CN1129777A - Centrifugal blower - Google Patents
Centrifugal blower Download PDFInfo
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- CN1129777A CN1129777A CN95115116A CN95115116A CN1129777A CN 1129777 A CN1129777 A CN 1129777A CN 95115116 A CN95115116 A CN 95115116A CN 95115116 A CN95115116 A CN 95115116A CN 1129777 A CN1129777 A CN 1129777A
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- housing
- receded disk
- disk impeller
- nose
- centrifugal blower
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
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Abstract
The invention relates to a centrifugal blower, a longitudinal section of the outer shell along the axial direction of a centrifugal impeller is in long circular shape roughly, the axial width is gradually expanded from a nose shape to the rotation direction of the centrifugal impeller and the maximum width part is positioned between the nose shape and an outlet, thus the axial diffusion rate of the shell body can be expanded so as to compensate the inhibition of the radial diffusion rate and ensure the substantive diffusion rate. The invention has no two-dimensional flow, namely, the vortex, etc. of the corner part of a traditional shell body. The invention can realize big wind volume and low noise without the increase of the volume; the wind volume is reduced and the noise is increased even if a thin pipeline is used.
Description
The present invention relates to centrifugal blower that housing is improved.
This traditional class centrifugal blower as shown in figure 37, have receded disk impeller 1, surround the housing 2 of this impeller 1, by being rotated driving with 3 pairs of these receded disk impellers 1 of motor, receded disk impeller 1 is discharged to circumferencial direction after axle direction sucks air, housing 2 is guided exhaust port 4 into after this air that is discharged from is concentrated, and in order by sending behind pipe joint portion 5 and the pipeline 6.
Above-mentioned centrifugal blower, when the pipeline that is used for for example being installed on the ceiling board back side was used ventilation fan, because the space at the ceiling board back side is limited, so require its volume little, air output was big, and noise is low.Yet, realize under the little condition of volume that so big air quantity and low noise are very difficult.
When the narrow and small ceiling board backside space in house is constructed, or, use thinner pipeline in order to reduce cost again.Yet if use the tubule road, the pressure loss that causes thus can increase, thereby reduces air quantity, increases noise.
In view of above-mentioned truth, the object of the present invention is to provide a kind of centrifugal blower, it can realize under the little condition of overall volume that strong wind quantizes and low noiseization, even and use the tubule road also can not cause air quantity reduction, noise to increase.
To achieve these goals, centrifugal blower of the present invention is characterised in that, form housing by following structure, promptly be oblong shape roughly along the axial longitudinal profile of centrifugal blower, its axial width enlarges gradually from nose the sense of rotation to centrifugal blower, and its wideest part is in between the exhaust port.
In this occasion, as the axle direction length of establishing receded disk impeller is b, and external diameter is d2, and the axle direction Extreme breadth of housing is Bmax, then can be decided to be:
b/d2＝0.45～0.70
b/Bmax＝0.55～0.75
Again, the position that partly forms of the axial Extreme breadth of housing preferably is 200～310 ° of angles from nose the sense of rotation to centrifugal blower.
And, the length that the axial minimum width of housing partly forms preferably be in from nose near the sense of rotation of the centrifugal blower scope to nose, especially be in the scope that is below the 45 from nose.
It is very big that the performance of centrifugal blower is influenced by shell dimension.This influence is also bigger than the influence of impeller outer diameter and axial length.
Centrifugal blower generally is radially to form the vortex shape with certain diffusivity, and its diffusivity is big more, can obtain big air quantity and high static pressure more.Yet,,, and have to make the radial diffusion rate of housing to be subjected to a certain degree inhibition because the space is limited in case a for example pipeline that uses centrifugal blower is loaded on the ceiling board back side with ventilation fan.
At this point, as mentioned above, as adopt following structure to form housing, promptly be oblong shape roughly along the axial longitudinal profile of receded disk impeller, its axial width enlarges gradually from nose the sense of rotation to centrifugal blower, and its wideest part is in between the exhaust port, then by increasing the axial diffusion rate of housing, can remedy the radially inhibition of diffusivity, guarantee the substantive diffusivity of housing.
Again, can eliminate at traditional section for oblong housing roughly along the axial longitudinal profile of receded disk impeller is that the two-dimensional flow that the housing corner part of rectangle takes place is phenomenons such as institute's Weihe eddy current, thereby can enlarge wind path in fact, the strong wind that can realize centrifugal blower thus quantizes, low noiseization, also can realize high static pressureization.
Again, in this occasion, the axle direction length of establishing receded disk impeller is b, and external diameter is d2, and the axle direction Extreme breadth of housing is Bmax, if be decided to be:
b/d2＝0.45～0.70
B/Bmax=0.55～0.75 o'clock, then according to actual test result, comparable other numerical value obtain better data.
In addition, if the position that the axial Extreme breadth of housing partly forms is 200～310 ° of angles from nose the sense of rotation to centrifugal blower, then according to actual test result, also comparable other numerical value obtain better data.
And, if the length that the axial minimum width of housing partly forms is near the scope of nose the sense of rotation to centrifugal blower to nose, then can reduce the wind that returns by nose gap, can obtain better result.Wherein, if the length that the least part of this housing forms is in the scope that is below the 45 from nose, then according to actual test result, comparable other numerical value obtain better data.
It below is simple declaration to accompanying drawing.
Fig. 1 is the profile stretch-out view along I-I line among Fig. 2 (expression the present invention the 1st embodiment).
Fig. 2 is whole longitudinal section.
Fig. 3 is a sectional elevation.
Fig. 4 is a plan view.
Fig. 5 is the partial, longitudinal cross-sectional of conventional centrifugal blower case portion.
The partial, longitudinal cross-sectional of Fig. 6 centrifugal blower housing section of the present invention.
Fig. 7 is the local amplification view of receded disk impeller.
Fig. 8 is the amplification view of the blade-section of receded disk impeller.
Fig. 9 is 1 of a performance plot.
Figure 10 is 2 of a performance plot.
Figure 11 is 3 of a performance plot.
Figure 12 is 4 of a performance plot.
Figure 13 is 5 of a performance plot.
Figure 14 is 6 of a performance plot.
Figure 15 is 7 of a performance plot.
Figure 16 is 8 of a performance plot.
Figure 17 is 9 of a performance plot.
Figure 18 is the suitable figure of Fig. 1 of expression the present invention the 2nd embodiment.
Figure 19 is 10 of a performance plot.
Figure 20 is 11 of a performance plot.
Figure 21 is 12 of a performance plot.
Figure 22 is expression the present invention the 3rd embodiment's a side view.
Figure 23 is expression the present invention the 4th embodiment's a sectional elevation.
Figure 24 is the sectional view along Figure 23 II-II line.
Figure 25 is the sectional view along Figure 23 III-III line.
Figure 26 is the sectional view along Figure 23 IV-IV line.
Figure 27 is the sectional view along Figure 23 V-V line.
Figure 28 is the amplification longitudinal section of expression the present invention the 5th embodiment's connection mouth body portion.
Figure 29 is the amplification stereogram of barge board monomer.
Figure 30 is the amplification longitudinal section of connection mouth body portion.
Figure 31 is the suitable figure of Figure 30 of expression the present invention the 6th embodiment.
Figure 32 is half longitudinal section of expression the present invention the 7th embodiment's integral body.
Figure 33 is the suitable figure of Fig. 1.
Figure 34 is the suitable figure of Fig. 2 of expression the present invention the 8th embodiment.
Figure 35 is the suitable figure of Fig. 2 of expression the present invention the 9th embodiment.
Figure 36 is the suitable figure of Fig. 2 of expression the present invention the 10th embodiment.
Figure 37 is the suitable figure of Fig. 2 of expression conventional example.
Below in conjunction with the description of drawings embodiments of the invention.
At first be used for the present invention 1st embodiment of pipeline with ventilation fan in conjunction with Fig. 1 to Figure 17 explanation.
Above-mentioned receded disk impeller 13 is crooked multi-disc blade 14 (see figure 8)s to be arranged in cylindric at the periphery of circular bottom plate 15, and each front end centers on end ring 16 and forms, and its integral body surrounds with housing 17 again.
Above-mentioned housing 17 is that main top and the lid 18 of being located at the intermediate portion up and down in the housing 11 constitute by the upper wall portions 11a of described housing 11, its longitudinal profile along 13 of receded disk impellers is shaped as roughly long-round-shape, and as shown in Figure 3, have and approaching nose 19 of receded disk impeller 13, and have the vortex shape ventilation road 20 that the distance from this nose 19 to 13 of receded disk impellers enlarges gradually.Also just like shown in Bmin among Fig. 1 and the Bmax, the width B of axial (above-below direction among Fig. 2) of this housing 17 enlarges gradually from above-mentioned nose 19 sense of rotation towards receded disk impeller 13 (R represents with arrow), its Extreme breadth Bmax partly is between exhaust port 21 (see figure 3)s, 21 dwindles gradually from this towards exhaust port again.
