CN208804044U - A kind of centrifugal blower with spiral case - Google Patents
A kind of centrifugal blower with spiral case Download PDFInfo
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- CN208804044U CN208804044U CN201821369078.0U CN201821369078U CN208804044U CN 208804044 U CN208804044 U CN 208804044U CN 201821369078 U CN201821369078 U CN 201821369078U CN 208804044 U CN208804044 U CN 208804044U
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Abstract
The utility model relates to a kind of centrifugal blower with spiral case, including spiral case, spiral case inlet pressure includes the first helix CD1, the second helix E1The M and Bezier D being arranged between1E1, the first helix CD1For the equiangular helical spiral that the angle of flare is constant, the second helix E1M is the tapered variable angle spiral of the angle of flare, curve D1E1D1Point and E1Point is located at the horizontal line OH by spiral case center O1Two sides up and down, wherein H1Point is to controlling curve D1E1The control point of bending direction, control point H1Positioned at the curve D1E1On.
Description
Technical field
The utility model relates to a kind of centrifugal blowers with spiral case, and in particular to a kind of centrifugal blower with spiral case.
Background technique
Domestic cooking fume remover is realized using centrifugal blower to be extracted oil laden air out kitchen and is discharged into common flue or direct
Discharge is outdoor, wherein the advantages that centrifugal blower is big, noise is low, compact-sized with its suction and obtained in range hood wide
General reference.Spiral case is one of core component of centrifugal blower, and effect is will to leave the gas concentration of impeller, exports to spiral case
Mouthful, and dynamic pressure is changed into static pressure.The volute structure of existing centrifugal blower includes spiral case top plate, spiral case bottom plate and connection spiral case top
The spiral case coaming plate of plate, spiral case bottom plate, wherein remaining molded line in addition to volute tongue position is consistent with spiral case bottom plate for spiral case top plate.Conventional volute
Design is generally carried out by a metatheory, and there are two it is assumed that assuming that flow parameter is uniformly distributed and in spiral case on import circumference
Air-flow momentum moment preserving, the spiral case inlet pressure by unitary Theoretical Design are usually equiangular helical spiral.But actually due to volute shape
The influence of non-axis symmetry, especially volute tongue will form a pressure field heterogeneous in impeller outlet, impeller will necessarily be made to go out
Mouthful, i.e. spiral case inlet flow field is uneven.Since a metatheory does not consider the non-of import circumference flow parameter in spiral case circumferential plane
The influence of uniformity and flow field, thus it is bad by the spiral case performance that this Theoretical Design comes out, especially in high back pressure working condition
Deterioration becomes apparent.
The volute structure of various centrifugal blowers is also disclosed in the prior art, such as Patent No. CN 201110118687.5
" a kind of centrifugal blower used for range hood and its snail disclosed in the Chinese invention patent of (Authorization Notice No. CN102182707B)
Shell mould line generation method ", which includes spiral case top plate, spiral case bottom plate and spiral case coaming plate, the profile in spiral case coaming plate medial type face
Line is spiral case inlet pressure, and spiral case inlet pressure is by first straight line DE, the first circular arc line EF, the second circular arc line FG, helix GH, second straight line
Section HI smoothly transits and is formed by connecting, although, after spiral case uses above-mentioned spiral case inlet pressure, be conducive to improve centrifugal blower air quantity, wind pressure,
Efficiency simultaneously reduces aerodynamic noise, but the volute structure is again without fully considering import circumference flow parameter in spiral case circumferential plane
Heterogeneity and flow field influence, and the side-to-side dimensions of spiral case compare larger, influence product outline size.
