WO2022195717A1 - Boîtier de volute, et dispositif de soufflage d'air et dispositif de climatisation équipés dudit boîtier de volute - Google Patents

Boîtier de volute, et dispositif de soufflage d'air et dispositif de climatisation équipés dudit boîtier de volute Download PDF

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Publication number
WO2022195717A1
WO2022195717A1 PCT/JP2021/010593 JP2021010593W WO2022195717A1 WO 2022195717 A1 WO2022195717 A1 WO 2022195717A1 JP 2021010593 W JP2021010593 W JP 2021010593W WO 2022195717 A1 WO2022195717 A1 WO 2022195717A1
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WO
WIPO (PCT)
Prior art keywords
region
cross
scroll
flow fan
air
Prior art date
Application number
PCT/JP2021/010593
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English (en)
Japanese (ja)
Inventor
奈穂 安達
拓矢 寺本
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 CN202180095450.1A priority Critical patent/CN116997725A/zh
Priority to EP21931469.7A priority patent/EP4310341A4/fr
Priority to US18/260,646 priority patent/US20240068486A1/en
Priority to PCT/JP2021/010593 priority patent/WO2022195717A1/fr
Priority to JP2023506439A priority patent/JPWO2022195717A1/ja
Publication of WO2022195717A1 publication Critical patent/WO2022195717A1/fr

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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
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/028—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by air supply means, e.g. fan casings, internal dampers or ducts
    • 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
    • F04D29/4226—Fan casings
    • 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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0025—Cross-flow or tangential fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0057—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in or on a wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers

Definitions

  • the present disclosure relates to a scroll casing that houses a fan, and a blower and an air conditioner that include this scroll casing.
  • the blower includes a cross-flow fan having a plurality of annularly arranged blades, and a blower section having a scroll casing that houses the cross-flow fan.
  • the air blowing section forms an air passage with a scroll casing, and blows air by rotating a cross-flow fan in this air passage.
  • the scroll casing of this type of air blowing section has a scroll section that spirally guides the airflow generated by the cross-flow fan. For example, see Patent Document 1).
  • the logarithmic spiral shape of the scroll casing of Patent Document 1 is the following shape when the scroll casing is viewed in a cross section perpendicular to the rotation axis of the cross-flow fan.
  • the logarithmic spiral shape is a shape in which the distance between the center of rotation of the cross-flow fan and the scroll casing increases continuously at a constant rate of change from the start of winding to the end of winding.
  • noise is reduced by forming the scroll casing into the shape described above.
  • Patent Document 1 The scroll casing of Patent Document 1 is a technology that focuses on reducing noise, and there is room for improvement in terms of reducing fan input.
  • An object of the present disclosure is to provide a scroll casing capable of reducing fan input, and an air blower and an air conditioner including the scroll casing. .
  • a scroll casing according to the present disclosure is a scroll casing that accommodates a cross-flow fan and forms an air passage, and has an upstream end of the scroll casing that is closest to the cross-flow fan, and an upstream side of the air passage.
  • the area from the upstream end of the scroll portion to the downstream end of the scroll portion is divided into three regions in the flow direction of the air current flowing through the air passage, and the three regions flow through the scroll portion.
  • the distance between the center of rotation of the cross-flow fan and the scroll portion expands at different rates from the upstream end to the downstream end of the scroll portion. are the first region, the second region and the third region in order from the upstream side, the change rate of the second region is the smallest.
  • a blower device includes the scroll casing described above and a cross-flow fan housed in the scroll casing.
  • An air conditioner includes the blower described above, a housing that houses the blower, and a heat exchanger arranged at a position through which the airflow generated by the blower passes.
  • the amount of air blown out from the blades in the second region can be reduced, and as a result, the torque applied to the blades in the second region can be reduced, and the fan input can be reduced.
  • FIG. 1 is a schematic cross-sectional view of an air conditioner provided with a scroll casing according to Embodiment 1;
  • FIG. 1 is a schematic cross-sectional view of an air blower according to Embodiment 1;
  • FIG. 5 is a diagram showing the shape of the scroll casing according to Embodiment 1 in comparison with the conventional one;
  • FIG. 5 is a graph showing a relationship between a casing position and a distance L in the scroll casing according to Embodiment 1, in comparison with the conventional scroll casing.
