JP2008232534A - Vapor production system and vapor production method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vapor production system of high energy efficiency. <P>SOLUTION: This vapor production system comprises a heat pump 10 in which a first medium flows, and a first passage 20 in which a second medium flows. The first passage 20 has an evaporating portion 22 for evaporating the second medium by the heat transferred from the heat pump 10. This vapor production system further comprises a device 90 thermally connected with the heat pump 10 to allow a third medium which loses heat to the first medium flowing in the heat pump 10, and a first heat storage portion 110 having a first heat storage material 111 and thermally connected with the heat pump 10 and the device 90. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a steam generation system and a steam generation method.

As a steam generation system, a configuration in which fuel is burned in a boiler to heat a medium to be heated is generally known (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.

  It is an object of the present invention to provide an energy efficient steam generation system and method.

  According to the first aspect of the present invention, the heat pump through which the first medium flows and the first path through which the second medium flows, the first medium having an evaporation section in which the second medium evaporates by heat transferred from the heat pump. 1 path, a device thermally connected to the heat pump, the device for flowing a third medium deprived of heat by the first medium flowing through the heat pump, a first heat storage material and the heat pump, And a first heat storage unit thermally connected to the device.

  According to this steam generation system, high energy efficiency can be obtained by using a heat pump as compared with a boiler. Further, by using heat storage, it is possible to suppress peak power and average power consumption, flexibly respond to steam / cold heat demand, and / or shorten the rise time of the steam generation process.

  According to the second aspect of the present invention, the step of evaporating the second medium flowing through the first path by the warm heat from the operating heat pump, the step of storing the cold heat from the operating heat pump in the first heat storage unit, And a step of releasing exhaust heat from an operating device to the first heat storage unit when the heat pump is not in operation or in an operating state.

  According to the third aspect of the present invention, the step of storing cold heat from the operating heat pump in the first heat storage unit, the step of storing hot heat from the operating heat pump in the second heat storage unit, and the heat pump being non- A step of releasing waste heat from the operating device in operation or operation state to the first heat storage unit, and transmission from at least one of the second heat storage unit and the heat pump when the heat pump is not in operation or operation state Evaporating the second medium flowing through the first path by heat, and providing a steam generation method.

  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 (first medium) flows, a supply path 20 for a medium to be heated (second medium), a compressor 30, a control device 70, a refrigerator ( A vapor compression refrigerator) 90. 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 and the refrigerator 90 are devices that pump heat from a low-temperature object and apply heat to the high-temperature object by a cycle including evaporation, compression, condensation, and expansion processes. Heat pumps and refrigerators generally have 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 13E), and an expansion part 14, which are piping. Connected through.

  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. In this embodiment, the heat absorption part 11 of the heat pump 10 is thermally connected to the heat dissipation part 91 of the refrigerator 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 two-stage compression structure including a first compression unit 12A and a second compression unit 12B. 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 and 12B 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, and power is supplied to the shaft. The compression ratio (pressure ratio) of each compression part 12A, 12B is set according to the specification of the steam generation system S1.

  The heat radiating units 13A, 13B, and 13E have pipes through which the working medium compressed by the compressing unit 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, three heat radiating portions 13A, 13B, 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. 13 A of 1st thermal radiation parts are arrange | positioned between the compression parts 12A and 12B, and the 3rd thermal radiation part 13E is arrange | positioned in the downstream position of the 2nd thermal radiation part 13B.

  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.

  In this embodiment, the refrigerator 90 has the heat radiating part 91, the expansion | swelling part 92, the heat absorption part 93, and the compression part 94 similarly to the heat pump 10, These are connected via piping. In the refrigerator 90, the heat of the medium (refrigerant, etc.) flowing through the heat radiating unit 91 is absorbed by the heat absorbing unit 11 of the heat pump 10, and the cold heat from the heat absorbing unit 93 is supplied to external equipment.

  In the present embodiment, the number of compression stages in the compression unit 94 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 in the refrigerator 90, 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. The refrigerator 90 is not limited to a vapor compression refrigerator.

  In another embodiment, instead of or in addition to the refrigerator (vapor compression refrigerator) 90, an absorption refrigerator (a gas direct absorption absorption refrigerator, a vapor absorption refrigerator, etc.), an adsorption refrigerator, or the like is employed. can do. Alternatively, in place of or in addition to the refrigerator 90, various devices such as a refrigeration device and an internal combustion engine that flow a medium having waste energy (hot waste heat) can be employed. In an apparatus including a heat radiating part thermally connected to the heat absorbing part 11 of the heat pump 10, at least a part of exhaust heat (exhaust energy) is recovered by the heat pump 10.

  In this embodiment, the heat storage part 110 is provided with respect to the heat exchange part of the heat absorption part 11 of the heat pump 10 and the heat dissipation part 91 of the refrigerator 90. The heat storage unit 110 includes a heat storage material 111 that stores cold heat from the heat pump 10. The heat from the heat radiating portion 91 of the refrigerator 90 is transmitted to the heat storage material 111. The material characteristics of the heat storage material 111 are determined according to the specifications of the steam generation system S1.

  In the present embodiment, the heat storage material 111 includes a latent heat storage material that stores and radiates heat with a liquid-solid phase change. That is, the heat storage material 111 stores cold heat when solidifying and releases cold heat when melting. It is desirable that the melting point of the heat storage material 111 is equal to or higher than the temperature of the working medium in the heat absorbing part 11 of the heat pump 10 (for example, 30 to 90 ° C. or higher). Examples of the heat storage material 111 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. As the heat storage material 111, other substances such as a sensible heat storage material and a chemical reaction heat storage material may be used.

  2A to 2D are cross-sectional views illustrating structural examples of the heat exchanger provided with the heat storage unit 110. 2A, the heat exchanger has a structure in which the piping of the heat absorption unit 11 of the heat pump 10 and the piping of the heat radiation unit 91 of the refrigerator 90 are in direct contact within the housing 112. In addition, a heat storage material 111 is disposed in the housing 112 so as to cover the piping of the heat absorption unit 11 and the piping of the heat dissipation unit 91. The heat radiating part 91 is directly and thermally connected to the heat absorbing part 11.

  In FIG. 2B, the heat exchanger has a structure in which the piping of the heat absorption unit 11 of the heat pump 10 and the piping of the heat dissipation unit 91 of the refrigerator 90 are arranged in the housing 112. In addition, the heat storage material 111 is disposed in the internal space in the housing 112 including the gap between the pipe of the heat absorbing unit 11 and the pipe of the heat radiating unit 91 so as to cover both pipes. The heat absorbing part 11 is thermally connected to the heat radiating part 91 via the heat storage material 111. In order to promote heat transfer from the piping of the heat radiating unit 91 to the piping of the heat absorbing unit 11, the heat storage material 111 may include a heat conductive material.

  In FIG. 2C, the heat exchanger has a structure in which the piping of the heat radiating portion 91 of the refrigerator 90 is arranged inside the piping of the heat absorbing portion 11 of the heat pump 10 having a channel having an annular cross section. Further, a heat storage material 111 is arranged in a gap between the pipe of the heat absorbing unit 11 and the pipe of the heat radiating unit 91. The heat absorbing part 11 is thermally connected to the heat radiating part 91 via the heat storage material 111. A housing 112 surrounding the piping of the heat absorbing unit 11 is provided, and the heat storage material 111 can be disposed also in a gap between the housing 112 and the piping of the heat absorbing unit 11. In another embodiment, in the heat exchanger, the pipe of the heat absorbing unit 11 may be arranged inside the pipe of the heat radiating unit 91 having a channel having an annular cross section.

  In FIG. 2D, the heat exchanger has a structure in which a plurality of (two in this example) pipes of the heat radiating section 91 are arranged inside the pipe of the heat absorbing section 11 having a channel having an annular cross section. Each piping of the heat radiating portion 91 is in direct contact with the piping of the heat absorbing portion 11. In addition, a heat storage material 111 is disposed in the inner space of the pipe of the heat absorbing unit 11. The heat absorbing part 11 is directly thermally connected to the heat radiating part 91 or is thermally connected to the heat radiating part 91 via the heat storage material 111. A housing 112 surrounding the piping of the heat absorbing unit 11 is provided, and the heat storage material 111 can be disposed also in a gap between the housing 112 and the piping of the heat absorbing unit 11.

  In addition, the shape, arrangement | sequence, material, etc. of each piping can be set arbitrarily, and various forms are applicable about the heat exchanger in which the heat storage part 110 was provided. In this heat exchanger, a heat insulating material is arrange | positioned as needed. Each pipe is provided with fins as necessary.

  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 second heat radiating part 13B and the third 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 third 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 second heat radiating part 13 </ b> B bypasses the third heat radiating part 13 </ b> E and merges with the working medium from the third heat radiating part 13 </ b> E before the expansion part 14. The remaining working medium from the second heat radiating section 13B flows through the third heat radiating section 13E, and the working medium and 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 second heat radiating unit 13 </ b> B is hotter than the working medium from the heat absorbing unit 11. In the regenerator 18, the working medium from the second heat radiating unit 13 </ b> B 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 supply path 20 includes a heating unit 21, an evaporation unit 22, and a duct 23 that fluidly connects the evaporation unit 22 and the compressor 30.

  The heating unit 21 includes a pipe that is thermally connected to the third heat radiating unit 13E of the heat pump 10 and through which water from a supply source (not shown) flows. The 1st heat exchanger 41 is comprised including the heating part 21 and the 3rd thermal radiation part 13E. The first heat exchanger 41 can have a countercurrent heat exchange system in which a low-temperature fluid (water in the supply path 20) and a high-temperature fluid (working fluid in the heat pump 10) flow in opposition. 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 third heat radiation unit 13E are arranged in contact with or adjacent to each other. For example, the piping of the third heat radiating unit 13E can be disposed on the outer peripheral surface or inside of the piping of the heating unit 21. In the heating unit 21, the temperature of the water in the supply path 20 rises due to the heat transferred from the third heat radiating unit 13 </ b> E of the heat pump 10.

  The evaporation unit 22 includes a deaeration tank 49, a tank 47 for storing at least a liquid medium to be heated (water), and a circulation pipe (first circulation pipe 48A, first fluid) fluidly connected to the tank 47 as necessary. 2 circulation piping 48B). A fluid drive unit 49C is disposed between the deaeration tank 49 and the tank 47 as necessary. A pump 49A and a discharge pipe 49B are fluidly connected to the deaeration tank 49. A gas-liquid separator may be disposed inside the deaeration tank 49. In the deaeration tank 49, water from the heating unit 21 is degassed, and the gas is appropriately discharged to the outside (atmosphere) through the pump 49A and the discharge pipe 49B. The tank 47 is provided with a water supply port from the deaeration tank 49 (heating unit 21) and a steam discharge port. The tank 47 includes a level sensor 50 that measures the liquid level and a gas-liquid separator (not shown) as necessary.

  In this embodiment, each circulation pipe 48 </ b> A, 48 </ b> B is fluidly connected to one tank 47. That is, each inlet end and each outlet end of the circulation pipes 48 </ b> A and 48 </ b> B 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 valves 53A and 53B are, for example, regulators, flow rate control valves, or open / close valves. In the present embodiment, the evaporation pipes 51A and 51B are fluidly connected to the tank 47 independently of each other. The evaporation pipes 51 </ b> A and 51 </ b> B are arranged in parallel with the tank 47 and the supply path 20. At least one of the pumps 52A and 52B may be omitted by utilizing 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. The second and third heat exchangers 42 and 43 are countercurrent heat exchanges in which a low-temperature fluid (water in the evaporation pipes 51A and 51B) and a high-temperature fluid (working fluid in the heat pump 10) flow opposite to each other. You can have a scheme. Alternatively, the second and third heat exchangers 42 and 43 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 and third heat exchangers 42 and 43 can be employed. The pipes of the heat radiating portions 13A and 13B of the heat pump 10 and the evaporation pipes 51A and 51B are arranged in contact with or adjacent to each other. For example, the pipes of the heat radiating portions 13A and 13B of the heat pump 10 can be disposed on the outer peripheral surface and inside of the evaporation pipes 51A and 51B.

  In the evaporation unit 22, the water whose temperature has increased in the heating unit 21 is supplied to the tank 47 through the supply port, and the water is stored in the tank 47 and the circulation pipes 48 </ b> A and 48 </ b> B. The amount of 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 water supplied to the tank 47 is controlled based on the measurement result of the level sensor 50. The water in the evaporation pipes 51A and 51B is heated by the heat transferred from the first and second heat radiation portions 13A and 13B of the heat pump 10, and at least a part of the 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 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 two-stage compression structure including a first compression unit 30A and a second compression unit 30B. 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 and 30B 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 power is supplied to the shaft. The compression ratio (pressure ratio) of each compression unit 30A, 30B is set according to the specification 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. For example, the control valve (such as a flow rate control valve (not shown)) or the compressor 30 on the supply path 20 can be controlled so that the internal pressure of the tank 47 becomes a negative pressure (negative pressure) lower than the atmospheric pressure. it can. This control is performed based on a measurement result of a sensor (not shown) that measures the internal pressure of the tank 47, for example.

  The tank 47 and the heat pump 10 are designed (capacity design, capacity design, etc.) so that water evaporates with respect to the set value of the internal pressure of the tank 47. 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. By reducing the internal space of the tank 47, 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. For example, the input temperature (initial temperature) of water is about 20 ° C., and the output temperature of water from the evaporation unit 22 is about 90 to 160 ° C.

  Next, the basic operation of the steam generation system S1 will be described. Various operation methods of the steam generation system S1 using the heat storage unit 110 will be described later.

  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 third heat radiating part 13 </ b> E of the heat pump 10. Thereafter, in the second and third heat exchangers 42 and 43, the water undergoes a phase change and evaporates due to the heat transferred from the first and second heat radiating portions 13A and 13B. That is, sensible heat heating of water is performed in the first heat exchanger 41, and latent heat heating of water is performed in the second and third heat exchangers 42 and 43. The first heat exchanger 41 is in a form suitable for sensible heat exchange, and the second and third heat exchangers 42 and 43 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.

  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 radiation units 13 </ b> A to 13 </ b> C), and is compressed by the compressor 30 to have a relatively high pressure. 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. 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. 3 is a Ts diagram illustrating an example of a state change of water by the steam generation system S1. As shown in FIG. 3, the temperature of the water rises to near the boiling point in the first heat exchanger 41 (see FIG. 1), and then changes in phase in the second and third heat exchangers 42 and 43 while keeping the temperature constant. At this time, saturated steam d0 is generated in the state of pressure P0.

  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. By cooling the superheated steam e2 at the pressure P2 under a constant pressure, a relatively high-temperature saturated steam can be obtained (broken line a in FIG. 3). 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.

  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. 3). 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. 3). 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.

  Thus, in this embodiment, both saturated steam and superheated steam can be easily generated by three-stage sequential heating including two-stage heating by the heat pump 10 and heating by the compressor 30 shown in FIG. 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 steam generation system S1 is highly flexible with respect to the steam specifications.

  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.

  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 to third heat exchangers 41 to 43.

  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, and the temperature of the working medium in the main path 15 of the heat pump 10 is raised. 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.

  Further, in the present embodiment, the working medium in the bypass path 17 whose temperature has dropped in the regenerator 18 is the first heat exchanger 41 (the third heat radiating section 13E) that flows through the main path 15 of the heat pump 10 before the expansion section 14. ) From the working medium. As described above, the output temperature of the working medium from the first heat exchanger 41 is set to be relatively low. By reducing the input temperature of the working medium to the expansion unit 14, the liquid gas ratio of the working medium is optimized, and as a result, the heat absorption unit 11 has a heat source outside the cycle (the medium flowing through the heat radiation unit 91 of the refrigerator 90 and / or Alternatively, heat is effectively absorbed from the heat storage material 111) of the heat storage unit 110.

  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 of the heat radiating portion 13A 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. As a result, the compression efficiency of the compression unit 12 is improved and The power of the compressor can be 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) between the stages (the number of reheating 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. Moreover, effective use of heat is also achieved from the point of heating water that is a medium to be heated by using cooling of the heat radiation part 13A between the stages.

  In the present embodiment, since the supply path 20 includes a plurality of evaporation pipes 51A and 51B, 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 and 51B, heating of water with 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. When the plurality of evaporation pipes 51A and 51B are independent from each other, the differential pressure is small, and the increase in water transport power accompanying the expansion of the heat exchange area is suppressed. The fact that the evaporation tubes 51A and 51B are arranged in parallel facilitates the realization of a configuration in which the plurality of evaporation tubes 51A and 51B 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 and 51B, 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 and 13B. Reheating in the multistage compression unit 12 having the heat radiation units 13A and 13B is achieved by individually controlling the flow rate of water flowing through the plurality of evaporation pipes 51A and 51B corresponding to the heat radiation units 13A and 13B. The control is optimized.

  FIG. 4 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 evaporator tubes 51 </ b> B and the corresponding heat radiating portions 13 </ b> B can adopt the same configuration.

  Next, an operation method of the steam generation system S1 will be described. 5A, 5B, and 5C each schematically show an example of the operation mode.

  In FIG. 5A, the heat pump 10 and the steam generation unit (evaporation unit 22, compressor 30 and the like) are operated, and the refrigerator 90 is stopped. Steam is generated with the operation of the heat pump 10 and the steam generation unit. That is, the pumps 52A and 52B (see FIG. 1), the compressor 30, and the pump 37 of the circulation pipes 48A and 48B are driven. The valves 53A and 53B (see FIG. 1) of the circulation pipes 48A and 48B are open. Hot water in the tank 47 circulates through the circulation pipes 48A and 48B. Due to the suction action of the compressor 30, the internal space of the evaporator 22 is decompressed. The hot water in the evaporation pipes 51A and 51B is heated by the heat transferred from the heat pump 10. As a result, the water in the supply path 20 becomes steam at a relatively low pressure and low temperature, and then becomes steam at a relatively high pressure and high temperature by compression by the compressor 30.

  In FIG. 5A, the heat storage material 111 stores the cold energy from the heat pump 10 as the heat pump 10 is operated. That is, in the heat absorption part 11 of the heat pump 10, the working medium absorbs the heat of the heat storage material 111, and at least a part of the working medium evaporates. In the heat storage unit 110, the heat storage material 111 changes from a liquid phase to a solid phase. In the heat storage unit 110, the solidification latent heat of the heat storage material 111 is stored as the heat storage material 111 is solidified. The control device 70 comprehensively controls the system.

  In FIG. 5B, the heat pump 10 and the steam generation unit are stopped, and the refrigerator 90 is operated. With the operation of the refrigerator 90, the heat storage material 111 releases cold heat. That is, the heat from the heat radiating unit 91 of the refrigerator 90 is transmitted to the heat storage material 111. In the heat storage unit 110, the heat storage material 111 that has absorbed the heat from the refrigerator 90 changes from a solid phase to a liquid phase. In the refrigerator 90, the heat from the heat radiating unit 91 is collected in the heat storage material 111, and the cold from the heat absorbing unit 93 is supplied to the outside.

  In FIG. 5C, the heat pump 10, the steam generation unit (evaporation unit 22, compressor 30 and the like), and the refrigerator 90 are operated. Steam is generated with the operation of the heat pump 10 and the steam generation unit. Further, with the operation of the refrigerator 90, cold heat from the refrigerator 90 is supplied to the outside. When there is more energy related to steam generation of the heat pump 10 than energy related to cold supply of the refrigerator 90, cold energy is stored in the heat storage unit 110 based on the energy difference.

  Thus, in this embodiment, the steam and cold supply can be individually supplied by the combination of the heat pump 10 and the refrigerator 90. Moreover, since thermal energy is buffered in the heat storage part 110 provided in the heat exchange part of the heat pump 10 and the refrigerator 90, inconsistency of both operation timing is permitted. Therefore, it is possible to easily adjust the timing and amount of steam generation and cold supply according to the steam demand and / or the cold demand. That is, the steam generation system S1 has high flexibility and controllability for steam supply and cold supply.

  In addition, the cold storage heat by the heat storage material 111 is advantageous in suppressing initial cost as compared with heat storage using a battery, and can be expected to have a heat storage efficiency equal to or higher than that. It is also possible to use a battery as a power complement.

  In the present embodiment, the hot exhaust heat of the refrigerator 90 is used as the low temperature heat source of the heat pump 10. This is advantageous in reducing the temperature difference between the low-temperature heat source and the high-temperature heat source of the heat pump 10 and thus improving the COP of the heat pump 10. In this embodiment, the supply temperature (exhaust heat temperature) of the working medium of the refrigerator 90 to the heat absorption unit 11 of the heat pump 10 is the initial temperature of water for steam generation (the supply temperature of water to the heating unit 21 of the heat pump 10). ) Is set higher than For example, the exhaust heat temperature of the refrigerator 90 is 30 ° C or higher and lower than 40 ° C, 40 ° C or higher and lower than 50 ° C, 50 ° C or higher and lower than 60 ° C, 60 ° C or higher and lower than 70 ° C, 70 ° C or higher and lower than 80 ° C, 80 ° C or higher and lower than 90 ° C. It is less than 90 ° C or 90 ° C or more.

  By setting the temperature of the low-temperature heat source of the heat pump 10 higher than that of the atmosphere, the heat pump 10 can be made compact and / or simplified based on the reduction of the heat source temperature difference. In this case, for example, the number of stages of the compression unit 12 can be reduced, and the heat exchangers in the heating unit 21 and the regenerator 18 can be made compact compared to a mode in which the atmosphere is a low-temperature heat source. When the demand temperature of steam is relatively low, the heat source temperature difference of the heat pump 10 can be further reduced by lowering the set temperature of the high-temperature heat source. It is also possible to adopt a configuration in which (compressors 30A, 30B, etc.) are deleted according to the steam demand temperature.

  Such a steam generation system S1 is preferably used, for example, in a food manufacturing process in which heating and cooling are repeated. The steam generation system S1 can be preferably used not only for the food production process but also for various facilities and processes that generate steam demand and cold demand.

  In another embodiment, as described above, the number of stages of the compression unit 94 of the refrigerator 90 may be a plurality of stages. Further, a configuration in which a plurality of refrigerators 90 are thermally connected to one heat pump 10 may be employed.

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

  FIG. 6 is a schematic view showing a steam generation system 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. 6, the steam generation system S <b> 2 is different from the first embodiment in that another heat storage unit 100 is provided in the heat exchange unit between the heat radiation units 13 </ b> A and 13 </ b> B of the heat pump 10 and the evaporation unit 22 of the supply path 20. ing.

  In the present embodiment, the heat storage unit 100 is provided for the second and third heat exchangers 42 and 43. The heat storage unit 100 includes a heat storage material 101 that stores heat transmitted from the heat pump 10. The heat of the heat storage material 101 is transmitted to the evaporation tubes 51A and 51B. The material characteristics of the heat storage material 101 are determined according to the specifications of the steam generation system S2. In the present embodiment, the heat storage material 101 includes a latent heat storage material that stores and radiates heat with a liquid-solid phase change. That is, the heat storage material 101 stores heat when melting and dissipates heat when solidified.

  In this embodiment, the melting point of the heat storage material 101 is set higher than the melting point of the heat storage material 111. It is desirable that the melting point of the heat storage material 101 is equal to or higher than the evaporation temperature of water in the evaporation tubes 51A and 51B (for example, 90 to 150 ° C.). Examples of the heat storage material 101 include hydrocarbons such as erythritol and alkanes, wax systems (paraffin wax, microcrystalline wax, etc.), and the like. Erythritol has a melting point of about 117 to 120 ° C. and has a relatively high heat storage amount (heat storage efficiency) per unit mass. 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. As the heat storage material 101, other substances such as a sensible heat storage material and a chemical reaction heat storage material may be used.

  7A and 7B are configuration examples of the heat storage unit 100. In FIG. 7A, one heat storage unit 100 is provided for the heat exchangers 42 and 43. In FIG. 7B, independent heat storage units 100 are provided for the heat exchangers 42 and 43.

  As a structural example of the heat exchanger provided with the heat storage unit 100, the same configuration as that of FIGS. Moreover, the structure by which the heat storage part 100 and the heat storage part 110 were provided integrally can also be employ | adopted.

  FIG. 8 is a cross-sectional view showing a structural example of a heat exchanger in which the heat storage unit 100 and the heat storage unit 110 are integrally provided. In FIG. 8, the heat exchanger has a structure in which the heat storage unit 100 is disposed inside the heat storage unit 110. On the center side of the heat exchanger, the pipes of the heat radiating portions 13A and 13B of the heat pump 10 are arranged inside the evaporation pipes 51A and 51B having flow passages having an annular cross section. Moreover, the heat storage material 101 is arrange | positioned in the clearance gap between evaporation pipe 51A, 51B and piping of the thermal radiation part 13A, 13B. Outside the heat exchanger, a pipe of the heat radiating portion 91 of the refrigerator 90 having the annular cross-section flow path is disposed inside the heat absorption section 11 of the heat pump 10 having the annular cross-section flow path. Further, a heat storage material 111 is arranged in a gap between the pipe of the heat absorbing unit 11 and the pipe of the heat radiating unit 91. The heat insulating material 120 can be disposed between the piping of the heat radiating portion 91 and the evaporation tubes 51A and 51B. A housing surrounding the piping of the heat absorbing unit 11 is provided, and the heat storage material 111 can also be disposed in a gap between the housing and the piping of the heat absorbing unit 11. The evaporation pipes 51A and 51B are thermally connected to the heat radiating portions 13A and 13B via the heat storage material 101. The heat absorbing part 11 is thermally connected to the heat radiating part 91 via the heat storage material 111. As in this structure, heat loss can be reduced by covering a pipe having a high fluid temperature with a pipe having a low fluid temperature.

  The volume ratio between the heat storage material 101 of the heat storage unit 100 and the heat storage material 111 of the heat storage unit 110 can be determined based on, for example, the volume ratio between the heat pump 10 and the refrigerator 90. In addition, the shape, arrangement | sequence, material, etc. of each piping can be set arbitrarily, and various forms are applicable about the heat exchanger in which the heat storage part 100 was provided. In this heat exchanger, a heat insulating material is arrange | positioned as needed. Each pipe is provided with fins as necessary.

  Next, an operation method of the steam generation system S2 will be described with reference to FIGS. 6, 9A, and 9B. 9A and 9B schematically show examples of operation modes.

  In FIG. 9A, the heat pump 10 is operated, and the steam generation unit (evaporation unit 22, compressor 30 and the like) and the refrigerator 90 are stopped. As the heat pump 10 is operated, the heat storage material 101 stores the heat from the heat pump 10. The operation of the heat pump 10 can be, for example, a time zone (for example, nighttime) in which the demand for steam is low and the power rate is set low. In the second and third heat exchangers 42 and 43, heat from the first and second heat radiating portions 13 </ b> A and 13 </ b> B of the heat pump 10 is stored in the heat storage material 101. That is, the heat storage material 101 is heated by the first and second heat radiation units 13A and 13B, and the heat storage material 101 changes from a solid phase to a liquid phase. In the heat storage unit 100, the latent heat of fusion of the heat storage material 101 is stored with the liquefaction of the heat storage material 101. The control device 70 comprehensively controls the system.

  Further, with the operation of the heat pump 10, the heat storage material 111 stores the cold energy from the heat pump 10. That is, in the heat absorption part 11 of the heat pump 10, the working medium absorbs the heat of the heat storage material 111, and at least a part of the working medium evaporates. In the heat storage unit 110, the heat storage material 111 changes from a liquid phase to a solid phase. In the heat storage unit 110, the solidification latent heat of the heat storage material 111 is stored as the heat storage material 111 is solidified.

  In addition, in the heating unit 21 (first heat exchanger 41) of the supply path 20, the temperature of water from a supply source (not shown) rises due to the heat transferred from the third heat radiating unit 13E of the heat pump 10 (for example, about 90 ° C). The tank 47 stores hot water from the heating unit 21. The capacity of the tank 47 is set corresponding to the amount of steam consumed in the daytime, for example. The heat storage capacity of the heat storage material 101 corresponds to the capacity of the tank 47. The temperature of the heat storage material 101 is higher than the hot water in the tank 47, and is, for example, 100 to 150 ° C.

  In this heat storage process, water may or may not exist in the evaporation pipes 51A and 51B. Treatment for preventing boiling of water in the evaporating unit 22 is performed as necessary. For example, at least the compressor 30 and the pump 37 are stopped. Along with the supply of hot water from the heating unit 21, the internal pressure of the evaporation unit 22 rises and water evaporation is suppressed. When the valves 53A and 53B of the circulation pipes 48A and 48B have a pressure adjusting function, the internal pressure of the evaporator 22 can be set by the valves 53A and 53B. Alternatively, the valves 53A and 53B are closed. The pumps 52 </ b> A and 52 </ b> B may be driven to apply a predetermined pressure to the circulation pipes 48 </ b> A and 48 </ b> B of the evaporation unit 22.

  In FIG. 9A, when a predetermined time elapses, warm water is stored in the tank 47, warm heat is stored in the heat storage material 101, and cold heat is stored in the heat storage material 111. For example, the end of the heat storage process is determined based on the time, the processing time, and / or the amount of water stored in the tank 47. You may repeat at least one part of a thermal storage process as needed.

  In FIG. 9B, the heat pump 10 is stopped, and the steam generation unit (evaporation unit 22, compressor 30 and the like) and the refrigerator 90 are operated. For example, this mode is executed in the daytime.

  During the operation of the steam generation unit, the pumps 52A and 52B (see FIG. 1) of the circulation pipes 48A and 48B, the compressor 30, the pump 37, and the like are driven. The valves 53A and 53B (see FIG. 1) of the circulation pipes 48A and 48B are open. Hot water in the tank 47 circulates through the circulation pipes 48A and 48B. Due to the suction action of the compressor 30, the internal space of the evaporator 22 is decompressed. The hot water in the evaporation pipes 51A and 51B is heated by the heat transferred from the heat pump 10. As a result, the water in the supply path 20 becomes steam at a relatively low pressure and low temperature, and then becomes steam at a relatively high pressure and high temperature by compression by the compressor 30.

  Moreover, with the operation of the refrigerator 90, the heat storage material 111 releases cold. That is, the heat from the heat radiating unit 91 of the refrigerator 90 is transmitted to the heat storage material 111. In the heat storage unit 110, the heat storage material 111 that has absorbed the heat from the refrigerator 90 changes from a solid phase to a liquid phase. In the refrigerator 90, the heat from the heat radiating unit 91 is collected in the heat storage material 111, and the cold from the heat absorbing unit 93 is supplied to the outside.

  In FIG. 9B, when a predetermined time elapses, the hot water in the tank 47 decreases, and the heat storage amount of the heat storage material 101 and the heat storage material 111 decreases. Again at night, the heat storage process shown in FIG. 9A is performed.

  As described above, in this embodiment, for example, the heat pump 10 is operated at night when the electricity rate is low, and a steam generation unit (evaporation unit 22, compressor 30 and the like) and a refrigerator in the daytime when there is a demand for steam and / or cold energy. Run 90. That is, by using heat storage, power consumption in the steam generation system S2 is distributed between nighttime and daytime. As a result, the peak power and average power consumption of the steam generation system S2 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).

  Further, the use of heat storage makes it possible to easily adjust the timing and amount of steam generation according to the steam demand. That is, the steam generation system S2 has high flexibility and controllability for the steam supply. In the heat storage process, heat is stored at two locations, the heat storage material 101 and the tank 47. The hot water is stored in the tank 47, which is advantageous for shortening the rise time of the steam generation process.

  In the present embodiment, a heat storage material can be disposed in the first heat exchanger 41. In this case, in the heat storage process, heat is stored in the heat storage material of the first heat exchanger 41 instead of the hot water storage in the tank 47. By avoiding the supply of water to the evaporation unit 22, it is not necessary to take measures to prevent the water in the evaporation unit 22 from boiling in the heat storage process. It is also possible to arrange the heat storage material in other places such as the regenerator 18.

  The heat storage heat by the heat storage material 101 and hot water is advantageous in suppressing initial cost compared to heat storage using a battery, and can be expected to have a heat storage efficiency equal to or higher than that. It is also possible to use a battery as a power complement. For example, the water in the tank 47 can be complementarily heated by the energy stored in the battery.

  In this mode, if there is no problem in terms of equipment, when the hot water in the tank 47 and the heat of the heat storage material 101 are used up, the heat pump 10 and the evaporation unit 22 can be operated to meet further steam demand. Is possible.

  In the present embodiment, operation modes other than those shown in FIGS. 9A and 9B can be employed.

  In one operation mode, the heat pump 10 is operated substantially continuously. When there is no steam demand, heat is stored in the heat storage materials 101 and 111, and when there is steam demand, steam is generated using the heat pump 10 and / or the heat storage material 101. Further, when there is a cold demand, cold heat from the refrigerator 90 is supplied to an external facility using the heat storage material 111.

  In this operation mode, the heat pump 10 is operated substantially continuously, and heat is stored in the heat storage material 101 when there is no or little steam demand. When there is a demand for steam, steam is generated using heat stored in the heat storage material 101 in addition to direct heat transfer from the heat pump 10. That is, when the heat of the heat pump 10 is used for steam generation, the heat storage material 101 and the tank 47 play the role of heat assistance and buffer. By optimizing the heat storage capacity according to the steam demand, in particular, the peak power and average power consumption of the heat pump 10 can be kept low. This is advantageous in reducing the size and cost of the heat pump 10. It is the same as the steam generation for the cold supply from the refrigerator 90.

  In another operation mode, particularly during the initial operation of the steam generation system S2, steam is generated using heat storage. During normal operation of the steam generation system S2, the heat pump 10 and the steam generation unit (evaporation unit 22, compressor 30, etc.) are operated to generate steam. Moreover, with the operation of the refrigerator 90, the cold heat from the refrigerator 90 is supplied to external equipment. At the end of the steam generation process, the heat pump 10 is in an operating state, and the steam generation unit (evaporation unit 22, compressor 30 and the like) and the refrigerator 90 are stopped. Heat is stored in the heat storage materials 101 and 111 and hot water is stored in the tank 47. Thereafter, the heat pump 10 is also stopped.

  During the next initial operation of the steam generation system S2, steam is generated using the heat of the heat storage material 101. Thereafter, when the warm-up of the steam generation system S2 (such as the heat radiating portions 13A, 13B, and 13E of the heat pump 10) is completed, the normal operation of the steam generation system S1 described above is executed. It is the same as the steam generation for the cold supply from the refrigerator 90.

  In this operation mode, the time required to warm up the steam generation system S2 can be reduced. That is, it is advantageous for shortening the rise time of the steam generation process and / or the cold supply process. In this operation mode, the heat storage capacity may be the amount consumed during initial operation. Compared with the other operation modes described above, the apparatus cost can be reduced.

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

  FIG. 10 is a schematic view showing a steam generation system 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. 10, in the steam generation system S3, unlike the above embodiment, the compression unit 12 of the heat pump 10 includes four compression chambers 12A, 12B, 12C, and 12D. The tank for storing water in the supply path 20 has a plurality of individual tanks 47A to 47D corresponding to the plurality of evaporation pipes 51A to 51D. The configuration of the refrigerator 90 is the same as that of the above embodiment.

  The supply path 20 includes a heating unit 21, an evaporation unit 22, and a duct 23 that fluidly connects the evaporation unit 22 and the compressor 30. The evaporation unit 22 includes a deaeration tank 49 and tanks (first tank 47A, second tank 47B, third tank 47C, fourth tank 47D) for storing at least a liquid medium to be heated (water) as necessary. And circulation pipes (first circulation pipe 48A, second circulation pipe 48B, third circulation pipe 48C, and fourth circulation pipe 48D) fluidly connected to the tanks 47A to 47D. A fluid drive unit 49C is disposed between the deaeration tank 49 and the tanks (47A to 47D) as necessary. Each of the tanks 47A to 47D is provided with a water supply port from the heating unit 21 (deaeration tank 49) and a steam discharge port. The tanks 47A to 47D include level sensors 50A to 50D that measure the liquid level and a gas-liquid separator (not shown) as necessary.

  In the present embodiment, a first circulation pipe 48A having an evaporation pipe 51A is fluidly connected to the first tank 47A. That is, each inlet end and each outlet end of the first circulation pipe 48A are fluidly connected to the first tank 47A. Similarly, a second circulation pipe 48B having an evaporation pipe 51B is fluidly connected to the second tank 47B. A third circulation pipe 48C having an evaporation pipe 51C is fluidly connected to the third tank 47C, and a fourth circulation pipe 48D having an evaporation pipe 51D is fluidly connected to the fourth tank 47D. The evaporation pipe 51 </ b> A is thermally connected to the first heat radiating part 13 </ b> A of the heat pump 10. Similarly, the evaporation tubes 51B, 51C, and 51D are thermally connected to the second heat radiating portion 13B, the third heat radiating portion 13C, and the fourth heat radiating portion 13D of the heat pump 10, respectively. The number of tanks and circulation pipes (evaporation pipes) is set according to the specification of the steam generation system S2, and is 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. In the present embodiment, each pair of the tanks 47 </ b> A to 47 </ b> D and the evaporation pipes 51 </ b> A to 51 </ b> D is arranged in parallel with the supply path 20.

  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.

  In this embodiment, the heat storage part 100 is provided with respect to the 2nd-5th heat exchangers 42-45. The heat storage unit 100 includes a heat storage material 101 that stores heat transmitted from the heat pump 10. The heat of the heat storage material 101 is transmitted to the evaporation tubes 51A to 51D. The material characteristics of the heat storage material 101 are determined according to the specifications of the steam generation system S1. In the present embodiment, the heat storage material 101 includes a latent heat storage material that stores and radiates heat with a liquid-solid phase change, as in the first embodiment. As shown in FIGS. 2A to 2D, 7A to 7B, and 8, various configurations can be applied to the configuration of the heat storage unit 100.

  In the evaporation unit 22, the water whose temperature has been increased in the heating unit 21 is branched and supplied to the tanks 47A to 47D, and water is stored in the tanks 47A to 47D and the circulation pipes 48A to 48D. The supply path 20 includes valves 80A to 80D that control the amount of water supplied to the tanks 47A to 47D. The amount of water supplied to each of the tanks 47A to 47D is controlled via the valves 80A to 80D so that the liquid levels in the tanks 47A to 47D are within a predetermined range. For example, the amount of water supplied to each of the tanks 47A to 47D is controlled based on the measurement results of the level sensors 50A to 50D. The water in the evaporation pipes 51A to 51D is heated by heat transfer from the first to fourth heat radiation portions 13A to 13D of the heat pump 10, and at least a part of the water is evaporated. Each tank 47 </ b> A to 47 </ b> D is fluidly connected to the compressor 30 via the duct 23. The internal spaces of the tanks 47 </ b> A to 47 </ b> D are sucked by the compressor 30 through the discharge ports and the ducts 23 of the tanks 47 </ b> A to 47 </ b> D.

  In the compressor 30 (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. In the case where the compressor 30 is a multistage type, the nozzle 35 may be disposed between the stages of the compressor 30. A pipe in which the nozzle 35 and the liquid phase position of at least one of the tanks 47 </ b> A to 47 </ b> D are fluidly connected via the pipe 36 can be configured. In this piping configuration, the liquid in the at least one tank 47 </ b> A to 47 </ b> D 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.

  Also in this embodiment, the water in the supply path 20 becomes steam having a relatively low pressure and low temperature due to heat transfer from the heat pump 10 (heat radiation units 13A to 13E), as in the above-described embodiment. Compression results in relatively high pressure and high temperature steam. In addition, by using heat storage using the heat storage materials 101 and 111 and the tanks 47A to 47D, the peak power and average power consumption of the steam generation system S3 can be suppressed, flexible response to steam / cooling demand, and / or steam. The rise time of the generation process can be shortened. The steam from the steam generation system S3 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. In this embodiment, by having a plurality of individual tanks 47A to 47D, flexibility with respect to fluctuations in steam demand is high.

Next, a fourth embodiment of the present invention will be described with reference to the drawings.
FIG. 11 is a schematic view showing a steam generation system 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. 11, the steam generation system S4 has a plurality of individual tanks 47A and 47B in which the internal pressure is individually set as a tank for storing water in the supply path 20, unlike the above embodiment. The steam generation system S4 includes a heat pump 10 through which a working medium (first medium) flows, a supply path 20 for a medium to be heated (second medium), and compressors 30 and 31.

  In this embodiment, the heat pump 10 has the heat absorption part 11, the compression part 12, heat dissipation part 13A-13D, and the expansion part 14, and these are connected through piping.

  In the present embodiment, the compression unit 12 has a structure that compresses the working medium in a single stage. In other embodiments described below, the compression unit 12 may have a structure that compresses the working medium in a plurality of stages. The compression unit 12 includes a compressor suitable for compressing a working medium among various compressors such as an axial flow compressor, a centrifugal compressor, a reciprocating compressor, and a rotary compressor. Power is supplied to the compressor. The compression ratio (pressure ratio) of the compression unit 12 is set according to the specification of the steam generation system S4.

  The heat radiating units 13A to 13D have pipes through which the working medium compressed by the compressing unit 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, four heat radiating portions 13A to 13D are arranged in series along the flow direction of the working medium. A heat radiating portion 13A, a heat radiating portion 13B, a heat radiating portion 13C, and a heat radiating portion 13D are arranged in that order along the flow direction of the working medium. The number of heat radiation units is set according to the specification of the steam generation system S3, and is 3, 4, 5, 6, 7, 8, 9, 10, or 11 or more.

  In the present embodiment, the supply path 20 fluidly connects the first and second heating units 21A and 21B, the first and second evaporation units 22A and 22B, the evaporation units 22A and 22B, and the compressors 30 and 31. Ducts 23A and 23B connected to the. In the present embodiment, the supply path 20 includes a branch section 24A, a branch path 25A that guides water from the branch section 24A to the first evaporator 22A, and a branch path that guides water from the branch section 24A to the second evaporator 22B. 25B.

  21 A of 1st heating parts are arrange | positioned adjacent to the thermal radiation part 13D of the heat pump 10, and contain the piping through which the water from a supply source (not shown) flows. The 1st heat exchanger 41 is comprised including 21 A of 1st heating parts, and the thermal radiation part 13D. In the first heating unit 21A, the temperature of the water in the supply path 20 rises due to heat transfer from the heat radiating unit 13D of the heat pump 10.

  The second heating unit 21B is disposed on the branch path 25B. The second heating unit 21B includes a pipe disposed adjacent to the heat dissipation unit 13B of the heat pump 10 and through which water from the first heating unit 21A flows. The 2nd heat exchanger 42 is comprised including the 2nd heating part 21B and the thermal radiation part 13B. In the second heating unit 21B, the temperature of the water in the branch path 25B rises due to heat transfer from the heat radiating unit 13B of the heat pump 10.

  The first and second heat exchangers 41 and 42 employ a counter-current heat exchange method in which a low-temperature fluid (water in the supply path 20) and a high-temperature fluid (working fluid in the heat pump 10) face each other. Can have. The first and second heat exchangers 41 and 42 may have a parallel flow type heat exchange system in which a high-temperature fluid and a low-temperature fluid flow in parallel. As the heat exchange structure of the first and second heat exchangers 41 and 42, various known ones can be adopted. For example, the piping of the heat radiating part 13D or the heat radiating part 13B of the heat pump 10 can be disposed on the outer peripheral surface and / or the inside of the pipe of the first heating part 21A or the second heating part 21B.

  In this embodiment, the pump 26 is arrange | positioned between the branch part 24A and the 2nd heating part 21B in the branch path 25B. The amount of water per unit time flowing through the branch path 25A and the branch path 25B (the amount of water distributed to the evaporators 22A and 22B) is controlled by the pump 26 and / or a flow rate control device (not shown) (not shown). . The arrangement position of the pump 26 is not limited between the branch part 24A and the second heating part 21B.

  The first evaporation section 22A includes a first tank 47A that stores at least a liquid medium to be heated (water), and a first circulation pipe 48A that is fluidly connected to the first tank 47A. That is, the inlet end and the outlet end of the first circulation pipe 48A are fluidly connected to the first tank 47A. The first tank 47A is provided with a water supply port from the first heating unit 21A and a steam discharge port. The first tank 47A includes a level sensor 50A for measuring the liquid level and a gas-liquid separator (not shown) as necessary. 48 A of 1st circulation piping has the evaporation pipe | tube 51A arrange | positioned adjacent to the thermal radiation part 13C of the heat pump 10, and the pump 52A as needed.

  Similar to the first evaporator 22A, the second evaporator 22B has a second tank 47B for storing at least a liquid medium to be heated (water), and a second circulation pipe 48B fluidly connected to the second tank 47B. And have. That is, the inlet end and the outlet end of the second circulation pipe 48B are fluidly connected to the second tank 47B. The second tank 47B is provided with a water supply port from the second heating unit 21B and a steam discharge port. The second tank 47B includes a level sensor 50B that measures the liquid level and a gas-liquid separator (not shown) as necessary. The 2nd circulation piping 48B has the evaporation pipe 51B arrange | positioned adjacent to the thermal radiation part 13A of the heat pump 10, and the pump 52B as needed.

  In the present embodiment, the first evaporator 22A (first tank 47A, evaporation pipe 51A) and the second evaporator 22B (second tank 47B, evaporation pipe 51B) are substantially parallel to the supply path 20. Be placed. As described above, the second evaporator 22B is the upstream position and the first evaporator 22A is the downstream position with respect to the flow direction of the working medium in the heat pump 10. At least one of the pumps 52A and 52B may be omitted by using heat convection of the medium to be heated (water) and / or differential pressure.

  A third heat exchanger 43 is configured including the evaporation pipe 51A and the heat radiating portion 13C. Similarly, the 4th heat exchanger 44 is comprised including the evaporation pipe | tube 51B and the thermal radiation part 13A. The third and fourth heat exchangers 43 and 44 are countercurrent heat exchanges in which a low-temperature fluid (water in the evaporation pipes 51A and 51B) and a high-temperature fluid (working fluid in the heat pump 10) flow opposite to each other. You can have a scheme. The third and fourth heat exchangers 43 and 44 may have a parallel flow type heat exchange method in which a high-temperature fluid and a low-temperature fluid flow in parallel. Various known heat exchange structures can be employed for the third and fourth heat exchangers 43 and 44. For example, the pipes of the heat radiating portions 13C and 13A of the heat pump 10 can be disposed on the outer peripheral surface and / or the inside of the evaporation pipes 51A and 51B.

  In the present embodiment, the heat storage unit 100 is provided for the third heat exchanger 43 and the fourth heat exchanger 44. The heat storage unit 100 includes a heat storage material 101 that stores heat transmitted from the heat pump 10. The heat of the heat storage material 101 is transmitted to the evaporation tubes 51A and 51B. The material characteristics of the heat storage material 101 are determined according to the specifications of the steam generation system S3. In the present embodiment, the heat storage material 101 includes a latent heat storage material that stores and dissipates heat with a liquid-solid phase change, as in the above embodiment. As shown in FIGS. 2A to 2D, 7A to 7B, and 8, various configurations can be applied to the configuration of the heat storage unit 100.

  In the first evaporation unit 22A, the water whose temperature has increased in the first heating unit 21A is supplied to the first tank 47A through the supply port, and the water is stored in the first tank 47A and the first circulation pipe 48A. The amount of water supplied to the first tank 47A is controlled so that the liquid level in the first tank 47A is within a predetermined range. For example, the amount of water supplied to the first tank 47A is controlled based on the measurement result of the level sensor 50A. The water in the evaporation pipe 51A is heated by heat transfer from the heat radiating portion 13C of the heat pump 10, and at least a part of the water evaporates. The first tank 47A is fluidly connected to the compressor 30 via the duct 23A. The internal space of the first tank 47A is sucked by the compressor 30 through the discharge port of the first tank 47A and the duct 23A. The steam in the first tank 47A flows toward the compressor 30 in the duct 23A.

  In the second evaporation section 22B, the water whose temperature has increased in the first and second heating sections 21A, 21B is supplied to the second tank 47B via the supply port, and water is supplied into the second tank 47B and the second circulation pipe 48B. Is stored. The amount of water supplied to the second tank 47B is controlled so that the liquid level in the second tank 47B is within a predetermined range. For example, the amount of water supplied to the second tank 47B is controlled based on the measurement result of the level sensor 50B.

  In this embodiment, the state (pressure etc.) of a working medium differs between the thermal radiation parts 13A and 13C. The heat balance control can be improved by individually controlling the flow rate per unit time of the water flowing through the evaporation pipes 51A and 51B corresponding to the heat radiation portions 13A and 13C.

  The water in the evaporation pipe 51B is heated by heat transfer from the heat radiating part 13A of the heat pump 10, and at least a part of the water evaporates. The second tank 47B is fluidly connected to the compressor 31 via the duct 23B. The internal space of the second tank 47B is sucked by the compressor 31 via the discharge port of the second tank 47B and the duct 23B. The steam in the second tank 47B flows toward the compressor 31 in the duct 23B.

  The compressor 30 is disposed on the branch path 25A of the supply path 20, and the position of the compressor 30 is downstream of the first tank 47A. The compressor 31 is disposed on the branch path 25B of the supply path 20, and the position of the compressor 31 is downstream of the second tank 47B. As the compressors 30 and 31, various compressors such as an axial 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 first tank 47A and flows the boosted steam downstream. The compressor 31 compresses the steam from the second tank 47 </ b> B and flows the boosted steam downstream.

  In the compressor 30 (or the branch path 25A), a nozzle 35A that supplies water to the steam is disposed as necessary. Similarly, a nozzle 35B is disposed in the compressor 31 (or the branch path 25B) as necessary. The arrangement positions of the nozzles 35A and 35B are, for example, the inlets and / or outlets of the compressors 30 and 31. When the compressors 30 and 31 are multistage, the nozzles 35A and 35B can be disposed between the stages of the compressors 30 and 31. A pipe configuration in which the nozzle 35A and the liquid phase position of the first tank 47A are fluidly connected via the pipe 36A can be employed. In this piping configuration, the liquid in the first tank 47A having a relatively high temperature is effectively used for supplying the nozzle 35A. Similarly, a pipe configuration in which the nozzle 35B and the liquid phase position of the second tank 47B are fluidly connected via the pipe 36B can be employed. For discharging (spraying) the liquid from the nozzles 35A and 36B, a power source such as pumps 37A and 37B may be used, or the pressure difference between the inlets and outlets of the pipes 36A and 36B may be used.

  Due to the suction action by the compressor 30, the internal space at the heating portion of the supply path 20 by the heat pump 10, that is, the internal space of the first tank 47 </ b> A is decompressed. A control valve (such as a flow control valve) on the supply path 20 (branch path 25A) so that the internal pressure of the first tank 47A is a negative pressure (negative pressure) that is lower than the atmospheric pressure (1 atm = about 0.1 MPa). (Not shown), the compressor 30 and the like are controlled. This control is performed based on a measurement result of a sensor (not shown) that measures the internal pressure of the first tank 47A, for example.

  The first tank 47A and the heat pump 10 are designed (capacity design, capacity design, etc.) so that water evaporates when the internal space of the first tank 47A is in a negative pressure state. The temperature of the water in the first tank 47A is lower than the standard boiling point. 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 first tank 47A 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. For example, the water inlet temperature to the first heating unit 21A is about 20 ° C., and the water outlet temperature from the first heating unit 21A (water inlet temperature to the first evaporation unit 22A) is about 90 ° C. It is. Further, for example, the outlet temperature of water (steam) from the first evaporator 22A is about 90 ° C.

  The internal pressure of the second tank 47B is set according to the input temperature of water to the second evaporator 22B. In the present embodiment, the inlet temperature of water to the second tank 47B is higher than that of the first tank 47A. The temperature of the water heated by the first and second heating units 21A and 21B (the water outlet temperature from the second heating unit 21B, the water inlet temperature to the second evaporation unit 22B) is about 120 ° C., for example. is there. The internal pressure of the second tank 47B is set higher than that of the first tank 47A. The internal pressure of the second tank 47B is set by control of a control valve (a flow rate control valve, etc., not shown), a pump 26, a compressor 31 and the like on the supply path 20 (branch path 25B). This control is performed based on the measurement result of a sensor (not shown) that measures the internal pressure of the second tank 47B, for example. The inlet and outlet temperatures at each of the above sites are examples. The inlet and outlet temperatures of the water at each site vary depending on conditions such as the temperature of the source water, air temperature, and required steam specifications.

  In the present embodiment, the water in the supply path 20 becomes steam by heat transfer from the heat pump 10. First, in the first heat exchanger 41 (first heating unit 21A), the temperature of the water in the supply path 20 rises due to heat transfer from the heat radiating unit 13D of the heat pump 10. The flow of water from the first heating unit 21A is divided into a branch path 25A and a branch path 25B through the branch part 24A. The water flowing through the branch path 25A is directed to the first evaporator 22A (first tank 47A). In the first tank 47A, water has a temperature close to the boiling point (first boiling point). In the third heat exchanger 43, water in the evaporation pipe 51A undergoes phase change and evaporates due to heat transfer from the heat radiating portion 13C.

  The water flowing through the branch path 25B goes to the second heat exchanger 42 (second heating unit 21B). In the second heat exchanger 42 (second heating unit 21 </ b> B), the temperature of the water in the branch path 25 </ b> B further rises due to heat transfer from the heat radiating unit 13 </ b> B of the heat pump 10. The internal pressure of the second tank 47B is higher than that of the first tank 47A. In the second tank 47B, the water has a temperature close to the boiling point (second boiling point). The temperature of the water in the second tank 47B is higher than that of the water in the first tank 47A. In the fourth heat exchanger 44, the water in the evaporation pipe 51A undergoes a phase change and evaporates due to heat transfer from the heat radiating portion 13A.

  In the present embodiment, water is sensible heat heated in the first and second heat exchangers 41 and 42 (first and second heating units 21A and 21B), and the third and fourth heat exchangers 43 and 44 (first Water is latently heated in the first and second evaporation pipes 51A and 51B). The first and second heat exchangers 41 and 42 are suitable for sensible heat exchange, and the third and fourth heat exchangers 43 and 44 are suitable for latent heat exchange. As illustrated, steam is generated through a preferred heating process.

  Also in this embodiment, by using heat storage using the heat storage materials 101 and 111 and the tanks 47A and 47B, suppression of the peak power and average power consumption of the steam generation system S4, flexible response to steam / cooling demand, And / or the rise time of the steam generation process can be shortened.

  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 13A to 13D), and relatively high pressure by compression by the compressors 30 and 31. And it becomes high temperature steam. That is, the water heated by the heat pump 10 is further heated by the compression by the compressors 30 and 31, thereby generating high-temperature steam of 100 ° C. or higher.

  FIG. 12 is a Ts diagram showing an example of a state change of the working medium of the heat pump 10 in the steam generation system S4. FIG. 13 schematically shows an example of a temperature change between water and the working medium of the heat pump in the fourth embodiment.

  As shown in FIG. 13, in the first heating unit 21A (see FIG. 11), the temperature of water from the supply source rises near the first boiling point by the heat exchange with the working medium (arrow m1 in FIG. 13). . In the first evaporation section 22A, the phase of water changes from liquid to vapor at a temperature near the first boiling point due to heat exchange with the working medium (arrow m2). In the second heating unit 21B, the temperature of water rises near the second boiling point due to heat exchange with the working medium (arrow m3). In the second evaporation part 22B, the phase of water changes from liquid to vapor at a temperature close to the second boiling point due to heat exchange with the working medium (arrow m4).

  Moreover, as shown in FIG. 13, the temperature of the working medium (steam) from the compression part 12 (refer FIG. 11) falls by the heat exchange with water (arrow n1). The working medium (steam) changes phase to a liquid by heat exchange with water (arrow n2). Furthermore, the temperature of the working medium (liquid) decreases due to heat exchange with water (arrow n3).

  In this way, by generating steam using the two evaporators set in different environments, the temperature difference between the working medium and water during heat exchange can be suppressed, and the heat exchange efficiency can be increased. In FIG. 13, it can be considered that the smaller the area of the region surrounded by the line indicating the temperature of water and the line indicating the temperature of the working medium, the higher the heat exchange efficiency.

  FIG. 14 is a schematic view showing a fifth embodiment which is a modification of the steam generation system S4 of FIG. In the following description, for the steam generation system S5, the same elements as those in the steam generation system S4 shown in FIG. 11 are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 14, the steam generation system S5 includes three evaporators 22A, 22B, and 22C and three compressors 30, 31, and 32. The supply path 20 includes first, second, and third heating units 21A, 21B, and 21C, first, second, and third evaporation units 22A, 22B, and 22C, and evaporation units 22A, 22B, and 22C. It has ducts 23A, 23B, and 23C that fluidly connect the compressors 30, 31, and 32. In the present embodiment, the supply path 20 includes branch portions 24A and 24B and branch paths 25A, 25B, 25C, and 25D. In the supply path 20, the branching part 24B is located between the second heating part 21B and the second tank 47B. The branch path 25C guides water from the branch part 24B to the second evaporation part 22B. The branch path 25D guides water from the branch part 24B to the third evaporation part 22C.

  In the present embodiment, six heat radiating portions 13A to 13F are arranged in series along the flow direction of the working medium. A heat radiating portion 13E, a heat radiating portion 13F, a heat radiating portion 13A, a heat radiating portion 13B, a heat radiating portion 13C, and a heat radiating portion 13D are arranged in that order along the flow direction of the working medium.

  The third heating unit 21C is disposed in the branch path 25D. The third heating unit 21C includes a pipe that is disposed adjacent to the heat radiation unit 13F of the heat pump 10 and through which water from the second heating unit 21B flows. A fifth heat exchanger 45 is configured including the third heating unit 21C and the heat dissipation unit 13F. In the third heating unit 21C, the temperature of the water in the branch path 25D rises due to heat transfer from the heat radiating unit 13F of the heat pump 10.

  In the present embodiment, the pump 27 is disposed between the branching part 24B and the third heating part 21C in the branching path 25D. The amount of water per unit time flowing through the branch path 25C and the branch path 25D (the amount of water distributed to the evaporators 22B and 22C) is controlled by the pump 27 and / or a flow control device (not shown) such as not shown. . The arrangement position of the pump 27 is not limited between the branch part 24B and the third heating part 21C.

  Similar to the first and second evaporators 22A and 22B, the third evaporator 22C is fluidly connected to the third tank 47C for storing at least a liquid heated medium (water) and the third tank 47C. And a third circulation pipe 48C. That is, the inlet end and the outlet end of the third circulation pipe 48C are fluidly connected to the third tank 47C. The third tank 47C is provided with a water supply port from the third heating unit 21C and a steam discharge port. The third tank 47C includes a level sensor 50C that measures the liquid level and a gas-liquid separator (not shown) as necessary. 48 C of 3rd circulation piping has the evaporation pipe 51C arrange | positioned adjacent to the thermal radiation part 13E of the heat pump 10, and the pump 52C as needed.

  In the present embodiment, the first evaporator 22A (first tank 47A, evaporation pipe 51A), the second evaporator 22B (second tank 47B, evaporation pipe 51B), and the third evaporator 22C (third tank 47C, evaporation pipe). 51C) is arranged substantially in parallel with the supply path 20. The first, second, and third heating units 21A, 21B, and 21C are arranged substantially in series with respect to the supply path 20. Note that the third evaporator 22C is an upstream position, the second evaporator 22B is an intermediate position, and the first evaporator 22A is a downstream position with respect to the flow direction of the working medium in the heat pump 10. At least one of the pumps 52A, 52B, and 52C may be omitted using heat convection of the medium to be heated (water) and / or differential pressure. A sixth heat exchanger 46 is configured including the evaporation pipe 51C and the heat radiating portion 13E.

  In the present embodiment, the heat storage unit 100 is provided for the third heat exchanger 43, the fourth heat exchanger 44, and the sixth heat exchanger 46. The heat storage unit 100 includes a heat storage material 101 that stores heat transmitted from the heat pump 10. The heat of the heat storage material 101 is transmitted to the evaporation tubes 51A to 51C. The material characteristics of the heat storage material 101 are determined according to the specifications of the steam generation system S5. In the present embodiment, the heat storage material 101 includes a latent heat storage material that stores and dissipates heat with a liquid-solid phase change, as in the above embodiment. As shown in FIGS. 2A to 2D, 7A to 7B, and 8, various configurations can be applied to the configuration of the heat storage unit 100.

  In the third evaporator 22C, the water whose temperature has increased in the first, second, and third heating units 21A, 21B, and 21C is supplied to the third tank 47C through the supply port, and the third tank 47C and the third tank Water is stored in the circulation pipe 48C. The amount of water supplied to the third tank 47C is controlled so that the liquid level in the third tank 47C is within a predetermined range. For example, the amount of water supplied to the third tank 47C is controlled based on the measurement result of the level sensor 50C. The water in the evaporation pipe 51C is heated by heat transfer from the heat radiating portion 13E of the heat pump 10, and at least a part of the water evaporates. The third tank 47C is fluidly connected to the compressor 32 via the duct 23C. The internal space of the third tank 47C is sucked by the compressor 32 through the discharge port of the third tank 47C and the duct 23C. The steam in the third tank 47C flows toward the compressor 32 in the duct 23C.

  The compressor 32 is disposed on the branch path 25D of the supply path 20, and the position of the compressor 32 is downstream of the third tank 47C. The compressor 32 compresses the steam from the third tank 47C, and flows the boosted steam downstream.

  The internal pressure of the third tank 47C is set according to the input temperature of water to the third evaporator 22C. In the present embodiment, the inlet temperature of water to the third tank 47C is higher than that of the first and second tanks 47A and 47B. Temperature of water heated by the first, second, and third heating units 21A, 21B, and 21C (water outlet temperature from the third heating unit 21C, water inlet temperature to the third evaporation unit 22C) Is about 150 ° C., for example. The internal pressure of the third tank 47C is set higher than that of the first and second tanks 47A and 47B. The internal pressure of the third tank 47C is set by control of a control valve (a flow rate control valve, etc., not shown), a pump 27, a compressor 32, and the like on the supply path 20 (branch path 25D). This control is performed based on a measurement result of a sensor (not shown) that measures the internal pressure of the third tank 47C, for example.

  In the present embodiment, the water flowing through the branch path 25D goes to the fifth heat exchanger 45 (third heating unit 21C). In the fifth heat exchanger 45 (third heating unit 21 </ b> C), the temperature of the water in the branch path 25 </ b> D further increases due to heat transfer from the heat radiating unit 13 </ b> F of the heat pump 10. The internal pressure of the third tank 47C is higher than that of the first and second tanks 47A and 47B. In the third tank 47C, the water has a temperature close to the boiling point (third boiling point). The temperature of the water in the third tank 47C is higher than the water in the first and second tanks 47A and 47B. In the sixth heat exchanger 46, the water in the evaporation pipe 51C undergoes phase change and evaporates due to heat transfer from the heat radiating portion 13E.

  Also in this embodiment, by utilizing the heat storage using the heat storage materials 101 and 111 and the tanks 47A to 47C, the peak power and average power consumption of the steam generation system S5 can be suppressed, and flexible response to steam / cooling demand can be achieved. And / or the rise time of the steam generation process can be shortened.

  In the present embodiment, saturated steam is generated under a relatively low pressure in the first tank 47A of the first evaporator 22A, and saturated steam is generated under a relatively high pressure in the third tank 47C of the third evaporator 22C. In the second tank 47B of the second evaporator 22B, saturated steam is generated under an intermediate pressure. By controlling each steam discharge amount (mixing ratio) of the first, second, and third evaporators 22A, 22B, and 22C, it is possible to change the specifications of the output steam.

  FIG. 15 schematically shows an example of a temperature change between water and the working medium of the heat pump in the fifth embodiment.

  As shown in FIG. 15, the temperature of the water that has risen through the first and second heating units 21A and 21B (see FIG. 14) is changed by the heat exchange with the working medium in the third heating unit 21C. It further rises to near 3 boiling points (arrow m5 in FIG. 15). In the third evaporation section 22C, the phase of water changes from liquid to vapor at a temperature near the third boiling point due to heat exchange with the working medium (arrow m6).

  Thus, by generating steam using the three evaporation parts set in different environments, the temperature difference between the working medium and water during heat exchange can be suppressed, and the heat exchange efficiency can be increased. In FIG. 15, it can be considered that the smaller the area of the region surrounded by the line indicating the temperature of water and the line indicating the temperature of the working medium, the higher the heat exchange efficiency.

  In the third and fourth embodiments, the number of evaporators (the number of tanks and circulation pipes (evaporation pipes)) is set according to the specifications of the steam generation system, and is 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more.

  FIG. 16 is a schematic view showing a sixth embodiment which is another modified example of the steam generation system S4 of FIG. In the following description, for the steam generation system S6, elements similar to those in the steam generation system S4 shown in FIG. 11 are denoted by the same reference numerals, and description thereof is omitted or simplified.

  In the steam generation system S6, as shown in FIG. 16, the compression unit 12 has a structure for compressing the working medium in a plurality of stages (in this example, two stages). In the present embodiment, the compression unit 12 includes a first compression unit 12A disposed in front of the heat dissipation unit 13A and a second compression unit 12B disposed in the middle stage of the heat dissipation unit 13A. Instead of or in addition to the second compression part 12B, a compression part can be provided in the middle stage of the heat radiation part 13C. The number of compression stages is set according to the specifications of the steam generation system, and is 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. The compression unit 12 can have a multiaxial compression structure in which the rotation speeds corresponding to the compression units 12A and 12B are individually controlled. Alternatively, the compression unit 12 can have a coaxial compression structure. The compression ratio (pressure ratio) of each compression part 12A, 12B is set according to the specification of a steam generation system.

  In the present embodiment, the heat storage unit 100 is provided for the third heat exchanger 43 and the fourth heat exchanger 44. The heat storage unit 100 includes a heat storage material 101 that stores heat transmitted from the heat pump 10. The heat of the heat storage material 101 is transmitted to the evaporation tubes 51A and 51B. The material characteristics of the heat storage material 101 are determined according to the specifications of the steam generation system S6. In the present embodiment, the heat storage material 101 includes a latent heat storage material that stores and dissipates heat with a liquid-solid phase change, as in the above embodiment. As shown in FIGS. 2A to 2D, 7A to 7B, and 8, various configurations can be applied to the configuration of the heat storage unit 100.

  In the present embodiment, energy efficiency is improved because the compression unit 12 is a multistage type. That is, the heat between the stages of the multistage compression unit 12 is deprived, thereby suppressing the temperature increase of the working medium during the compression process of the working medium. As a result, the compression efficiency of the compression unit 12 is improved and the compressor power is increased. Can be reduced. 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.

  Also in the present embodiment, by using the heat storage using the heat storage materials 101 and 111 and the tanks 47A and 47B, the peak power and average power consumption of the steam generation system S6 can be suppressed, and the steam / cold energy demand can be flexibly changed. It is possible to cope with and / or shorten the rise time of the steam generation process.

  FIG. 17 is a schematic view showing a seventh embodiment which is a modification of the steam generation system S5 of FIG. In the following description, with respect to the steam generation system S7, the same elements as those in the steam generation system S5 shown in FIG. 14 are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  In the steam generation system S7, as shown in FIG. 17, the compression unit 12 has a structure for compressing the working medium in a plurality of stages (in this example, two stages). In this embodiment, the compression part 12 has 12 A of 1st compression parts arrange | positioned before the thermal radiation part 13E, and 2nd compression part 12B arrange | positioned in the middle stage of the thermal radiation part 13E. Instead of or in addition to the second compression part 12B, a compression part can be provided in the middle stage of the heat radiation part 13A and / or the middle stage of the heat radiation part C.

  In the present embodiment, the heat storage unit 100 is provided for the third heat exchanger 43, the fourth heat exchanger 44, and the sixth heat exchanger 46. The heat storage unit 100 includes a heat storage material 101 that stores heat transmitted from the heat pump 10. The heat of the heat storage material 101 is transmitted to the evaporation tubes 51A to 51C. The material characteristics of the heat storage material 101 are determined according to the specifications of the steam generation system S7. In the present embodiment, the heat storage material 101 includes a latent heat storage material that stores and dissipates heat with a liquid-solid phase change, as in the above embodiment. As shown in FIGS. 2A to 2D, 7A to 7B, and 8, various configurations can be applied to the configuration of the heat storage unit 100.

  Also in this embodiment, by utilizing the heat storage using the heat storage materials 101 and 111 and the tanks 47A to 47C, the peak power and the average power consumption of the steam generation system S7 can be suppressed, and flexible response to the steam / cooling demand can be achieved. And / or the rise time of the steam generation process can be shortened.

  FIG. 18 is a schematic view showing an eighth embodiment which is another modified example of the steam generation system S4 of FIG. In the following description, for the steam generation system S8, the same elements as those in the steam generation system S4 shown in FIG. 11 are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  In the steam generation system S8, as shown in FIG. 18, the compression unit 12 has a structure for compressing the working medium in a plurality of stages (in this example, two stages). In this embodiment, the compression part 12 has 12 A of 1st compression parts arrange | positioned before 13 A of thermal radiation parts, and the 2nd compression part 12C arrange | positioned between the thermal radiation part 13B and the thermal radiation part 13C. In addition to the second compression unit 12C, a compression unit may be provided in the middle stage of the heat dissipation unit 13A and / or the heat dissipation unit 13C. The number of compression stages is set according to the specification of the steam generation system S8, and is 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. The compression unit 12 can have a multiaxial compression structure in which the rotation speeds corresponding to the compression units 12A and 12C are individually controlled. Alternatively, the compression unit 12 can have a coaxial compression structure. The compression ratio (pressure ratio) of each compression part 12A, 12C is set according to the specification of the steam generation system.

  In the present embodiment, the heat storage unit 100 is provided for the third heat exchanger 43 and the fourth heat exchanger 44. The heat storage unit 100 includes a heat storage material 101 that stores heat transmitted from the heat pump 10. The heat of the heat storage material 101 is transmitted to the evaporation tubes 51A and 51B. The material characteristics of the heat storage material 101 are determined according to the specifications of the steam generation system S8. In the present embodiment, the heat storage material 101 includes a latent heat storage material that stores and dissipates heat with a liquid-solid phase change, as in the above embodiment. As shown in FIGS. 2A to 2D, 7A to 7B, and 8, various configurations can be applied to the configuration of the heat storage unit 100.

  Also in the present embodiment, by using the heat storage using the heat storage materials 101 and 111 and the tanks 47A and 47B, the peak power and average power consumption of the steam generation system S8 can be suppressed, and flexible response to steam / cooling demand can be achieved. And / or the rise time of the steam generation process can be shortened.

  FIG. 19 is a schematic view showing a ninth embodiment which is another modified example of the steam generation system S5 of FIG. In the following description, for the steam generation system S9, the same elements as those in the steam generation system S5 shown in FIG. 14 are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  In the steam generation system S9, as shown in FIG. 19, the compression unit 12 has a structure for compressing the working medium in a plurality of stages (in this example, two stages). In the present embodiment, the compression unit 12 includes a first compression unit 12A disposed in front of the heat dissipation unit 13E, and a second compression unit 12C disposed between the heat dissipation unit 13F and the heat dissipation unit 13A. Instead of or in addition to the second compression part 12C, a compression part can be provided between the heat radiation part 13B and the heat radiation part 13C. In addition to the second compression unit 12C, a compression unit may be provided in the middle stage of the heat dissipation unit 13E, the heat dissipation unit 13A, and / or the heat dissipation unit 13C.

  In the present embodiment, the heat storage unit 100 is provided for the third heat exchanger 43, the fourth heat exchanger 44, and the sixth heat exchanger 46. The heat storage unit 100 includes a heat storage material 101 that stores heat transmitted from the heat pump 10. The heat of the heat storage material 101 is transmitted to the evaporation tubes 51A to 51C. The material characteristics of the heat storage material 101 are determined according to the specifications of the steam generation system S9. In the present embodiment, the heat storage material 101 includes a latent heat storage material that stores and dissipates heat with a liquid-solid phase change, as in the above embodiment. As shown in FIGS. 2A to 2D, 7A to 7B, and 8, various configurations can be applied to the configuration of the heat storage unit 100.

  Also in this embodiment, by using heat storage using the heat storage materials 101 and 111 and the tanks 47A to 47C, suppression of peak power and average power consumption of the steam generation system S9, flexible response to steam and cold demand, And / or the rise time of the steam generation process can be shortened.

  FIG. 20 is a schematic view showing a tenth embodiment which is another modified example of the steam generation system S9 of FIG. In the following description, for the steam generation system S10, elements similar to those in the steam generation system S9 shown in FIG. 19 are denoted by the same reference numerals, and description thereof is omitted or simplified.

  In the steam generation system S10, as shown in FIG. 20, the second heating unit 21B and the third heating unit 21C are arranged substantially in parallel with the supply path 20. Note that the third heating unit 21C is an upstream position and the second heating unit 21B is a downstream position with respect to the flow direction of the working medium in the heat pump 10.

  In the present embodiment, the supply path 20 includes branch portions 24A and 24C and branch paths 25A, 25F, 25G, and 25H. In the supply path 20, a branch path 25A and a branch path 25F are separated from the branch section 24A. As described above, the branch path 25A guides the water from the branch part 24A to the first evaporation part 22A. The branch part 24C is located on the branch path 25F from the branch part 24A. A branch path 25G and a branch path 25H are separated from the branch section 24C. The branch path 25G guides water from the branch part 24C to the second warming part 21B. The branch path 25H guides water from the branch part 24B to the third heating part 21C.

  In the present embodiment, the pump 28 is disposed in the branch path 25F. The amount of water per unit time flowing through the branch paths 25A, 25F, 25G, and 25H (the amount of water distributed to the evaporators 22A, 22B, and 23C) by the pump 28 and / or a flow rate controller (not shown) (not shown). Is controlled. The arrangement position of the pump 28 is not limited to the branch path 25F. In other embodiments, a pump can be placed on the branch path 25G and / or 25H.

  In the second evaporation part 22B, the water whose temperature has increased in the first and second heating parts 21A, 21B is supplied to the second tank 47B via the supply port. Similarly, in the third evaporation section 22C, the water whose temperature has increased in the first and third heating sections 21A, 21C is supplied to the third tank 47C via the supply port.

  In this embodiment, since the compression part 12 of the heat pump 10 is a multistage type, the heat transferred from the heat radiating part 13B to the second heating part 21B is the heat transferred from the heat radiating part 13E to the third heating part 21C. Can be as high as Since the second and third heating units 21B and 21C are arranged substantially in parallel, the water inlet temperature to the second evaporation unit 22B (the water outlet temperature from the second heating unit 21B) is The temperature of the water heated by the first and third heating units 21A and 21C (the outlet temperature of the water from the third heating unit 21C, the inlet temperature of the water to the third evaporation unit 22C) should be approximately the same. it can.

  The internal pressures of the second and third tanks 47B and 47C are set according to the input temperature of water to the second and third evaporators 22B and 22C. In this embodiment, the inlet temperature of water to the second and third tanks 47B and 47C is higher than that of the first tank 47A. Compared to the first tank 47A, the internal pressures of the second and third tanks 47B and 47C are set higher. The internal pressures of the second and third tanks 47B and 47C are controlled by the control of the control valve (flow rate control valve and the like), the pump 28, the compressors 31 and 32, etc. on the supply path 20 (the branch paths 25H and 25G). Is set. This control is performed based on, for example, a measurement result of a sensor (not shown) that measures the internal pressures of the second and third tanks 47B and 47C.

  In the present embodiment, saturated steam is generated at a relatively low pressure in the first tank 47A of the first evaporator 22A, and comparison is made in the second and third tanks 47B and 47C of the second and third evaporators 22B and 22C. Saturated steam is generated under moderately high pressure. By controlling each steam discharge amount (mixing ratio) of the first, second, and third evaporators 22A, 22B, and 22C, it is possible to change the specifications of the output steam. In this embodiment, since a plurality of evaporation tanks (second and third tanks 47B and 47C) that can be set to the same internal pressure are provided, a relatively large amount of steam corresponding to the conditions corresponding to the pressure is provided. Can be generated.

  In the present embodiment, the heat storage unit 100 is provided for the third heat exchanger 43, the fourth heat exchanger 44, and the sixth heat exchanger 46. The heat storage unit 100 includes a heat storage material 101 that stores heat transmitted from the heat pump 10. The heat of the heat storage material 101 is transmitted to the evaporation tubes 51A to 51C. The material characteristics of the heat storage material 101 are determined according to the specifications of the steam generation system S9. In the present embodiment, the heat storage material 101 includes a latent heat storage material that stores and dissipates heat with a liquid-solid phase change, as in the above embodiment. As shown in FIGS. 2A to 2D, 7A to 7B, and 8, various configurations can be applied to the configuration of the heat storage unit 100.

  Also in this embodiment, by utilizing the heat storage using the heat storage materials 101 and 111 and the tanks 47A to 47C, the peak power and average power consumption of the steam generation system S10 can be suppressed, and flexible response to steam / cooling demand can be achieved. And / or the rise time of the steam generation process can be shortened.

  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 sectional drawing which shows the structural example of the heat exchanger provided with the thermal storage part. It is sectional drawing which shows another structural example of the heat exchanger provided with the thermal storage part. It is sectional drawing which shows another structural example of the heat exchanger provided with the thermal storage part. It is sectional drawing which shows another structural example of the heat exchanger provided with the thermal storage part. 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 a figure which shows an example of an operation mode typically. It is a figure which shows an example of an operation mode typically. It is a figure which shows an example of an operation mode typically. It is the schematic which shows 2nd Embodiment. It is a structural example of a thermal storage part. It is another structural example of a thermal storage part. It is sectional drawing which shows the structural example of the heat exchanger with which two heat storage parts were provided integrally. It is a figure which shows an example of an operation mode typically. It is a figure which shows an example of an operation mode typically. It is the schematic which shows 3rd Embodiment. It is the schematic which shows 4th Embodiment. It is a Ts diagram which shows an example of the state change of the working medium of a heat pump. It is a figure which shows typically an example of the temperature change of the water in 4th Embodiment, and the working medium of a heat pump. It is the schematic which shows 5th Embodiment. It is a figure which shows typically an example of the temperature change of the water and working medium of a heat pump in 5th Embodiment. It is the schematic which shows 6th Embodiment. It is the schematic which shows 7th Embodiment. It is the schematic which shows 8th Embodiment. It is the schematic which shows 9th Embodiment. It is the schematic which shows 10th Embodiment.

Explanation of symbols

  S1 to S10: Steam generation system, 10: Heat pump, 11: Heat absorption part, 12: Compression part, 13A-13F ... Heat dissipation part, 14 ... Expansion part, 15 ... Main path, 17 ... Bypass path, 18 ... Regenerator, 20 ... Supply path, 21A-21C ... Warming part, 22A-22C ... Evaporation part, 23A-23C ... Duct, 24A, 24B, 24C ... Branch part, 25A, 25B, 25C, 25D, 25F, 25G, 25H ... Branch path , 26-28 ... pump, 30, 31, 32 ... compressor, 35A-35C ... nozzle, 41-46 ... heat exchanger, 47A-47C ... tank, 48A-48C ... circulation piping, 50A-50C ... level sensor, 51A-51C ... Evaporation tube, 70 ... Control device, 71,72 ... Sensor, 90 ... Refrigerator, 91 ... Heat dissipation part, 100,110 ... Heat storage part, 101,111 ... Heat storage material, 102 Housing.

Claims (10)

A heat pump through which the first medium flows;
A first path through which the second medium flows, the first path having an evaporation section in which the second medium evaporates by heat transferred from the heat pump;
A device thermally connected to the heat pump, and the device for flowing a third medium deprived of heat by the first medium flowing through the heat pump;
A steam generation system comprising: a first heat storage material having a first heat storage material and thermally connected to the heat pump and the device.   2. The steam generation system according to claim 1, wherein the heat pump includes a heat absorption unit in which at least a part of the first medium evaporates due to heat transferred from at least one of the device and the first heat storage unit.   The steam generation system according to claim 2, wherein a supply temperature of the third medium with respect to the first medium is higher than an initial temperature of the second medium.   The steam generation system according to any one of claims 1 to 3, wherein the third medium from the device includes waste energy of the device.   The steam generation system according to claim 4, wherein the device includes a refrigerator, a refrigerator, or an internal combustion engine.   A second heat storage unit having a second heat storage material and thermally connected to the heat pump and the evaporation unit; The steam generation system according to any one of claims 1 to 4, wherein the second medium evaporates.   The heat pump includes a heating unit that is disposed upstream of the evaporation unit and that heats the second medium by heat from the heat pump, a compression unit, and a part of the first medium from the compression unit. The bypass path for bypassing the heating unit, and a regenerator for transferring heat from the first medium in the bypass path to the first medium upstream of the compression unit. The steam generation system according to any one of 1 to 6.   The steam generation system according to claim 1, further comprising a control device that controls an operating state of the heat pump according to a time zone. Evaporating the second medium flowing in the first path by the heat from the heat pump in operation;
Storing cold heat from the heat pump in operation in the first heat storage unit;
And a step of releasing exhaust heat from a device in operation to the first heat storage unit when the heat pump is non-operating or operating. Storing cold heat from the operating heat pump in the first heat storage unit;
Storing the heat from the heat pump in operation in the second heat storage unit;
Releasing the exhaust heat from the operating device to the first heat storage unit when the heat pump is non-operating or operating;
Evaporating the second medium flowing through the first path by heat transferred from at least one of the second heat storage unit and the heat pump when the heat pump is not in operation or in an operating state. .

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