JP5223937B2 - 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 is providing the steam generation system with high energy efficiency.

  The steam generation system of the present invention includes a supply path for a medium to be heated and a heat pump, and the heat pump includes a heat absorption part, a compression part, a first heat radiation part, a second heat radiation part arranged in the flow direction of the working medium, and It has an expansion part, and the 2nd heat dissipation part and the 1st heat dissipation part heat the medium to be heated in the supply path in that order.

  According to the steam generation system of the present invention, high energy efficiency can be obtained by using a heat pump as compared with a boiler. Moreover, in this steam generation system, since the heat pump has a plurality of heating parts (first heat radiating part and second heat radiating part) for heating the heated medium in stages, the heating process of the heated medium and the configuration of the heat pump Optimization is achieved.

  In the steam generation system of the present invention, the heated medium in the supply path rises in temperature to near the boiling point due to heat from the second heat radiating portion, and changes in phase by heat from the first heat radiating portion to become steam. It can be configured.

  In the steam generation system of the present invention, the heat pump may further include a bypass path in which a part of the working medium from the first heat radiating part bypasses the second heat radiating part.

  In this configuration, the bypass path has an inlet end connected between the first heat radiating part and the second heat radiating part in the main path of the heat pump, and an outlet end of the second heat radiating part in the main path of the heat pump. And the expansion part.

  The heat pump may further include a regenerator that heats the working medium from the heat absorbing section by the working medium in the bypass path.

  In addition, the regenerator can be arranged between the heat absorption part and the compression part in the heat pump.

  In the steam generation system of the present invention, the compression section has a structure for compressing the working medium in multiple stages, and the second heat radiation section, the first heat radiation section, and the interstage heat radiation section of the compression section are in that order. The heating medium in the supply path can be heated.

  In the steam generation system of the present invention, the medium to be heated may be water, and the working medium may be ammonia or a fluorocarbon medium.

  The steam generation system of the present invention can be configured to further include a compressor that is disposed on the supply path and compresses the heated medium heated by the heat pump.

  In this configuration, the medium to be heated in the supply path becomes steam at a relatively low pressure and low temperature when heated by the heat pump, and becomes a steam at a relatively high pressure and high temperature when compressed by the compressor. Can be.

  Further, the internal pressure at the heating part by the heat pump in the supply path can be made lower than the atmospheric pressure.

  Further, the medium to be heated in the supply path becomes saturated steam at a negative pressure lower than atmospheric pressure by heating with the heat pump, and steam at atmospheric pressure or pressure higher than atmospheric pressure by compression by the compressor. Can be.

  Moreover, the internal space in the heating site | part by the said heat pump in the said supply path | route can be decompressed by the said compressor.

  Moreover, the nozzle which supplies the said liquid to-be-heated medium with respect to the vapor | steam of the said to-be-heated medium can be further provided.

It is the schematic which shows 1st Embodiment of the steam generation system which concerns on this invention. It is a Ts diagram which shows an example of the state change of the water by a steam generation system. It is the schematic which shows 2nd Embodiment of the steam generation system which concerns on this invention. It is a graph which shows typically an example of the temperature change of the to-be-heated medium and the working medium of a heat pump accompanying heat exchange. It is a graph which shows typically an example of the temperature change of the to-be-heated medium and the working medium of a heat pump accompanying heat exchange. It is a Ts diagram which shows an example of the state change of the working medium of a heat pump. It is a Hs diagram which shows an example of the state change of the working medium of a heat pump. It is 3rd Embodiment of the steam generation system which concerns on this invention, and is a modification of the steam generation system of FIG. It is 4th Embodiment of the steam generation system which concerns on this invention, and is another modification of the steam generation system of FIG. It is 5th Embodiment of the steam generation system which concerns on this invention, and is another modification of the steam generation system of FIG.

  Hereinafter, a steam generation system according to the present invention will be described with reference to the drawings.

FIG. 1 is a schematic view showing a first embodiment of a steam generation system according to the present invention.
In FIG. 1, the steam generation system S <b> 1 includes a heat pump 10, a heating medium (water in this example) supply path 20, and a compressor 30.

  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 absorption part 11, a compression part 12, a heat radiation part (first heat radiation part 13A, second heat radiation part 13B), and an expansion part 14, which are sequentially connected via a pipe. Yes. In the heat absorption part 11, the working medium flowing in the main path 15 absorbs heat from a heat source (for example, air) outside the cycle. 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. Power is supplied to the compression unit 12. The heat radiating parts 13A and 13B include a pipe through which a high-temperature working medium from the compressing part 12 flows. Further, the heat radiating portions 13A and 13B are arranged in series in that order in the flow direction of the working medium, and give heat of the working medium flowing in the main path 15 to a heat source outside the cycle. 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 media such as ammonia, a fluorocarbon medium, water, carbon dioxide, and air are applied.

  The supply path 20 includes a heating unit 21, an evaporation unit 22, and a duct 23 that connects the evaporation unit 22 and the compressor 30.

  The heating unit 21 includes a pipe through which water from a supply source flows, and is disposed adjacent to the second heat radiating unit 13B of the heat pump 10. The 1st heat exchanger 40 is comprised including the heating part 21 and the 2nd thermal radiation part 13B. In this example, the first heat exchanger 40 has a countercurrent heat exchange structure 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. However, the first heat exchanger 40 may have a parallel flow type heat exchange structure in which a high-temperature fluid and a low-temperature fluid flow in parallel. In the heating unit 21, the temperature of the water in the supply path 20 rises due to the heat from the second heat radiating unit 13 </ b> B of the heat pump 10.

The evaporation unit 22 includes a tank 47 for storing a liquid medium to be heated (water) and a circulation pipe 48.
The tank 47 or the circulation pipe 48 is provided with a water supply port from the heating unit 21 and a steam discharge port. The inlet end and the outlet end of the circulation pipe 48 are each connected to the tank 47. At least a part of the circulation pipe 48 is disposed adjacent to the first heat radiating portion 13 </ b> A of the heat pump 10. The 2nd heat exchanger 41 is comprised including the circulation piping 48 and 13 A of 1st thermal radiation parts. The second heat exchanger 41 has a countercurrent heat exchange structure in which a low-temperature fluid (water in the circulation pipe 48) and a high-temperature fluid (working fluid in the heat pump 10) face each other, or a high-temperature fluid It has a parallel flow type heat exchange structure in which a low-temperature fluid flows in parallel. A configuration in which the first heat radiating portion 13 </ b> A of the heat pump 10 is disposed on the outer peripheral surface or inside of the circulation pipe 48 may be employed. In the tank 47, a gas-liquid separator 49 is disposed adjacent to the outlet end of the circulation pipe 48 as necessary.

  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. 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 sensor (not shown) that measures the liquid level in the tank 47. Water is stored in the tank 47 and the circulation pipe 48, and the water in the circulation pipe 48 is heated by the first heat radiating portion 13A of the heat pump 10. With this heating, water (and steam) flows through the circulation pipe 48. 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 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, at least one of an inlet and 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. A pipe configuration in which the nozzle 35 and the liquid phase position of the tank 47 are connected via a pipe 36 can also be used. In this pipe configuration, the liquid in the tank 47 having a relatively high temperature is effective for supplying the nozzle 35. Used. 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 pipe 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. In this example, 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.

  In such a steam generation system S <b> 1, the water in the supply path 20 becomes steam by heating by the heat pump 10. Specifically, the temperature of the water in the supply path 20 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 40, and then the first heat exchanger 41 in the first heat exchanger 41. The water undergoes a phase change and evaporates due to heat from the heat radiating portion 13A. That is, sensible heat heating and latent heat heating of water are performed stepwise by separate heat exchangers 40 and 41 (heat radiation portions 13A and 13B).

  Therefore, according to this steam generation system S1, the 1st heat exchanger 40 containing the 2nd heat sink 13B is a form suitable for sensible heat exchange, and the 2nd heat exchanger 41 containing the 1st heat sink 13A is latent heat. The configuration of the apparatus is optimized such that the form is suitable for replacement, and 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. As described above, 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 the steam generation system S1, steam can be generated with higher energy efficiency than a boiler because the heat pump has individual heating parts (heat radiation parts 13A and 13B) corresponding to sensible heat exchange and latent heat exchange.

  Further, in the steam generation system S1, the water in the supply path 20 becomes steam having a relatively low pressure and low temperature by heating by the heat pump 10 (heat radiation units 13A and 13B), and relatively high pressure by compression by the compressor 30. 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, the temperature of the water changes to near the boiling point in the first heat exchanger 40 (see FIG. 1), and then changes in phase in the second heat exchanger 41 while keeping the temperature constant. At this time, saturated steam d0 is generated in a state of negative pressure P0 that is lower than atmospheric pressure (P1 = 1 atm = about 0.1 MPa). The temperature of the saturated vapor d0 is lower than the normal boiling point, for example, about 90 ° C.

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

  A saturated steam of about 160 ° C. can be obtained by cooling the superheated steam e2 of 0.8 MPa under a constant pressure (dashed line a in FIG. 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.

  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.

  Furthermore, by optimizing the supply amount and timing of water or hot water, the change from the relatively low pressure and low temperature saturated steam d0 to the relatively high pressure and high temperature saturated steam d2 can be made more direct. For example, when an appropriate amount of water or hot water is supplied to the steam at the inlet and / or in the middle of the compressor 30, the saturated steam d0 at the inlet of the compressor 30 changes to the saturated steam d2 at the outlet of the compressor 30. (Dotted 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 saturation can be discharged from the compressor 30.

  Thus, in the steam generation system S1, both saturated steam and superheated steam can be easily generated by the three-stage sequential heating including the two-stage heating by the heat pump 10 and the heating by the compressor 30. 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.

  Furthermore, since the compressor 30 supplements part of the heating process for steam generation in the steam generation system S1, the heat pump 10 is used at a high COP. Therefore, the steam generation system S1 is an overall primary energy saving. There is expected. That is, according to the steam generation system S1, the compressor 30 is used to heat the medium to be heated (water) in a relatively high temperature range, so that the temperature rise is shortened compared to heating by heat transfer. And it is advantageous for suppressing heat loss.

FIG. 3 is a schematic view showing a second embodiment of the steam generation system according to the present invention.
In FIG. 3, the steam generation system S <b> 2 includes a heat pump 50, a heating medium (water in this example) supply path 20, and a multistage compression unit 60.
The configuration of the supply path 20 is the same as that of the steam generation system S1 of FIG. The heat pump 50 includes a bypass path 51 and a regenerator 52 in addition to the same configuration as the heat pump 10 of FIG. In the following description, for the steam generation system S2, the same components as those in the steam generation system S1 in FIG. 1 are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  The inlet end of the bypass path 51 is connected to a pipe between the first heat radiating part 13A and the second heat radiating part 13B in the main path 15 of the heat pump 50, and the outlet end is the second heat radiating part 13B and the expansion part 14 in the main path 15. Connected to the pipe between. A flow rate control valve that controls the bypass flow rate of the working medium may be disposed at the inlet of the bypass path 51. In the bypass path 51, a part of the working medium from the first heat radiating unit 13 </ b> A bypasses the second heat radiating unit 13 </ b> B and merges with the working medium from the first heat radiating unit 13 </ b> A before the expansion unit 14. The remaining working medium from the first heat dissipating part 13A flows through the second heat dissipating part 13B, and the working medium and water in the supply path 20 exchange heat in the first heat exchanger 40.

  The regenerator 52 has a configuration in which a pipe of the bypass path 51 and a pipe of the main path 15 of the heat pump 50 (a pipe between the heat absorption unit 11 and the compression unit 60) are arranged adjacent to each other. In the heat pump 50, the working medium from the first heat radiating unit 13 </ b> A is hotter than the working medium from the heat absorbing unit 11. In the regenerator 52, the working medium from the first heat radiating portion 13 </ b> A flowing through the bypass path 51 and the working medium from the heat absorbing section 11 flowing through the main path 15 of the heat pump 50 exchange heat. By this heat exchange, the temperature of the working medium in the bypass path 51 is lowered, and the temperature of the working medium in the main path 15 is raised. The regenerator 52 has a countercurrent heat exchange structure in which a low-temperature fluid (a working medium in the main passage 15) and a high-temperature fluid (a working fluid in the bypass passage 51) face each other, or a high-temperature fluid. And a parallel flow type heat exchange structure in which a low-temperature fluid flows in parallel.

  The compression unit 60 has a structure for compressing the working medium in multiple stages. The number of stages may be two or three or more. A circulation pipe 48 of the evaporation unit 22 in the water supply path 20 and an interstage heat radiation unit 61 of the multistage compression unit 60 are arranged adjacent to each other. The 2nd heat exchanger 65 is comprised including the circulation piping 48, the interstage heat radiation part 61 of the compression part 60, and the 1st heat radiation part 13A. The second heat exchanger 65 has a countercurrent heat exchange structure in which a low-temperature fluid (water in the circulation pipe 48) and a high-temperature fluid (working fluid in the heat pump 50) face each other, or a high-temperature fluid It has a parallel flow type heat exchange structure in which a low-temperature fluid flows in parallel.

  In such a steam generation system S2, the second heat radiation part 13B, the first heat radiation part 13A, and the interstage heat radiation part 61 of the compression part 60 heat the water in the supply path 20 in that order. Specifically, the temperature of the water in the supply path 20 rises to near the boiling point by the heat from the second heat radiating portion 13B of the heat pump 50 in the first heat exchanger 40, and then the first heat exchanger 65 makes the first heat in the second heat exchanger 65. The water undergoes a phase change and evaporates due to heat from the heat radiating unit 13A and heat from the interstage heat radiating unit 61 of the compression unit 60. That is, sensible heat heating and latent heat heating of water are performed in stages by separate heat exchangers 40 and 65, respectively. On the other hand, the working medium undergoes a phase change from vapor to liquid while maintaining a constant temperature by heat exchange with water, and thereafter the temperature drops.

  Since a part of the working medium bypasses the first heat exchanger 40 via the bypass path 51, the flow rate of the working medium entering the first heat exchanger 40 is optimized. This is advantageous in effectively using the retained heat of the working medium, as will be described next.

4 and 5 are graphs schematically showing an example of a temperature change between the medium to be heated and the working medium of the heat pump accompanying heat exchange. FIG. 4 is a graph showing the previous steam generation system S1 (FIG. 1). Correspondingly, FIG. 5 corresponds to the steam generation system S2 (FIG. 3). In this example, the medium to be heated is water (H ₂ O), and the working medium is ammonia (NH ₃ ).

  As shown in FIG. 4 and FIG. 5, water rises in temperature to near the boiling point by heat exchange with ammonia, and then changes in phase from liquid to vapor while keeping the temperature constant. For example, the input temperature of water is about 20 ° C and the output temperature is about 90 ° C. Ammonia undergoes a phase change from vapor to liquid with a constant temperature due to heat exchange with water, and then drops in temperature.

  As shown in FIG. 4, in the previous steam generation system S1, since substantially the same amount of ammonia is used for heat exchange between the water temperature rise process (sensible heat) and the phase change process (latent heat), In order to avoid the reversal of temperature between water and ammonia (broken line in FIG. 4), the output temperature of ammonia needs to be a certain value or higher. This is because the heat of evaporation of water is larger than that of ammonia. In the previous steam generation system S1, for example, the ammonia inlet temperature is set to about 100 ° C. and the outlet temperature is set to about 80 ° C.

  On the other hand, as shown in FIG. 5, in the steam generation system S2, a part of the ammonia bypasses the downstream heat exchanger (first heat exchanger 40) with respect to the flow direction of ammonia. Thus, the output temperature of ammonia can be lowered. That is, the required amount of ammonia is optimized for each process of water temperature rise (sensible heat) and phase change (latent heat). In the steam generation system S2, for example, the inlet temperature of ammonia is set to about 100 ° C., and the outlet temperature is set to about 30 ° C.

  Returning to FIG. 3, in the steam generation system S <b> 2, a part of the working medium bypasses the first heat exchanger 40 via the bypass path 51, whereby the amount of working medium flowing into the first heat exchanger 40 is controlled. As a result, each of the first heat exchanger 40 and the second heat exchanger 65 is supplied with a working medium having a heat amount as required.

  The working medium flowing through the bypass path 51 exchanges heat with the working medium from the heat absorbing unit 11 flowing through the main path 15 of the heat pump 50 in the regenerator 52. By this heat exchange, the temperature of the working medium in the bypass passage 51 is lowered (for example, about 20 ° C.), and the temperature of the working medium in the main passage 15 of the heat pump 50 is raised (for example, about 95 ° C.). Due to the increase in the input temperature of the working medium to the compression unit 60, the power of the compression unit 60 is reduced.

  The bypass amount of the working medium is determined according to each physical property value (specific heat, etc.) of the medium to be heated and the working medium. When the medium to be heated is water and the working medium is ammonia, the bypass amount is preferably about 50% in terms of molar ratio with respect to the amount of working medium supplied to the second heat exchanger 65. In this case, as shown in FIG. 5, the heat balance between water and ammonia is good in both sensible heat and latent heat. Furthermore, since the specific heat of the liquid phase of ammonia is about twice that of the gas phase, the heat balance between the ammonia in the regenerator 52 is good. The same applies to the case where a chlorofluorocarbon medium is used instead of ammonia.

  The working medium (for example, about 20 ° C.) in the bypass passage 51 whose temperature has dropped by the regenerator 52 is in front of the expansion section 14 and flows through the main path 15 of the heat pump 50 (first heat exchanger 40 (second heat radiation section 13B)). From the working medium. As described above, the output temperature of the working medium from the first heat exchanger 40 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.

  Thus, according to the steam generation system S2, since the working medium after being used for water evaporation is used for warming the water and regenerating the working medium, the heat can be effectively used. The system S2 has high energy efficiency compared to the steam generation system S1.

  Further, in the steam generation system S2, the compression unit 60 is a multistage type, and the energy efficiency is also improved in that the working medium and water exchange heat in the interstage heat radiation unit 61 of the compression unit 60. That is, the heat of the interstage heat radiating unit 61 of the multistage compression unit 60 is deprived, thereby suppressing the temperature increase of the working medium during the compression process of the working medium. As a result, the compression efficiency of the compression unit 60 is improved and The power of the compressor can be reduced. The number of repetitions of the temperature rise of the working medium accompanying compression and the temperature drop of the working medium in the interstage heat radiating section 61 (the number of reheating stages) may be two or three 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.

  FIG. 6 is a Ts diagram showing an example of a state change of the working medium of the heat pump 50. FIG. 7 is an Hs diagram (Molier diagram) showing an example of a state change of the working medium of the heat pump 50. 6 and 7 are examples of four-stage reheating.

  In the steam generation system S <b> 2, the fact that the input temperature of the working medium to the multistage compression unit 60 is increased by the regenerator 52 is also advantageous in reducing the power of the compression unit 60. Moreover, effective use of heat is also achieved from the point of heating the water that is the medium to be heated by using the cooling of the interstage heat radiation portion 61.

  Further, in the steam generation system S2, the first heat exchanger 40 including the second heat radiating portion 13B is in a form suitable for sensible heat exchange, as in the previous steam generation system S1 (FIG. 1). 13A and the second heat exchanger 65 including the interstage heat dissipating part 61 of the compression part 60 are optimized in the configuration such that the second heat exchanger 65 is suitable for latent heat exchange. Will occur.

  Further, in the steam generation system S2, as in the previous steam generation system S1 (FIG. 1), the water in the supply path 20 becomes steam at a relatively low pressure and low temperature when heated by the heat pump 50, and is supplied by the compressor 30. Compression results in relatively high pressure and high temperature steam. That is, the water heated by the heat pump 50 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 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.

  Further, in the steam generation system S2, both saturated steam and superheated steam are obtained by multistage heating including heating by the heat pump 50 and heating by the compressor 30 as in the previous steam generation system S1 (FIG. 1). It can be easily generated. That is, after generating saturated steam at a negative pressure lower than the atmospheric pressure by heating by the heat pump 50, 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 S2 is highly flexible with respect to the steam specifications.

FIG. 8 shows a third embodiment of the steam generation system according to the present invention, which is a modification of the steam generation system S2 of FIG.
The steam generation system S3 of FIG. 8 has a heat pump 70 in which the bypass path 51 and the regenerator 52 are omitted from the heat pump 50 of the steam generation system S2 of FIG.

Here, a trial calculation example is shown. COP was estimated about the steam generation system S1 of FIG. 1, the steam generation system S2 of FIG. 3, and the steam generation system S3 of FIG. The medium to be heated is water, and the working medium is ammonia.
The COP of the steam generation system S1 in FIG. 1 was 3.07. The COP of the steam generation system S2 in FIG. 3 was 3.42 for the second stage of reheating and 3.52 for the fourth stage of reheating. The COP of the steam generation system S3 in FIG. 8 was 3.21 in the second stage of reheating.

FIG. 9 and FIG. 10 are the fourth and fifth embodiments of the steam generation system according to the present invention, respectively, and are other modifications of the steam generation system S2.
The steam generation system S4 in FIG. 9 differs from the steam generation system S2 in FIG. 3 in the input temperature of the medium to be heated (water) (about 60 ° C.).
The steam generation system S5 of FIG. 10 has a supply path 80 in which the compressor 30 is omitted from the supply path 20 of the steam generation system S2 of FIG.

  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 scope of the appended claims.

  S1, S2, S3, S4, S5 ... steam generation system, 10, 50, 70 ... heat pump, 11 ... heat absorption part, 12, 60 ... compression part, 13A ... first heat radiation part, 13B ... second heat radiation part, 14 ... Expansion unit, 15 ... main path, 20, 80 ... supply path, 21 ... heating unit, 22 ... evaporation unit, 23 ... duct, 30 ... compressor, 35 ... nozzle, 36 ... piping, 40 ... first heat exchanger , 41, 65 ... second heat exchanger, 47 ... tank, 48 ... circulation piping, 49 ... gas-liquid separator, 51 ... bypass path, 52 ... regenerator, 61 ... interstage heat radiation part.

Claims (10)

A heating medium supply path;
A heat pump,
The heat pump has a heat absorbing part, a compressing part, a first heat radiating part, a second heat radiating part, and an expanding part arranged in the flow direction of the working medium,
The second heat radiating section and the first heat radiating section heat the heated medium in the supply path in that order,
The compression unit has a structure for compressing the working medium in multiple stages,
The second heat dissipating part, the first heat dissipating part, and the interstage heat dissipating part of the compression part sequentially heat the heated medium in the supply path,
The heat from the interstage heat dissipation part is used for latent heat heating of the heated medium.
A steam generation system characterized by that.   The steam generation system according to claim 1, wherein the interstage heat dissipating part of the first heat dissipating part and the compression part is configured in one heat exchanger.   The heated medium in the supply path rises in temperature to near the boiling point due to heat from the second heat radiating part, and undergoes a phase change due to heat from the interstage heat radiating part of the first heat radiating part and the compression part. The steam generation system according to claim 1, wherein the steam generation system is steam. A compressor connected to the supply path and compressing the heated medium heated by the heat pump;
The heated medium in the supply path becomes steam at a negative pressure lower than atmospheric pressure by heating by the heat pump, and becomes steam at atmospheric pressure or pressure higher than atmospheric pressure by compression by the compressor.
The steam generation system according to any one of claims 1 to 3, wherein   The steam generation system according to claim 4, wherein an internal space at a heating portion by the heat pump in the supply path becomes a negative pressure due to a suction action by the compressor. The supply path has a tank capable of storing the liquid medium to be heated,
The inlet of the compressor leads to a steam outlet provided in the tank;
The steam generation system according to claim 4 or 5, characterized in that.   The steam generation system according to any one of claims 4 to 6, further comprising a nozzle that supplies the liquid to be heated with respect to the vapor of the medium to be heated.   The heat pump further includes a bypass path in which a part of the working medium from the first heat radiating unit bypasses the second heat radiating part, a flow rate control valve that controls a bypass amount of the working medium to the bypass path, The steam generation system according to any one of claims 1 to 7, characterized by comprising:   The steam generation system according to claim 8, wherein the bypass amount of the working medium is determined according to physical property values of the superheated medium and the working medium.   The steam generation system according to claim 8 or 9, wherein the heat pump further includes a heat exchanger that uses heat of the heated medium flowing through the bypass path.

Images