CN101660535B - Centrifugal fan and air fluid machinery using the same - Google Patents
Centrifugal fan and air fluid machinery using the same Download PDFInfo
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- CN101660535B CN101660535B CN2009101634287A CN200910163428A CN101660535B CN 101660535 B CN101660535 B CN 101660535B CN 2009101634287 A CN2009101634287 A CN 2009101634287A CN 200910163428 A CN200910163428 A CN 200910163428A CN 101660535 B CN101660535 B CN 101660535B
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- blade
- centrifugal fan
- mainboard
- guard shield
- fan
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/20—Rotors
- F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05D2240/303—Characteristics 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
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- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
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 a concave-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 points with 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 and the low wind area.
Description
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.; More detailed, 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 with motor axis of rotation mutually; 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 said 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 said blade 3 from said guard shield 2 leaked-in airs, and produce and the rightabout adverse current phenomenon of sense of rotation at said 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, said blade 3 departs from sense of rotation side with respect to said blade 3 with the commissura portion of said mainboard 1 with the joining portion of said guard shield 2 and engages, and in addition, the front end of said blade 3 is to the sense of rotation tilt.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 said 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 said centrifugal fan, most running air quantity that require are single situation, therefore, design through 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 to suck and flowed.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, seeing that at said 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, even therefore in the operating range of big air quantity, also can be suppressed at fan inner peel off phenomenon; And the centrifugal fan of high efficiency, low noise, and the air fluid machinery of the blast apparatus that uses this centrifugal fan etc. is provided.That is, a kind of phenomenon of peeling off that in big operating range, is suppressed at fan inside is provided, and can realizes the technology of high efficiency and low noise.
For realizing above-mentioned purpose, according to the present invention, a kind of centrifugal fan is provided at first, possess: possess: 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 said guard shield and the said mainboard, and said centrifugal fan will radially boost from the air of axial attraction and spray, and it is characterized in that; Said blade-shaped becomes; Its leading edge shape has concavity portion in axial substantial middle position, and, have protrusion respectively at said mainboard and said shroud.
In addition, in the present invention, in the centrifugal fan of said record; Further; The leading edge of the preferred said shroud of said blade is compared along sense of rotation forward with the leading edge of said mainboard side, further, said blade be preferably formed into; Blade installation angle in the position that the mainboard with said 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 said guard shield.Further, said 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 said centrifugal fan is installed, the discharge of carrying out air, the blast apparatus of supply are provided 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: through 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, the centrifugal fan of high efficiency, low noise can be provided, and the air flow 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 said centrifugal fan (embodiment one's) plan view and a side view.
Fig. 3 is illustrated in the figure that the blade installation angle of guard shield and the mainboard surface of contact of said centrifugal fan (embodiment one) distributes.
Fig. 4 is the enlarged side view of the blade of said centrifugal fan (embodiment one).
Fig. 5 is the sectional drawing that possesses the fan filter unit of said centrifugal fan (embodiment one).
Fig. 6 is through having represented said 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 through having represented result's the figure of the lift efficiency of the said centrifugal fan of the present invention of numeric value analysis with the comparison of existing centrifugal fan.
Fig. 8 is through having represented that with the comparison of existing centrifugal fan the whirlpool that the leading edge shape of the said 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 said centrifugal fan that the present invention relates to of expression (embodiment two).
Figure 10 is through having represented said 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 peel off whirlpool periphery 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 explain the time for mode of execution 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, with accompanying drawing 1～accompanying drawing 5 explanation at length 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) representes its plan view, and Fig. 2 (b) representes 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 said centrifugal fan 11 fan filter unit 13.
At first; Like Fig. 1 or Fig. 2 (a) and (b), the centrifugal fan 17 that the present invention relates to constitutes, and possesses: discoid mainboard 1 and guard shield 2; Said 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, said 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 through rivet) between the guard shield 2 through being separately positioned on said mainboard 1.
In addition, shown in Fig. 1 and Fig. 2 (a), the contacting part 5a of the guard shield 2 in the internal side diameter of the leading edge 3a of said 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 said 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 said guard shield 2.In addition, the trailing edge 3b of said 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, and be made as blade installation angle " β " with this cross line 7 and at tangent line 8 angulations of the outer surface of blade 3 for the arbitrary position that connects blade 3 and the straight line 6 of central shaft, 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 the roughly the same angle of blade outlet angle (among the figure shown in the straight dashed line, for example 50 °); 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, the setting angle " β " of the attachment face 3c of the blade 3 that then 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; Can know clearly also that from Fig. 3 in the present embodiment, blade installation angle " β " arrives said guard shield flex point 10 and obtains in roughly the same diameter with the outside diameter flex point 9b that arrives said 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 inner sameization that flows of fan with this through with than set this blade installation angle " β " in the littler mode of the setting angle of guard shield flex point 10.
In addition, shown in accompanying drawing 4, the leading edge shape 3a of said 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 to guard shield 2 (promptly; Its short transverse), its radius (with reference to the label 6 of Fig. 2 (a)) temporarily diminishes, after this; Become big in the half the position of blade height, then, its radius diminishes once more; After this radius increases till the guard shield, and in other words, the leading edge shape 3a of said 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 said 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 of which example, in the present embodiment, for being made as roughly 45 ° angle with the parallel horizontal plane of face that forms suction port.
Structure according to the centrifugal fan 17 of top detailed description; The air quantity point place that when design, sets; The leading edge shape 3a of said 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, suck the velocity distribution that flows, make in mobile being difficult to of guard shield 2 sides with this and peel off thereby can suitably tackle.
Further; On above-mentioned basis; As stated; Blade installation angle (that is, at the attachment face 3c of said mainboard 1 side and guard shield 2 sides, the setting angle " β " at 3d place, with reference to Fig. 3) through at said blade 3 adopts flex point (internal side diameter flex point 9a, outside diameter flex point 9b, guard shield flex point 10 etc.); Can be increased in said blade 3 before half side workload and in later half workload, and also can make in the inner velocity variations of this blade 3 identical and can be suppressed at the phenomenon of peeling off that blade interior produces.
Further; The little air quantity point of particularly in design, not considering of air quantity; Concavity portion that the short transverse substantial middle position of leading edge 3a through being arranged on said blade 3 forms and the protuberance that is separately positioned on 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, can suppress by forming and covering the reduction that this whirlpool causes near blade inlet area afterwards through this being peeled off whirlpool.
Promptly; Above effect according to being obtained by above-mentioned structure can provide following centrifugal fan, and said 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 like lower device, by boost air and make it pass through filter 15 of centrifugal fan 17, removes organic type gas of airborne dust or boron, phosphorus etc. with this filter 15 with this that is:.
Also clearly can know like figure; This fan filter unit 13 consists essentially of body shell 14 and the filter 15 that purifies air; And, be provided with the motor base 18 of fixing motor 16 in this body shell 14, and install and rotation drives said 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.
That is,, atmosphere or the air 21 that comes from not the space of removing dust are wherein absorbed through said centrifugal fan 17 according to this fan filter unit shown in Figure 5; 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, according to accompanying drawing 6, through with the comparison of for example said Figure 11 and existing centrifugal fan shown in Figure 12, the test result that the fan filter unit that following expression utilization becomes 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 article according to the centrifugal fan that becomes above-mentioned present embodiment 17, 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, can know in that static pressure increases and the static pressure efficiency rising than the littler zone of the air quantity point air quantity in when design.In addition, can know in and can reduce noise significantly than the littler zone of the air quantity point air quantity in when design.That is, can know that 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 from result shown in the figure (a)～(c).
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 representes to compare through 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, can know in the present embodiment, compare that the place workload little at radius increases with existing article by Fig. 7.And can know, along with from the substantial middle portion of radius towards external diameter, be reduced to and existing article 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 through 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 said 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 article.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 through the solid line that arrow is arranged.
Can know that according to these figure in existing article (Fig. 8 (b)), guard shield 2 sides are peeled off whirlpool 11a and produced from leading edge 3a, and 12 development significantly of flowing of periphery, near the suction surface side of suction port, blocking blade 3.On the other hand, in present embodiment (Fig. 8 (a)), can know that the leading edge shape 3a of said 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, and after this becomes big in the half the position of blade height; Then, its radius diminishes once more, and after this radius increases till the guard shield; Promptly; Utilize the leading edge shape 3a with the blade 3 of " ε " shapes similar, the whirlpool 11 of peeling off that produces from the said 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 can know that 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 article and to be diminished, and, can suppress the mobile of suction surface side with this in the obstruction area alleviation of the suction surface side of blade.
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 that suction is flowed, thus, mobile being difficult to of shroud peels off.In addition; Through using the flex point of blade installation angle, can be increased in blade before half side workload 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 through 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, and therefore produces skew with the interference of flowing of this obstacle along with the time and suppresses the main frequency sound of blade, also can be to the improvement of noise tone color as contribution with this.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 said 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 the situation of running under the state of the air quantity lower than design point.But, according to the situation of using said 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 representes to possess the side view of the centrifugal fan 17 of the blade that the present invention relates to.
