WO2012017483A1 - Unité intérieure pour climatiseur, et climatiseur - Google Patents

Unité intérieure pour climatiseur, et climatiseur Download PDF

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Publication number
WO2012017483A1
WO2012017483A1 PCT/JP2010/004916 JP2010004916W WO2012017483A1 WO 2012017483 A1 WO2012017483 A1 WO 2012017483A1 JP 2010004916 W JP2010004916 W JP 2010004916W WO 2012017483 A1 WO2012017483 A1 WO 2012017483A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
fan
indoor unit
side heat
air
Prior art date
Application number
PCT/JP2010/004916
Other languages
English (en)
Japanese (ja)
Inventor
福井智哉
山田彰二
迫田健一
加賀邦彦
道籏聡
森剛
鈴木仁人
高守輝
向山琢也
代田光宏
谷川喜則
松本崇
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2010/004916 priority Critical patent/WO2012017483A1/fr
Priority to JP2012527461A priority patent/JP5591335B2/ja
Publication of WO2012017483A1 publication Critical patent/WO2012017483A1/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
    • F24F1/0043—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
    • F24F1/0033—Indoor units, e.g. fan coil units characterised by fans having two or more 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
    • F24F1/0029—Axial 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
    • F24F13/28—Arrangement or mounting of filters

Definitions

  • the present invention relates to an indoor unit in which a fan and a heat exchanger are housed in a casing, and an air conditioner including the indoor unit.
  • an air conditioner in which a fan and a heat exchanger are housed in a casing.
  • an air conditioner comprising a main body casing having an air inlet and an air outlet, and a heat exchanger disposed in the main body casing, wherein the air outlet includes a plurality of small propellers.
  • an air conditioner in which a fan unit having a fan arranged in the width direction of the air outlet is disposed” (see, for example, Patent Document 1).
  • This air conditioner is provided with a fan unit at the air outlet to facilitate airflow direction control, and a fan unit having the same configuration is also provided at the suction port to improve the heat exchanger performance due to an increase in the air volume. I am doing so.
  • the air conditioner like patent document 1 is provided with the heat exchanger in the upstream of the fan unit (blower). For this reason, since the movable fan unit is provided on the air outlet side, the air flow is changed due to the movement of the fan and the instability of the flow due to the asymmetric suction causes a decrease in the air volume and a reverse flow. Furthermore, the air whose flow is disturbed flows into the fan unit. Therefore, in an air conditioner like Patent Document 1, the flow of air flowing into the outer peripheral part of the wing part (propeller) of the fan unit whose flow rate is high is disturbed, and the fan unit itself becomes a noise source (noise deterioration). There was a problem that Furthermore, the air conditioner shown in Patent Document 1 does not consider the installation position of the filter. For this reason, depending on the installation position of the filter, there is a problem that the pressure loss in the filter increases, the variation in the wind speed distribution generated in the heat exchanger increases, and the heat exchange performance deteriorates. It was.
  • the present invention has been made in order to solve the above-described problems, and a first object thereof is an indoor unit capable of suppressing pressure loss in a filter and suppressing deterioration in heat exchange performance, And obtaining an air conditioner provided with this indoor unit. Moreover, the 2nd objective is to obtain the indoor unit which can suppress the variation in the wind speed distribution which arises in a heat exchanger, and can suppress the fall of heat exchange performance, and an air conditioner provided with this indoor unit. is there.
  • An indoor unit of an air conditioner includes a casing having a suction port formed in an upper portion thereof and a blower outlet formed in a lower side of a front surface portion, and an axial flow type or a slant provided on the downstream side of the suction port in the casing.
  • a filter provided on the upstream side of the finger guard.
  • the indoor unit of the air conditioner according to the present invention includes a casing in which a suction port is formed in the upper part and a blower outlet is formed in the lower part of the front part, and an axial flow type provided on the downstream side of the suction port in the casing.
  • a filter provided between the containers.
  • an air conditioner according to the present invention is provided with the indoor unit described above.
  • the filter By disposing the filter on the upstream side of the finger guard provided at the suction port of the casing, the distance between the filter and the fan can be increased. For this reason, the effective air path of a filter can be enlarged and the pressure loss in a filter can be suppressed. Moreover, by providing a filter between the fan and the heat exchanger, the airflow blown from the fan can be rectified by the filter 10 and then flowed into the heat exchanger. For this reason, the variation in the wind speed distribution which arises in a heat exchanger can be suppressed. Therefore, by arranging the filter as in the present invention, it is possible to suppress a decrease in heat exchange performance.
  • FIG. 3 is a schematic diagram for explaining a configuration example of a heat exchanger 50.
  • FIG. It is explanatory drawing (longitudinal sectional drawing) for demonstrating the airflow in the nozzle of the indoor unit which concerns on Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 20 of this invention. It is a longitudinal cross-sectional view which shows another example of the indoor unit which concerns on Embodiment 20 of this invention. It is explanatory drawing for demonstrating the airflow which generate
  • each unit constituting the indoor unit of the air conditioner will be described.
  • the second and subsequent embodiments the detailed configuration of each unit or another example will be described.
  • the present invention will be described by taking a wall-mounted indoor unit as an example.
  • the shape and size of each unit (or a constituent member of each unit) may be partially different.
  • FIG. 1 is a longitudinal sectional view showing an indoor unit (referred to as an indoor unit 100) of an air conditioner according to Embodiment 1 of the present invention.
  • FIG. 2 is an external perspective view showing the indoor unit.
  • the left side in FIG. 1 will be described as the front side of the indoor unit 100.
  • the configuration of the indoor unit 100 will be described with reference to FIGS. 1 and 2.
  • the indoor unit 100 supplies conditioned air to an air-conditioning target area such as a room by using a refrigeration cycle that circulates a refrigerant.
  • the indoor unit 100 is mainly accommodated in a casing 1 in which a suction port 2 for sucking indoor air into the interior and a blower outlet 3 for supplying conditioned air to an air-conditioning target area are formed.
  • the fan 20 sucks room air from the suction port 2 and blows out the conditioned air from the blower outlet 3 and the air passage from the fan 20 to the blower outlet 3, and exchanges heat between the refrigerant and the room air for conditioned air.
  • a heat exchanger 50 for producing And the air path (arrow Z) is connected in the casing 1 by these components.
  • the suction port 2 is formed in the upper part of the casing 1.
  • the blower outlet 3 has an opening formed in the lower part of the casing 1 (more specifically, on the lower side of the front part of the casing 1).
  • the fan 20 is disposed on the downstream side of the suction port 2 and on the upstream side of the heat exchanger 50, and is configured by, for example, an axial flow fan or a diagonal flow fan.
  • the indoor unit 100 includes a control device 281 that controls the rotation speed of the fan 20 and the upper and lower vanes 70 and the left and right vanes 80 described later.
  • the controller 281 may not be shown in the drawings shown in the first embodiment and each embodiment described later.
  • the fan 20 is provided on the upstream side of the heat exchanger 50, so that it is compared with a conventional air conditioner indoor unit in which the fan 20 is provided at the outlet 3.
  • the generation of the swirling flow of the air blown from the outlet 3 and the variation in the wind speed distribution can be suppressed. For this reason, comfortable ventilation to an air-conditioning object area is attained.
  • there is no complicated structure such as a fan at the air outlet 3 it is easy to take measures against condensation that occurs at the boundary between warm air and cold air during cooling operation.
  • the fan motor 30 is not exposed to cold air or warm air that is air-conditioned air, a long operating life can be provided.
  • the indoor unit 100 according to Embodiment 1 includes three fans 20 arranged in parallel along the longitudinal direction of the casing 1 (in other words, the longitudinal direction of the air outlet 3). Yes.
  • approximately two to four fans 20 are preferable.
  • all the fans 20 are configured in the same shape, and almost the same amount of air flow can be obtained by all the fans 20 by operating all the operation rotational speeds equally.
  • the optimum fan design corresponding to the indoor unit 100 of various specifications can be achieved by combining the number, shape, size, and the like of the fans 20 according to the required air volume and the ventilation resistance inside the indoor unit 100. Is possible.
  • a bell mouth 5 on a duct is disposed around the fan 20.
  • the bell mouth 5 is for smoothly guiding the intake and exhaust of air to the fan.
  • the bell mouth 5 according to the first embodiment has a substantially circular shape in plan view.
  • the bell mouth 5 according to the first embodiment has the following shape.
  • the upper part 5a has a substantially arc shape whose end part widens upward.
  • the central portion 5b is a straight portion where the diameter of the bell mouth is constant.
  • the lower part 5c has a substantially arc shape whose end part extends downward.
  • the suction inlet 2 is formed in the edge part (arc part of the suction side) of the upper part 5a of the bellmouth 5.
  • FIG. 1 of the first embodiment has a duct shape configured higher than the height of the impeller of the fan 20, but is not limited thereto, and the height of the bell mouth 5 is not limited thereto.
  • a semi-open bellmouth configured lower than the height of the impeller of the fan 20 may be used.
  • the bell mouth 5 may not be provided with the straight portion 5b shown in FIG. 1 but may be constituted only by the end portions 5a and 5c.
  • the bell mouth 5 may be formed integrally with the casing 1, for example, in order to reduce the number of parts and improve the strength. Further, for example, the bell mouth 5, the fan 20, the fan motor 30, and the like may be modularized, and the casing 1 may be attached and detached to improve maintenance.
  • the end of the upper portion 5a of the bell mouth 5 (arc portion on the suction side) is configured in a uniform shape with respect to the circumferential direction of the opening surface of the bell mouth 5.
  • the bell mouth 5 has no structure such as a notch or a rib with respect to the rotation direction about the rotation axis 20a of the fan 20, and has a uniform shape having axial symmetry.
  • the end of the upper portion 5a of the bell mouth 5 (the arc portion on the suction side) has a uniform shape with respect to the rotation of the fan 20.
  • a uniform flow is realized as a flow. For this reason, the noise which generate
  • partition plate 90 As shown in FIG. 2, in the indoor unit 100 according to the first embodiment, a partition plate 90 is provided between adjacent fans 20. These partition plates 90 are installed between the heat exchanger 50 and the fan 20. That is, the air path between the heat exchanger 50 and the fan 20 is divided into a plurality of air paths (three in the first embodiment). Since the partition plate 90 is installed between the heat exchanger 50 and the fan 20, the end on the side in contact with the heat exchanger 50 has a shape along the heat exchanger 50. More specifically, as shown in FIG. 1, the heat exchanger 50 includes a longitudinal section from the front side to the rear side of the indoor unit 100 (that is, a longitudinal section when the indoor unit 100 is viewed from the right side. Are arranged in a substantially ⁇ shape. For this reason, the heat exchanger 50 side end part of the partition plate 90 is also substantially [Lambda] type.
  • the position of the end portion of the partition plate 90 on the fan 20 side may be determined as follows, for example.
  • the end of the partition plate 90 on the fan 20 side may be extended to the outlet surface of the fan 20.
  • the adjacent fans 20 are close enough to influence each other on the suction side, and the shape of the end of the upper portion 5a of the bell mouth 5 (arc portion on the suction side) can be formed sufficiently large.
  • the end of the plate 90 on the fan 20 side extends to the upstream side (suction side) of the fan 20 so as not to affect the adjacent air path (so that the adjacent fans 20 do not affect each other on the suction side). It may be extended.
  • the partition plate 90 can be formed of various materials.
  • the partition plate 90 may be formed of a metal such as steel or aluminum.
  • the partition plate 90 may be formed of resin or the like.
  • the heat exchanger 50 becomes a high temperature during the heating operation, when the partition plate 90 is formed of a low melting point material such as a resin, the heat exchanger 50 is slightly between the partition plate 90 and the heat exchanger 50. A good space should be formed.
  • the partition plate 90 is made of a material having a high melting point such as aluminum or steel, the partition plate 90 may be disposed in contact with the heat exchanger 50.
  • the heat exchanger 50 is, for example, a fin tube type heat exchanger, a partition plate 90 may be inserted between the fins of the heat exchanger 50.
  • the air path between the heat exchanger 50 and the fan 20 is divided into a plurality of air paths (three in the first embodiment).
  • a noise absorbing material can be provided in this air passage, that is, in the partition plate 90 and the casing 1 to reduce noise generated in the duct.
