• 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 transmission (10) for a motor vehicle, having an input shaft (11) and a main shaft (13), a first clutch (18) and a second clutch (19), and a first and a second countershaft (16, 17 ), wherein a first hydraulic machine (31) is drivingly connected to the first countershaft (16) and a second hydraulic machine (32) is connected to the second countershaft (17), wherein the two hydraulic machines (31, 32) comprise a synchronizing device (30). for speed adaptation of the countershafts (16, 17) to the main shaft (13) and in a first operating mode during a rotational speed adjustment of the countershafts (16, 17) to the main shaft (13) in a closed hydraulic circuit (33) are operable. In order to save installation space, weight and parts, it is provided that in a second operating mode both hydraulic machines (31, 32) can be operated as pumps and with a first hydraulic system (41) for providing a hydraulic system pressure and / or with a second hydraulic system (42) for providing a lubrication pressure are hydraulically connectable.
    公开号:AT512941A4
    申请号:T504352012
    申请日:2012-10-08
    公开日:2013-12-15
    发明作者:Stefan Infanger；Gerhard Woentner；Stefan Kuntner
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    Ö9ll6-2012 1 56495
    The invention relates to a transmission, in particular dual-clutch transmission, for a motor vehicle, with an input shaft and a main shaft, wherein the input shaft via a switchable first clutch with a first countershaft and a switchable second clutch with a second countershaft is connectable, wherein the first countershaft and the second countershaft is driveably connected to the main shaft via at least one pair of gears via a shifting device, wherein a first hydraulic machine is drivingly connected to the first countershaft and a second hydraulic machine is connected to the second countershaft, wherein each of the two hydraulic machines is either a hydraulic drive motor or is operable as a hydraulic pump, wherein the two hydraulic machines form a synchronizer for speed adjustment of the countershafts to the main shaft and in a first operating mode during a Dre adjustment of the countershaft to the main shaft in a closed hydraulic circuit are operable. Furthermore, the invention relates to a method for operating a transmission.
    From AT 510 966 Bl a dual-clutch transmission with a first and a second countershaft is known, each countershaft is connected to a hydraulic machine. The two hydraulic machines form a synchronizer, wherein a hydraulic machine is operated as a pump and the other hydraulic machine as a motor for driving the corresponding countershaft during a Synchronisiervorganges.
    The US 6,460,425 Bl discloses a dual-clutch transmission with two countershafts, on each of which a hydraulic pump is arranged, which provides the system pressure for the actuation of the two clutches.
    DE 10 2007 018 967 Al describes an automated group transmission for a vehicle with a main transmission and at least one upstream and / or downstream After area group and with at least one countershaft, wherein the countershaft is operatively connected to at least one hydraulic arrangement to provide a power take-off. The hydraulic arrangement has at least one drive unit for controlling and / or regulating each countershaft. 2 2 1-10-20¾ [102 (312/50435) Typically, various devices are used for synchronization, countershafts, providing system pressure to actuate the hydraulically actuated clutches, and providing lubrication oil pressure to lubricate engine and transmission bearing locations. However, this is space, manufacturing and cost consuming and also has a detrimental effect on the weight and the number of parts of the vehicle.
    The object of the invention is to avoid these disadvantages, and to reduce the manufacturing and cost and to reduce the weight and space requirements and the number of parts.
    According to the invention this is achieved in that in a second operating mode both hydraulic machines are operable and with a first hydraulic system for providing a system pressure - preferably for actuating at least one clutch or switching device - and / or with a second hydraulic system for providing a lubricating pressure for lubrication From bearings - preferably the transmission and / or a prime mover - are hydraulically connected.
    In the second mode of operation, the first hydraulic machine can be hydraulically connected to the first hydraulic system. Furthermore, the second hydraulic machine can be hydraulically connected to the second hydraulic system.
    In a preferred embodiment, in the second operating mode, the first hydraulic machine is connected to the first hydraulic system and the second hydraulic machine is connected to the second hydraulic system. Thus, the first hydraulic machine provides the system pressure for actuating the hydraulically operable clutches and the second hydraulic machinery provides the lubricating oil pressure for lubricating oil supply to engine and / or transmission mounts. Further hydraulic pumps for the hydraulic system pressure and the lubricating oil pressure can thus be omitted.
    The invention makes use of the fact that the synchronization of the Vorgelegeweilen only takes a very short period of time and thus the hydraulic machines are not needed during the remaining time for speed adjustment of countershafts to the main shaft.
    10-2Q12 HÖ 2012/50435 3
    The first and second hydraulic systems may be hydraulically separated from one another on the pressure side. By using the first hydraulic machine to build up the system pressure and the other hydraulic machine to build up the lubricating oil pressure, system pressure and oil pressure can be controlled separately.
    It is particularly advantageous if at least one of the - preferably both -hydraulic machines has a speed-independent flow control. The speed-independent displacement adjustment of the two hydraulic machines leads to a high efficiency, since in each case only that energy is generated, which is needed for the present situation.
    In an alternative embodiment of the invention, it is provided that, at least in the second operating mode, the first hydraulic system can be hydraulically connected to the second hydraulic system on the pressure side. Simple control is made possible if, at least in the second operating mode, the first hydraulic system can be hydraulically connected to the second hydraulic system on the pressure side. Thus, in this alternative embodiment both hydraulic machines are used both to provide the system pressure and to provide the lubricating oil pressure.
    In the first operating mode, the two hydraulic machines are operated in a closed hydraulic circuit, whereby one of the two hydraulic machines is operated as a pump, and the other hydraulic machine as a hydraulic motor.
    In the second operating mode, however, both hydraulic machines are operated as pumps in an open hydraulic circuit.
    The two hydraulic machines can be controlled independently of each other. A particularly compact solution is obtained when the transmission including the synchronization device is arranged in a common housing, wherein preferably the closed circuit is formed inside the housing. The fact that the entire hydraulic system of the closed circuit is disposed within the housing of the transmission, a very space-saving design can be made possible. 4 4 fÖ 2012/50435
    Printed; 09-1 Ö- ö ö 12
    The invention will be explained in more detail below with reference to FIGS.
    They show schematically:
    1 shows a transmission according to the invention with twelve forward gears,
    2 shows a variant of the range group transmission from FIG. 1
    Fig. 3 is a hydraulic circuit diagram of the transmission according to the invention in a first embodiment and
    Fig. 4 is a hydraulic circuit diagram of the transmission according to the invention in a second embodiment.
    Functionally identical parts are provided in the figures with the same reference numerals.
    The different gear ratios are indicated in the figures by the reference numerals 1, 2, 3, 4, 5, 6 for the forward gears and R, RI, R2 for the reverse gears.
    The illustrated in Fig. 1, designed as a double clutch transmission 10 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 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 gear stage 14 and the first countershaft 16, a first schajtbare coupling 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 hydraulically operated 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. bäiMi (eöi4 | ix®iMö435 5
    The countershafts 16,17 are each about gear stages z with the main shaft 13 in conjunction. Each gear stage Z has in each case at least one toothed wheel Zr freely rotating on a shaft - for example a countershaft 16, 17 - and a toothed wheel Zr connected in a rotationally fixed manner to another shaft - for example the main shaft 13. The gear stages ZR the reverse gears R, RI, R2 additionally have a reverse gear to. In order to save manufacturing costs, two on the countershafts 16, 17 opposite gears Zf or may be formed as equal parts. The gears Zf can be mounted on the countershafts 16,17 freewheeling and are engaged with rotatably connected to the main shaft 13 gears Zr in the tooth. Alternatively, however, the gears Zr may be non-rotatably connected to the respective countershaft 16, 17 and be in mesh with freely rotatably mounted on the main shaft 13 gears Zf (Fig. 2).
    To each drive the freely rotating gears Zf with the respective countershaft 16, 17 and main shaft 13 driveably connect switching elements 20 are provided, which are formed by simple, non-synchronized jaw clutches. The switching elements 20 can be hydraulically actuated by not shown actuators, for example.
    In the drive train of the transmission 10 may further be provided a connected to the main shaft 13 range group transmission 21, with which a switching between high ratios HIGH and low ratios LOW is possible. In the simplest case, the range group transmission 21 can be formed from two gear pairs 22, 23 with different gear ratios, each having a fixed gear Zr and a loose gear Zf, between which can be switched over a switching device 20 (Fig. 2). 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 festgehaiten via a switching device 20 or can be connected to a second element of the planetary gear 24 (Fig. 1).
    Reference numeral 25 denotes a parking lock connected to the main shaft 13 or output shaft 12.
    1102012/50435
    In the embodiment shown in Fig. 1, the input shaft 11 is directly connectable to the main shaft 13 via a dog clutch 40. 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 thus be used for different applications and vehicles, such as buses, trucks, road vehicles and off-road vehicles application.
    The transmission 10 further comprises a synchronizing device 30, with which each of the rotational speeds between a driven countershaft 16, 17 with a respective on the countershaft 16, 17 freewheeling gear Zf can be adjusted to allow a switching operation with the switching devices 20. The synchronizing device 30 has a first hydraulic machine 31 and a second hydraulic machine 32, wherein the hydraulic machines 31, 32 in the first operating mode for speed adjustment of the countershafts 16, 17 to the main shaft 13 as both a hydraulic motor, and as a hydraulic pump is operable , Each hydraulic machine 31, 32 is independent of the other controllable. The hydraulic machines 31, 32 are arranged in a first operating mode in a closed hydraulic circuit 33, wherein both the hydraulic machines 31, 32, and the closed hydraulic circuit 33 may be disposed within the housing of the transmission 10, not shown.
    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 first countershaft 16 is drivingly connected via an inserted gear, such as gear 3 with the main shaft 13, wherein the first hydraulic machine 31 operates as a hydraulic pump and pressure in the hydraulic circuit 33 builds. The second hydraulic machine 32 is used as a hydraulic motor to bring the second countershaft 17, which is not drivingly connected to the input shaft 11, to synchronous speed with the respective next gear stage to be shifted. If the synchronous speed is reached, by activating the respective switching device 20 the next gear, for example gear 4, can be engaged.
    With the hydraulic machines 31, 32, the rotational speed adjustment of the main shaft 13 with the range group transmission 21 and thus with the output shaft 12 in the case of a range group circuit can also be carried out.
    In the drive case, the main shaft 13 is drivingly connected via the switched to HIGH or LOW switching device 20 of the range group with the output shaft 12 and a switched gear, for example, gear ratio 2, with the countershaft 17. By means of the second clutch 19, a force flow thus takes place up to the output shaft 12.
    By opening the second clutch 19, there is a frictional connection interruption in the transmission 10 and, for example, in the position HIGH switched switching device 20 in the range group transmission 21, can be turned off. The power flow between the main shaft 13 and output shaft 12 is interrupted. The driven via the first clutch 18 and the countershaft 16 hydraulic machine 31 operates as a hydraulic pump and builds pressure in the hydraulic circuit 33. The second hydraulic machine 32 is used as a hydraulic motor to bring the main shaft 13 drivingly connected to the countershaft 17 and gear 1 to synchronous speed with the element of the range group transmission 21 to be shifted respectively. If the synchronous speed is reached, the desired range, for example LOW, can be set by activating the switching device 20 in the range group transmission 21. Thus, the power flow between the main shaft 13 and output shaft 12 is restored.
    The output shaft 12 is now driven via the vehicle mass and is drive-connected via the switched range group transmission 21, the main shaft 13 and the gear 1 with the countershaft 17 and via this with the hydraulic machine 32. The hydraulic machine 32 now works as a pump. The second hydraulic machine 31 is now used as a hydraulic motor to bring after opening the first clutch 18, the countershaft 16 at synchronous speed with the gearshifting gear, for example, gear 6. If the synchronous speed is reached, the gear stage can be engaged by activating the respective switching device 20. At the same time, the gear ratio still engaged, for example gear ratio 1, can be switched off. gl§ar®lfif
    10 201 ^ / 50435
    By closing the first clutch 18, the countershaft 16 is drivingly connected via the gear 6 with the main shaft 13 and this connected via the switched range group transmission 21 to the output shaft 12.
    Since the synchronization takes a very short period of time, the two hydraulic machines 31, 32 can be used the rest of the time for other services.
    Therefore, the hydraulic machines 31, 32 may be operated out-of-sync in a second mode of operation in which they provide the system pressure to actuate the clutches 18, 19 or shifters 20 and / or the lubricating oil pressure to lubricate engine or transmission 10 bearings.
    For this purpose, the two hydraulic machines 31, 32 are operated in the second operating mode as pumps by both clutches 18, 19 are closed and both hydraulic machines 31, 32 are driven via the respective countershaft 16,17. In this case, only one switching device 20 of a countershaft 16, 17 of the currently engaged gear in engagement with the corresponding gear Zf, the other switching devices 20 are in the open position to allow unimpeded rotation of the other countershaft 17, 16. In the second operating mode, the two hydraulic machines 31, 32 are no longer operated in a small closed circuit 33 within the housing, but operated in an open circuit. The first hydraulic machine 31 is hydraulically connected to a first hydraulic system 41 for providing a hydraulic system pressure for actuating at least one clutch 18, 19 or switching device 20. The second hydraulic machine 32 is hydraulically connected to a second hydraulic system 42 for providing a lubrication pressure for lubricating bearing points of the transmission and / or an engine. First and second hydraulic systems can be hydraulically separated (FIG. 3) or connected (FIG. 4).
    3 shows a hydraulic circuit diagram for the two hydraulic machines 31, 32. The switching between the closed circuit 33 and the open circuits of the first and second hydraulic systems 41, 42 takes place via, for example, 3/2 way valves formed first and second 9 9 Μ: 10: 201 ^ / 50435
    Switch valves 43, 44. Reference numerals 45, 46 pressure relief valves are designated. By means of the hydrostatic control units 47, 48, the delivery rate of the hydraulic machines 31, regardless of the input speed of the countershafts 16,17 are controlled. By reference numeral 49 check valves, designated by reference numeral 50, a filter unit. In the embodiment shown in Fig. 3, the hydraulic systems 41, 42 formed separately on the pressure side - thus can be controlled separately via the respective hydraulic machine 31, 32 of each hydraulic system 41, 42.
    By contrast, in the hydraulic circuit diagram shown in FIG. 4, the first and second hydraulic systems 41, 42 are connected to each other. By means of a third switching valve 51, the first hydraulic unit 31 can optionally be connected to the second hydraulic system 42 or - via a further check valve 52, a filter unit 53 and a pressure relief valve 54 with the first hydraulic system 41. Designated by reference numerals 55 and 56 are temperature and pressure sensors.
    In order to avoid a pressure drop, in particular in the first hydraulic system 41, in the short synchronization phases in which the hydraulic machines 31, 32 are in the first operating mode, a pressure accumulator 57 may be provided whose capacity is dimensioned such that the time can be bridged without problems until the second operating mode following the first operating mode with renewed pressure build-up.
    The invention has been described with reference to a 12-speed dual-clutch transmission. It goes without saying, however, that the invention is by no means limited thereto, but that it can also be used for a wide variety of speeds and gear arrangements.
    权利要求:
    Claims (17)
    [1]
    1. Patent application (10), in particular a double-clutch transmission, for a motor vehicle, having an input shaft (11) and a main shaft (13), wherein the input shaft (11) is connected via a switchable first clutch (18) to a first countershaft (10). 16) and via a switchable second clutch (19) with a second countershaft (17) is connectable, wherein the first countershaft (16) and the second countershaft (17) each have at least one via a Schaiteinrichtung (20) switchable gear pair (Z) with the main shaft (13) is drive-connected, wherein the first countershaft shaft (16) a first hydraulic machine (31) and with the second countershaft (17) a second hydraulic machine (32) is drivingly connected, wherein each of the two hydraulic machines ( 31, 32) is selectively operable as a hydraulic drive motor or as a hydraulic pump, wherein the two hydraulic machines (31, 32) a synchronizing means (30) for Drehzahlan adaptation of the countershafts (16, 17) to the main shaft (13) and are operable in a first operating mode during a rotational speed adjustment of the countershafts (16, 17) to the main shaft (13) in a closed hydraulic circuit (33), characterized that in a second operating mode both hydraulic machines (31, 32) are operable as pumps and with a first hydraulic system (41) for providing a hydraulic system pressure - preferably for actuating at least one clutch (18, 19) or switching device (20) - and / or with a second hydraulic system (42) for providing a lubricating pressure for lubrication of at least one bearing point - preferably the transmission (10) and / or a drive machine - are hydraulically connectable.
    [2]
    2. Transmission (10) according to claim 1, characterized in that in the second operating mode, the first hydraulic machine (31) with the first hydraulic system (41) is hydraulically connected.
    [3]
    3. Transmission (10) according to claim 1 or 2, characterized in that in the second operating mode, the second hydraulic machine (31) with the second hydraulic system (42) is hydraulically connected.

    §§2 / $$ 35 (Printed: 09-10-2012 ijEÖ15 11
    [4]
    4. Transmission (10) according to one of claims 1 to 3, characterized in that at least in the second operating mode, the first hydraulic system (41) with the second hydraulic system (42) is hydraulically connectable on the pressure side.
    [5]
    5. Transmission (10) according to one of claims 1 to 4, characterized in that in the second operating mode, both hydraulic machines (31, 32) with both the first, and with the second hydraulic system (42) are hydraulically connectable.
    [6]
    6. Transmission (10) according to one of claims 1 to 3, characterized in that the first and the second hydraulic system (41, 42) are hydraulically separated from each other on the pressure side.
    [7]
    7. Transmission (10) according to one of claims 1 to 4, characterized in that at least one of the two hydraulic machines (31, 32) has a control unit (47, 48) for speed-independent flow control.
    [8]
    8. Transmission (10) according to one of claims 1 to 7, characterized in that the first and / or second hydraulic system (41, 42) has a pressure accumulator (57).
    [9]
    9. transmission (10) according to one of claims 1 to 8, characterized in that in the second operating mode, the hydraulic machines (31, 32) are operable in an open hydraulic circuit.
    [10]
    10. Transmission (10) according to one of claims 1 to 9, characterized in that the transmission (10) together with the synchronization device (30) is arranged in a common housing, wherein preferably the closed hydraulic circuit (33) is formed within the housing.
    [11]
    11. A method for operating a transmission (10), in particular dual-clutch transmission, 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 via a switchable second clutch (19) with a second Vorgeiegewelle (17)) -10 ^ 2012 | θί $ flÖ2012 / 50435 12 is connectable, wherein the first countershaft (16) and the second countershaft (17) in each case via at least one a switching device (20) switchable gear pair (Z) to the main shaft (13) is drive-connected, wherein the first countershaft (16) drivingly connected to a first hydraulic machine (31) and the second countershaft (17) a second hydraulic machine (32) is, wherein each of the two hydraulic machines (31, 32) is selectively operated as a hydraulic drive motor or as a hydraulic pump, wherein the two hydraulic machines (31, 32) in one first operating mode during a gear change for speed adjustment of the countershafts (16, 17) to the main shaft (13) in a closed hydraulic circuit (33) are operated, characterized in that in a second operating mode, both hydraulic machines (31, 32) operated as pumps and at least with a first hydraulic system (41) for providing a system pressure, preferably for actuating at least one clutch (18, 19) or shifter (20), and / or with a second hydraulic system (42) for providing a lubrication pressure for lubrication a bearing - preferably the transmission and / or a prime mover -hydraulically connected.
    [12]
    12. The method according to claim 11, characterized in that in the second operating mode, the first hydraulic machine (31) with the first hydraulic system (41) is hydraulically connected.
    [13]
    13. The method according to claim 11 or 12, characterized in that in the second operating mode, the second hydraulic machine (32) with the second hydraulic system (42) is hydraulically connected.
    [14]
    14. The method according to any one of claims 11 to 13, characterized in that at least in the second operating mode, the first hydraulic system (41) with the second hydraulic system (42) is hydraulically connected on the pressure side.
    [15]
    15. The method according to any one of claims 11 to 14, characterized in that in the second operating mode both hydraulic machines (31, 32) with both the first, and with the second hydraulic system (41, 42) are hydraulically connected. 09 ^ 10-2012 ioeii 1102011 / 50¾ 13
    [16]
    16. The method according to any one of claims 11 to 15, characterized in that at least one of the two hydraulic machines (31, 32), the flow rate is controlled independently of speed.
    [17]
    17. The method according to any one of claims 11 to 16, characterized in that in the second operating mode, the hydraulic machines (31, 32) are operated in an open hydraulic circuit. 2012 10 08 Fu
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    同族专利:
    公开号 | 公开日
    DE112013004916A5|2015-09-03|
    AT512941B1|2013-12-15|
    WO2014056728A1|2014-04-17|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE4104167A1|1990-02-13|1991-10-24|Michael Meyerle|Switching device for vehicle automatic transmission|
    EP0505688A1|1991-03-26|1992-09-30|CLAAS Kommanditgesellschaft auf Aktien|Control for the positive displacement machine of a hydrostatic-mechanical gearing shiftable under load|
    US6460425B1|2001-01-10|2002-10-08|New Venture Gear, Inc.|Twin clutch automated transmission|
    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|
    DE102007038175A1|2007-08-13|2009-02-19|Magna Powertrain Ag & Co Kg|manual transmission|
    AT510966B1|2011-06-09|2012-08-15|Avl List Gmbh|GEARBOX, ESPECIALLY DOUBLE CLUTCH GEARBOX|DE102014016173A1|2014-11-03|2016-05-04|Audi Ag|Drive device for a motor vehicle|
    DE102015225301A1|2015-12-15|2017-06-22|Zf Friedrichshafen Ag|Hydraulic actuation of a coupling|
    法律状态:
    2018-06-15| MM01| Lapse because of not paying annual fees|Effective date: 20171008 |
    优先权:
    申请号 | 申请日 | 专利标题
    AT504352012A|AT512941B1|2012-10-08|2012-10-08|transmission|AT504352012A| AT512941B1|2012-10-08|2012-10-08|transmission|
    PCT/EP2013/070108| WO2014056728A1|2012-10-08|2013-09-26|Double-clutch transmission|
    DE112013004916.3T| DE112013004916A5|2012-10-08|2013-09-26|Double clutch|
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