CN107100966A - The planetary gear manual transmission of high transmission ratio - Google Patents
The planetary gear manual transmission of high transmission ratio Download PDFInfo
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- CN107100966A CN107100966A CN201710100281.1A CN201710100281A CN107100966A CN 107100966 A CN107100966 A CN 107100966A CN 201710100281 A CN201710100281 A CN 201710100281A CN 107100966 A CN107100966 A CN 107100966A
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- planetary gear
- load stage
- speed changer
- gear
- planetary
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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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- 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
-
- 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
- F16H3/64—Gearings having three or more central gears composed of a number of gear trains, the drive always passing through all the trains, each train having not more than one connection for driving another train
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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
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
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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
- F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
- F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
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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
- F16H2200/0021—Transmissions for multiple ratios specially adapted for electric 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
- F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two 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
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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
- F16H2200/201—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
- F16H2200/202—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
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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
- F16H2200/2035—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
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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
- F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The present invention relates to a kind of planetary gear manual transmission, have：Power input；Power take-off；Planetary gear speed changer, planetary gear speed changer is driven by power input, and it is driven effect and can switchably changed by fixed transmission element, and it has the first sun gear, the first planetary gearsets, the first pinion frame and the first gear ring；Load stage, load stage has fixed gearratio, and load stage is driven by the output end of planetary gear speed changer and forms power take-off, and load stage has load stage sun gear, load stage planetary gearsets, load stage pinion frame and load stage gear ring；Brake apparatus, brake apparatus has the first brake of the first rotary part for being used to optionally fix planetary gear speed changer and for the second brake for the second rotary part for optionally fixing planetary gear speed changer, wherein brake apparatus be arranged on planetary gear speed changer on the side of load stage.
Description
Technical field
It is motor-driven particularly for being used in the present invention relates to a kind of planetary gear manual transmission that there is height to be always driven effect
Che Zhong, the motor vehicle has electromechanical driver, wherein the planetary gear manual transmission includes multiple be respectively structured as
The speed change level of planetary transmission.
The content of the invention
The present invention is based on following purposes, realizes a kind of planetary gear manual transmission with high total transmission effect, described
Planetary gear manual transmission be characterised by it is compact construct, favourable gearshift performance and high mechanical efficiency.
The purpose realizes that the planetary gear gearshift becomes according to the present invention by following planetary gear manual transmissions
Fast utensil has：
- power input；
- power take-off；
- planetary gear speed changer, the planetary gear speed changer is driven by power input and its transmission is imitated
Fruit can switchably be changed by fixed transmission part, and the planetary gear speed changer has the first sun gear, the
One planetary gearsets, the first pinion frame and the first gear ring；
- the load stage with fixed gearratio, the output end that the load stage passes through planetary gear speed changer drives
And power take-off is formed, the load stage has load stage sun gear, load stage planetary gearsets, load stage planetary gear
Frame and load stage gear ring, and
- brake apparatus, the brake apparatus, which has, is used for the first rotation for optionally fixing planetary gear speed changer
First brake of part and for the second brake for the second rotary part for optionally fixing planetary gear speed changer；
- wherein brake apparatus be arranged on planetary gear speed changer on the side of load stage.
Thus, in an advantageous manner it is possible that realize following planetary gear manual transmissions, changed in the planetary gear
In shift transmission, gearshift function can be realized in the speed changer region with small torque load, and by with it is changeable
The load stage that sets of speed changer region direct neighbor can realize torque is brought up into output torque.In addition, brake apparatus can
To be embodied as compact component, the component is accessible simultaneously from the side of transmission input in favourable mode for safeguarding
And may be mounted on case of transmission.
By the speed changer according to the present invention, the scope in i=15 and i=7.5 can be realized in a particularly advantageous manner
In two gears, wherein in order to set required gearratio, it is necessary to for each gear respectively by an axle relative to shell
System is moved.In this regard, brake apparatus can be with the type structure of double clutch, its bell housing is persistently fixed not by following manner
It is dynamic：The bell housing is for example connected with housing.Can in a particularly advantageous manner asynchronously according to the speed changer of the present invention
Shifted gears under conditions of load.
According to the particularly preferred embodiment of the present invention, planetary gear manual transmission is configured to so that load
Level sun gear is the power input of load stage.The load stage sun gear be concentrically disposed with herein with transmission main shaft line and
In diametrically from interior bonds to the planetary gear of load stage planetary gearsets.
Planetary gear manual transmission is configured to so that the first gear ring, the first pinion frame and/or the first gear ring
Or second gear ring can switchably fix.Furthermore, it is possible to which planetary gear speed changer is configured to so that the planet tooth
Wheel transmission includes the second sun gear, and second sun gear can switchably be fixed via brake apparatus.
The driving of load stage can be realized advantageous by following manner：Load stage sun gear and the first pinion frame turn
It is dynamic rigidly to couple and driven by the first pinion frame.To this as an alternative, it is also possible to, load stage is connected to superposition
Speed changer can be accomplished in the following manner：Load stage sun gear and the first ring gear against rotation are rigidly coupled and by the first gear ring
Driving.
By the design according to the present invention, double shift transmissions of high transmission ratio are realized in an advantageous manner.Make to shift gears
With double clutch, especially dual brake.By speed changer described below, it can realize in i=15 and i=7.5 scope
Two gears, wherein for each gear respectively by an axle relative to housing brake.Double clutch is used this, its clutch
Device shell is regularly connected with case of transmission.Realize that the sub- speed changer of superposition of gearshift function is configured to couple speed changer.All become
Type form has in common that the load stage of output end.Speed change level can be separated spatially with double clutch.
Brief description of the drawings
The other details and feature of the present invention are drawn from description below in conjunction with the accompanying drawings.Accompanying drawing is shown：
Fig. 1 is shown for illustrating the first planet tooth according to the present invention preferred embodiment according to the present invention
The schematic diagram of the construction of manual transmission is taken turns, the first gear ring and the second sun gear of wherein planetary gear manual transmission can be selected
Fixed by means of brake apparatus to selecting property；
Fig. 2 is shown for illustrating the second planet tooth according to the present invention preferred embodiment according to the present invention
The schematic diagram of the construction of manual transmission is taken turns, the first gear ring and the second sun gear of wherein planetary gear manual transmission equally may be used
Optionally to fix；
Fig. 3 is shown for illustrating the 3rd planet tooth according to the present invention preferred embodiment according to the present invention
Take turns the first pinion frame and the second sun gear of the schematic diagram, wherein planetary gear manual transmission of the construction of manual transmission
Can optionally it fix；
Fig. 4 is shown for illustrating the 4th planet tooth according to the present invention preferred embodiment according to the present invention
The schematic diagram of the construction of manual transmission is taken turns, the first gear ring and the second gear ring of wherein planetary gear manual transmission can be selected
Property it is fixed.
Embodiment
The implementation of the planetary gear manual transmission according to the present invention of first embodiment is shown according to Fig. 1 view
Example.The planetary gear manual transmission includes：Power input I1；Planetary gear speed changer G1, the planetary gear
Speed changer is driven by power input I1, and the transmission effect of the planetary gear speed changer can pass through fixed speed change
Device element is changed in changeable mode, and the planetary gear speed changer has the first sun gear S1, the first planetary gearsets
P1, the first pinion frame C1 and the first gear ring H1.First planetary gearsets P1 planetary gear is supported on the first planetary gear
On frame C1 and diametrically from interior bonds into the first gear ring H1.
In addition, including load stage LS according to the planetary transmission of the present invention, the load stage has fixed transmission
Than the load stage is driven by planetary gear speed changer G1 output end G1A and forms planetary gear manual transmission
Power take-off O1.Load stage LS includes load stage sun gear LS1, load stage planetary gearsets LP1, load stage planetary gear
Frame LC1 and load stage gear ring LH1.Load stage sun gear LS1 by planetary gear speed changer G1 output end G1A driving and
Diametrically from interior bonds into planetary gearsets LP1 from variator axis.Planetary gearsets LP1 planetary gear supporting
On the pinion frame LC1 of load stage and diametrically from the gear ring LH1 of interior bonds to load stage LS.Gear ring LH1
It is fixed in case of transmission G.Load stage LS pinion frame LC1 drives its power take-off O1.
Gearshift function is accomplished in the following manner in the planetary gear manual transmission according to the present invention：Provided with braking dress
BR is put, the brake apparatus has：First brake BR1, first for optionally fixing planetary gear speed changer G1
Rotary part；With second brake BR2, the second rotary part for optionally fixing planetary gear speed changer G1.System
Dynamic device BR be arranged on herein planetary gear speed changer G1 on not changeable load stage LS side.Thus may
, gearshift function is realized in the speed changer region with small torque load, and realize torque by load stage LS
Output torque is brought up to, due to setting brake apparatus BR, the load stage can be with the changeable direct phases of speed changer region G1
Set adjacently.In addition, brake apparatus BR can be realized as compact component, with just mode favourable for maintenance from speed changer
The accessible component in side of input.By the transmission configuration shown, it can realize in a particularly advantageous manner in i=
Two gears in 15 and i=7.5 scope, wherein respectively must be braked an axle relative to housing G for each gear.
In this regard, brake apparatus BR can be with the type structure of double clutch, its bell housing BRC is persistently fixed not by following manner
It is dynamic：The bell housing is for example connected with housing G.
First sun gear S1 is planetary gear speed changer G1 power input, and load stage sun gear LS1 is negative
Carry level LS power input.The two sub- speed changers can be coupled by following manner kinematics：Load stage sun gear LS1
Couple and and then driven by the first pinion frame with the first pinion frame C1 rotational stiffness.
In the embodiment being shown here at, planetary gear speed changer G1 includes another in addition to the first pinion frame C1
One second pinion frame C2, the second sun gear S2, the second planetary gear P2 and the second gear ring H2.Second sun gear S2 is radially
On from interior bonds into the second planetary gear P2.Second planetary gear P2 is supported on the second pinion frame C2 and in footpath
Upwards from interior bonds into the second gear ring H2.Via brake apparatus BR the first brake BR1, the second pinion frame C2 energy
It is enough switchably to fix.Via brake apparatus BR second brake BR2, planetary gear speed changer G1 the second sun gear S2
Can optionally it fix.Coupled with the first gear ring H1 to second pinion frame C2 rotational stiffness.Whereby, the first gear ring H1
It can be fixed via the first brake BR1.Coupled with the first pinion frame C1 to second gear ring H2 rotational stiffness.
The basic ratios of first sun gear S1, the first planetary gearsets P1 and the first gear ring H1 gear mesh are for example herein
For -2.The basic ratios of second sun gear S2, the second planetary gearsets P2 and the second gear ring H2 gear mesh are, for example, herein-
3.The standard of first load stage sun gear LS1, the first load stage planetary gearsets LP1 and load stage gear ring LH1 gear mesh is passed
Dynamic is, for example, -4 than herein.
The second embodiment of planetary gear manual transmission according to the present invention is shown according to Fig. 2 view.The planet
Gear manual transmission includes power input I1；Planetary gear speed changer G1, the planetary gear speed changer passes through work(
Rate input I1 is driven, and the transmission effect of the planetary gear speed changer be able to can be cut by fixed transmission element again
Change with changing, the planetary gear speed changer has the first sun gear S1, the first planetary gearsets P1, the first pinion frame
C1 and the first gear ring H1.
In addition, including the load stage LS with fixed gearratio, institute according to the planetary gear manual transmission of the present invention
Load stage is stated to drive by planetary gear speed changer G1 output end G1A and form the power of planetary gear manual transmission
Output end O1.The load stage LS includes load stage sun gear LS1, load stage planetary gearsets LP1, load stage pinion frame
LC1 and load stage gear ring LH1.Load stage sun gear LS1 by planetary gear speed changer G1 output end G1A driving and from
Variator axis is risen diametrically from interior bonds into planetary gearsets LP1.Planetary gearsets LP1 planetary gear is supported on
On the pinion frame LC1 of load stage and diametrically from the gear ring LH1 of interior bonds to load stage LS.Gear ring LH1 exists
It is fixed in case of transmission G.Load stage LS pinion frame LC1 drives its power take-off O1.
In the second embodiment of the planetary gear manual transmission according to the present invention, pass through following manner and reality
Existing gearshift function：Provided with brake apparatus BR, the brake apparatus has：First brake BR1, for optionally fixing planet
First rotary part of toothed wheel speed changer；With second brake BR2, for optionally fixing planetary gear speed changer
Second rotary part.Brake apparatus BR is arranged on planetary gear speed changer at this as in the variations according to Fig. 1
On not changeable load stage LS side.Thus, and it is possible that in the speed changer area with small torque load
Gearshift function is realized in domain, and torque is brought up to by output torque by load stage LS realizations, due to setting brake apparatus BR,
The load stage can directly adjacent to one another be set with changeable speed changer region G1.In addition, brake apparatus BR can be as tight
The component that gathers realizes, with just mode favourable for maintenance from the accessible component in side of transmission input.By showing
The transmission configuration gone out, two gears in i=15 and i=7.5 scope can be realized in a particularly advantageous manner, wherein
An axle must be braked relative to housing G respectively for each gear.In this regard, brake apparatus BR can be with the class of double clutch
Type is constructed, and its bell housing BRC is persistently fixed by following manner：The bell housing is for example connected with housing G.
First sun gear S1 is planetary gear speed changer G1 power input, and load stage sun gear LS1 is negative
Carry level LS power input.The two sub- speed changers are coupled by following manner kinematics：Load stage sun gear LS1 and
Couple and and then be driven by it to one pinion frame C1 rotational stiffness.
In embodiment as shown here, the first pinion frame C1 except the first planetary gearsets P1 planetary gear it
The outer planetary gear for also supporting the second planetary gearsets P2, the planetary gear of the planetary gear and the first planetary gearsets P1 connects
Close.In addition, planetary gear speed changer G1 include the second sun gear S2, second sun gear diametrically from interior bonds to
In second planetary gearsets P2 planetary gear.Second planetary gearsets P2 planetary gear is supported on the first pinion frame C1
On.Via brake apparatus BR the first brake BR1, the first gear ring H1 can be fixed switchably.Via brake apparatus BR's
Second brake BR2, planetary gear speed changer G1 the second sun gear S2 can be fixed optionally.
The 3rd embodiment of planetary gear manual transmission according to the present invention is shown according to Fig. 3 view.The planet
Gear manual transmission includes power input I1；Planetary gear speed changer G1, the planetary gear speed changer passes through work(
Rate input I1 drives, and the transmission effect of the planetary gear speed changer can be changeable by fixed transmission element
Ground changes, and the planetary gear speed changer has the first sun gear S1, the first planetary gearsets P1, the first pinion frame C1
With the first gear ring H1.
In addition, including the load stage LS with fixed gearratio, institute according to the planetary gear manual transmission of the present invention
Load stage is stated to drive by planetary gear speed changer G1 output end G1A and form the power of planetary gear manual transmission
Output end O1.The load stage LS includes load stage sun gear LS1, load stage planetary gearsets LP1, load stage pinion frame
LC1 and load stage gear ring LH1.Load stage sun gear LS1 by planetary gear speed changer G1 output end G1A driving and from
Variator axis is risen diametrically from interior bonds into planetary gearsets LP1.Planetary gearsets LP1 planetary gear is supported on
On the pinion frame LC1 of load stage and diametrically from interior bonds to load stage in 1 gear ring LH1.Gear ring LH1 is becoming
It is fixed in fast device housing G.Load stage LS pinion frame LC1 drives its power take-off O1.
In the planetary gear manual transmission according to the present invention, gearshift function is accomplished in the following manner：Provided with braking
Device BR, the brake apparatus has：First brake BR1, first for optionally fixing planetary gear speed changer
Rotary part；With second brake BR2, the second rotary part for optionally fixing planetary gear speed changer.Braking
Device BR be arranged on herein planetary gear speed changer on not changeable load stage LS side.It is thereby possible to
It is that gearshift function is realized in the speed changer region with small torque load, and is proposed torque by load stage LS realizations
Height arrives output torque, and due to setting brake apparatus BR, the load stage can be with changeable speed changer region G1 direct neighbors
Ground is set.In addition, brake apparatus BR can be realized as compact component, with just mode favourable for maintenance it is defeated from speed changer
Enter the accessible component in side at end.By the transmission configuration shown, it can realize in a particularly advantageous manner in i=15
With two gears in i=7.5 scope, wherein for each gear must respectively by an axle relative to housing G brake.It is right
This, brake apparatus BR can be with the type structure of double clutch, and its bell housing BRC is persistently fixed by following manner：
The bell housing is for example connected with housing G.
First sun gear S1 is planetary gear speed changer G1 power input, and load stage sun gear LS1 is negative
Carry level LS power input.The two sub- speed changers are coupled by following manner kinematics：Load stage sun gear LS1 and
Couple to one gear ring H1 rotational stiffness and and then driven by the first gear ring H1.
In the embodiment being shown here at, the first pinion frame C1 except the first planetary gearsets P1 planetary gear it
The outer planetary gear for also supporting the second planetary gearsets P2, the planetary gear of the planetary gear and the first planetary gearsets P1 connects
Close.In addition, planetary gear speed changer G1 include the second sun gear S2, second sun gear diametrically from interior bonds to
In second planetary gearsets P2 planetary gear.Second planetary gearsets P2 planetary gear is supported on the first pinion frame C1
On.Via brake apparatus BR the first brake BR1, the first pinion frame C1 can be fixed switchably.Via braking dress
BR second brake BR2 is put, planetary gear speed changer G1 the second sun gear S2 can be fixed optionally.
