JP7529525B2 - Thermal storage type temperature difference battery, combined heat and power supply system, and combined heat and power supply system group - Google Patents

Description

This disclosure relates to a thermal storage temperature difference battery, a combined heat and power supply system, and a group of combined heat and power supply systems.

Traditionally, Japan has adopted an energy supply system that supplies electricity from large-scale centralized power plants, such as nuclear power plants. In recent years, however, from the perspective of stable energy supply and energy conservation, a distributed energy supply system that supplies energy by installing relatively small-scale energy conversion equipment in locations close to energy consumption areas has been attracting attention.

Patent Document 1 describes a district heat and power cogeneration system, which is one form of a distributed energy supply system. In the district heat and power cogeneration system described in Patent Document 1, at least a compressor and a radiator are provided on the side that supplies the heat medium, and a heat exchanger is provided on the side of the demand entity (multiple demand entities in the target area) to which the heat medium is supplied, forming a flow path for the heat medium between the side that supplies the heat medium and the side that is supplied, and constructing a large-scale heat pump cycle for multiple demand entities in the target area. This makes it possible to efficiently meet the demand for heating, cooling, and hot water in the target area with little input energy.

In this configuration, at least the compressor and the heat dissipation device are provided in the shared flow path of the heat medium as shared equipment for multiple consumers, and this simplifies the equipment configuration on each consumer side compared to when these facilities are installed on each consumer side. This makes it possible to reduce or eliminate problems with the installation space and noise of the combined heat and power supply equipment on each consumer side.

JP 2016-61190 A

The purpose of this disclosure is to provide a thermal storage temperature difference battery, which is a new type of battery that generates electricity by utilizing heat media of different temperatures stored in a heat pump cycle, as well as a combined heat and power supply system including the same and a group of combined heat and power supply systems capable of exchanging heat and power with each other.

In order to achieve the above object, a heat storage type temperature difference storage battery according to at least one embodiment of the present disclosure includes:
A compressor for compressing the heat medium;
a first flow path connected to the compressor for allowing the heat medium compressed by the compressor to flow;
A pressure-accumulating, insulated, high-temperature storage tank connected to the first flow path for storing the heat medium supplied from the first flow path;
A second flow path connected to the pressure-accumulating, insulated, high-temperature storage tank for flowing the heat medium that has left the pressure-accumulating, insulated, high-temperature storage tank;
an expansion device provided in the second flow path and configured to reduce the pressure of the heat medium flowing through the second flow path;
a pressure-accumulating, insulated, low-temperature storage tank provided upstream or downstream of the expansion device in the second flow path for storing the heat medium in the second flow path;
a third flow path connected to a downstream side of the second flow path and configured to supply the heat medium that has passed through each of the expansion device and the pressure-accumulating insulated low-temperature storage tank to the compressor;
a temperature difference generator configured to generate electricity by utilizing a temperature difference between the heat medium flowing on the upstream side of the expansion device in the second flow path and the heat medium flowing in the third flow path;
Equipped with.

In order to achieve the above object, a cogeneration system according to at least one embodiment of the present disclosure includes:
The heat storage type temperature difference storage battery;
A fourth flow path connected to the pressure-accumulating, insulated, high-temperature storage tank and configured to supply the heat medium from the pressure-accumulating, insulated, high-temperature storage tank to a consumer at a target site;
Equipped with.

In order to achieve the above object, a group of cogeneration systems according to at least one embodiment of the present disclosure includes:
A group of cogeneration systems including a plurality of the cogeneration systems,
The plurality of cogeneration systems are provided corresponding to a plurality of target sites, respectively;
The group of cogeneration systems further includes an integrated heat and power supply and demand system configured to optimize supply and demand of electric power and heat in the entire plurality of cogeneration systems.

The present disclosure provides a thermal storage temperature difference battery, which is a new type of battery that generates electricity by using heat media of different temperatures stored in a heat pump cycle, as well as a combined heat and power supply system and a group of combined heat and power supply systems that include the same.

1 is a schematic diagram showing a general configuration of a district heat and power cogeneration system 2 (2A) according to one embodiment. 2 is a schematic diagram showing a general configuration of a district heat and power cogeneration system group 4. FIG. 1 is a schematic diagram showing a general configuration of a district heat and power cogeneration system 2 (2B) according to one embodiment. FIG. 4 is a schematic diagram illustrating a circulation flow path 74 and a circulation flow path 76 in the district heat and power cogeneration system 2 (2B) shown in FIG. 3 by thick lines. 1 is a schematic diagram showing a general configuration of a district heat and power cogeneration system 2 (2C) according to one embodiment. FIG. 13 is a schematic diagram showing a modified example of the district heat and power cogeneration system 2 (2B).

Hereinafter, some embodiments of the present disclosure will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of components described as the embodiments or shown in the drawings are merely illustrative examples and are not intended to limit the scope of the invention.
For example, expressions expressing relative or absolute configuration, such as "in a certain direction,""along a certain direction,""parallel,""orthogonal,""center,""concentric," or "coaxial," not only express such a configuration strictly, but also express a state in which there is a relative displacement with a tolerance or an angle or distance to the extent that the same function is obtained.
For example, expressions indicating that things are in an equal state, such as "identical,""equal," and "homogeneous," not only indicate a state of strict equality, but also indicate a state in which there is a tolerance or a difference to the extent that the same function is obtained.
For example, expressions describing shapes such as a rectangular shape or a cylindrical shape do not only refer to rectangular shapes, cylindrical shapes, etc. in the strict geometric sense, but also refer to shapes that include uneven portions, chamfered portions, etc., to the extent that the same effect is obtained.
On the other hand, the expressions "comprise,""include,""have,""includes," or "have" of one element are not exclusive expressions excluding the presence of other elements.

(Outline of district heat and power supply system)
FIG. 1 is a schematic diagram showing a schematic configuration of a district heat and power cogeneration system 2 (2A) according to one embodiment.
The district heat and power cogeneration system 2 shown in Fig. 1 is a system that is constructed so that power generation and heat supply to consumers 100 at a target site can be performed in parallel. The size of the target site may be, for example, an area with a diameter of about 300 to 500 m, or it may be larger or smaller than that. The consumers 100 include at least one of various facilities such as detached houses, collective housing such as condominiums, shopping facilities, factories, and hospitals.

As shown in FIG. 1, the district heat and power cogeneration system 2 includes an electric motor 5, a compressor 6, a first flow path 8, a pressurized insulated high-temperature storage tank 10, a second flow path 12, an expansion turbine 14 (expansion device), a pressurized insulated low-temperature storage tank 18, a third flow path 20, a temperature difference generator 22, a fourth flow path 24, a fifth flow path 26, a sixth flow path 28, a seventh flow path 30, power transmission lines 32-38, a site heat and power supply and demand system 50, a temperature sensor 82, a temperature sensor 84, and a motor control unit 86. Note that in FIG. 1, the heat and power transmission paths are indicated by solid lines and dashed lines, respectively.

The electric motor 5 is connected to the compressor 6, and drives the compressor 6 using power supplied from the site heat and power supply system 50 via the power transmission line 32. The power supplied from the site heat and power supply system 50 to the electric motor 5 may be grid power, may be power supplied from the temperature difference generator 22, or may be power supplied from a generator connected to the expansion turbine 14 (described below), or from various electrical equipment such as an EV, NAS battery, or solar power installed in the consumer 100 via the power transmission line 36. When using grid power as the power supplied from the site heat and power supply system 50 to the electric motor 5, it is desirable to use inexpensive nighttime power.

The compressor 6 is configured to generate a high-temperature, high-pressure heat medium by compressing the medium-temperature, low-pressure heat medium supplied from the third flow path 20 by being driven by the electric motor 5. In another embodiment, the compressor 6 may be driven directly (without being converted into electric power) by a windmill, a waterwheel, or the like instead of the electric motor 5. The heat medium supplied to the compressor 6 from the third flow path 20 is not particularly limited as long as it is a heat medium usable in a heat pump cycle, and may be, for example, CO ₂ , ammonia, propane, butane, or a fluorocarbon alternative. In this specification, the expressions high temperature, medium temperature, and low temperature are used in order from the highest temperature to the lowest pressure as the relative temperature. The expressions high pressure, medium pressure, and low pressure are used in order from the highest pressure to the highest pressure as the relative pressure.

The first flow path 8 is connected downstream of the compressor 6 and is configured to carry the high-temperature, high-pressure heat medium compressed by the compressor 6.

The pressurized, insulated, high-temperature storage tank 10 is connected downstream of the first flow path 8 and is configured to store the high-temperature, high-pressure heat medium supplied from the first flow path 8.

The second flow path 12 is connected to the downstream side of the pressure-accumulating insulated high-temperature storage tank 10, and is configured to supply the heat medium that has left the pressure-accumulating insulated high-temperature storage tank 10 to the high-temperature side of the temperature difference generator 22, the expansion turbine 14, and the pressure-accumulating insulated low-temperature storage tank 18. In some embodiments, in accordance with a command from the site heat and power supply system 50 based on the demand and consumption of heat and electricity by the consumer 100, a part of the high-temperature and high-pressure heat medium stored in the pressure-accumulating insulated high-temperature storage tank 10 is supplied to the consumer 100 via the fourth flow path 24 described below, and a part is introduced to the high-temperature side of the temperature difference generator 22 via the second flow path 12, electricity is generated by the temperature difference with the low-temperature side of the temperature difference generator 22, and electricity is supplied to the consumer 100 via the power transmission line 34 and the power transmission line 35. The heat medium flowing through the second flow path 12 releases heat on the high-temperature side of the temperature difference generator 22 to reduce its temperature. In one embodiment, the high-temperature side of the temperature difference generator 22 functions as a condenser.

The expansion turbine 14 is provided downstream of the temperature difference generator 22 in the second flow path 12 and is configured to reduce the pressure of the medium-temperature, high-pressure heat medium (the medium-temperature, high-pressure heat medium after doing work on the high-temperature side of the temperature difference generator 22) flowing through the second flow path 12. In the example shown in FIG. 1, the expansion turbine 14 is driven by the medium-temperature, high-pressure heat medium flowing through the second flow path 12, and a generator (not shown) connected to the expansion turbine 14 generates electricity. The electricity obtained from the generator connected to the expansion turbine 14 is transmitted to the site heat and power supply system 50 via the power transmission line 33.

The pressure-accumulating, insulated, low-temperature storage tank 18 is provided downstream of the expansion turbine 14 in the second flow path 12 and is configured to store the low-temperature, low-pressure heat medium of the second flow path 12.

The third flow path 20 is connected to the downstream side of the second flow path 12 and is configured to supply the heat medium that has passed through each of the expansion turbine 14 and the pressure-accumulating insulated low-temperature storage tank 18 to the compressor 6 via the low-temperature side of the temperature difference generator 22. In some embodiments, in accordance with a command from the site heat and power supply system 50 based on the demand and consumption of cold and electricity by the consumer 100, a portion of the low-temperature, low-pressure heat medium stored in the pressure-accumulating insulated low-temperature storage tank 18 may be supplied to the consumer 100 via the sixth flow path 28 described below, and a portion may be introduced to the low-temperature side of the temperature difference generator 22 via the third flow path 20, and electricity may be generated by the temperature difference with the high-temperature side of the temperature difference generator 22, and the electricity may be supplied to the consumer 100 via the power transmission line 34 and the power transmission line 35.

The temperature difference generator 22 includes a Seebeck element (thermoelectric element) and is configured to generate electricity by the Seebeck effect using the temperature difference between the high-temperature, high-pressure heat medium flowing upstream of the expansion turbine 14 in the second flow path 12 and the low-temperature, low-pressure heat medium flowing in the third flow path 20. The electricity generated by the temperature difference generator 22 is supplied to the site heat and power supply system 50 via the power transmission line 34. The heat medium flowing in the third flow path 20 absorbs heat on the low-temperature side of the temperature difference generator 22 and is heated. In one embodiment, the low-temperature side of the temperature difference generator 22 functions as an evaporator. The medium-temperature, low-pressure heat medium after doing work in the temperature difference generator 22 in the third flow path 20 is returned to the compressor 6 and compressed again in the compressor 6 to become a high-temperature, high-pressure heat medium.

The fourth flow path 24 is connected downstream of the pressurized insulated high-temperature storage tank 10 and is configured to supply high-temperature and high-pressure heat medium (hot heat supply) from the pressurized insulated high-temperature storage tank 10 to the consumer 100 at the target site of the district heat and power cogeneration system 2. This hot heat may be stored again as heat in the form of hot water, etc. in a hot water storage tank provided in the consumer 100.

The fifth flow path 26 is configured to recover from the consumer 100 the medium-temperature, high-pressure heat medium that has been supplied to the consumer 100 via the fourth flow path 24 and whose temperature has been reduced by performing work on the consumer 100 side. The fifth flow path 26 is connected to a position between the temperature difference generator 22 and the expansion turbine 14 in the second flow path 12, and is configured to supply the medium-temperature, high-pressure heat medium recovered from the consumer 100 to a position between the temperature difference generator 22 and the expansion turbine 14 in the second flow path 12.

The sixth flow path 28 is connected to the downstream side of the pressure-accumulated insulated low-temperature storage tank 18, and is configured to supply (supply cold heat) the low-temperature, low-pressure heat medium that has left the pressure-accumulated insulated low-temperature storage tank 18 from the pressure-accumulated insulated low-temperature storage tank 18 to the consumer 100. When supplying a lower-temperature heat medium, the sixth flow path 28 may be connected to the downstream side of the expansion turbine 14, and the lower-temperature heat medium that has passed through the expansion turbine 14 may be supplied to the consumer 100.

The seventh flow path 30 is configured to recover from the consumer 100 the low-temperature, low-pressure heat medium supplied to the consumer 100 via the sixth flow path 28. The seventh flow path 30 is connected to a position between the temperature difference generator 22 and the compressor 6 in the third flow path 20, and is configured to supply the low-temperature, low-pressure heat medium recovered from the consumer 100 to a position between the temperature difference generator 22 and the compressor 6 in the third flow path 20.

The site heat and power supply and demand system 50 transmits DC power to the electric motor 5 via the power transmission line 32 to drive the electric motor 5. The site heat and power supply and demand system 50 receives DC power via the power transmission line 33 from the electric power generated by a generator (not shown) connected to the expansion turbine 14, and receives DC power from the electric power generated by the temperature difference generator 22 via the power transmission line 34.

The site heat and power supply and demand system 50 is configured to be able to supply DC power received from the generator connected to the expansion turbine 14 via the power transmission line 33 and DC power received from the temperature difference generator 22 via the power transmission line 34 to the consumer 100 at the target site via the power transmission line 35. The site heat and power supply and demand system 50 is configured to be able to receive power generated on the consumer side of the target site (for example, power output from a solar power generation facility, fuel cell, NAS battery, lithium ion battery installed in an electric vehicle used at the target site, etc.) via the power transmission line 36 as DC power.

The site heat and power supply and demand system 50 is configured to be capable of supplying DC power to the integrated heat and power supply and demand system 52 via the power transmission line 37, and is configured to be capable of receiving DC power from the integrated heat and power supply and demand system 52 via the power transmission line 38.

As shown in FIG. 2, the integrated heat and power supply and demand system 52 is configured to optimize the supply and demand of electricity and heat across multiple regional heat and power cogeneration systems 2. The integrated heat and power supply and demand system 52 and the site heat and power supply and demand systems 50 are configured to be able to exchange DC power, and DC power, high-temperature and high-pressure heat medium, and low-temperature and low-pressure heat medium are exchanged between the regional heat and power cogeneration systems 2. In FIG. 2, multiple regional heat and power cogeneration systems 2 are provided corresponding to multiple target sites, respectively, and the multiple regional heat and power cogeneration systems 2 and the integrated heat and power supply and demand system 52 constitute a regional heat and power cogeneration system group 4.

The temperature sensor 82 is provided in the pressure-accumulated, insulated high-temperature tank 10 and is configured to be able to detect the temperature of the heat medium stored in the pressure-accumulated, insulated high-temperature tank 10. The temperature sensor 84 is provided in the pressure-accumulated, insulated low-temperature tank 18 and is configured to be able to detect the temperature of the heat medium stored in the pressure-accumulated, insulated low-temperature tank 18.

The motor control unit 86 may be configured to replenish the high-temperature, high-pressure heat medium to the pressure-accumulating, insulated, high-temperature storage tank 10 by driving the electric motor 5 to operate the compressor 6 when the output of the temperature sensor 82 is equal to or lower than a threshold value. The pressure-accumulating, insulated, high-temperature storage tank 10 may also be provided with a remaining amount sensor (capacity sensor) capable of detecting the remaining amount of heat medium stored in the pressure-accumulating, insulated, high-temperature storage tank 10. In addition, when the remaining amount sensor is provided, the motor control unit 86 may be configured to replenish the high-temperature, high-pressure heat medium to the pressure-accumulating, insulated, high-temperature storage tank 10 by driving the electric motor 5 to operate the compressor 6 when the remaining amount of heat medium in the pressure-accumulating, insulated, high-temperature storage tank 10 detected by the remaining amount sensor falls below a threshold value.

When the output of the temperature sensor 84 is equal to or greater than the threshold value, the motor control unit 86 may drive the electric motor 5 to operate the compressor 6 to replenish the high-temperature, high-pressure heat medium in the pressure-accumulated, insulated high-temperature storage tank 10 and release the high-temperature, high-pressure heat medium from the pressure-accumulated, insulated high-temperature storage tank 10 to the second flow path 12, and generate electricity with the temperature difference generator 22. The pressure-accumulated, insulated low-temperature storage tank 18 may be provided with a remaining amount sensor (capacity sensor) capable of detecting the remaining amount of heat medium stored in the pressure-accumulated, insulated low-temperature storage tank 18. When the remaining amount sensor is provided, the motor control unit 86 may drive the electric motor 5 to operate the compressor 6 to replenish the high-temperature, high-pressure heat medium in the pressure-accumulated, insulated high-temperature storage tank 10 and release the high-temperature, high-pressure heat medium from the pressure-accumulated, insulated high-temperature storage tank 10 to the second flow path 12, and generate electricity with the temperature difference generator 22, when the remaining amount of heat medium in the pressure-accumulated, insulated low-temperature storage tank 18 detected by the remaining amount sensor falls below the threshold value.

In this case, heat is not simply released on the high-temperature side of the temperature difference generator 22, but a low-temperature, low-pressure heat medium is supplied from the pressure-accumulating, insulated, low-temperature storage tank 18 to the temperature difference generator 22 via the third flow path 20, generating electricity in the temperature difference generator 22 and recovering energy. Then, after being used for power generation on the high-temperature side of the temperature difference generator 22 in the second flow path 12, the medium-temperature, high-pressure heat medium is supplied to the expansion turbine 14 to drive the expansion turbine 14, and a generator (not shown) connected to the expansion turbine 14 is operated. The heat medium, which has passed through the expansion turbine 14 and has become low-temperature and low-pressure, is replenished in the pressure-accumulating, insulated, low-temperature storage tank 18.

According to the configuration shown in FIG. 1, a heat pump cycle can be constructed with a heat medium circulation flow path 25 consisting of a compressor 6, a first flow path 8, a pressure-accumulating, insulated high-temperature storage tank 10, a second flow path 12, an expansion turbine 14, a pressure-accumulating, insulated low-temperature storage tank 18, a third flow path 20, and a temperature difference generator 22. Heat pumps usually have a COP of over 3 (=300%), and are extremely efficient, with an efficiency several hundred percent higher than hot water supply using combustion equipment with an efficiency of about 90%. Therefore, a high-temperature, high-pressure heat medium and a low-temperature, low-pressure heat medium can be efficiently generated with a small input of energy.

In addition, the generated high-temperature and high-pressure heat medium and low-temperature and low-pressure heat medium are stored in the pressure-storage and heat-insulating high-temperature storage tank 10 and the pressure-storage and heat-insulating low-temperature storage tank 18, respectively, to store electricity as heat, and the high-temperature and high-pressure heat medium and the low-temperature and low-pressure heat medium and the temperature difference generator 22 can be supplied from the pressure-storage and heat-insulating high-temperature storage tank 10 and the pressure-storage and heat-insulating low-temperature storage tank 18 to generate electricity according to the demand for electricity. This makes it possible to provide a heat storage type temperature difference battery 3, which is a new type of battery that generates electricity using heat media with different temperatures stored in a heat pump cycle. In the configuration shown in FIG. 1, the compressor 6, the first flow path 8, the pressure-storage and heat-insulating high-temperature storage tank 10, the second flow path 12, the expansion turbine 14, the pressure-storage and heat-insulating low-temperature storage tank 18, the third flow path 20, and the temperature difference generator 22 constitute the heat storage type temperature difference battery 3.

This heat storage type temperature difference storage battery 3 can generate electricity with a simpler configuration that utilizes the heat medium in the heat pump cycle, compared to the configuration described in Patent Document 1 (wherein the high-temperature, high-pressure heat medium flowing through the heat pump cycle drives an expansion turbine and generates electricity using a generator connected to the expansion turbine).

In addition, the heat medium generated by the heat pump cycle of the district heat and power combined supply system 2 can be supplied to the consumer 100 at a temperature sufficient for general living (for example, approximately -30°C to approximately 60°C) including hot water supply, heating, cooling, ice storage, etc., and therefore can be utilized as a heat supply source for the district.
Particularly in areas where infrastructure is concentrated, such as compact cities and smart cities, more efficient operation will be possible without being restricted by the distance that heat must travel.

A distributed energy supply system can be realized in which relatively small-scale energy conversion equipment such as a compressor 6 and a temperature difference generator 22 are installed in locations close to the energy consumption area, which offers benefits in terms of stable energy supply and energy conservation.

In general, there is a high demand for cold energy in the summer and a high demand for warm energy in the winter. Some homes use a lot of heat, while others are unoccupied during the day and do not use much heat. Heat demand fluctuates due to a variety of factors, including the environment and lifestyle, and it is undesirable from an energy-saving perspective to release excess heat into the atmosphere as a result of these fluctuations. Like heat, electricity also fluctuates greatly per consumer, but this can be leveled out by managing multiple consumers together. The district heat and power cogeneration system 2 serves as a buffer for fluctuations in the demand for heat and electricity and the amount of power generated by renewable energy sources, and stores excess heat/electricity in a thermal state, making it possible to extract it as electricity as needed using a temperature difference generator 22.

