• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A method of operating a dual-clutch transmission (10) having an input shaft (11), an output shaft (12), a main shaft (13), a first clutch (18), a second clutch (19), a first countershaft (16) and a second one Countershaft (17), with a range group transmission (21). A load-switchable range group change can be made possible with the following steps: • separating the first countershaft (16) from the input shaft (11); • synchronizing a first gear stage (ZA1) with the output shaft (12); • synchronizing the first countershaft (16) with a first gear stage (ZA1); • changing the drive of the output shaft (12) from the second to the first countershaft (17, 16); Torque-disconnecting a planetary gear (24) of the range group transmission (21); synchronizing the second countershaft (17) with the input shaft (11); Decelerating the main shaft (13) by synchronizing it with the second countershaft (17) in a gear stage of the second countershaft (17) below the highest gear (6); Separating the second countershaft (17) from the input shaft (11) and the main shaft (13); • switching the range group transmission (21) to a fast • range group (HIGH); Decreasing the speed of the second countershaft (17) by synchronizing with the main shaft (13) in the lowest gear (2) of the second countershaft (17); • changing the drive of the output shaft (12) from the first to the second countershaft (16, 17);
    公开号:AT512917A4
    申请号:T505832012
    申请日:2012-12-12
    公开日:2013-12-15
    发明作者:Ernst Hundsberger
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    iPririted: 1342-2 * 312 (E014 [105012/50583 1 56527
    The invention relates to a method for operating a dual-clutch transmission for a motor vehicle, having an input shaft, an output shaft and a main shaft, wherein the input shaft via a switchable first clutch, the first countershaft and / or via a switchable second clutch drives the second countershaft, and the first and the second countershaft each drives via at least one switchable gear stage, the main shaft, and with a planetary gear having range group transmission for switching between a slow and a fast range group. Furthermore, the invention relates to a dual-clutch transmission for a motor vehicle, having an input shaft, an output shaft and a main shaft, wherein the input shaft via a first gear stage and a coaxially arranged to a first countershaft switchable first clutch with the first countershaft and a coaxial with a second countershaft arranged switchable second clutch is drivingly connected to a second countershaft, wherein the first countershaft and the second countershaft is in each case drive-connected via at least one switchable via a switching device gear stage with the main shaft, and wherein a range group transmission is arranged between the main shaft and an output shaft of the dual-clutch transmission.
    The AT 510 966 Bl discloses a dual-clutch transmission for a motor vehicle, having an input shaft and a main shaft, wherein the input shaft via a switchable first clutch with a first Vorgeiegewelle and via a switchable second clutch with a second countershaft is connectable. The first countershaft and the second countershaft can each be drive-connected to the main shaft via at least one gearwheel pair that can be shifted via a switching device. Between the main shaft and an output shaft of the transmission, a range group transmission is arranged. As a synchronization device, a hydraulic unit is provided, which hydraulic unit has a drive-connected to the first countershaft first hydraulic machine and a drive connected to the second countershaft second hydraulic machine. m rnrnmk 13-12 * 2012 IE014 10 2012/60583 2
    The gears of such dual clutch transmissions are switchable within a range group without interruption of traction. Switching the area group, however, can only be accomplished by separating the traction.
    From the publications US 6,427,549 Bl and EP 1 270 301 A2 dual-clutch transmission with an input shaft and an output shaft, and with two countershafts are known, wherein the rotational speeds of the countershafts via synchronizers with the speed of the output shaft are tuned.
    In this case, the rotational speed of the drive shaft not connected to the input shaft countershaft is driven or decelerated by an electric motor until synchronization with a free-running on the countershaft gear, which is connected via a gear stage to the output shaft. As soon as there is synchronization, the gearwheel is drive-connected to the countershaft via a dog clutch.
    The DE 10 2007 018 967 Al also describes an automated Gruppengebtriebe for a vehicle with a main gear and at least one upstream and / or downstream After area group and with at least one countershaft, the countershaft is at least one hydraulic arrangement in operative connection to a power take-off provided. The hydraulic arrangement has at least one drive unit for controlling and / or regulating each countershaft.
    EP 2 149 725 B1 discloses a transmission unit with a dual-clutch transmission and a group transmission, one of the dual-clutch transmission input shafts being designed as a hollow shaft and the other as a solid shaft. To change the switch group under load, the highest forward gear of the slow shift group and the lowest forward gear of the fast shift group must be switched simultaneously.
