EP1780492B1 - Refrigeration unit - Google Patents

Refrigeration unit Download PDF

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Publication number
EP1780492B1
EP1780492B1 EP05767439A EP05767439A EP1780492B1 EP 1780492 B1 EP1780492 B1 EP 1780492B1 EP 05767439 A EP05767439 A EP 05767439A EP 05767439 A EP05767439 A EP 05767439A EP 1780492 B1 EP1780492 B1 EP 1780492B1
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EP
European Patent Office
Prior art keywords
heat exchanger
outdoor heat
drain pan
plate fins
high temperature
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.)
Active
Application number
EP05767439A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1780492A4 (en
EP1780492A1 (en
Inventor
Toshimitsu DAIKIN INDUSTRIES LTD. KAMADA
Shun Daikin Industries Ltd. YOSHIOKA
Haruo Daikin Industries Ltd. NAKATA
Shinichirou Daikin Industries Ltd. KOBAYASHI
Teruo DAIKIN INDUSTRIES LTD. KIDO
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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Filing date
Publication date
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Publication of EP1780492A1 publication Critical patent/EP1780492A1/en
Publication of EP1780492A4 publication Critical patent/EP1780492A4/en
Application granted granted Critical
Publication of EP1780492B1 publication Critical patent/EP1780492B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/36—Drip trays for outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F24F1/18—Heat exchangers specially adapted for separate outdoor units characterised by their shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/22—Means for preventing condensation or evacuating 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
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/04—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by preventing the formation of continuous films of condensate on heat-exchange surfaces, e.g. by promoting droplet formation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from 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
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers

Definitions

  • the present invention relates to a refrigeration apparatus formed by a heat exchanger that has a heat exchanging surface.
  • frost In a refrigeration apparatus in which a heat exchanger is operated as an evaporator, frost usually forms on a heat exchanging surface of the heat exchanger when the temperature of air with which the heat exchanger exchanges heat is low or when the evaporation temperature of the evaporator is low.
  • the frost formation lowers the heat exchanging capability of the heat exchanger, and consequently lowers the refrigeration capability of the refrigeration apparatus.
  • the evaporation temperature of an outdoor heat exchanger operating as an evaporator decreases when the outdoor air temperature decreases during operation.
  • frost forms on the outdoor heat exchanger.
  • the frost formation lowers the evaporation capability of the outdoor heat exchanger, and consequently lowers the heating capability of the air conditioner.
  • the air conditioner performs a defrosting operation when necessary to remove frost from the outdoor heat exchanger.
  • the defrosting operation may suspend the heating operation of the air conditioner or lower the heating capability of the air conditioner depending on the type of defrosting operation. This may lower the heating comfort of the air conditioner.
  • the refrigeration operation particularly, the heating operation for the heat pump type air conditioner which is a typical refrigeration apparatus
  • JP-A-2002-323298 describes one example of a method for applying a frost formation prevention layer.
  • a coating film is formed by applying a composition containing 3 to 70 part by weight of a specific organo polysiloxane having a silanol group to 100 part by weight of specific organo polysiloxane to a heat exchanging surface and hardening the applied composition.
  • the frost formation prevention layer increases the water slippage and the water repellency of the heat exchanging surface.
  • the heat exchanger operates as an evaporator in this state, water droplets that have condensed quickly run down on the heat exchanging surface. As a result, the amount of frost formation on the heat exchanging surface is reduced.
  • Fig. 15 is a cross-sectional view schematically showing the structure of a heat exchanger.
  • a heat exchanger 42 which is the so-called cross fin and tube heat exchanger, includes many plate fins 43 and a heat exchanger pipe 45.
  • the plate fins 43 form a heat exchanging surface, and are arranged in parallel at intervals in a direction perpendicular to an air circulation direction 44.
  • Each plate fin 43 which is arranged in a manner that its longitudinal direction coincides with the vertical direction, forms a fin line. In Fig. 15 , two fin lines are formed in the circulation direction 44.
  • the heat exchanger pipe 45 is conventionally arranged to meander and extend through the plate fins 43.
  • a refrigerant circulates inside the heat exchanger pipe 45.
  • the heat exchanger pipe 45 has a plurality of portions that extend in a direction perpendicular to the air circulation direction 44. These portions of the heat exchanger pipe 45 are arranged at regular intervals in the longitudinal direction of the plate fins 43 between lower ends and upper ends of the plate fins 43.
  • a frost formation prevention layer which is for example the layer described above, is applied to the surface of the plate fins 43 to increase the water slippage and the water repellency of the plate fins 43.
  • a drain pan 46 for receiving water droplets that drip from the heat exchanger 42 and discharging the water droplets is arranged below the heat exchanger 42.
  • An upper surface 46a of the drain pan 46 is inclined to discharge water.
  • the heat exchanger 42 is arranged substantially horizontally relative to the drain pan 46 of which the upper surface 46a is inclined so that a lower end of the heat exchanger 42, or specifically the lower ends of the plate fins 43, partially comes into contact with the upper surface 46a of the drain pan 46.
  • a refrigeration unit having the features defined in the preamble of claim 1 is known from JP-A-54-030137 . Similar refrigeration units are disclosed by JP-A-02-501931 or WO-A-03/004947 .
  • the present invention provides a refrigeration apparatus that reduces the amount of frost that forms when a heat exchanger is operated as an evaporator.
  • the present invention provides a refrigeration apparatus having the features of claim 1.
  • a heat pump type air conditioner which is one type of refrigeration apparatus, according to a first embodiment will now be described with reference to the drawings.
  • Fig. 1 is a cross-sectional view showing a portion of an outdoor heat exchanger 2 used in an air conditioner 1 according to a first embodiment.
  • Fig. 2 is a circuit diagram showing a refrigerant circuit of the air conditioner 1.
  • the outdoor heat exchanger 2, an expansion valve 9, an indoor heat exchanger 10, a four-way switch valve 11, and a compressor 12 are connected by a refrigerant pipe to form a refrigerant circuit as shown in Fig. 2 .
  • the four-way switch valve 11 is set as indicated by solid lines in Fig. 2 .
  • a refrigerant serving as a heating medium discharged from the compressor 12 circulates in the order of the four-way switch valve 11, the outdoor heat exchanger 2, the expansion valve 9, the indoor heat exchanger 10, and the four-way switch valve 11, and is sucked into the compressor 12.
  • the outdoor heat exchanger 2 operates as a condenser and the indoor heat exchanger 10 operates as an evaporator.
  • a gasified refrigerant exchanges heat with the outdoor air and becomes a liquefied refrigerant so that the refrigerant releases heat into the outdoor air.
  • a liquefied refrigerant exchanges heat with the indoor air and evaporates to become a gasified refrigerant. As a result, the refrigerant absorbs heat from the indoor air and cools the indoor air.
  • the four-way switch valve 11 is set as indicated by broken lines as shown in Fig. 2 .
  • the refrigerant discharged from the compressor 12 circulates in the order of the four-way switch valve 11, the indoor heat exchanger 10, the expansion valve 9, the outdoor heat exchanger 2, and the four-way switch valve 11, and is then drawn into the compressor 12.
  • the indoor heat exchanger 10 operates as a condenser and the outdoor heat exchanger 2 operates as an evaporator.
  • a gasified refrigerant exchanges heat with the indoor air and condenses, so that the indoor air is heated by heat released from the refrigerant.
  • a liquefied refrigerant exchanges heat with the outdoor air and evaporates to become a gasified refrigerant. As a result, the refrigerant absorbs heat from the outdoor air.
  • the outdoor heat exchanger 2 which is a so-called cross fin and tube heat exchanger, includes many plate fins 3 and a single heat exchanger pipe 5.
  • the plate fins 3 form a heat exchanging surface and are arranged in parallel at intervals in a direction perpendicular to an air circulation direction 4.
  • the heat exchanger pipe 5 is formed to meander and extend through the plate fins 3.
  • a refrigerant circulates inside the heat exchanger pipe 5.
  • each plate fin 3 which is arranged in a manner such that its longitudinal direction coincides with the vertical direction, forms a fin line. Although two fin lines are formed in the circulation direction 4 in Fig. 1 , one fin line or three or more fin lines may be formed.
  • the heat exchanger pipe 5 has a plurality of portions that extend in the direction perpendicular to the air circulation direction 4. The portions of the heat exchanger pipe 5 are arranged at regular intervals in the longitudinal direction of the plate fins 3 between lower ends and upper ends of the plate fins 3. A coating film having water slippage and water repellency is applied to the surface of the plate fins 3 so that the surface of the plate fins 3 has high water slippage and high water repellency. Examples of the plate fins 3 include all plate-like fins, such as flat fins, slit fins, and waffle fins.
  • a drain pan 6 for receiving water droplets that drip from the outdoor heat exchanger 2 and discharging the water droplets is arranged below the outdoor heat exchanger 2.
  • An upper surface 6a of the drain pan 6 is inclined to discharge water that drips from the outdoor heat exchanger 2.
  • the outdoor heat exchanger 2 is arranged substantially horizontally to the drain pan 6 of which upper surface 6a is inclined.
  • space is formed between the entire lower end of the outdoor heat exchanger 2, or more specifically, lower ends 3a of the plate fins 3, and the upper surface 6a of the drain pan 6.
  • water droplets 8, which condense when the outdoor heat exchanger 2 operates as an evaporator run down the surface of the plate fins 3 and drip from the lower ends 3a of the plate fins 3 onto the upper surface 6a of the drain pan 6.
  • the outdoor heat exchanger 2 and the drain pan 6 have no contacting portions.
  • the water droplets 8 that have run down do not accumulate at portions of contact between the outdoor heat exchanger 2 and the drain pan 6. This prevents frost from forming from water droplets and growing upward from the lower ends 3a of the plate fins 3.
  • the first embodiment has the advantages described below.
  • the first embodiment may be modified in the following form.
  • a space is formed entirely between the outdoor heat exchanger 2 and the drain pan 6.
  • air may circulate through the space and lower the heat exchanging efficiency of the outdoor heat exchanger 2.
  • a shielding member may be arranged on the upper surface of the drain pan 6. In this case, the shielding member is arranged outward from the plate fins 3 so that the shielding member does not come into contact with the plate fins 3.
  • a second embodiment will now be described with reference to Figs. 3 to 5 .
  • the structure of the second embodiment is the same as the structure of the first embodiment except in the shape of the outdoor heat exchanger 2 and the positional relationship between the outdoor heat exchanger 2 and the drain pan 6.
  • the components of the second embodiment common to the first embodiment will not be described in detail.
  • Fig. 3 is a cross-sectional view showing a portion of an outdoor heat exchanger 2 according to the second embodiment of the present invention.
  • Fig. 4 is a rear view showing the outdoor heat exchanger 2 as viewed from a downstream side in an air circulation direction 4.
  • the outdoor heat exchanger 2 of the second embodiment is arranged in a manner such that its lower end partially comes into contact with an upper surface 6a of a drain pan 6.
  • the lower end of the outdoor heat exchanger 2 is supported by the drain pan 6.
  • the upper surface 6a of the drain pan 6 is inclined, and the outdoor heat exchanger 2 comes into contact with an upper part of the upper surface 6a.
  • the outdoor heat exchanger 2 and the drain pan 6 come into contact with each other at region R formed at the left side as viewed in the drawing.
  • the partial contact between the lower end of the outdoor heat exchanger 2, or specifically the lower ends of the plate fins 3, and the upper surface 6a of the drain pan 6 occurs at distal ends of inclined portions 3b, which are formed as projections, on the lower ends of the plate fins 3 that come into contact with the upper surface 6a of the drain pan 6.
  • the upper surface 6a of the drain pan 6 is inclined to discharge water, and the outdoor heat exchanger 2 is arranged substantially horizontally so that the lower end of the outdoor heat exchanger 2 partially comes into contact with the upper surface 6a of the drain pan 6.
  • the inclined portions 3b are inclined relative to the air circulation direction 4. As shown in Fig.
  • the inclined portion 3b of the plate fin 3 in the left line is inclined downward from the outer side toward the middle of the outdoor heat exchanger 2, and the inclined portion 3b of the plate fin 3 of the right line is inclined upward from the middle toward the outer side of the outdoor heat exchanger 2.
  • the inclined portions 3b may be formed by diagonally cutting the lower ends of the plate fins 3.
  • the shape of the plate fin 3 at the upstream side of the airflow, or the left plate fin 3 is the same as the shape of the plate fin 3 at the downstream side of the airflow, or the right plate fin 3.
