CN2837569Y - Cross flow fan for air conditioner indoor unit - Google Patents
Cross flow fan for air conditioner indoor unit Download PDFInfo
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- CN2837569Y CN2837569Y CN 200520017205 CN200520017205U CN2837569Y CN 2837569 Y CN2837569 Y CN 2837569Y CN 200520017205 CN200520017205 CN 200520017205 CN 200520017205 U CN200520017205 U CN 200520017205U CN 2837569 Y CN2837569 Y CN 2837569Y
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- air conditioner
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Abstract
The utility model relates to a cross flow fan for an indoor unit of a wall hanging type air conditioner, a plurality of blades are slantwise fixed to a circular plate along the circumferential direction according to a prescribed angle, each blade is slanted by a definite angle corresponding to the central axis of the circular plate in the longitudinal direction, and meanwhile, the installing intervals of the blades are not equal; the included angle of each two adjacent blades and the central axis of the circular plate is in the random distribution between 9 degrees and 11 degrees, and a section of blade wheel with multiple blades, a plurality of sections of the blade wheels are correspondingly staggered by a prescribed angle each other around the axis and are orderly stacked and fixedly connected along the axial direction, until the required length is reached, the two end surfaces are sealed and the cross flow fan of the utility model is formed. Compared with the traditional fan, the fan of the utility model has the advantages that the noise can be reduced, the air blowing performance can be improved, and the utility model can be machined easily in the production and the performance is stable in use.
Description
Technical field
The utility model relates to a kind of indoor unit fan of air conditioner, especially the used cross flow fan of wall-hanging air conditioner indoor unit.
Background technique
What wall-hanging indoor split-type air conditioner adopted is axial-flow fan.The impeller of this blower fan has the forward-type blade, and the axial wide of blade can be done very widely, is the cylinder shape, the both ends of the surface sealing.When impeller rotates, suck gas between the blade, under action of centrifugal force, gas is thrown to around the impeller, and volume compression, density increase, produce static pressure, strengthen airspeed simultaneously, produce dynamic pressure (promptly having improved kinetic energy), and gas is sent by the air port.In the case, the impeller core forms low-voltage space, and air constantly sucks, form air into and out of continuous circulation.
Cross flow fan is the fluid draught fan impeller of flowing through for twice, after fluid radially flows into impeller, radially flows out through impeller after being forced to reverse again, and there is inevitable eccentric vortex in blower fan inside.Because the air velocity direction takes a turn for the worse, therefore bigger pressure oscillation takes place, produce aerodynamic noise.The aerodynamic noise of cross-flow fan and air quantity, gas flow state have direct relation.The aerodynamic noise of cross flow fan is the main noise source of air conditioner indoor machine group.Aerodynamic noise during the cross flow fan rotation mainly is divided into rotational noise and eddy current crack.
Rotational noise be since cross flow fan when high speed rotating, blade is done cyclical movement, the noise that fluid produces at parts such as periodic shock blower fan whirlpool, outlet port tongue, the major character of rotational noise is the discrete frequency noise.
The rotational noise of cross flow fan claims discrete frequency noise or blade passing frequency noise again, and its genesis mechanism has two.(1) when impeller during in free-space rotation, because the gas medium of blade around hitting, air is subjected to the periodic excitation of blade and pressure field thereof and sounding on contiguous certain fixed position of blade, and its essence is rotational noise, its fundamental frequency:
f1＝ns/60，Hz
The rotational speed rpm of n-each second; The z-number of blade.
(2) effect of blade wake produces another kind of rotational noise.When air flow stream is crossed blade, form boundary layer at blade surface, particularly the boundary layer on suction limit is thickeied easily, and produces many whirlpools.At place, blade tail source, the boundary layer on suction limit and pressure limit converges formation tail district.In the tail district, the pressure of air-flow and speed all are significantly less than the main air flow district.Thereby when active wheel rotated, air-flow had very big nonuniformity in the blade exit district.This nonuniformity air-flow periodically acts on environment, produces pressure pulsation and forms noise.When the spacing between movable vane row and snail tongue was too small, front-seat blade wake is inswept, and back row's blade or the inswept snail tongue of movable vane wake flow all can produce pulsating force, thereby produced rotational noise.
Eddy current crack claims the vortex noise again.Impeller is in high speed rotating, all there is the phenomenon of gas separation in the outlet of the import of impeller, the inside of impeller, impeller, because the separation of gas, the separation of air-flow will cause eddy current, the moving and break of eddy current, make air-flow generation disturbance, in air-flow, form compression and sparse process, produce eddy current crack thus.Because there is inevitable eddy current in cross flow fan inside, the central position of eccentric vortex, size, strong and weak noise power and the gas flow that has directly influenced cross flow fan.
The cross flow fan eccentric vortex is subjected to the long-pending ratio of the air intake/outtake surface of air intake flow field, axial-flow fan, blade profile, hub ratio, the position of tongue piece, shape, angle, the position of dividing plate, the influences such as shape of volute, thereby, solve eddy current crack should be from the air channel and impeller design take all factors into consideration.
In the prior art, the noise reduction measure of cross flow fan mainly contains, and makes blade with respect to the fan shaft tilted configuration, and this configuration mode can make the pressure oscillation that produces in the interval between blade and snail tongue disperse, thereby reduces rotation.
In addition, with predetermined torsional angle and the structure of twisting direction with the blade arrangement curl, its principle is the same with the axle tilted configuration with blade with respect to fan shaft, also has the effect of disperseing above-mentioned pressure oscillation, reduction noise.
For example Japan Patent model utility communique reality public clear 59-39196 number, reality are opened clear 56-2092 number, open in fact and wait the cross flow fan of putting down in writing respectively on the communique clear 56-45196 number, it is non-parallel proposing by each blade being formed apparent wind fan axle, pressure oscillation is recurred, thus the scheme that above-mentioned rotation sound is reduced.
In the such scheme, adopt axially oblique impeller, impeller is different with the gap of snail tongue, spiral case in the axial direction, produces phase deviation, the noise frequency that is sent is also different, and the result of the noise of different frequency stack can avoid because the resonance noise peak that the same frequency noise superposes and brings.
Yet, even utilize phase deviation, also can not eliminate the rotation sound fully in full sound field, in addition, fan shaft and blade are formed than wide-angle, therefore the first-harmonic of rotation sound can not be eliminated fully.And, in the such scheme, the installation interval along sense of rotation of blade is defined as uniformly-spaced, therefore, the frequency of the first-harmonic of rotation sound becomes single-frequency, makes the frequency characteristic of air-supply noise have big peak value on this frequency, causes noise qualities to worsen.
Another kind of known technology is with multiple interval (equidistant) a plurality of aforesaid oblique twisted blades not to be arranged on the impeller dividing plate, and the crest frequency of the rotation sound that oblique twisted blade reduces is dispersed.
Adopting not equidistant impeller is one of effective means that reduces cross flow blower rotation fundamental frequency noise.We are known, the fundamental frequency f1 of equidistant impeller rotational noise is f1=n/60z, the angle that makes any two adjacent blades and impeller center is θ, so for equidistant impeller, θ is a definite value, and its size is relevant with the number of blade, i.e. θ=2 π/z=definite value, each blade is identical with the fluctuation intensity of snail tongue bump, and the phase difference of adjacent two blades bump snail tongue is 2 π/z.The relevant fluctuation intensity at fundamental frequency place that makes of this harmonic wave is enhanced.
Impeller when θ is stochastic variable is called not equidistant impeller.Adopt not design equidistantly, the scope of θ changes, though at this moment number of blade z is identical with equidistant design, the θ angle between the adjacent blades has nothing in common with each other.In this case, f1 becomes a kind of distribution frequency { f1}.
