GB2069639A - Improvements in hydraulic anti-skid braking systems for vehicles - Google Patents

Abstract

In an hydraulic anti-skid braking system for vehicles a supply of operating fluid from a supply (16) to a vehicle brake is modulated by a modulator assembly in accordance with skid signals from skid sensing means (6), and an hydraulic pump (3) incorporating a plunger (21) working in a bore has a working chamber (33) which is in communication with the modulator assembly to control brake application following skid correction. The pump plunger (21) works in a bore of a sleeve (23), and the sleeve (23) is axially movable in a bore in a housing (1) between an operative position and an inoperative position. When the sleeve (23) is in the operative position the plunger (21) can co-operate with a drive mechanism (22) so that the plunger (21) is reciprocated in the bore to draw fluid from a reservoir (35) and into the working chamber (33) through an inlet port (36) during an induction stroke and during a compression stroke to force it through an outlet port to the means (2) for controlling brake application. When the sleeve (23) is in the inoperative position the plunger (21) is prevented from co-operating with the drive mechanism (22) so that the pump (3) is disabled. <IMAGE>

Description

SPECIFICATION Improvements in hydraulic anti-skid braking systems for vehicles This invention relates to hydraulic anti-skid braking systems for vehicles of the kind in which a supply of operating fluid from a supply to a vehicle brake is modulated by a modulator assembly in accordance with skid signals from skid sensing means, and an hydraulic pump incorporating a plunger working in a bore has a working chamber which is in communication with means adapted to control brake re-application following skid correction.

An anti-skid braking system of the kind set forth is disclosed in our G.B. Patent Application No. 79 28209. In that system the pump is operable only to re-pressurise an expansion chamber following correction of a skid. This is achieved by the provision of disabler means for preventing the plunger of the pump from engaging with a drive until a dump valve, disposed between the expansion chamber of a modulator assembly for modulating the supply of operating fluid to the brake and reservoir for fluid, has opened.Specifically the pump plunger is of differential outline adapted to work in a stepped bore with the end of greater area exposed to the operating fluid and the end of the smaller area being engagable with the drive, and the disabler means comprise a spring for urging the smaller end of the plunger away from the drive in combination with the pressure in the working chamber which is generated by the operating pressure and which acts over an area of the plunger equal to the difference between opposite ends of the plunger. In such a construction elastomeric seals are provided between the two portions of the plunger and the complementary portions of the bore. Also a separate one-way valve is provided, through which fluid is drawn into the working chamber from the reservoir for fluid.However the elastomeric seals can be prone to excessive wear and the provision of a separate one-way valve adds to the cost of the pump.

According to our invention in an hydraulic anti-skid braking system of the kind set forth the pump plunger works in the bore of a sleeve, and the sleeve is axially movable in a bore in a housing between an operative position and an inoperative position, when the sleeve is in the operative position the plunger can co-operate with a drive mechanism so that the plunger is reciprocated in the bore to draw fluid from a reservoir and into the working chamber through an inlet port during an induction stroke and during a compression stroke to force it through an outlet port to the modulator assembly, and when the sleeve is in the inoperative position the plunger is prevented from co-operating with the drive mechanism so that the pump is disabled.

The sleeve is provided with opposed first and second faces of which the first face is exposed to the pressure of fluid in an expansion chamber, at least when the dump valve is closed, and the second face is exposed to the pressure from the supply, so that the sleeve is held in the inoperative position, when a dump valve is closed, by the incompressibility of the fluid in the expansion chamber, reduction in the pressure applied to the first face permitting the sleeve to move into the operative position in which the plunger can co-operate with the drive mechanism.

When the pump is disabled the plunger is prevented from co-operating with the drive mechanism by the engagement of a shoulder on the sleeve with a complementary shoulder on the plunger.

Preferably a spring also acts to urge the sleeve towards the inoperative position, and a second spring acts to urge the plunger towards the drive mechanism with respect to the sleeve.

Preferably the first and second faces of the sleeve are of smaller and greater areas respectively.

Preferably the plunger is hollow and incorporates at least one radial port through which the reservoir can communicate with the working chamber when the sleeve is in the inoperative position, and during the induction stroke when the pump is operating, the port being closed by the sleeve during the compression stroke. This eliminates the separate one-way inlet valve of the previous design and allows the elastomeric seals to be eliminated since any leakage between the plunger and the sleeve returns to the reservoir.

Our invention is particularly suitable for use in anti-skid braking systems in which the modulator assembly incorporates the expansion chamber to which the working chamber of the pump is connected, and the dump valve is disposed between the expansion chamber and the reservoir for fluid, the dump valve being movable by the skid sensing means between a normally closed position in which the expansion chamber is pressurised so that the modulator assembly is held in a first position permitting operating fluid to be supplied to the brake and an open postion when the skid signal is received whereby the pressure in the expansion chamber is reduced so that the modulator assembly can move into a second position to cut-off communication between the supply and the brake and subsequently reduce the pressure of fluid supplied to the brake.In such a construction the outlet port is connected to the expansion chamber.

On embodiment of our invention is illustrated in the accompanying drawings in which: Figure 1 is a transverse section through a combined modulator and skid assembly for an hydraulic anti-skid braking system suitable for motor-cycle; and Figure 2 is a section on the line 2-2 of Fig.

1.

The assembly illustrated in the drawings comprises a housing 1 incorporating a modulator assembly 2. an hydraulic pump 3 and a pressure dump valve 4. A longitudinally extending shaft 5 projecting at opposite ends from the housing 1 is coupled at one end to the wheel and at the other end carries skid sensing means 6 in the form of a flywheel assembly 7 which is enclosed within a cylindrical guard 8 carred from the adjacent end of the housing 1. The dump valve 4 and the skid sensing means 6 form the subject of our copending G.8. Patent Application No.

8005332 of even date and need not be described further herein.

The modulator assembly 2 comprises a bore 9 in which works a piston 10 which is normally urged Into an operative position by a spring 11. In this position the piston 10 urges a spring-loaded ball 1 3 away from a seating 14 to place an inlet port 1 5 for connection to an hydraulic master cylinder 1 6 in communication with an outlet port 1 7 for connection to a brake associated with the wheel which drives the shaft 5. The operative position is defined by the engagement of the piston 10 with a stop face 18 on a member 1 9 in which the seating 14 is incorporated. The dump valve 4 is in communication with that end of the bore 9 which is remote from the valve 13, 14.

The pump 3 comprises a plunger in the form of a hollow piston 21 of which the closed end is engageable with a drive mechanism comprising a ring 22 which is freely rotatable on a eccentric portion of the shaft 5.

The piston 21 is reciprocable in the bore of a stepped sleeve 23 which, in turn, is slidable in a stepped bore 24 in the housing 1. The end of the sleeve 23 which is of greater area is slidably and sealingly guided on a spigot 25 of a plug 26 which forms a closure for the outer end of the bore 24. A stepped annular face 27 defined by a portion of the sleeve 23 which is disposed between the bore 24 and the spigot 25 is exposed to the pressure at the inlet port 1 5. A stepped shoulder 28 is also provided at the change in diameter of the sleeve 23, and the shoulder 28 is of smaller area than the face 27.

A compression spring 29 acts on the sleeve 23 to urge it towards the plug 26. A compression spring 30 acts on the plunger 21 to urge it towards the ring 22. but it is held clear of the ring 22 by the engagement of a radial flange 31 on the inner end of the plunger 21 with a shoulder 32 on the sleeve 23.

A secondary working chamber 40 is defined by the annular volume bounded by the bore 24, the sleeve 23, and seals between corresponding portions of the sleeve 23 and the bore 24. The stepped shoulder 28 is exposed to pressure in the secondary working chamber 40.

A primary working chamber 33 is defined between the plunger 21, the sleeve 23 and the plug 26. The working chamber 33 communicates with the secondary working primary chamber 40 through a one-way valve 34 of the band type which encircles the sleeve 23, and with a reservoir 35 for fluid through radial ports 36 in the plunger 21, when the plunger 21 is in its inoperative position and during an induction stroke. The' reservoir 35 communicates with the ports 36 through a sealed chamber 37 in the housing 1 and in which the ring 22 is housed. The shaft 5 is therefore lubricated by the fluid.

An expansion chamber 20 is defined by that portion of the bore 9 between the piston 10 and the dump valve 4, the secondary working chamber 40, and a passage 41 between the dump valve 4, the secondary working chamber 40, and the said portion of the bore 9.

When the wheel is rotating in a "brakesoff" condition, the dump valve 4 is closed to cut-off communication between the working chamber 33 and the expansion chamber 20, and the reservoir 35 through a passage 38 in the housing 1. The sleeve 23 is held in an inoperative retracted position in engagement with the plug 26 by the spring 29, since the spring 29 is stronger than the spring 30. The plunger 21 is, in turn, held by the sleeve 23 out of engagement with the eccentric mounted ring 22.

The reservoir 35 is in open communication with the working chamber 33 through the chamber 37 and the radial ports 36, and the spring-loaded ball 1 3 is held away from its seating 14 by the spring 11, so that the brakes are in open communication with the reservoir for the master cylinder 16, which may be the same as, of different from, the reservoir 35.

During normal braking fluid from the master cylinder 1 6 is applied to the brakes through the ports 1 5 and 1 7 and the space between the ball 1 3 and the seating 14. This pressure also acts over the area of the stepped face 27 to tend to urge the sleeve 23 towards an advance operative position in which the pump plunger 21 can engage with the ring 22.

However, since the fluid in the expansion chamber 20 is trapped, a pressure is developed which acts over the area of the shoulder 28 to resist movement of the sleeve 23. The sleeve 23 is therefore unable to move towards the ring 22 so that it remains in its inoperative position and the pump 3 remains disabled. In addition since the area of the shoulder 28 is smaller than the area of the face 27, the same trapped fluid develops in the expansion chamber 20 a pressure which is higher than the pressure from the master cylinder 11, and this higher pressure acts on the piston 10 to hold it against the stop 1 8. This ensures that the ball 1 3 is held away from the seating 14 in opposition to pressure from the master cylinder.

If the angular deceleration of the braked wheel exceeds a predetermined value, the skid sensing member is operative to open the dump valve 4. This relieves the pressure trapped in the expansion chamber 20, by connecting it to the reservoir 35.

Reduction in pressure in the chamber 20 causes the piston 10 to be unbalanced so that it moves to permit the ball 1 3 to engage with the seating 14 which cuts off the supply from the master cylinder 1 6 to the brake. Further movement of the piston 10 in the same direction expands the brake volume to reduce the pressure applied to the brake.In addition the force on the sleeve 23 comprising the reaction of the trapped fluid acting over the area of the face 28 is reduced so that the pressure from the master cylinder 1 6 acting over the area 27 urges the sleeve 23 into its operative position in engagement with a stop 39 defined by an abutment for the spring 29 and in which position the plunger 21 can engage with the ring 22 so that the fluid is pumped in a closed circuit from the reservoir 35, and to which it is returned.In particular, during an induction stroke in which the plunger 21 can move relatively away from the plug 26 towards the ring 22, fluid is drawn into the primary working chamber 33 through the ports 36 and, during the compression stroke in which the plunger 21 is moved in the opposite direction, the ports 36 are first covered as the plunger 21 moves back into the sleeve 23, whereafter the fluid is pumped into the secondary working chamber 40 through the one-way valve 34, from whence it is returned to the reservoir 35. This continues whilst the dump valve 4 remains open.

Upon closure of the dump valve 4 at the termination of the skid signal, communication between the expansion chamber 20 and the reservoir 35 is cut-off so that fluid from the pump 3 progressively increases the pressure in the expansion chamber 20 and urges the piston 10 towards its operative position to reduce the brake volume and thereby increase the pressure applied to the brake. The pressure developed in the expansion chamber 20 also acts over the area of the shoulder 28.

This continues until the pressure applied to the brake attains that which caused the previous corrected skid to occur. The piston 10 them moves to engage with the stop 18, thereby opening the valve 1 3 . Thereafter, the pump 3 further increases the pressure'acting over the shoulder 28 to apply, together with the spring 29, a force to the sleeve 23 which overcomes the force of the pressure from the master cylinder 11 acting over the greater area of the face 27. The sleeve 23 is subjected to a net force which moves it relatively away from the ring 22 to withdraw the plunger 21 from its engagement with the ring 22, thereby disabling the pump 3.

Upon release of the brake fluid is drawn through the ports 36 and the one-way valve 34 and into the expansion chamber 20 as the sleeve 23 is urged fully into its inoperative position shown in the drawings, under the influence of the return spring 29.

Claims (9)

1. An hydraulic anti-skid braking system of the kind set forth in which the pump plunger works in the bore of a sleeve, and the sleeve is axially movable in a bore in a housing between an operative position and an inoperative position, and when the sleeve is in the operative position the plunger can cooperate with a drive mechanism so that the plunger is reciprocated in the bore to draw fluid from a reservoir and into the working chamber througn an inlet port during an induction stroke and during a compression stroke to force it through an outlet port to the.

modulator assembly, and when the sleeve is in the inoperative position the plunger is prevented from co-operating with the drive mechanism so that the pump is disabled.

2. A system as claimed in Claim 1, in which the sleeve is provided with opposed first and second faces of which the first face is exposed to the pressure of fluid in an expansion chamber, at least when a dump valve is closed, and the second face is exposed to the pressure from the supply, so that the sleeve is held in the inoperative position, when the dump valve is closed, by the incompressibility of the fluid in the expansion chamber, reduction in the pressure applied to the first face permitting the sleeve to move into the operative position in which the plunger can cooperate with the drive mechanism.

3. A system as claimed in Claim 1 or Claim 2, in which, when the pump is disabled, the plunger is prevented from co-operating with the drive mechanism by the engagement of a shoulder on the sleeve with a complementary shoulder on the plunger.

4. A system as claimed in any of Claims 1 to 3, in which a first spring also acts to urge the sleeve towards the inoperative position, and a second spring acts to urge the plunger towards the drive mechanism with respect to the sleeve.

5. A system as claimed in any preceding claim, in which the first and second faces of the sleeve are of smaller and greater areas respectively.

6. A system as claimed in any preceding claim, in which the plunger is hollow and incorporates at least one radial port through which the reservoir can communicate with the working chamber when the sleeve is in the inoperative position and during the induction stroke, the port being closed by the sleeve during the compression stroke.

7. A system as claimed in any preceding claim in which the modulator assembly incorporates an expansion chamber to which the working chamber of the pump is connected, and a dump valve is disposed between the expansion chamber and the reservoir for fluid, the dump valve being movable by the skid sensing means between a normally closed position in which the expansion chamber is pressurised so that the modulator assembly is held in a first position permitting operating fluid to be supplied to the brake and an open position when the skid signal is received whereby the pressure in the expansion chamber is reduced so that the modulator assembly can move into a second position to cut-off communication between the supply and the brake and subsequently reduce the pressure of fluid supplied to the brake.

8. A system as claimed in Claim 7, in which the outlet port is connected to the expansion chamber.

9. An hydraulic anti-skid braking system substantially as described herein with reference to and as illustrated in the accompanying drawings.