US20240077214A1 - Indoor unit and air-conditioning apparatus - Google Patents

Indoor unit and air-conditioning apparatus Download PDF

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Publication number
US20240077214A1
US20240077214A1 US18/261,724 US202118261724A US2024077214A1 US 20240077214 A1 US20240077214 A1 US 20240077214A1 US 202118261724 A US202118261724 A US 202118261724A US 2024077214 A1 US2024077214 A1 US 2024077214A1
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US
United States
Prior art keywords
air
indoor unit
downstream
flow fan
air passage
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Abandoned
Application number
US18/261,724
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English (en)
Inventor
Atsushi Kono
Takuya Teramoto
Yuki UGAJIN
Koji Yamaguchi
Tetsuo Yamashita
Takashi Ikeda
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TERAMOTO, TAKUYA, KONO, ATSUSHI, YAMASHITA, TETSUO, IKEDA, TAKASHI, UGAJIN, Yuki, YAMAGUCHI, KOJI
Publication of US20240077214A1 publication Critical patent/US20240077214A1/en
Abandoned legal-status Critical Current

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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
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0011—Indoor units, e.g. fan coil units characterised by air outlets
    • 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
    • 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
    • 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
    • F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
    • 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
    • F24F13/081—Air-flow control members, e.g. louvres, grilles, flaps or guide plates for guiding air around a curve
    • 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
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers

Definitions

  • the present disclosure relates to an indoor unit including a cross flow fan, and also relates to an air-conditioning apparatus.
  • An indoor unit of an air-conditioning apparatus includes a cross flow fan.
  • the indoor unit has a problem in that as air is more likely to flow reversely into the indoor unit from an air outlet, surging occurs in which the air is alternately blown out and sucked in through the air outlet. Therefore, an indoor unit with an improved surging-proof ability has been proposed (see, for example, Patent Literature 1).
  • the indoor unit in Patent Literature 1 includes a cross flow fan disposed in a casing, and a stabilizer to form an air flow passage between the cross flow fan and an air outlet.
  • the stabilizer has a protruding portion disposed at a longitudinal end portion of the air outlet.
  • a rough surface is provided on which irregularities are formed. Due to this rough surface of the stabilizer, the blown air is less likely to flow away from the stabilizer at the end portion of the air outlet. This prevents the air from flowing reversely from the air outlet, which improves the surging-proof ability.
  • the present disclosure has been made to solve the above problems, and it is an object of the present disclosure to provide an indoor unit and an air-conditioning apparatus in which a reduction in its surging-proof ability is lessened even when a cross flow fan is under high operational load, and to provide an air-conditioning apparatus.
  • An indoor unit includes: a casing that has an air outlet and an air inlet, and inside which an air passage is formed; a cross flow fan disposed in the air passage and configured to blow out, through the air outlet, air sucked in from the air inlet; a stabilizer configured to stabilize vortex of air caused by circulation of air and generated inside the cross flow fan upon rotation thereof; and a guide wall having a surface defining an outlet side air passage being a part of the air passage, the part being in downstream of the cross flow fan, wherein the stabilizer has a first surface that defines a surface opposite to the guide wall in the outlet side air passage, and a part of the outlet side air passage is formed such that a distance in a vertical direction from the first surface to the guide wall gradually decreases toward the downstream.
  • An air-conditioning apparatus includes: the indoor unit described above; and an outdoor unit connected to the indoor unit by pipes to form a refrigerant circuit in which refrigerant circulates.
  • a part of the outlet side air passage is formed such that a distance in a vertical direction from the first surface to the guide wall gradually decreases toward the downstream, thus to evenly distribute airflow in the outlet side air passage.
  • FIG. 1 is a perspective view illustrating the external appearance of an indoor unit according to Embodiment 1.
  • FIG. 2 is a vertical cross-sectional schematic diagram of the indoor unit according to Embodiment 1.
  • FIG. 3 is an enlarged vertical cross-sectional schematic diagram illustrating the relevant parts of the indoor unit according to Embodiment 1.
