GB2049845A - Disc Brakes - Google Patents
Disc Brakes Download PDFInfo
- Publication number
- GB2049845A GB2049845A GB7917075A GB7917075A GB2049845A GB 2049845 A GB2049845 A GB 2049845A GB 7917075 A GB7917075 A GB 7917075A GB 7917075 A GB7917075 A GB 7917075A GB 2049845 A GB2049845 A GB 2049845A
- Authority
- GB
- United Kingdom
- Prior art keywords
- carrier member
- pads
- discs
- disc brake
- rods
- Prior art date
- Legal status (The legal status 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 status listed.)
- Granted
Links
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
- 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
- F16D55/2265—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 the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
- F16D55/22655—Constructional details of guide pins
-
- 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
- F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
- F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
- F16D55/36—Brakes with a plurality of rotating discs all lying side by side
- F16D55/40—Brakes with a plurality of rotating discs all lying side by side actuated by a fluid-pressure device arranged in or one the brake
-
- 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
- F16D65/02—Braking members; Mounting thereof
- F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
- F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
- F16D65/095—Pivots or supporting members therefor
- F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
- F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
- F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
- F16D65/0977—Springs made from sheet metal
-
- 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
- F16D2055/0004—Parts or details of disc brakes
- F16D2055/0062—Partly lined, i.e. braking surface extending over only a part of the disc circumference
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
A disc brake assembly (1) for use on a heavy commercial vehicle having two discs (3, 4) mounted for sliding movement on a hub (7), along the axis of rotation of the hub (7) comprises an integrally formed carrier member (10) which is fixed to the vehicle and comprises a central web (12) which is located between the discs (3, 4) and end members (13, 14) which span the peripheries of the discs. Brake pads 9A-9D are mounted on the carrier member such that drag torque forces are transfered directly to the carrier member (10) via shoulders (19 or 20) formed thereon. A clamping mechanism (27) is mounted on the carrier member and comprises an actuator assembly (28) and a beam (29) interconnected by rods (30, 31) to provide the necessary clamping forces, but it does not receive any drag torque. Anti-rattle springs (24 or 25) are provided for the pads in alternative arrangements (Figures 1-4, Figures 5, 6). <IMAGE>
Description
SPECIFICATION
Disc Brakes
This invention relates to disc brakes for
vehicles, and more particularly to a disc brake
assembly suitable for use on a heavy commercial
vehicle.
Whilst disc brakes have various well
recognised advantages, they do suffer from the
disadvantage that because of the relatively small
area of friction lining material which is in contact with the disc and because of the absence of any self-servo effect produced by rotation of the axle
being braked, very large clamp forces must be
used to force the friction material against the disc in order to produce an acceptable braking torque.
This problem is particularly acute in the case of commercial vehicles where a high braking torque is required.
In an attempt to increase the braking torque produced by a given clamp force, disc brake assemblies have been proposed in which two discs are provided. Such assemblies are described in British Patent Specifications 1,035,279 and
1.396,503, and in West Germany
Offenlegungsschrift 2,165,817. However, each of these proposals suffer from various disadvantages. In the case of 1,035,279 all the torque forces applied to the pads during braking are transferred to the chassis of the vehicle via the clamping mechanism. The clamping mechanism cannot be produced economically with sufficient rigidity to absorb such torque forces without torsional distortion. Such torsional distortion leads to uneven pad wear and unsatisfactory braking performance.The problem is aggravated by the three piece construction of the clamping member which necessitates the use of bolts or the like to hold the clamping member assembled.
The bolts are loaded in shear by the torsional forces transmitted via the clamping member. The bolts must accordingly be of large dimensions and in any event tend not to produce a highly rigid structure.
In the case of 1,396,503 the torsionai twist problem described above also exists. Further, unless the clamping member is formed in two parts which are joined together it is difficult to machine the hydraulic cylinders. Accordingly the problems of connecting bolts outlined above also exist. Finally, because the torque forces on the brake pads are transferred to the clamping member by pins loaded in shear, these pins must be of substantial dimensions.
In the case of DOS 2,165,817 the torsional twist problem is again encountered. Further, although a clamping structure of one-piece construction is illustrated this would be extremely difficult to produce economically because of the difficulty of machining the hydraulic cylinders.
According to one feature of the present invention there is provided a disc brake assembly for a vehicle, comprising: two brake discs secured to a hub of the vehicle, the discs being rotationally fast with the hub but slidable along the axis of rotation of the hub; a carrier member fixed to the body of the vehicle and including a web located between and parallel to the disc, and end members secured to the web and spanning the peripheries of the discs; friction pads located on the carrier member for engaging the discs; and a clamping mechanism distinct from and mounted on the carrier member for clamping the friction pads into engagement with the disc, the arrangement being such that during braking torque forces on the pads are transmitted from the pads to the carrier with substantially no torque forces transmitted from the pads to the clamping mechanism.
In an embodiment of the present invention in which the torque forces on the pads during braking are transferred directly to the carrier member, and the clamping member serves only a clamping function without transferring any torque forces, the carrier member can be designed to provide adequate support for the torque forces without torsional distortion. By relieving the clamping member of any torsional loading the design of the clamping member is simplified. The torsional rigidity provided by the carrier member ensures even pad wear, increasing the service interval between pad replacement.
The above and further features and advantages of the invention will become clear from the following description of an embodiment thereof, given by way of example only, reference being had to the accompanying drawings, wherein:
Figure 1 is a cross sectional view of part of a disc brake assembly, the assembly being part of the front axle assembly of a heavy commercial vehicle with portions of the axle assembly illustrated in broken lines;
Figure 2 is a plan view of the disc brake assembly of Figure 1;
Figure 3 is a view substantially along the line Ill-Ill of Figure 2;
Figure 4 illustrates a portion of the assembly of
Figures 1 to 3; and
Figures 5 and 6 illustrates a modified brake pad retaining structure.
Referring to Figures 1-4 the disc brake assembly 1 comprises two discs 3,4 slidably mounted via splines 5 on a mounting member 6 secured to the hub 7 of the axle assembly. The splines 5 provide that the discs 3,4 are rotationally fast with the hub, but can slide relative to the hub in the direction of the axis of rotation A of the hub. Each disc 3, 4 has two friction surfaces 8A, 8B, 8C, and 8D which are engaged in use by respective brake pads 9A, 9B, 9C and 9D.
As best illustrated in Figure 2 the pads 9A-D are mounted on a carrier member 10 which is rigidly fixed to the chassis of the vehicle by flanges 11. The carrier member 10 includes a central web 1 2 which is disposed between and is parallel to the discs 3, 4. The web 1 2 is integrally formed with end members 1 3, 14. The end members 13, 14 each include a circumferentially extending portion 1 5 which spans the periphery of the discs 3, 4 and side portions 1 6, 1 7 which extend parallel to the central web 1 2 inwardly along a portion of the outermost face of the discs 3,4.
The central web 12 and side portions 1 6, 1 7 of the carrier member 10 are formed with shoulders
1 9, 20 between which the backing plates of the pads 9A-D are a sliding fit. Thus, when the wheel is rotating in one direction and the brakes are
applied, all torque or drag forces induced on the
pads are transferred by the pad backing plates to the shoulders 1 9. When the wheel is rotating in the opposite direction and the brakes are applied, all such forces are transferred to the shoulders 20.
The carrier member transfers the torque forces from the shoulders 1 9, 20 to the chassis of the vehicle via the flanges 11.
The pads 9A-D are retained in position on the
carrier member by retaining bars 21 secured to the carrier member 12 by screws 22. The bars 21
engage slots 23 in the backing plates of the pads 9A-D whereby the pads can slide along the bars
21. A spring 24 is trapped between each bar 21
and the carrier member 10 in order to bias the
outer surface of each slot 23 into engagement
with its associated bar 21 and thereby prevent the pads from rattling. In the alternative embodiment shown in Figures 5 and 6 the spring 24 is replaced by a spring 25 secured to the
outer surface of the bar 21 by means of screws
26. In this case the spring 25 biases the pads
outwardly so that the inner surface of each slot
23 engages a respective bar 21.
The assembly includes a clamping mechanism
27 comprising an actuator assembly 28 connected to a beam 29 by means of rods 30, 31.
The actuator assembly is supported on the carrier member for sliding movement in the direction of the axis of rotation of the hub by means of a pin
32 located adjacent each of the rods 30, 31 as described in more detail hereinafter with reference to Figure 4. Similarly, the beam 29 is supported
on the carrier member for sliding movement by
means of pins 33 located adjacent the rods 30,
31 again as described in more detail hereinafter in
relation to Figure 4.
The actuator assembly comprises two pistons 34 mounted in respective cylinders 35 such that
upon application of hydraulic pressure to the
cylinders 35 the pistons 34 move towards the
adjacent disc 4. The pistons 34 engage the back plate of pad 9D causing the pad 9D to move into contact with the disc 4. This in turn causes the disc 4 to slide on splines 5 to bring friction surface 8C into engagement with pad 9C. Since pad 9C is supported on the carrier member 10 which is itself fixed to the chassis of the vehicle a reaction force will at this time be produced on the body of the actuator assembly 28. This reaction force is transmitted by rods 30,31 to the beam 29 which applied the pad 9A against the friction surface 8A of the disc 3. The disc 3 then slides on splines 5 to bring the friction surface 8B into contact with the pad 9B which again rigidly supported on the carrier member.It will be seen therefore that the application of hydraulic pressure to the cylinders 35 causes the discs 3, 4 to be clamped between the fixed pads 9B, 9C and the movable pads 9A, 9D. As explained above, the torque forces produced on the pads 9A-D due to rotation of the discs 3, 4 is transferred via the shoulders 1 9 or 20 to the carrier and thence to the chassis of the vehicle. No torque forces are transferred to the clamping mechanism 27, and the sole function of the clamping mechanism is to provide the clamping force necessary to bring the pads into frictional engagement with the discs.
Referring now to Figure 4 it will be seen that the actuator assembly 28 and beam 29 are flexibly mounted on the carrier 10 by means of pins 32, 33 which are rigidly fixed to the carrier 10 and slidably engaged bores formed respectively in the actuator assembly 28 and beam 29. Resilent rings 36 are placed between the pins 32, 33 and their respective recesses in order to permit some flexibility of the position of the actuator assembly 28 and beam 29 relative to the carrier 10. Since the weight of the clamping assembly is supported by the pins 32, 33 on the carrier member the rods 30, 31 can pass through clearance bores 37 formed in the carrier member 10 and are not required to support the weight of the beam 29 or actuator assembly 28. By placing the axes of the rods 30, 31 in the plane of the action of the pistons 34, the rods 30, 31 are loaded purely in tension during braking.The rods can accordingly be designed with a view to taking only tension loading.
It will be appreciated that because the rods 30, 31 are located circumferentiaily outside of the pads 9A-D, and indeed nothing spans the periphery of the discs in the zone of the pads, the pads may easily be inspected to determine the extent of wear of the friction lining material, and can readily be replaced simply by removing the bars 21 and withdrawing the pads radially.
It will be noted that in the above described design all the torque forces are transferred to the vehicle chassis via a carrier member 10 having a substantial radial dimension. The central web 12 is integral with the side portions 1 6, 1 7 to form a rigid structure. This structure, with the addition of the integrally formed side portions 1 6, 1 7 forms a rigid box-like member which is well able to withstand the torsional stresses applied to it in
use. Very iittle torsional deflection of the carrier
member occurs in use. The carrier member may
be integrally formed by any suitable process, for
example casting. By freeing the clamping
mechanism of any torsional loads a simplified
design of clamping structure can be provided in which the connection between opposite sides of the discs is provided by rods 30 which need not
support the weight of the actuator assembly 28
and beam 29, and which are loaded purely in
tension when the brakes are applied.
Claims (10)
1. A disc brake assembly for a vehicle,
comprising: two brake discs secured to a hub of the vehicle, the discs being rotationally fast with the hub but slidable along the axis of rotation of the hub; a carrier member fixed to the body of the vehicle and including a web located between and parallel to the discs, and end members secured to the web and spanning the peripheries of the discs; friction pads located on the carrier member for engaging the discs; and a clamping mechanism distinct from and mounted on the carrier member for clamping the friction pads into engagement with the discs, the arrangement being such that during braking torque forces on the pads are transmitted from the pads to the carrier with substantially no torque forces transmitted from the pads to the clamping mechanism.
2. A disc brake assembly according to claim 1 wherein the clamping mechanism comprises an actuator assembly located on one side of the carrier member and a beam located on the other side of the carrier member, the actuator assembly and the beam being interconnected by rods which pass through the carrier member.
3. A disc brake assembly according to claim 2 wherein the actuator assembly and the beam are each flexibly mounted on the carrier member, and the rods pass through clearance holes in the carrier member.
4. A disc brake assembly according to claim 3 wherein the flexible mounting of the actuator assembly is provided by pins which are fixed to one of the carrier member and the actuator assembly adjacent the rods and extend into clearance holes in the other of the carrier member and the actuator assembly, and wherein the flexible mounting of the beam is provided by pins which are fixed to one of the carrier member and the beam adjacent the rods and extend into clearance holes in the other of the carrier member and the beam, resilient means being interposed between each pin and its associated clearance hole.
5. A disc brake assembly according to any of claims 2 to 4 wherein only two rods interconnect the beam and the actuator assembly, the rods being located on circumferentially opposite sides of brake pads and substantially in the plane of action of the actuator assembly.
6. A disc brake assembly according to any preceding claim including securing means securing the friction pads to the carrier, the securing means being releasable to permit removal of the friction pads radiaily outwardly from the carrier member whilst the clamping mechanism remains in its working position.
7. A disc brake assembly according to any preceding claim wherein the carrier member includes side portions which extend from the end members parallel to the web along the side of each disc remote from the web.
8. A disc brake assembly according to claim 7 wherein shoulders are formed on the side portions against which associated brake pads abut during braking to transfer torque forces to the carrier member.
9. A disc brake assembly according to any preceding claim wherein the carrier member is integrally formed.
10. A disc brake assembly, substantially as hereinbefore described with reference to and as shown in the accompanying drawings.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB7917075A GB2049845B (en) | 1979-05-16 | 1979-05-16 | Disc brakes |
| FR8011020A FR2456884A1 (en) | 1979-05-16 | 1980-05-16 | DISC BRAKE FOR VEHICLE |
| JP6518780A JPS55155929A (en) | 1979-05-16 | 1980-05-16 | Disc brake assembly |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB7917075A GB2049845B (en) | 1979-05-16 | 1979-05-16 | Disc brakes |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB2049845A true GB2049845A (en) | 1980-12-31 |
| GB2049845B GB2049845B (en) | 1983-04-27 |
Family
ID=10505200
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB7917075A Expired GB2049845B (en) | 1979-05-16 | 1979-05-16 | Disc brakes |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS55155929A (en) |
| FR (1) | FR2456884A1 (en) |
| GB (1) | GB2049845B (en) |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2541742A1 (en) * | 1983-02-25 | 1984-08-31 | Dba | BRAKE SYSTEM COMPRISING AT LEAST ONE SLIDING BRAKE DISC AND BRAKE DISC FOR SUCH A BRAKING SYSTEM |
| FR2548303A1 (en) * | 1983-06-30 | 1985-01-04 | Dba | IMPROVEMENTS IN MULTIDISK BRAKES |
| FR2548302A1 (en) * | 1983-06-30 | 1985-01-04 | Dba | IMPROVED MULTIDISC BRAKE |
| US4529067A (en) * | 1983-08-31 | 1985-07-16 | Rockwell International Corporation | Multiple disc brake |
| WO2000009901A1 (en) | 1998-08-15 | 2000-02-24 | Federal-Mogul Technology Limited | Disc brake pad assembly |
| US6223863B1 (en) | 1996-12-12 | 2001-05-01 | Federal-Mogul Technology Limited | Disc brake suspension for improved turning circle |
| WO2001033096A1 (en) * | 1999-11-04 | 2001-05-10 | Delphi Technologies Inc. | Device for retaining friction linings in a disc brake |
| US6244391B1 (en) | 1996-12-12 | 2001-06-12 | Federal-Mogul Technology Limited | Disc brake system with ABS |
| US6247560B1 (en) | 1996-12-12 | 2001-06-19 | Federal-Mogul Technology Limited | Slidable brake disc system |
| US6298953B1 (en) | 1996-12-12 | 2001-10-09 | Delphi Technologies, Inc. | Disc brake |
| WO2001098681A1 (en) * | 2000-06-21 | 2001-12-27 | Haldex Brake Products Ab | Spot-type disc brake with fixed caliper |
| CN111396471A (en) * | 2020-02-28 | 2020-07-10 | 四川宏华石油设备有限公司 | Braking device |
| CN114658778A (en) * | 2022-03-31 | 2022-06-24 | 长沙泊呈科技有限公司 | Brake cylinder and disc brake device provided with same |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2549179B1 (en) * | 1983-07-13 | 1989-02-24 | Dba | DISC BRAKE WITH REMOVABLE CALIPER REINFORCEMENT ARM |
| JP4863963B2 (en) * | 2007-10-18 | 2012-01-25 | 曙ブレーキ工業株式会社 | Multi-disc disc brake device |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1212367B (en) * | 1963-11-09 | 1966-03-10 | Teves Kg Alfred | Disc brake |
| JPS507701B1 (en) * | 1968-10-01 | 1975-03-28 | ||
| GB1430649A (en) * | 1973-06-05 | 1976-03-31 | Girling Ltd | Disc brakes |
| GB1575513A (en) * | 1976-04-01 | 1980-09-24 | Girling Ltd | Disc brake calipers |
-
1979
- 1979-05-16 GB GB7917075A patent/GB2049845B/en not_active Expired
-
1980
- 1980-05-16 FR FR8011020A patent/FR2456884A1/en active Granted
- 1980-05-16 JP JP6518780A patent/JPS55155929A/en active Pending
Cited By (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2541742A1 (en) * | 1983-02-25 | 1984-08-31 | Dba | BRAKE SYSTEM COMPRISING AT LEAST ONE SLIDING BRAKE DISC AND BRAKE DISC FOR SUCH A BRAKING SYSTEM |
| EP0117815A1 (en) * | 1983-02-25 | 1984-09-05 | BENDIX France | Braking-system with at least one sliding brake-disc and brake-disk for such a braking-system |
| US4540067A (en) * | 1983-02-25 | 1985-09-10 | Societe Anonyme D.B.A. | Braking system incorporating at least one sliding brake disc and brake disc for such a braking system |
| FR2548303A1 (en) * | 1983-06-30 | 1985-01-04 | Dba | IMPROVEMENTS IN MULTIDISK BRAKES |
| FR2548302A1 (en) * | 1983-06-30 | 1985-01-04 | Dba | IMPROVED MULTIDISC BRAKE |
| EP0130883A1 (en) * | 1983-06-30 | 1985-01-09 | BENDIX France | Multi-disc brakes |
| EP0131496A1 (en) * | 1983-06-30 | 1985-01-16 | BENDIX France | Multi-disc brake |
| US4576255A (en) * | 1983-06-30 | 1986-03-18 | Societe Anonyme D.B.A. | Multi-disc brakes |
| US4605103A (en) * | 1983-06-30 | 1986-08-12 | Societe Anonyme D.B.A. | Multi-disc brake |
| US4529067A (en) * | 1983-08-31 | 1985-07-16 | Rockwell International Corporation | Multiple disc brake |
| US6298953B1 (en) | 1996-12-12 | 2001-10-09 | Delphi Technologies, Inc. | Disc brake |
| US6223863B1 (en) | 1996-12-12 | 2001-05-01 | Federal-Mogul Technology Limited | Disc brake suspension for improved turning circle |
| US6244391B1 (en) | 1996-12-12 | 2001-06-12 | Federal-Mogul Technology Limited | Disc brake system with ABS |
| US6247560B1 (en) | 1996-12-12 | 2001-06-19 | Federal-Mogul Technology Limited | Slidable brake disc system |
| US6371250B1 (en) * | 1996-12-12 | 2002-04-16 | Delphi Technology, Inc. | Disc brake system with ABS |
| WO2000009901A1 (en) | 1998-08-15 | 2000-02-24 | Federal-Mogul Technology Limited | Disc brake pad assembly |
| WO2001033096A1 (en) * | 1999-11-04 | 2001-05-10 | Delphi Technologies Inc. | Device for retaining friction linings in a disc brake |
| WO2001098681A1 (en) * | 2000-06-21 | 2001-12-27 | Haldex Brake Products Ab | Spot-type disc brake with fixed caliper |
| US6705437B2 (en) | 2000-06-21 | 2004-03-16 | Haldex Brake Products Ab | Disc brake |
| CN111396471A (en) * | 2020-02-28 | 2020-07-10 | 四川宏华石油设备有限公司 | Braking device |
| CN114658778A (en) * | 2022-03-31 | 2022-06-24 | 长沙泊呈科技有限公司 | Brake cylinder and disc brake device provided with same |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2456884B1 (en) | 1983-12-30 |
| GB2049845B (en) | 1983-04-27 |
| JPS55155929A (en) | 1980-12-04 |
| FR2456884A1 (en) | 1980-12-12 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |