CN108223431A - 0.04 light substance high energy head compressor model grade of discharge coefficient and design method - Google Patents
0.04 light substance high energy head compressor model grade of discharge coefficient and design method Download PDFInfo
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- CN108223431A CN108223431A CN201711475812.1A CN201711475812A CN108223431A CN 108223431 A CN108223431 A CN 108223431A CN 201711475812 A CN201711475812 A CN 201711475812A CN 108223431 A CN108223431 A CN 108223431A
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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
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for 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
- F04D29/26—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
- F04D29/44—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
- F04D29/40—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
- F04D29/444—Bladed diffusers
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
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Abstract
The present invention provides 0.04 light substance high energy head compressor model grade of discharge coefficient; suitable for the Modulated Design of 0.04 light substance high energy head compressor model grade product of discharge coefficient; including impeller, vane diffuser, bend and return channel; impeller is located at the entry position of Stage; vane diffuser is equipped in the outlet of impeller; return channel is located at the outlet port of Stage, and vane diffuser is connected with return channel by bend；The machine Mach number M of Stagea2=0.2 0.65, design point discharge coefficient Φ1=0.04, design point energy head coefficient τ=0.7, the polytropic efficiency η under design discharge coefficient operating modepcl=0.862, the range of flow of application is the 0.66~1.45 of design point.The design method of the Stage is also provided.The Stage of the present invention is efficient, energy head coefficient is high, hub ratio is big, and span is small.
Description
Technical field
The present invention relates to Compressor Technology field, more particularly to a kind of 0.04 light substance high energy head compressor mould of discharge coefficient
Type grade and Design of Stage method.
Background technology
Light substance high energy head compressor is widely used in methanol (below 90 kilograms of outlet pressure) and chemical fertilizer plant (outlet pressure
150-160 kilograms of power) in, cover synthesis mechanism of qi group there are about 20-30 in the market every year, demand is big, while its industrial products is again more
It is the quality of the critical product for influencing the people's livelihood, model and design, influences the performance of this device unit, operation stability and energy consumption.
Current existing light substance compressor model stage efficiency is relatively low.Simultaneously existing Stage wheel hub it is smaller, when series compared with
It is unfavorable for the stability of rotor when more, and then there are larger in rigidity of product critical speed, rotor stability and axis etc.
The problem of, very big difficulty is brought to product design.In addition, the performance of unit is low compared with same kind of products at abroad.
Invention content
In order to solve the above problem existing for existing light substance compressor model grade, the purpose of the present invention is to provide one kind
0.04 light substance high energy head compressor model grade of discharge coefficient and design method, make light substance compressor product unit performance and fortune
Turn stability to be significantly improved, reduce the energy consumption of unit.
In order to solve the above technical problems, the present invention provides a kind of 0.04 light substance high energy head compressor models of discharge coefficient
Grade, including impeller 1, vane diffuser 2, bend 3 and return channel 4, wherein impeller 1 is located at the entry position of Stage, in impeller 1
Outlet be equipped with vane diffuser 2, the return channel 4 is located at the outlet port of Stage, vane diffuser 2 and return channel 4 it
Between be connected by bend 3；The machine Mach number M of the Stageu2=0.2-0.65, design point discharge coefficient Φ1=0.04,
Design point energy head coefficient τ=0.7, the polytropic efficiency η under each Mach number under design discharge coefficient operating modepd=0.862, it is applicable
Range of flow is the 0.66~1.45 of design point.
The present invention also provides a kind of design method of 0.04 light substance high energy head compressor model grade of discharge coefficient, packets
It includes：
Step 10, by one-dimensional thermal-design, meridional channel width and impeller basic parameter are obtained, including impeller inlet
Established angle β1A, impeller outlet established angle β2AAnd impeller outlet width b2；
Step 20 determines hub diameter according to hub ratio ds/D2 and given impeller diameter；
Step 30 passes through import relative velocity w1Minimum principle calculates impeller inlet diameter D0；
Step 40 changes linearly distribution according to the Beta angles of inlet and outlet blade and obtains the preliminary moulding of blade；
The runner threedimensional model of obtained impeller is carried out mesh generation by step 50, and the grid of generation is imported CFD points
It analyses in software, 3D viscous flow analysis is carried out to the impeller using Spalart-Allmaras turbulence models；The inlet side of analysis
Boundary's condition is total temperature, stagnation pressure；The export boundary condition of analysis is exported for mass flow；
Step 60 passes through velocity vector figure of the blade flow field to interception by wheel disc to wheel cap direction different cross section, interception
The velocity vector figure of impeller meridian direction and the blade of the impeller pressure face of interception and suction surface relative velocity figure to impeller
Flow field is analyzed, if the blade flow field of gained meets the first design condition, then it is assumed that design is completed；If flow field is unsatisfactory for first
Design condition, then for flow field there are the problem of carry out corresponding geometric corrections, and repeat step 50 and carry out CFD analyses, until
The blade flow field of gained meets design condition；
Step 70 carries out initial designs to vane diffuser first, and obtained impeller is calculated according to CFD in step 60
Exit flow angle beta 2 determines vane diffuser stagger angle α3A, setting vane diffuser exit installation angle α4A, determine that blade expands
Depressor entrance width b3 and exit width b4 is equal to impeller outlet width b2, and carries out preliminary moulding to vane diffuser, by institute
Obtained Stage runner threedimensional model carries out mesh generation, is then introduced into CFD analysis softwares, using obtained in step 60
The exit flow field situation of impeller is primary condition, using Spalart-Allmaras turbulence models to impeller and diffuser into
The continuous viscous flow analysis of row 3D is analyzed the flow field result of obtained CFD analyses, is obtained in vane diffuser runner
Between flowing velocity vector distribution map on the different height section of wheel disc to wheel cap, obtain the speed of vane diffuser meridional channel
Vector distribution map and vane diffuser exit flow angular distribution are spent, and analyses whether to meet the second design condition, if not satisfied,
Then vane diffuser geometric parameter is modified, CFD analyses is re-started and calculates；
Step 80, according to vane diffuser outlet flow angle, initial designs are carried out to bend and return channel blade, are determined back
Flow device stagger angle α5A, exit installation angle α6A, return channel entrance width b5, exit width b6, return channel entrance location diameter
D5 and outlet port diameter D6, and preliminary moulding is carried out to return channel, CFD analysis softwares are imported, using Spalart-
Allmaras turbulence models carry out the continuous viscous flow analysis of 3D to impeller, diffuser, bend and return channel, according to flow field analysis
As a result the amendment of return channel vane type line is carried out, and CFD analysis softwares is imported and iterates, if the bend (3) of gained, returning
Stream device (4) flow field meets third design condition, then designs completion.
0.04 light substance high energy head compressor model grade of discharge coefficient provided by the invention, efficient, energy head coefficient height, wheel
For hub than the characteristics of greatly, span is small, Stage using the present invention can cause light substance compressor to have higher operational efficiency
With can head coefficient, while complete machine rotor have shorter bearing span and higher operation stability.
Description of the drawings
Fig. 1 is the schematic diagram of 0.04 light substance high energy head compressor model grade of discharge coefficient provided in an embodiment of the present invention；
Fig. 2 is imported and exported for 0.04 light substance high energy head compressor model grade impeller of discharge coefficient provided in an embodiment of the present invention
Angle schematic diagram；
Fig. 3 is 0.04 light substance high energy head compressor model grade blade diffuser of discharge coefficient provided in an embodiment of the present invention
Pass in and out bicker schematic diagram；
Fig. 4 is passed in and out for 0.04 light substance high energy head compressor model grade return channel of discharge coefficient provided in an embodiment of the present invention
Bicker schematic diagram；
Fig. 5 is the high section relative velocity distribution map of 10% leaf of impeller provided in an embodiment of the present invention；
Fig. 6 is the high section relative velocity distribution map of 50% leaf of impeller provided in an embodiment of the present invention；
Fig. 7 is the high section relative velocity distribution map of 90% leaf of impeller provided in an embodiment of the present invention；
Fig. 8 is meridional channel relative velocity distribution map provided in an embodiment of the present invention；
Fig. 9 is the relative velocity distribution basis for estimation of impeller blade suction surface provided in an embodiment of the present invention and pressure face
Figure；
Figure 10 is the high section relative velocity distribution map of 10% leaf of vane diffuser provided in an embodiment of the present invention；
Figure 11 is the high section relative velocity distribution map of 50% leaf of vane diffuser provided in an embodiment of the present invention；
Figure 12 is the high section relative velocity distribution map of 90% leaf of vane diffuser provided in an embodiment of the present invention；
Figure 13 is the high section relative velocity distribution map of 10% leaf of return channel provided in an embodiment of the present invention；
Figure 14 is the high section relative velocity distribution map of 50% leaf of return channel provided in an embodiment of the present invention；
Figure 15 is the high section relative velocity distribution map of 90% leaf of return channel provided in an embodiment of the present invention；
Figure 16 is pressure ratio performance curve schematic diagram under different Mach number provided in an embodiment of the present invention；
Figure 17 is polytropic efficiency performance curve schematic diagram under different Mach number provided in an embodiment of the present invention；
Figure 18 is can head coefficient performance curve schematic diagram under different Mach number provided in an embodiment of the present invention.
Figure 19 is the impeller outlet air-flow angular distribution of axially opposed position provided in an embodiment of the present invention.
Figure 20 is distribution map of the vane diffuser outlet flow angle provided in an embodiment of the present invention along the high direction of leaf.
Specific embodiment
Referring to Fig. 1, a kind of 0.04 light substance high energy head compressor model grade of discharge coefficient provided in an embodiment of the present invention is fitted
For the Modulated Design of light substance compressor product, including impeller 1, vane diffuser 2, bend 3 and return channel 4, wherein impeller 1
Positioned at the entry position of Stage, vane diffuser 2 is equipped in the outlet of impeller 1, return channel 4 is located at the outlet position of Stage
It puts, is connected between vane diffuser 2 and return channel 4 by bend 3.The machine Mach number M that the Stage can useu2=
0.2-0.65, design point discharge coefficient Φ1=0.04, discharge coefficient is designed under each Mach number in design point energy head coefficient τ=0.7
Polytropic efficiency η under operating modepd=0.862, applicable range of flow is the 0.66~1.45 of design point.Specific performance curve is such as
Shown in Figure 16~18.
The hub ratio ds/D2 of the 0.04 light substance high energy head compressor model grade of discharge coefficient is very big, ds/D2=0.39.
About 16% is improved than general Stage hub ratio ds/D2=0.34, this can greatly improve the rotor using the Stage
Stability.
Impeller 1 is the 3 d impeller of enclosed, and the basic parameter of 3 d impeller is as follows：Impeller outlet diameter D2=500mm, leaf
The piece number Z=19, impeller opposite outlet widthb2For impeller outlet width.The impeller 1 is close to wheel cap and wheel disc side
Vane inlet established angle β 1As and β 1Ah are respectively 16 ° and 22 °, and impeller 1 is close to the exit vane angle beta 2As of wheel cap and wheel disc side
It it is 54 ° with β 2Ah, the β 1As, β 1Ah, β 2As, β 2Ah definition are as shown in Figure 2.The wheel cap side of impeller 1 and the son of reel side
Noon runner is spline curve.The relative velocity of the blade of 1 pressure face of impeller and suction surface is distributed in olive-type.Pressure face and suction
The position of the relative velocity difference maximum of the blade in power face is located at 60%~80% length of blade.For example, relative velocity difference
Maximum position is approximately located i at 65% length of blade, and this load is distributed so that the Stage has very high efficiency and wider
Condition range.Under design point Mach number and discharge coefficient working condition, the flowing of the impeller has following features：1st, the leaf
Wheel is on 10%, 50%, the 90% high section of leaf, the no any flow separation of flowing among impeller channel, such as Fig. 5~Fig. 7 institutes
Show.2nd, unsteady three-dimensional viscous flows CFD analysis results show on the meridional channel of the impeller also without any flowing point
From as shown in Figure 8.3rd, the polytropic efficiency of the impeller is very high, and the polytropic efficiency at impeller outlet is up to 96.2%.
