JPS58632A - Plate spring - Google Patents

Abstract

PURPOSE:To provide a plate spring with such a flat characteristic that the force of the spring has little change, by extending all or some of plural through openings provided in the inner part of the spring, to its outer part. CONSTITUTION:A plurality of through openings 10d are provided in a plate spring 10 inside its outer part 10a so that the through openings are continuous to the outer ends of slots 10c and located on a circumference. The through openings 10d are enlarged in the radial direction so that they are elliptically shaped and extend to the outer part 10a of the spring 10. When the plate spring 10 is fitted on a friction clutch or the like, a clearance is defined on the radially inner side of a rivet 8 because the through hole 10d extends to the outer part 10a of the spring. Because of the presence of the clearance, the pressure deformation of the plate spring 10 which is caused when the inner end of a tongue 10b is pushed in the direction of an arrow F2 by a release bearing is different from that of a conventional plate spring. This results in preventing the depressing force on a pedal from being increased due to the wear of a clutch friction plate.

Description

【発明の詳細な説明】 本発明は摩擦クラッチ装置等に用いて好適な皿ばねに関
するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a disc spring suitable for use in friction clutch devices and the like.

第１図に示すよう゛な摩擦クラッチ装置では、符号１に
て示す皿ばねをフライホイール２に一体のクラッチカバ
ー６と、クラッチディスク３の摩擦板４を前記フライホ
イール２に押圧するプレッシャプレート５との間に弾装
している。The friction clutch device shown in FIG. 1 includes a clutch cover 6 in which a disc spring indicated by reference numeral 1 is integrated with a flywheel 2, and a pressure plate 5 that presses a friction plate 4 of a clutch disc 3 against the flywheel 2. A bullet is loaded between the two.

従来のこの種の皿ばねは、第２図に合わせて示すように
環状のばね板よりなり、その外周側部位に設けたばね部
１＆と、内周端から半径方向に切込んだスロワ）ｔｏに
よって互に分離される複数の舌片１ｂとを有し、更にば
ね部１ａの内周側にはスロワ）ｉｏの外層部に連通して
穿設された透孔１ａを同−５周上に有している。This type of conventional disc spring consists of an annular spring plate, as shown in FIG. It has a plurality of tongue pieces 1b that are separated from each other, and further has a through hole 1a bored on the inner peripheral side of the spring part 1a so as to communicate with the outer layer part of the thrower) on the -5th circumference. are doing.

そして、皿ばね１は第１図のように、これを内外に挾む
一対の支点リング７．７ｔ−介して、透孔１ｄに挿通さ
れるリベット８で前記クラッチカバー６に枢支されてお
り、ばね部１ａの作用点９においてプレッシャプレート
５に矢印Ｐ１方向のばね力を付与して摩擦板４をフライ
ホイール２に押圧し、フライホイール２とクラッチディ
スク３との接続を行なっている。As shown in FIG. 1, the disc spring 1 is pivotally supported on the clutch cover 6 by a rivet 8 inserted into the through hole 1d via a pair of fulcrum rings 7.7t that sandwich it inside and outside. , a spring force in the direction of arrow P1 is applied to the pressure plate 5 at the point of action 9 of the spring portion 1a to press the friction plate 4 against the flywheel 2, thereby connecting the flywheel 2 and the clutch disc 3.

、　　一方、前述したクラッチ接続状態を解除するには
、クラッチペダルを踏込んで皿ばね１の舌片１ｂの内端
近傍をレリースベアリング１１により図示左方へ押せば
よく、これにより皿ばねＤ作用点９における矢印１□方
向の押圧力が低減ないし零となり、プレッシャプレート
５を介する、摩擦板４に対する押圧力が低下してクラッ
チを断層状態に切換えるのである。On the other hand, in order to release the above-mentioned clutch connection state, it is sufficient to depress the clutch pedal and push the vicinity of the inner end of the tongue piece 1b of the disc spring 1 to the left in the figure by the release bearing 11, thereby releasing the action point of the disc spring D. The pressing force in the direction of the arrow 1□ at 9 is reduced or becomes zero, and the pressing force against the friction plate 4 via the pressure plate 5 is reduced, switching the clutch to the disconnected state.

