US20210131699A1 - Indoor unit and air conditioner - Google Patents

Indoor unit and air conditioner Download PDF

Info

Publication number
US20210131699A1
US20210131699A1 US16/488,611 US201716488611A US2021131699A1 US 20210131699 A1 US20210131699 A1 US 20210131699A1 US 201716488611 A US201716488611 A US 201716488611A US 2021131699 A1 US2021131699 A1 US 2021131699A1
Authority
US
United States
Prior art keywords
airflow
direction changing
airflow direction
downstream
changing plate
Prior art date
Legal status (The legal status 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 status listed.)
Abandoned
Application number
US16/488,611
Other languages
English (en)
Inventor
Tadakiyo SEKI
Takashi Kobayashi
Hajime Ikeda
Seiji Hirakawa
Masayuki Oishi
Akinori Sakabe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KOBAYASHI, TAKASHI, HIRAKAWA, SEIJI, OISHI, MASAYUKI, SAKABE, Akinori, IKEDA, HAJIME, SEKI, Tadakiyo
Publication of US20210131699A1 publication Critical patent/US20210131699A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0011—Indoor units, e.g. fan coil units characterised by air outlets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/08—Air-flow control members, e.g. louvres, grilles, flaps or guide plates
    • F24F13/10—Air-flow control members, e.g. louvres, grilles, flaps or guide plates movable, e.g. dampers
    • F24F13/14—Air-flow control members, e.g. louvres, grilles, flaps or guide plates movable, e.g. dampers built up of tilting members, e.g. louvre
    • F24F13/15—Air-flow control members, e.g. louvres, grilles, flaps or guide plates movable, e.g. dampers built up of tilting members, e.g. louvre with parallel simultaneously tiltable lamellae
    • 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
    • F24F13/22—Means for preventing condensation or evacuating condensate
    • F24F13/222—Means for preventing condensation or evacuating condensate for evacuating condensate

