• 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 resonance torsional vibration damper, especially a multi-member vibration damper which includes a primary member including one, preferably a plurality of, fixedly interconnected parts and arranged on a shaft or crankshaft. The damper furthermore includes one or more secondary members arranged adjacent to each other in axial direction but spaced from each other and by means of elastic members connected to the primary member. In the primary part there are provided cooling air openings which lead outwardly and into the region of the secondary members. At the free end face or end faces of one or more secondary members there are provided preferably radially outwardly leading cooling fins.
    公开号:SU880261A3
    申请号:SU782646749
    申请日:1978-08-02
    公开日:1981-11-07
    发明作者:Бауэр Фридрих
    申请人:Машиненфабрик Аугсбург-Нюрнберг Аг (Фирма)；
    IPC主号:
    专利说明:

    The invention relates to devices for damping 'vibrations and can be used in the field of general engineering for damping torsional vibrations of the shafts of piston engines internally. 5 early combustion.
    A damper of resonant torsional vibration of shafts is known, made in the form of a figured disk rigidly mounted on the shaft end and connected to it through a flywheel rubber layer [1].
    The disadvantage of the damper is that as a result of deformation of the rubber and due to heat removal, for example, from is a hot crankshaft, high heating temperatures arise in the damper, which exceed the heating temperature that is acceptable for rubber compounds currently in use, 20 therefore the rubber layers harden, cracks form in them and, in the end, the damper loses its effectiveness, and its service life is significantly reduced.
    In terms of technical nature and the achieved result, the closest to the proposed one is the damper of resonant torsional vibration of the shafts, containing a rubber-metal element mounted on the shaft end and made in the form of disks, flywheels that are connected to the shaft, and rubber layers connecting the disks and flywheels, some of which have radially located cooling channels [2].
    The disadvantage of the damper is its complexity in manufacturing and, in addition, it does not provide effective cooling of the damper, due to the chosen design, and therefore the service life of the damper is small.
    The aim of the invention is to increase the life of the damper.
    This goal is achieved by the fact that in the damper, part of the rubber layers at 0 is vulcanized to the end surfaces of the flywheels and made in the form of profile ribs forming cooling channels with the surfaces of the flywheel or the disk and the flywheel, part of the discs are cups with flanges whose bottoms are perpendicular to the axis of the damper and in their walls there are holes uniformly arranged around the circumference associated with cooling channels, holes in the disks are of any shape, cooling fins can be bent depending on t direction of rotation of the shaft, and in cross section they are. have a rectangular, trapezoidal or triangular shape.
    In FIG. 1 is a cross-sectional view of a double damper; in FIG. 2 ι and 3 - options for the location of the cooling fins; in FIG. 4, 5, 6 are cross-sectional shapes of the ribs J in FIG. 7 “cross section of a triple damper.
    The damper comprises a rubber-metallic member 2 cal 1 · mounted on the end of the shaft 2 and formed as a drive shaft linkable with 3 *), 5, 6 and flywheel 7, 8, 9. Flywheels and disks interconnected by rubber layers 2 10, 11, 12, 13, 14, 15. Part of the rubber layers 11, 13 '15 start vulcanised to the flywheel end faces 7, 8 and 9 and is formed as a profiled rib 16, forming a surface po- e flywheel 8, 9, or disks and flywheel 7 cooling channels. Part of the disks, for example, 3, and 5 ^ _ are cups with flanges, the bottoms of which are perpendicular to the axis of the damper, and in case of using 3 , for example, a triple damper, disks 6 can be made flat. In the walls of the disks 3, ^, 5, holes 17, 18, 19 / uniformly spaced around the circumference are made * connected to the cooling channels, the holes can be of any shape, and the profile ribs 16 can be bent to one or the other side, depending on rotation Ba 4 la 2. rubber-metal element 1 is fixed to the screw shaft 20, and in the case of a triple damper between the rubber-metal elements are installed bushing 21, 22. 5
    Rubber-metal elements do not touch each other, and disks and flywheels are made of steel, the latter are also made of cast iron.
    The damper works as follows.
    Torsional vibrations from shaft 2 are transmitted to the rubber-metal element 1, through disks 3, 4, 5 and then through rubber layers 10, 12, 14 to flywheels 7, 8, 9, which play the role of additional mass, as in a dynamic vibration damper. In addition, torsional vibration energy is consumed. deformation of the rubber, which consequently warms up. When the shaft rotates, air is sucked into the holes 17, 18, 19 and, as in the radial compressor, is discharged through the cooling channels to the outside, while if the ribs 16 are bent like compressor blades, the cooling efficiency of the damper increases.
    权利要求:
    Claims (2)
    [1]
    But the flywheel or the flywheel and the flywheel cooling channels, a part of the discos are glasses with flanges of the bottom of which are perpendicular to the axis of the drum, and in their walls are evenly spaced around the holes connected to the cooling channels, the holes in the disks are any shape, The cooling fins can be bent depending on the direction of the shaft's rotation, and in cross section they are. have a rectangular, trapezoidal or triangular shape. FIG. 1 The cross section of the double damper is not present; in fig. 2 and 3 variants of the arrangement of the cooling fins; in fig. t, 5, 6 are cross-sectional shapes of edges J in FIG. 7 cross-section of a triple damper The damper contains a rubber-metal element 1 mounted on the end of shaft 2 and made in the form of disks 3,, 5, 6 connected to the shaft and flywheels 7, 8, 9 "Flywheels and disks are interconnected by rubber layers 10, 11, 12, 13, H, 15. Some of the rubber layers 11, 13, 15 are vulcanised to the end surfaces of the flywheels 7, 8 and 9 and made in the form of profile ribs 16, forming with the surfaces of the flywheels 8, 9 or disks and makhovika 7 cooling channels. Part of the discs, for example, 3, 5, are glasses with flanges, the bottom of which is perpe, idler axis of the damper, and in the case of using, for example, a triple damper, the disc 6 can be made flat. In the walls of the disks 3, 5, holes 17, 18, 19 / evenly spaced along the circumference are connected to the cooling channels, the holes can be made of any shape, and the profile fins 16 can be bent to one or the other side, depending from the direction of rotation of the shaft 2. The rubber-metal element 1 is attached to the shaft by a screw 20, and in the case of using a triple damper, the sleeves 21, 22 are installed between the rubber-metal elements and the rubber-metal elements do not touch each other, and the disks and flywheels are made are made of steel, n Latter are performed as iron. The damper works as follows. The torsional vibrations from the shaft 2 are transferred to the rubber-metal element 1, through the disks 3, 5, and then through the layers of rubber 10, 12, 1 to the flywheels 7, 8, 9, which play the role of additional mass, as in a dynamic vibration damper. In addition, the torsional energy is consumed for the deformation of the rubber, which is therefore heated. When the shaft rotates, air is sucked into the holes 17, 18, 19 and, as in the radial, the compressor is led out through the cooling channels to the outside, and if the fins 1b are bent like compressor blades, the efficiency of cooling the damper increases. Claim 1, A damper of resonant torsional vibrations of shafts, containing a rubber-metal element mounted on the shaft end and made in the form of disks connected to the shaft, flywheels and connecting disks and flywheels, rubber layers, some of which have radially arranged cooling Channels, characterized in that, in order to increase the damper service life, some of the rubber layers are vulcanized to the end surfaces of the flywheels and made in the form of shaped ribs, forming with flywheel surfaces or a disk and a flywheel, the cooling channels, and some of the disks are glasses with flanges, the bottoms of which are perpendicular to the axis of the damper, and in their walls are evenly spaced around the hole associated with the cooling channels, 2 o Damper according to claim 1, which differs by the fact that the holes in these discs are made in any shape, Zo Damper 1 and 2 each, and the fact that the cooling fins are bent, depending on the direction of rotation of the shaft, k. A damper according to Claim 1, characterized in that the cooling fins in the cross section have a rectangular, trapezoidal or triangular shape. Sources of information taken into account in the examination 1. V. Zhitomirsky, Mechanical oscillations and the practice of their elimination, M., 1966, Mechanical Engineering, p. 170171, Fig. 82, c.
    [2]
    2. The patent of Germany W 1J3679, cl. kja 20 (F06F) from I960 (prototype).
    (fJvz.J
    类似技术:
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    US4384858A|1983-05-24|Torsionally elastic shock and vibration absorbing coupling
    US2779210A|1957-01-29|Vibration dampener
    GB305527A|1929-11-21|
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    SU481727A1|1975-08-25|Friction clutch
    同族专利:
    公开号 | 公开日
    US4224835A|1980-09-30|
    JPS5427668A|1979-03-01|
    SE428965B|1983-08-01|
    GB2004974A|1979-04-11|
    SE7808323L|1979-02-03|
    IT1097489B|1985-08-31|
    CH631528A5|1982-08-13|
    GB2004974B|1982-05-06|
    IN149890B|1982-05-22|
    FR2399581A1|1979-03-02|
    DD137614A1|1979-09-12|
    IT7825440D0|1978-07-07|
    DE2734769A1|1979-02-15|
    HU177668B|1981-11-28|
    RO77583A|1981-11-04|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2477081A|1945-06-27|1949-07-26|Harold A King|Means for damping torsional vibrations in internal-combustion engines|
    US2585382A|1948-06-25|1952-02-12|Gen Motors Corp|Torsional vibration damper|
    US2594555A|1949-03-18|1952-04-29|Schwitzer Cummins Company|Vibration damper|
    US2716904A|1953-04-15|1955-09-06|Schwitzer Cummins Company|Damper assembly|
    US2779210A|1955-05-20|1957-01-29|Murphy Diesel Company|Vibration dampener|
    GB828354A|1957-02-27|1960-02-17|Metalastik Ltd|Improvements in or relating to torsional vibration dampers|
    FR1212425A|1957-10-17|1960-03-23|Holset Engineering Co|Improvements to torsional vibration dampers|
    US3088332A|1960-02-04|1963-05-07|Simpson Mfg Company|Vibration damper|
    GB1135495A|1966-07-19|1968-12-04|Holset Engineering Co|Means for cooling torsional vibration damper|
    US4041803A|1975-12-01|1977-08-16|Caterpillar Tractor Co.|Rubber torsional vibration damper with cooling means|JPS57145848U|1981-03-10|1982-09-13|
    US4483685A|1983-03-21|1984-11-20|The Singer Company|Motor isolator pulley|
    DE3326301A1|1983-07-21|1985-01-31|M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg|VIBRATION DAMPER FOR DAMPING ROTATING MASSES|
    JPS6336194Y2|1984-11-12|1988-09-26|
    JPS6336195Y2|1984-11-12|1988-09-26|
    JPS6336196Y2|1984-11-12|1988-09-26|
    JPS61215830A|1985-03-19|1986-09-25|Daikin Mfg Co Ltd|Flywheel equipped with dynamic damper|
    DE3531115C1|1985-08-30|1987-05-07|Tschan Gmbh & Co Kg|Device for suppressing torsional vibrations and radially acting bending vibrations of rotating shafts|
    US4815332A|1985-10-15|1989-03-28|Tokai Rubber Industries, Ltd.|Dual-type damper device|
    US4850243A|1986-06-04|1989-07-25|Household Manufacturing, Inc.|Uniform strain vibration damper|
    US4914949A|1986-10-01|1990-04-10|Firma Carl Freudenberg|Torsional vibration damper|
    JPH03501285A|1988-07-22|1991-03-22|
    JPH0427239U|1990-06-29|1992-03-04|
    DE4025848A1|1990-08-16|1992-02-20|Pahl Gummi Asbest|TURNING VIBRATION|
    JPH0527387U|1991-09-20|1993-04-09|エヌ・オー・ケー・メグラステイツク株式会社|damper|
    JP3538479B2|1995-06-26|2004-06-14|東海ゴム工業株式会社|Double mass dynamic damper and drive axle with dynamic damper|
    DE19641451A1|1996-10-08|1997-03-20|Voith Turbo Kg|Liquid-cooled automotive power unit with gearbox|
    DE60227862D1|2001-02-14|2008-09-11|Oiles Industry Co Ltd|Damper and motor vehicle seat with such a damper|
    DE102011104415B4|2010-06-29|2019-05-02|Schaeffler Technologies AG & Co. KG|Vibration damping device|
    JP2018115666A|2017-01-16|2018-07-26|Nok株式会社|Torsional damper|
    US10393220B2|2017-12-05|2019-08-27|Aprotech Powertrain Llc|Heat dissipation structures for crankshaft dampers|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE19772734769|DE2734769A1|1977-08-02|1977-08-02|RESONANCE ROTARY VIBRATION DAMPER|
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