JP4853125B2 - Steam generation system - Google Patents

Description

  The present invention relates to a steam generation system.

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

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

  This invention is made | formed in view of the situation mentioned above, and aims at providing a steam generation system with high energy efficiency.

  The steam generation system of the present invention is a heat pump through which a working medium flows, a supply path through which a medium to be heated flows, and the supply path having a plurality of evaporation pipes through which the medium to be heated evaporates by heat transfer from the heat pump; It is characterized by providing.

  According to this steam generation system, high energy efficiency can be obtained by using a heat pump as compared with a boiler. In this steam generation system, since the supply path has a plurality of evaporation pipes, the controllability of the evaporation process of the heated medium can be improved.

  In this steam generation system, the supply path may have a tank that stores the medium to be heated and is fluidly connected to the plurality of evaporation pipes.

  In this case, the tank may have a plurality of individual tanks corresponding to the plurality of evaporation pipes.

  In this steam generation system, the supply path may have a flow rate control unit that controls the flow rate of the heated medium in each of the plurality of evaporation pipes.

  In this steam generation system, the heat pump may have a plurality of heat radiation portions corresponding to the plurality of evaporation tubes.

  In this steam generation system, the heat pump may have a structure that compresses the working medium in multiple stages.

  In this steam generation system, the heat pump can be configured to have a heating heat dissipation unit that heats the heated medium before the heated medium flows into the plurality of evaporation tubes.

  In this steam generation system, the heat pump may include a regenerator that preheats the working medium before the working medium is compressed.

  In this steam generation system, it is preferable that the internal pressure of the plurality of evaporation pipes is lower than the atmospheric pressure.

  The steam generation system may further include a compressor that is disposed at a downstream position of the plurality of evaporation pipes on the supply path and compresses the heated medium.

  In this case, the medium to be heated in the evaporation pipe becomes steam at a relatively low pressure and low temperature by heat transfer from the heat pump, and becomes steam at a relatively high pressure and temperature by compression by the compressor. it can.

  The steam generation system may further include a nozzle that supplies the liquid medium to be heated to the vapor of the medium to be heated.

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

  FIG. 1 is a schematic view showing a steam generation system according to the first embodiment. In FIG. 1, the steam generation system S <b> 1 includes a heat pump 10, a heating medium (water) supply path 20, and a compressor 30. 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. Heat pumps generally have the advantage of being relatively high in energy efficiency and, as a result, relatively low in emissions of carbon dioxide and the like and being environmentally friendly.

  Specifically, the heat pump 10 includes a heat absorbing part 11, a compressing part 12, a heat radiating part (first heat radiating part 13A, second heat radiating part 13B, third heat radiating part 13C, fourth heat radiating part 13D, fifth heat radiating part 13E), And the expansion part 14 is provided, and these are connected via piping.

  In the heat absorption part 11, the working medium flowing in the main path 15 absorbs heat from a heat source outside the cycle (for example, the atmosphere). The compression unit 12 compresses the working medium using a compressor or the like. At this time, the temperature of the working medium usually increases.

  In the present embodiment, the compression unit 12 has a structure for compressing the working medium in multiple stages. The compression unit 12 illustrated in FIG. 1 has a four-stage compression structure including a first compression unit 12A, a second compression unit 12B, a third compression unit 12C, and a fourth compression unit 12D. The number of stages of compression is set according to the specification of the steam generation system S1, and is 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. 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 unit 12 can have a multiaxial compression structure in which the rotation speeds corresponding to the compression units 12A, 12B, 12C, and 12D 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, 12C, 12D is set according to the specification of the steam generation system S1.

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

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

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

  In the regenerator 18, 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 (the pipe between the heat absorption part 11 and the compression part 12) are arranged adjacent to each other. It has a configuration. In the heat pump 10, the working medium from the fourth heat radiating unit 13 </ b> D is hotter than the working medium from the heat absorbing unit 11. In the regenerator 18, the working medium from the fourth heat radiating unit 13 </ b> D flowing through the bypass path 17 and the working medium from the heat absorbing unit 11 flowing through the main path 15 of the heat pump 10 exchange heat. By this heat exchange, the temperature of the working medium in the bypass path 17 is lowered, and the temperature of the working medium in the main path 15 is raised. The regenerator 18 may have a countercurrent heat exchange system in which a low-temperature fluid (a working medium in the main path 15) and a high-temperature fluid (a working medium in the bypass path 17) face each other. 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 disposed adjacent to the fifth heat radiation 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 5th 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. 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. As the heat exchange structure of the first heat exchanger 41, various known ones can be adopted. For example, the pipe of the fifth heat radiating part 13 </ b> E of the heat pump 10 can be arranged on the outer peripheral surface or inside of the pipe of the heating part 21. In the heating unit 21, the temperature of water in the supply path 20 rises due to heat transfer from the fifth heat radiating unit 13 </ b> E of the heat pump 10.

  The evaporating unit 22 includes a tank 47 that stores at least a liquid heated medium (water), and circulation pipes fluidly connected to the tank 47 (first circulation pipe 48A, second circulation pipe 48B, and third circulation pipe 48C). 4th circulation piping 48D). The tank 47 is provided with a water supply port from the 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 the present embodiment, each circulation pipe 48 </ b> A, 48 </ b> B, 48 </ b> C, 48 </ b> D is fluidly connected to one tank 47. That is, each inlet end and each outlet end of the circulation pipes 48 </ b> A to 48 </ b> D are fluidly connected to the tank 47. The number of circulation piping 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 arrange | positioned adjacent to the 1st thermal radiation part 13A of the heat pump 10, and the pump 52A as needed. Similarly, the 2nd circulation piping 48B has the evaporation pipe | tube 51B arrange | positioned adjacent to the 2nd thermal radiation part 13B of the heat pump 10, and the pump 52B as needed. The third circulation pipe 48 </ b> C includes an evaporation pipe 51 </ b> C disposed adjacent to the third heat radiation part 13 </ b> C of the heat pump 10 and a pump 52 </ b> C as necessary, and the fourth circulation pipe 48 </ b> D is the fourth circulation pipe 48 </ b> D. It has the evaporation pipe 51D arrange | positioned adjacent to the thermal radiation part 13D, and the pump 52D as needed. In the present embodiment, the evaporation pipes 51 </ b> A to 51 </ b> D are individually fluidly connected to the tank 47. The evaporation pipes 51 </ b> A to 51 </ b> D are arranged in parallel to the tank 47 and the supply path 20. At least one of the pumps 52A to 52D may be omitted by using thermal convection of the medium to be heated (water) and / or differential pressure with the outside.

  A second heat exchanger 42 is configured including the evaporation pipe 51A and the first heat radiation part 13A. Similarly, the 3rd heat exchanger 43 is comprised including the evaporation pipe | tube 51B and the 2nd thermal radiation part 13B. A fourth heat exchanger 44 is configured including the evaporation pipe 51C and the third heat radiating portion 13C, and a fifth heat exchanger 45 is configured including the evaporation pipe 51D and the fourth heat radiating portion 13D. The second to fifth heat exchangers 42 to 45 are counter-current heat exchanges in which a low-temperature fluid (water in the evaporation pipes 51A to 51D) and a high-temperature fluid (working fluid in the heat pump 10) face each other. You can have a scheme. 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. 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 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 to 48 </ b> D. 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 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. 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 (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 the tank 47 are fluidly connected via the pipe 36 can be configured. 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. Control valves (such as a flow control valve, not shown) and the compressor 30 on the supply path 20 are controlled so that the internal pressure of the tank 47 becomes a negative pressure (negative pressure) lower than the atmospheric pressure. 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 when the internal space of the tank 47 is in a negative pressure state. The coefficient of performance of the heat pump 10 changes according to the difference between the input temperature and the output temperature of the medium to be heated (water), and if the temperature difference is excessively large, the coefficient of performance (COP) may decrease. Under the condition that the internal space of the tank 47 is in a negative pressure state, the heating temperature region (input / output temperature difference) is set to be relatively narrow, and the heat pump 10 can be used at a high COP. For example, the input temperature of water is about 20 ° C., and the output temperature of water from the evaporator 22 is about 90 ° C.

  Thus, in this 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, the temperature of the water in the supply path 20 rises to near the boiling point by heat transfer from the fifth heat radiating portion 13E of the heat pump 10. Thereafter, in the second to fifth heat exchangers 42 to 45, the water undergoes phase change and evaporates by heat transfer from the first to fourth heat radiating units 13A to 13D. That is, the sensible heat of water is performed in the first heat exchanger 41, and the latent heat of water is heated in the second to fifth heat exchangers 42 to 45. As a result, the apparatus configuration can be optimized such that the first heat exchanger 41 is in a form suitable for sensible heat exchange, and the second to fifth heat exchangers 42 to 45 are in form suitable for latent heat exchange. In response, steam is generated through a preferred heating process.

  The energy efficiency of the boiler is generally about 0.8 (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, steam can be generated with higher energy efficiency than a boiler because the heat pump has individual heating units corresponding to sensible heat exchange and latent heat exchange.

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

FIG. 2 is a Ts diagram illustrating an example of a state change of water by the steam generation system S1. As shown in FIG. 2, after the temperature rises to near the boiling point in the first heat exchanger 41 (see FIG. 1), water undergoes a phase change in the second to fifth heat exchangers 42 to 45 while the temperature remains constant. At this time, saturated steam d ₀ is generated in a state of negative pressure P ₀ that is lower than atmospheric pressure (P ₁ = 1 atm = about 0.1 MPa). Temperature of saturated steam d ₀ is lower than the standard boiling point, such as about 90 ° C..

Next, the saturated steam d ₀ becomes relatively high-pressure and high-temperature steam (superheated steam e ₂ ) by compression by the compressor 30 (see FIG. 1). That is, the temperature of the steam rises with the compression. The pressure _{P 2} of the superheated steam _{e 2} is greater than atmospheric pressure, for example, 0.8 MPa.

A saturated steam of about 160 ° C. can be obtained by cooling the superheated steam e _{2 of} 0.8 MPa under a constant pressure (dashed line a in FIG. 2). Similarly, saturated steam d ₁ 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.

Further, by optimizing the supply amount and timing of water or hot water, the change from the relatively low pressure and low temperature saturated steam d ₀ to the relatively high pressure and high temperature saturated steam d ₂ 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 d ₀ at the inlet of the compressor 30 changes to saturated steam d ₂ 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 d ₀ at the inlet of the compressor 30 becomes saturated steam at the outlet of the compressor 30. changes to d ₂ (dashed 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 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.

  Further, in this embodiment, since the compressor 30 compensates for a part of the heating process for generating steam, the heat pump 10 is used with a high COP. Therefore, the steam generation system S1 has an overall reduction in primary energy. 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 heat exchanger 41 and the second heat exchanger 42 (third to fifth heat exchangers 43 to 45).

  The working medium flowing through the bypass path 17 exchanges heat with the working medium from the heat absorbing unit 11 flowing through the main path 15 of the heat pump 10 in the regenerator 18. By this heat exchange, the temperature of the working medium in the bypass path 17 is lowered (for example, about 20 ° C.), and the temperature of the working medium in the main path 15 of the heat pump 10 is raised (for example, about 95 ° C.). Due to the increase in the input temperature of the working medium to the compression unit 12, the power of the compression unit 12 is reduced.

  Note that the amount of bypass of the working medium is determined according to each physical property value (such as specific heat) of the medium to be heated and the working medium. When the medium to be heated is water and the working medium is a chlorofluorocarbon medium or ammonia, the bypass amount is set to the flow rate per unit time of the working medium in the second to fifth heat exchangers 42 to 45. The molar ratio is preferably about 50%. In this case, the heat balance between water and the working medium is good in each of sensible heat and latent heat. Furthermore, the heat balance between the working media in the regenerator 18 is good.

  In the present embodiment, the working medium (for example, about 20 ° C.) in the bypass passage 17 whose temperature has dropped in the regenerator 18 is in front of the expansion unit 14 and flows through the main passage 15 of the heat pump 10. It merges with the working medium from the (fifth heat radiation part 13E). As described above, the output temperature of the working medium from the first heat exchanger 41 is set to be relatively low (for example, about 30 ° C.). The liquid gas ratio of the working medium is optimized by the decrease in the input temperature of the working medium to the expansion unit 14, and as a result, the heat absorption unit 11 effectively absorbs heat from a heat source (for example, the atmosphere) outside the cycle.

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

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

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

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

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

  FIG. 3 shows an example of a configuration for controlling the flow rate of water in the evaporation pipe 51A. The heat pump 10 is provided with a sensor 71 that measures the outlet temperature of the first heat radiating portion 13A corresponding to the evaporation pipe 51A. The control device 70 controls the flow rate of water per unit time flowing through the evaporation pipe 51A via the pump 52A for the evaporation pipe 51A based on the measurement result of the sensor 71. Thereby, the exit temperature of the working medium in the first heat radiating portion 13A can be set to the target value. You may use the sensor 72 which measures the inlet_port | entrance temperature of 13 A of 1st thermal radiation parts. In FIG. 1, the other evaporation pipes 51 </ b> B to 51 </ b> D and the corresponding heat radiation portions 13 </ b> B to 13 </ b> D can adopt the same configuration.

  FIG. 4 is a schematic view showing a steam generation system according to the second embodiment. In the following description, for the steam generation system S2, the same components as those in the steam generation system S1 of the first embodiment shown in FIG. 1 are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 4, in the steam generation system S2, unlike the first embodiment, 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 heat pump 10 is the same as that of the first 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 evaporating unit 22 fluidizes the tanks (first tank 47A, second tank 47B, third tank 47C, fourth tank 47D) for storing at least a liquid heated medium (water), and each of the tanks 47A to 47D. It has connected circulation piping (the 1st circulation piping 48A, the 2nd circulation piping 48B, the 3rd circulation piping 48C, and the 4th circulation piping 48D). Each of the tanks 47A to 47D is provided with a water supply port from the heating unit 21 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 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 tubes 51 </ b> A to 51 </ b> D is arranged in parallel with the supply path 20.

  In the supply path 20, the water whose temperature has risen in the heating unit 21 is branched and supplied to the tanks 47 </ b> A to 47 </ b> D, and water is stored in the tanks 47 </ b> A to 47 </ b> D and the circulation pipes 48 </ b> A to 48 </ b> D. 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 the present embodiment, as in the first embodiment, the water in the supply path 20 becomes steam at a relatively low pressure and low temperature due to heat transfer from the heat pump 10 (heat radiation units 13A to 13E), and the compressor 30 It becomes a steam of relatively high pressure and high temperature by compression by. The steam from the steam generation system S2 is supplied to a predetermined external facility such as a manufacturing plant, a cooking facility, an air conditioning facility, a power generation 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.

  The numerical values used in the above description and the temperatures described in the drawings are examples, and the present invention is not limited thereto.

  The preferred embodiments of the present invention have been described above, but the present invention is not limited to these embodiments. 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 the steam generation system concerning 1st Embodiment. It is a Ts diagram which shows an example of the state change of the water by a steam generation system. An example of the structure which controls the flow volume of the water in an evaporation pipe is shown. It is the schematic which shows the steam generation system concerning 2nd Embodiment.

Explanation of symbols

S1, S2 ... Steam generation system, 10 ... Heat pump, 11 ... Heat absorption part, 12 ... Compression part, 13A ... First heat radiation part, 13B ... Second heat radiation part, 13C ... Third heat radiation part, 13D ... Fourth heat radiation part, 13E ... 5th heat dissipation part, 14 ... Expansion part, 15 ... Main path, 17 ... Bypass path, 18 ... Regenerator, 20 ... Supply path, 21 ... Heating part, 22 ... Evaporation part, 23 ... Duct, 30 ... Compression 35, nozzle, 41-45, heat exchanger, tank ... 47, 47A ... first tank, 47B ... second tank, 47C ... third tank, 47D ... fourth tank, 48A-48D ... circulation piping, 50 ... level sensors, 51A to 51D ... evaporating tubes, 70 ... control devices, 71, 72 ... sensors.

Claims (12)

A heat pump through which the working medium flows;
A supply path through which the medium to be heated flows, the supply path having a plurality of evaporation pipes in which the medium to be heated evaporates by heat transfer from the heat pump;
Equipped with a,
The heat pump has a compression unit that compresses the working medium in multiple stages,
Wherein said each of the plurality of evaporation tubes by the heat from a plurality of heat radiating portion disposed between the stages of compression section heated medium is latent heating steam generating system according to claim Rukoto.   The steam generation system according to claim 1, wherein the supply path has a tank that stores the medium to be heated and is fluidly connected to the plurality of evaporation pipes.   The steam generation system according to claim 2, wherein the tank has one tank to which the plurality of evaporation pipes are fluidly connected. The tank, have a plurality of individual tanks corresponding to the plurality of evaporation pipes,
The steam generation system according to claim 2, wherein internal spaces of the plurality of individual tanks are connected to each other . The steam generation system according to any one of claims 1 to 4 , wherein the supply path includes a flow rate control unit that controls a flow rate of the heated medium in each of the plurality of evaporation pipes. The heat pump, steam generating system according to any of claims 1 5, characterized in that it comprises a plurality of heat radiation portions corresponding to the plurality of evaporation pipes.   The said heat pump has a thermal radiation part for a heating which heats the said to-be-heated medium before the inflow of the to-be-heated medium to these several evaporation pipes. Steam generation system.   The steam generation system according to claim 1, wherein the heat pump includes a regenerator that preheats the working medium before the working medium is compressed.   The steam generation system according to claim 1, wherein an internal pressure of the plurality of evaporation pipes is lower than an atmospheric pressure.   The steam generation system according to any one of claims 1 to 9, further comprising a compressor that is disposed downstream of the plurality of evaporation pipes on the supply path and compresses the medium to be heated.   The medium to be heated in the evaporation pipe becomes steam at a relatively low pressure and low temperature by heat transfer from the heat pump, and becomes steam at a relatively high pressure and high temperature by compression by the compressor. The steam generation system according to claim 10.   The steam generation system according to any one of claims 1 to 11, further comprising a nozzle that supplies the liquid to-be-heated medium with respect to the steam of the medium to be heated.

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