WO2020147751A1 - 立式空调器室内机 - Google Patents

立式空调器室内机 Download PDF

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Publication number
WO2020147751A1
WO2020147751A1 PCT/CN2020/072255 CN2020072255W WO2020147751A1 WO 2020147751 A1 WO2020147751 A1 WO 2020147751A1 CN 2020072255 W CN2020072255 W CN 2020072255W WO 2020147751 A1 WO2020147751 A1 WO 2020147751A1
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WIPO (PCT)
Prior art keywords
laminar flow
air
annular
indoor unit
flow fan
Prior art date
Application number
PCT/CN2020/072255
Other languages
English (en)
French (fr)
Inventor
李英舒
王晓刚
张蕾
李婧
王永涛
Original Assignee
青岛海尔空调器有限总公司
海尔智家股份有限公司
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Application filed by 青岛海尔空调器有限总公司, 海尔智家股份有限公司 filed Critical 青岛海尔空调器有限总公司
Publication of WO2020147751A1 publication Critical patent/WO2020147751A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0011—Indoor units, e.g. fan coil units characterised by air outlets
    • F24F1/0014—Indoor units, e.g. fan coil units characterised by air outlets having two or more outlet openings
    • 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
    • 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
    • F24F1/005—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted on the floor; standing on the floor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/24—Means for preventing or suppressing noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/24—Means for preventing or suppressing noise
    • F24F2013/247—Active noise-suppression

Definitions

  • the invention relates to the technical field of household appliances, in particular to a vertical air conditioner indoor unit.
  • the current air conditioning adjusting devices mainly include various types of air conditioners and fans, but most users believe that the hot or cold air generated by the current air conditioners is unevenly distributed in a room or a closed space, and has certain layout limitations.
  • fans used in indoor units of air conditioners are mainly centrifugal fans and cross-flow fans.
  • the centrifugal fan and the cross flow fan have the following problems: because the centrifugal fan needs dozens of large-volume blades to increase the wind pressure and air volume, the centrifugal fan is very noisy, and when the centrifugal fan is used in the indoor unit of a vertical air conditioner, Air from entering the centrifugal fan to sending out of the air conditioner requires two 90° turning directions, and each direction turning will cause air volume loss; although the cross flow fan has low noise, the wind pressure is too small and the air supply distance is short. In addition, the overall volume of the cross flow fan is large, but the actual effective volume is small, resulting in a waste of space.
  • An object of the present invention is to provide a vertical air conditioner indoor unit with low noise, high air volume, and high air pressure.
  • a further object of the present invention is to enable the indoor unit of the vertical air conditioner to realize 360° air supply, avoid direct wind blowing to the user, and improve the user experience.
  • the present invention provides a vertical air conditioner indoor unit, which includes: a housing with a cavity defined therein, an air outlet is opened on the upper part of the housing, and an air inlet is provided at the middle and lower part; a laminar flow fan is arranged at The inside of the cavity corresponding to the air outlet includes: a plurality of annular discs, which are arranged in parallel with each other and have the same central axis.
  • the centers of the plurality of annular discs jointly form an air inlet channel, and the air in the cavity passes through the inlet
  • the wind channel enters the gap between the plurality of annular disks; and the laminar flow motor is configured to drive the plurality of annular disks to rotate, so that the air boundary layer near the surface of the plurality of annular disks rotates from the inside to the outside, thereby forming a layer Flowing wind blows out from the air outlet.
  • the laminar flow fan further includes: a drive disc, which is arranged at intervals and parallel to one side of the plurality of annular discs; and a connecting member, which penetrates the drive disc and the plurality of annular discs to connect the plurality of annular discs Connected to the driving disc, the laminar flow motor is also configured to directly drive the driving disc to rotate, and then the driving disc drives a plurality of annular discs to rotate.
  • the indoor unit of the vertical air conditioner further includes: a fixing plate provided with a plurality of reinforcing ribs on one side and a plurality of clamping slots on the other side; A plurality of clamping claws corresponding to each clamping slot are used to fix the laminar flow motor between the fixing frame and the fixing plate after the plurality of clamping claws are respectively screwed into the multiple clamping slots, wherein the center of the fixing frame is provided with a hole, the laminar flow motor After passing through the perforation, the output shaft is fixed with the drive disc.
  • the indoor unit of the vertical air conditioner further includes: a draft ring, which is arranged on a side of the plurality of annular disks away from the driving disk, and is configured to guide the air entering the cavity through the air inlet into the air inlet channel.
  • a draft ring which is arranged on a side of the plurality of annular disks away from the driving disk, and is configured to guide the air entering the cavity through the air inlet into the air inlet channel.
  • the casing is provided with an air outlet around the laminar flow fan on its upper part.
  • the indoor unit of the vertical air conditioner further includes: a windshield, which is arranged on the outside of the laminar flow fan and has a gap; and the housing is provided with an air outlet at a position corresponding to the gap on the upper part of the housing.
  • a groove is formed in the center of the driving disk toward the plurality of annular disks, and the laminar flow motor is fixedly arranged in the groove.
  • the surface of the drive disc facing the laminar flow motor is flat, and the surface facing the plurality of annular discs has conical protrusions to guide the flow of air entering the laminar flow fan and assist in forming the laminar flow wind.
  • the connecting piece is a connecting piece
  • the cross section of the connecting piece has two curves arranged in sequence along the rotation direction of the annular disk, and the chord length of the two curves has a linear relationship with the air volume generated by the laminar flow fan.
  • the cross section of the connecting piece has double arcs arranged in sequence along the direction of rotation of the annular disc: an inner arc and a back arc, and both the inner arc and the back arc protrude in the direction of rotation of the annular disc.
  • the back arcs have the same center and are arranged in parallel or have different centers and both ends intersect.
  • the plurality of annular discs are arranged according to one or more of the following structures: the inner diameters of the plurality of annular discs gradually decrease from one side away from the driving disc to the other side; The distance between two adjacent annular discs gradually increases from one side away from the drive disc to the other; each annular disc gradually approaches the drive disc from the center to the edge and protrudes toward one side of the drive disc.
  • the arc-shaped disc is arranged according to one or more of the following structures: the inner diameters of the plurality of annular discs gradually decrease from one side away from the driving disc to the other side; The distance between two adjacent annular discs gradually increases from one side away from the drive disc to the other; each annular disc gradually approaches the drive disc from the center to the edge and protrudes toward one side of the drive disc.
  • the arc-shaped disc is arranged according to one or more of the following structures: the inner diameters of the plurality of annular discs gradually decrease from one side away from the driving disc to the other side; The distance between two adjacent annular
  • the indoor unit of the vertical air conditioner of the present invention includes: a housing with a cavity defined therein, an air outlet is opened on the upper part of the housing, and an air inlet is arranged at the middle and lower part; a laminar flow fan is arranged in the cavity corresponding to the air outlet
  • the interior includes: a plurality of annular discs, which are arranged in parallel with each other and have the same central axis.
  • the centers of the plurality of annular discs jointly form an air inlet channel, and the air in the cavity enters the plurality of annular discs through the air inlet channel
  • the gap between the disks; and the laminar flow motor are configured to drive the plurality of annular disks to rotate, so that the air boundary layer close to the surface of the plurality of annular disks rotates from the inside to the outside, thereby forming a laminar wind blown out from the air outlet.
  • the indoor unit of the vertical air conditioner is equipped with a laminar flow fan, which realizes laminar air supply through the viscous effect.
  • the air supply process has low noise and high air volume, which effectively improves the user experience.
  • the laminar flow fan further includes: a driving disc, which is arranged in parallel at intervals on one side of the plurality of annular discs; and a connecting piece that penetrates the driving disc and the plurality of annular discs
  • the laminar flow motor is also configured to directly drive the drive disc to rotate, and then the drive disc drives the plurality of annular discs to rotate.
  • the laminar flow motor is fixed between the fixing frame and the fixing plate, wherein a perforation is provided in the center of the fixing frame, and the output shaft of the laminar flow motor is fixed to the driving disc after passing through the perforation. It can effectively enhance the connection firmness of the laminar flow fan and the laminar flow motor, and improve the overall working reliability.
  • the multiple annular discs of the laminar flow fan can be arranged according to one or more of the following structures: the inner diameter of the multiple annular discs is changed from the one far away from the drive disc Gradually shrink from side to side; the distance between two adjacent ring disks in the plurality of ring disks gradually increases from one side away from the driving disk to the other side; each ring disk is from the center To the arc-shaped disc with the edge gradually approaching the driving disc and protruding to one side of the driving disc.
  • the above-mentioned forms of multiple annular disks can effectively increase the air volume of the laminar flow fan, so that the air output of the laminar flow fan meets the user's requirements.
  • the connecting piece may be a connecting piece, and the cross section of the connecting piece has two curves arranged in sequence along the rotation direction of the annular disc, and the chord length of the two curves has a linear relationship with the air volume generated by the laminar flow fan.
  • the setting of the connecting piece can effectively increase the wind pressure of the laminar flow fan, so that after the laminar air blows out through the gap between the multiple annular discs, due to the pressure difference, the air outside the laminar flow fan is compressed through the air inlet channel Into the annular disc, so cyclically reciprocating, thus forming a laminar air circulation.
  • the multiple air outlets formed by the gaps between multiple annular disks can make the laminar flow fan achieve 360° air supply, avoiding the user's various discomfort symptoms caused by the direct blowing of the air conditioner, and further improving the user's use Experience.
  • Fig. 1 is a schematic diagram of air supply of a centrifugal fan used in the indoor unit of a vertical air conditioner in the prior art
  • FIG. 2 is a schematic diagram of the overall structure of the indoor unit of the vertical air conditioner according to the first embodiment of the present invention
  • Fig. 3 is a partial structural diagram of the indoor unit of the vertical air conditioner in Fig. 2;
  • Figure 4 is an exploded schematic diagram of components of the indoor unit of the vertical air conditioner in Figure 2;
  • FIG. 5 is a schematic diagram of the overall structure of the indoor unit of a vertical air conditioner according to a second embodiment of the present invention.
  • Fig. 6 is a partial structural diagram of the indoor unit of the vertical air conditioner in Fig. 5;
  • Figure 7 is an exploded schematic diagram of the components of the indoor unit of the vertical air conditioner in Figure 5;
  • FIG. 8 is a schematic diagram of the overall structure of the indoor unit of a vertical air conditioner according to a third embodiment of the present invention.
  • Fig. 9 is a partial structural diagram of the indoor unit of the vertical air conditioner in Fig. 8.
  • Figure 10 is an exploded schematic diagram of components of the indoor unit of the vertical air conditioner in Figure 8.
  • FIG. 11 is a schematic diagram of the overall structure of the indoor unit of a vertical air conditioner according to a fourth embodiment of the present invention.
  • Figure 12 is a partial structural diagram of the indoor unit of the vertical air conditioner in Figure 11;
  • Figure 13 is an exploded schematic diagram of components of the indoor unit of the vertical air conditioner in Figure 11;
  • FIG. 14 is a schematic diagram of the overall structure of the indoor unit of a vertical air conditioner according to a fifth embodiment of the present invention.
  • Figure 15 is a partial structural diagram of the indoor unit of the vertical air conditioner in Figure 14;
  • Figure 16 is an exploded schematic diagram of the components of the indoor unit of the vertical air conditioner in Figure 14;
  • Figure 18 is a partial structural diagram of the indoor unit of the vertical air conditioner in Figure 17;
  • Figure 19 is an exploded schematic diagram of the components of the indoor unit of the vertical air conditioner in Figure 17;
  • 20 is a schematic diagram of air circulation of a laminar flow fan in an indoor unit of a vertical air conditioner according to an embodiment of the present invention
  • 21 is a schematic diagram of the air supply principle of the laminar flow fan in the indoor unit of a vertical air conditioner according to an embodiment of the present invention.
  • Figure 22 is a speed distribution and force distribution diagram of a laminar flow fan in an indoor unit of a vertical air conditioner according to an embodiment of the present invention
  • Figure 23 is a schematic view of the structure of a laminar flow fan with grooves on the drive disc
  • FIG. 24 is a schematic structural diagram of the laminar flow fan in FIG. 23 from another perspective;
  • FIG. 25 is a schematic structural diagram of the laminar flow fan in FIG. 23 from another perspective
  • Figure 26 is a cross-sectional view of the laminar flow fan in Figure 23;
  • Fig. 27 is a schematic diagram of the connection between the laminar flow fan and the laminar flow motor in Fig. 23;
  • Figure 28 is an exploded schematic diagram of the components of the laminar flow motor, the fixed plate and the fixed frame;
  • Figure 29 is a schematic diagram of the connection of a laminar flow fan with a conical protrusion on the drive disc and a laminar flow motor;
  • FIG. 30 is a schematic structural diagram of the laminar flow fan in FIG. 29 from another perspective
  • Figure 31 is a schematic cross-sectional view of the laminar flow fan in Figure 29;
  • Figure 32 is a schematic diagram of the relationship between the chord length of the connecting piece in Figure 31 and the air volume and pressure;
  • Figure 33 is a schematic diagram of the relationship between the installation angle of the connecting piece and the air volume and pressure in Figure 31;
  • Figure 34 is a schematic cross-sectional view of a laminar flow fan with aviation blades
  • 35 is a schematic diagram of the relationship between the installation angle of the aero blades of the laminar flow fan in FIG. 34 and the air volume and wind pressure;
  • FIG. 36 is a schematic diagram of the connection of a plurality of laminar flow fans with gradual pitches between annular disks and a laminar flow motor;
  • Fig. 37 is a schematic diagram of the connection between the laminar flow fan and the laminar flow motor in Fig. 36 from another perspective;
  • FIG. 38 is a schematic diagram of the relationship between the gradual change in the pitch of the annular disks of the laminar flow fan in FIG. 36 and the air volume and pressure;
  • Figure 39 is a partial cross-sectional view of a plurality of laminar flow fans with gradual inner diameters of annular discs;
  • FIG. 40 is a schematic diagram of the relationship between the gradual change in the inner diameter of the multiple annular disks of the laminar flow fan in FIG. 39 and the air volume and pressure;
  • 41 is a schematic diagram of the central angle of the inner and outer diameters of the laminar flow fan with the annular disc being an arc-shaped disc on the same longitudinal section passing through the central axis;
  • Fig. 42 is a schematic diagram of the relationship between the central angle of Fig. 41 and the air volume and air pressure.
