JP2556676B2 - Hydraulic control device for anti-skidding device - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a vehicle that controls a brake fluid pressure transmitted to a wheel cylinder of a wheel brake device according to a rotating state or a skid state of a wheel of a vehicle or the like. TECHNICAL FIELD The present invention relates to a hydraulic pressure control device for an anti-skid device.

[Prior Art and Problems Thereof] As this type of device, the wheel is arranged between a master cylinder and a wheel cylinder of a wheel brake device and receives a command from a control unit that evaluates a skid state of the wheel. There is known a hydraulic control device for an anti-skid device including a hydraulic control valve that controls a brake hydraulic pressure of a cylinder. For example, when the wheel is composed of a pair of front wheels and a pair of rear wheels, a hydraulic control valve is provided for each of the front and rear wheels, that is, four hydraulic control valves are provided, and brakes are independently provided. There is no problem if the hydraulic pressure is controlled. Alternatively, for both rear wheels, there is no problem even if the brake hydraulic pressure is commonly controlled by one hydraulic pressure control valve according to the skid state of the rear wheel having the smaller rotational speed.

However, in the above case, since three or four hydraulic control valves are used, the entire apparatus (generally unitized with a reservoir or the like) is increased in size and weight. Further, the hydraulic control valve is expensive, which increases the cost.

Therefore, for example, it is conceivable to control the brake fluid pressures of both front wheels by two fluid pressure control valves in an X-type piping system and commonly control the brake fluid pressures of the respective rear wheels. . However, when the friction coefficient μ is greatly different on both sides of the road surface, there is a risk that the rear wheels on the opposite side (diagonal position) to the front wheels on the high μ side road surface may be locked. In this case, the directional stability of the vehicle is lost, which is very dangerous.
It is also conceivable to control the brake fluid pressure by interposing a pressure reducing proportional control valve (proportioning valve) on the rear wheels, but the brake fluid pressure is proportional to the hydraulic pressure on the input side of this valve. As it rises, the fear of locking still persists.

In view of the above problems, the applicant has two hydraulic control valves (2
For the purpose of providing a hydraulic control device for an anti-skid device that can eliminate the risk of locking the rear wheels while reducing the size and weight of the device as a channel) Each of them is provided with the hydraulic pressure control valve, and when any one of these control valves starts control, the brake fluid pressure of at least the lower one of the rear wheels is adjusted according to the lower brake fluid pressure of the front wheel. A hydraulic pressure control device for an anti-skid device has been proposed, which is characterized in that the brake hydraulic pressure of the rear wheels on the same side as the front wheels is controlled. That is, pressure selecting means for outputting a pressure according to the lower one of the brake hydraulic pressures of both front wheels controlled by the hydraulic pressure control valve is provided between the wheel cylinders of both front wheels and the wheel cylinders of both rear wheels. Arranged. Further, the command from the control unit for controlling each hydraulic control valve is formed by evaluating the skid state of each front wheel.

However, in the above configuration, when braking strongly on a uniform road surface, it is assumed that the front and rear wheels are equipped with the same type of tires, and the braking force of the front and rear wheels is set so that the front wheels lock before the rear wheels. It is distributed appropriately,
If the above prerequisites are not satisfied, for example, when using spiked tires only on the front wheels on ice or snowy road surfaces, or if a chain is equipped and the rear wheels are normal tires, then the rear wheels are the reverse of the front wheels. You can lock it first. However, in the above configuration, the brake pressure is not controlled even if only the rear wheels tend to lock, so under such conditions, the control of the front wheels is started and the brake pressure may drop below the lock pressure of the rear wheels. Unless the rear wheels are unlocked, the directional stability of the vehicle cannot be maintained.

Even when the front and rear wheels are equipped with the same type of tire, when the friction coefficient of the brake lining decreases due to the so-called temperature fade phenomenon of the front wheel braking device and the lock pressure of the front wheels rises abnormally, especially on high μ road surfaces. At the time of strong braking, the brake pressure of the rear wheels is increased to a pressure proportional to the brake pressure of the front wheels by the pressure reducing proportional valve, and finally reaches the lock pressure or more, so that the rear wheels can lock before the front wheels. This causes the same problem as described above.

FIG. 7 is a graph showing such a problem. FIG. 7A shows a change in wheel speed when the brake is applied, FIG. 7B shows a command signal of the control unit, and FIG.
FIG. C shows changes in the brake fluid pressure of the wheels. That is, when the vehicle runs on a uniform road surface and the front and rear wheels are equipped with the same type of tire, when the brake pedal is depressed at time t ₀ , the brake fluid pressure P of the front wheels is as shown by the solid line in FIG. 7C. Rise and control the brake hold command at time t _1.
Units are generated. That is, the control signal EV and the control signal EV for each solenoid of the supply valve and the discharge valve that constitute the hydraulic control valve
Among AV, AV is still “0”, but EV is “1”. As a result, the brake fluid pressure P on the front wheels is kept constant. The control unit issues a brake slack command at time t ₂ . That is, the control signal EV is still "1", but the control signal AV changes from "0" to "1". This makes it
As shown in FIG. C, the brake fluid pressure P on the front wheels decreases. At time t ₃ , the control signal AV becomes “0”, but EV is still “1”
Is. This keeps the brake fluid pressure constant.
When the control signal EV also becomes “0” at time t ₄ (the control unit issues a brake re-loading command), the brake fluid pressure rises again. When the control signal EV becomes “1” again at time t ₅ , the brake fluid pressure is kept constant. After that, similarly, the brake fluid pressure P rises in the stair-filled state, and at time t ₆ , the control signal AV becomes “1” when the control signal EV is “1”. As a result, the brake fluid pressure P decreases. As described above, the brake fluid pressure P of the front wheels changes with time, but the brake fluid pressure P ′ of the rear wheels also decreases and changes according to the change of the brake fluid pressure P of the front wheels. Since the pressure reducing proportional valve is interposed, the brake fluid pressure P'of the rear wheels slightly lags the brake fluid pressure P of the front wheels due to the hysteresis phenomenon, but this delay is ignored in FIG. 7C. . In addition, the brake fluid pressure is affected by the hysteresis phenomenon of the pressure reducing proportional valve and the effect of the rigidity of the rear wheel brake device, that is, the wheel cylinder (a large amount of brake fluid is required to increase the brake fluid pressure by a certain amount in the low pressure range). The fluctuation range of P'is smaller than the fluctuation range of the brake fluid pressure P of the front wheels as shown in the figure.

