Patent GB-1135071-A (GB)
Title: Power transmission systems
Inventor: SINCLAIR HAROLD
IPC: F16H37/00
Filed: 1965-06-11
Abstract: 1,135,071. Change-speed control; ratchet clutches; hydrodynamic and disc brakes; fluidpressure brakes. S.S.S. PATENTS Ltd. 2 June, 1966 [11 June, 1965; 5 July, 1965; 10 Aug., 1965], Nos. 24868/65, 28403/65 and 34226/65. Headings F2C, F2D, F2E and F2F. A change-speed planet gear 3 for a fan or pump comprises input, output and reaction elements, the latter, 95, of which is selectively retarded by a hydrodynamic brake 19, held by a disc brake 45 or driven by an electric motor 5 to provide different ratios. Gear arrangement.-The planet gear 3 is connected to a main driving motor 4 and comprises a sun-ring train having an input ring gear, output sun gear and reaction planet carrier, or an input sun gear, output planet carrier and a reaction ring gear, or an input ring gear, output planet carrier and a reaction sun gear. The reaction element is geared at 95, 96, 97 to a shaft 18 selectively held by the brakes 19, 45 or connected by a clutch 8 to the motor 5. Clutches.-The clutch 8 is of the synchro selfshifting type wherein a pawl-and-ratchet 74, 76 initiates movement of an intermediate member 69 along helical splines 67 on a driving clutch element 64 to engage teeth 72 on the intermediate member 69 synchronously with teeth 81 on a driven clutch element 77. The splines are arranged so that the clutch engages when the driving-shaft 6 rotates in a direction opposite to the arrow a relative to the driven shaft 18, i.e. when the motor 5 is reversed. When the clutch is engaged a locking sleeve 8 is slid axially to engage teeth 92, 93 thereon with teeth 66, 94 on the driving and driven clutch elements 64, 77. The sleeve 8 is fast with a sleeve 85 splined at 91 to the intermediate member 69 so that when the clutch 72, 81 is disengaged the sleeve 8 is rotated and axial locking movement of the sleeve 8 is prevented by the teeth 66, 92 abutting end-on. A clutch looking servomotor 16 is supplied with pressure oil through an electromagnetically controlled valve 38 and the servopiston 15 is connected to the sleeve 8 through a resilient coupling 13 so that when pressure oil is supplied to the servomotor 16, the coupling 13 is compressed and biases the sleeve 8 towards a locking position although movement of the sleeve is prevented until the clutch teeth 72, 81 are engaged. Brakes.-The hydrodynamic brake 19 is of the inclined vane twin rotor type and is supplied with pressure water through a manually controlled valve 20 and a parallel valve 27 actuated by a servo-motor 29 supplied with pressure oil through an electromagnetically controlled valve 31. The disc brake 45 has piston-actuated friction pads 46 in a caliper unit 47 supplied with high-pressure oil from an intensifier 52 itself supplied with pressure oil through an electromagnetically controlled valve 55. An additional caliper unit 47<SP>1</SP> may be provided. Control and Operation.-Switches 36, 44, 61 in the circuits of the valves 31, 38, 55 are controlled by a hand lever 63<SP>1</SP>. To start the transmission the lever 63<SP>1</SP> is moved to the position S which starts the motor 4, closes the switch 36, and opens the switches 44, 61. Closure of the switch 36 energizes the valve 31 which supplies oil to the servo 29 to open the valve 27 whereupon the hydrodynamic brake 19 is filled and retards the shaft 18 and reaction element 95. When the brake 19 is full the speed of the output shaft 2 is 95% of its speed when the shaft 18 is held stationary (i.e. its nominal speed). Movement of the lever 63<SP>1</SP> to position a closes switch 44, opens switch 36 and starts the motor 5 in the high-speed reverse setting. The brake 19 is thus emptied and the clutch locking sleeve 8 biased to a locking position. When the shafts 6, 18 are synchronized the clutch 72, 81 engages and is locked engaged by the sleeve 8. The output speed is then 94% of its nominal speed. With the lever 63<SP>1</SP> in the position b the motor 5 is in its low-speed reverse setting and the switches 36, 61 remain open and the switch 44 remains closed to provide an output speed of 97% of the nominal speed. With the lever 63<SP>1</SP> in the position c the motor idles whilst the switch 61 is additionally closed to apply the disc brake 45 for nominal output shaft speed. Movement of the lever 63<SP>1</SP> to the d setting conditions the motor 5 for low-speed forward running and re-opens the switch 61 to provide an output speed of 103% of the nominal speed. With the lever 63<SP>1</SP> in the e position the motor 5 is conditioned for high-speed running and increases output speed to 106% of the nominal speed. For manual control the lever 63<SP>1</SP> is moved from the start S position to the M position in which the motor 5 is stopped and the switches 36, 44, 61 are all open. The filling of the hydrodynamic brake 19 is then controlled manually by the valve 20 to provide a steplessly variable output speed up to 95% of the nominal speed. In the event of an electrical failure whilst operating with the lever 63<SP>1</SP> in positions a, b, d or e, a safety circuit (not shown) stops the motor 5, opens the circuits to the switches 44, 61 and completes the circuit to the valve 31 and thus reduces output speed to that of the start position. Failure of the oil supply to the servomotor 16 operates a pressure-sensitive switch to stop both motors 4, 5.