  • the left and right plate fins 3 are arranged in a manner that inclined surfaces of the upstream inclined portion 3b and the downstream inclined portion 3b face opposite directions.
  • the water droplets 8 directly drip onto the drain pan 6, move along the inclined surfaces of the inclined portions 3b as indicated by arrow A2 and drip onto the drain pan 6 before reaching the distal ends of the inclined portions 3b, or move to the distal ends of the inclined portions 3b until reaching the drain pan 6.
  • the amount of water accumulating at the contacting portions of the outdoor heat exchanger 2 and the drain pan 6 decreases. This decreases the amount of ice formed at the contacting portions.
  • Figs. 5(a) to 5(c) are cross-sectional views showing projections having other shapes that are formed on the outdoor heat exchanger 2.
  • the projections shown in Fig. 5(a) are formed in a manner that an inclined portion 3c of a plate fin 3 of an upstream side and an inclined portion 3c of a plate fin 3 of a downstream side with respect to the circulation direction 4 form a single continuous inclined portion.
  • the two inclined portions 3c are formed in a manner that an inclined surface of the upstream inclined portion 3c and an inclined surface of the downstream inclined portion 3c lie along the same plane.
  • a distal end of the inclined portion 3c of the plate fin 3 in the downstream direction comes into contact with the upper surface 6a of the drain pan 6.
  • the projections 3d shown in Fig. 5(b) are each rectangular and are formed on plate fins 3 at downstream positions relative to the circulation direction 4.
  • the projection 3d is formed by cutting a portion of a lower end of each plate fin 3 into a rectangular shape.
  • the projections 3d shorten the length of the contacting portions of the outdoor heat exchanger 2 and the drain pan 6 in the circulation direction 4, and reduce the area of contact between the plate fins 3 and the upper surface 6a of the drain pan 6.
  • the projections 3e shown in Fig. 5(c) are formed on lower ends of plate fins 3 with a semi-circular cross-section.
  • the second embodiment has the advantages described below.
  • a third embodiment will now be described with reference to Fig. 6 .
  • the structure of the third embodiment is the same as the structure of the second embodiment except in the shape of the outdoor heat exchanger 2.
  • the components of the third embodiment common to the second embodiment will not be described in detail.
  • Fig. 6 is a rear view showing a portion of an outdoor heat exchanger 2 according to the third embodiment of the present invention as viewed from a downstream side in an air circulation direction 4.
  • projections are formed on lower ends of some plate fins 3L in such a manner that the projections extend more downward than lower ends of other plate fins 3S.
  • two types of plate fins 3L and 3S that differ in vertical length are used (reference numeral 3 refers generically to the two different plate fins), and each of the plate fins 3L with the long vertical length is arranged at every predetermined number of plate fins 3S with the short vertical length.
  • the plate fins 3S and the plate fins 3L are alternately arranged.
  • distal ends of the projections formed on the lower ends of the plate fins 3L that is, distal ends of the lower ends of the plate fins 3L having the long vertical length come into contact with the upper surface 6a of the drain pan 6 in the third embodiment to enable the outdoor heat exchanger 2 and the drain pan 6 to partially come into contact with each other in the same manner as in the second embodiment.
  • the area of contact between the outdoor heat exchanger 2 and the drain pan 6 is reduced.
  • the amount of water accumulating at the portions of contact between the outdoor heat exchanger 2 and the drain pan 6 decreases. This decreases the amount of ice formed on the contacting portions.
  • the plate fins 3S do not have any portions arranged between the lower ends of the adjacent plate fins 3L. This enlarges the air circulation passage at the lower end of the outdoor heat exchanger 2. In this case, the airflow resistance of the passage decreases and the airflow velocity increases. As a result, the surface temperature of the plate fins 3 increases. Thus, condensed water is less likely to freeze at the lower ends of the plate fins 3. Further, even if the condensed water freezes at the lower ends of the plate fins 3 and the ice 13 is formed on the plate fins 3, the ice 13 does not close the airflow passage because the airflow passage is large.
  • the third embodiment has the advantages described below.
  • the third embodiment may be modified in the following forms.
  • Portions arranged at large pitches, or more specifically, the surfaces of the projections of the plate fins 3L having the long vertical length, may be subjected to hydrophilic treatment.
  • the projections of the plate fins 3L are portions of the plate fins 3L that project more downward than the plate fins 3S having the short vertical direction.
  • the hydrophilic treatment may, for example, be performed by applying a hydrophilic agent, such as polyacrylic acid, to the plate fins 3 when the plate fins 3 are made of aluminum.
  • the water slipping and water repellent treatment may be performed after or before the hydrophilic treatment is performed.
  • the condensed water spreads thinly on the surface of the plate fins 3. Even when the condensed water freezes, ice resulting from the freezing has a low height from the surface of the plate fins 3. In other words, the ice resulting from the freezing grows toward adjacent plate fins 3 only by a small amount. Thus, the air circulation passage is not closed, and the airflow resistance is prevented from increasing.
  • the third embodiment describes a case in which the outdoor heat exchanger 2 comes into contact with the drain pan 6, a space may be formed entirely between the outdoor heat exchanger 2 and the drain pan 6 in the same manner as in the first embodiment.
  • a fourth embodiment according to the present invention will now be described with reference to Figs. 7 to 12 .
  • the structure of the fourth embodiment is the same as the structure of the second embodiment except in the structure of the outdoor heat exchanger 2.
  • the components of the fourth embodiment common to the second embodiment will not be described in detail.
  • Fig. 7 is a cross-sectional view showing a portion of an outdoor heat exchanger 2 according to a fourth embodiment of the present invention.
  • the lower part of the outdoor heat exchanger 2 includes a high temperature portion 14.
  • the high temperature portion 14 heats water droplets 8 that condense and run down on the surface of plate fins 3 to 0°C or higher when the outdoor heat exchanger 2 operates as an evaporator.
  • the high temperature portion 14 corresponds to lower parts of the plate fins 3 of the outdoor heat exchanger 2 in which a heat exchanger pipe 5 is not arranged.
  • the high temperature portion 14 includes only the plate fins 3.
  • the high temperature portion 14, which includes only the plate fins 3, has a piped structure having through holes 15 formed so that the heat exchanger pipe 5 can be extended through the plate fins 3 although the heat exchanger pipe 5 is actually not inserted through the through-holes 15.
  • the heat exchanger pipe 5 is not inserted through the first and second through-holes 15 from the lower ends of the plate fins 3.
  • a region W1 which is defined from the lower ends of the plate fins 3 to the vicinity of the highest one of the through-hole 15 free from the heat exchanger pipe 5, functions as the high temperature portion 14, and heat exchange is mainly performed in the remaining region W2 excluding the region W1.
  • the heat exchanger pipe 5 is not arranged in the high temperature portion 14, the temperature of the high temperature portion 14 is higher than the temperature in the upper region W2 in which the heat exchanger pipe 5 is arranged when the outdoor heat exchanger 2 operates as an evaporator.
  • the size of the region W1 in which the heat exchanger pipe 5 is not arranged is appropriately set in a manner that the temperature of the lower ends of the plate fins 3 is at least 0°C or higher.
  • the high temperature portion 14 is arranged in this manner.
  • water droplets 8 that have condensed and run down are heated to 0°C or higher by the high temperature portion 14 in the lower part when the outdoor heat exchanger 2 operates as an evaporator.
  • water droplets 8 that have run down do not freeze at the lower end of the outdoor heat exchanger 2.
  • Fig. 8 is a cross-sectional view describing a high temperature portion having another structure.
  • the surface of plate fins 3 in a region W1 corresponding to the high temperature portion 14a is subjected to hydrophilic treatment.
  • water droplets 8 that have run down from above and reached the high temperature portion 14a spread thinly on the surface of the high temperature portion 14a.
  • Adjacent water droplets 8 combine and spread thinly on the surface of the high temperature portion 14a so as to form a thin film 7 of water.
  • the water droplets 8 are prevented from growing on the surface of the high temperature portion 14a. This consequently prevents the airflow resistance from increasing and enables the surface temperature of the high temperature portion 14a to increase.
  • Fig. 9 is a rear view showing a high temperature portion having still another structure.
  • the high temperature portion 14b shown in Fig. 9 is formed only by plate fins 3 by setting the distance from the lower ends of the plate fins 3 to the lowest part of the heat exchanger pipe 5 to be greater than the pitch of the heat exchanger pipe 5 (the interval of adjacent portions of the pipe 5 in the longitudinal direction of the plate fins 3).
  • the high temperature portion 14b no through-holes are formed in region W1 of the plate fins 3.
  • This high temperature portion 14b functions in the same manner as the high temperature portion 14 shown in Fig. 7 .
  • the high temperature portion 14b may also have its surface subjected to the hydrophilic treatment in the same manner as the high temperature portion 14a shown in Fig. 8 .
  • Fig. 10 is a cross-sectional view showing a high temperature portion having still another structure.
  • a heater 16 is arranged to come into contact with a lower end surface of an outdoor heat exchanger 2, and lower parts of plate fins 3 are heated with the heater 16.
  • Region W1 heated by the heater 16 to 0°C or higher serves as a high temperature portion 14c.
  • This high temperature portion 14c also functions in the same manner as the high temperature portion 14 shown in Fig. 7 .
  • the temperature of the high temperature portion 14c shown in Fig. 10 can be set higher than the temperature of the other high temperature portions 14, 14a, and 14b.
  • the high temperature portion 14c may also have its surface subjected to the hydrophilic treatment in the same manner as the high temperature portion 14a shown in Fig. 8 .
  • Fig. 11 is a circuit diagram showing a refrigerant circuit for a high temperature portion having still another structure.
  • Fig. 12 is a cross-sectional view showing a portion of an outdoor heat exchanger 2.
  • the outdoor heat exchanger 2 is divided into an upper heat exchanging portion 2a and a lower heat exchanging portion 2b, and the upper heat exchanging portion 2a and the lower heat exchanging portion 2b are connected by an expansion valve 9.
  • a refrigerant is supplied to the lower heat exchanging portion 2b, the expansion valve 9, and the upper heat exchanging portion 2a in the stated order so that the lower heat exchanging portion 2b operates as a condenser and the upper heat exchanging portion 2a operates as an evaporator.
  • the lower heat exchanging portion 2b that operates as a condenser forms the high temperature portion 14d shown in Fig. 11 .
  • a compressor 12, a four-way switch valve 11, an indoor heat exchanger 10, the lower heat exchanging portion 2b, the expansion valve 9, and the upper heat exchanging portion 2a are connected by a refrigerant pipe to form the refrigerant circuit.
  • the four-way switch valve 11 is set as indicated by the solid line in Fig. 11 .