The basic parameter of vane diffuser 2 is as follows：The wheel cap of vane diffuser and the meridian molded line of reel side are by one section
Straight line is formed；2 entrance relative position of vane diffuserExport relative positionNumber of blade Z=13；
2 stagger angle α of vane diffuser3=26 °, exit installation angle α4=29 °, the α3And α4Definition is as shown in Figure 3；Reel side
Meridian molded line perpendicular to axial direction.The ratio b of 1 exit width of 2 entrance width of vane diffuser and impeller3/b2It is 1, which ensures
1 exit flow of impeller can smoothly enter vane diffuser 2；2 exit width of vane diffuser and vane diffuser 2 simultaneously
The ratio b of entrance width4/b3It is 1.The design can be very good the flow field at matching impeller outlet, inhibit the stream of diffuser shrouding disc side
Dynamic separation, reduces the flow losses in vane diffuser 2.As shown in Figure 10~Figure 12, without flowing point on the vane diffuser
From.The polytropic efficiency of the diffuser exit is very high, and the polytropic efficiency at impeller outlet is up to 95.6%.
In one embodiment, the inlet and outlet width of bend 3 compares b5/b4It is 1.1.The unsteady three-dimensional viscous flow of the Stage
Dynamic CFD analysis results show that under design point Mach number and discharge coefficient working condition 3 inside of bend does not have flow separation.Such as
Shown in Fig. 8.
In one embodiment, 4 blade of return channel uses overall height banana airfoil fan, number of blade Z=24, blade inlet phase
To position D5/D2=1.4, entrance established angle is α 5A=21.5 °, blade exit relative position D6/D2=0.7, exit installation angle
For α 6A=95.6 °, the definition of return channel import and export established angle is as shown in Figure 4；The design can be very good the outlet of matching bend
Flow field, and the control of return channel exit flow axial angle is arrived and is less than 1 °.Meanwhile return channel blade is under design discharge coefficient
There is no any flow separation.As shown in Figure 13~Figure 15.4 wheel cap side meridian molded line of return channel is a vertical straight line section, and curved
Road wheel cap side circular arc is tangent；Reel side meridian molded line is an oblique line section, tangent with bend reel side circular arc；Return channel exports section lid
Disk side and reel side are made of respectively two circular arcs and the straightway tangent with circular arc.
The embodiment of the present invention also provides the whole grade design method of 0.04 light substance high energy head compressor model grade of discharge coefficient,
It specifically includes：
Step 10 passes through one-dimensional thermal-design, acquisition impeller inlet established angle β1A, impeller outlet established angle β2A, Yi Jiye
Take turns exit width b2；
β1A=tan-1c1/u1+ i, wherein：
c1--- impeller inlet absolute velocity
u1--- impeller inlet peripheral speed
I --- the angle of attack
Wherein：
qvin--- import volume flow
D2--- impeller outer diameter
Kv2--- impeller outlet specific volume ratio
--- discharge coefficient impeller outlet radial direction discharge coefficient
u2--- peripheral speed
τ2--- blade exit blockage factor
Wherein：
--- discharge coefficient
--- peripheral speed coefficient
Step 20, according to hub ratio ds/D2 (for example, ds/D2=0.39) and given impeller diameter (for example, giving
Determine D2=500mm) determine hub diameter.Wherein ds is hub diameter, D2 is impeller outer diameter.
