CN104389978A - Manufacturing method of double-element blade profile guide wheel - Google Patents
Manufacturing method of double-element blade profile guide wheel Download PDFInfo
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- CN104389978A CN104389978A CN201410563513.3A CN201410563513A CN104389978A CN 104389978 A CN104389978 A CN 104389978A CN 201410563513 A CN201410563513 A CN 201410563513A CN 104389978 A CN104389978 A CN 104389978A
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- blade
- guide wheel
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- blade profile
- profile guide
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
- F16H41/26—Shape of runner blades or channels with respect to function
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
- F16H41/28—Details with respect to manufacture, e.g. blade attachment
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a manufacturing method of a double-element blade profile guide wheel so as to improve the performance of a hydraulic torque converter under a low-speed-ratio working condition. The method mainly comprises design of a double-element blade profile, design of the width of a slot between a main blade and a secondary blade and design of further suppression of boundary layer flow separation on a blade suction surface. A preliminary double-element guide wheel blade profile can be obtained through the design of the double-element blade profile. The rational value range of the width between the main and secondary blades can be between 4 percent and 8 percent through the design of the width of the slot between the main blade and the secondary blade. The double-element blade profile guide wheel with more superior comprehensive performance can be obtained through the design of the further suppression of the boundary layer flow separation on the blade suction surface. Finally momentum moment distribution is determined to be concentrated on the front edge of the secondary blade, so that the boundary layer flow separation on the guide wheel blade suction surface can be effectively suppressed at a low speed ratio.
Description
Technical field
The present invention relates to a kind of making method, particularly a kind of making method of automobile torque converter guide wheel being carried out to dual-element blade profile guide wheel.
Background technique
Fluid torque converter is one of critical component of Transmission System, and its performance plays material impact to car load power character and Economy.Traditional fluid torque converter list section blade carries out drawing based on being projected on the isogonism projective method launched in polycylindser face.Carry out the first-selected circulate circle needing to obtain designed fluid torque converter when blade is drawn, i.e. axis projection, and the turnover bicker of designed blade.Then, on axial plane figure, by equidistant point, 5-15 section is done to the streamline of done evolute.Then the isogonism graph in polycylindser face is obtained.The orthographic drawing of blade can be obtained, i.e. three dimendional blade by axial plane figure and polycylindser face isogonism projection figure.Concrete unit piece blade design working process please refer to the isogonism projective method being published the polycylindser face that the is projected on expansion in " the hydraudynamic drive theory and design " of in June, 2004 first edition by Chemical Industry Press that Marvin's star is write.
Car Torque Converter is with lock-up clutch, can when running at high speed locking, power is directly passed to speed changer by clutch, compensate for the defect that torque converter drive efficiency is lower to a great extent, and low speed than time require that fluid torque converter has higher converter torque ratio, thus improve the starting performance of vehicle and grade climbing performance.The non-constant width of fluid torque converter operating range, causes turbine outlet flow angle degree with speed ratio change greatly.In order to ensure fluid torque converter at a high speed than time there is higher efficiency, generally guide vane inlet angle is designed to, than time, there is the positive angle of shock (for just impacting during liquid flow impact blade pressure surface) at low speed, than time, there is the negative angle of shock at a high speed.But, low speed than time, owing to there is the larger positive angle of shock, cause liquid stream to occur at guide vane suction surface place being separated, the defection of liquid flow point causes high shearing runner.Generation due to separate bubble can reduce effective area of passage of runner, thus increases leaf loss, reduces the ability of transmission oil circular flow and fluid torque converter transmitting torque.In addition, also can affect the flow angle in guide wheel outlet port, increase uncertainty and the difficulty of design process.
Summary of the invention
The present invention aims to provide a kind of making method of dual-element blade profile guide wheel, design method in other words, by using this method can effectively suppress blade suction surface place boundary layer flow to be separated, improves power character during car starting.
