EXHAUST HEAT COLLECTING SYSTEM

Abstract

In one embodiment, an exhaust heat collecting system of collecting exhaust heat in a fluid treatment system. The fluid treatment system includes a fluid path to convey at least an operating fluid or a cooled fluid among first and second heat source fluids, the operating fluid and the cooled fluid. The fluid treatment system further includes a fluid treatment module including an expansion module, a power generator and a condenser for the operating fluid, or including a heat absorbing module and a heat releasing module for the cooled fluid. The exhaust heat collecting system includes a water path to heat water by using the condenser or the heat releasing module, and a heater to heat the water from the water path by using the first or second heat source fluid or the operating fluid to produce the water to be used as hot water or to produce steam.

Description

CROSS REFERENCE TO RELATED APPLICATIONS

This application is based upon and claims the benefit of priority from the prior Japanese Patent Applications No. 2015-201282, filed on Oct. 9, 2015, No. 2016-139375, filed on Jul. 14, 2016 and No. 2016-140406, filed on Jul. 15, 2016, the entire contents of which are incorporated herein by reference.

FIELD

Embodiments described herein relate to an exhaust heat collecting system.

BACKGROUND

FIG. 37 is a schematic diagram showing a first example representing the configuration of a conventional power generating system.

The power generating system in FIG. 37 includes a heat source fluid heater 1, a heat source fluid pump 2, a heat source fluid path 3, an evaporator 4, an operating fluid pump 5, an operating fluid path 6, an expansion module 7, a power generator 8, a condenser 9, a cooling water pump 11, a cooling water path 12, a cooling tower 13, a blower 14 and an atmosphere introducing portion 15.

The heat source fluid is conveyed through the heat source fluid path 3 by the heat source fluid pump 2, and is heated by the heat source fluid heater 1. An example of the heat source fluid heater 1 is a small-sized biomass boiler that burns biomass fuel of a wooden chip or the like, and an example of the heat source fluid is water of a gas or a liquid. In this case, the heat source fluid heater 1 heats the water of the liquid by combustion exhaust gases generated by burning the biomass fuel, thus converting the water of the liquid into water (steam) of the gas. Another example of the heat source fluid heater 1 is a solar energy collector, and an example of the heat source fluid in this case is thermal medium oil. A further other example of the heat source fluid heater 1 is an exhaust heat collector that collects factory exhaust heat or the like, and an example of the heat source fluid in this case is water. The heat source fluid discharged from the heat source fluid heater 1 flows into the evaporator 4, and is lowered in temperature by heating the operating fluid in the evaporator 4. The heat source fluid circulates between the heat source fluid heater 1 and the evaporator 4 through the heat source fluid path 3.

The operating fluid of the liquid is conveyed through the operating fluid path 6 by the operating fluid pump 5 and is heated by the evaporator 4 to be converted into the operating fluid of a gas. That is, the operating fluid evaporates. An example of the operating fluid is a low-boiling medium of chlorofluorocarbon (CFC) or the like. The operating fluid discharged from the evaporator 4 flows into the expansion module 7 and expands in the expansion module 7 to drive a rotational shaft of the expansion module 7. An example of the expansion module 7 is a turbine. The rotational shaft of the expansion module 7 is connected to the power generator 8, and the power generator 8 generates power by using shaft power of the rotational shaft. The operating fluid is lowered in pressure and temperature in the expansion module 7, is discharged from the expansion module 7 and flows into the condenser 9. The operating fluid having flowed into the condenser 9 is cooled by cooling water in the condenser 9 to be converted into an operating fluid of a liquid. That is, the operating fluid condenses. The operating fluid circulates among the evaporator 4, the expansion module 7 and the condenser 9 through the operating fluid path 6.

The cooling water is conveyed through the cooling water path 12 by the cooling water pump 11 and is heated by condensation heat of the operating fluid in the condenser 9. The cooling water discharged from the condenser 9 is cooled by the atmospheric air in the cooling tower 13. The cooling water circulates between the condenser 9 and the cooling tower 13 through the cooling water path 12.

The blower 14 conveys the atmospheric air introduced by the atmosphere introducing portion 15 to the cooling tower 13. This atmospheric air is heated in the cooling tower 13 by the condensation heat absorbed by the cooling water. As a result, the condensation heat of the operating fluid is given to the atmospheric air through the cooling water and is released to an exterior through the atmospheric air.

A cycle by which the operating fluid circulates is a Rankine cycle. The power generating system in FIG. 37 uses two kinds of thermal media composed of the heat source fluid and the operating fluid, and therefore is called a binary turbine system.

FIG. 38 is a schematic diagram showing a second example representing the configuration of the conventional power generating system. In FIG. 38, components identical or similar to those shown in FIG. 37 are referred to as identical signs, and an explanation overlapping the explanation in FIG. 37 is omitted (same in third to sixth examples to be hereinafter described).

The power generating system in FIG. 38 includes the heat source fluid heater 21, the heat source fluid pump 22 and the heat source fluid path 23 in addition to the components shown in FIG. 37. In the explanation in FIG. 38, components indicated at signs 1 to 3 are called the first heat source fluid heater 1, the first heat source fluid pump 2 and the first heat source fluid path 3, and components indicated at signs 21 to 23 are called the second heat source fluid heater 21, the second heat source fluid pump 22 and the second heat source fluid path 23. The heat source fluid conveyed through the first heat source fluid path 3 is called a first heat source fluid, and the heat source fluid conveyed through the second heat source fluid path 23 is called a second heat source fluid.

The first heat source fluid is conveyed through the first heat source fluid path 3 by the first heat source fluid pump 2, and is heated by the first heat source fluid heater 1. The first heat source fluid discharged from the first heat source fluid heater 1 flows into the second heat source fluid heater 21, and is lowered in temperature by heating the second heat source fluid in the second heat source fluid heater 21. The first heat source fluid circulates between the first heat source fluid heater 1 and the second heat source fluid heater 21 through the first heat source fluid path 3.

The second heat source fluid is conveyed through the second heat source fluid path 23 by the second heat source fluid pump 22, and is heated by the second heat source fluid heater 21. An example of the second heat source fluid is thermal medium oil or water. The second heat source fluid discharged from the second heat source fluid heater 21 flows into the evaporator 4, and is lowered in temperature by heating the operating fluid in the evaporator 4. The second heat source fluid circulates between the second heat source fluid heater 21 and the evaporator 4 through the second heat source fluid path 23.

Here, the power generating system in FIG. 37 and the power generating system in FIG. 38 will be compared.

In FIG. 37, since separated substances are accumulated in the evaporator 4 depending upon components contained in the heat source fluid, it is necessary to frequently disassemble the evaporator 4 for the cleaning. In this case, since the operating fluid path 6 containing a low-boiling medium of CFC or the like is to be disassembled, the disassembly is not preferable. On the other hand, in FIG. 38, not the evaporator 4 but the second heat source fluid heater 21 is disassembled and cleaned. Therefore, it is not necessary to disassemble the operating fluid path 6.

FIG. 39 is a supplementary diagram for explaining the conventional power generating system. FIG. 39 shows a part of the power generating system in each of FIGS. 37 and 38 with the same drawing for descriptive purposes.

In FIG. 37, the heat source fluid circulates, but as shown in FIG. 39, only passes through the evaporator 4 and does not need to circulate. In this case, an example of the heat source fluid is hot spring water welling from the ground 10, and the power generating system is not equipped with the heat source fluid heater 1. In a case where the heat source fluid is the hot spring water, separated substances tend to be easily accumulated in the evaporator 4 in FIG. 39, and it is necessary to frequently disassemble the evaporator 4 for the cleaning. On this occasion, the operating fluid path 6 is to be disassembled in this example.

Likewise, in FIG. 38, the first heat source fluid circulates, but as shown in FIG. 39, only passes through the second heat source fluid heater 21 and does not need to circulate. In this case, an example of the first heat source fluid is hot spring water welling from the ground 10, and the power generating system is not equipped with the first heat source fluid heater 1. In a case where the heat source fluid is the hot spring water, separated substances tend to be easily accumulated in the second heat source fluid heater 21 in FIG. 39, and it is necessary to frequently disassemble the second heat source fluid heater 21 for the cleaning. On this occasion, in this example it is not necessary to disassemble the operating fluid path 6.

FIG. 40 is a schematic diagram showing a third example representing the configuration of the conventional power generating system.

The power generating system in FIG. 40 does not include the heat source fluid heater 1, the heat source fluid pump 2, the heat source fluid path 3, the evaporator 4, and the operating fluid pump 5 shown in FIG. 37. An example of the operating fluid flowing in the operating fluid path 6 in FIG. 40 is a gas of geothermal steam or the like.

The operating fluid of the gas flows into the expansion module 7 from the operating fluid path 6 to drive the rotational shaft of the expansion module 7. The power generator 8 generates power by using the shaft power of the rotational shaft. The operating fluid is thereafter discharged to the operating fluid path 6 from the expansion module 7 and flows into the condenser 9. The operating fluid having flowed into the condenser 9 is cooled by cooling water in the condenser 9 to be converted into the operating fluid of a liquid, and is returned to the ground.

FIG. 41 is a schematic diagram showing a fourth example representing the configuration of the conventional power generating system.

The power generating system in FIG. 41 does not include the heat source fluid heater 1, the heat source fluid pump 2 and the heat source fluid path 3 shown in FIG. 37. An example of the evaporator 4 in FIG. 41 is a small-sized biomass boiler that burns biomass fuel of a wooden chip or the like, and an example of the operating fluid flowing in the operating fluid path 6 in FIG. 41 is water of a gas or liquid. In this case, the evaporator 4 heats water of a liquid by combustion exhaust gases generated by burning the biomass fuel, converting the water of the liquid into water (steam) of a gas. Another example of the evaporator 4 is a solar energy collector for collecting solar energy, and an example of the operating fluid in this case is CFC of a gas or liquid. A further other example of the evaporator 4 is an exhaust heat collector that collects factory exhaust heat or the like, and an example of the operating fluid in this case is water of a gas or liquid.

The operating fluid of the liquid is conveyed through the operating fluid path 6 by the operating fluid pump 5, is heated by the evaporator 4, and is converted into the operating fluid of the gas. The operating fluid discharged from the evaporator 4 flows into the expansion module 7 to drive the rotational shaft of the expansion module 7. The power generator 8 generates power by using the shaft power of the rotational shaft. The operating fluid is thereafter discharged from the expansion module 7 and flows into the condenser 9. The operating fluid having flowed into the condenser 9 is cooled by the cooling water in the condenser 9 to be converted into the operating fluid of the liquid. The operating fluid circulates among the evaporator 4, the expansion module 7 and the condenser 9 through the operating fluid path 6.

FIG. 42 is a schematic diagram showing a fifth example representing the configuration of the conventional cooling system.

The cooling system in FIG. 42 includes the heat source fluid heater 1, the heat source fluid pump 2, the heat source fluid path 3, the cooling water pump 11, the cooling water path 12, the cooling tower 13, the blower 14, the atmosphere introducing portion 15, a refrigerator 16, a cooled fluid pump 17, a cooled fluid path 18, and a cold load 19. The refrigerator 16 includes a heat absorbing module 16a, a cooling module 16b and a heat releasing module 16c. The refrigerator 16 according to the present embodiment is of an absorption type or adsorption type.

As similar to the case of the first example, the heat source fluid is conveyed through the heat source fluid path 3 by the heat source fluid pump 2, and is heated by the heat source fluid heater 1. The heat source fluid discharged from the heat source fluid heater 1 flows into the heat absorbing module 16a, and is lowered in temperature by heating the heat absorbing module 16a. That is, the heat absorbing module 16a absorbs heat of the heat source fluid. The heat source fluid circulates between the heat source fluid heater 1 and the heat absorbing module 16a through the heat source fluid path 3.

The refrigerator 16 includes the heat absorbing module 16a, the cooling module 16b and the heat releasing module 16c, and a cooling medium is contained in the refrigerator 16. An example of the cooling medium is water or ammonia. The cooling module 16b cools a cooled fluid (cooling target fluid) by evaporation heat (evaporative latent heat) of the cooling medium. An example of the cooled fluid is water. The heat absorbing module 16a uses the heat source fluid to cause the cooling medium or a substance holding the cooling medium to absorb heat. The heat absorbing module 16a, for example, heats an absorption liquid or an adsorption agent having collected the cooling medium from the cooling module 16b by the heat source fluid to vaporize the cooling medium. The heat releasing module 16c uses the cooling water to cause the cooling medium or a substance holding the cooling medium to release heat. The heat releasing module 16c, for example, cools the adsorption agent collecting the cooling medium by the cooling water or cools the cooling medium vaporized from the absorption liquid or the adsorption agent by the cooling water to liquidize (condense) the cooling medium. In this way, the heat releasing module 16c releases the heat received from the cooled fluid and the heat absorbed by the heat absorbing module 16a to the cooling water. The cooling module 16b cools the cooled fluid by using the cooling medium from the heat releasing module 16c.

The cooled fluid is conveyed through the cooled fluid path 18 by the cooled fluid pump 17, and is cooled by the cooling module 16b. The cooled fluid discharged from the cooling module 16b flows into the cold load 19, and is increased in temperature by cooling the cold load 19. An example of the cold load 19 is cooling target facilities such as building cooling or cooling target devices such as server computers. The cooled fluid in the former case is used in cold water for cold heat source in cooling air-conditioning. The cooled fluid circulates between the cooling module 16b and the cold load 19 through the cooled fluid path 18.

The cooling water is conveyed through the cooling water path 12 by the cooling water pump 11, and is increased in temperature by cooling the heat releasing module 16c. The cooling water discharged from the heat releasing module 16c is cooled by the atmospheric air in the cooling tower 13. The cooling water circulates between the heat releasing module 16c and the cooling tower 13 through the cooling water path 12.

The blower 14 conveys the atmospheric air introduced by the atmosphere introducing portion 15 to the cooling tower 13. This atmospheric air is heated in the cooling tower 13 by the heat absorbed by the cooling water. As a result, the potential heat of the heat source fluid or the cooled fluid is given to the atmospheric air through the cooling water and is released to an exterior through the atmospheric air.

FIG. 43 is a schematic diagram explaining an operation of the refrigerator 16 in FIG. 42.

As shown in FIG. 43, the heat absorbing module 16a absorbs enthalpy H₁ from the heat source fluid, and the cooling module 16b absorbs enthalpy H₂ from the cooled fluid. The heat releasing module 16c releases enthalpy H₃ to the cooling water. A relation of H₁+H₂=H₃ is established between enthalpy H₁ to H₃. An example of a ratio of enthalpy H₁ to H₃ is H₁:H₂:H₃=1.0:0.6:1.6. This explanation can be applied not only to the refrigerator 16 in FIG. 42 but also to the refrigerator in FIG. 44.

FIG. 44 is a schematic diagram showing a sixth example representing the configuration of the conventional cooling system.

The cooling system in FIG. 44 includes the heat source fluid heater 21, the heat source fluid pump 22 and the heat source fluid path 23 in addition to the components shown in FIG. 42. In the explanation in FIG. 44, as similar to the case in the second example, the first heat source fluid heater 1, the first heat source fluid pump 2, the first heat source fluid path 3, the second heat source fluid heater 21, the second heat source fluid pump 22, and the second heat source fluid path 23 are adopted as titles. The heat source fluid in the first heat source fluid path 3 is called a first heat source fluid, and the heat source fluid in the second heat source fluid path 23 is called a second heat source fluid.

The first heat source fluid is heated by the first heat source fluid heater 1, and is lowered in temperature by heating the second heat source fluid in the second heat source fluid heater 21. The second heat source fluid is heated by the second heat source fluid heater 21, and is lowered in temperature by heating the heat absorbing module 16a. That is, the heat absorbing module 16a absorbs heat of the second heat source fluid.

Here, the cooling system in FIG. 42 and the cooling system in FIG. 44 will be compared.

In FIG. 42, since separated substances are accumulated in the refrigerator 16 (heat absorbing module 16a) depending upon components contained in the heat source fluid, it is necessary to frequently disassemble the refrigerator 16 for the cleaning, but the disassembly of the refrigerator 16 is not preferable. On the other hand, in FIG. 44, not the refrigerator 16 but the second heat source fluid heater 21 is disassembled and cleaned, and therefore, it is not necessary to disassemble the refrigerator 16.

FIG. 45 is a supplementary diagram for explaining the conventional cooling system. FIG. 45 shows a part of the cooling system in each of FIG. 42 and FIG. 44 with the same drawing for descriptive purposes.

In FIG. 42, the heat source fluid circulates, but as shown in FIG. 45, only passes through the refrigerator 16 (heat absorbing module 16a) and does not need to circulate. This is the same with the first example. In this case, since separated substances of the hot spring water (heat source fluid) tend to be easily accumulated in the refrigerator 16 in FIG. 45, it is necessary to frequently disassemble the refrigerator 16 for the cleaning.

Likewise, in FIG. 44, the first heat source fluid circulates, but as shown in FIG. 45, only passes through the second heat source fluid heater 21 and does not need to circulate. This is the same with the second example. In this case, since separated substances of the hot spring water (first heat source fluid) tend to be easily accumulated in the second heat source fluid heater 21 in FIG. 45, it is necessary to frequently disassemble the second heat source fluid heater 21 for the cleaning. However, it is not necessary to disassemble the refrigerator 16.

FIG. 46 is a schematic diagram showing a first specific example of the refrigerator 16 in FIG. 42.

The refrigerator 16 in FIG. 46 is of an absorption type, and includes an evaporator 16d₁, a condenser 16d₂, an absorber 16d₃, and a regenerator 16d₄.

A cooling medium of a liquid is supplied to the evaporator 16d₁ from a flow path N₁. Since an atmosphere in the evaporator 16d₁ is set to a low pressure, the cooling medium vaporizes in the evaporator 16d₁. The evaporator 16d₁ cools a cooled fluid from the cooled fluid path 18 by evaporation heat of the cooling medium, and discharges the cooling medium of a gas to a flow path N₂. The evaporator 16d₁ corresponds to the aforementioned cooling module 16b.

A cooling medium of a gas is supplied to the absorber 16d₃ from the flow path N₂. The absorber 16d₃ causes an absorption liquid from a flow path N₄ to absorb the cooling medium, and discharges the absorption liquid containing the cooling medium to a flow path N₃. In this case, an example of a combination of the cooling medium and the absorption liquid is ammonia and water.

The absorption liquid containing the cooling medium is supplied to the regenerator 16d₄ from the flow path N₃. The regenerator 16d₄ heats the absorption liquid by the heat source fluid from the heat source fluid path 3. As a result, the cooling medium is released from the absorption liquid to vaporize. The absorption liquid having released the cooling medium is discharged to the flow path N₄ and the vaporized cooling medium is discharged to a flow path N₅. The regenerator 16d₄ corresponds to the aforementioned heat absorbing module 16a, and causes the cooling medium to absorb heat by using the heat source fluid.

A cooling medium of a gas is supplied to the condenser 16d₂ from the flow path N₅. The condenser 16d₂ cools the cooling medium by the cooling water from the cooling water path 12 and liquidizes (condenses) the cooling medium. The liquidized solvent is discharged to the flow path N₁. The condenser 16d₂ corresponds to the aforementioned heat releasing module 16c, and causes the cooling medium to release heat by using the cooling water.

FIGS. 47 and 48 are schematic diagrams each showing a second specific example of the refrigerator 16 in FIG. 42.

FIGS. 47 and 48 show different states of the same refrigerator 16. The refrigerator 16 is of an adsorption type, and includes an evaporator 16e₁, a condenser 16e₂, a first heat exchanger 16e₃, a second heat exchanger 16e₄, a first inlet valve 16e₅, a second inlet valve 16e₆, a first outlet valve 16e₇, a second outlet valve 16e₈, and a cooling medium pump 16e₉. The refrigerator 16 is operable to alternately repeat the state in FIG. 47 and the state in FIG. 48.

In FIG. 47, the first inlet valve 16e₅ and the second outlet valve 16e₈ are opened, and the second inlet valve 16e₆ and the first outlet valve 16e₇ are closed. In addition, a valve 12a in the cooling water path 12 is set to supply the cooling water to the first heat exchanger 16e₃ and the condenser 16e₂, and a valve 3a in the heat source fluid path 3 is set to supply the heat source fluid to the second heat exchanger 16e₄.

A cooling medium of a liquid is supplied to the evaporator 16e₁ in FIG. 47 from a flow path M₁ by the cooling medium pump 16e₉. An example of the cooling medium in this case is water. Since an atmosphere in the evaporator 16e₁ is set to a low pressure, the cooling medium vaporizes in the evaporator 16e₁. The evaporator 16e₁ cools a cooled fluid from the cooled fluid path 18 by evaporation heat of the cooling medium. The vaporized cooling medium flows into the first heat exchanger 16e₃ through the first inlet valve 16e₅ and the cooling medium staying in the liquid state is accumulated in a reserving module K₁. The cooling medium accumulated in the reserving module K₁ again flows into the flow path M₁ from a flow path M₂. The evaporator 16e₁ corresponds to the aforementioned cooling module 16b.

The first heat exchanger 16e₃ in FIG. 47 includes a first absorption agent K₃, and a cooling medium of a gas is supplied to the first heat exchanger 16e₃ from the first inlet valve 16e₅. The first absorption agent K₃ adsorbs this cooling medium to generate adsorption heat. The first heat exchanger 16e₃ absorbs this adsorption heat by the cooling water from the cooling water path 12. The first heat exchanger 16e₃ in this case corresponds to the aforementioned heat releasing module 16c, and uses the cooling water to cause a substance (adsorption agent) holding the cooling medium to release heat.

The second heat exchanger 16e₄ in FIG. 47 includes a second absorption agent K₄. The second absorption agent K₄ has already adsorbed the cooling medium at the previous state shown in FIG. 48. Therefore, when the second absorption agent K₄ is heated by the heat source fluid from the heat source fluid path 3, the cooling medium is desorbed from the second absorption agent K₄ to vaporize the cooling medium. The vaporized cooling medium flows into the condenser 16e₂ through the second outlet valve 16e₈. The second heat exchanger 16e₄ in this case corresponds to the aforementioned heat absorbing module 16a, and uses the heat source fluid to cause a substance (adsorption agent) holding the cooling medium to absorb the heat.

A cooling medium of a gas is supplied to the condenser 16e₂ in FIG. 47 from the second outlet valve 16e₈. The condenser 16e₂ cools the cooling medium by the cooling water from the cooling water path 12 to liquidize (condense) the cooling medium. The liquidized solvent is accumulated in the reserving module K₂. The cooling medium accumulated in the reserving module K₂ again flows into the flow path M₁ from a flow path M₃. The condenser 16e₂ corresponds to the aforementioned heat releasing module 16c, and uses the cooling water to release heat of the cooling medium.

On the other hand, in FIG. 48 the first inlet valve 16e₅ and the second outlet valve 16e₈ are closed, and the second inlet valve 16e₆ and the first outlet valve 16e₇ are opened. In addition, the valve 12a in the cooling water path 12 is set to supply the cooling water to the second heat exchanger 16e₄ and the condenser 16e₂, and a valve 3a in the heat source fluid path 3 is set to supply the heat source fluid to the first heat exchanger 16e₃.

The operations of the evaporator 16e₁, the condenser 16e₂, the first heat exchanger 16e₃, and the second heat exchanger 16e₄ in FIG. 48 are respectively similar to the operations of the evaporator 16e₁, the condenser 16e₂, the second heat exchanger 16e₄, and the first heat exchanger 16e₃ in FIG. 47. That is, in FIGS. 47 and 48, roles of the first heat exchanger 16e₃ and the second heat exchanger 16e₄ are reversed. As a result, the first and second adsorption agents K₃, K₄ alternately repeat adsorption and desorption of the cooling medium.

In general, the absorption type refrigerator 16 has an advantage that the cooling performance is high and an advantage that noises to be generated are small. On the other hand, the adsorption type refrigerator 16 has an advantage that a low-temperature heat source fluid tends to be easily used.

The explanation in FIGS. 46 to 48 can be applied to the refrigerator 16 in FIG. 44 when the heat source fluid path 3 is replaced by a heat source fluid path 23.

BRIEF DESCRIPTION OF THE DRAWINGS

FIGS. 1 to 8 are schematic diagrams showing the configuration of a power generating system according to each of first to eighth embodiments;

FIGS. 9 and 10 are schematic diagrams each showing the configuration of a power generating system according to each of a ninth embodiment and a modification thereof;

FIGS. 11 and 12 are schematic diagrams each showing the configuration of a power generating system according to each of a tenth embodiment and a modification thereof;

FIGS. 13 to 24 are schematic diagrams each showing the configuration of a power generating system according to each of eleventh to twenty-second embodiments;

FIGS. 25 to 32 are schematic diagrams each showing the configuration of a cooling system according to each of twenty-third to thirtieth embodiments;

FIGS. 33 and 34 are schematic diagrams each showing the configuration of a cooling system according to each of a thirty-first embodiment and a modification thereof;

FIGS. 35 and 36 are schematic diagrams each showing the configuration of a cooling system according to each of a thirty-second embodiment and a modification thereof;

FIGS. 37 and 38 are schematic diagrams showing first and second examples representing the configuration of a conventional power generating system;

FIG. 39 is a supplementary diagram explaining the conventional power generating system;

FIGS. 40 and 41 are schematic diagrams showing third and fourth examples representing the configuration of the conventional power generating system;

FIG. 42 is a schematic diagram showing a fifth example representing the configuration of a conventional cooling system;

FIG. 43 is a schematic diagram explaining an operation of a refrigerator in FIG. 42;

FIG. 44 is a schematic diagram showing a sixth example representing the configuration of the conventional cooling system;

FIG. 45 is a supplementary diagram explaining the conventional cooling system;

FIG. 46 is a schematic diagram showing a first specific example of the refrigerator in FIG. 42;

FIGS. 47 and 48 are schematic diagrams showing a second specific example of the refrigerator in FIG. 42;

FIG. 49 is a supplementary diagram explaining the power generating system according to the first embodiment; and

FIG. 50 is a supplementary diagram explaining a cooling system according to a twenty-third embodiment.

