JP4659601B2 - Energy supply system, energy supply method, and energy supply system remodeling method - Google Patents

Description

  The present invention relates to an energy supply system for supplying thermal energy to a heat utilization facility, an energy supply method, and a method for remodeling an energy supply system using existing facilities.

  One of the systems aimed at improving the energy efficiency of the system is to use a heat pump in a cogeneration system (see Patent Document 1, etc.). The heat pump takes in atmospheric heat, waste heat, and the like. In the above-described conventional technology, hot water and cold water generated by the heat pump are respectively used as cleaning water and cooling water in the facility.

  In addition, in a system with only a heat pump that does not generate electric power, it has been proposed to use water as a medium instead of the conventional freon system (see Patent Document 2, etc.).

Japanese Patent Publication No. 7-4212 JP 2001-147055 A

  However, when supplying heat energy to a heat utilization facility, it is difficult to secure a sufficient amount of energy that can be transported per medium weight even when hot water or cold water is used as a heat medium. Therefore, even if the conventional technology is applied and a configuration in which hot water or cold water obtained using a heat pump is supplied as a heat medium to a heat utilization facility, the installation location of the energy supply system is in a range close to the heat utilization facility. It will be limited.

  In addition, it is known that if water is used as the heat medium of the heat pump, water vapor having a high energy density can be used as the heat medium. Limited.

  The present invention has been made in view of the above points, and an object thereof is to provide an energy supply system, an energy supply method, and an energy supply system remodeling method capable of dramatically improving energy efficiency and energy supply efficiency. .

In order to achieve the above object, the present invention provides a boiler that generates steam by heating a heat medium, a steam turbine that is driven by steam from the boiler, and a steam having a set temperature by heating the heat medium by external heat. And a steam supply system that combines the steam discharged from the steam turbine and the steam heated by the heat exchanger, and mixes them by a combiner and supplies them to a heat utilization facility.

  According to the present invention, energy efficiency and energy supply efficiency can be dramatically improved.

  Hereinafter, embodiments of the cogeneration system of the present invention will be described with reference to the drawings.

(1) 1st Embodiment FIG. 1: is a system flow figure showing the whole structure of the energy supply system which concerns on the 1st Embodiment of this invention.
As shown in the figure, this system includes a gas turbine 10 that is a prime mover that converts combustion energy into driving force, and a boiler (waste heat recovery boiler) that uses combustion gas (exhaust gas) discharged from the gas turbine 10 as a heating source. 30, a heat pump 50 driven by steam from the boiler 30, and a steam supply system 70 that supplies steam generated by the heat pump 50 to the heat utilization facility 1.

(1-1.1) Configuration of Gas Turbine 10 The gas turbine 10 generates high-temperature and high-pressure combustion gas by combusting the fuel B together with the compressor 11 that sucks and compresses the atmosphere A and the compressed air from the compressor 11. A combustor 12 to be rotated, and a turbine 13 for obtaining rotational power by expansion work of combustion gas from the combustor 12. The fuel used in the combustor 12 may be natural gas, city gas containing natural gas as a main component, or kerosene, light oil, A heavy oil, or the like. In the present embodiment, a generator 14 is connected coaxially with the compressor 11, and the rotational power obtained by the turbine 13 is transmitted to the generator 14 and converted into electrical energy. However, the gas turbine 10 is not limited to the generator and may be connected to other load devices such as a pump.

(1-1.2) Configuration of Boiler 30 The boiler 30 generates steam by heating the heat medium with the combustion gas (exhaust gas) discharged from the gas turbine 10. The outlet of the exhaust gas of the boiler 30 is connected to the chimney 43. When it is necessary to reduce the nitrogen concentration in the exhaust gas C discharged from the chimney 43 to the atmosphere, a denitration device (not shown) in which the catalyst is filled in the boiler 30 is provided, and the concentration of nitrogen oxides contained in the gas C It is preferable to decompose most of it into harmless oxygen and nitrogen.

  The boiler 30 includes four heat exchangers in the order of a low-pressure economizer 31, a high-pressure economizer 32, a high-pressure evaporator 33, and a high-pressure superheater 34 from the downstream side in the combustion gas flow direction. In the boiler 30, the heat energy contained in the exhaust gas is recovered by the four heat exchangers 31 to 34, and the heat medium supplied by the circulation pump 35 is heated. The circulation pump 35 plays a role of circulating and supplying the heat medium condensed as a heat source in the heat utilization facility 1 after being supplied from the heat pump 50 to the heat utilization facility 1. If it is necessary to purify the heat medium due to the use conditions of steam at the heat utilization facility 1 or corrosion in the piping, a desalinator (not shown) filled with ion exchange resin in the previous stage of the circulation pump 35 is used. It is preferable to provide it.

  The heat medium guided to the boiler 30 by the circulation pump 35 flows in the order of the low-pressure economizer 31, the high-pressure economizer 32, the high-pressure evaporator 33, and the high-pressure superheater 34. Pipes 37 and 38 branched through a branch 36 are connected to the downstream side of the low-pressure economizer 31 in the flow direction of the heat medium. The piping 37 is connected to the high-pressure economizer 32 via a high-pressure pump 39, and the piping 38 is connected to the heat pump 50 via a regulating valve 40. The high pressure economizer 32 and the high pressure evaporator 33 are connected via a steam drum 41, and the steam drum 41 is further connected to a high pressure superheater 34 located on the most downstream side. The high pressure superheater 34 and the heat pump 50 are connected via a pipe 42.

  When the heat exchanger 34, 33, 32, 31 exchanges heat with the heat medium and the exhaust gas becomes low temperature, the water vapor contained in the exhaust gas condenses on the heat transfer surface of the low-pressure economizer 31, etc. Therefore, it is preferable that the low-pressure economizer 31 and the like use stainless steel or plastic material having excellent corrosion resistance for the piping material. In some cases, the low pressure economizer 31 or the like may be divided into an upstream side and a downstream side in the flow direction of the exhaust gas, and only the downstream side where the temperature becomes lower may be made of stainless steel. If necessary, stainless steel or a plastic material may be stretched on the exhaust gas outlet portion of the boiler 30 or the inner wall surface of the chimney 43.

(1-1.3) Configuration of Heat Pump 50 The heat pump 50 is connected to the steam turbine 51 driven by the heat medium (steam) supplied from the boiler 30 via the pipe 42 and coaxially with the steam turbine 51. The heat medium (high temperature water) preheated by the low pressure economizer 31 in the boiler 30 and diverted to the pipe 38 via the branch 36 in the boiler 30 is externally heated (the waste of the heat utilization facility 1). And a heat exchanger (evaporator) 54 for heating using heat or heat obtained from the surrounding environment. A high pressure superheater 34 is connected to the steam turbine 51 via a pipe 42, and a low pressure economizer 31 is connected to the heat exchanger 54 via a pipe 38.

  In the heat exchanger 54, a pipe 55 for circulating a heating medium for heating the heating medium supplied to the heat utilization facility 1 is disposed. The piping 55 is connected to the two-phase flow expansion turbine 52 on the downstream side in the flow direction of the heating medium and to the compressor 53 on the upstream side. The two-phase flow expansion turbine 52 is connected to an evaporator 57 via a pipe 56, and the evaporator 57 is connected to a compressor 53 via a pipe 58 so that the heating medium circulates in a closed system. It has become. In the present embodiment, for example, trifluoroethanol (TFE) may be used as the heating medium, but the heat medium supplied to the heat utilization facility 1 is set by adjusting the pressure in the two-phase flow expansion turbine 52 or the compressor 53. If the temperature is raised to a temperature sufficient for heating to the temperature, it may be replaced with air or water (for example, river water).

  The evaporator 57 plays a role of taking external heat into the heating medium to be circulated through the heat exchanger 54. Thereby, the heat exchanger 54 heats the heat medium (high temperature water) from the boiler 30 by exchanging heat with the heating medium from which the external heat is recovered. For example, when the heat transfer rate of the heat source is low, such as when the air is used as a heat source, it is conceivable to provide a fan 59 as shown to improve the heat exchange efficiency between the surrounding environment and the heating medium.

(1-1.4) Configuration of Steam Supply System 70 The steam supply system 70 is a piping system for appropriately supplying the steam from the heat pump 50 to the heat utilization facility 1. In the present embodiment, the steam supply system 70 includes a pipe 71 connected upstream to the outlet (or extraction port) of the steam turbine 51, a pipe 72 connected upstream to the pipe 38 via the heat exchanger 54, a pipe 71, A confluencer 73 connected to the downstream side of 72, and a pipe 74 connecting the confluencer 73 and the heat utilization facility 1. In the present embodiment, the steam discharged from the steam turbine 51 and the steam heated by the heat exchanger 54 are respectively circulated through the pipes 71 and 72, merged and mixed by the merger 73, and supplied to the heat utilization facility 1. Is done.

(1-1.5) Construction of this system When constructing this system, of course, the whole system may be newly constructed. However, if there are existing prime movers or boilers, use these existing facilities. It is also possible to modify it.

  For example, when the gas turbine 10 already exists, the boiler 30 is attached to the gas turbine 10, and the heat medium is heated by the exhaust gas of the gas turbine 10 to generate steam. Then, a heat pump 50 is additionally installed and connected to the boiler 30 so that the steam turbine 51 is driven by the steam from the boiler 30 and the heat medium preheated by the boiler 30 is heated by the heat exchanger to generate steam. To do. Next, the heat pump 50 and the heat utilization facility 1 are connected by the steam supply system 70 so that the steam discharged from the steam turbine 51 and the steam heated by the heat exchanger 54 are supplied to the heat utilization facility, The heat medium condensed by heat utilization in the heat utilization facility 1 is configured to be circulated to the boiler 30 by the circulation pump 35.

  When the boiler 30 (or another boiler) already exists, the heat medium is circulated through the existing boiler, and the heat pump 50, the steam supply system 70, and the circulation pump 35 are provided in the same manner as described above. It ’s fine. In this example, the heat medium supplied to the heat exchanger 54 of the heat pump 50 is a heat medium that is diverted from the heat medium that drives the steam turbine 51, but there is another heat medium supply source. May be configured such that the supply sources of the two heat media are separate.

Next, the operation of the energy supply system in the present embodiment having the above configuration will be described.
(1-2.1) Operation of Gas Turbine 10 When the atmosphere A from which foreign matter has been removed through a filter (not shown) is sucked into the compressor 11, it is compressed by the compressor 11 and set pressure (for example, about 8 atmospheres). Pressure. The air sucked into the compressor 11 is heated to a set temperature (for example, about 250 [° C.]) by being pressurized. The compressed air from the compressor 11 is combusted in the combustor 12 together with the fuel B, thereby generating high-temperature and high-pressure combustion gas. When this combustion gas is supplied to the turbine 13, the rotational power of the turbine 13 is obtained by the expansion work of the combustion gas, and the rotational power is transmitted to the generator 14 to obtain electrical energy.

(1-2.2) Operation of the boiler 30 The boiler 30 is supplied with combustion gas (exhaust gas) discharged by the expansion work in the turbine 13 as a heat source. The exhaust gas supplied to the boiler 30 has a high temperature (for example, about 560 [° C.]) in the vicinity of the outlet of the turbine 13, but passes through the heat exchangers 34, 33, 32, and 31 before being discharged from the chimney 43. At this time, heat is sequentially exchanged with the heat medium supplied by the circulation pump 35, and the temperature decreases.

  A heat medium having a predetermined temperature (for example, about 30 [° C.]) condensed as a heat source in the heat utilization facility 1 is first pressurized to a set pressure (for example, about 0.6 [MPa]) by the circulation pump 35. Thereafter, the heat medium in the state of high-temperature water supplied to the low-pressure economizer 31 and heated to a set temperature (for example, about 100 [° C.]) has a predetermined pressure (for example, 0.5 The pressure is reduced to [MPa], and the flow is branched to the pipes 37 and 38 via the branch 36. At this time, the flow rate of the heat medium that is divided into the pipes 37 and 38 is adjusted by the opening degree of the adjusting valve 40.

  The heat medium guided to the pipe 37 is pressurized to a set pressure (for example, about 5.4 [MPa]) by a high-pressure pump 39 and further heated to a saturation temperature (269 [° C.]) by a high-pressure economizer 32. The When supplied to the steam drum 41, the heat medium that has become saturated water is heated by the heat energy of the exhaust gas in a high-pressure evaporator 33 in a natural circulation manner, and changes in phase to steam. In the steam drum 41, saturated water and saturated steam are separated by the density difference, and the saturated steam is transferred from the upper gas phase portion to the high-temperature superheater 34. The heat medium heated and heated to a set temperature and pressure (for example, about 450 [° C.], about 5.0 [MPa]) by the high-temperature superheater 34 to become superheated steam is a steam turbine 51 that is a power source of the heat pump 50. To be supplied.

