CN110080999A - A kind of centrifugal blower with efficient aerodynamic efficiency - Google Patents
A kind of centrifugal blower with efficient aerodynamic efficiency Download PDFInfo
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- CN110080999A CN110080999A CN201910402334.4A CN201910402334A CN110080999A CN 110080999 A CN110080999 A CN 110080999A CN 201910402334 A CN201910402334 A CN 201910402334A CN 110080999 A CN110080999 A CN 110080999A
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- Prior art keywords
- symmetroid
- guide vane
- air inlet
- curved surface
- leaf
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
- F04D17/12—Multi-stage pumps
- F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
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- 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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/051—Axial thrust balancing
-
- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
-
- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
-
- 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
-
- 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
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
-
- 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
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
-
- 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
- F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
Abstract
The invention discloses a kind of centrifugal blowers with efficient aerodynamic efficiency, it is respectively equipped with symmetroid in the air inlet runner of its air intake casing and dominates leaf group and symmetroid pair guide vane group, and symmetroid dominates leaf group relative to symmetroid pair guide vane group close to air inlet；The two sides guide vane side of the leading leaf group of symmetroid and symmetroid pair guide vane group is corresponding with inner wall shape before and after air intake casing respectively and extends；Each blade of impeller includes positioned at the forward-type blade sections close to axial admission mouth one end and positioned at the backward type blade sections close to radial exhaust outlet one end, and forward-type blade sections are connect with backward type blade sections using radial vane section；The present invention is by carrying out special structure design to air intake casing and impeller blade, so that centrifugal blower has high intake efficiency, high pneumatic efficiency, high aerodynamic loading and the small Multiple techniques effect of aerodynamic noise simultaneously, the centrifugal blower with efficient aerodynamic efficiency has been finally obtained.
Description
Technical field
The invention belongs to centrifugal blower product manufacturing fields, and in particular to a kind of centrifugation with efficient aerodynamic efficiency
Air blower.
Background technique
The working principle of cfentrifugal blower increases the dynamic of gas mainly using several rotary blades to air work
Can, then by centrifugal action and diffusion process, improve the pressure of gas, to reach certain air quantity and wind pressure, and then reach big
The technical effect of flow high-pressure blowing-in.Cfentrifugal blower is because it is blown effect with preferable big-flow high-pressure, thus in dirt
Water process, power plant desulfurization and other industrial circles are used widely.
Cfentrifugal blower mainly includes the air intake casing for being equipped with air inlet, rotary drive unit, using rotary blade structure
At gas compression unit and the core components such as exit casing equipped with exhaust outlet, wherein air intake casing, impeller and exhaust
Structure and the shape setting of casing can all directly affect the pneumatic efficiency of centrifugal blower.
Specifically, one, in the cfentrifugal blower of the prior art, it will usually in the air inlet runner of air intake casing
A plurality of gusset is set, design gusset function be as structural reinforcement reinforcing rib act on, therefore all be using have one
That determines thickness faces the design of plate muscle chip architecture directly, does not make a concrete analysis of and studies it to influence brought by gas distribution when air inlet.
Secondly, in the centrifugal blower of the prior art, the shape of the shape of impeller blade, quantity and fan disk
It is the central factor for determining centrifugal blower pneumatic efficiency.In order to meet the performance needs that it is applied to all kinds of fields, Ren Mentong
Impeller blade is often designed to backward type, forward-type and three kinds of radial, wherein the bending direction and gas of backward type blade
Motion profile it is identical, pneumatic efficiency is high and noise is small, but aerodynamic loading is low；The bending direction of forward-type blade and the fortune of gas
Dynamic rail mark is on the contrary, aerodynamic loading is high, but since gas by blade changes direction by force, pneumatic efficiency is lower and noise compared with
Greatly；The bending direction of radial vane and the motion profile of gas are vertical, and correlated performance is between backward type blade and forward-type
Between blade；By that as can be seen that existing impeller blade respectively has advantage and disadvantage, can not have high pneumatic efficiency simultaneously above
With the performance of high aerodynamic loading.
Present inventor is based on many years development Experience in Fan Product field and with fluid flow mechanism
Theoretical knowledge, it is desirable to be realized by carrying out innovation structure design to dependency structure to the higher pneumatic efficiency of cfentrifugal blower.
Summary of the invention
In view of this, the purpose of the present invention is to provide a kind of centrifugal blowers with efficient aerodynamic efficiency, by right
Air intake casing and impeller blade carry out special structure design, so that centrifugal blower has high intake efficiency, height pneumatic simultaneously
Efficiency, high aerodynamic loading and the small Multiple techniques effect of aerodynamic noise, have finally obtained the centrifugation with efficient aerodynamic efficiency
Air blower.
The present invention, there are after technical problem described in background technique as above, relies on for many years in the existing cfentrifugal blower of discovery
Development Experience, by carrying out CFD calculating to air intake casing runner and impeller three-dimensional aerodynamics, while it is deeply divided
Analysis, optimizes the planform of air inlet runner and impeller, reduces flow boundary layer separation, the inside whirlpool group of air inlet runner
Generation and migration, more preferably aerodynamic loading distributed controll is realized while improving the pneumatic efficiency of centrifugal blower, is based on this,
The applicant finally proposes following technical solution:
A kind of centrifugal blower with efficient aerodynamic efficiency, including the rotation master being sequentially connected with rotary drive unit
Axis, the air intake casing being connected as one with live spindle installation, the multi-stage impeller being mounted in central enclosure and exhaust
Shell, wherein the air intake casing is equipped with the air inlet and air inlet runner being located above, and the air inlet passes through the inlet air flow
Road is connected with the impeller；It is respectively equipped with symmetroid in the air inlet runner and dominates leaf group and symmetroid pair guide vane group,
And the symmetroid dominates leaf group relative to the symmetroid pair guide vane group close to the air inlet；The symmetroid master
The two sides guide vane side of guide vane group and symmetroid pair guide vane group is corresponding with inner wall shape before and after the air intake casing respectively and prolongs
It stretches；
The impeller includes the impeller disk and several blades on the impeller disk, and each blade is evenly arranged on described
The inner circumferential of the impeller disk, the impeller disk are equipped with the rotary shaft hole and air inlet runner that connection is fixedly mounted with the live spindle
The axial admission mouth of connection and the radial exhaust outlet being connected to flow channel out；Each blade includes being located at close to the axis
To the forward-type blade sections of air inlet one end and positioned at the backward type blade sections close to described radial exhaust outlet one end, before described
It is connect to formula blade sections with the backward type blade sections using radial vane section.
Preferably, the symmetroid is dominated the root of leaf group and the root of the symmetroid pair guide vane group and is distributed in together
On one periphery concentric with the bearing block axis hole, the diameter of the periphery is less than the bore of the air inlet；And it is described
The root spacing that symmetroid dominates leaf group is less than the root spacing of the symmetroid pair guide vane group；The symmetroid is leading
Leaf group length is greater than the symmetroid pair guide vane group length.
Preferably, the air inlet runner is in arc surfaced, and internal diameter becomes larger along the air inlet to down toward the major axes orientation,
The air intake casing bottom includes the left arc surface shell wall and right arc surface shell wall for being symmetric and intersecting simultaneously, wherein institute
It states cross-shaped portion between left arc surface shell wall and right arc surface shell wall and the symmetroid and dominates the root of leaf group and described
The root of symmetroid pair guide vane group is distributed on the same periphery.
Preferably, it includes dominating leaf and right curved surface master in the left curved surface of symmetrical shape distribution that the symmetroid, which dominates leaf group,
Guide vane, the curvature that the left curved surface dominates leaf become smaller from its root to end direction；The symmetroid pair guide vane group is including being in
The left curved surface pair guide vane and right curved surface pair guide vane of symmetrical shape distribution, the curvature of the left curved surface pair guide vane is from its root to end
Direction becomes larger.
Preferably, the curvature that the leading leaf of the left curved surface is located at root is greater than the song that the left curved surface pair guide vane is located at root
Rate, and the left curved surface dominates leaf and is located at the curvature that the curvature of end is located at end less than the left curved surface pair guide vane.
Preferably, the root spacing that the left curved surface dominates that leaf and right curved surface are dominated between leaf is led less than the left curved surface pair
Root spacing between leaf and right curved surface pair guide vane；Simultaneously between the end between the leading leaf of the left curved surface and the leading leaf of right curved surface
Away from the bore for being less than the air inlet, end spacing between the left curved surface pair guide vane and right curved surface pair guide vane be greater than it is described into
The bore of port.
Preferably, the quantity of the blade is 8-16；The air inlet angle range of the forward-type blade sections is at 35-75 °；
The outlet angular range of the backward type blade sections is at 25-65 °.
It should be noted that air inlet angle of the present invention and outlet angle refer to that respective leaves segment and impeller are radial
Deviation angle.
Preferably, the live spindle both ends are respectively equipped with spiral shell to opposite air inlet side thread groove and exhaust side thread groove,
The air inlet side thread groove is located at close to the one end on gas inlet shell side, and the exhaust side thread groove is located at close to exit casing side
One end, and the air inlet side thread groove and exhaust side thread groove are distributed in symmetry shape.
Preferably, the centrifugal blower is additionally provided with axial thrust control device, and the axial thrust control device includes
Balancing frame, the balancing frame are set in the live spindle between live spindle end annular gas seals and impeller, and
Balancing frame sealing ring is installed between the balancing frame periphery and the exhaust casing.
The exhaust casing being preferably located between the balancing frame and live spindle end annular gas seals is equipped with pumping
Adapter tube, the pumping adapter tube other end access the air inlet of the air intake casing.
The present invention dominates leaf group and symmetroid pair guide vane by designing symmetroid in the air inlet runner of air intake casing
Group, which dominates leaf group and symmetroid pair guide vane group cooperates, and can preferably realize and suck to air inlet runner
Flow conductivity and cleanliness when gas is effectively combed and is guided to the gas of air inlet runner sucking, keeps its uniform and smooth
Impeller in ground inflow gas compression unit can also effectively reduce flow boundary layer separation and internal whirlpool group in air inlet runner
Generation, significantly reduce air suction and noise, and effectively increase the intake efficiency of centrifugal blower of the present invention, meanwhile, the present invention
Applicant is creatively changed current impeller blade shapes, is put forward for the first time using forward-type blade sections as import, after
To formula blade sections as outlet blade wheel structure, the structure simultaneously using positioned at middle part radial vane section come realize to it is preceding to
The connection of formula and double bent blades sections of backward type, the structure had both remained the pneumatic efficiency height that traditional backward type impeller has and had made an uproar
The small advantage of sound, while its forward-type blade sections makes aerodynamic loading of the invention be improved significantly；
Therefore, ensuring with existing impeller disk dimensional standard not using air intake casing provided by the invention and blade wheel structure
Under the premise of change, by carrying out special structure design to air intake casing and impeller blade, so that centrifugal blower has simultaneously
High intake efficiency, high pneumatic efficiency, high aerodynamic loading and the small Multiple techniques effect of aerodynamic noise, having finally obtained has height
Imitate the centrifugal blower of pneumatic efficiency.
Detailed description of the invention
Attached drawing 1 is the structural representation of the centrifugal blower 10 under the specific embodiment of the invention with efficient aerodynamic efficiency
Figure；
Attached drawing 2 is the front section view of the air intake casing 100 under the specific embodiment of the invention with higher intake efficiency；
Attached drawing 3 is the side sectional view of the air intake casing 100 under the specific embodiment of the invention with higher intake efficiency；
Attached drawing 4 is the positive structure schematic that symmetroid dominates leaf group 200 under the specific embodiment of the invention；
Attached drawing 5 is the side structure schematic diagram that symmetroid dominates leaf group 200 under the specific embodiment of the invention；
Attached drawing 6 is the positive structure schematic of symmetroid pair guide vane group 300 under the specific embodiment of the invention；
Attached drawing 7 is the side structure schematic diagram of symmetroid pair guide vane group 300 under the specific embodiment of the invention；
Attached drawing 8 is the front section view of impeller 30 in the embodiment of the present invention 1；
Attached drawing 9 is the side sectional view of impeller 30 in the embodiment of the present invention 1；
Attached drawing 10 is the positive structure schematic of blade 32 in the embodiment of the present invention 1；
Attached drawing 11 is the side structure schematic diagram of blade 32 in the embodiment of the present invention 1；
Attached drawing 12 is the front section view of impeller 30 ' in the embodiment of the present invention 2；
Attached drawing 13 is the side sectional view of impeller 30 ' in the embodiment of the present invention 2；
Attached drawing 14 is the positive structure schematic of blade 32 ' in the embodiment of the present invention 2；
Attached drawing 15 is the side structure schematic diagram of blade 32 ' in the embodiment of the present invention 2；
Attached drawing 16 is the structural schematic diagram of live spindle 50 under the specific embodiment of the invention；
Attached drawing 17 is structure enlargement diagram at A in Figure 16；
Attached drawing 18 is structure enlargement diagram at B in Figure 16；
Attached drawing 19 is the part section signal of 60 mounting structure of axial thrust control device under the specific embodiment of the invention
Figure.
Specific embodiment
The embodiment of the invention discloses a kind of centrifugal blowers with efficient aerodynamic efficiency, including with rotary drive unit
The live spindle of transmission connection, the air intake casing being connected as one with live spindle installation, the multistage being mounted in central enclosure
Impeller and exhaust casing, wherein air intake casing is equipped with the air inlet and air inlet runner being located above, and air inlet passes through inlet air flow
Road is connected with impeller；It is respectively equipped with symmetroid in air inlet runner and dominates leaf group and symmetroid pair guide vane group, and is symmetrical bent
Leaf group is dominated relative to symmetroid pair guide vane group close to air inlet in face；Symmetroid dominates leaf group and symmetroid pair guide vane group
Two sides guide vane side respectively with air intake casing before and after inner wall shape it is corresponding and extend；Impeller include the impeller disk and be located at the impeller disk
On several blades, each blade is evenly arranged on the inner circumferential of the impeller disk, and the impeller disk is equipped with and connection is fixedly mounted in live spindle
Rotary shaft hole, the axial admission mouth being connected to air inlet runner and the radial exhaust outlet being connected to flow channel out；Each blade packet
It includes and is located at close to the forward-type blade sections of axial admission mouth one end and positioned at the backward type blade close to radial exhaust outlet one end
Section, forward-type blade sections are connect with backward type blade sections using radial vane section.
Technical solution in order to enable those skilled in the art to better understand the present invention, below in conjunction with of the invention real
The attached drawing in example is applied, technical scheme in the embodiment of the invention is clearly and completely described, it is clear that described implementation
Example is only a part of the embodiment of the present invention, instead of all the embodiments.Based on the embodiments of the present invention, this field is common
Technical staff's every other embodiment obtained without making creative work, all should belong to protection of the present invention
Range.
Embodiment 1:
A kind of centrifugal blower 10 with efficient aerodynamic efficiency shown in Figure 1, including with rotary drive unit
The live spindle 50 of (not shown go out) transmission connection, the air intake casing 100 being connected as one with live spindle installation are mounted on
Multi-stage impeller 30 (impeller is not shown in Fig. 1) and exhaust casing 40 in portion's shell 20；
Please further referring to figs. 2 and 3 shown in air intake casing 100, by the bearing for being equipped with bearing (not shown go out)
Seat 110 and the main shaft of centrifugal blower (not shown go out) installation connects, and air intake casing 100 is equipped with the air inlet 120 being located above
With air inlet runner 130, air inlet 120 is connected by air inlet runner 130 with the gas compression unit of centrifugal blower；Inlet air flow
It is respectively equipped with symmetroid in road 130 and dominates leaf group 200 and symmetroid pair guide vane group 300, and symmetroid dominates leaf group 200
Relative to symmetroid pair guide vane group 300 close to air inlet 120；Symmetroid dominates leaf group 200 and symmetroid pair guide vane group
300 two sides guide vane side is corresponding with air intake casing 100 front and back inner wall, 140 shapes respectively and extends；
Preferably, in the present embodiment, symmetroid dominates leaf group 200 and symmetroid pair guide vane group 300 and air inlet
Shell 100 uses integrally casting shaping；
Preferably, in the present embodiment, symmetroid dominates root and the symmetroid pair guide vane group 300 of leaf group 200
Root be distributed on the same periphery 150 concentric with bearing block axis hole 111, the diameter of periphery 150 is less than air inlet 120
Bore；And symmetroid dominates the root space D of leaf group 200210Less than the root spacing of symmetroid pair guide vane group 300
D310；
Preferably, please further referring to fig. 4 and shown in Fig. 5, in the present embodiment, symmetroid is dominated leaf group 200 and is wrapped
Include and dominate leaf 210 and right curved surface in the left curved surface of symmetrical shape distribution and dominate leaf 220, left curved surface dominate the curvature of leaf 210 from its
Root becomes smaller to end direction；Please with further reference to shown in Fig. 6 and Fig. 7, symmetroid pair guide vane group 300 includes in shape pair
Claim the left curved surface pair guide vane 310 and right curved surface pair guide vane 320 of distribution, the curvature of left curved surface pair guide vane 210 is from its root to end
Direction becomes larger；
It is further preferred that in the present embodiment, air inlet runner 120 is in arc surfaced, internal diameter is downward along air inlet 110
Become larger to major axes orientation, while 100 bottom of air intake casing includes being symmetric and the left arc surface shell wall 160a intersected and the right side
Arc surface shell wall 160b, wherein cross-shaped portion and left curved surface master between left arc surface shell wall 160a and right arc surface shell wall 160b
The root of leaf 220, the root of left curved surface pair guide vane 310 and right curved surface pair guide vane 320 are dominated in the root of guide vane 210, right curved surface
Root be distributed on same periphery 150, the diameter of periphery 150 is less than the bore D of air inlet 120120；
It is further preferred that in the present embodiment, left curved surface dominates two sides guide vane side 210a, 210b difference of leaf 210
It is corresponding with air intake casing 100 front and back inner wall, 140 shapes and extend；Preferably, in the present embodiment, left curved surface dominates leaf
End space D between 210 and the leading leaf 220 of right curved surface220Less than the bore D of air inlet 120120；Preferably, in this embodiment party
In formula, left curved surface dominates 210 end of leaf to the axial distance L of air inlet 12021The axial distance of periphery 150 is arrived less than it
L22；
It is further preferred that in the present embodiment, two sides guide vane side 310a, 310b of left curved surface pair guide vane 310 distinguish
It is corresponding with air intake casing 100 front and back inner wall, 140 shapes and extend；Preferably, in the present embodiment, left curved surface pair guide vane
End space D between 310 and right curved surface pair guide vane 320320Greater than the bore D of air inlet120；
It is further preferred that in the present embodiment, left curved surface dominates leaf 210 and is located at the curvature of root greater than left curved surface pair
Guide vane 310 is located at the curvature of root, and left curved surface dominates leaf 210 and is located at the curvature of end and is located at less than left curved surface pair guide vane 310
The curvature of end；Preferably, in the present embodiment, between the root between the leading leaf 210 of left curved surface and the leading leaf 310 of right curved surface
Away from D210Less than the root space D between left curved surface pair guide vane 310 and right curved surface pair guide vane 320310；Preferably, in this embodiment party
In formula, the length that left curved surface dominates leaf 210 is greater than the length of left curved surface pair guide vane 310, it is further preferred that in present embodiment
In, the length of the leading leaf 210 of left curved surface is 1.5-3 times of the length of left curved surface pair guide vane 310；
Fig. 8 and a kind of impeller 30 shown in Fig. 9 are referred to, impeller 30 uses the impeller disk 31 of aluminium alloy integrally casting shaping
With several blades 32 being located on the impeller disk 31, each blade 32 is evenly arranged on the inner circumferential of the impeller disk 31, the impeller disk 31 be equipped with
Live spindle 50 be fixedly mounted the rotary shaft hole 33 of connection, the axial admission mouth 34 that is connected to air inlet runner and with flow channel out
The radial exhaust outlet 35 of connection；Wherein, each blade 32 includes positioned at the forward-type blade sections close to 34 one end of axial admission mouth
32a and positioned at backward type the blade sections 32c, forward-type blade sections 32a and backward type blade close to radial 35 one end of exhaust outlet
Section 32c uses radial vane section 32b connection；
Preferably, the embodiment of the present invention carries out three-dimensional aerodynamics CFD calculating by many experiments simultaneously, to impeller 30
Flow mechanism is analysed in depth, and further preferably proposes to set the quantity of blade 32 to 8-16, by blade 32
Structure and quantity carry out after this is specifically designed, and can make centrifugal blower 10 at the same time and have high pneumatic efficiency and high pneumatic carry
It is more excellent in the performance of lotus double technique effect；Particularly preferably, in the present embodiment, the quantity of blade 32 is 8；Before
To formula blade sections 32a air inlet angle range at 35-75 °；The outlet angular range of backward type blade sections 32c is at 25-65 °；
The embodiment of the present invention is by designing symmetroid in 100 air inlet runner 120 of air intake casing of centrifugal blower 10
Leading leaf group 200 and symmetroid pair guide vane group 300, the symmetroid dominate 300 phase of leaf group 200 and symmetroid pair guide vane group
Mutually cooperation can preferably realize flow conductivity and cleanliness when sucking gas to air inlet runner 120, effectively to air inlet runner
The gas of 120 suckings is combed and is guided, and is made it uniformly and is smoothly flowed therein impeller 30, can also effectively reduce air inlet runner
Flow boundary layer separation and the generation of internal whirlpool group, significantly reduce air suction and noise, effectively increase centrifugal blower in 120
10 intake efficiency, meanwhile, applicant of the embodiment of the present invention is creatively changed 32 shape of blade of current impeller 30,
It is put forward for the first time using forward-type blade sections 32a as import, impeller 30 structure of the backward type blade sections 32c as outlet, the knot
Structure realizes the connection of double bent blades sections to forward-type and backward type using the radial vane section 32b for being located at middle part simultaneously,
The structure had both remained the advantage that pneumatic efficiency that traditional backward type impeller has is high and noise is small, while its forward-type blade sections
So that the aerodynamic loading of the embodiment of the present invention is improved significantly；
Therefore, ensuring and existing impeller using air intake casing 100 provided in an embodiment of the present invention and 30 structure of impeller
Under the premise of 31 dimensional standard of disk is constant, special structure design is carried out by the blade 32 to air intake casing 100 and impeller 30,
So that centrifugal blower of the embodiment of the present invention 10 has high intake efficiency, high pneumatic efficiency, high aerodynamic loading and pneumatic simultaneously
The small Multiple techniques effect of noise, has finally obtained the centrifugal blower 10 with efficient aerodynamic efficiency；
It is further preferred that please with further reference to shown in Figure 10 and Figure 11, the forward-type leaf of the blade 32 of present embodiment
Fragment length 32a and backward type blade sections 32c equal length and radial vane section 32b length account for the 8- of 32 length of blade
12%；Particularly preferably, in the present embodiment, radial vane segment length 32b accounts for the 10% of 32 length of blade, the present embodiment
The concrete structure design of 1 blade 32 make forward-type blade sections 32a and backward type blade sections 32c be it is symmetrical, can obtain
Substantially approximate high pneumatic efficiency and high aerodynamic loading technical effect, performance more balanced compromise, be very suitable to for
Pneumatic efficiency and aerodynamic loading all have the centrifugal blower application scenarios of high requirement；
Please with further reference to shown in Figure 16, Figure 17 and Figure 18, live spindle 50 uses oil-leakage-prevention live spindle, live spindle
50 both ends are respectively equipped with spiral shell to opposite air inlet side thread groove 51 and exhaust side thread groove 52, and air inlet side thread groove 51, which is located at, to be leaned on
One end of nearly 100 side of air intake casing, exhaust side thread groove 52 are located at close to one end of 40 side of exhaust casing, and air inlet side thread groove
51 and exhaust side thread groove 52 in symmetry shape be distributed；Preferably, in the present embodiment, on the outside of air inlet side thread groove 51 be equipped with into
Gas side bearing installation step 53 is equipped with exhaust side bearing installation step 54 on the outside of exhaust side thread groove 52；Air inlet side bearing 51 is pacified
Dress is located on air inlet side bearing installation step 53, and exhaust side bearing 52 is positioned on exhaust side bearing installation step 54；
The embodiment of the present invention is by being arranged spiral shell to opposite air inlet side thread groove at the live spindle both ends of centrifugal blower
It is located at both ends and spiral shell to phase when lubricating oil enters in the thread groove for being located at live spindle both ends with exhaust side thread groove
Lubricating oil in anti-thread groove can return again with the rotation of live spindle respectively along the spin line direction of screw thread respectively simultaneously
To in the grease-box at both ends；Therefore the structure of the embodiment of the present invention is not only simple easy to implement, but also can effectively keep away
Exempt from the Leakage of centrifugal blower.
Please be further shown in Figure 19, in the present embodiment, 50 both ends of live spindle of centrifugal blower 10 pass through
Bearing 91 is mounted on bearing block 92, and centrifugal blower 10 is additionally provided with axial thrust control device 60, the final stage of multi-stage impeller 30
Impeller 30a is connected to exhaust casing 40, axial thrust control device, and 60 include balancing frame 61, and balancing frame 61 is set in rotation master
In live spindle 50 between shaft end annular gas seals 70 and impeller 30a, and 61 periphery of balancing frame and exhaust casing 40 it
Between install balancing frame sealing ring 62；
Preferably, in the present embodiment, the exit casing between balancing frame 61 and live spindle end annular gas seals 70
Body 40 is equipped with pumping adapter tube 63, the air inlet 120 of pumping 63 other end of adapter tube access air intake casing 100.
It should be noted that the present embodiment Fig. 1 is mainly used for illustrating the mounting structure of multistage centrifugal blower 10, not specifically
The specific structure of axial thrust control device 60 is shown, the specific structure of axial thrust control device 60 is please individually combined referring to figure
Content shown in 19；
In 10 course of work of the present embodiment multistage centrifugal blower, the shape between impeller 30a and exhaust casing 40
At cavity 81 in there are gases, gas pressure is identical as the outlet gas pressure of exhaust casing 40, therefore 81 gas of cavity
Know from experience the axial thrust to the generation of live spindle 50 towards impeller 30, the present invention is using balancing frame 61 and balancing frame sealing ring 62
On the one hand structure setting plays the role of preventing shaft end gas from leaking, while putting down what balancing frame 61 and exhaust casing 40 were formed
Weigh cavity 82, this 82 pressure of balance is identical as external atmospheric pressure by live spindle end annular gas seals 70, therefore flat
Weighing apparatus 61 both sides of the face of disk form certain pressure difference, so that the axial thrust towards 91 side of right end bearing is generated to balancing frame 61, into
And the axial thrust being subject to by as above controlling active balance live spindle 50 of the present invention；It is located at balancing frame 61 and rotation simultaneously
Exhaust casing 40 between main shaft end annular gas seals 70 is equipped with pumping adapter tube 63, be evacuated 63 other end of adapter tube be directly accessed into
The air inlet 120 of gas shell 100, therefore make to generate certain negative pressure in this balance 82, further such that making balancing frame 61
The pressure difference of both sides of the face increases, i.e., balancing frame 61 is by the axial thrust increase towards right end bearing 91, therefore acts on rotation
Bidirectional axial force on main shaft 50 is offset balance control by effective, centrifugal blower 10 of the present invention bearing 91 in use
The axial force born further is significantly reduced；
When the present embodiment is in use, with the raising of 10 outlet pressure of centrifugal blower, live spindle 50 is towards impeller 30
Axial thrust can also be gradually increased, balancing frame 61 and balancing frame sealing ring 62, and the setting of pumping adapter tube 63 also can be with
The pressure difference of 61 both sides of the face of balancing frame increases and offsets the axial force with coupling certainly, and therefore, the present embodiment is pushed away without using dedicated
Power bearing, reduces the manufacturing cost of the present embodiment, while also reducing the maintenance cost of the present embodiment.
Embodiment 2:
Remaining technical solution of the present embodiment 2 is identical as upper embodiment 1, and difference is only that blade wheel structure, specifically,
In the present embodiment 2, a kind of impeller 30 ' shown in 2 and Figure 13, impeller 30 ' use aluminium alloy integrally casting shaping referring to Figure 1
The impeller disk 31 ' and several blades 32 ' on the impeller disk, each blade 32 ' be evenly arranged on the inner circumferential of the impeller disk 31 ', impeller
Disk 31 ', which is equipped with, is fixedly mounted the rotary shaft hole 33 ' of connection, the axial admission mouth being connected to air inlet runner with live spindle 50
34 ' and the radial exhaust outlet 35 ' that is connected to flow channel out；Wherein, each blade 32 ' includes being located at close to axial admission mouth
The forward-type blade sections 32a ' of 34 ' one end and backward type blade sections 32c ' for being located at 35 ' one end of close radial exhaust outlet, forward direction
Formula blade sections 32a ' is connect with backward type blade sections 32c ' using radial vane section 32b '；
Preferably, in the present embodiment, 32 ' quantity of blade is 8-16；Particularly preferably, in the present embodiment,
The quantity of blade 32 ' is 8；The air inlet angle range of forward-type blade sections 32a ' is at 35-75 °；Backward type blade sections 32c's '
Outlet angular range is at 25-65 °；
It is further preferred that the blade 32 ' of present embodiment is using high pneumatic please with further reference to shown in Figure 14 and Figure 15
Load blade, the specific scheme is that forward-type blade sections 32a ' length is greater than 2 times and radial of backward type blade sections 32c ' length
Blade sections 32b ' length accounts for the 8-12% of 32 ' length of blade；Particularly preferably, in the present embodiment, forward-type blade sections
32a ' length accounts for the 65% of 32 ' length of blade, and radial vane section 32b ' length accounts for the 10% of 32 ' length of blade, backward type leaf
Segment 32c ' length accounts for the 25% of 32 ' length of blade, and the concrete structure design of 2 blade 32 ' of the present embodiment makes forward-type leaf
Segment 32a ' is significantly greater than backward type blade sections 32c ', and the structure of backward type blade sections 32c ' equally can effectively improve centrifugation
The pneumatic efficiency of air blower, while the ratio by increasing forward-type blade sections 32a ' can further significantly improve its gas
Dynamic loading performance is very suitable to the centrifugal blower application scenarios for having requirements at the higher level for aerodynamic loading, while relative to existing
Having the forward-type blade centrifugal blower of technology has higher pneumatic efficiency and lower noise.
It is obvious to a person skilled in the art that invention is not limited to the details of the above exemplary embodiments, Er Qie
In the case where without departing substantially from spirit or essential attributes of the invention, the present invention can be realized in other specific forms.Therefore, no matter
From the point of view of which point, the present embodiments are to be considered as illustrative and not restrictive, and the scope of the present invention is by appended power
Benefit requires rather than above description limits, it is intended that all by what is fallen within the meaning and scope of the equivalent elements of the claims
Variation is included within the present invention.Any reference signs in the claims should not be construed as limiting the involved claims.
In addition, it should be understood that although this specification is described in terms of embodiments, but not each embodiment is only wrapped
Containing an independent technical solution, this description of the specification is merely for the sake of clarity, and those skilled in the art should
It considers the specification as a whole, the technical solutions in the various embodiments may also be suitably combined, forms those skilled in the art
The other embodiments being understood that.
Claims (10)
1. a kind of centrifugal blower with efficient aerodynamic efficiency, including be sequentially connected with rotary drive unit live spindle,
The air intake casing being connected as one with live spindle installation, the multi-stage impeller and exit casing that are mounted in central enclosure
Body, which is characterized in that the air intake casing is equipped with the air inlet and air inlet runner that are located above, the air inlet by it is described into
Flow channel is connected with the impeller；It is respectively equipped with symmetroid in the air inlet runner and dominates leaf group and symmetroid pair guide vane
Group, and the symmetroid dominates leaf group relative to the symmetroid pair guide vane group close to the air inlet；The symmetrical song
Leaf group is dominated in face and the two sides guide vane side of symmetroid pair guide vane group is corresponding with inner wall shape before and after the air intake casing respectively
And extend；
The impeller includes the impeller disk and several blades on the impeller disk, and each blade is evenly arranged on the impeller
The inner circumferential of disk, the impeller disk are equipped with and the rotary shaft hole of connection are fixedly mounted with the live spindle, are connected to air inlet runner
Axial admission mouth and the radial exhaust outlet that is connected to flow channel out；Each blade include be located at close to the axial direction into
Forward-type blade sections of port one end and positioned at the backward type blade sections close to described radial exhaust outlet one end, the forward-type
Blade sections are connect with the backward type blade sections using radial vane section.
2. as described in claim 1 with the centrifugal blower of efficient aerodynamic efficiency, which is characterized in that the symmetroid master
The root of guide vane group and the root of the symmetroid pair guide vane group are distributed in the same circumference concentric with the bearing block axis hole
On face, the diameter of the periphery is less than the bore of the air inlet；And the root spacing of the leading leaf group of the symmetroid is small
In the root spacing of the symmetroid pair guide vane group；The symmetroid is dominated leaf group length and is led greater than the symmetroid pair
Leaf group length.
3. as claimed in claim 2 with the centrifugal blower of efficient aerodynamic efficiency, which is characterized in that the air inlet runner is in
Arc surfaced, internal diameter become larger along the air inlet to down toward the major axes orientation, while it is in pair that the air intake casing bottom, which includes,
Claim the left arc surface shell wall and right arc surface shell wall of distribution and intersection, wherein the left arc surface shell wall and right arc surface shell wall
Between cross-shaped portion and the symmetroid dominate the root of leaf group and the root of the symmetroid pair guide vane group and be distributed
On the same periphery.
4. as described in claim 1 with the centrifugal blower of efficient aerodynamic efficiency, which is characterized in that the symmetroid master
Guide vane group includes dominating leaf and right curved surface in the left curved surface of symmetrical shape distribution to dominate leaf, the left curved surface dominate the curvature of leaf from
Its root becomes smaller to end direction；The symmetroid pair guide vane group includes the left curved surface pair guide vane and the right side in symmetrical shape distribution
The curvature of curved surface pair guide vane, the left curved surface pair guide vane becomes larger from its root to end direction.
5. as claimed in claim 4 with the centrifugal blower of efficient aerodynamic efficiency, which is characterized in that the left curved surface is leading
The curvature that leaf is located at root is greater than the curvature that the left curved surface pair guide vane is located at root, and the left curved surface dominates leaf and is located at end
Curvature be less than the left curved surface pair guide vane and be located at the curvature of end.
6. as claimed in claim 4 with the centrifugal blower of efficient aerodynamic efficiency, which is characterized in that the left curved surface is leading
Leaf and right curved surface are dominated the root spacing between leaf and are less than between the root between the left curved surface pair guide vane and right curved surface pair guide vane
Away from；The left curved surface dominates leaf simultaneously and right curved surface dominates the bore that the end spacing between leaf is less than the air inlet, described
End spacing between left curved surface pair guide vane and right curved surface pair guide vane is greater than the bore of the air inlet.
7. as described in claim 1 with the centrifugal blower of efficient aerodynamic efficiency, which is characterized in that the quantity of the blade
It is 8-16；The air inlet angle range of the forward-type blade sections is at 35-75 °；The outlet angle model of the backward type blade sections
It is trapped among 25-65 °.
8. as described in claim 1 with the centrifugal blower of efficient aerodynamic efficiency, which is characterized in that the live spindle two
End is respectively equipped with spiral shell to opposite air inlet side thread groove and exhaust side thread groove, and the air inlet side thread groove is located at close to gas inlet shell
The one end on side, the exhaust side thread groove are located at close to the one end on exit casing side, and the air inlet side thread groove and exhaust
Side thread groove is distributed in symmetry shape.
9. as described in claim 1 with the centrifugal blower of efficient aerodynamic efficiency, which is characterized in that the centrifugal blower
It is additionally provided with axial thrust control device, the axial thrust control device includes balancing frame, and the balancing frame is set in the rotation
Turn in the live spindle between main shaft end annular gas seals and impeller, and the balancing frame periphery and the exhaust casing it
Between install balancing frame sealing ring.
10. as claimed in claim 9 with the centrifugal blower of efficient aerodynamic efficiency, which is characterized in that be located at the balance
Exhaust casing between disk and live spindle end annular gas seals is equipped with pumping adapter tube, the pumping adapter tube other end access
The air inlet of the air intake casing.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910402334.4A CN110080999B (en) | 2019-05-15 | 2019-05-15 | Centrifugal blower |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910402334.4A CN110080999B (en) | 2019-05-15 | 2019-05-15 | Centrifugal blower |
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| CN110080999B CN110080999B (en) | 2020-08-07 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114776607A (en) * | 2022-05-17 | 2022-07-22 | 山东省章丘鼓风机股份有限公司 | Weight reducing structure and method for centrifugal fan |
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| JP2017133404A (en) * | 2016-01-27 | 2017-08-03 | 株式会社川本製作所 | Pump casing and pump device |
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| US4775292A (en) * | 1986-07-08 | 1988-10-04 | Grundfos International A/S | Pump comprising a gas separator |
| EP1593854A2 (en) * | 2004-05-06 | 2005-11-09 | Hitachi Industries Co., Ltd. | Inlet casing and suction passage structure |
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| CN114776607A (en) * | 2022-05-17 | 2022-07-22 | 山东省章丘鼓风机股份有限公司 | Weight reducing structure and method for centrifugal fan |
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|---|---|
| CN110080999B (en) | 2020-08-07 |
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