CN100560984C - Centrifugal multi-blade fan - Google Patents
Centrifugal multi-blade fan Download PDFInfo
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- CN100560984C CN100560984C CNB2007100863839A CN200710086383A CN100560984C CN 100560984 C CN100560984 C CN 100560984C CN B2007100863839 A CNB2007100863839 A CN B2007100863839A CN 200710086383 A CN200710086383 A CN 200710086383A CN 100560984 C CN100560984 C CN 100560984C
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Abstract
A kind of according to centrifugal multi-blade fan of the present invention (10), described centrifugal multi-blade fan (10) is distolateral the be drawn into inner radial of air from the axial direction of running shaft (12), and described air is blown to radially outer.Described centrifugal multi-blade fan (10) comprises a plurality of blades (13), and described a plurality of blades (13) are positioned at running shaft (12) on every side.Each blade (13) has leading edge (22) that is positioned at inner radial and the trailing edge (25) that is positioned at radially outer.For example, the leading edge of each blade (22) has the sharp shape that has 0.2mm or littler radius of curvature.
Description
Technical field
The present invention relates to a kind of centrifugal multi-blade fan, described centrifugal multi-blade fan comprise be positioned at the rotation axial a plurality of blades.
Background technique
Usually, in this centrifugal multi-blade fan, the leading edge of each blade (edge on running shaft next door) cross section forms the shape of smooth curved, so that reduce the airflow breakaway in leading edge to a certain extent, and reduces that fan efficiency reduces and is generated by the described noise that causes that separates.
Yet when the leading edge cross section of each blade formed the shape of smooth curved, fluctuation can temporarily appear in stalling point and air-flow attachment point again.So it is unstable that the air-flow between the blade just becomes.As a result, reduced fan efficiency and produced noise.
For example, the centrifugal multi-blade fan that can reduce airflow breakaway has been described in JP-A-2002-168194.In this centrifugal multi-blade fan, be provided with the protruded object (tumor) that has with the shape similar shapes of separated region in the rear surface of each blade.The rear surface of each blade is on the surface of the side relative with the centrifugal multi-blade fan sense of rotation, and the ventral surface of each blade is the apparent surface of rear surface.
Like this, reduced the space of the airflow breakaway that produces from the rear surface of each blade according to the centrifugal multi-blade fan of JP-A-2002-168194, and reduced the noise that causes by described separation and generate.
Yet stalling point and air-flow attachment point again can erratical fluctuationses.And protruded object is difficult to fully the same with the shape in airflow breakaway zone.So the space that airflow breakaway produces can not be reduced fully.
Summary of the invention
Consider the problems referred to above, the objective of the invention is to propose the centrifugal multi-blade fan that a kind of fan efficiency is improved and noise is lowered.
According to a first aspect of the invention, a kind of centrifugal multi-blade fan is distolateral the be drawn into inner radial of air from the axial direction of running shaft, and described air is blown to radially outer.Described centrifugal multi-blade fan comprises a plurality of blades, and described a plurality of blades are positioned at around the running shaft.Each blade has leading edge that is positioned at inner radial and the trailing edge that is positioned at radially outer.The leading edge of each blade has the sharp shape that has 0.2mm or littler radius of curvature (perhaps edge shape, sharp shape; Edgeshape).
Because leading edge is to have the 0.2mm or the sharp shape of small radii of curvature more, so air-flow can always separate in leading edge.Therefore, separation point and again the fluctuation of attachment point can be prevented from, and may be limited to air-flow between the blade and become unstable.In addition, when leading edge is sharp shape, and be that level and smooth curved shape is compared when leading edge, separation point and again attachment point can be positioned at the upstream side of air-flow.Therefore, air-flow can controlled distance increase between the blade of trailing edge side, and can be so that the steady air current from blowing out between the blade.
As a result, the centrifugal multi-blade fan according to first aspect present invention can improve fan efficiency and reduce noise.
According to a second aspect of the invention, a kind of centrifugal multi-blade fan is distolateral the be drawn into inner radial of air from the axial direction of running shaft, and described air is blown to radially outer.Described centrifugal multi-blade fan comprises a plurality of blades, and described a plurality of blades are positioned at around the running shaft.Each blade has leading edge that is positioned at inner radial and the trailing edge that is positioned at radially outer.Each blade has the ventral surface of the front side on sense of rotation, with the rear surface relative with described ventral surface.Described leading edge has in first angle part of ventral surface side and second angle part on the side of rear surface, and at least the second angle part has 0.2mm or the sharp shape of small radii of curvature more.The leading edge of each blade has the sharp shape that has 0.2mm or littler radius of curvature (perhaps edge shape, sharp shape; Edgeshape).
Because second angle part is sharp shape, so air-flow can be always separated with profile in the rear surface of office, second bight.Therefore, can prevent separation point and the fluctuation of attachment point again, and the air-flow between can limit blade becomes unstable.In addition, when second angle part is sharp shape, and be that level and smooth curved shape is compared when second angle part, separation point and again attachment point can be positioned at the upstream side of air-flow.Therefore, air-flow can controlled distance increase between the blade of trailing edge side, and can be so that the steady air current from blowing out between the blade.
As a result, the centrifugal multi-blade fan according to second aspect present invention can improve fan efficiency and reduce noise.
According to a third aspect of the invention we, a kind of centrifugal multi-blade fan is distolateral the be drawn into inner radial of air from the axial direction of running shaft, and described air is blown to radially outer.Described centrifugal multi-blade fan comprises a plurality of blades, and described a plurality of blades are positioned at around the running shaft.Each blade has leading edge that is positioned at inner radial and the trailing edge that is positioned at radially outer.Described leading edge has the part of sharp shape, thereby always partly locates to separate in described sharp shape from one of the axial direction of running shaft distolateral air.
Because air-flow can be always partly be located to separate in sharp shape, therefore can prevent separation point and the fluctuation of attachment point again, and the instability that becomes of the air-flow between can limit blade.In addition, when leading edge has sharp shape part, compare when not having sharp shape part when leading edge, separation point and again attachment point can be positioned at the upstream side of air-flow.Therefore, air-flow can controlled distance increase between the blade of trailing edge side, and can be so that the steady air current from blowing out between the blade.
As a result, the centrifugal multi-blade fan according to third aspect present invention can improve fan efficiency and reduce noise.
Description of drawings
By describing preferred embodiment in detail below in conjunction with accompanying drawing, other purpose of the present invention and advantage will be more obvious.Among the figure:
Fig. 1 is the partial cross section view that comprises according to the blower of the centrifugal multi-blade fan of the first embodiment of the present invention;
Fig. 2 is the plan view of the blower among Fig. 1;
Fig. 3 is the viewgraph of cross-section of demonstration according to the amplification of first embodiment's centrifugal multi-blade fan;
Fig. 4 is the schematic representation that shows according to the air-flow between first embodiment's the centrifugal multi-blade fan blade;
Fig. 5 A is the chart that shows according to concerning between the maximum ga(u)ge position of first embodiment's centrifugal multi-blade fan blade and the concrete noise level, and Fig. 5 B is demonstration according to the chart that concerns between the maximum ga(u)ge position of first embodiment's centrifugal multi-blade fan blade and the fan efficiency;
Fig. 6 is the cross sectional view of demonstration according to the amplification of the centrifugal multi-blade fan of comparative example 2;
Fig. 7 A to Fig. 7 D is the chart of display application effect of the present invention;
Fig. 8 is the chart of the technical specification (or describing in detail) of blade in demonstration first embodiment and the comparative example 2, and described technical specification is used for the measurement at Fig. 7 A to Fig. 7 D;
Fig. 9 is the viewgraph of cross-section of demonstration according to the amplification of second embodiment's centrifugal multi-blade fan;
With
Figure 10 is the viewgraph of cross-section of demonstration according to the amplification of the 3rd embodiment's centrifugal multi-blade fan.
Embodiment
(first embodiment)
The first embodiment of the present invention obtains describing referring to figs. 1 through Fig. 8.Comprise that the blower 10 according to the centrifugal multi-blade fan of first embodiment of the invention typically is used for air conditioner for vehicles.Fig. 1 is the partial cross section view that comprises according to the blower 10 of centrifugal multi-blade fan 11 of the present invention.Fig. 2 is the plan view of blower 10.
Comprise according to centrifugal multi-blade fan of the present invention (being designated hereinafter simply as fan) 11: around a plurality of blades (wing) 13 of running shaft (center line among Fig. 1) 12 and the retaining plate (wheel hub) 14 of maintenance blade 13.Fan 11 distolaterally is drawn into inner radial with air from one of the axial direction of running shaft 12, and air is blown to radially outer.
In the suction side of fan 11 (that is, the axial direction of running shaft 12 one distolateral), the height H that the guard shield 15 that forms short circular shape on cross section is arranged to each blade 13 reduces to radially outer gradually from the inner radial of fan 11.
In the present embodiment, blade 13 is formed together by resin cutting and guard shield 15 with pursuing part, and blade 13 is fixing integratedly to form fan 11 with retaining plate 14.Blade 13 can form by metal cutting, and blade 13, guard shield 15 and retaining plate 14 can use resin or metal to form.
Resin volute type casing 16 holds fan 11 within it, and forms spiral flow channel 17, and the air that blows from fan 11 enters and by described flow channel 17.
Therefore, will be directed to the cross-section area of the flow channel 17 that is arranged on the distolateral outlet 18 of volute type casing 16, and begin side from the volute of volute type casing 16 and finish side to volute and enlarge gradually from the air that fan 11 blows out.
At inlet 19 external margin, be used for air expansion (expands) is directed to the horn mouth 21 of fan 11 to the inner radial of fan 11 and with inhaled air, form with volute type casing 16.
Fig. 3 has shown at the shape of cross section perpendicular to the blade in the plane of running shaft 12 13.Each blade 13 has circular shape on cross section.Each blade 13 be arranged to an end face to the inner radial of fan 11 and other end the radially outer to fan 11.
13a is a concave to the ventral surface of each blade 13 (that is, facing the surface of the sense of rotation " a " of fan 11), and the rear surface of each blade 13 (apparent surface of ventral surface) 13b is a convex shape.
The first angle part 22a is positioned at the position apart from the rotating center intended distance (hereinafter referred to as internal diameter) " d " of fan 11.In the present embodiment, the second angle part 22b also is positioned at the position apart from the rotating center inside diameter " d " of fan 11.
Because blade 13 forms by the resin cutting in the present embodiment, so the radius of curvature of all above-mentioned angle part 22a, 22b, 25a and 25b is all unlimited near zero.When blade 13 forms by mould, the radius of curvature of above-mentioned angle part 22a, 22b, 25a and 25b will become about 0.2mm owing to the mould manufacturing.
Although the ogive of each blade 13 (perhaps crestal line; Camber line) be set at the center line of the thickness direction of each fan 13 usually, but in the present embodiment, ogive is set on the ventral surface 13a.Therefore, the part that connects the first angle part 22a and third angle part 25a becomes string 29.The ogive chord limits according to JIS B 0132.Vane thickness, chord length, reference angle and concrete noise level also limit according to JIS B 0132.
The vane thickness of each blade 13 changes (hereinafter described direction is called as chordwise direction) on the direction that string 29 extends.Particularly, the rear surface 13b of each blade 13 expands to the opposition side of the sense of rotation " a " of fan 11, thereby the vane thickness of each blade 13 is increased to thickness part 28 gradually from leading edge 22 and trailing edge 25 on chordwise direction.
