KR20010073585A - Axial flow fan for refrigerator - Google Patents

Abstract

PURPOSE: An axial fan for a refrigerator is provided to optimize a number of blades, a ratio between inner and outer diameters, a hub ratio, a sweep angle, a pitch angle, a maximum camber ratio and the like for minimizing the wind blowing noise and simultaneously increasing the refrigerating efficiency with low energy consumption. CONSTITUTION: A refrigerator axial fan includes a hub(2) connected to a rotation shaft of a driving motor to rotate together with the rotation shaft, and five blades(4) mounted to an outer periphery of the hub with a uniform interval, wherein a ratio between an outer diameter of the hub and an outer diameter of the blades, that is, an inner diameter and an outer diameter of the fan is 0.25, the outer diameter(ID) is 35±1mm, the outer diameter(OD) is 140±1mm, a forward distance of the blades is 31.95±1mm, and a backward distance of the blades is 7.62±1mm.

Description

Axial flow fan for refrigerator}

The present invention relates to an axial fan for supplying air cooled through an evaporator in a refrigerator to a freezer compartment, and in particular, low noise by optimizing fan design factors such as the number of blades, the hub ratio, the sweep angle, the pitch angle, and the maximum cam ratio of the fan. The present invention relates to an axial flow fan for a refrigerator that can realize anger.

1 is a configuration diagram showing a freezer compartment cold air flow path structure of a typical refrigerator, and FIG. 2 is an enlarged view of a part A of FIG.

In the freezer compartment cold air flow channel structure, a grill fan 52 through which cold air is discharged is mounted at a rear side of the freezer compartment 50, and a driving motor 54 is fixed to the inside of the grill fan 52 by a motor mount 56. An axial fan 58 for supplying cold air to the freezing chamber 50 is fixed to the rotation shaft of the drive motor 54, and the shroud 60 is fixed to the grill pan 52 in the circumferential direction of the axial fan 58. Is positioned, and a suction flow path is formed between the drive motor 54 and the motor mount 56.

In addition, a heat exchanger 62 is provided on the suction flow path formed at the rear side of the freezing chamber 50 to provide cold air through heat exchange with the refrigerant, and a refrigerator machine room 64 is installed below.

That is, the cool air cooled while passing through the heat exchanger 62 flows into the axial fan 58 through the suction flow path between the drive motor 54 and the motor mount 56, and the axial fan 58 and the shroud ( The cold air passing through 60 is guided by the grill pan 52 and supplied to the refrigerating chamber 50.

3 is a front view of an axial flow fan for a refrigerator according to the prior art.

Referring to Figure 3, the structure and operation of the cold air circulation axial fan of the refrigerator according to the prior art will be described.

The axial fan includes a hub 102 connected to a rotation shaft of the drive motor and receiving a driving force of the drive motor, and a plurality of blades 104 installed at regular intervals on the outer circumferential surface of the hub 102.

The number of the blades 104 is typically formed of 3 to 4, the outer diameter of the blade is 110mm, the outer diameter of the hub is 25mm, the blade width is 28.1mm, and the sweep angle of the fan design factor Sweep angle, Pitch angle and maximum camber amount are formed relatively small.

However, the fan design factors such as the number of blades, hub ratio, pitch angle, etc. of the cold air axial flow fan made in this way do not generate a flow suitable for the large pressure loss and the complicated flow path characteristics of the refrigerator, which is becoming larger, which causes the refrigerator noise to increase. There was a problem.

In addition, the blade width is limited to a maximum of 40 mm, which is not suitable for sucking a large amount of cold air as a limit that does not increase the pitch angle, and the amount of camber is relatively small so as to effectively increase the matching of the fluid through the fan and shroud. There is a problem.

The present invention was created to solve the above problems, and optimizes the fan design factors such as the number of blades, hub ratio, sweep angle, pitch angle, maximum camber ratio, etc. to suit the low noise design of the fan to improve the cooling performance. The purpose of the present invention is to provide an axial fan for a refrigerator that can improve power consumption and reduce the noise of the refrigerator.

1 is a configuration diagram showing a freezer compartment cold air flow path structure of a typical refrigerator,

2 is an enlarged view of a portion A of FIG. 1,

3 is a front view of an axial flow fan for a refrigerator according to the prior art,

4 is a front view of the axial flow fan for a refrigerator according to the present invention,

5 is a side view of an axial flow fan for a refrigerator according to the present invention,

6 is a cross-sectional view showing a state in which the blade of the refrigerator axial flow fan according to the present invention is cut in the circumferential direction,

Figure 7 is a graph showing the noise rate according to the internal and external ratio of the axial fan according to the present invention,

8 is a graph showing the noise rate according to the maximum camber rate of the blade according to the present invention.

9 is a graph showing the noise rate according to the pitch angle of the blade according to the present invention.

10 is a graph showing the noise rate according to the sweep angle of the axial fan according to the present invention.

<Explanation of symbols for the main parts of the drawings>

2: hub 4: blade

θ: sweep angle ψ: pitch angle

CP: Maximum camber position

The axial flow fan for a refrigerator according to the present invention for achieving the above object includes a hub to which the motor shaft is connected, and a plurality of blades installed on the hub, the number of blades, internal and external costs, the sweep angle of the blade, The fan's design parameters including pitch angle and maximum camber ratio are selected as the optimal conditions, respectively, to create a flow of cold air suitable for the large pressure loss of the refrigerator and the complicated flow path characteristics, and at the same time, the fluid noise of the fan itself is reduced. It is characterized in that low noise can be realized.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

4 is a front view of the axial flow fan for a refrigerator according to the present invention, Figure 5 is a side view of Figure 4, Figure 6 is a cross-sectional view cut circumferentially the blade of the axial flow fan according to the present invention.

The structure and operation of the axial fan for a refrigerator according to the present invention will be described with reference to FIGS. 4 to 6 as follows.

As shown in FIG. 4, the cold air circulation axial fan includes a hub 2 connected to the rotating shaft of the driving motor, and a plurality of blades 4 installed at regular intervals on the outer circumferential surface of the hub 2.

The number of the blades 4 is most preferably 5 in consideration of various matters such as efficiency, air volume, wind pressure.

The diameter of the hub 2 is distributed in the range of 35 ± 1 mm, the outer diameter of the fan, that is, the outer diameter of the blade 4 is distributed in the range of 140 ± 1 mm. In addition, the inner and outer ratios of the diameter ratio of the outer diameter ID and the blade outer diameter OD of the hub 2 are 0.25.

In addition, the blade front leading distance (FD) is 31.95 ± 1 mm, the blade rear leading distance (RD) is 7.62 ± 1 mm, the blade trailing front distance (RD) is made smaller than the hub width (BD).

The blade front leading distance FD refers to the rotation axis from the center point of the data to the maximum blade leading edge RE, that is, the distance on the Z axis, and the blade trailing distance RD is the center point of the blade data (0,0, The distance on the axis of rotation, i.e., the Z axis, from 0) to the maximum blade trailing edge (TE).

Here, the data center point (0,0,0) is the center of the distance from the maximum blade leading edge (RE) to the maximum blade trailing edge (TE) of the blade hub (BH) mounted on the outer surface of the hub it means.

In addition, the maximum camber position CP in the blade 4 is 0.70 to 0.75, which is uniformly distributed from the blade hub BH to the blade tip BT. This maximum camber position CP is most preferably distributed to 0.73. The maximum camber ratio (%) is linearly distributed from the blade hub (BH) to the blade tip (BT) at 5.9% to 6.1% at the blade hub (BH) and 7.9% to 8.1% at the blade tip (BT). . This maximum camber rate (%) is 6.0 to 8.0% is most preferably distributed linearly from the blade hub (BH) to the blade tip (BT).

Here, the maximum camber position CP is a position where the blade 4 is farthest from the straight line connecting the blade leading edge RE and the blade trailing edge TE, and the straight line and the blade 4 at this time Is the maximum camber (C). In addition, the maximum camber ratio is a ratio of the maximum camber (C) and the code length (CL) as a percentage, the code length (CL) is connected to the blade leading edge (RE) and the blade trailing edge (TE) The distance on one straight line.

The pitch angle ψ of the blade 4 has a linear distribution from 43.0 ° to 28.0 ° from the blade hub BH to the blade tip BT. That is, the pitch angle ψ is linearly distributed from the blade hub BH to the blade tip BT at 47.9 to 43.1 at the blade hub BH and from 27.9 ° to 28.0 ° to the blade tip BT.

Here, the pitch angle ψ represents an angle formed by the straight line connecting the blade leading edge RE and the blade trailing edge TE to the X axis. That is, the pitch angle ψ means how inclined the blade 4 is with the plane perpendicular to the Z axis, which is the rotation axis.

In addition, the sweep angle θ of the blade 4 is 0.0 ° to 37.0 ° from the blade hub BH to the intermediate point between the blade tips BT, and 37.0 ° to 49.5 from the intermediate point to the blade tip BT. It is distributed in the form of a secondary parabola at °.

Here, the sweep angle θ is an angle where a straight line connecting the center of the blade hub BH and the center of the blade tip BT to each other after making the center of the blade hub BH coincide with the Y axis. Indicates. That is, the sweep angle θ means how biased the blade 4 is to the front.

As such, when the sweep angle θ, the pitch angle ψ, and the camber amount are relatively large, the operating noise of the fan is greatly reduced, the blade width BD is widened, and the amount of air to be sucked is increased. Since the static pressure of the fluid passing through the shroud can be effectively increased, power consumption is low and high air volume can be obtained.

In addition, the space | interval between the said blades 4 is distributed so that it may become 5.0 mm, 11.0 mm, 9.0 mm, and 17.0 mm respectively according to the positions of ㉠, ㉡, ㉢, and ㉣. At this time, if the position of the blade hub (BH) in the blade (4) is 0, the position of the blade tip (BT) is 1, 11.0mm and 9.0mm of the spacing between the blades are each blade hub (BH) Is located between 0.75 and 0.97, respectively, between the blade tips BT and the blade tip BT.

Noise ratios according to the respective design factors of the axial fan according to the present invention configured as described above are shown graphically in FIGS. 7, 8, 9, and 10, respectively.

The graph shown in FIG. 7 shows the noise ratio according to the inner and outer ratios of the axial fan. When the inner and outer ratios, which is the ratio of the outer diameter (OD) of the blade and the outer diameter (ID) of the hub, is 0.25, the noise is 22.4 dB, the lowest value. Indicates.

The graph shown in FIG. 8 shows the noise ratio according to the maximum camber ratio (%) of the axial fan, and the maximum camber ratio (%) of the axial fan is 6.0 to 8.0% from the blade hub (BH) to the blade tip (BT). Linearly distributed, the noise is the lowest at 22.5dB.

The graph shown in FIG. 9 shows the noise rate according to the pitch angle ψ of the blade 4, and the pitch angle ψ of the blade 4 is 43.0 ° from the blade hub BH to the blade tip BT. When linearly distributed at ˜28.0 °, noise is the lowest at 22.4dB.

The graph shown in FIG. 10 shows the noise ratio according to the sweep angle θ of the blade 4, and the sweep angle θ of the blade 4 is 0.0 ° from the blade hub BH to the blade tip BT. When distributed in a 2nd parabolic form at -37.0 degrees, the lowest value is represented by 22.6dB.

Boundary data of the blade (4) of the axial flow fan for the machine room as described above is shown in Table 1 below, the present invention is installed in a refrigerator of the same capacity, and then the noise value is measured Compared to the axial fan for the machine room, the fan noise at the same cooling performance is reduced.

No. X Y Z One -8.166 15.478 -7.615 2 -7.604 15.761 -7.184 3 -6.053 16.42 -5.986 4 -3.712 17.102 -4.163 5 -0.847 17.48 -1.918 6 2.191 17.362 0.465 7 4.97 16.779 2.732 8 6.845 16.106 5.017 9 7.849 15.641 6.866 10 8.166 15.478 7.615 11 7.791 21.994 7.158 12 7.313 28.235 6.676 13 6.806 34.322 6.234 14 6.3 40.344 5.856 15 5.689 46.319 5.463 16 4.222 52.33 4.576 17 1.786 58.306 3.227 18 -1.599 64.147 1.535 19 -9.035 69.414 -4.938 20 -10.847 69.154 -7.356 21 -16.179 68.105 -12.812 22 -24.731 65.486 -18.548 23 -35.384 60.399 -22.705 24 -45.539 53.162 -26.397 25 -53.856 44.716 -29.195 26 -59.682 36.58 -30.911 27 -62.999 30.515 -31.726 28 -64.081 28.172 -31.946 29 -57.979 27.492 -30.58 30 -50.377 29.41 -28.53 31 -43.206 29.825 -26.224 32 -36.621 28.925 -23.798 33 -30.642 26.99 -21.313 34 -24.85 24.647 -18.498 35 -19.177 21.976 -15.291 36 -13.621 18.945 -11.675 37 -8.166 15.478 -7.615

As described above, the present invention has been shown and described with respect to specific embodiments, but it is common knowledge in the art that various modifications and changes can be made without departing from the spirit and spirit of the invention as indicated by the claims. Anyone who has a can know it easily.

The axial fan for a refrigerator according to the present invention constructed and operated as described above has a large pressure of the refrigerator by optimizing fan design factors such as the number of blades, internal and external ratios, sweep angle θ, pitch angle ψ, and maximum camber ratio. The fan noise can be reduced while improving the cooling performance which can generate the flow of cold air suitable for the loss and complicated flow path characteristics.

Claims (5)

In the axial fan comprising a hub connected to the rotation shaft of the drive motor and a plurality of blades provided on the outer peripheral surface of the hub at regular intervals, The number of blades is made of five, axial flow fan for a refrigerator, characterized in that the inner and outer ratio of the diameter ratio of the outer diameter (ID) and the blade outer diameter (OD) of the hub is made of 0.25. The method of claim 1, The outer diameter of the hub is distributed in the range of 35 ± 1 mm, the outer diameter of the blade is distributed in the range of 140 ± 1 mm, the blade forward distance (FD) is 31.95 ± 1 mm, the blade trailing distance (RD) is Axial flow fan for refrigerator, characterized in that formed 7.62 ± 1㎜. The method of claim 1, The maximum camber position (CP) in the blade is 0.70 to 0.75, which is uniformly distributed from the blade hub (BH) to the blade tip (BT), and the maximum camber ratio (%) is 5.9% to 6.1% in the blade hub (BH). And a blade tip (BT), which is linearly distributed from the blade hub (BH) to the blade tip (BT) at 7.9% to 8.1% at the blade tip (BT). The method of claim 1, The pitch angle (ψ) of the blade is linearly distributed from the blade hub (BH) to the blade tip (BT) at 27.9 ° to 28.0 ° from the blade hub (BH) to 22.9 ° to 28.0 ° to the blade tip (BT). Axial flow fan for refrigerator. The method of claim 1, The sweep angle (θ) of the blade is 0.0 ° to 37.0 ° from the blade hub (BH) to the midpoint between the blade tips (BT) and from 27.0 ° to 49.5 ° from the midpoint to the blade tips (BT). Axial flow fans for refrigerators, characterized in that distributed in the form.