WO2022158263A1 - Unité intérieure de climatisation montée sur une paroi et dispositif de climatisation - Google Patents

Unité intérieure de climatisation montée sur une paroi et dispositif de climatisation Download PDF

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Publication number
WO2022158263A1
WO2022158263A1 PCT/JP2021/048382 JP2021048382W WO2022158263A1 WO 2022158263 A1 WO2022158263 A1 WO 2022158263A1 JP 2021048382 W JP2021048382 W JP 2021048382W WO 2022158263 A1 WO2022158263 A1 WO 2022158263A1
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WIPO (PCT)
Prior art keywords
heat exchange
exchange section
flow fan
casing
air
Prior art date
Application number
PCT/JP2021/048382
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English (en)
Japanese (ja)
Inventor
智哉 村上
浩輝 藤田
寛之 多田
海 藤原
恭彰 木村
一輝 角間
Original Assignee
ダイキン工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to CN202180079399.5A priority Critical patent/CN116490736B/zh
Publication of WO2022158263A1 publication Critical patent/WO2022158263A1/fr

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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
    • F24F1/0059—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/20—Casings or covers

Definitions

  • the present disclosure relates to wall-mounted air conditioner indoor units and air conditioners.
  • An air conditioner equipped with a wall-mounted air conditioning indoor unit is known.
  • a scroll-shaped blowout passage is formed inside a casing having a blowout opening. Air blown into the casing by the cross-flow fan passes through the heat exchanger. The air cooled or heated by the heat exchanger flows through the blowout flow path, and is then supplied to the indoor space through the blowout opening.
  • the air conditioning indoor unit For wall-mounted air conditioning indoor units, it is desirable to reduce the height of the casing. When the height of the casing is reduced, the air conditioning indoor unit can be installed, for example, on the wall surface between the window and the ceiling.
  • conventional air conditioner indoor units generally have a configuration in which the blow-out flow path is extended back and forth. Thereby, a horizontal airflow can be secured from the blow-out opening.
  • An object of the present disclosure is to provide a wall-mounted air conditioner indoor unit that can reduce the height of the casing and reduce the length of the casing in the front-rear direction.
  • a first aspect comprises a casing (31) forming an outer shell and having a blowout opening (37), a cross-flow fan (50) housed in the casing (31), and the cross-flow fan (50).
  • a flow path forming portion (60) forming a scroll-shaped blowout flow path (61) between itself and the blowout opening (37), wherein the casing (31) has a maximum vertical height H of 260 mm or less; , the wall-mounted air conditioning indoor unit, wherein the maximum longitudinal length L1 of the casing (31) is 290 mm or less, and the blowout passage (61) has a scroll angle ⁇ a of 15° or more.
  • the maximum vertical height H of the casing (31) is 260 mm or less, so the height of the casing (31) can be reduced. Since the blowout channel (61) has a scroll angle ⁇ a of 15° or more, the length of the entire blowout channel (61) in the front-rear direction can be reduced compared to a configuration in which the scroll angle ⁇ a is smaller than 15°. . Thus, even if the maximum longitudinal length L1 of the casing (31) is 290 mm or less, a sufficient space can be secured inside the casing (31).
  • a second aspect is the scroll angle ⁇ a of 35° or less in the first aspect.
  • the scroll angle ⁇ a When the scroll angle ⁇ a is greater than 35°, the height of the entire blowout passage (61) becomes too large. In addition, the horizontal velocity component of the air blown out from the blowing opening (37) becomes too small.
  • the scroll angle ⁇ a by setting the scroll angle ⁇ a to 35° or less, the height of the entire blowout flow path (61) can be suppressed. As a result, the maximum height H of the casing (31) can be 260 mm or less. In addition, it is possible to prevent the horizontal velocity component of the air blown from the blowing opening (37) from becoming too small.
  • the flow passage forming portion (60) includes a first portion ( 70), and the angle ⁇ b between the first surface (73) and the horizontal plane is 15° or more.
  • the angle ⁇ b between the first surface (73) of the blowout channel (61) and the horizontal plane is 15° or more, the length of the entire blowout channel (61) in the front-rear direction can be reduced.
  • a fourth aspect is any one of the first to third aspects, wherein a distance L2 in the longitudinal direction between the rear surface (33) of the casing (31) and the rear end of the blowout opening (37) is 125 mm or less. be.
  • the maximum length of the casing (31) in the longitudinal direction is L1 can be made small.
  • a front heat exchange section (41) is arranged in front of the cross flow fan (50), and and a rear heat exchange section (42) disposed on the side of the front heat exchange section (41) and the rear heat exchange section (42).
  • a plurality of refrigerant flow paths (P) are arranged in a direction, and the number of the plurality of refrigerant flow paths (P) in the front heat exchange section (41) is equal to the number of the plurality of refrigerant flow paths (P) in the rear heat exchange section (42). is more than twice the number of coolant channels (P) in the
  • the number of the plurality of refrigerant flow paths (P) in the front heat exchange section (41) is at least twice the number of the plurality of refrigerant flow paths (P) in the rear heat exchange section (42). Therefore, the flow path resistance of the air passing through the front heat exchange section (41) can be reduced. As a result, it is possible to ensure the flow velocity of the air flowing near the front side of the blowout channel (61).