  • Fig. 1 is a schematic diagram of a centrifugal fan used in the indoor unit of a vertical air conditioner in the prior art.
  • the two arrows in FIG. 1 show the direction in which the centrifugal fan 200 is applied to the indoor unit of a vertical air conditioner in the air flow direction.
  • the centrifugal fan 200 in the prior art is applied to the indoor unit of a vertical air conditioner.
  • the entire process from air inlet to air outlet requires two 90° turns, and each turn will be accompanied by more air loss.
  • the centrifugal fan 200 generally requires dozens of large-volume blades to increase the wind pressure and air volume. When the centrifugal fan 200 is working, the blades rotate and generate friction or impact with the air.
  • the blades of the centrifugal fan 200 are wide and thick. Therefore, when the motor of the centrifugal fan 200 runs at a high speed, very loud noise is generated.
  • cross-flow fans are commonly used in the prior art, but although the noise of the cross-flow fans is low, the wind pressure is too small and the air supply distance is short; and the overall volume of the cross-flow fan is large, but the actual effective volume is small, resulting in a waste of space .
  • This embodiment provides a vertical air conditioner indoor unit, which is provided with a laminar flow fan to realize laminar air supply through the viscous effect. The air supply process has low noise, high air volume, and high wind pressure, which effectively improves the user experience.
  • FIG. 2 is a schematic diagram of the overall structure of a vertical air conditioner indoor unit 300 according to the first embodiment of the present invention
  • FIG. 3 is a partial structural diagram of the vertical air conditioner indoor unit 300 in FIG. 2
  • FIG. 4 is a vertical air conditioner in FIG. 2
  • 5 is a schematic diagram of the overall structure of a vertical air conditioner indoor unit 300 according to the second embodiment of the present invention
  • FIG. 6 is a partial structural diagram of the vertical air conditioner indoor unit 300 in FIG. 5
  • FIG. 7 is a vertical air conditioner in FIG. 5
  • An exploded schematic diagram of the components of the indoor unit 300. 8 is a schematic diagram of the overall structure of a vertical air conditioner indoor unit 300 according to a third embodiment of the present invention, FIG.
  • FIG. 9 is a partial structural diagram of the vertical air conditioner indoor unit 300 in FIG. 8, and FIG. 10 is a vertical air conditioner in FIG. 8
  • FIG. 11 is a schematic diagram of the overall structure of a vertical air conditioner indoor unit 300 according to a fourth embodiment of the present invention
  • FIG. 12 is a partial structural diagram of the vertical air conditioner indoor unit 300 in FIG. 11
  • FIG. 13 is a vertical air conditioner in FIG. 11
  • 14 is a schematic diagram of the overall structure of the vertical air conditioner indoor unit 300 according to the fifth embodiment of the present invention
  • FIG. 15 is a partial structural diagram of the vertical air conditioner indoor unit 300 in FIG. 14, and
  • FIG. 16 is the vertical air conditioner in FIG.
  • FIG. 17 is a schematic diagram of the overall structure of the vertical air conditioner indoor unit 300 according to the sixth embodiment of the present invention
  • FIG. 18 is a partial structural diagram of the vertical air conditioner indoor unit 300 in FIG. 17,
  • FIG. 19 is the vertical air conditioner in FIG.
  • FIG. 20 is a schematic diagram of the air circulation of the laminar flow fan 100 in the indoor unit 300 of a vertical air conditioner according to an embodiment of the present invention.
  • FIG. 21 is an indoor unit of a vertical air conditioner according to an embodiment of the present invention.
  • FIG. 20 is a schematic diagram of the air circulation of the laminar flow fan 100 in the indoor unit 300 of a vertical air conditioner according to an embodiment of the present invention
  • FIG. 21 is an indoor unit of a vertical air conditioner according to an embodiment of the present invention.
  • FIG. 22 is a speed distribution and force distribution diagram of the laminar flow fan 100 in a vertical air conditioner indoor unit 300 according to an embodiment of the present invention.
  • FIG. 23 is a schematic structural view of the laminar flow fan 100 with a groove 32 in the driving disc 30
  • FIG. 24 is a schematic structural view of the laminar flow fan 100 in FIG. 23 from another perspective
  • the vertical air conditioner indoor unit 300 may generally include a casing 310, a laminar flow fan 100 and a laminar flow motor 20.
  • the housing 310 defines a cavity, and the upper part of the housing 310 is provided with an air outlet 320, and the middle and lower part is provided with an air inlet 330.
  • the laminar flow fan 100 is arranged inside the cavity corresponding to the air outlet 320, and includes a plurality of annular discs 10, which are arranged in parallel with each other and have the same central axis, and the centers of the plurality of annular discs 10 together form an inlet In the air channel 11, the air in the cavity enters the gap between the plurality of annular disks 10 through the air inlet channel 11.
  • the laminar flow motor 20 is configured to drive the plurality of annular disks to rotate, so that the air boundary layer 13 close to the surface of the plurality of annular disks rotates from the inside to the outside, thereby forming a laminar air blown out from the air outlet 320.
  • the laminar flow motor 20 drives the plurality of annular disks to rotate, so that the plurality of annular disks are in contact with the air between each other and move with each other, so that the air boundary layer 13 near the surface of the plurality of annular disks is caused by the viscous effect.
  • the multiple ring-shaped discs are driven to rotate from inside to outside to form laminar wind.
  • a plurality of air outlets 12 are formed in the gap between the plurality of annular discs, and each air outlet 12 can realize 360° air supply, and the laminar air discharged from the air outlet 12 is blown out to the vertical air conditioner through the air outlet 320 In the environment outside the indoor unit 300.
  • the laminar flow fan can achieve 360° air supply, but the air outlet 320 can be set according to the actual situation, and can respectively achieve four-sided air supply, three-sided air supply, two-sided air supply, or single-sided air supply.
  • the vertical air conditioner indoor unit 300 may further include an evaporator, which is disposed inside the cavity corresponding to the air inlet 330 and configured to exchange heat for the air entering the cavity through the air inlet 330.
  • the evaporator may be arranged below the laminar flow fan 100, and specifically may be a U-shaped evaporator 381, a flat evaporator 382, or a V-shaped evaporator.
  • a water receiving pan 390 may be provided under the evaporator to receive the condensed water generated by the evaporator.
  • the housing 310 may include a front panel 311, a rear case 312, a top plate 313 and a bottom plate 314, where the rear case 312 includes a rear panel 315 and two side panels 316.
  • An air deflector 321 may be provided at the air outlet 320 of the housing 310 to adjust the air outlet direction of the indoor unit 300 of the vertical air conditioner.
  • the air inlet 330 of the housing 310 may be provided in the form of an air inlet grill, which can suck indoor air into the cavity through different directions and filter the air.
  • the vertical air conditioner indoor unit 300 may further include an air guide ring 360 configured to guide the air entering the cavity through the air inlet 330 to enter the air inlet channel 11.
  • the draft ring 360 may be arranged between the evaporator and the laminar flow fan 100, the air entering the cavity through the air inlet 330 first exchanges heat through the evaporator, and the heat-exchanged air is guided into the laminar flow through the draft ring 360 The air inlet channel 11 of the fan 100.
  • the laminar flow fan 100 may further include: a driving disc 30 and a connecting member.
  • the driving discs 30 are arranged parallel to one side of the plurality of annular discs 10 at intervals.
  • the connecting member penetrates the driving disc 30 and the plurality of annular discs 10 to connect the plurality of annular discs 10 to the driving disc 30.
  • the connecting member may be a connecting piece 40.
  • the laminar flow motor 20 can also be configured to directly drive the driving disc 30 to rotate, and then the driving disc 30 drives a plurality of annular discs 10 to rotate.
  • the above-mentioned laminar flow motor 20 is configured to drive a plurality of annular disks 10 to rotate depends on that the laminar flow motor 20 first drives the driving disk 30 to rotate, and then the driving disk 30 drives the plurality of annular disks. 10 rotations.
  • the radius of the drive disc 30 and the outer diameter of the plurality of annular discs 10 are the same, and can be set in a certain range, for example, 170 mm to 180 mm, so as to occupy the volume of the laminar flow fan 100 in the lateral direction.
  • Constraint cooperate to limit the number of annular discs 10 and the distance between two adjacent annular discs 10, and restrict the longitudinal thickness of the laminar flow fan 100, which can effectively restrict the overall occupied volume of the laminar flow fan 100.
  • the inner diameter of the annular disk 10 refers to the radius of its inner circumference; the outer diameter refers to the radius of its outer circumference.
  • the specific numerical values of the outer diameter of the annular disk 10 are only examples, and not a limitation of the present invention.
  • Embodiment 1 As shown in Figures 2 to 4, the vertical air conditioner indoor unit 300 of this embodiment is provided with a U-shaped evaporator 381.
  • the U-shaped evaporator 381 is placed vertically inside the cavity and its cross section is U The U-shaped opening faces the front panel 311.
  • the air inlet 330 is provided on the rear panel 315 and the two side panels 316 of the rear shell 312, that is, the air enters from three sides.
  • the U-shaped evaporator 381 is arranged corresponding to the air inlet 330, and the air entering the cavity from the air inlet 330 can pass through the U-shaped evaporator 381 to exchange heat.
  • a partition 383 is also arranged in front of the U-shaped evaporator 381 to prevent the heat exchanged air from flowing to the front of the cavity.
  • the partition 383 in this embodiment is flat.
  • the heat-exchanged air enters the air inlet channel 11 of the laminar flow fan 100 through the guiding action of the air guide ring 360, and then enters between the multiple annular disks of the laminar flow fan 100.
  • the housing 310 of the indoor unit 300 of the vertical air conditioner of this embodiment is provided with an air outlet 320 around the laminar flow fan 100 on its upper part.
  • the front panel 311 of the vertical air conditioner indoor unit 300 of the present embodiment, the rear panel 315 of the rear housing 312, and the two side panels 316 are all provided with air outlets 320, and the laminar flow formed by the laminar flow fan 100 flows from the air outlets. 320 blow out, can achieve 360° air supply.
  • Embodiment 2 As shown in Figures 5 to 7, the vertical air conditioner indoor unit 300 of this embodiment is provided with a U-shaped evaporator 381.
  • the U-shaped evaporator 381 is placed vertically inside the cavity and its cross section is U The U-shaped opening faces the front panel 311.
  • the air inlet 330 is provided on the rear panel 315 and the two side panels 316 of the rear shell 312, that is, the air enters from three sides.
  • the U-shaped evaporator 381 is arranged corresponding to the air inlet 330, and the air entering the cavity from the air inlet 330 can pass through the U-shaped evaporator 381 to exchange heat.
  • a partition 383 is also arranged in front of the U-shaped evaporator 381 to prevent the heat exchanged air from flowing to the front of the cavity.
  • the partition 383 in this embodiment is flat.
  • the heat-exchanged air enters the air inlet channel 11 of the laminar flow fan 100 through the guiding action of the air guide ring 360, and then enters between the multiple annular disks of the laminar flow fan 100.
  • the vertical air conditioner indoor unit 300 of this embodiment further includes: a windshield, which is provided on the outside of the laminar flow fan 100 and has a notch 373; the housing 310 is provided with an air outlet 320 at a position corresponding to the notch 373 on its upper part.
  • the windshield of the vertical air conditioner indoor unit 300 of this embodiment may be a windshield 371, and the area around the laminar flow fan 100 that is not blocked by the windshield 371 is the gap 373.
  • the front panel 311 and the two side panels 316 of the rear shell 312 of the vertical air conditioner indoor unit 300 of this embodiment are provided with air outlets 320, and the laminar flow formed by the laminar flow fan 100 is blown out from the air outlets 320 to achieve Air supply on three sides.
  • Embodiment 3 As shown in FIGS. 8 to 10, the vertical air conditioner indoor unit 300 of this embodiment is provided with a flat evaporator 382, and the flat evaporator 382 is placed vertically inside the cavity and parallel to the front panel 311.
  • the air inlet 330 is disposed on the rear panel 315 of the rear shell 312, that is, the air enters on one side.
  • the flat plate evaporator 382 is arranged corresponding to the air inlet 330, and the air entering the cavity from the air inlet 330 can pass through the flat plate evaporator 382 to exchange heat.
  • a partition 383 is also arranged in front of the flat evaporator 382 to prevent the heat exchanged air from flowing to the front of the cavity.
  • the partition 383 in this embodiment is U-shaped, and the U-shaped opening faces the flat evaporator 382.
  • the heat-exchanged air enters the air inlet channel 11 of the laminar flow fan 100 through the guiding action of the air guide ring 360, and then enters between the multiple annular disks of the laminar flow fan 100.
  • the vertical air conditioner indoor unit 300 of this embodiment further includes: a windshield, which is provided on the outside of the laminar flow fan 100 and has a notch 373; the housing 310 is provided with an air outlet 320 at a position corresponding to the notch 373 on its upper part.
  • the windshield of the vertical air conditioner indoor unit 300 of this embodiment may be a windshield 371, and the area around the laminar flow fan 100 that is not blocked by the windshield 371 is the notch 373.
  • the front panel 311 and the two side panels 316 of the rear shell 312 of the vertical air conditioner indoor unit 300 of this embodiment are provided with air outlets 320, and the laminar flow formed by the laminar flow fan 100 is blown out from the air outlets 320 to achieve Air supply on three sides.
  • the vertical air conditioner indoor unit 300 of this embodiment is provided with a flat evaporator 382, and the flat evaporator 382 is placed vertically inside the cavity and parallel to the front panel 311.
  • the air inlet 330 is disposed on the rear panel 315 of the rear shell 312, that is, the air enters on one side.
  • the flat plate evaporator 382 is arranged corresponding to the air inlet 330, and the air entering the cavity from the air inlet 330 can pass through the flat plate evaporator 382 to exchange heat.
  • a partition 383 is also arranged in front of the flat evaporator 382 to prevent the heat exchanged air from flowing to the front of the cavity.
  • the partition 383 in this embodiment is U-shaped, and the U-shaped opening faces the flat evaporator 382.
  • the heat-exchanged air enters the air inlet channel 11 of the laminar flow fan 100 through the guiding action of the air guide ring 360, and then enters between the multiple annular disks of the laminar flow fan 100.
  • the vertical air conditioner indoor unit 300 of this embodiment further includes: a windshield, which is provided on the outside of the laminar flow fan 100 and has a notch 373; the housing 310 is provided with an air outlet 320 at a position corresponding to the notch 373 on its upper part.
  • the wind shield of the vertical air conditioner indoor unit 300 of this embodiment may be a wind shield 372, and the area around the laminar fan 100 that is not blocked by the wind shield 372 is the gap 373.
  • the front panel 311 of the vertical air conditioner indoor unit 300 of this embodiment is provided with an air outlet 320, and the laminar air formed by the laminar flow fan 100 is blown out from the air outlet 320, which can realize single-sided air supply.
  • Embodiment 5 As shown in Figures 14 to 16, the vertical air conditioner indoor unit 300 of this embodiment is provided with a V-shaped evaporator.
  • the V-shaped evaporator is actually two flat plate evaporators 382 in the cavity. It gradually moves away from the housing 310 until the bottom, and the overall longitudinal section is roughly V-shaped.
  • the air inlets 330 are arranged on the two side panels 316 of the rear shell 312, that is, the air enters from both sides.
  • the V-shaped evaporator is arranged corresponding to the air inlet 330, and the air entering the cavity from the air inlet 330 can exchange heat through the V-shaped evaporator.
  • the front and rear of the V-shaped evaporator are also provided with partitions 383, which can prevent the heat exchanged air from flowing to the front and rear of the cavity.
  • the partitions 383 in this embodiment are flat.
  • the heat-exchanged air enters the air inlet channel 11 of the laminar flow fan 100 through the guiding action of the air guide ring 360, and then enters between the multiple annular disks of the laminar flow fan 100.
  • the housing 310 of the indoor unit 300 of the vertical air conditioner of this embodiment is provided with an air outlet 320 around the laminar flow fan 100 on its upper part.
  • the front panel 311 of the vertical air conditioner indoor unit 300 of the present embodiment, the rear panel 315 of the rear housing 312, and the two side panels 316 are all provided with air outlets 320, and the laminar flow formed by the laminar flow fan 100 flows from the air outlets. 320 blow out, can achieve 360° air supply.
  • Embodiment 6 As shown in Figures 17 to 19, the vertical air conditioner indoor unit 300 of this embodiment is provided with a V-shaped evaporator.
  • the V-shaped evaporator is actually two flat plate evaporators 382 in the cavity. It gradually moves away from the housing 310 until the bottom, and the overall longitudinal section is roughly V-shaped.
  • the air inlets 330 are arranged on the two side panels 316 of the rear shell 312, that is, the air enters from both sides.
  • the V-shaped evaporator is arranged corresponding to the air inlet 330, and the air entering the cavity from the air inlet 330 can exchange heat through the V-shaped evaporator.
  • the front and rear of the V-shaped evaporator are also provided with partitions 383, which can prevent the heat exchanged air from flowing to the front and rear of the cavity.
  • the partitions 383 in this embodiment are flat.
  • the heat-exchanged air enters the air inlet channel 11 of the laminar flow fan 100 through the guiding action of the air guide ring 360, and then enters between the multiple annular disks of the laminar flow fan 100.
  • the vertical air conditioner indoor unit 300 of this embodiment further includes: a windshield, which is provided on the outside of the laminar flow fan 100 and has a notch 373; the housing 310 is provided with an air outlet 320 at a position corresponding to the notch 373 on its upper part.
  • the windshield of the vertical air conditioner indoor unit 300 of this embodiment may be a windshield 371, and the area around the laminar flow fan 100 that is not blocked by the windshield 371 is the gap 373.
  • the front panel 311 and the two side panels 316 of the rear shell 312 of the vertical air conditioner indoor unit 300 of this embodiment are provided with air outlets 320, and the laminar flow formed by the laminar flow fan 100 is blown out from the air outlets 320 to achieve Air supply on three sides.
  • the notch 373 is provided corresponding to the air outlet 320.
  • the wind baffle 371 can discharge the laminar flow formed by the laminar flow fan 100 on three sides, and there are three corresponding outlets 320; the wind baffle 372 can discharge the laminar flow formed by the laminar flow fan 100 on one side, and the outlet 320 corresponds to There is one set.
  • the windshield can ensure that the laminar flow formed by the laminar flow fan 100 will not be blown to other places in the cavity except through the air outlet 320, so as to avoid affecting the normal operation of other parts in the cavity.
  • the center of the plurality of annular disks 10 is jointly formed with an air inlet channel 11 to allow air outside the laminar flow fan 100 to enter.
  • a plurality of air outlets 12 are formed in the gaps between the plurality of annular disks 10 for the laminar wind to blow out.
  • the process of the air boundary layer 13 rotating from inside to outside to form laminar wind is centrifugal movement, so the speed when leaving the air outlet 12 is greater than the speed when entering the air inlet channel 11.
  • the pressure difference between the exhaust port 12 of the laminar flow fan 100 and the inlet of the air inlet channel 11 is the wind pressure.
  • the multiple air outlets 12 formed by the gaps between the multiple annular discs 10 can enable the laminar flow fan 100 to achieve 360° uniform air supply, avoiding the user from causing excessive air supply caused by the vertical air conditioner indoor unit 300. This kind of uncomfortable symptoms further enhance the user experience.
  • the air supply principle of the laminar flow fan 100 is mainly derived from the "Tesla turbine” discovered by Nikola Tesla. Tesla turbines mainly use the "laminar boundary layer effect” or “viscosity effect” of fluids to achieve the purpose of doing work on the "turbine disk”.
  • the laminar flow fan 100 of this embodiment drives the driving disc 30 through the laminar flow motor 20, and the driving disc 30 drives a plurality of annular discs 10 to rotate at a high speed.
  • the air in the interval of the annular discs 10 contacts and moves with each other, then they approach Due to the viscous shear force ⁇ , the air boundary layer 13 on the surface of each annular disk 10 is driven by the rotating annular disk 10 to rotate from inside to outside to form laminar wind.
  • FIG. 22 shows a schematic diagram of the viscous shear force distribution ⁇ (y) and velocity distribution u(y) of the air boundary layer 13.
  • the viscous shear force received by the air boundary layer 13 is actually the resistance generated by each annular disk 10 to the air boundary layer 13.
  • the abscissa axis in FIG. 22 refers to the distance in the moving direction of the air boundary layer 13, and the ordinate axis refers to the height of the air boundary layer 13 in a direction perpendicular to the moving direction.
  • v e is the airflow velocity at each point in the air boundary layer 13
  • ⁇ is the thickness of the air boundary layer 13
  • ⁇ w is the viscous shear force on the surface of the annular disk 10.
  • variable y in ⁇ (y) and u(y) refers to the height of the cross section of the air boundary layer 13 in the direction perpendicular to the direction of movement, and L is a certain point on the inner circumference of the annular disc 10 and a certain surface of the annular disc 10 The distance between one point. Then ⁇ (y) is the distribution of viscous shear force received when the height of the air boundary layer 13 section is y at this distance L; u(y) is at this distance L, the height of the air boundary layer 13 section is y The velocity distribution at time.
  • FIG. 27 is a schematic diagram of the connection between the laminar flow fan 100 and the laminar flow motor 20 in FIG. 23, and FIG. 28 is an exploded schematic view of the components of the laminar flow motor 20, the fixing plate 340 and the fixing frame 350.
  • the vertical air conditioner indoor unit 300 may further include a fixing plate 340 and a fixing frame 350.
  • One side of the fixing plate 340 is provided with a plurality of reinforcing ribs 341, and the other side is provided with a plurality of clamping slots 342.
  • the reinforcing ribs 341 can effectively improve the firmness of the fixing plate 340.
  • the fixing frame 350 is provided with a plurality of claws 351 corresponding to the plurality of clamping grooves 342 on the side facing the fixing plate 340, so as to fix the laminar flow motor 20 after the plurality of clamping claws 351 are respectively screwed to the plurality of clamping grooves 342 Between the fixing frame 350 and the fixing plate 340, a hole 352 is formed in the center of the fixing frame 350, and the output shaft 21 of the laminar flow motor 20 passes through the hole 352 and is fixed to the driving disc 30.
  • FIG. 29 is a schematic diagram of the connection of the laminar flow fan 100 with the conical protrusion 31 of the drive disc 30 and the laminar flow motor 20
  • FIG. 30 is a schematic diagram of the structure of the laminar flow fan 100 in FIG. 29 from another perspective
  • FIG. 31 is FIG. 29 A schematic cross-sectional view of the middle laminar flow fan 100.
  • the surface of the driving disc 30 of the laminar flow fan 100 in FIGS. 29 to 31 facing the laminar flow motor 20 is flat, and the surface facing the plurality of annular discs 10 has a conical protrusion 31 to guide the laminar flow fan 100 air flows and assists in the formation of laminar wind.
  • the main function of the driving disc 30 is to fix and receive the laminar flow motor 20, and to realize the connection with a plurality of annular discs 10 through a connecting piece, so as to drive the plurality of annular discs 10 to rotate when the laminar flow motor 20 drives the driving disc 30 to rotate. .
  • the output shaft 21 of the laminar flow motor 20 is fixedly arranged on the drive disc 30 after passing through the perforation 352 One side of the plane.
  • the connecting piece is a connecting piece 40
  • the cross section of the connecting piece 40 has two curves arranged in sequence along the direction of rotation of the annular disc 10, and the chord length of the two curves is the same as that of the laminar flow fan 100.
  • the air volume generated is linear.
  • the connecting piece 40 may be provided in plural, and penetrate the driving disc 30 and the plural annular discs 10 at even intervals.
  • a plurality of connecting pieces 40 penetrate the driving disc 30 and the plurality of annular discs 10 at even intervals, which can ensure that the connection relationship between the driving disc 30 and the plurality of annular discs 10 is stable, thereby ensuring that the laminar flow motor 20 drives the driving disc
  • the driving disc 30 can stably drive a plurality of annular discs 10 to rotate, which improves the working reliability of the laminar flow fan 100.
  • the two sections of curves 41 and 42 can be circular arcs, non-circular arcs, straight lines, etc., and the straight line can be used as a special curve.
  • the length of the chord line 51 may be the distance between the two ends of the curve 41 or the curve 42.
  • the length of the chord line 51 can be the cross section of the connecting piece 40 divided by the curve 41, The length of the line connecting the midpoint of the curve other than 42; if the curve 41 and the curve 42 intersect at only one end, the length of the chord line 51 can be the midpoint and the end of the intersection of the cross section of the connecting piece 40 except for the curves 41 and 42 The length of the connection.
  • the connecting piece 40 may be a double-arc blade 401, the cross-section of which has double-arcs sequentially arranged along the direction of rotation of the annular disc 10: inner arc 41 and back arc 42, and inner arc 41 and back
  • the arcs 42 all protrude in the direction in which the annular disc 10 rotates, have the same center and are arranged in parallel.
  • Figure 31 actually shows a cross-sectional schematic view of the laminar flow fan 100 when viewed from above.
  • the laminar flow motor 20 drives the annular disk 10 to rotate clockwise, and the convex direction of the back arc 42 and the inner arc 41 is the same as that of the annular disk 10 rotating.
  • the direction is the same.
  • the laminar flow motor 20 can also drive the annular disk 10 to rotate counterclockwise. At this time, the convex directions of the back arc 42 and the inner arc 41 can be opposite to those shown in FIG. 31.
  • FIG. 32 is a schematic diagram of the relationship between the length of the chord line 51 of the connecting piece 40 in FIG. 31 and the air volume and wind pressure. Since the connecting piece 40 of the laminar flow fan 100 in FIG. 31 is a double-arc blade 401, the distance between the two ends of the inner arc 41 is the same as the distance between the two ends of the back arc 42, and the length of the chord line 51 can be the inner arc 41 or the back arc. The distance between the two ends of the arc 42. In Fig.
  • the installation angle of the connecting piece 40 in this embodiment can be: on the same cross section of the connecting piece 40 and the annular disc 10, the chord line 51 between the two ends of the inner arc 41 and the annular disc passing through the midpoint of the chord line 51 The angle formed by the outer diameter 52 of 10.
  • the outer diameter of the annular disc 10 of the laminar flow fan 100 is 175mm
  • the inner diameter of the annular disc 10 is 115mm
  • the diameter of the annular disc 10 is 115mm.
  • the number of layers is 8 layers
  • the spacing of the annular disc 10 is 13.75mm
  • the thickness of the annular disc 10 is 2mm
  • the installation angle of the connecting piece 40 is 25.5°
  • the speed of the laminar flow motor 20 is 1000rpm (revolutions per minute, revolution/ Min)
  • the overall occupied volume of the laminar flow fan 100 needs to be restricted.
  • the outer and inner diameters of the annular disc 10 are constant, although the longer the string 51, the greater the air volume and pressure of the laminar flow fan 100, but the length of the string 51 must be restricted to avoid the connecting piece 10 Excessive penetration of the annular disk 10 causes the stability of the laminar flow fan 100 to decrease.
  • the length of the string 51 can be set to the maximum reachable range, so that the air volume and pressure of the laminar flow fan 100 can meet the user's requirements.
  • the length of the string 51 is set to the maximum reachable range: 40 mm to 42 mm. Moreover, when the length of the string 51 is set to 42 mm, the air volume of the laminar flow fan 100 can reach 1741 m 3 /h, and the wind pressure can reach 118.9 Pa, which can fully meet the user's needs. At this time, the difference between the outer diameter and the inner diameter of the annular disc 10 is 60mm, and the length of the chord line 51 is set to 42mm, so that the two ends of the inner arc 41 and the back arc 42 and the inner and outer circumferences of the annular disc 10 are about 9mm respectively. Distance, under the premise of ensuring the stability of the laminar flow fan 100, the length of the string 51 is set to the maximum reachable range, so that the air volume and pressure of the laminar flow fan 100 can meet the user's requirements.
  • FIG. 33 is a schematic diagram of the relationship between the installation angle ⁇ of the connecting piece 40 in FIG. 31 and the air volume and wind pressure of the suction side of the blade facing the incoming flow (Suction side upwind). Since the connecting piece 40 of the laminar flow fan 100 in FIG. 31 can be a double-arc blade 401, the installation angle ⁇ of the connecting piece 40 actually refers to: on the same cross-section of the double-arc blade 401 and the annular disk 10, The angle formed by the chord line 51 between the two ends of the arc 41 and the outer diameter 52 of the annular disc 10 passing through the midpoint of the chord line 51. The metal angle on the abscissa axis (Metal angle ( ⁇ )) in FIG.
  • FIG. 33 refers to the installation angle of the double arc blade 401 of the laminar flow fan 100, that is, on the same cross section of the double arc blade 401 and the annular disk 10, The angle formed by the chord line 51 between the two ends of the inner arc 41 and the outer diameter 52 of the annular disc 10 passing through the midpoint of the chord line 51.
  • the mass flow rate on the left ordinate axis (Mass flow rate) refers to the air volume
  • the pressure rise on the right ordinate axis refers to the wind pressure
  • the SS in the figure refers to the suction side facing the incoming flow (Suction side). upwind).
  • FIG. 33 shows that the outer diameter, inner diameter, number of layers, spacing, thickness, chord length of the double arc blade 401, and the rotation speed of the laminar flow motor 20 of the annular disk 10 of the laminar flow fan 100 remain unchanged.
  • the chord length of the double arc blade 401 in this embodiment may be the linear distance between the two ends of the inner arc 41 or the back arc 42.
  • the outer diameter of the annular disc 10 of the laminar flow fan 100 is 175mm
  • the inner diameter of the annular disc 10 is 115mm
  • the diameter of the annular disc 10 is 115mm.
  • the number of layers is 8; the spacing of the annular disc 10 is 13.75mm, the thickness of the annular disc 10 is 2mm, the chord length of the double-arc blade 401 is 35mm, and the speed of the laminar flow motor 20 is 1000rpm (revolutions per minute). /Min).
  • the installation angle ⁇ of the double-arc blade 401 can be set from -5° to 55°.
  • the installation angle ⁇ is A positive number; when the outer diameter 52 of the ring disk 10 passing through the midpoint of the chord line 51 and the chord line 51 between the two ends of the inner arc 41 in the direction of rotation of the ring disk 10 are in turn, the installation angle ⁇ is a negative number.
  • the laminar flow motor 20 drives the ring disk 10 to rotate clockwise, and the convex direction of the back arc 42 and the inner arc 41 is the same as that of the ring disk 10 rotating. The direction is the same. In some other embodiments, the laminar flow motor 20 can also drive the annular disk 10 to rotate counterclockwise. At this time, the convex directions of the back arc 42 and the inner arc 41 can be opposite to those shown in FIG. 34.
  • the installation angle ⁇ of the aviation blade 402 in FIG. 35 actually refers to: on the same cross section of the aviation blade 402 and the annular disk 10, the chord line 51 between the two ends of the inner arc 41 or the back arc 42 and the passing chord The angle formed by the outer diameter 52 of the annular disc 10 at the midpoint of the line 51.
  • FIG. 35 refers to the installation angle of the aviation blade 402 of the laminar flow fan 100, that is, on the same cross section of the aviation blade 402 and the annular disk 10, the inner arc 41 or The angle formed by the chord line 51 between the two ends of the back arc 42 and the outer diameter 52 of the annular disc 10 passing through the midpoint of the chord line 51.
  • Mass flow rate refers to the air volume
  • the pressure rise on the right ordinate axis refers to the wind pressure
  • the SS in the figure refers to the suction side facing the incoming flow (Suction side). upwind).
  • chord length of the aviation blade 402 in this embodiment may be the linear distance between the two ends of the inner arc 41 or the back arc 42, that is, the length of the chord line 51.
  • the outer diameter of the annular disc 10 of the laminar flow fan 100 is 175mm
  • the inner diameter of the annular disc 10 is 115mm
  • the diameter of the annular disc 10 is 115mm.
  • the spacing of the annular disc 10 is 13.75mm
  • the thickness of the annular disc 10 is 2mm
  • the chord length of the aviation blade 402 is 35mm
  • the speed of the laminar flow motor 20 is 1000rpm (revolutions per minute, revolutions per minute) )
  • the installation angle ⁇ of the aviation blade 402 can be set to -50° to 15°.
  • FIG. 36 is a schematic diagram of the connection between the laminar flow fan 100 and the laminar flow motor 20 with a gradual pitch of a plurality of annular discs 10
  • FIG. 37 is a schematic diagram of the connection of the laminar flow fan 100 and the laminar flow motor 20 in FIG. 36 from another perspective
  • FIG. 38 is 36 is a schematic diagram of the relationship between the gradual pitch of the plurality of annular disks 10 of the laminar flow fan 100 and the air volume and pressure.
  • the connecting member of the laminar flow fan 100 may also be a connecting rod 60.
  • the connecting rods 60 can also be provided in multiples and penetrate the driving disc 30 and the plurality of annular discs 10 at even intervals to ensure that the connection relationship between the driving disc 30 and the plurality of annular discs 10 is stable, thereby ensuring the laminar flow
  • the motor 20 drives the driving disc 30 to rotate
  • the driving disc 30 can stably drive a plurality of annular discs 10 to rotate, thereby improving the working reliability of the laminar flow fan 100.
  • the air volume of the laminar flow fan 100 will be effectively increased, so that the air output of the laminar flow fan 100 meets User needs.
  • the amount of change in the distance between two adjacent ring-shaped disks 10 is the same, that is, the distance between two adjacent ring-shaped disks 10 is changed from the side away from the drive disk 30. The same value increases to the other side.
  • the plate distance increase on the abscissa axis in FIG. 38 refers to the amount of change in the distance between two adjacent annular disks 10 in the direction from one side away from the driving disk 30 to the other side.
  • Shrinking, uniform and expanding refers to the decrease, constant and increase of the change.
  • the left ordinate axis mass flow rate (Mass flow rate) refers to air volume
  • the right ordinate axis pressure rise (Pressure rise) refers to wind pressure.
  • the amount of change in the spacing between two adjacent annular disks 10 is the same (the same), that is, the amount of increase or decrease in the spacing between two adjacent annular disks 10 is the same.
  • FIG. 38 shows that when the outer diameter, inner diameter, number, thickness, and rotation speed of the laminar flow motor 20 of the annular disc 10 of the laminar flow fan 100 remain unchanged, the pitch of the plurality of annular discs 10 gradually changes with the air volume.
  • Schematic diagram of the relationship with wind pressure As shown in FIG. 38, when the above-mentioned parameters remain unchanged, the distance between each two adjacent annular disks 10 in the plurality of annular disks 10 ranges from the side far from the driving disk 30 to The gradual change on the other side has a greater impact on the air volume and a small impact on the wind pressure.
  • the amount of change in the distance between two adjacent annular disks 10 in the direction from one side away from the driving disk 30 to the other side indicated by the axis of abscissa is a positive number
  • a plurality of annular disks 10 are described.
  • the distance between each two adjacent annular disks 10 gradually increases from one side far away from the driving disk 30 to the other side; when the abscissa axis represents the distance from the side far away from the driving disk 30 to
  • the amount of change in the distance between two adjacent annular disks 10 in the direction on the other side is negative, it means that the distance between every two adjacent annular disks 10 in the plurality of annular disks 10 changes from being away from the driving circle.
  • the disk 30 gradually shrinks from one side to the other side.
  • the air volume and pressure of the laminar flow fan 100 are very large. improve.
  • the distance between each two adjacent annular disks 10 in the plurality of annular disks 10 is set to gradually increase from one side far from the driving disk 30 to the other side. Big.
  • the outer diameter of the annular disc 10 of the laminar flow fan 100 is 175mm
  • the inner diameter of the annular disc 10 is 115mm
  • the number of the annular disc 10 is 8, and the thickness of the annular disc 10 is 2mm.
  • the rotation speed of the laminar flow motor 20 is 1000 rpm (revolutions per minute).
  • two adjacent annular discs can be set in the 8 annular discs 10
  • the spacing between 10 can be set in sequence from one side far from the drive disc 30 to the other side: 13.75mm, 14.75mm, 15.75mm, 16.75mm, 17.75mm, 18.75mm, 19.75mm, that is, two adjacent rings
  • the distance between the disks 10 increases by 1 mm from one side far away from the driving disk 30 to the other side.
  • the distance between two adjacent annular disks 10 in the plurality of annular disks 10 gradually increases from one side away from the driving disk 30 to the other side, which actually means that the distance between the two adjacent annular disks 10 is gradually increasing along the airflow. In the direction of flow in the wind channel 11, the distance between two adjacent annular disks 10 gradually increases.
  • FIG. 39 is a partial cross-sectional view of a laminar flow fan 100 with a gradual inner diameter of a plurality of annular disks 10
  • FIG. 40 is a schematic diagram of the relationship between the gradual inner diameter of the plurality of annular disks 10 of the laminar flow fan 100 in FIG. 39 and air volume and pressure.
  • the air volume of the laminar flow fan 100 is effectively increased, so that the air output of the laminar flow fan 100 meets the user's requirements.
  • the amount of change in the inner diameter of two adjacent annular discs 10 is the same, that is, the inner diameters of the plurality of annular discs 10 are reduced from one side away from the driving disc 30 to the other side.
  • the values are the same.
  • the inner radius increment of the abscissa axis in FIG. 40 refers to the amount of change between the inner diameter of each annular disc 10 and the inner diameter of the adjacent annular disc 10 below, shrinking, uniform, and expanding (shrinking uniform expansion) It means that the amount of change decreases, remains unchanged, and increases.
  • the left ordinate axis mass flow rate (Mass flow rate) refers to air volume
  • the right ordinate axis pressure rise (Pressure rise) refers to wind pressure.
  • FIG. 40 shows that when the outer diameter, spacing, number, thickness, and rotation speed of the laminar flow motor 20 of the annular disk 10 of the laminar flow fan 100 remain unchanged, the inner diameter of the plurality of annular disks 10 gradually changes and the air volume Schematic diagram of the relationship with wind pressure. As shown in FIG. 40, when the above-mentioned parameters remain unchanged, the inner diameter of the plurality of annular disks 10 gradually changes from one side far from the driving disk 30 to the other side, which has a greater impact on the air volume, The pressure effect is small.
  • the outer diameter of the annular disk 10 of the laminar flow fan 100 is 175 mm
  • the spacing of the annular disk 10 is 13.75 mm
  • the number of the annular disk 10 is 8, and the thickness of the annular disk 10 is 2mm
  • the rotation speed of the laminar flow motor 20 is 1000 rpm (revolutions per minute).
  • the inner diameter of each ring disk 10 can be set adjacent to the bottom
  • the amount of change in the inner diameter of the annular disc 10 is -5mm.
  • the inner diameters of the eight annular discs 10 can be set from one side far away from the driving disc 30 to the other side: 115mm, 110mm, 105mm, 100mm, 95mm, 90mm, 85mm, 80mm, the diameter of each annular disc 10
  • the inner diameter is 5 mm smaller than the inner diameter of the annular disc 10 adjacent below.
  • the distance between the annular disks 10 above specifically refers to the distance between two adjacent annular disks 10.
  • the inner diameters of the plurality of annular discs 10 gradually decrease from one side away from the driving disc 30 to the other side, which actually refers to the direction in which the airflow flows in the air inlet channel 11. The inner diameter of the disk 10 gradually decreases.
  • FIG. 41 is a schematic diagram of the central angle of the inner and outer diameters of the multiple ring disks 10 of the laminar flow fan 100 in which the ring disk 10 is an arc-shaped disk on the same longitudinal section passing through the central axis.
  • FIG. 42 is the diagram in FIG. 41 Schematic diagram of the relationship between the central angle and air volume and pressure.
  • Each annular disk 10 of the laminar flow fan 100 in FIG. 41 is an arc-shaped disk gradually approaching the driving disk 30 from the center to the edge and protruding toward the side of the driving disk 30.
  • the arc-shaped disk can make the angle at which the external air enters the laminar flow fan 100 more in line with the fluid flow, which is more conducive to the entry of the external air into the laminar flow fan 100 and effectively reduces air loss.
  • the inner diameters of the plurality of annular discs 10 gradually decrease from one side away from the driving disc 30 to the other side, and the inner and outer diameters of the plurality of annular discs 10 on the same longitudinal section passing through the central axis form a circle center. Angle ⁇ .
  • the abscissa axis ⁇ in Fig. 42 refers to the central angle of the connection between the inner and outer diameters of multiple annular disks 10 on the same longitudinal section passing through the central axis, and the left ordinate axis mass flow rate refers to the air volume. Pressure rise on the right ordinate axis refers to wind pressure.
  • FIG. 42 shows the relationship between the central angle ⁇ and the air volume and wind pressure when the outer diameter, number of layers, spacing, thickness, and rotation speed of the laminar flow motor 20 of the annular disk 10 of the laminar flow fan 100 remain unchanged. Schematic. As shown in FIG.
  • the air volume of the laminar flow fan 100 first increases and then decreases, while the wind pressure slightly increases.
  • the outer diameter of the annular disc 10 of the laminar flow fan 100 is 175 mm
  • the number of layers of the annular disc 10 is 10
  • the spacing of the annular disc 10 is 13.75 mm
  • the thickness of the annular disc 10 The speed of the laminar flow motor 20 is 1000 rpm (revolutions per minute).
  • the central angle ⁇ can be set from 9° to 30°.
  • the central angle ⁇ when the central angle ⁇ is set to 15°, the air volume of the laminar flow fan 100 reaches the maximum value.
