CN106499668A - 0.0385 pipeline compressor model level of discharge coefficient and method for designing impeller - Google Patents
0.0385 pipeline compressor model level of discharge coefficient and method for designing impeller Download PDFInfo
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- CN106499668A CN106499668A CN201611065210.4A CN201611065210A CN106499668A CN 106499668 A CN106499668 A CN 106499668A CN 201611065210 A CN201611065210 A CN 201611065210A CN 106499668 A CN106499668 A CN 106499668A
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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
- F04D29/40—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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- 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 0.0385 pipeline compressor model level of discharge coefficient, including impeller, vaneless diffuser, bend and return channel, wheel is located at the entry position of Stage, outlet in impeller is provided with vaneless diffuser, return channel is located at the exit position of Stage, and vaneless diffuser is connected by bend with return channel；The machine Mach number M of Stageu2=0.35～0.65, design point discharge coefficient Φ1=0.0385, design point energy head coefficient τ=0.606, polytropic efficiency η under each Mach number under design discharge coefficient operating modepcl=0.867～0.869, the range of flow of application for design point 60% 150%.The method for designing of the Stage impeller is also provided.The Stage efficiency high of the present invention, energy head coefficient are high, hub ratio is big, span is little, can cause light substance compressor that there is higher operational efficiency and wider condition range using the Stage, while working rotor rotating speed can be reduced, bearing span is reduced, the stability of rotor is improved.
Description
Technical field
The present invention relates to Compressor Technology field, more particularly to a kind of 0.0385 pipeline compressor model level of discharge coefficient and
Method for designing impeller.
Background technology
Pipeline compressor is to transfer natural gas from the west to the east the key equipment of key state project, and in its R＆D process, Stage sets
Meter is very crucial, and the research and development of new product depend on corresponding Stage.
Existing pipeline model level has that hub ratio is little, axial span is big, the low shortcoming of efficiency, so the mistake in product design
In journey, the rotating shaft diameter of axle is little, axial length, and then the aspect such as the rigidity in product critical speed, rotor stability and axle has larger asking
Topic, brings very big difficulty to product design.In addition, the performance of unit is low compared with same kind of products at abroad.
Content of the invention
In order to solve the problems referred to above that existing pipeline model level is present, it is an object of the invention to provide a kind of discharge coefficient
0.0385 pipeline compressor model level and its method for designing impeller, are significantly improved pipeline compressor product unit efficiency,
Reduce the power consumption of unit.
For solving above-mentioned technical problem, the invention provides a kind of 0.0385 pipeline compressor model level of discharge coefficient, its
Including impeller 1, vaneless diffuser 2, bend 3 and return channel 4, wherein impeller 1 is located at the entry position of Stage, in impeller 1
Outlet is provided with vaneless diffuser 2, and the return channel 4 is located at the exit position of Stage, between vaneless diffuser 2 and return channel 4
It is connected by bend 3；The machine Mach number M of the Stagea2=0.35～0.65, design point discharge coefficient Φ1=
0.0385, design point energy head coefficient τ=0.606, polytropic efficiency η under each Mach number under design discharge coefficient operating modepcl=
0.867～0.869,60%-150% of the applicable range of flow for design point.
The present invention also provides the method for designing of impeller in a kind of 0.0385 pipeline compressor model level of discharge coefficient, and which wraps
Include：
By one-dimensional thermal-design, obtain impeller inlet and angle beta is installed1A, impeller outlet install angle beta2A, and impeller outlet
Width b2；
Hub diameter is determined according to hub ratio ds/D2 and given impeller diameter；
By import relative velocity w1Minimum principle calculates impeller inlet diameter D0；
The preliminary moulding of blade is obtained according to the linear change profile in Beta angles for importing and exporting blade；
The runner threedimensional model of obtained impeller is carried out stress and strain model；
The grid for generating is imported in CFD analysis softwares, the impeller is entered using Spalart-Allmaras turbulence models
Row 3D viscous flow analysis；The inlet boundary condition of analysis is stagnation temperature, stagnation pressure, and the export boundary condition of analysis measured for quality stream
Mouthful；
The blade flow field result that CFD analyzes gained is analyzed, when blade flow field does not meet design requirement, is then adjusted
Impeller meridian and the coupling of vane type line, by changing iterating for the distribution of blade beta angles, meridian molded line and CFD analyses,
The final blade flow field for causing gained meets design requirement；The design requirement includes impeller on the high section of leaf, and impeller is in stream
Flowing in the middle of road is without flow separation；Without flow separation on the meridional channel of impeller；The outlet flow angle of impeller is evenly distributed；Go out
Mouth static pressure distribution is uniform；The relative velocity of the blade of pressure face and suction surface is approximately distributed in olive-type.
Further, the stress and strain model is that the Yplus for reducing wall during stress and strain model is less than 1, while grid
Length-width ratio less than 2000, extend than being less than 3, the orthogonality of grid is more than 15 °.
Further, on the high section of leaf, flowing of the impeller in the middle of runner is that impeller exists without flow separation to the impeller
10%th, on the high section of 50%, 90% leaf, flowing of the impeller in the middle of runner is without flow separation.
Further, it is 17～25 ° of average outlet flow angle that the outlet flow angle of the impeller is evenly distributed, and wherein, goes out
Mouth flow angle fluctuation range is less than 5 °.
Further, the exit static pressure is evenly distributed and refers to fluctuation range within the 2% of exit static pressure.
Further, the maximum position of the relative velocity difference of the blade of the pressure face and suction surface be located at 60%～
At 80% length of blade.
The pipeline compressor special purpose model level that the present invention is provided, efficiency high, energy head coefficient are high, hub ratio is big, and span is little, adopts
Can cause pipeline compressor that there is higher operational efficiency and wider condition range with the Stage of the present invention, while can be with
Reduce working rotor rotating speed, reduce bearing span, improve the stability of rotor.
Description of the drawings
Fig. 1 is the schematic diagram of 0.0385 pipeline compressor model level of discharge coefficient provided in an embodiment of the present invention；
Fig. 2 is that the turnover bicker of 0.0385 pipeline compressor model level impeller of discharge coefficient provided in an embodiment of the present invention is illustrated
Figure；
Fig. 3 is that the turnover bicker of 0.0385 pipeline compressor model level return channel of discharge coefficient provided in an embodiment of the present invention is shown
It is intended to；
Fig. 4 is the high section relative velocity distribution map of 10% leaf of impeller provided in an embodiment of the present invention；
Fig. 5 is the high section relative velocity distribution map of 50% leaf of impeller provided in an embodiment of the present invention；
Fig. 6 is the high section relative velocity distribution map of 90% leaf of impeller provided in an embodiment of the present invention；
Fig. 7 is meridional channel relative velocity distribution map provided in an embodiment of the present invention；
Fig. 8 is the impeller outlet flow angle distribution basis for estimation figure of axially opposed position provided in an embodiment of the present invention；
Fig. 9 is the impeller outlet static pressure distribution basis for estimation figure of axially opposed position provided in an embodiment of the present invention；
Figure 10 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 11 is the impeller outlet air-flow angular distribution of axially opposed position provided in an embodiment of the present invention；
Figure 12 is the impeller outlet static pressure distribution figure of axially opposed position provided in an embodiment of the present invention；
Figure 13 is the impeller outlet air-flow angular distribution of axially opposed position provided in an embodiment of the present invention；
Figure 14 is the high section relative velocity distribution map of 10% leaf of return channel provided in an embodiment of the present invention；
Figure 15 is the high section relative velocity distribution map of 50% leaf of return channel provided in an embodiment of the present invention；
Figure 16 is the high section relative velocity distribution map of 90% leaf of return channel provided in an embodiment of the present invention；
Figure 17 is pressure ratio performance curve schematic diagram under different Mach number provided in an embodiment of the present invention；
Figure 18 is polytropic efficiency performance curve schematic diagram under different Mach number provided in an embodiment of the present invention；
Figure 19 is can head coefficient performance curve schematic diagram under different Mach number provided in an embodiment of the present invention.
Specific embodiment
Referring to Fig. 1,0.0385 pipeline compressor model level of a kind of discharge coefficient provided in an embodiment of the present invention, it is adaptable to manage
Wire compression machine and the Modulated Design of other light substance compressor products, including impeller 1, vaneless diffuser 2, bend 3 and return channel
4, wherein impeller 1 is located at the entry position of Stage, and the outlet in impeller 1 is provided with vaneless diffuser 2, and return channel 4 is located at model
The exit position of level, is connected by bend 3 between vaneless diffuser 2 and return channel 4.The mechanical horse that the Stage can be used
Conspicuous several Ma2=0.35～0.65, design point discharge coefficient Φ1=0.0385, design point energy head coefficient τ=0.606, each Mach number
Polytropic efficiency η under lower design discharge coefficient operating modepcL=0.867～0.869, applicable range of flow are design point
60%-150%.Specific performance curve is as shown in Figure 17～19.
Hub ratio ds/D2 of the 0.0385 pipeline compressor model level of discharge coefficient is very big, ds/D2=0.40.Than general
Stage hub ratio ds/D2=0.34 improve about 18%, this can greatly improve stablizing for the rotor using the Stage
Property.
In one embodiment, 3 d impeller of the impeller 1 for enclosed, the basic parameter of 3 d impeller are as follows：Impeller outlet is straight
Footpath D2=450mm, number of blade Z=17, impeller opposite outlet widthb2For impeller outlet width.The impeller 1 is close
Wheel cap and wheel disc lateral lobe piece stagger angle β 1As and β 1Ah are respectively 8.2 ° and 18 °, and impeller 1 goes out near wheel cap and wheel disc side
Mouth blade angles 2As and β 2Ah are 38 °.The meridional channel of the wheel cap side and reel side of impeller 1 respectively by two sections of circular arcs tangent and
Into, and two sections of circular arcs each are tangent with two straightways.The relative velocity of the blade of 1 pressure face of impeller and suction surface divides in olive-type
Cloth.The maximum position of the relative velocity difference of the blade of pressure face and suction surface is located at 60%～80%% length of blade.Example
Such as, the maximum position of relative velocity difference is approximately at 65% length of blade, and this load is distributed and the Stage is had
Very high efficiency and wider condition range.Under design point Mach number and discharge coefficient working condition, the flowing tool of the impeller
There are following features：1st, on the high section of 10%, 50%, 90% leaf, the flowing in the middle of impeller channel does not have any flowing to the impeller
Separate, as shown in Fig. 4～Fig. 6.2nd, unsteady three-dimensional viscous flows CFD analysis results show, on the meridional channel of the impeller
Without any flow separation, as shown in Figure 7.3rd, 1 outlet flow angle of impeller is evenly distributed, and fluctuation range is less than 5 degree, such as Figure 11
Shown.4th, 1 exit static pressure distributing homogeneity of impeller is good, fluctuation range within the 2% of exit static pressure, as shown in figure 12.5th, should
The polytropic efficiency of impeller is very high, and the polytropic efficiency at impeller outlet is up to 96.8%.
In one embodiment, the meridian molded line of wheel cap and reel side without piece diffuser 2 is constituted by one section of straight line；Its
In, the meridian molded line of reel side is perpendicular to axial direction.Ratio b without 1 exit width of 2 entrance width of piece diffuser and impeller3/b2For 1,
The design ensure that 1 exit flow of impeller can smoothly enter vaneless diffuser 2；Simultaneously 2 exit width of vane diffuser and
The ratio b of 2 entrance width of vane diffuser4/b3About 0.917.The design can be very good to mate the flow field at impeller outlet, suppression
The flow separation of vaneless diffuser shrouding disc side processed, reduces the flow losses of vaneless diffuser.As shown in fig. 7, the vaneless diffuser
On almost without flow separation.Without 2 entrance relative position of piece diffuserOutlet relative position
In one embodiment, the import and export width ratio b of bend 35/b4For 1.194.The unsteady Three Dimensional Viscous of the Stage
Flowing CFD analysis results show, under design point Mach number and discharge coefficient working condition, do not have flow separation inside bend 3.
As shown in Figure 7.
In one embodiment, 4 blade of return channel adopts overall height banana airfoil fan, and the number of blade is Z=24, blade inlet phase
To position D5/D2=1.581, entrance established angle is 18 °, blade exit relative position D6/D2=0.72, exit installation angle is
98.63 °, the definition of return channel import and export established angle is as shown in Figure 3；The design can be very good the flow field for mating bend outlet, and
And by the angle control of return channel exit flow axial direction to less than 1 °.Meanwhile, return channel blade is not appointed under design discharge coefficient
What flow separation.As shown in Figure 14～Figure 16.4 wheel cap side meridian molded line of return channel is a vertical straight line section, with bend 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 outlet section shrouding disc side and
Reel side is made up of two circular arcs and the straightway tangent with circular arc respectively.
The embodiment of the present invention also provides the design of the core component impeller of 0.0385 pipeline compressor model level of discharge coefficient
Method, specifically includes：
Step 10, by one-dimensional thermal-design, obtain impeller inlet and angle beta be installed1A, impeller outlet install angle beta2A, Yi Jiye
Wheel exit width b2；
β1A=tan-1c1/u1+ i, wherein：
c1Impeller inlet absolute velocity
u1Impeller inlet peripheral speed
The i angles of attack
Wherein：
qvinImport volume flow
D2Impeller outer diameter
Kv2Impeller outlet specific volume ratio
Discharge coefficient impeller outlet radial direction discharge coefficient
u2Peripheral speed
τ2Blade exit blockage factor
Wherein：
Discharge coefficient
Peripheral speed coefficient
Step 20, (for example, given according to hub ratio ds/D2 (for example, ds/D2=0.4) and given impeller diameter
D2=450mm) determine hub diameter.Wherein ds is hub diameter, D2 is impeller outer diameter.