Here as if the axle direction Extreme breadth Bmax to described housing 17, the axle direction length of establishing described receded disk impeller 13 is b, and external diameter is the d2 (see figure 2), then can be decided to be:
b/d2＝0.45～0.70
b/Bmax＝0.55～0.75
Again, the position that partly forms of the axial Extreme breadth Bmax of housing 17 is 200～310 ° of angles from described nose 19 sense of rotation towards receded disk impeller 13.
In addition, described lid 18 has horn mouth 22 in the substantial middle portion in the face of receded disk impeller 13.Again, housing 11 is installed on the ceiling board 23 in house, is located at the ceiling board back side, and the opening portion below it is topped with decoration frame 24.And mounting plate shown in Figure 4 25 is housed on the ceiling board 23, make with connection mouth body 26 that this mounting plate 25 forms one to be communicated with, and the section thinner than the nominal diameter of traditional used pipeline 27 is the pipeline 28 of circle for circular front end is connecting at the section of connection mouth body 26 with described exhaust port 21.
The below effect of the centrifugal blower of the above-mentioned structure of explanation.
When adopting above-mentioned structure, in case make receded disk impeller 13 rotations with motor 12, the air that receded disk impeller 13 is about in the lower chambers that housing 11 faced sucks from the horn mouth 22 of axle direction by decoration frame 24 and lid 18, and discharge to circumferencial direction, the air of housing 1 ' will discharge is guided exhaust port 21 into after concentrating, and discharges outdoor from connection mouth body 26 through piping 28.
Yet the performance of centrifugal blower is subjected to the size impact of housing 17 very big.The shadow of this outside diameter d 2 that influences ratio centrifugal impeller 13 or axial length b is to also wanting big.
The housing 17 of centrifugal blower generally forms the vortex shape that certain diffusivity is radially arranged, and its diffusivity is big more, can obtain big air quantity, high static pressure more.That is, as shown in Figure 3, if to the outside diameter d 2 of receded disk impeller 13, establishing internal diameter parallel with the face of exhaust port 21 and the housing 17 by receded disk impeller 13 centers is D0, and then D0/d2 is big more, can obtain high-performance more.Yet, present actual conditions are, if will use for example pipeline of centrifugal blower to be loaded on the ceiling board back side with ventilation fan, then can have to dwindling housing 17 diffusivity radially to a certain degree because the space is limited, D0/d2 generally can only promptly must be controlled at below 2.0 about 1.4～1.6.
At this point, as mentioned above, as adopt following structure to form housing 17, promptly be oblong shape roughly along the longitudinal profile of 13 of receded disk impellers, its axial width B enlarges gradually from nose 19 sense of rotation to receded disk impeller 13, and its Extreme breadth Bmax partly is in between the exhaust port 21, then by increasing the axial diffusion rate of housing 17, can remedy the above-mentioned the sort of inhibition that diffusivity is radially carried out of having to, guarantee the substantive diffusivity of housing.
Again, along the longitudinal profile of 13 of receded disk impellers for oblong housing 17 roughly as shown in Figure 6, can eliminate at traditional section is that the two-dimensional flow shown in Fig. 5 arrow of taking place of housing 2 corner parts of rectangle is Weihe eddy current s of institute, thereby can enlarge wind path in fact, the strong wind that can realize centrifugal blower thus quantizes, low noiseization, also can realize high static pressureization.
Thereby, needn't increase volume and can realize that strong wind quantizes and low noiseization, also can realize high static pressureization, even use the tubule road thus, can not cause air quantity to reduce and the noise increase yet.
In addition, as follows when adopting above-mentioned structure, also further found out the optimum size of receded disk impeller 13 and the optimum size of housing 17.
(1) b/d2 (axial length/external diameter of receded disk impeller 13)
The suction area of receded disk impeller 13 and discharge useful area preferably equate.The useful area of so-called receded disk impeller 13, be meant from the area of the circumferential side portion of the discharge wind (air) of receded disk impeller 13 and remove blade 14 and base plate 15, end ring 16 wall thickness separately, and remove again the slough that takes place in the suction side of receded disk impeller 13 (because the direction of air-flow can rapid change, and take place in the suction side of receded disk impeller 13 blow part less than wind ... see Fig. 7), and almost blow circumferential side portion less than wind (because the cause of the wind that returns after by nose 19 gap from the discharge portion of housing 17 and do not blow out the part of wind from receded disk impeller 13 circumferential side portion at the receded disk impeller towards the about 2 one-tenth parts of sense of rotation 13 from nose 19 ... see Fig. 3) area.Ask the axial length b that the suction area of receded disk impeller 13 equates with effective discharge area and the ratio of outside diameter d 2 thus, then:
The suction area S1=π of receded disk impeller 13 * (d1/2)
2
The area S2=π * d2 * b of the circumferential side portion of receded disk impeller 13
The effective circumferential side portion area S2 '=S2 * A * C * E of receded disk impeller 13
D1: the internal diameter (see figure 7) of receded disk impeller 13
A: circumferential side portion area slip=0.40～0.65 of receded disk impeller 13
The circumferential side portion area slip A of so-called receded disk impeller 13, be actually useful area Se that wind goes out and the ratio of circumferential side portion area S2, useful area Se is that 14 sheets apart from p (see figure 8) and effective length b ' (see figure 7) and blade 14 of blade are counted the long-pending of Z.
Thereby,
A=Se/S2=(p * b ' * Z)/(π * d2 * b) common, plastic receded disk impeller 13 is A=0.40～0.55, metal receded disk impeller 13 then is A=0.50～0.65.
C: effective circumferential side portion area slip=about 0.8 that receded disk impeller 13 causes because of the slough
E: receded disk impeller 13 because of nose 19 almost blow area slip=about 0.8 that the part less than wind causes
Can draw thus:
S1＝S2’＝S2×A×C×E
π＝(d1/2)
2＝(π×d2×b)×(0.40～0.65)×0.8×0.8
And the boss ratio of receded disk impeller 13 (d1/d2) is typically designed to 0.82, thus d1=0.82 * d2, the above-mentioned formula of its substitution, then,
π×(0.82×d2/2)
2＝(π×d2×b)×(0.40～0.65)×0.8×0.8
(0.82/2)
2×d2＝b×(0.40～0.65)×0.8×0.8
b/d2＝0.40～0.56
Fig. 9 to Figure 11 is the performance plot of making according to the actual result who records.The result that they record when being 10 (cm), 18 (cm), 23 (cm) according to the outside diameter d 2 of receded disk impeller 13 respectively makes.From Fig. 9 to Figure 11 as can be known, there is the scope b/d2 of an air quantity and static pressure maximum, noise minimum, promptly 0.45～0.70.This scope departs from the numerical value of obtaining from above-mentioned theory slightly, and this is because the air-flow that takes place at blade 14 back sides is peeled off the cause that makes the actual effective circumferential side portion area of blowing dwindle (can think that circumferential side portion area slip A is in fact little than aforesaid numerical value) more.
Thereby the present invention is decided to be according to actual test result and with b/d2 can obtain high performance 0.45～0.70.
(2) b/Bmax (Extreme breadth of the axle direction length/housing 17 of receded disk impeller 13)
Figure 12 to Figure 14 is to use in above-mentioned each performance the receded disk impeller 13 near the size of minimum noise value b/d2, and tests after changing the Extreme breadth Bmax of housing 17 respectively, the performance plot of making according to measured result.From Figure 12 to Figure 14 as can be known, having an air quantity and static pressure is maximum value, and noise is the scope b/Bmax of minimum value, promptly 0.55～0.75.In this occasion, people often think easily that the Extreme breadth Bmax of housing 17 is big more, performance is good more, actually this is not so, because the discharge portion size of housing 17 is limited, its Extreme breadth Bmax is big more, and the minification of discharge portion is just big more, and it is big more that air-flow dwindles the loss that causes, the result makes performance degradation on the contrary.Thereby, must there be the housing Extreme breadth Bmax of the best that can average out.
Thereby the present invention is according to the actual result who records, and b/Bmax also is decided to be can obtain high performance 0.55～0.75.
Figure 15 to Figure 17 is to use the receded disk impeller 13 near the size of above-mentioned minimum noise value b/d2, and tests after changing the position of Extreme breadth Bmax part of housing 17 respectively, the performance plot of making according to measured result.From Figure 15 to Figure 17 as can be known, having an air quantity and static pressure is maximum value, and noise is the position of Extreme breadth Bmax part of the housing 17 of minimum value, promptly is the position at 200～310 ° of angles from nose 19 sense of rotation towards receded disk impeller 13.
Thereby the present invention is according to the actual result who records, and the position of the axle direction Extreme breadth Bmax part of housing 17 is also fixed on the position that can obtain high performance above-mentioned 200～310 ° of angles.
So, compare with measure-alike our company's tradition machine, air quantity can increase by 4～8 (%), and static pressure increases by 5～10 (%), and noise reduces by 0.8～1.3 (dB), has improved performance effectively.
Figure 18 to Figure 21 represents the 2nd embodiment of the present invention, the length that partly forms of axle direction minimum width Bmin of expression housing 17 is near the scope of the sense of rotation towards receded disk impeller 13 to nose 19 from nose 19, especially is in from the length range below nose 19 45.
In case the length that the axle direction minimum width Bmin of housing 17 partly forms be from nose 19 near the sense of rotation of receded disk impeller 13 scope to nose 19, then can reduce the wind that returns by nose 19 gap, can quantize at strong wind, obtain better result aspect the low noiseization, high static pressureization.
Particularly, in this occasion, if the length that the axle direction minimum width Bmin of housing 17 partly forms is from nose 19 scope that exceeds 45, then the path of the wind that blows out from receded disk impeller 13 can narrow down, and shown in the actual test result of Figure 19 to Figure 21, performance can reduce, and its length is fixed on scope below the 45, then can obtain high-performance reliably, especially can under the situation that keeps big air quantity, low noise, increase static pressure.
Figure 22 is the 3rd embodiment of the present invention, form curved shape for nose 19, opposite end (base plate 15 1 sides) the part 19b of the suction side of receded disk impeller 13 (end ring 16 1 sides) part 19a and suction sees near the circumferential side portion or circumferential side portion that extends to receded disk impeller 13 from exhaust port 21, so, near nose 19, pass through the gap of 13 of horn mouth 22 and receded disk impellers respectively, and with the gap of 13 of its opposed housing upper wall portions 11a and receded disk impellers in housing 17 the circuit air quantity just can reduce, so can quantize at strong wind, low noiseization, high static pressure aspect obtains better result.
Figure 23 to Figure 27 is the 4th embodiment of the present invention, the side section shape on each self-ventilation road 20 of the extending portion 19a19b that above-mentioned curved shape is nose 19 is an arcuation, and, be in being shaped as towards exhaust port 21 of its extending portion 19a, 19b of nose 19 housing 17 partly, its section becomes sub-circular by long-round-shape gradually.So, distinguished and admirable can be circular connection mouth body 26 from housing 17 inflow front end sections successfully, flows into section then and is circular pipeline 28, thereby can further increase air quantity and static pressure, reduces noise.
Figure 28 to Figure 30 is the 5th embodiment of the present invention, is located at anti-adverse current in the connection mouth body 26 with 29 one-tenths curved shapes of barge board, when this barge board 29 is opened owing to the pressure of the wind that blows out from exhaust port 21, is in above connection mouth body 26 circular-arc interior.Again, in this occasion, the pivot branch 30 of barge board 29 is located at the essentially identical position, upper limb position with connection mouth body 26 front ends, therefore, enter in the connection mouth body 26 from housing 17, then enter distinguished and admirable in the pipeline 28 and not successfully flowed into by the influence of barge board 29 and pivot branch 30 thereof, so can further increase air quantity and static pressure, the minimizing noise.Also can prevent the pivot branch 30 incidental eddy current sound of this occasion because of barge board 29.
Figure 31 is the 6th embodiment of the present invention, the pivot branch 31 of barge board 29 is located at the position higher than the front end upper limb of connection mouth body 26, can more not be subjected to the influence of barge board 29 and pivot branch 31 thereof and flow into smoothly thereby enter distinguished and admirable in the connection mouth body 26 and in the pipeline 28, and can more effectively prevent pivot branch 31 incidental eddy current sound because of barge board 29 from housing 17.
Figure 32 and Figure 33 are the present invention the 7th embodiments, system gets off according to the deviation of the central position of 26 of receded disk impeller 13 and connection mouth bodies and is staggered in nose 19 the position of housing 17 and the position of discharge portion, and the enlarged shape of nose 19 1 side of housing 17 and discharge portion one side to dwindle shape different, to make correspondence respectively.
In this occasion, owing to adopt the pipeline of this centrifugal blower to be loaded on the narrow ceiling board back side with ventilation fan, thus restricted to the product height, thereby as shown in figure 33, the extreme higher position of motor 12 (size H) is restricted.Wherein, when making the upper wall portions 11a of housing 11 with metal, because the problem of processing (for example deep-draw) aspect, the degree of depth G of housing 17 can not be too big, and the thing followed is that the position of receded disk impeller 13 is also inevitable restricted.
In addition, housing 11 specifically is to be fixed on the wooden frame of being adorned on the ceiling board 23 32.For connection mouth body 26 is connected with pipeline 28, need carry out the tapping operation, and in order to improve operation, requiring there is sufficient space between wooden frame 32 and the connection mouth body 26 again.For this reason, the mounting point of connection mouth 26 must raise.
From aspect of performance, receded disk impeller 13 preferably equates the central position of above-below direction separately with connection mouth body 26, yet, owing to be subjected to the restriction of above-mentioned market demands and processability aspect, can only be staggered in the receded disk impeller 13 and the central position of connection mouth body 26.For this reason, make the shape of different housing 17 as stated above, can make thus to enter distinguished and admirable in connection mouth body 26 and the pipeline 28 from housing 17 and still flow smoothly in the Extreme breadth Bmax of housing 17 part between the discharge portion this dislocation being remedied.
Figure 34 to Figure 36 is the 8th to the 10th embodiment of the present invention, and wherein the housing 33 of Figure 34 is formed by connecting by housing main body 34 and other upper wall 35, and 36 on lid is embedded to this joint.Again, the housing 37 of Figure 35 is by being formed by connecting than low housing main body 38 of the height of above-mentioned housing main body 34 and the upper wall 39 darker than the degree of depth of above-mentioned upper wall 35, and 40 on lid is embedded to this joint.Lid 41 among Figure 36 is because of the thickness of parts, formed the state that horn mouth 42 narrows down gradually from the open underneath portion of housing 11, thereby improved the imbedibility of air.
In addition, the present invention is not limited to address embodiment shown in the drawings, also can do suitably to implement after changing it in the scope that does not break away from main points of the present invention.
Centrifugal fan of the present invention described above has following effect.
The 1st, this centrifugal blower has by rotation air is sucked from direction of principal axis The receded disk impeller that backward circumferencial direction is discharged and have the nose that approaches with this receded disk impeller Shape section and the air that receded disk impeller is discharged concentrate on Vorticose ventilation road and guide discharge into The housing of oral area, and this housing along the axial longitudinal profile of receded disk impeller for roughly long Toroidal, its axial width is from above-mentioned nose the rotation side towards receded disk impeller To gradually enlarging, its largest portion is in between the above-mentioned outlet, thereby needn't increase whole The volume of body can be realized Wind Volume, low noise, and can realize high static pressure, so even use Thin pipe can not cause air quantity to reduce yet and noise increases.
The 2nd, when the direction of principal axis length of establishing above-mentioned receded disk impeller is b, external diameter is d2, when the direction of principal axis Breadth Maximum of housing is Bmax, by following setting, namely
b/d2＝0.45～0.70
B, Bmax=0.55～0.75 Can obtain in practice more preferably Wind Volume, low noise, high static pressure effect.
The 3rd and since the position that the direction of principal axis Breadth Maximum of above-mentioned housing partly forms be from Nose is 200～310 ° of angles to receded disk impeller 13 direction of rotation, so equally can be in reality Obtain desirable Wind Volume, low noise and high static pressure effect in the border.
The 4th, because the length that the direction of principal axis least part of above-mentioned housing forms is from nose Section is near the scope till the receded disk impeller direction of rotation is nose, so can reduce logical The air quantity of crossing the gap of nose section and returning can increase air quantity, reduce noise, improve static pressure The aspect obtains better effect.
The 5th and since the length that the direction of principal axis minimum widith of above-mentioned housing partly forms be from Nose is risen and to be in the following scope of 45° angle, so also can obtain in practice desirable big Air quantity, low noise, high static pressure effect.
Claims (5)
1. centrifugal blower, comprise by rotation from axle direction and suck the receded disk impeller of discharging to circumferencial direction behind the air, have the housing that concentrates on Vorticose ventilation road with described receded disk impeller approaching nose and with the air that receded disk impeller is discharged and guide exhaust port into, it is characterized in that, the shape of described housing is as follows: promptly, be oblong shape roughly along the axial longitudinal profile of receded disk impeller, its width from described nose to described receded disk impeller sense of rotation enlarge gradually, its Extreme breadth partly is in between the described exhaust port.
2. centrifugal blower according to claim 1 is characterized in that, when the axle direction length of establishing receded disk impeller is that b, external diameter are the axle direction Extreme breadth of d2, housing when being Bmax, does following setting:
b/d2＝0.45～0.70
b/Bmax＝0.55～0.75
3. centrifugal blower according to claim 1 is characterized in that, the axle direction Extreme breadth of housing partly is in the position that sense of rotation from nose portion towards receded disk impeller is 200～310 ° of angles.
4. centrifugal blower according to claim 1 is characterized in that, the length that the axle direction minimum width of housing partly forms is in from nose portion towards receded disk impeller near nose the scope.
5. centrifugal blower according to claim 4 is characterized in that, the length that the axle direction minimum width of housing partly forms is in nose scope that is below the 45.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP31650994A JP3442885B2 (en) | 1994-12-20 | 1994-12-20 | Centrifugal blower |
| JP94316509 | 1994-12-20 | ||
| JP316509/94 | 1994-12-20 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1129777A true CN1129777A (en) | 1996-08-28 |
| CN1056672C CN1056672C (en) | 2000-09-20 |
Family
ID=18077904
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN95115116A Expired - Fee Related CN1056672C (en) | 1994-12-20 | 1995-08-18 | Centrifugal blower |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP3442885B2 (en) |
| KR (1) | KR960023830A (en) |
| CN (1) | CN1056672C (en) |
| TW (1) | TW272251B (en) |
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| WO2016095838A1 (en) * | 2014-12-19 | 2016-06-23 | 特灵空调系统(中国)有限公司 | Fan housing |
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| JP2001182692A (en) * | 1999-12-28 | 2001-07-06 | Osaka Gas Co Ltd | Centrifugal air blower |
| CN200941495Y (en) | 2006-08-18 | 2007-08-29 | 富士康(昆山)电脑接插件有限公司 | Electrical connector |
| JP5439423B2 (en) * | 2011-03-25 | 2014-03-12 | 三菱重工業株式会社 | Scroll shape of centrifugal compressor |
| JP5432295B2 (en) * | 2012-01-10 | 2014-03-05 | 富士工業株式会社 | Belmouth and range hood for blower |
| JP6758520B2 (en) * | 2017-10-27 | 2020-09-23 | 三菱電機株式会社 | Centrifugal blower and blower |
| WO2019082392A1 (en) * | 2017-10-27 | 2019-05-02 | 三菱電機株式会社 | Centrifugal blower, air blower device, air conditioning device, and refrigeration cycle device |
| JP7161654B2 (en) * | 2018-02-28 | 2022-10-27 | サンデン株式会社 | Blower |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6295785B1 (en) * | 1999-03-22 | 2001-10-02 | Robert M. Herrmann | Geodesic dome and method of constructing same |
| EP2468343A1 (en) * | 2010-12-21 | 2012-06-27 | Sanofi-Aventis Deutschland GmbH | Front end for an auto-injector |
-
1994
- 1994-12-20 JP JP31650994A patent/JP3442885B2/en not_active Expired - Fee Related
-
1995
- 1995-07-29 TW TW084107867A patent/TW272251B/en active
- 1995-08-18 CN CN95115116A patent/CN1056672C/en not_active Expired - Fee Related
- 1995-08-19 KR KR1019950025813A patent/KR960023830A/en not_active Application Discontinuation
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105332939A (en) * | 2014-08-15 | 2016-02-17 | 珠海格力电器股份有限公司 | Mesh cover ring and fan with same |
| CN105332939B (en) * | 2014-08-15 | 2018-04-17 | 珠海格力电器股份有限公司 | Guard circle and the fan with the guard circle |
| WO2016095838A1 (en) * | 2014-12-19 | 2016-06-23 | 特灵空调系统(中国)有限公司 | Fan housing |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1056672C (en) | 2000-09-20 |
| JPH08177795A (en) | 1996-07-12 |
| TW272251B (en) | 1996-03-11 |
| JP3442885B2 (en) | 2003-09-02 |
| KR960023830A (en) | 1996-07-20 |
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