• 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:
    An infinitely variable cone pulley transmission has a first and a second pulley mounted on driving and driven shafts and connected by an endless belt. Each pulley is formed of first and second pulley discs. A hydraulic device sets and maintains each first pulley by hydraulic pressure in an axial position corresponding to a desired transmission ratio between the driving and the driven shafts. A torque sensor is mounted adjacent a second pulley disc for receiving a torque. The torque sensor has a pressing device mounted for axial displacement as a function of the torque and a valve arranged for displacement by the pressing device for varying the hydraulic pressure on the first pulley discs. The pressing device has a first ring torque-transmittingly and axially immovably mounted in the vicinity of the second pulley disc, a second ring relatively rotatably and axially slidably mounted between the second pulley disc and the first ring and forming a movable part of the valve. A torque transmitting device transmits torque from one ring to the other. The torque transmitting device comprises a cooperating camming arrangement carried by the two rings for axially displacing the second ring with respect to the first ring as a function of the torque applied to the second ring.
    公开号:SU1722246A3
    申请号:SU813306787
    申请日:1981-07-01
    公开日:1992-03-23
    发明作者:Карл Штойер Херберт
    申请人:П.И.Ф. Антриб Вернер Раймерс Гмбх Унд.Ко., Кг (Фирма)；
    IPC主号:
    专利说明:

    This invention relates to mechanical engineering, namely to continuously variable friction gears.
    The purpose of the invention is to provide a simple and compact design by reducing the axial dimensions and the number of parts of the torque sensor.
    Fig. 1 shows a schematic arrangement of a hydraulically adjustable conic friction gear; Figures 2-6 are versions of a torque sensor.
    The infinitely adjustable conic friction transmission (Fig. 1) contains two conical disks 1, 2 and 3, 4, mounted respectively on the drive 5 and the driven 6 shafts. Conical discs 1 and 3 are fixed on the shafts. The conical discs 2 and A are axially movable. The transfer means 7 covers the tapered disks 1.2 and 3.4. The conical disks 2 and 4 form cylinder-piston units with pistons 8 and 9 fixed on the shafts and cylinders 10 and 11 enclosing them, prismatic keys 12 and 13 fixed on rotation on the corresponding shafts 5 and 6. The cylinder-piston units have cylindrical cavities 14 and 15.
    A torque sensor 16 is mounted on the guide shaft 5, which includes pressure cams 17 and 18 and rolling elements in the form of balls 19. The pressure cams 17 are placed on the main ring 20 fixed on the shaft 5, held by an axle 21 and axially supported by the shaft 5 key 22. The pressure cams 18 are placed on the valve ring 23 located between the main ring 20 and the fixed conical disk 1 on the drive shaft 5 for rotation and axial movement and have a radial internal seal 24 on the shaft 5. The valve ring 23 with the side turned to the fixed disk 1, together with the side of the fixed disk 1, forms the cavity 25 of the torque sensor 16 communicated with the axial 26 and radial 27 shaft channels for supplying the working medium, which is outputted from the sensor 16 by the throttle to the outside.
    To ensure the input and output of torque, there is a bell-shaped rotor 28 mounted on the shaft, having a tooth 29, and on the outer surface of the valve ring 23 there is a tooth 30 interacting with the teeth 29 of the rotor 28.
    In addition, the continuously variable bevel-friction transmission has a working medium source 31 connected to a four-sided slide valve 32, which
    pipes 33 and 34 are connected with cylindrical cavities 14 and 15 of a cylinder-piston unit, and pipe 35 with a torque sensor 16. Shiber 36
    the spool 32 is mechanically connected with the setting lever 37 and the rocker 38, which with its free end enters the circumferential groove 39 of the conical disk 4 and, thus, directly reads the position of the gear ratio of the transmission.
    The cavity 25 of the sensor 16 may be formed by an annular recess 40 with scrape openings 41 for the working medium made in the fixed disk 1 and a valve 5 with the outer ring 23, the collar 42 of which provided on its end surface enters the recess 40 and forms with an annular groove 43 and through holes 41 choke for the working medium.
    0 The throttle for the working medium can be formed by the collar 44 of the valve ring 23 and the annular groove 45 connected to the hole 46 of the shaft 5 (Fig. 2). This embodiment allows the throttle to produce
    5 lubricated oil pressure cams 17 and 18 and teeth 29 and 30.
    The working medium can enter the cavity 25 through the radial through hole 47 of the shaft 5 and the through hole 48 s.
    0 by the annular groove 49 of the valve ring 23, and can flow out of the cavity 25 through the radial channel 27 with the annular groove 50 on the shaft 5 by means of the collar 44 (FIG. 3). In this case, the axial channel 26 is separated by a plug.
    5 51.
    The cavity of the sensor 16 may be formed by an annular recess made on the end surface of the valve ring 23 and the end surface of the fixed
    0 disk 1, and the remaining part 52 of the end surface of the valve ring 23 and the interacting end surface 53 of the fixed disk 1 form a choke for the working medium (Figures 4 and 5).
    5 FIG. 5 shows how the working medium through the through hole 54 in the fixed disk 1 can flow into the cavity 25. Throttling, as in FIG. 4. This form of execution is the most economical and convenient
    0 as it has no seals and additional parts.
    Figure 6 shows an embodiment of the rotor 28 in the form of a shaft with a gear wheel mounted parallel to the shaft 5.
    5 Transmission works as follows.
    The working medium supplied by the source 31 enters the spool 32, which feeds it through pipelines 33 and 34 to the driving and driven sides of the transmission.
    According to the well-known regularity for conical friction gears at steady-state, the working pressure of the working medium on the drive shaft side is higher than on the driven side, therefore, the gate 36 occupies a position shifted to the right from the middle position so that more working fluid flows from source 31 more pressure on the driving side of the gear than on the slave.
    The working medium 35 flowing out of the spool 32 has a hydraulic pressure equal to the pressure on the side of the driven shaft.
    If the transmission receives an increased load from the torque, then the sensor
    five
    When the torque 16 is reached, the valve ring 23 and the main ring 20 tend to move away from each other and the ring 23 shifts to the right, shutting off the working medium flow, as a result of which the hydraulic pressure on the side of the driven shaft rises.
    Increasing the pressure of the working medium causes the disc 4 to move to the right, and the transfer means 7 tends to take less on the drive disks 1 and 2, and a larger radius of the circumference on the driven disks 3 and 4. From the torque sensor 16, the working medium flows freely into a housing (not shown) and from there to the receiver, where it can again be used.
    sixteen
    28
    Phi $ .1
    from u Cloud
    SHSHZH
    26
    22 1№ 18 45 27 Fi 8.2

    y h h: GgTs-chh§
    -
    26
    Tl
    U ill 51 48 Fts3
    DCHU X X HHHUUCH T1
    /
    26
    s
    52
    L
    23 2b FieL
    FIG. five
    78
    L
    FIG. 6
    权利要求:
    Claims (4)
    [1]
    1. CONTINUOUS CONTROLLED CONIC FRICTIONAL TRANSMISSION, containing two conical disks placed on the driving and driven shafts, one of which is mounted with the possibility of movement in the axial direction, the other is fixedly mounted on the shaft, the transmission means covering the disks, a tetrahedral spool, an adjusting lever connecting the latter with one of the axially displaced disks mounted on at least one of the shafts of the torque sensor, including pushing placed opposite each other cams, one of which is fixedly connected to the ring fixed on the drive shaft, and obkatnye elements located between the pressure cams, the sensor cavity, limited by the side of the fixed disk and communicated with axial and radial channels of the shafts for supplying the working medium and having a throttle, cylinder piston an assembly, the cylinder of which is rigidly connected to the axially movable disk, and its piston is rigidly connected to the shaft, and t
    the working medium circulating through the axial and radial channels is distinguished by the fact that, in order to ensure a simple and compact design, the torque sensor is equipped with a valve ring located between the main ring and the stationary conical disk, mounted on the shaft for rotation and axial moving, bearing the other side of the cams and the forming side turned to the fixed disk, together with the side of the fixed disk is the sensor cavity, the working medium from which is output by the throttle.
    [2]
    2. The transmission according to claim 1, with the exception that in order to provide input and output of the torque, the transmission is equipped with a rotor having teeth, and teeth interacting with the teeth are made on the outer surface of the valve ring rotor.
    [3]
    3. Transmission according to claims 1 and 2, with the exception that the sensor cavity is formed by an annular recess with through holes. holes for the working medium, made in a fixed disk, and a valve ring, the flange of which, provided on its end surface, enters the recess and • forms a throttle for the working medium with through holes.
    [4]
    4. The transmission according to claims 1 ^. Characterized in that the sensor cavity is formed by an annular groove made on the end surfaces of the valve ring and the fixed disk, and the remaining part ί the end surface of the valve ring and the end surface of the fixed disk interacting with it form a throttle for the working medium .
    1722246 AZ
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1722246A3|1992-03-23|Infinitely variable tapering friction gearing
    US4467669A|1984-08-28|Working fluid distributing system for a belt drive continuously-variable speed automatic transmission
    JP3097439B2|2000-10-10|Oil passage structure for continuously variable transmission
    US3744606A|1973-07-10|Dual hydraulic or pneumatic coupling
    GB2092246A|1982-08-11|Continuously variable ratio transmissions
    JP2006010080A|2006-01-12|Start clutch and fixed disc assembly having torque detector
    US4287781A|1981-09-08|Transmission with double friction clutch
    US4549447A|1985-10-29|Belt drive continuously-variable speed automatic transmission
    US4608032A|1986-08-26|Infinitely variable belt drive with low friction seals for the primary and secondary sheaves
    US5468192A|1995-11-21|Adjustable pulley in a continuously variable transmission
    EP0004130B1|1982-06-30|Continuously variable transmission mechanism
    EP0305110A2|1989-03-01|Transmission systems
    US1859502A|1932-05-24|Speed change gear
    US4763765A|1988-08-16|Cone clutch transmission
    GB2033029A|1980-05-14|Variable-ratio gearing
    KR101713468B1|2017-03-07|Motive-power transmission device
    US4489621A|1984-12-25|Dual wet output clutch for power selection in a continuously variable transmission
    RU2313020C2|2007-12-20|Planetary gearbox central support member
    US3024885A|1962-03-13|Clutch
    US3628388A|1971-12-21|Friction-type variable-speed transmissions
    US20190293129A1|2019-09-26|Frictional coupling device of vehicular power transmitting system
    JP2545996B2|1996-10-23|Lubricating method and apparatus for belt type continuously variable transmission
    GB839844A|1960-06-29|Variable speed friction drive
    JPS6179823A|1986-04-23|Drive device for engine accessory
    JPH06221400A|1994-08-09|Advance/retreat changeover device of continuously variable transmission
    同族专利:
    公开号 | 公开日
    JPS6015814B2|1985-04-22|
    ATA233781A|1992-09-15|
    DE3028490C2|1983-01-13|
    NL185865B|1990-03-01|
    GB2080892B|1984-05-16|
    IT1142577B|1986-10-08|
    BR8103998A|1982-03-09|
    SE443032B|1986-02-10|
    US4439170A|1984-03-27|
    IN156087B|1985-05-11|
    GB2080892A|1982-02-10|
    NL185865C|1990-08-01|
    IT8148814D0|1981-07-02|
    JPS5751047A|1982-03-25|
    ZA812609B|1982-06-30|
    FR2493452A1|1982-05-07|
    CH654386A5|1986-02-14|
    FR2493452B1|1987-04-30|
    SE8103064L|1982-01-27|
    DE3028490A1|1982-06-09|
    DD203107A5|1983-10-12|
    AT396008B|1993-05-25|
    NL8102195A|1982-02-16|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    NL162183C|1976-02-09|1980-04-15|Doornes Transmissie Bv|INFLATABLE VARIABLE DRIVE.|
    DE2828347C2|1978-06-28|1982-10-21|P.I.V. Antrieb Werner Reimers GmbH & Co KG, 6380 Bad Homburg|Friction gears|
    DE2846580C2|1978-10-26|1982-12-09|P.I.V. Antrieb Werner Reimers GmbH & Co KG, 6380 Bad Homburg|Infinitely adjustable conical pulley gear|JPH0211778B2|1980-09-04|1990-03-15|Aisin Aw Co|
    US4541821A|1982-11-27|1985-09-17|Aisin-Warner Limited|V-belt type stepless transmission|
    DE3325523C2|1983-07-15|1985-10-03|P.I.V. Antrieb Werner Reimers GmbH & Co KG, 6380 Bad Homburg|Infinitely adjustable conical pulley belt drive|
    DE3403704C1|1984-02-03|1985-09-19|Audi AG, 8070 Ingolstadt|Continuously variable cone pulley transmission|
    JPS6110149A|1984-06-23|1986-01-17|Daihatsu Motor Co Ltd|Stepless v-belt speed changer|
    EP0194821B1|1985-03-12|1989-07-05|Honda Giken Kogyo Kabushiki Kaisha|Infinitely variable transmission|
    DE3538884C2|1985-11-02|1989-05-03|Ford-Werke Ag, 5000 Koeln, De|
    US4731044A|1985-12-18|1988-03-15|Borg-Warner Automotive, Inc.|Tension sensor and control arrangement for a continuously variable transmission|
    DE3872035T2|1987-04-24|1992-12-03|Honda Motor Co Ltd|CONTINUOUSLY ADJUSTABLE BELT GEARBOX FOR MOTOR VEHICLES.|
    JP2790627B2|1987-04-30|1998-08-27|本田技研工業株式会社|Control method and control device for belt continuously variable transmission|
    DE3817532C1|1988-05-24|1989-06-01|P.I.V. Antrieb Werner Reimers Gmbh & Co Kg, 6380 Bad Homburg, De|
    DE3917466C1|1989-05-30|1990-09-20|P.I.V. Antrieb Werner Reimers Gmbh & Co Kg, 6380 Bad Homburg, De|
    DE3938539A1|1989-11-21|1991-06-06|Ford Werke Ag|CONTROL SYSTEM FOR A CONTINUOUSLY ADJUSTABLE CONE DISC BELT GEARBOX|
    JPH0434548U|1990-07-19|1992-03-23|
    DE4128457C1|1991-08-28|1992-12-24|P.I.V. Antrieb Werner Reimers Gmbh & Co Kg, 6380 Bad Homburg, De|
    IN189939B|1993-12-20|2003-05-17|Torotrak Dev Ltd|
    KR0164937B1|1994-06-27|1998-12-15|쯔지 요시후미|Pulley device for continuously variable transmission|
    JP3441873B2|1996-02-15|2003-09-02|富士重工業株式会社|Pulley structure of belt-type continuously variable transmission and method of coupling movable sheave and hydraulic actuator member of the pulley|
    DE19909348A1|1998-03-19|1999-09-23|Luk Getriebe Systeme Gmbh|Torque sensor providing controllable torque on a control element over the whole torque range|
    DE19946336B4|1998-10-02|2013-04-25|Schaeffler Technologies AG & Co. KG|Continuously adjustable belt drive|
    DE19951950B4|1998-11-03|2013-02-28|Schaeffler Technologies AG & Co. KG|transmission|
    DE10331470A1|2003-07-11|2005-02-24|Piv Drives Gmbh|Stepless adjustable bevel gear with torque sensor|
    EP1655511B1|2004-11-08|2013-01-09|JATCO Ltd|Double piston and belt type continuously variable transmission|
    NL1029042C2|2005-05-13|2006-11-14|Gear Chain Ind Bv|Device for stretching the links of a transmission chain beyond the elastic limit.|
    NL1039925C2|2012-12-03|2014-06-04|Gear Chain Ind Bv|SYSTEM FOR ARRANGING A CONTINUALLY VARIABLE TRANSMISSION.|
    US10024404B2|2014-03-20|2018-07-17|Changzhou Dongfeng Continuously Variable Transmission Co., Ltd.|Continuously variable transmission with cone discs|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE3028490A|DE3028490C2|1980-07-26|1980-07-26|Infinitely adjustable conical pulley gear|
    [返回顶部]