To achieve the above object of the invention, the key point that the present invention makes is: the primary blades of (1) dual-element blade profile guide wheel and the making of back blades blade profile; (2) determination of groove gap length degree between primary blades and back blades.Particularly, a kind of making method of dual-element blade profile guide wheel, for fluid torque converter, step is as follows:
Step one, determine primary blades Inlet cone angle and the back blades exit angle of dual-element blade profile guide wheel: using unit piece prototype blade as benchmark, make the consistent respectively into and out of bicker of the primary blades Inlet cone angle of described dual-element blade profile guide wheel and back blades exit angle and above-mentioned unit piece prototype blade;
Step 2, determines the major and minor blade separation point of dual-element blade profile guide wheel: determined by the major and minor blade separation point of the dual-element blade profile guide wheel described in the first step at prototype blade mean camber line apart from leading edge 1/3rd place;
Step 3, determines groove gap length degree between the primary blades of dual-element blade profile guide wheel and back blades: between the primary blades of described dual-element blade profile guide wheel and back blades, the span of groove gap length degree is between 4% to 8% chord length;
Step 4, moves to back blades leading edge by the blade mean camber line inflection point of dual-element blade profile guide wheel.
On the basis of the above-described procedure, also need to illustrate as follows the method designed and produced of dual-element blade profile guide wheel and principle:
(1) in step one, using unit piece prototype as benchmark, the consistent respectively into and out of bicker of the primary blades Inlet cone angle of described dual-element blade profile guide wheel and back blades exit angle and above-mentioned unit piece prototype blade is made.
After the primary blades Inlet cone angle of above-mentioned dual-element blade profile guide wheel and back blades exit angle are determined, also need to carry out the design of blade mean camber line and blade wheel the outline design, all adopt parameterized making method.Its parameterized method is as follows:
Because blade mean camber line is made up of 2 nurbs curves.This nurbs curve is determined by 3 control vertexs altogether, and wherein head and the tail two control vertexs coincide with blade front and rear edges respectively.At nurbs curve head and the tail, place adopts three multiple knot respectively, and namely knot vector is
, thus make generated nurbs curve interpolation head and the tail two control vertexs respectively.
Control vertex
be positioned at the true origin of design plane.Control vertex
coordinate value along L axle (being equivalent to the X-axis of cartesian coordinate system) is the arc length of three dimensional space Leaf design baseline at cylindrical coordinates axis plane projection, and its coordinate value along N axle (being equivalent to the Y-axis of cartesian coordinate system) temporarily cannot be determined.First suppose control vertex
,
position is determined, then control vertex
coordinate obtained by following Solving Equations:
The control vertex line of being tried to achieve by above formula
with
equal blade respectively with the angle of N axle and pass in and out bicker, the character tangent with control vertex line at head and the tail place according to nurbs curve, the mean camber line generated by above-mentioned control vertex turnover bicker equals respectively
,
.
(2) in step 2, torque converter reactor blade belongs to leading edge and loads, and the Curvature varying of its mean camber line mainly concentrates on apart from blade inlet edge place, and its rear end part curvature is smooth, close to straight line.In order to get rid of blade by the impact of pressure surface curature variation on boundary layer separation, make primary blades leading edge profile line, especially consistent with unit piece blade profile by pressure surface boundary layer separation point place, therefore the major and minor blade separation point of the dual-element blade profile guide wheel described in the first step is determined at prototype blade mean camber line apart from leading edge 1/3rd place.
(3) in addition, after step 2, may described in the primary blades chord length of dual-element blade profile guide wheel shorter, therefore can by the suitable skiving of above-mentioned primary blades leading edge pressure side, and back blades thickness is consistent with unit piece prototype blade along the Changing Pattern of mean camber line simultaneously.
(4) in order to while making low speed have the effect of maximum suppression boundary layer separation than operating mode double-leaf guide wheel, in peak efficiency operating mode, there is less loss coefficient, so in step 3, between primary blades and back blades, groove gap reasonable groove gap length degree should be 4% to 8% of blade chord length.
Moment-resistance ratios opposed slot gap length degree that under stall operating mode, dual-element blade produces is convex curve, occurs significantly gliding when groove gap length degree is greater than 8% chord length.At a high speed than time, when groove gap length degree be less than 4% or be greater than 8% chord length time, dual-element guide wheel will make hydraulic losses significantly increase.Therefore, more rational span should between 4% to 8% chord length.
(5) method of the design suppressing blade suction surface place boundary layer flow to be separated further is:
Although above-mentioned dual-element blade profile guide wheel effectively alleviates blade suction surface place boundary layer flow and is separated, but still there is separation in some region of primary blades suction surface, this reason is that primary blades suction surface place blade profile profile is consistent with unit piece, this position curvature is still excessive, causes flowing cannot overcome inverse pressure and produce separation.In order to further control separation, reduce the curvature of primary blades suction surface, make full use of groove gap between major and minor blade and, to the inhibitory action of boundary layer flow separation, the blade mean camber line inflection point of dual-element blade profile guide wheel is moved to back blades leading edge.In addition, in order to adapt to the change of main lobe shape, ensureing that major and minor interlobate groove gap has the trend of convergence, thus fluid is accelerated through, suitably change accessory lobes shape suction surface amplitude distribution rule.
