Patent GB-842371-A (GB)
Title: Variable speed transmission mechanism
IPC: F16H61/70
Filed: 1956-11-05
Abstract: 842,371. Change-speed gear. BORG-WARNER CORPORATION. Nov. 5, 1956 [Nov. 17, 1955], No. 33751/56. Class 80 (2). A change-speed gear for a heavy vehicle comprises a main four-speed and reverse planet gear unit A, ahead of a direct-reduced twospeed planet gear " splitter " unit B, both units being controlled automatically in response, inter alia, to output-speed-responsive fluid pressure provided by a governor 180 driven by the final output shaft 12, and the splitter-unit selector controls a valve 213 which, when the splitter unit is in reduced drive, increases the level of the governor pressure effective on the main unit A, to prevent downshift in that unit as a result of downshift in the splitter unit B, such increase in governor pressure level being obtained by an associated regulator valve 211 which, in addition to increasing the slope of the pressure-speed curve for the above purpose, also provides for an abrupt reduction of the said slope above a predetermined value of governor pressure. Similar regulator valves, each providing a different level of governor pressure (Fig. 5, not shown), are controlled by the selector control of the main gear to prevent unwanted shift in the splitter gear. Function summary.-The output two-speed unit B provides a second series of four ratios intermediate the first four provided by the preceding main gear unit A, and is for this reason called a " splitter " unit. It also provides two reverse ratios from the single reverse of the unit A. Automatic accelerator- and output-speed-responsive control of all ratios in both main and splitter units A, B is provided, together with separate manual selector-valves 185, 221 for the respective units. With both manual controls in " D," Drive, setting, automatic upshifts occur first in the main unit A, the splitter remaining in low ratio, to provide in succession overall ratios called first low, second low, third low and fourth low. A final automatic upshift in the splitter unit B gives overall fourth high. Automatic downshifts again occur first in the main unit A, the splitter remaining in high, to give overall third high, second high and first high, followed by a final automatic downshift in the splitter unit to first low. Downshift sequence is altered and downshift speeds raised by accelerator kickdown, which causes the splitter downshift to take precedence, giving a sequence fourth high, fourth low, third low, second low and first low. Upshift sequence and shift speeds (as compared to normal full throttle) are unaffected. Shifting the main selector valve 185 to " 3 " setting prevents upshift above third in the main unit, although if fourth is effective at the time of the manual shift, the actual downshift to third can only occur below a safe engine speed. In settings " 2 " and " 1 " of the main selector 185, upshifts respectively above second and first ratios in the main unit are similarly prevented, the automatic splitter shift remaining effective in all these settings, as for D. With the main selector 185 in D and the splitter selector 221 in L (low) or H (direct), the splitter is permanently held in low or high respectively, and shifts occur in the main unit A only, as for D. If desired, eight ratios can be obtained in succession either by maintaining kick-down and suitably manipulating the main selector 185 manually, or by manipulating both selectors 185, 221 manually. For all forward operation the first ratio brake 19 only of the main unit A is applied by full line pressure, and all other brakes and clutches of both units are applied by accelerator-responsive compensator pressure. In reverse, servo pressure is augmented and both the reverse brake 18 and splitter brake or clutch are applied by full line pressure, pressure feeding a torque-converter and lubrication line being reduced back to its normal forward value. In a modification, servo pressure is augmented also in low and is made accelerator responsive. Gear arrangement.-The gear, which is always driven through a hydrodynamic torque-converter 13 of the overrun-reactor type, comprises a first main unit A, consisting of two intermeshed planet trains 14, 15 which provide three reduced ratios, direct drive and reduced reverse by four band brakes 17 ... 20 and a disc clutch 16, together with the series directreduced, ratio-splitting output sun-ring train B which provides an overall low ratio and three overall ratios midway between those of the main unit A alone. The two trains 14, 15 of the main unit A each have a sun 26, 32 fast on a converter-driven input shaft 11, and two intermeshed planets, the one meshing both a sun and a ring gear, the other meshing the first planet and an additional sun. In the main unit A the rear train 15 is always effective, alone for the lowest two ratios and compounded with the front 14 for the highest two and reverse. First is by applying the brake 19 to a ring 38 of the rear train 15. The planets 35, driven by the input sun 32, act alone to drive the planet-carrier 37, fast on a frontunit output shaft 11a. Second is by applying the brake 20 to a free sun 34 which now takes the reaction of the planets 35 through the intermeshed planets 36. Third ratio is by applying the brake 17 to a free sun 27 of the front train 14, the planet-carrier of which then drives the ring 38 of the rear train 15, the output carrier 37 of which combines this motion with the direct drive of the sun 32. Fourth ratio, direct-drive, is by clutching together at 16 the free sun 27 and carrier of the front train 14. Reverse is by braking at 18 a ring 31 of the front train which reverses the rotation of the front carrier and connected rear ring 38, which motion, combining with that of the directly driven sun 32 in the rear train 15, reverses the output planet carrier 37. The series splitter unit B comprises an input ring 66 integral with the output shaft 11a of the main unit A, planets carried by a final output shaft 12 and a free sun 63 which can be held by a band brake 62 for reduced drive or disc-clutched at 61 to the planet-carrier for direct-drive. With the rear unit B in direct drive, the four ratios of the main unit A are termed first high, second high, &c., and with the unit B in reduced drive the ratios are first low, second low, &c. A power take-off gear 52, integral with the ring 31 of the front train 14, can be driven at various ratios irrespective as to whether or not the splitter unit B is in neutral. Clutches and brakes.-The two multi-disc clutches 16, 61 are each engaged by fluidpressure acting on spring-released annular pistons 44 the cylinders of which have free ball valves 173 to release centrifugal pressure when the clutch is disengaged. The brakes, e.g. 17, are all engaged by tandem-piston servos comprising one spring-released piston 92 acting directly on the band, and a free piston 97 in a separate cylinder and butting on the first piston. Engagement is by supplying pressure simultaneously to the left faces of both pistons through a common apply line 601, whilst during upshift release is by supplying an equal pressure simultaneously to the right faces of the pistons through a common release line 911. Thus, during upshift, the same pressure which applies a new brake or clutch also releases the superseded brake. Pressure supply and regulation.-Input- and output-driven pumps 81, 83 supply the system, the latter, 83, through a non-return valve 339. The input pump 81 is of the kind having a vaned member rotating in a casing 263 which is radially slidable to eccentric positions under control of fluid pressure applied to its opposite sides through lines 273, 274. The pump 81 draws from a sump through a filter 175 and cooler 305, with by-pass 312, and delivers to a line 272 acting upwards on a piston 285 of a regulator valve 179, having ports supplying the lines 273, 274 to control eccentricity of the pump 81 for maintaining constant output pressure. This pressure is normally 95 p.s.i., but is augmented to 200 p.s.i. when additional downward loading is applied to the regulatorvalve 179 through a line 298 pressurized in reverse; or to 135 p.s.i. when additional loading pressure is supplied through an optionally provided line 962 to which TV pressure is supplied in first ratios only. Delivery pressure also passes through a line 260, torque-converter feed valve 178 and restrictor 242, to feed, at a lower pressure, the torque-converter 13 and thence through a relief valve 924 to a lubrication line. In reverse, pressure in the line 298 acts at 259 to shift the torque-converter feed valve 178 left, causing the torque-converter now to be fed through a line 244, second torqueconverter feed-valve 177 and restrictor 243, the latter 243 being smaller than the restrictor 242, so that, in spite of main pressure augmentation in reverse, torque-converter pressure remains unchanged. In Fig. 2DD, not shown, the torque-converter relief valve spills direct to the sump, and the lubricating line is fed from the pressure main 272 through an additional pair of restrictor - controlling valves similar to the torque-converter feed valves 177, 178. Control pressures.-Four variable pressures are involved in the control, as follows. A "TV" (throttle-variable) pressure 468 is provided by a TV valve 188 loaded by the usual accelerator pedal 187. Kick-down pressure 440 is provided by a kick-down valve 189 operated by accelerator overtravel, the kick-down pressure being equal to full-throttle TV pressure which is equal to line pressure. Compensator pressure 465 is provided by a compensator valve 190, loaded by TV pressure to meter line pressure to a value which increases at the same rate as TV pressure, but starts at a higher minimum, 45 p.s.i. at closed throttle compared to 12 p.s.i. for TV, and rises to the same maximum, 95 p.s.i., but at half throttle instead of full throttle as for TV pressure. Governor pressure 355 is provided by an output-driven g