JP5176491B2 - Steam generation system - Google Patents

Description

  The present invention relates to a steam generation system.

As a steam generation system, a configuration in which fuel is combusted in a boiler to heat a fluid 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.

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

  According to an aspect of the present invention, a first unit having a heat pump through which a first fluid flows; an evaporating part thermally connected to the heat pump and evaporating a second fluid; and fluidly connected to the evaporating part; A steam generation system comprising: a compressor that compresses at least a part of the steam from the evaporation unit; and a second unit that includes a supplementary path that guides a part of the compressed steam from the compressor to the evaporation unit. Is provided.

  According to the aspect of the present invention, by using a heat pump, high energy efficiency can be obtained compared to a boiler. Further, by guiding a part of the compressed steam from the compressor to the evaporation unit, evaporation of the second fluid in the evaporation unit is promoted.

  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 S1 according to the first embodiment. In FIG. 1, a steam generation system S1 includes a heat pump 10 (first unit) through which a working fluid (working medium, first fluid) flows and a supply unit 20 (second medium) for a heated fluid (heated medium, second fluid). Unit) and a control device 70. In the present embodiment, the fluid to be heated is water. The control device 70 comprehensively controls the entire system. The configuration of the steam generation system S1 can be variously changed according to the design requirements of the steam generation system S1.

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

  In the present embodiment, the heat pump 10 includes a heat absorbing part 11, a compressing part 12, a heat radiating part (a first heat radiating part 13A, a second heat radiating part 13B), and an expanding part 14, which are connected via a conduit. Yes.

  In the heat absorption part 11, the working fluid flowing in the main path 15 absorbs heat from a heat source outside the cycle. In this embodiment, the heat absorption part 11 of the heat pump 10 absorbs atmospheric heat. The heat absorption part 11 of the heat pump 10 can also be configured to absorb heat (exhaust heat or the like) from an external device.

  The compression unit 12 compresses the working fluid by a compressor or the like. At this time, the temperature of the working fluid usually increases. The compressing unit 12 has a structure for compressing the working fluid into a single stage or a plurality of stages. The number of compression stages is set according to the specifications of the steam generation system S1, and is 1, 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 a working fluid is applied. 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 S1.

  The heat radiating portions 13A and 13B have a conduit through which the working fluid compressed by the compressing portion 12 flows, and give heat of the working fluid flowing in the main path 15 to a heat source outside the cycle. In the present embodiment, the first heat radiating portion 13A and the second heat radiating portion 13B are arranged in that order along the flow direction of the working fluid. 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.

  The expansion unit 14 expands the working fluid by a pressure reducing valve, a turbine, or the like. At this time, the temperature of the working fluid 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 the working fluid used in the heat pump 10, various known heat media 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 supply unit 20 includes a heating unit 21, an evaporation unit 22, and a compressor 30.

  Heating unit 21 includes a conduit that is thermally connected to second heat radiating unit 13B of heat pump 10 and through which water from a supply source (not shown) flows. For example, the conduit of the heating unit 21 is disposed in contact with or adjacent to the conduit of the second heat radiating unit 13B. The 1st heat exchanger 41 is comprised including the heating part 21 and the 2nd thermal radiation part 13B. The first heat exchanger 41 can have a countercurrent heat exchange method in which a low-temperature fluid (water in the supply unit 20) and a high-temperature fluid (working fluid in the heat pump 10) flow opposite to each other. Alternatively, the first heat exchanger 41 may have a parallel flow type heat exchange system in which a high-temperature fluid and a low-temperature fluid flow in parallel. In the present embodiment, the conduit of the heating unit 21 is disposed inside the conduit of the second heat radiating unit 13 </ b> B of the heat pump 10. In the heating unit 21, the temperature of the water in the supply unit 20 rises due to the heat transferred from the second heat radiating unit 13 </ b> B of the heat pump 10. In other embodiments, the first heat exchanger 41 can employ another heat exchange structure. For example, the conduit of the second heat radiating portion 13B can be disposed on the outer peripheral surface of the conduit of the warming portion 21.

  The evaporation unit 22 includes a tank 47 that stores water as a medium to be heated, and a path 25 that guides water from the heating unit 21 to the tank 47. In the path 25, devices such as a control valve and a pump (not shown) are arranged as necessary. In addition, you may provide a deaeration apparatus between the heating part 21 and the tank 47, for example. The tank 47 is provided with a water supply port (not shown) to which the path 25 is fluidly connected and a steam discharge port (not shown) to which the duct 23 is fluidly connected. The tank 47 includes a level sensor (not shown) for measuring the liquid level, a sensor (not shown) for measuring information corresponding to the temperature of the internal water (steam), as necessary. A gas-liquid separator (not shown). The level sensor and information from the sensor are sent to the control device 70. The tank 47 is provided with the first heat radiating portion 13 </ b> A of the heat pump 10. Heat from the first heat radiating portion 13 </ b> A of the heat pump 10 is transmitted to the water in the tank 47.

  In the evaporation unit 22, the water whose temperature has risen in the heating unit 21 is supplied to the tank 47 through the path 25 and the supply port. 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 supply amount of water is controlled based on the measurement result of a level sensor (not shown) that measures the liquid level in the tank 47. Water is stored in the tank 47, and the water in the tank 47 is heated by the first heat radiating portion 13A of the heat pump 10. 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 generated in the tank 47 is guided to the compressor 30 through the duct 23.

  The compressor 30 is fluidly connected to the gas phase space of the tank 47 via the duct 23 and the discharge port 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.

  Due to the suction action by the compressor 30, the internal space of the tank 47 is decompressed. Control valves (such as a flow rate control valve, not shown) and the compressor 30 on the path 25 are controlled so that the internal pressure of the tank 47 becomes a negative pressure (negative pressure) lower than the atmospheric pressure. 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.

  In the compressor 30 and / or the supply unit 20, a nozzle 35 for supplying water (hot 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. The multistage compression structure of the compressor 30 is advantageous for increasing the temperature and pressure of steam. The compressor 30 can have a multiaxial compression structure in which the rotation speed corresponding to each of the multistage compression units is individually controlled. Alternatively, the compressor 30 can have a coaxial multistage compression structure. The compression ratio (pressure ratio) of each compression unit is set according to the specification of the steam generation system S1. In the present embodiment, the nozzle 35 and the branch path 25 </ b> A can be fluidly connected via the conduit 36. In this conduit configuration, the liquid in the branch path 25 </ b> A having a relatively high temperature pressurized by the pump 26 is effectively used for supplying the nozzle 35. For discharging the liquid from the nozzle 35, a power source such as a pump may be used, or a pressure difference between the inlet and the outlet of the conduit 36 may be used.

  In the present embodiment, the supply unit 20 further includes an auxiliary path 38 that extracts a part of the steam from the compressor 30 and guides it to the tank 47 of the evaporation unit 22. One end of the auxiliary path 38 is fluidly connected to the outlet of the compressor 30 and / or the interstage path. The other end of the auxiliary path 38 is fluidly connected to a liquid phase position (such as the bottom) in the tank 47. The steam extracted from the compressor 30 is guided to the liquid phase in the tank 47 through the auxiliary path 38. As will be described later, the extracted steam is used to promote evaporation in the tank 47.

  In such a steam generation system S1, the temperature of the water from the supply source rises to near the boiling point by the heat from the second heat radiating portion 13B of the heat pump 10 in the first heat exchanger 41. The warm water is supplied to the tank 47. In the tank 47, the water undergoes phase change and evaporates due to heat from the first heat radiating portion 13A of the heat pump 10.

  The tank 47 and the heat pump 10 are designed (capacity design, capacity design, etc.) so that water evaporates when the internal space of the tank 47 is in a negative pressure state. 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 if the temperature difference is excessively large, the coefficient of performance (COP) may decrease. In the present embodiment, due to the point that the internal space of the second evaporation unit 22B is in a negative pressure state and the state of the medium to be heated and the working fluid, the heat pump has an individual heating unit (heat radiating unit), etc. The temperature difference between input and output can be suppressed, and steam can be generated with higher energy efficiency than a boiler. The supply temperature of water to the heating unit 21 is, for example, about 20 ° C., and the outlet temperature of water from the heating unit 21 (the inlet temperature of water to the tank 47) is, for example, about 90 ° C. The above numerical values are examples for understanding, and the present invention is not limited thereto.

  Further, in the present embodiment, water from the supply source becomes steam having a relatively low pressure and low temperature when heated by the heat pump 10 (heat radiation portions 13A and 13B), and relatively high pressure and high temperature when compressed by the compressor 30. Of steam. That is, the water heated by the heat pump 10 is further heated by the compression by the compressor 30, thereby generating high-temperature steam at 100 ° C. or higher.

  FIG. 2 is a Ts diagram showing an example of a change in the state of water in the evaporation unit 22 and the compressor 30 shown in FIG. As shown in FIG. 2, after the temperature rises to near the boiling point, water undergoes a phase change while keeping the temperature constant. At this time, saturated steam d0 is generated in a state of negative pressure P0 that is lower than atmospheric pressure (P1 = 1 atm = about 0.1 MPa). The temperature of the saturated vapor d0 is lower than the normal boiling point, for example, about 90 ° C.

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

  A saturated steam of about 160 ° C. can be obtained by cooling the superheated steam e2 of 0.8 MPa under a constant pressure (dashed line a in FIG. 2). Similarly, saturated steam d1 at about 100 ° C. can be obtained by cooling superheated steam at atmospheric pressure (about 0.1 MPa) under constant pressure. The above numerical values are examples for understanding, and the present invention is not limited thereto.

  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 warm 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. 2). 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. 2). 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 sequential heating by the heat pump 10 and the compressor 30. That is, the steam generation system S1 is highly flexible with respect to the steam specifications. 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.

  Further, in the present embodiment, the vapor extracted from the compressor 30 is introduced into the liquid phase in the tank 47, whereby evaporation in the tank 47 is promoted.

  Here, in this embodiment, the temperature difference (hereinafter referred to as “surface superheat degree”) between the saturation temperature (boiling temperature) of water in the tank 47 and the first heat radiating portion 13A as the heat source is relatively small, for example, about 5 ° C to 15 ° C, 15 ° C to 25 ° C, 25 ° C to 35 ° C, 35 ° C to 45 ° C, 45 ° C to 55 ° C, 55 ° C to 65 ° C, 65 ° C to 75 ° C, It is about 75 degreeC to about 85 degreeC, about 85 degreeC to about 95 degreeC, or about 95 degreeC or more. When the degree of surface superheat is relatively small, it may belong to the sub-cooled boiling (also referred to as surface boiling) region. In the region of nucleate boiling where the degree of surface superheat is relatively high, intense heat transfer occurs and bubbles are repeatedly generated. In the present embodiment, by introducing the steam from the compressor 30 into the liquid phase in the tank 47, bubbles generated from the steam cause forced convection of the liquid phase, thereby improving heat transfer. it can. Such bubbling promotes evaporation in the tank 47.

  Further, as described above, in the present embodiment, saturated steam and / or superheated steam can be extracted from the compressor 30. The introduction of superheated steam is advantageous for stirring in the tank 47, suppressing the disappearance of bubbles in the tank 47, and increasing the heat transfer area. As a result, evaporation in the tank 47 is promoted.

