WO2013080395A1 - Appareil de conditionnement d'air - Google Patents

Appareil de conditionnement d'air Download PDF

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Publication number
WO2013080395A1
WO2013080395A1 PCT/JP2012/002177 JP2012002177W WO2013080395A1 WO 2013080395 A1 WO2013080395 A1 WO 2013080395A1 JP 2012002177 W JP2012002177 W JP 2012002177W WO 2013080395 A1 WO2013080395 A1 WO 2013080395A1
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WO
WIPO (PCT)
Prior art keywords
fan
distance
side end
stabilizer
air
Prior art date
Application number
PCT/JP2012/002177
Other languages
English (en)
Japanese (ja)
Inventor
敬英 田所
池田　尚史
慎悟 濱田
代田　光宏
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 CN201290001026.2U priority Critical patent/CN203926056U/zh
Publication of WO2013080395A1 publication Critical patent/WO2013080395A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/422—Discharge tongues
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings

Definitions

  • the present invention relates to an air conditioner, and more particularly to a separate type air conditioner indoor unit having an indoor unit and an outdoor unit.
  • the indoor unit of an air conditioner is installed indoors (in a house, office, etc.) that performs air conditioning, and heat exchanges the indoor air sucked from the suction port with the refrigerant circulating in the refrigeration cycle circuit using a heat exchanger.
  • a heat exchanger In the case of heating operation, the room air is warmed, and in the case of cooling operation, the room air is cooled and blown into the room again from the outlet.
  • the blower and heat exchanger are provided inside the indoor unit body. Is housed.
  • cross-flow fans cross-flow fans, cross-flow fans, cross-flow fans, etc.
  • blowers for wall-hanging types with long and narrow outlets and ceiling-mounted types with one-way blowing. It is well known that it is also used.
  • a heat exchanger is arranged upstream of the once-through fan for the air flow from the inlet to the outlet of the indoor unit of the air conditioner, that is, a heat exchanger is arranged between the inlet and the once-through fan.
  • An air outlet is located on the downstream side.
  • the length in the longitudinal direction of the blowout port of the indoor unit is substantially the same as the overall length in the longitudinal direction (rotation axis direction) of the cross-flow fan, and the cross-flow fan is provided with a predetermined space on the outside in the longitudinal direction at both ends of the cross-flow fan.
  • a support portion and a drive motor for supporting the rotating shaft are arranged.
  • a cross-flow fan (hereinafter abbreviated as “fan”) is formed by inclining a plurality of blades whose transverse section is curved in a substantially arc shape on a support plate that is an annular (ring-shaped) flat plate having an outer diameter and an inner diameter by a predetermined angle.
  • a plurality of impellers fixed concentrically and annularly are connected in the rotational axis direction.
  • each impeller In the direction of the rotation axis, a disk-shaped fan end plate to which a rotation shaft supported by the bearing unit of the indoor unit body is attached is fixed to the blade tip of the impeller alone at one end, and the other end Unlike the other support plates, each impeller has a fan end plate with a boss provided with a boss portion at the center to which a motor rotation shaft of a drive motor is attached and fixed.
  • the fan rotates around the rotation axis that is the center of the rotation axis.
  • the blade is inclined so that its outer peripheral tip is located forward in the rotational direction.
  • a single impeller connected in the direction of the rotation axis is called a series of fans.
  • each of the impellers positioned at both ends of the fan in the rotation axis direction is referred to as an end portion series.
  • the room air With the rotation of the fan, the room air is sucked into the indoor unit body of the air conditioner from the suction port, becomes conditioned air whose temperature is adjusted as described above when passing through the heat exchanger, crosses the fan, Blows out in the direction of rotation from the fan. After that, the conditioned air flows through a gradually expanding blowing air passage formed between a stabilizer provided on the front side of the cross-flow fan and a rear guide portion provided on the rear side, and the blowing air formed at the lower portion of the indoor unit main body. It is blown out from the exit into the room.
  • the plurality of blades constituting the cross-flow fan pass through the suction area on the upstream side and the blow-out area on the downstream side of the cross-flow fan. Due to the structure of such a cross-flow fan, it is known that a vortex is generated in the vicinity of a stabilizer that is disposed on the front side with respect to the blow-out direction of the air flow of the cross-flow fan and divides the suction region and the blow-out region.
  • the air flow may be disturbed by friction with the side wall of the indoor unit, and the air flow may not flow smoothly toward the outlet.
  • the static pressure Ps in the vicinity of the air outlet in the indoor unit becomes lower than the atmospheric pressure P0, and a phenomenon occurs in which room air is sucked into the indoor unit from the air outlet due to the pressure difference between the two. This phenomenon is called reverse suction.
  • Fan end plates constituting a single impeller as a rotating body are provided at both ends in the rotation axis direction of the fan, and the fan end plate is provided outside the fan end plate in the indoor unit body.
  • the side wall which comprises the side surface of an air path is arrange
  • the fan end plate and the side wall of the indoor unit main body are separated by a distance of, for example, about 5 mm, thereby preventing both from coming into contact and causing rotational friction.
  • the space formed between the fan end plate and the side wall facing the fan end plate is located outside both ends of the fan in the rotation axis direction, and pressure loss occurs when the airflow passes through the heat exchanger. Therefore, the pressure atmosphere is lower than the atmospheric pressure P0. Therefore, it is considered that reverse suction is likely to occur near both ends of the air outlet due to a pressure difference from the atmospheric pressure P0 outside the indoor unit.
  • the side connected to the stabilizer at the outlet is the side connected to the rear guide portion because the static pressure Ps becomes the lowest due to the vortex generated in the vicinity of the stabilizer and the difference from the atmospheric pressure P0 becomes the largest. Rather than reverse sucking.
  • the fan As a configuration for improving the flow rate performance at both ends of the fan in the rotation axis direction, which is a portion where reverse suction is likely to occur as described above, the fan gradually moves from the fan blowing portion to the ventilation passage of the housing blowing portion.
  • the side wall shape is changed so as to reduce the ventilation path in the rotation axis direction (see, for example, Patent Document 1).
  • a backflow prevention plate is provided at both ends of the fan in the rotation axis direction so as to cover the blowout portion in the vicinity of the suction portion, and further, the draft resistance is reduced as a chamfered shape (for example, see Patent Document 2) .
  • JP-A-8-121395 (columns 0013 to 0023, FIG. 1)
  • Japanese Patent Laid-Open No. 2001-201078 (columns 0030 to 0035, FIG. 2)
  • a backflow prevention plate is provided at both ends in the rotation axis direction of the fan so as to cover the blowout part in the vicinity of the suction part, and the airflow resistance is reduced as a chamfered shape
  • a stabilizer that has a low pressure due to the vortex A chamfer is also provided on the side. For this reason, there is a problem that the space between the backflow prevention plate and the fan is widened by the chamfered portion, and the indoor air is easily sucked into the indoor unit from the outlet.
  • the present invention has been made in order to solve the above-described problems, and performs reverse suction at both ends in the longitudinal direction of the air outlet, particularly on the stabilizer side of the air outlet, which is the part where the pressure is the lowest due to the vortex.
  • An object of the present invention is to obtain an air conditioner that can prevent power consumption and noise.
  • An air conditioner includes an indoor unit main body having a suction port for sucking air, and a blowout port that is formed long in the left-right direction and blows out air.
  • an indoor unit main body having a suction port for sucking air, and a blowout port that is formed long in the left-right direction and blows out air.
  • fan extension portions Provided in the indoor unit main body so that the left-right direction of the indoor unit main body and the rotation axis coincide with each other, fan extension portions extending outward from the longitudinal end portion of the outlet are provided at both left and right end portions.
  • a stabilizer and a rear guide part that are arranged to face each other with the cross-flow fan interposed therebetween, and form a blowout air passage that guides indoor air blown out of the cross-flow fan to the blowout port;
  • the indoor unit main body provided outside the left and right ends of the air outlet, respectively, and substantially along a part of the outer periphery of the fan extension so as to face the airflow blown out from the fan extension.
  • a wall structure having opposite surfaces When the distance in the radial direction of the fan extension portion between the opposing surface and the outer peripheral portion of the fan extension portion in a cross section perpendicular to the rotation axis of the opposite surface and the fan extension portion is a distance M,
  • the distance M which is the distance M at the point a of the facing surface near the stabilizer, the distance M in at least a part of the region of the facing surface near the rear guide portion with respect to the point a is It is comprised so that it may become longer than the distance Ma.
  • the stagnation pressure higher than the atmospheric pressure at both ends in the longitudinal direction of the air outlet, particularly on the stabilizer side of the air outlet, which is the portion where the pressure is the lowest due to the vortex. For this reason, while being able to prevent reverse suction, the increase in the energy loss by a collision wall can be suppressed, and a reduction in power and noise can be realized.
  • FIG. 4 is a longitudinal sectional view taken along line QQ in FIG. 1 according to the first embodiment.
  • 3A and 3B are schematic views showing the cross-flow fan according to Embodiment 1, in which FIG. 3A is a side view of the cross-flow fan, and FIG. 3B is a cross-sectional view taken along the line U-U in FIG.
  • FIG. 4 is an enlarged perspective view showing a fan formed by fixing five impellers (units) in the rotation axis direction according to the first embodiment (FIG. 4A), and an explanatory view showing a support plate (FIG. 4 (b)).
  • FIG. 4 is a perspective view showing a collision wall according to Embodiment 1.
  • FIG. FIG. 6 is a cross-sectional view taken along the line WW in FIG. 5 according to the first embodiment.
  • FIG. 4 is a schematic diagram illustrating the internal configuration of the indoor unit in a simplified manner according to the first embodiment.
  • FIG. 9 is an explanatory diagram illustrating, in an enlarged manner, a vicinity of a collision wall at a right end portion in FIG. 8 according to the first embodiment. It is explanatory drawing which concerns on Embodiment 1 and shows the airflow in the indoor unit main body by a cross-flow fan.
  • FIG. 12 is a diagram illustrating a distance M between the facing surface of the collision wall and the outer peripheral portion of the fan according to the first embodiment
  • FIG. 12A is an explanatory diagram illustrating a cross section perpendicular to the rotation axis
  • FIG. Is a graph showing the position in the depth direction AY of the facing surface of the collision wall on the horizontal axis and the distance M between the facing surface and the fan outer peripheral portion on the vertical axis.
  • FIG. 10 is an explanatory diagram illustrating an operation of a collision wall at the rear guide side end portion according to the first embodiment.
  • FIG. 16 is a graph illustrating a collision pressure Pv (FIG. 15A) and a stagnation pressure Pst (FIG. 15A) at the position in the depth direction AY of the facing surface according to the first embodiment.
  • 10 is a graph showing the position in the depth direction AY on the horizontal axis and the stagnation pressure Pst on the vertical axis according to another configuration example of the first embodiment.
  • FIG. 10 is a graph showing the position in the depth direction AY of the facing surface of the collision wall on the horizontal axis and the distance M between the facing surface and the fan outer periphery on the vertical axis according to another configuration example of the first embodiment. It is a perspective view which shows the collision wall which concerns on Embodiment 2 of this invention.
  • FIG. 19 is a diagram illustrating a distance M between the facing surface of the collision wall and the outer periphery of the fan according to the second embodiment
  • FIG. 19A is a vertical cross-sectional view perpendicular to the rotation axis
  • FIG. 1 It is a graph which shows the position M of the depth direction AY on an axis
  • FIG. It is sectional drawing which concerns on Embodiment 3 of this invention, and shows the edge part vicinity when a collision wall is cut
  • FIG. 10 is a diagram illustrating a distance M between the facing surface of the collision wall in the rotation axis direction AX and the outer periphery of the fan according to the third embodiment, where the horizontal axis indicates the position in the rotation axis direction AX, and the vertical axis indicates the facing surface and the outer periphery of the fan. It is a graph which shows distance M.
  • FIG. 10 is an explanatory diagram illustrating an enlarged collision wall according to the third embodiment. FIG.
  • FIG. 14 is a diagram illustrating a distance M between the facing surface of the collision wall in the rotation axis direction AX and the outer periphery of the fan according to another configuration example of the third embodiment, where the horizontal axis represents the position in the rotation axis direction AX and the vertical axis represents It is a graph which shows the distance M of a surface and a fan outer peripheral part.
  • FIG. 10 is an explanatory diagram illustrating a shape of a facing surface in another configuration example according to the third embodiment.
  • FIG. Embodiment 1 of the present invention will be described below with reference to the drawings.
  • 1 is an external perspective view showing an indoor unit 1 of an air conditioner equipped with a cross-flow fan 8 according to Embodiment 1
  • FIG. 2 is a longitudinal sectional view taken along line QQ in FIG.
  • the airflow is indicated by a white arrow in FIG. 1 and indicated by a dotted arrow in FIG.
  • an air conditioner actually constitutes a refrigeration cycle circuit with an indoor unit and an outdoor unit
  • the present invention relates to the configuration of the indoor unit, and the description of the outdoor unit is omitted. As shown in FIGS.
  • an indoor unit (hereinafter referred to as an indoor unit) 1 of an air conditioner has an elongated, substantially rectangular parallelepiped shape extending in the left-right direction, and is installed on a wall surface of a room.
  • a suction grill 2 serving as a suction port for sucking indoor air
  • an electric dust collector 5 for electrostatically collecting dust contained in the sucked indoor air
  • a mesh-like filter 6 for removing dust is disposed.
  • a heat exchanger 7 having a configuration in which the pipe 7b penetrates through the plurality of aluminum fins 7a arranged in parallel is arranged on the front side and the upper side of the cross-flow fan 8 so as to surround the cross-flow fan 8, and this heat exchanger 7 Exchanges heat with the indoor air sucked from the suction grill 2.
  • the front surface of the indoor unit 1 main body is covered with the front panel 1b, and the blower outlet 3 is provided in the lower part of the indoor unit 1 main body, and the indoor air heat-exchanged by the heat exchanger 7 blows out into the room from the blower outlet 3. Is done.
  • the blower outlet 3 is comprised by the opening extended elongate considering the left-right direction of the indoor unit 1 main body as a longitudinal direction. That is, the air outlet 3 is provided so that the longitudinal direction of the air outlet 3 coincides with the left-right direction of the main body of the indoor unit 1.
  • the cross-flow fan 8 as a blower is provided between the heat exchanger 7 and the outlet 3 so that the left-right direction (longitudinal direction) of the main body of the indoor unit 1 is the direction in which the rotation axis extends (referred to as the rotation axis direction). And is driven to rotate by a motor 16 (see FIG. 3) to blow indoor air from the suction grill 2 to the outlet 3.
  • the interior of the main body of the indoor unit 1 includes a stabilizer 9 and a rear guide part 10 that separate the suction area E1 and the blowing area E2 from the cross-flow fan 8.
  • the stabilizer 9 constitutes the front side of the blowout air passage 11 that guides the room air blown from the cross-flow fan 8 to the blowout port 3, and the rear guide portion 10 is, for example, a spiral shape and constitutes the back side of the blowout air passage 11.
  • the rear guide portion 10 has a gentler curved surface than the stabilizer 9 on the front side of the blowout air passage 11, and the blowout air passage 11 has a shape that gradually widens toward the air outlet 3. Up and down wind direction vanes 4a and left and right wind direction vanes 4b are rotatably attached to the air outlet 3, and these change the direction of blowing air into the room.
  • O represents the rotation center of the once-through fan 8
  • E1 represents the suction area of the once-through fan 8
  • E2 represents the blowing area located on the opposite side of the rotation area O from the suction area E1.
  • the suction region E1 and the blowout region E2 of the cross-flow fan 8 are separated by the tongue 9a of the stabilizer 9 and the upstream end portion 10a of the airflow of the rear guide unit 10.
  • RO shows the rotation direction of the cross-flow fan 8
  • AY shows the depth direction of the indoor unit 1, and in the depth direction AY of the indoor unit 1 main body, the side where the outlet 3 is located is the front side, and the rear guide part 10 is located.
  • the side is referred to as the back side.
  • FIG. 3A and 3B are schematic views showing the cross-flow fan 8 according to the first embodiment.
  • FIG. 3A is a side view of the cross-flow fan
  • FIG. 3B is a cross-sectional view taken along the line UU in FIG. is there.
  • the lower half of FIG. 3B shows a state where a plurality of wings on the other side can be seen, and the upper half shows one wing 13.
