WO2012096265A1 - Système de source de chaleur, procédé de commande associé et programme associé - Google Patents

Système de source de chaleur, procédé de commande associé et programme associé Download PDF

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Publication number
WO2012096265A1
WO2012096265A1 PCT/JP2012/050292 JP2012050292W WO2012096265A1 WO 2012096265 A1 WO2012096265 A1 WO 2012096265A1 JP 2012050292 W JP2012050292 W JP 2012050292W WO 2012096265 A1 WO2012096265 A1 WO 2012096265A1
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Prior art keywords
temperature
heat
heat source
cold
load
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PCT/JP2012/050292
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English (en)
Japanese (ja)
Inventor
宮島　裕二
菊池　宏成
隆成 水島
大島　昇
鈴木　浩二
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株式会社日立プラントテクノロジー
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Priority to SG2013053228A priority Critical patent/SG191930A1/en
Priority to CN2012800049638A priority patent/CN103314266A/zh
Publication of WO2012096265A1 publication Critical patent/WO2012096265A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/06—Several compression cycles arranged in parallel
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P80/00—Climate change mitigation technologies for sector-wide applications
    • Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier

Definitions

  • the present invention relates to a heat source system of a facility that requires cooling such as a building, factory, data center, and district heating / cooling, and more particularly to a heat source system that performs energy saving, a control method thereof, and a program thereof.
  • a heat source system is equipment that manufactures cold water with a refrigerator, circulates cold water through a load-side room or device, and cools the load-side room or device by heat exchange with the load-side air.
  • the refrigerator is controlled with a capacity corresponding to the magnitude of the load as the load increases or decreases. Further, the capacity corresponding to the load may be supplied by increasing or decreasing the number.
  • Cold water is circulated between the load side and the refrigerator by a pump.
  • Patent Document 1 As prior art documents related to the present application, there are the following patent documents 1 and 2.
  • Patent Document 2 describes a method for controlling the operation of a cold heat source machine that can enhance a system COP (Coefficient Of Performance) in consideration of auxiliary equipment such as a cold water pump, a cooling water pump, and a cooling tower.
  • COP Coefficient Of Performance
  • Japanese Patent Laying-Open No. 3854586 paragraphs 0067, 0068, FIG. 3, FIG. 6, etc.
  • Japanese Patent Laid-Open No. 2008-134013 paragraphs 0079 to 0085, FIGS. 9 to 14, etc.
  • FIG. 18 is a diagram showing the relationship between the cooling amount (%) and the COP in the turbo refrigerator. In such an operation state in which the difference in return temperature with respect to the load of cold water is small, as shown in FIG. 18, the COP of the refrigerator is decreased, the flow required for cooling with the load is increased, and the pump power may be increased. is there.
  • an object of the present invention is to provide a heat source system, a control method thereof, and a program thereof that improve the system COP without reducing the operation efficiency of the cold heat source.
  • the heat source system according to any one of claims 1, 2, and 5, wherein the heat medium is at least one of a cold heat source in which the heat medium is cooled and a heat exchanger in which heat is exchanged between the cooled heat medium and a load.
  • a heat source system in which a pump to be fed to the heat source, the cold heat source, and the heat exchanger of the load are connected by piping through which the heat medium flows, and has the following characteristics.
  • the heat source system measures a load heat quantity measuring unit that measures an amount of heat with which the heat medium exchanges heat with the load, and measures a temperature of the heat medium that is exchanged with the load and returns to the cold heat source.
  • the heat source system measures a load heat quantity measuring means for measuring a heat quantity at which the heat medium exchanges heat with the load, and measures a temperature of the heat medium that is exchanged with the load and returned to the cold heat source.
  • Cold water return temperature measuring means, and second control means for changing the temperature set value of the heat medium at the outlet of the cold heat source to a temperature lower than a preset set temperature at the maximum load.
  • the heat source system is a load heat quantity measuring unit that measures an amount of heat that the heat medium exchanges with the load, and cold water that measures a temperature of the heat medium that is exchanged with the load and returns to the cold heat source.
  • the temperature set value of the heat medium to be cooled is increased while the temperature is within the set low temperature determination flow range and the temperature of the heat medium is lower than a predetermined low temperature determination temperature.
  • third control means for lowering the temperature set value of the heat medium.
  • the heat source system control method according to claims 11, 12, and 15 is a control method for performing the heat source system according to claims 1, 2, and 5, respectively.
  • a program for a heat source system is a program for causing a computer to execute the control method for a heat source system according to any one of the eleventh, twelfth and fifteenth aspects.
  • FIG. 1 It is a lineblock diagram of the heat source system of Embodiment 1 concerning the present invention.
  • (a) is a figure which shows the operation example of the refrigerator of 2 units
  • (b) is one cold source when a cold water exit temperature is 5.5 degreeC
  • FIG. 1 is a figure which shows the operation example of the refrigerator of 2 units
  • (b) is one cold source when a cold water exit temperature is 5.5 degreeC
  • FIG. 2 It is a block diagram of the heat source system of Embodiment 2. It is a figure which shows the control flow of the control method of the heat source system of Embodiment 2.
  • FIG. It is a figure which shows the electric power of the (cold water) pump with respect to the cold water supply temperature (cold heat source outlet temperature), the electric power of the refrigerator of the cold heat source, and the total power consumption.
  • (a) is a figure which shows the whole process with respect to the flow of the apparatus characteristic of a pump
  • (b) is a figure which shows the pump electric power with respect to a flow
  • (c) is a figure which shows the relationship between a flow and piping resistance. It is a block diagram of the heat source system of Embodiment 6. It is a figure which shows the relationship between the amount of cooling (%) in a turbo refrigerator, and COP.
  • the heat source system N (N1 to N5) according to the embodiment of the present invention is a heat source system that performs cooling of facilities such as buildings, factories, data centers, and district heating and cooling.