  • these divided air paths are formed in a substantially square shape with one side being L1 and L2 in a plan view. That is, the width of the divided air path is L1 and L2. For this reason, for example, the amount of air generated by the fan 20 installed inside the substantially square shape formed by L1 and L2 is reliably transferred to the heat exchanger 50 in the region surrounded by L1 and L2 downstream of the fan 20. pass.
  • the air blown from each fan 20 is blown into the indoor unit 100 even if the flow field created downstream by the fan 20 has a swirling component. Cannot move freely in the longitudinal direction (the direction perpendicular to the plane of FIG. 1). For this reason, the air blown out by the fan 20 can be passed through the heat exchanger 50 in the region surrounded by L1 and L2 downstream of the fan 20. As a result, variation in the air volume distribution in the longitudinal direction of the indoor unit 100 flowing into the entire heat exchanger 50 (in the direction orthogonal to the plane of FIG. 1) can be suppressed, and high heat exchange performance can be achieved.
  • each partition plate 90 does not need to be formed with a single plate, and may be formed with a plurality of plates.
  • the partition plate 90 may be divided into two parts on the front side heat exchanger 51 side and the back side heat exchanger 55 side. Needless to say, it is preferable that there is no gap at the joint between the plates constituting the partition plate 90. By dividing the partition plate 90 into a plurality of parts, the assembling property of the partition plate 90 is improved.
  • the fan 20 is rotationally driven by a fan motor 30.
  • the fan motor 30 used may be an inner rotor type or an outer rotor type.
  • the outer rotor type fan motor 30 a structure in which the rotor is integrated with the boss 21 of the fan 20 (the boss 21 is provided with a rotor) is also used. Further, by making the size of the fan motor 30 smaller than the size of the boss 21 of the fan 20, it is possible to prevent loss of the airflow generated by the fan 20. Further, by arranging a motor inside the boss 21, the axial dimension can be reduced. By making the fan motor 30 and the fan 20 easy to attach and detach, the maintainability is also improved.
  • the use of a relatively expensive DC brushless motor as the fan motor 30 can improve efficiency, extend the service life, and improve the controllability. However, even if other types of motors are used, air conditioning It goes without saying that the primary function of the machine is satisfied. Further, the circuit for driving the fan motor 30 may be integrated with the fan motor 30 or may be configured externally to take dust and fire prevention measures.
  • the fan motor 30 is attached to the casing 1 by a motor stay 16. Further, the fan motor 30 is a box type (fan 20, housing, fan motor 30, bell mouth 5, motor stay 16 and the like are integrated into a module) used for CPU cooling and the like, and is detachable from the casing 1. If the structure is possible, the maintainability is improved and the accuracy of the chip clearance of the fan 20 can be increased. In general, a narrow tip clearance is preferable because of high air blowing performance.
  • the drive circuit of the fan motor 30 may be configured inside the fan motor 30 or may be outside.
  • the motor stay 16 includes a fixing member 17 and a support member 18.
  • the fixing member 17 is to which the fan motor 30 is attached.
  • the support member 18 is a member for fixing the fixing member 17 to the casing 1.
  • the support member 18 is, for example, a rod-like member, and extends from the outer peripheral portion of the fixing member 17, for example, radially. As shown in FIG. 1, the support member 18 according to the first embodiment extends approximately in the horizontal direction.
  • the support member 18 may provide a stationary blade effect as a blade shape or a plate shape.
  • the heat exchanger 50 of the indoor unit 100 according to Embodiment 1 is arranged on the leeward side of the fan 20.
  • the heat exchanger 50 for example, a fin tube heat exchanger or the like may be used.
  • the heat exchanger 50 is divided by a symmetry line 50a in the right vertical section.
  • the symmetry line 50a divides the installation range of the heat exchanger 50 in this cross section in the left-right direction at a substantially central portion. That is, the front side heat exchanger 51 is on the front side (left side in FIG. 1) with respect to the symmetry line 50a, and the rear side heat exchanger 55 is on the back side (right side in FIG. 1) with respect to the symmetry line 50a.
  • Each is arranged.
  • the front-side heat exchanger 51 and the rear-side heat exchanger 55 are arranged so that the distance between the front-side heat exchanger 51 and the rear-side heat exchanger 55 widens with respect to the air flow direction, that is, the right-side longitudinal section.
  • the heat exchanger 50 is arranged in the casing 1 so that the cross-sectional shape of the heat exchanger 50 is substantially ⁇ -shaped. That is, the front side heat exchanger 51 and the back side heat exchanger 55 are arranged so as to be inclined with respect to the flow direction of the air supplied from the fan 20.
  • the heat exchanger 50 is characterized in that the air passage area of the rear heat exchanger 55 is larger than the air passage area of the front heat exchanger 51. That is, in the heat exchanger 50, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51.
  • the longitudinal length of the back side heat exchanger 55 is longer than the longitudinal length of the front side heat exchanger 51 in the right vertical section.
  • the air path area of the back surface side heat exchanger 55 is larger than the air path area of the front surface side heat exchanger 51.
  • the other configurations (such as the length in the depth direction in FIG. 1) of the front side heat exchanger 51 and the back side heat exchanger 55 are the same. That is, the heat transfer area of the back side heat exchanger 55 is larger than the heat transfer area of the front side heat exchanger 51.
  • the rotating shaft 20a of the fan 20 is installed above the symmetry line 50a.
  • the heat exchanger 50 By configuring the heat exchanger 50 in this manner, the generation of a swirling flow of the air blown from the blower outlet 3 and the distribution of the wind speed are compared with a conventional air conditioner indoor unit in which a fan is provided at the blower outlet. Occurrence can be suppressed.
  • the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. And when the air which passed each of the front side heat exchanger 51 and the back side heat exchanger 55 merges by this air volume difference, this merged air will bend to the front side (blower outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced.
  • the flow direction of the air flowing out from the back side heat exchanger 55 is the flow from the back side to the front side. For this reason, the indoor unit 100 according to the first embodiment bends the flow of air after passing through the heat exchanger 50, as compared with the case where the heat exchanger 50 is arranged in a substantially v shape in the right vertical section. It becomes easy.
  • the indoor unit 100 has a plurality of fans 20 and thus tends to be heavy.
  • the strength of the wall surface for installing the indoor unit 100 is required, which is a restriction on installation. For this reason, it is preferable to reduce the weight of the heat exchanger 50.
  • positions the fan 20 in the upstream of the heat exchanger 50 the height dimension of the indoor unit 100 becomes large and tends to become restrictions on installation. For this reason, it is preferable to reduce the weight of the heat exchanger 50.
  • a fin tube heat exchanger is used as the heat exchanger 50 (the front side heat exchanger 51 and the back side heat exchanger 55), and the heat exchanger 50 is downsized.
  • the heat exchanger 50 according to the first embodiment includes a plurality of fins 56 stacked via a predetermined gap, and a plurality of heat transfer tubes 57 penetrating the fins 56.
  • the fins 56 are stacked in the left-right direction of the casing 1 (the direction orthogonal to the plane of FIG. 1). That is, the heat transfer tube 57 passes through the fin 56 along the left-right direction of the casing 1 (the direction orthogonal to the plane of FIG. 1).
  • Embodiment 1 in order to improve the heat exchange efficiency of the heat exchanger 50, two rows of heat transfer tubes 57 are arranged in the ventilation direction of the heat exchanger 50 (the width direction of the fins 56). These heat transfer tubes 57 are arranged in a substantially zigzag shape in the right vertical section.
  • the heat transfer tube 57 is formed by a thin tube (diameter of about 3 mm to 7 mm) and the refrigerant flowing through the heat transfer tube 57 (the refrigerant used in the indoor unit 100 and the air conditioner equipped with the indoor unit 100) is R32.
  • the heat exchanger 50 is reduced in size. That is, the heat exchanger 50 exchanges heat between the refrigerant flowing in the heat transfer tube 57 and the room air via the fins 56. For this reason, when the heat transfer tube 57 is made thin, the pressure loss of the refrigerant becomes large at the same refrigerant circulation amount as compared with a heat exchanger having a large heat transfer tube diameter.
  • R32 has a larger latent heat of vaporization at the same temperature than R410A, and can exhibit the same ability with a smaller amount of refrigerant circulation. For this reason, by using R32, the amount of refrigerant to be used can be reduced, and the pressure loss in the heat exchanger 50 can be reduced. Therefore, the heat exchanger 50 can be reduced in size by configuring the heat transfer tube 57 as a thin circular tube and using R32 as the refrigerant.
  • the heat exchanger 50 is reduced in weight by forming the fins 56 and the heat transfer tubes 57 from aluminum or an aluminum alloy.
  • the weight of the heat exchanger 50 does not become an installation-like restriction
  • the finger guard 15 and the filter 10 are provided at the suction port 2.
  • the finger guard 15 is installed for the purpose of preventing the rotating fan 20 from being touched.
  • the shape of the finger guard 15 is arbitrary as long as the hand cannot be touched to the fan 20.
  • the shape of the finger guard 15 may be a lattice shape, or may be a circular shape formed of a large number of different rings.
  • the finger guard 15 may be made of a material such as a resin or a metal material. However, when strength is required, the finger guard 15 is preferably made of a metal.
  • the finger guard 15 is preferably as thin and strong as possible from the viewpoint of lowering ventilation resistance and maintaining strength.
  • the filter 10 is provided to prevent dust from flowing into the indoor unit 100.
  • the filter 10 is detachably provided on the casing 1.
  • the indoor unit 100 which concerns on this Embodiment 1 may be provided with the automatic cleaning mechanism which cleans the filter 10 automatically.
  • the indoor unit 100 which concerns on this Embodiment 1 is provided in the blower outlet 3 with the up-and-down vane 70 and the right-and-left vane (not shown) which are mechanisms which control the blowing direction of airflow.
  • FIG. 3 is a perspective view of the indoor unit according to Embodiment 1 of the present invention as viewed from the front right side.
  • FIG. 4 is a perspective view of the indoor unit as viewed from the rear right side.
  • FIG. 5 is a perspective view of the indoor unit as viewed from the front left side.
  • FIG. 6 is a perspective view showing the drain pan according to Embodiment 1 of the present invention.
  • the right side of the indoor unit 100 is shown in cross section
  • FIG. 5 the left side of the indoor unit 100 is shown in cross section.
  • a front side drain pan 110 is provided below a lower end portion of the front side heat exchanger 51 (a front side end portion of the front side heat exchanger 51).
  • a back side drain pan 115 is provided below the lower end portion of the back side heat exchanger 55 (the back side end of the back side heat exchanger 55).
  • the back side drain pan 115 and the back portion 1b of the casing 1 are integrally formed.
  • the back side drain pan 115 is provided with connection ports 116 to which the drain hose 117 is connected at both the left end and the right end. In addition, it is not necessary to connect the drain hose 117 to both the connection ports 116, and the drain hose 117 may be connected to one of the connection ports 116.
  • the drain hose 117 when the drain hose 117 is to be pulled out to the right side of the indoor unit 100 during the installation work of the indoor unit 100, the drain hose 117 is connected to the connection port 116 provided at the right end of the back side drain pan 115, and the back side
  • the connection port 116 provided at the left end of the drain pan 115 may be closed with a rubber cap or the like.
  • the front side drain pan 110 is disposed at a position higher than the back side drain pan 115. Further, between the front side drain pan 110 and the back side drain pan 115, a drainage channel 111 serving as a drain moving path is provided at both the left end and the right end.
  • the drainage channel 111 has a front end connected to the front drain pan 110 and is provided so as to incline downward from the front drain pan 110 toward the rear drain pan 115.
  • a tongue portion 111 a is formed at the end of the drainage channel 111 on the back side. The rear end of the drainage channel 111 is disposed so as to cover the upper surface of the back side drain pan 115.
  • the front-side drain pan 110 is provided at a position higher than the back-side drain pan 115, so that the drain collected by the front-side drain pan 110 is directed toward the back-side drain pan 115 toward the drainage channel 111. Flowing.
  • the drain is dropped from the tongue 111 a of the drainage channel 111 to the back side drain pan 115 and collected by the back side drain pan 115.
  • the drain collected by the back side drain pan 115 passes through the drain hose 117 and is discharged to the outside of the casing 1 (indoor unit 100).
  • the drain collected by both drain pans is disposed on the back-side drain pan 115 (most rear side of the casing 1). Can be collected in the drain pan).
  • the connection port 116 of the drain hose 117 in the back side drain pan 115 the drain collected by the front side drain pan 110 and the back side drain pan 115 can be discharged to the outside of the casing 1. Therefore, when performing maintenance (such as cleaning the heat exchanger 50) of the indoor unit 100 by opening the front surface of the casing 1, it is not necessary to attach or detach the drain pan to which the drain hose 117 is connected. Improves.
  • the drainage channels 111 are provided at both the left end and the right end, even if the indoor unit 100 is installed in an inclined state, the drain collected by the front side drain pan 110 can be surely received from the back side drain pan. 115.
  • the connection ports for connecting the drain hose 117 are provided at both the left end and the right end, the hose pull-out direction can be selected according to the installation conditions of the indoor unit 100, and the indoor unit 100 The workability when installing is improved.
  • the drainage channel 111 is disposed so as to cover the backside drain pan 115 (that is, a connection mechanism is not required between the drainage channel 111 and the backside drain pan 115), the front side drain pan 110 is disposed. It becomes easy to attach and detach, and the maintainability is further improved.
  • the drainage channel 111 may be disposed so that the rear side end of the drainage channel 111 is connected to the rear side drain pan 115 and the front side drain pan 110 covers the drainage channel 111. Even in such a configuration, it is possible to obtain the same effect as the configuration in which the drainage channel 111 is disposed so as to cover the back side drain pan 115. Further, the front-side drain pan 110 does not necessarily need to be higher than the rear-side drain pan 115. Even if the front-side drain pan 110 and the rear-side drain pan 115 have the same height, the drain collected by both drain pans is connected to the rear-side drain pan 115. The drainage hose can be discharged.
  • the indoor unit 100 according to Embodiment 1 has an opening length d1 on the entrance side of the nozzle 6 in the right vertical section (between the drain pans defined between the front-side drain pan 110 and the back-side drain pan 115 portion.
  • the throttle length d1) is configured to be larger than the opening length d2 on the outlet side of the nozzle 6 (the length of the outlet 3). That is, the nozzle 6 of the indoor unit 100 satisfies d1> d2 (see FIG. 1).
  • d2 of the indoor unit 100 according to the first embodiment is approximately the same as the air outlet of the conventional indoor unit. It will be described as being length.
  • the air passage becomes larger and the angle A of the heat exchanger 50 arranged on the upstream side (the front side heat on the downstream side of the heat exchanger 50). It is possible to increase the angle formed by the exchanger 51 and the back side heat exchanger 55. For this reason, the wind speed distribution generated in the heat exchanger 50 is relaxed, and the air path downstream of the heat exchanger 50 can be formed large, so that the pressure loss of the entire indoor unit 100 can be reduced. Furthermore, the deviation of the wind speed distribution that has occurred near the inlet of the nozzle 6 can be made uniform by the effect of contraction and guided to the outlet 3.
  • the indoor unit 100 according to Embodiment 1 is provided with an active silencing mechanism as shown in FIG.
  • the silencing mechanism of the indoor unit 100 includes a noise detection microphone 161, a control speaker 181, a silencing effect detection microphone 191, and a signal processing device 201.
  • the noise detection microphone 161 is a noise detection device that detects the operation sound (noise) of the indoor unit 100 including the blowing sound of the fan 20.
  • the noise detection microphone 161 is disposed between the fan 20 and the heat exchanger 50. In the first embodiment, it is provided on the front surface in the casing 1.
  • the control speaker 181 is a control sound output device that outputs a control sound for noise.
  • the control speaker 181 is disposed below the noise detection microphone 161 and above the heat exchanger 50.
  • the silencing effect detection microphone 191 is a silencing effect detection device that detects the silencing effect by the control sound.
  • the muffler effect detection microphone 191 is provided in the vicinity of the air outlet 3 in order to detect noise coming from the air outlet 3. Further, the muffler effect detection microphone 191 is attached at a position avoiding the wind flow so as not to hit the blown air coming out of the blowout port 3.
  • the signal processing device 201 is a control sound generation device that causes the control speaker 181 to output a control sound based on the detection results of the noise detection microphone 161 and the silencing effect detection microphone 191.
  • the signal processing device 201 is accommodated in the control device 281, for example.
  • FIG. 8 is a block diagram showing the signal processing apparatus according to Embodiment 1 of the present invention.
  • Electric signals input from the noise detection microphone 161 and the muffler effect detection microphone 191 are amplified by the microphone amplifier 151 and converted from an analog signal to a digital signal by the A / D converter 152.
  • the converted digital signal is input to the FIR filter 158 and the LMS algorithm 159.
  • the FIR filter 158 generates a control signal that has been corrected so that the noise detected by the noise detection microphone 161 has the same amplitude and opposite phase as the noise when the noise reduction effect detection microphone 191 is installed.
  • the indoor unit 100 is provided with a water receptacle or the like (not shown) for preventing water droplets from coming out of the air outlet 3 in the vicinity of the air outlet 3.
  • a water receptacle or the like not shown
  • positioned is upstream of the area
  • the operation sound (noise) including the blowing sound of the fan 20 in the indoor unit 100 is detected by the noise detection microphone 161 attached between the fan 20 and the heat exchanger 50, and the microphone amplifier 151 and the A / D converter 152 are detected. And is input to the FIR filter 158 and the LMS algorithm 159.
  • the tap coefficients of the FIR filter 158 are sequentially updated by the LMS algorithm 159.
  • the coefficient is updated.
  • h is a filter tap coefficient
  • e is an error signal
  • x is a filter input signal
  • ⁇ is a step size parameter.
  • the step size parameter ⁇ controls a filter coefficient update amount for each sampling.
  • the digital signal that has passed through the FIR filter 158 whose tap coefficient has been updated by the LMS algorithm 159 is converted to an analog signal by the D / A converter 154, amplified by the amplifier 155, and the fan 20 and heat exchanger. 50 is emitted as a control sound from the control speaker 181 attached between the indoor unit 100 and the air passage in the indoor unit 100.
  • the sound is transmitted from the fan 20 through the air path to the muffler effect detection microphone 191 attached in the direction of the outer wall of the air outlet 3 so that the wind emitted from the air outlet 3 does not hit.
  • the sound after the control sound emitted from the control speaker 181 interferes with the noise coming out from the blow outlet 3 is detected. Since the sound detected by the muffling effect detection microphone 191 is input to the error signal of the LMS algorithm 159 described above, the tap coefficient of the FIR filter 158 is updated so that the sound after the interference approaches zero. become. As a result, noise in the vicinity of the air outlet 3 can be suppressed by the control sound that has passed through the FIR filter 158.
  • the noise detection microphone 161 and the control speaker 181 are arranged between the fan 20 and the heat exchanger 50, and the silencing effect detection microphone 191 is connected to the blower outlet 3. It is installed in the place where the wind current does not hit. For this reason, since it is not necessary to attach a member that requires active silencing to the region B where condensation occurs, water droplets are prevented from adhering to the control speaker 181, the noise detecting microphone 161, and the silencing effect detecting microphone 191, and the silencing performance is deteriorated. The failure of the speaker and microphone can be prevented.
  • the mounting positions of the noise detection microphone 161, the control speaker 181 and the mute effect detection microphone 191 shown in the first embodiment are merely examples.
  • the noise reduction effect detection microphone 191 may be disposed between the fan 20 and the heat exchanger 50 together with the noise detection microphone 161 and the control speaker 181.
  • the microphone has been exemplified as a means for detecting the silencing effect after the noise is canceled by the noise or the control sound, it may be configured by an acceleration sensor or the like that detects the vibration of the casing.
  • the sound may be regarded as air flow disturbance, and the noise reduction effect after the noise is canceled by noise or control sound may be detected as air flow disturbance.
  • a flow rate sensor, a hot wire probe, or the like that detects an air flow may be used as a means for detecting a silencing effect after noise is canceled by noise or control sound. It is also possible to detect the air flow by increasing the gain of the microphone.
  • the FIR filter 158 and the LMS algorithm 159 are used in the signal processing device 201.
  • any adaptive signal processing circuit that brings the sound detected by the mute effect detection microphone 191 close to zero may be active.
  • a filtered-X algorithm that is generally used in the dynamic silencing method may be used.
  • the signal processing device 201 may be configured to generate the control sound by a fixed tap coefficient instead of the adaptive signal processing.
  • the signal processing device 201 may be an analog signal processing circuit instead of digital signal processing.
  • the present invention is applicable even when the heat exchanger 50 that does not cause condensation is disposed. Therefore, it is possible to prevent performance deterioration of the noise detection microphone 161, the control speaker 181, the silencing effect detection microphone 191, and the like without considering the presence or absence of dew condensation due to the heat exchanger 50.
  • FIG. ⁇ Pre-filter> By installing the filter 10 as follows, effects such as reduction of the pressure loss of the filter and improvement of the wind speed distribution of the airflow flowing into the heat exchanger can be obtained. That is, by installing the filter 10 as described below, it is possible to suppress a decrease in heat exchange performance.
  • the same functions and configurations as those in the first embodiment will be described using the same reference numerals.
  • FIG. 10 is a longitudinal sectional view showing the indoor unit according to Embodiment 2 of the present invention.
  • the indoor unit 100 according to the second embodiment is different from the indoor unit 100 according to the first embodiment in the installation position of the filter 10. More specifically, in the indoor unit 100 according to the second embodiment, the filter 10 is disposed on the upstream side of the finger guard 15 (for example, the upper surface portion of the finger guard 15).
  • the reinforcing member of the filter 10 is for preventing the filter 10 from interfering with the fan 20, and is, for example, a member having a lattice shape or a vertical lattice shape. That is, by installing the filter 10 on the upstream side of the finger guard 15, the finger guard 15 not only functions as a finger guard 15 that prevents the fingers from entering the fan 20, but also interferes with the fan 20 and the filter 10. It also serves as a strength member to prevent. In other words, the reinforcing member of the filter 10 can be used as the finger guard 15. For this reason, since the reinforcing member provided in the conventional filter becomes unnecessary, the cost can be reduced by the amount of the reinforcing member.
  • the filter 10 is disposed on the upstream side of the finger guard 15, the distance between the filter 10 and the fan 20 is increased. For this reason, as shown in FIG. 10, the effective air path (hereinafter referred to as the front area) that actually passes through the filter 10 can be increased. For this reason, the pressure loss of the filter 10 at the same air volume can be reduced.
  • the shape of the finger guard 15 may be changed so that the front surface area of the filter 10 is enlarged.
  • the filter 10 and the finger guard 15 may be configured as separate bodies (both are detachable), or may be configured in an integrated shape by bonding or the like, for example.
  • the finger guard 15 is formed by inclining the peripheral portion of the finger guard 15 downward so that the front surface area of the filter 10 is enlarged.
  • Embodiment 3 the filter 10 may be installed on the downstream side of the fan 20.
  • items that are not particularly described are the same as those in the second embodiment, and the same functions and configurations are described using the same reference numerals.
  • FIG. 11 is a longitudinal sectional view showing the indoor unit according to Embodiment 3 of the present invention.
  • the indoor unit 100 according to the third embodiment is different from the indoor unit 100 according to the first and second embodiments in the installation position of the filter 10. More specifically, in the indoor unit 100 according to the third embodiment, the filter 10 is disposed between the fan 20 and the heat exchanger 50.
  • the filter 10 according to the third embodiment has a shape in which the front side and the back side are bent obliquely downward along the upper surface portion of the heat exchanger 50.
  • the filter 10 is bent to the front side and the back side of the casing 1, the front surface area of the filter 10 can be increased. For this reason, the pressure loss of the filter 10 can be reduced, and variation in the wind speed distribution generated in the heat exchanger 50 can be reduced. Therefore, the performance of the indoor unit 100 can be improved.
  • the filter 10 when forming the filter 10 by bending, as shown in FIG. 12, for example, the filter 10 may be formed by bending only the front side of the casing. By forming the filter 10 in this manner, the filter 10 can be easily attached and detached from the front side of the casing 1.
  • Embodiment 4 when the filter 10 is installed on the downstream side of the fan 20, if the distance between the filter 10 and the fan 20 can be sufficiently secured, for example, the filter 10 may be installed as follows.
  • items that are not particularly described are the same as those in Embodiment 2 or Embodiment 3, and the same functions and configurations are described using the same reference numerals.
  • FIG. 13 is a longitudinal sectional view of an indoor unit according to Embodiment 4 of the present invention.
  • the filter 10 is disposed between the fan 20 and the heat exchanger 50, similarly to the indoor unit 100 according to the third embodiment.
  • the shape of the filter 10 provided in the indoor unit 100 according to the fourth embodiment is different from the filter 10 shown in the third embodiment. More specifically, in the third embodiment, in order to ensure the front area of the filter 10 (in order to ensure a space where a part of the airflow blown from the fan 20 is temporarily converted into static pressure), the front side and the rear side The side was bent.
  • the indoor unit 100 according to Embodiment 4 can sufficiently secure the distance between the filter 10 and the fan 20, the filter 10 has a substantially planar shape (the front side and the back side are not bent). .
  • D indicates the diameter of the fan 20 (more specifically, the impeller 25 of the fan 20). If a sufficient distance between the filter 10 and the fan 20 can be secured, even if the filter 10 has a shape as shown in FIG. 13, a part of the airflow blown from the fan 20 can be converted into a static pressure.
  • the filter 10 and the fan 20 are arranged symmetrically with respect to the plane, noise generated when the airflow blown from the fan 20 directly collides with the heat exchanger (the filter 10 is replaced with the fan 20).
  • the noise generated when the airflow blown out from the fan 20 collides with the asymmetric filter 10 (the filter 10 in which only the front side is bent as shown in FIG. 12) is prevented. It becomes possible.
  • the filter 10 having the shape shown in the fourth embodiment on the downstream side of the fan 20, the following effects can be obtained.
  • 14 and 15 are explanatory views (longitudinal sectional views) for explaining airflow generated inside the indoor unit according to Embodiment 3 of the present invention.
  • 14 is an explanatory diagram (longitudinal sectional view) for explaining the airflow generated inside the indoor unit 100 shown in FIG. 11, and
  • FIG. 15 is generated inside the indoor unit 100 shown in FIG. It is explanatory drawing (longitudinal sectional view) for demonstrating an airflow.
  • the air blown from the fan 20 flows along the inclined range of the filter 10. That is, if the filter 10 has a tilted range, the airflow blown from the fan 20 becomes an airflow that flows toward the areas shown in D and E of FIG. 14 and F of FIG. Therefore, a large amount of airflow that has passed through the regions shown in FIGS. 14D and E and FIG. 15F flows into the heat exchanger 50. For this reason, the velocity distribution of the airflow flowing into the heat exchanger 50 varies.
  • the substantially planar filter 10 is arranged so that the filter 10 and the fan 20 are plane-symmetric. For this reason, the airflow blown out from the fan 20 is uniformly rectified by the fan 20. For this reason, the wind speed distribution generated in the heat exchanger downstream of the filter 10 can be improved, and the performance of the indoor unit 100 can be improved.
  • Embodiment 5 the filter 10 may be arranged on both the upstream side and the downstream side of the fan 20.
  • items that are not particularly described are the same as those in Embodiments 2 to 4, and the same functions and configurations are described using the same reference numerals.
  • FIG. 16 is a longitudinal sectional view showing an indoor unit according to Embodiment 5 of the present invention.
  • filters 10 are installed on both the upstream side and the downstream side of the fan 20.
  • the total pressure loss of the filter 10 provided on the upstream side and the downstream side of the fan 20 is the filter 10 shown in the second embodiment (installed only on the upstream side of the fan 20).
  • the pressure loss of the filter) and the pressure loss of the filter 10 shown in the third and fourth embodiments.
  • the total of these pressure losses is shown in the second embodiment by adjusting the roughness and front surface area of each of the filters 10 provided on the upstream side and the downstream side of the fan 20.
  • Pressure loss of the filter 10 (filter installed only on the upstream side of the fan 20) and pressure loss of the filter 10 (filter provided only on the downstream side of the fan 20) shown in the third and fourth embodiments It is set at the same level.
  • a honeycomb structure having a rectifying effect may be used.
  • a honeycomb structure cleaning filter not only dust collection but also an air cleaning function can be added.
  • a member having ventilation resistance may be disposed at the position of the filter 10 installed on the downstream side of the fan 20.
  • the airflow flowing into the heat exchanger 50 can be rectified, and the velocity distribution of the airflow flowing into the heat exchanger 50 can be improved (that is, heat The heat exchange performance of the exchanger 50 can be improved).
  • a heat exchanger other than the heat exchanger 50 may be provided as a member having ventilation resistance installed on the downstream side of the fan 20. Thereby, the performance (air conditioning performance) of the indoor unit 100 can be improved.
  • Embodiment 6 FIG. Moreover, you may collect
  • items that are not particularly described are the same as those in Embodiments 2 to 5, and the same functions and configurations are described using the same reference numerals.
  • the indoor unit 100 according to Embodiment 5 has a configuration in which the filters 10 are arranged on both the upstream side and the downstream side of the fan 20. For this reason, when the thickness (width in the front-rear direction) of the indoor unit 100 is configured to be thin, the front surface area of the filter 10 may decrease, and the pressure loss may increase.
  • the filter 10 may be installed only on the downstream side of the fan 20 and the dust adhering to the fan 20 may be collected as follows.
  • a filter in which the fan 20 is reversely rotated or the operating point of the fan 20 is changed to surging the fan 20 to drop dust attached to the fan 20, and the dropped dust is installed on the downstream side of the fan 20. 10 may be recovered.
  • the pressure applied to the fan 20 is increased by fully closing the air outlet 3 of the indoor unit 100 with the upper and lower vanes 70, the left and right vanes 80, etc., surging can be caused in the fan 20.
  • Embodiment 7 FIG. ⁇ Motor support structure>
  • noise can be suppressed by attaching the fan 20 to the casing 1 with the motor stay 16 as described below. Further, by using together with the filter 20 mounting structure described in the second to sixth embodiments, noise generated in the motor stay 16 can be suppressed.
  • the same functions and configurations as those in the first to sixth embodiments are described using the same reference numerals.
  • FIG. 17 is a longitudinal sectional view showing an indoor unit according to Embodiment 7 of the present invention.
  • the indoor unit 100 according to the seventh embodiment includes a fan 20 in which a fan motor 30 is connected to a boss 21.
  • the fan motor 30 is attached to the casing 1 by a motor stay 16.
  • the motor stay 16 includes a fixing member 17 and a support member 18.
  • the fixing member 17 is to which the fan motor 30 is attached.
  • the support member 18 is a member for fixing the fixing member 17 to the casing 1.
  • the support member 18 is, for example, a rod-like member, and extends from the outer peripheral portion of the fixing member 17, for example, radially.
  • the filter 10 is provided on the downstream side of the fan 20.
  • the motor stay 16 and the filter 10 are provided close to each other (for example, both are in contact with each other).
  • the support member 18 may provide a stationary blade effect as a blade shape or a plate shape.
  • the airflow discharged from the fan 20 has a velocity distribution.
  • the airflow having this velocity distribution collides with a downstream structure (for example, the motor stay 16), so that noise synchronized with the product of the rotational speed of the fan 20 and the number of blades is generated.
  • a member having ventilation resistance is installed downstream of the fan 20
  • the filter 10 (a member having ventilation resistance) is installed downstream of the fan 20.
  • a motor stay 16, which is a main structure of the noise generation source, is installed in the vicinity of the filter 10. For this reason, since the airflow with a reduced velocity distribution collides with the motor stay 16, the amount of fluctuation of the load applied to the motor stay 16 is reduced, and noise generated from the motor stay 16 can be suppressed.
  • the motor stay 16 is installed in the vicinity of the filter 10” indicates the following state.
  • a steep velocity deficit region region where the flow velocity is slow
  • the length of the velocity deficit area in the airflow direction is approximately the same as the dimension of the motor stay 16 projected in the airflow direction. Since the velocity deficit region is a portion where the velocity change of the air current is remarkable, strong vortices and turbulence of the air current are generated in the velocity deficit region due to the shearing force due to the velocity difference of the air current. As the strong vortex and air current turbulence occur, the amount of noise generated increases.
  • the wake (downstream airflow) of the fan 20 has a complex flow velocity distribution
  • the direction of the airflow that collides with the motor stay 16 varies.
  • the support member 18 of the motor stay 16 is cut along a cross section orthogonal to the longitudinal direction of the support member 18 and the maximum projection dimension is the maximum projection dimension among the projection dimensions of this cross section, This is substantially equal to the maximum projected dimension. That is, by making the distance between the motor stay 16 and the filter 10 smaller than the maximum projected dimension, it is possible to suppress the generation of noise due to the turbulence of the airflow that occurs in the velocity deficient region.
  • the motor stay 16 is installed in the vicinity of the filter 10” means that the motor stay 16 is arranged so that the distance between the motor stay 16 and the filter 10 is smaller than the maximum projected dimension. This means that it is installed upstream of the filter 10.
  • the filter 10 is provided below the motor stay 16 (that is, downstream), but the filter 10 may be provided above the motor stay 16 (that is, upstream) as shown in FIG.
  • the filter 10 is not necessary to provide the motor stay 16 and the filter 10 close to each other. Since the velocity distribution of the airflow that has passed through the filter is small, noise generated from the motor stay 16 can be suppressed as described above.
  • a moving guide for the filter 10 may be formed in the motor stay 16. Furthermore, it is desirable that the distance between the filter 10 as the ventilation resistor and the fan 20 is at least 25% of the fan 20 diameter.
  • the motor stay 16 into the following shape, noise generated from the motor stay 16 can be further suppressed.
  • FIG. 19 is a front view showing an example of a motor stay according to Embodiment 7 of the present invention (a plan view when the motor stay is attached to the indoor unit).
  • a motor stay 16 shown in FIG. 19 has rod-shaped support members 18 extending radially from a substantially disc-shaped fixing member 17. These support members 18 have shapes that do not match the rear edge shape of the blades 23 of the fan 20.
  • the support member 18 is formed in a curved shape, but the support member 18 may be formed in a linear shape. With this configuration, it is possible to prevent a large load from being applied to the support member 18 due to the overlapping of the rear edge portion of the blade 23 of the support member 18 and the fan 20, and further suppress noise generated from the motor stay 16. Can do.
  • the number of support members 18 of the motor stay 16 and the number of blades 23 of the fan 20 may be in a prime relationship.
  • the motor stay 16 By configuring the motor stay 16 in this way, it is possible to prevent the load on all the support members 18 from being in the maximum load state (the state in which the maximum load of the fluctuation amount of the load on the support member 18 is applied). The noise generated from the motor stay 16 can be further suppressed.
  • the noise generated from the motor stay 16 can be further suppressed even if the motor stay 16 has a cross-sectional shape that is dull in the air flow direction, and does not easily induce air flow separation. Furthermore, by providing a soft hair material on the surface of the motor stay 16, it is possible to suppress pressure fluctuations on the surface of the motor stay 16, and to further reduce the generation of noise.
  • the mounting structure of the fan motor 30 to the fixing member 17 is not particularly limited.
  • a fan motor 30 may be attached to the fixing member 17 as shown in FIG.
  • 20 to 23 are perspective views showing examples of attaching the fan motor to the fixing member of the motor stay according to Embodiment 7 of the present invention.
  • FIG. 20 even if the fan motor 30 is fixed by providing a through hole 17a penetrating in the vertical direction in the fixing member 17, and screwing the fan motor 30 with a screw inserted into the through hole 17a. Good.
  • the fan motor 30 is screwed, as shown in FIG. 21, the fan motor 30 is inserted into the fixing member 17 and the fan motor 30 is screwed by forming the through hole 17a on the side surface of the fixing member 17. Good.
  • the fixing member may be constituted by two fixing members 17b obtained by dividing the ring member.
  • the fan motor 30 may be fixed to the fixing member 17 by sandwiching the fan motor 30 with the fixing members 17b and fixing the fixing members 17b to each other with screws.
  • the strength of the shell portion having the weakest strength among the fan motors 30 can be improved. Since the shell portion having the weakest strength in the fan motor 30 is a portion that emits motor noise, the noise emitted from the fan motor 30 can be suppressed by improving the strength of the portion.
  • the fan motor 30 may be fixed to the fixing member 17 by combining a plurality of fixing structures shown in FIGS. In FIG. 23, the fan motor 30 is fixed to the fixing member 17 by using two fixing structures shown in FIG. By fixing the fan motor 30 at two points as described above, an effect of suppressing the swing of the fan motor 30 due to vibration or rotational imbalance can be obtained. Further, it goes without saying that a vibration isolator is provided on the fixing member 17 shown in FIGS. 20 to 23 to weaken the transmission of vibration to the casing 1.
  • the indoor unit 100 including the fan 20 in which the fan motor 30 is connected to the boss 21 has been described.
  • the fan in which the fan motor 30 is connected between the blades 23 and the casing 26 is described.
  • the indoor unit 100 provided with 20 may be sufficient.
  • a support structure 35 (see FIG. 24 described later) that is rotatably attached to the boss 21 may be fixed to the fixing member of the motor stay 16.
  • the motor stay 16 and the filter 10 may be integrally formed so that the motor stay 16 functions as a reinforcing member for the filter 10. Since the reinforcing member provided in the conventional filter is not necessary, the cost can be reduced by the amount of the reinforcing member.
  • Embodiment 8 FIG.
  • the motor stay 16 for attaching the fan 20 to the casing 1 may be configured as follows.
  • items not particularly described are the same as those in the seventh embodiment, and the same functions and configurations are described using the same reference numerals.
  • FIG. 24 is a longitudinal sectional view showing the indoor unit according to Embodiment 8 of the present invention.
  • FIG. 25 is an external perspective view showing the indoor unit. Note that FIG. 25 shows the casing 1 through. 24 and 25 include an indoor unit 100 including a fan 20 in which a fan motor 30 is provided between a blade 23 and a casing 26.
  • the motor stay 16 according to the eighth embodiment is configured by a fixing member 17 provided along the longitudinal direction of the indoor unit 100. Both ends of the fixing member 17 in the longitudinal direction are fixed to the casing 1. And, to this fixing member 17, a support structure 35 (one that rotatably supports the boss 21 of the fan 20) of each of the three fans 20 is fixed. Further, the fixing member 17 is located above the transmutation portion of the heat exchanger 50 (the location where the arrangement gradient of the heat exchanger 50 is transformed, that is, the location where the front side heat exchanger 51 and the back side heat exchanger 55 are connected). Is provided. Although the motor stay 16 according to the eighth embodiment is configured not to include the support member 18, the fixing member 17 may be fixed to the casing 1 by the support member 18.
  • Embodiment 9 FIG. Moreover, you may comprise the motor stay 16 which attaches the fan 20 to the casing 1 as follows.
  • items that are not particularly described are the same as those in the seventh embodiment or the eighth embodiment, and the same functions and configurations are described using the same reference numerals.
  • FIG. 26 is a longitudinal sectional view showing an indoor unit according to Embodiment 9 of the present invention.
  • the support member 18 of the motor stay 16 according to the ninth embodiment is such that the distance between the support member 18 and the rear edge of the blade 23 of the fan 20 is the tip of the blade 23 (the outer peripheral portion of the impeller 25). It is configured to grow as you go.
  • the airflow generated by the fan 20 increases toward the tip of the blade 23 (the outer peripheral portion of the impeller 25). That is, when the distance between the support member 18 and the trailing edge of the blade 23 is the same at the root portion and the tip portion of the blade 23, the load fluctuation amount related to the motor stay 16 is the tip portion of the blade 23 (the outer peripheral portion of the impeller 25. ) Grows toward However, in the ninth embodiment, the distance between the support member 18 and the rear edge of the blade 23 of the fan 20 is configured to increase toward the tip of the blade 23 (the outer peripheral portion of the impeller 25). Therefore, it is possible to suppress the load fluctuation amount related to the motor stay 16.
  • the distance between the support member 18 and the rear edge of the blade 23 becomes the same at the root portion and the tip portion of the blade 23.
  • noise generated from the motor stay 16 can be further suppressed.
  • Embodiment 10 FIG. ⁇ Heat exchanger>
  • the fan 20 is disposed on the upstream side of the heat exchanger 50.
  • production of a wind speed are suppressed compared with the indoor unit of the conventional air conditioner in which the fan is provided in the blower outlet. Therefore, the shape of the heat exchanger 50 is not limited to the shape shown in the first to ninth embodiments, and may be the following shape, for example. In the tenth embodiment, the same functions and configurations as those in the first to ninth embodiments will be described using the same reference numerals.
  • FIG. 27 is a longitudinal sectional view showing the indoor unit according to Embodiment 10 of the present invention.
  • the heat exchanger 50 that is not divided into the front side heat exchanger 51 and the back side heat exchanger 55 is provided on the downstream side of the fan 20.
  • the air that has passed through the filter 10 flows into the fan 20.
  • the air flowing into the fan 20 is less disturbed than the air flowing into the conventional indoor unit (passed through the heat exchanger).
  • the indoor unit 100 according to Embodiment 10 can suppress noise as compared with the conventional indoor unit.
  • the fan 20 is provided in the upstream of the heat exchanger 50, the indoor unit 100 is blown out from the blower outlet 3, compared with the indoor unit of the conventional air conditioner in which the fan is provided in the blower outlet.
  • the generation of the swirling air flow and the generation of the wind speed distribution can be suppressed.
  • there is no complicated structure such as a fan at the air outlet 3 it is easy to take measures against dew condensation caused by backflow or the like.
  • Embodiment 11 By configuring the heat exchanger 50 with the front side heat exchanger 51 and the back side heat exchanger 55, it becomes possible to further suppress noise than the indoor unit 100 according to the tenth embodiment.
  • the shape is not limited to the shape of the heat exchanger 50 shown in the first embodiment, and for example, the shape can be as follows.
  • the eleventh embodiment the difference from the above-described tenth embodiment will be mainly described, and the same parts as those in the tenth embodiment are denoted by the same reference numerals.
  • FIG. 28 is a longitudinal sectional view showing the indoor unit according to Embodiment 11 of the present invention.
  • the front-side heat exchanger 51 and the back-side heat exchanger 55 constituting the heat exchanger 50 are divided by a symmetric line 50a in the right vertical section.
  • the symmetry line 50a divides the installation range of the heat exchanger 50 in this cross section in the left-right direction at a substantially central portion. That is, the front side heat exchanger 51 is arranged on the front side (left side of the drawing) with respect to the symmetry line 50a, and the rear side heat exchanger 55 is arranged on the back side (right side of the drawing) with respect to the symmetry line 50a.
  • the front-side heat exchanger 51 and the rear-side heat exchanger 55 are arranged so that the distance between the front-side heat exchanger 51 and the rear-side heat exchanger 55 is narrow with respect to the air flow direction, that is, the right-side longitudinal section. It is arrange
  • the front side heat exchanger 51 and the back side heat exchanger 55 are arranged so as to be inclined with respect to the flow direction of the air supplied from the fan 20. Furthermore, the air path area of the back surface side heat exchanger 55 is characterized by being larger than the air path area of the front surface side heat exchanger 51.
  • the longitudinal length of the back surface side heat exchanger 55 is longer than the longitudinal direction length of the front surface side heat exchanger 51 in the right vertical section. Thereby, the air path area of the back surface side heat exchanger 55 is larger than the air path area of the front surface side heat exchanger 51.
  • the other configurations of the front side heat exchanger 51 and the back side heat exchanger 55 are the same. That is, the heat transfer area of the back side heat exchanger 55 is larger than the heat transfer area of the front side heat exchanger 51.
  • the rotating shaft 20a of the fan 20 is installed above the symmetry line 50a.
  • the fan 20 is provided on the upstream side of the heat exchanger 50, the same effect as in the tenth embodiment can be obtained.
  • the air of the quantity according to an air path area passes through each of the front side heat exchanger 51 and the back side heat exchanger 55.
  • this merged air will bend to the front side (blower outlet 3 side).
  • the indoor unit 100 according to the eleventh embodiment can further suppress noise compared to the indoor unit 100 according to the tenth embodiment. Moreover, since the indoor unit 100 which concerns on this Embodiment 11 can reduce the pressure loss in the blower outlet 3 vicinity, it also becomes possible to reduce power consumption.
  • the heat exchanger 50 shown in FIG. 28 is comprised by the substantially V shape by the front side heat exchanger 51 and the back side heat exchanger 55 which were formed separately, it is not limited to this structure.
  • the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured as an integrated heat exchanger (see FIG. 37).
  • each of the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured by a combination of a plurality of heat exchangers (see FIG. 37).
  • the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a.
  • the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a.
  • the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction.
  • the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.
  • the heat exchanger 50 is composed of a plurality of heat exchangers (for example, when the heat exchanger 50 is composed of the front side heat exchanger 51 and the back side heat exchanger 55), the location where the arrangement gradient of the heat exchanger 50 changes ( For example, the heat exchangers do not have to be in complete contact with each other at a substantial connection point between the front-side heat exchanger 51 and the back-side heat exchanger 55, and there may be some gaps.
  • the shape of the heat exchanger 50 in the right vertical section may be partially or entirely curved (see FIG. 37).
  • FIG. 37 is a schematic diagram for explaining a configuration example of the heat exchanger 50.
  • This FIG. 37 has shown the heat exchanger 50 seen from the right side longitudinal cross-section.
  • the whole shape of the heat exchanger 50 shown in FIG. 37 is a substantially (LAMBDA) type
  • the whole shape of a heat exchanger is an example to the last.
  • Fig.37 (a) you may comprise the heat exchanger 50 by a some heat exchanger.
  • the heat exchanger 50 may be configured as an integrated heat exchanger.
  • the shape of the heat exchanger 50 may be a curved shape.
  • Embodiment 12 FIG. Moreover, the heat exchanger 50 may be configured as follows. In the twelfth embodiment, the difference from the eleventh embodiment will be mainly described, and the same parts as those in the eleventh embodiment are denoted by the same reference numerals.
  • FIG. 29 is a longitudinal sectional view showing an indoor unit according to Embodiment 12 of the present invention.
  • the indoor unit 100 according to the twelfth embodiment is different from the indoor unit 100 according to the eleventh embodiment in the manner in which the heat exchanger 50 is arranged.
  • the heat exchanger 50 includes three heat exchangers, and each of these heat exchangers has a different inclination with respect to the flow direction of the air supplied from the fan 20. Has been placed. And the heat exchanger 50 is a substantially N type in the right side longitudinal cross-section.
  • the heat exchanger 51a and the heat exchanger 51b arranged on the front side of the symmetry line 50a constitute the front side heat exchanger 51
  • the heat exchanger 55b constitutes the back side heat exchanger 55. That is, in the twelfth embodiment, the heat exchanger 51b and the heat exchanger 55b are configured as an integrated heat exchanger.
  • the symmetry line 50a divides the installation range of the heat exchanger 50 in the right vertical section in the left-right direction at a substantially central portion.
  • the length of the rear side heat exchanger 55 in the longitudinal direction is longer than the length of the front side heat exchanger 51 in the longitudinal direction. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51.
  • the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 51 and the sum of the lengths of the heat exchanger groups constituting the back-side heat exchanger 55. Should be compared.
  • the air volume of the rear side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51.
  • this merged air is the front side (air outlet 3 To the side).
  • the indoor unit 100 according to the twelfth embodiment can further suppress noise compared to the indoor unit 100 according to the tenth embodiment.
  • the indoor unit 100 can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.
  • the shape of the heat exchanger 50 substantially N-shaped in the right vertical section, it is possible to increase the area through which the front-side heat exchanger 51 and the back-side heat exchanger 55 pass.
  • the wind speed can be made smaller than that in the eleventh embodiment. For this reason, compared with Embodiment 11, the pressure loss in the front side heat exchanger 51 and the back side heat exchanger 55 can be reduced, and further reduction in power consumption and noise can be achieved.
  • the heat exchanger 50 shown in FIG. 29 is comprised by the substantially N type by the three heat exchangers formed separately, it is not limited to this structure.
  • each of the three heat exchangers constituting the heat exchanger 50 may be configured by a combination of a plurality of heat exchangers (see FIG. 37).
  • the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a.
  • the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a.
  • the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction.
  • the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.
  • the heat exchanger 50 it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 37). Further, when the heat exchanger 50 is constituted by a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at a place where the arrangement gradient of the heat exchanger 50 changes, and there is a slight gap. May be. Moreover, the shape of the heat exchanger 50 in the right vertical section may be partially or entirely curved (see FIG. 37).
  • Embodiment 13 FIG. Moreover, the heat exchanger 50 may be configured as follows. In the thirteenth embodiment, differences from the above-described eleventh and twelfth embodiments will be mainly described, and the same parts as those in the eleventh and twelfth embodiments are denoted by the same reference numerals. is doing. Moreover, the case where the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.
  • FIG. 30 is a longitudinal sectional view showing an indoor unit according to Embodiment 13 of the present invention.
  • the indoor unit 100 of the thirteenth embodiment is different from the indoor units shown in the eleventh and twelfth embodiments in the manner in which the heat exchanger 50 is arranged.
  • the heat exchanger 50 includes four heat exchangers, and each of these heat exchangers is arranged with a different inclination with respect to the flow direction of the air supplied from the fan 20.
  • the heat exchanger 50 is substantially W-shaped in the right vertical section.
  • the heat exchanger 51a and the heat exchanger 51b arranged on the front side of the symmetry line 50a constitute the front side heat exchanger 51
  • the heat exchanger 55b constitutes the back side heat exchanger 55.
  • the symmetry line 50a divides the installation range of the heat exchanger 50 in the right vertical section in the left-right direction at a substantially central portion.
  • the length of the rear side heat exchanger 55 in the longitudinal direction is longer than the length of the front side heat exchanger 51 in the longitudinal direction. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51.
  • the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 51 and the sum of the lengths of the heat exchanger groups constituting the back-side heat exchanger 55. Should be compared.
  • the air volume of the rear side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51.
  • the indoor unit 100 according to the thirteenth embodiment can further suppress noise compared to the indoor unit 100 according to the tenth embodiment.
  • the indoor unit 100 can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.
  • the area which passes the front side heat exchanger 51 and the back side heat exchanger 55 can be taken large by making the shape of the heat exchanger 50 into a substantially W type in the right vertical section, it passes through each. It becomes possible to make a wind speed smaller than Embodiment 11 and Embodiment 12. For this reason, compared with Embodiment 11 and Embodiment 12, the pressure loss in the front side heat exchanger 51 and the back side heat exchanger 55 can be reduced, and further reduction in power consumption and noise can be achieved. It becomes.
  • the heat exchanger 50 shown in FIG. 30 is comprised by the substantially W shape by the four heat exchangers formed separately, it is not limited to this structure.
  • the four heat exchangers constituting the heat exchanger 50 may be configured as an integrated heat exchanger (see FIG. 37).
  • each of the four heat exchangers constituting the heat exchanger 50 may be configured by a combination of a plurality of heat exchangers (see FIG. 37).
  • the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a.
  • the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a.
  • the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction.
  • the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.
  • the heat exchanger 50 it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 37). Further, when the heat exchanger 50 is constituted by a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at a place where the arrangement gradient of the heat exchanger 50 changes, and there is a slight gap. May be. Moreover, the shape of the heat exchanger 50 in the right vertical section may be partially or entirely curved (see FIG. 37).
  • the heat exchanger 50 may be configured as follows.
  • the fourteenth embodiment differences from the above-described eleventh to thirteenth embodiments will be mainly described, and the same parts as those in the eleventh to thirteenth embodiments are denoted by the same reference numerals. is doing.
  • the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.
  • FIG. 31 is a longitudinal sectional view showing an indoor unit according to Embodiment 14 of the present invention.
  • the arrangement of the heat exchanger 50 is different from the indoor units shown in the eleventh to thirteenth embodiments. More specifically, the indoor unit 100 according to the fourteenth embodiment includes two heat exchangers (a front-side heat exchanger 51 and a rear-side heat exchanger 55) as in the eleventh embodiment. However, the arrangement of the front side heat exchanger 51 and the back side heat exchanger 55 is different from the indoor unit 100 shown in the eleventh embodiment.
  • the front side heat exchanger 51 and the back side heat exchanger 55 are arranged with different inclinations with respect to the flow direction of the air supplied from the fan 20.
  • a front side heat exchanger 51 is arranged on the front side of the symmetry line 50a
  • a back side heat exchanger 55 is arranged on the back side of the symmetry line 50a.
  • the heat exchanger 50 has a substantially ⁇ shape in the right vertical section.
  • the symmetry line 50a divides the installation range of the heat exchanger 50 in the right vertical section in the left-right direction at a substantially central portion.
  • the length of the rear side heat exchanger 55 in the longitudinal direction is longer than the length of the front side heat exchanger 51 in the longitudinal direction. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51.
  • the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 51 and the sum of the lengths of the heat exchanger groups constituting the back-side heat exchanger 55. Should be compared.
  • the indoor unit 100 configured as described above has the following air flow inside.
  • indoor air flows into the indoor unit 100 (casing 1) from the suction port 2 formed in the upper part of the casing 1 by the fan 20.
  • dust contained in the air is removed by the filter 10.
  • this indoor air passes through the heat exchanger 50 (the front-side heat exchanger 51 and the back-side heat exchanger 55), it is heated or cooled by the refrigerant that is conducted through the heat exchanger 50 to become conditioned air.
  • the air passing through the front side heat exchanger 51 flows from the front side to the back side of the indoor unit 100.
  • the air passing through the back side heat exchanger 55 flows from the back side of the indoor unit 100 to the front side.
  • the conditioned air that has passed through the heat exchanger 50 (the front-side heat exchanger 51 and the back-side heat exchanger 55) passes from the outlet 3 formed in the lower part of the casing 1 to the outside of the indoor unit 100, that is, the air-conditioning target area. Blown out.
  • the air volume of the rear side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. Therefore, as in the eleventh to thirteenth embodiments, when the air that has passed through the front-side heat exchanger 51 and the rear-side heat exchanger 55 merges due to the difference in air volume, It will bend to the side (air outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 100 according to the fourteenth embodiment can further suppress noise compared to the indoor unit 100 according to the tenth embodiment. Moreover, since the indoor unit 100 can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.
  • the flow direction of the air flowing out from the back side heat exchanger 55 is the flow from the back side to the front side.
  • the indoor unit 100 which concerns on this Embodiment 14 becomes easier to bend the flow of the air after passing the heat exchanger 50.
  • the heat exchanger 50 shown in FIG. 31 is comprised by the substantially (LAMBDA) type
  • the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured as an integrated heat exchanger (see FIG. 37).
  • each of the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured by a combination of a plurality of heat exchangers (see FIG. 37).
  • the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a.
  • the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a.
  • the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction.
  • the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.
  • the heat exchanger 50 it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 37). Further, when the heat exchanger 50 is constituted by a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at a place where the arrangement gradient of the heat exchanger 50 changes, and there is a slight gap. May be. Moreover, the shape of the heat exchanger 50 in the right vertical section may be partially or entirely curved (see FIG. 37).
  • Embodiment 15 FIG. Moreover, the heat exchanger 50 may be configured as follows. In the fifteenth embodiment, differences from the eleventh to fourteenth embodiments described above will be mainly described, and the same parts as those in the eleventh to fourteenth embodiments are denoted by the same reference numerals. ing.
  • FIG. 32 is a longitudinal sectional view showing an indoor unit according to Embodiment 15 of the present invention.
  • the indoor unit 100 of the fifteenth embodiment is different from the indoor units shown in the eleventh to fourteenth embodiments in the manner in which the heat exchanger 50 is arranged. More specifically, the indoor unit 100 of the fifteenth embodiment is composed of three heat exchangers as in the twelfth embodiment. However, the arrangement of these three heat exchangers is different from the indoor unit 100 shown in the twelfth embodiment.
  • each of the three heat exchangers constituting the heat exchanger 50 is arranged with a different inclination with respect to the flow direction of the air supplied from the fan 20.
  • the heat exchanger 50 has a substantially ⁇ type in the right vertical section.
  • the heat exchanger 51a and the heat exchanger 51b arranged on the front side of the symmetry line 50a constitute the front side heat exchanger 51
  • the heat exchanger 55b constitutes the back side heat exchanger 55. That is, in the fifteenth embodiment, the heat exchanger 51b and the heat exchanger 55b are configured as an integrated heat exchanger.
  • the symmetry line 50a divides the installation range of the heat exchanger 50 in the right vertical section in the left-right direction at a substantially central portion.
  • the length of the rear side heat exchanger 55 in the longitudinal direction is longer than the length of the front side heat exchanger 51 in the longitudinal direction. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51.
  • the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 51 and the sum of the lengths of the heat exchanger groups constituting the back-side heat exchanger 55. Should be compared.
  • the air volume of the rear side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. Therefore, as in the eleventh to fourteenth embodiments, when the air that has passed through the front-side heat exchanger 51 and the rear-side heat exchanger 55 merges due to the difference in air volume, It will bend to the side (air outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 100 according to the fifteenth embodiment can further suppress noise compared to the indoor unit 100 according to the tenth embodiment. Moreover, since the indoor unit 100 can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.
  • the flow direction of the air flowing out from the back side heat exchanger 55 is the flow from the back side to the front side.
  • the indoor unit 100 according to Embodiment 15 can more easily bend the air flow after passing through the heat exchanger 50. That is, the indoor unit 100 according to the fifteenth embodiment can more easily control the airflow of the air blown out from the outlet 3 than the indoor unit 100 according to the twelfth embodiment. Therefore, the indoor unit 100 according to the fifteenth embodiment further eliminates the need to bend the airflow in the vicinity of the outlet 3 more than the indoor unit 100 according to the twelfth embodiment, further reducing power consumption and noise. Is possible.
  • the area passing through the front side heat exchanger 51 and the back side heat exchanger 55 can be increased, so that each passes through.
  • the wind speed can be made smaller than that in the fourteenth embodiment. For this reason, compared with Embodiment 14, the pressure loss in the front side heat exchanger 51 and the back side heat exchanger 55 can be reduced, and further reduction in power consumption and noise can be achieved.
  • the heat exchanger 50 shown in FIG. 32 is comprised by the substantially ⁇ type
  • each of the three heat exchangers constituting the heat exchanger 50 may be configured by a combination of a plurality of heat exchangers (see FIG. 37).
  • the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a.
  • the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a.
  • the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction.
  • the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.
  • the heat exchanger 50 it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 37). Further, when the heat exchanger 50 is constituted by a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at a place where the arrangement gradient of the heat exchanger 50 changes, and there is a slight gap. May be. Moreover, the shape of the heat exchanger 50 in the right vertical section may be partially or entirely curved (see FIG. 37).
  • Embodiment 16 FIG. Moreover, the heat exchanger 50 may be configured as follows. In the sixteenth embodiment, differences from the eleventh to fifteenth embodiments will be mainly described, and the same parts as those in the eleventh to fifteenth embodiments are denoted by the same reference numerals. ing.
  • FIG. 33 is a longitudinal sectional view showing the indoor unit according to Embodiment 16 of the present invention.
  • the indoor unit 100 of the sixteenth embodiment is different from the indoor units shown in the eleventh to fifteenth embodiments in the manner in which the heat exchanger 50 is arranged. More specifically, the indoor unit 100 of the sixteenth embodiment is configured with four heat exchangers as in the thirteenth embodiment. However, the arrangement of these four heat exchangers is different from the indoor unit 100 shown in the thirteenth embodiment.
  • each of the four heat exchangers constituting the heat exchanger 50 is arranged with a different inclination with respect to the flow direction of the air supplied from the fan 20.
  • the heat exchanger 50 has a substantially M shape in the right vertical section.
  • the heat exchanger 51a and the heat exchanger 51b arranged on the front side of the symmetry line 50a constitute the front side heat exchanger 51
  • the heat exchanger 55b constitutes the back side heat exchanger 55.
  • the symmetry line 50a divides the installation range of the heat exchanger 50 in the right vertical section in the left-right direction at a substantially central portion.
  • the length of the rear side heat exchanger 55 in the longitudinal direction is longer than the length of the front side heat exchanger 51 in the longitudinal direction. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51.
  • the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 51 and the sum of the lengths of the heat exchanger groups constituting the back-side heat exchanger 55. Should be compared.
  • the air volume of the rear side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. Therefore, as in the eleventh to fifteenth embodiments, when the air that has passed through the front-side heat exchanger 51 and the rear-side heat exchanger 55 merges due to the difference in air volume, It will bend to the side (air outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 100 according to the sixteenth embodiment can further suppress noise compared to the indoor unit 100 according to the tenth embodiment. Moreover, since the indoor unit 100 can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.
  • the flow direction of the air flowing out from the back side heat exchanger 55 is the flow from the back side to the front side.
  • the indoor unit 100 according to the sixteenth embodiment can more easily bend the air flow after passing through the heat exchanger 50. That is, the indoor unit 100 according to the sixteenth embodiment can more easily control the airflow of the air blown out from the outlet 3 than the indoor unit 100 according to the thirteenth embodiment. Therefore, the indoor unit 100 according to the sixteenth embodiment further eliminates the need to bend the airflow in the vicinity of the air outlet 3 in comparison with the indoor unit 100 according to the thirteenth embodiment, further reducing power consumption and noise. Is possible.
  • the shape of the heat exchanger 50 substantially M-shaped in the right vertical section, it is possible to increase the area that passes through the front-side heat exchanger 51 and the back-side heat exchanger 55.
  • the wind speed can be made smaller than those in the fourteenth and fifteenth embodiments. For this reason, compared with Embodiment 14 and Embodiment 15, the pressure loss in the front side heat exchanger 51 and the back side heat exchanger 55 can be reduced, and further reduction in power consumption and noise is possible. It becomes.
  • the heat exchanger 50 shown in FIG. 33 is comprised by the substantially M type
  • the four heat exchangers constituting the heat exchanger 50 may be configured as an integrated heat exchanger (see FIG. 37).
  • each of the four heat exchangers constituting the heat exchanger 50 may be configured by a combination of a plurality of heat exchangers (see FIG. 37).
  • the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a.
  • the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a.
  • the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction.
  • the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.
  • the heat exchanger 50 it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 37). Further, when the heat exchanger 50 is constituted by a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at a place where the arrangement gradient of the heat exchanger 50 changes, and there is a slight gap. May be. Moreover, the shape of the heat exchanger 50 in the right vertical section may be partially or entirely curved (see FIG. 37).
  • Embodiment 17 FIG. Moreover, the heat exchanger 50 may be configured as follows. In the seventeenth embodiment, the differences from the eleventh to sixteenth embodiments described above will be mainly described, and the same parts as those in the eleventh to sixteenth embodiments are denoted by the same reference numerals. ing.
  • FIG. 34 is a longitudinal sectional view showing an indoor unit according to Embodiment 17 of the present invention.
  • the indoor unit 100 of the seventeenth embodiment is different from the indoor units shown in the eleventh to sixteenth embodiments in the way of arranging the heat exchanger 50. More specifically, the indoor unit 100 according to the seventeenth embodiment is configured with two heat exchangers (a front-side heat exchanger 51 and a rear-side heat exchanger 55), as in the fourteenth embodiment.
  • the pressure loss of the front side heat exchanger 51 and the pressure loss of the back side heat exchanger 55 are made different from each other, whereby the air volume of the front side heat exchanger 51 and the back side heat exchanger 55 are changed. The air volume is different.
  • the front side heat exchanger 51 and the back side heat exchanger 55 are arranged with different inclinations with respect to the flow direction of the air supplied from the fan 20.
  • a front-side heat exchanger 51 is disposed on the front side of the symmetry line 50a, and a back-side heat exchanger 55 is disposed on the back side of the symmetry line 50a.
  • the heat exchanger 50 has a substantially ⁇ shape in the right vertical section.
  • the length in the longitudinal direction of the back side heat exchanger 55 and the length in the longitudinal direction of the front side heat exchanger 51 are the same.
  • the specifications of the front-side heat exchanger 51 and the back-side heat exchanger 55 are determined so that the pressure loss of the back-side heat exchanger 55 is smaller than the pressure loss of the front-side heat exchanger 51.
  • the width of the fins 56 may be smaller than the length in the short side direction of the front side heat exchanger 51 (the width of the fins 56 of the front side heat exchanger 51) in the right vertical section.
  • the distance between the fins 56 of the back surface side heat exchanger 55 may be larger than the distance between the fins 56 of the front surface side heat exchanger 51.
  • the diameter of the heat transfer tube 57 of the back surface side heat exchanger 55 may be smaller than the diameter of the heat transfer tube 57 of the front surface side heat exchanger 51.
  • the number of the heat transfer tubes 57 of the back surface side heat exchanger 55 may be smaller than the number of the heat transfer tubes 57 of the front surface side heat exchanger 51.
  • the symmetry line 50a divides the installation range of the heat exchanger 50 in the right vertical section in the left-right direction at a substantially central portion.
  • the fan 20 is provided on the upstream side of the heat exchanger 50, the same effect as in the tenth embodiment can be obtained.
  • an amount of air corresponding to the pressure loss passes through each of the front side heat exchanger 51 and the back side heat exchanger 55. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. And when the air which passed each of the front side heat exchanger 51 and the back side heat exchanger 55 merges by this air volume difference, this merged air will bend to the front side (blower outlet 3 side).
  • the indoor unit 100 according to the seventeenth embodiment suppresses noise further than the indoor unit 100 according to the tenth embodiment without increasing the length of the back side heat exchanger 55 in the right vertical section. Is possible. Moreover, since the indoor unit 100 can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.
  • the heat exchanger 50 shown in FIG. 34 is comprised by the substantially (LAMBDA) type
  • the shape of the heat exchanger 50 in the right vertical section may be configured to be approximately V-shaped, approximately N-shaped, approximately W-shaped, approximately ⁇ -shaped, approximately M-shaped, or the like.
  • the front side heat exchanger 51 and the back side heat exchanger 55 may be configured as an integrated heat exchanger (see FIG. 37).
  • each of the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured by a combination of a plurality of heat exchangers (see FIG. 37).
  • the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a. That is, the pressure loss of the heat exchanger arranged on the back side of the symmetry line 50a may be made smaller than the pressure loss of the heat exchanger arranged on the front side of the symmetry line 50a.
  • the sum of the pressure losses of the plurality of heat exchangers constituting the front side heat exchanger 51 is configured by a combination of a plurality of heat exchangers, the sum of the pressure losses of the plurality of heat exchangers constituting the front side heat exchanger 51. However, it becomes the pressure loss of the front side heat exchanger 51.
  • the sum of the pressure losses of the plurality of heat exchangers constituting the back side heat exchanger 55 becomes the pressure loss of the back side heat exchanger 55.
  • the heat exchanger 50 is composed of a plurality of heat exchangers (for example, when the heat exchanger 50 is composed of the front side heat exchanger 51 and the back side heat exchanger 55), the location where the arrangement gradient of the heat exchanger 50 changes ( For example, the heat exchangers do not have to be in complete contact with each other at a substantial connection point between the front-side heat exchanger 51 and the back-side heat exchanger 55, and there may be some gaps.
  • the shape of the heat exchanger 50 in the right vertical section may be partially or entirely curved (see FIG. 37).
  • Embodiment 18 FIG. Further, in the above-described eleventh to seventeenth embodiments, the fan 20 may be arranged as follows. In the eighteenth embodiment, differences from the eleventh to seventeenth embodiments described above will be mainly described, and the same parts as those in the eleventh to seventeenth embodiments are denoted by the same reference numerals. ing.
  • FIG. 35 is a longitudinal sectional view showing an indoor unit according to Embodiment 18 of the present invention. A method of arranging the fans 20 in the indoor unit 100 will be described with reference to FIGS.
  • the heat exchanger 50 of the indoor unit 100 according to Embodiment 18 has the same arrangement as the indoor unit 100 of Embodiment 14. However, the indoor unit 100 according to the eighteenth embodiment is different from the indoor unit 100 according to the fourteenth embodiment in the manner in which the fan 20 is arranged. That is, in the indoor unit 100 according to Embodiment 18, the arrangement position of the fan 20 is determined according to the air volume and heat transfer area of the front side heat exchanger 51 and the back side heat exchanger 55.
  • the heat transfer area is larger than that of the front heat exchanger 51.
  • the air volume of the large rear side heat exchanger 55 may be insufficient.
  • the heat exchanger 50 (the front side heat exchanger 51 and the back side heat exchanger 55) may not be able to exhibit desired heat exchange performance.
  • the arrangement position of the fan 20 may be moved in the back direction.
  • the air volume of the back side heat exchanger 55 may be insufficient, such as when the pressure loss of the back side heat exchanger 55 is large.
  • the air volume adjustment by the configuration of the front side heat exchanger 51 and the back side heat exchanger 55 passed through the front side heat exchanger 51 and the back side heat exchanger 55.
  • the air that has joined later cannot be adjusted to a desired angle.
  • the air merged after passing through each of the front surface side heat exchanger 51 and the back surface side heat exchanger 55 may not bend more than a desired angle.
  • the arrangement position of the fan 20 may be moved in the back direction.
  • the heat transfer area of the front side heat exchanger 51 may be larger than the heat transfer area of the back side heat exchanger 55.
  • the arrangement position of the fan 20 may be moved in the front direction.
  • the air volume of the back side heat exchanger 55 may become larger than necessary.
  • the air volume adjustment by the configuration of the front side heat exchanger 51 and the back side heat exchanger 55 passed through the front side heat exchanger 51 and the back side heat exchanger 55.
  • the air merged after passing through each of the front side heat exchanger 51 and the back side heat exchanger 55 may bend more than a desired angle. In such a case, the arrangement position of the fan 20 may be moved in the front direction as shown in FIG.
  • the heat exchanger 50 shown in FIG. 35 is comprised by the substantially (LAMBDA) type
  • the shape of the heat exchanger 50 in the right vertical section may be configured to be approximately V-shaped, approximately N-shaped, approximately W-shaped, approximately ⁇ -shaped, approximately M-shaped, or the like.
  • the front side heat exchanger 51 and the back side heat exchanger 55 may be configured as an integrated heat exchanger (see FIG. 37).
  • each of the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured by a combination of a plurality of heat exchangers (see FIG. 37).
  • the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a.
  • the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a.
  • the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction.
  • the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.
  • the heat exchanger 50 is composed of a plurality of heat exchangers (for example, when the heat exchanger 50 is composed of the front side heat exchanger 51 and the back side heat exchanger 55), the location where the arrangement gradient of the heat exchanger 50 changes ( For example, the heat exchangers do not have to be in complete contact with each other at a substantial connection point between the front-side heat exchanger 51 and the back-side heat exchanger 55, and there may be some gaps.
  • the shape of the heat exchanger 50 in the right vertical section may be partially or entirely curved (see FIG. 37).
  • Embodiment 19 the fan 20 may be arranged as follows.
  • differences from the eleventh to eighteenth embodiments will be mainly described, and the same parts as those in the eleventh to eighteenth embodiments are denoted by the same reference numerals. is doing.
  • FIG. 36 is a longitudinal sectional view showing an indoor unit according to Embodiment 19 of the present invention.
  • the heat exchanger 50 of the indoor unit 100 according to Embodiment 19 has the same arrangement as the indoor unit 100 of Embodiment 14.
  • the indoor unit 100 according to the eighteenth embodiment is different from the indoor unit 100 according to the fourteenth embodiment in the manner in which the fan 20 is arranged. That is, in the indoor unit 100 according to the nineteenth embodiment, the inclination of the fan 20 is determined according to the air volume and heat transfer area of the front side heat exchanger 51 and the back side heat exchanger 55.
  • the air volume of the back side heat exchanger 55 having a larger heat transfer area than the front side heat exchanger 51 may be insufficient.
  • the fan 20 may not be adjusted by moving the fan 20 in the front-rear direction.
  • the heat exchanger 50 (the front side heat exchanger 51 and the back side heat exchanger 55) may not be able to exhibit desired heat exchange performance.
  • the fan 20 may be inclined toward the back side heat exchanger 55 in the right vertical section.
  • the air volume of the back side heat exchanger 55 may be insufficient.
  • the fan 20 may not be adjusted by moving the fan 20 in the front-rear direction.
  • the air merged after passing through each of the front surface side heat exchanger 51 and the back surface side heat exchanger 55 may not bend more than a desired angle.
  • the fan 20 may be inclined toward the back side heat exchanger 55 in the right vertical section.
  • the heat exchanger 50 shown in FIG. 36 is comprised by the substantially (LAMBDA) type
  • the shape of the heat exchanger 50 in the right vertical section may be configured to be approximately V-shaped, approximately N-shaped, approximately W-shaped, approximately ⁇ -shaped, approximately M-shaped, or the like.
  • the front side heat exchanger 51 and the back side heat exchanger 55 may be configured as an integrated heat exchanger (see FIG. 37).
  • each of the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured by a combination of a plurality of heat exchangers (see FIG. 37).
  • the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a.
  • the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a.
  • the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction.
  • the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.
  • the heat exchanger 50 is composed of a plurality of heat exchangers (for example, when the heat exchanger 50 is composed of the front side heat exchanger 51 and the back side heat exchanger 55), the location where the arrangement gradient of the heat exchanger 50 changes ( For example, the heat exchangers do not have to be in complete contact with each other at a substantial connection point between the front-side heat exchanger 51 and the back-side heat exchanger 55, and there may be some gaps.
  • the shape of the heat exchanger 50 in the right vertical section may be partially or entirely curved (see FIG. 37).
  • Embodiment 20 FIG. ⁇ Nozzle>
  • the nozzle 6 is configured such that the opening length d1 on the inlet side of the nozzle 6 is larger than the opening length d2 on the outlet side of the nozzle 6 in the right vertical section.
  • the deviation of the wind speed distribution that occurred in the vicinity of the inlet of the nozzle 6 was corrected.
  • the shape of the nozzle 6 in the right vertical section is different from that in the first embodiment.
  • the difference between the shape of the nozzle 6 according to the twentieth embodiment and the shape of the nozzle 6 according to the first embodiment will be described in detail.
  • FIG. 38 is an explanatory diagram (longitudinal sectional view) for explaining the airflow in the nozzle of the indoor unit according to Embodiment 1 of the present invention.
  • both the front side curve 6b and the back side curve 6a are convex on the back side.
  • FIG. 38 there is a case where reduction of the effective air passage due to separation, loss, and generation of the wind speed distribution at the outlet 3 become a problem due to the wraparound of the air flow from the back side drain pan 115. is there.
  • the flow rate passing through the back side heat exchanger 55 is larger than the flow rate passing through the front side heat exchanger 51.
  • the airflow that has passed through the bottom of the back side drain pan 115 located at the lower end of the back side heat exchanger 55 passes over the back side drain pan 115 and flows out to the nozzle 6, it cannot be bent due to a large flow velocity. It peels at the upper part of the curve 6a (the entrance side of the nozzle 6).
  • the larger the flow rate passing through the back side heat exchanger 55 and the larger the wind speed distribution at the lower end of the back side heat exchanger 55 the larger the separation area.
  • FIG. 39 is a longitudinal sectional view showing an indoor unit according to Embodiment 20 of the present invention.
  • the back surface side curve 6a configuring the nozzle 6 is configured by a curve that is convex to the front surface side.
  • the back side curve 6a may have a shape that is convex to the front as shown in FIG. 39, or a part of the back side curve 6a that is convex to the front as shown in FIG. Also good.
  • the above-described peeling region often occurs on the inlet side (upper part) of the nozzle 6, so when a part of the back side curve 6 a is convex on the front side, the upstream side from the center of the curve. It is desirable to form a convex shape.
  • the back side curve 6a may have a shape in which the upstream side is convex toward the front side and the downstream side is convex toward the back side. That is, the shape of the back-side curve 6a in the right vertical section may be a substantially S-shape as a whole.
  • the flow that flows over the back side drain pan 115 and flows into the nozzle 6 is guided to the outlet 3 without being separated. Furthermore, since there is no separation or reverse flow, the wind speed distribution at the outlet 3 is also improved. For this reason, since dew countermeasures due to backflow or the like and airflow direction control are facilitated, the quality of the indoor unit 100 as a whole can be improved.
  • Embodiment 21 By changing the shape of the nozzle 6 in the front-rear direction in the longitudinal direction (left-right direction) of the casing 1, it is possible to correct the deviation of the wind speed distribution of the outlet 3.
  • items that are not particularly described are the same as those in the twentieth embodiment, and the same functions and configurations are described using the same reference numerals.
  • the shape of the nozzle 6 is uniform in the longitudinal direction (left-right direction) of the casing 1.
  • the following problem may occur.
  • FIG. 41 is an explanatory diagram for explaining an air flow generated inside the indoor unit according to Embodiment 1 of the present invention.
  • 41A shows a plan sectional view of the indoor unit 100 according to Embodiment 1, and the lower side of FIG. 41A is the front side of the indoor unit 100.
  • FIG. FIG. 41B shows a YY sectional view of FIG. 41A, and
  • FIG. 41C shows an XX sectional view of FIG. 41A.
  • FIG. 41 shows a case where each fan 20 rotates counterclockwise when the indoor unit 100 is viewed in plan.
  • the wind speed in the G region in the heat exchanger 50 arranged on the downstream side increases due to the influence of the swirling flow generated by the fan 20 provided in the upper portion of the casing 1. (In other words, the air volume increases.)
  • This bias in the wind speed distribution generated in the heat exchanger 50 also exists on the downstream side. For this reason, the airflow that has passed through the heat exchanger flows into the nozzle 6 with such a wind speed distribution.
  • the air volume passing through the rear side heat exchanger 55 is the front side heat exchanger 51. Therefore, the wind speed distribution in the right vertical section is as shown in FIGS. 41 (b) and 41 (c). More specifically, in the cross-section YY, the flow rate from the back side heat exchanger 55 is large, so that the main flow in the nozzle 6 is slightly biased toward the approximate center of the nozzle 6 or the front side of the casing 1. It becomes. Further, in the section XX, the flow rate from the front side heat exchanger 51 is large, so the main flow in the nozzle 6 is slightly biased toward the back side of the casing 1.
  • the heat exchanger 50 such as the indoor unit 100 according to Embodiment 1 (right vertical section substantially ⁇ type)
  • each fan 20 rotates counterclockwise in a plan view.
  • a region where the wind speed is large or small The region is reversed in the left-right direction.
  • region changes when arrangement
  • FIG. 43 is an explanatory diagram showing an example of the nozzle shape of the indoor unit according to Embodiment 21 of the present invention.
  • 43 (a) is a longitudinal sectional view showing the vicinity of the nozzle 6 of the indoor unit 100 according to Embodiment 21, and
  • FIG. 43 (b) is a WW sectional view of FIG. 43 (a).
  • the lower side of FIG. 43B is the front side of the casing 1.
  • the nozzle 6 according to the twenty-first embodiment changes the width in the front-rear direction in accordance with the mainstream flow in the nozzle 6.
  • the width in the front-rear direction of the nozzle 6 is L1 before changing the width in the front-rear direction.
  • the front-rear width of the nozzle 6 is reduced to the front side, and the front-rear direction of the nozzle 6 is reduced.
  • the width is L2.
  • the width of the nozzle 6 in the front-rear direction is reduced to the back side, The width is L2.
  • the width of the nozzle 6 in the front-rear direction need not be changed stepwise along the left-right direction of the casing 1.
  • the width in the front-rear direction of the nozzle 6 may be changed smoothly along the left-right direction of the casing 1.
  • FIG. 44 is an explanatory diagram showing another example of the nozzle shape of the indoor unit according to Embodiment 21 of the present invention. As shown in FIG. 44, the position of the nozzle 6 in the front-rear direction gradually (smoothly) approaches the front side from the left side to the right side of the casing 1. FIG. 44 assumes a case where the main flow in the nozzle 6 approaches the front side of the casing 1 from the left side to the right side of the casing 1.
  • FIG. 45 is an explanatory diagram showing still another example of the nozzle shape of the indoor unit according to Embodiment 21 of the present invention. As shown in FIG. 45, the width of the nozzle 6 in the front-rear direction is gradually (smoothly) narrowed from L5 to L6 from the left side to the right side of the casing 1. Note that FIG. 45 assumes a case where the amount of air flowing through the nozzle 6 decreases from the left side to the right side of the casing 1.
  • the shape of the inlet side of the nozzle 6 has been described.
  • the shape of the outlet side of the nozzle 6 may be changed as described above.
  • Embodiment 22 When correcting the deviation of the wind speed distribution at the air outlet 3, a fan may be added as follows.
  • items not particularly described are the same as those in the twentieth or twenty-first embodiment, and the same functions and configurations are described using the same reference numerals.
  • FIG. 46 is a plan sectional view showing an indoor unit according to Embodiment 22 of the present invention.
  • the basic configuration of indoor unit 100 according to Embodiment 22 is the same as that of indoor unit 100 according to Embodiment 1. That is, in the indoor unit 100 according to the twenty-second embodiment, a heat exchanger having a right vertical section substantially ⁇ type is provided on the downstream side of the plurality of fans 20.
  • the difference between the indoor unit 100 according to Embodiment 22 and the indoor unit 100 according to Embodiment 1 is that a fan 20b is provided. The fan 20b is small enough not to affect the swirling flow of the adjacent fan 20.
  • the fan 20b may have a shape similar to that of the fan 20 or a different shape. However, it is preferable that the blades are designed so as to reduce the swirling flow of the fan 20 as much as possible.
  • the rotation direction of the fan 20b may be the same direction as the fan 20 or may be the opposite direction to the fan 20. In FIG. 46, the rotation direction of the fan 20b is the same as the rotation direction of the fan 20.
  • the fan 20b is disposed at the rear right side of the upper surface portion of the casing 1 in order to increase the air volume in a region where the air volume is reduced.
  • the indoor unit 100 configured as described above, it is possible to partially increase the air volume in a region where the wind speed is low. That is, it becomes possible to make the wind speed in the whole blower outlet 3 the state near uniform. For this reason, it is possible to improve the wind speed distribution in the vicinity of the air outlet 3, and it becomes easy to take measures against backflow or the like and to control the direction of the airflow, so that the quality of the entire indoor unit 100 can be improved.
  • the fans 20b may be provided at the right rear and the right front of the upper surface of the casing 1. You may provide in the vicinity of the full-angle part of the casing 1 upper surface part.
  • FIG. 47 is a plan sectional view showing another example of the indoor unit according to Embodiment 22 of the present invention.
  • the indoor unit 100 shown in FIG. 47 further includes a fan 20b in front of the right side of the upper surface of the casing 1 with respect to the indoor unit 100 shown in FIG.
  • the fan 20b may be installed near the left corner of the upper surface of the casing 1. That is, a plurality of fans 20b may be arranged on both the left and right side surfaces of the casing 1.

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  • Engineering & Computer Science (AREA)
  • 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)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

L'invention porte sur : une unité intérieure (100) configurée de sorte qu'une détérioration dans les performances d'échange de chaleur soit supprimée ; et un climatiseur comportant l'unité intérieure (100). L'unité intérieure (100) comporte : une enceinte (1) ayant une ouverture d'aspiration (2) qui est formée dans la partie supérieure de celle-ci, et ayant également une ouverture de décharge (3) qui est formée sur le côté inférieur de la surface avant de celle-ci ; un ventilateur à écoulement axial ou à écoulement mixte (20) disposé à l'intérieur de l'enceinte (1) en une position en aval de l'ouverture d'aspiration (2) ; un échangeur de chaleur (50) disposé à l'intérieur de l'enceinte (1) en une position en aval du ventilateur (20) et en amont de l'ouverture de décharge (3) et échangeant de la chaleur entre un réfrigérant et de l'air qui est soufflé à partir du ventilateur (20) ; un protège-doigts (15) disposé au niveau de l'ouverture d'aspiration (2) dans l'enceinte (1) ; et un filtre (20) disposé en amont du protège-doigts (15).
PCT/JP2010/004916 2010-08-04 2010-08-04 Unité intérieure pour climatiseur, et climatiseur WO2012017483A1 (fr)

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PCT/JP2010/004916 WO2012017483A1 (fr) 2010-08-04 2010-08-04 Unité intérieure pour climatiseur, et climatiseur
JP2012527461A JP5591335B2 (ja) 2010-08-04 2010-08-04 空気調和機の室内機、及び空気調和機

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EP3450861A4 (fr) * 2016-04-27 2019-05-08 Daikin Industries, Ltd. Unité extérieure pour dispositif de congélation
JPWO2019123743A1 (ja) * 2017-12-20 2020-12-10 パナソニックＩｐマネジメント株式会社 空気調和機の室内機
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