WO2021152731A1 - 送風機及び空気調和装置 - Google Patents

送風機及び空気調和装置 Download PDF

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Publication number
WO2021152731A1
WO2021152731A1 PCT/JP2020/003206 JP2020003206W WO2021152731A1 WO 2021152731 A1 WO2021152731 A1 WO 2021152731A1 JP 2020003206 W JP2020003206 W JP 2020003206W WO 2021152731 A1 WO2021152731 A1 WO 2021152731A1
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WIPO (PCT)
Prior art keywords
impeller
main plate
blower
casing
rotating shaft
Prior art date
Application number
PCT/JP2020/003206
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
皓亮 宮脇
智哉 福井
健一 迫田
翔太 森川
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 JP2021573694A priority Critical patent/JP7282215B2/ja
Priority to PCT/JP2020/003206 priority patent/WO2021152731A1/ja
Publication of WO2021152731A1 publication Critical patent/WO2021152731A1/ja

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Classifications

    • 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • 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
    • F24F1/0022—Centrifugal or radial fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0025—Cross-flow or tangential fans

Definitions

  • the present disclosure relates to a blower and an air conditioner including a blower.
  • blower mounted on an air conditioner a configuration is known in which disks are provided on both side surfaces of a cross flow fan, and an orifice covered with a scroll casing is provided on the outside of the disk as a suction port of the cross flow fan.
  • the blower described in Patent Document 1 is provided with a communication hole in the vicinity of the disk in order to connect the first impeller inside the scroll casing and the second impeller outside the scroll casing.
  • the inside of the scroll casing is boosted by the first impeller, while the suction surface of the second impeller outside the scroll casing is not boosted, so that the airflow flows through the communication hole of the scroll casing. Leakage from the inside to the outside, reducing the energy-saving performance of the blower.
  • a separate rotary motor must be provided for each impeller, the blower becomes larger, and the unit of the air conditioner on which the blower is mounted also becomes larger.
  • the present disclosure has been made against the background of the above-mentioned problems, and provides a blower that realizes high energy-saving performance and suppresses the increase in size, and an air conditioner equipped with such a blower. Is.
  • the blower according to the present disclosure includes a first centrifugal fan and a cross flow fan provided coaxially with the rotation shaft, and the first centrifugal fan is housed in the first casing and the first casing.
  • the first impeller has a first impeller, and the first impeller has a first rotating main plate that can rotate about the rotation axis, and a plurality of first plates provided on the first rotating main plate.
  • the first casing is provided at one end of both ends in the direction of the rotation axis, and a first suction hole for sucking airflow is formed. It has one side plate, a first fixed main plate provided at the other end and formed with a communication hole, and a first peripheral wall facing the outer periphery of the first impeller.
  • the cross-flow fan is provided on a second impeller provided on the surface of the first rotating main plate opposite to the surface on which the first blade is provided, and on the outer circumference of rotation of the second impeller.
  • the tongue portion is provided with a tongue portion arranged and a scroll casing arranged along the rotation outer periphery at a position facing the tongue portion with the second impeller sandwiching the second impeller, and the tongue portion is provided on the rotation outer periphery.
  • a suction region for sucking airflow is formed in one region of the region sandwiched between the scroll casing and the scroll casing, and a blowout region for blowing airflow is formed in the other region.
  • One end of both ends of the rotating shaft in the axial direction is connected to the surface of the first rotating main plate opposite to the surface on which the first blade is provided, and the first impeller Is configured so that the diameter of the second impeller is smaller than the diameter of the second impeller.
  • the blade diameter of the first impeller of the first centrifugal fan is smaller than the blade diameter of the second impeller of the first cross flow fan. Therefore, when the blower is operated, the airflow is boosted on the side corresponding to the suction region of the first cross-flow fan in the communication hole formed in the first fixed main plate of the first casing of the first centrifugal fan. As a result, the leakage of the airflow from the first centrifugal fan to the first cross current fan through the communication hole is reduced. That is, the leakage of the air flow through the communication hole is reduced without providing a motor for each of the first impeller of the first centrifugal fan and the second impeller of the first cross flow fan. Therefore, according to the present disclosure, it is possible to improve the energy-saving performance while suppressing the increase in size of the blower.
  • FIG. 5 is a perspective perspective view of an indoor unit unit including a blower according to the first embodiment. It is a schematic diagram which shows the structural example of the air conditioner provided with the blower which concerns on Embodiment 1. FIG. It is a vertical cross-sectional view of the blower of a conventional example. It is a graph which shows the performance improvement effect of Embodiment 1.
  • FIG. 1 It is a vertical sectional view of the blower which concerns on the modification 1 of Embodiment 1.
  • FIG. It is a vertical sectional view of the blower which concerns on the modification 2 of Embodiment 1.
  • FIG. It is a vertical sectional view of the blower which concerns on the modification 3 of Embodiment 1.
  • FIG. It is a vertical sectional view of the blower which concerns on the modification 4 of Embodiment 1.
  • FIG. It is a vertical sectional view of the blower which concerns on the modification 5 of Embodiment 1.
  • FIG. It is a vertical sectional view of the blower which concerns on the modification 6 of Embodiment 1.
  • FIG. It is a perspective view of the blower which concerns on Embodiment 2.
  • FIG. 2 It is a vertical sectional view of the blower which concerns on the modification 2 of Embodiment 1.
  • FIG. It is a vertical sectional view of the blower which concerns on the modification 3 of Embodiment 1.
  • FIG. It is a
  • FIG. 2 It is a cross-sectional view of the blower which concerns on the modification of Embodiment 2. It is sectional drawing of the blower which concerns on Embodiment 3.
  • FIG. It is sectional drawing of the blower which concerns on Embodiment 3.
  • FIG. It is a cross-sectional view of the blower which concerns on the modification of Embodiment 3.
  • FIG. It is sectional drawing of the blower which concerns on Embodiment 4.
  • FIG. It is sectional drawing of the blower which concerns on the modification of Embodiment 4.
  • FIG. It is sectional drawing of the blower which concerns on Embodiment 5.
  • FIG. It is a vertical sectional view of the blower which concerns on the modification of Embodiment 5.
  • blower and air conditioner according to the present disclosure will be described with reference to the drawings.
  • the present disclosure is not limited to the following embodiments, and can be variously modified without departing from the gist of the present disclosure.
  • the present disclosure includes all combinations of configurations that can be combined among the configurations shown in the following embodiments.
  • the blower and the air conditioner shown in the drawings show an example of the equipment to which the blower and the air conditioner of the present disclosure are applied, and the blower and the air conditioner shown in the drawings provide the applicable equipment of the present disclosure. It is not limited.
  • terms indicating directions for example, “top”, “bottom”, “right”, “left”, “front”, “rear”, etc.) are appropriately used for ease of understanding.
  • FIG. 1 is a perspective view of the blower according to the first embodiment.
  • FIG. 2 is a vertical cross-sectional view of the blower according to the first embodiment.
  • FIG. 3 is a cross-sectional view of the blower according to the first embodiment.
  • FIG. 4 is a cross-sectional view of the blower according to the first embodiment.
  • FIG. 2 is a view showing the blower 10 cut from the surface PA of FIG. 1 from above.
  • the surface PA is a horizontal plane including a rotation shaft 20 described later.
  • FIG. 3 is a view cut along the plane PB of FIG. 1, and corresponds to a DD cross-sectional view of FIG.
  • FIG. 4 is a view cut by the surface PC of FIG. 1, and corresponds to a cross-sectional view taken along the line EE of FIG.
  • the plane PB and the plane PC are planes on which the rotation axes 20 are orthogonal to each other.
  • the blower 10 includes a first centrifugal fan 11 and a cross flow fan 12.
  • the first centrifugal fan 11 and the cross flow fan 12 are provided coaxially. That is, the first centrifugal fan 11 and the cross flow fan 12 are provided so as to rotate about the rotation shaft 20.
  • the first centrifugal fan 11 is a single-suction multi-blade fan, and has a first impeller 31 and a first casing 8.
  • the first impeller 31 has a first rotating main plate 21 and a plurality of first blades 211 erected on one surface of the first rotating main plate 21.
  • the first casing 8 has a first fixed main plate 1, a first side plate 2, and a first peripheral wall 3.
  • the first fixed main plate 1 and the first side plate 2 face each other in the direction of the rotation shaft 20 of the first centrifugal fan 11 and the cross flow fan 12.
  • the first peripheral wall 3 connects the outer edge portion of the first fixed main plate 1 and the outer edge portion of the first side plate 2 and faces the outer periphery of the first impeller 31.
  • the first side plate 2 is formed with a first suction hole 4 for sucking airflow.
  • a first communication hole 5 is formed in the first fixed main plate 1.
  • the first rotating main plate 21 is located in the first communication hole 5 of the first fixed main plate 1.
  • the cross flow fan 12 has a second impeller 32, a tongue portion 6, and a scroll casing 7.
  • the second impeller 32 is provided coaxially with the first impeller 31.
  • the second impeller 32 is connected to the surface of the first rotating main plate 21 opposite to the surface on which the plurality of first blades 211 of the first impeller 31 are erected.
