JPH01126443A - Disc rotor - Google Patents
Disc rotorInfo
- Publication number
- JPH01126443A JPH01126443A JP28381987A JP28381987A JPH01126443A JP H01126443 A JPH01126443 A JP H01126443A JP 28381987 A JP28381987 A JP 28381987A JP 28381987 A JP28381987 A JP 28381987A JP H01126443 A JPH01126443 A JP H01126443A
- Authority
- JP
- Japan
- Prior art keywords
- heat
- insulating layer
- main body
- conductive layer
- heat insulating
- 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
Links
- 229910052751 metal Inorganic materials 0.000 claims description 4
- 239000002184 metal Substances 0.000 claims description 4
- 239000000463 material Substances 0.000 claims description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 abstract description 5
- VYZAMTAEIAYCRO-UHFFFAOYSA-N Chromium Chemical compound [Cr] VYZAMTAEIAYCRO-UHFFFAOYSA-N 0.000 abstract description 5
- 229910052799 carbon Inorganic materials 0.000 abstract description 5
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 abstract description 3
- WGLPBDUCMAPZCE-UHFFFAOYSA-N Trioxochromium Chemical compound O=[Cr](=O)=O WGLPBDUCMAPZCE-UHFFFAOYSA-N 0.000 abstract description 3
- 229910052802 copper Inorganic materials 0.000 abstract description 3
- 239000010949 copper Substances 0.000 abstract description 3
- 229910001060 Gray iron Inorganic materials 0.000 abstract description 2
- 229910000423 chromium oxide Inorganic materials 0.000 abstract description 2
- 238000010285 flame spraying Methods 0.000 abstract description 2
- 239000000203 mixture Substances 0.000 description 7
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 6
- 229910052804 chromium Inorganic materials 0.000 description 4
- 239000011651 chromium Substances 0.000 description 4
- 238000009792 diffusion process Methods 0.000 description 4
- 238000009423 ventilation Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 229910052742 iron Inorganic materials 0.000 description 3
- 238000007750 plasma spraying Methods 0.000 description 3
- PXHVJJICTQNCMI-UHFFFAOYSA-N Nickel Chemical compound [Ni] PXHVJJICTQNCMI-UHFFFAOYSA-N 0.000 description 2
- 230000000052 comparative effect Effects 0.000 description 2
- 238000007751 thermal spraying Methods 0.000 description 2
- ZOKXTWBITQBERF-UHFFFAOYSA-N Molybdenum Chemical compound [Mo] ZOKXTWBITQBERF-UHFFFAOYSA-N 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 229910052750 molybdenum Inorganic materials 0.000 description 1
- 239000011733 molybdenum Substances 0.000 description 1
- 229910052759 nickel Inorganic materials 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 238000010998 test method Methods 0.000 description 1
Landscapes
- Braking Arrangements (AREA)
Abstract
Description
【発明の詳細な説明】
技術分野
本発明はディスクブレーキの一構成要素であるディスク
ロータに関するものであり、特に、制動時の振動低減に
関するものである。DETAILED DESCRIPTION OF THE INVENTION Technical Field The present invention relates to a disc rotor, which is a component of a disc brake, and particularly relates to vibration reduction during braking.
従来の技術
ディスクブレーキは、自動車の車輪等、回転体の回転を
抑制するものであり、ディスクロータは金属製の円板状
を成し、回転体に取り付けられて回転体と共に回転する
。制動時にはディスクロータの両側の摩擦面にそれぞれ
摩擦部材が摺接させられることにより、回転体の回転が
抑制されるのであるが、その際、摩擦面には大量の摩擦
熱が発生し、また、制動が繰返し行われることにより摩
耗が生ずるため、ディスクロータは耐摩耗性、耐熱性に
優れていることが望ましい。そのため特開昭６２−８８
８２９号に記載のディスクロータにおいては、その両側
面にそれぞれ耐摩耗性、耐熱性に優れた溶射層を形成す
ることが行われている。BACKGROUND OF THE INVENTION A conventional disc brake suppresses the rotation of a rotating body such as a wheel of an automobile, and a disc rotor has a metal disk shape, is attached to the rotating body, and rotates together with the rotating body. During braking, friction members are brought into sliding contact with the friction surfaces on both sides of the disc rotor, thereby suppressing the rotation of the rotating body. At that time, a large amount of frictional heat is generated on the friction surfaces, and Since wear occurs due to repeated braking, it is desirable that the disc rotor has excellent wear resistance and heat resistance. Therefore, JP-A-62-88
In the disc rotor described in No. 829, a thermal spray layer having excellent wear resistance and heat resistance is formed on both sides of the disc rotor.
発明が解決しようとする問題点
ところで、ディスクロータにおいては、制動時に摩擦面
の一部の温度が他の部分より高くなるヒートスポットが
生ずることがある。このヒートスボッ１はディスクロー
タの厚さに円周方向において差を生じさせ、振動発生の
原因となる。プレー手作動時に摩擦部材がディスクロー
タの摩擦面に追従して微小な往復運動を行うからである
。例えば、摩擦部材をディスクロータに押し付けるアク
チュエータが液圧を駆動源とするシリンダにより構成さ
れている場合には、摩擦部材が往復運動すれば、それに
伴ってピストンがシリンダから出入して液圧室の容積が
変動するが、この変動は急激であるため、ブレーキ液の
液圧室からの流出入が十分に追従できず、液圧変動が生
ずる。そして、この液圧変動と、それに基づく制動トル
ク変動とによって、回転体ならびにディスクブレーキを
支持する部材や、それらが取り付けられた機構部全体に
振動が生ずるのであり、制動トルクの変動量が大きいほ
ど振動が大きくなる。Problems to be Solved by the Invention Incidentally, in a disc rotor, a heat spot may occur where the temperature of a portion of the friction surface is higher than other portions during braking. This heat sink 1 causes a difference in the thickness of the disc rotor in the circumferential direction, causing vibration. This is because the friction member follows the friction surface of the disc rotor and performs minute reciprocating motion when the player's hand is operated. For example, if the actuator that presses the friction member against the disc rotor is composed of a cylinder driven by hydraulic pressure, when the friction member reciprocates, the piston moves in and out of the cylinder, causing the hydraulic chamber to move in and out. The volume fluctuates, but since this fluctuation is rapid, the inflow and outflow of brake fluid from the hydraulic pressure chamber cannot be sufficiently followed, resulting in fluid pressure fluctuations. These fluid pressure fluctuations and braking torque fluctuations based on them cause vibrations in the rotating body, the members that support the disc brake, and the entire mechanism to which they are attached. Vibrations become louder.
特に、ベンチレーテッドタイプのディスクロータにおい
ては、通気孔が設けられている部分と設けられていない
部分とに温度差が生じ、振動が発生し易い。前述のよう
に側面に耐摩耗性、耐熱性に優れた溶射層を形成したデ
ィスクロータにおいてもこの問題は同様に発生する。In particular, in a ventilated type disc rotor, there is a temperature difference between a portion where ventilation holes are provided and a portion where no ventilation holes are provided, and vibrations are likely to occur. This problem also occurs in a disc rotor in which a sprayed layer with excellent wear resistance and heat resistance is formed on the side surface as described above.
問題点を解決するための手段
本発明は、上記の問題を解決するために、円板状を成す
金属製の本体の両側面にそれぞれ本体より熱伝導率の小
さい断熱層を設けるとともに、その断熱層の上に断熱層
より熱伝導率の大きい熱伝導層を設け、その熱伝導層の
表面を摩擦面としたものである。Means for Solving the Problems In order to solve the above problems, the present invention provides a heat insulating layer having a lower thermal conductivity than the main body on both sides of a disc-shaped metal main body, and A heat conductive layer having a higher thermal conductivity than the heat insulating layer is provided on the layer, and the surface of the heat conductive layer is used as a friction surface.
