JP2005321852A - Heat load prediction control system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat load prediction control system capable of optimizing an operation method according to a load of the day based on a previously set operation database for efficiently operating a latent heat storage tank, reducing power consumption of a heat source machine, and improving an environmental property, an energy saving property, and an economy property. <P>SOLUTION: When the most approximating load pattern among a limited number of load patterns previously set as operation patterns of the heat source machines RT-1 and RT-2 is set, an actual load varied momentarily is predicted and the heat source machines RT-1 and RT-2 and the heat storage tank 1 are started/stopped according to the previously planned operation pattern, the operation pattern can be decided according not to an operation pattern set by season but to the load of the day, and consequently, the heat load can be predicted more finely and the heat source machines RT-1 and RT-2 can be operated according to the finely set prediction. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention is applied to, for example, an air conditioning system that cools and heats a building or a heat process that requires cooling and heating. The present invention relates to a heat load prediction control system in a system.

  In the conventional heat storage system, the operation mode is switched mainly for each season, and the operation method of the heat source machine and the heat storage tank is almost fixed for each season. These heat source devices are started and stopped depending on the magnitude of the heat load at that time. Moreover, in the heat load prediction control with respect to the conventional heat storage system, the method of predicting the heat load of the next day and increasing / decreasing the heat storage amount of the day by the magnitude is taken.

  Furthermore, in the conventional heat storage system, the heat release from the heat storage tank or the start / stop determination of the heat source unit is performed by the operation method roughly determined according to the heat load. More specifically, the heat supply to a certain heat load is started early to cope with the heat load, but this is a heat source system equipped with a corner heat storage tank, but fully utilizes the heat amount of the heat storage tank Has difficulties that can not.

  For such difficulties, the target structure is automatically corrected by sequentially correcting the prediction model by the learning function of the neural network based on the provisional prediction model created from the past environmental element data and simulated data obtained in advance. There has been proposed a thermal load prediction system that generates a prediction model in which the characteristics of an object are taken into account and predicts a highly accurate air conditioning heat load prediction value (see Patent Document 1).

JP-A-8-35706 (paragraphs 0010, 0011, FIG. 2)

  As described above, the conventional thermal load prediction system uses the provisional prediction model for the same day environmental element data transmitted from the sensor unit, the next day weather element data transmitted from the weather prediction data collection unit, and the day of the week held internally. Calculate the predicted heat load for the next day from the data. Furthermore, the actual heat load value determined on the next day is compared with the calculated predicted heat load value, the weight is corrected and updated according to the error, and this is generated as an application model in the next time loop. It is.

  However, in this applied model, the daily heat load pattern is difficult to predict due to weather and other disturbances in the case of air conditioning load, etc. It becomes difficult to respond to sudden load fluctuations such as turning, and as a result, it is necessary to depend on the start and stop of heat source equipment based on the monthly or seasonal rough heat load pattern, that is, the operation setting. However, there are still unsolved problems, such as remaining excessively, or the amount of heat storage disappears sooner than expected, and the heat source machine has to be dealt with by forced partial load operation.

  The present invention has been made paying attention to such problems, and by optimizing the operation method according to the load on the operation day based on the operation database set in advance, the latent heat storage tank is effectively used. An object of the present invention is to provide a heat load prediction control system that can be operated and reduce the power consumption of a heat source machine to improve the environmental performance, energy saving, and economic efficiency of the heat source system.

  In order to solve the above-described object, the heat load prediction control system according to claim 1 of the present invention is operated in the time zone not corresponding to the heat load such as the heat source devices RT-1 and RT-2 at night. In a heat storage system that supplies heat in a heat load corresponding time zone by combining with the heat storage tank 1 that stores heat generated by the heat source devices RT-1 and RT-2, an actual heat load that varies from time to time is preliminarily determined. A thermal load prediction control system that performs thermal load prediction by setting a most suitable thermal load pattern among a finite number of thermal load patterns set as operation patterns of RT-1 and RT-2.

  A thermal load prediction control system according to a second aspect of the present invention is the thermal load prediction control system characterized in that the setting of the thermal load pattern is performed automatically and at appropriate time intervals.

  The heat load prediction control system according to claim 3 of the present invention includes the heat source devices RT-1 and RT-2 and the heat source devices RT-1 and RT-2 that are operated in a time zone that does not correspond to the heat load such as nighttime. In the heat storage system that supplies heat in the heat load corresponding time zone by combining with the heat storage tank 1 that stores the generated heat, the required remaining heat amount calculated from the heat load pattern selected at an arbitrary time, and the actual When it is determined that the heat source RT-1 and RT-2 can be stopped earlier than the time planned by the operation database by comparison between the heat storage amount and the remaining heat storage amount calculated from the heat release amount until that time, the operation is stopped. This is a heat load predictive control system characterized by doing the above.

  In the heat load prediction control system according to claim 4 of the present invention, the calculation of the residual heat amount required for stopping the heat source devices RT-1 and RT-2, which is a criterion, is an approximation obtained from the calculation result for each heat load pattern. A thermal load prediction control system characterized in that a determination according to the nature of the thermal load is performed using an equation.

  The present invention has the following effects.

  According to the first aspect of the present invention, the operation pattern is determined by the heat load of the day instead of setting the operation pattern for each season by starting and stopping the heat source unit and the heat storage tank according to the operation pattern planned in advance. Therefore, it is possible to predict the heat load that is finer than before and to operate the heat source device according to it.

  According to the second aspect of the present invention, by setting the thermal load pattern that is automatically and automatically performed at appropriate time intervals, the operation pattern that is further approximated is determined at a certain appropriate time interval. Therefore, it is possible to cope with a sudden load change such as a change from rain to sunny.

  According to the third aspect of the present invention, the actual remaining heat amount is grasped at regular time intervals, the expected planned load and the required remaining heat amount are compared each time, and the operation database is determined by the determination. By enabling the heat source machine to stop earlier than the planned time, it is possible to maximize the amount of heat released from the heat storage tank.

  According to the invention described in claim 4, since the heat dissipation characteristics that change according to the load are taken into account by using an approximate expression for calculating the amount of residual heat necessary for stopping the heat source machine, which is the criterion, from the heat storage tank. The heat radiation amount can be maximized, that is, the heat storage amount can be used up more reliably.

  Examples of the present invention will be described below.

  An embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a system circuit diagram showing a cooling operation flow operated in the first cooling mode of the heat storage system according to the first embodiment of the present invention, and FIG. FIG. 3 is a system circuit diagram showing a cooling operation flow operated in the third cooling mode, and FIG. 4 is a cooling operation operated in the fourth cooling mode. FIG. 5 is a system circuit diagram illustrating a flow, and FIG. 5 is a system circuit diagram illustrating a cooling operation flow operated in the nighttime cooling mode. In the above system circuit diagram, the piping section to be used is indicated by a thick line, the piping section not to be used is indicated by a thin line, the instrumentation line to be used is indicated by a bold dotted line, the instrumentation line not to be used is indicated by a thin dotted line, and the open or controlled state is shown. The valve is shown in white, and the valve in the closed state or uncontrolled state is shown in black.

  First, FIG. 1 shows a system circuit for performing a cooling operation flow operated in the first cooling mode as an embodiment of the present invention. This system circuit includes an ice heat storage tank 1 including four ice heat storage tanks 1a to 1d, each of the refrigerators RT-1 and RT-2 of the refrigeration apparatuses 8 and 10 serving as two cold heat source units, The heat transfer fluid (brine) cooled by the ice heat storage tank 1 and / or the refrigerator RT-1 and the refrigerator RT-2 is circulated and moved through the circulation line 16 by the circulation pump 5 to exchange heat with the equipment used. It is comprised from the heat exchangers 2 and 4 which do. The secondary side circulation pipe 18 on the side of the used equipment provided with an air conditioner or the like has two heat transfer fluids (brine) heat-exchanged by the heat exchangers 2 and 4 by the secondary side circulation pump 6. It is configured to circulate and move to the first and second heat using devices 12 and 14 via the secondary circulation pipes 6a and 6b, respectively.

  In the example of FIG. 16, this first cooling mode shows an operation pattern that is operated between 8 am and 10 am, and the brine cooled by the ice heat storage tank 1 and flowing out to the heat storage pipe 20 is radiated by the circulation pump 5. The circulation line 22c and the on-off valves V4 and V8 pass through the heat exchangers 2 and 4, pass through the on-off valves V2 and V1 through the heat radiation circulation lines 22b and 22a, circulate according to the arrows, and return to the ice heat storage tank 1 again. Forming a flow.

  The brine in the secondary circulation line 18 cooled by the circulating brine through the heat exchangers 2 and 4 is divided into two secondary circulation lines 6a, 3 by the three secondary circulation pumps 6. 6b is circulated and moved in accordance with the arrows, and the building is cooled to a constant temperature (for example, 25 ° C.) by first and second devices (such as air conditioners) equipped with air conditioners and the like.

  The circulation pump 5 is configured to control the frequency and the number of units according to the load. In the heat dissipation circulation line 22 c in the first cooling mode, three circulation pumps 5 are connected to one of the secondary side circulation lines 18. The flow rate is controlled by the temperature sensor T provided in the secondary side circulation pipe 6b through the pump controller 9 by an electrical signal, and the on-off valves V4 and V8 are similarly controlled. The on-off valves V1 and V3 of the heat storage pipes 20 and 21 are controlled to open and close based on the temperature detection signal measured by the temperature sensor T2 upstream of the circulation pump 5.

  Next, the second cooling mode shown in FIGS. 2 and 17 shows an operation pattern that is operated, for example, between 10:00 am and 11:00 am. In this operation pattern, one refrigerator RT-1 is activated and ice Heat radiation from the heat storage tank 1 and cooling by the refrigerator RT-1 are performed simultaneously.

  When the refrigerator RT-1 is started, the brine cooled by the refrigerator RT-1 is closed by closing the on-off valve V2 and closing part of the heat radiation circulation line 22a and simultaneously opening the on-off valve V5. According to the arrows, the heat transfer pipe 21 is moved from the on / off valve V3 or the heat storage pipe 20 on / off valve V1 to the heat exchangers 2 and 4 through the heat radiation circulation line 22c and the on / off valves V4 and V8 by one circulation pump 5. To do. The brine that has flowed from the heat exchanger 4 to the heat radiation circulation line 22b forms a flow that returns to the refrigerator RT-1 again by the heat radiation circulation line 24a.

  On the other hand, the brine that has moved from the heat radiation circulation line 22c to the pipe line 22e branched into the other heat exchanger 2 via the on-off valve V8, and the brine that has exited the heat exchanger 2 is one heat exchanger. 4 merges with the brine from 4 and returns to the refrigerator RT-1 from the cooling pipe 24a through the on-off valve V5. Further, a part of the brine flowing through the heat radiation circulation line 22c passes through the bypass line 22d in which the on-off valve V7 is opened and joins the cooling line 24a. This cooling mode is selected when the required brine flow rate in the heat exchangers 2 and 4 is smaller than the flow rate for one refrigerator, and is opened and closed by two on-off valves V4, V7, V8 is controlled.

  Next, the third cooling mode shown in FIG. 3 and FIG. 18 shows an operation pattern that is operated, for example, between 11:00 am and 17:00 pm, and in this operation pattern, one refrigerator is provided as in the second cooling mode. RT-1 is started and heat radiation from the ice heat storage tank 1 and cooling by the refrigerator RT-1 are performed simultaneously.

  When executing this operation pattern, when the refrigerator RT-1 is started, the on-off valve V2 is opened to open a part of the heat radiation circulation line 22a, and the on-off valve V7 is closed by the detection signal of the temperature sensor T. Then, by closing the bypass line 22d and simultaneously operating two of the three circulation pumps 5 by the pump control unit 9, the required brine flow rate in the heat exchangers 2 and 4 is equal to that of one refrigerator. It is selected when the flow rate is higher.

  Next, the 4th cooling mode shown by FIG.4 and FIG.19 shows the driving | operation pattern operated from 17:00 pm to 22:00 pm, for example. In this driving pattern, each of the two refrigerators RT-1 and chillers RT-2 is activated at the same time, and heat radiation from the ice heat storage tank 1 and cooling by the two refrigerators RT-1 and RT-2 are performed simultaneously.

  When this operation pattern is executed, the on-off valve V2 is closed and the heat radiation circulation line 22a is closed. When the two circulation pumps 5 are started, the brine cooled by the other refrigerator RT-2 merges with the brine cooled by the other refrigerator RT-1 through the heat storage pipe 20, and moves to the circulation pump 5. To do. The cooling brines exiting the two circulation pumps 5 are respectively connected to the refrigerators RT-1, RT through the cooling pipes 24a, 24b through the bypass pipe 22d in which the on-off valve V7 is opened as in the second cooling mode. Return to -2. In addition, since the brine flow that passes through the two heat exchangers 4 and 2 through different pipelines and merges with the brine that has passed through the bypass pipeline 22d forms the same flow as described above, the description thereof is omitted. .

  Next, the night-time cooling mode shown in FIGS. 5 and 20 shows an operation pattern that is operated, for example, between 22:00 and 24:00. In this operation pattern, each of the two refrigerators RT-1 and RT -2 are simultaneously activated to store heat in the ice storage tank 1 and cool by the two refrigerators RT-1 and RT-2.

  When this operation pattern is executed, the on-off valve V3 of the bypass line constituting a part of the heat storage line 21 is closed to cool the two refrigerating machines RT-1 and RT-2. The brine moves from the opened on-off valve V1 to the heat storage line 20 and stores heat when passing through the ice heat storage tank 1 including the four ice heat storage tanks 1a to 1d. The brine that has flown through the refrigeration machine RT-1 and the chiller RT-2 is circulated by the two circulating pumps 5 operated through the bypass line 22d in which the on-off valve V7 is opened from the heat radiation circulation line 22c. .

  Further, the brine that has passed through the open / close valve V4 from the heat radiation circulation line 22c and the brine that has passed through the open / close valve V8 in the pipe line 22e pass through the two heat exchangers 2 and 4, respectively, and are connected to each refrigerator through the heat radiation circulation line 22b. Cooling is also performed during the night time period when the electricity charge circulates in RT-1 and RT-2 and the electricity rate is reduced.

  Next, a database example of each operation mode at the time of partial load will be described with reference to FIGS. FIG. 6 to FIG. 15 are graphs showing graphs by load factor indicating the load heat quantity (kW) for each time for every 10% load factor (from 100% to 10%).

  First, the bar graph shown in FIG. 6 shows the relationship with the load (heat quantity kW) at each time of operation in the operation mode with a load factor of 100%. Each of the two refrigerators RT-1 and refrigerators The load by the thermal storage operation by RT-2, the heat radiation load, or the night load is shown. In addition, the number shown with the minus of the vertical axis | shaft has shown the heat storage amount (kW) at the time of heat storage driving | operation.

  Here, the refrigerator RT-1 is indicated by an upper right hatch, the refrigerator RT-2 is indicated by a white bar graph, the night load is indicated by a right lower hatch, and the heat radiation load is black white. Indicated by a filled bar graph.

  In this operation mode, the two refrigerators RT-1 and RT-2 are operated to store heat at a total load of about -2,600 kW from 0:00 am to 7:00 am, from 8:00 am to 11:00 pm Although a heat radiation load is generated, the maximum heat radiation load (around 3,200 kW) is from 11:00 am to 13:00 pm.

  Further, one refrigerator RT-1 is operated at a constant output from 10 am to 21 pm, and the other refrigerator RT-2 is simultaneously operated from 14:00 pm to 21 pm. And from 22:00 to 24:00, a night load of around 1,200 kW occurs, and at the same time, the heat storage operation by the two refrigerators RT-1 and RT-2 is started and the total load -2, It is operated at 600 kW.

  Next, in the operation mode with a load factor of 90% shown in FIG. 7, the maximum heat radiation load with the same heat quantity is extended until 16:00 pm, and the other refrigerator RT-2 is operated with the same output delayed from 17:00 pm. Be started.

  Further, in the operation mode with a load factor of 80% shown in FIG. 8, the maximum heat radiation load generated from 11:00 a.m. is reduced by about 13% from the load factor of 90% until 17:00 p.m. Until then, the load is drastically reduced, and at the same time, the refrigerator RT-2 is operated at the same output, and a load slightly lowered (1,900 kW to 1,800 kW) is generated again from 20:00 to 21:00. At 7 am, the heat storage operation of the refrigerator RT-2 is stopped.

  Next, in the operation mode with a load factor of 70% shown in FIG. 9, the operation of the refrigerator RT-1 from 11:00 am is continued at a constant output (about 2,000 kW) in the same time zone. In the operation mode of 70% or less, the simultaneous heat radiation operation by the refrigerator RT-2 is completely stopped and the heat radiation load becomes maximum (about 2,500 kW) at 10:00 am in this operation mode, but from 11:00 am to the afternoon Up to 21, the heat radiation load is reduced to about 1800 to 1,200 kW. The amount of heat stored by the two refrigerators RT-1 and RT-2 at 22:00 to 24:00 gradually increases as the load factor decreases.

  Further, in the operation mode with a load factor of 60% shown in FIG. 10, the heat radiation load at 10:00 am is reduced by about 15% from the load factor of 70%, and the maximum heat radiation of about 3,200 kW from 11 am to 14:00 pm. A load is generated, and from 15:00 to 21:00 pm, the refrigerator RT-1 is operated at a constant output (about 2,000 kW) with generation of a heat radiation load of about 1,200 kW to 800 kW. Others are the same as the operation mode with a load factor of 70%.

  From the operation mode with a load factor of 60% or less, the night load from 22:00 to 23:00 is reduced to about 1,000 kW, and the total heat storage amount in the heat storage operation by the two refrigerators RT-1 and RT-2. Increases to -1,500 kW.

  Next, in the operation mode with a load factor of 50% shown in FIG. 11, the maximum heat radiation load from 11:00 a.m. is reduced by about 20% from the load factor of 70% and continues until 17:00 p.m. Will drive from 18:00 to 21:00. Further, the amount of heat stored by the heat storage operation from 22:00 to 23:00 by the two refrigerators RT-1 and RT-2 increases to about -1,900 kW.

  Next, in the operation mode with a load factor of 50% shown in FIG. 11, the maximum heat radiation load is reduced to around 2,200 kW and is extended until 17:00 pm, and the heat radiation load is 200 pm from 18:00 pm to 21:00 pm. The refrigerator RT-1 is operated at a constant load (about 2,000 kW) while being reduced to ˜300 kW.

  In the operation mode with a load factor of 40% shown in FIG. 12, the heat radiation load generated from 8:00 am becomes the maximum heat radiation load (2,000 kW), which is about 25% less than the load factor 50% at 11:00 am. This maximum heat radiation load continues until 21 pm across the load of the refrigerator RT-1 operated at 19 pm.

  The night load generated from 22:00 to 23:00 decreases to about 400 kW, and the amount of heat stored by the heat storage operation increases to about -2,000 kW.

  Further, in the operation mode with a load factor of 30% shown in FIG. 13, the maximum heat radiation load from 11:00 am to 21:00 pm is reduced to about 1,600 to 1,800 kW, and the night load generated from 22:00 to 23:00 is The amount of heat stored by the heat storage operation increases to about -2,100 kW, and the heat storage operation is stopped at 6:00 am.

  Next, in the operation mode with a load factor of 20% shown in FIG. 14, the maximum heat radiation load from 11:00 am to 21:00 pm decreases to about 1,200 to 1,000 kW, and the nighttime that occurs from 22:00 to 23:00 pm The load decreases to about 200 kW, and the amount of heat stored by the heat storage operation increases to about -2,400 kW, and the heat storage operation at 3:00 am to 8:00 am is stopped.

  Finally, in the operation mode with a load factor of 10% shown in FIG. 15, the maximum heat radiation load from 10 am to 21:00 pm is reduced to about 500 to 300 kW, and the night load generated from 22:00 to 23:00 is about 100 kW. Decrease.

  And the heat storage amount from 22:00 to 24:00 is the total load −2 of the two refrigerators RT-1 and RT-2 that approximate the heat storage amount from 0:00 of the initial operation mode with a load factor of 100%, It becomes about 400 kW, and the heat storage operation from 1 am to 7 am is stopped.

  Next, it will be described with reference to FIGS. 16 to 20 and the chart of FIG. 21 in connection with the operation prediction by pattern when the load factor is 90% (see FIG. 7) operated in each cooling mode.

First, in the operation pattern in the first cooling mode at 8:00 am shown in FIG. 16, the load becomes 632 kW in order to obtain the supply temperature of chilled water of 7 ° C. in the secondary circulation line 18, and the heat exchangers 2 and 4 are circulated. The required flow rate of brine to be performed is a flow rate of 35 m ³ / h.

Therefore, by dissipating a heat radiation amount of 632 kW to the four ice heat storage tanks 1a to 1d, the cold water cooled to −6 ° C. in the ice heat storage tanks 1a to 1d is flown at a flow rate of 35 m ³ / h by one pump 5. Circulating and moving the heat radiation circulation lines 22a to 22c, and passing them through the heat exchangers 2 and 4, the flow rate of the circulation pump 5 so that the supply temperature of the secondary cold water measured by the temperature sensor T becomes 7 ° C. Are properly controlled by electrical signals.

Next, in the operation pattern in the second cooling mode at 10:00 am shown in FIG. 17, a load of 3,159 kW is necessary to obtain a supply temperature of cold water of 7 ° C. in the secondary side circulation line 18, and the heat exchanger The required flow rate of the brine circulating through 2 and 4 is a flow rate of 319 m ³ / h.

Therefore, by starting one refrigerator RT-1, 1,959 kW of cold heat is generated and the remaining 1,199 kW of heat is generated in the four ice heat storage tanks 1a to 1d, and cooled to 5 ° C. The brine is circulated through the heat radiation circulation lines 22a to 22c by a single pump 5 at a flow rate of 346 m ³ / h, of which 319 m ³ / h is passed through the heat exchangers 2 and 4 so that the secondary side The supply temperature of cold water is kept at 7 ° C.

In addition, the operation pattern in the third cooling mode at 11:00 am shown in FIG. 18 corresponds to the second cooling mode (rotational speed control) in the chart shown in FIG. 21, and in this third cooling mode, the secondary side In order to obtain the supply temperature of cold water of 7 ° C. in the circulation line 18, a load of 4,577 kW is required, and the required flow rate of the brine circulating in the heat exchangers 2, 4 becomes a flow rate of 506 m ³ / h.

Therefore, a load of 2,618 kW is generated in the four ice heat storage tanks 1a to 1d, and at the same time, one refrigerator RT-1 is started and the brine cooled by 1,959 kW is used as an ice heat storage tank. The necessary brine flow rate 506 m ³ / h circulated through 1 a to 1 d and cooled to 5 ° C. is circulated through the heat radiation circulation lines 22 a to 22 c by the two pumps 5, and is passed through the heat exchangers 2 and 4. Thus, the supply temperature of the cold water on the secondary side is kept at 7 ° C.

Further, the operation pattern in the fourth cooling mode at 17:00 pm shown in FIG. 19 corresponds to the third cooling mode in the chart shown in FIG. 21, and in this operation pattern, the chilled water in the secondary side circulation line 18 is shown. In order to obtain a supply temperature of 7 ° C., a load of 4,672 kW is required, and the required flow rate of brine circulating through the heat exchangers 2 and 4 is a flow rate of 488 m ³ / h.

Therefore, a load of 818 kW is generated in the four ice heat storage tanks 1a to 1d, and at the same time, the two refrigerators RT-1 and RT-2 are started and cooled to 3,854 kW. The required flow rate of 692 m ³ / h is further cooled to 5 ° C. by heat radiation from the ice heat storage tanks 1 a to 1 d, and is circulated through the heat radiation circulation lines 22 a to 22 c by the two pumps 5. 4, the supply temperature of the cold water on the secondary side is kept at 7 ° C.

Next, in the operation pattern in the nighttime cooling mode at 22:00 shown in FIG. 20, a load of 1,265 kW is required to obtain a supply temperature of chilled water of 7 ° C. in the secondary circulation line 18, and the heat exchanger 2 , 4 is the required flow rate of the brine circulating in the flow rate of 62 m ³ / h.

  Therefore, by starting up the two refrigerators RT-1 and RT-2, 3,854 kW of cold energy is generated, and the difference between the four ice heat storage tanks 1a to 1d and the secondary heat radiation amount of 1,265 kW is generated. 1,336 kW of cold energy is stored.

The brine 692 m ³ / h that has reached −2 ° C. at the outlet of the ice heat storage tank is circulated through the heat radiation circulation lines 22 a to 22 c by the two pumps 5, and is passed through the heat exchangers 2 and 4 to obtain a secondary The side cold water supply temperature is kept at 7 ° C.

  Next, operation prediction will be described with reference to FIGS. 22 and 23. FIG. FIG. 22 is an operation prediction chart, and FIG. 23 is a graph chart based on an operation mode with a load factor of 90%.

  When a load factor of 80% or more and less than 90% shown in FIG. 23 is predicted, operation is performed based on the operation mode of 90% load factor shown in FIG. 7, and residual heat control indicated by a thin dotted line from 16:00 pm , The refrigerator RT-2; 1 unit is stopped at 20:00 pm, and an operation prediction model indicated by a thick line indicating a temporal change is created based on the operation example chart of FIG.

  Therefore, as explained in the above embodiment, for each of a finite number of heat load patterns that can be conceived in advance, an operation pattern of the heat storage tank that obtains the maximum heat radiation amount and a heat source device 8 that enables the shortest operation time with high load operation. , 10 are constructed as an operation database shown in FIG.

During actual operation, the heat load pattern that most closely resembles the actual heat load is selected from the chart of the operation database, and the heat source units 8 and 10 and the heat storage tanks 1a to 1d are activated according to the operation pattern planned in advance in the application database. Stop.

  As a result, the operation pattern can be determined based on the heat load of the day, and the heat load can be predicted more finely than before and the heat source device can be operated according to the prediction. Further, the determination of the operation pattern to be approximated is performed at a certain appropriate time interval to cope with the temporal change of the thermal load, so that it is possible to cope with a sudden load fluctuation such as turning from rain to clear weather.

  In the latter half of the operation, the actual remaining heat amount is grasped at regular time intervals, the expected planned load and the remaining heat amount are compared each time, and the heat source units 8 and 10 are planned by the operation database. If it is determined that the heat can be stopped earlier than the time, the amount of heat released from the heat storage tanks 1a to 1d can be maximized by stopping the operation.

  The calculation of the amount of stored heat necessary for stopping the heat source machine, which is a determination criterion, uses an approximate expression obtained from the calculation result for each heat load pattern, and performs an accurate determination according to the character of the heat load. Thereby, maximization of the amount of heat radiation from the heat storage tanks 1a to 1d, that is, the use-up operation of the heat storage tanks 1a to 1d can be made more reliable.

  Although the embodiments of the present invention have been described with reference to the drawings, the specific configuration is not limited to these embodiments, and modifications and additions within the scope of the present invention are included in the present invention. It is.

It is a system circuit diagram which shows the operation flow at the time of air_conditioning | cooling operated by the 1st cooling mode of the thermal storage system in Example 1 of this invention. It is a system circuit diagram which shows the operation flow at the time of air_conditioning | cooling operated by 2nd cooling mode. It is a system circuit diagram which shows the operation flow at the time of air_conditioning | cooling operated by 3rd cooling mode. It is a system circuit diagram which shows the operation flow at the time of air_conditioning | cooling operated by 4th cooling mode. It is a system circuit diagram which shows the operation flow at the time of air_conditioning | cooling operated by night cooling mode. It is a graph chart operated in an operation mode of 100% load factor. It is a graph chart operated in an operation mode of 90% load factor. It is a graph figure operated by the operation mode of 80% of load factors. It is a graph chart operated by the operation mode of 70% of load factors. It is a graph chart operated in an operation mode of 60% load factor. It is a graph chart operated in an operation mode of 50% load factor. It is a graph figure operated by the operation mode of 40% of load factors. It is a graph figure operated by the operation mode of 30% of load factors. It is a graph chart operated by the operation mode of 20% of load factors. It is a graph chart operated by the operation mode of 10% of load factors. It is a driving | operation prediction circuit diagram classified by pattern operated in 8:00 am in 1st cooling mode. It is a driving | operation prediction circuit diagram classified by pattern operated at 10:00 am in 2nd cooling mode. It is a driving | operation prediction circuit diagram classified by pattern operate | moved at 11:00 am in 3rd cooling mode. It is a driving | operation prediction circuit diagram classified by pattern operated at 17:00 in the 4th cooling mode. It is a driving | operation prediction circuit diagram classified by pattern operated in 2pm in the night driving mode. It is a table | surface of the database in the operation mode of 90% of load factors. It is an operation prediction chart. It is a model graph chart based on the operation mode of 90% of load factors.

Explanation of symbols

1 ice storage tank (storage tank)
1a to 1d Ice heat storage tank 2, 4 Heat exchanger 5 Circulation pump 6 Secondary side circulation pumps 6a, 6b Secondary side circulation pipes 8, 10 Refrigeration unit 9 Pump control unit 12 First heat use device 14 Second heat use Equipment 16 Circulation line 18 Secondary side circulation lines 20 and 21 Heat storage lines 22a to 22c Heat radiation circulation lines 22d Bypass lines 22e Lines 24a and 24b Cooling lines RT-1 and RT-2 Refrigerator (heat source machine) )
T, T2 Temperature sensors V1-V8 Open / close valve

Claims (4)

Heat load by combining the heat source devices RT-1 and RT-2 with the heat storage tank 1 that stores the heat generated by the heat source devices RT-1 and RT-2 operated in a time zone that does not correspond to the heat load such as at night In a heat storage system that supplies heat during a corresponding time period,
Predicting the heat load by setting the actual heat load that fluctuates from time to time as the most suitable heat load pattern among a finite number of heat load patterns in which the operation patterns of the heat source devices RT-1 and RT-2 are optimally set in advance. A heat load prediction control system characterized by 2. The thermal load prediction control system according to claim 1, wherein the setting of the thermal load pattern is performed automatically and automatically at appropriate time intervals. Heat load by combining the heat source devices RT-1 and RT-2 and the heat storage tank 1 storing the heat generated by the heat source devices RT-1 and RT-2 operated in a time zone that does not correspond to the heat load such as at night In a heat storage system that supplies heat during a corresponding time period,
By comparing the required residual stored heat amount calculated from the heat load pattern selected at an arbitrary time with the actual stored heat amount and the remaining stored heat amount calculated from the amount of heat released until that time, the heat source machine RT-1, A thermal load predictive control system, wherein RT-2 is stopped when it is determined that it can be stopped earlier than the time planned by the operation database. The calculation of the residual heat amount necessary for stopping the heat source devices RT-1 and RT-2, which is the determination criterion, is performed according to the character of the heat load using an approximate expression obtained from the calculation result for each heat load pattern. The thermal load predictive control system according to claim 3, wherein

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