CN204196887U - Full decoupling EHB and corresponding vehicle - Google Patents
Full decoupling EHB and corresponding vehicle Download PDFInfo
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- CN204196887U CN204196887U CN201420590018.7U CN201420590018U CN204196887U CN 204196887 U CN204196887 U CN 204196887U CN 201420590018 U CN201420590018 U CN 201420590018U CN 204196887 U CN204196887 U CN 204196887U
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Abstract
Present specification discloses a kind of full decoupling EHB and corresponding vehicle, described full decoupling electric & hydraulic control system comprises: electronic control unit, motor, brake pedal displacement pickup, brake pedal, secondary master cylinder, pedal simulator, decoupling zero cylinder, master cylinder, wheel cylinder, reservoir, the pipeline between described decoupling zero cylinder and reservoir is provided with decoupling zero cylinder normally closed solenoid valve.Described master cylinder can realize and the decoupling zero of secondary master cylinder and driven by motor or be coupled to secondary master cylinder and driven by secondary master cylinder via decoupling zero cylinder.Described full decoupling electric & hydraulic control system does not adopt high pressure accumulator, pump, hydraulic tubing and electromagnetic valve, can realize ACTIVE CONTROL and the adjustment of hydraulic coupling yet, there is not the problem such as high pressure accumulator potential safety hazard, electromagnetic valve inefficacy; In addition, its structure is simple, without the need to changing master cylinder, reduces cost.The fail safe of brake system is also realized by the combined action of decoupling zero cylinder and normally closed solenoid valve.
Description
Technical field
The utility model belongs to automobile brake technical field, especially relates to a kind of full decoupling EHB and corresponding vehicle.
Background technology
The service braking system of current car adopts vacuum servo formula servo braking system usually, and it provides power-assisted by installing vacuum booster additional between brake pedal push rod and master brake cylinder.When vacuum booster provides brake boost, need to provide vacuum source by the induction maniflod of driving engine or special vacuum pump.When utilizing the induction maniflod of driving engine to provide vacuum source, if engine stop work, then vacuum servo event resolves.In addition, at present for the requirement of environmental protection, the application of pure electric automobile and hybrid vehicle gets more and more.Because electronlmobil replaces traditional combustion engine with electrical motor, lose the possibility utilizing combustion engine to provide vacuum source, and hybrid vehicle take also electrical motor as main power source or all using electrical motor as propulsion source, now vacuum source must realize with vacuum pump in some occasion.Which not only adds number of parts on automobile and corresponding control and reduce the reliability of automobile, also can increase the difficult arrangement of machinery space simultaneously and increase the work noise of automobile.Vacuum booster also also exists the larger shortcoming of volume.
The power-assisted size of electric booster braking is controlled, and assist motor can lack power-assisted or non-power-assisted according to demand to reduce friction braking, therefore for reclaiming more multi-energy during regenerative brake.Thus, current Electro-hydraulic brake system Application comparison is extensive, wherein common a kind of form is non-decoupling type electro-hydraulic brake system, its principle loads certain idle travel on brake boost part, regenerative braking force is provided by drive motor in this section of idle travel, after overcoming this section of idle travel, hydraulic braking gets involved, total braking force is provided together with regenerative brake, this composite braking system remains the mechanical connection of pedal and hydraulic efficiency pressure system, reliability and safety high, but its callable braking energy is few, has deviation with traditional brake pedal feel.
Minority brake system have employed full decoupling Electro-hydraulic brake system, but due to the completely de-coupling of pedal, when requiring that brake system must consider generation and some brake component et out of order of failure conditions according to national legislation, system still can carry out the braking of some strength; The fail safe mode that current full decoupling Electro-hydraulic brake system is commonly used is generally coordinate motor and the braking Input Forces of pump to hydraulic efficiency pressure system to carry out ACTIVE CONTROL by installation high-voltage energy storage; but this mode is changed larger to master cylinder; simultaneously high pressure accumulator technology immature, there is hidden danger in its reliability and safety.
Utility model content
For solving the problems of the technologies described above, developing a kind of full decoupling EHB and corresponding vehicle, Brake energy recovery and fail safe can be realized.
A kind of full decoupling EHB, is characterized in that, comprising:
Electronic control unit, connect described electronic control unit motor, connect described electronic control unit brake pedal displacement pickup, can by described brake pedal displacement pickup detect displacement information brake pedal, connect described brake pedal secondary master cylinder, connect described secondary master cylinder pedal simulator, connect the decoupling zero cylinder of described secondary master cylinder, between master cylinder and described master cylinder, there is the wheel cylinder of brake piping; Wherein, under the control of described electronic control unit, described master cylinder is suitable for selectivity and realizes and the decoupling zero of secondary master cylinder and driven by motor or be coupled to secondary master cylinder and driven by secondary master cylinder via decoupling zero cylinder;
Described EHB at least possesses the first mode of operation and the second mode of operation;
Wherein, under first mode of operation, described electronic control unit is suitable for the braking force of the pedal displacement information computation requirement according to described brake pedal, according to the regenerative braking force calculating hydraulic braking force of the drive motor that the braking force of described demand is connected with this electronic control unit; Described motor is suitable for driving master cylinder with required hydraulic braking force under the control of electronic control unit, and the braking liquid in described master cylinder flows to wheel cylinder to produce braking effect via brake piping; Described electronic control unit is also suitable for sending control signal, thus makes the hydraulic coupling of described secondary master cylinder be passed to pedal simulator to simulate pedal sense, and described secondary master cylinder realizes decoupling zero via described decoupling zero cylinder and master cylinder;
Under second mode of operation, described electronic control unit is suitable for control system power-off, described secondary master cylinder realizes and being coupled of master cylinder via decoupling zero cylinder, the braking force that described secondary master cylinder produces under the displacement effect of brake pedal is passed to master cylinder, and the braking liquid in described master cylinder flows to wheel cylinder to produce braking effect via brake piping.
