JP5141101B2 - Steam generation system - Google Patents

Description

  The present invention relates to a steam generation system.

As a steam generation system, generally known is a configuration in which a heated medium is heated by burning fuel in a boiler (see, for example, Patent Document 1).
JP-A-6-249450

  The energy efficiency of the boiler is generally about 0.8 (80%). With increasing awareness of environmental issues, further improvements in energy efficiency are desired for steam generation systems.

  An object of the present invention is to provide a steam generation system with high energy efficiency.

  According to the first aspect of the present invention, the heat pump is a heat pump through which the first medium flows, the heat pump having a heat absorption part, a compression part, a heat radiation part, and an expansion part, and heat for supplying heat to the heat absorption part of the heat pump. A supply unit, an evaporation tank that temporarily stores the second medium, an evaporation unit thermally connected to the heat radiating unit of the heat pump, and a decompression device that depressurizes the internal space of the evaporation tank, The decompression device that evaporates the second medium in the evaporation section by at least one of the decompression of the internal space and the heat transferred from the heat pump, a heat source that outputs the heated second medium, and the heat source A second path through which the second medium flows and fluidly communicates with the evaporation tank; and a second path through which the second medium flows and fluidly communicates with the heat supply unit. Generation system is provided.

  According to this steam generation system, the second medium from the heat source is guided to the evaporation tank via the first path, or is guided to the heat supply unit via the second path. By supplying the second medium from the heat source directly to the evaporation tank, steam can be generated from the second medium with substantially no or minimal heat transfer. This is advantageous for suppressing heat loss. Moreover, the heat which the 2nd medium supplied to the heat supply unit from the heat source is utilized as a heat source of a heat pump. By using a heat pump, high energy efficiency can be obtained compared to a boiler.

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

  FIG. 1 is a schematic diagram showing a steam generation system according to the first embodiment. In FIG. 1, a steam generation system S1 includes a heat pump 10 through which a working medium flows, a heating medium supply path 20, a compressor (decompression device) 30, a control device 70, a heat supply unit 90, and a heat source 100. Is provided. In the present embodiment, the medium to be heated is water. The control device 70 comprehensively controls the entire system. The configuration of the steam generation system S1 can be variously changed according to the design requirements of the steam generation system S1.

  The heat pump 10 is a device that pumps heat from a low-temperature object and applies heat to a high-temperature object by a cycle including evaporation, compression, condensation, and expansion processes. A heat pump generally has the advantage of relatively high energy efficiency and, as a result, relatively low emissions of carbon dioxide and the like.

  In the present embodiment, the heat pump 10 includes a heat absorbing part 11, a compressing part 12, a heat radiating part (a first heat radiating part 13A, a second heat radiating part 13B, a third heat radiating part 13C, a fourth heat radiating part 13D, and a fifth heat radiating part 13E). , And an inflating part 14, which are connected via a pipe.

  In the heat absorption part 11 of the heat pump 10, the working medium flowing in the main path 15 absorbs the heat of the heat source outside the cycle, and at least a part of the working medium evaporates. In the present embodiment, the heat absorption unit 11 of the heat pump 10 is thermally connected to the heat dissipation unit 91 of the heat supply unit 90.

  The compression unit 12 of the heat pump 10 compresses the working medium using a compressor or the like. At this time, the temperature of the working medium usually increases. In the present embodiment, the compression unit 12 has a structure for compressing the working medium in multiple stages. The compression unit 12 illustrated in FIG. 1 has a four-stage compression structure including a first compression unit 12A, a second compression unit 12B, a third compression unit 12C, and a fourth compression unit 12D. The number of stages of compression is set according to the specification of the steam generation system S1, and is 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. Among the various compressors such as an axial flow compressor, a centrifugal compressor, a reciprocating compressor, and a rotary compressor, a compressor suitable for compressing the working medium is applied. Power is supplied to the compressor. The compression unit 12 can have a multiaxial compression structure in which the rotation speeds corresponding to the compression units 12A to 12D are individually controlled. Alternatively, the compression unit 12 can have a coaxial compression structure. In the present embodiment, the compression units 12A and 12B are configured coaxially, the compression units 12C and 12D are configured coaxially, and power is supplied to each shaft. The compression ratio (pressure ratio) of each of the compression units 12A to 12D is set according to the specification of the steam generation system S1.

  The heat radiating parts 13A, 13B, 13C, 13D, and 13E have pipes through which the working medium compressed by the compressing part 12 flows, and give the heat of the working medium flowing in the main path 15 to a heat source outside the cycle. In the present embodiment, five heat radiating portions 13A, 13B, 13C, 13D, and 13E are arranged in series along the flow direction of the working medium. The number of heat radiation units is set according to the specifications of the steam generation system S1, and is 2, 3, 4, 5, 6, 7, 8, 9, 10, or 11 or more. 13A of 1st thermal radiation parts are arrange | positioned between the stages of compression part 12A and 12B, 13B of 2nd thermal radiation parts are arrange | positioned between the stage of compression parts 12B and 12C, and 13C of 3rd thermal radiation parts are the compression parts 12C and 12D. The fourth heat dissipating part 13D is disposed at a downstream position of the compression part 12D, and the fifth heat dissipating part 13E is disposed at a downstream position of the fourth heat dissipating part 13D.

  The expansion unit 14 expands the working medium using a pressure reducing valve, a turbine, or the like. At this time, the temperature of the working medium usually decreases. When a turbine is used, power can be taken out from the expansion unit 14, and the power may be supplied to the compression unit 12, for example. As a working medium used for the heat pump 10, various known heat mediums such as a chlorofluorocarbon medium (245, 134, etc.), ammonia, water, carbon dioxide, air, and the like depend on the specifications and heat balance of the steam generation system S1. Used. As will be described later, in the present embodiment, the expansion unit 14 includes a pressure reduction control valve 400.

  In the present embodiment, the heat pump 10 further includes a bypass path 17 and a regenerator 18. The inlet end of the bypass path 17 is fluidly connected to a pipe between the fourth heat radiating part 13D and the fifth heat radiating part 13E in the main path 15 of the heat pump 10. An outlet end of the bypass path 17 is fluidly connected to a pipe between the fifth heat radiating part 13 </ b> E and the expansion part 14 in the main path 15. A flow rate control valve for controlling the bypass flow rate of the working medium can be provided at the inlet of the bypass path 17. In the bypass path 17, a part of the working medium from the fourth heat radiating part 13 </ b> D bypasses the fifth heat radiating part 13 </ b> E and merges with the working medium from the fifth heat radiating part 13 </ b> E before the expansion part 14. The remaining working medium from the fourth heat radiating section 13D flows through the fifth heat radiating section 13E, and the working medium and the water in the supply path 20 exchange heat in the first heat exchanger 41.

  The regenerator 18 has a configuration in which a part of the pipe of the bypass path 17 and a part of the pipe of the main path 15 of the heat pump 10 (a pipe between the heat absorption unit 11 and the compression unit 12) are thermally connected. Have. For example, both pipes are arranged in contact with or adjacent to each other. In the heat pump 10, the working medium from the fourth heat radiating unit 13 </ b> D is hotter than the working medium from the heat absorbing unit 11. In the regenerator 18, the working medium from the fourth heat radiating unit 13 </ b> D flowing through the bypass path 17 and the working medium from the heat absorbing unit 11 flowing through the main path 15 of the heat pump 10 exchange heat. By this heat exchange, the temperature of the working medium in the bypass path 17 is lowered, and the temperature of the working medium in the main path 15 is raised. The regenerator 18 may have a countercurrent heat exchange system in which a low-temperature fluid (a working medium in the main path 15) and a high-temperature fluid (a working medium in the bypass path 17) face each other. Alternatively, the regenerator 18 may have a parallel flow type heat exchange system in which a high-temperature fluid and a low-temperature fluid flow in parallel.

  The heat source 100 outputs heated water. In the present embodiment, the heat source 100 includes a heat pump 101. As with the heat pump 10 described above, the heat pump 101 includes a heat absorption unit 102, a compression unit 103, a heat radiation unit 104, and an expansion unit 105, which are connected via a pipe. The cold heat from the heat absorption part 102 of the heat pump 101 is supplied to external equipment, for example.

  In the present embodiment, the number of compression stages in the compression unit 103 is set according to the specification of the steam generation system S1, and is 1, 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. As the working medium used for the heat pump 101, various known heat mediums such as a chlorofluorocarbon medium, ammonia, water, carbon dioxide, and air are used according to the specifications and heat balance of the steam generation system S1. In addition, the heat source 100 is not limited to the structure containing a heat pump.

  In other embodiments, water from various devices or waste energy (hot waste heat) can be used to heat the water. For example, a vapor compression refrigerator, an absorption refrigerator (gas direct-fired absorption refrigerator, vapor absorption refrigerator, etc.), an adsorption refrigerator, a refrigerator, or a combustion engine (boiler, internal combustion engine, etc.) is adopted as the device. can do.

  The supply path 20 includes a heating unit 21, an evaporation unit 22 having an evaporation tank 47, and a duct 23 that fluidly connects the evaporation unit 22 and the compressor 30. In the present embodiment, the supply path 20 further includes a path 201 through which water heated by the heat pump 101 flows and a path 202 through which water heated by the heating unit 21 flows. The path 201 is fluidly connected to the tank 47 of the evaporation unit 22. In the path 201, a storage tank 203 that is disposed between the heat pump 101 and the tank 47 and temporarily stores heated water from a heat source, and a fluid drive unit 204 are provided as necessary. The tank 203 is provided with a deaeration function as necessary. A gas-liquid separator is disposed inside the tank 203, and the degassed gas can be appropriately discharged to the outside (atmosphere) via a discharge pipe (not shown). Moreover, the tank 203 can have a level sensor for measuring the liquid level and a temperature sensor as necessary. In the present embodiment, the path 202 is also fluidly connected to the tank 47 of the evaporation unit 22. In the path 202, a tank, a fluid drive unit, or the like that temporarily stores hot water from the heating unit 21 can be provided between the heating unit 21 and the tank 47. A form in which a part of the path 202 includes a part of the path 201, that is, a form in which the path 202 is fluidly connected to the tank 47 through a part of the path 201 may be adopted.

  In the heating unit 21, a part of the path 202 is thermally connected to the fifth heat radiating unit 13 </ b> E of the heat pump 10. The 1st heat exchanger 41 is comprised including the heating part 21 and the 5th thermal radiation part 13E. The first heat exchanger 41 may have a countercurrent heat exchange system in which a low-temperature fluid (water in the path 202) and a high-temperature fluid (working fluid in the heat pump 10) flow opposite to each other. Alternatively, the first heat exchanger 41 may have a parallel flow type heat exchange system in which a high-temperature fluid and a low-temperature fluid flow in parallel. In the present embodiment, various known ones can be adopted as the heat exchange structure of the first heat exchanger 41. The piping of the heating unit 21 and the piping of the fifth heat radiation unit 13E are arranged in contact with or adjacent to each other. For example, the pipe of the fifth heat radiation part 13E can be disposed on the outer peripheral surface or inside of the pipe of the heating part 21. In the heating unit 21, the temperature of water in the path 202 rises due to the heat transferred from the fifth heat radiating unit 13 </ b> E of the heat pump 10.

  The evaporating unit 22 includes a tank 47 for storing a medium to be heated (water), and circulation pipes (first circulation pipe 48A, second circulation pipe 48B, third circulation pipe 48C, fourth fluid fluidly connected to the tank 47). A circulation pipe 48D). The tank 47 is provided with a water supply port from the tank 203 and a steam discharge port. The tank 47 includes a level sensor 50 that measures the liquid level as necessary, a sensor 60 that measures information corresponding to the temperature of water (steam) in the tank 47, and a gas-liquid separator (not used) as necessary. As shown). Information from the level sensor 50 and the sensor 60 is sent to the control device 70.

  In the present embodiment, the sensor 60 measures the temperature of the gas phase portion in the tank 47. In another embodiment, the sensor 60 can measure the temperature of the liquid phase part in the tank 47 or the temperature of both the gas phase part and the liquid phase part. The gas phase portion in the tank 47 often has a smaller temperature distribution width than the liquid phase portion. The sensor 60 is not limited to one that directly measures the temperature of water (steam). For example, the sensor 60 may measure the temperature of the wall of the tank 47 and may measure at least the pressure in the tank 47.

  In the present embodiment, each circulation pipe 48 </ b> A, 48 </ b> B, 48 </ b> C, 48 </ b> D is fluidly connected to one tank 47. That is, each inlet end and each outlet end of the circulation pipes 48 </ b> A to 48 </ b> D are fluidly connected to the tank 47. The number of circulation pipes is set according to the specification of the steam generation system S1, and is 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. 48 A of 1st circulation piping has the evaporation pipe | tube 51A thermally connected to the 1st thermal radiation part 13A of the heat pump 10, the pump 52A, and the valve | bulb 53A as needed. Similarly, the 2nd circulation piping 48B has the evaporation pipe | tube 51B thermally connected to the 2nd thermal radiation part 13B of the heat pump 10, the pump 52B, and the valve | bulb 53B as needed. The third circulation pipe 48C has an evaporation pipe 51C thermally connected to the third heat radiating portion 13C of the heat pump 10, a pump 52C, and a valve 53C as necessary, and the fourth circulation pipe 48D is a heat pump. It has an evaporation pipe 51D thermally connected to the tenth fourth heat radiation part 13D, a pump 52D, and a valve 53D as necessary. The valves 53A to 53D are, for example, regulators, flow rate control valves, or open / close valves. In the present embodiment, the evaporation pipes 51 </ b> A to 51 </ b> D are individually fluidly connected to the tank 47. Further, the evaporation pipes 51 </ b> A to 51 </ b> D are arranged in parallel to the tank 47 and the supply path 20. At least one of the pumps 52A to 52D may be omitted by using thermal convection of the medium to be heated (water) and / or differential pressure with the outside.

  A second heat exchanger 42 is configured including the evaporation pipe 51A and the first heat radiation part 13A. Similarly, the 3rd heat exchanger 43 is comprised including the evaporation pipe | tube 51B and the 2nd thermal radiation part 13B. A fourth heat exchanger 44 is configured including the evaporation pipe 51C and the third heat radiating portion 13C, and a fifth heat exchanger 45 is configured including the evaporation pipe 51D and the fourth heat radiating portion 13D. The second to fifth heat exchangers 42 to 45 are counter-current heat exchanges in which a low-temperature fluid (water in the evaporation pipes 51A to 51D) and a high-temperature fluid (working fluid in the heat pump 10) face each other. You can have a scheme. Alternatively, the second to fifth heat exchangers 42 to 45 may have a parallel flow type heat exchange system in which a high-temperature fluid and a low-temperature fluid flow in parallel. Various known heat exchange structures for the second to fifth heat exchangers 42 to 45 can be employed. The pipes of the heat radiation portions 13A, 13B, 13C, and 13D of the heat pump 10 and the evaporation pipes 51A, 51B, 51C, and 51D are arranged in contact with or adjacent to each other. For example, the pipes of the heat radiating portions 13A, 13B, 13C, and 13D of the heat pump 10 can be disposed on the outer peripheral surface and the inside of the evaporation pipes 51A, 51B, 51C, and 51D.

  The compressor 30 is disposed on the supply path 20 and is disposed downstream of the tank 47. As the compressor 30, various compressors such as an axial flow compressor, a centrifugal compressor, a reciprocating compressor, and a rotary compressor are applied, and those suitable for vapor compression are used. The compressor 30 compresses the steam from the tank 47 and flows the pressurized steam downstream.

  In the compressor 30 and / or the supply path 20, a nozzle 35 that supplies water to the steam is disposed as necessary. The arrangement position of the nozzle 35 is, for example, an inlet and / or an outlet of the compressor 30. When the compressor 30 is a multistage type, the nozzle 35 can be disposed between the stages of the compressor 30. In the present embodiment, the compressor 30 has a four-stage compression structure including a first compression unit 30A, a second compression unit 30B, a third compression unit 30C, and a fourth compression unit 30D. The multistage compression structure of the compressor 30 is advantageous for increasing the temperature and pressure of steam, which will be described later. The compressor 30 can have a multiaxial compression structure in which the rotation speeds corresponding to the compression units 30A, 30B, 30C, and 30D are individually controlled. Alternatively, the compressor 30 can have a coaxial compression structure. In the present embodiment, the compression units 30A and 30B are configured coaxially, and the compression units 30C and 30D are configured coaxially. Power is supplied to each of the two shafts. The compression ratios (pressure ratios) of the compression units 30A to 30D are set according to the specifications of the steam generation system S1. In this embodiment, the nozzle 35 is arrange | positioned between each stage. The nozzle 35 and the liquid phase position of the tank 47 can be fluidly connected via the pipe 36. In this piping configuration, the liquid in the tank 47 having a relatively high temperature is effectively used for supply to the nozzle 35. For discharging (spraying) the liquid from the nozzle 35, a power source such as a pump 37 may be used, or a pressure difference between the inlet and the outlet of the pipe 36 may be used.

  Due to the suction action by the compressor 30, the internal space at the heating portion by the heat pump 10 in the supply path 20, that is, the internal space of the tank 47 is decompressed. In the present embodiment, the control valve (such as a flow rate control valve, not shown) and the compressor 30 on the supply path 20 are controlled so that the internal pressure of the tank 47 becomes a negative pressure (negative pressure) lower than the atmospheric pressure. Is done. Accordingly, the water in the tank 47 can evaporate at less than 100 ° C.

  In the present embodiment, between the tank 47 and the compressor 30 of the evaporation unit 22, valves 301, 302, as switching devices that selectively guide the vapor from the tank 47 to any stage of the compressor 30. 303 is arranged. The valve 301 is fluidly connected to the inlet of the first compression unit 30A via a pipe or the like. Similarly, the valve 302 is fluidly connected to the inlet of the second compressor 30B, and the valve 303 is fluidly connected to the inlet of the third compressor 30C. For example, when the valve 301 is open and the other valves 302 and 303 are closed, steam from the tank 47 is introduced into the first compression unit 30A via the valve 301. The steam from the valve 301 is compressed in four stages by the first to fourth compression units 30A to 30D. The steam from the valve 302 is compressed in three stages by the second to fourth compression units 30B to 30D. The steam from the valve 303 is compressed in two stages by the third and fourth compression units 30C and 30D.

  The heat supply unit 90 includes storage tanks (110A, 110B) that are fluidly connected to the tank 47 of the evaporation unit 22 via a path 210. Hot water is supplied to the tanks (110A, 110B) of the heat supply unit 90 from the tank 47 of the evaporation unit 22 via the path 210. Normally, this hot water has a lower temperature than the hot water supplied from the heat source 100 to the tank 47. The heat supply unit 90 supplies the heat of the hot water in the tanks (110A, 110B) to the heat absorption unit 11 of the heat pump 10. Details of the configuration of the heat supply unit 90 will be described later.

  In this embodiment, regarding the temperature of the water in the tank 47, for example, three reference values TA1, TA2, and TA3 are set. For example, TA1 is 80 ° C., TA2 is 85 ° C., and TA3 is 90 ° C. The numerical value is an example, and the present invention is not limited to this. This reference value is stored in a storage unit (not shown) of the control device 70, for example.

  In the present embodiment, at least the operation of the heat pump 10, the operation of the compressor 30, and the operation of the heat supply unit 90 are controlled according to the phase determined along the reference value related to the temperature of the water in the tank 47. . The control device 70 calculates the temperature of water (steam) in the tank 47 based on information from the sensor 60. Normally, the control device 70 substantially stops the heat pump 10 and the heat supply unit 90 when the water in the tank 47 is above a predetermined temperature, and the heat pump 10 and the heat supply unit when the water in the tank 47 is lower than the predetermined temperature. 90 is activated. Further, the control device 70 controls the valves 301 to 303 based on the water temperature of the tank 47. Details of the configuration of the heat supply unit 90 will be described later.

  Here, the case where the water temperature of the tank 47 is equal to or higher than TA3 is referred to as A1 phase (Phase A1). TA2 or more and less than TA3 is designated as A2 phase (Phase A2). The case where TA1 or more and less than TA2 is designated as A3 phase (Phase A3). The case where it is less than TA1 is designated as A4 phase (Phase A4).

  FIGS. 2A, 2B, 2C, 2D, and 2E are schematic diagrams respectively showing the operation state of the steam generation system S1. FIG. 2A shows the A1 phase, and the second B shows the A2 phase. FIG. 2C is a transition phase between the A2 phase and the A3 phase. FIG. 2D shows the A3 phase, and FIG. 2D shows the A4 phase.

  In the A1 phase, as shown in FIG. 2A, hot water from the heat source 100 is appropriately stored in the tank 203. The output temperature of the hot water from the heat source 100 is, for example, 90 to 99 ° C. The numerical value is an example, and the present invention is not limited to this. Hot water from the tank 203 is introduced into the tank 47 of the evaporation unit 22. The control device 70 substantially stops the heat pump 10 and the heat supply unit 90 and operates the compressor 30. As the compressor 30 is operated, the hot water in the tank 47 is boiled under reduced pressure. In the A1 phase, since the water temperature of the tank 47 is higher than in the other phases, the water in the tank 47 can be boiled at a low pressure reduction level. The control device 70 opens the valve 303 and closes the valves 301 and 302. The steam from the tank 47 is introduced into the third compression unit 30C through the valve 303.

  In the present embodiment, the substantially stopped state of the heat pump 10 and the heat supply unit 90 may include a state in which some devices of the heat pump 10 and / or some devices of the heat supply unit 90 are operating. For example, in a substantially stopped state, a preparation operation, a test operation, a maintenance operation, or the like of the heat pump 10 or the heat supply unit 90 may be performed.

  In the A1 phase, the hot water in the tank 47 is deprived of the heat of evaporation and drops in temperature due to boiling under reduced pressure. When the hot water in the tank 47 becomes less than TA3, the system S1 shifts to the A2 phase.

  In the A2 phase, as shown in FIG. 2B, the valve 302 is opened and the valves 301 and 303 are closed. Thereby, the internal space of the tank 47 is set to a decompression level higher than that in the A1 phase. As a result, the hot water in the tank 47 having a temperature lower than that of the A1 phase can be boiled. The steam from the tank 47 is introduced into the second compression unit 30B through the valve 302. When the hot water in the tank 47 becomes less than TA2, the process proceeds to the A3 phase.

  In the A3 phase, as shown in FIG. 2C, the valve 301 is opened and the valves 302 and 303 are closed. As a result, the internal space of the tank 47 is set to a higher pressure reduction level than in the A2 phase. As a result, it is possible to boil the hot water in the tank 47 that is cooler than the A2 phase. Steam from the tank 47 is introduced into the first compression unit 30 </ b> A through the valve 301. In the boiling under reduced pressure, the hot water in the tank 47 is deprived of the evaporation heat and falls in temperature.

  In this embodiment, when the hot water in the tank 47 becomes less than TA1, as shown in FIG. 2D, the hot water is introduced from the tank 47 of the evaporation unit 22 into the tank of the heat supply unit 90 via the path 210. In other words, the relatively low temperature hot water used in the evaporation unit 22 is supplied to the heat supply unit 90. This hot water is used as a heat source of the heat pump 10 in the A4 phase.

  In addition, introduction of warm water from the tank 47 of the evaporation unit 22 to the tank of the heat supply unit 90 can be performed at an arbitrary timing. In other phases, the hot water in the tank 47 that has become less than TA1 can be appropriately introduced into the tank of the heat supply unit 90. Thereby, when discharging | emitting the warm water used by the evaporation part 22, it can prevent that a vapor | steam production | generation process middle-stages.

  The transition between the phases is not limited to that based on the water temperature of the tank 47 (measurement result of the sensor 60). For example, in other embodiments, transitions between phases can be performed based on at least the elapsed time of the phases. Or you may refer the information which measured the characteristic of the vapor | steam output from system S1.

  In the A4 phase, as shown in FIG. 2E, the control device 70 operates the heat pump 10, the compressor 30, and the heat supply unit 90, respectively. The heat supply unit 90 supplies the heat of the hot water supplied from the tank 47 of the evaporation unit 22 to the heat absorption unit 11 of the heat pump 10. The heat pump 10 pumps up the heat of the hot water by the heat absorption part 11, and discharge | releases the heat by the thermal radiation parts 13A-13E. For example, the control device 70 opens the valve 303 and closes the valves 301 and 302. As the compressor 30 is operated, the internal space of the tank 47 of the evaporation unit 22 is depressurized. The opening / closing control of the valves 301 to 303 in the A4 phase is not limited to the above. The valve 302 may be opened, the valves 301 and 303 may be closed, the valve 301 may be opened, and the valves 302 and 303 may be closed. In the A4 phase, the hot water can be boiled under reduced pressure by the decompression of the internal space and the heat transferred from the heat pump 10.

  In the A4 phase, the heat from the heat pump 10 is continuously transmitted to the hot water in the tank 47. Therefore, the warm water in the tank 47 can maintain a substantially constant temperature. On the other hand, with the operation of the heat pump 10, heat is taken from the hot water in the heat supply unit 90. When the amount of heat that can be supplied from the heat supply unit 90 to the heat pump 10 falls below a certain value, the system S1 shifts to the A1 phase. Thereafter, the system S1 can repeatedly execute the A1 phase to the A4 phase.

  As described above, according to the present embodiment, the relatively hot water from the heat source 100 is directly introduced into the tank 47 of the evaporation unit 22. In the system S1, the hot water having a relatively high temperature can be boiled under reduced pressure without substantially operating the heat pump 10. In this case, the hot water from the heat source 100 evaporates as it is, and heat transfer for generating steam is substantially omitted. As a result, there is little heat loss related to steam generation. In this case, since the heat pump 10 and the heat supply unit 90 are substantially stopped, the power consumption is small.

  In the present embodiment, since the tank 203 for temporarily storing hot water from the heat source 100 is provided between the heat source 100 and the tank 47, the operation timing between the heat pump 101 of the heat source 100 and the system S1 is provided. Can be absorbed. That is, since thermal energy is buffered in the tank 203, mismatching of the operation timings of both is allowed. The operation of the heat pump 101 of the heat source 100 may be, for example, a time zone (for example, at night) when the power rate is set low. In this case, power consumption in the system S1 can be distributed between night and daytime, and peak power and average power consumption can be kept low. This is advantageous for simplification and cost reduction of the power receiving equipment, and suppression of contract power (electric power basic charge).

  When the heat source 100 is used not only as a heat supply device but also as a cold heat supply device to the outside, the timing and amount of steam generation and cold supply can be adjusted according to the steam demand and / or the cold demand. That is, the system S1 has high flexibility and controllability for steam supply and cold supply. Such a system S1 is preferably used, for example, in a food manufacturing process in which heating and cooling are repeated. The system S1 is preferably applicable not only to food manufacturing processes but also to various facilities and processes that generate steam demand and cold demand.

  In the present embodiment, the decompression level of the internal space of the tank 47 is controlled in accordance with the hot water temperature in the tank 47 of the evaporation unit 22. As a result, hot water can be boiled under reduced pressure without operating the heat pump 10 over a relatively wide temperature range. Furthermore, in this embodiment, the relatively low temperature hot water used in the evaporation unit 22 is used as a heat source for the heat pump 10. The system S1 can use the hot water stored in the tank of the heat supply unit 90 to generate steam by operating the heat pump 10 regardless of the timing of supplying hot water from the heat source 100. As a result, in the system S1, the heat of hot water from the heat source 100 is widely used from the high temperature range to the low temperature range. In addition, the steam production | generation using the heat pump 10 can obtain high energy efficiency compared with a boiler.

  Returning to FIG. 1, the operation of the heat pump 10 will be described in detail. In the evaporation unit 22, the water heated by the heating unit 21 is supplied to the tank 47 through the supply port, and the hot water is stored in the tank 47 and the circulation pipes 48A to 48D. The amount of hot water supplied to the tank 47 is controlled so that the liquid level in the tank 47 falls within a predetermined range. For example, the amount of hot water supplied to the tank 47 is controlled based on the measurement result of the level sensor 50. The warm water in the evaporation pipes 51A to 51D is further heated by the heat transferred from the first to fourth heat radiation portions 13A to 13D of the heat pump 10, and at least a part of the warm water evaporates. The tank 47 is fluidly connected to the compressor 30 via the duct 23. The internal space of the tank 47 is sucked by the compressor 30 through the discharge port of the tank 47 and the duct 23. The steam in the tank 47 flows in the duct 23 toward the compressor 30.

  The coefficient of performance of the heat pump 10 changes according to the difference between the input temperature and the output temperature of the medium to be heated (water), and if the temperature difference is excessively large, the coefficient of performance (COP) may decrease. Under the condition that the internal space of the tank 47 is in a negative pressure state, the heating temperature region (input / output temperature difference) is set to be relatively narrow, and the heat pump 10 can be used at a high COP. When the heat pump 10 is in operation, the water input temperature to the heating unit 21 is, for example, about 20 ° C. Further, when the heat pump 10 is in operation, the output temperature of water from the evaporation unit 22 is about 90, for example. The numerical value is an example, and the present invention is not limited to this. The output temperature of water from the evaporation unit 22 during operation of the heat pump 10 may be 100 ° C., 110 ° C., 120 ° C., 130 ° C. or higher, or may be lower than 90 ° C.

  The heat supply unit 90 includes a first tank 110A, a second tank 110B, and a circulation path 120. In other embodiments, the number of tanks can be three or more. Hot water is introduced into the first tank 110 </ b> A from the tank 47 of the evaporation unit 22 via the path 202.

  In the present embodiment, a pump 121, a sensor 122, and a heat radiating unit 91 are disposed in the circulation path 120. Furthermore, a valve 125 for switching the supply source of the medium (water) to the heat radiating unit 91 and a valve 126 for switching the return destination of the medium (water) from the heat radiating unit 91 are arranged in the circulation path 120. The tanks 110A and 110B are appropriately provided with a sensor (such as a liquid level sensor) for measuring the amount of storage.

  In the present embodiment, the medium for supplying heat to the heat absorption unit 11 of the heat pump 10 is hot water introduced from the tank 47 of the evaporation unit 22 to the first tank 110A. As described above, hot water from the tank 47 of the evaporation unit 22 is stored in the first tank 110A at a predetermined timing. By operating the pump 121, the medium (hot water) from the first tank 110 </ b> A is supplied to the heat radiating unit 91 as a heat source supplied to the heat pump 10. The medium that has radiated heat returns from the heat radiating portion 91 to the second tank 110 </ b> B through the circulation path 120.

  When the medium in the first tank 110A falls below a predetermined amount, the control device 70 controls the valve 125 and the valve 126 to switch the medium supply route. Thereby, instead of the first tank 110 </ b> A, the medium (hot water) from the second tank 110 </ b> B is supplied to the heat radiating unit 91 as a heat source supplied to the heat pump 10. The medium that has radiated heat returns to the first tank 110 </ b> A from the heat radiating unit 91 via the circulation path 120. Thereafter, the medium (hot water) goes back and forth between the first tank 110A and the second tank 110B.

  The sensor 122 measures at least one of the temperature and the flow rate of the medium flowing through the circulation path 120. In the present embodiment, the sensor 122 measures the temperature and flow rate of the medium before flowing into the heat radiating unit 91 (the temperature of the heat inlet and the flow rate of the heat to the heat absorbing unit 11 of the heat pump 10). The measurement result of the sensor 122 is sent to the control device 70. In other embodiments, the sensor 122 may measure the outlet temperature and / or outlet flow rate of the medium, and may measure both the inlet and outlet temperature and / or flow rate. The control device 70 is configured such that a heat quantity (specific heat × temperature × flow rate) sufficient for the working medium of the heat pump 10 to vaporize (evaporate) from the medium (first medium) flowing through the circulation path 120 to the working medium (second medium) of the heat pump 10. A predetermined control is performed so as to be supplied to the medium.

  In the present embodiment, the control device 70 controls the heat exchange amount in the regenerator 18, the input position of the working medium to the compression unit 12, and the pressure reduction ratio in the expansion unit 14 based on the measurement result of the sensor 122. In another embodiment, the control device 70 controls any one or two of the heat exchange amount in the regenerator 18, the input position of the working medium to the compression unit 12, and the decompression ratio in the expansion unit 14. Also good.

  In the present embodiment, as shown in FIG. 1, valves 501, 502, 503 as devices (heat amount control devices) for controlling the heat exchange amount in the regenerator 18 are disposed between the heat absorbing unit 11 and the regenerator 18. 504 is arranged. Each of the valves 501 to 504 is fluidly connected to different input positions of the regenerator 18 through piping or the like. For example, when the valve 504 is open and the other valves 501 to 503 are closed, the working medium from the heat absorbing unit 11 flows through the main path 15 in the regenerator 18 via the valve 504. In the regenerator 18, when only the valve 504 is open, the heat exchange (heat from the working medium flowing through the bypass path 17 is transferred to the working medium flowing through the main path 15) has the longest span. When only valve 503 is open, the second span is the longest. The span becomes shorter in the order of the valve 503, the valve 502, and the valve 501. If the temperature of the working medium flowing through the bypass path 17 is constant, the amount of heat (heat exchange amount) transmitted to the working medium flowing through the main path 15 increases as the heat exchange span increases.

  The valve is not limited to an on-off valve. The combination of valves as the calorie control device can be changed as appropriate. In other embodiments, the heat control device for the regenerator 18 may have a mechanism for mechanically changing the span of substantial heat exchange. For example, the heat quantity control device can have a mechanism for mechanically changing the length (area) of the pipe of the main path 15 arranged adjacent to the pipe of the bypass path 17. Alternatively, the heat quantity control device can have a mechanism for mechanically changing the interval between the pipe of the bypass path 17 and the pipe of the adjacent main path 15.

  In this embodiment, between the regenerator 18 and the compression unit 12, a valve 521 as a switching device that selectively guides the working medium from the heat absorption unit 11 and the regenerator 18 to any stage of the compression unit 12. , 522, 523, 524 are arranged. The valve 521 is fluidly connected to the inlet of the fourth compression unit 12D via a pipe or the like. Similarly, the valve 522 is fluidly connected to the inlet of the third compressor 12C, the valve 523 is fluidly connected to the inlet of the second compressor 12B, and the valve 524 is fluidly connected to the inlet of the first compressor 12A. Connected to. For example, when the valve 521 is open and the other valves 522 to 524 are closed, the working medium from the regenerator 18 is supplied to the fourth compression unit 12D via the valve 521. The working medium from the valve 521 is single-stage compressed by the fourth compression unit 12D. The working medium from the valve 522 is compressed in two stages by the third compression unit 12C and the fourth compression unit 12D. The working medium from the valve 523 is compressed in three stages by the second, third, and fourth compression units 12B, 12C, and 12D. The working medium from the valve 524 is compressed in four stages by the first to fourth compression units 12A to 12D.

  In the present embodiment, as described above, the expansion unit 14 includes the pressure reducing control valve 400. The decompression control valve 400 can change the decompression ratio to multiple stages or continuously. In the present embodiment, the pressure reduction control valve 400 can control the pressure reduction ratio into four levels of high level (that is, the pressure reduction ratio is high), medium high level, medium low level, and low level.

  In the present embodiment, for example, four temperatures of TB1, TB2, TB3, and TB4 are provided for the warm temperature (the temperature of the medium (warm water) flowing through the heat dissipation unit 91 of the heat supply unit 90) supplied to the heat absorption unit 11 of the heat pump 10. A reference value is set. The reference value is stored in a storage unit (not shown) of the control device 70, for example.

  The control device 70 controls at least the valves 501 to 504, the valves 521 to 524, and the pressure reduction control valve 400 according to the phase determined along the reference value. As described above, the hot temperature is measured by the sensor 122 disposed at the entrance of the heat radiating unit 91 of the heat supply unit 90.

  Here, a case where the temperature of the warm heat (warm water) from the heat supply unit 90 is equal to or higher than TB4 is referred to as a B1 phase (Phase B1). The case where it is greater than or equal to TB3 and less than TB4 is referred to as B2 phase (Phase B2). The case where it is greater than or equal to TB2 and less than TB3 is referred to as B3 phase (Phase B3). The case where it is greater than or equal to TB1 and less than TB2 is referred to as B4 phase (Phase B4). In the present embodiment, each of the B1 to B4 phases is executed as a part of the A4 phase described above.

  In the present embodiment, the temperature of the warm heat supplied to the heat absorption part of the heat pump 10 changes stepwise. That is, every time the source of warm heat is switched between the tanks 110 </ b> A and 110 </ b> B of the heat supply unit 90, the warm heat supply temperature changes.

  At the beginning of the circulation supply, the temperature of the medium (hot water) from the first tank 110A is the highest, and the control device 70 controls the heat pump 10 so as to correspond to the B1 phase. Next, the temperature from the second tank 110B is lower than the initial temperature, and the control device 70 controls the heat pump 10 so as to correspond to the B2 phase. Thereafter, each time the tanks 110A and 110B that supply hot heat are switched, the heat pump 10 is shifted in the order of the B3 phase and the B4 phase. Thereby, the route of the working medium in the heat pump 10 is optimized according to the temperature fluctuation of the medium from the tanks 110A and 11B that are circulated. The phase transition does not necessarily correspond to tank switching. For example, the previous phase may be continued if the temperature of the heat that has fluctuated due to the single switching of the tank does not fall below a predetermined reference value.

  3A, 3B, 3C, and 3D are Ts diagrams illustrating an example of a state change of the working medium of the heat pump 10. FIG. FIG. 3A shows the B1 phase, and FIG. 3B shows the B2 phase. FIG. 3C shows the B3 phase, and FIG. 3D shows the B4 phase. 3A to 3D, changes in the warm temperature (the temperature of the medium (warm water) flowing through the heat radiating unit 91) accompanying heat exchange are conceptually shown by broken lines.

  In the B1 phase, as shown in FIG. 1, the control device 70 opens the valve 501, closes the valves 502, 503, and 504, opens the valve 521, and closes the valves 522, 523, and 524. Further, the pressure reduction control valve 400 is set to a low pressure reduction ratio. In the B1 phase, the heat exchange span in the regenerator 18 is the shortest, and single-stage compression is performed in the compression unit 12. That is, the working medium from the heat absorbing unit 11 is introduced into the regenerator 18 via the valve 501. The working medium from the regenerator 18 is introduced into the fourth compression unit 12D through the valve 521. The working medium is compressed by one stage by the fourth compression unit 12D.

  3A and 1, the B1 phase working medium undergoes phase change (evaporates) while keeping the temperature constant in the heat absorbing section 11. The temperature of the working medium from the heat absorbing unit 11 is raised in the regenerator 18. The temperature of the working medium further increases in the fourth compression unit 12D. The temperature of the working medium drops in the fourth heat radiating part 13D. The temperature of the working medium further decreases in the heating unit 21 or the regenerator 18. The working medium from the heating unit 21 is decompressed to about the saturated vapor pressure in the decompression control valve 400 and then introduced into the heat absorbing unit 11 again. The working medium from the pressure reduction control valve 400 has a higher pressure than the other phases. This is because the temperature of the working medium in the heat absorbing part 11 is higher than in other phases.

  In the B2 phase, as shown in FIG. 1, the control device 70 opens the valve 502, closes the valves 501, 503, and 504, opens the valve 522, and closes the valves 521, 523, and 524. Further, the pressure reducing control valve 400 is set to a medium to low level pressure reducing ratio. In the B2 phase, the heat exchange span in the regenerator 18 is short after the first phase, and the two-stage compression is performed in the compression unit 12. That is, the working medium from the heat absorption unit 11 is introduced into the regenerator 18 through the valve 502. The working medium from the regenerator 18 is introduced into the third compression unit 12C through the valve 522. The working medium is compressed in two stages by the third and fourth compression units 12C and 12D.

  In FIG. 3B and FIG. 1, the B2 phase working medium undergoes a phase change while keeping the temperature constant in the heat absorbing section 11, and the temperature is raised in the regenerator 18. In the second phase, the temperature of the working medium from the regenerator 18 is approximately the same as in the first phase. Moreover, the temperature of the working medium from the heat absorption part 11 is low compared with the 1st phase. Therefore, the heat exchange span in the regenerator 18 is longer than that in the first phase. The temperature of the working medium further increases in the third compression section 12C, and decreases in the third heat dissipation section 13C. The temperature of the working medium rises again in the fourth compression unit 12D and falls again in the fourth heat dissipation unit 13D. That is, in the third compression unit 12C, the third heat radiation unit 13C, the fourth compression unit 12D, and the fourth heat radiation unit 13D, the temperature of the working medium repeatedly increases and decreases. The temperature of the working medium from the fourth heat radiating unit 13D is approximately the same as in the first phase. The working medium from the heating unit 21 is depressurized by the depressurization control valve 400 and then introduced again into the heat absorbing unit 11. The pressure of the working medium from the pressure reducing control valve 400 is the second highest after the first phase.

  In the B3 phase, as shown in FIG. 1, the control device 70 opens the valve 503, closes the valves 501, 502, and 504, opens the valve 523, and closes the valves 521, 522, and 524. Further, the pressure reducing control valve 400 is set to a medium to high level pressure reducing ratio. In the B3 phase, the heat exchange span in the regenerator 18 is longer than that in the B2 phase, and the compression unit 12 performs three-stage compression. That is, the working medium from the heat absorption unit 11 is introduced into the regenerator 18 through the valve 503. The working medium from the regenerator 18 is introduced into the second compression unit 12B through the valve 523. The working medium is compressed in three stages by the second, third, and fourth compression units 12B, 12C, and 12D.

  In FIG. 3C and FIG. 1, the B3 phase working medium undergoes a phase change while keeping the temperature constant in the heat absorbing section 11, and the temperature is raised in the regenerator 18. In the B3 phase, the temperature of the working medium from the regenerator 18 is approximately the same as in the B1 and B2 phases. Moreover, the temperature of the working medium from the heat absorption part 11 is low compared with B2 phase. Therefore, the heat exchange span in the regenerator 18 is longer than that in the B2 phase. In the second compression unit 12B, the second heat radiation unit 13B, the third compression unit 12C, the third heat radiation unit 13C, the fourth compression unit 12D, and the fourth heat radiation unit 13D, the temperature of the working medium repeatedly increases and decreases. The temperature of the working medium from the fourth heat radiating unit 13D is approximately the same as in the B1 and B2 phases. The working medium from the heating unit 21 is depressurized by the depressurization control valve 400 and then introduced again into the heat absorbing unit 11. The pressure of the working medium from the pressure reduction control valve 400 is lower than that in the B2 phase.

  In the B4 phase, as shown in FIG. 1, the control device 70 opens the valve 504, closes the valves 501, 502, and 503, opens the valve 524, and closes the valves 521, 522, and 523. Further, the decompression control valve 400 is set to a high level decompression ratio. In the B4 phase, the heat exchange span in the regenerator 18 is the longest, and the compression unit 12 performs four-stage compression. That is, the working medium from the heat absorbing unit 11 is introduced into the regenerator 18 via the valve 504. The working medium from the regenerator 18 is introduced into the first compression unit 12A through the valve 524. The working medium is compressed in four stages by the first, second, third, and fourth compression units 12A, 12B, 12C, and 12D.

  In FIG. 3D and FIG. 1, the B4 phase working medium undergoes a phase change while keeping the temperature constant in the heat absorbing section 11, and the temperature is raised in the regenerator 18. In the B4 phase, the temperature of the working medium from the regenerator 18 is approximately the same as in the other phases. Moreover, the temperature of the working medium from the heat absorption part 11 is the lowest. Therefore, the heat exchange span in the regenerator 18 is the longest. In the first compression section 12A, the first heat radiation section 13A, the second compression section 12B, the second heat radiation section 13B, the third compression section 12C, the third heat radiation section 13C, the fourth compression section 12D, and the fourth heat radiation section 13D, The temperature of the working medium repeatedly rises and falls. The temperature of the working medium from the fourth heat radiating unit 13D is approximately the same as in the other phases. The working medium from the heating unit 21 is depressurized by the depressurization control valve 400 and then introduced again into the heat absorbing unit 11. The pressure of the working medium from the pressure reducing control valve 400 is the lowest.

  In addition, the temperature of the working medium which flows through the heat absorption part 11 in B1 phase is about 10 degreeC, for example, and a pressure is about 0.0829 MPa, for example. In the second phase, the third phase, and the fourth phase, the temperature of the working medium flowing through the heat absorbing unit 11 is, for example, about 33 ° C., about 55 ° C., and about 78 ° C., respectively. In the B4 phase, the pressure of the working medium after the first stage compression is, for example, about 0.174 MPa. Moreover, the pressure of the working medium after the second stage, the third stage, and the fourth stage compression is, for example, about 0.358 MPa, about 0.702 MPa, and about 1.26 MPa, respectively. The numerical value is an example, and the present invention is not limited to this.

  Thus, according to the present embodiment, switching of the path related to the regenerator 18 and the compression unit 12 and the control of the pressure reduction ratio in the expansion unit 14 according to the thermal temperature supplied to the heat absorption unit 11 of the heat pump 10. As a result, the heat radiation temperature from the heat pump 10 is maintained at a predetermined level. That is, the route of the working medium is optimized according to the change in the amount of heat received from the outside by the heat pump 10. Therefore, the system S1 has a wide allowable temperature range of the heat supplied to the heat pump 10, and can preferably cope with fluctuations in the heat temperature. Moreover, since the output of the compression part 12 is suppressed when comparatively high temperature heat is supplied to the heat pump 10, the efficiency of energy consumption is improved.

  Further, according to the present embodiment, the heat medium stored in the tanks 110 </ b> A and 110 </ b> B of the heat supply unit 90 is used as the heat source supplied to the heat pump 10, so that between the heat pump 10 and the heat pump 101 of the heat source 100. It is possible to absorb the deviation of the operation timing. That is, since thermal energy is buffered in the tanks 110A and 110B, mismatching of the operation timings of both is allowed.

  FIG. 4 schematically shows another modification of the heat supply unit 90. As shown in FIG. 4, the heat supply unit 90 includes a tank 110 and a circulation path 120.

  In the circulation path 120, a pump 121, a sensor 122, and a heat radiating unit 91 are arranged. When the pump 121 is activated, the medium (hot water) from the tank 110 flows through the circulation path 120. In the heat radiating unit 91, the heat of the medium flowing through the circulation path 120 is transmitted to the working medium flowing through the heat absorbing unit 11 of the heat pump 10. The medium that has radiated heat returns from the heat radiating unit 91 to the tank 110 via the circulation path 120. The medium in the tank 110 can be discharged to the outside through the discharge valve 123 as necessary.

  In the heat supply unit 90 of FIG. 4, when the pump 121 is operated, the medium from the tank 110 is circulated and supplied to the heat radiating unit 91 as a heat source supplied to the heat pump 10.

  In the heat supply unit 90 of FIG. 4, at the beginning of the circulation supply, the medium from the tank 110 has the highest temperature. The control device 70 controls the heat pump 10 so as to correspond to the B1 phase. When the medium radiated from the heat radiating unit 91 returns to the tank 110, the temperature of the medium in the tank 110 gradually decreases. When the measurement result of the sensor 122 becomes a predetermined value or less, the control device 70 controls the heat pump 10 so as to correspond to the B2 phase. Thereafter, the heat pump 10 is shifted in the order of the B3 phase and the B4 phase as the temperature of the medium from the tank 110 decreases. Thus, according to the form of FIG. 4, the route of the working medium in the heat pump 10 is optimized in accordance with the temperature fluctuation of the medium from the tank 110 that is circulated. That is, the medium (hot water) from the heat supply unit 90 is used over a wide temperature range as a heat source supplied to the heat pump 10. This is advantageous for improving energy efficiency. Note that the route of the working medium in the heat pump 10 may be optimized in accordance with the change in the flow rate of the medium in addition to the change in the temperature of the medium from the tank 110.

  Next, a basic steam generation process using the heat pump 10 will be described.

  As shown in FIG. 1, first, in the first heat exchanger 41, the temperature of the water in the supply path 20 rises to near the boiling point due to the heat transferred from the fifth heat radiating part 13 </ b> E of the heat pump 10. Thereafter, in the second to fifth heat exchangers 42 to 45, the water undergoes phase change and evaporates due to the heat transferred from at least one of the first to fourth heat radiating portions 13A to 13D. That is, sensible heat heating of water is mainly performed in the first heat exchanger 41, and latent heat heating of water is mainly performed in the second to fifth heat exchangers 42 to 45. The first heat exchanger 41 is in a form suitable for sensible heat exchange, and the second to fifth heat exchangers 42 to 45 are in a form suitable for latent heat exchange. Accordingly, steam is generated via a preferred heating process.

  The energy efficiency of the boiler is generally about 0.7 to 0.8 (70 to 80%), whereas the coefficient of performance (COP) as the energy efficiency of the heat pump is generally 2.5 to 5. 0. The coefficient of performance of the heat pump changes according to the input / output temperature difference of the medium to be heated (water), and the coefficient of performance tends to decrease at a relatively high input / output temperature difference. In this embodiment, since the heat pump has individual heating units corresponding to the sensible heat exchange and the latent heat exchange, it is possible to suppress the input / output temperature difference and generate steam with higher energy efficiency than the boiler.

  Further, in the present embodiment, the water in the supply path 20 becomes steam having a relatively low pressure and low temperature by heat transfer from the heat pump 10 (heat dissipating units 13 </ b> A to 13 </ b> E), and relatively high pressure by compression by the compressor 30. And it becomes high temperature steam. That is, the water heated by the heat pump 10 is further heated by the compression by the compressor 30, thereby generating high-temperature steam at 100 ° C. or higher. The steam from the steam generation system S1 is supplied to a predetermined external facility such as a manufacturing plant, a cooking facility, an air conditioning facility, a power plant, and the like.

  FIG. 5 is a Ts diagram showing an example of a change in the state of water by the steam generation system S1. As shown in FIG. 5, after the temperature rises to near the boiling point in the first heat exchanger 41 (see FIG. 1), water undergoes a phase change in the second to fifth heat exchangers 42 to 45 while keeping the temperature constant. At this time, saturated steam d0 is generated in a state of negative pressure P0 that is lower than atmospheric pressure (P1 = 1 atm = about 0.1 MPa). The temperature of the saturated vapor d0 is lower than the normal boiling point, for example, about 90 ° C.

  Next, the saturated steam d0 becomes a relatively high-pressure and high-temperature steam (superheated steam e2) by compression by the compressor 30 (see FIG. 1). That is, the temperature of the steam rises with the compression. The pressure P2 of the superheated steam e2 is higher than atmospheric pressure, for example, 0.8 MPa.

  A saturated steam of about 160 ° C. can be obtained by cooling the superheated steam e2 of 0.8 MPa under a constant pressure (dashed line a in FIG. 5). Similarly, saturated steam d1 at about 100 ° C. can be obtained by cooling superheated steam at atmospheric pressure (about 0.1 MPa) under constant pressure. The numerical value used in the above description is an example, and the present invention is not limited to this.

  By directly mixing liquid water or hot water into the cooling from superheated steam to saturated steam, the volume of steam is increased. In this case, for example, water or hot water is supplied to the steam at the outlet of the compressor 30.

  By optimizing the supply amount and timing of water or hot water, the change from the relatively low pressure and low temperature saturated steam d0 to the relatively high pressure and high temperature saturated steam d2 can be made more direct. For example, when an appropriate amount of water or hot water is supplied to the steam at the inlet of the compressor 30, the saturated steam d0 at the inlet of the compressor 30 changes to saturated steam d2 at the outlet of the compressor 30 (FIG. 5). Broken lines c1 (spray) and c2 (compression)). Alternatively, when an appropriate amount of water or hot water is supplied to the steam for each stage of the compressor 30 in the middle of the compressor 30, the saturated steam d0 at the inlet of the compressor 30 becomes saturated steam d2 at the outlet of the compressor 30. (Broken line b in FIG. 5). That is, by optimizing the combination of compression by the compressor 30 and cooling by water or warm water, steam close to a saturated state can be efficiently discharged from the compressor 30.

  As described above, in the present embodiment, the three stages including the two-stage heating by the heating part 21 and the heat radiating part (first to fourth heat radiating parts 13A to 13D) of the heat pump 10 shown in FIG. By sequential heating, both saturated steam and superheated steam can be easily generated. That is, after generating saturated steam at a negative pressure lower than the atmospheric pressure by heating by the heat pump 10, superheated steam or saturated steam at a pressure higher than atmospheric pressure or atmospheric pressure is generated by compression by the compressor 30. be able to. That is, the system S1 is highly flexible with respect to the steam specification.

  In the present embodiment, since the compressor 30 supplements a part of the heating process for steam generation, the heat pump 10 is used with a high COP. Therefore, the steam generation system S1 has a reduction in the primary energy as a whole. Be expected. That is, the use of the compressor 30 for heating in a relatively high temperature range with respect to the medium to be heated (water) is advantageous in shortening the temperature rise and suppressing heat loss compared to heating using only heat transfer. It is.

  In other embodiments, when the temperature of the heat supplied to the heat pump 10 is relatively high, for example, the decompression by the compressor 30 is omitted, and the heating unit 21 and the heat radiating unit (first to fourth) of the heat pump 10 are omitted. It is possible to generate steam by two-stage heating by the heat dissipating parts 13A to 13D).

  Moreover, in this embodiment, since a part of working medium bypasses the 1st heat exchanger 41 via the bypass path | route 17, optimization of the flow volume of the working medium which enters the 1st heat exchanger 41 is achieved. This is advantageous in effectively using the retained heat of the working medium.

  Moreover, in this embodiment, when a part of working medium bypasses the 1st heat exchanger 41 via the bypass path | route 17, the inflow amount of the working medium to the 1st heat exchanger 41 is controlled, As a result The working medium having an amount of heat as required is supplied to each of the first heat exchanger 41 and the second heat exchanger 42 (third to fifth heat exchangers 43 to 45).

  The working medium flowing through the bypass path 17 exchanges heat with the working medium from the heat absorbing unit 11 flowing through the main path 15 of the heat pump 10 in the regenerator 18. By this heat exchange, the temperature of the working medium in the bypass path 17 is lowered (for example, about 20 ° C.), and the temperature of the working medium in the main path 15 of the heat pump 10 is raised (for example, about 95 ° C.). Due to the increase in the input temperature of the working medium to the compression unit 12, the power of the compression unit 12 is reduced. Note that the amount of bypass of the working medium is determined according to each physical property value (such as specific heat) of the medium to be heated and the working medium. The numerical value used in the above description is an example, and the present invention is not limited to this.

  In the present embodiment, the working medium (for example, about 20 ° C.) in the bypass passage 17 whose temperature has dropped in the regenerator 18 is in front of the expansion unit 14 and flows through the main passage 15 of the heat pump 10. It merges with the working medium from the (fifth heat radiation part 13E). As described above, the output temperature of the working medium from the first heat exchanger 41 is set to be relatively low. The liquid gas ratio of the working medium is optimized by the decrease in the input temperature of the working medium to the expansion unit 14, and as a result, the heat source outside the cycle in the heat absorption unit 11 (medium flowing through the heat radiation unit 91 of the heat supply unit 90). Effectively absorbs heat.

  As described above, in the present embodiment, the working medium after being used for water evaporation is used for warming water and regenerating the working medium, thereby effectively using heat.

  In the present embodiment, the energy efficiency is also improved from the point that the compression unit 12 is a multistage type. That is, the heat dissipation of the heat dissipating parts 13A, 13B, and 13C between the stages of the multistage compression unit 12 is deprived, thereby suppressing the temperature rise of the working medium in the process of compressing the working medium. The efficiency is improved and the power of the compressor is reduced. The number of repetitions of the temperature rise of the working medium accompanying compression and the temperature drop of the working medium in the heat radiating section (13A, 13B, 13C) between the stages is 2, 3, 4, 5, 6 , 7, 8, 9, or 10 or more. It is advantageous for improving energy efficiency that the number of stages of reheating is large within the range of restrictions on the apparatus configuration.

  In the present embodiment, the point that the input temperature of the working medium to the multistage compression unit 12 is increased by the regenerator 18 is also advantageous in reducing the power of the compression unit 12. Further, effective use of heat can be achieved from the point of heating water that is a medium to be heated by using cooling of the heat radiation portions 13A, 13B, and 13C between the stages.

  In the present embodiment, since the supply path 20 includes the plurality of evaporation pipes 51A to 51D, the energy efficiency can be improved. In the evaporation pipe, the ratio of the gas (vapor) to the liquid increases along the direction of water flow, and the heat transfer coefficient decreases as the vapor generation proceeds. In the evaporator tube, it is preferable that water is dominant as a mass and a volume. Since the supply path 20 includes the plurality of evaporation pipes 51A to 51D, heating of water having a high gas ratio is avoided, and as a result, a decrease in heat transfer coefficient associated with steam generation is suppressed. In addition, if the length of the evaporation pipe is increased in order to increase the heat exchange area, the pressure difference between the inlet and outlet of the evaporation pipe increases, which may increase the power required to flow water through the evaporation pipe. is there. If the plurality of evaporation pipes 51A to 51D are individually independent, the differential pressure may be small, and an increase in water transport power accompanying the expansion of the heat exchange area is suppressed. The fact that the evaporation tubes 51A to 51D are arranged in parallel facilitates the achievement of a configuration in which the plurality of evaporation tubes 51A to 51D are individually independent, which is advantageous for simplification of the apparatus.

  In the present embodiment, the supply path 20 includes a plurality of independent evaporation pipes 51A to 51D, thereby improving the heat balance control. In the heat pump 10, the state (pressure etc.) of a working medium differs between the thermal radiation parts 13A-13D. Reheating in the multistage compression unit 12 having the heat radiation units 13A to 13D is achieved by individually controlling the flow rate per unit time of the water flowing through the plurality of evaporation pipes 51A to 51D corresponding to the heat radiation units 13A to 13D. The control is optimized.

  FIG. 6 shows an example of a configuration for controlling the flow rate of water in the evaporation pipe 51A. The heat pump 10 is provided with a sensor 71 that measures the outlet temperature of the first heat radiating portion 13A corresponding to the evaporation pipe 51A. The control device 70 controls the flow rate of water per unit time flowing through the evaporation pipe 51A via the pump 52A for the evaporation pipe 51A based on the measurement result of the sensor 71. Thereby, the exit temperature of the working medium in the first heat radiating portion 13A can be set to the target value. You may use the sensor 72 which measures the inlet_port | entrance temperature of 13 A of 1st thermal radiation parts. In FIG. 1, the other evaporation pipes 51 </ b> B to 51 </ b> D and the corresponding heat radiation portions 13 </ b> B to 13 </ b> D can adopt the same configuration.

  Next, a second embodiment will be described with reference to the drawings.

  FIG. 7 is a schematic diagram showing a steam generation system S2 according to the second embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 7, the steam generation system S2 is different from the first embodiment in that the evaporation unit 22 is provided with evaporation units 22a and 22b each having tanks 47a and 47b. The configurations of the heat source 100, the heat pump 10, and the heat supply unit 90 are substantially the same as those of the first embodiment.

  Each of the evaporation units 22a and 22b has the same configuration as the evaporation unit 22 in FIG. Specifically, as shown in FIG. 7, the evaporation units 22a and 22b include tanks 47a and 47b for storing a medium to be heated (water), and circulation pipes (first first) fluidly connected to the tanks 47a and 47b. The circulation pipes 48Aa and 48Ab, the second circulation pipes 48Ba and 48Bb, the third circulation pipes 48Ca and 48Cb, and the fourth circulation pipes 48Da and 48Db), respectively. The tanks 47a and 47b are provided with a water supply port from the tank 203 and a steam discharge port. The tanks 47a and 47b are provided with level sensors 50a and 50b for measuring the liquid level, sensors 60a and 60b for measuring information corresponding to the temperature of water (steam) in the tanks 47a and 47b, as necessary. Accordingly, a gas-liquid separator (not shown) is provided. Information from the level sensors 50 a and 50 b and the sensors 60 a and 60 b is sent to the control device 70.

  In the present embodiment, the sensors 60a and 60b measure the temperatures of the gas phase portions in the tanks 47a and 47b. In another embodiment, the sensors 60a and 60b can measure the temperature of the liquid phase part in the tanks 47a and 47b, or the temperature of both the gas phase part and the liquid phase part. The sensors 60a and 60b are not limited to those that directly measure the temperature of water (steam). For example, the sensors 60a and 60b may measure the temperature of the walls of the tanks 47a and 47b, and may measure at least the pressure in the tanks 47a and 47b.

  In the present embodiment, the circulation pipes 48Aa and 48Ab, 48Ba and 48Bb, 48Ca and 48Cb, 48Da and 48Db are fluidly connected to the tanks 47a and 47b, respectively. That is, as shown in FIG. 7, each inlet end and each outlet end of the circulation pipes 48Aa to 48Da are fluidly connected to the tank 47a. Each inlet end and each outlet end of the circulation pipes 48Ab to 48Db are fluidly connected to the tank 47b. The number of circulation pipes is set according to the specifications of the system S2, and is 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. The first circulation pipes 48Aa and 48Ab include evaporation pipes 51Aa and 51Ab that are thermally connected to the first heat radiating portion 13A of the heat pump 10, pumps 52Aa and 52Aa, and valves 53Aa and 53Ab as necessary. Similarly, the second circulation pipes 48Ba and 48Bb include evaporation pipes 51Ba and 51Bb that are thermally connected to the second heat radiating portion 13B of the heat pump 10, pumps 52Ba and 52Bb, and valves 53Ba and 53Bb as necessary. Have each. The third circulation pipes 48Ca and 48Cb include evaporation pipes 51Ca and 51Cb that are thermally connected to the third heat radiating portion 13C of the heat pump 10, pumps 52Ca and 52Cb, and valves 53Ca and 53Cb as necessary. The fourth circulation pipes 48Da and 48Db respectively have evaporation pipes 51Da and 51Db that are thermally connected to the fourth heat radiation part 13D of the heat pump 10, pumps 52Da and 52Db, and valves 53Da and 53Db as necessary. The valves 53Aa to 53Da and 53Ab to 53Db are, for example, regulators, flow rate control valves, or open / close valves. In the present embodiment, the evaporation pipes 51Aa to 51Da are fluidly connected to the tank 47a independently of each other. The evaporation pipes 51Ab to 51Db are fluidly connected to the tank 47b independently of each other. Further, the evaporation pipes 51 </ b> Aa to 51 </ b> Da are arranged in parallel to the tank 47 a and the supply path 20. The evaporation pipes 51Ab to 51Db are arranged in parallel to the tank 47b and the supply path 20. At least one of the pumps 52 </ b> Aa to 52 </ b> Da and 52 </ b> Ab to 52 </ b> Db may be omitted using thermal convection of the medium to be heated (water) and / or differential pressure with the outside.

  As shown in FIG. 7, the second heat exchanger 42 is configured including the evaporation pipe 51Aa, the evaporation pipe 51Ab, and the first heat radiation part 13A. Similarly, the 3rd heat exchanger 43 is comprised including evaporation pipe 51Ba, evaporation pipe 51Bb, and the 2nd thermal radiation part 13B. A fourth heat exchanger 44 is configured including the evaporation pipe 51Ca, the evaporation pipe 51Cb, and the third heat radiating portion 13C. A fifth heat exchanger 45 is configured including the evaporation pipe 51Da, the evaporation pipe 51Db, and the fourth heat radiation part 13D. The second to fifth heat exchangers 42 to 45 are counter-current heat exchanges in which a low-temperature fluid (water in the evaporation pipes 51A to 51D) and a high-temperature fluid (working fluid in the heat pump 10) face each other. You can have a scheme. Alternatively, the second to fifth heat exchangers 42 to 45 may have a parallel flow type heat exchange system in which a high-temperature fluid and a low-temperature fluid flow in parallel. Various known heat exchange structures for the second to fifth heat exchangers 42 to 45 can be employed. The pipes of the heat radiation portions 13A, 13B, 13C, and 13D of the heat pump 10 and the evaporation pipes 51Aa and 51Ab, 51Ba and 51Bb, 51Ca and 51Cb, 51Da and 51Db are arranged in contact with each other or adjacent to each other.

  In the present embodiment, the path 201 through which the heated water from the heat source 100 flows, as shown in FIG. 7, the substantial output destination of the heated water from the heat source 100 is changed to the evaporation unit 22a. And a valve 220 as a switch for selectively switching between the evaporation units 22b. The path 201 has branch paths 201a and 201b arranged between the tank 203 and the evaporation units (22a and 22b). The branch path 201a is fluidly connected between the valve 220 and the tank 47a of the evaporation unit 22a. The branch path 201b is fluidly connected between the valve 220 and the tank 47b of the evaporation unit 22b.

  As shown in FIG. 7, the path 210 through which the hot water flows toward the heat supply unit 90 has a valve 225 as a switch that selectively switches the supply source of the hot water between the evaporation unit 22a and the evaporation unit 22b. Further, the path 210 includes branch paths 210a and 210b arranged between the evaporation units (22a and 22b) and the tanks (110A and 110B) of the heat supply unit 90. The branch path 210a is fluidly connected between the tank 47a and the valve 225 of the evaporation unit 22a. The branch path 201b is fluidly connected between the tank 47b and the valve 225 of the evaporation unit 22b.

  As shown in FIG. 7, the path 202 through which the warm water from the heating unit 21 flows selects the substantial output destination of the heated water from the heating unit 21 between the evaporation unit 22a and the evaporation unit 22b. It has a valve 230 as a changeover switch. Moreover, the path | route 202 has the branch paths 202a and 202b arrange | positioned between the heating part 21 and the evaporation units (22a and 22b). The branch path 202a is fluidly connected between the valve 230 and the tank 47a of the evaporation unit 22a. The branch path 202b is fluidly connected between the valve 230 and the tank 47b of the evaporation unit 22b.

  As shown in FIG. 7, the duct 23 through which the steam from the evaporator 22 flows has a valve 240 as a switch that selectively switches the source of hot water between the evaporator unit 22 a and the evaporator unit 22 b. The duct 23 has branch paths 23 a and 23 b arranged between the evaporation units (22 a and 22 b) and the compressor 30. The branch path 23a is fluidly connected between the tank 47a and the valve 240 of the evaporation unit 22a. The branch path 23b is fluidly connected between the tank 47b of the evaporation unit 22b and the valve 240.

  In the present embodiment, the system S2 can execute the A1 phase to the A4 phase shown in FIGS. 2A to 2E with the evaporation unit 22a or the evaporation unit 22b selectively as a main body. The control device 70 can control the valves 220, 225, 230, 235, and 240 based on a predetermined condition.

  8A, 8B, and 8C are schematic diagrams respectively showing the operation state of the steam generation system S2.

  In FIG. 8A, when the hot water in the tank 47a of the evaporation unit 22a becomes less than TA1, the hot water is introduced from the tank 47a into the tank of the heat supply unit 90 via the path 210 (for example, the evaporation unit 22a This is the same as the state of transition from the A3 phase to the A4 phase shown in 2D.) The water temperature in the tank 47a can be measured based on information from the sensor 60a (see FIG. 7). In this embodiment, as shown in FIG. 8A, the system S2 is shown in FIGS. 2A to 2C with the evaporation unit 22b (tank 47b) as a main body in parallel with the supply of hot water from the tank 47a to the heat supply unit 90. The A1 phase to A3 phase can be executed.

  Specifically, as shown in FIG. 8A, the control device 70 controls the valve 225 to switch the hot water supply source for the heat supply unit 90 to the tank 47a of the evaporation unit 22a. Thereby, the comparatively low temperature warm water used with the evaporation unit 22a is guide | induced to the heat supply unit 90 via the branch path 210a. In addition, the control device 70 controls the valve 220 to switch the substantial output destination of the hot water from the heat source 100 to the tank 47b of the evaporation unit 22b. Thereby, the comparatively high temperature warm water from the heat source 100 is guide | induced to the tank 47b via the branch path | route 201b. Further, the control device 70 controls the valve 235 to switch the vapor suction source by the compressor 30 to the tank 47b of the evaporation unit 22b. Thereby, the vapor | steam from the tank 47b is guide | induced to the compressor 30 via the branch path 23b. Due to the suction action by the compressor 30, the hot water in the tank 47b is boiled under reduced pressure. The control device 70 controls the valve 240 to switch the supply source of the hot water to the nozzle 35 to the tank 47b of the evaporation unit 22b. Thereby, the warm water from the tank 47b of the evaporation unit 22b is guided to the nozzle 35 via the branch path 36b.

  Similarly, in FIG. 8B, when the hot water in the tank 47b of the evaporation unit 22b becomes less than TA1, the system S2 performs the evaporation unit 22a (tank 47a) in parallel with the hot water supply from the tank 47b to the heat supply unit 90. A1 phase to A3 phase shown in FIGS. 2A to 2C can be executed. The water temperature in the tank 47b can be measured based on information from the sensor 60b (see FIG. 7).

  Specifically, as shown in FIG. 8B, the control device 70 controls the valve 225 to switch the hot water supply source for the heat supply unit 90 to the tank 47b of the evaporation unit 22b. Thereby, the comparatively low temperature warm water used by the evaporation unit 22b is guide | induced to the heat supply unit 90 via the branch path 210b. In addition, the control device 70 controls the valve 220 to switch the substantial output destination of the hot water from the heat source 100 to the tank 47a of the evaporation unit 22a. Thereby, the comparatively high temperature warm water from the heat source 100 is guide | induced to the tank 47a via the branch path | route 201a. Further, the control device 70 controls the valve 235 to switch the vapor suction source by the compressor 30 to the tank 47a of the evaporation unit 22a. Thereby, the vapor | steam from the tank 47a is guide | induced to the compressor 30 via the branch path 23a. Due to the suction action by the compressor 30, the hot water in the tank 47a is boiled under reduced pressure. The control device 70 controls the valve 240 to switch the hot water supply source to the nozzle 35 to the tank 47a of the evaporation unit 22a. Thereby, the warm water from the tank 47a of the evaporation unit 22a is guided to the nozzle 35 via the branch path 36a.

  Thus, according to the present embodiment, the other tank 47b (or tank 47a) is installed in parallel with the supply of the hot water whose temperature has dropped from one tank 47a (or tank 47b) to the heat supply unit 90. Can be used to perform a steam generation process. As a result, it is possible to prevent the steam generation process from being interrupted when the hot water used in the evaporation units (evaporation units 22a and 22b) is discharged. That is, by alternately using the evaporation units 22a and the evaporation units 22b, steam can be continuously generated from the relatively high temperature hot water from the heat source 100.

  In the present embodiment, the steam generation process using the heat pump 10 can be executed at an arbitrary timing. For example, as shown in FIG. 8C, while the hot water from the heat source 100 is stored in the tank 47b of the evaporation unit 22b, steam can be generated using the heat pump 10 and the evaporation unit 22a (tank 47a). it can.

  Specifically, in FIG. 8C, the control device 70 controls the valve 220 to store hot water from the heat source 100 in the tank 47b of the evaporation unit 22b. The control device 70 operates the heat pump 10 and controls the valve 230 to guide the water heated by the heating unit 21 to the tank 47a of the other evaporation unit 22b. In FIG. 8C, the hot water of the evaporation unit 22b can be evaporated by the heat transferred from the heat pump 10 and the pressure reduction of the internal space of the tank 47a.

  In the present embodiment, the timing of steam generation using the heat pump 10 is not limited to the example of FIG. 8C. For example, the system S2 can generate steam using the heat pump 10 when the hot water supply from the heat source 100 is stopped. At this time, the heat pump 10 is operated using the hot water stored in the tank of the heat supply unit 90 as a heat source.

  According to the present embodiment, while the hot water is continuously supplied from the heat source 100, the steam is continuously generated by alternately using the evaporation units 22a and 22b, and the supply of the hot water from the heat source 100 is interrupted. Can continuously generate steam using the heat pump 10. Therefore, this system S2 has a high tolerance for the timing of supplying hot water from the heat source 100.

  In FIG. 7, the evaporation units 22 a and 22 b share the compressor 30. However, each of the evaporation unit 22a and the evaporation unit 22b may have a compressor.

  Next, a third embodiment will be described with reference to the drawings.

  FIG. 9 is a schematic diagram showing a steam generation system S3 according to the third embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 9, the steam generation system S3 is provided with a path 250 branched from the path 201, unlike the first embodiment. The path 201 is provided with a sensor 252 and a valve 254. The path 250 is substantially directly and fluidly connected between the heat source 100 and the heat supply unit 90. In the present embodiment, the path 250 is fluidly connected between the valve 254 and the first tank 110 </ b> A of the heat supply unit 90. The sensor 252 is disposed on the path 201 and upstream of the valve 254 and measures information corresponding to the output temperature of the hot water from the heat source 100. The valve 254 can switch the substantial output destination of the hot water from the heat source 100 between the tank 47 of the evaporator 22 and the first tank 110 </ b> A of the heat supply unit 90 based on the measurement result of the sensor 252. .

  In the present embodiment, when the output temperature of the hot water from the heat source 100 is relatively high, the hot water from the heat source 100 is guided to the tank 47 of the evaporation unit 22 via the tank 203. That is, the control device 70 controls the valve 254 to switch the substantial output destination of the hot water from the heat source 100 to the tank 47 of the evaporation unit 22 (the tank 203 in front of the tank 47 in this embodiment). On the other hand, when the output temperature of the hot water from the heat source 100 is relatively low, the hot water from the heat source 100 is guided to the first tank 110 </ b> A of the heat supply unit 90 via the path 250. That is, the control device 70 controls the valve 254 to switch the substantial output destination of the hot water from the heat source 100 to the first tank 110 </ b> A of the heat supply unit 90. The hot water supplied to the first tank 110A via the path 250 is stored in the first tank 110A. The hot water stored in the first tank 110 </ b> A is used as a heat source when steam is generated using the heat pump 10.

  As described above, according to the present embodiment, only hot water having a temperature suitable for direct generation of steam using the decompression effect shown in FIGS. be able to. This system S3 has a high tolerance for the temperature fluctuation of the hot water from the heat source 100. This is advantageous for improving thermal energy efficiency.

  In this embodiment, when the output temperature of the hot water from the heat source 100 is extremely low, it is possible to adopt a form that can avoid the introduction of the hot water to the first tank 110A of the heat supply unit 90. For example, a branch path different from the path 250 through which water from the heat source 100 that is difficult to use heat can flow.

  In addition, it is also possible to employ | adopt the form which combined 2nd Embodiment and 3rd Embodiment.

  Next, a fourth embodiment will be described with reference to the drawings.

  FIG. 10 is a schematic diagram showing a steam generation system S4 according to the fourth embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 10, in the steam generation system S4, unlike the first and second embodiments, the heat supply unit 90 has a plurality of heat dissipation units, and the heat pump 10 has a plurality of heat absorption units. The configuration of the supply path 20 including the heat source 100 and the evaporation unit 22 is substantially the same as that of the first embodiment.

  In the present embodiment, the heat pump 10 includes four heat absorbing portions 11A, 11B, 11C, and 11D. The expansion unit 14 of the heat pump 10 includes four pressure reduction control valves 400A, 400B, 400C, and 400D. In other embodiments, the number of heat absorbers and pressure reduction control valves can be 2, 3, or 5 or more.

  The main path 15 of the heat pump 10 has branch paths 15A, 15B, 15C, and 15D that branch the flow of the working medium toward the heat absorbing portions 11A to 11D. Decompression control valves 400A to 400D are arranged on the branch paths 15A to 15D, respectively. The pressure reduction ratio of the pressure reduction control valve 400A is set to the lowest (low level). The pressure reduction ratio of the pressure reduction control valve 400B is set to the second lowest (medium / low level). The pressure reduction ratio increases in the order of the pressure reduction control valve 400B, the pressure reduction control valve 400C (medium / high level), and the pressure reduction control valve 400D (high level).

  As shown in FIG. 10, a sensor 128 that measures the temperature of the medium (hot water) from the tank 110 and, if necessary, the flow rate of the medium can be arranged in the supply path 111 or the heat dissipation path 129. In this case, the pressure reduction ratio of the pressure reduction control valves 400A to 400D can be controlled based on the measurement result of the sensor 128. It is also possible to arrange the sensor 128 between the stages of the heat radiating portions 91A to 91D.

  The heat absorption parts 11A to 11D are part of a parallel path (first parallel path) that is fluidly connected to the branch paths 15A to 15D via the pressure reduction control valves 400A to 400D. The main path 15 of the heat pump 10 further includes parallel paths (second parallel paths) 15E, 15F, 15G, and 15H that are fluidly connected to the heat absorbing portions 11A to 11D, respectively. In the regenerator 18, a part of the piping of the bypass path 17 and a part of the piping of the paths 15E to 15H are thermally connected. For example, both pipes are arranged in contact with or adjacent to each other. The paths 15E, 15F, 15G, and 15H are fluidly connected to the introduction paths 15J, 15K, 15L, and 15M, respectively. The compressor 12B and the first compressor 12A are fluidly connected to each other.

  In the present embodiment, the heat exchange span in the regenerator 18 in the path 15E (the heat exchange span in which heat from the working medium flowing in the bypass path 17 is transferred to the working medium flowing in the main path 15) is the shortest. The heat exchange span in the regenerator 18 of the path 15F is the second shortest. The span becomes longer in the order of the routes 15F, 15G, and 15H. If the temperature of the working medium flowing through the bypass path 17 is constant, the amount of heat (heat exchange amount) transmitted to the working medium flowing through the main path 15 (15E to 15H) increases as the heat exchange span increases.

  The heat supply unit 90 includes a tank 110, a pump 121, and a heat dissipation path 129. The heat radiation path 129 has four heat radiation portions 91A, 91B, 91C, 91D arranged in series. The heat radiating portion 91A is located on the most upstream side. The heat radiating portion 91A, the heat radiating portion 91B, the heat radiating portion 91C, and the heat radiating portion 91D are arranged in this order along the flow of the medium. The heat radiating portions 91A to 91D are thermally connected to the heat absorbing portions 11A to 11D, respectively.

  Hot water from the tank 47 of the evaporation unit 22 is stored in the tank 110 of the heat supply unit 90. The medium (hot water) from the tank 110 flows through the heat dissipation path 129. Heat from the medium flowing through the heat radiating portion 91A is transferred to the working medium flowing through the heat absorbing portion 11A. The medium that has radiated heat from the heat radiating portion 91A is introduced into the heat radiating portion 91B. Thereafter, the heat from the medium flowing through the heat radiating portion 91B, the heat radiating portion 91C, and the heat radiating portion 91D is transmitted to the working medium flowing through the heat absorbing portion 11B, the heat absorbing portion 11C, and the heat absorbing portion 11D, respectively. The temperature of the medium flowing through the heat radiating portion 91A is the highest. The temperature of the medium flowing through the heat radiating portion 91B is the second highest. The temperature of the medium decreases in the order of the heat radiating portion 91B, the heat radiating portion 91C, and the heat radiating portion 91D.

  The working medium flowing through the heat absorbing unit 11A that has received the heat from the heat radiating unit 91A has a higher temperature than the other heat absorbing units 11B to 11D. Moreover, the working medium from the pressure reduction control valve 400A set to a low pressure reduction ratio has a higher pressure than the other heat absorbing portions 11B to 11D. As shown in FIG. 10, the working medium from the heat absorption part 11A flowing through the path 15E is introduced into the fourth compression part 12D via the regenerator 18 and the path 15J. The working medium is compressed by one stage by the fourth compression unit 12D (see FIG. 3A).

  The working medium flowing through the heat absorbing unit 11B that has received heat from the heat radiating unit 91B has the next highest temperature after the heat absorbing unit 11A. Further, the working medium from the pressure reducing control valve 400B set at the medium to low level pressure reducing ratio has the next highest pressure after the heat absorbing portion 11B. As shown in FIG. 10, the working medium from the heat absorption part 11B flowing through the path 15F is introduced into the third compression part 12C via the regenerator 18 and the path 15K. The working medium is compressed in two stages by the third and fourth compression units 12C and 12D (see FIG. 3B).

  Similarly, the working medium from the heat absorption part 11C flowing through the path 15G is introduced into the second compression part 12B via the regenerator 18 and the path 15L. The working medium is compressed in three stages by the second, third, and fourth compression units 12B, 12C, and 12D (see FIG. 3C). Further, the working medium from the heat absorption part 11D flowing through the path 15H is introduced into the first compression part 12A via the regenerator 18 and the path 15M. The working medium is compressed in four stages by the first, second, third, and fourth compression units 12A, 12B, 12C, and 12D (see FIG. 3D).

  According to the present embodiment, the heat absorption units 11 </ b> A to 11 </ b> D of the heat pump 10 are supplied with different temperatures (hot water from the heat supply unit 90). That is, the medium (warm water) from the heat supply unit 90 performs high-temperature heat dissipation with respect to the heat absorption part 11A. The medium from the heat absorbing part 11A that has fallen in temperature due to heat radiation performs medium-high temperature heat radiation to the heat absorbing part 11B. Thereafter, the medium from the heat supply unit 90 performs medium / low temperature heat radiation to the heat absorption unit 11C and performs low temperature heat radiation to the heat absorption unit 11D. As a result, in the heat pump 10, the working medium flows through each path divided according to the supply temperature of the hot heat, whereby the heat radiation temperature from the heat pump 10 is kept at a predetermined level. That is, the working medium flows through each optimized route in accordance with a change in the amount of heat received from the outside by the heat pump 10. Therefore, this steam generation system S4 has a wide allowable temperature range of the heat supplied to the heat pump 10, and can preferably cope with fluctuations in the heat temperature.

  In each of the above embodiments, a heat storage unit can be provided for at least one of the tank and the heat exchange unit. The heat storage unit can have a heat storage material that stores cold or a heat storage material that stores warm heat according to the characteristics of the tank or the heat exchange unit. The material characteristics of the heat storage material are determined according to the specifications of each system. As the heat storage material, for example, a latent heat storage material that stores and radiates heat with a liquid-solid phase change can be applied. The latent heat storage material stores cold heat when solidifying and releases cold heat when melted. Examples of the latent heat storage material include hydrocarbons such as sodium acetate trihydrate and alkanes, wax systems (paraffin wax, microcrystalline wax, etc.), and the like. Alkanes can be appropriately adjusted in molecular size, for example, by constructing a substance in which hydrogen in the side chain is substituted with a hydroxyl group so as to achieve a target melting point. The latent heat storage material has a small volume change accompanying the phase change, and is advantageous for downsizing the apparatus. Other materials such as a sensible heat storage material and a chemical reaction heat storage material can also be used as the heat storage material. By utilizing heat storage using a heat storage material, it is possible to suppress peak power and average power consumption of the system, flexibly respond to steam / cold heat demand, and / or shorten the rise time of the steam generation process.

  The numerical value used in the above description is an example, and the present invention is not limited to this.

  The preferred embodiments of the present invention have been described above, but the present invention is not limited to these embodiments. The numerical value used in the above description is an example, and the present invention is not limited to this. Additions, omissions, substitutions, and other modifications can be made without departing from the spirit of the present invention. The present invention is not limited by the above description, but only by the appended claims.

It is the schematic which shows 1st Embodiment. It is a schematic diagram which shows the driving | running state (A1 phase) of a system. It is a schematic diagram which shows the driving | running state (A2 phase) of a system. It is a schematic diagram which shows the driving | running state (A3 phase) of a system. It is a schematic diagram which shows the driving | running state (transition phase) of a system. It is a schematic diagram which shows the driving | running state (A4 phase) of a system. It is a Ts diagram which shows an example of the state change of the working medium of a heat pump, and shows B1 phase. It is a Ts diagram which shows an example of the state change of the working medium of a heat pump, and shows B2 phase. It is a Ts diagram which shows an example of the state change of the working medium of a heat pump, and shows B3 phase. It is a Ts diagram which shows an example of the state change of the working medium of a heat pump, and shows B4 phase. It is a schematic diagram which shows another modification of a heat supply unit. It is a Ts diagram which shows an example of the state change of the water by a steam production | generation system. It is a figure which shows an example of the structure which controls the flow volume of the water in an evaporation pipe. It is the schematic which shows 2nd Embodiment. It is a schematic diagram which shows the operation state of a steam generation system. It is a schematic diagram which shows the operation state of a steam generation system. It is a schematic diagram which shows the operation state of a steam generation system. It is the schematic which shows 3rd Embodiment. It is the schematic which shows 4th Embodiment.

Explanation of symbols

  S1 to S4 ... Steam generation system, 10, 101 ... Heat pump, 11 ... Endothermic part, 11A to 11D ... Endothermic part (first parallel path, first mechanism), 12 ... Compression part, 13A-13F ... Radiation part, 14 ... Expansion part, 15 ... main path, 15A-15D ... branch path (first mechanism), 15E-15H ... second parallel path, 15J-15M ... introduction path (first mechanism), 17 ... bypass path, 18 ... regenerator , 20 ... Supply path (second path), 21 ... Heating section, 22 ... Evaporating section, 22a, 22b ... Evaporating unit, 23 ... Duct, 30 ... Compressor (decompression device), 41-45 ... Heat exchanger, 47 ... Tank (evaporation tank), 51A to 51D ... Evaporation pipe, 60, 60a, 60b, 71, 72, 128, 252 ... Sensor, 70 ... Control device, 90 ... Heat supply unit, 91 ... Heat radiation unit, 100 ... Heat source , 110, 110 , 110B ... tank, 111 ... supply path, 120 ... circulation path (third path), 129 ... heat dissipation path (third path), 121 ... pump, 122, 128 ... sensors (first mechanism, second mechanism), 125 , 126, 220, 225, 230, 235, 240, 254, 301 to 303 ... valves, 201 ... route (first route), 202 ... route, 203 ... tank (first storage tank), 210 ... route (second) Route), 250 ... route (fourth route), 400, 400A to 400D ... pressure reducing control valve (first mechanism), 501 to 504 ... valve (second mechanism), 521-524 ... valve (switching device, first mechanism) ).

Claims (5)

A heat pump through which the first medium flows, the heat pump having a heat absorption part, a compression part, a heat radiation part, and an expansion part;
A heat supply unit for supplying heat to the heat absorption part of the heat pump;
An evaporation tank that temporarily stores the second medium, and an evaporation section thermally connected to the heat dissipation section of the heat pump;
A decompression device that decompresses the internal space of the evaporation tank, and the decompression device that evaporates the second medium in the evaporation unit by at least one of the decompression of the internal space and heat transferred from the heat pump;
A heat source for outputting the heated second medium;
A first path through which the second medium from the heat source flows and in fluid communication with the evaporation tank;
A second path through which the second medium flows and in fluid communication with the heat supply unit;
A first sensor for measuring information corresponding to the temperature of the second medium in the evaporation tank;
A control device that controls at least the operation of the heat pump and the operation of the heat supply unit based on the measurement result of the first sensor;
Equipped with a,
The decompressor is
A compressor having a multistage compression structure;
The first based on the sensor measurement results, the steam generation system of the second medium, characterized in Rukoto to have a, and selectively direct changer to one of the stages of the compressor from the evaporator tank . A heat pump through which the first medium flows, the heat pump having a heat absorption part, a compression part, a heat radiation part, and an expansion part;
A heat supply unit for supplying heat to the heat absorption part of the heat pump;
An evaporation tank that temporarily stores the second medium, and an evaporation section thermally connected to the heat dissipation section of the heat pump;
A decompression device that decompresses the internal space of the evaporation tank; and the decompression device that evaporates the second medium in the evaporation unit by at least one of the decompression of the internal space and heat transferred from the heat pump
A heat source for outputting the heated second medium;
A first path through which the second medium from the heat source flows and in fluid communication with the evaporation tank;
A second path through which the second medium flows and in fluid communication with the heat supply unit;
A first sensor for measuring information corresponding to the temperature of the second medium in the evaporation tank;
A control device that controls at least the operation of the heat pump and the operation of the heat supply unit based on the measurement result of the first sensor;
With
The evaporation section includes a plurality of evaporation units each having the evaporation tank and the first sensor, and a substantial output destination of the second medium from the heat source is switched between the plurality of evaporation units. Steam generation system characterized by changing . A heat pump through which the first medium flows, the heat pump having a heat absorption part, a compression part, a heat radiation part, and an expansion part;
A heat supply unit for supplying heat to the heat absorption part of the heat pump;
An evaporation tank that temporarily stores the second medium, and an evaporation section thermally connected to the heat dissipation section of the heat pump;
A decompression device that decompresses the internal space of the evaporation tank, and the decompression device that evaporates the second medium in the evaporation unit by at least one of the decompression of the internal space and heat transferred from the heat pump;
A heat source for outputting the heated second medium;
A first path through which the second medium from the heat source flows and in fluid communication with the evaporation tank;
A second path through which the second medium flows and in fluid communication with the heat supply unit;
With
The heat supply unit is fluidly connected to the evaporation tank through the second path, and a second storage tank that temporarily stores the second medium, and the second medium from the second storage tank A third path through which the heat from the second medium flowing through the third path is transferred to the first medium flowing through the heat absorption part of the heat pump, and
A fourth path fluidly connected between the heat source and the second storage tank;
A second sensor for measuring information corresponding to an output temperature of the second medium from the heat source;
And a valve that switches a substantial output destination of the second medium from the heat source between the evaporation tank and the second storage tank based on a measurement result of the second sensor. Steam generation system. A heat pump through which the first medium flows, the heat pump having a heat absorption part, a compression part, a heat radiation part, and an expansion part;
A heat supply unit for supplying heat to the heat absorption part of the heat pump;
An evaporation tank that temporarily stores the second medium, and an evaporation section thermally connected to the heat dissipation section of the heat pump;
A decompression device that decompresses the internal space of the evaporation tank, and the decompression device that evaporates the second medium in the evaporation unit by at least one of the decompression of the internal space and heat transferred from the heat pump;
A heat source for outputting the heated second medium;
A first path through which the second medium from the heat source flows and in fluid communication with the evaporation tank;
A second path through which the second medium flows and in fluid communication with the heat supply unit;
The first medium for the decompression ratio in the expansion part of the heat pump and the compression part of the heat pump according to at least one of the temperature and flow rate of the heat medium from the heat supply unit supplied to the heat absorption part of the heat pump A first mechanism that controls at least one of the input position of
The first mechanism includes: a branch path that branches the flow of the second medium toward the heat absorption part; a decompression valve that is disposed in each of the branch paths as a part of the expansion part; and at least a part of the first mechanism Each of the first parallel path, which is disposed in the heat absorption unit and is fluidly connected to the branch path, and which is thermally connected to the heat supply unit in order, and the first parallel path. An introduction path fluidly connected to any stage of the compression section,
The heat pump includes a heating unit that transmits heat from the first medium to the second medium before flowing into the evaporation unit, and a part of the first medium from the compression unit bypasses the heating unit. And a regenerator in which heat from the first medium in the bypass path is transferred to the first medium between the heat absorption part and the compression part,
A steam generation system , further comprising a second parallel path disposed at least in part in the regenerator and fluidly connected to the first parallel path . A heat pump through which the first medium flows, the heat pump having a heat absorption part, a compression part, a heat radiation part, and an expansion part;
A heat supply unit for supplying heat to the heat absorption part of the heat pump;
An evaporation tank that temporarily stores the second medium, and an evaporation section thermally connected to the heat dissipation section of the heat pump;
A decompression device that decompresses the internal space of the evaporation tank; and the decompression device that evaporates the second medium in the evaporation unit by at least one of the decompression of the internal space and heat transferred from the heat pump
A heat source for outputting the heated second medium;
A first path through which the second medium from the heat source flows and in fluid communication with the evaporation tank;
A second path through which the second medium flows and in fluid communication with the heat supply unit;
With
The heat supply unit is fluidly connected to the evaporation tank through the second path, and a second storage tank that temporarily stores the second medium, and the second medium from the second storage tank A third path through which the heat from the second medium flowing through the third path is transferred to the first medium flowing through the heat absorption part of the heat pump, and
The second storage tank includes a first sub-tank and a second sub-tank in which the second medium is in a relationship of going back and forth through the third path,
The first sub-tank and the second medium supplied to the third path from one of the second sub-tank, the vapor generation system, characterized in Rukoto back to the other of the first sub-tank and the second sub-tank.

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