JP5614267B2 - Hydraulic brake system - Google Patents

Description

  The present invention relates to a hydraulic brake system including a hydraulic brake that suppresses rotation of a wheel by hydraulic pressure of a brake cylinder.

In Patent Document 1, (a) a hydraulic brake that suppresses rotation of a wheel, (b) a master cylinder, (c) an accumulator, and (d) a drive of an electric actuator using the hydraulic pressure of the accumulator A pressure increasing mechanism that is actuated by the hydraulic pressure sensor, and (e) a selection valve that selects a higher one of the hydraulic pressure of the pressure increasing mechanism and the hydraulic pressure of the master cylinder and supplies the selected pressure to the brake cylinder of the hydraulic brake. A pressure brake system is described.
In Patent Document 2, (a) a hydraulic brake that is provided on the front, rear, left, and right wheels of the vehicle and suppresses the rotation of the wheel, (b) a master cylinder, and (c) a hydraulic brake brake for the master cylinder and the front wheels. A hydraulic brake system is described that includes a mechanical booster provided between the cylinder and (d) a high-pressure source and an electromagnetic valve that controls the hydraulic pressure of the high-pressure source.

Special table 2009-502645 Japanese Patent Laid-Open No. 10-287227

  An object of the present invention is to improve a hydraulic brake system.

Means and effects for solving the problem

The hydraulic brake system of the present invention is applied to a two-wheel or three-wheel brake cylinder so that the braking force acting on the left wheel and the braking force acting on the right wheel have different magnitudes when the power hydraulic system is abnormal. Supply manual hydraulic pressure.
When the power hydraulic system is normal, power control pressure is applied to the front, rear, left and right four-wheel brake cylinders (power control pressure is controlled by using the hydraulic pressure of the power type hydraulic pressure source in the power hydraulic system). However, if the power hydraulic system is abnormal, the manual hydraulic pressure is distributed to the two-wheel or three-wheel brake cylinder.
For example, when manual hydraulic pressure is supplied to two wheels (diagonal wheels) or three wheels, the sum of braking forces acting on the left front and rear wheels is different from the sum of braking forces acting on the right front and rear wheels. May be size. On the other hand, the center of gravity may not be at the center in the left-right direction depending on the vehicle. In the vehicle, when the sum of braking forces acting on the left front and rear wheels is different from the sum of braking forces acting on the right front and rear wheels, the yaw moment can be made difficult to occur. In addition, when the center of gravity is in the center in the left-right direction, if the position of the wheel of the brake cylinder to which manual hydraulic pressure is supplied is determined in advance when the power hydraulic pressure system is abnormal, it will occur when the power hydraulic system is abnormal. The direction of easy yaw moment can be determined in advance. It is desirable that the direction of the yaw moment that is likely to occur at the time of abnormality is determined in advance rather than the case where the direction of yaw moment is not determined.
In addition, when the manual hydraulic pressure is supplied to the three wheels, the sum of the braking forces acting on the left front wheel and the sum of the braking forces acting on the right front wheel may be substantially the same. .
Thus, in the hydraulic brake system according to the present invention, it is possible to improve the running safety when the control system is abnormal.
The manual hydraulic system is (x) supplying manual hydraulic pressure to the brake cylinders of two wheels that are diagonal to each other, or (y) supplying manual hydraulic pressure to the brake cylinders of three wheels. It can be done. Three-wheel brake cylinders include (y-1) left and right front wheel brake cylinders and left and right rear wheel brake cylinders, or (y-2) left and right rear wheel brake cylinders and left and right front wheels. The brake cylinder may be included.

Patentable invention

  In the following, the invention that is claimed to be claimable in the present application (hereinafter referred to as “claimable invention”. The claimable invention is at least the “present invention” to the invention described in the claims. Some aspects of the present invention, including subordinate concept inventions of the present invention, superordinate concepts of the present invention, or inventions of different concepts) will be illustrated and described. Each aspect is divided into a term like a claim, and it describes in the format which attaches a number to each term. The constituent elements constituting the claimable invention may be those described in the following items, or described in two or more sets of each item. In addition, an aspect in which another component is added to the aspect of each term, and an aspect in which the constituent element is deleted from the aspect of each term can also be an aspect of the claimable invention.

(1) A hydraulic brake that is provided on each of the four wheels on the front, rear, left, and right sides of the vehicle and that is operated by the hydraulic pressure of the brake cylinder to suppress the rotation of the wheels;
A hydraulic power system for generating and controlling hydraulic pressure by supplying electric energy, and supplying the controlled hydraulic pressure to the brake cylinders of the four front, rear, left and right wheels;
A manual hydraulic system for supplying manual hydraulic pressure generated due to a driver's brake operation to three brake cylinders of the four wheels when the power hydraulic system is abnormal. Features a hydraulic brake system.
The power hydraulic system includes a power hydraulic pressure source that generates hydraulic pressure by supplying electric energy, a power hydraulic pressure control device that controls the hydraulic pressure using the hydraulic pressure of the power hydraulic pressure source, a fluid passage, and the like. . Even if the power hydraulic pressure control device controls the output hydraulic pressure of the power hydraulic system by controlling the power hydraulic pressure source (i.e., controlling the pump motor) (ii) Including an electromagnetic control valve provided between the output side of the power hydraulic pressure source and the brake cylinder (and may include an electromagnetic control valve provided between the brake cylinder and the low pressure source); The output hydraulic pressure of the power type hydraulic pressure source may be controlled by controlling two or more electromagnetic control valves.
The manual hydraulic system includes a manual hydraulic pressure source that generates hydraulic pressure due to the driver's operation of the brake operation member, a liquid passage, and the like. Two or more manual hydraulic pressure sources that generate the hydraulic pressure independently of each other may be included.
(2) The manual system includes: (a) two first manual hydraulic pressure sources that generate hydraulic pressure according to the operating force of the driver's brake operating member; and (b) at least the two first manuals. A second manual hydraulic pressure source operable by one of the hydraulic pressure sources and generating a hydraulic pressure higher than the hydraulic pressure of the first manual hydraulic pressure source; (c) A hydraulic pressure of the other of the two first manual hydraulic pressure sources is supplied to a part of the three-wheel brake cylinder, and the remaining one of the three-wheel brake cylinders is supplied with the first And a mixed hydraulic pressure distribution unit that supplies the hydraulic pressure of the two manual hydraulic pressure sources.
For example, the first manual hydraulic pressure source may be a pressurizing chamber of the master cylinder, and the second manual hydraulic pressure source may be a pressure increasing device that is operated by the hydraulic pressure of the pressurizing chamber of the master cylinder. The hydraulic pressure of the other first manual hydraulic pressure source is supplied to one or two of the three brake cylinders, and the second manual hydraulic pressure source is supplied to the remaining two or one brake cylinder. The hydraulic pressure can be supplied.
For example, the hydraulic pressure of the first manual hydraulic pressure source is supplied to one (for example, the left front wheel) of the left and right front wheel brake cylinders, and the second manual type is supplied to the other (for example, the right front wheel) of the brake cylinder. When the hydraulic pressure of the hydraulic pressure source is supplied (that is, when the braking force F _FR applied to the right front wheel is larger than the braking force F _FL applied to the left front wheel: F _FR > F _FL ), the left rear wheel brake The hydraulic pressure of the second manual hydraulic pressure source can be supplied to the cylinder. In that case, the sum of the braking forces applied to the left wheel and the sum of the braking forces applied to the right wheel can be made substantially the same (F _FR + 0≈F _FL + F _RL ).
One of the first manual hydraulic pressure sources can be referred to as a pressure booster connection manual hydraulic pressure source.
(3) The manual system includes: (a) at least one first manual hydraulic pressure source that generates hydraulic pressure in accordance with an operation force of a driver's brake operation member; and (b) at least the at least one first pressure source. A second manual hydraulic pressure source that is operable by one hydraulic pressure of the one manual hydraulic pressure source and generates a hydraulic pressure higher than the hydraulic pressure of the one first manual hydraulic pressure source; c) a single-type hydraulic pressure distribution unit that supplies one of the second manual hydraulic pressure source and the at least one first manual hydraulic pressure source to the three-wheel brake cylinder; Can be included.
There are cases where the hydraulic pressure of the second manual hydraulic pressure source is supplied to all three brake cylinders and the hydraulic pressure of at least one first manual hydraulic pressure source is supplied. In the latter case, the first manual hydraulic fluid that is not connected to the second manual hydraulic fluid source is supplied from the first manual hydraulic fluid source connected to the second manual hydraulic fluid source. The pressure may be supplied from a first manual hydraulic pressure source connected to a second manual hydraulic pressure source to one or two of the three brake cylinders. Two or one of the wheels may be supplied from a first manual hydraulic pressure source that is not connected to a second manual hydraulic pressure source.
(4) A hydraulic brake that is provided on each of the four wheels on the front, rear, left, and right sides of the vehicle and that is operated by the hydraulic pressure of the brake cylinder to suppress the rotation of the wheels;
A hydraulic power system for generating and controlling hydraulic pressure by supplying electric energy, and supplying the controlled hydraulic pressure to the brake cylinders of the four front, rear, left and right wheels;
When the power hydraulic system is abnormal, the length of the arm from the center of gravity of the vehicle to the ground contact point of the right wheel is compared with the length of the arm from the ground contact point of the left wheel to the front and rear wheels on the long side. The brake cylinders of three of the four wheels on the front, rear, left and right are caused by the driver's brake operation so that the sum of the braking forces is smaller than the sum of the braking forces applied to the front and rear wheels on the short side. And a manual hydraulic system for supplying manual hydraulic pressure generated by the hydraulic brake system.
The technical features described in any one of items (1) to (3) can be adopted in this item.
For example, when the length of the arm rR from the center of gravity of the vehicle to the contact point of the right wheel is compared with the length of the arm rL to the contact point of the left wheel, the arm rR to the contact point of the right wheel is longer ( For rR> rL), the sum of the braking forces applied to the right front and rear wheels (ΣF _R = F _FR + F _RR ) is smaller than the sum of the braking forces applied to the left front and rear wheels (ΣF _L = F _FL + F _RL ). As described above (ΣF _R <ΣF _L ), manual hydraulic pressure is supplied to three brake cylinders among the four wheels on the front, rear, left and right. For example, it can be supplied to three brake cylinders, a left front wheel, a left rear wheel, and a right front wheel.
Further, when the arm to the ground contact point of the right wheel is shorter (rR <rL), the sum ΣF _{R of} braking force applied to the right front and rear wheels is greater than the sum ΣF _{L of} braking force applied to the left front and rear wheels. For example, it can be supplied to the brake cylinders of the left front wheel, the right front wheel, and the right rear wheel so as to increase (ΣF _R > ΣF _L ).
Thus, in the hydraulic brake system described in this section, the yaw moment generated when the power hydraulic system is abnormal can be reduced when the center of gravity of the vehicle is off the center in the left-right direction.
(5) Hydraulic pressure that is provided on each of the four front, rear, left, and right wheels of the vehicle with the driver's seat provided on the right side in the forward direction and that is operated by the hydraulic pressure of the brake cylinder to suppress the rotation of the wheels. Brakes,
A hydraulic power system capable of generating and controlling hydraulic pressure by supplying electric energy, and supplying the controlled hydraulic pressure to the brake cylinders of the four front, rear, left and right wheels;
When the power hydraulic system is abnormal, the manual hydraulic pressure generated due to the driver's brake operation is applied to the four brakes on the front, rear, left and right so that the yaw moment in the direction in which the vehicle turns leftward acts. A hydraulic brake system comprising a manual hydraulic system for supplying to three of the cylinders.
The technical features described in any one of items (1) to (3) can be adopted in this item.
The direction in which the so-called right-hand drive vehicle turns to the left in the region where the vehicle runs on the left side according to the law is the direction in which the front portion of the vehicle leaves the oncoming lane. Therefore, when a moment in the left turning direction is applied when the power hydraulic system is abnormal, traveling safety can be improved compared to a case in which a moment in the right turning direction is applied.
For example, servo pressure can be supplied to the right front wheel and left rear wheel brake cylinders, and manual hydraulic pressure can be supplied to the left front wheel brake cylinders.
(6) Hydraulic pressure that is provided on each of the four front, rear, left, and right wheels of the vehicle provided on the right side in the forward direction and that is operated by the hydraulic pressure of the brake cylinder to suppress the rotation of the wheels. Brakes,
A hydraulic power system capable of generating and controlling hydraulic pressure by supplying electric energy, and supplying the controlled hydraulic pressure to the brake cylinders of the four front, rear, left and right wheels;
Including a manual hydraulic system that supplies manual hydraulic pressure generated due to the brake operation of the driver to the right front wheel, left front wheel, and right rear wheel brake cylinder when the power hydraulic system is abnormal Hydraulic brake system.
The technical features described in any one of items (1) to (3) can be adopted in this item.
(7) A hydraulic pressure that is provided on each of the four front, rear, left, and right wheels of the vehicle provided on the left side in the forward direction and that is operated by the hydraulic pressure of the brake cylinder to suppress the rotation of the wheels. Brakes,
A hydraulic power system capable of generating and controlling hydraulic pressure by supplying electric energy, and supplying the controlled hydraulic pressure to the brake cylinders of the four front, rear, left and right wheels;
When the power hydraulic system is abnormal, the manual hydraulic pressure generated by the driver's braking operation is applied to the four brakes on the front, rear, left and right so that the yaw moment in the direction in which the vehicle turns to the right acts. A hydraulic brake system comprising a manual hydraulic system for supplying to three of the cylinders.
The technical features described in any one of items (1) to (3) can be adopted in this item.
In a region where a so-called left-hand drive vehicle travels on the right side according to regulations, the moment in the direction of turning to the right is the direction in which the front of the vehicle moves away from the oncoming lane. As described above, when a moment for turning in the right direction is applied, traveling safety can be improved as compared with a case in which a moment for turning in the left direction is applied.
(8) Hydraulic pressure that is provided on each of the four front, rear, left, and right wheels of the vehicle provided on the left side in the forward direction and that is operated by the hydraulic pressure of the brake cylinder to suppress the rotation of the wheels. Brakes,
A hydraulic power system capable of generating and controlling hydraulic pressure by supplying electric energy, and supplying the controlled hydraulic pressure to the brake cylinders of the four front, rear, left and right wheels;
A manual hydraulic system that supplies manual hydraulic pressure generated due to a driver's brake operation to the right front wheel, left front wheel, and left rear wheel brake cylinder when the power hydraulic system is abnormal. Hydraulic brake system.
The technical features described in any one of items (1) to (3) can be adopted in this item.
(9) A hydraulic brake system includes a common passage to which the second manual hydraulic pressure source is connected and brake cylinders of the four front, rear, left and right wheels are connected; the common passage; And an individual control valve provided between each of the brake cylinders, and the individual control valves corresponding to the three-wheel brake cylinders among the individual control valves are normally open when no current is supplied to the solenoid. It can be a valve.
The individual control valve is an electromagnetic on-off valve that can take at least an open state and a closed state. The electromagnetic on-off valve can be used as a linear control valve that can continuously control the differential pressure (and / or opening) between the front and rear by continuously controlling the amount of current supplied to the solenoid. A simple on-off valve that can be switched between an open state and a closed state by ON / OFF control may be used. Hereinafter, in the present specification, unless it is described as “linear control valve” or “simple on / off valve”, “valve” such as an electromagnetic on / off valve, electromagnetic control valve, and hydraulic control valve is a “linear control valve”. Also, it may be a “simple on-off valve”.
(10) A hydraulic brake that is provided on each of the four wheels on the front, rear, left, and right sides of the vehicle and that is operated by the hydraulic pressure of the brake cylinder to suppress the rotation of the wheels;
A hydraulic power system for generating and controlling hydraulic pressure by supplying electric energy, and supplying the controlled hydraulic pressure to the brake cylinders of the four front, rear, left and right wheels;
When the power hydraulic system is abnormal, the braking force applied to the right wheel and the braking force applied to the left wheel are different from each other in the two brake cylinders at the diagonal positions of the four wheels. And a manual hydraulic system that supplies a manual hydraulic pressure generated due to the driver's brake operation,
The manual hydraulic pressure system includes (i) at least one first manual hydraulic pressure source that generates hydraulic pressure in accordance with an operating force of a driver's brake operating member, and (ii) at least the at least one first hydraulic pressure source. A second manual hydraulic pressure source that is operable by one of the manual hydraulic pressure sources and generates a hydraulic pressure higher than the hydraulic pressure of the one first manual hydraulic pressure source; (iii) A hydraulic brake system comprising: a second hydraulic pressure supply unit that supplies the hydraulic pressure of the second manual hydraulic pressure source to the two brake cylinders at the diagonal positions.
For example, by applying to a vehicle where the center of gravity of the vehicle is not centered in the left-right direction, it is possible to make it difficult for a yaw moment to occur or to allow a yaw moment in a fixed direction to act.
The technical features described in any one of the items (1) to (9) can be employed in the hydraulic brake system described in this item.

1 is a diagram showing an entire vehicle equipped with a hydraulic brake system that is a common embodiment of the present invention. It is a circuit diagram showing the hydraulic brake circuit of the hydraulic brake system which concerns on Example 1 of this invention. It is sectional drawing of the pressure increase linear control valve contained in the said hydraulic brake circuit. It is a figure which shows the input side non-return valve contained in the said hydraulic brake circuit. (a) is a sectional view of a cup seat type check valve, (bi) is a sectional view of a ball type check valve, (b-ii) is an AA sectional view of (bi), (c) is a diagram conceptually showing a magnetic check valve. It is a flowchart showing the hydraulic pressure supply state control program memorize | stored in the memory | storage part of brake ECU contained in the said hydraulic brake system. In the said hydraulic brake system, it is a figure which shows a state when a supply state control program is performed (when normal). In the said hydraulic brake system, it is a figure which shows the state at the time of a supply state control program being performed (when a control system is abnormal 1) (a) In the said hydraulic brake system, it is a figure which shows a state when a supply state control program is performed (when control system is abnormal 2) (b) The right handle | steering vehicle equipped with the said hydraulic brake system Vehicle. FIG. 3 is a diagram showing a state where an ignition switch is OFF in the hydraulic brake system (when there is a possibility of liquid leakage). (a) A hydraulic brake circuit diagram of a hydraulic brake system according to a second embodiment of the present invention. (b) A left-hand drive vehicle equipped with the hydraulic brake system. (a) A hydraulic brake circuit diagram of a hydraulic brake system according to a third embodiment of the present invention. (b) A left-hand drive vehicle equipped with the hydraulic brake system. (a) A hydraulic brake circuit diagram of a hydraulic brake system according to a fourth embodiment of the present invention. (b) A right-hand drive vehicle equipped with the hydraulic brake system. (a) A hydraulic brake circuit diagram of a hydraulic brake system according to a fifth embodiment of the present invention. (b) A left-hand drive vehicle equipped with the hydraulic brake system. (a) A hydraulic brake circuit diagram of a hydraulic brake system according to a sixth embodiment of the present invention. (b) A right-hand drive vehicle equipped with the hydraulic brake system.

Hereinafter, a hydraulic brake system which is a plurality of embodiments of the present invention will be described in detail with reference to the drawings.
First, a vehicle equipped with a hydraulic brake system that is a hydraulic brake system according to a plurality of embodiments of the present invention will be described.
As shown in FIG. 1, the vehicle is a hybrid vehicle that includes an electric motor and an engine as a drive device. In the hybrid vehicle, the left and right front wheels 2 and 4 as drive wheels are driven by a drive device 10 including an electric drive device 6 and an internal combustion drive device 8. The driving force of the driving device 10 is transmitted to the left and right front wheels 2 and 4 via the drive shafts 12 and 14. The internal combustion drive 8 includes an engine 16, an engine ECU 18 that controls the operating state of the engine 16, and the like. The electrical drive 6 includes an electric motor 20, a power storage device 22, a motor generator 24, a power conversion device 26, A motor ECU 28, a power split mechanism 30 and the like are included. When the electric motor 20, the motor generator 24, and the engine 16 are connected to the power split mechanism 30, and only the driving torque of the electric motor 20 is transmitted to the output member 32 by these controls, the driving torque of the engine 16 and the electric power When both the driving torque of the motor 20 is transmitted, the output is switched to when the output of the engine 16 is output to the motor generator 24 and the output member 32, or the like. The driving force transmitted to the output member 32 is transmitted to the drive shafts 12 and 14 via a speed reducer and a differential device.
The power conversion device 26 includes an inverter and the like, and is controlled by the motor ECU 28. By the current control of the inverter, at least a rotational drive state in which electric energy is supplied to the electric motor 20 from the power storage device 22 and rotated, and charging that charges the power storage device 22 by functioning as a power generator by regenerative braking Switch to state. In the charged state, regenerative braking torque is applied to the left and right front wheels 2 and 4. In that sense, the electric drive device 6 can be considered as a regenerative brake device.

The hydraulic brake system includes a brake cylinder 42 of the hydraulic brake 40 provided on the left and right front wheels 2, 4, a brake cylinder 52 of the hydraulic brake 50 provided on the left and right rear wheels 46 and 48 (see FIG. 2 and the like), A hydraulic pressure control unit 54 capable of controlling the hydraulic pressure of the brake cylinders 42 and 52 is included. The hydraulic pressure control unit 54 is controlled by a brake ECU 56 mainly including a computer.
The vehicle is provided with a hybrid ECU 58, and the hybrid ECU 58, the brake ECU 56, the engine ECU 18, and the motor ECU 28 are connected via a CAN (Car area Network) 59. These can communicate with each other, and necessary information is communicated as appropriate.

In addition, this hydraulic brake system can also be mounted not only on a hybrid wheel but on a plug-in hybrid vehicle, an electric vehicle, and a fuel cell vehicle. In the electric vehicle, the internal combustion drive device 8 is not necessary. In a fuel cell vehicle, a driving motor is driven by a fuel cell stack or the like.
The present hydraulic brake system can also be mounted on an internal combustion drive vehicle. In a vehicle in which the electric drive device 6 is not provided, regenerative braking torque is not applied to the drive wheels 2, 4, so regenerative cooperative control is not performed.

  Hereinafter, the hydraulic brake system will be described, but when it is necessary to distinguish the brake cylinder, the hydraulic brake, and various electromagnetic on-off valves, which will be described later, according to the positions of the front, rear, left and right wheels, It is described with reference numerals (FL, FR, RL, RR) to be represented, and representatively or when it is not necessary to distinguish, it is described without reference numerals.

The hydraulic brake system according to the first embodiment includes a brake circuit shown in FIG.
Reference numeral 60 denotes a brake pedal as a brake operation member, and reference numeral 62 denotes a master cylinder that generates hydraulic pressure by operating the brake pedal 60. A power hydraulic pressure source 64 includes a pump device 65 and an accumulator 66. The hydraulic brakes 40 and 50 are actuated by the hydraulic pressure of the brake cylinders 42 and 52 to suppress the rotation of the wheels. In the present embodiment, the hydraulic brakes 40 and 50 are disc brakes.
The hydraulic brakes 40 and 50 can be drum brakes. Alternatively, the hydraulic brake 40 for the front wheels 2 and 4 can be a disc brake, and the hydraulic brake 50 for the rear wheels 46 and 48 can be a drum brake.
The master cylinder 62 is of a tandem type having two pressure pistons 68 and 69, and the pressure chambers 70 and 72 are in front of the pressure pistons 68 and 69, respectively. In this embodiment, the pressurizing chambers 70 and 72 correspond to manual hydraulic pressure sources, respectively. The pressurizing chambers 72 and 70 are respectively connected to the brake cylinder 42FL of the hydraulic brake 40FL of the left front wheel 2 and the brake cylinder of the hydraulic brake 40FR of the right front wheel 4 via master passages 74 and 76 as manual passages. 42FR is connected.
The pressurizing chambers 70 and 72 are communicated with the reservoir 78 when the pressurizing pistons 68 and 69 reach the retracted end, respectively. The interior of the reservoir 78 is partitioned into a plurality of storage chambers 80, 82, and 84 that store hydraulic fluid. The accommodating chambers 80 and 82 are provided corresponding to the pressurizing chambers 70 and 72, respectively, and the accommodating chamber 84 is provided corresponding to the pump device 65.

  In the motive power hydraulic pressure source 64, the pump device 65 includes a pump 90 and a pump motor 92, and the hydraulic fluid is pumped up from the storage chamber 84 of the reservoir 78 by the pump 90, and is stored in the accumulator 66. The pump motor 92 is controlled so that the pressure of the hydraulic fluid stored in the accumulator 66 is within a predetermined setting range. Further, the relief valve 93 prevents the discharge pressure of the pump 90 from becoming excessive.

A mechanical pressure booster 96 as a pressure booster is provided between the power hydraulic pressure source 64, the master cylinder 62, and the brake cylinders 42 and 52.
The mechanical pressure booster 96 includes a mechanical movable portion 98 as a movable portion, an input side check valve 99, and a high pressure side check valve 100. The mechanical movable portion 98 includes a housing 102 and a stepped piston 104 that is fluid-tight and slidably fitted to the housing 102. A large-diameter side chamber 110 is provided on the large-diameter side of the stepped piston 104. A small-diameter side chamber 112 is provided on the small-diameter side. The pressurizing chamber 72 is connected to the large-diameter side chamber 110. In the present embodiment, the pressurizing chamber 72 corresponds to a pressure-increasing device connection manual hydraulic pressure source (one manual hydraulic pressure source).
A high pressure chamber 114 connected to the power hydraulic pressure source 64 is communicated with the small diameter side chamber 112, and a high pressure supply valve 116 is provided between the small diameter side chamber 112 and the high pressure chamber 114. The high-pressure supply valve 116 includes a valve seat 122 formed in the housing 102, a valve element 120 provided so as to be able to approach and separate from the valve seat 122, and a spring 124. This acts in a direction to press the child 120 against the valve seat 122. The high pressure supply valve 116 is a normally closed valve.
In the small diameter side chamber 112, a valve opening member 125 is provided so as to face the valve element 120, and a spring 126 is provided between the valve opening member 125 and the stepped piston 104. The biasing force of the spring 126 acts in a direction to separate the valve opening member 125 and the stepped piston 104 from each other. The valve opening member 125 can also be considered as a component of the high pressure supply valve 116.
A spring 128 (return spring) is provided between the step portion of the stepped piston 104 and the housing 102 to urge the stepped piston 104 in the backward direction. A stopper (not shown) is provided between the stepped piston 104 and the housing 102 to restrict the forward end position of the stepped piston 104.
Further, in the stepped piston 104, an in-piston communication passage 129 that connects the large-diameter side chamber 110 and the small-diameter side chamber 112 is formed, and an in-piston check valve 130 is provided in the middle of the in-piston communication passage 129. The piston check valve 130 blocks the flow of hydraulic fluid from the large-diameter side chamber 110 toward the small-diameter side chamber 112 and allows the hydraulic fluid to flow from the small-diameter side chamber 112 toward the large-diameter side chamber 110.

  The high pressure check valve 100 is provided in the middle of the high pressure supply passage 132 that connects the high pressure chamber 114 and the power hydraulic pressure source 64. The high pressure side check valve 100 allows the flow of hydraulic fluid from the power hydraulic pressure source 64 to the high pressure chamber 114 when the hydraulic pressure of the power hydraulic pressure source 64 is higher than the hydraulic pressure of the high pressure chamber 114. When the hydraulic pressure of the motive power hydraulic pressure source 64 is equal to or lower than the hydraulic pressure of the high pressure chamber 114, the power supply pressure source 64 is in a closed state and prevents bidirectional flow. Therefore, even if the hydraulic pressure of the power hydraulic pressure source 64 decreases due to an abnormality in the electrical system, a decrease in the hydraulic pressure in the small-diameter side chamber 112 is prevented.

The input-side check valve 99 is a bypass passage 136 serving as a movable portion bypass passage that connects the master passage 74 and the output side of the mechanical movable portion 98 (or the small-diameter side chamber 112) by bypassing the mechanical movable portion 98. It is provided in the middle. The bypass passage 136 can also be considered as a passage connecting the master passage 74 and the common passage 94 by bypassing the mechanical movable portion 98.
The input-side check valve 99 allows the flow of hydraulic fluid from the master passage 74 to the output side of the mechanical movable unit 98 and blocks the reverse flow, and has a valve opening pressure of a set pressure. is there. The set pressure is a value determined based on a hydraulic pressure difference caused by a difference in height between the master reservoir 78 and the brake cylinders 42 and 52 (the master reservoir 78 is above the brake cylinders 42 and 52 in the vertical direction). The set pressure can be referred to as a height difference set pressure.
When the brake pedal 60 is not operated, the pressurizing chamber 72 of the master cylinder 62 is communicated with the master reservoir 78 and is at almost atmospheric pressure. Further, the hydraulic pressure of the brake cylinder 42 is almost atmospheric pressure, but there is a hydraulic pressure difference due to the difference in height between them.
On the other hand, if the valve opening pressure of the input-side check valve 99 is determined based on the hydraulic pressure difference due to the height difference, the hydraulic fluid from the master reservoir 78 is prevented from flowing out when the brake pedal 60 is not operated. Even if there is a leak around the brake cylinders 42FL, FR, 52RR, the flow of hydraulic fluid from the master reservoir 78 toward the brake cylinders 42FL, FR, 52RR can be prevented.
Further, when the brake pedal 60 is operated (the operation is performed so that the hydraulic brakes 40 and 50 are in an applied state and is usually a stepping operation), and the hydraulic pressure in the pressurizing chamber 72 is increased, the input is performed. The differential pressure before and after the side check valve 99 (the value obtained by subtracting the fluid pressure on the common passage side from the fluid pressure on the master cylinder side) is larger than the set pressure corresponding to the elevation difference, and the input side check valve 99 is switched to the open state. It is done. Thereby, the flow of hydraulic fluid from the master cylinder 62 toward the brake cylinder is allowed.

The input-side check valve 99 can have, for example, the structure shown in FIG. For example, as shown in FIG. 4 (a), a cup seal type check valve 99x is used, as shown in FIG. 4 (b), a ball type check valve 99y is used, or as shown in FIG. 4 (c). Thus, the magnetic check valve 99z can be used.
4A, the check valve 99x includes a housing 140 fixedly provided in the bypass passage 136, and an annular seal member 142 supported by the housing 140. The seal member 142 is formed of a material that is easily elastically deformed, such as rubber, and has a shape that is easily bent in the direction of the arrow X and hardly bent in the opposite direction. In the present embodiment, the master passage 74 is connected to the upstream side of the arrow X, and the common passage 94 is connected to the downstream side. The seal member 142 does not bend when the differential pressure before and after (the value obtained by subtracting the hydraulic pressure of the common passage 94 from the hydraulic pressure of the master passage 74) is equal to or lower than the set pressure corresponding to the elevation difference. The check valve 99x is in a closed state, and the outflow of hydraulic fluid from the master reservoir 78 is prevented. When the front-rear differential pressure becomes larger than the height difference setting pressure, the seal member 142 is bent. The check valve 99x is switched to the open state, and the outflow from the master cylinder 62 is allowed. Note that the flow of hydraulic fluid in the reverse direction, that is, from the common passage 94 toward the master passage 74 is blocked.

As shown in FIGS. 4B to 4I, the check valve 99y includes (a) a housing 142, (b) a valve seat 143 formed on the housing 142, and (c) a valve seat 143. It is a seating valve including a valve element 144 that can be approached and separated.
In the check valve 99y, the valve element 144 has a spherical shape and no spring is provided. Further, as shown in FIGS. 4B to 4I, a retaining portion 145 is provided on the opposite side of the housing 142 from the side on which the valve seat 143 is provided.
In this embodiment, the check valve 99y is disposed in a posture in which the axis L of the check valve 99y is inclined by an angle θ with respect to the horizontal line H, as shown in FIGS. The master passage 74 is connected to the downstream side of the axial component Ga (= mgsin θ) of the gravity G (= mg) acting on the valve element 144, and the common passage 94 is connected to the upstream side.

  In the check valve 99y, when the differential pressure before and after (the value obtained by subtracting the hydraulic pressure of the small-diameter side chamber 112 from the hydraulic pressure of the master reservoir 78) is equal to or smaller than the magnitude corresponding to the component Ga, the valve element 144 is 143 is in a seated state. The check valve 99y is closed, and the flow of hydraulic fluid from the master reservoir 78 to the output side of the pressure increasing device 98 is blocked. When the front-rear differential pressure becomes larger than the magnitude corresponding to the component Ga, the valve element 144 is separated from the valve seat 143, the check valve 99y is opened, and the working fluid from the master passage 74 toward the common passage 94 is opened. Flow is allowed. In this case, since the retaining portion 145 is provided, the valve element 144 is prevented from coming out of the check valve 99y. Further, when a flow of hydraulic fluid from the common passage 94 toward the master passage 74 is generated, a suction force is applied, and the valve element 144 is moved toward the valve seat 143 and is seated. In other words, the check valve 99y is provided in a posture in which the component Ga becomes a force corresponding to the height difference setting pressure (in a posture inclined by the angle θ).

In FIG. 4C, the check valve 99z includes a valve element 146 and a valve seat 147, but does not have a spring. Further, at least one of the valve element 146 and the valve seat 147 is a permanent magnet made of a ferromagnetic material, and is brought close to each other by a magnetic force. The magnetic force (attraction force) acting between the valve element 146 and the valve seat 147 has a magnitude corresponding to the height difference setting pressure.
The master passage 74 is connected to the upstream side of the arrow Z so that a differential pressure between the hydraulic pressure of the master passage 74 and the hydraulic pressure of the common passage 94 acts in the direction opposite to the magnetic force, that is, the common passage on the opposite side. 94 is connected. When the front-rear differential pressure is equal to or lower than the set pressure corresponding to the height difference, the check valve 99z is in a closed state, and the outflow of hydraulic fluid from the master reservoir 78 is prevented. When the front-rear differential pressure becomes larger than the height difference setting pressure, the valve element 146 moves away from the valve seat 147 against the magnetic force, and the check valve 99z is switched to the open state. Thereby, the flow of hydraulic fluid from the master passage 74 toward the common passage 96 is allowed.
In the check valve 99z, a retaining portion (not shown) can be provided.
In this embodiment, the bypass passage 136 and the piston internal passage 129 constitute the pressure booster internal passage, the input side check valves 99x, 99y, 99z, etc. constitute the first check valve, and the piston internal reverse passage. A stop valve 130 constitutes a second check valve.

  An input side shut-off valve 148 is provided between the master passage 74 and the mechanical pressure booster 96. The input side shut-off valve 148 is a normally open electromagnetic on-off valve that is open when no current is supplied to the solenoid coil (hereinafter abbreviated as current to the solenoid).

On the other hand, the brake cylinders 42FL and FR of the left and right front wheels 2 and 4 and the brake cylinders 52RL and RR of the left and right rear wheels 46 and 48 have individual passages 150FL, FR, RL, and RR as the brake side passage and the individual brake side passage, respectively. To the common passage 94.
The individual passages 150FL, FR, RL, RR are provided with holding valves (SHij: i = F, R, j = L, R) 153FL, FR, RL, RR1, and brake cylinders 42FL, FR, 52RL, respectively. , 52RR and the reservoir 78 are provided with pressure reducing valves (SRij: i = F, R, j = L, R) 156FL, FR, RL, RR1, respectively.
In the present embodiment, the holding valves 153FL, FR, 153RR1 provided corresponding to the left and right front wheels 2, 4 and the right rear wheel 48 are normally open electromagnetic on-off valves that are open when no current is supplied to the solenoid. The holding valve 153RL provided corresponding to the left rear wheel 46 is a normally closed electromagnetic on-off valve that is closed when no current is supplied to the solenoid.
The pressure reducing valves 156FL, FR and 156RR1 provided corresponding to the left and right front wheels 2 and 4 and the right rear wheel 48 are normally closed electromagnetic on-off valves which are closed when no current is supplied to the solenoid. A pressure reducing valve 156RL provided corresponding to the rear wheel 46 is a normally open electromagnetic on-off valve that is open when no current is supplied to the solenoid.

In addition to the brake cylinders 42 and 52, a power hydraulic pressure source 64 and a mechanical pressure booster 96 are connected to the common passage 94.
The power hydraulic pressure source 64 is connected to the common passage 94 via the power hydraulic pressure passage 170. The power hydraulic pressure passage 170 is provided with a pressure-increasing linear control valve (SLA) 172. The pressure-increasing linear control valve 172 is a normally closed electromagnetic on-off valve that is closed when no current is supplied to the solenoid, and the hydraulic pressure in the common passage 94 is controlled by continuously controlling the magnitude of the current supplied to the solenoid. Can be continuously controlled.
As shown in FIG. 3, the pressure-increasing linear control valve 172 includes a seating valve including a valve element 180 and a valve seat 182, a spring 184, and a solenoid (including a coil and a plunger) 186. The urging force F <b> 2 acts in a direction in which the valve element 180 approaches the valve seat 182, and an electromagnetic driving force F <b> 1 acts in a direction in which the valve element 180 is separated from the valve seat 182 when current is supplied to the solenoid 186. Further, in the pressure-increasing linear control valve 172, a differential pressure acting force F3 corresponding to the differential pressure between the power hydraulic pressure source 64 and the common passage 94 acts in a direction to separate the valve element 180 from the valve seat 182 (F1 + F3: F2). By controlling the current supplied to the solenoid 186, the differential pressure acting force F3 is controlled, and the hydraulic pressure in the power hydraulic pressure passage 170 is controlled. The pressure-increasing linear control valve 172 can also be referred to as an output hydraulic pressure control valve that controls the output hydraulic pressure of the power hydraulic pressure source 64. Note that, when the pressure reduction control of the common passage 94 is performed, at least one pressure reduction valve 156 is opened and closed when the holding valve 153 is open.
In the present embodiment, the power hydraulic pressure control device is configured by at least one of the pressure-increasing linear control valve 172 and the pressure-reducing valve 156.

  The mechanical pressure booster 96 is connected to the common passage 94 via the servo pressure passage 190. The servo pressure passage 190 is provided with an output side cutoff valve (SREG) 192 as a pressure booster cutoff valve. The output-side shut-off valve 192 is a normally-open electromagnetic on-off valve that is open when no current is supplied to the solenoid.

On the other hand, the master passages 74 and 76 are connected to the downstream sides of the holding valves 153FL and FR of the individual passages 150FL and FR of the left and right front wheels 2 and 4, respectively. That is, the master passages 74 and 76 bypass the mechanical pressure intensifier 96 and the common passage 94, and directly connect the pressurizing chambers 72 and 70 to the brake cylinders 42 of the left and right front wheels 2 and 4 ( The master passages 74 and 76 can be called direct connection type manual passages). Master cutoff valves (SMCFL, FR) 194FL, FR as manual cutoff valves are provided in the middle of the master passages 74, 76, respectively. The master shut-off valves 194FL and FR are normally closed electromagnetic on-off valves that are closed when no current is supplied to the solenoid.
Further, the stroke simulator 200 is connected to the master passage 74 via a simulator control valve 202. The simulator control valve 202 is a normally closed electromagnetic on-off valve.

As described above, in this embodiment, the hydraulic pressure is increased by the pump device 65, the pressure-increasing linear control valve 172, the master cutoff valve 194, the holding valve 153, the pressure reducing valve 156, the input side cutoff valve 148, the output side cutoff valve 192, and the like. A control unit 54 is configured.
The hydraulic pressure control unit 54 is controlled based on a command from the brake ECU 56. As shown in FIG. 1, the brake ECU 56 mainly includes a computer including an execution unit, an input / output unit, a storage unit, and the like. The input / output unit includes a brake switch 218, a stroke sensor 220, a master cylinder pressure sensor. 222, an accumulator pressure sensor 224, a brake cylinder pressure sensor 226, a level warning 228, a wheel speed sensor 230, an ignition switch 234, and the like, and a hydraulic pressure control unit 54 and the like are connected.
The brake switch 218 is a switch that turns from OFF to ON when the brake pedal 60 is operated.
The stroke sensor 220 detects an operation stroke (STK) of the brake pedal 60. In this embodiment, two sensors are provided, and similarly, an operation stroke of the brake pedal 60 is detected. Thus, since two stroke sensors 220 are provided, even if one breaks down, the operation stroke can be detected by the other.
The master cylinder pressure sensor 222 detects the hydraulic pressure (PMCFL) in the pressurizing chamber 72 of the master cylinder 62, and is provided in the master passage 74 in this embodiment.

The accumulator pressure sensor 224 detects the pressure (PACC) of the hydraulic fluid stored in the accumulator 66.
The brake cylinder pressure sensor 226 detects the hydraulic pressure (PWC) of the brake cylinders 42 and 52 and is provided in the common passage 94. When the holding valve 153 is in the open state, the brake cylinders 42 and 52 and the common passage 94 are communicated with each other, so that the hydraulic pressure in the common passage 94 can be made the hydraulic pressure in the brake cylinders 42 and 52.
The level warning 228 is a switch that is turned on when the hydraulic fluid stored in the master reservoir 78 is less than or equal to a predetermined set amount. In the present embodiment, when the amount of the hydraulic fluid stored in any one of the three storage chambers 80, 82, 84 becomes equal to or less than the set amount, it is turned ON.
Wheel speed sensors 230 are provided corresponding to the left and right front wheels 2, 4 and the left and right rear wheels 46, 48, respectively, and detect the rotational speed of the wheels. Further, the traveling speed of the vehicle is acquired based on the rotational speed of the four wheels.
The ignition switch (IGSW) 234 is a main switch of the vehicle.
Various programs, tables, and the like are stored in the storage unit.

<Operation in hydraulic brake system>
In the present embodiment, the supply state of the hydraulic pressure to the brake cylinders 42 and 52 is controlled in each of the case where there is a possibility of leakage, the possibility of leakage, and the case where the control system is abnormal.
The supply state control program represented by the flowchart of FIG. 5 is executed at predetermined time intervals.
In step 1 (hereinafter abbreviated as S1; the same applies to other steps), it is determined whether or not there is a braking request. When the brake switch 218 is ON, or when there is a request for operating the automatic brake, it is determined that there is a braking request, and the determination is YES. The automatic brake may be operated in traction control, vehicle stability control, inter-vehicle distance control, and collision avoidance control. When these control start conditions are satisfied, a braking request may be made.
When there is a braking request, in S2 and S3, a determination result as to whether there is a possibility of liquid leakage or whether the control system is abnormal is read.

The presence or absence of the possibility of liquid leakage does not matter whether the possibility of liquid leakage is high or low and the amount of liquid leakage. Therefore, there is a possibility that the possibility of liquid leakage is very low, or even if the amount of leakage is very small, it cannot be determined unless it is liquid leakage. Therefore, even if it is detected that there is a possibility of liquid leakage, the liquid leakage may not actually occur {the conditions (b) to (e) described later are caused by causes other than liquid leakage. May be met}.
For example, when (a) the level warning switch 228 is ON, (b) when a brake operation is performed, a predetermined relationship is established between the stroke of the brake pedal 60 and the hydraulic pressure of the master cylinder 62. In this case, it is assumed that there is no liquid leakage. However, if the hydraulic pressure in the master cylinder 62 is small relative to the stroke, there is a possibility of liquid leakage. Further, (c) when the detection value of the accumulator pressure sensor 224 does not exceed the liquid leakage determination threshold value even if the pump 92 continues to operate for a predetermined set time or longer, (d) regenerative cooperative control is performed. If the detected value of the brake cylinder pressure sensor 226 is smaller than the detected value of the master cylinder pressure sensor 222, (e) if it is detected that there is a possibility of liquid leakage during the previous brake operation ( In the case where the hydraulic pressure of the master cylinder 62 is supplied to the brake cylinders 42 of the left and right front wheels 2, 4 and the pump pressure is supplied to the brake cylinders 52 of the left and right rear wheels 46, 48), there is a possibility of liquid leakage. It is said.

