CN101737339B - Air conditioner - Google Patents
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- CN101737339B CN101737339B CN2009102540696A CN200910254069A CN101737339B CN 101737339 B CN101737339 B CN 101737339B CN 2009102540696 A CN2009102540696 A CN 2009102540696A CN 200910254069 A CN200910254069 A CN 200910254069A CN 101737339 B CN101737339 B CN 101737339B
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Abstract
The object of the present invention is that the present invention provides an air-conditioner, where an indoor unit for conditioning the indoor air is provided with a crosscurrent fan for generating a crosscurrent with reduced noises, while conserving energy and being operated in a quiet manner. The solution of the present invention is that a circular portion (13) is provided with a crosscurrent fan (1) having blades (12). The curve line (17) indicating the center along the thickness of each blade includes two arcs having opposing curvatures. The acting faces (18) of the blades (12) are consistent with the rotational axis. The width of the flow passages between the blades varies within the range of 60% to 80% of the ratio between the inner diameter and the outer diameter.
Description
The application is for dividing an application, and the applying date of original application is on June 9th, 2003, and application number is 03137505.7, and denomination of invention is an air conditioner.
Technical field
The present invention relates to be installed in the crossflow fan in the indoor set of air conditioner.
Background technique
In recent years; Air conditioner is being pursued economize on electricity and quiet always; A kind of method as economize on electricity is to increase the air quantity be arranged on the air exhauster in the indoor set, this blower fan be used for flow through the indoor air that refrigerant in the heat exchanger carried out heat exchange and discharge the indoor set outside.As the main flow blower fan of indoor set, be to adopt crossflow fan (crossflow fan) under the situation of wall air conditioner.As everyone knows, when increasing the air quantity of indoor set blower fan, just can improve the heat exchange performance of indoor heat exchanger.Increase the air quantity (electric power that is consumed is constant) of blower fan if can not increase the rotating speed of blower fan, the result just can improve the whole performance of air conditioner, can produce the air-conditioning effect identical with economize on electricity.
As the method for the air quantity of the above-mentioned blower fan of seeking to increase indoor set, admissible method has, and foregoing raising is as the rotating speed of the gas fan crossflow fan of indoor set, and the external diameter that increases blower fan.
; Because the ratio that the turbulent sound during indoor set work (being distributed in the interior sound of frequency range of high-frequency region) increases is 7～8 times of the scaling up of crossflow fan rotating speed; So if a kind of method makes air quantity increase by 30% before using, turbulent volume will increase 9dB.On the other hand, because the ratio that turbulent sound increases is 4-5 times of the scaling up of blower fan external diameter, so if use a kind of method in back to make air quantity increase by 30%, turbulent volume will increase 5dB.
Consequently, in order under the condition that does not increase noise (turbulent sound), to increase air quantity, it is generally acknowledged that a kind of method in back is more appropriate., the size of indoor set is limited, and therefore, the size that is installed in the inner crossflow fan of indoor set also has restriction, and it is difficult increasing the existing outside dimension of blower fan.In addition; When increasing to its limit size to the crossflow fan external diameter, also have such problem, promptly; Owing to the space between crossflow fan and the leading edge diminishes the especially significantly noise that produces (by the quantity Z of blade and rotational speed N (the frequency ZN (Hz) that/sec) product produces; Perhaps its high secondary frequencies), and because the distance of indoor heat exchanger and crossflow fan is too near, (slow down by the downstream that are distributed in pipe of the airspeed through heat exchanger near velocity wake region for the blade of crossflow fan; The zone that its local velocity's changes in distribution is very big), the sound that through this zone the time, produced of blade.
Therefore, in known spy opens flat 9-100795 communique and Te Kai 2001-50189 communique, disclose and suppressed the blade sound that produces owing to above-mentioned crossflow fan and interference thereof, the existing technology of reduction noise.The effect of these two pieces of patent documentations is different; But principle is the same, that is, because for increasing air quantity; Make crossflow fan increase and and the gap between the leading edge, and these two pieces of patent documentations all have the effect of the noise (blade sound) that suppresses to cause because this gap reduces.
Promptly; On principle; All be when changing crossflow fan, the structure of excircle front end of the blade of crossflow fan tilted, with respect to leading edge owing to this inclination with respect to the axial blade external diameter of rotation; Make the front end of blade excircle when the leading edge (perhaps velocity wake region), time of occurrence poor (phase difference).
Therefore, utilize the position relation between blade excircle front end and the leading edge, the periodicity sound that is produced is spread out in time, thereby can suppress the blade sound, reach the gap that reduces leading edge, and increase the purpose of air quantity.
Other existing technology, for example the spy opens flat 6-129387 communique, spy to open flat 6-173886 communique also is technique known.Below, the content of in these documents, putting down in writing is described.In order to prevent the blade sound of crossflow fan, its measure is to make the interval of mounting blades pitch on the circumferencial direction unequal mutually, and the peak value by means of making each blade at the difference inhibition noise of the phase place of circumferencial direction reduces noise on the whole.
In the low noise pitch air quantity technology that above-mentioned patent documentation is put down in writing, though different on the method, main points all are to disperse the cycle of blade sound equally, noise are reduced and the air quantity increase, thereby improve the performance of air conditioner.
, under reality, seek to make air conditioner further economize on electricity and quiet (low noise pitch air quantityization) always, therefore, needing a kind of efficient higher, the crossflow fan that noise is littler.In addition, in the sound of crossflow fan, have the very wide turbulent sound of frequency band that produces because of fluid, even if more than said existing technology can suppress periodic blade sound, but can not reduce turbulent sound.Therefore, in fact, only using the method that can find in the existing technology, is to be difficult to realize further reduce noise, the target of saving electric power.
Summary of the invention
The objective of the invention is, a kind of turbulent sound of causing owing to fluid of can reducing is provided, noise is reduced; Can realize the indoor air conditioner that economizes on electricity again by means of big air quantity.
For achieving the above object; Scheme one of the present invention is in indoor set, to be equipped with in the air conditioner of crossflow fan, and wherein, the line of the blade section mid-depth of above-mentioned crossflow fan comprises two circular arcs; The bending direction of these two circular arcs is opposite; And constitute, there is the centre of curvature point in the above-mentioned circular arc of internal diameter one side in the sense of rotation side, and there is the centre of curvature point in the above-mentioned circular arc of external diameter one side in an opposite side with sense of rotation.
In addition, scheme two of the present invention is on the basis of the air conditioner of scheme one, and making the width between the blade of above-mentioned crossflow fan is 60～80% in external diameter one side with respect to the ratio of internal diameter one side.
In addition, scheme three of the present invention is on the basis of the air conditioner of scheme one or scheme two, constitutes, and the external diameter of the blade of above-mentioned crossflow fan is changed with respect to the running shaft direction.
Have, scheme four of the present invention is on the basis of the air conditioner of arbitrary scheme of scheme one～scheme three again, makes the pressure side of the blade that constitutes above-mentioned crossflow fan consistent with respect to the running shaft direction.
According to the present invention, be equipped with in the air conditioner of crossflow fan at gas fan as indoor set, its structure is that the width between the blade of crossflow fan is 60～80% in external diameter one side with respect to the ratio of internal diameter one side.Crossflow fan is the blower fan of the acceleration flabellum type that increases gradually to exhaust one side of the speed of fluid basically, and the degree that fluid quickens is confirmed by width of flow path between the above-mentioned blade, so it can produce influence greatly to the performance of crossflow fan.
According to the present invention, be equipped with in the air conditioner of crossflow fan at gas fan as indoor set, its structure is for making that the pressure side that constitutes fan blade is consistent along the running shaft direction.Through making pressure side consistent, the velocity distribution on the running shaft direction just can be not disorderly, reaches balanced, thereby improve the performance of crossflow fan.
According to the present invention,, on the basis of such scheme one or scheme two, add of the direction variation of the external diameter of fan blade along spin axis in order to improve the effect that reduces noise.Because the blade external diameter is changed, make the interference of blade that the time difference (phase difference) arranged, just can reduce noise, seek low noiseization.
