BI-FLUIDIC BRAKE ACTUATOR FOR A VEHICLE BRAKING CIRCUIT

Abstract: A bi-fluidic brake actuator for a vehicle brake circuit comprising a closed shell (36) divided into first and second booster chambers (38, 40) by a flexible diaphragm (42), one chamber (40) being intended to be connected, in use, to a low pressure fluid, the two chambers (38, 40) being interconnectable by way of a passage (54) which may be selectively closed by a first valve means (62, 72), the other chamber (38) being selectively connectable by a second valve means (72, 76) to a source of high pressure fluid, the flexible diaphragm being connected to a valve (18) intended to control the flow of a second fluid therethrough. The actuator further includes an electromagnetic actuator (32) adapted to operate the first and second valve means (62, 72, 74) in response to a given electrical signal.

Description: The present invention relates to a bi-fluidic brake actuator for a vehicule braking circuit and, more particularly, to a brake circuit including a hydro-­ pneumatic actuator for use with an anti-skid braking system. In the majority of anti-skid braking systems electro-­ hydraulic valves are used to control the hydraulic pressure applied to the vehicle wheels during braking. The valves are linked to a sensing circuit which determines the speed of the wheel which is being braked. If the wheel locks a signal is sent to the electro-hydraulic valve causing it to decrease the hydraulic pressure applied to the wheel brake. The brake circuit also generally includes a hydraulic booster actuated by the brake pedal and connected to a source of high pressure fluid. When the wheel being braked starts to turn again the sensing circuit causes the electro-hydraulic valve to send fluid under pressure from the booster to the brakes and thus recommence braking. A braking system of the type described above is, however, complex and costly due to the number of specialised components which it requires. It is therefore an object of the invention to provide a bi-fluidic brake actuator for a vehicle braking circuit which is adapted for use in an anti-skid mode, which is simple and which uses readily available components of conventional design. According to a first aspect of the invention there is provided a bi-fluidic brake actuator for a vehicle brake circuit comprising a closed shell divided into first and second booster chambers by a flexible diaphragm, one chamber being intended to be connected, in use, to a low pressure fluid source, the two chambers being interconnectable by way of a passage which may be selectively closed by a first valve means, the other chamber being selectively connectable by a second valve means to a source of high pressure fluid, the flexible diaphragm being connected to a valve intended to control the flow of a second fluid therethrough, characterized in that the actuator further includes an electromagnetic actuator adapted to operate the first and second valve means in response to a given electrical signal. According to a second aspect of the present invention there is provided an anti-skid braking system for a vehicle comprising a bi-fluidic actuator, the input of which is connected to a vehicle master cylinder and the output of which is connected to a vehicle wheel brake, the system further comprising sensing means for determining the speed of rotation of the wheel, electronic processor and actuator means adapted to activate the electromagnetic actuator in response to the locking of the vehicle wheel. One embodiment of the present invention will now be described by way of example with reference to the accompanying drawings, in which : - Figure 1 is a schematic layout of a vehicle brake system including a bi-fluidic brake actuator according to the present invention; and - Figure 2 is a longitudinal sectional view of the pneumatic brake actuator of Figure 1. As shown in Figure 1, the vehicle brake system comprises a master cylinder 10 adapted to be actuated by a vehicle brake pedal 12. The master cylinder, in the example shown, is a conventional, hydrostatic master cylinder but it is envisaged that a hydrodynamic or assisted brake booster may be used. When the master cylinder is operated fluid under pressure passes along brake lines 14 and 16 by way of spool valve assembly 18 (which will be described below in greater detail) to disc brake 20. The disc brake 20 comprises a toothed, or phonic wheel 22 mounted on the brake disc 24 adjacent to which is mounted an inductive sensor 26 to determine the speed of rotation of the vehicle wheel (not shown). Signals from the inductive sensor 26 are analysed by an electronic processor 28 which is connected to an electric actuator 30. If the inductive sensor 26 determines that its associated wheel has locked during a braking operation, the electronic processor 28 causes the electric actuator 30 to send a control signal to an electromagnetic valve 32 which is mounted on a bi-fluidic brake actuator 34. Turning now to Figure 2 the bi-fluidic actuator which, in the example shown, is a hydro-pneumatic brake actuator 34 comprises a vacuum shell 36 which is divided into first and second actuator chambers 38 and 40 by a flexible diaphragm 42.The flexible diaphragm 42 supports a disc 44 to which is secured one end of a push rod 46. The flexible diaphragm 42 and disc 44 are urged to the left, when viewing the drawings, by two helical springs 48, 50 mounted in the actuator shell 36. The second actuator chamber 40 includes a vacuum check valve 52 intended to be connected to a vacuum source such as the engine inlet manifold (not shown). The first and second actuator chambers 38 and 40 are interconnected by a connecting pipe 54, one end 56 of which opens into the first chamber 38 and the other end 58 is connected to the second chamber 40 by way of the electromagnetic valve 32. The electromagnetic valve 32 comprises a solenoid 60 which is actuatable in response to signals from the electric actuator 30 to displace piston 62 to the right, when viewing the drawings. Piston 62 is slideably and sealingly received in a diaphragm 64 and comprises a longitudinal bore 66 which opens into the interior of the second chamber 40 by way of a lateral opening 68 and a passage through the solenoid 60. In the illustrated rest position the two actuator chambers 38 and 40 are interconnected by way of pipe 54, the interior of electromagnetic valve 32 and the longitudinal bore 66 through piston 62. The electromagnetic valve 32 comprises a pneumatic valve 70 adapted to be operated by the displacement of piston 62. The pneumatic valve 70 comprises a disc shaped valve member 72 which is urged to the left by a spring 74 against an annular valve seat 76. The interior of the electromagnetic valve 32 forms a valve chamber 78 which is isolated from the atmosphere by valve member 72 when it is in its rest position on valve seat 76. When the solenoid 60 of the electromagnetic valve 32 is energised the piston 62 moves to the right and its open end abuts valve member 72 and thus closes the passage between the first and second actuator chambers 38 and 40. Further movement of the piston 62 to the right lifts valve member 72 from its seat 76 and permits atmospheric air to pass through valve chamber 78 and pipe 54 to the first actuator chamber 38 while the second chamber 40 remains isolated. The spool valve assembly 18 comprises a body 80 having a longitudinal bore 82 in which a spool member 24 is slideably and sealingly received and adapted to be displaced by push rod 46. The push rod 46 is received in the bore 82 and passes through an annular seal 86 which isolates the first chamber 38 from the interior of the bore 82. The interior of the bore 82 between the spool member 84 and the seal 86 is open to the atmosphere by way of passage 88. Spool member 84 comprises a longitudinal passage 90 which opens directly into bore 82 at its left hand end and, adjacent its right hand by way of lateral opening 92. The body 80 further comprises a second bore 94 in which is received a one-way check valve 96. Brake line 14 from master cylinder 10 is connected to the interior of second bore 94 and communicates with bore 82 by way of an opening 98. Brake line 16 is connected to the upstream side of check valve 96 and to the end of bore 82 by a passage 100 The hydro-pneumatic actuator as described above operates as follows. When the vehicle engine is started a vacuum is applied to the second chamber 40 by way of check valve 52 and is consequently applied to the first chamber 38 by way of pipe 54. The flexible diaphragm 42 is thus subject to equal pneumatic pressure and is urged into its illustrated rest position by the two springs 48 and 50. In the rest position the push rod 46 and spool member 84 are in their extreme leftward position and the hydraulic passage between brake lines 14 and 16 by way of longitudinal passage 90 is open. When the brakes of the vehicle are applied, in normal braking conditions, fluid under pressure passes from master cylinder 10 to the disc brake 20 by way of brake lines 14 and 16 and spool valve assembly 18. The spool member 84 is restrained from moving to the right under the effect of increasing hydraulic pressure in the bore 82 by springs 48 and 50. In the event that the wheel locks during braking the anti-skid braking system comes into operation. The inductive sensor 26 picks up the locking of the wheel and the electronic processor 28 causes the electric actuator 30 to activate the solenoid 60 of electromagnetic valve 32. The actuation of solenoid 60 causes the piston 62 to move to the right into contact with valve member 72 thus isolating the first chamber 36 from the second chamber 40. Further movement of piston 62 causes valve member 72 to lift from its seat 76 and allow atmospheric air to pass through valve chamber 78 and pipe 54 into the first chamber 38. The resulting pressure differential across the flexible diaphragm 42 causes the push rod 46 to move to the right with the flexible diaphragm 42 allowing spool member 84 to move to the right under the effect of the hydraulic pressure in bore 82. The displacement of the spool member 84 moves lateral opening 92 out of communication with opening 98 and thus interrupts the hydraulic passage between brake lines 14 and 16. Furthermore the displacement of spool member 84 causes a decrease in the braking pressure in bore 82 applied to disc brake 20 which allows the wheel to begin to turn again. The spool member 84 has sufficient available travel in bore 82 to provide a disposable volume in the bore 82 for fluid from the brake 20 which is sufficient to lower the braking pressure to a minimum level at which the wheel is assured of rotating even in the worst possible road conditions. Movement of the piston 62 can be selectively limited by controlled actuation of the solenoid 60 so that it adopts a lap position in which passage 66 is closed by valve member 72 but in which valve member 72 is still closed on its seat 76. In this position the pressure differential across diaphragm 64 is equal to that across the flexible diaphragm 42. The reaction acting to the left on piston 62 is therefore in proportion to the force exerted by the flexible diaphragm 42 and to the force generated by the solenoid. The lap position gives a greater flexibility of operation to the actuator, allowing it to function with greater precision than would be allowed by a simple on/off function. Minor variations in the signal sent to the solenoid allow the actuator pressure, and thus the braking pressure, to be selectively increased or decreased by fractionally opening or closing the valve assembly 32. Thus controlled braking pressure modulation is allowed by controlled actuation of the solenoid into and out of the lap position. Once the inductive sensor 26 has determined that the wheel has begun to turn the actuating signal to the solenoid is switched off causing the piston 62 to return to the left under the effect of spring 74 and spring 102 which acts against diaphragm 64. The return of piston 62 causes valve member 72 to close on its seat 76, interrupting the passage of air to the first chamber 38, and opens passage 66 which allows the vacuum in the second chamber 40 to be applied to first chamber 38. The flexible diaphragm 42 moves back to the left under the effect of springs 48 and 50 causing the spool member 84 to move and re-open the hydraulic passage between brake lines 14 and 16. Braking pressure is thus re-applied to the disc brake 20. If the wheel being braked locks again the anti-skid cycle described above is repeated. Displacement of the spool member 84 allows any selected braking pressure below the initial braking pressure to be adopted. In order to increase the braking pressure beyond the initial level the spool member 84 must first close to allow further fluid under higher pressure to pass to the brakes 20 from the master cylinder 10. If the brake pedal is released while the spool member 84 is in its displaced position hydraulic fluid in brake line 16 can return to brake line 14 through the check valve 96. Similarly, when the spool member 84 is in its displaced position the master cylinder is isolated from the brakes and thus an increase in pressure on the brake pedal 12 has no corresponding increase in braking pressure. It is envisaged that the two springs 48 and 50 may be replaced by a single spring or by any other resilient means which would exert a force on the flexible diaphragm 42. The determining criterion is that the return force to the left on the flexible diaphragm 42 and hence on spool member 84 is calculated to be greater than the maximum possible braking pressure necessary to lock the wheels, which pressure tends to exert a rightward force on the spool member. Thus, in the event of failure of the actuator mechanism the spool member 84 cannot move to the right during braking and interrumpt the fluid flow to the brakes below a maximum possible braking pressure. Braking of the vehicle in the event of failure of the actuator is thus assured. The push rod 46 and the spool member 84 may be formed as a single piece to thus allow for a reduction in the length of the spool valve assembly. Furthermore the illustrated annular seals on the spool member 84 may be omitted to simplify construction and reduce the sliding friction between spool member 84 and the bore 82. The fluid seepage past the spool member 84 in use would be minimal and would not have an undesiderable effect in operation. It is furthermore envisaged that the device described could be modified for controlling a pneumatic braking circuit. This would necessitate an increase in the dimensions of spool valve 18 in order that movement of spool member 84 could produce the necessary change in braking pressure. The actuator could also include a pressure responsive switch by means of which an indicator light could warn the vehicle driver of an decrease in the operating vacuum which would render the actuator unoperational. While the actuator has been described with a vacuum operated mechanism for displacing the spool member 84 it is envisaged that the flexible diaphragm be displaced by high pressure air. In such a case, in the rest position, the first and second chambers 38 and 40 would be at atmospheric pressure. Alternatively differential hydraulic pressure could be used in the actuator to displace spool member 84. Furthermore, as an alternative to selectively increasing the pressure in the first chamber 38 it is alternatively possible that the actuator be operated by selectively decreasing the pressur in the second chamber 40.

Claims: 1/ A bi-fluidic brake actuator for a vehicle brake circuit comprising a closed shell (36) divided into first and second booster chambers (38,40) by a flexible diaphragm (42), one chamber (40) being intended to be connected, in use, to a low pressure fluid, the two chambers (38,40) being interconnectable by way of a passage (54) which may be selectively closed by a first valve means (62,72), the other chamber (38) being selectively connectable by a second valve means (72,76) to a source of high pressure fluid, the flexible diaphragm being connected to a valve (18) intended to control the flow of a second fluid therethrough, characterised in that the actuator further includes an electromagnetic actuator (32) adapted to operate the first and second valve means (62,72,74) in response to a given electrical signal. 2/ Actuator as claimed in claim 1 characterised in that the first and second valve means (62,72,74) comprise a common valve member (72) and are sequentially operated by the electromagnetic actuator (32). 3/ Actuator as claimed in claim 1 or 2 characterised in that the valve (18) is a spool valve comprising a spool member (84) displaceable in a bore (82) by the flexible diaphragm (42) between a first position allowing the passage of fluid through the valve (18) from an input (14) to an output (16) and a second position interrupting the passage of fluid. 4/ Actuator as claimed in claim 3 characterised in that the movement of the spool member (84) from its first to its second position is adapted to decrease the fluid pressure at the output (16). 5/ Actuator as claimed in any preceding claim characterised in that it comprises a one-way check valve (96) arranged to allow passage of fluid from the output (16) to the input (14). 6/ Actuator as claimed in any preceding claim in which the low pressure fluid source is a vacuum source, the high pressure fluid source is atmospheric air, and the second fluid is a hydraulic fluid. 7/ An anti-skid braking system for a vehicle comprising a bi-fluidic actuator as claimed in any one of claims 1 to 6 the input (14) of which is connected to a vehicle master cylinder (10) and the output of which is connected to a vehicle wheel brake (20), the system further comprising sensing means (22,26) for determining the speed of rotation of the wheel, electronic processor and actuator means (28,30) adapted to activate the electromagnetic actuator (32) in response to the locking of the vehicle wheel.

Inventors: CADEDDU, LEONARDO
Applicants: BENDIX ITALIA S.P.A.
Application year: 1987
Main classification: B60T8
IPC codes: B60T8