)         (209)
在步骤1432中，根据每台单机头冷水机组的预测能效比COPpre,k和制冷量Qk，确定冷水机组101的电功率Pw。
例如，控制器5根据公式(210)，计算冷水机组101的电功率Pw。
在步骤1433中，根据电功率Pw和冷水机组101的当前制冷量Qchw，确定多机头冷水机组的预测能效比COPpre。
例如，控制器5通过公式(210)，确定冷水机组101(多机头冷水机组)的预测能效比COPpre。
COPpre＝Qcw/Pw         (210)
这样，根据多个单机头冷水机组的性能模型，可以确定多机头冷水机组的性能模型(公式209至公式210)及多机头冷水机组的预测能效比COPpre。例如，在冷水机组101为单机头冷水机组的情况下，步骤14中冷水机组101的预测能效比COPpre(i,j)可以通过公式(209)获得；在冷水机组101为多机头冷水机组的情况下，步骤14中冷水机组101的预测能效比COPpre(i,j)可以通过公式(210)获得。
在本公开一些实施例中，可以快速建立大型的不同组合的多机头冷水机组的性能模型，并结合实际运行数据进行优化处理，这样，可以提高性能模型的精度。另外，且该种建模方式根据多个单机头冷水机组的特点，反映多机头冷水机组的运行情况，因此，利用该模型控制冷水机组101，可以达到良好的节能效果。
下文根据一种多机头冷水机组的运行数据，建立性能模型，并对该性能模型进行验证。
表1
例如，如表1所示，该多机头冷水机组的制冷量为500冷吨，且该500冷吨的多机头冷水机组由一台200冷吨的单机头冷水机组和两台150冷吨的单机头冷水机组组成。表1展示了该多机头冷水机组的冷冻水进水温度、冷冻水出水温度、冷却水进水温度、冷却水进水温度、冷却水流量、总功率、总冷负荷以及总负荷率。
表2
表3
表4
如表2至表4所示，表2展示了500冷吨的多机头冷水机组中200冷吨单机头冷水机组的运行数据。表3展示了500冷吨的多机头冷水机组中一台150冷吨单机头冷水机组的运行数据。表4展示了500冷吨的多机头冷水机组中另一台150冷吨单机头冷水机组的运行数据。
表5
在一些实施例中，如表5所示，选择20个样本点，通过上述公式(201)至公式(210)，控制器5计算出500冷吨的多机头冷水机组的预测能效比COPpre。
图8为根据一些实施例的一种多机头水机组的实际能效比和预测能效比的折线图。图9为根据一些实施例的一种多机头水机组的实际能效比和预测能效比的相对误差的折线图。
如图8所示，500冷吨的多机头水机组的实际能效比的折线和预测能效比的折线大部分重叠。如图9所示，500冷吨的多机头水机组的的实际能效比和预测能效比的相对误差较小。
如图8和图9所示，多机头冷水机组的预测能效比COPpre与实际能效比COP基本相同。
表6
这样，控制器5可以根据公式(209)和公式(210)，计算出在不同工况下的各台冷水机组101的预测能效比COPpre(i，j)。
在一些实施例中，以冷水机组空调系统100包括两台200冷吨的冷水机组101为例。
对于第一工况，控制器5根据第一冷负荷率PLR(1,1)、第一权值dT(1,1)、第一蒸发温度Te(1,1)、第一冷凝温度Tc(1,1)以及公式(209)计算出第一台冷水机组101的第一预测能效比COPpre(1,1)。
对于第一工况，控制器5根据第二冷负荷率PLR(1,2)、第二权值dT(1,2)、第二蒸发温度Te(1,2)、第二冷凝温度Tc(1,2)以及公式(209)计算出第二台冷水机组101的第二预测能效比COPpre(1,2)。
这样，由于第一平均负荷率PLR(1,1)与第二平均负荷率PLR(1,2)相同(PLR(1,1)＝PLR(1,2))，第一权值dT(1,1)与第二权值dT(1,2)相同(dT(1,1)＝dT(1,2))，第一台200冷吨的冷水机组101的第一蒸发温度Te(1,1)与第二台200冷吨的冷水机组101的第二蒸发温度Te(1,2)相同(Te(1,1)＝Te(1,2))，第一台200冷吨的冷水机组101的第一冷凝温度Tc(1,1)与第二台200冷吨的冷水机组101的第二冷凝温度Tc(1,2)相同(Tc(1,1)＝Tc(1,2))。因此，第一预测能效比COPpre(1,1)与第二预测能效比COPpre(1,2)相同(COPpre(1,1)＝COPpre(1,2))。
对于第二工况，控制器5根据第三冷负荷率PLR(2,1)、第三权值dT(2,1)、第三蒸发温度Te(2,1)、第三冷凝温度Tc(2,1)以及公式(209)计算出第一台冷水机组101的第三预测能效比COPpre(2,1)。控制器5根据第四冷负荷率PLR(2,2)、第四权值dT(2,2)、第四蒸发温度Te(2,2)、第四冷凝温度Tc(2,2)以及公式(209)计算出第二台冷水机组101的第四预测能效比COPpre(2,2)。
