CN103166360A - Motor support for a hybrid electric transmission - Google Patents
Motor support for a hybrid electric transmission Download PDFInfo
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- CN103166360A CN103166360A CN2012103977086A CN201210397708A CN103166360A CN 103166360 A CN103166360 A CN 103166360A CN 2012103977086 A CN2012103977086 A CN 2012103977086A CN 201210397708 A CN201210397708 A CN 201210397708A CN 103166360 A CN103166360 A CN 103166360A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/26—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the motors or the generators
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
- B60K6/405—Housings
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
- B60K6/48—Parallel type
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Hybrid Electric Vehicles (AREA)
Abstract
An assembly for supporting a motor of a vehicle power train includes a housing, a stator secured to the housing, a bearing having a radial position established by the housing, a member contacting the bearing, and a rotor secured to the member and including a radial outer surface spaced radially from the stator by an air gap established by contact between the bearing and the member.
Description
Technical field
The present invention relates to the dynamical system of hybrid electric vehicle, relate in particular to the rotor of supporting motor and stator to produce betwixt and to keep accurate air gap.
Background technology
Hybrid electric vehicle (HEVs) has explosive motor and motor, and they can be alternately or are used for propelled vehicles in the mode of combination.Multiple different power train is used in motor vehicle driven by mixed power.The present invention relates to configuration in parallel, wherein engine is connected to motor by disconnect-type clutch, the torque-converters input of motor driven automatic transmission.Hydrodynamic transmission has the output that is connected to the differential mechanism that two driving wheels with vehicle couple.The driving-chain power of this parallel mixed power electric vehicle known in the art is spread and is put.
The problem that the HEV designer faces is rotor and the stationary part of how cooling separation type clutch and motor.Various cooling systems based on air and liquid have been proposed; Yet most of system is all expensive and causes packing problem when attempting to convert non-motor vehicle driven by mixed power to the hybrid power operational mode.Disconnect-type clutch, motor, torque-converters and automatic transmission need to be packed with compact way, so that conventional truck can or not exist automobile body to change to be reconfigured for hybrid power system with relatively low cost and the change of automobile body seldom.
Summary of the invention
A kind of assembly of the motor for supporting automotive power, comprise shell, be fixed to shell stator, have bearing, the assembly of contact bearing and the rotor that is fixed to described assembly of the radial position of being determined by shell, described rotor comprises by air gap and the radially spaced radially-outer surface of stator, and described air gap is determined by the contact between bearing and described assembly.
The present invention relates to novel hybrid electric vehicle and parts and the subassembly of a plurality of novelties, it is particularly suitable for reorientating interior disconnect-type clutch and the motor of wet side of automatic transmission.This is not in the situation that change the conventional power stream that engine, disconnect-type clutch, motor, torque-converters, speed changer be connected in series and complete.
The invention provides the drive shell that engine is connected to the input side that is repositioned at the disconnect-type clutch in the automatic transmission shell, and be not as typically in non-motor vehicle driven by mixed power, torque-converters being connected directly to engine.Drive shell has consisted of big or small enough annular chambers that freely holds torque-converters.Motor also is arranged in the wet district of automatic transmission, and this is wet distinguishes preferably annulate shaft around disconnect-type clutch.The rotor of motor is connected to the output of disconnect-type clutch.Disconnect-type clutch is exported to be connected with rotor and is coupled to the armature spindle that is connected with the input turbine of torque-converters.Torque converter stator and output turbine are connected to respectively tubular stator axle and transmission input shaft.Transmission input shaft, stator axis, armature spindle and disconnect-type clutch hub (hub) and can be used by the annular opening of automatic transmission shell front side all concentrically with respect to one another.
Similar with traditional torque-converters, torque-converters and drive shell can be arranged on the front of gearbox case removedly.Drive shell is connected to mounting panel, rather than torque-converters is connected to the engine mounting panel.Torque-converters rotates freely with respect to drive shell in the drive shell chamber, forms compact and axial shorter motor/transmission assembly.By with disconnect-type clutch and the motor coaxial front portion that is placed in the wet district of automatic transmission, rotor and stationary part that transmission pressure fluid pump, relevant pump and pipe-line system can be come with the increase of less on axial length cooling separation type clutch and motor.
