WO2022139703A2 - A single-piston air disc brake - Google Patents
A single-piston air disc brake Download PDFInfo
- Publication number
- WO2022139703A2 WO2022139703A2 PCT/TR2020/051389 TR2020051389W WO2022139703A2 WO 2022139703 A2 WO2022139703 A2 WO 2022139703A2 TR 2020051389 W TR2020051389 W TR 2020051389W WO 2022139703 A2 WO2022139703 A2 WO 2022139703A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- type
- bearing
- disc brake
- value
- Prior art date
Links
- 230000007246 mechanism Effects 0.000 claims description 40
- 230000033001 locomotion Effects 0.000 claims description 11
- 238000000034 method Methods 0.000 claims description 8
- 230000005484 gravity Effects 0.000 claims description 3
- 238000005266 casting Methods 0.000 claims description 2
- 238000005242 forging Methods 0.000 claims description 2
- 238000009825 accumulation Methods 0.000 claims 2
- 230000035508 accumulation Effects 0.000 claims 2
- 238000013461 design Methods 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 6
- 230000004913 activation Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 238000004458 analytical method Methods 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
Classifications
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- 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
- F16D55/225—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 the braking members being brake pads
- F16D55/226—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 the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
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- 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
- F16D65/183—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 with force-transmitting members arranged side by side acting on a spot type force-applying member
-
- 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
- F16D2121/00—Type of actuator operation force
- F16D2121/02—Fluid pressure
- F16D2121/08—Fluid pressure acting on a membrane-type actuator, e.g. for gas pressure
-
- 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
- F16D2125/00—Components of actuators
- F16D2125/18—Mechanical mechanisms
- F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
- F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
- F16D2125/36—Helical cams, Ball-rotating ramps
-
- 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
- F16D2125/00—Components of actuators
- F16D2125/18—Mechanical mechanisms
- F16D2125/58—Mechanical mechanisms transmitting linear movement
- F16D2125/64—Levers
Definitions
- the present invention relates to a single-piston disc brake used in commercial vehicles and its comprised innovations. Using fewer parts than the number used in the prior art, the subject of the invention relates to the disc brake designed to reduce the complexity of the drive and adjustment mechanism in the closed volume of the caliper housing of the disc brake.
- the caliper housing is connected to the carrier via guide pins.
- the caliper housing can slide on the guide pins and move in the axial direction. In this way, force can be exerted on the pads.
- Inside the caliper housing there is a drive mechanism that can activate the brake by applying compressive force to one of the pads.
- the drive mechanism consists of one or more pistons, a lever and bearing elements that transmit the drive force to the piston by increasing it by variable rates.
- the half bearing which transfers the forces from the lever to the caliper housing and allows the lever to rotate on an axis
- the piston bushing which carries the lateral loads from the thruster piston and allows the thruster piston to move on an axis, is used.
- Patent file US10570970B2 which was introduced to the prior art, contains the inventions with a separate adjustment mechanism next to the piston. These adjustment mechanisms contain a large number of parts and they are in complex structures. In these techniques, the movement of the automatic adjustment mechanism is transmitted to the piston shaft with a gear or chain and the position of the thruster piston is automatically adjusted. In some techniques, the drive lever is seated with a half bearing and an additional bearing element. The geometry of the drive lever is complex and difficult to produce. Assembly labor and maintenance/service costs are high. ( Figure-26)
- the total weight of the brake is important for vehicle manufacturers. For this reason, it is expected that brake manufacturers will optimize the structural parts of the brake in order to increase the braking capacity and increase the crosssection of the load-carrying parts by reducing the weight of the internal mechanism.
- the weight of the internal mechanism parts has been substantially reduced by the present invention.
- This advantage has been made possible by the design of a simpler automatic adjustment mechanism. Instead of a complex and difficult to manufacture drive lever, a lightweight drive lever with simple geometry and easier to manufacture is designed. Thus, it has been ensured that the brake is less costly and easier to manufacture and maintain.
- the air disc brake has a carrier (1). Duty of the carrier is to hold the pins (1.1) guiding to the caliper housing (2). There is a brake disc (4) in the space in the middle of the carrier and pads (3) are placed on both sides of the brake disc (4). Another duty of the carrier is to carry the braking forces caused by the friction of the pads (3) on the brake disc (4). ( Figure-1, Figure-2)
- the invention in question has a thruster piston (5) in the caliper housing (2), an automatic adjustment mechanism (11) operating on the same axis as the piston shaft and integrated on it, a drive lever (6), a half bearing (7) operating with drive lever (6), and a return spring (9). There is also a manual adjustment mechanism (10) that provides motion transmission through a gear.
- the pressure plate (13) used for transmitting the drive force from the drive lever (6) to the piston shaft (11.4) in the caliper housing (2) of the invention is thin and lightweight.
- the force transmission line used in the invention is on a straight line. ( Figure-6, Figure-7)
- a thin pressure plate (13) can be used.
- the roller housing (6.6) on the drive lever (6) includes the roller bushing (20).
- the roller (19) can rotate in the roller bushing (20).
- the pressure plate (13) has a flat roller contact surface (13.1) in contact with the roller (19).
- the main innovation of the invention is the use of a drive lever (6) which has been manufactured by forging or casting method and machined with the bearing channel (6.2) in order to be used with the half bearing (7) used as bearing element.
- the drive forces acting on the drive lever (6) shown in Figure 18 and the stress level generated by these forces on the drive lever (6) are calculated.
- the cross-sectional dimensions of the lever arms (6.3) have been determined as arm width (b) between 7.5 - 9.5 mm and arm depth (c) between 18.5 - 21.5 mm.
- tooth locked washer (14) that is located between the return spring (9) and the driving gear (16) and contacts these two parts.
- the washer (15) contacts the other side of the return spring (9) and the washer (15) and return spring (9) are located over the piston bushing (8).
- the tooth locked washer (14) has been designed with a tooth form. Tooth (14.1) on the tooth locked washer (14) is placed into tooth locked washer channel (2.2) on caliper housing (2) during assembly and rotation movement of locked washer (14) is prevented.
- Tooth locked washer (14) prevents energy storage by shape change of the return spring (9) in rotation direction and generates a friction force as it contacts with driving gear (16).
- the friction force between the tooth locked washer (14) and driving gear (16) is designated by engineering calculations.
- Figure - 14 In this way, the cone clutch (11.7) in the automatic adjustment mechanism (11) can rotate the piston shaft (11.4) and the driving gear (16) while activation of the brake and adjust the operating clearance. Pressure force is transmitted to the cone clutch (11.7) by spring washers (11.5).
- a circlip (11.6) is connected to one end of the spring washer (11.5).
- the wrap spring (11.2) terminates the clutch function, allowing the adjustment ring (11.3) to return independently of the piston shaft (11.4).
- the piston shaft (11.4) does not rotate in the opposite direction and prevents the operating gap from increasing. If the friction force on the contact surface (16.1) between the tooth locked washer (14) and the driving gear (16) is high, the clutch moment of the cone clutch (11.7) is insufficient during braking. The cone clutch (11.7) slips and the adjustment cannot take place. If the friction between the tooth locked washer (14) and the driving gear (16) is insufficient, the piston shaft (11.4) rotates in the opposite direction in the brake release phase and an de-adjustment occurs. All these equilibrium on the automatic adjustment mechanism (11) could be achieved by engineering calculations.
- step (13.2) around the roller pressure surface (13.1).
- This step (13.2) can be circular or slot (22.2).
- the purpose of using the step (13.2) is to prevent the roller (19) from separating from the drive lever (6) due to forces caused by gravity or vibration. If the roller (19) is separated from the drive lever (6) and falls into the caliper housing (2), the braking is eliminated and causes accidents. Therefore, step (13.2) is of great importance.
- the second type automatic adjustment mechanism (21) shown in Figure 17 is connected to the second type pressure plate (22).
- the second type pressure plate (22) has a roller pressure surface (22.1) in contact with the roller (19) and a step (22.2) formed on both sides of the second type pressure plate (22).
- the width of the step (22.2) is between 38 - 40 mm and its length is between 8-18 mm by engineering calculations.
- the bearing seat surface (12.1) shown in Figure 21 and the bearing seat surface (12.1) used for bearing have two bearing tooth locked washer housings (12.2) at the bottom and above. Thanks to this feature, the half bearing (7), which serves as a bearing, is prevented from losing its function by leaving the housing with the effect of vibration forces and gravity by preventing the axial movement from the bearing seat surface (12.1). In addition, an easy-to-machining, low-cost caliper cover (12) is used due to its single bearing feature on the bearing seat surface (12.1).
- piston support (2.1) within the caliper housing (2).
- Figure - 11 It is positioned under the adjustment fork (11.1) for carrying the vertical forces from the drive lever (6).
- the adjustment fork (11.1) is designed in the form of a projection measured in the same radius as the outer radius. Thanks to this feature of the adjustment fork (11.1), the loads on the piston bushing (8) are reduced. Thus, the service life of the piston bushing (8) is extended. It also increases braking efficiency. Since both the linear movement and the rotational movement of the adjustment fork (11.1) are guided by this piston support (2.1), the piston support (2.1) is designed by evaluating engineering analyses and friction calculations.
- Another mode of application of the automatic adjustment mechanism (11) is the use of a larger diameter second type cone clutch (21.9), helix pressure spring (21.5), thrust bearing (21.7), which is the second type automatic adjustment mechanism (21). Due to production tolerances, different forces can be obtained in the same amount of compression in spring washers (11.5). This may cause each mechanism to have different efficiency and different characteristics. This is an undesirable case. Thanks to the helix pressure spring (21.5), the size of the pressure force applied to the second type of cone clutch (21.9) is more stable compared to the use of spring washer (11.5). The effect of the force variability in the second type of cone clutch (21.9) with large diameter (40-45 mm) and small clutch angle (1-5 degrees) can be kept to a minimum.
- the second type of cone clutch (21.9), the second type of adjustment ring (21.3) and the second type of adjustment fork (21.1) have a longer life.
- the second type circlip (21.8) is connected to the end of the second type adjustment fork (21.1).
- the adjustment efficiency is also increased as the compressive force required for the clutch is reduced.
- Piston fixing projections (5.1) and piston fixing channels (3.1) are designed by measuring the maximum manual adjustment moments and by calculating the strength of the parts to prevent damage to the parts in case of excessive moment application.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP20967154.4A EP4264078A2 (en) | 2020-12-25 | 2020-12-25 | A single-piston air disc brake |
PCT/TR2020/051389 WO2022139703A2 (en) | 2020-12-25 | 2020-12-25 | A single-piston air disc brake |
CN202080108141.9A CN117043488A (en) | 2020-12-25 | 2020-12-25 | Single piston air disc brake |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/TR2020/051389 WO2022139703A2 (en) | 2020-12-25 | 2020-12-25 | A single-piston air disc brake |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2022139703A2 true WO2022139703A2 (en) | 2022-06-30 |
Family
ID=82160168
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/TR2020/051389 WO2022139703A2 (en) | 2020-12-25 | 2020-12-25 | A single-piston air disc brake |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP4264078A2 (en) |
CN (1) | CN117043488A (en) |
WO (1) | WO2022139703A2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11971075B1 (en) | 2023-06-23 | 2024-04-30 | Bendix Commercial Vehicle Systems Llc | Single air disc brake tappet with features that mimic multiple tappets |
-
2020
- 2020-12-25 EP EP20967154.4A patent/EP4264078A2/en active Pending
- 2020-12-25 WO PCT/TR2020/051389 patent/WO2022139703A2/en active Application Filing
- 2020-12-25 CN CN202080108141.9A patent/CN117043488A/en active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11971075B1 (en) | 2023-06-23 | 2024-04-30 | Bendix Commercial Vehicle Systems Llc | Single air disc brake tappet with features that mimic multiple tappets |
Also Published As
Publication number | Publication date |
---|---|
CN117043488A (en) | 2023-11-10 |
EP4264078A2 (en) | 2023-10-25 |
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