Step 30 passes through import relative velocity w1Minimum principle obtains impeller inlet diameter D by the following formula0。
Wherein：
D --- hub diameter
D2 --- impeller outer diameter
Kv2--- impeller outlet specific volume ratio
--- discharge coefficient impeller outlet radial direction discharge coefficient
Kc--- velocity coeffficient
τ2--- blade exit blockage factor
Kv0--- impeller inlet specific volume ratio
KD--- diameter ratio
Wherein：
--- discharge coefficient
--- peripheral speed coefficient
Step 40 changes linearly distribution according to the Beta angles of inlet and outlet blade and obtains the preliminary moulding of blade, such as scheme
19。
The runner threedimensional model of obtained impeller is carried out mesh generation by step 50, during mesh generation, reduces wall
The Yplus in face is less than 1, while the length-width ratio of grid is less than 2000, extends than being less than 3, the orthogonality of grid is more than 15 °.It will be raw
Into grid import CFD analysis softwares in, using Spalart-Allmaras turbulence models to the impeller carry out 3D Viscous Flows
Analysis；The inlet boundary condition of analysis is total temperature, stagnation pressure；The export boundary condition of analysis is exported for mass flow.
Step 60 analyzes the impeller internal flow result of CFD analysis gained, i.e.,：Pass through the impeller stream to interception
Field is by the velocity vector figure of wheel disc to wheel cap direction different cross section, the velocity vector figure of the impeller meridian direction of interception and interception
The relative velocity figure of the blade of impeller pressure face and suction surface analyzes blade flow field, if the blade flow field of gained meets the
One design condition, then it is assumed that design is completed.If flow field is unsatisfactory for the first design condition, for flow field there are the problem of carry out phase
The geometric corrections answered, and repeat step 50 and carry out CFD analyses, until the blade flow field of gained meets design condition.Meet first
Design condition is：On 10%, 50%, 90% section of short transverse of wheel disc to wheel cap, the flowing among runner does not have impeller 1
Any flow separation.As shown in Fig. 5~Fig. 7；Also without any flow separation on the meridional channel of II impellers 1.Such as Fig. 8 institutes
Show；The relative velocity approximation of the blade of III pressure faces and suction surface is distributed in olive-type.The position position of relative velocity difference maximum
At 60%~80% length of blade.As shown in Figure 9.
Step 70 carries out initial designs to vane diffuser first, and obtained impeller is calculated according to CFD in step 60
Exit flow angle beta 2 determines vane diffuser stagger angle α3A, setting vane diffuser exit installation angle α4A(pass through for 30 °
A large amount of experiment, set angle are 30 °, can greatly reduce impact of the diffuser exit air-flow to return channel entrance), determine blade
Diffuser intake width b3 and exit width b4 is equal to impeller outlet width b2, and (a large amount of experiment of process, can by such setting
To ensure that flowing is smooth), and preliminary moulding is carried out to vane diffuser, obtained Stage runner threedimensional model is carried out
(during mesh generation, the Yplus for reducing wall surface is less than 1, while the length-width ratio of grid is less than 2000 to mesh generation, extension ratio
Less than 3, the orthogonality of grid is more than 15 °), CFD analysis softwares are then introduced into, utilize the outlet of impeller obtained in step 60
Flow field situation is primary condition, and carrying out 3D to impeller and diffuser using Spalart-Allmaras turbulence models continuously glues
Property flow field analysis, so as to obtain among vane diffuser runner on the different height section of wheel disc to wheel cap flowing velocity arrow
Amount distribution map, the velocity vector distribution map for obtaining vane diffuser meridional channel and vane diffuser exit flow angular distribution；
To flowing velocity vector distribution map, the leaf among obtained vane diffuser runner on the different height section of wheel disc to wheel cap
The velocity vector distribution map and vane diffuser exit flow angular distribution of piece diffuser meridional channel are analyzed, if above three
A aspect meets following three design conditions simultaneously, then it is assumed that design is completed, if not satisfied, then to vane diffuser geometric parameter
It is modified, re-starts CFD analyses and calculate.Meeting design condition is：(1) vane diffuser 2 is in the height of wheel disc to wheel cap
On 10%, 50%, 90% section of direction, the no any flow separation of flowing among runner.As shown in Figure 10~Figure 12；(2)
Also without any flow separation on the meridional channel of vane diffuser 2.As shown in Figure 8；(3) vane diffuser outlet flow angle
Degree is between 25 ° to 40 °, as shown in figure 20.The diffusion action of diffuser is ensured in this way, while reduces diffuser exit air-flow
Impact to return channel.Designer is allowd to directly acquire the mobility status inside diffuser runner in this way, and is directed to
The geometric parameter to vane diffuser of property is modified, being designed to vane diffuser rapidly and efficiently.Meanwhile use is non-
Permanent calculation and analysis methods, analysis obtain interaction force unsteady between impeller and vane diffuser, to reduce diffuser
The risk destroyed when its interaction force with impeller, it is determined that the inlet diameter D3's and impeller diameter D2 of vane diffuser
Ratio is 115%.
