WO2014010701A1 - 車両用制動装置 - Google Patents
車両用制動装置 Download PDFInfo
- Publication number
- WO2014010701A1 WO2014010701A1 PCT/JP2013/069039 JP2013069039W WO2014010701A1 WO 2014010701 A1 WO2014010701 A1 WO 2014010701A1 JP 2013069039 W JP2013069039 W JP 2013069039W WO 2014010701 A1 WO2014010701 A1 WO 2014010701A1
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- WIPO (PCT)
- Prior art keywords
- pressure
- piston
- master
- chamber
- pilot
- Prior art date
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
- B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
- B60T13/12—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid
- B60T13/16—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid using pumps directly, i.e. without interposition of accumulators or reservoirs
- B60T13/168—Arrangements for pressure supply
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T7/00—Brake-action initiating means
- B60T7/02—Brake-action initiating means for personal initiation
- B60T7/04—Brake-action initiating means for personal initiation foot actuated
- B60T7/042—Brake-action initiating means for personal initiation foot actuated by electrical means, e.g. using travel or force sensors
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
- B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
- B60T13/12—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid
- B60T13/14—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid using accumulators or reservoirs fed by pumps
- B60T13/142—Systems with master cylinder
- B60T13/145—Master cylinder integrated or hydraulically coupled with booster
- B60T13/146—Part of the system directly actuated by booster pressure
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
- B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
- B60T13/12—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid
- B60T13/16—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid using pumps directly, i.e. without interposition of accumulators or reservoirs
- B60T13/161—Systems with master cylinder
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
- B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
- B60T13/66—Electrical control in fluid-pressure brake systems
- B60T13/662—Electrical control in fluid-pressure brake systems characterised by specified functions of the control system components
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
- B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
- B60T13/66—Electrical control in fluid-pressure brake systems
- B60T13/68—Electrical control in fluid-pressure brake systems by electrically-controlled valves
- B60T13/686—Electrical control in fluid-pressure brake systems by electrically-controlled valves in hydraulic systems or parts thereof
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
- B60T17/18—Safety devices; Monitoring
- B60T17/22—Devices for monitoring or checking brake systems; Signal devices
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
- B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
- B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
- B60T8/4072—Systems in which a driver input signal is used as a control signal for the additional fluid circuit which is normally used for braking
- B60T8/4077—Systems in which the booster is used as an auxiliary pressure source
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T2270/00—Further aspects of brake control systems not otherwise provided for
- B60T2270/40—Failsafe aspects of brake control systems
- B60T2270/414—Power supply failure
Definitions
- the present invention relates to a vehicle braking device that applies a friction braking force to a vehicle.
- a vehicle braking device that applies a friction braking force to a vehicle
- a vehicle braking device shown in FIGS. 11 and 12 of Patent Document 1 is known.
- the input piston and the master piston are held in a state of being separated with a predetermined interval, and when the input piston moves, the required braking force is calculated according to the amount of movement of the input piston, The required friction braking force is calculated by subtracting the required regenerative braking force from the required braking force.
- the servo pressure generated based on the required friction braking force acts on the master piston to move the master piston, generate the master pressure in the master chamber, and apply the master pressure to the wheel cylinder to generate the required friction braking force.
- a master pressure is introduced into a pilot hydraulic pressure chamber provided on the end face side opposite to the second pilot hydraulic pressure chamber in the second pressure regulating piston.
- the second pressure regulating piston has a differential pressure between the master pressure and the pilot pressure. May be moved by moving the first pressure regulating piston in the direction of the first pressure regulating piston, which may affect the characteristics of the generated servo pressure.
- the present invention has been made in view of such circumstances, and in the event of an emergency such as a power system failure, the servo pressure supplied to the master cylinder by the master pressure generated by the driver pressing the brake pedal.
- An object of the present invention is to provide a vehicular braking apparatus capable of stably generating a servo pressure even when the master pressure is greater than the pilot pressure.
- the invention according to claim 1, which has been made to solve the above-described problem, includes a cylinder (10 a) and a master chamber (10 f) that is disposed in the cylinder so as to be slidable in the axial direction and pressurizes brake fluid.
- a master piston (11a) having a pressurizing piston portion (11a2) that divides the inner peripheral surface of the cylinder and a servo pressure receiving portion (11a1) that divides the servo pressure chamber (10e) from the inner peripheral surface of the cylinder;
- An input piston (12) disposed slidably in the axial direction on the rear side of the cylinder so as to be separated from a rear end surface of the master piston by a predetermined distance;
- a pilot pressure generator (40) that generates a pilot pressure corresponding to the operation amount of the input piston, and is slidable in the housing (55)
- a first piston (51) that divides the housing into a first pilot chamber (53) that communicates with the pilot pressure generator and a servo pressure generation chamber (57) that communicates with the servo pressure chamber;
- a valve mechanism (56) communicating the servo pressure generating chamber with the pressure accumulating device or the reservoir according to the movement of the first piston and the housing are fitted in the housing so as to be able to come into contact
- a regulator (50) having a second piston (52) that divides the first pilot chamber and a second pilot chamber (54) communicated with the master chamber.
- the end surface (52b1) exposed to the first pilot chamber side was formed to have a larger pressure receiving area than the end surface (52a1) exposed to the second pilot chamber side.
- the invention according to claim 2 is the invention according to claim 1, wherein the difference between the pressure receiving area of the end surface exposed to the first pilot chamber side of the second piston and the pressure receiving area of the end surface exposed to the second pilot chamber side is Even when the master piston is moved in the direction of decreasing the master pressure, and the master pressure becomes larger than the pilot pressure due to the influence of the sliding resistance between the master piston and the cylinder, the second The piston is set so as not to move in the direction of the first piston.
- the regulator in the first or second aspect, has a bottomed cylindrical shape in which one side is opened, the second pilot chamber, the second piston, the first pilot chamber, and A first case (58) in which the first pistons are stacked in the same order from the inner bottom surface, and fixed to the opening side of the first case, and the servo pressure between the first case and the first piston. And a second case (59) in which the valve mechanism is formed, and the first and second cases are integrally assembled in the housing.
- an end surface of the second piston exposed to the first pilot chamber to which the pilot pressure is supplied is exposed to the second piston exposed to the second pilot chamber to which the master pressure is supplied. It is formed with a larger pressure receiving area than the end face.
- the second piston, the first piston, etc. constituting the regulator are assembled and integrated with the first and second cases, and the integrated product is inserted into the housing to be regulated. Configure. As a result, the regulator can be easily assembled, which contributes to cost reduction.
- FIG. 3 is a schematic diagram illustrating urging forces Fm and Fp urged by a second piston in FIG. 2.
- 6 is a (time-hydraulic pressure) graph showing the behavior of pilot pressure Pp and master pressure Pm when the brake pedal is depressed and when the depression is released.
