WO2007083501A1 - Climatiseur - Google Patents

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Publication number
WO2007083501A1
WO2007083501A1 PCT/JP2006/326032 JP2006326032W WO2007083501A1 WO 2007083501 A1 WO2007083501 A1 WO 2007083501A1 JP 2006326032 W JP2006326032 W JP 2006326032W WO 2007083501 A1 WO2007083501 A1 WO 2007083501A1
Authority
WO
WIPO (PCT)
Prior art keywords
air
wind direction
air conditioner
direction plate
flow fan
Prior art date
Application number
PCT/JP2006/326032
Other languages
English (en)
Japanese (ja)
Inventor
Masaki Ohtsuka
Original Assignee
Sharp Kabushiki Kaisha
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
Priority claimed from JP2006011832A external-priority patent/JP4014618B2/ja
Priority claimed from JP2006011822A external-priority patent/JP4014617B2/ja
Application filed by Sharp Kabushiki Kaisha filed Critical Sharp Kabushiki Kaisha
Priority to EP06843414A priority Critical patent/EP1975522B1/fr
Priority to CN2006800513913A priority patent/CN101360954B/zh
Publication of WO2007083501A1 publication Critical patent/WO2007083501A1/fr

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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
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0057—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in or on a wall
    • 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
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0025—Cross-flow or tangential fans
    • 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

Definitions

  • the present invention relates to an air conditioner that harmonizes air taken from a room and sends the air into the room.
  • Patent Documents 1 and 2 Conventional air conditioners are disclosed in Patent Documents 1 and 2.
  • the air conditioner of Patent Document 1 improves the thickness distribution of the blades of the air supply fan and reduces the pressure loss of the blower fan. As a result, energy conservation of the air conditioner is achieved.
  • the air conditioner of Patent Document 2 has a movable panel that closes the suction port provided on the front surface of the casing of the indoor unit. When the air conditioner is driven, the movable panel is moved, and the air is taken in by opening the suction port widely. As a result, the pressure loss at the time of suction is reduced, and energy saving of the air conditioner is achieved.
  • Patent Document 1 Japanese Patent Laid-Open No. 2003-028089
  • Patent Document 2 Japanese Patent Laid-Open No. 2000-111082
  • An object of the present invention is to provide an air conditioner that can further save energy.
  • the present invention provides a suction port for taking indoor air into a housing of an indoor unit, an air outlet provided at a lower portion of the housing, and a space between the air inlet and the air outlet.
  • an air conditioner including a cross flow fan disposed between the indoor heat exchanger and the air outlet in the path, the air flow path guides the air forward and downward and flows toward the downstream. It has a front guide that enlarges the road area, and the sum of the length of the upper and lower walls of the air flow path downstream of the cross flow fan is 3.5 times the diameter of the cross flow fan. It is characterized by the above.
  • the air in the suction loca chamber is taken into the housing by the drive of the cross flow fan and flows through the air blowing path.
  • the air is harmonized by heat exchange with indoor heat exchange with a large pressure loss arranged in a plurality of rows in the vertical direction and in a plurality of rows in the depth direction by meandering the refrigerant pipe.
  • the conditioned air circulates through the front guide part along the upper and lower walls of the air flow path on the exhaust side of the cross-flow fan through the front guide, and is sent out from the outlet. At this time, the airflow along the upper and lower walls of the ventilation path is gradually decelerated, and the kinetic energy is converted to static pressure and recovered as static pressure.
  • the present invention provides the air conditioner configured as described above, further comprising a first wind direction plate that can change a wind direction of the air outlet up and down, and a front end of the upper wall from the front upper side during operation of the air conditioner. 1 It is characterized by arrange
  • a second wind direction plate is provided below the first wind direction plate, and a front end of the first wind direction plate is disposed forward of a front end of the second wind direction plate.
  • the present invention further includes first and second wind direction plates that are variable above and below the air outlet, and the upper wall is bent at a bent portion from an end of the upper surface of the front guide portion. And the rear end of the first wind direction plate is disposed in front of the bent portion, and the rear end of the second wind direction plate below the first wind direction plate is the front end.
  • the bent part It is characterized by being arranged at the rear.
  • the airflow flowing along the upper wall of the blowing path is bent by the second wind direction plate and flows forward and upward along the inclined surface.
  • the kinetic energy of the lower airflow bent by the second wind direction plate is recovered by being converted to static pressure by the flow path formed between the second wind direction plate and the first wind direction plate.
  • the kinetic energy of the upper air stream bent by the second wind direction plate is recovered by being converted into static pressure by the flow path formed between the first wind direction plate and the inclined surface.
  • the present invention is characterized in that an angle formed by the inclined surface and the first wind direction plate and an angle formed by the first and second wind direction plates are set to 10 ° to 15 °. Yes. According to this configuration, the airflow smoothly flows along the wall surface without being separated from the wall surface formed by the inclined surfaces of the first and second wind direction plates and the air flow path.
  • a third wind direction plate is provided below the second wind direction plate, and an angle formed by the second and third wind direction plates is set to 10 ° to 15 °. It is a feature. According to this configuration, the air flow smoothly flows along the wall surface without peeling off the wall force that is also the second and third wind direction plate force.
  • an angle formed between the wind direction plate disposed at the lowermost position and the tangent at the end of the lower wall of the front guide portion is set to 10 ° to 15 °. It features. According to this configuration, the airflow smoothly flows along the wall surface without peeling off the wall surface force, which is the lowest wind direction plate force.
  • the present invention is characterized in that the length of the upper wall is 1.5 times or more the diameter of the cross-flow fan.
  • the present invention is a suction port for taking indoor air into the housing of the indoor unit, a blowout port provided in the lower portion of the housing, a ventilation path that communicates between the suction port and the blowout port,
  • An indoor heat exchanger in which refrigerant tubes are arranged in a plurality of rows and in a plurality of rows and bent along the inner surface of the housing and disposed opposite to the suction port in the air supply path, and the indoors in the air supply path
  • An air conditioner including a cross-flow fan disposed between a heat exchanger ⁇ and the air outlet, and first and second air direction plates that change the air direction of the air outlet up and down
  • the path is a flow path surface as it guides air forward and downward from the cross flow fan and goes downstream.
  • the wall has an inclined surface that is bent at the terminal force bending portion of the front guide portion and is inclined forward and upward, and the rear end of the first wind direction plate is disposed in front of the bent portion, and the first wind direction plate Further, the rear end of the second wind direction plate below is arranged behind the bent portion.
  • the air in the suction loca chamber is taken into the housing by the driving of the cross flow fan and flows through the air blowing path.
  • the air is harmonized by heat exchange with indoor heat exchange with a large pressure loss arranged in a plurality of rows in the vertical direction and in a plurality of rows in the front and rear by meandering the refrigerant pipe.
  • the conditioned air circulates in the front guide section while expanding the flow path area along the upper and lower walls of the air flow path of the cross flow fan.
  • the airflow flowing along the upper wall of the ventilation path is bent by the second wind direction changing plate and flows forward and upward along the inclined surface.
  • the lower airflow bent by the second wind direction change plate is gradually decelerated by the flow path formed between the second wind direction change plate and the first wind direction change plate, and the kinetic energy is converted to static pressure and Recovered as pressure.
  • the upper airflow bent by the second wind direction change plate is gradually decelerated by the flow path formed between the first wind direction change plate and the inclined surface, and the kinetic energy is converted to static pressure and recovered as static pressure. Is done.
  • the present invention is characterized in that an angle formed by the inclined surface and the first wind direction plate and an angle formed by the first and second wind direction plates are 10 ° to 15 °. Yes.
  • the present invention includes a third wind direction plate provided below the second wind direction plate, and an angle formed by the second and third wind direction plates is set to 10 ° to 15 °. It is a feature.
  • an angle formed between the wind direction plate disposed at the lowermost position and the tangent at the end of the lower wall of the front guide portion is set to 10 ° to 15 °. It features.
  • the present invention provides a front end of the upper wall, a front end of the first wind direction plate, a front end of the second wind direction plate, and a front end of the lower wall when the air conditioner is operated. They are arranged in the order of the front edge. According to this configuration, the kinetic energy of the airflow flowing through the blower path is sequentially recovered in the downward force with the slow flow rate.
  • the present invention is a suction port for taking indoor air into the housing of the indoor unit, a blower outlet provided in the lower part of the housing, a blower path that communicates between the suction port and the blower outlet, An indoor heat exchanger disposed opposite to the suction port in the air passage, and a cross flow fan disposed between the indoor heat exchanger ⁇ in the air passage and the outlet. It is characterized in that the length of the upper wall of the air flow path on the downstream side of the cross flow fan is 1.5 times or more the diameter of the cross flow fan.
  • the air inside the suction loca is also taken into the housing by the driving of the cross flow fan, and flows through the ventilation path.
  • the air is harmonized by heat exchange with the indoor heat exchange, and the conditioned air flows from the exhaust side of the cross flow fan along the upper and lower walls of the air flow path and is sent out from the outlet.
  • the airflow along the upper and lower walls of the air flow path is gradually decelerated, and the kinetic energy is converted to static pressure and recovered as static pressure.
  • the present invention provides a suction port for taking indoor air into the housing of the indoor unit, a blowout port provided in a lower portion of the housing, a blower path communicating between the suction port and the blowout port, An indoor heat exchanger disposed opposite to the suction port in the air passage, and a cross flow fan disposed between the indoor heat exchanger ⁇ in the air passage and the outlet. It is characterized in that the sum of the length of the upper wall and the lower wall of the air flow path on the downstream side of the cross flow fan is at least 3.5 times the diameter of the cross flow fan.
  • the air inside the suction loci chamber is taken into the housing by the driving of the cross flow fan and flows through the air blowing path.
  • the air is harmonized by heat exchange with the indoor heat exchange, and the conditioned air flows from the exhaust side of the cross flow fan along the upper and lower walls of the air flow path and is sent out from the outlet.
  • the airflow along the upper and lower walls of the air flow path is gradually decelerated, and the kinetic energy is converted to static pressure and recovered as static pressure.
  • the air conditioner since the sum of the length of the upper wall and the length of the lower wall of the air flow path on the downstream side of the cross flow fan is 3.5 times or more the diameter of the cross flow fan, the air conditioner During operation, air flows smoothly along the upper and lower walls of the air flow path over a long distance. As a result, there is less air flow disturbance near the outlet, and the pressure loss associated with it is reduced. The kinetic energy is reduced by decelerating until the air along the long upper and lower walls is sufficiently slow. Converted to pressure. Therefore, the kinetic energy of the airflow can be sufficiently recovered to reduce the static pressure rise by the cross flow fan, and the energy saving of the air conditioner can be achieved.
  • the indoor heat exchangers ⁇ are arranged in multiple rows and multiple stages, even when using an indoor heat exchanger with large pressure loss, the kinetic energy of the airflow is sufficiently recovered to save energy in the air conditioner. Can be planned. Since the front guide portion is provided in which the flow area is increased as the air is guided to the lower front side and goes downstream, the airflow can be gradually decelerated to sufficiently recover the motion energy.
  • the front end of the upper wall, the front end of the first wind direction plate, and the front end of the lower wall are arranged in this order from the front upper side during operation of the air conditioner.
  • the rugged force can be recovered in order to efficiently recover the kinetic energy of the airflow.
  • the second wind direction plate is provided below the first wind direction plate, and the front end of the first wind direction plate is disposed in front of the front end of the second wind direction plate. It is possible to recover the kinetic energy of the airflow efficiently by recovering the power of density kinetic energy in order.
  • the rear end of the first wind direction plate is disposed in front of the bent portion between the upper surface of the front guide portion and the inclined surface, and the second wind direction below the first wind direction plate. Since the rear end of the plate is disposed behind the bent portion, the airflow can be bent along the inclined surface by the second wind direction plate. In addition, the kinetic energy of the air flow can be efficiently recovered by recovering in order from the low-density kinetic energy having a low downward flow velocity.
  • the angle formed between the inclined surface and the first wind direction plate and the angle formed between the first and second wind direction plates are set to 10 ° to 15 °.
  • the flow path between the first and second wind direction plates is continuously expanded, and the air flow smoothly flows along the wall surface without peeling off the wall force.
  • the kinetic energy of the airflow can be smoothly converted to static pressure, and the kinetic energy can be recovered efficiently.
  • the angle formed by the second wind direction plate and the third wind direction plate below the second wind direction plate is 10 ° to 15 °, the flow between the second and third wind direction plates is The channel is continuously expanded, and the airflow smoothly flows along the wall without peeling off the wall. This allows the kinetic energy to be efficiently recovered by converting the kinetic energy of the airflow into static pressure smoothly. wear.
  • the angle formed between the wind direction plate disposed at the lowermost position and the tangent at the end of the lower wall is set to 10 ° to 15 °, the lowermost wind direction plate and the lower wall of the air flow path The channel between the two is continuously expanded, and the airflow smoothly flows along the wall without peeling off the wall force. As a result, the kinetic energy of the airflow can be smoothly converted to static pressure, and the kinetic energy can be efficiently recovered.
  • the length of the upper wall of the air flow path on the downstream side of the cross flow fan is 1.5 times or more the diameter of the cross flow fan. It smoothly circulates a long distance along the upper wall of the ventilation path. As a result, there is less air flow disturbance in the vicinity of the air outlet, and the associated pressure loss is reduced. The kinetic energy is converted into static pressure by decelerating until the air along the long upper and lower walls becomes sufficiently slow, with a force tl. Accordingly, the kinetic energy of the airflow can be sufficiently recovered to reduce the static pressure rise by the cross flow fan, and the energy saving of the air conditioner can be achieved.
  • the kinetic energy can be recovered to increase the reach distance of the airflow with a reduced flow velocity.
  • the air sent out from the outlet also reaches the ceiling of the room and sequentially travels through the wall facing the air conditioner, the floor, and the wall on the air conditioner side. Therefore, the conditioned air stream reaches every corner of the room, and the air stream greatly stirs the entire room. Therefore, it is possible to obtain a comfortable space with almost no direct wind by equalizing the temperature distribution of the entire living area except for a part above the room.
  • the indoor heat exchanger is composed of a plurality of rows and stages, even when an indoor heat exchanger with a large pressure loss is used, the kinetic energy of the airflow is sufficiently recovered to save energy of the air conditioner. Can be planned. Since the front guide portion is provided in which the flow area is increased as the air is guided to the lower front side and goes downstream, the airflow can be gradually decelerated to sufficiently recover the motion energy.
  • the rear end of the first wind direction plate is disposed in front of the bent portion between the upper surface of the front guide portion and the inclined surface, and the rear end of the second wind direction plate below the first wind direction plate. Is disposed behind the bent portion, the airflow can be bent along the inclined surface by the second wind direction plate. In addition, the kinetic energy of the airflow is recovered by recovering in order from the lower flow velocity! Lugie can be collected efficiently.
  • the front end of the upper wall, the front end of the first wind direction plate, the front end of the second wind direction plate, and the front end of the lower wall are arranged in this order from the front upper side during operation of the air conditioner, the lower flow velocity
  • the kinetic energy of the airflow can be efficiently recovered by recovering in order of slow kinetic energy power.
  • FIG. 1 is a side cross-sectional view showing a state during operation of an indoor unit of an air conditioner according to a first embodiment of the present invention.
  • FIG. 2 is a side cross-sectional view showing details of a ventilation path of the indoor unit of the air conditioner according to the first embodiment of the present invention.
  • FIG. 3 is a side cross-sectional view showing details of a bent portion of a ventilation path of the indoor unit of the air conditioner according to the first embodiment of the present invention.
  • FIG. 4 is a side cross-sectional view showing a state when the operation of the indoor unit of the air conditioner according to the first embodiment of the present invention is stopped.
  • FIG. 5 is a side sectional view showing details of the vicinity of the air outlet of the indoor unit of the air conditioner according to the first embodiment of the present invention.
  • FIG. 6 is a diagram showing the relationship between the air volume of the cross flow fan of the indoor unit of the air conditioner according to the first embodiment of the present invention and the input of the fan drive motor.
  • FIG. 7 is a side sectional view showing a comparative example of the indoor unit of the air conditioner of the first embodiment of the present invention.
  • FIG. 8 is a static pressure of the comparative example of the indoor unit of the air conditioner of the first embodiment of the present invention. Figure explaining the transition of
  • FIG. 9 is a graph showing changes in static pressure of a comparative example of the indoor unit of the air conditioner according to the first embodiment of the present invention.
  • FIG. 10 is a diagram for explaining the transition of the static pressure of the air conditioner indoor unit according to the first embodiment of the present invention.
  • FIG. 11 is the transition of the static pressure of the air conditioner indoor unit of the first embodiment of the present invention.
  • FIG. 12 is a diagram showing the relationship between the length of the upper wall, the length of the lower wall, and the power consumption of the cross flow fan of the indoor unit of the air conditioner according to the first embodiment of the present invention.
  • FIG. 13 shows the length of the upper wall of the air flow path of the indoor unit of the air conditioner according to the first embodiment of the present invention. Diagram showing the relationship between wall length and crossflow fan airflow reach
  • FIG. 14 is a side cross-sectional view showing a state when the operation of the indoor unit of the air conditioner of the second embodiment of the present invention is stopped.
  • FIG. 15 is a side sectional view showing a state during operation of the indoor unit of the air conditioner according to the second embodiment of the present invention.
  • FIG. 16 is a side cross-sectional view showing a state when the operation of the indoor unit of the air conditioner according to the third embodiment of the present invention is stopped.
  • FIG. 17 is a side sectional view showing a state during operation of the indoor unit of the air conditioner according to the third embodiment of the present invention.
  • FIG. 18 is a side sectional view showing a state during operation of the indoor unit of the air conditioner according to the fourth embodiment of the present invention.
  • FIG. 19 is a side sectional view showing a state during operation of the indoor unit of the air conditioner according to the fifth embodiment of the present invention.
  • FIG. 1 is a side sectional view showing the indoor unit of the air conditioner of the first embodiment.
  • the indoor unit 1 of the air conditioner has a main body held by a cabinet 2, and a front panel 3 is detachably attached to the cabinet 2.
  • the cabinet of indoor unit 1 is composed of cabinet 2 and front panel 3.
  • the cabinet 2 is provided with a claw portion (not shown) on the rear side surface, and is supported by engaging the claw portion with a mounting plate (not shown) attached to the side wall W1 of the room.
  • An air outlet 5 is provided in the gap between the lower end of the front panel 3 and the lower end of the cabinet 2.
  • the air outlet 5 is formed in a substantially rectangular shape extending in the width direction of the indoor unit 1 and is provided facing the front lower side.
  • a lattice-shaped suction port 4 is provided on the upper surface of the front panel 3.
  • a blower path 6 that connects the suction port 4 and the blowout port 5 is formed inside the casing of the indoor unit 1.
  • a cross flow fan 7 for sending air is disposed in the air blowing path 6.
  • the air blowing path 6 is surrounded by the upper wall 6b and the lower wall 6c on the downstream side of the cross flow fan 7. Further, the air blowing path 6 has a front guide portion 6a for guiding the air sent out by the cross flow fan 7 forward and downward.
  • the front guide portion 6a is formed such that the flow path area increases as it goes downstream.
  • FIG. 2 is a side sectional view showing details of the air flow path 6 on the downstream side of the cross flow fan 7.
  • the upper wall 6b of the air flow path 6 has a stabilizer portion 6b7 along the peripheral surface of the cross flow fan 7.
  • the stabilizer portion 6b7 is formed extending in the exhaust direction of the cross flow fan 7, and is continuous with the upper surface 6b3 of the front guide portion 6a at the lower end.
  • the upper surface 6b3 of the front guide portion 6a is inclined forward and downward. End of upper surface 6b3 of front guide 6a An inclined surface 6b5 that is bent upward through the bent portion 6b4 and inclined forward and upward is formed.
  • the bend 6b4 is a gentle and smooth curved surface.
  • the lower wall 6c of the air flow path 6 has a rear guider part 6c5 along the peripheral surface of the cross flow fan 7.
  • the rear guider portion 6c5 is formed to extend in the exhaust direction of the cross flow fan 7, and the lower wall 6c is formed in a spiral curved surface including the lower end force of the rear guider portion 6c5 and the lower surface 6c3 of the front guide portion 6a.
  • the angle ⁇ formed by the upper surface 6b3 and the lower surface 6c3 of the front guide portion 6a is formed to be about 20 °.
  • the angle ⁇ between the slope 6b5 and the horizontal plane is about 20 °.
  • An angle ⁇ formed by the upper surface 6b3 of the front guide portion 6a and the horizontal plane is 5 °. Therefore, the angle ( ⁇ + y) formed by the upper surface 6 b3 of the front guide portion 6a and the inclined surface 6b5 is 25 °. It is desirable to form the squares j8 and ⁇ at about 15 ° to 20 °, 30 ° or less, and about 0 ° to 10 °, respectively.
  • the angle (j8 + ⁇ ) is 17 ° or less, the air along the wall surface of the flow path can be circulated with a small pressure loss to the sliding force without peeling off the wall surface force.
  • the angle (+ ⁇ ) is larger than 17 ° in order to divide the flow path into a plurality of parts by the horizontal louvers 111, 112, 113 as described later.
  • the middle horizontal louver 112 is disposed opposite to the bent portion 6b4 to suppress separation of the airflow.
  • At least one flat surface 6f may be provided in the bent portion 6b4, and the end portions of the flat surface 6f may be connected by a smooth curved surface 6e.
  • an angle 05 formed by the upper surface 6b3 of the front guide portion 6a and the plane 6f and an angle 06 formed by the plane 6f and the inclined surface 6b5 are formed to be 17 ° or less. If there are multiple planes 6f, the angles formed by the planes are all less than 17 °. Thereby, the air along the wall surface of the flow path can be smoothly circulated with a small pressure loss without peeling off the wall surface force. Therefore, energy saving can be improved.
  • the lengths of the upper wall 6b and the lower wall 6c of the air flow path 6 on the downstream side of the cross flow fan 7 are formed to be 1.9D and 2.1D, where the diameter of the cross flow fan 7 is D, respectively.
  • the ends 6b 1 and 6c 1 of the stabilizer part 6b7 and the rear guider part 6c5 are provided in the vicinity of the diameter direction perpendicular to the exhaust direction of the cross flow fan 7, and V is the starting point of the upper wall 6b and the lower wall 6c.
  • the front gear that minimizes the distance to the crossflow fan 7 is used.
  • the part 6b2 and the rear gap 6c2 may be the starting points of the upper wall 6b and the lower wall 6c.
  • the front end of the inclined surface 6b5 abuts on the lower end of the front panel 3 to form the end 6b6 of the upper wall 6b.
  • the front end of the lower surface of the cabinet 2 is formed with a small radius of curvature where the end 6c4 of the lower surface 6c3 of the front guide portion 6a becomes an inflection point.
  • the end 6c4 is the end point of the lower wall 6c (hereinafter, 6c 4 may be referred to as the end of the lower wall 6c.) 0
  • 98 indicates the tangent at the end 6b4 of the lower surface 6c3 of the front guide portion 6a.
  • the front guide portion 6a is provided with a vertical louver 12 capable of changing the blowing angle in the left-right direction.
  • the blower outlet 5 is provided with a plurality of lateral louvers 111, 112, 113 that can change the blowout angle in the vertical direction to the upper front, the horizontal direction, the lower front, and the right lower direction.
  • An air filter 8 is provided at a position opposite to the front panel 3 to collect and remove dust contained in the air sucked from the suction port 4! /.
  • An air filter cleaning device (not shown) is provided in a space formed between the front panel 3 and the air filter 8. The dust accumulated in the air filter 8 is removed by the air filter cleaning device.
  • the indoor heat exchanger 9 has meandering refrigerant pipes (not shown) arranged in a plurality of rows in the vertical direction and in a plurality of rows in the front and rear directions, and is bent in multiple stages along the front panel 3.
  • the indoor heat exchanger 9 is connected to a compressor (not shown) arranged outdoors, and the refrigeration cycle is operated by driving the compressor. During the cooling operation, the indoor heat exchanger 9 is cooled to a temperature lower than the ambient temperature by the operation of the refrigeration cycle. Further, during the heating operation, the indoor heat exchanger 9 is heated to a temperature higher than the ambient temperature.
  • an electric dust collector (not shown) and a temperature sensor 61 for detecting the temperature of the sucked air are provided.
