WO2011099277A1 - 電動倍力装置およびこれを用いたブレーキ装置 - Google Patents
電動倍力装置およびこれを用いたブレーキ装置 Download PDFInfo
- Publication number
- WO2011099277A1 WO2011099277A1 PCT/JP2011/000717 JP2011000717W WO2011099277A1 WO 2011099277 A1 WO2011099277 A1 WO 2011099277A1 JP 2011000717 W JP2011000717 W JP 2011000717W WO 2011099277 A1 WO2011099277 A1 WO 2011099277A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- power piston
- input
- electric booster
- brake
- relative displacement
- Prior art date
Links
Images
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
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01D—MEASURING NOT SPECIALLY ADAPTED FOR A SPECIFIC VARIABLE; ARRANGEMENTS FOR MEASURING TWO OR MORE VARIABLES NOT COVERED IN A SINGLE OTHER SUBCLASS; TARIFF METERING APPARATUS; MEASURING OR TESTING NOT OTHERWISE PROVIDED FOR
- G01D5/00—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable
- G01D5/12—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable using electric or magnetic means
- G01D5/14—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable using electric or magnetic means influencing the magnitude of a current or voltage
- G01D5/142—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable using electric or magnetic means influencing the magnitude of a current or voltage using Hall-effect devices
- G01D5/145—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable using electric or magnetic means influencing the magnitude of a current or voltage using Hall-effect devices influenced by the relative movement between the Hall device and magnetic fields
Definitions
- the present invention relates to the technical field of an electric booster that boosts and outputs an input with a predetermined servo ratio using electric power, and the technical field of a brake device that uses this electric booster.
- a brake booster that uses power to boost and output an input at a predetermined servo ratio is used.
- This brake booster boosts and outputs an input based on the pedal effort. Then, by operating the master cylinder with the output of the brake booster, a large braking force can be obtained with a small pedal effort.
- Patent Document 1 an electric booster using electric power has been proposed (see, for example, Patent Document 1).
- the electric booster described in Patent Document 1 when the brake pedal is depressed, the electric motor is driven and the driving force of the electric motor rotates the rotating member via the gear power transmission mechanism. At this time, the rotating member rotates according to the pedal stroke. The rotation of the rotating member advances the screw shaft by the ball screw mechanism and advances the input piston.
- the power piston is actuated by the advance of the input piston, and the electric booster boosts and outputs the input by the servo ratio based on the pedal depression force.
- the piston of the master cylinder integrated with the power piston is actuated by the output of the electric booster, and the master cylinder generates brake fluid pressure. And a brake cylinder act
- the brake booster is provided with a jump-in characteristic (also called a jumping characteristic).
- a jump-in characteristic in the input / output characteristic of the brake booster, there is no increase in input until a predetermined output is reached, and when the predetermined output is reached, the input increases as the output increases. At this time, it is a characteristic that an output increase occurs in which the input increase is boosted by the servo ratio.
- the jump-in characteristic is exhibited in the initial operation.
- the electric booster mechanically exhibits jump-in characteristics without relying on control software.
- This conventional electric booster includes a first split element that connects the input piston to the input pedal, and a second split that is connected to the piston of the master cylinder and moves relative to the first split element. It has a dividing element and spring means arranged between these first and second dividing elements.
- the present invention has been made in view of such circumstances, and an object of the present invention is to provide an electric booster capable of mechanically exhibiting both jump-in characteristics and hysteresis characteristics without relying on control software. It is to provide a brake device used.
- an electric booster includes an input shaft to which an input is applied, an input receiving member that receives an input from the input shaft, a power piston, and a power that supports the power piston.
- a motor an output shaft that is output by the operation of the power piston, and a reaction force member that is formed of a viscoelastic material and to which a reaction force from the output shaft is applied, and when the input receiving member is not operated It is spaced apart from the reaction force member with a predetermined gap, and is arranged so as to be able to contact the reaction force member during operation when a predetermined input is applied. It is characterized in that.
- the electric motor includes a stator to which a current based on the relative displacement detected by the relative displacement detection unit is supplied, and the stator is rotated by the stator and the relative power to the power piston. And a roller for applying a driving force based on the displacement.
- the electric booster of the present invention is characterized in that the relative displacement detecting means includes a magnetic sensor and a magnet.
- the electric booster according to the present invention is characterized in that the magnetic sensor is disposed on the power piston support member and the magnet is disposed on the input receiving member. Furthermore, the electric booster of the present invention is characterized in that the reaction force member is a reaction disk formed of rubber.
- the brake device of the present invention includes a brake operation member that performs a brake operation, an electric booster that generates an output in which an input from the brake operation member is boosted at a predetermined servo ratio, and the electric booster.
- a master cylinder that generates brake pressure and a brake cylinder that operates with the brake pressure from the master cylinder, and the electric booster is any one of the electric boosters of the present invention described above. It is characterized by being one.
- a propulsive force is applied to the power piston by the rotation of the electric motor to operate the power piston, and the input is performed at a predetermined servo ratio by the operation of the power piston.
- a boosted output is generated through the output shaft.
- the reaction force accompanying this output is transmitted from the output shaft to the reaction force member formed of a viscoelastic material.
- the input receiving member that receives the input is separated from the reaction force member with a predetermined gap when the input is not operated, and is brought into contact with the reaction force member when the predetermined input is applied.
- both the jump-in characteristic based on a predetermined gap between the input receiving member and the reaction force member and the hysteresis characteristic based on the viscoelasticity of the reaction force member can be mechanically exhibited without relying on control software.
- a booster can be realized.
- the relative displacement between the input receiving member and the power piston support member that supports the power piston is detected by the relative displacement detection means, and the electric piston is based on the relative displacement detected by the relative displacement detection means. Actuate.
- position a relative displacement detection means integrally in an electric booster Therefore, the number of parts can be reduced, and the installation space for the relative displacement detection means need not be specially provided outside the electric booster. As a result, the installation space for the electric booster can be further reduced, and the degree of freedom in installation can be increased.
- the operation of the electric motor is controlled based on the relative displacement between the power piston support member and the input receiving member detected by the relative displacement detection means, the operation of the electric booster can be controlled with higher accuracy. It becomes possible.
- the relative displacement detection means includes a magnet disposed on the input receiving member and a magnetic sensor disposed on the power piston support member and outputting based on the magnetic field of the magnet, thereby detecting relative displacement. It is possible to simplify the configuration of the means. Furthermore, by using a reaction disk in which the reaction member is made of rubber, the structure of the reaction member can be further simplified.
- the brake device using the electric booster of the present invention since the electric booster of the present invention is used, the installation space of the brake device can be further reduced and the degree of freedom of installation can be increased. At the same time, the brake control can be performed with higher accuracy.
- FIG. 1 It is a figure showing typically a brake device provided with an example of an embodiment of an electric booster concerning the present invention. It is a longitudinal cross-sectional view of the electric booster of this example. It is an input-output characteristic diagram of the electric booster of this example.
- FIG. 1 is a diagram schematically showing a brake device including an example of an embodiment of an electric booster according to the present invention.
- the brake device 1 of this example is basically the same as a conventionally known two-system brake device. That is, the brake device 1 includes a brake pedal 2, an electric booster 3, a tandem master cylinder 4, a reservoir tank 5, and a brake cylinder 6.
- the electric booster 3 of this example includes a front housing 7 and a rear housing 8 that are connected to each other.
- An electric motor 9 is disposed in the front housing 7.
- the electric motor 9 is provided with a stator 10 which is an annular magnetic force generation member made of a coil fixedly supported by the front housing 7, and is disposed on the inner periphery of the stator 10 so as to be relatively rotatable by the magnetic force of the stator 10.
- the rotor 11 is a cylindrical rotating member. The outer peripheral surfaces of both end portions in the axial direction of the rotor 11 are rotatably supported by the front housing 7 via a pair of bearings 12 and 13.
- the rotor 11 is supported between the front housing 7 and the rear housing 8 so as not to move in the axial direction (left-right direction in FIG. 2).
- a power source is connected to the stator 10 via a current control device, and the current control device is connected to an electronic control device of the brake device 1.
- a power piston 14 is disposed so as not to rotate relative to the rotor 11, and to allow relative linear movement in the axial direction.
- a ball screw mechanism 15 is disposed between the inner peripheral surface of the rotor 11 and the outer peripheral surface of the power piston 14.
- the ball screw mechanism 15 is a conventionally known ball screw mechanism, and includes a rotor side screw groove 16 formed on the inner peripheral surface of the rotor 11, a power piston side screw groove 17 formed on the outer peripheral surface of the power piston 14, and A predetermined number of balls 18 are provided between the rotor side thread groove 16 and the power piston side thread groove 17 so as to be able to roll.
- the power piston 14 is supported by a cylindrical power piston support member 19.
- the power piston 14 has an annular flange 14a projecting inwardly positioned in the radial direction (centering) with an annular flange 19a projecting outward of the power piston support member 19 so as to be separable in the axial direction.
- the power piston is supported by the power piston support member 19.
- the power piston support member 19 is disposed through the rear housing 8 and supported by the rear housing 8 via a bearing 20 so as to be linearly slidable.
- An input receiving member 21 is fitted in the inner peripheral hole of the power piston support member 19 so as to be linearly slidable relative to the power piston support member 19.
- An input shaft 22 is coupled to the input receiving member 21 so as to be capable of relative swinging, and the input shaft 22 is coupled to a pedal lever 2a of the brake pedal 2 so as to be capable of relative swinging as shown in FIG. .
- the output shaft 23 is fitted in the inner peripheral hole of the power piston support member 19 on the side opposite to the input shaft 22 so as to be linearly slidable.
- the output shaft 23 moves forward (leftward in FIG. 2) by the output of the power piston 14 to operate the primary piston 4a of the tandem master cylinder 4.
- a reaction disk 24 which is a reaction force member made of a viscoelastic material such as rubber, is disposed.
- a spacing member 25 is disposed in an inner peripheral hole of the power piston support member 19 between the input receiving member 21 and the reaction disk 24 so as to be linearly slidable relative to the power piston support member 19. Yes.
- the spacing member 25 is connected to the input receiving member 21 so as to move integrally with the input receiving member 21 and faces the reaction disk 24.
- a key member 26 is disposed between the power piston support member 19 and the input receiving member 21.
- the key member 26 penetrates the radial hole of the power piston support member 19 and enters the annular groove of the input receiving member 21.
- the key member 26 abuts against the rear housing 8 and is prevented from moving backward.
- the key member 26 thus prevented from retreating defines the retreat limit position (non-operation position) of the power piston support member 19 and the input receiving member 21.
- a predetermined gap ⁇ is set between the reaction disk 24 and the spacing member 25. That is, the gap ⁇ is adjusted by the spacing member 25.
- a relative displacement detection sensor 27 is disposed between the power piston support member 19 and the input receiving member 21.
- the relative displacement detection sensor 27 includes a magnetic sensor 28 such as a Hall element provided integrally with the power piston support member 19 and a magnet 29 provided integrally with the input receiving member 21.
- the magnetic sensor 28 is connected to the aforementioned electronic control device.
- the relative displacement detection sensor 27 detects the relative displacement of the input receiving member 21 (that is, the input shaft 22) with respect to the power piston support member 19.
- the magnet 29 moves relative to the magnetic sensor 28 due to the relative displacement of the input receiving member 21 with respect to the power piston support member 19, so that the magnetic sensor 28 has a current corresponding to the fluctuation of the magnetic field from the magnet 29, That is, a current corresponding to the relative displacement of the input receiving member 21 with respect to the power piston support member 19 is output to the electronic control unit. Therefore, the electronic control unit determines the relative displacement of the input receiving member 21 with respect to the power piston support member 19 based on the magnitude of the current input from the magnetic sensor 28.
- the power piston support member 19, the input receiving member 21, the reaction disk 24, the spacing member 25, the key member 26, and the gap ⁇ are respectively in a conventionally known negative pressure booster described in, for example, Japanese Patent No. 2606909. Corresponds to valve body, valve plunger, reaction disk, spacing member, key member, and gap. Therefore, referring to the description of Japanese Patent No. 2606909, these functions and operations can be easily understood, and thus detailed description thereof will be omitted. In that case, since the electric booster 3 does not use fluid as power, the power piston support member 19 and the input receiving member 21 both supply and discharge fluid by the valve body and the valve plunger described in Japanese Patent No. 2606909. Therefore, it does not correspond to a point that does not have a control valve function.
- a return spring 30 is contracted between the front housing 7 and the power piston support member 19.
- the return spring 30 always urges the power piston support member 19 in the non-operating direction.
- the annular flange 19a of the power piston support member 19 is always engaged with the annular flange 14a of the power piston 14 in the axial direction.
- a return spring 31 is contracted between the power piston support member 19 and the input shaft 22. The return spring 31 always urges the input shaft 22 against the power piston support member 19 in the non-operating direction.
- the electric booster 3 of this example will be described. First, the electric booster 3 when the brake is not operated will be described. In the non-operating state of the electric booster 3 in which the brake pedal 2 is not depressed, the power piston support member 19 and the input receiving member 21 are moved backward (rightward in FIG. 2) by the respective return springs 30 and 31 as shown in FIG. The key member 26 that is biased toward the rear housing 8 is brought into the non-operating position in the backward limit. In this case, the relative displacement of the input receiving member 21 with respect to the power piston support member 19 is defined as 0 when the electric booster 3 is not operated. In the electronic control unit, the current of the magnetic sensor 28 generated by the magnetic field of the magnet 19 is set to 0 as a reference value. Therefore, the electronic control unit controls the current control unit and does not supply power (current) from the power source to the stator 10.
- the stator 10 rotates the rotor 11 by the supplied current.
- a leftward propulsive force in FIG. 2 is applied to the power piston 14 via the ball screw mechanism 15, and the power piston 14 advances to the left.
- the rotation of the rotor 11 in the direction in which the power piston 14 moves forward is defined as forward rotation
- the rotation of the rotor 11 in the direction in which the power piston 14 moves backward to the right is defined as reverse rotation.
- the output shaft 23 advances together with the power piston support member 19 and the reaction disk 24.
- the hydraulic pressure of the tandem master cylinder 4 is transmitted to the output shaft 23 via the primary piston 4a, and the output shaft 23 presses the reaction disk 24 rearward with a reaction force corresponding to the hydraulic pressure.
- the reaction disk 24 is elastically deformed, it expands toward the spacing member 25 side.
- the spacing member 25 also advances and the gap ⁇ decreases, but the spacing member 25 does not contact the reaction disk 24 until the clearance ⁇ disappears. Therefore, as shown in FIG. 3, even if the output of the electric booster 3 increases, the input remains Fi 0 and does not increase.
- each brake cylinder 6 when the brake fluid pressure rises as the output of the electric booster 3 rises, each brake cylinder 6 generates a braking force, the brake is activated, and each wheel 32 is braked.
- the gap ⁇ disappears due to the expansion of the reaction disk 24, and the reaction disk 24 abuts against the spacing member 25 to press the spacing member 25 backward. That is, the jump-in characteristic (jumping characteristic) of the output Fo 0 is obtained at the input Fi 0 .
- the pressing force of the spacing member 25 is transmitted as a reaction force to the brake pedal 2 via the input receiving member 21 and the input shaft 22. That is, the reaction force corresponding to the braking force is transmitted to the brake pedal 2 when the brake is operated, and the driver recognizes the braking operation by the braking force corresponding to the pedal depression force.
- the electronic control unit controls the current control unit to gradually reduce the supply current to the stator 10.
- the return spring 30 contracts and the spring force increases so as to resist the advance of the power piston support member 19.
- the advance of the power piston support member 19 That is, the advance of the power piston 14 stops.
- the relative displacement between the input receiving member 21 and the power piston support member 19 is kept constant, and the current supplied to the stator 10 is kept constant. Therefore, the rotor 11 of the electric motor 9 continues to apply a driving force to the power piston 14 so as not to retract the power piston 14. Thereby, even if the piston support member 19 and the power piston 14 are urged rearward by the spring force of the return spring 30 and the reaction force from the output shaft 23, they are held at this stop position.
- the electric booster 3 includes an intermediate load region that generates the output Fo obtained by boosting the input Fi with a predetermined servo ratio.
- the output Fo of the electric booster 3 increases linearly along the input / output characteristic line ⁇ having a predetermined servo ratio as a gradient with respect to the increase of the input Fi.
- the ratio of the case, predetermined servo ratio, the pressure receiving area S 2 cm 2 (not shown) between the output shaft 23 and the reaction disc 24 against the pressure receiving area S 1 cm 2 (not shown) between the reaction disc 24 and the spacing member 25 It is given by (S 2 / S 1 ). Then, the braking force increases in relation to the output Fo of the electric booster 3 in which the pedal depression force is boosted.
- the output of the electric motor 9 decreases as the current applied to the stator 10 decreases. At this time, the reaction disk 24 and the spacing member 25 are kept in contact with each other. Then, the output Fo of the electric booster 3 decreases as the output of the electric motor 9 decreases, and the power piston 14 moves backward. That is, the electric booster 3 becomes an intermediate load region. Therefore, as indicated by the dotted line in FIG. 3, the output Fo of the electric booster 3 is input / output with the same servo ratio gradient (that is, the same gradient as the input / output characteristic line ⁇ ) with respect to the decrease of the input Fi. Decrease with characteristic line ⁇ . When the decrease of the input Fi is stopped in the intermediate load state, the output Fo of the electric booster 3 becomes a value on the input / output characteristic line ⁇ corresponding to the value of the input Fi at that time.
- the output Fo of the electric booster 3 is immediately after the input Fi decreases. It does not decrease and becomes constant. Then, when the input Fi becomes the input Fi 3 at the point P where the input / output characteristic line ⁇ intersects, the output Fo of the electric booster 3 is the input / output characteristic with respect to the decrease of the input Fi thereafter. After decreasing along the straight line ⁇ and jumping out, it becomes zero.
- the input / output characteristic of the electric booster 1 of this example has a hysteresis in which the output Fo when the operation of the electric booster 1 is released is larger than the output Fo during the operation for the same input.
- the input / output characteristics of the electric booster 1 have hysteresis, the feeling of the brake is improved.
- the electric booster 3 is actuated by the propulsion force applied to the power piston 14 by the rotation of the electric motor 9, and the power piston 14 is operated.
- An output Fo in which Fi is boosted at a predetermined servo ratio is generated through the output shaft 23.
- the reaction force accompanying the output Fo is transmitted from the output shaft 23 to the reaction disk 24 formed of a viscoelastic material.
- the spacing member 25 connected to the input receiving member 21 that receives the input Fi is spaced apart from the reaction disk 24 with a predetermined gap ⁇ when not operating, and the reaction is performed when operating with a predetermined output Fo 0. Abutted against the disk 24.
- both the jump-in characteristic based on the predetermined gap ⁇ between the spacing member 25 and the reaction disk 24 and the hysteresis characteristic based on the viscoelasticity of the reaction disk 24 can be mechanically exhibited without depending on the control software.
- the electric booster 3 can be realized.
- the relative displacement between the input receiving member 21 and the power piston support member 19 that supports the power piston 14 is detected by the relative displacement detection sensor 27, and the electric motor 9 is detected by the relative displacement detection sensor 27.
- the power piston 14 is operated based on the displacement.
- the relative displacement detection sensor 27 can be integrally disposed in the electric booster 3. Therefore, the number of parts can be reduced, and it is not necessary to provide a special installation space for the relative displacement detection sensor 27 outside the electric booster 3. As a result, the installation space for the electric booster 3 can be further reduced, and the degree of freedom in installation can be increased.
- the relative displacement detection sensor 27 has a magnet 29 disposed on the input receiving member 21 and a magnetic sensor 28 disposed on the power piston support member 19 and outputting based on the magnetic field of the magnet 29.
- the configuration of the relative displacement detection sensor 27 can be further simplified.
- the reaction disk 23 made of rubber as the reaction force member, the structure of the reaction force member can be further simplified.
- the brake device 1 of this example since the electric booster 3 of the present invention is used, the installation space of the brake device 1 can be further reduced, the degree of installation freedom can be increased, and the brake control can be performed. Can be performed with higher accuracy.
- the present invention is not limited to the example of the above-described embodiment.
- the relative displacement between the power piston support member 19 and the input receiving member 21 based on the decrease in input is caused when the power piston 14 is retracted by releasing the operation of the electric booster 3 or decreasing the input.
- the supply of the corresponding current to the stator 10 is also reduced, but the supply of current to the stator 10 is maintained.
- the electric booster 3 of the present invention when the power piston 14 is retracted, the current supply to the stator 10 is stopped, or the current is supplied to the stator so that the rotor 11 rotates in the reverse direction. it can.
- the spacing member 25 is not always necessary and may be omitted, and a predetermined gap ⁇ may be set between the input receiving member 21 and the reaction disk 24.
- the present invention can be modified in various ways within the scope of the matters described in the claims.
- the electric booster according to the present invention can be suitably used for an electric booster that uses electric power to boost and output an input at a predetermined servo ratio.
- the brake device according to the present invention can be suitably used for a brake device that brakes a wheel using an electric booster.
Abstract
Description
更に、本発明の電動倍力装置は、前記相対変位検出手段は磁気センサーとマグネットとを有することを特徴としている。
更に、本発明の電動倍力装置は、前記反力部材がゴムから形成されたリアクションディスクであることを特徴としている。
更に、反力部材がゴムで形成されたリアクションディスクとすることで、反力部材の構成がより一層簡単にできる。
図1は、本発明に係る電動倍力装置の実施の形態の一例を備えるブレーキ装置を模式的に示す図である。
図1に示すように、この例のブレーキ装置1は、基本的には従来公知の一般的な2系統のブレーキ装置と同じである。すなわち、ブレーキ装置1は、ブレーキペダル2、電動倍力装置3、タンデムマスタシリンダ4、リザーバタンク5、およびブレーキシリンダ6を備えている。
図示しないが、ステータ10には電流制御装置を介して電源が接続されているとともに、電流制御装置はブレーキ装置1の電子制御装置に接続されている。
まず、ブレーキ非作動時の電動倍力装置3について説明する。
ブレーキペダル2が踏み込まれない電動倍力装置3の非作動状態では、図2に示すようにパワーピストン支持部材19および入力受け部材21は、それぞれ各リターンスプリング30,31により後方(図2において右方)に付勢されて、リアハウジング8に当接したキー部材26により後退限の非作動位置とされている。その場合、この電動倍力装置3の非作動状態で、パワーピストン支持部材19に対する入力受け部材21の相対変位は0と規定されている。そして、電子制御装置では、マグネット19の磁界により発生する磁気センサー28の電流が基準値として0に設定される。したがって、電子制御装置は電流制御装置を制御して電源から電力(電流)をステータ10に供給しない。
前述の電動倍力装置3の非作動状態で、運転者によりブレーキペダル2が踏み込まれ、入力が図3に示すFi0に達すると、リターンスプリング31が撓んで、入力軸22が前進する。すると、入力受け部材21が前進するので、パワーピストン支持部材19に対して入力受け部材21が相対的に変位する。これにより、磁気センサー28に対するマグネット29の磁界が変動するので、磁気センサー28は電流を発生して、電子制御装置に出力する。したがって、電子制御装置は電流制御装置を制御して、電源から電流をステータ10に供給する。
まず、電動倍力装置3の全負荷状態の入力でブレーキが作動されている状態からの解除またはブレーキ力低減時について説明する。ブレーキペダル2が解放されると、入力Fiが減少するので、リターンスプリング31で入力軸22、入力受け部材21、および間隔部材25がパワーピストン支持部材19に対して相対的に後退する。このため、磁気センサー28に対するマグネット29の相対変位が減小するので、磁気センサー28の発生する電流も小さくなる。すると、電子制御装置はステータ10への供給電流を低減する。
更に、反力部材としてゴムで形成されたリアクションディスク23とすることで、反力部材の構成をより一層簡単にすることができる。
また、本発明に係るブレーキ装置は、電動倍力装置を用いて車輪にブレーキをかけるブレーキ装置に好適に利用することができる。
Claims (6)
- 入力が加えられる入力軸と、前記入力軸からの入力を受ける入力受け部材と、パワーピストンと、前記パワーピストンを支持するパワーピストン支持部材と、前記入力受け部材と前記パワーピストン支持部材との相対変位を検出する相対変位検出手段と、前記相対変位検出手段で検出された前記相対変位に基づいて前記パワーピストンを作動する電動モータと、前記パワーピストンの作動で出力する出力軸と、粘弾性材から形成されるとともに前記出力軸からの反力が加えられる反力部材とを少なくとも備え、前記入力受け部材は非作動時に前記前記反力部材に対して所定の間隙をおいて離間するとともに、所定の入力が加えられた作動時に前記反力部材に当接可能に配設されていることを特徴とする電動倍力装置。
- 前記電動モータは、前記相対変位検出手段で検出された前記相対変位に基づく電流が供給されるステータと、前記ステータにより回転されて前記パワーピストンに前記相対変位に基づく推進力を加えるローラとを有することを特徴とする請求項1に記載の電動倍力装置。
- 前記相対変位検出手段は磁気センサーとマグネットとを有することを特徴とする請求項1または2に記載の電動倍力装置。
- 前記磁気センサーは前記パワーピストン支持部材に配設されるとともに、前記マグネットは前記入力受け部材に配設されることを特徴とする請求項3に記載の電動倍力装置。
- 前記反力部材は、ゴムから形成されたリアクションディスクであることを特徴とする請求項1ないし4のいずれか1に記載の電動倍力装置。
- ブレーキ操作を行うブレーキ操作部材と、前記ブレーキ操作部材からの入力が所定のサーボ比で倍力された出力を発生する電動倍力装置と、前記電動倍力装置の出力で作動されてブレーキ圧を発生するマスタシリンダと、前記マスタシリンダからのブレーキ圧で作動するブレーキシリンダとを少なくとも備え、
前記電動倍力装置は請求項1ないし5のいずれか1に記載の電動倍力装置であることを特徴とするブレーキ装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11742027.3A EP2535234A4 (en) | 2010-02-12 | 2011-02-09 | ELECTRICAL SERVICE DEVICE AND BRAKING DEVICE THEREFOR |
US13/522,179 US20120324882A1 (en) | 2010-02-12 | 2011-02-09 | Electric booster and brake device using the same |
CN201180009029.0A CN102741104B (zh) | 2010-02-12 | 2011-02-09 | 电动增力装置以及使用该电动增力装置的制动装置 |
JP2011553756A JP5501386B2 (ja) | 2010-02-12 | 2011-02-09 | 電動倍力装置およびこれを用いたブレーキ装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010028628 | 2010-02-12 | ||
JP2010-028628 | 2010-02-12 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011099277A1 true WO2011099277A1 (ja) | 2011-08-18 |
Family
ID=44367563
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2011/000717 WO2011099277A1 (ja) | 2010-02-12 | 2011-02-09 | 電動倍力装置およびこれを用いたブレーキ装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20120324882A1 (ja) |
EP (1) | EP2535234A4 (ja) |
JP (1) | JP5501386B2 (ja) |
CN (1) | CN102741104B (ja) |
WO (1) | WO2011099277A1 (ja) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2883766A1 (en) | 2013-12-12 | 2015-06-17 | Nissin Kogyo Co., Ltd. | Hydraulic pressure generating apparatus |
JP2018526271A (ja) * | 2015-09-14 | 2018-09-13 | ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング | 電動機を備えるブレーキアシストシステム |
CN113173149A (zh) * | 2021-06-03 | 2021-07-27 | 浙江三星机电股份有限公司 | 一种电子刹车助力器 |
WO2022071389A1 (ja) * | 2020-09-29 | 2022-04-07 | 株式会社アドヴィックス | ブレーキ液圧制御装置 |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2011155074A1 (ja) * | 2010-06-08 | 2011-12-15 | トヨタ自動車株式会社 | 車両の電動式ブレーキ装置 |
KR101975174B1 (ko) * | 2012-11-28 | 2019-05-07 | 현대모비스 주식회사 | 전동부스터 방식 제동장치의 하중 지지 구조 |
WO2016194582A1 (ja) * | 2015-05-29 | 2016-12-08 | 日立オートモティブシステムズ株式会社 | 電動倍力装置 |
KR102585197B1 (ko) * | 2016-07-06 | 2023-10-05 | 에이치엘만도 주식회사 | 일체형 전동식 브레이크 장치의 액추에이터 조립체 |
ES2664369A1 (es) * | 2017-06-16 | 2018-04-19 | Robert Bosch Gmbh | Mecanismo de freno de un vehículo con capacidad de detección de atasco de pedal |
US20200276964A1 (en) * | 2017-09-25 | 2020-09-03 | Hitachi Automotive Systems, Ltd. | Electric booster |
DE102020109449A1 (de) * | 2020-04-03 | 2021-10-07 | Zf Active Safety Gmbh | Baugruppe für einen elektromechanischen Bremskraftverstärker einer Fahrzeug- Bremsanlage, Bremskraftverstärker mit einer solchen Baugruppe und Fahrzeug-Bremsanlage mit einer solchen Baugruppe |
DE102020109451A1 (de) * | 2020-04-03 | 2021-10-07 | Zf Active Safety Gmbh | Baugruppe für einen elektromechanischen Bremskraftverstärker einer Fahrzeug-Bremsanlage, Bremskraftverstärker mit einer solchen Baugruppe und Fahrzeug-Bremsanlage mit einer solchen Baugruppe |
CN111497811A (zh) * | 2020-05-06 | 2020-08-07 | 北京理工大学 | 一种多模式电子液压制动器助力系统及控制方法 |
CN113460016B (zh) * | 2021-06-03 | 2023-05-30 | 浙江三星机电股份有限公司 | 一种电子刹车助力器 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0516793A (ja) * | 1991-07-12 | 1993-01-26 | Jidosha Kiki Co Ltd | 倍力装置 |
JPH0930401A (ja) * | 1995-07-20 | 1997-02-04 | Aisin Seiki Co Ltd | 真空倍力装置 |
JP2606909B2 (ja) | 1988-11-22 | 1997-05-07 | 自動車機器株式会社 | 負圧倍力装置 |
JP2002321611A (ja) * | 2001-04-26 | 2002-11-05 | Bosch Braking Systems Co Ltd | 電動式ブレーキ倍力装置 |
JP2006281992A (ja) * | 2005-03-31 | 2006-10-19 | Hitachi Ltd | 電動倍力装置 |
JP2008081033A (ja) | 2006-09-28 | 2008-04-10 | Hitachi Ltd | 電動倍力装置 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0239403Y2 (ja) * | 1987-08-28 | 1990-10-23 | ||
JPH04368271A (ja) * | 1991-06-14 | 1992-12-21 | Jidosha Kiki Co Ltd | 倍力装置 |
JP2000108880A (ja) * | 1998-09-30 | 2000-04-18 | Aisin Seiki Co Ltd | 負圧式倍力装置 |
FR2809068B1 (fr) * | 2000-05-19 | 2002-08-09 | Bosch Gmbh Robert | Logement de reception d'un disque de reaction et servomoteur pneumatique d'assistance au freinage comportant un tel logement |
FR2860474B1 (fr) * | 2003-10-02 | 2006-04-28 | Bosch Gmbh Robert | Servomoteur electrique d'assistance au freinage et vehicule comportant un tel servomoteur |
FR2933936B1 (fr) * | 2008-07-17 | 2014-10-10 | Bosch Gmbh Robert | Servomoteur reglable d'assistance au freinage |
JP5685791B2 (ja) * | 2010-09-29 | 2015-03-18 | 日立オートモティブシステムズ株式会社 | 倍力装置 |
-
2011
- 2011-02-09 EP EP11742027.3A patent/EP2535234A4/en not_active Withdrawn
- 2011-02-09 WO PCT/JP2011/000717 patent/WO2011099277A1/ja active Application Filing
- 2011-02-09 CN CN201180009029.0A patent/CN102741104B/zh not_active Expired - Fee Related
- 2011-02-09 JP JP2011553756A patent/JP5501386B2/ja active Active
- 2011-02-09 US US13/522,179 patent/US20120324882A1/en not_active Abandoned
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2606909B2 (ja) | 1988-11-22 | 1997-05-07 | 自動車機器株式会社 | 負圧倍力装置 |
JPH0516793A (ja) * | 1991-07-12 | 1993-01-26 | Jidosha Kiki Co Ltd | 倍力装置 |
JPH0930401A (ja) * | 1995-07-20 | 1997-02-04 | Aisin Seiki Co Ltd | 真空倍力装置 |
JP2002321611A (ja) * | 2001-04-26 | 2002-11-05 | Bosch Braking Systems Co Ltd | 電動式ブレーキ倍力装置 |
JP2006281992A (ja) * | 2005-03-31 | 2006-10-19 | Hitachi Ltd | 電動倍力装置 |
JP2008081033A (ja) | 2006-09-28 | 2008-04-10 | Hitachi Ltd | 電動倍力装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2535234A4 |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2883766A1 (en) | 2013-12-12 | 2015-06-17 | Nissin Kogyo Co., Ltd. | Hydraulic pressure generating apparatus |
US10407038B2 (en) | 2013-12-12 | 2019-09-10 | Autoliv Nissin Brake Systems Japan Co., Ltd. | Hydraulic pressure generating apparatus |
JP2018526271A (ja) * | 2015-09-14 | 2018-09-13 | ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング | 電動機を備えるブレーキアシストシステム |
US11273813B2 (en) | 2015-09-14 | 2022-03-15 | Robert Bosch Gmbh | Electric motor brake assist system |
WO2022071389A1 (ja) * | 2020-09-29 | 2022-04-07 | 株式会社アドヴィックス | ブレーキ液圧制御装置 |
CN113173149A (zh) * | 2021-06-03 | 2021-07-27 | 浙江三星机电股份有限公司 | 一种电子刹车助力器 |
CN113173149B (zh) * | 2021-06-03 | 2023-06-23 | 浙江三星机电股份有限公司 | 一种电子刹车助力器 |
Also Published As
Publication number | Publication date |
---|---|
US20120324882A1 (en) | 2012-12-27 |
CN102741104A (zh) | 2012-10-17 |
JPWO2011099277A1 (ja) | 2013-06-13 |
EP2535234A4 (en) | 2015-05-20 |
EP2535234A1 (en) | 2012-12-19 |
JP5501386B2 (ja) | 2014-05-21 |
CN102741104B (zh) | 2015-05-20 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5501386B2 (ja) | 電動倍力装置およびこれを用いたブレーキ装置 | |
US7987950B2 (en) | Single motor electro wedge brake system using solenoid mechanism for implementing additional functions | |
US9108609B2 (en) | Electric motor-driven booster | |
US9260094B2 (en) | Vehicle brake device | |
JP4756247B2 (ja) | 電動倍力装置 | |
CN107406065B (zh) | 制动控制装置 | |
JP5980417B2 (ja) | 電動倍力装置 | |
JP2007126032A (ja) | ブレーキ装置 | |
JP2014046857A (ja) | 電動倍力装置 | |
JP2014139034A (ja) | 車両用電動倍力装置の制御装置 | |
JP2011079525A (ja) | 電動倍力装置 | |
JP6205821B2 (ja) | 電動駐車ブレーキ制御装置 | |
JP5321854B2 (ja) | 電動倍力装置 | |
JP5716525B2 (ja) | ブレーキ制御装置 | |
JP2973707B2 (ja) | ディスクブレーキ | |
JP5828688B2 (ja) | ストロークシミュレータおよび電動アクチュエータ | |
JP5262826B2 (ja) | ブレーキ倍力装置 | |
JP2021109649A (ja) | 分離型電動ブレーキ倍力装置 | |
JP5860627B2 (ja) | 倍力装置 | |
JP5245770B2 (ja) | ブレーキ倍力装置、ブレーキ倍力装置付き車両、およびブレーキ倍力方法 | |
JP7212567B2 (ja) | 電動式倍力装置 | |
JP2000052971A (ja) | 車両用マスタシリンダのための電動ブースタ | |
CN114728635B (zh) | 制动控制装置 | |
JP2024048594A (ja) | 車両のブレーキ装置 | |
WO2018097306A1 (ja) | 電動倍力装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 201180009029.0 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 11742027 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2011553756 Country of ref document: JP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2011742027 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13522179 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |