WO2017061211A1 - Évaporateur et turbo-congélateur équipé de celui-ci - Google Patents

Évaporateur et turbo-congélateur équipé de celui-ci Download PDF

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Publication number
WO2017061211A1
WO2017061211A1 PCT/JP2016/076068 JP2016076068W WO2017061211A1 WO 2017061211 A1 WO2017061211 A1 WO 2017061211A1 JP 2016076068 W JP2016076068 W JP 2016076068W WO 2017061211 A1 WO2017061211 A1 WO 2017061211A1
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Prior art keywords
refrigerant
heat transfer
pressure vessel
pressure
transfer tube
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PCT/JP2016/076068
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English (en)
Japanese (ja)
Inventor
直也 三吉
上田　憲治
白方　芳典
紀行 松倉
Original Assignee
三菱重工業株式会社
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Application filed by 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to CN201680036519.2A priority Critical patent/CN107850359B/zh
Priority to US15/736,130 priority patent/US20180187932A1/en
Publication of WO2017061211A1 publication Critical patent/WO2017061211A1/fr

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    • 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
    • F22B37/30—Steam-separating arrangements using impingement against baffle separators
    • 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
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
    • F28C1/00—Direct-contact trickle coolers, e.g. cooling towers
    • F28C1/16—Arrangements for preventing condensation, precipitation or mist formation, outside the cooler
    • 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
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1607—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1638—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
    • F28D7/1646—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one with particular pattern of flow of the heat exchange medium flowing outside the conduit assemblies, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/24—Arrangements for promoting turbulent flow of heat-exchange media, e.g. by plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
    • F25B2339/0242—Evaporators with refrigerant in a vessel in which is situated a heat exchanger having tubular elements
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/226—Transversal partitions
    • 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]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to an evaporator for vaporizing a low-pressure refrigerant and a turbo refrigeration apparatus equipped with the evaporator.
  • a turbo refrigeration system used as a heat source for district heating and cooling is, as is well known, a turbo compressor that compresses refrigerant, a condenser that condenses the compressed refrigerant, and a control valve that expands the condensed refrigerant. And an intercooler that gas-liquid separates the expanded refrigerant and an evaporator that evaporates the expanded refrigerant.
  • the evaporator has a cylindrical shell-shaped pressure vessel, and a heat transfer tube that allows a liquid to be cooled such as water to pass through the pressure vessel in the longitudinal axis direction. Groups are arranged.
  • a distribution plate refrigerant distribution plate
  • an eliminator is provided above the heat transfer tube group.
  • the liquid-phase refrigerant compressed by the turbo compressor and condensed by the condenser flows into the pressure vessel from the refrigerant inlet provided at the lower portion of the pressure vessel, and passes through a number of refrigerant circulation holes of the distribution plate.
  • heat is exchanged with the heat transfer tube group while diffusing throughout the interior of the pressure vessel.
  • the liquid to be cooled flowing inside the heat transfer tube group is cooled, and the cooled liquid to be cooled is used as a cooling medium for air conditioning or an industrial cooling liquid.
  • the liquid-phase refrigerant that exchanges heat with the heat transfer tube group boils and vaporizes due to the temperature difference. Then, when passing through the eliminator, the liquid phase component is removed, and only the gas-phase refrigerant is sucked into the turbo compressor from the suction pipe connected to the upper part of the pressure vessel and compressed again.
  • the inner diameter of the refrigerant flow hole in the distribution plate, the drilling interval, and the like are constant. That is, the area ratio of the refrigerant flow holes per unit area of the distribution plate is constant throughout the distribution plate.
  • the eliminator was disposed at a position sufficiently higher than the liquid level of the refrigerant in the pressure vessel. The reason for this is to prevent the so-called carryover (gas-liquid entrainment) in which the liquid droplets of the boiled refrigerant pass through the eliminator and enter the suction pipe in a liquid state, thereby suppressing the efficiency reduction of the turbo compressor. It is.
  • Low-pressure refrigerants such as R1233zd used at a maximum pressure of less than 0.2 MPaG are expected as next-generation refrigerants because they can increase the efficiency of turbo refrigeration equipment and have a low global warming potential.
  • the refrigerant boils violently because the temperature difference between the liquid to be cooled and the refrigerant flowing inside the heat transfer tube group is large, but in the downstream part of the heat transfer tube group, the above temperature difference As the temperature shrinks, the boiling of the refrigerant becomes gentle. For this reason, it becomes difficult to set and adjust the liquid level (floss level) of the liquid-phase refrigerant pool inside the evaporator.
  • the gap flow velocity is increased in the heat transfer tube group, there is a concern about fatigue failure due to the drag applied to each heat transfer tube.
  • the volume flow rate of the vaporized refrigerant sucked into the turbo compressor from the evaporator is much larger than that of the high-pressure refrigerant, so that the flow rate of the vaporized refrigerant inside the evaporator becomes high, and the vaporized refrigerant
  • the liquid-phase refrigerant is likely to carry over to the turbo compressor side on the flow, and there is a concern that the efficiency of the turbo compressor may be reduced.
  • the present invention has been made in view of such circumstances, and in a turbo refrigeration apparatus using a low-pressure refrigerant used at a maximum pressure of less than 0.2 MPaG, prevents the heat transfer tube group from being dried out in the evaporator. It is an object of the present invention to provide an evaporator capable of improving the heat transfer performance and suppressing a decrease in efficiency due to the liquid phase low-pressure refrigerant being carried over to the turbo compressor side, and a turbo refrigeration apparatus equipped with the evaporator And
  • the evaporator according to the first aspect of the present invention is provided in a lower part of the pressure vessel, which extends in a horizontal direction and into which a low-pressure refrigerant used at a maximum pressure of less than 0.2 MPaG is condensed and introduced.
  • a heat transfer tube group to be exchanged and a plate-like refrigerant distribution plate installed between the refrigerant inlet and the heat transfer tube group inside the pressure vessel and having a refrigerant flow hole formed therein, and the refrigerant
  • the area ratio of the refrigerant circulation holes per unit area in the distribution plate is larger than the other ranges in the range corresponding to the vicinity of the upstream position of the heat transfer tube group.
  • the area ratio of the refrigerant flow holes per unit area in the refrigerant distribution plate is larger than the other ranges in the range corresponding to the vicinity of the upstream position of the heat transfer tube group, so that the refrigerant inlet into the pressure vessel A large amount of the introduced low-pressure refrigerant is distributed near the position on the upstream side of the heat transfer tube group. A relatively small amount of low-pressure refrigerant is distributed to other positions. Thereby, the liquid level height (floss level) of the low-pressure refrigerant pool inside the pressure vessel is made uniform.
  • the low-pressure refrigerant boils violently due to the large temperature difference with the liquid to be cooled flowing inside the heat transfer tube group.
  • the position near the upstream side of the heat transfer tube group is surrounded by the low-pressure refrigerant boiling bubbles and does not dry out.
  • the state where the heat transfer tube group is immersed in the refrigerant two-phase liquid can be maintained. For this reason, the to-be-cooled liquid which flows through the inside of the heat transfer tube group and the low-pressure refrigerant can be favorably exchanged heat, and the heat transfer performance of the heat transfer tube group can be enhanced.
  • the floss level of the low-pressure refrigerant pool does not rise at both ends of the pressure vessel in the longitudinal direction intermediate portion of the pressure vessel, the refrigerant communicated with the suction pipe of the turbo compressor at the longitudinal direction intermediate portion of the pressure vessel.
  • the refrigerant inlet is provided in an intermediate portion in the longitudinal axis direction of the pressure vessel, and the area ratio of the refrigerant circulation holes in the refrigerant distribution plate is a range of an end portion in the longitudinal axis direction of the refrigerant distribution plate. It is good also as a structure larger than the range of a longitudinal-axis direction intermediate part.
  • a large amount of the low-pressure refrigerant introduced into the pressure vessel from the refrigerant inlet provided in the intermediate portion in the longitudinal axis direction of the pressure vessel is supplied to both ends in the longitudinal axis direction inside the pressure vessel.
  • a relatively small amount is supplied to the intermediate portion in the longitudinal axis direction of the pressure vessel, which is directly above the inlet.
  • the liquid level height (floss level) of the low-pressure refrigerant pool inside the pressure vessel is made uniform so that the liquid to be cooled and the low-pressure refrigerant flowing inside the heat transfer pipe group can exchange heat well, and the heat transfer of the heat transfer pipe group Performance can be increased.
  • the evaporator according to the second aspect of the present invention is provided in a lower part of the pressure vessel, which extends in the horizontal direction and into which a low-pressure refrigerant used at a maximum pressure of less than 0.2 MPaG is condensed and introduced.
  • a heat transfer tube group to be exchanged and a plate-like refrigerant distribution plate installed between the refrigerant inlet and the heat transfer tube group inside the pressure vessel and having a refrigerant flow hole formed therein, and the refrigerant A plurality of inlets are provided in a distributed manner along the longitudinal axis direction of the pressure vessel.
  • the volume flow rate flowing from the refrigerant inlet to the evaporator is large and the dynamic pressure is high.
  • the speed of ejection from the refrigerant circulation hole of the distribution plate increases, leading to vibration and breakage of the heat transfer tube group.
  • a plurality of refrigerant inlets are provided along the longitudinal axis direction of the pressure vessel, so that the inflow rate of the low-pressure refrigerant is reduced compared to a case where the refrigerant inlet is single. be able to. For this reason, the diameter of the refrigerant circulation hole of the refrigerant distribution plate can be increased, thereby reducing the speed at which the low-pressure refrigerant is ejected from the refrigerant circulation hole, and the vibration and breakage of the heat transfer tube group can be prevented.
  • the low-pressure refrigerant can be made to flow uniformly from the plurality of refrigerant inlets over the entire length of the pressure vessel in the longitudinal axis direction so that the floss level of the low-pressure refrigerant pool inside the pressure vessel can be made uniform.
  • the heat transfer performance is improved by preventing the heat transfer tube group from being dried out, and the liquid phase low-pressure refrigerant is locally blown up and suppressed from being carried over to the turbo compressor side. A reduction in the efficiency of the compressor can be avoided.
  • the evaporator according to the third aspect of the present invention is provided in a lower part of the pressure vessel, which extends in the horizontal direction and into which a low-pressure refrigerant used at a maximum pressure of less than 0.2 MPaG is condensed and introduced.
  • the cross-sectional area of the flow path from the outer opening of the inlet to the pressure vessel is enlarged from the outer opening toward the pressure vessel.
  • the flow path cross-sectional area from the outer opening of the refrigerant inlet to the pressure vessel increases toward the pressure vessel, so the flow rate of the low-pressure refrigerant flowing through the refrigerant inlet decreases toward the pressure vessel. .
  • the speed at which the low-pressure refrigerant is ejected from the refrigerant circulation holes of the refrigerant distribution plate is reduced to prevent vibration and breakage of the heat transfer tube group, and the liquid-phase low-pressure refrigerant is locally blown up and turbo compressed. Carrying over to the machine side can be suppressed, and a reduction in efficiency of the turbo compressor can be avoided.
  • the evaporator according to the fourth aspect of the present invention is provided in a lower part of the pressure vessel, which extends in the horizontal direction and into which the low-pressure refrigerant used at a maximum pressure of less than 0.2 MPaG is condensed and introduced.
  • the inlet has a tubular shape connected to the pressure vessel, and a flow rate attenuating member for attenuating the flow rate of the low-pressure refrigerant is provided in the tube.
  • the flow rate of the low-pressure refrigerant flowing into the pressure vessel from the refrigerant inlet is reduced by the flow velocity attenuating member. For this reason, the speed at which the low-pressure refrigerant is ejected from the refrigerant circulation holes of the refrigerant distribution plate is reduced to prevent vibration and breakage of the heat transfer tube group, and the liquid-phase low-pressure refrigerant is locally blown up and turbo compressed. Carrying over to the machine side can be suppressed, and a reduction in efficiency of the turbo compressor can be avoided.
  • the heat transfer tube group includes an outward tube group extending from one longitudinal end to the other end in the pressure vessel, and an outward tube group at the other longitudinal end in the pressure vessel.
  • a return pipe group that communicates and returns from the other end in the longitudinal axis direction to the one end in the longitudinal direction of the pressure vessel, and the forward tube group is disposed below and the return tube group is disposed above in the pressure vessel.
  • the outgoing pipe group in which the temperature difference from the liquid to be cooled flowing in the heat transfer pipe is large and the boiling of the low-pressure refrigerant is intense is arranged at the lower part of the pressure vessel, and the temperature difference from the liquid to be cooled is
  • a return pipe group in which the boiling of the small low-pressure refrigerant is gentle is arranged at the top of the pressure vessel.
  • the heat transfer tube group is configured such that a plurality of heat transfer tube bundles in which a plurality of heat transfer tubes are bundled are arranged in a horizontal direction, and a gap extending in the vertical direction is formed between the heat transfer tube bundles. Also good.
  • the vertical gap between the plurality of heat transfer tube bundles becomes a passage for the boiling bubbles of the low-pressure refrigerant boiled by heat exchange with the heat transfer tube group.
  • the boiling bubbles can easily float on the liquid level of the low-pressure refrigerant. Therefore, it is possible to prevent the heat transfer tube group from being surrounded by boiling bubbles and drying out under the refrigerant liquid level, and to improve the heat transfer performance of the heat transfer tube group.
  • the refrigerant circulation hole formed in the refrigerant distribution plate may be arranged vertically below the gap.
  • the flow of the low-pressure refrigerant that passes through the refrigerant flow hole formed in the refrigerant distribution plate and is discharged upward passes through the gap and reaches the upper end of the heat transfer tube group.
  • the heat transfer performance of the heat tube group can be enhanced.
  • a demister that is positioned between the refrigerant outlet and the heat transfer tube group inside the pressure vessel and performs gas-liquid separation of the refrigerant is disposed immediately above the heat transfer tube group.
  • a configuration may be adopted.
  • the gas flow rate is large, so that the distance until the droplets of the liquid-phase refrigerant that spouts are separated from the gas-phase refrigerant by its own weight becomes relatively long. For this reason, if the demister is installed at a position higher than the position where the droplets separate by their own weight, the distance from the coolant level to the demister becomes longer, and the shell diameter of the pressure vessel becomes larger.
  • the demister directly above the heat transfer tube group, it is possible to reduce the amount of droplets ejected by the demister and to reduce the carry-over amount. Furthermore, by placing the demister directly above the heat transfer tube group, the evaporation mist of the low-pressure refrigerant is promoted to become a large diameter droplet in the space above the demister, and the distance at which the droplet separates by its own weight is reduced to reduce the pressure. The carry over of the refrigerant can be prevented.
  • the demister may be provided so that the entire circumference of the demister is in contact with the inner circumference of the pressure vessel.
  • the entire amount of the low-pressure refrigerant gas flow inside the pressure vessel must pass through the demister, and the flow resistance of the gas flow increases. For this reason, the flow velocity distribution of the gas flow in the pressure vessel is leveled, the peak value of the local gas flow velocity is lowered, the amount of droplets generated is reduced, and the self-weight separation distance of the droplets is shortened. The carry over of the refrigerant can be prevented.
  • the individual heat transfer tubes constituting the heat transfer tube group have a surface direction intersecting with the longitudinal axis direction of the pressure vessel and are spaced in the longitudinal axis direction of the pressure vessel.
  • the heat transfer tube support plate is installed penetrating through the plurality of arranged heat transfer tube support plates, and the heat transfer tube support plate installation interval in the vicinity of the upstream position of the heat transfer tube group is greater than the heat transfer tube support plate installation interval at other positions.
  • the configuration may be reduced.
  • the temperature difference between the liquid to be cooled and the low pressure refrigerant flowing inside the heat transfer tube group is large, so that the low pressure refrigerant boils violently and the specific volume of the boiling bubbles is higher than that of the high pressure refrigerant. Because of the large size, a larger vibration is generated than when a high-pressure refrigerant is used. For this reason, there is a concern that the heat transfer tube group is damaged due to resonance with the vibration of the boiling bubbles.