  • FIG. 5 is a diagram showing the air volume distribution in the blowing region of a cross-flow fan when a conventional scroll casing is applied to a wall-mounted air conditioning indoor unit.
  • FIG. 10 is a diagram showing the fan input distribution in the blowout region of the cross-flow fan when the conventional scroll casing is applied to the wall-mounted air conditioning indoor unit;
  • FIG. 5 is a diagram showing the air volume distribution blown out from between the blades of the blowing region of the cross-flow fan in comparison with the conventional one when the scroll casing according to the first embodiment is applied to the wall-mounted air conditioning indoor unit.
  • FIG. 5 is a diagram showing fan input distribution in the blowing region of the cross-flow fan in comparison with the conventional one when the scroll casing according to Embodiment 1 is applied to the wall-mounted air conditioning indoor unit.
  • FIG. 10 is a schematic diagram showing the flow of airflow at low air volume when a conventional scroll casing is applied to a wall-mounted air conditioning indoor unit.
  • Embodiment 1 is a schematic cross-sectional view of an air conditioner provided with a scroll casing according to Embodiment 1.
  • the air conditioner 100 has a heat exchanger 10, an air blower 20 that generates an airflow and blows air to the heat exchanger 10, and a housing 50 that houses them.
  • a suction port 51 for sucking air into the housing 50 is formed on the upper surface of the housing 50 .
  • a blowout port 52 for blowing air from inside the housing 50 is formed in the lower front portion of the housing 50 .
  • the blower outlet 52 is provided with a wind direction plate 53 for freely changing the direction of the airflow blown out from the blower outlet 52 .
  • the heat exchanger 10 is arranged upstream of the in-housing channel from the inlet 51 to the outlet 52 , and the air blower 20 is arranged downstream.
  • the air conditioner 100 sucks the airflow generated by driving the blower 20 into the housing 50 from the suction port 51, exchanges the heat of the sucked airflow with the refrigerant in the heat exchanger 10, and then blows it into the room from the blowout port 52.
  • the indoor temperature is adjusted by letting the air out.
  • the term "upstream” in the following description means the upstream of the airflow in the air conditioner 100, and the term “downstream” means the downstream of the airflow in the air conditioner 100.
  • Dotted arrows in FIG. 1 indicate airflow in the air conditioner 100 .
  • FIG. 1 shows an example in which the air conditioner is a wall-mounted air conditioning indoor unit, it is not limited to this, and may be a ceiling-suspended air conditioning indoor unit, for example. .
  • the blower device 20 has a cross-flow fan 30 that generates an airflow, and a blower section 40 that houses the cross-flow fan 30 .
  • the cross-flow fan 30 includes a plurality of blades 31 arranged in an annular shape around the rotation center O of the rotating shaft, and a support plate (not shown) on which the plurality of blades 31 are installed and which integrally supports the plurality of blades 31. , are stacked in the rotation axis direction.
  • the cross-flow fan 30 rotates in the direction of the solid line arrow in FIG. 1, sucks the airflow from between the blades 31 on the heat exchanger 10 side, and blows the airflow from between the blades 31 on the scroll casing 41 side of the air blower 40, which will be described later. is.
  • the suction area 70 for sucking the airflow in the cross-flow fan 30 is located in the heat exchanger 10 in which the entire circumference of the cross-flow fan 30 is divided into two parts, one on the heat exchanger 10 side (front side) and the other on the air blowing section 40 side (back side). side (front side) area.
  • the blowing area 80 from which the cross-flow fan 30 blows air is the blowing area of the cross-flow fan 30, which is divided into two parts, one on the heat exchanger 10 side (front side) and the other on the blowing section 40 side (back side). This is an area on the part 40 side (back side).
  • a blowout start position S indicated by a dot circle in FIG. 1 indicates the position of the upstream end of the circumferential range of the blowout region 80 .
  • a blowout end position E indicated by a dot circle in FIG. 1 indicates the position of the downstream end of the circumferential range of the blowout region.
  • the blower section 40 has a scroll casing 41 , a rear guide 42 , side walls 43 and a discharge section 44 .
  • the scroll casing 41 accommodates the cross-flow fan 30 and forms an air passage 45 .
  • the scroll casing 41 straightens the air blown out from the cross-flow fan 30 .
  • the upstream end P ⁇ b>1 of the scroll casing 41 is the closest approach point to the cross-flow fan 30 in the scroll casing 41 .
  • a downstream end P ⁇ b>2 of the scroll casing 41 forms part of the peripheral wall of the outlet 52 of the housing 50 .
  • the scroll casing 41 has a scroll portion 41a and a discharge portion 41b.
  • the scroll portion 41a is a portion that guides the airflow generated by the cross-flow fan 30 in a spiral shape.
  • the scroll portion 41a extends from a height position on the upstream side of the height position of the rotation center O of the cross-flow fan 30 to a position downstream of the height position of the rotation center O, passing through the rear surface, which is a side of the cross-flow fan 30. It is a wall portion formed to extend.
  • the upstream end P1 of the scroll portion 41 a coincides with the upstream end P1 of the scroll casing 41 .
  • a downstream end P3 of the scroll portion 41a is located downstream of the height position of the rotation center O. As shown in FIG.
  • An upstream end P1 of the scroll portion 41a is a spiral winding start portion.
  • a downstream end P3 of the scroll portion 41a is a spiral winding end portion.
  • the discharge portion 41b is located downstream of the scroll portion 41a and is a portion through which the airflow that has passed through the scroll portion 41a is discharged.
  • the discharge portion 41b is a wall portion extending from the downstream end P3 of the scroll portion 41a toward the outlet 52 of the housing 50 .
  • the rear guide 42 is a wall extending upstream from the upstream end P1 of the scroll casing 41 .
  • the side wall 43 is a wall facing the scroll portion 41a with the cross-flow fan 30 interposed therebetween at a height position downstream of the height position of the rotation center O of the rotation shaft.
  • Side wall 43 is formed along the outer peripheral surface of cross-flow fan 30 .
  • a tongue portion 43a is formed at the downstream end portion of the side wall 43 as a narrowing portion for narrowing the airflow.
  • the discharge portion 44 is a wall portion extending from the tongue portion 43 a of the side wall 43 toward the discharge port of the blower portion 40 .
  • the outlet of the air blower 40 corresponds to the outlet of the air blower 20 and coincides with the outlet 52 of the housing 50 .
  • the outlet of the air blower 40 is not limited to the structure matching the outlet 52 of the housing 50, and a member that smoothly connects the outlet of the air blower 40 and the outlet 52 of the housing 50 is provided. It is good also as a structure which provided separately and connected.
  • the discharge portion 44 is formed facing the discharge portion 41 b of the scroll casing 41 .
  • the scroll portion 41 a of the scroll casing 41 and the rear guide 42 form the upstream side of the air passage 45 .
  • the discharge portion 44 and the discharge portion 41 b of the scroll casing 41 form the downstream side of the air passage 45 .
  • the downstream side of the air passage 45 is a discharge air passage 46 that guides the air flow blown out from the cross-flow fan 30 to the outside.
  • the discharge air passage 46 is an enlarged air passage whose cross-sectional area increases from upstream to downstream.
  • blower 20 In the blower device 20 , when the cross-flow fan 30 rotates, air is taken into the cross-flow fan 30 from between the blades 31 in the suction area 70 . The air taken into cross-flow fan 30 is blown radially outward from between blades 31 in blowing region 80 . The airflow blown radially outward from the cross-flow fan 30 flows along the scroll portion 41a of the scroll casing 41, is discharged to the discharge air passage 46, and is discharged from the discharge air passage 46 to the discharge port (the housing) of the blower portion 40. The air is blown into the room through the outlet 52) of 50.
  • the blower device 20 including the scroll casing 41 of Embodiment 1 has the effect of reducing fan input. A specific configuration that enables this effect will be described below.
  • FIG. 2 is a schematic cross-sectional view of the air blower according to Embodiment 1.
  • FIG. The shape of the scroll casing 41 will be described below with reference to FIG.
  • the scroll portion 41 a is divided into three regions in the direction of the air current flowing through the air passage 45 .
