CN103459925A - Steam generation system - Google Patents

Steam generation system Download PDF

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Publication number
CN103459925A
CN103459925A CN2011800697161A CN201180069716A CN103459925A CN 103459925 A CN103459925 A CN 103459925A CN 2011800697161 A CN2011800697161 A CN 2011800697161A CN 201180069716 A CN201180069716 A CN 201180069716A CN 103459925 A CN103459925 A CN 103459925A
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CN
China
Prior art keywords
heat pump
evaporimeter
heat
cold
compressor
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Granted
Application number
CN2011800697161A
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Chinese (zh)
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CN103459925B (en
Inventor
金丸真嘉
川上昭典
田坂美佳
森田昭生
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Miura Co Ltd
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Miura Co Ltd
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Publication of CN103459925A publication Critical patent/CN103459925A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/16—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being hot liquid or hot vapour, e.g. waste liquid, waste vapour
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B3/00—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P80/00—Climate change mitigation technologies for sector-wide applications
    • Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
    • Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

Provided is an efficient steam generation system with which the difference in the temperature of the heat pumped by a heat pump is reduced. A first heat pump (2) has a first evaporator (7) and a second evaporator (8). A second heat pump (3) is connected to the first heat pump (2) via an uppermost-stage condenser (10), which also serves as the aforementioned first evaporator (7). A heat source fluid is passed sequentially through the second evaporator (8) of the first heat pump (2) and an evaporator (12) of the second heat pump (3), and water is heated in a condenser (5) of the first heat pump (2), thus generating steam.

Description

The steam generation systems
Technical field
The present invention relates to a kind of with the next vaporific steam generation systems of heat pump.The application based on March 31st, 2011 No. 2011-079370, the Japanese Patent Application to Japanese publication advocate priority, its content quotation is in this.
Background technology
In the past, as disclosed as following patent documentation 1, known have in evaporimeter from row's warm water etc. draw heat and condenser to the water heating and vaporific heat pump.
In addition, as disclosed as following patent documentation 2, also proposing has following system, this system forms heat pump by upper and lower multistage, the heat exchanger by connecting upper and lower heat pump (is the condenser of hypomere heat pump and is also the evaporimeter of epimere heat pump.) water supply is heated, take out steam from the condenser of the heat pump of epimere.
And then, as disclosed as following patent documentation 3, also propose just like lower device, this device left and right arranges heat pump in parallel, makes water obtain high-temperature water by the condenser of each heat pump successively.
Technical literature formerly
Patent documentation
Patent documentation 1: Japanese kokai publication sho 58-40451 communique (the second figure)
Patent documentation 2: TOHKEMY 2006-348876 communique (Fig. 1, Fig. 2)
Patent documentation 3: the real clear 60-23669 communique (the second figure) of opening of Japan
Summary of the invention
The problem that invention will solve
Yet, if as described in only use the heat pump of single hop the invention put down in writing of patent documentation 1, draw heat temperature difference, be that the temperature difference of vaporizer side and condenser side is large, the deterioration of efficiency of heat pump.
In addition, even as described at upper and lower multistage, heat pump is set simply the invention put down in writing of patent documentation 2, in the situation that only from the evaporimeter of hypomere, draw heat, the invention of putting down in writing with described patent documentation 1 similarly, with regard to heat pump on the whole to draw temperature difference large, the efficiency of heat pump improves and has the limit.
In addition, even as described in heat pump is set in parallel the invention put down in writing of patent documentation 3 in left and right, in the situation that the left and right heat pump is same structure and only from the evaporimeter of hypomere, draws heat, the invention of putting down in writing with described patent documentation 2 similarly, draw temperature difference large, there is the limit in the efficiency raising of heat pump.
And then, at heat source fluid, be warm water or waste gas etc. and in the situation that self follow temperature to reduce when giving heat (enthalpy) to heat pump, only by the heat pump being arranged in parallel with the left and right same structure, passing through heat source fluid, in the heat pump in downstream, the temperature of heat source fluid reduces, and therefore also needs this is considered.
Draw temperature difference when the problem that the present invention will solve is to reduce with regard to entire system, thereby realize that the efficiency of system improves.In addition, problem of the present invention also is to provide a kind of and can also tackles in the situation that heat source fluid is given enthalpy to heat pump the steam generation systems of following in this temperature reduction.
For solving the means of problem
The present invention makes in order to solve described problem, the invention that technical scheme 1 is put down in writing is a kind of steam generation systems, it is characterized in that, this steam generation systems possesses: the first heat pump, it consists of single hop or multistage, and at least at hypomere, has the first evaporimeter and the second evaporimeter; The second heat pump, it consists of single hop or multistage, and be connected with described the first heat pump via the condenser doubled as the epimere of the first evaporimeter of described hypomere, heat source fluid is the evaporimeter of the hypomere of the second evaporimeter by described the first heat pump and described the second heat pump successively, in the condenser of the epimere of described the first heat pump, water is heated and produced steam.
The invention of putting down in writing according to technical scheme 1, can draw heat from the evaporimeter of the hypomere of the second evaporimeter of the first heat pump and the second heat pump and produce steam the condenser of the epimere of the first heat pump.Now, heat source fluid leads to the evaporimeter of the hypomere of the second heat pump after the second evaporimeter by the first heat pump.Thus, the second heat pump compensation amount that heat source fluid is cooled in the second evaporimeter of the first heat pump, thus can again draw heat from the heat source fluid by the second evaporimeter.In addition, in the first heat pump, can reduce the temperature difference of drawing, correspondingly can reduce the electric power of compressor, can improve the efficiency of steam generation systems.
It is basis that the steam generation systems that technical scheme 1 put down in writing is take in the invention that technical scheme 2 is put down in writing, it is characterized in that, described the second heat pump consists of the heat pump of single hop, draw heat from the heat source fluid of the evaporimeter of the hypomere of the second evaporimeter by described the first heat pump and described the second heat pump successively, in the condenser of the epimere of described the first heat pump, water is heated and produced steam.
The invention of putting down in writing according to technical scheme 2, possess the first heat pump of single hop or multistage and the second heat pump of single hop, heat source fluid is the evaporimeter of the hypomere of the second evaporimeter by the first heat pump and the second heat pump successively, can in the condenser of the epimere of the first heat pump, produce steam thus.
It is basis that the steam generation systems that technical scheme 1 or technical scheme 2 put down in writing is take in the invention that technical scheme 3 is put down in writing, it is characterized in that, described the first heat pump consists of the heat pump of multistage, wherein the heat pump of part or all possesses described the first evaporimeter and described the second evaporimeter as evaporimeter, each described first evaporimeter is connected to each other adjacent heat pump up and down, heat source fluid according to the heat pump from epimere successively towards the order of the heat pump of hypomere by each described second evaporimeter.
The invention of putting down in writing according to technical scheme 3, with regard to the steam generation systems on the whole, it consists of the heat pump more than three sections.And, heat source fluid can be at the heat pump according to from epimere successively towards order each second evaporimeter by the first heat pump of the heat pump of hypomere, the evaporimeter that leads to the hypomere of the second heat pump is heated and is produced steam water in the condenser of the epimere of the first heat pump.
The invention that technical scheme 4 is put down in writing be take steam generation systems that technical scheme 3 put down in writing as basis, it is characterized in that, the heat pump that forms each section of described the first heat pump possesses described the first evaporimeter and described the second evaporimeter as evaporimeter.
The invention of putting down in writing according to technical scheme 4, heat source fluid, after second evaporimeter of each section by the first heat pump, leads to the evaporimeter of the hypomere of the second heat pump, thereby can draw heat efficiently and produce steam with simple structure.
It is basis that the steam generation systems that any one is put down in writing in technical scheme 1～4 is take in the invention that technical scheme 5 is put down in writing, it is characterized in that, just form in the heat pump of the single hop of described the first heat pump or multistage, heat pump with section of described the first evaporimeter and described the second evaporimeter, be provided with in series or in parallel described the first evaporimeter and described the second evaporimeter from expansion valve at this heat pump towards the refrigerant flow path of compressor, or be provided with in parallel the first expansion valve and described the first evaporimeter and the second expansion valve and described the second evaporimeter from condenser towards the refrigerant flow path of compressor.
The invention of putting down in writing according to technical scheme 5, by the first evaporimeter and the second evaporimeter are set in series or in parallel, or the first expansion valve and the first evaporimeter and the second expansion valve and the second evaporimeter be set in parallel, thereby can draw heat from the evaporimeter of the hypomere of the second evaporimeter of the first heat pump and the second heat pump, in the condenser of the epimere of the first heat pump, produce steam.
The invention that technical scheme 6 is put down in writing be take any one is put down in writing in technical scheme 1～5 steam generation systems as basis, it is characterized in that, described the first heat pump is connected with any relation in following (a)～(c) with described the second heat pump,
(a) possess and accept from the cold-producing medium of the compressor of described the second heat pump with from the cold-producing medium of the expansion valve of described the first heat pump and make two cold-producing mediums carry out the indirect heat exchanger of heat exchange under unmixed state, this indirect heat exchanger is as the condenser of described the second heat pump and as the first evaporimeter of described the first heat pump
(b) possess and accept from the cold-producing medium of the compressor of described the second heat pump with from the cold-producing medium of the expansion valve of described the first heat pump and make two cold-producing mediums directly carry out contiguously the intercooler of heat exchange, this intercooler is as the condenser of described the second heat pump and as the first evaporimeter of described the first heat pump
(c) possess and accept from the cold-producing medium of the compressor of described the second heat pump with from the cold-producing medium of the expansion valve of described the first heat pump and make two cold-producing mediums directly carry out contiguously heat exchange and make this two cold-producing medium and condenser from described the first heat pump via expansion valve ground, to the cold-producing medium of the expansion valve supply of described the second heat pump, not carry out the intercooler of heat exchange under unmixed state, this intercooler is as the condenser of described the second heat pump and as the first evaporimeter of described the first heat pump.
The invention of putting down in writing according to technical scheme 6, can connect the first heat pump and the second heat pump by indirect heat exchanger or intercooler, thereby form the steam generation systems.
It is basis that the steam generation systems that any one is put down in writing in technical scheme 1～6 is take in the invention that technical scheme 7 is put down in writing, it is characterized in that, in the situation that described the first heat pump and/or described the second heat pump are multistage, the heat pump of adjacent section connects with any relation in following (a)～(c) each other
(a) possess and accept from the cold-producing medium of the compressor of hypomere heat pump with from the cold-producing medium of the expansion valve of epimere heat pump and make two cold-producing mediums carry out the indirect heat exchanger of heat exchange under unmixed state, this indirect heat exchanger is as the condenser of hypomere heat pump and as the evaporimeter of epimere heat pump
(b) possess and accept from the cold-producing medium of the compressor of hypomere heat pump with from the cold-producing medium of the expansion valve of epimere heat pump and make two cold-producing mediums directly carry out contiguously the intercooler of heat exchange, this intercooler is as the condenser of hypomere heat pump and as the evaporimeter of epimere heat pump
(c) possess and accept from the cold-producing medium of the compressor of hypomere heat pump with from the cold-producing medium of the expansion valve of epimere heat pump and make two cold-producing mediums directly carry out contiguously heat exchange and make this two cold-producing medium and condenser from the epimere heat pump via expansion valve ground, to the cold-producing medium of the expansion valve supply of hypomere heat pump, not carry out the intercooler of heat exchange under unmixed state, this intercooler is as the condenser of hypomere heat pump and as the evaporimeter of epimere heat pump.
The invention of putting down in writing according to technical scheme 7, can form the first heat pump and/or the second heat pump by multistage, by indirect heat exchanger or intercooler, the heat pump of adjacent segment is connected to each other, and forms thus the steam generation systems.
It is basis that the steam generation systems that technical scheme 6 put down in writing is take in the invention that technical scheme 8 is put down in writing, it is characterized in that, in the situation that described the first heat pump is connected with the relation of described the second heat pump with (b) of technical scheme 6, from the cold-producing medium of the compressor of described the second heat pump, replace supplying with and to supplying with towards the refrigerant flow path of compressor from described intercooler to described intercooler, or from the cold-producing medium of the compressor of described the second heat pump on the basis of supplying with to described intercooler to supplying with towards the refrigerant flow path of compressor from described intercooler.
The invention of putting down in writing according to technical scheme 8, by suppressing to enter intercooler from the cold-producing medium of the compressor of the second heat pump, thereby can form littlely by the heat exchanger that forms intercooler.In addition, can prevent that the lubricating oil of the compressor of the second heat pump from lodging in intercooler, and can prevent the first heat pump compressor oil consumption to the greatest extent.
It is basis that the steam generation systems that technical scheme 6 put down in writing is take in the invention that technical scheme 9 is put down in writing, it is characterized in that, in the situation that described the first heat pump is connected with the relation of described the second heat pump with (c) of technical scheme 6, from the cold-producing medium of the compressor of described the second heat pump, replace supplying with and supplying with or to supplying with towards the refrigerant flow path of intercooler or compressor from expansion valve towards the refrigerant flow path of compressor to the intercooler from described the first heat pump to described intercooler, or to the intercooler from described the first heat pump, towards the refrigerant flow path of compressor, supply with or to supplying with towards the refrigerant flow path of intercooler or compressor from expansion valve on the basis of supplying with to described intercooler from the cold-producing medium of the compressor of described the second heat pump.
The invention of putting down in writing according to technical scheme 9, by suppressing to enter intercooler from the cold-producing medium of the compressor of the second heat pump, thereby can make the heat exchanger that forms intercooler form littlely.
It is basis that the steam generation systems that technical scheme 6 put down in writing is take in the invention that technical scheme 10 is put down in writing, it is characterized in that, in the situation that described the first heat pump is connected with the relation of described the second heat pump with (c) of technical scheme 6, possess the separator that the cold-producing medium of the expansion valve from described the first heat pump is carried out to gas-liquid separation, the gas phase part after being separated by this separator is supplied with to the refrigerant flow path from described the second evaporator to compressor.
The invention of putting down in writing according to technical scheme 10, form by separator is set the structure that makes the gas phase part not enter intercooler and/or the second evaporimeter, thereby can form littlely by the heat exchanger that forms them.
The invention that technical scheme 11 is put down in writing be take any one is put down in writing in technical scheme 1～10 steam generation systems as basis, it is characterized in that, this steam generation systems possesses any one the above secondary heat exchanger in following (a)～(d),
(a) from the condenser of the epimere of described the first heat pump towards the cold-producing medium of expansion valve and the first secondary heat exchanger of water,
(b) from the evaporimeter of the hypomere of described the second heat pump towards the cold-producing medium of compressor and the second secondary heat exchanger of heat source fluid,
(c) in the situation that described the first evaporimeter is indirect heat exchanger, from the expansion valve of the hypomere of described the first heat pump towards the cold-producing medium of compressor and compressor from described the second heat pump the 3rd secondary heat exchanger towards the cold-producing medium of the first evaporimeter,
(d) from the expansion valve of the hypomere of described the first heat pump towards the cold-producing medium of compressor and the fourth officer heat exchanger of heat source fluid,
About water, steam towards the condenser of the epimere of described the first heat pump and the circulation order that is provided with this first secondary heat exchanger in the situation of the first secondary heat exchanger, in the situation that be provided with the described first secondary heat exchanger, be set as this first secondary heat exchanger front
About heat source fluid towards the second evaporimeter of described the first heat pump, the evaporimeter of hypomere that is provided with this fourth officer heat exchanger in the situation of fourth officer heat exchanger, described the second heat pump and the circulation order that is provided with this second secondary heat exchanger in the situation of the second secondary heat exchanger, be set as the evaporimeter of hypomere of described the second heat pump rear
Towards the first evaporimeter of described the first heat pump, the circulation order that is provided with the second evaporimeter of the 3rd secondary heat exchanger in the situation of the 3rd secondary heat exchanger, described the first heat pump and is provided with this fourth officer heat exchanger in the situation of fourth officer heat exchanger, be set as described the first evaporimeter and described the second evaporimeter is more forward than described the 3rd secondary heat exchanger and described fourth officer heat exchanger about cold-producing medium.
The invention of putting down in writing according to technical scheme 11, by making the subcooler of the first secondary heat exchanger as cold-producing medium, or make the superheater of the second secondary heat exchanger as cold-producing medium, or make the superheater of fourth officer heat exchanger as cold-producing medium, or the 3rd secondary heat exchanger further suitably is set, thereby can improve the efficiency of steam generation systems.
And then the invention that technical scheme 12 is put down in writing be take any one is put down in writing in technical scheme 1～11 steam generation systems as basis, it is characterized in that, described heat source fluid be the drainage liquid from steam use equipment.
The invention of putting down in writing according to technical scheme 12, can recuperation of heat be used the drainage liquid of equipment and produce steam from steam.
The invention effect
According to the present invention, draw temperature difference in the time of can reducing with regard to entire system, realize that thus the efficiency of system improves.In addition, in the situation that heat source fluid is given enthalpy to heat pump, can tackle the temperature of following with it and reduce.
The accompanying drawing explanation
Fig. 1 means the schematic diagram of the embodiment 1 of steam generation systems of the present invention.
Fig. 2 means the figure of heat source fluid to the circulation order of the evaporimeter of the second evaporimeter of fourth officer heat exchanger, the first heat pump, the second secondary heat exchanger, the second heat pump.
Fig. 3 means the figure of the cold-producing medium of the first heat pump to the circulation order of the second evaporimeter of the first evaporimeter of the first heat pump, the 3rd secondary heat exchanger, the first heat pump, fourth officer heat exchanger.
Fig. 4 is steam generation systems more of the present invention and the chart of the coefficient of refrigerating performance of known 2 sections heat pumps in the past.
Fig. 5 be steam generation systems more of the present invention and in the past known 2 sections heat pumps, the compressor of each section sucks the chart of volume flow up and down.
Fig. 6 A is the T-S line chart of Ideal Cycle.
Fig. 6 B is the T-S line chart of the heat pump (contrary Carnot cycle) of known single hop in the past.
Fig. 7 is the T-S line chart of the steam generation systems of the present embodiment.
Fig. 8 is illustrated in Fig. 7 the situation of the hop count that has increased heat pump.
Fig. 9 means the schematic diagram of the embodiment 2 of steam generation systems of the present invention.
Figure 10 means the schematic diagram of variation of the steam generation systems of embodiment 2.
Figure 11 means the schematic diagram of the embodiment 3 of steam generation systems of the present invention.
Figure 12 means the schematic diagram of variation of the steam generation systems of embodiment 3.
Figure 13 means the schematic diagram of the embodiment 4 of steam generation systems of the present invention.
Figure 14 means that the cold-producing medium of the first heat pump in embodiment 4 is to the first evaporimeter of the first heat pump, the circulation order of the 3rd secondary heat exchanger, and means that the cold-producing medium of the first heat pump is to the second evaporimeter of the first heat pump, the circulation figure sequentially of fourth officer heat exchanger.
Figure 15 means the schematic diagram of the embodiment 5 of steam generation systems of the present invention.
Figure 16 means the schematic diagram of variation of the steam generation systems of embodiment 5.
Figure 17 means the schematic diagram of the embodiment 6 of steam generation systems of the present invention.
Figure 18 means the schematic diagram of variation 1 of the steam generation systems of embodiment 6.
Figure 19 means the schematic diagram of variation 2 of the steam generation systems of embodiment 6.
Figure 20 means the figure of combination of the setting of the first separator, the second separator and the 3rd separator.
Figure 21 means the schematic diagram of the embodiment 7 of steam generation systems of the present invention.
Figure 22 means the schematic diagram of the embodiment 8 of steam generation systems of the present invention.
Figure 23 means the schematic diagram of variation 1 of the steam generation systems of embodiment 8.
Figure 24 means the schematic diagram of variation 2 of the steam generation systems of embodiment 8.
Figure 25 means the schematic diagram of the embodiment 9 of steam generation systems of the present invention.
Figure 26 means the schematic diagram of variation 1 of the steam generation systems of embodiment 9.
Figure 27 means the schematic diagram of variation 2 of the steam generation systems of embodiment 9.
Figure 28 means the figure of combination of the setting of the first separator and the second separator.
Figure 29 A means the schematic diagram of an example of the steam generation systems of the present invention consisted of the heat pump more than three sections.
Figure 29 B is that to make the first heat pump be that single hop, the second heat pump are the T-S line chart in the situation of two sections.
Figure 29 C is the T-S line chart that the first evaporimeter and the second evaporimeter is set in each section of the first heat pump of multistage and makes the situation that the second heat pump is single hop.
Figure 30 means the schematic diagram of an example of the vapor system of the steam generation systems that has used embodiment 1.
Figure 31 means the schematic diagram of variation of the vapor system of Figure 30.
The specific embodiment
Steam generation systems of the present invention possesses the heat pump of multistage, and the heat pump of part or all in the heat pump of each section except hypomere possesses the first evaporimeter and the second evaporimeter as evaporimeter, and each first evaporimeter is connected to each other adjacent heat pump up and down.And, heat source fluid with the heat pump from epimere in turn towards the mode of the heat pump of hypomere successively by each second evaporimeter, in the condenser of epimere, the water heating is produced to steam.
Below, with reference to the accompanying drawings specific embodiment of the present invention is described in detail.
Embodiment 1
Fig. 1 means the schematic diagram of the embodiment 1 of steam generation systems 1 of the present invention.The steam generation systems 1 of the present embodiment possesses the first heat pump 2 and the second heat pump 3.
The heat pump that the first heat pump 2 is steam compression type, the heat pump by single hop forms in the present embodiment.Specifically, the first heat pump 2 is in turn connected into ring-type by compressor 4, condenser 5, expansion valve 6 and evaporimeter 7,8 and forms.At this, the first heat pump 2 possesses the first evaporimeter 7 and second evaporimeter 8 these two evaporimeters as evaporimeter, and described evaporimeter 7,8 is connected in series in the present embodiment.In other words, from the cold-producing medium of the expansion valve 6 of the first heat pump 2 after (or as described later on the contrary) successively is by the first evaporimeter 7 and the second evaporimeter 8 to compressor 4 conveyings.
Then, compressor 4 compressed gas refrigerant and make it become HTHP.In addition, condenser 5 makes the gas refrigerant condensation liquefaction from compressor 4.And then expansion valve 6 makes to pass through from the liquid refrigerant of condenser 5, thus the pressure and temperature of reduction cold-producing medium.Then, the evaporation that evaporimeter 7,8 is realized from the cold-producing medium of expansion valve 6.
Therefore, in the first heat pump 2, cold-producing medium is captured heat from outside and gasifies at evaporimeter 7,8, on the other hand, cold-producing medium at condenser 5 to outside heat release and condensation.Utilize this point, the first heat pump 2 draws heat from heat source fluid etc. in evaporimeter 7,8, and in condenser 5, water is heated and produce steam.
There is no particular limitation for heat source fluid (thermal source of each heat pump 2,3), can suitably use the fluid of giving the fluid of enthalpy, following self temperature to reduce when to each heat pump 2,3, giving heat to each heat pump 2,3.For example, can use from steam use the drainage liquid of equipment, from the waste gas of boiler etc.
