JPH0131805Y2 - - Google Patents
Info
- Publication number
- JPH0131805Y2 JPH0131805Y2 JP1983143604U JP14360483U JPH0131805Y2 JP H0131805 Y2 JPH0131805 Y2 JP H0131805Y2 JP 1983143604 U JP1983143604 U JP 1983143604U JP 14360483 U JP14360483 U JP 14360483U JP H0131805 Y2 JPH0131805 Y2 JP H0131805Y2
- Authority
- JP
- Japan
- Prior art keywords
- driven shaft
- ball
- driven
- shaft
- type transmission
- 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
- 230000005540 biological transmission Effects 0.000 claims description 16
- 230000000694 effects Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
Landscapes
- Friction Gearing (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Description
【考案の詳細な説明】
(産業上の利用分野)
本考案は、軸受遊星機構により、駆動軸の回転
を加速又は減速して回転軸に伝達する軸受式変速
機の出力補償装置に関するものである。[Detailed Description of the Invention] (Field of Industrial Application) The present invention relates to an output compensation device for a bearing-type transmission that uses a bearing planetary mechanism to accelerate or decelerate the rotation of a drive shaft and transmit the accelerated or decelerated rotation to the rotating shaft. .
(従来例の構成とその問題点)
従来、軸受式変速機は、例えば、外レースが固
定された玉軸受のリテーナに駆動軸を、内レース
に従動軸をそれぞれ取り付けて、駆動軸を回転さ
せると、駆動軸の回転が減速されて、従動軸に伝
達され、又、外レースが固定された玉軸受の内レ
ースに駆動軸を、リテーナに従動軸をそれぞれ取
り付けて、駆動軸を回転させると、駆動軸の回転
が加速されて、従動軸に伝達されるものであつ
た。しかし、軸受式変速機では、外レースの案内
溝とボールと、内レースの案内溝とボールとは互
いに点接触しているだけなので、、相互の接触力
が弱く、従動軸に負荷が掛かると、それぞれの接
点において滑りが生じて、駆動軸から従動軸への
回転の伝達効率が著しく低下する欠点があつた。(Conventional structure and its problems) Conventionally, in a bearing type transmission, for example, a drive shaft is attached to a ball bearing retainer to which an outer race is fixed, and a driven shaft is attached to an inner race, and the drive shaft is rotated. Then, the rotation of the drive shaft is decelerated and transmitted to the driven shaft, and when the drive shaft is attached to the inner race of a ball bearing to which the outer race is fixed, and the driven shaft is attached to the retainer, the drive shaft is rotated. , the rotation of the drive shaft was accelerated and transmitted to the driven shaft. However, in a bearing type transmission, the guide groove and ball of the outer race and the guide groove and ball of the inner race are only in point contact with each other, so the mutual contact force is weak, and when a load is applied to the driven shaft, However, there was a drawback that slippage occurred at each contact point, and the efficiency of transmitting rotation from the drive shaft to the driven shaft was significantly reduced.
(考案の目的)
本考案の目的は、従動軸に負荷が掛かると、外
レースの案内溝とボールとの接点及び内レースの
案内溝とボールとの接点における接触圧力を高く
して、従動軸に負荷が掛かつているときの駆動軸
から従動軸への回転の伝達率を向上させることに
ある。(Purpose of the invention) The purpose of the invention is to increase the contact pressure at the contact point between the guide groove of the outer race and the ball and the contact point between the guide groove of the inner race and the ball when a load is applied to the driven shaft. The objective is to improve the transmission rate of rotation from the drive shaft to the driven shaft when a load is applied to the drive shaft.
(考案の構成)
本考案は、第2の従動軸に負荷が掛かつて、第
1の従動軸と第2の従動軸との間に回転速度差が
生じると、互いに係合する第1の従動軸の突起と
第2の従動軸の突起との接触点が球面の頂点の方
向にずれて、第1の従動軸を軸受式変速機の方向
に押圧することにより、軸受式変速機の各部品間
の接触圧力を高くして、出力の低下を補償するも
のである。(Structure of the invention) In the present invention, when a load is applied to the second driven shaft and a rotational speed difference occurs between the first driven shaft and the second driven shaft, the first driven shaft engages with each other. The contact points between the protrusions on the shaft and the second driven shaft are shifted toward the apex of the spherical surface, and the first driven shaft is pushed in the direction of the bearing type transmission, whereby each part of the bearing type transmission is This is to compensate for the drop in output by increasing the contact pressure between the two.
(実施例の説明)
第1図は、本考案の一実施例の構成を示すもの
で、1は歯科用ハンドピースのシヤンク部のケー
ス、2は、シヤンク部の後端に動力部(図示しな
い)を接続したときに、動力部に内装された電動
機の回転軸(図示しない)と接続される駆動軸、
3は、ケース1の内周に固定された、内周に案内
溝4を有する外レース5と、外周に案内溝6を凹
設した回動自在の内レース7と、案内溝4と案内
溝6との間に嵌挿された複数のボール8と、これ
等のボール8の間に介装されたリテーナ9とから
なる軸受式変速機、10は駆動軸2とリテーナ9
とを接続する接続管で、この接続管10はリテー
ナ9と一体に形成されている。11は先端に接続
管10が接続された駆動軸2をケース1の中に回
動自在に軸支する球軸受、12は、先端面外側
に、中心から等距離且つ相互に等間隔になるよう
に複数の穴13が凹設され、又、先端面中心部に
バネ受穴14が凹設された第1の従動軸で、この
第1の従動軸12は内レース7に固着されてい
る。15は従動軸12の先端面から半分程度突出
するようにして、複数の穴13にそれぞれ緩挿さ
れたボール〔第1図b参照〕、16は、先端面外
側に、中心から等距離且つ相互に等間隔になるよ
うに複数の穴17が凹設され、又、先端面中心部
にバネ受穴18が凹設された第2の従動軸で、穴
17は穴13と、バネ受穴18はバネ受穴14と
それぞれ対応する位置にある。19は従動軸16
の先端面から半分程度突出するようにして、複数
の穴17にそれぞれ緩挿されたボール〔第1図b
参照〕、20は第2の従動軸16の先端に固着さ
れた歯車、、21は第2の従動軸16をケース1
の中に回動自在に軸支する玉軸受、22はバネ受
穴14とバネ受穴18との間に介装されたバネ
で、このバネ22の伸張力により、第1の従動軸
12及び第2の従動軸16は互いに相反する方向
に付勢されて、案内溝6とボール8との接触力及
び案内溝4とボール8との接触力が予め高められ
る。23はヘツド部(図示しない)の回転軸24
の後端に固着された歯車で、この歯車23は、ヘ
ツド部の後端部をシヤンク部のケース1の先端部
に接続すると、歯車20に噛合される。(Description of Embodiment) Fig. 1 shows the configuration of an embodiment of the present invention, in which 1 is a case of the shank part of a dental handpiece, 2 is a power part (not shown) at the rear end of the shank part. ) is connected to the rotating shaft (not shown) of the electric motor built into the power unit,
3 is fixed to the inner periphery of the case 1 and includes an outer race 5 having a guide groove 4 on the inner periphery, a rotatable inner race 7 having a guide groove 6 on the outer periphery, and the guide groove 4 and the guide groove. 10 is a bearing type transmission consisting of a plurality of balls 8 fitted between the drive shaft 2 and the retainer 9, and a retainer 9 interposed between the balls 8.
This connecting tube 10 is formed integrally with the retainer 9. Reference numeral 11 denotes a ball bearing for rotatably supporting the drive shaft 2, which has a connecting tube 10 connected to its tip, in the case 1. Reference numeral 12 denotes a ball bearing provided on the outside of the tip surface so as to be equidistant from the center and equidistant from each other. The first driven shaft 12 has a plurality of holes 13 recessed therein and a spring receiving hole 14 recessed in the center of its tip surface.This first driven shaft 12 is fixed to the inner race 7. Balls 15 are loosely inserted into a plurality of holes 13 so as to protrude about half from the tip surface of the driven shaft 12 (see FIG. This is a second driven shaft having a plurality of holes 17 recessed therein at equal intervals, and a spring receiving hole 18 recessed in the center of the tip surface. are located at positions corresponding to the spring receiving holes 14, respectively. 19 is the driven shaft 16
The balls are loosely inserted into each of the holes 17 so that they protrude about half from the tip surface of the ball [Fig. 1 b
], 20 is a gear fixed to the tip of the second driven shaft 16, and 21 is a gear fixed to the tip of the second driven shaft 16.
A ball bearing 22 is a spring interposed between the spring receiving hole 14 and the spring receiving hole 18, and the tension of the spring 22 causes the first driven shaft 12 and The second driven shafts 16 are biased in opposite directions to increase the contact force between the guide groove 6 and the ball 8 and the contact force between the guide groove 4 and the ball 8 in advance. 23 is a rotating shaft 24 of the head portion (not shown)
This gear 23, which is a gear fixed to the rear end, meshes with the gear 20 when the rear end of the head part is connected to the tip of the case 1 of the shank part.
このように構成された本実施例では、駆動軸2
が駆動されて、リテーナ9が回転すると、ボール
8と案内溝4との間に生じる接触力によつて、ボ
ール8が、自転ながら、案内溝4に沿つて公転す
ると共に、ボール8と案内溝6との間に生じる接
触力によつて、内レース7が回転し、第1の従動
軸12が駆動され、且つ、円周方向において互い
に係合するボールル15及びボール19を介し
て、第1の従動軸12の回転が第2の従動軸16
に伝達される。ところで、ケケース1の先端にヘ
ツド部を装着して、歯車23を歯車20に噛合さ
せ、ヘツド部に切削刃具等(図示しない)を取り
付けただけの状態、即ち、ほぼ無負荷状態で駆動
軸2を駆動しても、第1の従動軸12と第2の従
動軸16との回転速度が一致して、ボール15と
ボール19との係合位置は、駆動軸2が停止して
いるときの係合位置とほとんど変化しない。しか
しながら、切削刃具等を被切削物に接触させた状
態、即ち、負荷状態で駆動軸2を駆動すると、第
1の従動軸12は無負荷状態における回転速度を
維持しようとするが、第2の従動軸16は無負荷
状態における回転速度よりも遅くなるため、第1
の従動軸12と第2の従動軸16との間にねじれ
の力が作用して、ボール15がボール19に乗り
上げて、第1の従動軸12及び第2の従動軸16
が相反する方向に移動する。このため、案内溝6
とボール8との接触力及び案内溝4とボール8と
の接触力がそれぞれ更に高くなつて、駆動軸2か
ら第1の従動軸12への回転の伝達率が向上し、
切削抵抗による第2の従動軸16の出力が低下分
が補償される。 In this embodiment configured in this way, the drive shaft 2
is driven and the retainer 9 rotates, the contact force generated between the balls 8 and the guide groove 4 causes the balls 8 to revolve around the guide groove 4 while rotating, and the balls 8 and the guide groove 4 to rotate. 6, the inner race 7 rotates and the first driven shaft 12 is driven. The rotation of the driven shaft 12 causes the rotation of the second driven shaft 16
is transmitted to. By the way, the drive shaft 2 is in a state where the head part is attached to the tip of the case 1, the gear 23 is meshed with the gear 20, and a cutting tool etc. (not shown) is attached to the head part, that is, in an almost unloaded state. Even if the drive shaft 2 is driven, the rotational speeds of the first driven shaft 12 and the second driven shaft 16 are the same, and the engagement position of the balls 15 and 19 is the same as when the drive shaft 2 is stopped. There is almost no change from the engaged position. However, when the drive shaft 2 is driven in a state where a cutting tool or the like is in contact with the workpiece, that is, in a loaded state, the first driven shaft 12 tries to maintain the rotational speed in the no-load state, but the second Since the rotation speed of the driven shaft 16 is slower than that in the no-load state, the first
A torsional force acts between the driven shaft 12 and the second driven shaft 16, the ball 15 rides on the ball 19, and the first driven shaft 12 and the second driven shaft 16
move in opposite directions. For this reason, the guide groove 6
The contact force between the guide groove 4 and the ball 8 and the contact force between the guide groove 4 and the ball 8 are further increased, and the transmission rate of rotation from the drive shaft 2 to the first driven shaft 12 is improved.
The decrease in the output of the second driven shaft 16 due to cutting resistance is compensated for.
第2図は、本考案の他の実施例の構成を示すも
ので、第1図の符号と同一符号のものは同一部分
を示しており、又、25は第2の従動軸16に凹
設したスライダー穴、26は第2の従動軸16の
内周壁面に中心線方向に凹設した溝、27は、後
端面外側に、中心から等距離且つ相互に等間隔に
なるように複数の穴28が凹設され、又、外周壁
面に、中心線方向に溝29が凹設されたスライダ
ーで、穴28はそれぞれ穴13と対応する位置に
ある。30は溝26と溝29との間に緩挿された
ボールで、このボール30は、スライダー穴25
に移動自在に挿入されたスライダー27の移動方
向を中心線方向に規制する。31は、スライダー
27の後端面から半分程度突出するようにして、
穴28にそれぞれ緩挿されたボール、32は第2
の従動軸16とスライダー27との間に介装され
たバネで、このバネ32の伸張力により、第1の
従動軸12及び第2の従動軸16は互いに相反す
る方向に付勢されて、案内溝6とボール8との接
触力及び案内溝4とボール8との接触力が予め高
められる。 FIG. 2 shows the configuration of another embodiment of the present invention, in which the same reference numerals as those in FIG. 26 is a groove recessed in the inner peripheral wall surface of the second driven shaft 16 in the direction of the center line, and 27 is a plurality of holes formed on the outer side of the rear end surface at equal distances from the center and at equal intervals from each other. 28 is recessed and grooves 29 are recessed in the outer peripheral wall surface in the direction of the center line, and the holes 28 are located at positions corresponding to the holes 13, respectively. A ball 30 is loosely inserted between the groove 26 and the groove 29, and this ball 30 is inserted into the slider hole 25.
The moving direction of the slider 27, which is movably inserted in the slider 27, is regulated in the direction of the center line. 31 projects about half from the rear end surface of the slider 27,
The balls 32 are loosely inserted into the holes 28, respectively.
The first driven shaft 12 and the second driven shaft 16 are biased in opposite directions by the tension of the spring 32, which is interposed between the driven shaft 16 and the slider 27. The contact force between the guide groove 6 and the ball 8 and the contact force between the guide groove 4 and the ball 8 are increased in advance.
このように構成された本実施例では、駆動軸2
が駆動されて、リテーナ9が回転すると、ボール
8と案内溝4との間に生じる接触力によつて、ボ
ール8が、自転しながら、案内溝4に沿つて公転
すると共に、ボール8と案内溝6との間に生じる
接触力によつて、、内レース7が回転し、第1の
従動軸12が駆動され、且つ、円周方向において
互いに係合するボール15及びボール31を介し
て、第1の従動軸12の回転が第2の従動軸16
に伝達される。ところで、ケース1の先端にヘツ
ド部に装着して、歯車23を歯車20に噛合さ
せ、ヘツド部に切削刃具等(図示しない)を取り
付けただけの状態、即ち、ほぼ無負荷状態で駆動
軸2を駆動しても、第1の従動軸12と第2の従
動軸16との回転速度が一致して、ボール15と
ボール31との係合位置は、駆動軸2が停止して
いるときの係合位置とほとんど変化しない。しか
しながら、切削刃具等を被切削物に接触させた状
態、即ち、負荷状態で駆動軸2を駆動すると、第
1の従動軸12は無負荷状態における回転速度を
維持しようとするが、第2の従動軸16は無負荷
状態における回転速度よりも遅くなるため、第1
の従動軸12と第2の従動軸16との間にねじれ
の力が作用して、ボール15がボール31に乗り
上げて、第1の従動軸12及び第2の従動軸16
が相反する方向に移動する。このため、案内溝6
とボール8との接触力及び案内溝4とボール8と
の接触力がそれぞれ更に高くなつて、駆動軸2か
ら第1の従動軸12への回転の伝達率が向上し、
切削抵抗による第2の従動軸16の出力の低下分
が補償される。 In this embodiment configured in this way, the drive shaft 2
is driven and the retainer 9 rotates, the contact force generated between the balls 8 and the guide groove 4 causes the balls 8 to rotate and revolve along the guide groove 4, and the balls 8 and the guide groove 4 to rotate. Due to the contact force generated between the inner race 7 and the groove 6, the first driven shaft 12 is driven, and via the balls 15 and 31 that engage with each other in the circumferential direction, The rotation of the first driven shaft 12 causes the rotation of the second driven shaft 16
is transmitted to. By the way, the drive shaft 2 is installed in the head section at the tip of the case 1, the gear 23 is meshed with the gear 20, and a cutting tool etc. (not shown) is attached to the head section, that is, in an almost unloaded state. Even if the drive shaft 2 is driven, the rotational speeds of the first driven shaft 12 and the second driven shaft 16 are the same, and the engagement position of the balls 15 and 31 is the same as when the drive shaft 2 is stopped. There is almost no change from the engaged position. However, when the drive shaft 2 is driven in a state where a cutting tool or the like is in contact with the workpiece, that is, in a loaded state, the first driven shaft 12 tries to maintain the rotational speed in the no-load state, but the second Since the rotation speed of the driven shaft 16 is slower than that in the no-load state, the first
A torsional force acts between the driven shaft 12 and the second driven shaft 16, and the ball 15 rides on the ball 31, causing the first driven shaft 12 and the second driven shaft 16 to
move in opposite directions. For this reason, the guide groove 6
The contact force between the guide groove 4 and the ball 8 and the contact force between the guide groove 4 and the ball 8 are further increased, and the transmission rate of rotation from the drive shaft 2 to the first driven shaft 12 is improved.
The decrease in the output of the second driven shaft 16 due to cutting resistance is compensated for.
尚、本考案は、軸受式変速装置を具備した工具
であれば、歯科用ハンドピース以外の工具にも使
用できる。又、第1及び第2の従動軸とのそれぞ
れの対向面に突設する半球状の突起は、前述の如
く、第1及び第2のとのそれぞれの対向面に穿設
した穴にボールを挿入して形設してもよく、又、
第1及び第2の従動軸とのそれぞれの対向面に半
球状の突起を削成してもよい。 Note that the present invention can be used for tools other than dental handpieces as long as they are equipped with a bearing type transmission device. Further, as described above, the hemispherical protrusions protruding from the surfaces facing the first and second driven shafts allow the ball to be inserted into the holes drilled in the surfaces facing the first and second driven shafts, respectively. It may be inserted and shaped, or
A hemispherical protrusion may be cut on each surface facing the first and second driven shafts.
(考案の効果)
以上説明したように、本考案によれば、第1の
従動軸の端面から丸く突出した第1のボールと第
2の従動軸の端面から丸く突出した第2のボール
との係合状態が、第1及び第2の従動軸のねじれ
方向に対して非常に不安定なので、被駆動機構に
おける僅かな負荷変動でも、第1のボールの第2
のボールへの乗上げ運動が円滑に行われて、出力
補償の応答速度が速くなる。この結果、歯科治療
の等ように非常に微妙な操作を要するハンドピー
スにあつては、負荷変動による彦駆動機構の出力
変動が少なくなるので、ハンドピースの操作性が
向上して、歯科等の治療時間或いは歯科技工等の
加工時間が短くなるという効果を奏する。(Effect of the invention) As explained above, according to the invention, the first ball protruding roundly from the end face of the first driven shaft and the second ball roundly protruding from the end face of the second driven shaft. Since the engaged state is very unstable with respect to the torsional direction of the first and second driven shafts, even a slight load change in the driven mechanism causes the second ball of the first ball to
The movement of the ball to run onto the ball is performed smoothly, and the response speed of output compensation becomes faster. As a result, in the case of handpieces that require extremely delicate operations such as those used in dental treatment, the output fluctuations of the Hiko drive mechanism due to load fluctuations are reduced, improving the operability of the handpiece and improving the operability of the handpiece. This has the effect of shortening treatment time or processing time for dental technicians, etc.
又、本考案の出力補償装置は、第1の従動軸及
び第2の従動軸の対向面にそれぞれ穿設した穴
と、その穴に緩挿するボーだけの単純な構造で、
第1及び第2のボールの相互の位置調整も不要な
ので、組立が簡単で、製造原価が安くなるという
効果を奏する。 Further, the output compensation device of the present invention has a simple structure consisting of holes drilled in the opposing surfaces of the first driven shaft and the second driven shaft, respectively, and a bow that is loosely inserted into the holes.
Since there is no need to adjust the positions of the first and second balls, assembly is simple and manufacturing costs are low.
更に、本考案の出力補償装置に、一般に販売さ
れているベアリング用等のボールを第1及び第2
のボールとして使用すると、製造原価が更に安く
なるという効果がある上、表面が鏡面仕上げされ
ている第1及び第2のボール相互の運動が一層円
滑になつて、出力補償の応答速度が更に速くなる
という効果を奏する。 Furthermore, the output compensator of the present invention is provided with balls for bearings, which are generally sold, in the first and second positions.
When used as a ball, the production cost is further reduced, and the movement between the first and second balls, whose surfaces are mirror-finished, becomes smoother, resulting in faster response speed for output compensation. It has the effect of becoming.
