CN101898509B - In-vehicle power transmission device and driving system for vehicle - Google Patents

In-vehicle power transmission device and driving system for vehicle Download PDF

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Publication number
CN101898509B
CN101898509B CN200910217181.2A CN200910217181A CN101898509B CN 101898509 B CN101898509 B CN 101898509B CN 200910217181 A CN200910217181 A CN 200910217181A CN 101898509 B CN101898509 B CN 101898509B
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CN
China
Prior art keywords
tumbler
power
power transmission
power distribution
tumblers
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Application number
CN200910217181.2A
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Chinese (zh)
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CN101898509A (en
Inventor
川崎宏治
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Denso Corp
Soken Inc
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Denso Corp
Nippon Soken Inc
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Priority claimed from JP2009179547A external-priority patent/JP5372648B2/en
Priority claimed from JP2009242314A external-priority patent/JP5203332B2/en
Application filed by Denso Corp, Nippon Soken Inc filed Critical Denso Corp
Publication of CN101898509A publication Critical patent/CN101898509A/en
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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
    • 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
    • B60K6/38—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 driveline clutches
    • B60K6/383—One-way clutches or freewheel devices
    • 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
    • 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
    • F16H37/0833—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 with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—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 with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H37/0846—CVT using endless flexible members
    • 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
    • F16H37/0833—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 with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—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 with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
    • 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
    • F16H37/0833—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 with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—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 with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
    • 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
    • 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
    • F16H2037/104—Power split variators with one end of the CVT 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
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • 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
    • F16H3/724—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 using external powered electric machines
    • F16H3/725—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 using external powered electric machines with means to change ratio in the mechanical gearing
    • 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

Abstract

The present invention relates to an in-vehicle power transmission device and a driving system for a vehicle. Particularly provided is an in-vehicle power transmission apparatus which is equipped with a plurality of power split rotors and a power transmission control mechanism. The power split rotors work to split power among a rotary electric machine such as a motor-generator, an internal combustion engine, and a driven wheel of the vehicle. If rotational energy, as outputted from the power split rotors, is defined as being positive in sign, the power split rotors are so assembled that when the power transmission control mechanism establishes transmission of the rotational energy that is positive in sign as the power from a first rotor that is one of the power split rotors to the internal combustion engine, the other power split rotors are so linked as to provide output rotational energies which are opposite in sign to each other. This enables the speed of the first rotor to be placed at substantially zero.

Description

In-vehicle power transmission device and the drive system for vehicle
Technical field
The present invention relates generally to a kind of in-vehicle power transmission device, its have multiple for by outputting power or torque at rotating machine (as dynamotor), carry out the power distribution tumbler that distributes between explosive motor and the flower wheel of vehicle, and this power distribution tumbler is designed to rotate synergistically each other, the invention still further relates to a kind of drive system of vehicle.
Background technology
In recent years, in the energy reducing automobile consumption, the so-called hybrid electric vehicle with rotating machine (propulsion source such as, in car also includes electrical motor and electrical generator except explosive motor) is used by practice.Usually the efficiency used in low cruise scope self-energy due to explosive motor is low, so hybrid electric vehicle is typically controlled to, explosive motor is quit work within the scope of low cruise.The difficulty that hybrid electric vehicle faces is, how to make explosive motor reset during vehicle operating.Such as, be difficult to couple with vehicle flower wheel and the tumbler rotated now is mechanically connected with the internal-combustion engine machine crankshaft being in stopping.
In order to avoid the problems referred to above, actual use has the hybrid electric vehicle of electrical motor, and the output shaft of this electrical motor is directly connected with the bent axle of driving engine, the torque exported from this electrical motor is sent to engine crankshaft, thus starts this driving engine.After the engine is started up, the torque generated by driving engine is transmitted to vehicle flower wheel.
In addition, actual use has the hybrid electric vehicle of typical epicyclic reduction gear (also crying epicylic reduction gear system), this epicyclic reduction gear is by three tumblers: sun wheel, frame (being also pinion carrier) and gear ring form, and these three tumblers couple with electrical generator, explosive motor and electrical motor respectively.Flower wheel and the electromechanics of vehicle couple.In operation, act on the torque of sun wheel or gear ring for revolving planet frame, thus the S. A. (that is, bent axle) of explosive motor is rotated.Explosive motor is by using the torque starting of pinion carrier.After explosive motor starts, explosive motor torque is transmitted to the flower wheel of vehicle by pinion carrier.
Such as, typical hybrid electric vehicle patent publication us is below known.Japanese Patent Publication No.3580257 Japanese Patent Publication No.3626151 Japanese Patent Publication No.3614409 Japanese Patent first time is No.2002-281607 Japanese Patent first time openly No.2000-142146 Japanese Patent first time openly No.9-46821 Japanese Patent first time openly No.2006-77859 openly
As mentioned above, the S. A. of electrical motor and directly coupling of the S. A. of explosive motor will cause the torque load produced by explosive motor to be applied on this electrical motor, thus cause the energy consumed to increase.Going back problems faced is equally, when explosive motor starts, the torque pulsation that explosive motor S. A. produces may cause the driving performance of vehicle to be deteriorated.
In addition, the use of epicyclic reduction gear will cause a problem, and namely when the rotative speed of pinion carrier is lower, the starting of explosive motor will cause this explosive motor temporarily to be remained on low cruise.This has just run counter to hybrid electric vehicle and has wished to make explosive motor to operate in wish in the high speed range of energy ecology.
Summary of the invention
Therefore, main purpose of the present invention avoids the shortcoming of prior art.
Another object of the present invention is to provide a kind of power drive for vehicle being designed to effectively to start explosive motor.
According to one aspect of the invention, provide a kind of power drive, this power drive is for having the vehicle of rotating machine, explosive motor and at least one flower wheel.Power drive comprises: (a) multiple power distribution tumbler, its rotate synergistically each other with by power vehicle rotating machine, distribute between explosive motor and flower wheel; And (b) power transmission control mechanism, it is for optionally setting up and interrupting the power transmission between the first tumbler and explosive motor, and wherein the first tumbler is one of power distribution tumbler.If the symbol that is rotated in exported from power distribution tumbler is just defined as, then arrange power distribution tumbler make when power transmission control mechanism set up picture from the first tumbler to the symbol the power of explosive motor be positive rotation can transmission time, other tumbler in power distribution tumbler except the first tumbler is connected to be provided in output rotation energy different from each other on symbol.
Especially, when power transmission control mechanism sets up the transmission of the rotation energy from the first tumbler to explosive motor, other tumbler in power distribution tumbler except the first tumbler rotates energy for being created on reciprocal output on symbol.This just makes the first tumbler be placed in pole slow speed of revolution or zero (0) speed or can be lowered extremely low-level situation from the rotation that the first tumbler exports.Therefore, when explosive motor quits work, but when vehicle is run by the power of rotating machine (as dynamotor), power drive can make the rotating speed of the first tumbler basic consistent with zero (0) rotating speed of explosive motor, and the initial moment that the rotation exported by the first tumbler can provide is applied to explosive motor to start it.The vibration of this power transmission control mechanism just making application initial moment and produce is minimum.After the initial moment from the first tumbler is applied to explosive motor, in other words after explosive motor is started, power drive can be used for the torque that explosive motor generates to input to one of power distribution tumbler or some tumblers (such as, the first tumbler or other power distribution tumbler) to drive vehicle.
In preference pattern of the present invention, generate in power distribution tumbler symbol is different each other rotation can some tumblers coupled by machinery each other by the path of the assembly of this power distribution tumbler by bypass.Especially, which achieves in power distribution tumbler some tumblers generating the different rotation energy of symbol each other and do not need two rotating machines (such as, dynamotor), in these tumblers one for supplying the rotation energy of output, another is then for receiving this rotation energy.
Some tumblers of power distribution tumbler are connected like this with the first tumbler, thus have the rotative speed linearly arranged in alignment chart (monographic chart).Power drive comprises coupled connection mechanism further, and its assembly at this power distribution tumbler is outer to be coupled in the machinery of two in these tumblers together.Coupled connection mechanism is as the change-speed box with variable-speed ratio (being also input and output speed ratio).Especially, alignment chart cathetus the transmitting ratio being tilted through controlled variator and change.Therefore, the rotating speed of the first tumbler controls by changing the transmitting ratio irrelevant with secondary speed.
Power transmission control mechanism is used as the first power transmission control mechanism, optionally to set up and to interrupt the power transmission between the first tumbler and the S. A. of explosive motor.Power drive also comprises the second power transmission control mechanism, and it is for optionally setting up and interrupting the power transmission between the second tumbler and explosive motor, and wherein the second tumbler is one of power distribution tumbler.This structure makes initial moment be applied to explosive motor S. A. from the first tumbler, and makes the torque generated by explosive motor be applied to the second tumbler.Especially, driving engine, by the torque starting exported from power distribution tumbler, does not therefore need independent engine primer.Further, power between first, second tumbler and driving engine transmits and is optionally interrupted or sets up, therefore minimize the energy consumed to the driving engine stopped by application of torque, and enable the torque transmission between first, second tumbler and driving engine become the function of the velocity contrast between engine rotation axle and first, second tumbler.
First power transmission control mechanism has unidirectional power transmission device, when the rotating speed of the outgoing side that the rotating speed of the input side that unidirectional power transmission device is connected with the first tumbler is connected with explosive motor S. A. relative to this unidirectional power transmission device is nonnegative value, power transmission set up by this unidirectional power transmission device.After driving engine is started, when fuel starts burned in this driving engine, S. A. will produce torque, the speed of this S. A. is increased sharply.This torque change being sent to the first tumbler can cause the torque pulsation in power drive.But time on the speed that engine speed is increased to the input side of the free-wheel clutch be connected with the first tumbler, the transmission of this change of the torque to the first tumbler will be prevented from, thus avoid the torque pulsation in power drive (i.e. car body).
First power transmission control mechanism can also have automatically controlled interrupter, and this automatically controlled interrupter separates with unidirectional power transmission device.Automatically controlled interrupter is for interrupting the power transmission between the first tumbler and explosive motor S. A..This just makes it possible to the power transmission avoided before needing to start explosive motor from the first tumbler to explosive motor, thus minimizes the energy by motive use being consumed in engine rotation axle.
Second power transmission control mechanism can have unidirectional power transmission device, when the rotating speed of the outgoing side that the rotating speed of the input side that unidirectional power transmission device is connected with explosive motor S. A. is connected with the second tumbler relative to this unidirectional power transmission device is nonnegative value, power transmission set up by this unidirectional power transmission device.When engine rotation axle needs to be mechanically connected with the second tumbler, during to add motor torque to second tumbler, preferably make the speed of the speed of engine rotation axle and the second tumbler consistent each other.But this just needs the precise hard_drawn tuhes to speed.When the speed of engine rotation axle equals the speed of the second tumbler, unidirectional power transmission device is used for the torque of driving engine to be applied to the second tumbler, does not thus need to carry out precise hard_drawn tuhes to the speed of engine rotation axle and the speed of the second tumbler.
One of power distribution tumbler is coupled to rotating machine by machinery.Power distribution tumbler is connected like this, the rotating speed of one of the power distribution tumbler rotating speed of the first tumbler directly being depended on couple with rotating machine.This just makes the rotating speed of the first tumbler can be controlled by the rotating speed of rotating machine.
One of power distribution tumbler is coupled to rotating machine by machinery.Power distribution tumbler is connected like this, makes the rotating speed of other tumbler of the power distribution tumbler except the tumbler being coupled to rotating machine directly depend on the rotating speed of the tumbler coupled with rotating machine and the rotating speed of the second tumbler.This just makes the rotating speed of other tumbler of power distribution tumbler can be controlled by the rotating speed of rotating machine or driving engine.
First tumbler and the second tumbler can be implemented by one of power distribution tumbler.First power transmission control mechanism separates with the second power transmission control mechanism.Further, the first power transmission control mechanism and the second power transmission control mechanism can be implemented by automatically controlled interrupter, and this automatically controlled interrupter is for interrupting the power transmission between the first tumbler and explosive motor S. A..In addition, the first tumbler preferably makes when non-vanishing with the speed of one of the mechanical power distribution tumbler coupled of flower wheel, and the speed of this first tumbler can be controlled as zero (0).Automatically controlled interrupter is supposed to work as described as follows, that is: when initial moment is applied to explosive motor from the first tumbler by needs, the first tumbler and engine rotation shaft mechanical are coupled together; Before fuel combustion after initial moment is employed and is within the engine controlled, interrupt the connection of the first tumbler and driving engine; And after the fuel combustion in driving engine controls to start, if the speed discrepancy between the first tumbler and driving engine is lower than given value, then the first tumbler and engine mechanical are coupled together.
First tumbler and the second tumbler are separately.This just makes it possible to torque to be applied to engine rotation axle from the first tumbler, and also the torque from driving engine can be applied to the second tumbler.Torque between first, second tumbler and driving engine transmits and selectively sets up or interrupt, and therefore makes it possible to start this driving engine when the speed of the first tumbler is the speed of applicable fire an engine.After driving engine is started, the torque generated by driving engine sends flower wheel to by the second tumbler.This just makes when driving engine runs on the speed different from the first tumbler, and the torque energy of driving engine is used.Therefore, can fire an engine be possible earlier when driving engine enters effective speed range.
Power distribution tumbler is connected like this, makes the rotating speed of the first tumbler lower than the rotating speed of the second tumbler.This just makes the first tumbler to be used to fire an engine, and the second tumbler can be used to motor torque to be applied to flower wheel, thus allow driving engine to operate in speed higher when starting than driving engine continuously, to send motor torque to flower wheel.Therefore, fire an engine is possible to make its speed enter effective speed range earlier.
Power distribution tumbler can be implemented by three or more tumblers, and these tumblers are connected like this, thus its rotative speed is linearly arranged in alignment chart.First tumbler is the tumbler being arranged in alignment chart rotative speed intermediate value place in three or more tumblers.This is conducive to making the first tumbler more easily have relatively low speed, and velocity contrast when therefore making engine starting between the first tumbler and engine rotation axle can reduce.
Can to be connected like this thus the tumbler that its rotative speed is linearly arranged in alignment chart realizes power distribution tumbler by three or more.Two tumblers in these three or more tumblers that rotative speed is different in alignment chart are coupled to rotating machine by machinery.
At least one in two tumblers in these three or more tumblers is coupled by the change-speed box and rotating machine with variable-speed ratio.This structure makes two of having in alignment chart in the tumbler of different rotation rates to be controlled mutually independently speed, just as in the situation that two tumbler machineries in two rotating machines and tumbler couple.In addition, when using two such rotating machines, this structure can also eliminate energy loss, and wherein this electric energy produces by one that operates into electrical generator in this rotating machine, and be supplied in this rotating machine another rotating machine operating into electrical motor.
One of machinery power distribution tumbler being coupled to flower wheel can have in alignment chart in these three or more tumblers and rotating machine machinery couple two tumblers rotative speed between middle rotative speed.In addition, power distribution tumbler is implemented by four tumblers (such as, Ravigneaux formula compound planet gear), and these four tumblers are connected like this, and its rotative speed is arranged on straight line in alignment chart.Be arranged in rotative speed in the middle of alignment chart in four tumblers and flower wheel can be coupled to by machinery with the tumbler that the first tumbler separates.Especially, flower wheel with there is the tumbler of middle speed in alignment chart be connected, be conducive to thus making along normal direction or reverse directions rotary drive wheel or making flower wheel stop being more prone to.The tumbler being coupled to flower wheel separates with the first tumbler, thus allows the speed of the first tumbler to be determined independent of the speed of flower wheel.
Power drive comprises first planet gear cluster and the second compound planet gear further, and each gear cluster all has sun wheel, pinion carrier and gear ring, and they are three power distribution tumblers.Two in the power distribution tumbler of first planet gear cluster to be coupled to two in the power distribution tumbler of the second compound planet gear by machinery.Four in 6 power distribution tumblers altogether of first, second compound planet gear have different rotating speeds in alignment chart, at least three in these four tumblers respectively machinery be coupled to rotating machine, explosive motor and flower wheel.Especially, four in 6 power distribution tumblers are connected like this, to have the rotative speed linearly arranged in alignment chart, thus specify the rotating speed of rotating machine, explosive motor and flower wheel.
Power drive comprises conv further, and it is converted to another for of the power distribution tumbler that machinery is coupled to flower wheel.
Flower wheel speed is adjusted to the other restriction that expectation value causes power distribution tumbler speed, this will cause the other restriction to rotating machine or internal-combustion engine motor speed.It may be the factor hindering rotating machine or the operation of explosive motor within the scope of effective velocity that this speed regulates.On the contrary, when needs make flower wheel reach desired speed, structure of the present invention alleviates the restriction to rotating machine speed or internal-combustion engine motor speed, thus rotating machine or explosive motor are operated within the scope of effective velocity.
Vehicle can be the automobile with two flower wheels.Power drive may further include conv, and this conv is used for other tumbler converted to by some tumblers being coupled to vehicle flower wheel in power distribution tumbler in power distribution tumbler.Be coupled to more described tumblers of flower wheel and other tumbler in power distribution tumbler and comprise a tumbler in the second tumbler and power distribution tumbler except the first tumbler respectively.
Second tumbler is coupled to flower wheel by the second power transmission control mechanism machinery.The anti-stopping power of this structure is sent to the second tumbler by the second power transmission control mechanism from explosive motor, and enables the speed of explosive motor be adjusted to the speed of flower wheel when torque is transferred into the second tumbler from explosive motor.At this moment, torque can be applied to flower wheel by from power distribution tumbler continuously.Then, flower wheel can be mechanically connected with the second tumbler by the second power transmission control mechanism, thus makes the flower wheel when flower wheel rotates with identical speed with engine rotation axle can be connected to engine rotation axle.This just minimizes the time of cutting off during conversion operations and flower wheel being provided to torque.
According to a second aspect of the invention, a kind of power drive for vehicle is provided, comprise: (a) multiple power distribution tumbler, its each other collaborative rotate with by power at rotating machine, distribute between explosive motor and vehicle flower wheel; (b) the first power transmission control mechanism, it is for optionally setting up and interrupting the power transmission between the first tumbler and explosive motor S. A., and wherein the first tumbler is one of power distribution tumbler; (c) the second power transmission control mechanism, it is for optionally setting up and interrupting the power transmission between the second tumbler and explosive motor S. A., and wherein the second tumbler is also one of power distribution tumbler.
Especially, driving engine, by the torque starting exported from power distribution tumbler, does not therefore need independent engine primer.Further, power transmission between first, second tumbler and driving engine is optionally interrupted or sets up, therefore minimize the energy consumed to the driving engine in stopping by application of torque, and make the transmission of the torque between first, second tumbler and driving engine can become the function of the velocity contrast between engine rotation axle and first, second tumbler.
In preference pattern of the present invention, first power transmission control mechanism can also have unidirectional power transmission device, when the rotating speed of the outgoing side that the rotating speed of the input side that this unidirectional power transmission device is connected with the first tumbler is connected with explosive motor S. A. relative to this unidirectional power transmission device is nonnegative value, power transmission set up by this unidirectional power transmission device.
First power transmission control mechanism can also have automatically controlled interrupter, and it separates with unidirectional power transmission device.Automatically controlled interrupter is for interrupting the power transmission between the first tumbler and explosive motor S. A..
Second power transmission control mechanism can have unidirectional power transmission device, when the rotating speed of the outgoing side that the rotating speed of the input side that this unidirectional power transmission device is connected with explosive motor S. A. is connected with the second tumbler relative to this unidirectional power transmission device is nonnegative value, power transmission set up by this unidirectional power transmission device.
One of power distribution tumbler can be coupled to rotating machine by machinery.Power distribution tumbler is connected like this, the rotating speed of one of the power distribution tumbler rotating speed of the first tumbler directly being depended on couple with rotating machine.
One of power distribution tumbler can be coupled to rotating machine by machinery.Power distribution tumbler is connected like this, and the rotating speed of other tumbler in power distribution tumbler except the tumbler being coupled to rotating machine is directly depended on by the rotating speed coupled with the rotating speed of the tumbler of rotating machine and the second tumbler.
First tumbler and the second tumbler can be implemented by one of power distribution tumbler.First power transmission control mechanism can separate with the second power transmission control mechanism.
First tumbler can separate with the second tumbler.
Power distribution tumbler can be connected like this, makes the rotating speed of the first tumbler lower than the rotating speed of the second tumbler.
Power distribution tumbler can be implemented by three or more tumblers, and these three or more tumblers are connected like this, thus its rotative speed is linearly arranged in alignment chart.First tumbler can be one in these three or more tumblers, and it is positioned at intermediate speed place in alignment chart.。
Power distribution tumbler can be implemented by three or more tumblers, and these three or more tumblers are connected like this, thus its rotative speed is linearly arranged in alignment chart.Two in these three or more tumblers that rotative speed is different in alignment chart can be coupled to rotating machine by machinery.
One is had at least to be coupled to rotating machine by the change-speed box with variable-speed ratio in described two tumblers in these three or more tumblers.
The rotative speed between the rotative speed being in and being coupled to two tumblers of rotating machine by machinery in three or more tumblers can be had in alignment chart by that tumbler that machinery is coupled to flower wheel in power distribution tumbler.
Power distribution tumbler can be implemented by four tumblers, and these four tumblers are connected like this, thus its rotative speed is linearly arranged in alignment chart.Mediate in four tumblers rotative speed and those tumblers that can separate with the first tumbler are coupled to flower wheel by machinery in alignment chart.
Power drive comprises first planet gear cluster and the second compound planet gear further, and each gear cluster all has sun wheel, pinion carrier and gear ring, and they are three power distribution tumblers.Two in the power distribution tumbler of first planet gear cluster two tumblers being coupled to the power distribution tumbler of the second compound planet gear by machinery.Four in 6 power distribution tumblers altogether of first, second compound planet gear have different rotating speeds in alignment chart, and in these four tumblers, at least three are coupled to rotating machine, explosive motor and flower wheel by machinery respectively.
Power drive may further include conv, this conv be used for by power distribution tumbler by machinery be coupled to flower wheel that tumbler be converted to another tumbler in power distribution tumbler.
Vehicle can be the automobile with two flower wheels.Power drive can comprise conv further, and this conv is used for other tumbler converted to by those tumblers being coupled to vehicle flower wheel in power distribution tumbler in power distribution tumbler.Be coupled to those tumblers described of flower wheel and other tumbler in power distribution tumbler and comprise a tumbler in the second tumbler and power distribution tumbler except the first tumbler respectively.
According to a third aspect of the present invention, provide a kind of driver for vehicle, it comprises power drive and controller.Power drive comprises (a) multiple power distribution tumbler, its each other collaborative rotate with by power at rotating machine, be arranged between explosive motor on vehicle and vehicle flower wheel and distribute; And (b) power transmission control mechanism, it is for optionally setting up and interrupting the power transmission between the first tumbler and explosive motor, and wherein the first tumbler is one of power distribution tumbler.If the rotation exported from power distribution tumbler just can be defined as at symbol, then power distribution tumbler is arranged such, make when power transmission control mechanism set up symbol be positive rotation can the transmission of (as from the first tumbler to the power of explosive motor) time, the output that other tumbler in power distribution tumbler except the first tumbler can be connected to provide symbol each other contrary rotates energy.Controller is for controlling the operation of power drive.When needing to start explosive motor and the rotating speed of this explosive motor lower than given value, controller control power transmission control mechanism with the symbol set up from the first tumbler to explosive motor be positive rotation can transmission.
According to a fourth aspect of the present invention, provide a kind of driver for vehicle, it comprises power drive and controller.Power drive comprises (a) multiple power distribution tumbler, its each other collaborative rotate with by power at rotating machine, be arranged between explosive motor on vehicle and vehicle flower wheel and distribute; (b) the first power transmission control mechanism, it is for optionally setting up and interrupting the power transmission between the first tumbler and explosive motor S. A., and wherein the first tumbler is one of power distribution tumbler; And (c) the second power transmission control mechanism, it is for optionally setting up and interrupting the power transmission between the second tumbler and explosive motor S. A., and wherein the second tumbler is one of power distribution tumbler.Controller is for controlling the operation of power drive.When needing to start explosive motor and the rotating speed of explosive motor lower than given value, controller control the first power transmission control mechanism with set up from the first tumbler to the symbol of explosive motor S. A. be positive rotation can transmission.
In drive system described above, the power drive of each also can be designed to have structure as above.