Definitions

  • the present disclosure relates to an indoor unit and an air conditioner.
  • An air conditioner is equipped with airflow direction changing plates for changing direction of blown air flowing out from an indoor unit.
  • a lateral airflow direction changing plate is proposed that has multiple slits formed thinly in a direction of airflow in an intermediate region and excluding an upstream end region and an airflow downstream end region of airflow.
  • Patent Literature 1 Unexamined Japanese Patent Application Kokai Publication No. 2008-80839
  • the lateral airflow direction changing plate is sometimes disposed in the downstream vicinity of a fin-and-tube type heat exchanger. In this case, the air reaches the lateral airflow direction changing plate in a state in which both a temperature distribution and an absolute humidity distribution of the air remain non-uniform, and such operation suffers from the occurrence of condensation on the lateral airflow direction changing plate.
  • an object of the present disclosure is to provide an indoor unit and an air conditioner that are equipped with an airflow direction changing plate on which condensation tends not to occur.
  • an indoor unit includes:
  • a heat exchanger disposed downstream from the air blower and including a plurality of fins and a heat transfer tube passing through the fins;
  • an airflow direction changing plate to change an airflow direction
  • the airflow direction changing plate being disposed downstream from the heat exchanger and having an opening portion in an airflow downstream region that is downstream from the heat transfer tube.
  • the airflow direction changing plate has an opening portion in the airflow downstream region from the heat transfer tube. Therefore, condensation on the airflow direction changing plate tends not to occur.
  • FIG. 1 is a cross-sectional drawing as viewed from a side face of an indoor unit according to Embodiment 1 of the present disclosure
  • FIG. 2A is a perspective view of a lateral airflow direction changing plate according to Embodiment 1;
  • FIG. 2B is a drawing illustrating arrangement of a heat exchanger and the lateral airflow direction changing plate as viewed at a frontally forward tilt;
  • FIG. 3A is a side view of the lateral airflow direction changing plate according to Embodiment 1;
  • FIG. 3B is a drawing for description of change of an opening fraction of slits per unit surface area
  • FIG. 4 is a contour diagram (contour drawing) of a numerical analysis illustrating a temperature distribution of air flowing in a periphery of the lateral airflow direction changing plate during cooling;
  • FIG. 5 is a contour diagram of a numerical analysis illustrating a condensation speed distribution of a lateral airflow direction changing plate surface in the case of the air temperature distribution conditions illustrated in FIG. 4 ;
  • FIG. 6 is a side view of a lateral airflow direction changing plate according to Embodiment 2 of the present disclosure.
  • FIG. 7 is a side view of a lateral airflow direction changing plate according to Embodiment 3 of the present disclosure.
  • FIG. 8 is a side view of a lateral airflow direction changing plate according to Embodiment 4 of the present disclosure.
  • FIG. 9 is a side view of a lateral airflow direction changing plate according to Embodiment 5 of the present disclosure.
  • FIG. 10A is a drawing illustrating an example of a cross-sectional shape of an opening portion of the lateral airflow direction changing plate surface
  • FIG. 10B is a drawing illustrating another example of a cross-sectional shape of an opening portion of the lateral airflow direction changing plate surface
  • FIG. 10C is a drawing illustrating yet another example of a cross-sectional shape of an opening portion of the lateral airflow direction changing plate surface
  • FIG. 10D is a drawing illustrating yet even another example of a cross-sectional shape of an opening portion of the lateral airflow direction changing plate surface.
  • FIG. 11 is a drawing of an air conditioner according to Embodiment 1.
  • the indoor unit 100 according to Embodiment 1, as illustrated in FIG. 11 is connected to an outdoor unit 102 via refrigerant tubes 101 , and these components together make up an air conditioner 110 .
  • FIG. 1 is a cross-sectional drawing as viewed from the side face of the indoor unit 100 , the left direction of the drawing is the indoor direction in which air is sent and is also termed “front (frontward)”, and the right direction of the drawing is the direction to the wall for attachment of the indoor unit 100 and is also termed “rear (rearward)”.
  • the upward direction in the drawing is also termed “up (above)”, and the downward direction is also termed “down (below)”.
  • a pushing-in type propeller fan 4 for sucking in indoor air from the inlet opening 2 and sending out the air to a heat exchanger side
  • a heat exchanger 50 positioned in an airflow downstream direction that is downstream from the propeller fan 4 and positioned in an airflow upstream direction that is upstream from the outlet opening 3
  • a drain pan 6 disposed below the heat exchanger 50 , for receiving and discharging water that is generated due to condensation by the heat exchanger 50 .
  • airflow is taken to mean the flow of air produced by the propeller fan 4 .
  • the propeller fan 4 is one example of an air blower.
  • the heat exchanger 50 heats or cools the air blown by the propeller fan 4 .
