EP4227608A1 - Dispositif d'évaporation et son procédé de commande, et cabine d'affichage réfrigérée - Google Patents

Dispositif d'évaporation et son procédé de commande, et cabine d'affichage réfrigérée Download PDF

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Publication number
EP4227608A1
EP4227608A1 EP21879256.2A EP21879256A EP4227608A1 EP 4227608 A1 EP4227608 A1 EP 4227608A1 EP 21879256 A EP21879256 A EP 21879256A EP 4227608 A1 EP4227608 A1 EP 4227608A1
Authority
EP
European Patent Office
Prior art keywords
heat exchange
channel sections
evaporator
area
channel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP21879256.2A
Other languages
German (de)
English (en)
Other versions
EP4227608A4 (fr
Inventor
Zhiqiang MIAO
Qingyiming SUN
Fuliang LI
Mingguo WU
Huanhao GUAN
Chen Zhang
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Publication of EP4227608A1 publication Critical patent/EP4227608A1/fr
Publication of EP4227608A4 publication Critical patent/EP4227608A4/fr
Pending legal-status Critical Current

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Classifications

    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47F—SPECIAL FURNITURE, FITTINGS, OR ACCESSORIES FOR SHOPS, STOREHOUSES, BARS, RESTAURANTS OR THE LIKE; PAYING COUNTERS
    • A47F3/00—Show cases or show cabinets
    • A47F3/04—Show cases or show cabinets air-conditioned, refrigerated
    • A47F3/0439—Cases or cabinets of the open type
    • A47F3/0443—Cases or cabinets of the open type with forced air circulation
    • A47F3/0447—Cases or cabinets of the open type with forced air circulation with air curtains
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/042—Air treating means within refrigerated spaces
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/04—Preventing the formation of frost or condensate
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D25/00—Charging, supporting, and discharging the articles to be cooled
    • F25D25/02—Charging, supporting, and discharging the articles to be cooled by shelves
    • 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
    • F28D1/0477—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 being bent in a serpentine or zig-zag
    • 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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/006—Preventing deposits of ice
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/02—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using coatings, e.g. vitreous or enamel coatings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/04—Treating air flowing to refrigeration compartments
    • F25D2317/041—Treating air flowing to refrigeration compartments by purification
    • F25D2317/0411—Treating air flowing to refrigeration compartments by purification by dehumidification
    • 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
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/04—Arrangements of conduits common to different heat exchange sections, the conduits having channels for different circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/08—Assemblies of conduits having different features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2245/00—Coatings; Surface treatments
    • F28F2245/04—Coatings; Surface treatments hydrophobic

Definitions

  • the present disclosure relates to the technical field of refrigeration equipment, and particularly relates to an evaporator, a control method thereof, and a refrigeration display cabinet.
  • a refrigeration display cabinet is a cabinet with refrigeration for display of food, medicine, or the like, and is widely used in large stores, supermarkets, etc.
  • the air-curtain type refrigeration display cabinet has an open structure, due to which hot air in environment can easily enter the cabinet and form frost on the evaporator, so that the heat and flow resistances of the outer surface of the evaporator become larger, and finally the power consumption caused by frequent defrosting is increased.
  • Various methods are being sought in the industry to reduce the frost, but none of them can well alleviate the frost formation for the evaporator.
  • Embodiments of the present disclosure provide an evaporator, a control method thereof, and a refrigeration display cabinet in order to well alleviate the frost formation for the evaporator.
  • an evaporator which includes:
  • the heat exchange body further includes an enhanced cooling area located downstream of the anti-frost cooling area in the first direction; and a number density of the first channel sections in the anti-frost cooling area is less than a number density of the first channel sections in the enhanced cooling area.
  • the heat exchange body further includes an enhanced cooling area located downstream of the anti-frost cooling area in the first direction; and a number density of the first channel sections in the anti-frost cooling area is less than a number density of the first channel sections in the enhanced cooling area.
  • a distance in the first direction between adjacent first channel sections in the anti-frost cooling area is greater than a distance in the first direction between adjacent first channel sections in the dehumidification area.
  • the heat exchange body further includes an enhanced cooling area located downstream of the anti-frost cooling area in the first direction; and a distance in the first direction between adjacent first channel sections in the anti-frost cooling area is greater than a distance in the first direction between adjacent first channel sections in the enhanced cooling area.
