WO2019047466A1 - 一种新型高效的hvac内机 - Google Patents

一种新型高效的hvac内机 Download PDF

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Publication number
WO2019047466A1
WO2019047466A1 PCT/CN2018/074392 CN2018074392W WO2019047466A1 WO 2019047466 A1 WO2019047466 A1 WO 2019047466A1 CN 2018074392 W CN2018074392 W CN 2018074392W WO 2019047466 A1 WO2019047466 A1 WO 2019047466A1
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WIPO (PCT)
Prior art keywords
volute
air outlet
cavity
side plate
air inlet
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Ceased
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PCT/CN2018/074392
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English (en)
French (fr)
Inventor
林炎虎
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Zhongshan Broad Ocean Motor Co Ltd
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Zhongshan Broad Ocean Motor Co Ltd
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Publication date
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Publication of WO2019047466A1 publication Critical patent/WO2019047466A1/zh
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0022—Centrifugal or radial fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • 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
    • F24F13/22—Means for preventing condensation or evacuating condensate
    • F24F13/222—Means for preventing condensation or evacuating condensate for evacuating condensate
    • 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
    • F24F13/20—Casings or covers
    • F24F2013/205—Mounting a ventilator fan therein

Definitions

  • the invention relates to a new and efficient HVAC internal machine.
  • the existing HVAC internal machine includes an outer casing, a heat exchanger and a centrifugal fan, and the outer casing is surrounded by an upper side plate, a lower side plate, a front side plate and a rear side plate, and the heat exchanger and the centrifugal fan are installed.
  • the left side of the cavity is provided with a left side plate, the left side plate is provided with a first air outlet, and the right side of the cavity is provided with a first air inlet, the first air outlet, the first inlet
  • the heat exchanger is V-shaped, the heat exchanger is located on the left side of the first air inlet, the centrifugal fan is located on the right side of the first air outlet, and the centrifugal fan comprises a volute and a wind a wheel and a motor
  • the volute includes a second air inlet and a second air outlet, the second air inlet includes a second upper air inlet and a second lower air inlet, the volute being located between the upper side plate and the lower side plate
  • the above structure has the following technical problems: 1) Since there is a distance between the second air outlet and the first air outlet, when the second air outlet discharges the wind to the first air outlet, the wind will have a vortex phenomenon, resulting in loss of air volume. Too much, reduce the operating efficiency of the fan, and increase the cost; 2) the second upper air inlet and the second lower air inlet of the volute are narrower than the distance between the upper side plate and the lower side plate, respectively, and the air volume of the volute is small, resulting in The fan exhaust air volume is reduced, and the fan operating efficiency is reduced. 3) The parameter ratio design of the volute and the cavity is unreasonable, affecting the efficiency of the fan and reducing the operating efficiency of the motor.
  • the object of the present invention is to provide a new and efficient HVAC internal machine, which can reduce the output power of the motor, improve the operating efficiency of the fan, and save energy.
  • a novel high-efficiency HVAC internal machine comprising a casing, a heat exchanger and a centrifugal fan, the casing being surrounded by an upper side plate, a lower side plate, a front side plate and a rear side plate, the heat exchanger and the centrifugal
  • the fan is installed in the d cavity, the left side of the cavity is provided with a left side plate, the left side plate is provided with a first air outlet, and the right side of the cavity is provided with a first air inlet, the first air outlet, the first An air inlet is connected to the cavity, the heat exchanger is V-shaped, the heat exchanger is located on the left side of the first air inlet, the centrifugal fan is located on the right side of the first air outlet, and the centrifugal fan includes a volute a wind wheel and a motor, the volute includes a second air inlet and a second air outlet, the second air outlet of the volute is provided with a volute tongue, and the second air inlet includes a second upper air
  • the first air outlet is connected to the second air outlet, and the volute of the volute is connected to a static pressure recovery plate, and the static pressure recovery plate is Tilting, one end of the static pressure recovery plate is connected with the volute tongue of the volute air outlet, and the other end of the static pressure recovery plate extends toward the first air outlet.
