JPH08105437A - Vibration reducing swing bearing - Google Patents
Vibration reducing swing bearingInfo
- Publication number
- JPH08105437A JPH08105437A JP6264365A JP26436594A JPH08105437A JP H08105437 A JPH08105437 A JP H08105437A JP 6264365 A JP6264365 A JP 6264365A JP 26436594 A JP26436594 A JP 26436594A JP H08105437 A JPH08105437 A JP H08105437A
- Authority
- JP
- Japan
- Prior art keywords
- outer ring
- rolling element
- inner ring
- ring
- groove
- 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.)
- Withdrawn
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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/56—Systems consisting of a plurality of bearings with rolling friction in which the rolling bodies of one bearing differ in diameter from those of another
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
- F16C19/166—Four-point-contact ball bearings
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
- F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/10—Application independent of particular apparatuses related to size
- F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Component Parts Of Construction Machinery (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、旋回機能を有する例
えば油圧ショベルのような車輌、機械等に使用される旋
回軸受に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a slewing bearing having a slewing function, which is used in vehicles such as hydraulic excavators, machines and the like.
【０００２】[0002]
【従来の技術】油圧ショベルなどの建設機械では上部旋
回体が下部走行体に対して旋回自在となっているが、こ
のような建設機械ではその旋回機構として旋回軸受が適
用されている。2. Description of the Related Art In a construction machine such as a hydraulic excavator, an upper revolving structure is capable of revolving with respect to a lower traveling structure. In such a construction machine, a revolving bearing is applied as its revolving mechanism.
【０００３】従来このような旋回軸受として、図３及び
図４に示すように、上部旋回体５のスウィングフレーム
50に固定される外輪１の内周面と、その外輪１と同心上
であって下部走行体６のベースフレーム60に固定される
内輪２の外周面との間に複数の転動体用溝３が形成さ
れ、その溝３に転動体である鋼球30が介挿される構造の
ものが汎用されている。As a conventional swing bearing, as shown in FIGS. 3 and 4, a swing frame of an upper swing body 5 is used.
A plurality of rolling element grooves 3 are provided between the inner peripheral surface of the outer ring 1 fixed to the outer ring 50 and the outer peripheral surface of the inner ring 2 concentric with the outer ring 1 and fixed to the base frame 60 of the lower traveling body 6. In general, a steel ball 30 as a rolling element is formed in the groove 3 and is inserted into the groove 3.
【０００４】一方このような従来構造では、外輪１と外
輪２とが撓む際に鋼球30との間に部分的な摩耗が生じて
しまうという問題があったため、本発明者らはこれを防
ぐために、図５に示すような旋回軸受を実開平３−８９
２１６号において提案している。すなわち、この旋回軸
受は、外輪１の一端面（同図では下端面10）に対向する
ように、内輪２の一端面（同図では下端面20）側に半径
方向対向側に突出する円板部21を設け、この円板部21と
外輪一端面10との間に溝４を形成して、その溝４に第２
転動体である鋼球40が介挿される構造となっており、こ
の第２転動体介挿部により外輪１と内輪２とが撓むこと
を未然に防止するものである。On the other hand, in the conventional structure as described above, there is a problem that partial wear occurs between the outer ring 1 and the outer ring 2 when the outer ring 1 and the outer ring 2 are bent. In order to prevent this, install a slewing bearing as shown in FIG.
Proposed in No. 216. That is, this slewing bearing is a disc that protrudes radially opposite to one end surface (lower end surface 20 in the figure) of the inner ring 2 so as to face one end surface (lower end surface 10 in the figure) of the outer ring 1. A portion 21 is provided, and a groove 4 is formed between the disc portion 21 and the one end surface 10 of the outer ring.
The structure is such that the steel balls 40, which are rolling elements, are inserted, and the second rolling element insertion portion prevents the outer ring 1 and the inner ring 2 from being bent.
【０００５】[0005]
【発明が解決しようとする課題】ところで、上記のよう
な旋回軸受では、転動体である鋼球30と外輪１及び内輪
２との間に間隙が形成されているため、機械部作業時、
車輌走行時や上部旋回体の旋回時の際に生じる機体の振
動により、その振幅が増大するという問題がある。By the way, in the slewing bearing as described above, a gap is formed between the steel ball 30 as the rolling element and the outer ring 1 and the inner ring 2, so that when the mechanical part is operated,
There is a problem in that the amplitude of the vehicle body increases due to vibration of the vehicle body that occurs when the vehicle is traveling or when the upper swing body is turning.
【０００６】これに対し、本発明者らの提案した上記実
開平３−８９２１６号では、外輪１と内輪２との、転動
体を介した連絡箇所が第１転動体介挿部以外に第２転動
体介挿部もあるため、機体振動による振幅は上記従来構
造よりは緩和されるものの、第２転動体介挿部にも転動
体（鋼球40）との間に間隙が形成されるため、満足ので
きる効果的な振動減少は得られるものとはなっていな
い。On the other hand, in the above-mentioned Japanese Utility Model Laid-Open No. 3-89216 proposed by the present inventors, the outer ring 1 and the inner ring 2 are connected to each other via the rolling element at the second position other than the first rolling element interposition part. Since there is also a rolling element insertion part, the amplitude due to machine body vibration is relaxed compared to the above conventional structure, but a gap is formed between the second rolling element insertion part and the rolling element (steel ball 40). However, a satisfactory and effective vibration reduction is not obtained.
【０００７】この発明は、以上のような問題に鑑み創案
されたもので、転動体と内輪及び外輪との間隙による振
動の振幅の増大を抑制し、より効果的な振動低減が図れ
る旋回軸受を提供しようとするものである。The present invention was devised in view of the above problems, and provides a slewing bearing that suppresses an increase in vibration amplitude due to a gap between a rolling element and an inner ring or an outer ring, and can reduce vibration more effectively. It is the one we are trying to provide.
【０００８】[0008]
【課題を解決するための手段】このため、本発明に係る
振動低減用旋回軸受は、外輪の内周面と、その外輪と同
心上に配置される内輪の外周面とに形成される溝に第１
転動体が介挿され、かつ前記内輪又は外輪の一端面側に
その半径方向対向側に突出して形成される円板部と、該
円板部に対向する前記外輪又は内輪の一端面とに形成さ
れる溝に第２転動体が介挿される旋回軸受であって、前
記第２転動体の介挿用溝を形成する前記内輪又は外輪の
円板部と、前記外輪又は内輪の一端面とのいずれか一方
又は両方に、前記第２転動体が当接するように緩衝部材
を配置したことを特徴とする。Therefore, the vibration reducing slewing bearing according to the present invention has a groove formed in the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring concentric with the outer ring. First
A disc portion in which a rolling element is inserted and which is formed on one end surface side of the inner ring or the outer ring so as to project to the radially opposite side, and is formed on one end surface of the outer ring or the inner ring facing the disc portion. Of the inner ring or the outer ring forming the groove for inserting the second rolling element, and the one end surface of the outer ring or the inner ring. It is characterized in that a cushioning member is arranged so that the second rolling element abuts on either or both of them.
【０００９】ここで、前記円板部は外輪と内輪のいずれ
かに形成されるが、それは半径方向対向側に突出するも
のであり、したがって外輪に形成される場合であれば内
輪方向側に、内輪に形成される場合であれば外輪方向側
にそれぞれ突出することになる。Here, the disk portion is formed on either the outer ring or the inner ring, but it is projected on the radially opposite side. Therefore, when it is formed on the outer ring, it is formed on the inner ring direction side. If it is formed on the inner ring, it will project to the outer ring direction side.
【００１０】[0010]
【作用】本発明では、実開平３−８９２１６号の場合と
同様、外輪と内輪との、転動体を介した連絡箇所が第１
転動体介挿部以外に第２転動体介挿部もあるため、その
介挿部の分だけ、機体振動による振幅が緩和されるが、
それにも増して第２転動体介挿部の介挿用溝を形成する
前記外輪又は内輪の円板部と、前記内輪又は外輪の一端
面とのいずれか一方又は両方に緩衝部材が配置され、し
かも第２転動体と間隙のないように当接して配置されて
いる。このため、機体振動は第２転動体に当接する緩衝
部材に吸収されることになる。すなわち、転動体と外輪
及び内輪との間隙が存在することにより不可避的に生じ
ていた機体振動の振幅増加は、第２転動体介装部の緩衝
部材の配置構造により、より効果的に減衰されることに
なる。In the present invention, as in the case of Japanese Utility Model Laid-Open No. 3-89216, the outer ring and the inner ring have the first connecting point via the rolling element.
Since there is a second rolling element interposing portion in addition to the rolling element interposing portion, the amplitude due to the machine body vibration is reduced by the amount of the interposing portion,
Further, a cushioning member is arranged on either or both of the outer ring or the disc part of the inner ring forming the insertion groove of the second rolling element insertion part and one end surface of the inner ring or the outer ring, Moreover, they are arranged in contact with the second rolling element so that there is no gap. For this reason, the machine body vibration is absorbed by the cushioning member that is in contact with the second rolling element. That is, the increase in the amplitude of the machine body vibration, which is unavoidably caused by the existence of the gaps between the rolling elements and the outer ring and the inner ring, is more effectively damped by the arrangement structure of the cushioning member of the second rolling element interposing section. Will be.
【００１１】[0011]
【実施例】本発明の具体的実施例を図面に基づき説明す
る。なお、以下に示す実施例は本発明の一例であり、本
発明の構成の範囲内であれば他の種々の具体的態様がと
りうることはいうまでもない。Embodiments of the present invention will be described with reference to the drawings. In addition, it is needless to say that the following examples are examples of the present invention, and various other specific modes can be adopted within the scope of the configuration of the present invention.
【００１２】図１は本発明に係る旋回軸受の要部を示す
断面図であり、図中は１は外輪、２は内輪、３は第１転
動体介挿用溝、４は第２転動体介挿用溝を各示す。FIG. 1 is a sectional view showing an essential part of a slewing bearing according to the present invention. In the figure, 1 is an outer ring, 2 is an inner ring, 3 is a groove for inserting a first rolling element, and 4 is a second rolling element. Each of the insertion grooves is shown.
【００１３】外輪１は、上部旋回体のスウィングフレー
ム50に固定される。外輪１の内周面には、断面略円弧状
の第１転動体介挿用溝３aがその全周に亘って形成され
るとともに、その下端面10には、その周方向に等間隔で
第２転動体介挿用溝４aが形成される。The outer ring 1 is fixed to a swing frame 50 of the upper swing body. A first rolling element inserting groove 3a having a substantially arcuate cross section is formed over the entire circumference on the inner peripheral surface of the outer ring 1, and the lower end surface 10 of the first rolling element inserting groove 3a is formed at equal intervals in the circumferential direction. Two rolling element insertion grooves 4a are formed.
【００１４】内輪２は、下部走行体のベースフレーム60
に固定され、前記外輪１と所定間隙を有しつつそれと同
心上に配置される。そして、内輪２の外周面には前記外
輪１の第１転動体介挿用溝３aに対応する位置に同様の
断面略円弧状の溝３bが形成される。すなわち、前記外
輪１の溝３aと内輪２の溝３bとで球状の溝が形成され、
そこに第１転動体である鋼球30が介挿される。また、内
輪２の下端面20側の外周部分には、半径方向対向側に突
出する円板部21が全周に亘って形成されている。円板部
21の上端面は所定間隙を有しつつ前記外輪１の下端面10
と対向するとともに、前記溝４aに対応する位置に同様
の溝４bがその全周に亘って形成される。The inner ring 2 is a base frame 60 of the lower traveling body.
Is fixed to the outer ring 1 and is arranged concentrically with the outer ring 1 with a predetermined gap. A groove 3b having a substantially arcuate cross section is formed on the outer peripheral surface of the inner ring 2 at a position corresponding to the first rolling element insertion groove 3a of the outer ring 1. That is, a spherical groove is formed by the groove 3a of the outer ring 1 and the groove 3b of the inner ring 2,
A steel ball 30, which is the first rolling element, is inserted there. Further, a disc portion 21 projecting toward the radially opposite side is formed on the outer peripheral portion on the lower end surface 20 side of the inner ring 2 over the entire circumference. Disk part
The upper end surface of 21 has a predetermined gap, and the lower end surface 10 of the outer ring 1
A similar groove 4b is formed at the position corresponding to the groove 4a and at the position corresponding to the groove 4a over the entire circumference.
【００１５】外輪１の第２転動体介挿用溝４aと、内輪
２の同様の溝４bとで、第２転動体介挿用溝４となる間
隙が形成され、そこに第２転動体である鋼球40が介挿さ
れる。そして特に、溝４a,４bには緩衝部材７が配置さ
れ、鋼球40が介挿された状態で圧縮力がかかる程度に鋼
球40に当接させる。ここで、緩衝部材７はブチルゴムや
ウレタンゴム等の減衰ゴムを用いるが、減衰作用が得ら
れる部材であれば他の緩衝部材でももちろん良い。The second rolling element interposing groove 4a of the outer ring 1 and the similar groove 4b of the inner ring 2 form a gap which becomes the second rolling element interposing groove 4, and the second rolling element forms a gap therein. A steel ball 40 is inserted. In particular, the cushioning member 7 is arranged in the grooves 4a and 4b, and the steel balls 40 are brought into contact with the steel balls 40 to such an extent that a compressive force is applied in the inserted state. Here, the cushioning member 7 uses a damping rubber such as butyl rubber or urethane rubber, but any other cushioning member may of course be used as long as it can obtain a damping action.
【００１６】本実施例の旋回軸受によれば、外輪１と内
輪２との、転動体を介した連絡箇所が第１転動体（鋼球
30）介挿部以外に第２転動体（鋼球40）介挿部もあるた
め、その介挿部の分だけ、機体振動による振幅が緩和さ
れるが、それにも増して第２転動体（鋼球40）介挿部の
介挿用溝４を形成する前記内輪円板部21の溝４bと、前
記外輪一端面10の溝４aとの両方に緩衝部材７が配置さ
れ、しかも第２転動体である鋼球40と間隙のないように
当接してあり、鋼球40は介挿状態で初期圧縮がかけられ
ている。このため、機体振動が発生した際でも、その振
動は鋼球40に当接する緩衝部材に効果的に吸収されるこ
とになり、不可避的に生じていた機体振動の振幅増加は
有効に抑制されることになる。According to the slewing bearing of this embodiment, the contact point between the outer ring 1 and the inner ring 2 via the rolling element is the first rolling element (steel ball).
30) Since there is a second rolling element (steel ball 40) interposing section in addition to the interposing section, the amplitude due to machine body vibration is reduced by the amount of the interposing section, but the second rolling element ( Steel ball 40) The cushioning member 7 is arranged in both the groove 4b of the inner ring disc portion 21 forming the insertion groove 4 of the insertion portion and the groove 4a of the outer ring one end face 10, and the second rolling member is used. The steel ball 40, which is a moving body, is in contact with the steel ball 40 without a gap, and the steel ball 40 is initially compressed in an inserted state. Therefore, even when the machine body vibration is generated, the vibration is effectively absorbed by the cushioning member that is in contact with the steel ball 40, and the increase in the amplitude of the machine body vibration that is unavoidably generated is effectively suppressed. It will be.
【００１７】図２は本実施例の作用効果の確認試験の結
果を示すグラフである。点線Ａが本実施例における機体
の振幅減衰をプロットしたグラフ、実線Ｂが自然減衰の
際の機体の振幅をプロットしたグラフをそれぞれ示す。
本実施例の旋回軸受によれば、自然減衰の場合の約３分
の１以下の時間で機体の振幅を抑制できることが明らか
となっている。FIG. 2 is a graph showing the results of the test for confirming the action and effect of this embodiment. A dotted line A is a graph plotting the amplitude attenuation of the airframe in the present embodiment, and a solid line B is a graph plotting the amplitude of the airframe at the time of natural attenuation.
It has been clarified that the swing bearing of the present embodiment can suppress the amplitude of the airframe in about one-third or less of the time in the case of natural damping.
【００１８】なお本発明が上記実施例に限定されるもの
でないことは上述のとおりであり、例えば円板部21が内
輪２の上端面側や外輪１の上端面又は下端面側に設けら
れる構成、緩衝部材７が外輪１又は内輪２のいずれか一
方に配置される構成等でもよい。As described above, the present invention is not limited to the above embodiment. For example, the disc portion 21 is provided on the upper end surface side of the inner ring 2 or the upper end surface or the lower end surface side of the outer ring 1. Alternatively, the buffer member 7 may be arranged on either the outer ring 1 or the inner ring 2.
【００１９】[0019]
【発明の効果】以上説明したように、本発明に係る旋回
用軸受によれば、機体振動の振幅増大を抑制し、効果的
な振動低減を図れるものとなっている。As described above, according to the swivel bearing of the present invention, it is possible to suppress the increase in the amplitude of the machine body vibration and effectively reduce the vibration.
【図１】本発明に係る旋回軸受の一実施例を示す要部断
面図である。FIG. 1 is a sectional view of an essential part showing an embodiment of a slewing bearing according to the present invention.
【図２】本実施例の振幅減衰作用の試験結果を示すグラ
フである。FIG. 2 is a graph showing the test results of the amplitude damping action of this example.
【図３】従来の旋回軸受の構造を示す要部切欠断面図で
ある。FIG. 3 is a cutaway sectional view showing a structure of a conventional slewing bearing.
【図４】図３中、旋回軸受の要部を拡大した断面図であ
る。FIG. 4 is an enlarged sectional view of a main part of the slewing bearing in FIG.
【図５】実開平３−８９２１６号で提案した旋回軸受の
構造を示す要部断面図である。FIG. 5 is a sectional view of an essential part showing the structure of a slewing bearing proposed in Japanese Utility Model Laid-Open No. 3-89216.
１ 外輪 ２ 内輪 ３ 第１転動体介挿用溝 ４ 第２転動体介挿用溝 ７ 緩衝部材 1 Outer ring 2 Inner ring 3 First rolling element insertion groove 4 Second rolling element insertion groove 7 Buffer member
Claims (1)
置される内輪の外周面とに形成される溝に第１転動体が
介挿され、かつ前記内輪又は外輪の一端面側にその半径
方向対向側に突出して形成される円板部と、該円板部に
対向する前記外輪又は内輪の一端面とに形成される溝に
第２転動体が介挿される旋回軸受であって、前記第２転
動体の介挿用溝を形成する前記内輪又は外輪の円板部
と、前記外輪又は内輪の一端面とのいずれか一方又は両
方に、前記第２転動体が当接するように緩衝部材を配置
したことを特徴とする振動低減用旋回軸受。1. A first rolling element is inserted into a groove formed in an inner peripheral surface of an outer ring and an outer peripheral surface of an inner ring arranged concentrically with the outer ring, and one end surface side of the inner ring or the outer ring. A slewing bearing in which a second rolling element is inserted into a groove formed in a disk portion formed to project to the radially opposite side and one end surface of the outer ring or the inner ring facing the disk portion. So that the second rolling element comes into contact with either or both of the disc portion of the inner ring or the outer ring forming the insertion groove of the second rolling element and the one end surface of the outer ring or the inner ring. A vibration-reducing slewing bearing, characterized in that a cushioning member is arranged in the.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6264365A JPH08105437A (en) | 1994-10-05 | 1994-10-05 | Vibration reducing swing bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6264365A JPH08105437A (en) | 1994-10-05 | 1994-10-05 | Vibration reducing swing bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08105437A true JPH08105437A (en) | 1996-04-23 |
Family
ID=17402148
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6264365A Withdrawn JPH08105437A (en) | 1994-10-05 | 1994-10-05 | Vibration reducing swing bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08105437A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006327567A (en) * | 2005-05-26 | 2006-12-07 | Dong-Il Rubber Belt Co Ltd | Under carriage having shock absorbing function |
| KR100687009B1 (en) * | 2005-06-23 | 2007-02-26 | 세메스 주식회사 | Shaft apparatus for substrate transportation |
| KR20210127330A (en) * | 2020-04-14 | 2021-10-22 | 대모 엔지니어링 주식회사 | Damping device for rotary-type quick coupler |
| KR20220094685A (en) * | 2020-12-29 | 2022-07-06 | 경성시험기주식회사 | Vibration tester with phase compensation mechanism |
-
1994
- 1994-10-05 JP JP6264365A patent/JPH08105437A/en not_active Withdrawn
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006327567A (en) * | 2005-05-26 | 2006-12-07 | Dong-Il Rubber Belt Co Ltd | Under carriage having shock absorbing function |
| KR100687009B1 (en) * | 2005-06-23 | 2007-02-26 | 세메스 주식회사 | Shaft apparatus for substrate transportation |
| KR20210127330A (en) * | 2020-04-14 | 2021-10-22 | 대모 엔지니어링 주식회사 | Damping device for rotary-type quick coupler |
| KR20220094685A (en) * | 2020-12-29 | 2022-07-06 | 경성시험기주식회사 | Vibration tester with phase compensation mechanism |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A300 | Withdrawal of application because of no request for examination |
Free format text: JAPANESE INTERMEDIATE CODE: A300 Effective date: 20020115 |