Description of drawings
Fig. 1 (a) is an overall diagram of seeing the indoor set of air conditioner in expression one embodiment of the present of invention from the front;
Fig. 1 (b) is an overall diagram of seeing the indoor set of air conditioner in expression the foregoing description from the side;
Fig. 2 (c) is the global shape of crossflow fan outward appearance in the foregoing description;
Fig. 2 (d) is a sectional view of seeing crossflow fan in the foregoing description from the running shaft direction;
Fig. 3 is the enlarged view of the blade section of the foregoing description;
Fig. 4 (e) is the enlarged view of the blade section of expression the foregoing description;
Fig. 4 (f) is the sectional view of fan part in expression the foregoing description;
Fig. 5 (g) is the enlarged view of the blade section of expression the foregoing description;
Fig. 5 (h) is the enlarged view of fan part section in expression the foregoing description;
Fig. 6 is the efficiency chart of expression the foregoing description effect;
Fig. 7 is the efficiency chart of expression the foregoing description effect;
Fig. 8 is the performance plot of expression the foregoing description performance.
Embodiment
Below, with reference to Fig. 1～Fig. 8 embodiments of the invention are described.
Fig. 1 is the overall diagram of expression indoor machine of air conditioner, and wherein (a) is the overall diagram of seeing from the front, (b) is the sectional view of seeing from the side of indoor set.Indoor set integral body all uses decorative sheet 2 to cover, and its formation comprises successively: filter 5, heat exchanger 6, crossflow fan 1 are provided with housing 7 below crossflow fan 1.
The outward appearance of crossflow fan 1 is as shown in Figure 2, and (c) wherein representes whole shape, (d) representes the section of seeing from the running shaft direction.There is the plectane 13 of blade 12 to become a fan part in circumferential directions,, promptly constitutes a crossflow fan 1 along several fan parts of running shaft direction combination.In addition, installed at the two ends of blower fan end face plectane 14 with have a wheel hub 16 wheel hub end face plectane 15 arranged, end face plectane 14 is arranged in bearing one side, has the end face plectane 15 of wheel hub to be arranged in motor reel one side, is rotated.
Under indoor set real-world operation state, crossflow fan 1 has motor 10 to drive, on Fig. 1 (b), turn right, the front grid 3 on being arranged on decorative sheet 2 with above grid 4 suck air, from the relief opening exhausting air of indoor set bottom.At the inner air-flow of indoor set, after filter 5, arrive heat exchanger 6, in the process that flows through this heat exchanger 6, be cooled, perhaps be heated.Air communication through after the heat exchange is crossed crossflow fan 1, flows to housing 7 one sides, near relief opening, by vertical wind direction board 8 and horizontal wind direction board 9 its wind directions of control, flows out indoor set then.
Fig. 3, Fig. 4 and Fig. 5 have represented the characteristics of the crossflow fan of present embodiment, are the section amplification figures of the crossflow fan 1 seen from the running shaft direction.Theing contents are as follows of its characteristics is said.
Among Fig. 3, the deflection curve 17 of mid-depth of expression blade 12 is to be that two circular arcs of p1 and p2 are formed by radius of curvature, and the bending direction of each bar circular arc is opposite mutually.In addition, form the distribution of above-mentioned blade 12 thickness, form from the midfield of wing chord length towards these two ends of front end of the front end of blade excircle and blade inner circumference the wing shape of attenuate gradually.
At this moment, if having in mind from the character of fluid, normally flow velocity is fast more, and turbulent sound is big more, in addition, also will increase the power of input.About turbulent sound, shown in following formula (1), it is relevant with flow velocity (representation speed) V (m/s) through crossflow fan blade front end.
[formula 1]
SPL ∝ log (α V) ... (formula 1)
In the formula: α is a conversion conefficient, is with the kind of the fluid machinery definite value different and different with state.Therefore, level of noise SPL will increase along with the value of representation speed V and change.The crossflow fan that is used for indoor air conditioner, if representation speed V reduces by 10%, then level of noise SPL can reduce 3dB.And about the power of input, shown in following formula (2), it is relevant with exhaust flow velocity (representation speed) V through the crossflow fan blade.