  • FIG. 1 is a configuration diagram of a heat source system N1 according to the first embodiment of the present invention.
  • the heat source system N1 of the first embodiment includes one or two or more cold heat sources R (R1, R2) that cool the heat medium water to provide cold water having a desired temperature, cold water sent from the cold heat source R, There is a load 1 (1a,%) (Air in the facility to be cooled) that is heat-exchanged by a heat exchanger (not shown).
  • the heat source system N1 includes a cold water pump P (P1, P2) provided on the primary side where the cold heat source R is provided and circulates water of the heat medium to each cold heat source R, and a load provided on the secondary side where the load 1 is provided.
  • P cold water pump
  • a pump P3 P3a, P3b,...) That sends chilled water produced by the cold heat source R, heat exchange with the low temperature side tank 5A and the load 1 in which the chilled water produced by the cold heat source R is stored.
  • the water tank 5 having the high temperature side tank 5B in which the heated water is stored, and the arithmetic unit 2 responsible for controlling the heat source system N1 are provided.
  • the cold water pump P and the pump P3 are each rated.
  • the computing unit 2 is a controller such as a PLC (programmable logic controller).
  • the heat source system N1 is controlled by executing a program stored in the memory of the controller.
  • the cold water cooled by the cold heat source R (R1, R2) is sent and stored in the low temperature side tank 5A of the water tank 5 via the cold water systems r1, r2 by the cold water pumps P (P1, P2), respectively.
  • Cold water stored in the low temperature side tank 5A of the water tank 5 is sent to each load 1 (1a,%) by a secondary side pump P3 (P3a, P3b,).
  • the cold water heated by the heat exchange with the load 1 (1a,...) Is sent to the high temperature side tank 5B of the water tank 5 by the secondary pump P3 and stored.
  • the cold water in the high temperature side tank 5B of the water tank 5 is sent to the cold heat source R (R1, R2) by the primary side cold water pump P (P1, P2), cooled again, and sent to the low temperature side tank 5A of the water tank 5.
  • the heat source system N1 changes the flow rate (cold water flow rate) of cold water that exchanges heat with the load 1 (1a, 1b,...) And the heat exchanger (not shown) and returns to the cold heat source R.
  • a flow sensor 3 for measuring (measuring) and a temperature sensor 4 for measuring the temperature of the refluxed cold water (cold water return temperature) are provided.
  • the flow rate sensor 3 and the temperature sensor 4 respectively measure the flow rate (cold water flow rate) and temperature (cold water return temperature) of the chilled water sent from the cold heat source R (R1, R2) and heat-exchanged with the load 1 and heated. .
  • the cold heat source R is a cold water production heat source system using a refrigerator such as a turbo refrigerator or an absorption refrigerator, an open cooling tower, or a closed cooling tower.
  • the cold heat source R (R1, R2) is, for example, a refrigerator capable of controlling the temperature of the cold water at the outlet of the cold heat source R cooled by the cold heat source R (cold water outlet temperature) to be constant,
  • the set value of the R cold water outlet temperature (outward temperature) can be changed.
  • the cold water outlet temperature of the cold heat source R can be set at a lower temperature than the set temperature supplied to the load 1.
  • Control of the secondary side pump P3 (P3a, P3b,...) May be flow rate control such as constant control of cold water pressure or optimized flow rate control.
  • the equipment configuration of the heat source system N1 includes, for example, a plurality of refrigerators of the cold heat source R, and the cold water is supplied at a constant flow rate by the primary cold water pump P and the secondary pump P3 that are rated. Is done.
  • FIG. 2 is an example of an operating state when the temperature of the chilled water Rt of the refrigerator Rt is lowered.
  • FIG. 2A shows the operation of the refrigerators Rt of the two chilled heat sources R when the temperature of the chilled water outlet is 7 ° C. An example is shown, and (b) shows an example of operation of the refrigerator Rt of one cold heat source R when the cold water outlet temperature is 5.5 ° C.
  • FIG. 3 shows the cooling load factor (%) and coefficient of performance (COP) ratio (%) per unit when the chilled water outlet temperature of the chiller Rt of the cold heat source R is 5.5 ° C. and 7 ° C. A graph is shown.
  • the cold water inlet temperature 8.5 ° C. and the cold water outlet temperature 7 ° C. (see FIG. 3) of the temperatures entering the refrigerators Rt 1 and Rt 2 as the cold heat sources R 1 and R 2 are as follows.
  • two units are operated at a load factor of 30% for each of the refrigerators Rt1 and Rt2 of the cold heat source R1 and a load factor of 60% in total of the cold heat source R1.
  • the refrigerator Rt2 stops operating, the cold water outlet temperature of the refrigerator Rt1 of the cold heat source R1 is 5.5 ° C., and the cold water inlet temperature is 8.5 ° C.
  • the cold source R1 may be the refrigerator Rt1
  • the cold source R2 may be the refrigerator Rt2.
  • the load factor of 100% in FIG. 3 is an example in which the temperature difference between the cold water inlet and the cold water outlet of the cold heat source R is 5 ° C. in the operation of the two refrigerators Rt1 and Rt2 having the rated flow rate.
  • the cooling water pump that sends the cooling water from the cooling tower and the cooling tower is omitted but is operated in conjunction with the refrigerators Rt1 and Rt2 of the cold heat source R.
  • the number of operating cold heat sources R decreases by lowering the cold water outlet temperature of the cold heat sources R. That is, the operations of the refrigerators Rt1 and Rt2 are the operations of only the refrigerator Rt1, and the COP (coefficient of performance) ratio is improved.
  • the turbo chiller may be an inverter turbo chiller, and the COP of the chiller becomes harder than that of a constant speed turbo chiller.
  • the hot water outlet temperature is increased to increase the load factor of the heat pump type heat source, thereby increasing the COP operation.
  • the system COP of the heat source system is operated at a high level, and the power consumption is reduced.