The abnormality of the control system means a state in which the hydraulic pressure of the brake cylinders 42 and 52 or the hydraulic pressure of the common passage 94 cannot be controlled using the hydraulic pressure of the power type hydraulic pressure source 64.
For example, (i) When an electromagnetic on-off valve or the like cannot be operated as commanded {an electromagnetic on-off valve such as a pressure increasing linear control valve 172 (for example, a holding valve 153, a pressure reducing valve 156, a master cutoff valve 194, an output side cutoff Valve 192 etc.) is disconnected, etc.}, (ii) when a detection value necessary for controlling the hydraulic pressure of the brake cylinders 42 and 52 cannot be obtained (including cases where it cannot be obtained accurately) [
Each sensor (brake switch 218, stroke sensor 220, master cylinder pressure sensor 222, accumulator pressure sensor 224, brake cylinder pressure sensor 226, wheel speed sensor 230, etc.) is disconnected, etc.], (iii) each electromagnetic open / close When power (also referred to as electrical energy or current) cannot be supplied to valves, sensors, etc. (such as when the power supply of the power storage device 22 or the like is broken or the wiring is broken), (iv) This corresponds to a case where high-pressure hydraulic fluid cannot be supplied from the pressure source 64 {for example, an abnormality of the pump motor 92, a case where electric power cannot be supplied to the pump motor 92 (including a case caused by an abnormality of the power source), etc.}.

When both determinations of S2 and S3 are NO and the hydraulic brake system is normal (in this embodiment, the control system is normal and there is no possibility of liquid leakage). In S4, normal control is performed. The output hydraulic pressure of the power hydraulic pressure source 64 is controlled by the pressure-increasing linear control valve 172, and the power control pressure is supplied to the common passage 94 and supplied to the brake cylinders 42 and 52.
If the control system is abnormal, the determination in S3 is YES, and in S5, no current is supplied to the solenoids of all the valves, thereby returning the original position. Further, the pump motor 92 is kept in a stopped state.
If it is detected that there is a possibility of liquid leakage, the determination in S2 is NO, and in S6, the hydraulic pressure of the master cylinder 62 is supplied to the brake cylinders 42 of the left and right front wheels 2, 4, and the left and right rear wheels 46, The output hydraulic pressure of the power type hydraulic pressure source 64 is controlled and supplied to the 48 brake cylinders 52. Since it is rare that both the abnormality of the control system and the possibility of liquid leakage occur, the control system is normal even if there is a possibility of liquid leakage, the control of each valve, the drive of the pump motor 92 Is considered possible.
In the present embodiment, the automatic brake is not operated when the control system is abnormal or when there is a possibility of liquid leakage.

1) When the system is normal As shown in FIG. 6, the hydraulic pressure of the power hydraulic pressure source 64 is controlled in the brake cylinders 42, 52 of the front, rear, left and right four wheels 2, 4, 46, 48 (control). In principle, regenerative cooperative control is performed.
In the regenerative cooperative control, the total braking torque, which is the sum of the regenerative braking torque applied to the driving wheels 2 and 4 and the friction braking torque applied to both the driving wheels 2 and 4 and the driven wheels 46 and 48, is the total required braking torque. The control is performed as follows.
The total required braking torque is acquired based on detection values of the stroke sensor 220 and the master cylinder pressure sensor 222 (braking torque requested by the driver), or acquired based on the running state of the vehicle (traction control). Braking torque necessary for vehicle stability control). Then, the information supplied from the hybrid ECU 58 (the power generation side upper limit value that is the upper limit value of the regenerative braking torque determined based on the rotation speed of the electric motor 20, the power storage that is the upper limit value determined based on the charging capacity of the power storage device 22, etc. Side upper limit value) and the total required braking torque (requested value) described above are determined as the required regenerative braking torque, and information representing the required regenerative braking torque is supplied to the hybrid ECU 58.
Hybrid ECU 58 outputs information representing the required regenerative braking torque to motor ECU 28. The motor ECU 28 outputs a control command to the power converter 26 so that the braking torque applied to the left and right front wheels 2 and 4 by the electric motor 20 becomes the required regenerative braking torque. The electric motor 20 is controlled by the power converter 26.
Information representing the operating state such as the actual rotational speed of the electric motor 20 is supplied from the motor ECU 28 to the hybrid ECU 58. The hybrid ECU 58 obtains the actual regenerative braking torque actually obtained based on the actual operating state of the electric motor 20, and outputs information representing the actual regenerative braking torque value to the brake ECU 56.
The brake ECU 56 determines the required hydraulic braking torque based on a value obtained by subtracting the actual regenerative braking torque from the total required braking torque, so that the brake cylinder hydraulic pressure approaches the target hydraulic pressure corresponding to the required hydraulic braking torque. The pressure increasing linear control valve 172, the pressure reducing valve 156 and the like are controlled.

  In regenerative cooperative control, in principle, the holding valves 153FL, FR, RL, RR1 of the front, rear, left and right wheels 2, 4, 46, 48 are all opened, and the pressure reducing valves 156FL, FR, RL, RR1 are all closed. State. Further, the master cutoff valves 194FL and FR are closed, the simulator control valve 202 is opened, the input side cutoff valve 148 is closed, and the output side cutoff valve 192 is closed. With the common passage 94 cut off from the mechanical pressure booster 96 and the brake cylinders 42FL and FR of the left and right front wheels 2 and 4 cut off from the master cylinder 62, the hydraulic pressure is controlled by the pressure boost linear control valve 172. The output hydraulic pressure of the source 64 is controlled, and the power control pressure is supplied to the common passage 94 and supplied to the four-wheel brake cylinders 42 and 52 in common. Note that when reducing the hydraulic pressure in the common passage 94, one or more of the pressure reducing valves 156FL, FR, RL, RR1 are controlled.

Thus, in this embodiment, the input side shut-off valve 148 is closed during normal operation.
Assume that the input side shut-off valve 148 is in an open state.
Since the output side shut-off valve 192 is in a closed state, the mechanical pressure intensifier 96 is in principle inoperative. However, the stepped piston 104 is allowed to advance within a range in which the sum of the volume of the high-pressure chamber 114, the volume of the small-diameter side chamber 112, and the volume of the large-diameter side chamber 110 is kept substantially constant. On the other hand, since the simulator control valve 202 is in the open state, the stroke simulator 200 is activated when the hydraulic pressure in the master passage 74 becomes larger than the operation start pressure of the stroke simulator 200. In this embodiment, the operation of the stroke simulator 200 is performed. The start pressure is smaller than the operation start pressure of the mechanical movable unit 98.
When the brake pedal 60 is operated and the hydraulic pressure in the master passage 74 becomes larger than the operation start pressure of the stroke simulator 200, the stroke simulator 200 is activated and the brake pedal 60 is allowed to advance. Thereafter, when the pressure exceeds the operation start pressure of the mechanical movable portion 98, the stepped piston 104 is moved forward, whereby the brake pedal 60 enters, and the driver feels uncomfortable.
On the other hand, in this embodiment, the input side shut-off valve 148 is closed. As a result, the brake pedal 60 is allowed to advance with the operation of the stroke simulator 200. Sudden entry is suppressed, and the driver's uncomfortable feeling can be reduced.
Further, by closing the input side shut-off valve 148, it is possible to reduce vibration, reduce operating noise, and the like.
The operation start pressure of the stroke simulator 200 is a value determined by a set load of the spring, a sliding resistance such as friction between the piston and the housing, and when the hydraulic pressure acting on the piston becomes larger than the operation start pressure, Movement is allowed. The operation start pressure is determined by the spring set load, frictional force, and the like.
The operation start pressure of the mechanical movable portion 98 is the same, and is a value determined by a set load of the spring 126, a sliding resistance such as a frictional force acting between the stepped piston 104 and the housing 102, and the like.

In this state, when the slip of the wheels 2, 4, 46, 48 becomes excessive and the antilock control start condition is satisfied, the holding valve 153 and the pressure reducing valve 156 are opened and closed independently, and the brake cylinders 42 are opened and closed. , 52 is controlled. The slip state of the front, rear, left and right wheels 2, 4, 46, 48 is set to an appropriate state.
Further, when the hydraulic brake system is mounted on a vehicle that does not include the electric drive device 8, in a vehicle in which regenerative cooperative control is not performed, when the system is normal, the total required braking torque and the hydraulic braking are performed. The pressure-increasing linear control valve 172 and the like are controlled so that the torque becomes equal.
The first input side shut-off valve control device and the second input side shut-off valve control device are configured by a portion that stores S4 of the hydraulic pressure supply state control program of the brake ECU 56, a portion that executes the program, and the like. Moreover, these can also be called a power control pressure supply part.
Further, the part for storing S4 of the brake ECU 56, the part for executing, the power hydraulic pressure source 64, the pressure-increasing linear control valve 172, the common passage 94, the individual passage 150, the brake cylinders 42, 52, etc. constitute a power hydraulic system. Is done.

2) When the control system is abnormal As shown in FIGS. The pressure-increasing linear control valve 172 is closed when no current is supplied to the solenoid 186, and the power hydraulic pressure source 64 is shut off from the common passage 94.
In addition, since the master shut-off valve 194 is closed, the brake cylinder 42 is shut off from the master cylinder 62.
Further, since the input side shut-off valve 148 and the output side shut-off valve 192 are opened, the mechanical pressure booster 96 is communicated with the master passage 74 and the common passage 94.
Further, since the holding valve 153RL is in the closed state and the holding valves 153FL, FR, and 153RR1 are in the open state, the brake cylinders 42FL, FR, and 52RR of the left and right front wheels 2 and 4 and the right rear wheel 48 are connected to the common passage 94. The brake cylinder 52RL of the left rear wheel 46 is shut off.
2-1) When the hydraulic pressure in the large-diameter side chamber 110 is equal to or less than the operation start pressure of the mechanical movable unit 98 As shown in FIG. In this case, the hydraulic pressure in the pressurizing chamber 72 (referred to as a master hydraulic pressure as a manual hydraulic pressure) is supplied to the common passage 94 via the master passage 74, the bypass passage 136, and the servo pressure passage 190, and the left and right front wheels 2 are supplied. , 4 and the right rear wheel 48 are supplied to the brake cylinders 42FL, FR, 52RR.
Since the valve opening pressure of the input-side check valve 99 is very small, it becomes possible to quickly supply the hydraulic fluid to the brake cylinder 42 in accordance with the operation of the brake pedal 60, and to reduce the delay in the effect of the hydraulic brake 40. be able to.

2-2) When the hydraulic pressure in the large-diameter side chamber 110 is higher than the operation start pressure of the mechanical movable unit 98 2-2-1) When the hydraulic pressure of the hydraulic fluid stored in the accumulator 66 is higher than the allowable pressure Even when the operation of 65 is stopped, if the hydraulic pressure of the hydraulic fluid stored in the accumulator 66 is higher than the set pressure, the operation of the mechanical movable unit 98 is permitted. The set pressure is such a size that the mechanical type capable portion 98 can be operated, in other words, a size capable of supplying the hydraulic pressure to the high pressure chamber 114 of the mechanical type movable portion 98, and the high pressure chamber 114 (the small diameter side chamber 112). ) Can be considered to be larger than the hydraulic pressure. The set pressure can be referred to as an operation permission pressure.
As indicated by the solid line in FIG. 8A, the stepped piston 104 is advanced by the hydraulic pressure in the large-diameter side chamber 110, contacts the valve opening member 125, and the high-pressure supply valve 116 is switched to the open state. The small-diameter side chamber 112 is shut off from the large-diameter side chamber 110, and high-pressure hydraulic fluid is supplied from the accumulator 66 to the high-pressure chamber 114 through the high-pressure side check valve 100 and then supplied to the small-diameter side chamber 112. The hydraulic pressure in the small-diameter side chamber 112 is made higher than the hydraulic pressure in the master cylinder 62, is supplied to the common passage 94 through the output-side shut-off valve 192 in the open state, passes through the holding valves 153FL, FR, 153RR1, and the left and right front wheels 2, 4 , Are supplied to the brake cylinders 42FL, 42RR, 52RR of the right rear wheel 48.
The hydraulic pressure Pout of the small-diameter side chamber 112 is assumed to be equal to the hydraulic pressure of the master cylinder 62 (the hydraulic pressure of the large-diameter side chamber 110) Pin and the large-diameter portion side of the stepped piston 104, assuming that the operation start pressure is zero. A value Pout = Pin · (Sin / Sout) obtained by multiplying the ratio (Sin / Sout) of the pressure receiving area Sin and the pressure receiving area Sout on the small diameter portion side
It becomes. This hydraulic pressure Pout is referred to as servo pressure. From this, the small-diameter side chamber 112 can be called a control pressure chamber.
The mechanical pressure increasing device 96 is actuated by the hydraulic pressure in the pressurizing chamber 72, and therefore can be considered as a manual hydraulic pressure source in a broad sense. In the present embodiment, the pressurizing chamber 72 corresponds to a manual pressure source connected to a pressure booster as a first manual hydraulic pressure source, and the mechanical pressure booster 96 corresponds to a second manual hydraulic pressure source. .

As shown in FIG. 8 (b), in a vehicle in which the driver's seat is on the right side in the forward direction (the steering member 300 is on the right side in the forward direction), a so-called right-hand drive vehicle, In some cases, the center of gravity G1 of the entire vehicle including the driver or the like is located on the right side of the center in the left-right direction. In this vehicle, the length rL of the arm from the center of gravity G1 to the contact point with the road surface of the left wheels 2, 46 is longer than the length rR of the arm to the contact point with the road surface of the right wheels 4, 48 (rL > RR).
In this case, when the hydraulic pressure of the mechanical pressure booster 96 is supplied to the brake cylinders 42FL and FR of the left and right front wheels 2 and 4 when the control system is abnormal, the yaw moment γ in the left turn direction is increased. Works.
γ = rR · (F _FR ) −rL · (F _FL ) <0

On the other hand, in this embodiment, as shown in FIG. 8A, when the control system is abnormal, the servo pressure, which is the hydraulic pressure of the mechanical pressure booster 96, is applied to the brake cylinders 42FL of the left and right front wheels 2, 4. , FR and the brake cylinder 52RR of the right rear wheel 48, the hydraulic pressures of these three-wheel brake cylinders 42FL, FR, RR are substantially the same (P _FL = P _FR = P _RR ). Therefore, the sum of the braking force (force acting between the road surface and the tire) caused by the hydraulic pressure supplied to the brake cylinders 42FL and 52RL of the left wheels 2 and 46 (the brake cylinder 52RL of the left rear wheel 46 has no liquid) Pressure is not supplied) is smaller than the sum of the braking forces resulting from the hydraulic pressure supplied to the brake cylinders 42FR, RR of the right wheels 4, 48 (F _FL <F _FR + F _RR ).
And the absolute value of the yaw moment γ acting on this vehicle is
| Γ | = | rR · (F _FR + F _RR ) −rL · (F _FL ) |
However, since the arm rL is longer than the arm rR as described above, the absolute value of the acting yaw moment γ can be reduced.

Thus, in this embodiment, when the control system is abnormal, the servo pressure of the mechanical pressure booster 96 is supplied to the three brake cylinders of the front, rear, left and right four wheels. The sum of the braking forces acting on 46 and the sum of the braking forces acting on the right wheels 4, 48 are not equal. However, when the servo pressure of the mechanical booster 96 is at a position where the center of gravity G1 deviates from the center in the left-right direction of the vehicle, the sum of the braking forces on the short side of the arm from the center of gravity G1 It is distributed so as to be larger than the sum of braking forces. Therefore, yaw moment can be made difficult to occur when the control system is abnormal.
In this embodiment, manual operation is performed by the master cylinder 62, the mechanical pressure intensifier 96, the common passage 94, the individual passages 150FL, FR, RR, the normally open holding valves 153FL, FR, RR1, the brake cylinders 42FL, FR, 52RR, and the like. A hydraulic system is constructed. The manual hydraulic system includes a single hydraulic distribution unit.

2-2-2) When the hydraulic pressure of the hydraulic fluid stored in the accumulator 66 is equal to or lower than the allowable pressure for operation When the hydraulic pressure of the hydraulic fluid stored in the accumulator 66 is equal to or lower than the allowable pressure of operation, FIG. Similarly to the state shown in the figure, the master hydraulic pressure in the pressurizing chamber 72 of the master cylinder 62 passes through the master passage 74, the bypass passage 136, the servo pressure passage 190, and the common passage 94 to brake the left and right front wheels 2, 4 and the right rear wheel 48. It is supplied to the cylinders 42 and 52RR.
On the other hand, when the hydraulic pressure of the hydraulic fluid stored in the accumulator 66 is lowered by the operation of the mechanical movable unit 98 and becomes lower than the operation permission pressure, the hydraulic fluid is not supplied from the accumulator 66 to the high-pressure chamber 114. Thereby, the mechanical movable part 98 becomes difficult to operate. For example, when a pumping brake operation is performed, the amount of hydraulic fluid consumed by the accumulator 66 increases, and the accumulator pressure becomes lower than the operation permission pressure. The forward movement of the stepped piston 104 is prevented (it is advanced until it abuts against the stopper, and then the forward movement is considered to be blocked), and the hydraulic pressure in the small-diameter side chamber 112 does not increase any further, and the mechanical type The movable part 98 cannot exhibit the boosting function. When the hydraulic pressure in the pressurizing chamber 72 becomes higher than the hydraulic pressure in the small-diameter side chamber 112, the hydraulic pressure in the pressurizing chamber 72 of the master cylinder 62 is changed to the bypass passage 136 as shown by the broken line in FIG. , The servo pressure passage 190 is supplied to the common passage 94. The hydraulic pressure in the pressurizing chamber 72 of the master cylinder 62 is supplied to the brake cylinders 42FL, 42FR, 52RR of the left and right front wheels 2, 4, and the right rear wheel 48 without being boosted.

  In the master cylinder 62, the volume of the pressurizing chamber 72 can be increased. If the volume of the pressurizing chamber 72 is increased, it is possible to avoid a shortage of fluid even when hydraulic fluid is supplied to both the brake cylinders 42FL and FR of the left and right front wheels 2 and 4. In this case, the stroke of the driver's brake pedal 60 may be increased.

3) When it is detected that there is a possibility of liquid leakage As shown in FIG. 9, the holding valves 153FL, FR of the left and right front wheels 2, 4 are closed, and the holding valves 153RL, RR1 of the left and right rear wheels 46, 48 are closed. Is opened. Further, the master cutoff valves 194FL and FR are opened, and the input side cutoff valve 148, the output side cutoff valve 192, and the simulator control valve 202 are closed. Further, all the pressure reducing valves 156 are closed.
The hydraulic pressures in the pressurizing chambers 72 and 70 of the master cylinder 62 are respectively supplied to the brake cylinders 42FL and FR of the left and right front wheels 2 and 4, and the pump devices are supplied to the brake cylinders 52RL and RR of the left and right rear wheels 46 and 48, respectively. A hydraulic pressure of 65 is controlled and supplied.
In this way, the holding valves 153FL, FR of the left and right front wheels 2, 4 are shut off, so that the brake cylinders 42FL, FR of the left and right front wheels 2, 4 are independent from each other. Further, the brake cylinders 42FL, FR of the left and right front wheels 2, 4 and the brake cylinders 52RL, RR of the left and right rear wheels 46, 48 are blocked. The brake cylinders of the front wheels 2 and 4 and the rear wheels 46 and 48 are blocked from each other, and the brake cylinders of the left front wheel 2 and the right front wheel 4 are blocked from each other on the front wheel side. That is, (brake system 250FL including the brake cylinder 42FL of the left front wheel 2), (brake system 250FR including the brake cylinder 42FR of the right front wheel 4), (brake system 250R including the brake cylinders 52FL and RR of the left and right rear wheels 46 and 48) ) Are disconnected from each other. As a result, even if liquid leakage occurs in one of these three brake systems, the other brake systems can be prevented from being affected.
In this sense, the holding valves 153FL and FR have a function as a separation valve that separates the brake systems 250FR, FL, and R.

In this embodiment, the brake system 250FR includes a brake cylinder 42FR, a master passage 76, a pressurizing chamber 70, a storage chamber 80, etc., and the brake system 250FL includes the brake cylinder 42FL, the master passage 74, and the pressurizing chamber 72. The brake system 250R includes the brake cylinders 52RL and RR, the individual passages 150RL and RR, the power hydraulic pressure source 64, the storage chamber 84, and the like. Therefore, the fact that the brake systems 250FR, FL, R are made independent from each other means that the storage chambers 80, 82, 84 of the reservoir 78 are also made independent from each other.
In the present embodiment, a manual hydraulic pressure / power control pressure supply unit is configured by a part that stores S6 of the brake ECU 56, a part that executes S6, and the like.

  Further, even when there is no possibility of liquid leakage, the state shown in FIG. 9 can be obtained when the hydraulic pressure of the hydraulic fluid stored in the accumulator 66 is lower than the operation permission pressure. It is considered that the hydraulic pressure of the hydraulic fluid stored in the accumulator 66 is lower than the operation permission pressure due to an abnormality of the pump device 65 (control of the electromagnetic on-off valve is possible). It is assumed that there is an abnormality in the control system, and the state shown in FIGS. However, even if the state shown in FIGS. 7 and 8 is established, the mechanical movable portion 98 becomes inoperable, and the brake cylinders 42FL, FR, and 52RR are pressurized by the master cylinder 62 as shown by the broken lines in FIG. The fluid pressure in the chamber 72 is supplied. On the other hand, if the state is switched to the state shown in FIG. 9, the pressurizing chambers 72 and 70 are communicated with the brake cylinders 42FL and FR, respectively, so that insufficient hydraulic pressure can be suppressed. If the hydraulic pressure in the brake cylinders 52RL and RR of the left and right rear wheels 46 and 48 cannot be effectively controlled due to the low hydraulic pressure of the hydraulic fluid stored in the accumulator 66, the pressure-increasing linear control is performed. It is desirable that the valve 172 be closed and the holding valves 153RL and RR1 be closed.

4) When the hydraulic brake is released When the brake operation is released, the current is not supplied to the solenoids of all the valves, thereby returning the original position of FIG. In the mechanical pressure increasing device 96, the stepped piston 104 is at the retracted end (or returned to the retracted end). The stepped piston 104 is separated from the valve opening member 125, and the intra-piston communication path 129 is opened. The hydraulic pressures in the brake cylinders 42FL, FR, 52RR of the left and right front wheels 2, 4 and the right rear wheel 48 are returned to the master cylinder 62 (master reservoir 78) via the piston internal communication passage 129 and the piston check valve 130. Further, the hydraulic pressure in the brake cylinder 52RL of the left rear wheel 46 is returned to the reservoir 78 via the pressure reducing valve 156RL.

5) Ignition switch 234 in OFF state By supplying current to the solenoids of all the valves, the original position in FIG. 2 is obtained.
a) As shown in FIG. 2, since the pressure-increasing linear control valve 172 is in the closed state, the power hydraulic pressure source 64 is cut off from the common passage 94. Therefore, even if there is a fluid leak on the downstream side (brake cylinders 42FL, FR, 52RR) from the common passage 94, the hydraulic fluid is not allowed to flow out from the storage chamber 84 of the reservoir 78 through the power hydraulic passage 170. Is prevented.
b) Since the master shut-off valve 194 is in the closed state, even if liquid leaks around the brake cylinders 42FL and FR of the left and right front wheels 2 and 4, the reservoir passages 80 and 82 pass through the master passages 74 and 76. The hydraulic fluid is prevented from flowing out.
c) Since the input side check valve 99 and the in-piston check valve 130 are provided, even if there is a liquid leak downstream of the common passage 94, the mechanical pressure booster from the storage chamber 82 of the master reservoir 78 The outflow of hydraulic fluid through 96 can be prevented. Even if there is a liquid leak on the downstream side of the common passage 94, the hydraulic fluid is prevented from flowing out from the storage chamber 82 of the master reservoir 78 through the in-piston communication passage 129, and the input side check valve 99, The in-piston check valve 130 and the like constitute an outflow prevention device 260.

The vehicle equipped with the hydraulic brake circuit and the hydraulic brake circuit is not limited to that in the first embodiment. An example is shown in FIGS. 10 (a) and 10 (b).
In the hydraulic brake circuit shown in FIG. 10A, the holding valve 153RR corresponding to the brake cylinder 52RR of the right rear wheel 48 is normally closed, and the pressure reducing valve 156RR is normally open. Further, the holding valve 153RL2 corresponding to the brake cylinder 52RL of the left rear wheel 46 is a normally open valve, and the pressure reducing valve 156RL2 is a normally closed valve. In this embodiment, when the control system is abnormal, the servo pressure of the mechanical pressure booster 96 is supplied to the brake cylinders 42FL, FR, 52RL of the left and right front wheels 2, 4 and the left rear wheel 46. Other parts are the same as those in the first embodiment.
As shown in FIG. 10 (b), the driver's seat is on the left side in the forward direction (the steering member 302 is on the left side in the forward direction). When the center of gravity G2 is located on the left side of the center in the left-right direction, the absolute value of the yaw moment γ acting on the vehicle when the control system is abnormal is
| Γ | = | rR (F _FR ) −rL (F _FL + F _RL ) |
It becomes.
In this case, the sum of the braking forces acting on the right wheels 4, 48 is smaller than the sum of the braking forces acting on the left wheels 2, 46 {(F _FR ) <(F _FL + F _RL )}, and the right wheel from the center of gravity G2 Since the arm rR to the contact point with respect to the road surface 4, 48 is longer than the arm rL to the contact point of the left wheel 2, 46 (rR> rL), the absolute value of the acting yaw moment γ can be reduced.
In this embodiment, manual operation is performed by a master cylinder 62, a mechanical pressure intensifier 96, a common passage 94, individual passages 150FL, FR, RL, normally open holding valves 153FL, FR, RL2, brake cylinders 42FL, FR, 52RR, and the like. A hydraulic system is constructed. The manual hydraulic system includes a single hydraulic distribution unit. The pressurizing chamber 72 corresponds to the first manual hydraulic pressure source, and the mechanical pressure intensifying device 96 corresponds to the second manual hydraulic pressure source.

In the hydraulic brake circuit of FIG. 11A, the master cutoff valve 194FR3 corresponding to the brake cylinder 42FR of the right front wheel 4 is a normally open valve, and the holding valve 153FR3 is a normally closed valve. Further, the holding valve 153RR3 corresponding to the brake cylinder 52RR of the right rear wheel 48 is a normally open valve, and the pressure reducing valve 153RR3 is a normally closed valve. Other parts are the same as those in the first embodiment.
When the control system is abnormal, the master pressure is supplied to the brake cylinder 42FR of the right front wheel 4, and the servo of the mechanical pressure booster 96 is applied to the brake cylinders 42FL and 52RR of the diagonal wheels (left front wheel 2, right rear wheel 48). Pressure is supplied.
The yaw moment γ in the right turn direction acting on the vehicle with the driver's seat on the left side in the forward direction (the vehicle with the steering wheel 302 on the left side) is
γ = rR (F _FR + F _RR ) −rL (F _FL )
It becomes.
In the above formula, the hydraulic pressure Pm of the master cylinder 62 is smaller than the servo pressure Pb of the mechanical pressure booster 96 (Pm <Pb). When the brake cylinder hydraulic pressure is the same, the braking force acting on the rear wheel is smaller than the braking force acting on the front wheel. Therefore, the sum of braking forces acting on the left wheels 2 and 46 and the sum of braking forces acting on the right wheels 4 and 8 are substantially the same.
(F _FL ) ≒ (F _FR + F _RR )
On the other hand, since the length of the arm rR is longer than the length of the arm rL (rR> rL), in this embodiment, the yaw moment γ is a positive value (γ> 0). Therefore, as shown in FIG. 11 (b), when the control system is abnormal, the yaw moment in the right turning direction acts on the left-hand drive vehicle.
The yaw moment that acts when the control system is abnormal is in the direction in which the vehicle deviates from the oncoming lane in an area where the left-hand drive vehicle travels on the right side according to regulations. As a result, for example, when the driver performs a correction operation, the safety of the vehicle can be improved as compared with the case where the yaw moment in the direction approaching the oncoming lane acts.
In the present embodiment, the power hydraulic pressure source 64, the pressure-increasing linear control valve 172, the common passage 94. The individual passage 150, the holding valve 153, the brake cylinders 42, 52, etc. constitute a power hydraulic system, and the master cylinder 62, the mechanical pressure booster 96, the common passage 94, the individual passages 150FL, RR, the normally open holding valve 153FL3. , RR3, master passage 76, normally open master shut-off valve 194FL3, brake cylinders 42FL, FR, 52RR, etc. constitute a manual hydraulic system. The manual hydraulic system includes a mixed hydraulic distribution unit. The pressurizing chamber 72 corresponds to the first manual hydraulic pressure source, and the mechanical pressure intensifying device 96 corresponds to the second manual hydraulic pressure source.

In the hydraulic brake circuit shown in FIG. 12A, the master shut-off valve 194FL4 corresponding to the brake cylinder 42FL of the left front wheel 2 is a normally open valve, and the holding valve 153FL4 is a normally closed valve. Further, the holding valve 153RL4 corresponding to the left rear wheel 46 is a normally open valve, and the pressure reducing valve 153RL4 is a normally closed valve. Other parts are the same as those in the first embodiment.
When the control system is abnormal, the master pressure is supplied to the brake cylinder 42FL of the left front wheel 2, and the servo pressure of the mechanical pressure booster 96 is applied to the brake cylinders 42FR and 52RL of the diagonal wheels (the right front wheel 4 and the left rear wheel 46). Is supplied.
The yaw moment γ in the right turn direction acting on the vehicle whose driver's seat is on the right side in the forward direction (the vehicle on which the steering wheel 300 is on the right side) is
γ = rR (F _FR ) −rL (F _FL + F _RL )
It becomes. In the above equation, the sum of braking forces acting on the left wheels 2 and 46 and the sum of braking forces acting on the right wheels 4 and 8 are substantially the same.
(F _FR ) ≒ (F _FL + F _RL )
On the other hand, since the arm rL is longer than the arm rR (rL> rR), the yaw moment γ becomes a negative value (γ <0) as shown in FIG.
This yaw moment is in a direction in which the vehicle deviates from the oncoming lane in an area where the right-hand drive vehicle travels in the left lane by law. As a result, traveling safety when the control system is abnormal can be improved.
In this embodiment, the master cylinder 62, the mechanical pressure increasing device 96, the common passage 94, the individual passages 150FR and RL, the normally open holding valves 153FR4 and RL4, the master passage 76, the normally open master shut-off valve 194FR4 and the brake cylinder. 42FL, FR, 52RL, etc. constitute a manual hydraulic system. The manual hydraulic system includes a single hydraulic distribution unit. The pressurizing chamber 72 corresponds to the first manual hydraulic pressure source, and the mechanical pressure intensifying device 96 corresponds to the second manual hydraulic pressure source.

  Further, when the control system is abnormal, the servo pressure can be supplied to the brake cylinders of the wheels that are diagonal to each other. For example, as shown in FIG. 13A, in the brake circuit shown in FIG. 11A, the master cutoff valve 194FR3 can be a normally closed valve (master cutoff valve 194FRb). In the present embodiment, the servo pressure is supplied to the brake cylinders 42FL and 52RR of the left front wheel 2 and the right rear wheel 48. As shown in FIG. 13B, in a vehicle with the steering wheel 302 provided on the left side, the braking force applied to the right wheel (the one with the longer arm) is greater than the braking force applied to the left wheel (the one with the shorter arm). Therefore, the yaw moment can hardly be generated. In the present embodiment, the second hydraulic pressure supply unit is configured by the part that stores S5 of the brake ECU 56, the part that executes S5, and the like. The pressurizing chamber 72 corresponds to the first manual hydraulic pressure source, and the mechanical pressure intensifying device 96 corresponds to the second manual hydraulic pressure source.

  As shown in FIG. 14 (a), in the brake circuit shown in FIG. 12 (a), the master cutoff valve 194FL4 can be a normally closed valve (master cutoff valve 194FLc). In the present embodiment, servo pressure is supplied to the brake cylinders 42FR and 52RL of the right front wheel 4 and the left rear wheel 46. As shown in FIG. 14B, in a vehicle with the steering wheel 300 provided on the right side, the braking force applied to the left wheel (the one with the longer arm) is greater than the braking force applied to the right wheel (the one with the shorter arm). Therefore, the yaw moment can hardly be generated. In the present embodiment, the second hydraulic pressure supply unit is configured by the part that stores S5 of the brake ECU 56, the part that executes S5, and the like. The pressurizing chamber 72 corresponds to the first manual hydraulic pressure source, and the mechanical pressure intensifying device 96 corresponds to the second manual hydraulic pressure source.

Other examples

In addition, the structure of a brake circuit is not ask | required.
Further, the mechanical pressure intensifying device 96 can be directly connected to the master passage 74. In other words, the input side shut-off valve 148 is not indispensable.
Furthermore, it is not essential to provide the outflow prevention device 260.
In the present embodiment, the input side shut-off valve 148 is not essential.
Furthermore, a pressure-reducing linear control valve can be provided between the common passage 94 and the reservoir 78, and the pressure-reducing control of the fluid pressure in the common passage 94 can be performed by the pressure-reducing linear control valve.

Although a plurality of embodiments have been described above, two or more of the plurality of embodiments may be combined with each other.
In addition, the present invention can be implemented in a mode in which a plurality of examples are combined, and in addition to the mode described above, the present invention is implemented in a mode in which various modifications and improvements are made based on the knowledge of those skilled in the art. Can do.

  40, 50: Hydraulic brake 42, 52: Brake cylinder 54: Hydraulic pressure control unit 56: Brake ECU 60: Brake pedal 62: Master cylinder 64: Powered hydraulic pressure source 66: Accumulator 70, 72: Pressurizing chamber 74, 76: Master passage 94: Common passage 96: Mechanical pressure booster 98: Mechanical movable portion 99: Input side check valve 100: High pressure side check valve 104: Stepped piston 110: Large diameter side chamber 112: Small diameter side chamber 116 : High pressure supply valve 132: High pressure side check valve 136: Bypass passage 148: Input side shutoff valve 150: Individual passage 153: Holding valve 156; Pressure reducing valve 170: Power hydraulic pressure passage 172: Boosting linear control valve 190: Servo pressure Passage 192: Output side shut-off valve 218: Brake switch 220: Stroke sensor 222: Master cylinder Pressure sensor 226: Brake cylinder pressure sensor 228: level warning 250FL, FR, R: the brake fluid pressure circuit

Claims (11)

A hydraulic brake provided on each of the four wheels on the front, rear, left, and right sides of the vehicle, each of which is operated by a hydraulic pressure of a brake cylinder to suppress rotation of the wheels;
Including a power hydraulic pressure source that generates hydraulic pressure by supplying electric energy, and controlling the output hydraulic pressure using the hydraulic pressure of the power hydraulic pressure source . Power hydraulic system to supply the brake cylinder of four wheels,
A manual hydraulic pressure source that generates hydraulic pressure by the driver's brake operation force is included, and when the power hydraulic system is abnormal that the output hydraulic pressure cannot be controlled, the brake of one of the four wheels is braked. A manual hydraulic system for supplying the manual hydraulic pressure to the three brake cylinders excluding the one of the four wheels without supplying a manual hydraulic pressure that is a hydraulic pressure of the manual hydraulic pressure source to the cylinder; A hydraulic brake system comprising: The power hydraulic system includes a power hydraulic pressure control device that controls the output hydraulic pressure using the hydraulic pressure of the power hydraulic pressure source;
The manual hydraulic system includes (i) at least one pressurizing chamber of a master cylinder that generates hydraulic pressure by an operating force of a driver's brake operating member, and (ii) a stepped piston, and the at least one additional pressure chamber. 2. The hydraulic brake system according to claim 1, further comprising: a pressure increasing device operable by a hydraulic pressure of one of the pressure chambers and generating a hydraulic pressure higher than a hydraulic pressure of the one pressurizing chamber. The manual hydraulic system, the three-wheel brake cylinders, a single type liquid-supplying either one of the fluid pressure of said at least one pressure chamber hydraulic said pressure boosting device as the manual hydraulic pressure The hydraulic brake system according to claim 2 , comprising a pressure supply unit. The master cylinder has two pressure chambers;
The manual hydraulic system includes the two pressurizing chambers,
The pressure increasing device is operable at least by the hydraulic pressure of one of the two pressurizing chambers and generates a hydraulic pressure higher than the hydraulic pressure of the one pressurizing chamber;
The manual hydraulic system, the part of the three-wheel brake cylinders, said other hydraulic two pressurizing chambers supplied as the manual hydraulic pressure, remaining of the three-wheel brake cylinder The hydraulic brake system according to claim 2 , further comprising: a mixed hydraulic pressure supply unit that supplies the hydraulic pressure of the booster as the manual hydraulic pressure . When the manual hydraulic system is abnormal in that the power hydraulic system cannot control the output hydraulic pressure, the arm length from the center of gravity of the vehicle to the ground contact point of the right wheel and the ground contact point of the left wheel Compared to the length of the arm, the four wheels on the front, rear, left, and right are compared so that the sum of the braking forces applied to the front and rear wheels on the long side is smaller than the sum of the braking forces applied to the front and rear wheels on the short side. hydraulic braking system according to any one of claims 1 to 4 comprising a supply unit for supplying said manual hydraulic pressure to the three wheel brake cylinders of the house. A hydraulic brake that is provided on each of the four wheels on the front, rear, left, and right of the vehicle provided on the right side in the forward direction, and is operated by the hydraulic pressure of the brake cylinder to suppress rotation of the wheels;
Including a power hydraulic pressure source that generates hydraulic pressure by supplying electric energy, and controlling the output hydraulic pressure using the hydraulic pressure of the power hydraulic pressure source . Power hydraulic system to supply the brake cylinder of four wheels,
A manual hydraulic pressure source that generates hydraulic pressure by the driver's brake operation force is included, and when the power hydraulic pressure system is abnormal that the output hydraulic pressure cannot be controlled , the yaw is directed to turn the vehicle to the left. as moment occurs before Symbol a is the manual hydraulic pressure not supply the hydraulic pressure of the manual hydraulic pressure source to a wheel brake cylinder of the four wheels, except the one wheel among the four wheels A hydraulic brake system including a manual hydraulic system for supplying the manual hydraulic pressure to a three-wheel brake cylinder. A hydraulic brake that is provided on each of the four wheels on the front, rear, left, and right of the vehicle provided on the right side in the forward direction, and is operated by the hydraulic pressure of the brake cylinder to suppress rotation of the wheels;
Including a power hydraulic pressure source that generates hydraulic pressure by supplying electric energy, and controlling the output hydraulic pressure using the hydraulic pressure of the power hydraulic pressure source . Power hydraulic system to supply the brake cylinder of four wheels,
Includes a manual hydraulic pressure source for generating hydraulic pressure by the brake operating force by the driver, the power hydraulic system is, if an abnormality that can not control the output hydraulic pressure, the brake of the left rear wheel of the four wheels A manual hydraulic system that supplies the manual hydraulic pressure to the brake cylinders of the right front wheel, the left front wheel, and the right rear wheel of the four wheels without supplying the manual hydraulic pressure that is the hydraulic pressure of the manual hydraulic pressure source to the cylinder. And a hydraulic brake system. A hydraulic brake that is provided on each of the four front, rear, left, and right wheels of the vehicle provided with a driver's seat on the left side in the forward direction, and that is operated by the hydraulic pressure of the brake cylinder to suppress the rotation of the wheels;
Including a power hydraulic pressure source that generates hydraulic pressure by supplying electric energy, and controlling the output hydraulic pressure using the hydraulic pressure of the power hydraulic pressure source . Power hydraulic system to supply the brake cylinder of four wheels,
A manual hydraulic pressure source that generates hydraulic pressure by a driver's brake operation force is included, and when the power hydraulic pressure system is abnormal that the output hydraulic pressure cannot be controlled , the yaw is oriented to turn the vehicle to the right. The manual hydraulic pressure, which is the hydraulic pressure of the manual hydraulic pressure source, is not supplied to the brake cylinder of one of the four wheels so that a moment is generated, and the one of the four wheels is excluded. A hydraulic brake system comprising: a manual hydraulic system for supplying the manual hydraulic pressure to a brake cylinder of the wheel. A hydraulic brake that is provided on each of the four front, rear, left, and right wheels of the vehicle provided with a driver's seat on the left side in the forward direction, and that is operated by the hydraulic pressure of the brake cylinder to suppress the rotation of the wheels;
Including a power hydraulic pressure source that generates hydraulic pressure by supplying electric energy, and controlling the output hydraulic pressure using the hydraulic pressure of the power hydraulic pressure source . Power hydraulic system to supply the brake cylinder of four wheels,
Includes a manual hydraulic pressure source for generating hydraulic pressure by the brake operating force by the driver, the power hydraulic system is, if an abnormality that can not control the output hydraulic pressure, the brake of the right rear wheel of the four wheels Manual fluid is supplied to the brake cylinders of the right front wheel, left front wheel, and left rear wheel of the four wheels without supplying manual fluid pressure that is the fluid pressure of the manual fluid pressure source to the cylinder. A hydraulic brake system including a pressure system. The power hydraulic system includes a power hydraulic pressure control device that controls the output hydraulic pressure using the hydraulic pressure of the power hydraulic pressure source,
The manual hydraulic system includes (i) at least one pressurizing chamber of a master cylinder that generates hydraulic pressure by an operating force of a driver's brake operating member, and (ii) a stepped piston, and the at least one additional pressure chamber. 10. The pressure intensifier device according to claim 6, further comprising a pressure increasing device operable by a hydraulic pressure of one of the pressure chambers and generating a hydraulic pressure higher than a hydraulic pressure of the one pressurizing chamber. Hydraulic brake system. A hydraulic brake provided on each of the four wheels on the front, rear, left, and right sides of the vehicle, each of which is operated by a hydraulic pressure of a brake cylinder to suppress rotation of the wheels;
Including a power hydraulic pressure source that generates hydraulic pressure by supplying electric energy, and controlling the output hydraulic pressure using the hydraulic pressure of the power hydraulic pressure source . Power hydraulic system to supply the brake cylinder of four wheels,
When the power hydraulic pressure system is abnormal in that the output hydraulic pressure cannot be controlled , the braking force applied to the right wheel and the left wheel are applied to the two brake cylinders diagonally positioned among the four wheels. as the braking force applied to become different sizes, the manual hydraulic supply pressure, said four of said two wheels of the brake cylinder with the exception of two wheels of the wheel does not supply the manual hydraulic pressure manual Including a hydraulic system,
The manual hydraulic system includes (i) at least one pressurizing chamber of a master cylinder that generates hydraulic pressure by an operating force of a driver's brake operating member, and (ii) a stepped piston, and the at least one additional pressure chamber. A pressure increasing device that is operable by a hydraulic pressure of one of the pressure chambers and that generates a hydraulic pressure higher than the hydraulic pressure of the one pressurizing chamber; and (iii) the two-wheel brake in the diagonal position A hydraulic brake system comprising: a second hydraulic pressure supply unit that supplies a hydraulic pressure of the pressure increasing device to the cylinder as the manual hydraulic pressure .

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