  3A and 3B are diagrams schematically showing an example of a steam outlet structure from the auxiliary passage 38 in the tank 47. FIG.

  As shown in FIG. 3A, the auxiliary path 38 may have a discharge port 61 disposed adjacent to the conduit of the first heat radiating portion 13 </ b> A. In this structure, the steam from the auxiliary path 38 is supplied near the surface of the conduit of the first heat radiating portion 13A. The auxiliary path 38 can have a head 62 having a plurality of discharge ports 61 as shown in FIG. 3B. For example, the head 62 is disposed in the tank 47 at a position below the first heat radiating portion 13A. In this structure, steam can be supplied into the tank 47 over a wide range in the tank 47. In other structures, it is also possible to provide a discharge port for the auxiliary passage 38 on the wall (eg, the bottom) of the tank 47.

  In the present embodiment, sensible heat heating of water is mainly performed in the first heat exchanger 41 (heating unit 21), and latent heat heating of water is mainly performed in the tank 47. Therefore, the first heat exchanger 41 including the second heat radiating portion 13B is in a form suitable for sensible heat exchange, and the heat exchanging unit including the first heat radiating portion 13A, the tank 47, the auxiliary path 38, and the like is suitable for latent heat exchange. The configuration of the apparatus, such as the form, is optimized, and accordingly, steam is generated through a preferable heating process.

  Moreover, in this embodiment, since the compressor 30 supplements a part of heating process for steam generation, the heat pump 10 is used with high COP. Therefore, the steam generation system S1 is expected to save primary energy as a whole.

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

  FIG. 4 is a schematic diagram showing a steam generation system S2 according to the second embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  4, the steam generation system S2 includes a heat pump 10 (first unit) through which a working fluid (working medium, first fluid) flows, and a supply unit 20 (second medium) for a heated fluid (heated medium, second fluid). Unit) and a control device 70. In the present embodiment, the fluid to be heated is water. The control device 70 comprehensively controls the entire system. The configuration of the steam generation system S2 can be variously changed according to the design requirements of the steam generation system S2.

  In the present embodiment, the heat pump 10 includes a heat absorbing portion 11, a compressing portion 12, a heat radiating portion (a first heat radiating portion 13A, a second heat radiating portion 13B, a third heat radiating portion 13C), and an expansion portion 14, which are conduits. Connected through.

  In the present embodiment, the heat absorption unit 11 of the heat pump 10 is thermally connected to the heat radiating pipe 91 of the cold heat supply device 90. In the cold heat supply device 90, the heat (heat exhaust heat) of the medium (refrigerant or the like) flowing through the heat radiating pipe 91 is absorbed by the heat absorption unit 11 of the heat pump 10. The cooled medium is supplied from the cold heat supply device 90 to a predetermined facility. The heat absorption part 11 of the heat pump 10 can also be configured to absorb the heat of other heat sources such as the atmosphere.

  In the present embodiment, the heat radiating units 13A, 13B, and 13C have conduits through which the working fluid compressed by the compression unit 12 flows, and give the heat of the working fluid flowing in the main path 15 to heat sources outside the cycle. In the present embodiment, the first heat radiating portion 13A, the second heat radiating portion 13B, and the third heat radiating portion 13C are arranged in that order along the flow direction of the working fluid. The number of heat radiation units is set according to the specification of the steam generation system S2, and is 2, 3, 4, 5, 6, 7, 8, 9, 10, or 11 or more.

  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 conduit between the heat radiation parts 13A and 13B and the third heat radiation part 13C in the main path 15 of the heat pump 10. The outlet end of the bypass path 17 is fluidly connected to a conduit between the third heat radiating part 13 </ b> C and the expansion part 14 in the main path 15. A flow rate control valve for controlling the bypass flow rate of the working fluid can be provided at the inlet of the bypass passage 17. In the bypass path 17, part of the working fluid from the first and second heat radiating portions 13 </ b> A and 13 </ b> B bypasses the third heat radiating portion 13 </ b> C and joins the working fluid from the third heat radiating portion 13 </ b> C before the expansion portion 14. To do. The remaining working fluid from the first and second heat radiating portions 13A and 13B flows through the third heat radiating portion 13C, and the heat from the third heat radiating portion 13C is transmitted to the water in the supply unit 20.

  The regenerator 18 has a configuration in which a part of the conduit of the bypass path 17 and a part of the conduit of the main path 15 of the heat pump 10 (the conduit between the heat absorption unit 11 and the compression unit 12) are thermally connected. Have. For example, both conduits are placed in contact with or adjacent to each other. In the heat pump 10, the working fluid from the first and second heat radiating units 13 </ b> A and 13 </ b> B is hotter than the working fluid from the heat absorbing unit 11. In the regenerator 18, the working fluid from the first and second heat radiating parts 13 </ b> A and 13 </ b> B flowing through the bypass path 17 and the working fluid from the heat absorbing part 11 flowing through the main path 15 of the heat pump 10 exchange heat. By this heat exchange, the temperature of the working fluid in the bypass path 17 is lowered, and the temperature of the working fluid in the main path 15 is raised. The regenerator 18 can have a countercurrent heat exchange structure in which a low-temperature fluid (working fluid in the main passage 15) and a high-temperature fluid (working fluid in the bypass passage 17) flow opposite to each other. Alternatively, the regenerator 18 may have a parallel flow type heat exchange structure in which a high-temperature fluid and a low-temperature fluid flow in parallel.

  The supply unit 20 includes a heating unit 21, an evaporation unit 22, and a compressor 30.

  In the present embodiment, the heating unit 21 includes a conduit that is thermally connected to the third heat radiating unit 13C of the heat pump 10 and through which water from a supply source (not shown) flows. For example, the conduit of the heating unit 21 is disposed in contact with or adjacent to the conduit of the third heat radiating unit 13C. The 1st heat exchanger 41 is comprised including the heating part 21 and the 3rd thermal radiation part 13C. In the present embodiment, the conduit of the heating unit 21 is disposed inside the conduit of the third heat radiating unit 13 </ b> C of the heat pump 10. In the heating unit 21, the temperature of the water in the supply unit 20 rises due to the heat transferred from the third heat radiating unit 13 </ b> C of the heat pump 10.

  In the present embodiment, the evaporation unit 22 includes a first evaporation unit 22A and a second evaporation unit 22B in which water (warm water) from the heating unit 21 evaporates, and a branch unit 24 that separates water from the heating unit 21. A branch path 25A for guiding water from the branch section 24 to the first evaporation section 22A, a branch path 25B for guiding water from the branch section 24 to the second evaporation section 22B, and a pump 26 disposed on the branch path 25A And a pressure reducing valve 27 arranged as necessary on the branch path 25B. In addition, you may provide a deaeration apparatus between the heating part 21 and 1st and 2nd evaporation part 22A, 22B, for example. The number of evaporators 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.

  The first and second evaporators 22A and 22B have a container structure for storing water as a medium to be heated. The first and second evaporators 22A and 22B are provided with a water supply port (not shown) and a steam discharge port (not shown). A branch path 25A is fluidly connected to the supply port of the first evaporator 22A, and a duct 29A is fluidly connected to the outlet of the second evaporator 22B. The branch path 25B is fluidly connected to the supply port of the second evaporator 22B, and the duct 29B is fluidly connected to the discharge port of the second evaporator 22B. Each of the evaporation units 22A and 22B includes a level sensor (not shown) that measures the liquid level, a sensor (not shown) that measures information corresponding to the temperature of the internal water (steam), as necessary. Accordingly, a gas-liquid separator (not shown) is included. The level sensor and information from the sensor are sent to the control device 70.

  A first heat radiating portion 13A of the heat pump 10 is disposed in the first evaporation portion 22A. A second heat radiating portion 13B of the heat pump 10 is disposed in the second evaporation portion 22B. The heat from each heat radiating part 13A, 13B of the heat pump 10 is transmitted to the water in each evaporation part 22A, 22B. A second heat exchanger 42 is configured including the first evaporation section 22A and the first heat radiation section 13A. The 3rd heat exchanger 43 is comprised including the 2nd evaporation part 22B and the 2nd thermal radiation part 13B. The second and third heat exchangers 42 and 43 employ a countercurrent heat exchange system in which a low-temperature fluid (water in the supply unit 20) and a high-temperature fluid (working fluid in the heat pump 10) face each other. Can have. 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.

  In the present embodiment, the first evaporator 22 </ b> A and the second evaporator 22 </ b> B are arranged substantially in parallel with the supply unit 20. On the other hand, in the heat pump 10, along the flow direction of the working fluid, the heat exchange position with the first evaporator 22A is on the upstream side, and the heat exchange position with the second evaporator 22B is on the downstream side.

  The first and second evaporators 22 </ b> A and 22 </ b> B have different internal pressures set according to the temperature change of the working fluid in the heat radiating part of the heat pump 10. In the present embodiment, water from the heating unit 21 is supplied to the first evaporation unit 22A. On the other hand, the gas (vapor) in the second evaporator 22 </ b> B is sucked by the compressor 30. As a result, the second evaporator 22B has a lower internal pressure than the first evaporator 22A. In the present embodiment, the internal pressure of the first evaporator 22A is equal to or higher than the atmospheric pressure (1 atm = about 0.1 MPa), and the internal pressure of the second evaporator 22B is lower than the atmospheric pressure. For example, the internal pressure of the first evaporator 22A is 1.4 atmospheres (about 0.14 MPa), and the internal pressure of the second evaporator 22B is 0.7 atmospheres (about 0.07 MPa). In addition, the said numerical value is an example for an understanding, and this invention is not limited to this. In order to set the internal pressure of the first and second evaporators 22A and 22B, for example, a control valve (a flow control valve or the like, not shown) on the supply unit 20, a pump 26, a compressor 30 and the like are controlled. . This control is performed by the control device 70 based on a measurement result of a sensor (not shown) that measures the internal pressures of the first and second evaporators 22A and 22B, for example.

  5, FIG. 6, FIG. 7, and FIG. 8 schematically show changes in the temperature of the working fluid that flows through the heat radiating portions (the first heat radiating portion 13A, the second heat radiating portion 13B, and the third heat radiating portion 13C) of the heat pump 10. Show. As described above, the working fluid flows in the order of the first heat radiating portion 13A, the second heat radiating portion 13B, and the third heat radiating portion 13C.

  As shown in FIGS. 5 to 8, in this embodiment, the working fluid flowing through the heat radiating portions (the first heat radiating portion 13A, the second heat radiating portion 13B, and the third heat radiating portion 13C (see FIG. 4)) flows. The temperature decreases along the direction. That is, in the first heat radiating portion 13A, the outlet temperature t2 is lower than the inlet temperature t1 of the working fluid. In the second heat radiating portion 13B, the outlet temperature t4 is lower than the inlet temperature t3 of the working fluid. In the third heat radiating portion 13C, the outlet temperature t6 is lower than the inlet temperature t5 of the working fluid. In addition, the working fluid inlet temperature t3 in the second heat radiating portion 13B is lower than the working fluid inlet temperature t1 in the first heat radiating portion 13A, and the working fluid inlet temperature t3 in the second heat radiating portion 13B is third. The inlet temperature t5 of the working fluid in the heat radiating portion 13C is low. When the phase change of the working fluid is substantially small in the heat dissipating part of the heat pump 10, the temperature of the working fluid tends to decrease with heat dissipation. For example, when at least a part of the working fluid flowing through the heat radiating portion of the heat pump 10 is a supercritical fluid or gas, the temperature of the working fluid relatively gradually decreases with heat radiation.

  FIG. 9 schematically shows changes in the temperature of water as the medium to be heated in the supply unit 20 (see FIG. 4) in association with the temperature of the working fluid in the heat pump 10 (see FIG. 4).

  As shown in FIG. 9, in the heating unit 21 (see FIG. 4), the temperature of water from the supply source rises due to heat exchange with the working fluid (arrow m1 in FIG. 9). The water from the heating unit 21 that has flowed into the second evaporation unit 22B via the branch path 25B (see FIG. 4) is in a reduced pressure atmosphere (for example, a negative pressure environment). In the second evaporation section 22B having a relatively low internal pressure, water changes phase from liquid to vapor at a temperature near the first boiling point due to heat exchange with the working fluid (arrow m2). On the other hand, the water from the heating unit 21 flowing into the first evaporation unit 22A via the branch path 25A (see FIG. 4) is pressurized by the pump 26 and rises in temperature (arrow m3 in FIG. 9). In the first evaporation section 22A having a relatively high internal pressure, water changes phase from liquid to vapor at a temperature near the second boiling point higher than the first boiling point due to heat exchange with the working fluid (arrow m4).

  In the present embodiment, the boiling point (first boiling point) in the second evaporation part 22B (see FIG. 4) is, for example, about 90 ° C., and the boiling point (second boiling point) in the first evaporation part 22A is, for example, about 110 ° C. In the heat pump 10 (see FIG. 4), the inlet temperature of the working fluid in the first heat radiating portion 13A is, for example, about 140 ° C., and the inlet temperature of the working fluid in the second heat radiating portion 13B is, for example, about 115 ° C. In addition, the said numerical value is an example for an understanding, and this invention is not limited to this.

  According to the present embodiment, the supply unit 20 includes the two evaporation units 22A and 22B having different internal pressures in accordance with the temperature change of the working fluid in the heat radiating unit of the heat pump 10, thereby The heat balance is optimized. For example, an excessive temperature difference between the working fluid and water at the time of heat exchange is avoided throughout the heat radiating portion of the heat pump 10. As a result, the heat exchange efficiency is increased.

  In the present embodiment, similarly to the first embodiment, the heat pump has individual heating parts (heat dissipating parts) according to the state of the medium to be heated and the working fluid, thereby suppressing the input / output temperature difference and comparing with the boiler. Steam can be generated with high energy efficiency. Under the condition that the internal space of the second evaporator 22B 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 supply temperature to the heating unit 21 is about 80 ° C., and the water outlet temperature from the heating unit 21 (the water inlet temperature to the first evaporation unit 22A) is about 90 ° C. The above numerical values are examples for understanding, and the present invention is not limited thereto.

  In addition, the number of the heat radiating part of the heat pump 10 and the evaporation part of the supply unit 20 is not limited to two, and is appropriately set according to the characteristics of the working fluid. In addition, the heating unit 21 (the third heat radiating unit 13C) can be omitted, for example, when the supply temperature of water from the supply source is relatively high.

  In the present embodiment, a part of the working fluid bypasses the first heat exchanger 41 via the bypass path 17, whereby the inflow amount of the working fluid to the first heat exchanger 41 is controlled. The working fluid flowing through the bypass path 17 exchanges heat with the working fluid from the heat absorbing section 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 fluid in the bypass passage 17 is lowered (for example, about 20 ° C.), and the temperature of the working fluid in the main passage 15 of the heat pump 10 is raised (for example, about 95 ° C.). Due to the increase in the input temperature of the working fluid to the compression unit 12, the power of the compression unit 12 is reduced. Note that the bypass amount of the working fluid is determined according to each physical property value (specific heat, etc.) of the fluid to be heated and the working fluid.

  In the present embodiment, the working fluid (for example, about 20 ° C.) in the bypass passage 17 whose temperature has dropped in the regenerator 18 flows through the main passage 15 of the heat pump 10 before the expansion section 14. It merges with the working fluid from (the third heat radiating portion 13C). As described above, the output temperature of the working fluid from the first heat exchanger 41 is set to be relatively low (for example, about 30 ° C.). By reducing the input temperature of the working fluid to the expansion section 14, the liquid-gas ratio of the working fluid is optimized, and as a result, the heat source outside the cycle in the heat absorbing section 11 (medium flowing through the heat radiating pipe 91 of the cold heat supply device 90). Effectively absorbs heat.

  As described above, in the present embodiment, the working fluid after being used for water evaporation is used for warming water and regenerating the working fluid, so that the heat can be effectively used.

  Returning to FIG. 4, the first evaporator 22 </ b> A is connected to a duct 37 connected to an outlet port of the compressor 30 via a duct 29 </ b> A. The steam from the first evaporator 22A is guided to the downstream position of the compressor 30 by the duct 29A. The second evaporator 22B is fluidly connected to the inlet port of the compressor 30 via the duct 29B. As described above, the internal space of the second evaporator 22B is sucked by the compressor 30 through the duct 29B. The steam in the second evaporator 22B is guided to the compressor 30 through the duct 29B.

In this embodiment, the compressor 30, the vapor from the second evaporation unit 22 B compresses, flow pressurized steam downstream.

  In the present embodiment, the supply unit 20 further extracts the first auxiliary path 38A and the second auxiliary path 38B that extract a part of the steam from the compressor 30 and guide it to the first evaporator 22A and the second evaporator 22B, respectively. Have. One ends of the first and second auxiliary paths 38A and 38B are fluidly connected to the outlet of the compressor 30 and / or the interstage path. The other ends of the first and second auxiliary paths 38A and 38B are fluidly connected to liquid phase positions (bottom portions and the like) in the first and second evaporation sections 22A and 22B. The steam extracted from the compressor 30 is guided to the liquid phase in the first evaporator 22A. Similarly, the steam extracted from the compressor 30 is guided to the liquid phase in the second evaporator 22B. In the present embodiment, as in the first embodiment, evaporation in the first evaporation section 22A and the second evaporation section 22B is promoted by bubbling using the steam extracted from the compressor 30.

  In the present embodiment, spray tubes 48A and 48B each having a spray nozzle 45 are disposed in the first and second evaporators 22A and 22B. A branch path 25A is fluidly connected to the spray pipe 48A, and a duct 29A is fluidly connected to an outlet (not shown) provided in the first evaporator 22A. A branch path 25B is fluidly connected to the spray pipe 48B, and a duct 29B is fluidly connected to an outlet (not shown) provided in the second evaporator 22B.

  In the present embodiment, an evaporation promoting member 46 to which water from the nozzle 45 adheres is disposed in the first and second evaporators 22A and 22B. The evaporation promoting member 46 includes a net-like shape, a flat plate shape, a corrugated plate shape, a perforated plate shape in which a plurality of holes are provided in a plate-like member, a cloth plate shape in which a cloth is attached to the plate-like member, and a plurality of plate-like members. It can have various shapes such as a shape, a winding shape, and a lattice shape. The evaporation promoting member 46 can have a Raschig ring. As the evaporation promoting member 46, a large number of cylindrical members may be randomly arranged in the first and second evaporation parts 22A and 22B, or a net-like member in which a large number of metal pieces and resin pieces are arranged. May be arranged.

  In the present embodiment, water is sprayed from each spray nozzle 45 of the spray tubes 48A and 48B. The spray pattern of the nozzle 45 is appropriately set according to the specification of the steam generation system S2. The water sprayed in each evaporation part 22A, 22B adheres to the surface (outer surface) of the evaporation promotion member 46 and the conduit | pipe (tube) of each thermal radiation part 13A, 13B. The heat of the working fluid in the conduit is quickly transferred to the attached water, and the water evaporates in each of the evaporation sections 22A and 22B. By sprinkling water from the nozzle 45 and installing the evaporation promoting member 46, the gas-liquid interface (heat transfer surface, evaporation area) is expanded, and the evaporation of water in the first and second evaporators 22A and 22B is promoted. The

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

  FIG. 10 is a schematic diagram showing a steam generation system S3 according to the third embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 10, in the steam generation system S3, the first and second evaporation units 22A and 22B of the supply unit 20 respectively have tanks 47A and 47B that store water as a medium to be heated. In the present embodiment, the first and second evaporators 22A and 22B further have circulation pipes 49A and 49B fluidly connected to the tanks 47A and 47B, respectively. Each tank 47A, 47B is provided with a water supply port (not shown) and a steam discharge port (not shown). The branch path 25A is fluidly connected to the supply port of the tank 47A, and the duct 29A is fluidly connected to the discharge port of the tank 47A. The branch path 25B is fluidly connected to the supply port of the tank 47B, and the duct 29B is fluidly connected to the discharge port of the tank 47B. Each tank 47A, 47B includes a level sensor (not shown) for measuring the liquid level, a sensor (not shown) for measuring information corresponding to the temperature of the internal water (steam), as necessary. And a gas-liquid separator (not shown). The level sensor and information from the sensor are sent to the control device 70. The number of tanks is set according to the specification of the steam generation system S3, and is 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more.

  In the present embodiment, each inlet end and each outlet end of the circulation pipes 49A and 49B are fluidly connected to the tanks 47A and 47B, respectively. The number of circulation piping is set according to the specification of the steam generation system S3, and is 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. The circulation pipe 49A includes an evaporation pipe 51A that is thermally connected to the first heat radiation part 13A of the heat pump 10, a pump 52A, and a valve 53A as necessary. Similarly, the circulation pipe 49B includes an evaporation pipe 51B that is thermally connected to the second heat radiating portion 13B of the heat pump 10, a pump 52B, and a valve 53B as necessary. The valves 53A and 53B are, for example, regulators, flow rate control valves, or open / close valves. In this embodiment, the evaporation pipes 51A and 51B are fluidly connected to the tank 47A or the tank 47B independently of each other. Further, the evaporation pipes 51 </ b> A and 51 </ b> B are arranged in parallel with the supply unit 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.

  FIG. 11 shows an example of a configuration for controlling the flow rate of water in the evaporation pipe 51A. In the heat pump 10, a sensor 71 that measures the outlet temperature of the heat radiating portion 13A corresponding to the evaporation pipe 51A is provided. 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 fluid in the 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 thermal radiation parts. The evaporation pipe 51B and the corresponding heat radiation part 13B shown in FIG. 10 can also adopt the same configuration.

  Returning to FIG. 10, water in the evaporation pipe 51 </ b> A is heated by heat transfer from the heat radiating portion 13 </ b> A of the heat pump 10, and at least a part of the water evaporates. Similarly, the water in the evaporation pipe 51B is heated by heat transfer from the heat radiating part 13B of the heat pump 10, and at least a part of the water evaporates.

  Also in the present embodiment, the first and second evaporators 22 </ b> A and 22 </ b> B have mutually different internal pressures set according to the temperature change of the working fluid in the heat radiating part of the heat pump 10. That is, the internal pressure of the tank 47B is lower than the internal pressure of the tank 47A. In the present embodiment, the internal pressure of the first evaporator 22A is equal to or higher than the atmospheric pressure (1 atm = about 0.1 MPa), and the internal pressure of the second evaporator 22B is lower than the atmospheric pressure. The supply unit 20 includes two evaporation units 22A and 22B having different internal pressures in accordance with the temperature change of the working fluid in the heat radiating unit of the heat pump 10, so that the heat balance between the working fluid and water is optimized. The For example, an excessive temperature difference between the working fluid and water at the time of heat exchange is avoided throughout the heat radiating portion of the heat pump 10. As a result, the heat exchange efficiency is increased.

  Further, in the present embodiment, the supply unit 20 extracts a part of the steam from the compressor 30 and supplies it to the first evaporator 22A (first tank 47A) and the second evaporator 22B (second tank 47B), respectively. A first auxiliary path 38A and a second auxiliary path 38B are further provided. One ends of the first and second auxiliary paths 38A and 38B are fluidly connected to the outlet of the compressor 30 and / or the interstage path. The other ends of the first and second auxiliary paths 38A and 38B are fluidly connected to liquid phase positions (such as bottom portions) in the first and second tanks 47A and 47B. The steam extracted from the compressor 30 is guided to the liquid phase in the first tank 47A. Similarly, the steam extracted from the compressor 30 is guided to the liquid phase in the second tank 47A. In the present embodiment, as in the above embodiments, the first evaporator 22A (first tank 47A) and the second evaporator 22B (second tank 47B) are made by bubbling using steam extracted from the compressor 30. Evaporation is promoted.

  Moreover, in this embodiment, the evaporation promotion member 46 is arrange | positioned in the evaporation pipes 51A and 51B. The evaporation promoting member 46 includes a net-like shape, a flat plate shape, a corrugated plate shape, a perforated plate shape in which a plurality of holes are provided in a plate-like member, a cloth plate shape in which a cloth is attached to the plate-like member, and a plurality of plate-like members. It can have various shapes such as a shape, a winding shape, and a lattice shape. The evaporation promoting member 46 can have a Raschig ring. As the evaporation promoting member 46, a large number of cylindrical members may be randomly arranged in the first and second evaporation parts 22A and 22B, or a net-like member in which a large number of metal pieces and resin pieces are arranged. May be arranged.

  In the present embodiment, the flow of water (warm water) in the evaporation pipes 51A and 51B is disturbed by the evaporation promoting member 46, and heat transfer is improved. Further, by installing the evaporation promoting member 46, the gas-liquid interface (heat transfer surface, evaporation area) can be expanded. As a result, evaporation of water in the first and second evaporators 22A and 22B is promoted.

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

  FIG. 12 is a schematic diagram showing a steam generation system S4 according to the fourth embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 12, in the steam generation system S4, the compression unit 12 has a structure that compresses the working fluid 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 first heat radiation unit 13A, and a second compression unit 12B disposed between the first heat radiation unit and the second heat radiation unit. Have The number of compression stages is not limited to two. The number of compression stages can be set according to the specifications of the steam generation system. For example, the number of compression stages 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.

  The heat radiating units 13A, 13B, and 13C have a conduit through which the working fluid compressed by the compression unit 12 flows, and give the heat of the working fluid flowing in the main path 15 to a heat source outside the cycle. In the present embodiment, the first heat radiating portion 13A, the second heat radiating portion 13B, and the third heat radiating portion 13C are arranged in that order along the flow direction of the working fluid. The number of heat radiation units is set according to the specification of the steam generation system S4, and is 2, 3, 4, 5, 6, 7, 8, 9, 10, or 11 or more. In addition, when the supply temperature of the water from a supply source is comparatively high, it is also possible to abbreviate | omit the 3rd thermal radiation part 13C (heating part 21).

  FIG. 13 schematically shows the temperature change of the working fluid in the heat pump 10 and the temperature change of water as the heated medium in the supply unit 20 in the fourth embodiment.

  As shown in FIG. 13, in this embodiment, the inlet temperature t3 of the working fluid in the second heat radiating portion 13B (see FIG. 12) is higher than the outlet temperature t2 of the working fluid in the first heat radiating portion 13A (see FIG. 12). high. This is because the working fluid from the first heat radiation part 13A (see FIG. 12) is compressed by the second compression part 12B (see FIG. 12). In this embodiment, similarly to the second embodiment, the outlet temperature t2 is lower in the first heat radiating section 13A than the inlet temperature t1 of the working fluid, and the inlet temperature t3 of the working fluid in the second radiating section 13B. The outlet temperature t4 is lower than Further, the inlet temperature t3 of the working fluid in the second heat radiating portion 13B is lower than the inlet temperature t1 of the working fluid in the first heat radiating portion 13A.

  Also in the present embodiment, the first and second evaporators 22 </ b> A and 22 </ b> B have mutually different internal pressures set according to the temperature change of the working fluid in the heat radiating part of the heat pump 10. That is, the internal pressure of the second evaporator 22B is lower than the internal pressure of the first evaporator 22A. In the present embodiment, the internal pressure of the first evaporator 22A is equal to or higher than the atmospheric pressure (1 atm = about 0.1 MPa), and the internal pressure of the second evaporator 22B is lower than the atmospheric pressure. The supply unit 20 includes two evaporation units 22A and 22B having different internal pressures in accordance with the temperature change of the working fluid in the heat radiating unit of the heat pump 10, so that the heat balance between the working fluid and water is optimized. The For example, an excessive temperature difference between the working fluid and water at the time of heat exchange is avoided throughout the heat radiating portion of the heat pump 10. As a result, the heat exchange efficiency is increased.

  Furthermore, in this embodiment, the temperature of the working fluid rises due to the compression unit 12B provided between the first heat radiation unit 13A and the second heat radiation unit 13B. Since the working fluid in the heat radiating section has a multistage temperature change, the heat balance between the working fluid and water is further optimized. For example, as shown in FIG. 13, the temperature difference between the working fluid and water in the second evaporator 22B (see FIG. 12) can be set relatively large. As a result, a relatively high temperature working fluid is supplied to each of the evaporation units 22A and 22B. This is advantageous for promoting the evaporation of water.

  Further, in the present embodiment, the supply unit 20 extracts a part of the steam from the compressor 30 and guides it to the first evaporator 22A and the second evaporator 22B, respectively, the first auxiliary path 38A and the second auxiliary path 38B. It has further. One ends of the first and second auxiliary paths 38A and 38B are fluidly connected to the outlet of the compressor 30 and / or the interstage path. The other ends of the first and second auxiliary paths 38A and 38B are fluidly connected to liquid phase positions (bottom portions and the like) in the first and second evaporation sections 22A and 22B. The steam extracted from the compressor 30 is guided to the liquid phase in the first evaporator 22A. Similarly, the steam extracted from the compressor 30 is guided to the liquid phase in the second evaporator 22B. In the present embodiment, as in the above embodiments, evaporation in the first evaporator 22A and the second evaporator 22B is promoted by bubbling using the steam extracted from the compressor 30.

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

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

It is the schematic which shows 1st Embodiment. It is a 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 typically an example of the exit structure of the vapor | steam from an auxiliary path. It is a figure which shows typically an example of the exit structure of the vapor | steam from an auxiliary path. It is the schematic which shows 2nd Embodiment. It is a figure which shows typically the temperature change of the working fluid which flows through the thermal radiation part of a heat pump. It is a figure which shows typically the temperature change of the working fluid which flows through the thermal radiation part of a heat pump. It is a figure which shows typically the temperature change of the working fluid which flows through the thermal radiation part of a heat pump. It is a figure which shows typically the temperature change of the working fluid which flows through the thermal radiation part of a heat pump. It is a figure which shows typically the temperature change of the water as a to-be-heated medium in a supply unit corresponding to the temperature of the working fluid in a heat pump. It is the schematic which shows 3rd Embodiment. It is a figure which shows an example of the structure which controls the flow volume of the water in an evaporation pipe. It is the schematic which shows 4th Embodiment. It is a figure which shows typically the temperature change of the working fluid in a heat pump in 4th Embodiment, and the temperature change of the water as a to-be-heated medium in a supply unit in correlation.

Explanation of symbols

  S1, S2, S3, S4 ... steam generation system, 10 ... heat pump, 11 ... heat absorption part, 12 ... compression part, 13A-13C ... heat dissipation part, 14 ... expansion part, 15 ... main path, 17 ... bypass path, 18 ... Regenerator, 20 ... supply unit, 21 ... heating unit, 22 ... evaporating unit, 22A ... first evaporating unit, 22B ... second evaporating unit, 30 ... compressor, 38, 38A, 38 ... auxiliary path, 41-43 DESCRIPTION OF SYMBOLS ... Heat exchanger, 45 ... Nozzle, 46 ... Evaporation promotion member, 47, 47A, 47B ... Tank, 48A, 48B ... Dispersion pipe, 51A, 51B ... Evaporation pipe, 70 ... Control device.

Claims (9)

A first unit having a heat pump through which the first fluid flows ;
An evaporator that is thermally connected to the heat pump and that evaporates a second fluid; a compressor that is fluidly connected to the evaporator and compresses at least a portion of the vapor from the evaporator; and A second unit having a supplementary path for guiding a part of the compressed steam to the evaporation unit ;
Equipped with a,
The evaporation unit includes a first evaporation unit in which the vapor is not directly sucked into the compressor, and a second evaporation unit in which the vapor is directly sucked into the compressor,
The first evaporation unit conducts heat exchange with the heat pump on the upstream side in the flow direction of the first fluid, thereby leading the vapor evaporated from the second fluid to the downstream of the compressor,
The second evaporating unit performs heat exchange with the heat pump on the downstream side in the flow direction of the first fluid, thereby allowing the vapor of the second fluid evaporated at a lower temperature than the first evaporating unit to enter the compressor Leading to
The steam generation system , wherein the auxiliary path guides a part of the steam from the compressor to the first evaporator .   The steam generation system according to claim 1, wherein the compressed steam guided from the compressor to the evaporation unit is at least one of saturated steam and superheated steam. In the evaporation section, the liquid second fluid is stored at least temporarily,
The steam generation system according to claim 1, wherein the auxiliary path guides a part of the compressed steam from the compressor to a liquid phase in the evaporator.   At least one of a bubble made of the vapor introduced from the compressor and a bubble generated in the liquid phase in the evaporation unit by heat from the introduced vapor promotes evaporation of the second fluid in the evaporation unit. The steam generation system according to any one of claims 1 to 3, wherein:   The steam generation system according to any one of claims 1 to 4, wherein the second unit further includes a nozzle that sprays the liquid second fluid into the evaporation section.   6. The steam generation system according to claim 1, wherein the second unit further includes an evaporation promoting member disposed in the evaporation unit and in contact with the liquid second fluid. Before Kiho path, the vapor generation system according to any one of claims 1 to 6, characterized in that guides the steam from the compressor also before Symbol second evaporator section. The steam generation system according to any one of claims 1 to 7 , wherein the compressor compresses the steam from the second evaporation section and flows a part of the pressurized steam to the downstream side. . The first evaporation unit has an internal pressure equivalent to atmospheric pressure or an internal pressure higher than atmospheric pressure, and the second evaporation unit has an internal pressure lower than atmospheric pressure. steam generating system according to claim 8.

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