    In this case, the uppermost forward gear of the lower shift group and the lowest forward gear of the upper shift group is operated with a same transmission ratio. As a result, the transmission effectively has a higher number of gears than the number of gears. The transmission thus has - compared to the effective number of translations - a high structural and spatial complexity. 3 3 [ia2012 / 5Ö583 13-12-2012 £ 014
    The object of the invention is to allow a power shiftable range group change with the least possible structural and spatial complexity with a dual-clutch transmission of the type mentioned.
    According to the invention this is achieved in that the following steps are performed for a zugkraftunterbrechungsfreien upshift from the slow range group in the fast range group - starting from a highest gear position of the gear stages of the second countershaft with closed first and second clutch and a neutral position in the shift sleeve of the other switching device :
    In the following, in addition to the speed equalization between two shafts and a speed adjustment between two interconnected by a gear ratio shafts called synchronization. • Opening the first clutch: The first countershaft is disconnected from the input shaft. The drive of the output shaft takes place only through the second countershaft. • Connecting the shift sleeve of the other switching device to the output shaft: The second idler gear of the first gear stage is driven at the speed of the output shaft - the first gear stage is thus synchronized with the output shaft. • Insertion of the first gear stage of the first countershaft: The speed of the first countershaft is - adapted according to the ratio of the first gear stage - to the speed of the first idler gear of the first gear stage, for example, reduced. The first countershaft is thus synchronized with the first gear stage. • Closing of the first clutch with simultaneous opening of the second clutch: The drive of the output shaft now takes place through the first countershaft. The speed of the input shaft is adjusted accordingly.
    [Printed: 13-12-2012 IE014 [102012/50583 4 • Switching the range group gear to a neutral position: The planetary gear is thus torque-free. The ring gear of the planetary gear is accelerated. • Closing the second clutch: The second countershaft is decelerated as a result - corresponding to the reduced speed of the input shaft - the second countershaft synchronized with the input shaft. • Setting a lower, preferably the second highest, gear position of the second countershaft: The speed of the main shaft is reduced according to the selected lower gear position by synchronizing with the second Vongelegewelle. The ring gear of the planetary gear is further accelerated. • opening the second clutch; • Deactivation of the lower gear position of the second countershaft: The second countershaft is thus switched torque-free. • Switching the range group transmission to the fast range group:
    The planetary gear is blocked, the input speed of the planetary gear corresponds to the output speed. The ring gear of the planetary gear and the main shaft synchronize with the speed of the output shaft. Preferably, a closing of the second clutch can be carried out in order to relieve the clutch (normaly closed cupling) or to minimize the losses. • Applying the lowest gear position of the second countershaft: The speed of the second countershaft is reduced according to the ratio of the second gear stage by synchronization with the main shaft. • Closing the second clutch while simultaneously opening the first clutch: The speed of the input shaft is correspondingly reduced. The drive of the output shaft is now through the second countershaft. 5 • The first gear stage can then be deactivated again and the first clutch closed. Thus, the first countershaft can be braked according to the speed of the input shaft.
    Furthermore, for a traction interruption-free downshift from the fast range group into the slow range group-starting from a lowest gear position of the gear stages of the second countershaft with the first and second clutches closed and a shift sleeve in rotationally fixed connection with the output shaft of the further shift device -folgenden steps can be performed : • Opening the first clutch: The first countershaft is disconnected from the input shaft. The drive of the output shaft is effected only by the second countershaft, wherein due to the switching position of the range group transmission, the planetary gear of
    Area group transmission is blocked and the speed of the output shaft corresponds to the speed of Hauptwelie. • Insertion of the first gear stage of the first countershaft: The speed of the first countershaft is - adapted according to the ratio of the first gear stage - to the speed of the first idler gear of the first gear stage, for example, increased. There is a synchronization of the first countershaft with the output shaft. • Closing of the first clutch with simultaneous opening of the second clutch: The drive of the output shaft now takes place through the first countershaft. The speed of the input shaft is increased accordingly. • deactivating the lowest gear position of the second countershaft; • Closing the second clutch: The second countershaft is thus accelerated - corresponding to the increased speed of the input shaft - and synchronized with the input shaft. • Switching the range group gear to a neutral position: The planetary gear is thus switched torque-free. The ring gear of the planetary gear is delayed.
    [Pfinted: 13-12-2012 iE014 [10 2012/50583 6 • Setting the second countershaft gear position higher, preferably the second highest: The main shaft speed is increased according to the selected higher gear position and synchronized with the second countershaft. The ring gear of the planetary gear is further delayed. Preferably, the higher gear position of the second countershaft can be deactivated and immediately afterwards the highest gear position of the second countershaft can be engaged. The speed of the main shaft is thereby further increased according to the selected highest gear position of the second countershaft. The ring gear of the planetary gear is further delayed. • opening the second clutch; • Switching the range group transmission to the slow range group:
    The ring gear of the planetary gear is held. • Closing the second clutch while simultaneously opening the first clutch: The output shaft is now driven by the second countershaft. The speed of the input shaft is increased accordingly. • Then the first gear stage of the first countershaft can be designed and the first clutch can be closed. The speed of the first countershaft is thus increased according to the speed of the input shaft.
    The method can be carried out particularly advantageously with a dual-clutch transmission of the type mentioned, in which at least one countershaft, preferably the first countershaft, via a switchable first or second gear stage and another switching device with the main shaft or with the output shaft is drive-connected, preferably the further switching device is arranged coaxially with the main shaft and / or output shaft.
    The first and / or second gear stage may have a coaxial with the first or second countershaft shaft arranged first idler gear and a coaxially arranged to the main shaft second idler gear. In this case, preferably, the second idler gear rotatably connected to a shift sleeve of the other switching device, wherein the 7 7 [10 2012/50583 13-12-2012 1E014
    Shift sleeve is rotatably connected in a first switching position with the main shaft and in a second switching position with the output shaft.
    The first and the second clutch is advantageously designed as a wet-running Lammelienkupplung, whereby high torques can be transmitted with a small space and low weight.
    Preferably, the first clutch is coaxial with the first countershaft and the second clutch coaxial with the second countershaft. The two clutches can be designed identical, in order to minimize the manufacturing costs.
    In order to keep the production costs as low as possible, it is advantageous if at least one gear group of the first countershaft and the second countershaft is of identical construction. By using as many common parts as possible, the costs can be kept very low.
    In a particularly preferred embodiment of the invention, it is provided that the range group transmission has a planetary gear, which can be designed as a simple Stirnradplanetengetriebe. In this way, particularly high gear ratios and required for a practicable gear ratio number of gears can be realized with a small number of components. The range group transmission can have two range groups - one slow and one fast range group. The further switching device can be drivingly connected to the planet carrier of the planetary gear.
    It is particularly advantageous if the input shaft is connected via a first gear stage to the first countershaft and via a second gear stage to the second countershaft, wherein preferably the first and the second gear stage have different gear ratios. Due to the different gear ratios, the Vorgelegewelten are driven at different speeds.
    In a particularly advantageous further embodiment, the ratio jump between the first and second gear stage corresponds to the desired ratio jump between the individual gear ratios, whereby a structurally identical design of the gear groups on the two countershafts 13-12-2012 is made possible.
    In contrast to EP 2 149 725 B1, a simultaneous switching of the switching groups is not required in the method according to the invention. The smallest gear of the fast range group is not engaged during upshifting, but counts as the highest gear of the slow range group - the fast range group is preselected and only in second gear the fast range group active.
    In order to enable a direct drive through, it can be provided in a further embodiment of the invention that the input shaft with the main shaft directly via a further switching device is connectable.
    The dual-clutch transmission can be modular and consists of a coupling part, a main gear! and the range group transmission part, preferably the further switching device is arranged in the main transmission part. Thus, it can be applied to various applications and vehicles, such as buses, trucks, road vehicles and off-road vehicles.
    The invention will be explained in more detail below with reference to FIG.
    2 to 17 different steps during the method according to the invention in an upshifting operation and FIGS. 13 to 29 different steps during the method according to the invention in a downshifting operation.
    The figures schematically show an inventive dual-clutch transmission 10 with twelve forward gears and two reverse gears.
    The different gear ratios are indicated in the figure by the reference numerals 1, 2, 3, 4, 5, 6 for the forward gears and RI, R2 for the reverse gears.
    The dual-clutch transmission 10 shown in FIGS. Has an input shaft 11 connected to an internal combustion engine (not shown) and a main shaft 13 connected to an output shaft 12. The input shaft 11 is above single-stage first and second gear stages 14, 15, which different
    Sf ^ hted: 13-12-2012 EQ14 1102012/50583 9 gear ratios, each with a first countershaft 16 and a second countershaft 17 in conjunction. Between the first gear stage 14 and the first countershaft 16, a first shiftable clutch 18, between the second gear stage 15 and the second countershaft 17, a switchable second clutch 19 is arranged. The clutches 18 and 19 are designed as wet-running multi-plate clutches. The first and second clutches 18, 19 may each be spring loaded in the closed position, whereby no active force application is required to establish the drive connection between the input shaft 11 and the respective countershaft 16, 17. For safety reasons but can also be done at least in one of the two clutches 18, 19 closing with hydraulic pressure instead of a closing spring.
    In the drive train of the Doppelkupptungsgetriebes 10 is further connected to the main shaft 13 Bereichgmppengetriebe 21 is provided, with which switching between high gear ratios - fast range group HIGH - and low gear ratios - slow range group LOW - is possible. In a compact design, the range group transmission 21 may be formed as a planetary gear 24, wherein an element of the planetary gear 24 - for example, the ring gear 24h - held on a switching device 201 or with a second element of the planetary gear 24 - for example, the planet carrier 24p - can be connected. The sun gear 24s of the planetary gear may be connected to the main shaft 13.
    Reference numeral 25 denotes a parking lock connected to the main shaft 13 or output shaft 12.
    The countershafts 16, 17 are each connected to the main shaft 13 via gear stages ZA1, ZA2, ZA3, ZA4, ZA5, ZA6, ZR1, ZR2.
    The gears of the gear stages ZAl, ZA2, ZA3, ZA4, ZA5, ZA6, ZR1, ZR2, the gear stages 14, 15 and the range group transmission 21 are zl, z2, z3, z4, z5, z6, z7, z8, z9, z10 , zll, zl2, zl3, zl4, zl5, zl6 denoted, wherein identical gears are provided with the same reference numeral. (102012/50583 13412-2Ö12 IE014 10
    Each gear stage ZA3, ZA4, ZA5, ZA6, ZR1, ZR2 has in each case at least one idler gear z5, z6, z7, zll circulating freely on a shaft - for example a countershaft 16, 17 - and one with another shaft - for example the main shaft 13-fixed fixed fixed wheel z9, zlO, zl3 on. The gear stages ZR1, ZR2 the reverse gears RI, R2 additionally have a reverse gear zl2. In order to save manufacturing costs, two each on the countershafts 16,17 opposite gears may be formed as equal parts. The idler gears can be mounted on the countershafts 16, 17 freewheeling and stand with rotatably connected to the main shaft 13 fixed gears in the toothed ratchet. In this case, two oppositely arranged in each case a gear level on different countershafts 16, 17 idler gears each mesh with a common fixed gear of the main shaft 13. To each drive the idler idler gears z5, z6, z7, zll with the respective countershaft 16, 17 driveably, switching elements 20 are provided, which by synchronizing units or - in particular in the case of external electric or hydraulic synchronizers - formed by simple, non-synchronized jaw clutches can be. The switching elements 20 can be hydraulically actuated by not shown actuators, for example.
    In contrast to the gear stages ZA3, ZA4, ZA5, ZA6, ZR1, ZR2 are coaxial with the respective countershaft 16, 17 arranged first idler gears z5 of the first and second gear stages ZA1, ZA2 not with a fixed gear, but with a rotatable about the main shaft 13th mounted second idler gear z8 meshing. The second idler gear z8 can be connected via a further switching device 202 either to the main shaft 13 or to the output shaft 12.
    The switchable via the switching means 202 additional gear stage ZAl, ZA2 acts in a switching position on the separated from the skin shaft 13 idler z8 on the Hauptwelie 13 on the sun gear 24s of the planetary gear 24 and in the other switching position on the planet carrier 24p of the planetary gear 24 of the range gearbox 21 directly on the output shaft 12 a. In the embodiment, the idler gear z8 is firmly connected to the shift sleeve 202a, which allows a compact and partially-saving arrangement. fl02Ö12 / 50 $ 83 13 ^ 2 ^ 012 IE014 11
    In the drive case! one of the two countershafts 16, 17 via the respective coupling 18, 19 drivingly connected to the input shaft 11, while the respective other countershaft 17, 16 is separated from the drive shaft 11.
    The drive-connected countershaft, for example, the second countershaft 17 is drivingly connected to the main shaft 13 via an engaged gear, such as gear 6. In the drive case, the main shaft 13 is drivingly connected to the second countershaft 17 via the switched to HIGH or LOW switching device 201 of the range group transmission 21 to the output shaft 12 and a switched gear, for example, gear stage 6. Thus, a power flow up to the output shaft 12 takes place via the second clutch 19.
    In the illustrated embodiment, the input shaft 11 is further connected to the main shaft 13 directly via a further switching device 40. Thereby, a direct drive between the input shaft 11 and the main shaft 13 are made possible.
    The dual-clutch transmission 10 may have a modular design and consist of a clutch hub 50, a main gear part 60 and the range group transmission part 70, and thus for different applications and vehicles, such as buses, trucks, road vehicles and off-road vehicles application.
    FIGS. 2 to 29 show individual method steps for upshifting and downshifting between the range groups LOW and HIGH on the basis of a concrete example. The active drive paths over the first countershaft 16 and dash-dotted lines indicate the active drive paths over the second countershaft 17 by dashed lines. Furthermore, the rotational speeds of the input shaft 1, the first and second countershafts 16, 17, the main shaft 13, the output shaft 12 and the ring gear 24 h of the planetary gear 24 are indicated for the exemplary embodiment for each method step.
    Hochschaltvoroana:
    When the highest gear 6 in the main gear 60 of the slower range group LOW is reached, a further upshift into a low gear of the fast 12 ^ <12012/50583 occurs
    Range group HIGH - starting from a highest gear position 6 all gear stages ZA2, ZA4, ZA6 of the second countershaft 17 with closed first and second clutch 18, 19 and a neutral position located in the shift sleeve 202a of the other switching device 202 (starting position see Fig. 2) - by the following steps: • Opening the first clutch 18: The first countershaft 16 is separated from the input shaft 11. The drive of the output shaft 12 takes place only through the second countershaft 17 (FIG. 3). • Connecting the shift sleeve 202a of the other switching device 202 with the output shaft 12 and with the planet carrier 24p: The second idler gear Z8 of the first gear stage ZAl is driven at the same speed as the output shaft 13 (FIG. 4). • Activation of the first gear stage ZAl of the first countershaft 16: The speed of the first countershaft 16 is - according to the ratio of the first gear stage ZAl - adapted to the speed of the first idler gear z8 of the first gear stage, here reduced (Fig. 5). • Closing of the first clutch 18 with simultaneous opening of the second clutch 19: The drive of the output shaft 12 is now through the first countershaft 16. The speed of the input shaft 11 is adjusted accordingly (Fig. 6). • Switching the switching device 201 of the range group transmission 21 in a neutral position: The planetary gear 24 is thus switched torque-free. The ring gear 24h of the planetary gear 24 is accelerated (Fig. 7). • Closing of the second clutch 19: The second countershaft 17 is thereby - in accordance with the reduced speed of the input shaft 11 - braked, the second countershaft 17 with the input shaft 11 synchronized (Fig. 8). 1
    Insertion of a lower, preferably the second highest, gear position 4 of the second countershaft 17: The rotational speed of the main shaft 13 is 13 corresponding to the selected lower gear position 4 reduced by synchronizing with the second countershaft 17. The ring gear 24h of the planetary gear 24 is further accelerated (FIG. 9). Opening the second clutch 17 (Figure 10); Deactivating the lower gear position 4 of the second countershaft 17: The second countershaft 17 is thus switched torque-free. (Figure 11). • Switching the range group transmission to the fast range group: The planetary gear is blocked, the input speed of the planetary gearbox corresponds to the output speed. The ring gear of the planetary gear and the main shaft synchronize with the rotational speed of the output shaft (FIG. 11). By closing the second clutch 19 losses can be minimized (FIGS. 12, 13). • Insertion of the lowest gear position 2 of the second countershaft 17: The speed of the second countershaft 17 is reduced in accordance with the ratio of the second gear stage ZA2 by synchronization with the main shaft 13 (FIG. 14). • Closing the second clutch 17 with simultaneous opening of the first clutch 18: The speed of the input shaft 11 is reduced accordingly. The drive of the output shaft 12 now takes place through the second countershaft 17 (FIG. 15). • Thereafter, the first gear stage ZA1 deactivated again and the first clutch 18 are closed. Thus, the first countershaft 16 can be decelerated according to the rotational speed of the input shaft 11 and prepared for further switching operations (Fig. 16, 17).
    Runterschaltvoroana:
    If the lowest gear 1 is reached in the skin gear 60 of the faster range group HIGH, then a further downshift takes place in a high gear of the slow
    Nnt0d: 1M2 ^ 012 [Ε0Ϊ4 [10: 001 ^ 00083 14
    Range group LOW - starting from a lowest gear position of all gear stages ZA2, ZA4, ZA6 of the second countershaft 17 with closed first and second clutch 18, 19 and one located in a rotationally fixed connection with the output shaft 12 shift sleeve 202a of the further switching device 202 - by the following steps: • Opening the first clutch 18: The first countershaft 16 is separated from the input shaft 11. The drive of the output shaft 12 takes place only through the second countershaft 17, wherein due to the shift position of the range group transmission 21, the planetary gear 24 of the range group transmission 21 is blocked and the speed of the output shaft 12 of the rotational speed of the main shaft 13 corresponds (Fig. 18). • Insertion of the first gear stage ZA1 of the first countershaft 16: The speed of the first countershaft 16 is - in accordance with the ratio of the first gear stage ZA1 - adapted to the speed of the second idler gear z8 of the first gear stage ZAl, for example increased. There is a synchronization of the first countershaft 16 with the output shaft 12 (FIG. 19). • Closing of the first clutch 18 with simultaneous opening of the second clutch 19: The drive of the output shaft 12 is now through the first countershaft 16. The speed of the input shaft 11 is increased accordingly (Fig. 20). Deactivating the lowest gear position of the second countershaft 17 (Figure 21); • Closing of the second clutch 19: The second countershaft 17 is thereby -accelerated in accordance with the increased speed of the input shaft 11 and synchronized with the input shaft 11 (FIG. 22). • Switching the switching device 201 of the range group transmission 21 in a neutral position: The planetary gear 24 is thus switched torque-free.
    The ring gear 24h of the planetary gear 24 is decelerated (FIG. 23). Inserting a higher, preferably the second highest, gear position 4 of the second countershaft 17: The speed of the main shaft 13 is increased according to the selected higher gear position 4 and synchronized with the second countershaft 17. The ring gear 24h of the planetary gear 24 is further decelerated (FIG. 23). Thereafter, the higher gear position 4 of the second countershaft 17 is deactivated and immediately thereafter the highest gear position 6 of the second countershaft 17 are inserted. The speed of the main shaft 13 is thereby further increased according to the selected highest gear position 6 of the second countershaft 17. The ring gear 24h of the planetary gear 24 is further decelerated (FIG. 24). Opening the second clutch 19 (Figure 25); Switching the range group transmission 21 to the low speed range group LOW: The ring gear 24h of the planetary gear 24 is retained (FIG. 26). • Closing of the second clutch 19 with simultaneous opening of the first clutch 18: The drive of the output shaft 12 is now carried by second countershaft 17. The speed of the input shaft 11 is increased accordingly (Fig. 27). Thereafter, the first gear stage ZAl of the first countershaft 16 can be deactivated (FIG. 27) and the first clutch 18 can be closed (FIG. 28). The speed of the first countershaft 16 is thus increased according to the speed of the input shaft 11 and prepared for further switching operations.
    If the range change has taken place, the next lower gear 6 can be engaged and by means of a clutch change 18 to 19 a normal load shift can be performed again.
    Thus, a switching of the range group transmission 21 can be performed without interruption of traction, wherein all gears can be formed with different transmission ratios.
    [rinted: 13-12-2012 IE014 110 2012/50583 16
    The modular design also allows application and upgrading of existing gearboxes. Thus, a use in the most common dual-clutch transmissions with range group is possible.
    权利要求:
    Claims (15)
    [1]
    A method of operating a motor vehicle dual-clutch transmission (10) comprising an input shaft (11), an output shaft (12) and a main shaft (13), wherein the input shaft (11) via a switchable first clutch (18) the first countershaft shaft (16) and / or via a switchable second clutch (19), the second countershaft (17) drives, and the first and the second countershaft (16, 17 ) drives in each case at least one switchable gear stage (ZAl, ZA2, ZA3, ZA4, ZA5, ZA6), the main shaft (13), and with a at least one planetary gear (24) having range group transmission (21) for switching between a slow and a fast range group (LOW, HIGH), characterized in that for a zugkraftunterbrechungsfreien upshift from the slow range group (LOW) in the fast range group (HIGH) - starting from a highest gear position (6) all tooth Radstufen (ZA2, ZA4, ZA6) of the second countershaft (17) with closed first and second clutch (18, 19) and in a neutral position located shift sleeve (202a) of the further switching device (202) - the following steps are performed: al) separating the first countershaft (16) from the input shaft (11); bl) synchronizing a first gear stage (ZAl) with the output shaft (12); cl) synchronizing the first countershaft (16) with the first gear stage (ZAl); dl) changing the drive of the output shaft (12) from the second to the first countershaft (17, 16); el) torque disconnection of the planetary gear (24) of the range group transmission (21); 18) Connecting the second countershaft (17) to the input shaft (11); gl) decelerating the main shaft (13) by synchronizing it with the second countershaft (17) in a gear stage of the second countershaft (17) below the highest gear (6); hl) separating the second countershaft (17) from the input shaft (11) and the main shaft (13); il) switching the range group transmission (21) to the fast range group (HIGH), preferably by blocking the planetary gear (24); jl) reducing the speed of the second countershaft (17) by synchronizing with the main armature (13) in the lowest speed step (2) of the second countershaft (17); kl) changing the drive of the output shaft (12) from the first to the second countershaft (16, 17);
    [2]
    2. The method according to claim 1, characterized in that the following steps are carried out: a2) opening of the first clutch (18); b2) connecting the shift sleeve of the further switching device (202) with the output shaft (12); c2) inserting the first gear stage (ZA1) of the first countershaft (16); d2) closing the first clutch (18) while simultaneously opening the second clutch (19); e2) switching the range group transmission (21) to a neutral position; 19 [102012/50683 f2) closing the second clutch (19) g2) inserting a lower, preferably the second highest, gear position (4) of the second countershaft (17); h2) opening the second clutch (19); i2) deactivating the lower gear position (4) of the second countershaft (17); j2) switching the range group transmission to the fast range group (HIGH); k2) inserting the lowest gear position (2) of the second countershaft (17); 12) closing the second clutch (19) with simultaneous opening of the first clutch (18).
    [3]
    3. The method according to claim 2, characterized in that after step j2) the following steps are performed: j21) closing the second clutch (19); j22) opening the second clutch (19).
    [4]
    4. The method according to claim 2 or 3, characterized in that after step 12) the following steps are performed: 121) deactivating the first gear stage (ZA1); 122) closing the first clutch (18).
    [5]
    5. A method for operating a dual-clutch transmission (10) for a motor vehicle, having an input shaft (11), an output shaft (12) and a main shaft (13), wherein the input shaft (11) via a switchable first clutch (18), the first countershaft (16) and / or via a switchable second clutch (19) drives the second countershaft (17), and the first and the second countershaft (16, 17) in each case via at least one switchable gear stage (ZA1, ZA2, ZA3, ZA4, ZA5, ZA6) drives the main shaft (13) and with a at least one planetary gear (24) having range group transmission (21) for switching between a slow and a fast range group (LOW, HIGH) , characterized in that for a zugkraftunterbrechungsfreien downshift from the fast range group (HIGH) in the slow range group (LOW) -ausgehend of a lowest gear position (2) of the gear stages (ZA2, ZA4, ZA6) d he second countershaft (17) with closed first and second clutch (18, 19) and one in a rotationally fixed connection with the output shaft (12) located shift sleeve (202a) of the further switching device (202) - the following steps are performed: a3) separating the first countershaft (16) from the input shaft (ii); b3) synchronizing the first countershaft (16) with the first gear stage (ZA1); c3) changing the drive of the output shaft (12) from the second to the first countershaft (17,16); d3) accelerating the second countershaft (17) by synchronizing with the input shaft (11); e3) Torque disconnection of the planetary gear (24) of the range group transmission (21); f3) accelerating the main shaft (13) by synchronizing with the second countershaft (17) in a gear stage of the second countershaft (17) above the lowest gear (2); g3) separating the second countershaft (17) from the input shaft (ii); 21 21 Η 02Ö12 / 50583 iPrinted: 13-12 * 2012 h3) Switching the range group transmission (21) to the slow range group (LOW), preferably by holding the ring gear (24h) of the planetary gear (24); 13) changing the drive of the output shaft (12) from the first to the second countershaft (16, 17);
    [6]
    6. The method according to claim 5, characterized in that the following steps are performed: a4) opening of the first clutch (18); b4) inserting the first gear stage (ZAl) of the first countershaft (16); c4) closing the first clutch (18) while simultaneously opening the second clutch (19); d4) deactivating the lowest gear position (2) of the second countershaft (17); e4) closing the second clutch (19); f4) switching the range group transmission (21) to a neutral position; g4) inserting a higher, preferably the second highest, gear position (4) of the second countershaft (17); h4) opening the second clutch (19); 14) switching the range group transmission (21) to the slow range group (LOW); j4) closing the second clutch (19) while simultaneously opening the first clutch (18). 22 (10 2012/50583
    [7]
    7. The method according to claim 6, characterized in that after step g4) the following steps are performed: g41) deactivating the higher gear position (4) of the second countershaft (17); g42) inserting the highest gear position (6) of the second countershaft (17).
    [8]
    8. The method according to claim 6 or 7, characterized in that after step j4) the following steps are performed: j41) deactivating the first gear stage (ZA1) of the first countershaft (16); j42) closing the first clutch (18).
