WO2019145820A1 - Régulateur de pression hydraulique de freins - Google Patents

Régulateur de pression hydraulique de freins Download PDF

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Publication number
WO2019145820A1
WO2019145820A1 PCT/IB2019/050289 IB2019050289W WO2019145820A1 WO 2019145820 A1 WO2019145820 A1 WO 2019145820A1 IB 2019050289 W IB2019050289 W IB 2019050289W WO 2019145820 A1 WO2019145820 A1 WO 2019145820A1
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WO
WIPO (PCT)
Prior art keywords
hydraulic
brake
housing
valve
accumulator
Prior art date
Application number
PCT/IB2019/050289
Other languages
English (en)
Japanese (ja)
Inventor
仁張勉
Original Assignee
ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング filed Critical ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング
Priority to JP2019567416A priority Critical patent/JP7013488B2/ja
Publication of WO2019145820A1 publication Critical patent/WO2019145820A1/fr

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Classifications

    • 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
    • B60T8/36—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 including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
    • B60T8/368—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units combined with other mechanical components, e.g. pump units, master cylinders
    • 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
    • B60T8/48—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 connecting the brake actuator to an alternative or additional source of fluid pressure, e.g. traction control systems
    • B60T8/4809—Traction control, stability control, using both the wheel brakes and other automatic braking systems
    • B60T8/4827—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems
    • B60T8/4863—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems
    • B60T8/4872—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems pump-back systems

Definitions

  • Patent application title Brake hydraulic pressure control device
  • the present invention relates to a brake fluid pressure control device.
  • the brake fluid pressure control device has an open / close adjustable valve and a pump which operates in conjunction with the adjustable valve.
  • the brake fluid pressure control device is electronically controlled to operate automatically, and controls the braking force generated on the wheels by increasing or decreasing the fluid pressure in the brake fluid pressure circuit.
  • Such a brake fluid pressure control device is provided with an accumulator as a piston-type reservoir used for depressurizing brake fluid and temporarily storing brake fluid. Further, in an ESP (Electronic Stability Program) control device, which is one aspect of the brake fluid pressure control device, a check valve is provided along the flow path to which the brake fluid stored in the accumulation reservoir is supplied. See, for example, Patent Document 1).
  • ESP Electronic Stability Program
  • Patent Document 1 Japanese Patent Application Publication No. 2015-205686
  • the accumulator has a piston and a spring housed in the inner weir 5 of the concave weir 5 formed on the outer surface of the hydraulic unit housing , Formed by caulking a capper against the opening of the recess 5.
  • the check valve has, for example, a cage, a pulp sheet disc, a valve body and a spring, and is assembled to the housing as well as the accumulator. Therefore, at the time of manufacture of the brake fluid pressure control device, it is necessary to assemble the accumulator and the check valve.
  • the present invention has been made in view of the above problems, and an accumulator and a check valve can be integrated to reduce the number of assembling steps to the housing and to reduce the size of the hydraulic unit. Provide a possible brake hydraulic control system.
  • a brake fluid pressure control device for controlling the fluid pressure of a brake fluid pressure circuit, which is a first internal flow path constituting a part of the brake fluid pressure circuit.
  • a housing having a second internal flow passage, one end of the first internal flow passage and the second internal flow passage being opened to the outer surface, and a first internal flow passage and a second internal flow passage of the housing And an accumulator unit attached at a position open at one end, the accumulator unit having a first through hole and a second through hole, a base fixed to the housing, and a sleeve member fixed to the base And a piston which is axially reciprocably held inside the sleeve member and receives the brake fluid flowing in via the first internal flow passage on a surface on the one end side in the axial direction, and the piston on one end side Biasing force toward the head, and the second internal from the inside of the sleeve member
  • a check valve for permitting the flow of brake fluid to the passage while blocking the flow of brake fluid
  • the non-return valve has a valve body that abuts on a sheath provided at the open end of the second flow hole, and a leaf spring that is fixed to the base and biases the valve toward the sheath.
  • a brake hydraulic control system is provided.
  • the accumulator and the check valve can be integrated to reduce the number of assembling steps to the housing, and the size of the hydraulic unit can be reduced.
  • FIG. 1 is a circuit diagram showing a brake hydraulic circuit according to an embodiment of the present invention.
  • FIG. 2 is a perspective view showing a brake fluid pressure control device.
  • FIG. 3 is a cross-sectional view showing a configuration example of an accumulator unit according to the same embodiment.
  • FIG. 4 is a perspective view showing an accumulator unit according to the same embodiment.
  • FIG. 5 is a perspective view showing the accumulator unit according to the same embodiment.
  • FIG. 6 is an exploded perspective view showing an accumulator unit according to the same embodiment.
  • FIG. 7 is a perspective view showing another configuration example of a leaf spring.
  • FIG. 8 is a perspective view showing another configuration example of a plate spring.
  • FIG. 9 is a cross-sectional view showing a conventional accumulator unit.
  • FIG. 10 is an explanatory view for comparing the sizes of the housings.
  • FIG. 11 is an explanatory view showing an example in which the sizes of accumulator units are made different.
  • FIG. 12 is an explanatory view showing an installation position of an accumulator unit.
  • FIG. 13 is an explanatory view showing an installation position of an accumulator unit.
  • FIG. 14 is an explanatory view showing an installation position of an accumulator unit.
  • a configuration example of a brake hydraulic circuit 1 to which the brake hydraulic pressure control device 20 according to the present embodiment can be applied will be described with reference to FIG.
  • the hydraulic circuit 1 for brakes according to the present embodiment is applied to a brake system that amplifies the depression force of the brake pedal 10 by the driver without using a booster and transmits it to the wheel cylinder.
  • the brake system shown in Fig. 1 is a brake system for four-wheeled vehicles, and is configured to be capable of performing ⁇ 5 control.
  • the brake pedal 10 is depressed by the driver when braking the vehicle. If it is an element that can input the driver's brake request, it may be replaced by the operation element of the brake pedal 10.
  • the brake pedal 10 is connected to the piston ⁇ ⁇ d 1 1.
  • a piston ⁇ -d 11 is provided with a stroke ⁇ -k sensor 8 for detecting a stroke ⁇ -k, which is an axial displacement of the piston ⁇ d 11.
  • the reservoir tank 16 holds hydraulic fluid as fluid that generates hydraulic pressure.
  • the reservoir tank 16 is connected to the master cylinder 14 and supplies hydraulic oil into the master cylinder 14.
  • the master cylinder 14 holds the primary piston 123 and the secondary piston 12 so as to be capable of advancing and retracting.
  • the master cylinder 14 shown in FIG. 1 is a tandem-type master cylinder 14 and has two pressure chambers 133 and 13 defined by a primary piston 123 and a secondary piston 12.
  • the primary piston 123 is provided at the tip of the piston ⁇ .
  • Secondary piston 12 pressure is pressure ⁇ 2019/145820 ⁇ (: 17132019/050289 Connected to the primary piston 12 3 via the coil spring 15 3 placed in the chamber 13 3 )
  • the pressure chamber 13 is connected to the secondary piston 12
  • two coil springs 15 3 and 15 have the same spring force.
  • each of the two pressure chambers 13 3 , 13 ⁇ ⁇ changes in accordance with the amount of stroke of the piston ⁇ ⁇ d 11.
  • the two pressure chambers 13 3 and 13 3 are connected to the hydraulic circuits 28 and 30, respectively.
  • the primary piston 12 3 and the secondary piston 12 are pressed through the pistons 11 and the hydraulic fluid is moved to the hydraulic circuits 28, 30.
  • the brake hydraulic control system 20 includes two hydraulic circuits 28, 30 having the same construction. On one of the hydraulic circuit 28 operating oil is supplied from one of the pressure chambers 13 3 of the master cylinder 14. Hydraulic fluid is supplied to the other hydraulic circuit 30 from the other pressure chamber 13 of the master cylinder 14.
  • the hydraulic circuit 1 for brakes according to the present embodiment is a so-called X type in which the hydraulic pressure is controlled by combining one front wheel and one rear wheel at diagonal positions of the vehicle by respective hydraulic circuits 28 and 30. Configured in a piping system
  • Hydraulic cylinder 30 for the hydraulic brake 22 for the right rear wheel (RR) and hydraulic cylinder 30 for the hydraulic cylinder 22 The hydraulic fluid is supplied through.
  • the brake system is not limited to the X-type piping system.
  • the brake system is a brake system for four-wheeled vehicles
  • the brake system of a two-wheeled vehicle or other vehicles may be used.
  • the hydraulic circuit 30 has the same configuration as the hydraulic circuit 28.
  • the hydraulic circuit 28 will be described, and the description of the hydraulic circuit 30 will be omitted.
  • a hydraulic circuit 28 to which hydraulic fluid is supplied from a pressure chamber 13 a of the master cylinder 14 has a plurality of control valves.
  • the control valves are a normally closed, linearly controllable circuit control valve 36, a normally closed, on / off controlled suction control valve 34, and a normally open, linearly controllable pressure booster valve 5 8 a, 5 8 b and a normally closed on / off controlled pressure reducing valve 5 4 a, 5 4 b.
  • the hydraulic circuit 28 comprises a pump element 44 driven by a motor 96.
  • the hydraulic circuit 28 also includes an accumulator 71 and a damper 73.
  • the circuit control valve 36 communicates or shuts off between the master cylinder 14 and the pressure increasing valves 5 8 a and 5 8 b.
  • the suction control valve 34 communicates or shuts off between the master cylinder 14 and the suction side of the pump element 44.
  • the driving circuit system valve 3 6 and the suction control valve 3 4 electronic control unit (not shown): is ⁇ 1 J your by (ECU Electronic Control Unit).
  • the circuit control valve 36 has a bypass flow path 41 with a non-return valve 40.
  • the check valve 40 has hydraulic fluid from the master cylinder 14 side to the hydraulic brake 22a on the right front wheel and the hydraulic brake 22b on the left rear wheel via the hydraulic fluid flow path 41 Allows the movement of On the other hand, the check valve 40 operates via the hydraulic flow passage 2 1 from the hydraulic brake 2 2 a on the right front wheel and the hydraulic brake 2 2 b on the left rear wheel to the master cylinder 14 side. Makes oil movement impossible.
  • Check valve 40 for example, when circuit control valve 36 is closed due to a failure of circuit control valve 36. ⁇ ⁇ 2019/145 2020 € 1/16 20 19/050 289 Master cylinder 1 4 side hydraulic brake on the right front wheel 2 2 3 and hydraulic brake on the rear left wheel 2 2 [ 3 side of working oil Ensure movement.
  • the pressure increasing valve 5 8 3 and the pressure reducing valve 5 4 3 are provided in an internal flow passage communicating with the wheel brake cylinder 3 8 3 of the hydraulic brake 2 2 3 of the right front wheel.
  • the pressure increasing valve 5 8 3 and the pressure reducing valve 5 4 3 are used to control the hydraulic brake 2 2 3 of the right front wheel.
  • the pressure increasing valve 58 and the pressure reducing valve 54 are provided in an oil passage communicating with the hydraulic brake 22 and the wheel cylinder 38 of the left rear wheel.
  • the pressure increasing valve 58 and pressure reducing valve 54 are used to control the hydraulic brake 22 of the left rear wheel.
  • the driving of the pressure increasing valve 5 8 3 5 8 and the pressure reducing valve 5 4 3 4 5 4 are controlled by a pressure not shown (: II.
  • Increasing valve 5 8 3 has a bypass passage 6 1 3 provided with the check valve 6 0 3.
  • the check valve 6 0 3 enables the hydraulic fluid to move from the hydraulic brake 2 2 3 side of the right front wheel to the master cylinder 1 4 and the bypass passage 6 1 3 to the circuit control valve 3 6 side. Do. On the other hand, check valve 6 0 3 does not move hydraulic fluid from master cylinder 1 4 and circuit control valve 3 6 side to hydraulic brake 2 3 3 side of right front wheel via hydraulic flow path 6 1 3 to enable.
  • the check valve 6 0 for example, the driver blur - when releasing the key operation, the hydraulic vibration of the right front wheel - bypass of the key 2 2 3 side or we master cylinder 1 4 and the circuit control valve 3 6 side It has the function to move the hydraulic oil without resistance by opening the flow path 6 1 3 and quickly return the brake pedal 10 to the home position.
  • Accumulator - evening 7 1 accumulates or release pressure reducing valve 5 4 3, 5 4 hydraulic oil while changing the volume according to the pressure of the working oil supplied through the 1 3.
  • the pressure reducing valve 5 4 3 can adjust the flow rate of hydraulic fluid flowing from the hydraulic brake 2 2 3 wheel cylinder 3 8 3 to the accumulator 7 1 by repeating opening and closing intermittently. .
  • Increasing valve 5 8 spoon is an internal flow path for connecting the circuit control valve 3 6 and the pressure increasing valve 5 8 3, hydraulic blur of the left rear wheel - is provided between the key 2 2 spoon of the wheel cylinder 3 8 spoon ing.
  • Increasing valve 5 8 spoon is made possible linear control, the master cylinder 1 4, circuit control valve 3 6, the pressure increasing valve 5 8 3 and the right front wheel hydraulic blur - key 2 2 3 Hui - Resid Linda 3 8 3 Continuously adjust the flow rate of hydraulic fluid from the side to the hydraulic brake 2 2 wheel cylinder 3 8 side of the left rear wheel.
  • the pressure increase valve 58 has a bypass flow passage 61 with a check valve 60.
  • the check valve 6 0 1 3 3 moves the hydraulic fluid from the hydraulic brake 2 2 ⁇ side of the left rear wheel to the master cylinder 1 4 and circuit control valve 3 6 side via the bypass flow path 6 1 ⁇ to enable.
  • the check valve 6 0 1 3 3 moves the hydraulic fluid from the master cylinder 1 4 and the circuit control valve 3 6 side to the hydraulic brake 2 2 side of the left rear wheel via the bypass flow path 6 1 side Make it impossible.
  • the check valve 6 0 1 3 3 is operated from the hydraulic brake 2 2 1 3 side of the left rear wheel to the master cylinder 14 and the circuit control valve 3 6 side. It has the function to move the hydraulic fluid without resistance by opening the pipe flow passage 61, and quickly return the brake pedal 10 to the home position.
  • ⁇ ⁇ 20 20/145820 ⁇ (: 17132019/050289
  • the pressure reducing valve 54 is a control valve which can be switched to full opening and full closing only.
  • the pressure reducing valve 54 is provided between the left rear wheel hydraulic brake 2 2 wheel cylinder 3 8 and the accumulator 71.
  • Pressure reducing valve 5 4 is in the open state and hydraulic oil supplied to the hydraulic brake 2 2 1 3 wheel cylinder 3 8 1 3 of the left rear wheel is stored in the accumulator 7 1 via the first inner part. Depressurize by supplying.
  • the flow rate of hydraulic fluid flowing from the hydraulic brake 2 2 wheel 3 8 8 to the accumulator 7 1 can be adjusted by repeating opening and closing the pressure reducing valve 5 4 intermittently. it can.
  • the pump element 4 4 is driven by a motor 96 to discharge hydraulic fluid.
  • the drive of the motor 96 is controlled by ⁇ II not shown.
  • the number of pump elements 44 is not limited to one.
  • the discharge side of the pump element 44 is connected to an internal flow path connecting the circuit control valve 36 and the pressure increasing valve 5 8 3 5 8.
  • a damper 73 is provided on the discharge side of the pump element 44.
  • the damper 73 has a function of reducing vibration or vibration noise accompanying a change in flow rate of hydraulic fluid in the hydraulic circuit 28.
  • a variable throttle 31 and a check valve 32 are provided between an internal flow path connecting the circuit control valve 36 and the pressure increase valves 5 8 3 5 8 and the damper 7 3.
  • the variable throttle 31 regulates the flow rate of hydraulic fluid supplied via the damper 73.
  • the check valve 32 enables movement of hydraulic fluid from the damper 73 side to the internal flow path side connecting the circuit control valve 36 and the pressure increase valve 5 8 3 5 8, while going in the opposite direction Impossible to move the hydraulic oil of
  • a second internal flow path 1 3 3 connecting the accumulation side 71 and the suction side of the pump element 4 4 is provided with a check valve 6 9.
  • Check valve 6 9 is operated from the accumulation side 7 1 side to the suction side of pump element 4 4 ( ⁇ : 1732019/050 289) It is possible to move the oil while making it impossible to move the hydraulic oil in the opposite direction.
  • a first pressure sensor 24 is provided in an internal flow passage communicating with the pressure chamber 1 3 3 of the master cylinder 1 4.
  • First pressure Kasensa 2 4 detects the pressure in the pressure chamber 1 3 3 (master cylinder pressure).
  • the second pressure sensor 26 detects the wheel cylinder pressure.
  • the second pressure sensor 26 may be provided in the inner channel 5 flow passage communicating with the left rear wheel hydraulic brake 2 2 wheel cylinder 3 8
  • the other hydraulic circuit 30 to which hydraulic fluid is supplied from the pressure chamber 1 3 1 3 of the master cylinder 1 4 is the hydraulic brake 2 20 of the left front wheel and the hydraulic brake 2 2 of the right rear wheel 2 2 Control 1
  • the hydraulic circuit 30 is the hydraulic brake 2 2 3 of the right front wheel in the description of the hydraulic circuit 2 8 above, and the hydraulic cylinder 3 8 3 is a hydraulic brake 2 2 of the left front wheel.
  • FIG. 2 is a perspective view showing an example of the brake hydraulic pressure control device 20 according to the present embodiment.
  • Brake fluid pressure control device 20 is a perspective view showing an example of the brake hydraulic pressure control device 20 according to the present embodiment.
  • Mode - evening circuit control valve 36 on the back of the 96 sides 130 3 attached is suction control valve 34, the pressure increasing valve 58 3, 58 spoon, pressure reducing valve 54 3, 54 spoon, a first pressure Kasensa 24 and the second The pressure sensor 26 is mounted.
  • - Snake (3 II 140 is mounted et the back side surface 130 3 evening 96 is attached.
  • Snake (: II 140 is motor - control and circuit control valve 36 to drive the evening 96, the suction control valve 34, an electronic control board for performing increasing valve 58 3, 58 spoon and the pressure reducing valve 54 3, 54 spoon opening and closing control such a.
  • Snake II 14 0 circuit control valve during operation of Snake 5 36, the suction control valve 34, the pressure increasing valve 58 3, 58 spoon and reduced valve 54 3, 541 3 front wheels and the left and right by controlling the opening and closing of the It controls brakes on rear wheels.
  • accumulator unit 150 provided in the brake fluid pressure control device 20 will be described in detail.
  • accumulator unit 150 provided in each of hydraulic pressure circuits 3 to 28 will be described as an example.
  • Figures 3 to 6 show an example of the configuration of the accumulator unit 150, and are explanatory views of the accumulator unit 150.
  • Figure 3 is a cross-sectional view of the accumulator unit 150 fixed to the eighting 130.
  • Fig. 4 is a perspective view of the accumulator unit 150 as viewed from the base ⁇ 151 side
  • Fig. 5 is a perspective view of the accumulator unit 150 as viewed from the sleeve member 153 side. It is a ⁇ view.
  • Accumulator - motor unit 150 are installed in the recess 130 6 formed on the lower surface 130 spoon eight Ujingu 130.
  • a first internal flow passage 131 communicating with the wheel cylinder 38 3 , 38 via the pressure reducing valve 54 3 and a second internal flow passage 133 communicating with the suction side of the pump element 44 are opened in the recess 130 6. doing.
  • Recess 130 6 and a small diameter portion provided coaxially in succession to the large diameter portion and the bottom surface of the large diameter portion which opens to the lower surface 1301 3.
  • the first internal channel 131 that are open to the bottom surface of the large diameter portion of the recess 130 6.
  • Second internal passage 133 is open to the bottom surface of the small-diameter portion of the recess 130 6.
  • An annular seal member 159, a valve body 161 and a plate spring 163 are provided.
  • the accumulator - motor unit 150 is mounted in a recess 130 6 formed on the eighth Ujingu 130 assembled integrally.
  • the base portion 151 has a protrusion 151, a fitting portion 1511 and a small diameter portion 151.
  • the projecting portion 151 ⁇ , the fitting portion 1511 and the small diameter portion 151 are arranged in this order along the axial direction.
  • Engaging portion 151 1 is a portion that is joined to the periphery of the ⁇ 5130 6 together is fitted in the recess 130 6 of the housing 130.
  • the small diameter portion 151 has a diameter substantially the same as the diameter of the inner periphery of the sleeve member 153.
  • the sleeve member 153 is fitted and joined.
  • the protrusion 151 ⁇ is formed so as to protrude in the axial direction from the end face of the fitting portion 151 1 on the side of the housing 130.
  • the outer peripheral surface of the projecting portion 151 is joined in a liquid-tight manner to the inner peripheral surface of the small diameter portion of the recess 130 6 eight Ujingu 130.
  • the first internal flow path 131 and the second internal passage 133 is prevented from communicating through the recess 130 6.
  • the bottom surface and the fitting portion 151 1 of the large diameter portion of the recess 130 6 spaced fluid Giyarari 135 is formed.
  • the bottom of the small diameter portion of the recess 130 6 and the protrusion 151 are separated to form a liquid gear lary 137.
  • the bonding method of the base 151 and the housing 130 there is no particular limitation on the bonding method of the base 151 and the housing 130.
  • the base 151 and the housing 130 may be joined by mechanical bonding, caulking, friction welding, ultrasonic welding or adhesive bonding.
  • the base 151 is first flow hole 151 3, the second flow hole 151 spoon, shea - having Urabe 151_Rei and the valve housing section 151 6.
  • the first flow hole 151 3 is an axial bore which is open at both ends in the axial direction through the interference fitting portion 151 1 and the small-diameter portion 151 of the base 151.
  • the first flow hole 151 8 communicating the interior of the first internal flow path 131 and the sleeve member 153.
  • Four first flow hole 151 3 are provided at equal intervals of 90 degrees around the axis in the present embodiment.
  • Four first flow mosquito larva and 151 3 is communicated with the first inner ⁇ 5 passage 131 through the liquid Giyarari 135.
  • the valve housing section 151 6 is a concave stepped formed over the opening and the protruding portion 151 and the fitting portion 151 1 to the end face eight Ujingu 130 side.
  • the second flow hole 151 spoon Sri bottom and Moto ⁇ 51 51 of the valve housing 151 6 - is an axial bore which is open on the end face of the probe member 153 side.
  • the valve housing section 151 6 is open to the liquid Giyarari 1 37 side, the valve housing section 151 6 and the second flow hole 151 spoon second internal flow path 133 Communicate with the inside of the sleeve member 153 and the inside of the sleeve member 153.
  • Sheet - Boku ⁇ 5151_Rei has a tapered shape whose diameter increases in the valve is formed in the connecting portion accommodating ⁇ 5151 6 side of the valve housing portion 151 6 and the second flow hole 151 spoon.
  • the valve body 161 constituting the check valve 69 abuts on the seat 5151.
  • the second through hole 151 is shut off, and when the valve 161 is separated from the seat 515 1 0, the second through hole 151 is opened. .
  • valve accommodating portion 151 6 , the seal portion 1510 and the second flow passage 151 have a base portion 15.
  • second flow hole 151 spoon It is formed a second flow hole 151 spoon, four first flow hole 151 3 is formed on the periphery thereof.
  • the valve body 161 and the plate spring 163 constitute a check valve 69 is accommodated in the valve accommodating portion 151 6.
  • the leaf spring 1 63 is joined to the stepped portion of the valve housing portion 151 6 at the outer edge portion.
  • the leaf spring 163 biases the valve body 161 toward the cylinder 5151.
  • the leaf spring 163 has a gap that allows the brake fluid to flow, so that the flow of the brake fluid is not impeded by the leaf spring 163.
  • the axial length of the check valve 69 is reduced by constructing the check valve 69 using the plate spring 163.
  • the axial length of Moto ⁇ 5151 it is possible to turn small recess 130 6 depth of eight Ujingu 130. As a result, the size of the housing 130 can be reduced.
  • leaf spring 163 configured in a spiral shape
  • the form of the leaf spring is not particularly limited.
  • a leaf spring 170, 18 comprising a spring 181 and pressing portions 173, 183 for pressing the valve body 161.
  • the sleeve member 1 53 is a cylindrical member whose one end in the axial direction is formed as an open end and the other end is formed as a closed end.
  • the open end of the sleeve member 1 5 3 is fitted and joined to the small diameter portion 1 5 1 of the base 1 5 1.
  • the base portion 15 1 and the sleeve member 1 5 3 may be joined by caulking, laser welding, or adhesive bonding.
  • the piston 15 5 is axially movably disposed inside the sleeve member 1 5 3.
  • a spring 1 5 7 is accommodated in a compressed state between the piston 1 5 5 and the bottom 1 5 3 3 of the sleeve member 1 5 3.
  • the piston 1 55 is urged toward the base 1 5 1 along the axial direction.
  • the piston 1 55 receives the brake fluid flowing into the inner 5 of the sleeve 5 5 3 via the first flow hole 1 5 1 3 at the end face on the base 1 5 1 side.
  • the piston 1 5 5 moves downward in the figure. That is, the position of the piston 1 5 5 changes according to the pressure of the brake fluid flowing into the sleeve member 1 5 3 and the volume of the brake fluid held in the sleeve member 1 5 3 changes. .
  • the spring 1 5 7 is an aspect of the biasing member in the present invention, and the biasing member is not limited to the spring 1 5 7.
  • the biasing member may be constituted by a plate spring, an elastic rubber or the like.
  • annular seal member 1 5 9 is placed in an annular groove 1 5 5 3 formed on the outer peripheral surface of the piston 1 5 5.
  • the annular seal member 1 5 9 is disposed between the inner peripheral portion of the sleeve member 1 5 3 and the outer peripheral portion of the piston 1 5 5 and slides on the inner peripheral surface of the slide member 1 5 3 It has a function to prevent the leakage of brake fluid to the space where the spring 1 57 is housed while moving.
  • the diameter of the fitting portion 1 5 1 1 and the protruding portion 1 5 1 of the base 5 1 5 1 is made constant and the recess 1 3 0 1 of the 1 8 0 1 0 1
  • the capacity of the accumulator 71 can be changed by changing other design dimensions as long as it can be joined to the
  • the thickness of the base 5 1 5 1 of the accumulator unit 1 5 0 shown in FIG. 3 may be changed, or the 1st passing 1 5 1 3 or the 2nd 3 ⁇ 4 3 4 passing of the base 5 1 5 1
  • the volume of the accumulator 71 can be changed without changing the design of the housing 130 by changing the diameter of at least one of the housings.
  • the amount of change in volume of the accumulator 71 can be adjusted without changing the design of the housing 130. At that time, the elastic force of the spring 1 5 7 may be changed.
  • the design of the components of the accumulator unit 150 is changed by changing the design of the fluid pressure unit 110.
  • Accumulator units 150 of different sizes can be installed in hydraulic units 110 without change. As a result, it is possible to improve the degree of freedom in designing the size of the accumulator unit 150 while sharing the hydraulic unit 130 of the hydraulic unit 10.
  • the sleeve member 1 5 3 is the mounting surface of the housing 1 3 0 ⁇ 0 2019/145 2020 (Fixed to the base 5 1 5 1 outside the position of: 171320 19/050 289. Therefore, piston and spring in the recess 5 formed in the housing 130)
  • the size of the housing can be reduced as compared to a conventional hydraulic unit in which the inner peripheral shell 5 of the concave shell 5 is used as a cylinder to constitute an accumulator.
  • FIG. 9 is a cross-sectional view showing the structure of a conventional accumulator 250. As shown in FIG. The conventional accumulator 250 is formed at a position where the first inner flow passage 2 6 7 and the second inner flow passage 2 6 9 in the hydraulic unit 8 21 2 1 open. It is configured using the recess 2 6 3.
  • a piston 25 5 and a spring 2 5 7 are accommodated in the recess 2 6 3 of the housing 2 6 1.
  • a plug 25 1 is attached to the opening of the recess 2 6 3 by caulking.
  • the outer peripheral surface of the piston 25 is provided with a ring-shaped seal 2 5 9.
  • the spring 2 5 7 is disposed in a compressed state between the piston 2 5 5 and the plug 2 5 1 to urge the piston 2 5 5 toward the bottom of the recess 2 6 3.
  • the piston 25 5 moves by receiving the brake fluid flowing in via the first internal flow passage 2 6 7 at the bottom end face of the recess 2 6 3. As a result, the accumulator 250 holds the brake fluid.
  • the check valve needs to be assembled to the housing 2 61 separately from the accumulator 250.
  • FIG. 10 is an explanatory view in which the size of the housing 2 61 of the conventional hydraulic unit is compared with the size of the housing 130 of the hydraulic unit 1 1 0 according to the present embodiment.
  • the accumulator 250 is configured by using the recessed portion 263 formed in the flange 221.
  • the accumulator unit is opposed to 8 1
  • the length of 1 _ can be reduced by 1 ⁇ 1 ⁇ 1 1 ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ 1 0 ⁇ ⁇ ⁇ / 16/16/16/16 1/16 20 19/050 289 ⁇ 1 0
  • the check valve 69 is integrated with the accumulator unit 150, the space for assembling the check valve 69 is not necessary.
  • the check valve 6 9 incorporated in the accumulator unit 1 50 is configured using a plate spring 1 6 3, the depth of the recess 1 3 0 1 3 0 1 can be made shallow, The dimensions of the housing 130 can be reduced. As a result, it is possible to reduce the material cost and weight of the housing 130 and the size of the hydraulic unit 110.
  • FIG. 11 shows an example in which the size of the accumulator unit 150 is different in the hydraulic unit 110 according to the present embodiment.
  • the brake fluid pressure control device according to the present embodiment even if the sizes of the accumulator units 150 are different, it is not essential to change the width 130 of the fluid pressure units 110.
  • the common accumulator 130 is used although the accumulator unit 150 provided is different in size. Therefore, design freedom of the size of accumulator unit 1 50 can be improved while sharing hydraulic unit 1 10 8 housing 1 3 0
  • the brake fluid pressure control device 20 is configured such that the accumulator unit 150 is externally attached to the housing 130 of the fluid pressure unit 110. It is possible to improve the freedom of installation position.
  • FIG. 12 to 14 are schematic views showing examples of installation positions of the storage unit 150 respectively.
  • Fig. 12 shows an accumulator unit 150 installed on the lower surface 130 of the housing 130 shown in Fig. 3 and Fig. 10 etc.
  • Figure 13 is an example where the accumulator unit 15 0 on the side surface 130 3 Eight Ujingu 130 motor 96 is attached. According to the configuration example shown in FIG. 13 min the accumulator unit 150 is eliminated that protrude from the lower surface 1301 3 eight Ujingu 130 downward, blurring as compared with the configuration example shown in FIG. 12 - shown in the gas-liquid pressure control device 20 The size in the vertical direction of the can be reduced.
  • the accumulator unit 150 protrudes in the direction in which the motor 96 protrudes from the housing 130, and therefore, the increase in the illustrated size of the brake fluid pressure control device 20 is suppressed. While the size in the vertical direction can be reduced.
  • the accumulator unit 150 does not protrude downward from the lower surface 130 of the housing 130 as compared with the configuration example shown in FIG.
  • the accumulator unit 150 is accommodated in the cage of (II: 140), and the vertical direction of the hydraulic pressure control device 20 in the vertical direction is not changed. Size can be reduced.
  • the installation position of the accumulator unit 150 illustrated in FIGS. 12 to 14 is merely an example.
  • This embodiment In the brake fluid pressure control device 20 according to the present invention, there is no need to form a recess P that functions as a cylinder of the piston in the housing 130 of the fluid pressure unit 110. Degree of freedom.
  • the brake fluid pressure control device 20 is an accumulator unit 150 having a base P 15 1, a piston 15 5, a spring 1 5 7 and a sleeve member 1 5 3.
  • a check valve 69 is integrated with the accumulator unit 150. Therefore, the accumulator 7 1 and the check valve 6 9 can be assembled simultaneously to the housing 1 3 0 of the hydraulic unit 1 1 0.
  • the accumulator unit 150 can be integrally assembled in advance. Therefore, the assembling work of the accumulator 71 and the check valve 69 can be made efficient.
  • the check valve 69 provided in the accumulator unit 150 is configured using a plate spring 136. Therefore, the axial length of the check valve 69 can be reduced, and the size of the housing 130 can be reduced. Therefore, the material cost and weight of the housing 130 and the size of the hydraulic unit can be reduced.
  • the accumulator unit 150 is externally attached to the housing 130. Therefore, the size of the accumulator unit 150 can be changed without changing the design of the hydraulic unit 130 by changing the design of the accumulator unit 150 ⁇ P product. This makes it possible to improve the freedom of design of the accumulator unit 150 while sharing the hydraulic unit 130 of the hydraulic unit 110.
  • the accumulator unit relative to the housing 130 is used. It is not necessary to provide a recess P for housing the piston in the housing 130 because the 150 is externally attached. As a result, the size of the housing 130 can be reduced, and the cost, weight, and size of the hydraulic unit can be reduced.
  • the accumulator unit 150 since the accumulator unit 150 is externally attached to the housing 130, the degree of freedom of the installation position of the accumulator unit 150 can be enhanced. Therefore, depending on the installation position of the accumulator unit 150, the size of the brake fluid pressure control device 20 can be reduced.
  • the brake fluid pressure control device mounted on a four-wheeled vehicle is described as an example.
  • the present invention is not limited to this example, and the brake fluid pressure mounted on other vehicles It may be a controller. [Description of the code]
  • ECU electronice control unit
  • Accumulator unit 151 base, 151 a ⁇ ⁇ ⁇ 1 flow hole, 151 b ⁇ second flow hole, 153 ⁇ sleeve member, 155 ⁇ ⁇ ⁇ piston, 157 spring, 159 annular seal member, 161 ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ leaf spring

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  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Regulating Braking Force (AREA)
  • Check Valves (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Abstract

La présente invention concerne un régulateur de pression hydraulique de freins capable d'éliminer un processus consistant à assembler un accumulateur et un clapet anti-retour avec un boîtier, en intégrant l'accumulateur et le clapet anti-retour, et capable de réduire la taille d'une unité hydraulique. Le régulateur de pression hydraulique de freins (20) comprend une unité (71, 150) d'accumulateur qui est fixée à une position où une extrémité de chaque conduit parmi un premier conduit interne (131) et un second conduit interne (133) d'un boîtier (130) est ouverte. L'unité (71, 150) d'accumulateur comprend: une base (151) présentant un premier trou (151a) de circulation et un second trou (151b) de circulation et qui est fixée au boîtier (130); un élément (153) de douille fixé à la base (151); un piston (155) retenu dans l'élément (153) de douille de manière à aller et venir dans une direction axiale et recevant un fluide de freinage; un élément (157) de sollicitation poussant le piston (155) vers un côté d'extrémité; et un clapet anti-retour (69). Le clapet anti-retour (69) comprend: un corps (161) de clapet portant sur un siège (151c) placé à une extrémité d'ouverture du second trou (151b) de circulation; et un ressort (163; 170) à lame fixé à la base (151) et poussant le corps (161) de clapet vers le siège (151c).
PCT/IB2019/050289 2018-01-23 2019-01-15 Régulateur de pression hydraulique de freins WO2019145820A1 (fr)

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JP2018008504A JP2019127082A (ja) 2018-01-23 2018-01-23 ブレーキ液圧制御装置
JP2018-008504 2018-01-23

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114206696A (zh) * 2019-08-19 2022-03-18 罗伯特·博世有限公司 用于液压的车辆制动系统的液压机组的液压块
US11590949B2 (en) * 2019-07-26 2023-02-28 Hyundai Mobis Co., Ltd. Hydraulic unit for brake system

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100327652A1 (en) * 2009-06-25 2010-12-30 Advics Co., Ltd. Check valve and brake hydraulic pressure control device using the same
DE102012219054A1 (de) * 2012-10-18 2014-04-24 Robert Bosch Gmbh Hydrospeicher für eine hydraulische Fahrzeugbremsanlage

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100327652A1 (en) * 2009-06-25 2010-12-30 Advics Co., Ltd. Check valve and brake hydraulic pressure control device using the same
DE102012219054A1 (de) * 2012-10-18 2014-04-24 Robert Bosch Gmbh Hydrospeicher für eine hydraulische Fahrzeugbremsanlage

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11590949B2 (en) * 2019-07-26 2023-02-28 Hyundai Mobis Co., Ltd. Hydraulic unit for brake system
CN114206696A (zh) * 2019-08-19 2022-03-18 罗伯特·博世有限公司 用于液压的车辆制动系统的液压机组的液压块
CN114206696B (zh) * 2019-08-19 2024-03-22 罗伯特·博世有限公司 用于液压的车辆制动系统的液压机组的液压块

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JPWO2019145820A1 (ja) 2020-11-19
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