WO2019042317A1 - Frein à disque et véhicule - Google Patents

Frein à disque et véhicule Download PDF

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Publication number
WO2019042317A1
WO2019042317A1 PCT/CN2018/102949 CN2018102949W WO2019042317A1 WO 2019042317 A1 WO2019042317 A1 WO 2019042317A1 CN 2018102949 W CN2018102949 W CN 2018102949W WO 2019042317 A1 WO2019042317 A1 WO 2019042317A1
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WO
WIPO (PCT)
Prior art keywords
brake
disc brake
disc
motor
reducer
Prior art date
Application number
PCT/CN2018/102949
Other languages
English (en)
Chinese (zh)
Inventor
郑祖雄
Original Assignee
比亚迪股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 比亚迪股份有限公司 filed Critical 比亚迪股份有限公司
Publication of WO2019042317A1 publication Critical patent/WO2019042317A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D67/00—Combinations of couplings and brakes; Combinations of clutches and brakes
    • F16D67/02—Clutch-brake combinations
    • F16D67/06—Clutch-brake combinations electromagnetically actuated
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/102—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction brakes

Definitions

  • the present disclosure relates to the field of brakes, and in particular to a disc brake and a vehicle.
  • the brake pedal In the traditional hydraulic or pneumatic brake system, there are obvious disadvantages such as complicated gas-liquid pipeline, difficult maintenance, complicated layout structure, slow braking dynamic response, and low brake comfort performance.
  • the brake pedal In a hydraulic brake system, the brake pedal generates a rebound vibration phenomenon when the anti-lock brake system is activated, which affects the braking comfort performance.
  • the brake pedal mechanism since the brake pedal mechanism is directly connected to the brake transmission device and the brake actuator, the impact force generated when the vehicle collides is directly transmitted to the cab through the brake system, which seriously affects the safety performance of the vehicle.
  • the components of the conventional hydraulic brake system such as the vacuum brake booster, the brake master cylinder, and the oil reservoir are used, so that the structure and the assembly are complicated and bulky. Maintenance problems are difficult, and since the system is provided with hydraulic brake lines and brake fluids that connect the corresponding components, it is necessary to periodically change the hydraulic oil and periodically check for the presence of hydraulic oil leakage.
  • the present disclosure also provides a vehicle including the disc brake as described above.
  • the axial length of the brake is reduced, making the brake structure more compact and occupying less space, facilitating the mounting arrangement on the entire vehicle.
  • FIG. 1 is a cross-sectional view of a disc brake in accordance with an embodiment of the present disclosure
  • Figure 2 is a partial enlarged view of Figure 1;
  • Figure 3 is a schematic structural view of a yaw-cone difference planetary reducer
  • Figure 4 is a schematic structural view of an electromagnetic clutch
  • FIG. 5 is a bottom view of a vehicle in accordance with an embodiment of the present disclosure.
  • orientation words used such as “left and right”, generally refer to the left and right of the drawing directions of the corresponding drawings, and the use of these orientation words is for convenience of description only. It is not to be construed as limiting the disclosure.
  • a disc brake including a caliper body 10, a brake disc 20, a first brake block 31, a motor 40, a speed reducer 50, and Screw mechanism 60.
  • the first brake block 31 is slidably mounted within the caliper body 10 and on one side of the brake disk 20.
  • the motor 40 is an outer rotor motor, and the stator 41 of the motor 40 is formed with a cavity 411 extending in the axial direction.
  • the screw mechanism 60 includes a lead screw 61 and a nut 62 fitted to the lead screw 61.
  • the lead screw 61 extends through the cavity 411, and the rotor 42 of the motor 40 drives the lead screw 61 to rotate through the reducer 50 so that the nut 62 is along the lead screw 61.
  • the axial movement moves to urge the first brake block 31 to move and press against the brake disc 20.
  • the axial length of the brake is reduced, so that the brake structure is more compact, the space is smaller, and the mounting arrangement on the entire vehicle is facilitated.
  • the disc brake of the present disclosure may be a fixed caliper disc brake or a float caliper disc brake.
  • the caliper body of the fixed caliper disc brake is fixedly mounted on the vehicle body and cannot be moved relative to the vehicle body.
  • the caliper body of the float caliper disc brake is slidably mounted on the vehicle body and is movable relative to the vehicle body in the same direction as the axial direction of the brake disc.
  • the brake further includes a second brake block 32 mounted on the caliper body 10 and located on the brake disc 20 On the other side, the caliper body 10 is axially movable relative to the brake disc 20. Specifically, as shown in FIGS. 1 and 2, when the service brake is performed, the rotor 42 of the motor 40 drives the screw 61 to rotate through the speed reducer 50 to move the nut 62 to the left along the screw 61, thereby pushing the first system.
  • the moving block 31 also moves to the left and is pressed against the brake disc 20, so that the brake disc 20 gives the nut 62 a rightward reaction force, which is transmitted to the caliper body 10, so that the caliper body 10 moves to the right until the second brake block 32 is also pressed against the brake disc 20.
  • the brake pads 31, 32 on both sides are pressed against the brake disc 20, thereby clamping the brake disc 20, generating a friction torque that prevents the wheel from rotating, and realizing the service brake.
  • the screw mechanism 60 can be a rolling screw mechanism.
  • a rolling body such as a ball or a roller is disposed between the nut 62 and the screw 61.
  • the screw mechanism 60 can be a planetary roller screw mechanism. Compared with other screw mechanisms, the planetary roller screw mechanism has the advantages of large load bearing capacity, strong impact resistance, high transmission precision and long service life.
  • the screw mechanism 60 can be a ball screw mechanism.
  • the advantageous effects of using the ball screw mechanism are similar to those of the above-described planetary roller screw, and the description thereof will be omitted herein to avoid redundancy.
  • the present disclosure is not limited thereto, and the screw mechanism 60 may also employ a slide screw mechanism or the like.
  • the screw angle of the screw pair can be made larger than the self-locking angle, so as to ensure that the screw pair does not self-lock, so that the force of the brake disc can be realized by the brake disc when the brake is released. The return of the nut.
  • the disc brake may further include a piston 90 that is slidably fitted to one end of the cavity 411, and the speed reducer 50 is disposed at the other end of the cavity 411 and connected to the lead screw 61, and the nut 62
  • the first brake block 31 is pushed by the piston 90 to move.
  • the piston 90 separates the interior of the cavity 411 from the outside, such that the screw mechanism 60 is in a relatively closed environment, protected from external water, impurities, and prolongs the service life of the brake.
  • the piston 90 can be clearance-fitted with the cavity 411, that is, the diameter of the cavity 411 can be slightly larger than the diameter of the piston 90.
  • the seal ring 100 may be provided between the piston 90 and the inner wall of the cavity 411.
  • the nut 62 may be fixed to the piston 90 by screwing, welding, gluing, or the like. However, in order to avoid stress concentration at the joint, in one embodiment, the nut 62 is not connected to the piston 90.
  • the piston 90 may be in a cylindrical structure in which one end is closed and the other end is open.
  • the nut 62 may be disposed in the piston 90 and is in clearance with the inner wall of the piston 90.
  • the thrust of the nut 62 acts on the closed end of the piston 90 to push The piston 90 moves toward the brake disc 20.
  • the nut 62 can also directly drive the first brake block 31 to move without the need to provide the piston 90.
  • a thrust bearing 70 may be mounted on the lead screw 61.
  • the lead screw 61 is formed with a flange 611 disposed between the flange 611 and the outer casing of the speed reducer 50.
  • the speed reducer 50 may employ any appropriate type of speed reducer as long as the output torque of the motor 40 can be reduced and torqued and transmitted to the lead screw 61.
  • the speed reducer 50 can be a yaw cone differential planetary reducer.
  • FIG. 3 is a schematic structural view of a yaw-cone difference planetary reducer, which is mainly composed of a rotating bevel gear 1, a yoke bevel gear 2, a yaw generator H on the input shaft 5, and a circumferential limiting pair.
  • the yaw generator H is composed of a shaft head 6 with an off-angle ⁇ at the end of the input shaft 5 and a tapered roller bearing 7.
  • the bevel gear 2 is equivalent to an inner bevel gear, and is internally meshed with a bevel gear 1 mounted on the output shaft 9.
  • One end of the yaw bevel gear 2 is mounted on the tapered roller bearing 7 at the yaw shaft head 6, and the other end
  • the spherical bearing 8 is coupled to the shaft end of the output shaft 9 to form a ball joint.
  • the tapered top of the bevel gear coincides with the center O point of the spherical bearing, and a drum-shaped outer ring gear 3 is provided on the outer edge of the yoke bevel gear 2, and the inner ring gear 4 constitutes a circumferential restricting pair.
  • the transmission principle of the yaw cone planetary reducer is: when the input shaft 5 drives the yaw shaft 6 to rotate around the fixed axis nn of the input shaft, the axis OO H of the yaw shaft head forms a cone angle of 2 ⁇ cone beam space. Since the yoke bevel gear 2 mounted on the yaw shaft head 6 is restrained by the circumferential limiting pair and cannot perform the revolving motion, the cone beam motion of the yaw moment head forces the yaw bevel gear 2 to circulate around the O point. The yaw motion forms a state of engagement with the rotating bevel gear 1 mounted on the output shaft 9.
  • the rotor 42 of the motor 40 is connected to the ring gear 4 of the planetary reducer which can be biased, and the output shaft 9 of the yaw-cone planetary reducer can be connected to the lead screw 61.
  • the electromagnetic clutch 8 is mounted on the input shaft 5 of the yaw cone planetary reducer. That is to say, the ring gear 4 serves as the input end of the yaw-cone difference planetary reducer, and the output shaft 9 serves as the output end of the yaw-cone difference planetary reducer.
  • the brake may further include an electromagnetic clutch 80 that is mounted on the reducer. On one of the rotating shafts 50, the rotating shaft is locked by the electromagnetic clutch 80 to lock the speed reducer 50, thereby realizing the parking brake.
  • the electromagnetic clutch 8 can be mounted on the input shaft 5 of the yaw cone difference planetary speed reducer and can lock the input shaft 5.
  • the electromagnetic clutch 80 when the electromagnetic clutch 80 is de-energized, the electromagnetic clutch 80 is engaged to lock a rotating shaft of the speed reducer 50, so that the speed reducer 50 is locked, so that the screw rod 61 cannot be rotated, so that the nut 62 cannot be moved, thereby maintaining the pair.
  • the thrust of the first brake block 31 realizes parking brake.
  • the electromagnetic clutch When the electromagnetic clutch is energized, the electromagnetic clutch is disengaged to release the retarder 50 and the parking brake is released.
  • the electromagnetic clutch 80 may include a clutch housing 81, an electromagnet, a translational friction plate 85, a rotating friction plate 86, an outer race 87, and an inner race 88.
  • the clutch housing 81 is fixed relative to the caliper body 10
  • the electromagnet may include a fixed iron core 82, a movable iron core 83, and a drive spring 84 acting on the movable iron core 83.
  • the inner race 88 is slidably coupled to one of the rotating shafts of the speed reducer 50, and the rotary lining 86 is disposed on the inner race 88 to be rotatable by the rotary shaft.
  • the outer race 87 is spline-slidably coupled to the inner wall of the clutch housing 81, and the translational friction plate 85 is disposed on the outer race 87 to be able to translate in the axial direction of the rotary shaft.
  • the fixed iron core 82 and the movable iron core 83 may be formed in an annular structure, and the moving iron core 83 is sleeved on the outside of the rotating shaft, and the fixed iron core 82 is sleeved on the outside of the moving iron core 83 to make the structure of the brake more Compact and smaller in axial dimensions.
  • the motor 40 when the parking brake function needs to be performed, the motor 40 is energized, and the screw 61 is driven to rotate by the reducer 50 in sequence, so that the nut 62 pushes the brake block to clamp the brake disk 20 to meet the parking requirement.
  • the motor 40 loses power, and the electromagnetic clutch 80 operates to lock the speed reducer 50.
  • the rotating shaft locks the speed reducer 50, maintains the parking brake force, and performs a parking brake function.
  • the electromagnetic clutch 80 loses the locking force, releases the rotating shaft, and unlocks the speed reducer 50.
  • the speed reducer 50 may be disposed between the motor 40 and the electromagnetic clutch 80 to make the brake compact and structurally uniform.
  • the motor 40, the retarder 50, and the electromagnetic clutch 80 can be housed within the same housing 110, which can be secured to the caliper body 10, such as by fasteners, as a brake A part of the caliper body 10.
  • the clutch housing 81 can be fixed within the housing 110.
  • a vehicle 200 that includes a disc brake as described above.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Braking Arrangements (AREA)

Abstract

L'invention concerne un frein à disque, comprenant un étrier (10) de frein, un disque (20) de frein, un premier patin (31) de frein, un moteur électrique (40), un réducteur (50) et un mécanisme de tige de vis (60), le moteur électrique (40) étant un moteur à rotor externe ; un stator (41) du moteur électrique (40) est pourvu d'une cavité (411) s'étendant dans une direction axiale ; le mécanisme de tige de vis (60) comprend une tige de vis (61) et un écrou (62) gainé sur la tige de vis (61) ; la tige de vis (61) traverse la cavité (411) ; et un rotor (42) du moteur électrique (40) entraîne en rotation la tige de vis (61), par l'intermédiaire du réducteur (50), de sorte que l'écrou (62) se déplace axialement le long de la tige de vis (61), amenant ainsi le premier patin (31) de frein à se déplacer pour presser le disque (20) de frein. L'invention concerne en outre un véhicule.
PCT/CN2018/102949 2017-08-29 2018-08-29 Frein à disque et véhicule WO2019042317A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201721091658.3 2017-08-29
CN201721091658.3U CN207145489U (zh) 2017-08-29 2017-08-29 盘式制动器及车辆

Publications (1)

Publication Number Publication Date
WO2019042317A1 true WO2019042317A1 (fr) 2019-03-07

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PCT/CN2018/102949 WO2019042317A1 (fr) 2017-08-29 2018-08-29 Frein à disque et véhicule

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CN (1) CN207145489U (fr)
WO (1) WO2019042317A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112303150A (zh) * 2019-07-31 2021-02-02 比亚迪股份有限公司 线控制动系统和车辆

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN207145489U (zh) * 2017-08-29 2018-03-27 比亚迪股份有限公司 盘式制动器及车辆
EP3626994A1 (fr) * 2018-09-18 2020-03-25 KNORR-BREMSE Systeme für Nutzfahrzeuge GmbH Ensemble frein et procédé de contrôle d'ensemble frein
CN110936974B (zh) * 2018-09-21 2021-02-23 比亚迪股份有限公司 制动器、轨道交通制动系统及轨道交通系统
CN112145582B (zh) * 2019-06-28 2021-11-12 比亚迪股份有限公司 盘式制动器、线控制动系统以及车辆
CN111649018B (zh) * 2020-06-04 2022-02-18 南京理工大学 一种集成外转子电机的泵控液压缸
CN112777266B (zh) * 2021-02-05 2022-08-26 淮北合众机械设备有限公司 一种可调心的滚筒式清扫器

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2597685A (en) * 1946-09-13 1952-05-20 Singer Mfg Co Clutch and brake for electric transmitters
EP1460301A2 (fr) * 2003-03-18 2004-09-22 Continental Teves AG & Co. oHG Frein à disque à commande électromécanique
US20060021831A1 (en) * 2004-07-29 2006-02-02 Ken Yamamoto Electric brake assembly
CN102410325A (zh) * 2011-10-27 2012-04-11 奇瑞汽车股份有限公司 一种电子机械制动器以及汽车
CN103644218A (zh) * 2013-12-10 2014-03-19 山东交通学院 一种复合式电子机械制动器
CN207145489U (zh) * 2017-08-29 2018-03-27 比亚迪股份有限公司 盘式制动器及车辆

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2597685A (en) * 1946-09-13 1952-05-20 Singer Mfg Co Clutch and brake for electric transmitters
EP1460301A2 (fr) * 2003-03-18 2004-09-22 Continental Teves AG & Co. oHG Frein à disque à commande électromécanique
US20060021831A1 (en) * 2004-07-29 2006-02-02 Ken Yamamoto Electric brake assembly
CN102410325A (zh) * 2011-10-27 2012-04-11 奇瑞汽车股份有限公司 一种电子机械制动器以及汽车
CN103644218A (zh) * 2013-12-10 2014-03-19 山东交通学院 一种复合式电子机械制动器
CN207145489U (zh) * 2017-08-29 2018-03-27 比亚迪股份有限公司 盘式制动器及车辆

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112303150A (zh) * 2019-07-31 2021-02-02 比亚迪股份有限公司 线控制动系统和车辆

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