CN110080999B - Centrifugal blower - Google Patents
Centrifugal blower Download PDFInfo
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- CN110080999B CN110080999B CN201910402334.4A CN201910402334A CN110080999B CN 110080999 B CN110080999 B CN 110080999B CN 201910402334 A CN201910402334 A CN 201910402334A CN 110080999 B CN110080999 B CN 110080999B
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- air inlet
- guide vane
- curved
- centrifugal blower
- symmetrical
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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
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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
- F04D29/26—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
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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
- F04D29/26—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
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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
- F04D29/40—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
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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
- F04D29/40—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
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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
- F04D29/66—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
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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
- F04D29/66—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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a centrifugal blower.A main guide vane group with a symmetrical curved surface and a secondary guide vane group with a symmetrical curved surface are respectively arranged in an air inlet flow channel of an air inlet shell of the centrifugal blower, and the main guide vane group with the symmetrical curved surface is close to an air inlet relative to the secondary guide vane group with the symmetrical curved surface; guide vane edges at two sides of the symmetrical curved surface main guide vane group and the symmetrical curved surface auxiliary guide vane group respectively correspond to and extend from the front and rear inner shell walls of the air inlet shell; each blade of the impeller comprises a forward blade section and a backward blade section, wherein the forward blade section is positioned at one end close to the axial gas inlet, the backward blade section is positioned at one end close to the radial gas outlet, and the forward blade section and the backward blade section are connected by adopting a radial blade section; according to the invention, through the special structural design of the air inlet shell and the impeller blades, the centrifugal blower has multiple technical effects of high air inlet efficiency, high pneumatic load and low pneumatic noise, and finally the centrifugal blower with high pneumatic efficiency is obtained.
Description
Technical Field
The invention belongs to the field of manufacturing of centrifugal blower products, and particularly relates to a centrifugal blower.
Background
The working principle of the centrifugal blower is mainly that a plurality of rotating impellers are utilized to do work on gas, the kinetic energy of the gas is increased, and then the pressure of the gas is improved through the centrifugal action and the diffusion process, so that certain air volume and air pressure are achieved, and the technical effect of large-flow high-pressure air supply is achieved. The centrifugal blower has better high-flow high-pressure air supply effect, so the centrifugal blower is widely applied to the fields of sewage treatment, power plant desulfurization and other industries.
The centrifugal blower mainly comprises an air inlet shell with an air inlet, a rotary driving unit, a gas compression unit formed by adopting a rotary impeller, an exhaust shell with an exhaust port and other core components, wherein the structure and the shape of the air inlet shell, the impeller and the exhaust shell can directly influence the pneumatic efficiency of the centrifugal blower.
Specifically, in the centrifugal blower in the prior art, a plurality of rib plates are usually arranged in the air inlet flow passage of the air inlet housing, and the designed rib plates function as reinforcing ribs for structural reinforcement, so that the structural design of straight-plane flat plate rib plates with certain thickness is adopted, and the influence of the rib plates on gas distribution during air inlet is not specifically analyzed and researched.
Secondly, in the centrifugal blower of the prior art, the shape and number of the blades on the impeller and the shape of the blade disc are the key factors for determining the aerodynamic efficiency of the centrifugal blower. In order to meet the performance requirements of various fields, people usually design impeller blades into a backward type, a forward type and a radial type, wherein the bending direction of the backward type blades is the same as the motion trail of gas, the pneumatic efficiency is high, the noise is low, and the pneumatic load is low; the bending direction of the forward type blades is opposite to the motion track of gas, the pneumatic load is high, but the direction of the gas is forcibly changed by the blades, so that the pneumatic efficiency is low and the noise is high; the bending direction of the radial type blades is vertical to the motion trail of the gas, and the related performance of the radial type blades is between that of the backward type blades and that of the forward type blades; from the above, it can be seen that the existing impeller blades have advantages and disadvantages, and cannot have the performances of high aerodynamic efficiency and high aerodynamic load at the same time.
Based on years of development experience in the field of fan products and theoretical knowledge of fluid flow mechanisms, the inventor hopes to realize higher aerodynamic efficiency of the centrifugal blower by innovating a related structure design.
Disclosure of Invention
In view of the above, the present invention provides a centrifugal blower, which has multiple technical effects of high air intake efficiency, high aerodynamic load and low aerodynamic noise by specially designing the air intake casing and the impeller blades, and finally obtains a centrifugal blower with high aerodynamic efficiency.
After the technical problems of the existing centrifugal blower in the background art are found, through years of development experience, CFD calculation is carried out on three-dimensional gas dynamics of a flow channel of an air inlet shell and an impeller, deep analysis is simultaneously carried out on the CFD calculation, the structural shapes of the air inlet flow channel and the impeller are optimized, separation of a flow boundary layer of the air inlet flow channel and generation and migration of internal vortex masses are reduced, pneumatic efficiency of the centrifugal blower is improved, and meanwhile, optimal pneumatic load distribution control is achieved, and based on the CFD calculation, the applicant finally provides the following technical scheme:
a centrifugal blower comprises a rotary main shaft in transmission connection with a rotary driving unit, an air inlet shell, a multi-stage impeller and an air outlet shell, wherein the air inlet shell is integrally mounted and connected with the rotary main shaft, the air inlet shell is mounted in a middle shell and provided with an air inlet and an air inlet flow passage, the air inlet is communicated with the impeller through the air inlet flow passage; a symmetrical curved surface main guide blade group and a symmetrical curved surface auxiliary guide blade group are respectively arranged in the air inlet flow channel, and the symmetrical curved surface main guide blade group is close to the air inlet relative to the symmetrical curved surface auxiliary guide blade group; guide vane edges at two sides of the symmetrical curved surface main guide vane group and the symmetrical curved surface auxiliary guide vane group respectively correspond to the shapes of the front and rear inner shell walls of the air inlet shell and extend;
the impeller comprises an impeller disc and a plurality of blades positioned on the impeller disc, each blade is uniformly distributed on the inner periphery of the impeller disc, and the impeller disc is provided with a rotating shaft hole fixedly installed and connected with the rotating main shaft, an axial air inlet communicated with the air inlet flow passage and a radial air outlet communicated with the air outlet flow passage; every the blade is including being located and being close to the preceding formula blade section of axial air inlet one end and being located and being close to the backward formula blade section of radial gas vent one end, preceding formula blade section with the backward formula blade section adopts radial formula blade section to connect.
Preferably, the root of the symmetrical curved surface main guide blade group and the root of the symmetrical curved surface auxiliary guide blade group are distributed on the same circumferential surface concentric with the shaft hole of the bearing seat, and the diameter of the circumferential surface is smaller than the caliber of the air inlet; the root spacing of the symmetrical surface main guide blade group is smaller than the root spacing of the symmetrical surface auxiliary guide blade group; the length of the symmetrical surface main guide blade group is greater than that of the symmetrical surface auxiliary guide blade group.
Preferably, the intake runner is arc-shaped, the inner diameter of the intake runner increases in a direction from the intake port to the main shaft, and the bottom of the intake housing includes a left arc-shaped housing wall and a right arc-shaped housing wall that are symmetrically distributed and intersect with each other, wherein an intersection between the left arc-shaped housing wall and the right arc-shaped housing wall, a root of the symmetrical curved primary guide vane group, and a root of the symmetrical curved secondary guide vane group are both distributed on the same circumferential surface.
Preferably, the main guide vane group with the symmetrical curved surface comprises a left main guide vane with the curved surface and a right main guide vane with the curved surface, which are symmetrically distributed in shape, and the curvature of the left main guide vane with the curved surface is reduced from the root part to the end part; the auxiliary guide vane group with the symmetrical curved surfaces comprises auxiliary guide vanes with the left curved surfaces and auxiliary guide vanes with the right curved surfaces, which are symmetrically distributed, and the curvature of the auxiliary guide vanes with the left curved surfaces is enlarged from the root parts to the end parts.
Preferably, the curvature that left side curved surface main guide vane is located the root is greater than the curvature that the vice guide vane of left side curved surface is located the root, just the curvature that left side curved surface main guide vane is located the tip is less than the curvature that the vice guide vane of left side curved surface is located the tip.
Preferably, the root space between the left curved surface main guide vane and the right curved surface main guide vane is smaller than the root space between the left curved surface auxiliary guide vane and the right curved surface auxiliary guide vane; simultaneously tip interval between left side curved surface main guide vane and the right curved surface main guide vane is less than the bore of air inlet, the tip interval between the vice guide vane of left side curved surface and the vice guide vane of right curved surface is greater than the bore of air inlet.
Preferably, the number of the blades is 8-16; the forward blade section has an air inlet angle in the range of 35-75 °; the air outlet angle of the backward blade section ranges from 25 to 65 degrees.
It should be noted that the air inlet angle and the air outlet angle in the present invention refer to the radial deviation angles of the corresponding blade segment and the impeller.
Preferably, an air inlet side thread groove and an air outlet side thread groove with opposite screw directions are respectively arranged at two ends of the rotating main shaft, the air inlet side thread groove is positioned at one end close to the air inlet shell, the air outlet side thread groove is positioned at one end close to the air outlet shell, and the air inlet side thread groove and the air outlet side thread groove are symmetrically distributed.
Preferably, the centrifugal blower is further provided with an axial thrust control device, the axial thrust control device comprises a balance disc, the balance disc is sleeved on the rotating main shaft between the rotating main shaft tail end air seal piece and the final-stage impeller, and a balance disc sealing ring is installed between the periphery of the balance disc and the exhaust housing.
Preferably, an air exhaust connecting pipe is arranged on the exhaust shell between the balance disc and the air seal piece at the tail end of the rotating main shaft, and the other end of the air exhaust connecting pipe is connected to an air inlet of the air inlet shell.
The invention designs a symmetrical curved surface main guide vane group and a symmetrical curved surface auxiliary guide vane group in an air inlet channel of an air inlet shell, the symmetrical curved surface main guide vane group and the symmetrical curved surface auxiliary guide vane group are mutually matched, so that the flow conductivity and the flow linearity of air sucked by the air inlet channel can be better realized, the air sucked by the air inlet channel can be effectively combed and guided to uniformly and smoothly flow into an impeller in an air compression unit, the separation of a flowing boundary layer and the generation of internal vortex groups in the air inlet channel can be effectively reduced, the air suction noise is obviously reduced, the air inlet efficiency of the centrifugal blower is effectively improved, meanwhile, the applicant of the invention creatively changes the shape of the prior impeller blades, firstly proposes an impeller structure which adopts a forward-direction blade section as an inlet and a backward-direction blade section as an outlet, and simultaneously adopts a radial-direction blade section positioned in the middle part to realize the connection of forward-direction and backward-direction double bent blade sections, the structure not only keeps the advantages of high pneumatic efficiency and low noise of the traditional backward impeller, but also obviously improves the pneumatic load of the invention by the forward blade section;
therefore, on the premise of ensuring that the size standard of the air inlet shell and the impeller structure provided by the invention is not changed with the existing impeller disc, the centrifugal blower has multiple technical effects of high air inlet efficiency, high pneumatic load and low pneumatic noise by specially designing the air inlet shell and the impeller blades, and finally the centrifugal blower with high-efficiency pneumatic efficiency is obtained.
Drawings
FIG. 1 is a schematic diagram of a centrifugal blower 10 according to an embodiment of the present invention;
FIG. 2 is a front cross-sectional view of an air induction housing 100 having increased air induction efficiency in accordance with an embodiment of the present invention;
FIG. 3 is a side cross-sectional view of the intake housing 100 with increased intake efficiency in accordance with an embodiment of the present invention;
fig. 4 is a schematic front structure diagram of a main blade group 200 with a symmetric curved surface according to an embodiment of the present invention;
fig. 5 is a schematic side view of a symmetrical surface leading vane group 200 according to an embodiment of the present invention;
fig. 6 is a schematic front structural view of a symmetrical surface secondary guide vane set 300 according to an embodiment of the present invention;
FIG. 7 is a schematic side view of a symmetrical surface sub-vane set 300 according to an embodiment of the present invention;
fig. 8 is a front sectional view of an impeller 30 in embodiment 1 of the present invention;
fig. 9 is a side sectional view of an impeller 30 in embodiment 1 of the present invention;
fig. 10 is a schematic front view of a blade 32 according to embodiment 1 of the present invention;
FIG. 11 is a side view schematically showing the structure of a blade 32 in embodiment 1 of the present invention;
fig. 12 is a front sectional view of an impeller 30' in embodiment 2 of the present invention;
FIG. 13 is a side sectional view of an impeller 30' in embodiment 2 of the present invention;
FIG. 14 is a schematic front view of a vane 32' according to embodiment 2 of the present invention;
FIG. 15 is a side view schematically showing the structure of a blade 32' in embodiment 2 of the present invention;
FIG. 16 is a schematic view of a rotary spindle 50 according to an embodiment of the present invention;
FIG. 17 is an enlarged view of the structure at A in FIG. 16;
FIG. 18 is an enlarged view of the structure at B in FIG. 16;
fig. 19 is a partial sectional view schematically showing the mounting structure of the axial thrust control device 60 according to the embodiment of the present invention.
Detailed Description
The embodiment of the invention discloses a centrifugal blower, which comprises a rotating main shaft in transmission connection with a rotating driving unit, an air inlet shell, a multi-stage impeller and an exhaust shell, wherein the air inlet shell is integrally installed and connected with the rotating main shaft, the multi-stage impeller is installed in a middle shell, the air inlet shell is provided with an air inlet and an air inlet flow channel which are positioned above the air inlet shell, and the air inlet is communicated with the impeller through the air inlet flow channel; a symmetrical curved surface main guide blade group and a symmetrical curved surface auxiliary guide blade group are respectively arranged in the air inlet flow channel, and the symmetrical curved surface main guide blade group is close to the air inlet relative to the symmetrical curved surface auxiliary guide blade group; guide vane edges at two sides of the symmetrical curved surface main guide vane group and the symmetrical curved surface auxiliary guide vane group respectively correspond to and extend from the front and rear inner shell walls of the air inlet shell; the impeller comprises an impeller disc and a plurality of blades positioned on the impeller disc, each blade is uniformly distributed on the inner periphery of the impeller disc, and the impeller disc is provided with a rotating shaft hole fixedly installed and connected with the rotating main shaft, an axial air inlet communicated with the air inlet channel and a radial air outlet communicated with the air outlet channel; each blade comprises a forward blade section and a backward blade section, wherein the forward blade section is located close to one end of the axial air inlet, the backward blade section is located close to one end of the radial air outlet, and the forward blade section and the backward blade section are connected through the radial blade section.
In order to make those skilled in the art better understand the technical solution of the present invention, the technical solution in the embodiment of the present invention will be clearly and completely described below with reference to the drawings in the embodiment of the present invention, and it is obvious that the described embodiment is only a part of the embodiment of the present invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Example 1:
referring to fig. 1, a centrifugal blower 10 includes a rotary shaft 50 drivingly connected to a rotary drive unit (not shown), an air inlet housing 100 integrally mounted to the rotary shaft, a multi-stage impeller 30 (not shown in fig. 1) mounted in a middle housing 20, and an air outlet housing 40;
referring further to the air inlet housing 100 shown in fig. 2 and 3, the air inlet housing 100 is connected to a main shaft (not shown) of a centrifugal blower through a bearing seat 110 mounted with a bearing (not shown), the air inlet housing 100 is provided with an air inlet 120 and an air inlet flow passage 130 located above, the air inlet 120 is communicated with a gas compression unit of the centrifugal blower through the air inlet flow passage 130; a symmetrical curved surface main guide vane group 200 and a symmetrical curved surface auxiliary guide vane group 300 are respectively arranged in the air inlet flow channel 130, and the symmetrical curved surface main guide vane group 200 is close to the air inlet 120 relative to the symmetrical curved surface auxiliary guide vane group 300; guide vane edges at two sides of the symmetrical curved surface main guide vane group 200 and the symmetrical curved surface auxiliary guide vane group 300 respectively correspond to and extend from the front and rear inner casing walls 140 of the air inlet casing 100 in shape;
preferably, in the present embodiment, the symmetrical surface main guide vane group 200 and the symmetrical surface auxiliary guide vane group 300 are integrally cast with the air intake housing 100;
preferably, in the present embodiment, the root of the symmetrical surface main guide vane group 200 and the root of the symmetrical surface auxiliary guide vane group 300 are distributed on the same circumferential surface 150 concentric with the bearing seat shaft hole 111, and the diameter of the circumferential surface 150 is smaller than the diameter of the air inlet 120; and the root interval D of the symmetrical surface leading blade group 200210Is less than the root space D of the symmetrical curved surface auxiliary guide vane set 300310；
Preferably, as further shown in fig. 4 and 5, in the present embodiment, the main guide vane group 200 with symmetric curved surfaces includes a left main guide vane 210 and a right main guide vane 220 with symmetric shapes, and the curvature of the left main guide vane 210 with curved surfaces becomes smaller from the root to the end thereof; as further shown in fig. 6 and 7, the symmetrical curved auxiliary guide vane group 300 includes a left curved auxiliary guide vane 310 and a right curved auxiliary guide vane 320 which are symmetrically distributed in shape, and the curvature of the left curved auxiliary guide vane 210 increases from the root to the end;
further preferably, in the present embodiment, the inlet conduit 120 is arc-shaped, and the inner diameter thereof increases along the direction from the inlet 110 to the main axis, and the bottom of the inlet housing 100 is at the same timeThe parts comprise a left arc surface shell wall 160a and a right arc surface shell wall 160b which are symmetrically distributed and intersected, wherein the intersection part between the left arc surface shell wall 160a and the right arc surface shell wall 160b and the root part of the left curved surface main guide vane 210, the root part of the right curved surface main guide vane 220, the root part of the left curved surface auxiliary guide vane 310 and the root part of the right curved surface auxiliary guide vane 320 are all distributed on the same circumferential surface 150, and the diameter of the circumferential surface 150 is smaller than the caliber D of the air inlet 120120；
Further preferably, in the present embodiment, the guide vane edges 210a and 210b on both sides of the left curved main guide vane 210 respectively correspond to and extend from the front and rear inner casing walls 140 of the air intake casing 100; preferably, in the present embodiment, the end spacing D between the left cambered main guide vane 210 and the right cambered main guide vane 220220Caliber D smaller than air inlet 120120Preferably, in the present embodiment, the axial distance L from the end of the left cambered main vane 210 to the air inlet 12021Less than its axial distance L from circumferential surface 15022；
Further preferably, in the present embodiment, the guide vane edges 310a and 310b on both sides of the left curved auxiliary guide vane 310 respectively correspond to and extend from the front and rear inner casing walls 140 of the air intake casing 100; preferably, in the present embodiment, the end spacing D between the left curved sub vane 310 and the right curved sub vane 320320Caliber D larger than air inlet120；
Further preferably, in the present embodiment, the curvature of the left curved main guide vane 210 at the root is greater than the curvature of the left curved auxiliary guide vane 310 at the root, and the curvature of the left curved main guide vane 210 at the end is less than the curvature of the left curved auxiliary guide vane 310 at the end; preferably, in the present embodiment, the root spacing D between the left cambered main guide vane 210 and the right cambered main guide vane 310210Is smaller than the root distance D between the left curved auxiliary guide vane 310 and the right curved auxiliary guide vane 320310(ii) a Preferably, in the present embodiment, the length of the left curved main guide vane 210 is greater than the length of the left curved auxiliary guide vane 310, and further preferably, in the present embodiment, the length of the left curved main guide vane 210 is 1.5 to 3 times the length of the left curved auxiliary guide vane 310;
referring to fig. 8 and 9, an impeller 30 is shown, the impeller 30 is an impeller disc 31 integrally cast and formed by aluminum alloy and a plurality of blades 32 located on the impeller disc 31, each blade 32 is uniformly distributed on the inner periphery of the impeller disc 31, and the impeller disc 31 is provided with a rotating shaft hole 33 fixedly installed and connected with a rotating main shaft 50, an axial air inlet 34 communicated with an air inlet flow passage, and a radial air outlet 35 communicated with an air outlet flow passage; wherein each blade 32 comprises a forward blade section 32a located at one end close to the axial inlet 34 and a backward blade section 32c located at one end close to the radial outlet 35, and the forward blade section 32a and the backward blade section 32c are connected by a radial blade section 32 b;
preferably, the embodiment of the present invention performs three-dimensional aerodynamic CFD calculation through a large number of experiments, deeply analyzes the flow mechanism of the impeller 30, and further preferably sets the number of the blades 32 to 8-16, so that the centrifugal blower 10 can have more excellent performance of having dual technical effects of high aerodynamic efficiency and high aerodynamic load at the same time by performing the special design on the structure and number of the blades 32; particularly preferably, in the present embodiment, the number of the blades 32 is 8; the forward blade section 32a has an inlet angle in the range of 35-75 °; the air outlet angle of the backward blade section 32c ranges from 25 degrees to 65 degrees;
in the embodiment of the present invention, by designing the symmetrical curved surface main guide vane set 200 and the symmetrical curved surface sub guide vane set 300 in the inlet flow channel 120 of the inlet housing 100 of the centrifugal blower 10, and the mutual cooperation between the symmetrical curved surface main guide vane set 200 and the symmetrical curved surface sub guide vane set 300, the flow conductivity and the flow linearity when the inlet flow channel 120 sucks in the gas can be well realized, the gas sucked in the inlet flow channel 120 can be effectively combed and guided, so that the gas can uniformly and smoothly flow into the impeller 30, the separation of the flowing boundary layer and the generation of the internal vortex group in the inlet flow channel 120 can be effectively reduced, the suction noise is significantly reduced, the air intake efficiency of the centrifugal blower 10 is effectively improved, and meanwhile, the applicant of the embodiment of the present invention creatively changes the shape of the blades 32 of the existing impeller 30, firstly proposes an impeller 30 structure in which the forward-direction blade section 32a is used as an inlet and the backward-direction blade section, the structure simultaneously adopts the radial blade section 32b positioned in the middle to realize the connection of the forward and backward double-bent blade sections, the structure not only keeps the advantages of high pneumatic efficiency and low noise of the traditional backward impeller, but also obviously improves the pneumatic load of the embodiment of the invention through the forward blade section;
therefore, on the premise of ensuring that the size standard of the air inlet housing 100 and the impeller 30 provided by the embodiment of the invention is not changed from the size standard of the existing impeller disc 31, the centrifugal blower 10 provided by the embodiment of the invention has multiple technical effects of high air inlet efficiency, high pneumatic load and low pneumatic noise by specially designing the air inlet housing 100 and the blades 32 of the impeller 30, and finally the centrifugal blower 10 with high-efficiency pneumatic efficiency is obtained;
