TWM491096U - Centrifugal fan - Google Patents

Description

Centrifugal fan

The present invention relates to a centrifugal fan, and more particularly to a centrifugal fan having the effect of reducing the overall thickness of the centrifugal fan to achieve a thin design requirement and improving the performance of the fan, and having a noise reduction.

Due to the gradual thinning of electronic devices (such as notebook computers or tablets), the internal space of the electronic device is extremely limited, so the heat-dissipating fan installed inside is required to be thinned, so the thickness thereof must be reduced, and the cooling fan and the adjacent The space between the components is also quite limited, resulting in poor heat dissipation of the cooling fan. In particular, in the case where the space is limited, the airflow of the cooling fan cannot be uniformly sent out from the air outlet of the cooling fan, thus affecting the heat dissipation efficiency.

A centrifugal fan is disclosed in which a plurality of blades are disposed on a top surface of a hub, and a second end of each of the blades collectively surrounds to form a virtual geometric profile; wherein the virtual geometric profile has A maximum outer diameter, a spacing between the second ends of any two adjacent vanes of the fan wheel, the spacing being less than the maximum outer diameter of the virtual geometric profile, thereby achieving improved heat dissipation.

Although the above-mentioned centrifugal fan can achieve the effect of improving the heat dissipation, it extends another problem because the blades are disposed on the top surface of the hub such that the axial height thereof is higher than that of the conventional centrifugal fan. Even higher, in other words, the original height of the hub plus the height of the blades will cause a large increase in the overall axial height of the fan wheel, which in turn will increase the overall height of the fan frame that accommodates the fan wheel. As seen from Fig. 4 of the conventional publication No. 201303165, the overall axial height of the fan frame is the axial height of the side wall portion plus the axial height of the side air outlet or the air inlet, and the axis of the opposite frame. to The height is also the height of the fan wheel as a whole, so that the overall thinning of the conventional centrifugal fan is rather limited and the thickness cannot be saved, and thus the height of the internal space of the electronic device is limited, so that the centrifugal fan cannot be installed in the height. The problem in the internal space of the electronic device, therefore, the industry is still unable to overcome the problem of how to achieve thinning, but also improve the performance of the fan.

Therefore, how to solve the above problems and problems in the past, that is, the creators of the case and the relevant manufacturers engaged in this industry are eager to study the direction of improvement.

Accordingly, in order to effectively solve the above problems, the main object of the present invention is to provide a centrifugal fan having a thickness that reduces the overall thickness of the centrifugal fan to achieve a thinner shape and an improved fan performance.

In order to achieve the above object, the present invention provides a centrifugal fan including a frame and an impeller, the upper side and the lower side of the fan wheel being closed and having a receiving space for receiving the impeller therein, and The fan frame has at least one air inlet and at least one air outlet. The air inlet and the air outlet communicate with the accommodating space, and are respectively disposed on one side and the other side of the fan frame, and the impeller has a plurality of blades, an extension portion and a hub, the extension portion is formed to extend outwardly from an outer circumferential side of the hub, and the blades are disposed away from the hub, the plurality of blades being provided with a front end and a rear end a virtual geometric profile defined by the trailing ends of the blades and a defined flow space between the hub and the hub, and a chord length between the front end and the rear end of the blades, the width of the flow guiding space It is greater than or equal to the chord length of the blades; through the design of the centrifugal fan, the effect of thinning and effectively improving the performance of the fan can be effectively achieved.

1‧‧‧ centrifugal fan

11‧‧‧Fan frame

111‧‧‧ Cover

112‧‧‧floor

1121‧‧‧ shaft seat

113‧‧ ‧ tongue block

114‧‧‧ side panels

1141‧‧‧First side wall

1142‧‧‧ second side wall

1143‧‧‧ third side wall

1144‧‧‧ fourth side wall

1151‧‧‧First straight section

1152‧‧‧Second straight section

Bending section from 1153‧‧

1156‧‧‧Expanded curved section

116‧‧‧ flow path

1161‧‧‧High wind pressure zone

1162‧‧‧Low wind pressure zone

117‧‧‧ accommodating space

118‧‧‧Air inlet

119‧‧‧air outlet

13‧‧‧ Impeller

131‧‧‧ leaves

1311‧‧‧ front end

1312‧‧‧ Backend

1313‧‧‧string length

1314‧‧‧Virtual geometric outline

132‧‧‧Drainage channel

133‧‧‧Extension

1331‧‧‧Extension arm

13311‧‧‧Free end

134‧‧‧Act

135‧‧‧ separated space

136‧‧ wheels

137‧‧‧ Diversion space

W‧‧‧ width of the diversion space

Figure 1 is an exploded perspective view showing the first preferred embodiment of the present invention.

Figure 2 is a schematic diagram showing the combination of the first preferred embodiment of the present invention.

Figure 3 is a top plan view showing a first preferred embodiment of the present invention.

Figure 4A is a top plan view showing the first preferred embodiment of the present invention.

Figure 4B is another top plan view showing the first preferred embodiment of the present invention.

Figure 4C is another top plan view showing the first preferred embodiment of the present invention.

Fig. 5A is a diagram showing the noise spectrum of the centrifugal fan of the first preferred embodiment of the present invention.

Fig. 5B is a perspective view showing the projection ratio of the centrifugal fan of the first preferred embodiment of the present invention.

Fig. 6A is a diagram showing the noise spectrum of a conventional centrifugal fan.

Fig. 6B is a spectrogram showing the projection ratio of a conventional centrifugal fan.

Figure 7 is another exploded view showing the first preferred embodiment of the present invention.

Fig. 8A is an exploded perspective view showing the second preferred embodiment of the present creation.

Figure 8B is another exploded view showing the second preferred embodiment of the present invention.

The above object of the present invention, as well as its structural and functional features, will be described in accordance with the preferred embodiments of the drawings.

The present invention provides a centrifugal fan. Please refer to Figures 1 and 2 for a breakdown and combination of the first preferred embodiment of the present invention, and supplemented with reference to Figure 3; It is disposed in an electronic device (such as a notebook computer, a tablet computer, an IPAD, a portable wearable device; not shown), and the centrifugal fan 1 includes a frame 11 and an impeller 13, the fan frame 11 The upper side and the lower side are closed and have an accommodating space 117 therein, and the fan frame 11 includes at least one air inlet 118, at least one air outlet 119, a cover 111, a bottom plate 112, and a tongue 113. a side plate 114, the air inlet 118 and the air outlet 119 are connected to the accommodating space 117, and are respectively opened on one side and the other side (ie, adjacent side) of the fan frame 11, that is, The air inlets 118 and the air outlets 119 are respectively formed on the first and second side walls 1141 and 1142 of the side plate 114, and the cover plate 111 is connected to the receiving space 117 defined by the bottom plate 112 and the side plate 114. The air inlet 118 and the air outlet 119. The front side plate 114 is formed to extend upward from the periphery of the bottom plate 112, and one end thereof (ie, the side plate 114 is opposite to the end of the bottom plate 112) is covered. There is an opposite cover plate 111; the side plate 114 and the bottom plate 112 of the preferred embodiment are integrally formed for illustration. The bottom plate 112 and the cover plate 111 are closed and do not have any holes.

The bottom plate 112 has a shaft seat 1121. The shaft seat 1121 is received in the center of the accommodating space 117, that is, the shaft seat 1121 is axially convex from the center of the bottom plate 112 in the accommodating space 117. The structure is stretched and pivoted with the opposite impeller 13. The first side wall 1141 has a first side wall 1141, a second side wall 1142, a third side wall 1143, and a fourth side wall 1144. The first and second side walls 1141, 1142 are in the preferred embodiment. The second side wall 1142 is perpendicular to the second side wall 1142; and the tongue portion 113 protrudes from the contact position of the first and second side walls 1141, 1142 toward the relative accommodating space 117, and adjacent to the impeller 13, which The tongue portion 113 is configured to prevent (or block) the airflow from the air outlet 119 from flowing back and leaking out from the air inlet 118, thereby reducing mutual interference between the airflow entering the air inlet 118 and the airflow flowing out of the air outlet 119, and further allowing The air inlet 118 is more easily sucked in, and the air intake efficiency of the centrifugal fan 1 is improved, thereby reducing the noise and increasing the air volume and the wind pressure.

The air outlet 119 is located between the tongue portion 113 and the fourth side plate 1114, and opposite to the third side wall 1143, the air inlet 118 is located between the tongue portion 113 and the third side wall 1143, and Opposite the fourth side wall 1144. The angle between the air outlet 119 and the air inlet 118 is between 30 degrees and 90 degrees, and the angle is based on the axis of the hub 136 to face the air outlet 119 and the air inlet 118. The angle defined by the dotted line is outwardly extended, and the angle between the air outlet 119 and the air inlet 118 of the preferred embodiment is preferably 90 degrees, but is not limited thereto. The user can design and adjust the angle between the air outlet 119 and the air inlet 118 to 30 degrees (as in FIG. 4C) according to the space size and the position of the electronic device in advance, or the air outlet 119 and The angle between the air inlets 118 is 45 degrees (as in FIG. 4B), or the angle between the air outlets 119 and the air inlets 118 is 60 degrees (as shown in FIG. 4A), including the first.

Continuing to refer to the first and third figures, the third and fourth side walls 1143 and 1144 are adjacent to each other and form a first straight section 1151, a second straight section 1152, a curved section 1153 and an expansion. a curved section 1156, the first straight section 1151 is located adjacent to the air inlet, one side of the curved section 1153 is connected to the opposite first straight section 1151, and the other side is connected to the opposite expansion curved section 1156 One side of the second straight section 1152 is located adjacent to the air outlet 119, which is connected to the other side of the expanded curved section 1156, in other words, the first straight section 1151 is adjacent to the inlet. The inner side of the third side wall 1143 at the tuyere 118 extends toward the air outlet 119, and sequentially connects the curved section 1153, the expanded curved section 1156 to the second straight section of the inner side of the fourth side wall 1144 at the adjacent air outlet 119. 1152.

The impeller 13 is received in the accommodating space 117, and has a plurality of blades 131, an extending portion 133 and a hub 136. The extending portion 133 is formed to extend outward from the outer peripheral side of the hub 136, and The blades 131 are disposed away from the hub 136; and the extending portion 133 has a plurality of extending arms 1331 extending outwardly from the outer peripheral side of the hub 136 and forming a free end 13311. The free ends 13311 are connected to each other to form a ring body 134. The blades 131 are looped on the ring body 134 and define a flow guiding channel 132 therebetween. The extending arms 1331 define a communication relationship with each other. The space 135 of the accommodation space 117. The extension portion 133 can be modified as a ring-shaped extension arm 1331, that is, as shown in FIG. 7, the extension arm 1331 extends outward along the outer circumferential side of the hub 136. The annular disc-shaped extension arms 1331 are annularly disposed on the circumferential end of the annular disc-shaped extension arm 1331 away from the hub 136.

The blade 131 is provided with a front end 1311 and a rear end 1312. The front end 1311 of the blade 131 protrudes out of an outer circumference of the ring body 134. The rear end 1312 of the blade 131 is in the preferred embodiment. The inner peripheral side of the ring body 134 is slanted and is opposite to the outer peripheral side of the hub 136. However, the present invention is not limited thereto. In the actual implementation of the present invention, the rear end 1312 of the blade 131 is provided. It can also be designed to protrude beyond the inner circumference of the hub 134 relative to the hub 136. A virtual geometric profile 1314 is defined by the rear end 1312 of the blade 131. The virtual geometric profile 1314 defines a flow guiding space 137 connecting the receiving space 117 and the guiding channel 132 with respect to the hub 136. A chord length 1313 is formed between the front end 1311 and the rear end 1312 of the vane 131. The width W of the flow guiding space 137 is greater than or equal to the chord length 1313 of the vanes 131. For example, the width of the diversion space 137 is 1.5. The centimeters (cm) are larger than the chord length 1313 of the blades 131 by 1.1 cm (cm), or the width of the flow guiding space 137 is 1.1 cm equal to the chord length 1313 of the blades 131 being 1.1 cm.

Therefore, the width W of the flow guiding space 137 through the creation is greater than or equal to the structural design of the chord length 1313 of the plurality of blades 131, so that the external airflow is effectively introduced into the fan frame 11 from the air inlet 118 in a radial direction. After the airflow is pressurized by the blades 131 into the flow guiding space 137 of the accommodating space 117, the plurality of blades 131 that are again transmitted through the impeller 13 are pressurized to cause the airflow to be directed in the radial direction toward the opposite air outlets 119. To the outside world, to effectively improve the performance of the fan. In addition, the structural design of the plurality of blades 131 of the present invention in a radial direction (or horizontal direction) corresponding to the hub 136 enables the axial height of the hub 136 to be reduced (or reduced), the opposite frame 11 The overall axial height also decreases, so that the thickness can be effectively saved, and the effect of reducing the thickness of the centrifugal fan 1 can be achieved.

Referring to FIGS. 1 to 3, the front end 1311 of the plurality of blades 131 is adjacent to the corresponding tongue portion 113, and the flow of the flow guiding channel 132 is communicated with the defining of the third and fourth side walls 1143, 1144. The width of the flow passage 116 is gradually increased from the curved section 1153 to the expanded curved section 1156, and the flow passage 116 includes the high-pressure zone 1161 and the first-class passage 116 of the first-class passage 116 having a relatively narrow width. a wide low wind pressure zone 1162, the high wind pressure zone 1161 being located adjacent to the first straight section 1151 of the curved section 1153, the low wind pressure zone 1162 being located at the curved section 1153, the expanded curved section 1156 And the outlet 119, so when the centrifugal fan 1 impeller When the motor 13 is in operation, the blades 131 of the impeller 13 introduce external airflow from the air inlet 118 into the fan frame 11 in a radial direction, so that the airflow is pressurized by the blades 131 and is guided by the flow guiding channel 132. At the same time in the flow guiding space 137, the airflow partially located at the first straight section 1151 is blocked by the flow resistance of the high wind pressure zone 1161, and is guided by the blades 131 into the flow guiding space 137 (ie, Guided by the vanes 131 to the low-pressure flow guiding space 137), and then re-pressurized by the vanes 131 of the impeller 13, a portion of the airflow is smoothly guided by the guiding passages 132 to the low wind. The curved section 1153 of the nip 1162 and the flow passage 116 of the expanded curved section 1156, and the airflow flowing to the inner curved passage 116 of the expanded curved section 1156 is pressurized by the expanded curved section 1156, in a radial direction The second straight section 1152 is led out to the air outlet 119, and then another part of the airflow is directly led out from the guide channels 132 to the opposite air outlet 119, thereby effectively achieving the performance of the fan and the thickness reduction. .

Therefore, the air inlet 118 and the air outlet 119 are provided on both sides of the fan frame 11 of the present invention, and the width of the flow guiding space 137 is greater than or equal to the chord length 1313 of the blades 131, so as to effectively reduce Noise and thickness savings, and thus effectively achieve the effect of improving fan performance.

Please refer to the 5A~6B diagram for comparing the noise test of the centrifugal fan 1 of the present invention with the conventional centrifugal fan; wherein the 6A and 6B are the noise spectrum diagram of the conventional centrifugal fan and the protrusion of the conventional centrifugal fan. Comparing the spectrogram, it can be found from Fig. 6A that the conventional centrifugal fan generates a higher blade frequency peak P1 in the noise spectrum diagram at a certain blade speed, and the blade frequency peak P1 is about 29 decibels. (dB). As can be seen from the 6B diagram, a correspondingly higher protrusion ratio can be found corresponding to the blade frequency peak P1 in FIG. 6A, and the ratio of the Prominence Ratio is close to 7 dB (decibel).

5A and 5B are the noise spectrum diagram of the centrifugal fan 1 of the present invention and the spectral ratio of the protruding ratio of the centrifugal fan 1. Therefore, the blade frequency of the centrifugal fan 1 of the preferred embodiment in FIG. 5A can be found. The peak value is about 19 decibels (dB), and as shown in Fig. 5B corresponding to the fan blade noise peak in Fig. 5A, a relatively high protrusion rate can be found, and the ratio of the Prominence Ratio is close. 5dB (decibel); in addition, when the ratio of the protrusion ratio exceeds 6dB, it is judged that the noise has a prominent "uneven sound", so after the above analysis, the centrifugal fan 1 of the present invention is significantly lower than the noise of the conventional centrifugal fan 1. Therefore, the design of the centrifugal fan 1 can achieve an effective noise reduction effect.

8A and 8B are schematic exploded views showing a second preferred embodiment of the present invention; the structure and connection relationship of the preferred embodiment and its function are substantially the same as those of the first preferred embodiment, so This is not to be repeated; the preferred embodiment of the present invention is mainly to modify the plurality of blades 131 of the first preferred embodiment to be arranged in a staggered arrangement of the plurality of blades 131 on the ring body 134, that is, a plurality of blades. The 131 ring is disposed on an upper end surface of the ring body 134, and the other portion of the plurality of blades 131 is annularly disposed on the lower end surface of the ring body 134, and is disposed in a staggered arrangement with the aforementioned plurality of blades 131.

Therefore, the design that the partial plurality of blades 131 and the other partial plurality of blades 131 are respectively disposed on the upper end surface and the lower end surface of the ring body 134 and are staggered with each other can effectively achieve the effect of reducing fan noise.

As mentioned above, this creation has the following advantages over the prior art:

1. It has the effect of saving thickness.

2. It has the effect of improving the performance of the centrifugal fan.

3. Has the effect of reducing noise.

However, the above descriptions are only preferred embodiments of the present invention, and variations of the methods, shapes, structures, and devices described above are intended to be included in the scope of the present invention.

1‧‧‧ centrifugal fan

113‧‧ ‧ tongue block

114‧‧‧ side panels

1141‧‧‧First side wall

1142‧‧‧ second side wall

1143‧‧‧ third side wall

1144‧‧‧ fourth side wall

1151‧‧‧First straight section

1152‧‧‧Second straight section

Bending section from 1153‧‧

1156‧‧‧Expanded curved section

116‧‧‧ flow path

1161‧‧‧High wind pressure zone

1162‧‧‧Low wind pressure zone

118‧‧‧Air inlet

119‧‧‧air outlet

131‧‧‧ leaves

1311‧‧‧ front end

1312‧‧‧ Backend

1313‧‧‧string length

1314‧‧‧Virtual geometric outline

132‧‧‧Drainage channel

134‧‧‧Act

136‧‧ wheels

137‧‧‧ Diversion space

Claims (7)

A centrifugal fan includes: a frame, the upper side and the lower side are closed and has an accommodating space therein, the fan frame has at least one air inlet and at least one air outlet, the air inlet is connected to the air outlet The accommodating space is respectively disposed on one side and the other side of the fan frame; and an impeller is disposed in the accommodating space, and has a plurality of blades, an extension portion and a hub. The extension portion is formed to extend outwardly from the outer peripheral side of the hub, and the blades are disposed away from the hub, and the blades are provided with a front end and a rear end, and the rear ends are collectively wound around the definition A virtual geometric profile defines a flow guiding space between the hub and the hub, and a chord length between the front end and the rear end of the blades, the width of the flow guiding space being greater than or equal to the chord length of the blades. The centrifugal fan of claim 1, wherein the fan frame comprises a cover plate, a bottom plate, a tongue portion and a side plate, wherein the side plate extends upward from the periphery of the bottom plate, and is provided with a first a side wall, a second side wall, a third side wall and a fourth side wall, wherein the air inlet and the air outlet are respectively formed on the first and second side walls, and the cover is attached to one end of the side plate, And the accommodating space is defined by the bottom plate and the side plate, and the tongue portion protrudes from the position where the first and second side walls are in contact with each other toward the accommodating space, and adjacently corresponds to the front end of the blade. The centrifugal fan of claim 2, wherein the third and fourth side walls are adjacent to each other and form a first straight section, a second straight section, a curved section and an expanded curved section. The first straight straight section is located adjacent to the air inlet, one side of the curved section is connected with respect to the first straight section, and the other side is connected to one side of the opposite expanded curved section, the second straight line A segment is located adjacent the vent, which is coupled to the other side of the expanded bend. The centrifugal fan of claim 3, wherein the front end of the vane defines a first-class track between the front end and the third and fourth side walls, and the width of the flow path is gradually expanded from the curved section to the expanded curved section. And the flow channel comprises a high wind pressure zone with a relatively narrow width of the first-class track and a low wind pressure zone with a relatively wide width of the first-class track. The centrifugal fan of claim 4, wherein the vanes define a flow guiding passage connecting the flow passage and the flow guiding space with each other, and the extending portion has a plurality of extending arms, and the extending arms are Extending outwardly on the outer peripheral side of the hub and forming a free end, the free ends are connected to form a ring body, the blade loops are disposed on the ring body, and the extending arms define a communication relationship with each other The space between the diversion spaces. The centrifugal fan according to any one of claims 1 to 5, wherein the air outlet and the air inlet are at an angle of between 30 and 90 degrees. The centrifugal fan of claim 1, wherein the extension has a plurality of extension arms extending outwardly from the outer circumferential side of the hub and forming a free end, the free ends being connected to each other And forming a ring body, and a part of the plurality of blade ring is disposed on an upper end surface of the ring body, and another part of the plurality of blades is ringed on the lower end surface of the ring body, and the plurality of blades are interlaced with each other. .