EP1512918B1

EP1512918B1 - Axial flow fan

Info

Publication number: EP1512918B1
Application number: EP04077405A
Authority: EP
Inventors: Won Chin Sim; Kee Chung Moon
Original assignee: LG Electronics Inc
Current assignee: LG Electronics Inc
Priority date: 2003-09-05
Filing date: 2004-08-25
Publication date: 2011-10-26
Anticipated expiration: 2024-08-25
Also published as: EP1512918A3; US20050053493A1; KR20050024158A; CN100339601C; CN1982729A; KR100547328B1; CN1590779A; JP2005083386A; EP1512918A2

Description

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to an axial flow fan of an air conditioner. An axial flow fan according to the preamble of claim 1 is indicated in US 6,447,251 B1 .

2. Background of the Related Art

In general, an air conditioner is mounted therein with a refrigerating cycle s ystem composed of a compressor, a condenser, a capillary tube, an evaporator and a heat exchanger. The air conditioner is an apparatus for properly sending cold air formed at t he evaporator or warm air generated at the condenser according to an indoor condition, a nd thus genially maintaining indoor atmosphere.
The air conditioner may be divided into a window type air conditioner wher e the refrigerating cycle system is mounted in a single body, a spilt type air conditioner w here an indoor unit and an outdoor unit are separated and installed indoors and outdoors r espectively, and so forth. Particularly, the spilt type air conditioner is again divided, acc ording to an installation method, into a wall-mounted type, a permanent-mounted type (in cluding a package air conditioner), a ceiling-mounted type, a ceiling-embedded type and so on. Especially, the indoor unit of the spilt type air conditioner may has a structure ca pable of alternatively using the wall-mounted type and the permanent-mounted type and being simultaneously applied as the ceiling-mounted type according to need of a user, wh ich is referred to as a convertible type indoor unit.
Fig. 1 schematically shows a general air conditioner.
Referring to Fig. 1, the conventional air conditioner is composed of an outd oor unit 20 which is disposed outdoors and exchanges heat with outdoor air, an indoor un it 10 which is disposed indoors and conditions indoor air, and a connecting line 30 which connects the outdoor unit and the indoor unit with each other.
To be more specific, the outdoor unit 20 is a means for converting a gas refr igerant of low temperature and low pressure, which is inputted from the indoor unit 10 by exchanging heat with the outdoor air, into a liquid refrigerant of low temperature and lo w pressure, and is composed of a compressor 11, a condenser 12 and an expansion valve 13.
Further, the compressor 11 is a component for converting the gas refrigeran t of low temperature and low pressure, which is inputted from the indoor unit 10, into the gas refrigerant of high temperature and high pressure, and the condenser 12 is a compone nt for converting the gas refrigerant of high temperature and high pressure into a liquid re frigerant of middle temperature and high pressure, and the expansion valve 13 is a compo nent for converting the liquid refrigerant of middle temperature and high pressure into the liquid refrigerant of low temperature and low pressure.
Here, the condenser 12 is a component for directly exchanging the heat wit h the outdoor air, and has a separate fan for introducing the outdoor air.
Meanwhile, the indoor unit 10 lowers an indoor temperature by means of e vaporation, which occurs when the liquid refrigerant of low temperature and low pressure introduced from the outdoor unit 20 is converted into the gas refrigerant of low temperat ure and low pressure.
The indoor unit 10 is composed of an evaporator 21 and a fan 21a, wherein the evaporator 21 converts the liquid refrigerant of low temperature and low pressure into the gas refrigerant of low temperature and low pressure. The connecting line 30 is a co mponent for connecting the indoor unit 10 and the outdoor unit 20 to circulate the refriger ant, and is properly disposed according to a distance between the outdoor unit 10 and the indoor unit 10.
As set forth above, the outdoor unit 20 of the split-type air conditioner inclu des the compressor, the condenser, a cooling fan (hereinafter, referred to as "axial flow fa n") which usually generate many noises, and a driving motor for rotating the axial flow fa n. The indoor unit 10 includes the evaporator 21 and the blow fan 21 a, and performs ref rigeration and circulation of the indoor air.
Fig. 2 is a perspective view illustrating a general split type air conditioner.
As shown in Fig. 2, the indoor unit 10 and the outdoor unit 20 are connecte d to each other by the connecting line 30.
Meanwhile, the axial flow fan 40, as shown in Fig. 3A, has a hub 42 couple d to a rotational shaft of the driving motor (not shown), and a plurality of blades 44 forme d on an outer circumferential surface of the hub 42, wherein the hub 42 is integrally form ed with the blades 44.
When the axial flow fan 40 is rotated by the driving motor, a pressure differ ence is generated between front and rear sides of the plurality of blades 44 formed on the outer circumferential surface of the hub 42.
This pressure difference generates a suction force capable of sucking up the air, thus sucking up the outdoor air toward the outdoor unit 20 through the suction. Th us, the outdoor air passes through the condenser 12 provided on an intake side of the outd oor unit. At this point, the outdoor air exchanges the heat with the gas refrigerant flowin g through the condenser to condense the gas refrigerant into a liquid state, and then flows out outside the outdoor unit 20 through ventilation of the axial flow fan 40.
