CN108944411A - Hybrid module and vehicle - Google Patents

Hybrid module and vehicle Download PDF

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Publication number
CN108944411A
CN108944411A CN201810586822.0A CN201810586822A CN108944411A CN 108944411 A CN108944411 A CN 108944411A CN 201810586822 A CN201810586822 A CN 201810586822A CN 108944411 A CN108944411 A CN 108944411A
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CN
China
Prior art keywords
gear
motor
planetary gear
hybrid
power module
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201810586822.0A
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Chinese (zh)
Inventor
李至浩
陈振辉
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to CN201810586822.0A priority Critical patent/CN108944411A/en
Publication of CN108944411A publication Critical patent/CN108944411A/en
Pending legal-status Critical Current

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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
    • B60K6/36—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 transmission gearings
    • B60K6/365—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 transmission gearings with the gears having orbital motion
    • 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
    • B60K6/44—Series-parallel type
    • 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)
  • Electric Propulsion And Braking For Vehicles (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Arrangement Of Transmissions (AREA)

Abstract

The invention relates to a hybrid module and a vehicle, the hybrid module comprising a hybrid transmission, a first electric machine and a second electric machine, wherein the hybrid transmission comprises an input shaft connected to an internal combustion engine, a first planetary gear, a clutch device and an output shaft, wherein the input shaft is connected in a rotationally fixed manner to a planet carrier, a first motor shaft of the first electric machine is connected in a rotationally fixed manner to a sun gear, a ring gear is able to transmit power to the output shaft, and the second electric machine is able to output power to the output shaft via a second motor shaft, wherein a first end and a second end of the clutch device are connected in a rotationally fixed manner to the planet carrier and the ring gear, respectively, wherein the first planetary gear, the first electric machine and the second electric machine are arranged coaxially, the first electric machine and the second electric machine are located on a side of the first planetary gear remote from the internal combustion engine, wherein the second motor shaft is a hollow shaft, the first motor shaft passes coaxially through the second motor shaft. The vehicle according to the present invention has the above hybrid module.

Description

Hybrid power module and vehicle
Technical field
The present invention relates to a kind of hybrid power modules.The invention further relates to a kind of vehicles including above-mentioned hybrid power module ?.
Background technique
In a kind of current plug-in hybrid module, two motors are set and are connect with hybrid gearbox, and And internal combustion engine is connect by hydraulic clutch with hybrid gearbox, the hybrid power module can be realized a variety of as a result, Operating mode.But traction electric machine and internal combustion engine can only provide single gear, be not enough to optimize the work of motor or internal combustion engine Make a little.Hydraulic clutch is according to engagement the case where internal combustion engine or disconnects.Such as in road running, the efficiency of internal combustion engine is higher, Speed is higher, and hydraulic clutch engages at this time, torque output of combustion engine, and traction electric machine is only used as generator to run, cannot Output torque；And in the traveling of city, the efficiency of internal combustion engine is very low, and speed is relatively low, and hydraulic clutch disconnects, only by traction Motor output torque.Therefore, the low-speed performance of hybrid drive system, especially grade climbing performance are unsatisfactory.Further, since traction The tractive torque of motor is limited, so it is generally necessary to additional back wheel driving gear, therefore hybrid electric drive system cost is non- Chang Gao.In addition, there are two the hybrid power modules of motor to have biggish size for existing arrangement, this is in hybrid electric vehicle Flexible arrangement in is very unfavorable.
Summary of the invention
The technical problem to be solved by the invention is to provide a kind of hybrid power modules for vehicle, so that vehicle, special It is not that hybrid vehicle can take into account power performance and fuel economy in various driving conditions, meanwhile, hybrid power Module also has the size of reduction.
Above-mentioned technical problem is solved by a kind of hybrid power module for vehicle, which includes mixing Power transmission, first motor and the second motor, wherein the hybrid gearbox includes connecting with the internal combustion engine of vehicle Input shaft, first planetary gear mechanism, arrangement of clutch and output shaft, wherein first planetary gear mechanism includes sun gear, planet Frame and gear ring, wherein input shaft and the antitorque connection of planet carrier, the first motor axis of first motor and the antitorque connection of sun gear, tooth Circle can transfer power on output shaft, and the second motor can output power to output shaft by the second motor shaft On, wherein arrangement of clutch has the first end and second end that can be interconnected and disconnect, first end and second end respectively with institute State planet carrier and the antitorque connection of the gear ring.If engaging arrangement of clutch, the connection between planet carrier and gear ring is realized, so that row Carrier and gear ring are with identical rotational speed, according to the characteristic of planetary gear mechanism, also further such that sun gear, planet carrier and Gear ring is with identical rotational speed；If disconnecting arrangement of clutch, the planetary gear mechanism of hybrid gearbox is according to its own Working principle operation.Therefore, more gears be can be realized, meet the needs of each driving condition.
According to the present invention, first planetary gear mechanism, first motor and the second motor are coaxially arranged, wherein the One motor and the second motor are respectively positioned on the side of first planetary gear mechanism, separate internal combustion engine, wherein the second motor shaft is empty Mandrel, first motor axis coaxially pass through the second motor shaft.
In a preferred embodiment, hybrid gearbox further includes the spur gear of a pair of meshing, i.e. first gear And second gear, wherein the gear ring unitary design of first gear and first planetary gear mechanism, second gear and output shaft are anti- Connection is turned round so as to simplify assembling process while reducing the radial dimension of hybrid power module.
In other preferred embodiment, first motor is Integrated Starter generator, and the second motor is traction electric machine. In the present invention, Integrated Starter generator is mainly used for power generation, speed regulation and starts internal combustion engine, and traction electric machine is mainly used for Traction drive vehicle.
In other preferred embodiment, the hybrid gearbox further includes the second planetary gear mechanism, wherein Second planetary gear mechanism coaxially arranges with first planetary gear mechanism, the second motor shaft and the second planet of the second motor The planetary gear of the antitorque connection of the sun gear of gear mechanism, the second planetary gear mechanism is fixed on the shell of hybrid gearbox On, and the antitorque connection of gear ring of the gear ring of the first planetary gear mechanism and second planetary gear mechanism.Therefore, real Primary transmission between existing second motor and the gear ring of first planetary mechanism.In addition, also can be by the second planetary gear mechanism Planet carrier be fixed on the shell of hybrid gearbox so that the revolving speed of the planet carrier is always zero, to realize level-one Transmission.
Advantageously, the gear ring of the gear ring of first planetary gear mechanism and the second planetary gear mechanism is designed to integral type. As a result, also power can be transmitted between the second planetary gear mechanism and the output shaft of hybrid gearbox by gear mesh.Together When, the design of integral type can also simplify manufacture, especially reduction installation step.
Alternatively, hybrid gearbox further includes third gear and the 4th gear, wherein third gear is designed to have There is the ring gear of interior teeth portion and the 4th gear is engaged with the interior teeth portion of third gear, wherein third gear and the first planetary mechanism The antitorque connection of gear ring, the 4th gear and the antitorque connection of the second motor shaft.So as to which the torque of the second motor is transmitted to output On axis.Meanwhile the gear ring of third gear and the first planetary mechanism also can be integrally designed, to simplify assembly.
In addition alternatively, hybrid gearbox further includes the spur gear of a pair of meshing, i.e. the 5th gear and the 6th gear, Wherein, the antitorque connection of the second motor shaft of the 5th gear and the second motor, the 6th gear and the antitorque connection of output shaft.So as to incite somebody to action Simply and easily the torque of the second motor is transmitted on output shaft, and can obtain institute by the way that gear parameter is reasonably arranged The transmission ratio needed improves the electrically driven (operated) performance of vehicle.
In other preferred embodiment, arrangement of clutch is jaw clutch or synchronizer.Thus, it is possible to quick, reliable And cost-effectively realize the separated and engagement of planet carrier and gear ring.
In other preferred embodiment, arrangement of clutch also has and the antitorque connection of the shell of hybrid gearbox Third end, first end and third end can be interconnected and disconnect, wherein first end can alternatively with second end or third end Engagement.First end can also be disconnected with second end and third end.If engaging third end and the first end of arrangement of clutch, i.e., will The planet carrier of first planetary mechanism is connected with the shell of mixed dynamic power transmission, then rotate planet carrier can not, thus will even The input shaft for being connected to internal combustion engine locks, and under vehicle electric drive mode, is conducive to the output of electrical drive power.
According to the present invention, above-mentioned technical problem also passes through a kind of vehicle, especially hybrid vehicle and solves, the vehicle packet Include hybrid power module as characterized above.
As a result, in accordance with the invention it is possible to according to internal combustion engine, first motor, the second motor and arrangement of clutch different conditions Following functions are provided:
It is driven by the pure electric vehicle of traction electric machine
Engine starting under vehicle stop state
Internal combustion engine start in vehicle travel process
Combination drive with ECVT mode
The combination drive directly driven by internal combustion engine
Pure internal combustion engine driving
Recycling charging
Standard charging
Especially in the combination drive mode with ECVT mode, the efficiency of hybrid electric drive system can be optimized, The operating point of internal combustion engine can especially be optimized, therefore hybrid vehicle has good fuel economy, according to the present invention It vehicle start and runs at a low speed, the efficiency of power performance and drive system has promotion.When running at high speed, can use The mode that internal combustion engine directly drives, there is no need to lose additional power to adjust the operating point of internal combustion engine, therefore, hybrid power The system effectiveness and fuel economy of vehicle are optimized.
Detailed description of the invention
The present invention is schematically illustrated below by attached drawing.Attached drawing are as follows:
Fig. 1 is the schematic diagram of the hybrid power module of first preferred embodiment according to the present invention,
Fig. 2 is the power transmitting schematic diagram and planetary gear mechanism of the pure electric vehicle drive mode of the first preferred embodiment Equivalent lever figure,
Fig. 3 is the power transmitting schematic diagram and planetary gear machine of the first engine starting mode of the first preferred embodiment The equivalent lever figure of structure,
Fig. 4 is the power transmitting schematic diagram and planetary gear machine of the second engine starting mode of the first preferred embodiment The equivalent lever figure of structure,
Fig. 5 is the power transmitting schematic diagram and planetary gear mechanism of the first hybrid mode of the first preferred embodiment Equivalent lever figure,
Fig. 6 is the power transmitting schematic diagram of the second hybrid mode of the first preferred embodiment,
Fig. 7 is the power transmitting schematic diagram of the third hybrid mode of the first preferred embodiment,
Fig. 8 is the power transmitting schematic diagram of the pure internal combustion engine drive mode of the first preferred embodiment,
Fig. 9 be the first preferred embodiment recycling charge mode power transmitting schematic diagram and planetary gear mechanism etc. Lever diagram is imitated,
Figure 10 is the power transmitting schematic diagram and planetary gear mechanism of the standard charging mode of the first preferred embodiment Equivalent lever figure,
Figure 11 is the first deformation scheme according to the first preferred embodiment,
Figure 12 is the second deformation scheme according to the first preferred embodiment,
Figure 13 is the third deformation scheme according to the first preferred embodiment,
Figure 14 is the 4th deformation scheme according to the first preferred embodiment,
Figure 15 is the schematic diagram of the hybrid power module of the second preferred embodiment according to the present invention, and
Figure 16 is the schematic diagram of the hybrid power module of third preferred embodiment according to the present invention.
In the accompanying drawings, the identical component of identical or function uses identical appended drawing reference.Planetary gear mechanism etc. It imitates in lever diagram, noutputIt is the revolving speed of gear ring, nISGIt is the revolving speed of Integrated Starter generator, nTMIt is the revolving speed of traction electric machine, nICEIt is the revolving speed for the input shaft being connect with internal combustion engine.
Specific embodiment
Fig. 1 shows the hybrid power module of the first preferred embodiment according to the present invention.The hybrid power module includes Hybrid gearbox and two independent motors are designed to the first motor 4 of Integrated Starter generator and are designed For the second motor 11 of traction electric machine.In the preferred embodiment, hybrid gearbox is defeated with connecting with internal combustion engine 1 The planetary gear mechanism for entering axis 3, output shaft 14, arrangement of clutch 6 and two sets coaxially and being disposed adjacently, i.e. first planetary gear Mechanism and the second planetary gear mechanism, wherein first planetary gear mechanism includes planet carrier 9, sun gear 7 and gear ring 8, the second row Star gear mechanism includes planet carrier 18, sun gear 19 and gear ring 17.Input shaft 3, the Integrated Starter hair of hybrid gearbox Motor 4, traction electric machine 11 and two sets of planetary gear mechanisms are coaxially arranged, and opposite two sets of planetary gear mechanisms, collection Accepted way of doing sth starter-generator 4 and traction electric machine 11 are disposed in the side far from internal combustion engine 1, wherein traction electric machine 11 is along axial direction It is disposed between two sets of planetary gear mechanisms and integrated form starter-generator 4.Arrangement in this way can reduce mixed The height along transmission input shaft radial direction of power plant module is closed, and is conducive to uniformly seal two motors, simplification is close Envelope design.
As shown in Figure 1, first planetary gear mechanism is disposed in 1 side of internal combustion engine.In first planetary gear mechanism, row Carrier 9 is connect advantageous by double mass flywheel 2 with internal combustion engine 1 by input shaft 3.Sun gear 7 passes through first motor axis 5 (i.e. Integrated Starter generator shaft) it is connected with the rotor of Integrated Starter generator 4, especially Integrated Starter generator 4.First Gear 13 is designed to the external tooth on gear ring 8, and second gear 12 is disposed on the output shaft 14 of hybrid gearbox, and First gear 13 is engaged with the second tooth 12 wheel.Thereby, it is possible to by meshed gears to 13,12 first planetary gear mechanism with Power is transmitted between the output shaft 14 of hybrid gearbox.Planet carrier 9 and gear ring 8 respectively with the first end of arrangement of clutch 6 and The mutually antitorque connection of second end, therefore when engaging arrangement of clutch 6, planet carrier 9 and gear ring 8 connect, and turn thus, it is possible to synchronous It is dynamic.
Second planetary gear mechanism is disposed in close to 11 side of traction electric machine.In the second planetary gear mechanism, the sun Wheel 19 is connect by the second motor shaft 10 (i.e. traction electric machine axis) with traction electric machine 11.Second motor shaft 10 is designed as hollow Axis, first motor axis 5 coaxially pass through the second motor shaft 10.It is achieved in two sets of planetary gear mechanisms, Integrated Starter power generation The compact radial arrangement of machine 4 and traction electric machine 11.Planet carrier 18 is fixed on the shell of hybrid gearbox.Second row The gear ring 17 of star gear mechanism is integrally designed with the gear ring 8 of first planetary gear mechanism, can also pass through gear mesh as a result, 13,12 transmit power between the second planetary gear mechanism and hybrid gearbox output shaft 14.In addition, hybrid power speed change The output shaft 14 of device can further transfer power to wheel by differential mechanism.
It, can be according to internal combustion engine 1, Integrated Starter generator by the hybrid power module according to this preferred embodiment 4, the different conditions of traction electric machine 11, arrangement of clutch 6 provide following operating mode:
1) pure electric vehicle drive mode, i.e., the mode only driven by traction electric machine 11.As the power above Fig. 2 transmits signal Shown in figure, internal combustion engine 1 and integrated form starter-generator 4 do not work, and arrangement of clutch 6 disconnects, and traction electric machine 11 is as unique Power source drive vehicle.The torque of traction electric machine 11 from traction electric machine axis 10 by the second planetary gear mechanism sun gear 19, Planet carrier 18, gear ring 17 and gear mesh 13,12 transmit output shaft 14, to drive vehicle wheel rotation.Such as the first planet among Fig. 2 Shown in the equivalent lever figure of gear mechanism, the revolving speed for the input shaft connecting with internal combustion engine 1 is 0, i.e. nICE=0, Integrated Starter hair The revolving speed of motor 4 is nISG=-ρ1*noutput, wherein ρ1It is the biography between the gear ring 8 of first planetary gear mechanism and sun gear 7 Dynamic ratio.As shown in the equivalent lever figure of the second planetary gear mechanism below Fig. 2, planet carrier 18 is fixed on shell, therefore nTM=-ρ2*noutput, wherein ρ2It is the transmission ratio between the gear ring 17 of the second planetary gear mechanism and sun gear 19.To sum up Out, nISG=ρ1*nTM/ρ2。
2) the first engine starting mode, wherein the starting of internal combustion engine carries out under vehicle stop state.As above Fig. 3 Power transmitting schematic diagram shown in, traction electric machine 11 does not work, and arrangement of clutch 6 disconnects, the torque of Integrated Starter generator 4 according to It is secondary to be transmitted to input by hollow Integrated Starter generator shaft 5, the sun gear 7 of first planetary gear mechanism and planet carrier 9 Thus axis 3 starts internal combustion engine 1 in the state that vehicle stops.As shown in the equivalent lever figure below Fig. 3, the revolving speed of gear ring 8 is 0, i.e. noutput=0, Integrated Starter generator 4 drives internal combustion engine 1, nISG=(1+ ρ1)*nICE, wherein ρ1It is the first planet tooth Take turns the transmission ratio between the gear ring 8 and sun gear 7 of mechanism.
3) the second engine starting mode, wherein engine starting carries out in vehicle travel process.Above Fig. 4 Power transmits shown in schematic diagram, and arrangement of clutch 6 disconnects, and traction electric machine 11 and integrated form starter-generator 4 work, traction electric machine 11 Torque from traction electric machine axis 10 by the second planetary gear mechanism sun gear 19, planet carrier 18, gear ring 17 and gear mesh 13, 12 are transmitted to transmission output shaft 14, so that vehicle wheel rotation is driven, meanwhile, the torque of Integrated Starter generator 4 successively passes through The sun gear 7 and planet carrier 9 of hollow Integrated Starter generator shaft 5, first planetary gear mechanism are transmitted to input shaft 3, by This starts internal combustion engine 1 in vehicle travel process.As shown in the equivalent lever figure below Fig. 4, gear ring 8 is with noutputRevolving speed turn Dynamic, Integrated Starter generator 4 drives internal combustion engine 1 to rotate, nICE=1/ (1+ ρ1)*nISG+noutput, wherein ρ1It is the first planet Transmission ratio between the gear ring 8 and sun gear 7 of gear mechanism.
4) the first combination drive mode, wherein the drive mode has the function of ECVT, and Integrated Starter generator 4 It works as generator.If shown in the power transmitting schematic diagram above Fig. 5, arrangement of clutch 6 is disconnected, the torque of traction electric machine 11 from Traction electric machine axis 10 is transmitted to by sun gear 19, planet carrier 18, gear ring 17 and the gear mesh 13,12 of the second planetary gear mechanism Output shaft 14, and the torque of internal combustion engine 1 successively passes through the planet carrier of double mass flywheel 2, first planetary gear mechanism from input shaft 3 9, gear ring 8 and gear mesh 13,12 are transmitted to the output shaft 14 of speed changer, so that vehicle wheel rotation is driven jointly, Integrated Starter hair Motor 4 is used as generator, and internal combustion engine 1 is successively passed through input shaft 3, planet carrier 9, sun gear 7 and integrated form starter-generator axis 5 It passs the mechanical energy (torque) come and is converted to electric energy, be stored in battery.As shown in the equivalent lever figure below Fig. 5,8 He of gear ring Internal combustion engine 1 is respectively with noutputAnd nICERotational speed, Integrated Starter generator 4 invert, nISG=-(1+ ρ1)(noutput- nICE), wherein ρ1It is the transmission ratio between the gear ring 8 of first planetary gear mechanism and sun gear 7.
5) the second combination drive mode, wherein the combination drive directly driven by internal combustion engine, and Integrated Starter is sent out Motor 4 works as generator.As shown in fig. 6, arrangement of clutch 6 engages, the torque of internal combustion engine 1 is from input shaft 3 successively by double Mass flywheel 2, the gear ring 8 of first planetary gear mechanism and gear mesh 13,12 are transmitted to the output shaft 14 of speed changer, to drive Vehicle wheel rotation, meanwhile, vehicle driving does not need the whole power generated by internal combustion engine 1, and Integrated Starter generator 4 is as power generation Machine comes planet carrier 9, sun gear 7 and the transmitting of integrated form starter-generator axis 5 through input shaft 3, first planetary gear mechanism The extra kinetic energy of internal combustion engine 1 is converted to electric energy, is stored in battery, thus charges.It is this to connect internal combustion engine 1 with gear ring 8 And directly to the mode of 14 output power of the output shaft of speed changer, help to reduce system power during highway driving Loss.
6) third combination drive mode, wherein the combination drive directly driven by internal combustion engine, and Integrated Starter is sent out Motor 4 works as traction electric machine.As shown in fig. 7, arrangement of clutch 6 engages, the torque of internal combustion engine 1 successively passes through from input shaft 3 Double mass flywheel 2, the gear ring 8 of first planetary gear mechanism and gear mesh 13,12 are transmitted to the output shaft 14 of speed changer, meanwhile, Integrated Starter generator 4 be used as traction electric machine, output torque from Integrated Starter generator shaft 5 successively by sun gear 7, The output shaft 14 of planet carrier 9, gear ring 8 and gear mesh 13,12 equally transmitting speed changer, in addition, the also output torque of traction electric machine 11, It is attached on output shaft 14 by the second planetary gear mechanism and gear mesh 13,12, to jointly drive vehicle wheel rotation.In this way Internal combustion engine 1 is connect and directly to 14 output power of the output shaft of speed changer with gear ring 8, is facilitated especially in highway row System power loss is reduced during sailing.
7) pure internal combustion engine drive mode, as shown in figure 8, Integrated Starter generator 4 and traction electric machine 11 do not work, clutch Device 6 engages, and internal combustion engine 1 is unique power resources, and torque successively passes through double mass flywheel 2,8 and of gear ring from input shaft 3 Gear 13,12 is transmitted to the output shaft 14 of speed changer, thus with motor car wheel.Under pure internal combustion engine drive mode, especially in vehicle During road running of the speed greater than 80km/h, since arrangement of clutch 6 engages, noutput=nICE=nISG=-nTM/ρ1, wherein ρ1 It is the transmission ratio between the gear ring 8 of first planetary gear mechanism and sun gear 7.
8) charge mode is recycled, as shown in the power transmitting schematic diagram above Fig. 9, internal combustion engine 1 and integrated form starting-generating Machine 4 does not work, and arrangement of clutch 6 disconnects, and traction electric machine 11 passes through 12,13 and the second planet of gear mesh with generator mode recycling The brake power of the wheel of gear mechanism transmitting, is changed into electric energy for mechanical energy.As shown in the equivalent lever figure below Fig. 9, During recycling charging, the revolving speed for the input shaft connecting with internal combustion engine 1 is 0, i.e. nICE=0, the revolving speed of Integrated Starter generator 4 nISG=-ρ1*noutput, therefore, nISG=ρ1*nTM/ρ2Wherein, ρ1It is between the gear ring 8 of first planetary gear mechanism and sun gear 7 Transmission ratio, ρ2It is the transmission ratio between the gear ring 17 of the second planetary gear mechanism and sun gear 19.
9) standard charging mode, as shown in the power transmitting schematic diagram above Figure 10, traction electric machine 11 does not work, integrated form Starter-generator 4 is used as generator, by the kinetic energy of the internal combustion engine 1 successively come from input shaft 3 through planet carrier 9 and the transmitting of sun gear 7 Electric energy is converted to, is stored in battery, thus standard charging.As shown in the equivalent lever figure below Figure 10, in standard charging Period, traction electric machine revolving speed are 0, i.e. noutput=0, internal combustion engine 1 drives Integrated Starter generator 4 to rotate, and rotation speed relation is logical Cross nISG=(1+ ρ1)*nICEIt indicates, wherein ρ1It is the transmission ratio between the gear ring 8 of first planetary gear mechanism and sun gear 7.
In addition, in order to save cost, additionally it is possible to by above-mentioned arrangement of clutch 6 replace with jaw clutch or synchronizer etc. its Its arrangement of clutch.
Figure 11 and Fig. 2 respectively illustrates two kinds of deformation schemes of the hybrid power module according to the first preferred embodiment. The first deformation scheme is shown in FIG. 11, wherein the arrangement of clutch of hybrid gearbox is jaw clutch 6, in Figure 12 Second deformation scheme is shown, wherein the arrangement of clutch of hybrid gearbox is synchronizer 6.The row of first planetary gear mechanism Carrier 9 and gear ring 8 can be rapidly and reliably connected with each other by jaw clutch 6 or synchronizer 6 or mutually be disconnected, thus When engaging jaw clutch 6 or synchronizer 6, noutput=nICE=nISG=-nTM/ρ1, wherein ρ1It is first planetary gear machine Transmission ratio between the gear ring 8 and sun gear 7 of structure.
Figure 13 and Figure 14 respectively illustrates other two kinds of deformations of the hybrid power module according to the first preferred embodiment Scheme.Third deformation scheme in figure 13 illustrates, wherein on the basis of the first deformation scheme, jaw clutch 6 can also be incited somebody to action Planet carrier 9 is connected with the shell of hybrid gearbox, or planet carrier 9 and gear ring 8 are connected.The 4th change is shown in FIG. 14 Shape scheme, wherein on the basis of the second deformation scheme, synchronizer 6 can also be by the shell of planet carrier 9 and hybrid gearbox Body connection, or planet carrier 9 and gear ring 8 are connected.When planet carrier 9 is connected with shell, i.e., jaw clutch or synchronizer are illustrated Property connect such as a figure left side, then rotate planet carrier 9 can not, thus lock the input shaft 3 for connecting internal combustion engine 1, therefore, work as traction When motor 11 and integrated form starter-generator 4 are in traction mode, vehicle can be driven jointly, improve the electric drive of vehicle Energy.When planet carrier 9 and gear ring 8 connect, i.e., schematically such as figure right side connects for jaw clutch or synchronizer, then gear ring 8, planet carrier 9 It is rotated synchronously with sun gear 7, noutput=nICE=nISG=-nTM/ρ1, wherein ρ1It is 8 He of gear ring of first planetary gear mechanism Transmission ratio between sun gear 7.
Figure 15 shows the schematic diagram of the hybrid power module of the second preferred embodiment according to the present invention.Wherein, exist And the first row the second above-mentioned planetary gear mechanism is saved in hybrid gearbox, replaces with the gear of a pair of meshing, i.e., The 4th gear that the gear ring 8 of star mechanism designs the third gear 20 for the ring gear form being integrated and is arranged on traction electric machine axis 10 21, wherein the 4th gear 21 is engaged with the interior teeth portion of third gear 20.Therefore, motor drive vehicle is used as in traction electric machine 11 When, the torque that traction electric machine 11 exports is transmitted on the output shaft 14 of speed changer through gear mesh 21,20, and can further be passed through Differential mechanism is transmitted to wheel.In addition, traction electric machine 11 passes through gear mesh with generator mode recycling in the case where recycling charge mode The brake power of the wheel of 20,21 transmitting, is changed into electric energy for mechanical energy.
Figure 16 shows the schematic diagram of the hybrid power module of third preferred embodiment according to the present invention.Wherein, exist The second planetary gear mechanism in the first preferred embodiment is saved in hybrid gearbox, is replacing with a pair of meshing just Gear, that is, the 5th be arranged on traction electric machine axis 10 gears 16 and the 6th gear that is arranged on the output shaft 14 of speed changer 15.Therefore, when traction electric machine 11 is as motor drive vehicle, the torque that traction electric machine 11 exports is passed through gear mesh 16,15 It is delivered on the output shaft 14 of speed changer, and wheel further can be transmitted to by differential mechanism.In addition, in the case where recycling charge mode, The brake power for the wheel that traction electric machine 11 is transmitted with generator mode recycling by gear mesh 15,16, mechanical energy is changed into Electric energy.
Although being illustratively described possible embodiment in the above description, it should be appreciated that arrive, still through institute With the presence of the variation of technical characteristic known and that furthermore technical staff is readily apparent that and a large amount of embodiments of combination of embodiment. Furthermore it should also be understood that illustrative embodiment is as just an example, this embodiment never limits in any form Protection scope of the present invention, application and construction processed.It is more that one kind is provided to technical staff for converting by preceding description The technological guidance of at least one illustrative embodiments, wherein, can be into without departing from the protection scope of claims Row various changes, especially with respect to the component function and structure in terms of change.
Reference signs list
1 internal combustion engine
2 double mass flywheels
3 input shafts
4 first motors, Integrated Starter generator
5 first motor axis, Integrated Starter generator shaft
6 arrangement of clutch
7 sun gears
8 gear rings
9 planet carriers
10 second motor shafts, traction electric machine axis
11 second motors, traction electric machine
12 second gears
13 first gears
14 output shafts
15 the 6th gears
16 the 5th gears
17 gear rings
18 planet carriers
19 sun gears
20 third gears
21 the 4th gears

Claims (10)

1. a kind of hybrid power module for vehicle, the hybrid power module include hybrid gearbox, first motor (4) and the second motor (11), wherein the hybrid gearbox includes the input connecting with the internal combustion engine of the vehicle (1) Axis (3), first planetary gear mechanism, arrangement of clutch (6) and output shaft (14), wherein the first planetary gear mechanism includes Sun gear (7), planet carrier (9) and gear ring (8), wherein the input shaft (3) and the planet carrier (9) antitorque connection, described the The first motor axis (5) of one motor (4) and the sun gear (7) antitorque connection, the gear ring (8) can transfer power to institute It states on output shaft (14), and second motor (11) can output power to the output by the second motor shaft (10) On axis (14), wherein the arrangement of clutch (6) has the first end and second end that can be interconnected and disconnect, and described first End and second end respectively with the planet carrier (9) and the gear ring (8) antitorque connection,
It is characterized in that, the first planetary gear mechanism, the first motor (4) and second motor (11) are by coaxial line Ground arrangement, wherein the first motor (4) and second motor (11) be respectively positioned on the first planetary gear mechanism, far Side from the internal combustion engine (1), wherein second motor shaft (10) is hollow shaft, first motor axis (5) coaxial line Ground passes through second motor shaft (10).
2. hybrid power module according to claim 1, which is characterized in that the hybrid gearbox further includes a pair The spur gear of engagement, i.e. first gear (13) and second gear (12), wherein the first gear (13) and the gear ring (8) Unitary design, the second gear (12) and the output shaft (14) antitorque connection.
3. hybrid power module according to claim 1, which is characterized in that the first motor (4) is Integrated Starter Generator, second motor (11) is traction electric machine.
4. hybrid power module according to claim 1, which is characterized in that the hybrid gearbox further includes second Planetary gear mechanism, wherein second planetary gear mechanism is coaxially arranged with the first planetary gear mechanism, described Sun gear (19) antitorque connection of the second motor shaft (10) of second motor (11) and second planetary gear mechanism, described the The planetary gear of two planetary gear mechanisms is fixed on the shell of the hybrid gearbox, and first planet Gear ring (9) antitorque connection of the gear ring (8) and second planetary gear mechanism of gear mechanism.
5. hybrid power module according to claim 4, which is characterized in that the gear ring of the first planetary gear mechanism (8) integral type is designed as with the gear ring (9) of second planetary gear mechanism.
6. hybrid power module according to claim 1, which is characterized in that the hybrid gearbox further includes third Gear (20) and the 4th gear (21), wherein the third gear (20) is configured to have the ring gear of interior teeth portion and described 4th gear (21) is engaged with the interior teeth portion of the third gear, wherein the third gear (20) and the gear ring (8) are antitorque Connection, the 4th gear and the antitorque connection of second motor shaft (10).
7. hybrid power module according to claim 1, which is characterized in that the hybrid gearbox further includes a pair The spur gear of engagement, i.e. the 5th gear (16) and the 6th gear (15), wherein the 5th gear (16) and second motor (11) the second motor shaft (10) antitorque connection, the 6th gear (15) and the output shaft (14) antitorque connection.
8. hybrid power module according to claim 1, which is characterized in that the arrangement of clutch (6) is jaw clutch Or synchronizer.
9. hybrid power module according to claim 1, which is characterized in that the arrangement of clutch (6) also have with it is described The third end of the antitorque connection of the shell of hybrid gearbox, the first end and the third end can be interconnected and break It opens, the first end can be engaged alternatively with the second end or the third end.
10. a kind of vehicle, the vehicle has hybrid power module according to any one of the preceding claims.
CN201810586822.0A 2018-06-08 2018-06-08 Hybrid module and vehicle Pending CN108944411A (en)

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109484155A (en) * 2018-12-17 2019-03-19 北京航空航天大学 Double electric machine double row planetary gear multi-mode electromechanical coupling transmission device
CN110962580A (en) * 2019-11-21 2020-04-07 北京航空航天大学 Electromechanical coupling transmission device and system and hybrid electric vehicle
CN112440716A (en) * 2019-08-30 2021-03-05 比亚迪股份有限公司 Hybrid power device and vehicle
CN113085535A (en) * 2021-04-12 2021-07-09 浙江吉利控股集团有限公司 DMT double-motor hybrid transmission
CN113459797A (en) * 2021-07-21 2021-10-01 义乌吉利自动变速器有限公司 Multi-speed-ratio hybrid transmission and vehicle with same
US20220072947A1 (en) * 2019-12-20 2022-03-10 Allison Transmission, Inc. Component alignment for a multiple motor mixed-speed continuous power transmission
US11840134B2 (en) 2019-12-20 2023-12-12 Allison Transmission, Inc. Motor configurations for multiple motor mixed-speed continuous power transmission

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109484155A (en) * 2018-12-17 2019-03-19 北京航空航天大学 Double electric machine double row planetary gear multi-mode electromechanical coupling transmission device
CN109484155B (en) * 2018-12-17 2023-09-05 北京航空航天大学 Double-motor double-planet-row multi-mode electromechanical coupling transmission device
CN112440716A (en) * 2019-08-30 2021-03-05 比亚迪股份有限公司 Hybrid power device and vehicle
CN112440716B (en) * 2019-08-30 2022-05-13 比亚迪股份有限公司 Hybrid power device and vehicle
CN110962580A (en) * 2019-11-21 2020-04-07 北京航空航天大学 Electromechanical coupling transmission device and system and hybrid electric vehicle
CN110962580B (en) * 2019-11-21 2022-01-25 北京航空航天大学 Electromechanical coupling transmission device and system and hybrid electric vehicle
US20220072947A1 (en) * 2019-12-20 2022-03-10 Allison Transmission, Inc. Component alignment for a multiple motor mixed-speed continuous power transmission
US11787281B2 (en) * 2019-12-20 2023-10-17 Allison Transmission, Inc. Component alignment for a multiple motor mixed-speed continuous power transmission
US11840134B2 (en) 2019-12-20 2023-12-12 Allison Transmission, Inc. Motor configurations for multiple motor mixed-speed continuous power transmission
CN113085535A (en) * 2021-04-12 2021-07-09 浙江吉利控股集团有限公司 DMT double-motor hybrid transmission
CN113459797A (en) * 2021-07-21 2021-10-01 义乌吉利自动变速器有限公司 Multi-speed-ratio hybrid transmission and vehicle with same

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