  • the turbo refrigeration apparatus is a turbo compressor that compresses low-pressure refrigerant used at a maximum pressure of less than 0.2 MPaG, a condenser that condenses the compressed low-pressure refrigerant, and evaporates the expanded low-pressure refrigerant.
  • a turbo compressor that compresses low-pressure refrigerant used at a maximum pressure of less than 0.2 MPaG
  • a condenser that condenses the compressed low-pressure refrigerant, and evaporates the expanded low-pressure refrigerant.
  • turbo refrigeration apparatus having the above-described configuration, when low-pressure refrigerant is used, dry-out of the heat transfer tube group due to boiling bubbles of the low-pressure refrigerant in the evaporator and droplets of the low-pressure refrigerant are carried over to the turbo compressor. This can be prevented and the efficiency can be improved by the low-pressure refrigerant.
  • the heat transfer tube group in the evaporator As described above, according to the evaporator according to the present invention and the turbo refrigeration apparatus including the evaporator, in the turbo refrigeration apparatus using the low-pressure refrigerant used at a maximum pressure of less than 0.2 MPaG, the heat transfer tube group in the evaporator As a result, it is possible to improve the heat transfer performance by preventing the dry-out of the liquid and to suppress a decrease in efficiency due to the liquid-phase low-pressure refrigerant being carried over to the turbo compressor side.
  • FIG. 1 is an overall view of a turbo refrigeration apparatus according to an embodiment of the present invention. It is a side view of the evaporator which shows 1st Embodiment of this invention by the II arrow view of FIG.
  • FIG. 3 is a longitudinal sectional view of the evaporator taken along line III-III in FIG. 2. It is a longitudinal cross-sectional view of the evaporator which follows the IV-IV line of FIG. It is a side view of the evaporator which shows 2nd Embodiment of this invention. It is a longitudinal cross-sectional view of the evaporator which shows 3rd Embodiment of this invention. It is a VII arrow line view of FIG.
  • FIG. 1 is an overall view of a turbo refrigeration apparatus according to an embodiment of the present invention.
  • the turbo refrigeration apparatus 1 includes a turbo compressor 2 that compresses refrigerant, a condenser 3, a high-pressure expansion valve 4, an intermediate cooler 5, a low-pressure expansion valve 6, an evaporator 7, and a lubricating oil tank 8.
  • the circuit box 9, the inverter unit 10, the operation panel 11 and the like are provided in a unit shape.
  • the lubricating oil tank 8 is a tank that stores lubricating oil to be supplied to the bearings, the speed increaser, and the like of the turbo compressor 2.
  • the condenser 3 and the evaporator 7 are formed in a cylindrical shell shape with high pressure resistance, and are arranged in parallel so as to be adjacent to each other with their axes extending in a substantially horizontal direction.
  • the condenser 3 is disposed at a relatively higher position than the evaporator 7, and a circuit box 9 is installed below the condenser 3.
  • the intercooler 5 and the lubricating oil tank 8 are installed between the condenser 3 and the evaporator 7.
  • the inverter unit 10 is installed on the top of the condenser 3, and the operation panel 11 is arranged above the evaporator 7.
  • the lubricating oil tank 8, the circuit box 9, the inverter unit 10, and the operation panel 11 are arranged so as not to protrude significantly from the entire outline of the turbo refrigeration apparatus 1 in plan view.
  • the turbo compressor 2 is of a known centrifugal turbine type that is rotationally driven by an electric motor 13, and is disposed above the evaporator 7 in a posture in which the axis thereof extends in a substantially horizontal direction.
  • the electric motor 13 is driven by the inverter unit 10.
  • the turbo compressor 2 compresses the gas-phase refrigerant supplied from the refrigerant outlet 23 of the evaporator 7 through the suction pipe 14.
  • a low-pressure refrigerant such as R1233zd used at a maximum pressure of less than 0.2 MPaG is used.
  • the discharge port of the turbo compressor 2 and the top of the condenser 3 are connected by a discharge pipe 15, and the bottom of the condenser 3 and the bottom of the intercooler 5 are connected by a refrigerant pipe 16. Further, the bottom of the intermediate cooler 5 and the evaporator 7 are connected by a refrigerant pipe 17, and the upper part of the intermediate cooler 5 and the middle stage of the turbo compressor 2 are connected by a refrigerant pipe 18.
  • the refrigerant pipe 16 is provided with the high-pressure expansion valve 4, and the refrigerant pipe 17 is provided with the low-pressure expansion valve 6.
  • First Embodiment 2 to 4 show a first embodiment of the evaporator 7.
  • the evaporator 7 is provided in a cylindrical shell-shaped pressure vessel 21 extending in the horizontal direction, a refrigerant inlet 22 provided in a lower portion of the pressure vessel 21, and an upper portion of the pressure vessel 21.
  • a refrigerant outlet 23, a heat transfer tube group 25 that passes through the inside of the pressure vessel 21 in the longitudinal axis direction, a refrigerant distribution plate 26, and a demister 27 are provided.
  • the refrigerant inlet 22 and the refrigerant outlet 23 are respectively disposed in the middle portion in the longitudinal axis direction of the pressure vessel 21, and the refrigerant inlet 22 is formed in a short pipe shape extending horizontally and tangentially from the bottom of the pressure vessel 21,
  • the refrigerant outlet 23 is formed in a short pipe shape extending vertically upward from the upper part of the pressure vessel 21.
  • the refrigerant inlet 17 is connected to the refrigerant pipe 17 extending from the bottom of the intermediate cooler 5, and the refrigerant outlet 23 is connected to the suction pipe 14 of the turbo compressor 2.
  • an inlet chamber 31 is provided below one end (for example, the left end in FIG. 2), and an outlet chamber 32 is provided as an independent room above the chamber.
  • a U-turn chamber 33 is provided as an independent room at the other inner end of the pressure vessel 21 (for example, the right end in FIG. 2).
  • the heat transfer tube group 25 is a forward tube group extending from one end (left end in FIG. 2) in the longitudinal axis direction to the other end (right end in FIG. 2) inside the pressure vessel 21.
  • 25A and a return pipe group 25B that communicates with the forward pipe group 25A at the other end in the longitudinal axis inside the pressure vessel 21 and returns from the other end in the longitudinal axis inside the pressure vessel 21 to one end.
  • the outgoing pipe group 25A is disposed so as to connect the inlet chamber 31 and the lower part of the U-turn chamber 33, and the return pipe group 25B is provided between the outlet chamber 32 and the upper part of the U-turn chamber 33. It arrange
  • the outward pipe group 25 ⁇ / b> A is arranged below the inside of the pressure vessel 21, and the return pipe group 25 ⁇ / b> B is arranged inside the pressure vessel 21.
  • water for example, water (tap water, purified water, distilled water, etc.) flows as a liquid to be cooled to be cooled by the refrigerant.
  • This water flows from the inlet chamber 31 and flows through the forward pipe group 25A, and after making a U-turn in the U-turn chamber 33, flows through the backward pipe group 25B, and flows out from the outlet nozzle 35 through the outlet chamber 32 as cold water.
  • the forward tube group 25A and the return tube group 25B constituting the heat transfer tube group 25 each include a plurality of heat transfer tube bundles 25a in which a large number of heat transfer tubes are bundled in the horizontal direction (for example, four Each) arranged in parallel.
  • a gap S1 extending in the vertical direction is formed between the heat transfer tube bundles 25a.
  • a gap S2 extending in the horizontal direction is formed between the forward tube group 25A and the backward tube group 25B.
  • individual heat transfer tubes constituting the heat transfer tube group 25 are fixed inside the pressure vessel 21 while being supported by a plurality of heat transfer tube support plates 37 inside the pressure vessel 21.
  • These heat transfer tube support plates 37 have a flat plate shape having a surface direction intersecting with the longitudinal axis direction of the pressure vessel 21.
  • a plurality of these heat transfer tube support plates 37 are arranged at intervals in the longitudinal axis direction of the pressure vessel 21. It is fixed.
  • a large number of through holes are formed in the heat transfer tube support plate 37, and the heat transfer tubes are densely inserted into the through holes.
  • the installation interval of the heat transfer tube support plate 37 along the longitudinal axis direction of the pressure vessel 21 is in the vicinity of the upstream position of the heat transfer tube group 25, that is, in the vicinity of the upstream position of the forward tube group 25A (left side in FIG. 2).
  • the installation interval L1 is smaller than the installation interval L2 at other positions. For example, L1 is about half of L2.
  • the refrigerant distribution plate 26 is installed between the refrigerant inlet 22 and the heat transfer pipe group 25 (outward pipe group 25A) inside the pressure vessel 21.
  • the refrigerant distribution plate 26 is a plate-like member having a large number of refrigerant flow holes 26a.
  • the area ratio of the refrigerant flow holes 26a per unit area in the refrigerant distribution plate 26 is in the range A1 corresponding to the vicinity of the upstream position of the heat transfer tube group 25 (25A), for example, in the middle of the heat transfer tube group 25. It is larger than the range A2 corresponding to the position of the section.
  • the area ratio of the refrigerant circulation hole 26a is larger in the ranges A1 and A3 at both ends in the longitudinal axis direction of the refrigerant distribution plate 26 than in the range A2 in the middle portion in the longitudinal axis direction.
  • the area ratio of the refrigerant flow holes 26a in the ranges A1 and A3 can be 33 to 38%, and the area ratio of the refrigerant flow holes 26a in the range A2 can be 24 to 33%, but is not limited to this range. .
  • the refrigerant distribution plate 26 is vertically below a gap S ⁇ b> 1 that extends between the plurality of heat transfer tube bundles 25 a constituting the heat transfer tube group 25 (25 ⁇ / b> A, 25 ⁇ / b> B).
  • a refrigerant circulation hole 26a is arranged. That is, the refrigerant circulation holes 26a are arranged along the longitudinal direction of the gap S1 in plan view.
  • the demister 27 is disposed inside the pressure vessel 21 between the refrigerant outlet 23 and the heat transfer tube group 25 (return tube group 25B).
  • the demister 27 is a member having high air permeability, for example, in which wires are entangled in a mesh shape, and performs gas-liquid separation of a low-pressure refrigerant. Not only a wire mesh but other porous substances may be used as long as air permeability is good.
  • the demister 27 is attached so that the entire circumference of the demister 27 is in contact with the inner circumference of the pressure vessel 21, and the internal space of the pressure vessel 21 is divided into upper and lower parts with the demister 27 as a boundary. Further, the installation height of the demister 27 is set directly above the heat transfer tube group 25. Specifically, the interval between the heat transfer tube group 25 and the demister 27 is about twice the tube arrangement pitch. On the other hand, a relatively large height difference (for example, about 50% or more of the diameter of the pressure vessel 21) is provided between the demister 27 and the refrigerant outlet 23.
  • the turbo compressor 2 is driven to rotate by the electric motor 13, and the gas-phase low-pressure refrigerant supplied from the evaporator 7 through the suction pipe 14 is supplied.
  • the compressed low-pressure refrigerant is supplied from the discharge pipe 15 to the condenser 3.
  • the high-temperature low-pressure refrigerant compressed by the turbo compressor 2 is heat-exchanged with the cooling water, whereby the heat of condensation is cooled and condensed.
  • the low-pressure refrigerant that has become a liquid phase in the condenser 3 expands by passing through the high-pressure expansion valve 4 provided in the refrigerant pipe 16 that extends from the condenser 3, and becomes a gas-liquid mixed state. 5 and is temporarily stored here.
  • the low-pressure refrigerant in the gas-liquid mixed state expanded by the high-pressure expansion valve 4 is separated into a gas phase and a liquid phase.
  • the liquid phase component of the low-pressure refrigerant separated here is further expanded by a low-pressure expansion valve 6 provided in the refrigerant pipe 17 extending from the bottom of the intermediate cooler 5 to become a gas-liquid two-phase flow, and the evaporator 7.
  • the gas phase component of the low-pressure refrigerant separated by the intermediate cooler 5 is fed to the middle stage of the turbo compressor 2 via the refrigerant pipe 18 extending from the upper part of the intermediate cooler 5 and is compressed again.
  • the low-temperature gas-liquid two-phase low-pressure refrigerant after adiabatic expansion in the low-pressure expansion valve 6 flows into the pressure vessel 21 from the refrigerant inlet 22, After being dispersed in the longitudinal axis direction of the pressure vessel 21 below the refrigerant distribution plate 26, the refrigerant passes through the refrigerant flow holes 26 a of the refrigerant distribution plate 26 and flows upward.
  • a pool of low-pressure refrigerant is formed inside the pressure vessel 21. The liquid level of the low-pressure refrigerant pool is automatically adjusted to be between the heat transfer tube group 25 and the demister 27.
  • the heat transfer tube group 25 (25A, 25B) is immersed in the low-pressure refrigerant pool inside the pressure vessel 21, and exchanges heat with the low-pressure refrigerant. Thereby, the water which passes the inside of the heat exchanger tube group 25 is cooled, and becomes cold water. This cold water is used as a cooling / heating medium for air conditioning, industrial cooling water, or the like.
  • the low-pressure refrigerant evaporated (vaporized) by heat exchange with the heat transfer tube group 25 is gas-liquid separated by the demister 27. That is, when the vaporized low-pressure refrigerant (vaporized refrigerant) travels through the pressure vessel 21 toward the refrigerant outlet 23, a fast flow is formed due to the characteristics of the low-pressure refrigerant having a larger specific volume than the high-pressure refrigerant. Then, the droplets of the unvaporized liquid-phase refrigerant ejected from the low-pressure refrigerant pool tend to come out from the refrigerant outlet 23 along with the fast flow of the vaporized refrigerant, and there is a possibility that carry-over occurs.
  • the area ratio of the refrigerant circulation holes 26a in the refrigerant distribution plate 26 installed between the refrigerant inlet 22 and the heat transfer tube group 25 (25A, 25B) inside the pressure vessel 21 is such that the heat transfer tube group.
  • the range A1 corresponding to the vicinity of the position on the upstream side of 25 (25A) is made larger than the other range A2.
  • the low-pressure refrigerant introduced into the pressure vessel 21 from the refrigerant inlet 22 is distributed in a relatively large amount near the upstream position of the heat transfer tube group 25 (25A).
  • a relatively small amount of low-pressure refrigerant is distributed to other positions. Thereby, the liquid level height (floss level) of the low-pressure refrigerant pool inside the pressure vessel 21 is made uniform.
  • the low-pressure refrigerant boils violently due to a large temperature difference from the water flowing inside the heat transfer tube group 25 (25A).
  • the vicinity of the upstream position of the heat transfer tube group 25 (25A) is surrounded by boiling bubbles of low-pressure refrigerant.
  • the heat transfer tube group 25 (25A, 25B) can be maintained immersed in the refrigerant two-phase liquid.
  • the to-be-cooled liquid and the low-pressure refrigerant flowing inside the heat transfer tube group 25 can be favorably exchanged, and the heat transfer performance of the heat transfer tube group 25 (25A, 25B) can be improved. it can.
  • the longitudinal axis direction intermediate portion of the pressure vessel 21 as in the present embodiment.
  • the evaporator 7 is provided with the refrigerant inlet 22 in the intermediate portion in the longitudinal axis direction of the pressure vessel 21, and the area ratio of the refrigerant flow holes 26 a in the refrigerant distribution plate 26 is equal to both longitudinal end portions of the refrigerant distribution plate 26.
  • the range A2 of the intermediate portion in the longitudinal axis direction is made larger.
  • the heat transfer tube group 25 of the evaporator 7 communicates with the forward tube group 25A extending from one end in the longitudinal axis inside the pressure vessel 21 to the other end, and the forward tube group 25A at the other longitudinal end inside the pressure vessel 21. And a return pipe group 25B that returns from the other end in the longitudinal axis direction inside the pressure vessel 21 to one end.