In order to solve the above-mentioned technical problem, as in CN201720581486.1 (Authorization Notice No. CN206845544U)
State's utility model patent " a kind of centrifugal blower volute " is successively arranged first between the start line AC and end lines MN of spiral case inlet pressure
The D point and E point of helix CD, trimming DE and the second helix EM, trimming DE are located at the horizontal line by spiral case central point O
The two sides up and down of OH, the first helix CD are the constant equiangular helical spiral of the angle of flare, and the second helix EM is that the angle of flare is tapered
Variable angle spiral.Above-mentioned centrifugal blower volute molded line further reduces the side-to-side dimensions of spiral case, improves spiral case internal gas flow
Collect, reduce spiral case internal airflow resistance, but the tangent line DE of the centrifugal blower volute molded line be equivalent to by spiral case right side into
Row local excision, although what the trimming DE of excision may result in that flowing when there is air-flow by the trimming has some setbacks asks
Topic.
Utility model content
Technical problem to be solved in the utility model is in view of the above-mentioned state of the art, to provide a kind of in holding snail
Shell side-to-side dimensions can improve the centrifugal blower with spiral case for the fluency that spiral case internal gas flow passes through while reducing.
Technical solution adopted by the utility model to solve the above technical problems is as follows: a kind of centrifugal blower with spiral case,
Including spiral case, the spiral case inlet pressure of the spiral case includes the end lines positioned at the start line AC of molded line one end and positioned at the molded line other end
MN is equipped with the first helix CD between the start line AC and end lines MN1With the second helix E1M, first helix
CD1For the equiangular helical spiral that the angle of flare is constant, the second helix E1M is the tapered variable angle spiral of the angle of flare, and feature exists
In: the first helix CD1With the second helix E1Curve D is provided between M1E1, the curve D1E1For Bezier,
The curve D1E1D1Point and E1Point is located at the horizontal line OH by spiral case center O1Two sides up and down, wherein H1Point is use
With controlling curve D1E1The control point of bending direction, the control point H1Positioned at the curve D1E1On.
In order to further reduce spiral case side-to-side dimensions, the Bezier D1E1Upper starting point D1Coordinate be PD1, knot
Beam spot E1Coordinate be PE1, control point H1Coordinate be PH1, the coordinate satisfaction of W:Bezier D1E1Meet Bi=(1-s)2PD1+2s(1-s)PH1+s2PE1, s ∈ [0,1], wherein PH1(LOH1, 0), LOH1For the control point H on Bezier1With spiral case
The distance between center O, LOH1=LOH, LOHBetween the H point on the trimming DE on existing spiral case inlet pressure and spiral case center O away from
From OH is the horizontal line by spiral case center O.In this way, improving the fluency that spiral case internal gas flow is collected with passed through, improve
The static pressure of maximum static pressure and effective wind rate section realizes and reaches big spiral case effect under small size, reduces aerodynamic noise；Simultaneously
Transition is carried out using Bezier, so that molded line connection is more smooth smooth, reduces spiral case interior air-flow because curvature mutation is made
At separation loss, reduce whirlpool cause noise.
In order to reduce the influence after existing spiral case inlet pressure is cut off to centrifugal blower performance, the existing spiral case inlet pressure trimming DE
On H point and the distance between spiral case center O LOHWith impeller outer diameter R2Relationship are as follows: LOH/R2∈[1,1.5]。
In order to prevent from the first helix to curvature mutation when Bezier transition, the Bezier D1E1On
Starting point D1Abscissa PD1(x)With the starting point D abscissa P of trimming DED(x)Relationship meet: PD1(x)=PD(x)+ d, d/R2∈[-
0.08,0], the starting point D1 abscissa P on the Bezier D1E1D1(x), the Bezier D1E1On starting point
D1Ordinate PD1(y)It is by the first helix CD1And PD1(x)Defined by.In this way, passing through impeller outer diameter R2Determine the d of offset,
Can be excessive to avoid offset, curvature mutation is prevented, and then prevent by curvature mutation and its local losses is caused to increase, stream
The problem of amount loss increases.
In order to reduce the influence after existing spiral case inlet pressure is cut off to centrifugal blower performance, the trimming of the existing spiral case inlet pressure
Angle formed by line OD between the starting point D and spiral case center O of the DE and horizontal line OH by spiral case center O is ψ, described
The starting point D abscissa P of trimming DED(x)It is by LOHWith defined by ψ, wherein 0≤ψ≤20 °.
