JPS60157515A - Shock-absorbing device of power transmission mechanism - Google Patents
Shock-absorbing device of power transmission mechanismInfo
- Publication number
- JPS60157515A JPS60157515A JP1412184A JP1412184A JPS60157515A JP S60157515 A JPS60157515 A JP S60157515A JP 1412184 A JP1412184 A JP 1412184A JP 1412184 A JP1412184 A JP 1412184A JP S60157515 A JPS60157515 A JP S60157515A
- Authority
- JP
- Japan
- Prior art keywords
- damper
- drive shaft
- transmission mechanism
- power transmission
- friction
- 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.)
- Granted
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
- F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
- F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
- F16D7/024—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces
- F16D7/025—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces with flat clutching surfaces, e.g. discs
- F16D7/027—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces with flat clutching surfaces, e.g. discs with multiple lamellae
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は主としてエンジンの動力伝達機構の緩衝装置に
関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention mainly relates to a shock absorber for a power transmission mechanism of an engine.
（従来技術）
トルク変動や衝撃を緩衝するだめの緩衝装置として、カ
ムダンパーやゴム等の弾性体ダンパーのみを備えたもの
は従来より知られている。ところが第１図に示すように
従来の緩衝装置は、ギヤ１．２等の伝達機構よりも被駆
動軸３側にダンパー４を配置し、トルク変動や衝撃等を
緩衝するようにしている。そのために歯車１．２には駆
動軸５の変動そのものが伝わり、ギヤ１．２の騒音低減
効果は小さい。(Prior Art) As a shock absorber for buffering torque fluctuations and shocks, a shock absorber equipped only with a cam damper or an elastic damper such as rubber is conventionally known. However, as shown in FIG. 1, in the conventional shock absorber, a damper 4 is arranged closer to the driven shaft 3 than the transmission mechanism such as the gears 1, 2, etc., so as to buffer torque fluctuations, shocks, and the like. Therefore, the fluctuation of the drive shaft 5 itself is transmitted to the gear 1.2, and the noise reduction effect of the gear 1.2 is small.
（発明の目的）
ギヤ等の騒音を大幅に低減すると共に、トルク変動等の
緩衝効果を大幅に向上させることを目的としている。(Objective of the invention) It is an object of the present invention to significantly reduce noise from gears, etc., and to significantly improve the buffering effect against torque fluctuations, etc.
（発明の構成）
本発明の原理図を示す第２図において、回転駆動軸１１
と回転被駆動軸１２とをギヤ式あるいは索条体巻掛式の
動力伝達機構１３により連動連結し、動力伝達機構１３
よりも駆動軸１１側にカムダンパー１４あるいはゴム等
の弾性体ダンパーを設けると共に摩擦ダンパー１５を設
けている。(Structure of the Invention) In FIG. 2 showing the principle diagram of the present invention, a rotary drive shaft 11
and the rotary driven shaft 12 are interlocked and connected by a gear-type or cable-wrapping type power transmission mechanism 13, and the power transmission mechanism 13
A cam damper 14 or an elastic damper such as rubber is provided on the drive shaft 11 side, and a friction damper 15 is also provided.
（第１実施例）
第３図は２気筒２クランク軸エンジンの縦断面略図であ
り、各シリンダ１６毎に駆動軸（クランク軸） １１を
備え、両部動軸ｌｌを互いに平行に配置している。両部
動軸１１はそれぞれ駆動ギヤ（りランクギヤ）１８を備
え、両駆動ギヤ１８は被駆動軸（クラッチ軸） ２０の
被駆動軸ギヤ（クラッチギヤ）２１に噛み合っている。(First Embodiment) FIG. 3 is a schematic vertical cross-sectional view of a two-cylinder, two-crankshaft engine, in which each cylinder 16 is provided with a drive shaft (crankshaft) 11, and both drive shafts are arranged parallel to each other. There is. Both driving shafts 11 each include a driving gear (rank gear) 18, and both driving gears 18 mesh with a driven shaft gear (clutch gear) 21 of a driven shaft (clutch shaft) 20.
被駆動ギヤ２１はクラッチを介して被駆動軸２０に連結
し、駆動ギヤ１８は本発明に係る緩衝装置を介して駆動
軸１１に連結している。The driven gear 21 is connected to the driven shaft 20 via a clutch, and the drive gear 18 is connected to the drive shaft 11 via a shock absorber according to the present invention.
