CN109083864A - A kind of radial-flow type rotating machinery impeller - Google Patents
A kind of radial-flow type rotating machinery impeller Download PDFInfo
- Publication number
- CN109083864A CN109083864A CN201810840483.4A CN201810840483A CN109083864A CN 109083864 A CN109083864 A CN 109083864A CN 201810840483 A CN201810840483 A CN 201810840483A CN 109083864 A CN109083864 A CN 109083864A
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- China
- Prior art keywords
- impeller
- primary blades
- blade
- radius
- impeller bodies
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- 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
- F04D29/2216—Shape, geometry
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
- F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
- F01D5/048—Form or construction
-
- 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
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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 radial-flow type rotating machinery impeller, including impeller bodies, the impeller bodies back side is equipped with multiple primary blades and multiple edging blades, and primary blades are evenly distributed on the back side of impeller bodies, primary blades protrusion setting along the circumferencial direction of impeller bodies；Edging blade is evenly distributed in the circumferential direction between the inducer of adjacent primary blade, edging blade protrusion setting.The present invention, significantly increase the solidity of blades of impeller bodies back radius large area, the increase of radius smaller area solidity of blades is avoided simultaneously, so that circumferential speed increases sharply after leak fluid enters impeller bodies back gap, leak fluid circumferential speed reduces with radius and is further increased under the drive of impeller bodies back blade, pressure reduction simultaneously, the reduction of radius large area Fluid pressure is more conducive to reduce impeller bodies back axial force, to balance impeller bodies axial force.
Description
Technical field
The present invention relates to radial-flow type rotating machinery impeller technical fields, and in particular to a kind of radial-flow type rotating machinery impeller.
Background technique
Radial-flow type rotating machinery is widely used in each neck of national product since volume compact, Study on Variable Condition Features are excellent
Domain, such as the centrifugal compressor and radial-inward-flow turbine of the centrifugal pump of petrochemical industry, the turbocharger of automobile industry, aircraft industry.Its
The fluid axial thrust that impeller back is born in operational process is typically larger than impeller leading faces, when rotating machinery operating pressure is higher
Impeller bears the biggish axial force for being directed toward impeller leading faces, may exceed the bearing capacity of thrust bearing, need to set on impeller
It counts some special structures such as balance hole, back blade etc. and carrys out balancing axial thrust.
The radial-flow type rotating machinery back blade structure being widely used at present is usually by a plurality of phases being evenly arranged
With the wheel back blade of blade composition, accelerated by blade band driving wheel back gap leak fluid, to reduce wheel back Fluid pressure, is subtracted
The axial force that small impeller is born.The circumferential spacing for being essentially characterized by camber line in adjacent blades of existing back vane structure is with half
Diameter increases and increases, this arrangement makes in the larger higher region of i.e. impeller linear velocity of radius, and back blade is between wheel back
The acceleration and pressure decrease effect of gap leak fluid is poor, and this region close to leakage stream import and area it is larger, to weaken whole
The fluid-pressure drop amplitude and axial force balance effect of a wheel back gap.As shown in Figure 1, the segment fluid flow in 2 outlet chamber 6 of impeller
Generate small amount of leakage by gap between 2 back of impeller and shell 1, leakage paths are successively are as follows: 2 back of impeller and shell 1 it
Between radial clearance 7, the axial gap 8 between 2 back of impeller and shell 1, the dynamic and static gaps 9 of 5 structure of dynamic sealing.Usual impeller
Back side leak fluid pressure is higher than front mainstream fluid, so that impeller bears to be directed toward positive axial force, when operating pressure is higher
When axial force it is larger.
In order to improve axial force balance effect, existing back vane structure needs to let out using biggish back blade height to improve
Leakage current pressure drop, as shown in Fig. 2 of the Figure of description of present patent application, the impeller back blade typical case applied in the prior art is several
What moulding: in the identical plurality of vanes 11 of 10 back side of impeller moulding evenly distributed in the circumferential direction, blade 11 and impeller 10 are carried on the back
Face is vertical, and any 11 outer end radius of blade is identical, inner end radius is identical, and 11 center line of blade is straight line radially in figure,
There is example center line and radial at an angle or for curve, bending direction is related with 10 direction of rotation 12 of impeller.Its geometry is special
Sign is that the circumferential spacing of camber line in adjacent blades increases as radius increases, and the biggish outer end circumferential direction spacing 13 of radius is obvious big
In the lesser inner end circumferential direction spacing 14 of radius.Leak fluid enters the impeller back gap Later Zhou Dynasty, one of the Five Dynasties to directional velocity and wheel rotation side
To identical, circumferential speed size is much smaller than wheel rotation linear velocity, the leak fluid circumferential speed under the drive of back blade
Reduce with radius and increase, while pressure reduction, since blade outer end spacing is larger, vane inlet region adds leak fluid
Fast antihypertensive effect is poor, needs to make up by increasing blade height, and then causes impeller power loss to increase, efficiency reduction.
In view of this, being badly in need of improving the structure of existing radial-flow type rotating machinery impeller, to reduce the function of impeller
Rate loss, improves fluid-pressure drop amplitude.
Summary of the invention
The technical problem to be solved by the present invention is to the axial force balance structures of existing radial-flow type rotating machinery impeller to deposit
In the high problem of power loss.
In order to solve the above-mentioned technical problem, the technical scheme adopted by the invention is that providing a kind of radial-flow type rotating machinery leaf
Wheel, including impeller bodies, the impeller bodies are equipped with:
Primary blades are multiple, and the back side of the impeller bodies is evenly distributed on along the circumferencial direction of the impeller bodies,
The primary blades protrusion setting；
Edging blade is multiple, evenly distributed in the circumferential direction between the inducer of the adjacent primary blades, the side
The protrusion setting of edge blade.
In another preferred embodiment, the outer end radius of each primary blades is identical, the inner end of each primary blades
Radius is identical, and the outer end radius of each edging blade is identical as the outer end radius of each primary blades, each edging blade
Inner end radius it is identical.
In another preferred embodiment, the middle camber line circumferential direction spacing of the adjacent edging blade is olo, with
The adjacent primary blades are equal with camber line circumferential direction spacing in the edging blade, arc in the inner end of the two adjacent primary blades
The circumferential spacing of line is interior spacing, and the olo is less than the interior spacing.
In another preferred embodiment, the primary blades are arc, and outlet section transition is to impeller direction of rotation
Bending.
In another preferred embodiment, the protrusion direction of the primary blades and the edging blade and the impeller master
The back side of body is vertical or has angle.
In another preferred embodiment, the edging blade quantity is the integral multiple of the primary blades.
Compared with prior art, of the invention, the solidity of blades of impeller bodies back radius large area is significantly increased, together
When avoid the increase of radius smaller area solidity of blades so that leak fluid enters circumferential speed behind the gap of impeller bodies back
It increases sharply, leak fluid circumferential speed reduces with radius and further increased under the drive of impeller bodies back blade, simultaneously
Pressure reduction；The solidity of blades for increasing radius large area by part can significantly increase back blade and leak fluid is driven to add
The effect of speed, further decreases the regional fluid pressure, since radius bigger region area in same radius change section is bigger,
The reduction of radius large area Fluid pressure is more conducive to reduce impeller bodies back axial force, to balance impeller bodies axial direction
Power.
Detailed description of the invention
Fig. 1 gives the radial flow impeller machinery sectional view that the present invention applies by taking centrifugal pump as an example；
Fig. 2 is the typical radial flow impeller rear elevation view of application wheel back blade in the prior art；
Fig. 3 is radial flow impeller rear elevation view of the invention；
Fig. 4 is impeller back tip leakage flow flow direction schematic diagram of the invention.
Specific embodiment
The present invention provides a kind of radial-flow type rotating machinery impellers, can be realized.With reference to the accompanying drawings of the specification and specifically
Embodiment is described in detail the present invention.
As shown in figure 3, radial-flow type rotating machinery impeller provided by the invention, including impeller bodies, including primary blades 3 and side
Edge blade 4.Primary blades 3 are multiple, and the back side of impeller bodies, primary blades 3 are evenly distributed on along the circumferencial direction of impeller bodies
Protrusion setting.Edging blade 4 is multiple, evenly distributed in the circumferential direction between the inducer of adjacent primary blade 3, edging blade
4 protrusion settings.There is the axial gap of very little between primary blades 3 and edging blade 4 and impeller back side fixed wall.
The present invention arranges primary blades 3 and edging blade 4 in impeller bodies back fixation, lets out for driving in the gap of back
Leakage current body accelerates, so that impeller bodies backside pressure is reduced, so that the axial force balance that impeller bodies are born is a smaller value.This
Invention compared with prior art, significantly increases the solidity of blades of impeller bodies back radius large area, while avoiding half
The increase of diameter smaller area solidity of blades, influence of this variation to impeller bodies back leakage flow are as follows: leak fluid into
It is identical as impeller bodies rotation direction to directional velocity to enter the impeller bodies back gap Later Zhou Dynasty, one of the Five Dynasties, circumferential speed size is much smaller than impeller
Body rotation linear velocity, leak fluid circumferential speed reduces with radius and is increased under the drive of impeller bodies back blade, simultaneously
Pressure reduction.The present invention increases the solidity of blades of radius large area by part, can significantly increase back blade and drive leakage
The effect that fluid accelerates, further decreases the regional fluid pressure；Due to the bigger area surface of same radius change section radius
Product is bigger, and the reduction of radius large area Fluid pressure is more conducive to reduce impeller bodies back axial force, to balance impeller
Main body axial force.
The biggish region back blade linear velocity of impeller back radius is larger, has to the acceleration and pressure decrease of leak fluid larger latent
Power, and the region area is larger, the pressure drop of leak fluid is larger to the contribution of balancing axial thrust, and the arrangement of edging blade 4 is kept away
Exempt from the increase of radius smaller area solidity of blades, which crosses conference and plays negative effect to axial thrust balancing,
It can more effectively drive leak fluid circumferential speed to increase, pressure reduction, be taken with smaller leaf height and lower power loss
Obtain the balance of axial force of impeller.
As shown in figure 4, the outer end radius of primary blades 3 is identical, the inner end radius of each primary blades 3 is identical, each edging blade 4
Outer end radius is identical as the outer end radius of each primary blades 3, and the inner end radius of each edging blade 4 is identical.In impeller outer edge, leakage stream
Circumferential speed direction is identical as wheel rotation direction when into impeller back gap, and circumferential speed size is much smaller than wheel rotation line
Speed, therefore opposite circumferential speed 18 is contrary with wheel rotation；As radius reduces, leakage stream is under the drive of back blade
Circumferential speed increases, and back blade linear velocity is gradually reduced, and the two speed difference reduces, and leakage stream is also gradually with respect to circumferential speed 18
Reduce, is all made of radial arrangement in this edges of regions blade 4 and primary blades 3, acceleration and pressure decrease of the arrangement to leakage stream
Effect is preferable.
The middle camber line circumferential direction spacing of adjacent edging blade 4 is olo 15, with adjacent primary blades 3 and edging blade 4
Middle camber line circumferential direction spacing is equal, and the circumferential spacing of camber line is interior spacing 17, and olo 15 in the inner end of two adjacent primary blades 3
Less than interior spacing 17.This structure breaches the limit that prior art back blade outer end circumferential direction spacing is naturally larger than inner end circumferential direction spacing
System, can dramatically increase the solidity of blades of radius large area, obtain impeller shaft with smaller leaf height and lower power loss
To the balance of power, rotating machine efficiency is improved.
As shown in figure 4, primary blades 3 are arc, and outlet section transition is to be bent to impeller direction of rotation 12.Passing through edge
Opposite circumferential speed is reversed at certain Radius after blade 4, becomes identical as wheel rotation direction, hereafter as radius reduces, lets out
Leakage current is gradually increased with respect to circumferential speed, is gradually to rotate to impeller from radial transition in the center line of this region primary blades 3
Direction 12 is bent, and to adapt to variation of the leakage stream with respect to circumferential speed, recovery section leakage flow energy while is further decreased
Fluid pressure.
The protrusion direction of primary blades 3 and edging blade 4 is vertical with the back side of impeller bodies or has angle, convenient for leakage
Fluid is oriented to, and included angle is related with leakage stream flow and Impeller Design revolving speed, should not be too large or too small.
4 quantity of edging blade is the integral multiple of primary blades 3, and this setup makes the number of primary blades 3 and edging blade 4
Amount is easier to be arranged, more convenient in processing.
The present invention significantly increases the solidity of blades of impeller bodies back radius large area, at the same avoid radius compared with
The increase of zonule solidity of blades, so that circumferential speed increases sharply after leak fluid enters impeller bodies back gap, in leaf
Leak fluid circumferential speed reduces with radius and is further increased under the drive of wheel body back blade, while pressure reduction；Pass through
Part increases the solidity of blades of radius large area, the effect that back blade drives leak fluid to accelerate can be significantly increased, into one
Step reduces the regional fluid pressure, since radius bigger region area in same radius change section is bigger, radius large area
The reduction of Fluid pressure is more conducive to reduce impeller bodies back axial force, to balance impeller bodies axial force.
The invention is not limited to above-mentioned preferred forms, and anyone should learn that is made under the inspiration of the present invention
Structure change, the technical schemes that are same or similar to the present invention are fallen within the scope of protection of the present invention.
Claims (6)
1. a kind of radial-flow type rotating machinery impeller, which is characterized in that including impeller bodies, the impeller bodies back side is equipped with:
Primary blades are multiple, and the back side of the impeller bodies is evenly distributed on along the circumferencial direction of the impeller bodies, described
Primary blades protrusion setting；
Edging blade is multiple, evenly distributed in the circumferential direction between the inducer of the adjacent primary blades, the marginal convolution
Piece protrusion setting.
2. radial-flow type rotating machinery impeller according to claim 1, which is characterized in that the outer end radius of each primary blades
Identical, the inner end radius of each primary blades is identical, the outer end of the outer end radius of each edging blade and each primary blades
Radius is identical, and the inner end radius of each edging blade is identical.
3. radial-flow type rotating machinery impeller according to claim 1, which is characterized in that in the adjacent edging blade
Camber line circumferential direction spacing is olo, two-phase equal with camber line circumferential direction spacing in the edging blade with the adjacent primary blades
The circumferential spacing of camber line is interior spacing in the inner end of the adjacent primary blades, and the olo is less than the interior spacing.
4. radial-flow type rotating machinery impeller according to claim 1, which is characterized in that the primary blades are arc, and are gone out
Mouth section transition is to be bent to impeller direction of rotation.
5. radial-flow type rotating machinery impeller according to claim 1, which is characterized in that the primary blades and the marginal convolution
The protrusion direction of piece is vertical with the back side of the impeller bodies or has angle.
6. radial-flow type rotating machinery impeller according to claim 1, which is characterized in that the edging blade quantity is described
The integral multiple of primary blades.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810840483.4A CN109083864A (en) | 2018-07-27 | 2018-07-27 | A kind of radial-flow type rotating machinery impeller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810840483.4A CN109083864A (en) | 2018-07-27 | 2018-07-27 | A kind of radial-flow type rotating machinery impeller |
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| Publication Number | Publication Date |
|---|---|
| CN109083864A true CN109083864A (en) | 2018-12-25 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810840483.4A Pending CN109083864A (en) | 2018-07-27 | 2018-07-27 | A kind of radial-flow type rotating machinery impeller |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110319053A (en) * | 2019-08-12 | 2019-10-11 | 烟台阳光泵业有限公司 | Unshrouded impeller and the low-flow high-lift centrifugal pump of single stage type for using unshrouded impeller |
| CN112855607A (en) * | 2021-01-18 | 2021-05-28 | 江苏大学 | Centrifugal pump impeller with a plurality of short blades |
| CN114857051A (en) * | 2022-05-23 | 2022-08-05 | 蔡义祥 | Novel ventilation equipment and fan |
| WO2023083588A1 (en) * | 2021-11-10 | 2023-05-19 | Robert Bosch Gmbh | Radial compressor and method for operating a radial compressor |
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| DE29904668U1 (en) * | 1999-03-13 | 1999-06-02 | Grundfos A/S, Bjerringbro | Circulation pump impeller of radial design |
| CN1800651A (en) * | 2005-10-14 | 2006-07-12 | 江苏大学 | Back vane structure for centrifugal pump |
| CN2893235Y (en) * | 2006-04-25 | 2007-04-25 | 宜兴市宙斯泵业有限公司 | Wear resisting centrifugal mortar pump |
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2018
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| DE29904668U1 (en) * | 1999-03-13 | 1999-06-02 | Grundfos A/S, Bjerringbro | Circulation pump impeller of radial design |
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| CN2893235Y (en) * | 2006-04-25 | 2007-04-25 | 宜兴市宙斯泵业有限公司 | Wear resisting centrifugal mortar pump |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110319053A (en) * | 2019-08-12 | 2019-10-11 | 烟台阳光泵业有限公司 | Unshrouded impeller and the low-flow high-lift centrifugal pump of single stage type for using unshrouded impeller |
| CN112855607A (en) * | 2021-01-18 | 2021-05-28 | 江苏大学 | Centrifugal pump impeller with a plurality of short blades |
| WO2023083588A1 (en) * | 2021-11-10 | 2023-05-19 | Robert Bosch Gmbh | Radial compressor and method for operating a radial compressor |
| CN114857051A (en) * | 2022-05-23 | 2022-08-05 | 蔡义祥 | Novel ventilation equipment and fan |
| CN114857051B (en) * | 2022-05-23 | 2024-05-07 | 王洪燕 | Novel ventilation equipment and fan |
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Application publication date: 20181225 |
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