KR100315781B1 - Refrigerator spray fan - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cold air supply fan for supplying cold air sucked from an evaporator to a freezer compartment and a refrigerating compartment in a side by side type refrigerator, and in particular, to overcome the system resistance of a refrigerator at a low rotational speed. The present invention relates to a refrigerator fan for achieving a low noise while satisfying an air volume.

The four-flow refrigerator fan for achieving the above object includes a hub to which the motor shaft is connected, and a plurality of blades installed in the hub; The number of blades is four, and the inner and outer ratios, which are the ratio between the inner diameter and the outer diameter, are 0.2 to 0.3. The outside diameter is 135 ± 1 mm, the inside diameter is 30 ± 1 mm, the hub tilt angle is 20 ± 0.5 °, the blade forward distance is (26.0-26.5) ± 1 mm, and the blade back distance is (23.0-23.5). ) ± 1 mm. In addition, the maximum camber position of the blade is 0.68 to 0.73 uniformly distributed from the blade hub to the blade tip, the maximum camber ratio is 7.5 to 8.0% at the blade hub, 13.5 to 14.0% at the blade tip to blade tip to blade tip It is distributed linearly. In addition, the pitch angle of the blade is linearly distributed from the blade hub to the blade tip at 44.0 ° -45.0 ° at the blade hub and 31.0 ° -32.0 ° at the blade tip. In addition, the sweep angle of the blade is distributed in the form of a secondary parabola from the blade hub to the blade tip at 0.0 ° at the blade hub and 38.0 ° at the blade tip.

Description

Refrigerator fan for refrigerator

The present invention relates to a cold air supply fan for supplying cold air sucked from an evaporator to a freezer compartment and a refrigerating compartment in a side by side type refrigerator, and in particular, generates a quadrature that can be referred to as an intermediate step between axial flow and vortex flow. The present invention relates to a four-flow fan for refrigerators having a structure in which the number of blades is 4, the inner and outer ratios of the fan are 0.2 to 0.3, and the sweep angle, pitch angle, and camber amount of the blades are relatively large.

1 is a block diagram showing a structure of a typical side-by-side type refrigerator, Figure 2 is a block diagram showing a mounting structure of a general cold air supply fan, Figure 3 is a side view of the freezer compartment and the refrigerating compartment in a side-by-side type refrigerator (A) is a side view showing the cold air flow path of the freezer compartment, (b) is a configuration diagram showing the cold air flow paths of the freezer compartment and the refrigerating compartment in three dimensions, and (c) shows the cold air flow passage of the refrigerating compartment. The side view shown.

As shown in FIG. 1, a general side-by-side type refrigerator includes a freezing compartment 10 that is formed to extend in an up and down direction, a refrigerating chamber 20 that is coupled to a side surface of the freezing compartment 10 and formed to extend in an up and down direction. An evaporator (11 in FIG. 3) installed at an upper end of the freezer compartment 10 to provide cold air through heat exchange with a refrigerant, and suctioned cold air provided from the evaporator 11 to the freezer compartment 10 and the refrigerating compartment 20. It is comprised including the fan 13 for cold air supply which supplies.

Here, the cold air supply fan 13, as shown in Figure 2, is fixed to the rotating shaft of the drive motor 15 is operated according to whether the drive motor 15 is driven, the grill fan (front) 16 is installed to provide the cold air sucked through the grill pan 16 by the cold air supply fan 13 to the freezing compartment 10 and the refrigerating compartment 20.

In addition, a shroud 17 is provided outside the cold air supply fan 13 to protect the blade of the cold air supply fan 13.

In the side-by-side type refrigerator configured as described above, first, when cold air is formed through heat exchange with a refrigerant in the evaporator 11, the cooling air supply fan 13 is operated by the driving motor 15. The cold air supply fan 13 sucks cold air provided from the evaporator 11 and supplies the cold air to the grill pan 16, and the cold air passing through the grill pan 16 is provided to the freezing chamber 10 and the refrigerating chamber 20. 3, the respective parts of the freezing compartment 10 and the refrigerating compartment 20 are circulated, and then supplied to the evaporator 11 again along the flow path formed at the lower end of the refrigerator. Subsequently, as the above process is repeated continuously, the temperature distribution of the freezer compartment 10 and the refrigerating compartment 20 is maintained at a low temperature.

A conventional axial flow fan has conventionally been used for the cold air supply fan 13 for supplying cold air to the freezing compartment 10 and the refrigerating compartment 20 in the side by side type refrigerator. However, the axial fan is suitable for a top mount type refrigerator, but is not suitable for a side by side type refrigerator having a larger capacity than the top mount type refrigerator. This is because the side by side type refrigerator requires a fixed pressure fan than the axial flow fan because the system static pressure of the freezer compartment 10 and the refrigerating compartment 20 is high.

Here, most conventional axial flow fans have three blades, a fan blade tip of 98 to 132 mm, a sweep angle of 0 to 32 degrees, a pitch angle of 32 to 35 degrees, and a camber. The amount is 3 to 9%, and the internal and external expenses are formed at 0.23.

As described above, the conventional axial fan tends to have a relatively small sweep angle, pitch angle, and camber amount (Camber,%).

However, 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, the axial fan and shroud Since the static pressure of the passing fluid cannot be efficiently increased, the fan speed must be increased.

Therefore, in order to meet the fixed pressure system required by the side-by-side type refrigerator, the cold air supply fan having a structure capable of realizing low noise while satisfying the required air volume by overcoming the system resistance of the refrigerator at a low rotational speed 13 ) Is required.

The present invention has been made in order to solve the above problems, the number of blades is 4, the inner and outer ratio of the fan is 0.2 ~ 0.3 and the sweep angle of the blades to generate the four-way flow that can be said to be the intermediate step between the axial flow and the vortex It is an object of the present invention to provide a reflux fan for a refrigerator, which has a structure in which pitch angles and cambers are formed relatively large, thereby overcoming the system resistance of the refrigerator at a low rotational speed, thereby realizing low noise while satisfying the required air volume.

1 is a configuration diagram showing the structure of a typical side-by-side type refrigerator;

2 is a configuration diagram showing a mounting structure of a general cold air supply fan,

3 is a configuration diagram showing the cold air flow path of the freezer compartment and the refrigerating compartment, respectively, in a typical side by side type refrigerator;

(a) is a side view showing the cold air passage of the freezer compartment,

(b) is a block diagram showing three-dimensional cold air flow path of the freezer compartment and the refrigerating compartment,

(c) is a side view showing the cold air passage of the refrigerating compartment.

4 is a front view and a side view of a four-flow fan for a refrigerator according to the present invention;

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

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

51: Hub 55: Blade

ID: Inside Diameter OD: Outside Diameter

HA: Hub tilt angle FD: Blade forward distance

RD: Blade trailing edge 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 blades is four, and the inside and outside ratio of the ratio between the inner diameter and the outer diameter is provided with a refrigerator fan for the refrigerator 0.2 ~ 0.3.

Further, according to the second aspect of the present invention, the outer diameter is 135 ± 1 mm, the inner diameter is 30 ± 1 mm, the hub tilt angle is 20 ± 0.5 °, and the blade forward distance is (26.0 to 26.5) ± 1 mm. Blade trailing distance is (23.0-23.5) ± 1 mm.

Further, according to the third aspect of the present invention, the maximum camber position of the blade is 0.68-0.73, which is uniformly distributed from the blade hub to the blade tip, and the maximum camber ratio is 7.5-8.0% at the blade hub, and 13.5- at the blade tip. 14.0% 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 44.0 ° -45.0 ° at the blade hub and 31.0 ° -32.0 ° 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 38.0 ° at the blade tip.

The present invention configured as described above has the advantage of overcoming the system resistance of the refrigerator at low rotational speed and realizing low noise while satisfying the required air volume.

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

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

Referring to FIG. 4, the four-flow fan for the 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 is four, 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 inlet side of the hub 51.

More specifically, the outer diameter OD of the four-flow fan for refrigerators according to the present invention is 135 ± 1 mm, the inner diameter ID is 30 ± 1 mm, and the inner and outer ratio is 0.233. In addition, the hub inclination angle HA of the side surface of the hub 51 and the Z axis, which is a rotation axis in an arbitrary direction, is 20 ± 0.5 °, and the blade forward distance FD is (26.0 to 26.5) ± 1 mm. Posterior forward distance (RD) is (23.0-23.5) ± 1 mm. Here, the blade front leading distance (FD) and the blade rear leading distance (RD) means the distance on the axis of rotation, that is, 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). do.

In addition, the maximum camber position CP in the blade 55 is 0.68 to 0.73, and is uniformly distributed from the blade hub BH to the blade tip BT, and the maximum camber ratio is 7.5 to the blade hub BH. 8.0% and 13.5-14.0% at the blade tip BT are 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 44.0 ° ~ 45.0 ° at the blade hub (BH), 31.0 ° ~ 32.0 ° 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 0.0 ° at the blade hub BH, 38.0 ° at the blade tip BT, and is distributed in a secondary parabolic form from the blade hub BH to 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 6.0 mm, 15.0 mm, 13.0 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 6.0 ± 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 6.0 ± 1 mm to 15.0 ± 1 mm, and in the 0.75 to 0.997 section of the blade 55, the blade 55 ) The spacing in the second parabola form from 15.0 ± 1 mm to 13.0 ± 1 mm. Finally, in the 0.97 to 1.0 section including the blade tip (BT) is increased in the third parabolic form from 13.0 ± 1 mm to 27.0 ± 1 mm.

In short, the portions 15.0 mm and 13.0 mm of the spacing between the blades 55 are located at portions 0.75 and 0.97, 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 preferred form of the four-flow fan for refrigerators according to the present invention having the above-described dimensional distribution, the number of blades 55 is four, the outer diameter (OD) is 135 mm, the inner diameter (ID) is 30 mm, the hub The angle of inclination (HA) is 20 °, the blade front leading distance (FD) is 26.4 ± 1 mm, and the blade rear leading distance (RD) is 23.1 ± 1 mm. In addition, the maximum camber position CP of the blade 55 is uniformly distributed from the blade hub BH to the blade tip BT at 0.7, and the maximum camber ratio is 7.82% at the blade hub BH, and the blade tip ( BT), 13.82%, the linear distribution from blade hub (BH) to blade tip (BT). In addition, the sweep angle θ of the blade 55 forms a secondary parabolic distribution from the blade hub BH to the blade tip BT at 0 ° at the blade hub BH and 38.0 ° at the blade tip BT. , Pitch angle (ψ) is 44.37 ° at the blade hub (BH), 31.37 ° at the blade tip (BT) to form a linear distribution from the blade hub (BH) to 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).

As described above, the four-flow fan for the refrigerator of the present invention is installed in a side-by-side type refrigerator having the same capacity, and then the noise is measured, and the noise is significantly reduced in comparison with other products in the same cooling performance. .

4, the number of blades 55, the inner and outer ratio of the fan is 0.2 to 0.3, the sweep angle θ of the blade 55, the pitch angle ( ψ) and the camber amount are relatively large, respectively, and generate a four-flow, which is an intermediate stage between the axial flow and the vortex, so that the system resistance of the refrigerator can be overcome at a low rotational speed, thereby achieving low noise while satisfying the required air flow. .

Claims (5)

A hub connected to the motor shaft and a plurality of blades installed in the hub; The number of blades is four, the inside and outside ratio of the ratio of the inner diameter and the outer diameter (r) is a four-flow refrigerator fan, characterized in that 0.2 to 0.3. The method of claim 1, The outside diameter is 135 ± 1mm, the inside diameter is 30 ± 1mm, the hub tilt angle is 20 ± 0.5 °, the blade forward distance is (26.0 ~ 26.5) ± 1mm, and the blade backward distance is (23.0 ~ 23.5) ± A refrigerator fan for refrigerators, characterized in that 1mm. The method of claim 1, The maximum camber position of the blade is 0.68 to 0.73, which is uniformly distributed from the blade hub to the blade tip, and the maximum camber ratio is 7.5 to 8.0% at the blade hub and 13.5 to 14.0% at the blade tip, which is linear from the blade hub to the blade tip. Four-flow fan for the refrigerator, characterized in that the distribution. The method of claim 1, The pitch angle of the blade is 44.0 ° to 45.0 ° in the blade hub, 31.0 ° to 32.0 ° in the blade tip is a four-flow refrigerator fan, characterized in that linearly distributed from the blade hub to the blade tip. The method of claim 1, Sweep angle of the blade is 0.0 ° at the blade hub, 38.0 ° at the blade tip of the four-sided fan for refrigerator, characterized in that distributed from the blade hub to the blade tip in the form of a secondary parabola.