WO2015032570A1 - Verfahren zum betreiben eines elektromechanischen bremskraftverstärkers sowie ein rekuperatives bremssystem und steuervorrichtung für einen elektromechanischen bremskraftverstärker eines bremssystems - Google Patents
Verfahren zum betreiben eines elektromechanischen bremskraftverstärkers sowie ein rekuperatives bremssystem und steuervorrichtung für einen elektromechanischen bremskraftverstärker eines bremssystems Download PDFInfo
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- WO2015032570A1 WO2015032570A1 PCT/EP2014/066908 EP2014066908W WO2015032570A1 WO 2015032570 A1 WO2015032570 A1 WO 2015032570A1 EP 2014066908 W EP2014066908 W EP 2014066908W WO 2015032570 A1 WO2015032570 A1 WO 2015032570A1
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- Prior art keywords
- brake
- target
- intermediate value
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- taking
- Prior art date
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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
- B60T13/74—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 electrical assistance or drive
- B60T13/745—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 electrical assistance or drive acting on a hydraulic system, e.g. a master cylinder
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/17—Using electrical or electronic regulation means to control braking
- B60T8/172—Determining control parameters used in the regulation, e.g. by calculations involving measured or detected parameters
Definitions
- the invention relates to a method for operating an electromechanical brake
- Brake booster of a brake system and a method for operating a recuperative braking system.
- the invention relates to a control device for at least one electromechanical brake booster of a brake system.
- the invention relates to an electromechanical brake booster and a braking system for a vehicle.
- PRIOR ART FR 2 947 228 A1 discloses a braking system with an electromechanical
- the electromechanical brake booster comprises a booster housing which can be adjusted by means of an electric motor and which has a continuous receiving opening for an adjustable valve body which can be adjusted therein and can be adjusted with the booster housing.
- the valve body has a continuous central opening, within which a valve piston is adjustable by means of a transmitted thereto driver braking force with respect to the valve body.
- an input rod contact the valve piston at least temporarily.
- an output piston is also adjustable so that a present in at least one pressure chamber of a master cylinder brake pressure can be increased.
- Brake booster of a brake system with the features of claim 1, a method for operating a recuperative braking system with a
- electromechanical brake booster with the features of claim 8
- a control device for at least one electromechanical brake booster of a brake system with the features of claim 9 an electromechanical
- the invention provides several ways of ensuring an advantageous (standard) brake feel (pedal feel) to a driver during a vehicle's deceleration / pause.
- the present invention is particularly advantageously applicable to a recuperative braking system. In such a use of the present invention, despite an increase / decrease in one of a master cylinder of the recuperative
- Brake system present master cylinder pressure ensures that the driver has an advantageous (standard) brake actuation feeling (pedal feel), regardless of the occurring fluctuations of the master cylinder pressure.
- recuperative braking system such as a brake pedal, adjustable.
- at least one generator braking torque of at least one generator can be blinded without this leading to an unfamiliar brake actuation feeling (pedal feel) for the driver.
- the position of the jump point that can be felt by the driver does not change.
- the force effect on the brake actuating element that can be felt by the driver does not differ from the standard perceptible force reaction with a braking operation carried out exclusively by the frictional braking torques of the wheel brake cylinders of the recuperative braking system.
- the advantages of the present invention are explained using the example of a recuperative braking system. It is noted, however, that the Applicability of the present invention does not require the use of a brake system designed for recuperative braking.
- the present invention enables the target differential path amount to be set with respect to the target differential path between the valve piston and the valve body of the present invention
- electromechanical brake booster or with respect to a position of a
- Boost body of the electromechanical brake booster wherein separated portions as a first intermediate value and as a second intermediate value depending on the respective set / present operating point of the electromechanical
- Brake booster can be used. As detailed below, setting the first intermediate value ensures that a gap between the valve piston and a reaction disc of the electro-mechanical brake booster will close precisely at a desired entry pressure. Above all, in this way a free adjustability / applicability of the jump-in value within given physical limits, such as a
- the determination of the second intermediate value ensures a minimization of the force fluctuations on the brake actuating element (brake pedal) in the case of a volumetric blending of the at least one generator braking torque described in greater detail below.
- the setting of the desired Differenzwegmother takes place with additional consideration of a quotient of a master cylinder pressure variable with respect to a present in a master cylinder of the brake system or master brake cylinder pressure as a dividend and the virtual target brake pressure as a divisor.
