JPS6155416A - Brake device for car - Google Patents
Brake device for carInfo
- Publication number
- JPS6155416A JPS6155416A JP17730284A JP17730284A JPS6155416A JP S6155416 A JPS6155416 A JP S6155416A JP 17730284 A JP17730284 A JP 17730284A JP 17730284 A JP17730284 A JP 17730284A JP S6155416 A JPS6155416 A JP S6155416A
- Authority
- JP
- Japan
- Prior art keywords
- annular
- groove
- piston
- hub
- shaped
- 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.)
- Pending
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
- B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
- B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
- B60T1/065—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels employing disc
-
- 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
- F16D55/28—Brakes with only one rotating disc
- F16D55/32—Brakes with only one rotating disc actuated by a fluid-pressure device arranged in or on 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
- 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
- F16D2055/0058—Fully lined, i.e. braking surface extending over the entire disc circumference
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Braking Arrangements (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は車両用ブレーキ装置に関するものであす、自動
車、産業用車両等に利用される。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a brake device for a vehicle, and is used in automobiles, industrial vehicles, and the like.
（従来の技術）
車両用ブレーキ装置として、本出願人の先願に係るもの
（特願昭５３−５８１０８号）がある。(Prior Art) As a brake device for a vehicle, there is one related to an earlier application of the present applicant (Japanese Patent Application No. 58108/1982).
このものは、第８図に示す如く、ホイールディスク２１
とブレーキドラム２２とアクスルシャフト２３とはボル
トナツトによって一体的に連結され、ブレーキドラム２
２の円筒部端面には、■溝２４が環状に形成されている
。■溝２４に密着するように環状のＶ字状制動部材２５
が装着され、■字状制動部材２５はブレーキリング２６
のフランジ部２６ａに固定され、ブレーキリング２６の
ボス部２６ｂはスプライン手段２７を介してハウジング
２８に軸方向に摺動的に嵌装され、ハウジング２８はア
クスルハウジング２９に固定され、アクスルシャフト２
３はハウジング２８に装着されたベアリングによって軸
支されている。ブレーキリング２６のボス部２６ｂには
環状のピストン２６ｃが同心的に一体成形され、ピスト
ン２６ｃはハウジング２８に固定された環状シリンダ３
０に嵌装され、環状シリンダ３０の開口部の内外両側に
はシール部材３１ａ、３１ｂがそれぞれ嵌装され、ここ
にピストン２６ｃと環状シリンダ３０とシール部材３１
ａ、３１ｂとによってホイールシリンダ３２が構成され
ている。３３ａ、３３ｂは可撓シール部材であり、３４
ａ、３４ｂはダスト防止用カバーであり、３５は止め輪
である。As shown in FIG. 8, this wheel disc 21
The brake drum 22 and the axle shaft 23 are integrally connected by bolts and nuts.
A groove 24 is formed in an annular shape on the end surface of the cylindrical portion 2. ■An annular V-shaped braking member 25 so as to fit tightly into the groove 24.
is installed, and the ■-shaped braking member 25 is attached to the brake ring 26.
The boss portion 26b of the brake ring 26 is slidably fitted in the housing 28 in the axial direction via the spline means 27, the housing 28 is fixed to the axle housing 29, and the axle shaft 2
3 is pivotally supported by a bearing mounted on the housing 28. An annular piston 26c is integrally molded concentrically with the boss portion 26b of the brake ring 26, and the piston 26c is connected to the annular cylinder 3 fixed to the housing 28.
0, and seal members 31a and 31b are fitted on both the inner and outer sides of the opening of the annular cylinder 30, and the piston 26c, the annular cylinder 30, and the seal member 31 are fitted therein.
A and 31b constitute a wheel cylinder 32. 33a and 33b are flexible seal members; 34
34a and 34b are dust prevention covers, and 35 is a retaining ring.
（発明が解決しようとする問題点）
この従来のブレ−キ装置は、ピストン２６ｃと環状シリ
ンダ３０とシール部材３１ａ、３１ｂとによってホイー
ルシリンダ３２を構成し、ブレーキリング２６のボス部
２６ｂはスプライン手段２７を介してハウジング２８に
軸方向に摺動的に嵌装され、かつブレーキリング２６の
フランジ部２６ａに固定されたｖ字状制動部材２５とブ
レーキドラム２２とが摩擦係合するので、ブレーキ装置
が大型化し、かつ複雑化するという問題がある。(Problems to be Solved by the Invention) In this conventional brake device, a wheel cylinder 32 is constituted by a piston 26c, an annular cylinder 30, and seal members 31a and 31b, and a boss portion 26b of the brake ring 26 is a spline member. The brake drum 22 frictionally engages with the V-shaped braking member 25, which is slidably fitted in the housing 28 in the axial direction via the brake ring 27 and fixed to the flange portion 26a of the brake ring 26. There is a problem in that it is becoming larger and more complex.
そこで、本発明が解決しようとする問題点は、ブレーキ
装置を小型化かつ簡略化することである。Therefore, the problem to be solved by the present invention is to miniaturize and simplify the brake device.
（問題点を解決するための手段）
上記問題点を解決するための手段は、側面に環状のＶ溝
を設け、かっ該Ｖ溝から外周面に至る貫通孔を複数個穿
設した回転円板と、側面の外周側に環状のＶ字状制動部
材を付設し、かつ側面の内周側に挿通孔を複数個穿設し
た環状部材と、該環状部材と係合する端面を曲面状に形
成した環状のピストンと、該環状部材と該ピストンとの
間に介装された第１弾性部材と、該環状部材の挿通孔と
係合するトルク支持部材と、該環状部材と当接する端面
に該ピストンと係合する環状溝および該トルク支持部材
と係合する係合孔を設けたハブと、該トルク支持部材と
該ハブとの間に介装された第２弾性部材とを設けること
である。(Means for Solving the Problems) A means for solving the above problems is to provide a rotating disk with an annular V-groove on the side surface and a plurality of through holes extending from the V-groove to the outer peripheral surface. an annular member having an annular V-shaped braking member attached to the outer circumferential side of the side surface and a plurality of insertion holes bored in the inner circumferential side of the side surface, and an end surface that engages with the annular member formed in a curved shape. a first elastic member interposed between the annular member and the piston; a torque support member that engages with the insertion hole of the annular member; and an end surface that contacts the annular member. A hub provided with an annular groove that engages with the piston and an engagement hole that engages with the torque support member, and a second elastic member interposed between the torque support member and the hub. .
（作用） 上記手段は次のように作用する。(effect) The above means works as follows.
Ｖ字状制動部材とＶ溝とが摩擦係合した状態で回転円板
が半径方向に応力を受けると、第１弾性部材および第２
弾性部材が変形して連結した回転円板とＶ字状制動部材
と環状部材とトルク支持部材とが一体的に半径方向に偏
位し、さらにピストンを環状部材に押圧すると、ピスト
ンの押圧力がピストンの曲面状端面および第１弾性部材
を介して環状部材に伝達され、Ｖ字状制動部材とＶ溝と
の摩擦面に大きな圧力が発生し、大きな制動力を発生す
る。次いで、摩擦係合により発生した摩耗粉は、回転円
板の回転による遠心力によって回転円板とＶ字状制動部
材とのＶ字状隙間を貫通孔の方に移動し、貫通孔を経て
貫通孔の開口から外部に排出される。When the rotating disk receives stress in the radial direction while the V-shaped braking member and the V groove are in frictional engagement, the first elastic member and the second elastic member
When the elastic member is deformed and the connected rotating disk, V-shaped braking member, annular member, and torque support member are integrally displaced in the radial direction, and the piston is further pressed against the annular member, the pressing force of the piston is increased. The pressure is transmitted to the annular member via the curved end surface of the piston and the first elastic member, and a large pressure is generated on the friction surface between the V-shaped braking member and the V groove, generating a large braking force. Next, the abrasion powder generated by the frictional engagement moves through the V-shaped gap between the rotating disk and the V-shaped braking member toward the through hole due to the centrifugal force caused by the rotation of the rotating disk, and penetrates through the through hole. It is discharged to the outside through the hole opening.
Ｖ字状制動部材とＶ溝との摩擦係合を解除すると、Ｖ字
状制動部材が回転円板から離れ、次いで第１弾性部材お
よび第２弾性部材が復元し、さらに回転円板の回転によ
る遠心力によって外気が貫通孔内に流入して回転円板の
外周端部を冷却する。When the frictional engagement between the V-shaped braking member and the V groove is released, the V-shaped braking member separates from the rotating disk, and then the first elastic member and the second elastic member return to their original positions. Centrifugal force causes outside air to flow into the through hole to cool the outer peripheral end of the rotating disk.
（実施例）
以下、上記手段の具体例を示す実施例について説明する
。(Example) Hereinafter, an example showing a specific example of the above means will be described.
第１図〜第４図において、１はホイールディスク、２は
回転円板、３はシャフトであって図示のようにボルトナ
ツトによって一体的に連結されている。回転円板２の外
周部には冷却フィン４が形成され、回転円板２の側面に
はＶ溝５が環状に形成され、さらにＶ溝５から回転円板
２の外周面に至る貫通孔６が複数個設けられている。■
溝５に密着するように環状のＶ字状制動部財７が嵌装さ
れ、■溝５のＶ形角度の１／２がＶ溝５と■溝５とＶ溝
５に嵌合するＶ字状制動部材７との間の摩擦係数に相当
する摩擦角度よりも大きい所定の角度であるように形成
され、■溝５に対してＶ字状制動部材７を押圧する力を
抜いた時には、自然に、 両者は密着から解放されるよ
うに形成されている。In FIGS. 1 to 4, 1 is a wheel disk, 2 is a rotating disk, and 3 is a shaft, which are integrally connected by bolts and nuts as shown. Cooling fins 4 are formed on the outer circumference of the rotating disk 2, a V-groove 5 is formed in an annular shape on the side surface of the rotating disk 2, and a through hole 6 is formed from the V-groove 5 to the outer circumferential surface of the rotating disk 2. There are several. ■
An annular V-shaped brake member 7 is fitted so as to fit tightly into the groove 5, and 1/2 of the V-shaped angle of the groove 5 forms a V-shaped groove that fits into the V-groove 5 and ■ the groove 5 and the V-shaped groove 5. The V-shaped brake member 7 is formed at a predetermined angle larger than the friction angle corresponding to the coefficient of friction between the V-shaped brake member 7 and the V-shaped brake member 7. In addition, both are formed so that they can be released from close contact.
■字状制動部材７は環状部材８の外周側に固定され、環
状部材８を介してＶ字状制動部材７と対向する位置に環
状のピストン９が同心的に配設され、ピストン９は環状
部材８と係合する端面が曲面状に形成され、環状部材８
とピストン９とが当接する所定部位に凹溝１０ａ、１０
ｂが複数個形成され、凹溝１０ａ、１０ｂに第１弾性部
材１１が複数個装着され、ハブ１２にピストン９と係合
する環状溝１２ａが穿設され、ピストン９とハブ１２と
の間に環状シール部材１３ａ、１３ｂがそれぞれ嵌装さ
れ、ここにピストン９と環状溝１２ａと環状シール部材
１３ａ、１．３ ｂとによってホイールシリンダ１４が
形成されている。環状部材８の内周側には貫通した挿通
孔１５が穿設され、挿通孔１５にはトルク支持部材１６
が挿通され、トルク支持部材１６は第２弾性部材１７を
介してハブ１２の端面に穿設された係合孔１２ｂに係止
されている。シャフト３はハブ１２に装着されたベアリ
ング１８によって軸支され、ハブ１２の端面開口部には
ハブ１２とシャフト３との間に環状のオイルシール部材
１９が嵌装され、２０は環状の可撓性ダストブーツであ
る。The brake member 7 is fixed to the outer periphery of the annular member 8, and an annular piston 9 is disposed concentrically at a position facing the V-shaped brake member 7 via the annular member 8. The end surface that engages with the member 8 is formed into a curved shape, and the annular member 8
Concave grooves 10a, 10 are provided at predetermined portions where the piston 9 and the piston 9 come into contact.
A plurality of first elastic members 11 are installed in the concave grooves 10a and 10b, and an annular groove 12a that engages with the piston 9 is bored in the hub 12. Annular seal members 13a, 13b are fitted therein, and a wheel cylinder 14 is formed by the piston 9, the annular groove 12a, and the annular seal members 13a, 1.3b. An insertion hole 15 is formed in the inner peripheral side of the annular member 8, and a torque support member 16 is inserted into the insertion hole 15.
is inserted through the torque support member 16, and the torque support member 16 is engaged with the engagement hole 12b formed in the end surface of the hub 12 via the second elastic member 17. The shaft 3 is pivotally supported by a bearing 18 attached to the hub 12, and an annular oil seal member 19 is fitted into the end opening of the hub 12 between the hub 12 and the shaft 3, and 20 is an annular flexible seal member. These are sex dust boots.
■字状制動部材７と■溝５とが摩擦係合した状態で回転
円板２が半径方向に応力を受けると、第１弾性部材１１
および第２弾性部材１７が変形して連結した回転円板２
とＶ字状制動部材７と環状部材８とトルク支持部材１６
とが一体的に半径方向に偏位し、引続いてマスクシリン
ダ（図示せず）の油圧がホイールシリンダ１４に作用す
ると、ピストン９が押圧され、第１弾性部材１１および
環状部材８を介してＶ字状制動部材７は■溝５に対して
押圧される。すると、楔の原理によりＶ字状制動部材７
とＶ溝５との摩擦面には大きな圧力が発生し大きな制動
力を発生する。しかも、Ｖ字状制動部材７とＶ溝５との
摩擦係合により摩耗粉が発生するが、摩耗粉は回転円板
２の回転による遠心力によって回転円板２のＶ溝５とＶ
字状制動部材７とのＶ字状隙間を貫通孔６の方に移動し
、貫通孔６を経て貫通孔６の開口から外部に排出される
。 ホイールシリンダ１４の油圧を抜くと、Ｖ字状制動
部材７とＶ溝５との摩擦係合が解除され、次いでＶ字状
制動部材７とＶ溝５とは密着から解放され、次いでｖ字
状制動部材７と■溝５とは密着から解放され、さらにビ
ス１−ン９は環状シール部材１３ａ、＋３ｂの引込み作
用を受け、Ｖ字状制動部材７は回転円板２から離れ、次
いで第１弾性部材１１および第２弾性部材１７が復元し
、さらに回転円板２の回転による遠心力によって外気が
貫通孔６に流入して回転円板２の外周端部を冷却する。When the rotating disk 2 is subjected to stress in the radial direction while the letter-shaped braking member 7 and the groove 5 are in frictional engagement, the first elastic member 11
and a rotating disk 2 to which the second elastic member 17 is deformed and connected.
, the V-shaped braking member 7 , the annular member 8 and the torque support member 16
are integrally displaced in the radial direction, and subsequently, when the hydraulic pressure of the mask cylinder (not shown) acts on the wheel cylinder 14, the piston 9 is pressed, and the piston 9 is pushed through the first elastic member 11 and the annular member 8. The V-shaped brake member 7 is pressed against the groove 5. Then, due to the wedge principle, the V-shaped brake member 7
A large pressure is generated on the friction surface between the V groove 5 and the V groove 5, and a large braking force is generated. In addition, abrasion powder is generated due to the frictional engagement between the V-shaped braking member 7 and the V groove 5, and the abrasion powder is caused by the centrifugal force caused by the rotation of the rotating disc 2 between the V groove 5 of the rotating disc 2 and the V groove 5.
It moves toward the through hole 6 through the V-shaped gap with the character-shaped brake member 7, passes through the through hole 6, and is discharged to the outside from the opening of the through hole 6. When the hydraulic pressure of the wheel cylinder 14 is released, the frictional engagement between the V-shaped braking member 7 and the V-groove 5 is released, the V-shaped braking member 7 and the V-groove 5 are released from close contact, and then the V-shaped braking member 7 and the V-groove 5 are released from close contact. The brake member 7 and the groove 5 are released from close contact, and the screw 1-9 receives the retracting action of the annular seal members 13a and +3b, and the V-shaped brake member 7 is separated from the rotating disk 2, and then the first The elastic member 11 and the second elastic member 17 are restored, and the centrifugal force caused by the rotation of the rotating disk 2 causes outside air to flow into the through hole 6 to cool the outer peripheral end of the rotating disk 2.
第５図〜第７図は他の実施例を示すものであり、環状部
材８と係合するピストン９の端面ば曲面状に形成され、
かつピストン９と係合する環状部材８の所定部位には環
状凹溝１０Ｃが形成され、凹溝１０Ｃに１対の環状の第
１弾性部材１１ａ、１１ｂが装着され、ピストン９の曲
面状端面と凹溝１０Ｃの底面とが当接し、かつピストン
９の端縁と第１弾性部材１１ａ、ｌｌｂとが当接してい
る。」１記以外は前記実施例と同様に形成され、前記実
施例と同様の作用を奏する。5 to 7 show another embodiment, in which the end surface of the piston 9 that engages with the annular member 8 is formed into a curved shape,
Further, an annular groove 10C is formed in a predetermined portion of the annular member 8 that engages with the piston 9, and a pair of annular first elastic members 11a and 11b are attached to the groove 10C. The bottom surface of the groove 10C is in contact with the bottom surface of the concave groove 10C, and the edge of the piston 9 is in contact with the first elastic members 11a and 11b. '' Except for item 1, the structure is the same as that of the embodiment described above, and the same function as that of the embodiment described above is achieved.
（発明の効果） 本発明は次の特有の効果を生じる。(Effect of the invention) The present invention produces the following unique effects.
本発明は環状の■溝を穿設した回転円板と、環状ピスト
ンと環状のｖ字状制動部材を付設した環状部材とを設け
るようにしたから、キャリパが不要となるので、ブレー
キ装置が小型化かつ簡略化され、しかも制動トルクがデ
ィスクブレーキ同様に回転円板側面に発生するので、フ
ィーリングが良好であり、さらにＶ字状制動部材またけ
Ｖ溝が摩耗すると、それに応じて環状部材は前進するの
で、摩擦面が摩耗しても間隙調整の必要がない。Since the present invention includes a rotating disc with an annular groove and an annular member having an annular piston and an annular V-shaped braking member attached thereto, a caliper is not required, so the brake device is compact. Moreover, since the braking torque is generated on the side surface of the rotating disc like a disc brake, the feeling is good.Furthermore, when the V groove that spans the V-shaped braking member wears out, the annular member changes accordingly. Since it moves forward, there is no need to adjust the gap even if the friction surface wears out.
曲面状端面を有するビス１−ンと第１弾性部材と第２弾
性部材とを設けるようにしたから、ブレーキ制動時にタ
イヤを介して路面から反力を受けて回転円板が半径方向
に偏位しても第１弾性部材と第２弾性部材とが変形して
ビス１ヘンの抑圧力がピストンの曲面状端面および第１
弾性部材を介して環状部材に伝達され、Ｖ字状制動部材
とＶ溝との摩擦面に大きな圧力を発生するので、良好な
ブレーキ制動力が得られる。Since the screw 1, which has a curved end surface, the first elastic member, and the second elastic member are provided, the rotating disk is deflected in the radial direction by receiving a reaction force from the road surface through the tires during braking. Even if the first elastic member and the second elastic member are deformed, the suppressing force of the screw 1 is applied to the curved end surface of the piston and the first elastic member.
Since the pressure is transmitted to the annular member via the elastic member and generates a large pressure on the friction surface between the V-shaped braking member and the V-groove, good braking force can be obtained.
回転円板とＶ字状制動部材との摺動面積はディスクブレ
ーキにおけるロータとパッドとの摺動面積と比べて広く
することができるので、制動力が大きくなり、しかも前
記の広い摺動面積によって面積当り荷重が少くなるので
、摩耗度が低くなる。Since the sliding area between the rotating disk and the V-shaped braking member can be made larger than the sliding area between the rotor and pad in a disc brake, the braking force is increased, and the large sliding area mentioned above increases Since the load per area is reduced, the degree of wear is reduced.
回転円板の■溝から外周面に至る貫通孔を複数個穿設し
であるから、外気が貫通孔内に流入するので、回転円板
の摺動部分の冷却効果が大であり、また水が回転円板の
Ｖ溝と環状部材のＶ字状側動部材とのＶ字状隙間に侵入
しても、水は回転円板の回転による遠心力によって前記
Ｖ字状隙間を貫通孔の方に移動し、貫通孔を経て貫通孔
の開口から外部に排出されるので、ブレーキ制動力が低
下せず、常時良好なブレーキ制動力が得られる。Since multiple through holes are drilled from the grooves of the rotating disk to the outer circumferential surface, outside air flows into the through holes, which has a great cooling effect on the sliding parts of the rotating disk, and also prevents water from flowing. Even if water enters the V-shaped gap between the V-groove of the rotating disk and the V-shaped lateral moving member of the annular member, the centrifugal force caused by the rotation of the rotating disk causes water to flow through the V-shaped gap towards the through hole. Since the brake fluid moves through the through hole and is discharged to the outside from the opening of the through hole, the brake braking force does not decrease and good braking force is always obtained.
第１図は本発明に係るブレーキ装置の正面図。
第２図は第１図のＩＴ−ＴＩ断面図、第３図は環状部材
の正面図、第４図は第３図のＩＶ−ＩＶ断面図、第５図
〜第７図は本発明の他の実施例を示し、第５図は他のブ
レーキ装置の断面図、第６図は他の環状部材の正面図、
第７図は第６図の■−■断面図、第８図は従来のブレー
キ装置の断面図である。
２・・・回転円板 ５・・・Ｖ溝 ６・・・貫通孔 ７
・・・ｖ字状制動部材 ８・・・環状部材９・・・ピス
トン １１、Ｉｌａ、ｌｌｂ・−−第１弾性部トｉ１２
・・・ハブ １２ａ・、・環状溝 １２ｂ・・・係合孔
１５・・・挿通孔１６・・・トルク支持部材 １７・
・、・第２弾性部材
？＋２父
熟１日FIG. 1 is a front view of a brake device according to the present invention. 2 is an IT-TI sectional view in FIG. 1, FIG. 3 is a front view of the annular member, FIG. 4 is an IV-IV sectional view in FIG. 3, and FIGS. FIG. 5 is a sectional view of another brake device, FIG. 6 is a front view of another annular member,
FIG. 7 is a cross-sectional view taken along the line ■--■ in FIG. 6, and FIG. 8 is a cross-sectional view of a conventional brake device. 2...Rotating disk 5...V groove 6...Through hole 7
... V-shaped braking member 8 ... Annular member 9 ... Piston 11, Ila, llb -- First elastic part i12
... Hub 12a... Annular groove 12b... Engagement hole 15... Insertion hole 16... Torque support member 17.
・・Second elastic member? +2 father mature 1 day
Claims (1)
貫通孔を複数個穿設した回転円板と、側面の外周側に環
状のＶ字状制動部材を付設し、かつ側面の内周側に挿通
孔を複数個穿設した環状部材と、該環状部材と係合する
端面を曲面状に形成した環状のピストンと、該環状部材
と該ピストンとの間に介装された第１弾性部材と、該環
状部材の挿通孔と係合するトルク支持部材と、該環状部
材と当接する端面に該ピストンと係合する環状溝および
該トルク支持部材と係合する係合孔を設けたハブと、該
トルク支持部材と該ハブとの間に介装された第２弾性部
材とからなる車両用ブレーキ装置A rotating disk having an annular V-groove on the side surface and a plurality of through holes extending from the V-groove to the outer circumferential surface, an annular V-shaped braking member attached to the outer circumferential side of the side surface, and an annular member having a plurality of insertion holes bored on the inner circumferential side; an annular piston having a curved end surface that engages with the annular member; and a piston interposed between the annular member and the piston. 1. An elastic member, a torque support member that engages with the insertion hole of the annular member, and an annular groove that engages with the piston and an engagement hole that engages with the torque support member on an end surface that comes into contact with the annular member. A vehicle brake device comprising: a hub; and a second elastic member interposed between the torque support member and the hub.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17730284A JPS6155416A (en) | 1984-08-24 | 1984-08-24 | Brake device for car |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17730284A JPS6155416A (en) | 1984-08-24 | 1984-08-24 | Brake device for car |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS6155416A true JPS6155416A (en) | 1986-03-19 |
Family
ID=16028617
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17730284A Pending JPS6155416A (en) | 1984-08-24 | 1984-08-24 | Brake device for car |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6155416A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2013182627A (en) * | 2012-02-29 | 2013-09-12 | D & M Holdings Inc | Reproducer |
-
1984
- 1984-08-24 JP JP17730284A patent/JPS6155416A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2013182627A (en) * | 2012-02-29 | 2013-09-12 | D & M Holdings Inc | Reproducer |
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