  • a control method of the heat source system N1 will be described with reference to FIG. 4 showing a control flow.
  • the control of the heat source system N1 shown in FIG. 4 is performed by the computing unit 2 at an arbitrary time interval such as a predetermined time interval, for example, a 5-minute interval, an 1-hour interval by measuring time using a timer.
  • a predetermined time interval for example, a 5-minute interval, an 1-hour interval by measuring time using a timer.
  • the flow rate (cold water flow rate) and temperature (cold water return temperature) of the chilled water recirculated by exchanging heat with the load 1 (1a,... ) Respectively.
  • the temperature information (cold water forward temperature) of the cold water in the forward path from the cold heat source R to the load 1 is acquired from the temperature control of the cold water of the cold heat source R.
  • the load 1 and the heat are determined by the difference between the temperature of the cold water in the return path exchanged with the load 1 measured by the temperature sensor 4 and the temperature of the cool water in the outbound path from the cold heat source R and the flow rate of the cold water measured by the flow sensor 3. Calculate the amount of heat exchanged.
  • the chilled water temperature of the outgoing path from the cold heat source R is measured by providing a temperature sensor on the low temperature side tank 5A of the water tank 5 or the secondary side pipe entering the load 1, or obtained from the cooling control at the cold heat source R. May be.
  • the process proceeds to S105, and the current set value of the chilled water temperature of the outgoing path from the cold heat source R is maintained (S105). .
  • the process proceeds to S106 and exits from the cold heat source R. Increase the temperature setting value of the outgoing cold water by a predetermined amount.
  • the temperature is raised at a width of 0.5 ° C., 1 ° C., or the like.
  • the temperature range for increasing the temperature can be arbitrarily set as appropriate in each heat source system.
  • the temperature to be increased is periodically changed, for example, to 0.5 ° C.
  • the temperature for low temperature determination is, for example, 8 ° C. when it is smaller than the design value at the maximum load, for example, when the cold water going temperature is 6 ° C. and the cold water returning temperature is 11 ° C.
  • the temperature for low temperature determination is the temperature of cold water, it has a width of 8 ° C. ⁇ ⁇ ° C.
  • the temperature for low temperature determination may be determined without a width as in 8 ° C., but it is more desirable to have a width as 8 ° C. ⁇ ⁇ ° C. because the control is stable and practical. .
  • the temperature for low temperature determination can be arbitrarily set according to the applied heat source system.
  • the temperature of the chilled water (cool water return temperature) that is refluxed by exchanging heat with the load 1 (1a, ...) is determined to be low. It is determined whether the temperature is equal to the service temperature (S104). When it is determined that the temperature of the chilled water recirculated by heat exchange with the load 1 (1a,%) (The chilled water return temperature) is equal to the temperature for low temperature determination (Yes in S104), the process proceeds to S105, and the cold heat source Maintain the current set value of the chilled water temperature of the outbound route from R.
  • the set value of the chilled water temperature of the outgoing path from the cold heat source R (R1, R2) is not the minimum value of the unique set temperature determined by the equipment of the cold heat source R (No in S107). Then, the set value of the chilled water temperature of the outgoing path from the cold heat source R is lowered to a predetermined value, for example, a range of 0.5 ° C., 1 ° C. or the like. The temperature to be lowered is periodically changed, for example, to 0.5 ° C. (S108). At this time, the temperature setting value of the chilled water at the outlet (outward path) of the cooling heat source R may be changed to a lower temperature than the preset temperature at the maximum load.
  • a predetermined value for example, a range of 0.5 ° C., 1 ° C. or the like.
  • the temperature to be lowered is periodically changed, for example, to 0.5 ° C. (S108).
  • the temperature setting value of the chilled water at the outlet (outward path) of the cooling heat source R may
  • the cold load on the secondary side becomes the minimum flow rate and the cooling load becomes the minimum number of operating units (for example, one) of the cold heat source R at low load
  • the cold water flow rate is not reduced, and the power of the cold water pump P and the pump P3 cannot be reduced. Therefore, when the load is low, the temperature of the cold heat source R is maintained at the minimum flow rate without lowering the temperature of the cold water. Thereby, it can prevent that a coefficient of performance (COP) falls by low temperature of the cold-water exit temperature of the refrigerator Rt which is the cold-heat source R.
  • COP coefficient of performance
  • the features of the heat source system N1 of the first embodiment are as follows.
  • the cold water supply temperature (the cold heat source of the cold water cooled by the cold heat source R) R outlet temperature) is lowered to increase the temperature difference between the cold water return temperature and the cold water feed temperature.
  • the cold water supply temperature and the cold water feed temperature are the same or substantially the same temperature.
  • the chiller Rt and Rt2 of the cold heat source R whose efficiency decreases when the cold water temperature becomes low, the cold water is lowered to prevent the temperature difference from becoming small, and the cold heat source R due to an increase in the number of operating units. It is possible to prevent the COP of the refrigerators Rt1 and Rt2 from being lowered and to increase the efficiency of the entire system.
  • FIG. 5 is a configuration diagram of the heat source system N2 according to the second embodiment of the present invention.
  • the heat source system N2 of the second embodiment includes one or two or more cold heat sources R (R1, R2) that cool water of the heat medium to produce cold water having a desired temperature, and cold water and heat sent from the cold heat source R.
  • loads 1 (1a, 1b,...) That exchange heat with an exchanger (not shown).
  • FIG. 5 the bypass path between the return headers is omitted.
  • the heat source system N2 is an arithmetic unit 2 responsible for controlling the inverter-controlled cold water pumps P (P1, P2) that circulate cold water to the cold heat sources R and the heat source system N2 (cold heat source R, cold water pump P, etc.). And.
  • the computing unit 2 is a controller such as a PLC (programmable logic controller).
  • the heat source system N2 is controlled by executing a program stored in the memory of the controller.
