CN101660535A - Centrifugal fan and air fluid machinery using the same - Google Patents

Centrifugal fan and air fluid machinery using the same Download PDF

Info

Publication number
CN101660535A
CN101660535A CN200910163428A CN200910163428A CN101660535A CN 101660535 A CN101660535 A CN 101660535A CN 200910163428 A CN200910163428 A CN 200910163428A CN 200910163428 A CN200910163428 A CN 200910163428A CN 101660535 A CN101660535 A CN 101660535A
Authority
CN
China
Prior art keywords
blade
centrifugal fan
mainboard
air
guard shield
Prior art date
Application number
CN200910163428A
Other languages
Chinese (zh)
Other versions
CN101660535B (en
Inventor
本多武史
佐藤博利
杉村和之
Original Assignee
株式会社日立产机系统
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to JP2008220905 priority Critical
Priority to JP2008-220905 priority
Priority to JP2008220905A priority patent/JP4612084B2/en
Application filed by 株式会社日立产机系统 filed Critical 株式会社日立产机系统
Publication of CN101660535A publication Critical patent/CN101660535A/en
Application granted granted Critical
Publication of CN101660535B publication Critical patent/CN101660535B/en

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/26Rotors specially for elastic fluids
    • F04D29/28Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30Vanes
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/26Rotors specially for elastic fluids
    • F04D29/28Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05DINDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00Components
    • F05D2240/20Rotors
    • F05D2240/30Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/303Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the leading edge of a rotor blade

Abstract

The present invention provides a centrifugal fan and an air fluid machinery which can inhibit stripping phenomenon of inner part of the fan within a large operating range and meet low noise and high effect of the operating air flow within a large range. In the centrifugal fan, a blade is arranged along the circumferential direction between a ring-shaped shield for forming a suction inlet and a mainboard arranged opposite to the shield, the blade along the radial direction boosts pressure and sprays out the fluid attracted from the axial direction, the shape of the front edge of the blade has aconcave-shaped body at the approximately central position in the height direction and has convex-shaped bodies at the mainboard and the shield sides, in the front edge of the blade of an suction inlet, the front edge of the shield side goes forward along the rotation direction compared with the front edge of the mainboard, the mounting angle of the mainboard of the blade has two inflection pointswith the trend outer diameter, and the mounting angle of the shield is formed by one inflection point, thereby can realize high efficiency and low noise of the centrifugal fan at the design point andthe low wind area.

Description

Centrifugal fan and use its air fluid machinery
Technical field
The present invention relates to centrifugal fan and carry the air fluid machinery that this centrifugal fan carries out the discharge of air, the blowing device of supply etc., in more detail, relate to and be used for obtaining high efficiency and also reducing the structure of the noise that produces from this centrifugal fan at the strong wind weight range.
Background technique
Existing centrifugal fan for example also has expression in following patent documentation 1, shown in accompanying drawing 11 and accompanying drawing 12, existing centrifugal fan comprises usually: mainboard 1, and it connects mutually with motor axis of rotation; The guard shield 2 of ring-type, it is arranged on the relative position of this mainboard 1; And multi-disc blade 3, it is opened along circumferential sky and is spaced apart and arranged between mainboard 1 and the guard shield 2, and the leading edge 3a of described blade is positioned at the position of directly comparing inner footpath with the suction of guard shield, and on the other hand, trailing edge 3b is positioned at the outer periphery of mainboard.
Patent documentation 1:(Japan) spy opens 2003-206892 number
That is, in existing centrifugal fan, be created in mobile the peeling off on the surface of described blade 3 from described guard shield 2 leaked-in airs, and produce and the rightabout adverse current phenomenon of sense of rotation at described trailing edge side 3b.These peel off phenomenon and the adverse current phenomenon often takes place, and they are to cause the reason that efficient reduces or noise increases.In order to reduce the influence that is brought by these phenomenons, described blade 3 departs from sense of rotation side with respect to described blade 3 with the commissura portion of described mainboard 1 with the joining portion of described guard shield 2 and engages, and in addition, the front end of described blade 3 is oblique to the sense of rotation inclination.Thus, constitute when preventing to rotate as far as possible structure in the generation of peeling off phenomenon and adverse current phenomenon of the suction surface side of described blade 3.
Usually aspect the minimizing noise, the rotating speed that reduces centrifugal fan is the most effective, even in said structure, if reduce the rotating speed of centrifugal fan, the static pressure of the air that then blows out reduces, but meanwhile, the worry that causes air quantity decline is arranged.Therefore, need a kind of centrifugal fan that does not cause the decline of air quantity and can reduce noise.
In addition, in described centrifugal fan, most running air quantity that require are single situation, therefore, design by the running air quantity with this requirement, have realized high efficiency or low noiseization.But, the air quantity of design and actual operating condition not simultaneously, the entrance shape of blade can not be followed inhalation flow.Therefore, produce from blade inlet edge 3a and to peel off whirlpool on a large scale, dwindle the area of blade inlet, and the phenomenon of peeling off of the suction surface side of blade 3 becomes big, produce big noise, further, the so-called worry that reduces air-supply efficient is arranged.
Summary of the invention
Therefore, in the present invention, in view of at described the problems of the prior art point, it is a kind of not only at fixing air quantity that its purpose is to provide, even in the air quantity of running arbitrarily that the user requires, also can satisfy low noise and high efficiency,, also can be suppressed at the phenomenon of peeling off of fan inside even therefore in the operating range of big air quantity, and the centrifugal fan of high efficiency, low noise, and provide the air fluid machinery of the blast apparatus that uses this centrifugal fan etc.That is, provide a kind of and in big operating range, be suppressed at the phenomenon of peeling off of fan inside, and can realize the technology of high efficiency and low noise.
For achieving the above object,, at first provide a kind of centrifugal fan, possess: possess according to the present invention: the guard shield of ring-type, it forms suction port; Mainboard, itself and this guard shield arranged opposite; And multi-disc blade, it is along circumferentially being configured between described guard shield and the described mainboard, described centrifugal fan will radially boost from the air of axial attraction and spray, it is characterized in that, described blade-shaped becomes, its leading edge shape has concavity portion in axial substantial middle position, and, have protrusion respectively at described mainboard and described shroud.
In addition, in the present invention, in the centrifugal fan of described record, further, the leading edge of the preferred described shroud of described blade is compared along sense of rotation forward with the leading edge of described mainboard side, further, described blade be preferably formed into, blade installation angle in the position that the mainboard with described blade joins has two flex points along with the increase of this radial location, and has a flex point in the blade installation angle of the position that joins with described guard shield.Further, described blade be preferably formed into, its trailing edge shape has convex body and concavity body along sense of rotation.
In addition, according to the present invention, in framework, form stream, and possess rotary drive mechanism, and described centrifugal fan is installed, provide the discharge of carrying out air, the blast apparatus of supply with this at this rotary drive mechanism in the part of this framework.
According to above-mentioned centrifugal fan of the present invention and the air fluid machinery that uses it of becoming, bring into play following excellent results, that is: by be suppressed at the phenomenon of peeling off of fan inside in big operating range, not only at fixing air quantity (design point), even in the air quantity of running arbitrarily that the user requires, also can satisfy low noise and high efficiency, therefore, even in the operating range of big air quantity, also can be suppressed at the phenomenon of peeling off of fan inside, and, high efficiency can be provided, the centrifugal fan of low noise, and the air flows machinery of the blast apparatus that uses this centrifugal fan etc. can be provided.
Description of drawings
Fig. 1 is the stereogram of unitary construction that expression possesses the centrifugal fan (embodiment one) of the blade that the present invention relates to.
Fig. 2 is described centrifugal fan (embodiment one's) plan view and a side view.
Fig. 3 is illustrated in the figure that the blade installation angle of the guard shield of described centrifugal fan (embodiment one) and mainboard surface of contact distributes.
Fig. 4 is the enlarged side view of the blade of described centrifugal fan (embodiment one).
Fig. 5 is the sectional drawing that possesses the fan filter unit of described centrifugal fan (embodiment one).
Fig. 6 is by having represented described centrifugal fan of the present invention (embodiment one's) air volume-static pressure characteristic, air quantity-efficiency characteristic, the figure of air quantity-noise properties with the comparison of existing centrifugal fan.
Fig. 7 is by having represented result's the figure of the lift efficiency of the described centrifugal fan of the present invention of numeric value analysis with the comparison of existing centrifugal fan.
Fig. 8 is by having represented that with the comparison of existing centrifugal fan the whirlpool that the leading edge shape of the described centrifugal fan that the present invention relates to is brought with it figure of scale takes place in the off-design point air quantity.
Fig. 9 is the side view of the described centrifugal fan that the present invention relates to of expression (embodiment two).
Figure 10 is by having represented described centrifugal fan (embodiment twos') air volume-static pressure characteristic, air quantity-efficiency characteristic, the figure of air quantity-noise properties with the comparison of existing centrifugal fan.
Figure 11 is the plan view of the existing centrifugal fan of expression.
Figure 12 is the side view of the existing centrifugal fan of expression.
[symbol description]
1 mainboard
2 guard shields
3 blades
The 3a leading edge
The 3b trailing edge
The face that the mainboard of 3c and blade joins
The face that the guard shield of 3d and blade joins
4 suction ports