  • the evaporator includes:
  • the heat exchange body further includes an enhanced cooling area located downstream of the anti-frost cooling area in the airflow direction; and a distance in the first direction between adjacent first channel sections in the anti-frost cooling area is greater than a distance in the first direction between adjacent first channel sections in the enhanced cooling area.
  • the number of the first channel sections in the anti-frost cooling area is greater than the number of the first channel sections in the dehumidification area; and/or the number of the first channel sections in the dehumidification area is greater than the number of the first channel sections in the enhanced cooling area.
  • the heat exchange body includes:
  • the heat exchange channel includes a plurality of the heat exchange channels arranged along a third direction, the plurality of the heat exchange channels each include a first end and a second end arranged along the first direction, the first end is configured for inflow of the refrigerant, the second end is configured for outflow of the refrigerant, and the third direction is perpendicular to the first direction and the second direction; and the plurality of the heat exchange channels at least include a pair of adjacent and crossed heat exchange channels, at the same side ends of the first channel sections, the second channel sections of the two crossed heat exchange channels are crossed with each other.
  • At least one side of the heat exchange body along the third direction is provided with the two crossed heat exchange channels.
  • an upwind surface of the heat exchange body includes a surface of the dehumidification area perpendicular to a third direction and facing inflow of air, and a surface of the dehumidification area perpendicular to the first direction, wherein the third direction is perpendicular to the first direction and the second direction.
  • a surface of the heat exchange body is coated with a hydrophobic coating.
  • the evaporator further includes:
  • the evaporator further includes:
  • the heat exchange tube has a diameter in a range of 6 mm to 13 mm.
  • a refrigeration display cabinet which includes the evaporator in the above embodiments.
  • the refrigeration display cabinet further includes:
  • the refrigeration display cabinet further includes:
  • a control method of the evaporator which includes:
  • control method when there is a need to adjust the opening degree of the throttling element, the control method further includes:
  • the airflow flows along the evaporator and in the first direction perpendicular to the first channel section, and thus different cooling effects will occur sequentially in different areas when the airflow passing through the evaporator.
  • this area is not easy to frost, but the humidity of the air is high.
  • the dehumidification area the dehumidification effect can be optimized.
  • some water vapor is still present in the airflow, and frost is easily formed during further cooling.
  • the amount of frost can be reduced to alleviate the frost formation.
  • the element when an element is referred to as being “on” another element, the element can be directly arranged on the other element, or can be indirectly arranged on the other element via one or more intermediate elements inserted therebetween.
  • the element when an element is referred to as being “connected” to another element, the element can be directly connected to the other element, or can be indirectly connected to the other element via one or more intermediate elements inserted therebetween.
  • the same reference sign represents the same element.
  • the present disclosure includes terms indicating directions or position relationships, such as “upper”, “lower”, “top”, “bottom”, “front”, “rear”, “inner”, “outer” and the like. These terms are only for facilitating the description of the present disclosure, rather than indicating or implying that the referred devices must have specific orientations or be constructed and operated in the specific orientations, and therefore, cannot be interpreted as limitations to the protection scope of the present disclosure.
  • the present disclosure provides an evaporator 10 for refrigeration.
  • the evaporator 10 includes a heat exchange body 1.
  • the heat exchange body 1 includes a dehumidification area A and an anti-frost cooling area B sequentially arranged along a first direction.
  • the dehumidification area A is located at an air inflow side in the first direction.
  • the heat exchange body 1 includes a heat exchange channel for refrigerant to flow.
  • the heat exchange channel includes a plurality of first channel sections and a plurality of second channel sections. The plurality of first channel sections are arranged at intervals along the first direction, and extend along a second direction perpendicular to the first direction.
  • the same side ends of adjacent first channel sections in the heat exchange channel are in communication with each other through the second channel sections.
  • the number density of the first channel sections in the anti-frost cooling area B is less than the number density of the first channel sections in the dehumidification area A.
  • the heat exchange body 1 further includes an enhanced cooling area C located downstream of the anti-frost cooling area B in the first direction.
  • the number density of the first channel sections in the anti-frost cooling area B is less than the number density of the first channel sections in the enhanced cooling area C.
  • the evaporator 10 includes the heat exchange body 1.
  • the heat exchange body 1 includes the dehumidification area A and the anti-frost cooling area B sequentially arranged along an airflow direction.
  • the dehumidification area A is located at the air inflow side, and the anti-frost cooling area B is located downstream of the dehumidification area A.
  • the heat exchange body 1 includes the heat exchange channel for refrigerant to flow.
  • the heat exchange channel includes an inlet 23 and an outlet 24.
  • the inlet 23 is provided for inflow of liquid refrigerant
  • the outlet 24 is provided for outflow of gaseous refrigerant.
  • the heat exchange body 1 includes the heat exchange channel for refrigerant to flow.
  • the heat exchange channel includes the plurality of first channel sections and the plurality of second channel sections.
  • the plurality of first channel sections are arranged at intervals along the first direction X, and extend along the second direction Y perpendicular to the first direction X.
  • the first direction X is parallel to the airflow direction.
  • the same side ends of adjacent first channel sections in the heat exchange channel are in communication with each other through a second channel section.
  • the first channel sections may be straight sections
  • the second channel sections may be in U-shape, arc-shape or other curved shape.
  • the heat exchange body 1 includes a base 1' and a heat exchange tube 2 mounted on the base 1'.
  • the heat exchange channel is defined inside the heat exchange tube 2.
  • the heat exchange tube 2 includes a plurality of first tube sections 21 and a plurality of second tube sections 22.
  • the first channel sections are defined inside the first tube sections 21, and the second channel sections are defined inside the second tube sections 22.
  • the heat exchange tube 2 includes the plurality of first tube sections 21 and the plurality of second tube sections 22.
  • the plurality of first tube sections 21 are arranged at intervals along the first direction X parallel to the airflow direction, and extend along the second direction Y perpendicular to the first direction X.
  • the same side ends of adjacent first tube sections 21 corresponding to the same heat exchange channel are in communication with each other through a second tube section 22.
  • the heat exchange channel can be directly defined by the heat exchange body 1.
  • the distance in the first direction X between adjacent first channel sections in the anti-frost cooling area B is greater than the distance in the first direction X between adjacent first channel sections in the dehumidification area A.
  • the airflow passes through the dehumidification area A for evaporation heat exchange, some water vapor is still present in the airflow, and the temperature of the airflow is reduced.
  • the airflow passes through the anti-frost cooling area B for further cooling, the water vapor in the airflow tends to condense on the surface of the heat exchange body 1 to form frost.
  • the frost amount can be reduced to alleviate the frost formation.
  • the airflow is further dehumidified by passing through the anti-frost cooling area B.
  • the present embodiment can ensure heat exchange and dehumidification effects while alleviate the frost formation for the evaporator 10, thereby improving the overall performance of the evaporator 10.
  • the heat exchange body 1 further includes the enhanced cooling area C located downstream of the anti-frost cooling area B in the airflow direction.
  • the enhanced cooling area C is located at an air outflow side.
  • the distance in the first direction X between adjacent first channel sections in the anti-frost cooling area B is greater than the distance in the first direction X between adjacent first channel sections in the enhanced cooling area C.
  • the content of the water vapor in the airflow is greatly reduced.
  • frost is not easy to be formed on the heat exchange body 1. Therefore, by reducing the distance between adjacent first channel sections in the enhanced cooling area C, the overall heat exchange amount of the evaporator 10 can be ensured to achieve.
  • the arrangement of the first channel sections in the anti-frost cooling area B is relatively sparse in the airflow direction, while the arrangement of the first channel sections in the dehumidification area A and the enhanced cooling area C is relatively dense in the airflow direction. Therefore, the effects of heat exchange and dehumidification are ensured while the frost formation of the evaporator 10 is alleviated, and thus the overall performance of the evaporator 10 is improved.
  • the number of the first channel sections in the anti-frost cooling area B is greater than the number of the first channel sections in the dehumidification area A.
  • the number of the first channel sections in the dehumidification area A is 3 to 5
  • the number of the first channel sections in the anti-frost cooling area B is 6 to 8.
  • the number of the first channel sections in the dehumidification area A is greater than the number of the first channel sections in the enhanced cooling area C.
  • the number of the first channel sections in the enhanced cooling area C is about 2.
