WO2021218292A1 - 离心风机及具有该离心风机的窗机空调 - Google Patents

离心风机及具有该离心风机的窗机空调 Download PDF

Info

Publication number
WO2021218292A1
WO2021218292A1 PCT/CN2021/076472 CN2021076472W WO2021218292A1 WO 2021218292 A1 WO2021218292 A1 WO 2021218292A1 CN 2021076472 W CN2021076472 W CN 2021076472W WO 2021218292 A1 WO2021218292 A1 WO 2021218292A1
Authority
WO
WIPO (PCT)
Prior art keywords
volute
fan
centrifugal fan
air
air outlet
Prior art date
Application number
PCT/CN2021/076472
Other languages
English (en)
French (fr)
Inventor
李英舒
徐志腾
吴强
吴涛
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 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 WO2021218292A1 publication Critical patent/WO2021218292A1/zh

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/028—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by air supply means, e.g. fan casings, internal dampers or ducts
    • F24F1/0284—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by air supply means, e.g. fan casings, internal dampers or ducts with horizontally arranged fan axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/022—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing comprising a compressor cycle
    • F24F1/027—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing comprising a compressor cycle mounted in wall openings, e.g. in windows
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/028—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by air supply means, e.g. fan casings, internal dampers or ducts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/03—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by mounting arrangements
    • F24F1/031—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by mounting arrangements penetrating a wall or window
    • 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
    • F24F13/20—Casings or covers
    • 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
    • F24F13/24—Means for preventing or suppressing noise
    • F24F2013/247—Active noise-suppression

