CN1297751C - Impeller for fun, fun therewith and air conditioner with the fun - Google Patents
Impeller for fun, fun therewith and air conditioner with the fun Download PDFInfo
- Publication number
- CN1297751C CN1297751C CNB001288504A CN00128850A CN1297751C CN 1297751 C CN1297751 C CN 1297751C CN B001288504 A CNB001288504 A CN B001288504A CN 00128850 A CN00128850 A CN 00128850A CN 1297751 C CN1297751 C CN 1297751C
- Authority
- CN
- China
- Prior art keywords
- blade
- impeller
- radius
- wheel hub
- representative
- Prior art date
- Legal status (The legal status 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 status listed.)
- Expired - Fee Related
Links
Images
Classifications
-
- 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
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
It is intended to lessen the effect of the blade end vortex of air generated on the negative pressure surface near the outer circumference of a rotating blade given to the influent air state on other blade rotating behind when it is separated from this blade and flows away. As a result, disturbance of influent air on each succeeding blade is reduced. The influent air coming into each blade is smooth. Unstable phenomena in the succeeding rotating blade such as air separation and decline of speed hardly take place. Accordingly, the blade noise is lowered and the static pressure is enhanced. An impeller has a hub and two blades disposed in the hub. Each blade has a shape with an aspect ratio (b/L) defined in a range of b/L<=1.
Description
(1) technical field
The air conditioner that the present invention relates to blower-use impeller and use the gas fan of this impeller and use this gas fan.
(2) background technique
The plan view of the impeller of inclined flow blower in the past as shown in figure 15, the rotary track figure of this impeller is as shown in figure 15.In using the impeller of this inclined flow blower, gas in impeller with respect to the turning axle oblique flow.That is, in Figure 15, the impeller 18 of inclined flow blower comprises the wheel hub 20 that is roughly the circular cone trapezoid shaped and is arranged on a plurality of blades 19 on this wheel hub 20.The rotary track figure of this impeller 18 as shown in figure 14.Gas fan comprises this impeller 18, and the housing of ccontaining this impeller 18 is with the turning axle that wheel hub 20 combines, motor.Make impeller 18 rotate the air-supply effect that produces by motor.As the aspect ratio " b/L " of the ratio of the representative physical length b of the chord length L of the blade of the representative mean square radius of gyration position of this blade 19 and blade radius direction less than 1 occasion, promptly in the scope of " b/L≤1 ", for obtaining sufficient static pressure, the quantity of blade 19 is at least more than 3 pieces.And the leading edge 21 of blade 19 has curve shapes such as logarithm spiral.
Yet, in above-mentioned structure in the past, aspect ratio " b/L " is less than 1 occasion (i.e. the scope of " b/L≤1 "), in the structure with the impeller that is at least 3 pieces of blades 19, produces as shown in the figure blade end eddy current 19D along the direction of arrow near the periphery of rotating blade 19.This blade end eddy current 19D and its blade 19 are peeled off, and the inflow air state of incoming rear blade 19 is produced very big influence.That is, rear blade 19 is subjected to the very big influence of blade end eddy current 19D of peeling off from the generation of the place ahead blade, and rear blade 19 is accepted disorderly greatly inflow air and carried out aerodynamic force work.Therefore, because the influence of this blade end eddy current 19D, the raising of low noiseization and static pressure characteristic is limited.
And the quantity of blade 19 is many more, and then the shared volume of impeller is big more, so the manufacture cost of impeller is inevitable very high.
(3) summary of the invention
The low noiseization that the objective of the invention is to blower-use impeller, the manufacture cost of raising static pressure and reduction impeller.
The invention provides a kind of blower-use impeller, it comprises wheel hub and is arranged at 2 pieces of blades on this wheel hub, each blade of described 2 pieces of blades is that the center is symmetrically set with described wheel hub, when the chord length of the blade of the representative mean square radius of gyration " Rr " position of each blade of described 2 pieces of blades is that the representative physical length of " L " and radial direction is during for " b ", the aspect ratio of each blade " b/L " has the shape of " b/L≤1 " scope, it is characterized in that, in the radial direction cross section of described each blade, from having with respect to the wind upside to the part of the most advanced and sophisticated side position of periphery near the position of the representative mean square radius of gyration of described blade is curve shape streamlined of spill, from having with respect to the wind upside to the part of the position of hub side near the position of the representative mean square radius of gyration of described blade is the curve shape of convex, because the rotation of described each blade, described each blade makes air flow into from the leading edge of described each blade, and flow out from trailing edge, the blade end eddy current that produces on the suction surface of described each blade is peeled off diffluence from described blade, interval between each blade is fully wide, to avoid being subjected to the influence of described blade end eddy current.
The present invention also provides a kind of gas fan, comprise motor and the impeller that is connected with described motor, described impeller comprises wheel hub and is arranged at 2 pieces of blades on this wheel hub, it is that the center is symmetrical that each blade of described 2 pieces of blades is arranged to described wheel hub, when the chord length of the blade of the representative mean square radius of gyration " Rr " position of each blade of described 2 pieces of blades is " L ", when the representative physical length of radial direction is " b ", the aspect ratio of described each blade " b/L " has the shape of " b/L≤1 " scope, in the radial direction cross section of described each blade, from having with respect to the wind upside to the part of the most advanced and sophisticated side position of periphery near the position of the representative mean square radius of gyration of described blade is curve shape streamlined of spill (2a), is the curve shape of convex from having with respect to the wind upside to the part of the position of hub side near the position of the representative mean square radius of gyration of described blade.
The present invention also provides a kind of air conditioner, comprise indoor set, outdoor unit, be arranged on the pipe arrangement between above-mentioned indoor set and the outdoor unit, described outdoor unit has heat exchanger and gas fan, above-mentioned gas fan has motor and the impeller that is connected with this motor, described impeller comprises wheel hub and is arranged at 2 pieces of blades on the described wheel hub, each blade of described 2 pieces of blades is that the center is arranged to symmetrically with described wheel hub, the chord length of the blade of the representative mean square radius of gyration " Rr " position of each blade of described 2 pieces of blades is that the representative physical length of " L " and radial direction is during for " b ", the aspect ratio of described each blade " b/L " has the shape of " b/L≤1 " scope, it is characterized in that, in the radial direction cross section of described each blade, from having with respect to the wind upside to the part of the most advanced and sophisticated side position of periphery near the position of the representative mean square radius of gyration of described blade is curve shape streamlined of spill, is the curve shape of convex from having with respect to the wind upside to the part of the position of hub side near the position of the representative mean square radius of gyration of described blade.