作用および効果
以上のように構成されたディスクロータにおいては、断
熱層により熱の伝導が妨げられて摩擦熱は本体に伝わり
難く、ディスクロータの表面から放散する熱量が多くな
って、本体の温度自体が低くなり、温度差も小さいもの
となる。しかも、熱伝導層が断熱層の上に設けられてい
るため、熱伝導層全体の温度がほぼ均一となり、本体の
温度差も小さくなる。熱伝導層を設けない場合には摩擦
熱は本体のどの部分にもほぼ同量ずつ伝わる傾向があり
、本体内部における熱の拡散速度が大きい部分の温度は
拡散速度の小さい部分より低くなって温度差が生ずるの
に対し、熱伝導層を設ければ、本体の温度が低い部分に
は温度が高い部分より多くの熱が伝えられることとなり
、ロータ本体の温度差が小さくなるのである。したがっ
て、ヒートスポットの発生による振動の発生が低減され
、乗心地が改善されるとともに、ディスクブレーキおよ
びそれを支持する装置の耐久性が向上する効果が得られ
る。Functions and Effects In the disc rotor configured as described above, heat conduction is hindered by the heat insulating layer, making it difficult for frictional heat to be transmitted to the main body, and the amount of heat dissipated from the surface of the disc rotor increases, causing the temperature of the main body itself to decrease. becomes lower, and the temperature difference becomes smaller. Moreover, since the heat conductive layer is provided on the heat insulating layer, the temperature of the entire heat conductive layer is almost uniform, and the temperature difference in the main body is also reduced. If a heat conductive layer is not provided, frictional heat tends to be transmitted in almost the same amount to every part of the body, and the temperature of the parts where the heat diffusion rate is high in the body is lower than that of the parts where the diffusion rate is low. However, if a heat conductive layer is provided, more heat will be transferred to the lower temperature parts of the rotor body than to the higher temperature parts, and the temperature difference in the rotor body will be reduced. Therefore, the occurrence of vibrations due to the generation of heat spots is reduced, the riding comfort is improved, and the durability of the disc brake and the device supporting it is improved.
実施例
以下、本発明の実施例を図面に基づいて詳細に説明する
。Embodiments Hereinafter, embodiments of the present invention will be described in detail based on the drawings.
第１図は本発明の一実施例であるディスクロータ（以下
、ロータと略称する）１０を示す図である。このディス
クロータｌＯはベンチレーテッドタイプのものであり、
その本体１２はねずみ鋳鉄（ＪＩＳ Ｆｅ１２）で鋳
造されている。本体１２は、有底円筒状部１４と、その
円筒状部１２の開口端から半径方向外向きに延び出させ
られたフランジ部１６とを備えている。有底円筒状部１
４はその底部に形成された嵌合穴１８においてアクスル
ハブのボス部に嵌合され、フランジ部１６は摩擦部材に
よりロータ回転中心線方向の両側から挾まれ、回転を抑
制される。フランジ部１６はその外径が２６０ｍｍ、厚
さ（ロータ回転中心線方向の寸法）２２鶴とされており
、厚さ方向の中央部には、ロータ１０の中心側から外周
側へ延びる複数の通気孔２０が周方向に等間隔に形成さ
れている。FIG. 1 is a diagram showing a disc rotor (hereinafter abbreviated as rotor) 10 which is an embodiment of the present invention. This disc rotor lO is a ventilated type,
The main body 12 is cast from gray cast iron (JIS Fe12). The main body 12 includes a bottomed cylindrical portion 14 and a flange portion 16 extending radially outward from the open end of the cylindrical portion 12 . Bottomed cylindrical part 1
4 is fitted into the boss portion of the axle hub through a fitting hole 18 formed at its bottom, and the flange portion 16 is held by friction members from both sides in the direction of the rotor's rotational centerline, thereby suppressing rotation. The flange portion 16 has an outer diameter of 260 mm and a thickness (dimension in the rotor rotation center line direction) of 22 mm, and has a plurality of passages extending from the center side of the rotor 10 to the outer circumference side in the center portion in the thickness direction. The pores 20 are formed at regular intervals in the circumferential direction.
フランジ部１６の両側面にはそれぞれ、断熱層２２が形
成されるとともに、その断熱層２２上に熱伝導層２４が
形成され、その熱伝導層２４の表面が摩擦面２６．２８
とされている。断熱層２２゜熱伝導層２４はいずれもプ
ラズマ溶射により形成されており、その組成は次の通り
である。なお、この組成は重量パーセントで示されてい
る。A heat insulating layer 22 is formed on each side of the flange portion 16, and a heat conductive layer 24 is formed on the heat insulating layer 22, and the surface of the heat conductive layer 24 is a friction surface 26.28.
It is said that The heat insulating layer 22 and the heat conductive layer 24 are both formed by plasma spraying, and their compositions are as follows. Note that this composition is expressed in weight percent.
（断熱層２２）
酸化クロム（Ｃｒ２０３）
（熱伝導層２４）
クロム・・・３０％
炭素・・・・ １％
銅・・・・・５０％
鉄・・・・・ 残部
断熱層２２．熱伝導層２４は、いずれもプラズマ溶射に
より０．３ ｍｍの厚さで形成された後、研削により厚
さ０．２５ｍに仕上げられている。このように形成され
た断熱１ｉ２２の熱伝導率は０．００６ｃａ１ ／Ｑｌ
ｓｅｃ”ｃ、熱伝導層２４の熱伝導率は０．４ｃａｌ
／ｃｍ ｓｅｃ”ｃである。(Heat-insulating layer 22) Chromium oxide (Cr203) (Heat-conducting layer 24) Chromium...30% Carbon...1% Copper...50% Iron...Remaining heat-insulating layer 22. The heat conductive layer 24 is formed by plasma spraying to a thickness of 0.3 mm, and then polished to a thickness of 0.25 m. The thermal conductivity of the heat insulation 1i22 formed in this way is 0.006ca1/Ql
sec"c, the thermal conductivity of the thermally conductive layer 24 is 0.4 cal
/cm sec”c.
本実施例のロータ１０の効果を確認するために、このロ
ータｌＯを備えたディスクブレーキを用いて制動を行い
、制動トルクの変動量（ロータ１０が１回転する間に生
ずる最小制動トルクと最大制動トルクとの差）を測定し
た。なお、ディスクブレーキはシリンダ径６０１ｍのピ
ンスライド式キャリパ浮動型である。また、試験方法は
、５ｋｇｍ５”のイナーシャの下で、２００ｋｍ／ｈの
速度から減速度０．３ｇで１１００ｋ／ｈの速度まで減
速する制動を２０回行ったものである。この試験時にお
ける制動トルクの変動量を調べたところ、第２図に実線
で示すようになった。In order to confirm the effect of the rotor 10 of this example, braking was performed using a disc brake equipped with this rotor lO, and the amount of variation in braking torque (minimum braking torque and maximum braking torque generated during one rotation of the rotor 10) was measured. torque) was measured. The disc brake is a pin slide type caliper floating type with a cylinder diameter of 601 m. The test method was to perform braking 20 times to decelerate from a speed of 200 km/h to a speed of 1100 km/h with a deceleration of 0.3 g under an inertia of 5 kgm5''.The braking torque at the time of this test was When we investigated the amount of variation in , we found that it became as shown by the solid line in Figure 2.
比較のために、円板状の本体の側面に溶射層を１層形成
したディスクロータの制動トルクの変動量を測定した。For comparison, we measured the amount of variation in braking torque of a disc rotor in which one thermally sprayed layer was formed on the side surface of a disc-shaped main body.
この溶射層の組成は、クロム５０％、炭素４％、モリブ
デン１０％、銅６％、鉄残部であり、熱伝導率は０．４
ｃａｌ ／ ｃｆｆｌｓｅｃ”ｃである。The composition of this sprayed layer is 50% chromium, 4% carbon, 10% molybdenum, 6% copper, balance iron, and the thermal conductivity is 0.4.
cal/cfflsec”c.
このような溶射層が形成されたロータについて本実施例
のロータ１０と同様な試験を行ったところ、制動トルク
の変動量は第２図に破線で示されるようになった。When a test similar to that of the rotor 10 of this embodiment was conducted on a rotor on which such a sprayed layer was formed, the amount of variation in braking torque was shown by the broken line in FIG. 2.
この試験の結果から明らかなように、比較例のディスク
ロータでは、制動トルクの変動量は制動回数が増えるに
従って大きくなっているのに対し、本実施例のロータ１
０においては、制動を繰返し行っても制動トルクの変動
量はほぼ一定の比較的小さい値を維持する。これは、本
体１２に断熱層２２と熱伝導１２４とが設けられており
、摩擦面２６．２８に生じた摩擦熱が本体１２に伝わり
難いため、制動回数が増えても本体１２の温度上昇が小
さく、温度差が小さくて済む上、断熱層２２の上に熱伝
導層２４が設けられているため、本体１２の通気孔２０
が設けられ、熱の拡散速度が大きくて温度の低い部分に
は、通気孔２０が設けられず、熱の拡散速度が小さくて
温度の高い部分より多くの熱が伝えられ、本体１２の温
度差が小さくなるからである。このように制動トルクの
変動量が小さい値に保たれることにより制動時の振動が
低減し、乗心地が向上する効果が得られる。As is clear from the results of this test, in the disc rotor of the comparative example, the amount of variation in braking torque increases as the number of braking increases, whereas in the rotor of the present example.
At 0, the amount of variation in braking torque maintains a substantially constant and relatively small value even if braking is repeated. This is because the main body 12 is provided with a heat insulating layer 22 and a heat conduction layer 124, and the frictional heat generated on the friction surfaces 26.28 is difficult to be transferred to the main body 12, so even if the number of braking increases, the temperature of the main body 12 will not rise. The ventilation hole 20 of the main body 12 is small and requires only a small temperature difference, and the heat conductive layer 24 is provided on the heat insulating layer 22.
The ventilation holes 20 are not provided in the areas where the heat diffusion rate is high and the temperature is low, so that more heat is transmitted than the areas where the heat diffusion rate is low and the temperature is high, and the temperature difference in the main body 12 is reduced. This is because it becomes smaller. By keeping the amount of variation in braking torque to a small value in this way, vibrations during braking are reduced, and riding comfort is improved.
なお、断熱層の組成を、重量パーセントで、クロム６０
％、炭素２％、鉄残部とし、熱伝導層の組成を、クロム
２０％、炭素５％、ニッケル１註よい。この場合、断熱
層の熱伝導率は０．０５ｃａｌ／ｃｍｓｅｃ’ｃであり
、熱伝導層２４の熱伝導率は０。The composition of the heat insulating layer is chromium 60 in weight percent.
%, carbon 2%, balance iron, and the composition of the thermally conductive layer is 20% chromium, 5% carbon, and 1 nickel. In this case, the thermal conductivity of the heat insulating layer is 0.05 cal/cmsec'c, and the thermal conductivity of the thermal conductive layer 24 is 0.
４ｃａｌ ／ｃｔａ ｓｅｃ℃であるが、前記実施例の
ロータ１０に近いトルク変動低減効果が得られる。Although the temperature is 4 cal/cta sec° C., a torque fluctuation reduction effect close to that of the rotor 10 of the embodiment described above can be obtained.
また、断熱層，熱伝導層の組成は上記したものに限らず
、断熱層の熱伝導率がロータ本体の熱伝導率より小さく
、かつ熱伝導層の熱伝導率の０．１〜２０％、特に望ま
しくは１〜１０％となる組成であればよい。The compositions of the heat insulating layer and the heat conductive layer are not limited to those described above, and the heat conductivity of the heat insulating layer is lower than that of the rotor body, and the thermal conductivity of the heat conductive layer is 0.1 to 20%, Particularly preferably, the composition should be 1 to 10%.
さらに、断熱層，熱伝導層は金属以外の材料により形成
してもよく、また、プラズマ溶射によれば容易に設ける
ことができるが、火炎溶射法等、他の溶射方法や溶射以
外の手段によって設けてもよい。Furthermore, the heat insulating layer and the thermally conductive layer may be formed of materials other than metal, and although they can be easily formed by plasma spraying, they can also be formed by other thermal spraying methods such as flame spraying or by means other than thermal spraying. It may be provided.
さらにまた、本発明はベンチレーテッドタイプ以外のデ
ィスクロータにも適用することができる。Furthermore, the present invention can be applied to disc rotors other than ventilated types.
その他、いちいち例示することはしないが、当業者の知
識に基づいて種々の変形．改良を施した態様で本発明を
実施することができる。In addition, various modifications may be made based on the knowledge of those skilled in the art, although no examples will be given one by one. The invention can be practiced in modified forms.
第１図は本発明の一実施例であるディスクロータを示す
正面断面図である。第２図はそのディスクロータの制動
トルク変動量を比較例の変動量と共に示すグラフである
。
１０：ディスクロータ １２：本体
２２：断熱層 ２４：熱伝導層２６、２８：摩
擦面FIG. 1 is a front sectional view showing a disc rotor that is an embodiment of the present invention. FIG. 2 is a graph showing the amount of variation in the braking torque of the disc rotor together with the amount of variation in the comparative example. 10: Disc rotor 12: Main body 22: Heat insulating layer 24: Heat conductive layer 26, 28: Friction surface
Claims (3)
体より熱伝導率の小さい断熱層を設けるとともに、その
断熱層の上に断熱層より熱伝導率の大きい熱伝導層を設
け、その熱伝導層の表面を摩擦面としたことを特徴とす
るディスクロータ。(1) A heat insulating layer having a lower thermal conductivity than the main body is provided on both sides of a metal body forming a disk shape, and a thermal conductive layer having a higher thermal conductivity than the heat insulating layer is provided on the heat insulating layer, A disc rotor characterized in that the surface of the heat conductive layer is a friction surface.
許請求の範囲第１項記載のディスクロータ。(2) The disc rotor according to claim 1, wherein the heat insulating layer and the heat conductive layer are thermally sprayed layers.
性の少なくとも一方において優れた材料により形成され
ている特許請求の範囲第１項および第２項のいずれかに
記載のディスクロータ。(3) The disc rotor according to any one of claims 1 and 2, wherein the heat conductive layer is made of a material that is superior to the main body in at least one of heat resistance and wear resistance.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62283819A JP2586522B2 (en) | 1987-11-10 | 1987-11-10 | Disk rotor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62283819A JP2586522B2 (en) | 1987-11-10 | 1987-11-10 | Disk rotor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01126443A true JPH01126443A (en) | 1989-05-18 |
| JP2586522B2 JP2586522B2 (en) | 1997-03-05 |
Family
ID=17670558
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62283819A Expired - Fee Related JP2586522B2 (en) | 1987-11-10 | 1987-11-10 | Disk rotor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2586522B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002535152A (en) * | 1999-01-19 | 2002-10-22 | エルンスト・ティーレンハウス・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング・ウント・コンパニー・コマンディトゲゼルシャフト | Processing method for flat surface of automobile disc brake |
| DE102004016096A1 (en) * | 2004-04-01 | 2005-10-20 | Volkswagen Ag | Brake disk for road vehicle has at least one intermediate layer and/or other layers with a coating giving increased thermal conductivity |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5659470U (en) * | 1979-10-15 | 1981-05-21 |
-
1987
- 1987-11-10 JP JP62283819A patent/JP2586522B2/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5659470U (en) * | 1979-10-15 | 1981-05-21 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002535152A (en) * | 1999-01-19 | 2002-10-22 | エルンスト・ティーレンハウス・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング・ウント・コンパニー・コマンディトゲゼルシャフト | Processing method for flat surface of automobile disc brake |
| DE102004016096A1 (en) * | 2004-04-01 | 2005-10-20 | Volkswagen Ag | Brake disk for road vehicle has at least one intermediate layer and/or other layers with a coating giving increased thermal conductivity |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2586522B2 (en) | 1997-03-05 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |