CN110291296B

CN110291296B - Cooling fan and seat cooling device with same

Info

Publication number: CN110291296B
Application number: CN201880009018.4A
Authority: CN
Inventors: 金炳秀
Original assignee: Amotech Co Ltd
Current assignee: Amotech Co Ltd
Priority date: 2017-03-17
Filing date: 2018-03-15
Publication date: 2022-01-28
Anticipated expiration: 2038-03-15
Also published as: CN110291296A; WO2018169316A1

Abstract

The cooling fan of the present invention includes: a fan housing having an air inlet formed in a front surface thereof for allowing air to flow therein and an air outlet formed in a side surface thereof for discharging the air; and an impeller installed in the fan housing to allow air to flow in an axial direction and to discharge the air in a radial direction, wherein a bypass passage for discharging the air moving in a reverse direction toward the air discharge port to the outside is formed at an edge of the air inlet, and the air moving in the reverse direction is discharged to the outside to minimize noise generation and improve air blowing efficiency when the cooling fan is at a high power.

Description

Cooling fan and seat cooling device with same

Technical Field

The present invention relates to a cooling fan that performs a cooling function and a seat cooling device having the same.

Background

Currently, a vehicle seat mainly uses a cooling seat that can cool the seat in summer. The cooling seat is provided with a seat cooling device comprising a cooling fan.

In addition, in order to prevent overheating of electronic products or lighting devices, a cooling fan is mainly used, which performs cooling by rotating blades driven by a motor to blow air, and when the power is high, the amount of air discharged to an air discharge port is rapidly increased or a load that impedes the flow of air is generated, and thus, wind pressure is increased, which generates noise and causes an overload on the motor.

In order to solve such a noise problem, as shown in korean utility model laid-open publication No. 20-0332249 (27/10/2003), a conventional centrifugal blower is provided with an impeller connected to a rotary shaft in a casing having an air inlet and an air outlet, a head wind prevention plate is provided at an upper end between the impeller and the air inlet, and a head wind prevention ring is provided in a connecting space between the impeller and the air inlet, thereby preventing generation of head wind and reducing noise.

In the conventional centrifugal blower, when the power is low, the air discharged in the radial direction is smoothly discharged through the air discharge port, and the reverse flow of the air is prevented by the reverse flow preventing plate.

However, when the output power is high, if the amount of air to be discharged is increased or if the flow of air is obstructed by a load on the air outlet side, a part of the air does not flow in the reverse direction but flows in the opposite direction, and collides with the air discharged to the air outlet, thereby generating noise and lowering the air blowing efficiency, and the motor is overloaded.

Disclosure of Invention

Technical problem

An object of the present invention is to provide a cooling fan and a seat cooling apparatus having the same, which can minimize noise and prevent overload of a motor by bypassing air moving in a reverse direction among air discharged to an air discharge port due to high power or occurrence of a phenomenon of blocking air flow to the outside.

Another object of the present invention is to provide a cooling fan and a seat cooling apparatus having the same, which can minimize noise and improve air blowing efficiency by removing a socket formed at an air inflow port.

Means for solving the problems

The cooling fan of the present invention may include: a fan housing having an air inlet formed in a front surface thereof for allowing air to flow therein and an air outlet formed in a side surface thereof for discharging the air; and an impeller installed in the fan housing, for allowing air to flow in an axial direction and discharging the air in a radial direction, and forming a bypass passage at an edge of the air inlet, thereby discharging the air moving in a direction opposite to the air outlet to the outside.

In the fan housing, an air suction passage for sucking air may be formed inside the impeller, an air discharge passage for discharging air may be formed outside the impeller, and the bypass passage may communicate with the air discharge passage.

The bypass passage may be extended in an outer direction at an edge of the air inlet port to expose the air discharge passage to the outside.

The bypass passage may be connected to support ribs radially formed at the air inflow port, so that the bypass passage is divided into a plurality of regions.

The bypass passage may be formed at a predetermined interval in a circumferential direction at an edge of the air inlet, and may be formed in a range of 90 degrees to 180 degrees at a position where the air outlet is formed.

The bypass passage may be formed at an edge of the air inlet port with a predetermined interval in a range of 360 degrees.

The bypass passage may include: a first bypass passage portion disposed at a position close to the air discharge port and exposing the air discharge passage; and a second bypass passage portion disposed on a remaining edge of the circumferential edge of the air inlet port, excluding the first bypass passage portion, and having an area smaller than that of the first bypass passage portion, so as to prevent the air discharge passage from being exposed.

The bypass passages may be formed at 2 to 6 intervals in the circumferential direction at the edge of the air inlet.

The bypass passage may be formed as a first bypass passage at a predetermined interval in a circumferential direction at an edge of the air inlet, and a second bypass passage may be formed between the first bypass passages, the second bypass passage having an area smaller than that of the first bypass passage.

ADVANTAGEOUS EFFECTS OF INVENTION

As described above, the cooling fan according to the present invention can prevent noise from being generated due to the flow of air being blocked and improve air blowing efficiency by forming the bypass passage at the edge of the air inflow port of the fan housing to discharge the air moving in the reverse direction to the outside.

Further, the socket formed at the air inlet can be removed, and the bypass passage communicated with the air discharge passage can be formed at a predetermined interval along the circumferential direction of the air inlet, thereby minimizing noise and improving air blowing efficiency.

Drawings

Fig. 1 is a perspective view of a cooling fan according to a first embodiment of the present invention.

Fig. 2 is a sectional view of a cooling fan according to a first embodiment of the present invention.

Fig. 3 is a plan view of a fan housing showing a bypass passage of a first embodiment of the present invention.

Fig. 4 is a plan view of a fan housing showing a bypass passage of a second embodiment of the present invention.

Fig. 5 is a plan view of a fan housing showing a bypass passage of a third embodiment of the present invention.

Fig. 6 is a plan view of a fan housing showing a bypass passage of a fourth embodiment of the present invention.

Fig. 7 is a plan view of a fan housing showing a bypass passage of a fifth embodiment of the present invention.

Fig. 8 is a plan view of a fan housing showing a bypass passage of a sixth embodiment of the present invention.

Fig. 9 is a side view of the seat cooling apparatus of the present invention.

Fig. 10 is a sectional view of the seat cooling device of the present invention.

Fig. 11 is a graph comparing the relationship between the RPM and the air blowing amount of the cooling fan of the present invention and the general cooling fan.

Detailed Description

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. In this process, the sizes, shapes, and the like of the constituent elements shown in the drawings may be exaggerated for clarity and convenience of description. Also, terms specifically defined in consideration of the structure and action of the present invention may be changed according to the intention or custom of a user or an operator. The definitions for such terms are defined throughout this specification.

Referring to fig. 1 and 2, the cooling fan of the present invention includes: a fan housing 10 having an air inlet 14 formed in a front surface thereof for allowing air to flow therein and an air outlet 18 formed in a side surface 16 thereof for discharging air; and a fan unit 20 installed inside the fan housing 10 for generating a wind force.

The fan unit 20 is a fan that causes air to flow in an axial direction and discharges the air in a radial direction, and includes: a rotary shaft 42 rotatably supported by a support portion 40 formed at the fan housing 10; a stator 50 fixed to the outer circumferential surface of the support portion 40 and to which power is applied; a rotor 60 fixed to the rotary shaft 42 and rotating together with the rotary shaft 42; and an impeller 70 integrally formed with the rotor 60 and the rotary shaft 42, for sucking air in an axial direction and discharging the air in a radial direction.

The stator 50 includes: a stator core 52 fixed to the outer peripheral surface of the support portion 40; and a coil 54 wound around stator core 52 and supplied with power.

The rotor 60 includes: a magnet 62 formed in a ring shape on the outer peripheral surface of the stator 50 with a predetermined gap therebetween; and a rotor support 64, which fixes the magnet 62, and is formed integrally with the rotary shaft 42 and the impeller 70.

A first bearing 44 and a second bearing 46 are mounted inside the support portion 40 to rotatably support the rotary shaft 42.

The impeller 70 includes: a hub 72 integrally formed with the rotor support body 64; blades 74 formed along the circumferential direction on the outer circumferential surface of the hub 72 for generating a wind force; and a ring portion 76 formed in a ring shape at the edge of the vane 74 for discharging air.

When the impeller 70 rotates as described above, air is sucked in the axial direction and discharged in the radial direction through the ring portion 76.