Being preferably above-mentioned 2 pieces of blades is arranged to symmetrical with respect to the center of above-mentioned wheel hub.
Gas fan of the present invention comprises motor and the impeller that is connected with this motor, is characterized in that above-mentioned impeller has the structure identical with aforementioned impeller.
Air conditioner of the present invention comprises indoor set, outdoor unit, is arranged on the pipe arrangement between above-mentioned indoor set and the outdoor unit, above-mentioned outdoor unit has heat exchanger and gas fan, above-mentioned gas fan has motor and the impeller that is connected with this motor, is characterized in that above-mentioned impeller has the structure identical with aforementioned impeller.
Adopt said structure, owing to the interval between 2 pieces of blades is fully roomy, blade end eddy current and this blade of the air that produces near the suction surface the rotary vane periphery are peeled off and diffluence, and alleviate the influence to the inflow air state of other blades at the rear that then turns over.And the disorder that each blade flows into air reduces.The inflow air that enters each blade is level and smooth.Air during revolution on the blade of rear is peeled off with wild effect such as stall and is difficult to produce.Therefore can reduce the noise in the blade, improve static pressure.
In addition, the impeller with 2 pieces of blades with have 3 pieces with the impeller of upper blade mutually specific energy reduce the shared volume of impeller, thereby reduce the manufacture cost of impeller.
(4) description of drawings
Fig. 1 is the rotary track figure of the impeller of the inclined flow blower of the blower-use impeller of expression use one embodiment of the invention.
Fig. 2 is the plan view of the blower-use impeller of expression one embodiment of the invention.
On behalf of mean square radius of gyration position, Fig. 3 dissect and launch, be suitable for the mounted blade figure of thick blade the blower-use impeller of one embodiment of the invention for expression.
On behalf of mean square radius of gyration position, Fig. 4 dissect and launch, be suitable for the mounted blade figure with certain thickness slim vane the air feeder vane wheel of one embodiment of the invention for expression.
Fig. 5 is the ideograph of expression with the running-active status of the air feeder vane wheel of one embodiment of the invention.
Fig. 6 is the performance plot of the relation of 41dB place air quantity for expression with the aspect ratio " b/L " of the air feeder vane wheel of one embodiment of the invention and the noise of blowing.
Fig. 7 is the performance plot after having the impeller of 2 pieces of blades in the air feeder vane wheel to one embodiment of the invention and the experimental value of the static pressure characteristic of the impeller with 3 pieces of blades of blower-use impeller comparing in the past.
Fig. 8 is illustrated in the rotary track figure of impeller that air feeder vane wheel with one embodiment of the invention is used for the embodiment 1 of axial fan.
Fig. 9 is illustrated in the plan view that the air feeder vane wheel of one embodiment of the invention is used for the impeller of axial fan.
Figure 10 is illustrated in the sectional drawing of radial direction of impeller that air feeder vane wheel with one embodiment of the invention is used for the embodiment 2 of inclined flow blower.
Figure 11 is the figure of the experimental result of the noise spectrum of expression embodiment's 2 air feeder vane wheel.
Figure 12 is illustrated in the plan view of motion of blade end eddy current of impeller that air feeder vane wheel with one embodiment of the invention is used for the embodiment 3 of inclined flow blower.
Figure 13 is the skeleton diagram of the air conditioner of the gas fan that uses the impeller with one embodiment of the invention.
Figure 14 represents the plan view of blower-use impeller in the past.
Figure 15 represents the rotary track figure of blower-use impeller in the past.
(5) embodiment
The blower-use impeller of one embodiment of the invention comprises wheel hub and is arranged at 2 pieces of blades on this wheel hub, when the chord length of the blade of the representative mean square radius of gyration position of each blade of above-mentioned 2 pieces of blades is that the representative physical length of radial direction of " L " and above-mentioned each blade is during for " b ", aspect ratio is expressed as ratio " b/L ", be characterized in that above-mentioned each blade has the shape of " b/L≤1 " scope; Being preferably above-mentioned 2 pieces of blades is arranged to symmetrical with respect to the center of above-mentioned wheel hub.
Adopt said structure, owing to the interval between 2 pieces of blades is fully roomy, blade end eddy current and this blade of the air that produces near the suction surface the rotating blade periphery are peeled off and diffluence, and the influence of the inflow air state of the blade at the rear of coming then turning round reduces.Like this, 2 pieces of blades are not subjected to the influence of blade end eddy current mutually.Therefore, the disorder of the inflow air that each blade is accepted reduces, and the inflow air that enters each blade is level and smooth.So being difficult to produce air in each blade peels off and wild effect such as stall.
In addition, specific volume is littler mutually with the impeller with 3 pieces or 4 pieces blades for above-mentioned impeller with 2 pieces of blades.
Be preferably, in the radial direction section of above-mentioned each blade, from having the curve shape of concavity with respect to the wind upside to the part of outer circumferential side position near the representative mean square radius of gyration position of blade, near the curve shape that has convex with respect to the wind upside to the part of hub side position the representative mean square radius of gyration position of blade.
Adopt said structure, because blade has the curve shape of concavity, blade itself is streamlined with respect to the gyratory directions of blade.Therefore, even be 2 pieces occasion, also be lower than the sound pressure level of turbulence noise as " nZ " sound of blade revolution noise at blade quantity.Consequently prevent unusual sound as whole impeller.And actual sense of hearing is good.
Be preferably, 1 leading edge at blade of the auxiliary blade of triangle overlaps with the intersection point place of periphery, and is close to and forms 1 limit of the auxiliary blade of triangle with above-mentioned leading edge.Thereby with the blade setting of the auxiliary blade of triangle as primary blades.
Adopt said structure, as starting point, the blade end eddy current is coniform generation at the suction surface of blade, and this blade end eddy current is peeled off diffluence at the blade middle part with the front end of the blade of triangle.The blade of this triangle has the effect that its front end place generates the blade end eddy current that is defined in.Therefore, the blade of triangle has stipulated that state that near this blade end eddy current suction surface place the periphery of blade takes place and blade end eddy current and blade peel off the state of diffluence.So it is minimal effect that the blade of triangle has the influence that makes the blade end eddy current of the rear blade that turns over.Therefore, even in the fully wide impeller in the interval between blade, also the inflow air state of the rear blade that then turns over can be made and have still less disorderly level and smooth appropriate state with 2 pieces of blades.And the rear blade more is difficult to be subjected to the influence of blade end eddy current, and the inflow air that each blade enters is the most level and smooth, more is difficult to produce air on the blade of rear and peels off and wild effects such as stall.
Be preferably, the blower setting that will have above-mentioned impeller is in the outdoor unit of the air conditioner with heat exchanger.
Adopt said structure, the outdoor unit noise in operating is less, and can reduce manufacture cost, and design becomes easy.
Following with reference to accompanying drawing 1 to 13 explanation exemplary embodiments of the present invention.
Exemplary embodiments 1:
Fig. 1 to Fig. 9 represents the blower-use impeller of exemplary embodiments of the present invention.Wherein, Fig. 1 is the rotary track figure that is used for the impeller of inclined flow blower.Fig. 2 is the plan view of the impeller of inclined flow blower.Fig. 3 for expression with the blower-use impeller of one embodiment of the invention in the unfolded drawing of representing after mean square radius of gyration position is dissectd.Among Fig. 3, blade has thick blade.On behalf of mean square radius of gyration position, Fig. 4 for dissect the figure that launch the back air feeder vane wheel, and being suitable for as blade is the occasion with certain thickness slim vane.Fig. 5 is used for the ideograph of running-active status of the impeller of gas fan for expression.Fig. 6 is the performance plot of characteristic test of the performance of expression air feeder vane wheel, and transverse axis is represented aspect ratio " b/L ", and the longitudinal axis noise of representing to blow is the air quantity at 41db place.The performance plot that Fig. 7 compares for the static pressure characteristic to blower-use impeller with 2 pieces of blades of this exemplary embodiments and the blower-use impeller with 3 pieces of blades in the past.Fig. 8 is the rotary track figure that is used for the blower-use impeller of axial fan.Fig. 9 is the plan view of the impeller of axial fan.
Among Fig. 1, the impeller 1 that is used for inclined flow blower comprises the roughly wheel hub 3 and 2 pieces of blades 2 that are arranged at the outer circumferential face of this wheel hub 3 of circular cone trapezoid shaped.2 pieces of blades 2 have same shape mutually, and each blade 2 is arranged at relative each other position.That is, each blade 2 is arranged at wheel hub 3 and is the center and the position of symmetry each other.Above-mentioned each blade 2 is the representative physical length of radial direction of " L " and above-mentioned each blade during for " b " in the chord length of the blade of the representative mean square radius of gyration position of blade, its ratio " b/L " expression aspect ratio.This aspect ratio is for being equal to or less than 1.That is, this aspect ratio is set in " b/L≤1 " scope.And 2 pieces of blades 2 with aspect ratio of setting are set in this scope.
Below further specify said structure.
Above-mentioned wheel hub 3 is for having the trapezoidal of circular cross-section.When the least radius of the above-mentioned circle of above-mentioned wheel hub 3 is the maximum radius of " r1 " and above-mentioned wheel hub during for " r2 ", as represent hub radius be " r ", then is defined as r=(r1+r2)/2.
Distance from the center of above-mentioned wheel hub to the maximum front end of above-mentioned blade be " R2 ", and extremely the distance of the minimum front end of above-mentioned blade is " R1 " from the center of above-mentioned wheel hub, and the representative hub radius of impeller is " R " as described, then is defined as R=(R1+R2)/2.
When representing the mean square radius of gyration, then be defined as Rr=((R for " Rr "
2+ r
2)/2)
1/2Above-mentioned " L " is the chord length of the above-mentioned blade of the above-mentioned representative mean square radius of gyration " Rr " position.
Among Fig. 1 be center line 31C-31C with impeller 1 as center line, be " P1 " by representing the mean square radius of gyration for the summit of the circular cone of " Rr ".Fig. 3 and Fig. 4 illustrate the unfolded drawing of blade 2 being dissectd along the line 32A-32A of this circular cone.The chord length of this blade 2 is " L ".This line 32A-32A line is expressed as curve 32A-32A in the Fig. 2 as plan view.In Fig. 1, the representative physical length " b " of the radial direction of blade 2 is represented the position of hub radius " r " and the physical length of the spanwise of the blade 2 of the position of representing radius " R " for connection.
As shown in Figure 5, the axle of motor 12 is fixed in the wheel hub 3, and they is placed in the suitable housing 11.Make impeller 1 rotate the air-supply effect that produces as shown by arrows by motor 12.At this moment, the air among Fig. 1 almost all flows into the leading edge 4 of blade 2 and flows out from trailing edge 5.Therefore, impeller 1 carries out aerodynamic force work.
In Fig. 1, inclined flow blower is represented aspect ratio with the chord length " L " of the representative mean square radius of gyration position of impeller 1 with the ratio " b/L " of the representative physical length " b " of the radial direction of blade.
Fig. 6 has the impeller of 2 pieces of blades for expression aspect ratio " b/L " is the performance plot of the relation of 41dB place air quantity with the air-supply noise.Fig. 6 makes according to the laboratory data with impeller 1 of 415 millimeters of diameters (φ).
As shown in Figure 6, when aspect ratio during in " b/L≤1 " scope, the wind sound is that the air quantity at 41dB place is saturated.Yet when aspect ratio during in " b/L 〉=1 " scope, air quantity promptly sharply reduces.
The inclined flow blower of this exemplary embodiments has 2 pieces of blades 2 that are arranged on the wheel hub 3 with impeller 1.The chord length " L " of the blade 2 of the representative mean square radius of gyration position of blade 2 is set at the scope of aspect ratio " b/L " in " b/L≤1 " with the representative physical length " b " of the radial direction of blade 2, and this impeller 1 has 2 pieces of blades with above-mentioned aspect ratio.The chord length of blade outer circumferential side is longer than the chord length of hub side.