further preferably, referring to fig. 10 and 11, the forward blade section 32a and the backward blade section 32c of the blade 32 of the present embodiment have the same length, and the length of the radial blade section 32b is 8-12% of the length of the blade 32; particularly preferably, in this embodiment, the length 32b of the radial blade segment accounts for 10% of the length of the blade 32, and the specific structural design of the blade 32 in this embodiment 1 enables the forward blade segment 32a and the backward blade segment 32c to be symmetrically distributed, so that the technical effects of basically similar high aerodynamic efficiency and high aerodynamic load can be obtained, the performance is more balanced and compromised, and the centrifugal blower is very suitable for the application scenario of the centrifugal blower with higher requirements on aerodynamic efficiency and aerodynamic load;
as further shown in fig. 16, 17 and 18, the rotation spindle 50 adopts an oil leakage prevention rotation spindle, two ends of the rotation spindle 50 are respectively provided with an air inlet side thread groove 51 and an air outlet side thread groove 52 with opposite screw directions, the air inlet side thread groove 51 is located at one end close to the air inlet housing 100 side, the air outlet side thread groove 52 is located at one end close to the air outlet housing 40 side, and the air inlet side thread groove 51 and the air outlet side thread groove 52 are symmetrically distributed; preferably, in the present embodiment, an intake side bearing mounting step 53 is provided outside the intake side thread groove 51, and an exhaust side bearing mounting step 54 is provided outside the exhaust side thread groove 52; the air inlet side bearing 51 is arranged on the air inlet side bearing mounting step 53, and the air outlet side bearing 52 is arranged on the air outlet side bearing mounting step 54;
in the embodiment of the invention, the two ends of the rotating main shaft of the centrifugal blower are provided with the air inlet side thread groove and the air outlet side thread groove which are opposite in screw direction, when lubricating oil enters the thread grooves at the two ends of the rotating main shaft, the lubricating oil in the thread grooves which are opposite in screw direction and are positioned at the two ends can respectively return to the lubricating oil tanks at the two ends along the spiral line direction of the screw thread; therefore, the structure of the embodiment of the invention is simple and easy to implement, and the problem of oil leakage of the centrifugal blower can be effectively avoided.
As further shown in fig. 19, in the present embodiment, two ends of a rotating main shaft 50 of the centrifugal blower 10 are mounted on bearing seats 92 through bearings 91, the centrifugal blower 10 is further provided with an axial thrust control device 60, a final-stage impeller 30a of the multistage impeller 30 is communicated with the exhaust housing 40, the axial thrust control device 60 includes a balance disk 61, the balance disk 61 is sleeved on the rotating main shaft 50 between the rotating main shaft end air seal 70 and the final-stage impeller 30a, and a balance disk seal ring 62 is mounted between the outer periphery of the balance disk 61 and the exhaust housing 40;
preferably, in the present embodiment, the exhaust casing 40 located between the balance disc 61 and the rotary spindle end air seal 70 is provided with an air suction connection pipe 63, and the other end of the air suction connection pipe 63 is connected to the air inlet 120 of the air inlet casing 100.
It should be noted that fig. 1 of the present embodiment is mainly used for explaining the installation structure of the multistage centrifugal blower 10, the specific structure of the axial thrust control device 60 is not specifically shown, and the specific structure of the axial thrust control device 60 is please refer to the content shown in fig. 19 in combination alone;
during operation of the multi-stage centrifugal blower 10 of the present embodiment, gas is present within the cavity 81 formed between the final stage impeller 30a and the exhaust housing 40, the gas pressure is the same as the outlet gas pressure of the exhaust housing 40, so that the gas in the cavity 81 can generate axial thrust towards the impeller 30 to the rotating main shaft 50, the structure arrangement of the balance disc 61 and the balance disc sealing ring 62 in the invention plays a role in preventing the gas leakage at the shaft end on one hand, and an equilibrium cavity 82 is formed between the balance disk 61 and the exhaust housing 40, the pressure of the equilibrium cavity 82 is the same as the external atmospheric pressure through the rotary spindle end air seal 70, a certain pressure difference is thus formed at both side end surfaces of the balance disk 61, thereby generating an axial thrust toward the right end bearing 91 side against the balance disk 61, the axial thrust applied to the rotating spindle 50 of the invention is effectively balanced by the control; meanwhile, the exhaust casing 40 between the balance disk 61 and the rotary spindle end air seal 70 is provided with an air exhaust connection pipe 63, and the other end of the air exhaust connection pipe 63 is directly connected to the air inlet 120 of the air inlet casing 100, so that a certain negative pressure is generated in the balance cavity 82, and the pressure difference of the end surfaces at two sides of the balance disk 61 is further increased, namely the axial thrust of the balance disk 61 towards the right end bearing 91 is increased, so that the bidirectional axial force acting on the rotary spindle 50 is effectively offset and balanced and controlled, and the axial force borne by the bearing 91 in the use process of the centrifugal blower 10 is further obviously reduced;
in use, as the outlet pressure of the centrifugal blower 10 increases, the axial thrust of the rotating main shaft 50 towards the impeller 30 gradually increases, and the arrangement of the balance disk 61, the balance disk seal ring 62, and the air suction adapter 63 also self-couples and cancels the axial force as the pressure difference between the two side end surfaces of the balance disk 61 increases, so that the present embodiment does not need to use a dedicated thrust bearing, reduces the manufacturing cost of the present embodiment, and also reduces the maintenance cost of the present embodiment.
Example 2:
the rest technical solutions of this embodiment 2 are the same as those of the above embodiment 1, and the differences are only in the impeller structure, specifically, in this embodiment 2, please refer to an impeller 30 'shown in fig. 12 and 13, in which the impeller 30' is an impeller disk 31 'integrally cast and formed by aluminum alloy, and a plurality of blades 32' located on the impeller disk, each blade 32 'is uniformly distributed on the inner circumference of the impeller disk 31', and the impeller disk 31 'is provided with a rotating shaft hole 33' fixedly installed and connected with a rotating main shaft 50, an axial air inlet 34 'communicated with an air inlet channel, and a radial air outlet 35' communicated with an air outlet channel; wherein each vane 32 'comprises a forward vane segment 32 a' located near one end of the axial inlet 34 'and a backward vane segment 32 c' located near one end of the radial outlet 35 ', and the forward vane segment 32 a' and the backward vane segment 32c 'are connected by a radial vane segment 32 b';
preferably, in the present embodiment, the number of the blades 32' is 8 to 16; particularly preferably, in the present embodiment, the number of the blades 32' is 8; the forward blade section 32 a' has an inlet angle in the range of 35-75; the air outlet angle of the backward blade section 32 c' ranges from 25 degrees to 65 degrees;
further preferably, please refer to fig. 14 and 15, the blade 32' of the present embodiment is a high aerodynamic load blade, and the specific scheme is as follows: the length of the forward blade section 32a 'is 2 times greater than that of the backward blade section 32 c' and the length of the radial blade section 32b 'accounts for 8-12% of that of the blade 32'; specifically, preferably, in this embodiment, the length of the forward blade section 32a ' is 65% of the length of the blade 32 ', the length of the radial blade section 32b ' is 10% of the length of the blade 32 ', and the length of the backward blade section 32c ' is 25% of the length of the blade 32 ', and the specific structural design of the blade 32 ' in this embodiment 2 makes the forward blade section 32a ' significantly larger than the backward blade section 32c ', and the structure of the backward blade section 32c ' can also effectively improve the aerodynamic efficiency of the centrifugal blower, and at the same time, the aerodynamic load performance of the centrifugal blower can be further significantly improved by increasing the proportion of the forward blade section 32a ', so that the centrifugal blower is very suitable for the application scenario of the centrifugal blower with higher requirements on aerodynamic load, and has higher aerodynamic efficiency and lower noise compared with the centrifugal blower of the forward blade in the prior art.
It will be evident to those skilled in the art that the invention is not limited to the details of the foregoing illustrative embodiments, and that the present invention may be embodied in other specific forms without departing from the spirit or essential attributes thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.
Furthermore, it should be understood that although the present description refers to embodiments, not every embodiment may contain only a single embodiment, and such description is for clarity only, and those skilled in the art should integrate the description, and the embodiments may be combined as appropriate to form other embodiments understood by those skilled in the art.
Claims (10)
1. A centrifugal blower comprises a rotary main shaft in transmission connection with a rotary driving unit, an air inlet shell, a multi-stage impeller and an exhaust shell, wherein the air inlet shell is integrally mounted and connected with the rotary main shaft; a symmetrical curved surface main guide blade group and a symmetrical curved surface auxiliary guide blade group are respectively arranged in the air inlet flow channel, and the symmetrical curved surface main guide blade group is close to the air inlet relative to the symmetrical curved surface auxiliary guide blade group; guide vane edges at two sides of the symmetrical curved surface main guide vane group and the symmetrical curved surface auxiliary guide vane group respectively correspond to the shapes of the front and rear inner shell walls of the air inlet shell and extend;
the impeller comprises an impeller disc and a plurality of blades positioned on the impeller disc, each blade is uniformly distributed on the inner periphery of the impeller disc, and the impeller disc is provided with a rotating shaft hole fixedly installed and connected with the rotating main shaft, an axial air inlet communicated with the air inlet flow passage and a radial air outlet communicated with the air outlet flow passage; every the blade is including being located and being close to the preceding formula blade section of axial air inlet one end and being located and being close to the backward formula blade section of radial gas vent one end, preceding formula blade section with the backward formula blade section adopts radial formula blade section to connect.
2. The centrifugal blower according to claim 1, wherein the roots of the pair of symmetrical surface guide vanes and the roots of the pair of symmetrical surface guide vanes are distributed on a same circumferential surface concentric with the shaft hole of the bearing seat, and the diameter of the circumferential surface is smaller than the caliber of the air inlet; the root spacing of the symmetrical surface main guide blade group is smaller than the root spacing of the symmetrical surface auxiliary guide blade group; the length of the symmetrical surface main guide blade group is greater than that of the symmetrical surface auxiliary guide blade group.
3. The centrifugal blower according to claim 2, wherein the inlet flow channel has a curved shape, an inner diameter of the inlet flow channel increases in a direction from the inlet port to the main axis, and the bottom of the inlet housing includes a left curved wall and a right curved wall that are symmetrically disposed and intersect each other, wherein an intersection between the left curved wall and the right curved wall, a root of the symmetrically curved primary set of vanes and a root of the symmetrically curved secondary set of vanes are disposed on the same circumferential surface.
4. The centrifugal blower of claim 1, wherein the set of symmetrically curved main guide vanes comprises left and right symmetrically shaped left and right curved main guide vanes, the left curved main guide vane having a curvature that decreases in a direction from the root to the tip thereof; the auxiliary guide vane group with the symmetrical curved surfaces comprises auxiliary guide vanes with the left curved surfaces and auxiliary guide vanes with the right curved surfaces, which are symmetrically distributed, and the curvature of the auxiliary guide vanes with the left curved surfaces is enlarged from the root parts to the end parts.
5. The centrifugal blower of claim 4, wherein the curvature of the left curved main guide vane at the root is greater than the curvature of the left curved auxiliary guide vane at the root, and the curvature of the left curved main guide vane at the end is less than the curvature of the left curved auxiliary guide vane at the end.
6. The centrifugal blower of claim 4, wherein a root spacing between the left curved main guide vane and the right curved main guide vane is less than a root spacing between the left curved secondary guide vane and the right curved secondary guide vane; simultaneously tip interval between left side curved surface main guide vane and the right curved surface main guide vane is less than the bore of air inlet, the tip interval between the vice guide vane of left side curved surface and the vice guide vane of right curved surface is greater than the bore of air inlet.
7. The centrifugal blower of claim 1, wherein the number of said blades is 8-16; the forward blade section has an air inlet angle in the range of 35-75 °; the air outlet angle of the backward blade section ranges from 25 to 65 degrees.
8. The centrifugal blower according to claim 1, wherein the rotation shaft is provided at opposite ends thereof with an intake side thread groove and an exhaust side thread groove, respectively, the intake side thread groove being located at an end close to the intake casing side, the exhaust side thread groove being located at an end close to the exhaust casing side, and the intake side thread groove and the exhaust side thread groove being symmetrically arranged.
9. The centrifugal blower of claim 1, further provided with an axial thrust control device comprising a balance disk that is sleeved on the rotating shaft between the rotating shaft tip air seal and the final stage impeller, and a balance disk seal is mounted between the periphery of the balance disk and the exhaust housing.
10. The centrifugal blower of claim 9 wherein an air extraction nozzle is provided in the air discharge housing between said balance disk and said rotary spindle end air seal, the other end of said air extraction nozzle being connected to the air inlet of said air inlet housing.
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| JP4573020B2 (en) * | 2004-05-06 | 2010-11-04 | 株式会社日立プラントテクノロジー | Suction casing, suction flow path structure and fluid machine |
| CN201827150U (en) * | 2010-10-15 | 2011-05-11 | 合肥通用机械研究院 | Flow guiding structure at impeller inlet of multistage centrifugal blower or multistage centrifugal compressor |
| KR101393054B1 (en) * | 2013-06-27 | 2014-05-09 | (주)에이스정공 | Adapter for preventing cavitaion and centrifugal pump having adapter |
| US10030669B2 (en) * | 2014-06-26 | 2018-07-24 | General Electric Company | Apparatus for transferring energy between a rotating element and fluid |
| WO2016120990A1 (en) * | 2015-01-27 | 2016-08-04 | 三菱重工コンプレッサ株式会社 | Centrifugal compressor bundle and centrifugal compressor |
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