JP3054716B2 - Friction engagement device - Google Patents
Friction engagement deviceInfo
- Publication number
- JP3054716B2 JP3054716B2 JP2411954A JP41195490A JP3054716B2 JP 3054716 B2 JP3054716 B2 JP 3054716B2 JP 2411954 A JP2411954 A JP 2411954A JP 41195490 A JP41195490 A JP 41195490A JP 3054716 B2 JP3054716 B2 JP 3054716B2
- Authority
- JP
- Japan
- Prior art keywords
- engagement device
- ceramic
- thin film
- metal plate
- 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.)
- Expired - Lifetime
Links
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- Mechanical Operated Clutches (AREA)
- Braking Arrangements (AREA)
- Other Surface Treatments For Metallic Materials (AREA)
Description
【０００１】[0001]
【産業上の利用分野】この発明は、湿式摩擦材と、鋼
板、アルミ板等の金属板とが接合し、摩擦力を発生する
摩擦係合装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a frictional engagement device in which a wet friction material is joined to a metal plate such as a steel plate or an aluminum plate to generate a frictional force.
【０００２】[0002]
【従来の技術】従来の摩擦係合装置は図２５に示す如く
インプットシャフト６に嵌装されたハブ５のスプライン
部５１に嵌合する駆動板２と、リテーナ４のスプライン
部４１に嵌合する受動板１の接触によりトルクが伝達さ
れる。図において３はプレッシャープレート、７はピス
トンである。2. Description of the Related Art As shown in FIG. 25, a conventional friction engagement device fits a drive plate 2 fitted to a spline portion 51 of a hub 5 fitted to an input shaft 6, and a spline portion 41 of a retainer 4. The torque is transmitted by the contact of the passive plate 1. In the figure, 3 is a pressure plate, and 7 is a piston.
【０００３】一般に、摩擦係合装置には、小型軽量であ
ること、作動ショックが小さいこと、及びトルク容量の
高いことが要求され、しかもその要求はきわめて大きい
ものである。[0003] In general, a friction engagement device is required to be small and light, to have a small operating shock, and to have a high torque capacity, and the demands are extremely large.
【０００４】[0004]
【発明が解決すべき課題】しかしながら、従来の摩擦係
合装置にあっては、作動ショック低減のため摩擦係数の
低い潤滑油が多用されるので、小型化すれば必然的に低
トルク容量となってしまう。そのため作動押力を高く
し、トルク容量を大きくするため、湿式摩擦材のハクリ
寿命の低下、相手摩擦面（受動板）のヒートスポット発
生、及び熱変形、油圧ポンプの大型化、作動油のもれ、
などの耐久寿命に関する問題点、またこれらを解決する
ために安全率を考慮せねばならなくなり、装置自体の小
型化は困難であった。However, in the conventional friction engagement device, since a lubricating oil having a low friction coefficient is frequently used to reduce the operation shock, if the size is reduced, the torque capacity is inevitably reduced. Would. Therefore, to increase the operating pressing force and increase the torque capacity, the service life of the wet friction material is shortened, the heat spot is generated on the mating friction surface (passive plate) and thermal deformation, the hydraulic pump is enlarged, and the hydraulic oil And
However, in order to solve these problems relating to the durable life and to solve these problems, it is necessary to consider a safety factor, and it has been difficult to reduce the size of the device itself.
【０００５】[0005]
【課題を解決するための手段】この発明は、前記のよう
な課題を解決するために、金属板の摩擦面の少なくとも
一方の面にセラミックス薄膜合成法によるセラミックス
薄膜を形成させると共に、前記のセラミックス薄膜の、
膜厚分布を変化させたことを特徴とする摩擦係合装置が
提供される。セラミックス薄膜の膜厚分布を金属板の摩
擦面上に種々の形態で形成させることにより、高い動摩
擦係数（μｄ）及び高い静摩擦係数（μｓ）を得ること
ができ、また理想的なトルク波形を経時的変化なく維持
させることが可能となり、装置の小型化などが可能とな
る。According to the present invention, a ceramic thin film is formed on at least one of frictional surfaces of a metal plate by a ceramic thin film synthesis method, and the above-mentioned ceramic material is formed. Thin film,
There is provided a friction engagement device characterized by changing a film thickness distribution. By forming the thickness distribution of the ceramic thin film in various forms on the friction surface of the metal plate, a high dynamic friction coefficient (μd) and a high static friction coefficient (μs) can be obtained, and an ideal torque waveform can be obtained over time. It is possible to maintain the target without any significant change, and it is possible to reduce the size of the device.