Step 80, according to vane diffuser outlet flow angle, initial designs are carried out to bend and return channel blade, are determined back
Flow device stagger angle α5AFor 21.5 °, exit installation angle α6ABe 95.6 °, return channel entrance width b5, exit width b6 and
Return channel entrance location D5, outlet port D6.And preliminary moulding is carried out to return channel, CFD analysis softwares are imported, are used
Spalart-Allmaras turbulence models carry out the continuous viscous flow analysis of 3D to impeller, diffuser, bend and return channel, according to
Flow field analysis result carries out the amendment of return channel vane type line, and imports CFD analysis softwares and iterate, if gained is curved
Road 3,4 flow field of return channel meet third design condition, then it is assumed that design is completed.Meeting third design condition is：I return channels 4 exist
On wheel disc to 10%, 50%, 90% section of short transverse of wheel cap, the no any flow separation of flowing among runner.Such as figure
Shown in 13~Figure 15；II bends 3, return channel 4 meridional channel on also without any flow separation.As shown in Figure 8.
It should be noted last that more than specific embodiment is merely illustrative of the technical solution of the present invention and unrestricted,
Although the present invention is described in detail with reference to example, it will be understood by those of ordinary skill in the art that, it can be to the present invention
Technical solution be modified or replaced equivalently, without departing from the spirit and scope of technical solution of the present invention, should all cover
In scope of the presently claimed invention.
Claims (10)
1. a kind of 0.04 light substance high energy head compressor model grade of discharge coefficient, it is characterised in that：Expand including impeller (1), blade
Depressor (2), bend (3) and return channel (4), wherein impeller (1) are set positioned at the entry position of Stage in the outlet of impeller (1)
Have a vane diffuser (2), the return channel (4) positioned at the outlet port of Stage, vane diffuser (2) and return channel (4) it
Between be connected by bend (3)；The machine Mach number M of the Stagea2=0.2-0.65, design point discharge coefficient Φ1=
0.04, design point energy head coefficient τ=0.7, the polytropic efficiency η under each Mach number under design discharge coefficient operating modepcl=0.862, energy
The range of flow of application is the 0.66~1.45 of design point.
2. 0.04 light substance high energy head compressor model grade of discharge coefficient according to claim 1, it is characterised in that：It is described
0.04 light substance high energy head compressor model grade of discharge coefficient hub ratio ds/D2=0.39, the ds is straight for wheel hub
Diameter, D2 are impeller outer diameter.
3. 0.04 light substance high energy head compressor model grade of discharge coefficient according to claim 1, it is characterised in that：It is described
Impeller (1) is the 3 d impeller of enclosed, and the basic parameter of 3 d impeller is as follows：
Impeller (1) outlet diameter D2=500mm, number of blade Z=19, impeller opposite outlet widthb2Go out for impeller
Mouth width degree, the impeller are respectively 16 ° and 22 ° close to wheel cap and wheel disc lateral lobe piece stagger angle β 1As and β 1Ah, and impeller is close
Wheel cap and exit vane angle beta 2As and the β 2Ah of wheel disc side are 54 °.
4. 0.04 light substance high energy head compressor model grade of discharge coefficient according to claim 1, it is characterised in that：It is described
The wheel cap side of impeller (1) and the meridional channel of reel side are respectively spline curve.
5. 0.04 light substance high energy head compressor model grade of discharge coefficient according to claim 1, it is characterised in that：It is described
The basic parameter of the blade of vane diffuser (2) is as follows：
Vane diffuser (2) entrance relative positionExport relative positionNumber of blade Z=13 is
Impeller outlet width, vane inlet established angle α3AIt is 26 °, blade exit established angle α4AIt it is 29 °, the D2 is straight for impeller
Diameter, D3 are the diameter of vane diffuser entrance location, and D4 is the diameter of vane diffuser outlet port.
6. 0.04 light substance high energy head compressor model grade of discharge coefficient according to claim 1, it is characterised in that：It is described
The ratio b3/b2 of vane diffuser (2) entrance width and impeller (1) exit width is 0.98, while vane diffuser (2) goes out mouth width
Degree and the ratio b4/b3 of vane diffuser (2) entrance width are 0.97, and the b2 is impeller outlet width, and b3 is vane diffuser
Entrance width, b4 are vane diffuser exit width.
7. 0.04 light substance high energy head compressor model grade of discharge coefficient according to claim 1, it is characterised in that：It is described
The inlet and outlet width of bend (3) compares b5/b4It is 1.07, the b5 is bend exit width.
8. 0.04 light substance high energy head compressor model grade of discharge coefficient according to claim 1, it is characterised in that：It is described
Return channel (4) blade uses overall height aerofoil profile Leaf of banana, number of blade Z=24, blade inlet relative position D5/D2=1.4, enter
Mouth established angle is 21.5 °, blade exit relative position D6/D2=0.7, exit installation angle is 95.6 °, and the D4 is return channel leaf
The diameter of piece outlet port, D5 are the diameter of return channel blade inlet position, and the D6 is the straight of return channel blade exit position
Diameter.
9. a kind of design setting for 0.04 light substance high energy head compressor model grade of claim 1-8 any one of them discharge coefficient
Meter method, which is characterized in that including：
Step 10, by one-dimensional thermal-design, obtain meridional channel width and impeller basic parameter, installed including impeller inlet
Angle beta1A, impeller outlet established angle β2AAnd impeller outlet width b2；
Step 20 determines hub diameter according to hub ratio ds/D2 and given impeller diameter；
Step 30 passes through import relative velocity w1Minimum principle calculates impeller inlet diameter D0；
Step 40 changes linearly distribution according to the Beta angles of inlet and outlet blade and obtains the preliminary moulding of blade；
The runner threedimensional model of obtained impeller is carried out mesh generation by step 50, and it is soft that the grid of generation is imported CFD analyses
In part, 3D viscous flow analysis is carried out to the impeller using Spalart-Allmaras turbulence models；The inlet boundary item of analysis
Part is total temperature, stagnation pressure；The export boundary condition of analysis is exported for mass flow；
Step 60, by the blade flow field to interception by wheel disc to wheel cap direction different cross section velocity vector figure, interception leaf
The relative velocity figure of the blade of the velocity vector figure of meridian direction and the impeller pressure face and suction surface of interception is taken turns to blade flow field
It is analyzed, if the blade flow field of gained meets the first design condition, then it is assumed that design is completed；If flow field is unsatisfactory for the first design
Condition, then for flow field there are the problem of carry out corresponding geometric corrections, and repeat step 50 and carry out CFD analyses, until gained
Blade flow field meet design condition；
Step 70 carries out initial designs to vane diffuser first, and the outlet of obtained impeller is calculated according to CFD in step 60
Flow angle β 2 determines vane diffuser stagger angle α3A, setting vane diffuser exit installation angle α4A, determine vane diffuser
Entrance width b3 and exit width b4 is equal to impeller outlet width b2, and carries out preliminary moulding to vane diffuser, by obtained by
Stage runner threedimensional model carry out mesh generation, be then introduced into CFD analysis softwares, utilize impeller obtained in step 60
Exit flow field situation for primary condition, 3D is carried out to impeller and diffuser using Spalart-Allmaras turbulence models
Continuous viscous flow analysis, to obtained CFD analysis flow field result analyze, obtain among vane diffuser runner
Flowing velocity vector distribution map on wheel disc to the different height section of wheel cap, the speed arrow for obtaining vane diffuser meridional channel
Distribution map and vane diffuser exit flow angular distribution are measured, and analyses whether to meet the second design condition, if not satisfied, then right
Vane diffuser geometric parameter is modified, and is re-started CFD analyses and is calculated；
Step 80, according to vane diffuser outlet flow angle, initial designs are carried out to bend and return channel blade, determine return channel
Stagger angle α5A, exit installation angle α6A, return channel entrance width b5, exit width b6, return channel entrance location diameter D5 and
Outlet port diameter D6, and preliminary moulding is carried out to return channel, CFD analysis softwares are imported, using Spalart-Allmaras rapidss
Flow model carries out the continuous viscous flow analysis of 3D to impeller, diffuser, bend and return channel, is returned according to flow field analysis result
The amendment of device vane type line is flowed, and imports CFD analysis softwares and iterates, if the bend (3) of gained, return channel (4) flow
Field meets third design condition, then designs completion.
10. according to the method for claim 11, which is characterized in that second design condition includes vane diffuser (2)
The no any flow separation of flowing among 10%, 50%, the 90% section upper runner of short transverse of wheel disc to wheel cap；Blade
There is no any flow separation on the meridional channel of diffuser (2)；Vane diffuser (2) exit flow angle 25 ° to 40 ° it
Between.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112032076A (en) * | 2020-09-15 | 2020-12-04 | 重庆通用工业(集团)有限责任公司 | Large chemical centrifugal compressor model level modeling type selection design method and device |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103047176A (en) * | 2011-10-17 | 2013-04-17 | 沈阳透平机械股份有限公司 | PCL compressor model stage and design method thereof |
| CN203500056U (en) * | 2013-10-16 | 2014-03-26 | 中国石油集团工程设计有限责任公司 | Closed-type high-flow and high-energy head model level |
| CN103807209A (en) * | 2014-02-13 | 2014-05-21 | 沈阳斯特机械制造有限公司 | Enclosed impeller of centrifugal compressor |
| CN104533836A (en) * | 2014-12-26 | 2015-04-22 | 沈阳鼓风机集团安装检修配件有限公司 | Inter-stage air feeding structure of centrifugal compressor and design method thereof |
| US20150369073A1 (en) * | 2014-06-24 | 2015-12-24 | Concepts Eti, Inc. | Flow Control Structures For Turbomachines and Methods of Designing The Same |
| CN106762815A (en) * | 2016-11-28 | 2017-05-31 | 沈阳透平机械股份有限公司 | The pipeline compressor model of discharge coefficient 0.0424 level and method for designing impeller |
-
2017
- 2017-12-29 CN CN201711475812.1A patent/CN108223431A/en not_active Withdrawn
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103047176A (en) * | 2011-10-17 | 2013-04-17 | 沈阳透平机械股份有限公司 | PCL compressor model stage and design method thereof |
| CN203500056U (en) * | 2013-10-16 | 2014-03-26 | 中国石油集团工程设计有限责任公司 | Closed-type high-flow and high-energy head model level |
| CN103807209A (en) * | 2014-02-13 | 2014-05-21 | 沈阳斯特机械制造有限公司 | Enclosed impeller of centrifugal compressor |
| US20150369073A1 (en) * | 2014-06-24 | 2015-12-24 | Concepts Eti, Inc. | Flow Control Structures For Turbomachines and Methods of Designing The Same |
| CN104533836A (en) * | 2014-12-26 | 2015-04-22 | 沈阳鼓风机集团安装检修配件有限公司 | Inter-stage air feeding structure of centrifugal compressor and design method thereof |
| CN106762815A (en) * | 2016-11-28 | 2017-05-31 | 沈阳透平机械股份有限公司 | The pipeline compressor model of discharge coefficient 0.0424 level and method for designing impeller |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112032076A (en) * | 2020-09-15 | 2020-12-04 | 重庆通用工业(集团)有限责任公司 | Large chemical centrifugal compressor model level modeling type selection design method and device |
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