WO2016095838A1 - Boîtier de ventilateur - Google Patents

Boîtier de ventilateur Download PDF

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Publication number
WO2016095838A1
WO2016095838A1 PCT/CN2015/097810 CN2015097810W WO2016095838A1 WO 2016095838 A1 WO2016095838 A1 WO 2016095838A1 CN 2015097810 W CN2015097810 W CN 2015097810W WO 2016095838 A1 WO2016095838 A1 WO 2016095838A1
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WO
WIPO (PCT)
Prior art keywords
fan casing
width
volute
fan
intake
Prior art date
Application number
PCT/CN2015/097810
Other languages
English (en)
Chinese (zh)
Inventor
狄义波
孙卫亮
靳杰
Original Assignee
特灵空调系统(中国)有限公司
特灵国际有限公司
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 特灵空调系统(中国)有限公司, 特灵国际有限公司 filed Critical 特灵空调系统(中国)有限公司
Priority to CN201580068853.1A priority Critical patent/CN107208656A/zh
Publication of WO2016095838A1 publication Critical patent/WO2016095838A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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

Definitions

  • the utility model relates to a fan casing for diffusing air, and more particularly to a centrifugal fan used in an indoor unit of an air conditioner.
  • Multi-blade centrifugal fans are widely used in variable coolant flow (VRF) products, especially in indoor units of air conditioners. It provides enough air to exchange heat with the coils and then cool or heat the various living places.
  • the fan has the advantages of small volume, large air volume, high pressure, low noise, compact structure and convenient installation, so it is especially suitable for ventilation and ventilation places with strict noise requirements and large air volume variation.
  • FIG 1 illustrates the configuration of a conventional centrifugal fan in an indoor unit of an air conditioner.
  • a large capacity air conditioner or heat pump typically requires more than one fan to be used in an indoor unit to provide improved airflow fluid flow characteristics.
  • Centrifugal fans generally include components such as a fan casing, an impeller, an air inlet, and an outer rotor motor.
  • the width W1 of the fan casing is a fixed value.
  • the fan casing (especially its volute portion) has a constant width W1 along its length or along its axis of rotation.
  • FIG. 2 is a schematic view showing the comparison between the width W1 of the fan casing and the width W2 of the coil. Although only two fan casings are shown, the outlet only covers a small portion of the coil width W2. In other words, if the ratio of W1/W2 is used to represent the ratio of the fan outlet area to the upstream area of the coil, it is clear that the ratio is within a small range. This results in a large mixing loss when the cross section of the fan is expanded, and the air flow velocity distribution on the coil is not uniform, so it is necessary to provide sufficient pressure to compensate for the above loss. However, this in turn leads to an increase in the fan speed and an increase in noise, which cannot meet the requirements for use.
  • the object of the present invention is to provide an improved fan casing.
  • the air conditioner indoor unit adopting the improved fan casing can effectively reduce the fan speed and reduce the noise level compared with the air conditioner indoor unit adopting the conventional fan casing.
  • the utility model provides a fan casing, comprising: an inlet volute for airflow entering, a hollow wheel portion at the center of the inlet volute; and a diffusion pipe, the diffusion pipe is connected with the inlet volute and the airflow flows out Wherein at least the width of the inlet volute is continuously varied in the fan casing.
  • the width of the inlet volute may gradually increase as its outer circumference extends in the direction of the helix.
  • the widths of the intake volute and the diffuser may gradually increase as their outer circumference extends.
  • the ratio d2/d1 of the width of the fan casing at the second position to the width of the fan casing at the first position is 1.05-1.30, wherein the first position is the starting position of the intake volute The second position is a position reached after the intake volute extends 360° from the first position in the spiral direction.
  • the ratio d3/d2 of the width of the fan casing at the third position to the width of the fan casing at the second position is 1.05-1.30, wherein the third position is the outlet position of the diffuser.
  • the width of the fan casing is gradually increased in a linear manner, and the spiral along which the outer periphery of the inlet volute extends forms an inclination angle ⁇ with the longitudinal direction of the fan casing, wherein the inclination angle ⁇ may be 5-30°.
  • the fan casing forms a C-shaped throat having a first radius R1 at both sides of the fan casing and a second radius R2 at an intermediate position of the fan casing 10, wherein the second radius and the first radius
  • the ratio R2/R1 can be 1.5-2.5.
  • the outer edge of the intake volute may be chamfered to 1/8 to 1/10 of the diameter of the hollow wheel portion of the intake volute.
  • the length L of the outer circumferential edge of the diffuser tube may be 0.7 to 1.2 times the diameter of the hollow wheel portion of the intake volute.
  • the fan casing of the present invention has the following advantages:
  • the distribution of the gas flow in the vicinity of the coil can be optimized to the utmost without minimizing the flow separation, and the average speed and noise generated at the outlet of the casing can be minimized.
  • Figure 1 shows the configuration of a conventional centrifugal fan in an indoor unit of an air conditioner
  • Figure 2 is a schematic view showing the comparison between the width of the fan casing of Figure 1 and the width of the coil;
  • Figure 3 is a front elevational view of the fan casing of the present invention.
  • Figure 3a is a cross-sectional view taken along line A-A of Figure 3;
  • Figure 4 is a plan view of the fan casing of Figure 3;
  • Figure 5 is a left side view of the fan casing of Figure 3;
  • Figure 6 shows the width dimensions of the fan casing having a variable width in a first position, a second position, and a third position
  • Figure 7 shows the width of the gap at the throat of the fan casing
  • FIGS. 8a and 8b are schematic cross-sectional views showing a fan speed and an air volume flow rate tested in an air flow test using an air conditioner indoor unit of the present invention, and a conventional air conditioner indoor unit;
  • Figures 8c and 8d show schematic bar graphs of the noise and fan speeds tested in the noise test of the air conditioner indoor unit using the fan casing of the present invention and the conventional air conditioner indoor unit.
  • FIG. 3 is a front view of the fan casing 10 of the present invention
  • FIGS. 4 and 5 are a plan view and a left side view, respectively, of the fan casing of FIG.