ところで、前述のようなりラッチ装置では、クラッチの
断接操作の繰返しによって摩擦板が摩耗した場合におい
てもクラッチの伝達トルクの低下が生じないように、例
えば第３図の皿ばね特性曲線で示すように、Ｊ。（ばね
カＰ。）点を初期たわみ設定点と定め、この初期たわみ
設定点δ。から摩擦板の摩耗によって皿ばねの撓み量が
減じて撓みがＪ、（ばね力Ｑ　ｍ）点に達するまでの区
間ムを使用範囲としている。しかしながら、従来の皿ば
ねの特性は同図の曲線■に示す通り皿ばねの撓み量が減
するに従って皿ばねのばね力が大巾に増加する特性とな
っており、このことは換言すればクラッチを断層する場
合に皿ばねの舌片に加えるべき押力すなわちクラッチペ
ダルの踏込み力が着しく増加することになる。したがっ
て、従来のクラッチ装置では、クラッチの使用を経て摩
擦板の摩耗が進行されるのに伴なってクラッチ断層時に
おけるクラッチペダルの踏込み力が徐々に増加し、クラ
ッチの軽快な操作性を損なうという不具合が生じている
。By the way, in the above-mentioned latch device, in order to prevent the transmission torque of the clutch from decreasing even when the friction plate is worn out due to repeated engagement and disengagement operations of the clutch, the latch device is designed so that the transmission torque of the clutch does not decrease, for example, as shown in the disc spring characteristic curve in Fig. 3. In, J. (Spring force P.) point is defined as the initial deflection setting point, and this initial deflection setting point δ. The range of use is defined as the period from when the amount of deflection of the disc spring decreases due to wear of the friction plate until the deflection reaches a point J (spring force Q m). However, the characteristics of conventional disc springs are such that as the amount of deflection of the disc spring decreases, the spring force of the disc spring increases significantly, as shown by the curve ■ in the same figure. When this happens, the pressing force that must be applied to the tongue of the disc spring, that is, the clutch pedal depression force, increases considerably. Therefore, in conventional clutch devices, as the friction plates wear out through use of the clutch, the clutch pedal depression force at the time of clutch failure gradually increases, impairing the ease of clutch operation. A problem has occurred.

本発明はこのような不具合に鑑みなされたもので、ばね
力の変化の少ない平担なばね特性を有し、摩擦クラッチ
装置に適用した場合にもその経時的な変化にかかわらず
常に円滑かつ軽快な操作を行なうことができしかも安定
したトルク伝達特性を得ることができる皿ばねを提供す
ることを目的としている。The present invention was developed in view of these problems, and has a flat spring characteristic with little change in spring force, so that even when applied to a friction clutch device, it will always be smooth and light regardless of changes over time. It is an object of the present invention to provide a disc spring that can be operated with ease and has stable torque transmission characteristics.

以下、本発明の具体的実施例を図面と共に説明する。Hereinafter, specific embodiments of the present invention will be described with reference to the drawings.

第４図は本発明の皿ばねを示し、同図体）は斜視図、―
）は一部を切除した平面図である。皿ばね１０は、自由
状態での形状を全体として截頭円錐状を呈した環状のば
ね板にて構成しており、その外周側の環状の部分をばね
部１０ｍとして構成している。前記ばね部１０＆の内周
側には皿ばね１０の内周端から半径方向に複数本のスロ
ット１０Ｇを形成し、これらのスロット１０ｃにより互
に円周方向に分離する複数の舌片１０ｂを構成している
。そして、前記ばね部１０ｍの内周側でかつ前記スロワ
）　１０ｃの外周端にはスロット１０ｃに連通する透孔
１０ｄを円周上位置に複数個形成しているが、本実施例
ではこれらの透孔１０ｄの全数の外周側一部を更に半径
方向に拡大形成して長円形とし、該一部が前記ばね部１
０＆に延在するように構成しているのである。Fig. 4 shows the disc spring of the present invention, the figure) is a perspective view, -
) is a partially cutaway plan view. The disc spring 10 is constituted by an annular spring plate having a truncated conical shape as a whole in a free state, and an annular portion on the outer peripheral side thereof is constituted as a spring portion 10m. A plurality of slots 10G are formed in the inner circumferential side of the spring portion 10& in the radial direction from the inner circumferential end of the disc spring 10, and a plurality of tongue pieces 10b are formed to be separated from each other in the circumferential direction by these slots 10c. are doing. A plurality of through holes 10d communicating with the slots 10c are formed at circumferential positions on the inner peripheral side of the spring portion 10m and at the outer peripheral end of the thrower 10c. A part of the outer peripheral side of all the holes 10d is further enlarged in the radial direction to form an oval shape, and the part is formed in the spring part 1.
It is configured to extend from 0&.