  • the forward tube group 25A is disposed below, and the return tube group 25B is disposed above.
  • the forward tube group 25A in which the temperature difference with the water flowing in the heat transfer tube is large and the boiling of the low-pressure refrigerant is intense is arranged at the lower part of the pressure vessel 21, and flows in the heat transfer tube.
  • a plurality of heat transfer tube bundles 25a in which a plurality of heat transfer tubes are bundled are arranged in the horizontal direction, and a gap S1 extending in the vertical direction is formed between these heat transfer tube bundles 25a.
  • the vertical gap S1 between the plurality of heat transfer tube bundles 25a becomes a passage for boiling bubbles of the low-pressure refrigerant boiled by heat exchange with the heat transfer tube group 25 (25A, 25B).
  • the boiling bubbles can easily float on the liquid level of the low-pressure refrigerant pool. Therefore, it is possible to prevent the heat transfer tube group 25 (25A, 25B) from being surrounded by boiling bubbles and dry out under the refrigerant liquid level, and to improve the heat transfer performance of the heat transfer tube group 25 (25A, 25B).
  • the refrigerant flow hole 26a drilled in the refrigerant distribution plate 26 is disposed vertically below the gap S1, it passes through the refrigerant flow hole 26a of the refrigerant distribution plate 26 and is discharged upward.
  • the flow of the low-pressure refrigerant passes through the gap S1 and reaches the upper end of the heat transfer tube group 25 (25A, 25B). Therefore, the heat transfer performance of the heat transfer tube group 25 (25A, 25B) can be enhanced.
  • the gas flow rate inside the pressure vessel 21 of the evaporator 7 is increased due to the characteristic of the low-pressure refrigerant that has a larger specific deposition than the high-pressure refrigerant. For this reason, the distance until the droplets of the liquid-phase refrigerant ejected from the low-pressure refrigerant pool inside the pressure vessel 21 are separated from the gas-phase refrigerant by its own weight becomes relatively long. For this reason, if the demister 27 is installed at a position higher than the position where the droplets separate by their own weight, the distance from the refrigerant liquid surface to the demister 27 becomes longer, and the shell diameter of the pressure vessel 21 becomes larger.
  • the demister 27 is disposed immediately above the heat transfer tube group 25, whereby the amount of liquid droplets ejected from the low-pressure refrigerant pool is reduced by the demister 27, and the low-pressure refrigerant liquid droplets exit from the refrigerant outlet 23. (Carry over) is suppressed. Furthermore, by disposing the demister 27 directly above the heat transfer tube group 25, the space height on the demister 27 is relatively increased, and the evaporation mist of the low-pressure refrigerant is promoted to be a droplet having a large diameter, By reducing the distance at which the droplets separate by their own weight, the carry-over of the low-pressure refrigerant can also be suppressed in this respect.
  • the demister 27 is provided so that the entire circumference of the demister 27 is in contact with the entire inner circumference of the pressure vessel 21.
  • interval L1 in the position vicinity of the upstream of the heat exchanger tube group 25 of the some heat exchanger tube support plate 37 which supports each heat exchanger tube of the heat exchanger tube group 25 is other position. Is smaller than the installation interval L2.
  • the temperature difference between the water flowing in the heat transfer tube group 25 and the low pressure refrigerant is large, so the low pressure refrigerant boils violently, and the specific volume of the boiling bubbles is Since it is larger than the high-pressure refrigerant, a larger vibration is generated than when the high-pressure refrigerant is used. For this reason, there is a concern that the heat transfer tube group 25 may be damaged due to resonance with the vibration of the boiling bubbles.
  • FIG. 5 is a side view of an evaporator showing a second embodiment of the present invention.
  • This evaporator 7A is different from the evaporator 7 (refrigerant inlet 22) of the first embodiment in that a plurality of refrigerant inlets 22A of the pressure vessel 21 are provided in a dispersed manner along the longitudinal axis direction of the pressure vessel 21.
  • a plurality of refrigerant inlets 22A of the pressure vessel 21 are provided in a dispersed manner along the longitudinal axis direction of the pressure vessel 21.
  • other configurations are the same. For this reason, the same code
  • the two refrigerant inlets 22A are provided so as to be dispersed along the longitudinal axis direction of the pressure vessel 21 and to be separated from each other.
  • the refrigerant inlet 22A may be provided at three or more locations.
  • These refrigerant inlets 22 ⁇ / b> A are formed in a short pipe shape that extends horizontally and tangentially from the bottom of the pressure vessel 21, similar to the refrigerant inlet 22 of the first embodiment.
  • the diameter of each refrigerant inlet 22A is made smaller than the diameter of the refrigerant inlet 22 of the first embodiment.
  • the volumetric flow rate flowing into the evaporator 7A is large and the dynamic pressure is high, but the refrigerant distribution holes 26a of the refrigerant distribution plate 26 are made smaller accordingly.
  • the pressure loss is increased by, for example, increasing the speed at which the low-pressure refrigerant is ejected from the refrigerant circulation hole 26a, the heat transfer tube group 25 is vibrated or damaged.
  • two or three or more refrigerant inlets 22A are provided separated along the longitudinal axis direction of the pressure vessel 21, thereby providing a single refrigerant inlet 22 as in the first embodiment.
