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    • 1. 发明专利
    • Improvements in or relating to torque transmitting devices
    • GB594536A
    • 1947-11-13
    • GB1760544
    • 1944-09-14
    • OTTO EDWARD WOLFF
    • F16D7/02F16D43/21
    • 594,536. Shaft couplings. WOLFF, O. E. Sept. 14, 1944, No, 17605. Convention date, Feb. 25. [Class 80(ii)] Torque is transmitted between members 22, 24, by friction between a surface 28 on the member 22 and a plurality of friction shoes 30 carried by the member 24 and urged into engagement by yielding material 36, such as rubber. The interior of the coupling contains lubricant. If the members 22, 24, are rotating at equal speeds there is dry friction between the surface 28 and shoes 30. Should the speeds vary, by overloading, for example, oil becomes wedged between the friction surfaces and the coupling action ceases. To re-couple the members their speeds must first be equalised. As shown, the shoes 30 have lubricant passages 48 and are carried with play in a cage 32 rigid with the member 24. A nut 40 and spring washer 42 carried by an adjusting screw 38 provide for axial compression of the yielding material 36 to vary the radial pressure between the friction surfaces. In a modification the cage 32 is omitted, the shoes being moulded in a rubber mass secured to the member 24. Axial compression of the rubber is effected through adjustable spring pressure. Each shoe may be in two parts, one part being. engaged by the yielding material and having a rounded projection on which the other part having the friction surface is universally supported. All constructions permit slight universal relative movements of the coupling members 22, 24.
    • 3. 发明专利
    • Improvements in or relating to power transmission device
    • GB569410A
    • 1945-05-23
    • GB1325142
    • 1942-09-19
    • OTTO EDWARD WOLFF
    • F16H61/02
    • 569,410. Variable, -speed gearing ; clutches. WOLFF, O. E. Sept. 19, 1942, No. 13251. Convention, date, April 15. [Class. 80 (ii)] A power transmission has a clutch adapted to transmit power from a driving shaft to a driven shaft only when the said shafts rotate at the same speed and a second power-transmitting means adapted to transmit power between said shafts only when they rotate at different speeds, the clutch being such that a change over from the clutch to the second power-transmitting means is automatically obtained at any speed whenever the driving torque exceeds a predetermined maximum for that speed. The clutch may be of the kind described in Specification 567,676. As shown, for a countershaft type gear-box, the inner members 65, 90 of two clutches are mounted on shafts 66, 88 and cooperate with the inner surface of a drum 62 fixed to a driving shaft 60. The drum 62 is fixed to a gear 77. Gears 86, 100 are fixed to the shafts 88, 66. Gears 77, 86, 100 mesh with gears 78, 85, 98, gear 78 being fixed to a countershaft 80 and gears 85, 98 being loose thereon and interconnected by freewheel clutches 84, 96. A final driven shaft 105 carries a dog clutch member 102. Fixed gears 106, 110 mesh with gears 108, 112 on the shaft 105, a reverse idler being arranged between the gears 110, 112. Each clutch comprises a spider 65 with centrifugal weights 70, Fig. 3, carrying pivoted pads 75. When the inner and outer parts of the clutch are revolving at the same speed oil is pressed out from between the pads 75 and the inner surface of the drum 62 and the clutch is engaged. If the torque transmitted becomes excessive the clutch slips and oil films are built up between the parts 75, 62, and the clutch is disengaged. With the parts positioned as shown in Fig. 2 and the driven shaft 105 stationary, rotation of the shaft 60 will drive the shaft 105 through the gears 77, 78, 85, 98, 100 and freewheel clutches 84, 96, and the drive will be in low gear. When the shaft 105 has increased in speed and a higher gear is required, the driving shaft 60 is retarded and when it reaches the speed of the clutch parts 90 the latter clutch engages and the drive is through the parts 60, 62, 90, 86, 85, 96, 98, 100, 105. When the parts have speeded up and high gear is required, the driving shaft is again retarded and the clutch 62, 65 engages and a one-to-one drive results through the parts 60, 62, 65, 66, 105. Gearing down is produced automatically in accordance with the torque on the driven shaft 105. When the clutch 102 is engaged with the gear 108 a fixed low gear results through the parts 60, 62, 77, 78, 106, 108, 102, 105. Instead of having, three automatic speeds as above one of the clutches and some of the gears may be omitted to give two automatic speeds. As applied to an epicyclic gear, gears 204, 212, Fig. 14, on driving and driven shafts 200, 202, mesh with parts 205, 206 of compound planet pinions carried by a cage 208. The latter has a clutch drum 220 and is prevented from rotating backwardly by a one-way brake 215. A spider 222 carrying centrifugal clutch members 224 is fixed to the shaft 202. When starting up the shaft 202 is driven at low gear through the gears 204. 205, 206, 212, the cage 208 being stationary. As the speed increases the weights 224 engage the drum 220. If the speed of the driving shaft is retarded inertia will cause the drum 220 to rotate forwardly and when its speed reaches that of the shaft 202 the parts 224, 220 engage in driving relationship and a direct drive results. Upon a predetermined maximum torque the gear goes automatically into low gear. In a modification, three epicyclic gears are arranged in series. A driving shaft 300, Fig. 16, has a clutch drum 312 and toothed annulus 315 meshing 'with planet pinions 316 on a carrier 322 fixed to a shaft 325. The carrier 322 has centrifugal weights 340 with pivoted pads 344 for engagement with the drum 312. The planets 316 mesh with a sun spur-wheel 326 connected to the fixed casing 334 by a one-way brake 330. A third shaft 364 is connected to the shaft 325 by a like epicyclic gear and the final driven shaft 302 is similarly geared to the shaft 364. The three sets of centrifugal weights are of differing weights, 340 being heavier than 365 and so on. The third epicyclic gear in the casing part 375 may be replaced by a reverse gear. At high loads all gears work epicyclically, giving a low gear. To increase the gear the driving shaft 300 is retarded to engage the clutch 312, 344 so that the first epicyclic gear becomes solid. When all the gears are solid the driven shaft 302 rotates at the same speed as the driving shaft 300. The clutches in any of the above constructions may be replaced by a clutch in which the outer member 122, Fig. 4, has a cam-like inner surface 128 and the inner clutch part comprises a spider 134 with links 136 carrying rollers 140 co-operating with the. surface 128. When the clutch is engaged the rollers engage in the corners 130 of the surface 128; at other times they roll round the surface 128.
    • 4. 发明专利
    • Improvements in or relating to clutch mechanism
    • GB567676A
    • 1945-02-27
    • GB1325242
    • 1942-09-19
    • OTTO EDWARD WOLFF
    • F16D43/02
    • 567,676. Friction clutches. WOLFF, O. E. Sept. 19, 1942, No. 13252. Convention date, Jan. 13, 1942. [Class 80 (ii)] [Also in Group XXXIV] In a friction clutch the driving and driven members are held in unlubricated static frictional contact whenever there is no relative motion thereof, or whenever the torque transmitted is less than a predetermined torque, and are sub-- stantially completely disengaged with continuous films of lubricant between their normally contacting surfaces whenever there -is relative motion, or whenever the torque reaches a predetermined value. As shown a plate 38, Fig. 1, on a driving shaft 32 is spring- urged towards a plate 60 on a driven shaft 36 and has friction pads 44 pivoted thereto. The housing 52 is partially filled with lubricant. When driving takes place there is no lubricant between the pads 44 and the plate 60, Fig. 4, but should relative motion or slip occur the pads 44 tilt and an oil film 68, Fig. 3, is built up and the clutch is disengaged. Re-engagement is obtained by bringing the plates 38, 60 to the same speed. In a modification the pads 85, Fig. 5, are supported by centrifugal weights 75 carried by arms 74 on the driving shaft 70, and bear on a drum 90 fixed to the driven shaft. Springs 80 also urge the weights radially outwardly. Thus the torque that can be transmitted is increased with the speed of rotation. The pads may be integral with the weights and may be chamfered at the leading edges. In another modification three sets of centrifugal weights 312, 314, Figs. 24, 25, are pivoted to arms 310 on the driving shaft 300, the pads 320 being carried by springs 318 on the weights. Movement of the weights under centrifugal force is limited by abutments 324, 325, some of the weights being permitted more movement than the others. The pads 320 engage a drum carried by the driven shaft 302. In another modification in which the clutch disengages when the speed exceeds a predetermined value, the pads 210, Fig. 19, engage the outside of a drum 204 on the driven shaft and are carried. by stems 206 radially slidable in a drum 198 on the driving shaft. Springs 216 urge the pads towards the drum 204. In another modification the pads 236, Fig. 20, are integral with centrifugal weights 232 slidingly carried by arms 230 on a casing 228 fixed to the driving shaft. Pins 237 in the casing carry gears 238 which mesh with a gear 225 on the driven shaft. Thus when relative motion occurs between the driving and driven shafts the gears act as oil pumps and oil passes through pipings 240 and ducts 244 to the engaging surfaces.
    • 7. 发明申请
    • Methods and apparatus for providing data transfer control
    • US20050172050A1
    • 2005-08-04
    • US11100697
    • 2005-04-07
    • Edwin BarryEdward Wolff
    • Edwin BarryEdward Wolff
    • G06F13/00G06F13/12G06F13/28
    • G06F13/126G06F13/28
    • A variety of advantageous mechanisms for improved data transfer control within a data processing system are described. A DMA controller is described which is implemented as a multiprocessing transfer engine supporting multiple transfer controllers which may work independently or in cooperation to carry out data transfers, with each transfer controller acting as an autonomous processor, fetching and dispatching DMA instructions to multiple execution units. In particular, mechanisms for initiating and controlling the sequence of data transfers are provided, as are processes for autonomously fetching DMA instructions which are decoded sequentially but executed in parallel. Dual transfer execution units within each transfer controller, together with independent transfer counters, are employed to allow decoupling of source and destination address generation and to allow multiple transfer instructions in one transfer execution unit to operate in parallel with a single transfer instruction in the other transfer unit. Improved flow control of data between a source and destination is provided through the use of special semaphore operations, signals and message synchronization which may be invoked explicitly using SIGNAL and WAIT type instructions or implicitly through the use of special “event-action” registers. Transfer controllers are also described which can cooperate to perform “DMA-to-DMA” transfers. Message-level synchronization can be used by transfer controllers to synchronize with each other.
    • 9. 发明申请
    • Methods and Apparatus for Providing Data Transfer Control
    • 提供数据传输控制的方法和装置
    • US20070088868A1
    • 2007-04-19
    • US11533897
    • 2006-09-21
    • Edwin BarryEdward Wolff
    • Edwin BarryEdward Wolff
    • G06F13/28
    • G06F13/126G06F13/28
    • A variety of advantageous mechanisms for improved data transfer control within a data processing system are described. A DMA controller is described which is implemented as a multiprocessing transfer engine supporting multiple transfer controllers which may work independently or in cooperation to carry out data transfers, with each transfer controller acting as an autonomous processor, fetching and dispatching DMA instructions to multiple execution units. In particular, mechanisms for initiating and controlling the sequence of data transfers are provided, as are processes for autonomously fetching DMA instructions which are decoded sequentially but executed in parallel. Dual transfer execution units within each transfer controller, together with independent transfer counters, are employed to allow decoupling of source and destination address generation and to allow multiple transfer instructions in one transfer execution unit to operate in parallel with a single transfer instruction in the other transfer unit. Improved flow control of data between a source and destination is provided through the use of special semaphore operations, signals and message synchronization which may be invoked explicitly using SIGNAL and WAIT type instructions or implicitly through the use of special “event-action” registers. Transfer controllers are also described which can cooperate to perform “DMA-to-DMA” transfers. Message-level synchronization can be used by transfer controllers to synchronize with each other.
    • 描述了用于在数据处理系统内改进数据传输控制的各种有利机制。 描述了一种DMA控制器,其被实现为支持多个传输控制器的多处理传输引擎,其可以独立地或协作地执行数据传输,每个传输控制器充当自治处理器,将DMA指令提取并分派给多个执行单元。 特别地,提供了用于启动和控制数据传输序列的机制,以及自动获取被顺序解码但并行执行的DMA指令的过程。 每个传输控制器内的双传送执行单元与独立的传输计数器一起被用于允许源和目标地址生成的解耦,并允许一个传送执行单元中的多个传输指令与另一个传输中的单个传输指令并行操作 单元。 通过使用特殊信号量操作,信号和消息同步,可以使用SIGNAL和WAIT类型指令明确地调用,或者通过使用特殊的“事件动作”寄存器来隐式地调用源和目标之间的数据流改进。 还描述了可以协作执行“DMA到DMA”传输的传输控制器。 传输控制器可以使用消息级同步来相互同步。