このように構成した皿ばね１０は第５図に示すように７
ライホイール２に一体のクラッチカバー６と、クラッチ
ディスク３の摩擦板４を前記フライホイール２に押圧す
るプレッシャプレート５との間に内装し、内外から挾む
一対の支点リング７．７を介して前記透孔１０（ｌに挿
通されるリベット８にてクラッチカバー６に枢支される
ことになる。したがって、この装着状態では、同図から
も明らかなようにリベット８の半径方向側には透孔１０
ｃｌをばね部１０＆に延在させたことによる空所が形成
されることになり、舌片１０ｂの内端を図外のレリーズ
ベアリングにより矢印１２方向に押圧されたときの皿ば
ね１ｏの圧扁化変形の状態はこの空所の存在によって第
１図、第２図のものとは異なったものとなる。The disc spring 10 constructed in this way has 7 parts as shown in FIG.
It is installed between a clutch cover 6 integrated with the flywheel 2 and a pressure plate 5 that presses the friction plate 4 of the clutch disc 3 against the flywheel 2, via a pair of fulcrum rings 7.7 sandwiched from the inside and outside. The clutch cover 6 is pivotally supported by the rivet 8 inserted through the through hole 10 (l).Therefore, in this installed state, as is clear from the figure, there is no through hole on the radial side of the rivet 8. hole 10
A void is formed by extending cl into the spring portion 10&, and when the inner end of the tongue piece 10b is pressed in the direction of arrow 12 by a release bearing (not shown), the flattening of the disc spring 1o is reduced. Due to the existence of this void, the state of deformation differs from that shown in FIGS. 1 and 2.

以上の結果、透孔１０（ｌのばね部１０ａにおける延在
寸法を適切な値とすることにより、第５図のクラッチ装
置内における皿ばね１ｏの特性曲線を第３図の曲線Ｉに
変化させることができた即ち、初期撓み設定点δ。から
撓み量を減じた撓み量〜時のばね力を贈から帽に低減で
き、しかもその間の有効作動区間ムのばね力の変化も緩
やかな傾きを有する直線近似の特性とすることができた
。これにより、クラッチ使用回数を経るのに伴なって摩
擦板の摩耗が進行しても、皿ばね１０の舌片１０ｂに加
えるべき押力すなわちクラッチペダルの踏込み力の極端
な増加は防止でき、クラッチ操作を円滑かつ軽快なもの
と１かつ安定したトルク伝達特性を得ることができるの
である。As a result of the above, by setting the extension dimension of the through hole 10(l) in the spring portion 10a to an appropriate value, the characteristic curve of the disc spring 1o in the clutch device in FIG. 5 is changed to the curve I in FIG. 3. In other words, it is possible to reduce the spring force when the amount of deflection is reduced from the initial deflection set point δ, and the change in spring force in the effective operating range during that time also has a gentle slope. As a result, even if the wear of the friction plate progresses over the number of times the clutch is used, the pushing force to be applied to the tongue piece 10b of the disc spring 10, that is, the clutch pedal This makes it possible to prevent an extreme increase in the pedal effort, and to achieve smooth and light clutch operation and stable torque transmission characteristics.

なお、逃孔１０ｄはその全数をばね部に延在させずに、
第６図に示すように円周上に配置した複数−の６孔１０
４．　１００の中、１個飛びの透孔１０ｄをのみばねＭ
、１０ｍに延在させるような構成としてもよい。In addition, all of the escape holes 10d do not extend to the spring part,
A plurality of six holes 10 arranged on the circumference as shown in FIG.
4. Check the through hole 10d every one out of 100 and use the spring M
, 10 m.

ここで、本発明の具体的実施例を第７図に基ついてｌ１
ｉ２明する。即ち、皿ばねの外径２１０　ｍｍ　。Here, a specific embodiment of the present invention will be described based on FIG.
i2 clear. That is, the outer diameter of the disc spring is 210 mm.

厚さ２．７６　！１１０１　、自由状態での角度１４°
で透孔の巾１１を９ｍ、中径方向長さ１２を１０ｍｎと
して円周上等間隔に１８個設け、かつばね部の内径を１
６９−１外側支持点直径を２０６ｍｍ、内側支持点直径
を１７１閣とした従来の皿ばねの特性曲線を曲線Ａで示
す。これに対し、透孔の半径方向の長さ１２を１５閣（
ばね部に４ｍｍ延在）とし、外径、内径及び各支点直径
を全て同一にした皿はねでは曲線げに示す特性が得られ
た。また、長さ１２をｌ　ｇ　ｗ　（ばね部に７鵬延在
）とした場合には曲線０輪示す特性が得られた。更に長
さ１２を１５ｍ＋。Thickness 2.76! 1101, angle 14° in free state
The width 11 of the through holes is 9 m, the length 12 in the middle diameter direction is 10 mm, and 18 holes are provided at equal intervals on the circumference, and the inner diameter of the spring part is 1.
69-1 Curve A shows the characteristic curve of a conventional disc spring in which the outer support point diameter is 206 mm and the inner support point diameter is 171 mm. On the other hand, the radial length 12 of the through hole is 15 kaku (
In a countersunk spring in which the outer diameter, inner diameter, and diameter of each fulcrum were all the same, the characteristic shown in the curved line was obtained. Further, when the length 12 was set to lgw (extending 7 lengths to the spring part), a characteristic showing zero curves was obtained. Furthermore, length 12 is 15m+.

ｌＱｍとした透孔を交互に配設した場合には曲線りに示
す特性が、長さ１２を１８ｍ、　１０ｍとした透孔を交
互に配設した場合には曲ａｍに示す特性が夫々得られた
。なお、実施例では初期設定点荷重（１’ｏ）を調節す
るために厚さおよび自由状態での角度を一部変更してお
り、その結果曲線りでは従来の皿ばね（曲線ム）に比較
して最大荷重が９２ｒｇ低下し、クラッチペダルの踏込
みで生ずる最低荷重は約１８４ｋｇ上昇した特性が得ら
れた。When the through holes with a length of 1Qm are arranged alternately, the characteristics shown in the curved line are obtained, and when the through holes with a length of 12 of 18 m and 10 m are arranged alternately, the characteristics shown in the curve am are obtained. Ta. In addition, in the example, the thickness and angle in the free state were partially changed in order to adjust the initial setting point load (1'o), and as a result, the curved shape was lower than that of a conventional disc spring (curved spring). As a result, the maximum load decreased by 92 rg, and the minimum load generated by pressing the clutch pedal increased by approximately 184 kg.

以上の説明から明らかなように本発明の皿ばねは透孔の
全数もしくは一部の一部分をばね部に延在させるように
構成しているので、ばね力に変化の少ない平担なばね特
性を得ることができ、この皿ばねを摩擦クラッチ装置に
適用した場合には摩擦板の摩耗にかかわらずクラッチ断
接操作におけるクラッチペダルの踏込み力の極端な増大
を防止でき、略一定した低い力での円滑かつ軽快な操作
を可能とし、しかも安定したトルク伝達特性、を得るこ
とができる。更に、クラッチ装置に適用した場合、皿ば
ね単体の製作誤差のほか各構成部品の製作誤差、組立誤
差等によって初期設定点に若干のばらつきが生じるのが
通常であるが、本発明の皿ばねな用いれは初期設定点近
傍のばね力の変化を小さくできるので、前記各種誤差の
影響を受けない安定した初期設定荷重を有するクラッチ
装置を得ることができるのである。As is clear from the above description, the disc spring of the present invention is configured so that all or a portion of the through holes extend into the spring portion, so that it has a flat spring characteristic with little change in spring force. When this disc spring is applied to a friction clutch device, it is possible to prevent an extreme increase in the clutch pedal depression force during clutch engagement/disengagement operations regardless of the wear of the friction plates, and it is possible to prevent an extreme increase in the clutch pedal depression force during clutch engagement/disengagement operations, and to maintain a substantially constant low force. Smooth and light operation is possible, and stable torque transmission characteristics can be obtained. Furthermore, when applied to a clutch device, there will normally be some variation in the initial setting point due to manufacturing errors of each component, assembly errors, etc. as well as manufacturing errors of the disc spring itself, but the disc spring of the present invention Since the change in spring force near the initial setting point can be reduced, it is possible to obtain a clutch device having a stable initial setting load that is not affected by the various errors mentioned above.

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

第１図は従来の皿ばねな施したクラッチ装置の要部断面
図、第２図はｉ来の皿ばねの一部切除した正面図、第３
図はばね特性の説明図、第４図は本発明の皿ばねを示し
、（Ａ）は斜視図、ａ３）は一部切除した正面図、第５
図は本発明の皿ばねを施したクラッチ装置の要部断面図
、第６図は他の実施例の皿ばねの一部切除した正面図、
第７図は初期設定荷重を一致させた従来の皿ば。 ねと本発明の皿ばねの特性を比較す−る特性図である。 １・・・従来の皿ばね、２・・・フライホイール、３・
−・クラッチディスク、４・・・摩擦板、５・・・プレ
ッシャプレート、６・・・クラッチカバー、８−・・リ
ベット、１０・・・皿ばね、１０＆・・・ばね部、１０
ｂ・・・舌片、１０ｃ・・・スロット、１０ｄ−・・透
孔。 第４図（Ａ） 第４図（Ｂ） 第５図Fig. 1 is a cross-sectional view of the main parts of a conventional clutch device equipped with a disc spring, Fig. 2 is a partially cutaway front view of a conventional disc spring, and Fig. 3 is a partially cutaway front view of a conventional disc spring.
The figure is an explanatory diagram of spring characteristics, FIG. 4 shows a disc spring of the present invention, (A) is a perspective view, a3) is a partially cutaway front view, and
The figure is a sectional view of a main part of a clutch device equipped with a disc spring according to the present invention, and FIG. 6 is a partially cutaway front view of a disc spring of another embodiment.
Figure 7 shows a conventional plate with the same initial setting load. FIG. 1... Conventional disc spring, 2... Flywheel, 3.
- Clutch disk, 4... Friction plate, 5... Pressure plate, 6... Clutch cover, 8-... Rivet, 10... Belleville spring, 10 &... Spring part, 10
b...tongue piece, 10c...slot, 10d-...through hole. Figure 4 (A) Figure 4 (B) Figure 5

Claims (2)

【特許請求の範囲】[Claims] （１）　　自由状態での形状が全体として截頭円錐状を
呈した環状のばね板より成り、その外周側部位にはばね
部を有するとともに、このばね部の内周側には円周配置
した懐数個の透孔を有し、その圧扁化変形に応じたばね
力を利用するようにした皿ばねにおいて、前記透孔の全
数もしくは選択された一部はその透孔の一部分を前記ば
ね部に延在してなることを特徴とする皿ばね。(1) Consists of an annular spring plate that has a truncated conical shape as a whole in its free state, and has a spring part on its outer circumferential side, and a circumferentially arranged spring plate on the inner circumferential side of this spring part. In a disc spring that has several through holes and utilizes a spring force corresponding to the compressed deformation of the through holes, all or a selected part of the through holes are partially connected to the spring portion. A disc spring characterized in that it extends into a disc spring. （２）　　ばね部の内周側には、内周端から半径方向に
切込んだスロットで互に分離する複数の舌片を有してな
る特許請求の範囲第１項記載の皿ばね。(2) The disc spring according to claim 1, wherein the inner peripheral side of the spring portion has a plurality of tongue pieces separated from each other by slots cut in a radial direction from the inner peripheral end.