In addition, for example, in order to increase the storage capacity of NAS batteries and lithium ion batteries, the cost tends to increase due to the need to increase the amount of lithium or sulfur, but in the case of this heat storage type temperature difference storage battery 3, the storage capacity can be easily increased by newly installing or expanding the pressurized insulated high-temperature storage tank 10 and the pressurized insulated low-temperature storage tank 18.

In addition, since the temperature difference generator 22 (thermoelectric element) has no moving parts, it has a long life, is highly reliable, and does not generate vibration or noise. The shape of the element of the temperature difference generator 22 (thermoelectric element) can be freely designed. The temperature difference generator 22 generates electricity per unit area several to several tens of times that of solar power generation. Since many of the materials used in the temperature difference generator 22 are metals or semiconductors, they may be subject to oxidative degradation in high temperature environments or due to oxygen, water vapor, etc., but from the perspective of suppressing this oxidative degradation, it is preferable that the heat medium used in the district heat and power cogeneration system 2 be an alternative to fluorocarbons.

In addition, in the temperature difference generator 22, if the amount of hot heat held by the heat medium stored in the pressure-accumulated insulated high-temperature storage tank 10 is not balanced with the amount of cold heat held by the heat medium stored in the pressure-accumulated insulated low-temperature storage tank 18, the temperature difference generator 22 cannot generate electricity efficiently.

In this regard, according to the district heat and power cogeneration system 2 equipped with the above-mentioned temperature sensor 82 and motor control unit 86, when the output of the temperature sensor 82 provided in the pressurized insulated high-temperature storage tank 10 is below a threshold value, the electric motor 5 drives the compressor 6 to replenish the heat energy contained in the heat medium stored in the pressurized insulated high-temperature storage tank 10 (to increase the temperature of the heat medium stored in the pressurized insulated high-temperature storage tank 10), thereby enabling efficient power generation by the temperature difference generator 22.

In addition, according to the district heat and power cogeneration system 2 equipped with the above-mentioned temperature sensor 84 and motor control unit 86, when the output of the temperature sensor 84 provided in the pressure-accumulated insulated low-temperature storage tank 18 is equal to or higher than a threshold value, the electric motor 5 drives the compressor 6 to generate a high-temperature, high-pressure heat medium, which is then cooled by the temperature difference generator 22 and expanded by the expansion turbine 14 to replenish the cold energy held by the heat medium stored in the pressure-accumulated insulated low-temperature storage tank 18 (the temperature of the heat medium stored in the pressure-accumulated insulated low-temperature storage tank 18 is lowered), and therefore the temperature difference generator 22 can generate electricity efficiently.

(Machine learning device)
In some embodiments, as shown in FIG. 1, the integrated heat and power supply and demand system 52 may further include a machine learning device 88 configured to learn the supply and demand trends of power and heat at each of the multiple target sites. In this case, the integrated heat and power supply and demand system 52 is configured to optimize the supply and demand of power and heat in the multiple heat and power cogeneration systems 2 as a whole based on the supply and demand trends of power and heat at each of the multiple target sites learned by the machine learning device 88 (hereinafter simply referred to as the "learning result of the machine learning device 88"). The machine learning device 88 is configured as a computer and includes a storage device including a CPU (processor) not shown, memories such as ROM and RAM, and external storage devices. In addition, the machine learning device 88, the integrated heat and power supply and demand system, and various facilities of the 100 consumers include mutual communication means (whether wired or wireless) necessary for transmitting and receiving data and instruction command signals between them. In the example shown in FIG. 1, the machine learning device 88 is provided in the integrated heat and power supply and demand system 52, but the machine learning device 88 may be provided for each site heat and power supply and demand system 50, or may be provided in other locations.

Based on the learning results of the machine learning device 88, the integrated heat and power supply and demand system 52 may optimize heat supply and demand, for example, to a site among the multiple target sites corresponding to the multiple regional heat and power cogeneration systems 2 that has a particularly high demand for a high-temperature heat medium, by extracting an extremely high-temperature heat medium immediately after compression by the compressor 6 from the first flow path 8 and actively supplying it. Based on the learning results of the machine learning device 88, the integrated heat and power supply and demand system 52 may optimize heat supply and demand, for example, to a site among the multiple target sites corresponding to the multiple regional heat and power cogeneration systems 2 that has a particularly high demand for a low-temperature heat medium (for example, an area with many food factories), by extracting an extremely low-temperature heat medium immediately after expansion by the expansion turbine 14 from the downstream side of the expansion turbine 14 in the second flow path and actively supplying it. Based on the learning results of the machine learning device 88, the integrated heat and power supply and demand system 52 may optimize heat supply and demand, for example, to a site among the multiple target sites corresponding to the multiple regional heat and power cogeneration systems 2 that does not require a high-temperature or low-temperature heat medium, by supplying the heat medium (return heat medium) after work at each site.

Based on the learning results of the machine learning device 88, the integrated heat and power supply and demand system 52 may, for example, control the amount of power generated by the temperature difference generator 22, the amount of power generated by a generator not shown connected to the expansion turbine 14, the drive of the electric motor 5, and the amount of heat stored and the timing of heat storage in each of the pressurized insulated high-temperature storage tank 10 and the pressurized insulated low-temperature storage tank 18 in each of multiple target sites corresponding to multiple regional heat and power cogeneration systems 2 in accordance with the depopulation or overpopulation of the site, thereby avoiding a shortage or oversupply of electricity and heat. In addition, the integrated heat and power supply and demand system 52 may, for example, at each of a number of target sites corresponding to a number of district heat and power cogeneration systems 2, control the amount of power generated by the temperature difference generator 22, the amount of power generated by a generator not shown connected to the expansion turbine 14, the drive of the electric motor 5, and the amount and timing of heat storage in the pressurized insulated high-temperature storage tank 10 and the pressurized insulated low-temperature storage tank 18, based on the learning results of the machine learning device 88 about the amount of fluctuation in power and heat demand due to lifestyles such as the age composition and employment status of people on the site (for example, energy usage time and usage at home), thereby avoiding a shortage or oversupply of power and heat.

Figure 3 is a schematic diagram showing the general configuration of a district heat and power combined supply system 2 (2B) according to one embodiment. In the district heat and power combined supply system 2 (2B) shown in Figure 3, reference symbols common to the respective components of the district heat and power combined supply system 2 (2A) shown in Figure 1 indicate the same components as those of the district heat and power combined supply system 2 (2A) shown in Figure 1 unless otherwise specified, and explanations thereof will be omitted.

The district heat and power cogeneration system 2 (2B) shown in FIG. 3 differs from the district heat and power cogeneration system 2 (2A) shown in FIG. 1 in that it includes a first branch flow path 60, a geothermal heat exchanger 62, a first return flow path 64, a second branch flow path 66, and a second return flow path 68.

The first branch flow path 60 branches off from the second flow path 12 between the temperature difference generator 22 and the expansion turbine 14, and is configured to allow the heat medium supplied from the second flow path 12 to flow to the first heat exchange section 70 or the second heat exchange section 72 of the geothermal heat exchange device 62.

The first heat exchange unit 70 is connected to the first branch flow path 60 and is configured to heat the high-temperature, high-pressure heat medium supplied from the first branch flow path 60 by heat exchange with geothermal heat as unused energy. Note that the first heat exchange unit 70 may be configured to heat the heat medium by heat exchange with unused energy such as factory exhaust heat or waste incineration plant exhaust heat instead of geothermal heat.

The first return flow path 64 is connected to the first heat exchange section 70 and is configured to supply the high-temperature, high-pressure heat medium that has passed through the first heat exchange section 70 between the pressure-accumulating, insulated high-temperature storage tank 10 and the temperature difference generator 22 in the second flow path 12.

In this way, in the district heat and power cogeneration system 2 (2B), a circulation flow path 74 (a circulation flow path consisting of the upper thick line portion of the two thick line portions in Figure 4 and the first heat exchange portion 70) can be formed by a part of the second flow path 12, the first branch flow path 60, the first heat exchange portion 70, and the first return flow path 64.

The second branch flow path 66 branches off from the third flow path 20 between the temperature difference generator 22 and the compressor 6, and is configured to allow the low-temperature, low-pressure heat medium supplied from the third flow path 20 to flow to the first heat exchange section 70 or the second heat exchange section 72 of the geothermal heat exchange device 62.

The second heat exchanger 72 is connected to the second branch flow path 66 and is configured to cool the low-temperature, low-pressure heat medium supplied from the second branch flow path 66 by heat exchange with geothermal heat as unused energy. The second heat exchanger 72 may be configured to cool the heat medium by heat exchange with unused energy such as river water, seawater, sewage water, or snow and ice heat, instead of geothermal heat.

The second return flow path 68 is connected to the second heat exchange section 72 and is configured to supply the low-temperature, low-pressure heat medium that has passed through the second heat exchange section 72 between the pressure-accumulated insulated low-temperature storage tank 18 and the temperature difference generator 22 in the third flow path 20.

In this way, in the district heat and power cogeneration system 2 (2B), a circulation flow path 76 (a circulation flow path consisting of the lower of the two thick line portions in Figure 4 and the second heat exchange portion 72) can be formed by a part of the third flow path 20, the second branch flow path 66, the second heat exchange portion 72, and the second return flow path 68.

In the temperature difference generator 22, if the amount of hot heat held by the heat medium flowing through the second flow path 12 and the amount of cold heat held by the heat medium flowing through the third flow path 20 are not balanced, the temperature difference generator 22 cannot generate power efficiently. In this regard, according to the heat storage type temperature difference battery of the above-mentioned regional heat and power cogeneration system 2 (2B), the heat medium flowing between the temperature difference generator 22 and the expansion turbine 14 in the second flow path 12 is supplied to the first heat exchange section 70 via the first branch flow path 60, heated by heat exchange with geothermal heat in the first heat exchange section 70, and then supplied to between the pressure-storage insulated high-temperature storage tank 10 and the temperature difference generator 22 in the second flow path 12 via the first return flow path 64. Therefore, when the amount of hot heat held by the heat medium flowing through the second flow path 12 is insufficient compared to the amount of cold heat held by the heat medium flowing through the third flow path 20 (when there is a shortage of hot medium), the amount of hot heat of the heat medium flowing through the second flow path 12 can be replenished using geothermal heat, and the temperature difference generator 22 can generate power efficiently.

The heat medium flowing through the third flow path 20 can be supplied to the second heat exchange section 72 via the second branch flow path 66, cooled by heat exchange with geothermal heat in the second heat exchange section 72, and then supplied through the second return flow path 68 to between the pressure-storage insulated low-temperature storage tank 18 and the temperature difference generator 22 in the third flow path 20. Therefore, when the amount of cold energy held by the heat medium flowing through the third flow path 20 is insufficient compared to the amount of hot energy held by the heat medium flowing through the second flow path 12 (when there is a refrigerant shortage), the amount of cold energy of the heat medium flowing through the third flow path 20 can be replenished by using unused energy, and electricity can be efficiently generated by the temperature difference generator 22.

In the configuration shown in Figures 3 and 4, the compressor 6, the first flow path 8, the pressure-accumulating insulated high-temperature storage tank 10, the second flow path 12, the expansion turbine 14, the pressure-accumulating insulated low-temperature storage tank 18, the third flow path 20, the temperature difference generator 22, the first branch flow path 60, the first heat exchanger 70, the first return flow path 64, the second branch flow path 66, the second heat exchanger 72, and the second return flow path 68 constitute the heat storage type temperature difference storage battery 3.

Figure 5 is a schematic diagram showing the general configuration of a district heat and power combined supply system 2 (2C) according to one embodiment. In the district heat and power combined supply system 2 (2C) shown in Figure 5, the reference symbols common to the respective components of the district heat and power combined supply system 2 (2A) and the district heat and power combined supply system 2 (2B) described above indicate the same components as the respective components of the district heat and power combined supply system 2 (2A) and the district heat and power combined supply system 2 (2B) described above unless otherwise specified, and the description thereof will be omitted.

The district heat and power cogeneration system 2 (2C) shown in FIG. 5 differs from the district heat and power cogeneration system 2 (2B) shown in FIG. 3 in that it includes temperature adjustment flow paths 78, 80. Basically, the temperature adjustment flow path 78 is connected to the second heat exchange section 72, and the temperature adjustment flow path 80 is connected to the first heat exchange section 70. However, in order to operate the system efficiently, a switching valve or the like may be installed to connect the temperature adjustment flow path 78 to the first heat exchange section 70 and the temperature adjustment flow path 80 to the second heat exchange section 72. However, each flow path is switched so that the heat medium supplied from the first branch flow path 60 and the heat medium supplied from the second branch flow path 66 do not mix in the underground heat exchange device 62. When the first branch flow path 60 is the inlet side flow path of the heat medium for the first heat exchanger 70, the temperature adjustment flow path 78 is the outlet side flow path of the heat medium for the first heat exchanger 70, and when the second branch flow path 66 is the inlet side flow path of the heat medium for the second heat exchanger 72, the temperature adjustment flow path 80 is the outlet side flow path of the heat medium for the second heat exchanger 72. When the first branch flow path 60 is the inlet side flow path of the heat medium for the second heat exchanger 72, the temperature adjustment flow path 78 is the outlet side flow path of the heat medium for the second heat exchanger 72, and when the second branch flow path 66 is the inlet side flow path of the heat medium for the first heat exchanger 70, the temperature adjustment flow path 80 is the outlet side flow path of the heat medium for the first heat exchanger 70.

The temperature adjustment flow path 78 is used when it is necessary to adjust the temperature of the high-temperature, high-pressure heat medium flowing through the second flow path 12. Specifically, it is used when the temperature is not sufficiently reduced by the temperature difference power generator 22.
The temperature adjustment flow path 80 is used when it is necessary to adjust the temperature of the low-temperature, high-pressure heat medium flowing through the third flow path 20. Specifically, it is used when the temperature difference power generator 22 does not sufficiently increase the temperature.

In the configuration shown in FIG. 5, the compressor 6, the first flow path 8, the pressure-accumulating insulated high-temperature storage tank 10, the second flow path 12, the expansion turbine 14, the pressure-accumulating insulated low-temperature storage tank 18, the third flow path 20, the temperature difference generator 22, the first branch flow path 60, the first heat exchange section 70, the first return flow path 64, the second branch flow path 66, the second heat exchange section 72, the second return flow path 68, and the temperature adjustment flow paths 78, 80 constitute the heat storage type temperature difference storage battery 3.

The present disclosure is not limited to the above-described embodiments, but also includes variations of the above-described embodiments and appropriate combinations of these embodiments.

For example, in each of the above-mentioned district heat and power cogeneration systems 2 (2A to 2C), another expansion device such as an expansion valve (an evaporator such as a pressure reducing valve) may be provided instead of the expansion turbine 14.