  • FIG. 4 is an enlarged vertical cross-sectional schematic diagram illustrating the relevant parts of the indoor unit according to Embodiment 2.
  • FIG. 5 is a first enlarged vertical cross-sectional schematic diagram illustrating the relevant parts of the indoor unit according to Embodiment 3.
  • FIG. 6 is a second enlarged vertical cross-sectional schematic diagram illustrating the relevant parts of the indoor unit according to Embodiment 3.
  • FIG. 7 is a cross-sectional view taken along the line between the Z-Z arrows in FIG. 6 .
  • FIG. 8 is a vertical cross-sectional schematic diagram of the indoor unit according to Embodiment 4.
  • FIG. 9 illustrates an example of the configuration of an air-conditioning apparatus according to Embodiment 5.
  • FIG. 1 is a perspective view illustrating the external appearance of an indoor unit 100 according to Embodiment 1.
  • FIG. 2 is a vertical cross-sectional schematic diagram of the indoor unit 100 according to Embodiment 1.
  • Embodiment 1 The configuration of the indoor unit 100 according to Embodiment 1 is described below.
  • terms that represent directions including, for example, “up,” “down,” “right,” “left,” “front,” and “rear,” are appropriately used for the sake of easy understanding. However, these terms are used merely for description purposes, and the embodiments are not limited by these terms.
  • the terms, such as “up,” “down,” “right,” “left,” “front,” and “rear,” are used where the indoor unit 100 is viewed from the front (viewed in the direction of arrow X in FIG. 2 ).
  • the indoor unit 100 according to Embodiment 1 is a ceiling concealed indoor unit that is installed and concealed in a ceiling.
  • the indoor unit 100 is not limited thereto, but may be, for example, a wall-mounted indoor unit.
  • the indoor unit 100 includes a box-shaped casing 1 concealed in a ceiling, a flat plate-like cosmetic panel 2 provided at a bottom portion of the casing 1 to serve as a design surface, and a flat plate-like suction grille 3 that is rotatably attached to the cosmetic panel 2 .
  • an air inlet 1 a is formed through which room air is sucked into the casing 1 .
  • an air outlet 1 b is formed through which conditioned air is blown out to the outside.
  • the air inlet 1 a is covered by the suction grille 3 when the suction grille 3 is closed.
  • the air inlet 1 a is provided with a filter 7 that is a porous part configured to remove dust, bacteria, and the like from the air. Room air sucked in from the air inlet 1 a passes through the filter 7 and is drawn into the casing 1 .
  • the air outlet 1 b is provided with an up-down vane 9 a configured to change the airflow direction within a predetermined range of the up-down direction, and left-right vanes 9 b configured to change the airflow direction within a predetermined range of the left-right direction.
  • a cross flow fan 6 In the casing 1 , a cross flow fan 6 , a motor (not illustrated), and a heat exchanger 5 are provided.
  • the cross flow fan 6 is disposed to be rotatable in a direction illustrated by the arrow Y in FIG. 2 , and is configured to generate airflow.
  • the motor is connected to the cross flow fan 6 and rotationally driven.
  • the heat exchanger 5 is disposed while being inclined to the horizontal plane and the depth direction, and is configured to exchange heat between refrigerant and room air sucked into the casing 1 through the air inlet 1 a by the cross flow fan 6 to produce conditioned air.
  • an air passage 20 is formed such that air passes through the heat exchanger 5 from the air inlet 1 a and flows to the air outlet 1 b .
  • the heat exchanger 5 and the cross flow fan 6 are disposed in the air passage 20 .
  • the heat exchanger 5 is made up of an upper heat exchanger 5 a and a lower heat exchanger 5 b . One end of the upper heat exchanger 5 a is connected to one end of the lower heat exchanger 5 b .
  • the heat exchanger 5 is disposed in such a manner as to form an obtuse angle between a surface of the upper heat exchanger 5 a opposite to the cross flow fan 6 , and a surface of the lower heat exchanger 5 b opposite to the cross flow fan 6 .
  • a drain pan 4 is disposed below the heat exchanger 5 in such a manner as to be opposite to the lower heat exchanger 5 b in its entirety and opposite to the lower end portion of the upper heat exchanger 5 a .
  • the drain pan 4 is configured to collect drain water from the heat exchanger 5 .
  • the stabilizer 10 divides the air passage 20 into an inlet side air passage 20 a located upstream of the cross flow fan 6 and an outlet side air passage 20 b located downstream of the cross flow fan 6 .
  • the guide wall 11 has a surface defining the outlet side air passage 20 b.
  • the cross flow fan 6 connected to the motor rotates, so that room air is sucked in from the air inlet 1 a .
  • the room air sucked in from the air inlet 1 a passes through the filter 7 and is sucked into the casing 1 .
  • the room air sucked into the casing 1 passes through the heat exchanger 5 during the process of flowing through the inlet side air passage 20 a .
  • the room air exchanges heat with refrigerant and becomes conditioned.
  • the conditioned air flows through the outlet side air passage 20 b and is blown out through the air outlet 1 b toward the room.
  • the direction of the conditioned air, to be blown out through the air outlet 1 b is changed depending on the directions of the up-down vane 9 a and the left-right vanes 9 b.
  • FIG. 3 is an enlarged vertical cross-sectional schematic diagram illustrating the relevant parts of the indoor unit 100 according to Embodiment 1.
  • the stabilizer 10 is configured to stabilize vortex of air caused by circulation of air and generated inside the cross flow fan 6 upon rotation of the cross flow fan 6 .
  • the stabilizer 10 has a first surface 10 a , a second surface 10 b , and a tongue-shaped portion 10 c .
  • the first surface 10 a defines a surface opposite to the guide wall 11 in the outlet side air passage 20 b .
  • the second surface 10 b is opposite to the cross flow fan 6 .
  • the tongue-shaped portion 10 c is provided between the first surface 10 a and the second surface 10 b .
  • the tongue-shaped portion 10 c is the apex of a convex portion of the stabilizer 10 that is convex toward the cross flow fan 6 .
  • the second surface 10 b is formed along the outer circumference of the cross flow fan 6 .
  • a gap is formed between the second surface 10 b and the cross flow fan 6 . Note that the gap between the second surface 10 b and the cross flow fan 6 is minimized at the most downstream location of the second surface 10 b in the rotation direction of the cross flow fan 6 .
  • the first surface 10 a has a flow-reduction surface 10 d formed such that the cross-sectional area of the outlet side air passage 20 b is reduced from the tongue-shaped portion 10 c toward the downstream.
  • This flow-reduction surface 10 d is inclined in such a manner as to gradually approach the guide wall 11 toward the downstream. Specifically, as illustrated by the dotted arrows in FIG. 3 , the flow-reduction surface 10 d is formed such that a distance in a vertical direction from the flow-reduction surface 10 d to the guide wall 11 gradually decreases toward the downstream.
  • the position of the tongue-shaped portion 10 c is illustrated by a dotted line H 1
  • the position of the lower end of the air outlet 1 b is illustrated by a dotted line H 2
  • the intermediate position between them is illustrated by a dotted line H 3
  • the flow-reduction surface 10 d is formed at a position upstream of the intermediate position (the dotted line H 3 ). The reason for this is to help conditioned air to be smoothly blown out downward through the air outlet 1 b .
  • forming the flow-reduction surface 10 d at a position downstream of the intermediate position (the dotted line H 3 ) makes the conditioned air less likely to be smoothly blown out downward through the air outlet 1 b .
  • the flow-reduction surface 10 d may be shaped into a flat surface forming a straight line in side view as illustrated in FIG. 3 , or may be shaped into a curved surface forming a convex curve toward the guide wall 11 in side view.
  • the stabilizer 10 is provided with the flow-reduction surface 10 d , thus to evenly distribute airflow in the outlet side air passage 20 b .
  • This increases the volume of airflow that passes along the stabilizer 10 .
  • a low airflow-speed region is less likely to be generated in the outlet side air passage 20 b and thus air is less likely to flow reversely from the air outlet 1 b . This can accordingly lessen a reduction in the surging-proof ability.
  • the airflow speed is lower on the downstream side in the rotation direction of the cross flow fan 6 , while being higher on the upstream side in the rotation direction of the cross flow fan 6 .
  • the flow-reduction surface 10 d is formed on the lower airflow-speed side, that is, on the first surface 10 a of the stabilizer 10 . This configuration can lessen an increase in the pressure loss, compared to the case where a flow-reduction surface with an inclination is formed on the higher airflow-speed side, that is, on the guide wall 11 .
  • the indoor unit 100 includes the casing 1 that has the air outlet 1 b and the air inlet 1 a , and inside which the air passage 20 is formed, the cross flow fan 6 disposed in the air passage 20 and configured to blow out, through the air outlet 1 b , air sucked in from the air inlet 1 a , the stabilizer 10 configured to stabilize vortex of air caused by circulation of air and generated inside the cross flow fan 6 upon rotation of the cross flow fan 6 , and the guide wall 11 having a surface defining the outlet side air passage 20 b being a part of the air passage 20 , the part being in downstream of the cross flow fan 6 .
  • the stabilizer 10 has the first surface 10 a that defines a surface opposite to the guide wall 11 in the outlet side air passage 20 b .
  • a part of the outlet side air passage 20 b is formed such that a distance in a vertical direction from the first surface 10 a to the guide wall 11 gradually decreases toward the downstream.
  • a part of the outlet side air passage 20 b is formed such that a distance in a vertical direction from the first surface 10 a to the guide wall 11 gradually decreases toward the downstream, thus to evenly distribute airflow in the outlet side air passage 20 b .
  • the first surface 10 a has the flow-reduction surface 10 d that is inclined in such a manner as to gradually approach the guide wall 11 toward the downstream.
  • the first surface 10 a of the stabilizer 10 has the flow-reduction surface 10 d that is inclined in such a manner as to gradually approach the guide wall 11 from the tongue-shaped portion 10 c toward the downstream. That is, the flow-reduction surface 10 d is formed on the lower airflow-speed side, that is, on the first surface 10 a of the stabilizer 10 . This can lessen an increase in the pressure loss, compared to the case where a flow-reduction surface with an inclination is formed on the higher airflow-speed side, that is, on the guide wall 11 .
  • Embodiment 2 will be described. The descriptions of the parts overlapping with those of Embodiment 1 will be omitted, and the same parts as or the corresponding parts to those of Embodiment 1 will be designated by the same reference numerals.
  • FIG. 4 is an enlarged vertical cross-sectional schematic diagram illustrating the relevant parts of the indoor unit 100 according to Embodiment 2.
  • the first surface 10 a of the stabilizer 10 has a downstream surface 10 e located downstream of the flow-reduction surface 10 d .
  • a vertical plane a dotted line V
  • a plane connecting an upstream end and a downstream end of the downstream surface 10 e is defined as ⁇ 2
  • ⁇ 1 an angle formed between the vertical plane (the dotted line V) and a plane connecting an upstream end and a downstream end of the flow-reduction surface 10 d
  • ⁇ 1 is smaller than ⁇ 1 . Note that since ⁇ 2 is equal to 0 degrees in FIG. 4 , FIG. 4 omits illustration of ⁇ 2 .
  • the angle formed between the vertical plane (the dotted line V) and the plane connecting the upstream end and the downstream end of the downstream surface 10 e is smaller than the angle formed between the vertical plane (the dotted line V) and the plane connecting the upstream end and the downstream end of the flow-reduction surface 10 d , so that the outlet side air passage 20 b is inclined gently on the downstream side of the flow-reduction surface 10 d .
