JPS6326579Y2 - - Google Patents
Info
- Publication number
- JPS6326579Y2 JPS6326579Y2 JP1980086819U JP8681980U JPS6326579Y2 JP S6326579 Y2 JPS6326579 Y2 JP S6326579Y2 JP 1980086819 U JP1980086819 U JP 1980086819U JP 8681980 U JP8681980 U JP 8681980U JP S6326579 Y2 JPS6326579 Y2 JP S6326579Y2
- Authority
- JP
- Japan
- Prior art keywords
- friction plate
- clutch
- restrainer
- suppressor
- clutch drum
- 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
- 239000000837 restrainer Substances 0.000 claims description 20
- 230000033001 locomotion Effects 0.000 claims description 5
- 229910000831 Steel Inorganic materials 0.000 description 6
- 239000010959 steel Substances 0.000 description 6
- 230000001133 acceleration Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000026058 directional locomotion Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 125000006850 spacer group Chemical group 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
- F16D13/68—Attachments of plates or lamellae to their supports
- F16D13/683—Attachments of plates or lamellae to their supports 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
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
-
- 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
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)
Description
【考案の詳細な説明】
本案は多板式クラツチの摩擦板受け装置の改良
に関するものである。[Detailed Description of the Invention] The present invention relates to an improvement of a friction plate receiving device for a multi-disc clutch.
従来の多板式クラツチの摩擦板受け装置を第１
図乃至第４図により説明すると、ａがクラツチ軸
（第５図の１参照）に固定したクラツチドラム、
a1，a2が同クラツチドラムａの内面に軸方向に連
続的に並ぶように設けた内歯スプライン、D3が
同内歯スプラインa1，a2の歯元円直径、D2が同
内歯スプラインa1の歯先円直径、D1が同内歯ス
プラインa2の歯先円直径で、同歯先円直径D2は
上記歯先円直径D1よりも大きい。またｂが摩擦
板抑え具、b1が同抑え具ｂの外周に設けた外歯ス
プライン、D4が同外歯スプラインb1の歯元円径、
D5が同外歯スプラインb1の歯先円直径で、同抑
え板ｂの外歯スプラインb1は上記クラツチドラム
ａの内歯スプラインa1に嵌合して、外歯スプライ
ンb1の歯元と内歯スプラインa1の歯先との間に頂
隙c1が、外歯スプラインb1の歯先と内歯スプライ
ンa1の歯元との間に頂隙c2が、それぞれ形成され
ている。またｄが上記クラツチドラムａの内歯ス
プラインa1部に設けた止め輪保持溝、ｅが同保持
溝ｄに嵌合した止め輪で、上記抑え具ｂが同止め
輪ｅと上記内歯スプラインa1，a2の間に形成した
段差部ｆと軸方向に移動させないように、また切
換弁（図示せず）を操作して、油室（第５図の１
４参照）（以下も算用数字の符号は第５図参照）
の油圧を解放すると、油圧ピストン３が戻りばね
８により右方へ移動し、駆動歯車１０の外歯スプ
ラインに係合した多数のスチール板４と上記クラ
ツチドラムａの内歯スプラインa2に係合した多数
の摩擦板５との間に隙間が形成されて、クラツチ
ドラムａから駆動歯車１０への動力伝達が遮断さ
れるように、また上記切換弁を操作して、圧油を
油室１４に送ると、油圧ピストン３が戻しばね８
に抗し左方へ移動し、スチール板４と摩擦板５と
が圧接されて、クラツチドラムａから駆動歯車１
０へ動力が伝達されるようになつている。 The first friction plate support device for a conventional multi-disc clutch
To explain with reference to FIGS. 4 to 4, a is a clutch drum fixed to the clutch shaft (see 1 in FIG. 5);
a 1 and a 2 are internal splines arranged continuously in the axial direction on the inner surface of the clutch drum a, D 3 is the root circle diameter of the internal splines a 1 and a 2 , and D 2 is the same The tip diameter D 1 of the internal spline a 1 is the tip diameter D 1 of the internal spline a 2 , and the tip diameter D 2 is larger than the tip diameter D 1 . In addition, b is a friction plate retainer, b 1 is an external spline provided on the outer periphery of the retainer b, D 4 is the root circle diameter of the external spline b 1 ,
D 5 is the tip circle diameter of the external spline b 1 , and the external spline b 1 of the holding plate b fits into the internal spline a 1 of the clutch drum a, and the teeth of the external spline b 1 A top gap c 1 is formed between the base and the tip of the internal spline a 1 , and a top gap c 2 is formed between the tip of the external spline b 1 and the root of the internal spline a 1 . ing. In addition, d is a retaining ring retaining groove provided in one part of the internal spline a of the clutch drum a, e is a retaining ring fitted in the retaining groove d, and the retainer b is the retaining ring e and the internal spline. The oil chamber (1 in Figure 5
(See Figure 5 for the signs of arithmetic numerals below.)
When the hydraulic pressure is released, the hydraulic piston 3 moves to the right by the return spring 8 and engages with the numerous steel plates 4 engaged with the external splines of the drive gear 10 and the internal splines a2 of the clutch drum a. The switching valve is operated so that a gap is formed between the clutch drum a and the large number of friction plates 5, and the power transmission from the clutch drum a to the drive gear 10 is cut off. When sent, the hydraulic piston 3 returns the spring 8
The steel plate 4 and the friction plate 5 are pressed against each other, and the drive gear 1 is moved from the clutch drum a to the clutch drum a.
Power is transmitted to 0.
前記多板式クラツチの摩擦板受け装置ｂ，ｄ，
ｅ，ｆでは、摩擦板抑え具ｂの外歯スプラインb1
をクラツチドラムａの内歯スプラインa1に嵌合し
たとき、摩擦板抑え具ｂの歯底部が内歯スプライ
ンa1，a2の間に形成した段差部ｆに当たり、同抑
え具ｂが第１図右方に移動できないようにするた
め、同抑え具ｂの歯底円径D4は、クラツチドラ
ムａの内歯スプラインa2の歯先円径D1よりも大
でなければならない。そのため、同外歯スプライ
ンb1の歯形は、歯丈が歯厚に対して極端に低い特
殊形状にならざるを得ず、同外歯スプラインb1を
標準カツターにより加工する場合には、まずカツ
ターの切込みを（D5−D4）／２とし、次いで所
要の歯厚を得るために円周方向に転位（通常これ
を横転位という）する必要があり、加工が非常に
面倒であつた。またこの加工を通常の歯切りのよ
うに行おうとすると、特殊形状の専用カツターを
必要として、コストを高めるという問題があつ
た。 Friction plate receiver devices b, d, for the multi-plate clutch;
In e and f, external spline b 1 of friction plate retainer b
When fitted to the internal spline a 1 of the clutch drum a, the tooth bottom of the friction plate retainer b hits the stepped portion f formed between the internal splines a 1 and a 2 , and the retainer b In order to prevent movement to the right in the figure, the root diameter D 4 of the retainer b must be larger than the tip diameter D 1 of the internal spline a 2 of the clutch drum a. Therefore, the tooth profile of the external tooth spline b 1 has to be a special shape in which the tooth height is extremely low compared to the tooth thickness. When machining the external tooth spline b 1 with a standard cutter, first It is necessary to set the depth of cut to (D 5 −D 4 )/2, and then dislocate the tooth in the circumferential direction (usually referred to as transverse dislocation) in order to obtain the required tooth thickness, which is extremely troublesome to process. Furthermore, if this process were to be carried out like normal gear cutting, a special cutter with a special shape would be required, which would increase costs.
本案は前記の問題点に対処するもので、クラツ
チドラム２に設けた内歯２ｂの歯先円直径D1よ
りも大きい直径D2を有する摩擦板抑え具嵌合部
２ｅに嵌合するとともに同内歯２ｂに係合したク
ラツチ摩擦板５とこれに隣接する摩擦板抑え具６
とを具え、同摩擦板抑え具６の軸方向移動を、上
記内歯２ｂ及び上記摩擦板抑え具嵌合部２ｅの間
に形成した段差部２ｅと上記クラツチドラム２に
取付けた止め輪７とにより阻止した多板式クラツ
チの摩擦板受け装置において、前記摩擦板抑え具
６の外周面を円筒面に形成して、同摩擦板抑え具
６を前記嵌合部２ｅ及び前記クラツチ摩擦板５に
対して相対回転可能に支持したことを特徴とする
多板式クラツチの摩擦板受け装置に係り、その目
的とする処は、特殊歯切り加工や特殊形状の専用
カツターを不要にできて、コストを低減できる改
良された多板式クラツチの摩擦板受け装置を供す
る点にある。 This proposal deals with the above-mentioned problem, and the internal teeth 2b provided on the clutch drum 2 are fitted into the friction plate retainer fitting portion 2e having a diameter D2 larger than the tooth tip circle diameter D1 , and the same. Clutch friction plate 5 engaged with internal teeth 2b and friction plate restrainer 6 adjacent thereto
The axial movement of the friction plate restrainer 6 is controlled by a step portion 2e formed between the internal teeth 2b and the friction plate restrainer fitting portion 2e, and a retaining ring 7 attached to the clutch drum 2. In the friction plate receiving device for a multi-plate clutch, the outer circumferential surface of the friction plate suppressor 6 is formed into a cylindrical surface, and the friction plate suppressor 6 is held against the fitting portion 2e and the clutch friction plate 5. This invention relates to a friction plate support device for a multi-plate clutch, which is characterized by being relatively rotatably supported by a multi-plate clutch, and its purpose is to reduce costs by eliminating the need for special gear cutting or special-shaped cutters. An object of the present invention is to provide an improved friction plate receiving device for a multi-plate clutch.
次に本案の多板式クラツチの摩擦板受け装置を
第５図乃至第８図に示す一実施例により説明する
と、１がクラツチ軸で、内燃機関（図示せず）等
により駆動される。また２がクラツチドラムで、
クラツチ軸１に焼ばめ等により固定されている。
また３がクラツチ軸１とクラツチドラム２とに摺
動自在に嵌挿した油圧ピストン、１４が油室ピス
トン３とクラツチドラム２との間に形成された油
室、２ａ，２ｂがクラツチドラム２の内面に軸方
向に連続的に並ぶように設けた内歯スプライン、
D3が同内歯スプライン２ａ，２ｂの歯元円直径、
D2が同内歯スプライン２ａの歯先円直径、D1が
同内歯スプライン２ｂの歯先円直径で、同歯先円
直径D2は同歯先円直径D1よりも大きい。また２
ｃが上記内歯スプライン２ａ，２ｂの間に形成さ
れた段差部、２ｄが上記内歯スプライン２ａ部に
設けた止め輪保持溝、２ｅが同保持溝２ｄと上記
段差部２ｅとの間に形成された摩擦板抑え具嵌合
部、６が本案で最も特徴とする摩擦板抑え具で、
その外周面が円筒面に形成されている。またその
直径は上記内歯スプライン２ａの歯先円直径と同
じD2で、上記嵌合部２ｅに嵌合し、止め輪保持
溝２ｄに嵌合した止め輪７と上記段差部２ｃとで
軸方向移動が阻止されるようになつている。また
４が多数のスチール板、５が多数の摩擦板で、こ
れらは上記摩擦板抑え具６と上記油圧ピストン３
との間に交互に配列されるとともに同スチール板
４が駆動歯車１０の外歯スプラインに、同摩擦板
５が上記クラツチドラム２の内歯スプライン２ｂ
に、それぞれ係合している。なお上記駆動歯車１
０は同歯車１０に圧入したブツシユ１１を介して
前記クラツチ軸１に遊嵌されている。また９がク
ラツチ軸１の止め輪保持溝に嵌合した止め輪、１
２，１３が同止め輪９と上記駆動歯車１０との間
に介装して同止め輪９と同駆動歯車１０と上記ク
ラツチ軸１とに対し摺動自在なスラストワツシヤ
と間座、８が同止め輪９と前記油圧ピストン３と
に間に介装した戻しばねである。なおクラツチド
ラム２は、内歯スプライン２ａ，２ｂの加工前に
直径D1の円孔と直径D2の円孔とを加工し、次い
で止め輪保持溝２ｄを加工し、次いで上記各円孔
に通常の歯切りを行つて、内歯スプライン２ａ，
２ｂを形成すればよい。また抑え具６の外周は円
形であるからその加工は極めて容易である。また
内歯スプライン２ａの歯先円直径と摩擦板抑え具
６の直径とはともにD2であるが、互の嵌合は遊
合でよい。 Next, the friction plate receiving device for a multi-disc clutch according to the present invention will be explained with reference to an embodiment shown in FIGS. 5 to 8. Reference numeral 1 denotes a clutch shaft, which is driven by an internal combustion engine (not shown) or the like. 2 is the clutch drum,
It is fixed to the clutch shaft 1 by shrink fitting or the like.
3 is a hydraulic piston slidably inserted into the clutch shaft 1 and the clutch drum 2; 14 is an oil chamber formed between the piston 3 and the clutch drum 2; and 2a and 2b are the hydraulic pistons of the clutch drum 2. Internal splines arranged continuously in the axial direction on the inner surface,
D 3 is the root diameter of the internal splines 2a and 2b,
D 2 is the tip diameter of the internal spline 2a, D 1 is the tip diameter of the internal spline 2b, and the tip diameter D 2 is larger than the tip diameter D 1 . Also 2
c is a stepped portion formed between the internal splines 2a and 2b, 2d is a retaining ring retaining groove provided in the internal spline 2a, and 2e is formed between the retaining groove 2d and the stepped portion 2e. The friction plate restrainer fitting part 6 is the friction plate restrainer that is the most distinctive feature of this project.
Its outer peripheral surface is formed into a cylindrical surface. Also, its diameter is D2 , which is the same as the diameter of the tip circle of the internal spline 2a, and the retaining ring 7, which is fitted into the fitting part 2e and fitted into the retaining ring retaining groove 2d, and the stepped part 2c are connected to the shaft. Directional movement is now prevented. Further, 4 is a large number of steel plates, and 5 is a large number of friction plates, which are connected to the friction plate suppressor 6 and the hydraulic piston 3.
The steel plates 4 are arranged alternately between the external splines of the drive gear 10, and the friction plates 5 are arranged on the internal splines 2b of the clutch drum 2.
are engaged with each other. Note that the above drive gear 1
0 is loosely fitted onto the clutch shaft 1 via a bush 11 that is press-fitted into the gear 10. 9 is a retaining ring fitted into the retaining ring retaining groove of the clutch shaft 1;
2 and 13 are interposed between the retaining ring 9 and the driving gear 10 and are slidable on the retaining ring 9, the driving gear 10, and the clutch shaft 1, and a spacer; 8 is the same; This is a return spring interposed between the retaining ring 9 and the hydraulic piston 3. In addition, before machining the internal splines 2a and 2b, the clutch drum 2 has a circular hole with a diameter D1 and a circular hole with a diameter D2 , and then a retaining ring retaining groove 2d is machined, and then each of the circular holes is machined. After performing normal gear cutting, the internal spline 2a,
2b may be formed. Further, since the outer periphery of the restrainer 6 is circular, its processing is extremely easy. Furthermore, although the diameter of the tip circle of the internal spline 2a and the diameter of the friction plate restrainer 6 are both D2 , they may fit loosely.
次に前記多板式クラツチの摩擦板受け装置の作
用効果を説明する。切換弁（図示せず）を操作し
て、油室１４の油圧を解放し、油圧ピストン３を
戻しばね８により右方へ移動し、駆動歯車１０の
外歯スプラインに係合した多数のスチール板４と
クラツチドラム２の内歯スプライン２ｂに係合し
た多数の摩擦板５との間に間隙を形成して、クラ
ツチドラム２から駆動歯車１０への動力伝達を遮
断したとき、摩擦板抑え具６には、軸方向にも回
転方向にも力が作用しない。また上記切換弁を操
作して、圧油を油室１４に送り、油圧ピストン３
を戻しばね８に抗し左方へ移動し、多数のスチー
ル板４と摩擦板５とを圧接して、クラツチドラム
２から駆動歯車１０へ動力を伝達するとき、摩擦
板抑え具６には、軸方向に押圧力が作用しても回
転方向には力が作用しない。そのため摩擦板抑え
具６は、軸方向に対して強度が充分であれば、外
周面に外歯スプラインを設ける必要がなく、外周
面は円筒面でよい。本案は摩擦板抑え具６をこの
ようにして、特殊歯切り加工や特殊形状の専用カ
ツターを不要にする。従つてその加工が前述のよ
うに極めて容易で、コストを低減できる効果があ
る。 Next, the effects of the friction plate receiving device of the multi-plate clutch will be explained. A switching valve (not shown) is operated to release the hydraulic pressure in the oil chamber 14, and the hydraulic piston 3 is moved to the right by the return spring 8, and a number of steel plates engaged with the external splines of the drive gear 10 are moved. 4 and a large number of friction plates 5 engaged with the internal splines 2b of the clutch drum 2 to cut off power transmission from the clutch drum 2 to the drive gear 10, the friction plate restrainer 6 No force acts in either the axial or rotational direction. Also, by operating the switching valve, pressure oil is sent to the oil chamber 14, and the hydraulic piston 3
When the clutch drum 2 is moved to the left against the return spring 8 and a large number of steel plates 4 and friction plates 5 are pressed together to transmit power from the clutch drum 2 to the drive gear 10, the friction plate restrainer 6 is moved to the left. Even if a pressing force is applied in the axial direction, no force is applied in the rotational direction. Therefore, as long as the friction plate restrainer 6 has sufficient strength in the axial direction, there is no need to provide an external spline on the outer circumferential surface, and the outer circumferential surface may be a cylindrical surface. In the present invention, the friction plate restrainer 6 is made in this manner, thereby eliminating the need for special gear cutting or special shaped cutters. Therefore, as mentioned above, the processing is extremely easy and has the effect of reducing costs.
なお本案では分解、組立を容易にするために摩
擦板抑え具６の外周面を円筒面に形成して、同摩
擦板抑え具６を摩擦板抑え具嵌合部２ｅに遊合し
ている。つまり摩擦板抑え具６を嵌合部２ｅ及び
クラツチ摩擦板５に対して相対回転可能に支持し
ているが、このようにしても全く問題がないこと
が判明した。即ち、クラツチを急激に遮断したり
入れたりすると、その瞬間、原動機例えば内燃機
関の回転数が若干変化して、クラツチドラム２に
角加速度が発生する。その際、クラツチドラム２
と摩擦板抑え具６とが遊合であると、抑え具６の
慣性により互の間に相対運動の起る可能性があ
る。しかし油圧クラツチは一般に、クラツチが急
に入るのを防止するために緩衝弁を設けている。
また急に負荷を遮断しても、負荷部例えば舶用プ
ロペラに相当大きな慣性があるので、クラツチド
ラム２の角加速度は小さい。本件について最も苛
酷な条件と思われる正転、逆転の繰返しを5000回
以上実施したところ、クラツチドラム２と摩擦板
抑え具６とが回転方向に相対運動を起した形跡は
殆んどなく、摩擦板抑え具６を摩擦板抑え具嵌合
部２ｅに遊合しても全く問題がないことが判明し
た。 In the present invention, in order to facilitate disassembly and assembly, the outer peripheral surface of the friction plate restrainer 6 is formed into a cylindrical surface, and the friction plate restrainer 6 is loosely engaged with the friction plate restrainer fitting portion 2e. In other words, although the friction plate restrainer 6 is supported so as to be rotatable relative to the fitting portion 2e and the clutch friction plate 5, it has been found that there is no problem at all even if this is done. That is, when the clutch is suddenly closed or engaged, the rotational speed of the prime mover, such as an internal combustion engine, changes slightly at that moment, and angular acceleration is generated in the clutch drum 2. At that time, clutch drum 2
If the friction plate retainer 6 and the friction plate retainer 6 are loose, there is a possibility that relative movement will occur between them due to the inertia of the retainer 6. However, hydraulic clutches generally include a buffer valve to prevent sudden engagement of the clutch.
Furthermore, even if the load is suddenly interrupted, the angular acceleration of the clutch drum 2 is small because the load portion, such as a marine propeller, has a considerable inertia. After repeating forward and reverse rotation more than 5,000 times, which is considered to be the most severe condition for this case, there was almost no evidence of relative movement between the clutch drum 2 and the friction plate restrainer 6 in the rotational direction, and there was no friction. It has been found that there is no problem at all when the plate restrainer 6 is loosely fitted into the friction plate restrainer fitting portion 2e.
第１図は従来の多板式クラツチの摩擦板受け装
置を示す縦断側面図、第２，３図はその分解縦断
側面図、第４図は第１図矢視−線に沿つた縦
断正面図、第５図は本案に係る多板式クラツチの
摩擦板受け装置の概略を示す縦断側面図、第６図
は第５図矢印部分を拡大して示す縦断側面図、
第７，８図はその分解縦断側面図である。
２……クラツチドラム、２ｂ……内歯、D1…
…内歯２ｂの歯先円直径、２ｃ……段差部、２ｅ
……摩擦板抑え具嵌合部、D2……嵌合部２ｅの
直径、５……摩擦板、６……摩擦板抑え具、７…
…止め輪。
FIG. 1 is a longitudinal side view showing a conventional multi-disc clutch friction plate receiving device, FIGS. 2 and 3 are exploded longitudinal side views thereof, and FIG. 4 is a longitudinal front view taken along the arrow line in FIG. 1. FIG. 5 is a vertical side view schematically showing the friction plate receiving device for a multi-disc clutch according to the present invention, and FIG. 6 is a vertical side view showing an enlarged view of the arrowed part in FIG.
Figures 7 and 8 are exploded longitudinal sectional side views thereof. 2...clutch drum, 2b...inner teeth, D 1 ...
...Tooth tip circle diameter of internal tooth 2b, 2c...Step portion, 2e
...Friction plate suppressor fitting part, D 2 ...Diameter of fitting part 2e, 5...Friction plate, 6...Friction plate suppressor, 7...
…Retaining ring.
Claims (1)
径D1よりも大きい直径D2を有する摩擦板抑え具
嵌合部２ｅに嵌合するとともに同内歯２ｂに係合
したクラツチ摩擦板５とこれに隣接する摩擦板抑
え具６とを具え、同摩擦板抑え具６の軸方向移動
を、上記内歯２ｂ及び上記摩擦板抑え具嵌合部２
ｅの間に形成した段差部２ｃと上記クラツチドラ
ム２に取付けた止め輪７とにより阻止した多板式
クラツチの摩擦板受け装置において、前記摩擦板
抑え具６の外周面を円筒面に形成して、同摩擦板
抑え具６を前記嵌合部２ｅ及び前記クラツチ摩擦
板５に対して相対回転可能に支持したことを特徴
とする多板式クラツチの摩擦板受け装置。 The clutch friction plate 5 is fitted into the friction plate suppressor fitting portion 2e having a diameter D2 larger than the tip circle diameter D1 of the internal tooth 2b provided on the clutch drum 2 and engaged with the internal tooth 2b. The friction plate suppressor 6 is provided with an adjacent friction plate suppressor 6, and the axial movement of the friction plate suppressor 6 is controlled by the internal teeth 2b and the friction plate suppressor fitting portion 2.
In a friction plate receiving device for a multi-plate clutch which is blocked by a stepped portion 2c formed between the gaps 2c and a retaining ring 7 attached to the clutch drum 2, the outer circumferential surface of the friction plate restrainer 6 is formed into a cylindrical surface. A friction plate support device for a multi-plate clutch, characterized in that the friction plate restrainer 6 is supported so as to be rotatable relative to the fitting portion 2e and the clutch friction plate 5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980086819U JPS6326579Y2 (en) | 1980-06-23 | 1980-06-23 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980086819U JPS6326579Y2 (en) | 1980-06-23 | 1980-06-23 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5710531U JPS5710531U (en) | 1982-01-20 |
| JPS6326579Y2 true JPS6326579Y2 (en) | 1988-07-19 |
Family
ID=29448966
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1980086819U Expired JPS6326579Y2 (en) | 1980-06-23 | 1980-06-23 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6326579Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014518999A (en) * | 2011-06-06 | 2014-08-07 | バリュー・エクストラクション・リミテッド・ライアビリティ・カンパニー | Clutch assembly with molded retaining ring |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58150974U (en) * | 1982-04-01 | 1983-10-08 | 高橋 公一郎 | odd fishing line |
| FR3130335B1 (en) * | 2021-12-14 | 2024-03-15 | Valeo Embrayages | Means for retaining an axial stop ring for a clutch, comprising at least one weld |
| FR3130336A1 (en) * | 2021-12-14 | 2023-06-16 | Valeo Embrayages | Retaining means for an axial stop ring for a clutch, comprising at least one retaining member |
-
1980
- 1980-06-23 JP JP1980086819U patent/JPS6326579Y2/ja not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014518999A (en) * | 2011-06-06 | 2014-08-07 | バリュー・エクストラクション・リミテッド・ライアビリティ・カンパニー | Clutch assembly with molded retaining ring |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5710531U (en) | 1982-01-20 |
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