Due to the change in the brake fluid pressure as described above, the wheel speeds V and V ′ of the front wheels and the rear wheels change as shown by the solid line in FIG. 7A and decrease without locking to perform desired anti-skid control. .

When the front wheel is equipped with a chain or the temperature fade phenomenon occurs, the lock pressure of the front wheel rises as described above, but in FIG. 7C, the brake fluid pressure P of the front wheel changes as shown by a broken line. That is, it fluctuates at a higher level than the solid line. On the other hand, the brake fluid pressure P'of the rear wheels
As shown by the broken line, the rear wheel lock limit pressure R is exceeded, and even if the brake fluid pressure P of the front wheels is reduced thereafter, the fluctuation range is smaller and the lock is not released. As shown by the broken line in FIG. 7A, the front wheels are not locked, but the rear wheels are locked. As a result, not only the anti-skid control is not properly performed, but also the directional stability is lost, which is extremely dangerous.

In view of the above problems, the applicant has two hydraulic control valves (2
In order to provide a hydraulic control device for an anti-skid device that can eliminate the risk of locking the rear wheels in any case while reducing the size and weight of the device as a channel)・
The unit evaluates the skid state of each of the pair of front wheels and the pair of rear wheels and logically evaluates the evaluation result of one of the front wheels and the evaluation result of one of the rear wheels on the same side as the front wheel. To issue a command to control the first hydraulic control valve, and logically combine the evaluation result of the other of the front wheels and the evaluation result of the other of the rear wheels on the same side as the front wheel. A hydraulic pressure control device for an anti-skid device, which is characterized in that a command for controlling the second hydraulic pressure control valve is issued in combination, has been previously proposed (Japanese Patent Application No. 60).
-17178).

In the above configuration, when one rear wheel first shows a locking tendency, the slack signal activates the hydraulic control valve for one front wheel on the same side as the slack signal. This reduces the braking force on both rear wheels and one front wheel. Similarly, when the other rear wheel has a tendency to lock first, the slack signal activates the hydraulic control valve for the other front wheel on the same side as the slack signal.
This reduces the braking force on both rear wheels and the other. Therefore, for example, when the loosening signal is output from one rear wheel,
Even if the braking force of the other rear wheel also decreases, if a slack signal is output from this rear wheel, the hydraulic control valve for the front wheel on the same side as this may be actuated. (No signal is output), the braking force also decreases and the braking distance increases. Also, during control, the driver's body sways back and forth, causing a bad feeling.

[Problems to be Solved by the Invention]

The present invention has been made in view of the above problems, and in any case eliminates the risk of locking the rear wheels, while making the control distance shorter than that of the conventional configuration and improving the feeling during braking. An object is to provide a control device.

[Means for solving the problem]

The above-mentioned object is to provide a pair of front wheels and a pair of rear wheels, each of which has a wheel cylinder connected to each other by X pipes, and is arranged between the first hydraulic pressure generating chamber of the master cylinder and one of the front wheels. A first hydraulic pressure control valve provided to control the brake hydraulic pressure of the wheel cylinder of the front wheel; disposed between the second hydraulic pressure generation chamber of the master cylinder and the wheel cylinder of the other front wheel of the front wheels A second hydraulic control valve for controlling the brake hydraulic pressure of the wheel cylinder of the front wheel; a control unit for evaluating a skid state of the wheel and issuing a command for controlling the first and second hydraulic control valves; According to the lower one of the brake fluid pressures of the front wheels, which is arranged between the wheel cylinders of the front wheels and the wheel cylinders of the both rear wheels and is controlled by the first and second hydraulic pressure control valves. Pressure In the hydraulic control device for an anti-skid device, the pressure selecting means for outputting the brake oil pressure in the skid state in which the brake hydraulic pressure of the one rear wheel is to be reduced and the other rear wheel is The brake fluid pressure of the front wheel on the same side as the one rear wheel is reduced by the logical sum of the logical product "not in skid state" and the skid state of the front wheel on the same side as the one rear wheel. And a hydraulic pressure control device for an anti-skid device, which is characterized in that a lowering command for causing the control is formed.

[Action]

A control signal indicating the logical product of the skid state in which the brake fluid pressure of one rear wheel should be reduced and the other rear wheel not being in the skid state, that is, the evaluation result of the rear wheel that has reached the skid state first. Then, the braking force of the front wheel on the same side is reduced by the logical sum of the skid state of the front wheel on the same side as the one rear wheel.
The pressure selecting means also reduces the braking force of the rear wheel on the same side, and prevents the rear wheel from being locked. Also, since the other rear wheel is diagonally arranged with the front wheel, the braking force is similarly reduced. Therefore, even if the other rear wheel has a tendency to lock, the braking force is reduced to finish in a short time, and when the one rear wheel is in a skid state in which the brake fluid pressure should be reduced, the other rear wheel is Even if the wheels reach a condition where they should reduce brake fluid pressure,
Since the braking force of the front wheels on the same side as the rear wheels is not reduced, the braking distance can be minimized.
Also, in the past, the braking force of the front wheel on the same side was also reduced by the skid condition of the other rear wheel, so the change in the braking force of the vehicle as a whole (decreasing further during the decrease and increasing from this decrease) increases. The inertial force acts on the driver each time, causing the body to sway back and forth greatly and the feeling to be bad, but the present invention can improve this. Further, even if the front wheels are faded or the chain is equipped, the rear wheels can be reliably prevented from being locked and the steering stability can be maintained.

