WO2016031139A1 - 除湿装置 - Google Patents

除湿装置 Download PDF

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Publication number
WO2016031139A1
WO2016031139A1 PCT/JP2015/003808 JP2015003808W WO2016031139A1 WO 2016031139 A1 WO2016031139 A1 WO 2016031139A1 JP 2015003808 W JP2015003808 W JP 2015003808W WO 2016031139 A1 WO2016031139 A1 WO 2016031139A1
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WO
WIPO (PCT)
Prior art keywords
air
passage
heat exchanger
dehumidifying
radiator
Prior art date
Application number
PCT/JP2015/003808
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
広幸 近藤
藤井　泰樹
崇 藤園
Original Assignee
パナソニックＩｐマネジメント株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by パナソニックＩｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Priority to JP2016544926A priority Critical patent/JP6754948B2/ja
Priority to CN201580046048.9A priority patent/CN106605106B/zh
Priority to KR1020177005334A priority patent/KR20170048365A/ko
Publication of WO2016031139A1 publication Critical patent/WO2016031139A1/ja

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    • 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
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/0358—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing with dehumidification means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/1405—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification in which the humidity of the air is exclusively affected by contact with the evaporator of a closed-circuit cooling system or heat pump circuit
    • 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
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/028—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by air supply means, e.g. fan casings, internal dampers or ducts
    • F24F1/0284—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by air supply means, e.g. fan casings, internal dampers or ducts with horizontally arranged fan axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/76—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by means responsive to temperature, e.g. bimetal springs
    • 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
    • F24F13/08—Air-flow control members, e.g. louvres, grilles, flaps or guide plates
    • F24F13/10—Air-flow control members, e.g. louvres, grilles, flaps or guide plates movable, e.g. dampers
    • F24F13/14—Air-flow control members, e.g. louvres, grilles, flaps or guide plates movable, e.g. dampers built up of tilting members, e.g. louvre
    • 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
    • F24F13/20—Casings or covers
    • 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
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • 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
    • F24F13/20—Casings or covers
    • F24F2013/205—Mounting a ventilator fan therein
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature

Definitions

  • the present invention relates to a dehumidifying device used in a living space or the like.
  • Dehumidifiers have been put into practical use to reduce the humidity of living spaces and increase comfort.
  • the main body case, the dehumidifying part provided in the main body case, and the air outside the main body case sucked in from the air suction port are passed through the dehumidifying part and then passed from the air outlet to the outside of the main body case.
  • the dehumidifying section is constituted by a refrigeration cycle in which a compressor, a radiator, an expander, and a heat absorber are sequentially connected in an annular shape.
  • a part of the air sucked into the main body case from the air inlet by the blower is blown out of the main body case from the air outlet through the heat absorber, the first passage of the heat exchanger, and the radiator.
  • the other part of the air sucked from the air suction port by the blower is configured to be blown out of the main body case from the air outlet through the second passage of the heat exchanger and the radiator (for example, Patent Document 1 below).
  • the other part of the air sucked from the air suction port by the blower is passed through the second passage of the heat exchanger and blown out of the main body case from the air outlet through the radiator.
  • the indoor air passing through the second passage of the heat exchanger is cooled by the air flowing from the heat absorber to the first passage of the heat exchanger, and also attempts to condense here.
  • the air flowing into the first passage of the heat exchanger is the air after the dew condensation is performed by the heat absorber, but it is not as cold as the heat absorber even if it is cooled by the heat absorber. For this reason, even if the air flowing into the second passage is cooled by the air flowing into the first passage, the air flowing into the second passage may not reach condensation. In this case, the air passing through the second passage is released into the room without being dehumidified, resulting in a low dehumidifying effect.
  • the present invention provides a dehumidifying device with enhanced dehumidifying effect.
  • a dehumidifying device dehumidifies air in a main body case by a refrigeration cycle in which a main body case having an air inlet and an air outlet, and a compressor, a radiator, an expander, and a heat absorber are connected in order.
  • a dehumidifying part is provided.
  • a blower is provided that blows air outside the main body case sucked from the air suction port out of the main body case from the air outlet after passing through the dehumidifying section.
  • the first passage and a second passage independent of the first passage are provided, and a heat exchanger is provided for exchanging heat between the air flowing through the first passage and the air flowing through the second passage.