这样，由于第三平均负荷率PLR(2,1)与第四平均负荷率PLR(2,2)相同(PLR(2,1)＝PLR(2,2))，第三权值dT(2,1)与第四权值dT(2,2)相同(dT(2,1)＝dT(2,2))，第一台200冷吨的冷水机组101的第三蒸发温度Te(2,1)与第二台200冷吨的冷水机组101的第四蒸发温度Te(2,2)相同(Te(2,1)＝Te(2,2))，第一台200冷吨的冷水机组101的第三冷凝温度Tc(2,1)与第二台200冷吨的冷水机组101的冷凝温度Tc(2,2)相同(Tc(1,1)＝Tc(1,2))。 因此，第三预测能效比COPpre(2,1)与第四预测能效比COPpre(2,2)相同(COPpre(2,1)＝COPpre(2,2))。
在另一些实施例中，以冷水机组空调系统100包括一台200冷吨的冷水机组101和一台150冷吨的冷水机组101为例。
对于第一工况，控制器5根据第一冷负荷率PLR(1,1)、第一权值dT(1,1)、第一蒸发温度Te(1,1)、第一冷凝温度Tc(1,1)以及公式(209)计算出第一台冷水机组101的第一预测能效比COPpre(1,1)。
对于第一工况，控制器5根据第二冷负荷率PLR(1,2)、第二权值dT(1,2)、第二蒸发温度Te(1,2)、第二冷凝温度Tc(1,2)以及公式(209)计算出第二台冷水机组101的第二预测能效比COPpre(1,2)。
这样，第一预测能效比COPpre(1,1)与第二预测能效比COPpre(1,2)不一定相同。
对于第二工况，控制器5根据第三冷负荷率PLR(2,1)、第三权值dT(2,1)、第三蒸发温度Te(2,1)、第三冷凝温度Tc(2,1)以及公式(209)计算出第一台冷水机组101的第三预测能效比COPpre(2,1)。控制器5根据第四冷负荷率PLR(2,2)、第四权值dT(2,2)、第四蒸发温度Te(2,2)、第四冷凝温度Tc(2,2)以及公式(209)计算出第二台冷水机组101的第四预测能效比COPpre(2,2)。
这样，第三预测能效比COPpre(2,1)与第四预测能效比COPpre(2,2)不一定相同。
其他工况下的各台冷水机组101的预测能效比COPpre(i,j)的计算过程与上文类似，在此不再叙述。
在步骤15中，根据在多个工况下每台冷水机组的预测能效比COPpre(i,j)，确定冷水机组空调系统100中的多台冷水机组101的运行状态。
这里，冷水机组101的运行状态指冷水机组101开启或关闭。
在步骤16中，根据确定的多台冷水机组101的运行状态控制多台冷水机组101的运行。
控制器5通过比较预测能效比COPpre,(i,j)，以确定开启或关闭冷水机组空调系统100中的对应的冷水机组101，从而使冷水机组空调系统100运行在能效比较大的工况下。
例如，冷水机组空调系统100包括两台200冷吨的冷水机组101。在第一工况下，第一台冷水机组101对应的第一预测能效比COPpre(1,1)与第二台冷水机组101对应的第二预测能效比COPpre(1,2)相同(COPpre (1,1)＝COPpre(1,2))。在第二工况下，第一台冷水机组101对应的第三预测能效比COPpre(2,1)与第二台冷水机组101对应的第四预测能效比COPpre(2,2)相同(COPpre(2,1)＝COPpre(2,2))。
又例如，冷水机组空调系统100包括一台200冷吨的冷水机组和一台150冷吨的冷水机组101。在第一工况下，一台200冷吨的冷水机组101对应的第一预测能效比COPpre(1,1)与一台150冷吨的冷水机组101对应的第二预测能效比COPpre(1,2)不一定相同。在第二工况下，一台200冷吨的冷水机组101对应的第三预测能效比COPpre(2,1)与一台150冷吨的冷水机组101对应的第四预测能效比COPpre(2,2)不一定相同。
其他工况下的比较预测能效比的过程与上文类似，在此不再叙述。这样，冷水机组空调系统100可以在较高能效比下运行。
需要说明的是，在冷水机组空调系统100包括两台冷水机组101的情况下，若控制器5计算出开启两台冷水机组101的能效比开启一台冷水机组的能效大，则冷水机组空调系统100工作在开启两台冷水机组101的工况下。在此情况下，若当前运行一台冷水机组101，则确定需要开启第二台冷水机组101。
同理，若计算出开启一台冷水机组101的能效比开启两台冷水机组101的能效大，则冷水机组空调系统100工作在开启一台冷水机组101的工况下。在此情况下，若当前运行两台冷水机组，则确定需要关闭一台冷水机组101。
图10为根据一些实施例的控制器执行步骤的又一种流程图。
为了避免冷水机组101的频繁启停，具体是否开启或关闭还需要考虑冷水机组空调系统100的冷负荷波动。因此，在一些实施例中，如图10所示，步骤16包括步骤161至步骤166。