  • this helps stabilize airflow in the outlet side air passage 20 b toward the air outlet 1 b , and increases the volume of airflow that passes along the stabilizer 10 , which can improve the surging-proof ability.
  • the flow-reduction surface 10 d and the downstream surface 10 e are formed such that the difference between ⁇ 2 and ⁇ 1 is equal to or smaller than 20 degrees.
  • the reason for this is that if the difference between ⁇ 2 and ⁇ 1 is too large, airflow is more likely to flow away from the stabilizer 10 , and thus the airflow blown out from the cross flow fan 6 flows away from the stabilizer 10 , and thereafter is more likely to hit the stabilizer 10 again, so that the pressure loss in the outlet side air passage 20 b is more likely to increase. Therefore, provided that the difference between ⁇ 2 and ⁇ 1 is equal to or smaller than 20 degrees, the indoor unit 100 can allow for an increase in the pressure loss in the outlet side air passage 20 b.
  • the first surface 10 a has the downstream surface 10 e located downstream of the flow-reduction surface 10 d , and the angle formed between the vertical plane (the dotted line V) and the plane connecting the upstream end and the downstream end of the downstream surface 10 e is smaller than the angle formed between the vertical plane (the dotted line V) and the plane connecting the upstream end and the downstream end of the flow-reduction surface 10 d.
  • the angle formed between the vertical plane (the dotted line V) and the plane connecting the upstream end and the downstream end of the downstream surface 10 e is smaller than the angle formed between the vertical plane (the dotted line V) and the plane connecting the upstream end and the downstream end of the flow-reduction surface 10 d , so that the outlet side air passage 20 b is inclined gently on the downstream side of the flow-reduction surface 10 d .
  • this helps stabilize airflow in the outlet side air passage 20 b toward the air outlet 1 b , and increases the volume of airflow that passes along the stabilizer 10 , which can improve the surging-proof ability.
  • Embodiment 3 will be described. The descriptions of the parts overlapping with those of Embodiments 1 and 2 will be omitted, and the same parts as or the corresponding parts to those of Embodiments 1 and 2 will be designated by the same reference numerals.
  • FIG. 5 is a first enlarged vertical cross-sectional schematic diagram illustrating the relevant parts of the indoor unit 100 according to Embodiment 3. Note that in FIG. 5 , the position of the end portion of the cross flow fan 6 located nearest the air outlet in the horizontal direction is illustrated by a dotted line B, the position of the tongue-shaped portion 10 c is illustrated by a dotted line A, and the position of the downstream end of the flow-reduction surface 10 d is illustrated by a dotted line C.
  • Embodiment 3 as illustrated in FIG. 5 , the end portion (the dotted line B) of the cross flow fan 6 located nearest the air outlet in the horizontal direction is positioned between the tongue-shaped portion 10 c (the dotted line A) and the downstream end (the dotted line C) of the flow-reduction surface 10 d in the horizontal direction.
  • This configuration helps airflow, blown out from the cross flow fan 6 , to easily approach the stabilizer 10 when the cross flow fan 6 is under normal operational load. As a result, even when the operational load of the cross flow fan 6 increases, the airflow blown out from the cross flow fan 6 is less likely to approach the guide wall 11 . Therefore, a low airflow-speed region is less likely to be generated in the outlet side air passage 20 b and thus air is less likely to flow reversely from the air outlet 1 b . This can accordingly lessen a reduction in the surging-proof ability.
  • FIG. 6 is a second enlarged vertical cross-sectional schematic diagram illustrating the relevant parts of the indoor unit 100 according to Embodiment 3.
  • FIG. 7 is a cross-sectional view taken along the line between the Z-Z arrows in FIG. 6 .
  • rotational axis direction As illustrated in FIGS. 6 and 7 , the distance from the downstream end of the flow-reduction surface 10 d to the guide wall 11 differs in the rotational axis direction of the cross flow fan 6 (hereinafter, simply referred to as “rotational axis direction”). Note that the rotational axis direction in FIG. 6 is perpendicular to the drawing.
  • a distance from the downstream end of the flow-reduction surface 10 d to the guide wall 11 at opposite end portions of the outlet side air passage 20 b in the rotational axis direction is defined as Lb 1
  • a distance from the downstream end of the flow-reduction surface 10 d to the guide wall 11 at the central portion of the outlet side air passage 20 b in the rotational axis direction is defined as Lb 2
  • Lb 1 is smaller than Lb 2 .
  • the distance from the downstream end of the flow-reduction surface 10 d to the guide wall 11 at opposite end portions of the outlet side air passage 20 b in the rotational axis direction is set shorter than the distance from the downstream end of the flow-reduction surface 10 d to the guide wall 11 at the central portion of the outlet side air passage 20 b in the rotational axis direction.
  • This configuration can increase the volume of airflow that passes along the stabilizer 10 at opposite ends of the outlet side air passage 20 b in the rotational axis direction, while lessening an increase in the pressure loss at the central portion of the outlet side air passage 20 b in the rotational axis direction. Consequently, this can lessen a reduction in the surging-proof ability, while lessening an increase in the pressure loss in the outlet side air passage 20 b.
  • the end portion of the cross flow fan 6 located nearest the air outlet 1 b in the horizontal direction is positioned between the tongue-shaped portion 10 c and the downstream end of the flow-reduction surface 10 d in the horizontal direction.
  • this configuration helps airflow, blown out from the cross flow fan 6 , to easily approach the stabilizer 10 when the cross flow fan 6 is under normal operational load.
  • the airflow blown out from the cross flow fan 6 is less likely to approach the guide wall 11 . Therefore, a low airflow-speed region is less likely to be generated in the outlet side air passage 20 b and thus air is less likely to flow reversely from the air outlet 1 b . This can accordingly lessen a reduction in the surging-proof ability.
  • the distance from the downstream end of the flow-reduction surface 10 d to the guide wall 11 differs in the rotational axis direction of the cross flow fan 6 . This distance is shorter at each end portion in the rotational axis direction than at the central portion in the rotational axis direction.
  • this configuration can increase the volume of airflow that passes along the stabilizer 10 at opposite ends of the outlet side air passage 20 b in the rotational axis direction, while lessening an increase in the pressure loss at the central portion of the outlet side air passage 20 b in the rotational axis direction. Consequently, this can lessen a reduction in the surging-proof ability, while lessening an increase in the pressure loss in the outlet side air passage 20 b.
  • Embodiment 4 will be described. The descriptions of the parts overlapping with those of Embodiments 1 to 3 will be omitted, and the same parts as or the corresponding parts to those of Embodiments 1 to 3 will be designated by the same reference numerals.
  • FIG. 8 is a vertical cross-sectional schematic diagram of the indoor unit 100 according to Embodiment 4. Note that in FIG. 8 , the position of the tongue-shaped portion 10 c is illustrated by the dotted line A, and the end portion of the heat exchanger 5 located nearest the air outlet in the horizontal direction is illustrated by a dotted line D.
  • the end portion (the dotted line D) of the heat exchanger 5 located nearest the air outlet in the horizontal direction is positioned closer to the air outlet 1 b than the tongue-shaped portion 10 c (the dotted line A) in the horizontal direction.
  • the end portion (the dotted line D) of the heat exchanger 5 located nearest the air outlet in the horizontal direction may be at the same position as the tongue-shaped portion 10 c (the dotted line A) in the horizontal direction.
  • This configuration can increase the heat transfer area of the heat exchanger 5 , and accordingly improve heat exchange efficiency. As the heat transfer area of the heat exchanger 5 increases, air passes through the heat exchanger 5 at a decreased speed. This lessens an increase in the pressure loss in the air passage, further can secure a sufficient margin for the stall point of the cross flow fan 6 , and accordingly can lessen a reduction in the surging-proof ability.
  • the indoor unit 100 includes the heat exchanger 5 configured to exchange heat between refrigerant and air sucked in from the air inlet 1 a by the cross flow fan 6 .
  • the end portion of the heat exchanger 5 located nearest the air outlet 1 b in the horizontal direction is at the same position as the tongue-shaped portion 10 c or is positioned closer to the air outlet 1 b than the tongue-shaped portion 10 c in the horizontal direction.
  • this configuration can increase the heat transfer area of the heat exchanger 5 , and accordingly improve heat exchange efficiency.
  • air passes through the heat exchanger 5 at a decreased speed. This lessens an increase in the pressure loss in the air passage, further can secure a sufficient margin for the stall point of the cross flow fan 6 , and accordingly can lessen a reduction in the surging-proof ability.
  • Embodiment 5 will be described. The descriptions of the parts overlapping with those of Embodiments 1 to 4 will be omitted, and the same parts as or the corresponding parts to those of Embodiments 1 to 4 will be designated by the same reference numerals.
  • FIG. 9 illustrates an example of the configuration of an air-conditioning apparatus according to Embodiment 5.
  • the indoor unit 100 and an outdoor unit 200 are connected by a gas refrigerant pipe 300 and a liquid refrigerant pipe 400 , forming a refrigerant circuit 500 in which refrigerant circulates.
  • the indoor unit 100 is any of those described in Embodiments 1 to 4.
  • the outdoor unit 200 includes a compressor 201 , a flow switching device 202 , an outdoor heat exchanger 203 , an outdoor fan 204 , and an expansion device 205 .
  • the compressor 201 is configured to suction low-temperature low-pressure refrigerant, compress the suctioned refrigerant into a high-temperature high-pressure state, and discharge the compressed high-temperature high-pressure refrigerant.
  • the compressor 201 is, for example, an inverter compressor whose capacity is controlled by changing the operational frequency. The capacity is the volume of refrigerant to be delivered per unit time.
  • the flow switching device 202 is, for example, a four-way valve, and configured to change the refrigerant flow direction to switch the operation mode between cooling and heating. Note that, in place of the four-way valve, a combination of a two-way valve and a three-way valve, for example, may be used as the flow switching device 202 .
  • the outdoor heat exchanger 203 is configured to exchange heat between outside air and refrigerant.
  • the outdoor heat exchanger 203 serves as an evaporator to evaporate and gasify the refrigerant.
  • the outdoor heat exchanger 203 serves as a condenser to condense and liquefy the refrigerant.
  • the outdoor fan 204 is provided in the vicinity of the outdoor heat exchanger 203 , and is configured to supply outside air to the outdoor heat exchanger 203 .
  • the volume of air to be delivered to the outdoor fan 204 is adjusted by controlling its rotation speed.
  • a centrifugal fan or a multiblade fan is used, which is driven by a motor such as a direct current (DC) fan motor or an alternating current (AC) fan motor.
  • the expansion device 205 is configured to reduce the pressure of refrigerant and expand the refrigerant.
  • the expansion device 205 is, for example, an electronic expansion valve that can adjust the throttle opening degree.
  • the expansion device 205 adjusts the opening degree to control the pressure of refrigerant that enters the heat exchanger 5 during cooling operation, and control the pressure of refrigerant that enters the outdoor heat exchanger 203 during heating operation.
  • the air-conditioning apparatus includes the indoor unit 100 described in any of Embodiments 1 to 4, and the outdoor unit 200 connected to the indoor unit 100 by pipes to form the refrigerant circuit in which refrigerant circulates.
  • the air-conditioning apparatus includes the indoor unit 100 described in any of Embodiments 1 to 4, and therefore can obtain the same effects as those obtained by the indoor unit 100 described in any of Embodiments 1 to 4.

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  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
US18/261,724 2021-03-19 2021-03-19 Indoor unit and air-conditioning apparatus Abandoned US20240077214A1 (en)

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WO2022195834A1 (ja) 2022-09-22
EP4310404A4 (en) 2024-04-10

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