CN100360834C - Power transmission device for vehicle - Google Patents
Power transmission device for vehicle Download PDFInfo
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- CN100360834C CN100360834C CNB2004100904360A CN200410090436A CN100360834C CN 100360834 C CN100360834 C CN 100360834C CN B2004100904360 A CNB2004100904360 A CN B2004100904360A CN 200410090436 A CN200410090436 A CN 200410090436A CN 100360834 C CN100360834 C CN 100360834C
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Abstract
The invention is aimed to simplify a bearing structure by directly pivotally supporting a hollow turbine shaft by a driving shaft of an engine in a vehicular power transmission device. An output gear, a torque converter, a start clutch are arranged on a crankshaft in turn from the crankcase side toward the outside in a vehicular power transmission device. A turbine runner is arranged between an output drum of the start clutch and a pump impeller. Connection between the pump impeller and the output drum is executed via a connecting member. A turbine shaft, which connects between a hub of the turbine runner and the output gear, is freely rotatably fitted in the outer periphery of the crankshaft via a bearing. A hollow stator shaft joined to a hub of a stator is freely relatively rotatably fitted in the outer periphery of the turbine shaft.
Description
Technical field
The present invention relates to a kind of actuating unit that is used for such as the vehicle of motorcycle or automobile, relate more specifically to a kind of improved actuating unit that is used for vehicle, wherein, output gear, torque-converters and starting clutch are arranged on the live axle of motor outside side direction engine block, supporting driving shaft with this order, this torque-converters comprises pump impeller, turbine rotor and stator, and this starting clutch comprises clutch input block and clutch output block, like this, the power sequence delivery of live axle is given starting clutch, torque-converters and output gear.
Background technique
For example, the known this actuating unit that is used for vehicle in Japanese Patent Application Laid-Open 2001-141025 open.
At this transmission device powered by conventional energy that is used for vehicle, be connected on the periphery of live axle that hollow stator axle on the stator can be sleeved on motor with the relative rotation, the hollow vortex wheel shaft that is connected on the turbine rotor can be sleeved on the periphery of stator axis with the relative rotation, and output gear is arranged in the place, end of turbine shaft.Therefore, three can be counterrotating axle, be the inside that live axle, stator axis and turbine shaft are arranged in output gear, and two high-performance bearings that need to bear the output gear load are arranged between these the dual mating part, this makes the complex structure of bearing.And mating part needs high accuracy of manufacturing, with the accumulation looseness of the mating part that prevents three axles to output gear and and the driven gear of its engagement between backlash exert an influence.
Summary of the invention
Consider above-mentioned situation and finish the present invention, and the purpose of this invention is to provide a kind of actuating unit that is used for vehicle that its allows hollow vortex wheel shaft directly by the drive shaft bearing of motor, to simplify the structure of bearing.
To achieve these goals, in accordance with a first feature of the invention, a kind of actuating unit that is used for vehicle is provided, wherein, output gear, torque-converters and starting clutch with this order from engine block, one side direction of supporting driving shaft is arranged in outward on the live axle of motor, this torque-converters comprises pump impeller, turbine rotor and stator, and this starting clutch comprises clutch input block and clutch output block, like this, the power sequence delivery of live axle is given starting clutch, torque-converters and output gear is characterized in that: turbine rotor is arranged between starting clutch and the pump impeller; Pump impeller is connected by the connected element that covers turbine rotor with the clutch output block; The hollow vortex wheel shaft that connects turbine rotor wheel hub and output gear can be sleeved on the periphery of live axle with the relative rotation; One bearing and the corresponding position of output gear be arranged between live axle and the turbine shaft; The hollow stator axle that is connected on the stator wheel hub can be sleeved on the periphery of turbine shaft with the relative rotation; And the wheel hub of pump impeller can be sleeved on the periphery of stator axis with the relative rotation.
Engine block and live axle are corresponding to crank box 1 and bent axle 2 in the embodiment of the invention of describing after a while, and clutch input block and clutch output block are corresponding to first drive plate 5 and output Gu tube 9.
By first feature, turbine rotor is arranged between starting clutch and the pump impeller, and stator axis can be sleeved on the periphery of turbine shaft with the relative rotation, thereby the turbine shaft that allows to connect turbine rotor and output gear can be sleeved on the periphery of live axle with the relative rotation.Therefore, and if the corresponding position of output gear be between live axle and the turbine shaft and arrange that a bearing is just enough, to simplify the bearing structure of turbine shaft.And the part count between live axle and output shaft can reduce, reducing the accumulation of parts error, thereby minimize cause owing to this error, the backlash between output gear and respective gears changes, to reduce noise.
And pump impeller is connected on the clutch output block of starting clutch by coating member, thereby is minimized in the dead band between torque-converters and the starting clutch, so that the actuating unit compactness.
Except first feature,, only allow to be arranged between turbine shaft and the live axle to the overrunning clutch that live axle transmits reverse load from turbine shaft according to second feature of the present invention.
By second feature, this overrunning clutch only is arranged between turbine shaft and the live axle, allowing that the reverse load of output gear is passed to live axle, thereby by simple structure acquisition engine braking effect.
Except first or second feature, according to the 3rd feature of the present invention, the clutch output block is the output drum barrel with end wall, connected element is connected on the periphery of output drum barrel with fluid tight manner, described end wall is arranged to be close to the rear surface of turbine rotor, and and is defined between end wall and the turbine rotor in the grease chamber of the recycle oil channel connection between pump impeller and the turbine rotor.
By the 3rd feature, the end wall of the output drum barrel of starting clutch also is used as the side cover of the grease chamber that is limited to turbine rotor rear surface side, with the structure of simplification actuating unit, and also allow to make torque-converters and starting clutch next-door neighbour to arrange, thereby make the actuating unit compactness.
Except the 3rd feature, according to the 4th feature of the present invention, end wall is along the bowl-type rear surface bending of turbine rotor.
By the 4th feature, torque-converters and starting clutch can be close to layout, thereby make actuating unit compacter.
Except the 3rd feature, according to the 5th feature of the present invention, be connected to clutch input block on the turbine shaft and be arranged in the output drum barrel, and the blocking clutch that can connect clutch input block and output drum barrel is arranged between clutch input block and the output drum barrel.
The clutch input block is corresponding to second drive plate 40 in the embodiment of the invention of describing after a while.
By the 5th feature, the output drum barrel is shared by the blocking clutch and the starting clutch of direct connection pump impeller and turbine rotor, easily to make the assembly compactness of starting clutch and blocking clutch.
Except the 5th feature, according to the 6th feature of the present invention, only allow to transmit to the clutch input block of starting clutch the overrunning clutch of reverse load from the clutch input block of blocking clutch, be arranged between the clutch input block of the clutch input block of starting clutch and blocking clutch, and in the output drum barrel.