Support ribs are formed radially at the air inlet 14 formed on the front surface 12 of the fan housing 10 to protect the impeller 76. An air outlet 18 for discharging air in a radial direction is formed in the side surface 16 of the fan cover 10.

When the impeller 70 rotates, the cooling fan described above causes air to flow in the axial direction through the air inlet 14 and discharges the air in the radial direction of the impeller 70. Therefore, the inside of the fan housing 10 is divided into an air intake passage 80 and an air discharge passage 82, the air intake passage 80 corresponds to the inner portion of the impeller and sucks air, and the air discharge passage 82 corresponds to the outer portion of the impeller and discharges air.

This cooling fan sucks air in the axial direction through the air inlet 14 and discharges the air in the radial direction through the air outlet 18. In this case, when the cooling fan is at low power, the flow of air is not so large that the air flows smoothly and noise is not generated due to the flow of air being blocked.

However, when the cooling fan is at a high output or the flow of air is blocked, the amount of air flowing into the air inlet 14 increases, but the amount of air discharged into the air outlet 18 decreases, and a part of the air flows into the housing 10 in the reverse direction due to the flow of air being blocked.

In this case, the air discharged through the air discharge port 18 collides with the air moving in the opposite direction to the air discharge port 18 to generate noise, thereby reducing the blowing efficiency. In particular, in the case where a cooling fan is provided in a cooling seat of a vehicle, air blown by the cooling fan is blocked in the process of blowing air to a fabric seat or in the process of passing through a filter, and noise is increased due to the blocking of the air flow.

In the present embodiment, when at low power, all air is discharged through the air discharge port 18, thereby preventing a reduction in the amount of blown air, and in the case of at high power or an air flow obstruction, reversely moving air is discharged to the outside to maintain the blowing performance and the bypass passage 90 is provided at the edge of the air inflow port 14 of the fan housing 10 to minimize noise generation.

When the cooling fan is at low power, the bypass passage 90 of the present invention prevents the air discharged to the air outlet 18 from flowing into the bypass passage 90 to maintain the air blowing performance, and reduces noise by discharging only the air moving in the reverse direction through the bypass passage 90.

The bypass passage 90 is formed in the front face 12 of the fan housing 10 so as to communicate with the air discharge passage 82 of the fan housing 10, so that the air moving in the reverse direction is bypassed in the axial direction.

The bypass passage 90 is formed at the edge of the air inlet 14, and is spaced apart by a distance L on the outer surface of the impeller 70 so as to communicate with the air discharge passage 82 of the fan housing 10, thereby exposing the air discharge passage 82 to the outside. That is, the bypass passage 90 is formed in the outer direction on the outer surface of the impeller 70, and the air discharge passage 82 is exposed to discharge the air moving in the opposite direction to the outside through the bypass passage 90.

The bypass passage 90 is connected to support ribs radially formed at the air inlet 14, and the bypass passage 90 is divided into a plurality of regions.

The cooling fan causes air to flow in the axial direction through an air inlet 14 formed in the front surface 12 of the fan housing 10, and discharges the air in the radial direction through an air outlet 18 formed in a side surface 16 of the fan housing 10. Therefore, at low power, the force of the air discharged in the radial direction acts on the air in the constant pressure region 82 of the fan cover 10, so that the air is not discharged to the bypass passage 90 formed in the axial direction of the fan cover 10, and even if the air is discharged, the amount of the discharged air does not affect the amount of the blown air.

When the cooling fan is at a high power or a load is applied to the air outlet side, a flow resistance occurs at the air outlet 18, and a part of the air discharged to the air outlet 18 flows in the reverse direction into the fan housing 10. In this case, the air moving in the reverse direction is discharged in the axial direction through the bypass passage 90 formed in the front surface of the fan housing 10, so that noise generated by collision with the air moving in the forward direction of the air outlet 18 is minimized and a reduction in the air volume due to flow resistance can be prevented.

As shown in fig. 3, the bypass passage 90 of the first embodiment is formed at a predetermined interval in the circumferential direction at the edge of the air inlet 14, and is formed in a range of 90 to 180 degrees from the vicinity of the air outlet 18.

That is, the bypass passage 90 of the first embodiment is expanded outward at the edge of the air inlet 14, and the air discharge passage 82 of the fan cover 10 is exposed to the outside.