- the master cylinder pressure quantity may be one in the
- Master cylinder master cylinder pressure measured, or a derived derived therefrom.
- the master brake cylinder pressure may also correspond to a desired master cylinder pressure, which for example for
- the calculation step described here for forming the quotient as a function of an operating point of the electromechanical brake booster softens the driver's brake request and a pressure set in the master brake cylinder (actual pressure) or the driver's brake request and one in the master brake cylinder to be set pressure (target pressure), ensures a particularly advantageous usability of the electromechanical brake booster.
- the target differential path size may be set as a minimum and the third intermediate value as a subtrahend.
- low-pass filtering may be performed to set the desired differential path size.
- a gradient limitation can be carried out for specifying the desired differential path variable.
- a manipulated variable limit can be executed. All of the approaches described herein may be used selectively to provide more advantageous definition of the desired differential path size.
- At least the following steps are carried out during actuation of the brake actuation element of the recuperative brake system: setting a generator braking torque executed by means of a generator of the recuperative brake system at least taking into account the actuation travel and / or the actuation strength of the actuation of the brake actuation element and corresponding activation of the generator, at least varying a Reibbremsmoments at least one wheel brake cylinder of the recuperative braking system, at least taking into account the specified
- Liquid volume at least taking into account the specified generator braking torque and corresponding driving the at least one Hydraulic device; and varying a restoring force of the brake operating member by operating the electro-mechanical brake booster.
- the method for operating the recuperative braking system can be further developed according to the above explanations of the method for operating the electromechanical brake booster.
- control device for at least one electromechanical brake booster of a brake system.
- the control device is designed, at least taking into account an actuating travel and / or an operating force of a
- control device is additionally designed to set a target Differenzwegmother with respect to a set between a valve piston and a valve body of the electromechanical brake booster setpoint differential path, at least by a first intermediate value
- Einsprungdruckmother which is a virtual target brake pressure magnitude, from which a non-actuation of the brake actuator element is closed, corresponds closed, and by a second intermediate value taking into account a second weighting relationship and a maximum of a second set of values comprising zero and a value of a difference the virtual target brake pressure magnitude as Minuend and the Einsprungdruckmother is defined as subtrahend, wherein the target Differenzwegschreib at least taking into account a sum of the first intermediate value and the second intermediate value can be determined, and wherein the
- Control device is designed to be a motor of the electromechanical
- control the brake booster such that one of the set target Differenzwegies corresponding differential travel between the valve piston and the valve body of the electromechanical brake booster is adjustable.
- the control device can also be developed in accordance with the above-described embodiments of the method for operating the electromechanical brake booster.
- control device is in addition to it
- Volume of at least one brake circuit of the brake system to determine different brake fluid volume and the at least one
- control device can thus also realize the advantages of the method for operating a recuperative brake system.
- electromechanical brake booster for a brake system comprising such a control device and a brake system for a vehicle with a corresponding control device and / or a corresponding one
- electromechanical brake booster contribute.
- the electromechanical brake booster contribute.
- Brake booster and the brake system can be further developed according to the embodiments described above.
- FIG. 1 is a block diagram for explaining an embodiment of the present invention
- Embodiments of the invention 1 is a block diagram for explaining an embodiment of the method of operating an electro-mechanical brake booster of a brake system.
- Fig. 1 The method schematically illustrated in Fig. 1 can be used to operate a variety of different types of electromechanical brake boosters.
- electromechanical brake boosters For example, all controllable or controllable electromechanical
- Brake booster can be operated by means of the reproduced in Fig. 1 method. It should be noted, however, that the feasibility of the method is not limited to this type of brake booster.
- a virtual setpoint brake pressure variable pv is determined at least taking into account an actuation travel and / or an actuation force of an actuation of a brake actuation element of the
- the virtual target brake pressure variable pv is preferably set to correspond to a (target) brake pressure which would be / would be present in a purely hydraulic braking of the brake system in accordance with the driver's brake request indicated by the actuation of the brake actuation element.
- the (target) brake pressure may be set as the virtual target brake pressure quantity pv.
- the virtual target brake pressure variable pv may also be another variable corresponding to the (target) brake pressure.
- a pedal travel, a bar travel, a driver brake force and / or a driver brake pressure for determining the virtual target brake pressure variable pv can be evaluated.
- At least taking into account the set virtual target brake pressure pv is a target Differenzweguß .DELTA.
- a target Differenzweguß .DELTA With respect to a between a valve piston and a valve body, or a Boost redesign the electromechanical
- the desired differential path to be set can be defined as the desired differential path size ⁇ .
- the BoostEffortion can Valve Body, or a Boost Body be understood.
- the valve piston is preferably understood to mean a component which is adjustably arranged in a central opening of the valve body and via which a driver braking force can be transmitted from the brake actuating element to at least one adjustable piston of a master brake cylinder of the brake system.
- the determination of the set differential path size ⁇ at least taking into account the set virtual target brake pressure variable pv is done by setting a first intermediate value x1 taking into account a first weighting relation a1 and a minimum min from a first set of values.
- the first set of values includes the virtual target brake pressure quantity pv and an injection pressure magnitude pO.
- Inrush pressure-sized pO is a quantity to be understood that corresponds to a virtual target brake pressure quantity pv, from a soft to a non-actuation of the
- Brake actuator element is closed gap. Frequently, when the brake actuating element is not actuated, there is a gap between a reaction disk of the electromechanical brake booster and the valve piston.
- the inrush pressure magnitude pO may thus correspond to a desired brake pressure which exists in a purely hydraulic braking at the time at which the actuation of the brake actuator causes the gap to close, while previously transmitting the driver brake force to the at least one adjustable piston the master cylinder due to the non-closed
- the entry pressure size pO may be a pressure value or a corresponding size.
- the entry pressure-large pO usually corresponds to the jump-in area of the electromechanical brake booster and is often described as the entry point or as (desired) Einsprungdruckgrenzwert.
- the intrusion pressure pO can be determined by the mechanics of the
- electromechanical brake booster specified or adjusted by programming its electronics.
- the virtual target brake pressure quantity pv is supplied to a block 10, by which the minimum min is determined from the first set of values.
- the entry pressure-size pO may for example be stored on a non-illustrated storage unit.
- the minimum is fed to a block 12 in which the first intermediate value x1 is calculated as the product of the minimum min and the first weighting relation a1.
- a second intermediate value x2 is determined taking into account a second weighting relation a2 and a maximum max from a second set of values.
- the second set of values includes the number 0 and a value of a difference d1.
- the difference d1 is calculated in a block 14 with the virtual target brake pressure quantity pv as Minuend and the Einsprung horrgroep pO as subtrahend.
- the difference d1 is fed to a block 16 which determines the maximum max from the second set of values.
- a product of the maximum max and the second weighting relation a2 is calculated as the second intermediate value x2.
- the first weighting relation a1 and / or the second weighting relation a2 can either each be a weighting factor, at least two factors or a characteristic curve.
- the first weighting factor a1 preferably corresponds to a quotient of a gap that is actually structurally present in the unconfirmed state of the electromechanical brake booster and a desired one
- the method of FIG. 1 thus realizes an at least two-factorial one
- a multifactorial pedal force compensation can also be performed.
- blocks 10 and 16 it is identified whether the virtual target brake pressure quantity pv is smaller or larger than the injection pressure-magnitude pO (to be set / predetermined).
- the first intermediate value x1 closes the gap exactly at the specified one
- the second mean x2 can be a
- the desired difference path size ⁇ is set at least taking into account a sum sum from the first intermediate value x1 and the second intermediate value x2.
- the intermediate values x1 and x2 can be supplied to a block 20 for summation.
- This can also be described as an addition of offset setpoint values for a desired position of the valve body / booster body.
- the setting of the desired Differenzweguß ⁇ is carried out with additional consideration of a (current) master cylinder pressure pa with respect to a present in the master cylinder of the brake system or to be set
- the master brake cylinder pressure pa may thus be either a magnitude with respect to an actual pressure in the master cylinder or with respect to a target pressure desired in the master cylinder.
- a pressure value or a corresponding variable can be used as master brake cylinder pressure variable pa.
- the setting of the nominal difference path size ⁇ is preferred with additional consideration of a quotient, which is derived with the
- a third intermediate value x3 is calculated in the method of FIG. 1 for specifying the nominal differential path size ⁇ .
- the third intermediate value x3 is a product of the sum sum (from the first intermediate value x1 and the second
- the third intermediate value x3 is taken into account when specifying the desired Differenzweguß ⁇ .
- a reciprocal k of the virtual target brake pressure variable pv is determined in a block 22.
- the reciprocal k is multiplied by the sum sum by means of a block 24.
- the product p thus formed is supplied together with the master cylinder pressure quantity pa to a block 26, which obtains the third intermediate value x3 by multiplying the product p by the number
- the setpoint differential path quantity ⁇ is determined taking into account a value of a difference d2 with the sum sum (from the first intermediate value x1 and the second intermediate value x2) as the minuend and the third intermediate value x3 as the subtrahend.
- electromechanical brake booster so controlled that one of the set target Differenzwegaise corresponding target differential path between the valve piston and the valve body, or the Boost stressess of the electromechanical
- Brake booster is set.
- This procedure is a variety of
- Control options can be used. It is therefore not discussed in more detail.
- the present in at least one wheel brake cylinder of the brake system regardless of a position / actuation of the brake operating member, in particular on
- recuperative braking system equipped with an electromechanical brake booster can also be used to carry out the method described below. Below are some
- recuperative braking system used to carry out the method is not limited to being equipped with precisely these brake system components.
- recuperative brake system suitable for carrying out the method is neither limited to a specific design of its brake circuits, nor are there any obstacles to the integration of a plurality of further brake system components.
- Fig. 2a shows a desired relation r1 between a restoring force Fr of a
- Brake operation member e.g., a brake pedal
- the output force Fout which results from the driver braking force and an engine power of an engine of the electromechanical brake booster, is transmitted to at least one adjustable piston of a master brake cylinder of the recuperative braking system and causes a corresponding
- Coordinate system of Fig. 2a is an abscissa the restoring force Fr and an ordinate the output force Fout.
- Fig. 2b illustrates a second set relation r2 between an input rod path sA (as an example of a brake operation path) and the restoring force Fr, wherein a
- drivers are used to being (almost) powerless
- Reaction disc bulges out due to the pressure load on a side facing the input rod. Only at an entry point P1, the gap is closed, so that in a further actuation of the brake actuator, the driver brake force to increase the brake pressure on the at least one adjustable piston of the master cylinder is transferable. Therefore, in a linear amplification area A3 adjoining the entry point P1, there is a constant relationship between the restoring force Fr and the output force Fout. Above a modulation point P2, an increase in the driver braking force can not be accompanied by an increase in the engine power of the engine, so that any further increase in the output force Fout on the at least one adjustable piston must be provided as a driver braking force. Above the Ausmatitigs P2 thus increases the restoring force Fr with a relatively large slope.
- a generator which is embodied by means of a generator of the recuperative brake system, is actuated.
- a setting of the generator braking torque is at least taking into account the actuation path and / or the operating force of
- the generator is driven so that a deceleration of the corresponding generator braking torque is performed so that the vehicle decelerates.
- the deceleration of the vehicle can be used to charge a vehicle battery.
- At least one friction braking torque of the at least one wheel brake cylinder of the recuperative braking system is varied at least taking into account the specified generator braking torque so that the driver's braking request is not / hardly exceeded.
- At least one hydraulic device is actuated in such a way that a brake fluid volume corresponding to the desired value is displaced between the at least one storage volume and the out-of-memory volume.
- an electromotive-driven volume Verblendaktuator in particular a plunger, and / or a capable of volume absorption and volume delivery ESP device can be used.
- brake fluid can be sucked into at least one actuator-own storage volume, in an external storage volume and / or in a brake fluid reservoir when needed and pushed out again.
- the volume facing actuator may be formed with either a self-locking gear or a high-efficiency gearbox.
- an increase in the generator braking torque eg, at the beginning of the actuation of the brake actuating element
- the volume displaced by the driver from the master brake cylinder to the wheel brake cylinders during a slow actuation of the brake actuation element can be displaced immediately into the at least one storage volume.
- Input rod path sA is rewritable.
- a situation occurs in which the generator is deactivated during a braking operation and the vehicle is only further slowed down by means of the at least one wheel brake cylinder of the recuperative braking system.
- a phase At1 of the regenerative deceleration of the vehicle is terminated from a limit input rod path sO, and a phase At2 of the purely friction brake-based braking is started.
- the time decrease of the generator braking torque can be compensated by the at least one friction braking torque by a
- Storage volume is increased in the non-memory volume. This causes an example relation f2 which below the limit input bar path s0 corresponds to the example relation f1 and lies above the limit input bar path s0 on the second set relation r2.
- a one-factorial pedal force compensation is a proportional to the deviation between the desired value and actual value of the at least one friction braking torque compensation factor for an offset movement of the
- Brake booster according to the procedure of FIG. 1 executed.
- the method thus realizes at least a two-factorial pedal force compensation according to the procedure described above.
- two-factorial pedal force compensation according to the procedure described above.
- Pedal force compensation can also be carried out a multifactorial pedal force compensation.
- FIG. 2f The effect of the at least two-factorial pedal force compensation is shown in FIG. 2f, wherein the realized actual relation r3 lies on the second desired relation r2.
- Brake actuation feeling / haptic feedback (brake characteristic).
- a pedal force / actuation path course does not change. This advantage is ensured, although the driver during the operation of the brake actuator on the
- the shape of the entry point transition in the pedal force / actuation path course can be easily and reliably influenced by software parameterization.
- a control device for at least electromechanical brake booster for at least electromechanical brake booster.
- an electromechanical brake booster for a brake system comprising such a control device, and a brake system for a vehicle with a corresponding control device and / or a corresponding electromechanical
- Brake booster ensure the advantages described above.
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- Braking Systems And Boosters (AREA)
Abstract
Description
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Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
MX2016002869A MX2016002869A (es) | 2013-09-04 | 2014-08-06 | Metodo para operar un amplificador de freno electromecanico, sistema de frenado recuperativo y dispositivo de control para un amplificador de freno electromecanico de sistema de frenado. |
PL416597A PL230542B1 (pl) | 2013-09-04 | 2014-08-06 | Sposob pracy elektromechanicznego wzmacniacza sily hamowania systemu hamowania, sposob pracy rekuperacyjnego systemu hamowania, urzadzenie sterujace dla przynajmniej jednego elektromechanicznego wzmacniacza sily hamowania systemu hamowania, elektromechaniczny wzmacniacz sily hamowania oraz system hamowania |
US14/914,715 US9676379B2 (en) | 2013-09-04 | 2014-08-06 | Method for operating an electromechanical brake booster, recuperative braking system, and control device for an electromechanical brake booster of a braking system |
CN201480048623.4A CN105492273B (zh) | 2013-09-04 | 2014-08-06 | 用于运行机电的制动助力器的方法以及再生制动系统和用于制动系统的机电的制动助力器的控制设备 |
JP2016537200A JP6280221B2 (ja) | 2013-09-04 | 2014-08-06 | 電気機械式のブレーキ倍力装置を運転するための方法、並びに回生ブレーキシステム、およびブレーキシステムの電気機械式のブレーキ倍力装置のための制御装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013217579.5 | 2013-09-04 | ||
DE102013217579.5A DE102013217579A1 (de) | 2013-09-04 | 2013-09-04 | Verfahren zum Betreiben eines elektromechanischen Bremskraftverstärkers eines Bremssystems, Verfahren zum Betreiben eines rekuperativen Bremssystems und Steuervorrichtung für zumindest einen elektromechanischen Bremskraftverstärker eines Bremssystems |
Publications (1)
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WO2015032570A1 true WO2015032570A1 (de) | 2015-03-12 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/EP2014/066908 WO2015032570A1 (de) | 2013-09-04 | 2014-08-06 | Verfahren zum betreiben eines elektromechanischen bremskraftverstärkers sowie ein rekuperatives bremssystem und steuervorrichtung für einen elektromechanischen bremskraftverstärker eines bremssystems |
Country Status (7)
Country | Link |
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US (1) | US9676379B2 (de) |
JP (1) | JP6280221B2 (de) |
CN (1) | CN105492273B (de) |
DE (1) | DE102013217579A1 (de) |
MX (1) | MX2016002869A (de) |
PL (1) | PL230542B1 (de) |
WO (1) | WO2015032570A1 (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016210369A1 (de) | 2015-07-21 | 2017-01-26 | Volkswagen Aktiengesellschaft | Elektromechanischer Bremskraftverstärker |
JP6508346B2 (ja) * | 2015-09-16 | 2019-05-08 | 三菱自動車工業株式会社 | 回生ブレーキ制御装置 |
DE102016215698A1 (de) * | 2016-08-22 | 2018-02-22 | Robert Bosch Gmbh | Steuervorrichtung und Verfahren zum Betreiben eines elektromechanischen Bremskraftverstärkers eines zur Ausführung von Antiblockierregelungen ausgelegten Bremssystems |
US11535211B2 (en) * | 2017-12-31 | 2022-12-27 | ZF Active Safety US Inc. | Vehicle brake system and method of detecting piston location of a plunger assembly |
CN111002966B (zh) * | 2019-12-24 | 2021-06-04 | 精诚工科汽车系统有限公司 | 车辆制动控制方法、装置及线控助力制动系统 |
CN111923883B (zh) * | 2020-07-15 | 2022-11-11 | 中国第一汽车股份有限公司 | 一种考虑主动制动功能的制动系统匹配分析方法和系统 |
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US6019440A (en) | 1996-04-03 | 2000-02-01 | Itt Manufacturing Enterprises Inc. | Process and device for regulating a power brake variable boosting factor |
DE59902552D1 (de) * | 1998-01-31 | 2002-10-10 | Continental Teves Ag & Co Ohg | Bremskraftübersetzungsvorrichtung, insbesondere für kraftfahrzeuge |
JP2001063540A (ja) * | 1999-09-01 | 2001-03-13 | Denso Corp | 車両制動装置及び車両制動方法 |
DE102010001037A1 (de) * | 2009-04-20 | 2010-10-21 | Robert Bosch Gmbh | Bremskraftverstärkersystem für ein Bremssystem eines Fahrzeugs und Verfahren zum Betreiben eines Bremssystems eines Fahrzeugs |
FR2947228B1 (fr) | 2009-06-25 | 2012-11-30 | Bosch Gmbh Robert | Systeme de freins a servofrein electrique |
DE102011003144A1 (de) * | 2011-01-26 | 2012-07-26 | Robert Bosch Gmbh | Steuervorrichtung für ein Bremssystem eines Fahrzeugs, Bremssystem und Verfahren zum Betreiben eines Bremssystems für ein Fahrzeug |
DE102011088942A1 (de) | 2011-12-19 | 2013-06-20 | Robert Bosch Gmbh | Verfahren zum Betreiben eines rekuperativen Bremssystems eines Fahrzeugs und Steuervorrichtung für ein rekuperatives Bremssystem |
FR2989658A1 (fr) | 2012-04-23 | 2013-10-25 | Peugeot Citroen Automobiles Sa | Dispositif de gestion des systemes de freinage dissipatif et recuperatif d'un vehicule a moteur, par prise en compte du couple de jeux de liaison mecanique |
DE102012215138A1 (de) | 2012-08-27 | 2014-02-27 | Robert Bosch Gmbh | Steuervorrichtung für ein rekuperatives Bremssystem und Verfahren zum Betreiben eines rekuperativen Bremssystems |
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2013
- 2013-09-04 DE DE102013217579.5A patent/DE102013217579A1/de active Pending
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2014
- 2014-08-06 MX MX2016002869A patent/MX2016002869A/es active IP Right Grant
- 2014-08-06 WO PCT/EP2014/066908 patent/WO2015032570A1/de active Application Filing
- 2014-08-06 US US14/914,715 patent/US9676379B2/en active Active
- 2014-08-06 JP JP2016537200A patent/JP6280221B2/ja active Active
- 2014-08-06 CN CN201480048623.4A patent/CN105492273B/zh active Active
- 2014-08-06 PL PL416597A patent/PL230542B1/pl unknown
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5505526A (en) * | 1992-05-26 | 1996-04-09 | Lucas Industries Public Limited Company | Adjusting actual brake pressure to match stored pressure values associated with a brake pedal position |
EP1081005A2 (de) * | 1999-09-01 | 2001-03-07 | Denso Corporation | Kaftfahrzeugbremsvorrichtung und Kraftfahrzeugbremsverfahren |
EP2631128A1 (de) * | 2010-10-20 | 2013-08-28 | Nissan Motor Co., Ltd | Bremskraftsteuervorrichtung für fahrzeuge |
Also Published As
Publication number | Publication date |
---|---|
CN105492273A (zh) | 2016-04-13 |
US20160207515A1 (en) | 2016-07-21 |
MX2016002869A (es) | 2016-06-22 |
JP2016529157A (ja) | 2016-09-23 |
US9676379B2 (en) | 2017-06-13 |
DE102013217579A1 (de) | 2015-03-05 |
CN105492273B (zh) | 2018-04-24 |
PL230542B1 (pl) | 2018-11-30 |
JP6280221B2 (ja) | 2018-02-14 |
PL416597A1 (pl) | 2016-08-16 |
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