CN1985092B

CN1985092B - Centrifugal blower and air conditionaer with centrifugal blower

Info

Publication number: CN1985092B
Application number: CN200580023831XA
Authority: CN
Inventors: 木下欢治郎
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2004-07-14
Filing date: 2005-07-14
Publication date: 2011-09-07
Anticipated expiration: 2025-07-14
Also published as: EP1783374A1; US20070251680A1; WO2006006668A1; JP3879764B2; CN1985092A; AU2005260828B2; AU2005260828A1; AU2005260828B8; EP1783374A4; JP2006194235A

Abstract

A centrifugal blower having a hub (2), to an axis section of which a rotating shaft (4a) of a motor (4) is connected, and a blade wheel (1) provided with blades (3) that are stood on the outer periphery of the hub (2) at predetermined spacings in a circumferential direction and whose front edge (3a) is inclined forward in a rotation direction, wherein a bellmouth (5) having an air suction opening(6) is provided on the air suction side of the blade wheel (1). A circulation flow f 2 is formed, in which the flow flows from the blowout side of the blade wheel (1) through the rear side of the air suction opening (6) in the bellmouth (5) to the blade wheel (1) into which the flow is sucked again.

Description

Centrifugal blower and have the aircondition of centrifugal blower

Technical field

The present invention relates to a kind of centrifugal blower and have the aircondition of centrifugal blower.

Background technique

Usually, as known centrifugal blower, it has impeller, and this impeller comprises: wheel hub, and this wheel hub is connected with the running shaft of motor; Guard shield, this guard shield is with peripheral part relative dispose of predetermined interval with this wheel hub; With a plurality of blades, these a plurality of blades along the circumferential direction are provided at predetermined intervals (with reference to patent documentation 1) between the peripheral part of this guard shield and this wheel hub.

In addition, as the centrifugal blower that does not possess guard shield, it has impeller, and this impeller comprises: wheel hub, and this wheel hub is connected with the running shaft of motor at axis central part; With a plurality of blades, these a plurality of blades are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub and are provided with, and, dispose horn mouth (bellmouth) (with reference to patent documentation 2) in the air sucking side of this impeller with air suction inlet.

Patent documentation 1: the Japanese documentation spy opens flat 11-101194 communique;

Patent documentation 2: the Japanese documentation spy opens flat 10-185238 communique.

But, how disclosed centrifugal blower is positioned at the sweepback aerofoil profile centrifugal blower (being turbofan) of rear side of the sense of rotation of impeller in the above-mentioned patent documentation 1 than internal side diameter end as the outside diameter end of blade, and between the peripheral part of guard shield and wheel hub the configuration a plurality of blades, its complex structure.Therefore, when making impeller, need on the integrally formed structure of wheel hub and blade, engage the guard shield of making separately in addition, thus aspect mass production and cost existing problems.

On the other hand, how disclosed centrifugal blower is positioned at the sweepforward aerofoil profile centrifugal blower (so-called Sirocco fan) of front side of the sense of rotation of impeller in the above-mentioned patent documentation 2 than internal side diameter end as the outside diameter end of blade, impeller simple in structure.But, if the vortex housing is not installed, then can be owing to the deterioration of aerodynamic quality and operation sound property in existing problems aspect property produced in batches and the cost.

Summary of the invention

The present invention puts in view of the above problems and makes, the object of the present invention is to provide a kind ofly help mass production, can reduce cost, noise is low and efficient is high centrifugal blower and have the aircondition of this centrifugal blower.

In the present invention, as first mode that is used to solve above-mentioned problem, centrifugal blower has impeller 1, and this impeller 1 comprises: wheel hub 2, and this wheel hub 2 is connected with the running shaft 4a of motor 4 at axis central part; With a plurality of blades 3, these a plurality of blades 3 are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub 2 and are provided with, and the leading edge 3a of described blade 3 tilts to the place ahead of sense of rotation, and, air sucking side at this impeller 1 disposes the horn mouth 5 with air suction inlet 6, this centrifugal blower is constituted as, and can form side is sucked described impeller 1 once more by the back side of the air suction inlet 6 of described horn mouth 5 the circular flow f that blows out from described impeller 1 ₂

According to such structure, for example in the impeller 1 of the blade of sweptback wing shape with turbofan representative, form from this impeller 1 blow out side by the back side of the air suction inlet 6 of horn mouth 5 by the circular flow f of intake impeller 1 once more ₂

Consequently, the air main flow f by blade 3 ₁At circular flow f ₂Effect under attracted to the forward end of blade 3, thereby can improve the wind speed profile of the exit portion of blade 3, with the low noiseization of the raising of seeking aerodynamic quality and operation sound.

And, owing to do not need guard shield, thus impeller 1 can integrally formedly be formed, and when can seeking to reduce cost, help mass production.

In the present invention, as second mode that is used to solve above-mentioned problem, centrifugal blower has impeller 1, and this impeller 1 comprises: wheel hub 2, and this wheel hub 2 is connected with the running shaft 4a of motor 4 at axis central part; With a plurality of blades 3, these a plurality of blades 3 are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub 2 and are provided with, and the leading edge 3a of the described blade 3 not either direction in sense of rotation the place ahead and sense of rotation rear tilts, air sucking side at this impeller 1 disposes the horn mouth 5 with air suction inlet 6, described centrifugal blower is constituted as, and can form side is sucked described impeller 1 once more by the back side of the air suction inlet 6 of described horn mouth 5 the circular flow f that blows out from described impeller 1 ₂

According to such structure, for example in the impeller 1 of blade with radially dull and stereotyped fan (radical plate fan) representative, also be formed with from this impeller 1 blow out side by the back side of the air suction inlet 6 of horn mouth 5 by the circular flow f of intake impeller 1 once more ₂

Consequently, the air main flow f by each blade 3 ₁At circular flow f ₂Effect under attracted to the forward end of each blade 3, thereby can improve the wind speed profile of the exit portion of each blade 3, with the low noiseization of the raising of seeking aerodynamic quality and operation sound.

The integral body of the blade 3 of preferred described impeller 1 tilts along sense of rotation.

According to such structure, each blade 3 is to the circular flow f that will form by ring body 20 ₂The directive effect that sucks, thus strong circular flow f formed ₂

In addition, even under the situation of the internal diameter of the air suction inlet 6 that increases horn mouth 5, above-mentioned strong circular flow f ₂Also can not be deep into the inboard of each blade 3, but near circulation glibly ring body 20.Consequently can realize better wind pushing performance.

In addition, the integral body of the blade 3 of described impeller 1 also can tilt to the despining direction, that is, can tilt to the opposition side of sense of rotation.

According to this structure, blade 3 is to the circular flow f that is difficult to form by ring body 20 ₂The directive effect that sucks.

In addition, even under the situation of the internal diameter of the air suction inlet 6 that reduces horn mouth 5, above-mentioned strong circular flow f ₂Also can not be deep into the inboard of blade 3, but near circulation glibly ring body 20.Consequently still can realize good wind pushing performance.

In addition, the wing tip of the blade 3 of described impeller 1 also can tilt along sense of rotation.

According to this structure, blade 3 is to the circular flow f that will form by ring body 20 ₂The directive effect that sucks, thus strong circular flow f formed ₂

In addition, even under the situation of the internal diameter of the air suction inlet 6 that increases horn mouth 5, above-mentioned strong circular flow f ₂Also can not be deep into the inboard of blade 3, but near circulation glibly ring body 20.Consequently can realize better wind pushing performance.

In addition, the wing tip of the blade 3 of described impeller 1 also can tilt to the opposition side of sense of rotation.

According to this structure, each blade 3 is to the circular flow f that is difficult to form by ring body 20 ₂The directive effect that sucks.

In addition, even under the situation of the internal diameter of the air suction inlet 6 that reduces horn mouth 5, above-mentioned strong circular flow f ₂Also can not be deep into the inboard of each blade 3, but near circulation glibly ring body 20.Consequently still can realize good wind pushing performance.

In addition, the internal diameter when the air suction inlet 6 of described horn mouth 5 is D ₀, the internal diameter of the blade 3 of described impeller 1 is D ₁, the external diameter of this blade 3 is D ₂The time, also its relation can be set at 0＜(D ₀-D ₁)/(D ₂-D ₁)＜0.6.

Under the aforesaid situation of structure, as the quantity of blade 3 (for example 5～15 time) after a little while, as shown in Figure 4, can suppress for lower than noise Ks, and can further seek the raising of aerodynamic quality and move the low noiseization of sound minimum.

If (D ₀-D ₁)/(D ₂-D ₁) 〉=0.6, then when the quantity of blade 3 after a little while, shown in Fig. 5 (B), when the adverse current f ' that takes place when the leading edge end at blade 3 strengthens, the circular flow f of the trailing edge front end of blade 3 ₂Die down, thereby hindered the raising of aerodynamic quality.

In addition, if 0 〉=(D ₀-D ₁)/(D ₂-D ₁), then when the quantity of blade 3 after a little while, shown in Fig. 5 (A), the leading edge front end of blade 3 can not effectively play a role, thereby has hindered the raising of aerodynamic quality.

In addition, the internal diameter when the air suction inlet 6 of described horn mouth 5 is D ₀, the internal diameter of the blade 3 of described impeller 1 is D ₁, the external diameter of this

blade

3,3 is D ₂The time, also its relation can be set at-0.3＜(D ₀-D ₁)/(D ₂-D ₁)＜0.3.

Under the aforesaid situation of structure, when the quantity many (for example 30～50) of blade 3, as shown in figure 14, can suppress for lower than noise Ks minimum, can advance-go on foot to seek the raising of aerodynamic quality and move the low noiseization of sound.

If (D ₀-D ₁)/(D ₂-D ₁) 〉=0.3, then when the quantity of blade 3 for a long time, when the adverse current that takes place when the leading edge end at blade 3 strengthens, the circular flow f of the trailing edge front end of blade 3 ₂Die down, thereby hindered the raising of aerodynamic quality.

In addition, if-0.3 〉=(D ₀-D ₁)/(D ₂-D ₁), then when the quantity of blade 3 for a long time, the leading edge front end of blade 3 can not effectively play a role, thereby hinders the raising of aerodynamic quality.

