CN107152413A - A kind of low pulse centrifugal impeller of combined type - Google Patents
A kind of low pulse centrifugal impeller of combined type Download PDFInfo
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- CN107152413A CN107152413A CN201710515648.6A CN201710515648A CN107152413A CN 107152413 A CN107152413 A CN 107152413A CN 201710515648 A CN201710515648 A CN 201710515648A CN 107152413 A CN107152413 A CN 107152413A
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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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2205—Conventional flow pattern
- F04D29/2222—Construction and assembly
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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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/24—Vanes
- F04D29/242—Geometry, shape
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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
- F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a kind of low pulse centrifugal impeller of combined type, including front shroud of impeller, back shroud of impeller, inner ring blade and outer ring blade, the quantity of the outer ring blade is more than the quantity of the inner ring blade；The low pulse centrifugal impeller of the combined type of the present invention is by being radially arranged the blade of varying number, and the number of blade especially set in outer ring is more than the number of blade of inner ring, meets the demand of higher efficiency, more excellent vibration and noiseproof feature.
Description
Technical field
The present invention relates to low pulse centrifugal impeller technical field, and in particular to a kind of low pulse centrifugal impeller of combined type.
Background technology
Centrifugal impeller makes fluid formation centrifugal motion get rid of to impeller outer edge acquisition kinetic energy by impeller rotation.Due to impeller leaf
Piece be fluid in finite number, rotary blade because inertia presence can form the axial vortex opposite with impeller direction of rotation,
This axial vortex exists in interlobate region.The actual mobility status of fluid can approximately regard this axial direction as in impeller
The superposition of vortex and the through-flow for flowing through static impeller.The effect of above-mentioned superposition result in that vacuum side of blade relative velocity is larger, blade
Working face relative velocity is smaller, so as to produce impeller outlet velocity-slip, i.e., in interlobate space at impeller outlet
The size and Orientation of absolute velocity all there occurs certain change.The sliding of above-mentioned muzzle velocity brings two adverse effects,
One is to cause the reduction of impeller head coefficient, reaches that same lift needs bigger impeller outer diameter, so as to bring more frictions to damage
Lose；Two be to cause the fluid velocity skewness at impeller outlet on circumferencial direction.Leaf is frequently and its frequency multiplication composition is centrifugal pump
The major frequency components of pressure fluctuation, it is mainly produced by the stator-rotor interaction of blade and spiral case/stator.Impeller outlet axially flows
The inhomogeneities of speed can aggravate stator-rotor interaction effect again, so as to aggravate vibration and the noise of centrifugal pump.
In order to solve the above problems, there is researcher to propose some improving countermeasures, such as Authorization Notice No. is
CN205089683U patent document discloses a kind of impeller, including upper cover plate, blade and lower cover, and blade is arranged at lid
Between plate and lower cover, upper cover plate includes upper and lower surface, and blade shapes with upper cover plate integrated injection molding, and blade is located at upper lid
The lower surface of plate, blade includes linear leaf and short blade, and linear leaf and short blade include one section of circular arc or multi-section circular arc
Combination or the combination of multi-section circular arc and straight line, the arc length of linear leaf are more than the arc length of short blade, and linear leaf is along upper
Cover plate even circumferential is distributed, and short blade is distributed along upper cover plate even circumferential, and linear leaf is identical with the quantity of short blade, linear leaf and
Short blade is intervally arranged along the circumferencial direction of upper cover plate, and the structure improves the efficiency of low specific-speed centrifugal pump, but the design can not
Effectively alleviate the adverse effect that impeller outlet velocity-slip is brought, and the short blade method for arranging can bring extra friction to damage
Lose.
Therefore researcher proposes new technical scheme again, such as Authorization Notice No. is literary for CN205117796U patent
Offer and disclose a kind of low specific-speed centrifugal pump impeller, keeping setting in vacuum side of blade in the case that front side of vane molded line is constant
One thickens cushion block, and making vane thickness, direction is gradually thickening from the inlet to the outlet.The utility model is blocked up by increasing vane thickness
Plug flow road, and by the equal width to expand impeller channel of spatial volume in impeller channel, it is ensured that volume that impeller needs and
Flow, even if exit blade pitgh reduces, and increases width, it is ensured that cross-sectional area is constant, so as to meet impeller rill
The high-lift performance of amount.The problem of impeller is present is in order to reach that enough lifts need bigger impeller outer diameter, so as to bring
More friction losses, and the impeller arrangement form will cause fluid uneven in the VELOCITY DISTRIBUTION of impeller outlet, so that plus
The vibration of acute pump, noise problem.
In another example application publication number, which is CN105889123A, discloses a kind of impeller of new construction low specific-speed centrifugal pump, its
The tandem cascade structure that blade is made up of front-seat blade and heel row blade, is conducive to improving the operational efficiency of pump.
Although the impeller is all provided with Internal and external cycle blade with the impeller described in the present invention in Leaf positional distribution pattern,
It is that the impeller has key difference in design philosophy and intention with the present invention, the impeller is intended to introduce tandem cascade structure to change
The flow field become in impeller is to improve the operational efficiency of pump.
The content of the invention
The invention provides a kind of low pulse centrifugal impeller of combined type, entrance is avoided while head coefficient is improved
Locate the too high adverse effect brought of excretion coefficient.
A kind of low pulse centrifugal impeller of combined type, including front shroud of impeller, back shroud of impeller, inner ring blade and outer ring
Blade, the quantity of the outer ring blade is more than the quantity of the inner ring blade.
The present invention is diametrically provided with inside and outside two circles blade, and inner ring uses the less number of blade, and outer ring is using more
The number of blade, the more outer ring number of blade is conducive to improving head coefficient, and less inner ring blade then avoids porch exclusion system
The too high adverse effect brought of number.Inner ring blade and outer ring blade use sweepback form.
It is preferred that, the length of the inner ring blade is more than outer ring blade.The outer ring blade quantity is more, chooses shorter
Outer ring length of blade can accomplish make full use of the outer ring blade quantity it is more can improve head coefficient, suppress Secondary Flow
Generation, while improve the advantage of vibration performance, it is to avoid blade excretion coefficient too high shortcoming.
It is preferred that, the quantity of the inner ring blade is 3~7.The purpose done work to working media can be realized, can also be had
Effect avoids blade excretion coefficient too high, improves cavitation performance.It is further preferred that the quantity of the inner ring blade is 3~5.
It is further preferred that the quantity of the inner ring blade is 5~7.The less inner ring blade quantity can be controlled further
Blade excretion coefficient, improves cavitation performance；The appropriate more inner ring blade quantity can improve the inner ring blade lift
Coefficient, so as to reduce impeller outer diameter.
It is preferred that, the ratio of the quantity of the outer ring blade and the quantity of the inner ring blade is a, 1 ＜ a ＜ 5.More
Outer ring blade quantity can effectively improve head coefficient, suppress Secondary Flow generation, improve vibration performance；The less inner ring number of blade
Amount can effectively control excretion coefficient, reduce inlet flow rate, improve cavitation performance.
It is preferred that, the internal diameter of the inner ring blade is D1, and the external diameter of the inner ring blade is D2, the outer ring blade it is interior
Footpath is D3, and the external diameter of the outer ring blade is D4, D3：D2=0.9~1.3, D4：D2=1.2~1.8.
The blade includes the blade inlet edge of relatively close impeller central and is relatively distant from the blade trailing edge of impeller central, leaf
The distance of piece leading edge to impeller central is referred to as the internal diameter of blade, and the trailing edge of blade is referred to as the outer of blade to the distance of impeller central
Footpath.
In order to optimize the hydraulic performance of centrifugal pump, improve the vibration noise performance of centrifugal pump, improve operational efficiency, preferably
, the working face angle of outlet of the inner ring blade is β 1, and the back side angle of outlet is β 2；The working face inlet angle of the outer ring blade is
β 3, back side inlet angle is β 4；The working face angle of outlet of the outer ring blade is β 5, and the back side angle of outlet is β 6；
β 1=15 °~45 °, β 6=15 °~45 °, | β 2- β 1 | 10 ° of ＜, | β 3- β 1 | 10 ° of ＜, | β 4- β 3 | 10 ° of ＜.Enter one
Walk preferably, β 1=15 °~30 °, β 6=15 °~30 °, | β 2- β 1 | 5 ° of ＜, | β 3- β 1 | 5 ° of ＜, | β 4- β 3 | 5 ° of ＜.Further
It is preferred that, β 1=30 °~45 °, β 6=30 °~45 °, | β 2- β 1 | 5 ° of ＜, | β 3- β 1 | 5 ° of ＜, | β 4- β 3 | 5 ° of ＜.
The blade angle of front side of vane is the angle of blade convex surface tangent line and circumferencial direction, the leaf of vacuum side of blade
Piece laying angle is that the blade angle at the angle of forward face surface tangent and circumferencial direction, internal diameter blade is blade inlet
Blade angle at angle, outer blade diameter is outlet blade angle.
In order to further reduce vibration, efficiency is improved, it is preferred that preferred, the inner ring vane thickness becomes along its molded line
Change, interior thickness is maximum, interior thickness is 2~6 times of two-end thickness, and the ＜ β 2 of β 1.Outer ring blade selects Varying-thickness leaf simultaneously
Piece, makes the front side of vane angle of outlet be less than the back side angle of outlet, to increase front side of vane relative velocity, reduces vacuum side of blade relative
Speed, so as to allow impeller outlet VELOCITY DISTRIBUTION is more uniform effectively to reduce centrifugal pump body vibration, the efficiency of raising centrifugal pump.
It is preferred that, it is characterised in that n times of the quantity of the outer ring blade and the inner ring blade quantity, n is integer.n
The periodicity of impeller Leaf distribution can be embodied for integral multiple, is that further differentiation is set so as to simplify blade arrangement
The circumferencial direction distribution of the outer ring blade and the blade angle of the outer ring blade provide feasibility and convenience.
In order to optimize the hydraulic performance of centrifugal pump, improve the vibration noise performance of centrifugal pump, improve operational efficiency, preferably
, it is preferred that described outer ring blade is divided into n groups, every group in order, from first on the linear leaf sweepback direction
The outer ring blade starting terminates to the last a piece of outer ring blade of the group, and the β 3 of each outer ring blade is sequentially reduced.
The last a piece of common n of blade of the group is arrived in first outer ring blade starting on the sweepback direction of the inner ring blade
Outer ring blade described in piece be one group, to should the inner ring blade, above-mentioned n be the outer ring blade quantity for the inner ring leaf
The multiple of piece quantity.
In order to optimize the hydraulic performance of centrifugal pump, improve the vibration noise performance of centrifugal pump, improve operational efficiency, preferably
, the working face leading edge of the working face leading edge and the line in axle center of any outer ring blade and the outer ring blade at the outer ring blade rear
The angle constituted with the line in axle center is α；
Described outer ring blade is divided into n groups, every group in order, from first institute on the linear leaf sweepback direction
State outer ring blade starting to the last a piece of outer ring blade of the group to terminate, the α between each outer ring blade is sequentially reduced.
Beneficial effects of the present invention：
The low pulse centrifugal impeller of the combined type of the present invention is by being radially arranged the blade of varying number, especially outside
The number of blade that circle is set is more than the number of blade of inner ring, meets the demand of higher efficiency, more excellent vibration and noiseproof feature.
Brief description of the drawings
Fig. 1 is structure of the low pulse centrifugal impeller of the combined type of embodiment 1 after front shroud and the back shroud are concealed
Schematic diagram.
Fig. 2 is the structural representation of the low pulse centrifugal impeller of the combined type of embodiment 1.
Fig. 3 is structure of the low pulse centrifugal impeller of the combined type of embodiment 2 after front shroud and the back shroud are concealed
Schematic diagram.
Fig. 4 is structure of the low pulse centrifugal impeller of the combined type of embodiment 3 after front shroud and the back shroud are concealed
Schematic diagram.
Fig. 5 is the structural representation of the low pulse centrifugal impeller of prior art.
Fig. 6 is the structural representation of the low pulse centrifugal impeller (coordinating with flow channel type guide blade) of embodiment 1.
