JP2002242954A - Frictional disk - Google Patents

Frictional disk

Info

Publication number
JP2002242954A
JP2002242954A JP2001037011A JP2001037011A JP2002242954A JP 2002242954 A JP2002242954 A JP 2002242954A JP 2001037011 A JP2001037011 A JP 2001037011A JP 2001037011 A JP2001037011 A JP 2001037011A JP 2002242954 A JP2002242954 A JP 2002242954A
Authority
JP
Japan
Prior art keywords
diameter side
friction
oil
plate
side row
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
Application number
JP2001037011A
Other languages
Japanese (ja)
Inventor
Atsushi Mori
篤 森
Takeshi Otsuki
武 大槻
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin AW Co Ltd
Original Assignee
Aisin AW Co Ltd
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 Aisin AW Co Ltd filed Critical Aisin AW Co Ltd
Priority to JP2001037011A priority Critical patent/JP2002242954A/en
Publication of JP2002242954A publication Critical patent/JP2002242954A/en
Pending legal-status Critical Current

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
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/648—Clutch-plates; Clutch-lamellae for clutches with multiple lamellae
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0284—Multiple disk type lock-up clutch
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0289—Details of friction surfaces of the lock-up clutch

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a frictional disk, which is formed with a good yield at a low cost by arranging and fixing segment-like frictional materials at prescribed positions and reduces a drag at the release of a clutch. SOLUTION: The segment-like frictional materials 10 and 11 are arranged and fixed in at least two lines of an outer diameter side line and an inner diameter side line or more so that the total channel area of oil grooves (a) formed on the inner diameter side line becomes larger than the total channel area of oil grooves c formed on the outer diameter side line. When the frictional disk 1 is rotated, oil flows to the outer diameter side by centrifugal force to achieve an effect to cool frictional heat at linear portions shown by an arrow A, and oil is accumulated in oil grooves b due to the difference between the total channel areas of the oil grooves (a) and the oil grooves c to generate pressure, and the riding force over the thickness of the frictional material 10 is generated at nearly T-shaped butt portions shown by an arrow B. At a clutch release, separating force between the frictional plate 1 and a separator plate, for example, is applied in cooperation with the pressure of the oil grooves b and riding force over the T-shaped butt portions, thereby resulting in so-called good disengagement of a clutch.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】本発明は、摩擦係合要素を構
成する摩擦板に係り、詳しくは、例えば自動変速機の所
定形状からなるセグメント状の摩擦材をコアプレート表
面上の所定位置に配置・固着され、所定形状の油溝が形
成された摩擦板に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a friction plate which constitutes a friction engagement element, and more particularly, for example, a segment-shaped friction material having a predetermined shape of an automatic transmission is arranged at a predetermined position on a surface of a core plate. The present invention relates to a friction plate which is fixed and has an oil groove of a predetermined shape.

【０００２】[0002]

【従来の技術】従来、摩擦板（以下、「フリクションプ
レート」とする。）は、例えば自動変速機の多板クラッ
チ、多板ブレーキ、ロックアップクラッチ等に摩擦係合
要素として使用されており、フェノール樹脂をしみ込ま
せた紙等からなる摩擦材がコアプレートの表面上に固着
されることで構成されている。このようなクラッチ（又
はブレーキ）は、クラッチ解放に際して、いわゆるクラ
ッチの切れが悪いために引きずりが発生するという問題
がある。2. Description of the Related Art Conventionally, friction plates (hereinafter referred to as "friction plates") have been used as friction engagement elements in, for example, a multi-plate clutch, a multi-plate brake, and a lock-up clutch of an automatic transmission. A friction material made of paper or the like impregnated with a phenol resin is fixed on the surface of the core plate. Such a clutch (or a brake) has a problem in that when the clutch is released, dragging occurs due to poor so-called disconnection of the clutch.

【０００３】そこで、クラッチの切れを良くする方法と
して、例えば特開平１１−１４１５７０号公報に示され
るものが提案されている。このものは、コアプレートの
表面上の摩擦材に、内週側より外周側に貫通する油溝
と、外周側には貫通しない油溝と、を有しており、クラ
ッチ解放に際して、フリクションプレートの回転に基づ
く遠心力によって貫通しない油溝に油を溜めて油圧を生
じさせ、該油圧がフリクションプレートとセパレータプ
レートとを引き離す方向に力を発生させることで、クラ
ッチの切れを良くして引きずりを低減している。Therefore, as a method of improving the disengagement of the clutch, for example, a method disclosed in Japanese Patent Application Laid-Open No. H11-141570 has been proposed. The friction plate on the surface of the core plate has an oil groove penetrating from the inner side to the outer peripheral side, and an oil groove not penetrating to the outer peripheral side. Oil is accumulated in oil grooves that do not penetrate due to centrifugal force due to rotation, and hydraulic pressure is generated, and this hydraulic pressure generates force in the direction separating the friction plate and separator plate, improving clutch disengagement and reducing drag are doing.

【０００４】[0004]

【発明が解決しようとする課題】しかし、上記従来の技
術のものは、油溝を有する摩擦材をその型に合わせて製
作するため、また、１枚の摩擦材により構成されている
ため、歩留りが悪くコストが高くなっていた。また、前
記貫通しない油溝は、潤滑油の流れが不安定であり、特
にクラッチ解放時又はスリップ制御時等、フリクション
プレート及びセパレータプレートとが接触しつつ相対回
転をする場合、油の流れが不安定で制御精度に影響を及
ぼすと共に、摩擦材への油の流れ不良による発熱の原因
になる虞がある。However, in the above-mentioned prior art, the yield is increased because a friction material having an oil groove is manufactured in accordance with the type of the friction material, and the friction material is constituted by one friction material. Was bad and the cost was high. In addition, the oil groove that does not penetrate has an unstable flow of the lubricating oil. In particular, when the friction plate and the separator plate rotate relative to each other while coming into contact with each other, such as when the clutch is released or slip control is performed, the flow of the oil is not stable. It is stable and affects control accuracy, and may cause heat generation due to poor oil flow to the friction material.

【０００５】そこで本発明は、セグメント状の摩擦材を
所定位置に配置・固着し、歩留りを良くしてコストダウ
ンを図ると共に、摩擦材に供給される油の流れを安定
し、かつクラッチの解放に際して引きずりを低減する摩
擦板を提供することを目的とする。Accordingly, the present invention is to dispose and fix a segment-shaped friction material at a predetermined position to improve the yield and reduce the cost, stabilize the flow of oil supplied to the friction material, and release the clutch. It is an object of the present invention to provide a friction plate that reduces drag.

【０００６】[0006]

【課題を解決するための手段】請求項１に係る本発明は
（例えば図２、図３及び図４参照）、円板状のコアプレ
ート（７）と、所定形状からなるセグメント状の複数の
摩擦材（１０，１１）と、を備え、前記コアプレート
（７）の表面上に前記各摩擦材（１０，１１）を固着
し、前記各摩擦材（１０，１１）間の隙間（ｓ１〜ｓ
６）によって油溝（ａ，ｂ，ｃ）を形成してなる摩擦板
において、前記摩擦材（１０，１１）は、前記コアプレ
ート（７）上に内径側列（例えば１１の列）と外径側列
（例えば１０の列）との少なくとも２列に、かつ、これ
ら内径側列（例えば１１の列）と外径側列（例えば１０
の列）との間に前記油溝（ｂ）を有するように、また前
記内径側列（例えば１１の列）に形成される前記油溝
（ａ）の総流路面積が、前記外径側列（例えば１０の
列）に形成される前記油溝（ｃ）の総流路面積より大き
くなるように配置・固着される、ことを特徴とする摩擦
板（１）にある。The present invention according to claim 1 (for example, see FIGS. 2, 3 and 4) comprises a disc-shaped core plate (7) and a plurality of segment-shaped segments having a predetermined shape. And a friction material (10, 11), wherein the friction material (10, 11) is fixed on the surface of the core plate (7), and a gap (s1 to s1) between the friction material (10, 11) is provided. s
In the friction plate having the oil grooves (a, b, c) formed by 6), the friction members (10, 11) are arranged on the core plate (7) with the inner diameter side row (for example, the row of 11) and the outer side. At least two rows including a radial side row (for example, 10 rows), and an inner diameter side row (for example, 11 rows) and an outer diameter side row (for example, 10 rows).
), And the total flow area of the oil grooves (a) formed in the inner diameter side row (for example, 11 rows) is smaller than the outer diameter side. The friction plate (1) is arranged and fixed so as to be larger than a total flow area of the oil grooves (c) formed in a row (for example, 10 rows).

【０００７】請求項２に係る本発明は（例えば図２、図
３及び図４参照）、前記油溝（ａ，ｂ，ｃ）は、前記外
径側列（例えば１０の列）及び前記内径側列（例えば１
１の列）に配置・固着される前記摩擦材（１０，１１）
の位置により、前記コアプレート（７）の半径方向に突
当る略々Ｔ字状の部分（例えば矢印Ｂ、矢印Ｃ及び矢印
Ｆ）を有してなる、請求項１記載の摩擦板（１）にあ
る。According to a second aspect of the present invention (see, for example, FIGS. 2, 3 and 4), the oil grooves (a, b, c) are provided in the outer diameter side row (for example, 10 rows) and the inner diameter side row. Side row (for example, 1
The friction material (10, 11) arranged and fixed on the first row)
2. The friction plate (1) according to claim 1, wherein the friction plate (1) has a substantially T-shaped portion (for example, an arrow B, an arrow C, and an arrow F) that abuts in a radial direction of the core plate (7) depending on the position of the core plate. It is in.

【０００８】請求項３に係る本発明は（例えば図２及び
図４参照）、前記油溝（ａ，ｂ，ｃ）は、前記外径側列
（例えば１０の列）及び前記内径側列（例えば１１の
列）に配置される前記摩擦材（１０，１１）の位置によ
り、前記外径側列（例えば１０の列）における各摩擦材
（１０）の間の油溝（ｃ）と前記内径側列（例えば１１
の列）における各摩擦材（１１）の間の油溝（ａ）が前
記コアプレート（７）の半径方向に直線的に連通する部
分（例えば矢印Ａ及び矢印Ｅ）を有してなる、請求項１
又は２記載の摩擦板（１）にある。According to a third aspect of the present invention (see, for example, FIGS. 2 and 4), the oil grooves (a, b, c) are provided in the outer diameter side row (for example, 10 rows) and the inner diameter side row (for example, 10 rows). For example, depending on the position of the friction material (10, 11) arranged in the eleventh row, the oil groove (c) between the friction materials (10) in the outer diameter side row (e.g., the tenth row) and the inner diameter Side row (for example, 11
), The oil groove (a) between the friction members (11) has a portion (for example, arrow A and arrow E) that linearly communicates in the radial direction of the core plate (7). Item 1
Or 2) the friction plate (1).

【０００９】請求項４に係る本発明は（例えば図１参
照）、車輌用自動変速機の摩擦係合装置（２０）におけ
る摩擦係合要素として適用されてなる、請求項１ないし
３のいずれか記載の摩擦板（１）にある。The present invention according to claim 4 (see, for example, FIG. 1) is applied as a friction engagement element in a friction engagement device (20) of an automatic transmission for a vehicle. In the described friction plate (1).

【００１０】なお、上記カッコ内の符号は、図面と対照
するためのものであるが、これは、発明の理解を容易に
するための便宜的なものであり、特許請求の範囲の構成
に何等影響を及ぼすものではない。Note that the reference numerals in parentheses are for the purpose of contrasting with the drawings, but are for convenience of understanding of the invention, and are not limited to the structure of the claims. It has no effect.

【００１１】[0011]

【発明の効果】請求項１に係る本発明によると、セグメ
ント状の複数の摩擦材を、コアプレート上に内径側列と
外径側列との少なくとも２列に、かつ内径側列に形成さ
れる油溝の総流路面積が、外径側列に形成される油溝の
総流路面積より大きくなるように配置・固着されるの
で、歩留りを良くしてコストダウンするものでありなが
ら、前記油溝、就中内径側列と外径側列との間の油溝に
油を溜めて油圧を生じさせ、クラッチ又はブレーキ解放
の際には、該油圧に基づいて摩擦板と例えばセパレータ
プレートとの間に引き離す力が生じて、クラッチの切れ
を良くし、クラッチ又はブレーキの引きずりを低減する
ことができる。According to the first aspect of the present invention, a plurality of segment-shaped friction materials are formed on the core plate in at least two rows of the inner diameter side row and the outer diameter side row and in the inner diameter side row. Is arranged and fixed so that the total flow area of the oil grooves formed in the outer diameter side row is larger than the total flow area of the oil grooves formed in the outer diameter side row, while improving the yield and reducing the cost. The oil groove, especially oil is stored in the oil groove between the inner diameter side row and the outer diameter side row to generate hydraulic pressure, and when the clutch or brake is released, the friction plate and the separator plate based on the hydraulic pressure are used. And a separating force is generated between them, so that the disengagement of the clutch can be improved and the drag of the clutch or the brake can be reduced.