As for characteristic factors determining a ventilation characteristic of the a xial flow fan 40, they are divided into two types: general factors such as the number of th e blades 44, a (outer) diameter D of the axial flow fan, a (outer) diameter d of the hub and so forth, and so-called blade factors such as a pitch angle β, a peak point of the camber P, a maximum quantity of the camber MC, a length of a chord, a sweep angle α and so fo rth at the blade, which will be described below with reference to Figs. 3A and 3B.
The pitch angle β of the blade, as in Fig. 3B, is an angle between a flow dir ection of the fluid or the air (x-axis in the figure) and a straight line, namely a chord, runn ing from a leading edge (L.E) of the blade 44 and its trailing edge (T.E).
Here, the quantity of the camber refers to a length joining the camber (a cen tral line across a cross section of the blade) and the chord. The maximum point of the c amber quantity, i.e., the maximum quantity of the camber MC, as in Fig. 3B, refers to the camber quantity between the L.E. of the blade 44 and the camber peak point P on the cho rd C running from the L.E to the T.E.
The sweep angle α refers to an angle between two lines that intersect, one o f which is one which connects the center of an inner end of the blade 44 or the center of a portion where the blade 44 comes into contact with the hub 42 but goes with a curvature of the blade 44, and the other is one (Y axis in the figure) which passes through the cent er (point) of the inner end of the blade 44 and the center (point) of the hub 42.
Especially, the sweep angle α is a factor determining a noise of an airflow o f the axial flow fan 40. When the sweep angle α is great, a phase difference of the airflo w between the hub 42 and a tip of the blade 44 becomes great. In contrast, when the sw eep angle α is great, the phase difference of the airflow becomes small.
The phase difference of the airflow causes a phase difference between a noi se generated at the outer end of the blade 44 and a noise generated at the inner end of the blade 44. The greater this noise phase difference is, the lower a frequency of the airflow passing through the blade 44 becomes. Hence, the noise becomes lower.
And, the number of the blades 44 is an important factor determining the airf low noise generated when the axial flow fan 40 is operated.
One example of this conventional axial flow fan 40 is disclosed in Korean Patent Publication No. 2003-14960 , titled AXIAL FLOW FAN OF OUTDOOR UNIT OF AIR CONDITIONER, previously filed by the present applicant and published as of Febru ary 20, 2003. As for the disclosed axial flow fan of the outdoor unit of the air condition er, it includes a hub 42 connected with a rotational shaft of a motor and a plurality of blad es 44 integrally formed on an outer circumferential surface of the hub, wherein the numb er of the blades 44 is set to three, a whole outer diameter of the fan is set to 340±2mm, a nd a diameter of the hub 42 is set to 100±2mm.
Further, each blade 44 is configured so that the pitch angle β is linearly chan ged from the hub 42 to the end thereof in a range between 20 degrees and 37 degrees.
Each blade 44 is also configured so that the peak point of the camber P is fo rmed at a point corresponding to 70% of the chord length in a direction from the L.E ther eof to the T.E thereof, and that the maximum quantity of the camber MC is set to 0.5% w ithin each radius from the hub 42 to the end of the blade 44.
Further, the sweep angle α of each blade 44 has a range between 47 degrees and 49 degrees when a dimensionless radius coordinate is less than 0.3 and is linearly in creased when the dimensionless radius coordinate exceeds 0.3 to have a range between 5 5 degrees and 57 degrees at the end of the blade.
For reference, the dimensionless radius coordinate is a factor for taking into consideration of performance of the axial flow fan only by the blades 44 except for the h ub 42, and is determined between 0 and 1 when a position where the blades and the hub c ome into contact with each other is set to 0, and the end of each blade 44 is set to 1.
The dimensionless radius coordinate is obtained by the follow formula. r=( R-Rh)/(Rt-Rh), where R is the length from the center of the axial flow fan (i.e. the center of the hub) to a certain position, Rh is the radius of the hub 42, Rt is the length from the c enter of the axial flow fan (i.e. the center of the hub) to the end of each blade 44, namely, the radius of the axial flow fan.
According to the axial flow fan 40 having three blades 44 in the outdoor uni t of the foregoing air conditioner, as shown in Figs. 4 and 5, a pressure coefficient and co nstant pressure efficiency are enhanced as compared to another conventional axial flow fa n having four blades. As a result, the motor for the axial flow fan having three blades ca n be also enhanced in operation efficiency at an operation point, and can be driven with a size smaller than that for another conventional axial flow fan having four blades. In add ition, the motor for the axial flow fan having three blades is reduced by about 22% in con sumption electrical power required for operation.
However, when the axial flow fan 40 is driven, a slip stream or wake comp onent is generated at the L.E and T.E of the leading blade 44, and a turbulent flow compo nent is generated by separation on a negative pressure surface. These two components h ave influence on the trailing blade 44, thus deteriorating the performance of the axial flo w fan 40, and simultaneously generating the noise by a turbulent flow.

SUMMARY OF THE INVENTION

Therefore, an objective of the present invention is to design an axial flow fa n within an optimal design range capable of suppressing increase in intensity of a turbule nt flow generated from a surface of each blade, increase in thickness of a boundary layer on the surface of each blade and disturbance of an airflow within a region of the hub.
It is another objective to provide an axial flow fan capable of remarkably re ducing a noise within the predetermined frequency range (between about 300 Hz and abo ut 1000 Hz) with respect to the same air volume as the conventional axial flow fan.
To achieve the above objective, the present invention provides an axial flo w fan according to claim 1.
Therefore, according to the present invention, the axial flow fan can reduc e the noise as low as possible and increase the pressure coefficient and the constant press ure efficiency compared to the conventional axial flow fan.

BRIEF DESCRIPTION OF THE DRAWINGS

The above objects, features and advantages of the present invention will be come more apparent from the following detailed description when taken in conjunction w ith the accompanying drawings, in which:
Fig. 1 schematically shows a general air conditioner;
Fig. 2 is a perspective view illustrating a general split type air conditioner;
Figs. 3A and 3B are front and side views of a conventional axial flow fan, r espectively;
Fig. 4 is a graph showing comparison of relation between a pressure coeffic ient and a flow rate coefficient in a conventional axial flow fan with that of another conve ntional axial flow fan;
Fig. 5 is a graph showing comparison of relation between constant pressure efficiency and a flow rate coefficient in a conventional axial flow fan with that of another conventional axial flow fan;
Figs. 6A and 6B are front and side views of an axial flow fan according to t he present invention, respectively;
Figs. 7A and 7B show a state where blades are tilted on an outer circumfere ntial surface of a hub at a certain rake angle in axial flow fans according to the prior art and the present invention;
Fig. 8 is a graph showing a state where a noise is changed according to a ch ange of a solidity with respect to axial flow fans of the prior art and the present invention;
Fig. 9 is a graph showing a state where a noise is changed according to a ch ange of a quantity of a camber with respect to axial flow fans of the prior art and the pres ent invention;
Fig. 10 is graph showing relation between a (constant) pressure coefficient, a constant pressure efficiency and a flow rate coefficient with respect to axial flow fans o f the prior art and the present invention; and
Fig. 11 is a graph showing comparison of a state where a noise is changed a ccording to a change of a frequency of an axial flow fan of the present invention with that of an axial flow fan of the prior art.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS

An exemplary embodiment of the present invention will now be described with reference to the accompanying drawings.
Figs. 6A and 6B are front and side views of an axial flow fan according to t he present invention, respectively. Figs. 7A and 7B show a state where blades are tilted on an outer circumferential surface of a hub at a certain rake angle in axial flow fans acco rding to the prior art and the present invention.
An axial flow fan 140 of an outdoor unit of an air conditioner according to t he present invention is composed of a hub 142 connected with a rotational shaft 141 of a motor, and a plurality of blades 144 integrally formed on an outer circumferential surface of the hub 142.
The axial flow fan 140 is configured so that the number of the blades is two , that a ratio of an inner diameter to an outer diameter (i.e. a ratio of the outer diameter of the hub and the outer diameter of the fan) is between about 0.35 and about 0.4, that a soli dity, a ratio of the whole area of the fan 140 and an area of the blades, has a range of 0.85 ±0.05, and that a quantity of a camber of the hub 142 has a range of 5.0%±1.0%.
Hereinafter, a detailed description will be made on the axial flow fan of the outdoor unit of the air conditioner according to the present invention.
Meanwhile, when the axial flow fan 140 is driven, a slip stream or wake co mponent may be generated at a leading edge (L.E) and a trailing edge (T.E) of the leading blade 144, and a turbulent flow component may be generated by separation on a negativ e pressure surface. These two components may have influence on the trailing blade 144, thus deteriorating performance of the axial flow fan 140, and simultaneously generating a noise by a turbulent flow. Thus, the present invention aims at preventing the drawbac ks of the axial flow fan 140.
Further, the present invention is to suppress increase in intensity of the turb ulent flow generated from a surface of each blade 144, increase in thickness of a boundar y layer on the surface of each blade 144, and disturbance of an ariflow within a region of the hub 142.
In order to accomplish the objectives, the axial flow fan 140 is formed so th at the number of the blades 144 is two, that the ratio of the inner diameter to the outer dia meter (i.e. the ratio of the outer diameter of the hub and the outer diameter of the axial flo w fan) is between about 0.35 and about 0.4, that the solidity, the ratio of the whole area of the fan 140 and the area of the blades, has the range of 0.85±0.05, and that the camber q uantity of the hub 142 has the range of 5.0%±1.0%. With regard to this, the detailed co nfiguration of the present invention is as follows.
The axial flow fan 140 of the outdoor unit of the air conditioner according t o the present invention, as shown in Fig. 6A, is composed of the hub 142 connected with the rotational shaft 141 of the motor, and the plurality of blades 144 integrally formed on the outer circumferential surface of the hub 142.
Here, the number of the blades 144 is set to two. The inner and outer dia meter ratio of the axial flow fan 140, i.e. the ratio of the outer diameter of the hub 142 an d the outer diameter of the axial flow fan 140, is set to a range between about 0.35 and ab out 0.40.
Further, the ratio of the whole area of the axial flow fan 140 and the area of the blades, i.e. the solidity, has the range of 0.85±0.05, and the camber quantity of the hu b 142 has the range of 5.0%±1.0%. The solidity can be expressed by the following form ula.
Solidity = (chord × Z) / 2πr
where 2π r : circumference length when a radius is r , chord : straight lin e joining the L.E of the blade with the T.E of the blade, Z : the number of blades.
Thus, a value of the solidity presented in the present invention may become a mean value from the hub and a tip, for example, an integral value.
For the axial flow fan 140, as shown in Figs. 7A and 7B, a rake base line of each blade 144 formed on the outer circumferential surface of the hub 142 is tilted from that formed horizontal to the outer circumferential surface of the conventional hub 42 by a rake angle between about 20 degrees and about 23 degrees. Here, the rake angle refers to an angle determining how much to tilt and form the blades 144 on the circumferential surface of the hub 142.
As for a state where the blades 144 are formed on the outer circumferential surface of the hub 142 through the rake angle, as shown in Figs. 7A and 7B, among the w hole length from the outer circumferential surface of the hub 142 to the outer end (i.e. tip) of each blade 144, a part from the outer circumferential surface of the hub 142 to a pred etermined portion of each blade 144 is tilted at the rake angle, and the other part from the predetermined portion of each blade 144 and the tip of each blade 144 is provided with a bulge 146 protruded toward a pressure surface. The tip of each blade 144 has the same angle as the rake angle from the outer circumferential surface of the hub 142 to the predet ermined portion of each blade 144. In this manner, a profile of the axial flow fan 140 is formed as a whole.
In other words, when the section from the outer circumferential surface of t he hub to the tip of each blade is divided into two sections, the first section performs rotat ional displacement at the identical angle, and the second section forms a non-linear angle raised toward the pressure surface. The tip (i.e. a section except for the two sections) is adapted to apply an identical value of the first section.
At this point, the outer diameter D of the axial flow fan is 460±2mm, and th e outer diameter d of the hub 142 is 170±2mm.
Here, a pitch angle, a peak point of a camber, and a sweep angle of each bla de 144 are the same as the pitch angle β, the peak point of the camber P, the maximum qu antity of the camber MC, and the sweep angle α of the conventional blade 44 shown in Fi gs. 3A and 3B. Now, the pitch angle, the peak point of the camber, and the sweep angle of each blade 144 will be described in detail below.
The pitch angle β of each blade 144 is configured to be linearly changed fro m the hub 142 to the end of the blade 144 within a range between 37 degrees and 20 degr ees.
Each blade 144 is configured so that the peak point of the camber P is form ed at a position corresponding to 70% of a length of a chord in a direction from the front end of the blade to the rear end of the blade, and that that the maximum quantity of the ca mber MC is kept constant at a value of 0.5% within each radius from the hub 142 to the e nd of the blade 144.
Furthermore, the sweep angle α of each blade 144 has a range between abo ut 47 degrees and about 49 degrees when a dimensionless radius coordinate is less than 0. 3 and is linearly increased when the dimensionless radius coordinate exceeds 0.3 to have a range between about 55 degrees and about 57 degrees at the end of the blade.
A change of the noise generated from the axial flow fan configured as set fo rth above will be described below.
Fig. 8 is a graph showing a state where a noise is changed according to a ch ange of a solidity with respect to axial flow fans of the prior art and the present invention. Fig. 9 is a graph showing a state where a noise is changed according to a change of a q uantity of a camber with respect to axial flow fans of the prior art and the present inventio n. Fig. 10 is graph showing relation between a (constant) pressure coefficient, a constan t pressure efficiency and a flow rate coefficient with respect to axial flow fans of the prior art and the present invention. Fig. 11 is a graph showing comparison of a state where a noise is changed according to a change of a frequency of an axial flow fan of the present invention with that of an axial flow fan of the prior art.
As seen from the foregoing description and the drawings, the solidity applie d to the present invention has a range of 0.85±0.05 and the camber quantity of the hub ha s a range of 5.0%±1.0%.
In contrast, the solidity applied to the prior art (Z=3) has a relatively great v alue compared to that of the present invention, and the camber quantity of the hub has a r elatively small value.
The following description will be made with reference to Figs. 10 and 11.
In the graph of Fig. 10, an upper line shows a comparison of relation of the (constant) pressure coefficient and the flow rate coefficient in the axial flow fan 140 with that of the conventional axial flow fan 40, while a lower line shows a comparison of relati on of the constant pressure efficiency and the flow rate coefficient in the axial flow fan 1 40 with that of the conventional axial flow fan 40.
For the axial flow fan 140 according to the present invention, the noise cha nge was measured depending on the change of the solidity as the ratio of the whole area o f the fan 140 to the area of the blades. It was found that as a result of the measurement, as shown in Fig. 8, when the ratio of the whole area of the fan 140 to the area of the blades, i.e. the solidity, was about 0.87, the noise was the lowest. Further, the noise change wa s measured depending on the change of the camber quantity of each blade of the axial flo w fan 140. It was found that as a result of the measurement, as shown in Fig. 9, when th e camber quantity of the blade 144 was about 0.5%, the noise was lowest.
For the axial flow fan 140 according to the present invention, it can be seen that as shown in Fig. 10, the pressure coefficient and the constant pressure efficiency wer e enhanced over the conventional axial flow fan 40, and that the operation efficiency was also enhanced at the operation point according to the enhancement of the pressure coeffic ient and the constant pressure efficiency of the axial flow fan 140 as set forth above.
Further, Fig. 11 is a graph showing comparison of a state where a noise is c hanged according to a change of a frequency of an axial flow fan of the present invention with that of an axial flow fan of the prior art. As shown in Fig. 11, it can be seen that w hen having an air volume equal to that of the conventional axial flow fan 40, the axial flo w fan 140 was subjected to great reduction of the noise in a range between about 300 Hz and about 1000Hz.
As set forth above, the present invention relates to the axial flow fan config ured so that the number of the blades is two, that a predetermined rake angle is kept const ant in the part from the hub to the predetermined portion of the blade among the whole pa rt from the hub to the outer end of the blade and is increased in the pressure surface direct ion in the other part from the predetermined portion of the blade to the the outer end of th e blade, and the ratio of the inner diameter to the outer diameter is between about 0.35 an d about 0.4.
Therefore, the axial flow fan of the present invention is designed within an optimal design range (that the solidity, the ratio of the whole area of the axial flow fan an d the area of the blades, is about 0.87 and that the camber quantity of the hub is about 5.0 %), for example, capable of suppressing increase in intensity of the turbulent flow genera ted from the surface of each blade, increase in thickness of the boundary layer on the surf ace of each blade and disturbance of the airflow within the region of the hub. As a resul t, the axial flow fan of the present invention can reduce the noise as low as possible and i ncrease the pressure coefficient and the constant pressure efficiency compared to the con ventional axial flow fan.
Further, the axial flow fan of the present invention can remarkably reduce t he noise within the predetermined frequency range (e.g. between about 300 Hz and about 1000 Hz) with respect to the same air volume as the conventional axial flow fan.
While the invention has been shown and described with reference to certain preferred embodiments thereof, it will be understood by those skilled in the art that vari ous changes in form and details may be made therein.
For example, the axial flow fan of the present invention may be applied to a refrigerator or other apparatuses for condensing and evaporating a refrigerant.

Claims

An axial flow fan (140) comprising:
a hub (142) connected with a rotational shaft (141) of a motor; and

at least one blade (144) contacting the hub (142),

wherein the blade (144) has a part from the hub (142) to a predetermined portion of the blade (144) among a whole part from the hub (142) to an outer end of the blade (144), and the other part from the predetermined portion of the blade (144) to the outer end of the blade (144), the part being equally applied at a predetermined rake angle, and the other part being raised in a direction of a pressure surface of the blade (144),

characterised in that

the outer edge has the same angle as the rake angle;

a rake base line of the blade (144) is formed on an outer circumferential surface of the hub (142) and within the part from the hub (142) to the predetermined portion, is tilted by the rake angle between about 20 degrees and about 23 degrees;

and in that a ratio of an inner diameter and an outer diameter of the axial flow fan (140) which is the ratio of the outer diameter of the hub (142) and the outer diameter of the axial flow fan (140), is between 0.35 and about 0.4.
An axial flow fan (140) as set forth in claim 1, wherein the number of the blades is two.
An axial flow fan (140) as set forth in claim 1, wherein a solidity has a range of 0.85±0.05.
An axial flow fan (140) as set forth in claim 1, wherein the outer diameter of the axial flow fan (140) has a range of 460±2mm.
An axial flow fan (140) as set forth in claim 1, wherein the hub (142) has an diameter of a range of 170±2mm.