  • the heat exchanger 50 includes a forward-tilted portion 50 a that is tilted forward, a rearward-tilted portion 50 b that is tilted rearward and positioned opposingly behind the forward-tilted portion 50 a, a forward-tilted portion 50 c that is tilted forward and positioned opposingly behind the rearward-tilted portion 50 b, and a rearward-tilted portion 50 d that is tilted rearward and positioned opposingly behind the forward-tilted portion 50 c; and these components are arranged in a W-shaped configuration.
  • the forward-tilted portion 50 a, the rearward-tilted portion 50 b, the forward-tilted portion 50 c, and the rearward-tilted portion 50 d each include flat plate-like fins 51 arranged in a row and heat transfer tubes 52 passing through the fins 51 to form a fin-and-tube type heat exchanger unit.
  • the fins 51 are arranged parallel to a direction of flow of air so as not to impede the flow of air
  • the heat transfer tubes 52 are arranged extending in a direction orthogonal to the direction of flow of air.
  • a frontward positioned front-side vertical airflow direction changing plate 7 and a rearward positioned rear-side vertical airflow direction changing plate 8 are arranged, and each of these plates can change vertically the airflow direction of the air.
  • the bottom-side lateral airflow direction changing plate 9 is arranged below the front-side vertical airflow direction changing plate 7 .
  • the bottom-side lateral airflow direction changing plate 9 can change the lateral airflow direction of the air subjected to heat exchange by the rearward-tilted portion 50 b, the forward-tilted portion 50 c, and the rearward-tilted portion 50 d.
  • multiple top-side lateral airflow direction changing plates 20 are arranged downstream from the forward-tilted portion 50 a .
  • the top-side lateral airflow direction changing plates 20 can laterally change the airflow direction of the air subject to heat exchange by the forward-tilted portion 50 a.
  • cylindrically shaped attaching parts 15 of the top-side lateral airflow direction changing plates 20 are supported by supporting parts 16 .
  • the supporting parts 16 are fixed to a fixing part 10 fixed to the drain pan 6 .
  • the drain pan 6 is attached to the housing 1 of the indoor unit 100 .
  • the top-side lateral airflow direction changing plates 20 are rotatably supported with respect to the supporting parts 16 so as to be capable of clockwise or counter-clockwise rotation around, as central axes, cylinder axes of the attaching parts 15 .
  • Each of the top-side lateral airflow direction changing plates 20 is connected to a single connector 12 via a respective fixing implement 14 , so that all of the top-side lateral airflow direction changing plates 20 are interlocked with the connector 12 to enable simultaneous change of direction.
  • all of the top-side lateral airflow direction changing plates 20 rotate in the counter-clockwise direction around, as the central axis of rotation, the cylinder axis of the respective attaching part 15 . In doing so, the flow of air subjected to heat exchange by the forward-tilted portion 50 a changes become directed rightward.
  • all of the top-side lateral airflow direction changing plates 20 rotate in the clockwise direction around, as the central axis of rotation, the cylinder axis of the respective attaching part 15 . In doing so, the flow of air changes to become directed leftward.
  • the lateral flow direction of air can be adjusted in this manner.
  • the top-side lateral airflow direction changing plates 20 are oriented in the same direction as that of the fins 51 , and are disposed at downstream locations of the air passing through gaps between the fins 51 .
  • the spacing between the fins 51 is narrow, such as about 1 mm. Therefore, all air passing between the fins 51 undergoes an effect of cooling by the fins 51 , and thus temperature imbalances are small. That is to say, temperature differences are small between an airflow 46 passing through the vicinity of the top-side lateral airflow direction changing plate 20 and an airflow 44 passing outside the vicinity of the top-side lateral airflow direction changing plate 20 .
  • a side-direction arrangement position of the top-side lateral airflow direction changing plate 20 in FIG. 2B may be freely selected as long as the arrangement position is downstream from the air passing within an overall region formed by the fins 51 .
  • control system technology is the same as that of a conventional control system.
  • technology of the outdoor unit 102 that is used for heat exchange is the same as that of a conventional outdoor unit.
  • each of the top-side lateral airflow direction changing plates 20 has, in a region of relatively low air temperature in comparison to the surroundings in the airflow downstream from the heat transfer tube 52 , two openings 21 a and 21 b having gradually decreasing widths from the air flow upstream to the downstream.
  • the openings 21 a and 21 b are referred to as the slits 21 a and 21 b.
  • the upper-right direction in FIG. 3A is the airflow upstream direction
  • the lower-left direction is the airflow downstream direction.
  • airflow downstream from the heat transfer tube 52 means the region at the downstream side through which air flows at the periphery of the heat transfer tube 52 . Due to the presence of multiple heat transfer tubes 52 , multiple airflow downstreams exist.
  • the term “slit” means an opening having a long-narrow shape.
  • the term “opening portion” means a hole, notch, or the like passing from one surface to the other surface of the top-side lateral airflow direction changing plate 20 .