(1-2.3) Operation of the heat pump 50 The heat medium (superheated steam) having a set pressure (for example, about 5.0 [MPa]) exiting the high-pressure superheater 34 is discharged from the steam turbine 51 and performs expansion work. The pressure is reduced to a set pressure (for example, about 0.4 [MPa]) when used as a heat source in the heat utilization facility 1. Rotational power obtained by the steam turbine 51 is transmitted to the two-phase flow expansion turbine 52 and the compressor 53 to drive them.

  A heating medium (TFE or the like) having a predetermined pressure (for example, about 0.03 [MPa]) flowing through the pipe 58 is compressed by the compressor 53 and pressurized to a set pressure (for example, about 1.1 [MPa]). The heating medium heated with the compression exchanges heat with the heat exchanger 54 having a predetermined temperature (for example, about 100 [° C.]) supplied from the boiler 30 through the pipe 38. As a result, the heat medium evaporates and becomes a saturated vapor having a set temperature and pressure (for example, about 140 [° C.] and about 0.4 [MPa]).

  The heat medium exchanged with the heat medium in the heat exchanger 54 condenses to become a liquid, and when the two-phase flow expansion turbine 52 adiabatically expands to a set pressure (for example, 0.03 [MPa]), a part of which has evaporated. It becomes a phase flow and the temperature is lowered to a set temperature (for example, about 45 [° C.]). The heating medium of the heat pump 50 expands to a low pressure and decreases in temperature in this way, so that heat from the outside can be absorbed very efficiently. The heating medium in a two-phase flow state is heated by the evaporator 57 with waste heat or the like at a predetermined temperature (eg, about 50 [° C.]) in the heat utilization facility 1 and changes into a vapor phase. If there is no suitable factory waste heat, the pressure can be further reduced and evaporated with atmospheric heat as described above. Since gas such as the atmosphere has low heat transfer efficiency, if the fan 59 is provided as shown to promote heat transfer, the heat exchange in the evaporator 57 is improved.

(1-2.4) Operation of Steam Supply System 70 After the steam discharged from the steam turbine 51 and the steam obtained by the heat exchanger 54 are mixed in the confluence 73 through the pipes 71 and 72, respectively. It is supplied to the heat utilization facility 1 via the pipe 74 and used as a heating source. Then, the heat medium that releases and condenses heat in the heat utilization facility 1 is discharged from the heat utilization facility 1, is appropriately purified, returns to the circulation pump 35, and is circulated and supplied to the boiler 30 by the circulation pump 35 again. The

(1-3) Operational Effects In the present embodiment, by supplying the heat medium in the vapor state to the heat utilization facility 1, the heat medium per unit weight of the medium is compared with the case where the heat medium is supplied in the liquid state. The amount of energy that can be transported can be dramatically improved. Accordingly, since the power for transporting heat can be reduced, the installation location of the present system is not limited to the range close to the corresponding heat utilization facility 1 and can be widely applied. Further, by using the heat pump 50 to generate the steam to be supplied to the heat utilization facility 1, in addition to the thermal energy of the boiler 50, in other words, the fuel energy input to the gas turbine 10, it is released without being used. It is possible to take in waste heat from the heat utilization facility 1 and the thermal energy of the infinite surrounding environment into the system, and the energy efficiency can be dramatically improved.

  For example, assuming that the heat medium temperature required in the heat utilization facility 1 is 50 [° C.], in the case where high temperature water of 100 [° C.] is generated in consideration of the temperature drop until it is conveyed from the heat pump 50, the medium to be transported The amount of heat energy per weight is calculated to be 0.21 [MJ / kg]. On the other hand, when steam of 100 [° C.] is generated, since the latent heat is large, the amount of heat energy per medium weight is 2.7 [MJ / kg] in calculation. In this case, by supplying the heat medium to the heat utilization facility 1 in a vapor state, the heat energy per weight of the medium to be transported is 13 times larger than when high temperature water is used.

  In the boiler 30, a case is considered in which, for example, the heat medium is completely vaporized by the high temperature evaporator 34 to generate steam at a set temperature and pressure (for example, about 450 [° C.] and 5.0 [MPa]). In this case, if the temperature of the heat medium supplied to the low-pressure economizer 31 is 30 [° C.], the enthalpy is 125 [kJ / kg]. On the other hand, since the enthalpy of superheated steam at 450 [° C.] is 3315 [kJ / kg], in order to raise the temperature of the heat medium to 450 [° C.], the heat amount of 3190 [kJ / kg] is applied to the heat medium in the boiler 30. Need to add. Assuming that the heat medium at the time of flowing into the high-pressure evaporator 33 is 269 [° C.] saturated water, the amount of heat required to heat the heat medium from that state until it changes to superheated steam at 450 [° C.] is 2137 [kJ / kg] and occupies 67% of the exchange heat amount (3190 [kJ / kg]) required by the boiler 30 as a whole.

  At this time, in order to transfer heat from the exhaust gas to the heat medium (saturated water) in the high-pressure evaporator 33, the exhaust gas in the vicinity of the high-pressure evaporator 33 is 10 [° C.] or more from the saturation temperature (269 [° C.]). It must be high and a temperature of at least 279 [° C.] is required. In this case, if the exhaust gas immediately after being exhausted from the turbine 13 is 560 [° C.], the temperature is reduced by 281 [° C.] by 279 [° C.] in the vicinity of the high-pressure evaporator 33.

  On the other hand, the amount of heat required to heat the 30 [° C.] heat medium supplied to the boiler 30 to 269 [° C.] until it flows into the high temperature evaporator 33 is 1178 [kJ / kg]. This amount of heat is as small as about 50% of the amount of heat (2137 [kJ / kg]) required to raise the temperature of the heat medium from 269 [° C.] to 450 [° C.], and the exhaust gas temperature at the exhaust gas outlet of the boiler 30 is It only drops to about 140 [° C]. In this case, the thermal energy corresponding to the difference between the exhaust gas temperature (140 [° C.]) near the outlet of the boiler 30 and the atmospheric temperature is released to the atmosphere without being used, and that amount of energy is lost.

  Therefore, in the present embodiment, in order to effectively utilize the unused heat amount of the exhaust gas C released into the atmosphere, of the heat medium (for example, about 100 [° C.]) that has become high-temperature water in the low-pressure economizer 31. 45% of the water is divided and supplied to the heat exchanger 54 of the heat pump 50. As a result, the heat medium heated by the heat pump 50 can be preheated using the amount of heat of the exhaust gas C released into the atmosphere, and the energy efficiency of the heat pump 50 can be further improved. In addition, the temperature of the exhaust gas C released into the atmosphere can be lowered, and thermal energy loss can be reduced. For example, when a 30 [° C.] heating medium supplied to the boiler 30 is heated to about 100 [° C.] by the low pressure economizer 31, the temperature of the exhaust gas C released to the atmosphere is from 140 [° C.] to near the atmospheric temperature ( For example, almost all of the fuel energy input to the combustor 12 is recovered.

