WO2020029516A1 - 一种薄壳式换热器、地铁废热源热泵系统及方法 - Google Patents

一种薄壳式换热器、地铁废热源热泵系统及方法 Download PDF

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Publication number
WO2020029516A1
WO2020029516A1 PCT/CN2018/122944 CN2018122944W WO2020029516A1 WO 2020029516 A1 WO2020029516 A1 WO 2020029516A1 CN 2018122944 W CN2018122944 W CN 2018122944W WO 2020029516 A1 WO2020029516 A1 WO 2020029516A1
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Prior art keywords
valve
heat
condenser
heat exchanger
temperature
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PCT/CN2018/122944
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English (en)
French (fr)
Inventor
胡松涛
季永明
刘国丹
佟振
童力
Original Assignee
青岛理工大学
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Publication date
Priority claimed from CN201810902021.0A external-priority patent/CN108981229A/zh
Priority claimed from CN201810941225.5A external-priority patent/CN109099738A/zh
Application filed by 青岛理工大学 filed Critical 青岛理工大学
Priority to EP18908282.9A priority Critical patent/EP3819561A4/en
Priority to AU2018408667A priority patent/AU2018408667B2/en
Priority to JP2019558776A priority patent/JP7026369B2/ja
Publication of WO2020029516A1 publication Critical patent/WO2020029516A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
    • F28F21/062—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material the heat-exchange apparatus employing tubular conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/18—Hot-water central heating systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24T—GEOTHERMAL COLLECTORS; GEOTHERMAL SYSTEMS
    • F24T10/00—Geothermal collectors
    • F24T10/10—Geothermal collectors with circulation of working fluids through underground channels, the working fluids not coming into direct contact with the ground
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24T—GEOTHERMAL COLLECTORS; GEOTHERMAL SYSTEMS
    • F24T50/00—Geothermal systems 
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B30/06—Heat pumps characterised by the source of low potential heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/003—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by using permeable mass, perforated or porous materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/11—Geothermal energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24T—GEOTHERMAL COLLECTORS; GEOTHERMAL SYSTEMS
    • F24T10/00—Geothermal collectors
    • F24T2010/50—Component parts, details or accessories
    • F24T2010/53—Methods for installation
    • 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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/02—Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels
    • 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
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
    • 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
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/40—Geothermal heat-pumps
    • 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]
    • Y02B30/12—Hot water central heating systems using heat pumps
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/10—Geothermal energy

Definitions

  • the invention relates to a composite heat pump system, in particular to a thin shell heat exchanger for a subway tunnel, a subway waste heat source heat pump system with the thin shell heat exchanger as the front end, and a method for installing the thin shell heat exchanger. And the working method of the subway waste heat source heat pump system.
  • the heat pump technology can be used to extract and release heat from the surrounding rock of the tunnel through a reasonable front-end heat exchanger, coupled with auxiliary cooling equipment, to achieve seasonal cooling for the air-conditioning on the ground and heating during the heating season.
  • auxiliary cooling equipment coupled with auxiliary cooling equipment
  • Underground tunnels and subway stations are basically below the underground thermostatic layer, and the underground rock and soil temperature is stable all year round, which is very suitable as a cold and heat source for heat pump systems.
  • the buried tube heat exchanger in the traditional ground source heat pump system has a large footprint, and because the soil thermal conductivity is small, the heat transfer capacity of a single buried tube is limited. Therefore, when the heat supply is large, the length of the buried tube is faced. It is too long, the cost of drilling is high, the construction is difficult, and the troubles of buried pipes are difficult to repair.
  • the present invention provides a thin shell heat exchanger for a subway tunnel, a subway waste heat source heat pump system with the thin shell heat exchanger as the front end, and the installation of the thin shell heat exchanger.
  • the construction method and the working method of the subway waste heat source heat pump system can effectively improve the quality of the subway environment and reduce the waste heat emission of the subway to the environment. It has the advantages of high heat exchange efficiency, environmental protection, economical and practicality, and long service life. It can also make full use of subway operations.
  • the waste heat generated is used to heat the ground building during the heating season and air-conditioning season. Freely choose the subway tunnel and its surrounding rock and soil as a cold source or use auxiliary cooling equipment to cool the ground building air-conditioning season. Give full play to the advantages of the subway waste heat source heat pump system .
  • a first object of the present invention is to provide a thin-shell heat exchanger, which includes a tunnel-lining, a thin-shell heat-exchanger body, and a tunnel-two in a tunnel surrounding rock which are sequentially arranged from the inside to the outside.
  • Lining a protective layer composed of mortar, geotextile, and waterproof board is sandwiched between the thin shell heat exchanger body and the tunnel second lining, and heat is exchanged with the surrounding tunnel rock of the subway through the thin shell heat exchanger body.
  • the thin shell heat exchanger body includes a water inlet main pipe, a return water main pipe, and a capillary grid connected between the water inlet main pipe and the return water main pipe, and the capillary grid is along the circumferential direction of the arc-shaped wall surface of the tunnel.
  • the capillary grid includes a plurality of capillary heat-conducting water pipes evenly distributed between the water inlet main and the water return main and passing through the water inlet main and the water return main.
  • the water inlet main and the water return main are arranged in a tunnel. On the same side is reserved in the main pipe trench.
  • a second object of the present invention is to provide a method for installing and constructing the thin-shell heat exchanger as described above, which includes the following steps:
  • the structure construction method of the tunnel lining, the thin shell heat exchanger and the tunnel lining is as follows:
  • a mortar layer, a geotextile, and a waterproof board are sequentially arranged on the outside of the thin shell heat exchanger;
  • the method for laying and installing the thin shell heat exchanger is:
  • a third object of the present invention is to provide a subway waste heat source heat pump system, which includes the thin-shell heat exchanger, a waste heat source heat pump system, a radiation end, and an auxiliary cold source as described above.
  • the waste heat source heat pump system includes a series connection. Compressor, condenser, throttle valve and evaporator, the thin-shell heat exchanger transports high-temperature liquid to the evaporator through a circulation loop between the winter subway waste heat source side heat exchanger and the heat pump unit, and the evaporator passes compression The machine sends high-temperature liquid to the condenser, and the low-temperature return water at the radiating end is sent to the condenser through the circulation loop between the radiating end of the load side and the heat pump unit in winter.
  • the temperature rises to high-temperature water.
  • the cooling water in the condenser is sent to the evaporator through the throttle valve, and the refrigerant is low temperature and low pressure in the evaporator.
  • the liquid exchanges heat with chilled water. After the chilled water is cooled, it is transported to the radiating end through a circulation loop between the radiating end of the load side in summer and the heat pump unit, and cooling the ground building.
  • the outlet of the compressor is connected to the first port of the condenser, the third port of the condenser is connected to the throttle valve, the other end of the throttle valve is connected to the fourth port of the evaporator, and the second port of the evaporator is connected
  • the interface is connected to the inlet of the compressor and forms the circulation loop of the waste heat source heat pump unit.
  • the circulation circuit between the winter subway waste heat source side heat exchanger and the heat pump unit includes valve five, first three-way, second three-way, first circulating water pump, valve eight, third three-way, and fourth three
  • the first port of the evaporator is connected to the nozzle of the thin shell heat exchanger through a valve five, a first three-way, a second three-way, and a first circulating water pump.
  • the third port of the evaporator is connected through The valve eight, the third tee and the fourth tee are connected to the second port of the thin shell heat exchanger.
  • the circulation loop between the winter load-side radiation end and the heat pump unit includes a sixth three-way, a ninth three-way, a valve four, a seventh three-way, an eighth three-way and a thirteenth valve, and a valve seven and a third.
  • a second circulating water pump, the second interface of the condenser is connected to the water inlet end of the radiation end through the sixth tee, the ninth tee, and the valve four, and the fourth interface of the condenser is through the seventh tee and the eighth tee Connected to the thirteenth pass, valve seven and the second circulating water pump are connected to the return end of the radiation end.
  • the circulation circuit between the summer auxiliary cold source side and the heat pump unit includes a sixth three-way, a fifth three-way, a valve two, a fourth circulating water pump, a seventh three-way, an eighth three-way, and a valve six.
  • the second interface of the condenser is connected to the water inlet of the auxiliary cold source through the sixth tee, the fifth tee, the valve two and the fourth circulating water pump, and the fourth interface of the condenser is connected through the seventh tee, the first Eight tees and valve six are connected to the return side of the auxiliary cold source.
  • the circulation loop between the summer load-side radiation end and the heat pump unit includes valve three, second three, ninth three, valve nine, fourth three, thirteen and third circulating water pump.
  • the first port of the evaporator is connected to the return end of the radiation end through valves three, second three and ninth, and the third port of the evaporator is connected through valves nine, fourth three, thirteen and th
  • the three-cycle water pump is connected to the water inlet end of the radiation end.
  • the circulation loop between the summer subway tunnel and its rock and soil cold source side and the heat pump unit, and the circulating liquid in the thin shell heat exchanger passes between the summer subway tunnel and its rock and soil cold source side and the heat pump unit.
  • the circulation loop is transported to the condenser, where heat is exchanged with the high-temperature and high-pressure refrigerant gas. After the temperature of the circulating liquid rises, it flows out of the condenser and is sent back to the thin-shell heat exchanger, which radiates heat to The rock or soil around the subway tunnel is stored or directly radiated into the tunnel and taken away by the piston wind.
  • the circulation loop between the summer subway tunnel and its geotechnical cold source side and the heat pump unit includes a sixth tee, a fifth tee, a third tee, a valve one, a seventh tee, and a first tee.
  • Valve ten and the first circulating water pump the second interface of the condenser is connected to the second port of the thin-shell heat exchanger through the sixth tee, the fifth tee, the third tee and the valve 1
  • the fourth port of the condenser is connected to the nozzle of the thin shell heat exchanger through a seventh tee, a first tee, a valve ten, and a first circulating water pump.
  • a fourth object of the present invention is to provide a working method of using a subway waste heat source heat pump system with an auxiliary cold source as described above.
  • the method includes the following steps:
  • the high-temperature and high-pressure refrigerant gas discharged from the compressor enters the condenser and condenses into a low-temperature and high-pressure liquid.
  • the low-temperature and high-pressure refrigerant liquid passes through the throttle valve to become a low-temperature and low-pressure refrigerant liquid and then flows into the evaporator.
  • the heat absorbed in the evaporator becomes low-temperature and low-pressure.
  • the low-temperature liquid at the radiation end is pumped into the condenser through the second circulating water pump, and after the heat exchange with the high-temperature and high-pressure refrigerant gas in the condenser The temperature rises into high-temperature water.
  • the high-temperature water flows out from the second interface of the condenser and enters the radiation end to heat the buildings on the ground.
  • the low-temperature water is pumped into the condenser through the second circulating water pump and sequentially circulates the heat;
  • the low-temperature and low-pressure refrigerant liquid and the chilled water return water are used for heating.
  • the chilled water is cooled from the third interface of the evaporator to the radiating end by the third circulating water pump. After cooling the ground to the user in the building, the temperature of the chilled water rises, flows back to the evaporator, and circulates the cooling in turn.
  • the thin-shell heat exchanger is arranged between the first lining of the tunnel and the second lining of the tunnel, and the thin-shell type heat exchanger and the second lining of the tunnel are protected by mortar, geotextile, and waterproof board.
  • Directly exchange heat with the surrounding rock of the subway tunnel radiate heat to the surrounding rock of the tunnel in summer, and take heat from the surrounding rock of the tunnel in winter to ensure the thermal balance of the surrounding rock of the subway tunnel, which can effectively improve the quality of the subway environment and reduce the waste heat emission of the subway to the environment.
  • the present invention makes full use of the waste heat generated from the operation of the subway, combines the subway waste heat source heat pump system with the auxiliary cold source to realize the simultaneous cooling and heating of the ground construction users, and also balances the subway tunnel and the surrounding rock and soil. Absorbs and releases heat, and can realize the free choice of summer cold source solution through the conversion of the valve, so that the subway waste heat source heat pump system inherits the advantages of the ground source heat pump system, and solves the problem of ground cooling for summer users. Devices are more energy efficient and environmentally friendly;
  • the present invention can make full use of the waste heat generated from the operation of the subway to heat the buildings above the ground, and can freely choose the subway tunnel and its surrounding rock and soil as the cold source or use the auxiliary cold source to cool the buildings in the summer to fully utilize the waste heat of the subway. Advantages of source heat pump systems.
  • FIG. 1 is a schematic structural diagram of a subway waste heat source heat pump system including a thin shell heat exchanger
  • Figure 2 is a structural diagram of a capillary grid
  • the required space is large; because the soil thermal conductivity is small, the heat transfer capacity of a single ground pipe is limited, so when the heat supply is constant, the required ground
  • the length of the buried pipe is longer, which results in more boreholes in the ground pipe and the larger heat exchange area required.
  • the installation of the buried pipe involves underground drilling, which is difficult to construct and has a high drilling cost. It is also difficult to repair and replace the local buried pipe when it fails.
  • This embodiment provides a thin shell heat exchanger.
  • the thin shell heat exchanger includes a tunnel lining 11, a thin shell heat exchanger body 12, and a tunnel second lining 16 arranged in order from the inside to the outside of the tunnel surrounding rock.
  • the thin-shell heat exchanger body 2 is used as a front-end heat exchange device of the subway waste heat source heat pump, and is arranged between the tunnel first lining 11 and the tunnel second lining 16 of the surrounding rock of the subway tunnel. 12 Exchange heat with the surrounding rock of the subway tunnel, radiate heat to the surrounding rock in the summer, and take heat from the surrounding rock in the winter to ensure the thermal balance of the surrounding rock of the subway tunnel.
  • a protective layer composed of mortar 13, geotextile 14 and waterproof plate 15 is sandwiched between the thin shell heat exchanger body 12 and the tunnel second lining 16 to thermally protect the thin shell heat exchanger body.
  • the above thin shell heat exchanger body is laid along the circumferential direction of the arc wall of the tunnel.
  • the thin shell heat exchanger body 2 includes a water inlet main pipe 9, a return water main pipe 10, connected to the water inlet main pipe 9 and the return water main pipe 10. Capillary grids and their connections, system pipes and fittings, etc.
  • water inlet main pipe 9 and the return water main pipe 10 and their connecting parts, system pipes and pipe fittings are made of plastic, stainless steel or copper. It should be determined after comprehensive comparison according to the working temperature, working pressure, design life, site waterproofing, water quality requirements, and construction requirements.
  • the color of the capillary grid should be uniform, and the inner and outer surfaces of the pipes and fittings should be smooth, flat, and clean, free of dents, bubbles, obvious scratches, and other surface defects that affect performance.
  • the capillary grid includes a plurality of capillary heat conducting water pipes 8 evenly distributed between the water inlet main pipe 10 and the water return main pipe 11 and penetrating through the water inlet main pipe and the water return main pipe, as shown in FIG. 2.
  • the inlet main pipe 10 and the return main pipe 11 are arranged in a reserved main pipe trench 7 on the same side of the tunnel.
  • the capillary heat-conducting water pipe 8 is a PPR pipe with a diameter of 4.3 mm and a wall thickness of 0.85 mm.
  • the distance between adjacent capillary heat-conducting water pipes is 10 mm and the width of each capillary network is 1 m.
  • the length of the capillary heat-conducting water pipe in the capillary grid can be determined according to Actually need to customize.
  • the PPR pipe should be formed at one time. Welding is not allowed in the middle. The end face of the pipe should be cut flat and perpendicular to the axis.
  • the PPR pipe grid requires factory water pressure test, and the end requires seamless seal and pressure. The factory test pressure Keep it at not lower than 0.3Mpa for 5-10 minutes.
  • a reserved main pipe trench 17 and a thin shell heat exchanger main pipe are provided on the side of the tunnel.
  • the role of the reserved main pipe trench 7 is to place a water inlet main pipe and a return water main pipe;
  • the thin shell heat exchanger main pipe is The collective name of the water inlet supervisor and the water return supervisor is to supply water and return water to the capillary heat-conducting water pipe, which is equivalent to the main pipe, and the capillary heat-conducting water pipe is a branch pipe.
  • the thin-shell heat exchanger for a subway tunnel is to arrange the thin-shell heat exchanger between the first lining of the tunnel and the second lining of the tunnel. It is protected by mortar, geotextile, and waterproof board. It can directly exchange heat with the surrounding rock of the subway tunnel. It releases heat to the surrounding rock of the tunnel in summer and draws heat from the surrounding rock of the tunnel in winter to ensure the thermal balance of the surrounding rock of the subway tunnel. Improving the quality of the subway environment and reducing the waste heat emissions of the subway to the environment have the advantages of high heat exchange efficiency, environmental protection, economical applicability, and long service life.
  • This embodiment also provides a method for installing and constructing a thin shell heat exchanger.
  • the method includes the following steps:
  • the base surface is leveled with cement mortar, where the ratio of sand: cement is 1: 3.
  • a leak test is performed on the capillary grid using a hydraulic pressure test method in the form of random inspection to eliminate the capillary grid with holes.
  • tunnel primary lining The construction methods of the tunnel primary lining, thin shell heat exchanger and tunnel secondary lining are:
  • the thin shell heat exchanger 12 is laid and installed.
  • the method for laying and installing the thin shell heat exchanger is:
  • a mortar protective layer After laying the thin shell heat exchanger, a mortar protective layer, a geotextile, and a waterproof plate protective layer are added to the outside of the shell heat exchanger.
  • a reserved main pipe trench and a thin shell heat exchanger main pipe are arranged on one side of the tunnel.
  • the installation and construction method of the thin-shell heat exchanger proposed in this embodiment is to arrange the thin-shell heat exchanger between the first lining of the tunnel and the second lining of the tunnel.
  • Mortar, geotextile, and waterproof board are used for protection, which can directly exchange heat with the surrounding rock of the subway tunnel, and radiate heat to the surrounding rock in the summer, and take heat from the surrounding rock in the winter to ensure the thermal balance of the surrounding rock of the subway, which can effectively improve the subway environment.
  • Quality, reducing the waste heat emission of the subway to the environment has the advantages of high heat exchange efficiency, environmental protection, economical and applicable, and long service life.
  • this embodiment also provides a subway waste heat source heat pump system including the thin-shell heat exchanger as described above and a working method thereof.
  • the auxiliary cooling source is provided to reach the ground. Construction users provide heating in winter and cooling in summer, making full use of the waste heat generated by subway operation.
  • the subway waste heat source heat pump system includes a capillary network front-end heat exchange system, a waste heat source heat pump system, a radiation end 6, and an auxiliary cold source 7.
  • the capillary network front-end heat exchange system includes the thin-shell type as described above.
  • the waste heat source heat pump system includes a compressor 2, a condenser 3 with a first interface a, a second interface b, a third interface c, and a fourth interface d, which throttles
  • the valve 4 and the evaporator 5 with a first interface e, a second interface f, a third interface g, and a fourth interface h; the entire system is connected to the valve by a pipeline, and the radiation end 6 is in a building on the ground.
  • the specific connection of the system is: the outlet of the compressor 2 is connected to the first interface a of the condenser 3, the third interface c of the condenser 3 is connected to the throttle valve 4, and the other end of the throttle valve 4 is connected to the evaporator 5
  • the fourth interface h is connected, and the second interface of the evaporator 5 is connected to the inlet of the f compressor 2 to form a circulation loop of the waste heat source heat pump unit.
  • the first interface e of the evaporator 5 is connected to the valve 5 through the first three-way k and the first
  • the two three links l and the first circulating water pump A are connected to the nozzle i of the thin shell heat exchanger 1.
  • the third interface g of the evaporator 5 is connected through the valve eight L, the third three link m and the fourth three link n.
  • the two shells j of the thin shell heat exchanger 1 are connected to form a circulation loop between the waste heat source side heat exchanger and the heat pump unit in winter; the first interface e of the evaporator 5 passes through the valve three G and the second three way l and The ninth tee s is connected to the return end of the radiation end 6.
  • the third interface g of the evaporator 5 is connected to the radiation end 6 through the valve IXM, the fourth tee n and the thirteenth tee, and the third circulating water pump C.
  • the water inlet end is connected to form a circulation loop between the radiation end of the load side in summer and the heat pump unit; the second interface b of the condenser 3 passes the sixth three-way p and the ninth
  • the valve s and valve H are connected to the water inlet of the radiation end 6.
  • the fourth interface d of the condenser 3 passes the seventh three way q, the eighth three way r and the thirteenth way t, the valve seven K, and the second cycle.
  • the water pump B is connected to the return end of the radiation end 6 and forms a circulation loop between the radiation end of the load side in winter and the heat pump unit; the second interface b of the condenser 3 passes the sixth three-way p, the fifth three-way o, and the third three
  • the valve m and the valve one E are connected to the nozzle two j of the thin-shell heat exchanger 1.
  • the fourth interface d of the condenser 3 is connected to the first three-way k through the seventh three-way q, the valve ten N, and the first circulating water pump.
  • A is connected to the pipe opening i of the thin-shell heat exchanger 1 to form a circulation loop between the summer subway tunnel and its geotechnical cold source side and the heat pump unit;
  • the second interface b of the condenser 3 is connected through the sixth tee p and
  • the fifth three-way o, the valve two F, and the fourth circulating water pump D are connected to the water inlet end of the auxiliary cold source 7, and the fourth interface d of the condenser 3 passes the seventh three-way q and the eighth three-way r, and the valve six J It is connected to the return water end of the auxiliary cold source 7 and forms a circulation loop between the auxiliary cold source side and the heat pump unit in summer.
  • the subway waste heat source heat pump system disclosed in the embodiment of the present invention provides heating and cooling for users in the above-ground building in winter and summer.
  • the waste heat generated in the subway tunnel is used as a heat source to supply users in the above-ground buildings.
  • soil is used as a cold source or a single auxiliary cold source is used to provide cooling for users in the above-ground buildings.
  • Two types of cold sources can also be used at the same time. Due to the subway operation, the heat accumulation of the subway tunnel and its surrounding rock and soil is inevitable. In order to maintain heat balance, it is preferred.
  • auxiliary cold sources are used for cooling.
  • the radiation end 6 can be a capillary network radiation system, but it is not limited to this form, and it can also be other radiation end forms;
  • the auxiliary cold source 7 can be a cooling tower, and the cooling tower should be located on the downwind side away from the crowd to reduce infection Legionella opportunities, but the auxiliary cold source 7 is not limited to cooling towers, but can also be other forms of auxiliary cold sources.
  • the disclosed waste heat source heat pump system for the subway makes full use of waste heat generated from the operation of the subway.
  • the combination of the waste heat source heat pump system for the subway and the auxiliary cold source achieves the simultaneous cooling and heating of building users on the ground, and also balances the subway tunnel and The heat absorption and release of the surrounding rock and soil can realize the free choice of summer cold source solutions through the conversion of the valve.
  • the use of radiant end heat exchangers is more energy-saving and environmentally friendly.
  • the subway waste heat source heat pump system inherits the advantages of the ground source heat pump system and avoids it. Its disadvantages.
  • the refrigerant cycle of the waste heat source heat pump is indispensable regardless of heating and cooling, and the principle is the same: the high temperature and high pressure refrigeration discharged from the compressor 2
  • the refrigerant gas enters the first interface a of the condenser 3 and condenses into a low-temperature and high-pressure liquid and flows out from the third interface c.
  • the low-temperature and high-pressure refrigerant liquid flows into the throttle valve 4 and becomes a low-temperature and low-pressure refrigerant liquid.
  • the fourth interface h flows into the evaporator 5 and absorbs heat in the evaporator 5 to become a low-temperature and low-pressure refrigerant gas.
  • the refrigerant gas flows out from the second interface f of the evaporator 5 and flows back to the compressor 2 to complete the cycle.
  • the working process of a subway waste heat source heat pump system with an auxiliary cold source is:
  • valves H, I, K, L need to be closed first, the valves G, M are opened, the circulating water pump B is closed, and the circulating water pump C is turned on. Then determine the choice of cold source. If the plan is to use the cooling tower 7 as the single source, the valves F, J and the circulating water pump D need to be opened, and the valves E, N and the circulating water pump A are closed. If the plan is to use the subway tunnel and its surroundings alone As a cold source, you need to open valves E, N and circulating water pump A, close valves F, J, and circulating water pump D. In this embodiment, if you choose to use the two types of cold sources at the same time, you need to open valves F, J , E, N and circulating water pumps A, D.
  • the circulation between the auxiliary cold source side and the heat pump unit is a cooling water cycle.
  • the cooling water in the condenser 3 exchanges heat with high-temperature and high-pressure refrigerant gas. After the temperature of the cooling water increases, it passes through the condenser 3.
  • the b interface is pressed by the circulating water pump D into the cooling tower 7 for cooling, and then returned to the condenser 3 to complete the cycle.
  • the shell heat exchange The liquid in the condenser 1 is pumped into the condenser 3 by the circulating water pump A through the d interface and exchanges heat with high-temperature and high-pressure refrigerant gas.
  • the heat exchanger 1 After the temperature of the circulating liquid rises, it flows out from the b interface of the condenser 3 and is returned to the thin shell.
  • the heat is dissipated to the rock and soil around the subway tunnel for storage or directly to the tunnel and taken away by the piston wind to complete the cycle; at the same time, the cycle between the load-side radiation end and the heat pump unit in summer
  • it is a chilled water cycle.
  • the low-temperature and low-pressure refrigerant liquid in the evaporator 5 exchanges heat with the chilled water. After the chilled water is cooled, it is pressed into the capillary network from the g interface of the evaporator 5 by a third circulating water pump.
  • Radiation system 6 after the user is cooled in the above-ground building, the temperature of the frozen water rises and flows back to the evaporator 5 through the e interface to complete the cycle.

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Abstract

一种薄壳式换热器（1）、地铁废热源热泵系统及方法，该系统包括薄壳式换热器（1）、压缩机（2）、冷凝器（3）、蒸发器（5）、辐射末端（6）和辅助冷源（7），冬季薄壳式换热器（1）通过循环回路将高温液体送至蒸发器（5），高温水从冷凝器（3）流入辐射末端（6）对地上建筑供热后返回冷凝器（3）；夏季冷凝器（3）中冷却水冷却制冷剂后通过循环回路送至辅助冷源（7）中冷却，蒸发器（5）中冷冻水降温后通过循环回路送至辐射末端（6）对地上建筑供冷。

Description

一种薄壳式换热器、地铁废热源热泵系统及方法 技术领域
本发明涉及一种复合热泵系统，特别涉及一种地铁隧道用的薄壳式换热器、以薄壳式换热器为前端的地铁废热源热泵系统及薄壳式换热器的安装施工方法和地铁废热源热泵系统的工作方法。
背景技术
目前，地铁已经成为越来越多大城市缓解交通压力的选择，地铁运行后，地铁隧道传热是一个长期缓慢的非稳态过程，隧道内的热堆积不可避免，这种热量随着地铁运行时间越久堆积越多，造成隧道内空气和围岩温度升高。针对这一问题，在地铁建设较早的广州、上海等地，大多采用地上设置冷却塔的方式直接为地铁隧道降温，但地铁经过的地段大多处于市中心繁华地带，这些地方既没有太多空间设置冷却塔，也容易因人员密集、颗粒物多而发生地铁空调冷却塔被军团菌污染并传播给附近人员的情况。
随着地铁不间断运行，大量废热源源不断地被存储于隧道周围岩土中。相对于地上建筑冷热负荷，地铁站内冷热负荷较小。因此，可利用热泵技术，通过合理的前端换热器对隧道围岩进行取放热，并配以辅助冷却设备，实现对地上建筑空调季供冷，采暖季供热，在解决地铁所在地下空间热污染的同时，为地上建筑进行能源供应的。该技术在实现地铁沿线区域能源周期内热平衡的同时，大大提高了能源利用率，真正意义上实现地铁的可持续运营。
地下隧道和地铁车站基本都处于地下恒温层以下，地下岩土温度常年稳定，非常适合作为热泵系统的冷热源。传统土壤源热泵系统中的地埋管换热器占地 面积大，且由于土壤导热系数较小，单根地埋管换热量有限，所以，当供热量较大时，面临埋管长度过长，钻孔成本高，施工难度大等问题，而且地埋管故障检修也困难。
目前，对于地埋管换热器土壤源热泵系统存在的诸多问题，例如占地面积大、钻孔多，施工难度大、成本高等问题，尚缺乏有效的解决方案。
发明内容
为了克服上述现有技术的不足，本发明提供了一种地铁隧道用的薄壳式换热器、以薄壳式换热器为前端的地铁废热源热泵系统及薄壳式换热器的安装施工方法和地铁废热源热泵系统的工作方法，可以有效改善地铁环境质量，减轻地铁对环境的废热排放，具有换热效率高，环保、经济实用，使用寿命长等优点，而且可以充分利用地铁运营产生的废热为地上建筑采暖季供热和空调季供冷，自由选择地铁隧道及其周围岩土作为冷源或采用辅助冷却设备为地上建筑空调季供冷，充分发挥地铁废热源热泵系统的优势。
本发明所采用的技术方案是：
本发明的第一目的是提供一种薄壳式换热器，该薄壳式换热器包括隧道围岩中由内到外依次布置的隧道一衬、薄壳式换热器本体和隧道二衬，在薄壳式换热器本体和隧道二衬之间夹设有由砂浆、土工布和防水板组成的保护层，通过薄壳式换热器本体与地铁隧道围岩交换热量。
进一步的，所述薄壳式换热器本体包括进水主管、回水主管以及连接于进水主管和回水主管之间的毛细管网栅，所述毛细管网栅沿隧道弧形壁面的圆周方向敷设；所述毛细管网栅包括均布于进水主管和回水主管之间均布且贯通进水主管和回水主管的若干根毛细导热水管，所述进水主管和回水主管布置在隧 道同一侧的预留主管管沟内。
本发明的第二目的是提供一种如上所述的薄壳式换热器的安装施工方法，该方法包括以下步骤：
(1)确定毛细管网栅的敷设位置，检查隧道壁面是否平整，并在相应位置开设沟槽；
(2)对毛细管网栅的进行检漏试验；
(3)试验合格后，进行隧道一衬、薄壳式换热器和隧道二衬的结构施工。
进一步的，采用水平仪、经纬仪或水准仪找正毛细管网栅的敷设位置；若隧道壁面凹凸不平，采用水泥砂浆对基面进行找平。
进一步的，所述隧道一衬、薄壳式换热器和隧道二衬的结构施工方法为：
(1)隧道一衬施工；
(2)薄壳式换热器的敷设安装；
(3)在薄壳式换热器外部依次设置砂浆层、土工布和防水板；
(4)隧道二衬施工。
进一步的，所述薄壳式换热器的敷设安装方法为：
依次安装进水主管、回水主管和毛细管网栅，将进水主管、回水主管与毛细管网栅连接；
对毛细管网栅分段进行水压试验，再对毛细管网栅和集管进行抹灰作业；
进行砂浆层标注、水压试验和冲洗。
本发明的第三目的是提供一种地铁废热源热泵系统，该系统包括如上所述的薄壳式换热器、废热源热泵系统、辐射末端和辅助冷源，所述废热源热泵系统包括串联的压缩机、冷凝器、节流阀和蒸发器，所述薄壳式换热器通过冬季 地铁废热源侧换热器与热泵机组之间循环回路将高温液体输送至蒸发器，蒸发器通过压缩机将高温液体输送至冷凝器，辐射末端的低温回水通过冬季负荷侧辐射末端与热泵机组之间循环回路被输送至冷凝器，在冷凝器中进行热交换后，升温变为高温水，高温水从冷凝器流入辐射末端对地上建筑进行供热；冷凝器中冷却水与高温高压制冷剂气体进行热交换后，通过夏季辅助冷源侧与热泵机组之间循环回路输送至辅助冷源中进行冷却，冷却后被送回冷凝器中，冷凝器中冷却水通过节流阀输送至蒸发器，在蒸发器中低温低压制冷剂液体与冷冻水进行热交换，冷冻水降温后通过夏季负荷侧辐射末端与热泵机组之间循环回路输送至辐射末端，对地上建筑进行供冷。
进一步的，所述压缩机的出口与冷凝器的第一接口相连，冷凝器的第三接口与节流阀相连，节流阀的另一端与蒸发器的第四接口相连，蒸发器的第二接口与压缩机的进口相连，构成废热源热泵机组循环回路。
进一步的，所述冬季地铁废热源侧换热器与热泵机组之间循环回路包括阀门五、第一三通、第二三通、第一循环水泵、阀门八、第三三通和第四三通，所述蒸发器的第一接口通过阀门五、第一三通、第二三通、第一循环水泵与薄壳式换热器的管口一相连，所述蒸发器的第三接口通过阀门八、第三三通和第四三通与薄壳式换热器的管口二相连。
进一步的，所述冬季负荷侧辐射末端与热泵机组之间循环回路包括第六三通、第九三通、阀门四、第七三通、第八三通和第十三通、阀门七和第二循环水泵，所述冷凝器的第二接口通过第六三通、第九三通、阀门四与辐射末端的进水端相连，冷凝器的第四接口通过第七三通、第八三通和第十三通、阀门七和第二循环水泵与辐射末端的回水端相连。
进一步的，所述夏季辅助冷源侧与热泵机组之间循环回路包括第六三通、第五三通、阀门二、第四循环水泵、第七三通、第八三通和阀门六，所述冷凝器的第二接口通过第六三通、第五三通、阀门二和第四循环水泵与辅助冷源的进水端相连，所述冷凝器的第四接口通过第七三通、第八三通和阀门六与辅助冷源的回水端相连。
进一步的，所述夏季负荷侧辐射末端与热泵机组之间循环回路包括阀门三、第二三通、第九三通、阀门九、第四三通、第十三通和第三循环水泵，所述蒸发器的第一接口通过阀门三、第二三通和第九三通与辐射末端的回水端相连，蒸发器的第三接口通过阀门九、第四三通、第十三通和第三循环水泵与辐射末端的进水端相连。
进一步的，还包括夏季地铁隧道及其岩土冷源侧与热泵机组之间循环回路，所述薄壳式换热器中循环液体通过夏季地铁隧道及其岩土冷源侧与热泵机组之间循环回路被输送至冷凝器，在冷凝器中与高温高压制冷剂气体进行热交换，循环液体温度升高后从冷凝器流出，并被送回至薄壳式换热器中，将热量散发到地铁隧道周围的岩土中储存或直接散发到隧道中被活塞风带走。
进一步的，所述夏季地铁隧道及其岩土冷源侧与热泵机组之间循环回路包括第六三通、第五三通、第三三通、阀门一、第七三通、第一三通、阀门十和第一循环水泵，所述冷凝器的第二接口通过第六三通、第五三通、第三三通和阀门一与薄壳式换热器的管口二相连，所述冷凝器的第四接口通过第七三通、第一三通、阀门十和第一循环水泵与薄壳式换热器的管口一相连。
