CN203189330U - Centrifugal fan - Google Patents
Centrifugal fan Download PDFInfo
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- CN203189330U CN203189330U CN 201320188462 CN201320188462U CN203189330U CN 203189330 U CN203189330 U CN 203189330U CN 201320188462 CN201320188462 CN 201320188462 CN 201320188462 U CN201320188462 U CN 201320188462U CN 203189330 U CN203189330 U CN 203189330U
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- centrifugal cutter
- diameter
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- trailing edge
- blades
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Abstract
The utility model relates to a centrifugal fan. A plurality of blades are arranged on the periphery of a round bearing part, wherein the round bearing part is in a circular ring shape when looked from the front, the blades are installed on an external rotating shaft through an installing part, wherein each blade comprises a front edge close to the center of the bearing part and a rear edge far from the center of the bearing part, and the thickness of the rear edge (t2) is smaller than that of the front edge (t2).
Description
Technical field
The utility model relates to from side's direction of rotary middle spindle and sucks fluid and discharging the centrifugal cutter of fluid with the direction of rotary middle spindle quadrature.
Background technique
In Japanese kokai publication hei 07-127599 publication communique (A), disclose centrifugal multiple wing Air Blast fan.This centrifugal multiple wing Air Blast fan is commonly called centrifugal cutter, as Fig. 1 of above-mentioned patent documentation and/or shown in Figure 2, the front that is provided with the cylinder support at the center is seen as the periphery of circular hub plate, is provided with the blade of a plurality of strips that extend along the rotating center axle direction at certain intervals.In so centrifugal multiple wing Air Blast fan, by the running shaft of motor being installed at the cylinder support and it being rotated driving, suck extraneous gas from side's direction of rotary middle spindle, and be that the radial direction of hub plate is discharged gas in the direction with the rotary middle spindle quadrature.
Yet above-mentioned centrifugal cutter (centrifugal multiple wing Air Blast fan) is generally used for the centrifugal blower with the air-supply of fluids such as air, and air-supply efficient is important design issue.As everyone knows, air-supply efficient is that mainly the mechanical form by centrifugal cutter decides with the driving power of running shaft and the amount of definition recently of the mechanical energy that is applied by the blade convection cell.
The model utility content
The utility model is In view of the foregoing made, and its purpose is that the air-supply efficient that makes compared with the past improves.
As the mode that solves above-mentioned problem, the utility model adopts following formation.
(1) centrifugal cutter of the utility model first aspect, a plurality of blades are arranged on the periphery that the front is seen as circular support circularly, be installed on the outside running shaft via assembly department, wherein, blade comprises that the thickness of trailing edge is than the thin thickness of leading edge with the nearer leading edge in the center of support with apart from the center of support trailing edge far away.
(2) in the centrifugal cutter of above-mentioned (1), can constitute, described face of blade is seen as curved shape, and the mode tangent with the back side of the line segment of the center that connects described support and described trailing edge and adjacent vanes arranges.
(3) in the centrifugal cutter of above-mentioned (1) or (2), can constitute, the sheet number of described blade is the sheet number that is equivalent to 360 approximate number.
(4) in the centrifugal cutter of above-mentioned (1)～(3) either side, can constitute, between the thickness t 2 of the thickness t 1 of described leading edge and described trailing edge, following relation is set up,
0.65≤t2/t1≤0.75。
(5) in the centrifugal cutter of above-mentioned (1)～(4) either side, can constitute, by between the diameter D1 of the annulus of the described leading edge regulation of a plurality of described blades and the diameter D2 by the annulus of the described trailing edge regulation of a plurality of described blades, following relation establishment
0.76＜D1/D2≤0.80。
(6) in the centrifugal cutter of above-mentioned (1)～(5) either side, can constitute, between length H that the rotary middle spindle of described blade makes progress and the diameter D2 by the annulus of the described trailing edge regulation of a plurality of described blades, following relation is set up,
0.4≤H/D2≤0.5。
According to above-mentioned aspect, because the thickness t 2 of vane trailing edge is thinner than the thickness t 1 of leading edge, so from the leading edge to the trailing edge, the flow path area of fluid increases gradually, follow in this, from the leading edge to the trailing edge, the pressure loss (flowing resistance) descend gradually (minimizing).As a result, because the difficult labour of peeling off of the fluid that the resistance between blade surface and the fluid causes is given birth to, the fluid energy loss that causes so can make the generation of separation vortex reduces, and therefore the air-supply efficient that can make compared with the past improves.
In addition, according to the utility model, owing to can suppress the vibration of the blade that separation vortex causes, so also can suppress the generation of noise.
Description of drawings
Fig. 1 is the stereogram that the integral body of the centrifugal cutter A of expression the utility model one mode of execution constitutes;
Fig. 2 is the front elevation of this centrifugal cutter A;
Fig. 3 is the sectional drawing under the situation of observing this centrifugal cutter A along the cross section (longitudinal section) of the rotary middle spindle L of centrifugal cutter A;
Fig. 4 is the part enlarged view of a part of blade 2 in the presentation graphs 2.
Embodiment
Below, with reference to accompanying drawing a mode of execution of the present utility model is described.
As shown in the figure, the centrifugal cutter A of present embodiment has roughly outer shape cylindraceous, and the solid of rotation that rotates around rotary middle spindle L in the counterclockwise direction.This centrifugal cutter A is by to rotation counterclockwise, is that side's direction side of rotary middle spindle L sucks fluids such as air from the top of Fig. 1, and is that peripheral direction is discharged fluid to the direction with rotary middle spindle L-orthogonal.
In addition, this centrifugal cutter A be with support 1, a plurality of blade 2, guard shield 3 and assembly department 4 as the main composition position, and for example with polypropylene as raw material and by formed in mould resin-formed body.Support 1 top view is circular vault (dome) shape, is from the fluid of top suction and the position of supporting a plurality of blades 2 for guiding.In this support 1, the face of fluid suction side (surface) is the guide surface 1a of guiding fluid.This guide surface 1a is for along with leaving the dome shape that rotary middle spindle L backs away.In addition, in such support 1, the face of the opposition side of above-mentioned guide surface 1a (back side) is concave face.
In addition, as Fig. 2 institute expressly, at the visual arrow mark 1b that is formed with the sense of rotation (counterclockwise) of this centrifugal cutter of expression A of above-mentioned guide surface 1a with recognizing.It is in 30 ° the scope that this arrow mark 1b is the angle that is arranged on around rotary middle spindle L circular-arcly, for example is 0.1～0.4mm apart from the height of guide surface 1a.
Each blade 2 is to be arranged on the periphery of support 1 and the strip position of extending along the direction of rotary middle spindle L at certain intervals.That is, each blade 2 separates certain intervals and is circular arrangement in the periphery of support 1.The sheet number of blade 2 is the sheet numbers that are equivalent to 360 approximate number, that is, the angle that is set at around rotary middle spindle L is the interval of integer, for example is 45 (8 ° of intervals).
In addition, the posture of each blade 2 is set to, one side (leading edge 2a) of two long legs is on the position near rotary middle spindle L, the opposing party of two long legs (trailing edge 2b) is far away apart from rotary middle spindle L, in addition, the front is seen as with the mode of sense of rotation side depression crooked curved shape gently.More specifically, as Fig. 4 institute expressly, each blade 2 is sectional shapes that leading edge 2a and trailing edge 2b are linked by back side 2c and outside of belly 2d, the mode tangent with the back side 2c of the line segment (imaginary line) of the center (being rotary middle spindle L) that connects support 1 and trailing edge 2b and adjacent blades 2 disposes, described back side 2c is with gently crooked in the outstanding mode of the direction opposite with sense of rotation, and described outside of belly 2d is gently crooked in the mode with respect to the sense of rotation depression.The underpart of each blade 2 like this is connected with support 1.
As shown in Figure 4, above-mentioned leading edge 2a and trailing edge 2b form the shape at thickness direction band circular arc.That is, because leading edge 2a forms the shape of band circular arc, reduced the resistance of air on the leading edge 2a.In addition, because trailing edge 2b forms the shape of band circular arc, when rotating, suppressed centrifugal cutter A the resistance of air of the back side 2c side of trailing edge 2b, so noise (air noise) reduces.
This each blade 2 is illustrated in greater detail, and the thickness (trailing edge thickness t 2) that each blade 2 forms trailing edge 2b is thinner than the thickness (leading edge thickness t 1) of leading edge 2a.That is, the thickness of each blade 2 from leading edge 2a to trailing edge 2b attenuation gently.More specifically, between leading edge thickness t 1 and trailing edge thickness t 2, following relation (1) is set up.In addition, t1 is identical with the unit of t2.
0.65≤t2/t1≤0.75 (1)
In addition, by between the diameter (leading edge diameter D1) of the annulus of the leading edge 2a of each blade 2 regulation and the diameter (trailing edge diameter D2) by the annulus of the trailing edge 2b regulation of each blade 2, following relation (2) establishment.In addition, D1 is identical with the unit of D2.
0.76＜D1/D2≤0.80 (2)
In addition, between the length (chord H) and above-mentioned trailing edge diameter D2 on the direction of the rotary middle spindle L of each blade 2, following relation (3) is set up.In addition, H is identical with the unit of D2.
0.4≤H/D2≤0.5 (3)
Then, the action effect to this centrifugal cutter A of such formation is described in detail.
In this centrifugal cutter A, separate certain radius with rotary middle spindle L and be a plurality of blades 2 of circular arrangement to rotation counterclockwise, thus, fluid is inhaled into from side's direction side (upper side Fig. 1) of rotary middle spindle L, and is discharged from the direction (peripheral direction) with rotary middle spindle L-orthogonal.That is, in this centrifugal cutter A, each circular blade 2 rotates around rotary middle spindle L, thereby makes attraction force acts carry out fluidization in the gas of top, and this fluid is discharged to peripheral direction deflection and to peripheral direction.
At this, in this centrifugal cutter A, because in each blade 2, trailing edge thickness t 2 forms thinner than leading edge thickness t 1, so from leading edge 2a to trailing edge 2b, the flow path area of fluid increases gradually, follow in this, from leading edge 2a to trailing edge 2b, the pressure loss (flowing resistance) descend gradually (minimizing).As a result, because the difficult labour of peeling off of the surface (back side 2c and outside of belly 2d) of blade 2 and the fluid that the resistance between the fluid causes is given birth to, the energy loss of the fluid that causes so can make the generation of separation vortex reduces.In addition, in this centrifugal cutter A, can suppress the vibration of the blade 2 that caused by above-mentioned separation vortex.
To this, Japanese kokai publication hei 07-127599 publication communique (A) although in disclosed centrifugal multiple wing Air Blast fan fully not open in above-mentioned patent documentation, but owing to do not comprise and the quite or similar feature of each blade 2 of such this centrifugal cutter A, so can not play the effect same with this centrifugal cutter A
Therefore, according to this centrifugal cutter A, because the energy loss of the fluid that the generation of separation vortex causes is reduced, so compared with the past, can improve air-supply efficient.In addition, according to this centrifugal cutter A, owing to can suppress the vibration of blade 2, so can suppress the generation of noise.
In addition, in this centrifugal cutter A, each blade 2 top view is curved shape, dispose in the tangent mode of line segment (imaginary line) and the back side 2c of adjacent blades 2 that connects rotary middle spindle L and trailing edge 2b, so, air-supply efficient is more effectively improved.Namely, fluid is under near situation about peeling off the point of contact of the back side of blade 2 2c and above-mentioned imaginary line, flow along the outside of belly 2d of adjacent vanes 2 (with depression mode crooked curved surface gently) because this peels off stream, so easily with the fluid stream of above-mentioned back side 2c interflow again.In addition, since the direction of ventilation of 2 in blade near the trailing edge 2b of blade 2 near the sense of rotation of centrifugal cutter A, so collaborate swimmingly easily in the fluid around the centrifugal cutter A.Therefore, in this centrifugal cutter A, the air-supply efficient of fluid is improved, and noise is reduced.
In addition, in this centrifugal cutter A, because the sheet number of blade 2 is the numbers that are equivalent to 360 approximate number, that is, the angle that is set at around rotary middle spindle L is the interval of integer, so design easily.
In addition, in this centrifugal cutter A, because between leading edge thickness t 1 and trailing edge thickness t 2, relation (1) is set up, so air-supply efficient is more effectively improved.
In addition, in this centrifugal cutter A, because between leading edge diameter D1 and trailing edge diameter D2, relation (2) is set up, so the relation between the decline of the air-supply decrease in efficiency that the size of the radial direction (orthogonal direction of rotary middle spindle L) of this centrifugal cutter A can be caused with the weight increase of the long blade that causes 2 of size of the blade 2 on this radial direction and the too short air output that causes.
In addition, in this centrifugal cutter A, because between the chord H and trailing edge diameter D2 of each blade 2, relation (3) is set up, so can take into account guaranteeing and moldability of air output.That is, if chord H is long with respect to trailing edge diameter D2, then when being shaped, deform easily, on the other hand, if too short, then can not guarantee air output, so by satisfying relation (3), can take into account guaranteeing and moldability of air output.
In addition, the utility model is not limited to above-mentioned mode of execution, can consider for example following such variation.
That is, in the above-described embodiment, to being that the centrifugal cutter A at main composition position is illustrated with support 1, a plurality of blade 2, guard shield 3 and assembly department 4, but the utility model is not limited in this.In above-mentioned centrifugal cutter A, because being shaped as along the strip of the direction extension of rotary middle spindle L of blade 2, so for the supporting that makes blade 2 more firm, be provided with guard shield 3 in the upper end portion of blade 2, but in (for example under the situation of length than weak point) under the different situation of blade shape, also can consider to remove guard shield 3.
In addition, in the above-described embodiment, sense of rotation is made as counterclockwise, but the utility model is not limited in this.That is, also sense of rotation can be made as clockwise direction, in this case, the bending direction of blade need be made as with above-mentioned blade 2 reverse.In addition, the curvature at each position also can suitably be set as required.
Claims (17)
1. a centrifugal cutter is arranged on the periphery that the front is seen as circular support with a plurality of blades circularly, is installed on the outside running shaft via assembly department, it is characterized in that,
Described blade comprises with the nearer leading edge in the center of described support with apart from the center of described support trailing edge far away, and the thickness of described trailing edge is t2 than the thickness of described leading edge is that t1 is thin.
2. centrifugal cutter as claimed in claim 1 is characterized in that,
Described face of blade is seen as curved shape, and the mode tangent with the back side of the line segment of the center that connects described support and described trailing edge and adjacent vanes arranges.
3. centrifugal cutter as claimed in claim 1 is characterized in that,
The sheet number of described blade is the sheet number that is equivalent to 360 approximate number.
4. centrifugal cutter as claimed in claim 2 is characterized in that,
The sheet number of described blade is the sheet number that is equivalent to 360 approximate number.
5. centrifugal cutter as claimed in claim 1 is characterized in that,
Be that the thickness of t1 and described trailing edge is between the t2 at the thickness of described leading edge, following relation is set up,
0.65≤t2/t1≤0.75。
6. centrifugal cutter as claimed in claim 2 is characterized in that,
Be that the thickness of t1 and described trailing edge is between the t2 at the thickness of described leading edge, following relation is set up,
0.65≤t2/t1≤0.75。
7. centrifugal cutter as claimed in claim 3 is characterized in that,
Be that the thickness of t1 and described trailing edge is between the t2 at the thickness of described leading edge, following relation is set up,
0.65≤t2/t1≤0.75。
8. centrifugal cutter as claimed in claim 4 is characterized in that,
Be that the thickness of t1 and described trailing edge is between the t2 at the thickness of described leading edge, following relation is set up,
0.65≤t2/t1≤0.75。
9. centrifugal cutter as claimed in claim 1 is characterized in that,
Be D1 with diameter by the annulus of the described trailing edge regulation of a plurality of described blades at the diameter by the annulus of the described leading edge regulation of a plurality of described blades be between the D2, following relation establishment,
0.76＜D1/D2≤0.80。
10. centrifugal cutter as claimed in claim 2 is characterized in that,
Be D1 with diameter by the annulus of the described trailing edge regulation of a plurality of described blades at the diameter by the annulus of the described leading edge regulation of a plurality of described blades be between the D2, following relation establishment,
0.76＜D1/D2≤0.80。
11. centrifugal cutter as claimed in claim 3 is characterized in that,
Be D1 with diameter by the annulus of the described trailing edge regulation of a plurality of described blades at the diameter by the annulus of the described leading edge regulation of a plurality of described blades be between the D2, following relation establishment,
0.76＜D1/D2≤0.80。
12. centrifugal cutter as claimed in claim 4 is characterized in that,
Be D1 with diameter by the annulus of the described trailing edge regulation of a plurality of described blades at the diameter by the annulus of the described leading edge regulation of a plurality of described blades be between the D2, following relation establishment,
0.76＜D1/D2≤0.80。
13. centrifugal cutter as claimed in claim 5 is characterized in that,
Be D1 with diameter by the annulus of the described trailing edge regulation of a plurality of described blades at the diameter by the annulus of the described leading edge regulation of a plurality of described blades be between the D2, following relation establishment,
0.76＜D1/D2≤0.80。
14. centrifugal cutter as claimed in claim 6 is characterized in that,
Be D1 with diameter by the annulus of the described trailing edge regulation of a plurality of described blades at the diameter by the annulus of the described leading edge regulation of a plurality of described blades be between the D2, following relation establishment,
0.76＜D1/D2≤0.80。
15. centrifugal cutter as claimed in claim 7 is characterized in that,
Be D1 with diameter by the annulus of the described trailing edge regulation of a plurality of described blades at the diameter by the annulus of the described leading edge regulation of a plurality of described blades be between the D2, following relation establishment,
0.76＜D1/D2≤0.80。
16. centrifugal cutter as claimed in claim 8 is characterized in that,
Be D1 with diameter by the annulus of the described trailing edge regulation of a plurality of described blades at the diameter by the annulus of the described leading edge regulation of a plurality of described blades be between the D2, following relation establishment,
0.76＜D1/D2≤0.80。
17. as each described centrifugal cutter in the claim 1～16, it is characterized in that,
The length that makes progress at the rotary middle spindle of described blade is H and is between the D2 by the diameter of the annulus of the described trailing edge regulation of a plurality of described blades that following relation is set up,
0.4≤H/D2≤0.5。
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320188462 CN203189330U (en) | 2013-02-26 | 2013-02-26 | Centrifugal fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320188462 CN203189330U (en) | 2013-02-26 | 2013-02-26 | Centrifugal fan |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203189330U true CN203189330U (en) | 2013-09-11 |
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ID=49106192
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201320188462 Expired - Fee Related CN203189330U (en) | 2013-02-26 | 2013-02-26 | Centrifugal fan |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203189330U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106122088A (en) * | 2016-08-17 | 2016-11-16 | 芜湖美智空调设备有限公司 | Centrifugal wind wheel and cabinet air-conditioner |
-
2013
- 2013-02-26 CN CN 201320188462 patent/CN203189330U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106122088A (en) * | 2016-08-17 | 2016-11-16 | 芜湖美智空调设备有限公司 | Centrifugal wind wheel and cabinet air-conditioner |
| CN106122088B (en) * | 2016-08-17 | 2019-04-02 | 芜湖美智空调设备有限公司 | Centrifugal wind wheel and cabinet air-conditioner |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130911 |