CN105156631A - Bionic double-turbine hydraulic torque converter - Google Patents

Abstract

The invention relates to a bionic double-turbine hydraulic torque converter. The bionic double-turbine hydraulic torque converter comprises a pump wheel, a pump wheel outer ring, a pump wheel inner ring, a first turbine, a guide wheel and a second turbine. Vanes of the pump wheel are bionic wheels. The polynomial of the circular rector distribution function of the pump wheel is y=ax3+bx2+cx+d, wherein x is the transverse coordinate of each equal diversion point on an arc line, y is the corresponding circular rector distribution value, -1.4827<=a<=-0.7116, -1.7632<=b<=-0.8364, 0.0377<=c<=1.1008, and -0.3767<=d<=0.3645. The vanes of the pump wheel are bionic wheels. Compared with a traditional common double-turbine hydraulic torque converter, the starting torque ratio and efficiency are increased, and the capacity factor of the pump wheel is larger than that of a hydraulic torque converter with common vanes.

Description

A kind of bionical twin-turbine torque converter

Technical field

The present invention relates to a kind of twin-turbine torque converter, be specifically related to the bionical twin-turbine torque converter of YJSW335 type.

Background technique

Fluid torque converter take liquid as working medium, utilize the change of kinetic energy to the transmission device realizing torque, rotating speed conversion and transmit, there is the advantages such as load self adaption, stepless change, vibration damping and vibration isolation and stable low-speed performance, at present, in various engineering machinery, hydraudynamic drive has accounted for absolute superiority, and being widely used in engineering machinery, automobile, military project and petroleum machinery etc., is the critical component of vehicle drive system.Its efficiency run has important and direct impact to the Economy of car load and discharge.But existing hydraulic torque converter of engineering machine efficiency is lower, substantially about 80%, even lower.This is not only the waste of natural resources and energy resources, and more discharge causes environmental deterioration.

Natural biology carries out constantly evolving, and oneself becomes the resource treasure-house of human research and study through defining optimized morphostructure and controlling coordination process the most accurately.The various structures of organism surface, tissue and excellent specific property, the research through scientist finds, according to certain rules, distribution or arrangement in order, simplify and form various bionical body, in gas, fluid and solid system, own warp is widely used its body surface.Such as, fish are under states such as accelerating travelling, turning of wagging the tail, and body presents certain arc, at this moment often has the reactivity of great power acceleration and rapid flexible.Geometric non-smooth is also one of important content of body drag reduction.Live in the biology of land, in slowly drained soil and the organism surface not easily adhering to soil show as non-smooth surface form; Live in the biology in ocean, especially the hydrobiose of Quick off the mark, its body surface is also much all rough, but the Non-smooth surface be made up of scale or subcutaneous connective tissue.Therefore, use the biomimetic features with excellent drag reduction mechanism, carry out the blade Bionic Design of fluid machinery, there is very high using value.

Summary of the invention

The technical problem to be solved in the present invention is to provide a kind of bionical twin-turbine torque converter, and this torque-converters, on the basis not changing original fluid torque converter structure, adopts bionic coupling technology to reach the object of energy efficiency, improves the efficiency of twin-turbine torque converter.

In order to solve the problems of the technologies described above, bionical twin-turbine torque converter of the present invention comprises pump impeller, pump impeller outer shroud, pump impeller inner ring, the first turbine, guide wheel, the second turbine; The blade of described pump impeller adopts bionic blade, and the multinomial of its circular rector partition function is: y=ax ³+ bx ²+ cx+d, wherein x is the abscissa of each equal diversion point on mean camber line, and y is corresponding circular rector apportioning cost, and the span of ginseng a, b, c, d is as follows:

$\left\{\begin{array}{c}-1.4827\&le;a\&le;-0.7116\\ -1.7632\&le;b\&le;-0.8364\\ 0.0377\&le;c\&le;1.1008\\ -0.3767\&le;d\&le;0.3645\end{array}\right..$

Described parameter a, b, c, d preferred a=-1.1129, b=-1.3475, c=0.7683, d=-0.0009.

The blade of pump impeller of the present invention adopts bionic blade, compared with original conventional twin-turbine torque converter, improves starting torque ratio and efficiency, and pump impeller capacity coefficient is greater than the fluid torque converter adopting common blade.

Further, the blade of described second turbine adopts bionic blade, and its circular rector partition function multinomial is: y=ax ²+ bx+c, wherein x is the abscissa of each equal diversion point on mean camber line, and y is corresponding circular rector apportioning cost; The span of parameter a, b, c is as follows:

$\left\{\begin{array}{c}-0.8972\&le;a\&le;-0.4629\\ -0.4886\&le;b\&le;-0.1032\\ 0.4709\&le;c\&le;1.5079\end{array}\right..$

Described parameter a, b, c preferred a=-0.7374, b=-0.2919, c=1.0108.

In the present invention, the second turbine blade adopts bionic blade, further increase starting torque ratio and efficiency, and pump impeller capacity coefficient CF is also greater than conventional twin-turbine torque converter.

Further, the blade of guide wheel of the present invention adopts bionic blade, and the multinomial of its circular rector partition function is: y=ax ³+ bx ²+ cx+d, wherein x is the abscissa of each equal diversion point on mean camber line, and y is corresponding circular rector apportioning cost, and the span of parameter a, b, c, d is as follows:

$\left\{\begin{array}{c}0.6044\&le;a\&le;1.4151\\ -0.5792\&le;b\&le;-0.1698\\ -0.1989\&le;c\&le;0.581\\ -0.4221\&le;d\&le;0.3746\end{array}\right..$

Described parameter a, b, c, d preferred a=0.992, b=-0.192, c=0.1936, d=-0.0058.

The blade of guide wheel of the present invention adopts bionic blade, further improves starting torque ratio and efficiency, and pump impeller capacity coefficient is greater than the fluid torque converter adopting common blade.

The blade suction surface of described guide wheel arranges U-shaped bionical groove near the front portion of blade inlet, the height h of this bionical groove and the dimensionless size h of distance s ⁺and s ⁺span be respectively 0 < h ⁺≤ 25,0 < s ⁺≤ 30.

The height h of described bionical groove and the size span of distance s are 0 < s≤0.83mm, 0 < h≤1mm.

The height h of described bionical groove and size preferred h=0.5mm, the s=0.5mm of distance s.

The described bionical trench region initial part distance of positions is L from the distance of blade inlet ₁=7.43mm, the position, end of bionical trench region is L from the distance of blade exit ₂=11.52mm.

In the flow field of fluid torque converter, separated flow produces material impact to its performance, and flow losses not only can be made sharply to increase, and the pressure pulsation that separated flow is formed also will cause producing mechanical vibration in torque-converters working procedure.The present invention processes the lateral trench of some and size on the guide vane suction surface of fluid torque converter, and to reduce adhesion and the resistance of liquid, better to control the flowing of boundary layer, turbulent flow drag reduction effect is obvious, improves fluid torque converter performance.

The blade of described first turbine adopts bionic blade, and the multinomial of its circular rector partition function is: y=ax ⁴+ bx ³+ cx ²+ dx+e, wherein x is the abscissa of each equal diversion point on mean camber line, and y is corresponding circular rector apportioning cost, and the span of parameter a, b, c, d, e is as follows:

$\left\{\begin{array}{c}3.0619\&le;a\&le;6.0894\\ -6.0787\&le;b\&le;-3.8151\\ -0.406\&le;c\&le;0.0147\\ -0.1814\&le;d\&le;0.4725\\ 0.5972\&le;e\&le;1.5149\end{array}\right..$

Described parameter a, b, c, d, e preferred a=4.1141, b=-5.08, c=-0.1494, d=0.1369, e=0.9918.

The present invention first turbine blade adopts bionic blade, further increases starting torque ratio and efficiency, and pump impeller capacity coefficient is greater than the fluid torque converter adopting common blade.

Described pump impeller inner ring and pump impeller outer shroud are distributed with spherical pit, and the span of pit depth S is 0.64mm ~ 1.24mm, and diameter D span is 1.28mm ~ 2.48mm.

Described pit is matrix arrangement, the depth S of pit, diameter D, horizontal spacing W and longitudinal pitch L preferred S=1mm, D=2mm, W=3mm, L=5mm.

The present invention processes the Non-smooth surface biomimetic features of pit type on the outer surface of face of fluid torque converter outer shroud upper inner surface and inner ring, because pit type non-smooth surface frictional force, shearing stress and neighbouring turbulent viscosity thereof all can diminish, the fluid simultaneously maintaining low speed flowing in pit makes tangential force diminish, thus reaches the effect reducing the moment of swaying.In addition, the bearing that in pit, the fluid picture of low speeds flow rolls, avoids swiftly flowing fluid above and directly contacts with impeller wall, avoid the rapid increase of velocity gradient, thus avoid a large amount of generations in whirlpool, prevent dissipation of energy, reach the object of Synergistic and energy-saving.

The pressure side exit region of described guide wheel 3 blade is uniformly distributed mastoid process cell cube and forms bionical mastoid process structure, the span of mastoid process cell cube radius R is 0.04mm ~ 0.1mm, the span of height H is 0.06mm ~ 0.16mm, and the span of the spacing Wr between mastoid process cell cube is 0.1mm ~ 0.25mm.

The value of the height H of described mastoid process cell cube, radius R, cell cube spacing height H is preferably H × R × R=0.16mm × 0.1mm × 0.1mm, spacing Wr=100 μm.

In the fluid flow process of reality, the pressure side exit region of torque converter reactor blade easily produces acyclic flow separation, especially in the tail region (exit region) of pressure side, liquid stream has higher turbulivity usually, the flow stream velocity of blade near wall is relatively large, cause skin friction drag and velocity gradient also can strain greatly mutually, energy loss is comparatively serious, therefore the present invention is provided with bionical mastoid process structure at its pressure side exit region, bionic blade surface is now super hydrophobic surface, skin friction drag can be reduced, improve flowing state.

The present invention is conceived to interaction mechanics between fluid torque converter and flowing medium and kinematic relation, adopt modern bionics principle, bionic coupling is theoretical, by bionical for fish body, U-shaped bionical groove, non-smooth surface, hydrophobic surface four factors is dissolved in the design of twin-turbine torque converter, by improving inner flowing state, reduce the pressure drag of stickiness stress and part area, angle is imported and exported in eliminating, center line of flow path radius, when the parameters such as lobe numbers are for torque-converters performance impact, by the circular rector partition function of change blade and at impeller blade surface portion region processing pit, groove, mastoid process biomimetic features improves fluid torque converter performance, reach the object of energy efficiency, serve good drag-reduction effect.

Accompanying drawing explanation

Below in conjunction with the drawings and specific embodiments, the present invention is described in further detail.

Fig. 1 is twin-turbine torque converter structural representation.

Fig. 2 is Blade measuring parameter schematic diagram.

Fig. 3 a, Fig. 3 b are respectively the blade schematic diagram of prior art second turbine and the second turbine blade schematic diagram of the present invention.Fig. 3 c, Fig. 3 d, Fig. 3 e are starting torque, efficiency, capacity coefficient comparison diagram when in original conventional torque-converters and the present invention, the second turbine adopts bionic blade.

Fig. 4 a, Fig. 4 b are respectively the blade schematic diagram of prior art first turbine and the first turbine blade schematic diagram of the present invention.Fig. 4 c, Fig. 4 d, Fig. 4 e are starting torque, efficiency, capacity coefficient comparison diagram when in original conventional torque-converters and the present invention, the first turbine adopts bionic blade.

Fig. 5 a, Fig. 5 b are respectively the blade schematic diagram of prior art pump impeller and pump impeller blade schematic diagram of the present invention.Fig. 5 c, Fig. 5 d, Fig. 5 e are starting torque, efficiency, capacity coefficient comparison diagram when in original conventional torque-converters and the present invention, pump impeller adopts bionic blade.

Fig. 6 a, Fig. 6 b are respectively the blade schematic diagram of prior art guide wheel and guide vane schematic diagram of the present invention.Fig. 6 c, Fig. 6 d, Fig. 6 e are starting torque, efficiency, capacity coefficient comparison diagram when in original conventional torque-converters and the present invention, guide wheel adopts bionic blade.

Fig. 7 is U-shaped bionical groove microcosmic schematic diagram.

Fig. 8 is the guide vane schematic diagram with U-shaped bionical groove.

Fig. 9 a, Fig. 9 b are pump impeller outer shroud, pump impeller inner ring enlarged view respectively.

Figure 10 a, Figure 10 b are sectional view and the plan view of pit matrix part respectively.

Figure 11 a, Figure 11 b, Figure 11 c, Figure 11 d are the rectangular arranged of pit matrix, equal-difference arrangement, diamond array and random alignment mode schematic diagram respectively.

Figure 12 is the drag-reduction effect schematic diagram under four kinds of arrangement modes of pit matrix.

Figure 13 has the guide vane structural representation of mastoid process biomimetic features.

Figure 14 a, Figure 14 b are mastoid process cell cube schematic diagram, mastoid process biomimetic features partial enlarged drawing.

Figure 15 is that the detent torque of the twin-turbine torque converter and original conventional twin-turbine torque converter that the present invention has many bionics feature contrasts.

Figure 16 is that the present invention has the twin-turbine torque converter of many bionics feature and the efficiency comparative of original conventional twin-turbine torque converter.

Figure 17 is that the capacity coefficient of the twin-turbine torque converter and original conventional twin-turbine torque converter that the present invention has many bionics feature contrasts.

Embodiment:

As shown in Figure 1, YJSW335 twin-turbine torque converter comprises pump impeller 1, pump impeller outer shroud 11, pump impeller inner ring 12, first turbine 2, guide wheel 3, the second turbine 4.

In twin-turbine torque converter, the Blade measuring parameter of each constituent element as shown in Figure 2, comprises the chord length in cross section, thickness, maximum camber, inlet angle, exit angle etc.

1. bionic blade

1.1 second turbine bionic blades,

The present invention adopts bionics techniques to change its circular rector partition function not changing on other structural parameter bases of the second turbine blade, and circular rector partition function multinomial is: y=ax ²+ bx+c.Wherein x is the abscissa of each equal diversion point on mean camber line, and y is corresponding circular rector apportioning cost.The span of parameter a, b, c is as follows:

$\left\{\begin{array}{c}-0.8972\&le;a\&le;-0.4629\\ -0.4886\&le;b\&le;-0.1032\\ 0.4709\&le;c\&le;1.5079\end{array}\right.$

Use ISIGHT Optimization Software to parameter a, b, c is optimized, in conjunction with the parameter a obtained, the span of b, c, take torque converter as objective function, select Latin hypercube method to choose sample point, application Radial Basis Function Method builds agent model, selects non-dominated sorted genetic algorithm to be optimized.Optimum results is as shown in table 1.

Table 1

a	b	c	η
				-0.8972	-0.422	1.258	81.28％
-0.882	-0.462	1.15	80.34％
				-0.867	-0.2891	1.079	82.22％
-0.8527	-0.156	1.043	84.13％
				-0.837	-0.342	1.401	82.98％
-0.822	-0.3162	0.578	81.87％
				-0.8074	-0.303	0.614	80.04％
-0.792	-0.409	0.542	80.24％
				-0.777	-0.4886	1.222	81.65％
-0.762	-0.329	1.329	82.73％
				-0.7471	-0.449	1.186	83.67％

-0.7374	-0.2919	1.0108	84.95％
				-0.717	-0.435	0.4709	84.31％
-0.703	-0.1032	0.864	83.75％
				-0.688	-0.369	1.365	81.99％
-0.6732	-0.382	0.65	84.48％
				-0.658	-0.223	0.9	83.74％
-0.643	-0.13	0.685	81.96％
				-0.628	-0.116	1.115	79.89％
-0.6135	-0.196	0.507	80.19％
				-0.598	-0.2634	1.5079	81.58％
-0.583	-0.236	0.972	78.64％
				-0.5686	-0.276	0.936	82.77％
-0.553	-0.17	0.757	83.42％
				-0.5389	-0.21	0.721	83.29％
-0.523	-0.1835	1.472	83.71％
				-0.508	-0.475	0.828	81.09％
-0.4938	-0.249	0.793	82.34％
				-0.478	-0.3566	1.436	83.41％
-0.4629	-0.396	1.293	82.63％

Wherein, work as a=-0.7374, when b=-0.2919, c=1.0108, the best performance of bionic blade.Circular rector partition function is now as follows:

y＝-0.7374x ²–0.2919x+1.0108

The inlet angle of the second turbine bionic blade leading edge is 43 °, the exit angle of trailing edge is 135.5 °, the height (maximum camber) of blade integral is 43.67mm, axial length (chord length) from import to outlet is 106.83mm, and blade shape is to such as shown in Fig. 3 a, 3b.

Bionical second turbine blade is become fluid torque converter with conventional pump impeller with guide wheel and the first turbine matched combined, its torque ratio, efficiency, pump impeller capacity coefficient contrast situation as shown in Fig. 3 c, Fig. 3 d, Fig. 3 e (in figure, abscissa is velocity ratio).On starting torque ratio, fluid torque converter starting torque 4.35 after the second turbine employing bionic blade, the starting torque adopting common blade is 4.27.Second turbine adopts bionic blade peak efficiency value to be 84.95%; , the peak efficiency value adopting common blade is 83.16%; The contrast of pump impeller capacity coefficient CF show the second turbine adopt bionic blade after the pump impeller capacity coefficient of fluid torque converter be greater than conventional bionic blade value; Biomimetic type fluid torque converter performance is better than original fluid torque converter.

1.2 first turbine bionic blades

The present invention changes its circular rector partition function on the basis not changing first other structural parameter of turbine blade, and the multinomial of circular rector partition function is: y=ax ⁴+ bx ³+ cx ²+ dx+e, wherein x is the abscissa of each equal diversion point on mean camber line, and y is corresponding circular rector apportioning cost.The span of parameter a, b, c, d, e is as follows:

$\left\{\begin{array}{c}3.0619\&le;a\&le;6.0894\\ -6.0787\&le;b\&le;-3.8151\\ -0.406\&le;c\&le;0.0147\\ -0.1814\&le;d\&le;0.4725\\ 0.5972\&le;e\&le;1.5149\end{array}\right.$

Use ISIGHT Optimization Software to parameter a, b, c, d, e are optimized, in conjunction with the parameter a obtained, b, the span of c, d, e, take torque converter as objective function, select Latin hypercube method to choose sample point, application Radial Basis Function Method builds agent model, selects non-dominated sorted genetic algorithm to be optimized.Optimum results is as shown in table 2.

Table 2

a	b	c	d	e	η
						3.0619	-4.674	-0.203	0.292	1.262	82.64％
3.17	-6.0787	-0.101	0.4725	0.977	79.26％
						3.276	-5.376	-0.043	0.224	1.42	81.31％
3.38	-5.142	-0.014	-0.136	1.009	78.19％
						3.48	-5.298	-0.246	0.022	0.882	79.28％
3.582	-5.845	-0.058	-0.1814	1.198	83.07％
						3.69	-4.908	-0.232	0.427	0.945	82.49％
3.7997	-4.596	-0.391	0.36	0.85	81.67％
						3.9	-6.001	-0.406	0.45	1.483	81.34％
4	-4.986	-0.174	-0.159	1.388	80.97％
						4.1141	-5.08	-0.1494	0.1369	0.9918	83.57％
4.21	-5.61	-0.362	0.315	0.914	81.11％
						4.31	-3.8151	-0.29	0.27	1.293	83.26％
4.42	-5.688	-0.217	0.247	1.04	81.03％
						4.5228	-4.127	-0.087	0.044	1.357	80.92％
4.63	-4.283	-0.377	-0.0466	0.629	79.77％
						4.73	-5.064	-0.275	-0.001	0.66	76.29％

4.8437	-4.752	-0.159	0.089	1.167	79.16％
						4.94	-5.532	-0.188	0.1797	0.755	80.27％
5.05	-5.22	-0.072	0.067	1.452	81.21％
						5.159	-3.893	-0.348	0.1124	1.23	82.99％
5.25	-4.83	-0.116	0.337	0.692	81.45％
						5.367	-5.766	-0.333	-0.024	0.819	82.56％
5.46	-3.971	-0.029	0.2029	0.5972	81.79％
						5.5755	-4.361	-0.304	-0.069	1.5149	80.66％
5.67	-4.44	0	-0.114	1.072	79.81％
						5.78	-4.518	0.0147	0.405	1.135	80.37％
5.881	-4.049	-0.261	0.1348	0.724	81.61％
						5.99	-4.205	-0.145	0.382	0.787	79.54％
6.0894	-5.923	-0.13	-0.0911	1.325	82.25％

Wherein, work as a=4.1141, when b=-5.08, c=-0.1494, d=0.1369, e=0.9918, torque-converters most effective, the best performance of bionic blade, circular rector partition function is now as follows:

y＝4.1141x ⁴-5.08x ³-0.1494x ²+0.1369x+0.9918

The inlet angle of the first turbine bionic blade leading edge is 118.5 °, apothem is 5.11mm, the exit angle of trailing edge is 152 °, its apothem is 0.32mm, length is about 3.6 ~ 4mm, the height (maximum camber) of blade integral is 22.29mm, and the axial length (chord length) from import to outlet is 31.03mm.

Bionical first turbine blade is become fluid torque converter with original pump impeller with guide wheel and the second turbine matched combined, and its torque ratio, efficiency, pump impeller capacity coefficient contrast situation is as shown in Fig. 4 c, Fig. 4 d, Fig. 4 e.On starting torque ratio, after the first turbine employing bionic blade, fluid torque converter is 4.38, adopts common blade 4.27.For efficiency, after the first turbine employing bionic blade, the peak efficiency of fluid torque converter is 83.57%, by the peak efficiency 83.16% of common blade; In the contrast of pump impeller capacity coefficient CF, after the first turbine adopts bionic blade, the pump impeller capacity coefficient of fluid torque converter is greater than employing common blade; Biomimetic type fluid torque converter performance is better than original fluid torque converter.

1.3 pump impeller bionic blades

The present invention adopts bionics techniques to change its circular rector partition function not changing on other structural parameter bases of pump impeller blade, and the multinomial of circular rector partition function is: y=ax ³+ bx ²+ cx+d.Wherein x is the abscissa of each equal diversion point on mean camber line, and y is corresponding circular rector apportioning cost.The span of parameter a, b, c, d is as follows:

$\left\{\begin{array}{c}-1.4827\&le;a\&le;-0.7116\\ -1.7632\&le;b\&le;-0.8364\\ 0.0377\&le;c\&le;1.1008\\ -0.3767\&le;d\&le;0.3645\end{array}\right..$

Use ISIGHT Optimization Software to parameter a, b, c, d are optimized, in conjunction with the parameter a obtained, the span of b, c, d, take torque converter as objective function, select Latin hypercube method to choose sample point, application Radial Basis Function Method builds agent model, selects non-dominated sorted genetic algorithm to be optimized.Optimize as shown in table 3.

Table 3

a	b	c	d	η
					-1.4827	-1.635	0.0377	-0.07	83.78％
-1.456	-1.571	0.294	0.211	81.95％
					-1.43	-1.22	0.734	0.083	80.24％
-1.403	-1.508	0.111	-0.198	79.64％
					-1.376	-1.667	0.514	0.007	83.97％
-1.35	-0.996	0.918	-0.121	82.44％
					-1.323	-1.7632	1.027	-0.3	81.79％
-1.297	-1.731	0.184	-0.096	82.31％
					-1.27	-1.444	0.881	0.3645	81.48％
-1.243	-1.348	0.331	0.058	82.12％
					-1.217	-1.124	0.258	0.339	80.04％
-1.19	-1.476	0.478	0.237	78.62％
					-1.164	-1.252	0.661	-0.274	79.49％
-1.137	-0.932	0.771	-0.172	80.17％
					-1.1129	-1.3475	0.7683	-0.0009	84.60％
-1.084	-1.699	0.954	0.186	83.29％
					-1.057	-0.964	0.551	-0.326	81.23％
-1.031	-1.06	0.368	-0.223	80.75％
					-1.004	-1.028	0.991	0.109	82.09％
-0.977	-1.38	0.148	0.16	83.16％
					-0.951	-1.092	0.074	0.134	81.21％
-0.924	-0.868	0.698	-0.3767	82.67％

-0.898	-1.539	0.844	0.032	83.16％
					-0.871	-1.412	0.624	-0.351	81.92％
-0.845	-1.284	1.064	-0.147	81.88％
					-0.818	-1.156	0.221	0.262	80.13％
-0.791	-1.316	0.404	-0.019	81.61％
					-0.765	-0.9	1.1008	0.288	81.26％
-0.738	-0.8364	0.441	0.313	80.35％
					-0.7116	-1.603	0.588	-0.044	82.79％

Wherein, work as a=-1.1129, when b=-1.3475, c=0.7683, d=-0.0009, fluid torque converter most effective, the best performance of bionic blade.Circular rector partition function is now as follows:

y＝-1.1129x ³-1.3475x ²+0.7683x-0.0009

The inlet angle of pump impeller bionic blade leading edge is 110 °, the exit angle of trailing edge is 78.5 °, the height (maximum camber) of blade integral is 55.13mm, and the axial length (chord length) from import to outlet is 96.89mm, and blade shape is to such as shown in Fig. 5 a, 5b.

Bionic pump impeller blade is become fluid torque converter with conventional second turbine with guide wheel and the first turbine matched combined, and its torque ratio, efficiency, pump impeller capacity coefficient contrast situation is as shown in Fig. 5 c, Fig. 5 d, Fig. 5 e.On starting torque ratio, pump impeller adopts bionic blade and adopts common blade fluid torque converter starting torque to be respectively 4.31,4.27.On efficiency curve, pump impeller adopts the peak efficiency 84.6% of the fluid torque converter that bionic blade is corresponding, and the peak efficiency adopting common blade is 83.16%; On pump impeller capacity coefficient CF, the pump impeller capacity coefficient of fluid torque converter corresponding to common blade is less than employing bionic blade, and the two difference is less, and biomimetic type fluid torque converter performance is better than original fluid torque converter.

1.4 guide wheel bionic blades

The present invention adopts bionics techniques to change its circular rector partition function not changing on other structural parameter bases of guide vane, and the multinomial of circular rector partition function is: y=ax ³+ bx ²+ cx+d.Wherein x is the abscissa of each equal diversion point on mean camber line, and y is corresponding circular rector apportioning cost.The span of parameter a, b, c, d is as follows:

$\left\{\begin{array}{c}0.6044\&le;a\&le;1.4151\\ -0.5792\&le;b\&le;-0.1698\\ -0.1989\&le;c\&le;0.581\\ -0.4221\&le;d\&le;0.3746\end{array}\right.$

Use ISIGHT Optimization Software to parameter a, b, c, d is optimized, in conjunction with the parameter a obtained, b, c, the span of d, take torque converter as objective function, select Latin hypercube method to choose sample point, application Radial Basis Function Method builds agent model, selection non-dominated sorted genetic algorithm is optimized, as shown in table 4.

Table 4

a	b	c	d	η
					0.6044	-0.184	0.42	0.292	81.69％
0.632	-0.297	0.178	0.155	80.16％
					0.66	-0.311	0.204	-0.257	79.28％
0.688	-0.1698	-0.038	-0.092	79.66％
					0.716	-0.5792	-0.091	0.21	82.91％
0.744	-0.537	0.312	0.1	81.37％
					0.772	-0.283	0.554	-0.23	82.11％
0.8	-0.353	-0.118	-0.34	83.08％
					0.828	-0.48	0.097	-0.202	80.06％
0.856	-0.339	0.043	-0.01	79.15％
					0.884	-0.255	0.5	0.32	78.97％
0.912	-0.367	0.258	0.347	83.13％
					0.94	-0.466	-0.064	-0.065	82.76％
0.968	-0.325	-0.145	0.127	81.43％
					0.992	-0.192	0.1936	-0.0058	83.79％
1.024	-0.494	0.366	-0.147	82.19％
					1.052	-0.509	-0.011	-0.312	80.61％
1.08	-0.551	0.393	-0.395	82.22％
					1.108	-0.24	0.151	-0.037	81.94％
1.136	-0.452	0.339	-0.4221	82.42％
					1.164	-0.523	0.473	-0.367	80.36％
1.191	-0.41	-0.172	0.045	80.69％
					1.219	-0.382	0.231	-0.175	81.59％
1.247	-0.212	0.285	0.182	82.73％
					1.275	-0.424	0.016	0.3746	80.92％
1.303	-0.438	0.527	-0.12	78.87％
					1.331	-0.198	0.581	-0.285	79.46％
1.359	-0.226	0.447	0.072	79.81％
					1.387	-0.269	0.124	0.017	80.62％

1.4151

-0.396

-0.1989

0.265

81.73％

Wherein, work as a=0.992, when b=-0.192, c=0.1936, d=-0.0058, the efficiency of fluid torque converter reaches the highest, the best performance of bionic blade.Now circular rector partition function is as follows:

y＝0.992x ³-0.192x ²+0.1936x-0.0058

The inlet angle of guide wheel bionic blade leading edge is 83 °, the exit angle of trailing edge is 30 °, the height (maximum camber) of blade integral is 44.08mm, and the axial length (chord length) from import to outlet is 28.81mm, and blade shape is to such as shown in Fig. 6 a, 6b.

Bionical guide vane is become fluid torque converter with conventional second turbine with pump impeller and the first turbine matched combined, and its torque ratio, efficiency, pump impeller capacity coefficient contrast situation is as shown in Fig. 6 c, Fig. 6 d, Fig. 6 e.On starting torque ratio, the fluid torque converter that bionical guide vane is corresponding is 4.43, and the fluid torque converter that common blade is corresponding is 4.27.For efficiency, the peak efficiency value that bionical guide vane is corresponding is respectively 83.79%; The peak efficiency value that common blade is corresponding is 83.16%; The contrast display of pump impeller capacity coefficient CF, the pump impeller capacity coefficient of fluid torque converter corresponding to common blade is less than bionic blade value; Biomimetic type fluid torque converter performance is better than original fluid torque converter.

The fluted guide wheel bionic blade of 2 tool

The present invention arranges near the front portion of blade inlet that on guide vane suction surface U-shaped bionical groove is with the flowing of interference edge interlayer.The microstructure of bionical groove as shown in Figure 7.The flowing property of groove pitch s and the height size design of h and fluid is closely related.According to a large amount of CFD simulation results, as its height h and the dimensionless size 0 < h of distance s ⁺≤ 25 and 0 < s ⁺when≤30, there is property of reduction drag, now, by formula s=s ⁺ν/V _τand h=h ⁺ν/V _τthe span of s and h calculated is 0 < s≤0.83mm, 0 < h≤1mm.Wherein ν is fluid motion viscosity, V _τ=(τ ₀/ ρ) ^0.5for blade wall shearing speed; ρ is fluid density, τ ₀for blade wall shearing stress.Wherein blade wall shearing stress τ ₀combined by Blasius friction factor and Fanning friction factor and approximate to solve:

$\left\{\begin{array}{c}{C}_{f,B}=0.0791{(V_{0}d/v)}^{-1/4}\\ C_{f,F}=2{\mathrm{\&tau;}}_0/{\mathrm{\&rho;V}}_0^2\\ C_{f,B}=C_{f,F}\end{array}\right.---\left(3\right)$

Obtaining wall shearing stress is:

τ ₀＝0.03955ν ^1/4ρV ₀ ^7/4d ^-1/4(4)

Wherein ν is fluid motion viscosity, and d=4A/D is runner hydraulic diameter, and A is cross-section area, and D is wetted perimeter, τ ₀for wall shearing stress, ρ is fluid density, V ₀for average flow velocity.

ISIGHT Optimization Software is used to be optimized parameter h and s, in conjunction with the span of the parameter h obtained and s, take torque converter as objective function, Latin hypercube method is selected to choose sample point, application Radial Basis Function Method builds agent model, selects non-dominated sorted genetic algorithm to be optimized.Optimum results is as shown in table 5.

Table 5

h	s	η
			0	0.63	0.76％
0.034	0.401	-5.34％
			0.069	0.172	6.28％
0.103	0.114	1.46％
			0.138	0.716	-2.52％
0.172	0.2	9.15％
			0.207	0.258	8.63％
0.241	0.286	7.22％
			0.276	0.229	6.45％
0.31	0.572	-1.29％
			0.345	0	0.25％
0.379	0.801	1.87％
			0.414	0.372	6.49％
0.448	0.143	7.14％
			0.483	0.658	8.21％
0.5	0.5	10.87％
			0.552	0.83	0.89％
0.586	0.057	1.73％
			0.621	0.687	-5.64％
0.655	0.086	9.13％
			0.69	0.487	-3.92％
0.724	0.343	6.41％
			0.759	0.773	5.49％
0.793	0.429	6.57％
			0.828	0.029	7.23％

0.862	0.515	10.16％
			0.897	0.458	7.68％
0.931	0.544	8.19％
			0.966	0.744	7.34％
1	0.315	6.81％

As seen from the above table, h=h is worked as ⁺ν/V _τ=0.5mm, s=s ⁺ν/V _τduring=0.5mm, drag-reduction effect is best, and maximum drag reducing efficiency is 10.87%.

