WO2014148165A1

WO2014148165A1 - Energy network operation control method and device

Info

Publication number: WO2014148165A1
Application number: PCT/JP2014/053452
Authority: WO
Inventors: 亮介中村; 勉河村; 白石　朋史; 良和石井; 和信森田; 秀世河野; 寿一郎渥美; 隆森知; 雅史坂齊; 真紀子市ヶ谷; 理國友
Original assignee: 株式会社日立製作所
Priority date: 2013-03-19
Filing date: 2014-02-14
Publication date: 2014-09-25
Also published as: JP2014181846A; JP6060014B2; MY173213A

Abstract

Provided is an energy network operation control method and device that varies the consumer-side air conditioning temperature in order to further decrease energy consumption of a heat source device so that, while reducing air conditioning heat demand of the customer to within an air conditioning temperature range that is set taking comfort into consideration, the number of operating heat source devices is reduced or operational efficiency thereof is improved. An operation control method for an energy network that comprises a plurality of heat consumers provided with a plurality of air conditioning apparatuses, and a heat supply plant comprising a plurality of heat source devices, is characterized in that the set temperature for an air conditioning apparatus is variably set on the side of the plurality of heat consumers from the view point of reducing energy consumption of the heat source devices of the heat supply plant, and the number of the plurality of heat source devices in operation is controlled on the heat supply plant side.

Description

Energy network operation control method and device

The present invention relates to a method and apparatus for performing optimum operation of heat source equipment in an energy network composed of a heat supply plant and a heat consumer such as a building.

In recent years, global warming prevention has become an urgent issue, and it is required to reduce energy-derived CO ₂ emissions. In this regard, in the manufacturing industry, energy shocks have been almost flat, with the oil shock taking the lead in actively promoting energy saving through modification of manufacturing processes, introduction of high-efficiency energy saving equipment, fuel conversion etc.

However, energy consumption in the manufacturing sector remains high, at about 40% in Japan. In addition, in the housing and business sectors, energy consumption is increasing year after year due to the spread of lifestyles that demand comfort and convenience.

In order to achieve further energy saving and CO ₂ emission reductions in the future, active use of renewable energy, mutual use of electricity and heat, effective use of energy, and control of consumers' energy consumption It is required to do.

As a specific application example to realize these problems, there is an energy network composed of a heat supply plant and a heat consumer such as a building. As a conventional technology for performing energy saving and CO ₂ reduction on the heat supply plant side that supplies heat to consumers in the energy network, for example, as shown in Patent Document 1, an operation control apparatus that optimally operates the number of heat source devices Are known.

Patent No. 4173973

FIG. 5 shows an example of a conventional general energy network configuration. The energy network comprises a heat supply plant 1 and a plurality of heat consumers 15 such as buildings. The heat supply plant may be any type of cooling and heating, but here a case of using water as a heat medium and supplying cold water will be described.

Among them, heat source equipment such as a plurality of refrigerators 2 and a water pump 3 are installed in the heat supply plant 1 on the side of supplying heat, and a plurality of heat demands of the chilled water 10 cooled by the respective refrigerators 2 Supply to the house 15 side. In order to control the cold water supplied by the heat supply plant 1, the heat source equipment operation control device 13 is installed, and the heat source equipment operation control device 13 takes in the cold water water supply temperature, the cold water return temperature, etc. from the

temperature detectors

6, 7 The operation control of the number of heat source devices such as the refrigerator 2 and the water pump 3 is performed. The heat demander 15 is a building or the like, and heat is generally supplied from a heat supply plant to a plurality of buildings to constitute a district cooling and heating system or the like.

The customer 15 is provided with a heat exchanger 4 for receiving cold heat from the cold water 10 supplied from the heat supply plant 1, and the cold water 11 is supplied from the heat exchanger 4 to each air conditioner 5 via the water pump 8. Each customer 15 arbitrarily sets the air conditioning set temperature 9 of each room, and supplies the air 12 heat-exchanged by the air conditioning equipment 5 to each room to perform cooling.

The customer 15 is provided with an air conditioning control device 14 for temperature control. The air conditioning control device 14 generally has a portion for controlling the air conditioning of the entire building (or each floor of the building) and a portion for controlling the air conditioning of each room, and in FIG. The part of the apparatus which sets temperature 9 arbitrarily is shown. The air conditioning of each room is performed by an indoor temperature control circuit provided on a wall or the like, and the temperature setting by the occupant is generally performed manually.

The cold water 10 warmed by the heat exchanger 4 at the customer 15 is returned to the heat supply plant 1, cooled again, and circulated and used between the customer 15 and the heat supply plant 1.

Here, in the example of the prior art shown in FIG. 5, the system of the reception facility of the customer 15 who receives the thermal energy supplied from the heat supply plant 1 is an indirect connection system via the heat exchanger 4. Also, there are two types of direct connection methods as another method, one is a direct connection method in which the heat medium (cold water, hot water, steam) to be supplied is used as it is in the air conditioner 5, and the other is supply It is a bleed-in system in which the forward heat transfer medium (cold water, hot water) and the return heat transfer medium from the air conditioner 5 are mixed. Although FIG. 5 shows an example of the indirect connection method, it may be a direct connection method.