DETAILED DESCRIPTION

Embodiments will now be explained with reference to the accompanying drawings.

In turbine power generation using hot spring heat, solar energy, a small-sized biomass boiler, factory exhaust heat, geothermal steam and the like as heat sources, a difference in temperature across the evaporator 4 is small, and a difference in pressure across the expansion module 7 is small. Further, since the expansion module 7 is small in size, a power generation coefficient or an energy utilization rate of the power generating system is low.

The power generation coefficient is a ratio between thermal energy given to an operating fluid by the evaporator 4 and electrical energy generated by the power generator 8 (refer to the first, second and fourth examples). However, the power generation coefficient of the third example is a ratio between the thermal energy that the operating fluid first has and the electrical energy generated by the power generator 8.

In addition, the ratio called the energy utilization rate in the present specification is a ratio between thermal energy given to a heat source fluid by the heat source fluid heater 1 and energy used by the power generating system (refer to the first and second examples). However, the energy utilization rate of the third example is a ratio between the thermal energy that the operating fluid first has and the energy used by the power generating system. In addition, the energy utilization rate of the fourth example is a ratio between the thermal energy given to the operating fluid by the evaporator 4 and the energy used by the power generating system. The conventional example of the energy used by the power generating system is electrical energy generated by the power generator 8.

For example, the power generation coefficient of each of the first to fourth examples is 10% or less, and 90% or more of the thermal energy given to the operating fluid is released to the cooling water as the condensation heat of the operating fluid. However, a temperature of the cooling water having collected the condensation heat is low, and the use value is low. For example, in a case of having collected the condensation heat by using tap water as cooling water, a temperature of the cooling water is approximately 30° C. Therefore, the condensation heat of the operating fluid in the first to fourth examples is discarded.

For example, in the power generating system (first example) in FIG. 37, when the thermal energy given to the operating fluid by the evaporator 4 is assumed to be 100, the thermal energy given to the heat source fluid by the heat source fluid heater 1 is approximately 100. In addition, the rotational energy of the expansion module 7 is approximately 10, and the electrical energy generated by the power generator 8 is approximately 10. However, consumption power of pumps 2, 5, 11 or the blower 14 will be ignored. Thereby, the power generation coefficient becomes approximately 10% (10/100), and the energy utilization rate becomes approximately 10% (10/100). This is the same as in the power generating systems (second to fourth examples) in FIG. 38, FIGS. 40 and 41.

In this way, in the turbine power generation using the hot spring heat, the solar energy, the small-sized biomass boiler, the factory exhaust heat, the geothermal steam and the like as the heat sources, a lot of the energy is wasteful. Therefore, it is preferable that the energy utilization rate of the power generating system is improved to reduce the waste of the energy.

In addition, in the cooling system in FIG. 42 or FIG. 44, the heat of the heat source fluid or the cooled fluid is given to the cooling water by the refrigerator 16, and the heat of the cooling water is discarded to the atmospheric air in the cooling tower 13. In this way, in the conventional cooling system, in many cases the exhaust heat of the refrigerator 16 is discarded to the atmospheric air. The reason is that a temperature of the cooling water having absorbed the heat of the heat source fluid or the cooled fluid is not high and the heat of the cooling water is low-quality heat, and therefore, a value of using the heat of the cooling water is low.

In the refrigerator 16 using the hot spring heat, the solar energy, the small-sized biomass boiler, the factory exhaust heat and the like as the heat sources, the temperature of the heat source fluid is low. Therefore, COP (COP: coefficient of performance) of the refrigerator 16 becomes smaller. COP is found by dividing an absolute value E2 of the cold heat produced by the refrigerator 16 by heat E1 used in a drive of the refrigerator 16 (COP=E2/E1). On the other hand, exhaust heat E3 of the refrigerator 16 is an addition of the absolute value E2 of the cold heat and the drive heat E1 (E3=E1+E2). Accordingly, the exhaust heat E3 of the refrigerator 16 is represented according to the following formula (1).

E3=E2 (1/COP+1)   (1)

In this way, when the refrigerator 16 produces the cold heat, the exhaust heat E3 greater than the absolute value E2 of the cold heat is generated. Therefore, it is desirable that this low-quality exhaust heat E3 is not put aside but is effectively used.

In one embodiment, an exhaust heat collecting system of collecting exhaust heat in a fluid treatment system. The fluid treatment system includes a fluid path configured to include at least an operating fluid path or a cooled fluid path among a first heat source fluid path, a second heat source fluid path, the operating fluid path and the cooled fluid path, the first heat source fluid path conveying a first heat source fluid, the second heat source fluid path conveying a second heat source fluid heated by heat of the first heat source fluid, the operating fluid path conveying an operating fluid, the cooled fluid path conveying a cooled fluid, the operating fluid being conveyed through or not through an evaporator that vaporizes the operating fluid by using the first or second heat source fluid, the cooled fluid being conveyed through a cooling module that cools the cooled fluid. The fluid treatment system further includes a fluid treatment module configured to include an expansion module that rotates and drives to expand the operating fluid, a power generator that is connected to a rotational shaft of the expansion module, and a condenser that condenses the operating fluid, or configured to include a heat absorbing module that absorbs heat of the first or second heat source fluid, and a heat releasing module that releases heat received from the cooled fluid and heat absorbed by the heat absorbing module. The exhaust heat collecting system includes a water path configured to supply water to the condenser or the heat releasing module, heat the water by the condensation in the condenser or by the heat release in the heat releasing module, and convey the water of a first temperature discharged from the condenser or the heat releasing module. The exhaust heat collecting system further includes a heater configured to heat the water from the water path by using the first heat source fluid, the second heat source fluid or the operating fluid to produce the water of a second temperature to be used as hot water or to produce steam.

In FIGS. 1 to 36, 49 and 50, components identical or similar to those in FIGS. 37 to 48 are referred to as identical signs, and an explanation overlapping the explanation in FIGS. 37 to 48 is omitted.

First Embodiment

FIG. 1 is a schematic diagram showing the configuration of a power generating system according to a first embodiment.

The power generating system in FIG. 1, as similar to the power generating system in FIG. 37, includes the heat source fluid heater 1, the heat source fluid pump 2, the heat source fluid path 3, the evaporator 4, the operating fluid pump 5, the operating fluid path 6, the expansion module 7, the power generator 8 and the condenser 9. The power generating system in FIG. 1 further includes a heater 31, a hot water tank 32, a water pump 33, and a water path 34 configuring an exhaust heat collecting system of collecting the exhaust heat of the power generating system.

The heat source fluid (first heat source fluid) is conveyed through the heat source fluid path 3 by the heat source fluid pump 2, and is heated by the heat source fluid heater 1. The heat source fluid according to the present embodiment is heated in the heat source fluid heater 1 obtaining heat from a heat source of non-fossil fuel. An example of this heat source fluid heater 1 includes a small-sized biomass boiler using biomass fuel as the heat source, a solar energy collector using solar energy as the heat source, an exhaust heat collector using factory exhaust heat as the heat source, and the like. The factory exhaust heat itself can be generally obtained from fossil fuel, but the fossil fuel is burned not in the heat source fluid heater 1, but outside of the heat source fluid heater 1. Therefore, the factory exhaust heat is also classified into the heat source in the non-fossil fuel. The heat source fluid discharged from the heat source fluid heater 1 flows into the evaporator 4, and is lowered in temperature by heating the operating fluid in the evaporator 4.

The heat source fluid in the present embodiment, as shown in FIG. 39, may be hot spring water springing forth from the ground 10. In this case, the power generating system in

FIG. 1 may not include the heat source fluid heater 1. The heat source fluid in the present embodiment may circulate as shown in FIG. 37 or may not circulate as shown in FIG. 39. This is the same as in second to tenth embodiments to be described later.

The operating fluid of the liquid is conveyed through the operating fluid path 6 by the operating fluid pump 5, is heated by the evaporator 4, and is converted in phase into the operating fluid of the gas. An example of the operating fluid is a low-boiling medium of CFC or the like. The operating fluid discharged from the evaporator 4 flows into the expansion module 7 and expands in the expansion module 7 to drive a rotational shaft of the expansion module 7. The rotational shaft of the expansion module 7 is connected to the power generator 8, and the power generator 8 generates power by using the shaft power of the rotational shaft. The operating fluid is lowered in pressure and temperature in the expansion module 7, is discharged from the expansion module 7 and flows into the condenser 9. The operating fluid having flowed into the condenser 9 is cooled by water in the condenser 9 to be converted in phase into an operating fluid of the liquid.

The water is conveyed through the water path 34 by the water pump 33 and is heated by condensation heat of the operating fluid in the condenser 9. The water discharged from the condenser 9 is conveyed through the water path 34, and is supplied to the heater 31.

The heater 31 is provided in the heat source fluid path 3. The heater 31 heats the water from the water path 34 by using the heat source fluid of the heat source fluid path 3 and produces water to be used as hot water. The hot water is conveyed through the water path 34 and is reserved in the hot water tank 32. The heater 31 in the present embodiment heats the water by using the heat source fluid flowing downstream of the evaporator 4. The heat source fluid discharged from the evaporator 4 flows into the heater 31, and is lowered in temperature by heating the water in the heater 31. The heat source fluid circulates among the heat source fluid heater 1, the evaporator 4 and the heater 31 through the heat source fluid path 3.

In the present embodiment, the condensation heat discharged in the condenser 9 is given to the water before being heated by the heater 31 without being given to the cooling tower 13. An example of the water includes tap water. In addition, a temperature of the reserved hot water is made to, for example, 60° C. estimated as a generally usable hot water temperature. This hot water is effectively used in bathing facilities, for dish washing in restaurants, and the like. In a case of using the hot water in linen laundry in hospitals, it is preferable to heat the hot water to 80° C. In the present embodiment, since there is no heat put aside externally, the energy utilization rate improves to 100%.

Here, a temperature of water in the water pump 33 is set to 15° C., a temperature of water heated by the condenser 9 is set to 30° C., and a temperature of water heated by the heater 31 is set to 60° C. 30° C. is set in the example of the first temperature, and 60° C. is set in the example of the second temperature.

In this case, when the thermal energy given to the heat source fluid by the heat source fluid heater 1 is assumed to be 100, electrical energy generated by the power generator 8, thermal energy given to water by the condenser 9 and thermal energy given to water by the heater 31 are respectively 3.6, 32.1 and 4.3. Accordingly, the energy utilization rate becomes 100% ((3.6+32.1+64.3)/100).

FIG. 49 is a supplementary diagram explaining the power generating system according to the first embodiment.

The power generating system in FIG. 49 includes the components shown in FIG. 1, and besides, the cooling water pump 11, the cooling water path 12, the cooling tower 13, the blower 14, and the atmosphere introducing portion 15.

In FIG. 49, the water in the water path 34 is heated only by the heater 31, and is not heated in the condenser 9. The condensation heat discharged in the condenser 9 is put aside externally. In this case, the energy utilization rate by the above-mentioned numerical example becomes 68% ((3.6+64.3)/100).

As described above, the power generating system according to the present embodiment uses the heat source fluid from the heat source fluid path 3 to heat the water of the first temperature and produce the water of the second temperature to be used as the hot water. Therefore, according to the present embodiment, it is possible to improve the energy utilization rate in the power generating system.

The present embodiment is applicable even if the heat source in the heat source fluid heater 1 is a high-temperature heat source, but is effectively applicable in a case where the heat source in the heat source fluid heater 1 is a low-temperature heat source such as biomass fuel, solar energy, factory exhaust heat and hot spring heat. Further, the present embodiment is effectively applicable in any heat source in a case where a temperature of the heat source fluid in an inlet of the evaporator 4 is 200° C. or less. This is true of second to twenty-second embodiments to be described later. The reason is that in a case where the heat source in the heat source fluid heater 1 is a low-temperature heat source, the power generation coefficient is lower, and the energy utilization rate in a case where the present embodiment is not applied is low. According to the present embodiment, it is possible to remarkably improve the energy utilization rate in a case where the heat source in the heat source fluid heater 1 is the low-temperature heat source. This is true of the second to twenty-second embodiments to be described later.

In addition, the configuration of the present embodiment is effectively applicable in a case where the maximum temperature of the heat source fluid in the heat source fluid path 3 is 200° C. or less.

In addition, the heater 31 may produce steam instead of producing the water to be used as the hot water. That is, the heater 31 may produce water of a gas instead of producing the water of the liquid. In this case, the hot water tank 32 is replaced by, for example, a facility for reserving, conveying or using the steam. This is true of the second to twenty-second embodiments to be described later (however, in the fourth and twentieth embodiments, a heat use destination 37 is replaced by, for example, a facility for reserving, conveying or using the steam).

Second Embodiment

FIG. 2 is a schematic diagram showing the configuration of a power generating system according to a second embodiment. In FIG. 2, components identical or similar to those in FIG. 1 are referred to as identical signs, and an explanation overlapping the explanation in FIG. 1 is omitted. This is true mutually between FIGS. 1 to 36.