【０００６】更に、セラミックス薄膜は、同一膜物質で
あっても、その合成法により著じるしく特性が異なるた
め要求特性に合った合成手法を選択する必要がある。そ
の摩擦特性の設計手法として、前記したセラミックス薄
膜の膜厚分布を変化させたことにより意図通りの摩擦特
性を有する製品を作成することができ、従って、前記の
問題点の解決が得られる。Further, even if the ceramic thin film is made of the same material, the characteristics are remarkably different depending on the synthesis method, so it is necessary to select a synthesis method that meets the required characteristics. As a method of designing the friction characteristics, by changing the thickness distribution of the ceramic thin film described above, it is possible to produce a product having the intended friction characteristics, and thus the above-mentioned problem can be solved.
【０００７】[0007]
【作 用】図２５に示す摩擦係合装置の受動板１を形成
する鋼板、アルミ板等の金属板の両面もしくは、片面に
セラミックス薄膜（例としてＴｉＣ、ＴｉＮ、ＳｉＣ、
Ｓｉ3 Ｎ4 、ＢＮ、Ａｌ2 Ｏ3 、ＴａＮ、ＣｒＮ、Ｔｉ
ＣＮ及びｉカーボン膜（非晶質透明硬質カーボン膜）等
が挙げられる。）の表面処理を施している。表面処理法
としては、薄膜合成法として、セラミック質の薄膜を母
材表面に合成する手法として、気相法、融液法、溶液塩
法、溶液法等が挙げられる。[Operation] A ceramic thin film (for example, TiC, TiN, SiC, or the like) is formed on both sides or one side of a metal plate such as a steel plate or an aluminum plate forming the passive plate 1 of the friction engagement device shown in FIG.
Si 3 N 4 , BN, Al 2 O 3 , TaN, CrN, Ti
CN and i carbon films (amorphous transparent hard carbon films) and the like. ) Surface treatment. Examples of the surface treatment method include a gas phase method, a melt method, a solution salt method, and a solution method as a method of synthesizing a ceramic thin film on a base material surface as a thin film synthesis method.
【０００８】受動板の処理後の表面粗さは粒子の小さい
もので処理した場合、下地面粗さと変らないため、処理
後の表面粗さの調整は、処理面を加工するか、下地面粗
さを処理前に設定しておくことが必要である。The surface roughness of the passive plate after treatment is the same as that of the underlying surface when the surface is treated with small particles. Therefore, the surface roughness after the treatment can be adjusted by processing the treated surface or Must be set before processing.
【０００９】従来受動板は駆動面からのトルクの伝達も
しくは熱の伝導の役目であったが、上記したような種々
の表面処理を施すことによって、図２６ないし図３１に
示すような摩擦特性の改善を得ることができる。（詳し
い説明は後述する。）Conventionally, the passive plate plays a role of transmitting torque or transmitting heat from the driving surface. However, by performing various surface treatments as described above, the passive plate has a frictional characteristic as shown in FIGS. An improvement can be obtained. (Detailed description will be given later.)
【００１０】[0010]
【実施例】図１は受動板１と駆動板２の関係の斜視図、
図２は側断面図を示し、受動板１は鋼板、アルミ板など
の金属板９からなり、スプライン歯９１を有している。FIG. 1 is a perspective view showing the relationship between a passive plate 1 and a driving plate 2.
FIG. 2 is a side sectional view. The passive plate 1 is made of a metal plate 9 such as a steel plate or an aluminum plate, and has spline teeth 91.
【００１１】駆動板２は金属板９の両面に湿式摩擦材８
が貼着されている。この発明においては、中央の受動板
１は両面にセラミックス処理が施されており、両端の受
動板１′、１′には片面のみにセラミックス表面処理が
施されている。The drive plate 2 has a wet friction material 8 on both sides of a metal plate 9.
Is affixed. In the present invention, the central passive plate 1 is subjected to ceramics treatment on both sides, and the passive plates 1 ', 1' at both ends are subjected to ceramics surface treatment on only one surface.
【００１２】図３は受動板１のスプライン歯９１の近辺
の拡大図であり、図４、図５は図３のＸ−Ｘ断面図を示
す。図４は金属板９の全面にセラミックス薄膜１０が施
されている場合、図５は片面のみに薄膜が存在する場合
を示している。FIG. 3 is an enlarged view of the vicinity of the spline teeth 91 of the passive plate 1, and FIGS. 4 and 5 are sectional views taken along line XX of FIG. FIG. 4 shows a case where the ceramic thin film 10 is provided on the entire surface of the metal plate 9, and FIG. 5 shows a case where the thin film exists on only one surface.