In addition, the axial forward end portion at the blade 3 of described impeller 1 also can be provided with the

ring body

9,20 that has predetermined width on centrifugal direction.Under the aforesaid situation of structure, the

ring body

9,20 that rotates together with impeller 1 is used as armature, under the viscous effect of armature, in the outlet stream of blade 3, cause flowing of sense of rotation, consequently, the raising and quietization of air blast performance sought in the rectification that can be by blowing out stream and the rectification of circular flow.

When the centrifugal direction width of described ring body 20 is H, the external diameter of the blade 3 of described impeller 1 is D ₂The time, also its relation can be set at 0.05＜ki=H/D ₂＜0.225.Under the aforesaid situation of structure, as shown in Figure 9, can suppress for lower than noise Ks, and can further seek the raising of aerodynamic quality and the low noiseization of operation sound minimum.

From seeking the angle of low noiseization, more preferred range is 0.1≤ki=H/D ₂≤ 0.15.

If ki=H/D ₂≤ 0.05, then can reduce effect, if ki=H/D ₂〉=0.225, then can produce harmful effect to the formation of circular flow, the circular flow of the trailing edge front end of blade 3 is died down, thereby hindered the raising of aerodynamic quality.

Blowing out side and also can be provided with and to blow out air-flow guiding oblique flow diffuser 23 from this impeller 1 at described impeller 1 to oblique rear side.Under the aforesaid situation of structure, can be efficiently static pressure be carried out in the dynamic pressure of the air-flow that blows out from impeller 1 and recover, thereby go far towards the raising (promptly efficiently, low noise) of performance.

In addition, blowing out side and also can be provided with at described impeller 1 with the centrifugal diffuser 23 of oblique flow that air-flow guides from oblique rear side along centrifugal direction that blows out from this impeller 1.Under the aforesaid situation of structure, can be efficiently static pressure be carried out in the dynamic pressure of the air-flow that blows out from impeller 1 and recover, and make the wind speed profile of the wind that is blown out even, thereby go far towards the raising (promptly efficiently, low noise) of performance.

Outer circumferential side at the air suction inlet 6 of described horn mouth 5 also can be formed with described circular flow f ₂The free air space S that can pass through under the aforesaid situation of structure, is easy to form reliably circular flow f ₂

When the outlet side height of each blade 3 of described impeller 1 is B, the external diameter of this blade 3 is D ₂The time, also its relation can be set at B/D ₂〉=0.113.Under the aforesaid situation of structure, can eliminate the air-flow streamline f of the outlet side of impeller 1 ₁The problem of fluctuation takes place, thereby obtains stable performance.

If B/D ₂＜0.113, then along with the increase of air quantity, the air-flow streamline f of the outlet side of impeller 1 ₁Have big fluctuation, final circular flow f ₂Stream between the closed leave 3, thus performance is sharply descended.

In addition, also the external diameter that constitutes the wheel hub 2 of described impeller 1 can be set for outer diameter D than described each blade 3 ₂Little.Under the aforesaid situation of structure, when the peripheral part in the hub side of each blade 3 forms opening 22, when particularly being provided with the centrifugal diffuser 23 of foregoing oblique flow diffuser 23 or oblique flow, to the resistance force diminishes that blows out of the air-flow that blows out from blade 3.

In addition, when the outlet side height of each blade 3 of described impeller 1 is B, the external diameter of this blade 3 is D ₂The time, also its relation can be set at B/D ₂〉=0.08.Under the aforesaid situation of structure,, also can eliminate the air-flow streamline f of the outlet side of impeller 1 even the outlet side height B of each blade 3 of impeller 1 diminishes ₁The problem of fluctuation takes place, thereby obtains stable performance.

If B/D ₂＜0.08, the air-flow streamline f of the outlet side of impeller 1 then ₁Have big fluctuation, final circular flow f ₂Stream between the closed leave 3, thus performance is sharply descended.

In addition, the quantity of the

blade

3,3 of described impeller 1 is preferably 5 to 15.At this moment, according to the present invention, as shown in Figure 4,, also can suppress for lower than noise Ks, thereby can seek the raising of aerodynamic quality and the low noiseization of operation sound effectively minimum even under the few situation of the quantity of blade 3.

In addition, the quantity of the blade 3 of described impeller 1 also can be 20 to 50.For example, as Figure 14 and shown in Figure 43, when the quantity of blade 3 for a long time, particularly can be when improving the highest static pressure efficiency ratio, suppress for lower than noise level minimum, thereby can more effectively seek the raising of aerodynamic quality and the low noiseization of operation sound.

The quantity of the blade 3 of described impeller 1 is preferably 30 to 72.

As Figure 14 and shown in Figure 50, when the quantity of blade 3 mostly is 30 to 72, can be in the highest static pressure efficiency ratio of special raising effectively, suppress for lower than noise level minimum as far as possible, thereby can more effectively seek the raising of aerodynamic quality and the low noiseization of operation sound.

In addition, aircondition forms by configuration heat exchanger 15 and blower X in the ventilation road 14 in being formed at shell 13, also can adopt the centrifugal blower of aforesaid way to be used as described blower X in this aircondition.Under the aforesaid situation of structure, can bring into play effective function and effect that centrifugal blower has, thereby go far towards to improve the performance of aircondition and reduce its cost.

Description of drawings

Fig. 1 is the centrifugal blower X of first mode of execution of the present invention ₁Sectional arrangement drawing;

Fig. 2 is the centrifugal blower X of first mode of execution ₁The plan view of impeller;

Fig. 3 (A), Fig. 3 (B), Fig. 3 (C) are the centrifugal blower X that first mode of execution is shown ₁The sectional drawing of major component of three kinds of variation;

Fig. 4 is the centrifugal blower X that first mode of execution is shown ₁Minimum than noise Ks with respect to variable k=(D ₀-D ₁)/(D ₂-D ₁) the performance plot of variation;

Fig. 5 (A) is the sectional drawing that the major component of k≤0 o'clock is shown; Fig. 5 (B) is the sectional drawing that the major component of k 〉=0.6 o'clock is shown;

Fig. 6 is the centrifugal blower X that has assembled first mode of execution ₁Aircondition Z ₁Sectional arrangement drawing;

Fig. 7 is the centrifugal blower X of second mode of execution ₂Sectional arrangement drawing;

Fig. 8 (A) to (L) is the centrifugal blower X that second mode of execution of the present invention is shown ₂The sectional drawing of major component of variation;

Fig. 9 is the centrifugal blower X that second mode of execution is shown ₂Minimum than noise Ks with respect to variable ki=H/D ₂The performance plot of variation;

Figure 10 is the centrifugal blower X that second mode of execution is shown ₂Minimum than noise Ks with respect to variables L/D ₂The performance plot of variation;

Figure 11 is the centrifugal blower X that has assembled second mode of execution ₂Aircondition Z ₂Sectional arrangement drawing;

Figure 12 is the centrifugal blower X of the 3rd mode of execution ₃Sectional arrangement drawing;

Figure 13 is the centrifugal blower X of the 3rd mode of execution ₃The plan view of impeller;

Figure 14 is the centrifugal blower X that the 3rd mode of execution is shown ₃Minimum than noise Ks with respect to variable k=(D ₀-D ₁)/(D ₂-D ₁) the performance plot of variation;

Figure 15 is the centrifugal blower X that the 3rd mode of execution is shown ₃Minimum than noise Ks with respect to L/D ₂The performance plot of variation;

Figure 16 is the centrifugal blower X that the 3rd mode of execution is shown ₃Static pressure with respect to the performance plot of the variation of air quantity;

Figure 17 is the centrifugal blower X that the 3rd mode of execution is shown ₃Peak rate of flow coefficient φ max (the peak rate of flow coefficient in the time of will not worsening is as reference value=1) with respect to B/D ₂The performance plot of variation;

Figure 18 is the centrifugal blower X that has assembled the 3rd mode of execution ₃Aircondition Z ₃Sectional arrangement drawing;

Figure 19 is the centrifugal blower X that the 3rd mode of execution is shown ₃Half sectional arrangement drawing of variation I;

Figure 20 is the centrifugal blower X that the 3rd mode of execution is shown ₃Half sectional arrangement drawing of variation II;

Figure 21 is the centrifugal blower X that the 3rd mode of execution is shown ₃Half sectional arrangement drawing of variation III;

Figure 22 is the centrifugal blower X of the 4th mode of execution ₄Half sectional arrangement drawing;

Figure 23 is the centrifugal blower X that the 4th mode of execution is shown ₃Peak rate of flow coefficient φ max (the peak rate of flow coefficient in the time of will not worsening is as reference value=1) with respect to B/D ₂The performance plot of variation;

Figure 24 is the centrifugal blower X that the 4th mode of execution is shown ₄Half sectional arrangement drawing of variation I;

Figure 25 is the centrifugal blower X that the 4th mode of execution is shown ₄Half sectional arrangement drawing of variation II;

Figure 26 is the centrifugal blower X that the 4th mode of execution is shown ₄Half sectional arrangement drawing of variation III;

Figure 27 is the centrifugal blower X that the 4th mode of execution is shown ₄Half sectional arrangement drawing of variation IV;

Figure 28 is the centrifugal blower X that the 4th mode of execution is shown ₄Half sectional arrangement drawing of variation V;

Figure 29 is the centrifugal blower X of the 5th mode of execution ₅Half sectional arrangement drawing;

Figure 30 is the centrifugal blower X that the 5th mode of execution is shown ₅Half sectional arrangement drawing of variation I;

Figure 31 is the centrifugal blower X that the 5th mode of execution is shown ₅Half sectional arrangement drawing of variation II;

Figure 32 is the centrifugal blower X that the 5th mode of execution is shown ₅Half sectional arrangement drawing of structure of variation III;

Figure 33 is the centrifugal blower X that the 5th mode of execution is shown ₅The structure of Comparative Examples (corresponding to Figure 19) of variation III and half sectional arrangement drawing of effect;

Figure 34 is the centrifugal blower X that illustrates as the 5th mode of execution ₅Half sectional arrangement drawing of structure of band guard shield centrifugal blower in the past of another Comparative Examples of variation III;

Figure 35 is the centrifugal blower X that the 5th mode of execution is shown with Comparative Examples with comparing ₅The noise of variation III reduce the chart of effect;

Figure 36 is the horizontal sectional drawing of structure that the centrifugal blower of the 6th mode of execution is shown;

Figure 37 is the sectional arrangement drawing of structure that the centrifugal blower of the 6th mode of execution is shown;

Figure 38 is the horizontal sectional drawing of structure that the centrifugal blower of the 7th mode of execution is shown;

Figure 39 is the sectional arrangement drawing of structure that the centrifugal blower of the 7th mode of execution is shown;

Figure 40 is the horizontal sectional drawing of structure that the centrifugal blower of the 8th mode of execution is shown;

Figure 41 is the sectional arrangement drawing of structure that the centrifugal blower of the 8th mode of execution is shown;

Figure 42 is the horizontal sectional drawing for the structure of the major component of test case that the centrifugal blower of the 8th mode of execution is shown;

Figure 43 is the chart for the relation of the performance of test case and blade sheet number that the centrifugal blower of the 8th mode of execution is shown;

Figure 44 be expression the 8th mode of execution centrifugal blower structure for half sectional arrangement drawing of test case;

Figure 45 is the horizontal sectional drawing of structure that the centrifugal blower of the 9th mode of execution is shown;

Figure 46 is the sectional arrangement drawing of structure that the centrifugal blower of the 9th mode of execution is shown;

Figure 47 is the horizontal sectional drawing of structure that the centrifugal blower of the tenth mode of execution is shown;

Figure 48 is the sectional arrangement drawing of structure that the centrifugal blower of the tenth mode of execution is shown;

Figure 49 is the horizontal sectional drawing for the structure of the major component of test case that the centrifugal blower of the tenth mode of execution is shown;

Figure 50 is the chart for the relation of the performance of test case and blade sheet number that the centrifugal blower of the tenth mode of execution is shown;

Figure 51 is the horizontal sectional drawing of structure that the centrifugal blower of the 11 mode of execution is shown;

Figure 52 is the sectional arrangement drawing of structure that the centrifugal blower of the 11 mode of execution is shown;

Figure 53 is the horizontal sectional drawing of structure that the centrifugal blower of the 12 mode of execution is shown;

Figure 54 is the sectional arrangement drawing of structure that the centrifugal blower of the 12 mode of execution is shown;

Figure 55 is half sectional arrangement drawing of structure that the centrifugal blower of the 13 mode of execution is shown;

Figure 56 is half sectional arrangement drawing of structure of major component that the centrifugal blower of the 13 mode of execution is shown;

Figure 57 illustrates the structure of major component of centrifugal blower of the 13 mode of execution and the horizontal sectional drawing of effect;

Figure 58 illustrates the structure of major component of centrifugal blower of the 13 mode of execution and the horizontal sectional drawing of effect;

Figure 59 is half sectional arrangement drawing of structure that the centrifugal blower of the 14 mode of execution is shown;

Figure 60 illustrates the structure of major component of centrifugal blower of the 14 mode of execution and the horizontal sectional drawing of effect.

Embodiment

Be described in detail several preferred implementation of the present invention with reference to the accompanying drawings.

(first mode of execution)

Fig. 1 to Fig. 6 shows the centrifugal blower X of first mode of execution of the present invention ₁With aircondition Z ₁

As depicted in figs. 1 and 2, this centrifugal blower X ₁Have impeller 1, this impeller 1 comprises: discoideus wheel hub 2, and this wheel hub 2 is connected with the running shaft 4a of motor 4 at axis central part; With a plurality of blades 3, these a plurality of blades 3 are along the circumferential direction erect configuration with predetermined interval at the peripheral part of this wheel hub 2, dispose the horn mouth 5 with air suction inlet 6 in the air sucking side of this impeller 1.

As shown in Figure 2, this impeller 1 is sweepback aerofoil profile (being turbofan), that is, the leading edge of this impeller 1 tilts to the place ahead of sense of rotation, and the outside diameter end 3b of each blade 3 is positioned at the rear side of the sense of rotation M of impeller 1 than internal side diameter end 3a.Like this, shared ratio is big because the static pressure of impeller 1 rises in total head rises, so do not need vortex.

In addition, the axis central part at described wheel hub 2 is formed with the recess 2a that is used to hold described motor 4.Motor fixing part 7 fixed motors 4.The running shaft 4a of 8 support motor 4 of bearing projection.Stiffening ring 9 connects the axial forward end portion of each blade 3.

And, the inside diameter D of the air suction inlet 6 of described horn mouth 5 ₀Be set to inside diameter D than the blade 3 of described impeller 1 ₁Greatly.In addition, at back side (in other words, being exactly outer circumferential side) the formation free air space S of described horn mouth 5, the structure of this free air space S makes it possible to form easily and reliably circular flow f ₂, this circular flow f ₂Be that the side that blows out from described impeller 1 is sucked the described impeller 1 once more by the back side of the air suction inlet 6 of described horn mouth 5.

In addition, the shape of the air suction inlet 6 of described horn mouth 5 both can be depicted as lineal shape as Fig. 3 (A), also can be depicted as wedge shape as Fig. 3 (B), can also be depicted as tubaeform as Fig. 3 (C).

In the present embodiment, the internal diameter when the air suction inlet 6 of described horn mouth 5 is D ₀, the internal diameter of the blade 3 of described impeller 1 is D ₁, the external diameter of this blade 3 is D ₂The time, its relation is set at 0＜(D ₀-D ₁)/(D ₂-D ₁)＜0.6.In addition, the sheet number of blade 3 is 10.

Can obtain action effect as described below in the centrifugal blower as constituted above.That is in said structure, be that the center forms circular flow f in its periphery, with strengthening rib 9 ₂, this circular flow f ₂Be from the back side that blows out the air suction inlet 6 of side by horn mouth 5 of impeller 1 and by the intake impeller 1 once more.Therefore, suck the air main flow f of back from air suction inlet 6 by blade 3 ₁At this circular flow f ₂Effect under attracted to the forward end of blade 3, thereby can improve the wind speed profile of the exit portion of blade 3, with the low noiseization of the raising of seeking aerodynamic quality and operation sound.And, owing to do not need guard shield, thus can impeller 1 is integrally formed, thus when can seeking to reduce cost, help mass production.

In addition, in the present embodiment, when the internal diameter of the air suction inlet 6 of described horn mouth 5 is D ₀, the internal diameter of the blade 3 of described impeller 1 is D ₁, the external diameter of this blade 3 is D ₂The time, its relation is set at 0＜k=(D ₀-D ₁)/(D ₂-D ₁)＜0.6.Like this, as shown in Figure 4, can suppress for lower than noise Ks, thereby can further seek the raising of aerodynamic quality and the low noiseization of operation sound minimum.

If 0 〉=k=is (D ₀-D ₁)/(D ₂-D ₁), then shown in Fig. 5 (A), the leading edge front end of blade 3 can not effectively play a role, thereby has hindered the raising of aerodynamic quality.In addition, if k=is (D ₀-D ₁)/(D ₂-D ₁) 〉=0.6, then shown in Fig. 5 (B), when the adverse current f ' that takes place when the leading edge end at blade 3 strengthens, the circular flow f of the trailing edge front end of blade 3 ₂Die down, thereby hindered the raising of aerodynamic quality.

Suppose the centrifugal blower X of present embodiment ₁In the internal diameter of blade 3 be D ₁, the external diameter of blade 3 is D ₂, the internal diameter of air suction inlet 6 is D ₀, and begin to the positions in 45 one meter in oblique the place aheads of degree microphone 12 to be set at center, the suction side Q from air suction inlet 6, and with k=(D ₀-D ₁)/(D ₂-D ₁) study minimum variation as variable than noise Ks, can obtain result as shown in Figure 4.According to The above results as can be known, in the scope of 0＜k＜0.6, can obtain good operation sound property.

Assembled the centrifugal blower X of present embodiment shown in Fig. 6 ₁Embedded suction head space transfer device Z ₁

In this case, configuration heat exchanger 15 and centrifugal blower X in the ventilation road 14 of the air-flow W in being formed at shell 13 ₁, and the motor fixing part 7 of fixed motor 4 becomes one with the top board 13a of shell 13.This aircondition Z ₁Have the grid 16 of suction, air filter 17, water-collecting tray (drain pan) 18 and air blow-off outlet 19.

Like this, can bring into play centrifugal blower X ₁The effective function effect that is had, thus go far towards aircondition Z ₁Improve performance and reduce cost.In addition, can make the traditional bore of the best relative aperture of air suction inlet 6 big, thereby the pressure loss of air filter 17 grades is suppressed for less.

(second mode of execution)

The centrifugal blower X of second mode of execution of the present invention has been shown among Fig. 7 and Figure 11 ₂With aircondition Z ₂

In this case, at centrifugal blower X ₂Impeller 1 on the configuration ring body 20 to replace the stiffening ring 9 in first mode of execution, described ring body 20 has predetermined width H on centrifugal direction.Other structures and action effect are identical with first mode of execution, therefore omit its explanation.

In addition, shown in Fig. 8 (A)～(L), ring body 20 can be a different shape.Shape shown below only is an example, and the shape beyond the diagram also is fine certainly.

That is, can be shown in Fig. 8 (A), at the axial end joint ring body 20 of blade 3; Also can shown in Fig. 8 (B), ring body 20 be installed with the state that tilts to the wheel hub opposition side; Also can shown in Fig. 8 (C), ring body 20 be installed with the state that tilts to hub side; Also can be shown in Fig. 8 (D), with the end on the centrifugal direction of ring body 20 as arc surface 20a; Also can be shown in Fig. 8 (E), the end on the centrifugal direction of ring body 20 as arc surface 20a, and is installed with integral body ring body 20 to the state of wheel hub opposition side curved incline.In this case, Coanda effect promotes circular flow f ₂Formation.

In addition, also can be shown in Fig. 8 (F), with the face of the wheel hub opposition side of ring body 20 as recess 20b.In this case, impel formation circular flow f owing to produce negative pressure at recess 20b ₂In addition, also can be shown in Fig. 8 (G), the face of the wheel hub opposition side of ring body 20 as recess 20b, and is installed ring body 20 with the state that tilts to hub side.This situation is identical with the situation shown in Fig. 8 (F), promotes circular flow f ₂Formation.In addition, also can be shown in Fig. 8 (H), with the face of the hub side of ring body 20 as recess 20c.In this case, impel formation circular flow f owing to produce negative pressure at recess 20c ₂

In addition, also can be shown in Fig. 8 (I), the face of the hub side of ring body 20 as recess 20c, and is installed ring body 20 with the state that tilts to hub side.This situation is also identical with the situation shown in Fig. 8 (H), promotes circular flow f ₂Formation.In addition, also can shown in Fig. 8 (J), constitute ring body 20 with thicker parts, and form

arc surface

20d, 20e respectively in the tip side of assembly department side and centrifugal direction.Can form smooth circular flow f under this situation ₂

In addition, also can shown in Fig. 8 (K), constitute ring body 20 with thicker parts, and form

arc surface

20d, 20e respectively, and ring body 20 is installed with the state that tilts to hub side in the tip side of assembly department side and centrifugal direction.Also identical under this situation with the situation shown in Fig. 8 (J), can form smooth circular flow f ₂

In addition, also can be shown in Fig. 8 (L), in wheel hub 2, in setting the plane of inclination 2b of the part formation of blade 3 to the inclination of blade opposition side is set, on the other hand, constitute ring body 20 with thicker parts, and form

arc surface

20d, 20e respectively, and then ring body 20 is installed on the plane of inclination 3c (identical) of the front end that is formed at blade 3 with the inclination of the plane of inclination 2b of described wheel hub 2 in the tip side of assembly department side and centrifugal direction.In this case, can be when being shaped the withdrawing pattern direction of mould as outer circumferential side.

Suppose the centrifugal blower X of present embodiment ₂In the external diameter of blade 3 be D ₂, the width of ring body 20 on centrifugal direction is H, and center, the suction side Q from air suction inlet 6 begin to the positions in 45 one meter in oblique the place aheads of degree be provided with microphone 12 study minimum than noise Ks with respect to variable ki=H/D ₂Variation, can obtain result as shown in Figure 9 thus.

According to The above results as can be known, in the scope of 0.05＜ki＜0.225, can obtain good operation sound property.In addition, preferred scope is 0.1＜ki＜0.15.If ki=H/D≤0.05 then can reduce effect,, the circular flow of the trailing edge front end of blade 3 is died down, thereby hindered the raising of aerodynamic quality if ki=H/D 〉=0.225 then can produce harmful effect to the formation of circular flow.

In addition, the distance of ring body 20 and horn mouth 5 is made as L, study minimum than noise Ks with respect to variables L/D ₂Variation, obtain the result of Figure 10 thus.According to The above results as can be known, at L/D ₂Can obtain good operation sound property in 〉=0.1 69 the scope.

Assembled the centrifugal blower X of present embodiment shown in Figure 11 ₂Embedded suction head space transfer device Z ₂In this case, dispose heat exchanger 15 and centrifugal blower X in the ventilation road 14 of the air-flow W in being formed at shell 13 ₂, and the motor fixing part 7 of fixed motor 4 becomes one with the top board 13a of shell 13.Aircondition Z ₂Have the grid 16 of suction, air filter 17, water-collecting tray 18 and air blow-off outlet 19.Like this, can bring into play centrifugal blower X ₂The effective function effect that is had, thus go far towards aircondition Z ₂Improve performance and reduce cost.In addition, can make the traditional bore of the best relative aperture of air suction inlet 6 big, thereby the pressure loss of air filter 17 is suppressed for less.

The centrifugal blower of the respective embodiments described above is applicable to the sheet number of blade 3 few (promptly 5～15) situation.

(the 3rd mode of execution)

Figure 12 to Figure 16 shows the centrifugal blower X of the 3rd mode of execution of the present invention ₃With aircondition Z ₃

As Figure 12 and shown in Figure 13, this centrifugal blower X ₃Have impeller 1, this impeller 1 comprises: discoideus wheel hub 2, and this wheel hub 2 is connected with the running shaft 4a of motor 4 at axis central part; With a plurality of blades 3, described a plurality of blades 3 are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub 2 and are provided with, and dispose the horn mouth 5 with air suction inlet 6 in the air sucking side of this impeller 1.

As shown in figure 13, this impeller 1 is sweepback aerofoil profile (being the turbofan type), that is, the leading edge of this impeller 1 tilts to the place ahead of sense of rotation, and the outside diameter end 3b of each blade 3 is positioned at the rear side of the sense of rotation M of impeller 1 than internal side diameter end 3a.In this case, shared ratio is big because the static pressure of impeller 1 rises in total head rises, so can not need vortex.In addition, the centrifugal blower X of present embodiment ₃The sheet number of blade 3 be set to centrifugal blower X than first and second mode of executions ₁, X ₂In blade sheet number many (for example 30～50).

In addition, the axis central part at described wheel hub 2 is formed with the recess 2a that is used to hold described motor 4.Motor fixing part 7 fixed motors 4.The running shaft 4a of 8 support motor 4 of bearing projection.

In addition, on the impeller 1 of present embodiment, identical with second mode of execution disposed the ring body 20 that has predetermined width H on centrifugal direction.In the present embodiment, the shape of this ring body 20 is, it is towards centrifugal direction and oblique to wheel hub 2 inclinations.

Back side (in other words, outer circumferential side) at described horn mouth 5 forms free air space S, and the structure of this free air space S makes it possible to form easily and reliably circular flow f ₂, this circular flow f ₂Be that the side that blows out from described impeller 1 is sucked the described impeller 1 once more by the back side of the air suction inlet 6 of described horn mouth 5.The shape of the air suction inlet 6 of described horn mouth 5 and first mode of execution identical both can be lineal shape, also can be wedge shape or tubaeform.

In the present embodiment, the internal diameter when the air suction inlet 6 of described horn mouth 5 is D ₀, the internal diameter of the blade 3 of described impeller 1 is D ₁, the external diameter of this blade 3 is D ₂The time, its relation is set at-0.3＜(D ₀-D ₁)/(D ₂-D ₁)＜0.3.In addition, the sheet number of blade 3 is 40.

Can obtain action effect as described below in the centrifugal blower as constituted above.

That is, form from impeller 1 blow out side by the back side of the air suction inlet 6 of horn mouth 5 by the circular flow f the intake impeller 1 once more ₂Therefore, the air main flow f by blade 3 ₁At this circular flow f ₂Effect attracted to down the forward end of blade 3, thereby can improve the wind speed profile of the exit portion of blade 3, with the raising of seeking aerodynamic quality and the low noiseization of operation sound.And, owing to do not need guard shield, thus impeller 1-body can be shaped, thus when can seeking to reduce cost, help mass production.

In addition, in the present embodiment, when the internal diameter of the air suction inlet 6 of described horn mouth 5 is D ₀, the internal diameter of the blade 3 of described impeller 1 is D ₁, the external diameter of this blade 3 is D ₂The time, its relation is set at-0.3＜k=(D ₀-D ₁)/(D ₂-D ₁)＜0.3.Like this, as shown in figure 14, can suppress for lower than noise Ks, thereby can further seek the raising of aerodynamic quality and the low noiseization of operation sound minimum.If-0.3 〉=k=is (D ₀-D ₁)/(D ₂-D ₁), then the leading edge front end of blade 3 can not effectively play a role, thereby has hindered the raising of aerodynamic quality.In addition, if k=is (D ₀-D ₁)/(D ₂-D ₁) 〉=0.3, then the adverse current f ' that takes place in the leading edge end of blade 3 strengthens, simultaneously, the circular flow f of the trailing edge front end of blade 3 ₂Die down, thereby hindered the raising of aerodynamic quality.

Suppose the centrifugal blower X of present embodiment ₃In the internal diameter of blade 3 be D ₁, the external diameter of blade 3 is D ₂, the internal diameter of air suction inlet 6 is D ₀, begin microphone to be set at center, suction side to the position of the oblique the place ahead-Mi of 45 degree from air suction inlet 6, and with k=(D ₀-D ₁)/(D ₂-D ₁) study minimum variation as variable than noise Ks, can obtain result as shown in figure 14.According to The above results as can be known, in the scope of-0.3＜k＜0.3, can obtain good operation sound property.

In addition, centrifugal blower X ₃The outer diameter D of blade 3 ₂And the relation of ring body 20 between the width H on the centrifugal direction and second mode of execution is identical.Centrifugal blower X ₃The outer diameter D of blade 3 ₂And the relation between the distance L of ring body 20 and horn mouth 5 as shown in figure 15, at L/D ₂Can suppress for lower than noise Ks minimum in 〉=0.07 the scope.And at L/D ₂In＜0.07 the scope, minimumly sharply increase than noise Ks.

In addition, if the outlet side height B of each blade 3 of impeller 1 diminishes, the air-flow streamline f of the outlet side of impeller 1 then ₁Fluctuation become big, final circular flow f ₂Stream between the closed leave 3.Like this, shown in the solid line of Figure 16, aerodynamic quality sharply descends, thus the problem of the appearance hysteresis characteristic shown in the dotted line of generation Figure 16.It doesn't matter for this situation and blade sheet number.

Therefore, be set at B/D in the present embodiment ₂〉=0.113.Like this, can eliminate the air-flow streamline f of the outlet side of impeller 1 ₁The such problem of fluctuation takes place, thereby shown in the double dot dash line of Figure 16, can obtain stable performance.If B/D ₂＜0.113, then the air-flow streamline of the outlet side of impeller 1 produces big fluctuation, final circular flow f ₂Stream between the closed leave 3, thus performance is sharply descended.