  • the number of the first channel sections in the dehumidification area A is the number of the first channel sections without frost. Since the ambient temperature is relatively high, at the beginning of the airflow passing through the heat exchange body 1, due to the high temperature of the airflow, frost is not easy to be formed even though the humidity of the airflow is at the maximum. However, as the airflow is gradually cooled, frost is easy to be formed because the temperature of the airflow decreases. Therefore, the number of the first channel sections in the dehumidification area A can be determined according to a critical position between the frost area and the no-frost area in the heat exchange body 1. As such, the first channel sections can be densely arranged to ensure the dehumidification effect and to prevent the dehumidification area A from frosting as well.
  • the number of the first channel sections in the anti-frost cooling area B is configured such that the dehumidification area A and the anti-frost cooling area B together remove a predetermined percentage of moisture in an airflow and to achieve a predetermined heat exchange amount.
  • the anti-frost cooling area B is a heat exchange main area, which can realize the main evaporation heat exchange while remove most of the water vapor in the airflow, thereby ensuring the dehumidification effect and preventing frost formation when the airflow passing through the enhanced cooling area C.
  • the number of the first channel sections in the enhanced cooling area C is configured such that the overall heat exchange amount of the heat exchange body 1 meets a requirement. Since the distancebetween the first channel sections is relatively large in the anti-frost cooling area B, the heat exchange performance will be compromised though the frost formation can be reduced. The heat exchange performance can be further enhanced by the densely arranged first channel sections in the enhanced cooling area C, thereby satisfying the overall heat exchange requirement of the heat exchange body 1.
  • a plurality of the heat exchange channels are arranged along a third direction Z (i.e., the thickness direction of the heat exchange body 1).
  • the plurality of the heat exchange channels each include a first end and a second end arranged along the first direction X.
  • the first end is configured for inflow of refrigerant
  • the second end is configured for outflow of the refrigerant.
  • the third direction Z is perpendicular to the first direction X and the second direction Y
  • the plurality of the heat exchange channels at least include a pair of adjacent and crossed heat exchange channels. At the same side ends of the first channel sections, the second channel sections of the two crossed heat exchange channels are crossed with each other. As shown on the left of FIG.
  • the second channel sections of the two crossed heat exchange channels, located at one end of the first channel sections, are crossed with each other.
  • the second channel sections of the crossed heat exchange channels, located at the other end of the first channel sections are parallel with each other.
  • the evaporator 10 is disposed in an air pathway.
  • the wind speed in the width direction of the air pathway i.e., the third direction Z
  • the temperature of a local position of the heat exchange body 1 may be over low, resulting in serious frost formation.
  • the crossed heat exchange channels it is possible to improve the uniformity of heat exchange and prevent local frosting due to a local low temperature.
  • At least one side of the heat exchange body 1 along the third direction Z is provided with the two crossed heat exchange channels.
  • edge areas on both sides of the heat exchange body 1 along the third direction are each provided with a pair of crossed heat exchange channels.
  • additional crossed heat exchange channels can be added as desired.
  • the evaporator 10 is disposed in the air pathway, e.g., in the air pathway of a refrigeration display cabinet. Due to the Coanda effect of the airflow in the air pathway, the airflow would flow on the wall of the air pathway at a high speed. Moreover, since the evaporator 10 is sandwiched and fixed between two plates and a gap is formed between the plates and the heat exchange body 1, the flow resistance is small and the speed of the airflow is high. As shown in FIG. 3 , the airflow speeds Q1 and Q3 located on both sides along the third direction Z are greater than the airflow speed Q2 in the middle, which would cause the local temperature of the heat exchange body 1 to be too low, resulting in serious frost formation. By using the crossed heat exchange channels, it is possible to improve the uniformity of heat exchange and prevent local frosting due to a local low temperature.
  • the heat exchange body 1 includes four heat exchange tubes 2, including, from left to right, a first heat exchange tube 2A, a second heat exchange tube 2B, a third heat exchange tube 2C, and a fourth heat exchange tube 2D.
  • the first heat exchange tube 2A and the second heat exchange tube 2B cross each other, and the third heat exchange tube 2C and the fourth heat exchange tube 2D cross each other.
  • an upwind surface S of the heat exchange body 1 includes a surface of the dehumidification area A perpendicular to the third direction Z and facing the inflow of air and a surface of the dehumidification area A perpendicular to the first direction X, wherein the third direction Z is perpendicular to the first direction X and the second direction Y
  • both the bottom surface and the side surface of the dehumidification area A of the heat exchange body 1 are exposed in the inflow of air, so that the area of the upwind surface of the heat exchange body 1 can be increased.
  • the upwind surface is not easy to frost.
  • the first channel sections in the dehumidification area A can be densely arranged to optimize the dehumidification effect while no-frost can be ensured.
  • a surface of the heat exchange body 1 is coated with a hydrophobic coating.
  • fins can be disposed on the heat exchange tube 2, and the hydrophobic coating can be applied to the surface of the heat exchange tube 2 and the surface of the fins.
  • frost formation can be more effectively suppressed by applying the hydrophobic coating in combination with the varied distances.
  • the hydrophobic coating can increase the contact angle between the condensed water and the surface of the heat exchange body 1, allowing the water vapor in the airflow to condense into a sphere on the surface of the fin in the evaporation and refrigeration.
  • the water sphere has a small contact area with the heat exchange body 1, and thus is not easy to freeze.
  • a degree of supercooling can be achieved such that the fin is at a predetermined temperature (e.g., -2°C) when the condensed water freezes, thereby the supercooling degree of frosting is increased and the frosting temperature is reduced.
  • the diameter of the heat exchange tube 2 ranges from 6 mm to 13 mm, for example, is 6 mm, 6.5 mm, 7 mm, 7.5mm, 8 mm, 8.5 mm, 9 mm, 9.5 mm, 10 mm, 10.5 mm, 11 mm, 11.5 mm, 12 mm, 12.5 mm, or 13 mm.
  • the diameter of the heat exchange tube 2 is 9.52 mm.
  • the heat exchange tubes may be equal distanced, and the heat exchange tube 2 is easy to frost when the diameter of the tube is small.
  • frost formation can be effectively suppressed by using the heat exchange tube with the varied distances, exposing the dehumidification area A to the inflow of air, and applying a hydrophobic coating.
  • the diameter of the heat exchange tube 2 can be reduced, the thickness of the evaporator 10 can be reduced, and the occupation of space of the air pathway can be reduced.
  • a double-layer double-temperature air curtain can be provided to effectively block the entry of ambient heat and water vapor.
  • the evaporator 10 of the present disclosure further includes a liquid supply tube 4, an gas outlet tube 5, and a first temperature detecting member 3.
  • the liquid supply tube 4 and the gas outlet tube 5 are respectively in communication with an inlet 23 and an outlet 24 at two ends of the heat exchange channel.
  • the liquid supply tube 4 is provided with a throttling element 8, such as an electronic expansion valve or a capillary tube.
  • the first temperature detecting member 3 which can be a temperature sensor, is disposed in the dehumidification area A of the heat exchange body 1 and configured to detect the temperature of the dehumidification area A of the heat exchange body 1.
  • the opening degree of the throttling element 8 increases on a condition that a detected value of the first temperature detecting member 3 exceeds a predetermined temperature value (of the dehumidification area A), and decreases on a condition that the detected value of the first temperature detecting member 3 does not exceed the predetermined temperature value.
  • the opening degree of the throttling element 8 can be automatically adjusted by a controller.
  • the temperature of the dehumidification area A can be detected, and the opening degree of the throttling element 8 can be adjusted in time according to the temperature of the dehumidification area A to change a superheat degree, thereby ensuring that the dehumidification area A does not frost and controlling the dehumidification area and the dehumidification temperature.
  • the evaporator 10 further includes a second temperature detecting member 6 and a third temperature detecting member 7.
  • the second temperature detecting member 6 is disposed on the liquid supply tube 4 and configured to detect a temperature of the liquid supply tube 4.
  • the third temperature detecting member 7 is disposed on the gas outlet tube 5 and configured to detect a temperature of the gas outlet tube 5.
  • the opening degree of the throttling element 8 is determined according to a difference between detected values of the third temperature detecting member 7 and the second temperature detecting member 6, and the opening degree of the throttling element 8 is positively correlated with the difference between the detected values.
  • an adjustment amount of the throttling element 8 can be further determined quantitatively based on the temperature difference between the third temperature detecting member 7 and the second temperature detecting member 6, so that a heat exchange effect can be ensured while a superior frost suppressing effect is achieved.
  • the evaporator 10 is used in a refrigeration display cabinet.
  • the temperature sensor on the liquid supply tube 4 By respectively arranging the temperature sensor on the liquid supply tube 4 to detect the liquid temperature and arranging the temperature sensor on the gas outlet tube 5 to detect the gas temperature, the temperature of the tube is detected in real time.
  • the number of steps that the electronic expansion valve takes can be adjusted based on the temperature difference between the gas outlet tube 5 and the liquid supply tube 4 in order to control the superheat degree of the evaporator 10.
  • the controller controls the opening degree of the electronic expansion valve to be increased, so as to reduce the superheat degree; and on a condition that this temperature is less than -2°C, the controller controls the opening degree of the electronic expansion valve to be reduced, so as to increase the superheat degree. Accordingly, it is possible to maintain a certain superheat degree of the evaporator such that the tube temperature of the dehumidification area A at the bottom of the evaporator is higher than or equal to -2°C, and thus this area can fulfil the dehumidifying function without frost formation.
  • the present disclosure also provides a refrigeration display cabinet, which includes the evaporator 10 in the above-described embodiments.
  • the refrigeration display cabinet can be a vertical display cabinet.
  • the evaporator 10 of the present disclosure Due to the open structure of the refrigeration display cabinet, hot air in the environment can easily enter the cabinet to frost the evaporator 10.
  • a superior frost suppressing effect can be achieved, and the frost formation on the surface of the heat exchange body 1 can be greatly reduced, thereby preventing increase of the heat and flow resistances of the surface of the heat exchange body 1, so as to improve the heat exchange effect, reduce the power consumption of the display cabinet, and stabilize the cabinet temperature.
  • the refrigeration display cabinet further includes a cabinet body 20 and a fan 70.
  • a first air pathway 30 and a second air pathway 40 are defined in the cabinet body 20.
  • the first air pathway 30 extends along a front-and-rear direction of the cabinet body 20 and is provided at a lower portion of the cabinet body 20.
  • the second air pathway 40 extends along an up-and-down direction of the cabinet body 20 and is provided at a rear portion of the cabinet body 20.
  • a lower portion of the second air pathway 40 is in communication with a rear portion of the first air pathway 30.
  • the fan 70 is disposed in the first air pathway 30 and configured to deliver cold air to the first air pathway 30. The cold air sequentially passes through the first air pathway 30 and the second air pathway 40 and forms a cold air curtain in the front surface of the cabinet body 20.
  • the evaporator 10 is disposed in a lower region of the second air pathway 40, and the first direction X coincides with the up-and-down direction. Accordingly, the air driven by the fan 70 will flow along the second air pathway 40 and pass through the evaporator 10 from the smallest side surface of the evaporator 10 so as to undergo different cooling effects during the airflow flowing through the evaporator 10.
  • a third air pathway 50 is also defined in the cabinet body 20, extends along the front-and-rear direction of the cabinet body 20, and is provided at a top portion of the cabinet body 20.
  • a rear portion of the third air pathway 50 is in communication with a top portion of the second air pathway 40. Accordingly, the airflow driven by the fan 70 can sequentially flow along the first air pathway 30, the second air pathway 40, and the third air pathway 50, and finally a first air curtain from top to bottom is formed in the front of the display cabinet.
  • a flow guide mechanism is located at an upper portion of the cabinet body 20.
  • a flow guide channel 60 is defined in the flow guide mechanism.
  • a flow guide outlet of the flow guide channel 60 is located in front of the outlet of the cold air.
  • External ambient air is supplied to the flow guide mechanism by another fan, and is blown out from the flow guide outlet, so that a second air curtain can be formed in front of the first air curtain.
  • the temperature of the second air curtain is higher than that of the first air curtain.
  • the evaporator 10 is disposed in the lower region of the second air pathway 40, the first direction X coincides with the up-and-down direction, and the third direction Z coincides with the front-and-rear direction.
  • the dehumidification area A is located at a lower side
  • the enhanced cooling area C is located at an upper side
  • the anti-frost cooling area B is located between the dehumidification area A and the enhanced cooling area C.
  • the evaporator 10 is vertically arranged, so that different cooling effects can be sequentially obtained when the airflow flows from the bottom to the top in the second air pathway 40.
  • the first tube sections 21 can be densely arranged, e.g., at a distance of 25.4 mm ⁇ 22 mm, to optimize the dehumidification effect.
  • the temperature and humidity of the airflow in the anti-frost cooling area B are lower than those of the airflow in the dehumidification area A, and higher than those of the airflow in the enhanced cooling area C.
  • the first tube sections 21 are sparsely arranged, e.g., at a distance of 50.8 mm ⁇ 22 mm to reduce the frost formation.
  • the surface temperature of the fins is increased, surface area with frost is reduced, and thus the anti-frost ability of the evaporator in this area is enhanced, thereby avoiding frost blocking induced by the frost formation.
  • the first tube sections 21 can be densely arranged so as to enhance heat exchange and ensure the overall heat exchange requirements of the evaporator 10.
  • the refrigeration display cabinet of the present disclosure further includes a baffle plate 80 disposed between the first air pathway 30 and the second air pathway 40.
  • the baffle plate 80 can be horizontally disposed in front of the evaporator 10.
  • the dehumidification area A is located below the baffle plate 80.
  • the anti-frost cooling area B and the enhanced cooling area C are located above the baffle plate 80.
  • the upwind surface S of the heat exchange body 1 includes a surface of the dehumidification area A directly facing the inflow of air and a bottom surface of the dehumidification area A.
  • the dehumidification area A of the heat exchange body 1 is exposed from the baffle plate 80.
  • the dehumidification area A can be exposed in the inflow of air, that is, both the bottom surface and the front side surface of the dehumidification area A are exposed in the inflow of air, so that the upwind surface area of the heat exchange body 1 can be increased.
  • the upwind surface is not easy to frost.
  • the first channel sections in the dehumidification area A can be densely arranged to optimize the dehumidification effect while no-frost can be ensured.
  • the evaporator adopting equal-distanced heat exchange tube is compared with the evaporator adopting varied distancedheat exchange tube of the present disclosure, and comparison of the refrigeration display cabinets is as follows: Table 1: Comparison of an evaporator adopting equal-distanced heat exchange tube with an evaporator adopting varied distanced heat exchange tube Evaporator type Conventional evaporator Evaporator of the present disclosure Average cabinet temperature before cabinet temperature imbalance occurs 7.1°C 3.6°C Refrigeration time until the cabinet temperature is imbalanced and rises 0.4°C 45 min 88 min
  • the present disclosure also provides a control method based on the evaporator 10 of the above embodiments.
  • the method includes:
  • the opening degree of the throttling element 8 can be adjusted in time according to the temperature of the dehumidification area A to change a superheat degree, thereby ensuring that the dehumidification area A does not frost and controlling the dehumidification area and the dehumidification temperature.
  • control method when there is a need to adjust the opening degree of the throttling element 8, the control method further includes:
  • an adjustment amount of the throttling element 8 can be further determined quantitatively based on the temperature difference between the third temperature detecting member 7 and the second temperature detecting member 6, so that a heat exchange effect can be ensured while an advantageous frost suppressing effect is achieved.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Freezers Or Refrigerated Showcases (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
EP21879256.2A 2020-10-12 2021-09-29 Dispositif d'évaporation et son procédé de commande, et cabine d'affichage réfrigérée Pending EP4227608A4 (fr)

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CN202011084822.4A CN112113379A (zh) 2020-10-12 2020-10-12 蒸发装置及其控制方法、制冷陈列柜
PCT/CN2021/121517 WO2022078210A1 (fr) 2020-10-12 2021-09-29 Dispositif d'évaporation et son procédé de commande, et cabine d'affichage réfrigérée

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CN112113379A (zh) * 2020-10-12 2020-12-22 珠海格力电器股份有限公司 蒸发装置及其控制方法、制冷陈列柜

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CN213119670U (zh) * 2020-10-12 2021-05-04 珠海格力电器股份有限公司 蒸发装置及制冷陈列柜

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JP2023538726A (ja) 2023-09-11
KR20230035103A (ko) 2023-03-10
WO2022078210A1 (fr) 2022-04-21
JP7556127B2 (ja) 2024-09-25
CN112113379A (zh) 2020-12-22
EP4227608A4 (fr) 2024-06-05

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