Preferably, the first helix CD1Polar radius RCD1Is defined as:Wherein, t
For the design gaps on the volute tongue top of impeller excircle and spiral case, and t/R2∈ [0.01,0.15], the angle of flare α ∈ [3 °, 8 °], θ0
For the first helix CD1D1The start angle of point, and θ0∈ [60 °, 180 °], θ are the first helix CD1The pole of upper arbitrary point
Coordinate angle variables.
In order to prevent from Bezier to curvature mutation when the second helix transition, the Bezier D1E1On
End point E1 abscissa PE1(x)With the end point E abscissa P of trimming DEE(x)Relationship meet: PE1(x)=PE(x)+ e, e/R2∈[-
0.08,0], wherein R2 is the outer diameter of impeller, the Bezier D1E1On end point E1Ordinate PE1(y)It is by the second spiral shell
Spin line E1M and PE1(x)Defined by.In this way, passing through impeller outer diameter R2Determine the e of offset, can be excessive to avoid offset, prevent
The problem of only curvature mutation, and then prevent by curvature mutation and its local losses is caused to increase, flow loss increases.
In order to reduce the influence after existing spiral case inlet pressure is cut off to centrifugal blower performance, the trimming DE's of existing spiral case inlet pressure
Angle ω, end point E abscissa P formed by line OE and horizontal line OH between end point E and spiral case center OE(x)It is by LOH
With defined by ω, wherein 0≤ω≤25 °.
Preferably, the second helix E1The polar radius R of ME1MIs defined as: α1And α2All ∈ [3,8], and α1≥a2,Adjustment item s
∈ [- 0.5,0.5], r ∈ [- 5,5] and r ≠ 1, θ are the second helix E1The polar angle variable of the upper arbitrary point M, α1For E1's
The angle of flare, α2For the angle of flare of M point,For the cornerite of the second helix.
Compared with the prior art, the advantages of the utility model are: by the first helix CD1With the second helix E1M
Between be arranged Bezier D1E1, the first helix is equiangular helical spiral, and the second helix is the tapered angle spiral of the angle of flare
Line, on the one hand, reduce spiral case side-to-side dimensions, improve the fluency that spiral case internal gas flow is collected with passed through, improve maximum
The static pressure of static pressure and effective wind rate section realizes and reaches big spiral case effect under small size, reduces aerodynamic noise；Another party
Face carries out transition using Bezier, shortens helix, so that molded line connection is more smooth smooth, reduces gas in spiral case
Stream reduces the aerodynamic noise that whirlpool causes because separating loss caused by curvature mutation.In addition, the control point of Bezier with
Trimming and the position of the horizontal intersection point by spiral case center remain unchanged on existing spiral case inlet pressure, to make spiral case or so ruler
Very little diminution.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of the utility model embodiment one；
Fig. 2 is the structural schematic diagram (having trimming DE) of spiral case inlet pressure in the prior art；
Fig. 3 is the structural schematic diagram that the utility model implements two；
Fig. 4 is the structural schematic diagram of spiral case inlet pressure in the prior art.
Specific embodiment
The utility model is described in further detail below in conjunction with figure embodiment.
As shown in Figure 1, first preferred embodiment of the utility model.
The centrifugal blower with spiral case of the present embodiment includes spiral case, and the spiral case inlet pressure of spiral case includes being located at molded line one end
Start line AC and end lines MN positioned at the molded line other end, wherein start line AC include neighbouring fan outlet straight line AB and
Corresponding to the curve BC at spiral case volute tongue position, air outlet of the end lines MN adjacent to blower.
The first helix CD is successively arranged between start line AC and end lines MN1, curve D1E1And the second helix E1M,
Wherein, the first helix CD1For the equiangular helical spiral that the angle of flare is constant, the second helix E1M is the tapered angle spiral of the angle of flare
Line, curve D1E1For Bezier, curve D1E1D1Point and E1Point is located at by spiral case center O (i.e. impeller center point)
Horizontal line OH1Two sides up and down, horizontal line OH1It is equivalent to the horizontal line by spiral case basic circle center, wherein H1Point for
Controlling curve D1E1The control point of bending direction, control point H1Positioned at curve D1E1On.In addition, end lines MN includes neighbouring air outlet
Straightway and neighbouring E1The curved section of M.
As shown in Figure 1, Bezier D1E1Upper starting point D1Coordinate be PD1, end point E1Coordinate be PE1, control point
H1Coordinate be PH1, Bezier D1E1On point W coordinate meet:Bezier D1E1Meet Bi=(1-s)2PD1
+2s(1-s)PH1+s2PE1, s ∈ [0,1], wherein PH1(LOH1, 0), LOH1For the control point H on Bezier1With spiral case center
The distance between O, LOH1≤LOH', LOH' it is point H ' and the distance between spiral case center O on existing spiral case inlet pressure, OH ' is to pass through
Cross the horizontal line of spiral case center O.
Existing spiral case inlet pressure in the present embodiment refers to spiral case inlet pressure as shown in Figure 2, existing spiral case inlet pressure
The first helix CD, trimming DE and the second helix EM, the first helix are disposed between start line AC and end lines MN
CD is the constant equiangular helical spiral of the angle of flare, and the second helix EM is the tapered variable angle spiral of the angle of flare, wherein start line AC
Including the straight line AB adjacent to fan outlet and corresponding to the curve BC at spiral case volute tongue position, the D point and E point of trimming DE distinguishes position
In the two sides up and down of the horizontal line OH of spiral case center O, after trimming DE is set on spiral case inlet pressure, it is equivalent to and is carried out on rear side of spiral case
Local excision, in the present embodiment, H ' is equivalent to the H point on trimming DE, then in the present embodiment, LOH1=LOH, LOHFor existing spiral case
The distance between H point and spiral case center O on trimming DE on molded line, LOHWith the relationship of impeller outer diameter R2 are as follows: LOH/R2∈[1,
1.5].In addition, line OD between the starting point D and spiral case center O of trimming DE and by spiral case center O horizontal line OH institute at
Angle be ψ, angle ω formed by the line OE between the end point E and spiral case center O of trimming DE and horizontal line OH, wherein 0
≤ ψ≤20 °, 0≤ω≤25 °.
In the present embodiment, Bezier D1E1On starting point D1Abscissa PD1(x)With the starting point D abscissa of trimming DE
PD(x)Relationship meet: PD1(x)=PD(x)+ d, d/R2The starting point D abscissa P of ∈ [- 0.08,0], trimming DED(x)It is by LOHAnd ψ
Defined by, Bezier D1E1On starting point D1Ordinate PD1(y)It is by the first helix CD1And PD1(x)Defined by.
The first above-mentioned helix CD1Polar radius RCD1Is defined as:Wherein, t is impeller
The design gaps on the volute tongue top of excircle and spiral case, and t/R2∈ [0.01,0.15], the angle of flare α ∈ [3 °, 8 °], θ0It is first
Helix CD1D1The start angle of point, and θ0∈ [60 °, 180 °], θ are the first helix CD1The polar coordinates angle of upper arbitrary point
Spend variable.
In the present embodiment, Bezier D1E1On end point E1Abscissa PE1(x)With the end point E abscissa of trimming DE
PE(x)Relationship meet: PE1(x)=PE(x)+ e, e/R2∈ [- 0.08,0], wherein R2 is the outer diameter of impeller, end point E abscissa
PE(x)It is by LOHWith defined by ω, Bezier D1E1On end point E1Ordinate PE1(y)It is by the second helix E1M and
PE1(x)Defined by.In the present embodiment, in the maximum width L of spiral case inlet pressure as shown in Figure 2OHWith the spiral case inlet pressure in Fig. 1
Maximum width LOH1Under conditions of remaining unchanged, the starting point D of Bezier1D point on relatively existing spiral case inlet pressure occurs inclined
It moves, the end point E of Bezier1End point E on relatively existing spiral case inlet pressure shifts, and passes through impeller outer diameter R2It determines
Offset d and e, can be excessive to avoid offset, prevents curvature from mutating, and then prevents by curvature mutation and lead to it
The problem of local losses increases, and flow loss increases.
The second above-mentioned helix E1The polar radius R of ME1MIs defined as: α1And α2All ∈ [3,8], and α1≥α2,Adjustment item s
∈ [- 0.5,0.5], r ∈ [- 5,5] and r ≠ 1, θ are the second helix E1The polar angle variable of the upper arbitrary point M, α1For E1's
The angle of flare, α2For the angle of flare of M point,For the cornerite of the second helix.
In the present embodiment, the starting point D of Bezier1With the line OD between the O of spiral case center1With process spiral case center O
Horizontal line OH1Formed angle is ψ1, the end point E of Bezier1With the line OE between the O of spiral case center1With horizontal line
OH1Formed angle ω1, wherein ψ1> ψ, ω1> ω.
Embodiment two:
As shown in figure 3, being second preferred embodiments of the utility model.The difference of the embodiment and above-described embodiment is only
It is: by Bezier D1E1One section of log spiral in the prior art is substituted, is reducing spiral case or so ruler to reach
While very little, increase the fluency of air-flow.
As shown in figure 4, for the spiral case inlet pressure of the prior art targeted in the present embodiment, the start line AC of the spiral case inlet pressure
It is that the angle of flare is constant that the first helix CD and the second helix DM, the first helix CD are disposed between end lines MN
Equiangular helical spiral, the second helix DM are the tapered variable angle spiral of the angle of flare, and the second helix DM is with process spiral case center O's
Horizontal intersection point is H ', carries out trimming on the second helix DM, which is DE, trimming DE and process spiral case center O
Horizontal intersection point is H, wherein LOH< LOH’。
As shown in figure 3, the position that the spiral case inlet pressure in the present embodiment is to maintain H point is constant, by one section of shellfish by H point
Sai Er curve D1E1Section spiral line acquisition is substituted, i.e., is set gradually between the start line AC and end lines MN of the spiral case inlet pressure
There are the first helix CD, Bezier D1E1, the second helix E1M, curve D1E1D1Point and E1Point is located at by snail
The horizontal line OH of shell center O (i.e. impeller center point)1Two sides up and down, horizontal line OH1It is equivalent to by spiral case basic circle center
Horizontal line, wherein H1Point is to controlling curve D1E1The control point of bending direction, control point H1Positioned at curve D1E1On, LOH1=
LOH。
Claims (9)
1. a kind of centrifugal blower with spiral case, including spiral case, the spiral case inlet pressure of the spiral case includes rising positioned at molded line one end
Initial line AC and end lines MN positioned at the molded line other end is equipped with the first helix CD between the start line AC and end lines MN1
With the second helix E1M, the first helix CD1For the equiangular helical spiral that the angle of flare is constant, the second helix E1M is
The tapered variable angle spiral of the angle of flare, it is characterised in that: the first helix CD1With the second helix E1Song is provided between M
Line D1E1, the curve D1E1For Bezier, the curve D1E1D1Point and E1Point is located at by spiral case center O's
Horizontal line OH1Two sides up and down, wherein H1Point is to controlling curve D1E1The control point of bending direction, the control point H1It is located at
The curve D1E1On.
2. the centrifugal blower according to claim 1 with spiral case, it is characterised in that: the Bezier D1E1It goes up
Initial point D1Coordinate be PD1, end point E1Coordinate be PE1, control point H1Coordinate be PH1, the coordinate satisfaction of W:Bezier D1E1Meet Bi=(1-s)2PD1
+2s(1-s)PH1+s2PE1, s ∈ [0,1], wherein PH1(LOH1, 0), LOH1For the control point H on Bezier1With spiral case center
The distance between O, LOH1=LOH, LOHFor the H point and the distance between spiral case center O on the trimming DE on existing spiral case inlet pressure,
OH is the horizontal line by spiral case center O.
3. the centrifugal blower according to claim 2 with spiral case, it is characterised in that: cutting on the existing spiral case inlet pressure
The distance between H point and spiral case center O on the DE of side LOHWith impeller outer diameter R2Relationship are as follows: LOH/R2∈[1,1.5]。
4. the centrifugal blower according to claim 3 with spiral case, it is characterised in that: the Bezier D1E1On
Starting point D1Abscissa PD1(x)With the starting point D abscissa P of trimming DED(x)Relationship meet: PD1(x)=PD(x)+ d, d/R2∈[-
0.08,0], the Bezier D1E1On starting point D1Ordinate PD1(y)It is by the first helix CD1And PD1(x)It is limited
's.
5. the centrifugal blower according to claim 4 with spiral case, it is characterised in that: the trimming of the existing spiral case inlet pressure
Angle formed by line OD between the starting point D and spiral case center O of the DE and horizontal line OH by spiral case center O is ψ, described
The starting point D abscissa P of trimming DED(x)It is by LOHWith defined by ψ, wherein 0≤ψ≤20 °.
6. the centrifugal blower according to claim 5 with spiral case, it is characterised in that: the first helix CD1Pole half
Diameter RCD1Is defined as:Wherein, between design of the t for the volute tongue top of impeller excircle and spiral case
Gap, and t/R2∈ [0.01,0.15], the angle of flare α ∈ [3 °, 8 °], θ0For the first helix CD1D1The start angle of point, and θ0
∈ [60 °, 180 °], θ are the first helix CD1The polar angle variable of upper arbitrary point.
7. the centrifugal blower according to claim 3 with spiral case, it is characterised in that: the Bezier D1E1On
End point E1Abscissa PE1(x)With the end point E abscissa P of trimming DEE(x)Relationship meet: PE1(x)=PE(x)+ e, e/R2∈[-
0.08,0], wherein R2For the outer diameter of impeller, the Bezier D1E1On end point E1Ordinate PE1(y)It is by the second spiral shell
Spin line E1M and PE1(x)Defined by.
8. the centrifugal blower according to claim 4 with spiral case, it is characterised in that: the trimming DE's of existing spiral case inlet pressure
Angle ω, end point E abscissa P formed by line OE and horizontal line OH between end point E and spiral case center OE(x)It is by LOH
With defined by ω, wherein 0≤ω≤25 °.
9. the centrifugal blower according to claim 8 with spiral case, it is characterised in that: the second helix E1The pole of M half
Diameter RE1MIs defined as: α1And α2All
∈ [3,8], and α1≥α2,Adjustment item s ∈ [- 0.5,0.5], r ∈ [- 5,5] and r ≠ 1, θ are the second helix
E1The polar angle variable of the upper arbitrary point M, α1For E1The angle of flare, α2For the angle of flare of M point,For the packet of the second helix
Angle.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201821369078.0U CN208804044U (en) | 2018-08-23 | 2018-08-23 | A kind of centrifugal blower with spiral case |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821369078.0U CN208804044U (en) | 2018-08-23 | 2018-08-23 | A kind of centrifugal blower with spiral case |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111159792A (en) * | 2020-01-07 | 2020-05-15 | 宁波方太厨具有限公司 | Volute profile generation method of centrifugal fan |
| CN112833032A (en) * | 2020-11-02 | 2021-05-25 | 宁波方太厨具有限公司 | Parallel double-fan system and range hood applying same |
-
2018
- 2018-08-23 CN CN201821369078.0U patent/CN208804044U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111159792A (en) * | 2020-01-07 | 2020-05-15 | 宁波方太厨具有限公司 | Volute profile generation method of centrifugal fan |
| CN111159792B (en) * | 2020-01-07 | 2023-08-18 | 宁波方太厨具有限公司 | Volute molded line generation method of centrifugal fan |
| CN112833032A (en) * | 2020-11-02 | 2021-05-25 | 宁波方太厨具有限公司 | Parallel double-fan system and range hood applying same |
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