From figure, can know clearly that also 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 said 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 through being arranged on mainboard 1 and guard shield 2 (for example, ca(u)lk structure or the combination through 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 said blade 3 is positioned at along sense of rotation position forward, and turns forward.Moreover as said shown in Figure 3, the leading edge shape 3a of said 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 in short transverse for the moment from mainboard; And become big for the moment in the half the 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 " shapes similar with Greece character.
In addition, as shown in Figure 9 in present embodiment two, the shroud of the trailing edge 3b of particularly said 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 said Fig. 2, be protruding shape along sense of rotation.And, as said shown in Figure 8, 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.
In the structure aspects of said blade 3, as stated, in the air quantity point of design; Through comparing with leading edge 5b at mainboard side;, along sense of rotation (with reference to said 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 that suction is flowed, and mobile being difficult to of shroud peels off.Further; In the little off-design point of air quantity; Can the whirlpool of peeling off on a large scale that produce in the leading edge of existing centrifugal fan be reduced into the small-scale scale of peeling off whirlpool of protrusion separately (that is " ε " shape) formation of the concavity body 3a that forms by substantial middle position and the shroud of leading edge and mainboard side in short transverse; 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 through blade 3 becomes convex and concavity (that is, the serpentine shape) guides this whirlpool along sense of rotation, and gets into the track of the whirlpool behind the blade 3 through control, can be suppressed at the phenomenon of peeling off that the suction surface side of blade 3 produces.Through 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 through the blade of blade 3 and obtain handling air quantity from suction port 4 leaked-in airs through rotation with regulation.
According to accompanying drawing 10 (a)～(c), through with the test result that relatively is illustrated in embodiment two of existing article.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.Can know clearly also from these test result, compare with existing article that static pressure efficiency increases in that the static pressure of design point is constant, and noise is identical according to the centrifugal fan that becomes said embodiment two.And can know that static pressure increases and the static pressure efficiency rising in the air quantity zone littler than design point air quantity.Further can know, in the air quantity zone littler, also can reduce noise identically 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 said Figure 10 (a)～(c).And; Obstacles etc. are during near fan outlet; Because noise increases with the mobile interference of blade outflow, but because circumferential move (that is the serpentine shape) in the trailing edge 3b of blade 3 edge; 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, through 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 efficient be high 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 said guard shield and the said mainboard, and said centrifugal fan will radially boost from the air of axial attraction and spray, it is characterized in that,
Said blade-shaped becomes, and its leading edge shape has concavity portion in axial substantial middle position, and, have protrusion respectively at said mainboard and said shroud.
2. centrifugal fan according to claim 1 is characterized in that,
In said blade, the leading edge of said shroud is more forward along sense of rotation than the leading edge of said mainboard side.
3. centrifugal fan according to claim 2 is characterized in that,
Said blade-shaped becomes, and the blade installation angle of the position that joins with mainboard of said blade has two flex points along with the increase of the radius of said blade, and has a flex point in the blade installation angle of the position that joins with said guard shield.