  • An exhaust passage is disposed between the first air outlet and the second air outlet, and the static pressure returning plate is disposed on the air exhaust passage and extends toward the first air outlet.
  • the width H1 of the first air outlet and the width H2 of the second air outlet are equal.
  • the volute top plate corresponding to the volute tongue on the second air outlet is in close contact with the rear side plate.
  • the second air outlet is located at a middle portion of the upper side plate and the lower side plate.
  • the first cavity is provided with a water drop tray, the water tray is located below the heat exchanger and the water tray is installed obliquely to the lower side plate.
  • the first cavity is divided into an A zone cavity and a B zone cavity, the centrifugal fan is located in the A zone cavity, the heat exchanger is located in the B zone cavity, and the A zone cavity zone is in the second air outlet. Between the leftmost end of the heat exchanger, the cavity region of the B region is between the leftmost end of the heat exchanger and the first air inlet.
  • the volute parameter setting satisfies the following condition: 0.5 ⁇ B1/B ⁇ 0.7, B1 is the width of the volute, and B is the width of the outer casing.
  • the ratio of the effective width of the wind wheel to the outer diameter of the wind wheel 0.7 ⁇ 2b2 / D2 ⁇ 1, b2 is the effective width of the wind wheel, and D2 is the outer diameter of the wind wheel.
  • the ratio of the length of the volute to the length of the cavity of the A zone is 0.7 ⁇ L1/L ⁇ 0.9, L1 is the length of the volute, and L is the length of the cavity of the A zone.
  • the volute tongue is a circular arc shape, and the radius r of the volute tongue is 13 mm ⁇ r ⁇ 15 mm.
  • the inclination angle a of the static pressure recovery plate is 20° ⁇ a ⁇ 30°.
  • the width H3 of the volute is 234 mm ⁇ H3 ⁇ 242 mm.
  • the diameter R of the wind wheel is 216 mm ⁇ R ⁇ 224 mm, and the width of the wind wheel is H4 at 214 mm ⁇ H3 ⁇ 222 mm.
  • the invention has the following effects:
  • the present invention includes a casing, a heat exchanger, and a centrifugal fan, the left side plate of the casing is provided with a first air outlet, and the right side panel is provided with a first air inlet, the first air outlet, the first The air inlet is in communication with the first cavity, the heat exchanger is V-shaped, the heat exchanger is located on the left side of the first air inlet, the centrifugal fan is located on the right side of the first air outlet, and the volute is located on the upper side a space between the second upper air inlet and the upper side plate, a distance between the second lower air inlet and the lower side plate, the first air outlet and the second The air outlet is connected, the volute of the volute is connected to a static pressure recovery plate, and the static pressure recovery plate is inclined, and one end of the static pressure recovery plate is connected with the volute tongue of the volute air outlet, and the static pressure is restored.
  • the other end of the plate extends toward the first air outlet, so that the centrifugal fan directly blows to the first air outlet, effectively avoiding the phenomenon of vortex flow and improving efficiency; overall, if the same air volume is output, the output power ratio of the motor is required now.
  • the original is lower, more energy saving, and lower costs;
  • the width H1 of the first air outlet is equal to the width H2 of the second air outlet, which can effectively reduce the loss of air volume and improve the air blowing efficiency of the fan;
  • the first cavity is provided with a water tray, the water tray is located below the heat exchanger and the water tray is inclined to the lower side plate, and the dripping water of the heat exchanger is flowed out through the water tray to prevent water from accumulating inside the shell. .
  • the inclination angle a of the static pressure recovery plate is 20° ⁇ a ⁇ 30°
  • the volute parameter setting satisfies the following conditions: 0.5 ⁇ B1/B ⁇ 0.7
  • B1 is the width of the volute
  • B is the width of the outer casing
  • the width H3 of the volute is 234mm ⁇ H3 ⁇ 242mm
  • the volute tongue is circular arc shape
  • the radius r of the volute tongue is 13mm ⁇ r ⁇ 15mm.
  • the output of the motor can be reduced. Power, saving energy;
  • Figure 1 is a perspective view of the present invention
  • Figure 2 is another perspective view of the present invention.
  • FIG. 3 is a schematic structural view of a hidden front side panel of the present invention.
  • Figure 4 is a front elevational view of the hidden front side panel of the present invention.
  • Figure 5 is a cross-sectional view taken along line A-A of Figure 4.
  • Figure 6 is a cross-sectional view showing the structure of the present invention.
  • FIG. 7 is a perspective view of the centrifugal fan of the present invention.
  • Figure 8 is a front elevational view of the centrifugal fan of the present invention.
  • Figure 9 is a schematic diagram of the parameter design of the centrifugal fan of the present invention.
  • Figure 10 is another schematic diagram of the parameter design of the centrifugal fan of the present invention.
  • Figure 11 is an experimental comparison diagram of the present invention.
  • Embodiment 1 As shown in FIG. 1 to FIG. 10, this embodiment is a new type of high-efficiency HVAC internal machine, comprising a casing 1, a heat exchanger 2 and a centrifugal fan 3, wherein the casing 1 is composed of an upper side plate 11, The lower side panel 12, the front side panel 15 and the rear side panel 16 enclose a cavity 10, the heat exchanger 2 and the centrifugal fan 3 are mounted in the cavity 10, and the left side panel 13 is provided on the left side of the cavity 10.
  • a first air outlet 131 is disposed on the left side plate 13
  • a first air inlet 14 is disposed on a right side of the cavity 10 , and the first air outlet 131 , the first air inlet 14 , and the cavity 10 are connected to each other.
  • the heat exchanger 2 is V-shaped, the heat exchanger 2 is located on the left side of the first air inlet 14, the centrifugal fan 3 is located on the right side of the first air outlet 131, and the centrifugal fan 3 includes a volute 31, a wind wheel 32, and
  • the volute 31 includes a second air inlet 311 and a second air outlet 312.
  • the second air outlet 312 of the volute 31 is provided with a volute tongue 313, and the second air inlet 311 includes a second upper air inlet 3111.
  • the volute 31 is located between the upper side plate 11 and the lower side plate 12, and the second upper air inlet 3111 and the upper side plate 11 are spaced apart from each other, and the second lower air inlet 3112 and under There is a space between the plates 12, and the first air outlet 131 is in communication with the second air outlet 312.
  • the volute 313 of the volute 31 is connected to a static pressure recovery plate 34.
  • the return plate 34 is inclined, and one end of the static pressure returning plate 34 is in contact with the volute tongue 313 of the second air outlet 312 of the volute 31, and the other end of the static pressure returning plate 34 extends in the direction of the first air outlet 131.
  • An exhaust passage 4 is disposed between the first air outlet 131 and the second air outlet 312.
  • the static pressure recovery plate 34 is disposed on the exhaust passage 4 and extends toward the first air outlet 131.
  • the width H1 of the first air outlet 131 and the width H2 of the second air outlet 312 are equal.
  • the top plate 314 of the volute 31 corresponding to the volute tongue 313 on the second air outlet 312 abuts against the rear side plate 16.
  • the second air outlet 312 is located at a middle portion of the upper side plate 11 and the lower side plate 12.
  • a water tray 5 is disposed in the first cavity 10, and the water tray 5 is located below the heat exchanger 2 and the water tray 5 is obliquely mounted in the direction of the lower side plate 12.
  • the first cavity 10 is divided into a cavity A of the A zone and a cavity 102 of the B zone, the centrifugal fan 3 is located in the cavity 101 of the A zone, and the heat exchanger 2 is located in the cavity 102 of the zone B, and the cavity 101 of the zone A is Between the second air outlet 312 and the leftmost end of the heat exchanger 2, the area B cavity 102 is between the leftmost end of the heat exchanger 2 and the first air inlet 14.
  • the parameter setting of the volute 31 satisfies the following condition: 0.5 ⁇ B1/B ⁇ 0.7, B1 is the width of the volute 31, and B is the width of the outer casing 1.
  • the ratio of the effective width of the wind wheel 32 to the outer diameter of the wind wheel 32 is 0.7 ⁇ 2b2 / D2 ⁇ 1, b2 is the effective width of the wind wheel 32, and D2 is the outer diameter of the wind wheel 32.
  • the ratio of the length of the volute 31 to the length of the cavity 101 of the A region is 0.7 ⁇ L1/L ⁇ 0.9, L1 is the length of the volute 31, and L is the length of the cavity 101 of the A region.
  • the volute tongue 313 has a circular arc shape, and the radius r of the volute tongue 313 is 13 mm ⁇ r ⁇ 15 mm.
  • the inclination angle a of the static pressure recovery plate 34 is 20° ⁇ a ⁇ 30°.
  • the width H3 of the volute 31 is 234 mm ⁇ H3 ⁇ 242 mm.
  • the diameter R of the wind wheel 32 is 216 mm ⁇ R ⁇ 224 mm, and the width of the wind wheel 32 is H4 at 214 mm ⁇ H3 ⁇ 222 mm.
  • the curve A1, the curve A2, the curve A3, the curve A4, the curve A5, and the curve A6 are respectively shown by the above-mentioned six sets of experimental data, and the curve A5 satisfies the volute.
  • 31 parameter setting conditions 0.5 ⁇ B1/B ⁇ 0.7, 0.7 ⁇ 2b2 / D2 ⁇ 1, 0.7 ⁇ L1/L ⁇ 0.9
  • the line C in Fig. 11 refers to the same operation when the air volume at the same operating point is 1780 CFM.
  • curve A2, curve A3, and curve A4 are in a critical condition, the motor output power of curve A5 is the lowest, and the motor output power of curve A1 and curve A6 is the highest.

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

Abstract

一种新型高效的HVAC内机，包括外壳（1）、换热器（2）和离心风机（3），换热器（2）和离心风机（3）安装在第一空腔（10）里，机壳（1）的左侧板（13）上设有第一出风口（13），右侧板上设有第一进风口（14），换热器（2）呈V字形，离心风机（3）包括蜗壳（31）、风轮（32）和电机（33），蜗壳（31）包括第二进风口（311）和第二出风口（312），蜗壳（31）位于上侧板（11）和下侧板（12）中间，第一出风口（131）与第二出风口（312）是连通的，蜗壳（31）的蜗舌（313）接一静压回复板（34），静压回复板（34）是倾斜设置，静压回复板（34）的一端与蜗壳出风口的蜗舌（313）相接，静压回复板（34）的另一端向第一出风口（131）方向延伸，使离心风机（3）直接吹向第一出风口（13），有效避免涡流现象，提高效率，在同样的出风量下可以降低电机的输出功率。

Description

一种新型高效的HVAC内机 技术领域：
本发明涉及一种新型高效的HVAC内机。
背景技术：
现有的HVAC内机，包括外壳、换热器和离心风机，所述外壳由上侧板、下侧板、前侧板和后侧板围成空腔，所述换热器和离心风机安装在d空腔里，空腔的左侧设有左侧板，左侧板上设有第一出风口，空腔的右侧设有第一进风口，所述第一出风口、第一进风口和空腔是连通的，所述换热器的呈V字形，换热器位于第一进风口的左侧，离心风机位于第一出风口的右侧，所述离心风机包括蜗壳、风轮和电机，所述蜗壳包括第二进风口和第二出风口，第二进风口包括第二上进风口与第二下进风口，所述蜗壳位于上侧板和下侧板中间，所述第二上进风口与上侧板之间有一端间距，所述第二下进风口与下侧板之间有一端间距，所述第一出风口与第二出风口是连通的。
上述的结构存在如下技术问题：1)由于第二出风口与第一出风口之间存在一端距离，当第二出风口往第一出风口排出风时，风会出现蜗流现象，导致风量流失过多，降低风机运行效率，成本增加；2)另外蜗壳的第二上进风口和第二下进风口分别与上侧板和下侧板之间的间距窄，蜗壳的进风量小，导致风机排风量减低，风机运行效率降低；3)蜗壳与空腔的参数比例设计不合理，影响风机的效率,降低电机运行效率。
发明内容：
本发明的目的是提供一种新型高效的HVAC内机,它可以降低电机输出功率，提高风机运行效率，节约电能。
本发明的目的是通过下述技术方案予以实现的。
一种新型高效的HVAC内机，包括外壳、换热器和离心风机，所述外壳由上 侧板、下侧板、前侧板和后侧板围成空腔，所述换热器和离心风机安装在d空腔里，空腔的左侧设有左侧板，左侧板上设有第一出风口，空腔的右侧设有第一进风口，所述第一出风口、第一进风口和空腔是连通的，所述换热器的呈V字形，换热器位于第一进风口的左侧，离心风机位于第一出风口的右侧，所述离心风机包括蜗壳、风轮和电机，所述蜗壳包括第二进风口和第二出风口，所述蜗壳的第二出风口处设有蜗舌，第二进风口包括第二上进风口与第二下进风口，所述蜗壳位于上侧板和下侧板中间，所述第二上进风口与上侧板之间有一段间距，所述第二下进风口与下侧板之间有一段间距，所述第一出风口与第二出风口是连通的，所述蜗壳的蜗舌接一静压回复板，所述静压回复板是倾斜设置，静压回复板的一端与蜗壳出风口的蜗舌相接，静压回复板的另一端向第一出风口方向延伸。
上述所述第一出风口与第二出风口之间设有排风通道，所述静压回复板设置在排风通道上且往第一出风口方向延伸。
上述所述第一出风口的宽度H1与第二出风口的宽度H2是相等的。
上述所述位于第二出风口上的蜗舌对应的蜗壳顶板紧贴在后侧板上。
上述所述第二出风口位于上侧板和下侧板的中部。
上述所述第一空腔里设有落水盘，所述落水盘位于换热器的下方且落水盘往下侧板方向倾斜安装。
上述所述第一空腔分为A区空腔和B区空腔，所述离心风机位于A区空腔，换热器位于B区空腔，所述A区空腔区域在第二出风口与换热器最左端之间，所述B区空腔区域在换热器最左端与第一进风口之间。
上述所述在静压回复板的基础上，蜗壳参数设置满足如下条件：0.5≤B1/B≤0.7，B1是蜗壳的宽度，B是外壳的宽度。
上述所述风轮的有效宽度与风轮的外径比例：0.7≤2b2/D2≤1，b2是风轮的有效宽度，D2是风轮的外径。
上述所述蜗壳的长度与A区空腔的长度比例：0.7≤L1/L≤0.9，L1是蜗壳 的长度，L是A区空腔的长度。
所述蜗舌是圆弧形，蜗舌的半径r在13mm≤r≤15mm。
所述静压回复板的倾斜角度a在20°≤a≤30°。
所述蜗壳的宽度H3在234mm≤H3≤242mm。
所述风轮的直径R在216mm≤R≤224mm，风轮的宽度为H4在214mm≤H3≤222mm。
本发明与现有技术相比，具有如下效果：