Not equidistant each blade of impeller is different with the intensity of snail tongue bump, and the phase difference of adjacent two blades bump snail tongue also has nothing in common with each other.On frequency characteristic, the peak value of equidistant impeller at f1 place slackened by equidistant impeller and is the less distribution value of numerical value, and makes not equidistantly that the OA overall noise level of impeller obviously descends.The de-noising mechanism of Here it is not equidistant impeller cross flow fan.
Chinese patent 95100627.4 discloses a kind of cross flow fan, and its technological scheme has adopted impeller not to be equally spaced exactly, and with blade and axle tilted configuration.
Adopt not equidistant effectively noise abatement of impeller, but in the such scheme, do not indicate interlobate spacing range.Bring difficulty for thus the not design of equidistant impeller cross flow fan.It adopts random choice method fully, and resulting noise reduction also has certain randomness, also makes the fan performance of producing have unstability.On the other hand, behind the equidistant impeller of employing, the width of runner has nothing in common with each other in the impeller, and the air-flow of air outlet is also inhomogeneous, is easy to generate turbulence noise.
In addition, according to laboratory data, it is less to adopt blade lean to reach the impeller noise that is not equally spaced when rotating speed is low, but its increase with rotating speed increases bigger; Under the rotating speed condition with higher, their noise characteristic is poorer than the straight impeller that is equally spaced on the contrary.That is to say, in theory, adopt be not equally spaced blade and tiltedly blade be feasible, can avoid the stack of same frequency noise like this and the resonance noise peak brought, but its optimum condition scope is arranged, when rotating speed increases, performance is easy to worsen, and impacting and separating sharply increases, therefore, noise also increases bigger, and the noise reduction value brought greater than avoiding same frequency noise stack of the value added of caused noise.But such scheme does not provide effective solution.
The effective ways one that reduce rotation speed of the fan are to increase impeller diameter, the 2nd, enlarge fan air intake district, and improve the air output of revolution.Be subjected to the restriction of indoor set volume and vaporizer shape, it is too big that impeller diameter can not be done, and impeller diameter becomes big, the spacing of itself and snail tongue and vaporizer is reduced,, can send ear-piercing howling though noise reduces, be that noise qualities worsens, make us being difficult to stand.Therefore be to increase fan air intake district than valid approach.Under the identical situation of vaporizer shape, fan air intake region area is relevant with the setting angle of fan blade on demarcation strip.But do not have as yet in the prior art by changing the design that this setting angle improves incoming air area.
Summary of the invention
The purpose of this utility model provides a kind of and can reduce noise just at the problems referred to above, can improve the cross flow fan of wind pushing performance simultaneously.
Another purpose of the present utility model be to provide be easy to processing in a kind of production, use in stable performance, cross flow fan efficiently.
The technical solution of the utility model is:
With a plurality of blades along circumferentially in accordance with regulations angle tilt be fixed on the plectane, and make above-mentioned each blade at vertically relative plectane inclined several angle, installation interval with above-mentioned blade is unequal interval simultaneously, and the angle of adjacent two blades and plectane central shaft random distribution between 9 °～11 °.Thus, form one section multiblade impeller.
Each other around the axle predetermined angular that staggers relatively, and stack gradually fixedly connectedly vertically the above-mentioned impeller of multistage,,, promptly form cross flow fan of the present utility model the both ends of the surface sealing until needed length; An outstanding rotating shaft is formed with the hub portion that engages with electric machine rotational axis in the middle of the fan one end face outside on the fan other end.And the axial width of one section impeller that is provided with hub portion is shorter than the axial width of other section impeller, its width be other section impeller axial width 1/3 to 2/3.
The cross section of blade described in the utility model is an arc, and from the middle of its cross section to both sides attenuation gradually.
In addition, blade also can be curved along its longitudinal bending.
The utility model is owing to be obliquely installed the relative fan shaft of blade, can make have this blade cross flow fan when rotated and between the snail tongue and and vaporizer between the pressure oscillation that produces continuous, thereby can reduce the rotation sound of cross flow fan.
Because setting the circumferential installation interval of blade for unequal interval, thus can disperse because of mutliblade tilted shape makes the crest frequency of lowered rotation sound, thus noise qualities is improved.And the angle of adjacent two blades and axle is limited between 9 °～11 °, has avoided the excessive or too small air-flow that causes of blade pitgh inhomogeneous, and made in the production and have regulations to abide by, also make the product performance of production have certain stability.
In addition, owing to being stacked gradually vertically, the multistage multiblade impeller is fixed into integrally formed cross flow fan, so manufacturing is simple, cost is low, and by suitably selecting the stacked number of multiblade impeller, can change the axial length of fan easily, and, owing to the axial width of the one section multiblade impeller that is provided with hub portion is shorter than the axial width of other multiblade impeller, the intensity of this section is improved, can bear the power that applies when motor shaft drives the fan rotation and indeformable.
Since with each blade in the middle of its cross section to both sides of the edge attenuation gradually, can effectively reduce air turnover resistance, make turnover wind smooth more.When air flow stream is crossed blade, be not easy to form boundary layer at blade surface, reduce the generation in whirlpool, thereby reduce rotational noise.
Owing to by blade body is longitudinally formed the circular-arc curve-like of Denging, thereby can make the non-parallel earth tilt of the easier relative fan shaft of blade, the rotation sound is reduced, and do not have residual stress owing on the blade body, can improve intensity.
By with a plurality of blades along circumferentially in accordance with regulations angle tilt be arranged on the above-mentioned discoideus side, can effectively enlarge air intake and air-out scope, when adopting multi-bended vaporizer, when equal rotating speed, can improve and pass in and out air quantity.For adapting to the different radians of different evaporators, in the utility model, above-mentioned inclination angle is set between 10 °-25 °.Above-mentioned angle of inclination be meant line between the two-end-point of leaf cross-section with an end points wherein to formed acute angle between the line of fan shaft.
Because adopting the prerequisite of the noise reduction measure that tilts to reach the blade that is not equally spaced is that rotating speed can not be too high, the utility model is by above-mentioned measure, improve the air intake flow field, enlarging the turnover demeanour encloses, the turnover air quantity of revolution is increased, thereby under the prerequisite that guarantees air quantity, reduce rotating speed, guarantee the noise reduction that adopts above-mentioned inclination and be not equally spaced blade.
Compare with traditional fan, fan of the present utility model can reduce noise, can improve wind pushing performance simultaneously, and stable performance in being easy in producing process, use.
Description of drawings
Fig. 1 is the stereogram of one section impeller
Fig. 2 dresses up the decomposing schematic representation of fan for the multistage impeller sets
Fig. 3 is the utility model cross flow fan one embodiment's a stereogram
Fig. 4 is the angle schematic representation of not equidistant impeller adjacent blades and fan shaft
Fig. 5 is the sectional arrangement drawing of air conditioner indoor machine
Specific embodiment
Below, in conjunction with the embodiments the utility model is elaborated with reference to the accompanying drawings.
At first referring to Fig. 1, Fig. 1 is one section leafy stereogram of taking turns.With a plurality of blades 1 along circumferentially in accordance with regulations angle [alpha] tilt to be fixed on the plectane 2.For adapting to the different radians of different evaporators, in the utility model, above-mentioned inclination alpha is set between 10 °-25 °.Above-mentioned tilt angle alpha be meant line between the two-end-point of leaf cross-section with an end points wherein to formed acute angle between the line of fan shaft.
And above-mentioned each blade 1 is at vertically relative plectane central shaft O inclination several angle β, and the installation interval with above-mentioned blade 1 is unequal interval simultaneously, and the angle theta of adjacent two blades 1 and plectane 2 central shaft O random distribution between 9 °～11 °.Thus, form one section multiblade impeller 3 as shown in Figure 1.
