CN106438879B - Multiple-speed gear-box - Google Patents
Multiple-speed gear-box Download PDFInfo
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- CN106438879B CN106438879B CN201610902619.0A CN201610902619A CN106438879B CN 106438879 B CN106438879 B CN 106438879B CN 201610902619 A CN201610902619 A CN 201610902619A CN 106438879 B CN106438879 B CN 106438879B
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- gear
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- planet
- pinion frame
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
- B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0008—Transmissions for multiple ratios specially adapted for front-wheel-driven vehicles
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
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- 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
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
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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
- 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
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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
- 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
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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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
- 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
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Structure Of Transmissions (AREA)
Abstract
A kind of multiple-speed gear-box, with three planet rows being coaxially arranged on main shaft system, the sun gear of second row is connected with drive shaft, the pinion frame of first row is connected with the first little gear and internal gear of the 3rd row, the internal gear of first row and the pinion frame of second row are connected, and the internal gear of second row is connected with the pinion frame of the 3rd row, multiple-speed gear-box has at least four shifting elements, first clutch between drive shaft and the internal gear of second row, second clutch between the sun gear of drive shaft and the 3rd row, the first brake on the sun gear of first row and the second brake on the sun gear of the 3rd row, multiple-speed gear-box has final gear, it has the second cylindrical gear pair between the first cylindrical gear pair and the second little gear on the 7th axle and the second gear on output shaft between the first gear in the first little gear and on the 7th axle.Multiple-speed gear-box has five forward by four shifting elements.
Description
Technical field
The present invention relates to a kind of multiple-speed gear-box, the multiple-speed gear-box is preferred for the horizontal vehicle of preposition forerunner,
The multiple-speed gear-box is arranged in case of transmission between the output shaft of drive shaft and arrangement in parallel, wherein, the multistage
Speed changer has three planet rows being coaxially arranged on main shaft system；The first planet row has the first sun gear, band wherein
There is the first planetary first pinion frame and the first internal gear；And the second planet row has second sun wherein
Take turns, with the second planetary second pinion frame and secondary annulus；And third planet row has the 3rd wherein
Sun gear, third planet tooth rest and the 3rd internal gear with third planet gear；And the second sun gear and drive wherein
Moving axis is connected；And the first pinion frame is connected with the first little gear and with the 3rd internal gear by the second axle wherein；And
Wherein the first internal gear by the 3rd axle with the second pinion frame by being connected；And secondary annulus passes through the 4th axle wherein
It is connected with third planet tooth rest；And wherein, the multiple-speed gear-box has at least four shifting elements, i.e.,：Drive shaft with
First clutch between 4th axle, the second clutch between drive shaft and the 5th axle, in the 6th axle and case of transmission
Between the first brake and the second brake between the 5th axle and case of transmission；Wherein described 3rd sun gear with
The 5th axle connection, first sun gear is connected with the 6th axle, and wherein, the multiple-speed gear-box has main deceleration
Gear (Endantrieb), the final gear has in the first little gear and the first tooth on the 7th axle (being equal to jackshaft)
The first cylindrical gear pair between wheel and the second little gear on the 7th axle and the on the 8th axle (be equal to output shaft)
The second cylindrical gear pair between two gears.
Background technology
In document DE19912480A1, particularly as being given in the gear shown in Fig. 6 according to prior art
Speed changer.However, having been given by shown in the prior art, three coaxial cloth in document US 5295924A earlier
The connection of the element for the planet row put.All it is directly successive successively in all speed changer embodiments according to prior art
Three planetary gearsets are arranged on ground.Four or other shifting element be partly placed directly coupling planetary gearsets it
It is preceding or afterwards.
Can be designed between five to six good shelves the forward gear of ratio and one according to the transmission for vehicles of prior art has
The reverse gear shift of suitable gear ratio.The speed changer can be flowed due to the small sliding rolling in single planet rowAnd with good efficiency and low torque load.Based on prior art for vehicle
There is the automatic transmission compactly constructed for, it has the torsion as the initiating element between internal combustion engine and drive shaft
Square converter.
The content of the invention
In order to further improve this multiple-speed gear-box, it is necessary to complete multiple tasks after analysis prior art.
In future, much smaller vehicle also should be equipped with 6 speed automatic transmissions, when passing through fine optimization gear stage, bearing
When make it that its efficiency is further up with shifting element and hydraulic control device, the speed changer is also by more suitably arranging institute
There is component to be designed to more compact.
Vehicle with internal combustion machine actuating device and electric driver can realize very small power consumption values, because two drivings
Device can realize very effective energy management for vehicle together.Because free space is very limited, it is possible to, will be in big portion
The start-up function undertaken in point automatic transmission by fluid torque-converter is transferred on the shifting element existed, and replaces fluid power
Torque-converters loads forceful electric power motivation and other shifting elements, such as switching on or off internal combustion engine.But for as short as possible
Structure length more urgently needs, for each load integrated (Lastkollektiv) optimally design all components and this
It is outer that all components are arranged in mutually optimal mode for maximum torque density, so that power is existed by transmission system
It is passed on most short path.
In addition, shortening the space that fundamental system is available for other transmission elements, by these transmission elements also
More changeable gears.Helpful herein to be, the basic speed changer of five gears is only extended to good shelves by increasing a small amount of element
Between ratio six gear, seven gear or eight shift transmissions.The present invention is realized according to following technical scheme.
The present invention's is mainly characterized by：Successively it is disposed with after initiating element on main shaft system：It is first
Pump controller before this in the first cross section followed by the first brake in the second cross section followed by horizontal the 3rd
First little gear of the first cylindrical gear pair in section followed by the first planet row in the 4th cross section followed by
The second planet row in 5th cross section followed by being mutually located in radial directions around arrangement in the 6th cross section
The first clutch in outside and second clutch positioned at inner side followed by third planet row in the 7th cross section and most
It is the second brake in the 8th cross section afterwards.
This arrangement of element may be such that the axle between each component is most short so that the axle mutually placed is as far as possible
It is few, and optimally utilize the possible constructions space in each cross section.
The second cylindrical gear pair of final gear is arranged in the second cross section in another design of the present invention.
Pump controller extends to the axle of arrangement in parallel in the first cross section from the centre of main shaft system, and the axle is in speed change
It is located at bottom in device housing as far as possible and drives oil pump, the oil pump only must sucks oil with relatively low suction head herein.The
One brake is located in the second cross section.First cylindrical gear pair of final gear extends in the 3rd cross section, that is,
Say, the 7th axle (being equal to jackshaft) parallel to main shaft system is laterally extended upwardly to from the second axle in the centre of main shaft system.Master subtracts
Second cylindrical gear pair of fast gear and then extended obliquely downward again to the 8th axle output shaft in other words from the 7th axle.By this
The first cylindrical gear pair and the second cylindrical gear pair of the mode of kind, pump controller and final gear can very save space
Ground is positioned around the first brake.
The present invention's is further technically characterized in that：Case of transmission has the shell of the first housing support shaft with can-like
Body dividing plate, the first housing support shaft surrounds the first brake and supports pinion bearing for the first little gear, and the 6th
Axle passes through the first housing support shaft of the can-like.
In order to gently carry out tooth engagement, construct two cylindrical gear pair helical teeth of final gear.In order to bear more
Big radial load and axial force, and in order to support heeling moment, pinion bearing is for example by the angular contact ball axle of two O shapes arrangements
Composition is held, it is by locking nut by pre- anxiety.In described embodiment, the housing support shaft of can-like is surrounded first and made
Dynamic portion, and be economical space saving located in the free structure space between pump controller and final gear.6th axle is passed through should
The support shaft of can-like, the 6th axle connects the first sun gear and the first braking parts.
The present invention's is further technically characterized in that：The first small tooth being supported in the 3rd cross section on pinion bearing
First planetary gear of the wheel directly with being arranged in towards the first little gear, the first planet row in the 4th cross section on side
The length for the outlet side that the pinion frame side plate of the outlet side of frame passes through the second axle adapts to first little gear (37) and institute
State the axle journal connection in space between pinion frame side plate (64).
By the arrangement of each element, the pinion frame side of the outlet side of the first little gear and the first pinion frame
Plate is directly juxtaposed to each other.Thus, it is necessary to which transmitting the axle journal of the outlet side of the second axle of max. output torque becomes very short.
6th axle passes through the axle journal of the outlet side, and the peak torque of the 6th axle is only the substantially half of max. output torque.First axle is worn
Cross the 6th axle, the peak torque of the peak torque of first axle also than the 6th axle is much smaller.By the axle of minimum load in inner side and most
The arrangement for the axle that the axle of heavy load is mutually placed at three of outside provides good precondition for cramped construction.
The present invention's is further technically characterized in that：For simply installing, transmission element is helpful to be, in the first row
Sprocket drive spindle is arranged between the axle journal and the first little gear of outlet side on the pinion frame side plate of the outlet side of gear rack
Connecting portion and bourrelet and axial thrust.
Shorter gear shaft connecting portion also transmits big moment of torsion in major diameter.Bourrelet be used for by big radial load from
First pinion frame is delivered on pinion bearing.Axial thrust is used to exist big axial load from the first pinion frame
It is delivered on force direction on pinion bearing.
The present invention's is further technically characterized in that：The planet of the outlet side of park lock gear and the first pinion frame
Tooth rest side plate is connected.
The pinion frame side plate of outlet side extends radially outwardly because its by being radially disposed in more lateral herein second
Axle is connected with the 3rd internal gear.The connection in this of park lock gear does not require extra axial arrangement space.In park lock
Load on gear is passed on pinion bearing in effective park lock by gear shaft connecting portion and bourrelet.
The present invention's is further technically characterized in that：Housing cap has the second housing support shaft, second housing supporting
Axle extends between drive shaft and the 6th axle, and it includes the outside for multiple oily Transmission systems being delivered in drive shaft
Element.
In order to manipulate first clutch and second clutch, oil pressure and oil volumetric flow rates must be passed from case of transmission
Onto drive shaft in other words first axle.It is possible that not needing extra axial direction to this in a kind of embodiment flexible program
Structure space.First little gear has so big diameter, comes hence for the second housing support shaft with oily Transmission system
Say there is enough radial spaces between first axle and the 6th axle.
Multiple-speed gear-box described in preamble can realize five by four shifting elements according to prior art
Forward gear.In another design of the present invention, multiple-speed gear-box also has the 3rd brake, that is to say, that the 4th
There is the 3rd brake between axle and case of transmission.3rd brake can be realized with the another of very big gearratio
Forward gear and the reverse gear shift with same gear ratios.
For more forward gears, the third planet tooth rest of third planet row of the invention is more broadly constructed, so that the
Four planetary gears coaxially and are secured to be arranged in third planet tooth rest with being connected, fourth line with third planet gear
In the 9th cross section of the star arrangement of gears between the 7th cross section and the 8th cross section, and fourth planet gear and the 4th sun
Wheel engagement.In addition, the 4th sun gear is connected with the 9th axle, the 9th axle can be connected by the 4th brake with case of transmission.
Eight forward gears can be realized and in speed change according to this embodiment flexible program of the multiple-speed gear-box of the present invention
There are three brakes in the rear portion of device.Thus it is apparent, by between the second planet row and third planet row
Two clutches arrangement produce structure on advantage.If the two clutches be arranged in third planet tooth rest it
Afterwards, then another axle is had to pass through in less 3rd sun gear of diametrically, and is disposed with five in the transmission portion at rear portion
Individual shifting element.
At most four brakes and two clutches and three planet rows are had according to the multiple-speed gear-box of the present invention,
Wherein, third planet row may have multi-stage planetary gear and two sun gears.Speed changer is in the gearshift system for different gears
There is only two clutches, and two fuel feeding portions are therefore only needed on rotary part, it is arranged in another function in system
Element internal, and do not need axial arrangement length.Brake provides oil pressure and oil volumetric flow rates by case of transmission.Brake is not
Need the device for compressing centrifugal force pressure and therefore shorter construct.Generally speaking, selective application said elements can be real
Now have five to the design of the multiple-speed gear-box closely of eight forward gears.
Can be in the multiple-speed gear-box of power shifting, usually using having the height that is used for accommodating power consumption and energy expenditure
The plate clutch or disk brake of thermal capacity.When can the multiple-speed gear-box of power shifting there is shifting element when, it is falling
It is closed, and is then opened from (x+1)th advance dammed up in car bumper and from the first forward gear to xth forward gear, the shifting element
It is not subjected in the case of steering force big at the same time in common gearshift control at present or is only subjected to slight slip.Changed at this
The power attenuation occurred in gear element is minimum.Therefore such shifting element can be designed to small thermal capacity more
The gear clutch that compactly designed cone clutch or be even designed to minimally is constructed.This is in the multistage according to the present invention
It is applied to the 3rd brake in speed changer.
Therefore, in another embodiment flexible program of the multiple-speed gear-box of the present invention, the 3rd brake is in the 4th axle
It is designed to the bicone clutch only with small rubbing surface between case of transmission or is designed to gear clutch.
The present invention is not limited only to the feature described in its claim.Further, it is contemplated that and proposing that single each of combination is weighed
Profit requires the combinatory possibility of feature and illustrates to neutralize the content and each right disclosed in design embodiment in advantage
It is required that the combinatory possibility of feature.
Especially, the present invention also relates to according to the equally valid solution of prior art.
Brief description of the drawings
Fig. 1 shown into Fig. 9 according to the present invention hybrid gearbox some embodiments, and on axle, OK
Star arrange and shifting element arrangement and be illustrated on principle function.In accompanying drawing：
Fig. 1 shows the drive mechanism of the multiple-speed gear-box according to the present invention, with as preposition forerunner
In the embodiment of the fluid torque-converter of the initiating element of horizontal vehicle, the multiple-speed gear-box have drive shaft and with drive
Six forward gears and a reverse gear shift between the output shaft of moving axis parallel arrangement；
Fig. 2 shows the other details of the speed changer structure according to Fig. 1, the system for the planet row being especially coupled to
Structure；
Fig. 3 shows the design of the configuration aspects of the multiple-speed gear-box according to Fig. 2；
Fig. 4 shows the detailed view of the multiple-speed gear-box according to Fig. 3, the bearing and little gear of special little gear 37
Connecting portion between 37 and the pinion frame side plate 64 of outlet side；
Fig. 5 is shown in the embodiment of P2 hybrid gearboxes, according to the multiple-speed gear-box of the present invention in driving
Speed changer structure between axle and the output shaft of drive shaft parallel arrangement, the P2 hybrid gearboxes have in driving side cloth
The motor and the 3rd clutch as initiating element put；
Fig. 6 shows the design of the configuration aspects of the multiple-speed gear-box according to Fig. 5；
Fig. 7 shows the flexible program of the speed changer structure of the multiple-speed gear-box according to Fig. 5, the multiple-speed gear-box
With only five forward and without reverse gear shift and with bigger motor；
Fig. 8 is shown in the embodiment as the torque converter of initiating element, according to the multistage of the present invention
The speed changer structure of speed changer, the multiple-speed gear-box has eight advances between drive shaft and coaxially arranged output shaft
Gear and a reverse gear shift；
Fig. 9 shows shift logic multiple-speed gear-box, with five, six or eight forward gears according to the present invention
Figure.
Embodiment
Fig. 1 shows the drive mechanism of the multiple-speed gear-box 1 according to the present invention.Fig. 2 is shown with the diagram slightly amplified
The other details of the multiple-speed gear-box 1.According to Fig. 1, the drive of the axle as main shaft system 49 is supported with case of transmission 2
Moving axis 11.Jackshaft 17 and output shaft 18 are also supported with case of transmission 2 parallel to the main shaft system 49.Internal combustion engine 69 can
It is connected by initiating element 48 with drive shaft 11.It is described to start in the embodiment flexible program according to Fig. 1 and Fig. 2
Element 48 is that have direct drive clutchFluid torque-converter.
Three planet rows have been coaxially arranged on main shaft system 49.As shown in FIG. 2, the first planet row 20 has first
Sun gear 21, the first pinion frame 22 and the first internal gear 24 with the first planetary gear 23.Second planet row 25 has
There are the second sun gear 26, the second pinion frame 27 and secondary annulus 29 with the second planetary gear 28.Third planet
Row 30 has the 3rd sun gear 31, the internal gear 34 of third planet tooth rest 32 and the 3rd with third planet gear 33.
Second sun gear 26 is connected with drive shaft 11.First pinion frame 22 passes through the second axle 12 and the first little gear 37
And be connected with the 3rd internal gear 34.First internal gear 24 is connected by the 3rd axle 13 with the second pinion frame 27.Second internal tooth
Wheel 29 is connected by the 4th axle 14 with third planet tooth rest 32.
In addition, multiple-speed gear-box 1 has five shifting elements, i.e.,：Between the axle 14 of drive shaft 11 and the 4th first from
Clutch 41, the second clutch 42 between drive shaft 11 and the 5th axle 15, between the 6th axle 16 and case of transmission 2
One brake 43, the second brake 44 between the 5th axle 15 and case of transmission 2 and in the 4th axle 14 and transmission case
The 3rd brake 45 between body 2, wherein the 3rd sun gear 31 is connected with the 5th axle；First sun gear 21 and the 6th
Axle is connected.
In addition, the multiple-speed gear-box 1 according to Fig. 1 has final gear (Endantrieb) 3, the main reducing gear
Wheel is with the first roller gear between the first gear 38 in the first little gear 37 and on the 7th axle 17 (being equal to jackshaft)
Between secondary 4 and the second little gear 39 on the 7th axle 17 and the second gear 40 on the 8th axle 18 (being equal to output shaft)
Second cylindrical gear pair 5.The differential mechanism 6 of the driving of output shaft 18 with first gear axle 7 and second gear axle 8.
In order to provide oil volumetric flow rates and oil pressure so as to lubricate, cool down and control multiple-speed gear-box 1, the multiple-speed gear-box 1
With two oil pumps, i.e.,：The oil pump 10 of one larger Mechanical Driven and a less electrically driven (operated) oil pump 47.The machinery
The oil pump 10 of driving by the pump controller 9 of machinery or be connected with drive shaft 11 or with driving element 48 and internal combustion engine
The side connection of 69 connections.
The structural detail of multiple-speed gear-box be eight, be successively arranged in backward from driving element 48 cross section 51 to
In 58.On main shaft system 49, successively it is disposed with after initiating element 48：It is the pump in the first cross section 51 first
Driver 9 followed by the first brake 43 in the second cross section 52 followed by the first cylinder in the 3rd cross section 53
First little gear 37 of gear pair 4 followed by the first planet row 20 in the 4th cross section 54 followed by the 5th cross section
The second planet row 25 in 55 followed by mutually it is located at outside around arrangement in radial directions in the 6th cross section 56
First clutch 41 and second clutch 42 positioned at inner side followed by there is the 3rd brake in the 7th cross section 57
45 third planet arranges 30 and is finally the second brake 44 in the 8th cross section 58.According to this to member of the present invention
The arrangement of part enables to the axle between single component most short so that the axle mutually placed is as few as possible, and optimal
Land productivity is used in the possible constructions space in single cross section.