  • the vertical air conditioner indoor unit 300 of this embodiment includes: a housing 310 with a cavity defined therein, and an air outlet 320 is opened on the upper part of the housing 310, and an air inlet 330 is provided at the middle and lower parts; a laminar flow fan 100 is provided Inside the cavity corresponding to the air outlet 320, it includes: a plurality of annular discs 10 arranged in parallel with each other and having the same central axis, the centers of the plurality of annular discs 10 collectively form an air inlet channel 11, and the cavity The air inside enters the gap between the plurality of annular disks 10 through the air inlet channel 11; and the laminar flow motor 20 is configured to drive the plurality of annular disks 10 to rotate so as to make the air boundary close to the surface of the plurality of annular disks 10 The layer 13 rotates and moves from the inside to the outside, so that the laminar wind blows out from the air outlet 320.
  • the indoor unit 300 of the vertical air conditioner is provided with a laminar flow
  • the laminar flow fan 100 further includes: a driving disc 30 arranged in parallel at intervals on one side of the plurality of annular discs 10; and a connecting piece that penetrates the driving disc 30 and a plurality of annular discs 10 to connect the plurality of annular discs 10 to the driving disc 30.
  • the laminar flow motor 20 is also configured to directly drive the driving disc 30 to rotate, and the driving disc 30 drives the plurality of annular discs.
  • the disk 10 rotates.
  • the laminar flow motor 20 is fixed between the fixing frame 350 and the fixing plate 340.
  • the fixing frame 350 is provided with a hole 352 in the center.
  • the output shaft 21 of the laminar flow motor 20 passes through the hole 352 and is fixed to the driving disc 30.
  • the multiple annular discs 10 of the laminar flow fan 100 can be arranged according to one or more of the following structures: the inner diameters of the multiple annular discs 10 are separated from each other by The drive disc 30 gradually decreases from one side to the other side; the distance between two adjacent annular discs 10 in the plurality of annular discs 10 gradually increases from one side away from the drive disc 30 to the other side; Each annular disk 10 is an arc-shaped disk gradually approaching the driving disk 30 from the center to the edge and protruding toward the side of the driving disk 30.
  • the connecting member may be a connecting piece 40.
  • the cross section of the connecting piece 40 has two curves arranged in sequence along the direction of rotation of the annular disc 10, and the chord length of the two curves has a linear relationship with the air volume generated by the laminar flow fan 100. .
  • the arrangement of the connecting piece 40 can effectively increase the wind pressure of the laminar flow fan 100, so that after the laminar air blows out through the gaps between the plurality of annular discs 10, due to the pressure difference, the air outside the laminar flow fan 100 passes through the inlet
  • the wind channel 11 is pressed into the annular disc 10 and reciprocates in this way, thereby forming a laminar air circulation.
  • the multiple air outlets 12 formed by the gaps between the multiple annular disks 10 can enable the laminar flow fan 100 to achieve 360° air supply, avoiding the user's various uncomfortable symptoms caused by direct air supply from the air conditioner, and further improving User experience.

Abstract

一种立式空调器室内机，包括：壳体(310)，其内部限定有空腔，且壳体(310)上部开设有出风口(320)，中下部设置有进风口(330)；层流风扇(100)，设置于对应出风口(320)的空腔内部，其包括：多个环形盘片(10)，彼此间隔地平行设置且具有相同的中心轴线，多个环形盘片(10)的中心共同形成有进风通道(11)，空腔内的空气通过进风通道(11)进入多个环形盘片(10)之间的间隙；以及层流电机(20)，配置成驱动多个环形盘片(10)旋转，以使靠近多个环形盘片(10)表面的空气边界层由内向外旋转移动，从而形成层流风由出风口(320)吹出。该立式空调器室内机设置有层流风扇，通过粘性效应实现层流送风，送风过程噪音小、风量高，有效提升用户的使用体验。

Description

立式空调器室内机 技术领域
本发明涉及家用电器技术领域，特别是涉及一种立式空调器室内机。
背景技术
随着社会发展以及人们的生活水平不断提高，各种空气调节装置已经成为人们日常生活中不可或缺的电气设备之一。各种空气调节装置可以在环境温度过高或过低时，帮助人们达到一个能够适应的温度。
目前的空调调节装置主要包括各种类型的空调器以及风扇，但是大部分用户认为目前的空调器产生的热气或者冷气在房间或密闭的空间内不均匀分布，具有一定的分布局限性。此外，空调器的室内机使用的风扇主要是离心风扇和贯流风扇。但是离心风扇和贯流风扇存在以下问题：由于离心风扇需要由几十个大体积叶片来提高风压和风量，导致离心风扇噪音很大，并且将离心风扇用于立式空调器室内机时，空气从进入离心风扇到送出空调器需进行两个90°的方向转折，每次方向转折都会有风量损失；贯流风扇虽然噪音较低，但是风压太小，送风距离短。并且贯流风扇整体体积大，而实际的有效体积小，造成空间浪费。
发明内容
本发明的一个目的是提供噪音小、风量高、风压大的立式空调器室内机。
本发明一个进一步的目的是使立式空调器室内机实现360°送风，避免出风直吹用户，提升用户的使用体验。
特别地，本发明提供了一种立式空调器室内机，包括：壳体，其内部限定有空腔，且壳体上部开设有出风口，中下部设置有进风口；层流风扇，设置于对应出风口的空腔内部，其包括：多个环形盘片，彼此间隔地平行设置且具有相同的中心轴线，多个环形盘片的中心共同形成有进风通道，空腔内的空气通过进风通道进入多个环形盘片之间的间隙；以及层流电机，配置成驱动多个环形盘片旋转，以使靠近多个环形盘片表面的空气边界层由内向外旋转移动，从而形成层流风由出风口吹出。
可选地，层流风扇还包括：驱动圆盘，间隔地平行设置于多个环形盘片的一侧；以及连接件，贯穿驱动圆盘和多个环形盘片，以将多个环形盘片连接至驱动圆盘，层流电机还配置成：直接驱动驱动圆盘旋转，进而由驱动圆盘带动多个环形盘片旋转。
可选地，立式空调器室内机还包括：固定板，其一侧设置有多条加强筋，另一侧设置有多个卡槽；以及固定架，朝向固定板的一侧设置有与多个卡槽对应的多个卡爪，以在多个卡爪分别螺接于多个卡槽之后将层流电机固定于固定架和固定板之间，其中固定架中心开设有穿孔，层流电机的输出轴穿过穿孔后与驱动圆盘固定。
可选地，立式空调器室内机还包括：引风圈，设置于多个环形盘片远离驱动圆盘的一侧，配置成引导通过进风口进入空腔的空气进入进风通道。
可选地，壳体在其上部环绕层流风扇一周设置出风口。
可选地，立式空调器室内机还包括：挡风件，设置于层流风扇的外部且具有缺口；壳体在其上部对应于缺口的位置设置出风口。
可选地，驱动圆盘的中心朝向多个环形盘片形成有凹槽，层流电机固定设置于凹槽中。
可选地，驱动圆盘朝向层流电机的表面为平面，朝向多个环形盘片的表面具有圆锥状的凸起部，以引导进入层流风扇的空气流动并协助形成层流风。
可选地，连接件为连接片，连接片的横截面具有沿环形盘片旋转的方向依次设置的两段曲线，两段曲线的弦线长度与层流风扇产生的风量为线性关系。
可选地，连接片的横截面具有沿环形盘片旋转的方向依次设置的双圆弧：内弧和背弧，且内弧和背弧均朝环形盘片旋转的方向凸起，内弧和背弧具有相同的圆心且平行设置或具有不同的圆心且两端均相交。
可选地，多个环形盘片按照以下结构中的一种或几种设置：多个环形盘片的内径由远离驱动圆盘的一侧至另一侧逐渐缩小；多个环形盘片中相邻两个环形盘片之间的间距由远离驱动圆盘的一侧至另一侧逐渐增大；每个环形盘片均为由中心至边缘逐渐靠近驱动圆盘且向驱动圆盘一侧凸起的弧形盘片。
本发明的立式空调器室内机，包括：壳体，其内部限定有空腔，且壳体上部开设有出风口，中下部设置有进风口；层流风扇，设置于对应出风口的空腔内部，其包括：多个环形盘片，彼此间隔地平行设置且具有相同的中心轴线，多个环形盘片的中心共同形成有进风通道，空腔内的空气通过进风通道进入多个环形盘片之间的间隙；以及层流电机，配置成驱动多个环形盘片旋转，以使靠近多个环形盘片表面的空气边界层由内向外旋转移动，从而形成层流风由出风口吹出。立式空调器室内机设置有层流风扇，通过粘性效应实现层流送风，送风过程噪音小、风量高，有效提升用户的使用体验。
进一步地，本发明的立式空调器室内机，层流风扇还包括：驱动圆盘，间隔地平行设置于多个环形盘片的一侧；以及连接件，贯穿驱动圆盘和多个环形盘片，以将多个环形盘片连接至驱动圆盘，层流电机还配置成：直接驱使驱动圆盘旋转，进而由驱动圆盘带动多个环形盘片旋转。层流电机固定于固定架和固定板之间，其中固定架中心开设有穿孔，层流电机的输出轴穿过穿孔后与驱动圆盘固定。可以有效增强层流风扇和层流电机的连接牢固度，提升整体工作可靠性。
更进一步地，本发明的立式空调器室内机，层流风扇的多个环形盘片可以按照以下结构中的一种或几种设置：多个环形盘片的内径由远离驱动圆盘的一侧至另一侧逐渐缩小；多个环形盘片中相邻两个环形盘片之间的间距由远离驱动圆盘的一侧至另一侧逐渐增大；每个环形盘片均为由中心至边缘逐渐靠近驱动圆盘且向驱动圆盘一侧凸起的弧形盘片。上述设置多个环形盘片的形式均可以有效提升层流风扇的风量，使得层流风扇的出风满足用户的使用需求。此外，连接件可以为连接片，连接片的横截面具有沿环形盘片旋转的方向依次设置的两段曲线，两段曲线的弦线长度与层流风扇产生的风量为线性关系。连接片的设置，可以有效提升层流风扇的风压，使得在层流风通过多个环形盘片之间的间隙吹出后，由于受到压差作用，层流风扇外部的空气通过进风通道被压入环形盘片，如此循环往复，从而形成层流空气循环。多个环形盘片彼此之间的间隙形成的多个排风口可以使得层流风扇实现360°送风，避免用户因空调器直吹送风而产生的多种不适症状，进一步提升用户的使用体验。
根据下文结合附图对本发明具体实施例的详细描述，本领域技术人员将会更加明了本发明的上述以及其他目的、优点和特征。
附图说明
后文将参照附图以示例性而非限制性的方式详细描述本发明的一些具体实施例。附图中相同的附图标记标示了相同或类似的部件或部分。本领域技术人员应该理解，这些附图未必是按比例绘制的。附图中：
图1是现有技术中立式空调器室内机采用离心风扇的送风示意图；
图2是根据本发明实施例一的立式空调器室内机的整体结构示意图；
图3是图2中立式空调器室内机的局部结构示意图；
图4是图2中立式空调器室内机的部件爆炸示意图；
图5是根据本发明实施例二的立式空调器室内机的整体结构示意图；
图6是图5中立式空调器室内机的局部结构示意图；
图7是图5中立式空调器室内机的部件爆炸示意图；
图8是根据本发明实施例三的立式空调器室内机的整体结构示意图；
图9是图8中立式空调器室内机的局部结构示意图；
图10是图8中立式空调器室内机的部件爆炸示意图；
图11是根据本发明实施例四的立式空调器室内机的整体结构示意图；
图12是图11中立式空调器室内机的局部结构示意图；
图13是图11中立式空调器室内机的部件爆炸示意图；
图14是根据本发明实施例五的立式空调器室内机的整体结构示意图；
图15是图14中立式空调器室内机的局部结构示意图；
图16是图14中立式空调器室内机的部件爆炸示意图；
图17是根据本发明实施例六的立式空调器室内机的整体结构示意图；
图18是图17中立式空调器室内机的局部结构示意图；
图19是图17中立式空调器室内机的部件爆炸示意图；
图20是根据本发明一个实施例的立式空调器室内机中层流风扇的空气循环示意图；
图21是根据本发明一个实施例的立式空调器室内机中层流风扇的送风原理示意图；
图22是根据本发明一个实施例的立式空调器室内机中层流风扇的速度分布和受力分布图；
图23是驱动圆盘具有凹槽的层流风扇的结构示意图；
图24是图23中层流风扇的另一视角的结构示意图；
图25是图23中层流风扇的又一视角的结构示意图；
图26是图23中层流风扇的剖视图；
图27是图23中层流风扇与层流电机的连接示意图；
图28是层流电机、固定板与固定架的部件爆炸示意图；
图29是驱动圆盘具有圆锥状凸起部的层流风扇与层流电机的连接示意图；
图30是图29中层流风扇的另一视角的结构示意图；
图31是图29中层流风扇的横截面示意图；
图32是图31中连接片的弦线长度与风量和风压的关系示意图；
图33是图31中连接片的安装角度与风量和风压的关系示意图；
图34是具有航空叶片的层流风扇的横截面示意图；
图35是图34中层流风扇的航空叶片的安装角度与风量和风压的关系示意图；
图36是多个环形盘片间距渐变的层流风扇与层流电机的连接示意图；
图37是图36中层流风扇与层流电机的另一视角的连接示意图；
图38是图36中层流风扇的多个环形盘片间距渐变与风量和风压的关系示意图；
图39是多个环形盘片内径渐变的层流风扇的局部剖视图；
图40是图39中层流风扇的多个环形盘片内径渐变与风量和风压的关系示意图；
图41是环形盘片为弧形盘片的层流风扇的多个环形盘片在经过中心轴线的同一纵截面上的内外径连线的圆心角示意图；以及
图42是图41中的圆心角与风量和风压的关系示意图。
具体实施方式
图1是现有技术中立式空调器室内机采用离心风扇的送风示意图。图1中的两个箭头示出了离心风扇200在应用于立式空调器室内机时送风过程中空气流动的方向，现有技术中的离心风扇200在应用于立式空调器室内机时由进风到出风的整个过程需要进行两次90°的转折，每次转折都会伴随着较多的风量损失。此外，离心风扇200一般需要由几十个大体积叶片来提高风压和风量，在离心风扇200工作时，叶片旋转与空气产生摩擦或发生冲击。离心风扇200的叶片较宽，且厚度大，因此在离心风扇200的电机高速运转时会产生非常大的噪音。此外，现有技术中还常 用贯流风扇，但是贯流风扇虽然噪音较低，但是风压太小，送风距离短；并且贯流风扇整体体积大，而实际的有效体积小，造成空间浪费。本实施例提供了一种立式空调器室内机，设置有层流风扇，通过粘性效应实现层流送风，送风过程噪音小、风量高、风压大，有效提升用户的使用体验。
图2是根据本发明实施例一的立式空调器室内机300的整体结构示意图，图3是图2中立式空调器室内机300的局部结构示意图，图4是图2中立式空调器室内机300的部件爆炸示意图。图5是根据本发明实施例二的立式空调器室内机300的整体结构示意图，图6是图5中立式空调器室内机300的局部结构示意图，图7是图5中立式空调器室内机300的部件爆炸示意图。图8是根据本发明实施例三的立式空调器室内机300的整体结构示意图，图9是图8中立式空调器室内机300的局部结构示意图，图10是图8中立式空调器室内机300的部件爆炸示意图。图11是根据本发明实施例四的立式空调器室内机300的整体结构示意图，图12是图11中立式空调器室内机300的局部结构示意图，图13是图11中立式空调器室内机300的部件爆炸示意图。图14是根据本发明实施例五的立式空调器室内机300的整体结构示意图，图15是图14中立式空调器室内机300的局部结构示意图，图16是图14中立式空调器室内机300的部件爆炸示意图。图17是根据本发明实施例六的立式空调器室内机300的整体结构示意图，图18是图17中立式空调器室内机300的局部结构示意图，图19是图17中立式空调器室内机300的部件爆炸示意图，图20是根据本发明一个实施例的立式空调器室内机300中层流风扇100的空气循环示意图，图21是根据本发明一个实施例的立式空调器室内机300中层流风扇100的送风原理示意图，图22是根据本发明一个实施例的立式空调器室内机300中层流风扇100的速度分布和受力分布图。图23是驱动圆盘30具有凹槽32的层流风扇100的结构示意图，图24是图23中层流风扇100的另一视角的结构示意图，图25是图23中层流风扇100的又一视角的结构示意图，图26是图23中层流风扇100的剖视图。如图2至图20所示，立式空调器室内机300一般性地可以包括：壳体310、层流风扇100和层流电机20。
其中，壳体310的内部限定有空腔，且壳体310上部开设有出风口320，中下部设置有进风口330。层流风扇100，设置于对应出风口320的空腔内部，其包括：多个环形盘片10，彼此间隔地平行设置且具有相同的中心轴线，多个环形盘片10的中心共同形成有进风通道11，空腔内的空气通过进风通道11进入多个环形盘片10之间的间隙。层流电机20，配置成驱动多个环形盘片旋转，以使靠近多个环形盘片表面的空气边界层13由内向外旋转移动，从而形成层流风由出风口320吹出。
具体地，层流电机20驱动多个环形盘片旋转，以使多个环形盘片与彼此之间的空气接触并相互运动，进而使靠近多个环形盘片表面的空气边界层13因粘性效应被旋转的多个环形盘片带动由内向外旋转移动形成层流风。多个环形盘片之间的间隙形成有多个排风口12，每个排风口12均能够实现360°送风，从排风口12排出的层流风通过出风口320吹出至立式空调器室内机300外部的环境中。层流风扇可以实现360°送风，但是出风口320可以根据实际情况进行设置，分别可以实现四面送风、三面送风、两面送风或单面送风。
立式空调器室内机300还可以包括蒸发器，设置于对应进风口330的空腔内部，配置成对通过进风口330进入空腔内的空气进行换热。其中蒸发器可以设置于层流风扇100的下方，具体可以是U型蒸发器381、平板蒸发器382或V型蒸发器等。此外，蒸发器下方可以设置有接水盘390，以承接蒸发器产生的冷凝水。壳体310可以包括：前面板311、后壳312、顶板313和底板314，其中后壳312包括后面板315和两个侧面板316。壳体310的出风口320处可以设置有导风板321，以调节立式空调器室内机300的出风方向。壳体310的进风口330处可以设置为进风栅的形式，能够将室内空气通过不同方向吸入空腔内部并对空气进行过滤。立式空调器室内机300还可以包括引风圈360，配置成引导通过进风口330进入空腔的空气进入进风通道11。具体地，引风圈360可以设置于蒸发器和层流风扇100之间，通过进风口330进入空腔的空气首先通 过蒸发器换热，换热后的空气通过引风圈360引导进入层流风扇100的进风通道11。
如图20所示，层流风扇100还可以包括：驱动圆盘30和连接件。其中驱动圆盘30间隔地平行设置于多个环形盘片10的一侧。连接件，贯穿驱动圆盘30和多个环形盘片10，以将多个环形盘片10连接至驱动圆盘30。如图23所示，连接件可以是连接片40。层流电机20还可以配置成：直接驱使驱动圆盘30旋转，进而由驱动圆盘30带动多个环形盘片10旋转。也就是说，上文中提到的层流电机20配置成驱动多个环形盘片10旋转是依赖于层流电机20先带动驱动圆盘30旋转，再由驱动圆盘30带动多个环形盘片10旋转。在一种具体的实施例中，驱动圆盘30的半径和多个环形盘片10的外径相同，可以均设置在一定的范围，例如170mm至180mm，从而对层流风扇100横向的占用体积进行约束，配合限定环形盘片10的数量和相邻两个环形盘片10之间的间距，对层流风扇100纵向的厚度进行约束，可以有效约束层流风扇100的整体占用体积。需要说明的是，环形盘片10的内径指的是其内圆周的半径；外径指的是其外圆周的半径。上述环形盘片10外径的具体数值仅为例举，而并非对本发明的限定。
以下对几个立式空调器室内机300的具体实施例进行介绍：
实施例一：如图2至图4所示，本实施例的立式空调器室内机300设置有U型蒸发器381，U型蒸发器381在空腔内部竖直放置且其横截面为U型，且U型开口朝向前面板311。进风口330设置于后壳312的后面板315和两个侧面板316，即三面进风。也就是说，U型蒸发器381与进风口330对应设置，从进风口330进入空腔的空气均能够经过U型蒸发器381换热。U型蒸发器381的前方还设置有隔板383，可以避免换热后的空气流向空腔前部，本实施例的隔板383为平板状。经过换热的空气通过引风圈360的引导作用进入层流风扇100的进风通道11，进而进入层流风扇100多个环形盘片之间。本实施例的立式空调器室内机300的壳体310在其上部环绕层流风扇100一周设置出风口320。具体地，本实施例的立式空调器室内机300的前面板311、后壳312的后面板315和两个侧面板316均设置有出风口320，层流风扇100形成的层流风从出风口320吹出，可以实现360°送风。
实施例二：如图5至图7所示，本实施例的立式空调器室内机300设置有U型蒸发器381，U型蒸发器381在空腔内部竖直放置且其横截面为U型，且U型开口朝向前面板311。进风口330设置于后壳312的后面板315和两个侧面板316，即三面进风。也就是说，U型蒸发器381与进风口330对应设置，从进风口330进入空腔的空气均能够经过U型蒸发器381换热。U型蒸发器381的前方还设置有隔板383，可以避免换热后的空气流向空腔前部，本实施例的隔板383为平板状。经过换热的空气通过引风圈360的引导作用进入层流风扇100的进风通道11，进而进入层流风扇100多个环形盘片之间。本实施例的立式空调器室内机300还包括：挡风件，设置于层流风扇100的外部且具有缺口373；壳体310在其上部对应于缺口373的位置设置出风口320。本实施例的立式空调器室内机300的挡风件可以为挡风板371，层流风扇100四周不被挡风板371遮挡的区域即为缺口373。具体地，本实施例的立式空调器室内机300的前面板311、后壳312的两个侧面板316设置有出风口320，层流风扇100形成的层流风从出风口320吹出，可以实现三面送风。
实施例三：如图8至图10所示，本实施例的立式空调器室内机300设置有平板蒸发器382，平板蒸发器382在空腔内部竖直放置且其与前面板311平行。进风口330设置于后壳312的后面板315，即单面进风。也就是说，平板蒸发器382与进风口330对应设置，从进风口330进入空腔的空气均能够经过平板蒸发器382换热。平板蒸发器382的前方还设置有隔板383，可以避免换热后的空气流向空腔前部，本实施例的隔板383为U型，且U型开口朝向平板蒸发器382。经过换热的空气通过引风圈360的引导作用进入层流风扇100的进风通道11，进而进入层流风扇100多个环形盘片之间。本实施例的立式空调器室内机300还包括：挡风件，设置于层流风扇100的外部且具有缺口373；壳体310在其上部对应于缺口373的位置设置出风口320。本实施例的立式空调器室内机300的挡风件可以为挡风板371，层流风扇100四周不被挡风板371遮挡的区 域即为缺口373。具体地，本实施例的立式空调器室内机300的前面板311、后壳312的两个侧面板316设置有出风口320，层流风扇100形成的层流风从出风口320吹出，可以实现三面送风。
实施例四：如图11至图13所示，本实施例的立式空调器室内机300设置有平板蒸发器382，平板蒸发器382在空腔内部竖直放置且其与前面板311平行。进风口330设置于后壳312的后面板315，即单面进风。也就是说，平板蒸发器382与进风口330对应设置，从进风口330进入空腔的空气均能够经过平板蒸发器382换热。平板蒸发器382的前方还设置有隔板383，可以避免换热后的空气流向空腔前部，本实施例的隔板383为U型，且U型开口朝向平板蒸发器382。经过换热的空气通过引风圈360的引导作用进入层流风扇100的进风通道11，进而进入层流风扇100多个环形盘片之间。本实施例的立式空调器室内机300还包括：挡风件，设置于层流风扇100的外部且具有缺口373；壳体310在其上部对应于缺口373的位置设置出风口320。本实施例的立式空调器室内机300的挡风件可以为挡风壳372，层流风扇100四周不被挡风壳372遮挡的区域即为缺口373。具体地，本实施例的立式空调器室内机300的前面板311设置有出风口320，层流风扇100形成的层流风从出风口320吹出，可以实现单面送风。
实施例五：如图14至图16所示，本实施例的立式空调器室内机300设置有V型蒸发器，V型蒸发器实际上为两个平板蒸发器382在空腔内由上至下逐渐远离壳体310，整体纵截面大致呈V型。进风口330设置于后壳312的两个侧面板316，即两面进风。也就是说，V型蒸发器与进风口330对应设置，从进风口330进入空腔的空气均能够经过V型蒸发器换热。V型蒸发器的前方和后方还均设置有隔板383，可以避免换热后的空气流向空腔前部和后部，本实施例的隔板383为平板状。经过换热的空气通过引风圈360的引导作用进入层流风扇100的进风通道11，进而进入层流风扇100多个环形盘片之间。本实施例的立式空调器室内机300的壳体310在其上部环绕层流风扇100一周设置出风口320。具体地，本实施例的立式空调器室内机300的前面板311、后壳312的后面板315和两个侧面板316均设置有出风口320，层流风扇100形成的层流风从出风口320吹出，可以实现360°送风。
实施例六：如图17至图19所示，本实施例的立式空调器室内机300设置有V型蒸发器，V型蒸发器实际上为两个平板蒸发器382在空腔内由上至下逐渐远离壳体310，整体纵截面大致呈V型。进风口330设置于后壳312的两个侧面板316，即两面进风。也就是说，V型蒸发器与进风口330对应设置，从进风口330进入空腔的空气均能够经过V型蒸发器换热。V型蒸发器的前方和后方还均设置有隔板383，可以避免换热后的空气流向空腔前部和后部，本实施例的隔板383为平板状。经过换热的空气通过引风圈360的引导作用进入层流风扇100的进风通道11，进而进入层流风扇100多个环形盘片之间。本实施例的立式空调器室内机300还包括：挡风件，设置于层流风扇100的外部且具有缺口373；壳体310在其上部对应于缺口373的位置设置出风口320。本实施例的立式空调器室内机300的挡风件可以为挡风板371，层流风扇100四周不被挡风板371遮挡的区域即为缺口373。具体地，本实施例的立式空调器室内机300的前面板311、后壳312的两个侧面板316设置有出风口320，层流风扇100形成的层流风从出风口320吹出，可以实现三面送风。
上述实施例中的挡风件，不管是挡风板371还是挡风壳372，缺口373均与出风口320对应设置。例如挡风板371可以使层流风扇100形成的层流风三面排出，则出风口320对应设置有三个；挡风壳372可以使层流风扇100形成的层流风单面排出，则出风口320对应设置有一个。挡风件可以保证层流风扇100形成的层流风除了通过出风口320吹出外，不会吹向空腔内的其他地方，避免影响空腔内其他部件的正常工作。
如图20所示，多个环形盘片10的中心共同形成有进风通道11，以使层流风扇100外部的空气进入。多个环形盘片10彼此之间的间隙形成有多个排风口12，以供层流风吹出。空气边界层13由内向外旋转移动形成层流风的过程是离心运动，因而离开排风口12时的速度要大于进入进风通道11时的速度。层流风扇100的排风口12与进风通道11进口处的压力差为风压。多个 环形盘片10彼此之间的间隙形成的多个排风口12可以使得层流风扇100实现360°均匀送风，避免用户因立式空调器室内机300直吹送风而产生的多种不适症状，进一步提升用户的使用体验。
层流风扇100的送风原理主要来源于尼古拉·特斯拉发现的“特斯拉涡轮机”。特斯拉涡轮机主要利用流体的“层流边界层效应”或者“粘性效应”实现对“涡轮盘片”做功的目的。本实施例的层流风扇100通过层流电机20驱使驱动圆盘30，驱动圆盘30带动多个环形盘片10高速旋转，各环形盘片10间隔内的空气接触并发生相互运动，则靠近各环形盘片10表面的空气边界层13因受粘性剪切力τ作用，被旋转的环形盘片10带动由内向外旋转移动形成层流风。
图22示出的就是空气边界层13受到的粘性剪切力分布τ(y)和速度分布u(y)的示意图。空气边界层13受到的粘性剪切力实际上是各环形盘片10对空气边界层13产生的阻力。图22中的横坐标轴指的是空气边界层13的的移动方向上的距离，纵坐标轴指的是空气边界层13在与移动方向垂直的方向上的高度。v e为空气边界层13内每一点的气流速度，δ为空气边界层13的厚度，τ w为环形盘片10表面处的粘性剪切力。τ(y)和u(y)中的变量y指的是空气边界层13在与移动方向垂直的方向上截面的高度，L为环形盘片10内圆周的某一点与环形盘片10表面某一点之间的距离。则τ(y)是在该距离L处，空气边界层13截面的高度为y时受到的粘性剪切力分布；u(y)是在该距离L处，空气边界层13截面的高度为y时的速度分布。
图23至图26所示的层流风扇100的驱动圆盘30的中心朝向多个环形盘片10形成有凹槽32，层流电机20固定设置于凹槽32中。图27是图23中层流风扇100与层流电机20的连接示意图，图28是层流电机20、固定板340与固定架350的部件爆炸示意图。如图27和图28所示，立式空调器室内机300还可以包括：固定板340和固定架350。其中固定板340的一侧设置有多条加强筋341，另一侧设置有多个卡槽342。其中加强筋341可以有效提高固定板340的牢固程度。固定架350，朝向固定板340的一侧设置有与多个卡槽342对应的多个卡爪351，以在多个卡爪351分别螺接于多个卡槽342之后将层流电机20固定于固定架350和固定板340之间，其中固定架350中心开设有穿孔352，层流电机20的输出轴21穿过穿孔352后与驱动圆盘30固定。对于图23至图26所示的层流风扇100，由于驱动圆盘30的中心朝向多个环形盘片10形成有凹槽32，层流电机20的输出轴21在穿过穿孔352后固定设置于驱动圆盘30的凹槽32中。
图29是驱动圆盘30具有圆锥状凸起部31的层流风扇100与层流电机20的连接示意图，图30是图29中层流风扇100的另一视角的结构示意图，图31是图29中层流风扇100的横截面示意图。图29至图31中的层流风扇100的驱动圆盘30朝向层流电机20的表面为平面，朝向多个环形盘片10的表面具有圆锥状的凸起部31，以引导进入层流风扇100的空气流动并协助形成层流风。
驱动圆盘30的主要作用在于固定承接层流电机20，并与多个环形盘片10通过连接件实现连接，以在层流电机20驱使驱动圆盘30旋转时带动多个环形盘片10旋转。对于图29至图31所示的层流风扇，由于驱动圆盘30朝向层流电机20的表面为平面，层流电机20的输出轴21在穿过穿孔352后固定设置于驱动圆盘30的平面一侧。而图29至图31所示的层流风扇100的驱动圆盘30朝向多个环形盘片10的表面具有圆锥状的凸起部31，可以有效引导通过进风通道11进入层流风扇100的空气进入各环形盘片10之间的间隙，进而提高形成层流风的效率。
在一种优选的实施例中，连接件为连接片40，连接片40的横截面具有沿环形盘片10旋转的方向依次设置的两段曲线，两段曲线的弦线长度与层流风扇100产生的风量为线性关系。连接片40可以设置为多个，且均匀间隔地贯穿驱动圆盘30和多个环形盘片10。多个连接片40均匀间隔地贯穿驱动圆盘30和多个环形盘片10，可以保证驱动圆盘30和多个环形盘片10的连接关系稳固，进而保证在层流电机20驱使驱动圆盘30旋转时，驱动圆盘30可以稳定地带动多个环形盘片10旋转，提高层流风扇100的工作可靠性。
需要说明的是，两段曲线41、42可以是圆弧、非圆弧的弧线、直线等线条，直线可以作为一种特殊的曲线。在曲线41两端点之间的距离与曲线42两端点之间的距离相同时，弦线51长 度可以是曲线41或曲线42两端点之间的距离。在曲线41两端点之间的距离与曲线42两端点之间的距离不同时，若曲线41和曲线42两端均不相交，则弦线51长度可以是连接片40的横截面除曲线41、42之外的曲线中点的连线长度；若曲线41和曲线42只有一端相交，则弦线51长度可以是连接片40的横截面除曲线41、42之外的曲线中点与相交的端点的连线长度。
如图31所示，连接片40可以为双圆弧叶片401，其横截面具有沿环形盘片10旋转的方向依次设置的双圆弧：内弧41和背弧42，且内弧41和背弧42均朝环形盘片10旋转的方向凸起，具有相同的圆心且平行设置。图31实际上示出的是俯视层流风扇100时的横截面示意图，层流电机20驱动环形盘片10顺时针旋转，背弧42和内弧41凸起的方向与环形盘片10旋转的方向一致。在其他一些实施例中，层流电机20还可以驱动环形盘片10逆时针旋转，此时的背弧42和内弧41的凸起方向可以与图31中示出的相反。
图32是图31中连接片40的弦线51长度与风量和风压的关系示意图。由于图31中层流风扇100的连接片40为双圆弧叶片401，内弧41两端点之间的距离和背弧42两端点之间的距离相同，弦线51长度可以是内弧41或背弧42两端点之间的距离。图32中横坐标轴叶弦(Blade chord)指的是层流风扇100的连接片40的弦线51长度，左纵坐标轴质量流速(Mass flow rate)指的是风量，右纵坐标轴压升(Pressure rise)指的是风压。具体地，图32示出的是在层流风扇100的环形盘片10外径、内径、层数、间距、厚度、连接片40的安装角度、层流电机20的转速均保持不变时，弦线51长度与风量和风压的关系示意图。本实施例的连接片40的安装角度可以是：在连接片40和环形盘片10的同一横截面上，内弧41两端点之间的弦线51与经过弦线51中点的环形盘片10的外径52形成的夹角。
在上述提及的各参数均保持不变时，例如在一种优选的实施例中，层流风扇100的环形盘片10外径为175mm，环形盘片10内径为115mm，环形盘片10的层数为8层，环形盘片10的间距为13.75mm，环形盘片10的厚度为2mm，连接片40的安装角度为25.5°，层流电机20的转速为1000rpm(revolutions per minute，转/分钟)，可以发现增加弦线51长度之后，风量和风压均有大幅度的提高，且基本呈线性。考虑到立式空调器室内机300的内在空间有限，对层流风扇100的整体占用体积需要有一定约束。在环形盘片10的外径和内径一定的情况下，虽然弦线51越长，层流风扇100的风量和风压越大，但是也要对弦线51长度进行一定的约束，避免连接片10过度贯穿环形盘片10，导致层流风扇100稳定度下降。总而言之，可以将弦线51长度设置为可达到的最大范围，使得层流风扇100的风量和风压能够满足用户的使用需求。
因此，在上述优选的实施例中，在保证层流风扇100的稳定度的前提下，将弦线51长度设置为可达到的最大范围为：40mm至42mm。并且，在将弦线51长度设置为42mm时，层流风扇100的风量可以达到1741m 3/h，风压可以达到118.9Pa，完全可以满足用户的使用需求。此时环形盘片10外径与内径之差为60mm，弦线51长度设置为42mm可以使得内弧41和背弧42的两端与环形盘片10的内圆周和外圆周分别有9mm左右的距离，在保证层流风扇100的稳定度的前提下，将弦线51长度设置为可达到的最大范围，使得层流风扇100的风量和风压能够满足用户的使用需求。
图33是图31中连接片40的安装角度α与叶片吸力面面向来流(Suction side upwind)的风量和风压的关系示意图。由于图31中层流风扇100的连接片40可以为双圆弧叶片401，连接片40的安装角度α实际上指的是：在双圆弧叶片401和环形盘片10的同一横截面上，内弧41两端点之间的弦线51与经过弦线51中点的环形盘片10的外径52形成的夹角。图33中横坐标轴金属角(Metal angle(α))指的是层流风扇100的双圆弧叶片401的安装角度，即在双圆弧叶片401和环形盘片10的同一横截面上，内弧41两端点之间的弦线51与经过弦线51中点的环形盘片10的外径52形成的夹角。左纵坐标轴质量流速(Mass flow rate)指的是风量，右纵坐标轴压升(Pressure rise)指的是风压，图中的SS面向来流指的是吸力面面向来流(Suction side upwind)。具体地，图33示出的是在层流风扇100的环形盘片10外径、内径、层数、间距、厚度、双圆弧 叶片401的弦长、层流电机20的转速均保持不变时，安装角度α与风量和风压的关系示意图。本实施例的双圆弧叶片401的弦长可以是内弧41或背弧42的两端点之间的直线距离。
在上述提及的各参数均保持不变时，例如在一种优选的实施例中，层流风扇100的环形盘片10外径为175mm，环形盘片10内径为115mm，环形盘片10的层数为8层，环形盘片10的间距为13.75mm，环形盘片10的厚度为2mm，双圆弧叶片401的弦长为35mm，层流电机20的转速为1000rpm(revolutions per minute，转/分钟)，此时综合风量和风压考虑，双圆弧叶片401的安装角度α可以设置为-5°至55°。需要说明的是，在沿环形盘片10旋转的方向上依次为内弧41两端点之间的弦线51、经过弦线51中点的环形盘片10的外径52时，安装角度α为正数；在沿环形盘片10旋转的方向上依次为经过弦线51中点的环形盘片10的外径52、内弧41两端点之间的弦线51时，安装角度α为负数。
图34是具有航空叶片402的层流风扇100的横截面示意图，图35是图34中层流风扇100的航空叶片402的安装角度α与风量和风压的关系示意图。在一种具体的实施例中，连接片40还可以是航空叶片402。航空叶片402的横截面具有朝环形盘片10旋转的方向凸起的双圆弧，且双圆弧包括沿环形盘片10旋转的方向依次设置的内弧41和背弧42，内弧41和背弧42具有不同的圆心且两端均相交。图34实际上示出的是俯视层流风扇100时的横截面示意图，层流电机20驱动环形盘片10顺时针旋转，背弧42和内弧41凸起的方向与环形盘片10旋转的方向一致。在其他一些实施例中，层流电机20还可以驱动环形盘片10逆时针旋转，此时的背弧42和内弧41的凸起方向可以与图34中示出的相反。
图35中的航空叶片402的安装角度α实际上指的是：在航空叶片402和环形盘片10的同一横截面上，内弧41或背弧42两端点之间的弦线51与经过弦线51中点的环形盘片10的外径52形成的夹角。图35中横坐标轴金属角(Metal angle(α))指的是层流风扇100的航空叶片402的安装角度，即在航空叶片402和环形盘片10的同一横截面上，内弧41或背弧42两端点之间的弦线51与经过弦线51中点的环形盘片10的外径52形成的夹角。左纵坐标轴质量流速(Mass flow rate)指的是风量，右纵坐标轴压升(Pressure rise)指的是风压，图中的SS面向来流指的是吸力面面向来流(Suction side upwind)。具体地，图35示出的是在层流风扇100的环形盘片10外径、内径、层数、间距、厚度、航空叶片402的弦长、层流电机20的转速均保持不变时，安装角度α与风量和风压的关系示意图。本实施例的航空叶片402的弦长可以是内弧41或背弧42的两端点之间的直线距离，即弦线51的长度。
在上述提及的各参数均保持不变时，例如在一种优选的实施例中，层流风扇100的环形盘片10外径为175mm，环形盘片10内径为115mm，环形盘片10的层数为8层，环形盘片10的间距为13.75mm，环形盘片10的厚度为2mm，航空叶片402的弦长为35mm，层流电机20的转速为1000rpm(revolutions per minute，转/分钟)，此时综合风量和风压考虑，航空叶片402的安装角度α可以设置为-50°至15°。
图36是多个环形盘片10间距渐变的层流风扇100与层流电机20的连接示意图，图37是图36中层流风扇100与层流电机20的另一视角的连接示意图，图38是图36中层流风扇100的多个环形盘片10间距渐变与风量和风压的关系示意图。
如图36和图37所示，层流风扇100的连接件还可以为连接杆60。连接杆60也可以设置为多个，且均匀间隔地贯穿驱动圆盘30和多个环形盘片10，以保证驱动圆盘30和多个环形盘片10的连接关系稳固，进而保证在层流电机20驱使驱动圆盘30旋转时，驱动圆盘30可以稳定地带动多个环形盘片10旋转，提高层流风扇100的工作可靠性。随着相邻两个环形盘片10之间的间距由远离驱动圆盘30的一侧至另一侧逐渐增大，会有效提升层流风扇100的风量，使得层流风扇100的出风满足用户的使用需求。在一种优选的实施例中，相邻两个环形盘片10之间的间距变化量相同，也就是说，相邻两个环形盘片10之间的间距由远离驱动圆盘30的一侧至另一侧增大的数值相同。
图38中横坐标轴叶片间距增量(Plate distance increase)指的是沿着由远离驱动圆盘30的一侧至另一侧的方向相邻两个环形盘片10之间的间距的变化量，收缩、一致和扩展(shrinking uniform expanding)指的是该变化量减小、不变和增大。左纵坐标轴质量流速(Mass flow rate)指的是风量，右纵坐标轴压升(Pressure rise)指的是风压。并且，相邻两个环形盘片10之间的间距变化量相同(一致)，也就是说，相邻两个环形盘片10之间的间距增大或缩小的数值相同。
具体地，图38示出的是在层流风扇100的环形盘片10外径、内径、数量、厚度、层流电机20的转速均保持不变时，多个环形盘片10间距渐变与风量和风压的关系示意图。如图38所示，在上述提及的各参数均保持不变时，多个环形盘片10中每两个相邻的环形盘片10之间的间距由远离驱动圆盘30的一侧至另一侧逐渐变化对风量影响较大，对风压影响很小。当横坐标轴表示的沿着由远离驱动圆盘30的一侧至另一侧的方向相邻两个环形盘片10之间的间距的变化量为正数时，说明多个环形盘片10中每两个相邻的环形盘片10之间的间距由远离驱动圆盘30的一侧至另一侧逐渐增大；当横坐标轴表示的沿着由远离驱动圆盘30的一侧至另一侧的方向相邻两个环形盘片10之间的间距的变化量为负数时，说明多个环形盘片10中每两个相邻的环形盘片10之间的间距由远离驱动圆盘30的一侧至另一侧逐渐缩小。
由图38可知，多个环形盘片10中每两个相邻的环形盘片10之间的间距变化量为-1mm、1mm和2mm时，层流风扇100的风量和风压均有很大的改善。综合考虑层流风扇100的风量和风压，将多个环形盘片10中每两个相邻的环形盘片10之间的间距设置为由远离驱动圆盘30的一侧至另一侧逐渐增大。在一种优选的实施例中，层流风扇100的环形盘片10外径为175mm，环形盘片10内径为115mm，环形盘片10的数量为8个，环形盘片10的厚度为2mm，层流电机20的转速为1000rpm(revolutions per minute，转/分钟)，此时综合层流风扇100的风量与风压的全面考虑，可以设置8个环形盘片10中相邻两个环形盘片10之间的间距由远离驱动圆盘30的一侧至另一侧可以依次设置为：13.75mm、14.75mm、15.75mm、16.75mm、17.75mm、18.75mm、19.75mm，即相邻两个环形盘片10之间的间距由远离驱动圆盘30的一侧至另一侧依次增大1mm。需要说明的是，多个环形盘片10中相邻两个环形盘片10之间的间距由远离驱动圆盘30的一侧至另一侧逐渐增大，实际上是指沿着气流在进风通道11中流动的方向，相邻两个环形盘片10之间的间距逐渐增大。
图39是多个环形盘片10内径渐变的层流风扇100的局部剖视图，图40是图39中层流风扇100的多个环形盘片10内径渐变与风量和风压的关系示意图。随着多个环形盘片10的内径由远离驱动圆盘30的一侧至另一侧逐渐缩小，会有效提升层流风扇100的风量，使得层流风扇100的出风满足用户的使用需求。在一种优选的实施例中，相邻两个环形盘片10的内径变化量相同，也就是说，多个环形盘片10的内径由远离驱动圆盘30的一侧至另一侧缩小的数值相同。
图40中横坐标轴内径增量(Inner radius increase)指的是每一个环形盘片10的内径与下方相邻的环形盘片10的内径的变化量，收缩、一致和扩展(shrinking uniform expanding)指的是该变化量减小、不变和增大。左纵坐标轴质量流速(Mass flow rate)指的是风量，右纵坐标轴压升(Pressure rise)指的是风压。具体地，图40示出的是在层流风扇100的环形盘片10外径、间距、数量、厚度、层流电机20的转速均保持不变时，多个环形盘片10内径渐变与风量和风压的关系示意图。如图40所示，在上述提及的各参数均保持不变时，多个环形盘片10的内径由远离驱动圆盘30的一侧至另一侧逐渐变化对风量影响较大，对风压影响很小。当横坐标轴表示的每一个环形盘片10的内径与下方相邻的环形盘片10的内径的变化量为正数时，说明多个环形盘片10的内径由远离驱动圆盘30的一侧至另一侧逐渐增加；当横坐标轴表示的每一个环形盘片10的内径与下方相邻的环形盘片10的内径的变化量为负数时，说明多个环形盘片10的内径由远离驱动圆盘30的一侧至另一侧逐渐缩小。
由图40可知，多个环形盘片10的内径由远离驱动圆盘30的一侧至另一侧逐渐缩小时，层流风扇100的风量有所增加，风压稍有减小；多个环形盘片10的内径由远离驱动圆盘30的一侧 至另一侧逐渐增加时，层流风扇100的风压稍有增加，风量减小很多。因而综合考虑层流风扇100的风量和风压，将多个环形盘片10的内径设置为由远离驱动圆盘30的一侧至另一侧逐渐缩小。
在一种优选的实施例中，层流风扇100的环形盘片10外径为175mm，环形盘片10的间距为13.75mm，环形盘片10的数量为8个，环形盘片10的厚度为2mm，层流电机20的转速为1000rpm(revolutions per minute，转/分钟)，此时综合层流风扇100的风量与风压的全面考虑，可以设置每一个环形盘片10的内径与下方相邻的环形盘片10的内径的变化量为-5mm。即8个环形盘片10的内径由远离驱动圆盘30的一侧至另一侧可以依次设置为：115mm、110mm、105mm、100mm、95mm、90mm、85mm、80mm，每一个环形盘片10的内径都比下方相邻的环形盘片10的内径缩小5mm。需要说明的是，上文中环形盘片10的间距具体指的是相邻两个环形盘片10之间的间距。而且需要强调的是，多个环形盘片10的内径由远离驱动圆盘30的一侧至另一侧逐渐缩小，实际上是指沿着气流在进风通道11中流动的方向，多个环形盘片10的内径逐渐缩小。
图41是环形盘片10为弧形盘片的层流风扇100的多个环形盘片10在经过中心轴线的同一纵截面上的内外径连线的圆心角示意图，图42是图41中的圆心角与风量和风压的关系示意图。图41中的层流风扇100的每个环形盘片10均为由中心至边缘逐渐靠近驱动圆盘30且向驱动圆盘30一侧凸起的弧形盘片。弧形盘片相较平面盘片可以使得外部空气进入层流风扇100的角度更加符合流体流动，从而更利于外部的空气进入层流风扇100，有效减少风量损失。此外，多个环形盘片10的内径由远离驱动圆盘30的一侧至另一侧逐渐缩小，且多个环形盘片10在经过中心轴线的同一纵截面上的内外径连线形成有圆心角θ。
图42中横坐标轴θ指的是多个环形盘片10在经过中心轴线的同一纵截面上的内外径连线的圆心角，左纵坐标轴质量流速(Mass flow rate)指的是风量，右纵坐标轴压升(Pressure rise)指的是风压。具体地，图42示出的是在层流风扇100的环形盘片10外径、层数、间距、厚度、层流电机20的转速均保持不变时，圆心角θ与风量和风压的关系示意图。如图42所示，在上述提及的各参数均保持不变时，随着圆心角θ逐渐增大，层流风扇100的风量先增大后减小，而风压有少许上升。在一种优选的实施例中，层流风扇100的环形盘片10外径为175mm，环形盘片10的层数为10层，环形盘片10的间距为13.75mm，环形盘片10的厚度为2mm，层流电机20的转速为1000rpm(revolutions per minute，转/分钟)，此时综合风量和风压考虑，多个环形盘片10在经过中心轴线的同一纵截面上的内外径连线的圆心角θ可以设置为9°至30°。并且如图42所示，在圆心角θ设置为15°时，层流风扇100的风量达到最大值。
本实施例的立式空调器室内机300，包括：壳体310，其内部限定有空腔，且壳体310上部开设有出风口320，中下部设置有进风口330；层流风扇100，设置于对应出风口320的空腔内部，其包括：多个环形盘片10，彼此间隔地平行设置且具有相同的中心轴线，多个环形盘片10的中心共同形成有进风通道11，空腔内的空气通过进风通道11进入多个环形盘片10之间的间隙；以及层流电机20，配置成驱动多个环形盘片10旋转，以使靠近多个环形盘片10表面的空气边界层13由内向外旋转移动，从而形成层流风由出风口320吹出。立式空调器室内机300设置有层流风扇100，通过粘性效应实现层流送风，送风过程噪音小、风量高，有效提升用户的使用体验。
进一步地，本实施例的立式空调器室内机300，层流风扇100还包括：驱动圆盘30，间隔地平行设置于多个环形盘片10的一侧；以及连接件，贯穿驱动圆盘30和多个环形盘片10，以将多个环形盘片10连接至驱动圆盘30，层流电机20还配置成：直接驱使驱动圆盘30旋转，进而由驱动圆盘30带动多个环形盘片10旋转。层流电机20固定于固定架350和固定板340之间，其中固定架350中心开设有穿孔352，层流电机20的输出轴21穿过穿孔352后与驱动圆盘30固定。可以有效增强层流风扇100和层流电机20的连接牢固度，提升整体工作可靠性。
更进一步地，本实施例的立式空调器室内机300，层流风扇100的多个环形盘片10可以按 照以下结构中的一种或几种设置：多个环形盘片10的内径由远离驱动圆盘30的一侧至另一侧逐渐缩小；多个环形盘片10中相邻两个环形盘片10之间的间距由远离驱动圆盘30的一侧至另一侧逐渐增大；每个环形盘片10均为由中心至边缘逐渐靠近驱动圆盘30且向驱动圆盘30一侧凸起的弧形盘片。上述设置多个环形盘片10的形式均可以有效提升层流风扇100的风量，使得层流风扇100的出风满足用户的使用需求。此外，连接件可以为连接片40，连接片40的横截面具有沿环形盘片10旋转的方向依次设置的两段曲线，两段曲线的弦线长度与层流风扇100产生的风量为线性关系。连接片40的设置，可以有效提升层流风扇100的风压，使得在层流风通过多个环形盘片10之间的间隙吹出后，由于受到压差作用，层流风扇100外部的空气通过进风通道11被压入环形盘片10，如此循环往复，从而形成层流空气循环。多个环形盘片10彼此之间的间隙形成的多个排风口12可以使得层流风扇100实现360°送风，避免用户因空调器直吹送风而产生的多种不适症状，进一步提升用户的使用体验。
本领域技术人员应理解，在没有特别说明的情况下，本发明实施例中所称的“上”、“下”、“左”、“右”、“前”、“后”等用于表示方位或位置关系的用语是以立式空调器室内机300的实际使用状态为基准而言的，这些用语仅是为了便于描述和理解本发明的技术方案，而不是指示或暗示所指的装置或部件必须具有特定的方位，因此不能理解为对本发明的限制。
至此，本领域技术人员应认识到，虽然本文已详尽示出和描述了本发明的多个示例性实施例，但是，在不脱离本发明精神和范围的情况下，仍可根据本发明公开的内容直接确定或推导出符合本发明原理的许多其他变型或修改。因此，本发明的范围应被理解和认定为覆盖了所有这些其他变型或修改。

Claims (11)

  1. 一种立式空调器室内机，包括：
    壳体，其内部限定有空腔，且所述壳体上部开设有出风口，中下部设置有进风口；
    层流风扇，设置于对应所述出风口的所述空腔内部，其包括：多个环形盘片，彼此间隔地平行设置且具有相同的中心轴线，多个所述环形盘片的中心共同形成有进风通道，所述空腔内的空气通过所述进风通道进入所述多个环形盘片之间的间隙；以及
    层流电机，配置成驱动所述多个环形盘片旋转，以使靠近所述多个环形盘片表面的空气边界层由内向外旋转移动，从而形成层流风由所述出风口吹出。
  2. 根据权利要求1所述的立式空调器室内机，其中，
    所述层流风扇还包括：驱动圆盘，间隔地平行设置于所述多个环形盘片的一侧；以及连接件，贯穿所述驱动圆盘和所述多个环形盘片，以将所述多个环形盘片连接至所述驱动圆盘；所述层流电机还配置成：直接驱动所述驱动圆盘旋转，进而由所述驱动圆盘带动所述多个环形盘片旋转。
  3. 根据权利要求2所述的立式空调器室内机，还包括：
    固定板，其一侧设置有多条加强筋，另一侧设置有多个卡槽；以及
    固定架，朝向所述固定板的一侧设置有与所述多个卡槽对应的多个卡爪，以在所述多个卡爪分别螺接于所述多个卡槽之后将所述层流电机固定于所述固定架和所述固定板之间，其中所述固定架中心开设有穿孔，所述层流电机的输出轴穿过所述穿孔后与所述驱动圆盘固定。
  4. 根据权利要求2所述的立式空调器室内机，还包括：
    引风圈，设置于所述多个环形盘片远离所述驱动圆盘的一侧，配置成引导通过所述进风口进入所述空腔的空气进入所述进风通道。
  5. 根据权利要求1所述的立式空调器室内机，其中，
    所述壳体在其上部环绕所述层流风扇一周设置所述出风口。
  6. 根据权利要求1所述的立式空调器室内机，还包括：挡风件，设置于所述层流风扇的外部且具有缺口；所述壳体在其上部对应于所述缺口的位置设置所述出风口。
  7. 根据权利要求2所述的立式空调器室内机，其中，所述驱动圆盘的中心朝向所述多个环形盘片形成有凹槽，所述层流电机固定设置于所述凹槽中。
  8. 根据权利要求2所述的立式空调器室内机，其中，
    所述驱动圆盘朝向所述层流电机的表面为平面，朝向所述多个环形盘片的表面具有圆锥状的凸起部，以引导进入所述层流风扇的空气流动并协助形成所述层流风。
  9. 根据权利要求2所述的立式空调器室内机，其中，
    所述连接件为连接片，所述连接片的横截面具有沿所述环形盘片旋转的方向依次设置的两段曲线，所述两段曲线的弦线长度与所述层流风扇产生的风量为线性关系。
  10. 根据权利要求9所述的立式空调器室内机，其中，
    所述连接片的横截面具有沿所述环形盘片旋转的方向依次设置的双圆弧：内弧和背弧，且所述内弧和所述背弧均朝所述环形盘片旋转的方向凸起，所述内弧和所述背弧具有相同的圆心且平行设置或具有不同的圆心且两端均相交。
  11. 根据权利要求2所述的立式空调器室内机，其中，所述多个环形盘片按照以下结构中的一种或几种设置：
    所述多个环形盘片的内径由远离所述驱动圆盘的一侧至另一侧逐渐缩小；
    所述多个环形盘片中相邻两个所述环形盘片之间的间距由远离所述驱动圆盘的一侧至另一侧逐渐增大；
    每个所述环形盘片均为由中心至边缘逐渐靠近所述驱动圆盘且向所述驱动圆盘一侧凸起的弧形盘片。
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CN209840264U (zh) * 2019-01-17 2019-12-24 青岛海尔空调器有限总公司 立式空调器室内机
CN209877119U (zh) * 2019-01-17 2019-12-31 青岛海尔空调器有限总公司 立式空调器室内机
CN209877122U (zh) * 2019-01-17 2019-12-31 青岛海尔空调器有限总公司 立式空调器室内机
CN209877123U (zh) * 2019-01-17 2019-12-31 青岛海尔空调器有限总公司 立式空调器室内机
CN209877120U (zh) * 2019-01-17 2019-12-31 青岛海尔空调器有限总公司 立式空调器室内机

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