By the 6th feature, be used for providing the overrunning clutch of engine braking effect to be arranged in, thereby make starting clutch, blocking clutch and one-way clutch assembly compactness by starting clutch and the shared output drum barrel of blocking clutch.
The 7th feature according to the present invention, a kind of actuating unit that is used for vehicle is provided, wherein, output gear can be rotated to support on the live axle of motor, starting clutch and torque-converters are disposed in series between live axle and the output gear, and blocking clutch is arranged between the pump impeller and turbine rotor of torque-converters, it is characterized in that: starting clutch is a centrifugal type, it comprises first drive plate that is connected on the live axle, be connected to the output drum barrel and first connection set on the pump impeller of torque-converters, this first connection set is supported by first drive plate, and when first drive plate at a predetermined velocity or the more speed rotation time connect first drive plate and output drum barrel; And blocking clutch is a centrifugal type, it is included in second drive plate and second connection set that is connected in the output drum barrel on the turbine rotor, this second connection set is supported by second drive plate, and connects second drive plate and output drum barrel during with predetermined high speed rotating when second drive plate.
Live axle is corresponding to the bent axle 2 in the embodiment of the invention of describing after a while, and first connection set and second connection set correspond respectively to first clutch watts 7 and second clutch watts 42.
By the 7th feature, starting clutch and blocking clutch all are centrifugal type, and shared output drum barrel, thereby allow to simplify effectively the modular construction of two clutches, and make the assembly compactness.
Except the 7th feature,, only allow to be arranged between second drive plate and the live axle to the overrunning clutch that live axle transmits reverse load from second drive plate according to the 8th feature of the present invention.
By the 8th feature, that the overrunning clutch that only transmits reverse load is arranged on is starting clutch, that be connected to first drive plate on the live axle and blocking clutch, be connected between second drive plate on the turbine rotor, thereby obtain engine braking effect by the single overrunning clutch that is arranged in the transmission path, to simplify the structure of actuating unit significantly.
Except the 8th feature, according to the 9th feature of the present invention, first drive plate and second drive plate are spaced apart from each other, thereby first connection set and second connection set are toward each other, and overrunning clutch is arranged between first drive plate and second drive plate, this overrunning clutch comprises the clutch inside part that is connected on first drive plate, be connected to that second dish is gone up and around the clutch external lateral portion and the clutch element of clutch inside part, this clutch element is arranged between clutch inside part and the clutch external lateral portion, and allows to transmit reverse load from the clutch external lateral portion to the clutch inside part.
By the 9th feature, except first connection set and second connection set, space in the output drum barrel between second drive plate of first drive plate spaced from each other, starting clutch and blocking clutch also has effectiveness in the layout overrunning clutch, thereby makes starting clutch, blocking clutch and one-way clutch assembly compactness with high space efficiency.
Except in the 7th to the 9th feature any one, according to the tenth feature of the present invention, turbine rotor is arranged between pump impeller and the output drum barrel, pump impeller is connected by the connected element around turbine rotor with the output drum barrel, and the output drum barrel has the end wall between output drum barrel and turbine rotor rear surface, and this end wall defines and the grease chamber of the recycle oil channel connection between pump impeller and turbine rotor.
By the tenth feature, the end wall of output drum barrel also is used as the side cover of the grease chamber that is limited to turbine rotor rear surface side, with the structure of further simplification actuating unit, also allow torque-converters, starting clutch and blocking clutch assembly next-door neighbour to arrange, thereby make actuating unit compacter.
Except the tenth feature, according to the 11 feature of the present invention, the output drum barrel has a plurality of exhaust ports of next-door neighbour's end wall, and the oil of supplying with starting clutch and blocking clutch is expelled to the outside of output drum barrel by these exhaust ports.
By the 11 feature, the oil of supplying with the output drum barrel is used for active part lubricated and cooling starting clutch and blocking clutch, and be expelled to the outside of output drum barrel from the output open surfaces of drum barrel or exhaust port, and at this moment, foreign matter (for example, be included in the oil smear metal refuse powder) is also discharged with oil.Especially, exhaust port is arranged to be close to the end wall of output drum barrel, thereby prevent to remain on more deeply in the output drum barrel, to avoid causing the premature wear of the sliding contact part of starting clutch and blocking clutch owing to foreign matter such as the foreign matter of smear metal refuse powder.
The 12 feature according to the present invention, a kind of actuating unit that is used for vehicle is provided, wherein, output gear can be rotated to support on the live axle of motor, starting clutch and torque-converters are disposed in series between live axle and the output gear, it is characterized in that: torque-converters is arranged so that turbine rotor is arranged between pump impeller and the starting clutch; Starting clutch is a centrifugal type, it comprises the drive plate that is connected on the live axle, have end wall and be connected to output drum barrel and connection set on the pump impeller by the connected element around turbine rotor, this connection set is supported by drive plate, and when drive plate at a predetermined velocity or more speed when rotation connect drive plate and output drum barrel; And end wall is arranged such that the grease chamber is defined between the rear surface of end wall and turbine rotor, this grease chamber and the recycle oil channel connection between pump impeller and turbine rotor.
Live axle is corresponding to the bent axle 2 in the embodiment of the invention of describing after a while, and drive plate and connection set are corresponding to first drive plate 5 and first clutch watts 7.
By the 12 feature, the end wall of output drum barrel also as the side cover of the grease chamber that is limited to turbine rotor rear surface side, to simplify the structure of actuating unit, also allows torque-converters and starting clutch next-door neighbour to arrange, thereby makes the actuating unit compactness.
Except the 12 feature, according to the 13 feature of the present invention, the hollow vortex axle sleeve is contained on the periphery of live axle, the turbine hub spline fitted of this hollow vortex wheel shaft and turbine rotor, and has a output gear in its end, this output gear is rotatable, but can not axial motion, one second wheel hub and the turbine shaft spline fitted axially aligned with turbine hub, in the output drum barrel and only allow to be arranged between second wheel hub and the live axle to the overrunning clutch that live axle transmits reverse load from second wheel hub, and the wheel hub of end wall is rotatable but can not be bearing in axial motion on the outer surface of the turbine hub and second wheel hub.
Second wheel hub is corresponding to the second drive plate wheel hub 40h in the embodiment of the invention of describing after a while.
By the 13 feature, turbine hub, turbine shaft and second wheel hub can according to they function and carry out surface treatment respectively, for example nitriding or carburizing easily providing hardness according to function, thereby guarantees serviceability.And the wheel hub of end wall of output drum barrel is only rotatable and can not be bearing in axial motion on the outer surface of the turbine hub and second wheel hub, with the axial motion of control output drum barrel and pump impeller, thereby simplifies the axial positioning structure of output drum barrel and pump impeller.The output drum barrel has the wheel hub on the turbine hub of being bearing in and the second wheel hub outer surface, thereby has prevented coming off of output drum barrel self significantly, and makes the working stability of starting clutch.
Except the 13 feature, according to the 14 feature of the present invention, a pair of annular convex shoulder is formed on the turbine hub and second wheel hub, and this is to the wheel hub of annular convex shoulder cooperation with maintenance end wall between them, and the axial motion of restriction wheel hub.
By the 14 feature, the axial motion of output drum barrel and pump impeller can limit by very simple structure, wherein, keep a pair of annular convex shoulder of the end wall wheel hub of output drum barrel to be formed on the turbine hub and second wheel hub betwixt, thereby further simplify the axial positioning structure of output drum barrel and pump impeller.
According to the 15 feature of the present invention, a kind of actuating unit that is used for vehicle is provided, wherein, output gear can be rotated to support on the live axle of motor, starting clutch and torque-converters are disposed in series between live axle and the output gear, it is characterized in that: torque-converters is arranged so that turbine rotor is arranged between pump impeller and the starting clutch, the hollow vortex wheel shaft that connects turbine rotor and output gear rotatably is sleeved on the live axle, and the hollow stator axle that is connected on the stator of torque-converters rotatably is sleeved on the periphery of turbine shaft; Starting clutch is a centrifugal type, it comprises the drive plate that is connected on the live axle, is connected to output drum barrel and connection set on the pump impeller by the connected element around turbine rotor, this connection set is supported by drive plate, and when drive plate at a predetermined velocity or more speed when rotation connect drive plate and output drum barrel; And overrunning clutch is arranged between turbine shaft and the live axle, and this overrunning clutch only allows to transmit reverse load from turbine shaft to live axle.
Live axle is corresponding to the bent axle 2 in the embodiment of the invention of describing after a while.Drive plate is corresponding to first drive plate, and connection set is corresponding to first clutch watt.
By the 15 feature, torque-converters is arranged so that turbine rotor is arranged between pump impeller and the starting clutch, the hollow vortex wheel shaft that connects turbine rotor and output gear rotatably is sleeved on the live axle, the stator axis that is connected to simultaneously on the stator rotatably is sleeved on the periphery of turbine shaft, and starting clutch is a centrifugal type, it comprises the drive plate that is connected on the live axle, be connected to output drum barrel and connection set on the pump impeller by link around turbine rotor, this connection set is supported by drive plate, and when drive plate at a predetermined velocity or more speed when rotation connect drive plate and output drum barrel, thereby overrunning clutch is provided, is used under the situation that not interfered by starting clutch and stator axis, between turbine shaft and live axle, transmitting reverse load.Therefore, when vehicle deceleration,, also can under the situation that not interfered by other parts (for example, turbine shaft), obtain engine braking effect, and can simplify the structure of actuating unit by operating single overrunning clutch although there is starting clutch.
Except the 15 feature, according to the 16 feature of the present invention, overrunning clutch comprise be connected on the turbine shaft and radial arrangement the clutch external lateral portion of connection set inside, be connected on the live axle and by the clutch external lateral portion around the clutch inside part and be arranged in the clutch external lateral portion and the clutch inside part between clutch element.
By the 16 feature of the present invention, can utilize the space in the output drum barrel of starting clutch to arrange overrunning clutch, thereby make the actuating unit compactness.
The 17 feature according to the present invention, a kind of actuating unit that is used for vehicle is provided, wherein, output gear, torque-converters and starting clutch are arranged on the live axle of motor outside side direction engine block, supporting driving shaft with this order, this torque-converters comprises pump impeller, turbine rotor and stator, this starting clutch comprises clutch input block and clutch output block, like this, the power sequence delivery of live axle is given starting clutch, torque-converters and output gear, and it is characterized in that: turbine rotor is arranged between starting clutch and the pump impeller; Pump impeller is connected by the connected element that covers turbine rotor with the clutch output block; The hollow vortex wheel shaft that connects turbine rotor and output gear can be sleeved on the periphery of live axle with the relative rotation, and this output gear is arranged to be close to engine block; The hollow stator axle that is connected on the stator can be sleeved on the periphery of turbine shaft with the relative rotation; And when being arranged between output gear and the pump impeller at the sub flywheel that rotates of the increase of the moment of torsion between pump impeller and turbine rotor time limit formulation.
Engine block and live axle correspond respectively to crank box 1 and the bent axle 2 in the embodiment of the invention of describing after a while.
By the 17 feature, output gear can be arranged to be close to engine block under the situation that not interfered by flywheel.This has minimized owing to the transmission reaction of output gear bending moment that cause, live axle, thereby has improved live axle and be used for serviceability with the main bearing of drive shaft bearing on engine block.
Except the 17 feature, according to the 18 feature of the present invention, flywheel comprises: the flywheel inner disc, and this flywheel inner disc is connected on the stator axis; A plurality of pawl bars, these pawl bars are bearing on the side surface of flywheel inner disc by axle swingably, and are circular layout along the circumferential direction of flywheel inner disc; Flywheel coils outward, on the abutment wall that the outer dish of this flywheel is fixed on engine block is connected, and has around the pawl teeth in the interior perimeter surface of described a plurality of pawl bars, and a plurality of pawl bars can be with these pawl teeth engagements and from these pawl teeth disengagements; And spring, this spring promotes each pawl bar along the direction with the pawl teeth engagement, and when the moment of torsion between pump impeller and turbine rotor increased, the flywheel inner disc was locked on the outer dish of flywheel by pawl bar.
By the 18 feature, flywheel is arranged to axially flat, thereby makes the actuating unit compactness.
Except the 18 feature, according to the 19 feature of the present invention, in each pawl bar, be furnished with counterweight part, be used to centrifugal force that pawl bar is thrown off from pawl teeth against the thrust of spring to produce during with predetermined high speed rotating when the flywheel inner disc.
By the 19 feature, after moment of torsion increased, pump impeller and turbine rotor rotated with stator, and entered when being scheduled to the high speed rotating state when stator, and pawl bar can be thrown off from pawl teeth against the thrust of spring.This allows the sliding contact of pawl bar releasing and pawl teeth, and prevents wearing and tearing and noise by the sliding contact generation.
Except the 19 feature, according to the 20 feature of the present invention, the pump impeller hub is formed on the pump impeller, this pump impeller hub protrudes towards flywheel, and can be rotated to support on the outer surface of stator axis, a plurality of pawl bars by axle be bearing in the flywheel inner disc, on the side surface of pump impeller side, and pawl bar is arranged to around the pump impeller hub.
By the 20 feature of the present invention, protrude and the pump impeller hub that can be rotated to support on the outer surface of stator axis is formed on the pump impeller towards flywheel, to prevent that reliably the pump impeller on the turbine shaft from coming off, and a plurality of pawl bars are arranged to around the pump impeller hub, allowing space around the pump impeller hub to be used to that effectively pawl bar is installed and flywheel coils, thereby make the actuating unit compactness outward.
By below with reference to the accompanying drawing detailed description of the preferred embodiment, will know aforementioned and other purpose of the present invention, feature and advantage.
Description of drawings
Fig. 1 is according to an embodiment of the invention, is used for the vertical sectional view of the actuating unit of motorcycle.
Fig. 2 is the enlarged view of the part 2 among Fig. 1.
Fig. 3 cuts open the sectional view of getting along the line 3-3 among Fig. 1.
Fig. 4 cuts open the sectional view of getting along the line 4-4 among Fig. 1.
Fig. 5 cuts open the sectional view of getting along the line 5-5 among Fig. 1.
Fig. 6 is the perspective exploded view of flywheel.
Embodiment
In Fig. 1 and 2, bent axle 2 is bearing on the crank box 1 of the motor E that is installed on the motorcycle by main bearing 3.Output gear 4, torque-converters T, blocking clutch C2 and starting clutch C1 with this order from main bearing 3 sides towards crank box 1 the outside and be installed in bent axle 2, be protruding on the part of main bearing 3 outsides.
At first, the structure of starting clutch C1 will be described with reference to Figure 3.
Starting clutch C1 comprises: first drive plate 5, and this first drive plate 5 is connected on the end of bent axle 2; A pair of first clutch watts 7 and 7, this is bearing on first drive plate 5 by pivot 6 swingably to first clutch watts 7 and 7; A pair of first Returnning spring 8 and 8, this is connected between the first clutch watts 7 and 7 first Returnning spring 8 and 8, and promotes first clutch watts 7 and 7 along compression direction; And closed end cylindricality output drum barrel 9, this output drum barrel 9 is arranged to around first clutch watts 7 and 7.The first drive plate wheel hub 5h and bent axle 2 spline fitted at the center by will being formed on first drive plate 5, wherein make the first drive plate wheel hub 5h by control panel 11 and against the annular convex shoulder 10 of bent axle 2, and pass through nut 12 screw threads for fastening on bent axle 2, and first drive plate 5 is connected on the end of bent axle 2.
Can be combined on the outer surface of first clutch watts 7 and 7 with the friction lining 7a of interior perimeter surface sliding contact of output drum barrel 9 and 7a.Retainer 13 and 13 against the interior perimeter surface of first clutch watts 7 and 7 is arranged on first drive plate 5, reduces the diameter of first clutch watts 7 and 7 with restriction.The weight of first clutch watts 7 and 7 and the constantly acting load of Returnning spring 8 and 8 are arranged to like this, promptly when bent axle 2 at a predetermined velocity or be higher than speed when rotation of idling speed, first clutch watts 7 and 7 expands by action of centrifugal force, so that friction lining 7a and 7a press the interior perimeter surface of output drum barrel 9.
Below, will introduce the structure of torque-converters T.
With reference to Fig. 1 and 2, torque-converters T comprises again: pump impeller 15; Turbine rotor 16, this turbine rotor 16 are arranged to facing to pump impeller 15; And stator 17, this stator 17 is arranged between the interior circumferential portion of pump impeller 15 and turbine rotor 16.Recycle oil passage 18 working oil, that be used for transmission is limited to three parts 15,16 and 17.
It should be noted that pump impeller 15 is arranged in crank box 1 side, and turbine rotor 16 is arranged in output drum barrel 9 sides, that is, turbine rotor 16 is arranged between pump impeller 15 and the output drum barrel 9.Be connected on the shell of pump impeller 15 above turbine rotor 16 axially extended cylindricality connected element 14 one from the periphery of pump impeller 15 shells, the top of connected element 14 is waited and is connected to fluid-tight fashion on the outer surface of output drum barrel 9 by welding.
The wheel hub of turbine rotor 16, promptly turbine hub 16h spline is connected on the periphery of hollow vortex wheel shaft 20, and this turbine shaft 20 can be sleeved on the periphery of bent axle 2 with the relative rotation.One end of turbine shaft 20 is arranged through oil pump actuation gear 26 and needle roller thrust bearing 22 and against the inner race of main bearing 3, and the other end is arranged to against control panel 11.Finally, turbine shaft 20 remains between needle roller thrust bearing 22 and the control panel 11, and has suppressed the axial motion of turbine shaft 20.
Output gear 4 splines of contiguous needle roller thrust bearing 22 are connected on the periphery of turbine shaft 20.Be connected to driven gear 25 and output gear 4 engagements on the transmission input shaft (not shown).Radial needle bearing 23 is arranged between turbine shaft 20 and the bent axle 2, and is positioned at and output gear 4 corresponding positions.
The wheel hub of stator 17, promptly stator wheel hub 17h is connected with hollow stator axle 21 splines, and this hollow stator axle 21 is sleeved on the periphery of turbine shaft 20 rotatably.The wheel hub of pump impeller 15, promptly pump impeller hub 15h by the outer surface of stator axis 21 by bearing sleeve 24 and rotatably mounted.
Only allow stator 17 along the flywheel F of predetermined direction rotation be connected to stator axis 21, from pump impeller hub 15h towards output gear on 4 tops of protruding.
Shown in Fig. 1,2,5 and 6, flywheel F comprises: flywheel inner disc 27, this flywheel inner disc 27 wait by welding and are connected on the top of stator axis 21; A plurality of pawl bars 29, these pawl bars 29 are bearing on the side surface of flywheel inner disc 27 swingably by pivot 28, and in pump impeller 15 sides; And the outer dish 30 of flywheel, the outer dish of this flywheel 30 is fixed on the abutment wall 1a that is connected with crank box 1 by bolt 32, and around these a plurality of pawl bars 29.Pawl teeth 31 is formed in the interior perimeter surface of the outer dish 30 of flywheel, and these a plurality of pawl bars 29 can and be thrown off with these pawl teeth 31 engagements.Each pawl bar 29 at one end has pawl 29a, and this pawl 29a and pawl teeth 31 engagements are also thrown off, and have counterweight 29b at the other end, and pivot 28 is between this pawl 29a and counterweight 29b.Spiral winding spring 33 is installed on the pivot 28, locking aperture 34 Elastic Meshing at the hook 33a and the flywheel inner disc 27 at spring 33 1 end places, and in locking aperture 35 Elastic Meshing of the hook 33b and the counterweight 29b at the other end place, thereby promote pawl bar 29 along direction with pawl teeth 31 engagements.Flywheel inner disc 27 is provided with retainer 36, and this retainer 36 provides the swing limit in its high speed rotating process when each pawl bar 29 is thrown off with pawl teeth 31 by the centrifugal action of counterweight 29b.The soundproof material 37 of rubber or synthetic resin is attached on the sliding bevel of pawl teeth 31.
Therefore, flywheel F is arranged between pump impeller 15 and the output gear 4, and especially, the outer dish 30 of a plurality of pawl bars 29 and flywheel is arranged on the periphery of pump impeller hub 15h, thereby around pump impeller hub 15h.
Below, will introduce the structure of blocking clutch C2 with reference to figure 1 and 4.
Blocking clutch C2 comprises: second drive plate 40, this second drive plate 40 have the second drive plate wheel hub 40h, and this second drive plate wheel hub 40h spline is connected on the periphery of turbine shaft 20, and axially aligns with turbine hub 16h; A pair of second clutch watts 42 and 42, this is bearing on second drive plate 40 by pivot 41 swingably to second clutch watts 42 and 42; A pair of second Returnning spring 43 and 43, this is connected between the second clutch watts 42 and 42 second Returnning spring 43 and 43, and reduces direction along diameter and promote second clutch watts 42 and 42; And output drum barrel 9, this output drum barrel 9 is arranged to around second clutch watts 42 and 42.Therefore, output drum barrel 9 is shared by starting clutch C1 and blocking clutch C2.
At this moment, first drive plate 5 of starting clutch C1 is arranged in the open surfaces side of output drum barrel 9, and second drive plate 40 of blocking clutch C2 is arranged in the end wall 9a side of output drum barrel 9, so clutch shoe 7 and 42 is arranged to toward each other.This allows the space between drive plate 5 and 40 can be used to install clutch shoe 7 and 42 effectively.
Can be combined on the outer surface of second clutch watts 42 and 42 with the friction lining 42a of interior perimeter surface sliding contact of output drum barrel 9 and 42a.Retainer 44 and 44 against the interior perimeter surface of second clutch watts 42 and 42 is arranged on second drive plate 40, thereby restriction reduces the diameter of second clutch watts 7 and 7.The weight of second clutch watts 42 and 42 and the constantly acting load of Returnning spring 43 and 43 are arranged to like this, promptly when turbine shaft 20 enters predetermined high speed rotating state, second clutch watts 42 and 42 expands by action of centrifugal force, so that friction lining 42a and 42a press the interior perimeter surface of output drum barrel 9.Second drive plate 40 is being provided with one or more hydraulic fluid ports 49 near the part place at center, and this hydraulic fluid port 49 provides the circulation between second drive plate 40 inside and outside.
The aduncate drum barrel wheel hub of axial direction 9h along output drum barrel 9 forms by deburring (burring) on the interior Zhou Duan of the end wall 9a that exports drum barrel 9.Drum barrel wheel hub 9h can be rotated to support on the periphery of the turbine hub 16h and the second drive plate wheel hub 40h by bearing sleeve 45.Therefore, the end wall 9a of output drum barrel 9 is as the side cover that limits the 18a of grease chamber, and the 18a of this grease chamber is communicated with the periphery of recycle oil passage 18 between the rear surface of end wall 9a and turbine rotor 16.End wall 9a is along the bowl-type rear surface bending of turbine rotor 16, and is arranged to be close to this rear surface.This makes the volume of the 18a of grease chamber reduce to minimum, and allows torque-converters T, starting clutch C1 and blocking clutch C2 can be close to layout, thereby makes the actuating unit compactness.
In the perisporium of output drum barrel 9, circumferentially be drilled with a plurality of exhaust ports 46 alignedly on edge, next-door neighbour's end wall 9a place, these exhaust ports 46 make the inside of exporting drum barrel 9 towards outside opening, and the lubricated and cold oil in the inflow output drum barrel 9 is discharged to the outside of exporting drum barrel 9 by this exhaust port 46 together with foreign matter (for example, the friction refuse powder of friction lining 7a and 42a).
The turbine hub 16h adjacent one another are and the second drive plate wheel hub 40h remain between the annular convex shoulder 47 and control panel 11 on the periphery that is formed at turbine shaft 20 middle parts, and have suppressed the axial motion of the turbine hub 16h and the second drive plate wheel hub 40h.Drum barrel wheel hub 9h remain on the turbine hub 16h and the second drive plate wheel hub 40h, annular convex shoulder 48 respect to one another and 48 ' between, thereby suppress the axial motion of drum barrel wheel hub 9h, and therefore suppressed by connected element 14 and each other in holistic pump impeller 15 and the axial motion of exporting drum barrel 9.And, drum barrel wheel hub 9h protrudes towards the inside of output drum barrel 9 from the interior Zhou Duan of end wall 9a, and drum barrel wheel hub 9h is by bearing sleeve 45 and by turbine hub 16h and second drive plate wheel hub 40h supporting, preventing that reliably exporting drum barrel 9 comes off, and make the working stability of starting clutch C1 and blocking clutch C2.
In output drum barrel 9, be arranged between turbine shaft 20 and the bent axle 2 to the overrunning clutch C3 that bent axle 2 transmits reverse load from turbine shaft 20 only.Overrunning clutch C3 has cylindricality clutch external lateral portion 50, and these clutch external lateral portion 50 one are connected on the second drive plate wheel hub 40h, and this second drive plate wheel hub 40h spline is connected on the turbine shaft 20.Clutch external lateral portion 50 surpasses control panel 11 and radially is arranged in first clutch watts 7 and second clutch watt 42 inside.By clutch external lateral portion 50 concentric rings around clutch inside part 51 and the periphery spline fitted of the first drive plate wheel hub 5h, and a plurality of clutch elements that are circular layout 52 (for example diagonal brace or roller) are arranged between clutch external lateral portion 50 and the clutch inside part 51, thereby allow to transmit reverse load from clutch external lateral portion 50 to clutch inside part 51.Constituted overrunning clutch C3 like this.
The oil supply gallery 55 and the oil drain passage 59 of longitudinal extension are arranged in the bent axle 2.From the oil that the oil pump (not shown) that is driven by oil pump actuation gear 26 is discharged, supply with oil supply gallery 55 from the end of bent axle 2.The first, the 3rd and second annular oil storage pool 56
1, 56
3With 56
2Begin to be arranged between bent axle 2 and the turbine shaft 20 from control panel 11 sides.First and second hydraulic fluid ports 57
1With 57
2Extend radially out from oil supply gallery 55, to arrive first and second oil storage pools 56
1With 56
2, and the 3rd hydraulic fluid port 57
3Extend radially out from oil drain passage 59, to arrive the 3rd oil storage pool 56
3 Oil drain passage 59 is connected on the unshowned lubricated part among the motor E.
In said structure, turbine shaft 20, output gear 4 and the second drive plate wheel hub 40h and clutch external lateral portion 50 carry out carburizing, so that their surface hardness maximum.Turbine hub 16h and stator wheel hub 17h with spline fitted part carry out nitriding, so that their surface hardness increases to the degree of expectation.Therefore, output gear 4, turbine shaft 20, turbine hub 16h, stator wheel hub 17h and the second drive plate wheel hub 40h carry out surface treatment (for example nitriding or carburizing) respectively according to its function, easily providing hardness according to function, thereby guarantee serviceability.
Below, will introduce the operation of present embodiment.
In the working procedure of motor E, supply with the part oil of oil supply gallery 55 by first hydraulic fluid port 57 from unshowned oil pump
1Flow into first oil storage pool 56
1In, the surface of revolution of lubricated bent axle 2 and turbine shaft 20, and by the gap between surface of revolution, to pass through in the end of stator axis 21 and the gap between the control panel 11, and the spline fitted part of supply between turbine shaft 20 and the turbine hub 16h and the second drive plate wheel hub 40h, with lubricated these parts.
Remaining part oil in oil supply gallery 55 is by second hydraulic fluid port 57
2Flow into second oil storage pool 56
2In, by side mouth 58
1With 58
2Supply with recycle oil passage 18 by the gap between stator 17 and pump impeller 15, and the circulation in recycle oil passage 18 as shown by arrows by the centrifugal action that is produced by the rotation of pump impeller 15, and a part that should oil is by the gap between stator 17 and turbine rotor 16 and subsequently by side mouth 58
3, the 3rd oil storage pool 56
3With the 3rd hydraulic fluid port 57
3And be expelled to oil drain passage 59.
Remaining part oil in recycle oil passage 18 enters the 18a of grease chamber from the part between the periphery of pump impeller 15 and turbine rotor 16, then enter in the output drum barrel 9, while lubricating bearings lining 45, part oil flow on the active part of starting clutch C1 and blocking clutch C2 by a plurality of hydraulic fluid ports 49 of drive plate 40, to be used for lubricated and to cool off this active part.At last, the oil in output drum barrel 9 is discharged to the outside of exporting drum barrel 9 from the open surfaces or the exhaust port 46 of output drum barrel 9.
At this moment, foreign matter (for example, the friction refuse powder of friction lining 7a and 42a) is discharged with oil.Especially, exhaust port 46 is arranged to be close to the end wall 9a of output drum barrel 9, thereby prevent to remain on more deeply in the output drum barrel 9, and avoid owing to the foreign matter such as friction refuse powder causes the friction lining 7a of clutch shoe 7 and 42 and the premature wear of 42a such as the foreign matter of friction refuse powder.
At second oil storage pool 56
2In a part of oil from the clearance leakage between bent axle 2 and turbine shaft 20, and supply with radial needle bearing 23 and needle roller thrust bearing 22, with lubricated this radial needle bearing 23 and needle roller thrust bearing 22.
In the idle running process of bent axle 2, first clutch watts 7 and 7 remains on diameter and reduces the position, herein first clutch watts 7 and 7 by the constantly acting load of first Returnning spring 8 and 8 against retainer 13 and 13, the interior perimeter surface of friction lining 7a and 7a and output drum barrel 9 is spaced apart, and therefore, starting clutch C1 keeps OFF (closing) state.Therefore, although torque-converters T is arranged, vehicle can remain on arrested state.
When bent axle 2 at a predetermined velocity or be higher than speed when rotation of the rpm that dallies, first clutch watts 7 and 7 is swung along expansion direction against the constantly acting load of first Returnning spring 8 and 8 by centrifugal force, and when friction lining 7a and 7a pressed the interior perimeter surface of output drum barrel 9, starting clutch C1 entered ON (opening) state.Therefore, export the rotation that drum barrel 9 is taken bent axle 2 out of, and pass to the pump impeller 15 of torque-converters T by connected element 14.
When pump impeller 15 rotates by output drum barrel 9, the working oil that is full of recycle oil passage 18 passes to turbine rotor 16 with the rotation torque of pump impeller 15, be circulated to turbine rotor 16, stator 17 and pump impeller 15 by centrifugal action from pump impeller 15 simultaneously, shown in arrow among Fig. 1; This working oil from turbine shaft 20 to output gear 4 transmitting torques; And also pass to the driving wheel of vehicle by unshowned actuating unit, with driving wheel, thus the starting vehicle.At this moment, connect vibration even produce in starting clutch C1, this vibration also can be absorbed by torque-converters T, to guarantee the smooth starting of vehicle.
When the moment of torsion that in torque-converters T, is increased between pump impeller 15 and the turbine rotor 16, follow the reaction force of this increase to be applied on the stator 17, but stator 17 prevents rotation with flywheel inner disc 27 by locking flywheel F (that is the engagement between pawl bar 29 and pawl teeth 31 bottoms).
When the increase of moment of torsion finished, stator 17 rotated along equidirectional with pump impeller 15 and turbine rotor 16, made flywheel F idle running by the reactive torque that is received by stator 17 simultaneously, that is, pawl bar 29 slides on the inclined-plane of pawl teeth 31.When flywheel inner disc 27 enters predetermined high speed rotating state with turbine rotor 16, each pawl bar 29 is swung along the direction of separating with pawl teeth 31 by being applied to the action of centrifugal force on the counterweight 29b, and the sliding contact of releasing and pawl teeth 31, thereby prevent the wearing and tearing and the noise that produce owing to sliding contact.
The rotation of turbine shaft 20 also passes to second drive plate 40 of blocking clutch C2.Therefore, when turbine rotor 16 during with predetermined high speed rotating, second clutch watts 42 and 42 is swung along expansion direction against the constantly acting load of second Returnning spring 43 and 43 by centrifugal force, so that friction lining 42a and 42a press the interior perimeter surface of output drum barrel 9, thereby blocking clutch C2 enters locking states.Therefore, pump impeller 15 is connected with turbine shaft 20 direct mechanical, thereby has eliminated the slippage loss between turbine rotor 16 and pump impeller 15, to increase transmission efficiency.
If reverse load passes to turbine shaft 20 from output gear 4 in the moderating process of vehicle, overrunning clutch C3 just enters coupled condition so, and reverse load passes to bent axle 2 from turbine shaft 20 orders by the second drive plate wheel hub 40h, clutch external lateral portion 50, clutch element 52, clutch inside part 51 and the first drive plate wheel hub 5h.Therefore, torque-converters T and starting clutch C1 are walked around in the reverse load bypass of output gear 4, and pass to bent axle 2, thereby, all will obtain gratifying engine braking effect no matter starting clutch C1 is in the slip between OFF state and turbine rotor 16 and the pump impeller 15.
Output gear 4 is arranged to the main bearing 3 of next-door neighbour's crank box 1 under the situation that not interfered by flywheel F, thereby has reduced by the driving reaction force of output gear 4 bending moment that cause, bent axle 2, and improves the serviceability of bent axle 2 and main bearing 3.And turbine rotor 16 is arranged between starting clutch C1 and the pump impeller 15, and stator axis 21 can be sleeved on the periphery of turbine shaft 20 with the relative rotation, thereby allows turbine shaft 20 to be sleeved on the relative rotation on the periphery of bent axle 2.Therefore, if make a bearing 23 and output gear 4 corresponding positions be arranged between bent axle 2 and the turbine shaft 20 just enough, thereby simplified the bearing structure of turbine shaft 20.And part count between bent axle 2 and output gear 4 reduces, reducing the accumulation of parts error, thereby suppress to cause owing to this error, the backlash between output gear 4 and driven gear 25 changes, thereby the reduction noise.
And pump impeller 15 is connected on the output drum barrel 9 of starting clutch C1 and blocking clutch C2 by connected element 14, thereby is minimized in the dead band between torque-converters T, starting clutch C1 and the blocking clutch C2, so that the actuating unit compactness.
The end wall 9a of output drum barrel 9 also is used as the side cover of the 18a of grease chamber that is limited to turbine rotor 16 rear surface sides, thereby has simplified the structure of actuating unit, also allows torque-converters T and starting clutch C1 next-door neighbour to arrange, thereby makes the actuating unit compactness.
The end wall 9a of output drum barrel 9 arranges thereby allow torque-converters T and output drum barrel 9 to be close to, and makes actuating unit compacter along the bowl-type rear surface bending of turbine rotor 16.
Starting clutch C1 and blocking clutch C2 are centrifugal type, and a shared output drum barrel 9, thereby allow to simplify effectively the modular construction of two clutch C1 and C2, and make this modular construction compactness.
And, overrunning clutch C3 is arranged between second drive plate 40 of first drive plate 5 of starting clutch C1 and blocking clutch C2, and the shared output drum barrel 9 of starting clutch C1 and blocking clutch C2, thereby make that with high efficiency the assembly of starting clutch C1, blocking clutch C2 and overrunning clutch C3 is obviously compact.
Be arranged in stator axis 21 on the periphery of turbine shaft 20 by being arranged in the flywheel F between pump impeller 15 and the output gear 4 and be connected, thereby effectively utilize space between pump impeller 15 and output gear 4, that be used to install flywheel F with abutment wall 1a on being connected to crank box 1.Especially, flywheel F is the ratchet type, and pawl bar 29 and the outer dish 30 of flywheel with pawl teeth 31 be arranged on the periphery of pump impeller hub 15h, with around pump impeller hub 15h, thereby effectively utilize the very little space between pump impeller 15 and output gear 4, so that actuating unit is compacter.
The present invention is not limited to the foregoing description, and under the situation that does not break away from theme of the present invention, can carry out various design modification.For example, ball bearing or plane bearing can be used to replace radial needle bearing 23.
Claims (12)
1. actuating unit that is used for vehicle, wherein, output gear, torque-converters and starting clutch are arranged on the live axle of motor outside side direction engine block, supporting driving shaft with this order, this torque-converters comprises pump impeller, turbine rotor and stator, and this starting clutch comprises clutch input block and clutch output block, like this, the power sequence delivery of live axle is given starting clutch, torque-converters and output gear, it is characterized in that:
This turbine rotor is arranged between starting clutch and the pump impeller; Pump impeller is connected by the connected element that covers turbine rotor with the clutch output block; One connects the hollow vortex wheel shaft of turbine rotor wheel hub and output gear, can be sleeved on the periphery of live axle with the relative rotation; One bearing and the corresponding position of output gear be arranged between live axle and the turbine shaft; Be connected to the hollow stator axle on the stator wheel hub, can be sleeved on the periphery of turbine shaft with the relative rotation; And the wheel hub of pump impeller can be sleeved on the periphery of stator axis with the relative rotation.
2. the actuating unit that is used for vehicle according to claim 1 is characterized in that: an overrunning clutch is arranged between turbine shaft and the live axle, and this overrunning clutch only allows to transmit reverse load from described turbine shaft to described live axle.
3. the actuating unit that is used for vehicle according to claim 1 and 2 is characterized in that: described clutch output block is the output drum barrel with end wall; Described connected element is connected on the periphery of output drum barrel with fluid tight manner; This end wall is arranged to be close to the rear surface of turbine rotor; And and be defined between end wall and the turbine rotor in the grease chamber of the recycle oil channel connection between pump impeller and the turbine rotor.
4. the actuating unit that is used for vehicle according to claim 3 is characterized in that: described end wall is along the bowl-type rear surface bending of turbine rotor.
5. the actuating unit that is used for vehicle according to claim 3 is characterized in that: a clutch input block that is connected on the described turbine shaft is arranged in the described output drum barrel; And a blocking clutch that can connect this clutch input block and output drum barrel is arranged between this clutch input block and the output drum barrel.
6. the actuating unit that is used for vehicle according to claim 5, it is characterized in that: an overrunning clutch is arranged between the clutch input block of the clutch input block of described starting clutch and described blocking clutch and in the output drum barrel, and this overrunning clutch only allows to transmit reverse load from the clutch input block of described blocking clutch to the clutch input block of starting clutch.
7. actuating unit that is used for vehicle, wherein, output gear can be rotated to support on the live axle of motor, and starting clutch and torque-converters are disposed in series between live axle and the output gear, it is characterized in that:
This torque-converters is arranged so that a turbine rotor is arranged between pump impeller and the starting clutch, a hollow vortex wheel shaft that connects turbine rotor and output gear rotatably is sleeved on this live axle, and a hollow stator axle that is connected on the stator of torque-converters rotatably is sleeved on the periphery of turbine shaft;
This starting clutch is a centrifugal type, it comprises the drive plate that is connected on the live axle, is connected to output drum barrel and connection set on the pump impeller by the connected element around turbine rotor, this connection set is supported by drive plate, and when drive plate at a predetermined velocity or more speed when rotation connect drive plate and output drum barrel; And
One overrunning clutch is arranged between this turbine shaft and the live axle, and this overrunning clutch only allows to transmit reverse load from turbine shaft to live axle.