Pump controller 9 extends to the axle of arrangement in parallel, the axle in the first cross section 51 from the centre of main shaft system 49
It is located at bottom as far as possible in case of transmission, and mechanically drives oil pump 10, the oil pump herein must be only high with small suction
Degree suction oil.First brake 43 is located in the second cross section 52.First cylindrical gear pair 4 of final gear 3 is horizontal the 3rd
In section 53, the 7th axle 17 parallel to main shaft system 49 is laterally extended upwardly to from the second axle 12 of the centre in main shaft system 49.
Second cylindrical gear pair 5 of final gear 3 is arranged in the second cross section 52, and is extended obliquely downward again from the 7th axle 17
To the 8th axle output shaft 18 in other words.In this way, the first cylindrical gear pair 4 of pump controller 9 and final gear 3
Economical space saving it can be positioned with the second cylindrical gear pair 5 around the surrounding of the first brake 43 very much.
According to Fig. 2, case of transmission 2 has the first housing support shaft with can-like
61 case partition 60, the first housing support shaft surrounds the first brake 43 and supports little gear for the first little gear 37
Bearing 63.In order to gently carry out tooth engagement, two cylindrical gear pairs 4 and 5 of final gear 3 are designed to helical teeth.For
Accommodate big tangential force, radial load and axial force in the first little gear 37 and in order to support heeling moment, pinion shaft
Hold 63 to be preferably made up of the angular contact ball bearing of two O shapes arrangements, it is by locking nut by pre- anxiety.6th axle 16 passes through tank
First sun gear 21 is connected by the housing support shaft 61 of shape, the 6th axle with the first brake 43.
First little gear 37 is supported on pinion bearing 63 in the 3rd cross section 53, and first little gear is directly and cloth
Put the first pinion frame 22 of towards the first little gear 37, the first planet row 20 in the 4th cross section 54 aside
The pinion frame side plate (Stegwange) 64 of outlet side connected by the axle journal 62 of the very short outlet side of the second axle 12
Connect, the axle journal of the outlet side must transmit the output torque of maximum on the position.6th axle 16 passes through the axle of the outlet side
Neck, the peak torque of the 6th axle is only the substantially half of max. output torque.First axle 11 passes through the 6th axle 16, and first axle is most
Peak torque of the high pulling torque also than the 6th axle 16 is much smaller.With the axle of minimum load internally and with the axle of maximum load outside
The arrangement for the axle that three of side mutually place provides good precondition for cramped construction.
Fig. 3 shows the design of the configuration aspects of the multiple-speed gear-box according to Fig. 2.By using with pump
The torque converter of hydraulic circulation constructed very shortly between gear, turbine and directive wheel, largely ellipse, and
Due to the very section space-efficient arrangement of the transmission element according to the present invention, the speed changer with 352mm is for 360Nm
Driving torque for structure be very small.
Fig. 4 shows the detailed view of the multiple-speed gear-box shown in Fig. 3, the particularly bearing of little gear 37 and little gear 37
Connecting portion between the pinion frame side plate 64 of outlet side.Install that transmission element is helpful to be for simple, the
Between the little gear 37 of axle journal 62 and first of outlet side on the pinion frame side plate 64 of the outlet side of one pinion frame 22
Arrange sprocket drive spindle connecting portion 65 and bourrelet 66 and axial thrust 67.
Shorter gear shaft connecting portion 65 can also transmit larger moment of torsion in major diameter.Bourrelet 66 is used for will be big
Radial load is delivered on pinion bearing 63 from the first pinion frame 22.Axial thrust 67 be used for by big axial load from
First pinion frame 22 is delivered on force direction on pinion bearing 63.
As shown in as shown in Figure 1 to Figure 4, the planet of the outlet side of the pinion frame 22 of park lock gear 50 and first
Tooth rest side plate 64 is connected.The pinion frame side plate 64 of outlet side extends radially outwardly because its pass through herein radially it is upper
The second axle 12 in more lateral is connected with the 3rd internal gear 34.Therefore this connection of park lock gear 50 does not require extra
Axial arrangement space.Load on park lock gear 50 passes through the foregoing He of gear shaft connecting portion 65 in effective park lock
Bourrelet 66 is passed on pinion bearing 63.
Case partition 60 also has the second housing support shaft68, the second housing support shaft is being driven
Extend between the axle 16 of moving axis 11 and the 6th and it includes the outside for multiple oily Transmission systems being delivered in drive shaft 11
Element.Because in order to manipulate first clutch 41 and second clutch 42, oil pressure and oil volumetric flow rates must be from case of transmissions 2
It is passed to by case partition 60 and the second housing support shaft 68 in first axle (equivalent to drive shaft 11).According to Fig. 3
In Fig. 4 embodiment flexible program, following situations are feasible, i.e., extra axial arrangement space is not needed to this.The
One little gear 37 has so big diameter so that for the second housing support shaft 68 with oily Transmission system
There is enough radial spaces between the axle 16 of first axle 11 and the 6th.
Fig. 5 is shown in the embodiment of P2 hybrid gearboxes, is being driven according to the multiple-speed gear-box 1 of the present invention
Speed changer structure between moving axis 11 and the output shaft 18 being arranged in parallel with drive shaft, the P2 hybrid gearboxes have six
Individual forward gear, also have the 3rd brake 45 and driving side arrange motor 70 and as initiating element 48 the 3rd from
Clutch 71.Hybrid drive has two driving sources.Motor 70 by it is from battery, pass through output control device
The electrical power of regulation is converted into mechanical output.The motor 70 is directly connected with drive shaft 11, and starts member in no other
In the case of part the drive shaft is driven from inactive state.Died down for the power of battery or feelings that battery charging state declines to a great extent
Condition, internal combustion engine 69 can be accelerated by the 3rd clutch 71 as initiating element 48 and is then ignited.Internal combustion engine will
Power carried in the volumetric fuel flow rate from fuel tank, related to chemistry is converted into mechanical output.By depending on car
Running status and battery accumulation of energy and select the use of battery appropriate power source, can be right again during travelling
Energy accumulator is charged, and can significantly reduce the energy expenditure in vehicle using such hybrid gearbox.
Fig. 6 shows the design of the configuration aspects of the multiple-speed gear-box according to Fig. 5, and it is exported for identical
There is 375mm structure length, the biography for the torque converter with shorter construction being only slightly longer than according to Fig. 3 for power
System embodiment.
Fig. 7 shows the speed changer structure of the multiple-speed gear-box 1 in the hybrid power embodiment according to Fig. 5
Another flexible program, it is with only five forward without reverse gear shift.This is completed by giving up the 3rd brake 45.By
This, for five forward gears being well classified, multiple-speed gear-box only needs four shifting elements.Thus, in the embodiment party
Multiple-speed gear-box 1 in formula flexible program also obtains very elongated housing on following positions of enging cabin, i.e., in the position
It is typically very narrow due to the frame structure of carrying to put the housing.Because third planet row 30 can be configured to narrower in addition
It is long, thus remain more spaces be used for have it is more significantly larger than embodiment flexible program according to Fig. 5 effective
The more powerful motor 70 of length.
Future, the power density and energy density of battery further increase so that thus motor vehicle driven by mixed power can have more
Big electric continual mileage and moment of torsion and the stronger motor of power.Vehicle with such hybrid gearbox it is main by
Electric drive.The moment of torsion of powerful motor be enough to make vehicle forwardly and rearwardly accelerate from inactive state or on big abrupt slope
It is dynamic.Therefore reverse gear shift can be given up.Also common first gear can be given up, the first gear mainly in internal combustion engine drive rotating speed be
It is necessary for substantially 8 to 9km/h low travel speed in the case of 1000/min.Internal combustion engine with smaller cylinder
It can also smaller construct, and be initially used for as the supplement for peak power and the supplement for continual mileage.
In the transport condition that essential electrical is run, travel such motor vehicle driven by mixed power very low noise.Internal combustion engine leads to
Often it is cut off.In order to less hear internal combustion engine in internal combustion engine operation, it is desirable to the measure of fine buffering vibration.Therefore, according to
Multiple-speed gear-box 1 shown in Fig. 7, which has, to be used for dual-spring system, the torsional vibration damper 72 of internal combustion engine 69 and for motor
70 another torsional vibration damper 73.
It is another for electric drive also using more powerful motor during the stronger electrification to car drive
One oil pump 47, the oil pump is then passed through to be run depending on the optimal driving rotating speed of operating point, and then is only required always actual
Necessary volume flow.The energy requirement of auxiliary unit is significantly reduced separately through such measure.
Fig. 8 is shown with as the fluid torque-converter of initiating element 48 and with eight forward gears and a reversing
In the embodiment of gear, according to the present invention it is multiple-speed gear-box 1, drive shaft 11 and coaxially arranged jackshaft 17 and with
Speed changer structure between its output shaft 18 being arranged in parallel.In order to which the quantity of forward gear is brought up into eight, the 3rd from six
The third planet tooth rest 32 of planet row 30 is more broadly constructed, so that fourth planet gear 36 and third planet gear 33 are coaxially
And be arranged in third planet tooth rest 32 with being secured to connection, fourth planet arrangement of gears is in the 7th cross section 57 and the 8th
In the 9th cross section 59 between cross section 58, and fourth planet gear is engaged with the 4th sun gear 35.In addition, the 4th sun gear
35 are connected with the 9th axle 19, and the 9th axle can be connected by the 4th brake 46 with case of transmission 2.
According to this embodiment flexible program multiple-speed gear-box 1, with eight forward gears of the present invention in speed change
There are three brakes 44,45,46 in the rear portion of device.Thus it is relatively sharp, by the second planet row 25 and
The arrangement of two clutches 41,42 between three planet rows 30 produces the advantage in structure.If the two clutches 41,42
It is arranged in after third planet tooth rest 32, then another axle is had to pass through in less 3rd sun gear 31 of diametrically, and
Five shifting elements are disposed with the transmission portion at rear.
Finally, Fig. 9 shows the shift logic figure of the multiple-speed gear-box 1 with five, six or eight forward gears.Carry
The flexible program of five and six forward gears has the planet row of three couplings.Only the flexible program with eight forward gears is the
There are level planetary gear and two sun gears in three speed changers level.The flexible program of five gears only has four shifting elements, i.e.,：Two
Realize to advance in individual clutch 41 and 42 and the first brake 43 and second brake 44, and embodiment described here and turn
The dynamic resultant gear ratio scope (Gesamtspreizung) than for 5.151.Extraly, the flexible program of six gears has the 3rd braking
Device 45 and the resultant gear ratio scope for being 6.411.Eight gear flexible programs also have the 4th brake 46 and for 8.083 it is big total
Gear range.In the above-mentioned flexible program with six gears and with eight gears of multiple-speed gear-box 1, two first
The major part of planet row 20,25 and third planet row 30 are identicals.It can be held very much by the flexible program of basic ratios
Change places and cover other gear ranges.
Can be in the multiple-speed gear-box of power shifting, usually using having the height that is used for accommodating power consumption and energy expenditure
The plate clutch or disk brake of thermal capacity.When can the multiple-speed gear-box of power shifting there is shifting element when, it is falling
It is closed, and is then opened always from (x+1)th advance dammed up in car bumper and from the first forward gear to xth forward gear, this is changed
It is not subjected in the case of gear element steering force big at the same time in common gearshift control at present or is only subjected to slight slip.
The power attenuation occurred in the shifting element is minimum.Therefore such shifting element can be designed to small thermal capacitance
The cone clutch (Konuskupplung) more compactly constructed of amount or the tooth-like clutch for being even designed to minimal construction
Device.This is applied to the 3rd brake between the 4th axle 14 and case of transmission 2 in the multiple-speed gear-box 1 according to the present invention
45.In the speed changer flexible program with six and with eight forward gears, the 3rd brake 45 is only neutralized in reverse gear shift
It is closed in the first forward gear.
For according to the present invention it is multiple-speed gear-box 1, show in Fig. 1 into the embodiment flexible program shown in Fig. 9
Go out big application, and it can be realized by this compact arrangement of transmission element.Because drive shaft
11 can be guided in both sides from case of transmission 2, and internal combustion engine 69 and motor 70 can be connected on both sides.Thus it is produced
His embodiment flexible program, it is especially useful in the vehicle with longitudinal drive.