Definitions

  • the invention relates to the field of air conditioning, in particular to a centrifugal fan and a window machine air conditioner with the centrifugal fan.
  • the overall size of the existing window air conditioners is getting smaller and smaller, but the requirements for air supply performance such as air volume and noise are getting higher and higher.
  • Fig. 1 is a schematic axonometric view of a volute of a centrifugal fan for a window machine air conditioner in the prior art
  • Fig. 2 is a volute shown in Fig. 1 extending along the rotation axis of the centrifugal fan and along the extension direction of the air outlet of the fan
  • the existing window air conditioner adopts a single-suction centrifugal fan with two volute side walls of the volute both being flat plates. It mainly relies on optimizing the centrifugal fan itself and the air duct profile of the volute. To improve the air supply performance, the production process requirements are too high. Comprehensive considerations require a high air volume, low noise and low cost centrifugal fan for window machine air conditioners and a window machine air conditioner with the centrifugal fan.
  • One objective of the first aspect of the present invention is to overcome at least one technical defect in the prior art and provide a centrifugal fan with a novel volute structure.
  • a further object of the first aspect of the present invention is to increase the air supply volume of the centrifugal fan.
  • Another further object of the first aspect of the present invention is to avoid an increase in noise.
  • An object of the second aspect of the present invention is to provide a window machine air conditioner with the centrifugal fan.
  • a centrifugal fan which is characterized in that it comprises:
  • the volute is provided with a fan inlet and a fan outlet;
  • the centrifugal fan is arranged in the volute and is configured to promote air to flow from the air inlet of the fan to the air outlet of the fan;
  • the air outlet of the fan is arranged to open along the thickness direction of the volute;
  • the side wall of the volute far away from the air outlet of the fan includes a flat plate portion and a convex portion arched away from the air outlet of the fan relative to the flat plate portion, so as to be in the interior of the volute. Form a cavity.
  • the distance between the cavity in the thickness direction of the volute is 20 times the maximum distance between the flat plate portion and the other side wall of the volute in the thickness direction of the volute. % ⁇ 40%.
  • the protrusion is provided at a position of the side wall of the volute corresponding to an outlet section of the volute peripheral wall of the volute.
  • the air outlet of the fan is arranged to extend perpendicular to the outlet section;
  • the size of the cavity in the extending direction of the air outlet of the fan is 20%-40% of the internal size of the volute passing through the rotation axis of the centrifugal fan in the extending direction of the air outlet of the fan.
  • the distance between the side wall of the volute and an imaginary plane perpendicular to the axis of rotation of the centrifugal fan and located between the two side walls of the volute varies with the distance between the side wall of the volute and the outlet section. As the distance increases, it decreases accordingly.
  • the protrusion includes:
  • the main body is arranged to be parallel to the flat plate part and to be spaced apart from the flat plate part in the thickness direction;
  • the transition section is arranged to extend obliquely from the main body to a direction close to the flat portion.
  • the air inlet of the fan is opened on another side wall of the volute, and the side wall of the other volute is a flat plate.
  • the air inlet of the fan is opened on another side wall of the volute.
  • the air outlet of the fan is arranged on a side of the air inlet of the fan away from the protrusion.
  • a window air conditioner which is characterized in that it comprises:
  • the cabinet has an indoor air inlet and an indoor air outlet;
  • the centrifugal fan according to any one of the above is arranged in the casing and configured to promote the flow of indoor air from the indoor air inlet to the indoor air outlet.
  • the window machine air conditioner further includes:
  • the indoor heat exchanger is arranged on the air inlet flow path between the indoor air inlet and the centrifugal fan to exchange heat with the indoor air flowing in from the indoor air inlet.
  • the centrifugal fan of the present invention is based on the existing centrifugal fan by providing protrusions on the side wall of the volute away from the air outlet of the fan, that is, a cavity away from the air outlet of the fan is formed inside the volute, and the volute is increased.
  • the air storage volume of the air duct significantly increases the air supply volume of the centrifugal fan with almost no increase in noise. It is especially suitable for window air conditioners that have high requirements on the size and air volume of the occupied space.
  • the protrusion is arranged at a position corresponding to the outlet section of the peripheral wall of the volute, and the dimensions of the protrusion in the thickness direction of the volute and the extension direction of the fan outlet are defined as the corresponding directions. 20% to 40% of the internal size of the volute, compared to arranging the protrusions in other positions, further increases the air supply volume of the centrifugal fan, reduces or even avoids the layout of other structures in the window air conditioner This prevents the overall size of the window air conditioner from increasing. After testing, the present invention improves 10.6% of the actual measured air volume compared with the prior art.
