CN104265792B - The clutch and its vehicle speed variation assembly of hybrid vehicle - Google Patents

The clutch and its vehicle speed variation assembly of hybrid vehicle Download PDF

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Publication number
CN104265792B
CN104265792B CN201410385451.1A CN201410385451A CN104265792B CN 104265792 B CN104265792 B CN 104265792B CN 201410385451 A CN201410385451 A CN 201410385451A CN 104265792 B CN104265792 B CN 104265792B
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China
Prior art keywords
power source
clutch
output shaft
source output
shaft
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CN104265792A (en
Inventor
李云峰
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SHENZHEN YUECHENG AUTOMOBILE TECHNOLOGY Co Ltd
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SHENZHEN YUECHENG AUTOMOBILE TECHNOLOGY Co Ltd
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    • 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
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
    • 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
    • B60K6/42—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
    • B60K2006/4825—Electric machine connected or connectable to gearbox 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
    • 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
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • 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
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2033—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with one engaging means
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three engaging means
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2041—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with four engaging means
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)

Abstract

The present invention relates to a kind of clutch of hybrid vehicle and vehicle speed variation assembly, which is connected to as individual components between the first and second power source output shafts of vehicle and fixed-shaft speed change gear set input shaft, including：The combined type planetary mechanism for being connected between the first and second power source output shafts and fixed-shaft speed change gear set input shaft and being combined by element sharing method by single planetary row and double planet wheel rows of mixing；And for being controlled such that the power exported from the first and/or second power source output shaft is transferred to through combined type planetary mechanism the control mechanism of fixed-shaft speed change gear set input shaft to the element in combined type planetary mechanism.The clutch and vehicle speed variation assembly of the present invention by using above-mentioned combined type planetary mechanism have the characteristics that it is of simple structure and low cost, powerful, be easily achieved multiple gearizations, be easy to implement automation.

Description

The clutch and its vehicle speed variation assembly of hybrid vehicle
Technical field
The present invention relates to a kind of clutch and vehicle speed variation assembly, more particularly to a kind of clutch of hybrid vehicle with And the vehicle speed variation assembly using the clutch.
Background technology
Hydraulic type automatic transmission (AT) mainly by fluid torque-converter (having the function of the clutch of vehicle), planetary gear, Wet multi-plate brake, wet-type multi-disc clutch and hydraulic control system composition, are transmitted and gear combination by fluid power Mode realizes bending moment and speed change.Such automatic transmission is in the case where low vehicle speeds, automobile braking mechanism are in running order, hair When motivation water temperature is in idling mode less than specified value, engine, fluid torque-converter is in couple state, and pump impeller blade always can Disturbance fluid torque-converter internal oil makes its flow at high speed, causes a large amount of energy losses, this is the main original for causing AT oil consumption high One of because.
In order to reduce oil consumption as possible, the designer of AT locking torque converter as soon as possible makes the power of engine straight It connects and is transmitted to planetary gear set.Meanwhile people have turned to thinking the design of multiple gearizations, to obtain better dynamic property, acceleration Property and lower oil consumption, also cause the structure of automatic transmission to become more complicated, manufacturing cost higher, the accuracy of manufacture is more in this way Height, maintaining difficulty higher.
It is well known that AT oil consumption highest, exhaust emissions problem when the urban road of support, frequently starting and low speed are run Also the most prominent, the efficiency of engine becomes very low.Therefore, under these conditions, it is suitable using motor as power source Ideal scheme, thus introduces hybrid power system so that vehicle is in the urban road of support, frequently starting and low speed operation When, by electric motor operation, tail-off, to improve the energy ecology of vehicle.Also, when vehicle deceleration is braked It waits, the energy that motor can also be wasted by regenerative braking when capturing vehicle braking can also improve the energy of vehicle Measure service efficiency.
Invention content
In order to which the structure for solving multi-speed automatic transmission assembly in the prior art is excessively complicated, cost is too high, service efficiency Low problem the present invention provides a kind of clutch of the uniaxial output of hybrid vehicle and uses the vehicle of the clutch Speed changing assembly.
Technical solution is used by the present invention solves above-mentioned technical problem：A kind of clutch of hybrid vehicle is provided Device, clutch is connected to the first power source output shaft of vehicle as individual components and the second power source output shaft becomes with fixed shaft type Between fast gear unit input shaft, which includes：It is connected to the first power source output shaft and the second power source output shaft and determines It is combined between shaft type change gear group input shaft and by single planetary row and double planet wheel rows of mixing by element sharing method compound Formula planetary mechanism；And for the element in combined type planetary mechanism be controlled such that from the first power source output shaft and/ Or second the power of power source output shaft output the control of fixed-shaft speed change gear set input shaft is transferred to through combined type planetary mechanism Mechanism processed.
Wherein, combined type planetary mechanism includes the first sun gear, the second sun gear, the first planetary gear, the second planetary gear, tooth Circle and planet carrier, the first planetary gear and the first sun gear external toothing, gear ring and the first planetary gear internal messing, the second planetary gear position Between the second sun gear and the first planetary gear and respectively with the second sun gear and the first planetary gear external toothing, the first planetary gear and The further common planet carrier of second planetary gear；Alternatively, combined type planetary mechanism includes sun gear, the first planetary gear, the second planet Wheel, the first gear ring, the second gear ring and planet carrier, the first planetary gear and sun gear external toothing, the first gear ring and the first planetary gear Internal messing, the second planetary gear between the first planetary gear and the second gear ring and with the first planetary gear external toothing, and with the second tooth Enclose internal messing, the first planetary gear and the further common planet carrier of the second planetary gear.
Wherein, control mechanism includes an at least arrestment mechanism, and arrestment mechanism is used for the element in combined type planetary mechanism It is braked, so that the power exported from the first power source output shaft and/or the second power source output shaft is through combined type planet The element for not being braked mechanism braking of mechanism is transferred to fixed-shaft speed change gear set input shaft.
Wherein, control mechanism includes an at least clutch, and clutch is used for two in combined type planetary mechanism Element is simultaneously engaged with to the first power source output shaft and/or the second power source output shaft or fixed-shaft speed change gear set input Axis, so that the power exported from the first power source output shaft and/or the second power source output shaft is passed through combined type planetary mechanism It is handed to fixed-shaft speed change gear set input shaft.
Wherein, control mechanism includes at least two clutches, and at least two clutches are used for combined type planet machine Different elements and the first power source output shaft and/or the second power source output shaft in structure or fixed-shaft speed change gear set input Axis is selectively engaged, so by the cooperation between clutch and the cooperation or clutch of arrestment mechanism make from First power source output shaft and/or the power of the second power source output shaft output are transferred to fixed shaft type through combined type planetary mechanism and become Fast gear unit input shaft.
Wherein, control mechanism includes an arrestment mechanism and two clutches, wherein being distinguished by two clutches Coordinate with arrestment mechanism so that the power exported from the first power source output shaft and/or the second power source output shaft is through combined type Planetary mechanism is transferred to fixed-shaft speed change gear set input shaft with First Speed ratio and second speed ratio, and passes through two clutches Cooperation between structure so that from the power of the first power source output shaft and/or the second power source output shaft through combined type planet machine Structure is transferred to fixed-shaft speed change gear set input shaft with third speed ratio.
Wherein, control mechanism includes two arrestment mechanisms and two clutches, wherein being distinguished by two clutches With a cooperation in two arrestment mechanisms so that exported from the first power source output shaft and/or the second power source output shaft Power is transferred to fixed-shaft speed change gear set input shaft through combined type planetary mechanism with First Speed ratio and second speed ratio, two One in clutch with another cooperation in two arrestment mechanisms so that from the first power source output shaft and/or second The power of power source output shaft output is transferred to fixed-shaft speed change gear set input through combined type planetary mechanism with third speed ratio Axis, and pass through the cooperation between two clutches so that it is defeated from the first power source output shaft and/or the second power source output shaft The power gone out is transferred to fixed-shaft speed change gear set input shaft through combined type planetary mechanism with fourth speed ratio.
Wherein, control mechanism includes two arrestment mechanisms and three clutches, wherein by three clutches First clutch and the second clutch coordinate with the first arrestment mechanism in two arrestment mechanisms respectively so that dynamic from first Power source output shaft and/or the power of the second power source output shaft output are fast with First Speed ratio and second through combined type planetary mechanism Degree ratio is transferred to fixed-shaft speed change gear set input shaft, passes through the first clutch and third clutch in three clutches Structure coordinates with the second arrestment mechanism in two arrestment mechanisms respectively so that from the first power source output shaft and/or the second power The power of source output shaft output is transferred to fixed shaft type gear teeth through combined type planetary mechanism with third speed ratio and fourth speed ratio Wheel group input shaft, and pass through the cooperation between any two clutch in three clutches so that from the first power source The power of output shaft and/or the second power source output shaft is transferred to fixed shaft type speed change through combined type planetary mechanism with the 5th speed ratio Gear unit input shaft.
Wherein, torsion damping mechanism is integrated on combined type planetary mechanism, torsion damping mechanism includes coaxial arrangement and energy The first rotatable parts and the second rotatable parts that enough relatively rotate and the rotation along the first rotatable parts and the second rotatable parts The spring cushion of direction elastic connection the first rotatable parts and the second rotatable parts.
Another technical solution is used by the present invention solves above-mentioned technical problem：A kind of vehicle speed variation assembly is provided, Including clutch and fixed-shaft speed change gear set, fixed-shaft speed change gear set includes a fixed-shaft speed change gear set input shaft With a fixed-shaft speed change gear set output shaft, clutch is connected to engine output shaft and fixed shaft type speed change as individual components Between gear unit input shaft, clutch includes：Be connected between engine output shaft and fixed-shaft speed change gear set input shaft and The combined type planetary mechanism being combined by element sharing method by single planetary row and double planet wheel rows of mixing；And for combined type Element in planetary mechanism is controlled such that the power exported from engine output shaft is selectively passed through combined type planetary mechanism It is handed to the control mechanism of fixed-shaft speed change gear set input shaft, wherein combined type planetary mechanism or fixed-shaft speed change gear set output Axis further connects motor output shaft, so that the power exported from motor output shaft is transferred to through combined type planetary mechanism and determines Shaft type change gear group input shaft, or it is transferred directly to fixed-shaft speed change gear set output shaft without combined type planetary mechanism.
Above-mentioned clutch and using the clutch vehicle speed variation assembly the advantages of be：It is exported using engine is connected to It is combined by element sharing method between axis and fixed-shaft speed change gear set input shaft and by single planetary row and double planet wheel rows of mixing Combined type planetary mechanism and defeated from engine output shaft for being controlled such that the element in combined type planetary mechanism The control mechanism that the power gone out is transferred to fixed-shaft speed change gear set input shaft through combined type planetary mechanism coordinates fixed shaft type speed change Gear set, have the characteristics that it is of simple structure and low cost, powerful, be easily achieved multiple gearizations, be easy to implement automation.Together When, due to further integrated torsional damper mechanism on the clutch, further by an individual components it is integrated simultaneously " from The multiple functions such as conjunction " and " vibration damping " can cancel existing " clutch ", " fluid torque-converter ", " flywheel " or " double quality fly The components such as wheel " further make such speed changing assembly more compact structure, simpler, cost is lower, is easier to maintenance etc..
Description of the drawings
Fig. 1 is the structural schematic diagram of vehicle speed variation assembly according to a first embodiment of the present invention；
Fig. 2-4 is the structural schematic diagram of clutch difference modification shown in FIG. 1；
Fig. 5 is the structural schematic diagram of clutch according to a second embodiment of the present invention；
Fig. 6-10 is the structural schematic diagram of clutch difference modification shown in fig. 5；
Figure 11 is the structural schematic diagram of clutch according to a third embodiment of the present invention；
Figure 12-18 is the structural schematic diagram of clutch difference modification shown in Figure 11；
Figure 19 is the structural schematic diagram of clutch according to a fourth embodiment of the present invention；
Figure 20-25 is the structural schematic diagram of clutch difference modification shown in FIG. 1；
Figure 26 is the structural schematic diagram of clutch according to a fifth embodiment of the present invention；
Figure 27 is the structural schematic diagram of clutch according to a sixth embodiment of the present invention；
Figure 28-31 is the structural schematic diagram of clutch difference modification shown in Figure 26-27；
Figure 32 is the structural schematic diagram of clutch according to a seventh embodiment of the present invention；
Figure 33 is the structural schematic diagram of clutch according to a eighth embodiment of the present invention；
Figure 34 is the structural schematic diagram of clutch according to a ninth embodiment of the present invention；
Figure 35 is the structural schematic diagram of clutch according to a tenth embodiment of the present invention；
Figure 36 is the structural schematic diagram of clutch according to a 11th embodiment of the present invention；
Figure 37-38 is the structural schematic diagram of clutch difference modification shown in Figure 33-36；
Figure 39 is the structural schematic diagram of clutch according to a 12th embodiment of the present invention；
Figure 40 is the structural schematic diagram of clutch according to a 13th embodiment of the present invention；
Figure 41 is the structure for being integrated in the torsion damping mechanism on clutch according to a 14th embodiment of the present invention Schematic diagram.