Reference numerals list：
1 multiple-speed gear-box
2 case of transmissions
3 final gears
4 first cylindrical gear pairs
5 second cylindrical gear pairs
6 differential mechanisms
7 first semiaxis
8 second semiaxis
9 pump controllers
The oil pump of 10 Mechanical Drivens
11 drive shafts (are equal to first axle)
12 second axles
13 the 3rd axles
14 the 4th axles
15 the 5th axles
16 the 6th axles
17 the 7th axles
18 the 8th axles
19 the 9th axles
20 first planet rows
21 first sun gears
22 first pinion frames
23 first planetary gears
24 first internal gears
25 second planet rows
26 second sun gears
27 second pinion frames
28 second planetary gears
29 secondary annulus
30 third planets are arranged
31 the 3rd sun gears
32 third planet tooth rests
33 third planet gears
34 the 3rd internal gears
35 the 4th sun gears
36 fourth planet gears
37 first little gears
38 first gears
39 second little gears
40 second gears
41 first clutches
42 second clutches
43 first brakes
44 second brakes
45 the 3rd brakes
46 the 4th brakes
47 electrically driven (operated) oil pumps
48 initiating elements (such as fluid torque-converter)
49 main shaft systems
50 park lock gears
51 first cross sections
52 second cross sections
53 the 3rd cross sections
54 the 4th cross sections
55 the 5th cross sections
56 the 6th cross sections
57 the 7th cross sections
58 the 8th cross sections
59 the 9th cross sections
60 case partitions
First housing support shaft of 61 can-like
The axle journal of the outlet side of 62 second axles
63 pinion bearings
The pinion frame side plate of the outlet side of 64 first pinion frames
Gear shaft connecting portion between 65 second axles and the first pinion frame
Bourrelet between 66 second axles and the first pinion frame
67 axial thrusts
68 second housing support shafts
69 internal combustion engines
70 motor
71 the 3rd clutches
72 are used for the torsional vibration damper of internal combustion engine
73 are used for the torsional vibration damper of motor
Claims (39)
1. a kind of multiple-speed gear-box (1), the multiple-speed gear-box is preferred for the horizontal vehicle of preposition forerunner, the multistage becomes
Fast device is arranged in case of transmission (2) between drive shaft (11) and the 8th axle (18) being arranged in parallel with drive shaft,
Wherein, the multiple-speed gear-box (1) has three planet rows being coaxially arranged on main shaft system (49)；Wherein first
Planet row (20) has the first sun gear (21), with the first pinion frame (22) of the first planetary gear (23) and first
Internal gear (24)；And the second planet row (25) has the second sun gear (26), the with the second planetary gear (28) wherein
Two pinion frames (27) and secondary annulus (29)；And wherein third planet row (30) have the 3rd sun gear (31),
Third planet tooth rest (32) and the 3rd internal gear (34) with third planet gear (33)；And the second sun gear wherein
(26) it is connected with drive shaft (11)；And the first pinion frame (22) passes through the second axle (12) and the first little gear (37) wherein
And be connected with the 3rd internal gear (34)；And wherein the first internal gear (24) by passing through the 3rd axle (13) and the second planetary gear
Frame (27) is connected；And secondary annulus (29) is connected by the 4th axle (14) with third planet tooth rest (32) wherein,
And wherein, the multiple-speed gear-box (1) has at least four shifting elements, i.e.,：In drive shaft (11) and the 4th axle (14)
Between first clutch (41), the second clutch (42) between drive shaft (11) and the 5th axle (15), in the 6th axle
(16) the first brake (43) between case of transmission (2) and between the 5th axle (15) and case of transmission (2)
Second brake (44), wherein the 3rd sun gear (31) is connected with the 5th axle；First sun gear (21) and institute
The connection of the 6th axle is stated,
And wherein, the multiple-speed gear-box (1) has final gear (3), the final gear has in the first little gear
(37) the first cylindrical gear pair (4) between the first gear (38) on the 7th axle (17) and on the 7th axle (17)
The second cylindrical gear pair (5) between second little gear (39) and second gear (40) on the 8th axle (18),
Characterized in that, being successively disposed with after initiating element (48) on the main shaft system (49)：Be first
Pump controller (9) in first cross section (51) followed by the first brake (43) in the second cross section (52) followed by
The first little gear (37) of the first cylindrical gear pair (4) in the 3rd cross section (53) followed by the 4th cross section (54)
In the first planet row (20) followed by the second planet row (25) in the 5th cross section (55) followed by transversal the 6th
In face (56) in radial directions mutually around the first clutch (41) positioned at outside of arrangement and positioned at inner side second
Clutch (42) followed by the third planet row (30) and be finally in the 8th cross section (58) in the 7th cross section (57)
In second brake (44).
2. multiple-speed gear-box (1) according to claim 1, it is characterised in that the second cylinder of the final gear (3)
Gear pair (5) is arranged in the second cross section (52).
3. multiple-speed gear-box (1) according to claim 1, it is characterised in that the case of transmission (2), which has, carries tank
The case partition (60) of first housing support shaft (61) of shape, the first housing support shaft surround the first brake (43) and
The pinion bearing (63) for the first little gear (37) is supported, and the 6th axle (16) passes through the first housing support shaft.
4. the multiple-speed gear-box (1) according to claim 2, it is characterised in that the case of transmission (2), which has, to be carried
The case partition (60) of first housing support shaft (61) of can-like, the first housing support shaft surrounds the first brake (43) simultaneously
And pinion bearing (63) for the first little gear (37) is supported, and the 6th axle (16) passes through the first housing support shaft.
5. multiple-speed gear-box (1) according to claim 1, it is characterised in that be supported in the 3rd cross section (53) small
The first little gear (37) on gear-bearing (63) directly be aside arranged in it is in the 4th cross section (54), small towards first
The pinion frame side plate (64) of the outlet side of gear (37), the first planet row (20) the first pinion frame (22) passes through
The length of the outlet side of second axle (12) adapts to empty between first little gear (37) and the pinion frame side plate (64)
Between very short axle journal (62) connection.
6. multiple-speed gear-box (1) according to claim 2, it is characterised in that be supported in the 3rd cross section (53) small
The first little gear (37) on gear-bearing (63) directly be aside arranged in it is in the 4th cross section (54), small towards first
The pinion frame side plate (64) of the outlet side of gear (37), the first planet row (20) the first pinion frame (22) passes through
The length of the outlet side of second axle (12) adapts to empty between first little gear (37) and the pinion frame side plate (64)
Between very short axle journal (62) connection.
