Patent GB-1402837-A (GB)
Title: Hydraulic power boost mechanism
IPC: B60T13/16
Filed: 1974-02-18
Abstract: 1402837 Fluid-pressure servomotor systems BENDIX CORP 18 Feb 1974 [23 March 1973] 7306/74 Heading G3P [Also in Division F2] A hydraulic boost mechanism 10 for a master cylinder 16 of a vehicle braking system comprises a spool valve member 42 actuable to control hydraulic pressure in a working chamber 76 housing a power piston 48, the piston 48 having an output plunger 115 projecting through a wall 96 into a control chamber 124; a pedal operated input plunger 126 also projects into the control chamber 124 and is slidable therein for generating pressure in the control chamber 124 to displace the valve member 42 to connect the working chamber 46 to a pump 12 to operate the power piston 48; a compensating valve device 140 incorporates a pin 156 having one end 160 connected to the plunger 126 whereby when the plunger 126 is in the released position the valve device 140 is held open to connect the reservoir of the pump 12 to the control chamber 124 to compensate for loss or gain in volume of fluid in the control chamber 124. The mechanism 10, as shown, has an inlet port 28 connected to the pump 12, an outlet port 30 connected to a steering gear 14 of the vehicle and an exhaust port 32 connected to the pump reservoir. The valve member 42 which in its unactuated position shown disconnects ports 28, 32 has a reduced end portion 64 exposed to the pressure in a cavity 70 which is connected to the control chamber 124 via a passageway 136. Thus in the unactuated condition of mechanism 10 the fluid pressure in chambers 46, 124 is essentially zero since the working chamber 46 is connected to exhaust port 32 via a passage 100, radial passage 82 in member 42, axially extending grooves 84 in a relief valve 86 disposed in a central passage 58 in member 42, the passage 58 and radial passages 60, whilst the control chamber 124 is connected to exhaust port 32 via the passage 100 and the passage 144, the valve device 140 being held open by inter-engagement of pin 156 and plunger 126. When the plunger 126 is actuated the pin 156 is displaced to the left to allow valve device 140 to close under the influence of a spring 148, and the displacement of the plunger 126 generates a pressure in control chamber 124 which pressure acts on member 42 to move it leftwards and connect working chamber 46 to the pump 12 whereby to move plunger 115 and piston 46 leftwards to operate the master cylinder 16. The movement of member 42 with respect to input plunger displacement is in the ratio of the areas between the end portion 64 and the end of input plunger 126, as represented by diameter 'D'. As shown, the area of plunger 126 is larger by about two to one. Also the area of plunger 126 is approximately twice that of output plunger 115 so that displacement of fluid in chamber 124 causes the output plunger 115 to move at twice the rate of the input plunger 126. Under normal conditions a gap 'B' between plungers 115, 126 is not taken up completely before piston 48 and with it plunger 115 is moved by the pressure in chamber 46 but should the pump 12 fail or valve member 42 stick the plunger 115 may be driven mechanically by plunger 126. Pressure generated in the control chamber 124 under these conditions will cause opening of relief valve 86 to connect chamber 124 to exhaust port 32. When the plunger 126 is released after a master cylinder actuation the pressure in chamber 124 is reduced creating a differential pressure across valve device 140 which opens to connect chamber 124 to the pump reservoir. The amount of movement of pin 156 which is pivotally mounted at its end 158 may be adjusted by adjusting means 162.