The heater 31 in the first embodiment, as shown in FIG. 1, heats the water by using the heat source fluid flowing downstream of the evaporator 4. On the other hand, the heater 31 in the second embodiment, as shown in FIG. 2, heats the water by using the heat source fluid flowing upstream of the evaporator 4.

In the present embodiment, a temperature of the heat source fluid in the inlet of the heater 31 is higher than a temperature of the heat source fluid in the inlet of the evaporator 4. Therefore, according to the present embodiment, the water tends to be easily heated to a higher temperature. On the other hand, according to the first embodiment, it is possible to use more percentage of thermal energy for the power generation by the power generator 8.

Third Embodiment

FIG. 3 is a schematic diagram showing the configuration of a power generating system according to a third embodiment.

The evaporator 4 and the heater 31 in the first and second embodiments are, as shown in FIG. 1 and FIG. 2, arranged in series to the flow of the heat source fluid. On the other hand, the evaporator 4 and the heater 31 in the third embodiment are, as shown in FIG. 3, arranged in parallel to the flow of the heat source fluid.

The heat source fluid path 3 in FIG. 3 is branched into a first branch flow path 35 provided with the evaporator 4 and a second branch flow path 36 provided with the heater 31. The first and second branch flow paths 35, 36 are branched from a single flow path L₁ at a first point P₁ and merge into the single flow path L₁ at a second point P₂.

In the present embodiment, a temperature of the heat source fluid in the inlet of the heater 31 is equal to a temperature of the heat source fluid in the inlet of the evaporator 4. Therefore, according to the present embodiment, both of the operating fluid and the water tend to be easily heated to a high temperature.

Fourth Embodiment

FIG. 4 is a schematic diagram showing the configuration of a power generating system according to a fourth embodiment.

In FIG. 4, the hot water tank 32 is replaced by the heat use destination 37, and the water path 34 is replaced by a circulation water path 38.

The water in the present embodiment is conveyed through the circulation water path 38 by the water pump 33, and is heated by the condensation heat of the operating fluid in the condenser 9. The water discharged from the condenser 9 is conveyed through the circulation water path 38, and is supplied to the heater 31. The heater 31 uses the heat source fluid from the heat source fluid path 3 to heat this water and produce water to be used as the hot water. The hot water is conveyed through the circulation water path 38 to be supplied to the heat use destination 37.

An example of the heat use destination 37 includes floor heating. The water supplied to the heat use destination 37 is lowered in temperature by being used as the heat source in the heat use destination 37. The water discharged from the heat use destination 37 is conveyed through the circulation water path 38 to be again supplied to the condenser 9. In this way, the water in the present embodiment circulates through the circulation water path 38 among the condenser 9, the heater 31 and the heat use destination 37. In a case of supplying the steam to the heat use destination 37 instead of the hot water, an example of the heat use destination 37 includes steam heating.

In a case of using the hot water in bathing facilities or for dish washing in restaurants, the hot water is disposable. On the other hand, in a case of using the hot water for floor heating, the hot water can be repeatedly used. As a result, in the present embodiment, a limited amount of water can be repeatedly used by circulating the water through the circulation water path 38. The heat use destination 37 may be facilities other than the floor heating or the steam heating.

Fifth Embodiment

FIG. 5 is a schematic diagram showing the configuration of a power generating system according to a fifth embodiment.

The heat source fluid path 3 in FIG. 5 includes a first bypass flow path 44 bypassing a first flow path provided with the evaporator 4, and a second bypass flow path 48 bypassing a second flow path provided with the heater 31. The heat source fluid path 3 in FIG. 5 is provided with a plurality of valves 41 to 43 and 45 to 47.

The first bypass flow path 44 is branched from the flow path L₁ at the first point P₁ and merges into the flow path L₁ at a third point P₃. The flow path L₁ between the first point P₁ and the third point P₃ is the above-mentioned first flow path. The valve 41 is provided in the first flow path between the first point P₁ and the evaporator 4. The valve 42 is provided in the first flow path between the evaporator 4 and the third point P₃. The valve 43 is provided in the first bypass flow path 44.

The second bypass flow path 48 is branched from the flow path L₁ at a fourth point P₄ and merges into the flow path L₁ at the second point P₂. The flow path L₁ between the fourth point P₄ and the second point P₂ is the above-mentioned second flow path. The valve 45 is provided in the second flow path between the fourth point P₄ and the heater 31. The valve 46 is provided in the second flow path between and the heater 31 and the second point P₂. The valve 47 is provided in the second bypass flow path 48.

In the present embodiment, upon performing both of the power generation and the hot water production, the valves 41, 42, 45, 46 are opened and the valves 43, 47 are closed. In this case, the water is heated by the condenser 9 and the heater 31 to be a high-temperature hot water.

In addition, upon performing only the power generation, the valves 41, 42, 47 are opened and the valves 43, 45, 46 are closed. In this case, the water is heated only by the condenser 9 to be a low-temperature hot water.

In addition, upon performing only the hot water production, the valves 43, 45, 46 are opened and the valves 41, 42, 47 are closed. In this case, the water is heated only by the heater 31. Therefore, in a case of producing the high-temperature hot water without lowering the temperature under this condition, a producing amount of the hot water is made small.

As described above, according to the present embodiment, it is possible to select three kinds of operations in regard to the power generation and the hot water production by using the first and second bypass flow paths 44, 48. In the present embodiment, two kinds of operations may be selected by providing only one of the first and second bypass flow paths 44, 48 to the power generating system.

Sixth Embodiment

FIG. 6 is a schematic diagram showing the configuration of a power generating system according to a sixth embodiment.

The power generating system in FIG. 6 includes the components shown in FIG. 3, and besides, includes a plurality of valves 51 to 54. The valve 51 is provided in the first branch flow path 35 between the first point P₁ and the evaporator 4. The valve 52 is provided in the first branch flow path 35 between the evaporator 4 and the second point P₂. The valve 53 is provided in the second branch flow path 36 between the first point P₁ and the heater 31. The valve 54 is provided in the second branch flow path 36 between the heater 31 and the second point P₂.

In the present embodiment, upon performing both of the power generation and the hot water production, the valves 51 to 54 are opened. In this case, the water is heated by the condenser 9 and the heater 31 to be a high-temperature hot water.

In addition, upon performing only the power generation, the valves 51, 52 are opened and the valves 53, 54 are closed. In this case, the water is heated only by the condenser 9 to be a low-temperature hot water.

In addition, upon performing only the hot water production, the valves 53, 54 are opened and the valves 51, 52 are closed. In this case, the water is heated only by the heater 31. Therefore, in a case of producing the high-temperature hot water without lowering the temperature under this condition, a producing amount of the hot water is made small.

As described above, according to the present embodiment, it is possible to select three kinds of operations in regard to the power generation and the hot water production by using the first and second branch flow paths 37, 38. In the present embodiment, two kinds of operations may be selected by providing only one of a pair of the valves 51, 52 and a pair of the valves 53, 54 to the power generating system.

Seventh Embodiment

FIG. 7 is a schematic diagram showing the configuration of a power generating system according to a seventh embodiment.

The power generating system in FIG. 7 includes the heat source fluid heater 21, the heat source fluid pump 22 and the heat source fluid path 23 in addition to the components shown in FIG. 1. In the explanation in FIG. 7, as similar to the explanation in FIG. 38, titles of the first heat source fluid heater 1, the first heat source fluid pump 2 and the first heat source fluid path 3, the second heat source fluid heater 21, the second heat source fluid pump 22, and the second heat source fluid path 23 are adopted. In addition, the heat source fluid of the first heat source fluid path 3 is called a first heat source fluid, and the heat source fluid of the second heat source fluid path 23 is called a second heat source fluid.

The first heat source fluid is conveyed through the first heat source fluid path 3 by the first heat source fluid pump 2, and is heated by the first heat source fluid heater 1. The first heat source fluid discharged from the first heat source fluid heater 1 flows into the second heat source fluid heater 21, and is lowered in temperature by heating the second heat source fluid in the second heat source fluid heater 21.

The second heat source fluid is conveyed through the second heat source fluid path 23 by the second heat source fluid pump 22, and is heated by the second heat source fluid heater 21. The second heat source fluid discharged from the second heat source fluid heater 21 flows into the evaporator 4, and is lowered in temperature by heating the operating fluid in the evaporator 4.

The operating fluid of the liquid is conveyed through the operating fluid path 6 by the operating fluid pump 5, is heated by the evaporator 4, and is converted in phase into the operating fluid of the gas. An example of the operating fluid is a low-boiling medium of CFC or the like. The operating fluid discharged from the evaporator 4 flows into the expansion module 7 and expands in the expansion module 7 to drive the rotational shaft of the expansion module 7. The rotational shaft of the expansion module 7 is connected to the power generator 8, and the power generator 8 generates power by using the shaft power of the rotational shaft. The operating fluid is lowered in pressure and temperature in the expansion module 7, is discharged from the expansion module 7 and flows into the condenser 9. The operating fluid having flowed into the condenser 9 is cooled by water in the condenser 9 to be converted in phase into the operating fluid of the liquid.

The water is conveyed through the water path 34 by the water pump 33 and is heated by condensation heat of the operating fluid in the condenser 9. The water discharged from the condenser 9 is conveyed through the water path 34, and is supplied to the heater 31.

In the present embodiment, the heater 31 is provided in the second heat source fluid path 23. The heater 31 heats the water from the water path 34 by using the second heat source fluid and produces water to be used as hot water. The hot water is conveyed through the water path 34 and is reserved in the hot water tank 32. The heater 31 in the present embodiment heats the water by using the second heat source fluid flowing downstream of the evaporator 4. The second heat source fluid discharged from the evaporator 4 flows into the heater 31, and is lowered in temperature by heating the water in the heater 31. The second heat source fluid circulates among the second heat source fluid heater 21, the evaporator 4 and the heater 31 through the second heat source fluid path 23.

Here, the power generating system in FIG. 1 and the power generating system in FIG. 7 will be compared.

In FIG. 1, since separated substances are accumulated in the evaporator 4 or the heater 31 depending upon components contained in the heat source fluid, it is necessary to frequently disassemble the evaporator 4 or the heater 31 for the cleaning. In this case, the operating fluid path 6 containing a low-boiling medium such as CFC or the water path 34 used in bathing facilities or for dish washing in restaurants will be disassembled, but particularly, the disassembly of the operating fluid path 6 is not preferable. On the other hand, in FIG. 7, not the evaporator 4 or the heater 31 but the second heat source fluid heater 21 is disassembled and cleaned, and therefore, it is not necessary to disassemble the operating fluid path 6.

As described above, the power generating system in the present embodiment heats the water of the first temperature by using the second heat source fluid to produce the water of the second temperature to be used as the hot water. Therefore, according to the present embodiment, it is possible to improve the energy utilization rate in the power generating system.

The heat source fluid heater 21, the heat source fluid pump 22, the heat source fluid path 23 and the heater 31 in the present embodiment may be applied to any of the second to sixth embodiments. This is true of the heat source fluid heater 21, the heat source fluid pump 22, the heat source fluid path 23 and the heater 31 in the eighth to tenth embodiments to be described later.

In addition, the second heat source fluid in the present embodiment is heated by the heat of the first heat source fluid, not through the other heat source fluid, but may be heated through one or more kinds of third heat source fluids by the heat of the first heat source fluid. That is, the second heat source fluid in the present embodiment may be directly or indirectly heated by the heat of the first heat source fluid. This is true of the eighth to tenth embodiments to be described later.

In addition, the first heat source fluid in the present embodiment is heated by the heat of the low-temperature heat source such as biomass fuel, not through the other heat source fluid, but may be heated through one or more kinds of fourth heat source fluids by the heat of the low-temperature heat source. That is, the first heat source fluid in the present embodiment may be directly or indirectly heated by the heat of the low-temperature heat source. This is true of the eighth to tenth embodiments to be described later.

Further, the configuration of the present embodiment can be effectively applied in a case where the maximum temperature of the second heat source fluid in the second heat source fluid path 23 is, for example, 200° C. or less.

Eighth Embodiment

FIG. 8 is a schematic diagram showing the configuration of a power generating system according to an eighth embodiment. In FIG. 8, components identical or similar to those in FIG. 7 are referred to as identical signs, and an explanation overlapping the explanation in FIG. 7 is omitted. This is true of the ninth and tenth embodiments.

In the present embodiment, the heater 31 is provided in the first heat source fluid path 3. The heater 31 heats the water from the water path 34 by using the first heat source fluid to produce water to be used as hot water. The hot water is conveyed through the water path 34 and is reserved in the hot water tank 32. The heater 31 in the present embodiment heats the water by using the first heat source fluid flowing downstream of the second heat source fluid heater 21. The first heat source fluid discharged from the second heat source fluid heater 21 flows into the heater 31, and is lowered in temperature by heating the water in the heater 31. The first heat source fluid circulates among the first heat source fluid heater 1, the second heat source fluid heater 21 and the heater 31 through the first heat source fluid path 3.