  • Each cold water produced by the cold heat source R (R1, R2) is supplied from the cold heat source R (R1, R2) through the cold water system r1, r2 by the cold water pump P (P1, P2) to load 1 (1a, 1b, ...) side.
  • the heat source system N2 is a sensor for measuring the physical quantity, and a flow rate of cooling water (cooling water flow rate) that exchanges heat with the load 1 (1a, 1b,...) And a heat exchanger (not shown) and returns to the cooling heat source R. And a temperature sensor 4 for measuring the temperature of the refluxed cooling water (cooling water return temperature).
  • the heat source system N2 is supplied from the cold heat source R (R1, R2), exchanges heat between the load 1 and the heat exchanger (not shown), and is heated (cool water return temperature) and flow rate (cold water flow rate). ) Can be measured by the temperature sensor 4 and the flow rate sensor 3, respectively.
  • the cold heat source R is a cold water production facility using a refrigerator such as a turbo refrigerator or an absorption refrigerator, an open cooling tower, or a closed cooling tower.
  • the cold heat source R (R1, R2) is, for example, a refrigerator capable of controlling the cold water supply temperature (the temperature at the outlet of the cold water source R cooled by the cold heat source R) to be constant, The set value of the R cold water supply temperature can be changed.
  • the outlet temperature of the refrigerator that is the cold heat source R (the temperature of the cold water at the outlet of the cold heat source R) can be set to a low temperature with respect to the set temperature designed to be supplied to the load.
  • the control of the chilled water pump P may be flow rate control such as constant control of the chilled water pressure or optimized flow rate control.
  • Control of the heat source system N2 shown in FIG. 6 is performed by the computing unit 2 at an arbitrary time interval such as a predetermined time interval such as a 5-minute interval by measuring time using a timer.
  • the flow rate of cold water (flow rate of cold water) and the temperature (cooling water return temperature) which are refluxed by exchanging heat with the load 1 (1a,... measure.
  • the temperature information (cold water forward temperature) of the cold water from the cold heat source R to the load 1 is acquired from the temperature control of the cold water of the cold heat source R, or a temperature sensor is provided in the pipeline of the cold water to the load 1 measure.
  • FIG. 7 is a diagram showing the power of the (cold water) pump P, the power of the refrigerator of the cold heat source R, and the total power consumption with respect to the cold water supply temperature (the temperature of the cold water at the outlet of the cold heat source R).
  • the outlet temperature of the cold heat source R is high (the flow rate of the cold water pump P is large because the amount of heat exchange is small) and when the outlet temperature of the cold heat source R is low (the heat exchange amount is large, the cold water pump P If the flow rate is small), the power consumption will increase.
  • the flow rate (cold water flow rate) of the chilled water exchanged with the load 1 (1a, 1b,...) Detected by the flow rate sensor 3 is a predetermined high temperature determination flow rate range of the chilled water temperature (the flow rate is too small). It is determined whether it is within the range. If it is determined in S202 that the flow rate of the chilled water that exchanges heat with the load 1 (the chilled water flow rate) is within the predetermined high temperature determination flow rate range (the range of the flow rate that is too small) (Yes in S202), It is determined whether or not the current set value of the cold water temperature of the outgoing path from the source R is the maximum set temperature determined by the equipment of the cold heat source R (S204).
  • the current temperature setting of the cold water from the cold heat source R is set. The value is maintained (S205).
  • the temperature setting of the outgoing cold water coming out of the cold heat source R Increase the value by a predetermined amount. For example, the temperature is raised at a width of 0.5 ° C., 1 ° C., or the like.
  • the temperature range for increasing the temperature can be arbitrarily set as appropriate in each heat source system. The temperature to be increased is periodically changed, for example, to 0.5 ° C. (S206).
  • the process proceeds to S207, where it is determined whether or not the temperature of the flow returning from the load 1 is lower than a predetermined predetermined temperature reduction determination temperature.
  • the temperature for low temperature determination is, for example, 8 ° C. when it is smaller than the design value at the maximum load, for example, when the cold water going temperature is 6 ° C. and the cold water returning temperature is 11 ° C.
  • the temperature for low temperature determination is given a width of 8 ° C. ⁇ 0.5 ° C.
  • the temperature for determining whether to lower the temperature may be determined without providing a width, such as 8 ° C.
  • a width such as 8 ° C. ⁇ 0.5 ° C.
  • the control is more stable and practical. More desirable.
  • the temperature for low temperature determination can be arbitrarily set according to the heat source system.
  • the temperature to be lowered is periodically changed, for example, to 0.5 ° C. (S210).
  • the temperature setting value of the chilled water at the outlet (outward path) of the cooling heat source R may be changed to a lower temperature than the preset temperature at the maximum load.
  • the heat source system N2 of Embodiment 2 uses a refrigerator that can set the cold water temperature of the refrigerator that is the cold heat source R to a temperature lower than the initial set temperature, the measured values of the cold water flow rate and the cold water return temperature are obtained. It is possible to lower the cold water outlet temperature of the refrigerator of the cold heat source R by using it. For example, since the temperature of the outlet of the cold heat source R can be lowered so that the cold water pump P has a rated flow rate, the number of operating cold water pumps P can be reduced. Therefore, the cold heat source R can be operated with high efficiency, the flow rate of cold water can be reduced, and the COP of the heat source system N2 can be improved.
  • FIG. 8 is a configuration diagram of the heat source system N3 according to the third embodiment of the present invention.
  • the heat source system N3 of the third embodiment is obtained by connecting an arbitrary number of cold heat sources R (Ra, Rb,%) In series in the heat source system N2 of the second embodiment.
  • the cold heat sources R (Ra, Rb,...) are connected in series, one cold water system r1 is used, and one inverter-controlled pump P1 is used.
  • the cold heat sources R they are a high temperature side cold heat source Ra and a low temperature side cold heat source Rb.
  • the refrigerator (Ra) on the high temperature side (for example, 16 ° C. is cooled to 11 ° C. at the maximum load) and the low temperature side (for example, 11 ° C. at the maximum load are cooled to 6 ° C.) ) Refrigerator (Rb) connected in series.
  • FIG. 8 illustrates the case where two cold heat sources R (Ra, Rb) are connected in series, any number of cold heat sources R can be connected in series.
  • the refrigerator of the high temperature side cold heat source Ra and the refrigerator of the low temperature side cold heat source Rb can be set to a temperature lower than the temperature set value at the maximum load.
  • the other structure is the same as that of the heat source system N2 of Embodiment 2, detailed description is abbreviate
  • the control of the heat source system N3 shown in FIG. 9 is performed at an arbitrary predetermined time interval by measuring time using a timer in the computing unit 2. For example, it is performed at an arbitrary time interval such as an interval of 5 minutes and an interval of 1 hour.
  • the chilled water outlet temperature of the refrigerator which is the high temperature side / low temperature side cold heat source Ra, Rb, is set according to the measured value of the chilled water return temperature measured by the temperature sensor 4 and the chilled water flow rate measured by the flow sensor 3. Each value can be lowered.
  • S (step) 301 of FIG. 9 cold water that is refluxed by exchanging heat with the load 1 (1a, 1b,...) And the heat exchanger (not shown) with the flow sensor 3 and the temperature sensor 4 shown in FIG. Measure the flow rate (cold water flow rate) and temperature (cold water return temperature).
  • the chilled water temperature of the forward path to the load 1 (1a, 1b,%) Is acquired from the temperature control of the chilled water cooled by the high temperature side / low temperature side cold heat sources Ra, Rb, or to the load 1 (1a, 1b,). Measured by a temperature sensor (not shown) provided on the forward path side.
  • the amount of heat exchanged with the load is calculated from the difference between the cold water temperature in the return path measured by the temperature sensor 4 and the cold water temperature in the forward path from the low temperature side cold heat source Rb.
  • S302 it is checked whether the flow rate of the cold water flowing for heat exchange with the load 1 (1a, 1b,9) Is too small using the high temperature determination flow range, while in S303, the low temperature determination flow range. Is used to check whether the flow rate of cold water flowing to exchange heat with the load 1 is too large.
  • the flow rate of cold water (cold water flow rate) flowing through heat exchange with the load 1 detected by the flow rate sensor 3 is within a predetermined high temperature determination flow rate range (range of flow rate too small) of the cold water temperature. It is determined whether or not.
  • the flow rate of cold water flowing through heat exchange between the load 1 and a heat exchanger (not shown) (cold water flow rate) is within a predetermined high temperature determination flow rate range (a range of flow rate that is too small) of the cold water temperature.
  • the set value of the current chilled water temperature of the outgoing path from the high temperature side / low temperature side cold heat source Ra, Rb is determined by the equipment of each cold heat source R (Ra, Rb) It is determined whether it is the highest value (S304).
  • Rb is the maximum value of the set temperature determined by the equipment of each cold heat source R (Ra, Rb) (S304 in FIG. 6) In Yes), the current set values of the chilled water temperatures of the respective outgoing paths from the high temperature side and low temperature side cooling heat sources Ra and Rb are maintained (S305). On the other hand, when it is determined that the set value of the chilled water temperature of the outgoing path from the high temperature side / low temperature side cold heat source Ra, Rb is not the maximum value of the set temperature determined by the equipment of each cold heat source R (Ra, Rb) (FIG.
  • the set value of the chilled water temperature in the outgoing path from the high temperature side / low temperature side cold heat sources Ra, Rb is increased by a predetermined amount (S306).
  • the temperature is raised at a width of 0.5 ° C., 1 ° C., or the like.
  • the temperature range for increasing the temperature can be arbitrarily set as appropriate in each heat source system.
  • the temperature to be increased is periodically changed, for example, to 0.5 ° C.
  • the flow rate of cold water (cold water flow rate) flowing through heat exchange with the load 1 (1a,...) Is not within the predetermined high temperature determination flow rate range (the range of flow rate too small) of the cold water temperature.
  • the flow rate of cold water (cold water flow rate) flowing through heat exchange with the load 1 detected by the flow rate sensor 3 is a low temperature determination flow rate of a predetermined cold water temperature. It is determined whether it is within the range (the range of the flow rate that is too large).
  • the flow rate of cold water (cold water flow rate) flowing through heat exchange with the load 1 detected by the flow rate sensor 3 is within a predetermined low temperature determination flow rate range (range of flow rate that is too large). Is determined (Yes in S303 in FIG. 9), it is determined whether or not the temperature of the chilled water returned by heat exchange with the load 1 is lower than a predetermined predetermined temperature reduction determination temperature (S307). ).
  • the temperature for low temperature determination is smaller than the design value at the maximum load, for example, when the temperature of the chilled water coming out from the low temperature side heat source Rb is 5 ° C. (6 ° C.) and the temperature of the chilled water returning to the high temperature side cold heat source Ra is 15 ° C.
  • the temperature for low temperature determination is, for example, 12 ° C. (8 ° C.).
  • the temperature for low temperature determination is given a width such as 12 ° C. ⁇ 0.5 ° C.
  • the temperature for low temperature determination may be determined without a width such as 12 ° C. (8 ° C.), but the control is more stable when a width such as 12 ° C. ⁇ 0.5 ° C. is provided. More desirable.
  • the temperature for low temperature determination can be arbitrarily set according to the heat source system.
  • the set value of the chilled water temperature of the outgoing path from the high temperature side / low temperature side cold heat sources Ra, Rb is not the minimum value of the specific set temperature determined by the equipment of the high temperature side / low temperature side cold heat sources Ra, Rb. If this is the case (No in S309), the set value of the cold water temperature of the high temperature side / low temperature side cold heat sources Ra, Rb is lowered to a predetermined value, for example, 0.5 ° C., 1 ° C., etc. (S310). The temperature to be lowered is periodically changed to 0.5 ° C., for example.