【００１２】請求項２に係る本発明によると、油溝は、
外径側列及び内径側列に配置・固着される摩擦材の位置
により、コアプレートの半径方向に突当る略々Ｔ字状の
部分を有しているので、クラッチ又はブレーキを解放さ
せる際に、Ｔ字状の突当り部分において、油の運動エネ
ルギが摩擦材に作用し、これが摩擦板と例えばセパレー
タプレートとの間に油が入り込む力となって、両者を引
き離す力を発生させることができる。それにより、クラ
ッチ又はブレーキの解放に際して、流量の差異より生じ
る油圧と相俟って、更にクラッチの切れを良くすること
ができる。According to the second aspect of the present invention, the oil groove is
Depending on the position of the friction material arranged and fixed in the outer diameter side row and the inner diameter side row, the core plate has a substantially T-shaped portion which abuts in the radial direction, so that when releasing the clutch or brake, The kinetic energy of the oil acts on the friction material at the T-shaped abutting portion, and this acts as a force for oil to enter between the friction plate and, for example, the separator plate, thereby generating a force for separating the two. Thereby, when the clutch or the brake is released, the disengagement of the clutch can be further improved in combination with the hydraulic pressure generated due to the difference in the flow rate.

【００１３】請求項３に係る本発明によると、油溝は、
外径側列及び内径側列に配置される摩擦材の位置によ
り、外径側列における各摩擦材の間の油溝と内径側列に
おける各摩擦材の間の油溝がコアプレートの半径方向に
直線的に連通する部分を有しているので、例えば油圧及
び油の運動エネルギに基づく摩擦板とセパレータプレー
トとを引離す力をバランス良く得るものでありながら、
直線的に連通する部分を油が流れることにより、摩擦板
に発生している摩擦熱を冷却する効果も充分に得ること
ができる。According to the third aspect of the present invention, the oil groove is
Depending on the position of the friction material arranged in the outer diameter side row and the inner diameter side row, the oil groove between each friction material in the outer diameter side row and the oil groove between each friction material in the inner diameter side row in the radial direction of the core plate. Since it has a portion that communicates linearly with, for example, while obtaining a well-balanced force separating the friction plate and the separator plate based on the kinetic energy of oil pressure and oil,
By flowing the oil through the linearly communicating portions, the effect of cooling the frictional heat generated in the friction plate can be sufficiently obtained.

【００１４】請求項４に係る本発明によると、摩擦板
は、車輌用自動変速機の摩擦係合装置における摩擦係合
要素として適用されるので、変速などの制御を、より精
度の高いものにすると共に滑らかなものにすることがで
きる。According to the fourth aspect of the present invention, the friction plate is applied as a friction engagement element in a friction engagement device of an automatic transmission for a vehicle. And can be smooth.

【００１５】[0015]

【発明の実施の形態】＜第１の実施の形態＞以下、本発
明に係る第１の実施の形態について図に沿って説明す
る。図１は多板クラッチ（又はブレーキ）２０を示す断
面図である。図１に示すように、例えば自動変速機の摩
擦係合装置として適用される多板クラッチ（又はブレー
キ）２０は、略々円筒形のスプライン５の内周面にスプ
ライン係合している複数のセパレータプレート２と、略
々円筒形のハブ８の外周面にスプライン係合している複
数のフリクションプレート１と、不図示の油圧ピストン
により図中左方から押圧された際にフリクションプレー
ト１とセパレータプレート２とを支持するためのリテー
ニングプレート３及びスナップリング４とを備えて構成
されている。スプライン５の外周面が、例えばドラムな
どの回転部材に備えられているとクラッチを構成し、例
えばミッションケースなどの固定部材に備えられている
とブレーキを構成する。DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment A first embodiment according to the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view showing a multi-plate clutch (or brake) 20. As shown in FIG. 1, for example, a multiple disc clutch (or brake) 20 applied as a friction engagement device of an automatic transmission has a plurality of splines 5 that are spline-engaged with the inner peripheral surface of a substantially cylindrical spline 5. A separator plate 2, a plurality of friction plates 1 spline-engaged with an outer peripheral surface of a substantially cylindrical hub 8, and a friction plate 1 and a separator when pressed from the left side in the figure by a hydraulic piston (not shown) It comprises a retaining plate 3 and a snap ring 4 for supporting the plate 2. When the outer peripheral surface of the spline 5 is provided on a rotating member such as a drum, it constitutes a clutch, and when it is provided on a fixed member such as a transmission case, it constitutes a brake.

【００１６】本発明の要部となるフリクションプレート
１は、コアプレート７とその両表面上に配置・固着され
ている摩擦材１０，１１（詳しくは後述する）とから構
成されており、上記ハブ８の外周面を軸とするような中
空の円板形状に形成されている。また、フリクションプ
レート１の内周面は、上述のようにハブ８の外周面とス
プライン係合しており、該ハブ８のスプラインに備えら
れた給油口６より潤滑油が供給される。つまり、フリク
ションプレート１が回転すると、その遠心力によって油
がフリクションプレート１の内周側より外周側に流動す
る。The friction plate 1 which is a main part of the present invention comprises a core plate 7 and friction members 10 and 11 (details will be described later) disposed and fixed on both surfaces thereof. 8 is formed in a hollow disk shape having the outer peripheral surface as an axis. The inner peripheral surface of the friction plate 1 is spline-engaged with the outer peripheral surface of the hub 8 as described above, and lubricating oil is supplied from an oil supply port 6 provided in the spline of the hub 8. That is, when the friction plate 1 rotates, the oil flows from the inner peripheral side to the outer peripheral side of the friction plate 1 due to the centrifugal force.

【００１７】ついで、本発明に係るフリクションプレー
ト１について図２に沿って説明する。図２は第１の実施
の形態に係るフリクションプレート１を示す一部省略正
面図である。図２に示すように、フリクションプレート
１は、コアプレート７の表面上に摩擦材１０及び摩擦材
１１が、外周側列と内周側列との少なくとも２列以上に
なるように配置・固着されている。摩擦材１０及び摩擦
材１１は、それぞれ所定の同形状にセグメント化するこ
とで、歩留りを良くすることができ、つまりコストダウ
ンすることができる。Next, the friction plate 1 according to the present invention will be described with reference to FIG. FIG. 2 is a partially omitted front view showing the friction plate 1 according to the first embodiment. As shown in FIG. 2, the friction plate 1 has friction members 10 and 11 arranged and fixed on the surface of the core plate 7 in at least two rows, an outer row and an inner row. ing. The friction material 10 and the friction material 11 are each segmented into a predetermined same shape, so that the yield can be improved, that is, the cost can be reduced.

【００１８】コアプレート７は例えば０．８〜１．２
［ｍｍ］の厚みを有する鋼板等により形成されており、
また、摩擦材１０及び摩擦材１１は例えば０．３〜０．
５［ｍｍ］の厚みを有し、上述のようにフェノール樹脂
をしみ込ませた紙等により形成されている。コアプレー
ト７の表面上に摩擦材１０及び摩擦材１１を配置・固着
すると、摩擦材１０及び摩擦材１１の上記厚みによりコ
アプレート７の表面上に油の流路となる油溝ａ，ｂ，ｃ
がそれぞれ形成される。The core plate 7 is, for example, 0.8 to 1.2.
Formed of a steel plate having a thickness of [mm],
Further, the friction material 10 and the friction material 11 are, for example, 0.3 to 0.1.
It has a thickness of 5 [mm] and is formed of paper or the like impregnated with a phenol resin as described above. When the friction material 10 and the friction material 11 are arranged and fixed on the surface of the core plate 7, oil grooves a, b, which serve as oil flow paths on the surface of the core plate 7 due to the thickness of the friction material 10 and the friction material 11. c
Are respectively formed.

【００１９】この際、外径側列を形成する複数の摩擦材
１０を、それぞれ所定の隙間ｓ１を有するように配置・
固着し、内径側列を形成する複数の摩擦材１１を、それ
ぞれ隙間ｓ１よりも大きい所定の隙間ｓ２を有するよう
に配置・固着すると、幅が隙間ｓ１となる油溝ｃと幅が
隙間ｓ２となる油溝ａが形成される。つまり、内径側列
に形成される各油溝ａの総流路面積が、外径側列に形成
される各油溝ｃの総流路面積より大きくなる。上記多板
クラッチ２０が係合状態である際、フリクションプレー
ト１が回転して遠心力によって内周側より外周側に油が
流れると、流量の差異によって内径側列と外径側列との
間の油溝ｂに油が溜まり、油圧が発生する。このため、
クラッチ解放の際には、該油圧に基づいてフリクション
プレート１とセパレータプレート２との間に引き離す力
が生じて、つまり、クラッチの引きずりを低減すること
ができる。At this time, a plurality of friction members 10 forming the outer diameter side row are arranged and arranged so as to have a predetermined gap s1.
When a plurality of friction members 11 that are fixed and form the inner diameter side row are arranged and fixed so as to have a predetermined gap s2 larger than the gap s1, an oil groove c having a width of the gap s1 and a width of the gap s2 Is formed. That is, the total flow area of each oil groove a formed in the inner diameter side row is larger than the total flow area of each oil groove c formed in the outer diameter side row. When the friction plate 1 rotates and oil flows from the inner peripheral side to the outer peripheral side due to centrifugal force when the multi-plate clutch 20 is in the engaged state, the difference in flow rate causes a difference between the inner diameter side row and the outer diameter side row. Oil accumulates in the oil groove b, and hydraulic pressure is generated. For this reason,
When the clutch is released, a force for separating the friction plate 1 and the separator plate 2 is generated based on the hydraulic pressure, that is, dragging of the clutch can be reduced.

【００２０】上述のように多板クラッチ２０が係合状態
において油が流れる際は、図２中の矢印Ａで示すように
内周側より外周側に、油溝ａ及び油溝ｃからなる直線的
に連通する部分を流れるものと、図２中の矢印Ｂで示す
ように油溝ａの両端付近から摩擦材１０に突当る形で油
溝ａ及び油溝ｂからなる略々Ｔ字状の部分を流れるもの
とがある。該矢印Ａで示す直線的に連通する部分を油が
流れることにより、上述のような油圧及び後述する油の
運動エネルギに基づくフリクションプレート１とセパレ
ータプレート２とを引離す力をバランス良く得るもので
ありながら、フリクションプレート１に発生している摩
擦熱を冷却する効果も充分に得ることができる。As described above, when the oil flows while the multiple disc clutch 20 is in the engaged state, a straight line composed of the oil groove a and the oil groove c extends from the inner peripheral side to the outer peripheral side as shown by an arrow A in FIG. 2 and an approximately T-shaped oil groove a and an oil groove b in such a manner as to abut against the friction material 10 from near both ends of the oil groove a as shown by an arrow B in FIG. There are things that flow through the part. By flowing the oil through the linearly communicated portion indicated by the arrow A, the force for separating the friction plate 1 and the separator plate 2 based on the above-mentioned oil pressure and the kinetic energy of the oil described later is obtained in a well-balanced manner. However, the effect of cooling the frictional heat generated in the friction plate 1 can be sufficiently obtained.

【００２１】一方、矢印Ｂで示す略々Ｔ字状の部分を油
が流れることにより、上述のように油溝ｂに油が溜まっ
て油圧を発生させるものでありながら、多板クラッチ２
０を解放させる際に、Ｔ字状の突当り部分において、油
の運動エネルギが摩擦材１０に作用する。これがフリク
ションプレート１とセパレータプレート２との間に油が
入り込む力となって、つまり両プレートを引き離す力を
発生させることができる。それにより、多板クラッチ２
０の解放に際して、上述した流量の差異より生じる油圧
と相俟って、クラッチの切れを良くすることができる。
また、それに伴って、自動変速機においては、変速など
の制御をより精度の高いものにすると共に滑らかなもの
にすることができる。On the other hand, while the oil flows through the substantially T-shaped portion indicated by the arrow B, the oil accumulates in the oil groove b to generate hydraulic pressure as described above.
When releasing 0, the kinetic energy of the oil acts on the friction material 10 at the T-shaped abutting portion. This becomes a force for oil to enter between the friction plate 1 and the separator plate 2, that is, a force for separating the two plates can be generated. Thereby, the multi-plate clutch 2
At the time of release of 0, the disengagement of the clutch can be improved in combination with the hydraulic pressure generated due to the difference in the flow rates described above.
Accordingly, in the automatic transmission, the control such as the speed change can be made more precise and smooth.

【００２２】＜第２の実施の形態＞以下、本発明に係る
第２の実施の形態について図３に沿って説明する。図３
は第２の実施の形態に係るフリクションプレートを示す
一部省略正面図である。なお、第２の実施の形態におい
ては、一部変更を除き、第１の実施の形態と同様な部分
の説明を省略する。<Second Embodiment> A second embodiment according to the present invention will be described below with reference to FIG. FIG.
FIG. 7 is a partially omitted front view showing a friction plate according to a second embodiment. In the second embodiment, the description of the same parts as in the first embodiment will be omitted except for some changes.

【００２３】図２に示すように、フリクションプレート
１’は、コアプレート７の表面上に摩擦材１０’及び摩
擦材１１’が、外周側列と内周側列との少なくとも２列
以上になるように、かつそれぞれ周方向において交互に
ずれる形で配置・固着されている。なお、第１の実施の
形態と同様に、摩擦材１０’及び摩擦材１１’は、それ
ぞれ所定の同形状にセグメント化することで、歩留りを
良くすることができ、つまりコストダウンすることがで
きる。As shown in FIG. 2, in the friction plate 1 ', the friction material 10' and the friction material 11 'are arranged on the surface of the core plate 7 in at least two rows, an outer row and an inner row. As described above, they are arranged and fixed so that they are alternately shifted in the circumferential direction. Note that, similarly to the first embodiment, the friction material 10 ′ and the friction material 11 ′ are each segmented into a predetermined same shape, so that the yield can be improved, that is, the cost can be reduced. .

【００２４】第２の実施の形態においては、コアプレー
ト７の表面上に摩擦材１０’及び摩擦材１１’を周方向
において交互にずれる形で配置・固着すると、摩擦材１
０’及び摩擦材１１’の上記厚みによりコアプレート７
の表面上に油の流路となる油溝ａ’，ｂ’，ｃ’が略々
市松状に形成される。In the second embodiment, when the friction members 10 'and 11' are arranged and fixed on the surface of the core plate 7 so as to be staggered in the circumferential direction, the friction members 1 '
0 'and the thickness of the friction material 11'
Oil grooves a ', b', and c 'serving as oil flow paths are formed substantially in a checkered pattern on the surface of the.

【００２５】この際、第１の実施の形態と同様に、外径
側列を形成する複数の摩擦材１０’を、それぞれ所定の
隙間ｓ３を有するように配置・固着し、内径側列を形成
する複数の摩擦材１１’を、それぞれ隙間ｓ３よりも大
きい所定の隙間ｓ４を有するように配置・固着すると、
内径側列に形成される各油溝ａ’の総流路面積が、外径
側列に形成される各油溝ｃ’の総流路面積より大きくな
る。上記多板クラッチ２０が係合状態である際、フリク
ションプレート１’が回転して遠心力によって内周側よ
り外周側に油が流れると、流量の差異によって内径側列
と外径側列との間の油溝ｂ’に油が溜まって油圧が発生
し、多板クラッチ２０の解放に際して、該油圧に基づい
てフリクションプレート１’とセパレータプレート２と
の間に引き離す力が生じて、クラッチの引きずりを低減
することができる。At this time, similarly to the first embodiment, a plurality of friction members 10 'forming the outer diameter side row are arranged and fixed so as to have a predetermined gap s3, respectively, to form the inner diameter side row. When a plurality of friction materials 11 ′ are arranged and fixed so as to have a predetermined gap s4 larger than the gap s3,
The total flow area of each oil groove a 'formed in the inner diameter side row is larger than the total flow area of each oil groove c' formed in the outer diameter side row. When the friction plate 1 'rotates and the oil flows from the inner peripheral side to the outer peripheral side due to centrifugal force when the multi-plate clutch 20 is in the engaged state, the difference between the flow rates causes the difference between the inner diameter side row and the outer diameter side row. Oil accumulates in the oil groove b ′ between them, and a hydraulic pressure is generated. When the multi-plate clutch 20 is released, a force separating the friction plate 1 ′ and the separator plate 2 is generated based on the hydraulic pressure, and the clutch is dragged. Can be reduced.

【００２６】また、多板クラッチ２０が係合状態におい
て油が流れる際は、図３中の矢印Ｃで示すように、油溝
ａ’及び油溝ｂ’からなる略々Ｔ字状の部分に摩擦材１
０’に突当る形で油が流れる。そして、図３中の矢印Ｄ
で示すように、油溝ｂ’及び油溝ｃ’からなる略々逆Ｔ
字状の部分より外周側に油が流れる。なお、図３中の矢
印Ｄに示すように、外周側に油が流れることにより、上
述のような油圧及び後述する油の運動エネルギに基づく
フリクションプレート１’とセパレータプレート２とを
引離す力をバランス良く得るものでありながら、フリク
ションプレート１’に発生している摩擦熱を冷却する効
果も充分に得ることができる。When the oil flows while the multi-plate clutch 20 is engaged, as shown by an arrow C in FIG. 3, the oil flows into a substantially T-shaped portion composed of an oil groove a 'and an oil groove b'. Friction material 1
Oil flows in the form of hitting 0 '. Then, the arrow D in FIG.
As shown in the figure, a substantially inverted T composed of an oil groove b 'and an oil groove c'
Oil flows to the outer peripheral side from the letter-shaped portion. In addition, as shown by the arrow D in FIG. 3, the oil flows to the outer peripheral side, so that the force for separating the friction plate 1 ′ and the separator plate 2 based on the above-described oil pressure and the kinetic energy of the oil described later is generated. While obtaining a good balance, the effect of cooling the frictional heat generated in the friction plate 1 'can be sufficiently obtained.