In many cases, a temperature of the first heat source fluid in the inlet of the heater 31 in the eighth embodiment is higher than a temperature of the second heat source fluid in the inlet of the heater 31 in the seventh embodiment. Therefore, according to the eighth embodiment, the water tends to be easily heated to a higher temperature. In addition, according to the eighth embodiment, it is not necessary to disassemble and clean the water path 34. On the other hand, according to the seventh embodiment, it is possible to use the higher percentage of thermal energy for the power generation by the power generator 8.

Ninth Embodiment

FIG. 9 is a schematic diagram showing the configuration of a power generating system according to a ninth embodiment.

The heater 31 in the eighth embodiment, as shown in FIG. 8, heats the water by using the first heat source fluid flowing downstream of the second heat source fluid heater 21. On the other hand, the heater 31 in the ninth embodiment, as shown in FIG. 9, heats the water by using the first heat source fluid flowing upstream of the second heat source fluid heater 21.

In the present embodiment, a temperature of the first heat source fluid in the inlet of the heater 31 is higher than a temperature of the first heat source fluid in the inlet of the second heat source fluid heater 21. Therefore, according to the present embodiment, the water tends to be easily heated to a higher temperature. On the other hand, according to the eighth embodiment, it is possible to use the higher percentage of the thermal energy for the power generation by the power generator 8.

FIG. 10 is a schematic diagram showing the configuration of a power generating system according to a modification of the ninth embodiment.

The heater 31 in the seventh embodiment, as shown in FIG. 7, heats the water by using the second heat source fluid flowing downstream of the evaporator 4. On the other hand, the heater 31 in the present modification, as shown in FIG. 10, heats the water by using the second heat source fluid flowing upstream of the evaporator 4.

In the present modification, a temperature of the second heat source fluid in the inlet of the heater 31 is higher than a temperature of the second heat source fluid in the inlet of the evaporator 4. Therefore, according to the present modification, the water tends to be easily heated to a higher temperature. In addition, according to the present modification, it is not necessary to disassemble and clean the water path 34. On the other hand, according to the seventh embodiment, it is possible to use the higher percentage of the thermal energy for the power generation by the power generator 8.

Tenth Embodiment

FIG. 11 is a schematic diagram showing the configuration of a power generating system according to a tenth embodiment.

The power generating system in FIG. 11 includes first and second heaters 31a, 31b instead of the heater 31. The first heater 31a is provided in the first heat source fluid path 3. The second heater 31b is provided in the second heat source fluid path 23. The first and second heaters 31a, 31b heat the water of the first temperature to produce the water of the second temperature to be used as hot water.

The first heat source fluid is conveyed through the first heat source fluid path 3 by the first heat source fluid pump 2, and is heated by the first heat source fluid heater 1. The first heat source fluid discharged from the first heat source fluid heater 1 flows into the second heat source fluid heater 21, and is lowered in temperature by heating the second heat source fluid in the second heat source fluid heater 21.

The second heat source fluid is conveyed through the second heat source fluid path 23 by the second heat source fluid pump 22, and is heated by the second heat source fluid heater 21. The second heat source fluid discharged from the second heat source fluid heater 21 flows into the evaporator 4, and is lowered in temperature by heating the operating fluid in the evaporator 4.

The operating fluid of the liquid is conveyed through the operating fluid path 6 by the operating fluid pump 5, is heated by the evaporator 4, and is converted in phase into the operating fluid of the gas. An example of the operating fluid is a low-boiling medium of CFC or the like. The operating fluid discharged from the evaporator 4 flows into the expansion module 7 and expands in the expansion module 7 to drive the rotational shaft of the expansion module 7. The rotational shaft of the expansion module 7 is connected to the power generator 8, and the power generator 8 generates power by using shaft power of the rotational shaft. The operating fluid is lowered in pressure and temperature in the expansion module 7, is discharged from the expansion module 7 and flows into the condenser 9. The operating fluid having flowed into the condenser 9 is cooled by water in the condenser 9 to be converted in phase into the operating fluid of the liquid.

The water is conveyed through the water path 34 by the water pump 33 and is heated by condensation heat of the operating fluid in the condenser 9. The water discharged from the condenser 9 is conveyed through the water path 34, and is supplied to the second heater 31b. A temperature of the water in the inlet of the condenser 9 is, for example, 15° C. A temperature of the water in the outlet of the condenser 9 is, for example, 30° C. 30° C. is an example of the first temperature.

The second heater 31b heats the water from the water path 34 by using the second heat source fluid. The water heated by the second heater 31b is conveyed through the water path 34, and is supplied to the first heater 31a. The first heater 31a heats the water flowing downstream of the second heater 31b by using the first heat source fluid, and produces the water to be used as the hot water. A temperature of the hot water is, for example, 60° C. 60° C. is an example of the second temperature. The hot water is conveyed through the water path 34, and is reserved in the hot water tank 32.

The first heater 31a in the present embodiment heats the water by using the first heat source fluid flowing downstream of the second heat source fluid heater 21. The first heat source fluid discharged from the second heat source fluid heater 21 flows into the first heater 31a, and is lowered in temperature by heating the water in the first heater 31a. The first heat source fluid circulates among the first heat source fluid heater 1, the second heat source fluid heater 21 and the first heater 31a through the first heat source fluid path 3.

In addition, the second heater 31b in the present embodiment heats the water by using the second heat source fluid flowing downstream of the evaporator 4. The second heat source fluid discharged from the evaporator 4 flows into the second heater 31b, and is lowered in temperature by heating the water in the second heater 31b. The second heat source fluid circulates among the second heat source fluid heater 21, the evaporator 4 and the second heater 31b through the second heat source fluid path 23.

In the present embodiment, the first heater 31a is heated by the second heater 31b to heat the water flowing out of the second heater 31b, but in the flowing order, the second heater 31b may be heated by the first heater 31a and may heat the water flowing out of the first heater 31a. In a case where a temperature of the first heat source fluid in the outlet of the first heater 31a is lower than a temperature of the second heat source fluid in the inlet of the second heater 31b, it is preferable to arrange the first heater 31a downstream of the second heater 31b. In addition, in the present embodiment, the first heater 31a and the second heater 31b are arranged in series to the flow of the water, but may be arranged in parallel to the flow of the water.

FIG. 12 is a schematic diagram showing the configuration of a power generating system according to a modification of the tenth embodiment.

The first heater 31a of the tenth embodiment, as shown in FIG. 11, heats the water by using the first heat source fluid flowing downstream of the second heat source fluid heater 21. On the other hand, the first heater 31a of the present modification, as shown in FIG. 12, heats the water by using the first heat source fluid flowing upstream of the second heat source fluid heater 21.

In addition, the second heater 31b of the tenth embodiment, as shown in FIG. 11, heats the water by using the second heat source fluid flowing downstream of the evaporator 4. On the other hand, the first heater 31a of the present modification, as shown in FIG. 12, heats the water by using the second heat source fluid flowing upstream of the evaporator 4.

In this manner, the first heater 31a may be arranged downstream or upstream of the second heat source fluid heater 21. Likewise, the second heater 31b may be arranged downstream or upstream of the evaporator 4. In addition, one of the first and second heaters 31a, 31b may be arranged as shown in FIG. 11, and the other of the first and second heaters 31a, 31b may be arranged as shown in FIG. 12.

In the present modification, the first heater 31a heats the water flowing downstream of the second heater 31b, but the second heater 31b may heat the water flowing downstream of the first heater 31a. Further, in the present modification, the first and second heaters 31a, 31b are arranged in series to the flow of the water, but the first and second heaters 31a, 31b may be arranged in parallel to the flow of the water.

As described above, the power generating system of the present embodiment includes the first and second heaters 31a, 31b instead of the heater 31. In a case of adopting this configuration, the heat exchangers in the power generating system increase in number, but the power generating system can be designed such that a difference in temperature between the heating fluid and the heated fluid is made small. Specifically, the power generating system can be designed such that a difference in temperature between the first heat source fluid and the second heat source fluid or a difference in temperature between the second heat source fluid and the operating fluid is made small. As a result, according to the present embodiment, the water tends to be easily heated to a higher temperature.

In addition, the first and second heaters 31a, 31b in FIGS. 11 and 12 may produce steam instead of producing the water to be used as the hot water. That is, the first and second heaters 31a, 31b may produce water of a gas instead of producing the water of the liquid. In this case, the hot water tank 32 is replaced by, for example, a facility for reserving, conveying or using the steam. This is true of third and fourth heaters 31c, 31d in twelfth, fourteenth, sixteenth, eighteenth, twentieth, twenty-first and twenty-second embodiments (however, in the twentieth embodiment, the heat use destination 37 is replaced by, for example, the facility for reserving, conveying or using the steam).

Eleventh Embodiment

FIG. 13 is a schematic diagram showing the configuration of a power generating system according to an eleventh embodiment.

When FIG. 1 and FIG. 13 are compared, the power generating system in FIG. 13 does not include the heat source fluid heater 1, the heat source fluid pump 2, the heat source fluid path 3, the evaporator 4 and the operating fluid pump 5 shown in FIG. 1. An example of the operating fluid flowing in the operating fluid path 6 in FIG. 13 is a gas of geothermal steam or the like.

The operating fluid path 6 in FIG. 13 is branched into a first fluid path 61 provided with the expansion module 7 and the condenser 9 and a second fluid path 62 provided with the heater 31. The first fluid path 61 and the second fluid path 62 are branched from a single flow path L₂ in a fifth point P₅. The operating fluid of the gas flowing in the operating fluid path 6 is branched in the fifth point P₅ and flows into the first fluid path 61 and the second fluid path 62.

The operating fluid having flowed in the first fluid path 61 is introduced in the expansion module 7 to drive the rotational shaft of the expansion module 7. The power generator 8 generates power by using the shaft power of the rotational shaft. The operating fluid is thereafter discharged into the first fluid path 61 from the expansion module 7, and flows into the condenser 9. The operating fluid having flowed into the condenser 9 is cooled by water (cooling water) from the water path 34 to be converted into the operating fluid of the liquid and be returned back to the ground.

On the other hand, the operating fluid having flowed in the second fluid path 62 is introduced in the heater 31. The heater 31 heats the water from the water path 34 by using the operating fluid in the second fluid path 62 to produce the water to be used as the hot water. The hot water is conveyed through the water path 34 to be reserved in the hot water tank 32. On the other hand, the operating fluid in the second fluid path 62 is lowered in temperature by heating the water in the heater 31 to be the condensed fluid, and is returned back to the ground. The operating fluid all may be condensed, only a part thereof may be condensed or the operating fluid may not be condensed at all (this is true of thirteenth, fifteenth and seventeenth embodiments, which will be described later).

The operating fluid in the first fluid path 61 is introduced in the expansion module 7 and is used as the operating fluid, but the operating fluid in the second fluid path 62 is not used as the operating fluid. However, since the operating fluid in the second fluid path 62 is the same as the operating fluid in the first fluid path 61, in the present embodiment the operating fluid in the second fluid path 62 is described as the operating fluid as similar to the operating fluid in the first fluid path 61. This is true of the subsequent embodiments.

According to the present embodiment, the heater 31 can be applied also to the power generating system not provided with the evaporator 4. The configuration of the present embodiment is effective since a ratio of the condensed heat to the power generation amount becomes large when the maximum temperature of the operating fluid in the operating fluid path 6 is 200° C. or less.

Twelfth Embodiment

FIG. 14 is a schematic diagram showing the configuration of a power generating system according to a twelfth embodiment.

In FIG. 14, the heater 31 in FIG. 13 is replaced by the third and fourth heaters 31c, 31d. The third heater 31c is provided in the second fluid path 62. The fourth heater 31d is provided downstream of the third heater 31c in the second fluid path 62.

In addition, the water path 34 in FIG. 14 is branched into a first water path 63 provided with the condenser 9 and a second water path 64 provided with the fourth heater 31d. The first and second water paths 63, 64 are branched from a single flow path L₃ in a sixth point P₆ and merge into the single flow path L₃ in a seventh point P₇. The water flowing in the water path 34 is branched into the first and second water paths 63, 64 in the sixth point P₆, and merges from the first and second water paths 63, 64 in the seventh point P₇. The third heater 31c is provided in the flow path L₃ (third water path) after the merging.

The operating fluid having flowed into the first fluid path is introduced in the expansion module 7 to drive the rotational shaft of the expansion module 7. The power generator 8 generates power by using the shaft power of the rotational shaft. The operating fluid is thereafter discharged into the first fluid path 61 from the expansion module 7, and flows into the condenser 9. The operating fluid having flowed into the condenser 9 is cooled by water (cooling water) from the first water path 63 to be converted into the operating fluid of the liquid and be returned back to the ground.

On the other hand, the operating fluid having flowed in the second fluid path 62 is introduced in the third heater 31c, and next, in the fourth heater 31d. The fourth heater 31d heats the water from the second water path 64 by using the operating fluid in the second fluid path 62. The water discharged from the condenser 9 to the first water path 63 and the water discharged from the fourth heater 31d to the second water path 64 merge in the seventh point P₇, which is introduced in the third heater 31c. The third heater 31c heats the water by using the operating fluid in the second fluid path 62 to produce the water to be used as the hot water. The hot water is conveyed through the water path 34 to be reserved in the hot water tank 32. On the other hand, the operating fluid in the second fluid path 62 is lowered in temperature by heating the water in the third and fourth heaters 31c, 31d to be the condensed fluid, which is returned back to the ground. The operating fluid all may be condensed, only a part thereof may be condensed or the operating fluid may not be condensed at all (this is true of fourteenth, sixteenth, eighteenth, twenty-third and twenty-fourth embodiments, which will be described later).

In the eleventh embodiment, in some cases the temperature of the operating fluid discharged from the heater is higher than that of the water discharged from the condenser 9. In this case, it is possible to further collect the heat of the potential heat amount of the operating fluid. On the other hand, in the present embodiment the third heater 31c collects the heat of the potential heat amount of the operating fluid by water and the fourth heater 31d collects heat of the potential heat amount of the operating fluid by lower-temperature water. Therefore, according to the present embodiment, it is possible to sufficiently collect the heat of the potential heat amount of the operating fluid.

Thirteenth Embodiment

FIG. 15 is a schematic diagram showing the configuration of a power generating system according to a thirteenth embodiment.

When FIGS. 1 and 15 are compared, the power generating system in FIG. 15 does not include the heat source fluid heater 1, the heat source fluid pump 2 and the heat source fluid path 3 shown in FIG. 1. An example of the evaporator 4 in FIG. 15 includes a small-sized biomass boiler for burning biomass fuel, a solar energy collector for collecting solar energy, and an exhaust heat collector for collecting factory exhaust heat or the like. An example of the operating fluid is water of a gas or liquid.

The operating fluid path 6 in FIG. 15 is branched into the first fluid path 61 provided with the expansion module 7 and the condenser 9 and the second fluid path 62 provided with the heater 31. The first fluid path 61 and the second fluid path 62 are branched from the single flow path L₂ in the fifth point P₅ and merge into the single flow path L₂ in an eighteenth point P₈. The operating fluid flowing in the operating fluid path 6 is branched into the first and second fluid paths 61, 62 in the fifth point P₅, and merges from the first fluid path 61 and the second fluid path 62 in the eighth point P_g. The evaporator 4 and the operating fluid pump 5 are provided in the flow path L₂ (third fluid path 66) after the merging. In addition, the first fluid path 61 is provided with an operating fluid pump 65.

The operating fluid of the liquid is conveyed through the operating fluid path 6 by the operating fluid pump 5 and is heated by the evaporator 4 to be converted into the operating fluid of a gas. The operating fluid of the gas discharged from the evaporator 4 is branched in the fifth point P₅, and flows into the first fluid path 61 and the second fluid path 62.

The operating fluid having flowed into the first fluid path 61 is introduced in the expansion module 7 to drive the rotational shaft of the expansion module 7. The power generator 8 generates power by using the shaft power of the rotational shaft. The operating fluid is thereafter discharged into the first fluid path 61 from the expansion module 7, and flows into the condenser 9. The operating fluid having flowed into the condenser 9 is cooled by water (cooling water) from the water path 34 to be converted into the operating fluid of the liquid and is conveyed to the eighth point P₈ by the operating fluid pump 65.

On the other hand, the operating fluid having flowed in the second fluid path 62 is introduced in the heater 31. The heater 31 heats the water from the water path 34 by using the operating fluid in the second fluid path 62 to produce the water used as the hot water. The hot water is conveyed through the water path 34 to be reserved in the hot water tank 32. On the other hand, the operating fluid in the second fluid path 62 is lowered in temperature to be the condensed fluid by heating the water in the heater 31, and is discharged to the eighth point P₈.

The operating fluid discharged from the condenser 9 to the first fluid path 61 and the operating fluid discharged from the heater 31 to the second fluid path 62 merge in the eighth point P₈ to be introduced in the evaporator 4. Thus, the operating fluid circulates among the evaporator 4, the expansion module 7, the condenser 9 and the heater 31 through the operating fluid path 6. The operating fluid pump 65 is provided as needed such that a pressure of the operating fluid flowing from the first fluid path 61 into the eighth point P₈ is made equal to or closer to a pressure of the operating fluid flowing from the second fluid path 62 into the eighth point P₈.

According to the present embodiment, the heater 31 can be applied also to the power generating system not provided with the heat source fluid heater 1. The present embodiment is applicable even if the heat source in the evaporator 4 is a high-temperature heat source, but is effectively applicable in a case where the heat source in the evaporator 4 is a low-temperature heat source such as biomass fuel, solar energy, factory exhaust heat or hot spring heat. This is true of fourteenth, seventeenth and eighteenth embodiments to be described later. The reason is that in a case where the heat source in the evaporator 4 is a low-temperature heat source, the power generation coefficient is lower, and the energy utilization rate in a case of not applying the present embodiment is low.

The configuration of the present embodiment is effectively applicable when the maximum temperature of the heat source fluid in the operating fluid path 6 is, for example, 200° C. or less.

Fourteenth Embodiment

FIG. 16 is a schematic diagram showing the configuration of a power generating system according to a fourteenth embodiment.

In FIG. 16, the heater 31 in FIG. 15 is replaced by the third and fourth heaters 31c, 31d. In addition, the water path 34 in FIG. 16 is branched into a first water path 63 provided with the condenser 9 and a second water path 64 provided with the fourth heater 31d. The above configuration is the same as the configuration shown in FIG. 14.

In the thirteenth embodiment, in some cases the temperature of the operating fluid discharged from the heater is higher than that of the water discharged from the condenser 9. In this case, it is possible to further collect heat of the potential heat amount of the operating fluid. On the other hand, in the present embodiment the third heater 31c collects the heat of the potential heat amount of the operating fluid by water, and the fourth heater 31d collects the heat of the potential heat amount of the operating fluid by low-temperature water. Therefore, according to the present embodiment, it is possible to sufficiently collect the heat of the potential heat amount of the operating fluid.

Fifteenth Embodiment

FIG. 17 is a schematic diagram showing the configuration of a power generating system according to a fifteenth embodiment.

The operating fluid path 6 in FIG. 13 is branched into the first fluid path 61 provided with the expansion module 7 and the condenser 9 and the second fluid path 62 provided with the heater 31. On the other hand, the operating fluid path 6 in FIG. 17 includes a fourth fluid path 67 that conveys the operating fluid discharged from an exhaust port 7a of the expansion module 7, and is provided with the condenser 9 and a fifth fluid path 68 that conveys the operating fluid extracted from an extraction port 7b of the expansion module 7 and is provided with the heater 31. The extraction port 7b of the expansion module 7 is provided in a preceding stage of the exhaust port 7a of the expansion module 7.

The configuration and function of the fourth and fifth fluid paths 67, 68 in FIG. 17 are the same as those of the first and second fluid paths 61, 62 in FIG. 13. Accordingly, the water discharged from the condenser 9 is heated by the operating fluid in the heater 31 to produce the hot water. According to the present embodiment, the heater 31 can be applied also to the power generating system not provided with the evaporator 4.

A temperature and a pressure of the operating steam in the extraction port 7b of the expansion module 7 are lower than a temperature and a pressure of the operating steam in the inlet of the expansion module 7. According to the present embodiment, it is possible to change the temperature and pressure of the operating steam for the heater 31 by changing a position of the extraction port 7b. In addition, according to the present embodiment, it is possible to use more energy of the operating fluid for power generation as compared to the eleventh embodiment. On the other hand, according to the eleventh embodiment, it is possible to adopt the heater 31 without providing the expansion module 7 with the extraction port 7b. This is true of the aforementioned twelfth to fourteenth embodiments and after-mentioned sixteenth to twenty-second embodiments.

Sixteenth Embodiment

FIG. 18 is a schematic diagram showing the configuration of a power generating system according to a sixteenth embodiment.

In FIG. 18, the first and second fluid paths 61, 62 in FIG. 14 are replaced by the fourth and fifth fluid paths 67, 68. Therefore, the condenser 9 is provided in the fourth fluid path 67, and the third and fourth heaters 31c, 31d are provided in the fifth fluid path 68.

According to the present embodiment, it is possible to sufficiently collect heat of the potential heat amount of the operating fluid by the third and fourth heaters 31c, 31d.

Seventeenth Embodiment

FIG. 19 is a schematic diagram showing the configuration of a power generating system according to a seventeenth embodiment.

In FIG. 19, the first and second fluid paths 61, 62 in FIG. 15 are replaced by the fourth and fifth fluid paths 67, 68. Therefore, the condenser 9 is provided in the fourth fluid path 67, and the heater 31 is provided in the fifth fluid path 68. Further, the fourth and fifth fluid paths 67, 68 merge into the single flow path L₂ in the eighth point P₈. The evaporator 4 and the operating fluid pump 5 are provided in the flow path L₂ (sixth fluid path 69) after the merging. In addition, the fourth fluid path 67 is provided with the operating fluid pump 65.

According to the present embodiment, the heater 31 can be applied even to the power generating system not provided with the heat source fluid heater 1.

Eighteenth Embodiment

FIG. 20 is a schematic diagram showing the configuration of a power generating system according to an eighteenth embodiment.

In FIG. 20, the first and second fluid paths 61, 62 in FIG. 16 are replaced by the fourth and fifth fluid paths 67, 68. Therefore, the condenser 9 is provided in the fourth fluid path 67, and the third and fourth heaters 31c, 31d are provided in the fifth fluid path 68. Further, the fourth and fifth fluid paths 67, 68 merge into the single flow path L₂ in the eighth point P₈. The evaporator 4 and the operating fluid pump 5 are provided in the flow path L₂ (sixth fluid path 69) after the merging. In addition, the fourth fluid path 67 is provided with the operating fluid pump 65.

According to the present embodiment, it is possible to sufficiently collect heat of the potential heat amount of the operating fluid by the third and fourth heaters 31c, 31d.

Nineteenth Embodiment

FIG. 21 is a schematic diagram showing the configuration of a power generating system according to a nineteenth embodiment.

The operating fluid path 6 in FIG. 13 is branched into the first and second fluid paths 61, 62. The first fluid path 61 is provided with the expansion module 7 and the condenser 9, and the second fluid path 62 is provided with the heater 31. On the other hand, the heater 31 in FIG. 21 is provided upstream of the expansion module 7 in the operating fluid path 6 with no branch. The heater 31 in FIG. 21 heats the water in the water path 34 by using the operating fluid upstream of the expansion module 7, and discharges the operating fluid to the expansion module 7.

In the eleventh embodiment, in some cases the temperature of the operating fluid discharged from the heater is higher than that of the water discharged from the condenser 9. In this case, it is possible to further collect the heat of the potential heat amount of the operating fluid. On the other hand, in the present embodiment, after the heater 31 collects the heat of the potential heat amount of the operating fluid by a desired amount, the operating fluid is used in the expansion module 7, which is discharged to the condenser 9. Therefore, according to the present embodiment, it is possible to sufficiently collect the heat of the potential heat amount of the operating fluid.

The arrangement of the heater 31 in the present embodiment can be applied not only to the eleventh embodiment but also to the thirteenth, twentieth and twenty-first embodiments.

Twentieth Embodiment

FIG. 22 is a schematic diagram showing the configuration of a power generating system according to a twentieth embodiment.

In FIG. 22, the hot water tank 32 in FIG. 14 is replaced by the heat use destination 37, and the water path 34 in FIG. 14 is replaced by the circulation water path 38. The details of the heat use destination 37 and the circulation water path 38 are similar to those in FIG. 4.

For example, the operating fluid instead of the hot water (or steam) can be supplied to the heat use destination 37. However, in a case where the operating fluid is geothermal steam, in many cases the operating fluid contains corrosiveness components or earth and sand. In this case, it is necessary to take measures of removing the corrosiveness components or earth and sand from the operating fluid. On the other hand, according to the present embodiment, it is possible to make this measure unnecessary by supplying clean hot water (or steam) instead of the operating fluid to the heat use destination 37.

According to the present embodiment, as similar to the fourth embodiment, it is possible to repeatedly use the hot water (or steam). The heat use destination 37 and the circulation water path 38 of the present embodiment can be applied not only to the twelfth embodiment but also to the eleventh, thirteenth to nineteenth, twenty-first and twenty-second embodiments.

Twenty-first Embodiment

FIG. 23 is a schematic diagram showing the configuration of a power generating system according to a twenty-first embodiment.

The power generating system in FIG. 23 includes the components shown in FIG. 14, and besides, valves 71 to 76. The valve 71 is provided upstream of the expansion module 7 in the first fluid path 61. The valve 72 is provided upstream of the third heater 31c in the second fluid path 62. The valve 73 is provided upstream of the condenser 9 in the first water path 63. The valve 74 is provided upstream of the fourth heater 31d in the second water path 64. The valve 75 is provided downstream of the condenser 9 in the first fluid path 61. The valve 76 is provided downstream of the fourth heater 31d in the second fluid path 62.

In a case of performing only the power generation in the power generating system, the valves 71, 73, 75 are opened, and the valve 72 is closed. On this occasion, it is preferable to close the valve 74, but the valve 76 may be opened or closed. In this case, since the water of the water path 34 is heated only by the condenser 9, the water becomes a low-temperature hot water. In addition, it is possible to adjust a power generation amount of the power generator 8 by adjusting an opening degree of the valve 71, and it is possible to adjust a flow amount of the water in the water path 34 by adjusting an opening degree of the valve 73.

In a case of performing only the hot water production in the power generating system, the valves 72, 74, 76 are opened, and the valve 71 is closed. On this occasion, it is preferable to close the valve 73, but the valve 75 may be opened or closed. In this case, it is possible to adjust a flow amount of the water (that is, a hot water flow amount) in the water path 34 by adjusting an opening degree of the valve 74, and it is possible to adjust a temperature or a heat amount of the hot water by adjusting an opening degree of the valve 72.

In a case of performing both of the power generation and the hot water production in the power generating system, all of the valves 71 to 76 are opened. In this case, it is possible to adjust a power generation amount of the power generator 8, and a flow amount, a temperature and a heat amount of the hot water by adjusting an opening degree of each of the valves 71 to 74.

In the present embodiment, the valves 74 to 76 may be not installed, but it is preferable to install them for the flow path management.

As described above, according to the present embodiment, it is possible to select three kinds of operations in the power generating system by the valves 71 to 76. That is, it is possible to select performing only the power generation, performing only the hot water production or both of the power generation and the hot water production. In addition, according to the present embodiment, it is possible to adjust a power generation amount of the power generator 8, and a flow amount, a temperature and a heat amount of the hot water.

The valves 71 to 76 in the present embodiment can be applied not only to the twelfth embodiment but also to the eleventh, thirteenth, fourteenth and twentieth embodiments.

Twenty-second Embodiment

FIG. 24 is a schematic diagram showing the configuration of a power generating system according to a twenty-second embodiment.

The power generating system in FIG. 24 includes the components shown in FIG. 18, and besides, the valves 73, 74 and valves 77, 78. The valve 73 is, as described above, provided upstream of the condenser 9 in the first water path 63. The valve 74 is, as described above, provided upstream of the fourth heater 31d in the second water path 64. The valve 77 is provided upstream of the third heater 31c in the fifth fluid path 68. The valve 78 is provided downstream of the fourth heater 31d in the fifth fluid path 68.

In a case of performing only the power generation in the power generating system, the valve 73 is opened, and the valves 77, 78 are closed. At this time, it is preferable to close the valve 74. In this case, since the water of the water path 34 is heated only by the condenser 9, the water becomes a low-temperature hot water.

In a case of performing both of the power generation and the hot water production in the power generating system, the valves 73, 77, 78 are opened, and the valve 74 is closed in a case of not placing importance on the hot water production. In this case, the water in the water path 34 is heated only by the condenser 9 and the third heater 31c.

In a case of performing both of the power generation and the hot water production in the power generating system, the valves 73, 74, 77, 78 all are opened in a case of placing importance on the hot water production. In this case, the water in the water path 34 is heated by the condenser 9, the third heater 31c and the fourth heater 31d.

In the present embodiment, the valves 73, 74, 78 may be not installed, but it is preferable to install them for the flow path management.

As described above, according to the present embodiment, it is possible to select three kinds of operations in the power generating system by the valves 73, 74, 77, 78. In addition, according to the present embodiment, it is possible to adjust a power generation amount of the power generator 8, and a flow amount, a temperature and a heat amount of the hot water by these valves.

The valves 73, 74, 77, 78 in the present embodiment can be applied not only to the sixteenth embodiment but also to the fifteenth, seventeenth and eighteenth embodiments.

Twenty-third Embodiment

FIG. 25 is a schematic diagram showing the configuration of a cooling system according to a twenty-third embodiment.

The cooling system in FIG. 25, as similar to the cooling system in FIG. 42, includes the heat source fluid heater 1, the heat source fluid pump 2, the heat source fluid path 3, the refrigerator 16, the cooled fluid pump 17, the cooled fluid path 18 and the cold load 19. The refrigerator 16 includes the heat absorbing module 16a, the cooling module 16b and the heat releasing module 16c. The refrigerator 16 in the present embodiment is of an absorption type or adsorption type, and, for example, has the structure shown in FIG. 46 or the structure shown in FIGS. 47 and 48. The cooling system in FIG. 25 further includes the heater 31, the hot water tank 32, the water pump 33 and the water path 34, configuring the exhaust heat collecting system for collecting the exhaust heat of the refrigerator 16 and the like.

The heat source fluid (first heat source fluid) is heated by the heat source fluid heater 1 to heat the heat absorbing module 16a and be lowered in temperature. The heat source fluid in the present embodiment, as shown in FIG. 45, may be made as the hot spring water from the ground 10. This is true of twenty-fourth to thirty-second embodiments to be described later.

The refrigerator 16 includes the heat absorbing module 16a, the cooling module 16b and the heat releasing module 16c, and the cooling medium is contained in the refrigerator 16. An example of the cooling medium is ammonia in case where the refrigerator 16 is of an absorption type, and is water in case where the refrigerator 16 is of an adsorption type. The cooling module 16b cools the cooled fluid by evaporation heat of the cooling medium. An example of the cooled fluid is water. In case where the refrigerator 16 is of an absorption type, the heat absorbing module 16a heats the absorption liquid having absorbed the cooling medium by the heat source fluid to vaporize the cooling medium. The heat releasing module 16c cools the cooling medium vaporized from the absorption liquid by the cooling water to liquidize the cooling medium. On the other hand, in a case where the refrigerator 16 is of an adsorption type, the heat absorbing module 16a heats the adsorption agent having adsorbed the cooling medium by the heat source fluid to cause the cooling medium to be desorbed from the adsorption agent. The heat releasing module 16c cools the adsorption agent by the cooling water to cause the adsorption agent to adsorb the cooling medium. The cooling module 16b cools the cooled fluid by using the cooling medium from the heat releasing module 16c.

The cooled fluid is conveyed through the cooled fluid path 18 by the cooled fluid pump 17, and is cooled by the cooling module 16b. The cooled fluid discharged from the cooling module 16b flows into the cold load 19, and is increased in temperature by cooling the cold load 19. An example of the cold load 19 is cooling target facilities such as building cooling or cooling target devices such as server computers.

The cooling water is increased in temperature by cooling the heat releasing module 16c, and is supplied to the heater 31 through the water path 34. The heater 31 is provided in the heat source fluid path 3. The heater 31 heats the water from the water path 34 by using the heat source fluid in the heat source fluid path 3 to produce the water used as the hot water. The hot water is conveyed through the water path 34 and is reserved in the hot water tank 32. The heat source fluid discharged from the heat absorbing module 16a is lowered in temperature by heating the water in the heater 31.

In the present embodiment, the heat discharged in the heat releasing module 16c is given to the water before being heated by the heater 31 without being given to the cooling tower 13. An example of the water includes tap water. In addition, a temperature of the reserved hot water is made to, for example, 60° C. estimated as a generally usable hot water temperature. This hot water is effectively used in bathing facilities, for dish washing in restaurants or the like. In the present embodiment, since there is no heat put aside externally, the energy utilization rate improves to 100%. The energy use rate in the present embodiment is a ratio between thermal energy given to the heat source fluid by the heat source fluid heater 1 and energy used by the cooling system.

Here, a temperature of water in the water pump 33 is set to 15° C., a temperature of water heated by the heat releasing module 16c is set to 30° C., and a temperature of water heated by the heater 31 is set to 60° C. 30° C. is an example of the first temperature, and 60° C. is an example of the second temperature. The refrigerator 16 is of an adsorption type, and COP of the refrigerator 16 is assumed to be 0.5 as a typical value.

In this case, when the drive heat E2 of the refrigerator 16 is assumed to be “2”, since an absolute value E1 of the cold heat becomes “1”, the exhaust heat E3 of the refrigerator 16 in the conventional cooling system becomes “3”. However, in the present embodiment, since use hot heat E4 of the refrigerator 16 becomes “3” because of using this heat for hot water production. Further, in the present embodiment, the drive heat of the heater 31 becomes “6” and the use hot heat of the heater 31 becomes “6” because of using the heat as much as twice for hot water production in the heater 31. As a result, the drive heat (drive heat of the refrigerator 16 and the heater 31) E2′ of the cooling system becomes “8”, and the use hot heat (use hot heat of the refrigerator 16 and the heater 31) E4′ of the cooling system becomes “9”. As a result, when a use heat conversion rate of the cooling system is assumed to be (E1+E4′)/E2′ and an exhaust heat rate of the cooling system is assumed to be E3/E2′, the use heat conversion rate of the present embodiment becomes 1.25 (=10/8), and the exhaust heat rate of the present embodiment becomes 0 (=0/8).

FIG. 50 is a supplementary diagram explaining the cooling system according to the twenty-third embodiment.

The cooling system in FIG. 50 includes the components shown in FIG. 25, and besides, the cooling water pump 11, the cooling water path 12, the cooling tower 13, the blower 14 and the atmosphere introducing portion 15.

In FIG. 50, the water in the water path 34 is heated only by the heater 31, and is not heated in the heat releasing module 16c. The heat discharged in the heat releasing module 16c is put aside externally. In this case, in the above-mentioned numerical example, the use heat conversion rate of the cooling system becomes 0.875 (=7/8), and the exhaust heat rate of the cooling system becomes 0.375 (=3/8).

In the cooling system in FIG. 42 or 44, the use heat conversion rate of the cooling system becomes 0.5 (=1/2), and the exhaust heat rate of the cooling system becomes 1.5 (=3/2).

As described above, the cooling system according to the present embodiment uses the heat source fluid from the heat source fluid path 3 to heat the water of the first temperature and produce the water of the second temperature to be used as the hot water. Therefore, according to the present embodiment, it is possible to effectively use the exhaust heat in the cooling system.

The present embodiment is applicable even if the heat source in the heat source fluid heater 1 is a high-temperature heat source, but is effectively applicable in a case where the heat source in the heat source fluid heater 1 is a low-temperature heat source such as biomass fuel, solar energy, factory exhaust heat or hot spring heat. Further, the present embodiment is effectively applicable in any heat source in a case where a temperature of the heat source fluid in the inlet of the heat absorbing module 16a is 200° C. or less. This is true of twenty-fourth to thirty-second embodiments to be described later. The reason is that in a case where the heat source in the heat source fluid heater 1 is a low-temperature heat source, COP of the refrigerator 16 is lower, and the energy utilization rate in a case where the present embodiment is not applied is low. According to the present embodiment, it is possible to remarkably improve the energy utilization rate in a case where the heat source in the heat source fluid heater 1 is the low-temperature heat source. This is true of the twenty-fourth to thirty-second embodiments to be described later.

In addition, the configuration of the present embodiment is effectively applicable in a case where the maximum temperature of the heat source fluid in the heat source fluid path 3 is 200° C. or less.

Twenty-fourth Embodiment

FIG. 26 is a schematic diagram showing the configuration of a cooling system according to a twenty-fourth embodiment.

The heater 31 in FIG. 26, as similar to the second embodiment, heats the water by using the heat source fluid flowing upstream of the heat absorbing module 16a. In the present embodiment, a temperature of the heat source fluid in the inlet of the heater 31 is higher than a temperature of the heat source fluid in the inlet of the heat absorbing module 16a. Therefore, the water tends to be easily heated to a higher temperature.

Twenty-fifth Embodiment

FIG. 27 is a schematic diagram showing the configuration of a cooling system according to a twenty-fifth embodiment.

The heat absorbing module 16a and the heater 31 in FIG. 27 are, as similar to the third embodiment, arranged in parallel to the flow of the heat source fluid. In the present embodiment, since a temperature of the heat source fluid in the inlet of the heater 31 is equal to a temperature of the heat source fluid in the inlet of the heat absorbing module 16a, both of the heat absorbing module 16a and the water tend to be easily heated to a high temperature as much as possible.

Twenty-sixth Embodiment

FIG. 28 is a schematic diagram showing the configuration of a cooling system according to a twenty-sixth embodiment.

The hot water tank 32 and the water path 34 in FIG. 28 are, as similar to the fourth embodiment, replaced by the heat use destination 37 and the circulation water path 38. The water in the present embodiment is heated and discharged by the heat releasing module 16c. The heater 31 uses the heat source fluid to heat this water and produce water to be used as the hot water. The hot water is conveyed through the circulation water path 38 to be supplied to the heat use destination 37. An example of the heat use destination 37 includes floor heating.

The floor heating is generally used in winter. Accordingly, in a case where the heat use destination 37 is the floor heating, there is estimated a high possibility that an application of the refrigerator 16 is performed for cooling a device such as a server computer rather than for cooling a facility such as building cooling. This is because in general, the former is used in summer and the latter is used regardless of seasons.

Twenty-seventh Embodiment

FIG. 29 is a schematic diagram showing the configuration of a cooling system according to a twenty-seventh embodiment.

The heat source fluid path 3 in FIG. 29, as similar to the fifth embodiment, includes a first bypass flow path 44 bypassing a first flow path provided with the heat absorbing module 16a, and a second bypass flow path 48 bypassing a second flow path provided with the heater 31.

In the present embodiment, upon performing both of the cold heat production and the hot water production, the valves 41, 42, 45, 46 are opened and the valves 43, 47 are closed. In addition, upon performing an operation of placing importance on only the cold heat production, the valves 41, 42, 47 are opened and the valves 43, 45, 46 are closed. In addition, upon performing only the hot water production, the valves 43, 45, 46 are opened and the valves 41, 42, 47 are closed.

As described above, according to the present embodiment, it is possible to select three kinds of operations in regard to the cold heat production and the hot water production by using the first and second bypass flow paths 44, 48.

Twenty-eighth Embodiment

FIG. 30 is a schematic diagram showing the configuration of a cooling system according to a twenty-eighth embodiment.

The cooling system in FIG. 30 includes the components shown in FIG. 27, and besides, the plurality of valves 51 to 54. This configuration is the same as that of the sixth embodiment.

In the present embodiment, upon performing both of the cold heat production and the hot water production, the valves to 54 are opened. In addition, upon performing an operation of placing importance on only the cold heat production, the valves 51, 52 are opened and the valves 53, 54 are closed. In addition, upon performing only the hot water production, the valves 53, 54 are opened and the valves 51, 52 are closed.

As described above, according to the present embodiment, it is possible to select three kinds of operations in regard to the cold heat production and the hot water production by using the first and second branch flow paths 37, 38.

Twenty-ninth Embodiment

FIG. 31 is a schematic diagram showing the configuration of a cooling system according to a twenty-ninth embodiment.

The cooling system in FIG. 31 includes the heat source fluid heater 21, the heat source fluid pump 22 and the heat source fluid path 23 in addition to the components shown in FIG. 25. This configuration is the same as that of the seventh embodiment. In the explanation in FIG. 31, as similar to the explanation in FIG. 44, the first heat source fluid heater 1, the first heat source fluid pump 2, the first heat source fluid path 3, the second heat source fluid heater 21, the second heat source fluid pump 22 and the second heat source fluid path 23 are adopted as titles. The heat source fluid in the first heat source fluid path 3 is called the first heat source fluid, and the heat source fluid in the second heat source fluid path 23 is called the second heat source fluid.

The first heat source fluid is heated by the first heat source fluid heater 1, and is lowered in temperature by heating the second heat source fluid in the second heat source fluid heater 21. The second heat source fluid is heated by the second heat source fluid heater 21 to heat the heat absorbing module 16a, and is thereby lowered in temperature.

The refrigerator 16 includes the heat absorbing module 16a, the cooling module 16b and the heat releasing module 16c, and the cooling medium is contained in the refrigerator 16. The cooling module 16b cools the cooled fluid by evaporation heat of the cooling medium. The heat absorbing module 16a heats the cooling medium by the second heat source fluid to be vaporized or desorbed. The heat releasing module 16c cools the cooling medium or the adsorption agent by the cooling water to cause the cooling medium to be vaporized or desorbed.

The cooled fluid is cooled by the cooling module 16b to cool the cold load 19, and is increased in temperature. The cooling water is increased in temperature by cooling the heat releasing module 16c, which is supplied to the heater 31.

In the present embodiment, the heater 31 is provided in the second heat source fluid path 23. The heater 31 heats the water from the water path 34 by using the second heat source fluid to produce the water to be used as the hot water. The second heat source fluid discharged from the heat absorbing module 16a flows into the heater 31 to heat the water in the heater 31, and is thereby lowered in temperature.

Here, the cooling system in FIG. 25 and the cooling system in FIG. 31 will be compared.

In FIG. 25, since separated substances are accumulated in the refrigerator 16 (heat absorbing module 16a) or the heater 31 depending upon components contained in the heat source fluid, it is necessary to frequently disassemble the refrigerator 16 or the heater 31 for the cleaning, but the disassembly of the refrigerator 16 or the heater 31 is not preferable. Further, it is also not preferable to disassemble the water path 34 used in bathing facilities or for dish washing in restaurants. On the other hand, in FIG. 31, since not the refrigerator 16 or the heater 31 but the second heat source fluid heater 21 is disassembled and cleaned, it is not necessary to disassemble the refrigerator 16, the heater 31 and the water path 34.

As described above, the cooling system according to the present embodiment uses the second heat source fluid to heat the water of the first temperature and produce the water of the second temperature to be used as the hot water. Therefore, according to the present embodiment, it is possible to effectively use the exhaust heat in the cooling system.

Thirtieth Embodiment

FIG. 32 is a schematic diagram showing the configuration of a cooling system according to a thirtieth embodiment.

The heater 31 in FIG. 32, as similar to the eighth embodiment, is provided in the first heat source fluid path 3, and heats the water by using the first heat source fluid flowing downstream of the second heat source fluid heater 21. In many cases a temperature of the first heat source fluid in the inlet of the heater 31 in the present embodiment is higher than a temperature of the second heat source fluid in the inlet of the heater 31. In the twenty-ninth embodiment. Therefore, the water tends to be easily heated to a higher temperature.

Thirty-First Embodiment

FIG. 33 is a schematic diagram showing the configuration of a cooling system according to a thirty-first embodiment.

The heater 31 in FIG. 33, as similar to the ninth embodiment, heats the water by using the first heat source fluid flowing upstream of the second heat source fluid heater 21. In the present embodiment, a temperature of the first heat source fluid in the inlet of the heater 31 is higher than a temperature of the first heat source fluid in the inlet of the second heat source fluid heater 21. Therefore, the water tends to be easily heated to a higher temperature.

FIG. 34 is a schematic diagram showing the configuration of a cooling system according to a modification of the thirty-first embodiment.

The heater 31 in FIG. 34, as similar to the modification of the ninth embodiment, heats the water by using the second heat source fluid flowing upstream of the heat absorbing module 16a. In the present modification, a temperature of the second heat source fluid in the inlet of the heater 31 is higher than a temperature of the second heat source fluid in the inlet of the heat absorbing module 16a. Therefore, the water tends to be easily heated to a higher temperature.

Thirty-Second Embodiment

FIG. 35 is a schematic diagram showing the configuration of a cooling system according to a thirty-second embodiment.

The cooling system in FIG. 35, as similar to the tenth embodiment, includes the first and second heaters 31a, 31b instead of the heater 31.

The first heat source fluid is heated by the first heat source fluid heater 1, and is lowered in temperature by heating the second heat source fluid in the second heat source fluid heater 21. The second heat source fluid is heated by the second heat source fluid heater 21 to heat the heat absorbing module 16a, and is thereby lowered in temperature.

The refrigerator 16 includes the heat absorbing module 16a, the cooling module 16b and the heat releasing module 16c, and the cooling medium is contained in the refrigerator 16. The cooling module 16b cools the cooled fluid by evaporation heat of the cooling medium. The heat absorbing module 16a heats the cooling medium by the second heat source fluid to be vaporized or desorbed. The heat releasing module 16c cools the cooling medium or the adsorption agent by the cooling water to cause the cooling medium to be liquidized or adsorbed.

The cooled fluid is cooled by the cooling module 16b to cool the cold load 19, and is thereby increased in temperature. The cooling water is increased in temperature by cooling the heat releasing module 16c, which passes through the second heater 31b and the first heater 31a on the water path 34 in that order, and is reserved in the hot water tank 32 as the hot water.

FIG. 36 is a schematic diagram showing the configuration of a cooling system according to a modification of the thirty-second embodiment.

The first heater 31a in FIG. 36, as similar to the modification of the tenth embodiment, heats the water by using the first heat source fluid flowing upstream of the second heat source fluid heater 21. Further, the second heater 31b in FIG. 36, as similar to the modification of the tenth embodiment, heats the water by using the second heat source fluid flowing upstream of the heat absorbing module 16a.

As described above, the cooling system in the present embodiment includes the first and second heaters 31a, 31b instead of the heater 31. In a case of adopting this configuration, the heat exchangers in the cooling system increase in number, but the cooling system can be designed such that a difference in temperature between the heating fluid and the heated fluid is made small. Specifically, the cooling system can be designed such that a difference in temperature between the first heat source fluid and the second heat source fluid is made small. As a result, according to the present embodiment, the water tends to be easily heated to a higher temperature.

While certain embodiments have been described, these embodiments have been presented by way of example only, and are not intended to limit the scope of the inventions. Indeed, the novel systems described herein may be embodied in a variety of other forms; furthermore, various omissions, substitutions and changes in the form of the systems described herein may be made without departing from the spirit of the inventions. The accompanying claims and their equivalents are intended to cover such forms or modifications as would fall within the scope and spirit of the inventions.

Claims

1. An exhaust heat collecting system of collecting exhaust heat in a fluid treatment system comprising: a fluid path configured to include at least an operating fluid path or a cooled fluid path among a first heat source fluid path, a second heat source fluid path, the operating fluid path and the cooled fluid path, the first heat source fluid path conveying a first heat source fluid, the second heat source fluid path conveying a second heat source fluid heated by heat of the first heat source fluid, the operating fluid path conveying an operating fluid, the cooled fluid path conveying a cooled fluid, the operating fluid being conveyed through or not through an evaporator that vaporizes the operating fluid by using the first or second heat source fluid, the cooled fluid being conveyed through a cooling module that cools the cooled fluid; anda fluid treatment module configured to include an expansion module that rotates and drives to expand the operating fluid, a power generator that is connected to a rotational shaft of the expansion module, and a condenser that condenses the operating fluid, or configured to include a heat absorbing module that absorbs heat of the first or second heat source fluid, and a heat releasing module that releases heat received from the cooled fluid and heat absorbed by the heat absorbing module,the exhaust heat collecting system comprising:a water path configured to supply water to the condenser or the heat releasing module, heat the water by the condensation in the condenser or by the heat release in the heat releasing module, and convey the water of a first temperature discharged from the condenser or the heat releasing module; anda heater configured to heat the water from the water path by using the first heat source fluid, the second heat source fluid or the operating fluid to produce the water of a second temperature to be used as hot water or to produce steam.

2. The exhaust heat collecting system of claim 1, wherein the heater heats the water by using the first or second heat source fluid that exists downstream or upstream of the evaporator or the heat absorbing module.

3. The exhaust heat collecting system of claim 1, wherein the first or second heat source fluid path is branched into a first branch flow path provided with the evaporator or the heat absorbing module, and a second branch flow path provided with the heater.

4. The exhaust heat collecting system of claim 3, comprising at least one of a first valve provided in the first branch flow path, and a second valve provided in the second branch flow path.

5. The exhaust heat collecting system of claim 1, wherein the first or second heat source fluid path comprises at least one of a first bypass flow path that bypasses a first flow path provided with the evaporator or the heat absorbing module, and a second bypass flow path that bypasses a second flow path provided with the heater.

6. The exhaust heat collecting system of claim 1, wherein the fluid treatment system further comprises a heat source fluid heater configured to heat the second heat source fluid by the heat of the first heat source fluid, the heater heating the water by using the first heat source fluid that exists downstream or upstream of the heat source fluid heater.

7. The exhaust heat collecting system of claim 1, comprising, as the heater, a first heater configured to heat the water by the heat of the first heat source fluid, and a second heater that configured to heat the water by the heat of the second heat source fluid.

8. The exhaust heat collecting system of claim 7, wherein one of the first and second heaters is heated by the other of the first and second heaters, and heats the water flowing out from the other of the first and second heaters.

9. The exhaust heat collecting system of claim 1, wherein the operating fluid path is branched into a first fluid path provided with the expansion module and the condenser, and a second fluid path provided with the heater.

10. The exhaust heat collecting system of claim 9, wherein the first and second fluid paths merge into a third fluid path that is provided with the evaporator, and the third fluid path is branched into the first and second fluid paths.

11. The exhaust heat collecting system of claim 1, wherein the operating fluid path comprises a fourth fluid path that conveys the operating fluid discharged from an exhaust port of the expansion module and is provided with the condenser, and a fifth fluid path that conveys the operating fluid extracted from an extraction port of the expansion module and is provided with the heater.

12. The exhaust heat collecting system of claim 11, wherein the fourth and fifth fluid paths merge into a sixth fluid path that is provided with the evaporator, and the sixth fluid path conveys the operating fluid to the expansion module.

13. The exhaust heat collecting system of claim 9, comprising at least one of a valve provided in the first or fourth fluid path and a valve provided in the second or fifth fluid path.

14. The exhaust heat collecting system of claim 9, comprising, as the heater, a third heater provided in the second or fifth fluid path, and a fourth heater provided downstream of the third heater in the second or fifth fluid path.

15. The exhaust heat collecting system of claim 14, wherein the water path is branched into a first water path provided with the condenser and a second water path provided with the fourth heater, and the first and second water paths merge into a third water path that is provided with the third heater.

16. The exhaust heat collecting system of claim 14, comprising at least one of a valve provided in the first water path and a valve provided in the second water path.

17. The exhaust heat collecting system of claim 1, wherein the heater heats the water by using the operating fluid that exists upstream of the expansion module.

18. The exhaust heat collecting system of claim 1, wherein the water path circulates the water between the heater and the condenser or the heat releasing module.

19. The exhaust heat collecting system of claim 1, wherein a maximum temperature of the first heat source fluid, the second heat source fluid or the operating fluid is equal to or less than 200° C.

20. The exhaust heat collecting system of claim 1, wherein the first heat source fluid is hot spring water or a fluid that is heated in a heat source fluid heater that obtains heat from a heat source of non-fossil fuel.