  • the three regions are such that the distance L between the rotation center O of the rotation shaft and the scroll portion 41a extends from the upstream end P1 to the downstream end P3 of the scroll portion 41a. It is a region that expands with different rate of change ⁇ . That is, the scroll portion 41a is composed of three regions with different change rates ⁇ .
  • these three regions are referred to as a first region A, a second region B and a third region C in order from the upstream side of the airflow.
  • the first area A, the second area B and the third area C are continuous in this order.
  • the blade 31 of the cross-flow fan 30 corresponding to the first region A is referred to as the blade 31 of the first region A.
  • the blades 31 of the cross-flow fan 30 corresponding to the first region A connect the upstream end and the downstream end of the first region A and the rotation center O when the scroll portion 41a is viewed in a cross section perpendicular to the rotation axis.
  • the blades 31 located within the fan-shaped cross-sectional area surrounded by each line and the first area A are indicated.
  • the blade 31 of the cross-flow fan 30 corresponding to the second region B is hereinafter referred to as the blade 31 of the second region B.
  • the blade 31 of the cross-flow fan 30 corresponding to the third region C is referred to as the third region C blade 31 .
  • the upstream end of the first region A is the upstream end P1 of the scroll portion 41a, which is the portion closest to the cross-flow fan 30 as described above.
  • the downstream end of the first region A coincides with the upstream end of the second region B.
  • the upstream end of the second region B is provided upstream of the height position of the rotation center O of the rotating shaft.
  • the downstream end of the second region B is provided downstream of the height position of the rotation center O of the rotating shaft.
  • the downstream end of the second region B coincides with the upstream end of the third region C.
  • the upstream end of the third region C is provided upstream of the height position of the tongue portion 43 a of the side wall 43 .
  • a downstream end of the third region C is provided downstream of the height position of the tongue portion 43 a of the side wall 43 .
  • the change rate ⁇ of the first area A is ⁇ 1
  • the change rate ⁇ of the second area B is ⁇ 2
  • the change rate ⁇ of the third area C is ⁇ 3.
  • the change rate ⁇ 2 of the second region B is set smaller than the change rate ⁇ of the first region A and the change rate ⁇ 3 of the third region C. That is, the change rate ⁇ 2 of the second area B is set to be the smallest in the scroll portion 41a.
  • the rate of change ⁇ 3 of the third region C is set to be greater than the rate of change ⁇ 1 of the first region A.
  • the scroll casing 41 satisfies the relationship ⁇ 2 ⁇ 1 ⁇ 3.
  • FIG. 3 is a diagram showing the shape of the scroll casing according to Embodiment 1 in comparison with the conventional one.
  • the dotted curved line on the back side of the scroll casing 41 indicates a conventional scroll casing.
  • a conventional scroll casing has a constant rate of change in the scroll portion.
  • FIG. 4 is a graph showing the relationship between the casing position and the distance L in the scroll casing according to Embodiment 1, in comparison with the conventional scroll casing.
  • the slope of the graph indicates the rate of change ⁇ . 3 and 4 show the case where the rate of change of the first region A is matched with the rate of change of the prior art.
  • the change rate ⁇ 2 of the second region B is the smallest, so the slope of the graph of the second region B is the same as that of the graphs of the first region A and the graph of the third region C, as shown in FIG. is smaller than the slope of Also, the slope of the graph in the second region B is smaller than in the conventional case. That is, the rate of change ⁇ 2 of the second region B is smaller than the conventional rate of change when the rate of change ⁇ 1 of the first region A is matched with the conventional rate of change. Since the rate of change ⁇ 2 of the second region B is smaller than in the conventional art, the position of the second region B in FIG.
  • the position of the second region B in the scroll portion 41a is set to a position effective for reducing the fan input. This point will be described with reference to FIGS. 5 and 6 below.
  • FIG. 5 is a diagram showing the air volume distribution in the blowing region of a cross-flow fan when a conventional scroll casing is applied to a wall-mounted air conditioning indoor unit.
  • the horizontal axis in FIG. 5 is the position within the blowing area, and the vertical axis is the air volume [m 3 /min].
  • FIG. 6 is a diagram showing the fan input distribution in the blowout region of the cross-flow fan when the conventional scroll casing is applied to the wall-mounted air conditioning indoor unit.