  • the temperature setting value of the chilled water at the outlets (outward paths) of the cooling heat sources Ra and Rb may be changed to a lower temperature than a preset setting temperature at the maximum load.
  • the cold heat source R can be operated with high efficiency by controlling the cold water outlet temperature of the cold heat source R to be low.
  • the flow rate of cold water can be reduced, and the COP of the heat source system N3 can be improved.
  • FIG. 10 is a configuration diagram of a heat source system N4 according to Embodiment 4 of the present invention.
  • the heat source system N4 of the fourth embodiment is the same as the heat source system N2 of the second embodiment in that the number of two or more cold heat sources R (R1, R2,. (See Handbook, Japan Air Conditioning and Sanitary Engineering Association, see pages 632 to 635).
  • the increase / decrease stage of the two or more cold heat sources R Measures the cold water return temperature returned to the cold heat source R so as to be performed by the calculator 2 at the flow rate and the load amount of the cold water. That is, the temperature of the chilled water discharged from the chilled heat source R is acquired from the control of the chilled heat source R or the temperature sensor 14, and the temperature sensor 4 measures the temperature of the chilled water returned by exchanging heat with the load 1 (1 a, 1 b,.
  • the flow rate sensor 3 measures the flow rate of cold water flowing through heat exchange between the load 1 and a heat exchanger (not shown). Then, the amount of heat consumed by heat exchange with the load 1 is calculated by the calculator 2 from the temperature difference and the flow rate of cold water flowing through heat exchange with the load 1.
  • the operation start / stop of the refrigerator that is the cold heat source R (R1, R2,%) Is operated / stopped of the refrigerator of the cold heat source R and the cold water pump P (P1, P2,. I do.
  • the chilled water pump P (P1, P2,%) May be controlled by constant flow control or variable flow control by pressure control.
  • the structure of the other heat source system N4 is the same as that of the heat source system N2 of Embodiment 2, detailed description is abbreviate
  • the cooling heat source R that is a heat source machine has the maximum capacity at the setting (design) flow rate and setting (design) temperature of each cooling heat source R (inlet cold water temperature, outlet cold water temperature). Is output, and the number control for increasing / decreasing the number of the cooling heat sources R is performed based on the value.
  • the number control of the cold heat source R is controlled based on the upper and lower limits of the cooling amount and the cold water flow rate. Since S401 to S410 of FIG. 11 of the control method of the heat source system N4 are the same as S201 to S210 of FIG. 6 of the control method of the heat source system N2, detailed description is omitted.
  • FIG. 12 is a diagram showing the COP with respect to the cooling amount (%) of the outlet temperature of the refrigerator of the cold heat source R (cold water supply temperature). Therefore, it is possible to prevent the number of cold heat sources R (R1, R2,%) From increasing, and to reduce the total power of the heat source system N4 as shown in FIGS.
  • FIG. 13 shows the power of the (cold water) pump P with respect to the chilled water supply temperature (the temperature of the chilled water that exits the cold heat source R) when the number of the chilled heat sources R (R1, R2,9) Is controlled at a constant flow rate.
  • the relationship between the power of the refrigerator of the source R and the total power is shown. Further, by controlling the number of the cooling heat sources R, it is possible to operate with the number of the flow rate more suitable for the load 1 side.
  • FIG. 14 is a diagram showing the relationship between the flow rate and power when each unit (chilled water) pump P performs constant flow rate control or variable flow rate (inverter control). Furthermore, as shown in FIG. 14, when each chilled water pump P is controlled at a constant flow rate by controlling the number of units, the power of the chilled water pump is increased in a stepped manner with a solid line such as one unit, two units, three units,. However, by performing variable flow rate (inverter control) for each pump P, the pump power in the shaded area can be reduced to save energy.
  • variable flow rate inverter control
  • FIG. 15 is a configuration diagram of the heat source system N5 of the fifth embodiment.
  • the heat source system N5 of the fifth embodiment is a facility having a cold water tank that enables the cold water production by the cold heat source R (R1, R2) to be switched by the computing unit 52.
  • the heat source system N5 includes a cold heat source R (R1, R2) and a cooling tower Ry as equipment for producing cold water for cooling the load 51 (51a,...), And cold water production is performed by the cold heat source R.
  • the heat source system N5 on the primary side, cold water pumps P51a and P51b of rated operation that flow water returned from the load 51 to the cold heat sources R1 and R2, respectively, and the cooling water cooled by the cooling tower Ry are supplied to the cooling water system t1.
  • the heat source system N5 is a water tank 55 having a low temperature side tank 55A in which cold water cooled by the cold heat source R is stored, and a high temperature side tank 55B in which cold water heated by exchanging heat with the load 51 is stored. Is provided.
  • the cold water sent to the cold heat source R (R1, R2) is sent to the low temperature side tank 55A of the water tank 55 through the cold water systems t2, t3, respectively.
  • a pump P53 (53a, 53a, 53a, etc.) that is rated for operating the cold water cooled by the cold heat source R and stored in the low temperature side tank 55A of the water tank 55 to each load 51 (51a,). 53b, ...) are provided.
  • pressure control of the forward header on the secondary side is omitted.
  • the cold water may be returned to the water tank so that the discharge pressure of the pump becomes constant.
  • the heat source system N5 As a sensor, heat is exchanged with a load 51 (51a,%) And a heat exchanger (not shown), and the temperature of the water returned to the cold heat source R on the primary side of the water tank 55 is measured. It has a temperature sensor 54 and a flow rate sensor 53 that measures the flow rate of water returned to the cold heat source R.
  • the heat source system N5 includes an arithmetic unit 52 such as a controller as a control unit that controls the heat source system N5.