The bionical trench region initial part distance of positions is L from the distance of blade inlet ₁=7.43mm, meanwhile, the position, end of trench region is L from the distance of blade exit ₂=11.52mm, the concrete distributing position of bionical groove is shown in Fig. 8, because when liquid stream directly impacts blade along upstream blade Way out, this region has positive pressure gradient, liquid speed is reduced very fast, finally causing the generation of the separation of boundary layer, the generation of whirlpool and diffusion, the separation of flow and Secondary Flow, is the region that flow losses are the most serious.

The 3 pump impeller inner and outer rings with pit Non-smooth surface bionic form

In turbulent flow, the thickness in boundary layer is higher means that the loss of kinetic energy is larger, the basic principle of bionic non-smooth surface drag reduction is to reduce boundary layer thickness, postpone or inhibit the flow separation of inside boundary, therefore the size of bionic, non-smooth cell cube depth S can be estimated by the thickness in boundary layer.The following formula of the present invention estimates the depth S of Non-smooth surface cell cube, y ⁺<30 ~ 70, y≤0.2 δ, wherein δ is boundary layer thickness, here y (i.e. S) degree of depth that is Non-smooth surface cell cube.The boundary layer thickness Flat Plate Turbulent Boundary Layer thickness formula of pump impeller inner and outer rings is estimated.Get single runner as computational fields, the radial arc length l of inner and outer rings is respectively 60mm, 118mm, and the radial flow rates on liquid stream relative pump impeller inner and outer rings surface in whole transmission process is U _∞=4.34 ~ 8.2m/s, utilizes the thickness in following formulae discovery boundary layer.

$\left\{\begin{array}{c}\mathrm{\&delta;}0.37{\mathrm{lRe}}^{-1/5}\\ \mathrm{Re}=U_{\mathrm{\&infin;}}l/v\end{array}\right.---\left(5\right)$

In formula, l is Mean length, and Re is reynolds' number, kinematic viscosity coefficient ν=3 × 10 of Fluid-transmission oil ^-5m ²/ s, the result of calculation of boundary layer thickness is as shown in table 2.2

Table 2.2 model boundary layer thickness

Therefore, the span of Non-smooth surface cell cube depth S is 0.64mm ~ 1.24mm, and the diameter D span of Non-smooth surface cell cube is 1.28 ~ 2.48.During design pit type cell cube size, the following parameter of main consideration: diameter D, horizontal spacing W, longitudinal pitch L and pit depth S, is shown in Figure 10 a, Figure 10 b.The present invention chooses D=2mm, W=3mm, L=5mm, S=1mm, with four kinds of arrangement modes, process on the inner and outer rings surface of face of fluid torque converter, four kinds of common arranging methods, are shown in Figure 11 a (matrix arrangement), Figure 11 b (equal-difference arrangement), Figure 11 c (diamond array), Figure 11 d (random alignment).Carry out CFD Simulation Evaluation to single runner, in order to verify the drag-reduction effect of non-smooth surface, drag reducing efficiency is defined as

$\frac{C_{SM}-C_{NS}}{C_{SM}}\&times;100\%---\left(6\right)$

Wherein C _nSand C _sMby viscous force factor C respectively on non-smooth surface and smooth surface _vand press factors C _ptotal coefficient of composition, viscous force factor C _vand press factors C _pbe defined as respectively

$C_V=\frac{F_V}{1/2{\mathrm{\&rho;v}}^{2}A}$ And $C_p=\frac{F_p}{1/2{\mathrm{\&rho;v}}^{2}A}---\left(7\right)$

In formula, v is the mean velocity of fluid on pump impeller housing, and ρ is fluid density, and A is the area on surface of shell.Figure 12 is the drag-reduction effect of four kinds of arrangement modes under the inlet velocity condition of 4 ~ 8m/s.In four kinds of arrangement modes, rectangular arranged drag-reduction effect is best, and drag reducing efficiency can reach 6%.Therefore, Non-smooth surface cell cube with rectangular arrangement pattern, processes on the inner and outer rings surface of face of fluid torque converter, sees Fig. 9 a, Fig. 9 b by the present invention.

The 4 torque converter reactor blades with mastoid process hydrophobic surface

In the fluid flow process of reality, the pressure side exit region of torque converter reactor blade easily produces acyclic flow separation, especially in the tail region (exit region) of pressure side, liquid stream has higher turbulivity usually, the flow stream velocity of blade near wall is relatively large, and cause skin friction drag and velocity gradient also can strain mutually greatly, energy loss is comparatively serious, therefore the present invention is provided with bionical mastoid process structure at its pressure side exit region, as shown in figure 13.According to a large amount of analysis results, the span of the radius R of mastoid process structure is designed to 0.04mm ~ 0.1mm by the present invention, the span of mastoid process Non-smooth surface unit height of projection H is 0.06mm ~ 0.16mm, and the spacing Wr scope 0.1mm ~ 0.25mm of mastoid process cell cube, as shown in Figure 14 a, Figure 14 b.In this case, the wrapping angle of water droplet on blade mastoid process body structure surface is greater than 150 °, and be super hydrophobic surface, bionic blade now can reduce skin friction drag, improves flowing state.The mastoid process cell cube of to be design size the be H × R × R=0.16mm × 0.1mm × 0.1mm of Figure 13 display, spacing Wr is 100 μm, and wrapping angle reaches 157.6 °.Mastoid process cell cube group is distributed in blade pressure surface afterbody, is evenly distributed, and the overall width Lt of head area is 15mm, and particular location as shown in figure 13.

5 twin-turbine torque converters with multi-biological characteristic

By the design of each bionical parts above-mentioned, consider the requirement of twin-turbine torque converter properties, original blade in each active wheel is replaced to bionic blade, thus composition bionic blade group, on this basis, pump impeller inner and outer rings surface portion region processing is become the non-smooth surface of pit type, simultaneously, the suction surface of bionical guide vane is arranged U-shaped bionical groove, mastoid process hydrophobic surface is set at pressure side.Finally, bionic blade group, bionical groove, non-smooth surface, hydrophobic surface four factors are dissolved in twin-turbine torque converter, invent a kind of bionic coupling twin-turbine torque converter with multiple biological characteristic.

By contrast, starting torque is than upper, and biomimetic type is elevated to 4.45 from 4.27 for biomimetic type fluid torque converter and conventional torque-converters, refers to accompanying drawing 15.Be respectively 83.16%, 84.67% in the slow-speed of revolution than with the peak efficiency value in high rotating ratio interval, the numerical value of raising is respectively 1.19,1.51 percentage point, under speed ratio 0.6 operating mode, minimum efficiency brings up to 67.39% from 64.18%, refers to accompanying drawing 15, Figure 16, Figure 17.The change of pump impeller capacity coefficient CF bionic blade group is less, refers to Figure 17.In sum, compared to original torque-converters, starting torque and the peak efficiency of biomimetic type fluid torque converter increase all to some extent, illustrate that the Bionic Design of hydrodynamic unit can reduce its hydraulic losses, there is good drag reduction synergistic effect, improve its working efficiency, thus improve the service behaviour of complete machine.

Claims (10)

1. a bionical twin-turbine torque converter, comprises pump impeller (1), pump impeller outer shroud (11), pump impeller inner ring (12), the first turbine (2), guide wheel (3), the second turbine (4); It is characterized in that the blade of described pump impeller (1) adopts bionic blade, the multinomial of its circular rector partition function is: y=ax ³+ bx ²+ cx+d, wherein x is the abscissa of each equal diversion point on mean camber line, and y is corresponding circular rector apportioning cost, and the span of ginseng a, b, c, d is as follows:

$\left\{\begin{array}{c}-1.4827\&le;a\&le;-0.7116\\ -1.7632\&le;b\&le;-0.8364\\ 0.0377\&le;c\&le;1.1008\\ -0.3767\&le;d\&le;0.3645\end{array}\right..$

2. bionical twin-turbine torque converter according to claim 1, is characterized in that a=-1.1129, b=-1.3475, c=0.7683, d=-0.0009.

3. bionical twin-turbine torque converter according to claim 1, it is characterized in that the blade of described second turbine (4) adopts bionic blade, its circular rector partition function multinomial is: y=ax ²+ bx+c, wherein x is the abscissa of each equal diversion point on mean camber line, and y is corresponding circular rector apportioning cost; The span of parameter a, b, c is as follows:

$\left\{\begin{array}{c}-0.8972\&le;a\&le;-0.4629\\ -0.4886\&le;b\&le;-0.1032\\ 0.4709\&le;c\&le;1.5079\\ \end{array}\right..$

4. bionical twin-turbine torque converter according to claim 3, it is characterized in that the blade of described guide wheel (3) adopts bionic blade, the multinomial of its circular rector partition function is: y=ax ³+ bx ²+ cx+d, wherein x is the abscissa of each equal diversion point on mean camber line, and y is corresponding circular rector apportioning cost, and the span of parameter a, b, c, d is as follows:

$\left\{\begin{array}{c}0.6044\&le;a\&le;1.4151\\ -0.5792\&le;b\&le;-0.1698\\ -0.1989\&le;c\&le;0.581\\ -0.4221\&le;d\&le;0.3746\end{array}\right..$

5. bionical twin-turbine torque converter according to claim 4, the blade suction surface that it is characterized in that described guide wheel (3) arranges U-shaped bionical groove near the front portion of blade inlet, the height h of this bionical groove and the dimensionless size h of distance s ⁺and s ⁺span be respectively 0 < h ⁺≤ 25,0 < s ⁺≤ 30.

6. bionical twin-turbine torque converter according to claim 1, it is characterized in that the blade of described first turbine (2) adopts bionic blade, the multinomial of its circular rector partition function is: y=ax ⁴+ bx ³+ cx ²+ dx+e, wherein x is the abscissa of each equal diversion point on mean camber line, and y is corresponding circular rector apportioning cost, and the span of parameter a, b, c, d, e is as follows:

$\left\{\begin{array}{c}3.0619\&le;a\&le;6.0894\\ -6.0787\&le;b\&le;-3.8151\\ -0.406\&le;c\&le;0.0147\\ -0.1814\&le;d\&le;0.4725\\ 0.5972\&le;e\&le;1.5149\end{array}\right.$

The blade suction surface of described guide wheel (3) arranges U-shaped bionical groove near the front portion of blade inlet, the height h of this bionical groove and the dimensionless size h of distance s ⁺and s ⁺span be respectively 0 < h ⁺≤ 25,0 < s ⁺≤ 30.

7. bionical twin-turbine torque converter according to claim 5, is characterized in that described pump impeller inner ring and pump impeller outer shroud are distributed with spherical pit.

8. bionical twin-turbine torque converter according to claim 7, is characterized in that described pit is matrix arrangement.

9. bionical twin-turbine torque converter according to claim 8, is characterized in that the depth S of described pit, diameter D, horizontal spacing W and longitudinal pitch L value are S=1mm, D=2mm, W=3mm, L=5mm.

10. bionical twin-turbine torque converter according to claim 5, it is characterized in that the pressure side exit region of described guide wheel (3) blade is uniformly distributed mastoid process cell cube and forms bionical mastoid process structure, the span of mastoid process cell cube radius R is 0.04mm ~ 0.1mm, the span of height H is 0.06mm ~ 0.16mm, and the span of the spacing Wr between mastoid process cell cube is 0.1mm ~ 0.25mm.