  • the fan casing 10 is composed of an intake volute 11 for air inflow and a diffuser pipe 12 for air outflow.
  • the intake volute 11 has a shape similar to a snail shell, and is provided with a hollow wheel portion 14 at its center, the outer circumference of which surrounds the circumference of the wheel portion 14 along a spiral (for example, Archimedes spiral or The logarithmic spiral line extends in the direction.
  • the diffuser tube 12 has a flare-like shape with its outer periphery extending tangentially at the junction with the inlet volute 11.
  • the length of the tangential extension of the outer circumference of the diffuser tube 12 is indicated by L.
  • L may be designed to be 0.7-1.2 times the diameter of the hollow wheel portion 14 of the intake volute 11.
  • the main feature of the fan casing of the present invention is different from the conventional fan casing: in the fan casing At least 10 of the inlet volutes 11 have a continuously varying width.
  • the width of the inlet volute 11 of the fan casing 10 gradually increases as its outer circumference extends in the direction of the helix.
  • the widths of the inlet volute 11 and the diffuser tube 12 of the fan casing 10 gradually increase as their outer circumference extends.
  • FIG. 6 there is shown the width dimension of the fan casing 10 in the first position (a, a'), the second position (b, b') and the third position (c, c'). It can be seen that the fan casing 10 has the smallest width at the first position and the largest at the third position.
  • first position (a, a') as defined in the present application means the initial position of the intake volute 11, that is, the position where the outer peripheral edge of the spiral of the intake volute 11 has the maximum curvature.
  • second position (b, b') as defined in the present application refers to a position reached after the intake volute 11 extends 360 degrees in the spiral direction around the center of the wheel portion 14 from the first position. The second position substantially coincides with the first position at the throat 13 of the fan casing 10.
  • third position (c, c') as defined in the present application refers to the exit position of the diffuser tube 12.
  • the width dimension of the fan casing 10 at the first position (a, a') is defined as d1
  • the width dimension of the fan casing 10 at the second position (b, b') is defined as D2
  • the ratio of d2/d1 is preferably between 1.05 and 1.30.
  • the width dimension of the fan casing 10 in the second position (b, b') is defined as d2 and the width dimension of the fan casing 10 in the third position (c, c') is defined as d3, d3 > d2 can be obtained. It has also been found through experiments that the ratio of d3/d2 is also preferably between 1.05-1.30.
  • the width d1 of the fan casing 10 at the first position is gradually increased in a linear manner to the width d2 at the second position, the spiral of the outer circumference of the intake volute 11 is extended.
  • An inclination angle ⁇ is formed with the longitudinal direction of the fan casing 10.
  • the value of the inclination angle ⁇ ranges from 5 to 30°.
  • the width d1 of the fan casing 10 at the first position can be gradually increased in a quadratic function to the width d2 at the second position, and these variations will fall into the present application. New range of protection.
  • FIG. 3a a cross-section of the fan casing taken along line A-A of Figure 3 is shown. It can be seen that the throat 13 has a C-shaped end face structure which exhibits a mid-high and low-end configuration along the width of the fan casing (also visible in Figure 6).
  • the C-shaped end throats 13 have different radii on both sides and intermediate portions of the fan casing 10. Specifically, the C-shaped end face throat 13 has a minimum radius R1 at both sides of the fan casing 10 and a maximum radius R2 at the intermediate position of the fan casing 10, wherein the ratio of R2/R1 falls within the range of 1.5-2.5. .
  • FIG. 7 shows the gap width t between the throat 13 of the fan casing 10 and the hollow wheel portion 14. It will be understood by one of ordinary skill in the art that if the gap width t between the wheel portion 14 and the throat portion 13 is too large, the average velocity of the airflow at the cross-section of the throat will be reduced. Although various modifications have been made to the shape of the throat 13 in the prior art to reduce separation and/or backflow of airflow in the throat region, the above average speed is still inevitably lowered and causes an increase in noise. By using the C-shaped end face throat of the fan casing of the present invention, it is possible to reduce the rotational impact of the airflow in the throat region, especially the intermediate portion of the throat along the width direction of the fan casing, thereby reducing the noise generated thereby.
  • the outer edge of the fan casing 10 may be chamfered such that both side surfaces of the fan casing 10 become curved.
  • the air conditioner indoor unit using the fan casing 10 of the present invention has a larger air volume flow rate (compared to an air conditioner indoor unit using a conventional fan casing) Increased rotation speed of 23 m 3 /hr or more) and lower by 54 rpm or more compared to an air conditioner indoor unit using a conventional fan casing.
  • the air conditioner indoor unit using the fan casing 10 of the present invention has a lower noise level (a reduction of 1.6dBA or more compared to an air conditioner indoor unit using a conventional fan casing) ) and lower rotational speed (70 rpm or more compared to an air conditioner indoor unit using a conventional fan casing).
  • the motor input energy consumed by the air conditioner indoor unit using the fan casing 10 of the present invention is substantially the same level (about 52-54 W) as compared with the air conditioner indoor unit using the conventional fan casing.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un boîtier de ventilateur (10) qui comporte : un boîtier de volute d'admission d'air (11) pour une admission d'air, une unité de roue creuse (14) disposée au centre du boîtier de volute d'admission d'air (11) et un tube de diffusion (12) relié au boîtier de volute d'admission d'air (11) et utilisé pour un écoulement de sortie d'air, au moins la largeur du boîtier de volute d'admission d'air (11) dans le boîtier de ventilateur (10) étant continuellement variable. Par rapport à une unité intérieure de climatisation employant un boîtier de ventilateur classique, l'unité intérieure de climatisation utilisant ledit boîtier de ventilateur (10) réduit efficacement la vitesse de rotation du ventilateur et le bruit.
PCT/CN2015/097810 2014-12-19 2015-12-18 Boîtier de ventilateur WO2016095838A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201580068853.1A CN107208656A (zh) 2014-12-19 2015-12-18 风机外壳

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201420815353.2U CN204553343U (zh) 2014-12-19 2014-12-19 风机外壳
CN201420815353.2 2014-12-19

Publications (1)

Publication Number Publication Date
WO2016095838A1 true WO2016095838A1 (fr) 2016-06-23

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ID=53828463

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2015/097810 WO2016095838A1 (fr) 2014-12-19 2015-12-18 Boîtier de ventilateur

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CN (2) CN204553343U (fr)
WO (1) WO2016095838A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107605802A (zh) * 2017-09-04 2018-01-19 广东顺威精密塑料股份有限公司 盘管机的蜗壳

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN204553343U (zh) * 2014-12-19 2015-08-12 特灵空调系统(中国)有限公司 风机外壳
CN106438405B (zh) * 2016-09-22 2019-04-26 中山大洋电机股份有限公司 一种盘管风机结构
US10865798B2 (en) 2016-05-30 2020-12-15 Zhongshan Broad-Ocean Motor Co., Ltd. Fan coil unit

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1129777A (zh) * 1994-12-20 1996-08-28 东芝株式会社 离心式送风机
US5839879A (en) * 1995-12-05 1998-11-24 Denso Corporation Centrifugal blower
CN101092974A (zh) * 2006-06-19 2007-12-26 高其海 离心式流体机械蜗壳
US20080232958A1 (en) * 2007-03-19 2008-09-25 Belanger, Inc. Spiral blower
CN101842598A (zh) * 2007-11-05 2010-09-22 加德纳·丹佛德国股份有限公司 侧通道压缩机
CN203516203U (zh) * 2013-10-29 2014-04-02 中联重科股份有限公司 离心风机蜗壳、离心风机和扫路车
CN204553343U (zh) * 2014-12-19 2015-08-12 特灵空调系统(中国)有限公司 风机外壳

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1129777A (zh) * 1994-12-20 1996-08-28 东芝株式会社 离心式送风机
US5839879A (en) * 1995-12-05 1998-11-24 Denso Corporation Centrifugal blower
CN101092974A (zh) * 2006-06-19 2007-12-26 高其海 离心式流体机械蜗壳
US20080232958A1 (en) * 2007-03-19 2008-09-25 Belanger, Inc. Spiral blower
CN101842598A (zh) * 2007-11-05 2010-09-22 加德纳·丹佛德国股份有限公司 侧通道压缩机
CN203516203U (zh) * 2013-10-29 2014-04-02 中联重科股份有限公司 离心风机蜗壳、离心风机和扫路车
CN204553343U (zh) * 2014-12-19 2015-08-12 特灵空调系统(中国)有限公司 风机外壳

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107605802A (zh) * 2017-09-04 2018-01-19 广东顺威精密塑料股份有限公司 盘管机的蜗壳

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CN107208656A (zh) 2017-09-26
CN204553343U (zh) 2015-08-12

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