CN102767610B - Gearbox - Google Patents
Gearbox Download PDFInfo
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- CN102767610B CN102767610B CN201210215650.9A CN201210215650A CN102767610B CN 102767610 B CN102767610 B CN 102767610B CN 201210215650 A CN201210215650 A CN 201210215650A CN 102767610 B CN102767610 B CN 102767610B
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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
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
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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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H2003/0826—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts wherein at least one gear on the input shaft, or on a countershaft is used for two different forward gear ratios
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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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
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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
- F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
For the gearbox of motor vehicle, it is changeable between several gear shift steps, there is two inputs (1,2) and an output (3,4), between two inputs (1,2), wherein arrange the changeable connection (R) being used for forward gear, and between two inputs (1,2) and output (3,4), arrange three the changeable connections being used for forward gear respectively.
Description
Technical field
The present invention relates to the gearbox for motor vehicle, it is changeable in several gear shift steps, has two inputs and an output.Two inputs are selectively driven and are connected to drive motor, such as internal-combustion engine.
Background technique
Such as, in DE10015336A1, this gearbox is disclosed.Double clutch gearbox described in it comprises two input shafts, and it is connected with drive motor respectively by friction clutch.Each in input shaft via two tooth-profile of gear to being optionally connected to an output shaft.Therefore, depend in two friction clutches which be engaged, the driving torque of drive motor is delivered to output shaft via the first input shaft or is delivered to output shaft via the second input shaft.Therefore, four gear shift steps of gearbox can altogether be realized.In order to increase the quantity of gear shift steps, provide parallel axes, its via the tooth-profile of gear to two fixed gears to one that is connected in input shaft with driving.And parallel axes is optionally connected to another input shaft via of two tooth-profile of gear centerings.Therefore, at least in regioselective gear shift steps, form power train by the first input shaft, parallel axes, the second input shaft and output shaft.Alternatively, power train can be formed by the second input shaft, parallel axes, the first input shaft and output shaft.Therefore, 12 gear shift steps can be realized in theory.
As the substitute of conventional automatic gearbox with torque converter, double clutch gearbox has appearred in market, and this is the power consumption advantage due to them.Reason for the power consumption advantage of double clutch gearbox is, does not use torque converter for driving (driveaway), but uses dry type or actuation in wet oiling condition clutch.But torque converter has as two that drive element essential advantages compared to clutch.Due to the amplification of its Motor torque, so it provide high drive propulsion, and it is very stable on thermal performance, can also allow thus with the long distance of trailer on hill creep phase place (creepingphase) or repeat drive.In contrast to this, especially, the double clutch gearbox especially effectively with dry clutch is more responsive, and it can cause disadvantageous operating conditions to the emergency cut-off of gearbox.
Problem pointed above solution and acquisition have double clutch gearbox equal traditional drive propulsion of automatic transmission case and the possibility of stability is by using very not enough driving gear ratio to expand range of gears (spread).But in the unlimited range of gears increased, need extra gear, gear surge (jump) can become too greatly or not occur for the favourable spool gear of power consumption in addition.
Traditional in the concept of double clutch gearbox, usually, respective gear is needed to connect for each gear or himself tooth-profile of gear pair, for this reason, add mechanical complexity, add the quantity of gear simultaneously, therefore also cause the problem of installing space.Today, there is common double clutch gearbox and usually can realize seven forward gears.
Summary of the invention
The object of the invention is to, when not increasing the installing space of gearbox, realizing favourable shift schedule at multiple available gear shift steps place.
According to the present invention by solving this object for the gearbox of motor vehicle, it is changeable between several gear shift steps, there is two inputs and an output, changeable connection wherein for forward gear is arranged between two inputs, and is arranged between two input and output for three changeable connections of forward gear.
Arranged by it according to gearbox of the present invention, especially by the connection between two inputs and three connections respectively between two input and output, make the gear with maximum quantity have low mechanical complexity becomes possibility simultaneously.
Two input and output provide the three degree of freedom of gearbox, and one of them degrees of freedom comprises all parts of gearbox gear wheels, such as axle and tooth-profile of gear, and it is connected to each other when not activating shifting element with driving.Three degree of freedom can be engaged with each other via changeable connection.A connection in this case, is altogether provided at least seven connections of forward gear, so that is required for only four selector forks of shifting gears, even if also will be had again to be used to reverse gear.In this case, usually, selector fork can be shifted gears two and be connected.
Due to the connection between two inputs, so three the direct connections for forward gear between the first input and output can be used to six forward gear shift steps of gearbox altogether.Three connections can be used in directly exporting from the first input queued switches.And likely input driver output in such a way by second, that is, the second input drives the first input via the connection between two inputs, then first input a driver output in connecting via three.Be same effective for directly connecting for three of the forward gear between the second input and output, it can be used in the Direct driver realized between the second input and output and the indirect output being input to output via the second input from first on the one hand.Therefore, 12 forward gears can altogether be realized with four selector forks.
In common double clutch gearbox, wherein do not connect between two inputs, at most only can realize seven forward gears with four selector forks.
Can realize reversing gear by the present invention, so that the changeable connection for reversing gear is arranged between two inputs.Alternatively, the changeable connection for reversing gear can be arranged in two input in one and export between.
Preferably, each in two inputs is connected to drive motor, such as internal-combustion engine via respective clutch (in particular friction clutch).
Preferably, two inputs comprise input shaft separately, and wherein two input shafts are arranged to coaxially to each other.
At least in three forward gears, preferably in four forward gears, connect and be arranged between two inputs, namely two inputs are engaged with each other via the connection between two inputs.
For the switching between two gear shift steps, especially, switching between two gear shift steps of following each other, on the one hand, can provide as the plain sequence in common double clutch transmission, wherein from via two input in one occur drive original tooth wheel shift steps to via two input in another occur drive higher or lower gear shift steps subsequently gearshift during, the shift clutch in driving gear shift steps is subsequently share by Continuous Closed, disconnect the shift clutch for driving initial gear shift steps continuously simultaneously, it is " intersect and mix (cross-fading) ".Occurred when not having tractive force to interrupt from a gear should " intersect and mix " to another.
On the other hand, it can provide gearbox to be controlled, so that from initial gear shift steps to during the gearshift of gear shift steps subsequently, initial gear shift steps and occur in gear shift steps subsequently via two input in same driving, initially it is switched (" intersect and mix ") to supporting gear shift steps, and wherein power path extends via another in two inputs.When driving via another in two inputs, select gear shift steps subsequently, then it is switched to gear shift steps subsequently, and the driving via identical input wherein occurs, and it is also used to drive initial gear shift steps.Term " selection " gear shift steps subsequently refers to, each connection is switched, and it must be used for driving via gear shift steps subsequently.Term " switching " refers to, clutch is engaged also guide power path via the connection selected.
So use, this is so-called " supporting gearshift ", when in the gear shift steps of following each other at two, the driving via identical input occurs.In this case, in common shift process, must temporarily be disconnected at the clutch of the driving input of correspondence, can select the connection of gearbox, after this, clutch can be coordinated again.But this can cause the interruption of tractive force.In order to prevent this situation, use " supporting gearshift ", wherein initially it is switched to higher gear shift steps, and the driving via another input wherein occurs.Preferably, it is switched to next higher gear shift steps, and the driving via another input wherein occurs.This gear shift steps is only used always or is selected, until the switching of gear shift steps subsequently has occurred and it can be got back to another input by intersection mixing.Therefore, it is possible to prevent the interruption of tractive force.
Preferably, in shift schedule, at least two forward gears are arrived via support gear shift steps.In other words, it must provide the driving being at least in two load of following each other switchable gear shift steps in two positions of shift schedule and occurring via identical input." load is changeable " refers to, in this connection, when not having tractive force to interrupt, shift process occurs.
Usually, it can also provide by the second drive motor be connected to two input in one.In this case, it can be such as motor.
Output can comprise two output shafts, and these two output shafts are arranged to parallel to each other and are connected to the common actuation gear of the power train for driving wheel with being all arranged for driving.In this case, it is preferably the actuation gear of differential gear.
Two input in first can comprise the first input shaft, and two input in second can comprise the second input shaft, the first and second input shafts are optionally driven by drive motor.Output can comprise the first output shaft and the second output shaft, and the first and second output shafts are all connected to the power train of the wheel for driving machine motor vehicle, and its of being transfused to respectively in axle is selectively driven.In this case, two input shafts are connected to each other via at least one gear with connecting driving.And each in two input shafts is at least connected at least one in output shaft via three gears with connecting driving.Term " gear connection " comprises traditional tooth-profile of gear pair.But, can also provide several tooth-profile of gear to and axle, especially, when power path has the transition several times from an axle to another axle.
Preferably, it provides the first input shaft to be connected to the first output shaft via at least three gears.And it can provide the second input shaft to be at least connected to the second output shaft three gear joints.
In an exemplary embodiment, the first input shaft is connected to the first output shaft with connecting driving via three gears, and the second input shaft is connected to the second output shaft with connecting driving via three gears.In another embodiment, the first input shaft is connected to the first output shaft via two gears and is connected to the second output shaft via gear.In this case, the second input shaft is connected to the second output shaft via three gears.
Accompanying drawing explanation
Below, by using accompanying drawing to describe preferred embodiment in detail.Which show:
Fig. 1: according to the schematic diagram of the first embodiment of gearbox of the present invention,
Fig. 2: according to the schematic diagram of the second embodiment of gearbox of the present invention,
Fig. 3: according to the schematic diagram of the degrees of freedom of two embodiments of Fig. 1 and 2,
Fig. 4: according to the schematic diagram of the 3rd embodiment of gearbox of the present invention,
The schematic diagram of the degrees of freedom of the gearbox of Fig. 5: Fig. 4,
Fig. 6: according to Fig. 1,2 and 4 the figure of shift schedule of gearbox,
Fig. 7: the torque characteristics in " intersect and mix (cross-fading) " shift process, and
Fig. 8: the torque characteristics in " supporting gearshift ".
Embodiment
Fig. 1 shows the first input shaft 1, and it is connected to drive motor with driving via the first shift clutch K1, is typically connected to the internal-combustion engine of motor vehicle.In addition, show the second input shaft 2, it is connected to drive motor with also driving via the second shift clutch K2.Two shift clutch K1, K2 are formed friction clutch, and wherein in order to simplify this schematic diagram, shift clutch K1, K2 are shown as only having a clutch element.But usually, other shift clutch are also possible, and it guarantees to have the shift process slided.
Two input shafts 1,2 can be selectively driven and can separated from one anotherly throw off.Therefore the first input shaft 1 is a part for the first input of gearbox, and the second input shaft 2 is parts of the second input of gearbox.
First input shaft 1 is formed as hollow shaft, and it is arranged to around the second input shaft 2 and can Concentric rotation relative to it.But usually, two input shafts 1,2 also can be arranged parallel to each other.But, coaxially arrangedly make compact design become possibility.
In addition, arrange the first output shaft 3 and the second output shaft 4, they are arranged to be parallel to two input shafts 1,2.Two output shafts 3,4 are also arranged to parallel to each other and are connected respectively to the actuation gear of differential mechanism via profile of tooth output gear 20,21, so that two output shafts 3,4 rotate together and can be jointly viewed as an output.
First input shaft 1 is connected to the first output shaft 3 with driving via connecting three of III, VI, IX gears in tooth-profile of gear.Tooth-profile of gear comprises fixed gear 5,6,7 and idler gear 8,9,10 respectively to III, VI, IX, and wherein fixed gear 5,6,7 to be non-rotatably connected on the first input shaft 1 and idler gear 8,9,10 is arranged to rotatably around the first output shaft 3.Two 8 in idler gear, 10 via first gearshift arrange A be connected to the first output shaft 3 and in idler gear another 9 via the 3rd gearshift arrange C be connected to the first output shaft 3, namely depend on that the drive range of A, C is arranged in gearshift, one in idler gear 8,9,10 is engaged to the first output shaft 3.In addition, arrange for each gearshift and provide neutral gear position, wherein idler gear 8,10 or idler gear 9 do not engage with the first output shaft 3.
Second input shaft 2 is connected to the second output shaft 4 with driving via connecting three of II, V, VIII gears in tooth-profile of gear.Tooth-profile of gear comprises a fixed gear 11,12,13 and idler gear 14,15,16 respectively to II, V, VIII, and wherein fixed gear 11,12,13 is non-rotatably connected to the second input shaft 2 and idler gear 14,15,16 is arranged to rotatably around the second output shaft 4.Two 15 in idler gear, 16 via second gearshift arrange B be connected to the second output shaft 4 and in idler gear another 14 via the 4th gearshift arrange D be connected to the second output shaft 4, namely depend on that the drive range of B, D is arranged in gearshift, one in idler gear 14,15,16 is engaged to the second output shaft 4.In addition, arrange that B, D provide neutral gear position for each gearshift, wherein idler gear 15,16 or idler gear 14 do not engage with the second output shaft 4.
Connect via gear, it comprises tooth-profile of gear to VI and tooth-profile of gear to T1, and the first input shaft 1 is connected to the second input shaft 2.Tooth-profile of gear comprises fixed gear 12 and idler gear 17 to T1, and fixed gear 12 or tooth-profile of gear are to a part of V, and idler gear 17 is rotatably arranged relative to the first output shaft 3.By the 3rd gearshift, idler gear 17 arranges that C is connected to tooth-profile of gear on the idler gear 9 of VI with driving.Expression due to Fig. 1 is schematic expression, so idler gear 9 also can be understood to fixed gear, it is non-rotatably arranged on parallel axes 18, and the parallel axes 18 being wherein formed as hollow shaft is arranged in shift gears on the first output shaft 3 and for idler gear/fixed gear 9 to the three rotatably arranges the connection of C.
First input shaft 1 drives ground to connect and is provided to reversing gear of the second input shaft 2 for connecting via gear, and this gear connects and comprises tooth-profile of gear to R and VIII.Tooth-profile of gear comprises idler gear 19 to R, and it is arranged to rotatable relative to the second output shaft 4 and engages with the idle running/fixed gear 9 of tooth-profile of gear to VI.Arrange D via the 4th gearshift, idler gear 19 can be connected to tooth-profile of gear on the idler gear 14 of VIII, so that produces between the first input shaft 1 and the second input shaft 2 and be rotatably connected.Therefrom, power path can connect continuation further via the gear between in input shaft 1,2 and output shaft 3,4.
In this connection, must it is mentioned that the expression of Fig. 1 simplifies, can show all tooth-profile of gear pair in one plane.In reality, when looking up in the side of axle, first input shaft 1 or be arranged to second input shaft 2, first output shaft 3 coaxial with the first input shaft 1 and the second output shaft 4 is disposed on imaginary triangle, thus idler gear 19 can engage with idler gear/fixed gear 9.
In the first embodiment in FIG, first power path is used to indicate the first gear shift steps, when the first shift clutch K1 coordinates and the second shift clutch K2 disconnects, this first power path extends to second input shaft 2 to VI and tooth-profile of gear to T1 via tooth-profile of gear from the first input shaft 1, wherein switch the 3rd gearshift and arrange C, so that the idler gear 9 of tooth-profile of gear to VI joins the idler gear 17 of tooth-profile of gear to T1 to.Suppose that idler gear 9 is looked at as fixed gear, it is arranged on parallel axes 18, and so idler gear 17 is engaged to parallel axes 18.From the second input shaft 2, power path extends to the second output shaft 4 via tooth-profile of gear to II further, and wherein the second gearshift arranges that B joins the idler gear 16 of tooth-profile of gear to II to second output shaft 4.Second output shaft 4 carries profile of tooth output gear 20, and it is engaged on the actuation gear of this not shown differential gear case.
In order to perform the second gear shift steps, use the second power path, when first clutch K1 disconnects and second clutch K2 coordinates, this second power path extends to second output shaft 4 via tooth-profile of gear to II from the second input shaft 2, and wherein the second gearshift arranges that B joins the idler gear 16 of tooth-profile of gear to II to second output shaft 4.
From the first gear shift steps to during the handoff procedure of the second gear shift steps, there is " intersect mixing " from the first shift clutch K1 to the second shift clutch K2, as this is also like this in common double clutch transmission.That is, during the first shift clutch K1 disconnects continuously, the second shift clutch K2 coordinates continuously, so that generation tractive force during shift process does not interrupt.In the figure 7, the torque characteristics shown along with time two shift clutch K1, K2 is simplified.When it is driven in the first gear shift steps, preselected second gear shift steps, so that when tractive force does not interrupt, it can be " intersect and mix ".To same extent, when the moment of torsion on the first shift clutch K1 reduces, the moment of torsion on the second shift clutch K2 increases.
In the 3rd gear shift steps, when the first shift clutch K1 coordinates and the second shift clutch K2 throws off, 3rd power path extends to first output shaft 3 via tooth-profile of gear to III from the first input shaft 1, and wherein the first gearshift arranges that A joins the idler gear 8 of tooth-profile of gear to III to first output shaft 3.
First power path of the corresponding first gear shift steps of the 4th power path of the 4th gear shift steps, but, wherein the second input shaft 2 is not connected to second output shaft 4 via tooth-profile of gear to V to II via tooth-profile of gear, and wherein the second gearshift arranges that B joins the idler gear 15 of tooth-profile of gear to V to second output shaft 4.
In the 5th gear shift steps, when the first shift clutch K1 throws off and the second shift clutch K2 coordinates, 5th power path extends to second output shaft 4 via tooth-profile of gear to V from the second input shaft 2, and wherein by the second gearshift, tooth-profile of gear arranges that B joins the second output shaft 4 to the idler gear 15 of V.
From the 3rd gear shift steps to during the handoff procedure of the 4th gear shift steps, in both these gear shift steps of following each other, first shift clutch K1 closes and the second shift clutch K2 disconnects, so that usual first shift clutch K1 temporarily must disconnect in order to shift process.This can cause the interruption of tractive force.In order to prevent this situation, for the endurance of shift process, within this endurance, switching the 3rd is shifted gears and is arranged that layout A is used for idler gear 8 is departed from from the first output shaft 3 C and switching first is shifted gears for being connected to by idler gear 9 on idler gear 17, use the 5th preselected gear shift steps, to play a role with supporting and to prevent the interruption of tractive force.
In this case, when driving via the 3rd gear shift steps and the extension of the 3rd power path, initially, the second shift clutch K2 coordinates continuously, and the first shift clutch K1 throws off continuously.Therefore, power path is " intersect and mix " on the direction of the 5th power path.Then, cancel selected 3rd gear, that is, switch the first gearshift and arrange A, so that tooth-profile of gear is separated from the first output shaft 3 idler gear 8 of III.In addition, select the 4th gear, that is, by the 3rd gearshift arrange C be engaged with each other idler gear 9 and 17 and by second gearshift arrange B joined idler gear 15 to second output shaft 4.Then, the first shift clutch K1 coordinates continuously and the second shift clutch K2 throws off continuously, so that it is " intersect and mix " from the 5th power path to the 4th power path.The 5th power path is only used when there is shift process.
In fig. 8, the torque characteristics shown along with time two shift clutch K1, K2 is simplified.In this case, what become apparent is for the endurance from the 3rd gear shift steps to the handoff procedure of the 4th gear shift steps, uses the 5th gear shift steps, owing to being stored in the kinetic energy in driving, moment of torsion even occurs increase, it compensates the low moment of torsion of the 5th gear.In certain degree, wherein moment of torsion reduces at the first shift clutch K1 place, and the moment of torsion at the second shift clutch K2 place increases.When selection the 4th gear, support it by the 5th gear shift steps.Then, the second shift clutch K2 place moment of torsion reduce and the moment of torsion at the first shift clutch K1 place is increased to identical degree.
Then for further upshift, it can on the contrary again " intersect and mix " to the 5th gear shift steps.
In the 6th gear shift steps, when the first shift clutch K1 is closed and the second shift clutch K2 disconnects, 6th power path extends to first output shaft 3 via tooth-profile of gear to VI from the first input shaft 1, wherein the 3rd gearshift arranges that C joins the idler gear 9 of tooth-profile of gear to VI to first output shaft 3, or wherein the 3rd gearshift arranges that C joins parallel axes 18 to first output shaft 3, depend on that gear 9 is counted as idler gear on parallel axes 18 or fixed gear.