Specific implementation mode
Below according to drawings and examples, the present invention is described in detail.
It is the structural schematic diagram of vehicle speed variation assembly according to a first embodiment of the present invention referring to Fig. 1, Fig. 1.In this implementation In example, which includes clutch 10 and the fixed-shaft speed change gear set that is connect with the clutch 10.Clutch 10 include：Connect the first power source output shaft 120 and the second power source output shaft 122 and fixed-shaft speed change gear set input shaft 13 Between combined type planetary mechanism 11, and for controlling the element in combined type planetary mechanism 11, so that from first Power source output shaft 120 and/or the power of the second power source output shaft 122 output are transferred to dead axle through combined type planetary mechanism 11 The control mechanism 14 of formula change gear group input shaft 13.In the present embodiment, clutch 10 is to be connected to vehicle as individual components The first power source output shaft 120 and the second power source output shaft 122 and fixed-shaft speed change gear set input shaft 13 between. In the present embodiment, the first power source output shaft 120 connects the first power source (not shown), the connection of the second power source output shaft 122 Second power source 123, preferably the first power source are diesel oil or petrol engine (hereinafter referred engine), and the second power source is Motor/generator (hereinafter referred motor).
It is further provided with power source clutch between first power source output shaft 120 and combined type planetary mechanism 11 121, the second power source output shaft 122 connects compound planetary machine directly or by transmission mechanism appropriate (such as driving gear set) Structure 11.Power source clutch 121 specifically exports the first power source for controlling the first power source output shaft 122 The power that axis 122 exports selectively is exported to combined type planetary mechanism 11.
Traditional wet type or dry type clutch mechanism can be used in power source clutch 121.For example, power source clutch 121 include driving link 1211 and driven member 1212, when driving link 1211 and the engagement of driven member 1212, the output of the first power source The power output that axis 120 exports is to combined type planetary mechanism 11.When driving link 1211 and driven member 1212 are separated from each other, first The power that power source output shaft 120 exports does not export to combined type planetary mechanism 11.Power source clutch 121 can also be by list It is replaced to clutch.When the rotating speed for the element of combined type planetary mechanism 11 being connect with the first power source output shaft 12 is more than When the rotating speed of power source, one-way clutch mechanism, which is in, surmounts state, avoids the reflux of power.It can certainly be in the second power source Power source clutch appropriate is set between output shaft 122 and compound planetary mechanism 11.
In the present embodiment, combined type planetary mechanism 11 is compound by element sharing method by single planetary row and double planet wheel rows of mixing It forms, and specifically includes the first sun gear 115, the second sun gear 116, the first planetary gear 112, the second planetary gear 114, gear ring 111 and planet carrier 113.114 common planet carrier 113 of wherein the first planetary gear 112 and the second planetary gear, the first planetary gear 112 With 115 external toothing of the first sun gear, 112 internal messing of gear ring 111 and the first planetary gear.First sun gear 115, the first planetary gear 112, gear ring 111 and planet carrier 113 constitute a single planetary row.Second planetary gear 114 is located at the second sun gear 116 and the first planet Wheel 112 between, and respectively with 112 external toothing of the second sun gear 116 and the first planetary gear.Second sun gear 116, the first planetary gear 112, the second planetary gear 114, gear ring 111 and planet carrier 113 further constitute a double planet wheel rows of mixing.In the present embodiment, control machine Structure 14 controls the first sun gear 115, and the second sun gear 116 connects the first power source output shaft 120 and/or the second power Source output shaft 122, gear ring 111 connect fixed-shaft speed change gear set input shaft 13.
In the present embodiment, control mechanism 14 is an arrestment mechanism, such as dry type braking mechanism, and specifically may include braking Disk 141 and caliper 142.Brake disc 141 is coaxially fixed on the first sun gear 115, and caliper 142 is used for brake disc 141 carry out selective braking.Control by above-mentioned arrestment mechanism to combined type planetary mechanism 11, come reach power transmission and Cut-out.In addition, control mechanism 14 can also use wet brakign mechanism.
In the present embodiment, above-mentioned when engine (the first power source) is run and motor (the second power source) is closed Clutch is equivalent to a common automatic clutch.Specifically, when the release of caliper 142, when not constraining brake disc 141, First power source output shaft 120 drives the rotation of the second sun gear 116.At this point, due to the second planetary gear 114, planet carrier 113, One planetary gear 112 and the first sun gear 115 are in free state, to not export power at gear ring 111, as commonly from " separation " state of clutch.When caliper 142 locks brake disc 141, the first sun gear 115 is similarly in locking state, the The power of one power source output shaft 120 input is transmitted to through the second sun gear 116, the second planetary gear 114, the first planetary gear 112 On gear ring 111, and export to fixed-shaft speed change gear set input shaft 13, as " engagement " state of ordinary clutch.In addition, working as Caliper 142 skids in braking not locked brake disc 141 between caliper 142 and brake disc 141, be equivalent to commonly from Clutch is in " half-clutch " state of starting and shift process, the at this time power of transmitting portions engine.
When engine (the first power source) is closed, and motor (the second power source) is run, motor (the second power source) Power is provided to combined type planetary mechanism 11 through the second power source output shaft 122, drives the rotation of the second sun gear 116.At this point, logical Cross above description similar mode control arrestment mechanism 14 so that the power of the second power source output shaft 122 output is through combined type Planetary mechanism 11 is transmitted to fixed-shaft speed change gear set input shaft 13, forms pure electric vehicle driving.
When engine (the first power source) and motor (the second power source) all provide power to combined type planetary mechanism 11 When, then form mixed running pattern in parallel.When needing anxious acceleration or to overcome larger running resistance, (first is dynamic for engine Power source) work, power source clutch 121 engages, to transmit the power of engine to combined type planetary mechanism 11, and meanwhile it is electronic Machine also provides power to combined type planetary mechanism 11, so that vehicle obtains the acceleration or driving force of bigger.
In vehicle high-speed operation, the efficiency of engine (the first power source) is relatively high, can be completely by engine driving Vehicle.At this point, motor is closed, and it is equivalent to a rotary inertia or a load.For example, when providing energy for motor Battery (not shown) energy storage it is inadequate when or vehicle high-speed when running, engine has power more than needed, motor under certain operating modes It can be used as generator to charge for battery, motor is equivalent to a load at this time.Further, when vehicle needs retarding braking, electricity Motivation can be changed into generator, carry out the energy of recovery vehicle keeping off counter drag as fixed-shaft speed change gear set, filled for battery Electricity.
In embodiments of the present invention, power source as starting power source and is preferably run at a low speed using motor, engine is made For power source of running at high speed.Further, in anxious starting, anxious acceleration, starting can be cooperateed with engine with motor.In addition, working as When motor can not work normally, need using engine as starting power source.
Since in embodiments of the present invention, other clutches of clutch 10 and subsequent descriptions are needed as starting clutch Device uses, it is necessary to bear prolonged sliding wear, while need to absorb and take away resulting amount of heat in time.Therefore it controls The arrestment mechanism used when as start clutch in other control mechanisms of mechanism 14 and subsequent descriptions and/or from Close mechanism dimensionally than inside common AT wet-type multi-disc arrestment mechanism or clutch it is much greater.
Specifically, in embodiments of the present invention, due to the use of dry brake, then control mechanism 14 is similar to uses extensively Disk brake in brake system of car, it directly and contacting external air (is equivalent to when control mechanism 14 generates sliding wear Conventional dry clutch " half-clutch ") when, generated heat directly can carry out heat exchange with outside air, can be timely It is taken away by air, so having excellent radiating condition, it is caused by opposite closed structure to solve conventional dry clutch It radiates bad and is easy that clutch even temperature of transmission is made to be increased to beyond safe range, clutch can be caused to lose when serious Effect, entire speed changer can not work normally, lead to power interruption, lead to the problem of potential danger.
The steel disc and friction plate outer diameter of wet-type multi-disc arrestment mechanism and clutch in common vehicle are generally 200MM Within, radial thickness is generally 10-20MM, and axial width is generally 2-4MM, and friction area is small.As starting in the present invention The outer diameter of steel disc and friction plate that the wet brakign mechanism and/or wet type clutch used when clutch uses is generally 250-300MM, radial thickness are generally 20MM or more, and axial width is generally 3-5MM, and friction area is big.It is worth noting that, The setting of above-mentioned size be the present inventor according to using above-mentioned clutch as start clutch use and innovative design out, Therefore the setting of above-mentioned size, which is not those skilled in the art, to readily occur in.
In Fig. 1, fixed-shaft speed change gear set is described by taking triple axle fixed-shaft speed change gear set as an example, includes mainly Fixed-shaft speed change gear set input shaft 13 and fixed-shaft speed change gear set jackshaft 151 disposed in parallel and fixed shaft type gear teeth Wheel group output shaft 152.Wherein, the gear 161 being fixed on fixed-shaft speed change gear set input shaft 13 becomes with fixed shaft type is fixed on Gear 162 on fast gear set jackshaft 151 engages, to receive the power of the input of fixed-shaft speed change gear set input shaft 13.Gu Due on fixed-shaft speed change gear set jackshaft 151 gear 172 and be set on fixed-shaft speed change gear set output shaft 152 Gear 171 engages, and gear 171 is further selectively engaged by selector 19 to fixed-shaft speed change gear set output shaft 152, by This is by power transmission to fixed-shaft speed change gear set output shaft 152.Wherein, gear 171,172 is with the more of different drive ratios Group, and selectively engaged with fixed-shaft speed change gear set output shaft 152 by different selectors 19, it is achieved in difference Forward range.Further, the gear 183 that is fixed on fixed-shaft speed change gear set jackshaft 151 and it is set in the idle pulley that reverses gear Gear 182 on axis 153 engages, gear 182 further with the gear that is set on fixed-shaft speed change gear set output shaft 152 181 engagements, and selectively engaged to fixed-shaft speed change gear set output shaft 152 by corresponding selector 19, it is achieved in down Gear.
The vehicle speed variation assembly that the clutch 10 of the present embodiment is formed with fixed-shaft speed change gear set does not have times keep off Function, that is to say, that it is basic " clutch ", and coupled fixed-shaft speed change gear set is kept off if it is N+1 (meaning N number of forward gear, 1 reverses gear), then entire speed changing assembly only has N+1 gear.
Fig. 2-Fig. 4 is the different modifications of the clutch in vehicle speed variation assembly shown in FIG. 1.Wherein, made in Fig. 2-Fig. 4 Combined type planetary mechanism is identical as combined type planetary mechanism shown in FIG. 1, and equally using arrestment mechanism come to combined type Element in planetary mechanism is controlled, and is differed only in dynamic for connecting first in the combined type planetary mechanism in Fig. 2-4 What the element and arrestment mechanism of power source output shaft, the second power source output shaft and fixed-shaft speed change gear set output shaft were braked Element is different with Fig. 1.It needs further exist for, it is emphasized that Fig. 4 further increases a brake on the basis of Fig. 1 Structure, i.e. Fig. 4 brake the different elements in combined type planetary mechanism using two arrestment mechanisms, so that the first power Source output shaft and/or the power of the second power source output shaft output are more defeated to fixed-shaft speed change gear set than exporting at different rates Shaft realizes " times shelves " function so that original gear of fixed-shaft speed change gear set doubles.