The fourth embodiment of planetary gear manual transmission according to the present invention is shown according to Fig. 4 view.The planet
Gear manual transmission includes power input I1；Planetary gear speed changer G1, the planetary gear speed changer passes through work(
Rate input I1 drives, and the transmission effect of the planetary gear speed changer can be changeable by fixed transmission element
Ground changes, and the planetary gear speed changer has the first sun gear S1, the first planetary gearsets P1, the first pinion frame C1
With the first gear ring H1 and the second gear ring H2 and the second planetary gearsets P2.
In addition, including the load stage LS with fixed gearratio, institute according to the planetary gear manual transmission of the present invention
Load stage is stated to drive by planetary gear speed changer G1 output end G1A and form the power of planetary gear manual transmission
Output end O1.The load stage LS includes load stage sun gear LS1, load stage planetary gearsets LP1, load stage pinion frame
LC1 and load stage gear ring LH1.Load stage sun gear LS1 by planetary gear speed changer G1 output end G1A driving and from
Variator axis is risen diametrically from interior bonds into planetary gearsets LP1.Planetary gearsets LP1 planetary gear is supported on
On the pinion frame LC1 of load stage and diametrically from interior bonds to load stage in 1 gear ring LH1.Gear ring LH1 is becoming
It is fixed in fast device housing G.Load stage LS pinion frame LC1 drives its power take-off O1.
In the planetary gear manual transmission according to the present invention, gearshift function is accomplished in the following manner：Provided with braking
Device BR, the brake apparatus has：First brake BR1, first for optionally fixing planetary gear speed changer
Rotary part；With second brake BR2, the second rotary part for optionally fixing planetary gear speed changer.Braking
Device BR is arranged on deviating from not for planetary gear speed changer G1 at this as in the embodiment being all described above
On changeable load stage LS side.It is thereby possible to, realize and change in the speed changer region with small torque load
Function is kept off, and torque is brought up to by output torque by load stage LS realizations, due to setting brake apparatus BR, the load stage
Can directly adjacent to one another it be set with changeable speed changer region G1.In addition, brake apparatus BR can be real as compact component
It is existing, with just mode favourable for maintenance from the accessible component in side of transmission input.By the speed changer shown
Construction, two gears in i=15 and i=7.5 scope can be realized in a particularly advantageous manner, wherein for each gear
Position respectively must brake an axle relative to housing G.In this regard, brake apparatus BR can be with the type structure of double clutch, its
Bell housing BRC is persistently fixed by following manner：The bell housing is for example connected with housing G.
First sun gear S1 is planetary gear speed changer G1 power input, and load stage sun gear LS1 is negative
Carry level LS power input.The two sub- speed changers are coupled by following manner kinematics：Load stage sun gear LS1 and
Couple to one pinion frame C1 rotational stiffness and and then driven by the first pinion frame.
In the embodiment being shown here at, the first pinion frame C1 except the first planetary gearsets P1 planetary gear it
The outer planetary gear for also supporting the second planetary gearsets P2, the planetary gear of the planetary gear and the first planetary gearsets P1 is same
Set axle and coupled with its rotational stiffness, to form so-called classification planetary gear.In addition, planetary gear speed changer
G1 includes the second gear ring H2, the second planetary gearsets P2 planetary gear diametrically from interior bonds to second gear ring
In.Second planetary gearsets P2 planetary gear is supported on the first pinion frame C1.Via brake apparatus BR the first system
Dynamic device BR1, the first gear ring H1 can be fixed switchably.Via brake apparatus BR second brake BR2, planetary gear becomes
Fast device G1 the second gear ring H2 can be fixed optionally.
The speed changer being described above can be designed to so that the gearratio difference scope in corresponding gearshift condition
From 1.4 to 2.4 factor, and it is furthermore possible to realize maximum transmission ratio of the scope from 11 to 17, in particular 15 maximum transmission
Than.
First sun gear S1 driving can be accomplished in the following manner by electromechanical main driving engine：First sun
S1 is taken turns on the armature spindle of the engine.Engine and the speed changer according to the present invention of description can be combined into knot
Structure unit.
Brake apparatus BR manipulation is carried out preferably by electromechanical actuator.The control of the actuator is preferably via electricity
Sub- control device is carried out, the electronic-controlled installation also power of distribution driving engine in shift process so that realize
Shift process as shock-free as possible.
