WO2004007985A1 - Ensemble freins a tambour a rendement eleve pour systeme de freinage d'automobiles - Google Patents

Ensemble freins a tambour a rendement eleve pour systeme de freinage d'automobiles Download PDF

Info

Publication number
WO2004007985A1
WO2004007985A1 PCT/IN2003/000221 IN0300221W WO2004007985A1 WO 2004007985 A1 WO2004007985 A1 WO 2004007985A1 IN 0300221 W IN0300221 W IN 0300221W WO 2004007985 A1 WO2004007985 A1 WO 2004007985A1
Authority
WO
WIPO (PCT)
Prior art keywords
assembly
drum brake
high performance
brake assembly
brake
Prior art date
Application number
PCT/IN2003/000221
Other languages
English (en)
Inventor
Paravasaraju Raajha
Vaidyanathan Lakshmi Narayanan
Original Assignee
Brakes India Limited
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 Brakes India Limited filed Critical Brakes India Limited
Priority to JP2004521073A priority Critical patent/JP2005532518A/ja
Priority to US10/521,043 priority patent/US20060124409A1/en
Priority to AU2003249581A priority patent/AU2003249581A1/en
Priority to GB0502788A priority patent/GB2407350B/en
Publication of WO2004007985A1 publication Critical patent/WO2004007985A1/fr

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
    • F16D51/00—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like
    • F16D51/16—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as brake-shoes pivoted on a fixed or nearly-fixed axis
    • F16D51/18—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as brake-shoes pivoted on a fixed or nearly-fixed axis with two brake-shoes
    • F16D51/20—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as brake-shoes pivoted on a fixed or nearly-fixed axis with two brake-shoes extending in opposite directions from their pivots
    • 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
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/58—Mechanical mechanisms transmitting linear movement
    • F16D2125/64—Levers
    • 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
    • F16D2125/70—Rods

Definitions

  • This invention in general pertains to automobile technology. More particularly this invention pertains to automotive braking system. In particular, this invention relates to the design of a new drum brake assembly for automotive braking purposes.
  • hydraulic drum brake assemblies have increased in size from ⁇ 7" to ⁇ l2" to date catering to the passenger car and utility vehicle applications.
  • duo-servo design has been developed to increase the service & parking brake performance to cater to the requirement. Sensitivity of the duo-servo design to changes in friction level has put limitations on wide acceptance to this design.
  • a drum brake assembly is designed which can substantially increase the brake output torque for a given hydraulic input pressure or reduce the required pipeline pressure to realize the current rated torque compared to the conventional design.
  • This design as explained in the following section overcomes all the above constraints in meeting friction level, pedal efforts, cost and packaging requirements while also providing all the features of a drum brake.
  • a cited PCT/US patent application having patent no WO 96/07833 dated 14/03/96 filed by HINO 3IDOSHA KOGYO KABUSHIKI KAISHA relates to an invention having a rod set up in the inner surface of the rim to effectively reduce the screeching of a brake.
  • a cited European patent application having patent no 95306755 dated 25/03/95 filed by Ford Motor Company relates to an invention of a mass damper for attenuating objectionable noise.
  • a cited European patent application having patent no 95106211 dated 25/4/95 filed by Nisshinbo Industries Inc relates to an invention of a coloured strip for visual indication of the brake lining wear.
  • a cited PCT/US patent application having patent no WO 96/16275 dated 30/5/96 filed by TOKYO BUHIN KOGYO CO LTD., relates to an invention of setting up different natural frequencies for the two shoes to reduce the possibility of a screeching sound.
  • a cited PCT/US patent application having patent no 6513632 dated 04/02/2003 filed up TRW Automotive relates to an invention of an actuator with an electric drive motor and an electronic unit for parking brake actuation.
  • a cited PCT/US patent application having patent no 4646885 dated 3/3/87 filed by FORD Motor Company relates to an invention of a dual drum brake assembly to generate an enhanced brake torque.
  • a cited US patent application having patent no 4332311 dated 1/06/82 filed by Toyota Uidosha Kogyo Kabushiki Kaisha, JP relates to an invention of a shoe hold down, device in a drum brake.
  • Cited PCT/US patent application having patent no WO 92/20938 dated 26/11/92 filed by Automotive Products pic relates to an invention of an adjuster comprising a lever member and pawl member mounted on one brake shoe with a bimetallic strip to prevent adjustment at elevated temperatures.
  • This invention proposes a drum brake assembly for automotive applications, which has various objectives such as to furnish a greater braking force, than normally possible, to handle higher speeds, larger sizes and greater vehicle weights, without any abnormal change in the dimensions or weight associated with the normal, known drum brake assembly.
  • the inventors have made great effort to provide a system, which meets the requirement of the industry and overcome the problem associated in the prior art.
  • a system is provided by which the unutilized space on the leading shoes near the wheel cylinder is utilized so as to enhance the utility of the drum brake assembly for automotive braking system.
  • second aspect and feature of the invention in addition to the first feature of the invention, comprises the utilization of space by employing an additional lever arrangement and connected in such way to the existing iined shoe in order to increase the brake output torque for a given pipe line pressure compared to identical drum brake design.
  • Figure 1 shows elevation of the known drum brake assembly
  • Figure 2 shows an embodiment of the elevation of the proposed drum brake assembly, by way of example and not by way of limitation, of the scope of this invention
  • Figure 3 shows a schematic sketch of the forces acting in the known drum brake assembly
  • Figure 4 shows a schematic sketch of the forces acting in the high performance drum brake design
  • Figure 5 shows a 3D model of the high performance drum brake assembly
  • Figure 6 shows the 3D back view model of the high performance drum brake assembly
  • Figure 7 shows a 3D model of the ciose-up view of the new lever arrangement on the lined leading shoe assembly
  • Figure 8 shows a 3D model of the links used for the ADAMS analysis.
  • Figure 9 shows a graph giving the input-output relationship of the conventional design and the High Performance design during dynamometer test at 25 kph equivalent vehicle speeds.
  • Figure 10 shows a graph giving the input-output relationship of the conventional design and the High Performance design during dynamometer test at 50 kph equivalent vehicle speed.
  • Figure 11 shows a graph giving the input-output relationship of the conventional design and the High Performance design during dynamometer test at 75 kph equivalent vehicle speed,
  • FIG. 1 illustrates the conventional drum brake now in use:
  • the drum brake assembly consists of a backplate (1), lined leading shoe (2), lined trailing shoe (3), wheel cylinder assembly (4), strut assembly (5), handbrake lever (6), shoe hold down springs (7,8) and shoe return springs (9,10).
  • the wheel cylinder assembly (4) is bolted to the backplate (1) and the lined leading shoe (2), iined trailing shoe (3) are assembled onto the backplate with the heip of shoe hold down springs (7,8) and shoe return springs (9,10).
  • FIG. 1 illustrates the High Performance Drum brake assembly of the invention
  • the conventional drum brake assembly has a linear input-output relationship and amplification is attempted either by increasing the wheel cylinder diameter, friction ievel or the brake diameter per se.
  • the salient feature of the invention is to provide a new lever on the leading shoe web whereby the output from the drum brake assembly can be enhanced.
  • the invention envisages utilization of the space on the leading shoe web near the wheel cylinder and connected in such a way to the lined shoe to increase the brake output torque.
  • the new lever (17) is pivoted on the iined leading shoe (19) with one end resting on the wheel cylinder assembly (4) piston (11) and the other end on the strut assembly (15).
  • This new lever (17) touches the wheel cylinder assembly (4) piston (11) instead of the lined leading shoe (19) and receives input from the pressurized wheel cylinder assembly (4).
  • the new lever (17) Upon actuating the wheel cylinder assembly (4), the new lever (17) rotates about its pivot (18) point and pushes the strut assembly (15).
  • the iined trailing shoe (3) now receives two inputs viz., one from the wheel cylinder assembly (4) and the other from the strut assembly (15), which is mechanically actuated by the new lever (17).
  • the reaction from the lined trailing shoe (3) is passed via the strut assembly (15) as an input to the lined leading shoe (19).
  • the combined force from the wheel cylinder assembly (4) and the reaction from the strut assembly (15) acting on the pivot (18) point achieve equilibrium of the new lever (17).
  • This brake design needs to have an auto-adjuster mechanism in place and should be operated through handbrake mechanism or through the service brake during pressure release.
  • Figures 3 & 4 show the input forces from the wheel cylinder assembly (4) acting on the lined leading shoe (19) and lined trailing shoe (3) for the known drum brake assembly and the high performance drum brake assembly.
  • Figures 5,6 and 7 show the 3D models of the high performance drum brake assembly indicating assembly of various parts constituting the invented drum brake assembly.
  • Figure 6 depicts the assembly of the new lever in the brake assembly.
  • Figure 7 gives the close-up view of the iever arrangement on to the lined leading shoe assembly.
  • a simple link model representative of the drum brake assembly is simulated using the software Adams/View 12.0 and is shown in Figure 8.
  • the lined leading shoe and lined trailing shoe are represented by links 100 and 101 respectively. Having grounded the links 100 & 101, the strut (106) is positioned across the links.
  • the new lever (102) is pivoted (103) to the link (100) with one end resting at the wheel cylinder input (104) and the other end resting at the strut input end (105).
  • the above geometry is built in Adams/View 12.0 for kinematic simulation to understand the force transfer mechanism.
  • the new lever (102) is pivoted to the link (100) by means of a revolute joint (108).
  • a translational joint (109) is provided for transfer of force from the new lever (102) to the strut (106).
  • an input force is given to the new lever (102) and also to the link (101) as shown.
  • the output forces are captured at the joint (108) and along the strut (106) axis.
  • the High Performance drum brake assembly for automotive braking system has an additional lever positioned on the leading shoe web and touches the wheel cylinder piston.
  • the High Performance drum brake assembly gives increased braking torque for a given pipe line pressure or needs substantially reduced pipe line pressure to realize the design rated brake torque.
  • Inertia dynamometer test was carried out on the conventional design and also on the high performance design to compare the input-output relationships.
  • Dynamometer test was carried out at different vehicle equivalent speeds and pressure levels. Hydraulic pressures of 20 bar to 80 bar in steps of 10 bar is applied to the drum brake assembly at each speed level and at an initial braking temperature of 80°C. The input hydraulic pressure and the brake output torque at each speed / pressure level is recorded and presented graphically. Figures 9,10 & 11 gives the relationship between input hydraulic pressure and the brake output torque for the conventional design and the high performance design at vehicle equivalents speeds of 50 kph and 75 kph respectively. For the conventional design, the graph indicating the input pressure and the output brake torque is shown with a square legend. For the same test conditions, the output obtained with the novel design is shown with a triangle legend.
  • the output brake torque obtained in the High Performance design is substantially higher than the conventional brakes.
  • High Performance Drum Brake delivers brake torque substantially higher than the existing drum brake assembly, without the necessity of increasing the drum brake size or the wheel size, which results in material savings, cost savings and compactness in packaging.
  • the High Performance drum brake design / assembly can use a low friction iinings to deliver the design rated brake torque.
  • the High Performance drum brake design / assembly can use a smaller wheel cylinder diameter to deliver the design rated brake torque.

Landscapes

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

Abstract

L'invention concerne un ensemble freins à tambour à rendement élevé qui peut augmenter sensiblement le couple de sortie du frein pour une certaine pression hydraulique d'entrée ou diminuer la pression requise dans la tuyauterie afin d'atteindre le couple nominal courant. L'ensemble freins comprend un nouveau levier (17) pivotant sur le segment primaire (19) de façon qu'une extrémité repose sur le piston (11) du cylindre récepteur et que l'autre extrémité repose sur l'ensemble entretoise (15). Le levier touche le piston au lieu du segment primaire et reçoit une entrée du cylindre récepteur pressurisé. Le levier tourne autour de son point de pivotement (18) et pousse l'ensemble entretoise. Le segment secondaire (3) reçoit deux entrées, l'une du cylindre récepteur et l'autre de l'ensemble entretoise. L'action conjointe de l'entrée du cylindre récepteur et de la force de réaction de l'entretoise sur le pivot, entraîne quasiment un doublement de la force exercée sur le segment primaire.
PCT/IN2003/000221 2002-07-11 2003-06-18 Ensemble freins a tambour a rendement eleve pour systeme de freinage d'automobiles WO2004007985A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2004521073A JP2005532518A (ja) 2002-07-11 2003-06-18 自動推進の乗物（ａｕｔｏｍｏｔｉｖｅ）用ブレーキシステムのための高性能ドラムブレーキアッセンブリ
US10/521,043 US20060124409A1 (en) 2002-07-11 2003-06-18 High performance drum brake assembly for automotive braking system
AU2003249581A AU2003249581A1 (en) 2002-07-11 2003-06-18 High performance drum brake assembly for automotive braking system
GB0502788A GB2407350B (en) 2002-07-11 2003-06-18 High performance drum brake assembly for automotive braking system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IN515CH2002 2002-07-11
IN515/MAS/2002 2002-07-11

Publications (1)

Publication Number Publication Date
WO2004007985A1 true WO2004007985A1 (fr) 2004-01-22

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ID=30012260

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IN2003/000221 WO2004007985A1 (fr) 2002-07-11 2003-06-18 Ensemble freins a tambour a rendement eleve pour systeme de freinage d'automobiles

Country Status (3)

Country Link
JP (1) JP2005532518A (fr)
GB (1) GB2407350B (fr)
WO (1) WO2004007985A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20230341018A1 (en) * 2022-04-25 2023-10-26 ZF Active Safety US Inc. Apparatus for drum brake assembly

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE480534C (de) * 1927-07-22 1929-08-03 Cristensen Air Brake Company Zylinder, insbesondere Bremszylinder
US2037432A (en) * 1931-12-31 1936-04-14 Hydraulic Brake Co Braking apparatus
US2232308A (en) * 1939-05-01 1941-02-18 Hydraulie Brake Company Brake
US4332311A (en) 1979-06-12 1982-06-01 Toyota Jidosha Kogyo Kabushiki Kaisha Shoe hold-down device in a drum brake
WO1992020938A1 (fr) 1991-05-15 1992-11-26 Automotive Products Plc Frein a tambour
WO1996007833A1 (fr) 1994-09-02 1996-03-14 Hino Jidosha Kogyo Kabushiki Kaisha Frein a tambour
WO1996016275A1 (fr) 1994-11-19 1996-05-30 Tokyo Buhin Kogyo Co., Ltd. Frein a tambour pour vehicules automobiles
EP0887570A2 (fr) * 1997-06-26 1998-12-30 Akebono Brake Industry Co., Ltd. Frein à tambour
EP1128082A2 (fr) * 2000-02-25 2001-08-29 Nisshinbo Industries, Inc. Dispositif de frein à tambour

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE480534C (de) * 1927-07-22 1929-08-03 Cristensen Air Brake Company Zylinder, insbesondere Bremszylinder
US2037432A (en) * 1931-12-31 1936-04-14 Hydraulic Brake Co Braking apparatus
US2232308A (en) * 1939-05-01 1941-02-18 Hydraulie Brake Company Brake
US4332311A (en) 1979-06-12 1982-06-01 Toyota Jidosha Kogyo Kabushiki Kaisha Shoe hold-down device in a drum brake
WO1992020938A1 (fr) 1991-05-15 1992-11-26 Automotive Products Plc Frein a tambour
WO1996007833A1 (fr) 1994-09-02 1996-03-14 Hino Jidosha Kogyo Kabushiki Kaisha Frein a tambour
WO1996016275A1 (fr) 1994-11-19 1996-05-30 Tokyo Buhin Kogyo Co., Ltd. Frein a tambour pour vehicules automobiles
EP0887570A2 (fr) * 1997-06-26 1998-12-30 Akebono Brake Industry Co., Ltd. Frein à tambour
EP1128082A2 (fr) * 2000-02-25 2001-08-29 Nisshinbo Industries, Inc. Dispositif de frein à tambour

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
pct/us patent application having patent no 4646885 dated 3/3/87
PCT/us patent application having patent no 6513632 dated 04/02/2003

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20230341018A1 (en) * 2022-04-25 2023-10-26 ZF Active Safety US Inc. Apparatus for drum brake assembly

Also Published As

Publication number Publication date
GB2407350A (en) 2005-04-27
JP2005532518A (ja) 2005-10-27
GB0502788D0 (en) 2005-03-16
GB2407350B (en) 2005-11-16

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