[formula 2]
W is the input power (w/m that provides for the per unit volume fluid
3), p and ρ are illustrated in pressure (Pa) and the density (kg/m in this fluid scope
3).Under the state that indoor air conditioner turns round, all be similar to atmospheric pressure in atmosphere, can think its almost not influence in the pressure p of upstream and downstream.In addition, aspect the wind pushing performance of the crossflow fan of indoor air conditioner, owing to can regard fluid as incompressible, so its density p is fixed, input power being produced the factor of big influence, is the representation speed of the gas of discharging from crossflow fan.Therefore, under the certain situation of flow,, make flow velocity V reduce, just can reduce the power w of input if discharge fluid with very big zone.Under the situation that input power w has confirmed, then, just can flow out more flow by means of discharging fluid with very big zone.
Can know from above analysis; Make the center line 17 of the blade section shape of crossflow fan 1 by two reverse circular arcs and to constitute; With regard to enlarging near the outflow zone of housing 7 one lateral lobe sheet excircles that becomes the Peak Flow Rate zone, make the fluid broadness and discharge lentamente.Below, explain and difference with a formed blade of circular arc (for example, form) by the ρ among Fig. 32.During to mobile analysis of the crossflow fan that adopts the blade that circular arc forms, to obtain between the most external circumference upper blade distribution of (with the front end of the blade in adjacent sense of rotation the place ahead front end) flow velocity earlier as the blade of calculation object.Just can understand thus, the distribution of flow velocity is different, as near special fast of the flow velocity the blade front end of calculation object.As stated, flow velocity is directly connected to noise, and, because it is be high flow rate on a part only, little for the influence of the size of whole air quantity.Therefore, in the present embodiment, can judge, make the semi-circle and the sense of rotation of front end of blade cylindrical side Monday opposite, just can suppress the high flow rate of originally giving prominence to.
As a result, reached the low noise efficient rate,, improved the performance of air conditioner to save the effect of electric power increase air quantity.About the effect of this wind pushing performance, statement as follows.Fig. 6 has represented crossflow fan 1 among Fig. 2 (d) when turning clockwise (to right rotation), the relation of radius of curvature ρ 1 and efficiency eta.Be the opposite direction of radius of curvature ρ 2 during as postive direction on the abscissa, the inverse of radius of curvature ρ 1 is that efficient is than η/η 0 on the y coordinate.(efficient of the existing crossflow fan of η 0 expression will be explained in Fig. 8 for existing blower fan.) efficiency eta that is used as the index of assess performance is the fan efficiency of crossflow fan, available formula (3) is represented.
[formula 3]
In the formula: P
tBe whole pressure (Pa); Q is flow (m
3/ s); T is the moment of torsion (Nm) of crossflow fan; ω is the angular velocity (rad/s) of crossflow fan.Can also use formula (4) with its expansion about whole pressure.
[formula 4]
P
t=P
s+ P
d,
(formula 4)
All pressure is used static pressure P
sWith dynamic pressure P
dSum is represented, dynamic pressure P
dBe to confirm by density p and representation speed V.From above the separate equations, can put out the formula (5) of expression efficiency eta in order.
[formula 5]
Providing certain flow Q, under the condition of certain rotating speed (certain angular velocity omega), efficiency eta is decided by: from the static pressure changes delta P that swims over to downstream of crossflow fan
s, the changes delta V of representation speed
2, the torque T of crossflow fan.In addition, in the performance evaluation of Fig. 6, the flow rotating speed is fixed; And because no matter blade shape is any situation, pressure side is all identical; Maximum one-tenth-value thickness 1/10 is fixed, and blade external diameter minimum diameter is all fixed equally, so provided the condition of the ratio=fixed number in inside and outside footpath.In addition, the state that the blade excircle changes along the running shaft direction, the straight line state of changing for shown in Fig. 4 (f) has provided D
1＜D
2Condition, and, under all conditions, from D
1To D
2Variance ratio all equate.Like this, just can estimate with the radius of curvature according to Fig. 6 is the wind pushing performance of parameter, can judge that from figure best efficiency point is in the opposite mutually negative zone of the radius of curvature of two circular arcs of the center line 17 that forms the blade section shape.That is, be under the shape of perk at the excircle front end of blade 12, have the effect that improves crossflow fan 1 performance, this effect is to link together with the performance that improves air conditioner.
In Fig. 4 (e), the section of two blades 12 that drawn, section separately are the sections of the axial position arbitrarily of rotation, and its location tables is shown in from radial direction and sees the sectional view (f) of fan part.Thicker bigger section A representes a side of the plectane 3 of a fan part, and the section of thin less section A ' expression side opposite with it.Can know that according to this sectional view pressure side 18 is facing to roughly the same on the direction of running shaft.In addition, in Fig. 4 (f), external diameter is from diameter D along the axial variation of rotation
1Mode with straight line changes to D
2, this D
1≠ D
2Relation be that beginning the time was set forth in the prior art, be the effect that the blade sound is reduced in order to obtain.Generally speaking, the so-called pressure side on fan blade is direct to the zone of fluid transferring power, and wind pushing performance is had very big influence.If this pressure side is in askew, the equilibrium of fluid will degenerate, and can cause very uneven flowing, and consequently, reduces problems such as noise increase just can produce performance.This problem is that the character by above-mentioned fluid causes, can fundamentally solve with identical principle.Existing that its description of contents is following.Formula (1), (2) listed from the front can know that the influence that level of noise and input power receive representation speed V is very big.Therefore, noise will increase along with the increase of flow velocity V, and input power also will increase.Here, the fluid that should pay special attention to flow through between the blade is rotating axial velocity distribution.Be under the situation of askew facing to the running shaft direction at pressure side, this shape just becomes the reason that alters a great deal along the axial velocity distribution of rotation.On the contrary, when pressure side was in full accord along the axial shape of rotation, the distribution of speed was roughly even, and fluid will flow out with identical flow velocity.Below, flow one timing at this moment is described, relatively the velocity distribution of this two states is to Effect on Performance.The blade that pressure side is crooked; For the mean velocity Vave that comes out according to flow rate calculation, exist local velocity V fast area and zone at a slow speed, to the power of each tiny area input of this velocity distribution; Power to the fast area input is big, and little to the power of zone input at a slow speed.Therefore, shown in formula (2), because the power of input is by square increase of flow velocity; In this velocity distribution; The input power that in high-speed region, increases is more than the input power that low-speed region reduces, the result, and the input power that total input power compares when velocity distribution is even on the whole is big.That is, the blade that pressure side is identical with respect to the mean velocity Vave that is come out by flow rate calculation, roughly is same flow velocity (Vave) on all pressure sides, can be described as the minimum state of the input power relevant with velocity distribution.In addition, consider, shown in formula (1) from the noise aspect; Because there is the fast zone of flow velocity V in the crooked blade of pressure side; Noise has increased, and the consistent blade of pressure side, owing to there is the fast zone of flow velocity V; Noise has just increased, so the noise that velocity distribution produced on the blade of pressure side unanimity is minimum.From the viewpoint of velocity distribution, at the consistent blade of running shaft direction upward pressure face, its velocity distribution is the same, so all be optimal state aspect the input power noise.Therefore, as stated, make pressure side 18 in full accord on the running shaft direction, just can improve the equilibrium of fluid, improve wind pushing performance, realize quiet.
Width of flow path by means of the regulation blade also can improve performance, and the content of this respect can be explained with Fig. 5.The width B of runner between the blade shown in Fig. 5 (g) is Extreme breadth Bmax in internal diameter blade one side, is minimum width Bmin in blade external diameter one side.Extreme breadth Bmax can use the internal diameter blade r shown in Fig. 5 (h)
InWith the front end of internal diameter blade with the spin axis be the determined blade of initial point at interval θ represent: Bmax=r
In* sin θ, minimum width Bmin then is defined as the minimum width of blade outside diameter.In this state, the result that the ratio Bmin/Bmax that only changes with width of flow path estimates fan performance as parameter is shown among Fig. 7.In addition, be fixed up the maximum ga(u)ge of blade, and also be fixed up internal diameter blade, external diameter, under the condition of the ratio=fixed number in inside and outside footpath, the shape (identical R) that the various conditions at internal diameter blade, external diameter two ends are all equated compares.Efficiency eta is the fan efficiency η of crossflow fan of expression wind pushing performance, is identical with above-mentioned definitions of efficiency, through from the upper reaches of crossflow fan until the variation in pressure and the flow in downstream, and confirmed with the moment of torsion and the rotating speed of blower fan.Here, the relation of the ratio Bmin/Bmax that efficiency eta and width of flow path is changed is explained.Near the relief opening of crossflow fan,,, just big more through the liquid speed at width of flow path Bmin place so Bmin/Bmax is more little owing to flow Q fixes.
, according to the character of fluid, the speed of fluid is big more, and the loss in each fluid mass is also big more, so in the downstream side of crossflow fan, flow velocity drops to the corresponding velocity distribution with flow Q.Therefore, apply torque T, make the excessive fluid of speedup, static pressure Ps is risen, and just increased the loss of energy through crossflow fan.Consequently, the ratio Bmin/Bmax that changes for width of flow path is in the zone 55% below, and width of flow path Bmin is narrow, will make the efficient reduction.In addition, in the big zone of Bmin/Bmax, the situation little with this ratio is opposite, and the liquid speed through width of flow path Bmin will reduce.Therefore, the relief opening at crossflow fan will make fluid not flow out with excessive speed.In this state, even crossflow fan is increased moment of torsion, fluid will be through crossflow fan the time, and static pressure Ps and dynamic pressure Pd can not rise.Consequently, the ratio Bmin/Bmax that width of flow path changes is in the zone more than 85%, and display efficiency is than η/η
MaxValue reduce decrease in efficiency.In addition, the ratio Bmin/Bmax that width of flow path changes is in 60～80% zone, because the equilibrium of static pressure Ps, dynamic pressure Pd, torque T is good, so efficient is than η/η
MaxValue just very high.Can know from above analysis, the width of flow path between the blade of blower fan, outside diameter is the highest in 60～80% scope internal efficiency with respect to internal side diameter, can improve the performance of blower fan.When the crossflow fan that makes the indoor set installation have said structure turns round, consume same electric power, air quantity is increased, concerning the raising of air conditioner overall performance.
More than, the crossflow fan that forms equal intervals has been described between blade, but, also can consider to use the crossflow fan of unequal interval.To be explained below.At present, at the inner crossflow fan of installing of the indoor set of air conditioner, much all be blade in a circumferential direction with the separation that do not wait.That is, Bmin, Bmax between each blade of crossflow fan are unequal, so the width of each runner is also unequal.This is because be applied in the above-mentioned existing technology, interferes during owing to the crossflow fan running, and it has the effect that the blade sound is reduced owing to staggering of blade phase place, so be widely used in the indoor set of present air conditioner.Therefore, for the unequal crossflow fan in blade interval, the value of the ratio Bmin/Bmax that above-mentioned width of flow path changes on each blade interval has nothing in common with each other.Like this, for the unequal crossflow fan in above-mentioned blade interval, on same meaning, used the mean value of the ratio Bmin/Bmax of definite width of flow path variation.When on the circumferencial direction of crossflow fan parts with the separation that do not wait during N piece blade, become Bmax=r
In* sin (2 π/N), Bmin=(∑ B ' min)/N.Bmax calculates according to the average angle of the N piece blade quantity on circumference of crossflow fan; Bmin is when being B ' min with the minimum flow path width between each blade of crossflow fan, the mean value that at interval summation (∑ B ' min) between whole blades is tried to achieve divided by blade quantity N.Like this, just can on same meaning, confirm the ratio Bmin/Bmax that width of flow path changes in the crossflow fan of unequal interval.
The adjusting of above-mentioned width of flow path can be accomplished through the thickness of adjusting vane basically.If between the blade is uniformly-spaced at interval; And the ratio Bmin/Bmax that original width of flow path changes also is 60～80%; So long as the thickness of some blade (more than a slice) is different from the thickness of other blades passable (thickness of not all blade all identical just can); If the interval between the blade is unequal, and original mean value also can be that the thickness of all blades is all inequality also within above-mentioned numerical value.
Fig. 8 representes that the performance of the blower fan of existing blower fan and present embodiment compares.The ratio Q/Q of expression air quantity on the abscissa
0, be respectively whole pressure ratio PT/PT on the y coordinate
0, input power compares Lm/Lm
o, level of noise SL-SL
0Wherein, Q
0, PT
0, Lm
0, SL
0Expression prior standard value.Condition relatively is that the shape of existing blower fan is identical with the inside and outside footpath of present embodiment blower fan under same rotating speed, and therefore, the ratio in inside and outside footpath also equates.In addition, with respect to the running shaft direction, the external diameter of blade changes, and as maximum outside diameter, it is that mode with straight line changes with near the external diameter of the fan part neutral position of axial direction.More than, be in the prior art, also be employed in the present embodiment, have the measure that suppresses blade audio fruit.But in addition, 60～80%, two circular arcs of variation of width of flow path are reverse between the blade, make pressure side be consistent shape, are not measures of the prior art just.Thus, just as shown in Figure 8, when comparing with various air quantity ratios, all the ratio of pressure approximately+20%; The ratio of input power about-10%; Level of noise approximately-1dB, visible, present embodiment is to the reduction of the improvement of performance and noise all clearly.
The present invention has reduced its noise owing to improved the efficient of crossflow fan, and a kind of increase air quantity is provided, and reduces noise, conservation of power and quiet air conditioner.
Claims (4)
1. air conditioner; In the indoor set of this air conditioner, crossflow fan is housed, it is characterized in that, the line of the blade section mid-depth of above-mentioned crossflow fan comprises two circular arcs; The bending direction of these two circular arcs is opposite; And constitute, there is the centre of curvature point in the above-mentioned circular arc of internal diameter one side in the sense of rotation side, and there is the centre of curvature point in the above-mentioned circular arc of external diameter one side in an opposite side with sense of rotation.
2. air conditioner as claimed in claim 1 is characterized in that, making the width between the blade of above-mentioned crossflow fan is 60～80% in external diameter one side with respect to the ratio of internal diameter one side.
3. according to claim 1 or claim 2 air conditioner is characterized in that, constitutes, and the external diameter of the blade of above-mentioned crossflow fan is changed with respect to the running shaft direction.
4. like each described air conditioner of claim 1～3, it is characterized in that, make the pressure side of the blade that constitutes above-mentioned crossflow fan consistent with respect to the running shaft direction.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002267540A JP4109936B2 (en) | 2002-09-13 | 2002-09-13 | Air conditioner |
| JP2002-267540 | 2002-09-13 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN03137505A Division CN100587274C (en) | 2002-09-13 | 2003-06-09 | Air conditioning machinery |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101737339A CN101737339A (en) | 2010-06-16 |
| CN101737339B true CN101737339B (en) | 2012-07-18 |
Family
ID=32089109
Family Applications (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN03137505A Expired - Fee Related CN100587274C (en) | 2002-09-13 | 2003-06-09 | Air conditioning machinery |
| CNA2007101046750A Pending CN101070982A (en) | 2002-09-13 | 2003-06-09 | Air conditioner |
| CN2009102540696A Expired - Fee Related CN101737339B (en) | 2002-09-13 | 2003-06-09 | Air conditioner |
Family Applications Before (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN03137505A Expired - Fee Related CN100587274C (en) | 2002-09-13 | 2003-06-09 | Air conditioning machinery |
| CNA2007101046750A Pending CN101070982A (en) | 2002-09-13 | 2003-06-09 | Air conditioner |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP4109936B2 (en) |
| CN (3) | CN100587274C (en) |
| MY (1) | MY139963A (en) |
| TW (1) | TWI227763B (en) |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4583095B2 (en) * | 2004-07-27 | 2010-11-17 | 東芝キヤリア株式会社 | Cross flow fan |
| JP4882533B2 (en) * | 2006-06-14 | 2012-02-22 | パナソニック株式会社 | Air conditioner |
| KR101436628B1 (en) * | 2007-10-23 | 2014-09-02 | 엘지전자 주식회사 | Cross flow fan amd air conditioner |
| CN101769266B (en) * | 2010-03-23 | 2011-08-31 | 上海交通大学 | Centrifugal fan blade |
| JP5187353B2 (en) * | 2010-06-22 | 2013-04-24 | パナソニック株式会社 | Cross-flow fan and air conditioner equipped with the same |
| JP5269036B2 (en) * | 2010-11-08 | 2013-08-21 | 三菱電機株式会社 | Cross-flow fan and air conditioner equipped with the same |