  • a first dehumidification path is provided for blowing a part of the air sucked into the main body case from the air suction port by the blower out of the main body case from the air outlet through the heat absorber, the first passage of the heat exchanger, and the radiator.
  • it has the 2nd dehumidification path
  • the amount of air flowing through the second passage of the heat exchanger is configured to be smaller than the amount of air flowing through the first passage of the heat exchanger.
  • the air flowing through the first passage of the heat exchanger can sufficiently condense the air flowing through the second passage. That is, dew condensation can be caused even in the heat exchanger portion, and the dehumidifying effect can be enhanced as a whole.
  • FIG. 1 is a perspective view of a dehumidifying device according to a first embodiment of the present invention.
  • 2 is a cross-sectional view taken along line 2-2 of FIG.
  • FIG. 3 is an exploded perspective view of the heat exchanger of the dehumidifier according to the first embodiment of the present invention.
  • FIG. 4 is a cross-sectional view of a dehumidifying device according to the second embodiment of the present invention.
  • FIG. 5 is a control block diagram of the dehumidifier according to the second embodiment of the present invention.
  • FIG. 6 is a diagram illustrating the operating state of the dehumidifying device according to the second embodiment of the present invention.
  • FIG. 7 is an operation flowchart of the dehumidifying apparatus according to the second embodiment of the present invention.
  • FIG. 8 is a cross-sectional view of a dehumidifier according to the third embodiment of the present invention.
  • FIG. 9 is a cross-sectional view of a dehumidifier according
  • a dehumidifying device 50 As shown in FIG. 1, a dehumidifying device 50 according to the present embodiment has a box-shaped main body case 1 as an outer shell, and the main body case 1 distinguishes the outside of the main body case 1 from the inside of the main body case 1.
  • an air suction port 2 is disposed at the upper portion, and an air suction port 3 is disposed at the lower portion of the air suction port 2.
  • An air outlet 4 is disposed on the front side of the main body case 1 facing the back side.
  • An operation unit 25 is disposed on the upper portion of the main body case 1.
  • the air suction port 2 and the air suction port 3 are provided as rectangular planes for sucking air from the direction perpendicular to the back surface.
  • a louver 31 that changes the direction of the air blown out from the air outlet 4 is provided above the air outlet 4.
  • the operation unit 25 accepts input from the user, for example, or displays information related to the dehumidifying device such as the operation mode and the current humidity to the user.
  • an air passage 34, a blower 6, and a dehumidifying unit 5 are provided in the main body case 1 of the dehumidifying device 50.
  • the air passage 34 communicates the air inlet 2 and the air inlet 3 with the air outlet 4.
  • the air passage 34 includes two dehumidification paths, that is, a first dehumidification path and a second dehumidification path, which will be described in detail later.
  • the blower 6 includes a motor 32 and a fan 33 that is connected to a rotating shaft of the motor 32 and sucks and exhausts air.
  • the blower 6 blows the air outside the main body case 1 sucked from the air suction port 2 and the air suction port 3 out of the main body case 1 from the air outlet 4 after passing through the dehumidifying part 5.
  • This air passage is an air passage 34.
  • the dehumidification part 5 is comprised by the refrigerating cycle which connected the compressor 7, the heat radiator 8, the expander 9, and the heat absorber 10 cyclically
  • an alternative chlorofluorocarbon HFC134a is used as a refrigerant.
  • the heat absorber 10 is provided on the air passage 2 and the air suction port 3 side (upstream side in the air flow direction) of the air passage 34.
  • a radiator 8 is provided on the air outlet 4 side of the air passage 34 (downstream side in the air flow direction).
  • a space is provided between the heat absorber 10 and the radiator 8, and a sensible heat type heat exchanger 11 is disposed in this space.
  • the heat absorber 10 is provided on the air suction port 2 and the air suction port 3 side of the air passage 34 communicating from the air suction port 2 and the air suction port 3 to the air outlet 4.
  • the heat exchanger 11 is provided, and then the radiator 8 is provided.
  • a funnel-shaped water collecting part 12 a is provided below the heat absorber 10 and the heat exchanger 11. Further, a water collection tank 12b is detachably disposed on the main body case 1 below the water collection unit 12a.
  • the dehumidifying device 50 is configured to generate condensation in the heat absorber 10 and the heat exchanger 11, collect the condensed water generated by the condensation in the water collecting part 12a, and flow it into the water collecting tank 12b.
  • the heat exchanger 11 is configured by alternately superposing a plurality of synthetic resin plate bodies 13 that form a vertical air passage and a synthetic resin plate body 14 that forms a horizontal air passage.
  • a plurality of ribs 15 extending in the vertical direction are formed integrally with the plate body 13 at predetermined intervals on the surface of the synthetic resin plate body 13 that forms the vertical air passage. Since one surface of the rib 15 is in close contact with the back surface of the adjacent plate body 14, the vertical air passage 13 a, that is, the second passage is formed by the surface of the plate body 13 and the rib 15 and the back surface of the plate body 14.
  • a plurality of ribs 16 extending in the lateral direction are formed integrally with the plate body 14 at predetermined intervals on the surface of the synthetic resin plate body 14 that forms a lateral air passage.
  • One surface of the rib 16 is in close contact with the back surface of the adjacent plate body 13, so that the surface of the plate body 14 and the rib 16 and the back surface of the plate body 13 form a lateral air passage 14 a, that is, a first passage.
  • the vertical air passage 13a and the horizontal air passage 14a are independent from each other, that is, there is no air traffic.
  • the heat exchanger 11 comprised in this way becomes a rectangular parallelepiped shape.
  • the rectangular parallelepiped shape here does not require that all surfaces are strictly rectangular, and it is not necessary that all adjacent surfaces intersect at right angles. That is, the rectangular parallelepiped shape may be a hexahedron at first glance.
  • an opening 17 for the first passage is formed on the opposing long sides of the rectangular parallelepiped shape.
  • the opening part 18 for 2nd passages is formed in the short side which a rectangular parallelepiped shape opposes. That is, the second passage has a longer air path than the first passage.
  • the heat absorber 10 side comprises the upstream opening part 17a
  • the radiator 8 side comprises the downstream opening part 17b.
  • the air inlet 2 side comprises the upstream opening part 18a
  • the water collection part 12a side (vertical downward direction) comprises the downstream opening part 18b.
  • the air X is sucked into the main body case 1 from the air suction port 3 by driving the blower 6.
  • the air X passes from the air outlet 4 to the outside of the main body case 1 via the heat absorber 10, the upstream opening 17 a of the heat exchanger 11, the lateral first passage, the downstream opening 17 b, the radiator 8, and the blower 6. Blown out.
  • This route of the air X is the first dehumidifying route described above.
  • the air X is the air sucked from the air suction port 3 out of the air suction port 2 and the air suction port 3, that is, can be defined as a part of the sucked air.
  • the air X flowing through such a path is first cooled by the heat absorber 10 to cause dew condensation.
  • the dew condensation water generated by the dew condensation is dropped downward, collected by the funnel-shaped water collecting part 12a, and introduced into the water collecting tank 12b.
  • the indoor humidity can be reduced.
  • the air Y is sucked into the main body case 1 from the air suction port 2 by driving the blower 6.
  • the air Y passes through the second vertical passage from the upstream opening 18 a of the heat exchanger 11, and goes out of the main body case 1 from the air outlet 4 through the downstream opening 18 b, the radiator 8, and the blower 6. Blown out.
  • This air Y path is the second dehumidifying path described above.
  • the air Y is the air sucked from the air suction port 2 out of the air suction port 2 and the air suction port 3, that is, can be defined as the other part of the sucked air.
  • the total amount of air sucked into the dehumidifying device 50 is obtained by adding two air, that is, a part of air and another part of air.
  • the air X flowing through the first lateral passage of the heat exchanger 11 is cooled by passing through the heat absorber 10 as described above.
  • the heat exchanger 11 can reduce the temperature of the air Y flowing through the second passage that does not pass through the heat absorber 10 by heat exchange.
  • the heat exchanger 11 generates dew condensation on the air Y flowing through the second passage.
  • the amount of air Y flowing through the second passage of the heat exchanger 11 is set to be smaller than the amount of air X flowing through the first passage of the heat exchanger 11.
  • the ventilation resistance of the second passage is larger than the ventilation resistance of the first passage (air X passage).
  • the heat exchanger 11 has a rectangular parallelepiped shape. Then, as shown in FIG. 3, the opening 17 for the first passage was formed on the opposing long side, and the opening 18 for the second passage was formed on the opposing short side. By making the opening area of the long-side opening 17 larger than the opening area of the short-side opening 18, the air resistance of the second passage is reduced from the viewpoint of the air flow to the blower 6. It is bigger.
  • the ventilation resistance of the second passage (air Y passage) of the heat exchanger 11 is made larger than the ventilation resistance of the first passage (air X passage) in this way, the air Y flowing through the second passage Is less than the air X flowing through the first passage.
  • the cooled air X flowing through the first passage can sufficiently cool the air Y less than the air X flowing through the second passage, and can generate dew condensation.
  • condensed water is also generated from the air Y flowing through the second passage.
  • the condensed water drops downward from the second passage, is collected by the funnel-shaped water collecting part 12a, and flows into the water collecting tank 12b.
  • the dried air Y after the generation of condensed water is blown out of the main body case 1 from the air outlet 4 through the downstream opening 18b of the heat exchanger 11, the radiator 8, and the blower 6.
  • indoor humidity reduction can be achieved.
  • downstream opening 18b of the heat exchanger 11 is an inclined surface that is inclined toward the radiator 8 as shown in FIG.
  • downstream opening 18b is inclined toward the next radiator 8 side, so that the air Y flows smoothly toward the radiator 8 side.
  • the inclined surface guides the dew condensation water generated and dripped in the second passage to the tip end portion 54 that is pointed further downward in the downstream opening 18b.
  • the condensed water guided to the tip 54 is combined with other condensed water, and the weight increases. Thereby, dripping of dew condensation water is promoted and water drainage is improved, and water droplets can be prevented from staying and becoming air resistance.
  • the flow rate ratio of air X to air Y is set to 26:18 by adopting the above configuration.
  • the amount of air flowing through the second passage (air Y passage) of the heat exchanger 11 is made smaller than the amount of air flowing through the first passage (air X passage) of the heat exchanger 11.
  • the passage length of the second passage is made longer than the passage length of the first passage.
  • a feature of the dehumidifying device 51 according to the present embodiment is that the dehumidifying device 50 according to the first embodiment is provided with an air flow rate adjusting unit that increases or decreases the amount of air flowing through the second passage of the heat exchanger 11. .
  • the air flow rate adjustment unit includes an opening / closing unit 19 that opens and closes the second passage of the heat exchanger 11 and a driving unit 20 that drives the opening / closing unit 19.
  • the opening / closing part 19 is a flat plate having an area including the upstream opening 18a, which is disposed between the air suction port 2 and the upstream opening 18a in the second passage.
  • the opening / closing part 19 is rotatably supported with a driving part 20 provided on an end of the upstream opening 18a opposite to the air suction port 2 as a rotation axis. By this rotation, the opening / closing part 19 opens and closes the upstream opening 18a of the heat exchanger 11, that is, the second passage.
  • the opening / closing part 19 is positioned so as to cover the upstream opening 18a in the closed state, that is, restricts the inflow of air into the heat exchanger 11.
  • the opening / closing part 19 enables the inflow of air into the upstream opening 18a by lifting the short side close to the air suction port 2 in the open state upward with the drive part 20 as the rotation axis.
  • the driving unit 20 functions as a rotating shaft of the opening / closing unit 19 and supports the opening / closing unit 19 rotatably in the vicinity of the upper end of the radiator 8.
  • the drive unit 20 corresponds to, for example, a motor and a gear that is rotationally driven by the motor.
  • the drive part 20 is connected to the control part 21 with the air blower 6 and the compressor 7, as shown in FIG.
  • the control unit 21 includes a first temperature sensor 22 that detects the temperature of the air entering the air suction port 3 shown in FIG. 4, a second temperature sensor 23 that detects the temperature of the heat absorber 10, A memory 24 and an operation unit 25 are connected.
  • the operation unit 25 is provided on the upper outer surface of the main body case 1, and the user instructs the dehumidifying device 51 to change the operation mode, for example, or selects a function, for example, a physical switch and the user information on the dehumidifying device.
  • a display panel for displaying is provided.
  • the control unit 21 is, for example, a microcomputer that controls the operation of the dehumidifying device 51 by reading and executing the operation program from the memory 24 in which the operation program is stored.
  • the control unit 21 receives temperature signals from, for example, the first temperature sensor 22 and the second temperature sensor 23, and based on this, turns on / off the operation of the blower 6, the compressor 7, the drive unit 20, and the like. . Details of each process performed by the control unit 21 will be described below.
  • the control unit 21 Performs the operation indicated by "normal temperature" in FIG.
  • the opening / closing part 19 opens the upstream opening 18a by the opening operation, and the above-described dehumidifying operation is performed (steps S1 and S2 in FIG. 7).
  • the control unit 21 displays “ The operation indicated by “low temperature” is performed.
  • the blower 6 and the compressor 7 are driven, and the opening / closing unit 19 is closed by the driving unit 20.
  • the opening / closing part 19 closes the upstream opening 18a by the closing operation, and the dehumidifying operation is executed in this state (steps S2 and S3 in FIG. 7).
  • the dried air X after the dew condensation occurs is the air outlet 4 through the upstream opening 17 a of the heat exchanger 11, the lateral first passage, the downstream opening 17 b, the radiator 8, and the blower 6. From outside the main body case 1. Thereby, for example, the indoor humidity can be reduced.
  • the second temperature sensor 23 that detects the temperature of the heat absorber 10 portion is set to the second set temperature ( It is determined whether or not t0 (for example, 0.5 ° C.) or less.
  • t0 for example, 0.5 ° C.
  • the initial operation time (TS) is the time from the start of the operation indicated by the “low temperature” described above.
  • the controller 21 When the temperature detected by the second temperature sensor 23 (ts) is equal to or lower than the second set temperature (t0, for example, 0.5 ° C.), the controller 21 performs an operation represented by “de-ice” in FIG. (Steps S5 and S6 in FIG. 7).
  • this state is a state in which frost formation has spread on the surface of the heat absorber 10 by continuing operation in a low temperature state
  • the control unit 21 performs a de-ice operation for eliminating the frost formation.
  • control unit 21 stops the compressor 7 and drives the blower 6 with the opening / closing unit 19 closed (step S6 in FIG. 7).
  • the air X sucked only from the air suction port 3 by the blower 6 is concentrated and blown to the heat absorber 10 to eliminate frost formation on the surface of the heat absorber 10.
  • the operation time of the de-ice operation is, for example, 10 minutes (Td: de-ice integrated time).
  • the control unit 21 acquires the temperature of the second temperature sensor 23 (ts) that detects the temperature of the heat absorber 10 portion. Whether the temperature detected by the second temperature sensor 23 (ts) is equal to or higher than the second set temperature (t0, for example, 0.5 ° C.) (step S8, step S9 in FIG. 7) or the set time When Td (for example, 10 minutes) elapses, the de-ice operation is terminated (steps S7 and S9 in FIG. 7).
  • the dehumidification operation can be performed while suppressing the promotion of frost formation and further eliminating the frost formation only by adjusting the air amount by the air flow rate adjustment unit shown in the “low temperature” operation. That is, even when frost formation occurs, frost formation can be eliminated while continuing the dehumidifying operation, and the dehumidification can be performed efficiently.
  • the dehumidifying device 52 is characterized in that, in addition to the first dehumidifying path through which air X flows and the second dehumidifying path through which air Y flows in the configuration shown in the first embodiment, This is a point provided with a third dehumidifying path through which the air Z flows.
  • Air Z is another part of the air sucked from the air suction port 2 or 3.
  • the total amount of air sucked into the dehumidifying device 52 is obtained by adding three airs, that is, a part of air, another part of air, and another part of air.
  • the other part of the air may be a part of the total amount of air sucked into the dehumidifying device 52 excluding a part of the air and the other part of the air.
  • the path through which this air Z passes is the third dehumidification path.
  • the radiator 8 protrudes vertically upward from the upper end of the heat absorber 10 and the upper end of the heat exchanger 11.
  • This protruding portion corresponds to the upper portion 8 a and can be a part of the radiator 8 above the center of the radiator 8 in the height direction.
  • the vertical upper direction indicates the upper direction when the dehumidifying device 52 is installed in a state where it can be normally operated.
  • the air Z passes through the upper part 8a of the radiator 8.
  • the air X and the air Y pass through the other part of the radiator 8 located below the upper part 8a of the radiator 8 through which the air Z passes.
  • the radiator 8 is cooled, and as a result, the heat absorber 10 is cooled, and the dehumidifying capability of the dehumidifying device 52 can be improved.
  • the refrigerant having a high temperature in the compressor 7 first flows into the upper part 8a side of the radiator 8. That is, in the radiator 8, the upper portion 8 a has a higher temperature than the other parts of the radiator 8. Since the air Z cools the upper portion 8a of the radiator 8 having a relatively high temperature, the radiator 8 can be effectively cooled. As a result, the radiator 8 is cooled and the heat absorber 10 is cooled, so that the dehumidifying ability of the dehumidifying device 52 can be improved.
  • the compressor 7 since the refrigerant
  • FIG. The refrigerant is liquefied by cooling by the radiator 8 and moves vertically downward.
  • the air Z is passing the upper part 8a, and the cooling effect of the heat radiator 8 is heightened.
  • the upper part 8a is not necessarily connected to the compressor 7 in terms of structure. In such a case, it is preferable to pass the air Z in the vicinity of the connection portion on the compressor 7 side of the connection portion on the compressor 7 side and the connection portion on the expander 9 side included in the radiator 8.
  • the third dehumidification path passes through the connecting portion on the compressor 7 side of the radiator 8 to thereby reduce the air. Z can cool the radiator 8 effectively.
  • the entire air amount (air X + air Y + air Z amount) can be increased.
  • the air Z cools the upper portion 8a of the radiator 8, the temperature rises when the air Z is blown out of the main body case 1 from the air blowout port 4 than when it is sucked from the air suction port 2 or 3.
  • the drying effect can be enhanced when clothes are dried in a living space using a dehumidifying device.
  • the amount of air Y flowing through the second passage of the heat exchanger 11 is configured to be smaller than the amount of air X flowing through the first passage of the heat exchanger 11.
  • the amount of air Z is smaller than the amount of air Y flowing through the second passage of the heat exchanger 11. Specifically, it is preferable that the ventilation resistance of the air Z is larger than the ventilation resistance of the air Y.
  • the dehumidifying ability of the dehumidifying device can be further effectively improved.
  • the dehumidifying device 53 is characterized in that, in the heat exchanger 11 in the configuration shown in the first embodiment, the upstream opening 18 a of the second passage is connected to the air inlet 2. It is the point made into the inclined surface 55 inclined toward the side.
  • a circuit board 61 as a control unit that controls the operation of the dehumidifier 53 is provided above the heat exchanger 11 in the main body case 1.
  • the circuit board 61 is disposed close to the heat exchanger 11.
  • the air Y sucked into the main body case 1 from the air suction port 2 by the blower 6 passes through a gap formed between the circuit board 61 and the heat exchanger 11 and exchanges heat from the upstream opening 18a of the second passage. Flows into the vessel 11. And it blows out of the main body case 1 from the air blower outlet 4 via the heat radiator 8 and the air blower 6.
  • the air X sucked into the main body case 1 from the air suction port 3 by the blower 6 passes through the heat absorber 10 and flows into the heat exchanger 11 from the upstream side opening 17a of the first passage.
  • the air X flows out from the downstream opening 17 b and is blown out of the main body case 1 from the air outlet 4 via the radiator 8 and the blower 6. At this time, heat exchange is performed between the air X and the air Y in the heat exchanger 11, and dew condensation occurs in the second passage.
  • the air that passes through a portion close to the radiator 8 has little cooling effect by the heat exchanger 11, so that condensation is unlikely to occur.
  • the air for cooling the air passing through the second passage is the air passing through the first passage.
  • path flows in into the heat exchanger 11 from the upstream opening part 17a which is the heat absorber 10 side, and flows out from the downstream opening part 17b which is the heat radiator 8 side. Therefore, first, the air passing through the portion of the second passage close to the heat absorber 10 is cooled, and then the air passing through the portion of the second passage close to the radiator 8 is cooled.
  • the air X flowing through the first passage is first heated by exchanging heat with the air passing through a portion near the heat absorber 10 in the second passage, and a portion near the radiator 8 in the second passage in the warmed state.
  • the air passing through will be cooled.
  • the temperature difference with the air passing through the portion of the second passage close to the radiator 8 is reduced, and the heat exchange rate is reduced. Since the heat exchange rate is slow, it is difficult to cool and condensation in the second passage is unlikely to occur.
  • the air Y taken in from the air suction port 2 provided on the back surface of the main body case 1 flows in the horizontal direction, but the upstream opening 18a of the second passage opens in the vertical direction (vertically upward). Therefore, the air flow is bent sharply.
  • the flow of the air Y is biased due to inertia, and more air flows into the portion of the second passage close to the radiator 8 that is outside the curve. Since a large amount of air flows through the portion of the second passage close to the radiator 8, more cooling heat is required to cool the air to the dew point temperature to cause condensation.
  • the air passing through the portion of the second passage close to the radiator 8 is not easily cooled, so that condensation is unlikely to occur.
  • the upstream opening 18a of the heat exchanger 11 is the inclined surface 55 that is inclined toward the air suction port 2 side, so that the air passing through the portion close to the radiator 8 in the second passage is used. It becomes easier to cool. Details thereof will be described below.
  • the length of the long side direction of the downstream opening 17b of the first passage is extended in the direction of the upper part 8a of the radiator 8.
  • the height after extending should just be a position higher than the downstream end part (upper end part of the heat absorber 10 in FIG. 9) of the heat absorber 10.
  • FIG. As a result, the upstream opening 18a is inclined toward the air inlet 2 as a result.
  • the passage length of the part near the radiator of the second passage is increased, and the time for passing through the heat exchanger 11 can be increased. Thereby, even if the temperature difference is small and the heat exchange rate is low, heat exchange can be performed for a longer time, and as a result, the amount of heat exchange can be increased. Since the amount of heat exchange can be increased, the amount of cooling with respect to the air flowing through the portion of the second passage close to the radiator 8 can be increased, and the generation of condensation can be increased.
  • the portion near the heat absorber 10 of the second passage Since the length of the long side direction of the downstream opening 17b of the first passage is extended and the upstream opening 18a is inclined toward the air suction port 2, the portion near the heat absorber 10 of the second passage. Will be easier to flow in, and the uneven air flow will be mitigated. That is, since the passage length of the second passage increases from the heat absorber 10 toward the radiator 8 in the second passage and the ventilation pressure loss increases, the air Y hardly flows into a portion near the radiator 8. . On the contrary, since it becomes easy to flow into the portion close to the heat absorber 10, the deviation of the airflow flowing through the second passage is alleviated.
  • the air flowing through the portion of the second passage close to the radiator 8 is reduced, and the amount of cooling heat required for cooling to the dew point temperature is reduced. Accordingly, it is possible to increase the generation of condensation due to the air flowing through the portion of the second passage close to the radiator 8.
  • a plurality of air suction ports corresponding to the respective air amounts may be provided.
  • control unit In the first embodiment and the third embodiment, the control unit is not described, but the control unit shown in the second embodiment is provided in the first embodiment and the third embodiment. Also good. In this case, a control part operates a dehumidification apparatus by transmitting a control command to a compressor or an air blower.
  • control unit shown in the second embodiment may be incorporated into the control unit shown in the fourth embodiment.
  • the above-described four embodiments may be performed simultaneously within a consistent range. For example, this corresponds to providing a dehumidifying device provided with an air flow rate adjusting unit and a third dehumidifying path.
  • the present invention can also cause condensation in the heat exchanger portion, it is extremely useful as a dehumidifying device having a high dehumidifying effect.
PCT/JP2015/003808 2014-08-29 2015-07-29 除湿装置 WO2016031139A1 (ja)

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JP2020121247A (ja) * 2019-01-29 2020-08-13 パナソニックＩｐマネジメント株式会社 除湿装置
JP2020146663A (ja) * 2019-03-15 2020-09-17 パナソニックＩｐマネジメント株式会社 除湿装置
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JP2020159595A (ja) * 2019-03-26 2020-10-01 パナソニックＩｐマネジメント株式会社 調湿機能付き熱交換形換気装置
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JP2021006758A (ja) * 2019-12-23 2021-01-21 パナソニックＩｐマネジメント株式会社 除湿機能付き熱交換形換気装置
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JPWO2018154837A1 (ja) * 2017-02-23 2019-07-25 三菱電機株式会社 除湿機
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JPWO2018154838A1 (ja) * 2017-02-23 2019-11-21 三菱電機株式会社 除湿機
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CN106605106B (zh) 2020-01-17

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