SU533756A1

SU533756A1 - Centrifugal fan

Info

Publication number: SU533756A1
Application number: SU2072234A
Authority: SU
Inventors: Владимир Алексеевич Ивлев; Надежда Сергеевна Лебедева; Галина Сергеевна Жукова
Original assignee: Предприятие П/Я Г-4371
Priority date: 1974-11-06
Filing date: 1974-11-06
Publication date: 1976-10-30

Description

Изобретение от1носитс к области вент} л торостроени .The invention relates to the field of ventilation.

Известны центробежные вентил торы, содержащие улиточный КОрлус с ЯЗЫКО-Л1 и входным коллектором и расположенное в корпусе рабочее колесо, при этом зык корпуса выполнен В виде конического перехода или с щелью.Known centrifugal fans that contain a snail corulus with a LANGUAGE-L1 and an inlet manifold and an impeller located in the housing, while the tongue of the housing is made As a conical junction or with a slit.

Из(вестен центробежный вентил тор, в котором рассто ние зыка до кром ки рабочего колеса вли ет на уровень шума вентил тора.From (a centrifugal fan is known, in which the distance of the tongue to the edge of the impeller affects the noise level of the fan.

Однако в известных вентил торах не определены о-птимальные значени конструктивных пара-метров вентил торов, пр.и которых уровень шума вентил тора на единицу его полезной мощности будет мин И1малыньгм. Кро-ме того , в известных вентил торах не учитываетс вли ние ВХОДНОГО коллектора на шум нагнетани вентил тора, что не дает возможности максимально сниз.ить общий уровень шума.However, in the known fans, the o-pimal values of the constructive parameters of the fans are not defined, and the noise level of the fan per unit of its useful power will be min I1malyngm. In addition, in known fans, the effect of the INPUT manifold on the fan noise of the fan is not taken into account, which makes it impossible to minimize the overall noise level as much as possible.

Целью изобретени вл етс уменьшение уровн шума на единицу полезной мощности.The aim of the invention is to reduce the noise level per unit of useful power.

Дл этого радиус зьгка равен 0,1-0,13 D2 и м.ипимальный зазор между зыком и кромкой рабочего колеса ра;вен 0,31)2°, а радиусы закруглени коллектора на входе и выходе потока равны соответственно 0,12-0,14 D и 0,05-0,07 DZ при внутреннем диаметре коллектора , равном 0,95/)ь тае Z) - рабочего колеса на входе потока, а D2 - н-а выходе.For this, the radius of the cable is 0.1-0.13 D2 and the minimum clearance between the tongue and the edge of the impeller; veins 0.31) 2 °, and the radii of rounding of the collector at the inlet and outlet of the flow are respectively 0.12-0 , 14 D and 0.05-0.07 DZ with an internal diameter of the collector equal to 0.95 /) Tae Z) - impeller at the flow inlet, and D2 - n-a outlet.

На фиг. 1 изображен опи1сываемый вентил тор , осевой разрез; на фнг. 2 - сечеи1 е по А-А на фиг. 1.FIG. Figure 1 shows the vented fan, axial section; on fng. 2 - cross section along A-A in FIG. one.

Центробежный вентил тор содержит рабочее колесо 1, входной коллектор 2 и улиточный корпус 3 с зыком 4.The centrifugal fan includes an impeller 1, an inlet manifold 2 and a snail body 3 with a tongue 4.

Описываемый центробежный вентил тор отличаетс от известнЕ 1х тем, что величины основных параметров наход тс в следующей зависимости от диаметра рабочего колеса: раднус зыка г 0,10-О,3D-2, минимальное рассто ние от зыка до кромки рабочего колеса / 0,3 радиусы закруглени коллектора на входе потока R 0,12-0.14 D2, а на выходе 0,05-Q,Q7 D2 при виутреине .м днаметре коллектора Do 0,9oD, где Dt-диаметр рабочего колеса на входе нотока .The described centrifugal fan differs from the known 1x in that the values of the main parameters are in the following dependence on the impeller diameter: radius 0.10-O, 3D-2, minimum distance from the impeller to the edge of the impeller / 0.3 the collector rounding radii at the inlet of the flow are R 0.12-0.14 D2, and the output is 0.05-Q, Q7 D2 at the viutrein. The collector has a minimum gauge of Do 0.9o D, where Dt is the diameter of the impeller at the inlet side.

При выиолнеинн зыка радиусом г меньше 0, повышаетс высокочастотна составл юща аэродинамического шума вептнл тора , а значит и общий уровень шума.When a wave language with a radius r is less than 0, the high-frequency component of the wind tunnel's aerodynamic noise increases, and hence the overall noise level.

Цри изготовле нии зыка с г, большим 0,13Е)2, иовышаютс сопротнвле 1ие потоку i.a выходе и уровень шума.Ries are made of a language with r greater than 0.13E) 2, and are increased to match the output stream i.a and the noise level.

Claims

When the distance from the tongue to the edge of the impeller K.0,30 D2 °°, the gas flow rate between the impeller and the housing increases, which causes an increase in the fan noise level 1e. When the language from the language to the working volume is more than 0.30 2 °, its specified aerodynamic characteristics are reduced and the ratio of the total noise level to the useful power of the ventilation generator, which is equal to the product of the half field, increases its prvpz1vol ytnost. A decrease in the fan noise level per unit of usable air flow is achieved not only with the manufacture of a specific design language, but with the optional production of a collector with a radius of rounded. I at the input / 0.12-0.14 02, and at the output 7 1 0.05-0.07 D2, while the inner diameter of the collector is Do 0 ,. Making a collector with certain radii at the inlet and outlet of the gas flow, PS overshoots its input into the collector and into the impeller, thereby reducing the fan’s vortex noise, and hence the general ypOBeiHb of its discharge noise. The execution of the rounding of the collector pipe at the inlet of the flow, 14D2, without lowering the general noise level of the fan, increases its axial size. Therefore, an increase in the radius of the rounded collector of more than 0.14Z) 2 is undesirable. Performing a rounding radius of the collector at the inlet of flow D leads to the formation of vortices and ultimately to an increase in the total noise level of the fan. The execution of the radius is ziruglen, and the collector at the outlet of the flow R in the range of 0.05-0.07 DZ increases the cross-section of the gas inlet into the impeller, thereby reducing the overall noise level due to the reduction of vortex formation. Increasing the collector radius at the outlet, 05-0.07 D, reduces the diameter of the flow inlet to the collector, which is undesirable, since the fan noise level and the main influence are the diameter of the flow inlet into the impeller, then the radius rounding the collector at the inlet and in the last place the rounding radius of the collector at the outlet. The manufacture of a collector with a DO diameter less than 0.95 Dj of the impeller at the flow inlet (D) will lead to an increase in POIK-a speed in the collector, and therefore to an increase in the obsh, its fan noise level. In addition, the collector can reduce the aerodynamic characteristics of the fan and the fan. A collector with internal diameters greater than D reduces the aerodynamic characteristics of the fan, since the efficiency of the impeller blades on the gas tray is reduced, increasing the ratio of the fan noise level to a unit of its useful capacity. The proposed fan has a mini Noise level per unit of useful power. Claims of the invention: A centrifugal fan containing a snail housing with a tongue and an inlet manifold and an impeller located in the housing, characterized in that, in order to reduce the noise level, the radius of the language faven 0.1-0, and equal to, 31) 2, and the radii of rounding of the collector at the inlet and outlet of the flow are equal to 0, L2-0.14 2 and 0.05-0.07 D, respectively, with an internal diameter of the collector equal to 0.95 D, where DI is the diameter of the impeller at the 1st flow inlet, and D2 - at the outlet.

FIG. 2