GB2217409A - Sliding-caliper disk brake - Google Patents

Sliding-caliper disk brake Download PDF

Info

Publication number
GB2217409A
GB2217409A GB8906761A GB8906761A GB2217409A GB 2217409 A GB2217409 A GB 2217409A GB 8906761 A GB8906761 A GB 8906761A GB 8906761 A GB8906761 A GB 8906761A GB 2217409 A GB2217409 A GB 2217409A
Authority
GB
United Kingdom
Prior art keywords
brake
caliper
disk
piston
pressure plate
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
Application number
GB8906761A
Other versions
GB2217409B (en
GB8906761D0 (en
Inventor
Paul Anthony
Wilhelm Schneider
Helmut Jager
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Deutsche Perrot Bremse GmbH
Original Assignee
Deutsche Perrot Bremse GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Deutsche Perrot Bremse GmbH filed Critical Deutsche Perrot Bremse GmbH
Publication of GB8906761D0 publication Critical patent/GB8906761D0/en
Publication of GB2217409A publication Critical patent/GB2217409A/en
Application granted granted Critical
Publication of GB2217409B publication Critical patent/GB2217409B/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • 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
    • F16D2055/007—Pins holding the braking members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid 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
    • F16D2121/00—Type of actuator operation force
    • F16D2121/14—Mechanical
    • 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
    • F16D2125/02—Fluid-pressure mechanisms
    • F16D2125/06—Pistons
    • 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

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Description

9 i 2217409 Mechanically actuatable sliding-caliper disk brake The
invention relates to a mechanically actuatable sliding-caliper disk brake comprising a brake anchor plate, arranged fixed, a caliper which is mounted in the brake anchor plate so as to be displaceable parallel to the axis of rotation of the wheel to be braked and has two legs which f it over a brake disk connected rotationally fast to the wheel, a piston which is mounted in the first caliper leg so as to be displaceable parallel to the axis of rotation of the wheel and is connected to a pressure plate, a first brake shoe which is arranged on the pressure plate and carries a brake lining which can be brought into contact with one side of the brake disk, a mechanically actuatable expanding device which is supported on the piston and on the first caliper leg, a second brake shoe which is arranged on the second caliper leg and carries a brake lining which can be brought into contact with the other side of the brake disk, and guides arranged on the brake anchor plate, for guiding and supporting the two brake shoes.
In the case of a sliding-caliper disk brake of this generic type descr!bed in German Offenlegungsschrift 3,431,773, the pressure plate is connected to the piston via a f it centring arrangement. This fit centring arrangement comprises a cylindrical projection of low height which is arranged concentrically on the end f ace of the piston and engages in a corresponding 2 - is flat cylindrical recess of the pressure plate. The purpose of this f it centring arrangement is to make possible swinging movements of the pressure plate in order to guarantee a full-surface contact of the associated brake lining against the brake disk. This is intended to counteract one-sided wear of the brake lining. However. in the course of the tests carried out, it was found that, under the effect of corrosion, soiling, and deformations due to loading and wear, sliding resistances occur at the brake shoe support, counteracting or preventing uniform lining wear.
The object on which the invention is based is to improve the slidingcaliper disk brake of the generic type in such a way that, under the conditions mentioned, uniform lining wear is forcibly brought about using the positive engagement of the piston in the piston bore.
According to the invention, this object is achieved by the fact that the pressure plate is rigidly connected to the piston.
By virtue of the rigid connection of the piston to the pressure plate, an integral unit is achieved, the centre of rotation of which is shifted during the braking procedure, compared to the known two-part embodiment, towards the lateral brake shoe. support and the brake surface. To be more precise, the centre of rotation is on the one hand shifted from the piston towards the outer edge of the pressure plate-forming a unit with the piston and, on the other hand, shifted 1 8 nearer to the friction surface by the thickness of the pressure plate. The positive engagement present between piston and pressure plate in the piston bore reduces is the torques which f avour oblique wear, the edge pres- sure at the leading piston undergoing no additional increase in the range of normal friction coefficients. However. the positive engagement for its part leads to the considerable advantage that uninfluencable friction coefficient fluctuations and frictional resistance increases cannot have a disadvantageous effect due to the surface pressure reserves, with the result that parallel wear is guaranteed over the whole lining thickness.
A preferred exemplary embodiment of the invention is illustrated in the drawing and is explained in greater detail below.
Fig. 1 shows a partially sectioned plan view of a conventional slidingcaliper disk brake, and Fig. 2 shows a representation which is similar to Fig. 1 but illustrates a sliding-caliper disk brake according to the invention.
The mechanically actuatable sliding-caliper disk brake represented in the drawing comprises a brake anchor plate 1, arranged fixed with respect to the brake disk (not shown), and a caliper 2 mounted in the brake anchor plate so as to be displaceable parallel to, the axis of rotation of the brake disk.
The caliper 2 has two legs 21 and 21 ' f ittin.g over the brake disk. A piston 5 is mounted in the first leg 21 of the caliper 2 so as to be displaceable parallel to the axis of rotation of the brake disk. A mechanically actuatable expanding device which is supported on the piston 5 and on the first caliper leg 2' serves for the displacement of the piston 5. Since the design of this expanding device does not form part of -the subject- matter of the present invention, it need not be explained in greater detail here. However, attention is drawn to the fact that such an expanding device is explaihed in every detail in German Offenlegungsschrift 3,142,799 A f irst and a second brake shoe 3, 4, each of which carries a brake lining 31 and 4 1, respectively, which can be brought into contact with the facing side of the brake disk, are arranged on respective sides of the brake disk. The first brake shoe 3 rests on the second leg 211 of the caliper 2, and the second brake shoe 4 rests on a pressure plate 6. Both brake shoes 3 and 4 are guided laterally in guides 8 of the brake anchor plate 1. These guides absorb the forces arising upon actuation of the brake, which are effective parallel to the brake linings 31, 41. The pressure plate 6 is connected to the piston 5 by a fit centring arrangement 10. This fit centring arrangement 10 comprises a cylindrical projection of low height which is arranged concentrically on the end face of the piston 5 and engages in a corresponding flat cylindrical recess of the pressure plate 6.
When the mechanical expanding device arranged in the f irst leg 21 of the caliper 2 is actuated, the 1 1 c 4 1 piston 5 is moved towards the brake disk, i.e. upwards according to Fig. 1, until the brake lining 41 arranged on the associated second brake shoe 4 comes into contact with the brake disk. As a result of the reaction force produced, the entire caliper 2, together with the expanding device, is shifted relative to the brake anchor plate 1, downwards according to Fig. 1, until the brake lining 31 arranged on the first brake shoe 3 likewise comes into contact with the brake disk.
In the case of the second brake shoe 4, onesided lining wear occurs at the run-in side of the brake disk as a consequence of the operating conditions which are formed by the moment composed of the braking force FB at the brake surface and the distance L'B to the bearing surface of the pressure plate 6 on the piston 5. However, the relatively short axial length of the fit centring arrangement 10 of the pressure plate 6 in the piston 5 makes possible a slight swinging movement of the pressure plate 6, which is intended to counteract one-sided wear of the brake lining 41. However, in tests it has been found that, under the effect of corrosion, soiling, deformations due to loading and wear at the brake shoe support A, a sluggishness arises and the out-of-centre application of force is no longer sufficient to ensure absolutely uniform lining wear.
Fig. I illustrates the forces which arise upon brake actuation, said forces bringing about a swivelling of the subassembly comprising brake lining 41, brake shoe 4 and pressure plate 6 about the point P'. The forces concerned here are the braking force FB act ing on the brake lining 41 and the corresponding supporting force FA as well as the friction force FR which both act on the brake shoe 4. Here, the friction force FR is the product of the supporting f orce FA and the f riction f actor p with respect to the brake anchor plate 1. The f orce FQ with the lever arm 1 q stands in place of the area load which counteracts the forces and moments acting.
Since the sum of all moments must be zero, the following equation is obtained:
I FA x WA - FR x_ 1' - FB x WB + FQ (1q - 11) = 0 or FA x WA - FA x P x 11 - FB x WB + FQ (1q - 11) = 0 In the case of the embodiment according to the invention shown in Fig. 2 of the drawing, in which the pressure plate and the piston are combined to form an integral component 6,, the subassembly comprising the brake lining 41 and brake shoe 4 rotates under the influence of the braking forces about the point P. Since, in this case too, the sum of all moments must be equal to 0. the following equation is obtained:
II FA x LA - FR x 1 FB x LB + FQ (lq - 1) 0 or FA x LA - FA x 1' x 1 FB x LB +FQ (1q - 1) = 0 Since in the case of the known embodiment according to Fig. 1. the centre of rotation P' is very near to the piston axis, a large lever arm lq is computed. This means that the gradient of the area load is shallow and the restoring moment correspondingly low.
ZM F As a result of the fact that, according to the embodiment according to the invention, the centre of rotation P has been shifted towards the brake surface and the brake shoe support A, at equal values for FA, FB and FQ, all operative lever arms have also been reduced.
A small lever arm 1 q indicates a steep rise of the area load, the restoring moment at the same time becomes high, and consequently a very uniform wear over the entire width of the brake lining can be achieved.
As a result of the f act that, in the case of the embodiment according to the invention shown in Fig. 2, the centre of rotation P is shifted further towards the brake surface and the brake shoe support and hence all lever arms are reduced, occurrences of sluggishness at the brake shoe support have a small effect on the uniform lining wear.
Thus, by reason of the operating conditions which are formed by the moment of the braking force FB at the brake surface and the supporting force FA as well as their friction force FRY one-sided lining wear occurs at the disk run-in side. As a consequence, a very much higher countermoment is produced by the extremely out-of-centre application of force in the centre of rotation P. said countermoment counteracting the 0 ne-sided lining wear.
Deviating from the embodiment showni in which the pressure plate and the piston are combined to form an integral component 6, these two parts could also be rigidly connected by means of a joining method. This - a - can be_ accomplished for example, screwing.
by welding or 1 1 - 9

Claims (3)

1. A mechanically actuatable sliding-caliper disk brake comprising a fixedly mounted brake anchor plate, a caliper which is mounted on the brake anchor plate so as to be displaceable parallel to the axis of rotation of the wheel to be braked and has two legs which fit around a brake disk which is connected rotationally fast to the wheel, a piston which is mounted in the f irst caliper leg so as to be displaceable parallel to the axis of rotation of the wheel and is connected to a pressure plate, a first brake shoe which is arranged on the pressure plate and carries a brake lining which can be brought into contact with one side of the brake disk, a mechanically actuatable expanding device which is located between the piston and the first caliper leg, a second brake shoe which is arranged on the second caliper leg and carries a brake lining which can be brought into contact with the other side of the brake disk, and guide means arranged on the brake anchor plate, for guidiorig and supporting the two brake shoes, characterized in that the pressure plate is rigidly connected to the piston.
2. A disk brake as claimed in Claim 1 wherein the pressure plate and the piston are combined as an integral component.
A
3. A mechanically actuatable sliding-caliPer disk brake substantially as hereinbefore described with reference to and as illustrated in Fig. 2 of the accompanying drawings.
W. 1 1 7 Published 1989 atThe Patent Office. State House, 801771 High Holborn, LondonWClR4TP.Furthereopies maybe obtained from The PatentOMoe. Sales BVanch, St Mary Cray. Orpington, Kent BA5 -%RD. Printed by Multiplex techniques Itd. St Mary Cray, Kent, COIL 1/87
GB8906761A 1988-04-11 1989-03-23 Mechanically actuatable sliding-caliper disk brake Expired - Fee Related GB2217409B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE3812037A DE3812037A1 (en) 1988-04-11 1988-04-11 MECHANICALLY ACTUATED SLIDING CALIPER DISC BRAKE

Publications (3)

Publication Number Publication Date
GB8906761D0 GB8906761D0 (en) 1989-05-10
GB2217409A true GB2217409A (en) 1989-10-25
GB2217409B GB2217409B (en) 1992-04-22

Family

ID=6351751

Family Applications (1)

Application Number Title Priority Date Filing Date
GB8906761A Expired - Fee Related GB2217409B (en) 1988-04-11 1989-03-23 Mechanically actuatable sliding-caliper disk brake

Country Status (4)

Country Link
DE (1) DE3812037A1 (en)
FR (1) FR2629887A1 (en)
GB (1) GB2217409B (en)
IT (1) IT1229095B (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015169832A1 (en) * 2014-05-07 2015-11-12 Tmd Friction Services Gmbh Brake piston head for a disk brake device, brake piston, and disk brake device

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4212382C1 (en) * 1992-04-13 1994-02-03 Knorr Bremse Ag Compress air-operated disk brake - is straddled by brake saddle on one side of which is tension device with pivotably located rotary lever
DE102006010754A1 (en) * 2006-03-08 2007-09-20 Haldex Brake Products Ab disc brake
DE102021127938A1 (en) 2021-10-27 2023-04-27 Bayerische Motoren Werke Aktiengesellschaft Brake piston and brake system

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3042152A (en) * 1957-04-01 1962-07-03 Dunlop Rubber Co Fluid actuated disc brakes and housings and friction elements therefor
GB1033158A (en) * 1961-11-04 1966-06-15 Girling Ltd Improvements relating to disc brakes
GB1280568A (en) * 1969-09-01 1972-07-05 Toyota Chuo Kenkyusho Kk Disc brake
GB1341949A (en) * 1971-06-28 1973-12-25 Bendix Corp Disc brake
GB1498007A (en) * 1974-01-22 1978-01-18 Girling Ltd Disc brakes
EP0001762A1 (en) * 1977-11-09 1979-05-16 The B.F. GOODRICH Company Mounting of friction pads in a disc brake

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB761479A (en) * 1954-06-04 1956-11-14 Girling Ltd Improvements in disc brakes for vehicles
DE1725017A1 (en) * 1964-09-23 1976-03-11 Dunlop Holdings Ltd ADJUSTMENT DEVICE FOR A BALL-RAMP BRAKE CONTROL DEVICE
GB1103867A (en) * 1965-11-04 1968-02-21 Teves Kg Alfred Improvements in or relating to slack adjusters for disc brakes
GB1495701A (en) * 1973-12-07 1977-12-21 Twiflex Couplings Industrial disc brakes
GB1595492A (en) * 1977-04-22 1981-08-12 Girling Ltd Brakes
CA1127096A (en) * 1978-12-29 1982-07-06 John A. Urban Wear indicator for disc brakes
DE3142799A1 (en) * 1981-10-28 1983-05-05 Deutsche Perrot-Bremse Gmbh, 6800 Mannheim Mechanically actuated sliding-calliper disc brake
FR2545897B1 (en) * 1983-05-11 1985-08-23 Valeo HYDRAULICALLY CONTROLLED BRAKE PROVIDED WITH A DEVICE AVOIDING AN EXCESSIVE TEMPERATURE RISING OF HYDRAULIC LIQUID
DE3431773A1 (en) * 1984-08-29 1986-03-13 Deutsche Perrot-Bremse Gmbh, 6800 Mannheim MECHANICALLY ACTUATED SLIDING DISC BRAKE

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3042152A (en) * 1957-04-01 1962-07-03 Dunlop Rubber Co Fluid actuated disc brakes and housings and friction elements therefor
GB1033158A (en) * 1961-11-04 1966-06-15 Girling Ltd Improvements relating to disc brakes
GB1280568A (en) * 1969-09-01 1972-07-05 Toyota Chuo Kenkyusho Kk Disc brake
GB1341949A (en) * 1971-06-28 1973-12-25 Bendix Corp Disc brake
GB1498007A (en) * 1974-01-22 1978-01-18 Girling Ltd Disc brakes
EP0001762A1 (en) * 1977-11-09 1979-05-16 The B.F. GOODRICH Company Mounting of friction pads in a disc brake

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015169832A1 (en) * 2014-05-07 2015-11-12 Tmd Friction Services Gmbh Brake piston head for a disk brake device, brake piston, and disk brake device

Also Published As

Publication number Publication date
DE3812037A1 (en) 1989-10-26
FR2629887A1 (en) 1989-10-13
GB2217409B (en) 1992-04-22
GB8906761D0 (en) 1989-05-10
IT8920005A0 (en) 1989-04-04
IT1229095B (en) 1991-07-18

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Legal Events

Date Code Title Description
PCNP Patent ceased through non-payment of renewal fee

Effective date: 19940323