JP6150525B2 - Heat supply system - Google Patents

Description

  The present invention relates to a heat supply system, and more particularly to a heat supply system that effectively utilizes unused energy.

In recent years, from the viewpoint of CO2 reduction and energy saving improvement, the effective use of unused energy represented by seawater heat, river water heat, sewage heat, underground cooling heat, high-temperature air exhaust heat, etc. has attracted attention. It has been proposed (for example, Patent Document 1).
Conventionally, when unused energy is directly used as a heat source of a heat supply system, the heat utilization system is generally configured to be fixed so as to be supplied to a predetermined application according to a temperature zone. For example, if the unused energy source is a low temperature zone, it is configured for cooling, and if it is a high temperature zone, it is configured for heating.

  However, in an office building where the temperature range required for heat load processing varies from season to season, if the heat utilization system is configured in a fixed manner, there will be times when unused energy cannot be utilized. As an example, a high temperature energy source for heating is not required in summer, and a low temperature energy source for cooling is not required in winter. In such a conventional heat utilization system, it is difficult to make maximum use of unused energy.

JP 2012-202578 A

  The present invention is for solving such problems, and provides a technique for transferring heat in the heat supply system so as to maximize the amount of unused energy used in the entire system. .

The gist of the present invention is as follows. That is, the heat supply system according to the present invention is:
(1) A heat supply system that performs heat interchange between a plurality of heat supply systems each having an independent heat source,
Heat supply system A (hereinafter, system A) capable of supplying heat only to other systems without using unused energy as a heat source and supplying heat to the system,
Heat supply system B that can supply heat only in the system, and can receive heat from other systems without supplying heat to other systems, and / or
Heat supply system C (hereinafter referred to as system C) capable of supplying heat to the system and other systems and receiving heat from other systems;
In accordance with a predetermined switching condition, an intersystem heat interchange control system D that controls heat interchange between the heat supply systems,
It is characterized by comprising.

(2) In the invention of (1), the system A is a system A1 that uses unused cold energy as a heat source,
The system B is constituted by a system B1 capable of receiving cold heat from the system A1 and receiving heat from the system C1.
The system C is configured by a system C1 capable of supplying the system B1 with the heat generated by the cooling power supply in the system and receiving the heat from the system A1,
The inter-system heat interchange control system D is
Cold supply (D1) from system A1 to system B1
Supply of cold from system A1 to system C1 (D2), and supply of heat from system C1 to system B1 (D4),
Cold supply (D3) from system A1 to system C1
Heat supply from system C1 to system B1 (D5),
It is a means which makes it possible to switch appropriately.

(3) In the invention of (1), the system A is composed of a system A1 that uses unused cold energy as a heat source and a system A2 that uses unused high-temperature energy as a heat source,
The system B is capable of receiving cold heat from the system A1 and high temperature heat from the system A2, respectively,
A system B3 capable of receiving high-temperature heat from the system A2, and
The inter-system heat interchange control system D is
Cold supply from system A1 to system B2 (D21), Cold supply from system A1 to system C1,
Supply of heat from the system C1 to the system B1, or / and supply of heat from the system A1 to the system B1,
Is a means that can be switched as appropriate.

(4) In the invention of the above (1), the system A is configured by a system A3 that uses unused cold energy as a heat source, and a system A4 that uses unused thermal energy as a heat source,
The system B is composed of systems B3 and B4 that can receive cold heat from the system A3 and can receive heat from the system A4, respectively.
The inter-system heat interchange control system D is
Parallel cooling supply from system A3 to system B4 and system B5 (D31, D32),
Series cold supply (D33) from system A3 to system B4 and system B5,
Cold supply from system A3 to system B5 (D34), and supply of heat from system A4 to system B4 (D35),
Parallel cold supply from system A4 to system B4 and system B5 (D36, D37),
Series cold supply from system A4 to system B4 and system B5 (D38),
Is a means that can be switched as appropriate.

  According to each of the above inventions, there is an effect that heat exchange is performed between different systems by cascade use of heat medium, direct use of cold / hot water, and waste heat recovery by a heat exchanger, and maximum utilization of unused energy becomes possible. is there.

  In addition, the heat exchange efficiency can be improved by changing the flow path of the cold / hot water by operating the valve of the cold / hot water pipe, and changing the use form of the heat exchanger (series or parallel, the direction in which the heat medium flows). effective.

  In addition, the cooling / heating water flow path can be changed by operating the chilled / hot water piping, so that one heat exchanger can handle cooling loads or heating loads, reducing initial costs compared to installing multiple heat exchangers. There is an effect that is possible.

It is a figure which shows the structure of the heat supply system 1 which concerns on 1st embodiment. It is a figure which shows the circuit structure of the heat accommodation control system D1. It is a figure which shows the circuit structure of the heat accommodation control system D2. It is a figure which shows the circuit structure of the heat interchange control system | strain D3. It is a figure which shows the circuit structure of the heat accommodation control system D4. It is a figure which shows the circuit structure of the heat interchange control system | strain D5. It is a figure which shows the aspect of heat interchange from system | strain A1-> system | strain B1. It is a figure which shows the aspect of the heat interchange to system | strain A1-> system | strain C1, and system | strain C1-> system | strain B1 in the heat supply system 1. FIG. It is a figure which shows the aspect of the heat interchange to the system | strain C1-> system | strain B1 same as the above. It is a figure which shows the aspect of the heat accommodation from system | strain A1-> system | strain C1 same as the above. It is a figure which shows the structure of the heat supply system 20 which concerns on 2nd embodiment. It is a figure in the heat supply system 20 which shows the aspect of heat interchange from system | strain A1-> system | strain B1 and system | strain A2-> system | strain B2. It is a figure which shows the aspect of heat interchange to system | strain A2-> system | strain B1 and system | strain B2 same as the above. It is a figure which shows the aspect of heat interchange from system | strain system A2-> system | strain B1 same as the above. It is a figure which shows the structure of the heat supply system 30 which concerns on 3rd embodiment. It is a figure which shows the aspect (the 1) of the heat | fever interchange from system | strain A3-> system | strain B3, B4 in the heat supply system 30. FIG. It is a figure which shows the aspect (the 2) of the heat | fever interchange from system | strain A3-> system | strain B3, B4 in the heat supply system 30. FIG. It is a figure which shows the aspect of heat interchange to system | strain A2-> system | strain B1 and system | strain B2 same as the above. It is a figure which shows the aspect of the heat interchange from the system A3-> system B3 same as the above, and the system A4-> system B4. It is a figure which shows the aspect (the 1) of the heat interchange to system | strain A4-> system | strain B3 and B4 same as the above. It is a figure which shows the aspect (the 2) of the heat | fever accommodation from system A4 same as the above-> systems B3 and B4.

  Hereinafter, each embodiment of an air conditioner with an outside air introduction cooling function according to the present invention will be described in more detail with reference to FIGS. In order to avoid redundant description, the same components are denoted by the same reference numerals in the respective drawings. Needless to say, the scope of the present invention is described in the claims and is not limited to the following embodiments.

<First embodiment>
This embodiment corresponds to the above-described invention (2). Referring to FIGS. 1 (a) and 1 (b), a heat supply system 1 according to this embodiment includes three heat supply systems A1, B1, and C1 each having an independent heat source.

System A1 is a geothermal heat utilization system, which includes a steel pipe pile 1b, a heat exchanger 1a, a circulation pump 1c, and a pipe group connecting these, taking cold heat from a steel pipe pile 1b buried in the ground, and exchanging heat. Heat is supplied to the systems B1 and C1 by the device 1a.
The system B1 is an air conditioning system that switches between cooling and heating depending on the season, such as office air conditioning, for example, a heat source machine (heat pump chiller) 2a that generates cold / hot water, an outgoing header 2b, a return water header 2d, and a plurality of air conditioning loads (for example, AHU, etc.) 2c, a circulation pump 2e for circulating cold / hot water, etc. are provided as main components, and the cold / hot water generated by the heat source unit 2a is branched by the header 2b and supplied to each air conditioning load 2c. Has been.

The system C1 is an air conditioning system that performs only cooling throughout the year, such as data center air conditioning, for example, a heat source device (for example, a packaged air conditioner) 3a, a cooling load (for example, a server group) 3b, and heat exchange disposed in a plurality of stages. The devices 3c and 3d are provided as main components.
With this configuration, the cooling heat Q1 generated by the air conditioner 3a is supplied to the cooling load 3b, the generated high-temperature exhaust heat Q2, Q2 'is given to other systems in the heat exchangers 3c, 3d, and the residual exhaust heat Q3 is supplied to the air conditioner. It returns to 3a and is comprised so that it may cool again.