Alternatively, the hydraulic tubing that described decoupling zero cylinder is connected with reservoir is provided with decoupling zero cylinder normally closed solenoid valve, is suitable for the couple state regulated under the opening and closing of described decoupling zero cylinder normally closed solenoid valve between described secondary master cylinder and master cylinder.
Alternatively, described EHB also comprises push rod and can coordinate the straight-line motion mechanism of described push rod; Described push rod is connected between decoupling zero cylinder and master cylinder, and described straight-line motion mechanism is connected to motor.
Alternatively, described decoupling zero cylinder comprises decoupling zero cylinder cylinder body and decoupling zero cylinder piston, forms decoupling zero cylinder hydraulic cavities between described decoupling zero cylinder piston and cylinder body one end face; Described decoupling zero cylinder piston connects secondary master cylinder; Described decoupling zero cylinder cylinder body connects described push rod; The fuel-displaced hydraulic tubing of described decoupling zero cylinder hydraulic chamber into communication is provided with decoupling zero cylinder normally closed solenoid valve, and described decoupling zero cylinder normally closed solenoid valve is connected to electronic control unit.
Alternatively, described decoupling zero cylinder and described secondary master cylinder, straight-line motion mechanism, push rod, master cylinder are coaxially arranged.
Alternatively, described pedal simulator comprises simulator cylinder body, emulator piston, simulator pull back spring; Form pedal simulator epitrochoidal chamber between described emulator piston and simulator cylinder body one end face, described simulator pull back spring is arranged in simulator epitrochoidal chamber; Described simulator cylinder body is connected to secondary master cylinder by hydraulic tubing; The fuel-displaced hydraulic tubing that described simulator epitrochoidal chamber is communicated with is provided with proportion magnetic valve; Described proportion magnetic valve is connected to electronic control unit.
Alternatively, the hydraulic tubing between described secondary master cylinder and described pedal simulator cylinder body is provided with pedal simulator pressure sensor.
Alternatively, described straight-line motion mechanism comprises worm gear-endless screw mechanism, Rack and pinion mechanism or guilde screw mechanism.
Alternatively, described push rod comprises putter body and the first longeron, the second longeron, and described putter body is perpendicular to first, second longeron described.
Alternatively, described putter body is through the worm screw in straight-line motion mechanism, tooth bar or leading screw; Worm screw in described putter body and straight-line motion mechanism, tooth bar or leading screw recessed bond ing.
Alternatively, described EHB also comprises the secondary master cylinder normally open solenoid valve on the fuel-displaced hydraulic tubing being arranged on the connection of secondary master cylinder; Described secondary master cylinder normally open solenoid valve is connected to electronic control unit.
Alternatively, described EHB also comprises antiblock device/dynamic stability control system module, is arranged between described master cylinder and wheel cylinder.
Alternatively, described master cylinder comprises master cylinder body, master cylinder first piston, master cylinder second piston, master cylinder first piston push rod, master cylinder first piston pull back spring, master cylinder second piston return spring; Wherein, master cylinder first piston and master cylinder second piston are all positioned at master cylinder body; Master cylinder first epitrochoidal chamber is formed between master cylinder first piston and master cylinder second piston; Master cylinder second piston and master cylinder body first end face form master cylinder second epitrochoidal chamber; First piston push rod is connected through master cylinder body second end face and master cylinder first piston end face; Master cylinder first piston pull back spring is arranged on master cylinder first piston and master cylinder second piston space; Master cylinder second piston return spring is arranged between master cylinder second piston and master cylinder body first end face.
Alternatively, described secondary master cylinder comprises secondary master cylinder body, secondary master cylinder push rod, secondary master cylinder pull back spring; Wherein, secondary master cylinder hydraulic pressure chamber is formed between secondary master cylinder push rod and secondary master cylinder body first end face; Secondary master cylinder pull back spring is arranged in secondary master cylinder hydraulic pressure chamber; Described secondary master cylinder push rod through described secondary master cylinder first end face, and is connected with decoupling zero cylinder piston; The oil outlet in described secondary master cylinder hydraulic pressure chamber is communicated to pedal simulator by hydraulic tubing.
Alternatively, described brake pedal is connected with secondary master cylinder push rod by rest pin.
Alternatively, described full decoupling EHB also comprises the monitoring diagnosis system for the detection and diagnosis system failure; The alarm device given the alarm when being also included in the system failure with described full decoupling EHB.
Alternatively, when motor or straight-line motion mechanism break down, described full decoupling EHB is in the second mode of operation; When described motor or straight-line motion mechanism do not break down, described full decoupling EHB is in the first mode of operation.
Alternatively, when motor and straight-line motion mechanism do not break down and hydraulic tubing leakage time, failure message is sent to electronic control unit by monitoring diagnosis system, is reported to the police by electronic control unit instruction alarm device.
In addition, the utility model additionally provides a kind of vehicle, comprises above-mentioned arbitrary described full decoupling EHB.
Compared with prior art, the technical solution of the utility model has the following advantages:
Adopt electric machine control, fast response time, accurately controls hydraulic braking force, well coordinates motor regenerative braking force, completes chaufeur braking intention preferably.
Adopt decoupling zero cylinder, make it possible to provide motor driving or secondary master cylinder to drive two kinds of modes, thus realize fail safe, improve system safety and reliability.
In a preferred embodiment, also have the following advantages:
Decoupling zero cylinder devises idle travel, the regenerative braking force of drive motor can be given full play to, simultaneously because the motor of automatically controlled straight-line motion mechanism is controlled, thus can according to the regenerative braking force of drive motor, required demand braking force, in good time adjustment hydraulic braking force, thus reclaim braking energy substantially.
By carrying out hydraulic efficiency governing to the proportion magnetic valve in pedal simulator exit, then can control the rate of change of pedal simulator hydraulic coupling, thus ACTIVE CONTROL can be carried out to the treadle effort of chaufeur.
In existing technology, or useful high pressure accumulator and electric-motor pump combined action carry out hydraulic coupling adjustment to master cylinder wheel cylinder, but high pressure accumulator adopts high pressure nitrogen, very high to the sealing requirements of system, simultaneously because its pressure is high, easily produce potential safety hazard.And this case motor and physical construction replace high pressure accumulator, pump, hydraulic tubing and electromagnetic valve, also can realize ACTIVE CONTROL and the adjustment of hydraulic coupling, there is not the problem such as high pressure accumulator potential safety hazard, electromagnetic valve inefficacy; Meanwhile, its structure is simple, without the need to changing master cylinder.
Under decoupling zero cylinder and the mating reaction of decoupling zero cylinder normally closed solenoid valve, treadle effort can be delivered to master cylinder push rod, still can produce certain hydraulic braking force, thus guarantees that system has very high safety, reliability, realizes fail safe.
Accompanying drawing explanation
Fig. 1 be in an embodiment of the present utility model full decoupling EHB structural representation;
Fig. 2 is the partial enlarged drawing of secondary master cylinder and decoupling zero cylinder in Fig. 1;
The partial enlarged drawing of Tu3Shi Tu1 linear movement mechanism, push rod and motor;
Description of reference numerals
1-brake pedal; 2-level master cylinder; 3-motor; 4-decoupling zero cylinder; 5-straight-line motion mechanism; 6-decoupling zero cylinder oil outlet; 7-push rod; 8-master cylinder; 9-master cylinder first piston push rod; 10-master cylinder first piston pull back spring; 11-reservoir; 12-master cylinder second piston; 13-master cylinder second piston return spring; 14-antiblock device/dynamic stability control system module; 15-first hydraulic tubing; 16-second hydraulic tubing; 17-the near front wheel hydraulic tubing; 18-off front wheel hydraulic tubing; 19-left rear wheel hydraulic tubing; 20-off hind wheel hydraulic tubing; 21-the near front wheel wheel cylinder; 22-off front wheel wheel cylinder; 23-left rear wheel wheel cylinder; 24-off hind wheel wheel cylinder; 25-master cylinder second epitrochoidal chamber; 26-master cylinder first epitrochoidal chamber; 27-proportion magnetic valve; 28-pedal simulator oil outlet; 29 simulator pull back springs; 30-decoupling zero cylinder normally closed solenoid valve; 31-pedal simulator pressure sensor; 32-level master cylinder outlet mouth; 33-level master cylinder return opening; 34-level master cylinder normally open solenoid valve; 35-level master cylinder push rod; 36-level master cylinder pull back spring; 37-pedal displacement sensor; 38-drive motor; 39-electronic control unit; 40-control path; 41-master cylinder first compensation orifice; 42-master cylinder second compensation orifice; 43-decoupling zero cylinder piston; 44-pedal simulator; 45-master cylinder body; 46-master cylinder first piston; 47-level master cylinder body, 48-level master cylinder hydraulic pressure chamber; 49-worm gear; 50-worm screw
Detailed description of the invention
For enabling above-mentioned purpose of the present utility model, feature and advantage more become apparent, and launch explanation below in conjunction with accompanying drawing to embodiment of the present utility model.
Shown in composition graphs 1 to Fig. 2, a kind of full decoupling EHB comprises: electronic control unit 39, connect the motor 3 of described electronic control unit 39, connect the brake pedal displacement pickup 37 of described electronic control unit 39, the brake pedal 1 of its displacement information can be detected by described brake pedal displacement pickup 37, connect the secondary master cylinder 2 of described brake pedal 1, connect the pedal simulator 44 of described secondary master cylinder 2, connect the decoupling zero cylinder 4 of described secondary master cylinder, master cylinder 8, brake piping 17 is there is with corresponding respectively between described master cylinder 8, 18, 19, the wheel cylinder 21 of 20, 22, 23 and 24, reservoir 11, pipeline between described decoupling zero cylinder 4 and reservoir 11 is provided with decoupling zero cylinder normally closed solenoid valve 30.
