JPS6137902Y2 - - Google Patents
Info
- Publication number
- JPS6137902Y2 JPS6137902Y2 JP15368083U JP15368083U JPS6137902Y2 JP S6137902 Y2 JPS6137902 Y2 JP S6137902Y2 JP 15368083 U JP15368083 U JP 15368083U JP 15368083 U JP15368083 U JP 15368083U JP S6137902 Y2 JPS6137902 Y2 JP S6137902Y2
- Authority
- JP
- Japan
- Prior art keywords
- clutch
- lock
- facing
- converter
- hydraulic oil
- 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
Links
- 239000010720 hydraulic oil Substances 0.000 description 15
- 239000002245 particle Substances 0.000 description 9
- 238000005461 lubrication Methods 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- 239000003921 oil Substances 0.000 description 3
- 238000010000 carbonizing Methods 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
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
- 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
- Mechanical Operated Clutches (AREA)
Description
【考案の詳細な説明】
本考案はトルクコンバータ、特にロツクアツプ
トルクコンバータに内蔵されるロツクアツプクラ
ツチのフエーシングに関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a facing for a lock-up clutch incorporated in a torque converter, particularly a lock-up torque converter.
ロツクアツプトルクコンバータは一般に第１図
の如く、ポンプインペラ（入力要素）１とタービ
ンランナ（出力要素）２と、ステータ（反力要
素）３と、ロツクアツプクラツチ４とを主たる構
成要素とする。ポンプインペラ１はコンバータカ
バー５を介してエンジンクランク６によりエンジ
ン駆動されてコンバータ室７内の作動油をかき廻
し、この作動油がタービンランナ２に衝突後ステ
ータ３を経てポンプインペラ１に戻る間、ステー
タ３による反力下でタービンランナ２をトルク増
大しつつ回転する。このようにしてタービンラン
ナ２に達したエンジン動力はこれに鋲着したター
ビンハブ８を経てこれにスプライン結合した出力
軸９より取出すことができる。 As shown in FIG. 1, a lock-up torque converter generally has a pump impeller (input element) 1, a turbine runner (output element) 2, a stator (reaction force element) 3, and a lock-up clutch 4 as its main components. The pump impeller 1 is driven by the engine crank 6 through the converter cover 5 to stir up hydraulic oil in the converter chamber 7, and while this hydraulic oil collides with the turbine runner 2 and returns to the pump impeller 1 via the stator 3, The turbine runner 2 rotates under the reaction force of the stator 3 while increasing the torque. The engine power that has reached the turbine runner 2 in this manner can be extracted from the output shaft 9 splined to the turbine hub 8 via the turbine hub 8 riveted thereto.
以上は、ロツクアツプクラツチ４がそのクラツ
チフエーシング１０をコンバータカバー５に押付
けられない釈放状態にある時のコンバータ状態で
の動作態様であるが、ロツクアツプ制御室１１内
の圧力を排除する時トルクコンバータは以下の如
くロツクアツプ状態で動作する。即ち、この時ロ
ツクアツプクラツチ４はコンバータ室７内の圧力
によりクラツチフエーシング１０をコンバータカ
バー５に押付けられてコンバータカバー５、従つ
てポンプインペラ１に駆動係合される。一方、ロ
ツクアツプクラツチ４はトーシヨナルダンパ１２
を介しタービンランナ２に駆動結合されており、
ロツクアツプクラツチ４はこの時ポンプインペラ
１及びタービンランナ２間を連結し、エンジン動
力をトルクコンバータのスリツプ（入出力要素
１，２間の相対回転）なしに出力軸９へ伝達す
る。 The above is the operation mode in the converter state when the lockup clutch 4 is in the released state where its clutch facing 10 is not pressed against the converter cover 5. operates in the lockup state as follows. That is, at this time, the lock-up clutch 4 is pressed against the converter cover 5 by the clutch facing 10 due to the pressure in the converter chamber 7, and is driven into engagement with the converter cover 5 and, therefore, with the pump impeller 1. On the other hand, lockup clutch 4 is torsional damper 12.
is drivingly coupled to the turbine runner 2 via
The lock-up clutch 4 then connects the pump impeller 1 and the turbine runner 2 and transmits the engine power to the output shaft 9 without torque converter slip (relative rotation between the input and output elements 1 and 2).
更に、ロツクアツプ制御室１１内の圧力を最大
値及び最小値間の中間値に制御してロツクアツプ
クラツチ４をコンバータカバー５にすべり結合す
る時、エンジン動力はコンバータ状態とロツクア
ツプ状態との間の中間的なスリツプ制御状態で出
力軸９に伝達される。 Further, when the pressure in the lockup control chamber 11 is controlled to an intermediate value between the maximum value and the minimum value and the lockup clutch 4 is slidably coupled to the converter cover 5, the engine power is maintained at an intermediate value between the converter state and the lockup state. It is transmitted to the output shaft 9 in a typical slip control state.
ところでクラツチフエーシング１０は従来、第
２図に示す如く内外周縁１０ａ，１０ｂが滑らか
な同心円を持つような円環状に構成され、ロツク
アツプクラツチ５の結合時、特にすべり結合時、
以下の理由から潤滑不良を起こす懸念があつた。
つまり、今クラツチフエーシング１０がコンバー
タカバー５に対し矢印α方向に相対回転している
とすると、作動油の粒子P1，P2，P3は夫々クラツ
チフエーシング１０に対し相対的に矢印β，γ，
δの方向へ回転していることになる。この時コン
バータカバー５に摺接しているクラツチフエーシ
ング１０の面１０ｃ上の作動油粒子P2は常時面１
０ｃ上にとどまり、摩擦熱を断続的に受ける結
果、時間と共に温度上昇して潤滑機能を失い、遂
にはフエーシング面１０ｃを炭化させて剥離す
る。 By the way, the clutch facing 10 has conventionally been constructed in an annular shape with smooth concentric circles on the inner and outer peripheral edges 10a and 10b as shown in FIG.
There was a concern that poor lubrication would occur for the following reasons.
In other words, if the clutch facing 10 is now rotating relative to the converter cover 5 in the direction of the arrow α, the hydraulic oil particles P 1 , P 2 , P 3 will each rotate in the direction of the arrow β relative to the clutch facing 10. ,γ,
This means that it is rotating in the direction of δ. At this time, the hydraulic oil particles P2 on the surface 10c of the clutch facing 10 that is in sliding contact with the converter cover 5 are always on the surface 1.
As a result of remaining above 0c and being intermittently exposed to frictional heat, the temperature rises over time and loses its lubricating function, eventually carbonizing the facing surface 10c and peeling it off.
この問題解決のため、フエーシング面１０ｃに
第２図中２点鎖線で示す如く油溝１０ｄを設ける
ことも考えられるが、これによつてもロツクアツ
プクラツチ５のすべり結合時油溝１０ｄが封じ込
め室となつてこれに対する作動油の出入りがない
ため、十分な解決策と言えず、加えてフエーシン
グ面１０ｃの摩耗で油溝１０ｄがなくなつた後は
上記の問題解決を全く望み得ない。 In order to solve this problem, it is conceivable to provide an oil groove 10d in the facing surface 10c as shown by the two-dot chain line in FIG. Since there is no flow of hydraulic oil in and out of this problem, this cannot be said to be a sufficient solution.In addition, after the oil groove 10d disappears due to wear of the facing surface 10c, the above problem cannot be solved at all.
本考案はこれに代るクラツチフエーシングの形
状変更によつて上記の問題を実現しようとするも
ので、これを径方向凹凸部が存在する形状に構成
したことを特徴とする。 The present invention attempts to solve the above problem by changing the shape of the clutch facing instead, and is characterized in that it is configured to have a radial uneven portion.
以下、図示の実施例により本考案を詳細に説明
する。 Hereinafter, the present invention will be explained in detail with reference to illustrated embodiments.
第３図は本考案一実施例の態様を示し、本考案
においてはクラツチフエーシング１０の内外周縁
１０ａ，１０ｂを夫々互に一定の間隔を保つ波形
にして、クラツチフエーシング１０に径方向凸部
１３及び径方向凹部１４を円周方向へ交互に配し
て設ける。 FIG. 3 shows an embodiment of the present invention. In the present invention, the inner and outer circumferential edges 10a, 10b of the clutch facing 10 are made into a corrugated shape that maintains a constant distance from each other, and the clutch facing 10 has a radial convex portion. 13 and radial recesses 14 are arranged alternately in the circumferential direction.
そして、内外周縁１０ａ，１０ｂの波形曲線
は、この場合凸部１３（凹部１４）が８個である
から、夫々ｒ＝a1＋bcos（８θ）及びｒ＝a2＋
bcos（８θ）で表わされるが、ここでフエーシ
ング１０の幅ｃ（但しｃ＝a2−a1）に対しｂをｂ
＞ｃとなるよう決定して、凸部１３の内径１３ａ
を凹部１４の外径１３ａより大きくする。 In this case, the wavy curves of the inner and outer circumferential edges 10a and 10b are expressed as r=a 1 +b cos(8θ) and r=a 2 +b cos(8θ) since there are eight convex portions 13 (concave portions 14 ).
b cos(8θ), where b is the width c of the facing 10 (where c=a 2 −a 1 ).
＞c, and the inner diameter 13a of the protrusion 13 is determined
is made larger than the outer diameter 13 a of the recess 14 .
かかるクラツチフエーシングにおいては、これ
が矢印αで示す方向へ回転する際、作動油粒子
P4，P5，P6が夫々矢で示す方向へフエーシング１
０に対し相対回転する。この際フエーシング面１
０ｃ上の作動油粒子P5は外周縁１０ｂより外側の
コンバータ室７に出て、フエーシング面１０ｃ上
に戻ることを繰り返す。従つて、フエーシング面
１０ｃ上の作動油粒子はフエーシング面１０ｃ上
にとどまらず、摩擦熱を断続的に受けることがな
く、温度上昇を防止されると共にフエーシング面
１０ｃの潤滑を常時良好に行なう。 In such a clutch facing, when it rotates in the direction shown by arrow α, hydraulic oil particles
P 4 , P 5 , P 6 are facing 1 in the direction indicated by the arrows respectively.
Rotates relative to 0. At this time, facing surface 1
The hydraulic oil particles P 5 above 0c go out to the converter chamber 7 outside the outer peripheral edge 10b and return onto the facing surface 10c repeatedly. Therefore, the hydraulic oil particles on the facing surface 10c do not remain on the facing surface 10c and are not intermittently subjected to frictional heat, preventing a temperature rise and always providing good lubrication of the facing surface 10c.
又、内周縁１０ａで囲まれたロツクアツプ制御
室１１内の作動油粒子P4及びコンバータ室７内の
作動油粒子P6もフエーシング面１０ｃ上に出入り
し、温度上昇を防止され、フエーシング面１０ｃ
の潤滑を良好に保つ。 Further, the hydraulic oil particles P 4 in the lockup control chamber 11 surrounded by the inner peripheral edge 10a and the hydraulic oil particles P 6 in the converter chamber 7 also enter and exit onto the facing surface 10c, preventing the temperature from rising and increasing the temperature of the facing surface 10c.
Maintain good lubrication.
なお本例では、内径１３ａを外径１４ａより大
きくするから、これら内外径間において作動油粒
子がコンバータ室７、フエーシング面１０ｃ及び
ロツクアツプ室１１の３者間で順次出入りし、室
７，１１間で作動油を往来させ得る。この場合、
ロツクアツプクラツチ４をすべり結合させるスリ
ツプ制御状態ではコンバータ室７内の作動油がス
リツプによつてロツクアツプ制御室１１内の作動
油より高温になるが、両室間で作動油を往来させ
ることによつて油温分布の片寄りを防止でき、フ
エーシング面１０ｃの偏摩耗をなくすことができ
る。 In this example, since the inner diameter 13a is made larger than the outer diameter 14a, the hydraulic oil particles sequentially enter and exit between the converter chamber 7, the facing surface 10c, and the lock-up chamber 11 between the inner and outer diameters, and the particles flow between the chambers 7 and 11. can move hydraulic oil back and forth. in this case,
In the slip control state in which the lock-up clutch 4 is slidably connected, the hydraulic oil in the converter chamber 7 becomes hotter than the hydraulic oil in the lock-up control chamber 11 due to the slip. As a result, it is possible to prevent the oil temperature distribution from becoming uneven, and it is possible to eliminate uneven wear on the facing surface 10c.
かくして本考案フエーシングは上述の如く、径
方向凹凸部１３，１４が存在する形状に構成した
から、前記作用説明通りロツクアツプクラツチ４
のすべり結合時もフエーシング面１０ｃ上に作動
油を出入りさせることができ、フエーシング面１
０ｃの潤滑を常時良好に保つてこれが炭化及び剥
離するのを防げ、ロツクアツプトルクコンバータ
の耐久性を向上させることができる。 Thus, since the facing of the present invention is configured to have the radial uneven portions 13 and 14 as described above, the lock-up clutch 4 can be operated as described above.
It is possible to allow hydraulic oil to flow in and out on the facing surface 10c even when the facing surface 1
It is possible to maintain good lubrication of 0c at all times to prevent it from carbonizing and peeling off, thereby improving the durability of the lockup torque converter.
第１図はロツクアツプトルクコンバータの一般
構造を示す縦断側面図、第２図は従来のロツクア
ツプクラツチフエーシングの正面図、第３図は本
考案ロツクアツプクラツチフエーシングの一例を
示す正面図である。
１……ポンプインペラ（入力要素）、２……タ
ービンランナ（出力要素）、３……ステータ、４
……ロツクアツプクラツチ、５……コンバータカ
バー、６……エンジンクランクシヤフト、７……
コンバータ室、８……タービンハブ、９……出力
軸、１０……クラツチフエーシング、１０ａ，１
０ｂ……同内外周縁、１０ｃ……フエーシング
面、１３……径方向凸部、１３ａ……同内径、１
４……径方向凹部、１４ａ……同外径。
Fig. 1 is a longitudinal side view showing the general structure of a lock-up torque converter, Fig. 2 is a front view of a conventional lock-up clutch facing, and Fig. 3 is a front view showing an example of the lock-up clutch facing of the present invention. be. 1... Pump impeller (input element), 2... Turbine runner (output element), 3... Stator, 4
... Lockup clutch, 5 ... Converter cover, 6 ... Engine crankshaft, 7 ...
Converter chamber, 8... Turbine hub, 9... Output shaft, 10... Clutch facing, 10a, 1
0b... Same inner and outer peripheral edges, 10c... Facing surface, 13... Radial convex portion, 13a... Same inner diameter, 1
4...Radial recess, 14a...Same outer diameter.
Claims (1)
クラツチを具え、該ロツクアツプクラツチのク
ラツチ面にクラツチフエーシングを設けたロツ
クアツプトルクコンバータにおいて、前記クラ
ツチフエーシングを径方向凹凸部が存在する形
状に構成してなるトルクコンバータのロツクア
ツプクラツチフエーシング。 ２ 径方向凸部の内径が径方向凹部の外径より大
きい実用新案登録請求の範囲第１項記載のトル
クコンバータのロツクアツプクラツチフエーシ
ング。[Claims for Utility Model Registration] 1. A lock-up torque converter that is equipped with a lock-up clutch that can directly connect input and output elements as appropriate, and that has a clutch facing on the clutch surface of the lock-up clutch, in which the clutch facing has a diameter. A lock-up clutch facing for a torque converter configured in a shape with directional unevenness. 2. The lock-up clutch facing for a torque converter according to claim 1, wherein the inner diameter of the radial convex portion is larger than the outer diameter of the radial concave portion.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15368083U JPS6061552U (en) | 1983-10-05 | 1983-10-05 | Torque converter lock-up clutch facing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15368083U JPS6061552U (en) | 1983-10-05 | 1983-10-05 | Torque converter lock-up clutch facing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6061552U JPS6061552U (en) | 1985-04-30 |
| JPS6137902Y2 true JPS6137902Y2 (en) | 1986-11-01 |
Family
ID=30339933
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15368083U Granted JPS6061552U (en) | 1983-10-05 | 1983-10-05 | Torque converter lock-up clutch facing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6061552U (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006037991A (en) * | 2004-07-22 | 2006-02-09 | Aisin Aw Co Ltd | Lock-up mechanism for torque converter |
| JP4784631B2 (en) * | 2008-09-30 | 2011-10-05 | トヨタ自動車株式会社 | Driving force transmission device |
-
1983
- 1983-10-05 JP JP15368083U patent/JPS6061552U/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6061552U (en) | 1985-04-30 |
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