Superiority of the present invention is:
The method adopts dual-element blade profile to substitute conventional unit piece blade profile, reaches and improves fluid torque converter at the technique effect of low speed than combination property under operating mode.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of preliminary dual-element guide wheel blade profile I;
Fig. 2 is blade mean camber line schematic diagram;
Fig. 3
weighted value is to the linear effect diagram of mean camber line;
The radius of curvature distribution situation figure of the corresponding blade mean camber line of the different weighted value of Fig. 4;
Fig. 5 blade wheel profile organigram;
Fig. 6 blade profile line computation schematic diagram;
Fig. 7 groove gap length degree compares schematic diagram with blade chord length;
Fig. 8 is unit piece and dual-element guide wheel fluid torque converter performance comparison figure;
Fig. 9 is the dual-element guide wheel blade profile II after optimizing;
Figure 10 is developable surface liquid flowing speed vector diagram in dual-element guide wheel blade profile I and II blade;
Figure 11 is dual-element guide wheel blade profile I and dual-element guide wheel blade profile II fluid power performance comparison figure.
Embodiment
Refer to below shown in accompanying drawing, the present invention is done to describing further.
The invention discloses a kind of making method of the dual-element blade profile guide wheel for fluid torque converter, for designing and producing of automobile torque converter guide wheel blade profile, basic step is as follows:
Step one, determine primary blades Inlet cone angle and the back blades exit angle of dual-element blade profile guide wheel: using unit piece prototype blade as benchmark, make the consistent respectively into and out of bicker of the primary blades Inlet cone angle of described dual-element blade profile guide wheel and back blades exit angle and above-mentioned unit piece prototype blade;
Step 2, determines the major and minor blade separation point of dual-element blade profile guide wheel: determined by the major and minor blade separation point of the dual-element blade profile guide wheel described in the first step at prototype blade mean camber line apart from leading edge 1/3rd place;
Step 3, determines groove gap length degree between the primary blades of dual-element blade profile guide wheel and back blades: between the primary blades of described dual-element blade profile guide wheel and back blades, the span of groove gap length degree is between 4% to 8% chord length;
Step 4, moves to back blades leading edge by the blade mean camber line inflection point of dual-element blade profile guide wheel.
Fig. 1 is dual-element blade profile scheme I.Using unit piece prototype blade as benchmark, make the consistent with the primary blades Inlet cone angle of dual-element blade profile guide wheel and back blades exit angle respectively into and out of bicker of unit piece prototype blade.Unit piece prototype blade belongs to leading edge and loads, and the Curvature varying of its mean camber line mainly concentrates on apart from blade inlet edge 1/3rd place, and its rear end part curvature is smooth, close to straight line.In order to get rid of blade by the impact of pressure surface curature variation on boundary layer separation, make primary blades leading edge profile line, especially consistent with unit piece blade profile by pressure surface boundary layer separation point place.Therefore major and minor blade separation point is determined at prototype blade mean camber line apart from leading edge 1/3rd place.Because primary blades chord length is shorter, therefore by the suitable skiving of primary blades leading edge pressure side, back blades thickness is consistent with unit piece prototype blade along the Changing Pattern of mean camber line.
Fig. 2, blade mean camber line schematic diagram.Blade mean camber line is made up of 2 nurbs curves.This nurbs curve is altogether by 3 control vertexs
determine, wherein head and the tail two control vertexs
coincide with blade front and rear edges respectively.At nurbs curve head and the tail, place adopts three multiple knot respectively, and namely knot vector is
, thus make generated nurbs curve interpolation head and the tail two control vertexs respectively.
Control vertex
be positioned at the true origin of design plane.Control vertex
coordinate value along L axle is the arc length of three dimensional space Leaf design baseline at cylindrical coordinates axis plane projection, and its coordinate value along N axle temporarily cannot be determined.First suppose control vertex
,
position is determined, then control vertex
coordinate obtained by following Solving Equations:
The control vertex line of being tried to achieve by above formula
with
equal blade respectively with the angle of N axle and pass in and out bicker, the character tangent with control vertex line at head and the tail place according to nurbs curve, the mean camber line generated by above-mentioned control vertex turnover bicker equals respectively
,
.
Fig. 3, P1 weighted value is to the linear effect diagram of mean camber line.The curvature distribution of blade mean camber line has a direct impact fluid power performance in the prior art, and the blade under different operating condition is also different to the requirement of its mean camber line curvature distribution.By changing control vertex
weighted value can control the curvature distribution of blade further.Weighted value is larger, the blade generated the closer to
point, blade Curvature varying Shaoxing opera near this control vertex is strong.Adopt less weighted value then can make the moment of momentum distribute evenly.
Fig. 4, the radius of curvature distribution situation figure of the corresponding blade mean camber line of different weighted value.
point weighted value
(in Fig. 4 b) and
(time in Fig. 4 c), vane curvature radius distribution situation is similar, and its minimum profile curvature radius is positioned at linear middle part.
time, the radius of curvature of its blade front and rear edge is comparatively large, and small radii of curvature is more concentrated, and the radius of curvature change along mean camber line is larger.
point weighted value
(time in Fig. 4 a), on mean camber line, the distribution situation of radius of curvature is just in time contrary, and the radius of curvature of blade front and rear edge is less, and the radius of curvature in mean camber line stage casing is larger.
Fig. 5, blade wheel profile organigram.Guide vane profile line is made up of closed 3 nurbs curves.The control vertex of blade profile nurbs curve is along mean camber line arranged on both sides.When determining the control vertex of blade profile nurbs curve, on mean camber line, first select some points, relatively get a little closeer at meanline curvature radius smaller part.Use the computational methods of NURBS derivative, calculate tangent line and the normal of each selected point on mean camber line, as shown in Figure 5 b.The control vertex of blade wheel profile is calculated, as shown in Figure 5 c according to the normal of each selected point on the vane thickness Changing Pattern determined and mean camber line.This nurbs curve head and the tail control vertex
be arranged on trailing edge place, and all adopt quadruple node at the head and the tail of knot vector, thus make its form one close and the blade profile curve of trailing edge interpolation specified point.In addition, in order to make nurbs curve interpolation blade inlet edge, edge place also arranges a control vertex in front of the blade
, and set up quadruple node at corresponding node vector place.
Fig. 6, blade profile line computation schematic diagram.Conformal transformation does not possess along path invariance, therefore carries out conformal transformation to mean camber line and both sides blade wheel profile thereof simultaneously, and after 3 curve mappings to three dimensional space in figure, 3 curves will not overlap at trailing edge place.Blade angle due to streamline vane is defined on mean camber line, and therefore, should ensure that the blade angle on mean camber line is constant from design plane in the mapping process of three-dimensional planar, the three dimensional space cylindrical coordinates value of mean camber line both sides profile line will calculate according to following relation:
In formula:
---non-straightedge vane profile line is in three-dimensional cylindrical coordinates value;
---non-straightedge vane mean camber line is in three-dimensional cylindrical coordinates value.
Fig. 7, groove gap length degree compares schematic diagram with blade chord length.Moment-resistance ratios opposed slot gap length degree that under stall operating mode, dual-element blade produces is convex curve, occurs significantly gliding when groove gap length degree is greater than 8% chord length.At a high speed than time, when groove gap length degree be less than 4% or be greater than 8% chord length time, dual-element guide wheel will make hydraulic losses significantly increase.Therefore, more rational span should between 4% to 8% chord length.
Fig. 8 is unit piece and dual-element guide wheel fluid torque converter performance comparison figure.Due to the effect of the line of rabbet joint between the major and minor blade of dual-element guide wheel, inhibit the separation of suction surface liquid stream, low speed than time, the stream recirculates flow in runner significantly increases, thus makes stall torque than all being promoted with impeller torque capacity coefficient.Near best efficiency point, peak efficiency value slightly declines, and is about 0.5%.
Fig. 9, for further optimize after dual-element guide wheel blade profile II.In order to further control separation, reduce the curvature of primary blades suction surface, make full use of groove gap between major and minor blade and, to the inhibitory action of boundary layer flow separation, bifolium blade mean camber line inflection point is moved to back blades leading edge.In addition, in order to adapt to the change of main lobe shape, ensureing that major and minor interlobate groove gap has the trend of convergence, thus fluid is accelerated through, suitably change accessory lobes shape suction surface amplitude distribution rule.
Figure 10, in dual-element guide wheel blade profile I and II blade, developable surface liquid flowing speed vector diagram contrasts.Occurred circulation whirlpool tail at the suction surface place of dual-element guide wheel blade profile I, and do not occurred in dual-element blade profile guide wheel II, visible dual-element amended primary blades suction surface boundary layer separation is effectively suppressed.
Figure 11 is dual-element guide wheel blade profile I and dual-element guide wheel blade profile II fluid power performance comparison figure.Can learn that its efficiency has almost no change by contrast, flow and converter torque ratio have and promote by a small margin, and impeller torque capacity coefficient obtains more obviously promoting.
Claims (2)
1. a making method for dual-element blade profile guide wheel, described dual-element blade profile guide wheel is used for fluid torque converter, it is characterized in that:
Step one, determine primary blades Inlet cone angle and the back blades exit angle of dual-element blade profile guide wheel:
Using unit piece prototype blade as benchmark, make the consistent respectively into and out of bicker of the primary blades Inlet cone angle of described dual-element blade profile guide wheel and back blades exit angle and above-mentioned unit piece prototype blade;
Step 2, determine the major and minor blade separation point of dual-element blade profile guide wheel:
The major and minor blade separation point of the dual-element blade profile guide wheel described in step one is determined at prototype blade mean camber line apart from leading edge 1/3rd place;
Step 3, determine groove gap length degree between the primary blades of dual-element blade profile guide wheel and back blades:
Between the primary blades of described dual-element blade profile guide wheel and back blades, the span of groove gap length degree is between 4% to 8% chord length;
Step 4, moves to back blades leading edge by the blade mean camber line inflection point of dual-element blade profile guide wheel.
2. the making method of a kind of dual-element blade profile guide wheel according to claim 1, it is characterized in that: between second step and the 3rd step, by the primary blades leading edge pressure side skiving of described dual-element blade profile guide wheel, and make back blades thickness consistent with above-mentioned unit piece prototype blade along the Changing Pattern of mean camber line.
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|---|---|---|---|
| CN201410563513.3A CN104389978B (en) | 2014-10-22 | Manufacturing method of double-element blade-shaped guide wheel |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410563513.3A CN104389978B (en) | 2014-10-22 | Manufacturing method of double-element blade-shaped guide wheel |
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| Publication Number | Publication Date |
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| CN104389978A true CN104389978A (en) | 2015-03-04 |
| CN104389978B CN104389978B (en) | 2017-01-04 |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105240480A (en) * | 2015-07-07 | 2016-01-13 | 同济大学 | Method for determining thickness of blades of hydraulic torque converter based on water-drop-shaped airfoil function |
| CN106979854A (en) * | 2017-05-19 | 2017-07-25 | 吉林大学 | Torque converter blades boundary layer flow measurement apparatus and measuring method |
| CN107035844A (en) * | 2017-05-25 | 2017-08-11 | 吉林大学 | A kind of fluid torque-converter segmented turbo blade |
| CN109185416A (en) * | 2018-08-09 | 2019-01-11 | 北京理工大学 | A kind of fluid torque-converter cavitation suppressing method based on fluting |
| CN115625595A (en) * | 2022-12-21 | 2023-01-20 | 太原理工大学 | Quantitative control blade polishing and grinding method |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105240480A (en) * | 2015-07-07 | 2016-01-13 | 同济大学 | Method for determining thickness of blades of hydraulic torque converter based on water-drop-shaped airfoil function |
| CN105240480B (en) * | 2015-07-07 | 2019-01-25 | 同济大学 | Method is determined based on the torque converter blades thickness of drops airfoil function |
| CN106979854A (en) * | 2017-05-19 | 2017-07-25 | 吉林大学 | Torque converter blades boundary layer flow measurement apparatus and measuring method |
| CN106979854B (en) * | 2017-05-19 | 2023-04-14 | 吉林大学 | Device and method for measuring flow of blade boundary layer of hydraulic torque converter |
| CN107035844A (en) * | 2017-05-25 | 2017-08-11 | 吉林大学 | A kind of fluid torque-converter segmented turbo blade |
| CN107035844B (en) * | 2017-05-25 | 2021-02-02 | 吉林大学 | Sectional type turbine blade of hydraulic torque converter |
| CN109185416A (en) * | 2018-08-09 | 2019-01-11 | 北京理工大学 | A kind of fluid torque-converter cavitation suppressing method based on fluting |
| CN115625595A (en) * | 2022-12-21 | 2023-01-20 | 太原理工大学 | Quantitative control blade polishing and grinding method |
| CN115625595B (en) * | 2022-12-21 | 2023-03-17 | 太原理工大学 | Quantitative control blade polishing and grinding method |
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