WO1995019508A1 - Tambour de frein a structure amortissante et frein en etant equipe - Google Patents
Tambour de frein a structure amortissante et frein en etant equipe Download PDFInfo
- Publication number
- WO1995019508A1 WO1995019508A1 PCT/JP1995/000029 JP9500029W WO9519508A1 WO 1995019508 A1 WO1995019508 A1 WO 1995019508A1 JP 9500029 W JP9500029 W JP 9500029W WO 9519508 A1 WO9519508 A1 WO 9519508A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- ring
- shaped
- brake
- damping member
- vibration
- Prior art date
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
- F16D65/00—Parts or details
- F16D65/0006—Noise or vibration control
-
- 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
- F16D65/10—Drums for externally- or internally-engaging 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/02—Vibration-dampers; Shock-absorbers with relatively-rotatable friction surfaces that are pressed together
-
- 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
- F16D2065/13—Parts or details of discs or drums
- F16D2065/1304—Structure
- F16D2065/1332—Structure external ribs, e.g. for cooling or reinforcement
Definitions
- the present invention relates to a drum brake, and more particularly to a drum brake capable of preventing brake squeal during braking.
- FIG. 8 is a sectional view of a conventional brake drum 20 used for a vehicle.
- the brake drum 20 is formed in a cylindrical shape with a bottom, and a ring-shaped projection 22 is integrally provided near the opening of the outer periphery 21 for reinforcement, and the bottom 25 is a mounting surface.
- FIG. 9 shows a front view of the brake 10 used in combination with the brake drum shown in FIG.
- the brake 10 consists of a wheel cylinder 1, a cover 2, a brake cylinder 3, a brake shoe 3, a lining 4 attached to the shoe 3 and a return spring 6, and is attached at a mounting surface 5. It is attached to the vehicle body using a bolt (not shown) through the hole 5a.
- a bolt not shown
- the hydraulic pressure in the wheel cylinder 1 rises, the brake shoe 3 expands, and the lining 4 presses the inner surface 2 la of the brake drum 20.
- the brake is released, the wheel cylinder is released.
- the brake 1 returns to its original position by the operation of the return spring 1 and the return spring 1.
- a loss factor Y which is a ratio of energy lost per cycle of vibration.
- the loss coefficient Y when the vibration N1 with the amplitude Xo attenuates to the amplitude Xn during the nth vibration is expressed by the following equation.
- the loss coefficient Y is measured for the brake drum, it is possible to know the damping performance of the brake drum, that is, the ease with which the brake drum squeals.
- the conventional brake drum 20 results of the measurements of several shape shown in FIG. 8, the value of the loss factor Y is Atsuta in 1. 0 X 1 0 one 3 from 0. 5 X 1 0-3 .
- the squeal of the brake is caused by both the brake drum 20 and the brake 10.
- the present invention aims to prevent the squeal caused by the brake drum 20, and particularly to improve the vibration damping performance of the brake drum. The purpose is to attenuate the vibration early to prevent squeal. Disclosure of the invention
- the present invention provides a cylindrical portion having a liner pressing inner peripheral surface, a pressure receiving portion formed on the outer periphery of the cylindrical portion, and a vibration damper provided in contact with the pressure receiving portion.
- a brake drum is constituted by the member and a pressing means for pressing the vibration damping member against the pressure receiving portion.
- the pressure receiving portion is composed of a ring-shaped projection formed on the outer periphery of the cylindrical portion and having a wedge-shaped cross section
- the damping member is composed of a pair of left and right ring-shaped semicircles having a two-part structure.
- a ring-shaped recess having a wedge-shaped cross section can be formed on the inner periphery of the body.
- the ring-shaped semicircle is attached to the outer periphery of the cylindrical portion such that the ring-shaped protrusion covers the ring-shaped protrusion and fits into the ring-shaped recess.
- the pressure receiving portion is composed of a ring-shaped concave portion having a wedge-shaped cross section formed on a ring-shaped protrusion on the outer periphery of the cylindrical portion, and a pair of right and left ring-shaped semicircles having a two-part structure of the vibration damping member.
- a ring-shaped projection having a wedge-shaped cross section may be formed on the inner periphery of each semicircle.
- the ring-shaped semicircle covers the ring-shaped recess, and the ring-shaped protrusion is attached to the outer periphery of the cylindrical portion so as to fit into the ring-shaped recess.
- the pressure-receiving portion is constituted by a ring-shaped protrusion formed on the outer periphery of the cylindrical portion, and the vibration-damping member is a cylindrical first vibration-damping member and a second vibration-damping member that sandwich the ring-shaped protrusion from the left and right. It can also be composed of members.
- a drum brake according to the present invention is a cylinder having a lining pressing inner peripheral surface.
- a brake drum including a pressure receiving portion formed on the outer periphery of the cylindrical portion, a vibration damping member disposed in contact with the pressure receiving portion, and pressing means for pressing the vibration damping member against the pressure receiving portion;
- a brake shoe having a lining disposed in opposition to the inner peripheral surface of the lining press; and a wheelchair for expanding the brake shoe to press the lining against the inner peripheral surface of the lining press. It consists of a binder and a binder.
- the outer periphery of the brake drum and the vibration damping member have opposing surfaces that are pressed against each other and come into contact with each other, and the opposing surfaces contact (fit) with a constant surface pressure. Therefore, when vibration occurs on the brake drum during braking, relative slippage occurs on the opposing surface according to the deformation of the brake drum corresponding to the vibration. Since the vibration energy is absorbed by the frictional resistance against the relative slip, the vibration of the brake drum is suppressed and the squeal is prevented.
- FIG. 1 is a sectional view showing a brake drum according to a first embodiment of the present invention
- FIG. 2 is a sectional view and a front view showing a vibration damping member constituting the brake drum
- FIG. 3 is a cross-sectional view showing a brake drum according to a second embodiment of the present invention
- FIG. 4 is a cross-sectional view and a side view showing a damping member constituting the brake drum
- FIG. 5 is a partial cross-sectional view showing a brake drum according to a third embodiment of the present invention
- FIG. 6 is a cross-sectional view showing a vibration damping member constituting the brake drum
- FIG. 7 is an example of vibration of the brake drum.
- Fig. 8 is a sectional view of a conventional brake drum
- FIG. 9 is a front view of the brake device. Example
- FIG. 1 shows a cross section of a brake drum 100 according to a first embodiment of the present invention
- FIG. 2 shows a two-part vibration damping member 30.
- the brake drum 100 is attached to the wheels, while the brake 100 shown in Fig. 9 enters the lining 4 so that the lining 4 faces the inner peripheral surface 11a of the brake drum 100, and moves toward the vehicle body. Fixedly held. Since the structure of the brake 10 is the same as that of the conventional brake and has the structure shown in FIG. 9, its description is omitted.
- the brake drum 100 is made of iron, steel, steel, or the like into a bottomed cylindrical shape, and has a cylindrical portion 1 1 1 1 forming an inner peripheral surface 1 1 a on which the lining 4 is pressed during braking. And a bottom surface 120 serving as a mounting surface to the wheel.
- a projection 1 1 2 having a ring shape and having a width decreasing toward the outer peripheral side is formed, and the projection 1 1 2 constitutes a pressure receiving portion. .
- the damping member 30 is made of steel or the like, and is composed of a pair of left and right ring-shaped semicircles 30a and 30b each having a two-part structure. Sensors 32 and 33 are provided. A wedge-shaped recess 31 is formed in the inner periphery of each of the vibration damping members 30 so as to increase in width toward the inner periphery.
- the vibration damping member 30 is mounted on the outer periphery of the brake drum 100 such that the concave portion 31 having a wedge-shaped cross section covers the projection 111 having the wedge-shaped cross section.
- the left and right damping members are bolted through fastening bolts (not shown) in the bolt holes 32a and 33a formed in 2 and 33.
- the two opposing surfaces 112a and 31a are in contact with a predetermined surface pressure, and a frictional resistance corresponding to the surface pressure acts on the relative slip.
- the vibration energy is absorbed and the vibration is rapidly attenuated. As a result, brake squeal during braking is suppressed.
- the deformation of the brake drum 100 becomes large, and the surface pressure becomes excessive due to the wedge effect accompanying this deformation, so that relative slip does not occur and the vibration is attenuated very little. It is also possible that they will not be able to do so. For this reason, the graphite, molybdenum disulfide, and talc are placed between the opposing surfaces (the wedge-shaped opposing surfaces 112a of the protrusions 112 and the model opposing surfaces 31a of the recesses 31). It is preferable to interpose a friction reducing agent consisting of ultra-fine particles such as powder, which makes relative slippage more likely to occur. The absorption of gears can be increased.
- FIG. 3 shows a cross section of a brake drum 200 according to a second embodiment of the present invention
- FIG. 4 shows a vibration damping member 40 having a two-part structure
- the brake drum 200 comprises a cylindrical portion 211 and a bottom portion 220.
- a ring-shaped protrusion is provided on the outer periphery of the cylindrical portion 211, and the width of the protrusion toward the outer peripheral side is formed on the outer peripheral surface.
- a wedge-shaped recessed portion 2 1 2 is formed to increase the width.
- the concave portions 212 constitute the pressure receiving portion.
- the vibration damping member 40 is composed of a pair of left and right ring-shaped semicircles 40a, 40b having a two-part structure, and mounting flanges 42, 43 are provided at both ends.
- a wedge-shaped cross-section projection 41 whose width decreases toward the inner peripheral side is formed.
- the vibration damping member 40 is mounted on the outer periphery of the brake drum 200 such that the projections 41 enter the recesses 2 12, and port holes 32 a, 33 a formed in the mounting flanges 32, 33. Then, bolt the left and right vibration damping members through a fastening bolt (not shown). As a result, the opposing surface 2 12 a of the recess 2 12 and the opposing surface 41 a of the projection 41 abut at a predetermined surface pressure.
- the vibration generated in the brake drum 200 and the brake 10 during braking is caused by the concave wedge-shaped recess 2 12 of the brake drum 200 and the protrusion of the vibration damping member 40.
- This causes relative slippage on the two opposing surfaces 2 1 2a and 4 1a, and the vibrational energy is absorbed by the frictional resistance to the relative slippage, and this vibration is rapidly attenuated, thereby suppressing brake squeal.
- FIG. 5 A cross section of a brake drum 300 according to a third embodiment of the present invention is shown in FIG. 5, and FIG. 6 shows a first vibration damping member 80 constituting the brake drum 300.
- the brake drum 300 has a cylindrical portion 3 1 1 and a bottom portion 320.
- a ring-shaped and parallelogram-shaped cross-section projection 312 is formed on the outer periphery of the cylindrical section 311, and the projection 312 constitutes a pressure receiving section.
- the damping member includes a cylindrical first damping member 80 shown in FIG. 6 and a ring-shaped second damping member 70.
- the first vibration damping member 80 has a cylindrical shape having a slightly larger inner diameter than the outer shape of the projection 312 except for a flange-shaped pressure receiving portion 80a having an opposing surface 80c on one side. It is formed in a shape having a space, and a female screw 80b is formed on the inner surface of the entrance of the cylindrical space.
- a ring-shaped retainer 81 having a male screw that is screwed into the female screw 80b is screwed into the female screw 80b, enters the cylindrical space, and is fixed.
- the cylindrical portion that forms the cylindrical space in the first vibration damping member 80 becomes a flange portion that connects the flange-shaped pressure receiving portion 80a and the ring-shaped retainer 81.
- the retainer 81 has a plurality of bolt screw holes 81a in which female threads are formed at equal intervals on the circumference.
- the second vibration damping member 70 is a ring-shaped member having a facing surface 70a on one side. After the first damping member 80 is attached to the outer periphery of the brake drum 300 so that the opposing surface 80 c faces the opposing surface 312 a, the cylindrical space of the first damping member 80 is formed. The second vibration damping member 70 is inserted therein. At this time, the opposing surface 70a of the second vibration damping member 70 opposes the opposing surface 312a of the projection 312.
- the retainer 81 is screwed into the first vibration damping member 80, and the bolt 71 is screwed into the port screw hole 81a.
- the tightening bolt 71 protrudes into the cylindrical space and abuts against the side surface of the retainer 81, and by further tightening this bolt 71, the first vibration damping member 80 and the second With the vibration damping member 70, the mechanical unit 3 12 is sandwiched from both left and right sides.
- the opposing surface 80 c of the first vibration damping member 80 and the opposing surface 7 0 a contacts the left and right opposing surfaces 3 1 2 a of the projections 3 1 2 respectively.
- the contact surface pressure at this time is determined by the tightening force of the tightening port 71, and since the opposing surface is inclined, the wedge effect chestnut increases the surface pressure.
- the vibration generated in the brake drum 300 and the brake 10 during braking is caused by the opposing surface 312a of the projection 312 of the brake drum 300 and the second Relative slip occurs between the opposing surfaces 80c, 70a of the first and second damping members 80, 70, and vibration energy is absorbed by frictional resistance to the relative slip, and this vibration is rapidly attenuated.
- the brake squeal is suppressed. Also in this case, it is preferable to interpose a friction reducing agent between the two opposing surfaces.
- the value of Y in a state of not intervening friction reducing agent, 2 X 1 0_ 3 from 1 1 X 1 0_ is 3, when interposing a friction dark small agent to the value of Y was from 5 X 1 0-3 1 2 X 1 0_ 3.
- the loss coefficient of the conventional brake drum is from 0.5 X 10-3 to 1.0 X 10-3, it is clear that the vibration damping effect of the present invention is very large. Therefore, when the brake drum of the present invention is used, brake squeal during braking can be significantly suppressed.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP95905766A EP0688969A4 (en) | 1994-01-12 | 1995-01-12 | BRAKE DRUM WITH DAMPER AND DRUM BRAKE EQUIPPED WITH SUCH A DRUM |
KR1019950701174A KR950704625A (ko) | 1994-01-12 | 1995-01-12 | 제진(制振)구조를 가지는 브레이크 드럼 및 이 브레이크 드럼을 구비한 드럼 브레이크 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP6025846A JP2699258B2 (ja) | 1994-01-12 | 1994-01-12 | 制振構造を有するブレーキドラム |
JP6/25846 | 1994-01-12 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1995019508A1 true WO1995019508A1 (fr) | 1995-07-20 |
Family
ID=12177214
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1995/000029 WO1995019508A1 (fr) | 1994-01-12 | 1995-01-12 | Tambour de frein a structure amortissante et frein en etant equipe |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0688969A4 (ja) |
JP (1) | JP2699258B2 (ja) |
KR (1) | KR950704625A (ja) |
WO (1) | WO1995019508A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6742632B2 (en) | 1998-12-01 | 2004-06-01 | Lucas Industries Plc | Apparatus with vibration-damped component, especially a brake |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN1297759C (zh) * | 2001-08-23 | 2007-01-31 | 雅马哈发动机株式会社 | 回转体用减振装置 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS54161488U (ja) * | 1978-04-28 | 1979-11-12 | ||
JPS56164236A (en) * | 1980-05-16 | 1981-12-17 | Sumitomo Electric Ind Ltd | Manufacture of brake disc |
JPS59141236U (ja) * | 1983-03-11 | 1984-09-20 | 住友電気工業株式会社 | 鳴き防止型デイスクロ−タ |
JPS6167432U (ja) * | 1984-10-09 | 1986-05-09 | ||
JPS6292331U (ja) * | 1985-11-29 | 1987-06-12 | ||
JPS62176530U (ja) * | 1986-04-28 | 1987-11-10 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB254561A (en) * | 1925-09-18 | 1926-07-08 | Wilfrid Thomas Groom | Improvements relating to brake drums |
GB491717A (en) * | 1937-03-03 | 1938-09-05 | Robert William Harvey Bailey | Vibrational dampers for camshafts |
DE728598C (de) * | 1941-07-19 | 1942-11-30 | Graef & Stift Automobilfabrik | Einrichtung zur Verhinderung des Bremsgeraeusches bei Bremsen fuer Drehbewegungen |
GB833643A (en) * | 1956-03-07 | 1960-04-27 | Motor Industry Res Ass | Improvements in or relating to vibration damping devices for use with drum brakes |
GB857043A (en) * | 1956-06-07 | 1960-12-29 | Saab Scania Ab | Improvements in or relating to devices for dampening noises in friction brakes |
DE1128766B (de) * | 1960-09-15 | 1962-04-26 | Porsche Kg | Backenbremse fuer Fahrzeuge, insbesondere fuer Kraftfahrzeuge |
FR2497314B1 (fr) * | 1980-12-26 | 1985-11-22 | Europ Propulsion | Amortisseur de vibrations mecanique |
-
1994
- 1994-01-12 JP JP6025846A patent/JP2699258B2/ja not_active Expired - Fee Related
-
1995
- 1995-01-12 EP EP95905766A patent/EP0688969A4/en not_active Withdrawn
- 1995-01-12 KR KR1019950701174A patent/KR950704625A/ko not_active Application Discontinuation
- 1995-01-12 WO PCT/JP1995/000029 patent/WO1995019508A1/ja not_active Application Discontinuation
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS54161488U (ja) * | 1978-04-28 | 1979-11-12 | ||
JPS56164236A (en) * | 1980-05-16 | 1981-12-17 | Sumitomo Electric Ind Ltd | Manufacture of brake disc |
JPS59141236U (ja) * | 1983-03-11 | 1984-09-20 | 住友電気工業株式会社 | 鳴き防止型デイスクロ−タ |
JPS6167432U (ja) * | 1984-10-09 | 1986-05-09 | ||
JPS6292331U (ja) * | 1985-11-29 | 1987-06-12 | ||
JPS62176530U (ja) * | 1986-04-28 | 1987-11-10 |
Non-Patent Citations (1)
Title |
---|
See also references of EP0688969A4 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6742632B2 (en) | 1998-12-01 | 2004-06-01 | Lucas Industries Plc | Apparatus with vibration-damped component, especially a brake |
Also Published As
Publication number | Publication date |
---|---|
EP0688969A1 (en) | 1995-12-27 |
EP0688969A4 (en) | 1997-05-14 |
KR950704625A (ko) | 1995-11-20 |
JP2699258B2 (ja) | 1998-01-19 |
JPH07208517A (ja) | 1995-08-11 |
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