TWI891495B - Cooling fan - Google Patents

Abstract

A cooling fan is used to solve the problem of insufficient air intake of conventional cooling fans. Includes: a fan frame with a base, one side wall connected to the base, a cover plate connected to the side wall, the cover plate opposite to the base, the cover plate has an air inlet, the base, the side wall and the cover together form an air outlet; a fan wheel is rotatably located in the fan frame, and the fan frame has an air duct; at least one pressurizing body is adjacent to the air duct, and the at least one pressurizing body has an air guide surface; and an air flow channel located in the fan frame, the air flow channel is axially aligned with the at least one pressurizing body, and the air flow channel extends radially to the air guide surface to communicate with the air channel , the airflow channel extends radially toward the side wall to connect the side wall. This can improve the cooling efficiency of the cooling fan.

Description

cooling fan

The present invention relates to a fan device, and more particularly to a heat dissipation fan for assisting electronic devices in dissipating heat.

Referring to FIG. 1 , a conventional heat dissipation fan 9 is shown. This conventional heat dissipation fan 9 comprises a housing 91 having an axial air inlet 92 and a radial air outlet 93. A fan wheel 94 is rotatably positioned within the housing 91. Rotation of the fan wheel 94 drives airflow axially from the axial air inlet 92 into the housing 91 and out through the radial air outlet 93. The airflow path of the heat dissipation fan 9 has a pressurized region 95 . Within this pressurized region 95 , a relatively narrow gap is formed between the fan wheel 94 and the inner wall of the housing 91 , allowing the airflow entering through the axial air inlet 92 to be compressed as the fan wheel 94 rotates.

Typically, a protrusion 96 is provided at the starting point of the pressurized zone 95. This protrusion 96 protrudes from the inner wall of the housing 91 toward the impeller 94. This creates a narrow gap between the protrusion 96 and the impeller 94, allowing the airflow to be pressurized by the protrusion 96. However, this narrow gap between the protrusion 96 and the impeller 94 reduces the amount of air entering the axial air inlet 92 at the location of the protrusion 96, resulting in insufficient air intake.

In view of this, conventional heat dissipation fans still need to be improved.

To solve the above-mentioned problem, the present invention aims to provide a heat dissipation fan that can increase the axial air intake volume.

Throughout this disclosure, directional terms or similar terms, such as "front," "rear," "left," "right," "upper (top)," "lower (bottom)," "inner," "outer," and "side," are primarily used with reference to the accompanying drawings. These directional terms or similar terms are intended solely to facilitate description and understanding of the various embodiments of the present invention and are not intended to limit the present invention.

The use of the quantifiers "a" or "an" in the elements and components described throughout this invention is merely for convenience and to provide a general understanding of the scope of the invention. They should be interpreted in this invention to include one or at least one, and the singular concept also includes the plural, unless it is obvious that it means otherwise.

Throughout this invention, similar terms such as "combination," "assembly," or "assembly" primarily encompass connection types that allow for separation without damaging the components, or connection types that render the components inseparable. Those skilled in the art will be able to select the appropriate type based on the materials of the components to be connected or the assembly requirements.

The heat dissipation fan of the present invention comprises: a fan frame having a base, a sidewall connected to the base, and a cover connected to the sidewall, the cover opposing the base and having an air inlet. The base, the sidewall, and the cover together form an air outlet; a fan wheel rotatably disposed within the fan frame, the fan frame having an air duct; at least one pressurizing element adjacent to the air duct, the at least one pressurizing element having a guide surface facing the fan wheel; and an airflow channel disposed within the fan frame, the airflow channel axially opposite the at least one pressurizing element, extending radially to the guide surface to connect to the air duct, and further extending radially toward the sidewall to connect to the sidewall.

Accordingly, the heat dissipation fan of the present invention utilizes an airflow channel axially aligned with the at least one pressurizing element. The airflow channel radially extends to the guide surface to connect to the air duct. This allows airflow introduced through the air inlet to not only enter the air duct but also to be accommodated by the airflow channel. This allows more airflow to enter through the air inlet, thereby increasing the airflow volume entering the air inlet and improving the heat dissipation efficiency of the heat dissipation fan.

The fan frame has a reference plane that passes through the geometric center of the air inlet and is radially perpendicular to the air outlet. This plane divides the air duct into a high-pressure zone and a strong wind zone according to the direction of rotation of the impeller. The pressurizing body is located in the high-pressure zone. This allows the air duct to transition from high pressure to low pressure as it moves from the high-pressure zone toward the strong wind zone, achieving a continuous flow from the air inlet to the air outlet.

