Anti-skid control apparatus with booster device and pressure reducing device

In a hydraulic brake system of the type having a master cylinder, rear wheel brakes, an actuator disposed between the master cylinder and the rear wheel brakes for controlling the brake pressure increase to be applied to the rear wheel brakes in accordance with the skidding condition of a vehicle wheel, control apparatus for applying a brake pressure increase controlling signal to the actuator, a hydraulic brake booster for operating the master cylinder in accordance with the brake pedal depression, a pressure power source for supplying power pressure to the booster and having the actuating pressure for the hydraulic brake booster utilized as the actuating pressure for the actuator, the improvement comprises the inter-position of a regulating device between the booster and the actuator for increasing the output pressure at the same ratio as the input pressure while the actuating pressure is below a predetermined value and for increasing the output pressure at a smaller ratio than the input pressure when the input pressure gets above the predetermined value and a piston arrangement for opening an on-off valve of the actuator for controlling the communication between the master cylinder and the rear wheel brakes when the input pressure to the actuator, that is, the output pressure of the regulating device, is below a predetermined value to increase the output pressure of the actuator at the same ratio as the input pressure and for repeating the on-off movement of the on-off valve when the input pressure of the actuator is more than the predetermined value thereby increasing the output pressure of the actuator at a smaller ratio than the input pressure thereto.

BACKGROUND OF THE INVENTION 
1. Field of the Invention 
The present invention relates to an anti-skid control apparatus and more 
particularly to an anti-skid control apparatus wherein an actuator 
utilizing a booster pressure applied by a hydraulic brake booster as the 
power pressure therefor may decrease the pressure applied to the rear 
wheel brake cylinders. 
2. Prior Art 
Conventionally, a proportioning valve is disposed between the master 
cylinder and the rear wheel brake cylinders to decrease proportionally the 
brake pressure. 
SUMMARY OF THE INVENTION 
The present invention provides an anti-skid control system wherein the 
cut-off valve of the actuator is on-off operated by decreasing the booster 
pressure being supplied to the actuator thereby controlling the 
proportional decrease of the pressure to be supplied to the rear wheel 
brakes. 
The present invention provides a first embodiment of the anti-skid control 
apparatus wherein the piston of the actuator can be reciprocated to 
decrease the wheel brake pressure relative to the master cylinder 
pressure, that is to act as a proportioning valve, even before the 
initiation of an anti-skid operation. 
The present invention provides a second embodiment of an anti-skid control 
apparatus wherein upon hydraulic failure of the front brakes, the power 
pressure supplied to the actuator is drained so as to permit the master 
cylinder to be fluidically connected to the wheel brake cylinders in a 
direct relationship, that is so as to cancel the proportioning valve 
effect. 
The present invention provides a third embodiment of an anti-skid control 
apparatus wherein upon hydraulic failure of the front brakes the booster 
pressure is directly supplied to the actuator so as to cancel the 
proportioning valve effect and to make possible the anti-skid operation 
when the rear wheels are to be locked. 
The foregoing and other objects, features and advantages of the invention 
will be apparent from the following more particular description of the 
preferred embodiments of the invention as illustrated in the accompanying 
drawings.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
The anti-skid brake control system according to the present invention as 
shown in the embodiment of FIG. 1 includes a brake pedal 3 which operates 
a conventional master cylinder 4 through a booster 7. A first conduit 15 
connects the master cylinder 4 with the front wheel brakes 5 and a second 
conduit 16 connects the master cylinder 4 with the inlet port 52 of the 
actuator 1. The rear wheel brakes 6 are connected to the outlet port 53 of 
the actuator 1 by conduit 17. 
A pump 61 is provided to supply control fluid under pressure from the 
reservoir 8 to the booster 7 to conduits 18 and 19 and thence to the power 
steering PS through the conduit 20. The conduit 21 connects the power 
steering back to the reservoir 8. The pump 61 also supplies fluid under 
pressure to the inlet 60 of the pressure decreasing device 2 through the 
conduits 22 and 23. The outlet 63 of the fluid decreasing device 2 is in 
fluid communication with the reservoir 8 by way of conduit 33, check valve 
10 and conduits 34 and 35. The outlet 62 of the pressure decreasing device 
2 is in fluid communication with the port 55 of the actuator 1 by way of 
conduits 26, 27, 28, restrictor 11 and conduit 29. The outlet port 62 of 
the fluid decreasing device 2 is also disposed in fluid communication with 
the port 54 of the actuator 1 by way of conduits 26, 27, 30, control valve 
14 and conduit 31. 
The actuator 1 is comprised of a main body having a pair of parallel 
stepped bores therein. The lower bore as viewed in FIG. 1 is provided with 
a pressure reducing piston 40 in the smaller diameter portion thereof 
which defines the pressure reducing chamber 100 at one end thereof. The 
opposite end of the pressure reducing piston 40 is disposed in engagement 
with a power piston 41 which is disposed in the larger diameter portion of 
the bore which defines a pressure chamber 97. The pressure reducing piston 
40 is provided with a projection at the right-hand end thereof which is 
adapted to protrude through the aperture in the valve seat 47 for 
engagement with the ball 45 of a cut-off valve disposed in the chamber 90 
which is in communication with inlet port 52. A spring 50 is provided in 
the chamber 90 for normally biasing the ball 45 into engagement with the 
valve seat 47 to shut-off communication between the chamber 90 and the 
pressure reducing chamber 100. 
The upper bore of the actuator 1 as viewed in FIG. 1 is provided with a 
pair of valve members having valve seats 48 and 49 between which a ball 
valve 46 is movable by means of valve pistons 42 and 43. The valve piston 
43 is disposed in operative engagement with a small power piston 44 which 
is operable in a bore defining a pressure chamber 96 in communication with 
the port 55. The valve piston 42 is provided with a through passage 105 
and the valve piston 42 is normally biased to the left as viewed in FIG. 1 
by the spring 51 located in the pressure chamber 104 which is in fluid 
communication with the pressure chamber 90 by way of passage 103. The 
chamber in which the ball valve 46 operates is connected to the conduit 17 
leading to the rear wheel brakes 6 through the port 53. The ball valve 46 
cooperates with the valve seat 49 to control communication between the 
chamber 106 and the outlet port 53 and cooperates with the valve seat 48 
to control communication of the chamber 92 with the outlet port 53. 
Chamber 92 is disposed in fluid communication with the pressure reducing 
chamber 100 through the passage 91. 
The pressure decreasing device 2 is comprised of a main body 56 having a 
central stepped bore therein closed at one end by the plug 57 in which the 
outlet port 62 is located. A spool valve piston 58 is slidably disposed 
within the bore in the body 56 and is normally biased into engagement with 
the plug 57 by the spring 59. The spool valve piston 58 and the bore in 
which it is slidable define a chamber 102 at one end thereof in 
communication with the outlet port 63 and a chamber 93 in communication 
with the inlet port 60. The spool valve piston 58 is provided with an 
internal passage 94 which communicates the inlet port 60 to the outlet 
port 62 when the piston 58 is shifted to the right as viewed in FIG. 1 and 
is also provided with an internal passage 101 which with the passage 94 
provides communication between the ports 62 and 63 when the piston 58 is 
shifted to the left and the edges 98 and 99 interrupt communication with 
the inlet port 60. 
The detailed construction of the two solenoid operated valves within the 
circle 14 in FIG. 1 is shown in FIG. 2. The control valve 14 includes 
solenoids 64 and 65 which are connected to the computer 13 by electrical 
lines 38 and 39, respectively. The computer 13 receives input signals from 
the wheel sensors 12 associated with the rear wheels by way of electrical 
lines 36 and 37. 
The armature of solenoid 64 is disposed in engagement with the piston 66 
which is operable within the chamber 89 and a second piston 67 is disposed 
in chamber 84 in alignment with the valve 66 and is normally biased toward 
the solenoid 64 by means of the spring 76. A ball valve 70 is disposed 
between the pistons 66 and 67 for movement between valve seats 72 and 73. 
The ball 70 and valve seat 72 control communication between the passage 85 
and the chamber 84 which in turn is in communication with the inlet port 
81. The ball 70 and the valve seat 73 control communication between the 
passage 85 and the outlet port 83. The inlet port 81 is connected to the 
pressure decreasing device 2 by way of conduits 26, 27 and 30 and the 
outlet port 83 is connected to the reservoir 8 by way of conduits 32 and 
35. 
The armature of solenoid 65 engages the piston 68 operable within the 
chamber 87 and a piston 69 in chamber 86 is disposed in alignment with the 
piston 68 and is normally biased toward the solenoid 65 by the spring 77. 
A ball valve 71 is disposed between the two pistons 68 and 69 for 
movement. between valve seats 74 and 75. The ball valve 71 and the valve 
seat 74 control communication between the passage 85 and the outlet port 
82 through chamber 86 and orifice 78. The ball valve 71 and the valve seat 
75 control communication between the passage 85 and the outlet port 82 by 
way of chamber 87, the small restricting hole 80 in orifice 79 and passage 
88. The outlet port 82 is connected to the port 54 of the actuator 1 by 
way of conduit 31. 
When the solenoid 64 is off and the solenoid 65 is on the inlet 81 is 
connected to the output 82 through the chamber 84, passage 85, chamber 87, 
restricting hole 80 and passage 88. When the solenoid 64 is on and the 
solenoid 65 is off the outlet 82 is connected to the outlet 83 through 
chamber 86, passage 85 and chamber 89. When both of the solenoids 64 and 
65 are on the outlet 82 is connected to the outlet 83 through the passage 
88, restricting hole 80, chamber 87, passage 85 and chamber 89. 
In operation, when the brake pedal 3 is depressed upon a normal brake 
application, the pressure of the hydraulic brake booster 7 is increased so 
as to increase the master cylinder pressure and actuate the front wheel 
brakes 5. The rear wheel brakes 6 are actuated by the increased hydraulic 
pressure through the conduit 16, inlet 52, chambers 90, 100, passage 91, 
chamber 92, outlet 53, and the conduit 17. The increase of the pressure in 
hydraulic brake booster 7 also causes the pressure in the conduits 18, 22 
to be increased. The thus increased pressure is supplied to the chamber 96 
of actuator 1 from the conduit 23 via inlet 60 of the pressure decreasing 
device 2, chamber 93, passage 940, chamber 95, outlet 62, and the conduits 
26, 27, 28 and 29. The pressure supplied to the chamber 96 is supplied 
also to the chamber 97 of actuator 1 through the conduit 30, control valve 
14, and the conduit 31. The relationship between the booster pressure 
P.sub.B of the hydraulic brake booster 7 and the master cylinder pressure 
P.sub.M is now expressed as follows: 
EQU P.sub.B = A .times. P.sub.M + b (1) 
This line may be indicated by the line l.sub.1 of FIG. 3 and the pressure 
is increased from Q to C on this line. When the booster pressure P.sub.B 
approaches the value P.sub.1, i.e., the point C, the piston 58 is 
gradually moved left because A.sub.4 -A.sub.5, A.sub.4 and A.sub.5 being 
larger and smaller sectional areas of the piston 58 of the pressure 
decreasing device 2, respectively, and S.sub.2 being the load of spring 
59. Thus, an edge 98 of the body 56 is finally brought into contact with 
an edge 99 of the piston 58 to thereby interrupt the fluid communication 
between the chambers 93 and 95, i.e., the inlet 60 and the outlet 62. The 
booster pressure P.sub.1 at this time is determined by the formula P.sub.1 
.times. A.sub.5 = S.sub.2. When the booster P.sub.B is increased more than 
P.sub.1 and the relationship between the pressure P.sub.B of the chamber 
93 and the pressure P.sub.R of the chamber 95 is as follows: 
EQU P.sub.R .times. A.sub.4 &lt; P.sub.B .times. (A.sub.4 - A.sub.5) + S.sub.2. 
then the piston 58 is moved right to disengage the edge 98 from the edge 99 
and to allow the communication between the chambers 93 and 95. Therefore, 
the pressure P.sub.R of the chamber 95 is increased. When P.sub.R .times. 
A.sub.4 is larger than P.sub.B .times. (A.sub.4 -A.sub.5) + S.sub.2, the 
edges 98, 99 are again engaged with each other so as to interrupt the 
fluid communication between the chambers 93 and 95 and the pressure 
P.sub.R is not increased before the edge 98 is disengaged from the edge 
99. As a consequence, the pressure P.sub.R is decreased from the pressure 
P.sub.B when P.sub.R .times. A.sub.4 = P.sub.B .times. (A.sub.4 -A.sub.5) 
+ S.sub.2, and applied to the chambers 97, 96 of the actuator 1. The last 
mentioned formula may be rearranged by substituting the said formula (1) 
thereinto as follows: 
EQU P.sub.R .times. A.sub.4 = (A .times. P.sub.M + b) .times. (A.sub.4 
-A.sub.5) + S.sub.2 
therefore 
##EQU1## 
The relationship between P.sub.R and P.sub.M is thus obtained. This 
relationship may be expressed by the line l 2 of FIG. 3. Now in the 
formula (2), 
##EQU2## 
may be substituted by g and h, respectively, for simplicity to get the 
following formula: 
EQU P.sub.R = g .times. P.sub.M + h (3) 
As stated above, when the booster pressure P.sub.B is increased more than 
P.sub.1, the regulating pressure P.sub.R supplied to the chamber 97 of the 
actuator 1 is increased as indicated by the line l.sub.2 of FIG. 3. 
Now, the line l.sub.3 of FIG. 3 may be expressed by the following formula: 
EQU P.sub.R .times. A.sub.3 = (P.sub.M .times. A.sub.2) + S.sub.1 (4) 
a.sub.2 : sectional area of the pressure decreasing piston 40 
A.sub.3 : sectional area of the power piston 41 
S.sub.1 : load of the spring 50 
In FIG. 3, E is an intersection of the lines l.sub.2 and l.sub.3, P.sub.0 
is the master cylinder pressure P.sub.M at E, and P.sub.2 is the 
regulating pressure P.sub.R at E. When P.sub.R is smaller than P.sub.2, 
P.sub.B is smaller than P.sub.1, or P.sub.M is smaller than P.sub.0, then 
the ball valve 45, the pressure decreasing piston 40 and the power piston 
41 of the actuator 1 are kept at the position illustrated in FIG. 1 to 
thereby separate the ball valve 45 from the valve seat 47 because P.sub.R 
.times. A.sub.3 &gt; (P.sub.M .times. A.sub.2) + S.sub.1. However, upon 
P.sub.R &gt; P.sub.2 or P.sub.M &gt; P.sub.0, P.sub.R .times. A.sub.3 is smaller 
than (P.sub.M .times. A.sub.2) + S.sub.1. Therefore, the pressure 
decreasing piston 40 and the power piston 41 are moved left to seat the 
ball valve 45 on the valve seat 47 by the spring 50. The fluidic 
communication between the chambers 90 and 100, i.e., the master cylinder 4 
and the rear wheel brakes 6 is thus interrupted. 
When it is designed that the increase of P.sub.R .times. A.sub.3 is much 
much more than the increase of P.sub.M .times. A.sub.1 by setting A.sub.3 
&gt;&gt;A.sub.1, the further pressure increase causes the power piston 41 and 
the pressure decreasing piston 40 to move right when P.sub.R .times. 
A.sub.3 + P.sub.W .times. A.sub.1 is larger than P.sub.W .times. A.sub.2 + 
P.sub.M .times. A.sub.1 + S.sub.1 (A.sub.1 : effective sectional area of 
sealing by the ball valve 45 and the valve seat 47). Accordingly, the ball 
valve 45 is released from the valve seat 47 so as to increase the pressure 
P.sub.W of the chamber 100 by admitting the pressure of the chamber 90 to 
the chamber 100. When P.sub.R .times. A.sub.3 + P.sub.W .times. A.sub.1 is 
smaller than P.sub.W .times. A.sub.2 + P.sub.M .times. A.sub.1 + S.sub.1, 
the piston 40 and the power piston 41 are moved left thereby interrupting 
the fluid communication between the chambers 90 and 100. The increase of 
the pressure P.sub.R, P.sub.M causes the repetition of the above-mentioned 
operation so as to reduce the pressure P.sub.W relatively to the pressure 
P.sub.M as seen in FIG. 4. That is to say, the actuator 1 accomplishes 
features similar to a proportioning valve. The relationship of P.sub.R, 
P.sub.M, P.sub.W at this time may be expressed by (P.sub.R .times. A.sub.3 
+ P.sub.W .times. A.sub.1 = P.sub.W .times. A.sub.2 + P.sub.M .times. 
A.sub.1 + S.sub.1). This formula may be rearranged by substituting the 
formula (3) thereinto as follows: 
EQU (g .times. P.sub.M + h) .times. A.sub.3 + P.sub.W .times. A.sub.1 = P.sub.W 
.times. A.sub.2 + P.sub.M .times. A.sub.1 + S.sub.1 
therefore 
EQU P.sub.W = {(g .times. A.sub.3 - A.sub.1)/(A.sub.2 - A.sub.1)} .times. 
P.sub.M + (h .times. A.sub.3 - S.sub.1)/(A.sub.2 - A.sub.1) (5) 
such formula may be indicated by the line l.sub.4 in FIG. 4. In FIG. 3, 
the line l.sub.5 shows the relationship of 
EQU P.sub.R .times. A.sub.3 = P.sub.M .times. A.sub.1. (6) 
the line l.sub.5 is modified to line l.sub.6 to intersect the point E. 
This l.sub.6 shows the following formula: 
##EQU3## 
In consideration of FIGS. 3, 4, formulae (2)-(5) and (7) the slope of the 
line l.sub.4, i.e., L.sub.N /K.sub.L may be obtained as follows: 
##EQU4## 
Consequently, when the size or dimension of each element is being set to 
obtain K.sub.L :L.sub. N = G.sub.J :G.sub. H, the above-mentioned 
characteristic features of the anti-skid control apparatus of this 
invention will be achieved. 
The normal release of brakes is explained hereinbelow. When the depressed 
brake pedal 3 is being released, the booster pressure P.sub.B is decreased 
to reduce the pressure within the chamber 93. Thus, the piston 58 of the 
pressure decreasing device 2 is further moved left to permit the fluid 
communication between the passage 101 and the chamber 102, so that the 
fluid pressure of the chamber 95 is drained to the reservoir 8 via 
passages 94, 101, chamber 102, outlet 63, conduit 33, check valve 10, and 
the conduits 34, 35. As a result, the pressure P.sub.R in the chamber 95 
is decreased. It is to be noted that the check valve 10 and the orifice 
10' are provided for the pressure applied to the conduit 32 upon anti-skid 
operation and not to impart any effect onto the pressure decreasing device 
2, as will be apparent hereinbelow. The pressure decrease of the chamber 
95 causes the piston 58 to move right so as to isolate the passage 101 
from the chamber 102. The pressure decrease of the chamber 93 
reestablishes the fluid communication between the passage 101 and the 
chamber 102 to decrease again the pressure of the chamber 95. Such 
repetition allows the pressure P.sub.R as well as the pressure P.sub.M to 
be decreased as the pressure P.sub.B is decreased. Therefore, the pressure 
P.sub.R, P.sub.M is decreased substantially in accordance with the line l 
2 of FIG. 3. When the pressure P.sub.R or the pressure in the chamber 97 
is decreased the pressure P.sub.M is also being decreased. However, since 
P.sub.M is larger than P.sub.W, no pressure is admitted to the chamber 90 
from the chamber 100 of actuator 1 and the pressure decreasing piston 40 
and the power piston 41 are moved left with the balance of P.sub.R .times. 
A.sub.3 = P.sub.W .times. A.sub.2. Thus, the pressure P.sub.W is decreased 
in accordance with the decrease of the pressure P.sub.R. When the pressure 
P.sub.R is below P.sub.2 or the pressure P.sub.M is decreased below the 
point E, the pressure P.sub.M is smaller than the pressure P.sub.W and the 
hydraulic pressure in the chamber 100 causes the ball valve 45 to be 
opened. Thus, the pressure P.sub.W is decreased. Simultaneously, the 
pressure decreasing piston 40 and the power piston 41 begin to move right 
until the ball valve 45 is opened to thereby keep the fluid communication 
between the chambers 90 and 100. Then, when the pressure P.sub.B is below 
P.sub.1, i.e., the pressure P.sub.B is decreased below the point C, the 
pressure P.sub.B is smaller than the pressure P.sub.R. Thus, the check 
valve 9 is opened to admit the pressure of the chamber 95 to the conduit 
24, thereby equalizing the pressure P.sub.B to the pressure P.sub.R. 
Therefore, the piston 58 of the pressure decreasing device 2 is moved 
right by the spring 59. So, all the constituting elements of the apparatus 
are positioned at the original position illustrated in FIG. 1. 
During the anti-skidding brake operation when the rear wheels are to be 
locked, the solenoid 64 is energized by the "on" signal of the computer 
13. The piston 66 is thus moved left in FIG. 2 to isolate the ball 70 from 
the valve seat 73 and to seat the same on the valve seat 72, so that the 
inlet 81 is fluidically isolated from the passage 85 while the outlet 83 
is fluidically connected to the passage 85. Consequently, the chamber 97 
of actuator 1 is fluidically isolated from the pressure decreasing device 
2 while the chamber 97 is fluidically connected to the reservoir 8. The 
hydraulic pressure in the chamber 97 is thus decreased. The pressure 
decreasing piston 40 and the power piston 41 are thus moved left by the 
pressure in the chamber 100 to thereby seat the ball 45 on the valve seat 
47 due to action of the spring 50. Such increase in capacity of the 
chamber 100 results in decrease of the pressure in the chamber 100 to 
reduce the brake application on the rear wheel brakes 6. Subsequently, the 
solenoid 65 is energized due to action of the computer 13 to move the 
piston 68 to the left. The ball 71 is released from the valve seat 75 to 
be seated on the valve seat 74. Therefore, the passage 85 is interrupted 
from the chamber 86 while the passage 85 is connected to the passage 88, 
to thereby admit the fluid pressure of the chamber 97 through the 
restricted hole 80 of the orifice 79. The speed for pressure decrease in 
the chamber 97 is thus slowed. Upon release of the rear wheel lock both of 
the solenoids 64 and 65 are deenergized to return all the constituting 
elements of the control valve 14 to the illustrated position of FIG. 2. 
Accordingly, the chamber 97 is again pressurized to move the pistons 40, 
41 to the right. The pressure in the chamber 100 is thus increased to 
apply the brakes on the rear wheels. Subsequently, the solenoid 65 is 
energized to slow the pressure increasing speed. The repetition of the 
above-mentioned movement attains the anti-skid operation. 
In the event of the power pressure failure, for instance due to the failure 
of the pump 61, the elements of the pressure decreasing device 2 are 
located at the illustrated position of FIG. 1 to decrease the hydraulic 
pressure in the chambers 96, 97 of actuator 1. The ball 45 is thus seated 
on the valve seat 47 due to the spring 50 and the pressure difference 
between the pressure P.sub.M and P.sub.W, and the ball 46 is seated on the 
valve seat 48 due to the spring 51 and the pressure difference between the 
pressure P.sub.M and P.sub.W. As a result, the pressure of the master 
cylinder 4 is supplied to the rear wheel brakes 6 through the conduit 16, 
inlet 52 of actuator 1, chamber 90, passage 103, chamber 104, passage 150 
on a piston 42, chamber 106, outlet 53 of the actuator 1, and the conduit 
17. 
As will be apparent from the foregoing description, according to the 
present invention the omission of the proportioning valve assembly to be 
disposed between the master cylinder and the wheel cylinders permits the 
air residing in the brake fluid to be easily expelled and the fluid 
quantity of the master cylinder used for brake application to be reduced, 
i.e., the brake pedal stroke to be reduced. In addition, the pressure 
decreasing device employs a spool valve, which means it is unnecessary to 
provide sealing cups and the like which have to be provided in the 
conventional proportioning valve assembly. Therefore, the elements or 
parts of the device may be diminished in number in comparison with a 
conventional system and any objectionable damage to the sealing cups or 
caused by the sealing cups may be avoided. Additionally, the response of 
the piston movement will be very quick upon the anti-skid brake operation 
since the pistons 40, 41 are being operated to close or slightly open the 
ball valve 45 relative to the valve seat 47. 
It will be understood that the pressure decreasing valve 2 may be replaced 
by a load sensing valve which varies the wheel brake pressure reducing 
point in accordance with the vehicle load, or by a deceleration sensing 
valve which varies the wheel brake pressure reducing point in accordance 
with the vehicle deceleration. 
The structure of the second embodiment shown in FIG. 5 is substantially the 
same as that of the first embodiment except for the provision of a 
differential valve assembly 107. The differential valve assembly 107 is 
provided for detecting and warning of a hydraulic failure in the front or 
rear brake line. The assembly 107 itself is well known in the prior arts. 
The differential valve assembly 107 comprises a switch 108, a body housing 
109, a sleeve 110, a piston 111, an inlet port 112 fluidically connected 
to the master cylinder 4, an outlet port 113 fluidically connected to the 
rear wheel brake 6 through the actuator 1, an inlet port 114 fluidically 
connected to the master cylinder 4, and an outlet port 115 fluidically 
connected to the front wheel brakes 5. The valve assembly 107 further 
comprises a spool valve section 116 which includes a body 117, spool lands 
118, 119 integral with the piston 111 to move in unison therewith, an 
inlet port 120 fluidically connected to the pressure decreasing device 2, 
an outlet port 121 fluidically connected to the actuator 1, and an outlet 
port 122 fluidically connected to the reservoir 8. 
The switch 108 is electrically connected to a lamp 123 by lead 126, a 
battery 124 by lead 127, then by lead 128 to ground 125 which is connected 
to the body 109 of the valve assembly 107 through the vehicle body. 
The differential valve assembly 107 is shown in the condition wherein no 
hydraulic failure has occurred, because the sectional areas of the piston 
111 are as follows: 
EQU A.sub.7 &gt; A.sub.8 - A.sub.9 &gt; A.sub.6 
a.sub.6 : sectional area of right land 132 of piston 111 
A.sub.7 : A.sub.6 plus sectional area of the sleeve 110 
A.sub.8 : sectional area of intermediate land 133 
A.sub.9 : sectional area of left land 134. 
When the front brakes including the conduit 15 have hydraulically failed, 
P.sub.M .times. (A.sub.8 - A.sub.9) is zero so that the piston 111 is 
moved left by P.sub.M .times. A.sub.6 to engage the spool land 118 and the 
projection 135 of body 117 while releasing the spool land 119 from the 
projection 136 of body 117. Therefore, the inlet port 120 of spool section 
116 is fluidically interrupted from the outlet port 121 while the outlet 
port 121 is connected to the outlet port 122. As a result, the fluidic 
communication between the pressure decreasing device 2 and the actuator 1 
is interrupted while the fluidic communication between the actuator 1 and 
the reservoir 8 is established to drain the pressure in the chambers 96, 
97 to the reservoir 8, as in the power pressure failure. Thus, the ball 46 
is released from the valve seat 49 to be seated on the valve seat 48, and 
the ball 45 is seated on the valve seat 47. The master cylinder pressure 
P.sub.M is directly supplied to the rear wheel brakes 6 through the inlat 
52 of the actuator 1, chamber 90, passage 103, chamber 104, passage 105 of 
piston 42, chamber 106, and the outlet 53. 
The regulating pressure of the pressure decreasing device 2 is not admitted 
to the actuator 1 since the spool land 118 of the spool section 116 blocks 
the outlet port 121 from the inlet port 120. Therefore, the regulating 
pressure is applied only in the chamber 95 of the device 2, the conduits 
26, 131 and 25. The booster pressure P.sub.B is, thus, not decreased and 
the hydraulic brake booster 7 is operated in the normal way. 
The left movement of the piston 111 of valve assembly 107 activates, the 
switch 108 to light lamp 123. After recovery from the front brake failure 
the brake application returns the piston 111 to its original position 
since P.sub.M .times. (A.sub.8 - A.sub.9) is larger than P.sub.M .times. 
A.sub.6. 
When the rear wheel brakes including the conduit 16 hydraulically fail, the 
piston 111 will be moved right to activate the switch 108. The spool land 
119 is at this time, separated from the body projection 135. Thus, the 
regulating pressure of the device 2 is admitted to the actuator 1 while no 
pressure is supplied to the reservoir 8. Consequently, the brake booster 7 
will be operated in the normal manner. 
The spool section 116 may be disposed within the conduit 22 in place of the 
conduits 131 and 27 if it can diminish the pressure of the chambers 97, 
96. In addition, the spool section 116 may be operated by activation of 
the switch 108 in place of mechanical movement of the piston 111, for 
instance, it may be constructed as an electric solenoid valve. 
In the general structure of the third embodiment shown in FIG. 6, the spool 
section 116 of FIG. 5 is omitted and the pressure decreasing device 2 is 
connected to the differential valve assembly 107. 
If the front wheel brakes including the conduit 15 have hydraulically 
failed, the piston 111 is moved to the left together with a rod 140 
integral therewith. Thus, the piston 58 of the pressure decreasing device 
2 is forced to move left. It is to be noted that (P.sub.M .times. A.sub.6 
+ S.sub.2) is larger than P.sub.B .times. A.sub.5. Thus, the edge 99 of 
the piston 58 is completely released from the edge 98 of the body 56 to 
thereby permit fluid communication between the chambers 93 and 95. The 
booster pressure P.sub.B is, therefore, applied directly to the actuator 
1. The relationship between the booster pressure P.sub.B and the master 
cylinder pressure P.sub.M will be shown by the line l 1 in FIG. 3, and the 
balancing relationship between the pressure P.sub.B and P.sub.M to the 
pistons 40, 41 will be shown by the line l 3. Therefore, (P.sub.B .times. 
A.sub.3) is larger than (P.sub.M .times. A.sub.2 + S.sub.1), to thereby 
keep the pistons 40, 41 in the illustrated position of FIG. 6. The master 
cylinder pressure P.sub.M is thus applied to the rear wheel brakes 6. 
Under this situation, when the rear wheels are to be locked, the hydraulic 
pressure in the chamber 97 is decreased as in the anti-skid brake 
operation explained hereinabove. Accordingly, the power piston 41 and the 
piston 40 are moved to the left to seat the ball 45 on the valve seat 47 
and to decrease the pressure in the chamber 100. The reciprocating 
movement of the pistons 40, 41 achieves the anti-skid brake operation as 
will be apparent from the previous description. 
If the rear brakes including the line 16 have hydraulically failed, the 
piston 111 is moved right to activate the switch 108. At this time, no 
effect is imparted to the piston 58 of the pressure decreasing device 2 so 
that the brake booster 70 may be operated in the usual way.