    [9]
    9. A dual-clutch transmission (10) for a motor vehicle, having an input shaft (11), an output shaft (12) and a main shaft (13), wherein the input shaft (11) via a first gear stage (14) and a coaxial with a first countershaft ( 16) arranged switchable first clutch (18) with the first countershaft (16) and via a coaxial with a second countershaft (17) arranged switchable second clutch (19) with a second countershaft (17) is drive-connected, wherein the first countershaft (16 ) and the second countershaft (17) in each case via at least one via a switching device (20) switchable gear stage (ZA1, ZA2, ZA3, ZA4, ZA5, ZA6) to the main shaft (13) is drive-connected, and wherein between the main shaft (13) and an output shaft (12) of the dual-clutch transmission, a range group transmission (21) is arranged, characterized in that at least one countershaft (16, 17) via a switchable first or second gear tufe (ZA1, ZA2) and a further switching device (202) optionally with the main shaft (13) or with the output shaft (12) is drive-connected, wherein preferably the further switching means (202) coaxial with the main shaft (13) and / or output shaft (12 ) is arranged. 23
    [10]
    10. dual-clutch transmission (10) according to claim 9, characterized in that the first and / or second gear stage (ZAl, ZA2) coaxial with the first or second countershaft (16, 17) arranged first idler gear (z5) and a coaxial with the main shaft ( 13) arranged second idler gear (Z8).
    [11]
    11. dual clutch transmission (10) according to claim 9 or 10, characterized in that the second idler gear (z8) rotatably connected to a shift sleeve (202a) of the further switching device (202), wherein the shift sleeve (202a) in a first switching position with the Main shaft (13) and in a second switching position with the output shaft (12) is rotatably connected.
    [12]
    12. Double clutch transmission (10) according to any one of claims 9 to 11, characterized in that the range group transmission (21) has a preferably designed as Stirnradplanetengetriebe planetary gear (24).
    [13]
    13. dual-clutch transmission (10) according to one of claims 9 to 12, characterized in that the first and the second gear stage (14,15) have different gear ratios, preferably the ratio jump between the first and second gear stage (14, 15) the desired ratio jump corresponds between the individual gears.
    [14]
    14. Double clutch transmission (10) according to any one of claims 9 to 13, characterized in that the input shaft (11) with the main shaft (13) directly via an additional switching device (40) is connectable.
    [15]
    15 dual-clutch transmission (10) according to one of claims 9 to 14, characterized in that the dual-clutch transmission (10) has a coupling part (50), a main transmission part (60) and a range group transmission part (70), wherein preferably the further switching device (202) in the main transmission part (60) is arranged. 2012 12 12 feet
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    同族专利:
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    EP2743548A1|2014-06-18|
    AT512917B1|2013-12-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE102005033027A1|2005-07-15|2007-01-25|Daimlerchrysler Ag|Automated powershift transmission|
    EP2249062A1|2009-05-08|2010-11-10|ZF Friedrichshafen AG|Method for operating a drive train|CN113090719A|2021-04-09|2021-07-09|江苏国茂减速机股份有限公司|Novel double-speed reducer for bevel gear|DE19939334A1|1999-08-19|2001-03-08|Daimler Chrysler Ag|Method for shifting double-clutch gearbox without tractive force interruption has two lay shafts connected to output shaft through shiftable gear stages and associated with friction clutch for connection to drive motor|
    US6427549B1|2001-01-10|2002-08-06|New Venture Gear, Inc.|Dual countershaft twin clutch automated transmission|
    EP1270301A3|2001-06-19|2007-02-21|Hitachi, Ltd.|Power transmission apparatus for automobile|
    DE102007018967A1|2007-04-21|2008-10-23|Zf Friedrichshafen Ag|Automated auxiliary transmission for commercial motor vehicle, has countershafts staying in connection with hydraulic arrangement to provide auxiliary output, and drive units controlling and regulating each countershaft|
    US7896770B2|2007-08-01|2011-03-01|GM Global Technology Operations LLC|Multi-speed transmission|
    DE102008036165A1|2008-08-02|2010-02-04|Daimler Ag|gear unit|
    AT510966B1|2011-06-09|2012-08-15|Avl List Gmbh|GEARBOX, ESPECIALLY DOUBLE CLUTCH GEARBOX|SE539248C2|2015-10-06|2017-05-30|Scania Cv Ab|A method for controlling a gearbox, a gearbox and a vehicle provided with such a gearbox|
    法律状态:
    2018-08-15| MM01| Lapse because of not paying annual fees|Effective date: 20171212 |
    优先权:
    申请号 | 申请日 | 专利标题
    AT505832012A|AT512917B1|2012-12-12|2012-12-12|Method for operating a dual-clutch transmission|AT505832012A| AT512917B1|2012-12-12|2012-12-12|Method for operating a dual-clutch transmission|
    EP13195275.6A| EP2743548A1|2012-12-12|2013-12-02|Method for operating a dual clutch transmission|
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