  • the scroll casing 7 has a base portion 71 and an extension portion 72.
  • the base 71 is along a substantially half portion in the circumferential direction on the outer circumference of rotation of the second impeller 32.
  • the extending portion 72 is continuous with one end of the base portion 71 and extends in a direction away from the outer circumference of the second impeller 32.
  • the tongue portion 6 is provided close to a part of the portion where the base portion 71 does not follow on the rotational outer circumference of the second impeller 32.
  • the tongue portion 6 and the base portion 71 of the scroll casing 7 face each other.
  • a suction region 22 in which airflow is sucked is formed in one region of the region sandwiched between the tongue portion 6 and the scroll casing 7 on the rotational outer circumference of the second impeller 32, and the other region.
  • a blowout region 23 is formed in which the airflow is blown out.
  • the motor 13 is provided on the side of both ends of the cross flow fan 12 in the direction of the rotation shaft 20 opposite to the end where the first centrifugal fan 11 is located.
  • the blower 10 is configured so that the first centrifugal fan 11 and the cross flow fan 12 rotate as the motor 13 rotates.
  • the blade diameter Ds of the first impeller 31 is smaller than the blade diameter Dc of the second impeller 32. That is, the diameter of the first impeller 31 is smaller than the diameter of the second impeller 32.
  • FIG. 3 when the inside of the blower 10 is viewed from the side of the first centrifugal fan 11 in the axial direction of the rotating shaft 20, a part of the tongue portion 6 of the cross flow fan 12 and a part of the scroll casing 7 Is visible, and the second impeller 32 is not visible.
  • the second impeller 32, the first fixed main plate 1, and the first rotating main plate 21 are viewed through in the direction of the rotating shaft 20, the second impeller 32 is covered with the first fixed main plate 1. There is.
  • the second impeller 32 when the inside of the blower 10 is viewed from the side of the first centrifugal fan 11 in the axial direction of the rotating shaft 20, the second impeller 32 is covered with the first fixed main plate 1. It is configured, but not limited to this. At least a part of the second impeller 32 may be covered with the first fixed main plate 1 on the side of the suction region 22 of the second impeller 32.
  • the first fixed main plate 1 and the first rotating main plate 21 overlap each other.
  • the second impeller 32 when the second impeller 32, the first fixed main plate 1, and the first rotating main plate 21 are viewed through in the direction of the rotating shaft 20, the second impeller 32 is on the side of the suction region 22. It suffices that at least a part of the impeller 32 is covered with the first fixed main plate 1, or at least a part of the first fixed main plate 1 is covered with the first rotating main plate 21.
  • FIG. 5 shows an indoor unit 201 provided on the wall portion 203 of the indoor space 300.
  • FIG. 5 shows the internal configuration of the indoor unit 201, only the outer shell of the housing of the indoor unit 201 is shown. Further, in order to avoid complication of the drawing, some of the structures mounted on the indoor unit unit 201 are omitted in FIG. Note that FIG. 5 shows a configuration in which one blower 10 is provided in the indoor unit 201, but the present invention is not limited to this, and the indoor unit 201 is equipped with a plurality of blowers 10. May be good. As shown in FIG. 5, in the indoor unit 201, a first heat exchanger 17 is provided between the panel constituting the housing of the indoor unit 201 and the blower 10.
  • an air flow flows from the indoor space 300 to the inside of the indoor unit unit 201 through a suction port (not shown) of the indoor unit unit 201.
  • the airflow flowing into the indoor unit 201 is separated and flows to the first centrifugal fan 11 and the cross current fan 12 of the blower 10 via a structure such as the first heat exchanger 17.
  • the airflow flowing through the first centrifugal fan 11 is boosted and accelerated by the first impeller 31, and a part of the airflow flows through the first communication hole 5 to the air passage of the cross flow fan 12, and is provided by the scroll casing 7.
  • the static pressure is restored, and the indoor unit 201 is discharged from the air outlet (not shown) into the indoor space 300 and circulates.
  • the airflow flowing through the cross flow fan 12 is boosted and accelerated by the second impeller 32, partly flows into the air passage of the first centrifugal fan 11, is statically restored by the first casing 8, and is an indoor unit. It is discharged from the air outlet of the unit 201 (not shown) to the indoor space 300 and circulates.
  • the airflow is exchanged between the air passage of the first centrifugal fan 11 and the air passage of the cross flow fan 12 through the first communication hole 5 located on the outer periphery of the second impeller 32.
  • the airflow leaking to the suction region 22 of the cross flow fan 12 mainly flows to the second impeller 32.
  • the air conditioner 200 includes an indoor unit unit 201 arranged in the indoor space 300 and an outdoor unit unit 202 arranged in the outdoor space 301.
  • the outdoor unit 202 includes a compressor 15, a four-way valve 16, a second heat exchanger 171 and a blower 18, and a throttle device 19.
  • the first heat exchanger 17 of the indoor unit unit 201 functions as an evaporator during the cooling operation and as a condenser during the heating operation.
  • the second heat exchanger 171 of the outdoor unit unit 202 functions as a condenser during the cooling operation and as an evaporator during the heating operation.
  • the refrigerant that has become a high-temperature and high-pressure gas in the compressor 15 flows through the four-way valve 16 to the second heat exchanger 171 mounted on the outdoor unit 202, dissipates heat to the outdoor air, and is a liquid phase refrigerant or a liquid main component. It becomes a refrigerant.
  • the liquid phase refrigerant or the liquid-based refrigerant is depressurized by the throttle device 19 and flows to the first heat exchanger 17 of the indoor unit 201.
  • the airflow generated by the blower 10 and the low-temperature low-pressure two-phase refrigerant exchange heat return to the outdoor unit 202, and are sucked into the compressor 15 again through the four-way valve 16.
  • the compressor 15, the four-way valve 16, the first heat exchanger 17, the second heat exchanger 171 and the throttle device 19 form a heat pump.
  • the blower 10 is arranged downstream of the first heat exchanger 17 in the air flow in the indoor unit 201, but is not limited to this.
  • the blower 10 may be arranged upstream of the first heat exchanger 17. Further, even if a blower having the same configuration as the blower 10 is mounted on the outdoor unit 202 as the blower 18, the same effect can be obtained.
  • FIG. 7 is a cross-sectional view showing a conventional blower.
  • the blade diameter Dc of the second impeller 32 has the same length as the blade diameter Ds of the first impeller 31.
  • the first casing 8 covering the outer periphery of the first impeller 31 through the first communication hole 5 near the connection portion between the first impeller 31 and the second impeller 32.
  • the leakage airflow 110 to the outside of the first casing 8 increases from the inside toward the suction region 22 of the cross flow fan 12.
  • the energy given to the leaked airflow 110 by the first impeller 31 is dissipated, and the blowing performance of the first centrifugal fan 11 deteriorates.
  • the blade diameter Dc of the second impeller 32 is smaller than the blade diameter Ds of the first impeller 31, similarly, from the inside to the outside of the first casing 8 through the first communication hole 5. Due to the leakage of the airflow in the airflow, the ventilation performance deteriorates.
  • the blade diameter Dc of the second impeller 32 is larger than the blade diameter Ds of the first impeller 31. Therefore, the vicinity of the first communication hole 5 is boosted by the second impeller 32, the leakage airflow 110 from the inside of the first casing 8 to the outside of the first casing 8 is reduced, and the performance of the blower 10 is improved. do.
  • the suction region of the second impeller 32 is obtained.
  • the ventilation resistance from the inside of the first casing 8 to the outside of the first casing 8 is improved, the leaked airflow 110 is reduced, and the performance of the blower 10 is improved.
  • the second impeller 32, the first fixed main plate 1, and the first rotating main plate 21 are viewed through in the direction of the rotating shaft 20, at least a part of the first fixed main plate 1 is the first rotating main plate. It is covered with 21.
  • the ventilation resistance from the inside of the first casing 8 to the outside of the first casing 8 is improved, the leaked airflow 110 is reduced, and the performance of the blower 10 is improved.
  • FIG. 8 is a graph showing the performance improvement effect of the first embodiment.
  • the horizontal axis represents the blade diameter ratio (Dc / Ds) of the first impeller 31 and the second impeller 32
  • the vertical axis represents the performance ratio (static pressure ⁇ air volume / input).
  • the blade diameter Dc of the second impeller 32 is relative to the blade diameter Ds of the first impeller 31. Is largely configured. Therefore, the leaked airflow 110 of the blower 10 can be reduced without providing a separate rotary motor or a complicated additional mechanism. As a result, it is possible to achieve both miniaturization of the blower 10 and the air conditioner 200 on which the blower 10 is mounted and improvement of energy saving.
  • the number of blowers 10 mounted on the indoor unit 201 may be 1 or more, and the orientation of the rotating shaft 20 does not matter.
  • the heat transfer tube may have a flat shape, and the direction of the flow of the refrigerant may be horizontal or perpendicular to the rotation axis 20 of the fan.
  • the indoor unit unit 201 in FIG. 5 is illustrated by taking a wall-mounted type as an example, the form is not limited, and the indoor unit unit 201 may be a floor-standing type, a ceiling-suspended type, or a ceiling-embedded type.
  • 9 to 14 are cross-sectional views showing a modified example of the first communication hole 5 and the first rotating main plate 21.
  • 9 to 14 are cross-sectional views of the blower 10 cut along the surface PA of FIG. 1, as in FIG. 2.
  • the outer diameter of the first rotating main plate 21 is larger than that of the first communication hole 5.
  • the suction region 22 side of the second impeller 32 is seen.
  • the first fixed main plate 1 is covered with the first rotating main plate 21.
  • a groove 24 is provided in the circumferential direction of the rotating shaft 20 of the first rotating main plate 21, and the hole diameter Dh of the first communication hole 5 is the blade diameter Ds of the first impeller 31. Is smaller than Further, when the first fixed main plate 1 is viewed in the axial direction of the rotating shaft 20, the hole diameter of the first communication hole 5 is smaller than the blade diameter Dc of the second impeller 32. This configuration also reduces the leaked airflow 110 and improves the performance of the blower 10.
  • the diaphragm mechanism 25 is provided on a part or the entire circumference of the opening end of the first communication hole 5.
  • the throttle mechanism 25 is configured such that the inner diameter gradually decreases from the cross flow fan 12 toward the first centrifugal fan 11.
  • ⁇ Modification example 4> In the modified example 4 shown in FIG. 12, in addition to the throttle mechanism 25 of the modified example 3, the vanes 26 are provided at the connecting portion between the first impeller 31 and the second impeller 32. The blades 26 are provided on the outer periphery of the first rotating main plate 21 shown in FIG. With this configuration, the communication space surrounded by the outer circumference of the first rotating main plate 21, which is the connecting portion between the first impeller 31 and the second impeller 32, and the first communication hole 5, is increased in pressure. The leaked airflow 110 is reduced, and the performance of the blower 10 is improved.
  • the first rotating main plate 21 may be arranged so as to be offset from the space surrounded by the tongue portion 6 and the scroll casing 7 of the cross flow fan 12, and the communication space may be lowered under high pressure.
  • the first rotating main plate 21 may be arranged so as to be offset from the space surrounded by the first casing 8 of the first centrifugal fan 11, and the communication space may be pressurized.
  • FIG. 15 is a perspective view showing an impeller 30 including the first rotating main plate 21 of the second embodiment.
  • the second embodiment relates to the first rotating main plate 21 of the first embodiment, and since the configurations of the blower 10 and the air conditioner 200 are the same as those of the first embodiment, the description thereof will be omitted and the same members will be used. Alternatively, the same reference numerals are given to the corresponding parts.
  • the first rotating main plate 21 according to the second embodiment has a first penetration penetrating in the direction of the rotating shaft 20 through a part of the inner peripheral side of the second impeller 32 when viewed in the direction of the rotating shaft 20.
  • a hole 27 is formed. As shown in FIG. 15, two first through holes 27 are formed.
  • the air passage near the first impeller 31 of the first centrifugal fan 11 is the second impeller 32 of the cross current fan 12. It communicates with the downstream of the second impeller 32 in the suction region 22 via a first through hole 27 formed in a part of the first rotating main plate 21. Therefore, the pressure difference between the air passage of the first centrifugal fan 11 and the cross flow fan 12 is reduced, and as a result, the leaked airflow 110 is reduced and the performance of the blower 10 is improved.
  • FIG. 16 is a diagram showing a modified example of the second embodiment.
  • FIG. 16 is a cross-sectional view taken along the plane PF of FIG.
  • FIG. 16 shows a modified example of the position of the first through hole 27.
  • the first through hole 27 may be formed on the inner peripheral side of the first impeller 31.
  • three first through holes 27 are formed.
  • FIGS. 15 and 16 do not limit the number of first through holes 27.
  • the number of the first through holes 27 formed in the first impeller 31 or the second impeller 32 may be one or four or more.
  • FIG. 17 is a cross-sectional view corresponding to FIG. 3, showing the blower 10 according to the third embodiment.
  • the airflow 111 orbiting in the vicinity of the nozzle of the airflow in the circumferential direction around the outer periphery of the first impeller 31 is indicated by a broken line arrow
  • the airflow 112 of the first centrifugal fan 11 is indicated by a solid arrow.
  • FIG. 18 is a cross-sectional view corresponding to FIG. 4, showing the blower 10 according to the third embodiment.
  • the third embodiment relates to the first communication hole 5 of the first embodiment, and the configuration of the blower 10 and the air conditioner 200 is the same as that of the first embodiment. Alternatively, the same reference numerals are given to the corresponding parts.
  • the opening area per unit angle on the blowout region 23 side of the second impeller 32 when viewed from the axial direction of the rotary shaft 20 is the axial direction of the rotary shaft 20.
  • the second impeller 32 is configured to be larger than the opening area per unit angle on the suction region 22 side.
  • the opening area per unit angle of the second impeller 32 on the blowout region 23 side when the first communication hole 5 is viewed from the axial direction of the rotating shaft 20 can be defined as follows. As shown in FIG. 18, when viewed from the axial direction of the rotating shaft 20, the angle from the tongue portion 6 of the cross flow fan 12 to the rotation direction of the second impeller 32 around the circumference and reaching the scroll casing 7 is determined. Let ⁇ be. Let S1 be the area of the opening of the first communication hole 5 cut out by ⁇ . When viewed from the axial direction of the rotating shaft 20, the angle from the tongue portion 6 of the cross flow fan 12 to the circumference of the second impeller 32 in the direction opposite to the rotating direction and away from the scroll casing 7 is defined as ⁇ . Let S2 be the area of the opening of the first communication hole 5 cut out by ⁇ . Then, the opening area of the first communication hole 5 may be defined so that S1 / ⁇ ⁇ S2 / ⁇ .
  • the first communication hole 5 is configured so that the blowout region 23 side of the second impeller 32 is larger than the suction region 22 side when viewed from the air flow. ing. Therefore, the amount of airflow leaking from the first centrifugal fan 11 to the cross flow fan 12 is increased on the blowout region 23 side of the second impeller 32 where the pressure difference is relatively small, and the blowout region is increased in the first centrifugal fan 11. The airflow circulating from the 23 side to the suction region 22 side can be reduced.
  • FIG. 19 is a cross-sectional view corresponding to FIG. 4, showing a modified example of the first communication hole 5 according to the third embodiment.
  • the blowout region 23 of the second impeller 32 is formed so that the distance from the rotation shaft 20 of the opening end of the first communication hole 5 is at least partly larger than Dc / 2.
  • the distance of the suction region 22 of the impeller 32 of 2 from the rotating shaft 20 at the opening end of the first communication hole 5 is formed to be smaller than Dc / 2.
  • the first communication hole 5 is opened only on the side of the blowout region 23 on the outer peripheral side of the second impeller 32. With this configuration, the effect of attracting the airflow 112 (see FIG.
  • the eccentric direction and the eccentricity from the rotating shaft 20 may be different from the example shown in FIG. 19 as long as it is on the blowout region 23 side.
  • the eccentric direction and the eccentricity from the rotation shaft 20 at the centroid position of the first communication hole 5 are adjusted according to the operating conditions of the blower 10.
  • FIG. 20 is a cross-sectional view corresponding to FIG. 4, showing the blower 10 according to the fourth embodiment.
  • the fourth embodiment relates to the first fixed main plate 1 of the first embodiment, and the configurations of the blower 10 and the air conditioner 200 are the same as those of the first embodiment. The same code is attached to the part.
  • the first fixed main plate 1 has the following features.
  • the center of rotation of the second impeller 32 is O
  • the vertical line 50 and the scroll drawn from the tongue 6 of the cross flow fan 12 to the scroll casing 7 are scrolled.
  • the contact point with the casing 7 is CA
  • the winding start position of the scroll casing 7 is SB.
  • the vertical line 50 is a straight line orthogonal to the side surface of the extending portion 72 of the scroll casing 7 on the side facing the tongue portion 6.
  • the winding start position of the scroll casing 7 is an end portion of the base portion 71 of the scroll casing 7 on the opposite side of the stretched portion 72.
  • the amount of airflow leaking from the blowout region 23 side of the second impeller 32 having a relatively small pressure difference is increased, and the airflow leaks from the suction region 22. It will be reduced. Therefore, the performance of the blower 10 is improved.
  • FIG. 21 is a cross-sectional view corresponding to FIG. 4, showing a modified example of the blower 10 according to the fourth embodiment.
  • a part of the second through hole 127 may be out of the range where the straight LOA and the straight LOB cut out the first fixed main plate 1.
  • a large performance improvement effect can be obtained.
  • FIG. 22 is a cross-sectional view corresponding to FIG. 2, showing the blower 10 according to the fifth embodiment.
  • FIG. 23 is a cross-sectional view corresponding to FIG. 4, showing the effect of the fifth embodiment.
  • the fifth embodiment relates to the first peripheral wall 3 of the first casing 8 of the first embodiment, and the configuration of the blower 10 and the air conditioner 200 is the same as that of the first embodiment, and thus the description thereof is omitted. However, the same reference numerals are given to similar members or corresponding parts.
  • the first peripheral wall 3 of the first casing 8 has an inclined portion 28.
  • the inclined portion 28 is provided on the side of the first casing 8 corresponding to the suction region 22 of the cross flow fan 12. As shown in FIG. 22, the first casing 8 is inclined so that the first side plate 2 side is narrower than the first fixed main plate 1 side. In other words, the inclined portion 28 is inclined so as to approach the rotation shaft 20 as it goes from the first fixed main plate 1 to the first side plate 2.
  • the inclined portion of the first peripheral wall 3 of the first casing 8 of the first centrifugal fan 11 located on the side corresponding to the suction region 22 of the cross flow fan 12. 28 is inclined so that the first side plate 2 side is narrowed. Therefore, the velocity of the airflow in the circumferential direction of the outer circumference of the first impeller 31 increases in the vicinity of the side of the first fixed main plate 1. At this time, as shown in FIG. 23, since the centrifugal force 60 acting on the airflow outward in the radial direction becomes large, the leakage airflow 110 from the first communication hole 5 is reduced, and the performance of the blower 10 is improved.
  • the inclined portion 28 is inclined as described above, the space on the outer peripheral side is improved, and the housing structure can be miniaturized when mounted on the air conditioner 200. As a result, according to the fifth embodiment, it is possible to achieve both improvement in energy saving and miniaturization of the blower 10.
  • FIG. 24 is a cross-sectional view corresponding to FIG. 2, showing a modified example of the blower 10 according to the fifth embodiment.
  • the above-mentioned effect can be obtained even if the inclined portion 28 of the first peripheral wall 3 of the first casing 8 is provided only in a part near the first side plate 2.
  • the range in which the inclined portion 28 is provided on the first peripheral wall 3 may be appropriately adjusted depending on the operating point of the blower 10.
  • FIG. 25 is a cross-sectional view corresponding to FIG. 3, showing the first centrifugal fan 11 according to the sixth embodiment.
  • FIG. 26 is a cross-sectional view taken along the line GG showing the blower 10 according to the sixth embodiment.
  • the sixth embodiment relates to the first peripheral wall 3 of the first casing 8 of the first embodiment, and the configuration of the blower 10 and the air conditioner 200 is the same as that of the first embodiment, and thus the description thereof is omitted. However, the same or corresponding parts are given the same reference numerals.
  • the blowout nozzle 29 from which the airflow blows out rotates from the first fixed main plate 1 to the first side plate 2 as shown in FIG. It is tilted so as to approach the axis 20. That is, when the blowout nozzle 29 is viewed from a plane (GG cross section) horizontal to the rotary shaft 20 and the extension direction 51 of the blowout nozzle 29 to the blowout port, the two end portions of the side plate and the rotary shaft 20 The distance between them is inclined so as to be shorter than the distance between the end on the side of the first fixed main plate 1 and the rotating shaft 20.
  • the blow nozzle 29 is tilted so that the first side plate 2 side is narrowed. Therefore, with respect to the airflow 113 that orbits in the vicinity of the airflow outlet nozzle 29 in the circumferential direction of the outer circumference of the first impeller 31, the velocity in the vicinity of the first fixed main plate 1 side increases. At this time, since the inertial force of the airflow 113 and the centrifugal force 60 acting on the outer side in the radial direction become large, the leakage airflow 110 from the first communication hole 5 near the suction region 22 of the cross flow fan 12 is reduced, and the blower 10 Performance improves.
  • FIG. 27 is a perspective view showing the blower 10 according to the seventh embodiment.
  • FIG. 28 is a view showing the blower 10 according to the seventh embodiment cut from the plane PH of FIG. 27 from above.
  • the seventh embodiment relates to the second impeller 32 in the blower 10 of the first embodiment provided in the air conditioner 200, and the configuration of the air conditioner 200 is the same as that of the first embodiment. It is omitted, and the same reference numerals are given to similar members or corresponding parts.
  • the blower 10 according to the seventh embodiment has a first centrifugal fan 11, a cross current fan 12, and a second centrifugal fan 14.
  • the second centrifugal fan 14 has a second casing 408 and a third impeller 33.
  • the third impeller 33 has a second rotating main plate 421 and a plurality of second blades 411 erected on one surface of the second rotating main plate 421.
  • the second casing 408 has a second fixed main plate 401, a second side plate 402, and a second peripheral wall 403.
  • the second fixed main plate 401 and the second side plate 402 face each other in the direction of the rotation shaft 20 of the second centrifugal fan 14 and the cross flow fan 12.
  • the second peripheral wall 403 connects the outer edge portion of the second fixed main plate 401 and the outer edge portion of the second side plate 402, and faces the outer periphery of the third impeller 33.
  • the second side plate 402 is formed with a second suction hole 404 for sucking airflow.
  • a second communication hole 405 is formed in the second fixed main plate 401.
  • the second rotating main plate 421 is located in the second communication hole 405 of the second fixed main plate 401. That is, the second centrifugal fan 14 is a single-suction multi-blade fan having the same configuration as the first centrifugal fan 11.
  • the first centrifugal fan 11 and the second centrifugal fan 14 are arranged so that the above-mentioned components are symmetrical in the direction of the rotation axis 20.
  • the second impeller 32 of the cross flow fan 12 is provided with one end of both ends of the rotating shaft 20 in the axial direction, and the first blade 211 is provided on the first rotating main plate 21. It is connected to the opposite side of the surface. Then, in the second impeller 32, the other end of both ends in the direction of the rotating shaft 20 is connected to the surface of the second rotating main plate 421 opposite to the surface on which the second blade 411 is provided. Has been done.
  • the end of the second impeller 32 and the third impeller 33 are connected via a second communication hole 405 of the second fixed main plate 401 of the second casing 408 of the second centrifugal fan 14. ing.
  • the cross flow fan 12 includes the first centrifugal fan 11 and the second centrifugal fan 14 provided at both ends in the rotation axis 20 direction, and the first of each.
  • the casing 8 is connected via the first communication hole 5 of the first fixed main plate 1. Therefore, the symmetry in the direction of the rotation axis 20 can be maintained with respect to the air flow flowing from the first centrifugal fan 11 and the second centrifugal fan 14 to the cross flow fan 12.
  • the velocity component in the radial direction of rotation increases as the velocity component in the axial direction of the rotating shaft 20 decreases, the inertial force in the radial direction increases, and the first centrifugal force increases.
  • the leakage airflow 110 from the fan 11 to the suction region 22 of the cross flow fan 12 is reduced. Therefore, the performance of the blower 10 is improved.
  • FIG. 29 is a graph showing the performance improvement effect on the blade width according to the seventh embodiment.
  • the horizontal axis represents each blade width ratio [L1 / (L1 + L2)] with respect to the first impeller 31 and the second impeller 32
  • the vertical axis represents the maximum performance ratio of the blower 10.
  • the blade width ratio [L1 / When (L1 + L2)] is 0.3 ⁇ L1 / (L1 + L2) ⁇ 0.85
  • a maximum performance ratio of 95% or more is shown. This also applies to the relationship between the sum of the blade widths of the third impeller 33 of the second centrifugal fan 14 and the sum of the blade widths of the second impeller 32 of the cross flow fan 12.
  • the relationship between the blade width of the first impeller 31 and the blade width of the second impeller 32, and the relationship between the blade width of the third impeller 33 and the second impeller 32 are as described above. That is, if it is mounted on the product housing with 0.3 ⁇ L1 / (L1 + L2) ⁇ 0.85, the following effects can be obtained. That is, the airflow loss due to the leakage and drift of the airflow 112 flowing through the first centrifugal fan 11 and the second centrifugal fan 14, and the outer periphery of the first casing 8 of each of the first centrifugal fan 11 and the second centrifugal fan 14. The ventilation resistance of the surface can be reduced. Therefore, a greater performance improving effect of the blower 10 can be obtained.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2020/003206 2020-01-29 2020-01-29 送風機及び空気調和装置 WO2021152731A1 (ja)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5822494U (ja) * 1981-08-06 1983-02-12 株式会社東芝 冷却装置
JPH0163926U (US20100223739A1-20100909-C00025.png) * 1987-10-16 1989-04-25
CN104421189A (zh) * 2013-09-04 2015-03-18 广东美的暖通设备有限公司 送风风机及具有其的空调
JP2018084368A (ja) * 2016-11-24 2018-05-31 株式会社富士通ゼネラル 空気調和機の室内機

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5822494B2 (ja) 2011-03-17 2015-11-24 大阪瓦斯株式会社 浴室暖房乾燥機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5822494U (ja) * 1981-08-06 1983-02-12 株式会社東芝 冷却装置
JPH0163926U (US20100223739A1-20100909-C00025.png) * 1987-10-16 1989-04-25
CN104421189A (zh) * 2013-09-04 2015-03-18 广东美的暖通设备有限公司 送风风机及具有其的空调
JP2018084368A (ja) * 2016-11-24 2018-05-31 株式会社富士通ゼネラル 空気調和機の室内機

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