  • a control unit (not shown) for controlling the driving of the air conditioner is provided on the side of the indoor unit 1. Drain pans 10 and 13 that collect condensation that has fallen from the indoor heat exchanger 9 during cooling or dehumidification are provided at the bottom before and after indoor heat exchange.
  • the lateral louvers 111 and 112 are disposed at positions that shield the upper and lower portions of the blowing path 6 as shown in FIG.
  • the lateral louver 113 is arranged inside the air blowing path 6.
  • the blower outlet 5 is obstruct
  • the horizontal louvers 111 and 112 are arranged along the front surface of the front panel 3.
  • the horizontal louver 112 is disposed so as to connect the lower end of the horizontal louver 111 and the bottom surface of the cabinet 2. As a result, the aesthetics of the indoor unit 1 are not impaired.
  • Condensation preventing means is provided on the side of the upper wall 6b that does not face the air passage 6.
  • the upper wall 6b may be formed of a heat insulating material, and a heat insulating material may be provided on the upper surface of the upper wall. Further, other dew condensation prevention means other than the heat insulating material may be used. Even if condensation occurs on the side of the upper wall 6b that does not face the air supply path 6, the condensed water is guided to the drain pan 10. Therefore, it is possible to obtain a highly reliable air conditioner without problems caused by condensed water.
  • the horizontal louvers 111, 112, and 113 are arranged with the air outlet 5 opened, as shown in FIG.
  • the vertical louver 12 is directed in a predetermined direction.
  • the cross flow fan 7 is driven, refrigerant from the outdoor unit (not shown) flows into the indoor heat exchanger 9, and the refrigeration cycle is operated.
  • air is sucked into the indoor unit 1 from the suction port 4, and dust contained in the air is removed by the air filter 8.
  • the air taken into the indoor unit 1 is cooled by exchanging heat with the indoor heat exchanger 9.
  • the conditioned air cooled by the indoor heat exchanger 9 is regulated in the left-right direction and the up-down direction by the vertical louver 12 and the horizontal louvers 111, 112, 113, as shown by an arrow E along the inclined surface 6b5.
  • the indoor unit 1 is in a state of blowing forward and upward, which sends conditioned air upward and upward.
  • the conditioned air sent from the outlet 5 along the inclined surface 6b5 forward and upward into the room reaches the ceiling surface S (see FIG. 2) of the room. Thereafter, the coanda effect causes the indoor unit 1 to be sucked from the ceiling surface S through the side wall facing the indoor unit 1, the floor, and the side wall W1 on the indoor unit 1 side.
  • the user is not always exposed to the cold wind or the warm wind directly.
  • the user's discomfort can be prevented and the comfort can be improved.
  • health safety can be improved without locally lowering the user's body temperature during cooling.
  • the air flow greatly stirs the entire room, the temperature distribution in the room is uniform around the set temperature. That is, except for the upper part of the room, the entire living area of the user Therefore, it is possible to obtain a comfortable space where the temperature variation is small and the direct wind hardly hits the user.
  • FIG. 5 is a side sectional view showing details of the vicinity of the air outlet 5 at this time.
  • the uppermost horizontal louver 111 faces the inclined surface 6b5, and the rear end thereof is disposed in front of the bent portion 6b4.
  • the middle horizontal louver 112 faces the bent portion 6b4, and the rear end thereof is disposed behind the bent portion 6b4. From the upper front, the end 6b6 of the upper wall 6b, the front end of the uppermost horizontal louver 111, the front end of the middle horizontal louver 112, the front end of the lowermost horizontal louver 113, and the end 6c4 of the lower wall 6c. Be placed.
  • the horizontal louver 111 is arranged so that the angle 01 between the inclined surface 6b5 and the uppermost horizontal louver 111 is 13 °.
  • the horizontal louver 112 is arranged so that an angle ⁇ 2 formed by the uppermost horizontal louver 111 and the middle horizontal louver 112 is 10 °.
  • the horizontal louver 113 is arranged so that the angle ⁇ 3 formed by the middle horizontal louver 112 and the lowermost horizontal louver 113 is 10 °.
  • the angle 04 between the lowermost horizontal louver 113 and the tangent line 98 is 12 °.
  • the horizontal louvers 111, 112, and 113 are arranged so that the angles 0 1 to 0 4 are equal to or less than 17 °, the airflow in the flow path divided by the horizontal louvers 111, 112, and 113 Separation of wall force is minimized. Therefore, it is possible to improve the energy saving property by smoothly flowing the airflow.
  • FIG. 6 shows the relationship between the airflow of the crossflow fan 7 and the input (power consumption) required by the fan drive motor (not shown) that drives the crossflow fan 7 when the airflow is sent out. Yes.
  • the vertical axis is the fan drive motor input (unit: W), and the horizontal axis is the airflow (unit: mVmin) of the cross flow fan 7.
  • K1 represents the present embodiment, and shows a case where horizontal lateral Lunos 111, 112, and 113 are arranged as shown in FIG.
  • K2 shows a fourth embodiment shown in FIG. 18 whose details will be described later, and the lateral louver 113 is omitted from this embodiment.
  • K3 shows a fifth embodiment of FIG. 19 whose details will be described later, and the arrangement and shape of the horizontal louvers 111, 112 are changed by omitting the horizontal louver 113 from this embodiment.
  • K4 represents a comparative example of FIG.
  • the lateral louver 113 is omitted, and the lengths of the upper wall 6b and the lower wall 6c are set to 1D and 2. ID, respectively.
  • This is a conventional air conditioner
  • the lengths of the upper wall 6b and the lower wall 6c that are usually formed are as follows.
  • the horizontal louvers 111 and 112 are arranged so as to divide the flow path substantially equally, and smoothly guide the air flow forward and upward.
  • K1 to K3 can be driven with less input (power consumption) than the comparative example (K4).
  • K1 was about 2dB lower than ⁇ 4
  • K2 and ⁇ 3 were equivalent to K1 and the noise level was higher than K1.
  • FIGS. 8 to 11 are diagrams for explaining the difference in power consumption of the crossflow fan 7 between the present embodiment (K1) and the comparative example ( ⁇ 4).