Claims (10)
1. a kind of planetary gear manual transmission, has：
- power input (I1)；
- power take-off (O1)；
- planetary gear speed changer (G1), the planetary gear speed changer is driven by the power input (I1), and
The transmission effect of the planetary gear speed changer can switchably be changed by fixed transmission element, the planetary gear
Sub- speed changer has the first sun gear (S1), the first planetary gearsets (P1), the first pinion frame (C1) and the first gear ring
(H1)；
- load stage (LS), the load stage has fixed gearratio, and the load stage passes through the planetary gear speed changer
(G1) output end (G1A) drives and forms the power take-off (O1) of the planetary gear manual transmission, described
Load stage has load stage sun gear (LS1), load stage planetary gearsets (LP1), load stage pinion frame (LC1) and load
Level gear ring (LH1), and
- brake apparatus (BR), the brake apparatus has：First brake (BR1), first brake is used for optionally
First rotary part of the fixed planetary gear speed changer (G1)；With second brake (BR2), the second brake is used
In the second rotary part for optionally fixing the planetary gear speed changer (G1),
- wherein described brake apparatus (BR) be arranged on the planetary gear speed changer (G1) away from the load stage (LS)
On side.
2. planetary gear manual transmission according to claim 1,
Characterized in that,
The brake apparatus (BR) is with the type structure of double clutch, and the bell housing (BRC) of the double clutch is persistently fixed
It is motionless.
3. planetary gear shift transmission according to claim 1 or 2,
Characterized in that,
First sun gear (S1) is the power input of the planetary gear speed changer (G1).
4. the planetary gear manual transmission according at least one in claims 1 to 3,
Characterized in that,
First gear ring (H1) can switchably fix.
5. the planetary gear manual transmission according at least one in Claims 1-4,
Characterized in that,
First pinion frame (C1) can switchably fix.
6. the planetary gear manual transmission according at least one in claim 1 to 5,
Characterized in that,
The planetary gear speed changer (G1) includes the second sun gear (S2), and second sun gear (S2) is via described
Brake apparatus (BR) can be fixed switchably.
7. planetary gear manual transmission according to any one of claim 1 to 6,
Characterized in that,
The planetary gear speed changer includes the second gear ring (H2), and second gear ring (H2) can switchably be consolidated
It is fixed.
8. planetary gear manual transmission according to claim 7,
Characterized in that,
Second gear ring (H2) couples with the first pinion frame (C1) rotational stiffness.
9. the planetary gear manual transmission according at least one in claim 1 to 8,
Characterized in that,
The load stage sun gear (LS1) is the load stage (LS) power input.
10. the planetary gear manual transmission according at least one in claim 1 to 9,
Characterized in that,
The load stage sun gear (LS1) couples and by described first with the first pinion frame (C1) rotational stiffness
Pinion frame drives, or the load stage sun gear (LS1) and the first gear ring (H1) rotational stiffness couple and
Driven by first gear ring.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102016202727.1 | 2016-02-23 | ||
| DE102016202727.1A DE102016202727A1 (en) | 2016-02-23 | 2016-02-23 | High-ratio epicyclic gearbox, in particular for an electrically operated motor vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107100966A true CN107100966A (en) | 2017-08-29 |
| CN107100966B CN107100966B (en) | 2021-12-24 |
Family
ID=59522299
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710100281.1A Active CN107100966B (en) | 2016-02-23 | 2017-02-23 | High ratio planetary gear shifting transmission |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN107100966B (en) |
| DE (1) | DE102016202727A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017010868A1 (en) * | 2017-11-24 | 2019-05-29 | Daimler Ag | Transmission device for an electric drive system, in particular of a motor vehicle, and electric drive system for a motor vehicle |
| CN108725583B (en) * | 2018-05-29 | 2021-04-02 | 山推工程机械股份有限公司 | Variable speed steering device, bulldozer and engineering machinery |
| DE102019119946B3 (en) * | 2019-07-24 | 2020-12-24 | Schaeffler Technologies AG & Co. KG | Drive device for a motor vehicle with a non-rotatable ring gear-planet carrier double bond |
| DE102019217155A1 (en) * | 2019-11-07 | 2021-05-12 | Zf Friedrichshafen Ag | Electric drive for a vehicle |
| DE102020105492A1 (en) | 2020-03-02 | 2021-09-02 | Schaeffler Technologies AG & Co. KG | Power shiftable transmission device for an electric drive of a vehicle |
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| Publication number | Publication date |
|---|---|
| CN107100966B (en) | 2021-12-24 |
| DE102016202727A1 (en) | 2017-08-24 |
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