  • opening having gradually decreasing width means that a fraction of an opening surface area of the openings 21 a and 21 b per a certain unit surface area of the top-side lateral airflow direction changing plate 20 gradually decreases.
  • four virtual rectangles 28 a, 28 b, 28 c , and 28 d are considered as indicated by short-dashed lines overlapping the opening of the slit 21 b. These are rectangles of the same surface area disposed adjacent to each other, in order, from the air flow upstream side to the downstream side of the slit 21 b. Firstly, the virtual rectangle 28 a is disposed such that the fraction of the opening of the slit 21 b included in the virtual rectangle 28 a is largest. Next, adjacent to the virtual rectangle 28 a, the virtual rectangle 28 b is disposed such that the fraction of the opening of the slit 21 b included in the virtual rectangle 28 b is largest.
  • the virtual rectangle 28 c and the virtual rectangle 28 d are disposed in order. Due to arrangement in this manner, the surface area fraction of the opening of the slit 21 b occupied in the surface area of the virtual rectangle 28 a is largest, the opening fraction of the slit 21 b occupied in the surface area of the virtual rectangle 28 b is next largest, the opening fraction of the slit 21 b occupied in the surface area of the virtual rectangle 28 c is next largest, and the smallest opening fraction is the opening fraction of the slit 21 b occupied by the virtual rectangle 28 d most at the downstream side. These relationships are similar for slit 21 a.
  • intermediate temperature regions 41 filled with hatching are regions through which air flows of a temperature that is between temperatures of a low temperature region 43 through which air flows that is cooled by the heat transfer tube 52 and a high temperature region 42 through which air flows that is near room temperature.
  • the long-dashed line indicates an isothermal line of the boundary between the low temperature region 43 and the intermediate temperature region 41 .
  • the short-dashed line indicates an isothermal line of the boundary between the high temperature region 42 and the intermediate temperature region 41 .
  • the long-dashed line is thus an isothermal line of lower temperature in comparison to the short-dashed line. Curvature of the flow of air in this manner is used because the drain pan 6 is disposed below the heat transfer tubes 52 and the flow of air there is blocked.
  • the air temperature of the intermediate temperature region 41 that is downstream in the airflow from the heat transfer tubes 52 is relatively low in comparison to the air temperature of the high temperature region 42 of air that flows by passing through the middle between the heat transfer tubes 52 .
  • the air of this intermediate temperature region 41 touches the surfaces of the lateral airflow direction changing plate 40 , and thus this air is cooled by the surfaces of the lateral airflow direction changing plate 40 .
  • heat conduction occurs and the low temperature portion reaches the region of the lateral airflow direction changing plate 40 through which the air of the high temperature region 42 passes, and the surface temperature of this region declines. Condensation occurs when the surface temperature of the region through which the air of the high temperature region 42 passes is less than or equal to a dew point temperature of air of the high temperature region 42 .
  • the hatched portion is a region in which condensation speed is greater than or equal to zero, that is to say, is a condensation region 47 in which condensation occurs.
  • condensation does not occur on the surface of the lateral airflow direction changing plate 40 in a vicinity of passage of a flowline 45 having, as an originating point, an airflow back portion the heat transfer tube 52 , but rather condensation occurs in a region at a periphery of such vicinity.
  • condensation on the lateral airflow direction changing plate 40 is caused by: the air that is cooled by the heat transfer tube 52 and is at relatively low temperature in comparison to the periphery contacting the lateral airflow direction changing plate 40 and being partially cooled by the lateral airflow direction changing plate 40 , and the region cooled by heat conduction within the lateral airflow direction changing plate 40 spreading so that there is a portion where the air contacting the surface is less than or equal to the dew point.
  • the slits 21 a and 21 b are arranged in the region through which flows air of relatively low temperature of the top-side lateral airflow direction changing plate 20 located in the airflow downstream from the heat transfer tube 52 . Due to such configuration, the surface area where the relatively low-temperature air contacts the top-side lateral airflow direction changing plate 20 can be decreased. Furthermore, the region of transmission of heat becomes smaller, and a heat conduction suppression effect can be anticipated.
  • the air cooled by the heat exchanger 50 gradually mixes with relatively warm air of the periphery from the airflow upstream to the downstream position, and the air temperature distribution is equalized so that the condensation region narrows with distance downstream. Width of the slits gradually decrease with distance from the airflow upstream to the downstream as in the slits 21 a and 21 b, and thus the lowering in airflow direction change performance can be suppressed while achieving the condensation prevention effect.
