CN103459894A - Transmission system, as well as method for changing first gear ratio - Google Patents
Transmission system, as well as method for changing first gear ratio Download PDFInfo
- Publication number
- CN103459894A CN103459894A CN2011800678283A CN201180067828A CN103459894A CN 103459894 A CN103459894 A CN 103459894A CN 2011800678283 A CN2011800678283 A CN 2011800678283A CN 201180067828 A CN201180067828 A CN 201180067828A CN 103459894 A CN103459894 A CN 103459894A
- Authority
- CN
- China
- Prior art keywords
- clutch
- transmission
- carry
- transmission system
- input
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- 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
-
- 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
-
- 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
- F16H2003/008—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 comprising means for selectively driving countershafts
-
- 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
-
- 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
- F16H2003/0933—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 with coaxial countershafts
-
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
A transmission system for a vehicle is disclosed. The transmission system comprises an input shaft which can be connected to a drive source, and an output shaft which can be connected to a load, and further comprises a clutch module which has an input that is connected among the input shaft and a first and a second output, as well as first clutch means which are located between the input and the first output and second clutch means which are located between the input and the second output, and gear stage means which are located between the input and the first or second output; as well as a transmission module which has a first and a second input and an output that is connected to the output shaft, a first sub-transmission which is located between the first input and the output, and a second sub-transmission which is located between the second input and the output; wherein the first output of the clutch module is connected to the first input of the transmission module and the second input of the clutch module is connected to the second input of the transmission module, and the first and second sub-transmissions each comprise an input shaft and an output shaft which are connected to the inputs and output of the transmission module and each comprise at least one gear stage located between the input and output shafts.
Description
Technical field
The present invention relates to a kind of transmission system for vehicle (transmission system), this transmission system comprises the input shaft that can be connected to driving source and the output shaft that can be connected to load.
Background technique
Patent documentation EP-A-1625037 discloses a kind of transmission system, when this transmission system is applied to vehicle, does not need to interrupt just can realize from driving source to the moment of torsion transmission of taking turns the change of gear stage (gear stage, gear).The module forming section of this known transmission system is very suitable for using in existing speed changer.
Summary of the invention
Target of the present invention is to provide a kind of transmission system of the type limited in first section, it is compared and has more cost benefit with known transmission system, and, by this transmission system, even do not interrupt, from driving source, to the moment of torsion transmission of wheel, can two or more gear stage, do not switched yet.Based on this purpose, transmission system according to the present invention is characterised in that, this transmission system comprises clutch module and transmission module, this clutch module has: input part, be connected to input shaft and the first and second carry-out parts, and first clutch device, it is between input part and the first carry-out part, the second clutch device, it is between input part and the second carry-out part, and gear stage device, it is between input part and the first or second carry-out part, the carry-out part that this transmission module has the first and second input parts and is connected to output shaft, the first auxiliary transmission, it is between the first input part and carry-out part, and second auxiliary transmission, it is between the second input part and carry-out part, wherein the first carry-out part of clutch module is connected to the first input part of transmission module, and the second carry-out part of clutch module is connected to the second input part of transmission module, and wherein the first and second auxiliary transmissions comprise the input part that is connected to transmission module and input shaft and the output shaft of carry-out part separately, and comprise separately at least one gear stage, these gear stage are between input shaft and output shaft.Can replace speed changer and clutch and use in vehicle according to transmission system of the present invention, and compare simpler with known transmission system and have more the cost benefit part and be: transmission module only need have less gear stage, but still can realize a lot of different gear ratios.
Preferably, at least one auxiliary transmission comprises at least one transmission clutch, and this transmission clutch is between the input shaft and output shaft of this auxiliary transmission.
According to an embodiment of transmission system of the present invention, be characterised in that, the first clutch device is formed by break, and the gear stage device is between input part and the first carry-out part, and formed by planetary gear set, this planetary gear set comprises at least three rotating members, wherein the first rotating member is connected to input part, and the second rotating member is connected to the first carry-out part, and the 3rd rotating member is connected to break.
According to another embodiment of transmission system of the present invention, be characterised in that, the first clutch device is formed by first clutch, and the gear stage device forms between input part and the first carry-out part and by the master gear level.
According to another embodiment of transmission system of the present invention, be characterised in that, transmission system comprises interposed clutch, and this interposed clutch is between two input parts of transmission module, or between two carry-out parts of clutch module.
The gear ratio of the maximum of this transmission system is preferably by making driving force obtain via first clutch device, interposed clutch and the second auxiliary transmission transmission, and wherein the second auxiliary transmission in two auxiliary transmissions has larger gear ratio.The rpm that this gear ratio is input part (RPM) is divided by the RPM of carry-out part.
In addition, preferably, the gear ratio of the minimum of this transmission system is by driving force is realized via second clutch device, interposed clutch and the first auxiliary transmission transmission, and wherein the first auxiliary transmission in two auxiliary transmissions has less gear ratio.
According to another embodiment of transmission system of the present invention, be characterised in that, transmission system comprises intermediate gear stages, this intermediate gear stages, between two input parts of transmission module, or between two carry-out parts of clutch module, and is connected to interposed clutch.
Two input parts and the carry-out part of transmission module are preferably coaxial.
Be characterised in that to there is direct clutch between the second input part of transmission module and carry-out part, in order to the second input part directly is connected to carry-out part according to another embodiment of transmission system of the present invention.
According to another embodiment of transmission system of the present invention, be characterised in that, the first auxiliary transmission comprises buncher.
The present invention relates to a kind of like this method equally, and the method is not interrupted the method that the moment of torsion from the input part according to transmission system of the present invention to carry-out part transmits for the first gear ratio is changed into to the second gear ratio thereafter.About the method, the invention is characterized in, be one of them energy supply of clutch device, and be wherein less energy supply of another clutch device, and transmission clutch is not changed.
The embodiment of the method according to this invention is characterised in that, at first gear ratio is changed into to the 3rd gear ratio, thereafter gear ratio is changed into to the second gear ratio.
The accompanying drawing explanation
Below, the example of the embodiment according to transmission system of the present invention based on shown in accompanying drawing is described to the present invention in more detail.
Embodiment
Fig. 1 provides the sketch according to the first embodiment of transmission system of the present invention.This transmission system M1 comprises: input shaft M
in, it can be connected to driving source A; And output shaft M
out, it can be connected to load L.Transmission system M1 also comprises clutch module C, and this clutch module has the input shaft of being connected to M
inand the first and second carry-out part C
out1and C
out2input part C
in.This clutch module comprises: the gear stage device, and it is formed by planetary gear set P; The first clutch device, it is formed by break B, and this break B is connected to a rotating member of planetary gear set; And the second clutch device, it is formed by clutch C2.Planetary gear set and break are positioned at input part C
inwith the first carry-out part C
out1between, clutch C2 is positioned at input part C
inwith the second carry-out part C
out2between.Transmission system M1 also comprises transmission module T, and this transmission module has the first and second input part T
in1and T
in2and be connected to output shaft M
outcarry-out part T
out.Transmission module T comprises: the first auxiliary transmission T1, it is positioned at the first input part T
in1with carry-out part T
outbetween; And the second auxiliary transmission T2, it is positioned at the second input part T
in2with carry-out part T
outbetween.The first carry-out part of clutch module C is connected to the first input part of transmission module T, and the second carry-out part of clutch module is connected to the second input part of transmission module.The first and second auxiliary transmission T1 and T2 have the input part that is connected respectively to transmission module and input shaft and the output shaft of carry-out part separately, and have respectively gear stage I1 and the I2 between input shaft and output shaft.The first auxiliary transmission T1 also comprises transmission clutch S1, and this transmission clutch is between the input shaft and output shaft of this auxiliary transmission.Transmission module T also has interposed clutch S, and this interposed clutch is positioned at two input part T of transmission module
in1with T
in2between.
Fig. 2 provides the sketch according to the second embodiment of transmission system of the present invention.In this transmission system M2, the first clutch device is formed by another clutch C1, and this gear stage device is formed by gear stage I.These gear stage devices I is located in clutch module and between the first carry-out part in clutch C1 and clutch module.
Fig. 3 and Fig. 4 show transmission system M3 and M4, and transmission system M3 and M4 have two transmission clutch S1, S11 laying respectively in each auxiliary transmission T1 and T2 and S2, S22 and two gear stage I1, I11 and I2, I22 separately.
The speed changer gear ratio (first grade) of the minimum of whole transmission system is to obtain by the gear stage device I of first clutch device C1/B, clutch module or P and the second auxiliary transmission T2, and interposed clutch S is closed simultaneously.
The gear stage device I of clutch module or the gear ratio of P are selected as making it possible to realize by closed clutch C1 or break B the minimum forward gears of transmission system (first grade).
The speed changer gear ratio (the most sluggish speed changer gear ratio) that there is the minimum from I1 to Ix in T2.
The velocity ratio of the maximum of whole transmission system is to obtain by second clutch device C2 and the first auxiliary transmission T1, and wherein interposed clutch S is closed.
The velocity ratio of the maximum of whole transmission system is to obtain by second clutch device C2 and the second auxiliary transmission T2, and wherein interposed clutch S is closed or opens.
The second gear of whole transmission system is to obtain by second clutch device C2 and the second auxiliary transmission T2, and wherein interposed clutch S is closed or opens.
From first grade of switching to second gear of transmission system, be by second clutch device C2 energy supply/closed second clutch device C2 and to first clutch device C1 or less energy supply of B/open first clutch device C1 or B realizes (keeping the moment of torsion carry-out part) simultaneously.Afterwards, do not need to operate another transmission clutch.
Fig. 5 shows the first functional modification of transmission system, wherein indicated a plurality of grades of G(to omit other details).1,2 grades and 4,5 grades also can be identical in T2 function conversion.Reverse gear R both can be located in T1 and T2, can be located between T1 and T2 again.
Fig. 6 and Fig. 7 illustrate the first embodiment of the first modification shown in Fig. 5, and it comprises bypass speed changer P, break B and a countershaft.Clutch S and S1 can operate by a reverse shift fork, and clutch S2 and S22 can operate by a reverse shift fork.
Fig. 8 and Fig. 9 show the second embodiment, and it comprises bypass speed changer P and break B and two countershafts.Clutch S and S1 can operate by a reverse shift fork, and clutch S2 and S22 also can operate by a reverse shift fork.
Figure 10 and Figure 11 show the 3rd embodiment, and it comprises gear stage I and clutch C1 and a countershaft.Clutch S and S1 can operate by a reverse shift fork, and clutch S2 and S22 also can operate by a reverse shift fork.
Figure 12 and Figure 13 show the 4th embodiment, and it comprises gear stage I, clutch C1 and two countershafts.Clutch S and S1 can operate by a reverse shift fork, and clutch S2 and S22 also can operate by a reverse shift fork.
The third gear of whole transmission system is to obtain by the gear stage element I of first clutch device C1 or B, clutch module or P and the first auxiliary transmission T1, and wherein another clutch S opens.
Switching from the second gear of whole transmission system to third gear is by first clutch device C1 or B energy supply/closed first clutch device C1 or B and to less energy supply of second clutch device C2/open second clutch device C2 to realize (keeping the moment of torsion carry-out part) simultaneously.Afterwards, do not need to operate other clutch.
The fourth speed of whole transmission system is to obtain by the gear stage element I of first clutch device C1 or B, clutch module or P and the second auxiliary transmission T2, and wherein another clutch S is closed.
The 5th grade of whole transmission system is to obtain by second clutch device C2 and the second auxiliary transmission T2, and wherein another clutch S is closed or opens.
Switching from the third gear of transmission system to fourth speed be by the C2 energy supply of second clutch device and to first clutch device C1 or B less energy supply realize (keeping the moment of torsion carry-out part) simultaneously.If first clutch device C1 or B be transmitting torque not basically, they are opened.Subsequently, another clutch S is closed, and to the further energy supply of second clutch device C2, until first clutch device C1 or B can be closed basically simultaneously, and second clutch device C2 can be opened.During this handover operation, other transmission clutch is operated really.During this handover operation, moment of torsion gain is by the 5th grade of generation lower than fourth speed.
From the switching of five grades of the fourth speeds to the of transmission system, be by second clutch device C2 energy supply/closed second clutch device C2 and to first clutch device C1 or less energy supply of B/open first clutch device C1 or B realizes (keeping the moment of torsion carry-out part) simultaneously.Afterwards, do not need to operate other transmission clutch.
Carry out one or more handover operations in transmission system, in transmission system, realize via (x+2), (x+3) or (x+4) shelves from the switching of x to the (x+1) grade of transmission system.
Clutch S and S1 operate by a reverse shift fork, and clutch S2 and S22 operate by another reverse shift fork.
In the transmission system shown in Figure 10 and Figure 11, transmission module is set to have a countershaft, and wherein the carry-out part of the carry-out part of T1 and T2 is connected to the carry-out part of transmission module by a final reduction part IF.
In the transmission system shown in Fig. 8 and Fig. 9 and Figure 12 and Figure 13, transmission module is set to have at least two countershafts, wherein the carry-out part of T1 is connected to the carry-out part of transmission module by a final reduction part IF1, and wherein the carry-out part of T2 is connected to the carry-out part of transmission module by two final reduction part (IF1 and IF2).
In following Figure 38 and the transmission system shown in Figure 39, transmission module is set to have at least two countershafts, wherein the carry-out part of T2 is connected to the carry-out part of transmission module by a final reduction part IF2, and wherein the carry-out part of T1 is connected to the carry-out part of transmission module by two final reduction part (IF1 and IF2).
In following Figure 40 and the transmission system shown in Figure 41, transmission module is set to have at least two countershafts, wherein the carry-out part of T1 is connected to the carry-out part of transmission module by two final reduction part (IF1 and IF2), and wherein the carry-out part of T2 is connected to the carry-out part of transmission module by two final reduction part (IF1 and IF2).
Transmission module also can comprise reverse gear, and this reverse gear can be in T1 and T2 and between T1 and T2.In the transmission system of describing in Fig. 5 and after Figure 35 and Figure 36 in, reverse gear R is arranged in T2, and is set to asynchronous (asynchronous engagement).
If reverse gear is between T1 and T2, it can consist of two extra gears (gearwheel), wherein the first gear and I1 or I engagement, and the second gear and I2 or I22 engagement.Also reversing clutch sr can be set between two extra gears, this reversing clutch sr preferably operates by another reverse shift fork.In addition, these two extra gears preferably arrange (having identical axis) coaxially with the second countershaft.
In the transmission system shown in Figure 10 and Figure 11 and Figure 12 and Figure 13, between two input parts of two carry-out parts of clutch module and/or transmission module, be provided with another gear stage.Another clutch S with respect to first and/or the second clutch device arrange coaxially.
Another clutch S can be set to friction clutch, dog-clutch, synchromesh clutch, or is set to freewheel bearing/free wheel device.Clutch C1 can be set to dry plate or humidity strip friction clutch.Clutch C2 also can be set to dry plate or humidity strip friction clutch.Break B can be set to dry plate or humidity strip friction brake.
Break B preferably is set to the humidity strip break, and clutch C2 is set to dry piece friction clutch, or break is set to the dry plate break, and clutch C2 is set to the humidity strip friction clutch.
Can be provided with another gear stage between the second carry-out part of clutch module and clutch C1 and/or between the second carry-out part of clutch module and clutch C2.
Gear stage device P can be set to have the bypass speed changer (planetary gear set) of minimum three rotating members, wherein the first member is connected to the input part of clutch module, second component is connected to the first carry-out part of clutch module, and the 3rd member is connected to break B.The first rotating member is preferably formed by ring gear, and the second rotating member is formed by planetary carrier, and the 3rd member is formed by sun gear.
The first and second input shafts of transmission module can be other by least one clutch S directly be coupled to each other.
Break B often leaves.Clutch C1 and/or C2 are Chang Kai or normally closed.Clutch C2 is operated by pull bar or the push rod through input transmission shaft (the second input shaft).
Auxiliary transmission T1 and T2 comprise a minimum gear stage that can switch on and off.Clutch s1, s11, s2, s22 etc. are positioned on the input side of gear stage I1, I11, I2, I22 and/or on outlet side.
The first gear from final reduction part IF to differential mechanism can be the gear identical with the second gear of gear stage I1, and wherein s1 is coaxial (having identical axis) with another clutch S.
Can be provided with the motor (motor/generator) that can drive vehicle.This motor can be connected to any arbitrary axis (arbitrary shaft) of driving mechanism or transmission system.This motor can be connected to and make it to drive in the mode of complete electric power, and in the case, internal-combustion engine can break away from from driver circuit.This motor is preferably located between driving source and clutch module, or this motor is connected to the second input shaft of transmission module and/or the second output shaft of clutch module.When be switched to next shelves from shelves, when the energy that makes motor can reduce significantly clutch C2 consumes, this motor can play booster action.Clutch C2 can be set to dog-clutch and/or synchromesh gear (synchromesh).
Above-mentioned driving concept can:
-for rear wheel drive, in the case, output shaft is connected to the rear portion differential mechanism by differential gear case;
-for four-wheel drive, in the case, front-wheel configuration (engine laterally is installed) or trailing wheel configuration (engine vertically is installed) are used as basis;
-be set to comprise any planetary gear set arbitrarily with break and clutch;
-combined with all embodiments of the planetary gear set with the break shown in above-mentioned accompanying drawing and clutch;
-be provided with the possible embodiment of any reverse gear; And
-be provided with the possible embodiment of any stop mechanism.
Figure 14 shows the second functional modification of the transmission system of gear stage comprising in T1 and a gear stage in T2.Figure 15 and Figure 16 show the constructive embodiment of this modification that comprises the buncher in T1.Speed changer T2 or IF hold reverse gear.The gear of T2 and/or I2 forms this part.
By to break B energy supply, can start in the forward and backward directions from halted state.Afterwards, can not load variable-speed motor (variator).When from break, being switched to clutch, driving torque exists.When clutch closure and break are opened, still do not load variable-speed motor.At this moment can make dog-clutch and/or synchronizer S throw off and closed S1.By from clutch, again switching and get back to break, can carry out the machine driving and realize higher gear by speed change.Therefore, there are two and start shelves (a drive-off gear) on gear and third gear, and can realize on a plurality of upgrading (3-10) by variable-speed motor.As a result, can realize very large velocity ratio coverage area.In addition, variable-speed motor can be set to much smaller pattern (RC between 3 and 4).
Figure 17 shows the 3rd functional modification of the transmission system of gear stage comprising in T1 and a gear stage in T2;
Figure 18 shows the 4th functional modification of the transmission system of gear stage comprising in T1 and two gear stage in T2;
Figure 19 shows the five-function modification of the transmission system of gear stage comprising in T1 and two gear stage in T2;
Figure 20 shows the 6th functional modification of the transmission system of gear stage comprising in T1 and two gear stage in T2;
Figure 21 shows the 7th functional modification of the transmission system of gear stage comprising in T1 and two gear stage in T2;
Figure 22 shows the 8th functional modification of the transmission system of two gear stage comprising in T1 and two gear stage in T2;
Figure 23 shows the 9th functional modification of the transmission system of two gear stage comprising in T1 and two gear stage in T2;
Figure 24 shows the tenth functional modification of the transmission system of two gear stage comprising in T1 and two gear stage in T2;
Figure 25 shows the 11 functional modification of the transmission system of two gear stage comprising in T1 and two gear stage in T2;
Figure 26 shows the 12 functional modification of the transmission system of gear stage comprising in T1 and three gear stage in T2;
Figure 27 shows the 13 functional modification of the transmission system of gear stage comprising in T1 and three gear stage in T2;
Figure 28 shows the 14 functional modification of the transmission system of gear stage comprising in T1 and three gear stage in T2;
Figure 29 shows the tenth five-function modification of the transmission system of gear stage comprising in T1 and three gear stage in T2;
Figure 30 shows the 16 functional modification of the transmission system of two gear stage comprising in T1 and three gear stage in T2;
Figure 31 shows the 17 functional modification of the transmission system of two gear stage comprising in T1 and three gear stage in T2;
Figure 32 shows the 18 functional modification of the transmission system of two gear stage comprising in T1 and three gear stage in T2;
Figure 33 shows the 19 functional modification of the transmission system of two gear stage comprising in T1 and three gear stage in T2;
Figure 34 shows the 20 functional modification of the transmission system of two gear stage comprising in T1 and three gear stage in T2;
Figure 35, Figure 36 and Figure 37 show the constructive embodiment of the 8th to the 12 modification that comprises a countershaft;
Figure 38 and Figure 39 show the constructive embodiment of the 8th to the 12 modification that comprises two countershafts;
Figure 40 and Figure 41 also show the constructive embodiment of the 8th to the 12 modification that comprises two countershafts;
Figure 42 and Figure 43 show the constructive embodiment of the 13 to the 15 modification that comprises two countershafts;
Figure 44 shows the constructive embodiment's of the rear wheel drive for comprising clutch SF and/or S3 example to Figure 51.Described belowly there is clutch SF(and there is no S3) modification there is the function identical with above-mentioned modification 1 to 7, but the input shaft of transmission system and output shaft are arranged (having identical axis) coaxially.This is applicable to rear wheel drive vehicle significantly, as (gently) truck and bus.IF has replaced gear stage I22, and SF has replaced clutch S22.By extra clutch S3, can realize extra gear via I1, I2 and SF, and not need to increase extra gear.
Figure 46 and Figure 47 show the embodiment of five grades of transmissions, and wherein S1 and S operate by a reverse shift fork, and S2 and SF are also like this.
Deceleration based on following forms the gear hereinafter mentioned:
Deceleration T1=1.4(1.0)
Deceleration T2=2.74(1.96)
Deceleration IF=1.0(1.4)
First grade of 3.84(break, S, s2 closure)
Second gear 2.74(clutch, s2 closure)
Third gear 1.96(break, s1 closure)
Fourth speed 1.4(clutch, S, s1 closure)
The 5th grade of (break, S, sf closure) (clutch, sf closure)
By changing the moment of torsion transmission between brakes and clutches, can when keeping moment of torsion to transmit, between first group of (1 to 5) gear, be switched, in the case, clutch s1, s2 and S can be switched on or switched off in unloaded.
Yet, carry out the switching meeting between third gear and fourth speed more difficult when keeping moment of torsion.In third gear, sf can be closed, makes the moment of torsion transmission to be undertaken by friction clutch C.Subsequently, by clutch C energy supply, can apply the 5th grade.Before the 5th grade of quilt is synchronous, can also be by be switched to S and closed break application fourth speed from s1.From this situation, by from break, changing to clutch and easily be switched to the 5th grade.
Figure 48 and Figure 49 show the embodiment of six grades of transmissions by the independent operation of S1 and S2.
Deceleration based on following forms the gear hereinafter mentioned:
Deceleration T1=1.96
Deceleration T2=3.84
Deceleration IF=1.0
First grade of 5.38(break, S, s2 closure)
Second gear 3.84(clutch, s2 closure)
Third gear 2.74(break, s1 closure)
Fourth speed 1.96(clutch, S, s1 closure)
The 5th grade of 1.4(break, S, sf closure)
The 6th grade of 1.0(clutch, sf closure)
By changing the moment of torsion transmission between brakes and clutches, can when keeping moment of torsion to transmit, between first group of (first to the 4th) gear, be switched, in the case, clutch s1, s2 and S can be switched on or switched off in unloaded.
By changing the moment of torsion transmission between brakes and clutches, can when keeping moment of torsion to transmit, between second group of (5 and 6) gear, be switched, in the case, clutch s1, s2 and S can be switched on or switched off in unloaded.
Yet, carry out the switching meeting between first and second group more difficult when keeping moment of torsion.For this purpose, sf must can be connected and not to its loading.Yet this can realize by for example from third gear, being switched to the 6th grade really.In third gear, sf can be closed, makes the moment of torsion transmission to be undertaken by friction clutch C.Afterwards, can operate the 6th grade by closed clutch C.Before the 6th grade of quilt is synchronous, the 5th grade can be operated.From this situation, any gear can arrive second group when keeping moment of torsion in.
Figure 50 and 51 shows the embodiment of seven grades of transmissions by adding S3 to form.
Deceleration based on following forms the gear hereinafter mentioned:
Deceleration T1=1.96
Deceleration T2=3.84
Deceleration IF=1.0
First grade of 5.38(break, S, s2, s3 closure)
Second gear 3.84(clutch, s2, s3 closure)
Third gear 2.74(break, s1, s3 closure)
Fourth speed 1.96(clutch, S, s1, s3 closure)
The 5th grade of 1.4(break, S, sf closure)
The 6th grade of 1.0(clutch, sf closure)
The 7th grade of 0.71(break, s1, s2, sf closure)
By changing the moment of torsion transmission between brakes and clutches, can when keeping moment of torsion to transmit, between first group of (first to the 4th) gear, be switched, in the case, clutch s, s1, s2 and s3 can be switched on or switched off in unloaded.
By changing the moment of torsion transmission between brakes and clutches, can when keeping moment of torsion to transmit, between second group of (the 5th to the 7th) gear, be switched, in the case, clutch s, s1, s2 and sf can be switched on or switched off in unloaded.
Yet, carry out the switching meeting between first group and second group more difficult when keeping moment of torsion.For this purpose, must between s3 and sf, switch and not to its loading.Yet this can realize by for example from third gear, being switched to the 6th grade really.In third gear, sf can be closed, makes it possible to carry out the moment of torsion transmission by friction clutch C, makes s3 no longer be loaded and can be opened (seeing Figure 52).Afterwards, can apply the 6th grade by closed clutch C.Before the 6th grade of quilt is synchronous, the 5th grade can be employed.From this situation, any gear can arrive second group when keeping moment of torsion in.
In an above-mentioned transmission system, between the input shaft of clutch module and internal-combustion engine, can be provided with torque-converters TC.See Figure 53.
In addition, in an above-mentioned transmission system, can construct coaxially a clutch service portion around the oily input/out parts of torque-converters.
In addition, on an above-mentioned transmission system, between the input shaft of clutch module and internal-combustion engine, can be provided with motor.
Described the present invention although above based on accompanying drawing, yet should see, the present invention never in any form or means be limited to the embodiment shown in accompanying drawing.The present invention also prolongs and is covered by the spirit and scope that claims limit but all embodiments different from the embodiment shown in accompanying drawing.
Claims (13)
1. the transmission system for vehicle, comprising: input shaft (M
in), it can be connected to driving source (A); And output shaft (M
out), it can be connected to load (L), and this transmission system comprises:
-clutch module (C), it has: input part (C
in), be connected to described input shaft and the first carry-out part (C
out1) and the second carry-out part (C
out2); First clutch device (B; C1), it is between described input part and described the first carry-out part; Second clutch device (C2), it is between described input part and described the second carry-out part; And gear stage device (P; I), it is between described input part and the described first or second carry-out part; And
-transmission module (T) has: the first input part (T
in1) and the second input part (T
in2) and the carry-out part (T that is connected to described output shaft
out); The first auxiliary transmission (T1), it is between described the first input part and described carry-out part; And second auxiliary transmission (T2), its between described the second input part and described carry-out part,
The first carry-out part (C of-wherein said clutch module
out1) be connected to the first input part (T of described transmission module
in1), and the second carry-out part (C of described clutch module
out2) be connected to the second input part (T of described transmission module
in1), and
-wherein said the first auxiliary transmission (T1) comprises with the second auxiliary transmission (T2) input shaft and the output shaft be connected with carry-out part with the input part of described transmission module separately, and comprise separately at least one gear stage (I1, I2), described gear stage is between described input shaft and described output shaft.
2. transmission system according to claim 1, it is characterized in that, at least one auxiliary transmission (T1, T11, T2, T22) comprises at least one transmission clutch (S1, S11, S2, S22), and described transmission clutch is between the input shaft and output shaft of this auxiliary transmission.
3. transmission system according to claim 1 and 2, it is characterized in that, described first clutch device is formed by break (B), and described gear stage device forms between described input part and described the first carry-out part and by planetary gear set (P), described planetary gear set comprises at least three rotating members, wherein the first rotating member is connected to described input part, and the second rotating member is connected to described the first carry-out part, and the 3rd rotating member is connected to described break.
4. transmission system according to claim 1 and 2, it is characterized in that, described first clutch device is formed by first clutch (C1), and described gear stage device forms between described input part and described the first carry-out part and by master gear level (I).
5. according to the described transmission system of any one of the preceding claims, it is characterized in that, described transmission system comprises interposed clutch (S), and described interposed clutch is between two input parts of described transmission module, or between two carry-out parts of described clutch module.
6. transmission system according to claim 5, is characterized in that, the gear ratio of the maximum of described transmission system is by making driving force via described first clutch device (B; C1), the transmission of described interposed clutch (S) and described the second auxiliary transmission (T2) realizes, described the second auxiliary transmission in wherein said two auxiliary transmissions has larger gear ratio.
7. according to the described transmission system of claim 5 or 6, it is characterized in that, the gear ratio of the minimum of described transmission system is that described the first auxiliary transmission in wherein said two auxiliary transmissions has less gear ratio by driving force is realized via the transmission of described second clutch device (C2), described interposed clutch (S) and described the first auxiliary transmission (T1).
8. according to claim 5,6 or 7 described transmission systems, it is characterized in that, described transmission system comprises intermediate gear stages (I ' '), described intermediate gear stages is between two input parts of described transmission module, perhaps between two carry-out parts of described clutch module, and be connected to described interposed clutch (S).
9. according to the described transmission system of any one of the preceding claims, it is characterized in that, two described input parts and the carry-out part of described transmission module are coaxial.
10. according to the described transmission system of any one of the preceding claims, it is characterized in that, there is direct clutch (SF) between the second input part of described transmission module and carry-out part, in order to described the second input part directly is connected to described carry-out part.
11. according to the described transmission system of any one of the preceding claims, it is characterized in that, described the first auxiliary transmission (T1) comprises stepless speed variator.
A 12. method; for being changed into to the second gear ratio thereafter, the first gear ratio do not interrupt the moment of torsion transmission from the input part as claim 5,6 or 7 claimed transmission systems to carry-out part; it is characterized in that; one of them energy supply for described clutch device; and be another less energy supply of described clutch device, and do not change described transmission clutch.
13. method according to claim 12, is characterized in that, at first described gear ratio changed into to the 3rd gear ratio, thereafter described gear ratio changed into to the second gear ratio.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610641064.9A CN106195190B (en) | 2011-10-18 | 2011-12-20 | Transmission system and the method for changing transmission ratio |
Applications Claiming Priority (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| NL2007613 | 2011-10-18 | ||
| NL2007613 | 2011-10-18 | ||
| NL2007625 | 2011-10-20 | ||
| NL2007625 | 2011-10-20 | ||
| NL2007939 | 2011-12-09 | ||
| NL2007939 | 2011-12-09 | ||
| PCT/NL2011/050862 WO2012112028A2 (en) | 2010-12-17 | 2011-12-20 | Transmission system, as well as method for changing a first gear ratio |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610641064.9A Division CN106195190B (en) | 2011-10-18 | 2011-12-20 | Transmission system and the method for changing transmission ratio |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103459894A true CN103459894A (en) | 2013-12-18 |
| CN103459894B CN103459894B (en) | 2016-09-14 |
Family
ID=49740491
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180067828.3A Active CN103459894B (en) | 2011-10-18 | 2011-12-20 | transmission system |
| CN201610641064.9A Active CN106195190B (en) | 2011-10-18 | 2011-12-20 | Transmission system and the method for changing transmission ratio |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610641064.9A Active CN106195190B (en) | 2011-10-18 | 2011-12-20 | Transmission system and the method for changing transmission ratio |
Country Status (1)
| Country | Link |
|---|---|
| CN (2) | CN103459894B (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104685261A (en) * | 2012-07-24 | 2015-06-03 | Dti集团有限公司 | Transmission system |
| CN107117023A (en) * | 2016-02-25 | 2017-09-01 | 通用汽车环球科技运作有限责任公司 | Automotive transmission |
| CN110273987A (en) * | 2018-03-15 | 2019-09-24 | 丰田自动车株式会社 | Automatic transmission |
| FR3083581A1 (en) * | 2018-07-06 | 2020-01-10 | Suzuki Motor Corporation | VEHICLE TRANSMISSION |
| EP3739238A1 (en) * | 2019-05-14 | 2020-11-18 | Deere & Company | Power transmission for agricultural machines |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE1027844B1 (en) * | 2019-12-11 | 2021-07-12 | Punch Powertrain Psa E Trans Nv | Transmission system for a vehicle |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1209017A2 (en) * | 2000-11-24 | 2002-05-29 | Honda Giken Kogyo Kabushiki Kaisha | Power transmission device for hybrid vehicle |
| CN1802272A (en) * | 2003-05-08 | 2006-07-12 | Dti集团有限公司 | Transmission system, in particular for a motor vehicle |
| CN101061013A (en) * | 2004-10-20 | 2007-10-24 | Dti集团有限公司 | Drive and transmission module with a layout adapted for a vehicle |
| CN101149093A (en) * | 2006-09-18 | 2008-03-26 | 通用汽车环球科技运作公司 | Multi-speed transmission |
| CN101189449A (en) * | 2005-04-08 | 2008-05-28 | Dti集团有限公司 | Drive for a vehicle, in particular a lorry |
| DE102008030516A1 (en) * | 2007-12-17 | 2009-06-18 | Hyundai Motor Company | Automatic transmission of a vehicle |
| CN101779060A (en) * | 2007-06-15 | 2010-07-14 | 麦格纳动力系有限公司 | Dual clutch transmission with planetary gearset |
-
2011
- 2011-12-20 CN CN201180067828.3A patent/CN103459894B/en active Active
- 2011-12-20 CN CN201610641064.9A patent/CN106195190B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1209017A2 (en) * | 2000-11-24 | 2002-05-29 | Honda Giken Kogyo Kabushiki Kaisha | Power transmission device for hybrid vehicle |
| CN1802272A (en) * | 2003-05-08 | 2006-07-12 | Dti集团有限公司 | Transmission system, in particular for a motor vehicle |
| CN101061013A (en) * | 2004-10-20 | 2007-10-24 | Dti集团有限公司 | Drive and transmission module with a layout adapted for a vehicle |
| CN101189449A (en) * | 2005-04-08 | 2008-05-28 | Dti集团有限公司 | Drive for a vehicle, in particular a lorry |
| CN101149093A (en) * | 2006-09-18 | 2008-03-26 | 通用汽车环球科技运作公司 | Multi-speed transmission |
| CN101779060A (en) * | 2007-06-15 | 2010-07-14 | 麦格纳动力系有限公司 | Dual clutch transmission with planetary gearset |
| DE102008030516A1 (en) * | 2007-12-17 | 2009-06-18 | Hyundai Motor Company | Automatic transmission of a vehicle |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104685261A (en) * | 2012-07-24 | 2015-06-03 | Dti集团有限公司 | Transmission system |
| CN104685261B (en) * | 2012-07-24 | 2018-03-23 | Dti集团有限公司 | Transmission system |
| US10955035B2 (en) | 2012-07-24 | 2021-03-23 | Punch Powertrain N.V. | Transmission system |
| CN107117023A (en) * | 2016-02-25 | 2017-09-01 | 通用汽车环球科技运作有限责任公司 | Automotive transmission |
| CN110273987A (en) * | 2018-03-15 | 2019-09-24 | 丰田自动车株式会社 | Automatic transmission |
| FR3083581A1 (en) * | 2018-07-06 | 2020-01-10 | Suzuki Motor Corporation | VEHICLE TRANSMISSION |
| EP3739238A1 (en) * | 2019-05-14 | 2020-11-18 | Deere & Company | Power transmission for agricultural machines |
| US11391353B2 (en) | 2019-05-14 | 2022-07-19 | Deere & Company | Power shift transmission for agricultural machines |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103459894B (en) | 2016-09-14 |
| CN106195190A (en) | 2016-12-07 |
| CN106195190B (en) | 2019-06-18 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20200208722A1 (en) | Transmission system, as well as a method for changing a transmission ratio | |
| US8992362B2 (en) | Hybrid power train for a motor vehicle | |
| KR101543164B1 (en) | Powertrain for hybrid vehicle | |
| US8408084B2 (en) | Dual clutch transmission device | |
| CN103851183B (en) | Automobile-used one-way clutch power coupling transmission control device and method, automobile | |
| JP5178845B2 (en) | Power transmission device for hybrid vehicle | |
| KR100893438B1 (en) | Power transmission system of hybrid vehicle | |
| WO2010070707A1 (en) | Power transmission device for hybrid vehicle | |
| US20100311540A1 (en) | Method for the operation of a hybrid drive system and hybrid drive system comprising two sub-transmissions | |
| KR101551123B1 (en) | Powertrain for hybrid vehicle | |
| JP2016070481A (en) | Vehicular transmission | |
| CN103459894A (en) | Transmission system, as well as method for changing first gear ratio | |
| CN105358873A (en) | Dual clutch transmission for a motor vehicle | |
| JP2010517872A (en) | Method for operating a vehicle drive train | |
| CN103492751A (en) | Transmission system | |
| KR20150012150A (en) | Power transmission apparatus for vehicle | |
| US10533637B2 (en) | Multiple hydraulic multi-plate clutch transmission for vehicle | |
| KR20200052380A (en) | Multi-mode power-split hybrid transmission with two planetary gear mechanisms | |
| US10047830B2 (en) | Transmission for vehicle | |
| CN104685261A (en) | Transmission system | |
| KR20210109064A (en) | Hybrid powertrain for vehicle | |
| KR20190004862A (en) | Transmission for vehicle | |
| CN203902248U (en) | Longitudinal hybrid dual-clutch transmission actuator | |
| CN203162010U (en) | Transmission device for dual-clutch transmission | |
| CN203822968U (en) | Hybrid longitudinal dual-clutch transmission drive device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20210120 Address after: St. treden, Belgium Patentee after: PUNCH POWERTRAIN N.V. Address before: Einhofen, the Netherlands Patentee before: DTI Group B.V. |
|
| TR01 | Transfer of patent right |