• 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 rotary transmission has an input shaft (11), an output shaft (19), two layshafts (14,15), two drive clutches (12,13) and gear trains selectively engageable by dog clutches (S3, S4, S5, S6) to transmit drive from the input shaft to the output shaft according to the state of engagement of the drive clutches and dog clutches. A transfer gear train (49, 48, 47) and dog clutch (S2) is provided for drive between the layshafts (14, 15), a further dog clutch (S1) being provided between one of the layshafts (14) and the output shaft. The transmission provides six sequential speed ratios with pre-selection of adjacent ratios, alternate speed ratios being driven respectively through one and the other clutch.
    公开号:SU1189330A3
    申请号:SU823493799
    申请日:1982-09-17
    公开日:1985-10-30
    发明作者:Джон Янг Аластэр
    申请人:Аутомотив Продактс,Плс (Фирма)；
    IPC主号:
    专利说明:

    00
    with
    00 00, The invention relates to rotator double-clutch gearboxes, namely gearboxes having gears, each of which is one of the group enclosing a series of pulsating speed ratios and two independently sustained clutches providing alternately The first drive paths are through gears between the common input and the common output, with the gears and queue relations in the group being driven through one and the other clutch, respectively. . Lime rotary power transmission, containing an input shaft with drive gears 1-1, connected by a constant gearing with the output shaft and intermediate shafts parallel to the drive shaft and input shaft with gears and gear couplings for coupling the driven gears by corresponding intermediate shafts, two friction gears clutches; installed by the Hai input shaft for communicating with it the respective leading gears, gears of the intermediate shafts are permanently engaged with the corresponding leading gears and gears CO. The disadvantage is structures A gearbox is the impossibility of obtaining a large range of transfer ratios. The purpose of the invention is to expand the kinematic range while maintaining the gearbox dimensions. The goal is achieved by the fact that a rotational power transmission box containing an input shaft with drive gears, constant gearing with the output shaft and intermediate shafts parallel to it and the input shaft with driven gears and gear couplings for communication is driven gears corresponding shafts, two friction clutches mounted on the input shaft to communicate with the respective drive gears, gears of the intermediate shafts are permanently engaged with the corresponding gears, is equipped with additional gear freely mounted on the input shaft and introduced into it into constant engagement with at least two additional driven gears, one of which is rigidly fixed on one intermediate shaft, and the other is connected to another intermediate shaft by means of a gear couplings. FIG. 1 shows a diagram of a gearbox with one of the intermediate shafts located in a different plane, an axial section; in fig. 2 - gear boxes, certain gears, front view. FIG. Figure 1 shows a gearbox having three main shafts lying in the same plane. As shown in FIG. 2, one of the shafts may be located outside the plane of the other two. Input torque is applied to the gearbox from the engine either directly or through a fluid connection, such as a hydraulic torque converter. The connection may include a locking sleeve, coupled to directly connect the inlet and the outlet. The gearbox is designed for automatic operation. FIG. 1 and 2 shows the input shaft .1- from the engine, connected through coupling 2 or through coupling 3 and transmissions from gears with output vagals and 4 and 5, having corresponding output gears 6 and 7. The latter are in engagement with gears the wheel 8 of the output shaft 9, which may form part of the differential gear assembly for transmitting the drive torque to the wheels of the vehicle. The wheel 6 is freely mounted on the shaft 4, and the wheel 7 rotates with the shaft 5. The coupling 2 preferably represents a conventional one-plate dry coupling, having a flywheel 10, a driven plate 11, a pressure plate 12, a blade 13 and springs 14. The release bearing 15 powered by. In order to unload the spring and thus unlatch the driven plate 11. The drive shaft 16, fixed for rotation with the flywheel 10, passes through a group of gears to the opposite side of the gearbox to drive another clutch. 3 The clutch 3 is a clutch with a wet plate, having a drive element 17, a pressure plate 18 and a slave-plate 19. The piston 20, displaced in the drive element 17, is supplied under pressure with a fluid through the channel 21 in the gearbox cover 22.. The piston 20 has a pressure relief valve. For each driven plate 11 and 19 of the clutch, the input gears are mounted on the drive shaft 16. Each gear wheel -23 and 24 are driven by two gear wheels 25 ,. 26 and 27, 28, respectively, mounted on the output shafts 4, 5. The intermediate gear gear between the output shafts comprises a gear wheel 29 mounted on the shaft 5, an intermediate gear 30 mounted on the drive shaft 16 midway between the input gears 23, 24 and a wheel 31 mounted for rotation with a shaft 4, Intermediate shchestren 30 has a corresponding profile for engagement with each of the wheels 29, 31 to ensure the same tension of the gears. The gearbox works as follows. , Both clutches 2, Z. and the nodes of synchronizers 32-37 uncoupled. In order to engage the first gear, the clutch units Zb and 33 are brought into the gearing. Clutch 2 for smooth transmission of the drive from the input shaft 1 through gears 23, 26, 31, 30 29 to the output shaft 5 and therefore through gear 7 differential gear 8.. The gear 6 is driven by the differential gear 8 all the time, but it rotates freely with respect to the output shaft 4 due to the free fit on. him By introducing the synchronizing unit 37 into engagement, a second gear can be preselected; the slave plate 19 of the clutch 3 is idled by the output shaft 4 through a gear train 28, 24. What ... to switch the gear transmission first to the second, simultaneously with disengagement of clutch 2, clutch 3 is brought into engagement. The drive is performed via gear 30.4 gear 24, 28, 31, 30, 29, and the driven plate of clutch 2 through gear 26, 23 is idle. The synchronizer assembly 36 may remain engaged in waiting for the gear shift back to the first, or it may be disengaged in preparation for shifting to the third gear. - -. The third gear can be selected preliminarily by engaging the synchronizer unit 34, idly driving the driven plate 1 via gear 25, 23. Shifting from second gear to third gear is done in the same way as the previous shift by simultaneously disengaging clutch 3 and introduction to the z.acelle. the coupling 2, and the nodes synchronization, congestion 37 and 33 then disengaged in preparation for further switching to a higher gear, if necessary. . In order to preselect the fourth gear, the synchronizer assembly 35 is engaged, the gear shift being performed by changing the drive from the clutch 2 to the clutch 3, and the synchronizer assembly 34 is subsequently disengaged. For the fifth gear, synchronizers 32 and .36, an idler drive slave plate 11 from output gear 6, are introduced into the gear .- To effect the speed shift, the drive is transmitted from clutch 3 to clutch 2.. Switching to the sixth gear is carried out, as indicated, after prior selection of the engagement of the synchronizer unit 37 .. The gearshift to the lower gears is performed in the same way by preselecting the next alternate gear in the group, which is followed by gearshift. water coupled to this coupling to coupled to this coupling. 11, a relief valve 38 should prevent the pressure from expanding behind the piston 20 due to centrifugal forces. The ball and valve openings are carefully chosen to ensure that the pressure is applied
    through the channel 21 will take the ball on its saddle, closing the valve. Reducing the clutch pressure allows the ball to roll off its seat under the action of centrifugal force, opening the valve.
    In the embodiment of the device shown in FIG. 1, the gear 6 is mounted for rotation with the output shaft 4, and the synchronizer assemblies 36 and. 37 and the gears 36 and 31 are mounted on an annular shaft, loosely mounted on the output shaft 4. Then the synchronizer assembly 32 connects
    J output shaft 4 with an annular shaft. The operation of the transmission does not change, but the device version may be more suitable for other installation conditions. .
    10 The invention can increase the kinematic range of a transmission without increasing its size.
    权利要求:
    Claims (1)
    [1]
    ROTARY POWER TRANSMISSION, containing an input shaft with drive gears, continuously engaged with the output shaft and parallel to it and the input shaft, intermediate shafts with driven gears and gear couplings for communication, driven gears with the corresponding intermediate shafts, two friction couplings mounted on the input shaft for communication with him the corresponding driving gears; the gears of the intermediate shafts are continuously engaged with the corresponding drive gears, which is different. the fact that, in order to expand the kinematic range while maintaining the dimensions of the gearbox, the latter is equipped with additional gear freely mounted on the input shaft and at least two additional driven gears engaged with it in constant engagement, one of which is rigidly fixed to one intermediate shaft, and the other is connected to the other countershaft by means of a gear coupling.
    SU m 1189330
    1 1189330 2
    类似技术:
    公开号 | 公开日 | 专利标题
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    CA1138681A|1983-01-04|Automatic transmission
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    EP0554354B1|1995-01-25|Motor vehicle gearbox
    JPH0874949A|1996-03-19|Gear shift device
    US2658405A|1953-11-10|Selective gear transmission
    US4693129A|1987-09-15|Countershaft automatic transmission
    JP2003525407A|2003-08-26|Automotive gearbox
    USRE33336E|1990-09-18|Change speed transmission
    EP0040864B1|1986-05-28|Power shift transmission
    US2722844A|1955-11-08|Transmissions
    JPH05248505A|1993-09-24|Multistage transmission with automatic load-shift spur gear
    EP0206734A1|1986-12-30|A change speed transmission
    GB2078318A|1982-01-06|Rotary change-speed transmission
    EP0675299A2|1995-10-04|Multi-axis countershaft power transmission
    同族专利:
    公开号 | 公开日
    US4476737A|1984-10-16|
    EP0075408B1|1987-02-25|
    EP0075408A2|1983-03-30|
    ES8308012A1|1983-08-16|
    AU552791B2|1986-06-19|
    EP0075408A3|1984-10-17|
    GB2107805B|1985-07-24|
    ES515792A0|1983-08-16|
    BR8205449A|1983-08-23|
    GB2107805A|1983-05-05|
    AU8779182A|1983-03-31|
    JPS5865350A|1983-04-19|
    DE3275478D1|1987-04-02|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    RU2545217C2|2010-03-05|2015-03-27|ДЖИЭМ Глобал Текнолоджи Оперейшн ЛЛЦ|Vehicle transmission|
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    GB594408A|1944-09-30|1947-11-11|Howard Frederick Hobbs|Improvements in or relating to power transmission mechanism|
    US1759558A|1928-04-04|1930-05-20|Krupp Ag|Variable-speed gear|
    US2543412A|1942-08-07|1951-02-27|Kegresse Adolphe Valentin|Change-speed transmission|
    US2466318A|1945-08-22|1949-04-05|Ford Motor Co|Automatic transmission and overdrive|
    US2599801A|1949-06-11|1952-06-10|Borg Warner|Double countershaft transmission|
    US2612787A|1950-07-22|1952-10-07|Borg Warner|Double countershaft transmission|
    GB717450A|1951-09-01|1954-10-27|Dietrich & Cie De|Improvements in change-speed mechanism|
    GB795260A|1955-09-29|1958-05-21|Brown David & Sons Ltd|An improvement in or relating to variable-speed gearboxes|
    DE1530994B2|1967-03-03|1974-07-25|Robert Bosch Gmbh, 7000 Stuttgart|Spur gear transmission with four forward gears, especially for motor vehicles|
    DE2445241C2|1974-09-21|1982-11-04|Fichtel & Sachs Ag, 8720 Schweinfurt|Manual transmissions for automobiles|
