GB1575676A - Disc brake - Google Patents
Disc brake Download PDFInfo
- Publication number
- GB1575676A GB1575676A GB3545777A GB3545777A GB1575676A GB 1575676 A GB1575676 A GB 1575676A GB 3545777 A GB3545777 A GB 3545777A GB 3545777 A GB3545777 A GB 3545777A GB 1575676 A GB1575676 A GB 1575676A
- Authority
- GB
- United Kingdom
- Prior art keywords
- pressure plates
- disc brake
- lever
- eccentric
- centering members
- 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.)
- Expired
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
- F16D55/04—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 moving discs or pads away from one another against radial walls of drums or cylinders
- F16D55/14—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 moving discs or pads away from one another against radial walls of drums or cylinders with self-tightening action, e.g. by means of coacting helical surfaces or balls and inclined surfaces
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
- Regulating Braking Force (AREA)
Description
(54) A DISC BRAKE
(71) We, KLöcKNER-HüMsoLDT-DEuTz AKTIBNGBSELLSCHAFT, a German Body Corporate, of Köln-Deutz, German Federal
Republic, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: This invention relates to a disc brake which, for example, is suitable for use in an agricultural motor vehicle such as a tractor, comprising a housing containing two juxtaposed pressure plates formed with corresponding recesses in their facing surfaces, the bottom surfaces of the recesses being inclined with respect to the planes of the pressure plates, a rolling member in each opposite pair of recesses to keep the pressure plates apart, return springs to urge the pressure plates towards each other, and an actuating device to produce relative rotation between the pressure plates to cause the rolling members to ride up the inclined surfaces of the recesses and force the pressure plates apart against the force of the return springs and into contact with brake discs mountable on a shaft to be braked.
A problem arising in connection with disc brakes of this kind is that, during braking, the forces exerted by one pressure plate on the other pressure plate, which is located by an associated abutment, give rise to tangential frictional forces which prevent the said other plate from rotating freely and thus reduce or eliminate the seTf- energizing effect of the brake. After releasing the brake, these frictional forces again cause difficulty, more particularly in preventing the pressures plates from rotating back to their starting positions. Centering members in the housing, which are constructed with locating surfaces, according to known practice, and the CO-ODerating periDheral surfaces of the pressure plates if corroded after prolonged use of the brakes, mav acquire a friction coefficient which is so high that the resulting: frictional forces jam the brake in the fullv "on" position after the brake pedal has been released.
An aim of the present invention, therefore, is to provide a disc brake of the aforementioned kind which reliably prevents the pressure plates from jamming, the selfenergizing action of the brake being adjustable substantially independently of the period during which the brake has been in use.
To this end the invention provides a disc brake comprising a housing containing two juxtaposed pressure plates formed with corresponding recesses in their facing surfaces, the bottom surfaces of the recesses being inclined with respect to the planes of the pressure plates, a rolling member in each opposite pair of recesses to keep the pressure plates apart, return springs to urge the pressure plates towards each other, an actuating device to produce relative rotation between the pressure plates to cause the rolling members to ride up the inclined surfaces of the recesses and force the pressure plates apart against the force of the return springs and into contact with brake discs mountable on a shaft to be braked, and three centering members spaced around the inside of the housing to engage the peripheries of the pressure plates, one centering member being fixed and the other two being radially movable away from and towards the Deripheries of the pressure plates during application and release of the brake.
The main benefit of this arrangement is in preventing the thick film of rust, which forms as a result of wear of the parts, from jamming the pressure plates in the housing.
This reliability prevents the servo or selfenergizing effect from being interfered with by jamming of the pressure plates.
According to an advantageous optional feature, the radially movable centering members are moved radially to an extent which is dependent upon the amount of movement of the actuating device or the angle of relative rotation between the pressure plates. This feature reliably prevents the pressure plates from jamming even when a very thick film of rust forms. since the radially movable centering members associ ated with the pressure plates are automatically moved at each brake application.
According to another optional feature, the radially movable centering members are in the form of eccentrics which are rotatable.
The main advantage of this feature is that it can be economically brought about by manufacturing the eccentric part by extrusion.
Advantageously, in order substantially to eliminate frictional forces between the eccentrics and the pressure plates, the radially movable centering members are in the form of eccentric rings carried on pins.
According to another optional feature, in oroder to make double use of the radially movable centering members for preventing jerky braking, the radially movable centering members are also constructed as movable abutments for the associated pressure plates.
According to another advantageous optional feature, each eccentric embodies a lever adjacent a projection of the associated pressure plate, the lever forming a movable abutment and being spring-urged towards the projection. The main advantage of the last-mentioned feature is that jerk-free braking, more particularly when the vehicle is turning, is achieved since the movable lever acts as an automatically movable abutment for the pressure plates.
Alternatively, an automatically movable abutment and an automatically movable centering member can be obtained in the same manner if each eccentric is connected to a lever which is directly or indirectly coupled to a projection of the associated pressure plate and/or a tension element of the actuating device.
Other details of the invention will become clear from the following description of the accompanying drawings which show three embodiments of the invention by way of example. In the drawings:
Figure 1 shows in section a disc brake according to the invention, the section being taken transversely of the axis of the shaft to be braked;
Figure 2 is a cross-section through the disc brake of Figure 1, taken on the line Il-Il; Figure 3 is a longitudinal section through a disc brake in which the radiallv movable centering members are mechanically coupled to the pressure plates;
Figure 4 is a ioneitudinal section through a disc brake comprising centering mem boers adjustable by the associated pressure plates; and
Figure 5 is a cross-section of the disc brake of Figure 4. taken on the line V-V.
Figures 1 and 2 show a disc brake cornprising a brake housing l which can be secured bv screws (not shown) to the trans rnission case (not shown) of a tractor.
Housing 1 has a lower fixed centering member 4 for centering two pressure plates 2, 3 which can be rotated and axially moved relative to one another, member 4 having an arcuate surface 5. The facing surfaces 6, 7 of pressure plates 2, 3 have recesses 8 which are opposite one another when the discs are in the neutral position, the bottom surfaces of the recesses being inclined with respect to the planes of the pressure plates.
A rolling member in the form of a ball 9 is disposed in each pair of facing recesses.
Pressure plates 2, 3 are axially urged towards each other by tension return springs 10. The outer surfaces of pressure plates 2, 3 each act on a brake disc 11, each brake disc 11 being mounted via a driving member 12 on a shaft 13 to be braked, in a non-rotatable and axially movable manner.
The faces of the brake discs 11 remote from pressure plates 2, 3 co-operate respectively with a lateral brake surface 14 of housing
I and a lateral brake surface 15 of a cover 16 secured by screws (not shown) to housing 1.
Pressure plates 2, 3 are also radially located via centering members 18 carried in housing 1 equi-angularly spaced around the shaft axis from centering member 4, which engages projections 17, centering members being radially movable and disposed peripherally at angular intervals of 1200, relative to projections 17. Members 18 are each formed by an eccentric sleeve or bush 20 mounted on a pin 19 disposed in housing 1 and cover 16, a lever 21 connected to sleeve 20, and a spring 22 loading the lever. The springs 22 of both the radially movable members 18 are each secured to housing 1 via a locking screw 23. Sleeves 20 are so disposed in housing 1 that when the brake is in the position shown, the sleeves have their maximum radial extension adjacent the pressure plates with respect to the centre of the disc brake.
In order to rotate the two pressure plates 2, 3 relative to one another, each of them is formed with a respective projection 24, 25 carrying a pin 26 connected to a link 27, 28 respectively, the links being pivotably coupled together by a pin 31 and to the forked end 29 of a member 30. Links 27, 28 form a toggle joint in conjunction with threaded member 30 and an actuating rod 32 screwed thereto. The levers 21 of the centering members 18 simultaneously act as abutments and preferably adioin the end faces 33, 34 of proiections 24, 25 respectivelv. End faces 33, 34 are preferably disposed on a radills extending towards Dins 26 of nroiections 24. 25. Actuating rod 32 is sealed from housing 1 by a seal and extends through a pivoted ring 35 and bears on it via nuts 36. The nivoted ring 35 is pivotably mounted in a forked lever 37. One end of lever 37 is supported on a pin 38 in a support bracket 39 of housing 1, while the other end of the lever 37 is connected to the operating rod 40 of a hydraulic brake cylinder 41, there being a tension spring 42 disposed between cylinder 41 and lever 37.
The centering members 18 operate as follows. When the brake is applied, pressure plates 2, 3 are rotated relative to one another via links 27, 28 and projections 24, 25 coupled thereto, the springs 22 and levers 21 loaded thereby rotate the eccentric sleeves 20 proportionally or substantially proportionally to the angles through which pressure plates 2, 3 rotate. As a result of the eccentricity of sleeve 20, which has an eccentricity of approximately one to two thousands of the diameter of pressure plates 2, 3, the radius of the centering members 18, which prevent tilting round the centering abutment 4, is increased by not more than this eccentricity, via lever 21, when the brake is applied. This prevents pressure plates 2, 3 from jamming against the respective centering members 18. When the disc brake is released via the brake cylinder 41, springs 10, 42 and links 27, 28 cause the projections 24, 25 connected thereto to rotate backwards, and springs 22 in conjunction with levers 21 prevent pressure plates 2, 3 from jumping back.
In the arrangement shown in Figure 3, in contrast to that shown in Figures 1 and 2, eccentric sleeves 44 constitute the centering members 43, which form variable abutments for the two pressure plates 2, 3. As before, each sleeve 44 is secured to or is preferably integral with a lever 45. Levers 45 are pivotably coupled by pins 46 to links 47 which have slots 48 engaged by pins 49 also engaging links 27, 28. Eccentric sleeves 44 are so designed and disposed in housing 1, that when the brake is in the released position as shown, sleeves 44 have their greatest radial extension radially towards the centre of the disc brake. Since the eccentric sleeves 44 are automatically coupled by levers 45 to links 27, 28, pressure plates 2, 3 cannot jam even if a very thick film of rust forms and acts on guides 43.
In Figures 4 and 5, the two pressure plates 2, 3 are centered by two movable centering members 50 in addition to the lower fixed centering member. The radially movable centering members 50 also serve as movable abutments for pressure plates 2, 3. Each member 50 is formed by an eccentric shaft 51 mounted in housing 1 and in cover 16, and by a sleeve 52 disposed on the shaft.
Each of the two shafts 51 is non-rotatably secured to a lever 53 which is also loaded by a spring 22. As before, each lever 53 is connected bv a nin 54 to a link 55, each link being pivotably connected by a pin 56 to the link 27 or 28. As before, the eccentric of shaft 51 is constructed so that when the brake is in the shown position, it has its greatest radial extension radially with respect to the centre of the disc brake, so that guides 50 provide the smallest guide clearance between pressure plates 2, 3 and the eccentric. At the same time, shaft 51 is mechanically coupled via lever 53 and links 55 to links 27, 28 respectively, thus ensuring that centering members 50, which prevent each pressure plate 2, 3 respectively from tilting, are moved sufficiently far outwards to prevent pressure plates 2, 3 from jam ming in housing 1.
WHAT WE CLAIM IS:- 1. A disc brake comprising a housing containing two juxtaposed pressure plates formed with corresponding recesses in their facing surfaces, the bottom surfaces of the recesses being inclined with respect to the planes of the pressure plates, a rolling member in each opposite pair of recesses to keep the pressure plates apart, return springs to urge the pressure plates towards each other, an 3actuating device to produce relative rotation between the pressure plates to cause the rolling members to ride up the inclined surfaces of the recesses and force the pressure plates apart against the force of the return springs and into contact with brake discs mountable on a shaft to be braked, and three centering members spaced around the inside of the housing to engage the peripheries of the pressure plates, one centering member being fixed and the other two being radially movable away from and towards the peripheries of the pressure plates during application and release of the brake.
2. A disc brake according to claim 1, in which the radially movable centering members are moved radially to an extent which is dependent upon the amount of movement of the actuating device or the angle of relative rotation between the pressure plates.
3. A disc brake according to claim 1 or claim 2, in which the radially movable centering members are in the form of eccentrics which are rotatable.
4. A disc brake according to claim 3, in which the radially movable centering members are in the form of eccentric rings carried on pins.
5. A disc brake according to any preceding claim, in which the radially movable centering members are also constructed as movable abutments for the associated pressure plates.
6. A disc brake according to claim 5, in which each eccentric embodies a lever adjacent a projection of the associated pressure plate, the lever forming a movable abutment and being spring-urged towards the projection.
**WARNING** end of DESC field may overlap start of CLMS **.
Claims (10)
1. A disc brake comprising a housing containing two juxtaposed pressure plates formed with corresponding recesses in their facing surfaces, the bottom surfaces of the recesses being inclined with respect to the planes of the pressure plates, a rolling member in each opposite pair of recesses to keep the pressure plates apart, return springs to urge the pressure plates towards each other, an 3actuating device to produce relative rotation between the pressure plates to cause the rolling members to ride up the inclined surfaces of the recesses and force the pressure plates apart against the force of the return springs and into contact with brake discs mountable on a shaft to be braked, and three centering members spaced around the inside of the housing to engage the peripheries of the pressure plates, one centering member being fixed and the other two being radially movable away from and towards the peripheries of the pressure plates during application and release of the brake.
2. A disc brake according to claim 1, in which the radially movable centering members are moved radially to an extent which is dependent upon the amount of movement of the actuating device or the angle of relative rotation between the pressure plates.
3. A disc brake according to claim 1 or claim 2, in which the radially movable centering members are in the form of eccentrics which are rotatable.
4. A disc brake according to claim 3, in which the radially movable centering members are in the form of eccentric rings carried on pins.
5. A disc brake according to any preceding claim, in which the radially movable centering members are also constructed as movable abutments for the associated pressure plates.
6. A disc brake according to claim 5, in which each eccentric embodies a lever adjacent a projection of the associated pressure plate, the lever forming a movable abutment and being spring-urged towards the projection.
7. A disc brake according to claim 3,
in which each eccentric is connected to a lever which is directly or indirectly coupled to a projection of the associated pressure plate and/or a tension element of the actuating device.
8. A disc brake according to claim 7, in which each lever connected to the eccentric is coupled via a rod formed with a slot to the projection and/or to the tension element of the actuating device.
9. A disc brake, constructed and arranged substantially as herein described, with reference to and as illustrated in Figures 1 and 2, or Figure 3, or Figures 4 and 5 of the accompanying drawings.
10. A motor vehicle, such as a tractor, fitted with a disc brake according to any preceding claim.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19762638145 DE2638145C2 (en) | 1976-08-25 | 1976-08-25 | Disc brakes, in particular for agricultural vehicles |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| GB1575676A true GB1575676A (en) | 1980-09-24 |
Family
ID=5986266
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB3545777A Expired GB1575676A (en) | 1976-08-25 | 1977-08-24 | Disc brake |
Country Status (2)
| Country | Link |
|---|---|
| DE (1) | DE2638145C2 (en) |
| GB (1) | GB1575676A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4458789A (en) * | 1981-03-14 | 1984-07-10 | Dunlop Limited | Brake assembly for a multi-disc brake including a force multiplying device |
| GB2141192A (en) * | 1983-06-11 | 1984-12-12 | Lucas Ind Plc | Improvements in self-energising disc brakes |
| EP0192396A1 (en) * | 1985-02-13 | 1986-08-27 | LUCAS INDUSTRIES public limited company | Improvements in self-energising disc brakes |
| EP0237158A1 (en) * | 1986-02-07 | 1987-09-16 | LUCAS INDUSTRIES public limited company | Improvements in self-energising disc brakes |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2700669C2 (en) * | 1977-01-08 | 1985-12-19 | Klöckner-Humboldt-Deutz AG, 5000 Köln | Disc brakes, in particular for motor vehicles |
| DE3066214D1 (en) * | 1980-01-04 | 1984-02-23 | Lucas Ind Plc | Improvements in disc brakes for vehicles |
| DE3621787A1 (en) * | 1986-06-28 | 1988-01-07 | Fendt & Co Xaver | DISC BRAKE |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1077077B (en) * | 1958-11-25 | 1960-03-03 | Opel Adam Ag | Automatic adjustment device for sliding or handlebar brakes, especially for motor vehicles |
| DE1239897B (en) * | 1963-08-16 | 1967-05-03 | Girling Ltd | Disc brake |
| DE1630079C2 (en) * | 1967-04-07 | 1974-09-19 | International Harvester Company Mbh, 4040 Neuss | Self-energizing disc brakes for motor vehicles |
-
1976
- 1976-08-25 DE DE19762638145 patent/DE2638145C2/en not_active Expired
-
1977
- 1977-08-24 GB GB3545777A patent/GB1575676A/en not_active Expired
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4458789A (en) * | 1981-03-14 | 1984-07-10 | Dunlop Limited | Brake assembly for a multi-disc brake including a force multiplying device |
| GB2141192A (en) * | 1983-06-11 | 1984-12-12 | Lucas Ind Plc | Improvements in self-energising disc brakes |
| EP0192396A1 (en) * | 1985-02-13 | 1986-08-27 | LUCAS INDUSTRIES public limited company | Improvements in self-energising disc brakes |
| EP0237158A1 (en) * | 1986-02-07 | 1987-09-16 | LUCAS INDUSTRIES public limited company | Improvements in self-energising disc brakes |
Also Published As
| Publication number | Publication date |
|---|---|
| DE2638145A1 (en) | 1978-03-02 |
| DE2638145C2 (en) | 1985-09-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US3701400A (en) | Parking actuator for disc brake | |
| US4031986A (en) | Disk brake construction having stamped support | |
| US3920102A (en) | Disc brake actuating and adjusting mechanism | |
| US3285372A (en) | Self-energization spot type brake systems | |
| US3628639A (en) | Disc brake caliper-mounting means | |
| US20120298457A1 (en) | Disc brake apparatus | |
| US3295636A (en) | Brake mechanism | |
| CA1054957A (en) | Automatic brake adjusting mechanism | |
| US3743060A (en) | Servo action parking brake with rotary actuator | |
| GB1575676A (en) | Disc brake | |
| GB1567478A (en) | Pad-wear compensating device for disc brake | |
| US3703944A (en) | Disk parking and service brake having servo action on parking brake only | |
| EP0027352B1 (en) | Improvements in automatic slack adjusters for vehicle shoe-drum brakes | |
| US3392806A (en) | Disk-brake and adjusting means therefor | |
| US3734242A (en) | Annular, antipodal, relatively-separable brake | |
| US3548976A (en) | Brake shoe bearing means | |
| US4213519A (en) | Disc brake, especially for motor vehicles | |
| US3575266A (en) | Self-adjusting parking brake | |
| JPH06185549A (en) | Machine operation type disc brake | |
| US4623046A (en) | Automatic adjuster for duo-servo internal shoe drum brakes | |
| GB1567345A (en) | Automatic adjusting device for expanding brakes | |
| US3386538A (en) | Internal shoe drum brakes for vehicles | |
| US3807535A (en) | Brake adjusting device | |
| JPH0456905B2 (en) | ||
| US4161238A (en) | Self energizing brake assembly |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PS | Patent sealed | ||
| PCNP | Patent ceased through non-payment of renewal fee |