本发明的第四目的是提供一种采用如上所述的带辅助冷源的地铁废热源热泵系统的工作方法，该方法包括以下步骤：
压缩机排出的高温高压制冷剂气体进入冷凝器后冷凝成低温高压液体，低温高压制冷剂液体经过节流阀变为低温低压制冷剂液体后流入蒸发器，在蒸发器中吸收热量变为低温低压制冷剂气体，并流回压缩机中；
冬季供热时，开启阀门四、阀门五、阀门七、阀门八，关闭阀门一、阀门二、阀门三、阀门六、阀门九和阀门十，开启第一循环水泵和第二循环水泵，关闭第三循环水泵和第四循环水泵；薄壳式换热器中高温液体通过管口一由第一循环水泵泵入蒸发器，与蒸发器中的低温低压制冷剂液体进行热交换，低温液体从蒸发器的第三接口流回薄壳式换热器中重新进行废热回收；同时，辐射末端的低温液体通过第二循环水泵泵入冷凝器，在冷凝器中与高温高压制冷剂气体进行热交换后升温变为高温水，高温水从冷凝器的第二接口流出，进入辐射末端对地上建筑进行供热，低温水经第二循环水泵泵入冷凝器中，依次循环供热；
夏季供冷时，关闭阀门四、阀门五、阀门七、阀门八，开启阀门三和阀门九，关闭第二循环水泵，开启第三循环水泵；将冷却塔作为冷源，开启阀门二、阀门六和第四循环水泵，关闭阀门一、阀门十和第一循环水泵；冷凝器中冷却水与高温高压制冷剂气体进行热交换，冷却水温度升高后通过冷凝器的第二接口由第四循环水泵压入冷却塔中进行冷却，冷却后被送回冷凝器中，冷凝器中冷却水经过节流阀被输送至蒸发器中，在蒸发器中低温低压制冷剂液体与冷冻水回水进行热交换，冷冻水降温后从蒸发器的第三接口由第三循环水泵压入辐射末端，在地上建筑内给用户供冷后，冷冻水温度升高，流回蒸发器中，依次循环供冷。
与现有技术相比，本发明的有益效果是：
(1)本发明将薄壳式换热器布置位置为隧道一衬与隧道二衬之间，在薄壳式换热器与隧道二衬之间由砂浆、土工布、防水板进行保护，可以直接与地铁隧道围岩交换热量，夏季向隧道围岩放热，冬季从隧道围岩取热以保证地铁隧道围岩的热平衡，可以有效的改善地铁环境质量，减轻地铁对环境的废热排放，具有换热效率高，环保，经济适用，使用寿命长等优点；
(2)本发明充分利用了地铁运营产生的废热，将地铁废热源热泵系统与辅助冷源相结合实现了同时对地上建筑用户的供冷供热，也平衡了地铁隧道及其周围岩土的吸放热量，通过阀门的转换能够实现夏季冷源方案的自由选择，使地铁废热源热泵系统继承了土壤源热泵系统的优点，解决了地上建筑用户夏季的供冷问题，采用辐射式末端换热器更加节能环保；
(3)本发明即可以充分利用地铁运营产生的废热为地上建筑供热，又可以自由选择地铁隧道及其周围岩土作为冷源或采用辅助冷源夏季为地上建筑供冷，充分发挥地铁废热源热泵系统的优势。
附图说明
构成本申请的一部分的说明书附图用来提供对本申请的进一步理解，本申请的示意性实施例及其说明用于解释本申请，并不构成对本申请的不当限定。
图1是含薄壳式换热器的地铁废热源热泵系统结构示意图；
图2是毛细管网栅结构图；
图中，1、薄壳式换热器，2、压缩机，3、冷凝器，4、节流阀，5、蒸发器，6、用户末端，7、辅助冷却设备，8、毛细导热水管9、进水主管，10、回水主管，11、隧道一衬，12、薄壳式换热器本体，13、砂浆，14、土工布，15、防水板，16、隧道二衬，17、预留主管管沟，a、冷凝器第一接口，b、冷凝器第 二接口，c、冷凝器第三接口，d、冷凝器第四接口，e、蒸发器第一接口，f、蒸发器第二接口，g、蒸发器第三接口，h、蒸发器第四接口，i、薄壳式换热器主管口一，j、薄壳式换热器主管口二，k、第一三通，l、第二三通，m、第三三通，n、第四三通，o、第五三通，p、第六三通，q、第七三通，r、第八三通，s、第九三通，t、第十三通，A、第一循环水泵，B、第二循环水泵，C、第三循环水泵，D、第四循环水泵，E、阀门一，F、阀门二，G、阀门三，H、阀门四，I、阀门五，J、阀门六，K、阀门七，L、阀门八，M、阀门九，N、阀门十。
具体实施方式
下面结合附图与实施例对本发明作进一步说明。
应该指出，以下详细说明都是例示性的，旨在对本申请提供进一步的说明。除非另有指明，本文使用的所有技术和科学术语具有与本申请所属技术领域的普通技术人员通常理解的相同含义。
需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、操作、器件、组件和/或它们的组合。
为了解决现有的地源热泵系统的地埋管换热器所需场地较大；由于土壤导热系数较小单根地埋管的换热量有限，所以当供热量一定时，所需地埋管长度较长，导致地埋管钻孔较多，所需的换热场地也较大。而且地埋管安装时涉及地下钻孔，施工难度大，钻孔成本较高，当地埋管出现故障时检修更换也比较困难的问题，本实施例提供一种薄壳式换热器。
如图1所示，该薄壳式换热器包括隧道围岩中由内到外依次布置的隧道一衬11、薄壳式换热器本体12和隧道二衬16。
具体地，所述薄壳式换热器本体2作为地铁废热源热泵的前端换热装置布置在地铁隧道围岩的隧道一衬11与隧道二衬16之间，通过薄壳式换热器本体12与地铁隧道围岩交换热量，夏季向隧道围岩放热，冬季从隧道围岩取热以保证地铁隧道围岩的热平衡。
在薄壳式换热器本体12和隧道二衬16之间夹设有由砂浆13、土工布14和防水板15组成的保护层，对薄壳式换热器本体进行热保护。
上述的薄壳式换热器本体沿隧道弧形壁面的圆周方向敷设，该薄壳式换热器本体2包括进水主管9、回水主管10、连接于进水主管9和回水主管10之间的毛细管网栅及其连接件、系统管道及管件等等。
进一步的，所述进水主管9、回水主管10及其连接件、系统管道及管件等材料采用塑料材质、不锈钢材质或铜质。具体应根据工作温度、工作压力、设计寿命、现场防水、水质要求，以及施工要求，经综合比较后确定。
所述毛细管网栅的颜色应均匀一致，管材、管件内外表面应光滑、平整、清洁，无凹陷、气泡、明显的划伤和其它影响性能的表面缺陷。
具体地，所述毛细管网栅包括均布于进水主管10和回水主管11之间均布且贯通进水主管和回水主管的若干根毛细导热水管8，如图2所示。进水主管10和回水主管11布置在隧道同一侧的预留主管管沟7内。
所述毛细导热水管8为直径4.3mm、壁厚0.85mm的PPR管，相邻的毛细导热水管之间的间距为10mm，每席毛细管网宽度1m，毛细管网栅中毛细导热水管的长度可根据实际需要定制。
所述PPR管应一次成型，不允许中间有接头焊接，管材的端面应切割平整，并应与轴线垂直，PPR管网栅要求出厂水压测试，端头要求无痕密封打压，并出厂测试压力不低于0.3Mpa保持5-10分钟。
在隧道一侧设置有预留主管管沟17和薄壳式换热器主管，该预留主管管沟7的作用是：放置进水主管和回水主管；该薄壳式换热器主管是进水主管和回水主管的统称，的作用是：给毛细导热水管供水和回水，相当于是主干管，毛细导热水管是支管。
本发明实施例一提出的用于地铁隧道的薄壳式换热器，将薄壳式换热器布置位置为隧道一衬与隧道二衬之间，在薄壳式换热器与隧道二衬之间由砂浆、土工布、防水板进行保护，可以直接与地铁隧道围岩交换热量，夏季向隧道围岩放热，冬季从隧道围岩取热以保证地铁隧道围岩的热平衡，可以有效的改善地铁环境质量，减轻地铁对环境的废热排放，具有换热效率高，环保，经济适用，使用寿命长等优点。
本实施例还提供一种薄壳式换热器的安装施工方法。该方法包括以下步骤：
S101，确定毛细管网栅的敷设位置，检查隧道壁面是否平整，并在相应位置开设沟槽，如图1中标号17所示位置。该沟槽即主管管沟。
在施工准备完成后，采用水平仪、经纬仪或水准仪对毛细管网栅的敷设位置进行定位放线，找正毛细管网栅的敷设位置。
若隧道壁面凹凸不平，对隧道壁面凹凸严重部位，采用水泥砂浆对基面进行找平，其中，沙子：水泥的比为1:3。
S102，对毛细管网栅的进行检漏试验。
毛细管网栅材料运抵工地后，采用抽检的形式应用水压试压方法对毛细管 网栅的进行检漏试验，排除存在漏洞的毛细管网栅。
S103，试验合格后，进行隧道一衬、薄壳式换热器和隧道二衬的结构施工。
所述隧道一衬、薄壳式换热器和隧道二衬的结构施工方法为：
S1031，进行隧道一衬施工。
S1032，薄壳式换热器的敷设安装。
隧道一衬施工完毕之后进行薄壳式换热器12的敷设安装。所述薄壳式换热器的敷设安装方法为：
依次安装进水主管、回水主管、和毛细管网栅，将进水主管、回水主管与毛细管网栅连接；
对毛细管网栅分段进行水压试验，再对毛细管网栅和集管进行抹灰作业；
进行砂浆层标注、水压试验和冲洗。
S1033，在薄壳式换热器外部依次设置砂浆层、土工布和防水板。
薄壳式换热器敷设完毕后对其外部添加砂浆保护层、土工布、防水板的保护层。
S1034，最后进行隧道二衬的施工；
还包括：在薄壳式换热器敷设安装之前，在隧道一侧安置预留主管管沟和薄壳式换热器主管。
本实施例提出的薄壳式换热器的安装施工方法，将薄壳式换热器布置位置为隧道一衬与隧道二衬之间，在薄壳式换热器与隧道二衬之间由砂浆、土工布、防水板进行保护，可以直接与地铁隧道围岩交换热量，夏季向隧道围岩放热，冬季从隧道围岩取热以保证地铁隧道围岩的热平衡，可以有效的改善地铁环境质量，减轻地铁对环境的废热排放，具有换热效率高，环保，经济适用，使用 寿命长等优点。
由于地铁运行过程中站内的冷负荷只占比较小的一部分，远小于地铁隧道这一冷热源所能供给的地上建筑用户的夏季冷负荷，而现有技术中并没有解决地上建筑用户夏季的供冷问题，为了解决如上的技术问题，本实施例还提供了一种含如上所述的薄壳式换热器的地铁废热源热泵系统及其工作方法，配以辅助冷源，达到给地上建筑用户冬季供热、夏季供冷，充分利用地铁运行产生的废热的效果。
如图1所示，该地铁废热源热泵系统包括毛细管网前端换热系统、废热源热泵系统、辐射末端6、辅助冷源7；所述毛细管网前端换热系统包括如上所述的薄壳式换热器1和第一循环水泵A；所述废热源热泵系统包括压缩机2，带有第一接口a、第二接口b、第三接口c、第四接口d的冷凝器3，节流阀4和带有第一接口e、第二接口f、第三接口g、第四接口h的蒸发器5；整个系统用管路与阀门进行连接，辐射末端6在地上建筑物内。
该系统具体连接方式为：压缩机2的出口与冷凝器3的第一接口a相连，冷凝器3的第三接口c与节流阀4相连，节流阀4的另一端与蒸发器5的第四接口h相连，蒸发器5的第二接口与f压缩机2的进口相连，构成废热源热泵机组循环回路；蒸发器5的第一接口e通过阀门五I和第一三通k和第二三通l、第一循环水泵A与薄壳式换热器1的管口一i相连，蒸发器5的第三接口g通过阀门八L、第三三通m和第四三通n与薄壳式换热器1的管口二j相连，构成冬季地铁废热源侧换热器与热泵机组之间循环回路；蒸发器5的第一接口e通过阀门三G和第二三通l和第九三通s与辐射末端6的回水端相连，蒸发器5的第三接口g通过阀门九M、第四三通n和第十三通t、第三循环水泵C与辐射 末端6的进水端相连，构成夏季负荷侧辐射末端与热泵机组之间循环回路；冷凝器3的第二接口b通过第六三通p和第九三通s、阀门四H与辐射末端6的进水端相连，冷凝器3的第四接口d通过第七三通q、第八三通r和第十三通t、阀门七K、第二循环水泵B与辐射末端6的回水端相连，构成冬季负荷侧辐射末端与热泵机组之间循环回路；冷凝器3的第二接口b通过第六三通p、第五三通o以及第三三通m、阀门一E与薄壳式换热器1的管口二j相连，冷凝器3的第四接口d通过第七三通q和第一三通k、阀门十N、第一循环水泵A与薄壳式换热器1的管口一i相连，构成夏季地铁隧道及其岩土冷源侧与热泵机组之间循环回路；冷凝器3的第二接口b通过第六三通p和第五三通o、阀门二F、第四循环水泵D与辅助冷源7的进水端相连，冷凝器3的第四接口d通过第七三通q和第八三通r、阀门六J与辅助冷源7的回水端相连，构成夏季辅助冷源侧与热泵机组之间循环回路。
本发明实施例公开的地铁废热源热泵系统，冬夏均为地上建筑内的用户供热供冷。冬季时，以地铁隧道内产生的废热为热源供给地上建筑内的用户；夏季时，可以通过切换阀门一E、阀门十N和阀门二F、阀门六J来选择单一使用地铁隧道及其周围岩土作为冷源还是单一使用辅助冷源为地上建筑内的用户供冷，也可同时使用两种冷源，由于地铁运行必然导致地铁隧道及其附近岩土热量累积，为了保持热量平衡，优先选择夏季使用辅助冷源供冷。
辐射末端6可以是毛细管网辐射系统，但不仅限于这一种形式，也可以是其它辐射末端形式；所述辅助冷源7可以是冷却塔，冷却塔应设置在远离人群的下风侧，减少感染军团菌的机会，但辅助冷源7不仅限于冷却塔，还可以是其它形式的辅助冷源。
本发明实施公开的地铁废热源热泵系统，充分利用了地铁运营产生的废热，地铁废热源热泵系统与辅助冷源相结合实现了同时对地上建筑用户的供冷供热，也平衡了地铁隧道及其周围岩土的吸放热量，通过阀门的转换能够实现夏季冷源方案的自由选择，采用辐射式末端换热器更加节能环保，使地铁废热源热泵系统继承了土壤源热泵系统的优点而避其缺点。
对于整个带辅助冷源的地铁废热源热泵系统来说，无论供热供冷，废热源热泵的制冷剂循环都是不可或缺的，其原理都是相同的：压缩机2排出的高温高压制冷剂气体进入冷凝器3的第一接口a后冷凝成低温高压液体并从第三接口c流出，然后低温高压制冷剂液体流入节流阀4变为低温低压制冷剂液体，接着从蒸发器5的第四接口h流入蒸发器5，在蒸发器5中吸收热量变为低温低压制冷剂气体，最后制冷剂气体从蒸发器5的第二接口f接口流出并流回压缩机2中，完成循环。
对于源侧和负荷侧的循环，供热供冷工作原理有所区别。本发明实施例提出的带辅助冷源的地铁废热源热泵系统的工作过程为：
冬季供热时，开启阀门H、I、K、L，关闭阀门E、F、G、J、M、N，开启循环水泵A、B，关闭循环水泵C、D。薄壳式换热器1中因吸收地铁废热而产生的高温液体通过i接口由循环水泵A泵入蒸发器5，与蒸发器5中的低温低压制冷剂液体进行热交换，之后源侧的低温液体从蒸发器5的g接口流回薄壳式换热器1中重新进行废热回收；与此同时，负荷侧供热水循环中的低温液体通过循环水泵B泵入冷凝器3，在冷凝器3中与高温高压制冷剂气体进行热交换，用于供热的液体升温变为高温水并从冷凝器3的b接口流出，接着进入毛细管网辐射系统6对地上建筑进行供热，低温水再流回循环水泵B中完成循环。
夏季供冷时，无论何种方案都需要首先关闭阀门H、I、K、L，开启阀门G、M，关闭循环水泵B，开启循环水泵C。之后判断冷源选择，若方案为单一使用冷却塔7作为冷源，则需开启阀门F、J和循环水泵D，关闭阀门E、N和循环水泵A；若方案为单一使用地铁隧道及其周围岩土作为冷源，则需开启阀门E、N和循环水泵A，关闭阀门F、J和循环水泵D；在本实施例中选则同时使用前述两种冷源，则还需开启阀门F、J、E、N和循环水泵A、D。
夏季辅助冷源侧与热泵机组之间的循环对于本发明实施例来说是冷却水循环，冷凝器3中冷却水与高温高压制冷剂气体进行热交换，冷却水温度升高后通过冷凝器3的b接口由循环水泵D压入冷却塔7中进行冷却，然后送回冷凝器3中，完成循环；对于夏季地铁隧道及其岩土冷源侧与热泵机组之间的循环，薄壳式换热器1中的液体由循环水泵A由d接口泵入冷凝器3中并与高温高压制冷剂气体进行热交换，循环液体温度升高后从冷凝器3的b接口流出，并被送回薄壳式换热器1中，将热量散发到地铁隧道周围的岩土中储存或直接散发到隧道中被活塞风带走，完成循环；与此同时，夏季负荷侧辐射末端与热泵机组之间的循环对于本实施例来说是冷冻水循环，蒸发器5中低温低压制冷剂液体与冷冻水进行热交换，冷冻水降温后从蒸发器5的g接口由第三循环水泵压入毛细管网辐射系统6，在地上建筑内给用户供冷后，冷冻水温度升高，由e接口流回蒸发器5中，完成循环。
上述虽然结合附图对本发明的具体实施方式进行了描述，但并非对本发明保护范围的限制，所属领域技术人员应该明白，在本发明的技术方案的基础上，本领域技术人员不需要付出创造性劳动即可做出的各种修改或变形仍在本发明的保护范围以内。

Claims (20)

  1. 一种薄壳式换热器，其特征是，包括隧道围岩中由内到外依次布置的隧道一衬、薄壳式换热器本体和隧道二衬，在薄壳式换热器本体和隧道二衬之间夹设有由砂浆、土工布和防水板组成的保护层，通过薄壳式换热器本体与地铁隧道围岩交换热量。
  2. 根据权利要求1所述的薄壳式换热器，其特征是，所述薄壳式换热器本体包括进水主管、回水主管以及连接于进水主管和回水主管之间的毛细管网栅，所述毛细管网栅沿隧道弧形壁面的圆周方向敷设。
  3. 根据权利要求2所述的薄壳式换热器，其特征是，所述毛细管网栅包括均布于进水主管和回水主管之间均布且贯通进水主管和回水主管的若干根毛细导热水管，所述进水主管和回水主管布置在隧道同一侧的预留主管管沟内。
  4. 根据权利要求1所述的薄壳式换热器，其特征是，所述毛细导热水管为直径4.3mm、壁厚0.85mm的PPR管，相邻的毛细导热水管之间的间距为10mm。
  5. 一种如权利要求1-4中任一项所述的薄壳式换热器的安装施工方法，其特征在是，包括以下步骤：
    (1)确定毛细管网栅的敷设位置，检查隧道壁面是否平整，并在相应位置开设沟槽；
    (2)对毛细管网栅的进行检漏试验；
    (3)试验合格后，进行隧道一衬、薄壳式换热器和隧道二衬的结构施工。
  6. 根据权利要求5所述的安装施工方法，其特征是，采用水平仪、经纬仪或水准仪找正毛细管网栅的敷设位置；若隧道壁面凹凸不平，采用水泥砂浆对基面进行找平。
  7. 根据权利要求5所述的安装施工方法，其特征是，采用抽检的形式应用 水压试压方法对毛细管网栅进行检漏试验。
  8. 根据权利要求5所述的安装施工方法，其特征是，所述隧道一衬、薄壳式换热器和隧道二衬的结构施工方法为：
    (1)隧道一衬施工；
    (2)薄壳式换热器的敷设安装；
    (3)在薄壳式换热器外部依次设置砂浆层、土工布和防水板；
    (4)隧道二衬施工。
  9. 根据权利要求8所述的安装施工方法，其特征是，所述薄壳式换热器的敷设安装方法为：
    依次安装进水主管、回水主管和毛细管网栅，将进水主管、回水主管与毛细管网栅连接；
    对毛细管网栅分段进行水压试验，再对毛细管网栅和集管进行抹灰作业；
    进行砂浆层标注、水压试验和冲洗。
  10. 根据权利要求5所述的安装施工方法，其特征是，还包括：在薄壳式换热器敷设安装之前，在隧道一侧安置预留主管管沟和薄壳式换热器主管。
  11. 一种地铁废热源热泵系统，其特征是，包括如权利要求1-4中任一项所述的薄壳式换热器、废热源热泵系统、辐射末端和辅助冷源，所述废热源热泵系统包括串联的压缩机、冷凝器、节流阀和蒸发器，所述薄壳式换热器通过冬季地铁废热源侧换热器与热泵机组之间循环回路将高温液体输送至蒸发器，蒸发器通过压缩机将高温液体输送至冷凝器，辐射末端的低温回水通过冬季负荷侧辐射末端与热泵机组之间循环回路被输送至冷凝器，在冷凝器中进行热交换后，升温变为高温水，高温水从冷凝器流入辐射末端对地上建筑进行供热； 冷凝器中冷却水与高温高压制冷剂气体进行热交换后，通过夏季辅助冷源侧与热泵机组之间循环回路输送至辅助冷源中进行冷却，冷却后被送回冷凝器中，冷凝器中冷却水通过节流阀输送至蒸发器，在蒸发器中低温低压制冷剂液体与冷冻水进行热交换，冷冻水降温后通过夏季负荷侧辐射末端与热泵机组之间循环回路输送至辐射末端，对地上建筑进行供冷。
  12. 根据权利要求11所述的带辅助冷源的地铁废热源热泵系统，其特征是，所述压缩机的出口与冷凝器的第一接口相连，冷凝器的第三接口与节流阀相连，节流阀的另一端与蒸发器的第四接口相连，蒸发器的第二接口与压缩机的进口相连，构成废热源热泵机组循环回路。
  13. 根据权利要求11所述的带辅助冷源的地铁废热源热泵系统，其特征是，所述冬季地铁废热源侧换热器与热泵机组之间循环回路包括阀门五、第一三通、第二三通、第一循环水泵、阀门八、第三三通和第四三通，所述蒸发器的第一接口通过阀门五、第一三通、第二三通、第一循环水泵与薄壳式换热器的管口一相连，所述蒸发器的第三接口通过阀门八、第三三通和第四三通与薄壳式换热器的管口二相连。
  14. 根据权利要求11所述的带辅助冷源的地铁废热源热泵系统，其特征是，所述冬季负荷侧辐射末端与热泵机组之间循环回路包括第六三通、第九三通、阀门四、第七三通、第八三通和第十三通、阀门七和第二循环水泵，所述冷凝器的第二接口通过第六三通、第九三通、阀门四与辐射末端的进水端相连，冷凝器的第四接口通过第七三通、第八三通和第十三通、阀门七和第二循环水泵与辐射末端的回水端相连。
  15. 根据权利要求11所述的带辅助冷源的地铁废热源热泵系统，其特征是， 所述夏季辅助冷源侧与热泵机组之间循环回路包括第六三通、第五三通、阀门二、第四循环水泵、第七三通、第八三通和阀门六，所述冷凝器的第二接口通过第六三通、第五三通、阀门二和第四循环水泵与辅助冷源的进水端相连，所述冷凝器的第四接口通过第七三通、第八三通和阀门六与辅助冷源的回水端相连。
  16. 根据权利要求11所述的带辅助冷源的地铁废热源热泵系统，其特征是，所述夏季负荷侧辐射末端与热泵机组之间循环回路包括阀门三、第二三通、第九三通、阀门九、第四三通、第十三通和第三循环水泵，所述蒸发器的第一接口通过阀门三、第二三通和第九三通与辐射末端的回水端相连，蒸发器的第三接口通过阀门九、第四三通、第十三通和第三循环水泵与辐射末端的进水端相连。
  17. 根据权利要求11所述的带辅助冷源的地铁废热源热泵系统，其特征是，还包括夏季地铁隧道及其岩土冷源侧与热泵机组之间循环回路，所述薄壳式换热器中循环液体通过夏季地铁隧道及其岩土冷源侧与热泵机组之间循环回路被输送至冷凝器，在冷凝器中与高温高压制冷剂气体进行热交换，循环液体温度升高后从冷凝器流出，并被送回至薄壳式换热器中，将热量散发到地铁隧道周围的岩土中储存或直接散发到隧道中被活塞风带走。
  18. 根据权利要求11所述的带辅助冷源的地铁废热源热泵系统，其特征是，所述夏季地铁隧道及其岩土冷源侧与热泵机组之间循环回路包括第六三通、第五三通、第三三通、阀门一、第七三通、第一三通、阀门十和第一循环水泵，所述冷凝器的第二接口通过第六三通、第五三通、第三三通和阀门一与薄壳式换热器的管口二相连，所述冷凝器的第四接口通过第七三通、第一三通、阀门 十和第一循环水泵与薄壳式换热器的管口一相连。
  19. 采用权利要求11至18中任一项所述的带辅助冷源的地铁废热源热泵系统的工作方法，其特征是，包括以下步骤：
    压缩机排出的高温高压制冷剂气体进入冷凝器后冷凝成低温高压液体，低温高压制冷剂液体经过节流阀变为低温低压制冷剂液体后流入蒸发器，在蒸发器中吸收热量变为低温低压制冷剂气体，并流回压缩机中；
    冬季供热时，开启阀门四、阀门五、阀门七、阀门八，关闭阀门一、阀门二、阀门三、阀门六、阀门九和阀门十，开启第一循环水泵和第二循环水泵，关闭第三循环水泵和第四循环水泵；薄壳式换热器中高温液体通过管口一由第一循环水泵泵入蒸发器，与蒸发器中的低温低压制冷剂液体进行热交换，低温液体从蒸发器的第三接口流回薄壳式换热器中重新进行废热回收；同时，辐射末端的低温液体通过第二循环水泵泵入冷凝器，在冷凝器中与高温高压制冷剂气体进行热交换后升温变为高温水，高温水从冷凝器的第二接口流出，进入辐射末端对地上建筑进行供热，低温水经第二循环水泵泵入冷凝器中，依次循环供热；
    夏季供冷时，关闭阀门四、阀门五、阀门七、阀门八，开启阀门三和阀门九，关闭第二循环水泵，开启第三循环水泵；将冷却塔作为冷源，开启阀门二、阀门六和第四循环水泵，关闭阀门一、阀门十和第一循环水泵；冷凝器中冷却水与高温高压制冷剂气体进行热交换，冷却水温度升高后通过冷凝器的第二接口由第四循环水泵压入冷却塔中进行冷却，冷却后被送回冷凝器中，冷凝器中冷却水经过节流阀被输送至蒸发器中，在蒸发器中低温低压制冷剂液体与冷冻水回水进行热交换，冷冻水降温后从蒸发器的第三接口由第三循环水泵压入辐 射末端，在地上建筑内给用户供冷后，冷冻水温度升高，流回蒸发器中，依次循环供冷。
  20. 根据权利要求19所述的方法，其特征是，还包括：
    夏季供冷时，关闭阀门四、阀门五、阀门七、阀门八，开启阀门三和阀门九，关闭第二循环水泵，开启第三循环水泵；将使用地铁隧道及其周围岩土作为冷源，开启阀门一、阀门十和第一循环水泵，关闭阀门二、阀门六和第四循环水泵，薄壳式换热器中的循环液体由第一循环水泵泵入冷凝器中，在冷凝器中与高温高压制冷剂气体进行热交换，循环液体温度升高后从冷凝器的第二接口流出，并被送回薄壳式换热器中，将热量散发到地铁隧道周围的岩土中储存或直接散发到隧道中被活塞风带走；冷凝器中冷却水温度降低后经过节流阀输送至蒸发器中，在蒸发器中低温低压制冷剂液体与冷冻水回水进行热交换，冷冻水降温后从蒸发器的第三接口由第三循环水泵压入辐射末端，在地上建筑内给用户供冷后，冷冻水温度升高，流回蒸发器中，依次循环供冷。
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CN112628901A (zh) * 2021-01-21 2021-04-09 中国建筑西北设计研究院有限公司 一种基于分区式能源站的区域供冷实现方法
CN115046237A (zh) * 2022-06-21 2022-09-13 西安西热节能技术有限公司 一种风光气地热多能互补分布式清洁供能系统及方法
CN117950471A (zh) * 2024-03-27 2024-04-30 楚岳(惠州)热传科技有限公司 一种风冷散热器
CN118391937A (zh) * 2024-06-28 2024-07-26 深圳大学 一种提取地铁余热的能源隧道系统及其控制方法