| CN102116314B (en) * | 2011-04-05 | 2012-11-07 | 湖南科力尔电机有限公司 | Cross-flow fan of composite wire blade impeller |
| CN103089661B (en) * | 2011-11-04 | 2015-04-01 | 上海交通大学 | Cross flow fan |
| JP6029355B2 (en) * | 2012-07-02 | 2016-11-24 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド | Air conditioner indoor unit |
| WO2014097625A1 (en) * | 2012-12-21 | 2014-06-26 | パナソニック株式会社 | Air conditioner |
| CN109209990A (en) * | 2018-10-26 | 2019-01-15 | 珠海格力电器股份有限公司 | Through-flow fan blade, cross flow fan, air conditioner |
| JP2020106024A (en) * | 2018-12-27 | 2020-07-09 | 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． | Blower, het exchange unit and air cleaning unit |
| KR20220081615A (en) * | 2020-12-09 | 2022-06-16 | 엘지전자 주식회사 | Air-conditioner |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1126181A2 (en) * | 2000-02-16 | 2001-08-22 | Lucent Technologies Inc. | Miniature pump |
| CN1365433A (en) * | 2000-03-21 | 2002-08-21 | 西门子公司 | Feed pump |
| JP4339199B2 (en) * | 2004-07-22 | 2009-10-07 | 北陸電力株式会社 | Water intake control method and water intake control system for flow-type hydroelectric power plant |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5962293U (en) * | 1982-10-18 | 1984-04-24 | 株式会社東芝 | lateral flow fan |
| JPS59192898A (en) * | 1983-04-15 | 1984-11-01 | Hitachi Zosen Corp | Centrifugal impeller |
| JPH01193099A (en) * | 1988-01-27 | 1989-08-03 | Diesel Kiki Co Ltd | Impeller of centrifugal flower |
| JPH0740718Y2 (en) * | 1988-04-11 | 1995-09-20 | 松下電器産業株式会社 | Cross flow fan |
| JP2667748B2 (en) * | 1991-05-15 | 1997-10-27 | 株式会社日立製作所 | Multi-wing impeller |
| JP2770677B2 (en) * | 1992-10-14 | 1998-07-02 | ダイキン工業株式会社 | Cross flow fan |
| JP2758800B2 (en) * | 1992-12-09 | 1998-05-28 | シャープ株式会社 | Cross flow fan |
| JP3918207B2 (en) * | 1995-08-02 | 2007-05-23 | 株式会社日立製作所 | Air conditioner |
| JPH10299694A (en) * | 1997-04-22 | 1998-11-10 | Toshiba Corp | Blower |
| JP2000240590A (en) * | 1999-02-23 | 2000-09-05 | Hitachi Ltd | Multiblade forward fan |
| JP3777891B2 (en) * | 1999-08-03 | 2006-05-24 | 株式会社日立製作所 | Air conditioner |
| JP3757802B2 (en) * | 2001-02-09 | 2006-03-22 | 三菱電機株式会社 | Turbofan, and blower and air conditioner using turbofan |
-
2002
- 2002-09-13 JP JP2002267540A patent/JP4109936B2/en not_active Expired - Fee Related
-
2003
- 2003-04-07 TW TW92107900A patent/TWI227763B/en not_active IP Right Cessation
- 2003-06-09 CN CN03137505A patent/CN100587274C/en not_active Expired - Fee Related
- 2003-06-09 CN CNA2007101046750A patent/CN101070982A/en active Pending
- 2003-06-09 CN CN2009102540696A patent/CN101737339B/en not_active Expired - Fee Related
- 2003-06-30 MY MYPI20032449 patent/MY139963A/en unknown
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1126181A2 (en) * | 2000-02-16 | 2001-08-22 | Lucent Technologies Inc. | Miniature pump |
| CN1365433A (en) * | 2000-03-21 | 2002-08-21 | 西门子公司 | Feed pump |
| JP4339199B2 (en) * | 2004-07-22 | 2009-10-07 | 北陸電力株式会社 | Water intake control method and water intake control system for flow-type hydroelectric power plant |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4109936B2 (en) | 2008-07-02 |
| CN101737339A (en) | 2010-06-16 |
| TWI227763B (en) | 2005-02-11 |
| CN100587274C (en) | 2010-02-03 |
| CN101070982A (en) | 2007-11-14 |
| CN1482367A (en) | 2004-03-17 |
| MY139963A (en) | 2009-11-30 |
| JP2004100663A (en) | 2004-04-02 |
| TW200404126A (en) | 2004-03-16 |
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