Adopt said structure, have at blade in the impeller of aspect ratio of " b/L≤1 " scope, because the interval between each blade 2 is fully wide, near each blade 2 periphery near the suction surface 8 of (being the blade tip 6) the blade end eddy current 33D of generation peel off diffluence from blade 2, considerably less for the influence of the inflow air state of the rear blade 2 that then turns over.Therefore, each blade 2 is not subjected to the influence of blade end eddy current 33D mutually.So the disorder of the inflow air that each blade 2 enters is few, each blade 2 is accepted level and smooth inflow air.Therefore, be difficult on the blade 2 produce and peel off or wild effect such as stall.Thereby improve the air quantity of impeller 1 when identical noise.Be used to confirm the data of this point shown in Fig. 6.Fig. 6 is the performance plot of the impeller 1 of the above-mentioned inclined flow blower of expression.
In addition,, be difficult on the rear blade 2 produce and peel off or wild effect such as stall, thereby improve the static pressure characteristic of impeller 1 because the blade end eddy current 33D of the place ahead blade that rotates is very little for the influence of rear blade 2.Fig. 7 represents characteristic curve that the impeller that has 2 pieces of blades in the inclined flow blower impeller and the static pressure characteristic with impeller of 3 pieces of blades are compared.The inclined flow blower of representing 415 millimeters of diameter phi among Fig. 7 is the static pressure characteristic of 29.5 cubic metres/timesharing with impeller with 712 rev/mins of runnings of rotating speed, open air quantity point.Open air quantity point is that static pressure is 0 o'clock a air quantity.Putting to the scope of air quantity point " Q1 " from open air quantity, the impeller with 2 pieces of blades is compared the strong slightly static pressure of demonstration with the impeller with 3 pieces of blades.In the scope from air quantity point " Q1 " to air quantity point " Q2 ", the impeller with 2 pieces of blades has same static pressure mutually with the impeller with 3 pieces of blades.From air quantity point " Q2 " to the scope of closing air quantity point (air quantity is 0 point), the impeller with 3 pieces of blades is compared the stronger static pressure of demonstration with the impeller with 2 pieces of blades.The gas fan that is used for air conditioner when heating usually from using near open air quantity point to the scope the air quantity point " Q2 ".Only when carrying out the warming operation of remarkable frosting on heat exchanger, just moving from air quantity point " Q2 " to the scope of closing air quantity point (air quantity is 0), the defrosting running is frequently generation.Therefore, not quite significant on Machinery Design near the performance to the scope of closing air quantity point the air quantity point " Q2 " of the gas fan that is used for air conditioner.Therefore, from air quantity point " Q2 " to the scope of closing air quantity point (air quantity is 0 point), the impeller with 3 pieces of blades is compared the strong slightly static pressure of demonstration with the impeller with 2 pieces of blades performance is out of question at the gas fan that is used for air conditioner.
Also have, the impeller that the shared volume ratio of impeller with 2 pieces of blades has 3 pieces or 4 pieces blades is little.Therefore, the manufacture cost of impeller is inevitable lower.
In addition, in Fig. 1, be center line 31C-31C with impeller as center line, the summit of the 32A-32A line of the circular cone by the mean square radius of gyration " Rr " is " P1 ", Fig. 3 and Fig. 4 illustrate the unfolded drawing of blade being dissectd along the line 32A-32A of this circular cone.Fig. 3 illustrates the blade with thick blade 7.In Fig. 3, the leading edge 4 of the blade 7 in the sectional shape of blade 7 has circular-arc, and trailing edge 5 has the shape that comes to a point.Blade 7 has pressure side 9 and suction surface 8.In Fig. 3, above-mentioned each blade all has the trailing edge 5 of circular-arc leading edge 4 and the shape that comes to a point, and has the shape from above-mentioned trailing edge to above-mentioned leading edge progressive additive.
Fig. 4 illustrates the blade with slim vane 10.In Fig. 4, blade 10 is for having the shape in certain thickness thin cross section.Promptly has roughly the same thickness from above-mentioned trailing edge to being shaped as of above-mentioned leading edge.Blade 10 has pressure side 9a and suction surface 8a.Pressure side 9a is positioned at the wind upside, and suction surface 8a is positioned at the wind upside.
Following blower-use impeller explanation axial fan as other exemplary embodiments of the present invention.Fig. 8 illustrates the rotary track figure of impeller in the axial fan, and Fig. 9 illustrates its plan view.In Fig. 8 and Fig. 9, impeller 15 has 2 pieces of blades 14.Here, represent the position of the mean square radius of gyration " Rr " to represent with the 34B-34B line.Even in the impeller 15 of this axial fan, as the blade 14 of the representative mean square radius of gyration position of blade 14 chord length " L " and the aspect ratio " b/L " of the ratio of the representative physical length " b " of the radial direction of blade 14 also be set at the scope of " b/L≤1 ".And 2 pieces of blades that will have the aspect ratio that is set at above-mentioned scope are arranged on the wheel hub 13.
The impeller of the axial fan of said structure has effect and the effect same with above-mentioned inclined flow blower impeller.
Exemplary embodiments 2:
Figure 10 is the sectional drawing of the radial direction of the inclined flow blower impeller of exemplary embodiments 2 of the present invention.Though Figure 10 illustrates along the sectional drawing of the radial direction of 35B-35B line among Fig. 2, the blade of the impeller of the blade of the impeller of this exemplary embodiments 2 and exemplary embodiments 1 is also inequality.Figure 11 represents the noise spectrum of the inclined flow blower impeller of this exemplary embodiments 2.
The impeller of exemplary embodiments 2 of the present invention compares with the impeller of exemplary embodiments 1 that only blade shape is different, and other structures are then identical.So allly identically with exemplary embodiments 1 structure all adopt same numeral, specify and be omitted, and be that the center is illustrated with the different piece with the part with same function effect.
From having with respect to the wind upside to the shape of the position of the blade tip 6 sides near the line 36A-36A of the representative mean square radius of gyration " Rr " by blade 2 is the curve shape of spill 2a, and having with respect to the wind upside from the shape by near the position to wheel hub 3 sides of the line 36A-36A that represents the mean square radius of gyration " Rr " is the curve shape of convex 2b.And 2 pieces of blades 2 that will have this shape are arranged on the wheel hub 3.These 2 pieces of blades 2 are that the center with respect to wheel hub 3 is symmetrical arranged.Each blade 2 has suction surface 8b and pressure side 9b.Impeller 16 has the blade 2 of 2 pieces of this shapes.This impeller 16 is used for inclined flow blower.
Adopt said structure, owing to be to be the curve shape of spill near the shape to the position of the outer circumferential side line 36A-36A of the representative mean square radius of gyration " Rr " by blade 2 with respect to the wind upside, so blade 2 gyratory directions with respect to impeller 16 own are streamlined.Therefore, even blade quantity is 2 pieces of blades, also the sound pressure level than turbulence noise is low as " nZ " sound of the revolution noise of blade 2.So can prevent the generation as the unusual sound of whole impeller 16, actual sense of hearing is good.Noise spectrum by Figure 11 can be understood this effect.
Figure 11 illustrate inclined flow blower impeller shown in Figure 10 with 720 rev/mins rotating speed drive, air quantity is 29.8 cubic metres of/minute noise spectrums under the situation.The impeller 16 that comprises blade 2 has 415 millimeters of diameter phi.Blade has circular-arc leading edge and the blade shape of the trailing edge of the shape that comes to a point.
Near 1 kilo hertz sound pressure level is a turbulence noise.1nZ sound and higher harmonics composition 2nZ, 3nZ, 4nZ sound are the revolution noise of blade 2.As seen from Figure 11, and compare as near the sound pressure level 1 kilo hertz of the turbulence noise, lower as the sound pressure level of the revolution noise 1nZ of blade 2 and higher harmonics composition 2nZ, 3nZ, 4nZ sound.
In addition, though this exemplary embodiments 2 is that the impeller that is used for inclined flow blower is described, even also can obtain and above-mentioned effect same to the impeller that is used for axial fan.
Exemplary embodiments 3:
Figure 12 is the plan view of impeller of the inclined flow blower of this exemplary embodiments 3.
The impeller of this exemplary embodiments 3 is compared blade only with the impeller of exemplary embodiments 1 shape is different, and other structures are then identical.So allly identically with exemplary embodiments 1 structure all adopt same numeral, specify and be omitted, and be that the center is illustrated with the different piece with the part with same function effect.
Among Figure 12, a bit the overlapping with the intersection point place of the blade tip 6 of leg-of-mutton auxiliary blade 17 in leading edge 4 as the blade 2 of primary blades.And one side of leg-of-mutton auxiliary blade 17 is close to the leading edge 4 of blade 2 and is wholely set.Wheel hub 3 is provided with 2 pieces of blades 2 with this leg-of-mutton auxiliary blade 17.Each blade 2 is that the center is symmetrical arranged with wheel hub 3.Constitute the impeller 40 of inclined flow blower like this.
Adopt said structure, the front end of leg-of-mutton auxiliary blade 17 is generated blade end eddy current 33D as starting point and at the suction surface of blade 2 coniformly, this blade end eddy current 33D peels off and diffluence in the middle of blade.
The front end of this leg-of-mutton auxiliary blade 17 has the effect of the generation of regulation blade end eddy current 33D.Therefore state that near the suction surface of this blade end eddy current 33D the blade tip 6 of blade 2 taken place and the state of peeling off also diffluence from blade 2 stipulates at all.So will be limited in inferior limit to the influence of the blade end eddy current 33D of the blade 2 at the rear that turns over.Therefore, it is the blade that has " b/L≤1 " scope as aspect ratio, even be spaced apart fully 2 pieces of wide blades between 2 pieces of blades 2, also the inflow air of the rear blade 2 that then turns over can be controlled at the still less disorderly state of maintenance, make the inflow air of level and smooth optimum state enter the rear blade.Because more be difficult to be subjected to the influence of blade end eddy current 33D for the blade 2 at rear, the inflow air that enters each blade is the most level and smooth, more is difficult to produce air on the blade 2 and peels off and wild effect such as stall.Consequently the blade noise further reduces, and static pressure further improves.
In addition, though this exemplary embodiments 3 is that the impeller that is used for inclined flow blower is described, even also can obtain and above-mentioned effect same to the impeller that is used for axial fan.
Exemplary embodiments 4:
Figure 13 illustrates the air conditioner of exemplary embodiments of the present invention.
In Figure 13, air conditioner 50 comprises and is arranged on indoor indoor set 51, is arranged on outdoor outdoor unit 52, is arranged on the circulation pipe arrangement 53 between above-mentioned indoor set 51 and the outdoor unit 52.Above-mentioned indoor set 51, outdoor unit 52 and circulation pipe arrangement 53 form the refrigeration cycle of refrigeration agent.
Outdoor unit 52 has heat exchanger 54 and gas fan 55.Gas fan 55 has impeller 56.Can adopt impeller 1, impeller 15, impeller 16 or the impeller 40 of explanation among the aforementioned typical embodiment 1 as impeller 56.Gas fan 55 has the air-supply effect of the heat exchange that is used to carry out heat exchanger 54.
That is, gas fan 55 is delivered to wind in the heat exchanger 54.Perhaps, gas fan 55 has the function that near heat exchanger 54 heats pressures are moved.
In the air conditioner 50 of this exemplary embodiments, the noise that is produced by gas fan 55 and the air conditioner that uses gas fan in the past specific energy mutually significantly reduce.And can improve wind pushing performance and heat exchange performance.Can also reduce manufacture cost in addition.
That is, 2 pieces blade is not owing to mutually be subjected to the influence of the blade end eddy current of the opposing party's blade, enters that the inflow air of each blade is disorderly to be reduced and level and smooth, on the blade peel off and wild effect such as stall is difficult to produce.Its result, the noise that blade produces significantly reduces, and has improved static pressure; Can also reduce the shared volume of impeller in addition, reduce manufacture cost.
In addition, also the sound pressure level than turbulence noise is low as " nZ " sound of the revolution noise of blade and higher harmonics thereof.So can prevent generation, and actual sense of hearing is good as the unusual sound of whole impeller.
In addition, because blade has leg-of-mutton auxiliary blade, further improved above-mentioned effect.
In addition, adopt the structure of air conditioner of the present invention, the noise that outdoor unit produces also can be lower than air conditioner in the past.And can improve the wind pushing performance and the heat exchange performance of air conditioner.And can obtain cheap air conditioner.
Claims (20)
1. blower-use impeller comprises wheel hub (3,13) and is arranged at 2 pieces of blades (2,14) on this wheel hub,
Each blade of described 2 pieces of blades is that the center is symmetrically set with described wheel hub,
When the chord length of the blade of the representative mean square radius of gyration " Rr " position of each blade of described 2 pieces of blades is the representative physical length of " L " and radial direction during for " b ",
The aspect ratio of each blade " b/L " has the shape of " b/L≤1 " scope, it is characterized in that, in the radial direction cross section of described each blade, from having with respect to the wind upside to the part of the most advanced and sophisticated side position of periphery near the position of the representative mean square radius of gyration of described blade is curve shape streamlined of spill (2a)
From having with respect to the wind upside to the part of the position of hub side near the position of the representative mean square radius of gyration of described blade is the curve shape of convex (2b),
Because the rotation of described each blade, described each blade make air flow into from the leading edge (4) of described each blade, and flow out from trailing edge (5),
Go up the blade end eddy current (33D) that produces at the suction surface of described each blade (8,8a, 8b) and peel off diffluence from described blade,
Interval between each blade is fully wide, to avoid being subjected to the influence of described blade end eddy current (33D).
2. blower-use impeller as claimed in claim 1, it is characterized in that, described each blade has leg-of-mutton auxiliary blade (17), and 1 leading edge at described blade of described auxiliary blade overlaps with the intersection point place of periphery, and 1 limit and the described leading edge of described auxiliary blade are close to formation.
3. blower-use impeller as claimed in claim 1 is characterized in that the chord length of the outer circumferential side of described each blade is longer than the chord length of hub side.
4. as each blower-use impeller among the claim 1-3, it is characterized in that described each blade has the trailing edge (5) of the leading edge (4) of circular arc and the shape that comes to a point, be shaped as shape with progressive additive from described trailing edge to described leading edge.
5. as each blower-use impeller among the claim 1-3, it is characterized in that described each blade has the trailing edge (5) of the leading edge (4) of circular arc and the shape that comes to a point, the thickness from described trailing edge to described leading edge is to have roughly the same thickness.
6. as each blower-use impeller among the claim 1-3, it is characterized in that,
Described wheel hub is have circular cross-section trapezoidal,
When the least radius of the described circle of described wheel hub is the maximum radius of " r1 " and described wheel hub during for " r2 ", as represent hub radius be " r ", then is defined as r=(r1+r2)/2,
Distance from the center of described wheel hub to the maximum front end of described blade be " R2 ", and extremely the distance of the minimum front end of described blade is " R1 " from the center of described wheel hub, when the representative radius of impeller is " R " as described, then is defined as R=(R1+R2)/2,
When representing the mean square radius of gyration, be defined as Rr=((R for " Rr "
2+ r
2)/2)
1/2,
Described " L " is the chord length of the described blade of the described representative mean square radius of gyration " Rr " position,
Described " b " is the length of the spanwise of the described blade of the position of the position that connects described representative hub radius " r " and described representative radius " R ".
7. as each blower-use impeller among the claim 1-3, it is characterized in that described impeller is used for the outdoor unit of air conditioner.
8. a gas fan comprises motor (12) and the impeller that is connected with described motor (1,15,16,40),
Described impeller comprises wheel hub (3) and is arranged at 2 pieces of blades (2) on this wheel hub,
It is that the center is symmetrical that each blade of described 2 pieces of blades is arranged to described wheel hub, when the chord length of the blade of the representative mean square radius of gyration " Rr " position of each blade of described 2 pieces of blades is the representative physical length of " L ", radial direction during for " b ",
The aspect ratio of described each blade " b/L " has the shape of " b/L≤1 " scope, it is characterized in that,
In the radial direction cross section of described each blade, be curve shape streamlined of spill (2a) from having with respect to the wind upside to the part of the most advanced and sophisticated side position of periphery near the position of the representative mean square radius of gyration of described blade,
From having with respect to the wind upside to the part of the position of hub side near the position of the representative mean square radius of gyration of described blade is the curve shape of convex (2b).
9. gas fan as claimed in claim 8 is characterized in that,
Described each blade has leg-of-mutton auxiliary blade (17),
1 leading edge at described blade of described auxiliary blade overlaps with the intersection point place of periphery, and 1 limit and the described leading edge of described auxiliary blade are close to formation.
10. gas fan as claimed in claim 8 is characterized in that,
The chord length of the outer circumferential side of described each blade is longer than the chord length of hub side.
11., it is characterized in that described impeller has the diagonal flow type structure as each described gas fan in the claim 8 to 10.
12., it is characterized in that described impeller has shaft flow structure as each described gas fan in the claim 8 to 10.
13. as each described gas fan in the claim 8 to 10, it is characterized in that,
Described wheel hub is have circular cross-section trapezoidal,
When the least radius of the described circle of described wheel hub is the maximum radius of " r1 " and described wheel hub during for " r2 ", as represent hub radius be " r ", then is defined as r=(r1+r2)/2,
Distance from the center of described wheel hub to the maximum front end of described blade be " R2 ", and extremely the distance of the minimum front end of described blade is " R1 " from the center of described wheel hub, and the representative radius of impeller is " R " as described, then is defined as R=(R1+R2)/2,
When representing the mean square radius of gyration, be defined as Rr=((R for " Rr "
2+ r
2)/2)
1/2,
Described " L " is the chord length of the described blade of the described representative mean square radius of gyration " Rr " position,
Described " b " is the length of the spanwise of the described blade of the position of the position that connects described representative hub radius " r " and described representative radius " R ".
14., it is characterized in that described blower-use is in the outdoor unit of air conditioner as each described gas fan in the claim 8 to 10.
15. an air conditioner comprises indoor set (51), outdoor unit (52), is arranged on the pipe arrangement (53) between above-mentioned indoor set and the outdoor unit,
(a) described outdoor unit has heat exchanger (54) and gas fan (55),
(b) above-mentioned gas fan has motor (12) and the impeller that is connected with this motor (1,15,16,40),
(c) described impeller comprises wheel hub (3) and is arranged at 2 pieces of blades (2) on the described wheel hub,
Each blade of described 2 pieces of blades is that the center is arranged to symmetrically with described wheel hub,
The chord length of the blade of the representative mean square radius of gyration " Rr " position of each blade of described 2 pieces of blades is the representative physical length of " L " and radial direction during for " b ",
The aspect ratio of described each blade " b/L " has the shape of " b/L≤1 " scope, it is characterized in that, in the radial direction cross section of described each blade, from having with respect to the wind upside to the part of the most advanced and sophisticated side position of periphery near the position of the representative mean square radius of gyration of described blade is curve shape streamlined of spill (2a)
From having with respect to the wind upside to the part of the position of hub side near the position of the representative mean square radius of gyration of described blade is the curve shape of convex (2b).
16. air conditioner as claimed in claim 15 is characterized in that,
Described each blade has leg-of-mutton auxiliary blade (17),
1 leading edge at described blade of described auxiliary blade overlaps with the intersection point place of periphery, and 1 limit and the described leading edge of described auxiliary blade are close to formation.
17. air conditioner as claimed in claim 15 is characterized in that, the chord length of the outer circumferential side of described each blade is longer than the chord length of hub side.
18., it is characterized in that described gas fan has the diagonal flow type structure as each described air conditioner in the claim 15 to 17.
19., it is characterized in that described gas fan has shaft flow structure as each described air conditioner in the claim 15 to 17.
20. as each described air conditioner in the claim 15 to 17, it is characterized in that,
Described wheel hub is have circular cross-section trapezoidal,
When the least radius of the described circle of described wheel hub is the maximum radius of " r1 " and described wheel hub during for " r2 ", as represent hub radius be " r ", then is defined as r=(r1+r2)/2,
Distance from the center of described wheel hub to the maximum front end of described blade be " R2 ", and extremely the distance of the minimum front end of described blade is " R1 " from the center of described wheel hub, and the representative radius of impeller is " R " as described, then is defined as R=(R1+R2)/2,
When representing the mean square radius of gyration, be defined as Rr=((R for " Rr "
2+ r
2)/2)
1/2,
Described " L " is the chord length of the described blade of the described representative mean square radius of gyration " Rr " position,
Described " b " is the length of the spanwise of the described blade of the position of the position that connects described representative hub radius " r " and described representative radius " R ".
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP270830/99 | 1999-09-24 | ||
| JP27083099A JP3743222B2 (en) | 1999-09-24 | 1999-09-24 | Blower impeller and air conditioner |
| JP270830/1999 | 1999-09-24 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1289897A CN1289897A (en) | 2001-04-04 |
| CN1297751C true CN1297751C (en) | 2007-01-31 |
Family
ID=17491616
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB001288504A Expired - Fee Related CN1297751C (en) | 1999-09-24 | 2000-09-22 | Impeller for fun, fun therewith and air conditioner with the fun |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP1087146B1 (en) |
| JP (1) | JP3743222B2 (en) |
| CN (1) | CN1297751C (en) |
| ES (1) | ES2312316T3 (en) |
| MY (1) | MY131508A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100584365C (en) * | 2006-12-01 | 2010-01-27 | 朱炜 | Pharmaceutical composition for treating acne |
Families Citing this family (31)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2372785B (en) * | 2001-01-11 | 2004-05-05 | Lg Electronics Inc | Fan for condenser of refrigerator |
| KR100487339B1 (en) * | 2002-11-18 | 2005-05-03 | 엘지전자 주식회사 | axial flow fan |
| JP4492060B2 (en) * | 2003-08-06 | 2010-06-30 | パナソニック株式会社 | Blower impeller |
| KR100547328B1 (en) * | 2003-09-05 | 2006-01-26 | 엘지전자 주식회사 | The fan of air-conditioner outdoor unit |
| JP4572617B2 (en) * | 2004-07-30 | 2010-11-04 | パナソニック株式会社 | Blower impeller for air conditioning |
| JP4572633B2 (en) * | 2004-09-08 | 2010-11-04 | パナソニック株式会社 | Blower impeller for air conditioning |
| JP4529613B2 (en) * | 2004-09-22 | 2010-08-25 | パナソニック株式会社 | Blower impeller |
| JP4521867B2 (en) * | 2004-10-19 | 2010-08-11 | 日立アプライアンス株式会社 | Air conditioner outdoor unit |
| JP4747784B2 (en) * | 2005-10-31 | 2011-08-17 | パナソニック株式会社 | Axial blower impeller |
| JP4802694B2 (en) * | 2005-12-13 | 2011-10-26 | パナソニック株式会社 | Blower impeller and air conditioner |
| JP4749176B2 (en) * | 2006-02-14 | 2011-08-17 | シャープ株式会社 | Propeller fan and fluid feeder |
| JP4749175B2 (en) * | 2006-02-14 | 2011-08-17 | シャープ株式会社 | Propeller fan and fluid feeder |
| JP4797776B2 (en) * | 2006-04-24 | 2011-10-19 | パナソニック株式会社 | Mixed flow blower impeller and air conditioner |
| JP4910534B2 (en) * | 2006-07-21 | 2012-04-04 | パナソニック株式会社 | Blower impeller |
| JP2007107530A (en) * | 2006-11-16 | 2007-04-26 | Toshiba Kyaria Kk | Axial flow fan |
| JP4967882B2 (en) * | 2007-07-23 | 2012-07-04 | パナソニック株式会社 | Mixed flow blower impeller and air conditioner |
| JP4967883B2 (en) * | 2007-07-23 | 2012-07-04 | パナソニック株式会社 | Mixed flow blower impeller and air conditioner |
| JP2012107538A (en) * | 2010-11-16 | 2012-06-07 | Panasonic Corp | Axial-flow fan or diagonal-flow fan, and air conditioner mounted outdoor unit with the same |
| WO2013082717A1 (en) | 2011-12-06 | 2013-06-13 | Bachellier Carl Roy | Improved impeller apparatus and dispersion method |
| JP6058276B2 (en) * | 2012-04-10 | 2017-01-11 | シャープ株式会社 | Propeller fan, fluid feeder and mold |
| WO2014050146A1 (en) * | 2012-09-28 | 2014-04-03 | ダイキン工業株式会社 | Propeller fan and air conditioner equipped with same |
| WO2015092924A1 (en) * | 2013-12-20 | 2015-06-25 | 三菱電機株式会社 | Axial flow fan |
| US9863423B2 (en) | 2014-04-14 | 2018-01-09 | Enevor Inc. | Conical impeller and applications thereof |
| JP6143725B2 (en) * | 2014-10-06 | 2017-06-07 | シャープ株式会社 | Propeller fan, fluid feeder and mold |
| JP5905985B1 (en) * | 2015-08-18 | 2016-04-20 | 山洋電気株式会社 | Axial flow fan and serial type axial flow fan |
| JP6068720B2 (en) * | 2016-07-29 | 2017-01-25 | シャープ株式会社 | Electric fan or circulator propeller fan, electric fan or circulator, and mold |
| CN106762823A (en) * | 2016-12-28 | 2017-05-31 | 东莞市卓奇电子科技有限公司 | Multiple flow passages axle stream wind focuses on impeller |
| CN107013487B (en) * | 2017-05-31 | 2023-03-24 | 广东美的制冷设备有限公司 | Oblique flow wind wheel and air conditioner with same |
| CN108869358B (en) * | 2018-07-09 | 2023-09-01 | 广东美的环境电器制造有限公司 | Fan with fan body |
| CN110513329A (en) * | 2019-09-30 | 2019-11-29 | 广东美的制冷设备有限公司 | Axial-flow windwheel and air conditioner with it |
| EP4130487A4 (en) * | 2020-03-24 | 2023-05-03 | Mitsubishi Electric Corporation | Axial fan, blowing device, and refrigeration cycle device |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1807397A (en) * | 1927-05-20 | 1931-05-26 | Westinghouse Electric & Mfg Co | Propeller type pump or fan |
| CN86209370U (en) * | 1986-11-26 | 1988-02-10 | 南昌电扇厂 | Energy-saving electric fan |
| US4893990A (en) * | 1987-10-07 | 1990-01-16 | Matsushita Electric Industrial Co., Ltd. | Mixed flow impeller |
| FR2723150A1 (en) * | 1994-07-29 | 1996-02-02 | Morin Philippe | Helical blade for air blower |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4138859A (en) * | 1977-11-02 | 1979-02-13 | General Electric Company | Split heat pump outdoor fan arrangement |
| GB2198190A (en) * | 1986-11-28 | 1988-06-08 | Frank L Cook | Air turbulence blades for ceiling fans |
-
1999
- 1999-09-24 JP JP27083099A patent/JP3743222B2/en not_active Expired - Lifetime
-
2000
- 2000-09-15 MY MYPI20004291 patent/MY131508A/en unknown
- 2000-09-15 ES ES00119461T patent/ES2312316T3/en not_active Expired - Lifetime
- 2000-09-15 EP EP20000119461 patent/EP1087146B1/en not_active Expired - Lifetime
- 2000-09-22 CN CNB001288504A patent/CN1297751C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1807397A (en) * | 1927-05-20 | 1931-05-26 | Westinghouse Electric & Mfg Co | Propeller type pump or fan |
| CN86209370U (en) * | 1986-11-26 | 1988-02-10 | 南昌电扇厂 | Energy-saving electric fan |
| US4893990A (en) * | 1987-10-07 | 1990-01-16 | Matsushita Electric Industrial Co., Ltd. | Mixed flow impeller |
| FR2723150A1 (en) * | 1994-07-29 | 1996-02-02 | Morin Philippe | Helical blade for air blower |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100584365C (en) * | 2006-12-01 | 2010-01-27 | 朱炜 | Pharmaceutical composition for treating acne |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3743222B2 (en) | 2006-02-08 |
| EP1087146A3 (en) | 2002-04-03 |
| EP1087146B1 (en) | 2008-08-27 |
| ES2312316T3 (en) | 2009-03-01 |
| EP1087146A2 (en) | 2001-03-28 |
| MY131508A (en) | 2007-08-30 |
| CN1289897A (en) | 2001-04-04 |
| JP2001090693A (en) | 2001-04-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1297751C (en) | Impeller for fun, fun therewith and air conditioner with the fun | |
| CN1296611C (en) | Exhaust diffuser for axial-flow turbine | |
| CN1022505C (en) | Non variable capacitance type rotary machine | |
| CN206175256U (en) | High -efficient axial fan | |
| CN1826464A (en) | Vertical-axis wind turbine | |
| CN1201514A (en) | Outlet unit for underfloor air conditionor and underfloor air conditioning system using same | |
| CN1756908A (en) | Radial fan wheel, fan unit, and radial fan arrangement | |
| CN1712733A (en) | Eccentric fan and air conditioner therewith | |
| CN1752457A (en) | Blower impeller | |
| CN1847669A (en) | Air feeder vane wheel | |
| CN1540170A (en) | High performance axial fan | |
| CN106837832A (en) | A kind of new portable electric fan | |
| JP2001509226A (en) | Impeller and fan incorporating it | |
| CN107975493A (en) | A kind of fan for air conditioner on vehicle impeller mechanism | |
| CN205331054U (en) | Axial -flow fan with many curved surfaces type blade | |
| CN110104154A (en) | A kind of pump-jet propulsor | |
| US7845899B2 (en) | Fluid powered turbine engine | |
| CN203130602U (en) | Cross-flow fan for air conditioner, cross-flow blower and air conditioner | |
| CN102852854A (en) | Floor type air conditioner and oblique flow fan thereof | |
| CN1221766C (en) | Outdoor unit of air conditioner | |
| CN106762829B (en) | Blade for impeller, impeller and fan | |
| CN202883468U (en) | Floor-stand air conditioner and oblique flow fan thereof | |
| CN102758793B (en) | Fan blade and axial flow fan with fan blade of air conditioner | |
| CN2575343Y (en) | Axial flow fan apparatus carried on mobile vehicle | |
| CN209818372U (en) | Negative pressure formula axial fan of high-efficient silence |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20070131 Termination date: 20130922 |