  • the horizontal axis in FIG. 6 is the position within the blowing area, and the vertical axis is the fan input [W].
  • the fan input [W] is the amount of input electric power calculated by multiplying the angular velocity by the torque applied to the blade at each position between the blowout start position and the blowout end position of the blowout area of the cross-flow fan.
  • the intermediate region in FIGS. 5 and 6 is the intermediate portion of the conventional scroll portion in the airflow direction.
  • This intermediate area has a relatively large air volume in the air path between the cross-flow fan and the scroll portion, and is an area where the pressure loss is high when the air currents blown out from the blades are mixed.
  • the high pressure drop results in relatively high fan input in the mid-region as shown in FIG.
  • the fan input is reduced as described below by setting the change rate ⁇ to be small in the intermediate region where the pressure loss is high. That is, in the first embodiment, the second region B is set as the intermediate region where the pressure loss is high.
  • the air blower 20 is used with the outlet 52 of the housing 50 provided at the lower front surface of the housing, and the outlet of the air blower 40 facing downward.
  • the scroll portion 41a is formed to extend in the vertical direction. Specifically, the scroll portion 41a passes from a height position upstream of the height position of the rotation center O of the cross-flow fan 30, passes through the back side of the cross-flow fan 30, and reaches the height position of the rotation center O. It is formed to extend to a height position downstream of.
  • the scroll portion 41a is formed in this way, the area where the pressure loss is high is generally around the height position of the rotation center O of the rotation shaft. Therefore, as shown in FIG. 2, the second region B is provided near the height position of the rotation center O of the rotation shaft, specifically, straddling the height position of the rotation center O of the cross-flow fan 30. .
  • the second region B of the first embodiment has a greater cross-flow than the conventional art.
  • the space between the fan 30 and the cross-flow fan 30 becomes narrower as it approaches the outer periphery of the fan 30. - ⁇ Since the space between the cross-flow fan 30 and the second region B becomes narrower, the static pressure in the space increases, and the air volume blown from the blades 31 in the second region B (hereinafter referred to as inter-blade air volume) decreases. Reduce.
  • the torque applied to the blades 31 in the second region B can be reduced, the resistance to the rotation of the cross-flow fan 30 is reduced, and the fan input necessary to drive the cross-flow fan 30 is reduced. can be reduced.
  • FIG. 7 is a diagram showing the air volume distribution blown out from between the blades of the blowing region of the cross-flow fan when the scroll casing according to Embodiment 1 is applied to the wall-mounted air conditioning indoor unit, in comparison with the conventional one.
  • the horizontal axis in FIG. 7 is the position within the blowing area, and the vertical axis is the air volume [m 3 /min].
  • FIG. 8 is a diagram showing the fan input distribution in the blowout region of the cross-flow fan when the scroll casing according to Embodiment 1 is applied to the wall-mounted air conditioning indoor unit, in comparison with the conventional one.
  • the horizontal axis of FIG. 8 is the position within the blowing area, and the vertical axis is the fan input [W].
  • the fan input [W] is the amount of input electric power calculated by multiplying the torque applied to the blades 31 at each position from the blowout start position to the blowout end position of the blowout region 80 by the angular velocity.
  • the scroll casing 41 of Embodiment 1 can reduce the amount of air blown between the blades in the second region B, in other words, the amount of air blown between the blades in the intermediate region where the conventional air volume was large.
  • the fan input based on the torque associated with the blades 31 in the second region B can be reduced compared to the conventional art.
  • the amount of air blown between the blades in the second region B is reduced, the amount of air blown out between the blades in the third region C increases as indicated by the upward arrow in FIG. Therefore, there is concern about an increase in pressure loss in the third region C.
  • the third region C has a wider space between the cross-flow fan 30 than the second region B, the pressure loss in the third region C is lower than the pressure loss in the second region B. Therefore, the amount of increase in the fan input due to the increase in the amount of air blown between the blades in the third region C is not large, and the fan input in the third region C is substantially the same as in the conventional art, as shown in FIG.
  • the change rate ⁇ 2 of the second region B is the smallest in the scroll portion 41a, so that the fan input of the entire fan can be reduced.
  • the air amount blown out between the blades in the third area C also increases for the following reasons. Specifically, since the rate of change ⁇ 3 of the third region C is greater than the rate of change ⁇ 1 of the first region A, the inter-blade blown air volume of the third region C increases.
  • the rate of change ⁇ 3 of the third region C is larger than the rate of change ⁇ 1 of the first region A, a wide space is secured between the third region C and the cross-flow fan 30, and the static pressure is low.
  • the inter-blade blown air volume in region C increases.
  • the rate of change ⁇ 1 of the first region A and the rate of change ⁇ 3 of the third region C are individually set according to the shape of the cross-flow fan 30 to be mounted.
  • the rate of change ⁇ 1 of the first region A and the rate of change ⁇ 3 of the third region C are individually set according to the installation angle of the blades 31 of the cross-flow fan 30 and the like.
  • the installation angle of the blades 31 is the angle between the center line of the blade thickness at the trailing edge side end (the downstream end in the flow direction) of the blades 31 and the circular arc connecting the trailing edges of the plurality of blades 31 . It is defined and affects the outflow angle of the airflow blown out from between the blades 31 .
  • the installation angle of the blade 31 may be defined by the angle between the center line of the thickness of the trailing edge side end of the blade 31 and a line extending in the radial direction of the impeller. It is considered that the change rate ⁇ 1 in the first region A and the change rate ⁇ 3 in the third region C have optimum values that can minimize the fan input at the set air flow rate, depending on the shape of the cross-flow fan 30 . Therefore, by setting the rate of change ⁇ 1 of the first area A and the rate of change ⁇ 3 of the third area C to optimum values, it is possible to configure an optimum scroll casing shape that can minimize the fan input at the set air volume.
  • the amount of airflow passing through the housing 50 may become low due to the accumulation of dust or the like on the suction port 51 of the housing 50, for example.
  • the operation of the scroll casing 41 when the air volume is low will be described below.
  • the rate of change ⁇ 1 of the first region A is greater than the rate of change ⁇ 2 of the second region B, so that the blowing region of the cross-flow fan 30 can be prevented from moving in the counter-rotational direction. , as a result, the effect of reducing the fan input is obtained. This point will be described in comparison with a conventional scroll casing in which the rate of change is constant.
  • FIG. 9 is a schematic diagram showing the flow of air when the air volume is low when a conventional scroll casing is applied to a wall-mounted air conditioning indoor unit.
  • the conventional scroll casing 410 cannot overcome the pressure loss in the discharge air passage 46, and the flow tends toward the scroll casing 410 side (back side). becomes.
  • blowout area 800 of cross-flow fan 300 is directed in the counter-rotational direction. That is, when FIG. 9 and FIG. 1 are compared, the blowout start position S and blowout end position E in FIG. moving in the direction of rotation.
  • the blowing area 800 of the cross-flow fan 300 moves in the counter-rotational direction, so that the following circulating flow is generated at the blowing end position E.
  • the airflow blown out from between the blades 310 in the blowing region of the cross-flow fan 300 flows back from the blowout port 520 toward the tongue portion 430a, passes through the gap between the tongue portion 430a and the cross-flow fan 300, and returns to the suction region 700 of the cross-flow fan 30.
  • circulating flow (arrow 61 in FIG. 9). Due to the occurrence of such a circulating flow, the required fan input increases when trying to secure the set air volume.
  • the change rate ⁇ 1 in the first region A is greater than the change rate ⁇ 2 in the second region B, so the inter-blade air volume in the first region A (see FIG. 2) can be secured.
  • the blowing region 800 of the cross-flow fan 300 can be suppressed from going in the counter-rotational direction when the air volume is low. Therefore, the flow from cross-flow fan 30 toward rear guide 420 can be suppressed. As a result, it is possible to reduce the loss caused by the flow from the cross-flow fan 30 toward the rear guide 420 side, and to suppress the increase in the fan input.
  • the inter-blade blowout flow rate in the third region C is increased, so that the following effect (C) can be obtained when the air flow rate is low.
  • C As the flow rate of air blown between the blades in the third region C increases, the airflow from the discharge air passage 46 toward the outlet 52 increases. Therefore, when the air volume is low, the backflow from the outlet 52 toward the tongue portion 43a can be suppressed, and the circulation flow toward the suction area 70 of the cross-flow fan 30 can be reduced. As a result, fan input can be reduced.