It should be noted that, in the circuit of heat pump 2, can be according to expectation and at the outlet side of compressor 4, oil eliminator is set, or at the outlet side of condenser 5, accumulator is set, or at the entrance side of compressor 4, accumulator is set, or setting makes mixedly not carry out the gas-liquid heat exchanger of heat exchange from condenser 5 towards the cold-producing medium of expansion valve 6 with from evaporimeter 7,8 cold-producing mediums towards compressor 4.This point is not limited to the first heat pump 2, like this too for the second heat pump 3.In addition, in the situation that the first heat pump 2, the second heat pump 3 are multistage, like this too for the heat pump of each section that forms it.
The heat pump that the second heat pump 3 is steam compression type, the heat pump by single hop forms in the present embodiment.The second heat pump 3 is essentially the structure same with described the first heat pump 2.In other words, the second heat pump 3 is in turn connected into ring-type by compressor 9, condenser 10, expansion valve 11 and evaporimeter 12 and forms.But the second heat pump 3 is without possess two kinds of evaporimeters as the first heat pump 2.And the second heat pump 3 draws heat from heat source fluid in evaporimeter 12, and in condenser 10, the cold-producing medium of the first heat pump 2 is heated and self realizes condensation.
The first heat pump 2 is connected as follows with the second heat pump 3.; possess and accept from the cold-producing medium of the compressor 9 of the second heat pump 3 with from the cold-producing medium of the expansion valve 6 of the first heat pump 2 and make the indirect heat exchanger 13 that carries out heat exchange under the unmixed state of two cold-producing mediums, this indirect heat exchanger 13 is as the condenser 10 of the second heat pump 3 and as the first evaporimeter 7 of the first heat pump 2.It should be noted that, the cold-producing medium of each heat pump 2,3 can be identical, also can be different.In addition, there is no particular limitation for the cold-producing medium used, and can suitably use carbon number is the hydrogen fluorohydrocarbon (HFC) (for example R mono-365mfc) more than 4 or cold-producing medium, the alcohols (for example ethanol, methyl alcohol or trifluoroethanol (TFE)) that adds therein water and/or extinguishing fluid or cold-producing medium or the water (for example pure water or soft water) that adds therein water and/or extinguishing fluid.
Heat source fluid is by the second evaporimeter 8 of the first heat pump 2 and the evaporimeter 12 of the second heat pump 3, and the details of this point is in rear explanation.Therefore, steam generation systems 1 draws heat from heat source fluid in described evaporimeter 8,12, and in the condenser 5 of the first heat pump 2, water is heated and produce steam.
Secondary heat exchanger more than any one in the various secondary heat exchanger 14～17 of following explanation also can be set in steam generation systems 1.
(a) the first secondary heat exchanger 14 be condenser 5 from the first heat pump 2 towards the cold-producing medium of expansion valve 6 and the indirect heat exchanger of water, its performance of subcooler as the cold-producing medium of the first heat pump 2 function.
(b) the second secondary heat exchanger 15 be evaporimeter 12 from the second heat pump 3 towards the cold-producing medium of compressor 9 and the indirect heat exchanger of heat source fluid, its performance of superheater as the cold-producing medium of the second heat pump 3 function.
(c) the 3rd secondary heat exchanger 16 be in the situation that the first evaporimeter 7 be indirect heat exchanger 13, from the expansion valve 6 of the first heat pump 2 towards the cold-producing medium of compressor 4 and compressor 9 from the second heat pump 3 indirect heat exchanger towards the cold-producing medium of the first evaporimeter 7, its performance of superheater as the cold-producing medium of the first heat pump 2 function.
(d) fourth officer heat exchanger 17 be expansion valve 6 from the first heat pump 2 towards the cold-producing medium of compressor 4 and the indirect heat exchanger of heat source fluid, its performance of superheater as the cold-producing medium of the first heat pump 2 function.
Next, the flow route of water and steam described.
The condenser 5 of the first heat pump 2 and the first secondary heat exchanger 14 arranged according to expectation are supplied to water is derived steam.About the circulation order of this water and steam, in the situation that be provided with the first secondary heat exchanger 14, set for and compare first circulation in this first secondary heat exchanger 14 with the condenser 5 of the first heat pump 2.And, usually, from the condenser 5 of the first heat pump 2, derive saturated vapor.It should be noted that, the condenser 5,10 of each heat pump 2,3 respectively is provided with respectively one in illustrated example, but also can consist of a plurality of heat exchangers of serial or parallel connection.
Next, the flow route of heat source fluid described.
The evaporimeter 12 of the second evaporimeter 8 of the first heat pump 2, the fourth officer heat exchanger 17 arranged according to expectation, the second heat pump 3, the second secondary heat exchanger 15 arranged according to expectation are with suitable order setting, and heat source fluid is passed through, can use any shown in Fig. 2 about its flow route.
Fig. 2 means the figure of heat source fluid to the circulation order of the evaporimeter 12 of the second evaporimeter 8 of the fourth officer heat exchanger 17 arranged according to expectation, the first heat pump 2, the second secondary heat exchanger 15 arranged according to expectation, the second heat pump 3.Numbering in figure means the circulation order to each heat exchanger 17,8,15,12, is numbered 0 expression this heat exchanger is not set.In addition, same reference numeral is arranged in parallel, but the heat exchanger of identical numbering can be replaced each other mutually.It should be noted that, the evaporimeter 8,12 of each heat pump 2,3 respectively is provided with respectively one in illustrated example, but also can consist of a plurality of heat exchangers of serial or parallel connection.
Enumerate several concrete examples and describe, for example, in the 1st row, be labeled as 1-2-3-4.That is the second evaporimeter 8 that, fourth officer heat exchanger 17 is 1, the first heat pump 2 is that the evaporimeter 12 that 2, the second secondary heat exchangers 15 are 3, the second heat pumps 3 is 4.In this case, heat source fluid is successively by fourth officer heat exchanger 17, the secondary heat exchanger 15 of the second evaporimeter 8, second of the first heat pump 2, the evaporimeter 12 of the second heat pump 3.
In addition, in the 2nd row, be labeled as 1-2-1-3.That is the second evaporimeter 8 that, fourth officer heat exchanger 17 is 1, the first heat pump 2 is that the evaporimeter 12 that 2, the second secondary heat exchangers 15 are 1, the second heat pump 3 is 3.In this case, heat source fluid is after the mode to walk abreast is by fourth officer heat exchanger 17 and the second secondary heat exchanger 15, successively by the second evaporimeter 8 of the first heat pump 2 and the evaporimeter 12 of the second heat pump 3.
And then, in the 4th row, be labeled as 1-2-0-3.That is the second evaporimeter 8 that, fourth officer heat exchanger 17 is 1, the first heat pump 2 is that the evaporimeter 12 that 2, the second secondary heat exchangers 15 are 0, the second heat pump 3 is 3.In this case, the second secondary heat exchanger 15 is not set, heat source fluid passes through successively the second evaporimeter 8 of the first heat pump 2 and the evaporimeter 12 of the second heat pump 3 after passing through fourth officer heat exchanger 17.
No matter adopt which kind of order, the circulation of heat source fluid order basically preferably so that the evaporimeter 12 of the second heat pump 3 after mode set.In other words, heat source fluid leads to the evaporimeter 12 of the second heat pump 3 after the second evaporimeter 8 by the first heat pump 2.
Fig. 3 means the figure of the cold-producing medium of the first heat pump 2 to the circulation order of the second evaporimeter 8 of the first evaporimeter 7 of the first heat pump 2, the 3rd secondary heat exchanger 16 arranged according to expectation, the first heat pump 2, the fourth officer heat exchanger 17 that arranges according to expectation.Numbering in figure means the circulation order to each heat exchanger 7,16,8,17, is numbered 0 expression this heat exchanger is not set.In addition, same reference numeral is arranged in parallel.
Enumerate several concrete examples and describe, for example, in the 1st row, be labeled as 1-3-2-3.That is, the first evaporimeter 7 is that 1, the three secondary heat exchanger 16 is that 3, the second evaporimeters 8 are that 2, the fourth officer heat exchangers 17 are 3.In this case, from the cold-producing medium of the expansion valve 6 of the first heat pump 2 successively by after the first evaporimeter 7 and the second evaporimeter 8, in the mode that walks abreast by the 3rd secondary heat exchanger 16 and fourth officer heat exchanger 17, thereby to compressor 4, carry.
In addition, in the 2nd row, be labeled as 1-3-2-4.That is, the first evaporimeter 7 is that 1, the three secondary heat exchanger 16 is that 3, the second evaporimeters 8 are that 2, the fourth officer heat exchangers 17 are 4.In this case, from the cold-producing medium of the expansion valve 6 of the first heat pump 2 successively by the first evaporimeter 7, the second evaporimeter the 8, the 3rd secondary heat exchanger 16 and fourth officer heat exchanger 17, thereby to compressor 4, carry.
And then, in the 4th row, be labeled as 1-3-2-0.That is, the first evaporimeter 7 is that 1, the three secondary heat exchanger 16 is that 3, the second evaporimeters 8 are that 2, the fourth officer heat exchangers 17 are 0.In this case, fourth officer heat exchanger 17 is not set, from the cold-producing medium of the expansion valve 6 of the first heat pump 2 successively by the first evaporimeter 7, the second evaporimeter 8 and the 3rd secondary heat exchanger 16, thereby to compressor 4, carry.
No matter adopt which kind of order, the circulation of the cold-producing medium of the first heat pump 2 order basically preferably so that the first evaporimeter 7 and the secondary heat exchanger 16 of the second evaporimeter 8 to the three and the forward mode of fourth officer heat exchanger 17 set.
As mentioned above, the steam generation systems 1 of the present embodiment is for example used drainage liquid as heat source fluid.As an example, the drainage liquid of 158 ℃ is supplied with to the second evaporimeter 8 of the first heat pump 2, after discharging under 125 ℃, to the evaporimeter 12 of the second heat pump 3, supply with, and 80 ℃ of discharges.The refrigerant temperature of the low temperature side of the second heat pump 3 (entrance side of compressor 9) is 75 ℃, the refrigerant temperature of the low temperature side of the first heat pump 2 (entrance side of compressor 4) is 120 ℃, the refrigerant temperature of high temperature side (outlet side of compressor 4) is 163 ℃, and produces the steam of 158 ℃ in condenser 5.
According to the steam generation systems 1 of the present embodiment, heat source fluid is after passing through the second evaporimeter 8 of the first heat pump 2, to evaporimeter 12 circulations of the second heat pump 3.Thus, the amount that the second heat pump 3 compensation drainage liquid are cooled in the second evaporimeter 8 of the first heat pump 2, can draw heat again from the drainage liquid by the second evaporimeter 8.In addition, in the first heat pump 2, can reduce the temperature difference of drawing, correspondingly can reduce the electric power of compressor 4, can improve the efficiency of steam generation systems 1.
In other words, with regard to steam generation systems 1, on the whole as the heat pump 2,3 by multistage (in the present embodiment being two sections), form, the part of the energy drawn (being typically half) is drawn from stage casing, therefore can increase coefficient of refrigerating performance.In addition, can reduce the energy (being typically half) drawn from hypomere, therefore can reduce the capacity of the compressor 9 of low band side (the second heat pump 3).
Fig. 4 is the steam generation systems 1 of comparison the present embodiment and the chart of the coefficient of refrigerating performance of known 2 sections heat pumps in the past.In figure, solid line means the steam generation systems 1 of the present embodiment, and dotted line means the heat pump of known 2 sections in the past.In addition, at this, the situation of using drainage liquid as heat source fluid is shown, take by the final drainage liquid temp after the evaporimeter 12 of the second heat pump 3 is transverse axis, take theoretic coefficient of refrigerating performance as the longitudinal axis.It should be noted that, cold-producing medium is R-365mfc and uses described condition, uses the drainage liquid of 158 ℃ of initial temperatures to produce 158 ℃ of (5kgf/cm 2(G) situation of steam) is studied.
