KR20000045689A - Axial fan for refrigerator - Google Patents

Abstract

PURPOSE: An axial fan for a refrigerator is provided to form blades to have a larger sweep angle, a larger pitch angle, and a larger camber for smooth suction and discharge of air in a machinery chamber, thereby increasing suction and discharge air flow and minimizing noise due to unnecessary air flow. CONSTITUTION: An axial fan for a refrigerator includes a hub connected to a motor shaft and a plurality of blades(55) mounted on the hub, wherein the number of the blades is three and a ratio of an inner diameter(ID) to an outer diameter(OD) is 0.2-0.3. In the blades, the outer diameter is 146±1mm, inner diameter is 34±1mm, a distance advanced forward(FD) is (26.0 to 26.5)±1mm, and a distance withdrawn backward(RD) is (25.5 to 26.0)±1mm. A maximum camber position of the blades is 0.7-0.75 uniformly from a blade hub to a blade tip, wherein a maximum camber is 3.1-3.4% at the blade hub and 9.1-9.4% at the blade tip in a linear distribution from the blade hub to the blade tip.

Description

Axial flow fan for refrigerator

The present invention relates to an axial flow fan for a refrigerator used to cool a compressor and a condenser installed in a machine room of a refrigerator. In particular, the number of blades is 3 and the internal and external cost of the fan is 0.2 in order to smooth air flow in the refrigerator machine room. It is -0.3 and it is related with the axial flow fan for refrigerators provided with the structure where the sweep angle, pitch angle, and camber amount of the said blade are comparatively large, respectively.

1 is a front view showing a structure and a cold air flow path of a typical top mount type refrigerator, FIG. 2 is a schematic side view of FIG. 1, FIG. 3 is a plan view showing a machine room structure and a cold air flow path of a typical top mount type refrigerator. 4 is a side view of FIG. 3.

1 and 2, a general top mount type refrigerator is divided into a freezer compartment 10 provided at an upper side and a refrigerating compartment 20 provided at a lower side of the freezer compartment 10.

Here, the freezer compartment 10 has an evaporator 11 that provides cold air through heat exchange with a refrigerant, and a cold air supply fan that sucks cold air provided from the evaporator 11 and supplies it to the freezer compartment 10 and the refrigerating compartment 20. (13) is provided.

In addition, as shown in FIGS. 3 and 4, the machine room 21 formed at the lower end of the refrigerating chamber 20 includes a compressor 22 for compressing a refrigerant and a refrigerant compressed by the compressor 22 with air. A condenser 23 for condensing through heat exchange of the heat exchanger and a cooling axial flow fan 25 for cooling the compressor 22 and the condenser 23 are provided.

In addition, the cooling axial flow fan 25 is fixed to the rotating shaft of the drive motor 26 is operated according to whether the drive motor 26 is driven, the outer side to protect the blade of the cooling axial flow fan 25 Shroud 27 is installed.

In the top mount type refrigerator configured as described above, first, when the refrigerant compressed by the compressor 22 of the machine room 21 is changed into a vapor state of high temperature and high pressure, and then sucked into the condenser 23, the condenser 23 is heated. The refrigerant is converted into a liquid state at room temperature and high pressure. Thereafter, the refrigerant condensed by the condenser 23 is decompressed while passing through a capillary tube, and part of the refrigerant is in a two-phase state in which a liquid and a gas are mixed. Thereafter, the refrigerant sucked into the evaporator 11 of the freezing chamber 10 completely vaporizes and takes away heat from the surroundings, thereby cooling the surrounding air. In this way, the air cooled through the evaporator 11 is provided to the freezing chamber 10 and the refrigerating chamber 20 by the cold air supply fan (13). Thereafter, the above process is continuously repeated, so that the temperatures of the freezing chamber 10 and the refrigerating chamber 20 are kept at a low temperature.

At this time, in the machine room 21, a cooling axial fan 25 is operated to cool the heat generated from the compressor 22 and the condenser 23 when the compressor 22 and the condenser 23 are operated. . That is, the air introduced through the suction port 21 ′ of the machine room 21 passes the driving motor 26 by the rotational force of the cooling axial fan 25, and then the cooling axial fan 25 and the shroud 27. Is reached through the condenser 23. Thereafter, the air cooled by the condenser 23 cools the surface of the compressor 22 while passing through the compressor 22, and then is discharged to the outside through the discharge port 21 ″ of the machine room 21.

As described above, the cooling axial flow fan 25 effectively sucks outside air, and then primarily cools the condenser 23 to improve the heat exchange rate of the condenser 23, thereby increasing the freezing efficiency of the refrigerator. Secondly, the temperature of the surface of the compressor 22 is kept low, thereby preventing the performance of the compressor 22 from being lowered.

Therefore, the performance of the cooling axial flow fan 25 has a great influence on the freezing efficiency and noise of the refrigerator. By the way, the cooling axial fan 25, which has been used a lot in the past, mostly has three blades, a fan outer diameter of 145 to 165 mm, a sweep angle, a pitch angle, and a camber amount. %) Tends to be relatively small, which results in poor performance in terms of freezing efficiency and noise.

If the sweep angle is small, the operation noise is greatly increased, and if the pitch angle is small, the width of the blade is small, which is not suitable for sucking a large amount of air, and when the camber amount is small, it passes through the axial fan and the shroud. This is because the static pressure of the fluid cannot be raised efficiently, so the fan speed must be increased.

Accordingly, by designing the fan design factors such as the sweep angle, pitch angle, camber amount, and the like to the system, it is necessary to manufacture the cooling axial fan 25 having a structure capable of realizing low noise while satisfying the required air volume.

The present invention has been made to solve the above problems, by promoting the flow of air in the refrigerator machine room to induce the smooth intake and discharge of air to minimize the noise caused by the unsmooth air flow, as well as In addition, an object of the present invention is to provide an axial flow fan for a refrigerator, which increases the amount of air sucked and discharged and ultimately achieves low noise while satisfying the air volume required for the machine room of the refrigerator.

1 is a front view showing a structure and a cold air passage of a typical top mount type refrigerator;

2 is a schematic side view of FIG. 1;

3 is a plan view showing a machine room structure and a cold air flow path of a typical top mount type refrigerator;

4 is a side view of FIG. 3;

5 is a front view and a side view showing the structure of the axial flow fan for a refrigerator according to the present invention;

6 is a cross-sectional view of the blade of the axial flow fan for a refrigerator according to the present invention.

<Explanation of symbols for main parts of drawing>

51: Hub 55: Blade

ID: Inside Diameter OD: Outside Diameter

FD: Before Blades RD: Before Blades

CP: Maximum camber position ψ: Pitch angle

θ: sweep angle

According to a first aspect of the present invention for achieving the above object, including a hub to which the motor shaft is connected, and a plurality of blades installed on the hub; The number of the blades is three, the inner and outer ratios of the ratio between the inner diameter and the outer diameter is provided with an axial flow fan for a refrigerator of 0.2 to 0.3.

Further, according to the second aspect of the present invention, the outer diameter is 146 ± 1 mm, the inner diameter is 34 ± 1 mm, the blade forward distance is (26.0-26.5) ± 1 mm, and the blade back distance is (25.5-26.0). ) ± 1 mm.

In addition, according to the third aspect of the present invention, the maximum camber position of the blade is 0.7 to 0.75, which is uniformly distributed from the blade hub to the blade tip, and the maximum camber ratio is 3.1 to 3.4% at the blade hub and 9.1 to 3.4 at the blade tip. 9.4% linearly distributed from blade hub to blade tip.

In addition, according to the fourth aspect of the present invention, the pitch angle of the blade is linearly distributed from the blade hub to the blade tip at 37.5 ° to 38.5 ° at the blade hub and 24.5 ° to 25.5 ° at the blade tip.

In addition, according to the fifth aspect of the present invention, the sweep angle of the blade is distributed in a secondary parabolic form from the blade hub to the blade tip at 0.0 ° at the blade hub and 37.0 ° at the blade tip.

According to the present invention configured as described above, the suction and discharge of the air in the refrigerator machine room is smoothly guided, thereby ultimately achieving low noise while satisfying the air volume required for the machine room of the refrigerator.

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

5 is a front view and a side view showing the structure of the axial fan for a refrigerator according to the present invention, Figure 6 is a cross-sectional view of the blade of the axial fan for a refrigerator according to the present invention.

5 and 6, the axial flow fan for a refrigerator according to the present invention includes a hub 51 to which a motor shaft is connected, and a plurality of blades 55 installed on the hub 51. The number of 55) is three, and the inner and outer ratios, which are the ratio between the inner diameter (ID) and the outer diameter (OD), are 0.2 to 0.3. Here, the inside diameter ID is equal to the diameter of the hub 51.

More specifically, the outer diameter OD of the axial flow fan for refrigerators according to the present invention is 146 ± 1 mm, the inner diameter ID is 34 ± 1 mm, and the inner and outer ratio is 0.233. In addition, the blade front forward distance (FD) is (26.0 ~ 26.5) ± 1mm, the blade back forward distance (RD) is (25.5 ~ 26.0) ± 1mm, the above blade front forward distance (FD) and the blade back forward distance (RD) ) Denotes the distance on the axis of rotation, i.e., the Z axis, from the center point of the blade data to the maximum blade leading edge RE and the maximum blade trailing edge TE.

In addition, the maximum camber position CP in the blade 55 is 0.7 to 0.75, and is uniformly distributed from the blade hub BH to the blade tip BT, and the maximum camber ratio is 3.1 to the blade hub BH. At 3.4%, the blade tip (BT) is 9.1-9.4% and is linearly distributed from the blade hub (BH) to the blade tip (BT).

Here, the maximum camber position CP is a position where the blade 55 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 55 at this time Is the maximum camber (C). The maximum camber ratio is a ratio of the maximum camber (C) and the code length (CL) as a percentage, and the code length (CL) is a straight line connecting the blade leading edge (RE) and the blade trailing edge (TE) The distance of the statue.

In addition, the pitch angle (ψ) of the blade 55 is 37.5 ° to 38.5 ° at the blade hub (BH), 24.5 ° to 25.5 ° at the blade tip (BT) from the blade hub (BH) to the blade tip (BT) It is distributed linearly. 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 55 with the plane perpendicular to the Z axis of the rotation axis.

In addition, the sweep angle (θ) of the blade 55 is distributed in a secondary parabolic form from the blade hub (BH) to the blade tip (BT) at 0.0 ° at the blade hub (BH) and 37.0 ° at the blade tip (BT). It is. 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 55 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. It is possible to effectively increase the static pressure of the fluid passing through the shroud, thereby reducing the fan speed.

In addition, the space | interval between the said blades 55 is distributed so that it may become 8.0 mm, 21.0 mm, 16.0 mm, and 27.0 mm, respectively according to the positions of ㉠, ㉡, ㉢, and ㉣. At this time, if the position of the blade hub (BH) in the blade 55 is 0, the position of the blade tip (BT) is 1, the spacing between the blades 55 in the blade hub (BH) is 8.0 ± 1mm, In the 0 to 0.75 section of the blade 55, the spacing between the blades 55 is increased in a second parabolic form from 8.0 ± 1 mm to 21.0 ± 1 mm, and in the 0.75 to 0.997 section of the blade 55 ) The spacing between 21.0 ± 1 mm and 16.0 ± 1 mm in the form of a secondary parabola. Finally, in the 0.97 to 1.0 section including the blade tip (BT) is increased in the third parabolic form from 16.0 ± 1 mm to 27.0 ± 1 mm.

In short, 21.0 mm and 16.0 mm portions of the spacing between the blades 55 are located at 0.75 and 0.97 portions, respectively, from the blade hub BH to the blade tip BT. At this time, the derivative function at 0.75 and 0.97, which is the boundary point of each section, is 0, and the interval distribution between the blades 55 in each section uses a second and third parabola.

The most preferable form of the axial flow fan for a refrigerator according to the present invention having the above-described dimensional distribution, the number of the blades 55 is 3, the outer diameter (OD) is 146mm, the inner diameter (ID) 34mm, the blade The forward leading distance (FD) is 26.05 ± 1 mm and the blade trailing distance (RD) is 25.83 ± 1 mm. In addition, the maximum camber position (CP) of the blade 55 is 0.73 uniformly distributed from the blade hub (BH) to the blade tip (BT), the maximum camber ratio is 3.26% at the blade hub (BH), blade tip ( BT) is 9.26% and linear distribution from blade hub (BH) to blade tip (BT). In addition, the sweep angle θ of the blade 55 is a secondary parabolic distribution from the blade hub (BH) to the blade tip (BT) at 0 ° at the blade hub (BH), 37.0 ° at the blade tip (BT) , Pitch angle (ψ) is a linear distribution from blade hub (BH) to blade tip (BT) at 37.97 ° at the blade hub (BH), 24.97 ° at the blade tip (BT), as shown in Table 1 below It is implemented in the same shape as the boundary data (Boundary Data) of one blade (55).

Blade width = 51.88 mm X Y Z -12.779 11.956 -10.424 -10.237 14.193 -8.774 -7.344 15.884 -6.766 -4.215 16.985 -4.497 -0.968 17.473 -2.062 2.279 17.351 0.442 5.415 16.641 2.926 8.321 15.395 5.332 10.788 13.780 7.817 12.779 11.956 10.424 16.801 16.982 14.639 20.451 22.327 18.328 23.686 27.990 21.382 26.443 33.979 23.712 28.643 40.303 25.259 30.190 46.967 25.998 31.128 53.876 26.040 31.556 60.924 25.539 27.269 69.867 18.124 16.657 73.127 4.467 3.626 74.912 -5.188 -10.819 74.216 -12.218 -25.122 70.667 -18.482 -38.674 64.260 -23.732 -50.863 55.117 -27.688 -61.098 43.498 -30.054 -68.824 29.803 -30.575 -73.579 14.532 -28.950 -66.965 14.939 -28.922 -58.919 20.003 -28.797 -50.894 22.959 -27.521 -43.131 24.175 -25.358 -35.766 23.971 -22.550 -28.947 22.506 -19.385 -22.789 19.935 -16.144 -17.382 16.388 -13.086 -12.779 11.956 -10.424

As described above, the axial flow fan for a refrigerator of the present invention is installed in a top mount type refrigerator having the same capacity, and then the noise level thereof is measured, and compared with other products, it can be seen that noise is significantly reduced in comparison with other products in the same cooling performance.

The axial flow fan for a refrigerator according to the present invention configured and operated as described above, the number of blades 55, the inner and outer ratio of the fan is 0.2 to 0.3, the sweep angle (θ), pitch angle ( ψ) and cambers have a relatively large structure, which induces smooth intake and discharge of air in the machine room of the refrigerator, thereby minimizing unnecessary noise caused by unsmooth air flow and at the same time By increasing the, ultimately there is an advantage that can achieve a low noise while satisfying the air volume required in the machine room of the refrigerator.

Claims (5)

A hub connected to the motor shaft and a plurality of blades installed in the hub; The number of the blade is three, the inner and outer ratio of the ratio of the inner diameter and the outer diameter (r) is an axial flow fan for a refrigerator, characterized in that 0.2 to 0.3. The method of claim 1, The outer diameter is 146 ± 1 mm, the inner diameter is 34 ± 1 mm, the blade forward distance is (26.0 ~ 26.5) ± 1 mm, the blade trailing distance is (25.5 ~ 26.0) ± 1 mm Axial flow fan. The method of claim 1, The maximum camber position of the blade is 0.7 to 0.75, which is uniformly distributed from the blade hub to the blade tip, and the maximum camber ratio is 3.1 to 3.4% at the blade hub and 9.1 to 9.4% at the blade tip, linearly from the blade hub to the blade tip. Axial flow fan for a refrigerator, characterized in that distributed as. The method of claim 1, The pitch angle of the blade is 37.5 ° to 38.5 ° at the blade hub, 24.5 ° to 25.5 ° at the blade tip, the axial flow fan for the refrigerator, characterized in that linearly distributed from the blade hub to the blade tip. The method of claim 1, The sweep angle of the blade is 0.0 ° at the blade hub, 37.0 ° at the blade tip, the axial flow fan for a refrigerator, characterized in that distributed from the blade hub to the blade tip in the form of a secondary parabola.