Accompanying drawing explanation
By the accompanying drawing of detailed description below and the preferred embodiment of the present invention, the present invention may be better understood, but this detailed description and accompanying drawing are not intended the present invention to be limited to specific embodiment, but just to the object explained and understand.In accompanying drawing: Fig. 1 (a) shows the block diagram of the hybrid power system of vehicle, power drive according to a first embodiment of the present invention and drive system are wherein installed; Fig. 1 (b) is the schematic diagram of the power transmission path of the power drive of Fig. 1 (a); Fig. 2 (a) shows the schematic block diagram of the power transmission path when vehicle is started by dynamotor; Fig. 2 (b) illustrates along with internal-combustion engine motor speed, the alignment chart of the operation of the distributing means for power supply of Fig. 1 power drive; Fig. 2 (c) is the chart of syntactics of the sun wheel of the distributing means for power supply listing Fig. 2 (a) and Fig. 2 (b), hand of rotation between pinion carrier and gear ring, torque and power; Fig. 3 (a) shows the schematic block diagram of the power transmission path when explosive motor is started by the distributing means for power supply of Fig. 1 (a); Fig. 3 (b) illustrates along with internal-combustion engine motor speed, the alignment chart of distributing means for power supply operation; Fig. 3 (c) is the sun wheel of the distributing means for power supply listing Fig. 3 (a) and Fig. 3 (b), between pinion carrier and gear ring with the syntactics chart of hand of rotation, torque and power; Fig. 4 (a) shows the schematic block diagram of the power transmission path when the distributing means for power supply of Fig. 1 (a) is exported in torque by explosive motor; Fig. 4 (b) illustrates along with internal-combustion engine motor speed, the alignment chart of the operation of distributing means for power supply; Fig. 5 shows the block diagram of power drive according to a second embodiment of the present invention; Fig. 6 (a) shows the block diagram of power drive according to a third embodiment of the present invention; Fig. 6 (b) is the schematic diagram of the power transmission path of the power drive of Fig. 6 (a); Fig. 7 (a) shows the block diagram of power drive according to a fourth embodiment of the present invention; Fig. 7 (b) is the schematic diagram of the power transmission path of the power drive of Fig. 7 (a); Fig. 8 (a) shows the block diagram of power drive according to a fifth embodiment of the present invention; Fig. 8 (b) is the schematic diagram of the power transmission path of power drive modification; Fig. 8 (c) is the schematic diagram of the power transmission path of power drive modification; Fig. 9 (a) shows the block diagram of power drive according to a sixth embodiment of the present invention; Fig. 9 (b) is the schematic diagram of the power transmission path of the power drive of Fig. 9 (a); Figure 10 (a) shows the schematic block diagram of power drive according to a seventh embodiment of the present invention; Figure 10 (b) illustrates along with internal-combustion engine motor speed, the alignment chart of the operation of the distributing means for power supply of the power drive of Figure 10 (a); Figure 11 (a) and Figure 11 (b) show the schematic diagram that power drive is arranged on the power transmission path of the power drive of Figure 10 (a) when front engine, front drives (FF) vehicle and front engine rear wheel to drive (FR) vehicle respectively; Figure 12 (a), Figure 12 (b) and Figure 12 (c) show the block diagram of the power drive modification of the first embodiment; Figure 13 (a) and Figure 13 (b) shows the block diagram of the modification of the power drive of the first embodiment; Figure 14 (a) and Figure 14 (b) shows the block diagram of the modification of the power drive of the first embodiment respectively; Figure 15 (a) and Figure 15 (b) shows the block diagram of the modification of the power drive of the second embodiment; Figure 16 (a), Figure 16 (b) and Figure 16 (c) illustrate in each modification of Figure 15 (a) and Figure 15 (b) along with the alignment chart that the distributing means for power supply of internal-combustion engine motor speed operates; Figure 17 (a) to Figure 17 (j) is the alignment chart of the modification structures illustrating distributing means for power supply of the present invention; Figure 18 (a) to Figure 18 (j) is the alignment chart of the modification structures illustrating distributing means for power supply of the present invention; Figure 19 (a), Figure 19 (b) and Figure 19 (c) show the block diagram of the modification of the power drive of the first embodiment; Figure 20 (a), Figure 20 (b), Figure 20 (c) and Figure 20 (d) show the block diagram of the modification of the power drive of the first embodiment; Figure 21 (a), Figure 21 (b), Figure 21 (c) and Figure 21 (d) show the block diagram of the modification of the power drive of the first embodiment; Figure 22 (a) and Figure 22 (b) shows the block diagram of the modification of the power drive of the first embodiment; Figure 23 (a) and Figure 23 (b) shows the block diagram of the modification of the power drive of the first embodiment; Figure 24 (a) and Figure 24 (b) shows the block diagram of the modification of the power drive of the first embodiment; And Figure 25 (a), Figure 25 (b) are the sequential charts of the operation of the power drive illustrating Figure 24 (a) with Figure 25 (c).
Detailed description of the invention
With reference to accompanying drawing, wherein identical Reference numeral represents identical parts in the drawings, with particular reference to Fig. 1 (a) and Fig. 1 (b), illustrated therein is the hybrid power system be made up of in-vehicle power transmission device according to a first embodiment of the present invention and drive system.Alternatively, in-vehicle power transmission device of the present invention can be used for only having the battery-driven car (EV) of electrical motor as the propulsion source making wheel run, or only has the automobile of explosive motor as the propulsion source making wheel run.Drive system has in-vehicle power transmission device and the controller for controlling the operation of this power drive.Drive system can also install propulsion source wherein, such as, and dynamotor, electrical motor or explosive motor.
Fig. 1 (a) shows the structure of hybrid power system.Fig. 1 (b) is the schematic diagram of power transmission path.
Hybrid power system comprises dynamotor (MG) 10 and distributing means for power supply 20.Dynamotor 10 is made up of three-phase alternating current (AC) dynamotor, and as in-vehicle power generating apparatus together with explosive motor 12.Distributing means for power supply 20 is in the dynamotor 10 of automobile, distributed power or torque between explosive motor 12 (such as, engine petrol) and flower wheel 14.
Distributing means for power supply 20 comprises first planet gear cluster 22 and the second compound planet gear 24.First planet gear cluster 22 comprises the gear ring R of the pinion carrier C being mechanically connected to the second compound planet gear 24, and comprises sun wheel S, and this sun wheel S is mechanically connected to the sun wheel S of the second compound planet gear 24.Output shaft (that is, S. A.) the 10a machinery of dynamotor 10 is coupled to the gear ring R of the second compound planet gear 24.Vehicle flower wheel 14 is mechanically connected to the gear ring R of first planet the gear cluster 22 and pinion carrier C of the second compound planet gear 24.Especially, the gear ring R of first planet the gear cluster 22 and pinion carrier C of the second compound planet gear 24 is coupled by typical differential gear and typical axle drive shaft and flower wheel 14 machinery.It should be noted that, the tumbler (being also referred to as power distribution tumbler hereinafter) of distributing means for power supply 20, as used herein, be not restricted to first planet gear cluster 22 and sun wheel S, pinion carrier C both the second compound planet gear 24 and gear ring R, but turning unit and/or the axle drive shaft of differential gear can be comprised in addition or only.
The pinion carrier C of first planet gear cluster 22 is coupled to the bent axle (that is, S. A. 12a) of explosive motor 12 by power-transfer clutch 30 and unilateral bearing 32 machinery.Power-transfer clutch 30 is used as electric-controlled mechanical interrupter and interrupts the transmission of power (torque) between the pinion carrier C and unilateral bearing 32 of first planet gear cluster 22.In this embodiment, power-transfer clutch 30 is normally open clutch.When the rotative speed of power-transfer clutch 30 is not less than the rotative speed of S. A. 12a of driving engine 12, unilateral bearing 32 is used as one-way transmission mechanism and allows power (torque) to be sent to driving engine 12 from power-transfer clutch 30.In other words, when power-transfer clutch 20 engages, unilateral bearing 32 works to make the S. A. 12a of driving engine 12 follow the rotation of the pinion carrier C of first planet gear cluster 22, till when speed height than the pinion carrier C of first planet gear cluster 22 of the speed of the S. A. 12a of driving engine 12.
Unilateral bearing 34 is arranged between the sun wheel S of first planet the gear cluster 22 and sun wheel S of the second compound planet gear 24.As unilateral bearing 32, when the speed of the S. A. 12a of driving engine 12 is not less than the speed of sun wheel S, unilateral bearing 34 is used as one-way transmission mechanism and allows power (torque) to be sent to first planet gear cluster 22 and the second compound planet gear 24 from driving engine 12.In other words, unilateral bearing 34 works to make the sun wheel S of first planet the gear cluster 22 and sun wheel S both the second compound planet gear 24 follow the rotation of the S. A. 12a of driving engine 12, till when speed height than S. A. 12a of the speed of sun wheel S.
First planet gear cluster 22 and the sun wheel S both the second compound planet gear 24 are coupled to the S. A. 10a of dynamotor 10 by power-transfer clutch 38 and toric transmission (CVT) 36 machinery.As shown in Fig. 1 (b), CVT 36 is mechanically connected to the gear ring R of the second compound planet gear 24 by counter gear CN.In other words, the sun wheel S of first planet the gear cluster 22 and sun wheel S both the second compound planet gear 24 is coupled together like this, to receive the torque of automotor-generator 10, and without any need for the turning unit of the distributing means for power supply 20 engaged with sun wheel S or tumbler (that is, power distribution tumbler).The number of teeth of counter gear CN both can identical from the number of teeth of the gear ring R of the second compound planet gear 24 also can be different.As adopted in this embodiment, CVT 36 is the mechanical type with metal tape or rubber tape.Power-transfer clutch 38 works as interrupting or open the electric-controlled mechanical interrupter of the power transmission between the sun wheel S of CVT 36 and first planet the gear cluster 22 and sun wheel S of the second compound planet gear 24.
Hybrid power system also comprises the controller 40 controlling power drive operation.Controller 40 controls the operation of power drive for actuated clutches 30 and 38 and determines the controlled variable of driving engine 12.Controller 40 also for the operation of control inverter 42 to determine the controlled variable of dynamotor 10.
The vehicle launch operation of the starting control that have employed power drive and driving engine 12 will be described below.
First, the vehicle launch operation that have employed dynamotor 10 is described in detail in detail with reference to Fig. 2 (a) and Fig. 2 (b).Fig. 2 (a) shows the power transmission path when vehicle is started.Fig. 2 (b) is the alignment chart of the operation of the distributing means for power supply 20 illustrated along with driving engine 12 speed.In the illustrated case, power-transfer clutch 30 has interrupted the connection between the pinion carrier C of unilateral bearing 32 and first planet gear cluster 22.Between the sun wheel S that power-transfer clutch 28 is connected to CVT 36 and first planet gear cluster 22 and sun wheel S both the second compound planet gear 24.
In the example of Fig. 2 (b), driving engine 12 quits work.The speed of the composition first planet gear cluster 22 of distributing means for power supply 20 and the tumbler of the second compound planet gear 24 depends on the speed of dynamotor 10 and the transmitting ratio (being also input and output speed ratio, variable-speed ratio, belt wheel ratio (pulleyratio) or CVT ratio) of CVT36.Especially, in the alignment chart of Fig. 2 (b), the speed of the speed of the sun wheel S of first planet gear cluster 22 and the sun wheel S both the second compound planet gear 24 (namely, drive link in Fig. 2 (b) or the speed of transmission shaft), the speed of the pinion carrier C of first planet gear cluster 22 (namely, the speed of the starting shaft in Fig. 2 (b)), the speed of the gear ring R of first planet gear cluster 22 and the pinion carrier C of the second compound planet gear 24 (namely, output speed in Fig. 2 (b)), and second compound planet gear 24 gear ring R speed (namely, the speed of MG 10) be all positioned on skew lines.Therefore, the speed of those tumblers in distributing means for power supply 20 except the sun wheel S of the sun wheel S of first planet gear cluster 22, both the second compound planet gears 24 and the gear ring R of the second compound planet gear 24 is set by the speed of the sun wheel S determining the gear ring R of the second compound planet gear 24, the sun wheel S of first planet gear cluster and the second compound planet gear.First planet gear cluster 22 and sun wheel S, pinion carrier C both the second compound planet gear 24 and gear ring R are collaborative each other to be rotated.Such as, the speed of pinion carrier C depends on that the speed of sun wheel S and gear ring R can be zero (0).
The structure of the power drive of this embodiment is designed to make dynamotor 10 can generate higher torque when starting vehicle, and does not need the size increasing dynamotor 10.This is due to following reason.
If the ratio of the tooth number Z s of sun wheel S and the tooth number Z r of gear ring R (namely in the second compound planet gear 24, Zs/Zr) ρ is defined as, the ratio of the rotating speed Nm of dynamotor 10 and the rotating speed Ns of sun wheel S (namely, Nm/Ns) β is defined as, the torque of gear ring R, sun wheel S, pinion carrier C and dynamotor 10 is respectively defined as Tr, Ts, Tc and Tm, then meet following equalities.Tr＝-Tc/(1+ρ) (c1)Ts＝-ρTc/(1+ρ) (c2)β(Tm+Tr)＝Ts (c3)
From equation (c3), utilize equation (c1) and (c2) cancellation torque Tr and Ts, obtain Tc=(1+ ρ) Tm/{ (ρ/β)-1} (c4)
Equation (c4) represents rolling up of the torque Tc of the pinion carrier C (i.e. the output shaft of distributing means for power supply 20) of the second compound planet gear 24, in other words, the torque being transmitted to flower wheel 14 obtains by making more closer to each other than ρ and β.Guarantee the torque of starting required by vehicle, and do not need the size increasing dynamotor 10.
(namely the hybrid power system of this embodiment can select the transmitting ratio of CVT36, speed ratio) realize so-called geared neutral (geared neutral), the speed of flower wheel 14 is set to zero (0) at dynamotor 10 run duration by it.Especially, distributing means for power supply 20 is designed to make the tumbler in the second compound planet gear 24 except being coupled to the pinion carrier C of flower wheel 14: the amount (i.e. power) of the output rotation energy of sun wheel S and gear ring R is opposite each other on symbol, as shown in Fig. 2 (c).Therefore, when setting up geared neutral so that the speed of flower wheel 14 is set to zero (0), this circulates causing power to pass through having the loop mechanical path of power-transfer clutch 38 and CVT 36 between sun wheel S and gear ring R.In other words, when distributing means for power supply 20 is in geared neutral, the amount (i.e. power) exporting to the rotation energy of flower wheel 14 will be zero (0).If power does not circulate by extend through the loop mechanical path of sun wheel S and gear ring R, then according to conservation of energy theorem, this can be totally consumed causing the output of dynamotor 10 as heat energy in the second compound planet gear 24.This can not be used for the unpractical structure of distributed power by causing the second compound planet gear 24 to become, in other words, the tumbler of the second compound planet gear 24 is not used as the power distribution tumbler of distributing means for power supply 20.When setting up geared neutral in the hybrid power system in this embodiment, this will make, and power is inevitable again to be circulated in distributing means for power supply 20.Sun wheel S is extended to and the loop paths returned to gear ring R does not need fully that machinery is continuously from the gear ring R of the second compound planet gear 24.Such as, this loop paths can be have optionally closed to make rotation can by the path of breaking part of again circulating by power-transfer clutch.Notice in Fig. 2 (c), positive sign (+) and the negative sign (-) of the hand of rotation of each sun wheel S, pinion carrier C and gear ring R represent contrary direction: their normal direction and opposite sense, rotating can (namely, power) positive sign (+) instruction rotation can export from distributing means for power supply 20, and the positive sign (+) of torque and negative sign (-) mark defined like this to satisfy condition: this condition be the symbol result of product of hand of rotation and torque will become rotation energy (namely power) symbol.
In geared neutral, first planet gear cluster 22 is not used in transmission power.Especially, power-transfer clutch 30 is separated, and makes the torque of pinion carrier C will be zero (0), and therefore according to equation as above (c1) and equation (c2), the torque of sun wheel S and gear ring R also will be zero (0).
Next the starting describing driving engine 12 is controlled.
Fig. 3 (a) and Fig. 3 (b) shows the operation of power drive fire an engine 12.Fig. 3 (a) shows the power transmission path when driving engine 12 is started.Fig. 3 (b) is the alignment chart of the operation of the distributing means for power supply 20 illustrated along with driving engine 12 speed.
When needs fire an engine 12, controller 40 (not shown) engaging clutch 30 is so that by the torque of the pinion carrier C from first planet gear cluster 22 (namely, torque from starting shaft) the S. A. 12a of driving engine 12 is sent to by power-transfer clutch 30 and unilateral bearing 32, thus realize the initial rotation of the S. A. 12a of driving engine 12.The S. A. 12a of driving engine 12 is driven by the rotation of the pinion carrier C of first planet gear cluster 22 or is rotated.When the rotating speed of the S. A. 12a of driving engine 12 is increased to given value, controller 40 starts the burning controlling fuel in driving engine 12.Starting stage when fuel takes fire, after driving engine 12 rotating crank, the torque on S. A. 12a raises fast, and the rotating speed of S. A. 12a is increased sharply.But at this moment the rotating speed of the revolution ratio pinion carrier C of S. A. 12a is high, makes torque not be transmitted to pinion carrier C, thus in the burning starting stage of driving engine 12, the pulsation of torque is not transmitted to distributing means for power supply 20.
The rotating speed of the pinion carrier C of first planet gear cluster 22 can be adjusted to pole low value or be entirely zero (0) by the hybrid power system of this embodiment.Especially, first planet gear cluster 22 is so connected, driving engine 12 can be exported to make just (+) of the pinion carrier C from first planet gear cluster 22 to be rotated when power-transfer clutch 30 engages, some tumblers in power distribution tumbler except the pinion carrier C of first planet gear cluster 22 (namely, be 2 in this embodiment) output rotate can be opposite each other on symbol, thus make the pinion carrier C of first planet gear cluster 22 to be placed in geared neutral.With reference to figure 3 (c), the sun wheel S of first planet gear cluster 22 and the output of gear ring R rotate can (namely, power) opposite each other on symbol, and be coupled to each other by loop mechanical path, thus make the pinion carrier C of first planet gear cluster 22 be arranged on geared neutral about such identical mode described by the second compound planet gear 24 above, and do not need two rotating machines (such as, dynamotor): one rotates energy for receiving the output generated by gear ring R, and another is for rotating can input to sun wheel S by this output.Similar to the second compound planet gear 24, loop mechanical path needs not be fully mechanical continuous print.
After the starting completing driving engine 12, controller 40 makes power-transfer clutch 30 be separated.When needing at short notice after driving engine 12 is stopped to reset driving engine 12, may cause before the rotating speed of the S. A. 12a of driving engine 12 is down to zero (0), driving engine 12 being subsequently restarted.In this case, reach consistent to make the rotating speed of sun wheel S with the rotating speed of the S. A. 12a of driving engine 12 by regulating the rotating speed of dynamotor 10 and/or the transmitting ratio of CVT36, the rotating speed simultaneously keeping flower wheel 14 is desired value, thus realizes resetting of driving engine 12.
Fig. 4 (a) and Fig. 4 (b) represent at driving engine 12 by the operation of power drive after starting.Fig. 4 (a) show from driving engine 12 export torque by the power transmission path transmitted.Fig. 4 (b) illustrates the alignment chart that the distributing means for power supply 20 along with driving engine 12 speed operates.Power-transfer clutch 30 is separated with the connection between the pinion carrier C disconnecting unilateral bearing 32 and first planet gear cluster 22.
After driving engine 12 is started, (namely the rotating speed of the S. A. 12a of driving engine 12 reaches the rotating speed of first planet gear cluster 22 and the sun wheel S both the second compound planet gear 24, the rotating speed of power drive shaft), thus send the torque of driving engine 12 to distributing means for power supply 20.After the torque from driving engine 12 is supplied to distributing means for power supply 20, dynamotor 10 can be operating as electrical generator or turn off inverter 42 so that dynamotor 10 is placed in non-load operation by controller 40.
Obviously known by describing above, the hybrid power system of this embodiment can start explosive motor 12 during providing the vehicle operating of power with dynamotor 10, in other words, during dynamotor 10 operates, do not need to adopt the representative engine starter with electrical motor, just can fire an engine 12.For fire an engine 12 tumbler (namely, the pinion carrier C of first planet gear cluster 22) and the tumbler that is sent to of the torque of driving engine 12 is (namely, first planet gear cluster 22 and the sun wheel S both the second compound planet gear 24) be designed to separate, in other words, be configured to independent of one another, thus make the rotating speed being provided to the tumbler of the torque of driving engine 12 after driving engine 12 starts to increase rapidly.The time that this just causes driving engine 12 to run within the scope of valid function increases.
The structure of the hybrid power system of this embodiment has the following advantages.
1) there is the power drive of the first power transmission control mechanism for setting up or interrupting at the first tumbler as distributing means for power supply 20 parts (namely, the pinion carrier C of first planet gear cluster 22) and the S. A. 12a of driving engine 12 between power transmission, and the second power transmission control mechanism is for setting up or interrupting as the power transmission between second tumbler (that is, the sun wheel S both first planet gear cluster 22 and the second compound planet gear 24) of distributing means for power supply 20 parts and the S. A. 12a of driving engine 12.Especially, power drive work to guarantee the starting of driving engine 12 during the vehicle operating adopting dynamotor 10, and makes the speed of driving engine 12 reach effective velocity scope fast.
2) (namely the first power transmission control mechanism has one-way driving mechanism, unilateral bearing 32), when the first tumbler (namely, the pinion carrier C of first planet gear cluster 22) rotating speed relative to the rotating speed non-negative of engine rotation axle 12a or when being not less than zero (0), this one-way driving mechanism work is to allow power or torque to be transferred into driving engine 12 from distributing means for power supply 20.This obviates the torque pulsation to distributing means for power supply 20 increased along with the rising from fuel initial combustion in driving engine 12 combustion chamber, therefore avoid the less desirable swing of car body.
3) (namely the first power transmission control mechanism also comprises electronic controlled power transmission interrupter, power-transfer clutch 30), (namely it except interrupting the first tumbler, the pinion carrier C of first planet gear cluster 22) and unilateral bearing 32 between power transmit outside, also interrupt the power transmission between this first tumbler and S. A. 12a of driving engine 12.Avoiding problems and just power or torque are sent to S. A. 12a from the first tumbler at driving engine 12 by prestart, thus decrease energy ezpenditure.
4) controller 40 makes power-transfer clutch 30 be separated after driving engine 12 starts, thus makes the electric energy being supplied to power-transfer clutch 30 be down to minimum.
5) (namely the second power transmission control mechanism has one-way driving mechanism, unilateral bearing 34), this one-way driving mechanism for the rotating speed at engine rotation axle 12a relative to the second tumbler (namely, first planet gear cluster 22 and the sun wheel S both the second compound planet gear 24) rotating speed non-negative or when being not less than zero, allow power or torque to be sent to driving engine 12 from dynamotor 10.Therefore, when the rotating speed of driving engine 12 S. A. 12a is equal with the rotating speed of sun wheel S, the torque produced by driving engine 12 is transmitted to sun wheel S.The use of the second power transmission control mechanism makes the starting increased from the torque of driving engine 12 to sun wheel S control to become simple, and when not needing the power of driving engine 12, also allow the rotating speed of driving engine 12 to be controlled in rotating speed lower than sun wheel S so that driving engine 12 is placed in non-load operation.
6) initial moment is added on driving engine 12 at the pinion carrier C place of first planet gear cluster 22, the rotating speed of the pinion carrier C of first planet gear cluster 22 is by the rotating speed of sun wheel S selected less than or equal to both first planet gear cluster 22 and the second compound planet gear 24, thus after driving engine 12 is started, make driving engine 12 promptly enter effective opereating specification immediately.
7) (namely distributing means for power supply 20 has three or more tumblers, three tumblers S, C and the R of first planet gear cluster 22 in this enforcement), it is designed to have in alignment chart the speed be positioned on straight line, and use in this three or more tumbler one of the middle speed had in alignment chart as tumbler initial moment being sent to driving engine 12, thus caused the velocity contrast between this tumbler and driving engine 12 S. A. 12a with reduction at driving engine 12 by prestart.
8) have at the right-hand member value of alignment chart medium velocity and left end value two (namely in tumbler, the tumbler of the second compound planet gear 24 in this embodiment) be mechanically connected to dynamotor 10, thus dynamotor 10 can be running within the scope of the valid function of increase.
9) described above, the tumbler had respectively in second compound planet gear 24 in the low order end value of alignment chart medium velocity and two tumblers of high order end value is mechanically connected with dynamotor 10 by CVT 36, thus make these two tumblers in tumbler by separate control in speed, just as application two dynamotors are the same with the situation that these two tumblers are connected respectively.When employing two this dynamotors, when electric energy is provided to a dynamotor as electric motor operated, this structure can also reduce the electric loss of energy that another dynamotor as generator operation produces.
10) there are four tumbler groups of different speed in alignment chart (namely respectively, (a) first planet gear cluster 22 in a first embodiment and the sun wheel S both the 2 24, the pinion carrier C of (b) first planet gear cluster 22, the gear ring R of (c) first planet gear cluster 22 and the pinion carrier of the second compound planet gear 24, and (d) the second gear ring R of compound planet gear 24) in except for all the other tumblers except initial moment being added to that tumbler that driving engine 12 is used for starting (namely, the gear ring R of first planet the gear cluster 22 and pinion carrier C of the second compound planet gear 24) be mechanically connected with flower wheel 14, thus make flower wheel 14 rotate in normal direction or reverse directions and stop the rotation to be more prone to.Rotating speed for the tumbler by initial moment supply engine 12 can be set up independent of the rotating speed of flower wheel 14.
11) distributing means for power supply 20 is designed to two in three of first planet gear cluster 22 tumblers to be mechanically connected with two in three tumblers of the second compound planet gear 24 respectively, thus make four of distributing means for power supply 20 groups in alignment chart, have the speed linearly arranged, as shown in Fig. 2 (b).
Fig. 5 illustrates hybrid power system according to a second embodiment of the present invention.Adopt the Reference numeral identical with Fig. 1 to indicate identical parts, will the detailed explanation to it be omitted herein.
The hybrid power system of this embodiment is designed to change between the tumbler of the distributing means for power supply 20 of vehicle flower wheel 14 mechanical connection.Especially, as knowing in Figure 5 and illustrating, this hybrid power system comprises electric control clutch 50, electric control clutch 50 is used as conv or finder, with the pinion carrier C of the gear ring R and the second compound planet gear 24 that select (a) first planet gear cluster 22 this to combination, or the gear ring R of selection (b) second compound planet gear 24, be connected with flower wheel 14.
The use of power-transfer clutch 50 makes dynamotor 10 or driving engine 12 can run within the scope of the valid function increased.Such as, during the operation of dynamotor 10, the rotating speed increasing the flower wheel 14 be connected with the pinion carrier C of the second compound planet gear 24 with the gear ring R of first planet gear cluster 22 needs the rotating speed of dynamotor 10 is increased on the rotating speed of flower wheel 14.The rotating speed increasing dynamotor 10, until its invalid operation scope, increases causing the energy consumed in hybrid power system.In order to alleviate the problems referred to above, when entering invalid operation scope, flower wheel 14 is mechanically connected to the gear ring R of the second compound planet gear 24 by controller 40, thus eliminates the needs be increased to by dynamotor 10 rotating speed on flower wheel 14 rotating speed.Equally, when flower wheel 14 is driven by explosive motor 12, controller 40 can work to change between the tumbler of distributing means for power supply 20 that be mechanically connected at flower wheel 14 in the scope that the control by means of only CVT 36 is difficult to make driving engine 12 effectively to run, thus driving engine 12 maintenance is operated within the scope of valid function.
By the second pattern that the gear ring R that the first mode that flower wheel 14 and the gear ring R of first planet the gear cluster 22 and pinion carrier C of the second compound planet gear 24 couple converts flower wheel 14 and the second compound planet gear 24 to couples, realized by following operation: operated clutch 50 interrupts the torque transmission from the gear ring R of first planet the gear cluster 22 and pinion carrier C of the second compound planet gear 24 to flower wheel 14, the rotating speed of dynamotor 10 is made to reach the rotating speed of flower wheel 14, and operated clutch 50 is with the mechanical connection of the gear ring R to flower wheel 14 that set up the second compound planet gear 24.On the contrary, the first mode becoming flower wheel 14 to be connected with the pinion carrier C of the second compound planet gear 24 with the gear ring R of first planet gear cluster 22 the second patten transformation that flower wheel 14 is connected with the gear ring R of the second compound planet gear 24, then realized by following operation: operated clutch 50 interrupts the torque transmission from the gear ring R of the second compound planet gear 24 to flower wheel 14, the operation controlling dynamotor 10 makes the rotating speed of the pinion carrier C of the gear ring R of first planet gear cluster 22 and the second compound planet gear 24 reach the rotating speed of flower wheel 14, and operated clutch 50 sets up the mechanical connection of the gear ring R of first planet the gear cluster 22 and pinion carrier C of the second compound planet gear 24 to flower wheel 14.
The structure of the hybrid power system of this embodiment is except having advantage as above (1) to except (11), and also tool has the following advantages.
12) provide power-transfer clutch 50 to select in distributing means for power supply 20 tumbler be mechanically connected with flower wheel 14 using the function of speed needed for flower wheel 14 one or two, to keep dynamotor 10 or driving engine 12 to operate within the scope of the valid function of preliminary election.
Fig. 6 (a) and Fig. 6 (b) shows hybrid power system according to a third embodiment of the present invention.Adopt the Reference numeral identical with Fig. 1 to indicate identical parts, will the detailed explanation to it be omitted herein.
Distributing means for power supply 20 has first planet gear cluster 22, and first planet gear cluster 22 is mechanically connected at the gear ring R of its pinion carrier C place and the second compound planet gear 24.Pinion carrier C and gear ring R is used as the engine starting tumbler of distributing means for power supply 20, thinks that driving engine 12 provides initial moment.The gear ring R of first planet gear cluster 22 and the pinion carrier C machinery of the second compound planet gear 24 couple, and both is mechanically connected with flower wheel 14 again.For convenience of explanation, flower wheel 14 is eliminated in Fig. 6 (a) and Fig. 6 (b).Alternatively, the path be mechanically connected with flower wheel 14 represents with " outer defeated path ".The sun wheel S of first planet gear cluster 22 is used as the tumbler be connected with power drive shaft, and is used to transmit the torque produced by driving engine 12.The sun wheel S of first planet gear cluster 22 is also mechanically connected to dynamotor 10 by CVT 36.Dynamotor 10 is also mechanically connected with the sun wheel S of the second compound planet gear 24.
The structure of the hybrid power system of this embodiment has same advantage as above (1) substantially to (11).
Fig. 7 (a) and 7 (b) show hybrid power system according to a fourth embodiment of the present invention.Adopt the Reference numeral identical with Fig. 1 to indicate identical parts, will the detailed explanation to it be omitted herein.
Distributing means for power supply 20 has first planet gear cluster 22, and first planet gear cluster 22 is mechanically connected at the sun wheel S of its pinion carrier C and the second compound planet gear 24.This pinion carrier C and sun wheel S is used as the engine starting tumbler of distributing means for power supply 20, thinks that driving engine 12 provides initial moment.The gear ring R of first planet gear cluster 22 and the pinion carrier C machinery of the second compound planet gear 24 couple, and both is also mechanically connected with flower wheel 14.For convenience of explanation, flower wheel 14 is eliminated in Fig. 7 (a) and Fig. 7 (b).As Fig. 6 (a) is the same with Fig. 6 (b), the path be mechanically connected with flower wheel 14 represents with " outer defeated path ".The sun wheel S of first planet gear cluster 22 is used as the tumbler be connected with power drive shaft, and is used to transmit the torque produced by driving engine 12.The sun wheel S of first planet gear cluster 22 is also mechanically connected to dynamotor 10 by CVT 36.Dynamotor 10 is also mechanically connected with the gear ring R of the second compound planet gear 24.
The structure of the hybrid power system of this embodiment has same advantage as above (1) substantially to (11).
Fig. 8 (a) to Fig. 8 (c) shows hybrid power system according to a fifth embodiment of the present invention.Adopt the Reference numeral identical with Fig. 1 to indicate identical parts, will the detailed explanation to it be omitted herein.
Distributing means for power supply 20 has first planet gear cluster 22, and first planet gear cluster 22 is mechanically connected at the sun wheel S of its pinion carrier C place and the second compound planet gear 24.This pinion carrier C and sun wheel S is used as the engine starting tumbler of distributing means for power supply 20, thinks that driving engine 12 provides initial moment.The sun wheel S of first planet gear cluster 22 and the pinion carrier C machinery of the second compound planet gear 24 couple, and both is mechanically connected with flower wheel 14 again.For convenience of explanation, flower wheel 14 is eliminated in Fig. 8 (a) to Fig. 8 (c).As Fig. 7 (a) is the same with Fig. 7 (b), the path be mechanically connected with flower wheel 14 represents with " outer defeated path ".The gear ring R of the second compound planet gear 24 is used as the tumbler be connected with power drive shaft, and is used to transmit the torque produced by driving engine 12.The gear ring R of the second compound planet gear 24 is also mechanically connected to dynamotor 10 by CVT 36.Dynamotor 10 is also mechanically connected at the gear ring R of its S. A. 10a place and first planet gear cluster 22.
Fig. 8 (b) and 8 (c) are schematic diagram, it illustrates the tumbler of distributing means for power supply 20 modification connection and in driving engine 12, power transmission path between flower wheel 14 and dynamotor 10.
The structure of the hybrid power system of this embodiment has same advantage as above (1) substantially to (11).
Fig. 9 (a) and Fig. 9 (b) shows hybrid power system according to a sixth embodiment of the present invention.Adopt the Reference numeral identical with Fig. 1 to indicate identical parts, will the detailed explanation to it be omitted herein.
Distributing means for power supply 20 has first planet gear cluster 22, and first planet gear cluster 22 is mechanically connected at the gear ring R of its gear ring R place and the second compound planet gear 24.First planet gear cluster 22 and the gear ring R both the second compound planet gear 24 are also mechanically connected with the second dynamotor 10B, and are used as the tumbler of the torque receiving driving engine 12 generation transmitted by unilateral bearing 34 in distributing means for power supply 20.The sun wheel S of first planet gear cluster 22 and the pinion carrier C machinery of the second compound planet gear 24 couple, and both is mechanically connected with flower wheel 14 again.For convenience of explanation, flower wheel 14 is eliminated in Fig. 9 (a) and Fig. 9 (b).As Fig. 8 (a) is the same with Fig. 8 (b), the path be mechanically connected with flower wheel 14 represents with " outer defeated path ".Sun wheel S and the first dynamotor 10A machinery of the second compound planet gear 24 couple.The pinion carrier C of first planet gear cluster 22 is used as the engine starting tumbler of distributing means for power supply 20, and provides initial moment for driving engine 12.
Fig. 9 (b) is for showing the schematic diagram of the power transmission path of fire an engine 12.For convenience of explanation, Fig. 9 (b) eliminates unilateral bearing 32 and 34.
Dynamotor 10A and 10B always need not be used as dynamotor.At least any one of being somebody's turn to do in both can be used as dynamotor.Such as, be designed to only as in generator operation situation at the first dynamotor 10A, the second dynamotor 10B that the electric energy produced by the first dynamotor 10A is used as electrical motor consumes to drive vehicle.Only be used as the first dynamotor 10A of electrical generator when needs abrupt deceleration vehicle also for providing braking effect, and be also used to the rotating speed of the tumbler of control distributing means for power supply 20.
The structure of the hybrid power system of this embodiment has same advantage as above (1) to (8) and (10) substantially to (11).
Figure 10 (a) and 10 (b) show hybrid power system according to a seventh embodiment of the present invention.Adopt the Reference numeral identical with Fig. 1 to indicate identical parts, will the detailed explanation to it be omitted herein.
Distributing means for power supply 20 has first planet gear cluster 22, and first planet gear cluster 22 is mechanically connected at the gear ring R of its gear ring R place and the second compound planet gear 24.First planet gear cluster 22 and the gear ring R both the second compound planet gear 24 are also mechanically connected with the second dynamotor 10B.The gear ring R of first planet gear cluster 22 and the pinion carrier C machinery of the second compound planet gear 24 couple, and both is also mechanically connected with flower wheel 14.For convenience of explanation, flower wheel 14 is eliminated in Figure 10 (a) and Figure 10 (b).As Fig. 9 (a) is the same with Fig. 9 (b), the path be mechanically connected with flower wheel 14 represents with " outer defeated path ".Gear ring R and the first dynamotor 10A machinery of the second compound planet gear 24 couple, and are used as the tumbler receiving the torque of the driving engine 12 transmitted by unilateral bearing 34 in distributing means for power supply 20.The pinion carrier C of first planet gear cluster 22 is used as engine starting tumbler, to provide initial moment for driving engine 12.
When needs fire an engine 12, the tumbler of distributing means for power supply 20 (namely, the pinion carrier C of first planet gear cluster 22) rotating speed be used to provide initial moment to driving engine 12, and the rotating speed of the tumbler be mechanically connected with the first dynamotor 10A is configured on symbol identical in alignment Figure 10 (b).After driving engine 12 is started, the torque of driving engine 12 is transmitted to the tumbler of distributing means for power supply 20 (that is, the gear ring R of the second compound planet gear 24).
Figure 11 (a) and Figure 11 (b) is arranged at hybrid power system the schematic diagram being represented power transmission path front engine, front drives and drives in (FR) vehicle with front engine rear wheel in (FF) vehicle when driving engine 12 starts respectively.For convenience of explanation, unilateral bearing 32 and 34 is omitted.
The structure of the hybrid power system of this embodiment has same advantage as above (1) to (8) and (10) substantially to (11).
The modification of the above-mentioned first to the 7th embodiment will be described in detail in detail below.
The hybrid power system of above-described embodiment has the power-transfer clutch 30 be arranged between unilateral bearing 32 and distributing means for power supply 20, the torque that power-transfer clutch 30 selectively sets up the S. A. 12a from distributing means for power supply 20 to driving engine 12 transmits with fire an engine 12, but as shown in Figure 12 (a), alternatively, power-transfer clutch 30 can be arranged between the S. A. 12a of unilateral bearing 32 and driving engine 12.This alternative applications shown in Figure 12 (a) is in the structure of the first embodiment.
For to disconnect or between closed distributing means for power supply 20 and driving engine 12, the power-transfer clutch 30 of power transmission path often opens type, but it also can be Closed type.Like this, even if from the angle of the power being reduced by power-transfer clutch 30 consumption after driving engine 12 starts, power-transfer clutch 20 is preferably kept to engage.
Each structure of the first to the 7th embodiment can omit power-transfer clutch 30.Even can obtain advantage as above (1) when not having power-transfer clutch 30, (2) and (4) are to (11).
When distributing means for power supply 20 starting shaft (namely, the power input side of unilateral bearing 32) rotating speed be more than or equal to the S. A. 12a of driving engine 12 (namely, the Power output side of unilateral bearing 32) rotating speed time, unilateral bearing 32 is arranged on to set up to the power transmission of driving engine 12 between distributing means for power supply 20 and driving engine 12, but the starting shaft that S. A. 12a also can be used to follow distributing means for power supply 20 rotates and tool is with or without free-wheel clutch or other similar type of slip.
The unilateral bearing 32 that the starting shaft for setting up or interrupt distributing means for power supply 20 to the torque of the S. A. 12a of driving engine 12 transmits can be omitted.In other words, between S. A. 12a and the starting shaft of distributing means for power supply 20, can power-transfer clutch 30 be only set.After driving engine 12 is started, controller 40 makes power-transfer clutch 30 be separated to interrupt the connection between driving engine 12 and distributing means for power supply 20, make speed than distributing means for power supply 20 starting shaft (namely, the pinion carrier C of first planet gear cluster 22) speed wants the tumbler (that is, sun wheel S) of high distributing means for power supply 20 to be connected to driving engine 12.This alternative applications shown in Figure 12 (b) is in the structure of the first embodiment.
Unilateral bearing 34 is arranged between distributing means for power supply 20 and driving engine 12, thus driving engine 12 S. A. 12a (namely, the power input side of unilateral bearing 34) rotating speed be more than or equal to the power drive shaft of distributing means for power supply 20 (namely, the Power output side of unilateral bearing 334) rotating speed time, set up the power transmission from the power drive shaft of driving engine 12 to distributing means for power supply 20, but also can use the free-wheel clutch that allows power drive shaft rotate with driving engine 12 S. A. 12a or other allied equipment (have slide or do not slide all can).
Unilateral bearing 34 can be replaced by power-transfer clutch similar with power-transfer clutch 30 in structure.Like this, when the rotating speed of driving engine 12 equals the rotating speed of the power drive shaft of distributing means for power supply 20, controller 40 engaging clutch is to guarantee the stability that the S. A. 12a of driving engine 12 is connected with power drive shaft.This alternative applications shown in Figure 12 (c) is in the structure of the first embodiment.Especially, power-transfer clutch 31 is arranged between the S. A. 12a of driving engine 12 and the power drive shaft of distributing means for power supply 20 to set up or to interrupt mechanical connection between the two.In the illustrated case, unilateral bearing 32 is omitted.
The hybrid power system of the first to the 5th embodiment all has power-transfer clutch 38, it is arranged between CVT 36 and distributing means for power supply 20 to interrupt dynamotor 10 by the mechanical connection between CVT 36 and distributing means for power supply 20, but power-transfer clutch 38 can be arranged between dynamotor 10 and CVT36 as shown in Figure 13 (a).Power-transfer clutch 38 also can be arranged between dynamotor 10 and distributing means for power supply 20 to replaced property as Suo Shi Figure 13 (b).
In a first embodiment, the power drive shaft of distributing means for power supply 20 is the axles connecting first planet gear cluster 22 and the sun wheel S both the second compound planet gear 24, but as shown in Figure 14 (a), alternatively, also can be the axle be connected with the gear ring R of the second compound planet gear 24.As shown in Figure 14 (b), alternatively, the axle connecting the gear ring R of first planet gear cluster 22 and the pinion carrier C of the second compound planet gear 24 can be used as power drive shaft.Like this, as in the first embodiment or as shown in Figure 14 (a), wherein the S. A. 12a of driving engine 12 is mechanically connected to distributing means for power supply 20 without the need to CVT 36, and being mechanically connected to distributing means for power supply 20 by CVT36, the speed of each tumbler of distributing means for power supply 20 can only control with driving engine 12.When dynamotor 10 stops, the rotating speed of flower wheel 14 is adjusted to expectation value with regard to allowing controller 40 by this.Equally, the power drive shaft of each in the second to the 5th embodiment distributing means for power supply 20 can be the axle being mechanically connected to the S. A. 10a of dynamotor 10 without the need to CVT 36.
The hybrid power system of above-described embodiment can be designed to start vehicle with driving engine 12 instead of with dynamotor 10.
The structure with the second embodiment of power-transfer clutch 50 can be combined with structure each in the 3rd to the 7th embodiment.Like this in alignment chart, the rotative speed of the tumbler be mechanically connected with flower wheel 14 in distributing means for power supply 20 does not need always identical with flower wheel 14 on symbol.Use for changing the direction control mechanism of this tumbler hand of rotation allows the power transmission path being connected to flower wheel 14 from distributing means for power supply 20 to be optionally converted.
The structurally variable type of second embodiment of Fig. 5 becomes as Figure 15 (a) or 15 (b).
Especially, the power-transfer clutch 50 in Figure 15 (a) is for selecting one to be mechanically connected with flower wheel 14 with this centering of sun wheel of both (b) first planet gear cluster 22 and the second compound planet gear 24 this pair from the gear ring R of (a) first planet gear cluster 22 and pinion carrier C of the second compound planet gear 24.Power-transfer clutch 50 in Figure 15 (b) for selecting one to be mechanically connected with flower wheel 14 from the gear ring R and the pinion carrier C this pair of the second compound planet gear 24 and S. A. 12a of (b) explosive motor 12 of (a) first planet gear cluster 22.In other words, the power-transfer clutch 50 in Figure 15 (b) is changed in the connection and being connected directly between driving engine 12 by flower wheel 14 of the gear ring R of flower wheel 14 to first planet the gear cluster 22 and pinion carrier C of the second compound planet gear 24.Notice, counter gear (not shown) actual installation is between power-transfer clutch 50 and the rotation 12a of driving engine 12.
The same with the structure of second embodiment of Fig. 5, realized in the structure of Figure 15 (a) by the connection disconnecting distributing means for power supply 14 and flower wheel 14 temporarily and conversion between the tumbler of distributing means for power supply 20 that flower wheel 14 is mechanically connected.On the contrary, the structure of Figure 15 (b) has while the tumbler of distributing means for power supply 20 is converted, and power is transferred into the advantage of flower wheel 14 serially.Figure 16 (a) illustrates the conversion operations order performed by controller 40 (see Fig. 1) to 16 (c), namely in the structure of Figure 15 (a), how the gear ring R of first planet the gear cluster 22 and pinion carrier C of the second compound planet gear 24 and the connection of flower wheel 14 are converted to the sun wheel S of both first planet gear cluster 22 and the second compound planet gear 24 and the connection of flower wheel 14.Figure 16 (a) represents that the gear ring R of first planet the gear cluster 22 and pinion carrier C of the second compound planet gear 24 is coupled to flower wheel 14, and the speed increasing driving engine 12 is supplied to the energy of flower wheel 14 from driving engine 12 with increase.But, when needing to supply other energy to flower wheel 14, the further increase of driving engine 12 speed reduces causing supplying energy to the efficiency of flower wheel 14, and controller 40 makes driving engine 12 speed reduce the rotating speed approaching driven 14 as shown in Figure 16 (b).The rotating speed of flower wheel 14 is kept by dynamotor 10.When the speed of driving engine 12 reaches the speed of flower wheel 14, controller 40 control clutch 50 is to set up the mechanical connection of S. A. 12a to flower wheel 14 of driving engine 12 by sun wheel S.As shown in Figure 16 (c), the speed of driving engine 12 is consistent with the speed of the sun wheel S of both first planet gear cluster 22 and the second compound planet gear 24, two such that driving engine 12 and CVT 36 set in alignment chart in four friction speeds.In the situation of the second compound planet gear 24, the speed of sun wheel S and gear ring R is set.Under this pattern, dynamotor 10 does not need produce power thus can be used as electrical generator.
Realize by following three kinds of modes in the conversion of Figure 15 (a) medium power distribution device 20 by the mechanical connection of power-transfer clutch 50 to flower wheel 14: first (a) wherein first planet gear cluster 22 and the sun wheel S both the second compound planet gear 24 be connected to flower wheel 14 to form flower wheel 14 two mechanical connections to the combination of the gear ring R of (1) first planet gear cluster 22 and pinion carrier C of the second compound planet gear 24 and the combination to the sun wheel S of both (2) first planet gear cluster 22 and the second compound planet gear 24 by power-transfer clutch 50, and flower wheel 14 is disconnected to the connection of the combination of the pinion carrier C of the gear ring R of (1) first planet gear cluster 22 and the second compound planet gear 24 by power-transfer clutch 50; B () wherein power-transfer clutch 50 is controlled to the mechanical connection simultaneously flower wheel 14 being converted to the combination of the sun wheel S of both (2) first planet gear cluster 22 and the second compound planet gear 24 to the mechanical connection of the combination of the pinion carrier C of the gear ring R of (1) first planet gear cluster 22 and the second compound planet gear 24; And (c) wherein the gear ring R of first planet gear cluster 22 first disconnect to make power-transfer clutch 50 be separated completely by power-transfer clutch 50 flower wheel 14 with the pinion carrier C of the second compound planet gear 24, and flower wheel 14 is realized to the mechanical connection of the combination of the sun wheel S of both first planet gear cluster 22 and the second compound planet gear 24 by power-transfer clutch 50.First method (a) is most preferred, this is because achieve and the conversion of the mechanical connection of flower wheel 14 and not to the loss that any torque of flower wheel 14 transmits.
The structure of the hybrid power system of Figure 15 (a) or Figure 15 (b) allows vehicle to be in case of emergency pulled.Especially, power-transfer clutch 50 is separated with the connection disconnecting flower wheel 14 and distributing means for power supply 20 completely, thus flower wheel 14 is rotated freely.Alternatively, power-transfer clutch 38 is separated with the connection of the gear ring R disconnecting sun wheel S and the second compound planet gear 24, thus flower wheel 14 is rotated freely.
The hybrid power system of the second embodiment or above-mentioned modification is designed to change or change the tumbler be mechanically connected with flower wheel 14 in distributing means for power supply 40, but alternatively, can be designed to change the tumbler be mechanically connected with dynamotor 10 in distributing means for power supply 40.
As long as (namely any two machineries in three tumblers (i.e. sun wheel S, pinion carrier C and gear ring R) of first planet gear cluster 22 are coupled to three tumblers of the second compound planet gear 24, sun wheel S, pinion carrier C and gear ring R) in any two time, the first planet gear cluster 22 of distributing means for power supply 20 is optionally designed to have the structure different from above-described embodiment with the second compound planet gear 24.Figure 17 (a) to Figure 17 (j) and Figure 18 (a) to Figure 18 (j) is the alignment chart of the possible modification representing first planet gear cluster 22 and the second compound planet gear 24.Each alignment chart illustrates the annexation between first planet gear cluster 22 and total 6 tumblers of the second compound planet gear 24, and in four friction speeds of alignment chart lined inside and the relation between first planet gear cluster 22 and 6 tumblers of the second compound planet gear 24.It is to be noted that cause conveniently, the number of teeth of sun wheel S is schematic with the ratio of the number of teeth of gear ring R.
In each alignment chart, sun wheel S, the pinion carrier C of first planet gear cluster 22 and gear ring R are illustrated in upside.Such as, in Figure 17 (b) and Figure 17 (c), first planet gear cluster 22 and the gear ring R both the second compound planet gear 24 are mechanically connected each other.First planet gear cluster 22 and the pinion carrier C both the second compound planet gear 24 are mechanically connected each other.In the ratio of number of teeth of the number of teeth of the number of teeth of the number of teeth of sun wheel S and the gear ring R of first planet gear cluster 22 and the gear ring R of the second compound planet gear 24, the greater is that the horizontal position of vertical curve by representing sun wheel S represents.By being connected from the left side in alignment chart by the tumbler of dynamotor 10 with the distributing means for power supply 20 being positioned at right-hand member or left end speed in alignment chart respectively, and the starting shaft of the tumbler with driving engine 12 with middling speed is connected with flower wheel 14, same advantage as in the first embodiment can be realized.The tumbler being mechanically connected to dynamotor 10 without the need to CVT 36 is not restricted to the tumbler being arranged in alignment chart right-hand member speed place, can be the tumbler being arranged in alignment chart left end yet.Figure 19 (a), Figure 19 (b) and Figure 19 (c) show the modification of the first embodiment, wherein dynamotor 10 be mechanically connected to the distributing means for power supply 20 being arranged in alignment chart left end speed place tumbler and without the need to CVT36.In the example of Figure 19 (a) and Figure 19 (b), unilateral bearing 32 is contrary with power-transfer clutch 30 position.Unilateral bearing 32 is eliminated in the example of Figure 19 (c).The tumbler be connected with flower wheel 14 with the starting shaft of driving engine 12 does not need always have the middling speed in alignment chart.When the tumbler in distributing means for power supply 20 except machinery is coupled to the tumbler of starting shaft exports different on the symbol of rotation energy at it, the speed of starting shaft can be arranged on pole low value or be entirely zero (0).Guarantee and initial moment is added to driving engine 12.When the tumbler in distributing means for power supply 20 except the tumbler that machinery is coupled to flower wheel 14 is when exporting different on the symbol rotating energy, the speed of flower wheel 14 can be arranged on the occasion of, negative value or zero (0), and the rotation of dynamotor 10 is maintained on an opposite sense simultaneously.
Alternatively, distributing means for power supply 20 can be designed to have single compound planet gear, one namely in first planet gear cluster 22 and the second compound planet gear 24.Such as, distributing means for power supply 20 can have single compound planet gear and two dynamotors: the first and second dynamotors.The sun wheel of the first dynamotor and compound planet gear is mechanically connected.The gear ring of the second dynamotor and compound planet gear is mechanically connected.The pinion carrier of compound planet gear and the starting shaft of distributing means for power supply 20 are mechanically connected.Power drive shaft is connected with the gear ring of compound planet gear.This makes driving engine 12 be started.Distributing means for power supply 10 also can be designed to have following structure, i.e. the structure that the first to the 3rd open source literature related in the background technology part of the application is instructed, instead of has the compound planet gear of sun wheel, pinion carrier and gear ring.By selecting the tumbler of the distributing means for power supply 20 being connected to starting shaft and power drive shaft, same advantage (6) such as in the first embodiment can be obtained, make the speed of starting shaft can less than or equal to the speed of power drive shaft.Distributing means for power supply 20 can be so designed, and is connected to the speed of the tumbler of dynamotor 10 to make the speed of the tumbler being connected to starting shaft depend on.This structure ensure that in the particularity of control linkage in the speed of the tumbler of starting shaft (that is, the starting shaft of driving engine 12).Distributing means for power supply 20 can be so designed, and is connected to the speed of the tumbler of dynamotor 10 and driving engine 12 to make the speed of the tumbler being connected to flower wheel 14 depend on.This structure ensure that in the particularity of control linkage in the speed of the tumbler of flower wheel 14.
In the above example, dynamotor 10 does not need always to be mechanically connected to the tumbler of the distributing means for power supply 20 being arranged in alignment chart right-hand member and left end speed place.Such as, dynamotor 10 can be mechanically connected to the tumbler in distributing means for power supply 20 except being arranged in those tumblers at alignment chart right-hand member or left end speed place.Like this, connect when this tumbler speed being positioned at one of right-hand member or left end place in setting alignment chart, then those tumblers can be connected with power drive shaft.Figure 20 (a) to Figure 22 (b) shows the modification of distributing means for power supply 20, and these modification are different from any one that be mechanically connected with dynamotor 10 and/or CVT 36 in the first embodiment.These modification can with in the second to the 5th embodiment or Figure 17 (a) be combined to the hybrid power system in Figure 18 (j).However, it is appreciated that, as shown in Figure 20 (a) to Figure 20 (d), the tumbler being mechanically connected to dynamotor 10 or CVT36 in distributing means for power supply 20 should be different from the tumbler being mechanically connected to flower wheel 14, makes the speed of the dynamotor 10 when the speed of flower wheel 14 is zero (0) can be adjusted to non-zero (0) value.Therefore, when the speed of flower wheel 14 is zero (0), driving engine 12 can be started with operational vehicle.In addition, when flower wheel 14 stops, dynamotor 10 can be used to the annex of drive installation on vehicle, such as, and air-conditioning compressor or brake pump in car.
Distributing means for power supply 20 also can be designed to have the rotative speed that is arranged in one of alignment chart right-hand member or left end place and the tumbler be mechanically connected with flower wheel 14.It is more accurate that the transmission system (such as, change-speed box) be arranged between tumbler and flower wheel 14 causes carrying out control aspect to flower wheel 14 speed.
As mentioned above, the power distribution tumbler of distributing means for power supply 20 needs the tumbler not only comprising compound planet gear, and can by means of only or additionally comprise the turning unit of differential gear and/or vehicle drive shaft realizes.Distributing means for power supply 20 also can be designed to have three or more tumblers of the speed outside alignment chart cathetus.Such as, distributing means for power supply 20 can be made up of the typical change speed gear box with power-transfer clutch.
The distributing means for power supply 20 of the first to the 5th embodiment has the tumbler of the speed being arranged in alignment chart right-hand member and left end place, and they one of be connected with dynamotor 10 by CVT 36, but, alternatively, all these tumblers also can be connected with CVT 36.
Alternatively, flower wheel 14, driving engine 12, dynamotor 10 realize by being different from mode mentioned above with the mechanical connection of distributing means for power supply 20.Such as, retarder (such as, train of reduction gears) or counter gear can be arranged between distributing means for power supply 20 and flower wheel 14.Depend on the selection of the counter gear of driving engine 12 specification (such as, its hand of rotation), will the power distribution of the expectation of flower wheel 14 be guaranteed.The mechanical connection of flower wheel 14 and distributing means for power supply 20 also by chain or bring realization, instead of is realized by rigid gear mechanism.
Equally, between the counter gear power drive shaft that also can be arranged on driving engine 12 and distributing means for power supply 20 or starting shaft.Preferably, the specification based on driving engine 12 selects counter gear.The mechanical connection of driving engine 12 and distributing means for power supply 20 also by chain or bring realization, instead of is realized by rigid gear mechanism.Transmission system (such as, change-speed box) also can be arranged between distributing means for power supply 20 and driving engine 12.In this case, because the tumbler of distributing means for power supply 20 that couples with power drive shaft to be connected to the S. A. 12a of driving engine 12 by transmission system, thus advantage same as the previously described embodiments can be obtained.This also makes the rotating speed of S. A. 12a can be different from the rotating speed of power drive shaft.In addition, boost installation (such as, multiplying wheel group) or retarder (such as, train of reduction gears) also can be arranged between driving engine 12 and distributing means for power supply 20.
Boost installation (such as, multiplying wheel group) or retarder (such as, train of reduction gears) also can be arranged between dynamotor 10 and distributing means for power supply 20 without the need in the mechanical connection of CVT 36.Illustrate as Fig. 1 (b) is clear, the hybrid power system of the first embodiment has the dynamotor 10 be mechanically connected by the gear ring of counter gear CN and the second compound planet gear 24.Equally, reversing device (such as, counter gear) also can be arranged between CVT 36 and first planet gear cluster 22 and the sun wheel S both the second compound planet gear 24.When the speed of sun wheel S and gear ring R is opposite each other on symbol, this is achieved when the rotating speed of pinion carrier C can be zero (0), but when sun wheel S is identical on symbol with the speed of gear ring R, this also can realize when the rotating speed of pinion carrier C can be zero (0).Such as, this can be by adopting the so-called double planetary gear unit as Japanese Patent openly No.2001-108073 instruction for the first time to realize.Dynamotor 10 and distributing means for power supply 20 also realize by usage chain or band and rigid gear mechanism without the need to the mechanical connection of CVT 36.
In the first to the 5th embodiment, CVT36 between the tumbler being arranged on dynamotor 10 and distributing means for power supply 20 needs not be belt type, and wherein the tumbler of distributing means for power supply 20 is arranged in one end place of the alignment chart defining its speed.Such as, Traction Drive type or hydraulic continuously variable transmission can be used.Alternatively, gear transmission can be used to replace CVT 36.Same change is applied to being arranged on the CVT 36 between the tumbler of the nomographic middle position of structure shown in such as Figure 20 (a) to Figure 22 (b) in dynamotor 10 and distributing means for power supply 20.
The tumbler be mechanically connected with dynamotor 10 and CVT 36 in distributing means for power supply 20 does not need to be the object linearly arranging speed place in alignment chart.As mentioned above, the tumbler of the distributing means for power supply 20 herein related to is not restricted to the tumbler of first planet gear cluster 22 and the second compound planet gear 24, but additionally or only can comprise turning unit and/or the automotive vehicle driving shaft of differential gear.Such as, when distributing means for power supply 20 has two compound planet gears coupled by CVT 36 as in Figure 20 (c) figure or 20 (d), one (directly) in three tumblers of one of these two compound planet gears is mechanically connected to one in three tumblers of another compound planet gear, and nomographic vertical axis two straight lines extending through the rotative speed of three tumblers representing one of compound planet gear can intersect at a point in alignment chart.Tumbler on one of these two lines and the tumbler on another line can be selected as the object be mechanically connected with dynamotor 10 and CVT 36.
In above-mentioned each embodiment, starting shaft separates with power drive shaft, but single axle is alternatively used as starting shaft and power drive shaft, as shown in Figure 23 (a) He Figure 23 (b).The example of Figure 23 (a) is the modification of the first embodiment.The pinion carrier C of first planet gear cluster 22, both as providing initial moment with the first tumbler of fire an engine 12, is used as again the second tumbler of the Power output generated by driving engine 12.The feature of this structure is that the pinion carrier C of first planet gear cluster 22 is by having the first power transmission path of power-transfer clutch 30 and unilateral bearing 32 and having unilateral bearing 34 and be connected with driving engine 12 with the second power transmission path of power-transfer clutch 31.Guarantee carry out fire an engine 12 by means of only (that is, pinion carrier C) in the tumbler of first planet gear cluster 22 and by the supply of power of driving engine 12 to distributing means for power supply 20.Especially, when needs fire an engine 12, controller 40 makes power-transfer clutch 31 be separated and power-transfer clutch 30 is engaged, and sends the S. A. 12a of driving engine 12 with the torque of the pinion carrier C by first planet gear cluster 22 to.After driving engine 12 starts, controller 40 makes power-transfer clutch 31 engage, the torque of driving engine 12 to be sent to the pinion carrier C of first planet gear cluster 22.
Equally, the example of Figure 23 (b) is the modification of the first embodiment.First planet gear cluster 22 and the sun wheel S both the second compound planet gear 24 are used as providing initial moment with fire an engine 12 and the tumbler of the distributing means for power supply 20 of Power output that generated by driving engine 12.As Figure 12 (a), the feature of this structure is first planet gear cluster 22 with the sun wheel S of both the second compound planet gears 24 by having the first power transmission path of power-transfer clutch 30 and unilateral bearing 32 and having unilateral bearing 34 and be connected with driving engine 12 with the second power transmission path of power-transfer clutch 31.The first power transmission path in Figure 23 (a) or Figure 23 (b) alternatively only has unilateral bearing 32.Similarly, the second power transmission path alternatively only has power-transfer clutch 31.
Same structure shown in Figure 23 (a) or Figure 23 (b) can be used to other embodiment or Figure 17 (a) in each in Figure 18 (j).
Above-mentioned driving engine 12 can be modified to shown in Figure 24 (a) and Figure 24 (b) by the structure that single power transmission path is connected with distributing means for power supply 20.Figure 24 (a) and Figure 24 (b) each in example in, power transmission path has the power-transfer clutch 30 be arranged on wherein, and power-transfer clutch 30 is set up as required or interrupted being sent to the power of driving engine 12 or the power transmission from driving engine 12.The example of such design Figure 24 (a), make when the speed of flower wheel 14 non-vanishing (0), the speed of the tumbler be mechanically connected with the S. A. 12a of driving engine 12 in distributing means for power supply 20 can be zero (0).Guarantee fire an engine 12 better.
Figure 25 (a) to Figure 25 (c) illustrates the operation of the hybrid power system fire an engine 12 of Figure 24 (a).Figure 25 (a) represents the rotating speed of the pinion carrier C of first planet gear cluster 22.Figure 25 (b) represents the state of power-transfer clutch 30.Figure 25 (c) represents the rotating speed of driving engine 12.When such as shown in Figure 25 (a), when the rotating speed of the pinion carrier C of first planet gear cluster 22 is zero (0), controller 40 makes power-transfer clutch 30 engage, initial moment is supplied to S. A. 12a with fire an engine 12 or make the crank of driving engine 12 rotate.Then, controller 40 makes power-transfer clutch 30 be separated, and to disconnect the mechanical connection between driving engine 12 and pinion carrier C, and starts the fuel combustion in driving engine 12.When the rotating speed of driving engine 12 equals the rotating speed of pinion carrier C, controller 40 makes power-transfer clutch 30 engage, to set up the mechanical connection between driving engine 12 and pinion carrier C.The joint of power-transfer clutch 30 does not need always only to set up when the rotating speed of driving engine 12 is equal to the rotating speed of pinion carrier C.The speed discrepancy that this joint can work as driving engine 12 and pinion carrier C is achieved close to time in the scope of zero (0) at given.The use of this condition enables the hybrid power system of Figure 24 (b) at dynamotor 10 run duration fire an engine 12.
The hybrid power system of above-mentioned each embodiment has single or two rotating machines, also dynamoelectric machine (that is, dynamotor 10, or dynamotor 10A and 10B) is called, but alternatively, also can have three or more rotating machines.These motors do not need to be designed to dynamotor.Such as, one of rotating machine or some only can be used as electrical motor or electrical generator.
Rotating machine is by having Three-phase AC motor or the DC electrical motor of brush, or induction motor (IM) is implemented.
Alternatively, the hybrid power system of each embodiment can be designed to have two or more explosive motors.
Alternatively, in-vehicle power transmission device and drive system can use together with the vehicle (such as, motor bike) with single flower wheel.
Described in above-mentioned each embodiment and modification, power drive can replace first planet gear cluster 22 and the second compound planet gear 24 with four axle distributing means for power supply.Such as, can adopt Ravigneaux formula (Ravineaux) compound planet gear, it mainly has four power distribution tumblers: define the sun wheel of four S. A.s, sun wheel, pinion carrier and gear ring.These four S. A.s by CVT 36 respectively machinery be coupled to dynamotor 10, flower wheel 14, driving engine 12 and dynamotor 10.
As mentioned above, drive system of the present invention has the power drive as described in above-described embodiment and modification and the controller as shown in Fig. 1 (a) 40.Such as, drive system can be designed to have the structure of Fig. 1 (a).Like this, when the speed of explosive motor 12 is lower than predetermined value and when needing to reset driving engine 12, controller 40 can make power-transfer clutch 30 engage S. A. 12a torque (that is, the symbol defined as Fig. 2 (c) is positive rotation energy) to be sent to driving engine 12 from the pinion carrier C of first planet gear cluster 22.Such as, the lower limit of driving engine 12 rotating speed when this predetermined value is vehicle operating, and driving engine 12 can be subsequently restarted or light a fire and not need to increase torque from outside to S. A. 12a.In other words, when need to reset driving engine 12 but the rotating speed of driving engine 12 too low to such an extent as to be not supplied to torque that S. A. 12a increases then driving engine 12 just can not reset time, controller 40 makes power-transfer clutch 30 engage S. A. 12a torque to be sent to driving engine 12 from distributing means for power supply 20.This structure does not need engine primer to reset driving engine 12.
Although in order to understand the present invention better, disclosing the present invention with optimum embodiment form, will be appreciated that, the present invention can be realized in many ways when not departing from the principle of the invention.Therefore, the present invention is to be understood as and comprises all possible embodiment, and when not departing from the principle of the invention as described in the appended claims to the modification of illustrated embodiment.

Claims (42)

1., for a power drive for vehicle, comprising:
Multiple power distribution tumbler, its each other collaborative rotate with by power vehicle rotating machine, distribute between explosive motor and flower wheel; With
Power transmission control mechanism, described power transmission control mechanism is arranged between the first tumbler and explosive motor, for optionally setting up and interrupting the power transmission between the first tumbler and described explosive motor, wherein said first tumbler is a tumbler in described power distribution tumbler; Described power transmission control mechanism is used as the first power transmission control mechanism;
Wherein, if it is just that the rotation exported from described power distribution tumbler can be defined by symbol, then described power distribution tumbler is arranged so that: when described power transmission control mechanism set up power from described first tumbler to the symbol of described explosive motor be positive rotation can transmission be the positive rotation energy from the first tumbler to transmit symbol by described power transmission control mechanism time, other tumbler in described power distribution tumbler except the first tumbler is connected, and rotating with the output providing symbol different from each other can;
Wherein, described multiple power distribution tumbler comprises the second tumbler and the 3rd tumbler;
Second power transmission control mechanism is arranged between explosive motor and the second tumbler;
3rd tumbler is connected to the flower wheel of described vehicle;
There is provided mechanical path, the second tumbler and the 3rd tumbler mechanically link together by this mechanical path;
When explosive motor is required to start, first power transmission control mechanism is set to the state allowing to be transmitted power by it, and the second power transmission control mechanism is set to stop and transmits the state of power by it, make the power produced by rotating machine be imported into the second tumbler thus the moment of torsion of input the first tumbler to explosive motor; The rotation energy symbol of described second tumbler and described 3rd tumbler is different from each other;
When the starting of explosive motor completes, first power transmission control mechanism is set to stop the state being transmitted moment of torsion by it, and the second power transmission control mechanism is set to set up the state transmitted by its power, the moment of torsion that explosive motor is produced is imported into the second tumbler.
2. power drive according to claim 1, wherein, generate in described power distribution tumbler the different rotation of symbol each other can those tumblers coupled by machinery each other through the path of the assembly of described power distribution tumbler by bypass.
3. power drive according to claim 2, wherein, some tumblers in described power distribution tumbler and described first tumbler are connected to the rotative speed having and be arranged in a linear in alignment chart, comprise coupled connection mechanism further, in described tumbler two machinery is coupled in together by described coupled connection mechanism outside the assembly of described power distribution tumbler, and wherein said coupled connection mechanism is as the change-speed box with variable-speed ratio.
4. power drive according to claim 1, wherein, first power transmission control mechanism is optionally set up and is interrupted the power transmission between described first tumbler and the S. A. of described explosive motor, and comprise the second power transmission control mechanism further, optionally to set up and to interrupt the power transmission between the second tumbler and described explosive motor, described second tumbler is a tumbler in described power distribution tumbler.
5. power drive according to claim 4, wherein, described first power transmission control mechanism has unidirectional power transmission device, when the rotating speed of the outgoing side that the rotating speed of the input side that described unidirectional power transmission device is connected with described first tumbler is connected with described explosive motor S. A. relative to described unidirectional power transmission device is nonnegative value, power transmission set up by described unidirectional power transmission device.
6. power drive according to claim 5, wherein, described first power transmission control mechanism also has automatically controlled interrupter, described automatically controlled interrupter separates with described unidirectional power transmission device, and described automatically controlled interrupter is for interrupting the described power transmission between described first tumbler and described explosive motor S. A..
7. power drive according to claim 4, wherein, described second power transmission control mechanism has unidirectional power transmission device, when the rotating speed of the input side that described unidirectional power transmission device is connected with described explosive motor S. A. is nonnegative value relative to the rotating speed of the outgoing side be connected with described second tumbler with described unidirectional power transmission device, described power transmission set up by described unidirectional power transmission device.
8. power drive according to claim 4, one of wherein said power distribution tumbler machinery is coupled to described rotating machine, and wherein said power distribution tumbler is connected like this, the rotating speed of described first tumbler is made directly to depend on the rotating speed of the tumbler coupled with described rotating machine in described power distribution tumbler.
9. power drive according to claim 4, wherein, one of described power distribution tumbler machinery is coupled to described rotating machine, and wherein said power distribution tumbler is connected like this, the rotating speed of other tumbler in described power distribution tumbler except being coupled to the tumbler of described rotating machine is made directly to depend on the rotating speed of the tumbler coupled with rotating machine and the rotating speed of described second tumbler.
10. power drive according to claim 4, wherein, described first tumbler and described second tumbler are implemented by the same tumbler in described power distribution tumbler, and wherein said first power transmission control mechanism separates with described second power transmission control mechanism.
11. power drives according to claim 4, wherein, described first tumbler and described second tumbler are implemented by the same tumbler in described power distribution tumbler, and wherein said first power transmission control mechanism and enforcement the second power transmission control mechanism are implemented by automatically controlled interrupter, implement automatically controlled interrupter for interrupting the described power transmission between described first tumbler and described explosive motor S. A..
12. power drives according to claim 4, wherein, described first tumbler separates with described second tumbler.
13. power drives according to claim 12, wherein, described power distribution tumbler is connected like this, makes the rotating speed of described first tumbler lower than the rotating speed of described second tumbler.
14. power drives according to claim 4, wherein, described power distribution tumbler is implemented by three or more tumblers, described three or more tumblers are connected like this, thus their rotative speed is linearly arranged in alignment chart, and wherein said first tumbler is a tumbler in described three or more tumblers with the intermediate value of rotative speed in alignment chart.
15. power drives according to claim 4, wherein, described power distribution tumbler is implemented by three or more tumblers, described three or more tumblers are connected like this, thus their rotative speed is linearly arranged in alignment chart, and in described three or more the tumblers that wherein rotative speed is different in alignment chart two are coupled to described rotating machine by machinery.
16. power drives according to claim 15, wherein, at least one in described two tumblers of described three or more tumblers is coupled to described rotating machine by the change-speed box with variable-speed ratio.
17. power drives according to claim 15, wherein, in described three or more tumblers, the mechanical tumbler being coupled to described flower wheel has the rotative speed of intermediate value between the mechanical rotative speed being coupled to described two tumblers of described rotating machine in described three or more tumblers in alignment chart.
18. power drives according to claim 1, wherein, described power distribution tumbler is implemented by four tumblers, described four tumblers are connected like this, thus their rotative speed is linearly arranged in alignment chart, and in wherein said four tumblers, there is in alignment chart rotative speed intermediate value and be coupled to described flower wheel with the tumbler that described first tumbler separates by machinery.
19. power drives according to claim 1, comprise further, first planet gear cluster and the second compound planet gear, each compound planet gear all has sun wheel, pinion carrier and gear ring, they are as three tumblers in described power distribution tumbler, two in the described power distribution tumbler of described first planet gear cluster to be coupled to two in the described power distribution tumbler of described second compound planet gear by machinery, and wherein have in the described first planet gear cluster of different rotating speeds and 6 power distribution tumblers altogether of the second compound planet gear four in alignment chart, at least three tumblers are coupled to described rotating machine by machinery respectively, explosive motor and flower wheel.
20. power drives according to claim 4, comprise conv further, and described conv is used for being converted to another tumbler by described power distribution tumbler by the tumbler that machinery is coupled to described flower wheel.
21. power drives according to claim 20, wherein, described vehicle comprises wheel further, comprise conv further, described conv is used for being converted to other tumbler by described power distribution tumbler by some tumblers that machinery is coupled to described flower wheel, and comprise a tumbler in described second tumbler and described power distribution tumbler except described first tumbler by being coupled to other tumbler described in flower wheel in more wherein said tumblers and described power distribution tumbler, and wherein said second tumbler is coupled to described flower wheel by described second power transmission control mechanism machinery.
22. 1 kinds, for the drive system of vehicle, comprising:
Power drive, described power drive comprises, (a) multiple power distribution tumbler, and it is collaborative each other rotates with by power rotating machine in the vehicle mounted, distribute between explosive motor and vehicle flower wheel; And (b) power transmission control mechanism, described power transmission control mechanism is arranged between the first tumbler and explosive motor, for optionally setting up and interrupting the power transmission between the first tumbler and explosive motor, described first tumbler is a tumbler in described power distribution tumbler, and described power transmission control mechanism is used as the first power transmission control mechanism; And if the rotation wherein exported from described power distribution tumbler just can be defined as at symbol, power distribution tumbler is then set, make when described power transmission control mechanism set up power from described first tumbler to described explosive motor and symbol is positive rotation can transmit with when to transmit symbol by described power transmission control mechanism be the positive rotation energy from the first tumbler, other tumbler in described power distribution tumbler except described first tumbler is connected to provide symbol is contrary each other output to rotate can; Wherein, described multiple power distribution tumbler comprises the second tumbler and the 3rd tumbler; Second power transmission control mechanism is arranged between explosive motor and the second tumbler; 3rd tumbler is connected to the flower wheel of described vehicle; There is provided mechanical path, the second tumbler and the 3rd tumbler mechanically link together by this mechanical path; When explosive motor is required to start, first power transmission control mechanism is set to the state allowing to be transmitted power by it, and the second power transmission control mechanism is set to stop and transmits the state of power by it, make the power produced by rotating machine be imported into the second tumbler thus the moment of torsion of input the first tumbler to explosive motor; The rotation energy symbol of described second tumbler and described 3rd tumbler is different from each other; When the starting of explosive motor completes, first power transmission control mechanism is set to stop the state being transmitted moment of torsion by it, and the second power transmission control mechanism is set to set up the state transmitted by its power, the moment of torsion that explosive motor is produced is imported into the second tumbler; And
For controlling the controller of described power drive operation, when needs start explosive motor, and when the rotating speed of described explosive motor is lower than given value, described controller controls power transmission control mechanism to set up the transmission that symbol is the positive energy of the rotation from described first tumbler to described explosive motor.
23. drive systems according to claim 22, wherein, generate in described power transmission tumbler the different rotation of symbol each other can some tumblers coupled by machinery each other through the path of the assembly of described power distribution tumbler by bypass.
24. drive systems according to claim 23, wherein, some tumblers of described power distribution tumbler are connected like this with the first tumbler, thus there is the rotative speed of straight-though arrangement in alignment chart, comprise coupled connection mechanism further, in described tumbler two machinery is coupled in together by described coupled connection mechanism outside the assembly of described power distribution tumbler, and wherein said coupled connection mechanism is as the change-speed box with variable-speed ratio.
25. drive systems according to claim 22, wherein, first power transmission control mechanism is optionally set up and is interrupted the power transmission between described first tumbler and the S. A. of described explosive motor, and comprise the second power transmission control mechanism further, described second power transmission control mechanism is used for optionally setting up and interrupting the power transmission between described second tumbler and described explosive motor, and described second tumbler is a tumbler in described power distribution tumbler.
26. drive systems according to claim 25, wherein, described first power transmission control mechanism has unidirectional power transmission device, when the rotating speed of the outgoing side that the rotating speed of the input side that described unidirectional power transmission device is connected with described first tumbler is connected with described explosive motor S. A. relative to described unidirectional power transmission device is nonnegative value, described power transmission set up by described unidirectional power transmission device.
27. drive systems according to claim 26, wherein, described first power transmission control mechanism also has automatically controlled interrupter, described automatically controlled interrupter separates with described unidirectional power transmission device, and described automatically controlled interrupter is for interrupting the power transmission between described first tumbler and described explosive motor S. A..
28. drive systems according to claim 25, wherein, described second power transmission control mechanism has unidirectional power transmission device, when the rotating speed of the outgoing side that the rotating speed of the input side that described unidirectional power transmission device is connected with described explosive motor S. A. is connected with described second tumbler relative to described unidirectional power transmission device is nonnegative value, described power transmission set up by described unidirectional power transmission device.
29. drive systems according to claim 25, wherein, one of described power distribution tumbler is coupled to described rotating machine by machinery, and wherein said power distribution tumbler is connected like this, the rotating speed of described first tumbler is made directly to depend on the rotating speed being coupled to the tumbler of described rotating machine in described power distribution tumbler.
30. drive systems according to claim 25, wherein, one of described power distribution tumbler is coupled to described rotating machine by machinery, and wherein said power distribution tumbler is connected like this, the rotating speed of some tumblers in described power distribution tumbler except being coupled to the tumbler of described rotating machine is made directly to depend on the rotating speed of the tumbler being coupled to described rotating machine and the rotating speed of described second tumbler.
31. drive systems according to claim 25, wherein, described first tumbler and described second tumbler are implemented by the same tumbler in described power distribution tumbler, and wherein said first power transmission control mechanism separates with described second power transmission control mechanism.
32. drive systems according to claim 25, wherein, described first tumbler and described second tumbler are implemented by the same tumbler in described power distribution tumbler, and wherein said first power transmission control mechanism and described second power transmission control mechanism are implemented by automatically controlled interrupter, and described automatically controlled interrupter is for interrupting the power transmission between described first tumbler and described explosive motor S. A..
33. drive systems according to claim 25, wherein, described first tumbler separates with described second tumbler.
34. drive systems according to claim 33, wherein, described power distribution tumbler is connected like this, makes the rotating speed of described first tumbler lower than the rotating speed of described second tumbler.
35. drive systems according to claim 25, wherein, described power distribution tumbler is implemented by three or more tumblers, described three or more tumblers are connected like this, thus their rotative speed is linearly arranged in alignment chart, and wherein said first tumbler is a tumbler in described three or more tumblers with the intermediate value of rotative speed in alignment chart.
36. drive systems according to claim 25, wherein, described power distribution tumbler is implemented by three or more tumblers, described three or more tumblers are connected like this, thus their rotative speed is linearly arranged in alignment chart, and in described three or more the tumblers that wherein rotative speed is different in alignment chart two are coupled to described rotating machine by machinery.
37. drive systems according to claim 36, wherein, at least one in two tumblers in described three or more tumblers is coupled to described rotating machine by the change-speed box with variable-speed ratio.
38. drive systems according to claim 36, wherein, the middle rotative speed between the rotative speed that be there are two tumblers being coupled to described rotating machine in described three or more tumblers by machinery in alignment chart by the tumbler that machinery is coupled to described flower wheel in described power distribution tumbler.
39. drive systems according to claim 22, wherein, described power distribution tumbler is implemented by four tumblers, described four tumblers are connected like this, thus their rotative speed is linearly arranged in alignment chart, and in wherein said four tumblers, there is in alignment chart rotative speed intermediate value and be coupled to described flower wheel with the tumbler that described first tumbler separates by machinery.
40. drive systems according to claim 22, comprise first planet gear cluster and the second compound planet gear further, each compound planet gear all has sun wheel, pinion carrier and gear ring, they are as three tumblers in described power distribution tumbler, two of the described power distribution tumbler of first planet gear cluster are coupled to two of the described power distribution tumbler of the second compound planet gear by machinery, and wherein have in the described first planet gear cluster of different rotating speeds and 6 power distribution tumblers altogether of the second compound planet gear four in alignment chart, at least three are coupled to described rotating machine by machinery respectively, explosive motor and flower wheel.
41. drive systems according to claim 25, comprise conv further, and the tumbler that described conv is used for machinery in described power distribution tumbler to be coupled to described flower wheel is converted to another tumbler.
42. drive systems according to claim 41, wherein, described vehicle comprises wheel further, comprise conv further, some tumblers that described conv is used for machinery in described power distribution tumbler to be coupled to described flower wheel are converted to other tumbler, and comprise tumbler in described second tumbler and described power distribution tumbler except described first tumbler by being coupled to other tumbler described in described flower wheel in more wherein said tumblers and described power distribution tumbler, and wherein said second tumbler is coupled to described flower wheel by described second power transmission control mechanism by machinery.
CN200910217181.2A 2008-11-11 2009-11-11 In-vehicle power transmission device and driving system for vehicle Active CN101898509B (en)

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JP2008-289166 2008-11-11
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JP2009-179547 2009-07-31
JP2009179547A JP5372648B2 (en) 2009-07-31 2009-07-31 Power transmission device and power transmission control system
JP2009242314A JP5203332B2 (en) 2008-11-11 2009-10-21 On-vehicle power transmission device and vehicle drive device
JP2009-242314 2009-10-21

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