Although similar with traditional torque-converters generally, in order to implement the present invention, torque-converters has been carried out unique transformation.Because torque-converters is not attached to the engine mounting panel, so the installation double-screw bolt is not provided on the shell of torque-converters.And being to provide central shaft to bearing assembly, it cooperates radially to support torque-converters and also axially limits the movement of forward direction with the engine mounting panel that possesses corresponding bearing assembly.Be the back towards thrust bearing assembly in torque-converters, it cooperates to limit torque-converters and moves axially on direction backward with the free end of transmission input shaft.
In order to implement the present invention, gearbox case preferably also carries out unique transformation.Gearbox case comprise part definition sealing wet district wet shell and and converter housing, it transform a side as and is fixed on wet shell and opposite side is fixed on cluster engine.Converter housing has the rear wall that forms the border between wet chamber and drying chamber, and wherein torque-converters and drive shell are directed.Rear wall has defined looping pit, and it cooperate with disconnect-type clutch input hub, and together with the associated rotor part and disconnect-type clutch output hub of motor, hub and armature spindle are inputted in supporting.
Description of drawings
Fig. 1 is the schematic diagram with hybrid electric vehicle of Parallel power-flow design;
Fig. 2 is the disconnect-type clutch of reorientating in the present invention and the rough schematic view of motor;
Fig. 3 is the simplification viewgraph of cross-section of automatic electric motivation/transmission assembly of the present invention;
Fig. 4 a is the more detailed cross-sectional side elevation view of automatic electric motivation/transmission assembly of the present invention;
Fig. 4 b is the graphical diagram of motor/transmission assembly of Fig. 4 a;
Fig. 4 c is six forward gears and reverse gear shift clutch application table separately;
Fig. 5 is the zoomed-in view that is in the cross section of torque-converters during disconnect-type clutch and motor cooperate;
Fig. 6 is the zoomed-in view of disconnect-type clutch and motor;
Fig. 7 is engine output on the mounting panel torque-converters and the zoomed-in view of transmission input shaft, and it shows their axial direction;
Fig. 8 is be used to the perspective view of implementing mounting panel of the present invention;
Fig. 9 is be used to the perspective view of implementing torque-converters of the present invention;
Figure 10 is the perspective view of drive shell;
Figure 11 is the view with the optional embodiment of wrapping the drive shell that carries torque converter;
Figure 12 is the side cross-sectional views that is positioned at the above automotive power part in axis;
Figure 13 is the vertical view of terminal base assembly;
Figure 14 is the side cross-sectional views that is positioned at the following automotive power part in axis;
Figure 15 is the above side cross-sectional views in axis of automotive power, and it shows the torsional damper between engine and torque-converters.
Embodiment
Fig. 1 has illustrated hybrid electric vehicle 10, and it schematically represents with parallel connection type hybrid electric power train.Hybrid electric vehicle possesses the engine 12 of the rotation output with the disconnect-type clutch 14 that is connected to drive motor 16.The output of motor is connected to the input of torque-converters 18, and the output of torque-converters is connected to the power shaft of automatic transmission 20.In traditional approach, automatic transmission is connected to driving wheel 22,22 ' by differential mechanism 24.In the diagram, hybrid electric vehicle 10 possesses a pair of non-driving wheel, yet, alternatively, can utilize transfer gear and the second differential mechanism to come all wheels of actual driving vehicle.Engine, disconnect-type clutch, motor, torque-converters and automatic transmission sequentially are connected in series, as shown in fig. 1.
Motor/transmission assembly 26 in the hybrid electric vehicle 10 ' that schematically illustrates in Fig. 2 is ressembled drive disk assembly when keeping power stream identical to those shown in Fig. 1.Engine 12 is mechanically connected to input side above disconnect-type clutch 14 by the drive shell 28 that forms doughnut (it is large enough to extend around torque-converters 18).The output of disconnect-type clutch 14 is connected to motor 16, motor and then be connected to the impeller " I " of torque-converters 18.The use of drive shell 28 allows disconnect-type clutch and motor to be positioned at the wet side of automatic transmission shell.Turbine " T " is connected to the output of torque-converters 18, and torque-converters is connected to the power shaft of automatic transmission in a conventional manner.The present invention can implement with extensive various automatic transmission.The preferred embodiment of speed changer described here is the design of six kinds of gear speed, three planetary gearsets, five clutches; Have still less or the more optional speed changer structure of multiple speed and different mechanical realization can benefit from the present invention equally.
