CN201027853Y - Floating pincers type double-push rod barometric disk brake - Google Patents
Floating pincers type double-push rod barometric disk brake Download PDFInfo
- Publication number
- CN201027853Y CN201027853Y CNU2006200997798U CN200620099779U CN201027853Y CN 201027853 Y CN201027853 Y CN 201027853Y CN U2006200997798 U CNU2006200997798 U CN U2006200997798U CN 200620099779 U CN200620099779 U CN 200620099779U CN 201027853 Y CN201027853 Y CN 201027853Y
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- Prior art keywords
- pressure arm
- needle roller
- torsion spring
- roller pair
- brake
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Abstract
The utility model discloses dual push rods pneumatic disc brake with floating caliper, relating to the brake used in medium weight and heavy commercial vehicles. The structure of the utility model is that a pressure arm component (10), a rotating shaft component (20), a reset spring (30), a rushing board (40), an inner friction plate (50), a braking disc (60), an outer friction plate (70), a bracket (80) and a caliper body (90) are arranged in turn. The utility model takes advantage of the feature of a rectangular torsional spring, and can not only realize one-way transmission of torque, but also effectively realizes overpower protection; the pressure arm component (10) is designed reasonably with a constant reinforcement ration in the process of braking to provide stable braking torque; the dual push rods moves with good synchronicity; braking torque is notably increased to enlarge the applied area of the pneumatic disc brake; the worn gap of the brake can adjust automatically; the braking toque above 20,000 Nm is provided to meet the demand of vehicles with rated load of 13 t.
Description
Technical field
The utility model relates in a kind of being applicable to, the break of heavy type commercial vehicle, relates in particular to a kind of floating tong type bipushing rod pneumatic disk brake; This break can significantly reduce brake noise, and bigger braking moment is provided, and effectively enlarges the application area of disk type braker.
Background technique
Air-pressure disc brake is a kind of as disk type braker, starts from the nineties in last century, can be widely used in M1, M2 class passenger car and the above lorry of N1 class.Air-pressure disc brake rapid heat dissipation, in light weight, simple structure, wearing clearance are adjusted automatically; Particularly resistance to high temperature is good, and braking effect is stable, can significantly reduce stopping distance, for vehicle provides reliable traffic safety guarantee.Simultaneously, air-pressure disc brake can reduce brake noise, effectively solves the city bus braking and causes noise pollution.As the drum brake update product, European trailer installation rate surpasses 50%, and city bus is to install as standard configuration.In order to meet the 2008 Beijing Olympic Games and 2010 Shanghai World's Fair, Beijing, Shanghai public transport modernization overlay, an important ring changes disc type with the break drum-type with exactlying, the minimizing brake noise.Domestic unique air-pressure disc brake that can provide in batches at present is that single pusher structure (is seen utility model patent, patent No. ZL 01212585.7), restricted power output structure restriction, the braking moment that can provide is limited, can not mate the above bus braking requirement of above vehicle bridge of 11t and 13m.
Two push rod air-pressure disc brakes of domestic acquisition utility model patent are still located experimental stage, and chain transmission is adopted in the compensation of two push rod clearances synchronously.Influenced by iron chains tension force, in the compensation process of gap, two push rod compensate for displacement there are differences, and big distance appears in long-time difference accumulation between two push rods, cause the friction plate inordinate wear, and the break life-span reduces.
Air-pressure disc brake is promoted bottleneck to be had:
1, compare with drum brake of the same type, braking moment is less than normal;
2, brake bush wearing clearance compensation mechanism job insecurity, poor reliability;
3, the existing pair of two push rod compensation of push rod air-pressure disc brake poor synchronization.
Summary of the invention
The purpose of this utility model is at the shortcoming and defect of existing single push rod and two push rod air-pressure disc brake existence, and a kind of floating tong type bipushing rod pneumatic disk brake is provided.
The purpose of this utility model is achieved in that
The rational brake clearance automatic adjusting mechanism of development structure; Design new pneumatic brake boosting mechanism, improve the whole transmission efficiency of reinforcement transfer mechanism; Guarantee that braking moment is stable in the break braking process, caliper body slides smooth and easy, and the wearing clearance self-adjustment structure is reliable and stable, good endurance.
Specifically, the utility model comprises friction plate 50, brake disc 60, outside friction disc 70, support 80 and caliper body 90 in the conventional general part; Also comprise pressure arm assembly 10, rotating assembly 20, return spring 30, push pedal 40; From right to left, pressure arm assembly 10, rotating assembly 20, return spring 30, push pedal 40, interior friction plate 50, brake disc 60, outside friction disc 70, support 80 and caliper body 90 are arranged in order, as Fig. 1;
Described pressure arm assembly 10 comprises pressure arm 11, fulcrum cylinder 12, little needle roller pair 13, big needle roller pair 14, shift fork 15, as Fig. 2;
Described rotating assembly 20 comprises adjusts cover 21, big torsion spring 22, turning collar 23, little torsion spring 24, active rotating shaft 25, reference seat 26, driven spindle 27, screw rod 28, gear 29, as Fig. 3;
Annexation between above-mentioned each functional part of the utility model is:
Axle on the reference seat 26 cooperates with clamp 90 endoporus, and return spring 30 is among 26 endoporus of reference seat, clamp 90 endoporus, supports reference seat 26; Pressure arm assembly 10 matches with reference seat 26 by big needle roller secondary 14, is pressed in clamp 90 cavitys by return spring 30; Support 80 constitutes the floating tong type structure with clamp 90 by pin rod, and interior friction plate 50 and outside friction disc 70 place on support 80 attachment faces; Push pedal 40 links together with screw rod 28, friction plate 50 in fitting.
Working principle of the present utility model is:
During braking, the air chamber push rod promotes pressure arm 11 ball-and-socket O3; Under air chamber push rod impetus, pressure arm 11 is around center O 1 rotation of fulcrum cylinder 12; Pressure arm 11 and fulcrum cylinder 12 constitute cam mechanism, and the rotation of pressure arm 11 is promptly braked displacement except that reinforcement also can produce the output displacement; Braking force behind the reinforcement and retarder location Mobile Communication cross reference seat 26 and pass to driving and driven rotating shaft 25,27, and driving and driven rotating shaft 25,27 passes to screw rod 28, and screw rod 28 will brake displacement and braking force passes to push pedal 40; Friction plate 50 in push pedal 40 promotes, interior friction plate 50 promotes brake disc 60, and by the slip of caliper body 90, outside friction disc 70 and interior friction plate 50 clamp brake disc 60, form braking.
End of braking, the air chamber push rod unclamps, and return spring 30 promotes reference seat 26, and reference seat 26 passes to return spring 30 thrusts the cam mechanism that is formed by pressure arm 11 and fulcrum cylinder 12; Cam mechanism is rotated by thrust, thereby assurance pressure arm 11 is got back to the braking initial position.
Gap width surpasses the initial setting gap width between friction plate and brake disc, and during braking, pressure arm 11 rotations drive shift fork 15 rotations; Shift fork 15 rotations are stirred and are adjusted cover 21 rotations; Adjust cover 21 and drive big torsion spring 22, turning collar 23 rotations, turning collar 23, little torsion spring 24 and active rotating shaft 25 threes constitute an overrunning clutch; During pressure arm 11 braking rotations, turning collar 23 drives little torsion spring 24 rotations, and active rotating shaft 25 is embraced in little torsion spring 24 rotations, drives active rotating shaft 25 and rotates together; Active rotating shaft 25 and screw rod 28 adopts screw-thread fit, between screw rod 28 and the push pedal 40 arranged spacing the cooperation, and screw rod 28 can not rotate; So active rotating shaft 25 rotations, screw rod 28 is screwed out, the gap width between friction compensation sheet and the brake disc; Driven spindle 27 and active rotating shaft 25 transmit rotation by gear 29, guarantee that two push rods stretch out the unanimity of displacement, avoid the friction plate eccentric wear.
End of braking is adjusted cover 21, big torsion spring 22 and turning collar 23 with pressure arm 11 revolutions, and little torsion spring 24 unclamps active rotating shaft 25.Pressure arm 11 returns only are subjected to the influence of return spring 40, and the return displacement is certain, and the friction disc wear gap width is compensated like this.