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110345667B (zh) * 2019-07-31 2021-12-17 青岛理工大学 一种地铁复合能源多功能末端热泵系统和方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103615841A (zh) * 2013-11-28 2014-03-05 青岛理工大学 一种应用于地铁隧道中的毛细管土壤源热泵系统
CN106152334A (zh) * 2015-04-08 2016-11-23 青岛理工大学 一种用于地铁隧道内毛细管壁面换热器
CN106705404A (zh) * 2017-02-25 2017-05-24 青岛理工大学 一种地铁隧道热泵前端毛细管换热器安装施工工法
CN108981229A (zh) * 2018-08-09 2018-12-11 青岛理工大学 一种带辅助冷源的地铁废热源热泵系统及其工作方法

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4535981B2 (ja) * 2005-10-14 2010-09-01 三菱マテリアルテクノ株式会社 トンネル熱交換用パネル及びトンネル熱利用熱交換システム
JP6207476B2 (ja) * 2013-07-03 2017-10-04 東日本旅客鉄道株式会社 地中熱利用ヒートポンプシステム
JP6237867B2 (ja) * 2016-11-29 2017-11-29 株式会社大林組 地中熱交換器の挿入方法
CN206397518U (zh) * 2016-12-16 2017-08-11 绍兴文理学院 能源隧道衬砌层埋式地温能热交换装置
CN206903674U (zh) * 2017-06-05 2018-01-19 慧邦开源（北京）科技有限公司 一种隧道防水结构
CN206987841U (zh) * 2017-07-07 2018-02-09 龚岗 防水布和土工布铺敷盛具
CN207245732U (zh) * 2017-09-15 2018-04-17 西南交通大学 一种适用于地铁隧道的相变混凝土与地埋管耦合降温系统

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103615841A (zh) * 2013-11-28 2014-03-05 青岛理工大学 一种应用于地铁隧道中的毛细管土壤源热泵系统
CN106152334A (zh) * 2015-04-08 2016-11-23 青岛理工大学 一种用于地铁隧道内毛细管壁面换热器
CN106705404A (zh) * 2017-02-25 2017-05-24 青岛理工大学 一种地铁隧道热泵前端毛细管换热器安装施工工法
CN108981229A (zh) * 2018-08-09 2018-12-11 青岛理工大学 一种带辅助冷源的地铁废热源热泵系统及其工作方法

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3819561A4 *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112628901A (zh) * 2021-01-21 2021-04-09 中国建筑西北设计研究院有限公司 一种基于分区式能源站的区域供冷实现方法
CN112628901B (zh) * 2021-01-21 2022-01-04 中国建筑西北设计研究院有限公司 一种基于分区式能源站的区域供冷实现方法
CN115046237A (zh) * 2022-06-21 2022-09-13 西安西热节能技术有限公司 一种风光气地热多能互补分布式清洁供能系统及方法
CN115046237B (zh) * 2022-06-21 2024-08-06 西安西热节能技术有限公司 一种风光气地热多能互补分布式清洁供能系统及方法
CN117950471A (zh) * 2024-03-27 2024-04-30 楚岳(惠州)热传科技有限公司 一种风冷散热器
CN117950471B (zh) * 2024-03-27 2024-06-11 楚岳(惠州)热传科技有限公司 一种风冷散热器
CN118391937A (zh) * 2024-06-28 2024-07-26 深圳大学 一种提取地铁余热的能源隧道系统及其控制方法

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