As shown in Figure 2, each other around the axle O predetermined angular that staggers relatively, and stack gradually fixedly connectedly vertically the above-mentioned impeller of multistage 3,,, promptly form cross flow fan shown in Figure 34 the both ends of the surface sealing until needed length; A plurality of telescoping grooves 5 are arranged on the plectane 2 of the one section impeller 3 in the left side among Fig. 2, and the tip portion that is used on the multiblade impeller that this section of figure is right adjacent each blade 1 of 3 embeds and is fixed therein.
An outstanding rotating shaft 6 is formed with the hub portion 7 that engages with electric machine rotational axis in the middle of the cross flow fan 4 one end faces outside on the fan other end.And, from Fig. 1 and Fig. 2 as can be seen, the axial width that is provided with one section impeller 3 ' of hub portion 7 is lacked than the axial width of other section impeller 3, the utility model its width is set at other section impeller axial width 1/3 to 2/3, the intensity of this section is improved, can bear the power that applies when motor shaft drives the fan rotation and indeformable.
As seen in Figure 4, to both sides of the edge attenuation gradually, so design can effectively reduce air turnover resistance to blade 1 of the present utility model, makes turnover wind smooth more in the middle of its cross section.
The utility model is owing to be provided with relative fan shaft O with each blade 1 and become non-parallel inclination, and the pressure that produces in the gap of the leading edge of cross flow fan 4 and snail tongue is changed continuously.For this reason, rotation sound peak value and its overtone peak value are all reduced.
In addition, because set a plurality of blades for unequal interval along circumferential installation interval,, the crest frequency composition of the rotation sound that the tilted shape because of each blade lowers is disperseed, thereby can improve noise qualities even in the occasion of the section of establishing staggered angle not.
The fundamental frequency f1 of equidistant impeller rotational noise is f1=n/60z, the angle that makes any two adjacent blades and impeller center is θ, so for equidistant impeller, θ is a definite value, its size is relevant with the number of blade, i.e. θ=2 π/z=definite value is for equidistant impeller, each blade is identical with the fluctuation intensity of snail tongue bump, and the phase difference of adjacent two blades bump snail tongue is 2 π/z.The relevant fluctuation intensity at fundamental frequency place that makes of this harmonic wave is enhanced.
As shown in Figure 4, adopt not design equidistantly, the scope of θ changes, though at this moment number of blade z is identical with equidistant design, the θ angle between the adjacent blades has nothing in common with each other.In this case, f1 becomes a kind of distribution frequency { f1}.
Not equidistant each blade of impeller is different with the intensity of snail tongue bump, and the phase difference of adjacent two blades bump snail tongue also has nothing in common with each other.On frequency characteristic, the peak value of equidistant impeller at f1 place slackened by equidistant impeller and is the less distribution value of numerical value, and makes not equidistantly that the OA overall noise level of impeller obviously descends.
Adopt the inhomogeneous of equidistant impeller outlet air-flow not, when blade pitgh has big difference, can form turbulence noise.Therefore the utility model is limited to the angle of adjacent two blades and axle between 9 °～11 °, makes blade pitgh unlikely excessive, and the inhomogeneous noise that causes of its air-flow is very little.So also make the fan performance of production have stability.
And, with a plurality of blades along circumferential installation interval by unequal interval set, the section of establishing staggered angle simultaneously, the acoustic pressure wave that takes place on the adjacent vanes because of forming phase difference, the section staggered angle is cancelled out each other, further reduce because of the rotation sound that reduces with the fan axioversion thereby can make because of each blade, and, owing to the radio-frequency component of sound insulation between remaining blade is disperseed, thereby can improve the noise quality.
Under the ideal situation, heat exchanger equates to the distance of blast fan import, and promptly the fan airintake direction is for radially, and this moment, air-flow was not turned back at inlet flow field, and air inlet is the most even, and flow losses are minimum also.But because the requirement of air-conditioning boundary dimension is difficult to realize and the concentrically ringed heat exchanger arrangement of impeller.During actual design, adopt multi-bended or arc evaporator, heat exchanger 8 as shown in Figure 5 makes the angle of yaw of air-flow before entering blast fan change difference and reduces more, and the excursion of the angle of attack also reduces.As seen, air-flow is before entering impeller, and pre-swing angle is inevitable.
According to present embodiment, by with a plurality of blades along circumferentially in accordance with regulations angle [alpha] be obliquely installed on above-mentioned plectane 2 sides, adapt to the angle of attack of air-flow when entering fan 4, can effectively enlarge air intake and air-out scope, when adopting arc to roll over vaporizer more, can improve when equal rotating speed and pass in and out air quantity, wind pushing performance further improves; Perhaps under the situation of equal air quantity, reduce rotating speed, thus noise-decreasing.
Present embodiment is connected and fixed multistage multiblade impeller 3 vertically, so, can change the entire length of cross flow fan 4 easily by its hop count of suitable adjustment, and pass through suitably to select the shape of the also easier change blade of section staggered angle, thereby manufacture cost is reduced.
In addition, because multiblade impeller 3 is that blade 1 and plectane 2 are formed one, thereby not needing to resemble in the past to when making impeller, blade being reversed, so there is not residue stress, thereby the intensity of blade and plectane is improved, stable accuracy and the raising of the setting angle α of 2 of blade 1 and plectanes can be made simultaneously, thereby the conformity of wind pushing performance can be improved; And because the fan that segmentation forms, every section blade 1 is shorter, so can choose bigger blade twist angle; By blade 1 self is vertically formed curve-likes such as arc along it, the torsion angle of blade is further increased, can reach the purpose of noise-decreasing significantly.
Owing to being stacked gradually vertically, multistage multiblade impeller 3 is fixed into integrally formed cross flow fan, so manufacturing is simple, cost is low, and by suitably selecting the stacked number of multiblade impeller, can change the axial length of fan easily, and, because it is shorter than the axial width of other multiblade impeller 3 to be provided with the axial width of one section multiblade impeller 3 ' of hub portion 7, and the intensity of this section is improved, can bear that motor shaft drives the power that applies when fan rotates and indeformable.
Since with each blade 1 in the middle of its cross section to both sides of the edge attenuation gradually, and two end part are level and smooth arc, can effectively reduce air turnover resistance, make turnover wind smooth more.When air flow stream is crossed blade, be not easy to form boundary layer at blade surface, reduce the generation in whirlpool, thereby reduce rotational noise.
Claims (7)
1, a kind of transverse flow fan of indoor unit of air conditioner, by the identical multiblade impeller of multistage diameter each other around the axle predetermined angular that staggers relatively, stack gradually vertically and fix and both ends of the surface are sealed to form, an outstanding rotating shaft in the middle of fan one end face, the hub portion that engages with the fan electromotor running shaft is arranged in the middle of the other end, it is characterized in that: the axial width that is provided with one section impeller of hub portion be other section impeller axial width 1/3 to 2/3.
2, transverse flow fan of indoor unit of air conditioner according to claim 1, it is characterized in that: described multiblade impeller, be that a plurality of blades are formed along circumferentially being fixed on the plectane, the installation interval of above-mentioned blade is unequal interval, and the angle of adjacent two blades and impeller middle spindle is between 9 °～11 °.
3, transverse flow fan of indoor unit of air conditioner according to claim 2 is characterized in that: the blade on the described multiblade impeller has certain inclination angle with described plectane and tilts with respect to the fan sense of rotation.
4, transverse flow fan of indoor unit of air conditioner according to claim 3 is characterized in that: described inclination angle is between 10 °～25 °.
5, transverse flow fan of indoor unit of air conditioner according to claim 2 is characterized in that: described blade and impeller shaft are non-parallel.
6, require the described transverse flow fan of indoor unit of air conditioner of arbitrary claim among the 1-5 according to aforesaid right, it is characterized in that: the cross section of described blade is an arc, and from the middle of its cross section to both sides attenuation gradually.
7, require the described transverse flow fan of indoor unit of air conditioner of arbitrary claim among the 1-5 according to aforesaid right, it is characterized in that: described blade is vertically curved along it.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520017205 CN2837569Y (en) | 2005-04-25 | 2005-04-25 | Cross flow fan for air conditioner indoor unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520017205 CN2837569Y (en) | 2005-04-25 | 2005-04-25 | Cross flow fan for air conditioner indoor unit |
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| CN2837569Y true CN2837569Y (en) | 2006-11-15 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 200520017205 Expired - Fee Related CN2837569Y (en) | 2005-04-25 | 2005-04-25 | Cross flow fan for air conditioner indoor unit |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104101028A (en) * | 2014-07-04 | 2014-10-15 | 宁波奥克斯空调有限公司 | Indoor air conditioner air flue and indoor air conditioner |
| CN104870904A (en) * | 2012-12-21 | 2015-08-26 | 松下知识产权经营株式会社 | Air conditioner |
| CN104981612A (en) * | 2013-02-12 | 2015-10-14 | 大金工业株式会社 | Air conditioner |
| CN106015087A (en) * | 2016-07-21 | 2016-10-12 | 美的集团武汉制冷设备有限公司 | Cross-flow wind wheel, cross-flow fan and air conditioner indoor unit |
| CN107380928A (en) * | 2017-08-15 | 2017-11-24 | 江苏万力机械股份有限公司 | A kind of Impeller powder feeder |
| CN107588041A (en) * | 2017-09-07 | 2018-01-16 | 珠海格力电器股份有限公司 | Tubular wine wheel and air conditioner |
| CN110500316A (en) * | 2018-05-16 | 2019-11-26 | 日清纺精密机器株式会社 | Fan impeller |
| CN111148945A (en) * | 2017-09-27 | 2020-05-12 | 大金工业株式会社 | Air conditioner |
-
2005
- 2005-04-25 CN CN 200520017205 patent/CN2837569Y/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104870904A (en) * | 2012-12-21 | 2015-08-26 | 松下知识产权经营株式会社 | Air conditioner |
| CN104870904B (en) * | 2012-12-21 | 2017-06-27 | 松下知识产权经营株式会社 | Air conditioner |
| CN104981612A (en) * | 2013-02-12 | 2015-10-14 | 大金工业株式会社 | Air conditioner |
| CN104981612B (en) * | 2013-02-12 | 2017-02-22 | 大金工业株式会社 | Air conditioner |
| CN104101028A (en) * | 2014-07-04 | 2014-10-15 | 宁波奥克斯空调有限公司 | Indoor air conditioner air flue and indoor air conditioner |
| CN106015087A (en) * | 2016-07-21 | 2016-10-12 | 美的集团武汉制冷设备有限公司 | Cross-flow wind wheel, cross-flow fan and air conditioner indoor unit |
| CN107380928A (en) * | 2017-08-15 | 2017-11-24 | 江苏万力机械股份有限公司 | A kind of Impeller powder feeder |
| CN107588041A (en) * | 2017-09-07 | 2018-01-16 | 珠海格力电器股份有限公司 | Tubular wine wheel and air conditioner |
| CN111148945A (en) * | 2017-09-27 | 2020-05-12 | 大金工业株式会社 | Air conditioner |
| CN110500316A (en) * | 2018-05-16 | 2019-11-26 | 日清纺精密机器株式会社 | Fan impeller |
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| C14 | Grant of patent or utility model | ||
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Granted publication date: 20061115 |