CN201561108U - Integrated hydraulic torque converter having lockup clutch - Google Patents
Integrated hydraulic torque converter having lockup clutch Download PDFInfo
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- CN201561108U CN201561108U CN2009202120229U CN200920212022U CN201561108U CN 201561108 U CN201561108 U CN 201561108U CN 2009202120229 U CN2009202120229 U CN 2009202120229U CN 200920212022 U CN200920212022 U CN 200920212022U CN 201561108 U CN201561108 U CN 201561108U
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Abstract
The utility model relates to an integrated hydraulic torque converter having a lockup clutch. The converter mainly comprises a pump impeller and a turbine which are integrally connected by the lockup clutch, first and second guide wheels which are arranged between the pump impeller and the turbine, an overrunning clutch which is connected with the first and second guide wheels, a thrust bearing which is connected with the second guide wheel, and a torque converter hub which is arranged at an output end. The thrust bearing comprises a round ring body provided with a plurality of radial slots. The integrated hydraulic torque converter is characterized in that an inlet angle of a middle streamline of a blade of the pump impeller is 116 to 117 degrees and the outlet angle thereof is 129.5 to 130.5 degrees; the inlet angle of the middle streamline of the blade of the turbine is 48 to 49 degrees and the outlet angle thereof is 154 to 155 degrees; the inlet angle of the middle streamline of the blade of the first guide wheel is 120 to 121 degrees and the outlet angle thereof is 91 to 92 degrees; and the inlet angle of the middle streamline of the blade of the second guide wheel is 74 to 75 degrees and the outlet angle thereof is 26 to 27 degrees. The thrust bearing is made of aluminums bronze ZCuAL10Fe3. Oil inlet and outlet channels of the torque converter hub are opposite to the positions of an oil inlet and an oil outlet on a shell. The integrated hydraulic torque converter has the advantages of high efficiency, reasonable matching with an engine, high reliability, long service life, and the like.
Description
Technical field
The utility model belongs to hydraulic machine transmission category, is specifically related to the converter coupling with lockup clutch.
Background technique
Fluid torque converter is the hydraulic machine that a kind of kinetic energy change by liquid changes transmitting torque.It is compared with general mechanical transmission, has the advantage that transmission performance is soft, efficient is high, is the main parts size of automatic transmission case therefore.The SGA3722 mine truck that Shoudu Iron and Steel Co heavy-duty car factory produces adopts 7523 mine car technology of other Lars company.Wherein automatic transmission case mainly is 7523 mine car automatic transmission case of imitated Byelorussia other Lars company.This automatic transmission case is a fixed axle gearbox, adopts electrically-controlled valve to form with the single-stage three-phase quaternary part centripetal turbine converter coupling of band lockup clutch.The single-stage three-phase quaternary part centripetal turbine converter coupling of this band lockup clutch is mainly by lockup clutch, a pump impeller, but the guide wheel of a turbine and two one-way rotation and free wheel device constitute, and it can form two fluid torque converter operating modes and a fluid coupling operating mode.Pump impeller is by the input shaft driven rotary during work, and work fluid is just made circulation movement and promoted turbine rotation and output torque in circulate circle, and liquid stream enters turbine from pump impeller, enters first order guide wheel again, through second level guide wheel, returns pump impeller.Near fluid torque converter efficient declared working condition is higher, and peak efficiency is 85～92%.Impeller is the core of fluid torque converter, and the shape of its pattern and position and blade has decisive action to the performance of torque-converters.
Because 7523 mine cars are long with the automatic transmission case import cycle, cost an arm and a leg, just domesticized in 1991, but in the production domesticization process, have following problem:
1, pump impeller, turbine blade became uneven, different blade same position thickness differences are more than 2mm, and it is very big to hold influence to torque-converters, and turbine Inlet cone angle and exit angle are bigger than normal, make efficient on the low side;
2, for the torque converter hub, as shown in Figure 1, this is a kind of structural representation of the torque converter hub of prior art fluid torque converter, and wherein a is the side view of torque converter hub, and b is the A-A sectional view of a.This torque converter hub comprises hub body 100, be arranged on filler opening groove 101, the oil outlet groove 102 of hub body, the oil inlet hole 103 that is communicated with the filler opening groove, the oil outlet 104 that is communicated with the oil outlet groove, are installed screw 109 to one grade of clutch oil duct of gearbox hole 106, to gearbox second gear clutch oil duct hole 107, to the logical oil groove 108 of gearbox third gear clutch and the circle that is arranged on hub body periphery at lockup clutch oil duct junction 105.Aperture d103, the d104 of turnover oilhole are φ 11mm, the central vertical line parallel of oil inlet hole and torque converter hub is provided with, groove depth h108 to the logical oil groove of gearbox third gear clutch is 14mm, the lockup clutch oil duct junction is provided with the dark rectangular recess of a 2.2mm 1052 around 105 apertures 1051, and the width h of the φ 200mm circular arc sealing surface around oil outlet groove 102 and the lockup clutch oil duct junction aperture between the rectangular recess is 7.5mm.This structure makes the torque converter hub only be 66% of enterprising, the oil outlet area of housing into and out of oily aisle spare, there are bigger inconsistent phenomenon in the position of torque converter hub oil inlet passage and housing filler opening, make that the oil-feed resistance is excessive, and the import oil pressure is too high, energy loss is bigger, and the torque-converters internal leakage increases.Again because to gearbox second gear clutch oil duct hole 107 and be to be obliquely installed between one grade of clutch oil duct of gearbox hole 106, minimum distance is too near between two holes, adds to bore a hole easily man-hour, influences the product qualified rate of product.
3, thrust bearing is that the tin bronze material constitutes owing to what adopt, and oil groove leaves deeply excessively, it is non-through between oil groove is circumferential, be not easy to set up lubricant film, have local friction's abrasion condition in machine operation procedure, make that its rate of wear is fast, this Tensile strength is low in addition, fracture damage makes the torque-converters reliability not high easily.
4, the torque-converters performance is not good, can hold on the low side, unreasonable with Engine Matching, make machine heating, friction plate scaling loss or the like.
Summary of the invention
The purpose of this utility model is to solve the irrational problem of Engine Matching of existing converter coupling and mine car, and the converter coupling of the band lockup clutch of a kind of and domestic 525 horsepower engine rational Match that provide, the converter coupling of this band lockup clutch has overcome the problems referred to above that existing fluid torque converter exists, and has improved the reliability of converter coupling.
To achieve these goals, the converter coupling of the utility model band lockup clutch mainly comprises: pump impeller, turbine, first guide wheel, second guide wheel, thrust bearing, lockup clutch, free wheel device, torque converter hub; Described pump impeller and turbine connect as one by lockup clutch; Described first guide wheel, second guide wheel are arranged between described pump impeller and the turbine; Described free wheel device is connected with second guide wheel with described first guide wheel; Described thrust bearing is connected with guide wheel; Described torque converter hub is arranged on output terminal, described torque converter hub comprises the hub body, be arranged on filler opening groove, the oil outlet groove of hub body, the oil inlet hole that is communicated with the filler opening groove, the oil outlet that is communicated with the oil outlet groove, are installed screw to gearbox second gear clutch oil duct hole, to the logical oil groove of gearbox third gear clutch and the circle that is arranged on hub body periphery at the lockup clutch oil duct junction; Respectively be provided with the blade of a plurality of distortions on described pump impeller, turbine, first guide wheel and second guide wheel; Described thrust bearing comprises two cirque body, has a plurality of radial grooves on this cirque body; Be characterized in that the calculating angle of the center line of flow path of the blade of described pump impeller is: 116 °～117 ° of inlet angles, 129.5 °～130.5 ° of exit angle; The calculating angle of the center line of flow path of the blade of described turbine is: 48 °～49 ° of inlet angles, 154 °～155 ° of exit angle; The calculating angle of the center line of flow path of the blade of described first guide wheel is: 120 °～121 ° of inlet angles, 91 °～92 ° of exit angle; The calculating angle of the center line of flow path of the blade of described second guide wheel is: 74 °～75 ° of inlet angles, 26 °～27 ° of exit angle; Described thrust bearing adopts aluminum bronze ZCuAL10Fe3 material to constitute; One circle of described torque converter hub is installed screw integral body and is rotated counterclockwise 7 °, angle between the central vertical line of its top-right screw and torque converter hub is 5 °, the diameter of torque-converters oil inlet hole and oil outlet all is 4 * φ 12mm, and the position of oil inlet hole and oil outlet is relative on oil inlet hole and oil outlet and the housing; Under the situation of described oil inlet hole aperture invariant position, described filler opening groove and oil inlet hole integral body are rotated counterclockwise 9 °, and each oil inlet hole favours the central vertical line of torque converter hub; The aperture of described lockup clutch oil duct junction is set to the egg type hole.
The converter coupling of above-mentioned band lockup clutch, wherein, the interior circle of described thrust bearing is provided with a circumferential groove in its end portion; Described radial groove is at least 4 branch grooves such as circumference, and its width is 3.32mm, and length is 13mm.
The converter coupling of above-mentioned band lockup clutch, wherein, described torque converter hub all is 4 * φ 12mm into and out of the oilhole size.
The converter coupling of above-mentioned band lockup clutch, wherein, the width of the φ 200mm circular arc sealing surface between described torque-converters hub oil outlet groove and the lockup clutch oil duct junction egg type hole is 20.4mm.
The converter coupling of above-mentioned band lockup clutch, wherein, the position of described logical oil groove to gearbox third gear clutch has been rotated counterclockwise 6 °, and groove depth is 23mm.
The converter coupling of above-mentioned band lockup clutch, wherein, described to gearbox second gear clutch oil duct hole and between one grade of clutch oil duct of gearbox hole for be arrangeding in parallel, wherein reach torque converter hub central vertical line the right, form 5 ° of angles with central vertical line the right to gearbox second gear clutch oil duct aperture.
The converter coupling of above-mentioned band lockup clutch, wherein, the thickness of described pump impeller inlet vane is 6mm, the thickness of outlet blade is 5mm; The turbine inlet vane thickness is 5mm, and the thickness of outlet blade is 3mm; The first guide wheel inlet vane thickness is 3.6mm, and the thickness of outlet blade is 2mm; The second guide wheel inlet vane thickness is 3.6mm, and the thickness of outlet blade is 2mm.
The converter coupling of above-mentioned band lockup clutch, wherein, the circulate circle diameter of described pump impeller, turbine, first guide wheel, second guide wheel is 470mm.
The converter coupling of above-mentioned band lockup clutch, wherein, the number of blade of described pump impeller is 28, the number of blade of turbine be the number of blade of 24, the first guide wheels be 29, the second guide wheels the number of blade be 23.
Because the utility model has adopted above technological scheme, the technique effect of its generation is tangible:
1, the utility model is revised by the blade profile parameters to fluid torque converter, adjusts the thickness of each position of blade, and pump impeller inlet vane thickness is adjusted into 6mm, reduces 25% than original pump impeller inlet vane thickness, has increased circulation area; Simultaneously the turbine outlet vane thickness is adjusted into 3mm, than original turbine outlet vane thickness attenuate 9～12.5%; Again circulate circle is finely tuned, by original diameter 471.5mm, changing diameter into is 470mm; Change the import and export angle of turbine blade, the import and export angle than original turbine blade reduces 1 °, 0.5 ° respectively, and the import and export angle of pump impeller blade increases 0.3 °, by the shape of change blade, thereby makes the efficient of fluid torque converter reach desirable.As calculated, the torque-converters zero-speed can be held increases by 17%, makes that torque-converters and Engine Matching are more reasonable, makes the converter pump Maximum Torque improve 100N.m, and tractive force increases by 12.08%.
2, by the material of thrust bearing is replaced by aluminum bronze ZCuAL10Fe3 by tin bronze, increase the tensile strength of thrust bearing greatly, can prevent the phenomenon of rupture after thrust bearing weares and teares; Because the viscosity of aluminum bronze is bigger,, it is carried out surface modification simultaneously, carry out siliconising and handle, improve surface abrasion resistance in order to improve its surperficial wear resistance; Structurally, former radial groove size is reduced, strengthen its intensity, and circumferentially opening circumferential groove in its end portion, can guarantee like this to float packing ring and mating part are in state of liquid friction, and its wear resistance is further improved; By above-mentioned improvement, improved the operational safety of thrust bearing greatly, prolong 3～5 times of its working lifes.Minimizing has improved user's economic benefit because of the parking loss that the torque-converters reliability failure causes.
3, for the torque converter hub, by being installed screw integral body, a circle is rotated counterclockwise 7 °, making the screw and the angle between the central vertical line on its right, the top is 5 °, and change into and out of the hydraulic fluid port groove with into and out of the position of oilhole, guarantee that torque converter hub position enterprising into and out of hydraulic fluid port and housing, oil outlet is in full accord, thereby reduce the phenomenon that misplaces into and out of hydraulic fluid port into and out of hydraulic fluid port and housing because of the torque converter hub, to increase 19% into and out of the area of oil duct simultaneously, reduce because of the excessive problem of the internal leakage that does not freely cause overpressure to cause into and out of oil.Owing to change lockup clutch oil duct junction aperture rectangular recess into the egg type hole, increase the sealing surface between lockup clutch oil duct junction egg type hole and the torque converter hub oil outlet groove, prevent that lockup clutch is not good at causing pressure anomaly fluctuation because of sealing, influence friction plate in conjunction with pressure, the sheet burning phenomenon of reducing friction improves the friction plate functional reliability; Again with described to gearbox second gear clutch oil duct hole and between one grade of clutch oil duct of gearbox hole for be arrangeding in parallel, prevented to add and caused the logical problem of two hole drills because of borehole throw man-hour, improved the up-to-standard rate of product.
Description of drawings
Concrete structure of the present utility model is further provided by following embodiment and accompanying drawing thereof.
Fig. 1 is a kind of embodiment's the structural representation of the torque converter hub of prior art fluid torque converter, and wherein a is the side view of torque converter hub, and b is the A-A sectional view of a.
Fig. 2 is a kind of embodiment's the overall structure schematic representation of the converter coupling of the utility model band lockup clutch.
Fig. 3 is the structural representation of the converter coupling active wheel of the utility model band lockup clutch, and wherein: a is the structural representation of pump impeller, and b is the structural representation of turbine, and c is the structural representation of first guide wheel, and d is the structural representation of second guide wheel.
Fig. 4 is the leaf schematic representation of the converter coupling active wheel of the utility model band lockup clutch, and wherein: a is the leaf schematic representation of pump impeller, and b is the leaf schematic representation of turbine, and c is the leaf schematic representation of first guide wheel, and d is the leaf schematic representation of second guide wheel.
Fig. 5 is a kind of embodiment's the structural representation of thrust bearing of the converter coupling of the utility model band lockup clutch.
Fig. 6 is a kind of embodiment's the structural representation of torque converter hub of the converter coupling of the utility model band lockup clutch, and wherein a is the side view of torque converter hub, and b is the A-A sectional view of a.
Embodiment
See also Fig. 2～Fig. 3, Fig. 2 is a kind of embodiment's the overall structure schematic representation of the converter coupling of the utility model band lockup clutch, Fig. 3 is the structural representation of the converter coupling active wheel of the utility model band lockup clutch, wherein: a is the structural representation of pump impeller, b is the structural representation of turbine, c is the structural representation of first guide wheel, and d is the structural representation of second guide wheel.Present embodiment is to exemplify a YJ470 fluid torque converter, mainly comprises: active wheel of being made up of pump impeller 1, turbine 2, first guide wheel 3, second guide wheel 4 and thrust bearing 5, lockup clutch 6, free wheel device 7, torque converter hub 8; Described pump impeller and turbine connect as one by lockup clutch; The inner radial of described pump impeller is provided with the blade 11 of many distortions, and the blade inner edge then is provided with and allows the lead ring of torque-converters fluid smooth flow.The inside of turbine also is provided with many blades 21, and the direction of twist of described turbine blade is opposite with the direction of the distortion of pump impeller blade, and the turbine center has splined hole and transmission input shaft to link.Pump impeller blade is relative with turbine blade to be settled, and there is the gap of ccontaining first guide wheel 3 and second guide wheel 4 centre.Described first guide wheel 3 and second guide wheel 4 respectively are provided with the blade 31,41 of a plurality of distortions, and described first guide wheel, second guide wheel are arranged between described pump impeller and the turbine.Described free wheel device is installed in respectively in described first guide wheel and second guide wheel; Described thrust bearing, wherein a slice is installed between first guide wheel and second guide wheel, and another sheet is connected with second guide wheel; Described torque converter hub is arranged on output terminal.Pump impeller is by the input shaft driven rotary during work, work fluid is made circulation movement and is promoted turbine rotation and output torque in circulate circle. and liquid stream enters turbine from pump impeller, enter first guide wheel again, through second guide wheel, return pump impeller, circulate again and again, the variation of leaning on the interaction of liquid and blade to produce the moment of momentum comes transmitting torque.Pump impeller passes to liquid with the mechanical energy of input shaft, and high-speed liquid promotes the turbine rotation, and energy is passed to output shaft.
The parameter of each blade of pump impeller described in the utility model, turbine, first guide wheel and second guide wheel comprises that circulate circle diameter, each blade are gone into, exit angle, the number of blade etc.It is 470mm that present embodiment is got the circulate circle diameter, and each impeller blade number is as follows: the pump impeller blade number is 28, and the turbine blade number is that 24, the first guide vane numbers are that 29, the second guide vane numbers are 23.
See also Fig. 4, Fig. 4 is the leaf schematic representation of the converter coupling active wheel of the utility model band lockup clutch, and wherein: a is the leaf schematic representation of pump impeller, and b is the leaf schematic representation of turbine, c is the leaf schematic representation of first guide wheel, and d is the leaf schematic representation of second guide wheel.
The calculating angle of the center line of flow path of the blade of pump impeller described in the utility model is: inlet angle β 1-1 is 116 °～117 °, and exit angle β 1-2 is 129.5 °～130.5 °; The calculating angle of the center line of flow path of the blade of described turbine is: inlet angle β 2-1 is 48 °～49 °, and exit angle β 2-2 is 154 °～155 °; The calculating angle of the center line of flow path of the blade of described first guide wheel is: inlet angle β 3-1 is 120 °～121 °, and exit angle β 3-2 is 91 °～92 °; The calculating angle of the center line of flow path of the blade of described second guide wheel is: inlet angle β 4-1 is 74 °～75 °, and exit angle β 4-2 is 26 °～27 °.
Because above-mentioned parameter is optimized design through the computer related software, the specific performance parameter through test is:
MB
g0＝532.7N·m
MBg
η＝511.15N·m
K
0＝2.71
ηmax＞＝84.8％
In the formula: MB
G0---under the torque-converters zero-speed working condition, the absorption moment of torsion of pump impeller when 1000rpm;
MBg
η---under the torque-converters peak efficiency working condition, the absorption moment of torsion of pump impeller when 1000rpm;
K
0---torque-converters zero-speed converter torque ratio, promptly under the zero-speed working condition, the ratio of the output torque of torque-converters and input torque;
The peak efficiency of η max---torque-converters.
By above test as can be seen: the zero-speed thousand torque MB of the converter coupling of the utility model band lockup clutch
G0Increased by 17%, peak efficiency thousand torque MBg
ηIncreased by 11%, highest efficiency eta max has increased by 4.4%, and through mating with 525 horsepower engines (QSX15-C525), during the turbine zero-speed, the pump impeller rotating speed is 92% of a rated speed, and its pump impeller Maximum Torque is 1972.1N.m, than the big 100N.m of design load.Matching effect is good, has satisfied the requirement of quarry tipper service behaviour.
See also Fig. 5, Fig. 5 is a kind of embodiment's the structural representation of thrust bearing of the converter coupling of the utility model band lockup clutch.Thrust bearing 5 described in the utility model is made of aluminum bronze ZCuAL10Fe3 material, this thrust bearing 5 comprises a cirque body 51, have a plurality of radial grooves 52 on this cirque body, described radial groove is at least 4 branch grooves such as circumference, present embodiment is provided with 8 branch grooves such as circumference, its width of each radial groove is 3.32mm, and length is 13mm, be equivalent to the prior art thrust bearing radial groove width of rebate 36%.At the interior circle of described thrust bearing and be provided with a circumferential groove in its end portion 53.The utility model is replaced by aluminum bronze ZCuAL10Fe3 with the material of thrust bearing 5 by tin bronze, can increase the tensile strength of this thrust bearing greatly, has prevented the phenomenon of rupture after thrust bearing is worn.Because the viscosity of aluminum bronze is bigger,, it is carried out surface modification simultaneously, carry out siliconising and handle, can improve surface abrasion resistance in order to improve its surperficial wear resistance.Because the radially fluting size of this thrust bearing is reduced, and at the circumferential open loop groove of interior circle, strengthen its intensity, its wear resistance is further improved in the time of can guaranteeing like this that thrust bearing and its mating part are in state of liquid friction.By above-mentioned improvement, the operational safety that has improved greatly prolongs 3～5 times of its working lifes.
See also Fig. 6, this is a kind of embodiment's the structural representation of torque converter hub of the converter coupling of the utility model band lockup clutch, and wherein a is the side view of torque converter hub, the A-A sectional view of a during b.Described torque converter hub comprises hub body 80, be arranged on filler opening groove 81, the oil outlet groove 82 of hub body, the oil inlet hole 83 that is communicated with the filler opening groove, the oil outlet 84 that is communicated with the oil outlet groove, are installed screw 89 to one grade of clutch oil duct of gearbox hole 86, to gearbox second gear clutch oil duct hole 87, to the logical oil groove 88 of gearbox third gear clutch and the circle that is arranged on hub body periphery at lockup clutch oil duct junction 85; The improvement that the relative prior art torque converter of torque converter hub hub in the utility model is done is, one circle of described torque converter hub is installed screw 89 integral body and is rotated counterclockwise 7 °, and the angle a891 between the central vertical line of its top-right screw 891 and torque converter hub is 5 °; Under the situation of described oil inlet hole aperture invariant position, described filler opening groove and oil inlet hole integral body are rotated counterclockwise 9 °, and each oil inlet hole favours the central vertical line of torque converter hub; Position with described logical oil groove 88 to gearbox third gear clutch has been rotated counterclockwise 6 ° simultaneously, makes this be increased to 17 ° to the logical oil groove center of arc of gearbox third gear clutch and the angle a between the torque converter hub transversal line, and h88 is made as 23mm with groove depth.Owing to changed the angle and the position of oil inlet passage, make the position of filler opening on oil inlet passage mouth and the housing relative fully, the diameter d 83 into and out of oilhole, d84 with the torque converter hub changes 4 * φ 12mm into by former 4 * φ 11mm simultaneously, make the circulation area of torque-converters outer circulation oil circuit improve 19%, thereby reduce phenomenon because of torque converter hub filler opening and the dislocation of housing filler opening, reduce because of the excessive problem of the internal leakage that does not freely cause overpressure to cause into and out of oil, make housing fully unobstructed to the oil circuit of torque converter hub.
Because the axle of torque converter hub is a Spielpassung with the hole of housing, the too small meeting of circular arc seal f ace width causes the oil of scurrying between oil duct between the oil duct junction, the utility model changes the aperture 851 of lockup clutch oil duct junction 85 into the egg type hole, and change torque converter hub oil outlet groove depth h82 into 10mm by 12mm, make the circular arc seal f ace width H between torque converter hub oil outlet groove bottom and the lockup clutch oil duct junction egg type hole, below increase to 20.4mm, therefore strengthened sealing effect herein.
The utility model and with described to gearbox second gear clutch oil duct hole and between one grade of clutch oil duct of gearbox hole for be arrangeding in parallel, wherein reach torque converter hub central vertical line the right to gearbox second gear clutch oil duct aperture 871, formation a87 is 5 ° a angle on the right of the central vertical line.Both solved and be machined to the gearbox second gear clutch oil duct hole and the problem of easily boring a hole to one grade of clutch oil duct of gearbox hole originally, can finish processing by a clamping again, improved work efficiency and finished product up-to-standard rate.
The utlity model has the efficient height, with reasonable, the advantages such as reliability is high, prolongation in working life of Engine Matching.
The above only is preferred embodiment of the present utility model, and all equivalences of being done according to the utility model claim scope change and modify, and all should belong to covering scope of the present utility model.
Claims (9)
1. the converter coupling of band lockup clutch mainly comprises: pump impeller, turbine, first guide wheel, second guide wheel, thrust bearing, lockup clutch, free wheel device, torque converter hub; Described pump impeller and turbine connect as one by lockup clutch; Described first guide wheel, second guide wheel are arranged between described pump impeller and the turbine; Described free wheel device is connected with second guide wheel with described first guide wheel; Described thrust bearing is connected with guide wheel; Described torque converter hub is arranged on output terminal, described torque converter hub comprises the hub body, be arranged on filler opening groove, the oil outlet groove of hub body, the oil inlet hole that is communicated with the filler opening groove, the oil outlet that is communicated with the oil outlet groove, are installed screw to one grade of clutch oil duct of gearbox hole, to gearbox second gear clutch oil duct hole, to the logical oil groove of gearbox third gear clutch and the circle that is arranged on hub body periphery at the lockup clutch oil duct junction; Respectively be provided with the blade of a plurality of distortions on described pump impeller, turbine, first guide wheel and second guide wheel; Described thrust bearing comprises two cirque body, has a plurality of radial grooves on this cirque body;
It is characterized in that,
The calculating angle of the center line of flow path of the blade of described pump impeller is: 116 °～117 ° of inlet angles, 129.5 °～130.5 ° of exit angle;
The calculating angle of the center line of flow path of the blade of described turbine is: 48 °～49 ° of inlet angles, 154 °～155 ° of exit angle;
The calculating angle of the center line of flow path of the blade of described first guide wheel is: 120 °～121 ° of inlet angles, 91 °～92 ° of exit angle;
The calculating angle of the center line of flow path of the blade of described second guide wheel is: 74 °～75 ° of inlet angles, 26 °～27 ° of exit angle;
Described thrust bearing adopts aluminum bronze ZCuAL10Fe3 material to constitute;
One circle of described torque converter hub is installed screw integral body and is rotated counterclockwise 7 °, angle between the central vertical line of its top-right screw and torque converter hub is 5 °, the diameter of torque-converters oil inlet hole and oil outlet is φ 12mm, and the position of oil inlet hole and oil outlet is relative on oil inlet hole and oil outlet and the housing; Under the situation of described oil inlet hole aperture invariant position, described filler opening groove and oil inlet hole integral body are rotated counterclockwise 9 °, and each oil inlet hole favours the central vertical line of torque converter hub; The aperture of described lockup clutch oil duct junction is set to the egg type hole.
2. the converter coupling of band lockup clutch according to claim 1 is characterized in that, the interior circle of described thrust bearing is provided with a circumferential groove in its end portion; Described radial groove is at least 4 branch grooves such as circumference, and its width is 3.32mm, and length is 13mm.
3. the converter coupling of band lockup clutch according to claim 1 is characterized in that, described torque converter hub all is 4 * φ 12mm into and out of the oilhole size.
4. the converter coupling of band lockup clutch according to claim 1 is characterized in that, the width of the φ 200mm circular arc sealing surface between described torque converter hub oil outlet groove and the lockup clutch oil duct junction egg type hole is 20.4mm.
5. the converter coupling of band lockup clutch according to claim 1 is characterized in that, the position of described logical oil groove to gearbox third gear clutch has been rotated counterclockwise 6 °, and groove depth is 23mm.
6. the converter coupling of band lockup clutch according to claim 1, it is characterized in that, described to gearbox second gear clutch oil duct hole and between one grade of clutch oil duct of gearbox hole for be arrangeding in parallel, wherein reach torque converter hub central vertical line the right, form 5 ° of angles with central vertical line the right to gearbox second gear clutch oil duct aperture.
7. the converter coupling of band lockup clutch according to claim 1 is characterized in that, the thickness of described pump impeller inlet vane is 6mm, and the thickness of outlet blade is 5mm; The turbine inlet vane thickness is 5mm, and the thickness of outlet blade is 3mm; The first guide wheel inlet vane thickness is 3.6mm, and the thickness of outlet blade is 2mm; The second guide wheel inlet vane thickness is 3.6mm, and the thickness of outlet blade is 2mm.
8. the converter coupling of band lockup clutch according to claim 1 is characterized in that, the circulate circle diameter of described pump impeller, turbine, first guide wheel, second guide wheel is 470mm.
9. according to the converter coupling of claim 1 or 8 described band lockup clutches, it is characterized in that the number of blade of described pump impeller is 28, the number of blade of turbine is 24, and the number of blade of first guide wheel is 29, second guide wheel the number of blade be 23.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009202120229U CN201561108U (en) | 2009-11-09 | 2009-11-09 | Integrated hydraulic torque converter having lockup clutch |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009202120229U CN201561108U (en) | 2009-11-09 | 2009-11-09 | Integrated hydraulic torque converter having lockup clutch |
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| CN201561108U true CN201561108U (en) | 2010-08-25 |
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| CN2009202120229U Expired - Lifetime CN201561108U (en) | 2009-11-09 | 2009-11-09 | Integrated hydraulic torque converter having lockup clutch |
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| CN102927236A (en) * | 2012-10-31 | 2013-02-13 | 陕西航天动力高科技股份有限公司 | Hydraulic torque converter for special transport vehicle |
| CN103277481A (en) * | 2013-06-21 | 2013-09-04 | 广西柳工机械股份有限公司 | Hydraulic single-turbine torque converter |
| CN103591245A (en) * | 2013-05-21 | 2014-02-19 | 广西柳工机械股份有限公司 | Double-turbine hydraulic torque converter |
| CN103939566A (en) * | 2014-05-07 | 2014-07-23 | 吴志强 | Compound type double-guide-wheel hydraulic torque converter and continuously variable transmission |
| CN104179924A (en) * | 2014-08-08 | 2014-12-03 | 洛阳雷斯达传动有限公司 | Hydraulic torque converter with flexible lock-out control function |
| CN105650236A (en) * | 2014-05-07 | 2016-06-08 | 吴志强 | Compound double-guide-wheel type hydraulic torque converter |
| CN106321771A (en) * | 2016-11-08 | 2017-01-11 | 哈尔滨广瀚动力传动有限公司 | Novel double-turbine double-guide wheel guide vane adjustable type hydraulic torque converter |
| CN104315106B (en) * | 2014-08-19 | 2017-02-15 | 中国北方车辆研究所 | Guide wheel shaft assembly of hydraulic torque converter |
| CN106641166A (en) * | 2016-12-01 | 2017-05-10 | 陕西航天动力高科技股份有限公司 | Three-oil-way closed type automotive hydraulic torque converter |
| CN106678318A (en) * | 2015-11-10 | 2017-05-17 | 熵零股份有限公司 | Torque converter |
| CN108612823A (en) * | 2018-06-25 | 2018-10-02 | 南京世界村汽车动力有限公司 | A kind of engine mission hydraulic torque converter |
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2009
- 2009-11-09 CN CN2009202120229U patent/CN201561108U/en not_active Expired - Lifetime
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| CN102080715A (en) * | 2011-01-07 | 2011-06-01 | 常州市万航工矿设备有限公司 | Hydraulic torque converting box of diesel locomotive |
| CN102080715B (en) * | 2011-01-07 | 2015-07-29 | 常州市万航工矿设备有限公司 | A kind of hydraulic torque converting box of internal combustion locomotive |
| CN102927236A (en) * | 2012-10-31 | 2013-02-13 | 陕西航天动力高科技股份有限公司 | Hydraulic torque converter for special transport vehicle |
| CN102927236B (en) * | 2012-10-31 | 2015-04-29 | 陕西航天动力高科技股份有限公司 | Hydraulic torque converter for special transport vehicle |
| CN103591245A (en) * | 2013-05-21 | 2014-02-19 | 广西柳工机械股份有限公司 | Double-turbine hydraulic torque converter |
| CN103591245B (en) * | 2013-05-21 | 2016-03-30 | 广西柳工机械股份有限公司 | Twin-turbine torque converter |
| CN103277481B (en) * | 2013-06-21 | 2015-10-14 | 广西柳工机械股份有限公司 | Hydraulic single-turbine torque converter |
| CN103277481A (en) * | 2013-06-21 | 2013-09-04 | 广西柳工机械股份有限公司 | Hydraulic single-turbine torque converter |
| CN103939566A (en) * | 2014-05-07 | 2014-07-23 | 吴志强 | Compound type double-guide-wheel hydraulic torque converter and continuously variable transmission |
| CN103939566B (en) * | 2014-05-07 | 2016-04-13 | 吴志强 | A kind of stepless speed variator with two guide-roller type fluid torque converter |
| CN105650236A (en) * | 2014-05-07 | 2016-06-08 | 吴志强 | Compound double-guide-wheel type hydraulic torque converter |
| CN104179924A (en) * | 2014-08-08 | 2014-12-03 | 洛阳雷斯达传动有限公司 | Hydraulic torque converter with flexible lock-out control function |
| CN104315106B (en) * | 2014-08-19 | 2017-02-15 | 中国北方车辆研究所 | Guide wheel shaft assembly of hydraulic torque converter |
| CN106678318A (en) * | 2015-11-10 | 2017-05-17 | 熵零股份有限公司 | Torque converter |
| CN106321771A (en) * | 2016-11-08 | 2017-01-11 | 哈尔滨广瀚动力传动有限公司 | Novel double-turbine double-guide wheel guide vane adjustable type hydraulic torque converter |
| CN106321771B (en) * | 2016-11-08 | 2018-12-18 | 哈尔滨广瀚动力传动有限公司 | A kind of double guide wheel guide vane adjustable hydraulic torque converters of novel twin turbines |
| CN106641166A (en) * | 2016-12-01 | 2017-05-10 | 陕西航天动力高科技股份有限公司 | Three-oil-way closed type automotive hydraulic torque converter |
| CN108612823A (en) * | 2018-06-25 | 2018-10-02 | 南京世界村汽车动力有限公司 | A kind of engine mission hydraulic torque converter |
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| GR01 | Patent grant | ||
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Effective date of registration: 20151112 Address after: 201108 Shanghai city Minhang District Huaning Road No. 3111 Building 1 room 629 Patentee after: Shanghai shine Heavy Industry Co., Ltd. Address before: 201108 Shanghai City Huaning Road No. 3111 Patentee before: The 711th Research Institute of China Shipbuilding Industrial Corporation(CSIC) |
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Granted publication date: 20100825 |