CN105307889A - Drive train for a hybrid vehicle - Google Patents

Drive train for a hybrid vehicle Download PDF

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Publication number
CN105307889A
CN105307889A CN201480025890.XA CN201480025890A CN105307889A CN 105307889 A CN105307889 A CN 105307889A CN 201480025890 A CN201480025890 A CN 201480025890A CN 105307889 A CN105307889 A CN 105307889A
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CN
China
Prior art keywords
shaft
driving device
attaching parts
torque
gear
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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
CN201480025890.XA
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Chinese (zh)
Inventor
D·格里勒伯格
S·里克特内格
A·雷恩巴赫
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AVL List GmbH
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AVL List GmbH
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Publication of CN105307889A publication Critical patent/CN105307889A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/727—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path
    • 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
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/543—Transmission for changing ratio the transmission being a continuously variable transmission
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
    • F16H2037/102—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts the input or output shaft of the transmission is connected or connectable to two or more differentials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Arrangement Of Transmissions (AREA)

Abstract

The invention relates to a drive train (1) for a hybrid vehicle, comprising an internal combustion engine (ICE), at least one electric machine (EM1, EM2), and a power-split transmission (4) having three connections (4a, 4b, 4c), wherein a first connection (4a) has a drive connection to at least one electric machine (EM2), a second connection (4b) has a drive connection to the internal combustion engine (ICE), and a third connection (4c) preferably formed by a summation shaft (s) has a drive connection to an output shaft (2) of the vehicle. Furthermore, a torque guiding module (5) formed by a two-course four-shaft transmission is connected to the first connection (4a).

Description

The transmission system of motor vehicle driven by mixed power
The present invention relates to the transmission system of motor vehicle driven by mixed power, it comprises combustion engine and at least one motor, comprise and there are three kinds of power division formula drivings device connected, wherein, first connection has being in transmission connection at least one motor, second connects and has being in transmission connection to combustion engine, and the 3rd connection be preferably made up of line shaft has being in transmission connection of output shaft to vehicle.
Elec. vehicle has the mileage shorter than the vehicle with combustion engine usually because of the relatively long charging duration of the gravimetric energy density low compared with fossil energy carrier of battery and battery.Have acceptable mileage in order to ensure under comparable overall vehicle weight, usual so-called distance increasing unit (rangeextender) is for having electrically-driven vehicle.In this case, combustion engine direct drive generator, extra energy is provided in battery by this electrical generator when needed.In these structuring concepts, mechanical horsepower bang path is not had to be arranged between combustion engine and drive wheel.This advantage had is that the optimum design of combustion engine can be made on little operation point and the optimum design of battery size can be made under low complex degree and low cost.Owing to not having power transimission between combustion engine and drive wheel, but this causes combustion engine-power transmittance path, and because of the frequent transitions between combustion engine-> electrical generator-> high-pressure system-> battery-> high-pressure system-> driving engine-> driving device, loss is high.Motor forms driving and must be designed for higher-wattage.
In power division formula hybrid power drives, some in the power provided by combustion engine are delivered to drive wheel by the round trip driving device direct mechanical for power division.In order to meet system static state require (balance of moment-hogging moment), must according to running condition to driving device provide power or from driving device remove power.This electrical motor by motor or generator operation realize.Therefore power division is realized by electric power bang path completely.
In order to combustion engine can be made to run at steady state in operation point, the power supply from power division must be mated with required driving power by the electrical motor of another motor or generator operation.In principle, therefore this can cause depending on the reactive power flows in the electric power bang path of running state and power requirement.
Possible reactive power flows is:
Motor 1-> high-pressure system-> battery-> high-pressure system-> electrical motor 2.
Electrical motor 2-> high-pressure system-> battery-> high-pressure system-> motor 1.
Therefore, can by the optimum design of the combustion engine of the advantage of the mechanical horsepower bang path of combustion engine and very little work point and lower vehicle mass combines due to smaller batteries.But shortcoming is that power division realizes completely electrically, consequently causes high loss by frequent transformation of energy.Electric power bang path possible reactive power flows cause comparatively low efficiency.In addition, due to the cause of system, the height obtained on controlling expends.
DE19909424A1 discloses the hybrid transmissions of the vehicle be made up of transmission shaft, output shaft, continuously adjusting gear device and mechanical laminating type power shift gear device.Laminating type wheel word is five axle planetary gear apparatuss of the adapter shaft had as wheel word output shaft.The intermeshing planetary wheel of the many groups of planetary gear carrier supporting.Planetary wheel and two gear rings and two sun gears engage each other.Two sun gears are interconnected by continuous electric adjusting gear device.First gear ring is connected to combustion engine securely.Second gear ring can be connected to gear case by drg.
EP1279545A2 discloses the hybrid powertrain of vehicle, and it has the planetary wheel of four elements and two degree of freedom, and planetary wheel comprises two sun gears, planetary gear carrier and at least one gear ring.Gear ring and planetary gear carrier are connected to the transmission shaft of combustion engine.Sun gear is connected respectively to each motor.
The object of the invention is to raise the efficiency and reduce control and expend.
According to the present invention, this is connected to the first connection to realize by the torque bootstrap module formed by round trip four shaft drive.
Power division round trip (degree of freedom=2) driving device is generally understood as the driving device with two kinematics degree of freedom: carry out unique certainty annuity kinematically by the rotating speed pre-determined on two axles.If the torque of adapter shaft is specified further, then system is also limited statically completely.Usually, for power transmission, driving device/sub-driving device must always have at least one adapter shaft, and just it does not have kinematics degree of freedom.Therefore, the simplest round trip driving device only has three adapter shafts.Epicyclic gear/planetary wheel forms the most simple designs of round trip three-axle gear.Draw from the condition of sum=0 of whole moment, the coupling torque of round trip driving device must be positive the bearing with part of part.In this case, always have two moments of band jack per line and a moment of band contrary sign, wherein, single moment corresponds to other two moment sums.The axle carrying single moment is called as line shaft, and other two axles are called as deviation shaft.
If the stationary gear of epicyclic gear is than being negative, then therefore this comprise so-called negative wheel word and therefore two center shafts are deviation shaft and adapter shaft (Stegwelle, spoke axle) is line shaft simultaneously.If on the other hand, the stationary gear of epicyclic gear is than being positive, then therefore we be commonly referred to spur gear means.A center shaft and adapter shaft are deviation shafts, and another center shaft is line shaft.
Preferably can specify, torque bootstrap module has four connections, first model calling has being in transmission connection to the first motor, second model calling has being in transmission connection to the second motor, and other model calling has to the first connection of power division formula driving device or being in transmission connection of the second connection.If torque bootstrap module comprises two round trip three-axle gears, then can obtain extra high efficiency and low control expends, wherein, the deviation shaft of two three-axle gears is coupled to each other, and wherein the line shaft of the first round trip three-axle gear forms the first model calling, and the line shaft of the second round trip three-axle gear forms the second model calling.
Two round trip three-axle gears have four round trip four shaft drives connected because dual connection is formed together, one of four connections form the line shaft of the first sub-driving device, another forms the line shaft of the second sub-driving device, and remains the deviation shaft system that two model calling form the connection of sub-driving device.
In this case, can specify, two deviation shafts of the first and second three-axle gears of torque bootstrap module are directly coupled to each other into positive deviation shaft system, and another two deviation shafts of the first and second three-axle gears are coupled to each other into minus tolerance axle system by reverse transmission.Therefore, between two sub-drivings device, positive deviation shaft system forms positive drive device, and minus tolerance axle system forms negative driving device.
First sub-driving device is used as open diff, and the drive torque of the first model calling is assigned to the model calling connected with deviation shaft system by this opening diff by a certain ratio.The torque being applied to the second connection provides the reallocation of the torque of each attaching parts connected with deviation shaft system.
In principle, torque distribution can be completed on transmission side or on the output side by torque bootstrap module.
In the first embodiment of the present invention, can specify, the deviation shaft of the deviation shaft system of torque bootstrap module have to first connect being in transmission connection, and another deviation shaft of another deviation shaft system has being in transmission connection of connecting to second of power division formula driving device.First of power division formula driving device is connected to the model calling being connected to positive deviation shaft system in this case or being connected to minus tolerance axle system.Second of power division formula driving device connects on the contrary or is connected to the minus tolerance axle system of torque bootstrap module or is connected to the positive deviation shaft system of torque bootstrap module.
In the second embodiment of the present invention, can specify, the deviation shaft of a deviation shaft system of torque bootstrap module have to second connect being in transmission connection, and the deviation shaft of another deviation shaft system has being in transmission connection of connecting to the 3rd of power division formula driving device.
The 3rd of power division formula driving device is connected to the direct deviation shaft system being connected to torque bootstrap module in this case or the reverse deviation shaft system being connected to torque bootstrap module.On the contrary, second of power division formula driving device connects or is connected to the reverse deviation shaft system of torque bootstrap module or is connected to the direct deviation shaft system of torque bootstrap module.
Therefore transmission system has two primary clusterings of band difference in functionality:
1) the power division round trip driving device (CVT-continuously variable transmission device) of CVT function
2) the torque bootstrap module (TVM=torque bootstrap module) that the dynamic power in system distributes
All advantages that the present invention not only causes the hybrid power with power division formula driving device to drive, the mechanical horsepower path of such as combustion engine, the optimum design of the combustion engine of very little work point and the vehicle mass low because of small size battery, and because the frequency of transformation of energy can be reduced, cause the lower loss due to mechanical horsepower branch and therefore relatively high efficiency.In addition, required control expends significantly lower.
Discuss the present invention in detail with reference to the accompanying drawings hereinafter.In accompanying drawing:
Fig. 1 show in the first embodiment according to transmission system of the present invention;
Fig. 2 shows the first modification of the embodiment from Fig. 1;
Fig. 3 shows the second modification of the embodiment from Fig. 1;
Fig. 4 show in the second embodiment according to transmission system of the present invention;
Fig. 5 shows the first modification of the embodiment from Fig. 4;
Fig. 6 shows the second modification of the embodiment from Fig. 4;
Fig. 7 show in the 3rd embodiment according to transmission system of the present invention;
Fig. 8 shows the first modification of the embodiment from Fig. 7;
Fig. 9 shows the second modification of the embodiment from Fig. 7;
Figure 10 show in the 4th embodiment according to transmission system of the present invention;
Figure 11 shows the first modification of the embodiment from Figure 10;
Figure 12 shows the second modification of the embodiment from Figure 10.
The parts in embodiment and modification with identical function are provided with same reference numerals.
Each figure respectively illustrates the transmission system 1 with the drive source formed by combustion engine ICE, the first motor EM1 and the second motor EM2, and wherein, at least one drive wheel 3 of vehicle is driven by output shaft 2.The power division formula driving device 4 with three attaching partss 4a, 4b, 4c is arranged in transmission system 1.First attaching parts 4a is connected to the first motor EM1 and the second motor EM2 by the torque bootstrap module 5 with four module connecting pieces 5a, 5b, 5c, 5d.Second attaching parts 4b is connected to the transmission shaft 6 of combustion engine ICE.
Power division formula driving device 4 is configured with the round trip driving device of two kinematics degree of freedom.This three-axle gear formed by epicyclic gear L or planetary wheel L always has about two identical axles of the torque sign of axle and an axle with contrary sign.Axle with jack per line is called as deviation shaft, and the axle of band contrary sign is called as line shaft.Only can transmit the axle connecting power and be called as adapter shaft.Can transmit not only connect power and also abandon power ( rolling power) axle be called as center shaft.Three-axle gear has the unique torque and rotational speed characteristic relevant with deviation shaft and line shaft.In order to describe three-axle gear from kinematics, employ so-called stationary gear ratio.Stationary gear is than the gear ratio be defined as when adapter shaft is in halted state between two center shafts.Stationary gear is more positive or negative than being, and this needs again the difference between so-called positive and negative gear.Negative gear refers to that wherein two center shafts form deviation shaft simultaneously and another adapter shaft is the three-axle gear of line shaft in this case.
Spur gear refers to that wherein one of adapter shaft and two center shafts form the three-axle gear that another center shaft of deviation shaft is then line shaft.
To engage each other with sun gear on the one hand and on the other hand with gear ring in an intermeshing only planetary single compound planet gear, for two center shafts of sun gear and gear ring are deviation shafts, adapter shaft is line shaft having.This compound planet gear has the kinematics characteristic of negative gear.
Have in one or more pairs of planetary compound planet gear, adapter shaft and the sun gear formation deviation shaft as the first center shaft, gear ring as the second center shaft is line shaft, in often pair of planetary wheel, first planet gear and sun gear and the second planetary wheel engage each other, and the second planetary wheel and gear ring and first planet gear engage each other.Therefore this compound planet gear has the kinematics characteristic of spur gear.In existing power division round trip driving device 4, such as, negative gear can be used.Unique certainty annuity is kinematically carried out by the rotating speed specifying in two axle places.If torque pre-determines further by attaching parts, then system is also limited statically completely.
In this case, the first attaching parts 4a of power division formula driving device 4 is become by deviation shaft D-shaped with the second attaching parts 4b, and the 3rd attaching parts 4c is formed by line shaft s.
Torque bootstrap module 5 is by two round trip three-axle gears (sub-driving device) T 1and T 2formed, two round trip three-axle gears form round trip four shaft drive with model calling 5a, 5b, 5c and 5d because of dual connection.Be connected to the first model calling 5a of the first motor EM1 by the first three-axle gear T 1line shaft S 1formed.Be connected to the second model calling 5b of motor EM2 by the second three-axle gear T 2line shaft S 2formed.First three-axle gear T 1deviation shaft d 1 +with the second three-axle gear T 2deviation shaft d 2 +be coupled to each other, to form positive deviation shaft system D +.First three-axle gear T 1deviation shaft d 1 -with the second three-axle gear T 2deviation shaft d 2 -connected by reverse transmission U, to form minus tolerance axle system D -.
First sub-driving device T 1be used as open diff, the drive torque of the first model calling 5a is assigned to module connecting piece 5c and 5d by a certain ratio by this opening diff.The torque being applied to the second module connecting piece 5d provides the reallocation of the Driving Torque of attaching parts 5c and 5d.
In principle, each figure can be divided into two groups.Fig. 1 to 6 inquires into the first group of embodiment and modification that have by the transmission side Torque distribution of torque bootstrap module 5.Fig. 7 to 12 illustrates the second group of embodiment and modification that have by the outgoing side Torque distribution of torque bootstrap module 5, and wherein, Fig. 1 illustrates the first main embodiment, and Fig. 4 illustrates the second main embodiment, and Fig. 7 illustrates the 3rd main embodiment and Figure 10 illustrates the 4th main embodiment.For each main embodiment, there is the sub-modification shown in Fig. 2 and Fig. 3, Fig. 5 and Fig. 6, Fig. 8 and Fig. 9 or Figure 11 and Figure 12.
The sign of the main embodiment shown in Fig. 1, Fig. 4, Fig. 7 and Figure 10 is made with so-called Wolf symbol, and wherein, for this reason, each epicyclic gear circle represents, and three attaching partss, three short-terms represent.Adapter shaft represents with the short-term stretching into circle and the two short-term of line shaft represents.
Reference numeral 7 represents pinion ratio or differential for vehicles.
In all embodiments, in torque bootstrap module 5, in all cases, the first three-axle gear T 1be embodied as spur gear, and the first three-axle gear T 2be embodied as negative gear.The respective difference of Fig. 2 and Fig. 3, Fig. 5 and Fig. 6, Fig. 8 and Fig. 9 and Figure 11 and Figure 12 is, center shaft is exchanged at power division formula driving device 4 place.In the modification of Fig. 2, Fig. 5, Fig. 8 and Figure 11, the sun gear L of the planetary wheel L of power division formula driving device 4 sbe connected to the transmission shaft 6 of combustion engine ICE.On the other hand, gear ring L hbe connected to the first three-axle gear T of torque bootstrap module 5 1pinion carrier T 1St.
In the modification of Fig. 3, Fig. 6, Fig. 9 and Figure 12, on the other hand, the transmission shaft 6 of combustion engine ICE is connected to the gear ring L of the planetary wheel L of power division formula driving device 4 h, sun gear L sbe connected to the first driving device T on the other hand 1pinion carrier T 1St.
In the modification shown in Fig. 2 and Fig. 3, the first driving device T 1sun gear T 1Swith the second driving device T 2sun gear T 2Sbe connected to the transmission shaft 6 of combustion engine ICE.First motor EM1 acts on gear ring T 1Hon.Second motor EM2 acts on the second three-axle gear T 2pinion carrier T 2Ston.Second three-axle gear T 2gear ring T 2Hwith the first three-axle gear T 1planetary gear carrier T 1Stbe coupled to each other by reverse transmission U.The planetary gear carrier T of driving device 4 stbe connected to output shaft 2.
Different from Fig. 2 and Fig. 3, in the exemplary embodiment of Fig. 5 and Fig. 6, center shaft that be not connected to the transmission shaft 6 of combustion engine ICE, that distribute driving device 4 is not only connected to the first three-axle gear T 1sun gear T 1Sand be connected to the second three-axle gear T 2sun gear T 2S.
There is-positive deviation shaft system the D that connects of-outgoing side of being connected to transmission system 1 relevant to power division formula driving device 4 +the example of Fig. 8 and Fig. 9 the layout being similar to Fig. 2 and Fig. 3 is shown, wherein, the center shaft not being connected to the power division formula driving device 4 of the transmission shaft 6 of combustion engine ICE is connected to the first three-axle gear T 1.In fig. 8, the center shaft of power division formula driving device 4 is connected to the first three-axle gear T 1planetary gear carrier T 1St.Compared with this, in fig .9, the sun gear L of the compound planet gear L of power division formula driving device 4 sbe connected to the first three-axle gear T 1planetary gear carrier T 1St.First three-axle gear T 1gear ring T 1Hbe connected to the first motor EM1.First three-axle gear T 1sun gear T 1Swith the first three-axle gear T 2sun gear T 2Sbe fixedly attached to output shaft 2.Planetary gear carrier T 1Stgear ring T is connected to by reverse level U 2H.Second motor EM2 acts on the second three-axle gear T 2planetary gear carrier T 2Ston.
Example shown in Figure 11 and Figure 12 shows the modification of the torque bootstrap module 5 connected with transmission system 1 on the outgoing side relevant to power division formula driving device 4, wherein, in fig. 11, and the sun gear 4 of the planetary set L of power division formula driving device 4 sconnect with the transmission shaft 6 of combustion engine ICE, and the gear ring L of planetary set L hhave to the first three-axle gear T 1sun gear T 1Swith the second three-axle gear T 2sun gear T 2Sbe in transmission connection.The planetary gear carrier L of power division formula driving device 4 sTbe connected to pinion carrier T 1St.First three-axle gear T 1this pinion carrier T 1Stby reverse gear U and the second three-axle gear T 2gear ring T 2Hconnect.First motor EM1 acts on the first three-axle gear T 1gear ring T 1Hon.Second motor EM2 is connected to the second three-axle gear T 2planetary gear carrier T 2St.The different of layout shown in Figure 12 and Figure 11 are only, the center shaft of power division formula driving device 4 is exchanged.In detail, the transmission shaft 6 of combustion engine ICE is connected to the gear ring L of the planetary set L of power division formula driving device 4 h, and the sun gear L of planetary set L sbe connected to the first three-axle gear T 1sun gear T 1Swith the second three-axle gear T 2sun gear T 2S.
Attaching parts 4a, 4b, 4c of power division formula driving device 4 and model calling 5a, 5b, 5c, 5d of torque bootstrap module 5 can comprise the virtual link point between driver element that the attaching parts of the physique of the adapter shaft such as between drive disk assembly or band be with or without isolation of components.Therefore the position connected only schematically shows in Fig. 2, Fig. 3, Fig. 5, Fig. 6, Fig. 8, Fig. 9, Figure 11 and Figure 12.

Claims (11)

1. the transmission system (1) of motor vehicle driven by mixed power, described transmission system comprises combustion engine (ICE) and at least one motor (EM1, EM2), and there are three attaching parts (4a, 4b, power division formula driving device (4) 4c), wherein, first attaching parts (4a) has being in transmission connection at least one motor (EM2), second attaching parts (4b) has being in transmission connection to described combustion engine (ICE), and the 3rd attaching parts (4c) be preferably made up of line shaft (s) has being in transmission connection of output shaft (2) to described vehicle, it is characterized in that, the torque bootstrap module (5) be made up of round trip four shaft drive is connected to described first attaching parts (4a).
2. transmission system (1) as claimed in claim 1, it is characterized in that, described torque bootstrap module (5) has four module connecting piece (5a, 5b, 5c, 5d), wherein, first module connecting piece (5a) has being in transmission connection to described first motor (EM1), second module connecting piece (5b) has being in transmission connection to described second motor (EM2), and other module connecting piece (5c, 5d) there is the described first or second attaching parts (4a to described power division formula driving device (4), being in transmission connection 4b).
3. transmission system (1) as claimed in claim 2, is characterized in that, described torque bootstrap module (5) comprises and has two deviation shaft (d respectively 1 -, d 1 +; d 2 -, d 2 +) and line shaft (S 1; S 2) two round trip three-axle gear (T 1, T 2), wherein, described two three-axle gear (T 1, T 2) described deviation shaft (d 1 -, d 1 +; d 2 -, d 2 +) be coupled to each other, and described first round trip three-axle gear (T 1) described line shaft (S 1) form described first module connecting piece (5a), and described second round trip three-axle gear (T 2) described line shaft (S 2) form described second module connecting piece (5b).
4. transmission system (1) as claimed in claim 3, is characterized in that, described first three-axle gear (T 1) be configured to positive drive device, and described second three-axle gear (T 2) be configured to negative driving device.
5. the transmission system (1) as described in claim 3 or 4, is characterized in that, the described first and second three-axle gear (T of described torque bootstrap module (5) 1, T 2) two deviation shaft (d 1 +, d 2 +) be directly coupled to each other into positive deviation shaft system (D +), and described first and second three-axle gear (T 1, T 2) another two deviation shaft (d 1 -, d 2 -) be coupled to each other into minus tolerance axle system (D by reverse transmission (U) -).
6. transmission system (1) as claimed in claim 5, is characterized in that, the deviation shaft system (D of described torque bootstrap module (5) +; D -) there is being in transmission connection to described first attaching parts (4a), and another deviation shaft system (D -; D +) there is being in transmission connection of described second attaching parts (4b) to described power division formula driving device (4).
7. transmission system (1) as claimed in claim 6, it is characterized in that, described first attaching parts (4a) of described power division formula driving device (4) is connected to described positive deviation shaft system (D +), and described second attaching parts (4b) of described power division formula driving device (4) is connected to the described minus tolerance axle system (D of described torque bootstrap module (5) -).
8. transmission system (1) as claimed in claim 6, it is characterized in that, described first attaching parts (4a) of described power division formula driving device (4) is connected to described minus tolerance axle system (D -), and described second attaching parts (4b) of described power division formula driving device (4) is connected to the described positive deviation shaft system (D of described torque bootstrap module (5) +).
9. the transmission system (1) as described in any one in claim 1 to 8, is characterized in that, the deviation shaft system (D of described torque oriented module (5) +; D -) there is being in transmission connection to described first attaching parts (4a), and another deviation shaft system (D of described torque oriented module (5) -; D +) there is being in transmission connection of described 3rd attaching parts (4c) to described power division formula driving device (4).
10. transmission system (1) as claimed in claim 9, it is characterized in that, described first attaching parts (4a) of described power division formula driving device (4) is connected to the described minus tolerance axle system (D of described torque bootstrap module (5) -), and described 3rd attaching parts (4c) of described power division formula driving device (4) is connected to the described positive deviation shaft system (D of described torque bootstrap module (5) +).
11. transmission systems (1) as claimed in claim 9, it is characterized in that, described first attaching parts (4a) of described power division formula driving device (4) is connected to the described positive deviation shaft system (D of described torque bootstrap module (5) +), and described 3rd attaching parts (4c) of described power division formula driving device (4) is connected to the described minus tolerance axle system (D of described torque bootstrap module (5) -).
CN201480025890.XA 2013-03-15 2014-03-12 Drive train for a hybrid vehicle Pending CN105307889A (en)

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ATA50176/2013A AT513986B1 (en) 2013-03-15 2013-03-15 Powertrain for a hybrid vehicle
PCT/EP2014/054833 WO2014140096A1 (en) 2013-03-15 2014-03-12 Drive train for a hybrid vehicle

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AT513986A4 (en) 2014-09-15
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AT513986B1 (en) 2014-09-15
JP2016511190A (en) 2016-04-14

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