• 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:
    The invention relates to a dual-clutch transmission (10), in particular for a motor vehicle, having an input shaft (11) and a main shaft (13), the input shaft (11) being connected to a first countershaft (16) via a switchable first clutch (18) and via a second shiftable one Coupling (19) with a second countershaft (17) is connectable, wherein the first countershaft (16) and the second countershaft (17) via at least one via a switching device (20) switchable gear pair (Z) is drive-connected to the main shaft (13), with at least one synchronizer (80) formed by an electric machine (81, 81, 281) for adjusting the speed of the countershafts (16, 17) to the main shaft (13). In order to provide a pressure source for hydraulic devices with as little space requirement and few parts as possible, it is provided that the electric machine (81, 181, 281) is drive-connected to a hydraulic pump (86, 186, 286), preferably a drive shaft (81a, 181a, 281a) the electric machine (81,181, 281) and a drive shaft of the hydraulic pump (86, 186, 286) are coaxially arranged.
    公开号:AT513388A4
    申请号:T50038/2013
    申请日:2013-01-22
    公开日:2014-04-15
    发明作者:Raphael Biancale
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    1 56539
    The invention relates to a dual-clutch transmission, in particular for a motor vehicle, having an input shaft and a main shaft, wherein the input shaft via a switchable first clutch with a first countershaft and via a switchable second clutch with a second countershaft is connectable, wherein the first countershaft and the second countershaft in each case via at least one via a switching device switchable gear pair with the main shaft is drive-connected, with at least one synchronizer formed by an electric machine for speed adjustment of the countershaft to the main shaft.
    From the publications US Pat. No. 6,427,549 B1, EP 1 270 301 A2, WO 2010/026022 A1, EP 1 610 038 A1, EP 1 237 230 B1, DE 10 2010 044 618 A1 and DE 10 2007 042 724 A1, dual-clutch transmissions with an input shaft and an output shaft, and known with two countershafts, wherein the rotational speeds of the countershafts are tuned by synchronizers formed by electric machines with the speed of the output shaft. 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 a synchronization, the gearwheel is clawed with a jaw clutch to the front of the car.
    Pumps, in particular lubricating oil pumps or the like are driven either by the internal combustion engine or by separate electric motors, which requires additional space and components.
    The object of the invention is to avoid these disadvantages and to propose a space and part-saving pressure source for hydraulic devices, in particular system pressure and / or lubricating oil systems.
    According to the invention this is achieved in that the electric machine is drive-connected to a hydraulic pump, wherein preferably a drive shaft of the electric machine and a drive shaft of the hydraulic pump, preferably a system pressure and / or lubricating oil pump, are arranged coaxially. 2/20 2
    The electric machine is thus designed as a multifunctional component and can be used for synchronization of the countershafts, as a drive for the hydraulic pump, or for hybrid functions, such as providing drive or braking torque, in particular for recuperation, as well as a starter motor for the internal combustion engine. As a result, components and space can be saved
    It is particularly advantageous if the electric machine can be drive-connected to the first or second countershaft via at least one clutch, preferably designed as a claw clutch, particularly preferably via at least one gear stage. Here, in a part and space-saving design, the electric machine by means of a single clutch, preferably a dog clutch, either via a first gear stage with the first countershaft or via a second gear stage with the second countershaft are drivingly connected. About the clutch, the electric machine can be connected to either the first or the second countershaft, or separated from both. As a result, the electric machine can ensure the drive for the lubricating oil pump even when the vehicle is at a standstill.
    In a first embodiment of the invention can be provided that a single electric machine via a first gear stage and a first clutch to the first countershaft and via a second gear stage and a second clutch to the second countershaft is drive-connected. This design is characterized by very few components.
    A second embodiment of the invention provides that the first countershaft a first electric machine and the second countershaft is assigned a second electric machine. The first electric machine is drive-connected via a first clutch, preferably a dog clutch, and at least a first gear stage with the first countershaft. It is particularly advantageous if the first electric machine can be drive-connected via the first clutch and a further first gear stage to the first clutch, preferably with an input-shaft-side part of the first clutch. This makes it possible, the first electric machine - bypassing the first countershaft - with the input shaft and thus directly to the 3/20 3rd
    Combine internal combustion engine, for example, for starting the internal combustion engine, or for charging the vehicle battery via the internal combustion engine when the vehicle is stationary.
    In the same way it can be provided that the second electric machine via a second clutch, preferably a dog clutch, and at least one second gear stage with the second countershaft and the second clutch and a further second gear stage with the second clutch - preferably with an input side part of the second Clutch drive is connectable.
    The first or second gear stage and the further first or second gear stages may optionally have different ratios.
    The first and the second clutch of the double clutch are advantageously designed as a wet-running Lammellenkupplungen, whereby high torques with a small space and low weight can be transmitted. The two clutches can be designed identical, in order to minimize the manufacturing costs.
    It is preferably provided that the switching devices are formed by jaw clutches. By means of the external synchronizing device formed by the electric machine, the switching devices themselves can be made unsynchronized.
    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 further embodiment of the invention it can be provided that a range group transmission is connected to the main shaft, wherein preferably the range group transmission comprises a planetary gear. 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. 4/20 4
    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 countershafts 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 is made possible.
    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 dog clutch with or without synchronization is connectable. The actuation of the dog clutches can be done via hydraulically actuated actuators.
    In order to enable space-saving manner different speeds of the electric machine and the pump can be provided in a further embodiment of the invention that the drive shaft of the electric machine is connected to the drive shaft of the pump via a planetary gear, preferably the drive shaft with a sun gear of the planetary gear and the drive shaft is rotatably connected to a web shaft of the planetary gear.
    The invention will be explained in more detail below with reference to FIGS.
    1 shows a double-clutch transmission according to the invention in a first embodiment, FIG. 2 shows a double-clutch transmission according to the invention in a second embodiment, FIG. 3 shows a double-clutch transmission according to the invention in a third embodiment and FIG. 4 shows a double-clutch transmission according to the invention in a fourth embodiment.
    Functionally identical parts are provided in the figures with the same reference numerals. 5/20 5
    The figures each show an inventive dual-clutch transmission 10 with twelve forward gears and four 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 illustrated in each of the figures 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 connected via single-stage first and second input gear stages 14, 15, which have different gear ratios, each having a first countershaft 16 and a second countershaft 17 in connection. Between the first input gear stage 14 and the first countershaft 16, a first shiftable clutch 18, between the second input 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 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 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 dual-clutch transmission 10 is further connected to the main shaft 13 range group transmission 21 may be provided with which switching between high gear ratios - fast range group HIGH - and low gear ratios - slow range group LOW - is possible. In the simplest case, the range group transmission 21 can be formed from two gear pairs with different gear ratios, each with a fixed gear and a loose gear between which can be switched by a switching device 20. In a compact embodiment, the range group transmission 21 may be formed as a planetary gear 24, wherein an element of the planetary gear 24 may be held by a switching device 20 or connected to a second element of the planetary gear 24. 6/20 6
    Reference numeral 25 denotes in FIG. 2 a parking lock connected to the main shaft 13 or output shaft 12.
    The countershafts 16, 17 are in each case via gear stages ZA1, ZA2, ZA3, ZA4, ZA5, ZA6, ZR1, ZR2 with the main shaft 13 in connection.
    The gears of the gear stages ZA1, ZA2, ZA3, ZA4, ZA5, ZA6, ZA7 ZR1, ZR2, the gear stages 14, 15 and the range group transmission 21 are zl, z2, z3, z4, z5, z6, z7, z8, z9, zlO, zll, zl2, zl3, zl4, zl5, zl6, zl7, zl8 denoted, wherein identical gears are provided with the same reference numerals.
    Each gear stage ZA1, ZA2, ZA3, ZA4, ZA5, ZA6, ZR1, ZR2 each have at least one free on a shaft - for example, a countershaft 16, 17 - circulating gear and one with another shaft - for example, the main shaft 13 - rotatably connected gear 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 gears can be mounted on the countershafts 16, 17 freewheeling and are rotatably connected to the main shaft 13 gears in the tooth-engaging.
    To each drive the freely rotating gears with the respective countershaft 16, 17 and main shaft 13 drive-proof, switching elements 20 are provided, which can be formed by synchronizing or - especially in the case of external electric or hydraulic synchronizers - by simple, non-synchronized jaw clutches. The switching elements 20 can be hydraulically actuated by not shown actuators, for example.
    In the drive case, one of the two countershafts 16, 17 via the respective clutch 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 via the switched to HIGH or LOW switching device 20 of the range group transmission 21 7/20 7 with the output shaft 12 and via a switched gear, such as gear 6, drivingly connected to the second countershaft 17. Thus, a power flow up to the output shaft 12 takes place via the second clutch 19.
    In the embodiment shown in Fig. 2, the input shaft 11 with the main shaft 13 directly via a clutch 40 is connected. Thereby, a direct drive between the input shaft 11 and the main shaft 13 are made possible.
    The dual-clutch transmission 10 may be modular and consist of a coupling part 50, a main transmission 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.
    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.
    In the embodiments shown in FIGS. 1 and 2, synchronizing devices 80 formed by electric machines 81, 181, 281 are provided which each have at least one clutch 82, 83 configured as a dog clutch and at least one gear stage 84, 85, 84 a, 85a, with the first or second countershaft 16, 17 is drive-connected. The drive shaft 81a, 181a, 281a of the electric machine 81, 181, 281 is drive-connected to the drive shaft 86a, 186a, 286a of a pump 86, 186, 286, for example a lubricating oil pump. The electrical machines 81, 181, 281 can be operated both by motor and by generator. The electrical machines 81, 181, 281 are designed as multifunctional components and serve to synchronize the countershafts 16, 17 during switching operations, to drive the pump 86, 186, 286, to start the internal combustion engine, to charge the vehicle battery and take over hybrid functions such as providing Drive and braking torque, as well as for recuperation.
    In the embodiment shown in Fig. 1, only a single electric machine 81 is provided, which is fixedly connected drive-connected with a pump 86. The shafts 81a, 86a can be brought into drive connection with either the first countershaft 16 or the second countershaft 17 via the first and second clutches 82, 83 and the first gear stage 84 and the second gear stage 85, respectively. As a result, the electric machine 81 in gear change operations as a central synchronization device for the
    Countershafts 16, 17 are used. On the other hand, hybrid functions can also be taken over by the electric machine 81, such as providing additional drive or braking torque. The electric machine 81 can also be used for starting the internal combustion engine or - operated as a generator - for charging the vehicle battery. If both the first and the second clutch 82, 83 are deactivated, the pump 86 - regardless of the speed of the countershafts 16, 17 - driven by the electric machine 81, whereby a sufficient lubricating oil supply can be made even when the vehicle is stationary. In each step, PiäscnifiSTrrest connected to the pump 86, whereby the required lubricating oil pressure is secured.
    The embodiment shown in FIG. 2 differs from FIG. 1 d, in that each countershaft 16, 17 is associated with an electric machine 181, 281, wherein the drive shaft 181a of the first electric machine 181 is associated with a
    Treibweile 186a a first pump 186, and the drive shaft 281a of the second electric machine 281 with a Treibweüe 286a a second pump 286 nt. wn ,! Electric machine 181 via the first clutch 82 with a first gear stage 84 or with another first gear stage 84a connectable. The first gear 84 is connected directly to the first Vorgelegewelie 16. The further first gear stage 84a starts with a coupling part 18a of the first 1/1 ö * e first fcjngangsget'rieöestufe 14 with the
    9
    The embodiment shown in Fig. 2 allows a smaller dimensioning of the pumps 186, 286, which space can be saved. The fact that each of the two electric machines 181, 281 can be selectively connected to the respective one (s).
    -1 'M | 11,11111 l! L internal combustion engine the vehicle battery over the harvest or second eizktrisr
    Haschine 181, 281 - or via both electrical machines 181, 281 are loaded directly. > over 81 ibwelle
    The embodiments of FIGS. 3 and 4 show Doppelkuppiungsgetriebe 10 c range group transmission. In each case, the drive shaft 86a of the pump 86, a planetary gear 90 is connected to the drive shaft 81a of the electric machine, wherein the drive shaft 81a with dam sun gear 90a and the Tra 10/20
    权利要求:
    Claims (6)
    [1]
    1. A dual-clutch transmission (10), in particular for a motor vehicle, having an input shaft (11) and a main shaft (13), wherein the input shaft (11) via a switchable first clutch (18) with a first countershaft (16) and a switchable second clutch (19) with a second countershaft (17) is connectable, wherein the first countershaft (16) and the second countershaft (17) via at least one via a switching device (20) switchable gear pair (Z) with the main shaft (17) 13) is drivably connectable to at least one synchronizing means (80) formed by an electrical machine (81, 181, 281) for the nmhzRh l.an match rg Ire 'i' (TV;;; TV ~ s s ur & & ur ur ur ur ur ur ^ fe '(TV ;, -J _ -J!! - ___: - S- - - i- -j - - - - E - t -i: - - λ λ L-: / / ~ ι * - " * ✓ ** »« a> SV. CM IC ΓΛ IU ICUÖ f ^ l ^ ^ OhcrernT '(Soa, "iSoa ^ SSoaj'oehvi' ^ criälirristfiei i pump (86, 186, 286), virtue example, a system pressure and / or lubricating oil pump, are arranged coaxially.

    11 / r, rp ^ | eo. ^ EUft. ^ L ^ u ^ d, iVibe, ^ a ,, T ^ 'l ^, Gpti: b ^ f0L'3iiiigglc> bj ύηά ei second .. u. ι ^ υμμΕΐινυμμι ui lyoycu icuc ^ j. Jj iiaun λλι Ι3μι uui ix, uauuiuu y c'ke Π ΠΖθίΟΐΊΠθΐ that the first countershaft (16) a first electric machine (181) and the second countershaft (17) a second electric machine (282) is assigned. in that the first electric machine (181) can be drive-connected to the first countershaft (16) via a first clutch (82), preferably a dog clutch, and at least one first gear stage (84, 84a).
    [2]
    7. Doppelkuppiungsgetriebe (10) according to any one of claims 6, characterized n § kö 0 naifü; α 1 1) ¾ rriPrA yrt TfJ i O: * · · · ·· - V c.r · ..... ·. · · · ·. , , / W. · BhVtspe'r



    12
    [3]
    11. dual-clutch transmission (10) according to claim 10, characterized in that the second gear stage (85) and the further second gear stage (85a) have different translations.
    [4]
    12 dual-clutch transmission (10) according to one of claims 1 to 11, characterized in that the input shaft (11) with the main shaft (13) directly via a jaw clutch (40) is connectable.
    [5]
    13. dual-clutch transmission (10) according to one of claims 1 to 12, characterized in that with the main shaft (13) a range group transmission (21) is connected, wherein preferably the range group transmission (21) comprises a planetary gear (24).
    [6]
    14 dual-clutch transmission (10) according to one of claims 1 to 13, characterized in that the drive shaft (81 a) of the electric machine (81) with the drive shaft (86 a) of the pump (86) via a planetary gear (90) is connected, Preferably, the drive shaft (81a) with a sun gear (90a) of the planetary gear (90) and the drive shaft (86a) with a web shaft (90b) of the planetary gear (90) is rotatably connected. 2013 01 22 Fu 13/20
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    同族专利:
    公开号 | 公开日
    WO2014114560A1|2014-07-31|
    AT513388B1|2014-04-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US20040166980A1|2001-05-03|2004-08-26|Joseph Supina|Transmission arrangements for hybrid electric vehicles|
    DE19850549A1|1998-11-03|2000-05-04|Bosch Gmbh Robert|Gearbox for a motor vehicle, in particular dual clutch manual gearbox, and method for operating the gearbox|
    DE10165096B3|2000-07-18|2015-08-13|Schaeffler Technologies AG & Co. KG|transmission|
    AT498788T|2004-06-21|2011-03-15|Getrag Ford Transmissions Gmbh|DOUBLE CLUTCH GEARBOX AND METHOD FOR CONTROLLING A DOUBLE CLUTCH GEAR|
    DE102006054281A1|2006-11-17|2008-06-12|Zf Friedrichshafen Ag|Double clutch winding transmission|
    AT510966B1|2011-06-09|2012-08-15|Avl List Gmbh|GEARBOX, ESPECIALLY DOUBLE CLUTCH GEARBOX|DE102015200067A1|2014-01-08|2015-07-09|Volkswagen Aktiengesellschaft|Hybrid drive arrangement of a motor vehicle and method for its control and / or regulation|
    DE102016122706B3|2016-11-24|2018-05-09|Getrag Ford Transmissions Gmbh|Manual transmission with oil pump|
    DE102018214430A1|2018-08-27|2020-02-27|Zf Friedrichshafen Ag|Hydraulic system for a double clutch transmission|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50038/2013A|AT513388B1|2013-01-22|2013-01-22|Double clutch|ATA50038/2013A| AT513388B1|2013-01-22|2013-01-22|Double clutch|
    PCT/EP2014/050851| WO2014114560A1|2013-01-22|2014-01-17|Double clutch transmission|
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