7th power path of the 7th gear shift steps corresponds to the first power path of the first gear shift steps, but, wherein the second input shaft 2 is not be connected to second output shaft 4 via tooth-profile of gear to VIII to II via tooth-profile of gear, and wherein the 4th gearshift arranges that D joins idler gear 14 to second output shaft 4.When from the 6th gear shift steps upshift, via octadentate wheel shift steps by supporting gearshift acquisition the 7th gear shift steps.
Represent that octadentate takes turns shift steps by the 8th power path, wherein when the first shift clutch K1 disconnects and the second shift clutch K2 closes, power path extends to the second output shaft 4 via tooth-profile of gear to VIII from the second input shaft 2, is wherein arranged by the 4th gearshift and joins the idler gear 14 of tooth-profile of gear to VIII to second output shaft 4.
The 9th gear shift steps is realized by the 9th power path, when the first shift clutch K1 is closed and the second shift clutch K2 disconnects, 9th power path extends to first output shaft 3 via tooth-profile of gear to IX from the first input shaft 1, wherein arranges that A joins the idler gear 10 of tooth-profile of gear to IX to first output shaft 3 by the first gearshift.
In the tenth gear shift steps, when the first shift clutch K1 disconnects and the second shift clutch K2 closes, the tenth power path extends to the first input shaft 1 via tooth-profile of gear to VI and extends to the first output shaft 3 via tooth-profile of gear to IX therefrom via tooth-profile of gear from the second input shaft 2 T1.In this case, via the 3rd gearshift, idler gear 17 arranges that C joins idler gear 9 to.In addition, via the first gearshift, idler gear 10 arranges that A is attached to the first output shaft 3.
Therefore, in the present embodiment of gearbox according to the present invention, be also advantageous in that two different shift processes are possible.On the one hand, " intersect and mix " from a shift clutch to another shift clutch is possible, as this is known from common double clutch gearbox.On the other hand, also possible situation is, the interruption of tractive force can be produced between two gear shift steps, when two gear shift steps of following each other realize via identical shift clutch, in order to prevent the interruption of tractive force, so that occur " supporting gearshift ", wherein for the endurance of shift process, support that ground uses gear shift steps, its power path extends via another shift clutch respectively.
Fig. 3 show schematically show the degrees of freedom of the gearbox of Fig. 1.By the first input expression first degrees of freedom of band first input shaft 1.By the second input expression second degrees of freedom of band second input shaft 2.Three Degree Of Freedom is represented by the output of band two output shafts 3,4.When these beam warps are rotated by profile of tooth output gear 20,21, two output shafts 3,4 form one degree of freedom (output) together, and this profile of tooth output gear connects with the actuation gear of differential mechanism, therefore can not rotate independently.The gearbox gear wheels of each degrees of freedom can be bonded to each other via connection (connecting the gear of form via in tooth-profile of gear in this case), so that also engage their rotary motion.Define each connection between each degrees of freedom in figure 3.Such as, the first input with the first input shaft 1 can connect via gear the second input that T1 joins band second input shaft 2 to.For engage two input different modification be connect R.Direct connection between the first input and output of band first input shaft 1, that is, to connect a generation in III, VI and IX via gear to the direct connection of in output shaft 3,4.The direct connection be input at second of band second input shaft 2 between in output shaft 3,4 connects II, V or VIII via gear and occurs.Therefore, direct gear is possible, wherein to output, Direct driver occurs via in connection from input.And " (generated) of generation " gear is possible, and wherein two inputs are connected to each other/engage, so that occur from input via the driving of another in input to output.
Fig. 2 shows the second embodiment according to gearbox of the present invention, wherein achieves the like combinations of the degrees of freedom of Fig. 3 and the identical shift schedule of Fig. 6 by this second embodiment.Corresponding parts provide identical reference character and are described with reference to Fig. 1.
With the gearbox of Fig. 1 unlike, parallel axes 18 is not formed hollow shaft, and the first output shaft 3 is formed hollow shaft.In addition, function is corresponding, and wherein present gear 9 only can be understood to be in the fixed gear on parallel axes 18.
In addition, tooth-profile of gear is arranged differently for reversing gear R.In this case, idler gear 19 is rotatably arranged into parallel axes 18 and engages with the idler gear 16 of tooth-profile of gear to II.
In addition, tooth-profile of gear is rotatably arranged around the second output shaft 4 sliding gear 8 of III.
Fig. 4 shows the 3rd embodiment according to gearbox of the present invention.The parts corresponding with the parts of first embodiment of Fig. 1 provide identical reference character and composition graphs 1 is described.
With the gearbox of the first embodiment unlike, via the 4th gearshift, idler gear 19 arranges that D joins the second output shaft 4 to and engages with the idler gear 8 of tooth-profile of gear to III.
Illustrate consequent degrees of freedom and connection in Figure 5.The shift schedule of forward gear corresponds to the shift schedule of Fig. 6.
Reference numerals list
1 first input shaft
2 second input shafts
3 first output shafts
4 second output shafts
5 fixed gears
6 fixed gears
7 fixed gears
8 idler gears
9 idler gear/fixed gears on axle
10 idler gears
11 fixed gears
12 fixed gears
13 fixed gears
14 idler gear/fixed gears on axle
15 idler gears
16 idler gears
17 idler gears
18 parallel axes
19 idler gears
20 profile of tooth output gears
21 profile of tooth output gears
Claims (15)
1. for the gearbox of motor vehicle, it is changeable between several gear shift steps, there is two inputs and an output, changeable connection (T1) wherein for forward gear is arranged between two inputs, and between being arranged in each in two inputs for three changeable connections of forward gear and exporting
Wherein, the first input in two inputs comprises the first input shaft (1), and the second input in two inputs comprises the second input shaft (2), and described first and second input shafts optionally can be driven by drive motor, and
Output comprises the first output shaft (3) and the second output shaft (4), described first and second output shafts are all connected to power train, for the wheel of driving machine motor vehicle, and it is selectively driven respectively by two input shafts (1,2)
Wherein two input shafts (1,2) are connected to each other via at least one gear with connecting (T1, R) driving, and
Each wherein in two input shafts (1,2) is at least connected at least one in two output shafts (3,4) via three gears with connecting driving.
2. gearbox according to claim 1, is characterized in that, the changeable connection (R) for reversing gear is arranged between two inputs.
3. gearbox according to claim 1, is characterized in that, the changeable connection (R) for reversing gear be arranged in two input in one and export between.
4. according to gearbox in any one of the preceding claims wherein, it is characterized in that, each in two inputs is connected to drive motor via respective clutch (K1, K2).
5. gearbox according to claim 3, is characterized in that, each in two inputs comprises input shaft (1,2), and wherein said two input shafts (1,2) are arranged to coaxially to each other.
6. gearbox according to any one of claim 1 to 3, is characterized in that, at least three forward gears, the changeable connection (T1) between two inputs is switched to status of ' connected '.
7. gearbox according to claim 6, is characterized in that, for four forward gears, the changeable connection (T1) between two inputs is switched to status of ' connected '.
8. gearbox according to any one of claim 1 to 3, it is characterized in that, gearbox is controlled so as to, from gear shift steps to gear shift steps subsequently shift process during, start gear shift steps in and occur in gear shift steps subsequently via two input in same driving, described gearbox is initially switched to supports gear shift steps, occur via another the driving in two inputs in described support gear shift steps, after this, during driving via another in two inputs, select gear shift steps subsequently, then, it is switched to gear shift steps subsequently, wherein there is the driving via the input identical with the gear shift steps started.
9. gearbox according to claim 8, is characterized in that, in shift schedule, reach at least two forward gears via support gear shift steps.
10. gearbox according to claim 8, is characterized in that, in the changeable gear shift steps of two loads of following each other, at least in two positions of shift schedule, the driving via identical input occurs.
11. gearboxes according to claim 9, is characterized in that, in the changeable gear shift steps of two loads of following each other, at least in two positions of shift schedule, the driving via identical input occur.
12. gearboxes according to any one of claim 1 to 3, is characterized in that, are connected to the second drive motor one in two inputs.