As shown in the drawing, regardless of the temperature of heat source fluid (drainage liquid), adopt the efficiency of steam generation systems 1 of the present embodiment all than the efficiency of heat pump of known 2 sections was high in the past.It should be noted that, for example with the setting of omitting the second evaporimeter 8 in Fig. 1, only from the evaporimeter 12 of the second heat pump 3 of hypomere, to draw the structure of heat identical for known 2 sections heat pumps in the past.
Fig. 5 be the steam generation systems 1 of comparison the present embodiment and in the past known 2 sections heat pumps, the compressor of each section sucks the chart of volume flow up and down.In figure, solid line means the steam generation systems 1 of the present embodiment, and dotted line means the heat pump of known 2 sections in the past.In addition, using the situation of drainage liquid this illustrate as heat source fluid, take by the final drainage liquid temp after the evaporimeter 12 of the second heat pump 3 is transverse axis, and it is the longitudinal axis that the compressor of take sucks volume flow.
As shown in the drawing, regardless of the temperature of heat source fluid (drainage liquid), adopt the steam generation systems 1 of the present embodiment all more can reduce compressor suction volume flow.Therefore, with the heat pump of known 2 sections in the past, compare, adopt steam generation systems 1 efficiency of the present embodiment higher.
Fig. 6 A is that the state at the inlet portion of the fluid that is endowed heat is T hsaturation water, the state of export department that is endowed the fluid of heat be T hsaturated vapor (fluid that is endowed heat is endowed latent heat) and the state of inlet portion of giving the fluid of heat is T hsaturation water, the state of export department of giving the fluid of heat be T 1the condition of supercooled water (fluid of giving heat is captured enthalpy) under, with perfect condition draw heat situation (below, be called Ideal Cycle.) the T-S line chart.In other words, the longitudinal axis means temperature, and transverse axis means entropy.
The leg-of-mutton area that this Ideal Cycle is surrounded by solid line becomes the minimum power (ideal power) for realizing described condition.And, coefficient of performance now=2 * (T h/ (T h-T 1)).
On the other hand, Fig. 6 B is the T-S line chart of the heat pump (contrary Carnot cycle) of known single hop in the past.But Fig. 6 B illustrates expansion valve discharge loss, overheat of compressor loss and the infinitely-great situation of heat exchange performance ignored.In this case, coefficient of performance=T h/ (T h-T 1).As shown in double dot dash line A, in the situation that make heat pump be two sections too.
Comparison diagram 6A and Fig. 6 B are known, and the amount that deducts the leg-of-mutton area of Fig. 6 A from the tetragonal area of Fig. 6 B can be described as compares unnecessary power with Ideal Cycle, and coefficient of refrigerating performance and this amount correspondingly reduce.
On the other hand, Fig. 7 is the T-S line chart of the steam generation systems of the present embodiment.In this case, coefficient of performance=(4/3) * (T h/ (T h-T 1)).In other words, be 4/3 times of efficiency of the heat pump of known single hop in the past.It should be noted that T m=(T h+ T 1)/2, S m=(S 1+ S 2)/2.Compare with Fig. 6 B, lack bottom-right position, thereby correspondingly power reduces, and can raise the efficiency.
In addition, making hop count in Fig. 7 is two sections, if but increase hop count, as shown in Figure 8, can further reduce the area surrounded by circulation, can further improve the efficiency of steam generation systems 1.Be in infinitely-great situation making hop count, in theory, become COP=2 * (T h/ (T h-T 1)).In other words, can realize 2 times of efficiency of the heat pump of known single hop in the past.Increased the concrete structure of steam generation systems 1 of hop count in rear explanation.
Embodiment 2
Fig. 9 means the schematic diagram of the embodiment 2 of steam generation systems 1 of the present invention.The steam generation systems 1 of the present embodiment 2 is basic same with described embodiment 1.Therefore, below only centered by both differences, describe, mark identical symbol in corresponding position and illustrate.
In the present embodiment 2, different with described embodiment 1 on the syndeton of the first heat pump 2 and the second heat pump 3.In described embodiment 1, the first heat pump 2 is connected by indirect heat exchanger 13 with the second heat pump 3, but, in the present embodiment 2, the first heat pump 2 is connected by intercooler 18 with the second heat pump 3.
Specifically, possess and accept from the cold-producing medium of the compressor 9 of the second heat pump 3 with from the cold-producing medium of the expansion valve 6 of the first heat pump 2 intercooler 18 that makes two cold-producing mediums directly carry out contiguously heat exchange, this intercooler 18 is as the condenser 10 of the second heat pump 3 and as the evaporimeter 7 of the first heat pump 2.More specifically, use hollow box (direct heat exchanger) as intercooler 18, acceptance is from the cold-producing medium of the compressor 9 of the second heat pump 3 with from the cold-producing medium of the expansion valve 6 of the first heat pump 2, and make their directly contacts in case, realize thus from the condensation of the cold-producing medium of the compressor 9 of the second heat pump 3 with from the gasification of the cold-producing medium of the expansion valve 6 of the first heat pump 2.Then, thus obtained liquid refrigerant is carried to the expansion valve 11 of the second heat pump 3, on the other hand, gas-liquid mixed refrigerant is carried and is got final product to compressor 4 via the second evaporimeter 8 of the first heat pump 2.
In the present embodiment 2, from the cold-producing medium of the expansion valve 6 of the first heat pump 2, basically via intercooler 18 and the second evaporimeter 8, to compressor 4, carry successively.Due to the relation that also makes the cold-producing medium boiling in the second evaporimeter 8, therefore make gas phase part and liquid phase part mix with the regulation ratio and carry towards the second evaporimeter 8 from middle cooler 18.The adjustment of this mixed proportion is for example undertaken by being located at from the aperture adjustment of the valve (omitting diagram) in the refrigerant flow path of the refrigerant flow path of the gas phase of intercooler 18 part and liquid phase part.
In addition, in the present embodiment 2, the 3rd secondary heat exchanger 16 is not set.Other structure and described embodiment 1 are same, and therefore description thereof is omitted.
Next, the variation of the steam generation systems 1 of the present embodiment 2 described.Now, centered by the difference with Fig. 9, describe, omit the explanation to same structure.In addition, marking identical symbol in corresponding position illustrates.
Figure 10 means the schematic diagram of variation of the steam generation systems 1 of the present embodiment 2.In the steam generation systems 1 of Fig. 9, cold-producing medium from the compressor 9 of the second heat pump 3 is supplied with to intercooler 18, but in this variation, replacement is supplied with or, on the basis of supplying with to intercooler 18, is supplied with towards the refrigerant flow path of compressor 4 to the intercooler 18 from the first heat pump 2 as shown in double dot dash line A to intercooler 18.Now, can supply with to the entrance side of the second evaporimeter 8, also can supply with to outlet side, in the situation that be provided with fourth officer heat exchanger 17, can supply with to the entrance side of this fourth officer heat exchanger 17, also can supply with to outlet side.In addition, as shown in double dot dash line B, from the cold-producing medium of the compressor 9 of the second heat pump 3 also can be to the expansion valve 6 from the first heat pump 2 the refrigerant flow path interflow towards intercooler 18.
Embodiment 3
Figure 11 means the schematic diagram of the embodiment 3 of steam generation systems 1 of the present invention.The steam generation systems 1 of the present embodiment 3 is basic same with described embodiment 1.Therefore, below only centered by both differences, describe, mark identical symbol in corresponding position and illustrate.
In the present embodiment 3, the first heat pump 2 is different with described embodiment 1 from the syndeton of the second heat pump 3.In described embodiment 1, the first heat pump 2 is connected by indirect heat exchanger 13 with the second heat pump 3, but, in the present embodiment 3, the first heat pump 2 is connected by intercooler 19 with the second heat pump 3.
Specifically, possesses intercooler 19, this intercooler 19 is accepted from the cold-producing medium of the compressor 9 of the second heat pump 3 with from the cold-producing medium of the expansion valve 6 of the first heat pump 2, two cold-producing mediums are directly contacted and carry out heat exchange, and make described two cold-producing mediums and the cold-producing medium of not supplying with to the expansion valve 11 of the second heat pump 3 via expansion valve 6 from the condenser 5 of the first heat pump 2 carry out heat exchange under unmixed state, this intercooler 19 is as the condenser 10 of the second heat pump 3 and as the evaporimeter 7 of the first heat pump 2.More specifically, as intercooler 19, make each fluid of first area 20 and second area 21 carry out the indirect heat exchanger of heat exchange under unmixed state, in first area 20, directly carry out heat exchange from the cold-producing medium of the compressor 9 of the second heat pump 3 and the cold-producing medium of expansion valve 6 from the first heat pump 2, on the other hand, in second area 21, make cold-producing medium via expansion valve 6 ground, not pass through and supply with and get final product to the expansion valve 11 of the second heat pump 3 from the condenser 5 of the first heat pump 2.In this case, from the cold-producing medium of the compressor 9 of the second heat pump 3 in intercooler 19, be used to cooling in the middle of the cold-producing medium of the expansion valve 6 of the first heat pump 2 is realized after, become the more gas refrigerant of high pressure-temperature in the compressor 4 of the first heat pump 2, and the condensation by the condenser 5 of the first heat pump 2.Then, the part of this liquid refrigerant is carried to the first area 20 of intercooler 19 via the expansion valve 6 of the first heat pump 2, and remaining liquid refrigerant reduces pressure in the expansion valve 11 of the second heat pump 3 via the second area 21 of intercooler 19, and gasify in the evaporimeter 12 of the second heat pump 3, again return to afterwards the compressor 9 of the second heat pump 3.
With such structure correspondingly, the 3rd secondary heat exchanger 16 is not set in the present embodiment 3.Other structures and described embodiment 1 are same, and therefore description thereof is omitted.
Next, the variation of the steam generation systems 1 of the present embodiment 3 described.Now, centered by the difference with Figure 11, describe, omit the explanation to same structure.In addition, marking identical symbol in corresponding position illustrates.
Figure 12 means the schematic diagram of variation of the steam generation systems 1 of the present embodiment 3.In the steam generation systems 1 of Figure 11, cold-producing medium from the compressor 9 of the second heat pump 3 is supplied with to intercooler 19, but in this variation, replacement is supplied with or, on the basis of supplying with to intercooler 19, is supplied with towards the refrigerant flow path of compressor 4 to the intercooler 19 from the first heat pump 2 as shown in double dot dash line A to intercooler 19.Now, can supply with to the entrance side of the second evaporimeter 8, also can supply with to outlet side, in the situation that be provided with fourth officer heat exchanger 17, can supply with to the entrance side of this fourth officer heat exchanger 17, also can supply with to outlet side.In addition, as shown in double dot dash line B, also can towards the refrigerant flow path of intercooler 19, supply with to the expansion valve 6 from the first heat pump 2.It should be noted that, in the situation that towards the refrigerant flow path of intercooler 19, separator 22 described later is set from the expansion valve 6 of the first heat pump 2, also can be to supplying with towards the refrigerant flow path of separator 22 from this expansion valve 6, also always the refrigerant flow path 23 of the gas phase of self-separation device 22 part is supplied with.
In addition, in this variation, at the outlet side of the expansion valve 6 of the first heat pump 2, be provided with separator 22.In this case, the liquid phase part separated by separator 22 is supplied with to intercooler 19, and the gas phase part is supplied with towards the refrigerant flow path of compressor 4 to the intercooler 19 from the first heat pump 2 as shown in stream 23.Now, can supply with to the entrance side of the second evaporimeter 8, also can supply with to outlet side, in the situation that be provided with fourth officer heat exchanger 17, can supply with to the entrance side of this fourth officer heat exchanger 17, also can supply with to outlet side.
It should be noted that, also can replace towards the refrigerant flow path of intercooler 19, separator 22 or on this basis being set at the expansion valve 6 from the first heat pump 2, from middle cooler 19, towards the refrigerant flow path of the second evaporimeter 8, separator 22 is being set.In this case, also can make liquid phase part supply with to the second evaporimeter 8, the gas phase part is to supplying with towards the position arbitrarily of the refrigerant flow path of compressor 4 from the second evaporimeter 8.
Embodiment 4
Figure 13 means the schematic diagram of the embodiment 4 of steam generation systems 1 of the present invention.The steam generation systems 1 of the present embodiment 4 is basic same with described embodiment 1.Therefore, below centered by both differences, describe, mark identical symbol in corresponding position and illustrate.
In described embodiment 1, the first evaporimeter 7 and the second evaporimeter 8 series connection arrange, but, in the present embodiment 4, the first evaporimeter 7 and the second evaporimeter 8 are arranged in parallel.; in the present embodiment; from the cold-producing medium of the expansion valve 6 of the first heat pump 2, when supplying with to compressor 4 via the first evaporimeter 7 and the 3rd secondary heat exchanger 16 that arranges according to expectation, via the second evaporimeter 8 and the fourth officer heat exchanger 17 that arranges according to expectation, to compressor 4, supply with.
The cold-producing medium that Figure 14 means the first heat pump 2 in the present embodiment 4 is to the circulation order of the first evaporimeter 7 of the first heat pump 2 and the 3rd secondary heat exchanger 16 that arranges according to expectation, and the cold-producing medium that means the first heat pump 2 is to the figure of the circulation order of the second evaporimeter 8 of the first heat pump 2 and the fourth officer heat exchanger 17 that arranges according to expectation.Numbering in figure means the circulation order to each heat exchanger 7,16,8,17, is numbered 0 expression this heat exchanger is not set.In addition, same reference numeral is arranged in parallel.
Several concrete examples are described, for example, in the 1st row, be labeled as 1-2-1-2.That is, the first evaporimeter 7 is that 1, the three secondary heat exchanger 16 is that 2, the second evaporimeters 8 are that 1, the fourth officer heat exchanger 17 is 2.In this case, from the cold-producing medium of the expansion valve 6 of the first heat pump 2 in the mode that walks abreast by following stream: by the refrigerant flow path of the first evaporimeter 7 and the 3rd secondary heat exchanger 16 and successively by the refrigerant flow path of the second evaporimeter 8 and fourth officer heat exchanger 17, to compressor 4, carry successively.
In addition, in the 2nd row, be labeled as 1-2-1-3.That is, the first evaporimeter 7 is that 1, the three secondary heat exchanger 16 is that 2, the second evaporimeters 8 are that 1, the fourth officer heat exchanger 17 is 3.In this case, from the cold-producing medium of the expansion valve 6 of the first heat pump 2, after the mode to walk abreast is by the first evaporimeter 7 and the second evaporimeter 8, successively by the 3rd secondary heat exchanger 16 and fourth officer heat exchanger 17, thereby carry to compressor 4.Perhaps, from the cold-producing medium of the expansion valve 6 of the first heat pump 2, successively by the first evaporimeter 7 and the 3rd secondary heat exchanger 16, and also lead to concurrently therewith the second evaporimeter 8, afterwards both interflow and carrying to compressor 4 via fourth officer heat exchanger 17.
And then, in the 4th row, be labeled as 1-0-1-1.That is, the first evaporimeter 7 is that 1, the three secondary heat exchanger 16 is that 0, the second evaporimeter 8 is that 1, the fourth officer heat exchanger 17 is 1.In this case, the 3rd secondary heat exchanger 16 is not set, from the cold-producing medium of the expansion valve 6 of the first heat pump 2 in the mode to walk abreast by after the first evaporimeter 7, the second evaporimeter 8 and fourth officer heat exchanger 17, to compressor 4, carry.
No matter adopt which kind of order, the circulation of the cold-producing medium of the first heat pump 2 order preferably basic so that the first evaporimeter 7 and the secondary heat exchanger 16 of the second evaporimeter 8 to the three and the forward mode of fourth officer heat exchanger 17 are set.Other structure and described embodiment 1 are same, and therefore description thereof is omitted.
Embodiment 5
Figure 15 means the schematic diagram of the embodiment 5 of steam generation systems 1 of the present invention.The steam generation systems 1 of the present embodiment 5 is basic same with described embodiment 2.Therefore, below centered by both differences, describe, mark identical symbol in corresponding position and illustrate.
In described embodiment 2, gas phase part and liquid phase part with the mixed proportion of regulation from middle cooler 18 via the second evaporimeter 8, the fourth officer heat exchanger 17 that arranges according to expectation and to compressor 4 supplies, but, in the present embodiment 5, link the gas phase section of intercooler 18 and the refrigerant flow path of compressor 4 and be arranged in parallel with the liquid phase section that links intercooler 18 and the refrigerant flow path of compressor 4.In addition, the fourth officer heat exchanger 17 that is provided with the second evaporimeter 8 and arranges according to expectation on the latter's refrigerant flow path.It should be noted that, from the cold-producing medium of the gas phase of intercooler 18 part except directly supplying with to the entrance side of compressor 4, also as shown in double dot dash line A, in the situation that be provided with fourth officer heat exchanger 17 to side supply in front of it.
The present embodiment 5 is corresponding with respect to the relation of described embodiment 1 with described embodiment 2 with respect to the relation of described embodiment 4.Other structure and described embodiment 2 are same, and therefore description thereof is omitted.
Next, the variation of the steam generation systems 1 of the present embodiment 5 described.Now, centered by the difference with Figure 15, describe, to same incomplete structure explanation.In addition, marking identical symbol in corresponding position illustrates.
Figure 16 means the schematic diagram of variation of the steam generation systems 1 of the present embodiment 5.In the steam generation systems 1 of Figure 15, cold-producing medium from the compressor 9 of the second heat pump 3 is supplied with to intercooler 18, but in this variation, replacement is to intercooler 18 supplies or on the basis of supplying with to intercooler 18, as shown in double dot dash line A to supplying with towards the refrigerant flow path of the gas phase of compressor 4 part from middle cooler 18, perhaps, as shown in double dot dash line B to supplying with towards the refrigerant flow path of the liquid phase part of compressor 4 from middle cooler 18.In the situation that adopt the latter, can supply with to the entrance side of the second evaporimeter 8, also can supply with to outlet side, in the situation that be provided with fourth officer heat exchanger 17, can supply with to the entrance side of this fourth officer heat exchanger 17, also can supply with to outlet side.In addition, also can be as shown in double dot dash line C, from the cold-producing medium of the compressor 9 of the second heat pump 3 to the expansion valve 6 from the first heat pump 2 the refrigerant flow path interflow towards intercooler 18.
Embodiment 6
Figure 17 means the schematic diagram of the embodiment 6 of steam generation systems 1 of the present invention.The steam generation systems 1 of the present embodiment 6 is basic same with described embodiment 3.Therefore, below centered by both differences, describe, mark identical symbol in corresponding position and illustrate.
In described embodiment 3, cold-producing medium from the expansion valve 6 of the first heat pump 2 is supplied with to compressor 4 via intercooler 19 and the second evaporimeter 8, but in the present embodiment 6, from the cold-producing medium of the expansion valve 6 of the first heat pump 2, via intercooler 19 but do not supply with to compressor 4 via the second evaporimeter 8 ground, and via intercooler 19, via the second evaporimeter 8, to compressor 4, do not supply with concurrently therewith.
It should be noted that, as shown in double dot dash line A, 6 supplies towards intercooler 19 of the expansion valve from the first heat pump of cold-producing medium also can be collaborated to carry out towards the cold-producing medium of intercooler 19 with the compressor 9 from the second heat pump 3.In addition, as shown in double dot dash line X, according to circumstances different, from middle cooler 19, towards the cold-producing medium of compressor 4, also can partly supply with to the front of fourth officer heat exchanger 17.
The present embodiment 6 is corresponding with respect to the relation of described embodiment 1 with described embodiment 3 with respect to the relation of described embodiment 4.Other structure and described embodiment 3 are same, and therefore description thereof is omitted.
Next, the variation of the steam generation systems 1 of the present embodiment 6 described.Now, centered by the difference with Figure 17, describe, to same incomplete structure explanation.In addition, marking identical symbol in corresponding position illustrates.
Figure 18 means the schematic diagram of variation 1 of the steam generation systems 1 of the present embodiment 6.In the steam generation systems 1 of Figure 17, cold-producing medium from the compressor 9 of the second heat pump 3 is supplied with to intercooler 19, but in this variation, replacement is to intercooler 19 supplies or on the basis of supplying with to intercooler 19, also can be as shown in double dot dash line A to the expansion valve 6 from the first heat pump 2 the refrigerant flow path interflow towards intercooler 19, also can be to supplying with towards the refrigerant flow path of compressor 4 via the second evaporimeter 8 from expansion valve 6 as shown in double dot dash line B, can also be to supplying with towards the refrigerant flow path of compressor 4 from middle cooler 19 as shown in double dot dash line C.
Figure 19 means the schematic diagram of variation 2 of the steam generation systems 1 of the present embodiment 6.In this variation, at the outlet side of the expansion valve 6 of the first heat pump 2, be provided with separator 22 (22A～22C).From the cold-producing medium of the expansion valve 6 of the first heat pump 2, via common flow path 24, branch into towards the stream 25 of the second evaporimeter 8 with towards the stream 26 of intercooler 19, separator 22 can be arranged on wherein on arbitrary position.The separator that the separator that also can make to be arranged at common flow path 24 is the first separator 22A, be arranged at separator towards the stream 25 of the second evaporimeter 8 is the second separator 22B, be arranged at towards the stream 26 of intercooler 19 is the 3rd separator 22C, thereby is arranged with the combination shown in Figure 20.In Figure 20,1 means to arrange, and 0 means without arranging.
In Figure 20, under the pattern of the 1st row, any separator is not set.Under the pattern of the 2nd row, the first separator 22A only is set.In this case, the liquid phase part separated by separator 22A is supplied with to intercooler 19 and the second evaporimeter 8, and the gas phase part is supplied with to the arbitrary position from the second evaporimeter 8 to compressor 4 as shown in double dot dash line A.
In addition, under the pattern of the 3rd row, only be provided with the second separator 22B.In this case, cold-producing medium from the expansion valve 6 of the first heat pump 2 is supplied with to intercooler 19 and separator 22B, the liquid phase part separated by separator 22B is supplied with to the second evaporimeter 8, and the gas phase part is supplied with to the arbitrary position from the second evaporimeter 8 to compressor 4 as shown in double dot dash line A.
In addition, under the pattern of the 4th row, only be provided with the 3rd separator 22C.In this case, cold-producing medium from the expansion valve 6 of the first heat pump 2 is supplied with to the second evaporimeter 8 and separator 22C, the liquid phase part separated by separator 22C is supplied with to intercooler 19, and the gas phase part is supplied with to the arbitrary position from the second evaporimeter 8 to compressor 4 as shown in double dot dash line A.
And then, as shown in the pattern of the 5th row, also can the second separator 22B and the 3rd separator 22C both sides.No matter adopt which kind of pattern, by separator 22 is set, form the structure that the gas phase part does not enter intercooler 19, the second evaporimeter 8, can reduce thus the heat exchanger that forms them.
Embodiment 7
Figure 21 means the schematic diagram of the embodiment 7 of steam generation systems 1 of the present invention.The steam generation systems 1 of the present embodiment 7 is basic same with described embodiment 4.Therefore, below centered by both differences, describe, mark identical symbol in corresponding position and illustrate.
In described embodiment 4, the first evaporimeter 7 and the second evaporimeter 8 are arranged in parallel, passed through the cold-producing medium of shared expansion valve 6 respectively by the first evaporimeter 7 and the second evaporimeter 8, and in the present embodiment 7, from the cold-producing medium of the condenser 5 of the first heat pump 2 in the mode that walks abreast by following stream: the refrigerant flow path that possesses the refrigerant flow path of the first expansion valve 6A and the first evaporimeter 7 and possess the second expansion valve 6B and the second evaporimeter 8, then to compressor 4, supply with.Other structure and described embodiment 4 are same, and therefore description thereof is omitted.
Embodiment 8
Figure 22 means the schematic diagram of the embodiment 8 of steam generation systems 1 of the present invention.The steam generation systems 1 of the present embodiment 8 is basic same with described embodiment 5.Therefore, below centered by both differences, describe, mark identical symbol in corresponding position and illustrate.
In described embodiment 5, from the refrigerant flow path of the gas phase of intercooler 18 part and the refrigerant flow path of liquid phase part, be arranged in parallel, passed through the cold-producing medium of shared expansion valve 6 respectively by the refrigerant flow path of described gas phase part and the refrigerant flow path of liquid phase part, and in the present embodiment 8, cold-producing medium from the condenser 5 of the first heat pump 2 is supplied with to intercooler 18 via the first expansion valve 6A, and via the second expansion valve 6B, also to the second evaporimeter 8, supplies with concurrently therewith.And the gas phase section of intercooler 18 is connected by refrigerant flow path with compressor 4.On the other hand, from the cold-producing medium of the second expansion valve 6B, via the second evaporimeter 8 with according to the fourth officer heat exchanger 17 of expecting to arrange, to compressor 4, supply with.Other structure and described embodiment 5 are same, and therefore description thereof is omitted.
Next, the variation of the steam generation systems 1 of the present embodiment 8 described.Now, centered by the difference with Figure 22, describe, to same incomplete structure explanation.In addition, marking identical symbol in corresponding position illustrates.
Figure 23 means the schematic diagram of variation 1 of the steam generation systems 1 of the present embodiment 8.In the steam generation systems 1 of Figure 22, cold-producing medium from the compressor 9 of the second heat pump 3 is supplied with to intercooler 18, but in this variation, replacement is to intercooler 18 supplies or on the basis of supplying with to intercooler 18, also can be as shown in double dot dash line A to supplying with towards the refrigerant flow path of compressor 4 from middle cooler 18, also can be as shown in double dot dash line B to from the second expansion valve 6B arbitrary position supply towards the refrigerant flow path of compressor 4 via the second evaporimeter 8.Perhaps, also can make cold-producing medium from the compressor 9 of the second heat pump 3 as shown in double dot dash line C with the cold-producing medium interflow of the first expansion valve 6A from the first heat pump 2 and supply with to intercooler 18.
Figure 24 means the schematic diagram of variation 2 of the steam generation systems 1 of the present embodiment 8.In this variation, from the second expansion valve 6B, towards the refrigerant flow path of the second evaporimeter 8, be provided with separator 22.Thus, cold-producing medium from the second expansion valve 6B passes through separator 22 by gas-liquid separation, its liquid phase part is supplied with to the second evaporimeter 8, the gas phase part as shown in double dot dash line A to the arbitrary position supply towards the refrigerant flow path of compressor 4 from the second evaporimeter 8.
Embodiment 9
Figure 25 means the schematic diagram of the embodiment 9 of steam generation systems 1 of the present invention.The steam generation systems 1 of the present embodiment 9 is basic same with described embodiment 6.Therefore, below centered by both differences, describe, mark identical symbol in corresponding position and illustrate.
In described embodiment 6, in the first heat pump 2, from the cold-producing medium of shared expansion valve 6, in the mode that walks abreast, by intercooler 19 and the second evaporimeter 8, to compressor 4, supply with, and in the present embodiment 9, cold-producing medium from the condenser 5 of the first heat pump 2 is supplied with to intercooler 19 via the first expansion valve 6A, and via the second expansion valve 6B, also to the second evaporimeter 8, supplies with concurrently therewith.It should be noted that, also can be as shown in double dot dash line A, make the cold-producing medium interflow with compressor 9 from the second heat pump 3 from the cold-producing medium of the second expansion valve 6B, and supply with to intercooler 19.Other structure and described embodiment 6 are same, and therefore description thereof is omitted.
Next, the variation of the steam generation systems 1 of the present embodiment 9 described.Now, centered by the difference with Figure 25, describe, omit the explanation to same structure.In addition, marking identical symbol in corresponding position illustrates.
Figure 26 means the schematic diagram of variation 1 of the steam generation systems 1 of the present embodiment 9.In the steam generation systems 1 of Figure 25, cold-producing medium from the compressor 9 of the second heat pump 3 is supplied with to intercooler 19, and in this variation, replacement is to intercooler 19 supplies or on the basis of supplying with to intercooler 19, also can be to the refrigerant flow path interflow towards intercooler 19 from the first expansion valve 6A as described in double dot dash line A, also can be to supplying with towards the refrigerant flow path of compressor 4 from middle cooler 19 as shown in double dot dash line B, can also be as shown in double dot dash line C to supplying with towards arbitrary position of the refrigerant flow path of compressor 4 via the second evaporimeter 8 from the second expansion valve 6B.
Figure 27 means the schematic diagram of variation 2 of the steam generation systems 1 of the present embodiment 9.In this variation, from the second expansion valve 6B, be provided with the first separator 22A towards the refrigerant flow path of the second evaporimeter 8.Thus, from the cold-producing medium of the second expansion valve 6B in the first separator 22A by gas-liquid separation, its liquid phase part is supplied with to the second evaporimeter 8, the gas phase part as shown in double dot dash line A to the arbitrary position supply towards the refrigerant flow path of compressor 4 from the second evaporimeter 8.In addition, also can towards the refrigerant flow path of intercooler 19, the second separator 22B be set from the first expansion valve 6A.Thus, from the cold-producing medium of the first expansion valve 6A in the second separator 22B by gas-liquid separation, its liquid phase part is supplied with to intercooler 19, the gas phase part as shown in double dot dash line B to the arbitrary position supply towards the refrigerant flow path of compressor 4 from the second evaporimeter 8.
Figure 28 means the figure that combination is set of the first separator 22A and the second separator 22B.In the figure, 1 means to arrange, and 0 means without arranging.As shown in the drawing, two separator 22A, 22B can be set, also a wherein side separator, the setting that can also omit two sides' separator can only be set.
Embodiment 10
In described each embodiment, the first heat pump 2 consists of single hop, and the second heat pump 3 also consists of single hop, but the hop count of each heat pump 2,3 can suitably change.In other words, in described each embodiment, exemplified the second heat pump 3 combinations of the first heat pump 2 of single hop and single hop, the example on the whole formed as the heat pump by two sections with regard to steam generation systems 1, but the hop count of the heat pump of formation steam generation systems 1 can suitably change.It should be noted that, in the heat pump of a plurality of sections (multistages), except the heat pump of the such one dimension multistage of Fig. 9, also comprise the heat pump of a plurality of dimensions (multidimensional) that Fig. 1 is such or the heat pump of both combinations.
For example, Figure 29 A means that the first heat pump 2 is by two sections form, the second heat pump 3 consists of single hop example.In other words, form steam generation systems 1 by the heat pump of three sections.It should be noted that, for the second heat pump 3, also can with known two sections heat pumps in the past similarly, by two or more multistage, formed.
In the steam generation systems 1 of Figure 29 A, except the heat pump (the second heat pump 3) of hypomere, be provided as the first evaporimeter 7A, 7B and the second evaporimeter 8A, the 8B of the evaporimeter of each heat pump (the first heat pump 2A, the 2B of each section), by the first evaporimeter 7A, 7B, neighbouring heat pump is connected to each other, heat source fluid is by the second evaporimeter 8A, 8B.Now, adjacent heat pump up and down also can connect according to the arbitrary relation illustrated in described each embodiment each other.In other words, neighbouring heat pump connects by indirect heat exchanger 13 (13A, 13B) each other in illustrated example, but also can pass through as described above intercooler 18,19, connects.In addition, the heat pump that forms each section of the first heat pump 2 is not limited to the structure of described embodiment 1, also can adopt the structure of other embodiment.In addition, be typically, heat source fluid according to the heat pump from epimere successively towards the mode of the heat pump of hypomere successively by each second evaporimeter 8 (8A, 8B).
In the situation that steam generation systems 1 forms (the first heat pump 2 is multistage) by the heat pump more than 3 sections, be preferably, except the heat pump (the second heat pump 3) of hypomere, as evaporimeter, the first evaporimeter 7A, 7B and the second evaporimeter 8A, 8B are set in the first heat pump 2A, the 2B of all sections, by each first evaporimeter 7A, 7B, neighbouring heat pump is connected to each other, heat source fluid is to pass through successively each second evaporimeter 8A, 8B from epimere towards the mode of hypomere.
Preferably this kind of structure the reasons are as follows.; Figure 29 B makes the first heat pump 2 for the T-S line chart in single hop, the second heat pump 3 situation that is two sections; Figure 29 C is that the first heat pump 2 is two sections and the first evaporimeter 7A, 7B is set in each section and the second evaporimeter 8A, 8B, and the T-S line chart in the second heat pump 3 situation that is single hop.Known when comparison diagram 29B and Figure 29 C, the area of the loss amount of describing oblique line of Figure 29 C can reduce.Therefore, in steam generation systems 1, preferably in heat pump 2A, the 2B of heat pump 3 with external each section except hypomere, the second evaporimeter 8A, 8B are set and heat source fluid is passed through.
In the situation that so make steam generation systems 1 form (the first heat pump 2 is multistage) by the heat pump more than 3 sections, when wish arranges the first secondary heat exchanger 14, the first secondary heat exchanger 14 is arranged in the heat pump (the heat pump 2A of the epimere of the first heat pump 2) of epimere and gets final product.
In addition, in the situation that steam generation systems 1 is consisted of the heat pump more than 3 sections, when wish arranges the second secondary heat exchanger 15, the second secondary heat exchanger 15 is arranged in the heat pump (heat pump of the hypomere of the second heat pump 3) of hypomere and gets final product.
And then, in the situation that steam generation systems 1 is consisted of the heat pump more than 3 sections, when wish arranges the 3rd secondary heat exchanger 16 and/or fourth officer heat exchanger 17, the 3rd secondary heat exchanger 16 and/or fourth officer heat exchanger 17 can be arranged in first heat pump 2 (2A, 2B) of each section.In this case, in the first heat pump 2B of hypomere, the 3rd secondary heat exchanger 16 become from the expansion valve 6B of the hypomere of the first heat pump 2 towards the cold-producing medium of compressor 4B and from the compressor 9 of the second heat pump 3 indirect heat exchanger towards the cold-producing medium of the first evaporimeter 7B, but, in each first heat pump 2A of top section than it, the 3rd secondary heat exchanger 16 becomes from the expansion valve 6A of the first heat pump 2A of this section the indirect heat exchanger towards the cold-producing medium of the first evaporimeter 7A towards the compressor 4B of the cold-producing medium of compressor 4A and the first heat pump 2B from next section.
Figure 30 means the schematic diagram of an example of the vapor system 27 of the steam generation systems 1 that has used described embodiment 1.At this, for convenience of description, the evaporimeter 12 of the second evaporimeter 8 of the first heat pump 2, the fourth officer heat exchanger 17 arranged according to expectation, the second heat pump 3, the second secondary heat exchanger 15 of arranging according to expectation being called to heat draws with heat exchanger (8,17,12,15).In addition, the condenser of the first heat pump 25, the first secondary heat exchanger 14 of arranging according to expectation being called to steam occurs with heat exchanger (5,14).
Vapor system 27 possesses steam generation systems 1 and boiler 28.
Steam generation systems 1 is used the structure of embodiment 1, but also can use described other the structure of embodiment.No matter adopt which kind of structure, steam generation systems 1 draws with drawing the heat of drainage liquid in heat exchanger (8,17,12,15) at heat, at steam, steam occurs to be produced with in heat exchanger (5,14), water heating.Therefore, heat draw with in heat exchanger (8,17,12,15) by the drainage liquid that uses equipment 29 from steam is arranged.The pass-through mode towards each evaporimeter 8,12 that draws use heat exchanger (8,17,12,15) as heat and each secondary heat exchanger 17,15 of drainage liquid is as illustrated based on Fig. 2.
On the other hand, can occur to supply feedwater with heat exchanger (5,14) to steam by supply-water pump 30, occur with accumulating the water of desired amount in heat exchanger (5,14) at steam.Specifically, by pure water or soft water or replace them or sneak into using the drainage liquid of equipment 29 to occur to supply with heat exchanger (5,14) to steam via supply-water pump 30, feed water valve 31, non-return valve 32 from steam among them.Water, steam towards as steam, occur with the pass-through mode of the condenser 5 of heat exchanger (5,14) and the first secondary heat exchanger 14 as described in illustrate in each embodiment.
Be typically, boiler 28 is fuel burning boiler or boilers heated electrically.The fuel burning boiler is to make the device of steam by the burning of fuel, in the mode that vapour pressure is maintained in to the vapour pressure of expectation, adjusts having or not of burning and quantity combusted.In addition, boilers heated electrically is to make the device of steam by electric heater, in the mode that vapour pressure is maintained in to the vapour pressure of expectation, adjusts having or not and delivery to the power supply of electric heater.Can supply feedwater to boiler 28 via supply-water pump 33 and non-return valve 34, the water level in the cylinder body of boiler 28 is maintained in the water level of expectation.
With the steam road 35 of heat exchanger (5,14) and the mode of collaborating from the steam road 36 of boiler 28, form occurring from steam.This interflow can be carried out with the steam manifold.In addition, occurring, on the steam road 35 with heat exchanger (5,14), at the upstream side than the top trip of interflow section, to be provided with non-return valve 37 from steam.Thus, in stopping, steam generation systems 1 can prevent from occurring by heat exchanger (5,14) adverse current to steam from the steam of boiler 28.
And then, on the steam road 36 from boiler 28, at the upstream side than the top trip of interflow section, be provided with boiler steam supply valve 38.Boiler steam supply valve 38 is the pressure-reducing valve (secondary pressure adjustment valve) of self-operated type in illustrated example.It should be noted that, the upstream side of boiler steam supply valve 38 is maintained in than downstream high pressure by boiler 28.
Steam from steam generation systems (5,14), boiler 28 is used equipment 29 to carry to one or more steams.The drainage liquid that steam is used equipment 29 via the first steam trap 39 separator box 40 to hollow container shaped discharge.Be connected with the first stream 41 on the top of separator box 40, be connected with the second stream 42 in bottom.
On the first stream 41, be disposed with heat and draw with heat exchanger (8,17,12,15) and the second steam trap 43 from separator box 40 sides.Owing to adopting such structure, the drainage liquid that steam is used equipment 29 by the first steam trap 39 to after discharging under low pressure, by heat, draw with heat exchanger (8,17,12,15), then by the second steam trap 43 to (being typically under atmospheric pressure) discharge under low pressure more.In other words, steam is used the drainage liquid of equipment 29 by discharging via the first steam trap 39, thereby become shwoot steam and condensed water thereof, draw be cooled with heat exchanger (8,17,12,15) (comprising supercooling) by heat after, discharge from the second steam trap 43.In the situation that such structure, at heat, draw with the fluid of giving heat to cold-producing medium in heat exchanger (8,17,12,15) and can be maintained the temperature that surpasses 100 ℃ with superatmospheric pressure.It should be noted that, draining from the second steam trap 43 can directly discard, also can supply with to the supply tank 44 that boiler 28 and/or steam are occurred to supply water with heat exchanger (5,14), can also be via such supply tank 44 as occurring to use with the water supply of heat exchanger (5,14) to steam.
On the other hand, be provided with dump valve 45 on the second stream 42.Dump valve 45 is the pressure-reducing valve (pressure-regulating valve) of self-operated type in illustrated example.Owing to being such structure, thus steam use equipment 29 drainage liquid can by the first steam trap 39 to after discharging under low pressure, by dump valve 45, to (being typically under atmospheric pressure) under low pressure more, discharge.And, fluid from dump valve 45 can directly discard, also can supply with to the supply tank 44 that boiler 28 and/or steam are occurred to supply water with heat exchanger (5,14), can also be via such supply tank 44 as occurring to use with the water supply of heat exchanger (5,14) to steam.
And then, when urgent in order to tackle and while having a power failure, preferably, the separator box 40 on the first stream 41 and heat draw with between heat exchanger (8,17,12,15), the magnetic valve 46 of normal pass type being set, and the magnetic valve 47 of open type is set side by side with dump valve 45 on the second stream 42.In this case, when common, the magnetic valve 46 of the first stream 41 is maintained in the state of opening, and the magnetic valve 47 of the second stream 42 is maintained in the state of cutting out.And, when urgent or while having a power failure, the magnetic valve 46 of the first stream 41 cuts out, the magnetic valve 47 of the second stream 42 is opened, and therefore from steam, uses the drainage liquid of equipment 29 via heat, not draw with heat exchanger and discharge (8,17,12,15).
To steam, occur to supply with pure water or soft water, to use drainage liquid or such drainage liquid and the mixing water of pure water or soft water of equipment 29 from steam with heat exchanger (5,14).For the water system of supplying with, having no particular limits, can be for example following structure.It should be noted that, the drainage liquid that uses equipment 29 from steam is except be only the state of liquid, can also be the state of gas-liquid two-phase (at shwoot steam and the condensed water thereof of the drainage liquid of superatmospheric state generation when emitting under the low pressure than its low pressure).
(A), as shown in double dot dash line A, the drainage liquid that will consist of the liquid separated by separator box 40 from the upstream side of dump valve 45 is supplied with to the entrance side of supply-water pump 30.
(B), as shown in double dot dash line B, from the upstream side of the second steam trap 43, will draw with the drainage liquid heat exchanger (8,17,12,15) and supply with to the entrance side of supply-water pump 30 by heat.It should be noted that, heat draws with heat exchanger (8,17,12,15) and consists of a plurality of heat exchangers, but also can as shown in double dot dash line B ', make drainage liquid branch after passing through a part of heat exchanger, and supplies with to the entrance side of supply-water pump 30.
(C), as shown in double dot dash line C, from the downstream of the second steam trap 43, will draw with the drainage liquid heat exchanger (8,17,12,15) and supply with to the entrance side of supply-water pump 30 by heat.
(D), as shown in the dashed region of Figure 30 bottom, will temporarily accumulate in supply tank 44 from the drainage liquid of the second steam trap 43 and/or from the drainage liquid of dump valve 45 etc., and the water in this supply tank 44 will be supplied with to the entrance side of supply-water pump 30.Except use the drainage liquid of equipment 29 from steam, can also suitably supply with pure water or soft water to supply tank 44.
(E) also can adopt any combination more than two in described A～D.In this case, supplying water to steam generation heat exchanger (5,14) for the interflow, water route more than two, but in the situation that each are different for the pressure in water route, after each is for the interflow, water route, supply-water pump 30 is not set, and is getting final product by the Ge Gong water route, position of front, supply-water pump being set than interflow section.
Occur to be provided with the steam of heat exchanger (5,14) with from the position of the pressure of the interflow steam of the steam of boiler 28 first sensor 48 formed by pressure sensor can detect from steam.In addition, to draw by pressure or the temperature of the fluid of heat exchanger (8,17,12,15) and be provided with the second sensor 49 formed by pressure sensor or temperature sensor in order to detect by heat.In addition, steam generation systems 1 is controlled according to one or both the detected value in first sensor 48 and the second sensor 49.
For example, control the compressor (compressor 4 of the first heat pump) of the heat pump of epimere according to the detected pressures of first sensor 48, and control and get final product according to the pressure of the cold-producing medium of the evaporimeter 7,8 of the condenser 10 of this section or an epimere at the compressor (compressor 9 of the second heat pump 3) of each heat pump of its hypomere.
Perhaps, control the compressor (compressor 9 of the second heat pump 3) of the heat pump of hypomere according to the detected pressures of the second sensor 49 or detected temperatures, and the compressor (compressor 4 of the first heat pump 2) of each heat pump of section is controlled and is got final product thereon according to the pressure of the cold-producing medium of the condenser 10 of 7,8 or hypomeres of evaporimeter of this section or temperature.
Figure 31 means the schematic diagram of variation of the vapor system 27 of Figure 30.The vapor system 27 of Figure 31 is also basic and Figure 30 is same.Therefore, below centered by both differences, describe, mark identical symbol in corresponding position and illustrate.
In this variation, steam is used the drainage liquid of equipment 29 temporarily to accumulate in the baffle-box 50 as drainage liquid accumulating part.And the drainage liquid of baffle-box 50 can draw with heat exchanger (8,17,12,15) and supply with to heat by the first stream 41, and can via heat, not draw with heat exchanger and discharge by the 3rd stream 51 (8,17,12,15).
Specifically, be connected with the first stream 41 in the bottom of baffle-box 50, be connected with the 3rd stream 51 in the position than its top section.In the first stream 41, from baffle-box 50 1 sides, start to be disposed with import valve 52, heat draws with heat exchanger (8,17,12,15) and the second steam trap 43.Import valve 52 is the pressure-reducing valve (secondary pressure adjustment valve) of self-operated type in this variation.
Owing to being such structure, therefore, the drainage liquid that steam is used equipment 29 is by importing valve 52 to after discharging under low pressure, by heat, drawing with heat exchanger (8,17,12,15) afterwards by the second steam trap 43 to (being typically under atmospheric pressure) discharge under the low pressure of low pressure more.And, draining from the second steam trap 43 can directly discard, also can supply with to the supply tank 44 that boiler 28 and/or steam are occurred to supply water with heat exchanger (5,14), can also be via such supply tank 44 as occurring to use with the water supply of heat exchanger (5,14) to steam.
On the other hand, be provided with the 3rd steam trap 53 in the 3rd stream 51.Because the 3rd stream 51 is connected with baffle-box 50 in the position than the first stream 41 top sides, the drainage liquid therefore overflowed from baffle-box 50 is discharged from the 3rd stream 51.And this draining is discharged via the 3rd steam trap 53.Then, draining from the 3rd steam trap 53 can directly discard, also can, to supply tank 44 supplies of supplying water with heat exchanger (5,14) are occurred to for boiler 28 and/or steam, can also via such supply tank 44, as occurring to steam, with the water supply of heat exchanger (5,14), not use.
And then, when urgent in order to tackle and while having a power failure, preferably between the importing valve 52 in the first stream 41 and baffle-box 50, be provided with the magnetic valve 46 of normal pass type.In this case, when common, the magnetic valve 46 of the first stream 41 is maintained in the state of opening.And, when urgent or while having a power failure, the magnetic valve 46 of the first stream 41 cuts out, therefore, steam is used the drainage liquid of equipment 29 via heat, not draw with heat exchanger and discharge (8,17,12,15) by the 3rd stream 51.
In the situation that this variation similarly, to steam, occur to supply with pure water or soft water, to use drainage liquid or such drainage liquid and the mixing water of pure water or soft water of equipment from steam with heat exchanger (5,14).For the water system of supplying with, having no particular limits, can be for example similarly following structure with the situation of Figure 30.
(A), as shown in double dot dash line A, from the upstream side that imports valve 52, (being provided with any side of swimming from it in side or downstream the situation of magnetic valve 46 all can.) will to the entrance side of supply-water pump 30, supply with from the drainage liquid of baffle-box 50.
(B), as shown in double dot dash line B, from the upstream side of the second steam trap 43, will draw with the drainage liquid heat exchanger (8,17,12,15) and supply with to the entrance side of supply-water pump 30 by heat.It should be noted that, heat draws with heat exchanger (8,17,12,15) and consists of a plurality of heat exchangers, but also can as shown in double dot dash line B ', make drainage liquid branch after passing through a part of heat exchanger, and supplies with to the entrance side of supply-water pump 30.
(C), as shown in double dot dash line C, from the downstream of the second steam trap 43, will draw with the drainage liquid heat exchanger (8,17,12,15) and supply with to the entrance side of supply-water pump 30 by heat.
(D), as shown in the dashed region of Figure 31 bottom, will temporarily accumulate in supply tank 44 from the drainage liquid of the second steam trap 43 and/or from the drainage liquid of the 3rd steam trap 53 etc., and the water in this supply tank 44 will be supplied with to the entrance side of supply-water pump 30.Except use the drainage liquid of equipment 29 from steam, can also suitably supply with pure water or soft water to supply tank 44.It should be noted that, supply tank 44 can be the situation of Figure 30, can be not yet opening and can accumulate drainage liquid with superatmospheric pressure upward.
(E) also can adopt any combination more than two in described A～D.In this case, supplying water to steam generation heat exchanger (8,17,12,15) for the interflow, water route more than two, but in the situation that each are different for the pressure in water route, after each is for the interflow, water route, supply-water pump 30 is not set, gets final product and in the Ge Gong water route, position more forward than interflow section, supply-water pump is set.
Steam generation systems 1 of the present invention is not limited to the structure of described each embodiment, can suitably be changed.For example, used the vapor system 27 shown in Figure 30 and Figure 31 as the Application Example of steam generation systems 1, but can certainly use system in addition.In addition, thermal source as steam generation systems 1 has illustrated the example of using from the drainage liquid of steam use equipment 29, but be not limited to drainage liquid, such as the water that also can use waste gas from boiler etc., the water used as the cooling water of this waste gas, row's warm water of discharging from factory etc., the water used as the cooling water of compressor, the water used as cooling water the oil cooler of engine (drive units of compressor etc.), use as the cooling water of the water jacket (jacket) of engine etc.
And then steam generation systems 1 is not limited to the temperature that reduces heat source fluid and passes through the situation of this heat generation steam.For example, also can use from steam and use the discharge steam of equipment 29 as heat source fluid.In this case, for example also can in Fig. 1, make to discharge steam by fourth officer heat exchanger 17 and second evaporimeter 8 of the first heat pump 2, and reducing pressure by passing through steam trap, throttle orifice or pressure-reducing valve after this second evaporimeter 8, and by the second secondary heat exchanger 15 and evaporimeter 12 of the second heat pump 3.In discharging the stream of steam, can steam trap etc. also be set at the outlet side of the evaporimeter 12 of the second heat pump 3, can not arrange yet.In other words, the steam of the evaporimeter 12 by the second heat pump 3 can be superatmospheric state, can be also atmospheric pressure.It should be noted that, can certainly omit one or both in fourth officer heat exchanger 17 and the second secondary heat exchanger 15.
Symbol description
1 steam generation systems
2 first heat pumps
3 second heat pumps
4 (the first heat pump) compressor
5 (the first heat pump) condenser
6 (the first heat pump) expansion valve
7 (the first heat pump) first evaporimeter
8 (the first heat pump) second evaporimeter
9 (the second heat pump) compressor
10 (the second heat pump) condenser
11 (the second heat pump) expansion valve
12 (the second heat pump) evaporimeter
13 indirect heat exchangers
14 first secondary heat exchangers
15 second secondary heat exchangers
16 the 3rd secondary heat exchangers
17 fourth officer heat exchangers
18 intercoolers
19 intercoolers
22 separators
27 vapor systems
29 steams are used equipment

Claims (12)

1. a steam generation systems, is characterized in that, this steam generation systems possesses:
The first heat pump, it consists of single hop or multistage, and at least at hypomere, has the first evaporimeter and the second evaporimeter;
The second heat pump, it consists of single hop or multistage, and is connected with described the first heat pump via the condenser doubled as the epimere of the first evaporimeter of described hypomere,
Heat source fluid is the evaporimeter of the hypomere of the second evaporimeter by described the first heat pump and described the second heat pump successively,
In the condenser of the epimere of described the first heat pump, water is heated and produced steam.
2. steam generation systems according to claim 1, is characterized in that,
Described the second heat pump consists of the heat pump of single hop,
Draw heat from the heat source fluid of the evaporimeter of the hypomere of the second evaporimeter by described the first heat pump and described the second heat pump successively,
In the condenser of the epimere of described the first heat pump, water is heated and produced steam.
3. steam generation systems according to claim 1 and 2, is characterized in that,
Described the first heat pump consists of the heat pump of multistage, and wherein the heat pump of part or all possesses described the first evaporimeter and described the second evaporimeter as evaporimeter,
Each described first evaporimeter is connected to each other adjacent heat pump up and down,
Heat source fluid according to the heat pump from epimere successively towards the order of the heat pump of hypomere by each described second evaporimeter.
4. steam generation systems according to claim 3, is characterized in that,
The heat pump that forms each section of described the first heat pump possesses described the first evaporimeter and described the second evaporimeter as evaporimeter.
5. according to the described steam generation systems of any one in claim 1 to 4, it is characterized in that,
With regard to the heat pump of in the heat pump of the single hop that forms described the first heat pump or multistage, section that there is described the first evaporimeter and described the second evaporimeter, be provided with in series or in parallel described the first evaporimeter and described the second evaporimeter at it from expansion valve towards the refrigerant flow path of compressor, or be provided with in parallel the first expansion valve and described the first evaporimeter and the second expansion valve and described the second evaporimeter from condenser towards the refrigerant flow path of compressor.
6. according to the described steam generation systems of any one in claim 1 to 5, it is characterized in that,
Described the first heat pump is connected with any relation in following (a)～(c) with described the second heat pump,
(a) possess and accept from the cold-producing medium of the compressor of described the second heat pump with from the cold-producing medium of the expansion valve of described the first heat pump and make two cold-producing mediums carry out the indirect heat exchanger of heat exchange under unmixed state, this indirect heat exchanger is as the condenser of described the second heat pump and as the first evaporimeter of described the first heat pump
(b) possess and accept from the cold-producing medium of the compressor of described the second heat pump with from the cold-producing medium of the expansion valve of described the first heat pump and make two cold-producing mediums directly carry out contiguously the intercooler of heat exchange, this intercooler is as the condenser of described the second heat pump and as the first evaporimeter of described the first heat pump
(c) possess and accept from the cold-producing medium of the compressor of described the second heat pump with from the cold-producing medium of the expansion valve of described the first heat pump and make two cold-producing mediums directly carry out contiguously heat exchange and make this two cold-producing medium and condenser from described the first heat pump via expansion valve ground, to the cold-producing medium of the expansion valve supply of described the second heat pump, not carry out the intercooler of heat exchange under unmixed state, this intercooler is as the condenser of described the second heat pump and as the first evaporimeter of described the first heat pump.
7. according to the described steam generation systems of any one in claim 1 to 6, it is characterized in that,
In the situation that described the first heat pump and/or described the second heat pump are multistage, the heat pump of adjacent section connects with any relation in following (a)～(c) each other,
(a) possess and accept from the cold-producing medium of the compressor of hypomere heat pump with from the cold-producing medium of the expansion valve of epimere heat pump and make two cold-producing mediums carry out the indirect heat exchanger of heat exchange under unmixed state, this indirect heat exchanger is as the condenser of hypomere heat pump and as the evaporimeter of epimere heat pump
(b) possess and accept from the cold-producing medium of the compressor of hypomere heat pump with from the cold-producing medium of the expansion valve of epimere heat pump and make two cold-producing mediums directly carry out contiguously the intercooler of heat exchange, this intercooler is as the condenser of hypomere heat pump and as the evaporimeter of epimere heat pump
(c) possess and accept from the cold-producing medium of the compressor of hypomere heat pump with from the cold-producing medium of the expansion valve of epimere heat pump and make two cold-producing mediums directly carry out contiguously heat exchange and make this two cold-producing medium and condenser from the epimere heat pump via expansion valve ground, to the cold-producing medium of the expansion valve supply of hypomere heat pump, not carry out the intercooler of heat exchange under unmixed state, this intercooler is as the condenser of hypomere heat pump and as the evaporimeter of epimere heat pump.
8. steam generation systems according to claim 6, is characterized in that,
In the situation that described the first heat pump is connected with the relation of described the second heat pump with (b) of claim 6, from the cold-producing medium of the compressor of described the second heat pump, replace supplying with and to supplying with towards the refrigerant flow path of compressor from described intercooler to described intercooler, or from the cold-producing medium of the compressor of described the second heat pump on the basis of supplying with to described intercooler to supplying with towards the refrigerant flow path of compressor from described intercooler.
9. steam generation systems according to claim 6, is characterized in that,
When the relationship between the first connection and the second heat pump to the heat pump of claim 6, (c), the compressor from the second to the heat pump instead of the refrigerant which is supplied to the intercooler from the intercooler pump toward the first refrigerant flow path of the compressor is supplied toward the intercooler or the compressor or expansion valve of the refrigerant from the supply flow path or the second compressor from the refrigerant pump on the basis of the intercooler to be supplied to the refrigerant flow path is supplied from the first compressor toward the intermediate cooler or heat toward the intercooler to the compressor or expansion valve of the refrigerant flow from the supply path.
10. steam generation systems according to claim 6, is characterized in that,
In the situation that described the first heat pump is connected with the relation of described the second heat pump with (c) of claim 6, possess the separator that the cold-producing medium of the expansion valve from described the first heat pump is carried out to gas-liquid separation,
Gas phase part after being separated by this separator is supplied with to the refrigerant flow path from described the second evaporator to compressor.
11. according to the described steam generation systems of any one in claim 1 to 10, it is characterized in that,
This steam generation systems possesses any one the above secondary heat exchanger in following (a)～(d),
(a) from the condenser of the epimere of described the first heat pump towards the cold-producing medium of expansion valve and the first secondary heat exchanger of water,
(b) from the evaporimeter of the hypomere of described the second heat pump towards the cold-producing medium of compressor and the second secondary heat exchanger of heat source fluid,
(c) in the situation that described the first evaporimeter is indirect heat exchanger, from the expansion valve of the hypomere of described the first heat pump towards the cold-producing medium of compressor and compressor from described the second heat pump the 3rd secondary heat exchanger towards the cold-producing medium of the first evaporimeter,
(d) from the expansion valve of the hypomere of described the first heat pump towards the cold-producing medium of compressor and the fourth officer heat exchanger of heat source fluid,
About water, steam towards the condenser of the epimere of described the first heat pump and the circulation order that is provided with this first secondary heat exchanger in the situation of the first secondary heat exchanger, in the situation that be provided with the described first secondary heat exchanger, be set as this first secondary heat exchanger front
About heat source fluid towards the second evaporimeter of described the first heat pump, the evaporimeter of hypomere that is provided with this fourth officer heat exchanger in the situation of fourth officer heat exchanger, described the second heat pump and the circulation order that is provided with this second secondary heat exchanger in the situation of the second secondary heat exchanger, be set as the evaporimeter of hypomere of described the second heat pump rear
Towards the first evaporimeter of described the first heat pump, the circulation order that is provided with the second evaporimeter of the 3rd secondary heat exchanger in the situation of the 3rd secondary heat exchanger, described the first heat pump and is provided with this fourth officer heat exchanger in the situation of fourth officer heat exchanger, be set as described the first evaporimeter and described the second evaporimeter is more forward than described the 3rd secondary heat exchanger and described fourth officer heat exchanger about cold-producing medium.
12. according to the described steam generation systems of any one in claim 1 to 11, it is characterized in that,
Described heat source fluid is to use the drainage liquid of equipment from steam.
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