在步骤161中，计算冷水机组空调系统100前一时刻的冷负荷相对于需求冷负荷的负荷变化率ROC。
在步骤162中，判断负荷变化率ROC是否达到待开启的冷水机组101的负荷变化率的上限值ROC1。若“是”，则执行步骤163，并返回至步骤11；若“否”，则执行步骤166。
在步骤163中，开启冷水机组空调系统100中的一台冷水机组101。
在步骤164中，判断负荷变化率ROC是否达到待关闭的冷水机组101的负荷变化率的上限值ROC2。 若“是”，则执行步骤165，并返回至步骤11；若“否”，则执行步骤166。
在步骤165中，关闭冷水机组空调系统100中的一台冷水机组101。
在步骤166中，控制冷水机组空调系统100在当前的运行状态下继续运行。
在冷水机组空调系统100运行时，控制器5通过计算冷水机组空调系统100前一时刻的冷负荷相对于需求冷负荷的负荷变化率，可以判断冷负荷是否发生了急剧变化。
该急剧变化包括两种变化：一种是急剧较小，需要关闭冷水机组101；一种是急剧增大，需要开冷水机组101。
若负荷变化率ROC达到待关闭的冷水机组101的负荷变化率的上限值ROC1，间接说明在第一预设时长内负荷急剧减小了，若不关闭该冷水机组101，在该第一预设时长内水温不能马上调到设定值。也就是说，冷水机组空调系统100在该第一预设时长内制冷量不能及时减少到需求冷负荷，需要关闭对应的冷水机组101。
若负荷变化率ROC达到待开启的冷水机组101的负荷变化率的上限值ROC2，间接说明在第一预设时长内负荷急剧增加了，若不加开启该冷水机组101，在该第一预设时长内水温不能马上调到设定值。也就是说，冷水机组空调系统100在该第一预设时长内制冷量不能及时增加到需求冷负荷，需要开启冷水机组101。
若负荷变化率未达到待开启或待关闭的冷水机组101的负荷变化率的上限值，间接说明在第一预设时长内负荷存在少许波动(波动亦可能是传感器测量误差所致)。此时，即使不开启或关闭对应的冷水机组101，在该第一预设时长内水温亦能够调到设定值。
这样，通过上述步骤161至步骤166可以减小冷水机组101的频繁启停，确保系统稳定性。这里，所述第一预设时长可以是设定的用于周期获取冷水机组空调系统100的冷负荷的时间。例如所述第一预设时长T1为5分钟。
在一些实施例中，负荷变化率ROC与冷水机组空调系统100的需求冷负荷、冷水机组空调系统100的冷负荷以及第一预设时长T1有关。例如，负荷变化率ROC与冷水机组空调系统100的需求冷负荷、冷水机组空调系统100的冷负荷以及第一预设时长T1满足公式(301)。
ROC＝(Qd-Qf)/T1          (301)
这里，Qf为冷水机组空调系统100的需求冷负荷，Qd为冷水机组空调系统100的冷负荷，T1为第一预设时长。
在一些实施例中，假设冷水机组空调系统100中冷水机组101合适的启停时间间隔为第二预设时长T2。例如，第二预设时长T2为30分钟。
若当前需要开启一冷水机组101，控制器5可以获取到该冷水机组101的额定冷负荷Qch。可根据公式(302)计算待开启的冷水机组101的负荷变化率ROC1。
ROC1＝Qch/T2         (302)
在负荷变化率ROC达到待开启的冷水机组101的负荷变化率的上限值ROC1(即，ROC≥ROC1)，开启冷水机组空调系统100中对应的冷水机组101。
需要说明的是，每次仅开启一台冷水机组101。之后，控制器5返回执行步骤11，直至负荷变化率ROC小于待开启的冷水机组101的负荷变化率的上限值ROC1(ROC＜ROC1的上限值)。
若当前需要关闭一冷水机组101，控制器5可以获取到该冷水机组101的额定冷负荷Qch。
可根据公式(303)计算待关闭的冷水机组101的负荷变化率的上限值ROC2。
ROC2＝Qch/T2        (303)
在负荷变化率ROC达到待关闭的冷水机组101的负荷变化率的上限值ROC2(ROC≥ROC2)，关闭冷水机组空调系统100中对应的冷水机组101。
需要说明的是，每次仅关闭一台冷水机组101。之后，控制器5返回步骤11，直至负荷变化率ROC小于待关闭的冷水机组101的负荷变化率的上限值ROC2(ROC＜ROC2)。
例如，在冷水机组空调系统100包括一台200冷吨的冷水机组101和一台150冷吨的冷水机组101的 情况下，若控制器5计算出开启两台冷水机组101的能效比开启一台200冷吨的冷水机101组的能效大，则该冷水机组空调系统100需要工作在开启两台冷水机组101的工况下。
若当前运行一台200冷吨的冷水机组101，则确定需要开启另一台150冷吨的冷水机组101。控制器5根据待开启的150冷吨的冷水机组101的额定冷负荷Qch,通过公式(302)计算待开启的冷水机组101的负荷变化率ROC1。若负荷变化率ROC大于或等于待开启的冷水机组101的负荷变化率的上限值ROC1，控制器5确定开启该台150冷吨的冷水机组101，否则，保持当前运行一台200冷吨的冷水机组101。