In the heat supply plant 1 disclosed in Patent Document 1, in order to save energy and reduce CO ₂ emissions by reducing the power and fuel consumed by the heat source equipment, a plurality of heat source equipment are operated according to the heat demand on the demand side. It is carried out. Specifically, the number operation of the heat source equipment is determined from the heat quantity based on the water supply temperature, the return temperature and the water supply flow rate of the heat medium of the heat source equipment.

In the heat supply plant 1 of patent document 1, the refrigerator 2 is operated so that the heat demand required by all the consumers 15 may be satisfy | filled. The necessary heat supply amount Q (W) is the water temperature Ts (° C.) of the cold water 10 sent from the heat supply plant 1, the return temperature Tr (° C.), the water flow rate W (m ³ / s) from the total refrigerator 2 The density _{w w} (kg / m ³ ) of the cold water 10 and the specific heat C _Pw (J / kg / ° C.) are used to calculate the equation (1).
[Equation 1]
Q = _{w w} C _Pw W (TsTr) (1)
Here, in the case of cold water, since the amount of heat supply Q is a negative value according to the equation (1), the amount of cold heat is represented by (−Q).

The refrigerator is controlled so that the water supply temperature Ts becomes constant. When the water supply flow rate W is controlled to be constant, the return temperature Tr changes in the heat exchanger 4 according to the air-conditioning cold heat amount. In addition, when the return temperature Tr is controlled to be constant, the flow rate is controlled by the flow control valve of the heat exchanger 4, and the water flow rate W changes. Therefore, the amount of cold heat (-Q) supplied from the refrigerator is automatically controlled to match the amount of cold air required by the customer.

An example of the method of operating the number of refrigerators in this case is shown in FIG. FIG. 6 shows from the top the air conditioning set temperature Td of the customer, the air conditioning cold energy (-Q), the overall coefficient of performance (total COP: coefficient of performance) of the heat source device (refrigerator), the energy consumption of the heat source device (refrigerator) Is shown. The horizontal axis shows the time of day. Further, the outside air temperature rises to a peak at, for example, noon (time T6 in FIG. 6), and thereafter decreases.

Of these quantities, the room temperature Td of the topmost customer is generally constant (for example, 26 degrees). In addition, the cold water water supply temperature Ts is assumed to be operated to maintain, for example, 7 degrees.

It is known that the total heat demand (air conditioning cold heat amount) of consumers changes mainly in conjunction with the outside air temperature. As mentioned earlier, the outside air temperature rises to a peak at noon and then falls. The number operation control of the refrigerator 2 accompanying the temperature rise in this case is performed by the following method.

First, in the time-series change of the second stage air conditioning cold heat amount (−Q) from the top of FIG. 6, the solid line is the air conditioning cold heat amount at the reference temperature, which fluctuates due to the increase or decrease of the outside air temperature change. The dimmed portion indicates the supplyable cold energy of the refrigerator.

In this case, the air conditioning cold heat amount increases due to the rise of the outside air temperature from time T1, the air conditioning cold heat amount coincides with the maximum heat supply amount of one refrigerator at time T2, and the outside air temperature rises thereafter. After time T2, cooling is insufficient in one refrigerator, and rising of cold water supply temperature or return temperature is detected, or air conditioning cold heat is compared with the maximum amount of heat supplied from the operating refrigerator. The first refrigerator is activated. A similar under-cooling condition also occurs at time T5, and the third refrigerator is activated.

On the other hand, after the time T6 (12 o'clock) when the outside air temperature starts to decrease, the air-conditioning cold heat amount decreases. At time T7, since the air-conditioned cold heat at the reference temperature shown by the solid line decreases to the same extent as the maximum cold heat given by the operation of two refrigerators, the third refrigerator is stopped. At time T10, since the air-conditioned cold energy at the reference temperature shown by the solid line decreases to the same extent as the maximum cold energy given by one refrigerator operation, the second refrigerator is stopped. Immediately before the step-up of the refrigerator at time T2 and T5, and immediately after the step-down of the refrigerator at time T7 and T10, the refrigerator is almost in the rated operation state, but in other time periods it is the partial load operation .

An example of the load factor of the turbo refrigerator (the ratio of the amount of heat supply to the rated heat supply) and the efficiency of the refrigerator (COP: coefficient of performance) is shown in FIG. FIG. 4 shows an example of the energy consumption characteristic of the heat source equipment whose abscissa represents the load factor and the ordinate represents the coefficient of performance COP of one turbo refrigerator. According to this, assuming that the COP when the load factor is 100% is 6, when the load factor is 66.7%, the COP is about 5.4, and when the load factor is 50%, the COP is about 4.7 Show a tendency to

The overall COP shown in the third stage of FIG. 6 shows the result when the above operation control is carried out, and immediately after the stage increase of the refrigerator at time T2 and immediately before the stage decrease of the refrigerator at time T10, the refrigerator The load factor for one unit will be 50%, and the total COP will be about 4.7. Further, immediately after the stage increase of the refrigerator at time T5 and immediately before the stage reduction of the refrigerator at time T7, the load factor of one refrigerator is 66.7%, and the total COP is approximately 5.4.

Here, although the example of the turbo refrigerator is shown in FIG. 4 and FIG. 6, the same tendency is shown also in the case of other heat source devices such as an absorption type refrigerator and a heat pump.

Generally, the energy consumption efficiency of the heat source equipment changes with the load factor. Therefore, in the conventional heat source equipment operation, the heat source equipment operating according to the heat demand is shared with the heat demand and supplied, so that each heat source equipment is not operated at the highest efficiency condition, especially low In the case of operating at a load factor, the operating efficiency is lowered, so there is a problem that the energy saving and CO ₂ emission reduction effects are smaller than in the case of operating at a high efficiency.

Also, in the conventional operation control of heat source equipment, energy saving and CO ₂ emission reduction were carried out by performing optimal operation of heat source equipment to the heat demand required by customers, but in the future, further energy saving And in order to realize the reduction of CO ₂ emissions, it is necessary to carry out the optimum operation of the heat demand control of the customer and the heat source equipment on the heat supply side in cooperation.

The present invention has been made in view of the problems of the prior art as described above, and in order to further reduce the energy consumption of the heat source equipment, while reducing the air conditioning heat demand of the customer within the set air conditioning temperature range, Provided is an operation control method and apparatus for an energy network that changes the air conditioning temperature of a customer so as to reduce the number of operating heat source devices or improve the operation efficiency.

From the above, the present invention is a method for controlling the operation of an energy network comprising a heat supply plant having a plurality of heat source devices and a plurality of heat consumers having a plurality of air conditioning facilities, the plurality of heat consumers On the side, the set temperature of the air conditioner is variably set from the viewpoint of reducing the energy consumption of the heat source equipment of the heat supply plant, and on the heat supply plant side, the number of operating heat source equipment is controlled.

From the above, the present invention is an operation control apparatus of an energy network comprising a heat supply plant including a plurality of heat source devices, and a plurality of heat consumers including a plurality of air conditioners,
Air conditioning measurement data input unit, room temperature upper limit / lower limit decision unit, air conditioning operation control plan unit and air conditioning operation command unit for control of heat consumers on multiple heat consumers The temperature is set variably in terms of reducing the energy consumption of the heat source equipment of the heat supply plant,
Heat source equipment measurement data input unit of heat supply plant, supplied heat quantity calculation unit, number-of-operations determination unit, heat source equipment operation control plan unit, and heat source equipment operation command unit for control on the heat supply plant side Control of the number of operating units

Achieve energy saving and CO ₂ reduction of the entire energy network by changing the air conditioning temperature of the customer to reduce the energy consumption of the heat source equipment while reducing the air conditioning heat demand of the customer within the set air conditioning temperature range It is possible to provide a method and apparatus for controlling the number and load factor of heat source equipment to be

The figure which shows the structure of the energy network which concerns on a present Example. The figure which shows the concrete apparatus structure of the control apparatus in a present Example. The figure which shows each part state when the driving | operation of one Example of this invention is implemented. The figure which shows an example of the energy consumption characteristic of a heat-source apparatus. The figure which shows an example of a general energy network structure. The figure which shows an example of the operating method of the refrigerator in a general energy network. The figure which shows the heat load model in the consumers, such as a building. The figure which shows the outline | summary of the conventional comfort parameter PMV. The figure which shows each part state when the driving | operation of one Example of this invention is implemented.

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 shows the configuration of an energy network according to an embodiment of the present invention. Comparing FIG. 1 with the conventional energy network of FIG. 5, the configuration of the heat supply system 1 and the customer 15 remains unchanged.

Also in this case, a plurality of refrigerators 2 are installed in the heat supply plant 1, and the cold water 10 generated by each refrigerator is sent to each customer 15 by each water pump 3. The customer 15 is provided with a heat exchanger 4 for receiving cold heat from the cold water 10 supplied from the heat supply plant, and the cold water 11 is sent from the heat exchanger 4 to each air conditioner 5. The air 12 thus supplied is supplied to each room to perform cooling.

Here, in the embodiment of the present invention shown in FIG. 1, the system of the reception facility of the customer 15 who receives the heat energy supplied from the heat supply plant 1 is an indirect connection system via the heat exchanger 4. Also, there are two types of direct connection methods as another method, one is a direct connection method in which the heat medium (cold water, hot water, steam) to be supplied is used as it is in the air conditioner 5, and the other is supply It is a bleed-in system in which the forward heat transfer medium (cold water, hot water) and the return heat transfer medium from the air conditioner 5 are mixed. Although FIG. 1 shows an example of the indirect connection method, it may be a direct connection method.

In the present embodiment, control device configurations for controlling the heat supply system 1 and the customer 15 are different. A heat source equipment operation control device 13 for controlling the heat supply system 1 and an air conditioning-heat source equipment cooperation control device 20 for controlling the air conditioning control device 14 for controlling the customer 15 in association with each other are provided. In the present embodiment, the heat source equipment operation control device 13, the air conditioning control device 14, and the air conditioning-heat source device cooperation control device 20 are connected by the information network 16 and share information.

A specific controller configuration in this embodiment is shown in FIG. In FIG. 2, the air conditioning-heat source equipment cooperation control device 20 includes an air conditioning-heat source equipment cooperation control planning unit 21, a heat source equipment operation control planning unit 221, and an air conditioning operation control planning unit 231. Controls the heat source operation control planning unit 221 and the air conditioning operation control planning unit 231 in cooperation with each other.

