JPS62200025A - Power transmission device - Google Patents
Power transmission deviceInfo
- Publication number
- JPS62200025A JPS62200025A JP61041044A JP4104486A JPS62200025A JP S62200025 A JPS62200025 A JP S62200025A JP 61041044 A JP61041044 A JP 61041044A JP 4104486 A JP4104486 A JP 4104486A JP S62200025 A JPS62200025 A JP S62200025A
- Authority
- JP
- Japan
- Prior art keywords
- elastic member
- power transmission
- transmission device
- elastic
- axle
- 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.)
- Pending
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 38
- 239000000463 material Substances 0.000 claims abstract description 13
- 239000000853 adhesive Substances 0.000 claims description 2
- 230000001070 adhesive effect Effects 0.000 claims description 2
- 239000007788 liquid Substances 0.000 abstract description 2
- 238000010521 absorption reaction Methods 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 5
- 230000035939 shock Effects 0.000 description 2
- FKKVFHDDYXJFFL-MOSFFKILSA-N [(7S,9E,11S,12R,13S,14R,15R,16R,17S,18S,19E,21E)-2,15,17,27,29-pentahydroxy-11-methoxy-3,7,12,14,16,18,22-heptamethyl-6,23-dioxo-26-[(E)-piperazin-1-yliminomethyl]-8,30-dioxa-24-azatetracyclo[23.3.1.14,7.05,28]triaconta-1(29),2,4,9,19,21,25,27-octaen-13-yl] acetate Chemical compound CO[C@H]1\C=C\O[C@@]2(C)Oc3c(C2=O)c2c(O)c(\C=N\N4CCNCC4)c(NC(=O)\C(C)=C\C=C\[C@H](C)[C@H](O)[C@@H](C)[C@@H](O)[C@@H](C)[C@H](OC(C)=O)[C@@H]1C)c(O)c2c(O)c3C FKKVFHDDYXJFFL-MOSFFKILSA-N 0.000 description 1
- 238000010586 diagram 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
- F16D3/76—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members shaped as an elastic ring centered on the axis, surrounding a portion of one coupling part and surrounded by a sleeve of the other coupling part
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は、動力伝達時に加わる振動術′ＲＡを緩和す
ることができる動力伝達装置多こ関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a power transmission device capable of alleviating the vibration force RA applied during power transmission.
第７図は従来の減速歯車装置付の車両駆動用動力伝達装
置の台車への取付状態を示す平面図、第８図は例えば特
開昭５２−１５４９５２号公報に示された従来の動力伝
達装置の構成を示す断面図である。図ｉｃ２いて、（１
）は車両用の台車枠、（２）はこの台車枠（１）１こ回
転自在に嵌合される車軸、（３）はこの車軸（２）の両
端部≦こ夫々固着させる車輪、（４）は軸方向が上記車
軸（２）と平行に配設される電動機、（５）はこの電動
機（４）を台車枠（１）Ｉこ緩衝支持する弾性支持装置
、（６）は上記電動機（４）と結合され、上記車軸（２
）が貫通する開口部に有する歯車箱、（７）はこの歯車
箱（６）の開口部に夫々嵌合同着される。２個の軸受。FIG. 7 is a plan view showing a state in which a conventional power transmission device for driving a vehicle with a reduction gear device is attached to a truck, and FIG. FIG. Figure ic2 and (1
) is a bogie frame for a vehicle, (2) is an axle to which this bogie frame (1) is rotatably fitted, (3) is a wheel to which both ends of this axle (2) are fixed respectively, (4) ) is an electric motor whose axial direction is arranged parallel to the axle (2), (5) is an elastic support device that cushions and supports this electric motor (4) on the bogie frame (1), and (6) is an electric motor ( 4), and the axle (2)
The gear boxes (7) each have an opening through which the gear boxes (7) are fitted and attached to the openings of the gear box (6). 2 bearings.
（９）は上記歯車箱（６）の開口部に配され、上記両軸
受（７）に支承され、上記車軸（２）に遊嵌される外筒
、（８）は上記歯車箱（６）内暑こ配され、外筒（９）
に嵌合固着される歯車であり、上記電動機（４）に取付
けられた歯車（図示せず）と噛合って、上記電動機（４
）の動力を減速して外筒（９）に伝える。（１０）は上
記外筒（９）の内周薔こ固着される肉厚ｔを有する円筒
形状の弾性部材、（１０ａ）はこの弾性部材（１０）の
側面、即ち、自由表面である。σηはこの弾性部材αＯ
の内周と車軸（２）Ｉこ夫々固着される円筒形状の内筒
である。(9) is an outer cylinder arranged at the opening of the gear box (6), supported by both the bearings (7), and loosely fitted to the axle (2); (8) is the outer cylinder of the gear box (6); It's hot inside, outside cylinder (9)
It is a gear that is fitted and fixed to the electric motor (4), and meshes with a gear (not shown) attached to the electric motor (4).
) is decelerated and transmitted to the outer cylinder (9). (10) is a cylindrical elastic member having a wall thickness t fixed to the inner periphery of the outer cylinder (9), and (10a) is a side surface, that is, a free surface, of this elastic member (10). ση is this elastic member αO
It is a cylindrical inner cylinder to which the inner periphery of the axle (2) and the axle (2) are respectively fixed.
次に動作について説明する。電動機（４）が回転すると
その回転は歯車（８）により減速され外筒（９）、弾性
部材αＱ、内筒（６）を介して、車軸（２）に固着され
る車輪（３）番こ伝えられ、台車枠（１）を走行させる
。Next, the operation will be explained. When the electric motor (4) rotates, its rotation is decelerated by the gear (8), and the wheel (3) fixed to the axle (2) is rotated through the outer cylinder (9), the elastic member αQ, and the inner cylinder (6). is transmitted, and the bogie frame (1) is made to travel.
台車枠（１）が走行中に７−ルの継き目やホイントなど
を通過すると、車輪（３）に衝撃か発生し、この衝撃が
車軸（２）に伝わるので、弾性部材αＱや弾性支持装置
＋５）ｉこより緩衝して、？！電動機４）や歯車（８）
ｉこ直接伝わらないように構成されていた。When the bogie frame (1) passes through a joint or hoint in the 7-ru while running, an impact is generated on the wheel (3), and this impact is transmitted to the axle (2), so the elastic member αQ and the elastic support Device + 5) Buffer from i? ! Electric motor 4) and gears (8)
It was structured so that it could not be directly transmitted.
上記従来例において、上記のような衝撃を伴う動力が作
用した時番こ、この衝撃を十分に緩衝するには弾性部材
αＱの持つバネ定数をこの衝撃番こ合うよう選択すれば
よい。そして、上記従来例においては、このバネ定数か
弾性部材（１０）の両側面の面積即ち自由表面（１０ａ
）槓（こより決まる。従って大きな衝撃に合ったバネ定
数を得ようとすれば、側面のｔ寸法が太き（なり、外筒
（９）を犬さくせねばならず、反対にｔ寸法がそのまま
だと大きい衝撃が緩衝できない。In the above-mentioned conventional example, when a power accompanied by an impact as described above is applied, in order to sufficiently buffer this impact, the spring constant of the elastic member αQ may be selected to match the impact. In the above conventional example, this spring constant is determined by the area of both side surfaces of the elastic member (10), that is, the free surface (10a
Therefore, in order to obtain a spring constant suitable for large shocks, the t dimension of the side surface becomes thick (and the outer cylinder (9) must be made narrower, but on the other hand, the t dimension remains the same. It cannot absorb large shocks.
従来の動力伝達装置は以上のように１弾性部材αＱの両
側面にのみ自由表面（ｔｏａ）があるｔめ、大きな衝撃
が作用した時１こ、伝達部打器の大きざを大・ きくし
なければ緩衝できないという問題点があった０
この発明は上記のような問題点を解消するためになされ
たもので、伝達部材（９）の大きさがそのま＼でも大き
い衝撃が容易に吸収できる。耐衝撃性に勝れた動力伝達
装置を提供することを目的とする。As mentioned above, conventional power transmission devices have free surfaces (TOA) only on both sides of one elastic member αQ, so when a large impact is applied, the size of the transmission part hammer must be increased. This invention has been made to solve the above-mentioned problems, and even if the size of the transmission member (9) remains unchanged, large impacts can be easily absorbed. The purpose is to provide a power transmission device with excellent impact resistance.
この発明蔽こ係る動力伝達装置は、回転軸（２）と伝達
部材（９）との間に非圧縮性材料よりなる３個所以上の
自由表面を有する弾性部材を設けたものである。The power transmission device according to the present invention is provided with an elastic member made of an incompressible material and having three or more free surfaces between the rotating shaft (2) and the transmission member (9).
この発明においては、回転軸（２）と伝達部材（９）と
の間に３個所以上の自由表面を有する弾性部材を設けた
ことにより１弾性部材の自由表面積が容易蚤こ大きくで
きる。In this invention, the free surface area of one elastic member can be easily increased by providing an elastic member having three or more free surfaces between the rotating shaft (2) and the transmission member (9).
以上、この発明による動力伝達装置を図について説明す
る。第１図はこの発明の一実施例の構成を示す断面図で
ある。図１こおいて、１２＋ 、 ＋４１ 、 （６）
ないしく９）は上記従来装置と同様のものである。（ト
）は円筒形状で、これを軸方向に分割し、この分割部に
所定の隙ｒ１５Ｗを設け、伝達部材としての外筒（９）
の内周と回転軸としての車軸（２）との間ｔ ＋ＣｔＥ
人された弾性部材であり１列んばゴム材料が使わｎる。The power transmission device according to the present invention will be described above with reference to the drawings. FIG. 1 is a sectional view showing the structure of an embodiment of the present invention. In Figure 1, 12+, +41, (6)
Items 9) to 9) are similar to the above-mentioned conventional device. (G) has a cylindrical shape, which is divided in the axial direction, and a predetermined gap r15W is provided between the divided parts, and an outer cylinder (9) is used as a transmission member.
t +CtE between the inner circumference of the wheel and the axle (2) as the rotation axis
It is a flexible elastic member and one row is made of rubber material.
また、この弾性部材（ハ）は接着剤を併用して固着する
ことにより、さらに大きな動力が伝達できる。Furthermore, by fixing this elastic member (c) together with an adhesive, even greater power can be transmitted.
（ｔＳａ）は上記弾性部材（ト）の側面であり、上記外
筒（９）の円周や車軸（２）と接触する部分を除いた自
由表面を表わす。(tSa) is the side surface of the elastic member (G), and represents the free surface excluding the circumference of the outer cylinder (9) and the portion that contacts the axle (2).
上記弾性部材（へ）ｉこ使用されるゴムは弾性を持チ、
液体と同じように非圧縮性の材料である。従ってバネ定
数は荷重を受けた特番こ変形することができる自由表面
（１５＆）積の大きざに逆比例する。今、回転軸（２）
、外筒（９）と接触する受圧面積ＡＰと自由表面積ＡＰ
の比率、ＡＦ／ＡＰ：＝αと、ゴム自身の圧縮弾性係数
ＥＦ、見掛けの弾性係数Ｅ、との関係は第９図のように
なる。よって、自由表面積ＡＦが大になると、受圧面積
ＡＰとの比率αが犬となり、圧縮弾性係数ＥＦが一定の
時に、見掛けの弾性係数ｇｐと比例するバネ定数は小さ
くなる。The rubber used in the above elastic member has elasticity,
Like liquids, they are incompressible materials. Therefore, the spring constant is inversely proportional to the size of the free surface (15&) product that can be deformed under load. Now, the rotation axis (2)
, pressure receiving area AP and free surface area AP in contact with the outer cylinder (9)
The relationship between the ratio AF/AP:=α, the compressive elastic modulus EF of the rubber itself, and the apparent elastic modulus E is shown in FIG. Therefore, when the free surface area AF becomes large, the ratio α to the pressure-receiving area AP becomes small, and when the compressive elastic coefficient EF is constant, the spring constant proportional to the apparent elastic coefficient gp becomes small.
このようにして弾性部材（至）のバネ定数を最適な値に
選ぶことができる。In this way, the spring constant of the elastic member can be selected to an optimal value.
この実施例において、動力伝達中に弾性部材（ト）の隙
間Ｗ８保てば、バネ定数ははシ一定の値をとるっまたＷ
寸法を所定の大きさの動力で隣同士か接するように取れ
ば、自由表面（１５ａ）積は接触により小さくなる。従
って、動力の大きざ番こ合わせ、バネ定数の変わる点を
自由に設定することかできる。In this embodiment, if the gap W8 between the elastic members (G) is maintained during power transmission, the spring constant will take a constant value.
If the dimensions are taken such that they are adjacent or in contact with each other with a predetermined amount of power, the free surface (15a) area becomes smaller due to the contact. Therefore, it is possible to freely set the magnitude of the power and the point at which the spring constant changes.
第２図はこの発明による他の実施例の構成を示す断面図
である。この実施例においては１弾性部凋
材（ト）か断面が丸形の円環をした複数５のリング材Ｄ
５ｆ）よりなり、このリング材（１５ｆ）を軸（２）方
向で外筒（９）と車軸（２）１こ固着される円筒状形の
内筒Ｑｌ）との間昏こ配したものである。FIG. 2 is a sectional view showing the structure of another embodiment according to the present invention. In this embodiment, one elastic member (G) or a plurality of five ring members D each having a circular cross section are used.
5f), and this ring material (15f) is interposed between the outer cylinder (9) and the cylindrical inner cylinder Ql) fixed to the axle (2) in the axis (2) direction. be.
第３図はこの発明のざらに異なる第３の実施例の構成を
示す断面図である。この実施例では外筒（９）の内周を
２段の内径を荷するものとし、異った外径を有するリン
グ材（１５ｂ） 、 Ｌ１５ｃ）よりなる弾性部材（へ
）を上記外筒（９）に固着したものであり、上記リング
材（ｒ５ｂ）、 （ｔ５ｃ）の各側面が自由表面（１５
ａ）となる。FIG. 3 is a sectional view showing the configuration of a third slightly different embodiment of the present invention. In this embodiment, the inner periphery of the outer cylinder (9) is loaded with two stages of inner diameter, and the elastic member (to) made of ring materials (15b), L15c) having different outer diameters is attached to the outer cylinder (9). 9), each side of the ring material (r5b), (t5c) is a free surface (15
a).
この実施例では、リング材（１５ｆｉ） 、 （１５ｃ
）の自由表面（１５ａ）積か大々異なっており、２植煩
のバネ定数をイすることになるため、動力伝達中の振動
による共振を押えることかできる。In this example, ring materials (15fi), (15c
) are greatly different in free surface (15a) area, and the spring constant of the two types is increased, making it possible to suppress resonance due to vibration during power transmission.
なお、この実施例では弾性部材μｓを外径の異なるもの
としたが、内径が異なるものであっても同様の効果を奏
する。In this embodiment, the elastic members μs have different outer diameters, but the same effect can be achieved even if the elastic members μs have different inner diameters.
第４図はこの発明のざらに異なる第４の実施例の構成を
示す断面図である。この実施例では１弾性部材（ト）が
内筒形状で、その内外周に沿ってリング状のｆｉ （１
５ｄ）を有するものであり、この弾性部材（ト）の各側
面と谷溝（１５ｄ）の内面とが夫々自由表面（１５ａ）
となる。FIG. 4 is a sectional view showing the configuration of a slightly different fourth embodiment of the present invention. In this embodiment, one elastic member (G) has an inner cylindrical shape, and a ring-shaped fi (1
5d), and each side surface of this elastic member (G) and the inner surface of the valley groove (15d) are respectively free surfaces (15a).
becomes.
なお、この実施例では！ （１５ｄ）をリング状とした
か、内外周の軸方向に沿った溝としても同様の効果が得
られる。In addition, in this example! The same effect can be obtained by making (15d) ring-shaped or by making grooves along the axial direction on the inner and outer peripheries.
第５図はこの発明のざらに異なる第５の実施例の構成を
示す断面図である。この実施例では、弾性部材に）か円
筒形状で内部の周方向にリング状の空洞（１５ｅ ）を
有するものであり、この弾性部材（へ）の各側面と空洞
（１５ｅ ）の内面とが夫々自由表面（ｉｓａ ）番こ
なる。FIG. 5 is a sectional view showing the configuration of a fifth embodiment of the present invention which is slightly different. In this embodiment, the elastic member (15e) has a cylindrical shape and has a ring-shaped cavity (15e) in the circumferential direction inside, and each side surface of the elastic member (15e) and the inner surface of the cavity (15e) The free surface (ISA) is in turn.
第６図はこの発明のざらに異なる第６の実施例の構成を
示す断面図である。この実施例においては、外筒（９）
か歯車箱（６）の電動機（４）側に延材し、内筒（ロ）
と弾性部材萌を上記外筒（９）の延材部に設けたもので
ある。この実施例においては１弾性部材（イ）を丸形断
面のリング材（１５ｆ）を軸方向に複数個配列したもの
で示しているがこれ以外の実施例に示した弾性部材（ト
）を用いてもよい。FIG. 6 is a sectional view showing the configuration of a slightly different sixth embodiment of the present invention. In this embodiment, the outer cylinder (9)
Extend the material to the motor (4) side of the gear box (6), and insert the inner cylinder (b).
and an elastic member is provided on the elongated portion of the outer cylinder (9). In this example, one elastic member (A) is shown as a plurality of ring members (15f) with a round cross section arranged in the axial direction, but the elastic members (G) shown in other examples may be used. It's okay.
な２．上記各実施例においては、弾性部材（ト）を円筒
形状で周がつながっているものにつき示したが、゛円周
上で分割し、これを組合せたものであってもよい。2. In each of the above embodiments, the elastic member (g) is shown as having a cylindrical shape and having a continuous circumference, but it may also be divided on the circumference and combined.
また、上記各実施例は車両用の減速歯車装置を例として
示したが、これ以外の衝撃が加わる動力伝達に利用でき
ることは言うまでもない。Moreover, although each of the above-mentioned embodiments has been shown as an example of a reduction gear device for a vehicle, it goes without saying that the present invention can be used for power transmission to which other impacts are applied.
以上のようにこの発明によれば１回転軸（２）と伝達部
材（９）との間に非圧縮性材料よりなる３個所以上の自
由表面（１５８）を有する弾性部材（ト）を設けたこと
により、伝達部材（９）の大きざがそのま＼でも。As described above, according to the present invention, an elastic member (G) having three or more free surfaces (158) made of an incompressible material is provided between the rotation shaft (2) and the transmission member (9). Therefore, even if the size of the transmission member (9) remains the same.
大きな衝撃を容易＋１吸収できるという効果がある。It has the effect of easily absorbing large impacts by +1.
第１図はこの発明の一実施例の動力伝達装置の構成を示
す断面図、第２図はこの発明の他の実施例を示す断面図
、第３因ないし＠６図はこの発明のざらに異なる＠３な
いし第６の実施例を夫々示す断面図、第７図は従来の減
速歯車装置付の車両駆動用動力伝達装置の台車への取付
状態を示す平面図、第８図は従来例の動力伝達装置の断
面図、第９図はゴムの弾性係数と表面積との関係を示す
図である。
図に３いて、（２）は車軸（回転軸） 、 （９）は外
筒（伝達部材）、αυは内筒、（ト）は弾性部材、（１
５ａ）は自由表面である。
なお、各図中同一符号は同一、または相当部分を示す。Fig. 1 is a sectional view showing the configuration of a power transmission device according to one embodiment of the present invention, Fig. 2 is a sectional view showing another embodiment of the invention, and Figs. 7 is a plan view showing how a conventional vehicle drive power transmission device with a reduction gear device is attached to a bogie, and FIG. 8 is a cross-sectional view showing different @3 to 6th embodiments, respectively. FIG. 9, a cross-sectional view of the power transmission device, is a diagram showing the relationship between the elastic modulus and surface area of rubber. In Figure 3, (2) is the axle (rotating shaft), (9) is the outer cylinder (transmission member), αυ is the inner cylinder, (g) is the elastic member, (1
5a) is the free surface. Note that the same reference numerals in each figure indicate the same or corresponding parts.
Claims (10)
回転軸との間に設けられた非圧縮性材料よりなる３個所
以上の自由表面を有する弾性部材を備え、上記回転軸と
上記伝達部材との間で動力を伝達することを特徴とする
動力伝達装置。(1) A transmission member loosely fitted to a rotating shaft, an elastic member having free surfaces at three or more locations made of an incompressible material and provided between the transmitting member and the rotating shaft; A power transmission device characterized by transmitting power between it and a transmission member.
ことを特徴とする特許請求の範囲第１項記載の動力伝達
装置。(2) The power transmission device according to claim 1, wherein the elastic member has a cylindrical shape and is divided in the axial direction.
を有することを特徴とする特許請求の範囲第２項記載の
動力伝達装置。(3) The power transmission device according to claim 2, wherein the elastic member has a gap between the divided portions even during power transmission.
特許請求の範囲第２項記載の動力伝達装置。(4) The power transmission device according to claim 2, wherein the elastic members have different outer diameters.
いずれかで、この周に沿うリング状の溝を有することを
特徴とする特許請求の範囲第１項記載の動力伝達装置。(5) The power transmission device according to claim 1, wherein the elastic member has a cylindrical shape and has a ring-shaped groove along at least one of its inner and outer circumferences.
状の空洞を有することを特徴とする特許請求の範囲第１
項記載の動力伝達装置。(6) Claim 1, characterized in that the elastic member is cylindrical and has a ring-shaped cavity in the inner circumferential direction.
The power transmission device described in section.
請求の範囲第１項記載の動力伝達装置。(7) The power transmission device according to claim 1, wherein the elastic member is press-fitted.
る特許請求の範囲第１項記載の動力伝達装置。(8) The power transmission device according to claim 1, wherein the elastic member is fixed by adhesive.
請求の範囲第１項または第２項記載の動力伝達装置。(9) The power transmission device according to claim 1 or 2, wherein the elastic member is made of a rubber material.
れることを特徴とする特許請求の範囲第１項記載の動力
伝達装置。(10) The power transmission device according to claim 1, wherein the elastic member is fixed to the shaft via a cylindrical inner cylinder.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61041044A JPS62200025A (en) | 1986-02-25 | 1986-02-25 | Power transmission device |
| GB8703843A GB2187262B (en) | 1986-02-25 | 1987-02-19 | Power transmission device |
| SE8700778A SE464988B (en) | 1986-02-25 | 1987-02-24 | POWER TRANSMISSION DEVICE INCLUDING A SPRING ELEMENT |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61041044A JPS62200025A (en) | 1986-02-25 | 1986-02-25 | Power transmission device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS62200025A true JPS62200025A (en) | 1987-09-03 |
Family
ID=12597402
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61041044A Pending JPS62200025A (en) | 1986-02-25 | 1986-02-25 | Power transmission device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS62200025A (en) |
| GB (1) | GB2187262B (en) |
| SE (1) | SE464988B (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS52154952A (en) * | 1976-06-16 | 1977-12-23 | Mitsubishi Electric Corp | Driving apparatus |
| JPS5761835A (en) * | 1980-10-01 | 1982-04-14 | Fukoku Gomme Kogyo Kk | Bushing device |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1065344A (en) * | 1963-06-21 | 1967-04-12 | Leonard Gordon Davies | Improvements in resilient couplings |
| CH444590A (en) * | 1967-02-03 | 1967-09-30 | Dreiding Andre Dr Prof | Detachable coupling |
| GB1243234A (en) * | 1968-08-06 | 1971-08-18 | Dowding & Plummer Ltd | Improvements in or relating to shaft mountings |
| GB1430863A (en) * | 1973-04-06 | 1976-04-07 | Dunlop Ltd | Couplings rotatable assembly including two vaned wheels mounted on a |
| GB2019529B (en) * | 1978-04-15 | 1982-08-25 | Dunlop Ltd | Resilient shaft couplings |
| DE3334881A1 (en) * | 1983-09-27 | 1985-04-11 | Fa. Carl Freudenberg, 6940 Weinheim | RUBBER CLUTCH |
-
1986
- 1986-02-25 JP JP61041044A patent/JPS62200025A/en active Pending
-
1987
- 1987-02-19 GB GB8703843A patent/GB2187262B/en not_active Expired - Fee Related
- 1987-02-24 SE SE8700778A patent/SE464988B/en not_active IP Right Cessation
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS52154952A (en) * | 1976-06-16 | 1977-12-23 | Mitsubishi Electric Corp | Driving apparatus |
| JPS5761835A (en) * | 1980-10-01 | 1982-04-14 | Fukoku Gomme Kogyo Kk | Bushing device |
Also Published As
| Publication number | Publication date |
|---|---|
| SE8700778L (en) | 1987-08-26 |
| GB8703843D0 (en) | 1987-03-25 |
| GB2187262B (en) | 1990-01-04 |
| GB2187262A (en) | 1987-09-03 |
| SE8700778D0 (en) | 1987-02-24 |
| SE464988B (en) | 1991-07-08 |
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