Wherein, under the control of described electronic control unit 39, described master cylinder 8 is suitable for selectivity and drives or be coupled to secondary master cylinder 2 by described motor 3 via decoupling zero cylinder 4 and the decoupling zero of secondary master cylinder 2 and driven by secondary master cylinder 2.
Based on above-mentioned structure, described full decoupling EHB at least possesses the first mode of operation and the second mode of operation.
Wherein, under first mode of operation, described electronic control unit 39 is suitable for the braking force of the pedal displacement information computation requirement according to described brake pedal 1, according to the regenerative braking force calculating hydraulic braking force of the drive motor 38 that the braking force of described demand is connected with this electronic control unit 39; Described motor 3 is suitable for driving master cylinder 8 with required hydraulic braking force under the control of electronic control unit 39, and the braking liquid in described master cylinder 8 flows to corresponding wheel cylinder 21,22,23,24 to produce braking effect via brake piping 17,18,19,20; Described electronic control unit 39 is also suitable for sending control signal, thus make the hydraulic coupling of described secondary master cylinder 2 be passed to pedal simulator 44 to simulate pedal sense, and the pipeline between decoupling zero cylinder 4 and reservoir 11 is opened, make the hydraulic coupling of described secondary master cylinder 2 can not be passed to master cylinder 8;
Under second mode of operation, described electronic control unit 39 is suitable for control system power-off; Path between secondary master cylinder 2 and reservoir 11 is opened, the braking liquid of described secondary master cylinder 2 li is back to reservoir 11, the braking force that described secondary master cylinder 2 produces under the displacement effect of brake pedal is passed to master cylinder 8, and the braking liquid in described master cylinder 8 flows to wheel cylinder 21,22,23,24 to produce braking effect via brake piping 17,18,19,20 correspondence.
Continue to consult Fig. 1, in one embodiment, for transmitting the propulsive effort of motor 3 pairs of master cylinders 8, between motor 3 and master cylinder 8, be provided with push rod 7 and the straight-line motion mechanism 5 that can coordinate described push rod 7, wherein said push rod 7 connects master cylinder 8 and decoupling zero cylinder 4, and described straight-line motion mechanism 5 connects motor 3.
Below in conjunction with specific embodiment, above-mentioned embodiment is set forth in more detail.Shown in composition graphs 1 to Fig. 2, the full decoupling EHB of the present embodiment comprises: master cylinder 8, secondary master cylinder 2, decoupling zero cylinder 4, brake pedal 1, electronic control unit (ECU) 39, drive motor 38, straight-line motion mechanism 5, push rod 7, motor 3, pedal simulator 44, pedal displacement sensor 37, first hydraulic tubing 15, second hydraulic tubing 16, the near front wheel hydraulic tubing 17, off front wheel hydraulic tubing 18, left rear wheel hydraulic tubing 19, off hind wheel hydraulic tubing 20, the near front wheel wheel cylinder 21, off front wheel wheel cylinder 22, left rear wheel wheel cylinder 23, off hind wheel wheel cylinder 24, reservoir 11 and proportion magnetic valve 27, decoupling zero cylinder normally closed solenoid valve 30, secondary master cylinder normally open solenoid valve 34.
Described master cylinder 8 adopts two cavate master brake cylinders, comprises master cylinder body 45, master cylinder first piston 46, master cylinder second piston 12, master cylinder first piston push rod 9, master cylinder first piston pull back spring 10, master cylinder second piston return spring 13; Wherein, master cylinder first piston 46 and master cylinder second piston 12 are all positioned at master cylinder body 45; Master cylinder first epitrochoidal chamber 26 is formed between master cylinder first piston 9 and master cylinder second piston 12; Master cylinder second piston 12 and master cylinder body 45 front end face form master cylinder second epitrochoidal chamber 25; Master cylinder first piston push rod 9, through master cylinder body 45 aft end face, is connected with master cylinder first piston 46 end face; Master cylinder first piston pull back spring 10 is provided with between master cylinder first piston 46 and master cylinder second piston 12; Master cylinder second piston return spring 13 is provided with between master cylinder second piston 12 and master cylinder body 45 front end face; Master cylinder first epitrochoidal chamber 26 and master cylinder second epitrochoidal chamber 25 have master cylinder first compensation orifice 41 and master cylinder second compensation orifice 42 that are connected reservoir 11 respectively.Master cylinder first epitrochoidal chamber 26 and master cylinder second epitrochoidal chamber 25 are connected to described antiblock device/dynamic stability control system module 14 by first, second hydraulic tubing 15,16.
Described secondary master cylinder 2 comprises secondary master cylinder body 47, secondary master cylinder push rod 35, secondary master cylinder pull back spring 36; Wherein, secondary master cylinder push rod 35 forms secondary master cylinder hydraulic pressure chamber 48 with secondary master cylinder body 47 front end face; Secondary master cylinder pull back spring 36 is positioned at secondary master cylinder hydraulic pressure chamber 48, and coaxially arranged with secondary master cylinder push rod 35; Described secondary master cylinder push rod 35 through described secondary master cylinder front end face, and is connected with decoupling zero cylinder piston 43 end face; Described secondary master cylinder is also provided with secondary master cylinder return opening 33 and secondary master cylinder outlet mouth 32.
Described decoupling zero cylinder 4 comprises decoupling zero cylinder cylinder body, decoupling zero cylinder piston 43, and decoupling zero cylinder piston 43 and decoupling zero cylinder front end face form decoupling zero cylinder hydraulic cavities; Described decoupling zero cylinder piston 43 is connected with described secondary master cylinder push rod 35; Described decoupling zero cylinder cylinder body is connected with described push rod 7; Described decoupling zero cylinder 4 is coaxially arranged with described secondary master cylinder 2, straight-line motion mechanism 5, push rod 7, master cylinder 8.
Described pedal simulator 44 comprises simulator cylinder body, emulator piston, simulator pull back spring 29; Wherein, emulator piston is positioned at simulator cylinder body; As epitrochoidal chamber between emulator piston and simulator cylinder body front end face, and be axially provided with simulator pull back spring 29 between pedal simulator piston and simulator cylinder body front end face; Pedal simulator 44 is by simulator pull back spring 29 and proportion magnetic valve 27 combined action simulation pedal sense; Described pedal simulator 44 is connected with secondary master cylinder outlet mouth 32 by hydraulic tubing.
Described brake pedal 1 is connected with the secondary master cylinder push rod 35 in secondary master cylinder 2 by rest pin.
Reservoir 11 is connected with master cylinder second epitrochoidal chamber 25 with master cylinder first epitrochoidal chamber 26 respectively; Also be connected with secondary master cylinder 2 by secondary master cylinder return opening 33 simultaneously.The hydraulic tubing that reservoir 11 is connected with pedal simulator 44 is provided with proportion magnetic valve 27; The hydraulic tubing that reservoir 11 is connected with decoupling zero cylinder 4 is provided with decoupling zero cylinder normally closed solenoid valve 30; Reservoir 11 and secondary master cylinder outlet mouth 32 connected hydraulic pipeline are provided with secondary master cylinder normally open solenoid valve 34.
The oil outlet 32 of secondary master cylinder 2 is connected with pedal simulator 44 by hydraulic tubing; And hydraulic tubing between described secondary master cylinder outlet mouth 32 and described pedal simulator 44 is provided with pedal simulator pressure sensor 31.
As a kind of preferred implementation of the technical program, full decoupling EHB also comprises antiblock device/dynamic stability control system module (ABS/ESP) 14, and described master cylinder 8 is connected to described antiblock device/dynamic stability control system module (ABS/ESP) 14 by first, second hydraulic tubing 15,16.Described antiblock device/dynamic stability control system module (ABS/ESP) 14 is connected with the near front wheel wheel cylinder 21, off front wheel wheel cylinder 22, left rear wheel wheel cylinder 23, off hind wheel wheel cylinder 24 by front-wheel hydraulic tubing 17, off front wheel hydraulic tubing 18, left rear wheel hydraulic tubing 19, off hind wheel hydraulic tubing 20 are corresponding respectively.
Under first mode of operation, as shown in Figure 1, when stepping on brake pedal, proportion magnetic valve 27, decoupling zero cylinder normally closed solenoid valve 30, secondary master cylinder normally open solenoid valve 34 all power on.Proportion magnetic valve 27 by the switch ratio of Controlling solenoid valve, thus controls the treadle effort that pedal simulator 44 is simulated; Secondary master cylinder push rod 35 promotes decoupling zero cylinder piston 43 and travels forward.
Decoupling zero cylinder normally closed solenoid valve 30 powers on and opens, secondary master cylinder normally open solenoid valve 34 powers on cut out, brake pedal 1 promotes secondary master cylinder push rod 35, braking liquid is injected into pedal simulator 44 from secondary master cylinder outlet mouth 32 by secondary master cylinder 2, and pedal simulator 44 is by pedal simulator spring 29 and proportion magnetic valve 27 combined action simulation pedal sense; Meanwhile, the liquid in decoupling zero cylinder 4 flows into reservoir 11 through decoupling zero cylinder normally closed solenoid valve 30, decoupling zero cylinder cylinder body and the decoupling zero of decoupling zero cylinder piston 43.
Now pedal displacement sensor 37 obtains pedal displacement signal, receive braking intention and the demand braking force of chaufeur, the pedal displacement signal collected is delivered in electronic control unit 39 by control path 40, electronic control unit 39 calculates the size of drive motor 38 regenerative braking force according to drive motor 38 operating characteristic and cell operating status, drive motor regenerative braking force is deducted by total demand braking force, obtain hydraulic braking force size required in this time braking, then electronic control unit 39 controls motor 3 by control path 40 and drives straight-line motion mechanism 5, straight-line motion mechanism 5 drives push rod 7 to promote the master cylinder first piston 46 be connected with master cylinder first piston push rod 9, when master cylinder first piston 46 blocks master cylinder the first compensation orifice 41, master cylinder first epitrochoidal chamber 26 starts to build pressure, then by master cylinder first piston pull back spring 10, master cylinder first piston push rod 9 promotes master cylinder second piston 12 straight-line motion, when master cylinder second piston 12 blocks master cylinder the second compensation orifice 42, master cylinder second epitrochoidal chamber 25 starts to build pressure, braking liquid is through first, second hydraulic tubing 15, 16 flow to antiblock device/dynamic stability control system module (ABS/ESP) 14, then each wheel cylinder 21 is flowed to, 22, 23, 24 produce braking force.