  • refrigerant discharged from the compressor 12 circulates in the order of the four-way switch valve 11, the indoor heat exchanger 10, the lower heat exchanging portion 2b, the expansion valve 9, the upper heat exchanging portion 2a, and the four-way switch valve 11, and is drawn into the compressor 12.
  • the indoor heat exchanger 10 and the lower heat exchanging portion 2b operate as a condenser and the upper heat exchanging portion 2a operates as an evaporator.
  • a gasified refrigerant exchanges heat with the indoor air and condenses so that the indoor air is heated by heat released from the refrigerant.
  • the refrigerant also releases heat so that the lower heat exchanging portion 2b functions as the high temperature portion 14d.
  • a liquefied refrigerant exchanges heat with the outdoor air and evaporates to become a gasified refrigerant. As a result, the refrigerant absorbs heat from the outdoor air.
  • the four-way switch valve 11 is set as indicated by the broken line shown in Fig. 11 .
  • refrigerant discharged from the compressor 12 circulates in the order of the four-way switch valve 11, the upper heat exchanging portion 2a, the expansion valve 9, the lower heat exchanging portion 2b, the indoor heat exchanger 10, and the four-way switch valve 11, and is drawn into the compressor 12.
  • the upper heat exchanging portion 2a operates as a condenser
  • the lower heat exchanging portion 2b and the indoor heat exchanger 10 operate as an evaporator.
  • a gasified refrigerant exchanges heat with the outdoor air and becomes a liquefied refrigerant, so that the refrigerant releases heat to the outdoor air.
  • the indoor heat exchanger 10 that operates as an evaporator
  • the liquefied refrigerant exchanges heat with the indoor air and evaporates to become a gasified refrigerant, so that the refrigerant absorbs heat from the indoor air and cools the indoor air.
  • the lower heat exchanging portion 2b that operates as an evaporator, liquefied refrigerant exchanges heat with the outdoor air and evaporates to become a gasified refrigerant, so that the refrigerant cools the outdoor air.
  • the air conditioner 1 appropriately performs the cooling operation although unnecessary heat exchange occurs in the lower heat exchanging portion 2b.
  • the high temperature portion 14d functions in the same manner as the high temperature portion 14 shown in Fig. 7 .
  • the high temperature portion 14d, or the lower heat exchanging portion 2b, may also have its surface subjected to the hydrophilic treatment in the same manner as the high temperature portion 14a shown in Fig. 8 .
  • the fourth embodiment has the advantages described below.
  • the fourth embodiment may be modified in the following forms.
  • a high temperature portion may be formed by avoiding circulation of the refrigerant in portions of the heat exchanger pipe 5 extended through the portions of the plate fins 3 corresponding to the high temperature portion.
  • the heat exchanger pipe 5 is extended throughout the plate fins 3. This improves the strength of the structure of the outdoor heat exchanger 2.
  • a fifth embodiment will now be described with reference to Figs. 13 and 14 .
  • the structure of the fifth embodiment is the same as the structure of the first embodiment except in the structure of the drain pan 6.
  • the components of the fifth embodiment common to the first embodiment will not be described in detail.
  • the upper surface 6a of a drain pan 6 is subjected to a water slipping and water repellent treatment.
  • the water slipping and water repellent treatment is performed by applying a coating film having water slippage and water repellency to the upper surface 6a of the drain pan 6.
  • water dripping from the outdoor heat exchanger 2 flows smoothly on the upper surface 6a without accumulating on the upper surface 6a of the drain pan 6.
  • the drain pan 6 shown in Fig. 13 includes a water outlet 17 in the middle portion of the outdoor heat exchanger 2 in the longitudinal direction.
  • the upper surface 6a of the drain pan 6 is inclined from the two end portions of the drain pan 6 in the longitudinal direction toward the water outlet 17 formed in the middle portion.
  • the water outlet 17 formed in the middle portion shortens the distance from the highest position of the inclined upper surface 6a to the water outlet 17 as compared with when a water outlet is formed in an end portion of the drain pan 6 in the longitudinal direction, and enables water to be drained smoothly.
  • the upper surface 6a is subjected to the water slipping and water repellent treatment, water is drained more smoothly.
  • the upper surface 6a of the drain pan 6 shown in Fig. 14 is inclined from an upstream side toward a downstream side in a manner that its downstream portion in the air circulation direction 4 is at the lower position.
  • the upper surface 6a inclined in the circulation direction 4 shortens the distance from the highest position of the inclined upper surface 6a to the lowest position of the inclined upper surface 6a as compared with when the upper surface 6a is inclined in a direction perpendicular to the circulation direction 4, and enables water to be drained smoothly.
  • the upper surface 6a is subjected to the water slipping and water repellent treatment, water is drained more smoothly.
  • the fifth embodiment has the advantages described below.
  • a sixth embodiment will now be described.
  • the structure of the sixth embodiment is the same as the structure of the fifth embodiment except in the structure of the drain pan 6.
  • the components of the sixth embodiment common to the fifth embodiment will not be described in detail.
  • an upper surface 6a of a drain pan 6 is subjected to the hydrophilic treatment.
  • the hydrophilic treatment may, for example, be performed by applying a hydrophilic agent, such as polyacrylic acid, to the upper surface 6a when the drain pan 6 is made of aluminum.
  • a hydrophilic agent such as polyacrylic acid
  • the sixth embodiment has the advantage described below.
EP05767439A 2004-07-30 2005-07-29 Refrigeration unit Active EP1780492B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004224898A JP2006046694A (ja) 2004-07-30 2004-07-30 冷凍装置
PCT/JP2005/013954 WO2006025169A1 (ja) 2004-07-30 2005-07-29 冷凍装置