  • the flow velocity of the air flowing near the front side of the blowout channel (61) decreases, the air outside the casing (31) flows back into the blowout channel (61) through the front part of the blowout opening (37). A so-called surging phenomenon may occur.
  • the flow velocity of the air flowing toward the front side of the blowout passageway (61) can be ensured, so the occurrence of the surging phenomenon can be suppressed.
  • a front heat exchange section (41) is arranged in front of the cross flow fan (50), and and a rear heat exchange section (42) arranged on the side of the cross flow fan (50), wherein the front heat exchange section (41) is positioned above the cross flow fan (50) and faces the cross flow fan (50).
  • the rear heat exchanging portion (42) includes an inclined front inclined portion (H1), and the rear heat exchange portion (42) is positioned above the cross flow fan (50) and inclined toward the cross flow fan (50).
  • the front sloped portion (H1) of the front heat exchange section (41) and the rear sloped portion (42) of the rear heat exchange section (42) are separated from each other, and the shortest The distance is 20 mm or more. This prevents the front sloped portion (H1) and the rear sloped portion (42) from interfering with the cross flow fan (50), thereby reducing the height H of the casing (31).
  • the inclination angle ⁇ c of the front inclined portion (H1) with respect to the vertical plane is 45° or less, it is possible to prevent the condensed water on the surface of the front inclined portion (H1) from dropping downward.
  • the inclination angle ⁇ d of the rear sloped portion (42) with respect to the vertical plane is 45° or less, it is possible to prevent the condensed water on the surface of the rear sloped portion (42) from dropping downward.
  • the front auxiliary heat exchange section (43) overlaps only the upper portion of the front heat exchange section (41) and does not overlap the lower portion of the front heat exchange section (41). As a result, it is possible to ensure the flow velocity of the air flowing near the front side of the blowout channel (61). As a result, the occurrence of the surging phenomenon described above can be suppressed.
  • the wind direction adjusting plates (91, 92) for changing the wind direction of the air blown out from the blowing opening (37) and the Coanda effect are used.
  • the scroll angle ⁇ a When the scroll angle ⁇ a is set to 15° or more, the horizontal velocity component of the blown air becomes smaller compared to a configuration in which the scroll angle ⁇ a is smaller than 15°.
  • control device (100) controls the airflow direction adjusting plates (91, 92) to a predetermined posture, so that the Coanda effect can be used to blow out horizontal airflow.
  • the scroll angle ⁇ a is 15° or more, the horizontal velocity component of the blown air can be ensured.
  • a ninth aspect is an air conditioner comprising the air conditioning indoor unit (30) of any one of the first to eighth aspects.
  • FIG. 1 is a schematic piping system diagram of an air conditioner according to an embodiment.
  • FIG. 2 is a perspective view of the indoor unit as seen from the front side.
  • FIG. 3 is a longitudinal sectional view showing the internal structure of the indoor unit.
  • FIG. 3 shows a cross section perpendicular to the axis of the cross flow fan.
  • FIG. 4 is a block diagram including the basic elements of an air conditioner.
  • FIG. 5 is a diagram corresponding to FIG. 3 of the indoor unit in the horizontal blowing mode.
  • FIG. 6 is a diagram corresponding to FIG. 3 of the indoor unit in the downward blowing mode.
  • FIG. 7 shows predetermined dimensions and predetermined angles in FIG.
  • FIG. 7 omits illustration of some of the devices in FIG.
  • FIG. 1 shows a schematic piping diagram of an air conditioner (10).
  • the air conditioner (10) adjusts the temperature of the air in the target space.
  • the target space is the indoor space (I).
  • the air conditioner (10) performs cooling operation and heating operation. In cooling operation, the air conditioner (10) cools the air in the indoor space (I). In heating operation, the air conditioner (10) heats the air in the indoor space (I).
  • the air conditioner (10) has a refrigerant circuit (11).
  • the refrigerant circuit (11) is filled with refrigerant.
  • the refrigerant circuit (11) performs a refrigeration cycle by circulating refrigerant.
  • the air conditioner (10) includes an outdoor unit (20), an indoor unit (30), a first communication pipe (12), and a second communication pipe (13).
  • the air conditioner (10) is a pair type having one outdoor unit (20) and one indoor unit (30).
  • the outdoor unit (20) includes a compressor (21), an outdoor heat exchanger (22), an expansion valve (23), a four-way switching valve (24), and an outdoor fan (25).
  • the indoor unit (30) includes an indoor heat exchanger (40) and a cross-flow fan (50).
  • Outdoor unit The outdoor unit (20) is installed in the outdoor space.
  • the compressor (21) compresses the refrigerant.
  • the compressor (21) is a rotary compressor.
  • the rotary compressor (21) is configured by an oscillating type, a rolling piston type, a scroll type, or the like.
  • the outdoor heat exchanger (22) exchanges heat between the refrigerant and the outdoor air.
  • the outdoor heat exchanger (22) is of the fin and tube type.
  • the outdoor fan (25) conveys outdoor air. Air carried by the outdoor fan (25) passes through the outdoor heat exchanger (22).
  • the outdoor fan (25) is a propeller fan.
  • the expansion valve (23) reduces the pressure of the refrigerant.
  • the expansion valve (23) is an electronic or temperature sensitive expansion valve.
  • the four-way switching valve (24) reverses the flow of refrigerant in the refrigerant circuit (11).
  • the four-way switching valve (24) switches between a first state indicated by solid lines in FIG. 1 and a second state indicated by broken lines in FIG.
  • the four-way switching valve (24) in the first state communicates the discharge side of the compressor (21) with the gas side of the outdoor heat exchanger (22), and at the same time, exchanges heat with the suction side of the compressor (21). communicate with the gas side of the vessel (40).
  • the four-way switching valve (24) in the second state allows communication between the discharge side of the compressor (21) and the gas side of the indoor heat exchanger (40), and at the same time exchanges heat with the suction side of the compressor (21). communicate with the gas side of the vessel (22).
  • the indoor heat exchanger (40) exchanges heat between the refrigerant and indoor air.
  • the indoor heat exchanger (40) is of the fin-and-tube type.
  • a cross-flow fan (50) is an indoor fan that conveys indoor air. Air carried by the cross-flow fan (50) passes through the indoor heat exchanger (40).
  • the first communication pipe (12) and the second communication pipe (13) connect the indoor unit (30) and the outdoor unit (20) to each other.
  • the first communication pipe (12) is a gas pipe
  • the second communication pipe (13) is a liquid pipe.
  • the first communication pipe (12) is connected to the gas end of the indoor heat exchanger (40).
  • the second communication pipe (13) is connected to the liquid end of the indoor heat exchanger (40).
  • FIG. 2 is a front perspective view of the indoor unit (30).
  • FIG. 3 is a longitudinal sectional view of the indoor unit (30).
  • the terms “upper”, “lower”, “front”, “back”, “left”, and “right” are based on the directions indicated by the arrows in FIG.
  • the indoor unit (30) is installed on the wall.
  • the indoor unit (30) is a wall-mounted air conditioning indoor unit.
  • the indoor unit (30) includes a casing (31), a filter (38), an indoor heat exchanger (40), a cross flow fan (50), a flow path forming portion (60), a first flap (91), and a second A flap (92) is provided.
  • the casing (31) forms the outer shell of the indoor unit (30).
  • An internal space (S1) is formed inside the casing (31) to accommodate the filter (38), the indoor heat exchanger (40), and the cross flow fan (50).
  • the casing (31) is shaped like a horizontally long box.
  • the casing (31) has a front plate (32), a rear plate (33), an upper plate (34) and a lower plate (35).
  • the front plate (32) is formed at the front end of the casing (31).
  • the front plate (32) constitutes the front surface of the casing (31).
  • the rear plate (33) is formed at the rear end of the casing (31).
  • the rear plate (33) constitutes the rear surface of the casing (31).
  • the upper plate (34) is formed on the top of the casing (31).
  • the upper plate (34) includes a first upper plate portion (34a) and a second upper plate portion (34b).
  • the first upper plate portion (34a) is formed on the front side of the upper plate (34), and the second upper plate portion (34b) is formed on the rear side of the upper plate (34).
  • the front end of the first upper plate portion (34a) is connected to the upper end of the front plate (32).
  • the rear end of the second upper plate portion (34b) is connected to the upper end of the rear plate (33).
  • the second upper plate portion (34b) forms a substantially horizontal upper surface of the casing (31).
  • the first upper plate portion (34a) extends obliquely upward from the front plate (32) toward the second upper plate portion (34b).
  • the lower plate (35) is formed at the bottom of the casing (31).
  • the lower plate (35) includes a first lower plate portion (35a) and a second lower plate portion (35b).
  • the first lower plate portion (35a) is formed on the front side of the lower plate (35), and the second lower plate portion (35b) is formed on the rear side of the lower plate (35).
  • the front end of the first lower plate portion (35a) is connected to the lower end of the front plate (32).
  • the rear end of the second lower plate portion (35b) is connected to the lower end of the rear plate (33).
  • the second lower plate portion (35b) forms a substantially horizontal lower surface of the casing (31).
  • the first lower plate portion (35a) extends obliquely downward from the front plate (32) toward the second lower plate portion (35b).
  • a suction opening (36) is formed in the upper part of the casing (31).
  • a suction opening (36) is formed in the top plate (34). More precisely, the suction openings (36) are formed in the first upper plate portion (34a) and the second upper plate portion (34b).
  • the suction opening (36) extends in the longitudinal direction (horizontal direction) of the casing (31).
  • the suction opening (36) takes the air in the indoor space (I) into the internal space (S1) of the casing (31).
  • the suction opening (36) is positioned higher than the center of rotation (axis 0) of the crossflow fan (50).
  • a blowout opening (37) is formed in the lower part of the casing (31).
  • the blowout opening (37) is formed in the lower plate (35). More strictly, the blowout opening (37) is formed in the first lower plate portion (35a).
  • the blowout opening (37) extends in the longitudinal direction of the casing (31).
  • the blowout opening (37) faces obliquely downward.
  • the blowout opening (37) blows out the air that has flowed through the blowout channel (61) into the indoor space (I).
  • the blow-out opening (37) is positioned lower than the axis 0 of the crossflow fan (50).
  • the rear end of the blowout opening (37) is positioned slightly forward of the axis 0 of the crossflow fan (50).
  • the filter (38) is arranged upstream of the indoor heat exchanger (40) in the internal space (S1).
  • the filter (38) collects dust and the like in the air sent from the suction opening (36) to the indoor heat exchanger (40).
  • the indoor unit (30) of this embodiment has a dust removing mechanism (39).
