JP2528572Y2 - Wet multi-plate friction engagement device - Google Patents
Wet multi-plate friction engagement deviceInfo
- Publication number
- JP2528572Y2 JP2528572Y2 JP12627490U JP12627490U JP2528572Y2 JP 2528572 Y2 JP2528572 Y2 JP 2528572Y2 JP 12627490 U JP12627490 U JP 12627490U JP 12627490 U JP12627490 U JP 12627490U JP 2528572 Y2 JP2528572 Y2 JP 2528572Y2
- Authority
- JP
- Japan
- Prior art keywords
- plate
- friction
- wet
- engagement device
- wet multi
- 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
Description
【考案の詳細な説明】 産業上の利用分野 この考案は湿式多板クラッチや湿式多板ブレーキなど
の湿式多板摩擦係合装置に関し、4輪駆動車のトランス
ファーの摩擦クラッチなど連続滑り状態で使用される装
置にも利用できるものである。DETAILED DESCRIPTION OF THE INVENTION INDUSTRIAL APPLICATION This invention relates to a wet multi-plate friction engagement device such as a wet multi-plate clutch and a wet multi-plate brake, and is used in a continuous sliding state such as a friction clutch for a transfer of a four-wheel drive vehicle. It can also be used for devices that are used.
従来の技術と解決すべき課題 湿式多板摩擦係合装置としては、例えば第1図に示す
ような装置がある。2. Description of the Related Art As a wet multi-plate friction engagement device, there is, for example, a device as shown in FIG.
図において、6はインプットシャフト、5はクラッチ
ギヤであって、駆動側部材を構成し、51はクラッチギヤ
に形成されたスプライン部、7は押圧用ピストンを示
す。In the figure, reference numeral 6 denotes an input shaft, 5 denotes a clutch gear, which constitutes a drive side member, 51 denotes a spline portion formed in the clutch gear, and 7 denotes a pressing piston.
又4は受動側部材としてのクラッチドラムであって、
41はそのスプライン部である。4 is a clutch drum as a passive member,
41 is the spline part.
1はスプライン部41に嵌合された受動板、2はスプラ
イン部51に嵌合された駆動板、3はプレッシャプレート
である。従来の装置では第3図(b)に示すように駆動
板2は鋼板9′の両側に湿式摩擦材8が張られており、
受動板1は鋼板9からのみ構成されている。1 is a passive plate fitted to the spline portion 41, 2 is a drive plate fitted to the spline portion 51, and 3 is a pressure plate. In the conventional device, as shown in FIG. 3 (b), the drive plate 2 has a wet friction material 8 stretched on both sides of a steel plate 9 '.
The passive plate 1 is constituted only by the steel plate 9.
ところで、現在クラッチ板に求められている特性は非
常にきびしいものであって、(1)耐熱、耐久性(2)
高容量(3)低フリクション(引きずりトルクが小)
(4)作動ショックの低減の各条件を成立させなければ
ならない。By the way, the characteristics required of the clutch plate at present are very severe, and (1) heat resistance and durability (2)
High capacity (3) Low friction (small drag torque)
(4) Each condition for reducing the operation shock must be satisfied.
そこで受動板1の熱の流れを示す第3図(a)及び側
面図で示す第3図(b)について説明すると、受動板1
はクラッチドラム4のスプライン部41と係合しており、
装置が締結状態の時湿式摩擦材8と受動板1との摩擦熱
はスプライン歯91の端部eから矢印αで示す如くクラッ
チドラム内側のスプライン部41の端面fに伝導される。
又ピストン7側(第1図)及びプレッシャープレート3
側の受動板1は熱容量が大きいため表面温度は低いが、
中央部程摩擦熱が蓄積されるため表面温度が高くなる。
ここで湿式摩擦材8及び湿式摩擦材8と鋼板9′間の接
着剤は熱伝達率が小さいため、駆動板2の鋼板9′は熱
伝導にほとんど寄与しない。従って湿式摩擦材8の一面
当りの受動板1の熱容量をいかに大きく設定できるかが
表面温度を下げる手法となり耐熱、耐久性向上のポイン
トとなる。3 (a) showing the flow of heat in the passive plate 1 and FIG. 3 (b) shown in a side view.
Is engaged with the spline portion 41 of the clutch drum 4,
When the apparatus is in the engaged state, the frictional heat between the wet friction material 8 and the passive plate 1 is transmitted from the end e of the spline teeth 91 to the end face f of the spline 41 inside the clutch drum as shown by the arrow α.
The piston 7 side (FIG. 1) and the pressure plate 3
Although the passive plate 1 on the side has a large heat capacity and a low surface temperature,
As the frictional heat is accumulated in the center, the surface temperature increases.
Here, since the wet friction material 8 and the adhesive between the wet friction material 8 and the steel plate 9 'have a small heat transfer coefficient, the steel plate 9' of the drive plate 2 hardly contributes to heat conduction. Therefore, how large the heat capacity of the passive plate 1 per one surface of the wet friction material 8 can be set is a method of lowering the surface temperature, which is a point of improving heat resistance and durability.
このように従来の湿式多板摩擦係合装置にあっては受
動板1の表面温度は熱伝導の問題から位置によって大き
く異なり、湿式摩擦材8の部分的な焼損、及び受動板1
にヒートスポット(熱による部分的な変態)が発生し、
湿式摩擦材8の異常摩耗、ハクリの発生原因となり耐久
性を悪化させるという欠点を免れなかった。As described above, in the conventional wet-type multi-plate friction engagement device, the surface temperature of the passive plate 1 greatly differs depending on the position due to the problem of heat conduction, and the partial burnout of the wet friction material 8 and the passive plate 1
Heat spot (partial transformation by heat) occurs in
Abnormal wear of the wet friction material 8 and the occurrence of peeling caused the deterioration of durability, which was inevitable.
課題を解決するための手段 この考案は前記のような問題点を解決するために、受
動板と駆動板は鋼板のみで構成し、受動板と駆動板の間
にスプラインに嵌合されていない独立の摩擦板が存在す
るように構成したものである。Means for Solving the Problems In order to solve the above-mentioned problems, the present invention has a configuration in which the passive plate and the driving plate are formed of only steel plates, and independent friction is not fitted to the spline between the passive plate and the driving plate. It is configured so that a plate exists.
作用 第2図にこの考案の多板摩擦係合装置の説明図を示
し、受動板1は鋼板9からなり外周にスプライン歯91を
有している。駆動板2も鋼板9′からなり、内周にスプ
ライン歯91′を有している。そして受動板1と駆動板2
との間にスプラインと嵌合しない独立の摩擦板10が存在
する。第3図(c)は受動板1の熱の流れの説明図、
(d)は駆動板2の熱の流れの説明図、(e)は側面図
であって、駆動板2の鋼板9′と摩擦板10とが分離、独
立していることにより鋼板9′も摩擦熱の伝導径路とし
て利用することができる。第3図(c)は摩擦熱が矢印
βで示す如く受動板1のスプライン歯91からクラッチド
ラム4のスプライン部4に流れるところを示している。
又、(d),(e)は摩擦熱が摩擦板10から駆動板2へ
も流れ、やはり矢印βで示すように、駆動板2のスプラ
イン歯91′の端面e′からクラッチギヤ5のスプライン
部51の端面f′の方に流れるところを示している。FIG. 2 is an explanatory view of the multi-plate friction engagement device of the present invention. The passive plate 1 is made of a steel plate 9 and has spline teeth 91 on the outer periphery. The drive plate 2 is also made of a steel plate 9 'and has spline teeth 91' on the inner periphery. And passive plate 1 and drive plate 2
There is an independent friction plate 10 that does not fit with the spline. FIG. 3 (c) is an explanatory diagram of the heat flow of the passive plate 1,
(D) is an explanatory view of the heat flow of the drive plate 2, and (e) is a side view, in which the steel plate 9 ′ and the friction plate 10 of the drive plate 2 are separated and independent so that the steel plate 9 ′ It can be used as a conduction path for frictional heat. FIG. 3 (c) shows that frictional heat flows from the spline teeth 91 of the passive plate 1 to the spline portion 4 of the clutch drum 4 as indicated by the arrow β.
(D) and (e) show that frictional heat also flows from the friction plate 10 to the drive plate 2 and, as also indicated by the arrow β, the spline of the clutch gear 5 starts from the end face e ′ of the spline teeth 91 ′ of the drive plate 2. The flow toward the end face f 'of the portion 51 is shown.
第4図は締結時の温度上昇の状態を示す説明図で
(a)は従来の装置の断面図、(b)はその温度上昇の
状態を示し、摩擦板8ならびに摩擦板8と駆動板2の鋼
板9′との接着剤は熱伝達率が小さいため、受動板1と
摩擦板8の間の摩擦熱は駆動板2の鋼板9′には逃げな
いため受動板1側の温度上昇は駆動板2に比して大きく
なり、温度分布は均等にならない。(c)はこの考案の
側断面を示し、前記の如く摩擦熱は受動板1にも駆動板
2にも流れるので、温度分布は均一に近くなることを
(d)で模式的に示している。4A and 4B are explanatory views showing the state of temperature rise at the time of fastening. FIG. 4A is a cross-sectional view of a conventional device, and FIG. 4B shows the state of temperature rise. Since the adhesive with the steel plate 9 ′ has a small heat transfer coefficient, the frictional heat between the passive plate 1 and the friction plate 8 does not escape to the steel plate 9 ′ of the drive plate 2, so that the temperature rise on the side of the passive plate 1 is driven. It becomes larger than the plate 2 and the temperature distribution is not uniform. (C) shows a side cross section of the present invention, and (d) schematically shows that the temperature distribution becomes nearly uniform because the frictional heat flows to both the passive plate 1 and the driving plate 2 as described above. .
実施例 第5図ないし第16図は摩擦板10の各種の実施例を示
し、各図とも(a)は側断面図、(b)は(a)のX−
X断面図を示す。Embodiments FIGS. 5 to 16 show various embodiments of the friction plate 10, in which (a) is a side sectional view and (b) is an X-
The X sectional view is shown.
第5図に示す例では摩擦板10は湿式摩擦材8の間にコ
アプレート11があり、摩擦板10の剛性を高めている。In the example shown in FIG. 5, the friction plate 10 has a core plate 11 between the wet friction materials 8 to increase the rigidity of the friction plate 10.
第6図の例ではコアプレート11は湿式摩擦材8より突き
出していて摩擦材保護を高めている。又コアプレート11
に切欠き12を設けて積極的に摩擦材8に潤滑油の供給を
させるもので、切欠き12の形状は任意でよい。In the example of FIG. 6, the core plate 11 protrudes from the wet friction material 8 to enhance protection of the friction material. Also core plate 11
A notch 12 is provided to positively supply the friction material 8 with lubricating oil, and the shape of the notch 12 may be arbitrary.
第7図に示す例ではコアプレート11に貫通孔15があけ
られており、湿式摩擦材8の内部の潤滑油の流れや保持
性を良くしている。この孔15内には、第7図のように摩
擦材8が存在していてもよく、又空間にしてもよい。In the example shown in FIG. 7, a through hole 15 is formed in the core plate 11 to improve the flow and retention of the lubricating oil inside the wet friction material 8. In this hole 15, the friction material 8 may exist as shown in FIG.
第8図に示す例では湿式摩擦材8の内、外周に環状の
保護部分13が設けられ、摩擦板10の剛性を高め又スプラ
イン部からの保護性を高めている。尚この保護部分13は
摩擦材8とは別の硬質材の場合もあり、又摩擦材8の密
度を部分的に高めて硬くする場合もある。In the example shown in FIG. 8, an annular protective portion 13 is provided on the outer periphery of the wet friction material 8 to increase the rigidity of the friction plate 10 and the protection from the spline portion. The protective portion 13 may be a hard material different from the friction material 8, or may be partially increased in the density of the friction material 8 so as to be hard.
第9図は第8図の変形であって、保護部分13が部分的
に設定されている。FIG. 9 is a modification of FIG. 8, in which the protection portion 13 is partially set.
第10図と第11図は、湿式摩擦材からなる摩擦板10が平
板でなく、夫々逆台形型とか、中ふくらみ型などをして
いて、引きずりトルクの低減を目的としている。FIGS. 10 and 11 show that the friction plate 10 made of a wet friction material is not a flat plate but has an inverted trapezoidal shape or a middle bulge type, respectively, for the purpose of reducing drag torque.
第12図の例では、摩擦板10の内、外周を特性が異なる
別々の湿式摩擦材8,8′で構成してある。例えば外周側
を摩擦係数の低い湿式摩擦材、内周側を耐面圧強度の高
い湿式摩擦材とすることなどで、バランスのとれた特性
の摩擦板となる。In the example shown in FIG. 12, the outer periphery of the friction plate 10 is constituted by separate wet friction materials 8, 8 'having different characteristics. For example, a friction plate having balanced characteristics can be obtained by using a wet friction material having a low friction coefficient on the outer peripheral side and a wet friction material having a high surface pressure resistance on the inner peripheral side.
第13図に示された例ではコアプレートに当る部分を特
性の異なる湿式摩擦材8′とすることで疲労寿命、耐久
性を向上することができる。例えばコア部に潤滑油透過
率の高い摩擦材8′とすることで両面の摩擦材に内部か
ら潤滑油を供給でき、耐熱、耐久性が向上する。In the example shown in FIG. 13, the fatigue life and durability can be improved by making the portion corresponding to the core plate a wet friction material 8 'having different characteristics. For example, by using a friction material 8 'having a high lubricating oil permeability in the core portion, lubricating oil can be supplied from both inside to the friction material on both surfaces, and heat resistance and durability are improved.
第14図の例では、摩擦材8の表面に油溝14をつけ耐
熱、耐久性を高めている。図では溝に平行に設けられて
いるが。In the example of FIG. 14, an oil groove 14 is provided on the surface of the friction material 8 to improve heat resistance and durability. In the figure, it is provided parallel to the groove.
第15図に示されたものは、第14図に示されたものに内
部貫通孔15もしくは溝が設けられているもので、耐熱、
耐久性を一層高めているものである。The one shown in FIG. 15 is the one shown in FIG. 14 in which the internal through hole 15 or the groove is provided,
The durability is further enhanced.
第16図に示されたものは、孔16が第14図の場合のよう
に貫通しておらず、非貫通孔もしくは溝となっている例
である。FIG. 16 shows an example in which the hole 16 does not penetrate as in the case of FIG. 14, but is a non-through hole or groove.
効果 この考案は前記の如き構成であって、摩擦板をスプラ
インと嵌合させずに、受動板及び駆動板と独立させて設
けてあるので、摩擦熱は受動板と駆動板の両方に流れて
温度上昇を均一化させ、湿式摩擦剤の耐熱、耐久性の向
上とを両立させることができた。Effect The present invention is configured as described above, and the friction plate is provided independently of the passive plate and the driving plate without fitting the friction plate to the spline, so that frictional heat flows to both the passive plate and the driving plate. The temperature rise was made uniform and both the heat resistance and the durability of the wet friction agent were improved.
さらに摩擦板が受動板、駆動板から独立しているの
で、従来の装置より引きずりトルクが発生しにくく、低
フリクション効果をも得ることができた。Furthermore, since the friction plate is independent of the passive plate and the drive plate, drag torque is less likely to be generated than in the conventional device, and a low friction effect can be obtained.
第1図は湿式多板摩擦係合装置の構成の説明図、第2図
はこの考案の多板摩擦装置の構成の説明図、第3図
(a)は受動板における熱の流れの説明図、第3図
(b)は従来の装置の側断面による説明図、第3図
(c)(d)はこの考案の装置の熱の流れの説明図、第
3図(e)はこの考案の装置の側断面による説明図、第
4図(a)〜(d)は従来装置とこの考案の装置との温
度上昇の比較図、第5図〜第16図は摩擦板の構成の種々
の実施例を示す図であって、各図とも(a)は側断面
図、(b)は(a)のX−X方向断面図を示している。 符号の説明 1……受動板、2……駆動板 3……プレッシャープレート 4……クラッチドラム、41……スプライン部 5……クラッチギヤ、51……スプライン部 6……インプットシャフト 7……ピストン、8,8′……湿式摩擦材 9,9′……鋼板、91,91′……スプライン歯 10……独立摩擦板FIG. 1 is an explanatory view of a configuration of a wet multi-plate friction engagement device, FIG. 2 is an explanatory view of a configuration of a multi-plate friction device of the present invention, and FIG. 3 (a) is an explanatory view of heat flow in a passive plate. FIG. 3 (b) is an explanatory view of a conventional apparatus in a side sectional view, FIGS. 3 (c) and 3 (d) are explanatory views of heat flow of the apparatus of the present invention, and FIG. 4 (a) to 4 (d) are comparison diagrams of temperature rise between the conventional device and the device of the present invention, and FIGS. 5 to 16 are various embodiments of the structure of the friction plate. It is a figure which shows an example, (a) is a side sectional view and (b) has shown the XX direction sectional view of (a) in each figure. DESCRIPTION OF SYMBOLS 1... Passive plate 2... Drive plate 3... Pressure plate 4... Clutch drum 41... Spline 5... Clutch gear 51 51 Spline 6. Input shaft 7. , 8,8 '... wet friction material 9,9' ... steel plate, 91,91 '... spline teeth 10 ... independent friction plate
Claims (8)
係合されている駆動板と受動板は鋼板のみによって形成
されており、駆動板と受動板の間に、スプラインに嵌合
されていない独立した摩擦板が存在することを特徴とす
る湿式多板摩擦係合装置。The drive plate and the passive plate, which are spline-engaged with the drive side member and the passive side member, respectively, are formed only of steel plates, and are provided between the drive plate and the passive plate independently of the splines. A wet multi-plate friction engagement device, wherein a friction plate is present.
両面に湿式摩擦材を接着した構成であることを特徴とす
る前記請求項(1)項記載の湿式多板摩擦係合装置。2. The wet multi-plate friction engagement device according to claim 1, wherein said friction plate has a structure in which a wet friction material is bonded to both surfaces of a thin steel plate or resin.
とを特徴とする前記請求項(1)項記載の湿式多板摩擦
係合装置。3. The wet multi-plate friction engagement device according to claim 1, wherein said friction plate comprises only a wet friction material.
部を、環状、もしくは部分的に、金属、樹脂、又は高密
度加工部分等によって保護されていることを特徴とする
前記請求項(1)項記載の湿式多板摩擦係合装置。4. The friction plate according to claim 1, wherein an inner periphery and an outer periphery of the wet friction material are annularly or partially protected by a metal, a resin, a high-density processing part, or the like. The wet multi-plate friction engagement device according to claim 1.
を特徴とする前記請求項(1)項記載の湿式多板摩擦係
合装置。5. The wet multi-plate friction engagement device according to claim 1, wherein said friction plate has a non-flat cross section.
湿式摩擦材から構成されていることを特徴とする前記請
求項(1)項記載の湿式多板摩擦係合装置。6. The wet multi-plate friction engagement device according to claim 1, wherein said friction plate is made of two or more types of wet friction materials having different characteristics.
に、内部に潤滑用の孔が存在することを特徴とする前記
請求項(1)項記載の湿式多板摩擦係合装置。7. The wet multi-plate frictional engagement device according to claim 1, wherein said friction plate has an oil groove on a surface and a lubrication hole inside.
鋼板に湿式摩擦材潤滑用の孔もしくは切欠きが存在する
ことを特徴とする湿式多板摩擦係合装置。8. A wet multi-plate friction engagement device according to claim 2, wherein a thin steel plate inside the friction plate has a hole or notch for lubricating a wet friction material.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP12627490U JP2528572Y2 (en) | 1990-11-30 | 1990-11-30 | Wet multi-plate friction engagement device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP12627490U JP2528572Y2 (en) | 1990-11-30 | 1990-11-30 | Wet multi-plate friction engagement device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0484832U JPH0484832U (en) | 1992-07-23 |
JP2528572Y2 true JP2528572Y2 (en) | 1997-03-12 |
Family
ID=31873835
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JP12627490U Expired - Lifetime JP2528572Y2 (en) | 1990-11-30 | 1990-11-30 | Wet multi-plate friction engagement device |
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DE102015202345B4 (en) | 2014-02-13 | 2022-06-23 | Ford Global Technologies, Llc | WET FRICTION CLUTCH |
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US6484853B1 (en) * | 2001-08-15 | 2002-11-26 | Raytech Composites, Inc. | Single sided friction assembly compensating for thermal distortions |
JP4813037B2 (en) * | 2004-10-06 | 2011-11-09 | Nskワーナー株式会社 | Wet multi-plate clutch friction plate |
KR101941731B1 (en) | 2011-11-08 | 2019-01-23 | 혼마 가가쿠 가부시키가이샤 | Multiple free disc-type clutch |
AT516209A1 (en) | 2014-08-22 | 2016-03-15 | Miba Frictec Gmbh | friction unit |
AT516208A1 (en) | 2014-08-22 | 2016-03-15 | Miba Frictec Gmbh | friction unit |
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-
1990
- 1990-11-30 JP JP12627490U patent/JP2528572Y2/en not_active Expired - Lifetime
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015202345B4 (en) | 2014-02-13 | 2022-06-23 | Ford Global Technologies, Llc | WET FRICTION CLUTCH |
KR101912503B1 (en) | 2016-09-27 | 2019-01-14 | 이티알 주식회사 | Clutch assembly |
Also Published As
Publication number | Publication date |
---|---|
JPH0484832U (en) | 1992-07-23 |
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