7. multiple-speed gear-box (1) according to claim 3, it is characterised in that be supported in the 3rd cross section (53) small
The first little gear (37) on gear-bearing (63) directly be aside arranged in it is in the 4th cross section (54), small towards first
The pinion frame side plate (64) of the outlet side of gear (37), the first planet row (20) the first pinion frame (22) passes through
The length of the outlet side of second axle (12) adapts to empty between first little gear (37) and the pinion frame side plate (64)
Between very short axle journal (62) connection.
8. multiple-speed gear-box (1) according to claim 4, it is characterised in that be supported in the 3rd cross section (53) small
The first little gear (37) on gear-bearing (63) directly be aside arranged in it is in the 4th cross section (54), small towards first
The pinion frame side plate (64) of the outlet side of gear (37), the first planet row (20) the first pinion frame (22) passes through
The length of the outlet side of second axle (12) adapts to empty between first little gear (37) and the pinion frame side plate (64)
Between very short axle journal (62) connection.
9. multiple-speed gear-box (1) according to claim 5, it is characterised in that in order to simply install, in the second axle (12)
Between the pinion frame side plate (64) of the outlet side of the first pinion frame (22) arrange sprocket drive spindle connecting portion (65) and
Bourrelet (66) and axial thrust gear (67).
10. multiple-speed gear-box (1) according to claim 6, it is characterised in that in order to simply install, in the second axle
(12) and the first pinion frame (22) outlet side pinion frame side plate (64) between arrange sprocket drive spindle connecting portion
(65) and bourrelet (66) and axial thrust gear (67).
11. multiple-speed gear-box (1) according to claim 7, it is characterised in that in order to simply install, in the second axle
(12) and the first pinion frame (22) outlet side pinion frame side plate (64) between arrange sprocket drive spindle connecting portion
(65) and bourrelet (66) and axial thrust gear (67).
12. multiple-speed gear-box (1) according to claim 8, it is characterised in that in order to simply install, in the second axle
(12) and the first pinion frame (22) outlet side pinion frame side plate (64) between arrange sprocket drive spindle connecting portion
(65) and bourrelet (66) and axial thrust gear (67).
13. multiple-speed gear-box (1) according to claim 1, it is characterised in that park lock gear (50) and the first planet
Pinion frame side plate (64) connection of the outlet side of tooth rest (22).
14. multiple-speed gear-box (1) according to claim 2, it is characterised in that park lock gear (50) and the first planet
Pinion frame side plate (64) connection of the outlet side of tooth rest (22).
15. multiple-speed gear-box (1) according to claim 3, it is characterised in that park lock gear (50) and the first planet
Pinion frame side plate (64) connection of the outlet side of tooth rest (22).
16. multiple-speed gear-box (1) according to claim 4, it is characterised in that park lock gear (50) and the first planet
Pinion frame side plate (64) connection of the outlet side of tooth rest (22).
17. multiple-speed gear-box (1) according to claim 5, it is characterised in that park lock gear (50) and the first planet
Pinion frame side plate (64) connection of the outlet side of tooth rest (22).
18. multiple-speed gear-box (1) according to claim 6, it is characterised in that park lock gear (50) and the first planet
Pinion frame side plate (64) connection of the outlet side of tooth rest (22).
19. multiple-speed gear-box (1) according to claim 7, it is characterised in that park lock gear (50) and the first planet
Pinion frame side plate (64) connection of the outlet side of tooth rest (22).
20. multiple-speed gear-box (1) according to claim 8, it is characterised in that park lock gear (50) and the first planet
Pinion frame side plate (64) connection of the outlet side of tooth rest (22).
21. multiple-speed gear-box (1) according to claim 9, it is characterised in that park lock gear (50) and the first planet
Pinion frame side plate (64) connection of the outlet side of tooth rest (22).
22. multiple-speed gear-box (1) according to claim 10, it is characterised in that park lock gear (50) and the first row
Pinion frame side plate (64) connection of the outlet side of gear rack (22).
23. multiple-speed gear-box (1) according to claim 11, it is characterised in that park lock gear (50) and the first row
Pinion frame side plate (64) connection of the outlet side of gear rack (22).
24. multiple-speed gear-box (1) according to claim 12, it is characterised in that park lock gear (50) and the first row
Pinion frame side plate (64) connection of the outlet side of gear rack (22).
25. the multiple-speed gear-box (1) according to any one of claim 1 to 24, it is characterised in that housing cap (60) has
There is the second housing support shaft (68), the second housing support shaft extends and described between drive shaft (11) and the 6th axle (16)
Second housing support shaft is included in the outer member for multiple oily Transmission systems in drive shaft (11).
26. the multiple-speed gear-box (1) according to any one of claim 1 to 24, it is characterised in that the 4th axle (14) can
It is connected by the 3rd brake (45) with case of transmission (2).
27. multiple-speed gear-box (1) according to claim 25, it is characterised in that the 4th axle (14) can pass through the 3rd system
Dynamic device (45) is connected with case of transmission (2).
28. the multiple-speed gear-box (1) according to any one of claim 1 to 24, it is characterised in that third planet arranges (30)
Third planet tooth rest (32) more broadly construct so that fourth planet gear (36) and third planet gear (33) are coaxially simultaneously
And be secured to connection be arranged in third planet tooth rest, the fourth planet arrangement of gears the 7th cross section (57) with
In the 9th cross section (59) between 8th cross section (58), and the fourth planet gear is engaged with the 4th sun gear (35),
And the 4th sun gear (35) be connected with the 9th axle (19), the 9th axle can pass through the 4th brake (46) and case of transmission
(2) connect.
29. multiple-speed gear-box (1) according to claim 25, it is characterised in that the third planet of third planet row (30)
Tooth rest (32) is more broadly constructed, so that fourth planet gear (36) coaxially and is secured to third planet gear (33)
It is arranged in third planet tooth rest to connection, the fourth planet arrangement of gears is in the 7th cross section (57) and the 8th cross section
(58) in the 9th cross section (59) between, and the fourth planet gear is engaged with the 4th sun gear (35), and the 4th sun
Wheel (35) is connected with the 9th axle (19), and the 9th axle can be connected by the 4th brake (46) with case of transmission (2).
30. multiple-speed gear-box (1) according to claim 26, it is characterised in that the third planet of third planet row (30)
Tooth rest (32) is more broadly constructed, so that fourth planet gear (36) coaxially and is secured to third planet gear (33)
It is arranged in third planet tooth rest to connection, the fourth planet arrangement of gears is in the 7th cross section (57) and the 8th cross section
(58) in the 9th cross section (59) between, and the fourth planet gear is engaged with the 4th sun gear (35), and the 4th sun
Wheel (35) is connected with the 9th axle (19), and the 9th axle can be connected by the 4th brake (46) with case of transmission (2).
31. multiple-speed gear-box (1) according to claim 27, it is characterised in that the third planet of third planet row (30)
Tooth rest (32) is more broadly constructed, so that fourth planet gear (36) coaxially and is secured to third planet gear (33)
It is arranged in third planet tooth rest to connection, the fourth planet arrangement of gears is in the 7th cross section (57) and the 8th cross section
(58) in the 9th cross section (59) between, and the fourth planet gear is engaged with the 4th sun gear (35), and the 4th sun
Wheel (35) is connected with the 9th axle (19), and the 9th axle can be connected by the 4th brake (46) with case of transmission (2).
32. the multiple-speed gear-box (1) according to any one of claim 1 to 24, it is characterised in that the 4th axle (14) with
The 3rd brake (45) between case of transmission (2) is configured to bicone clutch or is configured to gear clutch.
33. multiple-speed gear-box (1) according to claim 25, it is characterised in that in the 4th axle (14) and case of transmission
(2) the 3rd brake (45) between is configured to bicone clutch or is configured to gear clutch.
34. multiple-speed gear-box (1) according to claim 26, it is characterised in that in the 4th axle (14) and case of transmission
(2) the 3rd brake (45) between is configured to bicone clutch or is configured to gear clutch.
35. multiple-speed gear-box (1) according to claim 27, it is characterised in that in the 4th axle (14) and case of transmission
(2) the 3rd brake (45) between is configured to bicone clutch or is configured to gear clutch.
36. multiple-speed gear-box (1) according to claim 28, it is characterised in that in the 4th axle (14) and case of transmission
(2) the 3rd brake (45) between is configured to bicone clutch or is configured to gear clutch.
37. multiple-speed gear-box (1) according to claim 29, it is characterised in that in the 4th axle (14) and case of transmission
(2) the 3rd brake (45) between is configured to bicone clutch or is configured to gear clutch.
38. multiple-speed gear-box (1) according to claim 30, it is characterised in that in the 4th axle (14) and case of transmission
(2) the 3rd brake (45) between is configured to bicone clutch or is configured to gear clutch.
39. multiple-speed gear-box (1) according to claim 31, it is characterised in that in the 4th axle (14) and case of transmission
(2) the 3rd brake (45) between is configured to bicone clutch or is configured to gear clutch.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102016008479 | 2016-07-13 | ||
| DE1020160084790 | 2016-07-13 |
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| Publication Number | Publication Date |
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| CN106438879A CN106438879A (en) | 2017-02-22 |
| CN106438879B true CN106438879B (en) | 2017-07-21 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610902619.0A Active CN106438879B (en) | 2016-07-13 | 2016-10-17 | Multiple-speed gear-box |
| CN201611253263.9A Active CN106594200B (en) | 2016-07-13 | 2016-12-30 | Multiple-speed gear-box |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201611253263.9A Active CN106594200B (en) | 2016-07-13 | 2016-12-30 | Multiple-speed gear-box |
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| Country | Link |
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| CN (2) | CN106438879B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106594200A (en) * | 2016-07-13 | 2017-04-26 | 盛瑞传动股份有限公司 | Multi - stage transmission |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6506339B2 (en) * | 2017-03-31 | 2019-04-24 | 本田技研工業株式会社 | Control device |
| CN108131427A (en) * | 2017-12-27 | 2018-06-08 | 合肥工业大学 | A kind of 2 speed automatic transmissions and shifting control system |
| JP6952625B2 (en) * | 2018-03-06 | 2021-10-20 | 本田技研工業株式会社 | Transmission for motors |
| CN108799442A (en) * | 2018-08-21 | 2018-11-13 | 盛瑞传动股份有限公司 | Multiple-speed gear-box |
| CN108799441A (en) * | 2018-08-21 | 2018-11-13 | 盛瑞传动股份有限公司 | Multiple-speed gear-box |
| CN108843753A (en) * | 2018-08-21 | 2018-11-20 | 盛瑞传动股份有限公司 | Multiple-speed gear-box |
| DE102019103771A1 (en) * | 2018-11-05 | 2020-05-07 | Schaeffler Technologies AG & Co. KG | Transmission unit and hybrid module with a transmission-side partition |
| DE102019208595A1 (en) * | 2019-06-13 | 2020-12-17 | Robert Bosch Gmbh | Transmission for a hybrid drive arrangement |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3248348A1 (en) * | 1982-12-28 | 1984-07-05 | Daimler-Benz Ag, 7000 Stuttgart | Automatic gearbox of the epicycloidal gear train type for motor vehicles |
| US6045479A (en) * | 1998-08-10 | 2000-04-04 | Ford Global Technologies, Inc. | Differential mechanism for an automotive vehicle having a cold formed housing assembly |
| JP5775113B2 (en) * | 2013-06-11 | 2015-09-09 | 本田技研工業株式会社 | Control device for automatic transmission |
| JP6219145B2 (en) * | 2013-08-30 | 2017-10-25 | アイシン・エィ・ダブリュ株式会社 | Multi-speed transmission |
| JP6066100B2 (en) * | 2014-01-29 | 2017-01-25 | マツダ株式会社 | Automatic transmission |
| CN105667294B (en) * | 2016-03-03 | 2018-04-10 | 科力远混合动力技术有限公司 | A kind of transmission device for forerunner's plug-in hybrid vehicle |
| CN106438879B (en) * | 2016-07-13 | 2017-07-21 | 盛瑞传动股份有限公司 | Multiple-speed gear-box |
-
2016
- 2016-10-17 CN CN201610902619.0A patent/CN106438879B/en active Active
- 2016-12-30 CN CN201611253263.9A patent/CN106594200B/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106594200A (en) * | 2016-07-13 | 2017-04-26 | 盛瑞传动股份有限公司 | Multi - stage transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106438879A (en) | 2017-02-22 |
| CN106594200A (en) | 2017-04-26 |
| CN106594200B (en) | 2019-03-01 |
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