In addition, in the above-described embodiment, an example was given of the case where the electricity generated by the temperature difference generator 22 and the electricity generated by the generator connected to the expansion turbine 14 are supplied to the consumer 100 at the target site, but the electricity generated by the temperature difference generator 22 and the electricity generated by the generator connected to the expansion turbine 14 may be used, for example, to drive the electric motor 5, or may be sold to an electric power company via the integrated heat and power supply and demand system 52.

For example, in each of the above-mentioned district heat and power cogeneration systems 2 (2A to 2C), a buffer tank for storing the heat medium may be installed as necessary in each flow path, such as the first flow path 8, the second flow path 12, and the third flow path 20. In addition, the buffer tank may be provided with a remaining amount sensor (capacity sensor) for detecting the remaining amount of heat medium in the buffer tank.

In addition, in some of the above-mentioned embodiments, the power transmission lines 32, 33, 34, 35, 36, 37, and 38 are provided, but each of the power transmission lines is not an essential component of the district heat and power cogeneration system 2. For example, hydrogen may be produced by electrolyzing water using the electricity generated by the temperature difference generator 22, and the hydrogen may be transported to the consumer 100 and electricity may be generated by a fuel cell on the consumer 100 side.

For example, in each of the above-mentioned district heat and power cogeneration systems 2 (2A to 2C), the pressurized insulated low-temperature storage tank 18 is provided downstream of the expansion turbine 14 in the second flow path 12, but the pressurized insulated low-temperature storage tank 18 may be provided upstream of the expansion turbine 14 in the second flow path 12. In this case, in each of the above-mentioned district heat and power cogeneration systems 2 (2A to 2C), the position of the expansion turbine 14 and the position of the pressurized insulated low-temperature storage tank 18 can be interchanged (see, for example, FIG. 6). This allows the liquid heat medium before it is vaporized in the expansion turbine 14 to be stored in the pressurized insulated low-temperature storage tank 18. Therefore, the pressurized insulated low-temperature storage tank 18 can be made smaller than when the gaseous heat medium after it is vaporized in the expansion turbine 14 is stored in the pressurized insulated low-temperature storage tank 18.

The contents described in each of the above embodiments can be understood, for example, as follows:

(1) A heat storage type temperature difference storage battery according to an embodiment of the present disclosure (for example, the heat storage type temperature difference storage battery 3 described above) has the following features:
A compressor (e.g., the above-mentioned compressor 6) for compressing the heat medium;
A first flow path (for example, the above-mentioned first flow path 8) connected to the compressor and through which the heat medium compressed by the compressor flows;
A pressure-accumulating, insulated, high-temperature storage tank (for example, the above-mentioned pressure-accumulating, insulated, high-temperature storage tank 10) connected to the first flow path and for storing the heat medium supplied from the first flow path;
A second flow path (for example, the above-mentioned second flow path 12) connected to the pressure-accumulating, insulated, high-temperature storage tank for flowing the heat medium that has left the pressure-accumulating, insulated, high-temperature storage tank;
an expansion device (e.g., the expansion turbine 14 described above) provided in the second flow path and configured to reduce the pressure of the heat medium flowing through the second flow path;
A pressure-accumulating, insulated, low-temperature storage tank (e.g., the pressure-accumulating, insulated, low-temperature storage tank 18) is provided on the upstream or downstream side of the expansion device in the second flow path and stores the heat medium in the second flow path;
A third flow path (e.g., the above-mentioned third flow path 20) is connected to the downstream side of the second flow path and is configured to supply the heat medium that has passed through each of the expansion device and the pressure-accumulating insulated low-temperature storage tank to the compressor;
a temperature difference generator (e.g., the above-mentioned temperature difference generator 22) configured to generate electricity by utilizing a temperature difference between the heat medium flowing on the upstream side of the expansion device in the second flow path and the heat medium flowing in the third flow path;
Equipped with.

According to the heat storage type temperature difference storage battery described in (1) above, the heat medium compressed by the compressor and brought into a high temperature and high pressure state is sent to the pressure-storage insulated high temperature tank via the first flow path and stored therein.
The high-temperature, high-pressure heat medium leaving the pressure-accumulating, insulated, high-temperature storage tank is supplied to the temperature difference generator through the second flow path, where it dissipates heat and is supplied to the expansion device. The heat medium supplied to the expansion device is decompressed in the expansion device to become a low-temperature, low-pressure heat medium. The low-temperature, low-pressure heat medium that has passed through the expansion device and the pressure-accumulating, insulated, low-temperature storage tank is supplied to the temperature difference generator through the third flow path, where it supplies cold energy to the temperature difference generator before being returned to the compressor.
In this way, a heat pump cycle can be constructed by the heat medium circulation flow path provided with the compressor, the first flow path, the pressure-accumulating insulated high-temperature storage tank, the expansion device, the pressure-accumulating insulated low-temperature storage tank, the third flow path, and the temperature difference generator, so that a high-temperature, high-pressure heat medium and a low-temperature, low-pressure heat medium can be efficiently generated with little input energy.
In addition, electricity can be accumulated by storing the produced high-temperature, high-pressure heat medium and low-temperature, low-pressure heat medium in a pressure-accumulated, insulated high-temperature tank and a pressure-accumulated, insulated low-temperature tank, respectively, and power can be generated by supplying the high-temperature, high-pressure heat medium and the low-temperature, low-pressure heat medium from the pressure-accumulated, insulated high-temperature tank and the pressure-accumulated, insulated low-temperature tank to a temperature difference generator according to power demand.This makes it possible to provide a heat storage type temperature difference storage battery, which is a new type of battery that generates power using heat media of different temperatures stored in a heat pump cycle.
With this heat storage type temperature difference storage battery, power generation can be performed with a simpler configuration that utilizes the heat medium in the heat pump cycle, compared to, for example, the configuration described in Patent Document 1 (a configuration in which an expansion turbine is driven by a high-temperature, high-pressure heat medium flowing through a heat pump cycle, and power generation is performed by a generator connected to the expansion turbine).

(2) In some embodiments, in the heat storage type temperature difference storage battery described in (1) above,
a first branch flow path (for example, the above-mentioned first branch flow path 60) that branches off from a portion of the second flow path between the temperature difference power generator and the expansion device and that allows the heat medium supplied from the second flow path to flow;
A first heat exchange unit (for example, the above-mentioned first heat exchange unit 70) connected to the first branch flow path and configured to heat the heat medium supplied from the first branch flow path by heat exchange with unused energy;
A first return flow path (for example, the above-mentioned first return flow path 64) connected to the first heat exchange unit and configured to supply the heat medium that has passed through the first heat exchange unit between the pressure-accumulating insulated high-temperature storage tank and the temperature difference power generator in the second flow path;
It further comprises:

In a temperature difference generator, if the amount of hot heat held by the heat medium flowing through the second flow path and the amount of cold heat held by the heat medium flowing through the third flow path are not balanced, the temperature difference generator cannot generate power efficiently. In this regard, according to the heat storage type temperature difference battery described in (2) above, the heat medium flowing through the second flow path can be supplied to the first heat exchange section via the first branch flow path, heated by heat exchange with unused energy in the first heat exchange section, and then supplied to between the pressure-storage insulated high-temperature storage tank in the second flow path and the temperature difference generator via the first return flow path. Therefore, when the amount of hot heat held by the heat medium flowing through the second flow path is insufficient compared to the amount of cold heat held by the heat medium flowing through the third flow path (when there is a hot medium shortage), the amount of hot heat of the heat medium flowing through the second flow path can be replenished by using unused energy, etc., and the temperature difference generator can generate power efficiently.