  The energy consumption efficiency (COP) indicating the performance of the heat pump 50 is defined by the ratio between the power given to the heat pump 50 by the compressor 53 and the amount of heat given to the steam generated by the heat exchanger 54. The amount of heat used to heat the heat medium by the heat exchanger 54 is expressed as the sum of the amount of heat from the outside collected in the heat medium by the evaporator 57 and the power when the compressor 53 pressurizes the heat medium. Using the COP value as a parameter, the energy of the fuel input to the combustor 12 as the denominator, and the sum of the amount of power generated by the generator 14 and the amount of heat supplied to the heat utilization facility 1 as a numerator, When the gas temperature shows the behavior as mentioned above, the total efficiency of the system exceeds 100% when the COP value exceeds 1.7, and becomes 128% when the COP value is increased to 5. This is an effect that heat energy is taken in from the outside by the evaporator 57 separately from the energy of the fuel input to the combustor 12. The power used by the circulation pump 35 and the high-pressure pump 39 in the boiler 30 also contributes to the heating of the heat medium.

  The overall efficiency of a general cogeneration system is about 80%, but compared with that, the overall efficiency of this system is extremely high, and this system has an impact on global warming compared to a system with an overall efficiency of 80%. It is possible to reduce the amount of generated CO2 by as much as 37%. The thermal loss in this system is a heat amount of a temperature difference between the exhaust gas C released from the boiler 30 to the atmosphere and the atmosphere A sucked into the compressor 11. Therefore, if an amount of heat larger than this heat loss is taken in from the outside by the evaporator 57, the total efficiency of this system exceeds 100%.

  Further, in the present embodiment, the power obtained by the steam turbine 51 is not converted into electric power, but is used for the driving force of the compressor 53 and the two-phase flow expansion turbine 52 of the heat pump 50. There is no loss associated with conversion. Further, by mixing the steam after the expansion work by the steam turbine 51 and the steam generated by the heat pump 50 and transporting them to the heat utilization facility 1 by the common steam pipe 74, more heat medium can be utilized without waste. It can be supplied to the facility 1. These points are also significant advantages of this system.

  Furthermore, if there is already a prime mover facility or boiler facility that releases waste heat that will not be used, the system can be easily constructed using such existing facility. This is a major merit of the system.

(2) Second Embodiment FIG. 2 is a system flow diagram showing the overall configuration of an energy supply system according to a second embodiment of the present invention. In this figure, parts similar to those in FIG.
As shown in FIG. 2, this embodiment is different from the first embodiment in the configuration of the heat pump 50A, and the boiler is used for the heating medium cycle without using the heating medium such as TFE described above. The heat medium from 30 is supplied, and the steam obtained by the cycle is supplied to the heat utilization facility 1. As a result, the heat exchanger (heat exchanger 54 in FIG. 1) for exchanging heat between the heat medium supplied to the heat utilization facility 1 and the heat medium that heats the heat medium is omitted.

  The heat pump 50A includes a steam turbine 51 that is driven by a heat medium (steam) supplied from a boiler 30 that is supplied via a pipe 42, a two-phase flow expansion turbine 52A and a compressor 53A that are coaxially connected to the steam turbine 51. 53B, and a heat exchanger (evaporator) 54A that heats the heat medium (high-temperature water) supplied from the boiler 30 via the pipe 38 by using external heat (waste water, air, etc. of the heat utilization facility 1) Have

  In the present embodiment, the pipe 38 from the low pressure economizer 31 is connected to the two-phase flow expansion turbine 52A. The two-phase flow expansion turbine 52A is connected to the upstream compressor 53A via the heat exchanger 54A, and the compressor 53A is connected to the downstream compressor 53B via the pipe 60, the mixer 61, and the pipe 62. Further, a branch 80 is provided in the pipe 38 connecting the low pressure economizer 31 and the two-phase flow expansion turbine 52 </ b> A, and a pipe 81 branched from the pipe 38 is connected to the previous mixer 61 through the branch 80. ing. An adjustment valve 82 is provided in the pipe 81, and the flow rate ratio of the heat medium to be divided into the pipes 38 and 81 is adjusted by the opening degree of the adjustment valve 82.

  The heat exchanger 54A is provided with a pipe 83 through which waste water, the atmosphere, and the like of the heat utilization facility 1 and the like pass. A partition 84 is provided inside the heat exchanger 54A, and an upper space is partitioned on the two-phase flow expansion turbine 52A side and the compressor 53A side.

  Other configurations are the same as those of the first embodiment described above, and in this embodiment, the same effects as those of the first embodiment can be obtained, and the existing prime mover and boiler are similarly configured. The system can be constructed using In addition, the present embodiment has the following operational effects.

  By using the heat medium supplied from the boiler 30 as the medium of the heat pump 50A as in the present embodiment, for example, the system is configured so that the heat medium heated to almost the saturation condition flows into the two-phase flow expansion turbine 52A. In this way, large power can be obtained with the two-phase flow expansion turbine 52A.

  Therefore, for example, when the heat medium is high-temperature water of approximately 130 [° C.] and 0.5 [MPa] close to the saturation condition at the outlet of the low pressure economizer 31 of the boiler 30, the opening degree of the adjustment valve 82 is By adjusting, the heat medium is supplied to the two-phase flow expansion turbine 52A through the branch 80 at a rate of 80%, and the heat medium is about 0.01 [MPa] and 46 [° C.] by the two-phase flow expansion turbine 52A. Until the pressure is reduced. The heat medium supplied to the heat exchanger 54A evaporates a predetermined ratio (for example, about 14%) in the expansion process in the two-phase flow expansion turbine 52A to form a two-phase flow, and the liquid phase separated from the vapor phase is It stays in the lower part of the heat exchanger 54A. In this case, the liquid phase is heated and evaporated by using factory waste heat or city waste heat of about 50 to 60 [° C.]. When the outlet pressure of the two-phase flow expansion turbine 52A is further decreased (for example, to about 0.002 [MPa]), the temperature inside the heat exchanger 54A is further decreased (for example, to about 18 [° C]). Therefore, in this case, it is also possible to evaporate the heat medium using the heat of the atmosphere that exists infinitely.

  Steam at a predetermined pressure (for example, about 0.01 [MPa]) existing in the upper space of the heat exchanger 54A is pressurized by the compressors 53A and 53B (for example, up to about 0.4 [MPa]) to use heat as a heat source. 1 is supplied. In the mixer 61 between the former compressor 53A and the latter compressor 53B, the heat medium in the state of high-temperature water is sprayed through the pipe 81 branched from the branch 80, and supplied from the compressor 53A to the compressor 53B. The temperature of the heated heat medium is lowered.

  For example, when 0.01 [MPa] steam is compressed to 0.4 [MPa], even if the compression efficiency is 100%, the steam temperature reaches about 490 [° C] unless it is cooled in the middle. If the compression efficiency is about 85%, the steam temperature will be about 550 [° C.]. In this case, energy corresponding to a temperature difference between the saturation temperature 46 [° C.] and 550 [° C.] of the heat medium (water) of 0.01 [MPa] is required as power for the compressors 53A and 53B. In gas compression, the required compression power increases as the gas density decreases. Therefore, the flow rate is controlled by the regulating valve 82 to branch from the branch 80, and 0.5 [MPa] high-temperature water is injected into the mixer 61 and sprayed on the steam in the compression process to lower the temperature.

  In the present embodiment, the two compressors 53A and 53B are provided and the mixer 61 is provided therebetween. However, in order to reduce the power of the compressor, three or more compressors are provided and adjacent compressors are provided. It is also conceivable to provide a mixer for every interval.

  As described above, in the present embodiment, the temperature of the superheated steam can be easily lowered to the saturation temperature by spraying the steam on the heat medium in the state of the superheated steam flowing out from the compressor 53A. Moreover, when spraying a heat medium, it is also considered to spray a heat medium until it becomes a slightly wet steam. In this case, the heat medium is in a state of wet steam at the inlet of the subsequent compressor 53B, but water droplets evaporate inside the compressor 53B. Thus, since the temperature rise inside the compressor 53B can be suppressed, the compressor power can be reduced as a whole. It is efficient to adjust the spray amount of the heat medium in the merger 61 so that the water vapor temperature at the outlet of the compressor 53B becomes the temperature used in the heat utilization facility 1 (for example, about 140 [° C.]).

  The power used in the compressors 53A and 53B is supplied by the steam turbine 51 and the two-phase flow expansion turbine 52A. By using the heat medium supplied to the heat utilization facility 1 as the medium of the heat pump 50, it is possible to cool the medium by directly spraying the heat medium between the compressors 53A and 53B, and a dedicated heating medium such as TFE can be used. A large heat exchanger (in the example of FIG. 1, the heat exchanger 54) that is necessary when the heat medium is indirectly cooled by using it becomes unnecessary. Since the weight of the two evaporators 54 and 57 occupies more than half of the weight of the heat pump 50 in FIG. 1, being able to omit one as in this embodiment is very useful for simplification of equipment. Moreover, when the heat medium is heated by exchanging heat with the other heat medium such as TFE, a temperature difference between the heat medium to be heated and the heat medium to be heated is necessary. Will improve.

  In the case of the present embodiment, the pressure of the heat exchanger 54A is low (eg, about 0.01 [MPa]), and the fluid density at the outlet of the two-phase flow expansion turbine 52A and the inlet of the compressor 53A is reduced. Therefore, as shown in the drawing, by connecting the outlet of the two-phase flow expansion turbine 52A and the inlet of the compressor 53A to the upper space of the heat exchanger 54A, piping that has to speed up the fluid on the way is unnecessary. can do. Further, by partitioning the inside of the heat exchanger 54A with the partition 84, it is possible to prevent water droplets at the outlet of the two-phase flow expansion turbine 52A from directly flowing into the compressor 53A. The liquid phase portion is static inside the heat exchanger 54A, but when the heat exchange efficiency is poor between the liquid phase and the pipe 83, an agitator (not shown) for forcibly flowing the liquid phase and an internal partition (see FIG. It is even better to create a homogeneous flow to promote heat transfer.

(3) Third Embodiment FIG. 3 is a system flow diagram showing the overall configuration of an energy supply system according to a third embodiment of the present invention. In this figure, parts similar to those in the previous figures are given the same reference numerals, and description thereof is omitted.
As shown in FIG. 3, this embodiment is different from the above-described embodiments in that the ratio between the power generation output and the heat output is configured to be variable, and a steam turbine is connected via a variable speed reducer 85. 51 and the drive shaft of the compressor 53B.

  Further, a condenser 86 for condensing steam discharged from the steam turbine 51 and performing expansion work is connected to the outlet of the steam turbine 51 through a pipe 87. The condenser 86 is connected via a pipe 90 to a merger 89 provided in a pipe 88 that connects the heat utilization facility 1 and the circulation pump 35. The pipes 88 and 90 are provided with adjusting valves 91 and 92, respectively. Further, an adjustment valve 93 is provided in the pipe 71 connecting the extraction port of the steam turbine 51 and the merger 73.

  Other configurations are the same as those in the second embodiment described above, and in this embodiment, the same effects as those in the second embodiment can be obtained, and the existing prime mover and boiler are similarly configured. The system can be constructed using In addition, the present embodiment has the following operational effects.

  First, since the compressors 53A and 53B are coaxially connected to the gas turbine 10 in addition to the two-phase flow expansion turbine 52A and the steam turbine 51, the rotational power obtained by the turbine 13 is used as the power of the compressors 53A and 53B. Can be used. The remaining power after driving the compressors 53A and 53B is converted into electric energy by the generator 14.

  Further, the ratio of heat and electric power required in the heat utilization facility 1 etc. varies. On the other hand, in this system, the ratio of heat supply to the total energy supply amount can be continuously changed from 0% (power supply 100%) to 100% (power supply 0%).

  When supplying only electric power, the regulating valve 40 is closed and the flow rate of steam generated by the heat pump 50A (heat exchanger 54A) is set to 0 (zero). If it is in this state, the rotation speed of the circulation pump 35 is controlled so that the superheated steam conditions finally produced | generated by the high pressure superheater 34 in the boiler 30 may be controlled, and the supply amount of the heat medium with respect to the boiler 30 will be adjusted. Thus, when the regulating valve 40 is closed and the heat medium is not circulated through the pipe 38, the temperature of the exhaust gas C discharged from the boiler 30 rises.

  Here, the supply amount of the heat medium to the boiler 30 by the circulation pump 35 can be determined by dividing the heat amount given to the heat medium in the boiler 30 by the heat amount required per unit flow rate. The amount of heat given to the heat medium in the boiler 30 can be calculated from the temperature difference between the exhaust gas at the turbine 13 outlet and the boiler 30 outlet and the flow rate of the exhaust gas discharged from the turbine 13. The amount of heat required per unit flow rate can be determined from the difference between the enthalpy of the heat medium at the outlet of the circulation pump 35 and the enthalpy of the heat medium at the outlet of the high-pressure superheater 34.

  When the regulating valve 93 is closed and the supply of the heat medium extracted from the steam turbine 51 to the heat utilization facility 1 is shut off and the regulating valve 92 is opened, all the heat medium that has driven the steam turbine 51 is supplied to the condenser 86. Condensate back to water. Since a heat medium does not flow through the two-phase flow expansion turbine 52A and the compressors 53A and 53B, energy loss can be reduced by disconnecting the variable speed reducer 85 and disconnecting from the steam turbine 51.

  On the other hand, when electric power and heat are supplied to the heat utilization facility 1 at the same time, the heat pump 50 and the high-pressure economizer 32 are supplied via the branch 36 by controlling the opening degree of the regulating valve 40 and the rotational speed of the circulation pump 35. The flow rate of the heat medium to be adjusted is adjusted. The flow rate of the heat medium sprayed onto the heat medium in the superheated steam state at the midpoint between the compressors 53A and 53B is constant with respect to the flow rate of the heat medium flowing into the compressor 53B by adjusting the opening of the adjustment valve 82. Try to be a proportion.

  Since the performance of the heat pump 50A is determined by the pressure of the evaporator 54A, the rotational speeds of the compressors 53A and 53B are controlled by the variable speed reducer 85 so that the predetermined pressure is obtained. While the heat demand is low, the regulating valve 93 is closed to maximize the output of the steam turbine 51. After increasing the flow rate of the two-phase flow expansion turbine 52A until the evaporation capacity of the heat medium in the evaporator 54A is fully exhibited, when there is a demand for further increasing the heat output, the opening degree of the regulating valve 93 Is increased, and the heat medium guided to the merger 73 is increased. When the opening degree of the regulating valve 93 is increased, the flow rate of the heat medium guided to the merger 73 increases, and accordingly, the output of the steam turbine 51 decreases and the power generation amount of the generator 14 decreases. When the power generation amount becomes 0 (zero), the heat output of the entire system becomes maximum.

  When the steam discharged from the steam turbine 51 is led to the condenser 86 and condensed, the heat of condensation is recovered in the cooling water and released to the outside. Therefore, the amount of heat of the exhaust gas C discharged from the chimney 43 and this heat of condensation become the heat loss of the system. If the regulating valve 92 is closed under the maximum heat energy condition so that the heat medium does not flow to the condenser 86, the total energy efficiency of the system will show the highest value.

  In the case of energy supply with only heat output, the ratio of the energy of the heat medium that can be supplied to the heat utilization facility 1 and the energy of the fuel that is supplied to the combustor 12 is the temperature of the waste heat that can be used in the evaporator 54A and the compressor 53A, Depending on the efficiency of 53B, it will be in the range of 180-220%. In a general boiler, the steam energy that can be used is about 90% of the input fuel energy and does not exceed 100%. However, in this system, the power obtained by the gas turbine 10 is also used as the driving force of the heat pump 50A. As a result, the total amount of energy that can be supplied to the heat utilization facility 1 exceeds 200% depending on conditions because the evaporator 54A can use the energy of the atmosphere and waste heat in addition to the fuel energy supplied to the combustor 12. It is also possible.

(4) Reference Example FIG. 4 is a system flow diagram showing the overall configuration of an energy supply system according to a reference example . In this figure, parts similar to those in the previous figures are given the same reference numerals, and description thereof is omitted.
As shown in FIG. 4, this example is different from the above-described embodiments in that the steam exhausted from the steam turbine 51 and subjected to expansion work and the steam heated by the heat exchanger 54A are different from each other. It is the point comprised so that it might supply to heat utilization facilities 1A and 1B.

In this example , the steam supply system 70 includes a pipe 75 that connects the steam turbine 51 and a heat utilization facility 1A such as a factory, and a pipe 76 that connects the compressor 53B and another heat utilization facility 1B such as a hot water pool. The heat medium that drives the steam turbine 51 and the heat medium heated by the heat exchanger 54A are supplied to the heat utilization facilities 1A and 1B via the pipes 75 and 76, respectively. The heat medium condensed in the heat utilization facilities 1A and 1B is discharged from the heat utilization facilities 1A and 1B, and then merged by the merger 94 and returned to the circulation pump 35.

About another structure, it is the same as that of 2nd Embodiment mentioned above, and while being able to acquire the effect similar to 2nd Embodiment, supplying a heat medium to several heat utilization facilities suitably. it can. Similarly, a system can be constructed. In this example , the case where energy is supplied to a plurality of heat utilization facilities in the system of the second embodiment has been described as an example. However, the case where energy is supplied to a plurality of heat utilization facilities according to the other embodiments described above. It is also applicable to.

(5) Fourth Embodiment FIG. 5 is a system flow diagram showing the overall configuration of an energy supply system according to a fourth embodiment of the present invention. In this figure, parts similar to those in the previous figures and parts having similar functions are denoted by the same reference numerals and description thereof is omitted.
As shown in FIG. 5, the present embodiment is different from the above-described embodiments in that the prime mover (gas turbine 10 or the like) is discarded as a heat source that generates steam (heat medium) that drives the heat pump 50. Instead of heat, the boiler 30A installed in various facilities such as a cleaning factory is used. The boiler 30A includes an incinerator boiler of a cleaning factory, but is not limited to this, and any boiler that can heat a heat medium and convert it into steam, such as a boiler that uses heavy oil or old tires as fuel, is sufficient. In the present embodiment, water pumped from the river 96 by the pump 95 is guided to the heat exchanger 54A as a heating medium for heating the heat medium by the heat pump 50A. In this system, with such a configuration, the amount of heat obtained from river water is added to the amount of heat obtained by the heat exchanger 30Aa provided in the boiler 30A, and heat energy is supplied to the heat utilization facility 1 such as a hot water pool with high efficiency. It is like that.

  The heat medium returned from the heat utilization facility 1 is pressurized to a set pressure (for example, about 7 [MPa]) by the circulation pump 35, then supplied to the boiler 30A, and heated by the heat exchanger 30Aa. The heat medium that has become high-temperature and high-pressure water is supplied to the expansion turbine 52A through the pipe 38, and the heat medium that has become high-pressure superheated steam is supplied to the steam turbine 73 that drives the heat pump 50A through the pipe 42. When the heat medium is water, when it expands to about 0.002 [MPa] by the expansion turbine 52A, the saturation temperature becomes 17.5 [° C.], so that it evaporates with the unlimited heat of the river 96. The water of the river 96 is supplied to the heat exchanger 54A through the pipe 83 by the pump 79. When the degree of pollution of river water is high, a filter is provided in the middle of the pipe 83 to remove insoluble substances.

  The evaporated saturated steam is compressed to a set pressure (for example, about 0.4 [MPa]) by the compressors 53A and 53B. In order to reduce the compression power of the compressors 53A and 53B, a heat medium in the state of high-temperature water is sprayed and cooled between the compressors 53A and 53B. As power for driving the compressors 53A and 53B, a pressure (for example, 0.4 [MPa) for using a heat medium in a superheated steam state at a set pressure (for example, about 7 [MPa]) in the steam turbine 51 in the heat utilization facility 1 is used. The energy at the time of depressurization to a degree is used. The steam that exits the steam turbine 51 and the steam that exits the compressor 53 </ b> B are mixed by the merger 73 and supplied to the heat utilization facility 1 as a heat source.

  Also in the present embodiment, the same effects as those of the above-described embodiments can be obtained, and a system can be constructed using an existing boiler in the same manner. Compared to supplying only the steam generated in the existing boiler 30A to the heat utilization facility 1, by using the heat of the river 96, the amount of heat that can be supplied from the same boiler 30A is 1.8 times depending on the conditions. It is also possible to increase to a certain extent.

  In each of the above embodiments, the case where water is used as the heat medium supplied to the heat utilization facility has been described. However, since the heat medium does not circulate through the closed system and flow out to the outside, for example, carbon dioxide or Other media such as ammonia or trifluoroethanol may be used as the heat medium. Of course, these other media may be used alone as a heat medium, but depending on the case, a plurality of types may be mixed or used by mixing with water. When a harmless and mixable medium is used as the heat medium, it is not always necessary to use a closed system. In that case, the heat medium that drives the steam turbine 51 and the heat medium that is heated by the heat pumps 50 and 50A are supplied differently. You may comprise so that it may supply from a source. Furthermore, in the case of using a plurality of heat mediums, when the heat medium that drives the steam turbine 51 and the heat medium that is heated by the heat pumps 50 and 50A are supplied to different heat utilization facilities and each is circulated in a closed system, it is not always necessary. Both heat media may not be miscible.

(6) Fifth Embodiment In FIG. 1, the heat medium used in the heat utilization facility 1 is condensed and returned to the circulation pump 35. However, in the present embodiment, the heat medium that is used as a heat source in the heat utilization facility 1 is not provided with a piping that circulates and supplies the heat medium to the boiler 30, and the heat medium is supplied from other than the heat utilization facility 1 to the circulation pump 35. Features.

  In the heat utilization facility 1, not only the heat of the water vapor (heat medium) supplied from the steam supply system 70 but also the use of water vapor for the reaction process is assumed. It is difficult to circulate and use the water vapor after the reaction process directly in the heat pump. Therefore, in the present embodiment, a circulation pump that purifies water from other than the heat utilization facility 1 such as a river or ground water without providing a piping that circulates and supplies the condensed heat medium used as a heat source in the heat utilization facility 1 to the boiler 30. 35. With such a system configuration, there is no need to install a return pipe from the heat utilization facility 1 to the circulation pump 35. Therefore, the farther the distance between the heat pump 50 and the heat utilization facility 1, the greater the effect that the equipment cost can be reduced. .

(7) Sixth Embodiment In FIG. 2 shown in the second embodiment, the heat medium supplied to the heat utilization facility 1 is used as the heat medium of the heat pump 50. Therefore, in this embodiment, a case where water is used as a heat medium will be described.

Here, it is the same structure as the conventional heat pump, Comprising: It demonstrates in comparison with the system structure when a heat medium is only replaced with water. FIG. 6 is a system flow diagram showing an overall configuration of an energy supply system that is a conventional heat pump and uses water as a heat medium. Compared with FIG. 2 that has already been described, the heat pump 50A has one compressor 53, and includes a mixer 61 that is branched and connected from a pipe 38 that connects the low-pressure economizer 31 and the two-phase flow expansion turbine 52A. Absent. In the case of FIG. 6, the temperature rise when the gas is compressed by the compressor 53 of the heat pump 50A increases as the gas density decreases. For example, the density of water vapor at 0.01 [MPa] 46 [° C.] is 0.068 kg / m ³ , which is only 13% of 0.52 kg / m ³ of R-11, which is one of the refrigerants. Therefore, in the case of R-11, even if compressed to 0.4 [MPa], the temperature rises only to 185 [° C.], but with steam, it rises to 490 [° C.]. Since the saturation temperature of water at 0.4 [MPa] is 144 [° C.], the power for raising the temperature from 144 [° C.] to 490 [° C.] is merely changed to heat, and the system efficiency is greatly improved. descend. Therefore, simply changing the heat medium to water with the same configuration as that of the conventional heat pump makes the efficiency drop too large and practical application is difficult.

  Therefore, as shown in FIG. 2 of the present embodiment, the compressor 53 of the heat pump 50A is divided into a plurality of stages, and the compression power is reduced by cooling the water vapor and increasing the density in the middle to reduce the compression power. This structure is necessary when water is used as the heat medium.

  As a method for cooling water vapor in the middle of compressors arranged in a plurality of stages, in addition to a method for spraying water into the water vapor, a method for cooling by providing a heat exchanger is also conceivable. Although the heat exchanger is provided outside the containers of the compressors 53A and 53B and the apparatus becomes large, the water vapor temperature can be adjusted with high accuracy.

  Further, as a form of use of steam in the heat utilization facility 1, there are the following utilization methods in addition to simply condensing the steam and using it as heat. First, an absorption refrigerator using lithium bromide as a medium is provided in a heat utilization facility, and high-temperature steam is used for evaporation of the refrigerant, so that the facility can be cooled. Second, in chemical and drying processes, steam can be injected or sprayed directly onto the product. In this case, it is not necessary to provide the heat utilization facility 1 with a condenser that condenses the steam.

It is a system flow figure showing the whole energy supply system composition concerning a 1st embodiment of the present invention. It is a system flow figure showing the whole structure of the energy supply system which concerns on the 2nd Embodiment of this invention. It is a system flow figure showing the whole structure of the energy supply system which concerns on the 3rd Embodiment of this invention. It is a system flow figure showing the whole energy supply system composition concerning a reference example . It is a system flow figure showing the whole structure of the energy supply system which concerns on the 4th Embodiment of this invention. It is a conventional heat pump, Comprising: It is a system flow figure showing the whole structure of the energy supply system using water for the heat medium.

Explanation of symbols

1, 1A, 1B Heat utilization facility 10 Gas turbine 30, 30A Boiler 50, 50A Heat pump 51 Steam turbine 52, 52A Two-phase expansion turbine 53, 53A, 53B Compressor 54, 54A Heat exchanger 70 Steam supply system 73 Merger 85 Variable speed reducer

Claims (13)

A boiler that generates steam by heating a heat medium;
A steam turbine driven by steam from the boiler, and a heat pump having a heat exchanger that heats a heat medium with waste heat or heat obtained from the surrounding environment to generate steam at a set temperature;
A steam supply system that supplies steam discharged from the steam turbine and steam heated by the heat exchanger to a heat utilization facility ,
The steam supply system includes a merger that merges and mixes the steam discharged from the steam turbine and the steam heated by the heat exchanger . A boiler that generates steam by heating a heat medium;
A steam turbine driven by steam from the boiler, and a heat pump having a heat exchanger that generates heat at a set temperature by heating the heat medium preheated by the boiler with waste heat or heat obtained from the surrounding environment;
A steam supply system for supplying steam discharged from the steam turbine and steam heated by the heat exchanger to a heat utilization facility;
A circulation pump for circulating a heat medium condensed by heat utilization in the heat utilization facility, to the boiler ;
The steam supply system includes a merger that merges and mixes the steam discharged from the steam turbine and the steam heated by the heat exchanger . A prime mover that converts combustion energy into driving force;
A boiler that generates steam by heating the heat medium with the exhaust gas of the prime mover;
A steam turbine driven by steam from the boiler, and a heat pump having a heat exchanger that heats a heat medium preheated by the boiler with waste heat or heat obtained from the surrounding environment to generate steam at an installation temperature;
A steam supply system for supplying steam discharged from the steam turbine and steam heated by the heat exchanger to a heat utilization facility;
A circulation pump that circulates the heat medium condensed by heat utilization in the heat utilization facility to the boiler ,
The steam supply system includes a merger that merges and mixes the steam discharged from the steam turbine and the steam heated by the heat exchanger .   In the energy supply system in any one of Claims 1-3, the said heat pump heats the said heat medium by carrying out heat exchange with the medium which collect | recovered waste heat or the heat of the surrounding environment with the said heat exchanger. A featured energy supply system.   The energy supply system according to any one of claims 1 to 3, wherein the heat pump heats the heat medium by directly flowing waste heat or ambient environment heat through the heat exchanger. Supply system.   The energy supply system according to claim 3, wherein the heat pump includes a variable speed reducer that connects the steam turbine and a compressor or a turbine that is driven by power obtained by the steam turbine. Supply system. The steam turbine is driven by steam obtained by heating the heat medium with a boiler, and steam at a set temperature is generated by heating the heat medium with a heat exchanger installed in the heat pump by waste heat or heat obtained from the surrounding environment. And
An energy supply method characterized in that the steam discharged from the steam turbine and the steam heated by the heat exchanger are merged and mixed by a merger and supplied to a heat utilization facility. The steam turbine is driven with steam obtained by heating the heat medium with a boiler, and the heat medium preheated with the boiler is heated with a heat exchanger provided in the heat pump by waste heat or heat obtained from the surrounding environment. To generate steam at the set temperature,
The steam discharged from the steam turbine and the steam heated by the heat exchanger are merged and mixed by a merger and supplied to a heat utilization facility,
An energy supply method comprising circulating a heat medium condensed by heat utilization in the heat utilization facility to the boiler. Steam is generated by heating the heat medium in the boiler with the exhaust gas from the prime mover,
A steam turbine is driven by steam from the boiler, and a heat medium preheated by the boiler is heated by a heat exchanger provided in a heat pump by waste heat or heat obtained from the surrounding environment to generate steam at a set temperature. ,
The steam discharged from the steam turbine and the steam heated by the heat exchanger are merged and mixed by a merger and supplied to a heat utilization facility,
An energy supply method comprising circulating a heat medium condensed by heat utilization in the heat utilization facility to the boiler. The heat medium is distributed to the existing boiler that generates steam,
A heat pump having a steam turbine driven by steam obtained by heating the heat medium with this boiler, and a heat exchanger that generates heat at a set temperature by heating the heat medium with waste heat or heat obtained from the surrounding environment;
Remodeling of the energy supply system, wherein a steam supply system for adding the steam discharged from the steam turbine and the steam heated by the heat exchanger to the heat utilization facility by mixing and mixing by a combiner Method. The heat medium is distributed to the existing boiler that generates steam,
Steam turbine driven by steam obtained by heating a heat medium with this boiler, and heat exchanger for generating steam at a set temperature by heating the heat medium preheated with the boiler with waste heat or heat obtained from the surrounding environment A heat pump having
A steam supply system in which steam discharged from the steam turbine and steam heated by the heat exchanger are combined and mixed by a combiner and supplied to a heat utilization facility;
A method for remodeling an energy supply system, comprising additionally installing a circulation pump for circulating a heat medium condensed by heat utilization in the heat utilization facility to the boiler. A boiler that heats a heat medium with exhaust gas from the prime mover and generates steam is attached to an existing prime mover that converts combustion energy into driving force.
A steam turbine driven by steam from the boiler, and a heat pump having a heat exchanger that heats a heat medium preheated by the boiler with waste heat or heat obtained from the surrounding environment to generate steam at an installation temperature;
A steam supply system in which steam discharged from the steam turbine and steam heated by the heat exchanger are combined and mixed by a combiner and supplied to a heat utilization facility;
A method for remodeling an energy supply system, comprising additionally installing a circulation pump that circulates a heat medium condensed by heat utilization in the heat utilization facility to the boiler. A boiler that generates steam by heating water;
A steam turbine driven by steam from this boiler, a heat exchanger for generating steam by heating water with waste heat or heat obtained from the surrounding environment, a multi-stage compressor for compressing steam generated by this heat exchanger, And a heat pump having a mixer for supplying water on a path through which steam flows between these compressors,
A steam supply system for supplying steam discharged from the steam turbine and steam discharged from the compressor to a heat utilization facility ,
The steam supply system includes a merger that merges and mixes the steam discharged from the steam turbine and the steam heated by the heat exchanger .

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