• 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 shiftable friction clutch for gear drives, in which a shift collar is arranged axially movably on a carrier sleeve which is mounted on the shaft which must be coupled to a gear, and in which at least one axially movable friction ring is provided, which belongs to a first clutch half and which cooperates through clutch friction surfaces with a second clutch half and which is supported through rolling elements on the carrier sleeve for producing the contact pressure by means of pressure surfaces which are arranged on the front surfaces remote from the clutch surfaces and which are inclined with respect to the plane of rotation. The friction clutch is constructed as a spring-loaded safety clutch, in which the friction members which are pressed onto one another during the starting or engagement operation are supported against a spring.
    公开号:SU826974A3
    申请号:SU792720155
    申请日:1979-02-05
    公开日:1981-04-30
    发明作者:Штрелер Рихард；Бартль Макс
    申请人:Карл Хурт Машинен-Унд (Фирма)；
    IPC主号:
    专利说明:

    (54) Friction clutch
    the sleeve engages the sleeve 8 of the turn-on, making longitudinal motion. It is fixed from the gate on the guide sleeve. Friction rings 9 and 10 are installed on both corons from the guide bush, with the possibility of rotation. The friction rings have internal cones 11 and 12, which interact respectively with the external cones 13 and 14 of gear wheels 2 and 3. Together with the guide sleeve 7, they are provided with neither sides facing each other grooves 15 and 16. These grooves have two inclined surfaces 17, 18 and 19, 20. Balls 21 are located between the bodies. When the friction ring and the guide sleeve, as they rotate relative to each other, the balls 21 slide onto flat inclined surfaces and squeeze the friction ring from the guide sleeve. its previously mentioned cones are pressed against each other. Due to this, the corresponding gear wheel engages with the shaft. The grooves may have such an inclination that the rolling bodies can run onto the inclined plane, only in one direction of rotation. The friction rings 9 and 10 are pressed against the guide sleeve by one or more return springs 22, which are located outside the perimeter of the friction rings and are made in the form of twisted flat springs. Cams are provided around the perimeter of the friction rings.
    The inclusion sleeve 8 consists of a housing 23 having on the surface: 24 along the perimeter an annular groove 25 for the connection fork. Along the inner perimeter, the housing is provided at the end with two inclined surfaces converging to the center, referred to as initial surfaces. If the inclined surfaces, such as surfaces 17 and 18, of the working elements are inclined in a certain direction of the SRI around the circumference, causing broadening (recess) of the groove 15, then the initial surfaces 26 and 27 converge in the same direction to the central plane (plane of rotation). The initial surfaces of the sleeve housing part are adjacent to the openings 28, in which the indicated return springs 22 are located. At some distance from the initial surfaces 26 and 27 on the sleeve housing, axes are provided in the axial direction on the facing surfaces of the sleeve surfaces. parallel surfaces 31 and 32 parallel to them. The sleeve housing and jumpers have gaps 33 and 34, as well as protrusions 35 and 36, which
    they have on their side beveled surfaces 37 and 38, the latter are parallel to the initial surfaces indicated earlier on the friction rings. On the other side, protrusions 35 and 36 have sloping side surfaces 39 and 40 mating with surfaces 31 and 32. Projections 35 and 36 have abutting side surfaces 41 and 42, which are located at a right angle to the plane of rotation. When the clutch is turned on, the starting surface 26 is pressed against the mating surface, e.g. the surface 37, as a result of moving the hub sleeve. As a result, the friction ring is displaced to the friction surfaces (cones), thereby transmitting torque. Due to the incidence of the balls 21 on inclined surfaces, the transmitted torque increases. Switching off takes place by pressing the mating surfaces of the switch sleeve onto the adjacent side of the friction ring. Due to the interaction of the thrust surfaces with the thrust side surfaces, the involuntary engagement of the disengaged friction ring is prevented.
    权利要求:
    Claims (2)
    [1]
    A spring-loaded locking pin 43 is installed in the guide sleeve 7 with the possibility of radial movement. A corresponding cut is provided in the middle of the sleeve case to fix the turn-on sleeve in the off state (in the neutral position). At the ends of the insertion sleeve there are two chamfers 44 and 45 for fixing both insertion positions. The guide sleeve 7 mounted on the shaft 1 can be moved in the axial direction, in its neutral position is held by two locking rings 46 and 47 inserted with a small radial clearance in the annular grooves 48 and 49, made in the shaft body 1. The grooves are wider than the locking rings . The cup springs 50 and 51 are pressed against the counter-bushing guide of the locking rings, which rest on the other side against the stops 52 and 53. The guide bushing 7 has pcs; lugs 54, and the tapered rings 9 and 10 have splined grooves 55 the gap relative to the protrusions 54. When the body engages, the rolling rolls onto inclined surfaces. The friction ring has mobility in the axle; the circumferential direction, and the spline joint limits this mobility AND serves as a stop when moving in the axial direction. When the clutch is engaged, the friction ring abuts by means of rolling elements onto the spring guide sleeve. Thus, the maximum frictional force and the maximum transmitted torque depend on the tension of the springs 50 or 51. When switched on, the corresponding friction ring, for example the ring 10, abuts through the balls into the guide sleeve 7, which, overcoming the action of the cup springs 50, deflects goes right. The conical ring 10 is loaded in the same way with the cup springs 50, having engaged. In this case, the cup springs 51 are inactive, since, when the guide sleeve is deflected (shifted), their pretension does not change. Exceeding the prescribed overload moment as a result of shocks, such as when switching at high speeds or in boat gears, for example when hitting the ground, is impossible in the proposed coupling. The springs 50 and 51 in the disengaged state do not act on the working surfaces of the cones, so as there is a two-way axial fixation, and the spring travel in the direction to the working surfaces is limited. The widths of the slots 48 and 49 are chosen such that the locking rings cannot adhere to their walls, since at first the tangential gap of the spline joint is chosen. The proposed coupling allows smooth connection (without impacts), since the force of the preliminary tension (initial load) of the disc springs 50 and 51 is influenced only by the forces of small masses, in particular, the neutral mass of gears 2 and 3 remains. In addition, the clutch has a compact design, so that the Ks1k panplates can be positioned inside the conical clutch itself and could be used with one-way or multi-plate clutch. Claim 1. A friction clutch comprising an inclusion sleeve mounted thereon a guide to the eagle and mounted on the drive shaft and mounted on its end parts through splined joints, friction rings, spring-loaded relative to the followers, with cup springs, characterized in that, in order to ensure smoothness of inclusion, it is provided with annular stops located on the shaft on both sides of the guide bush, and the latter is mounted on the shaft axially movable, while the disc springs are located between ring stops and driven elements. 2. Coupling POP.1, characterized in that a wedge element is made on the inclusion sleeve, and on the friction rings there are spaced p6 both sides of it with radial protrusions with beveled side surfaces. 3. Mufta on PP. 1 and 2, characterized in that the spline joint of the drive guide bush and the friction rings is made with a tangential gap. 4. Coupling according to claims 1-3, characterized in that the drive sleeve, the friction rings, the driven elements and the shaft are installed to form cavities, and the disc springs are displaced therein. Sources of information taken into account examination 1. The author's certificate of the USSR 323581, cl. F 16 D 13/52, 1972.
    [2]
    2. The patent of Germany No. 2225096, cl. F 16 D 13/52, 1972 (prototype).
    类似技术:
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    同族专利:
    公开号 | 公开日
    ES482079A0|1980-04-01|
    GB2024341A|1980-01-09|
    FR2429937A1|1980-01-25|
    IT1203229B|1989-02-15|
    ES8100025A1|1980-04-01|
    SE7813053L|1979-12-31|
    JPS5510175A|1980-01-24|
    BR7902396A|1980-10-29|
    IT7947724D0|1979-01-22|
    DE2828722A1|1980-01-10|
    US4289223A|1981-09-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE4302083A1|1993-01-19|1994-07-21|Black & Decker Inc|Power tool, in particular power tool|US2546712A|1947-08-30|1951-03-27|Int Harvester Co|Sprag type synchronizer device|
    US2874817A|1955-02-23|1959-02-24|Daimler Benz Ag|Friction clutch with torque responsive lock|
    US3189147A|1961-09-11|1965-06-15|Borg Warner|Multiple clutch with lever|
    DE1261360B|1962-03-21|1968-02-15|Zahnradfabrik Friedrichshafen|Friction clutch, especially for boat gears|
    DE2045383B2|1970-09-14|1971-12-09|Carl Hurth Maschinen und Zahnrad fabrik, 8000 München|SWITCHING DEVICE FOR A FRICTION CLUTCH|
    DE2614845A1|1976-04-06|1977-10-20|Hurth Masch Zahnrad Carl|REVERSING GEAR, IN PARTICULAR FOR A Z-DRIVE FOR WATER VEHICLES|DE3063618D1|1979-09-28|1983-07-07|Rotork Controls|Actuator with alternative motor or manual drive|
    SE425650B|1981-03-05|1982-10-25|Volvo Penta Ab|TRANSMISSION, BATTERY ENGINE SPECIFICATIONS|
    US4534236A|1983-03-15|1985-08-13|Honda Giken Kogyo Kabushiki Kaisha|Vibration and noise reduction means for a transmission vehicle|
    DE3623142C2|1986-07-09|1989-06-01|Carl Hurth Maschinen- Und Zahnradfabrik Gmbh & Co, 8000 Muenchen, De|
    SE8903444A|1989-10-19|1990-11-26|
    SE502042C2|1993-11-18|1995-07-24|Volvo Ab|Synchronization device in a vehicle gearbox|
    GB2357125A|1999-12-08|2001-06-13|Eaton Corp|Synchronizer with a resilient force limiting ramp members and blocker teeth|
    US6467598B2|1999-12-08|2002-10-22|Eaton Corporation|Synchronizer|
    DE10302236B4|2003-01-20|2012-12-06|Zf Friedrichshafen Ag|Friction clutch or friction brake with self-reinforcement|
    US7384366B2|2004-03-12|2008-06-10|Borgwarner Inc.|Transfer case with torque synchronizer clutching|
    DE102010029863A1|2010-06-09|2011-12-15|Zf Friedrichshafen Ag|Releasable axial fixation of two components|
    DE102014108202A1|2014-06-11|2015-12-17|Hoerbiger Antriebstechnik Holding Gmbh|Synchronization unit for a transmission|
    CN110131029B|2018-02-08|2020-07-21|河南德昌机械制造有限公司|Automatic water tank cleaning device with forward and reverse rotating fans|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE19782828722|DE2828722A1|1978-06-30|1978-06-30|SWITCHABLE FRICTION COUPLING FOR GEAR GEARBOXES|
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