The more detailed of motor/transmission assembly 26 has been shown but simple explanation very in Fig. 3.Engine possesses the bent axle output flange 30 that is fixed by bolts in a conventional manner on mounting panel 32.Mounting panel 32 is fixed on diameter enough around torque-converters and be connected on the drive shell 28 of input hub (hub) 34 of disconnect-type clutch 14, rather than is connected to the shell of torque-converters.The output of disconnect-type clutch is fixed on rotor " R " part of motor 16, and and then is connected to armature spindle 36.Armature spindle 36 is coaxial to be nested in disconnect-type clutch input hub 34, and extends to the annular opening in the wall section of gearbox case of wet zone of definition speed changer.Armature spindle 36 is connected to the impeller " I " of torque-converters 18, and impeller and then driving are connected to the turbine T of transmission input shaft 38.It is coaxial between the periphery of the internal diameter of armature spindle 36 and transmission input shaft 38 that what separate is stator axis 40, its with respect to gearbox case be fix and supporting be positioned at the stator component S of torque-converters 18.
Preferably, the housing of motor/transmission assembly is by the wet shell 42 in the chamber, wet district of definition sealing partly, and is transformed into the converter housing 44 that is fixed on wet shell 42 and cluster engine 46 and forms.Converter housing 44 preferably possesses the rear wall 48 that has ring shaped axial opening 50 on the speed changer center line.Rear wall 48 in gearbox case chamber, wet district and drying chamber between form the physical boundary.Torque-converters 18 and drive shell 28 are positioned at dry section as shown in the figure.Rear wall 48 cooperates with disconnect-type clutch input hub 34, the rotor portion R of disconnect-type clutch input hub and then supporting motor armature spindle 36 and the motor 16 of being correlated with.
Motor/transmission assembly possesses for the pump P at the hydraulic fluid of the wet district of gearbox case interior orientation, and it is driven by armature spindle 36.Pump P provides the hydraulic fluid of pressurization to come clutch and the brake in the operation transmission power train and handles disconnect-type clutch and provide cooling for clutch and motor 16.Similarly, disconnect-type clutch and motor are shared shared sump 52 and the shared common pump filter screen 54 that is used for transmission fluid.Automatic transmission 20 possesses output shaft 56.Fig. 4 a is the cross-sectional side elevation view of motor/transmission assembly 26.Again emphasize, the present invention can use multiple different transmission gear trains configuration, and is not limited to disclosed six kinds of gear speed, three planetary gearsets speed changers.
With reference to the graphical diagram of figure 4b, the preferred embodiment of the multiple-speed gear-box shown in Fig. 4 a is more readily understood.Drive the mounting panel 32 on the drive shell 28 that is fixed on the input hub 34 that is connected to disconnect-type clutch 14 from the input of engine.The outlet side of disconnect-type clutch 14 is connected to the rotor portion of motor 16, this rotor portion and then be connected to armature spindle 36.Armature spindle 36 interior coaxial orientations be the fixing stator axis 40 that is mounted to case of transmission, and transmission input shaft 38.Torque converter impeller I drives the torque converter turbine T that is connected to transmission input shaft 38.Torque-converters 18 also possesses by one-way clutch 56 and is arranged on stator S on stator axis 40.In a preferred embodiment, torque-converters 18 also possesses the lock-up clutch 58 that in known manner turbine is locked to impeller.
The gear train of planetary automatic transmission 20 is comprised of three planetary stages: planet 1, planet 2 and planet 3, as shown in the figure, their arranged in co-axial alignment and axially-spaced.Each planetary gearsets has central gear, gear ring and is bearing in a series of planetary gears on planet carrier.Central gear, gear ring and planet carrier component can be by a series of five clutches and brake interconnection.For example, in the first gear, clutch A and brake D are as joint as described in Fig. 4 c clutch application table.Transmission input shaft 38 is connected to the gear ring of planetary gearsets planet 1.Central gear be fix and planet carrier be connected to the central gear of planetary gearsets 3 by clutch A.When clutch D engaged, the planet carrier of planetary gearsets 3 was fixed, and causes the gear ring drive speed transmission output shaft 56 of planetary gearsets 3.In order to be converted to the second gear, release brake D and while engage brake C are to cause the variation of speed changer gear ratio.No matter each conversion is upwards or downward, all by unclamping clutch or a brake and engaging another realization.Similarly, be by unclamping single clutch from the first conversion of reversing gear, engage simultaneously that another clutch completes.
Planetary gearsets 2 and 3 sharing of common planetary components and shared gear ring.Planetary gearsets 1 and 2 is tradition, simple planetary gearsets, and planetary gearsets 3 is the dual planetary gear groups with a pair of intermeshing planet, and this engages central gear, a soldered tooth torus to one in intermeshing planet.In the embodiment described in Fig. 4 b, compound planetary is arranged and is allowed the third planet gear train to use less central gear, thereby obtains higher gear reduction ratio.In addition, describe planetary gearsets and be only for preferred embodiment is described, yet the present invention can also implement with extensive various automatic transmission structure.
Fig. 5 is sectional view, and it is expressed as the less diameter mounting panel 64 of adaptation and the optional drive shell layout 62 of design.The output flange 30 of engine crankshaft passes being bolted on mounting panel 64 of in mounting panel one group hole that separates with the mounting panel center by a series of.The peripheral edge of mounting panel 64 possesses gear ring 66 to cooperate with the pinion of starting motor.In the car of the periphery of mounting panel, a side is that a series of sizes can be held the hole of threaded fastener so that drive shell 62 is connected to mounting panel 64.In an illustrated embodiment, drive shell 62 possesses stud 108, and its one group of hole passing in mounting panel 64 receives nut so that drive shell is securely fixed on mounting panel.Nut can be welded on the bolt that passes the hole in mounting panel on mounting panel with reception alternatively.In order to reduce torque ripple, mounting panel can also comprise double mass damper (not shown) alternatively.
Different from traditional vehicle with automatic transmission, torque-converters 18 is not fixed by bolts on the engine mounting panel, but rotates freely in the annular chamber by drive shell 62 and mounting panel 64 definition.The rear end of drive shell forms tubulose drive shell spout assembly 68, and this assembly is connected to disconnect-type clutch input hub 34." afterwards " refers to the direction towards transmission output shaft 56, and this direction can be the rear portion of vehicle in traditional rear wheel drive front-mounted engine vehicle, yet using term " afterwards " and " front " is for purpose simple and explanation.What they not necessarily meaned is the front and rear of vehicle, because if be that just laterally being arranged in f-w-d vehicle has been not this situation.The front side of torque-converters 18 typically is not used for being connected to the bolt of mounting panel.
Preferably, drive shell tubulose output hub 68 possess internal spline with disconnect-type clutch input hub 34 on the external splines of complementation axially cooperate.Disconnect-type clutch 14 has the plate of a series of spaces, and it is connected to input hub 34 and output hub 70 alternatively.Cooperate in the corresponding chamber that separate type nave collar shape piston 72 forms in disconnect-type clutch output hub 70, and it can axially conversion between the latched position of extending and advanced position, wherein, be in the latched position of extension when receiving the hydraulic pressure signal that advances disconnect-type clutch piston 72, be in advanced position when not having this signal.Be fixed in disconnect-type clutch output hub 70 periphery be rotor R.Disconnect-type clutch output hub 70 and rotor R all are mounted and fixed on armature spindle 36.Armature spindle 36 possesses the external splines of the size that cooperates with the internal spline of complementation on the torque-converters of drives impeller I input hub 74.Torque-converters 18 also possesses the stator S that is arranged on stator hub 76, and the output turbine T that is connected to turbine output hub 78 by the torsional damper 82 described in Fig. 5.Turbine output hub 78 possesses the internal spline that cooperates with transmission input shaft 38.Stator hub 76 is arranged on stator axis 40, and it is fixed on gearbox case and extends transmission case.In the embodiment shown, in a conventional manner stator is arranged on the one-way clutch center.
Torque-converters 18 and drive shell 62 together from speed changer in the assembly of four different arranged in co-axial alignment closely cooperate, and sliping off or closing as the traditional torque-converters in automatic transmission in installation process, has simply an extra coaxial module, i.e. the tubulose of drive shell 62 output 68.Therefore, use drive shell to occupy extra axial space very little in motor/transmission assembly.Yet, but occupy some extra axial spaces in gearbox case for speed changer increases disconnect-type clutch 14 and motor 16.As shown in Figure 6, motor and the coaxial orientation of disconnect-type clutch that is arranged in motor rotor R.Motor stator S is securely fixed on gearbox case by the bolt that a series of ring-types of passing stator lasmination separate.Motor rotor R is arranged on the periphery of the disconnect-type clutch output hub 70 that is bearing on armature spindle 36.
Disconnect-type clutch output hub 70 possesses the transmission fluid of making and flows into the interior coolant passage 92 of rotor R through disconnect-type clutch output hub.When fluid by and when leaving the rotor R of rotation, its coil that passes stator S is to remove waste heat from stator coil and relevant stator lasmination.As shown in Figure 6, disconnect-type clutch output hub 70 also possesses the output spline 94 for driving pump P.
Because torque-converters 18 no longer is fixed on the engine mounting panel, so must be axially and radially limit torque-converters.Torque-converters 18 is bearing on engine mounting panel 32 and 64 in Fig. 3 and 5 pivotally. Engine mounting panel 32,64 possesses the clutch shaft bearing assembly 96 of axial installation, and it cooperates with the second bearing assembly of matching on torque-converters 18.As shown in Figure 7, the clutch shaft bearing assembly in preferred embodiment is provided by the roller bearing 96 that is bearing in bearing outer ring 98 (it is fixed on mounting panel on the speed changer center line).Corresponding the second bearing assembly is provided by the minor axis 100 on the shell that is fixed on torque-converters 18.Minor axis provides radial support for torque-converters, and bearing 96 also provides axial retention for torque-converters on direction forward.Move backward in order to limit torque-converters, torque-converters possesses back-oriented thrust bearing 102 on the longitudinal center line of shell inside, with the end regions of joined speed variator power shaft 38.Certainly, can use optional structure, be placed on torque converter casing as minor axis is placed on mounting panel and with roller bearing.
Motor/transmission assembly 26 as mentioned before, has used a plurality of independent novel subassemblies.Fig. 8 is the perspective view of the mounting panel 64 that is made of disk, and this mounting panel possesses the clutch shaft bearing assembly of center axially-aligned, namely is arranged on the roller bearing 96 in bearing outer ring 98.Dish possesses the installing hole of two circular array, and an array is close to the center to be connected to the bent axle of engine, and the contiguous periphery of another array is to be connected to drive shell 28.
Torque-converters 18 described in Fig. 9 is novel equally.This converter housing does not possess the conventional mounting double-screw bolt, and possesses central shaft to the second bearing assembly, and it is provided by minor axis 100 in this case.Also can use alternatively other axial centre bearing assemblies, if they with mounting panel on corresponding bearing arrangement cooperate to bear radial load and definite stop forward of moving for torque-converters be provided.Torque-converters has towards the annular rear portion of the pipe-type outlet hub 68 that is connected to armature spindle 36, and the rear portion of the thrust bearing 102 on the center line in the shell as shown in Figure 7 is with the end near transmission input shaft 38.
Figure 10 has illustrated the perspective view of drive shell 28.Drive shell is to have greatly to the ring-shaped component of enough free rings around the peripheral structure of torque-converters.The leading edge of drive shell 28 possesses securing member 104 that a series of intervals separate to cooperate with mounting panel 32.The rear end of drive shell forms tubulose output 68, and it preferably has the internal diameter that has spline and inputs corresponding spline on hub 34 to engage disconnect-type clutch.The securing member 104 that described interval separates is a series of welding screws, yet welding screw can also be used for cooperating with the bolt that passes mounting panel corresponding hole.
Figure 11 has illustrated the optional drive shell embodiment 62 in Fig. 5 as previously described.For the mounting panel that holds small diameter and relatively large torque-converters, drive shell possesses a series of radial component of inwardly stretching out 106 with the supporting securing member.Shown in securing member provided by the double-screw bolt 108 of the diameter that is positioned at the array hole on mounting panel (it is significantly less than the diameter of torque-converters).Therefore, the assembly 106 that inwardly stretches out wraps in the larger annular chamber of drive shell 62 interior formation and carries torque-converters 18 to produce the sub-assembly of described drive shell torque-converters.
With reference to Figure 12, disconnect-type clutch 14 also comprises: barrier ring 110, and it is fixing not with respect to 70 axial displacements of output hub; Balance cuts off 112, and it is also fixing not with respect to 70 axial displacements of output hub; Return spring 114, its other end contact piston 72 and balance at spring cuts off 112; And the hydraulic cylinder 116 of sealing, wherein piston is limited by the power of spring 114 and pressure and moves.Hydraulic channel 118 passes through axial passages 123 with driving pressure from the outlet 120 of pump case 122 and is passed to the cylinder portion 116 that is positioned at piston 72 back.When the pressure in passage 118 was higher, the power of piston 72 antagonistic springs 114 axially was moved to the left, with friction plate and the mutual CONTACT WITH FRICTION of dividing plate of promotion clutch 14, thus engaging clutch 14.
Axial hydraulic passage 124 is passed to fluid in the cylinder portion 116 between piston 72 and balance partition 112 through passages 126 from pump case 122.Hydraulic channel 124 also is passed to from pump case 122 fluid rotor R and the stator S of motor 16 through radial passage 92.Passage 92 is communicated with passage 128, and its directing fluid passes the width of motor 16 and arrives on the surface of rotor R.Due to centrifugal force, the fluid that leaves rotor flows and arrives on the surface of stator S at opposite axial both sides outward radial.Heat is taken out of this fluid of motor 16, through the opening 129 (shown in Figure 14) in shell 42 to downstream to sump 52.
The hydraulic fluid of filling torque-converters 18 transmits through the axial passage 132 radial passage 130 and the annular space between stator axis 40 and transmission input shaft 38 from pump P.The front end of passage 132 is communicated with by radial passage 134 with the doughnut of torque-converters, wherein torque-converters by guard shield 136 around and comprise impeller I, turbine T and stator S.The hydraulic fluid that leaves torque-converters 18 transmits through the axial passage 138 that forms in transmission input shaft 38, and extends along axle 140.
As shown in figure 12, the stator S of motor is fixed to case of transmission 42 by a series of bolts 150, and it is comprised of opening 152.Each bolt 150 is passed in the hole that forms in stator S, and the thread handle of each bolt engages the screwed hole that is formed in housing 42.Accurate dimensional tolerance is at the lower surface 153 of stator S, by the hole in stator S and the center line of bolt 150, and determines between the position of axle 140.In this way, the distance between the lower surface 153 of axle 140 and stator S determines in the dimensional tolerance of precision, to determine and to keep the stator S of motor and the narrower air gap between rotor R.
The rotor R of motor 16 is fixed to output hub 70, in order to determine the air gap between the radially-outer surface 176 of the plane of reference 153 of stator and rotor.
Axially being determined with the contacting of rear wall 48 of shell 44 by it with radial position of bearing 84.Axially being determined with contacting of bearing 84 by it with radial position of clutch input hub 34.The position of the front end of armature spindle 36 is determined with contacting of roller bearing 80 by it, and the position of the rear end of armature spindle 36 is determined with the contacting of inner surface of pump case 122 by it.
The position of the front end of output hub 70 and rotor R is definite by contacting between the inner surface of the outer surface of armature spindle 36 and output hub 70.Axially being determined with contacting of pump case 122 by it with radial position of bearing 190.The position of the rear end of output hub 70 and rotor R is definite by contacting between bearing 190 and output hub 70.
In this way, the radial position of the radially-outer surface 176 of the rotor R of motor 16 is positioned such that air gap is parallel to the radius that extends and be preferably about 122mm from axle 140 between the radially-outer surface 176 of the plane of reference 153 of stator and rotor.
Figure 15 shows the torsional damper 196 in power path between engine 12 and drive shell 28,62.Engine 12 is connected to the input of damper 196 by bent axle flange 30, and around axle 140 a series of bolts 108 spaced apart from each other, the output of damper 196 is connected to drive shell 28,62.Damper 196 weakens the twisting vibration that is produced by engine.The peripheral edge of damper 196 possesses gear ring 66, and its pinion by the starting motor rotating drive engages.
Figure 15 show and engine 12 and transmission input shaft 38 between the damper 196 of damper 82 arranged in series.The existence of the damper 196 in dynamical system can be eliminated the needs to torsional damper 82, in the torque transmission paths of the torque-converters 18 of this torsional damper between impeller guard shield 136 and turbine hub 78.When eliminating damper 82, can reduce torque-converters 18 and drive shell 28,62 axial dimension.
As requested, the detailed embodiment of the present invention disclosed herein; Yet, should be appreciated that the disclosed embodiments are only examples of the present invention, these examples can with various and optionally mode realize.Accompanying drawing not necessarily proportionally; Some features may be exaggerated or dwindle to show the details of concrete parts.Therefore, concrete structure disclosed herein and functional details should not be considered as limitation of the present invention, and are only as representative basis in order to instruct those skilled in the art to use from many aspects the present invention.
Although exemplary embodiment above has been described, this does not also mean that these embodiment have illustrated all possible forms of the invention.Yet the statement that uses in specification is the statement of unrestricted explanation, and should be appreciated that and can make a variety of changes in the situation that do not deviate from content of the present invention and scope.In addition, can form the other embodiment of the present invention in conjunction with the feature of the embodiment of various execution.
Claims (5)
1. an assembly that is used for the motor of supporting automotive power, is characterized in that, comprises:
Shell;
Be fixed to the stator of shell;
Bearing with radial position of being determined by shell;
Contact the assembly of described bearing;
Be fixed to the rotor of described assembly, described rotor comprises by air gap and the radially spaced radially-outer surface of stator, and described air gap is determined by the contact between bearing and described assembly.
2. assembly as claimed in claim 1, is characterized in that, further comprises:
Has the first main body by the radial position of determining with housing contacts;
Have by contact definite radial position and the second main body of contact bearing with the first main body.
3. assembly as claimed in claim 1, is characterized in that, further comprises:
Have by with housing contacts determine axially and the second bearing of radial position;
Have by contact the second assembly of the axial and radial position of determining with the second bearing;
Thrust bearing between assembly and the second assembly is used for restrict rotor and assembly in the displacement of the first axial direction.
4. assembly as claimed in claim 1, is characterized in that, described bearing has the axial location of being determined by described shell, in order to limit described rotor and assembly in the displacement of the first axial direction, further comprises:
Have by with housing contacts determine axially and the second bearing of radial position;
Have by contact the second assembly of the axial and radial position of determining with the second bearing;
Thrust bearing between assembly and the second assembly is used for restrict rotor and assembly in the second axial direction displacement.
5. assembly as claimed in claim 1, is characterized in that, further comprises:
Has the first main body by the radial position of determining with housing contacts;
Contact bearing also has by contact the second main body of the radial position of determining with the first main body, and described bearing restrict rotor and assembly are in the displacement of the first radial direction.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US13/325,137 US9263924B2 (en) | 2011-10-11 | 2011-12-14 | Motor support for a hybrid electric transmission |
| US13/325,137 | 2011-12-14 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103166360A true CN103166360A (en) | 2013-06-19 |
| CN103166360B CN103166360B (en) | 2018-07-06 |
Family
ID=48522255
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210397708.6A Active CN103166360B (en) | 2011-12-14 | 2012-10-18 | For the support of motor of hybrid electric speed changer |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN103166360B (en) |
| DE (1) | DE102012219250A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111868403A (en) * | 2018-07-09 | 2020-10-30 | 舍弗勒技术股份两合公司 | Oil distribution in hybrid modules |
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| US5427196A (en) * | 1992-07-08 | 1995-06-27 | Kabushikikaisha Equos Research | Electric motor drive system |
| JP2000185566A (en) * | 1998-12-24 | 2000-07-04 | Toyota Motor Corp | Hybrid power plant |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111868403A (en) * | 2018-07-09 | 2020-10-30 | 舍弗勒技术股份两合公司 | Oil distribution in hybrid modules |
| CN111868403B (en) * | 2018-07-09 | 2023-10-31 | 舍弗勒技术股份两合公司 | Oil distribution in a hybrid module |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103166360B (en) | 2018-07-06 |
| DE102012219250A1 (en) | 2013-06-20 |
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