In the case, the chordwise distance (Lm) that becomes maximum thickness part 28 of the vane thickness from leading edge 22 to each blade 13 and the ratio (Lm/Lc) from the leading edge of each blade 13 to the chord length (Lc) of trailing edge are configured to 0.5.In addition, the maximum blade thickness (tm) of each blade 13 and be configured to 2.8 at the ratio (tm/tf) of the vane thickness (tf) at the first and second angle part 22a, 22b place.
The operation of first embodiment with last surface construction is described below.By driving and rotary fan 11 on the direction of arrow in Fig. 2 " a " to motor 20 power supply, fan 11 is drawn into inner radial from the distolateral inlet 19 at running shaft 12 axial directions with air, and inhaled air is blown to radially outer.The air that blows from fan 11 flows to outlet 18 by flow channel 17, and from exporting 18 outsides that blow to blower 10.
Fig. 4 is the schematic representation that shows the air-flow between the blade 13.Shown in arrow " b ", 19 inhaled airs flow to each blade 13 with reference angle " i " from entering the mouth.In the air that flows to each blade 13, clash into the air of the ventral surface 13a of each blade 13, shown in arrow " c ", flow, and shown in arrow " m ", be blown to the radially outer of fan 11 along the concave of ventral surface 13a.
On the other hand, in the air that flows to each blade 13, the air of bump leading edge 22 shown in arrow " e ", flows to the side of rear surface 13b.Yet air can not flow along the profile of rear surface 13b, because the second angle part 22b has the sharp shape that has 0.2mm or littler radius of curvature.So air-flow always separates with the profile of rear surface 13b by the second angle part 22b.
Shown in the A of attachment point again on the 13b of rear surface, separated air-flow is attached to each blade 13 again near the core of chordwise direction.In the rear surface of each blade 13 13b side, formed the separation zone S of air-flow.Again the air-flow that is attached to the rear surface 13b of each blade 13 flows along convex shape, and is blown to the radially outer of fan 11 shown in arrow " f ".
In Fig. 4, double dot dash line C is the rear surface 13b of each blade 13 in the comparative example 1, and vane thickness is constant substantially on chordwise direction in comparative example 1.Some B among Fig. 4 shows the attachment point again in the comparative example 1.
In first embodiment, the rear surface 13b of each blade 13 expands to the opposition side of the sense of rotation " a " of fan 11, thereby is increased to thickness part 28 at chordwise direction upper blade thickness gradually from leading edge 22 and trailing edge 25.So the space that produces airflow breakaway in rear surface 13b side can be reduced.
More specifically, the A of attachment point again among first embodiment can be positioned at a side of leading edge 22, rather than the B of attachment point again in the comparative example 1.In first embodiment, the separation zone S of air-flow is little than the separation zone of the air-flow in the example 1 frequently, so the minimizing of the fan efficiency η that by airflow breakaway caused of the generation of the minimizing of the fan efficiency η that is caused by airflow breakaway and noise in the comparative example 1 and the generation of noise further reduce.
(L * N) expression, wherein Q is volume of air flow (m to fan efficiency η with η=Q * Pt/
3/ sec), Pt is the total pressure (Pa) of fan, L is that air horsepower (Nm) and N are rotational speed (rad/sec).
Fig. 5 A shows the maximum ga(u)ge position of each blade 13 from the leading edge to the trailing edge and the chart of the relation between the concrete noise level.Fig. 5 B shows the maximum ga(u)ge position of each blade 13 and the chart of the relation between the fan efficiency η.Fig. 5 A and Fig. 5 B have shown in the operation point measurement to have the concrete noise level of several types blade 13 of different maximum ga(u)ge positions and the check result of fan efficiency η.Transverse axis is the ratio Lm/Lc of the distance L m chord length L c from leading edge 22 to the maximum ga(u)ge position.
As shown in Fig. 5 A and Fig. 5 B, by with in the above-mentioned scope that is set in 0.4-0.6 than Lm/Lc, concrete noise level and fan efficiency η are improved.In addition, by with in the above-mentioned scope that is set in 0.45-0.55 than Lm/Lc, concrete noise level and fan efficiency η are further improved.
When the maximum ga(u)ge position is positioned at trailing edge 25 (Lm/Lc=1) side rather than when thickness part 28 (Lm/Lc=0.5), concrete noise level and fan efficiency η variation.Reason is as described below.
As everyone knows,, effectively be increased in the distance between near the blade 13 the trailing edge 25 of sense of rotation " a " side of fan 11, and enlarge near the air passageways area trailing edge 25 in order to increase the air mass flow of sense of rotation " a " side that blows to fan 11.
By with the maximum ga(u)ge set positions near trailing edge 25, the distance between the blade 13 shortens, and has reduced to blow to the volume of air flow of sense of rotation " a " side of fan 11.Therefore, fan efficiency η becomes poorer.In addition, when the volume of air flow reduced, the rotation number of fan 11 must increase to blow predetermined volume of air flow.Therefore, owing to increase the rotation number of fan 11, concrete noise level becomes poorer.
Fig. 6 is the enlarged cross-sectional view of demonstration according to the part of the centrifugal multi-blade fan of comparative example 2.In comparative example 2, the vane thickness of each blade 13 is constant substantially on chordwise direction, and the leading edge 22 of each blade 13 and trailing edge 25 have level and smooth curved shape with respect to first embodiment.
When leading edge 22 has the smooth curved shape of picture comparative example 2, at (shown in arrow " b ") in the air that flows to each blade 13, the air of bump leading edge 22 be divided into shown in arrow " g " towards the air of ventral surface 13a side flow and shown in arrow " h " towards the air of rear surface 13b side flow.Air " g " towards ventral surface 13a side flow is mobile along the concave of ventral surface 13a, and is blown to the radially outer of fan 11 shown in arrow " k ".
On the other hand, can not be mobile towards the air " h " of rear surface 13b side flow along rear surface 13b, and air-flow separates with rear surface 13b.
According to present inventor's test, the separation point of airflow breakaway is erratical fluctuations shown in some C1 among Fig. 6 and C2.According to the fluctuation of separation point, the D1 of attachment point again, the D2 of the air-flow of separation be erratical fluctuations as illustrated in fig. 6 also.
Because separation point C1 and C2 and the fluctuation of attachment point D1 and D2 again, also fluctuate in the separation zone among Fig. 6 shown in S1 and S2, and the air-flow between the blade 13 becomes unstable.Therefore, fan efficiency η reduces and the generation noise.
In first embodiment, as shown in Figure 4, at least the second angle part 22b forms the sharp shape with 0.2mm or littler radius of curvature, so always separate with the profile of rear surface 13b by the second angle part 22b air-flow.Because the separation point of air-flow, the fluctuation of attachment point and separation zone can be prevented from again, so the air-flow between can limit blade 13 becomes unstable.Therefore, can improve fan efficiency η and can reduce noise.
Fig. 7 A-7D is the chart that shows effect of the present invention, and has shown first embodiment's (FE) who compares with the test result of comparative example 2 (CE2) test result.Fig. 8 has shown the chart that is used for the technical specification (or describing in detail) in the measurement of Fig. 7 A to Fig. 7 D of blade.JIS B 8330 and JJIS B 8346 are comply with in above-mentioned test.The inlet angle, exit angle and decalage (perhaps alternate angle; Stagger angle) limits according to JIS B 0132.
As shown in Fig. 7 A-7D, by comparing fan total pressure Pt, fan efficiency η and the concrete noise level that (point of intersection of draw resistance curve (draft resistance curve) and fan total pressure Pt) located in the operation point in operation point (point of intersection of draw resistance curve (draft resistance curve) and fan total pressure Pt) fan total pressure Pt, the fan efficiency η that locates and concrete noise level and comparative example 2 among first embodiment, fan total pressure Pt can increase 11Pa, fan efficiency η can improve 4%, and concrete noise level is to reduce 1.7dB.
When the first angle part 22a and the second angle part 22b have sharp shape, in the airflow strikes first angle part 22a and the second angle part 22b, produced Edge tone, and concrete noise level increases.Yet the level that concrete noise level reduces by top effect is greater than the level of passing through the Edge tone increase of concrete noise level.Therefore, in first embodiment, concrete noise level reduces on the whole.
(second embodiment)
In above-mentioned first embodiment, the first angle part 22a and the second angle part 22b are formed separated from each other at leading edge 22 places of each blade 13.Yet in a second embodiment, as shown in Figure 9, the first angle part 22a and the second angle part 22b are not formed on leading edge 22 places, and leading edge 22 forms the shape of sharp-pointed point.
In addition, in a second embodiment, first embodiment's third angle part 25a and the 4th angle part 25b are not formed on trailing edge 25 places of each blade 13, and trailing edge 25 also forms the shape of sharp-pointed point.
In a second embodiment, because leading edge 22 forms the shape of sharp-pointed point, so air-flow always separates in leading edge 22.Therefore, can obtain the effect similar to first embodiment.
In addition, in a second embodiment, the vane thickness of leading edge 22 sides and trailing edge 25 sides can be thinner than the vane thickness of 22 sides of the leading edge among first embodiment and trailing edge 25 sides.Can be extended because compare the air passageways that is formed between the blade 13 with the air passageways between the blade 13 among first embodiment, so compare with the volume of air flow that blows out from fan 11 among first embodiment, can increase the volume of air flow that blows out from fan 11.
In a second embodiment, the further feature of blade 13 can be formed similar to the further feature among first embodiment.
(the 3rd embodiment)
In above-mentioned first embodiment, the vane thickness of each blade 13 increases to thickness part 28 gradually from leading edge 22 and trailing edge 25 on chordwise direction.Yet in the 3rd embodiment, as shown in Figure 10, vane thickness is constant substantially on chordwise direction.
Although in the 3rd embodiment, the trailing edge 25 of each blade 13 forms the curved shape of cross-section smooth, and third angle part 25a can be individually formed at trailing edge 25 places as first embodiment with the 4th angle part 25b.
In the 3rd embodiment, because the second angle part 22b forms sharp shape, so air-flow can always separate at 22b place, second angle part.The air-flow that separates is attached to each blade 13 again at attachment point E place again, and the separation zone S of air-flow is formed on the rear surface 13b side of each blade 13.
In Figure 10, comparative example 2 is illustrated by double dot dash line F.In comparative example 2, the leading edge 22 of each blade 13 is opposite with the 3rd embodiment to form level and smooth curved shape.
As mentioned above, in comparative example 2, leading edge 22 cross sections are level and smooth curved shape, so separation point, temporarily fluctuate in attachment point and separation zone again.In comparative example 2, in Figure 10, in the upstream of air-flow, separation point is by shown in the C3, and attachment point is by shown in the D3 again, and the separation zone is by shown in the S3.
When leading edge 22 is during as the sharp shape among the 3rd embodiment, separation point can be positioned at the upstream side of air-flow, rather than as the upstream side in the comparative example 2, so the E of attachment point again of air-flow S and separation zone can be positioned at the upstream side of air-flow.
Because between the blade 13 of trailing edge 25 sides air-flow can be controlled distance increase, so that very stable from the air-flow that blows out between the blade 13 in the 3rd embodiment.As a result, can improve fan efficiency according to the 3rd embodiment's centrifugal multi-blade fan and reduce noise simultaneously.
The effect of describing among the 3rd embodiment also can obtain in first embodiment and second embodiment.Promptly, therein the blade 13 that vane thickness increases gradually from leading edge 22 and trailing edge 25 to thickness part 28, by leading edge 22 is formed sharp shape, with compare during for level and smooth curved shape on cross section when leading edge 22, separation point, attachment point E and separation zone S can be positioned at the upstream side of air-flow again.
In the 3rd embodiment, the further feature of blade 13 can be made similarly to the further feature among first embodiment.
(other embodiment)
Although the present invention is noted that for those of ordinary skills also variations and modifications to be arranged with reference to accompanying drawing, fully describe in conjunction with its preferred embodiment.
For example, in first embodiment, the second angle part 22b not only, and also the first angle part 22a, third angle part 25a and the 4th angle part 25b form sharp shape.Yet the first angle part 22a, third angle part 25a and the 4th angle part 25b must not be sharp shapes.For example, they can form the circular shape that has greater than the radius of curvature of 0.2mm.In first embodiment, at least the second angle part 22b forms sharp shape, and other shape of the first angle part 22a, third angle part 25a and the 4th angle part 25b can suitably be changed.
In a second embodiment, the leading edge 22 of blade 13 not only, and also trailing edge 25 forms the shape of sharp-pointed point.Yet trailing edge 25 must not be the shape of sharp-pointed point.For example, trailing edge 25 can form the circular shape that has greater than the radius of curvature of 0.2mm.
These variations and modification will be understood to be in the protection domain that is defined by the claims of the present invention.
Claims (7)
1, a kind of centrifugal multi-blade fan (10), described centrifugal multi-blade fan (10) is with distolateral the be drawn into inner radial of air from the axial direction of running shaft (12), and described air blown to radially outer, wherein said centrifugal multi-blade fan (10) comprising:
A plurality of blades (13), described a plurality of blades (13) are positioned at running shaft (12) on every side,
Wherein each blade (13) has leading edge (22) that is positioned at inner radial and the trailing edge (25) that is positioned at radially outer, and
Wherein the leading edge of each blade (22) has the sharp shape of 0.2mm or littler radius of curvature.
2, centrifugal multi-blade fan according to claim 1 (10),
Wherein each blade (13) has the ventral surface (13a) of the front side on sense of rotation, with the rear surface (13b) relative with ventral surface (13a),
Wherein said leading edge (22) has in first angle part (22a) on ventral surface (13a) side and second angle part (22b) on the side of rear surface (13b), and
Wherein at least the second angle part (22b) has the sharp shape of 0.2mm or littler radius of curvature.
3, centrifugal multi-blade fan according to claim 1 (10), the edge shape of wherein said leading edge (22) are sharp-pointed pointed.
4, centrifugal multi-blade fan according to claim 1 (10), wherein the vane thickness of each blade (13) increases to maximum blade thickness part (28) gradually from leading edge (22) and trailing edge (25) on chordwise direction.
5, centrifugal multi-blade fan according to claim 4 (10), wherein the chordwise distance (Lm) of part (28) and the ratio (Lm/Lc) from the leading edge (22) of each blade (13) to the chord length (Lc) of trailing edge (25) are set in from 0.4 to 0.6 the scope from leading edge (22) to maximum blade thickness.
6, centrifugal multi-blade fan according to claim 5 (10), wherein said being set in than (Lm/Lc) in from 0.45 to 0.55 the scope.
7, centrifugal multi-blade fan according to claim 1 (10), wherein said leading edge (22) has the surface of flat in inner radial.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006070383 | 2006-03-15 | ||
| JP2006070383 | 2006-03-15 | ||
| JP2006283711 | 2006-10-18 |
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| CN101038001A CN101038001A (en) | 2007-09-19 |
| CN100560984C true CN100560984C (en) | 2009-11-18 |
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| CNB2007100863839A Active CN100560984C (en) | 2006-03-15 | 2007-03-15 | Centrifugal multi-blade fan |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104500443A (en) * | 2009-01-08 | 2015-04-08 | 台达电子工业股份有限公司 | Ventilation device and impeller thereof |
| CN107701509B (en) * | 2017-10-23 | 2024-02-23 | 广东美的制冷设备有限公司 | Centrifugal wind wheel, air conditioner indoor unit and air conditioner |
| JP7394614B2 (en) * | 2019-12-18 | 2023-12-08 | サンデン株式会社 | centrifugal blower |
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