Fig. 7 is the radial load pulsation amplitude frequency spectrum figure of embodiment 1.
Fig. 8 is the radial load pulsation amplitude frequency spectrum figure of the measurement point of the low pulse centrifugal pump of prior art.
Embodiment
Embodiment 1
As illustrated in fig. 1 and 2, the low pulse centrifugal impeller inner ring of the combined type of the present embodiment is made up of 5 linear leafs 1, outside
Circle is made up of 15 short blades 2.The length of linear leaf 1 is more than the length of short blade 2, and linear leaf 1 and short blade 2 are sweepback form.
The uniform arrangement in a circumferential direction between front shroud 3 and back shroud 4 of linear leaf 1, short blade is in front shroud 3 with after
Uniform arrangement in a circumferential direction between cover plate 4.The linear leaf leading edge of linear leaf 1 including relatively close impeller central and relatively remote
From the linear leaf trailing edge of impeller central, short blade 2 includes the short blade leading edge of relatively close impeller central and is relatively distant from impeller
The short blade trailing edge at center.The trailing edge of linear leaf 1 is referred to as to the distance of impeller central before the outer diameter D 2 of linear leaf, short blade 2
Edge is referred to as the internal diameter D3 of short blade to the distance of impeller central, and the trailing edge of short blade 2 is referred to as short blade to the distance of impeller central
Outer diameter D 4.
In the present embodiment：D3：D2=1.0065, D4：D2=1.4706.
The blade angle of front side of vane is the angle of blade convex surface tangent line and circumferencial direction, the leaf of vacuum side of blade
Piece laying angle is that the blade angle at the angle of forward face surface tangent and circumferencial direction, internal diameter blade is blade inlet
Blade angle at angle, outer blade diameter is outlet blade angle.
The working face angle of outlet of linear leaf 1 is β 1, and the back side angle of outlet is β 2；The working face inlet angle of short blade 2 is β 3, the back of the body
Face inlet angle is β 4；The working face angle of outlet of short blade 2 is β 5, and the back side angle of outlet is β 6.
In the present embodiment：β 1 is 26.4 °, and β 2 is 27.1 °, and β 3 is 37.7 °, and β 4 is 24.2 °, and β 5 is 16.4 °, and β 6 is
40.8°。
The thickness of short blade 2 changes along its molded line, and thickness is maximum in the middle, and interior thickness is the 2~6 of two-end thickness
Times.
Embodiment 2
As shown in figure 3, the present embodiment is different from the Varying-thickness short blade 2 of outer ring in embodiment 1, the outer ring of the present embodiment is short
Blade equal thickness short blade, the blade angle and back side laying angle of the working face of uniform thickness short blade is equal in magnitude；With implementation
The blade angle of short blade 2 is consistent different in example 1, and the short blade 2 in the present embodiment can set according to specific laying angle and advise
Rule sets blade angle, and remaining structure is same as Example 1.
Outer ring described in first short blade 2 starting to the last a piece of common n pieces of blade of the group on the sweepback direction of linear leaf 1
Blade be one group, to should linear leaf 1, above-mentioned n be the quantity of short blade 2 for the quantity of linear leaf 1 multiple.
The quantity of short blade 2 is 3 times of the quantity of linear leaf 1 in the present embodiment, short blade 201, short blade marked in figure
202nd, short blade 203 correspond to same linear leaf 1 according to above-mentioned packet and consistent relationship, and other 12 short blades are by other 4
Individual linear leaf is with above-mentioned packet and consistent relationship correspondence.The length of linear leaf 1 is more than the length of short blade 2, linear leaf 1 and short blade 2
It is sweepback form.
Linear leaf 1 includes the linear leaf leading edge of relatively close impeller central and is relatively distant from the run-out that comes into leaves of impeller central
Edge, short blade 2 includes the short blade leading edge of relatively close impeller central and is relatively distant from the short blade trailing edge of impeller central.Come into leaves
The trailing edge of piece 1 is referred to as to the distance of impeller central before the outer diameter D 2 of linear leaf, short blade 201, short blade 202, short blade 203
The internal diameter that edge is referred to as short blade to the distance of impeller central is respectively D3a, D3b, D3c, and the trailing edge of short blade 2 arrives impeller central
The outer diameter D 4 of distance referred to as short blade.Short blade 201, short blade 202, internal diameter D3a, D3b, D3c of short blade 203 are respectively length
Outer blade diameter 1.0065,1.0065,1.0065 times.The outer diameter D 4 of short blade is 1.4706 times of linear leaf external diameter.
The blade angle of front side of vane is the angle of blade convex surface tangent line and circumferencial direction, the leaf of vacuum side of blade
Piece laying angle is that the blade angle at the angle of forward face surface tangent and circumferencial direction, internal diameter blade is blade inlet
Blade angle at angle, outer blade diameter is outlet blade angle.
The working face angle of outlet of linear leaf 1 is β 1, and the back side angle of outlet is β 2；Short blade 201, short blade 202, short blade
203 working face inlet angle is respectively β 3a, β 3b, β 3c, and back side inlet angle is respectively β 4a, β 4b, β 4c；Short blade 201, short leaf
Piece 202, the working face angle of outlet of short blade 203 are respectively β 5a, β 5b, β 5c, and the back side angle of outlet is respectively β 6a, β 6b, β 6c.
β 1 size is 26.4 °, and β 2 size is 27.1 °, and β 3a size is 41.6 °, and β 3b size is 34.9 °, β 3c
Size be 24.4 °, β 6a size is 45.1 °, β 6b size is 37.5 °, β 6c size is 36.4 °.The thickness of short blade
Uniformly, it is equal with the blade angle of working face on Radius and the back side.
Embodiment 3
As shown in figure 4, the present embodiment is with outer ring Varying-thickness short blade 2 in Examples 1 and 2, circumferentially uniform array is distributed
The position of the short blade 2 of outer ring Varying-thickness in difference, the present embodiment in a circumferential direction is circumferentially arranged rule distribution with specific
And using the number of linear leaf as number of iterations；It is consistent different from the blade angle of Varying-thickness short blade in outer ring in embodiment 1,
The short blade 2 of outer ring Varying-thickness in the present embodiment sets rule to set blade angle according to specific laying angle.
In the present embodiment, the quantity of short blade 2 is three times of the quantity of linear leaf 1, short blade 201, short leaf marked in figure
Piece 202, short blade 203 correspond to same linear leaf 1, and other 12 short blades are by other 4 linear leafs with identical rule pair
Should.The length of linear leaf 1 is more than the length of short blade 2, and linear leaf 1 and short blade 2 are sweepback form.Linear leaf 1 includes relative lean on
The linear leaf leading edge of nearly impeller central and the linear leaf trailing edge for being relatively distant from impeller central, short blade 2 include relatively close impeller
The short blade leading edge at center and the short blade trailing edge for being relatively distant from impeller central.
The trailing edge of linear leaf is referred to as the outer diameter D 2 of linear leaf to the distance of impeller central, short blade 201, short blade 202, short
The internal diameter that the distance of the leading edge of blade 203 to impeller central is referred to as short blade is respectively D3a, D3b, D3c, and the trailing edge of short blade is arrived
The distance of impeller central is referred to as the outer diameter D 4 of short blade.Short blade 201, short blade 202, the internal diameter D3a of short blade 203, D3b,
D3c be respectively linear leaf external diameter 1.0065,1.0065,1.0065 times.1.4706 times of the bit length blade of outer diameter D 4 of short blade.
Short blade 202 is considered as position by the back side of the short blade 201 in figure herein towards the working face of short blade in figure 202
In short blade a rear.Short blade 203 is located at the rear of short blade 202 in figure.By that analogy, by the short of the rear of short blade 203
Blade is referred to as short blade 204, short blade 205 etc. successively.The working face leading edge of short blade 201 and the line and short blade in axle center
The angle that the working face leading edge of the short blade 202 at 201 rears and the line in axle center are constituted is angle 1.Before the working face of short blade 202
The folder that the working face leading edge of the short blade 203 of the line and the rear of outer ring short blade 202 in edge and axle center and the line in axle center are constituted
Angle is angle 2, by that analogy, defines angle 3, angle 4 etc..Each 3 short blades are one group, are divided into 5 groups and correspond to a linear leaf respectively
1, short blade 201, short blade 202, short blade 203 are one group, and short blade 204, short blade 205, short blade 206 are one group.With
This analogizes.In the group where short blade 201, short blade 202, short blade 203, angle 1, angle 2, the size rule at angle 3 are angle 1>
Angle 2>Angle 3, in the group where short blade 204, short blade 205, short blade 206, angle 4, angle 5, the size rule at angle 6 are angle 4>
Angle 5>Angle 6.Wherein angle 1 is 27.0 °, and angle 2 is 24.9 °, and angle 3 is 20.1 °.
The blade angle of front side of vane is the angle of blade convex surface tangent line and circumferencial direction, the leaf of vacuum side of blade
Piece laying angle is that the blade angle at the angle of forward face surface tangent and circumferencial direction, internal diameter blade is blade inlet
Blade angle at angle, outer blade diameter is outlet blade angle.The working face angle of outlet of linear leaf is β 1, and the back side angle of outlet is β
2；Short blade 201, short blade 202, the working face inlet angle of short blade 203 are respectively β 3a, β 3b, β 3c, back side inlet angle difference
For β 4a, β 4b, β 4c；Short blade 201, short blade 202, the working face angle of outlet of short blade 203 are respectively β 5a, β 5b, β 5c, the back of the body
The face angle of outlet is respectively β 6a, β 6b, β 6c.β 1 size is 26.4 °, and β 2 size is 27.1 °, and β 3a size is 37.8 °, β
3b size is 35.1 °, and β 3c size is 32.8 °, and β 4a size is 24.1 °, and β 4b size is 22.1 °, β 4c size
For 20.1 °, β 6a size is 40.8 °, and β 6b size is 38.8 °, and β 6c size is 36.8 °, and β 5a size is 16.1 °, β
5b size is 14.1 °, and β 5c size is 12.1 °.The thickness of short blade changes along its molded line, and thickness is larger in the middle, in
Portion's thickness is 2 to 6 times of two-end thickness.
Comparative example
Fig. 5 is the assembling schematic diagram of conventional centrifugal impeller and flow channel type guide blade.Fig. 6 is the impeller and flow channel type of embodiment 1
The assembling schematic diagram of stator.Flow channel type guide blade 3 is set for three runners, is arranged in impeller outer ring.
Fig. 5 and Fig. 6 flow channel type guide blade structural parameters all same.The meridian plane of conventional impeller and the impeller of embodiment 1 is joined
Number is consistent, and conventional impeller outer diameter is equal to the position of the measurement point 4 in the impeller short blade external diameter of the embodiment 1, Fig. 5 and Fig. 6
Put in same radial location.
Impeller and conventional centrifugal impeller to embodiment 1 carry out numerical simulation respectively, obtain radial load microseismic data, numerical value
The rotating speed of the impeller of embodiment 1 and conventional centrifugal impeller is 3000 turns per minute in simulation.
Fig. 7 is the radial load pulsation amplitude frequency spectrum figure of embodiment 1, and Fig. 8 is the radial direction of the measurement point of conventional centrifugal impeller
Power pulsation amplitude frequency spectrum figure.Fig. 7 and Fig. 8 contrast the impeller of visible embodiment 1 radial load pulsation amplitude be significantly less than it is conventional from
Lobus cardiacus wheel radial load pulsation amplitude, and the impeller of embodiment 1 radial load pulsation amplitude be distributed on frequency domain it is more uniform.By
This contrast is visible, and the impeller of embodiment 1 substantially can control radial load to pulse, and reaches the effect for reducing bladed disk vibration.
Claims (10)
1. a kind of low pulse centrifugal impeller of combined type, including front shroud of impeller, back shroud of impeller, inner ring blade and outer ring leaf
Piece, it is characterised in that the quantity of the outer ring blade is more than the quantity of the inner ring blade.
2. the low pulse centrifugal impeller of combined type as claimed in claim 1, it is characterised in that the length of the inner ring blade is big
In outer ring blade.
3. the low pulse centrifugal impeller of combined type as claimed in claim 1 or 2, it is characterised in that the number of the inner ring blade
Measure as 3~7.
4. the low pulse centrifugal impeller of combined type as claimed in claim 1 or 2, it is characterised in that the number of the outer ring blade
The ratio of amount and the quantity of the inner ring blade is a, 1 ＜ a ＜ 5.
5. the low pulse centrifugal impeller of combined type as claimed in claim 1 or 2, it is characterised in that the inner ring blade it is interior
Footpath is D1, and the external diameter of the inner ring blade is D2, and the internal diameter of the outer ring blade is D3, and the external diameter of the outer ring blade is D4,
D3：D2=0.9~1.3, D4：D2=1.2~1.8.
6. the low pulse centrifugal impeller of combined type as claimed in claim 1 or 2, it is characterised in that the work of the inner ring blade
Make the face angle of outlet for β 1, the back side angle of outlet is β 2；The working face inlet angle of the outer ring blade is β 3, and back side inlet angle is β 4；
The working face angle of outlet of the outer ring blade is β 5, and the back side angle of outlet is β 6；
β 1=15 °~45 °, β 6=15 °~45 °, | β 2- β 1 | 10 ° of ＜, | β 3- β 1 | 10 ° of ＜, | β 4- β 3 | 10 ° of ＜.
7. the low pulse centrifugal impeller of combined type as claimed in claim 6, it is characterised in that the outer ring vane thickness along its
Molded line changes, and interior thickness is maximum, and interior thickness is 2~6 times of two-end thickness, and the ＜ β 2 of β 1.
8. the low pulse centrifugal impeller of combined type as claimed in claim 1 or 2, it is characterised in that the number of the outer ring blade
N times of amount and the inner ring blade quantity, n is integer.
9. the low pulse centrifugal impeller of combined type as claimed in claim 8, it is characterised in that described outer ring blade is in order
Be divided into n groups, every group, from the linear leaf sweepback direction first outer ring blade starting it is finally a piece of to the group
The outer ring blade terminates, and the β 3 of each outer ring blade is sequentially reduced.
10. the low pulse centrifugal impeller of combined type as claimed in claim 8, it is characterised in that the work of any outer ring blade
The folder that the line of the working face leading edge and axle center of edge and the line in axle center and the outer ring blade at the outer ring blade rear is constituted in front
Angle is α；
Described outer ring blade is divided into n groups, every group in order, from the linear leaf sweepback direction first it is described outer
The starting of circle blade terminates to the last a piece of outer ring blade of the group, and the α between each outer ring blade is sequentially reduced.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710515648.6A CN107152413B (en) | 2017-06-29 | 2017-06-29 | A kind of low pulse centrifugal impeller of combined type |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710515648.6A CN107152413B (en) | 2017-06-29 | 2017-06-29 | A kind of low pulse centrifugal impeller of combined type |
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| Publication Number | Publication Date |
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| CN107152413A true CN107152413A (en) | 2017-09-12 |
| CN107152413B CN107152413B (en) | 2019-10-15 |
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| CN201710515648.6A Active CN107152413B (en) | 2017-06-29 | 2017-06-29 | A kind of low pulse centrifugal impeller of combined type |
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|---|---|
| CN (1) | CN107152413B (en) |
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| CN111054231A (en) * | 2020-01-07 | 2020-04-24 | 上海远安流体设备科技有限公司 | Impeller, emulsification pump and emulsification system |
| CN111911414A (en) * | 2019-05-07 | 2020-11-10 | 马勒国际有限公司 | Fluid pump |
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| CN1113551A (en) * | 1995-06-02 | 1995-12-20 | 北京矿冶研究总院 | Centrifugal pulp pump impeller |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111911414A (en) * | 2019-05-07 | 2020-11-10 | 马勒国际有限公司 | Fluid pump |
| CN111054231A (en) * | 2020-01-07 | 2020-04-24 | 上海远安流体设备科技有限公司 | Impeller, emulsification pump and emulsification system |
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| CN107152413B (en) | 2019-10-15 |
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