- 6 is a (time-biasing force) graph showing the behavior of urging forces Fm and Fp urged by the second piston according to the present invention when the brake pedal is depressed and when the depression is released.
- a hybrid vehicle (hereinafter simply abbreviated as a vehicle) on which the friction brake device BK (vehicle braking device) of the present embodiment is mounted is, for example, left and right front wheels Wfl which are driving wheels by an engine and a motor generator (both not shown). , Wfr.
- the motor generator described above constitutes a regenerative brake device.
- the regenerative braking device generates a regenerative braking force based on a “target regenerative braking force” described later on the left and right front wheels Wfl and Wfr by a motor generator.
- the motor and the generator may be configured separately.
- each wheel Wfl, Wfr, Wrl, Wrr there is a brake disk that rotates integrally with each wheel Wfl, Wfr, Wrl, Wrr, and a friction that generates a target friction braking force by pressing the brake pad against the brake disk.
- a brake (both not shown) is provided.
- the friction brake is provided with wheel cylinders WCfl, WCfr, WCrl, WCrr that press the brake pad against the brake disc by a master pressure Pm generated by a master cylinder 10 (see FIG. 1) described later.
- the target friction braking force that is a target is determined from the target braking force that is determined based on the depression amount of the brake pedal 4 (see FIG. 1) that the driver has depressed by the brake ECU 2 that will be described later. It is calculated by reducing the regenerative braking force.
- the friction brake device BK vehicle brake device
- the friction brake device BK vehicle brake device
- the friction brake device BK vehicle brake device
- the friction brake device BK vehicle brake device
- the brake ECU 2 and various sensors 15 and 73 to 75 that can communicate with the brake ECU 2 are provided.
- the accumulator 30, the pilot pressure generator 40, the regulator 50 and the like constitute a servo pressure generator for generating the servo pressure Ps.
- the master cylinder 10 includes a cylinder 10a having a substantially cylindrical shape with a bottom opened to the right in FIG. 1, an input piston 12 and a first master piston 11a housed in the cylinder 10a. , Second master piston 11b, reaction force pressure chamber 10p, servo pressure chamber 10e, first master chamber 10f, spring 13a, spring 13b, and second master chamber 10g.
- the master cylinder 10 will be described with the left side in FIG. 1 of the master cylinder 10 being the front and the right side being the rear.
- the input piston 12 is a piston that reciprocates in the cylinder 10a in the axial direction by an operation amount corresponding to the operation of the brake pedal 4 to increase or decrease the volume of the reaction force pressure chamber 10p.
- the reaction force pressure chamber 10p is defined by an inner peripheral surface (cylinder hole 10b) of the cylinder 10a, a partition wall 10c in the cylinder 10a, and a flange 12b of the input piston 12.
- a seal member 63 which is a rubber O-ring, is disposed to provide a liquid-tight seal between the cylinder hole 10b and the flange 12b of the input piston 12. Yes.
- the servo pressure receiving portion 11a1 of the first master piston 11a receives the servo pressure Ps, and the first master piston 11a and the front end surface of the front end portion 12a of the input piston 12 are spaced apart from each other while the first master piston 11a is spaced apart. 11a starts moving toward the front.
- the servo pressure Ps is not supplied to the servo pressure chamber 10e, the volume of the servo pressure chamber 10e is reduced, and the front end surface of the front end portion 12a of the input piston 12 contacts the rear end surface of the first master piston 11a. Thereafter, the first master piston 11a is pushed forward.
- the second master chamber 10g is defined by the pressurizing piston portion 11b1 of the second master piston 11b1, the bottom wall 10d of the cylinder 10a and the cylinder hole 10b (inner peripheral surface of the cylinder 10a), and the second master piston 11b moves forward. By doing so, the brake fluid is pressurized and the master pressure Pm is generated.
- the spring 13a is contracted between the first master piston 11a and the second master piston 11b in the first master chamber 10f, and the first master chamber 10f expands the first master piston 11a and the second master piston 11b, respectively. Energize in the direction that is.
- the spring 13b is contracted between the second master piston 11b and the bottom wall 10d in the second master chamber 10g, and biases the second master piston 11b in the direction in which the second master chamber 10g is expanded.
- the cylinder 10a of the master cylinder 10 is formed with ports 10h to 10j, ports 10m, 10n, 10q and a port 10r which communicate the inside and the outside.
- the port 10h communicates the first master chamber 10f and the atmospheric pressure reservoir 14 via a pipe 91
- the port 10i communicates the second master chamber 10g and the reservoir 14 via a pipe 92.
- the port 10h and the port 10i are the front ends of the first master piston 11a and the second master piston 11b located at predetermined positions, specifically, the first master piston 11a and the second master piston 11b, and the cylinder hole 10b.
- the predetermined positions of the first master piston 11a and the second master piston 11b referred to here mean that the hydraulic pressure is not supplied to the servo pressure chamber 10e in the second master piston 11b (for example, the brake pedal 4 is This means a position where the spring 13a and the spring 13b are urged in the opposite direction to be balanced and stopped when not depressed.
- the back end surface of the 1st master piston 11a is contact
- the port 10h and the port 10i are arranged in front of the front end with respect to the predetermined positions of the first master piston 11a and the second master piston 11b, the first master piston 11a and the second master piston When 11b starts moving forward, immediately after the start, the port 10h and the port 10i are closed by the seal members 66 and 68, and the first master chamber 10f and the second master chamber 10g are blocked from the reservoir 14.
- the port 10j communicates the servo pressure chamber 10e and the servo pressure generation chamber 57 of the regulator 50 via a pipe 93.
- the port 10m allows the first master chamber 10f and the wheel cylinders WCrr, WCrl to communicate with each other via the pipe 61 and the ABS 60.
- the port 10n is in communication with the second master chamber 10g and the wheel cylinders WCfr, WCfl via the pipe 62 and the ABS 60.
- the ports 10q and 10r are formed behind the partition wall 10c and penetrate the cylinder hole 10b.
- the port 10q communicates with the reaction force generator 20 via a pipe 94.
- the port 10r is disposed so as to open immediately in front of the front end of the flange portion 12b of the input piston 12 when the brake pedal 4 is not depressed, and the reaction force pressure chamber 10p and the reservoir 14 are connected via the pipe 95. Communicate. Specifically, the port 10r is opened at the outer periphery of the flange portion 12b in the immediate vicinity of the front end of the seal member 63 that fluid-tightly seals between the flange portion 12b and the cylinder hole 10b (inner peripheral surface of the cylinder 10a). Arranged to do.
- the stroke sensor 15 is a sensor that is disposed in the vicinity of the brake pedal 4 and detects an operation amount (depression amount) of the brake pedal 4, and transmits a detection result to the brake ECU 2. Since the brake pedal 4 is connected to the rear end of the input piston 12, as a result, the movement amount (operation amount) of the input piston 12 in the axial direction is detected.
- the reaction force generator 20 includes a stroke simulator 21.
- the stroke simulator 21 is a device that generates a reaction force pressure in the reaction force pressure chamber 10p in accordance with the operation of the brake pedal 4 and reproduces the normal operation feeling (stepping force feeling) of the brake device.
- the stroke simulator 21 is configured such that a piston 212 is slidably fitted into a cylinder 211 and a pilot liquid chamber 214 is formed on the front side of the piston 212 urged forward by a compression spring 213. .
- the stroke simulator 21 is connected to the reaction force pressure chamber 10p via a pipe 94 and a port 10q.
- the input piston 12 moves forward, the port 10r is closed, and the reaction force pressure chamber 10p and the reservoir 14 are shut off. Thereafter, the brake fluid flows into the stroke simulator 21 from the reaction force pressure chamber 10p according to the movement of the input piston 12, and the stroke simulator 21 generates a reaction force pressure corresponding to the stroke amount in the reaction force pressure chamber 10p. That is, the stroke simulator 21 applies a reaction force pressure corresponding to the operation amount (the operation amount of the brake pedal 4) that is the stroke amount of the input piston 12 to the brake pedal 4 connected to the input piston 12.
- the pressure sensor 73 is a sensor that mainly detects the fluid pressure (reaction force pressure) in the reaction force pressure chamber 10 p and is connected to the pipe 94. A signal from the pressure sensor 73 is transmitted to the brake ECU 2.
- the servo pressure generator is mainly composed of a pressure accumulator 30, a pilot pressure generator 40, and a regulator 50.
- the pressure accumulator 30 is a device that provides high-pressure brake fluid to the regulator 50 based on instructions from the brake ECU 2.
- the pressure accumulator 30 mainly includes an accumulator 31, a hydraulic pump 32, a motor 33, and a reservoir 34 in an atmospheric pressure state.
- the accumulator 31 accumulates the hydraulic pressure generated by the hydraulic pump 32.
- the accumulator 31 is connected to the regulator 50, the pressure sensor 75, and the hydraulic pump 32 by a pipe 31a.
- the hydraulic pump 32 is connected to the motor 33 and the reservoir 34, and supplies the brake fluid stored in the reservoir 34 to the accumulator 31 when the motor 33 is driven.
- the pressure sensor 75 detects the hydraulic pressure of the accumulator 31.
- the motor 33 When the pressure sensor 75 detects that the accumulator pressure has dropped below a predetermined value, the motor 33 is driven based on the control signal from the brake ECU 2, and the hydraulic pump 32 supplies brake fluid to the accumulator 31. Pressure energy is supplied to the accumulator 31.
- the pilot pressure generator 40 controls the regulator 50 so that the regulator 50 can generate the servo pressure Ps.
- the pilot pressure generator 40 generates a pilot pressure Pp with a predetermined pressure (in this embodiment, the servo pressure Ps is the same as the servo pressure Ps). Device).
- the pilot pressure generator 40 includes a pressure reducing valve 41 and a pressure increasing valve 42.
- the pressure reducing valve 41 is a normally open type electromagnetic valve, one of which is connected to the atmospheric pressure reservoir 43 via a pipe 411 and the other is connected to a pipe 413.
- the pressure reducing valve 41 controls the fluid pressure in the downstream flow path by linearly controlling the opening area of the flow path by the brake ECU 2.
- the pressure increasing valve 42 is a normally closed solenoid valve.
- One of the pressure increasing valves 42 is connected to the pressure accumulating device 30 by being connected to the pipe 422, the other side of the pressure increasing valve 42 is connected to the pipe 421, and the pipe 421 is the pipe 413. It is connected to the.
- the hydraulic pressure in the downstream flow path is controlled by linearly controlling the opening area of the flow path by the brake ECU 2.
- the regulator 50 adjusts the hydraulic pressure in the servo pressure chamber 10e of the master cylinder 10 mainly by supplying and discharging the pilot pressure Pp to and from the first pilot chamber 53.
- the regulator 50 mainly includes a housing 55, a first piston 51, a second piston 52, a first pilot chamber 53, a second pilot chamber 54, a valve mechanism 56, and a servo pressure generating chamber. 57.
- the second pilot chamber 54, the second piston 52, the first pilot chamber 53, and the first piston 51 are in a first case 58 that is a substantially bottomed cylindrical member having a bottom surface on the front side.
- the valve mechanism 56 is configured in a second case 59 that also serves as the valve housing 56a of the valve mechanism 56, and is fixed to the opening side of the first case 58.
- the first case 58 corresponds to the housing according to the present invention together with the housing 55.
- the sub-assembly 80 is formed by the first case 58 and the second case 59 fixed integrally. At this time, the servo pressure generation chamber 57 is formed by a space surrounded by the first case 58 and the second case 59. Then, the subassembly 80 is inserted into the housing 55, and the opening of the housing 55 is screwed and sealed by a lid member 55b described later to constitute the regulator 50.
- the left side of the regulator 50 in FIGS. 1 and 2 is defined as the front and the right side is defined as the rear.
- the housing 55 has a substantially bottomed cylindrical housing body 55a having a bottom surface on the rear side, and a front opening of the housing body 55a is screwed and closed, and the rear end surface abuts on the front end surface of the subassembly 80.
- the above-described lid member 55b that presses the assembly 80 to the bottom surface side of the housing body 55a is provided.
- the lid member 55b is a screw having an inner hexagonal hole in the present embodiment.
- the housing body 55a is formed with a plurality of ports 55c to 55h for communicating the inside and the outside.
- the port 55c is connected to the pipe 31a.
- the port 55d is connected to the pipe 93.
- the port 55 e is connected to a pipe 431 that communicates with the reservoir 43.
- the port 55f is connected to the pipe 413.
- the port 55g is connected to a pipe 432 connected to the pipe 431.
- the port 55h is connected to a pipe 611 branched from the pipe 61.
- a small diameter portion 55i that accommodates the valve mechanism 56 portion of the subassembly 80, a middle diameter portion 55j that accommodates the first case 58 portion of the subassembly 80, and a lid member 55b are screwed from the bottom surface side. It is formed by a large diameter screw portion 55k.
- a communication channel 55c1 having a predetermined width in the axial direction of the housing body 55a is formed on the entire circumference of the position where the port 55c opens on the inner circumferential surface of the small diameter portion 55i.
- communication channels 55d1, 55e1, 55f1, 55g1 having a predetermined width in the axial direction of the housing body 55a are provided on the entire periphery of the inner peripheral surface of the intermediate diameter portion 55j where the ports 55d to 55h are opened. 55h1 is engraved respectively.
- a first case 58 is disposed in the middle diameter portion 55j of the housing body 55a, with the opening side of the first case 58 at the top.
- the first piston 51 partitions the first case 58 into the first pilot chamber 53 and the servo pressure generating chamber 57 (see FIGS. 1 and 2) communicated with the servo pressure chamber 10e.
- the second piston 52 is fitted in the first case 58 so as to be able to contact and separate with respect to the first piston 51, and the first pilot 58 is communicated with the first pilot chamber 53 and the first master chamber 10f in the first case 58.
- the chamber 54 is partitioned.
- the first case 58 is formed with a plurality of ports 58d to 58h for communicating the inside and the outside.
- the port 58d communicates with the communication flow path 55d1 formed on the inner peripheral surface of the housing body 55a and the servo pressure generating chamber 57 in a state where the first case 58 is disposed in the housing body 55a.
- the port 58e communicates the communication channel 55e1 formed on the inner peripheral surface of the housing body 55a with the communication channel 51a1 (atmospheric pressure chamber).
- the port 58f communicates the communication channel 55f1 formed on the inner peripheral surface of the housing body 55a with the first pilot chamber 53.
- the port 58g communicates the communication flow path 55g1 formed on the inner peripheral surface of the housing body 55a with the intermediate atmospheric pressure chamber 52c shown in FIG. Further, the port 58h communicates the communication channel 55h1 formed on the inner peripheral surface of the housing body 55a with the second pilot chamber 54.
- two ports 58d to 58h are provided at positions 180 degrees apart from each other on the outer periphery of the first case 58.
- the present invention is not limited to this. May be provided, or three or more may be provided.
- the second pilot chamber 54 is defined by the bottom surface of the first case 58, the inner peripheral surface of the first case 58, and the second piston 52.
- the second pilot chamber 54 is connected to the pipe 611 through the port 58h, the communication channel 55h1, and the port 55h, and communicates with the first master chamber 10f of the master cylinder 10.
- the small diameter cylindrical portion 52a and the large diameter cylindrical portion 52b are provided with seal members 81 and 82, respectively, and the space between the inner peripheral surface of the first case 58 is liquid-tightly sealed.
- the master pressure Pm and the pilot pressure Pp are controlled to be the same pressure.
- the pressure receiving area A of the small diameter cylindrical portion 52a and the pressure receiving area B of the large diameter cylindrical portion 52b that is, the biasing force Fm ⁇ the biasing force Fp
- the outer diameters of the small-diameter cylindrical portion 52a and the large-diameter cylindrical portion 52b are appropriately set.
- the intermediate atmospheric pressure chamber 52c described above is provided between the second piston 52 and the inner peripheral surface of the first case 58 by being shifted to the opening side of the first case 58. That is, the intermediate atmospheric pressure chamber 52 c is provided between the seal member 81 and the seal member 82.
- the intermediate atmospheric pressure chamber 52c communicates with the port 58g of the first case 58, and the port 58g communicates with the reservoir 43 via the communication channel 55g1 and the port 55g.
- the first piston 51 is fitted on the inner peripheral surface of the first case 58 in a liquid-tight manner and coaxially with the second piston 52 so as to be slidable in the axial direction.
- the first piston 51 mainly includes a body 51a and a control piston 51b that is press-fitted into the body 51a.
- the body 51a is formed in a bottomed cup shape.
- the cylindrical outer diameter of the first piston 51 is formed to be the same diameter as the outer diameter of the large-diameter column portion 52 b of the second piston 52.
- the front end surface 51a3 of the body 51a is disposed to face the rear end surface 52b1 of the second piston 52, and the first pilot is formed by the front end surface 51a3, the rear end surface 52b1 and the inner peripheral surface of the first case 58.
- a chamber 53 is defined.
- Seal members 83 and 84 are disposed on the outer peripheral surface of the body portion 51a on the first pilot chamber 53 side and on the opening side of the first case 58, respectively. Is sealed.
- the communication channel 51 a 1 described above is provided between the seal members 83 and 84 and communicates with a port 58 e formed in the first case 58.
- the control piston 51b has a substantially cylindrical main body 51b1 and a substantially cylindrical protrusion 51b2 that protrudes from the center of the cylinder axis of the main body 51b1 and has a smaller diameter than the main body 51b1.
- the outer peripheral surface of the main body 51b1 of the control piston 51b is fitted into the inner peripheral surface of the body 51a via a seal member 85, thereby being movable in the axial direction integrally with the body 51a.
- a passage 51b3 formed from the tip of the protrusion 51b2 is provided so as not to penetrate the main body 51b1.
- a passage 51b4 extending in the circumferential direction (vertical direction in the drawing) that is orthogonal to the passage 51b3 and opens on the outer peripheral surface of the main body 51b1 is provided in the main body 51b1.
- a communication channel 51b5 is engraved on the outer peripheral surface of the main body 51b1 over the entire outer periphery so as to communicate with the passage 51b4.
- path 51a2 which connects the communication flow path 51b5 and the communication flow path 51a1 carved in the outer peripheral surface of the body part 51a is provided so that it may extend in the circumferential direction (drawing up-down direction).
- the valve mechanism 56 opens and closes the valve body 56b according to the movement of the first piston 51, and controls communication and non-communication of the servo pressure generating chamber 57 to the pressure accumulator 30. At this time, when not communicating, the servo pressure generating chamber 57 communicates with the reservoir 43 and is in an atmospheric pressure state.
- the valve mechanism 56 includes a valve housing 56a that also serves as the second case 59, a valve body 56b, a valve seat portion 56c, and a coil spring 56d.
- the valve housing 56a protrudes coaxially in a direction in which the first cylindrical portion 56a1 (large diameter side) and the second cylindrical portion 56a2 (small diameter side) having different diameters face each other, and the first cylindrical portion 56a1 and the second cylindrical portion Between 56a2, the collar part 56a3 standingly provided with respect to a cylinder outer periphery is provided.
- the bottomed first cylindrical portion 56a1 protrudes toward the bottom surface side of the housing body 55a, and the second cylindrical portion 56a2 having an opening protrudes toward the bottom surface side of the first case 58.
- a cylindrical hole 56a4 provided in the first cylindrical portion 56a1 and the second cylindrical portion 56a2 is drilled from the second cylindrical portion 56a2 side to the bottom surface of the first cylindrical portion 56a1.
- a sliding hole 56a5 passes through the center of the bottom surface of the first cylindrical portion 56a1.
- a port 56a6 passes through the cylindrical hole 56a4 from the outer peripheral surface of the first cylindrical portion 56a1. At this time, the opening on the outer peripheral surface side of the port 56a6 communicates with a communication channel 55c1 formed on the inner peripheral surface of the medium diameter portion 55j in the housing body 55a. As a result, the port 55c communicates with the cylindrical hole 56a4.
- the valve body 56b is disposed on the first cylindrical portion 56a1 side in the cylindrical hole 56a4, and the ball valve 56b2 is formed so that the extended line of the axis intersects the center point of the spherical ball valve 56b2 and the ball valve 56b2 formed at the tip thereof.
- the valve shaft 56b1 is inserted into and supported by a sliding hole 56a5 provided through the bottom surface of the first cylindrical portion 56a1, and is slidable in the longitudinal direction of the valve housing 56a.
- the valve seat portion 56c includes a valve seat member 56c1 and a valve seat 56c2 formed on the valve seat member 56c1.
- the valve seat member 56c1 has a substantially cylindrical shape, and the outer peripheral surface of the cylinder is press-fitted into the cylindrical hole 56a4 of the valve housing 56a.
- the front end surface (the right side in FIG. 2) of the valve seat 56c2 side of the press-fitted valve seat member 56c1 enters and is fixed to substantially the center of the cylindrical hole 56a4.
- the valve seat 56c2 is formed on the rear side of the valve seat member 56c1.
- the portion where the valve seat 56c2 is formed has a through hole 56c3 that is smaller in diameter than the other inner diameter portion of the valve seat member 56c1.
- the valve seat 56c2 is formed on a truncated cone-shaped tapered surface provided between the through hole 56c3 and the rear end surface of the valve seat member 56c1, or at the intersection of the through hole 56c3 and the tapered surface.
- the coil spring 56d urges the ball valve 56b2 toward the valve seat 56c2, and is contracted between the valve body 56b and the bottom surface of the valve housing 56a in the second space 46.
- the valve body 56b has a step portion on the valve shaft 56b1, and one end surface of the coil spring 56d is seated on the step portion (see FIG. 2).
- the ball valve 56b2 is pressed against the valve seat 56c2 by the bias of the coil spring 56d, and the first space 45 and the second space 46 are liquid-tightly blocked.
- the valve mechanism 56 (subassembly 80) is disposed in the housing 55
- the rear side end face of the flange portion 56a3 of the valve housing 56a has a small diameter portion 55i and a medium diameter in the housing 55.
- the sub assembly 80 is positioned in the axial direction by contacting the stepped portion connecting the portion 55j.
- a predetermined gap is provided between the rear end surface of the valve housing 56 a and the bottom surface of the small diameter portion 55 i of the housing 55. This clearance allows the valve shaft 56b1 to move beyond the rear end face of the valve housing 56a, and ensures the stroke amount of the valve shaft 56b1.
- the outer peripheral surface of the flange portion 56a3 of the valve housing 56a (second case 59) is press-fitted to an inner peripheral surface for press-fitting provided at the opening end portion of the first case 58. Accordingly, the inner peripheral surface of the first case 58, the outer peripheral surface, the inner peripheral surface and the bottom surface of the body portion 51a of the first piston 51, the outer peripheral surface of the second cylindrical portion 56a2 of the valve housing 56a, and the front end surface of the flange portion 56a3.
- a servo pressure generating chamber 57 is formed by the enclosed space. Thus, the servo pressure generation chamber 57 communicates with the first space 45.
- a spring 47 is contracted on the bottom surface side of the body portion 51a via a spacer, and the first piston 51 is connected to the second piston 52. Energized to the side.
- the ports 61m of the first master chamber 10f and the second master chamber 10g that generate the master pressure Pm and the port 10n of the second master chamber 10g are connected to pipes 61 and 62 and a normally open on-off valve 62a, respectively.
- a well-known ABS (Anti-lock Break System) 60 is connected through 61a.
- the ABS 60 includes a holding valve 60a, a pressure reducing valve 60b, a reservoir 60c, a pump 60d, and a motor 60e.
- the holding valve 60a is a normally-open electromagnetic valve, and opening / closing of the holding valve 60a is controlled by the brake ECU 2.
- the holding valve 60a is arranged so that one is connected to the pipe 62 and the other is connected to the wheel cylinder WCfr and the pressure reducing valve 60b. That is, the holding valve 60a is an input valve of the ABS 60.
- ABS is well-known, detailed description about an operation
- the brake ECU 2 is an electronic control unit, and includes a microcomputer.
- the microcomputer includes an input / output interface, a CPU, a RAM, a ROM, a nonvolatile memory, and the like connected to each other via a bus. Yes.
- the CPU executes a program or the like corresponding to a “linear mode” or “REG mode” described later.
- the RAM temporarily stores variables necessary for program execution, and the storage unit stores the program, map data, and the like.
- the brake ECU 2 communicates with the various sensors 15, 73 to 75, and controls the electromagnetic valves 41, 42, 60a, 60b, the motor 33, and the like.
- FIG. 1 the connection of only the brake ECU 2 and the stroke sensor 15 is represented by a broken line as a representative, and the brake ECU 2 and other various sensors 73 to 75, the electromagnetic valves 41, 42, 60a, 60b, and the motor 33 are illustrated. Connection with is not shown.
- the brake ECU 2 is connected to a hybrid ECU (not shown) so as to be communicable with each other, and the “required braking force” is generated by the “target regenerative braking force” generated by the regenerative brake device and the friction brake device BK.
- the cooperative control (regenerative cooperative control) is performed so as to be equal to the sum of the “target friction braking force”.
- the brake ECU 2 stores two control modes of “linear mode” and “REG mode”.
- the “linear mode” is normal brake control, and is a mode for controlling the “servo pressure Ps” of the servo pressure chamber 10 e by controlling the pressure reducing valve 41 and the pressure increasing valve 42.
- the brake ECU 2 calculates the “request braking force” of the driver from the operation amount of the brake pedal 4 (operation amount of the input piston 12) detected by the stroke sensor 15.
- the brake ECU 2 outputs the driver's “required braking force” to the hybrid ECU, acquires the target value of the regenerative braking device, that is, the “target regenerative braking force” from the hybrid ECU, and obtains the “target braking force” from the “target braking force”.
- target friction braking force By subtracting “regenerative braking force”, “target friction braking force” is calculated.
- the brake ECU 2 controls the pressure reducing valve 41 and the pressure increasing valve 42 of the pilot pressure generating device 40 based on the calculated “target friction braking force” to generate a pilot pressure Pp of a predetermined pressure.
- the brake ECU 2 controls the pressure reducing valve 41 to close and the pressure increasing valve 42 to open based on the “target friction braking force”.
- the pressure increasing valve 42 is opened, the accumulator 31 and the first pilot chamber 53 communicate with each other. Further, the first pilot chamber 53 and the reservoir 43 are shut off by closing the pressure reducing valve 41.
- the pilot pressure Pp in the first pilot chamber 53 can be increased by the high-pressure brake fluid supplied from the accumulator 31. As the pilot pressure Pp increases, the first piston 51 (control piston 51b) is urged toward the valve mechanism 56, and the control piston 51b slides toward the bottom surface side of the housing body 55a.
- the protruding portion 51b2 pushes the ball valve 56b2 toward the bottom surface side of the housing body 55a, and separates the ball valve 56b2 from the valve seat 56c2. .
- the first space 45 and the second space 46 communicate with each other through the through hole 56c3 of the valve seat member 56c1. Since the high pressure brake fluid is supplied from the accumulator 31 to the second space 46, the fluid pressure in the first space 45 increases due to the communication.
- the brake ECU 2 controls the pressure increasing valve 42 in the valve opening direction and closes the pressure reducing valve 41 so that the pilot pressure Pa in the first pilot chamber 53 increases as the “target friction braking force” increases. Control in the direction. That is, as the “target friction braking force” increases, the pilot pressure Pa increases and the servo pressure Ps, that is, the hydraulic pressure in the servo pressure chamber 10e also increases.
- the target servo pressure Ps in the servo pressure chamber 10e is controlled to be equal to the pilot pressure Pp.
- the pressure receiving area B of the end surface 52b1 that receives the pilot pressure Pp of the first pilot chamber 53 in the second piston 52 is larger than the pressure receiving area A of the end surface 52a1 that receives pressure from the second pilot chamber 54. Since it is formed large, the second piston 52 is normally biased toward the second pilot chamber 54 side, and the second piston 52 does not move.
- the pressure reducing valve 41 When releasing the brake operation, on the contrary, the pressure reducing valve 41 is opened, the pressure increasing valve 42 is closed, and the reservoir 43 and the first pilot chamber 53 are communicated. As a result, the hydraulic pressure in the first pilot chamber 53 is linearly reduced to the atmospheric pressure as targeted, and the control piston 51b is urged backward by the spring 47 and returns to the state before the brake pedal 4 is depressed.
- FIG. 4 exemplifies the transient characteristic (broken line) of the master pressure Pm and the transient characteristic (solid line) of the pilot pressure Pp when the brake pedal 4 is specifically depressed and released (the vertical axis indicates the hydraulic pressure). P and the horizontal axis is time t).
- the second piston including the small-diameter cylindrical portion 52a having the pressure-receiving area A that receives the master pressure Pm and the large-diameter cylindrical portion 52b having the pressure-receiving area B that receives the pilot pressure Pp and has a larger diameter than the small-diameter cylindrical portion 52a.
- the urging forces Fp and Fm for urging 52 in the axial direction always satisfy Fp> Fm. For this reason, during the increase of the master pressure Pm and when the pressure increase is completed, the second piston 52 is not pushed and moved toward the first pilot chamber 53, and there is a possibility of affecting the servo pressure Ps. Absent.
- the biasing force Fm of the surface that receives the master pressure Pm is the pilot pressure Pp. Is greater than the urging force Fp of the surface receiving the pressure, moving the second piston 52 toward the first piston 51, which may affect the servo pressure Ps.
- a step is provided in the cylindrical axis direction of the second piston 52, and the pressure receiving area B of the large diameter cylindrical portion 52b receiving the pilot pressure Pp is the pressure receiving area of the small diameter cylindrical portion 52a receiving the master pressure Pm. It set so that it might become a larger diameter than A. At this time, the difference between the pressure receiving area A and the pressure receiving area B is that the urging force Fp and the urging force Fm urged when the second piston 52 receives the pilot pressure Pp and the master pressure Pm are shown in FIG. It is set so as to satisfy the characteristics (particularly the characteristics on the right release side).
- the “REG mode” is a mode in which the pressure reducing valve 41 and the pressure increasing valve 42 are in a non-energized state, or a mode in a non-energized state (maintenance maintained) due to a failure or the like.
- the pressure reducing valve 41 and the pressure increasing valve 42 are not energized (controlled), the pressure reducing valve 41 is open, and the pressure increasing valve 42 is closed.
- the non-energized state (non-control state) is maintained even after the brake pedal 4 is depressed.
- the hydraulic pressure in the first master chamber 10f and the second master chamber 10g increases as in the “linear mode”.
- the hydraulic pressure in the second pilot chamber 54 also increases due to the increase in the hydraulic pressure in the first master chamber 10f.
- the second piston 52 slides toward the bottom surface side of the housing body 55a while pushing the first piston 51 as the hydraulic pressure in the second pilot chamber 54 increases.
- the protrusion 51b2 of the control piston 51b slides toward the bottom side of the housing body 55a.
- the protrusion 51b2 contacts the ball valve 56b2, thereby blocking the inlet of the passage 51b3 penetrating through the protrusion 51b2, and blocking the communication between the first space 45 (ie, the servo pressure generating chamber 57) and the reservoir 43.
- the protruding portion 51b2 pushes the ball valve 56b2, and the ball valve 56b2 moves by being pushed toward the bottom surface side of the housing body 55a.
- the first space 45 and the second space 46 are communicated, and high-pressure brake fluid from the accumulator 31 is supplied to the servo pressure chamber 10 e via the servo pressure generation chamber 57.
- the second piston 52 has a step on the outer peripheral surface, and the small-diameter columnar portion 52a and the large-diameter columnar portion 52b are liquid-tightly sealed from the inner peripheral surface of the first case 58, respectively. Seal members 81 and 82 are provided. An intermediate atmospheric pressure chamber 52 c communicating with the reservoir 43 is provided between the seal members 81 and 82 in the axial direction.
- the brake fluid communicates with the leakage reservoir 43 from the seal member 81, so that it becomes difficult to generate the master pressure Pm having a predetermined pressure in the first master chamber 10f. Therefore, by monitoring the hydraulic pressure in the first master chamber 10f, it is only necessary to detect a decrease in the function of the seal member 81 so that it can be dealt with early.
- the pilot pressure Pp of a predetermined pressure cannot be generated in the first pilot chamber 53, and the servo pressure by the pilot pressure Pp is not generated. Ps cannot be generated.
- the master pressure Pm corresponding to the depression operation force of the brake pedal 4 described in the REG mode can be generated in the first pilot chamber 53.
- the master pressure Pm pushes the second piston 52 and the first piston 51 to generate the servo pressure Ps, and the predetermined master pressure Pm can be generated, so that the braking force can be ensured and the safety can be ensured. Sex can be secured.
- the brake fluid in the first pilot chamber 53 leaks from the seal member 82 to the reservoir 43, resulting in a pilot pressure of a predetermined pressure. Generation of Pp becomes difficult. Therefore, by monitoring the hydraulic pressure in the first pilot chamber 53, it is only necessary to detect a decrease in the function of the seal member 82 and to cope with it early. As described above, by providing the two sealing members 81 and 82 via the intermediate atmospheric pressure chamber 52c, even when the sealing function of one sealing member is deteriorated, the brake performance is greatly reduced. The reliability can be improved.
- the end surface 52b1 of the large-diameter cylindrical portion 52b of the second piston 52 exposed to the first pilot chamber 53 to which the pilot pressure Pp is supplied is defined as the master. It is formed with a larger pressure receiving area than the end face 52a1 of the small diameter cylindrical portion 52a of the second piston 52 exposed to the second pilot chamber 54 to which the pressure Pm is supplied.
- the pressure receiving area B of the end surface 52b1 of the large diameter cylindrical portion 52b exposed to the first pilot chamber 53 of the second piston 52 and the end surface 52a1 of the small diameter cylindrical portion 52a exposed to the second pilot chamber 54 are provided. Is set so that it does not move in the direction of the first piston 51 even when a phenomenon occurs in which the master pressure Pm becomes larger than the pilot pressure Pp, such as when the brake is released. Is done. This prevents the second piston 52 from moving in the direction of the first piston 51 due to the differential pressure between the master pressure Pm and the pilot pressure Pp and affecting the generation of the servo pressure Ps.
- the second piston 52 and the first piston 51 constituting the regulator 50 are assembled and integrated with the first and second cases 58 and 59, and the integrated product is contained in the housing 55. And the regulator 50 is configured. This makes it possible to easily assemble the regulator 50, contributing to cost reduction.
- the sliding resistance f between the first master piston 11a and the cylinder hole 10b is set as the reason for changing the master pressure Pm while the brake pedal 4 is being depressed and released. I gave it as an explanation.
- the brake pedal 4 is released rapidly, it is found that not only the sliding resistance f but also the master pressure Pm varies depending on the viscosity of the brake fluid as shown by the two-dot chain line in FIG. ing.
- the influence ⁇ appears in the same direction as the sliding resistance f, and when the brake pedal 4 is depressed, ⁇ (and the pressure loss ⁇ P) is negative.
- the outer diameter of the small-diameter cylindrical portion 52a (that is, the pressure receiving area A) and the outer diameter of the large-diameter cylindrical portion 52b (that is, the pressure receiving area B) may be set so as to be larger.
- the brake ECU 2 calculates “required braking force” based on only the movement amount (operation amount) of the input piston 12 and then calculates “target friction braking force”. .
- the brake ECU 2 detects not only the amount of movement of the input piston 12 but also the reaction force pressure of the reaction force generator 20 and calculates the “required braking force” by adding the reaction force pressure.
- An embodiment that calculates “power” may be used.
- the stroke sensor 15 that detects the movement amount of the input piston 12 is a sensor that is disposed in the vicinity of the brake pedal 4 and detects the stroke amount of the brake pedal 4.
- the stroke sensor 15 may be a sensor that is disposed in the vicinity of the input piston 12 and directly detects the movement amount (stroke amount, operation amount) of the input piston 12.
- the member that transmits the operating force of the driver to the input piston 12 is the brake pedal 4.
- the member that transmits the operating force is not limited to the brake pedal 4, and may be, for example, a brake lever or a brake handle.
- the technical idea of the present invention can be applied even when the vehicle braking device (friction brake device BK) of the present embodiment is applied to a motorcycle or other vehicles.
- the second pilot chamber 54, the second piston 52, the first pilot chamber 53, and the first piston 51 are accommodated in order from the bottom surface in the first case 58, and the valve mechanism 56 is a valve mechanism.
- the second case 59 also serves as the 56 valve housings 56a.
- the opening side of the first case 58 and the second case 59 are integrally fixed to form a subassembly 80, and the subassembly 80 is inserted into the housing 55 to constitute the regulator 50.
- the present invention is not limited to this configuration, and the second pilot chamber 54, the second piston 52, the first pilot chamber 53, the first piston 51, and the valve mechanism 56 are directly placed in the housing 55 in the same order without using the first case 58.
- the regulator 50 may be configured by being housed. At this time, a stepped portion corresponding to the step provided on the outer periphery of the second piston 52 provided in the first case 58 may be provided on the inner peripheral surface of the housing 55. Thereby, since the expensive 1st case 58 can be abolished, significant cost reduction can be aimed at.
- 2 ... brake ECU, 4 ... brake pedal, 10 ... master cylinder, 11a ... master piston (first master piston), 11b ... second master piston, 12 ... input piston, 15 ... Stroke sensor, 20 ... Reaction force generator, 30 ... Pressure accumulator, 31 ... Accumulator, 40 ... Pilot pressure generator, 41 ... Pressure reducing valve, 42 ... Increase Pressure valve, 50 ... Regulator, 51 ... First piston, 52 ... Second piston, 53 ... First pilot chamber, 54 ... Second pilot chamber, 55 ... Housing, 56 ..Valve mechanism, 57 ... servo pressure generation chamber, 60 ... ABS, 73, 74, 75 ... pressure sensor, BK ... friction brake device ( Dual braking system), WCfl, WCfr, WCrl, WCrr ⁇ wheel cylinder, Wfl, Wfr, Wrl, Wrr ⁇ wheel.
- BK ... friction brake device ( Dual braking system), WCfl, WCfr
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Abstract
Description
圧力センサ73は、主に反力圧室10pの液圧(反力圧)を検出するセンサであり、配管94に接続されている。圧力センサ73の信号はブレーキECU2に送信される。
そして、小径部55iの内周面においてポート55cが開口する位置の全周には、ハウジングボデー55aの軸線方向に所定の幅を有した連絡流路55c1が刻設されている。また、中径部55jの内周面においてポート55d~ポート55hが開口する位置の全周には、ハウジングボデー55aの軸線方向に所定の幅を有した連絡流路55d1,55e1,55f1,55g1および55h1がそれぞれ刻設されている。ハウジングボデー55aの中径部55jには、第1ケース58が、第1ケース58の開口側を先頭に挿入されて配設されている。
増圧弁42が開くことでアキュムレータ31と第1パイロット室53とが連通する。また、減圧弁41が閉じることで、第1パイロット室53とリザーバ43とが遮断される。アキュムレータ31から供給される高圧のブレーキ液により、第1パイロット室53のパイロット圧Ppを上昇させることができる。パイロット圧Ppが上昇することで、第1ピストン51(制御ピストン51b)が弁機構56方向に付勢され、制御ピストン51bがハウジングボデー55a底面側に向かって摺動する。これにより、制御ピストン51bの突出部51b2先端がボール弁56b2に当接し、突出部51b2の通路51b3がボール弁56b2により塞がれ、第1空間45とリザーバ43との連通が遮断される。
(数1)
増圧時 :Pm=Pp-ΔP
(数2)
減圧時 :Pm=Pp+ΔP
(数3)
増圧時 :Pm=Pp-ΔP-α
(数4)
減圧時 :Pm=Pp+ΔP+α
Claims (3)
- シリンダと、
前記シリンダ内に軸線方向摺動可能に配設されブレーキ液を加圧するためのマスタ室を前記シリンダ内周面とで区画する加圧ピストン部およびサーボ圧室を前記シリンダ内周面とで区画するサーボ圧受部を有するマスタピストンと、
前記マスタピストンの後端面と所定距離離間可能に前記シリンダ内の後方に軸線方向摺動可能に配設された入力ピストンと、
前記ブレーキ液を蓄圧する蓄圧装置と、
前記蓄圧装置の前記ブレーキ液を使用し、前記入力ピストンの操作量に応じたパイロット圧を生成するパイロット圧発生装置と、
ハウジング内に摺動可能に嵌合され前記ハウジング内を前記パイロット圧発生装置に連通された第1パイロット室と前記サーボ圧室に連通されたサーボ圧生成室とに区画する第1ピストン、前記第1ピストンの移動に応じて前記サーボ圧生成室を前記蓄圧装置またはリザーバに連通する弁機構および前記ハウジング内に前記第1ピストンに対して接離可能に嵌合され、前記ハウジング内を前記第1パイロット室と前記マスタ室に連通された第2パイロット室とに区画する第2ピストンを備えるレギュレータと、を備え、
前記第2ピストンは、前記第1パイロット室側に露出する端面が前記第2パイロット室側に露出する端面よりも受圧面積が大きく形成された車両用制動装置。 - 請求項1において、
前記第2ピストンの前記第1パイロット室側に露出する端面の受圧面積と前記第2パイロット室側に露出する端面の受圧面積との差は、前記マスタピストンが前記マスタ圧を減少させる方向に移動され、前記マスタピストンと前記シリンダとの間の摺動抵抗の影響によって前記マスタ圧が前記パイロット圧よりも大きくなった場合にも、前記第2ピストンが前記第1ピストン方向に移動しないように設定されている車両用制動装置。 - 請求項1または請求項2において、
前記レギュレータは、
一方が開口された有底円筒形状を呈し、前記第2パイロット室、前記第2ピストン、前記第1パイロット室および前記第1ピストンを同順に内部底面から積層して収容する第1ケースと、
前記第1ケースの開口側に固定され、前記第1ケースおよび前記第1ピストンとの間で前記サーボ圧生成室を区画し、前記弁機構が内部に形成される第2ケースと、を備え、
前記第1および第2ケースは、一体で前記ハウジング内に組み付けられる車両用制動装置。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/413,342 US9315184B2 (en) | 2012-07-12 | 2013-07-11 | Braking device for vehicle |
CN201380035951.6A CN104470777B (zh) | 2012-07-12 | 2013-07-11 | 车辆用制动装置 |
DE112013003489.1T DE112013003489B4 (de) | 2012-07-12 | 2013-07-11 | Bremsvorrichtung für ein Fahrzeug |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012-156149 | 2012-07-12 | ||
JP2012156149A JP5796554B2 (ja) | 2012-07-12 | 2012-07-12 | 車両用制動装置 |
Publications (1)
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US (1) | US9315184B2 (ja) |
JP (1) | JP5796554B2 (ja) |
CN (1) | CN104470777B (ja) |
DE (1) | DE112013003489B4 (ja) |
WO (1) | WO2014010701A1 (ja) |
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KR102016357B1 (ko) * | 2014-10-28 | 2019-08-30 | 주식회사 만도 | 페달 시뮬레이터 |
JP6149847B2 (ja) * | 2014-11-25 | 2017-06-21 | 株式会社アドヴィックス | 車両の制動装置 |
JP6325493B2 (ja) | 2015-07-29 | 2018-05-16 | 株式会社アドヴィックス | 車両用制動装置 |
JP2017053796A (ja) * | 2015-09-11 | 2017-03-16 | 株式会社アドヴィックス | ペダル操作検出装置 |
DE102016222578A1 (de) * | 2016-11-16 | 2018-05-17 | Continental Teves Ag & Co. Ohg | Bremsanlage und Verfahren zum Betreiben einer Bremsanlage |
JP7067099B2 (ja) * | 2018-02-09 | 2022-05-16 | 株式会社アドヴィックス | 車両の制動制御装置 |
JP6744352B2 (ja) * | 2018-03-30 | 2020-08-19 | 株式会社アドヴィックス | 車両用制動装置 |
DE102018212018A1 (de) * | 2018-07-19 | 2020-01-23 | Robert Bosch Gmbh | Verfahren zur Dichtheitsprüfung einer hydraulischen Fahrzeugbremsanlage |
KR102613627B1 (ko) * | 2018-11-22 | 2023-12-14 | 에이치엘만도 주식회사 | 전자식 브레이크 시스템 및 작동방법 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH1120663A (ja) * | 1997-06-30 | 1999-01-26 | Aisin Seiki Co Ltd | 車両用液圧ブレーキ装置 |
JPH11180290A (ja) * | 1997-12-19 | 1999-07-06 | Aisin Seiki Co Ltd | 車両の液圧ブレーキ装置 |
JP2006069301A (ja) * | 2004-08-31 | 2006-03-16 | Yamaha Motor Co Ltd | 自動二輪車用ブレーキ装置および自動二輪車 |
JP2011240873A (ja) * | 2010-05-20 | 2011-12-01 | Advics Co Ltd | ブレーキ装置 |
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JP4320968B2 (ja) * | 2000-05-02 | 2009-08-26 | トヨタ自動車株式会社 | ブレーキシステム |
JP3972859B2 (ja) * | 2003-05-14 | 2007-09-05 | 株式会社アドヴィックス | ストロークシミュレータ |
DE102006040424A1 (de) * | 2006-08-29 | 2008-03-06 | Continental Teves Ag & Co. Ohg | Bremssystem für Kraftfahrzeuge |
JP5273472B2 (ja) | 2009-04-30 | 2013-08-28 | 日立オートモティブシステムズ株式会社 | ブレーキシステム |
JP5240237B2 (ja) * | 2010-05-20 | 2013-07-17 | 株式会社アドヴィックス | ブレーキ装置 |
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2012
- 2012-07-12 JP JP2012156149A patent/JP5796554B2/ja active Active
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2013
- 2013-07-11 US US14/413,342 patent/US9315184B2/en active Active
- 2013-07-11 CN CN201380035951.6A patent/CN104470777B/zh active Active
- 2013-07-11 DE DE112013003489.1T patent/DE112013003489B4/de active Active
- 2013-07-11 WO PCT/JP2013/069039 patent/WO2014010701A1/ja active Application Filing
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH1120663A (ja) * | 1997-06-30 | 1999-01-26 | Aisin Seiki Co Ltd | 車両用液圧ブレーキ装置 |
JPH11180290A (ja) * | 1997-12-19 | 1999-07-06 | Aisin Seiki Co Ltd | 車両の液圧ブレーキ装置 |
JP2006069301A (ja) * | 2004-08-31 | 2006-03-16 | Yamaha Motor Co Ltd | 自動二輪車用ブレーキ装置および自動二輪車 |
JP2011240873A (ja) * | 2010-05-20 | 2011-12-01 | Advics Co Ltd | ブレーキ装置 |
Also Published As
Publication number | Publication date |
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DE112013003489T5 (de) | 2015-03-19 |
JP5796554B2 (ja) | 2015-10-21 |
DE112013003489B4 (de) | 2021-06-24 |
JP2014019172A (ja) | 2014-02-03 |
CN104470777B (zh) | 2016-04-20 |
CN104470777A (zh) | 2015-03-25 |
US9315184B2 (en) | 2016-04-19 |
US20150151730A1 (en) | 2015-06-04 |
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