On the heat source device operation control planning unit 221 side, the heat source device measurement data input unit 222 acquires measurement data regarding the operating state of the heat source device 2 of the heat supply plant 1, the water pump 3 and the like. What is actually acquired is the supply temperature (cold water supply water temperature) Ts of the cold water 10 supplied from the heat supply plant, the return temperature Tr, the water supply flow rate W from all the refrigerators, the start / stop state of the heat source equipment 2 and the like.

The heat quantity calculation unit 223 of the heat source equipment operation control planning unit 221 performs the above (1) based on the water supply temperature Ts of the cold water 10 supplied from the heat supply plant 1, the return temperature Tr, and the water supply flow rate W from all the refrigerators. The total cold demand (air conditioning cold heat) (-Q) is calculated by the equation.

The operation number determination unit 224 of the heat source device operation control planning unit 221 determines the operation number of heat source devices based on the total cold energy demand (−Q). As this premise, since the maximum cold energy of each heat source equipment is known from the rated capacity of each refrigerator etc., the total maximum cold energy calculated by the current operation heat source equipment and the total cold energy demand obtained by the equation (1) The supply and demand balance is determined by the comparison of -Q), and then the heat source equipment to be started or stopped is determined, and the number of units to be operated is set.

Based on the above information, the heat source equipment operation control planning unit 221 judges from the balance of supply and demand by the change of the water supply temperature Ts or the comparison of the maximum cold heat of the heat source equipment and the total cold demand (-Q). Determine the time of increase of equipment. The time of stage reduction of the heat source equipment is obtained by comparing the total maximum amount of cold heat from the operating heat source equipment when the stage reduction is performed and the predicted total cold energy demand (−Q).

In response to the processing result of the heat source device operation control plan unit 221, the heat source device operation command unit 225 instructs the heat source device whose heat source device control plan unit 221 decides to increase or decrease the stage to start and stop. put out.

On the other hand, the air conditioning measurement data input unit 232 on the air conditioning operation control planning unit 231 side acquires the operation information and the room temperature data of the air conditioner 5 from all the air conditioners 5 of the customers managed by itself.

The reference temperature, the allowable upper limit temperature, and the allowable lower limit temperature determination unit 233 set the reference temperature, the allowable upper limit temperature, and the allowable lower limit temperature based on the specifications and conditions of each room.

The air conditioning operation control plan unit 231 acquires operation data of each heat source facility, and controls the room temperature of each room in consideration of the air conditioning measurement data.

The air conditioning operation command unit 234 instructs each air conditioning control device 14 the air conditioning operation condition determined by the air conditioning operation control plan unit 231.

In the air conditioning-heat source equipment cooperation control device 20 of the present invention, the heat source equipment operation control planning unit 221 and the air conditioning operation control planning unit 231 perform coordinated operation according to the command signal given by the air conditioning-heat source equipment cooperation control planning unit 21.

The concept of the coordinated operation of the heat source equipment operation control planning unit 221 and the air conditioning operation control planning unit 231 by the air conditioning-heat source equipment cooperation control planning unit 21 added by the present invention in the air conditioning-heat source equipment cooperation control device 20 Explain.

FIG. 7 shows a heat load model in a customer 15 such as a building. As shown in this figure, many forms of heat are applied to the room 17 of the building. Part of the heat applied to the room 17 of the building is from the outside, for example, ventilation heat of entry q _V which enters the building by ventilation, window heat passing through the surface of the window by solar radiation q _G , and the like wall throughflow heat q _W caused by contact. Further, as things generated inside the building, there are equipment heat generation q _E emitted from equipment such as lighting and personal computer, and human body heat generation q _P emitted from the resident himself.

On the other hand, there is heat supplied from a customer 15 such as a building. This is the air conditioning heat load q _A, doing conditioning of buildings the room 17 by being supplied by the air conditioning equipment 5. In the building heat load model of FIG. 7, the equation (2) is established between the sum of the applied heat _{k k} q _k (= q _v + q _G + q _W + q _E + q _P ) and the supplied heat q _A .
[Equation 2]
CC _P V (dT / dt) = q _V + q _G + q _W + q _E + q _P + q _A = _{k k} q _k + q _A (2)
In the equation (2), 左 C _P V (dT / dt) on the left side is the rate of change in heat of the building room 17, ρ is the air density (kg / m ³ ), and C _P is the specific heat of air (J / kg / C), V is the volume of the room (m ³ ), dT / dt represents the temperature change per unit time. In addition, when the value of q _A is positive, it means heating, and when it is negative, it means cooling.

In the present embodiment, since processing using a computer is performed, equation (3) is obtained by modifying equation (2).
[Equation 3]
T _i = T _i ^* + (Σ _k q _ki ^* + q _Ai ^* ) Δt / ρC _P V _i (3)
In this equation, symbol i means any room, and * means the value before Δt. Here, the heat quantity Q to be supplied by the heat source plant is the sum of the air conditioning heat loads q _Ai of all rooms of a plurality of consumers. Although Σ _k q _ki and q _Ai use values before Δt in equation (3), they may be calculated using values after Δt.
[Equation 4]
_{_{Q = Σ i q Ai (4}} )
Here, the size of q _Ai is, for example, distributed in proportion to the volume V of each room or the total Σ _k q _k of the heat load of the room.

Set the cold water heat quantity (-Q) to reduce the consumption energy of the heat source equipment while reducing the air conditioning cold energy of the customer within the set air conditioning temperature range using the relationship between the equations (3) and (4) and, by changing the air-conditioning temperature of the customer, realizing energy saving · CO ₂ reduced energy network.

