JP5927694B2 - HEAT SOURCE SYSTEM AND HEAT SOURCE SYSTEM CONTROL METHOD - Google Patents

Description

  The present invention relates to a heat source system and a control method for the heat source system.

A heat source system includes a plurality of heat source units, and supplies heat to the heat load by supplying a high-temperature heat medium to the heat load, or cools the heat load by supplying a low-temperature heat medium to the heat load. Is a system that removes heat from the heat load.
In the operation of the heat source system, evaluation functions such as energy consumption of the entire heat source system, operating cost of the entire heat source system, and carbon dioxide emissions from the heat source system are set and controlled so that the evaluation function is minimized. It has become so.
For example, when the evaluation function is an integrated value of all electric power energy consumed by the heat source system and all gas energy, control can be performed so as to minimize the energy consumption of the entire heat source system. Further, for example, when the evaluation function is an integrated value of all the power costs consumed by the heat source system and all the gas costs, the control can be performed so as to minimize the operation cost of the entire heat source system. Yes.

In general, the relationship between the load factor and the coefficient of performance (COP) in the heat source device included in the heat source system is such that, for example, as shown in FIG. 4 of Patent Document 2, the COP increases as the load factor increases. It has become.
For this reason, the control of the number of operating heat source units in the heat source systems disclosed in Patent Literature 1 and Patent Literature 2 is to operate the minimum number of heat source devices capable of processing the heat load amount (heat load demand amount) to be processed. Moreover, the control by the number is the number that reduces the most energy consumption in the heat load demand.

JP 2008-292043 A JP 2005-114295 A

  By the way, in the heat source machine, for example, there are heat source machines having different characteristics (for example, load factor-COP characteristics) such as a turbo chiller, an inverter turbo chiller, an absorption chiller / heater, and an exhaust heat absorption chiller / heater. . For this reason, when the heat source system processes the heat load demand, it is not a change in the number of operating heat source machines as in the control in the conventional heat source system (for example, see Patent Document 1 and Patent Document 2), but the heat load demand. In some cases, energy can be saved and the cost of the entire heat source system can be reduced by appropriately distributing the heat to each heat source unit.

  For example, when the configuration of the heat source device included in the heat source system is one inverter turbo chiller and a plurality of exhaust heat absorption chiller / heater with small processing capacity, the exhaust heat absorption chiller / heater is Since the COP may be high at low load (see FIG. 6 (c) described later), when the thermal load demand is reduced from the state where only one inverter turbo chiller is operating, the inverter turbo refrigeration In some cases, the energy consumption of the entire heat source system can be reduced by stopping the operation of the machine and starting the operation of a plurality of exhaust heat absorption chiller / heater units.

  However, the control of the number of operating heat source units in the heat source systems disclosed in Patent Document 1 and Patent Document 2 cannot cope with such a case. Furthermore, as the number and types of heat source units included in the heat source system increase, the problem of operation unit control for reducing energy consumption becomes more complicated.

  Then, this invention makes it a subject to provide the control method of the heat source system and heat source system which reduce energy consumption, an operating cost, or a carbon dioxide emission amount etc. about a heat source system provided with a some heat source machine.

In order to solve such problems, the present invention controls at least two or more heat source units, a transport unit that transports a heat transport medium from the heat source unit to a heat load, and controls the heat source unit and the transport unit. A heat source system comprising: a control means, wherein the control means generates a pattern for generating a heat load to each of the heat source machines, and an evaluation function of the heat source system in the generated heat load distribution pattern. Simulation means for calculating the thermal load distribution pattern based on the evaluation function, pattern extraction means for extracting one thermal load distribution pattern from the thermal load distribution pattern generated by the pattern generation means, and the extracted thermal load distribution pattern based on, have a, and operation control means for controlling the heat source apparatus and said transport means, said pattern generating means, the heat load distribution Pas Of over emissions, when there is the heat source unit having a non-load factor operation among the heat source apparatuses, a heat source system and deletes the heat load distribution pattern.

The present invention also includes a heat source system comprising at least two or more heat source units, a transport unit that transports a heat transport medium from the heat source unit to a heat load, and a control unit that controls the heat source unit and the transport unit. The control means includes: a generation step for generating a thermal load distribution pattern for each of the heat source units; and among the heat load distribution patterns generated in the generation step , When there is the heat source device having an inoperable load factor, a deletion step of deleting the heat load distribution pattern, and an evaluation function of the heat source system in the heat load distribution pattern that is not deleted as a result of the deletion step Based on the calculation step of calculating, and the evaluation function calculated in the calculation step, one of the thermal load distribution patterns generated in the generation step An extraction step for extracting a load distribution pattern, and a control step for controlling the heat source unit and the transfer means based on the thermal load distribution pattern extracted in the extraction step. It is a control method.
Other solutions are described in the embodiments.

  ADVANTAGE OF THE INVENTION According to this invention, about the heat source system provided with a some heat source machine, the control method of the heat source system and heat source system which reduce energy consumption, an operating cost, or a carbon dioxide emission amount etc. can be provided. In particular, even when the heat source system includes heat source units having different characteristics, by controlling the number of operating heat source units and the amount of heat load distributed to each heat source unit, the energy consumption and operation of the entire heat source system are controlled. Costs or carbon dioxide emissions can be reduced.

It is a lineblock diagram of the heat source system concerning a 1st embodiment. It is a flowchart which shows operation | movement of the control apparatus of the heat-source system which concerns on 1st Embodiment. It is a schematic diagram which shows the division | segmentation of the heat load which a heat source system should process. It is a table | surface which shows the thermal load distribution pattern which a thermal load distribution pattern production | generation part produces | generates. It is the table | surface which extracted the heat load distribution pattern which can be drive | operated. It is a graph which shows the load factor-COP characteristic of each heat-source equipment, (a) is an inverter turbo refrigerator, (b) is a turbo refrigerator, (c) is an exhaust-heat utilization absorption type cold / hot water machine. . It is a table | surface which shows the heat load distribution pattern which the heat load distribution pattern generation part in 2nd Embodiment produces | generates. It is a figure which shows an example of a thermal load distribution pattern. (A) is a table which shows the power consumption of the heat source machine which consumes electric power, (b) is a table which shows the gas consumption of the heat source machine which consumes gas.

  Hereinafter, modes for carrying out the present invention (hereinafter referred to as “embodiments”) will be described in detail with reference to the drawings as appropriate. In each figure, common portions are denoted by the same reference numerals, and redundant description is omitted.

<< First Embodiment >>
<Heat source system S>
FIG. 1 is a configuration diagram of a heat source system S according to the first embodiment.
As shown in FIG. 1, the heat source system S includes three systems of heat source units (first heat source unit 1, second heat source unit 2, and third heat source unit 3), a heat load 4, and cold / hot water pumps 5a, 5b, 5c, a cold / hot water return header 6a, a cold / hot water return header 6b, and a control device 30, and a heat source unit (first heat source unit 1, second heat source unit 2, third heat source unit 3) and heat load 4 Cold and hot water circulates between the two.
In the following description, the heat load 4 is a load source (for example, an air conditioner that performs cooling operation) as a cold demand, and the heat source system S is a system that supplies cold heat to the heat load 4. To do.

The heat source unit (the first heat source unit 1, the second heat source unit 2, the third heat source unit 3) cools the cold / hot water flowing in from the cold / hot water inlet and flows out from the cold / hot water outlet.
As shown in FIG. 1, in the first heat source unit 1 (an inverter turbo refrigerator 11 described later), the cold / hot water inlet is connected to the discharge side of the cold / hot water pump 5a, and the cold / hot water outlet is connected to the cold / hot water header 6a. ing. In the second heat source unit 2 (a turbo refrigerator 12 described later), the cold / hot water inlet is connected to the discharge side of the cold / hot water pump 5b, and the cold / hot water outlet is connected to the cold / hot water header 6a. In the third heat source unit 3 (exhaust heat utilization absorption chiller / heater 13 to be described later), the chilled / hot water inlet is connected to the discharge side of the chilled / hot water pump 5c, and the chilled / hot water outlet is connected to the chilled / hot water header 6a.
The details of the heat source units (the first heat source unit 1, the second heat source unit 2, and the third heat source unit 3) will be described later.

  The thermal load 4 is a load source as a cold demand, and as shown in FIG. 1, one end (cold / hot water inlet side) of the thermal load 4 is connected to the cold / hot water forward header 6a and the other end (cold / hot water outlet side). Is connected to the cold / hot water return header 6b.

The cold / hot water pumps 5a, 5b, 5c are pumps for circulating cold / hot water between the heat source unit (the first heat source unit 1, the second heat source unit 2, the third heat source unit 3) and the heat load 4.
As shown in FIG. 1, the cold / hot water pump 5a has the suction side connected to the cold / hot water return header 6b, and the discharge side connected to the cold / hot water inlet of the first heat source unit 1 (an inverter turbo refrigerator 11 described later). The cold / hot water pump 5b has a suction side connected to the cold / hot water return header 6b and a discharge side connected to a cold / hot water inlet of the second heat source unit 2 (a turbo refrigerator 12 described later). The cold / hot water pump 5c has a suction side connected to the cold / hot water return header 6b, and a discharge side connected to the cold / hot water inlet of the third heat source unit 3 (exhaust heat utilization absorption type cold / hot water machine 13 described later).

  Inverters 21a, 21b, and 21c are connected to the cold / hot water pumps 5a, 5b, and 5c, respectively. The control device 30 controls the inverters 21a, 21b, and 21c to change the flow rate of the cold / hot water in the cold / hot water pumps 5a, 5b, and 5c within a predetermined range (for example, from 40% of the rated flow rate to the rated flow rate). Can be done.

In this way, the heat source system S drives the cold / hot water pumps 5a, 5b, 5c, thereby causing the heat source unit (first heat source unit 1, second heat source unit 2, third heat source unit 3) to be supplied from the cold / hot water return header 6b. Cold and warm water flows. And the cold / hot water cooled by the heat source unit (the 1st heat source unit 1, the 2nd heat source unit 2, the 3rd heat source unit 3) is supplied to the thermal load 4 via the cold / hot water header 6a. .
The cold / hot water supplied to the heat load 4 supplies cold heat to the heat load 4 (the cold / warm water is heated by the heat load 4), and the cold / hot water whose temperature has risen returns to the cold / hot water return header 6b. Yes.

<First heat source unit 1, second heat source unit 2, third heat source unit 3>
Next, the heat source unit (the first heat source unit 1, the second heat source unit 2, the third heat source unit 3) will be described.
As shown in FIG. 1, the first heat source unit 1 includes an inverter turbo chiller (heat source machine) 11, a cooling tower 7 a having a blower fan 8 a, and a cooling water pump 9 a. Cooling water circulates between the cooling towers 7a.
The second heat source unit 2 includes a turbo chiller (heat source machine) 12, a cooling tower 7b having a blower fan 8b, and a cooling water pump 9b. The second heat source unit 2 is provided between the turbo chiller 12 and the cooling tower 7b. Cooling water circulates.
The third heat source unit 3 includes an exhaust heat utilization absorption chiller / heater (heat source device) 13, a cooling tower 7c having a blower fan 8c, a cooling water pump 9c, an exhaust hot water pump 15, and a gas engine 14. The cooling water is circulated between the exhaust heat utilization absorption chiller / heater 13 and the cooling tower 7c, and the exhaust heat utilization absorption chiller / heater 13 and the gas engine 14 are circulated. It has become.

The cooling towers 7a, 7b, and 7c cool the cooling water by exchanging heat with the air from the cooling water inlet and / or by heat of vaporization when the cooling water evaporates. It flows out from the exit.
As shown in FIG. 1, the cooling water inlet of the cooling tower 7a is connected to the cooling water outlet of the inverter turbo refrigerator 11, and the cooling water outlet of the cooling tower 7a is connected to the suction side of the cooling water pump 9a. . The cooling water inlet of the cooling tower 7b is connected to the cooling water outlet of the turbo refrigerator 12, and the cooling water outlet of the cooling tower 7b is connected to the suction side of the cooling water pump 9b. The cooling water inlet of the cooling tower 7c is connected to the cooling water outlet of the exhaust heat utilization absorption chiller / heater 13, and the cooling water outlet of the cooling tower 7c is connected to the suction side of the cooling water pump 9c.

  The cooling towers 7a, 7b, and 7c are air blows for taking the atmosphere into the cooling towers 7a, 7b, and 7c in order to promote heat exchange between the cooling water and the atmosphere and / or to promote evaporation of the cooling water. Fans 8a, 8b and 8c are provided.

  Inverters 22a, 22b, and 22c are connected to the blower fans 8a, 8b, and 8c, respectively. The control device 30 can change the air flow rate of the blower fans 8a, 8b, and 8c by controlling the inverters 22a, 22b, and 22c.

The cooling water pumps 9a, 9b, 9c circulate cooling water between the heat source devices (inverter turbo chiller 11, turbo chiller 12, exhaust heat utilization absorption chiller / heater 13) and cooling towers 7a, 7b, 7c. It is a pump for making it.
As shown in FIG. 1, the cooling water pump 9 a has a suction side connected to a cooling water outlet of the cooling tower 7 a and a discharge side connected to a cooling water inlet of the inverter turbo chiller 11. The cooling water pump 9b has a suction side connected to a cooling water outlet of the cooling tower 7b, and a discharge side connected to a cooling water inlet of the turbo refrigerator 12. The cooling water pump 9c has a suction side connected to a cooling water outlet of the cooling tower 7c and a discharge side connected to a cooling water inlet of the exhaust heat utilization absorption chiller / heater 13.

  Inverters 23a, 23b, and 23c are connected to the cooling water pumps 9a, 9b, and 9c, respectively. The control device 30 controls the inverters 23a, 23b, and 23c to change the flow rate of the cooling water in the cooling water pumps 9a, 9b, and 9c within a predetermined range (for example, from 40% of the rated flow rate to the rated flow rate). Can be done.

  The inverter turbo chiller 11 includes a refrigeration cycle (heat pump cycle) (not shown), consumes electric power, and drives a compressor (not shown) of the refrigeration cycle (heat pump cycle), thereby cooling water from the cooling water inlet. Cooling water is drawn from the cooling water flowing into the cooling water, the cold / hot water flowing in from the cold / hot water inlet is cooled, and the cooled cold / hot water flows out from the cold / hot water outlet.

  The turbo refrigerator 12 includes a refrigeration cycle (heat pump cycle) (not shown), and consumes electric power to drive a compressor (not shown) of the refrigeration cycle (heat pump cycle), so that the cooling water inlet to the cooling water outlet. Cold heat is drawn from the flowing cooling water, the cold / hot water flowing in from the cold / hot water inlet is cooled, and the cooled cold / hot water flows out from the cold / hot water outlet.

  The inverter turbo chiller 11 can control the rotational speed of a compressor (not shown) of a refrigeration cycle (heat pump cycle), and the turbo chiller 12 is a compressor (not shown) of a refrigeration cycle (heat pump cycle). Since the rotation speed is constant, the characteristics (load factor-COP characteristics) are different as shown in FIGS. 6A and 6B described later.

  The waste heat utilizing absorption chiller / heater 13 heats the absorption liquid (not shown) by burning hot exhaust water and gas flowing from the exhaust hot water inlet to the exhaust hot water outlet, and from the cooling water inlet to the cooling water outlet. By cooling with the flowing cooling water, the absorption refrigeration cycle is driven to cool the cold / hot water flowing in from the cold / hot water inlet, and the cooled cold / warm water flows out from the cold / hot water outlet. As shown in FIG. 6C described later, the characteristics (load factor-COP characteristics) are the same as that of the inverter turbo chiller 11 (see FIG. 6A) and the turbo chiller 12 (see FIG. 6B). Is different.

  In each heat source machine (inverter turbo chiller 11, turbo chiller 12, exhaust heat utilization absorption chiller / heater 13), the temperature of the chilled / warm water flowing out from the chilled / warm water outlet (cold / warm water outlet temperature) becomes the control target temperature. Drive to. The control device 30 can control the cold / hot water outlet temperature by instructing the control target temperature to each heat source machine (inverter turbo chiller 11, turbo chiller 12, exhaust heat utilization absorption chiller / heater 13). It is like that.

The gas engine 14 is a device that generates rotational force by burning fuel (gas). The generated rotational force is transmitted to a generator (not shown) to generate electric power. Further, the gas engine 14 has a heat exchanger (not shown) capable of exchanging heat between the high-temperature exhaust gas after combustion and the exhaust warm water, and heats the exhaust warm water flowing from the exhaust warm water inlet, It flows out from the exit.
As shown in FIG. 1, the exhaust hot water inlet of the gas engine 14 is connected to the exhaust hot water outlet of the exhaust heat utilization absorption chiller / heater 13, and the exhaust hot water outlet of the gas engine 14 is connected to the suction side of the exhaust hot water pump 15. It is connected.

The exhaust hot water pump 15 is a pump for circulating the exhaust hot water between the exhaust heat utilization absorption chiller / heater 13 and the gas engine 14.
As shown in FIG. 1, the exhaust hot water pump 15 has a suction side connected to an exhaust hot water outlet of the gas engine 14 and a discharge side connected to an exhaust hot water inlet of the exhaust heat utilization absorption chiller / heater 13.
An inverter 24 is connected to the exhaust hot water pump 15, and by controlling the inverter 24, the flow rate of the exhaust hot water of the exhaust hot water pump 15 can be changed within a predetermined range.

  The electric power generated by the gas engine 14 is configured to be supplied to an electric power demand source (not shown), and the gas engine 14 and the exhaust hot water pump 15 are electric power from an electric power demand source (not shown). It is designed to be driven according to demand.

<Control device 30>
Next, the control device 30 provided in the heat source system S will be described.
As shown in FIG. 1, the control device 30 includes a thermal load distribution pattern generation unit 31, a simulation unit 32, a thermal load distribution pattern extraction unit 33, and an operation control command unit 34.

Here, the heat source system S includes various sensors (not shown), and the detected values are input to the control device 30.
Specifically, at the cooling water inlet of each heat source machine (inverter turbo chiller 11, turbo chiller 12, exhaust heat utilization absorption chiller / heater 13), the temperature of cooling water flowing into each heat source machine (cooling water) A temperature sensor (not shown) for detecting an inlet temperature) and a flow rate sensor (not shown) for detecting a flow rate of cooling water (cooling water flow rate) flowing into each heat source unit are provided. A temperature sensor (not shown) for detecting the temperature of the cooling water flowing out from the heat source machine (cooling water outlet temperature) is provided.
Further, at the cold / hot water inlet of each heat source machine, a temperature sensor (not shown) for detecting the temperature of cold / hot water flowing into each heat source machine (cold hot water inlet temperature) and the flow rate of cold / hot water flowing into each heat source machine ( A flow rate sensor (not shown) for detecting the temperature of the cold / hot water is provided, and a temperature sensor (not shown) for detecting the temperature (cold / warm water outlet temperature) of the cold / warm water flowing out from each heat source unit is provided at the cooling water outlet. Is provided.

  A temperature sensor (not shown) for detecting the temperature of the cooling water flowing into the heat load 4 and a flow rate sensor for detecting the flow rate of the cooling water flowing into the heat load 4 are provided at one end (cold / hot water inlet side) of the heat load 4. (Not shown) is provided, and a temperature sensor (not shown) for detecting the temperature of the cooling water flowing out from the heat load 4 is provided at the other end (cold hot water outlet side) of the heat load 4.

  The cooling towers 7a, 7b and 7c include a dry bulb temperature sensor (not shown) and a relative temperature sensor for detecting the temperature and humidity of the air taken into the cooling towers 7a, 7b and 7c by the blower fans 8a, 8b and 8c. (Not shown) is provided.

  The heat load distribution pattern generation means 31 distributes the heat load amount (heat load demand amount) of the heat load 4 to each heat source device (inverter turbo chiller 11, turbo chiller 12, exhaust heat utilization absorption chiller / heater 13). It has a function of generating a thermal load distribution pattern. In the heat load distribution pattern, when the heat load distributed to a certain heat source device is “0”, this means that the heat source device is stopped. That is, the heat load distribution pattern includes information on the number of operating heat source devices and heat load distribution information to each heat source device.

  The simulation means 32 performs a simulation on the heat load distribution pattern generated by the heat load distribution pattern generation means 31, and the evaluation function (for example, energy consumption, operation cost or carbon dioxide emission amount) is minimized for each heat load distribution pattern. And a function for obtaining the evaluation function value (flow rate of the cold / hot water pumps 5a, 5b, 5c, flow rate of the blower fans 8a, 8b, 8c, flow rate of the cooling water pumps 9a, 9b, 9c). doing.

  The thermal load distribution pattern extraction unit 33 has a function of extracting a thermal load distribution pattern that minimizes the value of the evaluation function obtained by the simulation unit 32 from a plurality of thermal load distribution patterns generated by the thermal load distribution pattern generation unit 31. Have.

  The operation control command means 34 sends signals to the inverters 21a, 21b, 21c to control the flow rates of the cold / hot water pumps 5a, 5b, 5c so as to realize the heat load distribution pattern extracted by the heat load distribution pattern extraction means 33. The signal for controlling the flow rate of the blower fans 8a, 8b, 8c is transmitted to the inverters 22a, 22b, 22c, and the signal for controlling the flow rate of the cooling water pumps 9a, 9b, 9c is transmitted to the inverters 23a, 23b, 23c. It has the function to transmit and transmit the signal which controls the cold / hot water outlet temperature of each heat source machine (inverter turbo refrigerator 11, turbo refrigerator 12, exhaust heat utilization absorption type cold / hot water machine 13) to each heat source machine. .

  As described above, the control device 30 of the heat source system S includes the flow rates of the cold / hot water pumps 5a, 5b, 5c, the flow rates of the blower fans 8a, 8b, 8c, the flow rates of the cooling water pumps 9a, 9b, 9c, The temperature of the chilled / hot water outlet of the inverter turbo chiller 11, the turbo chiller 12, and the exhaust heat utilization absorption chiller / heater 13) is controlled.

  The control device 30 controls the heat source system S so as to minimize the evaluation function. Here, if the evaluation function is energy consumption of the entire heat source system S, the control device 30 controls the heat source system S so as to minimize the energy consumption of the heat source system S. The energy consumption of the heat source system S is the cold / hot water pumps 5a, 5b, 5c, the blower fans 8a, 8b, 8c, the cooling water pumps 9a, 9b, 9c, the inverter turbo refrigerator 11, the turbo refrigerator 12, the exhaust heat This is the sum of the energy consumption of each of the utilization absorption chiller / heaters 13.

In the heat source system S according to the present embodiment, a heat source machine (inverter turbo chiller 11, turbo chiller 12, exhaust heat utilization absorption chiller / heater 13) and heat load 4 are connected to a chilled / hot water header 6a and chilled / hot water return. It is a centralized heat source system connected via a header 6b, and the cold / hot water inlet temperature of the inverter turbo chiller 11, the cold / hot water inlet temperature of the turbo chiller 12, and the cold / hot water of the exhaust heat utilization absorption chiller / heater 13 The inlet temperature is the same.
Further, the control target temperature is set so that the cold / hot water outlet temperature of the inverter turbo chiller 11, the cold / hot water outlet temperature of the turbo chiller 12, and the cold / hot water outlet temperature of the exhaust heat utilization absorption chiller / heater 13 are the same. Set and controlled.

For this reason, the heat load distribution to each heat source machine (inverter turbo chiller 11, turbo chiller 12, exhaust heat utilizing absorption chiller / hot water machine 13) is performed by the flow of chilled / hot water flowing into each heat source machine (cold / warm water flow). That is, it is proportional to the flow rate of the cold / hot water pumps 5a, 5b, 5c.
For example, when the temperature difference between the cold / hot water inlet temperature and the cold / hot water outlet temperature of the heat source device is 5 ° C., the flow rate of the cold / hot water pump 5a is 500 m ³ / h, the flow rate of the cold / hot water pump 5b is 500 m ³ / h, When the flow rate of the pump 5c is 200 m ³ / h, the heat load amounts to be processed by the inverter turbo chiller 11, the turbo chiller 12, and the exhaust heat utilization absorption chiller / heater 13 are 2907 kW, 2907 kW, and 1163 kW, respectively.

  Therefore, in the heat source system S according to the present embodiment, load distribution to the heat source units (inverter turbo chiller 11, turbo chiller 12, exhaust heat utilization absorption chiller / heater 13) determined by the simulation unit 32 is realized. Therefore, the cold / hot water flow rate ratio of the heat source machine is adjusted by inverter-controlling the cold / hot water pumps 5a, 5b, 5c according to a command from the control device 30.

<Distribution of heat load to each heat source unit>
The heat load distribution process to each heat source unit of the heat source system S will be described with reference to FIG. FIG. 2 is a flowchart showing the operation of the control device 30 of the heat source system S according to the first embodiment.

In step S101, the heat load distribution pattern generation means 31 of the control device 30 calculates the heat load amount (heat load demand amount Q ₄ ) to be processed by the heat source system S. Specifically, based on the temperature T _{4in of the} cooling water flowing into the heat load 4, the temperature T _{4out of the} cooling water flowing out of the heat load 4, and the flow rate F _{4 of the} cooling water flowing into the heat load 4. , Calculated by equation (1).
Q ₄ = (T _4out -T _4in ) × F ₄ (1)
In the following description, Q ₄ = 1000 RT (RT: refrigeration ton) will be described.

In step S102, the thermal load distribution pattern generation means 31 of the control device 30, the heat load demand Q ₄ each heat source apparatus (inverter turbo chiller 11, a turbo chiller 12, waste heat utilization absorption chiller 13) Generate a heat load distribution pattern to distribute.

Here, as shown in FIG. 3, the distribution of the heat load amount to each heat source device is made by dividing the heat load demand Q ₄ by an appropriate number n (for example, n = 5) and dividing them into each heat source device. It is done by sorting. First, the heat load distribution pattern generation means 31 divides the heat load demand Q ₄ into several blocks (number of divisions: n) in order to distribute the heat load demand Q ₄ to each heat source machine. In the example shown in FIG. 3, the thermal load demand Q ₄ = (= 1000 RT) is divided into five (n = 5) blocks. Since this blocking is equally divided, the heat load demand Q ₄ is divided into five blocks of 200 RT.

FIG. 4 is a table showing a thermal load distribution pattern generated by the thermal load distribution pattern generation unit 31. Here, the pattern number 401 is a serial number assigned for each thermal load distribution pattern. The thermal load distribution pattern 402 is a set of loads (distributed loads) distributed to each heat source device.
The thermal load distribution pattern generation means 31 generates a thermal load distribution pattern 402 by distributing the blocked thermal load (200RT) to each heat source unit.

Next, the thermal load distribution pattern generation unit 31 obtains the load factor 403 of the heat source unit based on the thermal load distribution pattern 402. Here, the load factor of each heat source machine is obtained by dividing the distribution load of each heat source machine by the maximum cooling capacity.
The maximum cooling capacity of the inverter turbo chiller 11 is 1000 RT, the maximum cooling capacity of the turbo chiller 12 is 500 RT, and the maximum cooling capacity of the exhaust heat utilization absorption chiller / heater 13 is 1000 RT.

Next, the thermal load distribution pattern generation unit 31 determines whether or not the operation is permitted 404.
The operation availability 404 indicates whether or not the heat load distribution pattern 402 can be operated by the heat source system S. “O” indicates that operation is possible and “X” indicates that operation is not possible.
As described above, the heat load distribution to each heat source unit (inverter turbo chiller 11, turbo chiller 12, exhaust heat utilization absorption chiller / heater 13) is performed by the flow rate of chilled / hot water flowing into each heat source unit (cold / warm water). Flow rate), that is, proportional to the flow rate of the cold / hot water pumps 5a, 5b, 5c. For this reason, according to the flow rate control range (for example, from 40% of a rated flow rate to a rated flow rate) of the cold / hot water pumps 5a, 5b, 5c, the load factor range (for example, 40% to 100%) that can be operated also for each heat source machine ). The load factor 0% (distributed load 0RT) indicates that the heat source unit is stopped, and is included in the operable load factor range.

  Thus, the thermal load distribution pattern generation means 31 determines that the thermal load distribution pattern 402 can be operated by the heat source system S when all the heat source units are within the load factor range in which the operation can be performed (the operation availability 404 is determined as “ ”), When at least one heat source unit is outside the operable load factor range, it is determined that the heat load distribution pattern 402 cannot be operated by the heat source system S (operation availability 404 is“ x ”). .

  Returning to FIG. 2, in step S <b> 103, the simulation unit 32 of the control device 30 extracts the thermal load distribution pattern determined to be operable, performs simulation for each thermal load distribution pattern, and evaluates as shown in FIG. 5. A function value 504 is obtained.

  Here, in order to simplify the calculation of the simulation means 32, the evaluation function will be described as the energy consumption of the heat source unit having a large proportion of the energy consumption of the heat source system S as a whole.

First, the simulation means 32 calculates | requires COP of each heat source machine in a thermal load distribution pattern.
FIG. 6 is a graph showing the load factor-coefficient of performance (COP) characteristics of each heat source machine, (a) is the inverter turbo chiller 11, (b) is the turbo chiller 12, (C) is a waste heat utilization absorption chiller / heater 13. As shown in FIGS. 6A to 6C, the characteristics differ depending on the type of heat source device. The simulation means 32 calculates the COP of each heat source unit from the load factor 403 (see FIG. 5) of each heat source unit using the load factor-COP characteristic of each heat source unit (see FIGS. 6A to 6C). Convert.

Next, the simulation means 32 calculates the energy consumption of each heat source machine.
Here, COP is a value obtained by dividing "heat load processed by heat source machine (distributed load of heat source machine)" by "energy consumption of heat source machine". That is, the “energy consumption of the heat source device” is obtained by dividing the “heat load processed by the heat source device (distributed load of the heat source device)” by the COP. The simulation means 32 calculates energy consumption of each heat source unit in the heat load distribution pattern by dividing the distribution load (see FIG. 5) of each heat source unit of the heat load distribution pattern 402 by the COP of each heat source unit. Can do.

Next, the simulation unit 32 calculates a value 504 (see FIG. 5) of the evaluation function (energy consumption of the heat source system S).
Here, the inverter turbo chiller 11 and the turbo chiller 12 consume electric power (secondary energy) as an energy source, whereas the exhaust heat absorption chiller / heater 13 uses gas (secondary energy) as an energy source. Consume. For this reason, the consumption of each heat source unit is multiplied by the conversion factor to the consumption energy of each heat source unit using the inverse of the conversion efficiency from primary energy (for example, oil or natural gas) to secondary energy (electricity, gas) as the conversion factor. The primary energy was obtained, and the primary energy consumption of each heat source machine was added to obtain an evaluation function (energy consumption of the heat source system S).
In this manner, the evaluation function value 504 is calculated for each thermal load distribution pattern 402.

  Returning to FIG. 2, in step S <b> 104, the thermal load distribution pattern extraction unit 33 of the control device 30 extracts the thermal load distribution pattern 402 (see FIG. 5) having the smallest evaluation function value 504 (see FIG. 5).

  In step S <b> 105, the operation control command unit 34 controls the heat source system S so as to realize the heat load distribution pattern extracted by the heat load distribution pattern extraction unit 33.

<Summary>
Thus, since the heat source system S according to the present embodiment is a concentrated heat source system, each heat source unit (inverter turbo chiller 11, by controlling the flow rate of the cold / hot water of the cold / hot water pumps 5 a, 5 b, 5 c is used. It is possible to distribute the heat load to the turbo refrigerator 12 and the exhaust heat absorption chiller / heater 13). The thermal load distribution pattern generation unit 31, the simulation unit 32, and the thermal load distribution pattern extraction unit 33 obtain a thermal load distribution pattern that minimizes the evaluation function. By operating the system S, energy consumption can be reduced.

There are innumerable combinations (thermal load distribution patterns) for distributing the thermal load demand amount Q ₄ in the thermal load distribution pattern generating means 31 to the three heat source machines. If the number of thermal load distribution patterns is large, the number of simulations in the simulation unit 32 at the subsequent stage increases, which increases the calculation time and increases the loss until switching to suitable control.
For this reason, in step S102, by dividing the heat load demand Q ₄ by an appropriate number n (for example, n = 5 as shown in FIG. 3) and distributing them to each heat source unit, the subsequent stage The number of simulations in the simulation means 32 can be reduced, the calculation time can be shortened, and the loss until the control is switched can be reduced.

Note that r is the number of heat source units included in the heat source system S, and n is the number of divisions for dividing the heat load demand Q ₄ (in this embodiment, r = 3 as shown in FIG. N = 5 as shown in FIG. 3), and the total number of thermal load division patterns is
_{n + 1} H _r-1 = (n + r-1)! / (N! ・ (R-1)!)
It becomes. That is, the maximum value of the number of simulations executed in step S103 described later is _{n + 1Hr-1} . For this reason, it is desirable to determine the division number n so as to be the total number of division patterns that can be processed by the control device 30.

  Although the evaluation function used by the simulation unit 32 has been described as the energy consumption of the heat source unit having a large proportion of the energy consumption of the entire heat source system S, the evaluation function is not limited to this, and the cold / hot water pump 5a, The power consumption of the entire heat source system S may be used as an evaluation function in consideration of the power consumption of 5b, 5c, the blower fans 8a, 8b, 8c and the cooling water pumps 9a, 9b, 9c.

  Moreover, when the simulation means 32 calculates | requires COP of each heat source machine, COP of each heat source machine demonstrated as what is uniquely determined by a load factor, as shown to Fig.6 (a)-(c). In detail, it depends on the cooling water inlet temperature of the heat source unit and the wet bulb temperature of the outside air. Therefore, the simulation means 32 may obtain the COP of each heat source machine in consideration of these.

  When the start / stop state of each heat source unit of the heat load distribution pattern simulated by the simulation means 32 is different from the current start / stop state of each heat source unit, the current heat load distribution pattern is changed to the heat load distribution pattern being simulated. In shifting, it will be accompanied by the start and stop of each heat source machine. For example, in the current heat load distribution pattern, the inverter turbo chiller 11 and the turbo chiller 12 are in an operating state, and in the heat load distribution pattern being simulated, the inverter turbo chiller 11 and the exhaust heat utilization absorption chiller / heater 13 are When the heat load distribution pattern in the simulation is applied to the control in the operation state, the operation of the turbo chiller 12 is stopped and the operation of the exhaust heat utilization absorption chiller / heater 13 is accompanied.

In the heat source system S, when the heat source machine starts and stops, a large energy consumption is associated with the heat load to be processed in a transient period until the temperature state of the heat source system S and the state of the heat source machine reach a steady state. In some cases, this leads to a loss of energy consumption.
Therefore, if the on / off state of each heat source unit in the heat load distribution pattern during simulation is different from the current on / off state of each heat source unit, a correction value that allows for the loss of the transient period is added to the evaluation function, A configuration may be adopted in which a loss of energy consumption due to the start and stop of the heat source device is taken into the evaluation function and evaluated by applying a correction coefficient that anticipates the loss of the target period.

<< Second Embodiment >>
Next, the heat source system S according to the second embodiment will be described. The configuration of the heat source system S according to the second embodiment is the same as the configuration of the heat source system S according to the first embodiment (see FIG. 1), and a description thereof will be omitted. On the other hand, in the heat source system S according to the second embodiment, the process of the thermal load distribution pattern generation unit 31 that generates the thermal load distribution pattern (the process of step S102 in FIG. 2) and the process of the simulation unit 32 that calculates the evaluation function ( 2 is different from the heat source system S according to the first embodiment.

<Distribution of heat load to each heat source unit>
The load distribution process to each heat source machine of the heat source system S according to the second embodiment will be described with reference to FIG. Here, the processes of steps S101, S104, and S105 are the same as the processes of the heat source system S according to the first embodiment, and a description thereof is omitted.

In step S102, the thermal load distribution pattern generation means 31 distributes the thermal load demand Q ₄ to each heat source unit (inverter turbo chiller 11, turbo chiller 12, exhaust heat utilization absorption chiller / heater 13). Generate a distribution pattern.

  Here, the thermal load distribution pattern generation means 31 sets the load factor (%) of each heat source unit (inverter turbo chiller 11, turbo chiller 12, exhaust heat utilization absorption chiller / heater 13), for example, every 10%. By changing, a heat load distribution pattern is generated.

  FIG. 7 is a table showing a thermal load distribution pattern generated by the thermal load distribution pattern generation unit 31 in the second embodiment. Here, the pattern number 701 is a serial number assigned for each thermal load distribution pattern (load factor pattern 702). The load factor pattern 702 is a set of load factors of each heat source machine. The operation availability 703 indicates whether or not the load factor pattern 702 can be operated by the heat source system S. The operation availability is indicated by “◯”, and the operation impossible is indicated by “X”. In addition, when the load factor of all the heat source machines is in the load factor range (for example, 0%, 40%-100%) which can be drive | operated, the operation propriety 703 can be drive | operated.

A method for obtaining the thermal load distribution pattern from the load factor pattern 702 will be described with reference to FIG.
For example, the load factor of the heat source unit (inverter turbo refrigerator) 11 is 50%, the load factor of the heat source unit (turbo refrigerator) 12 is 60%, and the load factor of the heat source unit (exhaust heat utilization absorption chiller / heater) 13 is In the case of 60%, as shown in FIG. 8, the heat load processed by each heat source device is obtained from the maximum cooling capacity and load factor of each heat source device. A set of heat loads processed by each obtained heat source machine corresponds to a heat load distribution pattern.

Then, the thermal load distribution pattern generation means 31 includes the thermal load demand amount Q ₄ calculated in step S101 by the total thermal load processed by each heat source unit among the operable load factor patterns 702 (thermal load distribution patterns). Is extracted and sent to the simulation means 32.

  In step S103, the simulation unit 32 performs a simulation on the load factor pattern 702 (thermal load distribution pattern) to obtain the value of the evaluation function.

  Here, the evaluation function of the simulation unit 32 according to the second embodiment will be described as a running cost per hour (yen / h). By setting the evaluation function in this way, the heat source system S according to the second embodiment can be operated so as to minimize the running cost.

  First, the simulation means 32 calculates | requires the energy consumption of the apparatus which comprises the heat source system S. FIG. In the present embodiment, the devices that consume energy are chilled / hot water pumps 5a, 5b, 5c, cooling water pumps 9a, 9b, 9c, blower fans 8a, 8b, 8c, inverter turbo chiller 11, turbo There are a refrigerator 12 and an exhaust heat absorption chiller / heater 13 that consumes gas.

  The gas engine 14 also consumes gas. However, the gas engine 14 is operated according to the power demand of a power demand source (not shown) that exists separately from the heat load demand of the heat load 4, and the gas engine 14 The operation status 14 is input to the control device 30.

The power consumption P [kW] of the cold / hot water pumps 5a, 5b, 5c, the cooling water pumps 9a, 9b, 9c and the blower fans 8a, 8b, 8c is calculated by the following equation (2).
P = PR × (FR / 100) ³ = PR × (F / RF) ³ (2)
Here, PR is power consumption [kW] during rated operation, FR is a flow rate ratio [%], F is a pump flow rate or fan air flow [m ³ / h], and RF is during rated operation. The pump flow rate or the fan airflow [m ³ / h].

FIG. 9A is a table showing the power consumption of the heat source machines (inverter turbo chiller 11 and turbo chiller 12) that consume power, and FIG. 9B is the heat source machine that uses gas (utilizing exhaust heat). It is a table which shows the consumption gas of the absorption-type cold / hot water machine 13).
The energy consumption (power consumption, gas consumption) of each heat source machine (inverter turbo chiller 11, turbo chiller 12, exhaust heat utilization absorption chiller / heater 13) is determined by the load factor [%] of the heat source machine and the cooling water outlet. Calculation is made based on a table with the temperature [° C.] as a parameter. For example, linear interpolation is used for data interpolation.

Thus, the evaluation function (running cost of the heat source system S) AF [yen / h] is given by the following equation (3).
AF = PSUM × PC + GSUM × GC (3)
Here, PSUM is the total power consumption [kW], PC is the power cost [yen / kWh], GSUM is the total consumed gas [m ³ / h], and GC is the gas cost [yen / (m ^3]. ]].

  As described above, the heat source system S according to the second embodiment extracts and extracts the heat load distribution pattern that minimizes the value of the evaluation function (running cost of the heat source system S) by the heat load distribution pattern extraction unit 33. By operating the heat source system S so as to have a heat load distribution pattern, the running cost of the heat source system S can be reduced.

≪Modification≫
The heat source system S according to the present embodiment is not limited to the configuration of the above embodiment, and various modifications can be made without departing from the spirit of the invention.

  In the heat source system S according to the present embodiment, the heat load 4 is a load source as a cold demand (for example, an air conditioner that performs cooling operation), and the heat source device has been described as a configuration that functions as a refrigerator. The heat load 4 is not limited and may be a load source (for example, an air conditioner that performs heating operation) as heat demand, and the heat source device may function as a heater.

Further, the heat source system S according to the present embodiment has been described as a configuration in which heat source machines (refrigerators) having different characteristics are used in combination. However, the present invention is not limited to this, and for example, a heat source machine (refrigerator) having the same characteristics. May be used in combination.
Further, the number of heat source units (refrigerators) included in the heat source system S is not limited to three, and may be two or more than three.

  Further, the heat source apparatus system S according to the present embodiment evaluates the energy consumption of the heat source apparatus (or the energy consumption of the entire heat source system S) in the first embodiment as an evaluation function, and the running per hour in the second embodiment. Although described as evaluating the cost (yen / h), the present invention is not limited to this. The evaluation function may be, for example, the energy consumption of the entire heat source system S, the operating cost of the entire heat source system S, the carbon dioxide emission from the heat source system S, or the like.

The heat source system S according to the present embodiment performs a simulation on the thermal load distribution pattern that can be operated by the simulation unit 32, obtains the value of the evaluation function for all the operable thermal load distribution patterns, and then extracts the thermal load distribution pattern. The means 33 extracts the thermal load distribution pattern that minimizes the value of the evaluation function. However, the present invention is not limited to this. First, the simulation means 32 performs a simulation on one operable heat load distribution pattern. If the value of the evaluation function obtained by the thermal load distribution pattern extracting means 33 is equal to or less than a predetermined value, the thermal load distribution pattern is extracted. The simulation unit 32 may perform a simulation.
According to such a configuration, compared with the case where simulation is performed for all thermal load distribution patterns, the number of simulations until a suitable thermal load distribution pattern is obtained and the calculation time is shortened. Loss before switching can be reduced.

S Heat source system 1 1st heat source unit 2 2nd heat source unit 3 3rd heat source unit 4 Heat load 5a, 5b, 5c Cold / hot water pump (conveyance means)
6a Cold / hot water header 6b Cool / hot water return headers 7a, 7b, 7c Cooling towers 8a, 8b, 8c Blower fans 9a, 9b, 9c Cooling water pump 11 Inverter turbo refrigerator (heat source machine)
12 Turbo refrigerator (heat source machine)
13 Absorption heat absorption chiller / heater (heat source machine)
14 Gas engine 15 Waste water pump 30 Control device (control means)
31 Thermal load distribution pattern generation means (pattern generation means)
32 Simulation means 33 Thermal load distribution pattern extraction means (pattern extraction means)
34 Control command means (operation control means)
21a, 21b, 21c, 22a, 22b, 22c, 23a, 23b, 23c, 24 Inverter 402 Thermal load distribution pattern 504 Evaluation function

Claims (9)

A heat source system comprising at least two or more heat source units, a transport unit that transports a heat transport medium from the heat source unit to a heat load, and a control unit that controls the heat source unit and the transport unit,
The control means includes
Pattern generating means for generating a heat load distribution pattern to each of the heat source units;
Simulation means for calculating an evaluation function of the heat source system in the generated heat load distribution pattern;
Pattern extraction means for extracting one thermal load distribution pattern from the thermal load distribution pattern generated by the pattern generation means based on the evaluation function;
Based on the extracted the heat load distribution patterns, have a, and operation control means for controlling the heat source apparatus and said transport means,
The pattern generation means deletes the heat load distribution pattern when there is the heat source device having a load factor that cannot be operated among the heat load devices among the heat load distribution patterns. Heat source system. The pattern extraction means includes
The heat source system according to claim 1, wherein a heat load distribution pattern that minimizes the evaluation function calculated by the simulation unit is extracted. The operation control means includes
3. The heat source system according to claim 1, wherein the heat source unit and the transfer unit are controlled by the control including inverter control or temperature control so that the extracted heat load distribution pattern is obtained. The simulation means includes
The heat source system according to any one of claims 1 to 3, wherein power consumption of the heat source system is used as the evaluation function. The simulation means includes
The heat source system according to claim 1, wherein a running cost of the heat source system is the evaluation function. The simulation means includes
The heat source system according to any one of claims 1 to 3, wherein the amount of carbon dioxide discharged from the heat source system is used as the evaluation function. The pattern generation means includes
The total load amount of the heat load is divided by a predetermined number, and the heat load distribution pattern is generated by allocating the divided load amount to each heat source unit as a unit. The heat source system according to any one of 6. The pattern generation means includes
The heat source system according to any one of claims 1 to 6, wherein the heat load distribution pattern is generated by changing a load factor of each heat source unit at a predetermined interval. A control method for a heat source system, comprising: at least two or more heat source units; a transfer unit that transfers a heat transfer medium from the heat source unit to a heat load; and a control unit that controls the heat source unit and the transfer unit. ,
The control means includes
Generating step of generating a heat load distribution pattern to each of the heat source units;
Of the heat load distribution patterns generated in the generation step, if there is the heat source unit having a load factor that cannot be operated among the heat source units, a deletion step of deleting the heat load distribution pattern,
As a result of the deletion step, a calculation step for calculating an evaluation function of the heat source system in the heat load distribution pattern that has not been deleted ;
An extraction step of extracting one thermal load distribution pattern from the thermal load distribution pattern generated in the generation step based on the evaluation function calculated in the calculation step;
And a control step of controlling the heat source unit and the conveying means based on the thermal load distribution pattern extracted in the extraction step.

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