8. the actuating unit that is used for vehicle according to claim 7 is characterized in that: described overrunning clutch comprise be connected on the turbine shaft and radial arrangement the clutch external lateral portion of described connection set inside, be connected on the live axle and by the clutch external lateral portion around the clutch inside part and be arranged in the clutch external lateral portion and the clutch inside part between clutch element.
9. actuating unit that is used for vehicle, wherein, output gear, torque-converters and starting clutch are arranged on the live axle of motor outside side direction engine block, supporting driving shaft with this order, this torque-converters comprises pump impeller, turbine rotor and stator, and this starting clutch comprises clutch input block and clutch output block, like this, the power sequence delivery of live axle is given starting clutch, torque-converters and output gear, it is characterized in that:
This turbine rotor is arranged between starting clutch and the pump impeller; Pump impeller is connected by the connected element that covers turbine rotor with the clutch output block; A hollow vortex wheel shaft that connects turbine rotor and output gear can be sleeved on the periphery of live axle with the relative rotation, and this output gear is arranged to be close to engine block; A hollow stator axle that is connected on the stator wheel hub can be sleeved on the periphery of turbine shaft with the relative rotation; And the flywheel of the increase of the moment of torsion between pump impeller and turbine rotor time limit formulation rotation is arranged between output gear and the pump impeller.
10. the actuating unit that is used for vehicle according to claim 9 is characterized in that, described flywheel comprises: the flywheel inner disc, and this flywheel inner disc is connected on the stator axis; A plurality of pawl bars, these pawl bars are bearing on the side surface of flywheel inner disc by axle swingably, and are circular layout along the circumferential direction of flywheel inner disc; Flywheel coils outward, on the abutment wall that the outer dish of this flywheel is fixed on engine block is connected, and has around the pawl teeth in the interior perimeter surface of these a plurality of pawl bars, and a plurality of pawl bars can be with these pawl teeth engagements and from these pawl teeth disengagements; And spring, this spring promotes each pawl bar along the direction with the pawl teeth engagement; And when the moment of torsion between pump impeller and turbine rotor increased, the flywheel inner disc was locked on the outer dish of flywheel by pawl bar.
11. the actuating unit that is used for vehicle according to claim 10, it is characterized in that: in each pawl bar, be furnished with counterweight part, be used for centrifugal force that pawl bar is thrown off from pawl teeth against the thrust of spring to produce during with predetermined high speed rotating when described flywheel inner disc.
12. the actuating unit that is used for vehicle according to claim 11 is characterized in that: a pump impeller hub is formed on the described pump impeller, and this pump impeller hub protrudes towards flywheel, and can be rotated to support on the outer surface of stator axis; Described a plurality of pawl bar by axle be bearing in the flywheel inner disc, on the side surface of pump impeller side; And described pawl bar is arranged to around the pump impeller hub.
Applications Claiming Priority (10)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003392925A JP4414206B2 (en) | 2003-11-21 | 2003-11-21 | Power transmission device for vehicle |
| JP2003392925 | 2003-11-21 | ||
| JP2003392926 | 2003-11-21 | ||
| JP2003392924A JP4414205B2 (en) | 2003-11-21 | 2003-11-21 | Power transmission device for vehicle |
| JP2003392924 | 2003-11-21 | ||
| JP2003392923A JP4414204B2 (en) | 2003-11-21 | 2003-11-21 | Power transmission device for vehicle |
| JP2003392923 | 2003-11-21 | ||
| JP2003392926A JP2005155725A (en) | 2003-11-21 | 2003-11-21 | Vehicular power transmission device |
| JP2003392922 | 2003-11-21 | ||
| JP2003392922A JP4414203B2 (en) | 2003-11-21 | 2003-11-21 | Power transmission device for vehicle |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007103076337A Division CN101323251B (en) | 2003-11-21 | 2004-11-18 | Vehicular power transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1619186A CN1619186A (en) | 2005-05-25 |
| CN100360834C true CN100360834C (en) | 2008-01-09 |
Family
ID=34799851
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100904360A Expired - Fee Related CN100360834C (en) | 2003-11-21 | 2004-11-18 | Power transmission device for vehicle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100360834C (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012237418A (en) * | 2011-05-13 | 2012-12-06 | Yutaka Giken Co Ltd | Hydraulic power transmission with lock-up clutch |
| JP5258950B2 (en) * | 2011-11-24 | 2013-08-07 | 株式会社エクセディ | Torque converter |
| JP6260556B2 (en) * | 2015-03-03 | 2018-01-17 | トヨタ自動車株式会社 | Torsional vibration reduction device |
| CN109253213B (en) * | 2018-11-27 | 2019-09-24 | 安徽江淮汽车集团股份有限公司 | A kind of normal engagement starts the flywheel of motor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1214610A (en) * | 1969-02-26 | 1970-12-02 | Borg Warner | Transmission mechanism |
| JP2000205373A (en) * | 1998-11-13 | 2000-07-25 | Yutaka Giken Co Ltd | Transmission device for compact vehicle |
| JP2000213625A (en) * | 1998-11-20 | 2000-08-02 | Yutaka Giken Co Ltd | Transmission gear for small-sized vehicle |
| JP2000213626A (en) * | 1998-11-20 | 2000-08-02 | Yutaka Giken Co Ltd | Transmission gear for small-sized vehicle |
| JP2002130426A (en) * | 2000-10-30 | 2002-05-09 | Unisia Jecs Corp | Hydraulic pump for automatic transmission |
| JP2003154862A (en) * | 2001-11-20 | 2003-05-27 | Exedy Corp | Torque transmission device |
| JP2003214524A (en) * | 2002-01-24 | 2003-07-30 | Yutaka Giken Co Ltd | Torque converter |
-
2004
- 2004-11-18 CN CNB2004100904360A patent/CN100360834C/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1214610A (en) * | 1969-02-26 | 1970-12-02 | Borg Warner | Transmission mechanism |
| JP2000205373A (en) * | 1998-11-13 | 2000-07-25 | Yutaka Giken Co Ltd | Transmission device for compact vehicle |
| JP2000213625A (en) * | 1998-11-20 | 2000-08-02 | Yutaka Giken Co Ltd | Transmission gear for small-sized vehicle |
| JP2000213626A (en) * | 1998-11-20 | 2000-08-02 | Yutaka Giken Co Ltd | Transmission gear for small-sized vehicle |
| JP2002130426A (en) * | 2000-10-30 | 2002-05-09 | Unisia Jecs Corp | Hydraulic pump for automatic transmission |
| JP2003154862A (en) * | 2001-11-20 | 2003-05-27 | Exedy Corp | Torque transmission device |
| JP2003214524A (en) * | 2002-01-24 | 2003-07-30 | Yutaka Giken Co Ltd | Torque converter |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1619186A (en) | 2005-05-25 |
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