【００１３】図４、図５においては、理解しやすいよう
に、金属板９の大きさに対して薄膜１０の厚さを誇張し
て示している。図６は別な実施例の斜視図、図７は互に
相接した場合の側断面図を示し、受動板１と駆動板２は
何れも片面のみに湿式摩擦材８が接着され、その反対面
は金属板が表れ、セラミックス表面処理が施されてい
る。In FIGS. 4 and 5, the thickness of the thin film 10 is exaggerated relative to the size of the metal plate 9 for easy understanding. FIG. 6 is a perspective view of another embodiment, and FIG. 7 is a side sectional view when they are in contact with each other. Both the passive plate 1 and the driving plate 2 have a wet friction material 8 adhered to only one surface, and the opposite. A metal plate appears on the surface, and a ceramic surface treatment is applied.
【００１４】図８ないし図１１は図６に示す実施例の表
面処理の態様を示し、図８は受動板１のセラミックス処
理側の表面を示し、図９はそのＸ−Ｘ断面図、図１０は
駆動板２のセラミックス処理側の表面を示し、図１１は
そのＹ−Ｙ断面図である。何れの図も８は湿式摩擦材
を、１０はセラミックス薄膜を示し、又黒点は薄膜分布
を示している。又薄膜１０は内周側が厚みを増すように
膜厚が変化している。FIGS. 8 to 11 show the form of the surface treatment of the embodiment shown in FIG. 6, FIG. 8 shows the surface of the passive plate 1 on the ceramics treatment side, FIG. Shows the surface of the drive plate 2 on the ceramics processing side, and FIG. 11 is a sectional view taken along the line YY. In each of the figures, 8 indicates a wet friction material, 10 indicates a ceramic thin film, and black dots indicate a thin film distribution. The film thickness of the thin film 10 is changed so that the inner peripheral side increases in thickness.
【００１５】図１２ないし図２４はセラミックス表面処
理の種々の変形例を示し、図１２、図１４、図１６、図
１９、図２１、図２３はセラミックス表面処理側の表面
を示し、それらの図の次の図はそのＸ−Ｘ断面図を示し
ている。図１２、図１３は図８の変形であり、図１４、
図１５は薄膜の厚みが段階的に変化している例を示し、
図１６、図１７、図１８はセラミックス表面処理が部分
的にされている例であって、図１７は中央の板、図１８
は端部にある板に該当する。FIGS. 12 to 24 show various modifications of the ceramic surface treatment, and FIGS. 12, 14, 16, 19, 21 and 23 show the surface on the ceramic surface treatment side. The following figure shows a sectional view taken along line XX. 12 and 13 are modifications of FIG. 8, and FIG.
FIG. 15 shows an example in which the thickness of the thin film changes stepwise,
FIGS. 16, 17, and 18 show examples in which the ceramic surface treatment is partially performed. FIG.
Corresponds to the plate at the end.
【００１６】図１９、図２０は表面処理を一部施してい
ない例であって、その部分が円周方向に油溝１１となり
うる形態となっている。この例では外周部の方に未処理
部の巾を大きくすることにより、内周部の歪分布を平均
化し、冷却性を向上させることができる。図２１、図２
２は図１９の変形であって、未処理部が閉じられた形状
１２となっていて、冷却効果や、内外周の処理面積のバ
ランスから形状、個数、大きさ、位置などを使用条件に
よって決定する。FIGS. 19 and 20 show an example in which the surface treatment is not partially performed, and the portion can be formed into an oil groove 11 in the circumferential direction. In this example, by increasing the width of the unprocessed portion toward the outer peripheral portion, the strain distribution in the inner peripheral portion can be averaged, and the cooling performance can be improved. FIG. 21, FIG.
19 is a modification of FIG. 19, in which the unprocessed portion is a closed shape 12, and the shape, the number, the size, the position, and the like are determined according to the use condition from the cooling effect and the balance of the inner and outer processing areas. I do.
【００１７】図２３、図２４は未処理部が半径方向の溝
１４となっている場合であって、使用条件から、外周と
内周の処理面積のバランスを考慮して角度、本数、貫通
又は未貫通などを決定する。なお、図８以降に種々あげ
た例以外にも様々な態様が可能である。FIGS. 23 and 24 show the case where the unprocessed portion is a groove 14 in the radial direction. In consideration of the use conditions, the angle, number, penetration, Determine non-penetration, etc. In addition, various modes other than the examples given variously after FIG. 8 are possible.
【００１８】図２６ないし図２９は耐久試験におけるす
べり速度の変化に応じた摩擦力（トルク）の特性を表し
ている。図２６はこの発明のものの耐久初期の特性、図
２７は従来のものの耐久初期の特性、図２８はこの発明
のものの、図２９は従来のものの耐久後の特性を夫々示
している。FIGS. 26 to 29 show the characteristics of the frictional force (torque) according to the change in the sliding speed in the durability test. 26 shows the characteristics of the device of the present invention in the early stage of durability, FIG. 27 shows the characteristics of the conventional device in the early stage of durability, FIG. 28 shows the characteristics of the device of the present invention, and FIG. 29 shows the characteristics of the conventional device after durability.
【００１９】何れの図もたて軸はクラッチトルク（摩擦
力）を示し、横軸は制動時間（回転したフライホイール
を停止させるのに必要とする時間を示し、Ａはこの発明
のもの、Ｂは従来のものの変化を示す。従来のものでは
回転数が０になる直前にルースタテイルとよばれるピー
クが発生し、μ−Ｖ特性（すべり速度の変化に伴う摩擦
係数μの変化を表す特性）も、作動ショックに不利とな
る右上りの特性を示す。In each of the figures, the vertical axis shows the clutch torque (frictional force), the horizontal axis shows the braking time (the time required to stop the rotated flywheel, A is the invention, B is Indicates a change of the conventional one, and in the conventional one, a peak called a rooster tail occurs immediately before the rotation speed becomes 0, and the μ-V characteristic (the characteristic indicating the change of the friction coefficient μ with the change of the sliding speed) is also obtained. In addition, the upper right characteristic which is disadvantageous to the operation shock is shown.
【００２０】この発明では、同じ湿式摩擦材、同じ潤滑
油を用いて、ルースタテイルは消滅し、μ−Ｖ特性もフ
ラットもしくは右下りの傾向を示し、トルク（動摩擦係
数μｄ、静摩擦係数μｓ）の絶対レベルも２０〜４０％
向上する結果が出ている。これは作動ショックに非常に
有利であるばかりでなく、連続滑りに使用された際にも
ジャダー等の自励振動発生を抑制しながら高トルク容量
を得ることが可能となる。In the present invention, using the same wet friction material and the same lubricating oil, the rooster tail disappears, the μ-V characteristic also shows a tendency to flatten or go down to the right, and the absolute value of the torque (dynamic friction coefficient μd, static friction coefficient μs) is reduced. The level is 20-40%
The results have improved. This is not only very advantageous for operating shock, but also makes it possible to obtain a high torque capacity while suppressing the occurrence of self-excited vibration such as judder when used for continuous sliding.
【００２１】図３０と図３１はこの発明のものと従来品
の耐久試験中の摩擦係数（動・静）の経時変化を示す。
図３０は動摩擦係数、図３１は静摩擦係数について夫々
示し、何れの図もＡはこの発明のもの、Ｂは従来品の変
化を示している。Ａはどちらも安定しており、サイクル
数（試験回数）に関係なくフラットである。それに対し
従来品は大きな経時変化を示している。FIGS. 30 and 31 show the change over time in the coefficient of friction (dynamic / static) of the device of the present invention and the conventional product during the durability test.
FIG. 30 shows the dynamic friction coefficient, and FIG. 31 shows the static friction coefficient. In each figure, A shows the change of the present invention and B shows the change of the conventional product. A is stable, and is flat regardless of the number of cycles (the number of tests). On the other hand, the conventional product shows a large change with time.
【００２２】[0022]
【発明の効果】この発明の摩擦係合装置は前記の如き構
成であって、(1) 動摩擦係数及び静摩擦係数の向上、
(2) 摩擦特性の改善によるピーク発生の解消、(3) 長期
使用における摩擦係数の経時変化の改善が、摩擦係合装
置の小型、軽量化、及び高トルク容量を得て、それによ
り信頼性の高い製品を提供できるという効果を得たもの
である。The friction engagement device according to the present invention has the above-described configuration, and (1) improves the dynamic friction coefficient and the static friction coefficient;
(2) Elimination of peak generation by improving friction characteristics, and (3) Improvement of friction coefficient over time during long-term use, resulting in a smaller, lighter, and higher torque capacity of the friction engagement device, thereby improving reliability. The effect is that a product with high quality can be provided.
【００２３】なお、この発明の摩擦係合装置は実施例に
示した多板クラッチのみならず、トルクコンバーターの
直結クラッチ、ブレーキバンド、変速機のシンクロナイ
ザーリング等、多くの用途に用いられる。The friction engagement device of the present invention is used not only for the multi-plate clutch shown in the embodiment, but also for various applications such as a direct coupling clutch of a torque converter, a brake band, and a synchronizer ring of a transmission.
【図１】受動板と駆動板の配列を示す図FIG. 1 shows an arrangement of a passive plate and a driving plate.
【図２】側断面図FIG. 2 is a side sectional view
【図３】一部拡大図FIG. 3 is a partially enlarged view
【図４、図５】図３のＸ−Ｘの断面図4 and 5 are cross-sectional views taken along line XX of FIG.
【図６】別な実施例の配列を示す図FIG. 6 shows an arrangement of another embodiment.
【図７】側断面図FIG. 7 is a side sectional view;
【図８】一実施例の正面図FIG. 8 is a front view of one embodiment.
【図９】図８のＸ−Ｘ断面図9 is a sectional view taken along line XX of FIG.
【図１０】別実施例の正面図FIG. 10 is a front view of another embodiment.
【図１１】図１０のＸ−Ｘ断面図11 is a sectional view taken along line XX of FIG.
【図１２】別実施例の正面図FIG. 12 is a front view of another embodiment.
【図１３】図１２のＸ−Ｘ断面図FIG. 13 is a sectional view taken along line XX of FIG. 12;
【図１４】別実施例の正面図FIG. 14 is a front view of another embodiment.
【図１５】図１４のＸ−Ｘ断面図FIG. 15 is a sectional view taken along line XX of FIG. 14;
【図１６】別実施例の正面図FIG. 16 is a front view of another embodiment.
【図１７、図１８】図１６のＸ−Ｘ断面図17 and 18 are XX cross-sectional views of FIG.
【図１９】別実施例の正面図FIG. 19 is a front view of another embodiment.
【図２０】図１９のＸ−Ｘ断面図20 is a sectional view taken along line XX of FIG. 19;
【図２１】別実施例の正面図FIG. 21 is a front view of another embodiment.
【図２２】図２１のＸ−Ｘ断面図FIG. 22 is a sectional view taken along line XX of FIG. 21;
【図２３】別実施例の正面図FIG. 23 is a front view of another embodiment.
【図２４】図２３のＸ−Ｘ断面図24 is a sectional view taken along line XX of FIG.
【図２５】摩擦係合装置の一例の側断面図FIG. 25 is a side sectional view of an example of the friction engagement device.
【図２６】この発明のもののクラッチトルクと制動時間
の耐久初期の関係を示す図FIG. 26 is a diagram showing a relationship between clutch torque and braking time in the initial stage of durability according to the present invention.
【図２７】従来のものの図２６と同様な図FIG. 27 is a diagram similar to FIG. 26 of a conventional device.
【図２８】この発明のものの耐久後の図２６と同様な図FIG. 28 is a view similar to FIG. 26 after durability of the thing of the present invention.
【図２９】従来のものの耐久後の図２６と同様な図FIG. 29 is a view similar to FIG. 26 after the endurance of the conventional one.
【図３０】動摩擦係数の経時変化を示す図FIG. 30 is a diagram showing a change with time of a dynamic friction coefficient.
【図３１】静摩擦係数の経時変化を示す図FIG. 31 is a diagram showing a change over time in a coefficient of static friction.
１ 受動板 ２ 駆動板 ３ プレッシャープレート ４ リテーナ ４１ スプライン部 ５ ハブ ５１ スプライン部 ６ インプットシャフト ７ ピストン １０ セラミックス薄膜 １１ 溝 １２ 閉じた溝又は孔 DESCRIPTION OF SYMBOLS 1 Passive plate 2 Drive plate 3 Pressure plate 4 Retainer 41 Spline part 5 Hub 51 Spline part 6 Input shaft 7 Piston 10 Ceramic thin film 11 Groove 12 Closed groove or hole
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 平４−249628（ＪＰ，Ａ) 特開 平２−278022（ＪＰ，Ａ) 特公 昭46−15043（ＪＰ，Ｂ１) (58)調査した分野(Int.Cl.7，ＤＢ名) F16D 13/62 C23C 30/00 F16D 69/00 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-4-249628 (JP, A) JP-A-2-278022 (JP, A) JP-B-46-15043 (JP, B1) (58) Field (Int.Cl. 7 , DB name) F16D 13/62 C23C 30/00 F16D 69/00
Claims (5)
板とが接合し、摩擦力を発生する摩擦係合装置におい
て、 金属板の摩擦面の少なくとも一方の面にセラミックス薄
膜合成法によるセラミックス薄膜を形成させると共に、
前記のセラミックス薄膜の、膜厚分布を変化させたこと
を特徴とする摩擦係合装置。1. A friction engagement device in which a wet friction material is joined to a metal plate such as a steel plate or an aluminum plate to generate a frictional force, wherein at least one of the friction surfaces of the metal plate is formed by a ceramic thin film synthesis method. Rutotomoni to form a ceramic film,
A friction engagement device characterized in that the thickness distribution of the ceramic thin film is changed .
属板において、金属板の下地粗さもしくはセラミックス
薄膜の表面粗さ分布を変化させたことを特徴とする請求
項１記載の摩擦係合装置。2. Gold subjected to the above-mentioned ceramic surface treatment
In metal plates, the roughness of the metal plate or ceramics
Claims characterized by changing the surface roughness distribution of the thin film
Item 3. The friction engagement device according to Item 1 .
属板において、セラミックス粒子の大きさを同一表面上
において変化させたことを特徴とする請求項１または２
記載の摩擦係合装置。3. The size of the ceramic particles on the same surface of the metal plate subjected to the above-mentioned ceramic surface treatment.
Characterized in that varying according to claim 1 or 2
The friction engagement device according to claim 1.
属板において、２種類以上のセラミック質を薄膜として
形成させたことを特徴とする請求項１〜３の何れか１項
記載の摩擦係合装置。4. In the metal plate which has been subjected to the ceramic surface treatment, two or more types of ceramics are used as a thin film.
The frictional engagement device of any one of claims 1 to 3, characterized in that to form.
属板において、前記セラミックス表面処理が、部分的に
施されていることを特徴とする請求項１〜４の何れか１
項記載の摩擦係合装置。5. In the metal plate subjected to the ceramic surface treatment, the ceramic surface treatment is partially performed.
The method according to any one of claims 1 to 4, wherein
Item 8. The friction engagement device according to Item 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2411954A JP3054716B2 (en) | 1990-12-20 | 1990-12-20 | Friction engagement device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2411954A JP3054716B2 (en) | 1990-12-20 | 1990-12-20 | Friction engagement device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04366029A JPH04366029A (en) | 1992-12-17 |
| JP3054716B2 true JP3054716B2 (en) | 2000-06-19 |
Family
ID=18520863
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2411954A Expired - Lifetime JP3054716B2 (en) | 1990-12-20 | 1990-12-20 | Friction engagement device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3054716B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102016210829B4 (en) | 2015-06-29 | 2021-12-16 | GM Global Technology Operations LLC | Aluminum gear components with an electro-ceramic coating |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2582215Y2 (en) * | 1992-07-23 | 1998-09-30 | エヌエスケー・ワーナー株式会社 | Friction engagement device |
| US5535870A (en) * | 1995-04-13 | 1996-07-16 | Dynax Corporation | Wet multidisc friction engaging device |
| JP4304598B2 (en) * | 2001-09-27 | 2009-07-29 | 株式会社豊田中央研究所 | High friction sliding member |
| JP4263014B2 (en) | 2003-04-18 | 2009-05-13 | 株式会社ダイナックス | Friction mating material coated with hard coating |
| JP4813037B2 (en) * | 2004-10-06 | 2011-11-09 | Ｎｓｋワーナー株式会社 | Wet multi-plate clutch friction plate |
| JP2007146927A (en) * | 2005-11-25 | 2007-06-14 | Nsk Warner Kk | Lock-up clutch |
| JP2008002558A (en) * | 2006-06-22 | 2008-01-10 | Nsk Warner Kk | Wet type friction plate and wet type multiple disc clutch using the same |
-
1990
- 1990-12-20 JP JP2411954A patent/JP3054716B2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102016210829B4 (en) | 2015-06-29 | 2021-12-16 | GM Global Technology Operations LLC | Aluminum gear components with an electro-ceramic coating |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH04366029A (en) | 1992-12-17 |
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