在冷水机组空调系统100包括一台200冷吨的冷水机组和一台150冷吨的冷水机组101的情况下，若控制器5计算出开启一台200冷吨的冷水机组101的能效比开启两台冷水机组101的能效大，则该冷水机组空调系统101需要工作在开启一台150冷吨的冷水机组101的工况下。
若当前运行两台冷水机组101，则确定需要关闭另一台150冷吨的冷水机组101。
控制器5根据待关闭的150冷吨的冷水机组101的额定冷负荷Qch,通过公式(303)计算待关闭的150冷吨的冷水机组101的负荷变化率ROC2。
若负荷变化率ROC大于或等于待关闭的冷水机组101的负荷变化率的上限值ROC2(ROC≥ROC2)，控制器5确定关闭该台150冷吨冷水机组101，否则，保持当前运行两台冷水机组101。
需要说明的是，在关闭对应的冷水机组101时，可以优先关闭冷水机组空调系统100中运行时间最长的冷水机组101。
需要说明的是，通过本公开一些实施例提供的控制器5执行的步骤，可以实现保持冷水机组空调系统100高能效运行，也可以通过负荷变化率ROC的大小，及时对冷水机组空调系统100进行负荷调节，以实现节能。
下文采用由一台300冷吨的冷水机组和一台250冷吨的冷水机组组成的冷水机组空调系统100为例对本公开一些实施例提供的控制器5执行的步骤进行验证。
图11为根据一些实施例的冷水机组空调系统的样本点的需求冷负荷的统计图。图12为根据一些实施例的冷水机组空调系统的样本点的冷冻水供水温度的统计图。
如图11和图12所示，横坐标表示所采集的559个样本点，图11展示了559个样本点的需求冷负荷Qf。图12展示了559个样本点的冷冻水供水温度Te。
图13为根据一些实施例的冷水机组空调系统的样本点的冷却水回水温度的统计图。图14为根据一些实施例的冷水机组空调系统的样本点的控制台数的统计图。图15为根据一些实施例的冷水机组空调系统的样本点的预测能效比的统计图。
如图13至图15所示，横坐标表示所采集的559个样本点，图13展示了559个样本点的冷却水回水温度Tc。图14展示了559个样本点的控制台数。图15展示了559个样本点的预测能效比COPpre。结合图14和图15，通过控制器5执行的步骤对冷水机组空调系统100的进行控制，控制高效及准确，且冷水机组空调系统100的稳定性较高。
本公开一些实施例中的步骤序号仅是为了便于描述本公开中的一些实施例，而不能理解为对步骤的顺序限定。步骤的执行顺序可以根据实际需求具体确定，不限于本公开一些实施例中的步骤顺序。
本公开一些实施例还提供了一种冷水机组空调系统的控制方法，所述冷水机组空调系统与冷水机组空调系统100的结构类似。例如，所述冷水机组空调系统包括多个冷水机组101和控制器5，且该方法可由控制器5执行。
该方法包括：计算在多个工况下所述多台冷水机组中每台冷水机组的平均负荷率；所述多个工况互不相同，且在所述多个工况下所述多台冷水机组的开启数量不同；计算在所述多个工况下所述每台冷水机组的蒸发温度和冷凝温度；根据所述每台冷水机组的蒸发温度和冷凝温度，计算在所述多个工况下所述每台冷水机组对应的第一权值；所述第一权值与所述蒸发温度和所述冷凝温度之间的温差相关；根据预设的所述冷水机组的性能模型、以及在所述多个工况下所述每台冷水机组的蒸发温度和冷凝温度，计算在所述多个工况下所述每台冷水机组的预测能效比；所述性能模型表征性能系数与所述平均冷负荷率和所述第一权值的关系；所述预测能效比与所述性能系数、所述蒸发温度和所述冷凝温度之间存在预设关系；根据在所述多个工况下所述每台冷水机组的预测能效比，确定所述多台冷水机组的运行状态；所 述冷水机组的运行状态指所述冷水机组开启或关闭；根据确定的所述多台冷水机组的运行状态，控制所述多台冷水机组的运行。
在一些实施例中，该方法还包括：在确定所述多台冷水机组的运行状态后，计算所述冷水机组空调系统前一时刻的冷负荷相对于需求冷负荷的负荷变化率；若所述负荷变化率达到待开启或待关闭的冷水机组的负荷变化率的上限值，控制所述冷水机组空调系统在确定的运行状态下运行；若所述负荷变化率小于待开启或待关闭的冷水机组的负荷变化率的上限值，控制所述冷水机组空调系统在当前的运行状态下继续运行。
在一些实施例中，该方法还包括：若所述负荷变化率达到所述待开启的冷水机组的负荷变化率的上限值，控制所述待开启的冷水机组开启；若所述负荷变化率达到所述待关闭的冷水机组的负荷变化率的上限值，控制所述待关闭的冷水机组关闭；所述待关闭的冷水机组为运行的冷水机组中运行时间最长的冷水机组。
在一些实施例中，该方法还包括：根据所述冷水机组空调系统的需求冷负荷、所述冷水机组空调系统中开启的冷水机组的数量、以及所述多台冷水机组的额定冷负荷，计算在所述多个工况下所述每台冷水机组的所述平均冷负荷率。
在一些实施例中，该方法还包括：获取冷冻水供水温度、冷却水回水温度、冷水机组在额定负荷下运行时对应的冷却水供回水温差、冷水机组在额定负荷下运行时对应的蒸发器换热温差、冷水机组在额定负荷下运行时对应的冷凝器换热温差、以及冷水机组在额定负荷下运行时对应的冷冻水供回水温差；根据预设的第一关系，计算在所述多个工况下所述每台冷水机组的蒸发温度；所述第一关系表征所述蒸发温度与所述平均冷负荷率、所述冷冻水供水温度、冷水机组在额定负荷下运行时对应的冷却水供回水温差、以及冷水机组在额定负荷下运行时对应的冷凝器换热温差之间的关系；根据预设的第二关系，计算在所述多个工况下所述每台冷水机组的冷凝温度；所述第二关系表征所述冷凝温度与所述平均冷负荷率、所述冷却水回水温度、冷水机组在额定负荷下运行时对应的冷冻水供回水温差、以及冷水机组在额定负荷下运行时对应的蒸发器换热温差之间的关系。
在一些实施例中，该方法还包括：根据所述冷水机组的冷凝温度和蒸发温度之间的最大温差、所述冷水机组的冷凝温度和蒸发温度之间的最小温差、计算出的蒸发温度和冷凝温度，计算所述每台冷水机组对应的所述第一权值。
在一些实施例中，该方法还包括：采集所述冷水机组的运行数据；所述运行数据包括所述冷水机组中每台单机头冷水机组的蒸发温度、冷凝温度、以及运行负载；根据采集的蒸发温度、冷凝温度、运行负载、以及所述每台单机头冷水机组的额定制冷量和能效比，确定所述每台单机头冷水机组的性能模型；根据确定的每台单机头冷水机组的性能模型，确定所述多机头冷水机组的性能模型；所述冷水机组的性能模型包括所述单机头冷水机组的性能模型或所述多机头冷水机组的性能模型中的至少一个。
在一些实施例中，该方法还包括：根据采集的蒸发温度、冷凝温度以及能效比，计算所述单机头冷水机组的性能系数；根据所述单机头冷水机组的所述性能系数、第二权值和负荷率，拟合并确定所述单机头冷水机组的性能系数的关系式。这里，所述单机头冷水机组的性能系数的关系式为所述单机头冷水机组的性能模型，所述第二权值与采集的蒸发温度、采集的冷凝温度以及所述单机头冷水机组的冷凝温度和蒸发温度之间的温差相关。
在一些实施例中，该方法还包括：根据所述单机头冷水机组的运行负载和额定制冷量、所述冷水机组的当前制冷量，计算所述负荷率。
在一些实施例中，该方法还包括：根据确定的所述每台单机头冷水机组的性能模型、采集的蒸发温度和冷凝温度，计算所述每台单机头冷水机组的预测能效比；根据所述每台单机头冷水机组的预测能效比和制冷量，确定所述冷水机组的电功率；所述每台单机头冷水机组的制冷量与所述单机头冷水机组的运行负载以及所述冷水机组的当前制冷量相关；根据所述电功率和所述冷水机组的当前制冷量，确定所述多机头冷水机组的预测能效比。
在一些实施例中，该方法还包括：删除采集的运行数据中的异常值。
在一些实施例中，所述删除采集的运行数据中的异常值包括：根据所述冷冻水回水温度、所述冷冻水供水温度、所述冷冻水流量以及水的比热容，计算所述冷水机组的当前制冷量；根据所述冷却水出水温度、所述冷却水进水温度、所述冷却水流量以及水的比热容，计算所述冷水机组的当前排热量；根据所述冷水机组的当前制冷量、所述冷水机组的当前排热量以及所述每台单机头冷水机组的运行功率，计 算能量平衡系数；若所述能量平衡系数大于预设值，确定采集的运行数据为异常值；删除确定为异常值的运行数据。
本领域的技术人员将会理解，本发明的公开范围不限于上述具体实施例，并且可以在不脱离本申请的精神的情况下对实施例的某些要素进行修改和替换。本申请的范围受所附权利要求的限制。

Claims (20)

  1. 一种冷水机组空调系统，包括：
    多台冷水机组，所述多台冷水机组共用水路，且所述多台冷水机组的制冷剂流路互相独立，所述多台冷水机组中的每台冷水机组包括：
    至少一个压缩机，且被配置为压缩冷媒以使低压冷媒受压缩形成高压冷媒；
    冷凝器，被配置为将气态冷媒冷凝为液态冷媒，并与冷却水进行热交换；
    节流件，且被配置为控制流经所述节流件的所述冷媒的流量和压力；以及
    蒸发器，被配置为将液态冷媒蒸发为气态冷媒，并与冷冻水进行热交换；所述压缩机、所述冷凝器、所述节流件和所述蒸发器依次连接形成冷媒循环；以及
    控制器，所述控制器被配置为：
    建立所述冷水机组的性能模型；所述冷水机组的性能模型与所述冷水机组的运行数据相关；
    计算在多个工况下所述多台冷水机组中每台冷水机组的目标参数；所述多个工况互不相同，且在所述多个工况下所述多台冷水机组的开启数量不同；
    根据所述冷水机组的性能模型、以及所述每台冷水机组的目标参数中的至少一个，计算所述每台冷水机组的预测能效比；
    根据所述每台冷水机组的所述预测能效比，确定所述多台冷水机组的运行状态；所述冷水机组的运行状态指所述冷水机组开启或关闭；以及
    根据确定的所述多台冷水机组的运行状态，控制所述多台冷水机组的运行。
  2. 根据权利要求1所述的冷水机组空调系统，其中，所述目标参数包括平均负荷率、蒸发温度、冷凝温度以及第一权值，所述控制器被配置为：
    计算在所述多个工况下所述每台冷水机组的平均负荷率；
    计算在所述多个工况下所述每台冷水机组的蒸发温度和冷凝温度；
    根据所述每台冷水机组的蒸发温度和冷凝温度，计算在所述多个工况下所述每台冷水机组对应的第一权值；所述第一权值与所述蒸发温度和所述冷凝温度之间的温差相关。
  3. 根据权利要求2所述的冷水机组空调系统，其中，在计算出所述第一权值后，所述控制器被配置为：
    根据所述冷水机组的性能模型、以及在所述多个工况下所述每台冷水机组的蒸发温度和冷凝温度，计算在所述多个工况下所述每台冷水机组的预测能效比；
    其中，所述性能模型表征性能系数与所述平均负荷率和所述第一权值的关系；所述预测能效比与所述性能系数、所述蒸发温度和所述冷凝温度之间存在预设关系；所述目标参数包括在所述多个工况下所述每台冷水机组的所述蒸发温度和所述冷凝温度。
  4. 根据权利要求2所述的冷水机组空调系统，其中，所述控制器被配置为：
    获取冷冻水供水温度、冷却水回水温度、冷水机组在额定负荷下运行时对应的冷却水供回水温差、冷水机组在额定负荷下运行时对应的蒸发器换热温差、冷水机组在额定负荷下运行时对应的冷凝器换热温差、以及冷水机组在额定负荷下运行时对应的冷冻水供回水温差；
    根据预设的第一关系，计算在工况下所述每台冷水机组的蒸发温度；所述第一关系表征所述蒸发温度与平均冷负荷率、所述冷冻水供水温度、冷水机组在额定负荷下运行时对应的冷却水供回水温差、以及冷水机组在额定负荷下运行时对应的冷凝器换热温差之间的关系；
    根据预设的第二关系，计算在所述工况下所述每台冷水机组的冷凝温度；所述第二关系表征所述冷凝温度与平均冷负荷率、所述冷却水回水温度、冷水机组在额定负荷下运行时对应的冷冻水供回水温差、以及冷水机组在额定负荷下运行时对应的蒸发器换热温差之间的关系。
  5. 根据权利要求3所述的冷水机组空调系统，其中，所述控制器被配置为：
    根据所述冷水机组的冷凝温度和蒸发温度之间的最大温差、所述冷水机组的冷凝温度和蒸发温度之间的最小温差、计算出的蒸发温度和冷凝温度，计算所述每台冷水机组对应的所述第一权值。
  6. 根据权利要求1至5任一项所述的冷水机组空调系统，其中，所述冷水机组包括单机头冷水机组和多机头冷水机组之一，所述单机头冷水机组包括一个压缩机，所述多机头冷水机组包括多个压缩机，且所述多机头冷水机组由多个单机头冷水机组构成，所述控制器还被配置为：
    采集所述冷水机组的运行数据；所述运行数据包括所述冷水机组中每台单机头冷水机组的蒸发温 度、冷凝温度、以及运行负载；
    根据采集的蒸发温度、冷凝温度、运行负载、以及所述每台单机头冷水机组的额定制冷量和能效比，确定所述每台单机头冷水机组的性能模型；
    根据确定的每台单机头冷水机组的性能模型，确定所述多机头冷水机组的性能模型；所述冷水机组的性能模型包括所述单机头冷水机组的性能模型或所述多机头冷水机组的性能模型中的至少一个。
  7. 根据权利要求6所述的冷水机组空调系统，其中，所述控制器被配置为：
    根据采集的蒸发温度、冷凝温度以及能效比，计算所述单机头冷水机组的性能系数；
    根据所述单机头冷水机组的所述性能系数、第二权值和负荷率，拟合并确定所述单机头冷水机组的性能系数的关系式；
    其中，所述单机头冷水机组的性能系数的关系式为所述单机头冷水机组的性能模型，所述第二权值与采集的蒸发温度、采集的冷凝温度以及所述单机头冷水机组的冷凝温度和蒸发温度之间的温差相关。
  8. 根据权利要求7所述的冷水机组空调系统，其中，所述负荷率与所述单机头冷水机组的运行负载和额定制冷量、所述冷水机组的当前制冷量有关；所述当前制冷量与采集的冷冻水回水温度、采集的冷冻水供水温度、采集的冷冻水流量以及水的比热容有关。
  9. 根据权利要求7所述的冷水机组空调系统，其中，所述控制器被配置为：
    根据确定的所述每台单机头冷水机组的性能模型、采集的蒸发温度和冷凝温度，计算所述每台单机头冷水机组的预测能效比；
    根据所述每台单机头冷水机组的预测能效比和制冷量，确定所述冷水机组的电功率；所述每台单机头冷水机组的制冷量与所述单机头冷水机组的运行负载以及所述冷水机组的当前制冷量相关；
    根据所述电功率和所述冷水机组的当前制冷量，确定所述多机头冷水机组的预测能效比。
  10. 根据权利要求6所述的冷水机组空调系统，其中，采集的运行数据还包括冷冻水供水温度、冷冻水回水温度、冷冻水流量、冷却水进水温度、冷却水出水温度、冷却水流量、所述冷水机组内每台单机头冷水机组的运行功率；所述控制器还被配置为：
    根据所述冷冻水回水温度、所述冷冻水供水温度、所述冷冻水流量以及水的比热容，计算所述冷水机组的当前制冷量；
    根据所述冷却水出水温度、所述冷却水进水温度、所述冷却水流量以及水的比热容，计算所述冷水机组的当前排热量；
    根据所述冷水机组的当前制冷量、所述冷水机组的当前排热量以及所述每台单机头冷水机组的运行功率，计算能量平衡系数；
    若所述能量平衡系数大于预设值，确定采集的运行数据为异常值；
    删除确定为异常值的运行数据。
  11. 根据权利要求2至10中任一项所述的冷水机组空调系统，其中，所述控制器被配置为：
    根据所述冷水机组空调系统的需求冷负荷、所述冷水机组空调系统中开启的冷水机组的数量、以及所述多台冷水机组的额定冷负荷，计算在多个工况下所述每台冷水机组的平均冷负荷率。
  12. 根据权利要求1至11任一项所述的冷水机组空调系统，其中，所述控制器还被配置为：
    在确定所述多台冷水机组的运行状态后，计算所述冷水机组空调系统前一时刻的冷负荷相对于需求冷负荷的负荷变化率；
    若所述负荷变化率达到待开启或待关闭的冷水机组的负荷变化率的上限值，控制所述冷水机组空调系统在确定的运行状态下运行；
    若所述负荷变化率小于待开启或待关闭的冷水机组的负荷变化率的上限值，控制所述冷水机组空调系统在当前的运行状态下继续运行。
  13. 根据权利要求12所述的冷水机组空调系统，其中，所述控制器还被配置为：
    若所述负荷变化率达到所述待开启的冷水机组的负荷变化率的上限值，控制所述待开启的冷水机组开启；
    若所述负荷变化率达到所述待关闭的冷水机组的负荷变化率的上限值，控制所述待关闭的冷水机组关闭；所述待关闭的冷水机组为运行的冷水机组中运行时间最长的冷水机组。
  14. 根据权利要求13所述的冷水机组空调系统，其中，
    所述负荷变化率与所述冷水机组空调系统的所述需求冷负荷、所述冷水机组空调系统的冷负荷以及第一预设时长相关；
    所述待开启的冷水机组的负荷变化率的上限值为所述待开启的冷水机组的额定冷负荷与第二预设时长的比值；
    所述待关闭的冷水机组的负荷变化率的上限值为所述待关闭的冷水机组的额定冷负荷与所述第二预设时长的比值。
  15. 一种冷水机组空调系统的控制方法，所述冷水机组空调系统包括：
    多台冷水机组，所述多台冷水机组共用水路，且所述多台冷水机组的制冷剂流路互相独立，所述多台冷水机组中的每台冷水机组包括：
    至少一个压缩机，且被配置为压缩冷媒以使低压冷媒受压缩形成高压冷媒；
    冷凝器，被配置为将气态冷媒冷凝为液态冷媒，并与冷却水进行热交换；
    节流件，且被配置为控制流经所述节流件的所述冷媒的流量和压力；以及
    蒸发器，被配置为将液态冷媒蒸发为气态冷媒，并与冷冻水进行热交换；所述压缩机、所述冷凝器、所述节流件和所述蒸发器依次连接形成冷媒循环；以及
    控制器，被配置为控制所述多台冷水机组的运行；
    所述方法包括：
    计算在多个工况下所述多台冷水机组中每台冷水机组的平均负荷率；所述多个工况互不相同，且在所述多个工况下所述多台冷水机组的开启数量不同；
    计算在所述多个工况下所述每台冷水机组的蒸发温度和冷凝温度；
    根据所述每台冷水机组的蒸发温度和冷凝温度，计算在所述多个工况下所述每台冷水机组对应的第一权值；所述第一权值与所述蒸发温度和所述冷凝温度之间的温差相关；
    根据预设的所述冷水机组的性能模型、以及在所述多个工况下所述每台冷水机组的蒸发温度和冷凝温度，计算在所述多个工况下所述每台冷水机组的预测能效比；所述性能模型表征性能系数与所述平均冷负荷率和所述第一权值的关系；所述预测能效比与所述性能系数、所述蒸发温度和所述冷凝温度之间存在预设关系；
    根据在所述多个工况下所述每台冷水机组的预测能效比，确定所述多台冷水机组的运行状态；所述冷水机组的运行状态指所述冷水机组开启或关闭；以及
    根据确定的所述多台冷水机组的运行状态，控制所述多台冷水机组的运行。
  16. 根据权利要求15所述的冷水机组空调系统的控制方法，根据确定的所述多台冷水机组的运行状态，控制所述多台冷水机组的运行，包括：
    在确定所述多台冷水机组的运行状态后，计算所述冷水机组空调系统前一时刻的冷负荷相对于需求冷负荷的负荷变化率；
    若所述负荷变化率达到待开启或待关闭的冷水机组的负荷变化率的上限值，控制所述冷水机组空调系统在确定的运行状态下运行；
    若所述负荷变化率小于待开启或待关闭的冷水机组的负荷变化率的上限值，控制所述冷水机组空调系统在当前的运行状态下继续运行。
  17. 根据权利要求16所述的冷水机组空调系统的控制方法，其中，若所述负荷变化率达到待开启或待关闭的冷水机组的负荷变化率的上限值，控制所述冷水机组空调系统在确定的运行状态下运行，包括：
    若所述负荷变化率达到所述待开启的冷水机组的负荷变化率的上限值，控制所述待开启的冷水机组开启；
    若所述负荷变化率达到所述待关闭的冷水机组的负荷变化率的上限值，控制所述待关闭的冷水机组关闭；所述待关闭的冷水机组为运行的冷水机组中运行时间最长的冷水机组。
  18. 根据权利要求15至17中任一项所述的冷水机组空调系统的控制方法，其中，所述计算在多个工况下所述多台冷水机组中每台冷水机组的平均负荷率包括：
    根据所述冷水机组空调系统的需求冷负荷、所述冷水机组空调系统中开启的冷水机组的数量、以 及所述多台冷水机组的额定冷负荷，计算在所述多个工况下所述每台冷水机组的所述平均冷负荷率。
  19. 根据权利要求15至18中任一项所述的冷水机组空调系统的控制方法，其中，所述冷水机组包括单机头冷水机组和多机头冷水机组之一，所述单机头冷水机组包括一个压缩机，所述多机头冷水机组包括多个压缩机，且所述多机头冷水机组由多个单机头冷水机组构成，所述方法还包括：
    采集所述冷水机组的运行数据；所述运行数据包括所述冷水机组中每台单机头冷水机组的蒸发温度、冷凝温度、以及运行负载；
    根据采集的蒸发温度、冷凝温度、运行负载、以及所述每台单机头冷水机组的额定制冷量和能效比，确定所述每台单机头冷水机组的性能模型；
    根据确定的每台单机头冷水机组的性能模型，确定所述多机头冷水机组的性能模型；所述冷水机组的性能模型包括所述单机头冷水机组的性能模型或所述多机头冷水机组的性能模型中的至少一个。
  20. 根据权利要求19所述的冷水机组空调系统的控制方法，根据采集的蒸发温度、冷凝温度、运行负载、以及所述每台单机头冷水机组的额定制冷量和能效比，确定所述每台单机头冷水机组的性能模型，包括：
    根据采集的蒸发温度、冷凝温度以及能效比，计算所述单机头冷水机组的性能系数；
    根据所述单机头冷水机组的所述性能系数、第二权值和负荷率，拟合并确定所述单机头冷水机组的性能系数的关系式；
    其中，所述单机头冷水机组的性能系数的关系式为所述单机头冷水机组的性能模型，所述第二权值与采集的蒸发温度、采集的冷凝温度以及所述单机头冷水机组的冷凝温度和蒸发温度之间的温差相关。
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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106503388A (zh) * 2016-11-09 2017-03-15 东南大学 空调系统特征识别方法
CN106524410A (zh) * 2016-11-07 2017-03-22 深圳市奥宇节能技术股份有限公司 一种中央空调冷水机组实际效率的诊断方法
CN109000948A (zh) * 2018-06-29 2018-12-14 广州能迪能源科技股份有限公司 基于冷水机热力学模型的多台冷水机组节能空间评估方法
CN111442480A (zh) * 2020-04-08 2020-07-24 广东美的暖通设备有限公司 空调设备的运行控制方法和系统、空调设备和存储介质
CN115309056A (zh) * 2022-09-05 2022-11-08 青岛海信日立空调系统有限公司 一种多冷水机组的控制方法
CN115453869A (zh) * 2022-08-31 2022-12-09 青岛海信日立空调系统有限公司 一种多机头磁悬浮冷水机组的建模方法

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106524410A (zh) * 2016-11-07 2017-03-22 深圳市奥宇节能技术股份有限公司 一种中央空调冷水机组实际效率的诊断方法
CN106503388A (zh) * 2016-11-09 2017-03-15 东南大学 空调系统特征识别方法
CN109000948A (zh) * 2018-06-29 2018-12-14 广州能迪能源科技股份有限公司 基于冷水机热力学模型的多台冷水机组节能空间评估方法
CN111442480A (zh) * 2020-04-08 2020-07-24 广东美的暖通设备有限公司 空调设备的运行控制方法和系统、空调设备和存储介质
CN115453869A (zh) * 2022-08-31 2022-12-09 青岛海信日立空调系统有限公司 一种多机头磁悬浮冷水机组的建模方法
CN115309056A (zh) * 2022-09-05 2022-11-08 青岛海信日立空调系统有限公司 一种多冷水机组的控制方法

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