第３図のＩＶ−ＩＶ断面拡大図を示す第４図において、
駆動ギヤ１８の内周面には筒体２４が溶着され筒体２４
は駆動軸１１の外周面に回動可能に嵌合している。駆動
ギヤ１８はカムダンパー１４及び摩擦ダンパー１５を介
して駆動軸１１に連動連結している。In FIG. 4 showing an enlarged cross-sectional view of IV-IV in FIG. 3,
A cylindrical body 24 is welded to the inner peripheral surface of the drive gear 18.
is rotatably fitted to the outer peripheral surface of the drive shaft 11. The drive gear 18 is operatively connected to the drive shaft 11 via the cam damper 14 and the friction damper 15.
カムダンパー１４はフォロワー（カム）２６とカムフェ
イス２７により構成されており、半円状のフォロワー２
６は支持リング２８に一体に形成されると共に駆動軸１
１の外周スプライン歯２９に軸方内方移動可能にスプラ
イン嵌合している。カムフェイス２７は前記筒体２４に
凹面状に形成されている。フォロワー２６はコイルスプ
リング３００弾性力化よりカムフェイス２７に当接して
いる。The cam damper 14 is composed of a follower (cam) 26 and a cam face 27, and has a semicircular follower 2.
6 is integrally formed with the support ring 28 and is connected to the drive shaft 1.
It is spline-fitted to the outer peripheral spline teeth 29 of No. 1 so as to be movable inward in the axial direction. The cam face 27 is formed in the cylinder body 24 in a concave shape. The follower 26 is in contact with the cam face 27 due to the elasticity of the coil spring 300.
摩擦ダンパー１５は、複数枚の第１環状プレート３１と
、複数枚の第２環状プレート３２と、複数枚の環状摩擦
材３３により構成されている。第１環状プレー）３１は
駆動軸１１の外周スプライン歯２９に軸方向移動可能に
スプライン嵌合し、第２環状グレート３２は駆動ギヤ１
８の内周スプライン歯３４に軸方向移動自在に嵌合して
おり、第１環、状プレート３１に上記摩擦材３３が溶着
されている。The friction damper 15 includes a plurality of first annular plates 31, a plurality of second annular plates 32, and a plurality of annular friction members 33. The first annular plate 31 is spline-fitted to the outer peripheral spline teeth 29 of the drive shaft 11 so as to be movable in the axial direction, and the second annular plate 32 is spline-fitted to the outer peripheral spline teeth 29 of the drive shaft 11.
The friction material 33 is fitted onto the inner peripheral spline teeth 34 of No. 8 so as to be movable in the axial direction, and the friction material 33 is welded to the first ring-shaped plate 31.
開環状プレー）３１．３２は前記コイルスプリン・グ３
０の弾性力により摩擦材３３を介して互いに圧接してい
る。Open ring play) 31.32 is the coil spring ring 3.
They are pressed against each other via the friction material 33 by an elastic force of 0.
なおコイルスプリング３０は矢印Ｆ側の第２環状プレー
ト３２と環状ばね押え３５の間に縮設されている。また
逆矢印Ｆ側端の第１環状プレート３１は摩擦材３６を介
して支持リング２８に当接している。３８はストッパリ
ングである。The coil spring 30 is compressed between the second annular plate 32 on the arrow F side and the annular spring retainer 35. Further, the first annular plate 31 at the end on the side of the reverse arrow F is in contact with the support ring 28 via a friction material 36. 38 is a stopper ring.
（作用）
駆動軸１１の回転はカムダンパー１４及び摩擦ダンパー
１５を介して駆動ギヤ１８に伝達され、被駆動ギヤ２１
及びクラッチを介して被駆動２０に伝達される。(Function) The rotation of the drive shaft 11 is transmitted to the drive gear 18 via the cam damper 14 and the friction damper 15, and the rotation of the drive shaft 11 is transmitted to the drive gear 18
and is transmitted to the driven 20 via the clutch.
駆動軸１１のトルク変動及び衝撃等は、スプリング３０
の弾性力に抗してフォロワー２６がカムフェイス２７を
摺接移動するカムダンパー作用と、第１環状プレー１−
３１及び摩擦材３３が第２環状プレート３２に対して回
転方向にねじれる摩擦ダンｔ＜ −ｆｇ用により、吸収
される。カムダンパー１４４こよってはトルク変動等を
吸収し、放出し、摩擦ダンパー１５によってはトルク変
動のエネルギーを熱に変換し、発散させる。Torque fluctuations and impacts of the drive shaft 11 are handled by the spring 30.
The cam damper action in which the follower 26 slides against the cam face 27 against the elastic force of the first annular play 1-
31 and the friction material 33 are twisted in the rotational direction with respect to the second annular plate 32 by the friction damper t<-fg. The cam damper 144 absorbs and releases torque fluctuations, and the friction damper 15 converts the energy of torque fluctuations into heat and releases it.
第９図は摩擦ダンパー１５による荷重変位曲線を示して
おり、横軸の変位θは第２環状プレート３２に対する第
１環状プレート３１の回転方向へのねじり角度であり、
縦軸の荷重Ｔは駆動軸ｉｉ（第１環状）゛レート３１）
のねじりトルクである。 比Ｔは摩擦ダンパー１４によ
るヒステリシストルクである。FIG. 9 shows a load displacement curve due to the friction damper 15, where the displacement θ on the horizontal axis is the twist angle in the rotational direction of the first annular plate 31 with respect to the second annular plate 32.
The load T on the vertical axis is the drive shaft ii (first annular) rate 31)
is the torsional torque of The ratio T is the hysteresis torque caused by the friction damper 14.
（第２実施例） 第５図に示すように摩擦ダンパー１５として。(Second example) As a friction damper 15 as shown in FIG.
テーパー摩擦面４０ａを有する環状部材４０と、テーパ
ー摩擦面４１ａ及び外周摩擦面４１ｂを有する３つ割状
摩擦部材４１ （第６図）とを備えている。It includes an annular member 40 having a tapered friction surface 40a, and a three-part friction member 41 (FIG. 6) having a tapered friction surface 41a and an outer peripheral friction surface 41b.
３つ割状摩擦部材４１はスゲリング３ｏにより逆矢印Ｆ
方向へ付勢されており、それによりテーパー摩擦面４１
ａが環状部材４ｏのテーパー摩擦面ａに圧接すると共に
、両摩擦面４Ｑａ、４１ａ間のカム作用により各摩擦部
材４１が半径方向外方へ拡開し、外周摩擦面４１ｔ）が
駆動ギヤ１８の内周面１８ａに圧接している。摩擦部材
４１としては焼結合金等を用いるが、摩擦面４１ａ 、
４１１）に摩擦材を接着するようにしてもよい。The three-part friction member 41 is moved by the reverse arrow F due to the suge ring 3o.
direction, thereby causing the tapered friction surface 41
a comes into pressure contact with the tapered friction surface a of the annular member 4o, and each friction member 41 expands radially outward due to the cam action between the two friction surfaces 4Qa and 41a, so that the outer peripheral friction surface 41t) of the drive gear 18 It is in pressure contact with the inner circumferential surface 18a. A sintered alloy or the like is used as the friction member 41, and the friction surface 41a,
411) may be bonded with a friction material.
第５図の緩衝装置は上記のような摩擦ダンパー１５と第
４図と同様のカムダンパー１４とを組み合わせたもので
ある。なお第５図において第４図に対応する部品には第
４図と同じ番号を付している。The shock absorber shown in FIG. 5 is a combination of a friction damper 15 as described above and a cam damper 14 similar to that shown in FIG. In FIG. 5, parts corresponding to those in FIG. 4 are given the same numbers as in FIG. 4.
（第３実施例）
第７、第８図に示すように、緩衝装置としてゴムダンパ
ー４２と摩擦ダンパー１５を組み合わせている。(Third Embodiment) As shown in FIGS. 7 and 8, a rubber damper 42 and a friction damper 15 are combined as a shock absorbing device.
即ち第８図において、駆動軸１１の外周スプライン歯２
９には筒体４３が軸方向移動可能に嵌合しており、筒体
４３には円周方向に等間隔を隔てて３本の外向き突起４
４が形成されている。−刃駆動ギャ１８の内周面には円
周方向に等間隔を隔てて３木の内向き突起４５が形成さ
れており、該内向き突起４５と前記外向き突起４４の間
にそれぞれゴムダンパー４２が配置されている。That is, in FIG. 8, the outer peripheral spline teeth 2 of the drive shaft 11
A cylindrical body 43 is fitted into the cylindrical body 9 so as to be movable in the axial direction.
4 is formed. - Three inward protrusions 45 are formed on the inner peripheral surface of the blade drive gear 18 at equal intervals in the circumferential direction, and a rubber damper is provided between the inward protrusions 45 and the outward protrusions 44, respectively. 42 are arranged.
また第７図において、筒体４３の矢印Ｆ側の端部には摩
擦フランジ部４６が形成されており、該フランジ部４６
はスプリング３０により逆矢印Ｆ側へ付勢され、逆矢印
Ｆ側の摩擦面４６ａが内向き突起４５の矢印Ｆ側の摩擦
面４５ａに圧接している。Further, in FIG. 7, a friction flange portion 46 is formed at the end of the cylinder 43 on the arrow F side.
is urged toward the reverse arrow F side by the spring 30, and the friction surface 46a on the reverse arrow F side is in pressure contact with the friction surface 45a of the inward protrusion 45 on the arrow F side.
即ち摩擦面４６ａを有するフランジ部４６と、摩擦面４
５ａを有する内向き突起４５により摩擦ダンパー１５を
構成している。That is, the flange portion 46 having the friction surface 46a and the friction surface 4
The friction damper 15 is constituted by the inward protrusion 45 having the shape 5a.
なお第７、第８図において第４図に対応する部品には第
４図と同じ番号を付している。In FIGS. 7 and 8, parts corresponding to those in FIG. 4 are given the same numbers as in FIG. 4.
（その他の実施例）
（１） 弾性体ダンパーとして、ゴムの代りにスプリン
グを用いる。例えば第８図の両突起４４．４５間にコイ
ルスプリングを縮設する。(Other Examples) (1) A spring is used instead of rubber as the elastic damper. For example, a coil spring is compressed between both protrusions 44 and 45 in FIG.
（２） 自動車の後車軸（被駆動軸）とドライブシャフ
ト（駆動軸）の間の緩衝装置として用いる。(2) Used as a shock absorber between the rear axle (driven shaft) and drive shaft (drive shaft) of an automobile.
（３） チェノ及びスプロケット等よりなるチェノ式伝
達機構や、ベルト及びプーリ等よりなるべｐト式伝達機
構のような索条体巻掛式動力伝達機構に本発明を適用す
る。(3) The present invention is applied to a cable-wrapping type power transmission mechanism such as a chain type transmission mechanism consisting of a chain wheel, a sprocket, etc., and a belt type transmission mechanism consisting of a belt, a pulley, etc.
（発明の効果）
＋１１ ２ａｌｌのダンパー、即ちカムダンパーあるい
はゴム等の弾性体ダンパーと摩擦ダンパーとを備えてい
るので、駆動軸のトルク変動や衝撃を緩衝する効果が大
きい。(Effects of the Invention) Since the present invention includes +11 2 all dampers, that is, a cam damper or an elastic damper such as rubber, and a friction damper, it is highly effective in damping torque fluctuations and impacts of the drive shaft.
即ちトルク変動等を熱に変換して消滅させる摩擦ダンパ
ーと、トルク変動等を蓄積する弾性体ダンパー等を兼ね
備えているので、トルク変動等の緩衝効果が大きい。That is, since it has both a friction damper that converts torque fluctuations, etc. into heat and eliminates them, and an elastic damper, etc. that accumulates torque fluctuations, etc., it has a large buffering effect against torque fluctuations, etc.
（２） 動力伝達機構よりも駆動軸側に両ダンパーを備
えているので、ギヤ、チェノあるいはベルト等の伝達要
素には駆動軸のトルク変動は伝わらない。(2) Since both dampers are provided closer to the drive shaft than the power transmission mechanism, torque fluctuations of the drive shaft are not transmitted to transmission elements such as gears, chains, or belts.
それによりトルク変動あるいは衝撃等によるギヤ等の損
傷を防止でき、また動力伝達に伴う騒音の低減も達成で
きる。This can prevent damage to gears and the like due to torque fluctuations or impacts, and can also reduce noise associated with power transmission.
第１図は従来例の原理を説明する模式図、第２図は本発
明の詳細な説明する模式図、第３図は本発明を適用する
２気筒２クランク軸エンジンの縦断面略図、第４図は第
３図のＩＶ−ＩＶ断面拡大図、第５図は別の実施例の断
面拡大図（第６図の■−■断面図）、第６図は第５図の
ＶＩ−ＶＩ断面図、第７図はさらに別の実施例の断面拡
大図（第８図の■−■断面図）、第８図は第７図の■−
■断面図、第９図は荷重変位曲線である。１１・・・駆
動軸、１２・・・被駆動軸、１３・・・動力伝達機構、
１４・・・カムダンパー、１５・・・摩擦ダンパー、４
２−・・ゴムダンパー（弾性体ダンパー）
特許出願人 川崎重工業株式会社FIG. 1 is a schematic diagram explaining the principle of a conventional example, FIG. 2 is a schematic diagram explaining the present invention in detail, FIG. The figure is an enlarged sectional view of IV-IV in Fig. 3, Fig. 5 is an enlarged sectional view of another embodiment (■-■ sectional view of Fig. 6), and Fig. 6 is a VI-VI sectional view of Fig. 5. , FIG. 7 is an enlarged cross-sectional view of another embodiment (cross-sectional view taken along ■-■ in FIG. 8), and FIG. 8 is a cross-sectional view taken along ■-■ in FIG.
■The cross-sectional view and FIG. 9 are load displacement curves. 11... Drive shaft, 12... Driven shaft, 13... Power transmission mechanism,
14... Cam damper, 15... Friction damper, 4
2-...Rubber damper (elastic damper) Patent applicant Kawasaki Heavy Industries, Ltd.
Claims (1)
掛式の動力伝達機構により連動連結し、動力伝達機構よ
りも駆動軸側に、カムダンパーあるいはゴム等の弾性体
ダンパーを設けると共に摩擦ダンパーを設けたことを特
徴とする動力伝達機構の緩衝装置。The rotary drive shaft and the rotary driven shaft are interlocked and connected by a gear type or cable wrapping type power transmission mechanism, and a cam damper or an elastic damper such as rubber is provided on the drive shaft side from the power transmission mechanism. A shock absorber for a power transmission mechanism characterized by being provided with a friction damper.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1412184A JPS60157515A (en) | 1984-01-27 | 1984-01-27 | Shock-absorbing device of power transmission mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1412184A JPS60157515A (en) | 1984-01-27 | 1984-01-27 | Shock-absorbing device of power transmission mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60157515A true JPS60157515A (en) | 1985-08-17 |
| JPH0364731B2 JPH0364731B2 (en) | 1991-10-08 |
Family
ID=11852284
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1412184A Granted JPS60157515A (en) | 1984-01-27 | 1984-01-27 | Shock-absorbing device of power transmission mechanism |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60157515A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001301630A (en) * | 2000-04-25 | 2001-10-31 | Showa Corp | Electric power steering device |
| EP1793143A1 (en) * | 2005-12-01 | 2007-06-06 | Bonfiglioli Riduttori S.p.A. | Worm/Crown-wheel-assembly gear reducer comprising a torque limiter |
| EP3181933A4 (en) * | 2014-08-12 | 2018-04-25 | Kabushiki Kaisha F.C.C. | Power transmission device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS52124561A (en) * | 1976-04-12 | 1977-10-19 | Yanmar Agricult Equip | Shock absorption type transmission clutch |
| JPS55119246A (en) * | 1979-03-08 | 1980-09-12 | Honda Motor Co Ltd | Friction damper for transmission system |
-
1984
- 1984-01-27 JP JP1412184A patent/JPS60157515A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS52124561A (en) * | 1976-04-12 | 1977-10-19 | Yanmar Agricult Equip | Shock absorption type transmission clutch |
| JPS55119246A (en) * | 1979-03-08 | 1980-09-12 | Honda Motor Co Ltd | Friction damper for transmission system |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001301630A (en) * | 2000-04-25 | 2001-10-31 | Showa Corp | Electric power steering device |
| EP1793143A1 (en) * | 2005-12-01 | 2007-06-06 | Bonfiglioli Riduttori S.p.A. | Worm/Crown-wheel-assembly gear reducer comprising a torque limiter |
| EP3181933A4 (en) * | 2014-08-12 | 2018-04-25 | Kabushiki Kaisha F.C.C. | Power transmission device |
| US10247260B2 (en) | 2014-08-12 | 2019-04-02 | Kabushiki Kaisha F.C.C. | Power transmitting apparatus |
| EP3617541A1 (en) * | 2014-08-12 | 2020-03-04 | Kabushiki Kaisha F.C.C. | Power transmitting apparatus |
| US10670087B2 (en) | 2014-08-12 | 2020-06-02 | Kabushiki Kaisha F.C.C. | Power transmitting apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0364731B2 (en) | 1991-10-08 |
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