(3) In some embodiments, in the heat storage type temperature difference storage battery described in (1) or (2) above,
a second branch flow path (for example, the above-mentioned second branch flow path 66) that branches off from the third flow path between the temperature difference power generator and the compressor and through which the heat medium supplied from the third flow path flows;
A second heat exchange unit (for example, the above-mentioned second heat exchange unit 72) connected to the second branch flow path and configured to cool the heat medium supplied from the second branch flow path by heat exchange with unused energy;
A second return flow path (for example, the above-mentioned second return flow path 68) that is connected to the second heat exchange unit and is configured to supply the heat medium that has passed through the second heat exchange unit between the pressure-accumulating insulated low-temperature storage tank and the temperature difference power generator in the third flow path;
It further comprises:

In a temperature difference generator, if the amount of hot energy held by the heat medium flowing through the second flow path and the amount of cold energy held by the heat medium flowing through the third flow path are not balanced, the temperature difference generator cannot generate power efficiently. In this regard, according to the heat storage type temperature difference storage battery described in (3) above, the heat medium flowing through the third flow path can be supplied to the second heat exchange section via the second branch flow path, cooled by heat exchange with unused energy in the second heat exchange section, and then supplied to between the pressure-storage insulated low-temperature storage tank in the third flow path and the temperature difference generator via the second return flow path. Therefore, when the amount of cold energy held by the heat medium flowing through the third flow path is insufficient compared to the amount of hot energy held by the heat medium flowing through the second flow path (when there is a refrigerant shortage), the amount of cold energy of the heat medium flowing through the third flow path can be replenished by using unused energy, etc., and the temperature difference generator can generate power efficiently.

(4) A cogeneration system according to an embodiment of the present disclosure,
A heat storage type temperature difference storage battery according to any one of (1) to (3) above;
A fourth flow path (e.g., the above-mentioned fourth flow path 24) connected to the pressure-accumulating, insulated, high-temperature storage tank and configured to supply the heat medium from the pressure-accumulating, insulated, high-temperature storage tank to a consumer (e.g., the above-mentioned consumer 100) at the target site;
Equipped with.

According to the cogeneration system described in (4) above, the heat medium stored in the pressure-storage, insulated, high-temperature storage tank in the heat storage type temperature difference storage battery can be used to meet the heat demand of the consumer (e.g., heating demand and hot water demand).

(5) In some embodiments, in the cogeneration system according to (4) above,
a fifth flow path (e.g., the above-mentioned 65th flow path 26) for recovering the heat medium supplied to the consumer via the fourth flow path from the consumer,
The fifth flow path is configured to supply the heat medium recovered from the consumer to a position in the second flow path between the temperature difference power generator and the expansion device.

According to the cogeneration system described in (5) above, a heat pump cycle can be constructed by a circulation flow path for the heat medium, which includes the first flow path, the pressurized insulated high-temperature storage tank, the fourth flow path, the fifth flow path, the expansion device, the pressurized insulated low-temperature storage tank, and the third flow path, so that a high-temperature and high-pressure heat medium can be efficiently supplied to a consumer with a small input of energy.

(6) In some embodiments, in the cogeneration system according to (4) or (5) above,
Further comprising a sixth flow path (for example, the sixth flow path 28 described above) connected to the pressure-accumulating insulated low-temperature storage tank;
The sixth flow path is configured to supply the heat medium from the pressure-accumulating, insulated, low-temperature storage tank to a consumer at a target site.

According to the cogeneration system described in (6) above, the heat storage type temperature difference storage battery can use the heat medium stored in the pressure storage insulated low-temperature storage tank to meet the cold energy demand (e.g., cooling demand) of the consumer.

(7) In some embodiments, in the cogeneration system according to (6) above,
The heat transfer device further includes a seventh flow path (e.g., the seventh flow path 30 described above) for recovering the heat transfer medium supplied to the consumer via the sixth flow path,
The seventh flow path is configured to supply the heat medium recovered from the consumer to a position in the third flow path between the temperature difference power generator and the compressor.

According to the cogeneration system described in (7) above, a heat pump cycle can be constructed by a circulation flow path for the heat medium, which includes the first flow path, the pressurized insulated high-temperature storage tank, the second flow path, the expansion device, the pressurized insulated low-temperature storage tank, the sixth flow path, and the seventh flow path, so that a low-temperature, low-pressure heat medium can be efficiently supplied to a consumer with a small input of energy.

(8) In some embodiments, in the cogeneration system according to (1) above,
The pressurized insulated low-temperature storage tank is provided in the second flow path upstream of the expansion device.

According to the cogeneration system described in (8) above, the liquid heat transfer medium before being vaporized in the expansion device can be stored in the pressure-accumulated, insulated, low-temperature storage tank. Therefore, the pressure-accumulated, insulated, low-temperature storage tank can be made smaller than when the gaseous heat transfer medium after being vaporized in the expansion device is stored in the pressure-accumulated, insulated, low-temperature storage tank.

(9) In some embodiments, in the cogeneration system according to any one of (1) to (8),
an electric motor (e.g. the electric motor 5 described above) for driving the compressor;
A remaining amount sensor (for example, the remaining amount sensor described above) for detecting the remaining amount of the heat medium in the pressure-accumulating, insulated, high-temperature storage tank;
a motor control unit (e.g., the motor control unit 86 described above) for controlling the electric motor;
Equipped with
The motor control unit is configured to drive the electric motor when the remaining amount of the heat medium in the pressure-accumulating, insulated, high-temperature storage tank detected by the remaining amount sensor is equal to or less than a threshold value.

In a temperature difference generator, if the amount of hot heat held by the heat medium stored in the pressure-storage insulated high-temperature tank is not balanced with the amount of cold heat held by the heat medium stored in the pressure-storage insulated low-temperature tank, the temperature difference generator cannot generate power efficiently. In this regard, with the heat storage type temperature difference storage battery described in (9) above, when the remaining amount of heat medium in the pressure-storage insulated high-temperature tank detected by the remaining amount sensor is below a threshold, the electric motor can drive the compressor to replenish the amount of hot heat held by the heat medium stored in the pressure-storage insulated high-temperature tank, allowing the temperature difference generator to generate power efficiently.

(10) In some embodiments, in the cogeneration system according to any one of (1) to (9),
an electric motor (e.g. the electric motor 5 described above) for driving the compressor;
A remaining amount sensor (for example, the remaining amount sensor described above) for detecting the remaining amount of the heat medium in the pressure-accumulating insulated low-temperature storage tank;
a motor control unit (e.g., the motor control unit 86 described above) for controlling the electric motor;
Equipped with
The motor control unit is configured to drive the electric motor when a remaining amount of the heat medium in the pressure-accumulating insulated low-temperature storage tank detected by a remaining amount sensor is equal to or less than a threshold value.

In a temperature difference generator, if the amount of hot heat held by the heat medium stored in the pressure-storage insulated high-temperature storage tank is not balanced with the amount of cold heat held by the heat medium stored in the pressure-storage insulated low-temperature storage tank, the temperature difference generator cannot generate power efficiently. In this regard, with the heat storage type temperature difference storage battery described in (10) above, when the remaining amount of heat medium in the pressure-storage insulated low-temperature storage tank detected by the remaining amount sensor is below a threshold, the electric motor can drive the compressor to replenish the amount of cold heat held by the heat medium stored in the pressure-storage insulated low-temperature storage tank, allowing the temperature difference generator to generate power efficiently.

(11) A group of cogeneration systems according to an embodiment of the present disclosure includes:
A group of cogeneration systems (for example, the above-mentioned district cogeneration system group 4) including a plurality of the cogeneration systems according to any one of (1) to (10),
The plurality of cogeneration systems are provided corresponding to a plurality of target sites, respectively;
The group of cogeneration systems further includes an integrated heat and power supply and demand system (for example, the integrated heat and power supply and demand system 52 described above) configured to optimize the supply and demand of electricity and heat in the entire plurality of cogeneration systems.

According to the cogeneration system described in (11) above, the integrated cogeneration system optimizes the supply and demand of electricity and heat across multiple cogeneration systems, thereby leveling out the loads of electricity and heat and efficiently meeting the demand for electricity and heat with a small amount of input energy.

(12) In some embodiments, in the group of cogeneration systems described in (11) above,
Further comprising a machine learning device (e.g., the above-mentioned machine learning device 88) that learns the supply and demand trends of electricity and heat at each of the plurality of target sites;
The integrated heat and power supply and demand system is configured to optimize the supply and demand of electricity and heat across the multiple combined heat and power systems based on the supply and demand trends of electricity and heat and electricity market prices at each of the multiple target sites learned by the machine learning device.

According to the group of cogeneration systems described in (12) above, by learning the trends in power and heat supply and demand at each of the multiple target sites and optimizing the power and heat supply and demand across the multiple cogeneration systems, it is possible to level out the power and heat loads and efficiently meet the power and heat demand with a small amount of input energy.

2 District heat and power combined supply system 3 Heat storage type temperature difference storage battery 4 District heat and power combined supply system group 5 Electric motor 6 Compressor 8 First flow path 10 Pressure storage insulated high temperature storage tank 12 Second flow path 14 Expansion device 18 Pressure storage insulated low temperature storage tank 20 Third flow path 22 Temperature difference generator 24 Fourth flow path 26 Fifth flow path 25 Circulation flow path 28 Sixth flow path 30 Seventh flow path 32, 33, 34, 35, 36, 37, 38 Power transmission line 50 Site heat and power supply and demand system 52 Integrated heat and power supply and demand system 60 First branch flow path 62 Geothermal heat exchanger 64 First return flow path 66 Second branch flow path 68 Second return flow path 70 First heat exchanger 72 Second heat exchanger 74, 76 Circulation flow path 78, 80 Temperature adjustment flow path 82, 84 Temperature sensor 86 Motor control unit 88 Machine learning device 100 Demand entity

Claims (12)

A compressor for compressing the heat medium;
a first flow path connected to the compressor and through which the heat medium compressed by the compressor flows;
A pressure-accumulating, insulated, high-temperature storage tank connected to the first flow path for storing the heat medium supplied from the first flow path;
A second flow path connected to the pressure-accumulating, insulated, high-temperature storage tank for flowing the heat medium that has left the pressure-accumulating, insulated, high-temperature storage tank;
an expansion device provided in the second flow path and configured to reduce the pressure of the heat medium flowing through the second flow path;
a pressure-accumulating, insulated, low-temperature storage tank provided upstream or downstream of the expansion device in the second flow path for storing the heat medium in the second flow path;
a third flow path connected to a downstream side of the second flow path and configured to supply the heat medium that has passed through each of the expansion device and the pressure-accumulating insulated low-temperature storage tank to the compressor;
a temperature difference generator configured to generate electricity by utilizing a temperature difference between the heat medium flowing on the upstream side of the expansion device in the second flow path and the heat medium flowing in the third flow path;
A heat storage type temperature difference storage battery comprising: a first branch flow path that branches off from the second flow path between the temperature difference power generator and the expansion device, and through which the heat medium supplied from the second flow path flows;
A first heat exchange unit connected to the first branch flow path and configured to heat the heat medium supplied from the first branch flow path by heat exchange with geothermal heat, factory exhaust heat, or exhaust heat from a waste incineration plant ;
A first return flow path connected to the first heat exchange unit and configured to supply the heat medium that has passed through the first heat exchange unit to a portion between the pressure-accumulating insulated high-temperature storage tank and the temperature differential power generator in the second flow path;
The heat storage type temperature difference storage battery according to claim 1 , further comprising: a second branch flow path that branches off from the third flow path between the temperature difference power generator and the compressor, and through which the heat medium supplied from the third flow path flows;
A second heat exchange unit connected to the second branch flow path and configured to cool the heat medium supplied from the second branch flow path by heat exchange with geothermal heat, river heat, seawater heat, sewage heat, or snow and ice heat ;
A second return flow path connected to the second heat exchange unit and configured to supply the heat medium that has passed through the second heat exchange unit to a portion between the pressure-accumulating insulated low-temperature storage tank and the temperature difference power generator in the third flow path;
The heat storage type temperature difference storage battery according to claim 1 or 2, further comprising: A heat storage type temperature difference storage battery according to any one of claims 1 to 3;
A fourth flow path connected to the pressure-accumulating, insulated, high-temperature storage tank and configured to supply the heat medium from the pressure-accumulating, insulated, high-temperature storage tank to a consumer at a target site;
A combined heat and power system comprising: a fifth flow path for recovering the heat medium supplied to the consumer via the fourth flow path from the consumer,
The combined heat and power supply system according to claim 4 , wherein the fifth flow path is configured to supply the heat medium recovered from the consumer to a position in the second flow path between the temperature difference power generator and the expansion device. Further comprising a sixth flow path connected to the pressure-accumulating insulated low-temperature storage tank;
The combined heat and power supply system according to claim 4 or 5, wherein the sixth flow path is configured to supply the heat medium from the pressure-accumulating insulated low-temperature storage tank to a consumer at a target site. a seventh flow path for recovering the heat medium supplied to the consumer via the sixth flow path,
The combined heat and power supply system according to claim 6 , wherein the seventh flow path is configured to supply the heat medium recovered from the consumer to a position in the third flow path between the temperature difference power generator and the compressor. The heat storage type temperature difference storage battery according to claim 1, wherein the pressure-storage insulated low-temperature storage tank is provided upstream of the expansion device in the second flow path. an electric motor for driving the compressor;
A remaining amount sensor for detecting the remaining amount of the heat medium in the pressure-accumulating, insulated, high-temperature storage tank;
A motor control unit that controls the electric motor;
Equipped with
The heat and power cogeneration system according to any one of claims 1 to 8, wherein the motor control unit is configured to drive the electric motor when the remaining amount of the heat medium in the pressurized insulated high-temperature storage tank detected by the remaining amount sensor is equal to or less than a threshold value. an electric motor for driving the compressor;
A remaining amount sensor for detecting the remaining amount of the heat medium in the pressure-accumulating insulated low-temperature storage tank;
A motor control unit that controls the electric motor;
Equipped with
The heat and power cogeneration system according to any one of claims 1 to 9, wherein the motor control unit is configured to drive the electric motor when the remaining amount of the heat medium in the pressurized insulated low-temperature storage tank detected by the remaining amount sensor is equal to or less than a threshold value. A group of cogeneration systems comprising a plurality of cogeneration systems according to any one of claims 1 to 10,
The plurality of cogeneration systems are provided corresponding to a plurality of target sites, respectively;
The group of cogeneration systems further includes an integrated heat and power supply system configured to optimize supply and demand of electricity and heat in the entire group of the plurality of cogeneration systems. Further comprising a machine learning device configured to learn trends in supply and demand of electricity and heat at each of the plurality of target sites;
The group of cogeneration systems described in claim 11, wherein the integrated cogeneration supply and demand system is configured to optimize the supply and demand of electricity and heat in the entire cogeneration systems based on the supply and demand trends of electricity and heat at each of the target sites learned by the machine learning device.

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