  • the risk of the occurrence of condensation on the top-side lateral airflow direction changing plate 20 can be decreased, and even if condensation occurs, a decrease in the condensation amount can be achieved.
  • the top-side lateral airflow direction changing plate 20 has the slits 21 a and 21 b in which slit width gradually decreases from the air flow upstream to the downstream, of the rear portion of the heat transfer tube 52 , in the region contacted by air of relatively low temperature in comparison to the periphery. Due to such configuration, an indoor unit 100 can be provided for which condensation tends not to occur even when the top-side lateral airflow direction changing plate 20 is positioned in the downstream vicinity of the fin-and-tube type heat exchanger 50 .
  • the shapes of the slits 21 a and 21 b are determined so as to match the distribution of air temperature as described above, in the case in which the shape of the distribution of air temperature differs in accordance with the position of the top-side lateral airflow direction changing plate 20 , the shapes of the slits 21 a and 21 b may differ among the top-side lateral airflow direction changing plates 20 . Moreover, although there are two slits 21 a and 21 b in Embodiment 1, the number of the slits may be freely determined to match the distribution state of the air temperature.
  • the bottom-side lateral airflow direction changing plate 9 in Embodiment 1 is disposed at the downstream side of the heat transfer tube 52 of the rearward-tilted portion 50 b, the forward-tilted portion 50 c, and the rearward-tilted portion 50 d, the distance from the heat transfer tube 52 is great, and relatively low temperature air and warm air may intermix, and thus condensation tends not to be locally generated.
  • the slits are thus not arranged in the bottom-side lateral airflow direction changing plate 9 , in the case in which a distribution of air temperature arises due to the arrangement relationship between the heat transfer tubes 52 and the bottom-side lateral airflow direction changing plate 9 such that condensation easily occurs, slits can be arranged also in the bottom-side lateral airflow direction changing plate 9 .
  • Embodiment 2 is an example of arrangement of, rather than the slits 21 a and 21 b of Embodiment 1, notches 22 a and 22 b having a shape in which the upstream end of the slit opens.
  • the notches 22 a and 22 b are examples of openings similar to the slits 21 a and 21 b.
  • FIG. 6 is a view of a top-side lateral airflow direction changing plate 20 a according to Embodiment 2 as viewed from the side.
  • the top-side lateral airflow direction changing plate 20 a has two notches 22 a and 22 b that decreases gradually in notch width from the airflow upstream to the downstream in a region, in airflow downstream from the heat transfer tube 52 , contacted by air of relatively low temperature in comparison to the periphery.
  • the term “notch” means an opening portion that opens up to an edge surface of the top-side lateral airflow direction changing plate 20 a.
  • the slits 21 a and 21 b in the top-side lateral airflow direction changing plate 20 of Embodiment 1 are through holes that do not open to the end surface, the notches 22 a and 22 b open up to the airflow upstream-side end surface of the top-side lateral airflow direction changing plate 20 a .
  • the gradual decrease in the width of the notches means that the fraction of opening surface area of the notches 22 a and 22 b per virtual unit surface area gradually decreases toward the downstream side.
  • the number of the notches is freely selected, meaning that the number is not limited to two, and may be one or three or more.
  • width of the notches 22 a and 22 b gradually decreases from the air flow upstream side to the downstream side, and thus while decreasing the risk of condensation, this has the effect of suppressing the lowering of airflow direction change performance.
  • the upstream end of the top-side lateral airflow direction changing plate 20 a is the location at which condensation tends to occur due to the air temperature distribution being the most equalized, notching of the upstream end has the effect of decreasing the risk of condensation.
  • Embodiment 3 is an example of an arrangement of, rather than the slits 21 a and 21 b of Embodiment 1, multiple through holes 23 having different diameters in the airflow downstream regions of the heat transfer tubes 52 .
  • the through holes 23 are examples of openings.
  • FIG. 7 is a view as seen from the side face of a top-side lateral airflow direction changing plate 20 b according to Embodiment 3.
  • the top-side lateral airflow direction changing plate 20 b has multiple circular through holes 23 of gradually decreasing diameters from the airflow upstream to the downstream in the regions, of the airflow downstream from the heat transfer tubes 52 , where air flows of relatively low temperature in comparison to the periphery.
  • the gradual decrease in diameter of the circular through holes 23 means that the opening fraction of the through holes 23 per virtual unit surface area gradually decreases toward the downstream side.
  • the circular through holes 23 are disposed in two rows, the number of rows of the arranged through holes in this case is also freely selected, meaning the number is not limited to two rows, and may be one row, or three or more rows.