Although FIG. 3 shows the state of each part when the operation of the present invention is carried out, the above-mentioned idea is clearly shown. The state of each part in FIG. 3 indicates the air conditioning set temperature Td, the air conditioning cold heat amount (-Q), the overall coefficient of performance COP, and the consumption energy of the heat source equipment in order from the top. In this figure, in order to facilitate understanding, the air conditioning equipment and operation method of all rooms are the same.

In this embodiment, the reference temperature and the allowable lower limit temperature are 26 ° C., and the allowable upper limit temperature is 28 ° C. The air conditioning set temperature is controlled within this temperature range so as to reduce the energy consumption of the refrigerator.

The transition of time-series processing in operation and state quantities of each part at that time will be described with reference to the method A of this embodiment with reference to FIG.

First, an air conditioner and one refrigerator in each room are started from time T1, and the air conditioning set temperature is a reference temperature (26 ° C.). As time passes, the air-conditioning cold energy increases with the rise of the outside air temperature, and at time T2, the air-conditioning cold energy reaches the maximum cold energy of one refrigerator. In the conventional method, the number of refrigerators is increased to two at time T2, whereas in method A, which is the present embodiment, the air-conditioning cold heat is maintained at the maximum cold heat of one refrigerator to increase the number of refrigerators In order to suppress the stage, the air conditioning set temperature is increased.

Since the air conditioning set temperature reaches the allowable upper limit temperature (28 ° C.) at time T3, the number of refrigerators is increased to two. From time T3 to T4, the air-conditioning set temperature is decreased to the reference temperature by maintaining the air-conditioning cold heat amount as the maximum cold heat amount of the two refrigerators. At time T4 to T5, the air conditioning set temperature is maintained at the reference temperature, and at time T5, the air conditioning cold heat amount reaches the maximum cold heat amount of two refrigerators. From time T5 to T7, the air conditioning set temperature is increased in order to maintain the air conditioning cold heat amount as the maximum cold heat amount of the two refrigerators to suppress an increase in the number of stages of the refrigerator.

Next, the outside air temperature decreases at time T6, and the air-conditioning cold heat amount also starts to decrease. From time T7 to T8, the air conditioning cold energy is maintained at the maximum cold energy of the two refrigerators to lower the air conditioning set temperature to the reference temperature. The room temperature is maintained at the reference temperature from time T8. Here, in the case where the number of refrigerators is reduced from two to one, it is possible to maintain the air-conditioning cold heat at the maximum cold heat of one refrigerator and to set the air-conditioning set temperature below the allowable upper limit temperature. And reduce the stage of the refrigerator from two to one at time T9.

From time T9 to T10, the air conditioning cold heat is maintained at the maximum cold heat of one refrigerator to increase the air conditioning set temperature. From time T10 to T11, the air conditioning cold energy is maintained at the maximum cold energy of one refrigerator to lower the air conditioning set temperature. During time T11 to T12, if the air conditioning set temperature is maintained at the reference temperature, the amount of heat generated by the air conditioning decreases with the passage of time, and the operation of the air conditioner and the refrigerator is stopped at time T12.

According to the above operation, since the air conditioning set temperature is the reference temperature in each of the time periods T1 to T2, T4 to T5, T8 to T9, and T11 to T12, the air conditioning cold heat is the maximum of the activated refrigerator It is smaller than the amount of cold heat, and the refrigerator is in a state of partial load operation. Therefore, the total COP is smaller than the maximum COP (6). On the other hand, in each of the time zones from time T2 to T4, T5 to T8, and T9 to T11, since the refrigerator is in rated operation, the total COP becomes maximum COP (6).

With regard to the heat source equipment consumption energy in FIG. 3, in the method A, since the air conditioning set temperature is increased from time T2 to T3 to suppress an increase in the number of stages of the refrigerator, the energy consumption of the refrigerator is reduced compared to the conventional method. ing. On the other hand, at time T3 to T4, in the method A, since the system is operated at the rated load of the refrigerator, the energy consumption of the refrigerator is increased as compared with the conventional method. However, at time T2 to T4, the required air conditioning cold energy is smaller because the air conditioning set temperature is higher in method A than in the conventional method, and the total COP of the refrigerator is high. The total energy consumption of the aircraft is reduced. Similarly, also at time T5 to T8 and time T9 to T11, the total energy consumption of the refrigerator is smaller in the method A than in the conventional method.

Note that, in order to execute the operation shown in FIG. However, as a heat source device, there are a heat source device that generates cold water and a heat source device that generates steam or hot water.
The description of the embodiments so far has been made with the heat source device for producing the former cold water in mind. Moreover, FIG. 3 is also illustrated on the premise.

Therefore, in the following description, with reference to FIG. 3, it is clarified that the situation is different while the cases are separated regarding the measures in the case of operating the heat source device generating cold water and the case of the heat source device generating hot water. While explaining.

First, at time T2 in FIG. 3, in the conventional method, the heat source equipment should be increased from one to two in the conventional method, and in the present invention, operation is performed by controlling the room temperature Td within a predetermined upper and lower temperature range. It is possible to suppress an increase in the number of heat source devices inside.

When raising the stage using a heat source device that generates cold water, the increase can be suppressed by controlling the room temperature at or below the upper limit temperature so as to be equal to or less than the maximum cold heat supply amount of the heat source device in operation. On the other hand, assuming that the stage reduction is performed, in the case of stage reduction using the heat source apparatus that generates cold water, the maximum cold heat supply amount of the heat source apparatus after the stage reduction at time T9 in FIG. Step-down can be promoted by controlling the room temperature below the upper limit temperature.

On the other hand, when raising the stage using heat source equipment that generates steam or hot water, the temperature increase is controlled by controlling the room temperature above the lower limit temperature so as to be equal to or less than the maximum heat supply of the operating heat source equipment. can do. When reducing the stage using heat source equipment that generates steam or hot water, promote the reduction by controlling the room temperature above the lower limit temperature so as to be equal to or less than the maximum heat supply of the heat source equipment after the stage reduction. be able to.

Furthermore, according to the characteristics of FIG. 3, the concept of control in the operation control device of the energy network of the present invention is shown. First, when the preset temperature Td of each room reaches the upper limit temperature at time T3 in FIG. 3, the heat source equipment for generating cold water is increased to be equal to or less than the maximum cooling heat supply amount of the heat source equipment in operation at time T3 to T4. The set temperature Td of each room is lowered to the reference temperature.

On the other hand, when using heat source equipment that generates steam or hot water, the set temperature Td of each room reaches the lower limit temperature in the scene of time T3 in FIG. The set temperature Td of each room is raised to the reference temperature so as to be equal to or less than the maximum heat supply amount of the heat source device in operation in the time zone corresponding to the time T3 to T4.

In addition, when the set temperature Td of each room reaches the upper limit temperature at time T10 in FIG. 3, the set temperature of each room is set to be equal to or less than the maximum cooling energy supply amount of the heat source device generating cold water in operation T10 to T11. Decrease Td to the reference temperature.

On the other hand, when using a heat source device that generates steam or hot water, the set temperature Td of each room reaches the lower limit temperature in the scene of time T10 in FIG. 3 and therefore the time corresponding to the subsequent times T10 to T11 The set temperature Td of each room is raised to the reference temperature so as to be equal to or less than the maximum heat supply amount of the heat source device in operation in the zone.

Thus, when there is a possibility to increase or decrease the heat source equipment, the air conditioning thermal load can be reduced by changing the air conditioning set temperature within the allowable temperature range, and the heat source equipment increase suppression and reduction in stages are promoted. Energy consumption can be reduced by minimizing the number of operating heat source devices.

Furthermore, according to the characteristic of FIG. 9, the reference temperature, the upper limit, and the lower limit temperature of the air conditioning are determined based on the comfort index.

As described above, by variably controlling each air conditioning set temperature, it is possible to reduce the energy consumed by the heat source equipment and realize energy saving and CO ₂ emission reduction.

For example, in a district heating and cooling system, there are often a plurality of heat consumers such as buildings for one heat supply plant. Also, taking up the building itself, it is customary to have multiple air conditioning units.

Among these heat consumers, there are also facilities such as hospitals that are required to maintain a constant temperature. In the present invention, it is not recommended to variably set the temperature including the above circumstances.

Therefore, on the heat demander side, it is necessary to consider the distribution of the heat supply amount. In the distribution, the necessary heat amount is preferentially supplied (load distribution) to the special circumstances such as a hospital, and the remaining equipment may perform variable setting according to the heat demand.

As another embodiment of the present invention, a method of using PMV as an example of the comfort index in the reference temperature, the allowable upper limit temperature, and the allowable lower limit temperature determination unit 233 of FIG. 2 will be shown.

PMV (Predicted Mean Vote) is a comfort index adopted in ISO-7730 of the following document.
ISO7730: 2005, Ergonomics of the thermal environment-Analytical determination and interpretation of thermal comfort using calculation of the PMV and PPD indices and local thermal comfort criteria
FIG. 8 shows an overview of the comfort index PMV. First, as input data when evaluating PMV, the following quantities in the room 17 are obtained by detection, analysis, or setting.

These are room temperature ta, humidity rh, radiation temperature tr, room air velocity vs, metabolic rate M, dressing amount Icl. Among these, a constant value is usually set and input for the wind speed vs, the metabolic amount M, and the dressing amount Icl in the room. For the room temperature ta and the humidity rh, measured values are used. The radiation temperature tr is evaluated based on the measurement value of the glove thermometer, but there is also a method of evaluating it using an indoor air conditioning temperature analysis.

These pieces of information are input to Fanger's comfort equation shown in equation (5) and converted into PMV values. The value of PMV is given as -3 to +3, and when PMV = 0, it is reported that 95% of the students feel comfortable. Also, according to ISO7730, the comfortable range is -0.5 to +0.5.

The evaluation equation of PMV is shown in equation (5).
[Equation 5]
PMV = L (0.303 exp (-0.036 M) + 0.028) (5)
However, L = (MW) EdEsEreCreR-C
Here, M is a metabolic rate, W is a mechanical work amount, Ed is an insensitive steaming amount, Es is an evaporation heat loss amount by perspiration, Ere is a latent heat loss amount by respiration, Cre is a sensible heat loss amount by respiration, R is The amount of radiant heat loss, C indicates the amount of convective heat loss.