第1図aは本考案の一実施例を具備した歯科用
ハンドピースのシヤンク部の断面図、第1図bは
本考案の一実施例の正面図、第2図は本考案の他
の実施例を具備した歯科用ハンドピースのシヤン
ク部の断面図である。
2……駆動軸、3……軸受式変速機、4,6…
…案内溝、5……外レース、7……内レース、
8,15,19,30,31……ボール、9……
リテーナ、12……第1の従動軸、13,17,
28……穴、16……第2の従動軸、22,32
……バネ、27……スライダー。
FIG. 1a is a cross-sectional view of the shank portion of a dental handpiece equipped with an embodiment of the present invention, FIG. 1b is a front view of an embodiment of the present invention, and FIG. 2 is another embodiment of the present invention. 1 is a cross-sectional view of a shank portion of a dental handpiece with an example; FIG. 2... Drive shaft, 3... Bearing type transmission, 4, 6...
...Guide groove, 5...Outer race, 7...Inner race,
8, 15, 19, 30, 31...ball, 9...
Retainer, 12...first driven shaft, 13, 17,
28... Hole, 16... Second driven shaft, 22, 32
...Spring, 27...Slider.
Claims (1)
減速して、回転軸に伝達する軸受式変速機におい
て、 一端が前記軸受式変速機に接続された第1の従
動軸と、 一端が前記回転軸を介して被駆動機構に接続さ
れた第2の従動軸と、 前記第1の従動軸の他端面に凹設された穴と、 前記第1の従動軸の他端面と対向する前記第2
の従動軸の他端面に凹設された穴と、 前記第1の従動軸の他端面から突出するように
前記第1の従動軸の穴に装着された第1のボール
と、 前記第2の従動軸の他端面から突出するように
前記第2の従動軸の穴に装着されて、前記第1の
従動軸のボールと係合する第2のボールと からなり、 前記第2の従動軸に負荷が掛かつて、前記第1
のボールが前記第2のボールの上に乗り上がる
と、前記第1の従動軸がスラスト方向に移動し
て、前記軸受式変速機の各部品間の接触圧力が高
まることにより、前記軸受式変速機における出力
の低下が補償されることを特徴とする軸受式変速
機の出力補償装置。[Claims for Utility Model Registration] In a bearing type transmission that accelerates or decelerates the rotation of a drive shaft and transmits the rotation to the rotating shaft using a bearing planetary mechanism, a first driven gear whose one end is connected to the bearing type transmission; a second driven shaft whose one end is connected to the driven mechanism via the rotating shaft; a hole formed in the other end surface of the first driven shaft; and a second driven shaft other than the first driven shaft. the second facing the end surface;
a hole recessed in the other end surface of the driven shaft; a first ball installed in the hole of the first driven shaft so as to protrude from the other end surface of the first driven shaft; a second ball that is mounted in a hole of the second driven shaft so as to protrude from the other end surface of the driven shaft and engages with a ball of the first driven shaft; When a load is applied, the first
When the ball rides on the second ball, the first driven shaft moves in the thrust direction and the contact pressure between the parts of the bearing type transmission increases, so that the bearing type transmission An output compensation device for a bearing type transmission, characterized in that a decrease in output in the machine is compensated for.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP14360483U JPS6051347U (en) | 1983-09-19 | 1983-09-19 | Output compensation device for bearing type transmission |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP14360483U JPS6051347U (en) | 1983-09-19 | 1983-09-19 | Output compensation device for bearing type transmission |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS6051347U JPS6051347U (en) | 1985-04-11 |
JPH0131805Y2 true JPH0131805Y2 (en) | 1989-09-29 |
Family
ID=30320499
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP14360483U Granted JPS6051347U (en) | 1983-09-19 | 1983-09-19 | Output compensation device for bearing type transmission |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6051347U (en) |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5629142A (en) * | 1979-08-20 | 1981-03-23 | Toshiba Corp | Measuring method of deterioration degree of ferrite heat-resisting steel |
JPS5714852A (en) * | 1980-07-02 | 1982-01-26 | Ricoh Co Ltd | Carrier for electrophotographic dry type developer |
-
1983
- 1983-09-19 JP JP14360483U patent/JPS6051347U/en active Granted
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5629142A (en) * | 1979-08-20 | 1981-03-23 | Toshiba Corp | Measuring method of deterioration degree of ferrite heat-resisting steel |
JPS5714852A (en) * | 1980-07-02 | 1982-01-26 | Ricoh Co Ltd | Carrier for electrophotographic dry type developer |
Also Published As
Publication number | Publication date |
---|---|
JPS6051347U (en) | 1985-04-11 |
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