WO2015064347A1 - Dispositif de production de vapeur et pompe à chaleur de production de vapeur - Google Patents

Dispositif de production de vapeur et pompe à chaleur de production de vapeur Download PDF

Info

Publication number
WO2015064347A1
WO2015064347A1 PCT/JP2014/077218 JP2014077218W WO2015064347A1 WO 2015064347 A1 WO2015064347 A1 WO 2015064347A1 JP 2014077218 W JP2014077218 W JP 2014077218W WO 2015064347 A1 WO2015064347 A1 WO 2015064347A1
Authority
WO
WIPO (PCT)
Prior art keywords
evaporator
gas
liquid separator
water
refrigerant
Prior art date
Application number
PCT/JP2014/077218
Other languages
English (en)
Japanese (ja)
Inventor
拓人 小池
祐輔 大西
Original Assignee
富士電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 富士電機株式会社 filed Critical 富士電機株式会社
Priority to JP2015544909A priority Critical patent/JP5967315B2/ja
Publication of WO2015064347A1 publication Critical patent/WO2015064347A1/fr

Links

Images

Classifications

    • 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
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/26—Steam-separating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/34—Adaptations of boilers for promoting water circulation
    • 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
    • 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

Definitions

  • the present invention relates to a steam generation device that generates steam by circulating water from a gas-liquid separator to an evaporator using a thermosiphon phenomenon, and a steam generation heat pump including the steam generation device.
  • a steam generation device is usually provided.
  • Patent Document 1 discloses that an evaporator having a heat transfer core through which a refrigerant flows and a gas-liquid separator that stores water are arranged side by side.
  • a steam generator using a thermosiphon phenomenon in which an upper part and a lower part are communicated with each other by an upper pipe and a lower pipe is disclosed.
  • This steam generator generates water by circulating water in the gas-liquid separator to the evaporator through the lower pipe due to the thermosyphon phenomenon, and supplies the generated steam from the upper pipe to the gas-liquid separator. It is configured to send out to the equipment.
  • the gas-liquid separator and the evaporator are installed at substantially the same position in the height direction, so that the gas-liquid separator is transferred to the evaporator.
  • the flow rate of the circulated water is always constant and cannot be controlled. For this reason, since the flow rate of the supplied water does not change even when the load on the evaporator fluctuates, it is difficult to improve the heat exchange performance in the evaporator, and the steam generation efficiency is low. .
  • the present invention has been made in consideration of the above-described problems of the prior art, can control the flow rate of water circulated to the evaporator, and can improve the steam generation efficiency and It aims at providing the steam generation heat pump provided with this steam generation device.
  • a steam generator includes a gas-liquid separator that stores water and an evaporator through which a refrigerant flows, and the upper and lower parts of the gas-liquid separator and the evaporator are an upper pipe and a lower pipe, respectively.
  • the water in the gas-liquid separator is supplied to the evaporator through the lower pipe and evaporated by heat exchange with the refrigerant, and the vapor generated in the evaporator is vaporized through the upper pipe.
  • a steam generation device that forms a thermosiphon circuit that is supplied to the liquid separator and is sent out from the gas-liquid separator, wherein an outlet of the steam in the evaporator is the water stored in the gas-liquid separator.
  • the positional relationship in the height direction of the evaporator and the gas-liquid separator is defined so as to be lower than the water surface.
  • the steam generation heat pump includes a gas-liquid separator that stores water and an evaporator through which a refrigerant flows, and the upper and lower portions of the gas-liquid separator and the evaporator are respectively connected to an upper pipe.
  • a gas-liquid separator that stores water and an evaporator through which a refrigerant flows
  • the upper and lower portions of the gas-liquid separator and the evaporator are respectively connected to an upper pipe.
  • a steam generator that forms a thermosiphon circuit that is supplied to the gas-liquid separator through the gas-liquid separator and is sent out from the gas-liquid separator, a compressor, a refrigerant condenser connected to the discharge side of the compressor, and the refrigerant
  • a steam generation heat pump comprising: an expansion valve connected to an outlet side of the condenser; a refrigerant evaporator connected to an outlet side of the expansion valve; and a refrigerant cycle device for circulating the refrigerant, As the evaporator Using the refrigerant condenser of the medium cycle device, the evaporator and the gas-liquid separation are so arranged that the outlet of the vapor in the evaporator is positioned lower than the surface of the water stored in the gas-liquid separator. The positional relationship in the height direction of the vessel is defined.
  • a height difference is provided between the evaporator and the gas-liquid separator, and the evaporator is placed below the gas-liquid separator.
  • the flow rate of water circulated and supplied from the gas-liquid separator to the evaporator via the lower pipe can be changed only by changing the water level in the gas-liquid separator.
  • the load (heat exchange amount) in the evaporator changes, the heat exchange efficiency in the evaporator is optimally controlled to improve the steam generation efficiency and the amount of steam generated is also increased.
  • the evaporator can be miniaturized.
  • a water supply pipe for supplying water to the inside is connected to the lower pipe or the gas-liquid separator, and based on the amount of heat exchange between the water and the refrigerant in the evaporator, It is preferable to control the water level in the gas-liquid separator by changing the amount of water supplied from the water supply pipe.
  • the amount of heat input from the refrigerant to the evaporator may be used as the amount of heat exchange. Moreover, you may use the flow volume of the vapor
  • the flow rate of water circulated and supplied from the gas-liquid separator to the evaporator can be changed with a simple configuration. Therefore, even when the load on the evaporator changes, the heat exchange efficiency in the evaporator can be optimally controlled, and the steam generation efficiency can be improved.
  • FIG. 1 is an overall configuration diagram of a steam generation heat pump including a steam generation apparatus according to an embodiment of the present invention.
  • FIG. 2 is a configuration diagram of the steam generator shown in FIG.
  • FIG. 3 is a table showing an example of correlation data between the amount of heat input to the evaporator and the water level of the gas-liquid separator.
  • FIG. 1 is an overall configuration diagram of a steam generation heat pump 12 including a steam generation device 10 according to an embodiment of the present invention
  • FIG. 2 is a configuration diagram of the steam generation device 10 shown in FIG.
  • a steam generation heat pump 12 generates a steam by evaporating water and sends the steam to the outside, and a refrigerant cycle apparatus serving as a heat source for generating steam in the steam generation apparatus 10 14 and a controller 15 (see FIG. 2) for controlling the system.
  • the steam generator 10 includes a gas-liquid separator 16 that stores water inside the container, and an evaporator (steam generator) 20 through which a refrigerant circulating in the refrigerant cycle device 14 circulates. And the upper and lower portions of the evaporator 20 are communicated with each other by an upper pipe 22 and a lower pipe 24 to form a thermosiphon circuit.
  • the gas-liquid separator 16 is constituted by a cylindrical container along the vertical direction, and water is supplied from a water supply pipe 26 connected to a lower pipe 24 connected to a lower part of the gas-liquid separator 16.
  • the water supply pipe 26 is connected to a water pipe or a water tank (not shown), and a water pump 28 for pumping water into the gas-liquid separator 16 is provided in the middle.
  • the water pump 28 can change the water level W ⁇ b> 1 of the water stored in the gas-liquid separator 16 by changing the water supply flow rate into the gas-liquid separator 16 by controlling the rotation speed by the controller 15. .
  • the water supply pipe 26 can be connected to the gas-liquid separator 16 instead of the lower pipe 24, it is preferable to connect to the lower pipe 24 from the viewpoint of preventing cavitation in the suction pipe of the water pump 28.
  • the gas-liquid separator 16 has a lower pipe 24 connected to its lower end wall, an upper pipe 22 connected to the upper part of the side wall, and a steam delivery pipe 30 connected to its upper end wall.
  • the lower pipe 24 is a liquid pipe for supplying water stored in the gas-liquid separator 16 to the evaporator 20.
  • the upper pipe 22 is a steam pipe for supplying the steam generated in the evaporator 20 to the gas-liquid separator 16.
  • the steam delivery pipe 30 is used to send the steam generated by the evaporator 20 and supplied to the gas-liquid separator 16 via the upper pipe 22 and separated into gas and liquid to the external steam utilization device side. It is piping. That is, the connection port 16a of the lower pipe 24 becomes an outlet of water, the connection port 16b of the upper pipe 22 becomes an inlet of steam, and the connection port 16c of the steam delivery pipe 30 becomes an outlet of steam after gas-liquid separation.
  • the steam delivery pipe 30 is provided with a pressure control valve (not shown).
  • the controller 15 controls the opening of the pressure adjusting valve based on the vapor pressure in the gas-liquid separator 16 detected by a pressure sensor (not shown), thereby setting the vapor pressure sent from the vapor delivery pipe 30 to a predetermined value. Can be controlled.
  • a water level sensor 32 for measuring the water level W1 of the stored water is installed in the gas-liquid separator 16.
  • the detected value WL of the water level W1 detected by the water level sensor 32 is transmitted to the controller 15 and used for controlling the rotational speed of the water pump 28.
  • the evaporator 20 evaporates the water supplied from the lower pipe 24 and supplies it to the gas-liquid separator 16 from the upper pipe 22 as steam.
  • the evaporator 20 is, for example, a plate fin type heat exchanger, and a refrigerant passage 18a through which the refrigerant on the refrigerant cycle device 14 side circulates and a water passage 18b through which water (and steam) flows are alternately stacked. Yes.
  • the refrigerant passage 18a causes the refrigerant to flow from the upper side to the lower side in the vertical direction
  • the water passage 18b causes the water to flow from the lower side to the upper side in the vertical direction.
  • water supplied from the lower pipe 24 is water (liquid phase) below the water level W2 in the evaporator 20, and is in a state where water and steam are mixed above the water level W2 (mixed phase). Then, it becomes steam (gas phase).
  • the evaporator 20 has a lower pipe 24 connected to its lower end wall and an upper pipe 22 connected to its upper end wall. That is, the connection port 20a of the lower pipe 24 serves as an inlet for water, and the connection port 20b of the upper pipe 22 serves as an outlet for steam.
  • the evaporator 20 is installed at a lower position in the height direction than the gas-liquid separator 16.
  • the connection port 20 b that is the steam outlet in the evaporator 20 is positioned lower than the water level (water level W ⁇ b> 1) of water stored in the gas-liquid separator 16.
  • the positional relationship in the height direction between the evaporator 20 and the gas-liquid separator 16 is defined.
  • a water level difference (water surface head difference) W is formed between the water level W 1 of the gas-liquid separator 16 and the water level W 2 of the evaporator 20, and the water in the gas-liquid separator 16 Can be reliably circulated to the evaporator 20.
  • the controller 15 is a control device that performs overall control of the steam generation device 10 and the steam generation heat pump 12 including the same.
  • the controller 15 controls the rotational speed of the water pump 28 based on the detected value WL from the water level sensor 32 and the heat exchange amount (heat output) in the evaporator 20 described later, and the water level in the gas-liquid separator 16. W1 is controlled.
  • the controller 15 controls the water pump 28 so that the water level W1 corresponds to the fluctuation value when the heat exchange amount fluctuates while controlling the water level W1 to be constant.
  • the controller 15 is provided with a storage unit (not shown) that stores data (for example, see FIG. 3) that serves as a control parameter for the water level W1.
  • the water in the gas-liquid separator 16 is supplied to the evaporator 20 via the lower pipe 24 by the thermosiphon phenomenon.
  • the water supplied to the evaporator 20 is heated and evaporated by heat exchange with the refrigerant flowing through the refrigerant passage 18a, and becomes vapor.
  • the steam generated in the evaporator 20 is supplied to the gas-liquid separator 16 via the upper pipe 22, and then water contained in the steam is separated in the gas-liquid separator 16, and the steam delivery pipe 30. Sent to the outside. The water separated at this time is stored in the gas-liquid separator 16 and supplied again from the lower pipe 24 to the evaporator 20.
  • the refrigerant cycle device 14 includes a compressor 40, a refrigerant condenser 42 connected to the discharge side of the compressor 40, and an expansion valve connected to the outlet side of the refrigerant condenser 42. 44 and a refrigerant evaporator 46 connected to the outlet side of the expansion valve 44, and a refrigeration cycle (heat pump) that circulates refrigerant (refrigerant).
  • the refrigerant that has been sucked into the compressor 40 and has become high-temperature and high-pressure is radiated and condensed by the refrigerant condenser 42, is adiabatically expanded by the expansion valve 44, absorbs heat from the outside by the refrigerant evaporator 46, evaporates, and is compressed again. Return to machine 40.
  • a well-known refrigeration circuit can be used.
  • a refrigerant condenser 42 that condenses the high-temperature and high-pressure refrigerant discharged from the compressor 40 is used as the evaporator 20 of the vapor generation device 10. That is, the high-temperature and high-pressure refrigerant discharged from the compressor 40 circulates in the refrigerant condenser 42 (evaporator 20), where the water is heated by exchanging heat with the water circulating in the steam generation device 10, while The refrigerant itself is cooled and condensed, and sent to the expansion valve 44.
  • the heat generated in the refrigerant condenser 42 of the refrigerant cycle device 14 is used as a heat source for water evaporation in the steam generation device 10.
  • a heat source other than the refrigerant cycle device 14 may be used as a heat source for water evaporation in the steam generation device 10.
  • the state of water in the evaporator 20 depends on water (liquid phase), a state in which water and steam are mixed (mixed phase), and steam (gas phase) in order from the bottom to the top. It is in a three-layer state.
  • water has low heat transfer efficiency in the liquid phase state, so that the heat exchange efficiency is low, and in the mixed phase state, the heat transfer property is best and the heat exchange efficiency is high.
  • the amount of steam generated in the evaporator 20 and the evaporator are controlled by controlling the flow rate of water flowing into the evaporator 20 so as to optimize the ratio of the mixed phase in the evaporator 20.
  • the amount of water circulated to 20 is matched to maximize the efficiency of steam generation in the evaporator 20.
  • the flow rate of water supplied to the evaporator 20 is increased in a state where the heat exchange amount (load) between the refrigerant and water in the evaporator 20 is small, the proportion of water (liquid phase) in the evaporator 20 increases. As a result, the water level W2 rises, resulting in a decrease in the amount of steam generated.
  • the flow rate of water supplied to the evaporator 20 is small in a state where the amount of heat exchange between the refrigerant and water in the evaporator 20 is large, all the water is evaporated in the evaporator 20 and is generated as a result. The amount of steam is not sufficient.
  • the height position of the evaporator 20 is disposed below the gas-liquid separator 16 to form the water level difference W.
  • the rotation speed of the water pump 28 is appropriately controlled to change the amount of water supplied from the water supply pipe 26 to the gas-liquid separator 16 and change the water level W1 in the gas-liquid separator 16, the water level difference W Can be used to change and control the flow rate of the water circulated from the lower pipe 24 to the evaporator 20 to maximize the efficiency of steam generation in the evaporator 20.
  • the controller 15 includes a heat exchange amount between water and the refrigerant in the evaporator 20 and a water level W1 at which the steam generation efficiency is maximized at the heat exchange amount (that is, the evaporator 15).
  • Data of the correlation with the flow rate of water supplied to 20) is obtained through experiments or the like and stored in advance.
  • the data may be, for example, tabular data as shown in FIG.
  • the controller 15 calls the data of the water level W1 that maximizes the steam generation efficiency at the heat exchange amount based on the current heat exchange amount in the evaporator 20, and the water level is set so that the water level W1 is reached.
  • the rotational speed of the pump 28 is controlled to change the amount of water supplied to the gas-liquid separator 16.
  • the correlation data between the heat exchange amount and the water level W1 is obtained when the heat exchange amount increases, the water level W1 in the gas-liquid separator 16 increases, and the heat exchange amount decreases.
  • the content is that the water level W1 in the gas-liquid separator 16 is lowered.
  • the water level W1 in the gas-liquid separator 16 is set higher than the predetermined water level, and when the heat exchange amount decreases from the predetermined value, The content of making the water level W1 in the liquid separator 16 lower than a predetermined water level may be sufficient.
  • the water level W1 in the gas-liquid separator 16 is increased to increase the amount of water supplied to the evaporator 20 so that the mixed phase is properly adjusted in the evaporator 20. While maintaining the amount, the generation of steam is promoted to maximize the efficiency and amount of steam generation.
  • the water level W1 in the gas-liquid separator 16 is lowered to reduce the amount of water supplied to the evaporator 20 and excessively increase the evaporator 20. Water is prevented from being supplied, and steam generation is promoted while maintaining a proper amount of the mixed phase to maximize steam generation efficiency and generation amount.
  • an input heat quantity Q from the refrigerant to the evaporator 20 is used as a specific parameter of the amount of heat exchange between the water and the refrigerant in the evaporator 20 serving as an index for controlling the water level W1. If the input heat quantity Q from the refrigerant is obtained, the optimum water supply flow rate to the evaporator 20 at this input heat quantity Q is determined, so the water pump 28 is controlled so that the water level W1 at which this supply flow rate is obtained. become.
  • the input heat quantity Q is determined, for example, by measuring the suction pressure P, the suction temperature T, and the rotation speed rpm at the compressor 40 of the refrigerant cycle device 14 (see FIG. 1). Since it is known, the controller 15 can calculate the refrigerant circulation amount to the evaporator 20 and can estimate it from the refrigerant circulation amount.
  • the data of the correlation between the input heat quantity Q and the water level W1 stored in the controller 15 is, for example, as shown in FIG. 3, when the input heat quantity Q is 30 kW, the water level W1 is set to the highest level 3 in three stages, When the input heat quantity Q is 20 kW, the water level W1 is set to an intermediate level 2 in three stages, and when it is 15 kW, the water level W1 is set to the lowest level 1 in three stages. Levels 1 to 3 of the water level W1 are set to 37% for level 3, 24% for level 2, and 10% for level 1 when the height of the gas-liquid separator 16 is 100%, for example.
  • the controller 15 controls the rotational speed of the water pump 28 so that the water level W1 in the gas-liquid separator 16 becomes a desired level 1 to 3 according to the input heat quantity Q at that time. Will do.
  • the flow rate of the steam sent out from the steam delivery pipe 30 F may be used as a specific parameter of the heat exchange amount between the water and the refrigerant in the evaporator 20 serving as an index for controlling the water level W1
  • the flow rate F can be measured, for example, by installing a flow meter (FC) 34 in the steam delivery pipe 30 (see the flow meter 34 indicated by a two-dot chain line in FIG. 2).
  • the water level W1 in the gas-liquid separator 16 is controlled so that the flow rate F and the flow rate of the water circulated and supplied to the evaporator 20 are matched. That's fine.
  • the controller 15 performs control to increase the water level W1 to increase the amount of water that is circulated.
  • control is performed to lower the water level W1, to prevent excessive water from being supplied to the evaporator 20, and to maintain the mixed phase at an appropriate amount.
  • connection port 20b serving as the steam outlet in the evaporator 20 has the water surface stored in the gas-liquid separator 16 and the water surface.
  • the positional relationship in the height direction between the evaporator 20 and the gas-liquid separator 16 is defined so as to be lower than the water level W1.
  • the gas-liquid separator 16 can be changed to the evaporator 20 only by changing the water level W ⁇ b> 1 in the gas-liquid separator 16. And the flow rate of the water circulated through the lower pipe 24 can be changed.
  • the load (heat exchange amount) in the evaporator 20 changes, the heat exchange efficiency in the evaporator 20 is optimally controlled to improve the steam generation efficiency, and the amount of steam generated is also increased.
  • the evaporator 20 can be downsized.
  • the steam generation apparatus 10 does not require a circulation pump for changing the flow rate of water to the evaporator 20 as in the above-described prior art, the apparatus can be made small and simple, and the cost can be reduced. it can.

Landscapes

  • 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

La présente invention se rapporte à un dispositif de production de vapeur et à une pompe à chaleur de production de vapeur. Un dispositif de production de vapeur (10) est configuré de telle sorte que la partie supérieure d'un séparateur gaz-liquide (16) et la partie supérieure d'un évaporateur (20) soit raccordées par une tuyauterie supérieure (22) et que la partie inférieure du séparateur gaz-liquide (16) et la partie inférieure de l'évaporateur (20) soit raccordées par une tuyauterie inférieure (24), ce qui permet de former un circuit thermosiphon. Le circuit thermosiphon fournit de l'eau contenue dans le séparateur gaz-liquide (16) à l'évaporateur (20) au moyen de la tuyauterie inférieure (24), provoque l'évaporation de l'eau par l'échange de chaleur entre l'eau et un réfrigérant qui circule à travers l'évaporateur (20), fournit la vapeur produite par l'évaporateur (20) au séparateur gaz-liquide (16) au moyen de la tuyauterie supérieure (22) et transmet la vapeur à travers le séparateur gaz-liquide (16). La relation positionnelle entre l'évaporateur (20) et le séparateur gaz-liquide (16) est spécifiée de telle sorte que la position de l'orifice de sortie de vapeur de l'évaporateur (20) soit située en dessous de la surface de l'eau stockée dans le séparateur gaz-liquide (16).
PCT/JP2014/077218 2013-10-31 2014-10-10 Dispositif de production de vapeur et pompe à chaleur de production de vapeur WO2015064347A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2015544909A JP5967315B2 (ja) 2013-10-31 2014-10-10 蒸気生成装置及び蒸気生成ヒートポンプ

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013227043 2013-10-31
JP2013-227043 2013-10-31

Publications (1)

Publication Number Publication Date
WO2015064347A1 true WO2015064347A1 (fr) 2015-05-07

Family

ID=53003957

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2014/077218 WO2015064347A1 (fr) 2013-10-31 2014-10-10 Dispositif de production de vapeur et pompe à chaleur de production de vapeur

Country Status (2)

Country Link
JP (1) JP5967315B2 (fr)
WO (1) WO2015064347A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106287622A (zh) * 2016-08-21 2017-01-04 侴乔力 竖管升膜凝汽源热泵驱动蒸汽锅炉
JP2017020716A (ja) * 2015-07-10 2017-01-26 富士電機株式会社 ヒートポンプ式蒸気生成装置及び該ヒートポンプ式蒸気生成装置の運転方法
KR101878234B1 (ko) * 2016-12-05 2018-07-16 한국에너지기술연구원 고온증기 생산을 위한 증기 주입 히트펌프 시스템
JP2020098037A (ja) * 2018-12-17 2020-06-25 富士電機株式会社 蒸気生成装置
CN112729882A (zh) * 2020-11-24 2021-04-30 合肥通用机械研究院有限公司 一种高温热泵型蒸汽发生机组性能评价方法与测试装置

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7135618B2 (ja) * 2018-09-07 2022-09-13 富士電機株式会社 蒸気生成ヒートポンプ装置
CN112963816B (zh) * 2021-02-26 2023-01-06 楚天华通医药设备有限公司 纯蒸汽发生装置及其工作方法

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007232357A (ja) * 2006-02-01 2007-09-13 Kansai Electric Power Co Inc:The ヒートポンプ式蒸気・温水発生装置
JP2008064422A (ja) * 2006-09-11 2008-03-21 Ebara Refrigeration Equipment & Systems Co Ltd 高温再生器及び吸収冷凍機
JP2011242018A (ja) * 2010-05-14 2011-12-01 Fuji Electric Co Ltd ヒートポンプ式蒸気生成装置
JP2012021717A (ja) * 2010-07-15 2012-02-02 Fuji Electric Co Ltd ヒートポンプ式蒸気生成装置
JP2012047439A (ja) * 2010-07-27 2012-03-08 Fuji Electric Co Ltd ヒートポンプ式蒸気生成装置
JP2012167852A (ja) * 2011-02-14 2012-09-06 Fuji Electric Co Ltd ヒートポンプ式蒸気生成装置
JP2012247156A (ja) * 2011-05-30 2012-12-13 Toyo Eng Works Ltd ヒートポンプ式蒸気発生方法

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007232357A (ja) * 2006-02-01 2007-09-13 Kansai Electric Power Co Inc:The ヒートポンプ式蒸気・温水発生装置
JP2008064422A (ja) * 2006-09-11 2008-03-21 Ebara Refrigeration Equipment & Systems Co Ltd 高温再生器及び吸収冷凍機
JP2011242018A (ja) * 2010-05-14 2011-12-01 Fuji Electric Co Ltd ヒートポンプ式蒸気生成装置
JP2012021717A (ja) * 2010-07-15 2012-02-02 Fuji Electric Co Ltd ヒートポンプ式蒸気生成装置
JP2012047439A (ja) * 2010-07-27 2012-03-08 Fuji Electric Co Ltd ヒートポンプ式蒸気生成装置
JP2012167852A (ja) * 2011-02-14 2012-09-06 Fuji Electric Co Ltd ヒートポンプ式蒸気生成装置
JP2012247156A (ja) * 2011-05-30 2012-12-13 Toyo Eng Works Ltd ヒートポンプ式蒸気発生方法

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017020716A (ja) * 2015-07-10 2017-01-26 富士電機株式会社 ヒートポンプ式蒸気生成装置及び該ヒートポンプ式蒸気生成装置の運転方法
CN106287622A (zh) * 2016-08-21 2017-01-04 侴乔力 竖管升膜凝汽源热泵驱动蒸汽锅炉
CN106287622B (zh) * 2016-08-21 2023-05-19 侴乔力 竖管升膜凝汽源热泵驱动蒸汽锅炉
KR101878234B1 (ko) * 2016-12-05 2018-07-16 한국에너지기술연구원 고온증기 생산을 위한 증기 주입 히트펌프 시스템
JP2020098037A (ja) * 2018-12-17 2020-06-25 富士電機株式会社 蒸気生成装置
JP7192471B2 (ja) 2018-12-17 2022-12-20 富士電機株式会社 蒸気生成装置
CN112729882A (zh) * 2020-11-24 2021-04-30 合肥通用机械研究院有限公司 一种高温热泵型蒸汽发生机组性能评价方法与测试装置
CN112729882B (zh) * 2020-11-24 2022-11-29 合肥通用机械研究院有限公司 一种高温热泵型蒸汽发生机组性能评价方法与测试装置

Also Published As

Publication number Publication date
JPWO2015064347A1 (ja) 2017-03-09
JP5967315B2 (ja) 2016-08-10

Similar Documents

Publication Publication Date Title
JP5967315B2 (ja) 蒸気生成装置及び蒸気生成ヒートポンプ
CA2863530C (fr) Procede et appareil destines a produire et a utiliser une energie thermique dans un appareil thermique et electrique combine
KR101222331B1 (ko) 히트 펌프식 급탕기
JP5605991B2 (ja) 蒸気発生装置
JP3915770B2 (ja) ヒートポンプ給湯機
JP5788235B2 (ja) 蒸気発生装置
CN102713459A (zh) 热泵系统
JP2002106959A (ja) ヒートポンプ給湯機
JP2009092258A (ja) 冷凍サイクル装置
JP5605557B2 (ja) ヒートポンプ式蒸気発生装置
JP2013079739A (ja) 加熱器利用装置
JP2011075257A (ja) ヒートポンプ式給湯機
JP5802514B2 (ja) ヒートポンプ式給湯機
JP5560515B2 (ja) 蒸気製造システム、および蒸気製造システムの立ち上げ制御方法
JP2010169364A (ja) サーモサイフォン式蒸気発生装置
JP4950004B2 (ja) ヒートポンプ式給湯装置
JP5929464B2 (ja) ヒートポンプ及びヒートポンプの起動方法
JP5721408B2 (ja) 温泉水供給システムおよび温泉水供給方法
US20200292221A1 (en) Phase-change cooling system and method for controlling the same
JP5092677B2 (ja) 吸収式冷凍装置
JP2005164161A (ja) 吸収式冷凍機及び吸収冷凍機の再生器内の溶液レベル制御方法
JP2008281256A (ja) 給湯機
JP2017138067A (ja) 冷凍サイクル装置
JP5950064B1 (ja) ヒートポンプ式蒸気生成装置
JP2013040725A (ja) 加熱器利用装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14858319

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2015544909

Country of ref document: JP

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: IDP00201601429

Country of ref document: ID

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 14858319

Country of ref document: EP

Kind code of ref document: A1