  Next, referring to FIG. 1 (b), the heat interchange control system D1 is a system connecting the systems A1 and B1, and includes a heat exchanger 1a, a forward water header 2b, an air conditioning load 2c, a return water header 2d, and an on-off valve. It is comprised by V1V4, the circulation pump 1c, and the piping group which connects these. With this configuration, it is possible to reduce the load on the heat source device 2a by supplying the cold heat extracted in the system A1 to the air conditioning load 2c of the system B1.

  Referring to FIG. 1 (c), the heat interchange control system D2 is a first system connecting the systems A1 and C1, and includes a heat exchanger 1a, on-off valves V2, V10, a heat exchanger 3d, a four-way valve V5, It is comprised by V9, the circulation pump 1c, and the piping group which connects these. With such a configuration, in the heat exchanger 3d, the cold heat from the system A1 and the exhaust heat Q2 'are heat-exchanged to reduce the load on the heat source unit 3a.

With reference to FIG.1 (d), the heat interchange control system D3 is the 2nd system which connects between system A1 and C1, and heat exchanger 1a, on-off valve V2, V10, heat exchanger 3d, four-way in order of a flow path. The valve V5, the heat exchanger 3c, the on-off valve V7, the four-way valve V5, the on-off valve V9, the circulation pump 1c, and a pipe group connecting them. With this configuration, it is possible to reduce the load on the heat source unit 3a by exchanging heat between the cold heat from the system A1 and the exhaust heat Q2 in the heat exchanger 3c and further exchanging heat between the residual cold heat and the exhaust heat Q2 ′ in the heat exchanger 3d. It is said.

  With reference to FIG.1 (e), the heat interchange control system D4 is the 1st system which connects between system | strain B1 and C1, and heat exchanger 3c, the four-way valve V5, the on-off valve V8, the circulation pump 2e, in order of a flow path. The heat source device 2a, the outgoing water header 2b, the air conditioning load 2c, the return water header 2d, the on-off valve V6, the heat exchanger 3d, and a piping group connecting them. With this configuration, the heat exchanger 3c exchanges heat between the exhaust heat Q2 and the return water from the system B1, thereby reducing the load on the heat source device 2a.

  With reference to FIG.1 (f), the heat interchange control system D5 is the 2nd system which connects between system | strain B1 and C1, and heat exchanger 3c, four-way valve V5, heat exchanger 3d, on-off valve V11 in order of a flow path. , Four-way valve V5, on-off valve V8, circulation pump 2e, heat source unit 2a, outgoing water header 2b, air conditioning load 2c, return water header 2d, on-off valve V6, heat exchanger 3c, and a piping group connecting them. ing. With this configuration, the heat exchangers 3c and 3d exchange heat between the exhaust heat Q2 and the return water from the system B1, thereby reducing the load on the heat source unit 2a.

  In addition, the heat interchange control of the heat supply system 1 is a control that controls each on-off valve and the circulation pump by performing a heat amount calculation based on a temperature sensor (not shown) provided in the piping path and these measured values. (Not shown).

The heat supply system 1 is configured as described above, and next, each aspect of heat exchange between systems in the present embodiment will be sequentially described with reference to FIGS. 1 (g) to 1 (j).
<(1-1) Heat interchange from system A1 to system B1>
Referring to FIG. 1 (g), this mode assumes a summer cooling peak time, and system A1 is operated by operating heat interchange control system D1 in a state where both systems B1 and C1 are in cooling operation. The cold heat is transferred to the system B1. In addition, although the illustration of each on-off valve and the circulation pump is omitted in the figure (the same applies to FIG. 1 (g) and subsequent figures), the operating state of each on-off valve is as shown in Table 1. The circulation pumps 1c and 2e are both in an operating state. In the case of this aspect, the exhaust heat of the system | strain C1 is not utilized.
With the above control, the cold energy of the system A1 is accommodated to the system B1 side, and the load on the heat source unit 2a of the system B1 can be reduced.

<(1-2) System A1 → System C1, System C1 → Heat interchange to System B1>
With reference to FIG.1 (h), this aspect assumes the winter season, the system C1 is air_conditionaing | cooling operation and system | strain B1 is heating operation. The operation of the heat interchange control system D2 allows the cold heat of the system A1 to be heat-conducted to the cooling of the system C1, and the operation of the heat interchange control system D4 allows the warm heat of the system C1 to be heat-conducted to the heating of the system B1. Table 2 shows the operating states of the on-off valves in this embodiment. The circulation pumps 1c and 2e are both in an operating state.
By the above-described control, it is possible to improve the energy saving performance of the heat source units 2a and 3a.

<(1-3) System C1 → Heat interchange to system B1>
With reference to FIG.1 (i), this aspect assumes the severe winter season, the system | strain C1 is a cooling operation and system | strain B1 is a heating operation state. With the operation of the heat interchange control system D5, the heat generated in the system C1 is transferred to the heating of the system B1. This embodiment is characterized in that the heat exchangers 3c and 3d are cascaded. By using the cascade, it is possible to increase the return temperature of the hot water to the heat source unit 2a and to lower the air temperature of Q3. The operating state of each on-off valve in this embodiment is as shown in Table 3. The circulation pump 1c is stopped and the circulation pump 2e is in an operating state.
With the above control, it is possible to reduce the load on the heat source units 2a and 3a.

<(1-4) System A1 → Heat interchange from system B1>
With reference to FIG.1 (j), this aspect assumes an intermediate period or night, and the system | strain C1 is a cooling operation, and system | strain B1 is a state without load. By operating the heat interchange control system D3, the cold energy of the system A1 is heat-conducted to the cooling system C1. Table 4 shows the operating state of each on-off valve in this embodiment. The circulation pump 1c is in operation and the circulation pump 2e is in a stopped state.
With the above control, the cold energy of the system A1 is accommodated to the system C1 side, and the load on the heat source device 3a can be reduced.

  In the present embodiment, the package air conditioner is used as the heat source device of the system C1 and the exhaust heat from the server room is used. However, the present invention is not limited to this, and the cooling water exhaust heat is used using the water-cooled air conditioner. It can also be set as the aspect which utilizes.

Next, regarding the selection of each of the above heat accommodation modes (1-1 to 1-4), following the table below is effective in terms of energy efficiency. In the table, T1: return temperature to the heat source unit 2a,
T2: air temperature of the heat exchanger 3c, T3: air temperature of the heat exchanger 3d (see FIG. 1A).

<Second Embodiment>
Next, another embodiment of the present invention will be described. This embodiment corresponds to the above-described invention (3). With reference to Fig.2 (a), the heat supply system 20 which concerns on this embodiment is comprised by three heat supply system A1, A2, B2, B3 which has an independent heat source, respectively.
Since the systems A1 and B3 are the same heat supply systems as the systems A1 and B2 of the first embodiment described above, redundant description is omitted. The system A2 is an unused high-temperature energy utilization system, which takes out, for example, solar heat collection, high-temperature ground heat, industrial wastewater, etc., and supplies heat to other systems with a heat exchanger.

The system B3 is a heat supply system that supplies a hot water supply load (high temperature water) throughout the year using, for example, a hot water boiler as a heat source machine.
In the figure (the same applies to the following figures), the details of the control valve and the piping system are not shown, but the same as in the first embodiment so as to enable the following heat interchange control control. It has a configuration.

The heat supply system 20 is configured as described above, and hereinafter, each aspect of heat exchange between the air conditioning systems in the present embodiment will be sequentially described with reference to FIGS. 2 (b) to 2 (d). .
<Heat exchange from system A1 to system B2 (D21), system A2 to system B3 (D22)>
This mode assumes the summer cooling peak time, and heat-conducts the cooling heat of the system A1 to the system B2 and the high-temperature heat of the system A2 to the system B3. The system B2 performs cooling operation, and the system B3 supplies hot water. The circulation path of the cold / hot water in this embodiment is shown as in FIG.
With the above control, the cooling energy is interchanged from the system A1 to the system B2, so that the energy saving performance of the heat source device 2a can be improved. Moreover, the high-temperature heat of system | strain A2 can be interchanged by system | strain B3, and the energy-saving improvement of the heat-source equipment 22a can be aimed at.

<Heat interchange from system A2 to system B2 (D24), system B3 (D23)>
This mode is a control mode assuming early winter / early spring season, and system B2 is in heating operation and system B2 is supplied with hot water. The circulation path of the cold / hot water in this embodiment is shown as in FIG. The feature of this control is that cascade use is performed when the high-temperature heat of the system A2 is thermally transferred to the systems B2 and B3. That is, high-temperature heat is given to the system B3 side by the heat exchanger 21b, and the heat that has become lower than this is given to the system B2 by the heat exchanger 21c.
With the above control, heat accommodation corresponding to the temperature level is possible, and energy saving performance of the heat source units 2a and 22a can be improved.

<Heat interchange from system A2 to system B2 (D25)>
This mode is a control mode assuming winter, and system B2 is in a heating operation, and system B3 is in a hot water supply stop state. The feature of this control is that all the high-temperature heat of the system A2 is thermally transferred to the system B2. The circulation path of the cold / hot water in this embodiment is shown as FIG. By such control, the energy saving performance of the heat source device 2a can be improved.

