GB2162267A

GB2162267A - Improvements in hydraulic anti-skid systems for vehicles

Info

Publication number: GB2162267A
Application number: GB08517320A
Authority: GB
Inventors: Glyn Phillip Reginald Farr
Original assignee: Lucas Industries Ltd
Current assignee: ZF International UK Ltd
Priority date: 1984-07-25
Filing date: 1985-07-09
Publication date: 1986-01-29
Also published as: DE3570217D1; EP0169686A2; KR860000976A; EP0169686B1; GB8418950D0; KR920006342B1; GB2162267B; EP0169686A3; JPS6137570A; GB8517320D0

Abstract

An hydraulic anti-skid braking system for a vehicle incorporates only one skid sensor and modulating unit (21). The unit is associated with one front wheel (14) and also controls operation of the brakes (15, 16) on both rear wheels (17, 18) of the vehicle. <IMAGE>

Description

1 - 65 GB 2 162 267A 1

SPECIFICATION

Improvements in hydraulic anti-skid eyetems for vehicles This invention relates to hydraulic anti-skid braking systems for a vehicle of the four wheel type in which the behaviour of a braked wheel is sensed by skid sensing means and at a skid point is operative to actuate an anti-skid 75 modulator for modulating the supply of brake applying fluid to the brake of that wheel to prevent that wheel from locking.

The aim of hydraulic anti-skid systems of the kind set forth under a skid condition is to 80 ensure that the vehicle can be steered and also that it has lateral or sideways stability.

In known anti-skid systems, for example forming the subject of GB 1 193 269, a modulator is fitted to each front wheel brake, 85 and each modulator also modulates the sup ply of fluid to the brake on the diagonally opposite rear wheel. If one modulator should fail, for example because of failure of its drive mechanism, one pair of diagonally opposed wheels can be braked fully to a skid point. On normal surfaces this provides a reasonably controlled stop because one of the front wheels is rotating, which allows the vehicle to be steered, and one of the rear wheels is also 95 rotating to provide lateral or sideways stabil ity. However, if the vehicle is on a split g surface, that is to say where the wheels on opposite sides of the vehicle are running on surfaces of which the co-efficients of friction 100 (g) are different, then the front wheel, of which the brake is controlled by the modula tor will be running on a surface of a different g from that over which the diagonally opposite wheel is running. If the front wheel provided with the modulator is on the good surface and its diagonally opposite rear is on a slippery surface, then three of the four wheels can lock, and the vehicle is liable to spin.

We are also aware of U.S. Patents Nos. 4421362 and 4229049 which disclose antiskid braking systems for vehicles of the fourwheel type. Each antiskid braking system comprises a single anti-skid modulator for modulating the supply of brake-applying fluid to the brakes on the rear wheels of a vehicle in responce to a skid signal, and means for equalising the pressures applied to the brakes on the rear wheels under such conditions. In the systems disclosed in U.S. Patents Nos. 4421362 and 4229049 full brake- applying pressure, suitably from a master cylinder, is applied at all times directly to the brakes on both front wheels of the vehicle when the master cylinder is operated, and this pressure is not modulated by the anti-skid modulator when a skid signal is operative. Thus a situation can arise in which both front wheels can lock, which would prevent the vehicle from being steered.

According to our invention an hydraulic anti-skid system of the kind set forth for a vehicle of the four-wheel type incorporates only one skid sensing means and only one anti-skid modulator, and the skid sensing means and the modulator are both associated with one front wheel, the modulator also controlling the operation of brakes on both rear wheels of the vehicle.

When the vehicle is travelling on a normal surface it follows therefore that a reasonably controlled stop is achieved because one of the front wheels is rotating, which allows the vehicle to be steered, and both of the rear wheels are also rotating to provide lateral or sideways stability. Similarly, when the vehicle is braked on a split g surface, one of the front wheels will be rotating to provide steering, and the rear wheel on the surface of higher g will also be rotating to provide lateral or sideways stability.

When the system is of the X split type with each front wheel brake interconnected to the brake on the diagonally opposite rear wheel, the rear wheel brakes are interconnected by a rear control valve which senses the pressure in the line downstream from the anti-skid modulator and is operative to isolate the brake on the front wheel not provided with the modulator from the brake on the diagonally opposite uncontrolled rear wheel and reduce the pressure applied to the brake in that uncontrolled rear wheel to that of the controlled rear.

When the system is of the 'HI' split type in which a portion, suitably one half, of the brakes on both front wheels are connected in a circuit with the brakes on both rear wheels, and the remaining portions of the two front brakes are connected in a second circuit, the single anti-skid modulator modulates the pressure in its associated front wheel half directly and half indirectly by means of the rear control valve, and the brakes on both rear wheels.

This leaves the two halves of the other front wheel brake applied normally without antiskid, as before.

Some anti-skid braking systems are illustrated in the accompanying drawings in which:

Figure 1 is a layout of a known hydraulic anti-skid brake system of the X split type; Figure 2 shows the layout of Figure 1 in a different mode; Figure 3 is a layout similar to Figure 1, but incorporating a single skid sensing means and a single modulator; Figure 4 shows the layout of Figure 3 in a different mode; Figure 5 is a layout of an hydraulic anti-skid system according to our invention; Figure 6 shows the layout of Figure 5 in a different mode; Figure 7 is a layout similar to Figures 5 and 6 but including a section through the rear 2 GB 2 162 267A 2 control valve; and Figure 8 is a layout of an hydraulic anti-skid braking system of the 'HI' split type in accordance with our invention and incorporating the control valve of Figure 7.

In the known system for a vehicle of the four-wheel type shown in the layout of Figures 1 and 2, a brake 1, 2 on each front wheel 3, 4 is interconnected to a brake 5, 6 on each diagonally opposite rear wheel 7, 8. Each front wheel 3, 4 is provided with a skid sensing and brake-pressure modulating unit 9, 10 which modulates the supply of pressure from a source of brake-applying fluid, suitably on hydraulic master cylinder (not shown), to the brake on a respective front wheel and on its diagonally opposite respective rear wheel in accordance with the behaviour of the said front wheel.

As shown in Figure 1, when the brakes are applied with the vehicle travelling over a split g surface with the wheels 3 and 8 travelling over the portion having a higher It and the wheels 4 and 7 travelling over the portion having a lowerju, the unit 10 is operable to reduce the pressure applied to the brakes 2 and 6. The wheels 4 and 8 will continue to rotate, as will the front wheel 3 which is braked on the portion of highera and in any case can be controlled by the unit 9, but the rear wheel 7 will skid. This means that both front wheels 3 and 4 can steer, and the controlled rear wheel brake 6 is applied to give lateral or sideways stability to the vehicle. 35 Similarly, as shown in Figure 2, when the portions of higher and lower tt are reversed, the unit 9 operates, and again both front wheels 3 and 4 rotate and steer, as can the rear wheel 7, but the rear wheel 8 will skid. 40 Figures 3 and 4 show the effect of omitting 105 the sensing and modulating unit 9 from the layout of Figures 1 and 2. When the brakes in the system of Figures 3 and 4 are applied with the vehicle travelling over a splitu surface and with the wheels 3 and 8 on the portion of higher g and the wheels 4 and 7 on the portion of lower tt, then the effect is similar to that described above with reference to Figure 1. In other words, the wheels 4 and 8 will rotate, but the wheels 3 and 7 will lock. However the wheel 4 rotating, on low g, provides some steering control and the wheel 8, on high a, provides good lateral stability.

If the vehicle passes onto a surface where the modulated front wheel 4 is on high IL, see Figure 4, then the wheel 4 will rotate but the wheel 8, on low g, will lock. Also the wheels 3 and 7 will lock, since there is no anti-skid control on the diagonal which interconnects the brakes 1 and 5. In this case, with the three wheels 3, 7 and 8 locked, the vehicle lacks lateral or sideways stability and the rear end of the vehicle will probably swing round.

This disadvantage can be avoided if both rear wheels are controlled from the single modulating unit 10 for the front wheel 4.

An hydraulic anti-skid braking system in accordance with this invention and in the form of an X-split, is illustrated schematically in the layout of Figures 5 and 6, and in more detail in Figure 7. As illustrated a brake 11, 12 on each front wheel 13, 14 is interconnected with a brake 15, 16 on each diagonally opposite rear wheel 17, 18 through brake lines 19, 20. The front wheel 14 is provided with a skid sensing and brakepressure modulating unit 21, which comprises the sole modulating unit incorporated in the system. The unit 21 may be of any convenient construction. The brake lines 19 and 20 are interconnected on the downstream side of the unit 21 through a rear wheel control valve 22, and an apportioning valve 23 is located in the line 20 between the modulating unit 21 and the brake 16 in the diagonally opposite rear wheel 18.

The rear wheel control valve 22, see Figure 7, comprises a housing 24 having a longitudi- nally extending bore 25 which is closed at both ends and in which works a pair of oppositely acting expander and safety pistons 26 and 27 respectively which are urged away from each other and towards the closed ends of the bore 25 by means of compression spring 28. The piston 26 is of substantially constant diameter throughout its axial length, but the piston 27 includes a portion 29 of increased diameter which works in an interme- diate portion 30 of the bore, also of similarly increased diameter.

A one-way valve 31 is operated by the piston 26 to control communication between the brakes 11 and 15 through the line 19, with the fluid in the line 19 acting on the end of the piston 27 which is remote from the spring 28.

The brakes 11 and 15, and the brakes 12 and 16, are supplied with fluid under pressure from different pressure spaces of a tandem master cylinder 32, through lines 1 9a and 20a respectively, with the line 20a leading to the modulating unit 21. A branch line 33 from the line 20a is connected into the hous- ing 24 so that fluid from that pressure space acts on a shoulder 34 at the step in diameter of the piston 27 to urge the piston 27 into engagement with the adjacent closed end of the bore 25. In addition a space 35 in the bore 25 between the pistons 26 and 27 is connected into the line 20 on the downstream side of the apportioning valve 23 so that, normally, the valve 31 is held in an open position to provide unrestricted communi- cation between the brakes 11 and 15 through the brake-line 19.

When the master cylinder is operated to apply the brakes normally fluid is supplied to the brakes 12 and 11 directly, simultaneously to the brake 16 through the apportioning 3 1 GB2162267A 3 valve 23, and to the brake 15 through the one-way valve 31 which is held open by pressure from the line 20 which is present in the space 35 to hold the piston 26 against the adjacent closed end of the bore 25.

If the braked wheel 14 starts to lock the modulator unit 21 is operative to isolate the line 20a from the front brake 12 and the line 20, and reduce the pressure applied to the front brake 12 and the pressure in line 20 applied to the rear brake 16. Since the pressure in the space 35 is also reduced, due to the pressure acting on the outer end of the piston 26, the piston 26 is displaced away from the adjacent closed end of the bore 25. Initial movement of the piston 26 in this direction permits the valve 31 to close, which isolates the rear brake 15 from the front brake 11, and subsequent movement of the piston 26 in this direction reduces the pressure ap- plied to the brake 15 by expanding the effec tive volume of the portion of the line 19, between the valve 22 and the brake 15.

When the wheel 14 recovers, the unit 21 re applies pressure to the brakes 12 and 16, and 90 the pressure applied to the brake 15 is also increased by the increased pressure in the space 35 displacing the piston 26 towards the adjacent closed end of the bore 25.

Thus on a normal surface the driver, by pressing too hard on the pedal of the master cylinder 32, can only lock the wheel 13. The three remaining wheels will rotate to enable the vehicle to be steered and to provide it with lateral stability.

When the vehicle is travelling over a split It surface and the brakes are applied with the wheels 13 and 18 travelling over the portion of higher g as illustrated in Figure 5 then, as described above, the brakes 12, 16 and 15 are released due to the operation of the unit 21 which senses the behaviour of the front wheel 14 travelling over the portion of lower g. The wheels 14, 18 and 17 will rotate to provide steering and lateral or sideways stability.

When the wheels 13 and 18 are travelling over the portion of lower g as illustrated in Figure 6, and the modulated front wheel 14 is on high g then if the brakes are applied hard enough potentially to lock the front wheel 14, the modulating unit 21 will operate to reduce the brake torque on the wheels 14 and 18 directly and, on the wheel 17 indirectly via the control valve 22. However, as the wheel 18 is on low g it will lock, but the wheel 17, on high tt, will rotate and provide lateral stability. Since front wheel 14 can be steered, the vehicle can be steered and has lateral stability.

In the event of failure of the line 20a, the pressure in the line 19 urges the piston 27 upwardly to co-operate with the piston 26 and hold the valve 31 in an open position. This ensures that the brake 15 can be applied in addition to the brake 11 on the diagonally opposite front wheel 13.

Should the line 1 ga fail, then the brakes 12 and 16 can be applied normally, with anti- lock control if the brakes are applied too hard.

In the system of Figures 5 to 7 only a single apportioning valve 23 is incorporated since this is situated upstream of the rear control valve 22. When situated upstream a reduction in the pressure in the line 20 will automatically cause a reduction in the pressure line 19 to the brake 15 with operation of the control valve 22. Thus both rear wheel brakes 15 and 16, even though they are supplied with fluid from two separate master cylinder lines 1 9a, 20a, can be apportioned with a single valve. Two such valves would be required if they were situated downstream of the control valve 22, with one apportioning valve disposed in each line 19, 20, respectively.

The hydraulic anti-skid braking system illustrated in Figure 8 of the drawings, is of "HI"split type. Half 11 a, 1 2a of the brakes on the front wheels 13 and 14 are connected in first circuit with the master cylinder 32 and with the brakes 15, 16 on the rear wheels 17 and 18, and the remaining halves 11 b and 1 2b of the brakes on the front wheels 13 and 14 are connected in a second circuit with the master cylinder 32.

The rear wheel control valve 22 is connected into both circuits.

The branch line 33 connects the master cylinder 32 and the brake halves 11 a and 1 2a into the housing 24 so that the pressure acts on the shoulder 34, and a line 50 to the brakes 15 and 16 on both rear wheels 17 and 18 is connected into the space 35 with an apportioning valve 51 being disposed between the brakes 15 and 16 and the connection between the line 50 and the space 35. The brake halves 11 b and 1 2b are interconnected through the one-way valve 31 with the pressure in that circuit acting on the outer end of the piston 27 in opposition to the force of the pressure acting over the shoulder 34.

When the master cylinder 32 is operated to apply the brakes normally, fluid is supplied to the brake halves 11 a, 11 b, and 1 2a directly, to the brakes 15 and 16 through the apportioning valve 5 1, and to the brake half 12 b through the one-way valve 31 which is held open by the pressure in the space 35 holding the piston 26 against the adjacent closed end of the bore 25.

If the braked wheel 14 starts to lock, the modulator unit 21 is operative to reduce the pressure applied to the brake halves 11 a and 1 2a, and the pressure applied to both brakes 15 and 16 on the rear wheels 17 and 18 through the apportioning valve 51. Since the pressure in the space 35 is also reduced, the pressure from the master cylinder 32 acting on the outer end of the piston 26 urges that 4 1 GB2162267A 4 piston inwardly, initially to permit the one-way valve 31 to close thereby isolating the brake half 12 b from the brake half 11 b, and subsequently reducing the pressure applied to the brake half 1 2b by expanding the effective volume of the connection between the valve 22 and the brake half 1 2b.

Thus, as in the embodiment of Figures 5 to 7, on a normal surface only the wheel 13 can be locked. The three remaining wheels will rotate to enable the vehicle to be steered, and to provide it with lateral stability.

When the vehicle is travelling over a splitu surface and the brakes are applied with the wheels 13 and 18 travelling over the portion of higher g, then as described above the brake halves 12a and 12b, and the brakes 15 and 16 are released due to operation of the unit 21 which senses the behaviour of the front wheel 14 travelling over the portion of lower It.

When the wheels 13 and 18 are travelling over portions of lower g, the wheels 13 and 18 will skid but since the pressure applied to the brake 15 on the rear wheel 17 is controlled by the modulating unit 21, the wheel 17 will continue to rotate. Since the wheel 14 can be steered, the vehicle.can be steered and has lateral or sideways stability.

The construction and operation of the brak- ing system of Figure 8 is otherwise the same as that of Figures 5 to 7, and corresponding reference numerals have been applied to corresponding parts.

Claims

1. An hydraulic anti-skid system of the kind set forth incorporating only one skid sensing means and only one anti-skid modulator, and the skid sensing means and the modulator are 105 both associated with one front wheel, the modulator also controlling the operation of brakes on both rear wheels of the vehicle.

2. A system as claimed in Claim 1, in which the system is of the X split type with each front wheel brake interconnected to the brake on the diagonally opposite rear wheel, and the rear wheel brakes are interconnected by a rear control valve which senses the pressure in the line downstream from the anti skid modulator and is operative to isolate the brake on the uncontrolled front wheel not provided with the modulator from the brake on the diagonally opposite rear wheel and reduce the pressure applied to the brake on that uncontrolled rear wheel to that of the controlled rear.

3. A system as claimed in Claim 2, in which an apportioning valve is disposed in a fine between the modulator and the brake on 125 the diagonally opposite rear wheel.

4. A system as claimed in Claim 2 or Claim 3, in which the rear control valve comprises a housing having a bore in which works an expander piston normally biassed by a spring into an advanced position to hold in an open position a one-way valve controlling communication between uncontrolled brakes on the diagonally opposite front and rear wheels, opposite ends of the piston being exposed to the pressures applied to the brake on the controlled front wheel and the uncontrolled rear wheel normally to hold the piston in an advanced position in which the one-way valve is open, a reduction in pressure applied to the brake on the controlled front wheel in response to a skid signal permitting the piston to move away from the advanced position initially causing the one-way valve to close and isolate the brake on the uncontrolled rear wheel from the brake on the uncontrolled front wheel and subsequently reducing the pressure applied to the said uncontrolled rear wheel to that applied to the brake on the controlled rear wheel.

5. A system as claimed in Claim 4, in which each front wheel brake is operated by a different supply of brake-applying pressure, and a safety piston also works in the bore in the housing, the spring acting between opposite ends to the two pistons, and the safety piston being exposed over its inner end to the pressure applied to the brake on the controlled rear wheel, over its outer end to the pressure applied to the brake on the uncontrolled front wheel, and over the area of a radial shoulder of increased diameter to the supply of brake-applying pressure which is applied to the brake on the controlled front wheel, failure of the said supply reducing the force on the piston due to pressure acting on the radial shoulder whereafter the pressure from the other supply urges the safety piston in direction to co-operate with the expander piston and hold the one-way valve in its open position.

6. A system as claimed in Claim 1, in which the system is of the 'H]' split type in which a portion of the brakes on both front wheels are connected in a circuit with the brakes on both rear wheels, and the remaining portions of the two front brakes are connected in a second circuit, and the single antiskid modulator modulates the pressure in its associated front wheel portion directly and the remaining portion indirectly by means of the rear control valve, and the brakes on both rear wheels.

7. A system as claimed in Claim 4, in which each portion of each front brake cornprises one half the brake on each respective wheel.

8. A system as claimed in Claim 4 or Claim 5, in which an apportioning valve is disposed in a line between the modulator and the brakes on both rear wheels of the vehicle.

9. A system as claimed in any of Claims 68, in which the rear control valve comprises a housing having a bore in which works an expander piston normally biassed by a spring GB 2 162 267A 5 into an advanced position to hold in an open position a one-way valve controlling communication between one of the portions of the brake on the uncontrolled front wheel, and the uncontrolled portion of the brake on the controlled front wheel, opposite ends of the piston being exposed to pressure supplied to the said one portion of the brake on the uncontrolled front wheel, and the pressure applied to the controlled portion of the brake on the controlled front wheel, which is also applied to the brake on both rear wheels, a reduction in the pressure applied to the controlled portion of the brake on the controlled front wheel in response to a skid signal permitting the expander piston to move away from its advanced position initially causing the one-way valve to close to isolate the portion of the brake on the uncontrolled front wheel from the uncontrolled portion of the brake in the controlled front wheel, and subsequently reducing the pressure applied to the said uncontrolled portion of the brake on the controlled front wheel to that of the controlled portion of the brake on that controlled front wheel.

10. A system as claimed in Claim 9, in which there are two supplies of brake applying pressure, one for each circuit, and a safety piston also works in the bore in the housing, the spring acting between adjacent ends of both pistons, and the safety piston between being exposed over its inner end to the pressure applied to the controlled portion of the brake on the controlled front wheel from a first supply of brake-applying pressure, over its outer end to the pressure applied from the second supply of brake-applying fluid to a corresponding portion of the brake on the uncontrolled front wheel, and over the area of a radial shoulder of increased diameter to the other second supply of brake-applying pressure, failure of the said second supply reducing the force in the safety piston due to pressure acting on the radial shoulder whereafter the pressure from the first supply urges the safety piston in a direction to co- operate with the expander piston are hold the one-way in its open position.

11. An anti-skid braking system for a vehicle of the four-wheel type substantially as described herein with reference to and as illustrated in Figures 5, 6 and 7 of the accompanying drawings.

12. An anti-skid braking system for a vehicle of the four-wheel type substantially as described herein with reference to and as illustrated in Figure 8 of the accompanying drawings.

Printed in the United Kingdom for Her Majesty's Stationery Office, Dd 8818935, 1986, 4235. Published at The Patent Office, 25 Southampton Buildings, London, WC2A 1 AY, from which copies may be obtained.