    US4033200A|1975-04-24|1977-07-05|Ford Motor Company|Five speed overdrive transmission|
    FR2396213B1|1977-06-30|1982-06-25|Berliet Automobiles|
    SU680923A1|1977-12-08|1979-08-25|Московский Трижды Ордена Ленина,Ордена Октябрьской Революции И Ордена Трудового Красного Знамени Автомобильный Завод Им.А.И.Лихачева|Three-stage transmission for a vehicle|
    JPS54153957A|1978-05-26|1979-12-04|Daikin Mfg Co Ltd|Transmission|
    JPS54153958A|1978-05-26|1979-12-04|Daikin Mfg Co Ltd|Transmission|
    AU6430980A|1979-11-26|1981-06-04|Automotive Products Ltd.|Dual clutch transmission|
    EP0060624A3|1981-03-10|1983-09-14|Automotive Products Public Limited Company|Rotary transmission|GB8406969D0|1984-03-16|1984-04-18|Automotive Prod Plc|Change speed transmission|
    USRE33336E|1984-03-16|1990-09-18|Automotive Products Plc|Change speed transmission|
    GB8411896D0|1984-05-10|1984-06-13|Automotive Prod Plc|Transmission|
    GB2159216B|1984-05-25|1988-08-10|Automotive Products Plc|Transmission control system|
    US4597304A|1984-10-09|1986-07-01|General Motors Corporation|Multi-speed power transmission|
    US4676115A|1985-05-13|1987-06-30|Eaton Corporation|Semi-automatic transmission|
    DE3530017A1|1985-08-22|1987-02-26|Porsche Ag|GEARBOX TRANSMISSION FOR A MOTOR VEHICLE|
    FR2605377B2|1985-10-25|1993-11-26|Renault|MECHANICAL GEARBOX WITH A PRIMARY SHAFT AND TWO SECONDARY SHAFTS|
    DE3543269C2|1985-12-06|1990-02-01|J.M. Voith Gmbh, 7920 Heidenheim, De|
    JPS6455452A|1987-08-21|1989-03-02|Toyota Motor Corp|Manual transmission for vehicle|
    JPH01303340A|1988-05-31|1989-12-07|Fuji Heavy Ind Ltd|Automatic transmission for vertical type engine|
    US5009118A|1990-03-30|1991-04-23|General Motors Corporation|Power transmission with parallel identical countershafts|
    US5385064A|1992-10-23|1995-01-31|Borg-Warner Automotive, Inc.|Dual clutch countershaft automatic transmission|
    US5390560A|1993-02-09|1995-02-21|General Motors Corporation|Countershafts power transmission|
    US6450309B1|1999-04-23|2002-09-17|Kanzaki Kokyukoki Mfg. Co., Ltd.|Transmission system structure of vehicle|
    JP2002130396A|2000-10-30|2002-05-09|Aisin Seiki Co Ltd|Variable speed gear|
    KR100569141B1|2003-12-10|2006-04-07|현대자동차주식회사|Double clutch transmission|
    DE102004056936B4|2004-11-23|2011-02-03|Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg|Variable speed gearbox for a motor vehicle|
    FR2882417B1|2005-02-24|2008-08-29|Renault Sas|MOUNTING BEARINGS ON CONCENTRIC TREES|
    FR2885980B1|2005-05-18|2007-08-10|Renault Sas|GEARBOX WITH SIDE OIL PUMP|
    JP4380660B2|2006-05-30|2009-12-09|三菱自動車工業株式会社|Double clutch transmission|
    DE102008000822B4|2008-03-26|2020-01-09|Zf Friedrichshafen Ag|Device for reducing rattling noises in step gears|
    DE102008000821B4|2008-03-26|2017-01-26|Zf Friedrichshafen Ag|step transmission|
    US8220352B2|2009-04-23|2012-07-17|GM Global Technology Operations LLC|Dual clutch transmission|
    US8528431B2|2009-04-28|2013-09-10|GM Global Technology Operations LLC|Dual clutch transmission|
    FR2956175A1|2010-02-05|2011-08-12|Renault Sas|Automated dual clutch gearbox, has hollow shaft guided by bearing supported by clutch casing, where shaft extends until another bearing supported by clutch mechanism housing in part opposite to clutch casing|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    GB8128374|1981-09-19|
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