In addition, according to another preferred embodiment of the present utility model, this full decoupling type EHB also devises fail safe scheme.
As shown in Figure 1, when motor 3 and straight-line motion mechanism 5 do not break down and hydraulic tubing leakage time, failure message is sent to electronic control unit 39 by monitoring diagnosis system, by electronic control unit 39 instruction alarm device warning reminding chaufeur.A system warning reminding and do not carry out system cut-off.
When motor 3 and/or straight-line motion mechanism 5 break down, failure message can be sent to electronic control unit 39 by described monitoring diagnosis system, enter the second mode of operation, by electronic control unit 39 instruction alarm device warning reminding chaufeur and instruction repertoire power-off.
After proportion magnetic valve 27, decoupling zero cylinder normally closed solenoid valve 30, the power-off of secondary master cylinder normally open solenoid valve 34, proportion magnetic valve 27 and secondary master cylinder normally open solenoid valve 34 are in open mode, the hydraulic coupling of secondary master cylinder 2 is discharged rapidly by secondary master cylinder normally open solenoid valve 34, is back to reservoir 11; Decoupling zero cylinder normally closed solenoid valve 30 is in closed condition, and the liquid in decoupling zero cylinder hydraulic cavities does not flow out by decoupling zero cylinder normally closed solenoid valve 30, and decoupling zero cylinder cylinder body is coupled with decoupling zero cylinder piston 43; Now step on brake pedal 1, brake pedal 1 acts on decoupling zero cylinder 4 by secondary master cylinder push rod 35, decoupling zero cylinder 4 acts on push rod 7, and promote master cylinder first piston push rod 9 by push rod 7 and make master cylinder 8 delivery pressure to antiblock device/dynamic stability control system module (ABS/ESP) 14, then flow to each wheel cylinder 21,22,23,24 and produce braking force.
As shown in Figure 3, according to a preferred embodiment of the present utility model, described straight-line motion mechanism 5 can adopt worm gear-endless screw mechanism, described worm gear 49 is connected with motor 3, there is through hole at the center of worm screw 50, described push rod 7 body is through the through hole of worm screw 50, and push rod 7 is not connected with master cylinder first piston push rod 9 by the second longeron of push rod 7 through the body side of through hole.In a first operation mode, motor 3 Driving Torque, worm gear 49 rotates and drives worm screw 50 and push rod 7 straight-line motion, thus promotion master cylinder first piston 46 and the second piston 12 move.In addition, push rod 7 is connected with decoupling zero cylinder 4 through the side of worm screw 50 through hole.
According to another embodiment of this case, described straight-line motion mechanism 5 can also adopt pinion and rack, the center of tooth bar has through hole, described putter body is through the through hole of described tooth bar, motor 3 Driving Torque, pinion rotation band carry-over bar and push rod 7 straight-line motion, promote first piston 46 and the second piston 12 moves.
In some cases, described straight-line motion mechanism also can adopt screw-nut body, described leading screw center has through hole, described putter body is through the through hole of described leading screw, motor output torque, nut rotation drives leading screw and push rod 7 straight-line motion, promotes master cylinder first piston 46, second piston 12 and moves.
In addition, the utility model additionally provides a kind of vehicle, comprises full decoupling EHB as above.
Although the utility model discloses as above, the utility model is not defined in this.Any those skilled in the art, not departing from spirit and scope of the present utility model, all can do various variation and amendment, and therefore protection domain of the present utility model should be as the criterion with claim limited range.
Claims (19)
1. a full decoupling EHB, is characterized in that, comprising:
Electronic control unit, connect described electronic control unit motor, connect described electronic control unit brake pedal displacement pickup, can by described brake pedal displacement pickup detect displacement information brake pedal, connect described brake pedal secondary master cylinder, connect described secondary master cylinder pedal simulator, connect the decoupling zero cylinder of described secondary master cylinder, between master cylinder and described master cylinder, there is the wheel cylinder of brake piping; Wherein, under the control of described electronic control unit, described master cylinder is suitable for selectivity and realizes and the decoupling zero of secondary master cylinder and driven by motor or be coupled to secondary master cylinder and driven by secondary master cylinder via decoupling zero cylinder;
Described EHB at least possesses the first mode of operation and the second mode of operation;
Wherein, under first mode of operation, described electronic control unit is suitable for the braking force of the pedal displacement information computation requirement according to described brake pedal, according to the regenerative braking force calculating hydraulic braking force of the drive motor that the braking force of described demand is connected with this electronic control unit; Described motor is suitable for driving master cylinder with required hydraulic braking force under the control of electronic control unit, and the braking liquid in described master cylinder flows to wheel cylinder to produce braking effect via brake piping; Described electronic control unit is also suitable for sending control signal, thus makes the hydraulic coupling of described secondary master cylinder be passed to pedal simulator to simulate pedal sense, and described secondary master cylinder realizes decoupling zero via described decoupling zero cylinder and master cylinder;
Under second mode of operation, described electronic control unit is suitable for control system power-off, described secondary master cylinder realizes and being coupled of master cylinder via decoupling zero cylinder, the braking force that described secondary master cylinder produces under the displacement effect of brake pedal is passed to master cylinder, and the braking liquid in described master cylinder flows to wheel cylinder to produce braking effect via brake piping.
2. full decoupling EHB as claimed in claim 1, it is characterized in that, the hydraulic tubing that described decoupling zero cylinder is connected with reservoir is provided with decoupling zero cylinder normally closed solenoid valve, is suitable for the couple state regulated under the opening and closing of described decoupling zero cylinder normally closed solenoid valve between described secondary master cylinder and master cylinder.
3. full decoupling EHB as claimed in claim 1, is characterized in that, also comprises push rod and the straight-line motion mechanism that can coordinate described push rod; Described push rod is connected between decoupling zero cylinder and master cylinder, and described straight-line motion mechanism is connected to motor.
4. full decoupling EHB as claimed in claim 3, it is characterized in that, described decoupling zero cylinder comprises decoupling zero cylinder cylinder body and decoupling zero cylinder piston, forms decoupling zero cylinder hydraulic cavities between described decoupling zero cylinder piston and cylinder body one end face; Described decoupling zero cylinder piston connects secondary master cylinder; Described decoupling zero cylinder cylinder body connects described push rod; The fuel-displaced hydraulic tubing of described decoupling zero cylinder hydraulic chamber into communication is provided with decoupling zero cylinder normally closed solenoid valve, and described decoupling zero cylinder normally closed solenoid valve is connected to electronic control unit.
5. full decoupling EHB as claimed in claim 4, it is characterized in that, described decoupling zero cylinder and described secondary master cylinder, straight-line motion mechanism, push rod, master cylinder are coaxially arranged.
6. full decoupling EHB as claimed in claim 3, it is characterized in that, described pedal simulator comprises simulator cylinder body, emulator piston, simulator pull back spring; Form pedal simulator epitrochoidal chamber between described emulator piston and simulator cylinder body one end face, described simulator pull back spring is arranged in simulator epitrochoidal chamber; Described simulator cylinder body is connected to secondary master cylinder by hydraulic tubing; The fuel-displaced hydraulic tubing that described simulator epitrochoidal chamber is communicated with is provided with proportion magnetic valve; Described proportion magnetic valve is connected to electronic control unit.
7. full decoupling EHB as claimed in claim 6, is characterized in that, the hydraulic tubing between described secondary master cylinder and described pedal simulator cylinder body is provided with pedal simulator pressure sensor.
8. full decoupling EHB as claimed in claim 3, it is characterized in that, described straight-line motion mechanism comprises worm gear-endless screw mechanism, Rack and pinion mechanism or guilde screw mechanism.
9. full decoupling EHB as claimed in claim 8, it is characterized in that, described push rod comprises putter body and the first longeron, the second longeron, and described putter body is perpendicular to first, second longeron described.
10. full decoupling EHB as claimed in claim 9, is characterized in that, described putter body is through the worm screw in straight-line motion mechanism, tooth bar or leading screw; Worm screw in described putter body and straight-line motion mechanism, tooth bar or leading screw recessed bond ing.
11. full decoupling EHBs as claimed in claim 1, is characterized in that, also comprise the secondary master cylinder normally open solenoid valve on the fuel-displaced hydraulic tubing being arranged on the connection of secondary master cylinder; Described secondary master cylinder normally open solenoid valve is connected to electronic control unit.
12. full decoupling EHBs as claimed in claim 1, is characterized in that, also comprise antiblock device/dynamic stability control system module, be arranged between described master cylinder and wheel cylinder.
13. full decoupling EHBs as claimed in claim 3, it is characterized in that, described master cylinder comprises master cylinder body, master cylinder first piston, master cylinder second piston, master cylinder first piston push rod, master cylinder first piston pull back spring, master cylinder second piston return spring; Wherein, master cylinder first piston and master cylinder second piston are all positioned at master cylinder body; Master cylinder first epitrochoidal chamber is formed between master cylinder first piston and master cylinder second piston; Master cylinder second piston and master cylinder body first end face form master cylinder second epitrochoidal chamber; First piston push rod is connected through master cylinder body second end face and master cylinder first piston end face; Master cylinder first piston pull back spring is arranged on master cylinder first piston and master cylinder second piston space; Master cylinder second piston return spring is arranged between master cylinder second piston and master cylinder body first end face.
14. full decoupling EHBs as claimed in claim 4, is characterized in that, described secondary master cylinder comprises secondary master cylinder body, secondary master cylinder push rod, secondary master cylinder pull back spring; Wherein, secondary master cylinder hydraulic pressure chamber is formed between secondary master cylinder push rod and secondary master cylinder body first end face; Secondary master cylinder pull back spring is arranged in secondary master cylinder hydraulic pressure chamber; Described secondary master cylinder push rod through described secondary master cylinder first end face, and is connected with decoupling zero cylinder piston; The oil outlet in described secondary master cylinder hydraulic pressure chamber is communicated to pedal simulator by hydraulic tubing.
15. full decoupling EHBs as claimed in claim 14, it is characterized in that, described brake pedal is connected with secondary master cylinder push rod by rest pin.
16. as arbitrary in claim 1-15 as described in full decoupling EHB, it is characterized in that: described full decoupling EHB also comprises the monitoring diagnosis system for the detection and diagnosis system failure; The alarm device given the alarm when being also included in the system failure with described full decoupling EHB.
17. full decoupling EHBs as claimed in claim 1, is characterized in that, when motor or straight-line motion mechanism break down, described full decoupling EHB is in the second mode of operation; When described motor or straight-line motion mechanism do not break down, described full decoupling EHB is in the first mode of operation.
18. full decoupling EHBs as claimed in claim 16, it is characterized in that, when motor and straight-line motion mechanism do not break down and hydraulic tubing leakage time, failure message is sent to electronic control unit by monitoring diagnosis system, is reported to the police by electronic control unit instruction alarm device.
19. 1 kinds of vehicles, is characterized in that, described vehicle has arbitrary described full decoupling EHB in claim 1-18.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420590018.7U CN204196887U (en) | 2014-10-13 | 2014-10-13 | Full decoupling EHB and corresponding vehicle |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420590018.7U CN204196887U (en) | 2014-10-13 | 2014-10-13 | Full decoupling EHB and corresponding vehicle |
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| CN204196887U true CN204196887U (en) | 2015-03-11 |
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| CN201420590018.7U Withdrawn - After Issue CN204196887U (en) | 2014-10-13 | 2014-10-13 | Full decoupling EHB and corresponding vehicle |
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| CN (1) | CN204196887U (en) |
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| CN104760587A (en) * | 2015-04-28 | 2015-07-08 | 清华大学 | Man-machine parallel electric brake booster system and control method thereof |
| CN105882637A (en) * | 2014-10-13 | 2016-08-24 | 陈晶杰 | Fully-decoupled electronic hydraulic braking system and corresponding vehicle |
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| CN107237793A (en) * | 2017-06-28 | 2017-10-10 | 无锡英捷汽车科技有限公司 | A kind of electrohydraulic cylinder |
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| CN105882637A (en) * | 2014-10-13 | 2016-08-24 | 陈晶杰 | Fully-decoupled electronic hydraulic braking system and corresponding vehicle |
| CN105882637B (en) * | 2014-10-13 | 2023-09-12 | 上海千顾汽车科技有限公司 | Fully decoupled electro-hydraulic brake system and corresponding vehicle |
| CN104802777B (en) * | 2015-03-20 | 2017-12-15 | 同济大学 | A kind of analog EHB of pedal sense active |
| CN104760587B (en) * | 2015-04-28 | 2017-08-11 | 清华大学 | Man-machine parallel electric braking booster system and its control method |
| CN104760587A (en) * | 2015-04-28 | 2015-07-08 | 清华大学 | Man-machine parallel electric brake booster system and control method thereof |
| CN106476777B (en) * | 2015-08-24 | 2020-04-24 | 陈晶杰 | Decoupling electronic hydraulic power-assisted braking system and braking method |
| CN106476777A (en) * | 2015-08-24 | 2017-03-08 | 陈晶杰 | Decoupling electro-hydraulic energy assisted braking system and braking method |
| CN107237793A (en) * | 2017-06-28 | 2017-10-10 | 无锡英捷汽车科技有限公司 | A kind of electrohydraulic cylinder |
| CN107662596A (en) * | 2017-09-01 | 2018-02-06 | 金勇� | Automobile electrically-controlled brakes |
| CN111016867A (en) * | 2018-10-09 | 2020-04-17 | 上海汽车集团股份有限公司 | Vehicle and braking system thereof |
| CN111391807A (en) * | 2019-01-03 | 2020-07-10 | 罗伯特·博世有限公司 | Purging method for decoupling brake system and brake system applying purging method |
| CN111391807B (en) * | 2019-01-03 | 2023-09-12 | 罗伯特·博世有限公司 | Purging method of decoupling braking system and braking system applying method |
| CN113771815A (en) * | 2021-09-06 | 2021-12-10 | 北京英创汇智科技有限公司 | Vehicle integrated electro-hydraulic braking system device |
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Assignee: DIAS AUTOMOTIVE ELECTRONIC SYSTEM Co.,Ltd. Assignor: SHANGHAI QIANGU AUTOMOTIVE TECHNOLOGY Co.,Ltd. Contract record no.: X2022310000151 Denomination of utility model: Fully decoupled electro-hydraulic brake system and corresponding vehicle Granted publication date: 20150311 License type: Common License Record date: 20221012 Assignee: SHANGHAI QINGDU AUTOMOBILE TECHNOLOGY Co.,Ltd. Assignor: SHANGHAI QIANGU AUTOMOTIVE TECHNOLOGY Co.,Ltd. Contract record no.: X2022310000150 Denomination of utility model: Fully decoupled electro-hydraulic brake system and corresponding vehicle Granted publication date: 20150311 License type: Common License Record date: 20221012 |
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