It is the structural schematic diagram of clutch according to a second embodiment of the present invention referring to Fig. 5, Fig. 5.In the present embodiment, from Clutch 20 includes：It connects the first power source output shaft 220 and the second power source output shaft 222 is inputted with fixed-shaft speed change gear set Combined type planetary mechanism 21 between axis 23, and for controlling the element in combined type planetary mechanism 21, so that from First power source output shaft 220 and/or the power of the second power source output shaft 222 output are transferred to through combined type planetary mechanism 21 The control mechanism 24 of fixed-shaft speed change gear set input shaft 23.
In the present embodiment, combined type planetary mechanism 21 is compound by element sharing method by single planetary row and double planet wheel rows of mixing It forms, and specifically includes sun gear 216, the first gear ring 215, the second gear ring 211, the first planetary gear 212, the second planetary gear 214 And planet carrier 213.214 common planet carrier 213 of first planetary gear 212 and the second planetary gear.First planetary gear 212 and sun gear 216 external toothings, and with 215 internal messing of the first gear ring.Sun gear 216, the first planetary gear 212, the first gear ring 215 and planet carrier 213 constitute a single planetary row.Second planetary gear 214 is set between the first planetary gear 212 and the second gear ring 211, and with first 212 external toothing of planetary gear, at the same with 211 internal messing of the second gear ring.Sun gear 216, the first planetary gear 212, the second planetary gear 214, the second gear ring 211 and planet carrier 213 further constitute a double planet wheel rows of mixing.In the present embodiment, planet carrier 213 is by control machine Structure 24 is controlled.Sun gear 216 connects the first power source output shaft 220 and the second power source output shaft 222, the second gear ring 211 connection fixed-shaft speed change gear set input shafts 23.
In the present embodiment, control mechanism 24 is an arrestment mechanism, such as dry brake, and specifically includes brake disc 241 and caliper 242.Brake disc 241 is coaxially fixed on planet carrier 213, and caliper 242 is used to carry out brake disc 241 Selectivity braking.Control by above-mentioned arrestment mechanism to combined type planetary mechanism 21, to reach the transmission and cut-out of power.
When the release of caliper 242, when not constraining brake disc 241, the first power source output shaft 220 and/or the second power source Output shaft 222 drives sun gear 216 to rotate, due to the first planetary gear 212, planet carrier 213, the second planetary gear 214 and first Gear ring 215 is in free state, therefore power is not exported at the second gear ring 211, as " separation " state of ordinary clutch. When control mechanism 24 locks planet carrier 213, the first power source output shaft 220 and/or the second power source output shaft 222 output Power is transferred to the second gear ring 211 through sun gear 216, the first planetary gear 212, the second planetary gear 214, to be input to fixed shaft type Change gear group input shaft 23, as " engagement " state of ordinary clutch.
Fig. 6-Figure 10 is the different modifications of clutch shown in fig. 5.Wherein, the combined type planet used in Fig. 6-Figure 10 Mechanism is identical as combined type planetary mechanism shown in fig. 5, and equally using arrestment mechanism come to the member in combined type planetary mechanism Part is controlled, differ only in the combined type planetary mechanism in Fig. 6-10 for connecting the first power source output shaft, the The element and Fig. 5 that the element and arrestment mechanism of two power source output shafts and fixed-shaft speed change gear set output shaft are braked are It is different.It needs further exist for, it is emphasized that Figure 10 further increases an arrestment mechanism on the basis of Fig. 5, i.e. Figure 10 is used Two arrestment mechanisms brake the different elements in combined type planetary mechanism so that the first power source output shaft and/ Or second the output of power source output shaft power at different rates than exporting to fixed-shaft speed change gear set output shaft, and then make The original gear for obtaining fixed-shaft speed change gear set doubles, that is, realizes " times shelves " function.
First and second embodiment carries out exemplary description, people in the art only as preferred embodiment to the present invention Member can design other clutches using single arrestment mechanism on the basis of above-mentioned combined type planetary mechanism 11 and 21, not It is limited to structure shown in above-mentioned modification.Theoretically, only need to by the first sun gear 115 of first embodiment, the second sun gear 116, Gear ring 111 and planet carrier 113 or by the sun gear 216 of second embodiment, the first gear ring 215, the second gear ring 211 and row Any two in carrier 213 respectively with the first power source output shaft and/or the second power source output shaft and fixed shaft type gear teeth Wheel group input shaft is attached, and is braked to an any other element using arrestment mechanism and the first power source may be implemented Output shaft and/or the second power source output shaft to fixed-shaft speed change gear set input shaft power transmission.
It is the structural schematic diagram of clutch according to a third embodiment of the present invention referring to Figure 11, Figure 11.In the present embodiment, Clutch 30 includes being connected to the first power source output shaft 320 and the second power source output shaft 322 and fixed-shaft speed change gear set Combined type planetary mechanism 31 between input shaft 33, and for controlling the element in combined type planetary mechanism 31, with The power exported from the first power source output shaft 320 and/or the second power source output shaft 322 is set to be passed through combined type planetary mechanism 31 It is handed to the control mechanism 34 of fixed-shaft speed change gear set input shaft 33.
Combined type planetary mechanism 31 is combined by single planetary row and double planet wheel rows of mixing by element sharing method, and is specifically wrapped Include the first sun gear 315, the second sun gear 316, the first planetary gear 312, the second planetary gear 314, gear ring 311 and planet carrier 313, concrete structure is similar with first embodiment shown in FIG. 1, and details are not described herein.
In the present embodiment, control mechanism 34 includes an arrestment mechanism 341 and a clutch 342.Specifically, system Motivation structure 341 is identical as the arrestment mechanism 141 in first embodiment, and clutch 342 includes being separately positioned on two difference portions Driving link on part and driven member, when the driving link of clutch 342 and driven member engagement, clutch drives it to be controlled Two components of system rotate synchronously.
In the present embodiment, the first sun gear 315 is controlled by arrestment mechanism 341 and clutch 342, specific clutch First sun gear 315 is bound selectively to the first power source output shaft 320 and the second power source output shaft 322, brake by 342 Structure 341 then carries out selective braking to the first sun gear 315.In addition, the second sun gear 316 connects the first power source output shaft 320 and the second power source output shaft 322, gear ring 311 connect fixed-shaft speed change gear set input shaft 33.
When clutch 342 is all detached with arrestment mechanism 341, the first power source output shaft 320 and/or the second power source Output shaft 322 drives the rotation of the second sun gear 316.At this point, due to the second planetary gear 314, planet carrier 313, the first planetary gear 312 And first sun gear 315 be in free state, to not export power at gear ring 311, as ordinary clutch " point From " state.When the separation of clutch 342, arrestment mechanism 341 lock the first sun gear 315, the first power source output shaft 320 And/or second power source output shaft 322 input power through the second sun gear 316, the second planetary gear 314, the first planetary gear 312 It is transmitted on gear ring 311, to First Speed ratio output to fixed-shaft speed change gear set input shaft 33.When clutch 342 When engagement, arrestment mechanism 341 detach, the power of the first power source output shaft 320 and/or the input of the second power source output shaft 322 Constant-speed transmission is to the second sun gear 316 and the first sun gear 315, the second sun gear 316, the first sun gear 315, the second row simultaneously Star-wheel 314, the first planetary gear 312 and planet carrier 313 are mutually locked, and then with second speed than driving gear ring 311 to rotate, with Make the power that the first power source output shaft 320 and/or the second power source output shaft 322 export with second speed than output to dead axle Formula change gear group input shaft 33.Above-mentioned two situations are " engagement " state of ordinary clutch.Likewise, in the present embodiment In, it can also realize the half-clutch state of ordinary clutch.Arrestment mechanism 341 only need to be controlled when with First Speed than exporting power Brake disc and caliper between skid, or with second speed than output power when control clutch 342 driving link It skids between driven member.In the present embodiment, when as start clutch in use, it is preferred that passing through arrestment mechanism 341 Combined type planetary mechanism 31 is controlled to transmit power.
Figure 12-Figure 18 is the different modifications of clutch shown in Figure 11.Wherein, the combined type used in Figure 12-Figure 18 Planetary mechanism is identical as combined type planetary mechanism shown in Figure 11, and equally uses at least one arrestment mechanism and a clutch Structure controls the element in combined type planetary mechanism, differs only in the combined type planetary mechanism in Figure 12-18 Element and system for connecting the first power source output shaft, the second power source output shaft and fixed-shaft speed change gear set output shaft The element that motivation structure and clutch are braked and Figure 11 are different.It needs further exist for, it is emphasized that Figure 17-18 further increases An arrestment mechanism is added, i.e. Figure 17-18 is using two arrestment mechanisms to the different elements system in combined type planetary mechanism It is dynamic.
It is the structural schematic diagram of clutch according to a fourth embodiment of the present invention referring to Figure 19, Figure 19.In the present embodiment, Clutch 40 includes being connected to the first power source output shaft 420 and the second power source output shaft 422 and fixed-shaft speed change gear set Combined type planetary mechanism 41 between input shaft 43, and for controlling the element in combined type planetary mechanism 41, with The power exported from the first power source output shaft 420 and/or the second power source output shaft 422 is set to be passed through combined type planetary mechanism 41 It is handed to the control mechanism 44 of fixed-shaft speed change gear set input shaft 43.
Combined type planetary mechanism 41 is combined by single planetary row and double planet wheel rows of mixing by element sharing method, and is specifically wrapped Sun gear 416, the first gear ring 415, the second gear ring 411, the first planetary gear 412, the second planetary gear 414 and planet carrier 413 are included, Its concrete structure is similar with second embodiment shown in fig. 5, and details are not described herein.
In the present embodiment, control mechanism 44 includes an arrestment mechanism 441 and a clutch 442.Specifically, system Motivation structure 441 and clutch 442 in above-described embodiment arrestment mechanism and clutch it is identical, details are not described herein again.Row Carrier 413 is controlled by arrestment mechanism 441, specifically carries out selective braking by arrestment mechanism 441.First gear ring 415 It is controlled by clutch 442, is specifically selectively engaged to the first power source output shaft 420 and/or by clutch 442 Two power source output shafts 422.Sun gear 416 connects the first power source output shaft 420 and/or the second power source output shaft 422, the Two gear rings 411 connect fixed-shaft speed change gear set input shaft 43.
When clutch 442 is all detached with arrestment mechanism 441, the first power source output shaft 420 and/or the second power source Output shaft 422 drives sun gear 416 to rotate, due to the first planetary gear 412, planet carrier 413, the second planetary gear 414 and first Gear ring 415 is in free state, therefore power is not exported at the second gear ring 411, as " separation " state of ordinary clutch. When the separation of clutch 442, arrestment mechanism 441 lock planet carrier 413, the first power source output shaft 420 and/or the second power Source output shaft 422 drives sun gear 416 to rotate, and power is through sun gear 416, the first planetary gear 412, the second planetary gear at this time 414 are transmitted to the second gear ring 411, to First Speed ratio output to fixed-shaft speed change gear set input shaft 43.Work as clutch When the engagement of structure 442, arrestment mechanism 441 detach, the first power source output shaft 420 and/or the second power source output shaft 422 drive too Sun wheel 416 and the first constant velocity rotation simultaneously of gear ring 415, sun gear 416, the first gear ring 415, the second planetary gear 414, the first planet Wheel 412 and planet carrier 413 are mutually locked, thus with second speed than transmission the second gear ring 411 rotation, so that the first power The output power of source output shaft 420 and/or the second power source output shaft 422 is with second speed than output to fixed shaft type change gear Group input shaft 43.Above-mentioned two situations are " engagement " state of ordinary clutch.Likewise, in the present embodiment, it also can be real The half-clutch state of existing ordinary clutch.It only need to be in the brake disc with First Speed than controlling arrestment mechanism 441 when output power It skids between caliper, or in the driving link and driven member with second speed than controlling clutch 442 when output power Between skid.As start clutch in use, it is preferred that pass through arrestment mechanism 441 control combined type planetary mechanism 41 transmit power.
Figure 20-Figure 25 is the different modifications of clutch shown in Figure 19.Wherein, the combined type used in Figure 20-Figure 25 Planetary mechanism is identical as combined type planetary mechanism shown in Figure 19, and equally uses at least one arrestment mechanism and a clutch Structure controls the element in combined type planetary mechanism, differs only in the combined type planetary mechanism in Figure 20-25 Element and system for connecting the first power source output shaft, the second power source output shaft and fixed-shaft speed change gear set output shaft The element that motivation structure and clutch are braked and Figure 19 are different.It needs further exist for, it is emphasized that Figure 23-25 further increases An arrestment mechanism is added, i.e. Figure 23-25 is using two arrestment mechanisms to the different elements system in combined type planetary mechanism It is dynamic.
By the third and fourth embodiment it is found that when there are a clutch and an arrestment mechanism, pass through braking The braking of mechanism and the separation of clutch from the first power source output shaft and/or the second power source output shaft so that export dynamic Power is transferred to fixed-shaft speed change gear set input shaft through combined type planetary mechanism with First Speed ratio；And connecing by clutch It closes and the separation of arrestment mechanism is so that from the first power source output shaft and/or the power of the second power source output shaft output through compound Formula planetary mechanism is transferred to fixed-shaft speed change gear set input shaft with second speed ratio.Third is with fourth embodiment only as excellent Embodiment is selected to carry out exemplary description to the present invention, those skilled in the art can be in above-mentioned combined type planetary mechanism 31 and 41 On the basis of design other clutches using single arrestment mechanisms and single clutch, however it is not limited to tied shown in above-mentioned modification Structure.Theoretically, two elements of above-mentioned combined type planetary mechanism 31 and 41 need to only be simultaneously engaged with to first using clutch The first power may be implemented in power source output shaft and/or the second power source output shaft or fixed-shaft speed change gear set input shaft Source output shaft and/or the second power source output shaft to fixed-shaft speed change gear set input shaft power transmission.
Clutch 30 and the 40 vehicle speed variation assemblies that are formed with fixed-shaft speed change gear set, " clutch " has times keep off (M =2) function, that is to say, that coupled fixed-shaft speed change gear set keeps off if it is N+1 and (means N number of forward gear, 1 is fallen Gear), then theoretically, entire speed changing assembly can have 2 × (N+1) a gears.
More specifically, as " the planetary mechanism clutch " in 3rd embodiment and fourth embodiment is existing common The starting of " clutch ", gearshift function, and have the function of " times keep off (M=2) ", so to realize that the vehicle of 8 forward gears becomes Fast assembly, that just only needs to be connected thereto a fixed-shaft speed change gear set with N+1 (N=4) to gear set.Further, The function of " times keep off (M=3) " may be implemented in modification shown in Figure 17-18 and Figure 23-25.
It is the structural schematic diagram of clutch according to a fifth embodiment of the present invention referring to Figure 26, Figure 26.In the present embodiment, Clutch 50 includes being connected to the first power source output shaft 520 and/or the second power source output shaft 522 and fixed shaft type change gear Combined type planetary mechanism 51 between group input shaft 53, and for controlling the element in combined type planetary mechanism 51, So that the power exported from the first power source output shaft 520 and/or the second power source output shaft 522 is through combined type planetary mechanism 51 It is transferred to the control mechanism 54 of fixed-shaft speed change gear set input shaft 53.
Combined type planetary mechanism 51 is combined by single planetary row and double planet wheel rows of mixing by element sharing method, and is specifically wrapped Include the first sun gear 515, the second sun gear 516, the first planetary gear 512, the second planetary gear 514, gear ring 511 and planet carrier 513, concrete structure is similar with first embodiment shown in FIG. 1, and details are not described herein.
In the present embodiment, control mechanism 54 includes an arrestment mechanism 541 and the first clutch 542 and the second clutch Mechanism 543.First sun gear 515 is controlled by arrestment mechanism 541, specifically carries out selective braking by arrestment mechanism 541.Second too Sun wheel 516 is controlled by the first clutch 542, is specifically selectively engaged to the first power source and is exported by the first clutch 542 Axis 520 and/or the second power source output shaft 522, planet carrier 513 is controlled by the second clutch 543, specifically by the second clutch Structure 543 is selectively engaged to the first power source output shaft 520 and/or the second power source output shaft 522.Gear ring 511 connects dead axle Formula change gear group input shaft 53.
When the first clutch 542 and the second clutch 543 are all in discrete state, combined type planetary mechanism 51 The first power source output shaft 520 and/or the power of the second power source output shaft 522 output can not be accessed, thus at gear ring 511 not Export power, as " separation " state of ordinary clutch.When the first clutch 542 engages, arrestment mechanism 541 is braked, together When the second clutch 543 when being in discrete state, the first power source output shaft 520 and/or the second power source output shaft 522 are defeated The power gone out is transferred to the second sun gear 516 through the first clutch 542.And since arrestment mechanism 541 locks the first sun gear 515, power is after the second sun gear 516, the second planetary gear 514, the first planetary gear 512 with First Speed than output to gear ring 511, to make the power that the first power source output shaft 520 and/or the second power source output shaft 522 export through combined type planet machine Structure 51 is transferred to fixed-shaft speed change gear set input shaft 53 with First Speed ratio.When the engagement of the second clutch 543, arrestment mechanism 541 brakings, while when the first clutch 542 is in discrete state, the first power source output shaft 520 and/or the second power source The power that output shaft 522 exports is transferred to planet carrier 513 through the second clutch 543.Also due to arrestment mechanism 541 locked the One sun gear 515, power after planet carrier 513, the first planetary gear 512 with second speed than output to gear ring 511, to make the One power source output shaft 520 and/or the power of the second power source output shaft 522 output are fast with second through combined type planetary mechanism 51 Degree ratio is transferred to fixed-shaft speed change gear set input shaft 53.When the first clutch 542 is all engaged with the second clutch 543, When arrestment mechanism 541 is in discrete state simultaneously, the first power source output shaft 520 and/or the output of the second power source output shaft 522 Power by the first clutch 542 and the second clutch 543 simultaneously constant-speed transmission to the second sun gear 516 and planet carrier 513.At this point, the second sun gear 516, the second planetary gear 514, planet carrier 513, the first planetary gear 512 are mutually locked, and then with the Three speed are than driving gear ring 511 to rotate, to make the first power source output shaft 520 and/or the second power source output shaft 522 export Power fixed-shaft speed change gear set input shaft 53 is transferred to third speed ratio through combined type planetary mechanism 51.Above-mentioned three kinds of shapes State is equivalent to " engagement " state of ordinary clutch.In addition, when the first clutch 542 or the second clutch 543 engage, but When caliper (not indicating) braking in arrestment mechanism 541 does not lock brake disc (not indicating), between caliper and brake disc Skid, be equivalent to " half-clutch " state of ordinary clutch, at this time still can transmitting portions engine power.It can certainly lead to Cross between the first clutch 542 of control and/or the driving link and driven member of the second clutch 543 skid realize " half from Close " state.It is being controlled as start clutch in use, coordinating it is preferable to use the first clutch 542 and arrestment mechanism 541 Combined type planetary mechanism 51 transmits power.
The vehicle speed variation assembly that the clutch 50 of the present embodiment is formed with fixed-shaft speed change gear set, " clutch " has The function of times keep off (M=3), that is to say, that coupled fixed-shaft speed change gear set (means N number of advance if it is N+1 gears Gear, 1 reverses gear), then theoretically, entire speed changing assembly can have 3 × (N+1) a gears.
More specifically, as starting of " planetary mechanism clutch " in the present embodiment existing common " clutch ", changing Function is kept off, and has the function of " times keep off (M=3) ", so to realize the vehicle speed variation assembly of 9 forward gears, that is just only needed It is connected thereto a fixed-shaft speed change gear set with N+1 (N=3) to gear set.
Such speed changing assembly equally rises to 9 gears, shift time is essentially the same, shift quality compared with 9AT from 1 gear It is essentially the same.And manufacturing cost and speed changing assembly complexity are well below 9 gear AT.
It is the structural schematic diagram of clutch according to a sixth embodiment of the present invention referring to Figure 27, Figure 27.In the present embodiment, Clutch 60 includes being connected to the first power source output shaft 620 and the second power source output shaft 622 and fixed-shaft speed change gear set Combined type planetary mechanism 61 between input shaft 63, and for controlling the element in combined type planetary mechanism 61, with The power exported from the first power source output shaft 620 and/or the second power source output shaft 622 is set to be passed through combined type planetary mechanism 61 It is handed to the control mechanism 64 of fixed-shaft speed change gear set input shaft 63.
Combined type planetary mechanism 61 is combined by single planetary row and double planet wheel rows of mixing by element sharing method, and is specifically wrapped Include the first sun gear 615, the second sun gear 616, the first planetary gear 612, the second planetary gear 614, gear ring 611 and planet carrier 613, concrete structure is similar with first embodiment shown in FIG. 1, and details are not described herein.
With the 5th embodiment institute it is similar, in the present embodiment, control mechanism 64 include the first clutch 642, second from It closes mechanism 643 and arrestment mechanism 641 forms.But with the 5th embodiment the difference is that in the present embodiment, the first clutch Structure 642 controls the first sun gear 615, specifically by the first sun gear 615 selectively engage to the first power source output shaft 620 and/ Or the second power source output shaft 622, the second clutch 643 control the second sun gear 616, specifically select the second sun gear 616 Selecting property is bonded to the first power source output shaft 620 and/or the second power source output shaft 622, and arrestment mechanism 641 controls gear ring 611, Selective braking specifically is carried out to gear ring 611, and planet carrier 613 then connects fixed-shaft speed change gear set input shaft 63.
When the first clutch 642 and the second clutch 643 are all in discrete state, combined type planetary mechanism 61 The first power source output shaft 620 and/or the power of the second power source output shaft 622 output can not be accessed, at planet carrier 613 Do not export power, as " separation " state of ordinary clutch.When the first clutch 642 engages, arrestment mechanism 641 is braked, When the second clutch 643 is in discrete state simultaneously, the first power source output shaft 620 and/or the second power source output shaft 622 The power of output is transferred to the first sun gear 615 through the first clutch 642.Since arrestment mechanism 641 locks gear ring 611, move Power is through the first sun gear 615, the first planetary gear 612 and planet carrier 613 with First Speed than output to fixed shaft type change gear Group input shaft 63.When the second clutch 643 engages, arrestment mechanism 641 is braked, while the first clutch 642 is in separation When state, the power of the first power source output shaft 620 and/or the output of the second power source output shaft 622 is through the second clutch 643 It is transferred to the second sun gear 616.Since arrestment mechanism 641 locks gear ring 611, power is through the second sun gear 616, the second planetary gear 614, the first planetary gear 612 and planet carrier 613 are with second speed ratio output to fixed-shaft speed change gear set input shaft 63.When One clutch 642 is all engaged with the second clutch 643, while when arrestment mechanism 641 is in discrete state, the first power source Output shaft 620 and/or the power of the second power source output shaft 622 output pass through the first clutch 642 and the second clutch 643 simultaneously constant-speed transmission to the first sun gear 615 and the second sun gear 616.At this point, the first sun gear 615, the second sun gear 616, the first planetary gear 612 and the second planetary gear 614 are mutually locked, and then drive planet carrier 613 with third speed than rotating, from And make the power that the first power source output shaft 620 and/or the second power source output shaft 622 export through combined type planetary mechanism 61 with Third speed ratio is transferred to fixed-shaft speed change gear set input shaft 43.Above-mentioned three kinds of states are equivalent to " engagement " of ordinary clutch State.As start clutch in use, it is preferred that controlling combined type by the second clutch 643 and arrestment mechanism 641 Planetary mechanism 61 transmits power.
Figure 28-Figure 31 is the different modifications of clutch shown in Figure 26 and Figure 27.Wherein, used in Figure 28-Figure 31 Combined type planetary mechanism is identical as combined type planetary mechanism shown in Figure 26 and Figure 27, and equally uses an arrestment mechanism and two A clutch controls the element in combined type planetary mechanism, differs only in the combined type in figure Figure 28-Figure 31 It is used to connect the first power source output shaft, the second power source output shaft and fixed-shaft speed change gear set output shaft in planetary mechanism Element and the element braked of arrestment mechanism and clutch and Figure 26 and Figure 27 it is different.
It is the structural schematic diagram of clutch according to a seventh embodiment of the present invention referring to Figure 32, Figure 32.In the present embodiment, Clutch 70 includes being connected to the first power source output shaft 720 and the second power source output shaft 722 and fixed-shaft speed change gear set Combined type planetary mechanism 71 between input shaft 73, and for controlling the element in combined type planetary mechanism 71, with The power exported from the first power source output shaft 720 and/or the second power source output shaft 722 is set to be passed through combined type planetary mechanism 71 It is handed to the control mechanism 74 of fixed-shaft speed change gear set input shaft 73.
Combined type planetary mechanism 71 is combined by single planetary row and double planet wheel rows of mixing by element sharing method, and is specifically wrapped Sun gear 716, the first gear ring 715, the second gear ring 711, the first planetary gear 712, the second planetary gear 714 and planet carrier 713 are included, Its concrete structure is similar with second embodiment shown in fig. 5, and details are not described herein.
In the present embodiment, control mechanism 74 includes an arrestment mechanism 741 and two clutches 742,743.Planet Frame 713 is controlled by the second clutch 743, is specifically selectively engaged to the first power source output shaft by the second clutch 743 720 and the second power source output shaft 722, sun gear 716 is controlled by the first clutch 742, specifically by the first clutch 742 It selectively engages to the first power source output shaft 720 and the second power source output shaft 722, the first gear ring 715 is by arrestment mechanism 741 Control, specifically carries out selective braking by arrestment mechanism 741.Second gear ring 711 connects fixed-shaft speed change gear set input shaft 73.
When the first clutch 742 and the second clutch 743 are all in discrete state, the first power source output shaft 720 and/or second power source output shaft 722 without normal direction combined type planetary mechanism 71 export power, at the second gear ring 711 not Export power, as " separation " state of ordinary clutch.When the engagement of the first clutch 742, the braking of arrestment mechanism 741, together When the second clutch 743 when being in discrete state, the first power source output shaft 720 and/or the second power source output shaft 722 are defeated The power gone out is transferred to sun gear 716 via the first clutch 742.Since arrestment mechanism 741 locks the first gear ring 715, the One power source output shaft 720 and/or the power of the second power source output shaft 722 output are through sun gear 716, the first planetary gear 712 And second be transferred to the second gear ring 711 after planetary gear 714 with First Speed ratio, to make the first power source output shaft 720 and/ Or second power source output shaft 722 export power fixed shaft type speed change is transferred to First Speed ratio through combined type planetary mechanism 71 Gear unit input shaft 73.When the engagement of the second clutch 743, the braking of arrestment mechanism 741, while the first clutch 742 is in When discrete state, the power of the first power source output shaft 720 and/or the output of the second power source output shaft 722 is via the second clutch Mechanism 743 is transferred to planet carrier 713.Also due to arrestment mechanism 741 locks the first gear ring 715, the first power source output shaft 720 And/or second power source output shaft 722 export power through planet carrier 713, the first planetary gear 712 and the second planetary gear 714 The second gear ring 711 is transferred to second speed ratio afterwards, to make the first power source output shaft 720 and/or the second power source export The power that axis 722 exports is transferred to fixed-shaft speed change gear set input shaft 73 through combined type planetary mechanism 71 with second speed ratio. When the first clutch 742 is all engaged with the second clutch 743, while arrestment mechanism 741 is in discrete state, first is dynamic Power source output shaft 720 and/or the power of the second power source output shaft 722 output are through the first clutch 742 and the second clutch 743 constant-speed transmission of structure is to sun gear 716 and planet carrier 713.At this point, sun gear 716, the first planetary gear 712, the second planetary gear 714 and planet carrier 713 it is mutually locked, and then the rotation of the second gear ring 711 is driven with third speed, to keep the first power source defeated Shaft 720 and/or the power of the second power source output shaft 722 output are transferred to through combined type planetary mechanism 71 with third speed ratio Fixed-shaft speed change gear set input shaft 73.Above-mentioned three kinds of states are equivalent to " engagement " state of ordinary clutch.As starting Clutch by the first clutch 742 and arrestment mechanism 741 to control the transmission of combined type planetary mechanism 71 in use, it is preferred that moved Power.
By the five, the 6th and the 7th embodiment it is found that when there are two clutches and an arrestment mechanism, pass through Two clutches coordinate with arrestment mechanism respectively so that defeated from the first power source output shaft and/or the second power source output shaft The power gone out is transferred to fixed-shaft speed change gear set input shaft through combined type planetary mechanism with First Speed ratio and second speed ratio, And pass through the cooperation between two clutches so that export from the first power source output shaft and/or the second power source output shaft Power fixed-shaft speed change gear set input shaft is transferred to third speed ratio through combined type planetary mechanism.5th, the 6th and Seven embodiments carry out exemplary description only as preferred embodiment to the present invention, theoretically for, need to only ensure the 5th implementation First sun in the first sun gear 515, the second sun gear 516, planet carrier 513, gear ring 511 or sixth embodiment in example Take turns the 615, second sun gear 616, planet carrier 613, gear ring 611 or sun gear 716 in the 7th embodiment, the first gear ring 715, Arbitrary three elements in second gear ring 711, planet carrier 713 are controlled by said one and two clutches respectively, and A remaining element connects the first power source output shaft and/or above-mentioned function may be implemented in the second power source output shaft.It needs It is noted that since the clutch of the present invention is used as independent clutch, in the above-described embodiments, the 5th implements It is defeated to be transferred to fixed-shaft speed change gear set with the 7th embodiment with First Speed ratio, second speed ratio and third speed ratio for example The power of the power and the first power source output shaft and/or the output of the second power source output shaft that enter axis is to rotate in same direction, and the 6th is real It applies in example, with First Speed than the power and the first power source with third speed than being transferred to fixed-shaft speed change gear set input shaft Output shaft and/or the power of the second power source output shaft output are to rotate in same direction, and fixed shaft type speed change is transferred to second speed ratio The power of gear unit input shaft and the power of the first power source output shaft and/or the second power source output shaft output are reversed turn It is dynamic.
It is the structural schematic diagram of clutch according to a eighth embodiment of the present invention referring to Figure 33, Figure 33.In the present embodiment, Clutch 80 includes being connected to the first power source output shaft 820 and the second power source output shaft 822 and fixed-shaft speed change gear set Combined type planetary mechanism 81 between input shaft 83, and for controlling the element in combined type planetary mechanism 81, with The power exported from the first power source output shaft 820 and/or the second power source output shaft 822 is set to be passed through combined type planetary mechanism 81 It is handed to the control mechanism 84 of fixed-shaft speed change gear set input shaft 83.
Combined type planetary mechanism 81 is combined by single planetary row and double planet wheel rows of mixing by element sharing method, and is specifically wrapped Include the first sun gear 815, the second sun gear 816, the first planetary gear 812, the second planetary gear 814, gear ring 811 and planet carrier 813, concrete structure is similar with first embodiment shown in FIG. 1, and details are not described herein.
In the present embodiment, control mechanism 84 includes two arrestment mechanisms 841,842 and two clutches 843,844. Specifically, two arrestment mechanisms include the first arrestment mechanism 841 and the second arrestment mechanism 842, two clutches include the One clutch 843 and the second clutch 844.The structure of arrestment mechanism and clutch such as above-described embodiment, herein not It repeats again.
In the present embodiment, the first sun gear 815 is controlled by the first arrestment mechanism 841, specifically by the first arrestment mechanism 841 Selective braking is carried out, the second sun gear 816 is controlled by the first clutch 843, specifically by 843 selectivity of the first clutch It is bonded to the first power source output shaft 820 and the second power source output shaft 822, planet carrier 813 is by the second clutch 844 and Two arrestment mechanisms 842 control, and specifically carry out selective braking by the second arrestment mechanism 842, and selected by the second clutch 844 Property is bonded to the first power source output shaft 820 and the second power source output shaft 822.Gear ring 811 connects fixed-shaft speed change gear set Input shaft 83.
When the first clutch 843 and the second clutch 844 are all in discrete state, combined type planetary mechanism 81 The first power source output shaft 820 and/or the power of the second power source output shaft 822 output can not be accessed, thus at gear ring 811 not Export power, as " separation " state of ordinary clutch.When the engagement of the first clutch 843, the first arrestment mechanism 841 system It is dynamic, while when other clutches are in discrete state with arrestment mechanism, the first power source output shaft 820 and/or the second power The power that source output shaft 822 exports is transferred to the second sun gear 816 through the first clutch 843.Due to the first arrestment mechanism 841 Locked first sun gear 815, power is after the second sun gear 816, the second planetary gear 814, the first planetary gear 812 with First Speed Than output to gear ring 811, to the power warp for making the first power source output shaft 820 and/or the second power source output shaft 822 export Combined type planetary mechanism 81 is transferred to fixed-shaft speed change gear set input shaft 83 with First Speed ratio.When the second clutch 844 Engagement, the braking of the first arrestment mechanism 841, while when other clutches and arrestment mechanism are in discrete state, the first power source Output shaft 820 and/or the power of the second power source output shaft 822 output are transferred to planet carrier 813 through the second clutch 844. Also due to the first arrestment mechanism 841 locks the first sun gear 815, power is after planet carrier 813, the first planetary gear 812 with the Two speed are than output to gear ring 811, to make the first power source output shaft 820 and/or the second power source output shaft 822 export Power is transferred to fixed-shaft speed change gear set input shaft 83 through combined type planetary mechanism 81 with second speed ratio.When the first clutch The engagement of structure 843, the braking of the second arrestment mechanism 842, while when other clutches and arrestment mechanism be in discrete state, first moves Power source output shaft 820 and/or the power of the second power source output shaft 822 output are transferred to second too through the first clutch 843 Sun wheel 816.And since planet carrier 813 is locked by the second arrestment mechanism 842, power is through the second sun gear 816, the second planet Take turns after the 814, first planetary gear 812 with third speed than output to gear ring 811, to make the first power source output shaft 820 and/or The power of second power source output shaft 822 output is transferred to fixed shaft type gear teeth through combined type planetary mechanism 81 with third speed ratio Wheel group input shaft 83.When the first clutch 843 is all engaged with the second clutch 844, while arrestment mechanism 841,842 is in When discrete state, the power of the first power source output shaft 820 and/or the output of the second power source output shaft 822 passes through the first clutch Mechanism 843 and the second clutch 844 simultaneously constant-speed transmission to the second sun gear 816 and planet carrier 813.At this point, second sun It is mutually locked to take turns the 816, second planetary gear 814, the first planetary gear 812 and planet carrier 813, and then with fourth speed than driving gear ring 811 rotations, to make the power that the first power source output shaft 820 and/or the second power source output shaft 822 export through combined type row Star mechanism 81 is transferred to fixed-shaft speed change gear set input shaft 83 with fourth speed ratio.Above-mentioned four kinds of states are equivalent to common clutch " engagement " state of device.Wherein, dead axle is transferred to First Speed ratio, second speed ratio, third speed ratio and fourth speed ratio The power and the first power source output shaft 820 of formula change gear group input shaft and/or the second power source output shaft 822 export dynamic Power is to rotate in same direction.As start clutch in use, it is preferred that passing through the first clutch 843 and the first arrestment mechanism 841 Power is transmitted to control combined type planetary mechanism 81.
It is the structural schematic diagram of clutch according to a ninth embodiment of the present invention referring to Figure 34, Figure 34.In the present embodiment, Clutch 9 includes being connected to the first power source output shaft 920 and the second power source output shaft 922 and fixed-shaft speed change gear set is defeated Enter the combined type planetary mechanism 91 between axis 93, and for controlling the element in combined type planetary mechanism 91, so that The power exported from the first power source output shaft 920 and/or the second power source output shaft 922 is transmitted through combined type planetary mechanism 91 To the control mechanism 94 of fixed-shaft speed change gear set input shaft 93.
Combined type planetary mechanism 91 is combined by single planetary row and double planet wheel rows of mixing by element sharing method, and is specifically wrapped Sun gear 916, the first gear ring 915, the second gear ring 911, the first planetary gear 912, the second planetary gear 914 and planet carrier 913 are included, Its concrete structure is similar with second embodiment shown in Fig. 2, and details are not described herein.
In the present embodiment, control mechanism 94 includes two arrestment mechanisms 941,942 and two 943,944 groups of clutches At.Specifically, two arrestment mechanisms 941,942 include the first arrestment mechanism 941 and the second arrestment mechanism 942, two clutches Mechanism 943,944 includes the first clutch 943 and the second clutch 944.The structure of arrestment mechanism and clutch is such as Above-described embodiment, details are not described herein again.
Planet carrier 913 is controlled by the second arrestment mechanism 942 and the second clutch 944, specifically by the second arrestment mechanism 942 Selective braking is carried out, and is selectively engaged to the first power source output shaft 920 and the second power source by the second clutch 944 Output shaft 922, sun gear 916 are controlled by the first clutch 943, are specifically selectively engaged to by the first clutch 943 One power source output shaft 920 and the second power source output shaft 922, the first gear ring 915 are controlled by the first arrestment mechanism 941, specifically Selective braking is carried out by the first arrestment mechanism 941.Second gear ring 911 connects fixed-shaft speed change gear set input shaft 93.
When the first clutch 943 and the second clutch 944 are all in discrete state, the first power source output shaft 920 and/or second power source output shaft 922 without normal direction combined type planetary mechanism 91 export power, at the second gear ring 911 not Export power, as " separation " state of ordinary clutch.When the engagement of the first clutch 943, the first arrestment mechanism 941 system It is dynamic, while when other clutches are in discrete state with arrestment mechanism, the first power source output shaft 920 and/or the second power The power that source output shaft 922 exports is transferred to sun gear 916 via the first clutch 943.And due to the first arrestment mechanism 941 The power of locked first gear ring 915, the first power source output shaft 920 and/or the output of the second power source output shaft 922 is through sun gear 916, second gear ring 911 is transferred to First Speed ratio after the first planetary gear 912 and the second planetary gear 914, to make first The power that power source output shaft 920 and/or the second power source output shaft 922 export is through combined type planetary mechanism 91 with First Speed Than being transferred to fixed-shaft speed change gear set input shaft 93.When the engagement of the second clutch 944, the braking of the first arrestment mechanism 941, together When other clutches and arrestment mechanism when be in discrete state, the first power source output shaft 920 and/or the second power source export The power that axis 922 exports is transferred to planet carrier 913 via the second clutch 944.Also due to the first arrestment mechanism 941 is locked First gear ring 915, the first power source output shaft 920 and/or the second power source output shaft 922 output power through planet carrier 913, Second gear ring 911 is transferred to second speed ratio after first planetary gear 912 and the second planetary gear 914, to make the first power Source output shaft 920 and/or the power of the second power source output shaft 922 output are passed through combined type planetary mechanism 91 with second speed ratio It is handed to fixed-shaft speed change gear set input shaft 93.When the engagement of the first clutch 943, the braking of the second arrestment mechanism 942, while its When his clutch is in discrete state with arrestment mechanism, the first power source output shaft 920 and/or the second power source output shaft The power of 922 outputs is transferred to sun gear 916 via the first clutch 943.Since the second arrestment mechanism 942 locks planet carrier 913, therefore the first power source output shaft 920 and/or the power of the second power source output shaft 922 output are through sun gear 916, first Second gear ring 911 is transferred to third speed ratio after planetary gear 912 and the second planetary gear 914, to keep the first power source defeated Shaft 920 and/or the power of the second power source output shaft 922 output are transferred to through combined type planetary mechanism 91 with third speed ratio Fixed-shaft speed change gear set input shaft 93.When the first clutch 943 is all engaged with the second clutch 944, while brake When structure 941,942 is in discrete state, the power of the first power source output shaft 920 and/or the output of the second power source output shaft 922 Through the first clutch 943 and 944 constant-speed transmission of the second clutch to sun gear 916 and planet carrier 913.At this point, sun gear 916, the first planetary gear 912, planet carrier 913, the second planetary gear 914 are mutually locked, and then with fourth speed than driving the second tooth 911 rotation of circle, to make the power that the first power source output shaft 920 and/or the second power source output shaft 922 export through combined type Planetary mechanism 91 is transferred to fixed-shaft speed change gear set input shaft 93 with fourth speed ratio.Above-mentioned four kinds of states be equivalent to commonly from " engagement " state of clutch.Wherein, it is fixed to be transferred to First Speed ratio, second speed ratio, third speed ratio and fourth speed ratio What the power and the first power source output shaft 920 of shaft type change gear group input shaft and/or the second power source output shaft 922 exported Power is to rotate in same direction.
It is the structural schematic diagram of clutch according to a tenth embodiment of the present invention referring to Figure 35, Figure 35.In the present embodiment, Clutch 100 includes being connected to the first power source output shaft 1020 and the second power source output shaft 1022 and fixed shaft type change gear Combined type planetary mechanism 1010 between group input shaft 1030, and for being carried out to the element in combined type planetary mechanism 1010 Control, so that the power exported from the first power source output shaft 1020 and/or the second power source output shaft 1022 is through combined type row Star mechanism 1010 is transferred to the control mechanism 1040 of fixed-shaft speed change gear set input shaft 1030.
Combined type planetary mechanism 1010 is combined by single planetary row and double planet wheel rows of mixing by element sharing method, and specific Including the first sun gear 1015, the second sun gear 1016, the first planetary gear 1012, the second planetary gear 1014, gear ring 1011 and Planet carrier 1013, concrete structure is similar with first embodiment shown in FIG. 1, and details are not described herein.
In the present embodiment, control mechanism 1040 include two arrestment mechanisms 1041,1042 and two clutches 1043, 1045.In the present embodiment, the first sun gear 1015 is controlled by the first arrestment mechanism 1041 and the second clutch 1045, specifically Selective braking is carried out by the first arrestment mechanism 1041, and is selectively engaged by the second clutch 1045 defeated to the first power source Shaft 1020 and the second power source output shaft 1022.Second sun gear 1016 is controlled by the first clutch 1043, specifically by One clutch 1043 is selectively engaged to the first power source output shaft 1020 and the second power source output shaft 1022.Planet carrier 1013 are controlled by the second arrestment mechanism 1042, specifically carry out selective braking by the second arrestment mechanism 1042.Gear ring 1011 connects Fixed-shaft speed change gear set input shaft 1030.
When the first clutch 1043 and the second clutch 1045 are all in discrete state, combined type planetary mechanism 1010 can not access the power of the first power source output shaft 1020 and/or the output of the second power source output shaft 1022, to gear ring Power, as " separation " state of ordinary clutch are not exported at 1011.When the engagement of the first clutch 1043, the second brake Structure 1042 is braked, while when other clutches and arrestment mechanism are in discrete state, the first power source output shaft 1020 and/or The power of second power source output shaft 1022 output is transferred to the second sun gear 1016 through the first clutch 1043.And due to row Carrier 1013 is locked by the second arrestment mechanism 1042, therefore power is through the second sun gear 1016, the second planetary gear 1014, the first row With First Speed than exporting to gear ring 1011, to make the first power source output shaft 1020 and/or the second power after star-wheel 1012 The power that source output shaft 1022 exports is transferred to fixed-shaft speed change gear set through combined type planetary mechanism 1010 with First Speed ratio Input shaft 1030.When the engagement of the second clutch 1045, the braking of the second arrestment mechanism 1042, while other clutches and braking When mechanism is in discrete state, the power of the first power source output shaft 1020 and/or the output of the second power source output shaft 1022 passes It is handed to the first sun gear 1015.And since the second arrestment mechanism 1042 locks planet carrier 1013, power is through the first sun gear 1015 and first planetary gear 1012 exported to gear ring 1011 with second speed ratio, to make the first power source output shaft 1020 and/ Or second power source output shaft 1022 export power fixed shaft type is transferred to second speed ratio through combined type planetary mechanism 1010 Change gear group input shaft 1030.When the engagement of the first clutch 1043, the braking of the first arrestment mechanism 1041, while other clutches When mechanism is in discrete state with arrestment mechanism, the first power source output shaft 1020 and/or the second power source output shaft 1022 are defeated The power gone out is transferred to the second sun gear 1016 through the first clutch 1043.And due to the first arrestment mechanism 1041 locked first Sun gear 1015, power is after the second sun gear 1016, the second planetary gear 1014, the first planetary gear 1012 with third speed than defeated Go out to gear ring 1011, to the power warp for making the first power source output shaft 1020 and/or the second power source output shaft 1022 export Combined type planetary mechanism 1010 is transferred to fixed-shaft speed change gear set input shaft 1030 with third speed ratio.When the first clutch 1043 all engage with the second clutch 1045, while when arrestment mechanism is in discrete state, the first power source output shaft 1020 and/or second power source output shaft 1022 export power pass through the first clutch 1043 and the second clutch 1045 Constant-speed transmission is to the second sun gear 1015 and the second sun gear 1016 simultaneously.At this point, planet carrier 1013, the second planetary gear 1014, First planetary gear 1012 is mutually locked, and then with fourth speed than driving gear ring 1011 to rotate, to make the first power source export Axis 1020 and/or the power of the second power source output shaft 1022 output are transmitted through combined type planetary mechanism 1010 with fourth speed ratio To fixed-shaft speed change gear set input shaft 1030.
Above-mentioned four kinds of states are equivalent to " engagement " state of ordinary clutch.Wherein, with First Speed ratio, third speed ratio Power and the first power source output shaft 1020 and/or second with fourth speed than being transferred to fixed-shaft speed change gear set input shaft The power that power source output shaft 1022 exports is to rotate in same direction, and fixed-shaft speed change gear set input shaft is transferred to second speed ratio Power and the first power source output shaft and/or the second power source output shaft output power be rotate backward.
It is the structural schematic diagram of clutch according to a 11th embodiment of the present invention referring to Figure 36, Figure 36.In the present embodiment In, clutch 110 includes being connected to the first power source output shaft 1120 and the second power source output shaft 1122 and fixed shaft type speed change Combined type planetary mechanism 1110 between gear unit input shaft 1130, and for the element in combined type planetary mechanism 1110 It is controlled, so that the power exported from the first power source output shaft 1120 and/or the second power source output shaft 1122 is through compound Formula planetary mechanism 1110 is transferred to the control mechanism 1140 of fixed-shaft speed change gear set input shaft 1130.
Combined type planetary mechanism 1110 is combined by single planetary row and double planet wheel rows of mixing by element sharing method, and specific Including sun gear 1116, the first gear ring 1115, the second gear ring 1111, the first planetary gear 1112, the second planetary gear 1114 and row Carrier 1113, specifically similar with second embodiment shown in Fig. 2, details are not described herein.
In the present embodiment, control mechanism 1140 by two arrestment mechanisms 1141,1142 and two clutches 1143, 1145 compositions.Specifically, arrestment mechanism 1141,1142 includes the first arrestment mechanism 1141 and the second arrestment mechanism 1142, from It includes the first clutch 1143 and the second clutch 1145 to close mechanism 1143,1145.
Sun gear 1116 is controlled by the first clutch 1143, is specifically selectively engaged to by the first clutch 1143 One power source output shaft 1120 and the second power source output shaft 1122, the first gear ring 1115 is by the first arrestment mechanism 1141 and second Clutch 1145 controls, and specifically binds selectively to the first power source output shaft 1120 and second by the second clutch 1145 Power source output shaft 1122, and selective braking is carried out by the first arrestment mechanism 1141, planet carrier 1113 is by the second arrestment mechanism 1142 controls, specifically carry out selective braking by the second arrestment mechanism 1142.Second gear ring 1111 connects fixed shaft type change gear Group input shaft 1130.