5 leaf positions in suction port
6 connect the line of leaf position and central shaft
The line of 7 and 6 quadratures
The tangent line of 8 blade shapes
The flex point of 9 blade installation angles
9a internal side diameter flex point
9b outside diameter flex point
10 guard shield flex points
11 the whirlpools of peeling off in the leading edge generation
The 11a shroud is peeled off whirlpool
The 11b hub side is peeled off whirlpool
12 peripheries of peeling off whirlpool flow
13 fan filter units
14 body shell
15 filters
16 motors
17 centrifugal fans
18 motor bases
19 seal rings (mouth rin)
20 bases
Embodiment
Below, at length be illustrated the time for embodiments of the present invention with reference to accompanying drawing.
At first, for centrifugal fan that becomes embodiments of the invention one and fan filter unit, explain with accompanying drawing 1~accompanying drawing 5 as an example of the air fluid machinery that uses it.
Fig. 1 is the stereogram that expression possesses the centrifugal fan 17 of the blade that the present invention relates to, and Fig. 2 (a) represents its plan view, and Fig. 2 (b) represents its side view.And, Fig. 3 be expression constitute the centrifugal fan 17 that the present invention relates to blade 3 and surface of contact guard shield (with reference to the 3d of Fig. 4) and with the chart of the blade installation angle of the surface of contact (with reference to the 3c of Fig. 4) of mainboard.Further, Fig. 4 is the side view of blade 3 of the centrifugal fan 17 of Fig. 1, and accompanying drawing 5 expressions are as the sectional drawing of the embodiment's of the fluid machinery that possesses described centrifugal fan 11 fan filter unit 13.
At first, as Fig. 1 or Fig. 2 (a) and (b), the centrifugal fan 17 that the present invention relates to constitutes, possess: discoid mainboard 1 and guard shield 2, described guard shield 2 and this mainboard 1 opposite disposed, form circular and form therein that heart portion has suction port 4 by the raw material of flat board, and, in its circumferencial direction, leave constant interval multi-disc (being 5 in this example) blade 3 is set between above-mentioned mainboard 1 and guard shield 2.
In addition, described blade 3 for example uses the raw material of metal plate to form, and forms the pressure side of this blade with plane or mild male and fomale(M﹠F).And above-mentioned blade 3 is installed with the fixation arrangement (for example comprising ca(u)lk structure or combining by rivet) between the guard shield 2 by being separately positioned on described mainboard 1.
In addition, shown in Fig. 1 and Fig. 2 (a), the contacting part 5a of the guard shield 3 in the internal side diameter of the leading edge 3a of described blade 3 and suction port 4 be positioned at than with the contacting part 5b of mainboard 1 along the forward position of sense of rotation, that is, turn forward.
On the other hand, shown in Fig. 1 and Fig. 2 (b), in the trailing edge 3b of described blade 3, be positioned at than comparing along sense of rotation forward with the contacting part 5d of mainboard 1 with the contacting part 5c of described guard shield 3.In addition, the trailing edge 3b of described blade 3 becomes along sense of rotation shape forward in roughly 1/3 position of blade exit height " Z ".In addition, in this example, be 0.18 divided by the fan outlet width of fan outer circumference diameter " D " than Z/D with this blade exit height " Z ", promptly, as the form of centrifugal fan, for the device height of the fan filter unit that suppresses to carry this fan and adopt less value.
In addition, in Fig. 2 (a), if draw cross line 7 for the arbitrary position that connects blade 3 and the straight line 6 of central shaft, and this cross line 7 and tangent line 8 angulations at the outer surface of blade 3 are made as blade installation angle " β ", then as shown in Figure 3, the setting angle of the blade 3 on the mainboard internal diameter internal side diameter of the suction port on the mainboard 14 (that is) is set at bigger than the blade installation angle on the guard shield minimum diameter.And, the setting angle " β " of the attachment face 3c of the blade 3 that joins with mainboard 1 is shown in the full curve of Fig. 3, along with increasing towards external diameter (increase of radius R) and reaching and blade outlet angle (among the figure shown in the straight dashed line, for example 50 °) roughly the same angle, after this, this point as internal side diameter flex point 9a, is reduced to than till the little value of the blade angle of mainboard internal diameter, and reaches outside diameter flex point 9b.And if surpass this outside diameter flex point 9b, then the setting angle " β " of the attachment face 3c of the blade 3 that joins with mainboard 1 is once more along with increasing towards external diameter (increase of radius R).That is, the setting angle of the attachment face 3c of the blade 3 that joins with mainboard 1 distributes and is set at along with having two flex point 9a, 9b towards external diameter.
Next, the setting angle of the attachment face 3d of the blade 3 that joins with guard shield 2 is shown in the dash curve of Fig. 3, from the guard shield minimum diameter along with increasing towards external diameter, arrive guard shield flex point 10, after this, increase towards blade outlet angle (along with the increase of radius R) with the little ratio of increase than the setting angle of the attachment face 3c of the blade 3 that joins with mainboard 1.That is, the setting angle of the attachment face 3d of the blade 3 that joins with guard shield 2 distributes and is set at along with having a flex point 10 towards external diameter.
And, also as can be known clear and definite from Fig. 3, in the present embodiment, blade installation angle " β " arrives described guard shield flex point 10 and obtains in roughly the same diameter with the outside diameter flex point 9b that arrives described mainboard 1 side, more particularly, be set at respect to fan outer circumference diameter D and become the roughly position of 0.85D.And, at the outside diameter flex point 9b of mainboard 1 side,, reduce the load of mainboard side, and be implemented in sameization that flows of fan inside with this by with than set this blade installation angle " β " in the littler mode of the setting angle of guard shield flex point 10.
In addition, as shown in Figure 4, the leading edge shape 3a of described blade 3 has concavity in the substantial middle position of blade height H (H/2), and has convex from this concavity portion respectively to mainboard 1 side and guard shield 2 sides.That is, the leading edge shape 3a according to blade 3 forms following shape, that is: from mainboard 1 (promptly to guard shield 2, its short transverse), its radius (with reference to the label 6 of Fig. 2 (a)) temporarily diminishes, after this, become big in half position of blade height, then, its radius diminishes once more, and after this radius increases till the guard shield, in other words, the leading edge shape 3a of described blade 3 has the shape that is similar to Greece character " ε ".
In addition, as above-mentioned shown in Figure 4, the leading edge shape 3a of described blade 3 is set at: it is roughly the same with the decline angle to a side of this guard shield of the part that forms protuberance in guard shield 2 sides to come comfortable mainboard 1 side to form the angle of elevation of this mainboard 1 of part of protuberance, as an one example, in the present embodiment, be made as roughly 45 ° angle for the horizontal plane parallel with the face that forms suction port.
Structure according to the centrifugal fan 17 that describes in detail above, the air quantity point place that when design, sets, the leading edge shape 3a of described blade 3 the position of guard shield 2 sides with compare along sense of rotation forward in the position of mainboard 1 side, promptly turn forward, thereby can suitably tackle the velocity distribution of inhalation flow, make in mobile being difficult to of guard shield 2 sides with this and peel off.
Further, on above-mentioned basis, as mentioned above, by (promptly in the blade installation angle of described blade 3, at the attachment face 3c of described mainboard 1 side and guard shield 2 sides, the setting angle " β " at 3d place, with reference to Fig. 3) employing flex point (internal side diameter flex point 9a, outside diameter flex point 9b, guard shield flex point 10 etc.), can be increased in the preceding half side workload of described blade 3 and in later half workload, and also can make velocity variations identical and can be suppressed at the phenomenon of peeling off that blade interior produces in these blade 3 inside.
Further, the little air quantity point of in design, not considering of air quantity particularly, the concavity portion that the short transverse substantial middle position of leading edge 3a by being arranged on described blade 3 forms and be separately positioned on the protuberance of guard shield 2 sides and mainboard 1 side, can dwindle the scale of peeling off whirlpool on a large scale that in existing centrifugal fan, produces in its leading edge, it is transformed to the small-scale whirlpool of peeling off, and be separated in mainboard 1 side and guard shield 2 sides by this being peeled off whirlpool, can suppress by forming and covering the reduction that this whirlpool causes near the area after the blade inlet.
Promptly, above effect according to being obtained by above-mentioned structure can provide following centrifugal fan, and described centrifugal fan is the point of the air quantity in design not only, even especially in the strong wind weight range that contains low air quantity zone, also can realize high efficiency, low noiseization.
In addition, according to above structure, between mainboard 1, guard shield 2, multi-disc blade 3, form air flow path, and make centrifugal fan 17 runnings of this structure with the rotation of regulation, thereby extruded by its blade 3 from suction port 4 leaked-in airs, can access the predetermined process air quantity with this.
Next, accompanying drawing 5 expressions are as the fan filter unit of an example of the air fluid machinery that uses described centrifugal fan.In addition, this fan filter unit 13 is as lower device, by boost air and make it pass through filter 15 of centrifugal fan 17, removes the gas of organic class of airborne dust or boron, phosphorus etc. with this with this filter 15 that is:.
Also as can be known clear and definite as figure, the filter 15 that this fan filter unit 13 consists essentially of body shell 14 and purifies air, and, be provided with the motor base 18 of fixing motor 16 in this body shell 14, and install and rotation drives described centrifugal fan 17 at the running shaft of this motor.In addition, be separately installed with in body shell 14 and be used for inducing mobile seal ring 19 and being used for the base 20 that flows that the air of this centrifugal fan is come from rectification to centrifugal fan 17.
Promptly, according to this fan filter unit shown in Figure 5, by described centrifugal fan 17 atmosphere or the air 21 that comes from not the space of removing dust are wherein absorbed, after this, in the stream that the inwall by motor base 20 and body shell 14 constitutes, make and change equally from the mobile of air of this centrifugal fan 17 ejections, further, sidewalls in the collision body shell 14 and after the bending, purify by filter 15, and in the space that needs purify, blow out.
Next, with reference to the accompanying drawings 6, by with the comparison of for example described Figure 11 and existing centrifugal fan shown in Figure 12, following expression utilization becomes the test result that the fan filter unit of the centrifugal fan 17 of the above embodiments obtains.In addition, in this Fig. 6, air quantity is made as transverse axis, and the test result of fan static pressures (Fig. 6 (a)), fan static pressures efficient (Fig. 6 (b)), noise level (Fig. 6 (c)) is represented.
Shown in these Fig. 6 (a)~(c), to compare with existing product according to the centrifugal fan 17 that becomes above-mentioned present embodiment, the static pressure of the air quantity point when design is constant, but static pressure efficiency increases, and noise is roughly the same.On the other hand, in the zone that the air quantity point air quantity than design the time is littler, static pressure increases and static pressure efficiency rises as can be known.In addition, can reduce noise significantly in the zone that the air quantity point air quantity than design the time is littler as can be known.That is, from result shown in the figure (a)~(c) as can be known, according to present embodiment, the air quantity point when not only containing design also contains in the big flow region in low wind zone, can realize high efficiency, the low noiseization of centrifugal fan.
Further, for the described centrifugal fan 17 that becomes present embodiment, in order to investigate the effect at the improved efficiency of design point, Fig. 7 represents to compare by the lift of the blade of numeric value analysis.In addition, this Fig. 7 carries out the result of integration with this radius to the lift (L) of blade from the numeric value analysis result of simulation test state, can be known the workload of blade by this figure.That is, as shown in Figure 7 in the present embodiment, compare with existing product, the place workload little at radius increases.And as can be known, along with from the substantial middle portion of radius towards external diameter, be reduced to and existing product equal extent as the blade lift (L) of blade working amount, still at outside diameter, workload still increases.This is the situation that the blade installation angle of mainboard side causes, and therefore increases the workload of blade and raises the efficiency by changing the blade installation angle.
Next, in the described centrifugal fan 17 that becomes present embodiment, particularly to helping the structure at low air quantity area decreases noise, that is, the influence that the shape of the leading edge 3a of described blade 3 causes field of flow describes with accompanying drawing 8.Fig. 8 (a) is near the schematic representation with the track of whirlpool of flowing that is illustrated in the leading edge 3a of blade 3 of off-design point air quantity of present embodiment, and in order to compare, Fig. 8 (b) is illustrated in flowing and the track of whirlpool in the existing product.In addition, the schematic representation of these Fig. 8 (a) and Fig. 8 (b) is based on the schematic representation of the numeric value analysis result of simulation test state, dot the center of peeling off whirlpool 11a that produces from the leading edge 3a of blade 3, and, represent to flow 12 around it by the solid line that arrow is arranged.
According to these figure as can be known, in existing product (Fig. 8 (b)), guard shield 2 sides are peeled off whirlpool 11a and are produced from leading edge 3a, and 12 development significantly of flowing of periphery, near the suction surface side of blocking blade 3 suction port.On the other hand, in present embodiment (Fig. 8 (a)) as can be known, the leading edge shape 3a of described blade 3 becomes following shape: from mainboard 1 to guard shield 2, promptly on short transverse, its radius (with reference to the label 6 of Fig. 2 (a)) temporarily diminishes, after this become big in half position of blade height, then, its radius diminishes once more, after this radius increases till the guard shield,, utilizes the leading edge shape 3a with the blade 3 of " ε " similar shapes that is, the whirlpool 11 of peeling off that produces from the described leading edge 3a of blade 3 becomes two, and promptly shroud is peeled off whirlpool 11a and mainboard side is peeled off whirlpool 11b.And as can be known, flowing of the periphery of peeling off whirlpool that produces at the protuberance of the leading edge 3a of blade 3 12 compared with existing product and to be diminished, and in the obstruction area alleviation of the suction surface side of blade, can suppress the mobile of suction surface side with this.
By the above, according to present embodiment one, at the air quantity point of design, the leading edge 5a of the guard shield of the suction bore 4 of blade 3 compares with the leading edge 5b of mainboard and is positioned at along sense of rotation position forward, thereby can be corresponding with the velocity distribution of inhalation flow, thus, mobile being difficult to of shroud peels off.In addition, by using the flex point of blade installation angle, can be increased in the preceding half side workload of blade and later half workload thereof, and can change equally variation in the speed of this blade interior, with this, can be suppressed at the phenomenon of peeling off of blade interior generation.Further, particularly at the little off-design point of air quantity, the effect of the protuberance by guard shield 2 sides that form at the leading edge 3a of blade 3 and mainboard 1 side, the whirlpool of peeling off on a large scale that will produce in the leading edge of existing centrifugal fan is separated into mainboard side and shroud, and can become the small-scale whirlpool of peeling off separately.That is, dwindle the scale of peeling off whirlpool, and can be suppressed at the minimizing near the suction area after the inlet of blade 3 with this in the leading edge generation of centrifugal fan.