The centrifugal blower X of research present embodiment ₃Peak rate of flow coefficient φ max (the peak rate of flow coefficient in the time of will not worsening is as reference value=1) with respect to B/D ₂Variation, can obtain result shown in Figure 17.Here, φ max=Qmax/60 (π D ₂B) u ₂u ₂=π D ₂N; Qmax: standard-sized sheet air quantity (m ³/ min); N: revolution (rpm).By the result of Figure 17 as can be known, at B/D ₂In 〉=0.113, peak rate of flow coefficient φ max represents reference value=1.

Assembled the centrifugal blower X of present embodiment shown in Figure 18 ₃An embedded suction aircondition Z ₃In this case, configuration heat exchanger 15 and centrifugal blower X in the ventilation road 14 of the air-flow W in being formed at shell 13 ₃, and the top board 13a of the motor fixing part 7 of fixed motor 4 and shell 13 becomes-body.Aircondition Z ₃Have the grid 16 of suction, air filter 17, water-collecting tray 18 and air blow-off outlet 19.Like this, can bring into play centrifugal blower X ₃The effective function effect that is had, thus go far towards aircondition Z ₃Improve performance and reduce cost.In addition, can make the traditional bore of the best relative aperture of air suction inlet 6 big, thereby the pressure loss of air filter 17 can be suppressed for less.

Below to the centrifugal blower X of the 3rd mode of execution ₃Variation describe.

(variation I)

Also can be as shown in figure 19, the end, top side of each blade 3 that makes impeller 1 is to tilt with roughly the same tilt angle, the tilt angle of ring body 20.In this case, D ₀, D ₁, D ₂, H, L, B relation with described identical before.

(variation II)

Also can be as shown in figure 20, the end, top side of each blade 3 that makes impeller 1 is to tilt with roughly the same tilt angle, the tilt angle of ring body 20, simultaneously, the inlet side end that makes each blade 3 is just to tilt the closer to the mode of the centripetal direction of impeller 1 towards hub side.In this case, D ₀, D ₁, D ₂, H, L, B relation also with described identical before.

(variation III)

Also can be as shown in figure 21, the end, top side of each blade 3 that makes impeller 1 is to tilt with roughly the same tilt angle, the tilt angle of ring body 20, simultaneously, the inlet side end that makes each blade 3 to be just tilting the closer to the mode of the centripetal direction of impeller 1 towards hub side, and forms sawtooth 21 in this inlet side end.Can suppress the formation in the boundary layer of blade surface like this, thereby reduce air-supply sound.In this case, D ₀, D ₁, D ₂, H, L, B relation also with described identical before.

(the 4th mode of execution)

Figure 22 shows the centrifugal blower X of the 4th mode of execution of the present invention ₄At this moment, the outer diameter D of the wheel hub 2 of impeller 1 will be constituted ₃Set outer diameter D for than each blade 3 ₂Little.Like this, when the peripheral part in the hub side of each blade 3 forms opening 22, and when oblique flow diffuser 23 is set as described later (with reference to Figure 29), to the resistance force diminishes that blows out of the air-flow that blows out from blade 3.Other structure is identical with the 3rd mode of execution with action effect, therefore omits its explanation.

Also identical in the present embodiment with the 3rd mode of execution, if the outlet side height B of each blade 3 of impeller 1 diminishes, the air-flow streamline f of the outlet side of impeller 1 then ₁Fluctuation become big, final circular flow f ₂Stream between the closed leave 3.Shown in the solid line of Figure 16, aerodynamic quality sharply descends, thus the problem of the appearance hysteresis characteristic shown in the dotted line of generation Figure 16.It doesn't matter for this situation and blade sheet number.

Therefore, be set at B/D in the present embodiment ₂〉=0.08.Why with B/D ₂The upper limit set for forr a short time than the 3rd mode of execution, be owing to be formed with opening 22 at the peripheral part of the hub side of each blade 3.Like this, can eliminate the air-flow streamline f of the outlet side of impeller 1 ₁The problem of fluctuation takes place, thereby shown in the double dot dash line of Figure 15, can obtain stable performance.If B/D ₂＜0.08, then the air-flow streamline of the outlet side of impeller 1 has big fluctuation, final circular flow f ₂Stream between the

closed impeller

3,3, thus performance is sharply descended.

The centrifugal blower X of research present embodiment ₄Peak rate of flow coefficient φ max (the peak rate of flow coefficient in the time of will not worsening is as reference value=1) with respect to B/D ₂Variation, can obtain result shown in Figure 23.Here, φ max=Qmax/60 (π D ₂B) u ₂u ₂=π D ₂N; Qmax: standard-sized sheet air quantity (m ³/ min); N: revolution (rpm).By the result of Figure 23 as can be known, at B/D ₂In 〉=0.08 scope, peak rate of flow coefficient φ max represents reference value=1.

Below to the centrifugal blower X of the 4th mode of execution ₄Variation describe.

(variation I)

Also can be as shown in figure 24, the end, top side of each blade 3 that makes impeller 1 is to tilt with roughly the same tilt angle, the tilt angle of ring body 20.In this case, D ₀, D ₁, D ₂, H, L, B relation also with described identical before.

(variation II)

Also can be as shown in figure 25, the end, top side of each blade 3 that makes impeller 1 is to tilt with roughly the same tilt angle, the tilt angle of ring body 20, simultaneously, the inlet side end that makes each blade 3 is just to tilt the closer to the mode of the centripetal direction of impeller 1 towards hub side.In this case, D ₀, D ₁, D ₂, H, L, B relation also with described identical before.

(variation III)

Also can be as shown in figure 26, the end, top side of each blade 3 that makes impeller 1 is to tilt with roughly the same tilt angle, the tilt angle of ring body 20, simultaneously, the inlet side end that makes each blade 3 to be just tilting the closer to the mode of the centripetal direction of impeller 1 towards hub side, and forms sawtooth 21 in this inlet side end.Can suppress the formation in the boundary layer of blade surface like this, thereby reduce air-supply sound.In this case, D ₀, D ₁, D ₂, H, L, B relation also with described identical before.

(variation IV)

Also can make impeller 1 become the diagonal flow fan type as shown in figure 27, promptly the outer circumferential side of wheel hub 2 (promptly being provided with the part of blade 3) tilts.In this case, D ₀, D ₁, D ₂, H, L, B relation also with described identical before.

(variation V)

Also can make impeller 1 become the diagonal flow fan type as shown in figure 28, promptly the outer circumferential side of wheel hub 2 (promptly being provided with the part of blade 3) tilts, and the inlet side end that makes each blade 3 is just to tilt the closer to the mode of the centripetal direction of impeller 1 towards hub side.In this case, D ₀, D ₁, D ₂, H, L, B relation also with described identical before.

Certainly, the centrifugal blower X of present embodiment ₄Also can be assembled in the aircondition.

(the 5th mode of execution)

Figure 29 shows the centrifugal blower X of the 5th mode of execution of the present invention ₅At this moment, the outer diameter D of the wheel hub 2 of impeller 1 will be constituted ₃Be set at outer diameter D than each blade 3 ₂Little, simultaneously, the centrifugal diffuser 23 of oblique flow is set in the side that blows out of described impeller 1, the centrifugal diffuser 23 of this oblique flow will further guide along centrifugal direction from oblique rear side from the air-flow that blows out of this impeller 1.Like this, peripheral part in the hub side of each blade 3 forms opening 22, so, to the resistance force diminishes that blows out of the air-flow that blows out from blade 3, and can be efficiently static pressure be carried out in the dynamic pressure of the air-flow that blows out from impeller 1 and recover, thereby go far towards the raising (promptly efficiently, low noise) of performance.Other structure is identical with action effect and the 3rd mode of execution, therefore omits its explanation.

Below to the centrifugal blower X of the 5th mode of execution ₅Variation describe.

(variation I)

Also can be as shown in figure 30, the end, top side of each blade 3 that makes impeller 1 is to tilt with roughly the same tilt angle, the tilt angle of ring body 20.In this case, D ₀, D ₁, D ₂, H, L, B relation also with described identical before.

(variation II)

Also can be as shown in figure 31, the end, top side of each blade 3 that makes impeller 1 is to tilt with roughly the same tilt angle, the tilt angle of ring body 20, simultaneously, the inlet side end that makes each blade 3 is just to tilt the closer to the mode of the centripetal direction of impeller 1 towards hub side.In this case, D ₀, D ₁, D ₂, H, L, B relation also with described identical before.

The centrifugal blower of the 3rd～the 5th above-mentioned mode of execution is applicable to the sheet number of

blade

3,3 many (promptly 30～50) situation.

Certainly, the centrifugal blower X of present embodiment ₄Also can be assembled in the aircondition.In addition, under the situation of vortex housing, also can obtain same effect.

(variation III)

Centrifugal blower X shown in Figure 32 ₅Centrifugal blower X with respect to the 3rd above-mentioned mode of execution ₃Impeller and bell-mouthed structure, it is characterized in that being provided with the centrifugal diffuser 23 of the oblique flow identical with Figure 29～Figure 31.

Like this, as shown in the figure, the wind speed profile of the export department of each blade 3 of impeller 1, then reduces in wheel hub 2 sides sucking the oral-lateral change greatly relatively owing to the guiding function of above-mentioned ring body 20.But then, thereby the blow out air of diffuser passageway wheel hub 2 sides on the oblique flow direction of passing through deflection wheel hub 2 sides is after acceleration on the oblique flow direction, finally the blow-off outlet from centrifugal direction blows out, and, all be uniform for integral body from the speed that blows out that blows out stream that blow-off outlet blew out of centrifugal direction.Thereby when improving air-supply efficient, improved quiet performance effectively.

In order to confirm this effect, for example can with the centrifugal blower X among the variation I of aforesaid the 3rd mode of execution shown in Figure 19 ₃(Figure 33) compare, can draw following result thus with the wind speed profile separately that is provided with the band guard shield centrifugal blower (Figure 34) in the past of the centrifugal diffuser 23 of oblique flow.

That is, at first, in the band guard shield centrifugal blower in the past of Figure 34, the air-flow that sucks from the air suction inlet 6 of horn mouth 5 is to wheel hub 2 lateral deviations stream, thereby the wind speed profile of the export department of each blade 3 is to reduce at air suction inlet 6, and become big in wheel hub 2 sides, so significantly be offset to wheel hub 2 sides.

And the air-flow that moves to these wheel hub 2 lateral deviations further strengthens skew rearward owing to the path of the oblique flow direction of passing through the centrifugal diffuser 23 of oblique flow, and directly blows out along centrifugal direction, and therefore, the wind speed profile of the air-flow that finally blows out rearward significantly is offset.

Relative with it, the centrifugal blower X in the variation I of the 3rd mode of execution shown in Figure 33 ₃Situation under, as stating, do not have guard shield, and ring body 20 be set, at the circular flow f that forms by this ring body 20 in the axial forward end portion periphery of blade 3 ₂Effect under, main flow f ₁Be drawn towards the forward end of blade 3, therefore, the wind speed profile of the exit portion of blade 3 is greatly improved.But, when the blow out air of ring body 20 parts big, and when observing, then not necessarily uniform as blow-off outlet integral body.

Relative with it, for the centrifugal blower X of the centrifugal diffuser 23 of oblique flow described in the modified embodiment of the present embodiment III with radial direction movable that passage shape changes on radial direction ₅Situation, shown in figure 32, finally the wind speed profile of the air-flow that blows out from the blow-off outlet of centrifugal direction is all even for integral body, therefore, as shown in figure 35, it reduces the situation of anti noise much larger than band guard shield centrifugal blower in the past shown in Figure 34.

(the 6th mode of execution)

The impeller of the centrifugal blower of the 6th mode of execution of the present invention has been shown in Figure 36 and Figure 37.

Figure 36 and shown in Figure 37 for example, the impeller 1 of this centrifugal blower comprises: discoideus wheel hub 2, this wheel hub 2 is connected with the running shaft 4a of motor 4 at axis central part; With a plurality of blades 3, described a plurality of blades 3 are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub 2 and are provided with.

Each blade 3 of this impeller 1 is sweepback aerofoil profile (being the turbofan type), promptly, internal side diameter end 3a as blade inlet edge tilts to the place ahead of sense of rotation, and be positioned at the rear side of the sense of rotation M of impeller 1 as the outside diameter end 3b of trailing edge than internal side diameter end 3a, and mean camber line (camberline) protrudes on sense of rotation.

In addition, the quantity of the blade 3 of above-mentioned impeller 1 for example is set to 20～50, and is arranged on the ring body 20 that has predetermined width H on the centrifugal direction in the periphery of its horn mouth side end.In the present embodiment, the horn mouth side end of this ring body 20 and blade 3 is identical with the situation of Figure 24, forms respectively towards centrifugal direction and to the oblique shape of wheel hub 2 inclinations.Other structure and the respective embodiments described above are basic identical.

This impeller 1 is constituted the centrifugal blower of present embodiment with horn mouth 5 combinations identical with the respective embodiments described above under the situation that guard shield is not set, in the centrifugal blower of present embodiment, also can obtain following beneficial effect and the effect identical with the respective embodiments described above.

That is, owing to the existence of above-mentioned ring body 20 form from impeller 1 blow out side by the back side of the air suction inlet 6 of horn mouth 5 by the circular flow f the intake impeller 1 once more ₂, therefore, by the air main flow f of blade 3 ₁At this circular flow f ₂Effect be attracted to down the forward end of blade 3 effectively, and the wind speed profile of the exit portion of blade 3 is improved as equalization, thereby can seek the raising of aerodynamic quality and the low noiseization of operation sound.

And, owing to do not need guard shield, thus can impeller 1 is integrally formed, thus when can seeking simplified structure, reducing cost, help mass production.

(the 7th mode of execution)

Figure 38 and Figure 39 show the impeller of the centrifugal blower of the 7th mode of execution of the present invention.Figure 38 and shown in Figure 39 for example, the impeller 1 of this centrifugal blower comprises: discoideus wheel hub 2, this wheel hub 2 is connected with the running shaft 4a of motor 4 at axis central part; With a plurality of blades 3, described a plurality of blades 3 are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub 2 and are provided with.

Each blade 3 of this impeller 1 is sweepback aerofoil profile (being the turbofan type), promptly, internal side diameter end 3a as blade inlet edge tilts to the place ahead of sense of rotation, and be positioned at the rear side of the sense of rotation M of impeller 1 as the outside diameter end 3b of trailing edge than internal side diameter end 3a, and mean camber line (camber1ine) is recessed in sense of rotation.

(the 8th mode of execution)

Figure 40 and Figure 41 show the impeller of the centrifugal blower of the 8th mode of execution of the present invention.Figure 40 and shown in Figure 41 for example, the impeller 1 of this centrifugal blower comprises: discoideus wheel hub 2, this wheel hub 2 is connected with the running shaft 4a of motor 4 at axis central part; With a plurality of blades 3, described a plurality of blades 3 are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub 2 and are provided with.

Each blade 3 of this impeller 1 is sweepback aerofoil profile (being the turbofan type), promptly, tilt to the place ahead of sense of rotation as the internal side diameter end 3a of blade inlet edge, and be positioned at the rear side of the sense of rotation M of impeller 1 than internal side diameter end 3a, and mean camber line is a lineal shape as the outside diameter end 3b of trailing edge.

In addition, the quantity of the blade 3 of above-mentioned impeller 1 is set to multi-disc, and for example 20～50, and be arranged on the ring body 20 that has predetermined width H on the centrifugal direction in the periphery of its horn mouth side end.In the present embodiment, the horn mouth side end of this ring body 20 and blade 3 is identical with the situation of Figure 24, forms respectively towards centrifugal direction and to the oblique shape of wheel hub 2 inclinations.Other structure and the respective embodiments described above are basic identical.

That is, owing to the existence of above-mentioned ring body 20 form from impeller 1 blow out side by the back side of the air suction inlet 6 of horn mouth 5 by the circular flow f the intake impeller 1 once more ₂, therefore, by the air main flow f of blade 3 ₁At this circular flow f ₂Effect be attracted to down the forward end of blade 3 effectively, and the wind speed profile of the exit portion of blade 3 is improved as equalization, thereby can seek the raising of aerodynamic quality and the low noiseization of operation sound.And, owing to do not need guard shield, thus can impeller 1 is integrally formed, thus when can seeking simplified structure, reducing cost, help mass production.

Centrifugal blower has adopted such impeller and has constituted, that is: described impeller has adopted sweptback wing as described above, it is the outside diameter end 3b of each blade 3 is positioned at the sense of rotation M of impeller 1 than internal side diameter end 3a rear side, and mean camber line is a lineal shape, for the centrifugal blower of formation like this, the chart of Figure 43 shows measures the highest static pressure efficiency than (reference value 1.0) and minimum than the result of noise level than (reference value level ± 0) with its number of blade as parameter.

Constitute the Inlet cone angle θ of each blade 3 by above-mentioned Figure 40 and impeller shown in Figure 41 for the centrifugal blower of measuring ₁, exit angle θ ₂As shown in figure 42, be θ ₁=25 °, θ ₂=50 °, in addition, the entrance height B of blade 3 ₁, the outlet height B ₂, horn mouth 25 the inside diameter D of air suction inlet 6 ₀, blade 3 inside diameter D ₁, outer diameter D ₂Respectively as shown in figure 44, be B ₁=35mm, B ₂=30mm, D ₀=130mm, D ₁=110mm, D ₂=160mm.

Measurement result according to Figure 43 is judged, when the sheet number of blade 3 is less than 20, because above-mentioned circular flow f ₂F as Figure 44 ₂' shown in significantly enter the inboard of blade 3, so mis-behave.On the other hand, when the number of blade surpasses 50, because the interval P between the leading edge of blade 3 became narrow, so mis-behave.

Relative therewith, when the quantity of blade 3 is 20 to 50, not only be difficult to take place problem as described above, the static pressure efficiency ratio is high, and can also will suppress lowly as far as possible than noise level ratio.That is, when air-supply efficient is improved, can also effectively improve quiet performance.

The above-mentioned the 6th, the 7th and the structure of dozenth each mode of execution described later in, can expect the performance boost that causes by identical with it blade quantity equally.

(the 9th mode of execution)

Figure 45 and Figure 46 show the centrifugal blower of the 9th mode of execution of the present invention.Figure 45 and shown in Figure 46 for example, the impeller 1 of this centrifugal blower comprises: discoideus wheel hub 2, this wheel hub 2 is connected with the running shaft 4a of motor 4 at axis central part; With a plurality of blades 3, described a plurality of blades 3 are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub 2 and are provided with.

Each blade 3 of this impeller 1 is radial wing formula (so-called radially dull and stereotyped fan type (radial platefan type)), promptly, internal side diameter end 3a as blade inlet edge does not tilt to the place ahead and the either direction in the rear of sense of rotation M, and mean camber line lineal shape on radial direction extends.

In addition, the quantity of the blade 3 of above-mentioned impeller 1 is set to multi-disc, and for example 30～72, and, be provided with the ring body 20 that on centrifugal direction, has predetermined width H in the periphery of its horn mouth side end.In the present embodiment, the horn mouth side end of this ring body 20 and blade 3 is identical with the situation of above-mentioned Figure 44, forms respectively towards centrifugal direction and to the oblique shape of wheel hub 2 inclinations.Other structures and the respective embodiments described above are basic identical.

Such impeller 1 is constituted the centrifugal blower of present embodiment with horn mouth 5 combinations identical with the respective embodiments described above under the situation that guard shield is not set, in the centrifugal blower of present embodiment, also can obtain following beneficial effect and the effect identical with the respective embodiments described above.

That is, owing to the existence of above-mentioned ring body 20 form from impeller 1 blow out side by the back side of the air suction inlet 6 of horn mouth 5 by the circular flow f the intake impeller 1 once more ₂, therefore, by the air main flow f of blade 3 ₂At this circular flow f ₂Effect be attracted to down the forward end of blade 3 effectively, and the wind speed profile of the exit portion of blade 3 is improved as equalization, thereby can seek the raising of aerodynamic quality and the low noiseization of operation sound.

And, owing to do not need guard shield, thus can impeller 1 is integrally formed, thus can be by simplified structure, improve the significantly reduction that cost is sought in mass production.

(the tenth mode of execution)

Figure 47 and Figure 48 show the impeller of the centrifugal blower of the tenth mode of execution of the present invention.Figure 47 and shown in Figure 48 for example, the impeller 1 of this centrifugal blower comprises: discoideus wheel hub 2, this wheel hub 2 is connected with the running shaft 4a of motor 4 at axis central part; With a plurality of blades 3, described a plurality of blades 3 are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub 2 and are provided with.

Each blade 3 of this impeller 1 is radial wing formula (first deformation types of above-mentioned radially dull and stereotyped fan type (radial platefan type)), promptly, internal side diameter end 3a as blade inlet edge does not tilt to the place ahead and the either direction in the rear of sense of rotation M, and mean camber line tilts to the rear of sense of rotation M a little.

In addition, the quantity of the blade 3 of above-mentioned impeller 1 is set to multi-disc, and for example 30～72, and, be provided with the ring body 20 that on centrifugal direction, has predetermined width H in the periphery of its horn mouth side end.In the present embodiment, the horn mouth side end of this ring body 20 and blade 3 is identical with the situation of Figure 44, forms respectively towards centrifugal direction and to the oblique shape of wheel hub 2 inclinations.Other structures and the respective embodiments described above are basic identical.

That is, owing to the existence of above-mentioned ring body 20 form from impeller 1 blow out side by the back side of the air suction inlet 6 of horn mouth 5 by the circular flow f the intake impeller 1 once more ₂, therefore, by the air main flow f of blade 3 ₁At this circular flow f ₂Effect be attracted to down the forward end of blade 3 effectively, and the wind speed profile of the exit portion of blade 3 is improved as equalization, thereby can seek the raising of aerodynamic quality and the low noiseization of operation sound.And, owing to do not need guard shield, thus can impeller 1 is integrally formed, thus can seek the significantly reduction of cost, and be beneficial to mass production by simplified structure, raising mass production.

Now, for the centrifugal blower of present embodiment, the chart of Figure 50 shows measures the highest static pressure efficiency than (reference value 1.0) and minimum than the result of noise level than (reference value level ± 0) with its number of blade as parameter.

Constitute the Inlet cone angle θ of each blade 3 by above-mentioned Figure 47 and impeller shown in Figure 48 for the centrifugal blower of measuring ₁, exit angle θ ₂As shown in figure 49, be θ ₁=90 °, θ ₂=75 °, in addition, the entrance height B of

blade

3,3 ₁, the outlet height B ₂, horn mouth 5 the inside diameter D of air suction inlet 6 ₀, impeller 1 the inside diameter D of blade 3 ₁, outer diameter D ₂Be B ₁=25mm, B ₂=20mm, D ₀=130mm, D ₁=90mm, D ₂=150mm.

Measurement result according to Figure 50 is judged, in this structure, when the sheet number of blade 3 is less than 30, because above-mentioned circular flow f ₂F as Figure 44 ₂' shown in significantly enter the inboard of blade 3, so suction performance worsens.On the other hand, when the number of blade surpasses 72, because the interval P between front edge 3a, the 3a of blade 3 became narrow, so mis-behave.

Relative therewith, when the quantity of blade 3 is 30 to 72, not only be difficult to take place the problems referred to above, the static pressure efficiency ratio is high, and can also will suppress enough lowly than noise level ratio.That is, when air-supply efficient is improved, can also effectively improve quiet performance.

The above-mentioned the 9th and below in the structure of the 11 each mode of execution that will narrate, also can expect the performance boost that causes by identical with it blade quantity equally.

(the 11 mode of execution)

Figure 51 and Figure 52 show the impeller of the centrifugal blower of the 11 mode of execution of the present invention.For example shown in Figure 51 and Figure 52, the impeller 1 of this centrifugal blower comprises: discoideus wheel hub 2, and this wheel hub 2 is connected with the running shaft 4a of motor 4 at axis central part; With a plurality of blades 3, described a plurality of blades 3 are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub 2 and are provided with.

Each blade 3 of this impeller 1 is radial wing formula (second deformation types of above-mentioned radially dull and stereotyped fan type (radial platefan type)), promptly, internal side diameter end 3a as blade inlet edge does not tilt to the place ahead and the either direction in the rear of sense of rotation M, and mean camber line tilts to the place ahead of sense of rotation M a little.

In addition, the quantity of the blade 3 of above-mentioned impeller 1 and the above-mentioned the same multi-disc that is set to, for example 30～72, and, be provided with the ring body 20 that on centrifugal direction, has predetermined width H in the periphery of its horn mouth side end.In the present embodiment, the horn mouth side end of this ring body 20 and blade 3 is identical with the situation of Figure 44, forms respectively towards centrifugal direction and to the oblique shape of wheel hub 2 inclinations.Other structures and the respective embodiments described above are basic identical.

(the 12 mode of execution)

Figure 53 and Figure 54 show the impeller of the centrifugal blower of the 12 mode of execution of the present invention.

For example shown in Figure 53 and Figure 54, the impeller 1 of this centrifugal blower comprises: discoideus wheel hub 2, and this wheel hub 2 is connected with the running shaft 4a of motor 4 at axis central part; With a plurality of blades 3, described a plurality of blades 3 are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub 2 and are provided with.

Each blade 3 of this impeller 1 is radial wing formula (exit angle θ ₂Be about 90 ° radial tip fan type (radial tip fan type)), that is, and the curve of its mean camber line for being recessed in sense of rotation.

In addition, the quantity of the blade 3 of above-mentioned impeller 1 is also identical with above-mentioned the 6th, the 7th, the 8th mode of execution, for example is set to 20～50, and, be provided with the ring body 20 that on centrifugal direction, has predetermined width H in the periphery of its horn mouth side end.In the present embodiment, the horn mouth side end of this ring body 20 and blade 3 is identical with the situation of above-mentioned Figure 44, forms respectively towards centrifugal direction and to the oblique shape of wheel hub 2 inclinations.Other structures and the respective embodiments described above are basic identical.

(the 13 mode of execution)

Below, in the structure of the major component of the centrifugal blower of the 13 mode of execution of the present invention shown in Figure 55 to Figure 58.

For example shown in Figure 55 to Figure 58, the impeller 1 of this centrifugal blower is identical with the respective embodiments described above, comprising: discoideus wheel hub 2, and this wheel hub 2 is connected with the running shaft of motor at axis central part; With a plurality of blades 3, described a plurality of blades 3 are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub 2 and are provided with.

Each blade 3 of this impeller 1 be its integral body to the blade 3A of the aerofoil profile that leans forward of the place ahead of sense of rotation M predetermined oblique angle (Figure 57), or the blade 3B (Figure 58) of hypsokinesis aerofoil profile in contrast.

In addition, no matter be the blade of which kind of type, the quantity of the blade 3 of above-mentioned impeller 1 is set to multi-disc, for example is 30～72, and, be provided with the ring body 20 that on centrifugal direction, has predetermined width H in the periphery of its horn mouth side end.In the present embodiment, the horn mouth side end of this ring body 20 and blade 3 forms respectively as we know from Figure 55 towards centrifugal direction and to the oblique shape of wheel hub 2 inclinations.Other structures and the respective embodiments described above are basic identical.

Such impeller 1 is constituted the centrifugal blower of present embodiment with horn mouth 5 combinations identical with the respective embodiments described above under the situation that guard shield is not set, in the centrifugal blower of present embodiment, also can obtain following effect and the effect identical with the respective embodiments described above.

That is, form from the back side that blows out the air suction inlet 6 of side by horn mouth 5 of impeller 1 owing to above-mentioned ring body 20 and by the circular flow f the intake impeller 1 once more ₂, therefore, by the air main flow f of blade 3 ₁At circular flow f ₂Effect be attracted to down the forward end of blade 3 effectively, and the wind speed profile of the exit portion of blade 3 is enhanced, thereby can seek the raising of aerodynamic quality and the low noiseization of operation sound.And, owing to do not need guard shield, thus can impeller 1 is integrally formed, thus when can seeking simplified structure, reducing cost, help mass production.

Under the situation of this structure, also by with the inside diameter D of the air suction inlet 6 of horn mouth 5 ₀Relation and produce following distinctive action effect.

When (A) blade 3 is forward blade 3A.

At this moment, for example shown in Figure 57, blade 3 (3A) is to sucking the circular flow f that forms by ring body 20 ₂Directive effect, thereby form strong circular flow f ₂

In addition, shown in label 6A among Figure 55, even in the inside diameter D of the air suction inlet 6 that increases horn mouth 5 ₀Situation under, above-mentioned strong circular flow f ₂Also can not be deep into the inboard of blade 3 (3A), but near circulation glibly ring body 20.Consequently can realize good wind pushing performance.

When (B) blade 3 is for hypsokinesis blade 3B.

At this moment, for example shown in Figure 58, blade 3 (3B) is to being difficult to suck the circular flow f that forms by ring body 20 ₂Directive effect.In addition, shown in label 6B among Figure 55, even in the inside diameter D of the air suction inlet 6 that dwindles horn mouth 5 ₀Situation under, above-mentioned circular flow f ₂Also can not be deep into the inboard of blade 3 (3B), but near circulation glibly ring body 20.Consequently still can realize good wind pushing performance.

(the 14 mode of execution)

Below, in the structure of the major component of the centrifugal blower of the 14 mode of execution of the present invention shown in Figure 59 and Figure 60.

For example shown in Figure 59 and Figure 60, the impeller 1 of this centrifugal blower is identical with the respective embodiments described above, comprising: discoideus wheel hub 2, and this wheel hub 2 is connected with the running shaft of motor at axis central part; With a plurality of blades 3, described a plurality of blades 3 are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub 2 and are provided with.

Each blade 3 of this impeller 1 be only its wing tip 3C to the blade 3A of the aerofoil profile that leans forward of the place ahead of sense of rotation M predetermined oblique angle, or the blade 3B of hypsokinesis aerofoil profile in contrast (bending line L).

No matter be the blade of which kind of type, the quantity of the blade 3 of above-mentioned impeller 1 is set to multi-disc, for example is 30～72, and, be provided with the ring body 20 that on centrifugal direction, has predetermined width H in the periphery of its horn mouth side end.In the present embodiment, the horn mouth side end of this ring body 20 and blade 3 forms respectively as we know from Figure 59 towards centrifugal direction and to the oblique shape of wheel hub 2 inclinations.Other structures and the respective embodiments described above are basic identical.

Shown in Figure 59, such impeller 1 is constituted centrifugal blower with horn mouth 5 combinations identical with the respective embodiments described above, in this centrifugal blower, also can obtain following effect and the effect identical with the respective embodiments described above.

That is, form from the back side that blows out the air suction inlet 6 of side by horn mouth 5 of impeller 1 owing to above-mentioned ring body 20 and by the circular flow f the intake impeller 1 once more ₂, therefore, by the air main flow f of blade 3 ₁At circular flow f ₂Effect attracted to down the forward end of blade 3, and the wind speed profile of the exit portion of blade 3 is enhanced, thereby can seek the raising of aerodynamic quality and the low noiseization of operation sound.And, owing to do not need guard shield, thus can impeller 1 is integrally formed, thus when can seeking simplified structure and reducing cost, help mass production.

(A) be that the wing tip 3C of blade 3 is when forward blade 3A that sense of rotation the place ahead tilts.

At this moment, for example shown in Figure 60, blade 3 (3A) is to sucking the circular flow f that forms by ring body 20 ₂Directive effect, thereby form more intense circular flow f ₂

In addition, shown in label 6A among Figure 59, even in the inside diameter D of the air suction inlet 6 that increases horn mouth 5 ₀Situation under, above-mentioned more intense circular flow f ₂Also can not be deep into the inboard of blade 3 (3A), but near circulation glibly ring body 20.Consequently can realize good wind pushing performance.

(B) be that the wing tip 3C of blade 3 is when hypsokinesis blade 3B that the sense of rotation rear tilts.

At this moment, for example shown in Figure 60, blade 3 (3B) is to being difficult to suck the circular flow f that forms by ring body 20 ₂Directive effect.

In addition, shown in label 6B among Figure 59, even in the inside diameter D of the air suction inlet 6 that dwindles horn mouth 5 ₀Situation under, above-mentioned strong circular flow f ₂Also can not be deep into the inboard of blade 3 (3B), but near circulation glibly ring body 20.Consequently still can realize good wind pushing performance.

Claims

1. centrifugal blower, this centrifugal blower has impeller (1), and this impeller (1) comprising: wheel hub (2), this wheel hub (2) is connected with the running shaft (4a) of motor (4) at axis central part; With a plurality of blades (3), these a plurality of blades (3) are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub (2) and are provided with, and the leading edge (3a) of described blade (3) tilts to the place ahead of sense of rotation,

Dispose the have air suction inlet horn mouth (5) of (6) in the air sucking side of this impeller (1), described centrifugal blower is characterised in that,

This centrifugal blower is constituted as, and can form side is sucked described impeller (1) once more by the back side of the air suction inlet (6) of described horn mouth (5) the circular flow (f that blows out from described impeller (1) ₂),

Axial forward end portion at the blade (3) of described impeller (1) is provided with the ring body (9,20) that has predetermined width on centrifugal direction,

When the centrifugal direction width of described ring body (20) is H, the external diameter of the blade (3) of described impeller (1) is D ₂The time, its relation is set at 0.05＜ki=H/D ₂＜0.225.

2. centrifugal blower as claimed in claim 1 is characterized in that, the wing tip of the blade (3) of described impeller (1) tilts along sense of rotation.

3. centrifugal blower as claimed in claim 1 is characterized in that, the wing tip of the blade (3) of described impeller (1) tilts to the opposition side of sense of rotation.

4. centrifugal blower as claimed in claim 1 is characterized in that, when the internal diameter of the air suction inlet (6) of described horn mouth (5) is D ₀, the internal diameter of the blade (3) of described impeller (1) is D ₁, the external diameter of this blade (3) is D ₂The time, its relation is set at 0＜(D ₀-D ₁)/(D ₂-D ₁)＜0.6.

5. centrifugal blower as claimed in claim 1 is characterized in that, when the internal diameter of the air suction inlet (6) of described horn mouth (5) is D ₀, the internal diameter of the blade (3) of described impeller (1) is D ₁, the external diameter of this blade (3) is D ₂The time, its relation is set at-0.3＜(D ₀-D ₁)/(D ₂-D ₁)＜0.3.

6. centrifugal blower as claimed in claim 1 is characterized in that, is provided with the oblique flow diffuser (23) that air-flow guides to oblique rear side that blows out from this impeller (1) in the side that blows out of described impeller (1).

7. centrifugal blower as claimed in claim 1 is characterized in that, is provided with oblique flow and the centrifugal diffuser (23) that air-flow guides from oblique rear side along centrifugal direction that blow out from this impeller (1) in the side that blows out of described impeller (1).

8. centrifugal blower as claimed in claim 1 is characterized in that, is formed with described circular flow (f at the outer circumferential side of the air suction inlet (6) of described horn mouth (5) ₂) free air space (S) that can pass through.

9. centrifugal blower as claimed in claim 1 is characterized in that, when the outlet side height of each blade (3) of described impeller (1) is B, the external diameter of this blade (3) is D ₂The time, its relation is set at B/D ₂〉=0.113.

10. centrifugal blower as claimed in claim 1 is characterized in that, will constitute the outer diameter D of the wheel hub (2) of described impeller (1) ₃Set outer diameter D for than described each blade (3) ₂Little.

11. centrifugal blower as claimed in claim 10 is characterized in that, when the outlet side height of each blade (3) of described impeller (1) is B, the external diameter of this blade (3) is D ₂The time, its relation is set at B/D ₂〉=0.08.

12. centrifugal blower as claimed in claim 1 is characterized in that, the quantity of the blade (3) of described impeller (1) is 20 to 50.

13. centrifugal blower as claimed in claim 1 is characterized in that, the quantity of the blade (3) of described impeller (1) is 30 to 72.

14. an aircondition, this aircondition forms by configuration heat exchanger (15) and blower (X) in the ventilation road (14) in being formed at shell (13), and described aircondition is characterised in that,

This aircondition adopts the described centrifugal blower of claim 1 to be used as described blower (X).

15. a centrifugal blower, this centrifugal blower have impeller (1), this impeller (1) comprising: wheel hub (2), and this wheel hub (2) is connected with the running shaft (4a) of motor (4) at axis central part; With a plurality of blades (3), these a plurality of blades (3) are along the circumferential direction erect with predetermined interval at the peripheral part of this wheel hub (2) and are provided with, and the not inclination of the either direction in sense of rotation the place ahead and sense of rotation rear of the leading edge (3a) of described blade (3),

16. centrifugal blower as claimed in claim 15 is characterized in that, the integral body of the blade (3) of described impeller (1) tilts along sense of rotation.

17. centrifugal blower as claimed in claim 15 is characterized in that, the integral body of the blade (3) of described impeller (1) tilts to the opposition side of sense of rotation.

18. centrifugal blower as claimed in claim 15 is characterized in that, the wing tip of the blade (3) of described impeller (1) tilts along sense of rotation.

19. centrifugal blower as claimed in claim 15 is characterized in that, the wing tip of the blade (3) of described impeller (1) tilts to the opposition side of sense of rotation.

20. centrifugal blower as claimed in claim 15 is characterized in that, when the internal diameter of the air suction inlet (6) of described horn mouth (5) is D ₀, the internal diameter of the blade (3) of described impeller (1) is D ₁, the external diameter of this blade (3) is D ₂The time, its relation is set at 0＜(D ₀-D ₁)/(D ₂-D ₁)＜0.6.

21. centrifugal blower as claimed in claim 15 is characterized in that, when the internal diameter of the air suction inlet (6) of described horn mouth (5) is D ₀, the internal diameter of the blade (3) of described impeller (1) is D ₁, the external diameter of this blade (3) is D ₂The time, its relation is set at-0.3＜(D ₀-D ₁)/(D ₂-D ₁)＜0.3.

22. centrifugal blower as claimed in claim 15 is characterized in that, is provided with the oblique flow diffuser (23) that air-flow guides to oblique rear side that blows out from this impeller (1) in the side that blows out of described impeller (1).

23. centrifugal blower as claimed in claim 15 is characterized in that, is provided with oblique flow and the centrifugal diffuser (23) that air-flow guides from oblique rear side along centrifugal direction that blow out from this impeller (1) in the side that blows out of described impeller (1).

24. centrifugal blower as claimed in claim 15 is characterized in that, is formed with described circular flow (f at the outer circumferential side of the air suction inlet (6) of described horn mouth (5) ₂) free air space (S) that can pass through.

25. centrifugal blower as claimed in claim 15 is characterized in that, when the outlet side height of each blade (3) of described impeller (1) is B, the external diameter of this blade (3) is D ₂The time, its relation is set at B/D ₂〉=0.113.

26. centrifugal blower as claimed in claim 15 is characterized in that, will constitute the outer diameter D of the wheel hub (2) of described impeller (1) ₃Set outer diameter D for than described each blade (3) ₂Little.

27. centrifugal blower as claimed in claim 26 is characterized in that, when the outlet side height of each blade (3) of described impeller (1) is B, the external diameter of this blade (3) is D ₂The time, its relation is set at B/D ₂〉=0.08.

28. centrifugal blower as claimed in claim 15 is characterized in that, the quantity of the blade (3) of described impeller (1) is 5 to 15.

29. centrifugal blower as claimed in claim 15 is characterized in that, the quantity of the blade (3) of described impeller (1) is 20 to 50.

30. centrifugal blower as claimed in claim 15 is characterized in that, the quantity of the blade (3) of described impeller (1) is 30 to 72.

31. an aircondition, this aircondition forms by configuration heat exchanger (15) and blower (X) in the ventilation road (14) in being formed at shell (13), and described aircondition is characterised in that,

This aircondition adopts the described centrifugal blower of claim 15 to be used as described blower (X).