  • the scroll casing 41 is applied to a wall-mounted air conditioner indoor unit, but similar effects can be obtained when it is applied to other types of indoor units.
  • the scroll casing 41 of Embodiment 1 is a scroll casing 41 that accommodates the cross-flow fan 30 and forms an air passage 45 .
  • the scroll casing 41 includes a scroll portion 41a that has an upstream end P1 that is closest to the cross-flow fan 30 in the scroll casing 41 and that forms the upstream side of the air passage.
  • the area from the upstream end P1 of the scroll portion 41a to the downstream end P3 of the scroll portion 41a is divided into three regions in the flow direction of the air current flowing through the air passage 45. As shown in FIG.
  • the three regions are the distance between the rotation center of the cross-flow fan 30 and the scroll portion 41a from the upstream end P1 to the downstream end P3 of the scroll portion 41a when the scroll portion 41a is viewed in a cross section orthogonal to the rotation axis of the cross-flow fan. are regions that expand at different rates of change ⁇ .
  • the change rate ⁇ 2 of the second region B is the smallest.
  • the second region B is a region in which pressure loss is relatively high when the airflows blown out from the blades 31 are mixed. Fan input can be reduced.
  • the rate of change ⁇ 1 in the first region A and the rate of change ⁇ 3 in the third region C are individually set according to the shape of the cross-flow fan 30 so that the fan input is minimized at the set air volume.
  • the scroll casing 41 according to the first embodiment satisfies ⁇ 2 ⁇ 1 ⁇ 3, where ⁇ 1 is the rate of change in the first region A, ⁇ 2 is the rate of change in the second region B, and ⁇ 3 is the rate of change in the third region C. fulfill the relationship.
  • the rate of change ⁇ 2 of the second region B By setting the rate of change ⁇ 2 of the second region B to be the smallest in the scroll portion 41a in this manner, the air volume blown out from the blades 31 of the second region B can be reduced. Since the space between the second region B and the cross-flow fan 30 is a region where the pressure loss tends to be relatively high, by reducing the air volume in this region, the torque applied to the blades 31 in the second region B can be reduced. High input reduction effect. As a result, the fan input of the entire fan can be reduced.
  • the inter-blade air volume in the third region C increases.
  • the effects (A), (B) and (C) described above are obtained by increasing the inter-blade blown air volume in the third region C.
  • the inter-blade air volume in the first region A (see FIG. 2) can be secured, and when the air volume is low, the cross-flow fan 30 can be suppressed from going in the counter-rotational direction. Therefore, the flow from cross-flow fan 30 toward rear guide 42 can be suppressed. As a result, it is possible to reduce the loss caused by the flow from the cross-flow fan 30 toward the rear guide 42 side, and to suppress the increase in the fan input.
  • the scroll portion 41a passes through the side of the cross-flow fan 30 from a height position on the upstream side of the airflow relative to the height position of the rotation center O of the cross-flow fan 30, It is formed extending from the height position of O to a height position on the downstream side of the airflow.
  • the second area B is provided so as to straddle the height position of the rotation center O of the cross-flow fan 30 .
  • the scroll casing 41 of Embodiment 1 has a side wall 43 provided at a position facing the scroll casing 41 with the cross-flow fan 30 interposed therebetween. is provided on the upstream side of the height position where is located.
  • the blower device 20 of Embodiment 1 includes the scroll casing 41 and the cross-flow fan 30 described above. Further, the air conditioner 100 of Embodiment 1 includes the blower 20, the housing 50 that houses the blower 20, and the heat exchanger arranged at a position through which the airflow generated by the blower 20 passes. 10 and.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un boîtier de volute qui reçoit un ventilateur tangentiel et qui forme un passage de ventilation, ledit boîtier de volute comprenant une partie de volute, dont l'extrémité amont est le point du boîtier de volute qui est le plus proche du ventilateur tangentiel, et qui forme la partie côté amont du passage de ventilation. La partie de volute est divisée en trois régions de l'extrémité amont à l'extrémité aval de la partie de volute, dans la direction dans laquelle un courant d'air s'écoule dans le passage de ventilation. Dans les trois régions, la distance entre le centre de rotation du ventilateur tangentiel et la partie de volute augmente à des taux de changement différents de l'extrémité amont à l'extrémité aval de la partie de volute lorsque la partie de volute est vue dans une section transversale orthogonale à l'axe de rotation du ventilateur tangentiel. Lorsque les trois régions sont définies comme une première région, une deuxième région et une troisième région dans l'ordre depuis le côté amont, le taux de changement dans la deuxième région est le plus faible.
PCT/JP2021/010593 2021-03-16 2021-03-16 Boîtier de volute, et dispositif de soufflage d'air et dispositif de climatisation équipés dudit boîtier de volute WO2022195717A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN202180095450.1A CN116997725A (zh) 2021-03-16 2021-03-16 涡壳、具备该涡壳的送风装置以及空调装置
EP21931469.7A EP4310341A4 (fr) 2021-03-16 2021-03-16 Boîtier de volute, et dispositif de soufflage d'air et dispositif de climatisation équipés dudit boîtier de volute
US18/260,646 US20240068486A1 (en) 2021-03-16 2021-03-16 Scroll casing, and air-sending device and air-conditioning apparatus which include the same
PCT/JP2021/010593 WO2022195717A1 (fr) 2021-03-16 2021-03-16 Boîtier de volute, et dispositif de soufflage d'air et dispositif de climatisation équipés dudit boîtier de volute
JP2023506439A JPWO2022195717A1 (fr) 2021-03-16 2021-03-16

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2021/010593 WO2022195717A1 (fr) 2021-03-16 2021-03-16 Boîtier de volute, et dispositif de soufflage d'air et dispositif de climatisation équipés dudit boîtier de volute

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WO2022195717A1 true WO2022195717A1 (fr) 2022-09-22

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PCT/JP2021/010593 WO2022195717A1 (fr) 2021-03-16 2021-03-16 Boîtier de volute, et dispositif de soufflage d'air et dispositif de climatisation équipés dudit boîtier de volute

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Country Link
US (1) US20240068486A1 (fr)
EP (1) EP4310341A4 (fr)
JP (1) JPWO2022195717A1 (fr)
CN (1) CN116997725A (fr)
WO (1) WO2022195717A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57134388U (fr) * 1981-02-16 1982-08-21
JPS61118597A (ja) * 1984-10-30 1986-06-05 Mitsubishi Electric Corp 貫流型送風機
JPH0274599U (fr) * 1988-11-25 1990-06-07
JPH07305695A (ja) * 1995-04-14 1995-11-21 Sanyo Electric Co Ltd 空気調和機
JP2000220592A (ja) 1999-01-28 2000-08-08 Pacific Ind Co Ltd クロスフローファンのケーシング
CN206035853U (zh) * 2016-08-17 2017-03-22 青岛海尔空调器有限总公司 用于空调器的贯流风机

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5943878A (en) * 1998-05-22 1999-08-31 American Standard Inc. Tangential fan scroll and discharged diffuser design
KR100337287B1 (ko) * 1999-07-28 2002-05-17 윤종용 원심 송풍기
CN104696281A (zh) * 2013-12-04 2015-06-10 珠海格力电器股份有限公司 风机及具有该风机的空调器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57134388U (fr) * 1981-02-16 1982-08-21
JPS61118597A (ja) * 1984-10-30 1986-06-05 Mitsubishi Electric Corp 貫流型送風機
JPH0274599U (fr) * 1988-11-25 1990-06-07
JPH07305695A (ja) * 1995-04-14 1995-11-21 Sanyo Electric Co Ltd 空気調和機
JP2000220592A (ja) 1999-01-28 2000-08-08 Pacific Ind Co Ltd クロスフローファンのケーシング
CN206035853U (zh) * 2016-08-17 2017-03-22 青岛海尔空调器有限总公司 用于空调器的贯流风机

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP4310341A4

Also Published As

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JPWO2022195717A1 (fr) 2022-09-22
CN116997725A (zh) 2023-11-03
US20240068486A1 (en) 2024-02-29
EP4310341A1 (fr) 2024-01-24
EP4310341A4 (fr) 2024-06-05

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