This shows overall employing floating tong type structure of the present utility model; Air-pressure disc brake adopts two push rods to brake; Thereby provide bigger braking moment.Especially:
1, the pressure arm design form guarantees that braking-force ratio is constant in the braking process;
2, cooperate with pressure arm and be all the needle roller pair, improve retardation efficiency;
3, clearance self-regulating mechanism adopts the secondary torsion spring to constitute overrunning clutch;
4, two push rod clearance adjustment adopt gear transmission to guarantee synchronously.
The utlity model has following advantage and good effect:
1, utilizes the rotation and the functional characteristic of rectangular cross-section torsion spring, under particular environment, not only realize the unidirectional delivery moment of torsion, can also effectively realize overload protection.Novel overrunning clutch constitutes by adjusting cover 21, big torsion spring 22, turning collar 23, little torsion spring 24 and active rotating shaft 25.
2, pressure arm assembly 10 is reasonable in design, and force increasing ratio is constant in the braking process, provides braking moment stable.During pressure arm 11, make full use of lever principle in the design pressure arm component 10, input power center O
3, rotating center O
2With the ouput force center O
1Be on the same straight line, guarantee that force increasing ratio is constant, braking moment is stable, avoids the left and right wheels braking deviation; Pressure arm assembly 10 adopts and is all the secondary cooperation of needle roller up and down, improves transmission efficiency, and transmission efficiency reaches more than 95%.
3, two pushrod movement synchronisms are good.Adopt gear 29 to connect between two push rods, efficient accurate transmission of gear guarantees that two pushrod movement synchronisms are reliable and stable.
4, braking moment significantly increases, and enlarges the air-pressure disc brake application area.By the application of two push rods and the raising of boosting mechanism transmission efficiency, greatly improve the retardation efficiency of pneumatic brake;
5, the brake wear gap is adjusted automatically.
6, provide 20,000 Nm above braking moment, satisfy the user demand of 13t load rating vehicle bridge.
Description of drawings
Fig. 1-the utility model assembly structure chart (analysing and observe);
Fig. 2-pressure arm and counterpart structural drawing (analysing and observe) thereof;
Fig. 3-clearance self-regulating mechanism and force transmission mechanism assembly structure chart (analysing and observe);
Fig. 4-pressure arm structural drawing;
Fig. 5-fulcrum round column structure figure;
Fig. 6-adjustment noose composition;
Fig. 7-big torsion spring structural drawing;
Fig. 8-turning collar structural drawing;
Fig. 9-little torsion spring structural drawing;
Figure 10-active rotating shaft structural drawing;
Figure 11-reference seat structural drawing;
Figure 12-driven spindle structural drawing;
Figure 13-screw-rod structure figure;
Figure 14-gear structure figure;
Figure 15-push pedal structural drawing.
Wherein:
10-pressure arm assembly,
The 11-pressure arm, 12-fulcrum cylinder, the little needle roller pair of 13-,
The big needle roller pair of 14-, the 15-shift fork;
The 20-rotating assembly,
21-adjusts cover, the big torsion spring of 22-, and the 23-turning collar,
The little torsion spring of 24-, the 25-active rotating shaft, the 26-reference seat,
The 27-driven spindle, the 28-screw rod, the 29-gear,
The 30-return spring;
The 40-push pedal;
Friction plate in the 50-;
The 60-brake disc;
The 70-outside friction disc;
The 80-support;
The 90-clamp.
Embodiment
Describe in detail below in conjunction with drawings and Examples:
1, the pressure arm assembly 10
Aforementioned, pressure arm assembly 10 comprises pressure arm 11, fulcrum cylinder 12, little needle roller pair 13, big needle roller pair 14, shift fork 15, as Fig. 2;
Pressure arm 11 is a kind of boosting levers, constitutes cam mechanism with fulcrum cylinder 12, as Fig. 4.
Fulcrum cylinder 12 is cylindrical bodys of one of a kind of vertical excision, and its function provides pivot point, as Fig. 5.
Little needle roller pair 13 is a kind of semi-circular cylindrical needle roller pairs, and its function is the frictional force that reduces between the revolute, as Fig. 2.
Big needle roller pair 14 is a kind of semi-circular cylindrical needle roller pairs, and its function is the frictional force that reduces between the revolute, as Fig. 2.
Shift fork 15 is a kind of needle rollers, and its function is to stir to adjust cover 21, as Fig. 2.
Its annexation is:
Is connected by little needle roller secondary 13 between pressure arm 11 and the fulcrum cylinder 12, is connected by big needle roller pair 14 between the reference seat 26 of pressure arm 11 and rotating assembly 20, pressure arm 11 is provided with shift fork 15.
2, rotating assembly 20
Aforementioned, rotating assembly 20 comprises adjusts cover 21, big torsion spring 22, turning collar 23, little torsion spring 24, active rotating shaft 25, reference seat 26, driven spindle 27, screw rod 28, gear 29, as Fig. 3;
Its annexation is:
Adjust between cover 21 and the turning collar 23 and adopt big torsion spring 22 to be connected, the little torsion spring 24 of employing is connected between turning collar 23 and the active rotating shaft 25: employing axis hole fit system connection between the reference seat 26 of driving and driven rotating shaft 25,27 and rotating assembly 20; Screw rod 28 adopts screw-thread fit with driving and driven rotating shaft 25,27.
Adjusting cover 21 is revolving parts, and its function is a transmitting torque, as Fig. 6.
Big torsion spring 22 is rectangular cross-section torsion springs, and its function is a transmitting torque, as Fig. 7.
Turning collar 23 is revolving parts, and its function is a transmitting torque, as Fig. 8.
Little torsion spring 24 is rectangular cross-section torsion springs, and its function is a transmitting torque, as Fig. 9.
Active rotating shaft 25 is step cylindrical bodys, and endoporus and screw rod 28 are by screw-thread fit, and its function is to transmit braking force, as Figure 10.
Reference seat 26 is ironcastings, and its function is to transmit braking force and braking displacement, as Figure 11.
Driven spindle 27 is step cylindrical bodys, and endoporus and screw rod 28 are by screw-thread fit, and its function is to transmit braking force, as Figure 12.
Screw rod 28 is a kind of screw rods, and its function is to promote push pedal 40, transmits braking force, as Figure 13.
Gear 29 is a kind of mechanical gears, and its function is to transmit rotation, as Figure 14.
3, return spring 30
Described return spring 30 is cylindrically coiled springs, and its function provides the returning place force of the reference seat 26 of rotating assembly 20, as Fig. 1.
4, push pedal 40
Push pedal 40 is a kind of dull and stereotyped stamping part, and its function is to increase area of contact between screw rod 28 and the interior friction plate 50, as Figure 15.
5, interior friction plate 50, outside friction disc 70
Inside and outside friction plate the 50, the 70th, by the tablet that friction material and steel backing are formed, its function is the frictional force between increase and the brake disc 60, belongs to conventional general part, as Fig. 1.
6, brake disc 60
Brake disc 60 is cast iron revolving parts, and its function provides one of braking force friction pair, belongs to conventional general part, as Fig. 1.
7, support 80
Support 80 is a kind of ironcastings, and its function is supporting caliper body 90 and places inside and outside friction plate 50,70, belongs to conventional general part, as Fig. 1.
8, caliper body 90
Caliper body 90 is a kind of cast iron structural members, and its function is to bear the braking counter-force, for other functor provides assembly space, belongs to conventional general part, as Fig. 1.
Claims (5)
1. a floating tong type bipushing rod pneumatic disk brake comprises friction plate (50), brake disc (60), outside friction disc (70), support (80) and caliper body (90) in the conventional general part;
It is characterized in that:
Also comprise pressure arm assembly (10), rotating assembly (20), return spring (30), push pedal (40);
From right to left, pressure arm assembly (10), rotating assembly (20), return spring (30), push pedal (40), interior friction plate (50), brake disc (60), outside friction disc (70), support (80) and caliper body (90) are arranged in order;
Described pressure arm assembly (10) comprises pressure arm (11), fulcrum cylinder (12), little needle roller pair (13), big needle roller pair (14), shift fork (15);
Described rotating assembly (20) comprises adjusts cover (21), big torsion spring (22), turning collar (23), little torsion spring (24), active rotating shaft (25), reference seat (26), driven spindle (27), screw rod (28), gear (29);
Axle on the reference seat (26) cooperates with clamp (90) endoporus, and return spring (30) is among reference seat (26) axle endoporus, clamp (90) endoporus, supports reference seat (26); Pressure arm assembly (10) matches with reference seat (26) by big needle roller pair (14), is pressed in clamp (90) cavity by return spring (30); Support (80) constitutes the floating tong type structure with clamp (90) by pin rod, and interior friction plate (50) and outside friction disc (70) place on support (80) attachment face; Push pedal (40) links together with screw rod (28), friction plate (50) in fitting.
2. by the described floating tong type bipushing rod pneumatic disk brake of claim 1, it is characterized in that pressure arm assembly (10) is:
Be connected by little needle roller pair (13) between pressure arm (11) and the fulcrum cylinder (12), be connected by big needle roller pair (14) between the reference seat (26) of pressure arm (11) and rotating assembly (20), pressure arm (11) is provided with shift fork (15);
Described pressure arm (11) is a kind of boosting lever, constitutes cam mechanism with fulcrum cylinder (12);
Described fulcrum cylinder (12) is the cylindrical body of one of a kind of vertical excision;
Described little needle roller pair (13) is a kind of semi-circular cylindrical needle roller pair;
Described big needle roller pair (14) is a kind of semi-circular cylindrical needle roller pair;
Described shift fork (15) is a kind of needle roller.
3. by the described floating tong type bipushing rod pneumatic disk brake of claim 1, it is characterized in that rotating assembly (20) is:
Adjust between cover (21) and the turning collar (23) and adopt big torsion spring (22) to be connected, the little torsion spring of employing (24) is connected between turning collar (23) and the active rotating shaft (25); Adopt the axis hole fit system to connect between the reference seat (26) of driving and driven rotating shaft (25,27) and rotating assembly (20); Screw rod (28) adopts screw-thread fit with driving and driven rotating shaft (25,27);
Described adjustment cover (21) is a kind of revolving part;
Described big torsion spring (22) is a kind of rectangular cross-section torsion spring;
Described turning collar (23) is a kind of revolving part;
Described little torsion spring (24) is a kind of rectangular cross-section torsion spring;
Described active rotating shaft (25) is a kind of step cylindrical body, and endoporus and screw rod (28) pass through screw-thread fit;
Described reference seat (26) is a kind of ironcasting;
Described driven spindle (27) is a kind of step cylindrical body, and endoporus and screw rod 28 pass through screw-thread fit;
Described screw rod (28) is a kind of screw rod;
Described gear (29) is a kind of mechanical gear.
4. by the described floating tong type bipushing rod pneumatic disk brake of claim 1, it is characterized in that:
Return spring (30) is a kind of cylindrically coiled spring.
5. by the described floating tong type bipushing rod pneumatic disk brake of claim 1, it is characterized in that:
Push pedal (40) is a kind of dull and stereotyped stamping part.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2006200997798U CN201027853Y (en) | 2006-11-06 | 2006-11-06 | Floating pincers type double-push rod barometric disk brake |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2006200997798U CN201027853Y (en) | 2006-11-06 | 2006-11-06 | Floating pincers type double-push rod barometric disk brake |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201027853Y true CN201027853Y (en) | 2008-02-27 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2006200997798U Expired - Fee Related CN201027853Y (en) | 2006-11-06 | 2006-11-06 | Floating pincers type double-push rod barometric disk brake |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201027853Y (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103511521A (en) * | 2013-09-24 | 2014-01-15 | 深圳市特尔佳科技股份有限公司 | One-way clutch used for clearance adjustment |
| CN104088935A (en) * | 2014-07-25 | 2014-10-08 | 武汉元丰汽车零部件有限公司 | Air pressure disc brake pressure arm with bearing limiting structure |
| CN104728312A (en) * | 2015-01-27 | 2015-06-24 | 武汉元丰汽车零部件有限公司 | Integrated clamp pneumatic disc brake of locating block rotation-prevention structure |
| CN105805188A (en) * | 2016-04-11 | 2016-07-27 | 许昌学院 | Floating caliper disc brake |
| CN106151316A (en) * | 2016-08-17 | 2016-11-23 | 中国重汽集团济南动力有限公司 | The disk brake assembly that air chamber is positioned radially |
| CN106594128A (en) * | 2016-12-23 | 2017-04-26 | 武汉元丰汽车零部件有限公司 | Pressure arm with adjustable lever ratio and pneumatic plate type brake |
| CN107120368A (en) * | 2017-05-24 | 2017-09-01 | 武汉元丰汽车零部件有限公司 | A kind of double push rod air-pressure disc brakes of floating tong type radial direction |
| CN110914567A (en) * | 2017-05-26 | 2020-03-24 | 瀚德刹车片产品公司 | Disc brake and brake actuator |
| CN112032225A (en) * | 2020-09-24 | 2020-12-04 | 吉林大学青岛汽车研究院 | Wet-type multi-disc brake with shifting fork force-increasing mechanism and using method thereof |
| CN114704570A (en) * | 2022-04-14 | 2022-07-05 | 武汉元丰汽车零部件有限公司 | Brake mechanism and brake |
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2006
- 2006-11-06 CN CNU2006200997798U patent/CN201027853Y/en not_active Expired - Fee Related
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103511521B (en) * | 2013-09-24 | 2016-05-11 | 深圳市特尔佳科技股份有限公司 | A kind of one-way clutch of adjusting for gap |
| CN103511521A (en) * | 2013-09-24 | 2014-01-15 | 深圳市特尔佳科技股份有限公司 | One-way clutch used for clearance adjustment |
| CN104088935A (en) * | 2014-07-25 | 2014-10-08 | 武汉元丰汽车零部件有限公司 | Air pressure disc brake pressure arm with bearing limiting structure |
| CN104088935B (en) * | 2014-07-25 | 2017-02-15 | 武汉元丰汽车零部件有限公司 | Air pressure disc brake pressure arm with bearing limiting structure |
| CN104728312A (en) * | 2015-01-27 | 2015-06-24 | 武汉元丰汽车零部件有限公司 | Integrated clamp pneumatic disc brake of locating block rotation-prevention structure |
| CN104728312B (en) * | 2015-01-27 | 2017-04-19 | 武汉元丰汽车零部件有限公司 | Integrated clamp pneumatic disc brake of locating block rotation-prevention structure |
| CN105805188A (en) * | 2016-04-11 | 2016-07-27 | 许昌学院 | Floating caliper disc brake |
| CN105805188B (en) * | 2016-04-11 | 2023-09-05 | 许昌学院 | Floating caliper disc brake |
| CN106151316B (en) * | 2016-08-17 | 2018-04-06 | 中国重汽集团济南动力有限公司 | The disk brake assembly that air chamber is positioned radially |
| CN106151316A (en) * | 2016-08-17 | 2016-11-23 | 中国重汽集团济南动力有限公司 | The disk brake assembly that air chamber is positioned radially |
| CN106594128A (en) * | 2016-12-23 | 2017-04-26 | 武汉元丰汽车零部件有限公司 | Pressure arm with adjustable lever ratio and pneumatic plate type brake |
| CN107120368A (en) * | 2017-05-24 | 2017-09-01 | 武汉元丰汽车零部件有限公司 | A kind of double push rod air-pressure disc brakes of floating tong type radial direction |
| CN110914567A (en) * | 2017-05-26 | 2020-03-24 | 瀚德刹车片产品公司 | Disc brake and brake actuator |
| CN110914567B (en) * | 2017-05-26 | 2021-08-27 | 瀚德刹车片产品公司 | Disc brake and brake actuator |
| CN112032225A (en) * | 2020-09-24 | 2020-12-04 | 吉林大学青岛汽车研究院 | Wet-type multi-disc brake with shifting fork force-increasing mechanism and using method thereof |
| CN112032225B (en) * | 2020-09-24 | 2024-03-22 | 吉林大学青岛汽车研究院 | Wet type multi-disc brake with shifting fork force increasing mechanism and using method thereof |
| CN114704570A (en) * | 2022-04-14 | 2022-07-05 | 武汉元丰汽车零部件有限公司 | Brake mechanism and brake |
| CN114704570B (en) * | 2022-04-14 | 2024-01-30 | 武汉元丰汽车零部件有限公司 | Braking mechanism and brake |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080227 Termination date: 20101106 |