CN2133675Y - Front-bend, back-glance centrifugal impeller of turbine for automobile booster - Google Patents
Front-bend, back-glance centrifugal impeller of turbine for automobile booster Download PDFInfo
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- CN2133675Y CN2133675Y CN 92224735 CN92224735U CN2133675Y CN 2133675 Y CN2133675 Y CN 2133675Y CN 92224735 CN92224735 CN 92224735 CN 92224735 U CN92224735 U CN 92224735U CN 2133675 Y CN2133675 Y CN 2133675Y
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- impeller
- angle
- antecurvature
- turbine
- blade profile
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Abstract
The utility model relates to a front-bend and back-glance centrifugal impeller for the turbine of an automobile booster, comprising an impeller boss body and a plurality of vanes connected with the impeller boss body. The inlet vane profile angles of the vanes are unevenly bent, wherein, the central section is front bent. The boss section and the hub section are backward bent and arranged along the vane height like a parabolic curve. Therefore, the vanes can aim at the actual interacting conditions and the influence of the internal flow characteristics for reasonably structuring the flow field and raising the inflow efficiency of the impeller. The range of operating condition is widened, the turbine performance of the automobile booster is improved, and finally the performance of a supercharged engine is modified.
Description
The utility model belongs to " vehicle turbocharger " technical field that the Thermal Turbomachinery aerothermodynamics combines with automobile-used explosive motor supercharging technology, particularly a kind of impeller that is used for vehicular engine pressurized machine radial turbine.
Radial turbine is used very extensive, and particularly along with the fast development of Vehicle Turbocharged technology and pressurized machine, its prospect is very wide.
The internal flow of radial turbine is very complicated.With regard to impeller, from radially to axial turnover, flow has tangible ternary feature to air-flow in the Ye Daozhong of high speed rotating experience, and the influence of brotherization power and centrifugal force is very big; The impeller physical dimension is little in addition, and the influence of viscosity and gap gas leakage is bigger; But also be subjected to the restriction of impeller inlet inlet flow conditions.For the vehicle supercharger turbine impeller, the influence of impeller inlet incoming flow is fairly obvious, is in particular in following three faces:
(1) vehicle supercharger turbine generally adopts no foliar spray to chew (claiming vaneless scroll again) with simplified structure, reduce cost and improve adaptability for working condition, but owing to there has not been the constraint of nozzle blade, its outlet be the impeller inlet flow parameter vertically (leaf height) very inhomogeneous;
(2) vehicular engine adopts the pulse pressure-charging mode mostly, but the intermittence exhaust of motor directly has influence on impeller air inlet state, makes it to become the astable of pulsation and flows;
(3) vehicular engine is always worked under the variable working condition condition, and operating mode haves a wide reach, changes frequent.
Therefore in fact strict, the impeller inlet inlet flow conditions is very serious space-time distortion stream, and this gives, and stream brings totally unfavorable influence in the impeller.When the vehicular engine worker dash to change especially when the low speed operating mode move, the impeller internal flow is easy to deterioration, and turbine efficiency obviously descends, and has limited the variable working condition accommodation of turbine.And the improvement of the low speed performance of operating condition key of vehicular engine supercharging just.
But, traditional impeller design does not take into full account above-mentioned factor and influence thereof, and the impeller of its approximate radial import molded lines is difficult to adapt to above-mentioned inhomogeneous air inlet state and sharp drastic changeization thereof, and internal flow is easy to separate, turbine efficiency descends, and can not satisfy the requirement of Vehicle Turbocharged.From domestic and international present Research, because the difficulty of current test in the radial turbine, relevant research still rested on certain stage, particularly the specific effect that no foliar spray is chewed due to this structure also is not fully recognized that, impeller design had not both had fine basic characteristics at variable parameter operation, do not consider the characteristic that its unsteady state is flowed yet, do not notice that more no foliar spray chews the uneven influence of exit flow field.Therefore, must consider above-mentioned influence conscientiously, improve the design and the structure of impeller.
The purpose of this utility model is intended to according to the actual operating conditions of impeller and to the influence of inner flowing characteristic, profile structural design by impeller inlet, the rationalization flow field, thereby stream efficient in the raising impeller, expansion operating mode scope, improve the vehicle supercharger turbine performance, finally improve the supercharged engine performance.
The space-time distortion condition of impeller inlet incoming flow is equivalent to different off-design behaviour condition and variation thereof.By the Aerothermodynamics of Turbomachinery basic principle as can be known, under the off-design behaviour condition, the influence that turbine stage efficient and performance decrease depend primarily on the incidence loss of impeller inlet with deterioration and the leaf road internal flow that causes thus separates.From the radial inlet molded lines structure of conventional impellers, the approach of dealing with problems is to improve the design of impeller inlet molded lines.Below at structure, incoming flow and the operation characteristic of vehicle supercharger turbine and to the influence of impeller air inlet state, provide concrete measure of the present utility model and design.