〔Example〕

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

FIGS. 1 to 6 show an embodiment of the present invention. In FIG. 1, the master cylinder (1) is connected to a pedal (2), and one of the hydraulic pressure generating chambers has a conduit (3), It is connected to the wheel cylinder (7a) of the right front wheel (6a) via the pressure control valve (4a) and the pipe line (5). The line (5) is connected to the first input boat (9) of the valve device (8) which will be described in more detail below. The first output port (10), which normally communicates with the first input port (9) of the valve device (8), is the wheel cylinder of the left rear wheel (11b) via the pipe line (13) and the pressure reducing proportional valve (32b). Connected to (12b).

The other hydraulic pressure generating chamber of the master cylinder (1) is
6), the hydraulic control valve (4b), and the pipe (17), and is connected to the wheel cylinder (7b) of the left front wheel (6b). The line (17) is further connected to the second input port (18) of the valve device (8). Normally the second input port (18) of the valve device (8)
The second output port (14) communicating with is connected to the wheel cylinder (12a) of the right rear wheel (11a) via the pipe line (15).

The hydraulic pressure control valves (4a) (4b) are composed of supply valves (33a) (33b) and discharge valves (34a) (34b) as switching valves, respectively, and discharge ports of the discharge valves (34a) (34b) are connected to a conduit ( It is connected to the reservoirs (25a) (25b) via 60a) (60b). The reservoirs (25a) (25b) consist of pistons (27a) (27b) and weak springs (26a) (26b) slidably fitted to the main body,
This reservoir chamber is connected to the suction port of the hydraulic pump (20). As is well known, the hydraulic pump (20) includes a main body (21) that slidably accommodates a piston, an electric motor (22) that reciprocates the piston, and check valves (23a) (23b) (24a) (24b). The discharge port, that is, the check valve (23a) (23b) side is connected to the conduits (3) (16).

Wheel speed detectors (28a) (28b) (29a) (29b) are arranged on the wheels (6a) (6b) (11a) (11b), respectively.
From these detectors, a pulse signal having a frequency proportional to the rotation speed of the wheels (6a) (6b) (11a) (11b) is obtained and applied to the control unit (31) as an input.

The control unit (31) includes a first evaluation circuit (35a) and a first logic circuit (36) as surrounded by a chain line.
a), a second evaluation circuit (35b) independent of the first evaluation circuit (35a) but having the same circuit configuration, and having the same circuit structure as the first logic circuit (36a) but having an input signal Different second logic circuit (36b) and motor drive circuit (37)
Made of. Each of these circuits (35a) (35b) (36a)
(36b) (37) will be described in detail later, but the output terminals of the wheel speed detectors (28a) (29b) are connected to the input terminals a ₁ and a ₂ of the first evaluation circuit (35a), respectively. input terminal a ₁ of 2 evaluation circuit (35b) ', a _2' respectively of the wheel speed detector output terminal (28a) (29b) is connected. That is, the first evaluation circuit (35a) receives the wheel speed signal of the right front wheel (6a) and the wheel speed signal of the left rear wheel (11b), evaluates these signals, respectively, and evaluates the evaluation results by the first logic circuit (36).
a) and logically combine these as will be described later to generate control signals EV and AV at output terminals C ₁ and C ₂ , respectively. The second evaluation circuit (35b) receives the wheel speed signal of the left front wheel (6b) and the wheel speed signal of the right rear wheel (11a),
Each of these is evaluated, and the evaluation results are logically combined as described later, and output terminals C ₁ ′ and C ₂ ′ are
To generate control signals EV 'and AV', respectively. These control signals EV, AV, EV ', AV' are transmitted to the 2-position electromagnetic switching valve (33a) (3
4a), (33b) and (34b) solenoids Sa, Sa ', Sb, Sb'
Is supplied to. 2-position solenoid switching valve (33a) (34a), (33
b) (34b) takes one of two positions A, B or C, D depending on whether EV, AV, EV ', AV' to the solenoid is low "0" or high "1". Is configured. That is, when the control signals EV and EV 'are "0",
The switching valves (33a) (33b) serving as the supply valves are set to the position A so that the passages on both sides are communicated with each other, and when EV and EV 'are "1", they are connected to B.
Take the position of and cut off the passages on both sides. Control signal AV, AV ′
When is "0", the switching valve (34a) (34b) as a discharge valve
Takes the position of C and connects the master cylinder (1) side with the wheel cylinders (7a) (7b) side, but when AV and AV 'are "1", it takes the position of D and the master cylinder (1)
Side and the wheel cylinder (7a) (7b) side are cut off, and the wheel cylinder (7a) (7b) side and the reservoir (25a) (25b)
Communicate with the side. That is, when the control unit (31) issues a brake slack command, the control signal E
V, EV 'and AV, AV' are all "1", EV and EV 'are "1" for constant brake command, and AV, AV' are "0", and EV, EV 'are for brake putting command. And AV, A
Both V'are "0". Control unit (31)
The motor drive circuit (37) in (1) issues a brake slack command, and thereafter continuously generates a motor drive signal Q during the anti-skid control, and this signal Q causes the motor (22) to
Are driven next to the front wheel (6a) (6b) wheel cylinders (7a) (7
Details of the valve device (8) which receives the brake fluid pressure from b) will be described with reference to FIG.

A stepped through hole (61a) is formed in the main body (61) of the valve device (8) in the axial direction, and a lid (62) has a seal ring (35) interposed in the right end opening in FIG. Screwed,
A lid (36) is screwed to the left end opening with a seal ring (37) interposed. The lid (62) (36) has the above-mentioned first input port (9) and second input port (18), respectively.
Are formed.

Seal ring (39) (40) in the center of stepped hole (61a)
The piston (38) fitted with is fitted slidably,
The shaft-like parts (41a) (41b) integrally formed at both ends cross the output chambers (50a) (50b) and are in contact with the valve balls (47a) (47b) in the normal illustrated state. . Valve ball (47a) (4
7b) is located in the input chamber (49a) (49b) and the spring (48a) (4b)
It is urged toward the valve seats (46a) (46b) by 8b). One valve seat (46b) is formed on the inner wall of the main body (61), while the other valve seat (46a) is formed on the valve seat member (45) press-fitted into the tubular member (44). . Cylindrical member (4
The above-mentioned output chamber (50a) is formed inside 4), and the first output port (1) is formed through the hole (44a) formed in this peripheral wall.
It is in communication with 0). The other output chamber (50b) directly communicates with the second output port (14).

The spring bearing rings (42a) (42b) are fitted in the shaft-like parts (41a) (41b) of the piston (38) in a loosely fitted state, and between them and the step part of the stepped hole (33). Springs (43a) (43b) are stretched and urge the spring bearing rings (42a) (42b) toward the center. In the normal state shown in the drawing, the flange portions of the spring receiving rings (42a) (42b) are the step portions (58) of the main body (61).
a) It is in contact with (58b). In this state, the piston (3
Only a small gap is formed between the main part (59) of 8) and the spring receiving rings (42a, 42b). This regulates the neutral position of the piston (38) in the stepped hole (33).

The hole formed in the center of the body (32) has a switch (5
2) is fitted and fitted with a seal linder (53), and its actuator is fitted in a groove (51) formed on the outer circumference of the piston (38) at the neutral position. The lead wire (54) from the switch (52) is connected to the + terminal of the battery (57) via the contact (55) of the b-contact relay and the alarm lamp (56). That is, the contact (55) is closed and the switch (52)
The alarm lamp (56) is configured to light up when the actuator of is activated. The contact (55) of the b-contact relay is opened when the anti-skid device shown in FIG. 1 is activated and is normally closed. This is, for example, a relay that is excited by pressure when the hydraulic pump (20) is activated.

When the piston (38) is in the normal neutral position shown, the valve balls (47a) (47b) are separated from the valve seats (46a) (46b) by the shaft-shaped parts (41a) (41b). (49a) (4
9b) and the output chamber (50a) (50b) are connected. Further, in FIG. 1, the pipelines (3) and (5) and (16) and (1
The check valves (19a) and (19b) are connected to 7).
Although the forward direction is from the wheel cylinder side to the master cylinder side, the switching valves (33a) (33b) (34
Since a) and (34b) communicate with each other at the A and C positions via the throttle holes, the wheel cylinder (7a) ( 7b) (12a) (12b) is provided to circulate the pressure liquid to the master cylinder (1).

Since the first and second evaluation circuits (35a) and (35b) have the same structure, only one of the first evaluation circuits (35a) will be described with reference to FIG.

First, second evaluation circuit (35a) (35b) each front wheel evaluation circuit section (35a ₁₎ (35b ₁₎ and the rear wheel evaluation circuit section (35a ₂₎
(35b ₂ ), but these evaluation circuit sections are similarly constructed.

The signals from the wheel speed detectors (28a) (28b) are supplied to the wheel speed calculators (72a) (72b), and these calculators (72a) (72
A digital or analog output proportional to the wheel speed is obtained from b), and the approximate vehicle speed generators (76a) (76b), the slip signal generators (77a) (77b), and the wheel acceleration / deceleration calculator or differentiator (73a) ) (73b).

The approximate vehicle speed generators (76a) (76b) receive the outputs of the wheel speed calculators (72a) (72b) and generate outputs equal to the wheel speed until the wheel deceleration reaches a predetermined value. When the deceleration of is equal to or more than the predetermined value, the wheel speed at that time is set as an initial value, and thereafter, an approximate vehicle body speed that decreases at a predetermined gradient is generated. Approximate vehicle speed generator (76a) (7
The output of 6b) is supplied to the high output selector (71), and the higher output selected by this is the slip signal generator (77a) (7).
Wheel speed calculator (72a) (72b)
When the former is smaller than the latter by a predetermined amount or more, a slip ratio signal S is generated. The predetermined amount is set, for example, as a reference rate of 15%, and the percentage of the wheel speed with respect to the approximate vehicle speed is 100
(Slip rate) is compared with the reference rate. If the slip rate is greater than the reference rate, the slip rate signal S
Occurs.

Differentiators (73a) (73b) are wheel speed calculators (72a) (72
The output of b) is received and differentiated with respect to time, and the differentiated output is supplied to the deceleration signal generators (75a) (75b) and the acceleration signal generators (74a) (74b). The deceleration signal generator (75a) (75b) has a deceleration reference value (for example, -1.5g) set, and this is compared with the output of the differentiator (73a) (73b) to determine the differentiator (73a (73b), that is, when the wheel deceleration is greater than the deceleration reference value, the deceleration signal generators (75a) (75b) generate the deceleration signal -b.
Further, an acceleration reference value (for example, 0.5 g) is set in the acceleration signal generators (74a) (74b), and this is compared with the output of the differentiator (73a) (73b), and the differentiator ( 73a) (7
When the output of 3b), that is, the acceleration of the wheel is larger than the acceleration reference value, the generators (74a) (74b) generate the acceleration signal +
b is generated.

The output terminals of the acceleration signal generators (74a) (74b) are the logical negation input terminals of the AND gates (92a) (92b) (shown with a circle. The same applies below) and the logical negation of the AND gates (90a) (90b). The input terminals are connected to the input terminals of the AND gates (90a) (90b) and the first input terminals of the OR gates (94a) (94b) via the OFF delay timers (88a) (88b). The output terminals of the AND gates (90a) (90b) are the input terminals of the pulse oscillators (78a) (78b) and the AND gates (93a) (9
3b) input terminal, pulse generator (78a) (78
The output terminal of b) is connected to the logical negation input terminals of AND gates (93a) (93b). Acceleration signal generator (74a)
(74b), OFF delay timer (88a) (88b), pulse oscillator (78a) (78b), OR gate (94a) (94b) and AND gate (90a) (90b) (93a) (93b) The generators (81a) and (81b) are configured to generate a pulse signal for slowly increasing the brake pressure. Consider the time during which the brake pressure should be slowly increased during anti-skid control, as described later. Then, the delay time of the off delay timer (88a) (88b) is set. The output terminals of the AND gates (93a) (93b) are connected to the second input terminals of the OR gates (94a) (94b) described above.

The output terminals of the deceleration signal generators (75a) (75b) are connected to the OR gates (94a) (9b) via the off delay timers (97a) (97b).
4b) is connected to the third input terminal, and the output terminals of the slip signal generators (77a) (77b) are connected to the above-mentioned AND gate (92a).
a) (92b) is connected to the other input terminal, and the output terminals of the AND gates (92a) (92b) are connected to the above-mentioned OR gate (94a).
a) Connected to the fourth input terminal of (94b). Output terminal of OR gate (94a) (94b) and AND gate (92a) (9
The signals EV ₁ , EV ₂ , AV ₁ and AV _{2 at} the output terminal of 2b) are supplied to the first logic circuit (36a) or the second logic circuit (36b) in the subsequent stage.

The output terminals of the AND gates (92a) (92b) are further connected to the off delay timers (95a) (95b).
The output terminals of a) and (95b) are connected to the motor drive circuit (37). The delay time of the timer (95a) (95b) becomes "1" when the output of the AND gate (92a) (92b) becomes "1" first, and then becomes "1" during the anti-skid control even after it becomes "0". "Is set long enough to last.

The second evaluation circuit signal EV ₁ in the first evaluation circuit in the same manner in (35b) (35a), EV 2, AV 1, the signal EV ₁ corresponding to _{AV 2 ', EV 2',} AV 1 ', AV 2 'Is formed and these are combined in the first or second logic circuit (36a) (36b).

The first and second logic circuits (36a) and (36b) are respectively 4A
As shown in FIGS. 4B, the circuit configurations are the same, but the input signals are different.

That is, in the logic circuits (36a) and (36b), the outputs EV ₁ and EV ₁ ′ are supplied to _one input terminals of the first OR gates (100a) and (100b), respectively, and the other input terminals have the first EV ₁ and EV ₁ ′, respectively.
The outputs of the AND gates (101a) (101b) are supplied. Outputs EV ₂ ′ and EV ₂ ′ are supplied to one input terminals of the AND gates (101a) (101b), respectively, and outputs AV ₁ Z are output to the other input terminals via the knot gates (102a) (102b). ,
AV ₁ Z'is supplied.

The outputs AV ₁ and AV ₁ ′ are supplied to _one input terminal of the second OR gates (103a) (103b), and the second input is supplied to the other input terminal of the second OR gate (103a) (103b).
The outputs of AND gates (104a) (104b) are supplied. Outputs AV ₂ and AV ₂ ′ to one input terminal of the second AND gate (104a) via the NOT gates (105a) and (105b), respectively.
Is supplied, and outputs AV ₂ ′ and AV ₂ are supplied to the other input terminal. OR gate (100a) (100b) (103a) (103b)
Output terminals of the amplifiers (106a) (106b) (107a)
Supply valve (33a) (33b) in FIG. 1 via (107b)
Are connected to the solenoids Sa, Sb and the solenoids Sa ', Sb' of the discharge valves (34a) (34b). That is, the amplifier (106
a) Control signals EV, AV, EV ', AV' amplified by (106b), (107a), (107b) are solenoids Sa, Sa ', Sb, Sb'.
Is supplied to.

FIG. 5 shows a motor drive circuit (37), which is composed of an OR gate (114) and an amplifier (110). The AV ₂ Z signal from the first evaluation circuit (35a) is supplied to the first input terminal of the OR gate (114), and the AV ₁ Z signal is supplied to the second input terminal. The AV ₁ Z signal is formed by the skid state of the right front wheel (6a) and the AV ₂ Z signal is formed by the skid state of the left rear wheel (11b). The same applies to the second evaluation circuit (35b). the AV ₁ Z by skid state of the left front wheel (6b) signal is formed 'signal, AV ₂ Z by skid condition of the right rear wheel (11a)', fourth, third input of each of these OR gates (114) Connected to the terminal. The second and fourth input terminals are respectively connected to the first and second logic circuits (36
a) Connected to (36b) as described above. OR gate (11
The output of 4) is amplified by the amplifier (115) and becomes a Q signal which becomes a signal for driving the motor (22) in FIG.

The embodiment of the present invention is configured as described above. Next, this operation will be described.

It is now assumed that the brake pedal (2) is depressed to apply a sudden brake. In addition, the wheels (6a) (6b) (11a) (1
1b) is assumed to be equipped with the same type of tires and traveling on a road surface with a uniform friction coefficient. Signals EV, AV, E from the control unit (31) at the beginning of braking
Since V'and AV 'are both "0", the switching valve (33a)
(34a), (33b) and (34b) are at the positions A and C, respectively. Therefore, the pressure liquid from the master cylinder (1) is supplied to the pipe lines (3) (16), the switching valves (33a) (34a), (33b) (34b).
It is supplied to the wheel cylinders (7a) (7b) of the front wheels (6a) (6b) through the pipes (5) (17). This pressure liquid is further applied to the first input port (9), the second input port (18), the input chambers (49a) (49b), the output chambers (50a) (5) of the valve device (8).
0b), the first output port (10), the second output port (14),
It is also supplied to the wheel cylinders (12a) (12b) of the rear wheels (11a) (11b) through the pipes (13) (15) and the pressure reducing valves (32a) (32b). As a result, the wheels (6a) (6b) (11a) (1
The brake is applied to 1b). The pressure reducing valves (32a) (32b) perform known operations, and when the pressure on the input side is below a predetermined value,
Although it is transmitted to the output side as it is, when it is equal to or higher than a predetermined value, the pressure is reduced at a substantially constant rate and transmitted to the output side.

Wheels (6a) (6b) (11a) due to increased brake fluid pressure
When (11b) reaches a predetermined deceleration (in this case, they are simultaneously reached for the sake of clarity of explanation. The same applies to the slip ratio below), that is, the evaluation circuits (35a) and (35b) reduce the speed. Speed signal generator (75a) (75b)
(The first evaluation circuit (35a) is representatively indicated.)
Generates a deceleration signal -b, EV ₁ , EV ₂ , EV ₁ ', EV ₂ '
The signal becomes "1", and the output EV of the logic circuit (36a) (36b),
EV 'becomes "1". Therefore, the switching valves (33a) (33b) are
The position is switched to the position of, and the master cylinder (1) side and the wheel cylinder (7a) (7b) side are disconnected. As a result, the brake fluid pressure in the wheel cylinders (7a) (7b) (12a) (12b) is kept constant.

When the wheel deceleration becomes smaller than a predetermined value, the deceleration signal -b disappears, but the input to the OR gates (94a) (94b) is still held at "1" by the off delay timers (97a) (97b). . After that, when the wheel reaches a predetermined slip rate, or when this slip rate is reached during the generation of the deceleration signal, or when this slip rate is reached during the generation of the deceleration signal, the slip signal generator (77a) in FIG. (77b) generates a slip signal S. Acceleration signal generator (74a)
Since (74b) has not yet generated the acceleration signal + b, the outputs of AND gates (92a) and (92b) AV ₁ , AV ₂ , AV ₁ ', A
V ₂ ′ also becomes “1”, and the output AV of the logic circuit (36a) (36b),
AV 'becomes "1" together with EV and EV'. As a result, the switching valves (33a) (33b), (34a) (34b) are switched to the B and D positions. Pipe lines (3) and (5) and (16) and (17) are cut off, but pipe lines (5), (60a) and (17)
And (60b) are communicated.

The brake fluid in the wheel cylinders (7a) (7b) of the front wheels (6a) (6b) flows into the reservoirs (25a) (25b) through the pipelines (5) (60a), (17) (60b). In addition, the rear wheels (11
The brake fluid in the wheel cylinders (12a) and (12b) of a) and (11b) is also pipe lines (15) and (13), the output ports (14) and (10) of the valve device (8), and the output chambers (50a) and (50b). , Input room (49a)
(49b), input port (18) (9), pipeline (17)
(5), (60b) (60a) through the reservoir (25a) (25
b) flows in. This releases the brakes on the front wheels (6a) (6b) and the rear wheels (10a) (10b).

The hydraulic pump (20) starts driving when the signals AV ₁ , AV ₂ , AV ₁ ′ and AV ₂ ′ become “1”, and the reservoirs (25a) (25b)
Since it is sent to the pipe lines (3) and (16) with an almost equal intake amount, the hydraulic pressure on both sides of the piston (38) in the valve device (8) decreases at about the same speed. Therefore piston (38)
Does not move from the neutral position and moves the valve balls (47a) (47b) into the valve seat (46
It has been separated from a) and (46b).

When the wheel speed recovers and reaches a predetermined acceleration, acceleration signal + b is generated from the acceleration signal generators (74a) (74b). As a result, the output EV ₁ , E of the evaluation circuit (35a) (35b)
V ₂ , EV ₁ ′, and EV ₂ ′ become “1”, and the logic circuit (36a) (36
The outputs EV and EV 'in b) are "1". The brake fluid pressure on the wheels is kept constant.

When the acceleration signal + b disappears, the pulse oscillator (78a) (7
8b) is activated and outputs EV ₁ , EV ₂ , EV ₁ ′, EV ₂ ′ are “1”, “0”, for the delay time of the OFF delay timer (88a) (88b).
It changes in a pulse shape such as “1”, “0” .... As a result, the outputs EV and EV 'of the logic circuits (36a) and (36b) are also changed, and the brake fluid pressure of the wheels is increased on the stairs.

Hereinafter, similar control is repeated, and when the vehicle reaches a desired speed or stops, the depression on the brake pedal (2) is released. Along with this, brake fluid is supplied from the wheel cylinders (7a) (7b) (12a) (12b) to each pipeline,
Valve device (8), switching valve (4a) (4b), check valve (19a) (1
Return to the master cylinder (1) through 9b). Therefore, the brake is released.

In the above description of the action, it is assumed that EV ₁ , EV ₂ , EV ₁ ′, EV ₂ ′, or AV ₁ , AV ₂ , AV ₁ ′, AV ₂ ′ become “0” or “1” at the same time. However, when the friction coefficient of the road surface on which the wheels (6a) (6b) (11a) (11b) travel greatly differs, for example, when the friction coefficient of the road surface on the wheel (6a) (11a) side is relatively small ( The so-called split road surface) will be described next.

The right wheel (6a) (11
The deceleration signal -b or the slip signal S of a) shall be generated at the same time. That is, since the outputs EV ₁ , EV ₂ ′ and AV ₁ , AV ₂ ′ of the evaluation circuits (35a) (35b) become “0” and “1” at the same time, the output EV or AV of the first logic circuit (36a). Is EV ₁ , AV
_It becomes “0” and “1” in synchronization with 1, and the switching valves (33a) (34a)
As a result, the brake fluid pressure of the right front wheel (6a) is held constant or reduced. Since the left front wheel (6b) and the left rear wheel (11b) on the high μ side are not yet in a lock tendency, the output EV ', A
V ′ is “0”, the switching valves (33b) and (34b) are not operated, and the brake fluid pressure of the front wheels (6b) is still rising.

Therefore, in FIG. 2, the hydraulic pressures of the input chamber (49a) and the output chamber (50a) on the right side of the piston (38) are lower than those on the left side, so that the piston (38) moves to the right. As a result, the left valve ball (47b) is seated on the valve seat (46b) by the spring force of the spring (48b). On the other hand, the valve ball (47a) on the right side is pushed by the shaft-like portion (41a) in a direction further away from the valve seat (46a). The input chamber (49a) on the right side of the piston (38) is in communication with the output chamber (50a), but the input chamber (49b) on the left side and the output chamber (50b) are blocked. That is, the liquid supply from the master cylinder (1) to the wheel cylinder (12a) of one rear wheel (11a) is shut off.

When the piston (38) moves further to the right with the pressure drop in the right input (49a) and output chamber (50a) in the blocked state as described above, the blocked output chamber ( The volume of 50b) increases. That is, this output chamber (5
The hydraulic pressure in the wheel cylinder (12a) of the rear wheel (11a), which communicates with 0b) via the output port (14) and the pipe line (15), decreases. As long as the left valve ball (47b) is seated on the valve seat (46b), when the hydraulic pressure in the right input chamber (49a) and output chamber (50a) rises again (the signals EV and AV are 0 "), the piston (38) moves to the left and the volume of the left output chamber (50b) decreases. As a result, the brake fluid pressure in the wheel cylinder (12) of the rear wheel (11a) rises again.
That is, the rear wheel (11a) on the same side as the front wheel (6a) is controlled according to the brake fluid pressure of the front wheel (6a). Therefore, the rear wheel (11a) on the low friction coefficient side of the road surface
Is locked like the front wheel (6a) on the same side. If the brake fluid pressure on the rear wheel (11a) as well as the front wheel (6b) on the higher friction coefficient side of the other road surface is controlled, it will lock.

Although the above description has been made assuming that all wheels are equipped with the same type of tires, the case where only the front wheels (6a) and (6b) are equipped with spiked tires or chains will be described next.
First, the case where the vehicle is running on a split road surface will be described.

Now, the front wheels (6a) and rear wheels (11a) are on the low μ side, and the front wheels (6a
b) The rear wheel (11b) is on the high μ side.

When sudden braking is applied, the front wheels (6
a), Bureki fluid pressure P of the rear wheel (11a), P is 'is gradually increased, the output EV ₂ becomes the time t _1' becomes "1" as shown in Figure 6 C. That is, the deceleration signal -b of the rear wheel (11a)
Occurs. As a result, the output EV of the first logic circuit (36a)
Becomes "1" and the brake fluid pressure PP 'is held constant. The brake fluid pressure P'of the rear wheel (11a) is reduced and rises with respect to the brake fluid pressure P of the front wheel when the fluid pressure exceeds a certain value due to the action of the pressure reducing valve (32a). Output AV ₂ ′ at time t ₂
Becomes “1”. That is, the slip signal S of the rear wheel (11a)
Occurs. Since the slip signal S of the other rear wheel (11b) is still "0", the AND gate (104
The output of a) is "1", therefore the output of the OR gate (103a) is "1", and the output AV of the logic circuit (36a) is "1".
The output EV ₂ ′ is still “1”. This allows the front wheels (6
The brake fluid pressure P in a) decreases. The brake fluid pressure of the rear wheel (11b) is also reduced by the action of the valve device (8) like the brake fluid pressure P'shown in FIG. 6B, like the other rear wheel (11a). In addition, in FIG. 4B, an AND gate (104b)
Input to both input terminals is "0", OR gate (100b) (10
Since the inputs to both input terminals of 3b) are also "0", the outputs EV 'and AV' of the second logic circuit (36b) are "0", and the brake fluid pressure of the front wheel (6b) on the high μ side is Is still rising.

Slip signal S is generated in the rear wheel of the time t becomes ₃ when irrespective high μ side to have reduced the brake fluid pressure P '(11b). That is, the output AV ₂ becomes "1" as shown in FIG. 6C. This causes the AND gate (104
The input to one input terminal of a) becomes "0", and the output AV of the AND gate (104a), and thus the first logic circuit (36a) becomes "0". The output EV ₂ ′ is still “1”, so
Here, the brake fluid pressures P and P'are kept constant.

At time t ₄ , the output AV ₂ becomes “0” again, but the output A
V ₂ ′ is still “1”. Therefore, in FIG. 4A, the output of the AND gate (104a) becomes "1" again, and the output AV of the first logic circuit (36a) becomes "1". Brake fluid pressure P,
P'decreases again. In FIG. 4B, even if the output AV ₂ becomes “1”, the other output AV ₂ ′ is still “1”, the output of the AND gate (104b) is “0”, and Brake fluid pressure on the front wheels (6b) continues to rise.

At time t ₅ , the slip signal S of the rear wheel (11a) disappears and the output AV ₂ ′ becomes “0”, but since the output EV ₂ ′ is still “1”, the brake fluid pressures P and P ′ are Holds constant.

Even after the deceleration signal −b of the rear wheel (11a) disappears, the output EV ₂ ′ is “1” for the delay time of the off delay timer, but during this period, the acceleration signal + b is generated and while this signal + b is being generated. The output EV ₂ ′ remains “1”. Acceleration signal + b is time t
_When it disappears at ₆ , the pulse oscillator (81b) starts driving in the evaluation circuit (36b), and the output EV ₂ ′ is “0”, “1”, “0”,
The pulse pressure changes to "1" ..., and the brake fluid pressures P and P'continue to increase stepwise. Note that FIG. 6A shows changes in wheel speed, and V ₁ , V ₂ , and V ₃ are wheel speeds of the right front wheel, the left rear wheel, and the right rear wheel, respectively.

Thereafter, the same anti-skid control as described above is repeated to prevent both rear wheels from locking together. Further, since the front wheel (6b) on the high μ side can increase the brake fluid pressure as it is, the braking distance is not lengthened and the feeling of the driver during control is better than before.

Next, a case where both front wheels are equipped with spiked tires or chains and all the wheels are traveling on a uniform road surface will be described.

In this case, it is conceivable that both rear wheels (11a) and (11b) will be locked at the same time, and the outputs AV ₂ and AV ₂ ′ will both be “1”, but in reality either one will become “1” first, As a result, both rear wheels (11a, 11b) can reduce the brake fluid pressure via the valve device (8), so that both rear wheels are not locked together. Incidentally, in FIG. 6, the front wheel (6a)
Only (6b) is equipped with spiked tires or chains,
I explained the case of traveling on a split road surface, but output
AV _2, AV ₂ 'time t ₃ in ~t ₄ are "1", during which the brake fluid pressure P, P' is held constant, the time t ₂ ~t ₃
Of the rear wheels by the brake loosened, that since the wheel speed brake fluid pressure is sufficiently reduced is recovered sufficiently, it will lock the rear wheels both by the brake constant retention time t ₃ ~t ₄ In the case where the brake on one rear wheel is released, the valve device (8) controls the hydraulic control valve for the brake on the front wheel of the same system to release the brake on the other rear wheel). output AV ₂ 'in comparison with the (low μ side) output AV ₂ (high μ side)
Becomes "0" again in a short time. However, if the brake fluid pressure of the front wheels (6b) is reduced by the output AV ₂ , it takes a short time, but acceleration of both front wheels gives a large inertial force to the driver, resulting in a bad feeling. In the present embodiment, this is greatly improved.

Next, a case where a failure occurs in either one of the systems will be described.

For example, if liquid leakage occurs in the system on the side of the pipeline (3), the hydraulic pressure in the wheel cylinders (7a) (12b) will not rise even if the brake pedal (2) is depressed. On the other hand, pipelines (16)
The piston (38) moves to the right in the valve device (8) due to the pressure increase in the side system. Since the anti-skid control is not performed, the contact (55) remains closed, and the switch (52) is closed by the movement of the piston (38), so current flows from the battery (57) and the alarm lamp (56) lights up. To do. This allows the driver to recognize that the device is failing. If the contact has not failed, the contact (55) opens with anti-skid control (for example, driving of the hydraulic pump (20) starts), so the piston (38)
The alarm lamp (56) does not light up when is moved.

Although the embodiments of the present invention have been described above, needless to say, the present invention is not limited to these, and various modifications can be made based on the technical idea of the present invention.

For example, as the evaluation circuit, the one shown in FIG. 2 is given, but various known control units can be applied.

In addition, depending on the logic configuration, each one three-position electromagnetic switching valve may be used as the hydraulic pressure control valve (4a) (4b).

In the above embodiments, the approximate vehicle speed generator (76a) (7
Although the larger one of the outputs of 6b) is taken, the one having the larger wheel speed may be selected to form the approximate vehicle body speed.

〔The invention's effect〕

As described above, according to the hydraulic control device for an anti-skid device of the present invention, the number of hydraulic control valves is two (two channels).
Since it is used only for 3 channels and 4 channels, the device is smaller and lighter and the cost is reduced.
Further, even if the front wheels have a fade phenomenon or the chain is equipped, the braking distance can be made as short as possible to reliably prevent the rear wheels from being locked, and the steering stability can be maintained. Also, the driving sensation during control should be good.

[Brief description of drawings]

FIG. 1 is a diagram showing a piping system and electric wiring of a hydraulic pressure adjusting device for an anti-skid control device according to an embodiment of the present invention, and FIG.
The drawing is an enlarged cross-sectional view of the valve device in FIG. 1, and FIG.
FIG. 4 is a block diagram of a first evaluation circuit in the figure, FIGS. 4A and 4B are block diagrams of first and second logic circuits in FIG. 1, and FIG. 5 is a block diagram of a motor drive circuit in FIG. FIG. 7 is a graph for explaining the operation of the present embodiment, and FIG. 7 is a graph for explaining the operation of the conventional anti-skid device hydraulic pressure adjusting device. In the figure, (4a) (4b) ... hydraulic control valve (6a) (6b) (11a) (11b) ... wheel (8) ... valve device (31) ... control unit (35a) ( 35b) …… Evaluation circuit (36a) (36b) …… Logic circuit

Claims (1)

(57) [Claims] 1. A pair of front wheels and a pair of rear wheels each of which has a wheel cylinder connected to each other in an X pipe arrangement; disposed between a first hydraulic pressure generating chamber of a master cylinder and one of the front wheels. A first hydraulic pressure control valve provided to control the brake hydraulic pressure of the wheel cylinder of the front wheel; disposed between the second hydraulic pressure generation chamber of the master cylinder and the wheel cylinder of the other front wheel of the front wheels A second hydraulic control valve for controlling the brake hydraulic pressure of the wheel cylinder of the front wheel;
A control unit that evaluates the skid state of the wheels and issues a command to control the first and second hydraulic pressure control valves; disposed between the wheel cylinders of the front wheels and the wheel cylinders of the rear wheels, A hydraulic pressure control device for an anti-skid device, the pressure selection device outputting a pressure according to a lower one of the brake hydraulic pressures of the front wheels controlled by the first and second hydraulic pressure control valves; A logical product of a skid state in which the brake fluid pressure of the one rear wheel is to be reduced and the other rear wheel is not in the skid state among the evaluation results, and the same side as the one rear wheel. And a skid state of the front wheel at the front side of the front wheel. The anti-ski command is formed to reduce the brake fluid pressure of the front wheel on the same side as the one rear wheel. For de apparatus fluid pressure control apparatus.