  • 4A is an enlarged perspective view showing the cross-flow fan 8 formed by fixing the five impellers 14 according to the first embodiment in the rotation axis direction AX
  • FIG. 4B is a support plate.
  • FIG. In FIG. 4, the motor 16 and the motor shaft 16 a are omitted, and the impeller portion is shown as the cross-flow fan 8.
  • the number of impeller single bodies 14 constituting the cross-flow fan 8 and the number of blades 13 constituting one impeller single body 14 may be any number.
  • the cross-flow fan 8 has a plurality of, for example, five impellers 14 in the rotation axis direction AX (longitudinal direction).
  • the impeller single body 14 is provided with an annular support plate 12 at one end, and a plurality of blades 13 extending in the rotation axis direction AX are provided along the outer periphery of the support plate 12.
  • a single impeller 14 formed of a thermoplastic resin such as an AS resin or an ABS resin is provided in the rotation axis direction AX, and the side end of the blade 13 is arranged next to each other by ultrasonic welding or the like. Adhering to the plate 12, the impellers 14 are connected together.
  • a fan shaft 15a is provided at the center of a support plate 12a (hereinafter referred to as a fan end plate) located at one end in the rotational axis direction AX, and a fan boss 15b is provided at the center of the fan end plate 12b located at the other end.
  • the fan boss 15b and the motor shaft 16a of the motor 16 are fixed with screws or the like.
  • the fan end plates 12a and 12b located at both ends of the cross-flow fan 8 in the rotation axis direction AX have a disk shape, and the fan shaft 15a and the fan boss 15b are formed in the central portion where the rotation axis 17 is located.
  • the support plate 12 excluding both ends has an annular space at the center where the rotation axis 17 serving as the center of rotation is located, and has an inner diameter K1 and an outer diameter K2 as shown in FIG. 4B.
  • the alternate long and short dash line is a virtual rotation axis that connects the motor shaft 16a and the fan shaft 15a and indicates the rotation center O.
  • the rotation axis 17 is referred to as the rotation axis 17.
  • the direction in which is extended is the rotation axis direction AX.
  • a single impeller is referred to as a ream 14, and reams 14 positioned at both ends of the cross-flow fan 8 in the rotational axis direction AX are referred to as end reams 14 a.
  • FIG. 5 is a perspective view of the main body of the indoor unit 1 of the air conditioner according to this embodiment when viewed obliquely from below.
  • the vertical wind direction vane 4 a and the left and right wind direction vane 4 b are removed, and a part of the cross-flow fan 8 is visible through the outlet 3.
  • the length L2 of the cross flow fan 8 in the rotation axis direction AX is configured to be longer (L2> L1).
  • This blower outlet 3 is opened so that the longitudinal direction thereof coincides with the left-right direction of the main body of the indoor unit 1.
  • a part of end section 14a of once-through fan 8 is extended in the direction which axis of rotation 17 extends from both ends of the longitudinal direction of blower outlet 3, and this extension part is called fan extension part 8a. That is, the fan extension 8 a is a part of the end link 14 a located at each of both ends of the cross-flow fan 8, and protrudes outward in the longitudinal direction from the left and right ends of the outlet 3 and faces the outlet 3. It is a part that is not.
  • a side wall 30 is provided so as to extend substantially parallel to the surface facing the outside of the fan end plates 12a, 12b at a position away from the fan end plates 12a, 12b of the cross-flow fan 8 by a predetermined distance in the rotational axis direction AX.
  • the side wall 30 constitutes both left and right side surfaces of the air path from the suction grill 2 inside the indoor unit 1 to the blowout port 3.
  • the rear guide portion 10 is formed in a spiral shape from the upstream end 10 a of the rear guide portion 10 to the outlet 3, and the distance from the outer periphery of the impeller of the cross-flow fan 8 to the rear guide portion 10 is blown. It is the structure which becomes long gradually, so that the exit 3 is approached.
  • the front side of the blowout air passage 11 is composed of a stabilizer 9.
  • FIG. 6 is a perspective view showing collision walls 18 provided at both ends in the left-right direction inside the main body of the indoor unit 1 according to Embodiment 1, for example, arranged at the right end toward the outlet 3.
  • the collision wall 18 is shown enlarged.
  • the collision wall 18 disposed at the left end of the blower outlet 3 has the same shape, and the right collision wall may be reversed left and right.
  • FIG. 7 is a cross-sectional view taken along the line WW in FIG.
  • FIG. 5 shows a vertical cross section perpendicular to the rotation axis 17 of the indoor unit 1 in a portion including the collision wall 18 in the vicinity of the fan end plate 12b.
  • the rear guide part 10 in the cross section of the fan extension 8 a, the stabilizer 9, and the collision wall 18 constitute a wall against the airflow blown from the fan extension 8 a and are indicated by oblique lines.
  • the opposing surface 18a which is one surface of the collision wall 18, is a surface facing the fan extension 8a, and the airflow blown from the fan extension 8a is the opposing surface 18a. Collide with. Further, as shown in the cross section of FIG. 7, the rear surface of the blowout air passage 11 facing the fan extension 8 a is configured on the upstream side of the rear guide part 10 partway, but the rear guide part side end 19 b in the middle. It is comprised by the opposing surface 18a of the collision wall 18, and is not connected to opening like the blower outlet 3, but follows the stabilizer 9. FIG.
  • the collision wall 18 connects the stabilizer side end portion 19a disposed on the stabilizer 9 side and the rear guide portion side end portion 19b disposed on the rear guide portion 10 side of the fan extension portion 8a. It is provided surrounding the outer periphery.
  • the radial distance (the distance between the position 20a and the position 19a) between the fan outer peripheral portion 8b and the facing surface 18a at the stabilizer side end portion 19a is Ma
  • the fan outer peripheral portion 8b at the rear guide portion side end portion 19b is the facing surface.
  • a collision area where the blown air flow blown out from the fan extension 8a collides with the collision wall 18 is indicated by a region E3. That is, of the blowing area E2 (see FIG. 2) showing the area where the airflow is blown from the once-through fan 8, the area where the airflow blown from the fan extension 8a collides with the collision wall 18 is defined as a collision area E3. This collision area E3 becomes a part of the blowing area E2.
  • the collision wall 18 since the rear guide portion side end portion 19b of the collision wall 18 is smoothly connected to the rear guide portion 10, the collision wall 18 actually has a zero rise height from the rear guide portion 10 at the extreme end portion. It becomes.
  • the rear guide portion side end portion 19b is adjacent to the rear end portion adjacent to the end portion where the collision wall 18 is connected to the rear guide portion 10 when viewed in the rotation axis direction AX.
  • the facing surface 18a protrudes from the surface of the guide portion 10 with a slight step.
  • the distance M is the same at any position of the collision wall 18 in the rotation axis direction AX. That is, the facing surface 18 a of the collision wall 18 is configured to be parallel to the rotation axis 17 in the rotation axis direction AX.
  • FIG. 8 is a schematic diagram showing the internal configuration of the indoor unit 1 according to Embodiment 1 in a simplified manner, and the suction grill 2, the heat exchanger 7, the cross-flow fan 8, and the outlet according to the airflow direction (white arrow). 3 is shown in a simplified manner.
  • the end portions 14a disposed at both ends of the cross-flow fan 8 have fan extension portions 8a, respectively, and the fan extension portions 8a face the facing surface 18a of the collision wall 18 in the collision area E3.
  • the portion excluding the fan extension 8 a that is, the central portion of the cross-flow fan 8 in the rotational axis direction AX faces the outlet 3.
  • the collision walls 18 provided at the left and right ends are connected to the side walls 30 because they are integrally formed with the left and right side walls 30, for example, and extend inward in the left-right direction with the side walls 30 as one end. Since the side wall 30 may be uneven in the rotational axis direction AX for the convenience of the configuration, the length Na of the opposing surface 18a in the rotational axis direction AX is substantially parallel to the rotational axis 17 with respect to the fan extension 8a. The length of the facing surface 18a facing each other from the fan end plates 12a and 12b.
  • the positions of the fan end plates 12a and 12b in the rotational axis direction AX are the positions of the outward faces of the fan end plates 12a and 12b facing the outside of the main body of the indoor unit 1.
  • the outer diameter K2 (see FIG. 4) of the annular support plate 12 fixed to the blade 13 at the end of the impeller 14 is ⁇ 110 mm and the inner diameter K1 (see FIG. 4) is ⁇ 60 mm.
  • 35 wings 13 are fixed on the top.
  • the longitudinal length L1 of the outlet 3 is 610 mm
  • the total length L2 of the cross flow fan 8 in the rotation axis direction AX is 640 mm.
  • the length Na in the rotation axis direction AX of the facing surface 18a of the collision wall 18 is 15 mm. Further, in FIG.
  • a region denoted by S indicates a space formed between the fan end plates 12 a and 12 b at both ends of the cross-flow fan 8 and the side wall 30.
  • the length of the space S in the rotation axis direction AX is, for example, 10 mm. Further, the length of the end portion 14a in the rotation axis direction AX is 25 mm (left side in FIG. 8) at one end portion 14a and 70 mm (right side in FIG. 8) at the other end portion 14a.
  • the length AX of the other series 14 excluding the end series 14a is approximately 80 mm.
  • Distance Mb 25 mm
  • FIG. 9 is an explanatory view showing, in an enlarged manner, the vicinity of the collision wall 18 at the right end portion in FIG. Based on FIGS. 8 and 9, the airflow inside the indoor unit 1 and the action of the collision wall 18 at both ends in the longitudinal direction of the indoor unit 1 will be described.
  • the air conditioner is operated, and the cross flow fan 8 is rotated in the RO direction by the motor 16.
  • the cross-flow fan 8 rotates, the indoor air sucked from the suction grill 2 is heat-exchanged by the heat exchanger 7.
  • the heat-exchanged room air becomes an air flow A, which is blown by the once-through fan 8 and blown out from the blowout port 3 through the blowout area E2.
  • the static pressure Ps becomes Pe, which is lower than the atmospheric pressure P0.
  • the static pressure Ps indicating the atmospheric pressure in the indoor unit 1 is affected by the ventilation resistance, and thus shows various values at each location in the indoor unit 1.
  • the space S in the vicinity of the outward surface of the end plate 12b is a space that is continuous with the suction region E1 and has the same pressure atmosphere, and thus exhibits a static pressure Ps equivalent to that of the suction region E1, and is Pe ( ⁇ atmospheric pressure P0). .
  • the airflow Aa blown to a location facing the collision wall 18 collides with the facing surface 18a of the collision wall 18, and the energy of the wind speed is converted into pressure energy.
  • the stagnation pressure Pst is generated in the collision area E3.
  • the stagnation pressure Pst static pressure Ps + the collision pressure Pv.
  • the value of the stagnation pressure Pst becomes higher than the atmospheric pressure P0.
  • the wind speed Va when the stagnation pressure Pst becomes higher than the atmospheric pressure P0 varies depending on the pressure loss of the mounted heat exchanger or the like.
  • the space S outside the both ends of the cross-flow fan 8 is an area where the air flow by the cross-flow fan 8 does not act.
  • the static pressure Ps of the space S is Pe, which is lower than the atmospheric pressure P0, and there is almost no increase in pressure due to air blowing. Therefore, reverse suction due to the indoor air flowing into the space S through the outlet 3 is likely to occur.
  • a wall having a stagnation pressure Pst higher than the atmospheric pressure P0 is formed in the collision region E3 between the space S and the blowout air passage 11 leading to the blowout port 3, so that the outside of the indoor unit 1 is removed.
  • the reverse suction G into which room air flows in through the outlet 3 can be blocked.
  • the collision flow to the collision wall 18 does not become a blowing airflow to the outside of the indoor unit 1, it is a loss to make the stagnation pressure Pst higher than the atmospheric pressure P0 for the purpose of blowing air. That is, a collision wall 18 that forms a uniform collision pressure Pv is provided from the stabilizer-side end 19a to the rear guide-side end 19b in the depth direction AY, and the blown airflow collides with the collision wall 18. That increases the draft resistance.
  • the increase in ventilation resistance increases the load on the once-through fan 8, leading to an increase in energy loss and noise.
  • FIG. 10 is an explanatory diagram showing an air flow in the main body of the indoor unit 1 by the cross-flow fan 8 according to the first embodiment.
  • a vortex (circulation vortex) F ⁇ b> 1 is generated in the vicinity of the stabilizer 9 in the cross-flow fan 8 as the airflow passes.
  • the area E4 around the vortex F1 has the lowest static pressure Ps in the indoor unit 1 and the lowest value Pmin, and the difference from the atmospheric pressure P0 is the largest.
  • surroundings of the vortex F1 blows off is more static pressure Ps than the rear guide part side (Gb) which the airflow J2 which passes the part away from the vortex F1 blows. Decreases and the difference from the atmospheric pressure P0 increases.
  • FIG. 11 is a graph showing the static pressure Ps when the collision wall 18 is not provided on the blowout side of the cross-flow fan 8 at both ends in the left-right direction of the indoor unit 1 according to Embodiment 1, and the horizontal axis indicates the depth direction.
  • the position of AY is shown, and the static pressure Ps is shown on the vertical axis.
  • Pe indicates the static pressure Ps in the suction area E1 on the suction side of the cross-flow fan 8 in the indoor unit 1.
  • Ha is a pressure drop due to the airflow J1 passing through the cross-flow fan 8 near the stabilizer tongue 9a of the stabilizer 9
  • Hb is the airflow J2 passing through the cross-flow fan 8 near the upstream end 10a of the rear guide part 10. It shows the pressure drop by.
  • Psa indicates the static pressure Ps near the stabilizer side end 19a
  • Psb indicates the static pressure Ps near the rear guide side end 19b.
  • the pressure in the indoor unit 1 is lower than the atmospheric pressure P0, and the static pressure Ps in the suction region E1 of the cross-flow fan 8 is Pe (less than the atmospheric pressure P0). Low). Further, due to the vortex F1 generated inside the cross flow fan 8 when the indoor air flows across the cross flow fan 8, the pressure drop Ha at the stabilizer side end 19a is large, and the static pressure Ps at the stabilizer side end 19a is Psa. Thus, the lowest value Pmin in one indoor unit is shown.
  • the pressure drop Hb at the rear guide part side end 19b is smaller than the pressure drop Ha because the airflow passes through the part away from the vortex F1, and the static pressure Ps at the rear guide part side end 19b is higher than Psa. Psb.
  • a higher collision pressure Pv is required at the stabilizer-side end 19a than at the rear guide-side end 19b.
  • the stagnation pressure Pst higher than the atmospheric pressure P0 can be formed at the collision pressure Pv lower than the stabilizer side end 19a at the rear guide side end 19b.
  • the rear guide part side end 19b is configured to collide with the opposing surface 18a at least an airflow that provides the necessary collision pressure Pv, and airflow other than the airflow necessary for the collision pressure Pv is blown to the outlet 3.
  • FIG. 12 is a diagram showing the distance M between the facing surface 18a of the collision wall 18 according to the first embodiment and the fan outer peripheral portion 8b.
  • 12A is an explanatory view showing a cross section perpendicular to the rotation axis 17 (see FIG. 9) at both ends of the indoor unit 1 in the longitudinal direction
  • FIG. 12B is a horizontal axis showing the depth of the collision wall 18. It is a graph which shows the distance M of the opposing surface 18a of the collision wall 18, and the fan outer peripheral part 8b on the position of the direction AY, and a vertical axis
  • the radial distance Mb between the facing surface 18a that faces the cross-flow fan 8 and the fan outer peripheral portion 8b is made longer than the distance Ma in the stabilizer side end portion 19a.
  • the distance (Ma) at the stabilizer-side end 19a is the largest for the distance M between the facing surface 18a of the collision wall 18 and the fan outer peripheral portion 8b.
  • region from the increase start position 19c in the opposing surface 18a to the rear guide part side edge part 19b is comprised so that the distance M may increase smoothly toward the rear guide part side edge part 19b from the increase start position 19c.
  • the start of increase means the start of an increase in the radial distance M between the facing surface 18a and the fan outer peripheral portion 8b.
  • the increase start position 19c is provided in the middle of the opposing surface 18a between the stabilizer-side end 19a and the rear guide portion-side end 19b, and the stabilizer when increasing the distance M between the opposing surface 18a and the fan outer peripheral portion 8b. This is the start position on the 9th side.
  • an increase start position 19c is provided at a position that is about 10% of the total length and is away from the stabilizer side end 19a to the rear guide portion side end 19b.
  • FIG. 13 is an explanatory view showing the action of the collision wall 18 at the stabilizer side end 19a according to the first embodiment.
  • the static pressure Ps of the indoor unit 1 is caused by the vortex F ⁇ b> 1 generated in the cross-flow fan 8 at the stabilizer side end 19 a positioned on the front side in the depth direction AY.
  • the lowest value Pmin in the cabin is shown.
  • the airflow blown from the fan extension 8a collides with the facing surface 18a of the collision wall 18 that is separated from the fan outer periphery 8b by a distance Ma.
  • the distance Ma is the same as the distance between the tongue portion 9a of the stabilizer 9 disposed closest to the cross-flow fan 8 and the fan outer peripheral portion 8b, and is short. For this reason, the air flow blown out from the fan outer peripheral portion 8b flows toward the facing surface 18a as it is and collides with the facing surface 18a, so that the collision pressure Pva is applied, and the stagnation pressure Psta is applied to the collision region E3 of the stabilizer side end portion 19a. It is formed.
  • FIG. 14 is an explanatory diagram showing the action of the collision wall 18 at the rear guide side end 19b according to the first embodiment.
  • the side wall 30 side (right side in the figure) that is the end of the rotation axis direction AX of the indoor unit 1 and the center side of the indoor unit 1
  • the side wall 30 side spreads to both the blowout air passage 11 side (left side in the figure) leading to the blowout port 3.
  • the airflow toward the side wall 30 collides with the side wall 30 to apply pressure, and generates stagnation pressure on the side wall 30. Thereby, the pressure gradient that the side wall 30 side is high and the blowing air passage 11 side is low is generated.
  • FIG. 15 is a graph (FIG. 15A) showing the collision pressure Pv with respect to the position in the depth direction AY of the facing surface 18a according to the first embodiment (FIG. 15A) and a graph showing the stagnation pressure Pst with respect to the position in the depth direction AY (FIG. 15B). )).
  • the collision pressure Pva at the stabilizer side end 19a is compared with the collision pressure Pvb at the rear guide side end 19b, the air current that collides with the collision wall 18 at the rear guide side end 19b is more than the stabilizer side end 19a.
  • the collision pressure Pv becomes Pva> Pvb.
  • the collision pressure Pv shows substantially the same value as Pva from the stabilizer side end 19a to the increase start position 19c, and gradually decreases from Pva from the increase start position 19c to the rear guide side end 19b.
  • the static pressure Ps described in FIG. 11 is applied with the collision pressure Pva at the stabilizer side end 19a and the collision pressure Pvb at the rear guide side end 19b as shown in FIG. 15 (a). It shows the stagnation pressure Pst after.
  • the difference (Pva ⁇ Pvb) in the collision pressure Pv between the stabilizer-side end 19a and the rear guide-side end 19b in FIG. 15A is the difference (Ha) in the static pressure Ps shown in FIG. Same as -Hb). That is, when the distance M is adjusted so as to obtain such a collision pressure Pv, the difference (Psa ⁇ Psb) in the static pressure Ps is canceled, and the stagnation pressure Pst formed in the collision area E3 of the facing surface 18a is As shown by the straight line Pst1 in FIG. 15 (b), the entire pressure in the depth direction AY from the stabilizer-side end 19a to the rear guide-side end 19b is higher than the atmospheric pressure P0 and substantially constant. .
  • the airflow flowing toward the blowout air passage 11 on the center side of the indoor unit 1 blows out of the indoor unit 1 through the blowout air passage 11 and the blowout port 3.
  • the airflow flowing through the blowout air passage 11 acts on the air flow.
  • the distance M between the fan outer peripheral part 8b and the facing surface 18a of the collision wall 18 is configured to be longer than the stabilizer side end part 19a (Mb> Ma).
  • a stagnation pressure Pst that can prevent sucking can be formed in the collision area E3, and a blown airflow can be secured.
  • the increase in ventilation resistance by the collision wall 18 is increased. Can be kept small, and the power consumption required for the necessary air flow rate can be kept small. Furthermore, an increase in noise due to a collision can be reduced.
  • the cross-flow fan 8 mounted in the indoor unit 1 of the air conditioner is set to the number of rotations that is operated according to the operation mode such as weak cooling or strong cooling.
  • the operation mode such as weak cooling or strong cooling.
  • the stagnation pressure Psta higher than the atmospheric pressure P0 is obtained at the stabilizer side end 19a at the wind speed when operating at the lowest rotational speed among the operation modes of the once-through fan 8.
  • the radial distance Ma between the collision wall 18 and the outer peripheral portion 8b of the cross-flow fan 8 at the stabilizer side end 19a, and the length Na in the rotation axis direction AX are determined.
  • the distance Ma is set to about the distance between the fan outer peripheral portion 8b and the stabilizer 9, and the distance Ma (here, 5 mm) is set, so that a stagnation pressure Psta higher than the atmospheric pressure P0 can be obtained by testing or simulation. (Here, 15 mm) is determined. Furthermore, by assuming the change in the static pressure Ps in the depth direction AY in the vicinity of the facing surface 18a in the indoor unit 1, that is, the static pressure Ps at each position in the depth direction AY of the facing surface 18a, the atmospheric pressure P0 at each position. The minimum necessary collision pressure Pv for forming a higher stagnation pressure Pst can be set.
  • the expansion of the jet flow width of the jet fluid is proportional to the distance in which the fluid advances (here, the distance M from the fan outer peripheral portion 8b to the collision wall 18).
  • the distance M may be set in consideration of If the collision wall 18 is provided so as to have the dimensions determined in this way, during the operation of the indoor unit 1, that is, when the cross-flow fan 8 is rotating, the collision region E3 is made to be more than the atmospheric pressure P0 by the blown airflow from the fan extension 8a. A space having a high and almost constant stagnation pressure Pst can be obtained.
  • the same stagnation pressure Pst is formed in the entire collision area E3 from the stabilizer side end 19a to the rear guide side end 19b.
  • the distance between the fan outer peripheral portion 8b and the facing surface 18a was set.
  • the collision wall 18 is configured so that the stagnation pressure Pst of different magnitude is formed in the collision area E3 on the entire surface from the stabilizer side end 19a to the rear guide part side end 19b. Also good.
  • FIG. 16 is a graph showing the stagnation pressure Pst formed in the collision area E3 with respect to the position in the depth direction AY according to another configuration example of the first embodiment.
  • the horizontal axis indicates the position in the depth direction AY.
  • the stagnation pressure Pst is shown on the vertical axis. Even in the stagnation pressure Pst as shown by the straight line Pst2 in FIG. 16, the stagnation pressure Pst larger than the atmospheric pressure P0 over the entire surface from the stabilizer side end 19a to the rear guide side end 19b in the depth direction AY. Is shown. For this reason, reverse suction can be prevented.
  • the stagnation pressure Pst necessary for preventing reverse suction is the stabilizer side end portion 19a. May be lower.
  • the stagnation pressure Pst having a large difference from the atmospheric pressure P0 is formed at the stabilizer side end 19a where reverse suction is likely to occur, thereby reliably preventing reverse suction.
  • the atmospheric pressure can be increased by increasing the distance Mb from the fan outer peripheral portion 8b to the collision wall 18 as compared with the straight line Pst1 shown in FIG.
  • a stagnation pressure Pst that is about the same as P0 or slightly higher than the atmospheric pressure P0 is formed at the rear guide side end 19b, and the ratio of the air flow is increased compared to the straight line Pst1.
  • the collision pressure Pvb at the straight line Pst2 is smaller than the collision pressure Pvb at the straight line Pst1.
  • the same stagnation pressure Pst can be obtained from the stabilizer side end portion 19a to the rear guide portion side end portion 19b.
  • the change in the stagnation pressure Pst formed from the stabilizer side end 19a to the rear guide side end 19b in the depth direction AY of the collision wall 18 is represented by the straight line Pst1 and the straight line Pst2, it is not limited thereto. is not.
  • the change in the stagnation pressure Pst formed from the stabilizer side end portion 19a to the rear guide portion side end portion 19b may change in a curved line or may change in a step shape.
  • the fan outer peripheral portion is formed so that the stagnation pressure Pst necessary to prevent the occurrence of reverse suction at that position is formed.
  • the collision wall 18 may be configured in consideration of the radial distance M between 8b and the facing surface 18a.
  • the increase start position 19c is a position that is about 10% of the length of the collision wall 18 in the depth direction from the stabilizer side end 19a, but is not limited to this.
  • FIG. 1 shows that the increase start position 19c is a position that is about 10% of the length of the collision wall 18 in the depth direction from the stabilizer side end 19a, but is not limited to this.
  • the increase start position 19 c is such that the straight line Z connecting the rotation center O of the once-through fan 8 and Gb on the rear guide part 10 side of the outlet 3 intersects the facing surface 18 a of the collision wall 18. It is preferable that the position be closer to the rear guide portion side end 19b than the position (indicated by the increase start position 19c in FIG. 10). This is because the region from the stabilizer side end 19a to the crossing position of the straight line Z and the facing surface 18a is close to the region E4 where the pressure is low due to the vortex F1, and reverse suction is likely to occur.
  • the collision wall 18 is the start position on the side of the stabilizer 9 when the distance M between the fan outer peripheral portion 8 b and the facing surface 18 a is longer than the distance Ma.
  • a start position 19c is provided in the middle between the stabilizer-side end 19a and the rear guide-side end 19b. Then, with respect to the radial distance M between the fan outer peripheral portion 8b and the facing surface 18a, reverse suction occurs by making the distance M in the region from the stabilizer side end portion 19a to the increase start position 19c the same as the distance Ma. Since the stagnation pressure Pst sufficiently higher than the atmospheric pressure P0 is stably formed from the easy stabilizer side end 19a to the increase start position 19c, there is an effect that the reverse suction can be surely prevented.
  • FIG. 17 relates to another configuration example of the first embodiment.
  • the horizontal axis indicates the position in the depth direction AY of the facing surface 18a of the collision wall 18, and the vertical axis indicates the radial distance M between the facing surface 18a and the fan outer peripheral portion 8b. It is a graph which shows. Any distance change of ln2 to ln5 shown here may be used.
  • the straight line ln2 is an example in which, without providing the increase start position 19c, the shortest distance Ma is set at the stabilizer side end 19a, and the longest distance Mb is set at the rear guide side end 19b.
  • a curve ln3 is an example in which the distance Ma is the shortest at the stabilizer side end 19a, and the distance M is increased in about 2/3 of the entire portion near the rear guide side end 19b, and the rear guide side end 19b. It is suitable for the indoor unit 1 having a configuration in which reverse suction does not occur much in the vicinity.
  • the distance M is also set near the rear guide side end 19b as shown by curves ln4 and ln5.
  • the stagnation pressure Pst is formed by shortening and obtaining a high collision pressure Pv.
  • a stagnation pressure Psta sufficiently higher than the atmospheric pressure P0 can be formed at the stabilizer side end 19a.
  • the collision pressure Pvb is lower than the collision pressure Pva, but a level capable of forming a stagnation pressure Pstb higher than the atmospheric pressure P0 is obtained, Backwashing can be prevented by the stagnation pressure Pstb, and an airflow that contributes to blowing is obtained by spreading the airflow toward the center in the rotational axis direction AX.
  • an optimum shape can be obtained by considering the state of the static pressure Ps in the indoor unit 1 as shown in FIG. The collision wall 18 is obtained.
  • the suction grill 2 that is provided in the upper portion of the main body of the indoor unit 1 and sucks room air
  • the heat exchanger 7 that exchanges heat with the room air sucked from the suction grill 2
  • a blower outlet 3 provided at a lower portion of the main body of the indoor unit 1 so as to extend in the longitudinal direction in the left-right direction of the main body of the indoor unit 1, and blows out indoor air heat-exchanged by the heat exchanger 7 into the room;
  • the left-right direction of the main body of the indoor unit 1 and the direction AX in which the rotation axis 17 extends coincide with each other, and more than the longitudinal end of the blower outlet 3.
  • a cross-flow fan 8 having fan extension portions 8a extending to the outside at both left and right ends, a stabilizer 9 constituting the front side of a blow-out air passage 11 that guides indoor air to the blow-out port 3 on the downstream side of the cross-flow fan 8; Constructs the back side of the blowing air passage 11
  • the rear guide part 10 and the both ends of the main body of the indoor unit 1 are provided so as to connect the stabilizer 9 and the rear guide part 10 to the room air blown out from the fan extension 8a.
  • a collision wall 18 having a facing surface 18a provided substantially along a part of the outer peripheral portion of the fan extension 8a, and the facing surface 18a in the cross section perpendicular to the rotation axis 17 and the fan extension.
  • the rear guide part of the opposing surface 18a is more than the distance Ma at the stabilizer side end 19a connected to the stabilizer 9 of the opposing surface 18a.
  • the distance Mb at the rear guide part side end part 19b connected to 10 is configured to be long.
  • the radial distance M between the fan outer peripheral portion 8b and the facing surface 18a should be longer than the distance Ma at the stabilizer side end portion 19a.
  • a part of the airflow from the fan extension 8a is used as a blown airflow, and the airflow that blows out from the fan extension 8a and collides with the collision wall 18 is made smaller than that on the side of the stabilizer 9.
  • a stagnation pressure Pst lower than the atmospheric pressure P0 which is lower than the collision pressure Pv on the airflow in the vicinity of the vortex F1 but which can prevent reverse suction, is formed in the vicinity of the rear guide portion 10 to extend the fan. It is possible to suppress an increase in energy loss and noise due to the collision of all airflows blown out from the portion 8a with the collision wall 18, thereby realizing low power and low noise.
  • FIGS. 18 and 19 are explanatory views showing the indoor unit of the air conditioner according to this embodiment.
  • FIG. 18 is a perspective view showing the collision wall 18 on the right side of the indoor unit 1 according to this embodiment.
  • 19 is a diagram showing a distance M between the facing surface 18a of the collision wall 18 according to the second embodiment and the fan outer peripheral portion 8b
  • FIG. 19A is a longitudinal section perpendicular to the rotation axis 17 of the indoor unit 1.
  • 19B is a graph in which the horizontal axis indicates the position of the collision wall 18 in the depth direction AY, and the vertical axis indicates the distance M between the fan outer peripheral portion 8 b and the facing surface 18 a of the collision wall 18.
  • the rear guide portion side end portion 19b of the collision wall 18 is positioned at the upstream end portion of the air flow in the rear guide portion 10 with respect to the position in the first embodiment shown in FIG. It is characterized by being connected near 10a.
  • the same reference numerals as those in Embodiment 1 denote the same or corresponding parts.
  • FIG. 10 shows the relationship between the fan outer peripheral portion 8b and the blowout air passage 11 at the central portion in the left-right direction of the indoor unit 1, that is, the central portion where the collision wall 18 is not formed.
  • the vicinity of the upstream end portion 10a of the airflow of the rear guide portion 10 and the tongue portion 9a of the stabilizer 9 have a function of separating the suction region E1 and the blowing region E2.
  • the upstream end 10a and the tip of the tongue 9a of the stabilizer 9 are disposed closer to the fan outer peripheral portion 8b than the other components.
  • the distance Mb at the rear guide portion side end portion 19b is longer than the distance Ma at the stabilizer side end portion 19a.
  • the distances Ma and Mb at the stabilizer-side end 19a and the rear guide-side end 19b are shorter than the distance M at the facing surface 18a therebetween, for example, at the center in the depth direction AY.
  • the distance Md at the position 19d is the longest.
  • the distance M with respect to the position in the depth direction AY of the facing surface 18a is short from the stabilizer side end portion 19a to the increase start position 19c, as indicated by a curve ln6 in FIG. Ma, Mc). Then, it increases from the increase start position 19c, is longest at the center position 19d (Md), and is kept long for a predetermined time from the center position 19d toward the rear guide side end 19b. Thereafter, the distance gradually decreases toward the rear guide portion side end portion 19b, and becomes a distance Mb at the rear guide portion side end portion 19b.
  • the distance Mb is longer than the distance Ma and shorter than the distance Md.
  • Ventilation resistance varies depending on the internal configuration of the indoor unit 1 of the air conditioner, and a vortex F2 as shown in FIG. 19A may be generated in the vicinity of the upstream end portion 10a of the airflow of the rear guide portion 10.
  • the static pressure Ps in the indoor unit 1 is reduced due to the influence of the vortices F1 and F2.
  • the static pressure Ps with respect to the position in the depth direction AY is as shown in FIG. .
  • the collision wall 18 having the shape shown in FIG. 19B has distances Ma and Mb between the stabilizer tongue portion 9a and the fan outer peripheral portion 8b in the vicinity of the stabilizer side end portion 19a and the rear guide portion side end portion 19b.
  • the collision pressure Pv is lower than the stabilizer side end 19a and the rear guide side end 19b, but the static pressure Ps is high, so that a stagnation pressure Pst higher than the atmospheric pressure P0 is formed.
  • the stagnation pressure Pst is Pstd
  • the static pressure Ps is Psd
  • the collision pressure Pv is Pvd
  • the stagnation pressure Pstd static pressure Psd + the collision pressure Pvd
  • the stagnation pressure Pstd higher than the atmospheric pressure P0 can be formed similarly to the stagnation pressure Pstb at the rear guide portion side end 19b.
  • the distance M between the fan outer peripheral portion 8b and the collision wall 18 is uniform from the stabilizer side end portion 19a to the rear guide portion side end portion 19b.
  • the distance M is shortened to obtain a high collision pressure Pv
  • the distance M is set longer than a position where the static pressure Ps is low.
  • the distance M is changed according to the static pressure Ps so as to obtain a collision pressure Pv lower than the collision pressure Pv at the position where Ps becomes low.
  • the suction grill 2 that is provided in the upper portion of the main body of the indoor unit 1 and sucks room air
  • the heat exchanger 7 that exchanges heat with the room air sucked from the suction grill 2
  • a blower outlet 3 provided at the lower part of the main body of the indoor unit 1 so as to extend in the longitudinal direction in the left-right direction of the main body of the air conditioner 1, and blows out indoor air heat-exchanged by the heat exchanger 7 into the room;
  • the left-right direction of the main body of the indoor unit 1 coincides with the direction in which the rotation axis 17 extends, and is outside the longitudinal end of the air outlet 3.
  • a cross-flow fan 8 having fan extension portions 8a extending in the left and right ends, a stabilizer 9 constituting a front surface side of a blow-out air passage 11 that guides indoor air to the blow-out port 3 on the downstream side of the cross-flow fan 8; Constructs the back side of the air outlet 11
  • the rear guide part 10 and the both ends of the main body of the indoor unit 1 are provided so as to connect the stabilizer 9 and the rear guide part 10 to the room air blown out from the fan extension 8a.
  • a collision wall 18 having a facing surface 18a provided substantially along a part of the outer peripheral portion 8b of the fan extension 8a, and the facing surface 18a in the cross section perpendicular to the rotation axis 17 and the fan.
  • the stabilizer side is more than the distance Ma that is the distance M at the stabilizer side end portion 19a connected to the stabilizer 9 of the facing surface 18a.
  • At least a part of the distance M between the end portion 19a and the rear guide portion side end portion 19b connected to the rear guide portion 10 of the facing surface 18a is:
  • the change in the distance M with respect to the position in the depth direction AY is not limited to ln6 shown in FIG.
  • the distance M between the facing surface 18a and the fan outer peripheral portion 8b is constant from the stabilizer side end portion 19a to the increase start position 19c, but is not limited thereto.
  • the increase start position 19c when a sufficient stagnation pressure Pst that can prevent reverse suction is obtained at the stabilizer side end 19a, and the decrease in the static pressure Ps near the increase start position 19c is not as great as that at the stabilizer side end 19a, the increase start position 19c.
  • the distance M between the fan extension 8a and the facing surface 18a may be increased from the stabilizer side end 19a toward the central position 19d.
  • the configuration is not limited to the change indicated by ln6, and the configuration may be such that the distance M of the region from the stabilizer side end portion 19a to the rear guide portion side end portion 19b is changed stepwise, curved or linear, The shape may be changed. If the distance M at least part of any one of the stabilizer side end portion 19a to the rear guide portion side end portion 19b is configured to be longer than the distance Ma at the stabilizer side end portion 19a, all of the facing surface 18a is formed. It is possible to reduce power consumption and noise compared to the same configuration as the distance Ma.
  • the following can be said about the rear guide part side end part 19b.
  • the front side of the collision wall 18 is connected to the stabilizer 9 in a cross section perpendicular to the rotation axis 17, but the back side is from the upstream end 10 a to the rear guide part side Gb of the outlet 3.
  • the airflow and static pressure Ps inside the indoor unit 1 main body are taken into consideration, and the collision wall 18 according to the necessity / unnecessity of the collision pressure. What is necessary is just to determine the position of the rear guide part side edge part 19b.
  • the distance M between the fan outer peripheral portion 8b and the facing surface 18a may be determined in consideration of how much collision pressure is necessary.
  • FIG. 21 is a cross-sectional view showing the vicinity of the end portion 14 a inside the indoor unit 1 according to this embodiment, and shows a cross section when the collision wall 18 is cut along a plane including the rotation axis 17.
  • the right end of the cross-flow fan 8 in the left-right direction is shown, and the left end is horizontally reversed.
  • the same reference numerals as those in Embodiment 1 denote the same or corresponding parts.
  • the distance M between the fan outer peripheral portion 8b and the facing surface 18a on the facing surface 18a of the collision wall 18 is the same in the rotation axis direction AX.
  • the distance M is different in the rotation axis direction AX.
  • an end portion located on the end plate 12 b side of the cross-flow fan 8 is a side wall-side end portion 21 e, and the center side of the cross-flow fan 8, that is, Let the edge part which adjoins be the blowing wind path side edge part 21f.
  • the distance M between the fan outer peripheral portion 8b and the facing surface 18a is set such that the distance Me at the side wall side end portion 21e is smaller than the distance Mf at the blowout air passage side end portion 21f.
  • the cross section perpendicular to the rotation axis 17 is in the depth direction AY of the facing surface 18a as described in the first embodiment or the second embodiment. It is assumed that the relationship of the distance M at each position is satisfied.
  • FIG. 22 is a diagram showing the distance M between the facing surface of the collision wall in the rotation axis direction AX and the outer periphery of the fan according to Embodiment 3, the horizontal axis indicates the position in the rotation axis direction AX, and the vertical axis indicates the facing surface and the fan. It is a graph which shows the distance M with an outer peripheral part.
  • FIG. 22 is an explanatory view showing an air flow on the opposing surface 18a configured as described above.
  • the side wall side end portion 21e of the opposing surface 18a is adjacent to the space S where the static pressure Ps is low and the blown airflow does not flow directly, and the side wall side end portion 21e has a draft resistance due to the end plate 12b and the like. Due to the fact that the static pressure Ps is higher than that of the road side end portion 21f, reverse suction in which room air enters the machine through the outlet 3 is likely to occur.
  • the distance Me from the fan outer peripheral portion 8b is configured to be shorter than the distance Mf at the blowout air passage side end portion 21f at the side wall side end portion 21e.
  • the airflow spreading from the fan outer peripheral portion 8b in the side wall side end portion 21e having a short distance M spreads in the rotation axis direction AX before reaching the facing surface 18a.
  • the collision pressure Pve that is less than the collision pressure Pvf of the blowout air passage side end portion 21f is obtained.
  • the collision pressures Pve and Pvf are applied, and the opposing surface 18a
  • the stagnation pressure Pst formed at the side wall end 21e is Pste, which is higher than Pstf, which is the stagnation pressure Pst formed at the blowout air passage side end 21f (Pste> Pstf> P0).
  • the collision wall 18 is formed so that the stagnation pressures Pste and Pstf are both higher than the atmospheric pressure P0.
  • the distance Me is set such that a collision pressure Pve necessary to form a stagnation pressure Pste having a magnitude that reliably prevents reverse suction is obtained.
  • the distance Mf is set such that a collision pressure Pvf necessary for forming a stagnation pressure Pstf ( ⁇ P0) comparable to the atmospheric pressure P0 is obtained.
  • This distance Mf is longer than the distance Me, and the blowout air passage side end portion 21f of the facing surface 18a is configured to be further away from the fan outer peripheral portion 8b than the side wall side end portion 21e. It flows into the blowout air passage 11 and acts on the air flow.
  • the airflow does not collide perpendicularly to the facing surface 18a, but collides with the slope of the facing surface 18a, so that the airflow X and the airflow component Xa acting on the collision pressure as shown in FIG. It is decomposed into an airflow Xb that acts on the air flow. Due to the air flow component Xb acting on the air flow and the pressure difference due to the level of the stagnation pressure Pst in the rotation axis direction AX, an air flow Xc from the side wall side end portion 21e to the blowing air path side end portion 21f is generated on the facing surface 18a. For this reason, the airflow Xc comes to collide with the reverse suction airflow, and further reverse suction can be prevented.
  • the distance Mf between the air outlet side end portion 21f of the facing surface 18a and the outer peripheral portion 8b of the cross-flow fan 8 is the side wall-side end portion of the facing surface 18a located on the end side of the cross-flow fan 8.
  • the distance Me is longer than the distance Me between the fan outer peripheral portion 8b and 21e. That is, when viewed in the direction of the rotation axis 17, the blown air passage side end 21 f that is the end of the facing surface 18 a near the center of the cross-flow fan 8 is the side wall-side end that is the end near the end of the cross-flow fan 8. It was configured to be farther from the outer peripheral portion 8b of the fan extension 8a than 21e.
  • FIG. 25A shows the shape of the facing surface 18a configured to obtain the distance M indicated by the curve ln12 in FIG.
  • the fan outer peripheral portion 8b has a substantially constant distance M from the side wall end 21e to the position 21g as shown by the curve ln12 in FIG.
  • the distance M from the position 21g to the blowing air passage side end 21f may be changed so as to be longer than the position 21g and the side wall end 21e.
  • the pressure field of the stagnation pressure formed at the side wall end portion 21e can be formed widely from the side wall side end portion 21e to the position 21g in the rotation axis direction AX, and the reverse suction can be reliably prevented.
  • FIG. 25B shows the facing surface 18a when the distance M is changed corresponding to the position in the rotational axis direction AX as indicated by the curve ln13 in FIG.
  • the opposing surface 18a is formed with a smooth curved surface from the side wall side end portion 21e to the blowing air passage side end portion 21f. Form.
  • the flow of the airflow flowing on the facing surface 18a becomes smooth, and in particular, an airflow flowing smoothly in the blowout air passage 11 is obtained, and the ventilation resistance can be reduced.
  • the shape of the facing surface 18a is not limited to the change of the distance M such as ln11, ln12, and ln13, and the shape of the facing surface 18a may be changed in any way in the rotation axis direction AX.
  • the shape of the facing surface 18a viewed from the rotation axis direction AX may be linearly and smoothly changed from the side wall side end 21e to the blowout air channel side end 21f, or may be changed stepwise and curved. It's okay. However, at any position in the rotational axis direction AX, the distance M on the side closer to the blowout air passage side end 21f is longer or the same as that on the side closer to the side wall end 21e at that position.
  • the shape of the surface 18a may be changed.
  • the distance M from the fan outer peripheral portion 8b does not decrease from the side wall side end portion 21e toward the blowing air passage side end portion 21f.
  • the side wall side end portion 21e of the opposing surface 18a is configured to obtain a higher collision pressure than the blowout air passage side end portion 21f, the collision wall of the airflow blown from the fan extension 8a The airflow that does not collide with the air 18 flows smoothly toward the blowing air passage 11.
  • blowing air passage side end portion 21f is configured to have a round shape instead of a corner portion, the air flow is not disturbed or a vortex is formed by the corner portion, so that the air flow is smoothly downstream of the blowing air passage 11. Increase in flow and draft resistance can be prevented.
  • the shape of the facing surface 18a in the rotation axis direction AX may not be the same at each position in the depth direction AY.
  • a shape in which a large amount of airflow directed toward the blowout air passage 11 may be obtained, such as a straight line ln11 illustrated in FIG. 22 and a curve ln13 illustrated in FIG.
  • the collision wall 18 may be formed integrally with the housing constituting the container of the indoor unit 1 or as a separate body, for example, fixed to the inside of the side wall 30 by bonding, claw fixing, screw fixing, or the like. It may be configured. And the shape should just be comprised so that the airflow which blown off from the both ends of the left-right direction of the once-through fan 8 may collide, and the energy of a wind speed may be converted into the energy of a pressure.
  • the fan extension portion 8a is blown out by the end region of the stabilizer 9 facing the fan extension portion 8a, the end region of the rear guide portion 10, and the collision wall 18 connecting them.
  • the example which comprises the wall structure which has the opposing surface 18a provided substantially along the outer peripheral part of the fan extension part 8a so as to oppose the airflow to be performed was shown.
  • a wall structure may be configured by an integral member different from the stabilizer 9 and the rear guide portion 10.
  • the above-described wall structure provided in correspondence with the fan extension portion 8a in the first to third embodiments in which the left and right widths of the stabilizer 9 and the rear guide portion 10 are the same as the left and right widths of the air outlet 3
  • the structure corresponding to is configured by an integral member, and this is provided inside the side wall 30 of the indoor unit 1. Even in this case, the same effects as those shown in the first to third embodiments can be obtained.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Abstract

La présente invention se rapporte à un appareil de conditionnement d'air avec lequel il est possible d'empêcher une inversion de la circulation de l'air intérieur provenant de l'intérieur et à travers l'orifice d'évacuation agencé à l'intérieur de l'appareil de conditionnement d'air au niveau des deux extrémités dans le sens de la longueur de l'orifice d'évacuation d'une unité intérieure de l'appareil de conditionnement d'air et avec lequel il est possible d'empêcher une augmentation de la perte d'énergie, ce qui permet de réduire la consommation d'énergie et de réduire le bruit. La construction est telle que la longueur d'un ventilateur à écoulement transversal (8) dans la direction (AX) de l'axe de rotation est plus importante que la longueur de l'orifice d'évacuation (3) dans le sens longitudinal et que le ventilateur à écoulement transversal (8) présente des extensions de ventilateur (8a) qui s'étendent vers l'extérieur dans la direction (AX) de l'axe de rotation depuis les deux extrémités de l'orifice d'évacuation (3). En outre, le corps principal de l'unité intérieure est pourvu d'une paroi de collision (18) que vient heurter l'écoulement d'air sorti des extensions (8a) du ventilateur. En outre, une surface opposée (18a) de la paroi de collision (18) est construite de telle sorte que, selon une coupe transversale perpendiculaire à l'axe de rotation (17), la distance (Mb) entre la partie d'extrémité (19b) côté guide arrière de la surface opposée (18a) et la partie circonférentielle externe (8b) du ventilateur soit plus importante que la distance (Ma) entre la partie d'extrémité (19a) côté stabilisateur de la surface opposée (18a) et la partie circonférentielle externe (8b) du ventilateur.
PCT/JP2012/002177 2011-12-02 2012-03-29 Appareil de conditionnement d'air WO2013080395A1 (fr)

Priority Applications (1)

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JP2011-264476 2011-12-02
JP2011264476 2011-12-02

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016145692A (ja) * 2015-02-09 2016-08-12 シャープ株式会社 空気調和機
EP3640548B1 (fr) * 2017-12-08 2023-07-26 Gree Electric Appliances, Inc. of Zhuhai Climatiseur

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7329969B2 (ja) * 2019-06-06 2023-08-21 シャープ株式会社 空気調和機
JP7271356B2 (ja) * 2019-07-19 2023-05-11 シャープ株式会社 送風装置、空気調和機

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5487405U (fr) * 1977-12-02 1979-06-20
JPS56139890U (fr) * 1980-03-24 1981-10-22
JPS57182295U (fr) * 1982-04-08 1982-11-18
JPS6127443A (ja) * 1984-07-19 1986-02-06 Matsushita Electric Ind Co Ltd 流れ方向制御装置
JPH08121396A (ja) * 1994-10-28 1996-05-14 Matsushita Electric Ind Co Ltd 送風機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5487405U (fr) * 1977-12-02 1979-06-20
JPS56139890U (fr) * 1980-03-24 1981-10-22
JPS57182295U (fr) * 1982-04-08 1982-11-18
JPS6127443A (ja) * 1984-07-19 1986-02-06 Matsushita Electric Ind Co Ltd 流れ方向制御装置
JPH08121396A (ja) * 1994-10-28 1996-05-14 Matsushita Electric Ind Co Ltd 送風機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016145692A (ja) * 2015-02-09 2016-08-12 シャープ株式会社 空気調和機
EP3640548B1 (fr) * 2017-12-08 2023-07-26 Gree Electric Appliances, Inc. of Zhuhai Climatiseur

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