The at least one pressurizing element is located adjacent to the air outlet. This forms the starting point of the air duct, thereby creating a longer air duct and increasing air volume.

There is a first axial distance between the base and the cover plate, the total axial thickness of the at least one pressurizing element is greater than or equal to 50% of the first axial distance, and the total axial thickness of the at least one pressurizing element is less than the first axial distance. In this way, the at least one pressurizing element can achieve a better pressurizing effect.

There is a first axial distance between the base and the cover, and the airflow channel has a second axial distance that is less than or equal to 50% of the first axial distance and not zero. This prevents the airflow channel from being too large, thereby affecting the effectiveness of the at least one supercharging body in supercharging.

The second axial distance is a constant value. This allows the airflow channel to accommodate more incoming airflow, thereby allowing more airflow to enter through the air inlet.

The impeller has a plurality of blades, each having a second axial thickness. The second axial distance of the airflow channel is greater than or equal to 80% of the second axial thickness and less than the first axial distance. This facilitates the entry of air into the airflow channel.

The at least one pressure booster is provided in two pieces, one on the base and one on the cover, with the airflow channel located between the two. This allows the pressure booster to achieve a superior pressure boosting effect while also further increasing the airflow volume entering the air inlet.

The two pressure boosters have the same first axial thickness. This allows the two pressure boosters to achieve a better pressure boosting effect.

The two pressurizing bodies are aligned in the axial direction. Thus, the two pressurizing bodies can jointly form the airflow channel.

The airflow channel radially expands from the guide surface toward the sidewall. This further reduces eddy currents and the noise caused by them.

The airflow channel tapers radially from the guide surface toward the sidewall. This further reduces eddy currents and the noise caused by them.

The at least one pressurizing body is located on the base, and the airflow channel is located between the at least one pressurizing body and the cover. This allows the pressurizing body to achieve a better pressurization effect and further increase the air volume entering the air inlet.

The airflow channel radially converges or expands from the guide surface toward the side wall. This can further increase the air intake volume of the air inlet and reduce the noise caused by vortex flow.

The at least one pressure booster is located on the cover, and the airflow channel is located between the at least one pressure booster and the base. This allows the pressure booster to achieve a better pressure boosting effect and further increase the air volume entering the air inlet.

The airflow channel radially converges or expands from the guide surface toward the sidewall. This can further increase the airflow volume of the air inlet and reduce noise caused by vortex flow.

[The present invention]

1: Fan frame

11: Base

12: Sidewall

13: Cover plate

14: Air Inlet

15: Air outlet

16: Axle tube

17: Stator

2: Fan wheel

21: Wheel Hub

22: Leaves

23: Axis

3: Supercharger

31: Diversion surface

31a: First end

31b: Second end

4: Airflow Channels

D: Rotation direction

F: Cooling fan

R: Air Duct

R1: High pressure area

R2: Strong wind area

S: Datum plane

O: Geometric Center

H: radial spacing

H1: First axial distance

H2: Second axial distance

M1: First axial thickness

M2: Second axial thickness

[Practice]

9: Cooling fan

91: Shell

92: Axial air inlet

93: Radial air outlet

94: Fan wheel

95: Boost Zone

96: Protrusion

[Figure 1] A diagram of a common heat dissipation fan.

[Figure 2] Exploded perspective view of the first embodiment of the present invention.

[Figure 3] Side view of the first embodiment of the present invention.

[Figure 4] Front view of the assembly of the first embodiment of the present invention.

[Figure 5] Sectional view along line A-A in Figure 4.

[Figure 6] The booster body of the second embodiment of the present invention is located on the base.

[Figure 7] The booster body of the second embodiment of the present invention is located on the cover plate.

[Figure 8] A diagram showing the airflow channel of the third embodiment of the present invention gradually expanding toward the side wall.

[Figure 9] A zoomed-out view of the airflow channel toward the side wall of the third embodiment of the present invention.

[Figure 10] The booster body of the fourth embodiment of the present invention is located on the base.

[Figure 11] The booster body of the fourth embodiment of the present invention is located on the cover plate.

To make the above and other objects, features, and advantages of the present invention more clearly understood, the following provides a detailed description of the preferred embodiments of the present invention with reference to the accompanying drawings. Furthermore, elements marked with the same symbols in different drawings are considered identical and their descriptions will be omitted.

Please refer to Figures 2 and 3, which illustrate a first embodiment of the heat dissipation fan F of the present invention. The fan comprises a fan frame 1, a fan wheel 2, at least one pressurizing element 3, and an airflow channel 4. The fan wheel 2 is rotatably mounted within the fan frame 1, and the at least one pressurizing element 3 and the airflow channel 4 are located within the fan frame 1.

The fan frame 1 has a base 11 and a sidewall 12. The sidewall 12 is connected to the base 11. For example, the sidewall 12 can be integrally formed with the base 11. The fan frame 1 also has a cover 13 connected to the sidewall 12. The cover 13 can be integrally formed with the sidewall 12 and can face the base 11. The fan frame 1 has an air inlet 14 located on the cover 13. The base 11, the sidewall 12, and the cover 13 together form an air outlet 15. The base 11 has a shaft 16, and a stator 17 is located on the outer periphery of the shaft 16.

As shown in Figures 2 and 4 , the impeller 2 may include a hub 21 and a plurality of blades 22 disposed around the hub 21. The impeller 2 may include a rotating shaft 23, one end of which may be coupled to and positioned on the hub 21, and the other end of which may be located on the shaft tube 16. An air duct R may be defined within the fan frame 1 along a rotational direction D of the impeller 2, connecting the air inlet 14 and the air outlet 15. Thus, the impeller 2 can rotate to direct airflow from the air inlet 14 into the air duct R of the fan frame 1, and then out through the air outlet 15.

Continuing with Figures 3 and 4, the fan frame 1 has a virtual reference plane S that passes through the geometric center O of the air inlet 14 and is radially perpendicular to the air outlet 15. Based on the rotation direction D of the impeller 2 (counterclockwise in Figure 4), the reference plane S can sequentially divide the air duct R into a high-pressure region R1 and a strong wind region R2. Furthermore, the air duct R can radially expand from the high-pressure region R1 toward the strong wind region R2, and from the high-pressure region R1 to the strong wind region R2, a high-pressure to low-pressure region can be formed. In this way, a pressure difference can be generated by the radially expanding air duct R, allowing airflow to be continuously introduced through the air inlet 14 and discharged through the air outlet 15.

The at least one pressurizing element 3 is located within the fan frame 1 and connected to the sidewall 12. Together, the at least one pressurizing element 3 and the sidewall 12 form a radial distance H with the impeller 2, thereby forming the air duct R. The at least one pressurizing element 3 can be located within the high-pressure region R1 to generate high wind pressure. Thus, the at least one pressurizing element 3 can form the starting point of the air duct R. Preferably, the at least one pressurizing element 3 can be located adjacent to the air outlet 15 of the high-pressure region R1. This formation of the starting point of the air duct R by the at least one pressurizing element 3 creates a longer air duct R, thereby increasing airflow.

The at least one supercharger 3 may have a guide surface 31. This guide surface 31 faces the impeller 2, that is, radially toward the plurality of blades 22. A radial distance H is formed between the guide surface 31 and the impeller 2, allowing the airflow entering the air inlet 14 to be initially pressurized by the at least one supercharger 3. Furthermore, the guide surface 31 extends radially generally along the rotational direction D of the impeller 2. Preferably, the guide surface 31 has a first end 31a and a second end 31b, sequentially along the rotational direction D of the impeller 2. The radial distance H between the guide surface 31 and the impeller 2 may gradually increase from the first end 31a toward the second end 31b. That is, the first end 31a has a minimum radial distance H from the impeller 2, and the second end 31b is connected to the sidewall 12. Consequently, the at least one pressurizing element 3 and the sidewall 12 can form a gradually expanding air duct R with the impeller 2, thereby generating a pressure difference.

Continuing with FIG. 5 , the number of the at least one pressurizing body 3 can be adjusted as needed. For example, the number of the at least one pressurizing body 3 can be one, two, or even more, and the present invention is not limited thereto. In this embodiment, there are two at least one pressurizing body 3 , one located on the base 11 and the other on the cover 13 . The two pressurizing bodies 3 can be aligned axially and each have a first axial thickness M1 . The first axial thickness M1 of the two pressurizing bodies 3 can be the same, or different. Furthermore, a first axial distance H1 can be defined between the base 11 and the cover 13. The total axial thickness of the at least one booster 3 is greater than or equal to 50% of the first axial distance H1, and the total axial thickness of the at least one booster 3 is less than the first axial distance H1. For example, in this embodiment, the total thickness 2×M1 of the two boosters 3 is greater than or equal to 50% of the first axial distance H1. This ensures that the two boosters 3 achieve a better boosting effect. Preferably, the first axial thickness M1 can be 1-1.1 mm, and the first axial distance H1 can be 3.8-4.2 mm.

The airflow channel 4 is located between the base 11 and the cover 13. It is axially aligned with the at least one pressurizing element 3. The airflow channel 4 extends radially to the guide surface 31 of the at least one pressurizing element 3 to connect to the air duct R. The airflow channel 4 can also extend radially toward the sidewall 12 to connect to the sidewall 12. In this way, when the airflow from the air inlet 14 enters the air duct R adjacent to the at least one supercharger 3, it can then enter the airflow channel 4. That is, after being introduced through the air inlet 14, the airflow not only enters the air duct R, but also further accommodates the incoming airflow through the airflow channel 4, thereby allowing more airflow to enter through the air inlet 14 and increasing the air intake volume of the air inlet 14. Furthermore, the airflow channel 4 can disrupt the vortex at the front ends of the plurality of blades 22, thereby reducing the noise caused by the vortex.

In this embodiment, the airflow channel 4 can be located between the two superchargers 3. The airflow channel 4 has a second axial distance H2. The second axial distance H2 can be set to a certain value so that the second axial distance H2 is equidistant, that is, the distance between the two superchargers 3 is equidistant. It is worth noting that the second axial distance H2 is less than or equal to 50% of the first axial distance H1 and is not zero. This prevents the airflow channel 4 from being too large and affecting the supercharging effect of the at least one supercharger 3. Furthermore, the plurality of blades 22 have a second axial thickness M2, and the second axial distance H2 of the airflow channel 4 is greater than or equal to 80% of the second axial thickness M2 of the plurality of blades 22, and the second axial distance H2 is less than the first axial distance H1. Furthermore, in this embodiment, the second axial thickness M2 can be the distance from the upper edge, including the connecting ring, to the lower edge of each blade 22. In this manner, the airflow channel 4 can facilitate the entry of airflow. Accordingly, the present invention, while achieving a superior supercharging effect through the at least one supercharging body 3, can also further increase the airflow volume entering the air inlet 14 through the airflow channel 4. Preferably, the second axial distance H2 can be 2-2.1 mm, and the second axial thickness M2 can be 2.4 mm.

Please refer to Figures 6 and 7, which illustrate a second embodiment of the heat dissipation fan F of the present invention. In this embodiment, the supercharger 3 is a single unit. The supercharger 3 can be positioned within the base 11 (as shown in Figure 6), with the airflow channel 4 positioned between the supercharger 3 and the cover 13. Alternatively, the supercharger 3 can be positioned within the cover 13 (as shown in Figure 7), with the airflow channel 4 positioned between the supercharger 3 and the base 11. In this manner, the supercharger 3 can achieve a superior pressure boosting effect while further increasing the airflow volume entering the air inlet 14 through the airflow channel 4. Furthermore, the airflow channels 4 can be equidistant in the axial direction, that is, the pressure booster 3 and the cover plate 13 are equidistant, or the pressure booster 3 and the base 11 are equidistant.

Please refer to Figures 8 and 9, which illustrate a third embodiment of the heat dissipation fan F of the present invention. This embodiment is substantially similar to the first embodiment described above. In this embodiment, the two pressurizing bodies 3 are located on the base 11 and the cover 13, respectively. The airflow channel 4 can be located between the two pressurizing bodies 3. The airflow channel 4 can radially expand from the guide surface 31 toward the side wall 12 (as shown in Figure 8), or it can radially converge from the guide surface 31 toward the side wall 12 (as shown in Figure 9). In this way, the airflow channel 4 can further reduce the generation of vortexes, thereby further reducing the noise caused by vortexes.

Please refer to Figures 10 and 11, which show a fourth embodiment of the heat dissipation fan F of the present invention. This embodiment is substantially the same as the second embodiment described above. In this embodiment, the supercharger 3 is a single supercharger 3, which can be located on the base 11, so that the airflow channel 4 is located between the supercharger 3 and the cover plate 13. The airflow channel 4 can radially form a gradual contraction (as shown in Figure 10) or gradual expansion from the guide surface 31 toward the side wall 12. Alternatively, the booster 3 can be located on the cover plate 13, with the airflow channel 4 located between the booster 3 and the base 11. The airflow channel 4 can radially converge (as shown in Figure 11) or expand from the guide surface 31 toward the sidewall 12. This can further increase the airflow volume of the air inlet 14 and reduce noise caused by vortex flow.

In summary, the heat dissipation fan of the present invention utilizes an airflow channel axially aligned with the at least one pressurizing element. The airflow channel radially extends to the guide surface to connect to the air duct. Thus, after airflow is introduced through the air inlet, it not only enters the air duct but also further accommodates the incoming airflow through the airflow channel. This allows more airflow to enter through the air inlet, thereby increasing the airflow volume entering the air inlet and improving the heat dissipation efficiency of the heat dissipation fan.

Although the present invention has been disclosed using the preferred embodiments described above, they are not intended to limit the present invention. Any modifications and alterations made by one skilled in the art without departing from the spirit and scope of the present invention are within the technical scope protected by the present invention. Therefore, the scope of protection of the present invention includes all modifications within the meaning and equivalent scope of the appended patent claims. Furthermore, if the above-mentioned embodiments can be combined, the present invention encompasses any combination of these embodiments.

1: Fan frame

11: Base

12: Sidewall

13: Cover plate

14: Air Inlet

15: Air outlet

16: Axle tube

17: Stator

2: Fan wheel

21: Wheel Hub

22: Leaves

23: Axis

3: Supercharger

31: Diversion surface

31a: First end

31b: Second end

F: Cooling fan

Claims (16)

A heat dissipation fan comprises: A fan frame having a base, a sidewall connected to the base, a cover connected to the sidewall, the cover opposing the base and having an air inlet, the base, the sidewall, and the cover together forming an air outlet; A fan wheel rotatably positioned within the fan frame, the fan frame having an air duct; At least one booster body adjacent to the air duct, the at least one booster body having a guide surface facing the fan wheel; and An airflow channel is located in the fan frame. The airflow channel is axially opposite to the at least one pressurizing body. The airflow channel radially extends to the guide surface to connect to the air duct. The airflow channel also radially extends toward the sidewall to connect to the sidewall. As in claim 1, the heat dissipation fan, wherein the fan frame has a reference plane, the reference plane passes through a geometric center of the air inlet, the reference plane is radially perpendicular to the air outlet, and the reference plane divides the air duct into a high-pressure zone and a strong wind zone in sequence according to a rotation direction of the fan wheel, and the booster is located in the high-pressure zone. The heat dissipation fan of claim 2, wherein the at least one pressurizing body is adjacent to the air outlet. As in claim 1, the heat dissipation fan, wherein there is a first axial distance between the base and the cover, the total axial thickness of the at least one pressurizing body is greater than or equal to 50% of the first axial distance, and the total axial thickness of the at least one pressurizing body is less than the first axial distance. As in claim 1, the heat dissipation fan, wherein the base and the cover have a first axial distance, the airflow channel has a second axial distance, and the second axial distance is less than or equal to 50% of the first axial distance and is not zero. The heat dissipation fan of claim 5, wherein the second axial distance is a constant value. The heat dissipation fan of claim 1, wherein the fan wheel has a plurality of blades, the plurality of blades have a second axial thickness, and the second axial distance of the airflow channel is greater than or equal to 80% of the second axial thickness. As in claim 1, the heat dissipation fan comprises two at least one pressurizing body, the two pressurizing bodies are located on the base and the cover respectively, and the air flow channel is located between the two pressurizing bodies. A heat dissipation fan as claimed in claim 8, wherein the two pressurizing bodies have the same first axial thickness. As in claim 8, the heat dissipation fan, wherein the two pressurizing bodies are aligned in the axial direction. As in claim 8, the heat dissipation fan, wherein the air flow channel gradually expands radially from the guide surface toward the side wall. As in claim 8, the heat dissipation fan, wherein the air flow channel is radially tapered from the guide surface toward the side wall. As in claim 1, the heat dissipation fan, wherein the at least one pressurizing body is located on the base, and the air flow channel is located between the at least one pressurizing body and the cover plate. As in claim 13, the heat dissipation fan, wherein the air flow channel is radially formed to gradually converge or expand from the guide surface toward the side wall. As in claim 1, the heat dissipation fan, wherein the at least one pressurizing body is located on the cover plate, and the air flow channel is located between the at least one pressurizing body and the base. As in claim 15, the heat dissipation fan, wherein the air flow channel is radially formed to gradually converge or expand from the guide surface toward the side wall.