  • the inflow speed of the low-pressure refrigerant into the pressure vessel 21 can be reduced.
  • coolant distribution board 26 can be enlarged, and the speed at which a low-pressure refrigerant
  • FIG. 6 is a longitudinal sectional view of an evaporator showing a third embodiment of the present invention
  • FIG. 7 is a view taken along arrow VII in FIG.
  • the flow path cross-sectional area from the outer opening 22a of the refrigerant inlet 22 provided at the bottom of the pressure vessel 21 to the pressure vessel 21 increases from the outer opening 22a toward the pressure vessel 21.
  • an expansion channel 22 b is provided between the outer opening 22 a and the pressure vessel 21. Since the other configuration is the same as that of the evaporator 7 of the first embodiment shown in FIG. 3, the same reference numerals are given to the parts having the same configuration and the description thereof is omitted.
  • the extended flow path 22b is formed, for example, in a box shape, and the flow path cross-sectional area is larger than the flow path cross-sectional area of the refrigerant inlet 22.
  • the cross-sectional area of the expansion flow path 22b is set to about 2 to 5 times the cross-sectional area of the refrigerant inlet 22.
  • the shape of the extended flow path 22b is not limited to a box shape, and may be other shapes as long as the flow path cross-sectional area is larger than the outer opening 22a of the refrigerant inlet 22.
  • the expansion channel 22b may be formed in a bulge shape or the like.
  • the refrigerant inlet 22 is formed in a tapered tubular shape whose diameter increases from the outer opening 22a toward the pressure vessel 21 without providing the expansion channel 22b.
  • FIGS. 8A and 8B are longitudinal sectional views of an evaporator showing a fourth embodiment of the present invention.
  • This evaporator 7C is different from the evaporator 7 (refrigerant inlet 22) of the first embodiment in that a flow velocity attenuating member for attenuating the flow velocity of the low-pressure refrigerant is provided in the pipe of the refrigerant inlet 22, and other configurations. Are the same.
  • a porous plate (punching plate or the like) 22c is installed in the pipe of the refrigerant inlet 22, or as shown in FIG. Can be installed in a maze.
  • the flow rate of the low-pressure refrigerant in the pipe of the refrigerant inlet 22 can be attenuated, other than these may be installed as the flow velocity attenuating member.
  • the flow rate of the low-pressure refrigerant flowing into the pressure vessel 21 from the refrigerant inlet 22 is reduced. Therefore, the speed at which the low-pressure refrigerant is ejected from the refrigerant flow hole 26a of the refrigerant distribution plate 26 is reduced to prevent the heat transfer tube group 25 from being vibrated or damaged, and the liquid-phase low-pressure refrigerant is locally ejected. Thus, carry over to the turbo compressor 2 side can be suppressed, and a decrease in efficiency of the turbo compressor 2 can be avoided.
  • the low-pressure refrigerant that is used at a maximum pressure of less than 0.2 MPaG As described above, according to the evaporators 7, 7A, 7B, and 7C according to the present embodiment and the turbo refrigeration apparatus 1 including these evaporators, the low-pressure refrigerant that is used at a maximum pressure of less than 0.2 MPaG.
  • the heat transfer performance is improved by preventing the heat transfer tube group 25 from being dried out in the evaporator, and the liquid phase low-pressure refrigerant is carried over to the turbo compressor 2 side. A decrease in efficiency can be suppressed.
  • the present invention is not limited to the configuration of the above-described embodiment, and can be appropriately changed or improved. Embodiments with such changes and improvements are also included in the scope of the right of the present invention. And for example, the above first to fourth embodiments may be combined.

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Abstract

L'invention concerne un évaporateur capable, dans un turbo-congélateur mettant en œuvre un réfrigérant basse pression utilisé à une pression maximale inférieure à 0,2 MPaG, d'empêcher l'assèchement d'un groupe de tuyaux de transfert thermique dans un évaporateur afin d'augmenter les performances de transfert thermique et supprimer une efficacité réduite due à l'entraînement du réfrigérant basse pression en phase liquide vers un côté du turbo-compresseur, ainsi qu'un turbo-congélateur équipé de cet évaporateur. L'évaporateur (7) comprend un récipient sous pression (21) dans lequel un réfrigérant est introduit et comprimé, un orifice d'entrée de réfrigérant (22) agencé sur une partie inférieure du récipient sous pression, un orifice de sortie de réfrigérant (23) agencé sur une partie supérieure du récipient sous pression, un groupe de tuyaux de transfert thermique (25) qui échangent la chaleur avec le réfrigérant à travers l'intérieur du récipient sous pression et une plaque tabulaire de distribution de réfrigérant (26), installée entre l'orifice d'entrée du réfrigérant et le groupe de tuyaux de transfert thermique, et dans laquelle des trous d'écoulement de réfrigérant sont percés (26a). Le rapport de surface des trous d'écoulement de réfrigérant, par unité de surface sur la plaque de distribution de réfrigérant dans une zone (A1) correspondant à une position proche du côté amont du groupe de tuyaux de transfert de chaleur, est supérieur à celui d'une autre zone (A2).
PCT/JP2016/076068 2015-10-09 2016-09-06 Évaporateur et turbo-congélateur équipé de celui-ci WO2017061211A1 (fr)

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US15/736,130 US20180187932A1 (en) 2015-10-09 2016-09-06 Evaporator and centrifugal chiller provided with the same

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