(1) chews the influence of structure exit flow field for no foliar spray, theoretically, if the profile structure of impeller inlet section and the meridian stream interface of actual flow are matched, no foliar spray is chewed exit flow and can be entered movable vane smoothly and excessive incidence loss does not take place, just might suppress to separate, improve flow efficiency.This shows that new design must be conceived to the S of impeller
1Profile, promptly profile of impeller vane has in various degree bending along Ye Gaoying.If with the definition of average flow inlet angle relatively or corresponding to blade radially, then the intermediate portion profile of impeller must be antecurvature, hub and wheel hub profile palintrope can vow with actual flow speed conform to.Antecurvature being defined as against the bending of impeller sense of rotation, palintrope is then opposite.
(2) influence of flowing for the unsteady state of pulse incoming flow, the exhaust flux of motor mainly concentrates on the peak region of Pulse wave, and this moment, pairing expansion ratio of turbine was big; As long as the operating mode of motor is certain, its exhaust pulses can not cause the too big variation of secondary speed simultaneously, thereby at the speed ratio u/c of peak region turbine stage
oLess, if make the optimum speed ratio u/c of level
OoprApproach the speed ratio u/c of peak region
o, just can maximally utilise pulse energy.Thereby should make blade profile import molded lines antecurvature to consider the pulse influence by the impeller of steady flow design.Such structure also can be brought 2 benefits: the first, for non-peak region, and speed ratio u/c
oBigger, the inlet incidence angle of preceding bending impeller is for negative, a little less than the influence relatively, so its Applicable scope can be relaxed; The second, when the low engine speed operating mode, the amplitude of exhaust pulses ripple increases to some extent, reduces u/c
oMore help improving the low-speed torque characteristic of supercharged engine.
(3) move the influence (difficult avoid) of caused inlet incidence angle for off-design behaviour, key is to select suitable design point, has determined that by the significance of low engine speed operating mode design point should be at u/c
oChoose more among a small circle.This is consistent with the design that improves the effect of Fluid Pulsation characteristic, promptly should make blade profile antecurvature.
Based on above-mentioned analysis, propose the new design of antecurvature sweepback impeller: the non-homogeneous bending in import blade profile angle of blade, wherein zone line is antecurvature, hub and wheel hub district palintrope.Be approximate parabolic type along the leaf height and distribute, but blade profile angle average result vertically still is antecurvature, thereby guarantee corresponding to little speed ratio u/c
oCondition is to make full use of pulse energy and to improve the low engine speed performance of operating condition; And whole blade profile Changing Pattern and no foliar spray are chewed exit flow field and are coincide, with the appropriate coupling on the acquisition flox condition.
Fig. 1 is a structure principle chart of the present utility model.
Fig. 2 is that import blade profile of the present utility model angle is along one of high schematic representation that distributes of leaf.
With reference to Fig. 1, the utility model comprises an impeller boss body (1), the some blades (2) that link to each other with impeller boss body (1), the non-homogeneous bending in import blade profile angle of blade (2), zone line (3) antecurvature (opposite) wherein with the impeller sense of rotation, hub district (4) and wheel hub district (5) palintrope are approximate parabola (referring to Fig. 2) along the leaf height and distribute, and blade profile angle average result vertically still is antecurvature.
The maximum blade profile angle β that zone line Fig. 1 (3) is antecurvature
BmaxFor:
β
bmax≤180°－arctg（2tgα
1）
Wherein, α
1Be the absolute air flow angle of impeller inlet incoming flow, different α
1Different β is arranged
BmaxValue is as to α
1=25 °, can get β
Bmax≤ 137 ° (is 47 by radially counting kyphotic angle) ° in the practical application, considers many-sided factor, desirable β
b=105 °-125 ° (radially counting kyphotic angle is 15 °-35 °) and the back bent angle of hub district (4) and wheel hub district (5) is desirable:
β
bThe variation at=60 °-90 ° (radially count back bent angle be 0 °-30 °) whole impeller inlet blade profile angles can represent that it is along the high regularity of distribution of leaf by parabola:
β＝a（ (Z)/(L) ）
2＋b（ (Z)/(L) ）＋c，
In the formula: Z is along the high axial coordinate of leaf, and L is an import leaf height, therefore by wheel hub (Z=0, (Z)/(L)=0, β=β
h), average leaf height (Z=(L)/2, (Z)/(L)=1/2, β=β
m), hub (Z=L, (Z)/(L)=1, β=β
t) parameter substitution following formula can determine whole molded lines equation.Wherein:
a＝2（β
h＋β
t－2β
m）
b＝4（β
m－β
t－3β
h）
c＝β
h
Wherein, β
h, β
tThe back bent angle that is equivalent to wheel hub, hub, span be at 60 °-90 °, β
mBe maximum kyphotic angle, span is 105 °-125 °, and the span that the substitution following formula can get three functions in the quadratic curve relation is as follows:
a＝－60°～－260°
b＝60°～260°
c＝60°～90°
According to the designed a kind of embodiment of structural principle of the present utility model as shown in Figure 2, wherein molded lines equation coefficient a=-60 °, b=60 °, c=90 °.This embodiment compares (both molded lines are different except entrance region, and all the other position molded lines are identical), different working conditions (speed ratio u/c with prior art WZJ-70 type booster turbine
o=result of calculation under 0.61-0.89) shows: prior art is chewed under the inhomogeneous situation of exit flow field parameter at no foliar spray, and the suction surface entrance region flows and worsens, and especially the hub place secondary speed-reducing diffusion occurs and forms and separate; And that the present embodiment longshore current changes to parameter is mild, and almost in all operating mode scopes, secondary speed-reducing is eliminated substantially, thereby suppresses effectively even eliminated flow separation.
Among Fig. 2, β
bBe the blade profile angle from radially counting, wherein kyphotic angle is just got, and back bent angle is got negative; Z/L is the high axial coordinate of relative import leaf, and Z is along the high axial coordinate of leaf, and L is an import leaf height; Curve (6) is that the utility model embodiment's import blade profile angle is along the high distribution curve of leaf; Curve (7) is that the import blade profile angle of prior art WZJ-70 type booster turbine impeller is along the high distribution curve of leaf.
Claims (5)
1, the antecurvature sweepback impeller of vehicle supercharger turbine, comprise an impeller boss body, the some blades that link to each other with the impeller boss body, feature of the present utility model is, the non-homogeneous bending in import blade profile angle of blade, zone line antecurvature (opposite) wherein, hub district and wheel hub district palintrope with the impeller sense of rotation, be approximate parabolic distribution along the leaf height, blade profile angle average result vertically still is antecurvature.
2, impeller according to claim 1 is characterized in that, the regularity of distribution at the import blade profile angle of said blade is β:
β＝a（ (Z)/(L) ）
2＋b（ (Z)/(L) ）＋c
Wherein: a=2(β
h+ β
t-β
m)
b＝4β
m－β
t－3β
h
c＝β
h
Z is along the high axial coordinate of leaf;
L is an import leaf height;
β
hBack bent angle for wheel hub;
β
tBack bent angle for hub;
β
mKyphotic angle for average leaf eminence.
3, according to claim 1,2 described impellers, it is characterized in that the maximum blade profile angle β that said zone line is antecurvature
BmaxFor:
β
bmax180°－arctg′（2tgα
1）
Wherein, α
1Absolute air flow angle for the impeller inlet incoming flow.
According to claim 1,2 described impellers, it is characterized in that 4, the back bent angle in said hub district and wheel hub district is 60 °-90 °.
5, impeller according to claim 3 is characterized in that, the maximum blade profile angle β that said zone line is antecurvature
BmaxIt is 105 °-125 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 92224735 CN2133675Y (en) | 1992-06-19 | 1992-06-19 | Front-bend, back-glance centrifugal impeller of turbine for automobile booster |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 92224735 CN2133675Y (en) | 1992-06-19 | 1992-06-19 | Front-bend, back-glance centrifugal impeller of turbine for automobile booster |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2133675Y true CN2133675Y (en) | 1993-05-19 |
Family
ID=33769809
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 92224735 Expired - Fee Related CN2133675Y (en) | 1992-06-19 | 1992-06-19 | Front-bend, back-glance centrifugal impeller of turbine for automobile booster |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2133675Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102080672A (en) * | 2010-09-18 | 2011-06-01 | 中国兵器工业集团第七○研究所 | Centrifugal cooling water pump |
| CN106194275A (en) * | 2014-12-08 | 2016-12-07 | 现代自动车株式会社 | Turbine wheel for turbocharger |
-
1992
- 1992-06-19 CN CN 92224735 patent/CN2133675Y/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102080672A (en) * | 2010-09-18 | 2011-06-01 | 中国兵器工业集团第七○研究所 | Centrifugal cooling water pump |
| CN106194275A (en) * | 2014-12-08 | 2016-12-07 | 现代自动车株式会社 | Turbine wheel for turbocharger |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |