WO2007124636A1 - Soupape composite de freinage hydraulique pour véhicule - Google Patents

Soupape composite de freinage hydraulique pour véhicule Download PDF

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Publication number
WO2007124636A1
WO2007124636A1 PCT/CN2007/000114 CN2007000114W WO2007124636A1 WO 2007124636 A1 WO2007124636 A1 WO 2007124636A1 CN 2007000114 W CN2007000114 W CN 2007000114W WO 2007124636 A1 WO2007124636 A1 WO 2007124636A1
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WO
WIPO (PCT)
Prior art keywords
valve
pressure
nut
spring
hole
Prior art date
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Ceased
Application number
PCT/CN2007/000114
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English (en)
Chinese (zh)
Inventor
Guangming Li
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Individual
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Individual
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Publication of WO2007124636A1 publication Critical patent/WO2007124636A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • B60T13/24—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 gaseous
    • B60T13/46—Vacuum systems
    • B60T13/52—Vacuum systems indirect, i.e. vacuum booster units
    • B60T13/57—Vacuum systems indirect, i.e. vacuum booster units characterised by constructional features of control valves

Definitions

  • the present invention relates to a valve, and more particularly to a control valve for a vehicle hydraulic brake safety system. Background technique
  • ABS organic integrated
  • MABS mechanical
  • the electromechanical integration (ABS) anti-lock system consists of an electronic controller, a wheel speed sensor, an electromagnetic on-off valve, and a load-sensing proportional valve. It mainly simulates the "point brake, brake, that is, the lock-and-relaxation cycle from the outside of the brake system, so that the vehicle is maneuverable, balanced and safe during emergency braking.
  • the shortcoming of this system is : Complex structure, difficult to manufacture, install and maintain; high price; large body shake during work; can not significantly shorten the braking distance; can not adapt to changes in vehicle load.
  • the load-sensing proportional valve is one of the main parts of the (ABS) system. Installed on some mid- and low-end passenger cars, as a tail-fighting component to prevent braking, but due to structural defects, it can not adapt to changes in vehicle load, nor can it shorten the braking distance, without any anti-lock function; Basically, it cannot be repaired and used.
  • Mechanical (MABS) system has low manufacturing cost. Easy installation and maintenance, but it loses braking force and does not have anti-lock function. It can not shorten the braking distance. Role; can not adapt to load changes.
  • the technical problem to be solved by the present invention is to provide an automobile hydraulic brake composite valve, which can make the hydraulic brake system of the automobile work stably, safely and reliably, and can effectively shorten the braking distance and avoid the emergency especially when braking.
  • the brakes are braked, the vehicle tails phenomenon occurs due to the wheel lock.
  • the automobile hydraulic brake composite valve of the invention has an oil passage formed in the valve body, and the inlet of the oil passage is connected with the input end of the automobile main pump pressure oil passage .
  • the composite valve is provided with a residual pressure regulating valve, a pressure limiting valve, a high pressure switching valve, an accumulator and an exhaust bolt, wherein the inlet of the oil passage is through the exhaust bolt, the accumulator, the high pressure switch valve and the residual pressure regulating valve
  • the inlet, the pressure limiting valve is connected in series with the pressure limiting valve, the outlet of the pressure limiting valve and the high pressure switch The outlet of the valve merges to connect the wheel sub-pump.
  • the automobile hydraulic brake composite valve of the invention can control the braking force and the time difference of the braking process to ensure the smoothness of the braking.
  • the automobile hydraulic brake composite valve of the invention is installed in the brake oil passage between the automobile master pump and the front wheel pump and the rear wheel pump, and is installed in the master pump and the front wheel.
  • the cylinder between the pumps is called the front wheel brake compound valve
  • the short wheel brake compound valve is installed between the master pump and the rear wheel cylinder.
  • the structure of the front wheel brake compound valve and the rear wheel brake compound valve is exactly the same, only the internal pressure limiting valve, the high pressure switch valve, and the accumulator spring force setting value are different.
  • the opening and closing of each valve is determined by the respective spring force setting values.
  • the front wheel brake compound valve and the rear wheel brake compound valve make the brake pressure difference and time difference of the front and rear wheels controllable, so as to ensure that the rear wheel is not locked and the vehicle tails are not present. In addition, it can also increase the starting working pressure, control the critical locking pressure, increase the deceleration, and increase the braking force at low speed to ensure the braking distance is shortened.
  • the pressure oil from the main pump of the car is respectively combined with the front wheel brake compound valve and the rear wheel brake compound valve.
  • the residual pressure regulating valve and the pressure limiting valve enter the front and rear wheel sub-pumps, and also enter the accumulator and the high-pressure switch valve.
  • the pressure of the sub-pump gradually rises to the set value of the pressure limiting valve, the P pressure valve closes, the pressure oil cannot pass through the pressure limiting valve to the front and rear wheel sub-pumps, and the sub-pump maintains the pressure limiting valve. pressure. That is, the critical lock pressure, the car gets a large deceleration.
  • the function of the accumulator is to prevent the high-pressure on-off valve of the rear-wheel brake compound valve from being opened earlier than the high-pressure switch valve of the front-wheel brake compound valve when the emergency brake is applied, so that the rear wheel is locked before the front wheel, resulting in the vehicle ⁇ Tail, side slip.
  • the spring force value of the accumulator and high-pressure switch valve of the rear wheel brake compound valve is higher than that of the front wheel brake compound valve. (The pressure value varies according to different vehicles), and the front wheel brake compound can be ensured.
  • the high pressure switch valve of the valve and the rear wheel brake compound valve opens with a time difference, and the rear wheel never locks before the front wheel.
  • the master pump unloads (releases the brake pedal), the brake oil of the sub-pump passes through the pressure limiting valve, the residual pressure regulating valve, and returns to the main pump or accumulator of the car, so that the high-pressure switch valve is closed again, the pressure limiting valve And the accumulator is in its original state. Due to the damping effect of the residual pressure regulating valve, the oil pressure in the pipeline from the residual pressure regulating valve to the sub-pump Hold a certain value (can be adjusted as needed).
  • the function of the residual pressure regulating valve is as follows: First, the pipeline from the valve to the pump is filled with oil. The response time during braking (or unloading) can be accelerated, the initial working pressure is increased, and the braking distance is shortened.
  • the brakes increase the gap due to wear.
  • the gap can be adjusted without adjusting the gap mechanism, and the residual pressure is used to adjust the gap, which greatly reduces the workload of adjustment.
  • the exhaust bolts of the front wheel brake compound valve and the rear wheel brake compound valve are only used when the gas in the system needs to be removed.
  • the beneficial effects of the present invention are that the braking distance is significantly shortened, the braking process is smooth and reliable, and the side slip and the squat are effectively prevented.
  • the static friction distance of the tire during braking is shortened, which extends the life of the tire from the surface and protects the road surface.
  • the brake oil pressure is regulated and balanced by the brake system itself. It has strong adaptability to vehicle load changes.
  • the valve has low manufacturing cost, low price, convenient installation and maintenance, simple use, long service life and high cost performance.
  • FIG. 1 is a schematic view showing the connection of an oil passage of a hydraulic brake composite valve of an automobile according to an embodiment of the present invention
  • FIG. 2 is a schematic structural view of a hydraulic brake composite valve of an automobile according to an embodiment of the present invention
  • Figure 3 is a side view of the automobile hydraulic brake composite valve in the embodiment of the present invention.
  • T--automobile master cylinder B--accumulator; C-- high pressure switch valve; D-balance pressure regulating valve; E--pressure limiting valve; P- Wheel sub-pump; 1- - bonnet; 2 - free piston; 3 sealing ring; 4 - spring; 5-- adjusting nut; 6 - nut; 7 - sealing ring; 8 adjusting screw; 9- combination washer; 11—Pressure valve seat; 12-pressure valve sleeve; 13-ring seal ring; 14—end face seal ring; 15-valve core; 16—seal ring; 17 spring; 18—adjustment screw; 19--nut; 20- gland; 21--end face seal; 22—seal ring; 23-spool; 24—seal ring; 25—spring; 26— adjusting screw; 27—nut; 28—seat; 30-screw; 31-joint plate; 32-screw; 33-inlet; 34-outlet.
  • the automobile hydraulic brake composite valve in this embodiment has an oil passage formed in the valve body, and an inlet 33 of the oil passage is connected to an input end of the automobile prime pump T pressure oil passage.
  • the composite valve is provided with a residual pressure regulating valve 0, a pressure limiting valve E, a high pressure switching valve C, an accumulator B and an exhaust bolt 29, wherein the inlet 33 of the oil passage is directly connected to the inlet of the exhaust bolt 29, the accumulator B, the high pressure switch valve C and the residual pressure regulating valve D, and the residual pressure regulating valve D is connected in series with the pressure limiting valve E, the pressure limiting valve
  • the outlet of E is connected to the outlet of the high pressure switching valve C to connect the wheel cylinder P.
  • the opening and closing of each valve is determined by the respective spring force setting values.
  • the automobile hydraulic brake composite valve of the embodiment makes the braking force and the time difference of the braking process controllable to ensure the smoothness of the braking.
  • FIG. 2 shows a specific structure of each valve in the hydraulic brake composite of the embodiment of the present invention: the residual pressure regulating valve D is composed of a nut 6, a sealing ring 7, an adjusting screw 8, a combination washer 9, a spring 10, The residual pressure valve seat 11 and the residual pressure valve sleeve 12 are formed, wherein the residual pressure valve sleeve 12 is sleeved on the residual pressure valve seat 11, one end of the spring 10 is placed in the residual pressure valve seat 11, and the other end is inserted into the adjusting screw 8; the nut 6 is screwed to the adjusting rod 8, and the compression ratio of the spring 10 can be adjusted at the other end of the adjusting rod 8; the sealing ring 7 is disposed at the connecting end of the nut 6 and the adjusting rod 8 to prevent the brake fluid at the joint
  • the combination gasket 9 is installed between the valve body and the nut 6, and seals the nut 6 and the hole of the valve cover 1 to prevent the brake fluid from leaking out.
  • the accumulator B is composed of a free piston 2, a sealing jaw 3, a 'spring 4, and an adjusting nut 5.
  • the sealing jaw 3 is placed in the groove of the free piston 2, and the free piston 2 is mounted in the hole of the valve body for axial movement in the hole.
  • the spring 4 is mounted in a corresponding hole of the free piston 2 and the adjusting nut 5, and the adjusting nut 5 is screwed to the valve body, and the spring force for balancing the hydraulic pressure is set by the adjusting nut 5.
  • the high pressure switch C is composed of an end seal ⁇ 14, a spool 15, a seal 16, a spring 17, an adjustment screw 18 and a nut 19.
  • the end face sealing jaw 14 is fastened in the groove of the valve core 15, and the sealing ring 16 is fitted in the groove of the valve core 15, and the valve core 15 is installed in the hole of the valve body for axial movement.
  • the spring 17 is mounted in the hole of the valve body 15, the nut 19 is screwed into the screw hole of the valve body, the adjusting screw 18 is installed in the screw hole of the nut 19, and the axial position of the adjusting screw 18 is adjusted to adjust the high voltage.
  • the opening pressure of the switching valve is composed of an end seal ⁇ 14, a spool 15, a seal 16, a spring 17, an adjustment screw 18 and a nut 19.
  • the pressure limiting valve E is composed of a gland 20, an end face sealing ring 21, a valve core 23, a sealing ring 24, a spring 25, an adjusting screw 26, and a nut 27, wherein the end face sealing ring 21 is fastened in the groove of the gland 20.
  • the sealing ring 24 is installed in the groove of the valve core 23, and the valve core 23 is installed in the valve body hole, and can be axially inserted in the hole Exercise.
  • the nut 27 is screwed into the screw hole of the valve body, and the spring 25 is mounted in the hole of the valve body 23.
  • the adjusting screw 26 is installed in the screw hole of the nut 27, and the axial limit position of the adjusting screw 26 can be adjusted to adjust the pressure limiting pressure of the pressure limiting valve.
  • the valve body is composed of a detachably connected valve cover 1 and a valve seat 28, and the residual pressure regulating valve D, the accumulator B and the exhaust bolt 29 are disposed on the valve cover.
  • the high pressure switching valve C and the pressure limiting valve E are disposed in the valve seat 28.
  • the exhaust bolt 29 is screwed into the screw hole of the valve cover 1, and the seal rings 13, 22 are installed in the end face groove of the valve cover 1, and the function is to seal the joint surface of the valve cover 1 and the valve seat 28.
  • the bonnet 1 and the valve port 28 are coupled by a screw 30.
  • the coupling plate 31 is coupled to the composite valve body by screws 32.
  • the automobile hydraulic brake composite valve of the embodiment is installed in the brake oil passage between the automobile master pump T and the front wheel split pump and the rear wheel split pump P.
  • the front wheel brake compound valve is simply referred to as a front wheel brake compound valve installed between the master cylinder T and the front wheel cylinder pump P, and is simply referred to as a rear wheel brake compound valve between the master cylinder T and the rear wheel cylinder pump P.
  • the structure of the front wheel brake compound valve and the rear wheel brake compound valve is completely the same, only the internal pressure limiting valve E, the high pressure switch valve C, and the accumulator B spring force setting values are different.
  • the front wheel brake compound valve and the rear wheel brake compound valve make the brake pressure difference and the time difference of the front and rear wheels controllable, so as to ensure that there is no phenomenon that the rear wheel first locks and the vehicle tails.
  • the initial working pressure can be increased, the critical locking pressure can be controlled, the deceleration can be increased, and the braking force at low speed can be increased to ensure that the braking distance is shortened.
  • the "Import 33" in Figure 2 is connected to the car master cylinder T, and the "outlet 34" is connected to the sub-pump P of the car.
  • the pressure oil from the automobile master cylinder T enters the front wheel brake compound valve and the rear wheel brake compound valve respectively, and enters the front and rear wheel sub-pumps P through the residual pressure regulating valve D and the pressure limiting valve E, and also enters the accumulator. B and high pressure switch valve C.
  • the pressure of the sub-pump P gradually rises to the limit value of the pressure-limiting valve E, the pressure-limiting valve E is closed, the pressure oil cannot pass through the pressure-limiting valve E to the front and rear wheel sub-pumps P, and the sub-pump P remains
  • the pressure set by the pressure limiting valve E that is, the critical locking pressure, the car obtains a large deceleration.
  • the pressure of the oil from the master cylinder T continues to rise, the oil pressure entering the accumulator B overcomes the spring force of the accumulator B to move the free piston 2 in the accumulator B to store energy.
  • the high pressure switch valve C When the oil pressure rises to the pressure set by the high pressure switch valve C, the high pressure switch valve C is opened, the high pressure oil enters the front and rear wheel sub-pumps P, and the braking force of the sub-pump P increases accordingly. Until the front and rear wheels are locked, complete the whole process of car braking and parking.
  • the function of the accumulator B is to prevent the high-pressure switch valve C of the rear-wheel brake compound valve from being opened earlier than the high-pressure switch of the front-wheel brake compound valve when the emergency brake is applied, so that the rear wheel is locked before the front wheel, resulting in the car Iris, side slip.
  • the spring force value of the high pressure switch valve C is higher than that of the front wheel brake compound valve (the pressure value varies according to different vehicles), and the front wheel brake can be ensured.
  • the high pressure switch valve C of the compound valve and the rear wheel brake compound valve has a time difference, and the rear wheel never locks before the front wheel.
  • Automobile main pump T unloading (releasing the brake circuit board) the brake oil of the sub-pump P is returned to the main pump T or the accumulator B via the pressure limiting valve E and the residual pressure regulating valve D, so that the high-voltage switch is wide C It is in the closed state again, and the pressure limiting valve E and the accumulator B are in the original state.
  • the residual pressure regulating valve D Due to the damping effect of the residual pressure regulating valve D, the oil pressure in the line of the residual pressure regulating valve D to the partial pump P is kept constant (can be adjusted as needed).
  • the residual pressure regulating valve D has two functions: one is to ensure that the pipeline after the reading to the sub-pump P is full of oil. The response time during braking (or unloading) can be accelerated, the starting working pressure is increased, and the braking is shortened. The second is that the brake increases the gap due to wear. In a certain range, the gap can be adjusted without adjusting the gap mechanism, and the residual pressure is used to adjust the gap, thereby greatly reducing the workload of adjustment.
  • the exhaust bolts 29 of the front wheel brake compound valve and the rear wheel brake compound valve are used only when the gas in the system needs to be removed.
  • the system workflow is as follows:
  • the working process of the composite valve is as follows:
  • the pressure oil of the automobile master cylinder enters the b-cavity from the inlet of the composite valve through the 29 holes, and the gap of the residual pressure valve sleeve 12 is opened by the small hole d through the small hole c around the residual pressure valve seat 11
  • the cavity e enters the cavity g through the gap f, enters the sub-pump from the outlet through the hole i, enters the cavity j from the h, and the pressurized oil enters the cavity n through the small hole m, and enters the cavity 1 through the small hole k.
  • the spool 15 moves axially, the passage k and! 1.
  • the i is connected, so that the oil pressure of the sub-pump is also raised to the oil inlet pressure.
  • the sub-pump completes the low-pressure clasp brake, a pressure-limiting brake, and a controllable process of the high-pressure lock brake. Due to the energy storage of the Q valve of the front wheel
  • the spring force setting value of the high pressure switch valve is low.
  • the value of the 4 ⁇ wheel H valve is low. Therefore, the high pressure switch valve of the Q valve is opened earlier than the high pressure switch valve of the H valve, so that the rear wheel can not be locked first than the front wheel.
  • the unloading process is as follows: When the brake pedal is released, the theoretical pressure of the chamber b is zero when the master pump is unloaded, and the spring of the brake forces the pump to return oil. The spring 25 forces the spool 23 to move upwards in the axial direction, so that the i, f, and e passages are unblocked. Since the b chamber has no pressure, the residual pressure valve sleeve 12 returns to its original state due to its own elastic force (the original gap does not exist), and the residual pressure is sealed. A small hole in the valve seat 11. The oil of the e cavity cannot be returned to oil through d and c.
  • the pressure of the oil return overcomes the spring force of the spring 10, and the residual pressure valve seat 11 and the residual pressure valve sleeve 12 form a gap between the residual pressure valve sleeve 12 and the valve cover 1.
  • the return oil flows back to the main pump through this gap, and at the same time, the residual pressure maintains the residual pressure set by the spring 10 between the cavity e and the sub-pump.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Abstract

L'invention concerne une soupape composite de freinage hydraulique pour véhicule qui comprend un corps principal. Un passage de fluide est présent dans le corps principal. L'entrée (33) du passage de fluide est connectée à l'extrémité d'entrée d'un cylindre maître (T). Une soupape de régulation de pression résiduelle (D), une soupape de limitation de pression (E), une soupape de commutation haute pression (C), un accumulateur (B) et un boulon d'évacuation d'air (29) sont présents dans le corps principal. L'entrée (33) du passage de fluide est en communication directe avec les entrées du boulon d'évacuation d'air (29), l'accumulateur (B), la soupape de commutation haute pression (C) et la soupape de régulation de pression résiduelle (D). La sortie de la soupape de régulation de pression résiduelle (D) est montée en série avec la soupape de limitation de pression (E). La sortie de la soupape de limitation de pression (E) et la sortie de la soupape de commutation haute pression (C) sont raccordées l'une à l'autre et connectées à un cylindre de roue.
PCT/CN2007/000114 2006-04-27 2007-01-11 Soupape composite de freinage hydraulique pour véhicule Ceased WO2007124636A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN200610020917.3 2006-04-27
CNB2006100209173A CN100402355C (zh) 2006-04-27 2006-04-27 汽车液压制动复合阀

Publications (1)

Publication Number Publication Date
WO2007124636A1 true WO2007124636A1 (fr) 2007-11-08

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2007/000114 Ceased WO2007124636A1 (fr) 2006-04-27 2007-01-11 Soupape composite de freinage hydraulique pour véhicule

Country Status (2)

Country Link
CN (1) CN100402355C (fr)
WO (1) WO2007124636A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108515956A (zh) * 2018-06-15 2018-09-11 李中辉 一种三桥继动阀
CN110696796A (zh) * 2019-11-19 2020-01-17 湖南鸿辉科技有限公司 一种全液压制动系统双继动阀
CN113404797A (zh) * 2021-07-28 2021-09-17 徐志伟 双助动分泵集成阀

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112874498B (zh) * 2021-03-30 2024-07-09 吉林大学 一种汽车制动比例阀

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US4761041A (en) * 1985-10-29 1988-08-02 Aisin Seiki Kabushiki Kaisha Fluid pressure control valve for vehicle braking system
CN2174380Y (zh) * 1993-11-10 1994-08-17 米光 高效汽车制动控制器
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JPH1067310A (ja) * 1996-08-28 1998-03-10 Aisin Seiki Co Ltd 車両用ブレーキ液圧モジュレータ
US6217132B1 (en) * 1997-12-02 2001-04-17 Kelsey-Hayes Company Hydraulic control unit having a master cylinder and anti-lock braking valves integrally mounted therein

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US5390987A (en) * 1993-03-08 1995-02-21 Kelsey-Hayes Company Brake system metering valve with a pressure actuated brake switch
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CN2477882Y (zh) * 2001-04-29 2002-02-20 山东工程机械厂 多功能充液阀
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Publication number Priority date Publication date Assignee Title
US4618188A (en) * 1984-08-13 1986-10-21 Aisin Seiki Kabushiki Kaisha Hydraulic anti-skid apparatus for automotive vehicles
US4761041A (en) * 1985-10-29 1988-08-02 Aisin Seiki Kabushiki Kaisha Fluid pressure control valve for vehicle braking system
CN2174380Y (zh) * 1993-11-10 1994-08-17 米光 高效汽车制动控制器
US5538336A (en) * 1994-12-23 1996-07-23 General Motors Corporation Integrated ABS/TCS hydraulic modulator braking system
JPH1067310A (ja) * 1996-08-28 1998-03-10 Aisin Seiki Co Ltd 車両用ブレーキ液圧モジュレータ
US6217132B1 (en) * 1997-12-02 2001-04-17 Kelsey-Hayes Company Hydraulic control unit having a master cylinder and anti-lock braking valves integrally mounted therein

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108515956A (zh) * 2018-06-15 2018-09-11 李中辉 一种三桥继动阀
CN108515956B (zh) * 2018-06-15 2024-06-04 李中辉 一种三桥继动阀
CN110696796A (zh) * 2019-11-19 2020-01-17 湖南鸿辉科技有限公司 一种全液压制动系统双继动阀
CN113404797A (zh) * 2021-07-28 2021-09-17 徐志伟 双助动分泵集成阀

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CN1899897A (zh) 2007-01-24
CN100402355C (zh) 2008-07-16

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