<Third embodiment>
This embodiment corresponds to the above-described invention (4). With reference to Fig.3 (a), the heat supply system 30 which concerns on this embodiment is comprised by four heat supply system A3, A4, B4, B5 which has an independent heat source, respectively.

  The system A3 is a cold supply system similar to the system A1 of the first embodiment described above. System A4 is an unused thermal energy utilization system that extracts medium temperature exhaust heat of about 30 ° C. such as double skin exhaust heat and void heat collection. The difference from the above-described system A1 is that two heat exchangers are provided and can be used in cascade as described later.

  The systems B4 and B5 are air conditioning systems that switch between cooling and heating according to the seasons, similar to the system B1 of the first embodiment. However, the system B5 is, for example, a radiant air conditioning system using a panel, and has a feature that the outlet temperature of the system B4 is higher than the outlet temperature of the system B4 during cooling, and the outlet temperature of the system B4 is lower during heating.

The heat supply system 1 is configured as described above, and each aspect of heat interchange between systems in the present embodiment will be sequentially described.
<Heat interchange from system A3 to systems B4 and B5 (part 1)>
With reference to FIG. 3 (b), this mode is a heat accommodation mode suitable for the summer cooling peak, and the cooling heat of the system A3 is transferred to the system B4 via the heat exchanger 31c (D31) and the heat exchanger 31b. Thus, the system B5 (D32) is provided for heat interchange. By such control, the cold energy of the system A3 is supplied to the systems B4 and B5, and the load on the heat source units 33a and 34a of the systems B4 and B5 can be reduced.

<Heat interchange from system A3 to systems B4 and B5 (part 2)>
With reference to FIG.3 (c), this aspect is a heat accommodation aspect suitable at the time of a summer cooling peak, and about the point where the cold heat of system | strain A3 is interchanged to the system | strain B4 and B5 side, it is as mentioned above (the 1). Are the same. The difference is that cascade utilization is used for heat accommodation. That is, the cooling heat of the system A3 is given to the system B5 side through the heat exchanger 31b, and the circulating chilled water from the cooling load 34b of the system B5 is cooled again by the heat source unit 34a and supplied to the cooling load 33b of the system B4 ( D33).
With the above control, heat interchange corresponding to the temperature level of each system cooling load is possible, and energy saving performance of the heat source devices 33a and 33b can be improved. Further, by using a plurality of systems as a single system by using the cascade, it is possible to reduce the number of operating D33 circulation pumps and to reduce the conveyance power.

<Heat exchange from system A3 to system B4, system A4 to system B5>
With reference to FIG.3 (d), this aspect is a heat interchange aspect suitable for the conditions which one requires cooling load and the other requires heating load among system | strains B4 and B5. The cold heat of the system A3 is transferred to the system B4 via the heat exchanger 31b (D34), and the hot heat of the system A4 is transferred to the system B5 via the heat exchanger 32c (D35).
By such control, it becomes possible to reduce the cooling load of the system B4 and the heating load of the system B5, and energy saving of the heat source devices 33a and 34a can be achieved.

<Heat interchange from system A4 to systems B4 and B5 (part 1)>
With reference to FIG.3 (e), this aspect is a heat interchange aspect suitable at the time of winter heating, and heat of the system A3 is sent to the system B4 through the heat exchanger 32c (D36), and through the heat exchanger 31b. Each of the systems B5 (D37) is heat-conducted. By such control, the heat of the system A4 is accommodated to the systems B4 and B5, thereby reducing the heating load and saving energy of the heat source devices 33a and 34a.

<Heat interchange from system A4 to systems B4 and B5 (part 2)>
Referring to FIG. 3 (f), this mode is also a heat accommodation mode suitable for winter heating, and the point that the heat of system A4 is accommodated to systems B4 and B5 is the same as (Part 1) described above. is there. The difference is that cascade utilization is used for heat accommodation.
That is, the heat of the system A4 is given to the system B5 via the heat exchanger 32b, and the circulating cold water from the heating load 34b of the system B5 is heated again by the heat source unit 34a and supplied to the heating load 33b of the system B4 ( D38).

  By the above control, heat interchange corresponding to the temperature level of each system heating load is possible, and the energy saving performance of the heat source devices 33a and 33b can be improved. In addition, by using a plurality of systems as a single system by using cascades, the number of circulating pumps of D33 can be reduced and the conveyance power can be reduced.

  The present invention is widely applicable to an air conditioner with an outside air introduction cooling function regardless of the type of heat source, refrigerant, air conditioning system, building structure, and the like.

1, 20, 30... Heat supply system 1a, 3c, 3d, 21b, 21c, 31b, 31c... Heat exchanger 2a, 3a, 22a, 33a. .... Air conditioning load 3a ... Air conditioner 3b ... Cooling loads A, B, C ... Heat supply system D ... Inter-system heat interchange control system V1-V4 , V6 to V11 ... On-off valve V5 ... Four-way valve

Claims (3)

A heat supply system that performs heat interchange between a plurality of heat supply systems each having an independent heat source,
Heat supply system A (hereinafter, system A) capable of supplying heat only to other systems without using unused energy as a heat source and supplying heat to the system,
Heat supply system B that can supply heat only in the system, and can receive heat from other systems without supplying heat to other systems, and / or
Heat supply system C (hereinafter referred to as system C) capable of supplying heat to the system and other systems and receiving heat from other systems;
In accordance with a predetermined switching condition, an intersystem heat interchange control system D that controls heat interchange between the heat supply systems,
And comprising
The system A is a system A1 that uses unused cold energy as a heat source,
The system B is constituted by a system B1 capable of receiving cold heat from the system A1 and receiving heat from the system C1.
The system C is configured by a system C1 capable of supplying the system B1 with the heat generated by the cooling power supply in the system and receiving the heat from the system A1,
The inter-system heat interchange control system D is
Cold supply (D1) from system A1 to system B1
Supply of cold from system A1 to system C1 (D2), and supply of heat from system C1 to system B1 (D4),
Cold supply (D3) from system A1 to system C1
Heat supply from system C1 to system B1 (D5),
Is a means to enable switching as appropriate.
Heat supply system that is characterized in that. A heat supply system that performs heat interchange between a plurality of heat supply systems each having an independent heat source,
Heat supply system A (hereinafter, system A) capable of supplying heat only to other systems without using unused energy as a heat source and supplying heat to the system,
Heat supply system B that can supply heat only in the system, and can receive heat from other systems without supplying heat to other systems, and / or
Heat supply system C (hereinafter referred to as system C) capable of supplying heat to the system and other systems and receiving heat from other systems;
In accordance with a predetermined switching condition, an intersystem heat interchange control system D that controls heat interchange between the heat supply systems,
And comprising
The system A is composed of a system A1 that uses unused cold energy as a heat source and a system A2 that uses unused high-temperature energy as a heat source,
The system B is capable of receiving cold heat from the system A1 and high temperature heat from the system A2, respectively,
A system B3 capable of receiving high-temperature heat from the system A2, and
The system C is configured by a system C1 capable of supplying the system B1 with the heat generated by the cooling power supply in the system and receiving the heat from the system A1,
The inter-system heat interchange control system D is
Cold supply from system A1 to system B2 (D21), Cold supply from system A1 to system C1,
Supply of heat from the system C1 to the system B1, or / and supply of heat from the system A1 to the system B1,
Heat supply system that is characterized in that the appropriate, a means for enabling the switching. A heat supply system that performs heat interchange between a plurality of heat supply systems each having an independent heat source,
Heat supply system A (hereinafter, system A) capable of supplying heat only to other systems without using unused energy as a heat source and supplying heat to the system,
Heat supply system B that can supply heat only in the system, and can receive heat from other systems without supplying heat to other systems, and / or
Heat supply system C (hereinafter referred to as system C) capable of supplying heat to the system and other systems and receiving heat from other systems;
In accordance with a predetermined switching condition, an intersystem heat interchange control system D that controls heat interchange between the heat supply systems,
And comprising
The system A is composed of a system A3 that uses unused cold energy as a heat source, and a system A4 that uses unused thermal energy as a heat source,
The system B is composed of systems B3 and B4 that can receive cold heat from the system A3 and can receive heat from the system A4, respectively.
The inter-system heat interchange control system D is
Parallel cooling supply from system A3 to system B4 and system B5 (D31, D32),
Series cold supply (D33) from system A3 to system B4 and system B5,
Cold supply from system A3 to system B5 (D34), and supply of heat from system A4 to system B4 (D35),
Parallel heat supply from system A4 to system B4 and system B5 (D36, D37),
Series heat supply from system A4 to system B4 and system B5 (D38),
Heat supply system that is characterized in that the appropriate, a means for enabling the switching.

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