• 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:
    Drive mechanism for a four-wheel-drive tractor, comprising a pair of input shafts in double tube construction with one fitted to nest in the other, main gearing shaft assembly, differential gearing, front-wheel-drive-shaft assembly, gearing wheels provided in both frontal and rear portions of the front-wheel-drive-shaft assembly, a power-take-off shaft and a drive shaft-assembly. Driving power taken out from the gearing wheel provided in front portion of the front-wheel-drive-shaft assembly is transmitted to front wheels via a transmission shaft with a mating gear, disposed at an underbelly portion of the tractor. The drive assembly is provided above the differential gearing. With this construction, the front-wheel-drive-shaft can be made short, sufficient empty space height can be provided in the underbelly portion of the tractor, and the transmission housing can be minimized.
    公开号:SU1233795A3
    申请号:SU772524799
    申请日:1977-09-28
    公开日:1986-05-23
    发明作者:Икегами Сейичи
    申请人:Кубота Лтд (Фирма)；
    IPC主号:
    专利说明:

    it is freely mounted on the additional drive shaft and is engaged in engagement with the gear of the second intermediate shaft and with the gear of the output shaft, wired on the movable coupling half of the output shaft with the second intermediate shaft.
    The invention relates to a tractor machinery industry, in particular to a tractor powertrain with four drive wheels, in which the front ones are steerable.
    The purpose of the invention is to expand the kinematic ranges and reduce the vertical size of the transmission to provide increased ground clearance on the tractor.
    FIG. shows a tractor with wheels removed from the left side, side view; in fig. 2 - kinematic diagram of a tractor power transmission with four driving wheels; Fig. 3 is the front structure of a power train; Fig. 4 illustrates the structure of an intermediate part of a power train; Fig. 5 illustrates the rear structure of a power train.
    The tractor with four drive wheels contains the engine 1 and the crankcase 2 of the gearbox. The controlled front wheel is connected to the front wheel axle 4 and the front differential housing 5, the rear wheel 6 is connected to the rear wheel axle 7. There is a power take-off shaft 8 for operating on -Any tractor mounted implement, controlled by a lifting 9 for raising and lowering the tractor attachment. In addition, the tractor contains the driver's seat 10, pz left wheel 11, fuel tank 12, battery 13 and radiator 14,
    The tractor has two telescopic shaft designs: an inner 15 and an outer 16, which are longitudinally positioned to the tractor in the upper part of the crankcase 2 of the gearbox. At the same time, the outer shaft 16 operates as the primary shaft of the gearbox to ensure the movement of the tractor, and the inner shaft 15 - for from3. The power transmission in accordance with claim 1, i t is l and h and with the fact that on the movable coupling half of the coupling of the input shaft of the reducer with the internal input shaft is placed a gear for engagement with the gear of the output shaft,
    bora power. At the front end of the primary shafts 15 and 16, respectively, are installed independently of each other from the engine shaft 17
    disc friction clutches 18 and 19. The complete gear shaft assembly, consisting of the first 20, second 21 and third 22 shafts, which are coaxially between themselves and along and
    below the primary shafts 15 and 16, which allows them to rotate relative to each other. Three gears 23-25 are loosely seated on the first intermediate shaft 20, which are located in
    constant gearing with gears 26-28, respectively, with all three last gears having a splined connection with the outer shaft 6, and a gear wheel 29 engaging with the gear 30 of the gear change, also having a splined connection with the outer shaft 16 and the synchronizing gears 31 and 32 are located between the gears 23
    and 24 and between gears 25 and 29, respectively, ensuring that the forward speed of rotation of the first shaft 20 is switched in four stages (change in forward speed) beyond
    synchronization gears selective control account 31 and / or 32.
    In addition, on the first intermediate shaft 20, a gear wheel 33 is fixedly mounted, which is in constant friction with the reverse gear 34, which is rotatably mounted on a separate shaft, which allows the rotation speed to be changed in the reverse gear of the first intermediate shaft 20 reverse gear) due to the introduction into gearing gear gear with the stubble 34 of the rear axle. In addition, gear 35 is small
    the diameter is connected at the splines to the rear end of the first intermediate shaft 20, and the larger gear 36 is freely fitted onto the front end of the second intermediate shaft 21 and synchronized gear 37 is placed between the two gears 35 and 36.
    The outer ring of the rolling bearing, mounted at the rear end of the outer intermediate shaft 16, serves as a support for two gears, made in the form of one piece, gears 38 and 39, which are in constant engagement with the specified gears 25 and 36, respectively, which ensures obtaining an auxiliary speed switch mechanism for transmitting torque from the first intermediate shaft 20 to the second intermediate shaft 21 with two-step switching of higher and lower speeds due to the use of synchronization gears 37.
    In addition, the gear shaft 40 of the transmission shaft can slide between the position where it connects the rear end of the second intermediate shaft 21 and the front end of the third intermediate shaft 22, and another position where it is located only on the third intermediate shaft 22 without being connected to the rear end of the second intermediate shaft 21, Vrash; the center of the third intermediate shaft 22 is transmitted through bevel gear 41 to differential 42 for transmitting torque to the rear wheels 6,
    The front wheel drive assembly 43 includes first 44 and second 45 drive shafts, which are aligned in the opposite direction to each other, ensuring relatively free rotation along and below the intermediate shafts 20, 21 and 22 of the main transmission shaft assembly, a coupling 46, which serves to connect the opposite ends of the two drive shafts 44 and 45. A gear 47 is fixed at the rear end of the second drive shaft 45, which is in constant engagement with the gear 48 fixed on the third intermediate shaft 22 of the main gear datochnogo shaft assembly, and the front end of the first drive shaft 44 is fixed gears 49, transmitting the torque to the front wheels 3.
    33795
    Thus, the power transmitted by gear 49 through mating gear 50 and secondary shaft 51 is transmitted to the casing of the front differential 5, which ensures the rotation of the front wheels of the synchropro with the rotation of the rear wheels 6, and the transmission only to the rear wheels 6 may occur when the coupling is unlocked 4 6.
    In the rear or second drive shaft 45 of the drive shaft assembly, two gears 52 and 53, which are made in one piece, are freely seated, while gear 52 is in constant contact with the fixed drive gear 54 mounted on the second intermediate shaft 21 of the main gearbox shaft assembly, and leading
    The 20 gear 53 is selectively engaged with the gear 40, when the gear 40 is properly slidably mixed to ensure such engagement with the drive gear.
    25 gear, which allows the transfer of the maximum reduction in rotational speed from the second intermediate shaft 2 to the rear or third intermediate shaft 22 when
    3Q limit gear reduction.
    Thus, the second drive assembly 45 of the front-wheel drive assembly is also used as a support for the gear 52 and 53 of the lower gears, and this is 5
    0
    Considers the possibility of obtaining a compact powertrain design. I
    A continuation of the rear end of the inner input shaft 15 is the power take-off shaft of the drive shaft 55, which is coaxial with the shaft 15 to ensure free relative rotation with it, with the opposite ends of the shafts 15 and 46 being interconnected using the gear 56. Two gears 57 and 58 are mounted on the rear of the power shaft of the drive shaft 55 and are located
    is in constant engagement with mating gears 59 and 60, respectively, which are loosely seated on the power take-off shaft 8, with synchronizing gear 61 between the two gears 59 and 60 55 to provide a two-stage shift of the lowered and increased speeds of the power take-off shaft 8 at
    given direction using the synchronizing gear 61.
    It is also easy to slide the gear 56 to shut down the direct connection between the power shaft of the drive shaft 55 with the input shaft 15 and for connecting the gear shift 56 with the gear 48. mounted on the third intermediate shaft 22, which actuates the shaft 8 power take-offs, respectively, of the operating speed and direction of travel of the tractor. With this design
    Sch 73
    the gearshift gear Zb performs two functions, namely: coupling and uncoupling the input shaft
    5 15 with the power shaft of the drive shaft 55, as well as the clutch and disengagement of the power shaft of the drive shaft 55 with the rear or third intermediate shaft 22 of the main transfer shaft assembly, which provides a compact power transmission design compared to the design, which a separate gear is used to perform the specified function.
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    Editor A. Shandor
    Compiled by S. Belousko Tehred I. Popovich Corrector Es Sirokhman
    Order 2786/59 Circulation 647 Subscription
    VNIIPI USSR State Committee
    for inventions and discoveries 113035, Moscow, Zh-35, Rautska nab., d. 4/5
    Production and printing company tsig.Uzhhorod, Proektna str., 4
    权利要求:
    Claims (3)
    [1]
    1 . TRACTOR POWER TRANSFER
    WITH FOUR DRIVING WHEELS, comprising, independently from the engine, located in the upper part of the crankcase in the upper part in the longitudinal direction of the tractor, the outer and inner telescopic input shafts located in it in the form of a double-walled pipe, gears are fixed to the outer shaft and the inner shaft is connected via a controlled coupling to . the input shaft of the gearbox of the power take-off shaft in the form of a gear train of constant engagement located in the differential zone of the rear axle, located — below the input shafts — the first intermediate shaft with freely mounted gears and couplings for connecting the gears to this shaft, connected through the coupling with the second located coaxially with it an intermediate shaft with gears, while the gear half-couplings of this coupling are connected to each other through a gear block mounted parallel to the input shaft, an output shaft with gears connected to one side with the differential back his bridge% and the other connected cinematically with the second intermediate eelom located longitudinally tractor drive shaft front axle differential is located parallel to one of the intermediate shafts and the associated cinematically through a gear wheel, otlichayuschayas I that, in order to increase the kinematic ranges and reduce the vertical size of the gear to provide increased ground clearance on the tractor, the power take-off shaft gearbox is additionally equipped with a gear series of constant gearing and a clutch for coupling freely mounted gears with a power take-off shaft, a block gear is freely mounted on the internal input shaft, the output shaft is aligned with the second intermediate shaft and connected through the coupling, the front axle differential drive shaft is connected to the first the intermediate shaft through the gear (installed in the housing on a separate drive shaft, and with the output shaft through an additional drive shaft with gears engaged with the gears of the output shaft, while the drive the additional shaft and the pinion shaft are mounted coaxially and connected through a controlled coupler located on the outer surface of the opposite ends of said drive shafts.
    [2]
    2. The power transmission according to claim 1, characterized in that it is provided with an additional block gear M > SU., ”1233795 AZ of it, freely mounted on an additional drive shaft and engaged with the gear of the second intermediate shaft and with the gear output shaft, made on a movable coupling half of the output shaft with the second intermediate shaft.
    I233795
    [3]
    3. Power transmission according to π, 1; characterized in that on the movable coupling half of the coupling of the input shaft of the gearbox with the internal input shaft, a gear is placed for engagement with the gear of the output shaft, ί
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1233795A3|1986-05-23|Power transmission of four-wheel drive tractor
    EP0072990B1|1986-04-09|Four-wheel vehicle drive system
    US4476953A|1984-10-16|Four-wheel vehicle drive system
    US4431079A|1984-02-14|Four-wheel vehicle drive system
    US4428452A|1984-01-31|Four-wheel-drive system for vehicle
    US4441575A|1984-04-10|Four-wheel vehicle drive system
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    US6113512A|2000-09-05|Full-time transfer case with integrated planetary gear assembly and synchronized range shift mechanism
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    US4878399A|1989-11-07|Planetary sub-transmission
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    US4399717A|1983-08-23|Change-speed transmission for wheeled vehicles
    US5380255A|1995-01-10|Transfer case for part time front wheel drive in a four wheel drive motor vehicle
    GB2075933A|1981-11-25|Driving system for four-wheel driven vehicle
    JPH06241288A|1994-08-30|Gear transmission
    CA1083492A|1980-08-12|Tractor
    US4233857A|1980-11-18|Multiple speed transmission with auxiliary transfer drive
    EP1361101B1|2007-01-24|A compact four-wheel drive system for motor vehicles
    CN210344178U|2020-04-17|Power transmission system and tractor
    CN214465905U|2021-10-22|Gearbox and agricultural machine
    CN212313281U|2021-01-08|Three-box type tractor transmission system and tractor
    同族专利:
    公开号 | 公开日
    FR2393986B1|1981-07-31|
    TR20557A|1981-11-13|
    AU2854977A|1979-03-15|
    CA1071894A|1980-02-19|
    PH15452A|1983-01-18|
    PT67082A|1977-10-01|
    CH618647A5|1980-08-15|
    US4208923A|1980-06-24|
    PT67082B|1979-02-22|
    FR2393986A1|1979-01-05|
    BE858151A|1977-12-16|
    NZ185115A|1980-04-28|
    GB1555436A|1979-11-07|
    AU502102B2|1979-07-12|
    NL7709490A|1978-12-13|
    JPS543732A|1979-01-12|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    DE2405023C2|1974-02-02|1982-07-08|Klöckner-Humboldt-Deutz AG, 5000 Köln|Gear change transmissions in group design for motor vehicles, in particular for motor vehicles that can be used in agriculture and / or construction|
    US4116090A|1974-03-02|1978-09-26|Klockner-Humboldt-Deutz Aktiengesellschaft|Change gear transmission in group arrangement, especially for motor vehicles for use in agriculture and in the construction field|
    DE2513615C2|1975-03-27|1983-09-22|Klöckner-Humboldt-Deutz AG, 5000 Köln|Gear change gearboxes in group design, in particular for motor vehicles that can be used in agriculture and / or construction|JPS5447230A|1977-09-20|1979-04-13|Kubota Ltd|Double clutch device for agricultural tractor|
    FR2447824B1|1979-02-01|1982-08-20|Citroen Sa|
    US4318305A|1979-04-04|1982-03-09|Deere & Company|Synchronized transmission|
    JPS569921U|1979-07-02|1981-01-28|
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    JPS6361210B2|1980-04-25|1988-11-28|
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    GB2092533B|1980-12-24|1984-12-19|Fuji Heavy Ind Ltd|Two-four wheel drive mechanism|
    JPS629059B2|1981-01-09|1987-02-26|Nissan Motor|
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    JPS629057B2|1981-05-11|1987-02-26|Nissan Motor|
    DE3120684A1|1981-05-23|1982-12-09|Xaver Fendt & Co, 8952 Marktoberdorf|Auxiliary drive on commercial vehicles|
    DE3125612A1|1981-06-30|1983-01-13|Volkswagenwerk Ag, 3180 Wolfsburg|Manual shift transmission for a motor vehicle with permanent all-wheel drive|
    JPS6232098Y2|1981-09-11|1987-08-17|
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    WO2010002371A1|2008-07-03|2010-01-07|Deere & Company|Compact creeper gear arrangement for a transmission|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    JP6909077A|JPS543732A|1977-06-11|1977-06-11|Transmission structure for four-wheel drive tractor|
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