  • the protrusion is set to extend from the edge of the peripheral wall of the volute parallel to the flat part, and then extend obliquely towards the direction of the flat part, so as to avoid the formation of gas vortex, make the gas flow more smoothly, and avoid The increase in noise improves the user experience.
  • Fig. 1 is a schematic axonometric view of a volute of a centrifugal fan for a window machine air conditioner in the prior art
  • FIG. 2 is a schematic cross-sectional view of the volute shown in FIG. 1 taken along a plane passing through the rotation axis of the centrifugal fan and extending along the extension direction of the air outlet of the fan;
  • Fig. 3 is a schematic axonometric view of a window machine air conditioner according to an embodiment of the present invention.
  • FIG. 4 is a schematic cross-sectional view of the window machine air conditioner shown in FIG. 3 taken along a vertical plane extending in a front-to-rear direction;
  • Fig. 5 is a schematic cross-sectional view of the window machine air conditioner shown in Fig. 3 taken along a horizontal plane;
  • Fig. 6 is a schematic axonometric view of the volute in Fig. 5;
  • FIG. 7 is a schematic cross-sectional view of the volute shown in FIG. 6 taken along a plane passing through the rotation axis of the centrifugal fan and extending along the extension direction of the air outlet of the fan;
  • Fig. 8 is a gas flow field diagram in the vertical direction measured on the volute shown in Fig. 1;
  • Fig. 9 is a gas flow field diagram in the horizontal direction measured on the volute shown in Fig. 1;
  • Fig. 10 is a gas flow field diagram in the vertical direction measured on the volute shown in Fig. 6;
  • Fig. 11 is a diagram of the gas flow field in the horizontal direction measured on the volute shown in Fig. 6.
  • Fig. 3 is a schematic isometric view of a window machine air conditioner 200 according to an embodiment of the present invention
  • Fig. 4 is a schematic cross-sectional view of the window machine air conditioner 200 shown in Fig. 3 taken along a vertical plane extending in a front-to-rear direction
  • Fig. 5 is a view 3 shows a schematic cross-sectional view of the window machine air conditioner 200 taken along a horizontal plane.
  • the window machine air conditioner 200 may include a cabinet 210 and a centrifugal fan 100.
  • the cabinet 210 may be divided into an indoor side located in an indoor environment and an outdoor side located in an outdoor environment. Wherein, an indoor air inlet 211 and an indoor air outlet 212 may be opened on the indoor side. An outdoor air inlet 213 and an outdoor air outlet 214 can be opened on the outdoor side.
  • the centrifugal fan 100 may be disposed in the casing 210 and configured to promote the flow of indoor air from the indoor air inlet 211 to the indoor air outlet 212, thereby promoting air flow in the indoor environment.
  • the centrifugal fan 100 may include a volute 110 provided with at least one fan air inlet 117 and a fan air outlet 116, and a centrifugal fan arranged in the volute 110 and configured to promote air flow from the fan air inlet 117 to the fan air outlet 116 120.
  • the volute 110 may include two volute side walls that jointly define a volute air passage and a volute peripheral wall 113 that connects the two volute side walls.
  • the volute peripheral wall 113 may include a volute section that gradually expands with respect to the outer contour of the centrifugal fan 120, and a volute section and an outlet section respectively extending from both ends of the volute section.
  • Each fan air inlet 117 can be opened on a side wall of a volute, and the air flow sucked in by the fan air inlet 117 can be blown out between the volute tongue section and the outlet section.
  • FIG. 6 is a schematic axonometric view of the volute 110 in FIG. 5.
  • the air outlet 116 of the fan may be arranged to open along the thickness direction of the volute 110. That is, the air outlet 116 of the fan may be configured to blow the air flow along the direction of the rotation axis of the centrifugal fan 120, so as to reduce the overall size of the window machine air conditioner 200.
  • volute side wall 112 of the volute 110 away from the fan outlet 116 may include a flat plate portion 1121 and a convex portion arched away from the fan outlet 116 with respect to the flat plate portion 1121, so as to be on the volute 110
  • a cavity is formed inside to increase the air storage volume of the volute air duct, and the air supply volume of the centrifugal fan 100 is significantly increased under the condition of almost no increase in noise.
  • the window air conditioner 200 may further include an indoor heat exchanger 220.
  • the indoor heat exchanger 220 may be arranged on the air inlet flow path between the indoor air inlet 211 and the centrifugal fan 100 to exchange heat with indoor air flowing in from the indoor air inlet 211 and reduce wind resistance.
  • the window air conditioner 200 may further include an outdoor heat exchanger 240 and a heat dissipation fan 230 for dissipating heat from the outdoor heat exchanger 240.
  • the heat dissipation fan 230 may be configured to cause airflow to flow from the outdoor air inlet 213 through the outdoor heat exchanger 240 and toward the outdoor air outlet 214.
  • the number of the fan air inlet 117 may be one, so as to further reduce the occupied space of the window air conditioner 200.
  • the air inlet 117 of the fan may be opened on the other side wall 111 of the volute 110, and the other side wall 111 of the volute may be a flat plate.
  • the air outlet 116 of the fan may be disposed on a side of the air inlet 117 of the fan away from the protrusion. That is, the air outlet 116 of the fan may be located in front of the air inlet 117 of the fan to use the peripheral wall of the air outlet 116 of the fan to divert the indoor air around the air inlet 117 and the air outlet 116 of the fan, and to improve the air supply of the centrifugal fan 100 distance.
  • the volute 110 may further include an air guide 114 for receiving the gas flowing out between the volute tongue section and the outlet section and guiding the gas along the thickness direction of the volute 110.
  • the protrusion may be provided at a position of the volute side wall 112 corresponding to the exit section of the volute peripheral wall 113 of the volute 110, so as to further increase the air supply volume of the centrifugal fan 100 and reduce the The layout of other structures in the window air conditioner 200 is affected.
  • the fan outlet 116 is arranged to extend perpendicular to the outlet section, so as to further reduce the overall size of the window air conditioner 200.
  • FIG. 7 is a schematic cross-sectional view of the volute 110 shown in FIG. 6 taken along a plane passing through the rotation axis of the centrifugal fan 120 and extending along the extension direction of the fan outlet 116.
  • the distance W 1 of the cavity in the thickness direction of the volute 110 may be the maximum distance W between the plate portion 1121 and the other side wall 111 of the volute 110 in the thickness direction of the volute 110 2 20% to 40%, e.g., 20%, 33%, or 40%.
  • the dimension L 1 of the cavity in the extension direction of the fan outlet 116 may be 20%-40% of the internal dimension L 2 of the volute 110 passing through the rotation axis of the centrifugal fan 120 in the extension direction of the fan outlet 116, for example, 20%, 33%, or 40%, so as to avoid excessive increase in the occupied space of the volute 110 while increasing the air supply volume.
  • the distance between the side wall 112 of the volute and an imaginary plane perpendicular to the rotation axis of the centrifugal fan 120 and located between the side walls of the two volutes may increase as the distance from the outlet section increases. Reduce to avoid the formation of gas vortex, make the gas flow more smoothly, and avoid the increase of noise.
  • the protrusion may include a main body 1122 and a transition section 1123.
  • the main body 1122 can be arranged parallel to the flat plate portion 1121 and spaced apart from the flat plate portion 1121 in the thickness direction.
  • the transition section 1123 may be arranged to extend obliquely from the main body 1122 to the direction close to the flat portion 1121 to avoid the formation of gas vortex, so that the gas flow is smoother and the noise is prevented from increasing.
  • volute peripheral wall 113, the main body 1122, the transition section 1123, and the flat plate portion 1121 can be smoothly connected to each other to further improve the smoothness of the gas flow.
  • FIG 8 is a gas flow field in the vertical direction measured on the volute 110 shown in Figure 1;
  • Figure 9 is a gas flow in the horizontal direction measured on the volute 110 shown in Figure 1 Field diagram;
  • Figure 10 is the gas flow field in the vertical direction measured on the volute 110 shown in Figure 6;
  • Figure 11 is the horizontal direction measured on the volute 110 shown in Figure 6
  • Gas flow field diagram. 8 to 9 are the gas flow field diagrams of the centrifugal fan 100 measured under the same experimental conditions, in which the volute 110 shown in FIG. 1 and the volute 110 shown in FIG. 6 have the same dimensions except for the arrangement of the protrusions.
  • the specifications of the centrifugal fan 120 used in the experiment are all the same, and the rotation speed of the centrifugal fan 120 during the experiment is the maximum rotation speed.
  • the present invention (provided with protrusions) is compared with the prior art shown in Figure 1 (without protrusions), at the fan outlet 116 (especially the position adjacent to the outlet section) Where) the gas flow rate is more uniform and the average flow rate is faster, and there is no vortex generated, that is, the centrifugal fan 100 of the present invention can have a larger air supply volume, a longer air supply distance, and the same degree of noise.
  • the present invention (provided with protrusions) is compared with the prior art shown in Figure 1 (without protrusions), although a small amount of low-velocity vortexes are generated at the position of the outlet section , But the gas flow rate at the position of the volute tongue section is more uniform and there are fewer vortices. As measured by the noise measuring instrument, the noise of the present invention only increases by 0.73% compared with the prior art shown in FIG. 1, and the noise is almost unchanged.
  • the centrifugal fan 100 of the present invention can also be applied to a new fan of a window machine.
  • the fan air inlet 117 may be arranged on the side wall 112 of the volute away from the fan air outlet 116 and arranged toward the outdoors.

Abstract

一种离心风机（100）及具有其的窗机空调（200）。该离心风机（100）包括蜗壳（110）和设置于蜗壳（110）内的离心风扇（120）。蜗壳（110）开设有一个风机进风口（117）和一个风机出风口（116）。离心风扇（120）配置为促使空气由风机进风口（117）向风机出风口（116）流动。风机出风口（116）设置为沿蜗壳（110）的厚度方向开口。蜗壳（110）的远离风机出风口（116）的蜗壳侧壁（112）包括平板部（1121）和相对于平板部（1121）向远离风机出风口（116）的方向拱起的凸起部，以在蜗壳（110）的内部形成凹腔增加蜗壳风道的储风体积，在几乎不增加噪音的情况下，显著地提高离心风机（100）的送风量，特别适用于对占用空间的大小和风量有较高要求的窗机空调（200）。

Description

离心风机及具有该离心风机的窗机空调 技术领域
本发明涉及空气调节领域，特别是涉及一种离心风机及具有该离心风机的窗机空调。
背景技术
现有窗机空调的整机尺寸越来越小，但却对风量、噪音等送风性能要求越来越高。
图1是现有技术的用于窗机空调的离心风机的蜗壳的示意性轴测图；图2是图1所示蜗壳沿经过离心风扇的转动轴线并沿风机出风口的延伸方向延伸的平面截取的示意性剖视图。参见图1和图2，现有窗机空调采用单吸式且蜗壳的两个蜗壳侧壁均为平板的离心风机，主要依靠对离心风机本身和蜗壳的风道型线进行优化来提高送风性能，对生产工艺要求过高。综合考虑，在设计上需要一种高风量、低噪音且低成本的用于窗机空调的离心风机及具有该离心风机的窗机空调。
发明内容
本发明第一方面的一个目的是要克服现有技术中的至少一个技术缺陷，提供一种具有新型蜗壳结构的离心风机。
本发明第一方面的一个进一步的目的是要提高离心风机的送风量。
本发明第一方面的另一个进一步的目的是要避免噪音增加。
本发明第二方面的一个目的是要提供一种具有该离心风机的窗机空调。
根据本发明的第一方面，提供了一种离心风机，其特征在于，包括：
蜗壳，开设有一个风机进风口和一个风机出风口；和
离心风扇，设置于所述蜗壳内，配置为促使空气由所述风机进风口向所述风机出风口流动；其中
所述风机出风口设置为沿所述蜗壳的厚度方向开口；且
所述蜗壳的远离所述风机出风口的蜗壳侧壁包括平板部和相对于所述平板部向远离所述风机出风口的方向拱起的凸起部，以在所述蜗壳的内部形成凹腔。
可选地，所述凹腔在所述蜗壳的厚度方向上的间距为所述平板部与所述 蜗壳的另一蜗壳侧壁在所述蜗壳的厚度方向上的最大间距的20％～40％。
可选地，所述凸起部设置于所述蜗壳侧壁的对应于所述蜗壳的蜗壳周壁的出口段的位置处。
可选地，所述风机出风口设置为垂直于所述出口段延伸；且
所述凹腔在所述风机出风口的延伸方向上的尺寸为所述蜗壳经过所述离心风扇的转动轴线在所述风机出风口的延伸方向上的内部尺寸的20％～40％。
可选地，所述蜗壳侧壁与一垂直于所述离心风扇的转动轴线并位于所述蜗壳的两个蜗壳侧壁之间的的假想平面的间距随其与所述出口段的距离的增加而相应减小。
可选地，所述凸起部包括：
主体，设置为与所述平板部平行，并与所述平板部在所述厚度方向上间隔设置；和
过渡段，设置为自所述主体向靠近所述平板部的方向倾斜延伸。
可选地，所述风机进风口开设于所述蜗壳的另一蜗壳侧壁，且所述另一蜗壳侧壁为平板。
可选地，所述风机进风口开设于所述蜗壳的另一蜗壳侧壁；且
所述风机出风口设置于所述风机进风口的远离所述凸起部的一侧。
根据本发明的第二方面，提供了一种窗机空调，其特征在于，包括：
机壳，开设有室内进风口和室内出风口；和
根据以上任一所述的离心风机，设置于所述机壳内，并配置为促使室内空气由所述室内进风口向所述室内出风口流动。
可选地，所述窗机空调还包括：
室内换热器，设置于所述室内进风口与所述离心风机之间的进风流路上，以与由所述室内进风口流入的室内空气进行热交换。
本发明的离心风机在现有离心风机的基础上通过在蜗壳远离风机出风口的蜗壳侧壁上设置凸起，即在蜗壳的内部形成远离风机出风口的凹腔，增加了蜗壳风道的储风体积，在几乎不增加噪音的情况下，显著地提高了离心风机的送风量，特别适用于对占用空间的大小和风量有较高要求的窗机空调。
进一步地，本发明通过将凸起部设置在对应于蜗壳周壁的出口段的位置 处，并将凸起部在蜗壳厚度方向上和风机出风口的延伸方向上的尺寸限定为相应方向上的蜗壳内部尺寸的20％～40％，相比于将凸起部设置在其他位置，进一步地提高了离心风机的送风量，减小甚至避免了对窗机空调内的其他结构的布局影响，避免了窗机空调的整机尺寸增大。经测试，本发明相对于现有技术的实测风量提高了10.6％。
进一步地，本发明将凸起部设置为先自蜗壳周壁的边缘平行于平板部延伸，再向靠近平板部的方向倾斜延伸，避免了气体涡流的形成，使得气体的流动更加顺畅，避免了噪音的增加，提高了用户体验。
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是现有技术的用于窗机空调的离心风机的蜗壳的示意性轴测图；
图2是图1所示蜗壳沿经过离心风扇的转动轴线并沿风机出风口的延伸方向延伸的平面截取的示意性剖视图；
图3是本发明一个实施例的窗机空调的示意性轴测图；
图4是图3所示窗机空调沿一前后方向延伸的竖直平面截取的示意性剖视图；
图5是图3所示窗机空调沿一水平平面截取的示意性剖视图；
图6是图5中的蜗壳的示意性轴测图；
图7是图6所示蜗壳沿经过离心风扇的转动轴线并沿风机出风口的延伸方向延伸的平面截取的示意性剖视图；
图8是对图1所示蜗壳进行测试测得的在竖直方向上的气体流场图；
图9是对图1所示蜗壳进行测试测得的在水平方向上的气体流场图；
图10是对图6所示蜗壳进行测试测得的在竖直方向上的气体流场图；
图11是对图6所示蜗壳进行测试测得的在水平方向上的气体流场图。
具体实施方式
图3是本发明一个实施例的窗机空调200的示意性轴测图；图4是图3 所示窗机空调200沿一前后方向延伸的竖直平面截取的示意性剖视图；图5是图3所示窗机空调200沿一水平平面截取的示意性剖视图。参见图3至和图5，窗机空调200可包括机壳210和离心风机100。
机壳210可被划分为位于室内环境中的室内侧和位于室外环境中的室外侧。其中，室内侧可开设有室内进风口211和室内出风口212。室外侧可开设有室外进风口213和室外出风口214。
离心风机100可设置于机壳210内，并配置为促使室内空气由室内进风口211向室内出风口212流动，进而促进室内环境中的空气流动。
离心风机100可包括开设有至少一个风机进风口117和一个风机出风口116的蜗壳110、以及设置于蜗壳110内并配置为促使空气由风机进风口117向风机出风口116流动的离心风扇120。
蜗壳110可包括共同限定出蜗壳风道的两个蜗壳侧壁和连接两个蜗壳侧壁的蜗壳周壁113。蜗壳周壁113可包括相对于离心风扇120的外轮廓渐扩的蜗形区段和自蜗形区段的两端分别延伸出的蜗舌区段和出口区段。每个风机进风口117可开设于一个蜗壳侧壁，由风机进风口117吸入的气流可经蜗舌区段和出口区段之间吹出。
图6是图5中的蜗壳110的示意性轴测图。参见图5和图6，风机出风口116可设置为沿蜗壳110的厚度方向开口。即，风机出风口116可设置为使气流沿离心风扇120的转动轴线方向吹出，以减少窗机空调200的整机尺寸。
特别地，蜗壳110的远离风机出风口116的蜗壳侧壁112可包括平板部1121和相对于平板部1121向远离风机出风口116的方向拱起的凸起部，以在蜗壳110的内部形成凹腔增加蜗壳风道的储风体积，在几乎不增加噪音的情况下，显著地提高离心风机100的送风量。
在一些实施例中，窗机空调200还可包括室内换热器220。室内换热器220可设置于室内进风口211与离心风机100之间的进风流路上，以与由室内进风口211流入的室内空气进行热交换，并降低风阻。
窗机空调200还可包括室外换热器240和为室外换热器240散热的散热风机230。散热风机230可配置为促使气流由室外进风口213流经室外换热器240并向室外出风口214流动。
在一些实施例中，风机进风口117的数量可为一个，以进一步地减少窗 机空调200的占用空间。风机进风口117可开设于蜗壳110的另一蜗壳侧壁111，且另一蜗壳侧壁111可为平板。
在一些实施例中，风机出风口116可设置于风机进风口117的远离凸起部的一侧。即，风机出风口116可位于风机进风口117的前侧，以利用风机出风口116的周壁对风机进风口117和风机出风口116周围的室内空气进行导流，并提高离心风机100的送风距离。
蜗壳110还可包括导风部114，用于接收自蜗舌区段和出口区段之间流出的气体，并将该气体沿蜗壳110的厚度方向导出。
在一些实施例中，凸起部可设置于蜗壳侧壁112的对应于蜗壳110的蜗壳周壁113的出口段的位置处，以进一步地提高离心风机100的送风量，减小对窗机空调200内的其他结构的布局影响。
在一些进一步地实施例中，风机出风口116设置为垂直于出口段延伸，以进一步地减少窗机空调200的整机尺寸。
图7是图6所示蜗壳110沿经过离心风扇120的转动轴线并沿风机出风口116的延伸方向延伸的平面截取的示意性剖视图。参见图6和图7，凹腔在蜗壳110的厚度方向上的间距W 1可为平板部1121与蜗壳110的另一蜗壳侧壁111在蜗壳110的厚度方向上的最大间距W 2的20％～40％，例如，20％、33％、或40％。
凹腔在风机出风口116的延伸方向上的尺寸L 1可为蜗壳110经过离心风扇120的转动轴线在风机出风口116的延伸方向上的内部尺寸L 2的20％～40％，例如，20％、33％、或40％，以在提高送风量的同时，避免蜗壳110的占用空间过分的增大。
在一些进一步地实施例中，蜗壳侧壁112与一垂直于离心风扇120的转动轴线并位于两个蜗壳侧壁之间的假想平面的间距可随其与出口段的距离的增加而相应减小，以避免气体涡流的形成，使得气体的流动更加顺畅，避免噪音的增加。
在一些进一步地实施例中，凸起部可包括主体1122和过渡段1123。其中，主体1122可设置为与平板部1121平行，并与平板部1121在厚度方向上间隔设置。过渡段1123可设置为自主体1122向靠近平板部1121的方向倾斜延伸，以避免气体涡流的形成，使得气体的流动更加顺畅，避免噪音的增加。
蜗壳周壁113、主体1122、过渡段1123和平板部1121可圆滑过渡连接，以进一步地提高气体流动的顺畅性。
图8是对图1所示蜗壳110进行测试测得的在竖直方向上的气体流场图；图9是对图1所示蜗壳110进行测试测得的在水平方向上的气体流场图；图10是对图6所示蜗壳110进行测试测得的在竖直方向上的气体流场图；图11是对图6所示蜗壳110进行测试测得的在水平方向上的气体流场图。图8至图9是在相同实验条件下测得的离心风机100气体流场图，其中，图1所示蜗壳110与图6所示蜗壳110除凸起部的设置外其他尺寸均相同，且实验所用离心风扇120规格均相同、实验过程中的离心风扇120的转速均为其最大转速。
参见图8和图10，本发明(设置有凸起部)相比于图1所示的现有技术(未设置凸起部)，在风机出风口116处(特别是邻近出口区段的位置处)的气体流速更加均匀且平均流速更快，且无涡流产生，即本发明的离心风机100可具有更大的送风量、更远的送风距离，相同程度的噪音。
参见图8和图10，本发明(设置有凸起部)相比于图1所示的现有技术(未设置凸起部)，虽然在出口区段的位置处有少量的低流速涡流产生，但在蜗舌区段的位置处的气体流速更加均匀且涡流更少。经噪音测量仪测量，本发明相比于图1所示的现有技术噪音仅增长了0.73％，噪音几乎不变。
在另一些实施例中，本发明的离心风机100也可适用于窗机新风机。在该实施例中，风机进风口117可设置在远离风机出风口116的蜗壳侧壁112上，并朝向室外布置。
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 (10)

  1. 一种离心风机，包括：
    蜗壳，开设有一个风机进风口和一个风机出风口；和
    离心风扇，设置于所述蜗壳内，配置为促使空气由所述风机进风口向所述风机出风口流动；其中
    所述风机出风口设置为沿所述蜗壳的厚度方向开口；且
    所述蜗壳的远离所述风机出风口的蜗壳侧壁包括平板部和相对于所述平板部向远离所述风机出风口的方向拱起的凸起部，以在所述蜗壳的内部形成凹腔。
  2. 根据权利要求1所述的离心风机，其中，
    所述凹腔在所述蜗壳的厚度方向上的间距为所述平板部与所述蜗壳的另一蜗壳侧壁在所述蜗壳的厚度方向上的最大间距的20％～40％。
  3. 根据权利要求1所述的离心风机，其中，
    所述凸起部设置于所述蜗壳侧壁的对应于所述蜗壳的蜗壳周壁的出口段的位置处。
  4. 根据权利要求3所述的离心风机，其中，
    所述风机出风口设置为垂直于所述出口段延伸；且
    所述凹腔在所述风机出风口的延伸方向上的尺寸为所述蜗壳经过所述离心风扇的转动轴线在所述风机出风口的延伸方向上的内部尺寸的20％～40％。
  5. 根据权利要求3所述的离心风机，其中，
    所述蜗壳侧壁与一垂直于所述离心风扇的转动轴线并位于所述蜗壳的两个蜗壳侧壁之间的的假想平面的间距随其与所述出口段的距离的增加而相应减小。
  6. 根据权利要求3所述的离心风机，其中，所述凸起部包括：
    主体，设置为与所述平板部平行，并与所述平板部在所述厚度方向上间隔设置；和
    过渡段，设置为自所述主体向靠近所述平板部的方向倾斜延伸。
  7. 根据权利要求1所述的离心风机，其中，
    所述风机进风口开设于所述蜗壳的另一蜗壳侧壁，且所述另一蜗壳侧壁为平板。
  8. 根据权利要求1所述的离心风机，其中，
    所述风机进风口开设于所述蜗壳的另一蜗壳侧壁；且
    所述风机出风口设置于所述风机进风口的远离所述凸起部的一侧。
  9. 一种窗机空调，包括：
    机壳，开设有室内进风口和室内出风口；和
    根据权利要求1-8中任一所述的离心风机，设置于所述机壳内，并配置为促使室内空气由所述室内进风口向所述室内出风口流动。
  10. 根据权利要求9所述的窗机空调，还包括：
    室内换热器，设置于所述室内进风口与所述离心风机之间的进风流路上，以与由所述室内进风口流入的室内空气进行热交换。
PCT/CN2021/076472 2020-05-25 2021-02-10 离心风机及具有该离心风机的窗机空调 WO2021218292A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202010449333.8A CN113719912A (zh) 2020-05-25 2020-05-25 离心风机及具有该离心风机的窗机空调
CN202010449333.8 2020-05-25

Publications (1)

Publication Number Publication Date
WO2021218292A1 true WO2021218292A1 (zh) 2021-11-04

Family

ID=78331738

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2021/076472 WO2021218292A1 (zh) 2020-05-25 2021-02-10 离心风机及具有该离心风机的窗机空调

Country Status (2)

Country Link
CN (1) CN113719912A (zh)
WO (1) WO2021218292A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114370680A (zh) * 2021-12-21 2022-04-19 上海优墅智能科技有限责任公司 一种窗载新风机

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2167851A (en) * 1984-10-18 1986-06-04 Mitsubishi Electric Corp Air conditioning apparatus
CN1249028A (zh) * 1997-12-30 2000-03-29 开利公司 用于室内空调机的空气引导组件
KR100351811B1 (ko) * 1999-12-15 2002-09-11 엘지전자주식회사 열교환기 통과유속 균일화 장치
CN102022383A (zh) * 2009-09-11 2011-04-20 珠海格力电器股份有限公司 空调器风道装置及空调器
CN106224292A (zh) * 2016-08-31 2016-12-14 珠海格力电器股份有限公司 蜗壳组件及具有其的窗式空调器
CN206094454U (zh) * 2016-09-22 2017-04-12 Tcl空调器(中山)有限公司 空调器的风道结构及空调器
CN212431131U (zh) * 2020-05-25 2021-01-29 青岛海尔空调器有限总公司 离心风机及具有该离心风机的窗机空调

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2167851A (en) * 1984-10-18 1986-06-04 Mitsubishi Electric Corp Air conditioning apparatus
CN1249028A (zh) * 1997-12-30 2000-03-29 开利公司 用于室内空调机的空气引导组件
KR100351811B1 (ko) * 1999-12-15 2002-09-11 엘지전자주식회사 열교환기 통과유속 균일화 장치
CN102022383A (zh) * 2009-09-11 2011-04-20 珠海格力电器股份有限公司 空调器风道装置及空调器
CN106224292A (zh) * 2016-08-31 2016-12-14 珠海格力电器股份有限公司 蜗壳组件及具有其的窗式空调器
CN206094454U (zh) * 2016-09-22 2017-04-12 Tcl空调器(中山)有限公司 空调器的风道结构及空调器
CN212431131U (zh) * 2020-05-25 2021-01-29 青岛海尔空调器有限总公司 离心风机及具有该离心风机的窗机空调

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114370680A (zh) * 2021-12-21 2022-04-19 上海优墅智能科技有限责任公司 一种窗载新风机
CN114370680B (zh) * 2021-12-21 2023-05-12 上海优墅智能科技有限责任公司 一种窗载新风机

Also Published As

Publication number Publication date
CN113719912A (zh) 2021-11-30

Similar Documents

Publication Publication Date Title
US9759441B2 (en) Air-conditioning apparatus
JP2005248950A (ja) 送風ファンの構造
WO2014069301A1 (ja) 空気調和機
JP6008993B2 (ja) 空気調和機
JP5837235B2 (ja) 空気調和機の室外ユニット
CN211575291U (zh) 壁挂式空调室内机及其导风板
WO2021218292A1 (zh) 离心风机及具有该离心风机的窗机空调
CN212431131U (zh) 离心风机及具有该离心风机的窗机空调
US20170003038A1 (en) Air-conditioning indoor machine
CN208382343U (zh) 空调室内机和空调器
JP3582366B2 (ja) 送風機
CN216307996U (zh) 壁挂式空调室内机
CN205937220U (zh) 风轮、轴流风机、空调柜机及空调器
CN111981566B (zh) 风机及空调室内机
WO2017049447A1 (zh) 一种空调混合出风室内机
WO2020048203A1 (zh) 一种风道组件以及空调器
WO2017049542A1 (zh) 一种空调室内机
WO2017049465A1 (zh) 一种分体壁挂式空调
KR20140014409A (ko) 공기조화기의 실내기
CN108375108B (zh) 壁挂式空调室内机
JP4214994B2 (ja) 空気調和機
WO2024087274A1 (zh) 换热器及空调器
WO2017206643A1 (zh) 一种送风系统及应用其的室内机和空调
WO2022174619A1 (zh) 壁挂式空调室内机
CN110185642A (zh) 一种出风组件及空调器

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 21796404

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 21796404

Country of ref document: EP

Kind code of ref document: A1