The method B which is air conditioning-heat source equipment cooperation control using PMV which is one example of the present invention is explained below. The basic control method of method B is the same as method A shown in FIG. 3, but when evaluating the reference temperature, the allowable upper limit temperature, and the allowable lower limit temperature, evaluation is performed using PMV, and the reference temperature, the allowable upper limit Temperature and allowable lower limit temperature change with time depending on conditions.

The transition of time-series processing in operation and state quantities of each part at that time will be described with respect to the method B of the present embodiment with reference to FIG. First, one air conditioner and refrigerator in each room are activated from time T1, and the air conditioning set temperature is set to, for example, a reference temperature based on PMV = 0. As time passes, the air-conditioning cold energy increases with the rise of the outside air temperature, and at time T2, the air-conditioning cold energy reaches the maximum cold energy of one refrigerator.

In the method C in which the reference temperature is controlled based on PMV = 0, the number of refrigerators is increased to two at time T2, whereas in the method B according to the present embodiment, the air-conditioning cold energy is the maximum of one refrigerator The air conditioning set temperature is increased in order to maintain the amount of cold heat and to suppress an increase in the number of stages of the refrigerator.

Since the air conditioning set temperature reaches the allowable upper limit temperature based on, for example, PMV = 0.5 at time T3, the number of stages of the refrigerator is increased to two. From time T3 to T4, the air-conditioning set temperature is decreased to the reference temperature by maintaining the air-conditioning cold heat amount as the maximum cold heat amount of the two refrigerators. At time T4 to T5, the air conditioning set temperature is maintained at the reference temperature, and at time T5, the air conditioning cold heat amount reaches the maximum cold heat amount of two refrigerators.
From time T5 to T7, the air conditioning set temperature is increased in order to maintain the air conditioning cold heat amount as the maximum cold heat amount of the two refrigerators to suppress the stage increase of the refrigerator.

Here, the outside air temperature decreases at time T6, and the air-conditioning cold heat amount also starts to decrease. From time T7 to T8, the air conditioning cold energy is maintained at the maximum cold energy of the two refrigerators to lower the air conditioning set temperature to the reference temperature. The room temperature is maintained at the reference temperature from time T8.

Here, in the case where the number of refrigerators is reduced from two to one, it is possible to maintain the air-conditioning cold heat at the maximum cold heat of one refrigerator and to set the air-conditioning set temperature below the allowable upper limit temperature. And reduce the stage of the refrigerator from two to one at time T9.

In each time zone from time T1 to T2, T4 to T5, T8 to T9, and T11 to T12, the air conditioning set temperature is the reference temperature, so the air conditioning cold heat is smaller than the maximum cold heat of the activated refrigerator, The machine is in partial load operation. Therefore, the total COP is smaller than the maximum COP (6). On the other hand, in each of the time zones from time T2 to T4, T5 to T8, and T9 to T11, since the refrigerator is in rated operation, the total COP becomes maximum COP (6).

As for the heat source equipment consumption energy of FIG. 9, in the method B, since the air conditioning set temperature is increased at time T2 to T3 to suppress an increase in the number of stages of the refrigerator, the energy consumption of the refrigerator decreases compared to the method C. ing. On the other hand, at time T3 to T4, in the method B, since the operation is performed at the rated load of the refrigerator, the energy consumption of the refrigerator is increased compared to the method C. However, at time T2 to T4, the required air conditioning cold heat is small because the air conditioning set temperature is higher in method B than in method C, and furthermore, since the total COP of the refrigerator is high, refrigeration at time T2 to T4 The total energy consumption of the aircraft is reduced. Similarly, also at time T5 to T8 and time T9 to T11, the total energy consumption of the refrigerator is smaller in method B than in method C.

Furthermore, in the conventional air conditioning operation for cooling, as shown in the diagram of the air conditioning set temperature in FIG. 9, the room temperature is controlled at a constant value, so the room tends to be too cold and energy consumption tends to be large. In method B and method C, since the reference temperature is calculated at each time using the comfort index PMV, an appropriate air conditioning set temperature is obtained, and the average temperature is higher than in the conventional method. Energy can be reduced.

As described above, when the air conditioning set temperature is changed within the range of the reference temperature based on the comfort index PMV and the allowable upper limit temperature, it is possible to further save energy and reduce CO ₂ emissions compared to the conventional method.

In an embodiment of the present invention, a heat source equipment operation control planning unit comprising a heat source equipment measurement data input unit, a heat supply quantity calculation unit, an operation quantity determination unit and a heat source equipment operation command unit, an air conditioning measurement data input unit for a heat consumer An air conditioning-heat source equipment cooperation control device comprising an air conditioning control planning unit having a reference temperature, an allowable upper limit temperature, an allowable lower limit temperature determination unit and an air conditioning operation command unit, and an air conditioning-heat source equipment cooperation control planning unit linking these Information on the operating state of the heat source equipment of the supply plant is taken in, and the set temperature of each room is controlled so as to reduce the energy consumption of each heat source equipment.

According to the above-described method, it is possible to provide an optimum operation control method and apparatus of a heat supply plant which minimize energy consumption and CO ₂ emission.

Save energy by controlling the customer air conditioning temperature in an energy network that mutually interchanges the power and heat used in an area consisting of a heat supply plant and an energy demander or in an industrial park where multiple manufacturing plants are located The present invention can provide an optimum operation method and apparatus of a heat supply facility which realizes reduction of CO ₂ emissions.

DESCRIPTION OF SYMBOLS 1 ... Heat supply plant, 2 ... Refrigerator, 3 ... Water pump of a refrigerator, 4 ... Heat exchanger of a demander, 5 ... Air conditioning equipment of a demander, 6 ... Cold water water temperature, 7 ... Cold water return temperature, 8 ... Water exchanger pump of heat exchanger, 9 ... Air conditioning set temperature, 10 ... Cold water from heat source equipment, 11 ... Cold water of heat exchanger, 12 ... Air from air conditioning equipment, 13 ... Heat source equipment operation control device, 14 ... Air conditioning control device , 15 ... consumer, 16 ... information network, 17 ... room

Claims

An operation control method of an energy network comprising a heat supply plant including a plurality of heat source devices and a plurality of heat consumers including a plurality of air conditioning units,
The plurality of heat consumers set the set temperature of the air conditioner variably in view of reducing the energy consumption of the heat source equipment of the heat supply plant,
A method of controlling an operation of an energy network, comprising controlling the number of operating heat source devices on the side of the heat supply plant.
The energy network operation control method according to claim 1,
The set control temperature of the air conditioning equipment at the heat consumer side is variably set within a predetermined temperature range.
The operation control method of the energy network according to claim 2, wherein
In the case of increasing the number of heat source devices, an operation control method of an energy network characterized by suppressing the increase of heat source devices in operation by controlling the room temperature within a predetermined temperature range.
The operation control method of the energy network according to claim 2, wherein
In the case of reducing the temperature of the heat source equipment, an operation control method of an energy network characterized by promoting temperature reduction of the heat source equipment in operation by controlling a room temperature within a predetermined temperature range.
The operation control method of the energy network according to claim 3, wherein
When increasing the number of heat source devices that generate cold water among the heat source devices, the room temperature is equal to or lower than the allowable upper limit temperature and not less than the reference temperature so that the cooling energy supply amount of the heat source devices is equal to or less than the maximum cooling energy supply amount An operation control method of an energy network characterized by suppressing an increase in speed by controlling in a range.
The operation control method of an energy network according to claim 3,
When increasing the number of heat source devices that generate steam or hot water among the heat source devices, room temperature is higher than the allowable lower limit temperature and the reference temperature so that the heat supply amount of the heat source devices becomes equal to or less than the maximum heat supply amount of the heat source devices in operation. An operation control method of an energy network characterized by suppressing an increase in a stage by controlling in the following range.
The operation control method of an energy network according to claim 4, wherein
When reducing the heat source equipment that generates cold water among the heat source equipment, the room temperature is equal to or lower than the allowable upper limit temperature and the reference temperature so that the cold heat supply amount of the heat source equipment becomes equal to or less than the maximum cold heat supply amount of the heat source equipment. An operation control method of an energy network characterized by promoting reduction of steps by controlling within the above range.
The operation control method of an energy network according to claim 4, wherein
When reducing the heat source equipment that generates steam or hot water among the heat source equipment, the room temperature is equal to or higher than the allowable lower limit temperature so that the heat supply quantity of the heat source equipment becomes equal to or less than the maximum heat supply quantity of the heat source equipment after reduction. An operation control method of an energy network characterized by promoting step-down by controlling in a range below a reference temperature.
The energy network operation control method according to claim 1,
The operation control method of an energy network, wherein the set temperature of the air conditioning is determined based on a comfort index.
The operation control method of an energy network according to claim 9,
The driving control method of an energy network characterized in that the comfort index uses PMV (Predicted Mean Vote: predicted mean thermal sensation report).
An operation control apparatus of an energy network comprising a heat supply plant including a plurality of heat source devices and a plurality of heat consumers including a plurality of air conditioning units,
The plurality of heat consumers set the set temperature of the air conditioner variably in view of reducing the energy consumption of the heat source equipment of the heat supply plant,
An operation control device for an energy network, wherein the heat supply plant side controls the number of operating heat source devices.
An operation control apparatus of an energy network comprising a heat supply plant including a plurality of heat source devices and a plurality of heat consumers including a plurality of air conditioning units,
An air conditioning measurement data input unit, an allowable upper limit temperature / allowable lower limit temperature determination unit of a plurality of heat consumers, an air conditioning operation control plan unit, and an air conditioning operation command unit for control on the plurality of heat consumers. Setting the set temperature of the air conditioner variably in terms of reducing energy consumption of the heat source equipment of the heat supply plant,
The heat source equipment measurement data input unit of the heat supply plant, the heat quantity calculation unit, the operation quantity determination unit, the heat source equipment operation control plan unit, and the heat source equipment operation command unit for control on the heat supply plant side An operation control device for an energy network, comprising controlling the number of operating heat source devices.
The operation control device of the energy network according to claim 11, wherein
The set temperature of the air conditioning equipment on the heat consumer side is variably set within a predetermined temperature range,
When the heat source equipment is increased or decreased, the operation control of the energy network characterized by suppressing the increase of the heat source equipment in operation or promoting the reduction of the heat source equipment by controlling the room temperature within a predetermined temperature range. apparatus.
In the energy network operation control device according to claim 11,
An operation control apparatus of an energy network, wherein the set temperature of the air conditioning includes an allowable upper limit temperature and an allowable lower limit temperature, and a reference temperature set between them, and is determined based on the comfort index.