Publications (3)

Publication Number Publication Date
EP1780492A1 EP1780492A1 (en) 2007-05-02
EP1780492A4 EP1780492A4 (en) 2010-07-21
EP1780492B1 true EP1780492B1 (en) 2011-11-23

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Family Applications (1)

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EP05767439A Active EP1780492B1 (en) 2004-07-30 2005-07-29 Refrigeration unit

Country Status (8)

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US (1) US20080035318A1 (zh)
EP (1) EP1780492B1 (zh)
JP (1) JP2006046694A (zh)
KR (1) KR20070026835A (zh)
CN (1) CN1989388A (zh)
AT (1) ATE534878T1 (zh)
AU (4) AU2005278722B2 (zh)
WO (1) WO2006025169A1 (zh)

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Also Published As

Publication number Publication date
CN1989388A (zh) 2007-06-27
ATE534878T1 (de) 2011-12-15
EP1780492A4 (en) 2010-07-21
JP2006046694A (ja) 2006-02-16
EP1780492A1 (en) 2007-05-02
US20080035318A1 (en) 2008-02-14
AU2008207451A1 (en) 2008-09-11
AU2008207452A1 (en) 2008-09-11
AU2008207453A1 (en) 2008-09-11
AU2005278722B2 (en) 2008-10-02
WO2006025169A1 (ja) 2006-03-09
AU2005278722A1 (en) 2006-03-09
KR20070026835A (ko) 2007-03-08

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