13. gearboxes according to any one of claim 1 to 3, is characterized in that, export and comprise two output shafts (3,4), and described output shaft is arranged parallel to each other and is arranged to be connected to driving a common driver gear of differential gear.
14. gearboxes according to claim 1, is characterized in that, the first input shaft (1) connects (III, VI, IX) via at least three gears and is connected to the first output shaft (3).
15. gearboxes according to claim 1 or 14, it is characterized in that, the second input shaft (2) connects (II, V, VIII) via at least three gears and is connected to the second output shaft (4).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102011050083.9 | 2011-05-04 | ||
| DE201110050083 DE102011050083A1 (en) | 2011-05-04 | 2011-05-04 | Gear box for motor car, has two input shafts connected to drive machine i.e. electro motor, and switchable gear wheel connection arranged between input shafts and output shafts and utilized for forward gears |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102767610A CN102767610A (en) | 2012-11-07 |
| CN102767610B true CN102767610B (en) | 2016-01-20 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210215650.9A Active CN102767610B (en) | 2011-05-04 | 2012-05-02 | Gearbox |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN102767610B (en) |
| DE (1) | DE102011050083A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012001948A1 (en) | 2012-02-02 | 2013-08-08 | Daimler Ag | Double clutch |
| WO2014166541A1 (en) | 2013-04-11 | 2014-10-16 | Fev Gmbh | Gearbox and method for operating the gearbox |
| DE102013019118B4 (en) * | 2013-11-15 | 2018-05-17 | Daimler Ag | Double clutch |
| DE102014206149A1 (en) | 2014-04-01 | 2015-10-01 | Volkswagen Aktiengesellschaft | Method for switching a motor vehicle transmission |
| DE102020003896A1 (en) | 2020-06-30 | 2020-09-10 | FEV Group GmbH | Double clutch |
| IT202100018032A1 (en) | 2021-07-08 | 2023-01-08 | Ge Avio Srl | GAS TURBINE |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10015336A1 (en) * | 2000-03-28 | 2001-10-04 | Volkswagen Ag | Dual clutch gearbox has elements arranged so that for certain engaged gear drive train consists of first drive shaft, parallel shaft, second input shaft and output shaft |
| DE10133695A1 (en) * | 2000-07-18 | 2002-03-07 | Luk Lamellen & Kupplungsbau | Double clutch gear has input and output shafts, pairs of cog wheels of loose and fixed wheels, with corresponding shafts, gears and drive unit |
| US7225696B2 (en) * | 2004-03-05 | 2007-06-05 | Daimlerchrysler Ag | Double clutch transmission |
| CN101251168A (en) * | 2007-02-22 | 2008-08-27 | 通用汽车环球科技运作公司 | Multi-speed transmission with countershaft gearing |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004263708A (en) * | 2003-01-14 | 2004-09-24 | Kyowa Metal Work Co Ltd | Twin clutch type transmission |
| DE102004043939B4 (en) * | 2004-09-11 | 2016-09-29 | Daimler Ag | Double clutch |
-
2011
- 2011-05-04 DE DE201110050083 patent/DE102011050083A1/en not_active Ceased
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2012
- 2012-05-02 CN CN201210215650.9A patent/CN102767610B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10015336A1 (en) * | 2000-03-28 | 2001-10-04 | Volkswagen Ag | Dual clutch gearbox has elements arranged so that for certain engaged gear drive train consists of first drive shaft, parallel shaft, second input shaft and output shaft |
| DE10133695A1 (en) * | 2000-07-18 | 2002-03-07 | Luk Lamellen & Kupplungsbau | Double clutch gear has input and output shafts, pairs of cog wheels of loose and fixed wheels, with corresponding shafts, gears and drive unit |
| US7225696B2 (en) * | 2004-03-05 | 2007-06-05 | Daimlerchrysler Ag | Double clutch transmission |
| CN101251168A (en) * | 2007-02-22 | 2008-08-27 | 通用汽车环球科技运作公司 | Multi-speed transmission with countershaft gearing |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102767610A (en) | 2012-11-07 |
| DE102011050083A1 (en) | 2012-11-08 |
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