CN204186916U - Hydraulic single-turbine torque converter - Google Patents
Hydraulic single-turbine torque converter Download PDFInfo
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Abstract
A kind of hydraulic single-turbine torque converter, circulate circle diameter D=370 ~ 390mm; Pump impeller blade outer shroud inlet angle is β
p1=104 ° ~ 114 °, outer shroud exit angle is β
p2=79 ° ~ 89 °, outer shroud inlet side thickness H
p1=7 ~ 8mm, outer shroud Exit-edge thickness H
p2=3.2 ~ 4.2mm, inner ring inlet angle is β
p3=104 ° ~ 114 °, inner ring exit angle is β
p4=83 ° ~ 93 °, inner ring inlet side thickness H
p3=4 ~ 5mm, inner ring Exit-edge thickness H
p4=2.5 ~ 3.5mm; Turbine blade outer shroud inlet angle is β
t1=42 ° ~ 50 °, outer shroud exit angle is β
t2=140 ° ~ 150 °, outer shroud inlet side thickness H
t1=2 ~ 2.5mm, outer shroud Exit-edge thickness H
t2=2 ~ 2.5mm; Its advantage is the pump impeller nominal torque MBg0=250 ~ 258Nm under stall operating mode, stall torque is than K0=2.25 ~ 2.38, the peak efficiency value of torque-converters is 0.896 ~ 0.920, it is more reasonable to mate with 1850rpm, 131KW diesel engine, efficiency is higher, ensure that bulldozer has good overall performance, particularly there is excellent power performance and fuel economy.
Description
Technical field
The utility model relates to a kind of hydraulic single-turbine torque converter being applied to engineering machinery, particularly relates to a kind of hydraulic single-turbine torque converter being applied to loader.
Background technique
Along with the develop rapidly of the every building cause of China, the demand of various engineering machinery sharply increases.Bulldozer, as one of representational machine of most in the native Transportation Engineering machinery of shovel, is an entirety of being got up by many component combinations.Fluid torque converter is the vitals of bulldozer, and the quality of its design parameter will directly have influence on the quality of bulldozer overall performance.What require power performance, fuel economy, travelling comfort along with bulldozer improves constantly, exploitation high performance and energy-saving bulldozer becomes current top priority, and the hydraulic single-turbine torque converter accordingly as Bulldozer core component must also carry out redesigning and researching and developing thereupon.
Existing bulldozer, it generally all adopts rated speed to be 1850rpm, and rated power is about the diesel engine of about 131kw, but hydraulic single-turbine torque converter that is that match exists 3 problems because hydraulic single-turbine torque converter design is unreasonable:
1, the nominal torque MBg0 of stall operating mode is higher, be 270 ~ 285 Nm, when the nominal moment of torsion Mbg0 of stall operating mode is bigger than normal, there will be following problem: (P is power according to rating formula P=MBg0N/ proportionality constant, MBg0 is nominal moment of torsion, N is pump impeller rotating speed, pump impeller is directly connected with motor, the rotating speed of motor is pump impeller rotating speed), under guarantee fluid torque converter can absorb the prerequisite of engine power rating completely (namely P is definite value), stall operating mode nominal moment of torsion Mbg0 and rotating speed N is inversely proportional to, as MBg0 is too high, then N step-down, this also just mean fluid torque converter and motor to mate rotating speed point on the low side, cause the speed of a motor vehicle of bulldozer low, although meet the tractive force requirement of complete machine, but can not meet the speed of a motor vehicle requirement of complete machine, namely combination property is poor,
The converter torque ratio K0 of 2, stall operating mode is less, is 2.0 ~ 2.15, and when torque-converters stall torque is less than K0 value, torque converter curve right avertence, causes that bulldozer fuel utilization ratio is low, energy consumption is high;
Above 2 will cause the problems such as bulldozer whole synthesis poor performance, engine fuel consumption quantity are high.
Model utility content
The purpose of this utility model be exactly the shortcoming that nominal torque is higher, bending moment is smaller for existing bulldozer hydraulic single-turbine torque converter stall operating mode and provide a kind of stall operating mode nominal moment of torsion rationally, stall torque is than large and that peak efficiency is high hydraulic single-turbine torque converter.
Solution of the present utility model is such:
A kind of hydraulic single-turbine torque converter, the diesel engine rated speed matched is 1850rpm, rated power 131KW, the nominal moment of torsion MBg of hydraulic single-turbine torque converter stall operating mode
0=253 ± 5 Nm, maximum torque-converters compares K
0=2.32 ± 0.07, best efficiency point efficiency eta>=89%, includes turbine, blade system that pump impeller, guide wheel are formed and the circulate circle that coordinates with blade system, it is characterized in that: described circulate circle diameter D=370 ~ 390mm; In described blade system, pump impeller blade outer shroud inlet angle is β
p1=104 ° ~ 114 °, outer shroud exit angle is β
p2=79 ° ~ 89 °, outer shroud inlet side thickness H
p1=7 ~ 8mm, outer shroud Exit-edge thickness H
p2=3.2 ~ 4.2mm, inner ring inlet angle is β
p3=104 ° ~ 114 °, inner ring exit angle is β
p4=83 ° ~ 93 °, inner ring inlet side thickness H
p3=4 ~ 5mm, inner ring Exit-edge thickness H
p4=2.5 ~ 3.5mm; Turbine blade outer shroud inlet angle is β
t1=42 ° ~ 50 °, outer shroud exit angle is β
t2=140 ° ~ 150 °, outer shroud inlet side thickness H
1=2 ~ 2.5mm, outer shroud Exit-edge thickness H
t2=2 ~ 2.5mm, inner ring inlet angle is β
t3=43 ° ~ 53 °, inner ring exit angle is β
t4=140 ° ~ 150 °, inner ring inlet side thickness H
3=2 ~ 3mm, inner ring Exit-edge thickness H
t4=5 ~ 6mm; Guide vane outer shroud inlet angle is β
s1=98 ° ~ 108 °, outer shroud exit angle is β
s2=24 ° ~ 34 °, outer shroud inlet side thickness H
s1=6 ~ 7mm, outer shroud Exit-edge thickness H
s2=3.5 ~ 4.5mm, inner ring inlet angle is β
s3=71 ° ~ 81 °, inner ring exit angle is β
s4=12 ° ~ 22 °, inner ring inlet side thickness H
s3=6.4 ~ 7.4mm, inner ring Exit-edge thickness H
s4=3 ~ 4mm.
Technological scheme also comprises more specifically: described circulate circle diameter is 380 ~ 385mm; Pump impeller blade outer shroud inlet angle is β
p1=106 ° ~ 111 °, outer shroud exit angle is β
p2=81 ° ~ 85 °, inner ring inlet angle is β
p3=106 ° ~ 111 °, inner ring exit angle is β
p4=85 ° ~ 90 °; Turbine blade outer shroud inlet angle is β
t1=44 ° ~ 48 °, outer shroud exit angle is β
t2=142 ° ~ 146 °, inner ring inlet angle is β
t3=45 ° ~ 50 °, inner ring exit angle is β
t4=142 ° ~ 146 °; Guide vane outer shroud inlet angle is β
s1=100 ° ~ 106 °, outer shroud exit angle is β
s2=25 ° ~ 32 °, inner ring inlet angle is β
s3=73 ° ~ 75 °, inner ring exit angle is β
s4=15 ° ~ 19 °.
Further: described circulate circle diameter D=370mm; In described blade system, pump impeller blade outer shroud inlet angle is β
p1=111 ° ~ 114 °, outer shroud exit angle is β
p2=79 ° ~ 81 °, inner ring inlet angle is β
p3=111 ° ~ 114 °, inner ring exit angle is β
p4=83 ° ~ 85 °; Turbine blade outer shroud inlet angle is β
t1=42 ° ~ 44 °, outer shroud exit angle is β
t2=146 ° ~ 148 °, inner ring inlet angle is β
t3=43 ° ~ 45 °, inner ring exit angle is β
t4=146 ° ~ 148 °; Guide vane outer shroud inlet angle is β
s1=98 ° ~ 100 °, outer shroud exit angle is β
s2=24 ° ~ 26 °, inner ring inlet angle is β
s3=71 ° ~ 73 °, inner ring exit angle is β
s4=12 ° ~ 15 °.
Further: described circulate circle diameter is 380; Pump impeller blade outer shroud inlet angle is β
p1=108 ° ~ 111 °, outer shroud exit angle is β
p2=81 ° ~ 83 °, inner ring inlet angle is β
p3=108 ° ~ 111 °, inner ring exit angle is β
p4=85 ° ~ 88 °; Turbine blade outer shroud inlet angle is β
t1=44 ° ~ 46 °, outer shroud exit angle is β
t2=144 ° ~ 146 °, inner ring inlet angle is β
t3=45 ° ~ 47 °, inner ring exit angle is β
t4=144 ° ~ 146 °; Guide vane outer shroud inlet angle is β
s1=100 ° ~ 104 °, outer shroud exit angle is β
s2=26 ° ~ 29 °, inner ring inlet angle is β
s3=73 ° ~ 75 °, inner ring exit angle is β
s4=15 ° ~ 17 °.
Further: described circulate circle diameter is D=385mm; Pump impeller blade outer shroud inlet angle is β
p1=106 ° ~ 108 °, outer shroud exit angle is β
p2=83 ° ~ 86 °, inner ring inlet angle is β
p3=106 ° ~ 108 °, inner ring exit angle is β
p4=88 ° ~ 90 °; Turbine blade outer shroud inlet angle is β
t1=46 ° ~ 48 °, outer shroud exit angle is β
t2=142 ° ~ 144 °, inner ring inlet angle is β
t3=47 ° ~ 50 °, inner ring exit angle is β
t4=142 ° ~ 144 °; Guide vane outer shroud inlet angle is β
s1=104 ° ~ 106 °, outer shroud exit angle is β
s2=29 ° ~ 32 °, inner ring inlet angle is β
s3=75 ° ~ 78 °, inner ring exit angle is β
s4=17 ° ~ 19 °.
Further: described circulate circle diameter D=390; In described blade system, pump impeller blade outer shroud inlet angle is β
p1=104 ° ~ 106 °, outer shroud exit angle is β
p2=86 ° ~ 89 °, inner ring inlet angle is β
p3=104 ° ~ 106 °, inner ring exit angle is β
p4=90 ° ~ 93 °; Turbine blade outer shroud inlet angle is β
t1=48 ° ~ 50 °, outer shroud exit angle is β
t2=140 ° ~ 142 °, inner ring inlet angle is β
t3=50 ° ~ 53 °, inner ring exit angle is β
t4=140 ° ~ 142 °; Guide vane outer shroud inlet angle is β
s1=106 ° ~ 108 °, outer shroud exit angle is β
s2=32 ° ~ 34 °, inner ring inlet angle is β
s3=78 ° ~ 81 °, inner ring exit angle is β
s4=19 ° ~ 22 °.
The utility model has the advantages that the pump impeller nominal torque MBg0=246 ~ 262Nm under hydraulic single-turbine torque converter stall operating mode, stall torque is than K0=2.26 ~ 2.42, the peak efficiency value of torque-converters is 0.866 ~ 0.919, it is more reasonable to mate with 1850rpm, 131KW diesel engine, efficiency is higher, ensure that bulldozer has good overall performance, particularly there is excellent power performance and fuel economy.
Accompanying drawing explanation
Accompanying drawing 1 is hydraulic single-turbine torque converter erection drawing;
Accompanying drawing 2 is pump impeller blade figure;
Accompanying drawing 3 is pump impeller blade outer shroud import and export angle, imports and exports limit thickness chart;
Accompanying drawing 4 is pump impeller blade inner ring import and export angle, imports and exports limit thickness chart;
Accompanying drawing 5 is turbine blade figure;
Accompanying drawing 6 is turbine blade outer shroud import and export angle, imports and exports limit thickness chart;
Accompanying drawing 7 is turbine blade inner ring import and export angle, imports and exports limit thickness chart;
Accompanying drawing 8 is guide vane figure;
Accompanying drawing 9 is guide vane outer shroud import and export angle, imports and exports limit thickness chart;
Accompanying drawing 10 is guide vane inner ring import and export angle, imports and exports limit thickness chart;
In accompanying drawing, each parts mark is detailed as follows:
Guide wheel 1, turbine 2, pump impeller 3; PM1 is pump impeller outer shroud, and PM2 is pump impeller inner ring, β
p1for pump impeller blade outer shroud inlet angle, β
p2for pump impeller blade outer shroud exit angle, H
p1for pump impeller blade outer shroud inlet side thickness, H
p2for pump impeller blade outer shroud Exit-edge thickness, β
p3for pump impeller blade inner ring inlet angle, β
p4for pump impeller blade inner ring exit angle, H
p3for pump impeller blade inner ring inlet side thickness, H
p4for pump impeller blade inner ring Exit-edge thickness; TM1 is turbine outer ring, and TM2 is turbine inner ring, β
t1for turbine blade outer shroud inlet angle, β
t2for turbine blade outer shroud exit angle, H
t1for turbine blade outer shroud inlet side thickness, H
t2for turbine blade outer shroud Exit-edge thickness, β
t3for turbine blade inner ring inlet angle, β
t4for turbine blade inner ring exit angle, H
t3for turbine blade inner ring inlet side thickness, H
t4for turbine blade inner ring Exit-edge thickness; SM1 is guide wheel outer shroud, and SM2 is guide wheel inner ring, β
s1for guide vane outer shroud inlet angle, β
s2for guide vane outer shroud exit angle, H
s1for guide vane outer shroud Exit-edge thickness, H
s2for guide vane outer shroud Exit-edge thickness, β
s3for guide vane inner ring inlet angle, β
s4for guide vane inner ring exit angle, H
s3for guide vane inner ring Exit-edge thickness, H
s4for guide vane inner ring Exit-edge thickness.
Embodiment
The hydraulic single-turbine torque converter of the present embodiment, the diesel engine rated speed matched is 1850rpm, rated power 131KW, the nominal moment of torsion MBg of hydraulic single-turbine torque converter stall operating mode
0=246 ~ 262Nm, maximum torque-converters compares K
0=2.26 ~ 2.42, best efficiency point efficiency eta>=89%.
Described circulate circle diameter D=370 ~ 390mm; In described blade system, pump impeller blade outer shroud inlet angle is β
p1=104 ° ~ 114 °, outer shroud exit angle is β
p2=79 ° ~ 89 °, outer shroud inlet side thickness H
p1=7 ~ 8mm, outer shroud Exit-edge thickness H
p2=3.2 ~ 4.2mm, inner ring inlet angle is β
p3=104 ° ~ 114 °, inner ring exit angle is β
p4=83 ° ~ 93 °, inner ring inlet side thickness H
p3=4 ~ 5mm, inner ring Exit-edge thickness H
p4=2.5 ~ 3.5mm; Turbine blade outer shroud inlet angle is β
t1=42 ° ~ 50 °, outer shroud exit angle is β
t2=140 ° ~ 150 °, outer shroud inlet side thickness H
1=2 ~ 2.5mm, outer shroud Exit-edge thickness H
t2=2 ~ 2.5mm, inner ring inlet angle is β
t3=43 ° ~ 53 °, inner ring exit angle is β
t4=140 ° ~ 150 °, inner ring inlet side thickness H
3=2 ~ 3mm, inner ring Exit-edge thickness H
t4=5 ~ 6mm; Guide vane outer shroud inlet angle is β
s1=98 ° ~ 108 °, outer shroud exit angle is β
s2=24 ° ~ 34 °, outer shroud inlet side thickness H
s1=6 ~ 7mm, outer shroud Exit-edge thickness H
s2=3.5 ~ 4.5mm, inner ring inlet angle is β
s3=71 ° ~ 81 °, inner ring exit angle is β
s4=12 ° ~ 22 °, inner ring inlet side thickness H
s3=6.4 ~ 7.4mm, inner ring Exit-edge thickness H
s4=3 ~ 4mm.
Each parameter can optimize value further as follows: described circulate circle diameter is 380 ~ 385mm; Pump impeller blade outer shroud inlet angle is β
p1=106 ° ~ 111 °, outer shroud exit angle is β
p2=81 ° ~ 85 °, inner ring inlet angle is β
p3=106 ° ~ 111 °, inner ring exit angle is β
p4=85 ° ~ 90 °; Turbine blade outer shroud inlet angle is β
t1=44 ° ~ 48 °, outer shroud exit angle is β
t2=142 ° ~ 146 °, inner ring inlet angle is β
t3=45 ° ~ 50 °, inner ring exit angle is β
t4=142 ° ~ 146 °; Guide vane outer shroud inlet angle is β
s1=100 ° ~ 106 °, outer shroud exit angle is β
s2=25 ° ~ 32 °, inner ring inlet angle is β
s3=73 ° ~ 75 °, inner ring exit angle is β
s4=15 ° ~ 19 °.
Embodiment of the present utility model is as follows:
Embodiment 1:
Described circulate circle diameter D=370mm; In described blade system, pump impeller blade outer shroud inlet angle is β
p1=111 ° ~ 114 °, outer shroud exit angle is β
p2=79 ° ~ 81 °, inner ring inlet angle is β
p3=111 ° ~ 114 °, inner ring exit angle is β
p4=83 ° ~ 85 °; Turbine blade outer shroud inlet angle is β
t1=42 ° ~ 44 °, outer shroud exit angle is β
t2=146 ° ~ 148 °, inner ring inlet angle is β
t3=43 ° ~ 45 °, inner ring exit angle is β
t4=146 ° ~ 148 °; Guide vane outer shroud inlet angle is β
s1=98 ° ~ 100 °, outer shroud exit angle is β
s2=24 ° ~ 26 °, inner ring inlet angle is β
s3=71 ° ~ 73 °, inner ring exit angle is β
s4=12 ° ~ 15 °.
By test, obtain the pump impeller nominal torque MBg0=246 ~ 250Nm under the hydraulic single-turbine torque converter stall operating mode of the present embodiment, stall torque is than K0=2.38 ~ 2.42, the peak efficiency value of torque-converters is 0.891 ~ 0.912, mate rationally with 1850rpm, 131KW diesel engine, efficiency is high, has excellent power performance and fuel economy.
Embodiment 2:
Described circulate circle diameter is 380; Pump impeller blade outer shroud inlet angle is β
p1=108 ° ~ 111 °, outer shroud exit angle is β
p2=81 ° ~ 83 °, inner ring inlet angle is β
p3=108 ° ~ 111 °, inner ring exit angle is β
p4=85 ° ~ 88 °; Turbine blade outer shroud inlet angle is β
t1=44 ° ~ 46 °, outer shroud exit angle is β
t2=144 ° ~ 146 °, inner ring inlet angle is β
t3=45 ° ~ 47 °, inner ring exit angle is β
t4=144 ° ~ 146 °; Guide vane outer shroud inlet angle is β
s1=100 ° ~ 104 °, outer shroud exit angle is β
s2=26 ° ~ 29 °, inner ring inlet angle is β
s3=73 ° ~ 75 °, inner ring exit angle is β
s4=15 ° ~ 17 °.
By test, obtain the pump impeller nominal torque MBg0=250 ~ 254Nm under the hydraulic single-turbine torque converter stall operating mode of the present embodiment, stall torque is than K0=2.34 ~ 2.38, the peak efficiency value of torque-converters is 0.895 ~ 0.916, mate rationally with 1850rpm, 131KW diesel engine, efficiency is high, has excellent power performance and fuel economy.
Embodiment 3:
Described circulate circle diameter is D=385mm; Pump impeller blade outer shroud inlet angle is β
p1=106 ° ~ 108 °, outer shroud exit angle is β
p2=83 ° ~ 86 °, inner ring inlet angle is β
p3=106 ° ~ 108 °, inner ring exit angle is β
p4=88 ° ~ 90 °; Turbine blade outer shroud inlet angle is β
t1=46 ° ~ 48 °, outer shroud exit angle is β
t2=142 ° ~ 144 °, inner ring inlet angle is β
t3=47 ° ~ 50 °, inner ring exit angle is β
t4=142 ° ~ 144 °; Guide vane outer shroud inlet angle is β
s1=104 ° ~ 106 °, outer shroud exit angle is β
s2=29 ° ~ 32 °, inner ring inlet angle is β
s3=75 ° ~ 78 °, inner ring exit angle is β
s4=17 ° ~ 19 °.
By test, obtain the pump impeller nominal torque MBg0=254 ~ 258Nm under the hydraulic single-turbine torque converter stall operating mode of the present embodiment, stall torque is than K0=2.30 ~ 2.34, the peak efficiency value of torque-converters is 0.893 ~ 0.913, mate rationally with 1850rpm, 131KW diesel engine, efficiency is high, has excellent power performance and fuel economy.
Embodiment 4:
In described blade system, pump impeller blade outer shroud inlet angle is β
p1=104 ° ~ 106 °, outer shroud exit angle is β
p2=86 ° ~ 89 °, inner ring inlet angle is β
p3=104 ° ~ 106 °, inner ring exit angle is β
p4=90 ° ~ 93 °; Turbine blade outer shroud inlet angle is β
t1=48 ° ~ 50 °, outer shroud exit angle is β
t2=140 ° ~ 142 °, inner ring inlet angle is β
t3=50 ° ~ 53 °, inner ring exit angle is β
t4=140 ° ~ 142 °; Guide vane outer shroud inlet angle is β
s1=106 ° ~ 108 °, outer shroud exit angle is β
s2=32 ° ~ 34 °, inner ring inlet angle is β
s3=78 ° ~ 81 °, inner ring exit angle is β
s4=19 ° ~ 22 °.
By test, obtain the pump impeller nominal torque MBg0=258 ~ 262Nm under the hydraulic single-turbine torque converter stall operating mode of the present embodiment, stall torque is than K0=2.26 ~ 2.30, the peak efficiency value of torque-converters is 0.898 ~ 0.919, mate rationally with 1850rpm, 131KW diesel engine, efficiency is high, has excellent power performance and fuel economy.
Claims (6)
1. a hydraulic single-turbine torque converter, includes turbine, blade system that pump impeller, guide wheel are formed and the circulate circle that coordinates with blade system, it is characterized in that: described circulate circle diameter D=370 ~ 390mm; In described blade system, pump impeller blade outer shroud inlet angle is β
p1=104 ° ~ 114 °, outer shroud exit angle is β
p2=79 ° ~ 89 °, outer shroud inlet side thickness H
p1=7 ~ 8mm, outer shroud Exit-edge thickness H
p2=3.2 ~ 4.2mm, inner ring inlet angle is β
p3=104 ° ~ 114 °, inner ring exit angle is β
p4=83 ° ~ 93 °, inner ring inlet side thickness H
p3=4 ~ 5mm, inner ring Exit-edge thickness H
p4=2.5 ~ 3.5mm; Turbine blade outer shroud inlet angle is β
t1=42 ° ~ 50 °, outer shroud exit angle is β
t2=140 ° ~ 150 °, outer shroud inlet side thickness H
t1=2 ~ 2.5mm, outer shroud Exit-edge thickness H
t2=2 ~ 2.5mm, inner ring inlet angle is β
t3=43 ° ~ 53 °, inner ring exit angle is β
t4=140 ° ~ 150 °, inner ring inlet side thickness H
t3=2 ~ 3mm, inner ring Exit-edge thickness H
t4=5 ~ 6mm; Guide vane outer shroud inlet angle is β
s1=98 ° ~ 108 °, outer shroud exit angle is β
s2=24 ° ~ 34 °, outer shroud inlet side thickness H
s1=6 ~ 7mm, outer shroud Exit-edge thickness H
s2=3.5 ~ 4.5mm, inner ring inlet angle is β
s3=71 ° ~ 81 °, inner ring exit angle is β
s4=12 ° ~ 22 °, inner ring inlet side thickness H
s3=6.4 ~ 7.4mm, inner ring Exit-edge thickness H
s4=3 ~ 4mm.
2. hydraulic single-turbine torque converter according to claim 1, is characterized in that: described circulate circle diameter is 380 ~ 385mm; Pump impeller blade outer shroud inlet angle is β
p1=106 ° ~ 111 °, outer shroud exit angle is β
p2=81 ° ~ 85 °, inner ring inlet angle is β
p3=106 ° ~ 111 °, inner ring exit angle is β
p4=85 ° ~ 90 °; Turbine blade outer shroud inlet angle is β
t1=44 ° ~ 48 °, outer shroud exit angle is β
t2=142 ° ~ 146 °, inner ring inlet angle is β
t3=45 ° ~ 50 °, inner ring exit angle is β
t4=142 ° ~ 146 °; Guide vane outer shroud inlet angle is β
s1=100 ° ~ 106 °, outer shroud exit angle is β
s2=25 ° ~ 32 °, inner ring inlet angle is β
s3=73 ° ~ 75 °, inner ring exit angle is β
s4=15 ° ~ 19 °.
3. hydraulic single-turbine torque converter according to claim 1, is characterized in that: described circulate circle diameter D=370mm; In described blade system, pump impeller blade outer shroud inlet angle is β
p1=111 ° ~ 114 °, outer shroud exit angle is β
p2=79 ° ~ 81 °, inner ring inlet angle is β
p3=111 ° ~ 114 °, inner ring exit angle is β
p4=83 ° ~ 85 °; Turbine blade outer shroud inlet angle is β
t1=42 ° ~ 44 °, outer shroud exit angle is β
t2=146 ° ~ 148 °, inner ring inlet angle is β
t3=43 ° ~ 45 °, inner ring exit angle is β
t4=146 ° ~ 148 °; Guide vane outer shroud inlet angle is β
s1=98 ° ~ 100 °, outer shroud exit angle is β
s2=24 ° ~ 26 °, inner ring inlet angle is β
s3=71 ° ~ 73 °, inner ring exit angle is β
s4=12 ° ~ 15 °.
4. hydraulic single-turbine torque converter according to claim 2, is characterized in that: described circulate circle diameter is 380; Pump impeller blade outer shroud inlet angle is β
p1=108 ° ~ 111 °, outer shroud exit angle is β
p2=81 ° ~ 83 °, inner ring inlet angle is β
p3=108 ° ~ 111 °, inner ring exit angle is β
p4=85 ° ~ 88 °; Turbine blade outer shroud inlet angle is β
t1=44 ° ~ 46 °, outer shroud exit angle is β
t2=144 ° ~ 146 °, inner ring inlet angle is β
t3=45 ° ~ 47 °, inner ring exit angle is β
t4=144 ° ~ 146 °; Guide vane outer shroud inlet angle is β
s1=100 ° ~ 104 °, outer shroud exit angle is β
s2=26 ° ~ 29 °, inner ring inlet angle is β
s3=73 ° ~ 75 °, inner ring exit angle is β
s4=15 ° ~ 17 °.
5. hydraulic single-turbine torque converter according to claim 2, is characterized in that: described circulate circle diameter is D=385mm; Pump impeller blade outer shroud inlet angle is β
p1=106 ° ~ 108 °, outer shroud exit angle is β
p2=83 ° ~ 86 °, inner ring inlet angle is β
p3=106 ° ~ 108 °, inner ring exit angle is β
p4=88 ° ~ 90 °; Turbine blade outer shroud inlet angle is β
t1=46 ° ~ 48 °, outer shroud exit angle is β
t2=142 ° ~ 144 °, inner ring inlet angle is β
t3=47 ° ~ 50 °, inner ring exit angle is β
t4=142 ° ~ 144 °; Guide vane outer shroud inlet angle is β
s1=104 ° ~ 106 °, outer shroud exit angle is β
s2=29 ° ~ 32 °, inner ring inlet angle is β
s3=75 ° ~ 78 °, inner ring exit angle is β
s4=17 ° ~ 19 °.
6. hydraulic single-turbine torque converter according to claim 1, is characterized in that: described circulate circle diameter D=390; In described blade system, pump impeller blade outer shroud inlet angle is β
p1=104 ° ~ 106 °, outer shroud exit angle is β
p2=86 ° ~ 89 °, inner ring inlet angle is β
p3=104 ° ~ 106 °, inner ring exit angle is β
p4=90 ° ~ 93 °; Turbine blade outer shroud inlet angle is β
t1=48 ° ~ 50 °, outer shroud exit angle is β
t2=140 ° ~ 142 °, inner ring inlet angle is β
t3=50 ° ~ 53 °, inner ring exit angle is β
t4=140 ° ~ 142 °; Guide vane outer shroud inlet angle is β
s1=106 ° ~ 108 °, outer shroud exit angle is β
s2=32 ° ~ 34 °, inner ring inlet angle is β
s3=78 ° ~ 81 °, inner ring exit angle is β
s4=19 ° ~ 22 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420602475.3U CN204186916U (en) | 2014-10-17 | 2014-10-17 | Hydraulic single-turbine torque converter |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420602475.3U CN204186916U (en) | 2014-10-17 | 2014-10-17 | Hydraulic single-turbine torque converter |
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| Publication Number | Publication Date |
|---|---|
| CN204186916U true CN204186916U (en) | 2015-03-04 |
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| CN201420602475.3U Active CN204186916U (en) | 2014-10-17 | 2014-10-17 | Hydraulic single-turbine torque converter |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106286756A (en) * | 2016-10-11 | 2017-01-04 | 广西柳工机械股份有限公司 | Hydraulic single-turbine torque converter |
| CN106763633A (en) * | 2016-12-14 | 2017-05-31 | 广西柳工机械股份有限公司 | Hydraulic single-turbine torque converter |
| CN108980296A (en) * | 2018-09-14 | 2018-12-11 | 天津工程机械研究院有限公司 | A kind of face of fluid torque converter structure |
| CN108980297A (en) * | 2018-09-14 | 2018-12-11 | 天津工程机械研究院有限公司 | A kind of transformer turbine structure |
| CN109027175A (en) * | 2018-09-14 | 2018-12-18 | 天津工程机械研究院有限公司 | A kind of torque converter reactor structure |
| CN113374850A (en) * | 2021-07-08 | 2021-09-10 | 江苏汇智高端工程机械创新中心有限公司 | Guide wheel structure of hydraulic torque converter of engineering machinery |
-
2014
- 2014-10-17 CN CN201420602475.3U patent/CN204186916U/en active Active
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106286756A (en) * | 2016-10-11 | 2017-01-04 | 广西柳工机械股份有限公司 | Hydraulic single-turbine torque converter |
| CN106763633A (en) * | 2016-12-14 | 2017-05-31 | 广西柳工机械股份有限公司 | Hydraulic single-turbine torque converter |
| CN108980296A (en) * | 2018-09-14 | 2018-12-11 | 天津工程机械研究院有限公司 | A kind of face of fluid torque converter structure |
| CN108980297A (en) * | 2018-09-14 | 2018-12-11 | 天津工程机械研究院有限公司 | A kind of transformer turbine structure |
| CN109027175A (en) * | 2018-09-14 | 2018-12-18 | 天津工程机械研究院有限公司 | A kind of torque converter reactor structure |
| CN108980297B (en) * | 2018-09-14 | 2024-03-19 | 天津工程机械研究院有限公司 | Turbine structure of hydraulic torque converter |
| CN108980296B (en) * | 2018-09-14 | 2024-03-19 | 天津工程机械研究院有限公司 | Pump wheel structure of hydraulic torque converter |
| CN113374850A (en) * | 2021-07-08 | 2021-09-10 | 江苏汇智高端工程机械创新中心有限公司 | Guide wheel structure of hydraulic torque converter of engineering machinery |
| CN113374850B (en) * | 2021-07-08 | 2023-12-05 | 江苏汇智高端工程机械创新中心有限公司 | Guide wheel structure of hydraulic torque converter of engineering machinery |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20170703 Address after: 545007 the Guangxi Zhuang Autonomous Region Liuzhou City Liu Tai Road No. 1 Patentee after: Liugong Liuzhou transmission parts Co., Ltd. Address before: 545007 the Guangxi Zhuang Autonomous Region Liuzhou City Liu Tai Road No. 1 Patentee before: Guangxi Liugong Machinery Co., Ltd. |