When the first clutch 1143 and the second clutch 1145 are all in discrete state, the output of the first power source Axis 1120 and/or the second power source output shaft 1122 export power without normal direction combined type planetary mechanism 1110, to the second gear ring Power, as " separation " state of ordinary clutch are not exported at 1111.When the engagement of the first clutch 1143, the second brake Structure 1142 is braked, while when other clutches and arrestment mechanism are in discrete state, the first power source output shaft 1120 and/or The power of second power source output shaft 1122 output is transferred to sun gear 1116 via the first clutch 1143.And due to second Arrestment mechanism 1142 locks planet carrier 1113, therefore the first power source output shaft 1120 and/or the second power source output shaft 1122 The power of output is transferred to after sun gear 1116, the first planetary gear 1112 and the second planetary gear 1114 with First Speed ratio Two gear rings 1111, to make the power that the first power source output shaft 1120 and/or the second power source output shaft 1122 export through multiple Box-like planetary mechanism 1110 is transferred to fixed-shaft speed change gear set input shaft 1130 with First Speed ratio.When the second clutch 1145 engagements, the braking of the second arrestment mechanism 1142, while when other clutches and arrestment mechanism be in discrete state, first moves Power source output shaft 1120 and/or the power of the second power source output shaft 1122 output are transferred to first through the second clutch 1145 In gear ring 1115.And since the second arrestment mechanism 1142 locks planet carrier 1113.Power is through the first gear ring 1115, the first planetary gear 1112, the second planetary gear 1114 is exported with second speed ratio to the second gear ring 1111, to make the first power source output shaft 1120 And/or second power source output shaft 1122 export power dead axle is transferred to second speed ratio through combined type planetary mechanism 1110 Formula change gear group input shaft 1130.When the first clutch 1143 engagement, the first arrestment mechanism 1141 braking, while other from When conjunction mechanism is in discrete state with arrestment mechanism, the first power source output shaft 1120 and/or the second power source output shaft 1122 The power of output is transferred to sun gear 1116 via the first clutch 1143.Since the first arrestment mechanism 1141 locks the first tooth The power of circle 1115, the first power source output shaft 1120 and/or the output of the second power source output shaft 1122 is through sun gear 1116, the Second gear ring 1111 is transferred to third speed ratio after one planetary gear 1112 and the second planetary gear 1114, to make the first power The power that source output shaft 1120 and/or the second power source output shaft 1122 export is through combined type planetary mechanism 1110 with third speed Than being transferred to fixed-shaft speed change gear set input shaft 1130.When the first clutch 1143 and the second clutch 1145 all connect It closes, while when other clutches and arrestment mechanism are in discrete state, the first power source output shaft 1120 and/or the second power The power that source output shaft 1122 exports is through the first clutch 1143 and 1145 constant-speed transmission of the second clutch to sun gear 1116 and first gear ring 1115.At this point, sun gear 1116, planet carrier 1113, the first planetary gear 1112 and the second planetary gear 1114 It is mutually locked, and then with fourth speed than driving the rotation of the second gear ring 1111, to make the first power source output shaft 1120 and/or The power of second power source output shaft 1122 output is transferred to fixed shaft type with fourth speed ratio through combined type planetary mechanism 1110 and becomes Fast gear unit input shaft 1130.
Above-mentioned four kinds of states are equivalent to " engagement " state of ordinary clutch.Wherein, with First Speed ratio, third speed ratio Power and the first power source output shaft 1120 and/or second with fourth speed than being transferred to fixed-shaft speed change gear set input shaft The power that power source output shaft 1122 exports is to rotate in same direction, and fixed-shaft speed change gear set input shaft is transferred to second speed ratio Power and the first power source output shaft and/or the second power source output shaft output power be rotate backward.
Figure 37 and Figure 38 is the different modifications of clutch shown in Figure 33 and 36.Figure 37 and Figure 38 is equally using two brakings Mechanism and two clutches control the element in combined type planetary mechanism, differ only in Figure 37 and Figure 38 It is used to connect the first power source output shaft, the second power source output shaft and fixed-shaft speed change gear set in combined type planetary mechanism The element and Figure 33 and 36 that the element and arrestment mechanism and clutch of output shaft are braked are different.
By the 8th to the 11st embodiment it is found that when there are two clutches and two arrestment mechanisms, pass through two A clutch coordinates with one in two arrestment mechanisms respectively so that from the first power source output shaft and/or the second power The power of source output shaft output is transferred to fixed shaft type gear teeth through combined type planetary mechanism with First Speed ratio and second speed ratio Wheel group input shaft.One in two clutches with another cooperation in two arrestment mechanisms so that from the first power source Output shaft and/or the power of the second power source output shaft output are transferred to fixed shaft type through combined type planetary mechanism with third speed ratio Change gear group input shaft.And pass through the cooperation between two clutches so that from the first power source output shaft and/or second The power of power source output shaft output is transferred to fixed-shaft speed change gear set input through combined type planetary mechanism with fourth speed ratio Axis.8th to the 11st embodiment carries out exemplary description only as preferred embodiment to the present invention, theoretically for, only need An arrestment mechanism is further increased on the element by clutch control in the 5th to the 7th and other similar embodiments Said effect can be achieved.
It is the structural schematic diagram of clutch according to a 12th embodiment of the present invention referring to Figure 39, Figure 39.In the present embodiment In, clutch 120 includes being connected to the first power source output shaft 1220 and the second power source output shaft 1222 and fixed shaft type speed change Combined type planetary mechanism 1210 between gear unit input shaft 1230, and for the element in combined type planetary mechanism 1210 It is controlled, so that the power exported from the first power source output shaft 1220 and/or the second power source output shaft 1222 is through compound Formula planetary mechanism 1210 is transferred to the control mechanism 1240 of fixed-shaft speed change gear set input shaft 1230.
Combined type planetary mechanism 1210 is combined by single planetary row and double planet wheel rows of mixing by element sharing method, and specific Including the first sun gear 1215, the second sun gear 1216, the first planetary gear 1212, the second planetary gear 1214, gear ring 1211 and Planet carrier 1213, concrete structure is similar with first embodiment shown in FIG. 1, and details are not described herein.
In the present embodiment, control mechanism 1240 by two arrestment mechanisms 1241,1242 and three clutches 1243, 1244,1245 composition.Specifically, two arrestment mechanisms 1241,1242 include the first arrestment mechanism 1241 and the second brake Structure 1242, clutch 1243,1244,1245 include the first clutch 1243, the second clutch 1244 and third from Close mechanism 1245.
In the present embodiment, the first sun gear 1215 is controlled by the first arrestment mechanism 1241 and third clutch 1245, Selective braking is specifically carried out by the first arrestment mechanism 1241, and is selectively engaged to the first power by third clutch 1245 Source output shaft 1220 and the second power source output shaft 1222.Second sun gear 1216 is controlled by the first clutch 1243, specifically It is selectively engaged to the first power source output shaft 1220 and the second power source output shaft 1222 by the first clutch 1243.Planet Frame 1213 is controlled by the second clutch 1244 and the second arrestment mechanism 1242, is specifically selected by the second arrestment mechanism 1242 Property braking, and selectively engaged to the first power source output shaft 1220 and the second power source output shaft by the second clutch 1244 1222.Gear ring 1211 connects fixed-shaft speed change gear set input shaft 1230.
When the first clutch 1243, the second clutch 1244 and third clutch 1245 are all in discrete state When, combined type planetary mechanism 1210 is defeated without hair the first power source output shaft 1220 of access and/or the second power source output shaft 1222 The power gone out, to not export power, as " separation " state of ordinary clutch at gear ring 1211.When the first clutch 1243 engagements, the braking of the first arrestment mechanism 1241, while when other clutches and arrestment mechanism be in discrete state, first moves Power source output shaft 1220 and/or the power of the second power source output shaft 1222 output are transferred to second through the first clutch 1243 Sun gear 1216.And since the first arrestment mechanism 1241 locks the first sun gear 1215, power is through the second sun gear 1216, second With First Speed than exporting to gear ring 1211, to make the first power source output shaft after planetary gear 1214, the first planetary gear 1212 1220 and/or second power source output shaft 1222 export power be transferred to First Speed ratio through combined type planetary mechanism 1210 Fixed-shaft speed change gear set input shaft 1230.When the engagement of the second clutch 1244, the braking of the first arrestment mechanism 1241, while its When his clutch is in discrete state with arrestment mechanism, the first power source output shaft 1220 and/or the second power source output shaft The power of 1222 outputs is transferred to planet carrier 1213 through the second clutch 1244.Also due to the first arrestment mechanism 1241 is locked First sun gear 1215, power are exported with second speed ratio to gear ring 1211 after planet carrier 1213, the first planetary gear 1212, from And make the power that the first power source output shaft 1220 and/or the second power source output shaft 1222 export through combined type planetary mechanism 1210 are transferred to fixed-shaft speed change gear set input shaft 1230 with second speed ratio.When the engagement of the first clutch 1243, second Arrestment mechanism 1242 is braked, while when other clutches and arrestment mechanism are in discrete state, the first power source output shaft 1220 and/or second power source output shaft 1222 export power be transferred to the second sun gear through the first clutch 1243 1216.And since planet carrier 1213 is locked by the second arrestment mechanism 1242, power is through the second sun gear 1216, the second planet It is exported to gear ring 1211, to make the first power source output shaft 1220 with third speed ratio after taking turns the 1214, first planetary gear 1212 And/or second power source output shaft 1222 export power dead axle is transferred to third speed ratio through combined type planetary mechanism 1210 Formula change gear group input shaft 1230.When third clutch 1245 engagement, the second arrestment mechanism 1242 braking, while other from When conjunction mechanism is in discrete state with arrestment mechanism, the first power source output shaft 1220 and/or the second power source output shaft 1222 The power of output is transferred to the first sun gear 1215.And since the second arrestment mechanism 1242 locks planet carrier 1213, power It is exported to gear ring 1211 with fourth speed ratio through the first sun gear 1215 and the first planetary gear 1212, to keep the first power source defeated Shaft 1220 and/or the power of the second power source output shaft 1222 output are passed through combined type planetary mechanism 1210 with fourth speed ratio It is handed to fixed-shaft speed change gear set input shaft 1230.When the first clutch 1243, the second clutch 1244 and third clutch Both arbitrary engagement among mechanism 1245, while when other clutches are in discrete state with arrestment mechanism, at this point, second Sun gear 1216, planet carrier 1213, the second planetary gear 1214, the first planetary gear 1212 are locked, and then are driven with the 5th speed ratio Gear ring 1211 rotates, to the power warp for making the first power source output shaft 1220 and/or the second power source output shaft 1222 export Combined type planetary mechanism 1210 is transferred to fixed-shaft speed change gear set input shaft 1230 with the 5th speed ratio.Above-mentioned five kinds of state phases When in " engagement " state of ordinary clutch.Wherein, with First Speed ratio, second speed ratio, third speed ratio and the 5th speed Than the power and the first power source output shaft 1220 and the second power source output shaft that are transferred to fixed-shaft speed change gear set input shaft The power of 1222 outputs is to rotate in same direction, the power and first with fourth speed than being transferred to fixed-shaft speed change gear set input shaft Power source output shaft and/or the power of the second power source output shaft output are to rotate backward.
It is the structural schematic diagram of clutch according to a 13th embodiment of the present invention referring to Figure 40, Figure 40.In the present embodiment In, clutch 130 includes being connected to the first power source output shaft 1320 and the second power source output shaft 1322 and fixed shaft type speed change Combined type planetary mechanism 1310 between gear unit input shaft 1330, and for the element in combined type planetary mechanism 1310 It is controlled, so that the power exported from the first power source output shaft 1320 and/or the second power source output shaft 1322 is through compound Formula planetary mechanism 1310 is transferred to the control mechanism 1340 of fixed-shaft speed change gear set input shaft 1330.
Combined type planetary mechanism 1310 is combined by single planetary row and double planet wheel rows of mixing by element sharing method, and specific Including sun gear 1316, the first gear ring 1315, the second gear ring 1311, the first planetary gear 1312, the second planetary gear 1314 and row Carrier 1313, specifically similar with second embodiment shown in Fig. 2, details are not described herein.
In the present embodiment, control mechanism 1340 by two arrestment mechanisms 1341,1342 and three clutches 1343, 1344,1345 composition.Specifically, arrestment mechanism 1341,1342 includes the first arrestment mechanism 1341 and the second arrestment mechanism 1342, clutch 1343,1344,1345 includes the first clutch 1343, the second clutch 1344 and third clutch Mechanism 1345.Sun gear 1316 is controlled by the first clutch 1343, specifically by the first clutch 1343 selectively engage to First power source output shaft 1320 and the second power source output shaft 1322, the first gear ring 1315 is by the first arrestment mechanism 1341 and Three clutches 1345 control, and specifically bind selectively to the first power source output shaft 1320 and the by third clutch 1345 Two power source output shafts 1322, and selective braking is carried out by the first arrestment mechanism 1341, planet carrier 1313 is by the second brake Structure 1342 and the second clutch 1344 control, and specifically bind selectively to the output of the first power source by the second clutch 1344 Axis 1320 and the second power source output shaft 1322, and selective braking is carried out by the second arrestment mechanism 1342.Second gear ring 1311 Connect fixed-shaft speed change gear set input shaft 1330.
In the first clutch 1343, the second clutch 1344 and third clutch 1345 all in discrete state When, the first power source output shaft 1320 and/or the second power source output shaft 1322 are exported without normal direction combined type planetary mechanism 1310 Power, to not export power, as " separation " state of ordinary clutch at the second gear ring 1311.When the first clutch 1343 engagements, the braking of the first arrestment mechanism 1341, while when other clutches and arrestment mechanism be in discrete state, first moves Power source output shaft 1320 and/or the power of the second power source output shaft 1322 output are transferred to too via the first clutch 1343 Sun wheel 1316.Since the first arrestment mechanism 1341 locks the first gear ring 1315, the first power source output shaft 1320 and/or second is dynamic The power that power source output shaft 1322 exports is after sun gear 1316, the first planetary gear 1312 and the second planetary gear 1314 with first Speed ratio is transferred to the second gear ring 1311, to make the first power source output shaft 1320 and/or the second power source output shaft 1322 The power of output is transferred to fixed-shaft speed change gear set input shaft 1330 through combined type planetary mechanism 1310 with First Speed ratio.When The engagement of second clutch 1344, the braking of the first arrestment mechanism 1341, while other clutches are in arrestment mechanism and detach When state, the power of the first power source output shaft 1320 and/or the output of the second power source output shaft 1322 is via the second clutch Structure 1344 is transferred to planet carrier 1313.Also due to the first arrestment mechanism 1341 locks the first gear ring 1315, the first power source is defeated Shaft 1320 and/or the power of the second power source output shaft 1322 output are through planet carrier 1313 and the first planetary gear 1312, the Second gear ring 1311 is transferred to second speed ratio after two planetary gears 1314, to make the first power source output shaft 1320 and/or The power of second power source output shaft 1322 output is transferred to fixed shaft type with second speed ratio through combined type planetary mechanism 1310 and becomes Fast gear unit input shaft 1330.When the first clutch 1343 engages, the second arrestment mechanism 1342 is braked, while other clutches When structure is in discrete state with arrestment mechanism, the first power source output shaft 1320 and/or the output of the second power source output shaft 1322 Power be transferred to sun gear 1316 via the first clutch 1343.And since the second arrestment mechanism 1342 locks planet carrier 1313, thus the first power source output shaft 1320 and/or the second power source output shaft 1322 output power through sun gear 1316, Second gear ring 1311 is transferred to third speed ratio after first planetary gear 1312 and the second planetary gear 1314, to make first to move Power source output shaft 1320 and/or the power of the second power source output shaft 1322 output are fast with third through combined type planetary mechanism 1310 Degree ratio is transferred to fixed-shaft speed change gear set input shaft 1330.When the engagement of third clutch 1345, the second arrestment mechanism 1342 Braking, while when other clutches and arrestment mechanism be in discrete state, the first power source output shaft 1320 and/or second moves The power that power source output shaft 1322 exports is transferred to through third clutch 1345 in the first gear ring 1315.And due to the second braking Mechanism 1342 locks planet carrier 1313, and power is through the first gear ring 1315, the first planetary gear 1312, the second planetary gear 1314 with the 4th Speed is than exporting to the second gear ring 1311, to make the first power source output shaft 1320 and/or the second power source output shaft 1322 The power of output is transferred to fixed-shaft speed change gear set input shaft 1330 through combined type planetary mechanism 1310 with fourth speed ratio.When Arbitrary the two engagement in first clutch 1343, the second clutch 1344 and third clutch 1345, sun gear 1316, planet carrier 1313, the first planetary gear 1312 and the second planetary gear 1314 are mutually locked, and then with the 5th speed than driving the Two gear rings 1311 rotate, to the power for making the first power source output shaft 1320 and/or the second power source output shaft 1322 export Fixed-shaft speed change gear set input shaft 1330 is transferred to the 5th speed ratio through combined type planetary mechanism 1310.
Above-mentioned five kinds of states are equivalent to " engagement " state of ordinary clutch.Wherein, with First Speed ratio, second speed Than, power and first power source output shaft of the third speed than being transferred to fixed-shaft speed change gear set input shaft with the 5th speed ratio 1320 and/or second power source output shaft 1322 export power be rotate in same direction, with fourth speed ratio be transferred to fixed shaft type become The power of the power of fast gear unit input shaft and the output of the first power source output shaft 1320 and/or the second power source output shaft 1322 To rotate backward.
By the 12nd to the 13rd embodiment it is found that when there are three clutches and two arrestment mechanisms, pass through The first and second clutches in three clutches coordinate with the first arrestment mechanism in two arrestment mechanisms respectively so that The power exported from the first power source output shaft and/or the second power source output shaft is through combined type planetary mechanism with First Speed ratio It is transferred to fixed-shaft speed change gear set input shaft with second speed ratio, passes through first and third clutch in three clutches Structure coordinates with the second arrestment mechanism in two arrestment mechanisms respectively so that from the first power source output shaft and/or the second power The power of source output shaft output is transferred to fixed shaft type gear teeth through combined type planetary mechanism with third speed ratio and fourth speed ratio Wheel group input shaft, and pass through the cooperation between any two clutch in three clutches so that from the first power source Output shaft and/or the power of the second power source output shaft output are transferred to fixed shaft type through combined type planetary mechanism with the 5th speed ratio Change gear group input shaft.12nd to the 13rd embodiment carries out demonstration to the present invention only as preferred embodiment and retouches State, theoretically for, only need to further increase a clutch in the 8th to the 11st and other similar embodiments Realize said effect.
Above-mentioned clutch as individual components be connected to vehicle the first power source output shaft and/or the second power source it is defeated Between shaft and fixed-shaft speed change gear set input shaft, and as the start clutch and shift clutch of vehicle.Likewise, In above-described embodiment, " half-clutch " state can be also realized as described in first embodiment or 3rd embodiment.In addition, above-mentioned each Arrestment mechanism in embodiment may be wet multi-plate brake or suitable brake structure.
By the above-mentioned means, the clutch of the present invention, which utilizes, is connected to the first power source output shaft and the output of the second power source It is combined by element sharing method between axis and fixed-shaft speed change gear set input shaft and by single planetary row and double planet wheel rows of mixing Combined type planetary mechanism, coordinate control mechanism, have the characteristics that it is simple in structure, be easy to implement automation.
As shown in figure 14, Figure 14 is the torsion damping for being integrated on clutch according to fourteenth embodiment of the invention The structural schematic diagram of mechanism.In the present invention, the further integrated torsional damper mechanism 140 in above-mentioned clutch.In this implementation In example, which includes mainly the first rotating disc 1401, the second rotating disc 1402 and spring cushion 1403.Wherein, the first rotating disc 1401 and the coaxial arrangement of the second rotating disc 1402, and can relatively rotate.In the first rotating disc 1401 and second form an annular housing between rotating disc 1402, and spring cushion 1403 is to be set in the annular housing Curved spring, and along 1401 He of the first rotating disc of rotation direction elastic connection of the first rotating disc 1401 and the second rotating disc 1402 Second rotating disc 1402.Preferably, which is connected in series by the spring of at least two different coefficient of elasticity, is thus improved Effectiveness in vibration suppression.
It in other embodiments, can be in the first rotating disc 1401 and the second rotating disc 1402 respectively along respective circumferential direction to shape At multiple spring windows (not shown), spring cushion 1403 includes then the multiple straights being placed in respectively in spring window at this time Spring (not shown).It is also preferable that the coefficient of elasticity of straight spring at least two spring windows is different.
In the present embodiment, torsion damping mechanism 140 can be integrated in any one disk shaped part of clutch shown in FIG. 1 On, for example, be preferably integrated in the second sun gear 116 etc. one or more on.For example, when torsion damping mechanism 140 is integrated in When on two sun gears 116, one in the first rotating disc 1401 and the second rotating disc 1402 with the first power source output shaft and/or Second power source output shaft is directly connected to, and is provided on another in the first rotating disc 1401 and the second rotating disc 1402 outer Tooth, and then carry out external toothing with the second planetary gear 114.When torsion damping mechanism 140 is integrated in brake disc 141, first turn One in Moving plate 1401 and the second rotating disc 1402 is directly connected to sun gear 115, and caliper 142 is to the first rotating disc 1401 and second another in rotating disc 1402 braked.It should be noted that torsion damping mechanism 140 can collect simultaneously At in the second sun gear 116 and brake disc 141, i.e. setting and above description on the second sun gear 116 and brake disc 141 respectively Identical first torsion damping mechanism of structure and the second torsion damping mechanism.It is achieved in two level vibration damping.In the present embodiment, it turns round Turning damper mechanism 140 can also be integrated in the one or more of planet carrier 113, gear ring 111 and the first sun gear 115, by This realizes multi-level damping.Certainly, the second sun gear 116 and brake disc 141 are more highly preferred to.
Equally, torsion damping mechanism 140 can also be integrated in any one disk shaped part of clutch shown in Fig. 2-Figure 11 On, such as on one or more of sun gear, planet carrier, brake disc, gear ring.
Due to from engine to automotive transmission rotating speed and torque be periodically continually changing, this can make power train The twisting vibration of generation；On the other hand since running car is on uneven road, automotive transmission is made angular speed occur unexpected Variation, can also cause twisting vibration.These twisting vibrations all can cause impact load to Parts for Power Train, its service life is made to contract Short or even part of damage.The present invention by the integrated torsional damper mechanism on times keep off arrangement of clutch, can eliminate twisting vibration and It avoids resonating, prevents power train from overloading, therefore the multinomial work(such as " clutch " and " vibration damping " can be integrated simultaneously with an individual components Energy.
Further, since torsion damping mechanism using double rotation dish structures and has certain mass, by calculating and The quality for configuring the two may be implemented function identical with double mass flywheel, and then further integrate " double mass flywheel " function.
In the above-described embodiments, exemplary description only has been carried out to the present invention, but those skilled in the art are reading this The present invention can be carry out various modifications without departing from the spirit and scope of the present invention after patent application.

Claims (2)

1. a kind of speed changing assembly of hybrid vehicle, it is characterised in that：The speed changing assembly includes clutch and fixed shaft type Change gear group, the fixed-shaft speed change gear set include a fixed-shaft speed change gear set input shaft and a fixed shaft type speed change Gear set output shaft, the clutch as individual components be connected to vehicle the first power source output shaft and the second power source it is defeated Between shaft and fixed-shaft speed change gear set input shaft, the clutch includes：
It is connected to the first power source output shaft and the second power source output shaft and the fixed-shaft speed change gear set is defeated Enter the combined type planetary mechanism being combined between axis and by element sharing method by single planetary row and double planet wheel rows of mixing, it is described multiple Box-like planetary mechanism includes the first sun gear, the second sun gear, the first planetary gear, the second planetary gear, gear ring and planet carrier, Described in the first planetary gear and the first sun gear external toothing, the gear ring and the first planetary gear internal messing, described the Two planetary gears between second sun gear and first planetary gear and respectively with second sun gear and described One planetary gear external toothing, first planetary gear and second planetary gear further share the planet carrier；
The power source clutch being connected between the first power source output shaft and the combined type planetary mechanism, it is described dynamic Power source clutch is for controlling the first power source output shaft connected to it, by connected to it described the Selectively output is to the combined type planetary mechanism for the power of one power source output shaft output, wherein the power source clutch For one-way clutch mechanism, when the rotating speed of the element for exporting axis connection with first power source of the combined type planetary mechanism is big When exporting the rotating speed of power source of axis connection with first power source, the one-way clutch mechanism, which is in, surmounts state, keeps away Exempt from power reflux；And
For being controlled such that the element in the combined type planetary mechanism from the first power source output shaft and/or institute Stating the power of the second power source output shaft output, through the combined type planetary mechanism to be transferred to the fixed-shaft speed change gear set defeated Enter the control mechanism of axis, the control mechanism includes brake disc and caliper, and the brake disc is coaxially fixed on described first too On sun wheel, the caliper is used to carry out selective braking to the brake disc, steel used by the brake disc and caliper The outer diameter of piece and friction plate is 250-300MM, and radial thickness is 20MM or more, axial width 3-5MM.
2. speed changing assembly as described in claim 1, it is characterised in that：It is integrated with torsion damping on the combined type planetary mechanism Mechanism, the torsion damping mechanism include coaxial arrangement and the first rotatable parts that can relatively rotate and the second rotatable parts with And along the first rotatable parts and institute described in the rotation direction elastic connection of first rotatable parts and second rotatable parts State the spring cushion of the second rotatable parts.
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