1)本发明包括外壳、换热器和离心风机，所述机壳的左侧板上设有第一出风口，右侧板上设有第一进风口，所述第一出风口、第一进风口和第一空腔是连通的，所述换热器的呈V字形，换热器位于第一进风口的左侧，离心风机位于第一出风口的右侧，所述蜗壳位于上侧板和下侧板中间，所述第二上进风口与上侧板之间有一段间距，所述第二下进风口与下侧板之间有一段间距，所述第一出风口与第二出风口是连通的，所述蜗壳的蜗舌接一静压回复板，所述静压回复板是倾斜设置，静压回复板的一端与蜗壳出风口的蜗舌相接，静压回复板的另一端向第一出风口方向延伸，使离心风机直接吹向第一出风口，有效避免蜗流现象，提高效率；整体来说就是假如输出同样的风量，现在所需要电机的输出功率比原来的更低，更加节约电能，降低成本；
2)第一出风口的宽度H1与第二出风口的宽度H2是相等的，可以有效减少风量的流失，提高风机的吹风效率；
3)第一空腔里设有落水盘，所述落水盘位于换热器的下方且落水盘往下侧板方向倾斜安装，通过落水盘将换热器的滴水往外流，防止外壳内部积水。
4)在静压回复板的基础上，静压回复板的倾斜角度a在20°≤a≤30°，蜗壳参数设置满足如下条件：0.5≤B1/B≤0.7，B1是蜗壳的宽度，B是外壳的宽度，蜗壳的宽度H3在234mm≤H3≤242mm，蜗舌是圆弧形，蜗舌的半径r在13mm≤r≤15mm，在输出同样的风量中，可以降低电机的输出功率，节约电能；
5)风轮的有效宽度与风轮的外径比例：0.7≤2b2/D2≤1，b2是风轮的有效 宽度，D2是风轮的外径，风轮的直径R在216mm≤R≤224mm，风轮的宽度为H4在214mm≤H3≤222mm，在输出同样的风量中，可以降低电机的输出功率，节约电能；
6)蜗壳的长度与A区空腔的长度比例：0.7≤L1/L≤0.9，L1是蜗壳的长度，L是A区空腔的长度，在输出同样的风量中，可以降低电机的输出功率，节约电能。
附图说明：
图1是本发明的立体图；
图2是本发明的另一角度立体图；
图3是本发明隐藏前侧板的结构示意图；
图4是本发明隐藏前侧板的正视图；
图5是图4中A-A的剖视图；
图6是本发明的结构剖视图；
图7是本发明的离心风机立体图；
图8是本发明的离心风机的正视图；
图9是本发明的离心风机的参数设计原理图；
图10是本发明的离心风机的参数设计的另一原理图；
图11是本发明的实验对照图。
具体实施方式：
下面通过具体实施例并结合附图对本发明作进一步详细的描述。
实施例一：如图1至图10所示，本实施例是一种新型高效的HVAC内机，包括外壳1、换热器2和离心风机3，所所述外壳1由上侧板11、下侧板12、前侧板15和后侧板16围成空腔10，所述换热器2和离心风机3安装在空腔10里，空腔10的左侧设有左侧板13，左侧板13上设有第一出风口131，空腔10的右侧设有第一进风口14，所述第一出风口131、第一进风口14和空腔10是连通的，所述换热器2的呈V字形，换热器2位于第一进风口14的左侧，离心 风机3位于第一出风口131的右侧，所述离心风机3包括蜗壳31、风轮32和电机33，所述蜗壳31包括第二进风口311和第二出风口312，所述蜗壳31的第二出风口312处设有蜗舌313，第二进风口311包括第二上进风口3111与第二下进风口3112，所述蜗壳31位于上侧板11和下侧板12中间，所述第二上进风口3111与上侧板11之间有一段间距，所述第二下进风口3112与下侧板12之间有一段间距，所述第一出风口131与第二出风口312是连通的，其特征在于：所述蜗壳31的蜗舌313接一静压回复板34，所述静压回复板34是倾斜设置，静压回复板34的一端与蜗壳31第二出风口312的蜗舌313相接，静压回复板34的另一端向第一出风口131方向延伸。
所述第一出风口131与第二出风口312之间设有排风通道4，所述静压回复板34设置在排风通道4上且往第一出风口131方向延伸。
所述第一出风口131的宽度H1与第二出风口312的宽度H2是相等的。
位于第二出风口312上的蜗舌313对应的蜗壳31顶板314紧贴在后侧板16上。
所述第二出风口312位于上侧板11和下侧板12的中部。
所述第一空腔10里设有落水盘5，所述落水盘5位于换热器2的下方且落水盘5往下侧板12方向倾斜安装。
第一空腔10分为A区空腔101和B区空腔102，所述离心风机3位于A区空腔101，换热器2位于B区空腔102，所述A区空腔101区域在第二出风口312与换热器2最左端之间，所述B区空腔102区域在换热器2最左端与第一进风口14之间。
在静压回复板34的基础上，蜗壳31参数设置满足如下条件：0.5≤B1/B≤0.7，B1是蜗壳31的宽度，B是外壳1的宽度。
所述风轮32的有效宽度与风轮32的外径比例：0.7≤2b2/D2≤1，b2是风轮32的有效宽度，D2是风轮32的外径。
所述蜗壳31的长度与A区空腔101的长度比例：0.7≤L1/L≤0.9，L1是蜗 壳31的长度，L是A区空腔101的长度。
所述蜗舌313是圆弧形，蜗舌313的半径r在13mm≤r≤15mm。
所述静压回复板34的倾斜角度a在20°≤a≤30°。
所述蜗壳31的宽度H3在234mm≤H3≤242mm。
所述风轮32的直径R在216mm≤R≤224mm，风轮32的宽度为H4在214mm≤H3≤222mm。
如图11所述，根据上述数据经试验测试：在表1设置的客观条件下进行实验验证：
表2中实验参数选择为：2b2/D2＝0.936、B1/B＝0.591、L1/L＝0.786；经过实验，得到不同风量情况下的对应的效率值，并在图11中描点拟合成曲线A1；
表3中实验参数选择为：2b2/D2＝0.936、B1/B＝0.591、L1/L＝0.786；经过实验，得到不同风量情况下的对应的效率值，并在图11中描点拟合成曲线A2；
表4中实验参数选择为：2b2/D2＝0.758、B1/B＝0.567、L1/L＝0.873；经过实验，得到不同风量情况下的对应的效率值，并在图11中描点拟合成曲线A3；
表5中实验参数选择为：2b2/D2＝0.87、B1/B＝0.591、L1/L＝0.837；经过实验，得到不同风量情况下的对应的效率值，并在图11中描点拟合成曲线A4；
表6中实验参数选择为：2b2/D2＝0.833、B1/B＝0.591、L1/L＝0.837；经过实验，得到不同风量情况下的对应的效率值，并在图11中描点拟合成曲线A5；
表7中实验参数选择为：2b2/D2＝0.84、B1/B＝0.665、L1/L＝0.925；经过实验，得到不同风量情况下的对应的效率值，并在图11中描点拟合成曲线A6；
通过上述的其中6组实验数据描出的图11曲线图，分别描出曲线A1、曲线A2、曲线A3、曲线A4、曲线A5、曲线A6，通过图11的曲线图可以看出，曲线A5满足蜗壳31参数设置条件：0.5≤B1/B≤0.7、0.7≤2b2/D2≤1、0.7≤L1/L≤0.9，在图11中的标号C线是指在同一运行点风量1780CFM时，在同一运行点风量中：曲线A2、曲线A3、曲线A4处于临界条件，曲线A5的电机输出功率是最低，曲线A1、曲线A6的电机输出功率是最高的。
Figure PCTCN2018074392-appb-000001
表1
Figure PCTCN2018074392-appb-000002
表2
Figure PCTCN2018074392-appb-000003
表3
Figure PCTCN2018074392-appb-000004
Figure PCTCN2018074392-appb-000005
表4
Figure PCTCN2018074392-appb-000006
表5
Figure PCTCN2018074392-appb-000007
Figure PCTCN2018074392-appb-000008
表6
Figure PCTCN2018074392-appb-000009
Figure PCTCN2018074392-appb-000010
表7
以上实施例为本发明的较佳实施方式，但本发明的实施方式不限于此，其他任何未背离本发明的精神实质与原理下所作的改变、修饰、替代、组合、简化，均为等效的置换方式，都包含在本发明的保护范围之内。

Claims (13)

  1. 一种新型高效的HVAC内机，包括外壳(1)、换热器(2)和离心风机(3)，所述外壳(1)由上侧板(11)、下侧板(12)、前侧板(15)和后侧板(16)围成空腔(10)，所述换热器(2)和离心风机(3)安装在空腔(10)里，空腔(10)的左侧设有左侧板(13)，左侧板(13)上设有第一出风口(131)，空腔(10)的右侧设有第一进风口(14)，所述第一出风口(131)、第一进风口(14)和空腔(10)是连通的，所述换热器(2)的呈V字形，换热器(2)位于第一进风口(14)的左侧，离心风机(3)位于第一出风口(131)的右侧，所述离心风机(3)包括蜗壳(31)、风轮(32)和电机(33)，所述蜗壳(31)包括第二进风口(311)和第二出风口(312)，所述蜗壳(31)的第二出风口(312)处设有蜗舌(313)，第二进风口(311)包括第二上进风口(3111)与第二下进风口(3112)，所述蜗壳(31)位于上侧板(11)和下侧板(12)中间，所述第二上进风口(3111)与上侧板(11)之间有一段间距，所述第二下进风口(3112)与下侧板(12)之间有一段间距，所述第一出风口(131)与第二出风口(312)是连通的，其特征在于：所述蜗壳(31)的蜗舌(313)接一静压回复板(34)，所述静压回复板(34)是倾斜设置，静压回复板(34)的一端与蜗壳(31)第二出风口(312)的蜗舌(313)相接，静压回复板(34)的另一端向第一出风口(131)方向延伸。
  2. 根据权利要求1所述的一种新型高效的HVAC内机，其特征在于：所述第一出风口(131)与第二出风口(312)之间设有排风通道(4)，所述静压回复板(34)设置在排风通道(4)上且往第一出风口(131)方向延伸。
  3. 根据权利要求2所述的一种新型高效的HVAC内机，其特征在于：所述第一出风口(131)的宽度H1与第二出风口(312)的宽度H2是相等的。
  4. 根据权利要求1或2或3所述的一种新型高效的HVAC内机，其特征在于：位于第二出风口(312)上的蜗舌(313)对应的蜗壳(31)顶板(314)紧贴在后侧板(16)上。
  5. 根据权利要求4所述的一种新型高效的HVAC内机，其特征在于:所述第二出风口(312)位于上侧板(11)和下侧板(12)的中部。
  6. 根据权利要求4所述的一种新型高效的HVAC内机，其特征在于：所述第一空腔(10)里设有落水盘(5)，所述落水盘(5)位于换热器(2)的下方且落水盘(5)往下侧板(12)方向倾斜安装。
  7. 根据权利要求4所述的一种新型高效的HVAC内机，其特征在于：第一空腔(10)分为A区空腔(101)和B区空腔(102)，所述离心风机(3)位于A区空腔(101)，换热器(2)位于B区空腔(102)，所述A区空腔(101)区域在第二出风口(312)与换热器(2)最左端之间，所述B区空腔(102)区域在换热器(2)最左端与第一进风口(14)之间，所述蜗壳(31)的长度与A区空腔(101)的长度比例：0.7≤L1/L≤0.9，L1是蜗壳(31)的长度，L是A区空腔(101)的长度。
  8. 根据权利要求7所述的一种新型高效的HVAC内机，其特征在于：在静压回复板(34)的基础上，蜗壳(31)参数设置满足如下条件：0.5≤B1/B≤0.7，B1是蜗壳(31)的宽度，B是外壳(1)的宽度。
  9. 根据权利要求8所述的一种新型高效的HVAC内机，其特征在于：所述风轮(32)的有效宽度与风轮(32)的外径比例：0.7≤2b2/D2≤1，b2是风轮(32)的有效宽度，D2是风轮(32)的外径。
  10. 根据权利要求9所述的一种新型高效的HVAC内机，其特征在于：所述蜗舌(313)是圆弧形，蜗舌(313)的半径r在13mm≤r≤15mm。
  11. 根据权利要求8所述的一种新型高效的HVAC内机，其特征在于：所述静压回复板(34)的倾斜角度a在20°≤a≤30°。
  12. 根据权利要求8所述的一种新型高效的HVAC内机，其特征在于：所述蜗壳(31)的宽度H3在234mm≤H3≤242mm。
  13. 根据权利要求9所述的一种新型高效的HVAC内机，其特征在于：所述风轮(32)的直径R在216mm≤R≤224mm，风轮(32)的宽度为H4在214mm≤ H3≤222mm。
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