  • FIG. 8 is a side sectional view of the indoor unit 1 schematically showing the state of ⁇ 4.
  • Fig. 9 is a diagram schematically showing the transition of the static pressure of the airflow flowing through the interior of the indoor unit 1 at this time. The vertical axis shows the static pressure of the airflow, and the horizontal axis shows the direction of the airflow. It shows.
  • the cross flow fan 7 has a total static pressure drop due to the pressure loss ( ⁇ Pa +
  • the product ( ⁇ PO X Q) of this static pressure rise ⁇ PO and the flow rate Q of flow ( ⁇ PO X Q) is the work of the cross flow fan 7. If the increase in static pressure by the cross flow fan 7 is smaller than the total decrease in static pressure ( ⁇ ⁇ A Pa + A Pb + A Pc + A Pdl), the cross flow fan 7 Cannot be distributed. Therefore, sufficient air conditioning cannot be performed.
  • FIG. 10 is a side sectional view of the indoor unit 1 schematically showing the state of K1.
  • Fig. 11 is a diagram schematically showing the transition of the static pressure of the airflow flowing through the interior of the indoor unit 1 at this time, as in Fig. 9.
  • the vertical axis shows the static pressure of the airflow, and the horizontal axis Indicates the direction of air flow.
  • the pressure loss ⁇ Pd2 of the airflow sent from the outlet 5 is the pressure loss of the comparative example of FIG.
  • the flow path area is gradually enlarged by the front guide portion 6a of the blower path 6, and then the flow path area is gradually enlarged by the inclined surface 6b5 and the lateral louver 113. For this reason, the airflow flows along the inclined surface 6b5 smoothly after passing through the front guide portion 6a while gradually expanding the basin area.
  • the cross flow fan 7 is the sum of the static pressure drop due to the pressure loss (A Pa +
  • a Pb + A Pc + A Pd2) must be increased at once by subtracting the static pressure increase ⁇ ⁇ 2. For this reason, the static pressure increase ⁇ ⁇ 1 by the cross flow fan 7 becomes A Pa + A Pb + A Pc + ⁇ d2— ⁇ 2.
  • the required static pressure increase ⁇ ⁇ 1 is only ⁇ ⁇ 2 + A Pdl— A Pd2 compared to the static pressure increase ⁇ PO required for the cross flow fan 7 in the comparative example (see FIGS. 8 and 9) Get smaller.
  • the work force A Pdl—A Pd2) X Q of the cross flow fan 7 is reduced, and thus the fan drive motor input (power consumption) can be reduced by this amount to save energy.
  • the pressure loss A Pd2 in the vicinity of the outlet 5 can be reduced, and the upper wall 6b and the lower wall can be reduced.
  • the air along 6c is decelerated, the kinetic energy is converted to static pressure, and the crossflow fan 7 is assisted by the static pressure rise ⁇ P2.
  • the kinetic energy previously taken away by the surrounding air can be fully recovered and converted to static pressure, which can be used for work for blowing air. Therefore, the increase in static pressure due to the cross flow fan 7 can be reduced, and energy saving of the air conditioner can be achieved.
  • the flow velocity (kinetic energy) of the airflow is converted to static pressure (potential energy) in order to gradually and smoothly reduce the wind speed from the lower side of the airflow and convert it to static pressure.
  • the loss at the time is small. For this reason, the conversion efficiency for converting the flow velocity into static pressure is extremely improved, and it is possible to convert a large amount of kinetic energy into static pressure.
  • FIG. 12 is a contour diagram showing the results of examining the input (power consumption, unit: W) of the fan drive motor of the cross flow fan 7 while varying the lengths of the upper wall 6b and the lower wall 6c.
  • the vertical axis indicates the length of the upper wall 6 b and is dimensionless by dividing by the diameter D of the cross flow fan 7.
  • the horizontal axis shows the length of the lower wall 6c, which is made dimensionless by dividing by the diameter D of the crossflow fan 7.
  • the airflow of the crossflow fan 7 is 16m 3 / min—constant.
  • Kl and ⁇ 4 are the same conditions as in Figure 6 above.
  • the power consumption of the cross flow fan 7 can be reduced by increasing the length of the upper wall 6b and the length of the lower wall 6c.
  • the power consumption value changes abruptly in the vicinity of the line L1 where the sum of the length of the upper wall 6b and the length of the lower wall 6c is 3.5D. Therefore, if the sum of the length of the upper wall 6b and the length of the lower wall 6c is 3.5D or more, power consumption can be significantly reduced.
  • the kinetic energy of the airflow continues to be converted to static pressure until the velocity of the airflow becomes sufficiently low, and the kinetic energy of the airflow can be sufficiently converted to static pressure and recovered.
  • FIG. 13 is a contour diagram showing the results of examining the reach distance (unit: m) of the airflow along the ceiling surface while varying the lengths of the upper wall 6b and the lower wall 6c.
  • the reach is the distance to the position where the average wind speed over 30 seconds is 0.05 mZs.
  • the vertical axis shows the length of the upper wall 6b. However, it is made dimensionless by dividing by the diameter D of the crossflow fan 7.
  • the horizontal axis shows the length of the lower wall 6c, which is made dimensionless by dividing by the diameter D of the crossflow fan 7.
  • the airflow of the cross flow fan 7 is 16m 3 / min—constant.
  • Kl and ⁇ 4 are the same conditions as in Figure 6 above.
  • the length of the upper wall 6b and the lower wall 6c is less than 0.5D and less than 1.5D, respectively, the length is extremely short and the cross flow fan 7 is not formed, so measurement is omitted. . Also, since the measurement points in the figure are finite, the contour diagram is completed using interpolation and prediction of each measurement value.
  • the reach distance varies greatly depending on the length of the upper wall 6b, which is less dependent on the length of the lower wall 6c.
  • it is effective to prevent the kinetic energy from dissipating in the upward direction of the air current, which is greatly affected by the length of the upper wall 6b.
  • the reach distance rapidly changes in the vicinity of the line L2 where the length of the upper wall 6b is 1.5D. That is, the airflow blown out from the outlet 5 immediately induces the movement of the surrounding air due to viscosity, and the kinetic energy of the airflow is gradually taken away by the surrounding air.
  • the length of the upper wall 6b is set to 1.5D or more, the upper wall 6b has a sufficient length, so that the air movement in the upward direction of the airflow is drastically reduced. As a result, the kinetic energy is not lost and the airflow reaches far. In other words, even in the airflow after sufficient kinetic energy has been recovered, a large reachable distance can be secured by making the length of the upper wall 6b 1.5D or more.
  • the air flow path 6 is divided into a plurality of flow paths in the vertical direction, and the flow paths are made longer in order as the lower flow paths are relatively short and go upward.
  • the aerodynamic kinetic energy having the non-uniform energy density unique to the cross flow fan 7 can be efficiently recovered. Therefore, in the present embodiment, the air passage 1 is divided into four vertically by the horizontal louvers 111, 112, 113 during the operation of the air conditioner 1.
  • the air flow path is divided into two flow paths.
  • each divided flow path can be sequentially lengthened as it goes upward.
  • angles ⁇ 1 to ⁇ 4 representing the enlargement ratio of the channel area of each channel be in the range of 10 ° to 15 °.
  • angles 0 1 to 04 are larger than 15 °, the airflow flowing through each flow path is separated from the wall surface or rapidly decelerated, and loss occurs when the kinetic energy is converted to static pressure. The possibility increases. If the angles 0 1 to 0 4 are smaller than 10 °, the path is unnecessarily extended, and the amount of kinetic energy due to the friction between the airflow and the wall increases accordingly.
  • the magnitude of the kinetic energy of the airflow is proportional to the square of the flow velocity.
  • the wind speed of the airflow that flows through the upper part of the airflow path 6 is several times the wind speed of the airflow that flows through the lower part of the airflow path 6 (near the lower wall 6c).
  • the kinetic energy of the airflow that flows through the upper part of the ventilation path 6 is several tens of times the kinetic energy of the airflow that flows through the lower part of the ventilation path 6 (near the lower wall 6c)
  • the amount of kinetic energy to be recovered is very large in the upper part of the ventilation path 6, a sufficiently long flow path is required.
  • the angle oc (see FIG. 2) representing the enlargement ratio of the flow path area of the front guide portion 6a of the air blowing path 6 is preferably about 20 ° as described above.
  • the angle ⁇ is larger than that, the airflow passing through the front guide 6a is separated from the wall surface or decelerated abruptly, resulting in energy loss.
  • the channel is divided by the horizontal louver and the channel area is expanded in the range of 10 ° to 15 °, it can only be divided into two. As a result, it is extremely difficult to effectively recover kinetic energy from an air current that is several tens of times wide as described above.
  • the middle horizontal louver 112 faces the bent portion 6b4, the rear end thereof is arranged behind the bent portion 6b4, and is arranged substantially parallel to the upper surface 6b3 of the front guide portion 6a.
  • the flow path of the airflow flowing through the front guide portion 6a is divided into two vertically.
  • the lower flow path of the horizontal louver 112 can be further divided into two by the horizontal louver 113 so that 0 3 and 04 are in the range of 10 ° to 15 °.
  • the upper wall 6b is bent upward at the bent portion 6b4 facing the lateral louver 112.
  • the gradually expanding flow path formed by the horizontal louver 112 and the inclined surface 6b5 is formed by the uppermost horizontal louver 111.
  • the horizontal louver 111 is positioned above the horizontal louver 112 by 0 °, 0 2 from 10 ° to 15 °. It can be divided into two in the range of. Note that it is not very efficient to bend the lower surface 6c3 of the front guide portion 6a downward and expand it in the same way because the wind speed is slow.
  • the horizontal louvers 111, 112, and 113 are configured to be rotatable around a rotation axis (not shown), the wind direction can be changed in other arrangements.
  • the sum of the length of the upper wall 6b and the length of the lower wall 6c of the air flow path 6 on the downstream side of the cross flow fan 7 is 3.5 times the diameter D of the cross flow fan 7 or more. Therefore, during the operation of the air conditioner, air smoothly flows over a long distance along the upper wall 6b and the lower wall 6c of the air blowing path 6. As a result, the air flow disturbance near the outlet 5 is reduced and the pressure loss A Pd2 is reduced accordingly.
  • the kinetic energy can be recovered to increase the reach distance of the airflow with a reduced flow velocity.
  • the air sent out from the outlet 5 reaches the ceiling of the room and sequentially travels through the wall surface facing the air conditioner, the floor surface, and the wall surface on the air conditioner side. Therefore, the conditioned air stream reaches every corner of the room, and the air stream greatly stirs the entire room. Therefore, it is possible to obtain a comfortable space with almost no direct wind by equalizing the temperature distribution of the entire living area except a part of the upper part of the room.
  • the cross flow fan 7 generally causes surging when the pressure loss in the flow path increases. Rub. As a result, the desired air volume cannot be obtained or the noise may increase significantly.
  • the indoor heat exchanger 9 is bent and configured with a plurality of stages and a plurality of rows of refrigerant tubes as in the present embodiment, a very high pressure loss occurs. For this reason, it is necessary to take a countermeasure against surging by increasing the number of revolutions of the cross flow fan 7 considerably. As a result, the noise of the cross flow fan 7 increases and the energy saving performance deteriorates.
  • FIG. 14 is a side sectional view showing the indoor unit of the air conditioner of the second embodiment.
  • the same parts as those in the first embodiment shown in FIGS. 1 to 13 are denoted by the same reference numerals.
  • the front panel 3 is pivotally supported by the rotating shaft 22 at the lower end. Further, the front panel 3 can be bent by a rotating shaft 23 arranged on the front surface. Other parts are the same as in the first embodiment.
  • the front panel 3 is arranged so that the upper end is in contact with the upper part of the casing, as shown in FIG. Further, the outlet 5 is shielded by the horizontal louvers 111 and 112 as in the first embodiment.
  • the front panel 3 When the air conditioner is driven, as shown in FIG. 15, the front panel 3 is rotated by the rotating shafts 22 and 23, and the front panel 3 between the rotating shafts 22 and 23 is inclined surface 6b5 of the air flow path 6 Is formed.
  • the length of the upper wall 6b of the air flow path 6 on the downstream side of the cross flow fan 7 is formed to be 1.5D or more, where D is the diameter of the cross flow fan 7.
  • the sum of the length of the upper wall 6b and the length of the lower wall 6c of the air flow path 6 on the downstream side of the cross flow fan 7 is formed to be 3.5D or more. Therefore, the same effect as the first embodiment can be obtained.
  • FIG. 16 is a side sectional view showing the indoor unit of the air conditioner of the third embodiment.
  • the same reference numerals are used for the same parts as those in the first embodiment shown in FIGS. Is attached.
  • the lower portion of the front panel 3 is opened, and a movable panel 21 that closes the opening is pivotally supported at the lower end by a rotating shaft 22.
  • Other parts are the same as in the first embodiment.
  • the movable panel 21 is arranged so as to block the lower part of the front panel 3 as shown in FIG. Further, the outlet 5 is shielded by the horizontal louvers 111 and 112 as in the first embodiment.
  • the movable panel 21 When the air conditioner is driven, as shown in FIG. 17, the movable panel 21 is rotated by the rotation shaft 22, and the inclined surface 6 b 5 of the blowing path 6 is formed by the movable panel 21.
  • the length of the upper wall 6b of the blower passage 6 on the downstream side of the cross flow fan 7 is formed to be 1.5D or more, where D is the diameter of the single fan 7 of the cross fan.
  • the sum of the length of the upper wall 6b and the length of the lower wall 6c of the air flow path 6 on the downstream side of the cross flow fan 7 is formed to be 3.5D or more. Therefore, the same effect as that of the first embodiment can be obtained.
  • FIG. 18 is a side sectional view showing the indoor unit of the air conditioner of the fourth embodiment.
  • the same parts as those in the first embodiment shown in FIGS. 1 to 13 are given the same reference numerals.
  • the lateral louver 113 of the first embodiment is omitted as described above.
  • Other parts including the lengths of the upper wall 6b and the lower wall 6c of the air blowing path 6 are the same as those in the first embodiment.
  • the lowermost horizontal louver 113 is omitted as compared with the air conditioner of the first embodiment, so that the efficiency of the recovery of the kinetic energy of the airflow flowing under the air flow path 6 is eliminated. Slightly decreases.
  • the power consumption can be made smaller than in Comparative Example K4 in FIG. 7, and energy saving can be achieved compared to the conventional example.
  • FIG. 19 is a side sectional view showing the indoor unit of the air conditioner of the fifth embodiment.
  • the same parts as those in the first embodiment shown in FIGS. 1 to 13 are given the same reference numerals.
  • the lateral louver 113 of the first embodiment is omitted, and the length and arrangement of the lateral louvers 111, 112 are changed.
  • Other parts including the lengths of the upper wall 6b and the lower wall 6c of the air blowing path 6 are the same as those in the first embodiment.
  • the horizontal louvers 111, 112 arranged above and below are opposed to the bent portion 6b4, and the rear ends thereof are arranged behind the bent portion 6b4.
  • the front ends of the horizontal louvers 111, 112 are arranged at substantially the same position in front of the bent portion 6b4 and in the front-rear direction. Further, the lateral louvers 111 and 112 form a flow path in which the front guide portion 6a of the air blowing path 6 is divided at substantially equal intervals.
  • the efficiency of recovering the kinetic energy of the airflow flowing in the air supply path 6 is lower than that of the air conditioner of the first and second embodiments.
  • the power consumption can be made smaller than in the comparative example K4 in FIG. 7, and energy saving can be achieved compared to the conventional example.
  • the present invention can be used for an air conditioner that takes in indoor air and harmonizes it.

Abstract

Climatiseur comportant un orifice (4) de prise d'air servant à introduire l'air présent dans une pièce dans le boîtier d'une machine d'intérieur (1), un orifice (5) de refoulement d'air formé à la partie inférieure du boîtier, un passage (6) d'écoulement d'air servant à faire communiquer l'orifice (4) de prise d'air avec l'orifice (5) de refoulement d'air, un échangeur (9) de chaleur d'intérieur doté de tubes à agent frigorigène agencés en une pluralité d'étages et de rangées parallèles les uns aux autres et disposés de façon incurvée le long de la surface intérieure du boîtier de façon à faire face à l'orifice (4) de prise d'air, et un ventilateur (7) à écoulement transversal disposé entre l'échangeur (9) de chaleur d'intérieur dans le passage (6) d'écoulement d'air et l'orifice (5) de refoulement d'air. Le passage (6) d'écoulement d'air comprend une partie (6a) de guidage avant qui guide l'air vers le côté avant inférieur et présente une aire de passage d'écoulement progressivement agrandie en direction du côté aval. La somme des longueurs de la paroi (6b) supérieure et de la paroi (6c) inférieure du passage (6) d'écoulement d'air plus près du côté aval que le ventilateur (7) à écoulement transversal est fixée à au moins 3,5 fois le diamètre du ventilateur (7) à écoulement transversal.
PCT/JP2006/326032 2006-01-20 2006-12-27 Climatiseur WO2007083501A1 (fr)

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EP06843414A EP1975522B1 (fr) 2006-01-20 2006-12-27 Climatiseur
CN2006800513913A CN101360954B (zh) 2006-01-20 2006-12-27 空气调节机

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JP2006011832A JP4014618B2 (ja) 2006-01-20 2006-01-20 空気調和機
JP2006-011822 2006-01-20
JP2006-011832 2006-01-20
JP2006011822A JP4014617B2 (ja) 2006-01-20 2006-01-20 空気調和機

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WO2023005329A1 (fr) * 2021-07-28 2023-02-02 青岛海尔空调器有限总公司 Unité intérieure de climatiseur murale

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CN101788164B (zh) * 2009-04-02 2012-08-22 宁波奥克斯空调有限公司 挂式空调室内机
CN105757792B (zh) * 2014-12-18 2019-02-19 奥克斯空调股份有限公司 空调室内机
CN104595975B (zh) * 2015-01-05 2017-10-10 美的集团武汉制冷设备有限公司 具有轴流风机的空调器

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WO2023005329A1 (fr) * 2021-07-28 2023-02-02 青岛海尔空调器有限总公司 Unité intérieure de climatiseur murale

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EP1975522B1 (fr) 2013-02-27
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EP1975522A4 (fr) 2011-11-02
KR20080077699A (ko) 2008-08-25

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