And,,,, also can realize high efficiency, the low noiseization of centrifugal fan even in low air quantity zone not only at design point according to above effect.And, when near fan outlet, having obstacle etc., because noise increases with the interference of the effluent that comes from blade, but vane trailing edge is along circumferentially moving, therefore produce skew with the interference of flowing of this obstacle along with the time and suppress the main frequency sound of blade, also can be with this to the improvement of noise tone color as contribution.And, particularly because as the running continuously in the period of several usually of the fan filter unit 13 of an example of the air fluid machinery that uses described centrifugal fan, therefore dust is attached to its filter 15, and therefore, the pressure loss in this filter increases year in year out.That is, therefore, in fan filter unit, consider to have situation about under the state of the air quantity lower, turning round than design point.But, according to the situation of using described centrifugal fan of the present invention, to compare with existing fan, the situation that noise increases or efficient reduces tails off, and keeps high efficiency in can be on a large scale, further, also can turn into power saving and contribution.
Next, describe for embodiment's dual-purpose accompanying drawing 9 following as another embodiment of the present invention.In addition, this Fig. 9 particularly represents to possess the side view of the centrifugal fan 17 of the blade that the present invention relates to.
Also as can be known clear and definite from figure, identical with Fig. 1 or Fig. 2, the centrifugal fan 17 that becomes present embodiment constitutes to be possessed: mainboard 1; And so-called guard shield 2, itself and this mainboard 1 opposite disposed, and form in its part by the raw material of flat board and to have suction portion 4, further, between described mainboard 1 and guard shield 2, separate constant interval at circumferencial direction multi-disc (being 5 pieces in this example) blade 3 is set.Moreover, also same as described above for this blade 3, the raw material that for example uses metal plate forms the pressure side of blade with plane or smooth male and fomale(M﹠F), and, fixation arrangement by being arranged on mainboard 1 and guard shield 2 (for example, ca(u)lk structure or the combination by rivet) is installed.
In addition, compare with the leading edge 5b of mainboard, the leading edge 5a of the guard shield of the suction bore 4 of described blade 3 is positioned at along sense of rotation position forward, and turns forward.Moreover shown in Figure 3 as described, the leading edge shape 3a of described blade has concavity in the substantial middle position of blade height H (H/2), and has convex at mainboard and shroud.That is, to guard shield, radius diminishes for the moment in short transverse from mainboard, and become big for the moment in half position of blade height, radius diminishes once more afterwards, and radius becomes the shape of increase before the guard shield, and the leading edge shape becomes " ε " similar shapes with Greece character.
In addition, in present embodiment two, as shown in Figure 9, the shroud of the trailing edge 3b of particularly described blade 3 spreads all over guard shield 2 sides from mainboard 1 side, with respect to sense of rotation protuberance and recess is set.That is, hold flex point at roughly 1/2 place of blade exit height Z, becoming at mainboard side is protruding along sense of rotation, and is recessed roughly serpentine shape in shroud.In order to ensure workload in mainboard 1 side, promptly identical with described Fig. 2, be protruding shape along sense of rotation.And, shown in Figure 8 as described, the growth of peeling off whirlpool that the concavity of guard shield 2 sides owing to suppress is further produced by the leading edge 3a of blade 3 in guard shield 2 sides, and reduce area between the blade of guard shield 2 sides thus.
Configuration aspects at described blade 3, as mentioned above, in the air quantity point of design, by comparing with leading edge 5b at mainboard side,, along sense of rotation (with reference to described Fig. 1 and Fig. 2 (a)) forward that is, turn forward at the leading edge 5a of the shroud of the blade 3 of the internal diameter of suction port 4, can be corresponding with the velocity distribution of inhalation flow, and mobile being difficult to of shroud peels off.Further, in the little off-design point of air quantity, the whirlpool of peeling off on a large scale that the leading edge at existing centrifugal fan can be produced is reduced into, the protrusion separately of the concavity body 3a that is formed by the substantial middle position in short transverse and the shroud of leading edge and mainboard side (promptly, " ε " shape) the small-scale scale of peeling off whirlpool of Gou Chenging, and be divided into mainboard side and shroud, can suppress to form and cover the minimizing of the blade area afterwards of whirlpool thus.In addition, the trailing edge shape 3b by blade 3 becomes convex and concavity (that is, the serpentine shape) guides this whirlpool along sense of rotation, and enters the track of the whirlpool behind the blade 3 by control, can be suppressed at the phenomenon of peeling off that the suction surface side of blade 3 produces.By above effect,, further,, also can realize high efficiency, the low noiseization of centrifugal fan even in low air quantity zone not only at design point.
According to above structure, between the blade 3 of mainboard 1, guard shield 2 and majority, form air flow path, then, make the centrifugal fan running of formation like this, can extrude by the blade of blade 3 and obtain handling air quantity from suction port 4 leaked-in airs by rotation with regulation.
10 (a)~(c) with reference to the accompanying drawings, by with the test result that relatively is illustrated in embodiment two of existing product.In addition, in these figure, air quantity is as transverse axis, and on the other hand, the longitudinal axis is represented fan static pressures (Figure 10 (a)), fan static pressures efficient (Figure 10 (b)), noise level (Figure 10 (c)) respectively.Also as can be known clear and definite from these test result, compare with existing product according to the centrifugal fan that becomes described embodiment two, static pressure efficiency increases in that the static pressure of design point is constant, and noise is identical.And as can be known, static pressure increases and the static pressure efficiency rising in the air quantity zone littler than design point air quantity.Further as can be known, in the air quantity zone littler, also can reduce noise in the same manner with design point than design point air quantity.
That is,,,,, also can realize high efficiency, the low noiseization of centrifugal fan even in low air quantity zone not only at design point according to present embodiment by result shown in described Figure 10 (a)~(c).And, obstacles etc. are during near fan outlet, noise increases owing to flow out the interference of flowing with blade, but because the trailing edge 3b of blade 3 is along circumferentially moving (promptly, the serpentine shape), therefore with the interference of flowing of obstacle in produce skew in time and can suppress the main frequency sound of blade, also can make contributions to the improvement of noise tone color.In addition, because fan filter unit running continuously in the period of several, so dust is attached to filter, and the pressure loss of filter increases year in year out.Therefore, compare, by considering the situation of the running under the state lower than design point air quantity with existing fan, and use centrifugal fan of the present invention, can abate the noise increases or the efficient reduction, and keeps high efficiency on a large scale, therefore, can turn into power saving and contribution.
Embodiment as the centrifugal fan that carries fan filter unit more than has been described, still, even be used under other the situation of equipment of air-conditioning equipment for example etc., also can be at efficient height on a large scale, and power saving turned into contribution.

Claims (5)

1. centrifugal fan possesses: the guard shield of ring-type, and it forms suction port; Mainboard, itself and this guard shield arranged opposite; And the multi-disc blade, it is along circumferentially being configured between described guard shield and the described mainboard, and described centrifugal fan will radially boost from the air of axial attraction and spray, it is characterized in that,
Described blade-shaped becomes, and its leading edge shape has concavity portion in axial substantial middle position, and, have protrusion respectively at described mainboard and described shroud.
2. centrifugal fan according to claim 1 is characterized in that,
In described blade, the leading edge of described shroud is more forward along sense of rotation than the leading edge of described mainboard side.
3. centrifugal fan according to claim 2 is characterized in that,
Described blade-shaped becomes, and the blade installation angle of the position that joins with mainboard of described blade has two flex points along with the increase of this radial location, and has a flex point in the blade installation angle of the position that joins with described guard shield.
4. according to each described centrifugal fan in the claim 1~3, it is characterized in that,
Described blade-shaped becomes, and its trailing edge shape has convex and concavity along sense of rotation.
5. an air fluid machinery is characterized in that,
In framework, form stream, and possess rotary drive mechanism, and each described centrifugal fan in the claim 1~4 is installed, thereby carry out discharge, the supply of air at this rotary drive mechanism in the part of this framework.
CN2009101634287A 2008-08-29 2009-08-19 Centrifugal fan and air fluid machinery using the same CN101660535B (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2008220905 2008-08-29
JP2008-220905 2008-08-29
JP2008220905A JP4612084B2 (en) 2008-08-29 2008-08-29 Centrifugal fan and air fluid machine using the same

Publications (2)

Publication Number Publication Date
CN101660535A true CN101660535A (en) 2010-03-03
CN101660535B CN101660535B (en) 2012-06-27

Family

ID=41788752

Family Applications (1)

Application Number Title Priority Date Filing Date
CN2009101634287A CN101660535B (en) 2008-08-29 2009-08-19 Centrifugal fan and air fluid machinery using the same

Country Status (3)

Country Link
JP (1) JP4612084B2 (en)
CN (1) CN101660535B (en)
TW (1) TWI394895B (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103452869A (en) * 2012-05-28 2013-12-18 台达电子工业股份有限公司 Centrifugal fan with axial flow wind direction
CN104564805A (en) * 2013-10-29 2015-04-29 海尔集团公司 Fan blade structure of centrifugal draught fan, centrifugal draught fan and embedded air conditioner inner unit
TWI484101B (en) * 2012-05-28 2015-05-11 Delta Electronics Inc A centrifugal fan with axial airflow
CN105134658A (en) * 2014-05-28 2015-12-09 Lg电子株式会社 Centrifugal fan
CN106609763A (en) * 2015-10-22 2017-05-03 松下知识产权经营株式会社 Centrifugal fan
CN109162961A (en) * 2014-05-14 2019-01-08 珠海格力电器股份有限公司 Centrifugation blade
CN109268309A (en) * 2017-07-18 2019-01-25 日本电产株式会社 Centrifugal fan wheel and centrifugal fan
CN110300855A (en) * 2017-02-20 2019-10-01 株式会社电装 Centrifugal blower

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5496002B2 (en) * 2010-07-27 2014-05-21 日本無機株式会社 Fan filter unit
WO2014061094A1 (en) * 2012-10-16 2014-04-24 三菱電機株式会社 Turbo fan and air conditioner
KR101645178B1 (en) 2013-05-10 2016-08-03 엘지전자 주식회사 Centrifugal fan and manufacturing method thereof
EP2829733B1 (en) 2013-05-10 2021-01-27 Lg Electronics Inc. Centrifugal fan
ITFI20130261A1 (en) * 2013-10-28 2015-04-29 Nuovo Pignone Srl "centrifugal compressor impeller with blades having an s-shaped trailing edge"
JP2017186914A (en) * 2016-04-01 2017-10-12 株式会社日立製作所 Radial impeller and centrifugal fluid machine including the same
CN106015090B (en) * 2016-06-27 2019-03-15 珠海格力电器股份有限公司 A kind of centrifugation blade, centrifugal blower and air-conditioning equipment
WO2018151013A1 (en) * 2017-02-20 2018-08-23 株式会社デンソー Centrifugal blower

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2730396B2 (en) * 1992-05-13 1998-03-25 ダイキン工業株式会社 Centrifugal fan impeller
BR0003706A (en) * 2000-05-30 2002-02-13 Tecsis Tecnologia E Sist S Ava Axle fan for low noise and high efficiency
JP3861008B2 (en) * 2002-01-10 2006-12-20 三菱重工業株式会社 Turbofan and air conditioner equipped with the same
JP4014887B2 (en) * 2002-02-08 2007-11-28 シャープ株式会社 Centrifugal fan and cooking device equipped with the centrifugal fan
JP4663259B2 (en) * 2004-06-18 2011-04-06 日立アプライアンス株式会社 Blower and vacuum cleaner
JP4689262B2 (en) * 2004-12-21 2011-05-25 東芝キヤリア株式会社 Axial fan, outdoor unit of air conditioner
JP2006291735A (en) * 2005-04-06 2006-10-26 Matsushita Electric Ind Co Ltd Blower impeller
JP2007170771A (en) * 2005-12-26 2007-07-05 Daikin Ind Ltd Turbofan and indoor unit of air conditioner using the same
CN200996391Y (en) * 2007-01-31 2007-12-26 广东美的电器股份有限公司 Axial-flow wind wheel

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103452869A (en) * 2012-05-28 2013-12-18 台达电子工业股份有限公司 Centrifugal fan with axial flow wind direction
TWI484101B (en) * 2012-05-28 2015-05-11 Delta Electronics Inc A centrifugal fan with axial airflow
CN103452869B (en) * 2012-05-28 2016-08-17 台达电子工业股份有限公司 The centrifugal fan of tool axial flow wind direction
US10458417B2 (en) 2012-05-28 2019-10-29 Delta Electronics, Inc. Centrifugal fan with axial-flow wind
CN104564805A (en) * 2013-10-29 2015-04-29 海尔集团公司 Fan blade structure of centrifugal draught fan, centrifugal draught fan and embedded air conditioner inner unit
CN104564805B (en) * 2013-10-29 2017-11-10 海尔集团公司 Machine in a kind of blade structure of centrifugal blower, centrifugal blower and embedded type air conditioner
CN109162961A (en) * 2014-05-14 2019-01-08 珠海格力电器股份有限公司 Centrifugation blade
CN105134658A (en) * 2014-05-28 2015-12-09 Lg电子株式会社 Centrifugal fan
CN106609763B (en) * 2015-10-22 2019-03-01 松下知识产权经营株式会社 Centrifugal fan
CN106609763A (en) * 2015-10-22 2017-05-03 松下知识产权经营株式会社 Centrifugal fan
CN110300855A (en) * 2017-02-20 2019-10-01 株式会社电装 Centrifugal blower
CN109268309A (en) * 2017-07-18 2019-01-25 日本电产株式会社 Centrifugal fan wheel and centrifugal fan

Also Published As

Publication number Publication date
TWI394895B (en) 2013-05-01
CN101660535B (en) 2012-06-27
JP4612084B2 (en) 2011-01-12
JP2010053803A (en) 2010-03-11
TW201014983A (en) 2010-04-16

Similar Documents

Publication Publication Date Title
JP6461172B2 (en) Air cleaner and its blower
CN104995375B (en) Sealing assembly between hot gas route and disc cavity in turbine engine
CA2140163C (en) Exhaust fan apparatus
US7018166B2 (en) Ducted wind turbine
CN1072318C (en) Air moving device
CN107023884A (en) Air regulator
CN104145118B (en) Propeller fan, fluid delivery system and molding die
CN103270315B (en) There is round entrance and the ventilator diffuser of non-rotationally-symmetric outlet
US9157452B2 (en) Radial fan wheel, fan unit and radial fan arrangement
EP2102504B1 (en) Apparatus for delivering a regulated supply of a gas, particularly respiratory assistance apparatus
CN1854531B (en) Centrifugal blower
US6955521B2 (en) Flow-forced generator with turbo-charging deflection hood
CA1219245A (en) Single-stage, multiple outlet centrifugal blower
WO2011132855A2 (en) Bladeless air blower for air circulation
US20020144599A1 (en) Two-stage water extractor
KR20100084646A (en) Side channel compressor
WO2011062062A1 (en) Multi-blade fan for centrifugal blower
JP2001271792A (en) Flow path for compressor with flute
CN104428539A (en) Centrifugal compressor
JP2003161167A (en) Bleed deflector
EP1290347A4 (en) In-line centrifugal fan
EP0206977B1 (en) Quiet bypass exhauster motor
CA2420109A1 (en) Static air mixing apparatus
CN202789707U (en) Centrifugal blower
US8915698B2 (en) Turbofan of air conditioning system

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant
CF01 Termination of patent right due to non-payment of annual fee
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20120627

Termination date: 20180819