As described above, the bypass passage 90 of the first embodiment is formed only in the position near the air discharge port 18 for discharging the air flowing in the reverse direction at the air discharge port.

As shown in fig. 4, the

bypass passages

92, 94 of the second embodiment include: a first bypass passage portion 94 formed at a predetermined interval in a position close to the air outlet 18 and exposing the air outlet passage 82 to the outside; and a second bypass passage portion 92 formed at an edge other than the first bypass passage portion 94 among the circumferential edges of the air inflow port 14, and having an area smaller than that of the first bypass passage portion 94, to prevent the air discharge passage 82 from being exposed.

The first bypass passage portion 94 may be formed in a range of 90 to 180 degrees near the air outlet 18.

The first bypass passage portion 94 functions in the same manner as the bypass passage 90 described in the first embodiment, and the area of the second bypass passage portion 92 is smaller than that of the first bypass passage portion 94, so that the air suction area is expanded, and the air that has not been discharged to the first bypass passage portion 94 but has moved to the air suction passage 80 of the fan housing 10 can be discharged for the second time.

As shown in fig. 5, the bypass passage 96 of the third embodiment is formed at predetermined intervals in the circumferential direction on the entire 360-degree surface of the edge of the air inlet 14, and the area of the bypass passage 90 described in the first embodiment is increased to improve the bypass efficiency of the air moving in the reverse direction.

As shown in fig. 6, the

bypass passages

102, 104 of the fourth embodiment include: a first bypass passage portion 104 formed at a position close to the air outlet 18 and preventing the air discharge passage 82 from being exposed to the outside; and a second bypass passage portion 102 formed at a remaining edge other than the first bypass passage portion 104, of the circumferential edge of the air inflow port 14, with an area larger than that of the first bypass passage portion 104, to prevent the air discharge passage 82 from being exposed to the outside next.

As shown in fig. 7, the number of the bypass passages 150 of the fifth embodiment is 2 to 6 at equal intervals in the circumferential direction at the edge of the air inlet 14. The structure of the bypass passage 150 is the same as that of the bypass passage 90 described in the first embodiment.

Further, the edge of the air inflow port 14 is formed in a flat plate shape, not in a curved shape like a socket, thereby preventing the occurrence of noise. That is, the conventional inlet for sucking air is formed as a socket having a curved surface shape in order to increase the constant pressure, thereby minimizing noise generated from the socket.

When the number of the bypass passages 150 is 2 or less, the amount of air discharged in the reverse direction is small, and it is difficult to perform the noise reduction function, and when the number of the bypass passages 150 is 6 or more, the discharged air leaks, and the amount of air blown is reduced.

The bypass passages 150 are formed at 180-degree intervals in the circumferential direction of the air inlet port in the case of 2, at 120-degree intervals in the case of 3, at 90-degree intervals in the case of 4, at 72-degree intervals in the case of 5, and at 60-degree intervals in the case of 6. The bypass passages 150 are arranged at equal intervals in the circumferential direction, so that the air moving in the opposite direction can be sequentially discharged.

As shown in fig. 7, if the bypass passage 150 is formed of the first bypass passage portion 152, the second bypass passage portion 154, and the third bypass passage portion 156 formed at intervals of 120 degrees, noise can be minimized and the amount of air blown can be maintained.

As shown in fig. 8, the bypass passage 170 of the sixth embodiment includes: first bypass passage portions 172 formed at equal intervals in the circumferential direction at the edge of the air inflow port 14; and a second bypass passage portion 174 which is disposed between the first bypass passage portions 172 and has an area smaller than that of the first bypass passage portions 172.

The area of the first bypass passage portion 172 needs to be large to expose the air discharge passage 82 to the outside, and the area of the second bypass passage portion 174 is smaller than the area of the first bypass passage portion 172 to prevent the air discharge passage 82 from being exposed.

The first bypass passage 172 is formed in 2 to 6 pieces at an equal pitch, and the second bypass passage portion 174 is also formed in 2 to 6 pieces at an equal pitch. More preferably, if 3 first bypass passages 172 are formed at equal intervals and 3 second bypass passage portions 174 are also formed at equal intervals, optimum conditions for noise reduction and prevention of reduction in air blowing amount can be satisfied.

Fig. 9 is a side view of a cooling seat provided with the seat cooling device of the present invention, and fig. 10 is a sectional view of the seat cooling device of an embodiment of the present invention.

The seat cooling device includes: a cooling fan 200 for supplying air required for cooling the seat; and a duct 210 connected between the cooling fan 200 and the seat 220 for supplying the air generated in the cooling fan 200 to the seat 220. An air passage for uniformly distributing the air supplied through the duct to the entire seat is formed inside the seat.

The same cooling fan as that described in the above embodiment is applied to the cooling fan.

The duct 210 includes: a first connection portion 212 arranged along the horizontal direction and connected to the air outlet 18 of the cooling fan; a second connection portion 214 arranged along the vertical direction and guiding air in the vertical direction; a first vertical guide part 230 for guiding air discharged from the cooling fan 200 in a vertical direction; a horizontal guide part 232 guiding the air guided to the first vertical guide part 230 in a horizontal direction; and a second vertical guide part 234 guiding the air guided to the horizontal guide part 232 in a vertical direction.

Also, a filter for filtering out foreign substances in the air discharged from the cooling fan may be provided at the duct 210.

In the seat cooling device, the flow path of the duct is complicated in terms of the property of cooling the seat, and the air passage for the exhaust air is small and complicated in the cooling seat, so that the degree of obstruction of the exhaust air by the cooling fan increases. Therefore, a part of the air discharged to the cooling fan flows in a reverse direction into the cooling fan, collides with the air discharged from the cooling fan, generates noise, and causes an overload on the motor.

Therefore, when the cooling fan of the present invention is applied to a seat cooling device, noise is minimized and reduction in the amount of blown air is prevented.

Fig. 11 is a graph comparing the relationship between the RPM and the air blowing amount of the cooling fan of the present invention and the general cooling fan. Line a shows the relationship between the RPM and the air volume of the conventional cooling fan, and line B shows the relationship between the RPM and the air volume of the cooling fan according to the present invention.

As shown in the graph of fig. 11, it was confirmed that the cooling fan of the present invention generates almost the same air volume at the same RPM as the conventional cooling fan in the actual use frequency band. Therefore, the cooling fan of the present invention can generate the same air volume as that of the conventional cooling fan in the actual use frequency band and can minimize the noise generation.

While the present invention has been shown and described with respect to certain preferred embodiments, it is not intended that the present invention be limited to the above-described embodiments, and that various changes and modifications may be effected therein by one of ordinary skill in the art without departing from the spirit of the present invention.

Industrial applicability

The present invention is a cooling fan which is installed in a cooling seat, a high-performance electronic product, a lighting fixture, or the like to perform a heat dissipation function, can minimize noise generation and can improve air supply efficiency, and is suitable for an air-cooled cooling device.

Claims

1. A kind of cooling fan is disclosed, which comprises a fan body,

the method comprises the following steps:

a fan housing having an air inlet formed in a front surface thereof for allowing air to flow therein and an air outlet formed in a side surface thereof for discharging the air; and

an impeller installed inside the fan housing to allow air to flow in an axial direction and to discharge air in a radial direction,

a bypass passage for discharging air moving in a reverse direction toward the air outlet to the outside is formed along an axial direction of the fan housing at an edge of the air inlet, an air suction passage for sucking air is formed inside the fan housing and an air discharge passage for discharging air is formed outside the impeller,

the above-described cooling fan is characterized in that,

the bypass passage includes:

a first bypass passage portion disposed at a position close to the air discharge port, and formed in a range of 90 degrees to 180 degrees at a position where the air discharge port is formed, so that the air discharge passage is exposed; and

and a second bypass passage portion disposed on a circumferential edge of the air inlet, the second bypass passage portion being disposed on a remaining edge except the first bypass passage portion and having an area smaller than that of the first bypass passage portion, so as to prevent the air discharge passage from being exposed.

2. The cooling fan as claimed in claim 1, wherein the bypass passage is connected to support ribs radially formed at the air inflow port, so that the bypass passage is divided into a plurality of regions.

3. A seat cooling device is characterized in that,

the method comprises the following steps:

a seat having an air passage formed therein for passing air therethrough;

a cooling fan for generating air required for cooling the seat; and

a duct for connecting the cooling fan and the seat,

the cooling fan described above is the cooling fan described in claim 1 or 2.