  • the computing unit 52 receives detection information from the temperature sensor 54, the flow sensor 53, and the like, and outputs a control signal to a device such as the cold heat source R.
  • the calculator 52 controls the number of the cooling heat source R and the cooling tower Ry. Although the number control of the cooling heat source R and the cooling tower Ry may not be performed, it is desirable to perform the number control because the efficiency of the heat source system N5 is increased.
  • the operation switching by the calculator 52 is performed by optimizing the operation state in which the energy consumption is minimized based on conditions such as the load 51.
  • the energy consumption is calculated by setting equipment characteristics and piping resistances such as the cold water pump P51, the cooling water pump P52, the pump P53, and the cold heat source R, and the cold heat source R, the cold water pump P51, the cooling water pump P52, the pump P53, and the like.
  • a simulator that can calculate electric power from operating conditions is used.
  • the device characteristics of the chilled water pump P51, the chilled water pump P52, and the pump P53 include a flow rate Q—total stroke (FIG. 16A) and a flow rate Q—pump power (FIG. 16B).
  • FIG. 16C shows the relationship between the flow rate Q and the pipe resistance.
  • the heat source system N5 has a cold water flow temperature (cool water flow temperature) cooled by the cold heat source R and stored in the low temperature side tank 55A of the water tank 55, a cold water flow rate measured by the flow sensor 53, and a temperature.
  • the cold water return temperature (cold water return temperature) measured by the sensor 54 is used.
  • the going-out temperature of the cold water stored in the low temperature side tank 55 ⁇ / b> A is acquired by controlling the cooling of the cold heat source R, or the temperature of the outgoing cold water provided on the load 51 side or stored in the low temperature side tank 55 ⁇ / b> A of the water tank 55. It is measured by a forward temperature sensor (not shown) that measures the temperature of the cold water.
  • the cold heat source R Reduce the chilled water outlet temperature setting for systems that contain At this time, the temperature setting value of the chilled water outlet (outward path) of the system including the chilling heat source R may be changed to a temperature lower than the preset temperature at the maximum load.
  • the temperature difference between the cold water flow temperature (cold water flow temperature) to the load 51 (51a,...) And the return temperature (cold water return temperature) is close to the design value (set value)
  • the chilled water flow rate is small. Control to maintain the state. Control for reducing the number of operating units without performing control for reducing the number of operating cooling towers Ry and cooling heat sources R with sufficient margin to prevent hunting by predicting the cooling load with a known load predicting means. May be incorporated.
  • the temperature measurement of the cold water outlet from the cold heat source R may be installed in the cold water forward piping system, or the temperature may be acquired by controlling the cold heat source R. It is possible to cope with the case where there is no temperature output.
  • FIG. 17 is a configuration diagram of a heat source system N6 of the sixth embodiment.
  • the heat source system N6 of the sixth embodiment is a facility that enables cold water production by the refrigerator Rt (Rt1, Rt2).
  • the heat source system N6 is a refrigerator that produces cold water for cooling the load 61 (61a,). Rt is provided, and cold water production is performed by the refrigerator Rt.
  • the heat source system N6 cools the cooling water cooled by the cooling towers Ry and the chilled water pumps P61a and P61b that flow the returned water through the load 61 and the heat exchanger (not shown) to the refrigerators Rt1 and Rt2, respectively. Cooling water pumps P62a and P62b that flow to the refrigerators Rt1 and Rt2 via the water system t1 are provided.
  • the cold water pumps P61a and P61b and the cooling water pumps P62a and P62b of the sixth embodiment are inverter controlled. Further, unlike the heat source system N5 of the fifth embodiment, no water tank is provided.
  • the heat source system N6 includes, as sensors, a forward temperature sensor 64a that measures the temperature of cold water cooled by the refrigerator Rt and sent to the load 61 through the cold water systems t2 and t3, and the load 61 (61a,...) And heat A return temperature sensor 64b that measures the temperature of water returned to the refrigerator Rt by exchanging heat with an exchanger (not shown), a flow rate sensor 63 that measures the flow rate of cold water returned to the refrigerator Rt, and measures the temperature of the outside air An outside air temperature sensor 64c that measures the humidity of the outside air.
  • the heat source system N6 includes a calculator 62 such as a controller as a control unit that controls the heat source system N6.
  • the calculator 62 receives detection information from the forward temperature sensor 64a, the return temperature sensor 64b, the flow rate sensor 63, the outside air temperature sensor 64c, the humidity sensor 65, and the like, while the refrigerator Rt, the cooling tower Ry, the cold water pump P61, Control signals are output to the water pump P62, the pump P63, and the like.
  • the calculator 62 in the heat source system N6 controls the number of refrigerators Rt and cooling towers Ry. Note that the number of refrigerators Rt and cooling towers Ry need not be controlled, but it is desirable to perform the number control because the system COP of the heat source system N6 becomes higher.
  • the operation switching by the calculator 62 is performed by optimizing the operation state in which the energy consumption is minimized based on the conditions of the outside air / load 61.
  • the energy consumption is calculated by setting equipment characteristics and piping resistance such as the cold water pump P61, the cooling water pump P62, the pump P63, the refrigerator Rt, the cooling tower Ry, the refrigerator Rt, the cooling tower Ry, the cold water pump P61, the cooling A simulator capable of calculating the power of the water pump P62, the pump P63, and the cooling tower fan from the operating conditions is used.
  • the device characteristics of the chilled water pump P61, the chilled water pump P62, and the pump P63 include a flow rate Q—total stroke (FIG. 16 (a)) and a flow rate Q—pump power (FIG. 16 (b)).
  • the equipment characteristics of the refrigerator Rt include equipment characteristics such as how much power is generated by the inlet / outlet temperature difference and the cooling amount (see FIG. 12).
  • the equipment characteristics of the cooling tower Ry include equipment characteristics of flow rate-cooling amount-electric power.
  • the heat source system N6 has a cold water forward temperature (cold water forward temperature) measured by the forward temperature sensor 64a, a cold water flow rate measured by the flow sensor 63, and a cold water measured by the return temperature sensor 64b.
  • the return temperature (cold water return temperature) is used. Then, when the temperature difference between the cold water forward temperature (cold water forward temperature) measured by the forward temperature sensor 64a and the cold water return temperature (cold water return temperature) measured by the return temperature sensor 64b is small and the chilled water flow rate is large, The temperature setting of the chilled water outlet of each of the heat source devices, such as the refrigerator Rt and the cooling tower Ry, and the system including the refrigerator Rt and the cooling tower Ry is lowered.
  • the temperature setting value of the chilled water outlet (outward path) of the chiller Rt, the cooling tower Ry, the chiller Rt, and the system including the cooling tower Ry of each heat source device is higher than the preset set temperature at the maximum load. May be changed to low temperature.
  • the temperature difference between the cold water flow temperature (cold water flow temperature) and the return temperature (cold water return temperature) to the load 61 (61a,...) Is close to the design value and the cold water flow rate is small, the state is maintained. Take control.
  • the cooling load prediction may be performed by a known load prediction unit, and the control for reducing the stage based on the prediction result may be incorporated without performing the control for reducing the number of operating units with a margin to prevent hunting.
  • the temperature measurement of the chilled water outlet from the refrigerator Rt may be installed in the chilled water outgoing piping system as shown by the outgoing temperature sensor 64a in FIG. 17, or may be obtained from the temperature control of the water supply side refrigerator Rt. It is also possible to cope with the case where there is no temperature output of the refrigerator Rt.
  • the refrigerator Rt may be an inverter-controlled turbo refrigerator, and energy saving of a partial load can be achieved by inverter control.
  • the forward temperature of the chilled water toward the load is lowered, and the load side
  • the pump power per unit of heat is lowered, and energy is not wasted.
  • the load side is a general plate heat exchanger, a heat exchanger such as a cooling coil used in an air conditioner, and the temperature difference with the cold water at the outlet increases when the cold water temperature is lowered.
  • a heat exchanger such as a cooling coil used in an air conditioner
  • the load side is a general plate heat exchanger, a heat exchanger such as a cooling coil used in an air conditioner, and the temperature difference with the cold water at the outlet increases when the cold water temperature is lowered.
  • the centrifugal chiller has a small coefficient of performance when the load is low (for example, 30% load rate per unit). Therefore, compared to the case where the load per two units is 30% and the two units are operated, the operation of one unit is 60%, so that the operation with a high COP (coefficient of performance) can be achieved, and the pump transport power is wasted. It can be omitted.
  • Increasing the flow rate of cold water increases resistance, but it can be efficiently operated by decreasing the flow rate by lowering the temperature at the outlet of the cold heat source and increasing the load factor per refrigerator of the cold heat source.
  • the chilled water transport system may be a primary pump or load side secondary pump system on the cold heat source side, and the flow rate will decrease when the difference in the return temperature of the chilled water to the load on the secondary side becomes large. Can also be reduced.
  • the pipe size does not change, it is possible to introduce the cold water going temperature (chilled water going temperature) set value to the load at the time of renewal of the refrigerator by setting the temperature lower than the preset temperature.
  • water is exemplified as the heat medium, but a material other than water may be used as the heat medium.
  • the respective configurations have been described individually. However, the configurations of the first to sixth embodiments may be arbitrarily combined.

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Abstract

L'invention porte sur un système de source de chaleur pour lequel le système COP est amélioré sans réduire l'efficacité de fonctionnement de la source froide ; l'invention porte également sur son procédé de commande et un programme associé. Ce système de source de chaleur (N1) est un système pour lequel des pompes (P, P3) qui transmettent un milieu chauffant à une source froide (R) qui refroidit le milieu chauffant et/ou a un échangeur de chaleur qui échange de la chaleur entre le milieu chauffant refroidi et une charge (1), et la source froide (R), et un échangeur de chaleur pour la charge (1), sont raccordées par des tuyaux (r1, r2) à travers lesquels le milieu chauffant s'écoule. Le système de source de chaleur a : des moyens de mesure de quantité de chaleur de charge (3, 4) qui mesurent la quantité de chaleur que le milieu chauffant échange avec la charge (1) ; un moyen de mesure de température de circulation d'eau de refroidissement (4) qui mesure la température du milieu chauffant (R) qui échange de la chaleur avec la charge (1) et retourne à la source froide ; et un premier moyen de commande (2) qui abaisse la température réglée pour le milieu chauffant au niveau de la sortie de la source froide (R) lorsque la température du milieu chauffant chute au-dessous de la température réglée pour celui-ci et que la différence par rapport à la température réglée pour le milieu chauffant au niveau de la sortie de la source froide (R) devient inférieure à une quantité prescrite.
PCT/JP2012/050292 2011-01-11 2012-01-10 Système de source de chaleur, procédé de commande associé et programme associé WO2012096265A1 (fr)

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JP5472413B2 (ja) * 2012-09-20 2014-04-16 ダイキン工業株式会社 デマンド制御装置
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CN104478137A (zh) * 2014-12-18 2015-04-01 中国第一重型机械股份公司 一种工业循环冷却水节能回用组合系统
CN105004011B (zh) * 2015-07-31 2017-11-03 新智能源系统控制有限责任公司 适用于空调二级泵系统的变流量控制系统
EP3882524B1 (fr) * 2020-03-16 2023-11-08 Mitsubishi Electric Corporation Système de climatisation
CN111664524B (zh) * 2020-05-18 2022-05-13 华为数字能源技术有限公司 一种供冷系统及其供冷方法
JP2022127376A (ja) * 2021-02-19 2022-08-31 三菱重工サーマルシステムズ株式会社 制御装置及び熱源システム、並びに制御方法、並びに制御プログラム

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