Patent GB-1484360-A (GB)
Title: Hydraulic control systems
IPC: F16H61/02
Filed: 1974-10-23
Abstract: 1484360 Change-speed control ROBERT BOSCH GmbH 23 Oct 1974 [23 Oct 1973] 45809/74 Heading F2D Relates to a control circuit for hydraulically engaged clutches K1, K2 and brakes B1 ... B3, selecting three forward and one reverse ratios in an automatic transmission on a motor vehicle, having a manual selector valve 15 and 1-2 and 2-3 spring-biased shift relay valves 35, 31, controlled by fluid pressure supplied by two respective pilot valves 28, 33, operated by solenoids energized by an automatic electronic circuit (not described), responding to output speed and engine load, the shift valves cooperating with shuttle valves 18, 21. The invention is directed mainly to ensuring that, in the event of failure of the electronic system it will still be possible to select first ratio and reverse, and, if failure occurs at high speed, the system will automatically downshift to first ratio, which, being a one-way ratio in the automatic mode, will be inconsequential. In addition establishment of reverse above a predetermined low forward speed, is inhibited. In a modification, Fig. 2, not shown, third ratio is established by electronic failure. Ratio clutches and brakes.-In the planetary gear, not shown, a forward clutch K1 is engaged for all forward ratios. A brake B1 is applied in second and third ratios; a brake B2 in second only; whilst a brake B3 is applied only for reverse and two-way manual first. Automatic first (setting 3 of the manual valve) is one-way, requiring no brake. A direct-reverse clutch K2 is engaged for third ratio and reverse. Fluid pressure supply and regulation.-A single pump 11 supplies the system through a pressure regulator 14 having a differentially landed spool loaded rightwards, for pressure decrease, by inlet pressure supplied through a restrictor 66, and leftwards, for pressure increase, by springs 65 and pressure supplied to a chamber 64 by a pilot regulator valve 24, which receives line pressure 22 in all positions of the manual selector valve 15, and regulates it to a delivery port 25a under the spring-opposed loading of a solenoid, variably energized by an electronic circuit, not described, responding to engine throttle setting and output speed. Automatic shift valves.-Relay shift valves 35, 31, associated respectively with first-second and second-third ratios, are shifted, in opposition to springs 72, 71, by fluid pressure supplied to respective end-chambers 34, 29 by twoposition pilot valves 33, 28 actuated by solenoids energized under control of the abovementioned automatic electronic circuit. Although two-way pilot valves may be used, those shown close single exhausts 0 when their solenoids are energized, causing build up of pressure in relay-actuating lines 34, 29 fed through restrictors 32, 27 from the pilot regulator valve line 25. Shift sequence.-In the initial starting condition the solenoids of both pilot valves 28, 33 are de-energized, exhausting both relay valve ports 34, 29, so that the springs 72, 71 shift the respective relay valves 35, 31 left and right (the valve 31 is shown in its leftward, pressure-biased position). In the automatic setting 3 of the manual valve 15, line pressure at its port 51 feeds the forward clutch K1 constantly, but is blocked at port 52 of the relay valve 35 so that no other clutch or brake is engaged and oneway automatic first ratio is established. 1-2 upshift occurs when the electronic circuit energizes the solenoids of both pilot valves 31, 33, to pressure bias the relay valve 35 to the right and 31 left. Pressure 51 now passes through the relay valve 35 and port 36 to the brake B1, and, through ports 38, 42 of the relay valve 31, to the brake B2, thus establishing second ratio. 2-3 upshift occurs when the electronic circuit de-energizes the solenoid of the pilot valve 28, opening the relay valve port 29 to exhaust, and permitting the spring 71 to shift the relay valve 31 to the right, exhausting the brake B2 and supplying pressure through the ports 52, 36 of the relay valve 35, the shuttle valve 18 and ports 41, 45 of the relay valve 31, to the direct-reverse clutch K2. With the forward clutch K1 and brake B1 still engaged, third ratio is now established. Manual settings.-In manual 1 the manual valve 15 pressurizes a port 69, and, provided that the pilot valve 33 is de-energized, causing leftward movement of the relay valve 35, line pressure is supplied through ports 70, 47 and the shuttle valve 21 to engage the brake B3 for two-way first ratio, the shuttle valve 21 closing to the exhausted port 16b of the manual valve. In R setting the manual valve 15 blocks the forward clutch port 51, exhausts 69 and feeds ports 16a, 16b, the latter, 16b, feeding the lowreverse brake B3 through the shuttle valve 21, which closes the exhausting line 70, 69, whilst the former 16a, feeds, through the shuttle valve 18, the inlet port 41 of the relay valve 31, which, providing that it has been moved to the right by de-energizing the pilot valve 28 to exhaust the port 29, directs pressure through the ports 41, 45 to engage the direct-reverse clutch K2. Since de-energizing the pilot 28 occurs only below a predetermined speed, reverse cannot be established above that speed, and both first and reverse can be selected by the manual valve 15 even in the event of complete failure of the electronic system. In Fig. 2, not shown, the restricted lines to the pilot valves 28, 32 are fed by a separate constant pressure regulator valve (55) which also feeds an hydrodynamic torque converter (56), and, through a restrictor (57) the pilot regulator 24, the outlet of which has a separate filter screen (58) opening into the main reservoir 12 below the filter screen 13 of the pump 11. The energization pattern of the pilot valves 28, 33 is changed, both being energized for first ratio, 33 only for second, neither for third or reverse and both for manual 1. In this case electronic failure in automatic mode establishes third ratio.