Step 30, pass through import relative velocity w1Minimum principle, obtains impeller inlet diameter D by below equation0.
Wherein：
D hub diameters
D2 impeller outer diameters
Kv2Impeller outlet specific volume ratio
Discharge coefficient impeller outlet radial direction discharge coefficient
KcVelocity coeffficient
τ2Blade exit blockage factor
Kv0Impeller inlet specific volume ratio
KDDiameter ratio
Wherein：
Discharge coefficient
Peripheral speed coefficient
Step 40, the preliminary moulding of blade is obtained according to the linear change profile in Beta angles for importing and exporting blade, for example, schemed
13.
Step 50, the runner threedimensional model of obtained impeller is carried out stress and strain model, during stress and strain model, reduce 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, and the orthogonality of grid is more than 15 °.Will be raw
Into grid import CFD analysis softwares in, 3D Viscous Flows are carried out to the impeller using Spalart-Allmaras turbulence models
Analysis；The inlet boundary condition of analysis is stagnation temperature, stagnation pressure；The export boundary condition of analysis is exported for mass flow.
Step 60, the flow field result of the CFD of gained analysis gained is post-processed, if the blade flow field of gained meet with
Lower condition, then it is assumed that design is completed.Meeting design condition is：On the high section of 10%, 50%, 90% leaf, impeller 1 flows impeller 1
Flowing in the middle of road does not have any flow separation.As shown in Fig. 4～Fig. 6；Also without any stream on the meridional channel of II impellers 1
Dynamic separation.As shown in Figure 7；The outlet flow angle of III impellers 1 is evenly distributed, and average outlet flow angle is 17～25 °.Work off one's feeling vent one's spleen
Stream angle fluctuation range is less than 5 °；As shown in Figure 8：IV exit static pressures distributing homogeneity is good, fluctuation range exit static pressure 2% with
Interior.As shown in Figure 9；The relative velocity of the blade of V pressure faces and suction surface is approximately distributed in olive-type.Relative velocity difference is maximum
Position be located at 60%～80% length of blade at.As shown in Figure 10.
Step 70, the flow field result of the CFD of gained analysis gained is post-processed, if the blade flow field of gained is unsatisfactory for
Conditions above, then the coupling of adjustment impeller meridian and vane type line, is analyzed by the distribution of blade beta angles, meridian molded line and CFD
Iterate, the final blade flow field for causing gained meets conditions above, now, complete design.
It should be noted last that, above specific embodiment only in order to technical scheme to be described and unrestricted,
Although being described in detail to the present invention with reference to example, it will be understood by those within the art that, can be to the present invention
Technical scheme modify or equivalent, without deviating from the spirit and scope of technical solution of the present invention, which all should be covered
In the middle of scope of the presently claimed invention.
Claims (10)
1. 0.0385 pipeline compressor model level of a kind of discharge coefficient, it is characterised in that：Including impeller (1), vaneless diffuser
(2), bend (3) and return channel (4), wherein impeller (1) are located at the entry position of Stage, and the outlet in impeller (1) is provided with nothing
Leaf diffuser (2), described return channel (4) are located at the exit position of Stage, lead between vaneless diffuser (2) and return channel (4)
Cross bend (3) to be connected；The machine Mach number M of the StageU2=0.35～0.65, design point discharge coefficient Φ1=
0.0385, design point energy head coefficient τ=0.606, the polytropic efficiency under each Mach number under design discharge coefficient operating mode60%-150% of the applicable range of flow for design point.
2. 0.0385 pipeline compressor model level of discharge coefficient according to claim 1, it is characterised in that：The flow system
The hub ratio ds/D2=0.40 of several 0.0385 pipeline compressor model levels, the ds are hub diameter, D2 is impeller outer
Footpath.
3. 0.0385 pipeline compressor model level of discharge coefficient according to claim 1, it is characterised in that：The impeller
(1) it is the 3 d impeller of enclosed, the basic parameter of 3 d impeller is as follows：
Impeller (1) outlet diameter D2=450mm, number of blade Z=17, impeller opposite outlet widthb2For impeller outlet
Width, the impeller are respectively 8.2 ° and 18 ° near wheel cap and wheel disc lateral lobe piece stagger angle β 1As and β 1Ah, and impeller is near wheel
Exit vane angle beta 2As and β 2Ah of lid and wheel disc side is 38 °.
4. 0.0385 pipeline compressor model level of discharge coefficient according to claim 1, it is characterised in that：Impeller (1)
Wheel cap side and the meridional channel of reel side formed by two sections of circular arcs are tangent respectively, and two sections of circular arcs each are tangent with two straight lines
Section；The meridian molded line of the wheel cap and reel side without piece diffuser (2) is constituted by one section of straight line；The meridian of the reel side
Molded line is perpendicular to axial direction.
5. 0.0385 pipeline compressor model level of discharge coefficient according to claim 1, it is characterised in that：Described without piece diffusion
The ratio b3/b2 of device (2) entrance width and impeller (1) exit width is 1, while vane diffuser (2) exit width and blade expand
The ratio b4/b3 of depressor (2) entrance width is about 0.917, described：B2 is impeller outlet width, and b3 is diffuser intake width, b4
For diffuser exit width.
6. 0.0385 pipeline compressor model level of discharge coefficient according to claim 1, it is characterised in that：Described without piece expand
Depressor (2) entrance relative positionOutlet relative positionThe D2 is impeller diameter, and D3 is diffuser
The diameter of entrance location, diameters of the D4 for diffuser exit position.
7. 0.0385 pipeline compressor model level of discharge coefficient according to claim 1, it is characterised in that：The bend
(3) import and export width ratio b5/b4For 1.194, the b5 is bend exit width.
8. 0.0385 pipeline compressor model level of discharge coefficient according to claim 1, it is characterised in that：The return channel
(4) blade adopts overall height banana airfoil fan, and the number of blade is Z=24, blade inlet relative position D5/D2=1.581, entrance is pacified
Dress angle is 18 °, blade exit relative position D6/D2=0.72, exit installation angle is 98.63 °, and the D5 enters for return channel blade
The diameter of mouth position, diameters of the D4 for return channel blade exit position.
9. 0.0385 pipeline compressor model level of discharge coefficient according to claim 1, it is characterised in that：The return channel
(4) meridian molded line in wheel cap side is a vertical straight line section, tangent with bend wheel cap side circular arc；Reel side meridian molded line is an oblique line
Section, tangent with bend reel side circular arc；Return channel outlet section shrouding disc side and reel side are respectively by two circular arcs and tangent with circular arc
Straightway composition.
10. described in a kind of design any one of claim 1-9 in 0.0385 pipeline compressor model level of discharge coefficient impeller side
Method, it is characterised in that include：
By one-dimensional thermal-design, obtain impeller inlet and angle beta is installed1A, impeller outlet install angle beta2A, and impeller outlet width
b2；
Hub diameter is determined according to hub ratio ds/D2 and given impeller diameter；
By import relative velocity w1Minimum principle calculates impeller inlet diameter D0；
The preliminary moulding of blade is obtained according to the linear change profile in Beta angles for importing and exporting blade；
The runner threedimensional model of obtained impeller is carried out stress and strain model；
The grid for generating is imported in CFD analysis softwares, 3D is carried out to the impeller using Spalart-Allmaras turbulence models
Viscous flow analysis；The inlet boundary condition of analysis is stagnation temperature, stagnation pressure, and the export boundary condition of analysis is mass flow outlet；
The blade flow field result that CFD analyzes gained is analyzed, when blade flow field does not meet design requirement, then impeller is adjusted
Meridian and the coupling of vane type line, by changing iterating for the distribution of blade beta angles, meridian molded line and CFD analyses, finally
So that the blade flow field of gained meets design requirement；The design requirement includes impeller on the high section of leaf, and impeller is in runner
Between flowing without flow separation；Without flow separation on the meridional channel of impeller；The outlet flow angle of impeller is evenly distributed；Outlet is quiet
Pressure is evenly distributed；The relative velocity of the blade of pressure face and suction surface is approximately distributed in olive-type.
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| CN201611065210.4A CN106499668A (en) | 2016-11-28 | 2016-11-28 | 0.0385 pipeline compressor model level of discharge coefficient and method for designing impeller |
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2016
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| 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 |
| CN104343725A (en) * | 2013-07-23 | 2015-02-11 | 沈阳透平机械股份有限公司 | MCL compressor model level and design method thereof |
| CN105090123A (en) * | 2015-08-25 | 2015-11-25 | 浙江理工大学 | Centrifugal compressor model |
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Application publication date: 20170315 |