  • cooling of the top-side lateral airflow direction changing plate 20 b decreases during the cooling operation, and heat conduction within the top-side lateral airflow direction changing plate 20 b can be suppressed.
  • the risk of condensation can be decreased in comparison to the conventional technology, and even if condensation occurs, the amount of condensation can be decreased.
  • the opening fraction of the through holes 23 gradually decreases, in a manner similar to that of Embodiment 1, from the airflow upstream to the downstream, and thus while decreasing the risk of condensation, this has the effect of suppressing the lowering of the airflow direction change performance.
  • Embodiment 4 is an example of arrangement of, in place of the slits 21 a and 21 b of Embodiment 1, multiple circular through holes 24 , each of the same diameter, in the airflow downstream region from the heat transfer tubes 52 .
  • FIG. 8 is a view from the side face of the top-side lateral airflow direction changing plate 20 c according to Embodiment 4.
  • the top-side lateral airflow direction changing plate 20 c has multiple circular through holes 24 for which a distribution count gradually decreases from the airflow upstream to the downstream in the regions, in the airflow downstream from the heat transfer tubes 52 , where air flows of relatively low temperature in comparison to the periphery.
  • the diameters of the multiply arranged through holes 24 are the same, the number (distribution fraction) decreases with distance in the downstream direction. That is to say, the opening fraction of the through holes 24 per virtual unit surface area gradually decreases toward the downstream side.
  • the circular through holes 24 are arranged in two rows, the number of rows is not limited to two rows, and the arrangement may be in one row or three or more rows.
  • the cooling of the top-side lateral airflow direction changing plate 20 c during the cooling operation may decrease, and heat conduction within the top-side lateral airflow direction changing plate 20 c can be suppressed.
  • the risk of condensation can thus be decreased in comparison to the conventional technology, and even if condensation occurs, a decrease in the condensation amount can be achieved.
  • the distribution fraction of the number of the through holes 24 gradually decreases from the airflow stream to the downstream, and thus in a manner similar to that of Embodiment 1, while decreasing the risk of condensation, this has the effect of suppressing the lowering of the airflow direction change performance.
  • Embodiment 5 is an example in which through holes 25 are disposed over an entire surface rather than as the slits 21 a and 21 b of Embodiment 1.
  • FIG. 9 is a view from the side of a top-side lateral airflow direction changing plate 20 d according to Embodiment 5.
  • the top-side lateral airflow direction changing plate 20 d has square-shaped through holes 25 evenly over the entire region thereof, forming a mesh pattern.
  • the shape of the through holes 25 is not limited to a square, and the shape may be freely selected. Also, the number of such holes can be freely selected.
  • the arrangement density of the through holes 25 can be uniform overall as shown in FIG. 9 , the opening density of the through holes 25 preferably decreases gradually from the upstream side to the downstream side. Reason being, even when the airflow is irregular, since the air of the upstream side is cooled more than the air of the downstream side, it is more effective for prevention of condensation to increase the opening density at the upstream side.
  • the direction of change of the airflow is not limited to any particular direction.
  • the airflow direction changing plate of the present disclosure may change airflow in the lateral direction, or may change airflow in the forward-rearward direction.
  • the present disclosure is applicable as long as an airflow direction changing plate is disposed downstream from the fin-and-tube type heat exchanger.
  • the opening portion preferably has a shape that does not make the flow of air passing through the opening portion unsteady.
  • the opening portion may have a right-angled end surface in the surface of the top-side lateral airflow direction changing plate 20 as illustrated in FIG. 10A , from the standpoint of not making the passage of air unsteady, the opening portion preferably has an end surface that is bowed or sloped as illustrated in FIGS. 10B to 10D .
  • FIG. 10B is an example of an end surface shape that is smoothly bowed
  • FIG. 10C is an example of an end surface shape that is sloped
  • FIG. 10D is an example of an end surface shape in which faces are formed tilted from both surface sides.
  • the shape of the end surface may be different for the upstream side versus the downstream side.
  • the propeller fan is used as the air blower in Embodiments 1 to 5.
  • the type of the air blower is not limited to this type.
  • a crossflow fan may be used.
  • the propeller fan may be an axial flow propeller fan or a diagonal flow propeller fan.
  • a centrifugal fan may be used.
  • the present disclosure can be used with advantage for an indoor unit of an air conditioner.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
  • Air-Flow Control Members (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
  • Duct Arrangements (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US16/488,611 2017-04-11 2017-04-11 Indoor unit and air conditioner Abandoned US20210131699A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2017/014858 WO2018189814A1 (ja) 2017-04-11 2017-04-11 室内機および空気調和機

Publications (1)

Publication Number Publication Date
US20210131699A1 true US20210131699A1 (en) 2021-05-06

Family

ID=63793252

Family Applications (1)

Application Number Title Priority Date Filing Date
US16/488,611 Abandoned US20210131699A1 (en) 2017-04-11 2017-04-11 Indoor unit and air conditioner

Country Status (4)

Country Link
US (1) US20210131699A1 (ja)
JP (1) JP6727415B2 (ja)
CN (1) CN110462305A (ja)
WO (1) WO2018189814A1 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11859861B2 (en) * 2018-01-20 2024-01-02 Daikin Industries, Ltd. System and method for heating and cooling

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61213429A (ja) * 1985-03-19 1986-09-22 Matsushita Electric Ind Co Ltd 空気調和機の吸込装置
JPH0651741U (ja) * 1992-12-16 1994-07-15 株式会社竹中工務店 空調吹出口用結露防止金具
JPH0861767A (ja) * 1994-08-19 1996-03-08 Fujitsu General Ltd 空気調和機
JP4196445B2 (ja) * 1998-09-03 2008-12-17 ダイキン工業株式会社 空気調和機の風向調節用垂直羽根
JP2000320885A (ja) * 1999-05-10 2000-11-24 Mitsubishi Electric Corp 空気調和機
CN2718442Y (zh) * 2004-05-27 2005-08-17 海尔集团公司 插接式的空调器横向送风摆动叶片组
CN100513893C (zh) * 2004-11-29 2009-07-15 乐金电子(天津)电器有限公司 壁挂式空调器
JP2008080839A (ja) * 2006-09-26 2008-04-10 Calsonic Kansei Corp 空気調和装置の吹き出し口グリル
JP4544364B1 (ja) * 2009-04-17 2010-09-15 ダイキン工業株式会社 空気調和装置
JP2012021704A (ja) * 2010-07-14 2012-02-02 Sharp Corp 空気調和機
CN102374583B (zh) * 2010-08-17 2016-03-02 乐金电子(天津)电器有限公司 空调器室内机
JP5518013B2 (ja) * 2011-08-18 2014-06-11 三菱電機株式会社 空気調和機の室内機、及びこの室内機を備えた空気調和機
JP2013096684A (ja) * 2011-11-07 2013-05-20 Hitachi Appliances Inc 空気調和機の偏向板取付構造
JP5516666B2 (ja) * 2012-07-26 2014-06-11 ダイキン工業株式会社 空調室内機
CN202813591U (zh) * 2012-10-16 2013-03-20 海尔集团公司 空调器及其摆叶
CN203478553U (zh) * 2013-06-19 2014-03-12 海尔集团公司 空调器导风摆叶装配结构

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11859861B2 (en) * 2018-01-20 2024-01-02 Daikin Industries, Ltd. System and method for heating and cooling

Also Published As

Publication number Publication date
JP6727415B2 (ja) 2020-07-22
JPWO2018189814A1 (ja) 2019-11-07
WO2018189814A1 (ja) 2018-10-18
CN110462305A (zh) 2019-11-15

Similar Documents

Publication Publication Date Title
JP6433582B2 (ja) 熱源ユニット
JP6311427B2 (ja) 空気調和装置
JP2013019596A (ja) 熱交換器、室内機、および室外機
JP4544364B1 (ja) 空気調和装置
JP6237435B2 (ja) 空気調和装置
JPWO2020218059A1 (ja) 局所冷却器及び局所冷却方法
US20210131699A1 (en) Indoor unit and air conditioner
WO2017068725A1 (ja) 空気調和機の室内機
JP6370399B2 (ja) 空気調和装置の室内機
JP6253513B2 (ja) 空気調和機の室内ユニット
EP3382287B1 (en) Fan coil unit
WO2018092783A1 (ja) 空気調和装置の室内ユニット
JP2010230208A (ja) 空気調和機の室内ユニット
JP2009287880A (ja) 空調機用散水装置
JP2017172935A (ja) 空気調和機
JP5962645B2 (ja) 熱交換器
JP6422588B2 (ja) 床置形空気調和機の室内機
JP2010127533A (ja) 空気調和装置及び空気調和装置におけるファンユニットの設置方法
US20150300668A1 (en) Air conditioning apparatus
JP2016017695A (ja) フィンチューブ熱交換器
EP3770526B1 (en) Indoor unit for air conditioner
JP2010129779A (ja) 空気調和装置
JP2008215758A (ja) 熱交換器
JP3863034B2 (ja) 熱交換器
JP2008008542A (ja) 熱交換器および熱交換器を備えた空気調和装置の室内機

Legal Events

Date Code Title Description
AS Assignment

Owner name: MITSUBISHI ELECTRIC CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SEKI, TADAKIYO;KOBAYASHI, TAKASHI;IKEDA, HAJIME;AND OTHERS;SIGNING DATES FROM 20190702 TO 20190705;REEL/FRAME:050160/0522

STPP Information on status: patent application and granting procedure in general

Free format text: APPLICATION DISPATCHED FROM PREEXAM, NOT YET DOCKETED

STPP Information on status: patent application and granting procedure in general

Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION

STPP Information on status: patent application and granting procedure in general

Free format text: NON FINAL ACTION MAILED

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION