CN109519416A - A kind of centrifugal blower - Google Patents
A kind of centrifugal blower Download PDFInfo
- Publication number
- CN109519416A CN109519416A CN201710844636.8A CN201710844636A CN109519416A CN 109519416 A CN109519416 A CN 109519416A CN 201710844636 A CN201710844636 A CN 201710844636A CN 109519416 A CN109519416 A CN 109519416A
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- China
- Prior art keywords
- impeller
- side inner
- spiral case
- rear side
- spiral casing
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- 230000005611 electricity Effects 0.000 claims description 4
- 238000009792 diffusion process Methods 0.000 abstract description 3
- 230000000694 effects Effects 0.000 abstract description 3
- 238000009434 installation Methods 0.000 abstract description 2
- 238000004064 recycling Methods 0.000 abstract description 2
- 238000010586 diagram Methods 0.000 description 3
- 241000237858 Gastropoda Species 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000002146 bilateral effect Effects 0.000 description 1
- 238000000354 decomposition reaction Methods 0.000 description 1
- 238000007634 remodeling Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/4226—Fan casings
- F04D29/4233—Fan casings with volutes extending mainly in axial or radially inward direction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/663—Sound attenuation
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A kind of centrifugal blower, including spiral case, impeller and motor, spiral case includes antetheca, rear wall and the annular wall being connected between antetheca, rear wall, the forward and backward side of spiral case is respectively provided with front side air inlet and rear side air inlet, impeller includes mid-game, front side inner spiral casing is installed on the inner wall of spiral case antetheca, rear side inner spiral casing is installed on the inner wall of spiral case rear wall.The centrifugal blower passes through the inner spiral casing on front side of the installation of the inner wall of spiral case antetheca, rear side inner spiral casing is installed on the inner wall of spiral case rear wall, i.e. using the double-suction type inner spiral casing structure to match with double-entry impeller, it can be further improved the diffusion ability of spiral case, realize the recycling of impeller outlet kinetic energy, reinforce effective acting ability of impeller, to effectively reduce flow losses and reduce fan noise, and, before, rear side inner spiral casing also plays the effect of anti-vortex ring, reduce the gap of blades front disk and hub disk and spiral case, and then reduce the loss of the leakage inside blower fan system.
Description
Technical field
The present invention relates to a kind of centrifugal blowers.
Background technique
The impeller of double-suction type multi-wing centrifugal fan is double-sided impeller, and double-sided impeller is because it is with biggish discharge coefficient
And it is widely used in European type cooker hood.The blade of current double-suction type multi-wing centrifugal fan blade is blade passage
It is short, and blade is long, if to reinforce the effect of fume-exhausting, needs further to be promoted its aeroperformance, if further added
Linear leaf so that being easy to appear unbalance dynamic in rotation process, and then generates additional noise since impeller is rotatable parts.
And by increasing revolving speed improving performance, the increase of noise can be brought.Also, double-suction type multi-wing centrifugal fan is pacified in complete machine because of it
The limitation of dress mode, the flow difference for causing front and rear sides to be entered the wind is big, and blade exit air-flow difference is big, if using identical snail
, will be so that outlet housing exit flow be uneven if shell mould line carries out diffusion, and then lead to that noise increases and fan performance deteriorates.
The main purpose of double-suction type spiral case is to recycle the kinetic energy of double-entry impeller outlet, promotes the pressure of entire blower fan system, therefore spiral case
It is even more important with the matched design of impeller type.
The double-suction type multi-wing centrifugal fan system being currently used in range hood, due to the limitation of outer dimension, driving
Motor is typically mounted at the side of spiral case, while there is also impeller two sides air inlet height is variant, these reasons are finally resulted in
Bilateral simultaneously the flow that enters in impeller be not equivalent relationship, in the case where identical blade parameter, cause two sides from
Impeller outlet is flowed into the air-flow in spiral case and great inhomogeneities is presented, and not only brings a large amount of flow losses, noise also increases
Add.Therefore, in order to improve this situation, it is contemplated that the particularity of multi-wing centrifugal fan needs to improve volute structure, with
Improve the uniformity of exit flow, and then achievees the purpose that improve fan efficiency and reduce noise.
Summary of the invention
The technical problem to be solved by the present invention is to be directed to above-mentioned state of the art, providing a kind of can improve exit flow
Inhomogeneities, the relatively small double-suction type multi-wing centrifugal fan of size.
The technical scheme of the invention to solve the technical problem is: the centrifugal blower, including spiral case, impeller and electricity
Machine, the spiral case includes antetheca, rear wall and the annular wall being connected between antetheca, rear wall, before the forward and backward side of spiral case is respectively provided with
Side air inlet and rear side air inlet, the impeller include mid-game, and the motor is mounted on the rear side of spiral case, the output shaft of motor
It is connected in the mid-game, it is characterised in that: front side inner spiral casing is installed on the inner wall of the spiral case antetheca, in the snail
Rear side inner spiral casing is installed on the inner wall of shell rear wall.
Preferably, the front side inner spiral casing is set to around the front side air inlet, and the rear side inner spiral casing is set to described
Around rear side air inlet.
Further preferably, front end face of the back edge of the front side inner spiral casing adjacent to the impeller, the rear side inner spiral casing
Front along the neighbouring impeller rear end face.
The molded line of front side inner spiral casing and rear side inner spiral casing can have a variety of structures, it is preferable that the type of front side inner spiral casing
The molded line of line and rear side inner spiral casing includes straightway and curved section, air outlet of the straightway adjacent to the blower, song
The starting point of line segment is the lower end of straightway, and the end of curved section is connected on the straightway and tie point is close to straight line
The upper end of section.
Further preferably, the wheel nose muzzle velocity is C2m in axial component, wheel nose muzzle velocity
The component of circumferencial direction is C2u, and impeller outer diameter R2, the base circle diameter (BCD) of spiral case is R0, and the polar radius of front side inner spiral casing is R, leaf
Vertical range between the mid-game and front side inner spiral casing of wheel is B0, and the width of front side inner spiral casing is B1, front side inner spiral casing it is initial
Angle is θ 0, then meets following formula:
Further preferably, the impeller back outlet speed is C2m ' in axial component, impeller back outlet speed
It is C2u ' in the component of circumferencial direction, the base circle diameter (BCD) of impeller outer diameter R2, spiral case are R0, and the polar radius of rear side inner spiral casing is
R ', the vertical range between the mid-game and rear side inner spiral casing of impeller are B2, and the width of rear side inner spiral casing is B3, rear side inner spiral casing
Initial angle is 0 ' of θ, then meets following formula:
Motor can be there are many mounting structure, it is preferable that motor mounting rack, the electricity are equipped on rear side of the spiral case
Machine is mounted on the motor mounting rack.
Compared with the prior art, the advantages of the present invention are as follows: the centrifugal blower on the inner wall of spiral case antetheca by pacifying
Dress front side inner spiral casing is equipped with rear side inner spiral casing on the inner wall of spiral case rear wall, i.e., double using matching with double-entry impeller
Suction inner spiral casing structure, air-flow distance of rubbing action in spiral case is small, can reduce wheel friction loss and reduces blower and makes an uproar
Sound further increases the diffusion ability of spiral case, realizes the recycling of impeller outlet kinetic energy, and then reinforces the effective of impeller and do function
Power, also, front side inner spiral casing and rear side inner spiral casing also play the effect of anti-vortex ring, reduce blades front disk and hub disk and spiral case
Gap, and then reduce the leakage inside blower fan system loss.In addition, the centrifugal blower can be shorter in blade situation
Under, it realizes higher aeroperformance, blower sizes can be made relatively small.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of the embodiment of the present invention；
Fig. 2 is the structural schematic diagram of another angle of the embodiment of the present invention；
Fig. 3 is the decomposition diagram of the embodiment of the present invention；
Fig. 4 is the structure sectional view of the embodiment of the present invention；
Fig. 5 is the side view of the embodiment of the present invention；
Fig. 6 is the structure sectional view of B-B direction in Fig. 5；
Fig. 7 be Fig. 5 in C-C to structure sectional view.
Specific embodiment
The present invention will be described in further detail below with reference to the embodiments of the drawings.
As shown in Figure 1 to Figure 3, the centrifugal blower in the present embodiment include spiral case 1, impeller 2, motor 3, front side inner spiral casing 4,
Rear side inner spiral casing 5 and motor mounting rack 6.
With direction shown in arrow A in Fig. 1 be it is preceding to, spiral case 1 include antetheca 11, rear wall 12 and be connected to antetheca, rear wall it
Between annular wall 13, the forward and backward side of spiral case 1 be respectively provided with front side air inlet 14 and rear side air inlet 15, impeller 2 include mid-game
21, shroud 22 and hub disk 23, the front and rear sides of mid-game 21 are respectively formed advance air port and the rear air inlet of impeller 2, motor installation
Frame 6 is mounted on the rear side of spiral case 1, and motor 3 is mounted on motor mounting rack 6.The output shaft of motor 3 is connected in mid-game 21, electricity
Mid-game 21 is driven to rotate when machine 3 rotates, and then impeller 2 rotates.Above structure and existing double-suction type multi-wing centrifugal fan
Structure is identical, herein not specifically expansion description.
In the present embodiment, front side inner spiral casing 4 is mounted on the inner wall of spiral case antetheca 11, and front side inner spiral casing 4 is set to front side
Around air inlet 14, and the front end face of the back edge adjacent impeller 2 of front side inner spiral casing 4.After rear side inner spiral casing 5 is mounted on spiral case
On the inner wall of wall 12, rear side inner spiral casing 5 is set to around rear side air inlet 15, and the front of rear side inner spiral casing 5 is along neighbouring leaf
The rear end face of wheel 2.In addition, the molded line of front side inner spiral casing 4 and the molded line of rear side inner spiral casing 5 include straightway 71 and curved section
72, for straightway 71 adjacent to the air outlet of blower, the starting point of curved section 72 is the lower end of straightway 71, the end of curved section 72
End is connected on straightway 71 and tie point is close to the upper end of straightway 71.
As shown in Figures 4 to 6, if 2 front end exit speed of impeller in axial component is C2m, C2m can be with front end exit wind
Amount and the number of blade of impeller calculate, and are C2u according to the component in circumferencial direction of 2 front end exit speed of impeller, C2u can basis
Laying angle, revolving speed and the air quantity of blade calculate, and 2 outer diameter of impeller is R2, and the base circle diameter (BCD) of spiral case 1 is R0, the pole of front side inner spiral casing 4
Radius is R, and the vertical range between the mid-game 21 and front side inner spiral casing 4 of impeller 2 is B0, and the width of front side inner spiral casing 4 is B1, preceding
The initial angle of side inner spiral casing 4 is θ 0, then meets following formula:
As shown in Fig. 4, Fig. 5 and Fig. 7, if 2 back outlet speed of impeller is C2m ' in axial component, C2m ' can basis
The number of blade of back outlet air quantity and impeller calculates, and the component in circumferencial direction of 2 back outlet speed of impeller is C2u ', C2u '
It can be calculated according to the laying angle, revolving speed and air quantity of blade, 2 outer diameter of impeller is R2, and the base circle diameter (BCD) of spiral case 1 is R0, in rear side
The polar radius of spiral case 5 is R ', and the vertical range between the mid-game 21 and rear side inner spiral casing 5 of impeller 2 is B2, rear side inner spiral casing 5
Width is B3, and the initial angle of rear side inner spiral casing 5 is 0 ' of θ, then meets following formula:
The foregoing is merely the preferred embodiment of the present invention, it is noted that for those of ordinary skills,
Under the premise of not departing from the principle of the present invention, a variety of remodeling or improvement can be carried out to the present invention, these are regarded as the present invention
Protection scope within.
Claims (7)
1. a kind of centrifugal blower, including spiral case (1), impeller (2) and motor (3), the spiral case (1) include antetheca (11), rear wall
(12) and the annular wall (13) that is connected between antetheca, rear wall, the forward and backward side of spiral case (1) are respectively provided with front side air inlet (14)
With rear side air inlet (15), the impeller (2) includes mid-game (21), and the motor (3) is mounted on the rear side of spiral case (1), electricity
The output shaft of machine (3) is connected on the mid-game (21), it is characterised in that: is installed on the inner wall of the spiral case antetheca (11)
There is front side inner spiral casing (4), rear side inner spiral casing (5) is installed on the inner wall of the spiral case rear wall (12).
2. centrifugal blower according to claim 1, it is characterised in that: the front side inner spiral casing (4) be set to the front side into
Around air port (14), the rear side inner spiral casing (5) is set to around the rear side air inlet (15).
3. centrifugal blower according to claim 1, it is characterised in that: the back edge of the front side inner spiral casing (4) is adjacent to institute
The front end face of impeller (2) is stated, the front of the rear side inner spiral casing (5) is along the rear end face adjacent to the impeller (2).
4. centrifugal blower according to claim 1, it is characterised in that: in the molded line and rear side of the front side inner spiral casing (4)
The molded line of spiral case (5) includes straightway (71) and curved section (72), the outlet air of the neighbouring blower of the straightway (71)
Mouthful, the starting point of curved section (72) is the lower end of straightway (71), and the end of curved section (72) is connected to the straightway
(71) on and tie point close to straightway (71) upper end.
5. centrifugal blower according to claim 1, it is characterised in that: impeller (2) the front end exit speed is in axial direction
Component is C2m, and the component in circumferencial direction of impeller (2) front end exit speed is C2u, and impeller (2) outer diameter is R2, spiral case (1)
Base circle diameter (BCD) be R0, the polar radius of front side inner spiral casing (4) is R, between the mid-game (21) and front side inner spiral casing (4) of impeller (2)
Vertical range be B0, the width of front side inner spiral casing (4) is B1, and the initial angle of front side inner spiral casing (4) is θ 0, then meets following public
Formula:
6. centrifugal blower according to claim 1, it is characterised in that: impeller (2) the back outlet speed is in axial direction
Component is C2m ', and the component in circumferencial direction of impeller (2) back outlet speed is C2u ', and impeller (2) outer diameter is R2, spiral case
(1) base circle diameter (BCD) is R0, and the polar radius of rear side inner spiral casing (5) is R ', mid-game (21) and rear side inner spiral casing (5) of impeller (2)
Between vertical range be B2, the width of rear side inner spiral casing (5) is B3, and the initial angle of rear side inner spiral casing (5) is 0 ' of θ, then meets
Following formula:
7. according to claim 1 to centrifugal blower described in any claim in 6, it is characterised in that: in the spiral case (1)
Rear side is equipped with motor mounting rack (6), and the motor (3) is mounted on the motor mounting rack (6).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710844636.8A CN109519416B (en) | 2017-09-19 | 2017-09-19 | Centrifugal fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710844636.8A CN109519416B (en) | 2017-09-19 | 2017-09-19 | Centrifugal fan |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109519416A true CN109519416A (en) | 2019-03-26 |
| CN109519416B CN109519416B (en) | 2024-01-16 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710844636.8A Active CN109519416B (en) | 2017-09-19 | 2017-09-19 | Centrifugal fan |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109519416B (en) |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030012649A1 (en) * | 2001-07-16 | 2003-01-16 | Masaharu Sakai | Centrifugal blower |
| JP2008008154A (en) * | 2006-06-27 | 2008-01-17 | Hitachi Plant Technologies Ltd | Double suction centrifugal pump |
| CN201526472U (en) * | 2009-09-25 | 2010-07-14 | 浙江苏泊尔家电制造有限公司 | Centrifugal fan with air inlet at both surfaces |
| CN102959250A (en) * | 2010-10-25 | 2013-03-06 | 三菱重工业株式会社 | Multi-blade centrifugal fan and air conditioner using same |
| CN103534461A (en) * | 2011-06-10 | 2014-01-22 | 博格华纳公司 | Double flow turbine housing turbocharger |
| CN203453126U (en) * | 2013-09-09 | 2014-02-26 | 株洲联诚集团有限责任公司 | Double-volute centrifugal ventilator for heat dissipation of generator cooling system |
| CN103742453A (en) * | 2013-12-30 | 2014-04-23 | 宁波方太厨具有限公司 | Range hood centrifugal fan with double air inlet structure |
| CN104295531A (en) * | 2014-09-19 | 2015-01-21 | 珠海格力电器股份有限公司 | Centrifugal fan and air conditioner |
| CN106524263A (en) * | 2016-12-16 | 2017-03-22 | 宁波方太厨具有限公司 | Range hood |
| CN206338839U (en) * | 2016-12-16 | 2017-07-18 | 宁波方太厨具有限公司 | A kind of range hood |
-
2017
- 2017-09-19 CN CN201710844636.8A patent/CN109519416B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030012649A1 (en) * | 2001-07-16 | 2003-01-16 | Masaharu Sakai | Centrifugal blower |
| JP2008008154A (en) * | 2006-06-27 | 2008-01-17 | Hitachi Plant Technologies Ltd | Double suction centrifugal pump |
| CN201526472U (en) * | 2009-09-25 | 2010-07-14 | 浙江苏泊尔家电制造有限公司 | Centrifugal fan with air inlet at both surfaces |
| CN102959250A (en) * | 2010-10-25 | 2013-03-06 | 三菱重工业株式会社 | Multi-blade centrifugal fan and air conditioner using same |
| CN103534461A (en) * | 2011-06-10 | 2014-01-22 | 博格华纳公司 | Double flow turbine housing turbocharger |
| CN203453126U (en) * | 2013-09-09 | 2014-02-26 | 株洲联诚集团有限责任公司 | Double-volute centrifugal ventilator for heat dissipation of generator cooling system |
| CN103742453A (en) * | 2013-12-30 | 2014-04-23 | 宁波方太厨具有限公司 | Range hood centrifugal fan with double air inlet structure |
| CN104295531A (en) * | 2014-09-19 | 2015-01-21 | 珠海格力电器股份有限公司 | Centrifugal fan and air conditioner |
| CN106524263A (en) * | 2016-12-16 | 2017-03-22 | 宁波方太厨具有限公司 | Range hood |
| CN206338839U (en) * | 2016-12-16 | 2017-07-18 | 宁波方太厨具有限公司 | A kind of range hood |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109519416B (en) | 2024-01-16 |
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