4. according to each described centrifugal fan in the claim 1～3, it is characterized in that,
Said 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 the discharge or the supply of air at this rotary drive mechanism in the part of this framework.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008220905 | 2008-08-29 | ||
| JP2008220905A JP4612084B2 (en) | 2008-08-29 | 2008-08-29 | Centrifugal fan and air fluid machine using the same |
| JP2008-220905 | 2008-08-29 |
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| Publication Number | Publication Date |
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| CN101660535A CN101660535A (en) | 2010-03-03 |
| CN101660535B true CN101660535B (en) | 2012-06-27 |
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| CN2009101634287A Expired - Fee Related CN101660535B (en) | 2008-08-29 | 2009-08-19 | Centrifugal fan and air fluid machinery using the same |
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| Country | Link |
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| JP (1) | JP4612084B2 (en) |
| CN (1) | CN101660535B (en) |
| TW (1) | TWI394895B (en) |
Families Citing this family (24)
| 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 |
| 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 |
| TWI484101B (en) * | 2012-05-28 | 2015-05-11 | Delta Electronics Inc | A centrifugal fan with axial airflow |
| WO2014061094A1 (en) * | 2012-10-16 | 2014-04-24 | 三菱電機株式会社 | Turbo fan and air conditioner |
| EP2829733B1 (en) | 2013-05-10 | 2021-01-27 | Lg Electronics Inc. | Centrifugal fan |
| KR101645178B1 (en) | 2013-05-10 | 2016-08-03 | 엘지전자 주식회사 | Centrifugal fan and manufacturing method thereof |
| ITFI20130261A1 (en) * | 2013-10-28 | 2015-04-29 | Nuovo Pignone Srl | "CENTRIFUGAL COMPRESSOR IMPELLER WITH BLADES HAVING AN S-SHAPED TRAILING EDGE" |
| 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 |
| CN103967838B (en) * | 2014-05-14 | 2019-03-19 | 珠海格力电器股份有限公司 | Centrifugal fan blade |
| KR102227374B1 (en) * | 2014-05-28 | 2021-03-11 | 엘지전자 주식회사 | Centrifugal fan |
| JP2017078386A (en) * | 2015-10-22 | 2017-04-27 | パナソニックＩｐマネジメント株式会社 | Centrifugal fan |
| 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 | Centrifugal fan blade, centrifugal fan and air conditioning equipment |
| JP6747421B2 (en) * | 2017-02-20 | 2020-08-26 | 株式会社デンソー | Centrifugal blower |
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| CN113167289B (en) * | 2018-12-13 | 2023-03-24 | 三菱电机株式会社 | Centrifugal fan and air conditioner |
| WO2021144942A1 (en) * | 2020-01-17 | 2021-07-22 | 三菱電機株式会社 | Centrifugal blower and air conditioning device |
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| JP7003337B1 (en) * | 2020-11-25 | 2022-01-20 | 三菱電機株式会社 | Turbofan and air conditioner |
| WO2022139498A1 (en) * | 2020-12-25 | 2022-06-30 | 삼성전자주식회사 | Air conditioner including centrifugal fan |
| CN114857098B (en) * | 2022-05-25 | 2023-12-12 | 佛山市炬墺特暖通科技有限公司 | Roof axial fan |
| CN116464675B (en) * | 2023-06-20 | 2023-09-01 | 河北拓顺医疗科技有限公司 | Shock-absorbing noise reduction device for ventilator built-in fan |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1153909C (en) * | 2000-05-30 | 2004-06-16 | 泰克西斯先进技术及体系有限公司 | Blade for axial flow fan |
| JP2006002689A (en) * | 2004-06-18 | 2006-01-05 | Hitachi Home & Life Solutions Inc | Fan |
| CN1793670A (en) * | 2004-12-21 | 2006-06-28 | 东芝开利株式会社 | Tube-axial fan, outdoor unit of air conditioner |
| CN1847669A (en) * | 2005-04-06 | 2006-10-18 | 松下电器产业株式会社 | Air feeder vane wheel |
| 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 |
| JP2007170771A (en) * | 2005-12-26 | 2007-07-05 | Daikin Ind Ltd | Turbofan and indoor unit of air conditioner using 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 |
| CN200996391Y (en) * | 2007-01-31 | 2007-12-26 | 广东美的电器股份有限公司 | Axial-flow wind wheel |
Family Cites Families (1)
| 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 |
-
2008
- 2008-08-29 JP JP2008220905A patent/JP4612084B2/en active Active
-
2009
- 2009-06-24 TW TW098121193A patent/TWI394895B/en active
- 2009-08-19 CN CN2009101634287A patent/CN101660535B/en not_active Expired - Fee Related
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1153909C (en) * | 2000-05-30 | 2004-06-16 | 泰克西斯先进技术及体系有限公司 | Blade for axial flow fan |
| 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 |
| JP2006002689A (en) * | 2004-06-18 | 2006-01-05 | Hitachi Home & Life Solutions Inc | Fan |
| CN1793670A (en) * | 2004-12-21 | 2006-06-28 | 东芝开利株式会社 | Tube-axial fan, outdoor unit of air conditioner |
| CN100422567C (en) * | 2004-12-21 | 2008-10-01 | 东芝开利株式会社 | Tube-axial fan, outdoor unit of air conditioner |
| CN1847669A (en) * | 2005-04-06 | 2006-10-18 | 松下电器产业株式会社 | Air feeder vane wheel |
| 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 |
Also Published As
| Publication number | Publication date |
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| JP2010053803A (en) | 2010-03-11 |
| TWI394895B (en) | 2013-05-01 |
| JP4612084B2 (en) | 2011-01-12 |
| CN101660535A (en) | 2010-03-03 |
| TW201014983A (en) | 2010-04-16 |
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