【００２７】第２の実施の形態におけるフリクションプ
レート１’では、全ての油が略々Ｔ字状である突当り部
分に流れるので、油溝ｂ’に油が溜まって油圧を発生さ
せるものでありながら、多板クラッチ２０を解放させる
際に、Ｔ字状である突当り部分において、油の運動エネ
ルギが摩擦材１０’により大きく作用する。これがフリ
クションプレート１’とセパレータプレート２との間に
油が入り込むより大きな力となって、つまり両プレート
を引き離す力を大きく発生させることができ、上述した
流量の差異より生じる油圧と相俟って、多板クラッチ２
０の解放に際してクラッチの切れを更に良くすることが
できる。また、それに伴って、自動変速機においては、
変速などの制御をより精度の高いものにすると共に滑ら
かなものにすることができる。In the friction plate 1 'according to the second embodiment, since all the oil flows to the substantially T-shaped abutting portion, the oil accumulates in the oil groove b' to generate hydraulic pressure. When the multi-plate clutch 20 is released, the kinetic energy of the oil acts more on the friction material 10 'at the T-shaped abutting portion. This results in a greater force for oil to enter between the friction plate 1 ′ and the separator plate 2, that is, a greater force for separating the two plates, and in combination with the above-described oil pressure generated due to the difference in flow rate. , Multi-plate clutch 2
The disengagement of the clutch can be further improved when releasing 0. Accordingly, in automatic transmissions,
Controls such as shifting can be made more precise and smoother.

【００２８】＜第３の実施の形態＞以下、本発明に係る
第３の実施の形態について図４に沿って説明する。図４
は第３の実施の形態に係るフリクションプレートを示す
一部省略正面図である。なお、第３の実施の形態におい
ては、一部変更を除き、第１又は第２の実施の形態と同
様な部分の説明を省略する。<Third Embodiment> Hereinafter, a third embodiment of the present invention will be described with reference to FIG. FIG.
FIG. 9 is a partially omitted front view showing a friction plate according to a third embodiment. In the third embodiment, the description of the same parts as those in the first or second embodiment will be omitted except for some changes.

【００２９】図４に示すように、フリクションプレート
１”は、コアプレート７の表面上に摩擦材１０”及び摩
擦材１１”が、外周側列と内周側列との少なくとも２列
以上になるように、また周方向において１個所の摩擦材
１０”に対して摩擦材１１”が内周側に例えば２箇所と
なるように配置・固着されている。なお、第１及び第２
の実施の形態と同様に、摩擦材１０”及び摩擦材１１”
は、それぞれ所定の同形状にセグメント化することで、
歩留りを良くすることができ、つまりコストダウンする
ことができる。As shown in FIG. 4, in the friction plate 1 ", the friction material 10" and the friction material 11 "are formed on the surface of the core plate 7 in at least two rows of an outer row and an inner row. As described above, the friction material 11 "is arranged and fixed on the inner peripheral side with respect to one friction material 10" in the circumferential direction, for example, at two places.
As in the embodiment, the friction material 10 ″ and the friction material 11 ″
Are each segmented into the same shape.
The yield can be improved, that is, the cost can be reduced.

【００３０】第３の実施の形態においては、コアプレー
ト７の表面上に１個所の摩擦材１０”に対して摩擦材１
１”が内周側の周方向に例えば２箇所となるように配置
・固着すると、摩擦材１０”及び摩擦材１１”の上記厚
みによりコアプレート７の表面上に油の流路となる油溝
ａ”，ｂ”，ｃ”がそれぞれ形成される。In the third embodiment, one friction material 10 ″ is provided on the surface of the core plate 7.
When 1 ″ is arranged and fixed at, for example, two locations in the circumferential direction on the inner peripheral side, an oil groove serving as an oil flow path on the surface of the core plate 7 on the surface of the core plate 7 due to the thicknesses of the friction material 10 ″ and the friction material 11 ″. a ″, b ″ and c ″ are formed respectively.

【００３１】この際、外径側列を形成する複数の摩擦材
１０”を、それぞれ所定の隙間ｓ５を有するように配置
・固着し、内径側列を形成する複数の摩擦材１１”を、
それぞれ隙間ｓ５と同じ大きさの隙間ｓ６を有するよう
に配置・固着すると、内径側列に形成される各油溝ａ”
の総流路面積が、外径側列に形成される各油溝ｃ”の総
流路面積より約２倍ほど大きくなる。上記多板クラッチ
２０が係合状態である際、フリクションプレート１”が
回転して遠心力によって内周側より外周側に油が流れる
と、流量の差異によって内径側列と外径側列との間の油
溝ｂ”に油が溜まって油圧が発生し、多板クラッチ２０
の解放に際して、該油圧に基づいてフリクションプレー
ト１”とセパレータプレート２との間に引き離す力が生
じて、クラッチの引きずりを低減することができる。At this time, a plurality of friction members 10 "forming the outer diameter side row are arranged and fixed so as to have a predetermined gap s5, respectively, and a plurality of friction materials 11" forming the inner diameter side row are formed.
When arranged and fixed so as to have a gap s6 of the same size as the gap s5, each oil groove a ″ formed in the inner diameter side row
Is approximately twice as large as the total flow area of each oil groove c ″ formed in the outer diameter side row. When the multi-plate clutch 20 is in the engaged state, the friction plate 1 ″ Rotates, and oil flows from the inner peripheral side to the outer peripheral side due to centrifugal force. Due to the difference in flow rate, oil accumulates in the oil groove b ″ between the inner diameter side row and the outer diameter side row, and hydraulic pressure is generated. Plate clutch 20
When the clutch is released, a separating force is generated between the friction plate 1 ″ and the separator plate 2 based on the hydraulic pressure, so that dragging of the clutch can be reduced.

【００３２】上述のように多板クラッチ２０が係合状態
において油が流れる際は、図４中の矢印Ｅで示すように
内周側より外周側に、油溝ａ”及び油溝ｃ”からなる直
線的に連通する部分を流れるものと、図４中の矢印Ｆで
示すように油溝ａ”から摩擦材１０”に突当る形で油溝
ａ”及び油溝ｂ”からなる略々Ｔ字状の部分を流れるも
のとがある。該矢印Ｅで示す直線的に連通する部分を油
が流れることにより、上述のような油圧及び後述する油
の運動エネルギに基づくフリクションプレート１”とセ
パレータプレート２とを引離す力をバランス良く得るも
のでありながら、フリクションプレート１”に発生して
いる摩擦熱を冷却する効果も充分に得ることができる。As described above, when the oil flows in the engaged state of the multi-plate clutch 20, the oil flows from the oil groove a "and the oil groove c" from the inner peripheral side to the outer peripheral side as shown by an arrow E in FIG. And a substantially T formed by an oil groove a "and an oil groove b" which flow from the oil groove a "to the friction material 10" as shown by an arrow F in FIG. Some of them flow through the letter-shaped part. By flowing the oil through the linearly communicated portion indicated by the arrow E, a well-balanced force for separating the friction plate 1 "and the separator plate 2 based on the hydraulic pressure and the kinetic energy of the oil described below is obtained. However, the effect of cooling the frictional heat generated in the friction plate 1 "can be sufficiently obtained.

【００３３】一方、矢印Ｆで示す略々Ｔ字状の部分を油
が流れることにより、上述のように油溝ｂ”に油が溜ま
って油圧を発生させるものでありながら、多板クラッチ
２０を解放させる際に、Ｔ字状の突当り部分において、
油の運動エネルギが摩擦材１０”に作用する。これがフ
リクションプレート１”とセパレータプレート２との間
に油が入り込む力となって、つまり両プレートを引き離
す力を発生させることができる。それにより、多板クラ
ッチ２０の解放に際して、上述した流量の差異より生じ
る油圧と相俟って、クラッチの切れを良くすることがで
きる。また、それに伴って、自動変速機においては、変
速などの制御をより精度の高いものにすると共に滑らか
なものにすることができる。On the other hand, while the oil flows through the substantially T-shaped portion indicated by the arrow F, the oil accumulates in the oil groove b "to generate hydraulic pressure as described above. When releasing, at the T-shaped end,
The kinetic energy of the oil acts on the friction material 10 ". This serves as a force for oil to enter between the friction plate 1" and the separator plate 2, that is, a force for separating the two plates. Thereby, when the multi-plate clutch 20 is released, the disengagement of the clutch can be improved in combination with the hydraulic pressure generated due to the difference in the flow rates described above. Accordingly, in the automatic transmission, the control such as the speed change can be made more precise and smooth.

【００３４】なお、第３の実施の形態において、隙間ｓ
５と隙間ｓ６は同じ隙間でなく、隙間ｓ６は隙間ｓ５の
半分以上の大きさであればよく、つまり内径側列に形成
される各油溝ａ”の総流路面積が、外径側列に形成され
る各油溝ｃ”の総流路面積より大きくなればよい。ま
た、周方向において１個所の摩擦材１０”に対して摩擦
材１１”が内周側に例えば２箇所となるように配置・固
着されているが、該摩擦材１０”に対する摩擦材１１”
は、３箇所、又はそれ以上でもよく、Ｔ字状の突当り部
分において、フリクションプレート１”とセパレータプ
レート２とを引き離す力を発生させることができるもの
であればよい。In the third embodiment, the gap s
5 and the gap s6 are not the same gap, and the gap s6 may be at least half the size of the gap s5. That is, the total flow area of each oil groove a ″ formed in the inner diameter side row is equal to the outer diameter side row. It is only necessary that the area be larger than the total flow passage area of each oil groove c ″ formed in the above. In addition, the friction material 11 "is arranged and fixed to one friction material 10" in the circumferential direction on the inner peripheral side, for example, at two places.
May be provided at three or more positions, as long as a force capable of separating the friction plate 1 ″ from the separator plate 2 can be generated at the T-shaped abutting portion.

【００３５】なお、以上の第１、第２及び第３の実施の
形態において、摩擦材は内径側と外径側との２列となる
ように配置・固着されているが、３列以上であってもよ
く、外径側より内径側が順次総流路面積の大きくなるよ
うなものであれば何列でもよい。また、本発明の実施の
形態として多板クラッチについて説明したが、多板ブレ
ーキ、単板クラッチ、単板ブレーキなどに本発明を適用
してもよく、これに限らず、摩擦板を用いるものであれ
ば何れのものに本発明を適用してもよい。更に、コアプ
レートの両面側に摩擦材を配置・固着しているが、片面
側のみに摩擦材を配置・固着したものであってもよい。In the above first, second and third embodiments, the friction materials are arranged and fixed in two rows of the inner diameter side and the outer diameter side. Any number of rows may be used as long as the total flow path area increases sequentially from the outer diameter side to the inner diameter side. Further, although the multi-plate clutch has been described as an embodiment of the present invention, the present invention may be applied to a multi-disc brake, a single-disc clutch, a single-disc brake, and the like. If so, the present invention may be applied to any of them. Further, the friction material is arranged and fixed on both sides of the core plate, but the friction material may be arranged and fixed only on one side.

【図面の簡単な説明】[Brief description of the drawings]

【図１】多板クラッチ（又はブレーキ）を示す断面図。FIG. 1 is a sectional view showing a multi-plate clutch (or brake).

【図２】第１の実施の形態に係るフリクションプレート
を示す一部省略正面図。FIG. 2 is a partially omitted front view showing the friction plate according to the first embodiment.

【図３】第２の実施の形態に係るフリクションプレート
を示す一部省略正面図。FIG. 3 is a partially omitted front view showing a friction plate according to a second embodiment.

【図４】第３の実施の形態に係るフリクションプレート
を示す一部省略正面図。FIG. 4 is a partially omitted front view showing a friction plate according to a third embodiment.

【符号の説明】[Explanation of symbols]

１ 摩擦板（フリクションプレート） ７ コアプレート １０ 摩擦材 １１ 摩擦材 ｓ１〜ｓ６ 隙間 ａ 油溝 ｂ 油溝 ｃ 油溝 Reference Signs List 1 friction plate (friction plate) 7 core plate 10 friction material 11 friction material s1 to s6 gap a oil groove b oil groove c oil groove

───────────────────────────────────────────────────── フロントページの続き Ｆターム(参考） 3J056 AA60 AA62 BA02 BB12 BE13 BE23 CA04 CA07 CA09 CA18 GA05 GA12 3J057 AA03 AA04 AA06 BB04 DB01 DB03 EE05 GA80  ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3J056 AA60 AA62 BA02 BB12 BE13 BE23 CA04 CA07 CA09 CA18 GA05 GA12 3J057 AA03 AA04 AA06 BB04 DB01 DB03 EE05 GA80

Claims (4)

【特許請求の範囲】[Claims] 【請求項１】 円板状のコアプレートと、所定形状から
なるセグメント状の複数の摩擦材と、を備え、前記コア
プレートの表面上に前記各摩擦材を固着し、前記各摩擦
材間の隙間によって油溝を形成してなる摩擦板におい
て、 前記摩擦材は、前記コアプレート上に内径側列と外径側
列との少なくとも２列に、かつこれら内径側列と外径側
列との間に前記油溝を有するように、また前記内径側列
に形成される前記油溝の総流路面積が、前記外径側列に
形成される前記油溝の総流路面積より大きくなるように
配置・固着される、 ことを特徴とする摩擦板。1. A disk-shaped core plate, and a plurality of segment-shaped friction materials having a predetermined shape, wherein each of the friction materials is fixed on a surface of the core plate, and the friction material is provided between the friction materials. In a friction plate in which an oil groove is formed by a gap, the friction material is formed on the core plate in at least two rows of an inner diameter side row and an outer diameter side row, and the inner diameter side row and the outer diameter side row With the oil grooves between them, the total flow area of the oil grooves formed in the inner diameter side row is larger than the total flow area of the oil grooves formed in the outer diameter side row. The friction plate is arranged and fixed on the friction plate. 【請求項２】 前記油溝は、前記外径側列及び前記内径
側列に配置・固着される前記摩擦材の位置により、前記
コアプレートの半径方向に突当る略々Ｔ字状の部分を有
してなる、 請求項１記載の摩擦板。2. The oil groove has a substantially T-shaped portion that abuts in a radial direction of the core plate depending on a position of the friction material arranged and fixed in the outer diameter side row and the inner diameter side row. The friction plate according to claim 1, comprising: 【請求項３】 前記油溝は、前記外径側列及び前記内径
側列に配置される前記摩擦材の位置により、前記外径側
列における各摩擦材の間の油溝と前記内径側列における
各摩擦材の間の油溝が前記コアプレートの半径方向に直
線的に連通する部分を有してなる、 請求項１又は２記載の摩擦板。3. The oil groove between the friction material in the outer diameter side row and the inner diameter side row according to a position of the friction material arranged in the outer diameter side row and the inner diameter side row. 3. The friction plate according to claim 1, wherein the oil groove between the friction members has a portion that linearly communicates in a radial direction of the core plate. 4. 【請求項４】 車輌用自動変速機の摩擦係合装置におけ
る摩擦係合要素として適用されてなる、 請求項１ないし３のいずれか記載の摩擦板。4. The friction plate according to claim 1, wherein the friction plate is applied as a friction engagement element in a friction engagement device of an automatic transmission for a vehicle.
JP2001037011A 2001-02-14 2001-02-14 Frictional disk Pending JP2002242954A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2001037011A JP2002242954A (en) 2001-02-14 2001-02-14 Frictional disk

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2001037011A JP2002242954A (en) 2001-02-14 2001-02-14 Frictional disk

Publications (1)

Publication Number Publication Date
JP2002242954A true JP2002242954A (en) 2002-08-28

Family

ID=18900198

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2001037011A Pending JP2002242954A (en) 2001-02-14 2001-02-14 Frictional disk

Country Status (1)

Country Link
JP (1) JP2002242954A (en)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004150449A (en) * 2002-10-28 2004-05-27 Aisin Chem Co Ltd Segment type friction material
JP2006132581A (en) * 2004-11-02 2006-05-25 Aisin Chem Co Ltd Segment type friction material
JP2006342819A (en) * 2005-06-07 2006-12-21 Mazda Motor Corp Clutch structure of transmission
JP2007146900A (en) * 2005-11-24 2007-06-14 Nsk Warner Kk Wet multiple disc friction clutch device
JP2007155096A (en) * 2005-12-08 2007-06-21 Nsk Warner Kk Wet type multiple disc clutch
JP2009138901A (en) * 2007-12-10 2009-06-25 Aisin Chem Co Ltd Torque transmitting mechanism for automatic transmission
EP2194289A1 (en) * 2007-09-25 2010-06-09 Kito Corporation Wet friction plate
JP2010520429A (en) * 2007-03-06 2010-06-10 ツェットエフ、フリードリッヒスハーフェン、アクチエンゲゼルシャフト Clutch body and synchronization ring for synchronizer
WO2011111117A1 (en) * 2010-03-12 2011-09-15 トヨタ自動車株式会社 Lock-up clutch
JP2012047278A (en) * 2010-08-27 2012-03-08 Aisin Aw Industries Co Ltd Wet friction plate
CN107542806A (en) * 2016-06-23 2018-01-05 通用汽车环球科技运作有限责任公司 Clutch plate with discontinuous friction material pattern

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004150449A (en) * 2002-10-28 2004-05-27 Aisin Chem Co Ltd Segment type friction material
JP2006132581A (en) * 2004-11-02 2006-05-25 Aisin Chem Co Ltd Segment type friction material
US8727092B2 (en) 2004-11-02 2014-05-20 Aisin Kako Kabushiki Kaisha Segment-type friction material
JP4715317B2 (en) * 2005-06-07 2011-07-06 マツダ株式会社 Transmission clutch structure
JP2006342819A (en) * 2005-06-07 2006-12-21 Mazda Motor Corp Clutch structure of transmission
JP2007146900A (en) * 2005-11-24 2007-06-14 Nsk Warner Kk Wet multiple disc friction clutch device
JP2007155096A (en) * 2005-12-08 2007-06-21 Nsk Warner Kk Wet type multiple disc clutch
JP2010520429A (en) * 2007-03-06 2010-06-10 ツェットエフ、フリードリッヒスハーフェン、アクチエンゲゼルシャフト Clutch body and synchronization ring for synchronizer
EP2194289A1 (en) * 2007-09-25 2010-06-09 Kito Corporation Wet friction plate
EP2194289A4 (en) * 2007-09-25 2012-03-21 Kito Kk Wet friction plate
JP2009138901A (en) * 2007-12-10 2009-06-25 Aisin Chem Co Ltd Torque transmitting mechanism for automatic transmission
WO2011111117A1 (en) * 2010-03-12 2011-09-15 トヨタ自動車株式会社 Lock-up clutch
CN102812268A (en) * 2010-03-12 2012-12-05 丰田自动车株式会社 Lock-up Clutch
JP5333651B2 (en) * 2010-03-12 2013-11-06 トヨタ自動車株式会社 Lock-up clutch
US8657088B2 (en) 2010-03-12 2014-02-25 Toyota Jidosha Kabushiki Kaisha Lock-up clutch
JP2012047278A (en) * 2010-08-27 2012-03-08 Aisin Aw Industries Co Ltd Wet friction plate
CN107542806A (en) * 2016-06-23 2018-01-05 通用汽车环球科技运作有限责任公司 Clutch plate with discontinuous friction material pattern

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