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Means for forward and reverse gear drive of hydro mechanical power transmissions
Means for forward and reverse gear drive of hydro mechanical power transmissions
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机译:液压机械动力传动装置的前进和后退齿轮驱动装置
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1,004,420. Hydro-mechanical variable speed gear. SVENSKA ROTAR MASKINER A.B. Sept. 13, 1961 [Oct. 5, 1960], No. 32805/61. Headings F2C, F2D and F2L. A variable-speed gear for a motor vehicle comprises a hydro-dynamic torque converter 12 having an impeller 20, first turbine 24, 28 and second turbine 26 which turbines are connected to each other and to an output shaft 48 by two sun-ring planet trains controlled by selective engagement of hydraulically operated friction brakes 56, 70 and a clutch 47 to provide two forward speed stages during which the turbines rotate in opposite directions and the same direction respectively and a reverse speed stage. The second turbine 26 is fast with the planet carrier 50 of the first gear train the planets 52 of which mesh a sun gear 44 fast with the first turbine 24, 28 and a ring gear 54 which may be held at 56. The planets 64 of the second train mesh a sun 62 fast with the first planet carrier 50 and an output carried ring gear 72 and the planet carriers 66 may be held at 70. The clutch 47 connects the first turbine directly to the output shaft 48. Oil under pressure is supplied to the torque converter through lines 116, 84, 86 from a pump 74 driven through gears 77, 76, 78, 80 from the torque converter casing 12. Outflow from the torque converter passes through lines 87, 88, 89, a one-way pressure relief valve 90, a cooler 91 and a filter 92 back into a sump 94. Pressure oil from the pump 74 is selectively supplied to servos 102, 106, 49 of the brakes 56, 70 and clutch 47 under the control of a manual neutral-forward-reverse selector valve 120, a valve 126 responsive to the speed ratio between the input and output shafts and a valve 142 responsive to accelerator pedal position. The valve spool 126 is splined at 128 to the gear 78 driven from the torque converter casing 12 and at its other end carries a friction disc 132 on a screw-threaded portion 130 thereof. The disc 132 is pressed by a spring into engagement with a drum 134 driven through gears 108, 110, 112 from the output shaft 48 so that below a predetermined ratio between the input and output shafts the valve spool is screwed to the left and above the predetermined speed is screwed to the right (position shown). For neutral with the vehicle stationary and the valve 126 in its left hand position the selector valve 120 is moved to the position 120a in which it blocks the oil pressure supply lines 118, 146 and exhausts the brake servo 102 at 152 through lines 136, 124, the brake servo 106 at 154 through lines 138, 122 and the clutch servo 49 at 156 through line 150. For forward drive the selector valve 120 is moved to the position 120b (position shown) in which pressure oil is supplied through lines 118, 122, 136 to engage brake 70 and through line 140 valve 142 and lines 146, 150 to the clutch 47. With the accelerator pedal in the throttle closed position the valve 142 is in the position 142a in which the pressure oil passes from the line 140 through a restriction 140b to the valve which now communicates with a pressure relief valve 148 so that reduced pressure is applied to the clutch 47 which thus slips and slows the first turbine 24, 28 prior to full clutch engagement. Depression of the accelerator pedal moves the valve 142 to the position 142b (position shown) to provide unrestricted communication between pressure supply line 140 and clutch line 150, for full clutch engagement and forward drive in a low ratio stage, during which the turbines rotate in opposite directions. At a predetermined speed ratio between the input and output members the valve 126 shifts to the position shown to vent the brake servo 106 at 152 through lines 138, 124 and engage the brake 56 by supplying pressure oil to its servo 102 through lines 122, 136 for high ratio stage during which the turbines rotate in the same direction. For reverse the selector valve 120 is moved to the position 120c in which the clutch servo is exhausted at 156 and with the valve 126 in its left-hand position pressure oil is supplied to servos 102, 106 through lines 118, 124, 136 ; 140, 146, 122, 138 respectively. The brake 70 is only partially engaged due to the valve 142 occupying its throttle closed position in which it reduces the oil pressure supplied to the brake servo 106, so that the planet carrier 66 is braked slowly. Depression of the accelerator pedal shifts the valve 142 for full engagement of the brake 70 providing reverse ratio. The valve 142 is operated by a solenoid the circuit of which is completed by closing a switch when the throttle valve is closed. In Fig. 2 (not shown), the planet carrier 50 is provided with an additional brake which when engaged together with the clutch 47 provides an additional forward ratio. Specification 880,063 is referred to.
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机译:1,004,420。液压机械变速齿轮。 SVENSKA ROTAR MASKINER A.B. 1961年9月13日[十月1960年5月],第32805/61号。标题F2C,F2D和F2L。用于机动车辆的变速齿轮包括具有叶轮20的液力变矩器12,第一涡轮机24、28和第二涡轮机26,这些涡轮机通过两个太阳环行星架彼此连接并且与输出轴48连接。通过液压操纵的摩擦制动器56、70和离合器47的选择性接合来控制的动力传动系提供两个前进速度级,在该两个前进速度级中,涡轮分别沿相反的方向和相同的方向旋转,并且提供反向速度级。第二涡轮机26与第一齿轮系的行星齿轮架50固定在一起,该行星齿轮架的行星齿轮52的太阳齿轮44与第一涡轮机24、28快速地啮合,并且齿圈54可保持在56。第二轮系与第一行星架50和输出齿圈72快速啮合太阳62,行星架66可以保持在70。离合器47将第一涡轮直接连接到输出轴48。从泵74通过齿轮77、76、78、80驱动的泵74通过线116、84、86从变矩器壳体12供应到变矩器。变矩器的流出物通过线87、88、89,一个-方向溢流阀90,冷却器91和过滤器92返回到油底壳94。在手动控制下,来自泵74的压力油有选择地供应到制动器56、70和离合器47的伺服102、106、49中立-前进-后退选择阀120,响应速度比的阀126输入轴和输出轴以及响应加速踏板位置的阀142。阀芯126在128处用花键连接至从变矩器壳体12驱动的齿轮78,并且在其另一端在其螺纹部分130上承载摩擦盘132。盘132被弹簧压入与从输出轴48通过齿轮108、110、112驱动的鼓134啮合,从而在输入轴和输出轴之间的预定比率以下,阀芯被拧到左侧并在其上方。预定的速度拧到右侧(显示的位置)。为了在车辆静止且阀126处于其左手位置时保持空档,选择阀120移至位置120a,在该位置中,选择阀120阻塞油压供应管线118、146,并通过管线136、124在152处排出制动助力器102。 ,伺服伺服器106在154通过线138、122,离合器伺服器49在156通过线150。为了向前驱动,选择阀120移动到位置120b(所示位置),在此处通过线118供给压力油, 122、136使制动器70接合并通过管路140阀142和管路146、150到达离合器47。在加速踏板处于节气门关闭位置的情况下,阀142处于位置142a,压力油从管路140通过通过限制器140b到达阀,该阀现在与泄压阀148连通,从而将减小的压力施加到离合器47,从而在完全离合器接合之前使第一涡轮24、28打滑并减速。踩下油门踏板会将阀142移至位置142b(所示位置),以在压力供应管线140和离合器管线150之间提供不受限制的连通,从而在低速比阶段实现离合器的完全接合和前进驱动,在此期间涡轮机旋转相反的方向。在输入和输出构件之间的预定速比下,阀126移至所示位置,以通过管线138、124在152处使制动助力器106排气,并通过通过管线122、136向其伺服器102供应压力油来接合制动器56。用于高比例阶段,在该阶段涡轮机以相同方向旋转。为了换向,选择阀120移动到位置120c,在该位置离合器离合器在156处排气,并且在阀126处于其左侧位置的情况下,压力油通过管线118、124、136被供应到伺服器102、106。 140、146、122、138。制动器70由于阀142占据其节气门关闭位置而仅部分接合,在该节气门关闭位置中,它减小了供应给制动伺服机构106的油压,从而行星齿轮架66被缓慢地制动。踩下油门踏板会使阀142换挡,从而使制动器70完全接合,从而提供倒档比。阀142由螺线管操作,该螺线管的电路通过在节气门关闭时闭合开关来完成。在图2(未示出)中,行星齿轮架50设有附加制动器,该制动器在与离合器47接合时提供附加的前进比。参考规格880,063。
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