  • the dust removing mechanism (39) removes dust collected on the filter (38).
  • the indoor heat exchanger (40) includes a plurality of fins (F) arranged in the direction of the axis 0 of the cross flow fan (50) and a plurality of fins (F) penetrating the fins (F). of heat transfer tubes.
  • the fins (F) are formed in a vertically long rectangular shape.
  • the width direction of the fin (F) corresponds to the front-rear direction.
  • a refrigerant channel (P) is formed inside each of the plurality of heat transfer tubes.
  • the refrigerant channel (P) forms part of the refrigerant circuit (11).
  • the indoor heat exchanger (40) includes a front heat exchange section (41) and a rear heat exchange section (42).
  • the indoor heat exchanger (40) further includes a front auxiliary heat exchange section (43) and a rear auxiliary heat exchange section (44).
  • the front heat exchange section (41), the rear heat exchange section (42), the front auxiliary heat exchange section (43), and the rear auxiliary heat exchange section (44) are configured separately from each other.
  • the front heat exchange section (41) is arranged in front of the cross flow fan (50).
  • the front heat exchange section (41) includes, in order from top to bottom, a first heat exchange section (H1), a second heat exchange section (H2), and a third heat exchange section (H3).
  • Each fin (F) of the first heat exchange section (H1), the second heat exchange section (H2), and the third heat exchange section (H3) is integrally formed.
  • the first heat exchange section (H1) is the front inclined section of the present disclosure.
  • the first heat exchange section (H1) is located above the front side of the crossflow fan (50) and is inclined toward the crossflow fan (50).
  • the fins (F) of the first heat exchange section (H1) are inclined rearward and downward from the vertical plane.
  • the second heat exchange section (H2) is arranged vertically in front of the cross flow fan (50).
  • the fins (F) of the second heat exchange section (H2) are substantially aligned with the vertical plane.
  • the third heat exchange section (H3) is located on the lower front side of the crossflow fan (50) and is inclined toward the crossflow fan (50).
  • the fins (F) of the third heat exchange section (H3) are tilted rearward from the vertical plane.
  • the rear heat exchange section (42) is arranged behind the cross flow fan (50).
  • the rear heat exchange section (42) constitutes the rear inclined section of the present disclosure.
  • the rear heat exchange section (42) is positioned rearward and upward of the crossflow fan (50) and is inclined toward the crossflow fan (50).
  • the fins (F) of the rear heat exchange section (42) are inclined forward and downward from the vertical plane.
  • the first heat exchange section (H1) and the rear heat exchange section (42) are separated from each other. There is a space in the front-rear direction between the first heat exchange section (H1) and the rear heat exchange section (42).
  • a closed part (45) is provided between the first heat exchange part (H1) and the rear heat exchange part (42).
  • the closing part (45) is formed by folding a plate-like metal.
  • a front end of the closed part (45) is connected to the first heat exchange part (H1).
  • a rear end of the closing part (45) is connected to the rear heat exchange part (42).
  • the blocking part (45) blocks the space between the first heat exchanging part (H1) and the rear heat exchanging part (42).
  • the blocking portion (45) prevents air taken into the suction opening (36) from passing between the front heat exchange portion (41) and the rear heat exchange portion (42).
  • the front auxiliary heat exchange section (43) is arranged in front of the cross flow fan (50) and in front of the front heat exchange section (41).
  • the front auxiliary heat exchange section (43) is arranged on the upstream side of the air flow in the front heat exchange section (41).
  • the front auxiliary heat exchange section (43) includes, in order from top to bottom, a fourth heat exchange section (H4) and a fifth heat exchange section (H5).
  • Each fin (F) of the fourth heat exchange section (H4) and the fifth heat exchange section (H5) is integrally formed.
  • the front auxiliary heat exchange section (43) overlaps only the upper portion of the front heat exchange section (41). Specifically, the front auxiliary heat exchange section (43) overlaps the entire first heat exchange section (H1) and overlaps the upper portion of the second heat exchange section (H2). The front auxiliary heat exchange section (43) does not overlap the lower portion of the second heat exchange section (H2) and does not overlap the entire third heat exchange section (H3).
  • the fourth heat exchange section (H4) is inclined along the first heat exchange section (H1).
  • the fourth heat exchange section (H4) overlaps the entire first heat exchange section (H1).
  • the fifth heat exchange section (H5) is provided vertically along the second heat exchange section (H2).
  • the fifth heat exchange section (H5) overlaps only the upper portion of the second heat exchange section (H2) and does not overlap the lower portion of the second heat exchange section (H2).
  • the rear auxiliary heat exchange section (44) is arranged behind the cross flow fan (50) and behind the rear heat exchange section (42).
  • the rear auxiliary heat exchange section (44) is arranged on the upstream side of the air flow in the rear heat exchange section (42).
  • the rear auxiliary heat exchange section (44) overlaps the rear heat exchange section (42). Specifically, the rear auxiliary heat exchange section (44) overlaps the intermediate portion of the rear heat exchange section (42), but does not overlap its upper and lower ends.
  • a plurality of first refrigerant flow paths (P1) are formed in the front heat exchange section (41). Specifically, in the front heat exchange section (41), a plurality of first refrigerant flow paths (P1) are formed in two front and rear rows. In each row, ten first refrigerant flow paths (P1) are arranged vertically. Specifically, in each row, four first refrigerant flow paths (P1) are formed in the first heat exchange section (H1), and four first refrigerant flow paths (P1 ) are formed, and two first refrigerant flow paths (P1) are formed in the third heat exchange section (H3).
  • a plurality of second refrigerant flow paths (P2) are formed in the rear heat exchange section (42). Specifically, in the rear auxiliary heat exchange section (44), a plurality of second refrigerant flow paths (P2) are respectively formed in two front and rear rows. In each row, the number of the plurality of second refrigerant flow paths (P2) aligned vertically is four.
  • a plurality of third refrigerant flow paths (P3) are formed in one row in the front auxiliary heat exchange section (43). In one row, the number of vertically aligned third coolant flow paths (P3) is six. Specifically, four third refrigerant flow paths (P3) are formed in the fourth heat exchange section (H4), and two third refrigerant flow paths (P3) are formed in the fifth heat exchange section (H5). be.
  • a plurality of fourth refrigerant flow paths (P4) are formed in one row in the rear auxiliary heat exchange section (44). In one row, the number of vertically aligned fourth coolant flow paths (P4) is two.
  • the cross flow fan (50) includes a fan rotor (51) extending horizontally (horizontal direction) and a motor (52) for driving the fan rotor (51).
  • the fan rotor (51) has a plurality of fan blades (53) circumferentially arranged around its axis.
  • the cross-flow fan (50) rotates in the direction of arrow R in FIG.
  • a rotating cross-flow fan (50) conveys the air in the internal space (S1).
  • the flow path forming portion (60) forms a scroll-shaped blowout flow path (61) between the cross flow fan (50) and the blowout opening (37).
  • the flow path forming portion (60) includes a stabilizer (70) and a rear guider (80).
  • the stabilizer (70) is arranged in front of the cross flow fan (50). Strictly speaking, the stabilizer (70) is arranged between the crossflow fan (50) and the first lower plate (35a). The stabilizer (70) forms part 1 of this disclosure.
  • the stabilizer (70) forms a tongue (71), a front water catch (72) and a front side (73).
  • the tongue (71) forms a curved surface on the part of the stabilizer (70) closest to the cross-flow fan (50).
  • the front water receiving portion (72) is formed in a portion of the upper portion of the stabilizer (70) located below the front heat exchange portion (41) and the front auxiliary heat exchange portion (43).
  • the front water receiver (72) is a drain pan that receives condensed water.
  • the front side (73) constitutes the first side of the present disclosure.
  • the front side surface (73) faces the front portion of the blowout channel (61).
  • the front side surface (73) is formed of a plane that is inclined downward with respect to the horizontal plane fh.
  • the stabilizer (70) further forms a continuous surface (74) that continues forward from the front end of the front side surface (73).
  • the rear guider (80) is arranged behind the cross flow fan (50). Strictly speaking, the rear guider (80) is arranged between the crossflow fan (50) and the rear plate (33) and between the crossflow fan (50) and the second lower plate (35b). The rear guider (80) forms a rear water receiving portion (81) and a rear side surface (82).
  • the rear water receiving portion (81) is formed in a portion of the upper portion of the rear guider (80) located below the rear heat exchange portion (42) and the rear auxiliary heat exchange portion (44).
  • the rear water receiver (81) is a drain pan that receives condensed water.
  • the rear side surface (82) faces the rear portion of the blowout channel (61).
  • the rear side surface (82) gently curves along the blowout channel (61).
  • the rear side surface (82) extends from the upper portion of the crossflow fan (50) to the blowout opening (37).
  • a piping space (S2) is formed between the lower portion of the rear plate (33) of the casing (31) and the rear guider (80).
  • the piping space (S2) accommodates refrigerant piping of the refrigerant circuit (11), a condensed water discharge path (for example, a hose), and the like.
  • the blowout opening (37) is provided with a first flap (91) and a second flap (92).
  • the first flap (91) and the second flap (92) constitute an airflow direction adjusting plate that changes the direction of the air blown out from the blowout opening (37).
  • the first flap (91) is provided near the rear side of the blowout opening (37).
  • the first flap (91) extends laterally along the blowout opening (37).
  • the first flap (91) changes its inclination about the first axis (91a) when driven by a motor (not shown).
  • the second flap (92) is provided near the front side of the blowout opening (37).
  • the second flap (92) is positioned forward of the first flap (91).
  • the second flap (92) extends laterally along the blowout opening (37).
  • the second flap (92) changes its inclination about the second axis (92a) when driven by a motor (not shown).
  • the center of the second shaft (92a) is located slightly higher than the center of the first shaft (91a).
  • the air conditioner (10) has a control device (100).
  • the control device (100) includes a remote controller (101), an indoor controller (102), and an outdoor controller (103).
  • the remote control (101) is provided in the indoor space (I).
  • a remote controller (101) is an operation unit operated by a user. By operating the remote control, the user can change the operation mode, airflow mode, and set temperature.
  • the remote control (101) transmits a command according to its operation to the indoor controller (102) via radio or wire.
  • the indoor controller (102) that has received the command from the remote controller (101) controls the indoor unit (30).
  • the indoor controller (102) that has received the command from the remote controller (101) transmits a command corresponding to the operation of the remote controller (101) to the outdoor controller (103) wirelessly or by wire.
  • the indoor controller (102) controls the cross flow fan (50), the first flap (91), and the second flap (92) according to the received command.
  • the outdoor controller (103) controls the compressor (21), the expansion valve (23), the four-way switching valve (24), and the outdoor fan (25) according to the received command.
  • the air conditioner (10) performs cooling operation and heating operation.
  • the control device (100) sets the four-way switching valve (24) to the first state.
  • the controller (100) operates the compressor (21), the outdoor fan (25), and the cross flow fan (50).
  • the control device (100) adjusts the degree of opening of the expansion valve (23).
  • the refrigerant circuit (11) performs a refrigeration cycle (cooling cycle) in which the outdoor heat exchanger (22) functions as a radiator and the indoor heat exchanger (40) functions as an evaporator.
  • the refrigerant compressed by the compressor (21) flows through the outdoor heat exchanger (22).
  • the outdoor heat exchanger (22) exchanges heat between refrigerant and outdoor air.
  • the refrigerant that has released heat or condensed in the outdoor heat exchanger (22) is decompressed by the expansion valve (23) and then flows through the indoor heat exchanger (40).
  • the indoor heat exchanger (40) exchanges heat between the refrigerant and indoor air.
  • the refrigerant evaporated in the indoor heat exchanger (40) is compressed again in the compressor (21).
  • the control device (100) sets the four-way switching valve (24) to the second state.
  • the controller (100) operates the compressor (21), the outdoor fan (25), and the cross flow fan (50).
  • the control device (100) adjusts the degree of opening of the expansion valve (23).
  • the refrigerant circuit (11) performs a refrigeration cycle (heating cycle) in which the indoor heat exchanger (40) functions as a radiator and the outdoor heat exchanger (22) functions as an evaporator.
  • the refrigerant compressed by the compressor (21) flows through the indoor heat exchanger (40).
  • the indoor heat exchanger (40) exchanges heat between the refrigerant and indoor air.
  • the refrigerant that has released heat or condensed in the indoor heat exchanger (40) is decompressed by the expansion valve (23) and then flows through the outdoor heat exchanger (22).
  • the outdoor heat exchanger (22) exchanges heat between refrigerant and outdoor air.
  • the refrigerant evaporated in the outdoor heat exchanger (22) is compressed again in the compressor (21).
  • the air in the indoor space (I) is taken into the internal space (S1) through the suction opening (36). Air drawn in through the suction opening (36) passes through the filter (38). The filter (38) collects dust and the like in the air. The air that has passed through the filter (38) flows through the indoor heat exchanger (40). The indoor heat exchanger (40) cools the air. The air cooled by the indoor heat exchanger (40) passes through the cross-flow fan (50) and flows through the blowout flow path (61). The air in the blowout channel (61) is guided forward and downward, and is blown out from the blowout opening (37) into the interior space (I).
  • first flap (91) and the second flap (92) have an angle close to the horizontal, the horizontal velocity component of the blown air increases. Therefore, it is possible to prevent the blown air from hitting the user directly.
  • the control device (100) can execute the horizontal blowing mode even in the blowing operation and the dry operation.
  • the blowing operation is an operation in which the indoor heat exchanger (40) is substantially stopped and air is blown into the indoor space (I).
  • Dry operation is an operation in which the evaporation temperature of the indoor heat exchanger (40) is lowered and cooled and dehumidified air is supplied to the indoor space (I).
  • the air in the indoor space (I) is taken into the internal space (S1) through the suction opening (36). Air drawn in through the suction opening (36) passes through the filter (38). The filter (38) collects dust and the like in the air. The air that has passed through the filter (38) flows through the indoor heat exchanger (40). The indoor heat exchanger (40) heats the air. The air heated by the indoor heat exchanger (40) passes through the cross-flow fan (50) and flows through the blowout channel (61). The air in the blowout channel (61) is guided forward and downward, and is blown out from the blowout opening (37) into the interior space (I).
  • the first flap (91) and the second flap (92) have an angle close to the vertical, so the velocity component in the vertical direction of the blown air increases. Therefore, it becomes easier to supply warm air to the floor side.
  • the maximum vertical height H of the casing (31) is 250 mm.
  • the maximum height H of the casing (31) is preferably 260 mm or less. Thereby, the height of the indoor unit (30) can be reduced.
  • the indoor unit (30) can be arranged on the wall of the indoor space (I) between the window and the ceiling.
  • the maximum height H of the casing (31) is preferably 250 mm or less.
  • the maximum height H of the casing (31) should be 240 mm or more. Thereby, the distance between the indoor heat exchanger (40) and the cross flow fan (50) can be secured, and noise such as NZ noise can be suppressed.
  • the number of vertical refrigerant flow paths (P) in one row in the indoor heat exchanger (40) (the number of stages of the indoor heat exchanger (40)) can be increased. As a result, an increase in flow resistance of air passing through the indoor heat exchanger (40) can be suppressed.
  • the maximum longitudinal length L of the casing (31) is 267 mm.
  • the maximum longitudinal length L1 of the casing (31) is preferably 290 mm or less.
  • the maximum longitudinal length L1 of the casing (31) is preferably 270 mm or less.
  • the maximum longitudinal length L1 of the casing (31) is preferably 267 mm or more.
  • a space for accommodating the front auxiliary heat exchange section (43) and the rear auxiliary heat exchange section (44) can be secured in the internal space (S1).
  • the volume of the piping space (S2) can be secured, and refrigerant piping and drainage can be accommodated in the piping space (S2).
  • the scroll angle ⁇ a of the blowout passage (61) is defined as follows. Let o1 be the position of the rear end of the blowout opening (37). In the vertical cross-sectional view shown in FIG. 7, the shortest path is connected from the rear end position o1 of the blowout opening to the front side surface (73) (first surface) of the blowout passageway (61). Let o2 be the end point of this shortest path on the front side surface (73) of the blowout flow path (61).
  • f1 be a plane (first plane) connecting the positions o1 and o2.
  • f2 be a plane (second plane) orthogonal to the first plane f1.
  • the scroll angle ⁇ a is the angle between the horizontal plane fh and the second plane f2.
  • the scroll angle ⁇ a is the downward inclination angle of the second plane f2 with respect to the horizontal plane fh.
  • the scroll angle ⁇ a of the blowout passage (61) is approximately 27.7°.
  • the scroll angle ⁇ a of the blowout passage (61) is preferably 15° or more.
  • the scroll angle ⁇ a is set to 15° or more, the length of the entire blowout passage (61) in the front-rear direction can be shortened as compared with the conventional example. Therefore, the maximum length L1 of the casing (31) in the longitudinal direction can be shortened, and the maximum length L1 can be suppressed to 290 mm or less, further 270 mm or less.
  • the scroll angle ⁇ a of the blowout passage (61) is preferably 35° or less. By setting the scroll angle ⁇ a to 35° or less, it is possible to prevent the vertical height of the entire blowout passage (61) from becoming too large. As a result, the maximum height H of the casing (31) can be shortened, and the maximum height H can be suppressed to 260 mm, and further to 250 mm or less.
  • the angle ⁇ b formed between the front side surface (73) (first surface) of the blowout flow path (61) and the horizontal plane fh is approximately 23.5°.
  • This angle ⁇ b is preferably 15° or more.
  • the angle ⁇ b is set to 15° or more, the length of the entire blowout passage (61) in the front-rear direction can be shortened as compared with the conventional example. Therefore, the maximum length L1 of the casing (31) in the longitudinal direction can be shortened, and the maximum length L1 can be suppressed to 290 mm or less, further 270 mm or less.
  • the angle ⁇ b should be 30° or less. When the angle ⁇ b is 30° or less, it is possible to prevent the vertical height of the entire blowout passage (61) from becoming too large. As a result, the maximum height H of the casing (31) can be shortened, and the maximum height H can be suppressed to 260 mm, and further to 250 mm or less.
  • Distance L2 in the longitudinal direction between the rear surface of the casing and the rear end of the blowout opening L2 is the distance in the longitudinal direction from the rear surface (rear plate (33)) of the casing (31) to the rear end of the blowout opening (37).
  • the distance L2 is 103 mm.
  • the distance L2 is preferably 125 mm or less. By setting the distance L2 to 125 mm or less, the maximum longitudinal length L1 of the casing (31) can be shortened.
  • the distance L2 should be 95 mm or more. By setting the distance L2 to 95 mm or more, the length of the piping space (S2) in the front-rear direction can be secured, and the refrigerant piping and the discharge path can be accommodated in the piping space (S2).
  • the number is ten, and the number of one row of refrigerant passages (P) (second refrigerant passages (P)) in the rear heat exchange section (42) is four.
  • the number n1 of the plurality of first refrigerant flow paths (P) in one row of the front heat exchange section (41) is the number of the plurality of second refrigerant flow paths (P) in one row of the rear heat exchange section (42). It is preferable to make it twice or more of n2.
  • the first heat exchange section (H1) and the rear heat exchange section (42) are separated from each other. , are spaced apart in the fore-and-aft direction.
  • the shortest distance L3 between the first heat exchange section (H1) and the rear heat exchange section (42) is approximately 37 mm. This shortest distance L3 is preferably 20 mm or more.
  • a space for arranging the cross flow fan (50) can be secured between the first heat exchange section (H1) and the rear heat exchange section (42), and the casing (31 ) can be reduced.
  • the shortest distance L3 should be 40 mm or less. Thereby, the maximum longitudinal length L1 of the casing (31) can be reduced.
  • the first heat exchange section (H1) is inclined toward the cross flow fan (50) (rearward) by a first inclination angle ⁇ c with respect to the vertical plane fv.
  • the first inclination angle ⁇ c with respect to the vertical plane fv in the first heat exchange section (H1) is 41°.
  • the first tilt angle ⁇ c is preferably 45° or less. If the first inclination angle ⁇ c is greater than 45°, the condensed water on the surface of the first heat exchange section (H1) may drop downward due to its own weight.
  • by setting the first inclination angle ⁇ c to 45° or less, it is possible to prevent the condensed water from falling downward.
  • the first inclination angle c is preferably 38° or more.
  • the vertical height of the front heat exchange section (41) can be suppressed. Thereby, the maximum height H of the casing (31) can be reduced.
  • the second heat exchange section (H2) is inclined toward the cross flow fan (50) (front side) by a second inclination angle ⁇ d with respect to the vertical plane fv.
  • the second inclination angle ⁇ d with respect to the vertical plane fv in the second heat exchange section (H2) is 43°.
  • the second tilt angle ⁇ d is preferably 45° or less. If the second inclination angle ⁇ d is greater than 45°, the condensed water on the surface of the second heat exchange section (H2) may drop downward due to its own weight.
  • the second inclination angle ⁇ d by setting the second inclination angle ⁇ d to 45° or less, it is possible to prevent the condensed water from falling downward.
  • the second tilt angle d is preferably 38° or more.
  • the vertical height of the rear heat exchange section (42) can be suppressed. Thereby, the maximum height H of the casing (31) can be reduced.
  • the front auxiliary heat exchange section (43) overlaps only the upper portion of the front heat exchange section (41).
  • the flow path resistance of the air in the lower portion of the front heat exchange section (41) can be reduced.
  • the blowout channel (61) the flow velocity of the air near the front side surface (73) can be ensured, so that the occurrence of the above-described surging phenomenon can be suppressed.
  • the control device (100) controls the first flap (91) and the second flap (92). Specifically, the control device (100) controls the attitudes of the first flap (91) and the second flap (92) so as to blow out horizontal air from the blowout opening (37) using the Coanda effect. do.
  • the angle of the first upper surface (91b) of the first flap (91) is closer to the horizontal plane.
  • the angle of the second lower surface (92b) of the second flap (92) is closer to the horizontal plane than the first upper surface (91b) of the first flap (91).
  • the front end of the first upper surface (91b) of the first flap (91) overlaps the rear end of the second lower surface (92b) of the second flap (92) in the vertical direction.
  • the angle of the second upper surface (92c) of the second flap (92) is closer to the horizontal plane.
  • a continuous surface (74) and a first lower plate portion (35a) are formed above the second upper surface (92c) of the second flap (92).
  • a surface formed by the continuous surface (74) and the first lower plate portion (35a) is gradually inclined upward toward the front side.
  • the air conditioner (10) may be of a multi-type having multiple indoor units (30).
  • the air conditioner (10) may have a humidity control section that controls the humidity of the air.
  • the indoor unit (30) may also serve as a ventilation device. Specifically, the indoor unit (30) takes in outdoor air into the casing (31), and supplies the air that has passed through the indoor heat exchanger (40) to the indoor space (I) through the blowout opening (37). good too.
  • the indoor heat exchanger (40) may omit the front auxiliary heat exchange section (43) and the rear auxiliary heat exchange section (44).
  • the front auxiliary heat exchange section (43) may be arranged behind the front heat exchange section (41).
  • the present disclosure is useful for air conditioner indoor units and air conditioners.
  • REFERENCE SIGNS LIST 10 air conditioner 30 air conditioner indoor unit 31 casing 33 rear plate (rear surface) 37 blow-out opening 41 front heat exchange section 42 rear heat exchange section (rear inclined section) 43 Front auxiliary heat exchange section 50 Cross flow fan 60 Flow path forming section 61 Blow-out flow path 70 Stabilizer (first part) 73 First surface 91 First flap (wind direction adjusting plate) 92 2nd flap (wind direction adjustment version) 100 control device

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

Dans la présente invention, la hauteur maximale H d'un boîtier (31) dans la direction verticale est de 260 mm ou moins. La longueur maximale L1 du boîtier (31) dans la direction avant-arrière est de 290 mm ou moins. L'angle de défilement θa d'un canal de soufflage (61) est de 15° ou plus.
PCT/JP2021/048382 2021-01-22 2021-12-24 Unité intérieure de climatisation montée sur une paroi et dispositif de climatisation WO2022158263A1 (fr)

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JP2021008521A JP7244773B2 (ja) 2021-01-22 2021-01-22 壁掛け式の空調室内機、および空気調和装置
JP2021-008521 2021-01-22

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Citations (3)

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JP2006010257A (ja) * 2004-06-28 2006-01-12 Mitsubishi Heavy Ind Ltd 空調用室内ユニットおよび空気調和装置
JP2015124985A (ja) * 2013-12-27 2015-07-06 ダイキン工業株式会社 空調室内機
WO2019155664A1 (fr) * 2018-02-06 2019-08-15 シャープ株式会社 Climatiseur

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Publication number Priority date Publication date Assignee Title
JPH11148708A (ja) * 1997-11-18 1999-06-02 Daikin Ind Ltd 空気調和装置
JP3731067B2 (ja) * 2002-05-15 2006-01-05 ダイキン工業株式会社 空気調和装置の室内機
CN100526762C (zh) * 2006-03-28 2009-08-12 海尔集团公司 壁挂式空调室内机的连续圆弧形蒸发器
JP2012073024A (ja) * 2011-12-09 2012-04-12 Sharp Corp 空気調和機の室内機
JP2015124986A (ja) * 2013-12-27 2015-07-06 ダイキン工業株式会社 空調室内機
JP2017227423A (ja) * 2016-06-24 2017-12-28 ダイキン工業株式会社 空気調和機の室内ユニット
CN109790842B (zh) * 2016-09-30 2021-03-23 大金工业株式会社 横流式风机及包括该横流式风机的空调装置的室内机组
CN109882943A (zh) * 2019-03-22 2019-06-14 广东美的制冷设备有限公司 整体式空调器

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006010257A (ja) * 2004-06-28 2006-01-12 Mitsubishi Heavy Ind Ltd 空調用室内ユニットおよび空気調和装置
JP2015124985A (ja) * 2013-12-27 2015-07-06 ダイキン工業株式会社 空調室内機
WO2019155664A1 (fr) * 2018-02-06 2019-08-15 シャープ株式会社 Climatiseur

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