WO2019149154A1 - Architecture de système de freinage hydraulique anti-blocage et son procédé de mise en oeuvre - Google Patents

Architecture de système de freinage hydraulique anti-blocage et son procédé de mise en oeuvre Download PDF

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Publication number
WO2019149154A1
WO2019149154A1 PCT/CN2019/073234 CN2019073234W WO2019149154A1 WO 2019149154 A1 WO2019149154 A1 WO 2019149154A1 CN 2019073234 W CN2019073234 W CN 2019073234W WO 2019149154 A1 WO2019149154 A1 WO 2019149154A1
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Prior art keywords
module
hydraulic
brake
hydraulic brake
piston rod
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PCT/CN2019/073234
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English (en)
Chinese (zh)
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张奉琦
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张奉琦
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Publication of WO2019149154A1 publication Critical patent/WO2019149154A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62L—BRAKES SPECIALLY ADAPTED FOR CYCLES
    • B62L1/00—Brakes; Arrangements thereof
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62L—BRAKES SPECIALLY ADAPTED FOR CYCLES
    • B62L1/00—Brakes; Arrangements thereof
    • B62L1/005—Brakes; Arrangements thereof constructional features of brake elements, e.g. fastening of brake blocks in their holders
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62L—BRAKES SPECIALLY ADAPTED FOR CYCLES
    • B62L3/00—Brake-actuating mechanisms; Arrangements thereof
    • B62L3/02—Brake-actuating mechanisms; Arrangements thereof for control by a hand lever
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62L—BRAKES SPECIALLY ADAPTED FOR CYCLES
    • B62L3/00—Brake-actuating mechanisms; Arrangements thereof
    • B62L3/02—Brake-actuating mechanisms; Arrangements thereof for control by a hand lever
    • B62L3/023—Brake-actuating mechanisms; Arrangements thereof for control by a hand lever acting on fluid pressure systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads

Definitions

  • the invention relates to an anti-dead lock hydraulic brake system structure and an implementation method thereof for a hydraulic brake system, in particular to a hydraulic brake clamp capable of providing a fully automatic mechanical or electric "anti-dead lock brake” "Functional anti-dead lock hydraulic brake system architecture and its implementation method.
  • Anti-dead lock hydraulic brake system architecture comprising a hydraulic brake actuation module, a housing module, a collection oil circuit module, a throttle damping module, a hydraulic clamping brake module, an oil pressure waveform actuation module And a drive module, and can add a pull wire to activate the piston push rod as a "semi-hydraulic" anti-dead lock hydraulic brake system structure.
  • FIG. 1A and 1B are schematic views showing the structure of a conventional hydraulic brake system.
  • 4A, 4B, and 4C are schematic views showing the operation of the first embodiment of the throttle damping module of the present invention.
  • FIG. 5A is a schematic view showing a second embodiment of the throttle damping module of the present invention.
  • FIG. 5B is a schematic view of a third embodiment of the throttling damping module of the present invention.
  • 6A, 6B, and 6C are schematic views of three mechanical energy driving modules of the present invention.
  • FIG. 7A, 7B, and 7C are schematic diagrams of three power drive modules of the present invention.
  • FIGS. 8A and 8B are schematic views showing a first embodiment of a built-in mechanical energy drive module of the present invention.
  • FIG. 9 is a schematic view of a first embodiment of an external mechanical energy drive module of the present invention.
  • Figure 10 is a schematic view of a second embodiment of the mechanical energy drive module of the present invention.
  • 11A and 11B are schematic views showing a third embodiment of the mechanical energy driving module of the present invention.
  • Figure 12 is a schematic view of a fourth embodiment of the mechanical energy drive module of the present invention.
  • FIG. 13 is a schematic view of a first embodiment of a built-in type electric energy driving module of the present invention.
  • FIG. 14 is a schematic view of a first embodiment of an external power drive module of the present invention.
  • 15 is a schematic view of a second embodiment of an external power drive module of the present invention.
  • Figure 16 is a schematic view showing a third embodiment of the external type electric power driving module of the present invention.
  • the main feature of the anti-dead lock hydraulic brake system structure and the implementation method thereof is that the structure is simple and the action is reliable, and the anti-dead lock brake function is synchronously executed every time the rider performs the braking action, and All related module components are built into a single housing at the same time. Different module components can be placed in different housings respectively.
  • the power source can be selected in the form of mechanical energy or electric energy. Therefore, it can be integrated according to various application requirements. Specific configuration. Here, the most basic combination configuration will be first described as the first embodiment of the present invention, and the system architecture, implementation method and operation will be described in detail, and then other embodiments will be described step by step.
  • the system architecture includes at least a hydraulic brake actuation module 3 and a housing module 10 .
  • a set of oil circuit module 20, a throttle damper module 30, a hydraulic clamp brake module 50, an oil pressure waveform actuation module 60 and a drive module 70, and a pull wire actuating piston push rod 6 can be added as needed.
  • the utility model relates to a structure of a semi-hydraulic anti-dead lock hydraulic brake system, wherein the housing module 10 is configured with a receiving space for accommodating each module, the throttling damping module 30, the hydraulic waveform actuating module 60 and the driving module 70 can cooperate to apply a continuous reciprocatingly varying high/low pressure wave force to the force receiving surface of the piston 51 inside the hydraulic clamp module 50, thereby allowing the piston 51 to continuously apply a tight force on the brake disc 5 A loose, fast-brake effect produces a continuous “anti-deadlock” brake.
  • the continuous reciprocating change of the high/low pressure wave is mainly caused by the high damping effect of the throttle damping module 30 when the internal pressure of the oil passage changes rapidly, and the high damping effect can effectively maintain the rear oil.
  • the magnitude of the internal pressure change of the road will not be weakened, and thus an effective one-tight-slow-fast braking effect will be produced.
  • FIG. 2 The reason why the throttle damping module 30 can generate a high damping effect on the continuously reciprocating high/low pressure wave is shown in FIG. 2, FIG. 3 and FIG. 4A to FIG. 4C.
  • An accommodating space is formed in the interior of the module, the front half of the accommodating space is larger than the rear half of the accommodating space, and the front half of the accommodating space is provided with a front blocking piece 31 having an area larger than the rear half sectional area, and the second half of the accommodating space
  • a rear blocking piece 32 having a smaller area than the rear half of the space is disposed, and a hole 35 is formed in the center of the front blocking piece 31.
  • the front blocking piece 31 and the rear blocking piece 32 are attached to each other, and a front compression is further provided.
  • the spring 33 abuts against the rear of the front flap 31 and a rear compression spring 34 against the rear flap 32, and the viscous resistance of the front flap 31 and the rear flap 32 and the two compression springs 33 and
  • the thrust provided by 34 provides the function of "the faster the fluid pressure changes, the greater the flow damping".
  • 4A shows that when the rider just starts to brake, the brake oil will push the rear flap 32 through the perforation 35 and continue to flow to the rear hydraulic clamp module 50.
  • the throttle damping module 30 is "Shoring large flow low damping mode”
  • FIG. 4B shows that when the rider continues to tighten the brake handle, the drive module 70 generates a reciprocating driving force to continuously drive the hydraulic waveform actuation module 60 inside the oil passage.
  • An oil pressure clamp brake pressure change curve 9 that produces a continuous high pressure/low pressure change between the front flap 31 and the rear flap 32 of the throttle damping module 30 when the continuous high pressure/low pressure change rate is fast
  • the "bonding surface viscous effect” and the thrust of the compression spring 34 against the pressing of the rear flap 32 directly increase the opening resistance of the rear flap 32 when the corresponding rear hydraulic pressure is rapidly lowered, and the front flap
  • the “bonding surface viscous effect” between the wall 31 and the pipe wall and the thrust of the compression spring 33 before the front flap 31 are directly increased to open the front flap 31 when the rear oil pressure is rapidly increased.
  • FIG. 4C shows that the brake oil at this time pushes the front flap 31 backward from the hydraulic clamp brake module 50 and continues to flow back to the front oil passage until the pressure is completely released.
  • the throttle damping module 30 is a "reverse large flow low damping mode”.
  • the throttling damping module 30 consisting of two flaps and two compression springs can be simplified to be composed of a baffle and a compression spring, and still provides a similar throttling damping effect. Please refer to FIG. 2 first. As shown in FIG. 3 and FIG. 5A, after the simplification, the internal accommodating space of the throttle damper module only needs to be provided with a blocking piece 36.
  • the blocking piece 36 is disposed at the center with a thin through hole 37, and a front compression spring 33 is disposed to abut the same.
  • the front side of the flap 36 by the viscous resistance of the flap 36, the thrust of the front compression spring 33, and the throttling resistance of the thin perforation 37, can still produce an action pattern similar to that shown in Figs.
  • the throttle damping module 30 can also provide a damping effect by using a normally open electric throttle valve module.
  • the normally open electric throttle valve module includes an electromagnetic coil 41 and a magnetic permeability.
  • the metal block 42, a compression spring 43, a sealing cover 45 and a throttle passage 48 when a driving circuit continuously sends a current to drive the electromagnetic coil 41, the magnetic conductive metal block 42 can be pushed out, in the section
  • the flow passage opening 48 forms a narrow passage and creates a throttling resistance.
  • the driving module 70 can be divided into the following diagrams for explaining the driving module 70 in the anti-deadlock hydraulic brake system architecture of the present invention.
  • the mechanical energy driving module shown in FIG. 6A to FIG. 6C is different from the power driving module shown in FIG. 7A to FIG. 7C.
  • the embodiment of the mechanical energy driving module can also be divided into the disk type driving module 70a and FIG. 6B of FIG. 6A.
  • Three types of drive modules, such as the wheel type drive module 70b and the axle type drive module 70c of FIG. 6C, the embodiment of the power drive module can be divided into the motor type drive module 70d of FIG.
  • FIG. 7A and the piezoelectric actuator of FIG. 7B Three types of power drive modules, such as the type drive module 70e and the electromagnet type drive module 70f of FIG. 7C, will be described in detail in the description of the disc type drive module and the motor type drive module, respectively, and other types of power sources refer to these two types. A preferred embodiment will be described.
  • the driving module 70a includes a crank 713 and a disk 71 having a cam-shaped outer edge. The difference between the concave point and the convex point of the outer edge of the disk 71 is P.
  • the crank 713 is pivoted with a rotating shaft 715.
  • the 713 is provided with a torsion spring 717 such that one end of the crank 713 contacts the piston rod 61 of the oil pressure waveform actuation module 60, and the other end can be pivoted with a pulley 716, and an adjustment bolt 718 can be further disposed to adjust the pulley. Maintaining a proper spacing G between the outermost edge of the disc 71 and the outer edge of the disc 71.
  • the piston rod 61 of the hydraulic waveform actuating module 60 is automatically pushed out by the pressure-raised internal brake fluid, thereby Driving one end of the crank 713 and contacting the pulley 716 at the other end to the outer edge of the disc 71, the kinetic energy of the disc 71 can be actuated by the crank 713, and the hydraulic waveform actuating module 60
  • the piston rod 61 continues to generate a stroke distance of Z toward
  • the compound movement, by the above-mentioned "frequency damping effect" can generate a reciprocating high/low pressure wave, and provides an "anti-dead lock" brake function for the point brake effect.
  • the anti-dead lock hydraulic brake system architecture of the present invention uses a disk as an external mechanical energy drive module. Referring to FIG. 9, it is apparent from the content shown in FIG. The mechanical kinetic energy conversion mechanisms of the external type and the built-in type mechanical energy drive module are identical to each other, and therefore, for all subsequent built-in type mechanical energy drive module embodiments, the preferred embodiment of the external type will not be repeatedly described.
  • the disc is used as the implementation method of the second embodiment of the built-in mechanical energy drive module.
  • the handle 70a includes a crank 713 and a disc 71a having a circular outer edge.
  • the crank 713 is pivotally provided with a rotating shaft 715.
  • the rotating shaft 715 is sleeved with a torsion spring 717 to contact one end of the crank 713 with the hydraulic waveform actuating module 60.
  • the other end of the piston rod 61 is pivoted with an eccentric wheel 719. The distance between the center of the eccentric wheel 719 and the axis is twice.
  • An adjusting bolt 718 can be provided to adjust the setting of the eccentric 719 and the disc. A proper spacing G is maintained between the outermost edges of the disc 71a.
  • One end of the eccentric 719 at the other end of the disk 719 is in contact with the outer edge of the disk 71a, and the kinetic energy of the disk 71a can be converted by the eccentric 719 and the crank 713, and the hydraulic waveform actuating module
  • the piston rod 61 of 60 continues to generate a stroke distance Z reciprocating movement, by the above "frequency of the damping effect", can produce a reciprocating high / low pressure waves provide Diancha effect "anti-lock” brake function.
  • the implementation method of the third embodiment using the disk as the built-in mechanical energy drive module in the anti-dead lock hydraulic brake system architecture of the present invention is described.
  • the 70a includes a disk 71 having a cam-shaped outer edge.
  • the difference between the concave point and the convex point of the outer edge of the disk 71 is Z, and the exposed end of the piston rod 61 of the hydraulic waveform actuation module 60 is pivoted.
  • a pulley 716, the pulley 716 and the outermost edge of the disc 71 are maintained at an appropriate distance G.
  • the piston rod 61 of the hydraulic waveform actuating module 60 is automatically pressurized.
  • the inner brake oil is pushed out, so that the pulley 716 starts to contact the outer edge of the disc 71, and the kinetic energy of the disc 71 can continuously generate a reciprocating stroke with a stroke distance Z on the piston rod 61 of the oil pressure waveform actuation module 60.
  • the above-mentioned "frequency damping effect” can generate a reciprocating high/low pressure wave, and provide a "anti-deadlock” braking function for the point brake effect.
  • a disc is used as a method for implementing the fourth embodiment of the built-in mechanical energy drive module.
  • the 70a includes a disk 71a having a circular outer edge.
  • An eccentric wheel 719 is pivotally disposed at an exposed end of the piston rod 61 of the oil pressure waveform actuation module 60.
  • the eccentric wheel 719 and the outermost edge of the disk 71a Maintaining a proper spacing G, the distance between the center of the eccentric 719 and the axis is twice, and when the rider starts to brake, the piston rod 61 of the hydraulic waveform actuating module 60 is automatically pressurized.
  • the high internal brake oil is pushed out so that the eccentric 719 contacts the outer edge of the disc 71a, and the kinetic energy of the disc 71a can continue to generate a stroke distance Z on the piston rod 61 of the hydraulic waveform actuating module 60.
  • a reciprocating high/low pressure wave can be generated, and an "anti-deadlock” braking function for the point brake effect can be provided.
  • the motor module is used as the built-in type electric power drive module.
  • the electric power drive module 70 d includes a power source 77 .
  • a motor control circuit module 742 a brake state detecting device 78 and a brushless outer rotor type motor module 74
  • the motor control circuit module 742 is electrically connected to the power source 77, the brake state detecting device 78 and the motor
  • the module 74, the brake state detecting device 78 can detect the brake state and transmit the brake state signal to the motor control circuit module 742
  • the motor module 74 is provided with a cam profile and the difference between the pit and the bump
  • the power output of the Z is a cam shaft 745.
  • the outer edge of the cam shaft 745 contacts the piston rod 61 of the oil pressure waveform actuation module 60.
  • the brake state detecting device 78 can be a mechanical type mounted on the brake handle.
  • the handle position sensing switch or a hydraulic pressure sensing switch connected to the collecting oil passage when the rider starts to brake, the brake state detecting device 78 will "
  • the "in brake” status signal is transmitted to the motor control circuit module 742 such that the motor control circuit module 742 drives the motor module 74 to continue to rotate, and the power of the motor module 74 can be applied to the oil through the conversion of the cam shaft 745.
  • the piston rod 61 of the pressure waveform actuating module 60 continuously generates a reciprocating movement with a stroke distance of Z.
  • a reciprocating high/low pressure wave can be generated to provide a point brake effect.
  • Anti-dead lock" brake function By the above-mentioned "frequency damping effect", a reciprocating high/low pressure wave can be generated to provide a point brake effect. Anti-dead lock" brake function.
  • the implementation method of using the motor module as an external type electric power driving module in the anti-dead lock hydraulic brake system structure of the present invention is described. Referring to FIG. 7A and FIG. 14, the content shown in FIG. 14 can be clearly seen.
  • the external type is identical to the kinetic energy transfer conversion mechanism of the built-in power drive module, so the description will not be repeated.
  • the embodiment of the embodiment of the anti-dead lock hydraulic brake system of the present invention uses a piezoelectric actuator as an external power drive module.
  • the power drive module 70e includes a power source 77, a piezoelectric actuator control circuit module 752, a brake state detecting device 78 and a piezoelectric actuator 75.
  • the piezoelectric actuator 75 is composed of a laminated voltage transistor 753 and a positive electrode 755.
  • the negative electrode 756 is configured to have a length change end contacting the piston rod 61.
  • the piezoelectric actuator control circuit module 752 is electrically connected to the power source 77, the brake state detecting device 78, The positive electrode 755 and the negative electrode 756, the brake state detecting device 78 can detect the braking state and transmit the braking state signal to the piezoelectric actuator control circuit module 752.
  • the braking state detecting device 78 can be a a mechanical handle position sensing switch mounted on the brake handle or a hydraulic pressure sensing switch connected to the collecting oil passage, when the rider starts to brake, the braking state detecting device 78 immediately "brakes" The "state" signal is transmitted to the piezoelectric actuator control circuit module 752, so that the piezoelectric actuator control circuit module 752 immediately drives the laminated voltage transistor 753 by the positive electrode 755 and the negative electrode 756.
  • the reciprocating length changes, so that the reciprocating movement of the stroke distance Z can be continuously generated on the piston rod 61 of the hydraulic waveform actuation module 60.
  • a reciprocating high can be generated.
  • Low pressure wave providing anti-dead lock brake function for point brake effect.
  • the embodiment of the embodiment of the anti-dead lock hydraulic brake system of the present invention uses an electromagnet module as an external power drive module.
  • the power drive module 70f includes a power supply. 77.
  • the electromagnet module 76 is composed of a magnetic conductive metal body 763, an electromagnetic coil 764 and a compression spring 765.
  • the electromagnet control circuit module 762 is electrically connected to the power source 77, the brake state detecting device 78 and the electromagnetic coil 764.
  • the brake state detecting device 78 can detect the braking state and transmit the braking state signal to the electromagnet control circuit module.
  • the measuring device 78 can be a mechanical handle position sensing switch mounted on the brake handle or a hydraulic pressure sensing switch connected to the collecting oil passage when the rider starts to brake
  • the brake state detecting device 78 immediately transmits a "brumking" status signal to the electromagnet control circuit module 762, so that the electromagnet control circuit module 762 immediately drives the electromagnetic coil 764 to generate electromagnetic attraction, and the electromagnetic attraction is
  • the compression spring 765 can push the magnetic conductive metal body 763 to produce a reciprocating displacement change, so that the reciprocating movement of the stroke distance Z can be continuously generated on the piston rod 61 of the hydraulic waveform actuation module 60.
  • the “frequency damping effect” can generate a reciprocating high/low pressure wave and provide an “anti-deadlock” brake function for the point brake effect.
  • FIG. 1A and FIG. 1B indicate a conventional hydraulic brake system. It can be divided into two types: full hydraulic type and semi-hydraulic type. Therefore, the anti-dead lock hydraulic brake system structure of the present invention can also be connected with a pull rod to actuate the piston push rod according to the application requirement.
  • the structure of the "semi-hydraulic" anti-dead lock hydraulic brake system for braking the brakes, Figure 2 and Figure 3 indicate that the modules in the anti-dead lock hydraulic brake system can be built-in or external. The combination of the two systems is achieved.
  • Figures 4A to 4C, 5A and 5B indicate that the main function of the throttle damping module is to provide greater flow damping when the rate of pressure change inside the rear oil passage is faster, and therefore Other throttling damper module implementation methods can be used.
  • Figures 6A-6C and 8-12 show that the power source of the mechanical energy drive module can include at least three types of discs, wheels or axles, and the wheel type and axle type The disc type is the same as the rotary kinetic energy storage carrier. Therefore, both the wheel type and the axle type can use the implementation methods of all the disc type drive modules described above, and accordingly, the mechanical energy drive module can cover all mechanical energy. The conversion is the implementation of the driving force.
  • the power source of the power driving module may include at least three types of motors, piezoelectric actuators, and electromagnets.
  • the power drive module also covers all implementations that convert electrical energy into driving force.
  • the oil pressure clamping brake module in the structure of the anti-dead lock hydraulic brake system of the present invention although the contents of the present specification are all described by the disc-type hydraulic clamping brake module, the present invention is in fact It is not only suitable for disc type hydraulic clamp system, but also for other types of active hydraulic brake modules, such as C-type hydraulic brake module, V-type hydraulic brake module or drum-type hydraulic brake module.
  • the hydraulic waveform actuation module is not limited to the hydraulic actuator that can only use the piston rod type, and any other volume pressure that can accept a reciprocating driving force or a rotary driving force to change the volume and pressure can be Variable devices, such as scroll-type compressor devices, rotor-type compressor devices, diaphragm-type compressor devices, or screw-type compressor devices, which are well known in the art, are also within the scope of the present invention.
  • At least one body motion state physical quantity sensing module can be electrically connected to the control circuit module in the power driving module (for example, the amount of the acceleration sensor) Taking the attitude value of the vehicle body, taking the angular acceleration rate value of the vehicle body by the gyro sensor, taking the pressure value of the brake oil by the brake oil pressure sensor, and/or taking the wheel speed value by the speed sensor, etc.), so that the control circuit is made
  • the module utilizes various real-time driving conditions to improve anti-dead lock brake control performance. Therefore, the application examples disclosed herein are intended to be illustrative of the invention and not to limit the invention. The scope of the invention should be defined by the claims and the legal equivalents thereof, and not limited by the foregoing description.
  • the anti-dead lock hydraulic brake system structure and the implementation method thereof have the unprecedented innovative structure, and the practical functions are far less than those of the prior art, and conform to the Chinese patent law.
  • the provisions on the application requirements for invention patents are filed in accordance with the law.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Braking Arrangements (AREA)
  • Regulating Braking Force (AREA)

Abstract

L'invention concerne une architecture de système de freinage hydraulique anti-blocage, comprenant au moins un module d'actionnement de frein hydraulique (3), un module de logement (10), un module de trajet de fluide hydraulique de collecte (20), un module d'étranglement et d'amortissement (30), un module de frein à serrage hydraulique (50), un module d'actionnement de forme d'onde hydraulique (60), et un module d'entraînement (70), et, une tige de poussée de piston actionnée par un fil de traction pouvant en outre être fournie selon les besoins pour former une architecture de système de freinage hydraulique anti-blocage "semi hydraulique". L'architecture du système de freinage hydraulique anti-blocage est efficacement simplifiée, permet de doter les systèmes de freinage hydrauliques de divers véhicules à deux roues tels que des motocyclettes, des bicyclettes électriques et des bicyclettes ordinaires d'une fonction "anti-blocage", ce qui offre les avantages significatifs de "réduire les coûts de production, de vente et d'application, d'augmenter le degré et la largeur de popularité, et de sauver plus de vies."
PCT/CN2019/073234 2018-02-02 2019-01-25 Architecture de système de freinage hydraulique anti-blocage et son procédé de mise en oeuvre WO2019149154A1 (fr)

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CN201810104377.X 2018-02-02
CN201810104377.XA CN110126959A (zh) 2018-02-02 2018-02-02 一种防死锁油压剎车系统架构及其实施方法

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Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB446266A (en) * 1934-09-25 1936-04-27 Fichtel & Sachs Ag Improvements in and relating to free wheel brake hubs
CN1195623A (zh) * 1997-01-21 1998-10-14 本田技研工业株式会社 两轮车用制动装置、其调节方法以及制动液压缸
CN2502955Y (zh) * 2001-09-10 2002-07-31 陈志铿 防滑煞车系统液压调节装置
CN1433922A (zh) * 2003-02-26 2003-08-06 邵锐勋 液压变速自行车
CN1448297A (zh) * 2003-04-21 2003-10-15 张庙康 防抱死车辆液压制动装置
US7000739B2 (en) * 2002-10-07 2006-02-21 Ciamillo Theodore J Cam assisted wheel brake
CN204210679U (zh) * 2014-11-06 2015-03-18 三阳工业股份有限公司 刹车防死锁系统
CN107117143A (zh) * 2017-04-07 2017-09-01 江苏理工学院 一种制动感觉压电式可调阻尼制动踏板机构
CN107161120A (zh) * 2017-04-07 2017-09-15 江苏理工学院 一种线性可调式踏板感觉模拟器及其制动踏板机构

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWM491246U (zh) * 2014-02-14 2014-12-01 Tronco Electric Machinery Inc 電容式觸控開關之結構
CN105383626B (zh) * 2014-09-04 2017-12-29 四川农业大学 一种机械式abs自行车制动系统及装置
ITUB20152710A1 (it) * 2015-07-31 2017-01-31 Freni Brembo Spa Impianto frenante per veicoli, in particolare cicli e motocicli, e metodo di attuazione di un impianto frenante per veicoli
CN105882857A (zh) * 2016-03-02 2016-08-24 杨书健 一种自行车刹车力度自适应调节装置
CN206037514U (zh) * 2016-08-29 2017-03-22 青岛海尔空调器有限总公司 一种节流装置

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB446266A (en) * 1934-09-25 1936-04-27 Fichtel & Sachs Ag Improvements in and relating to free wheel brake hubs
CN1195623A (zh) * 1997-01-21 1998-10-14 本田技研工业株式会社 两轮车用制动装置、其调节方法以及制动液压缸
CN2502955Y (zh) * 2001-09-10 2002-07-31 陈志铿 防滑煞车系统液压调节装置
US7000739B2 (en) * 2002-10-07 2006-02-21 Ciamillo Theodore J Cam assisted wheel brake
CN1433922A (zh) * 2003-02-26 2003-08-06 邵锐勋 液压变速自行车
CN1448297A (zh) * 2003-04-21 2003-10-15 张庙康 防抱死车辆液压制动装置
CN204210679U (zh) * 2014-11-06 2015-03-18 三阳工业股份有限公司 刹车防死锁系统
CN107117143A (zh) * 2017-04-07 2017-09-01 江苏理工学院 一种制动感觉压电式可调阻尼制动踏板机构
CN107161120A (zh) * 2017-04-07 2017-09-15 江苏理工学院 一种线性可调式踏板感觉模拟器及其制动踏板机构

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