JP2009014193A - Friction damper device - Google Patents

Friction damper device Download PDF

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Publication number
JP2009014193A
JP2009014193A JP2007201310A JP2007201310A JP2009014193A JP 2009014193 A JP2009014193 A JP 2009014193A JP 2007201310 A JP2007201310 A JP 2007201310A JP 2007201310 A JP2007201310 A JP 2007201310A JP 2009014193 A JP2009014193 A JP 2009014193A
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bearing
friction damper
damper
periphery
bending
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Japanese (ja)
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Kaname Ogura
要 小椋
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Ogura Tekko Kk
小椋鉄工株式会社
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a friction damper device having great damping capability while permitting great displacement using an external damper for a bearing, instead of a conventional external damper which is mounted on a rolling bearing or a sliding bearing under special conditions, having less damping effects, and which has a small range of elastic deformation and a great spring constant, as disadvantages. <P>SOLUTION: A band plate material is formed polygonal, wound on a bearing and mounted on a bearing housing to form a bent beam with 6-12 contact points on the while periphery. Spring force with the bending of the beam is utilized for elastically supporting it, and minute-slide friction with the deformation of the beam is utilized for absorbing vibration energy. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

高速回転装置において、運転条件によっては、軸受のばね定数が大きく、ダンピングが効かないことがあり、大きな振動を発生することがあるが、このような軸受の外側に入れるダンパー装置に関するものである。In a high-speed rotating device, depending on operating conditions, the spring constant of the bearing may be large, damping may not work, and large vibrations may be generated. However, the present invention relates to a damper device placed outside such a bearing.
特許公開2005−24046  Patent Publication 2005-24046 特許公開平11−193816  Patent Publication No. Hei 11-193816 特許公開2005−24047  Patent Publication 2005-24047
図16〜図19に、従来より用いられているころがり軸受用のダンピングプレートを示したものである。図16は、帯状の板に無数の突起を設け、厚さ方向のばね効果を狙ったもので、図19に示すように、プレート1001を図示されていないがころがり軸受の外周部に巻き付けるように取り付け、軸受ハウジングに圧入する。これによって、軸受ハウジングとアウターレース間のすきまがなくなり、ころがり軸受の外部ダンパーとしての効果が得られる。  16 to 19 show a conventionally used damping plate for a rolling bearing. FIG. 16 is intended to provide an infinite number of protrusions on the belt-like plate and aim at the spring effect in the thickness direction. As shown in FIG. 19, the plate 1001 is not shown, but is wound around the outer periphery of the rolling bearing. Install and press fit into bearing housing. As a result, there is no gap between the bearing housing and the outer race, and an effect as an external damper of the rolling bearing can be obtained.
図18に示すダンパープレート1011は帯状の平板であるが、これを図示されていないころがり軸受の外周に図19に示すように二重に、場合によっては三重に巻いて、軸受ハウジングに圧入する。ダンパープレートが持っているわずかなうねりによって、厚さ方向のばね効果が得られる。また、板の間に潤滑油が浸入し、粘性ダンピング効果なども得られる。  The damper plate 1011 shown in FIG. 18 is a belt-like flat plate, and is wound around the outer periphery of a rolling bearing (not shown) twice as shown in FIG. A slight undulation of the damper plate provides a spring effect in the thickness direction. Moreover, lubricating oil permeates between the plates, and a viscous damping effect or the like is obtained.
図示されていないが、上記の例の他に、リング状に厚さの異なる帯状平板をころがり軸受の外側に巻き付け、軸受ハウジングに圧入するようなダンパープレートも実用化されている。いずれも図17や図19と同様な効果が得られる。  Although not shown in the drawings, in addition to the above example, a damper plate is also put into practical use in which a strip-shaped flat plate having a ring-like thickness is wound around the outside of a rolling bearing and press-fitted into the bearing housing. In either case, the same effects as in FIGS. 17 and 19 can be obtained.
また、薄板の代わりに、軸受外周またはハウジング側にリング状の溝を設け、この中に、ゴム製の角形0リングあるいは丸形0リングをそう入し、ゴムの弾性力を利用して、弾性支持をする方法が取られている。  Also, instead of a thin plate, a ring-shaped groove is provided on the outer periphery of the bearing or on the housing side, and a rubber square 0-ring or round 0-ring is inserted into the groove, and the elastic force of the rubber is used for elasticity. A way to support is taken.
以上のような方法は、比較的小さな振動には有効であり、広く利用されている。  The above method is effective for relatively small vibrations and is widely used.
しかし、比較的大きな振動を生ずる回転機械装置などでは、ダンパー部における大きな変位を取ることができず、その効果に限りがある。また、薄板の微小なうねりを期待しているため、沢山の枚数を重ねて巻き付けると、中心保持精度が悪く、また設計時に、ダンパーのばね定数を正確に求めたり設計したりすることが困難であること、製作、組立時に、ダンパーの性状品質を安定させることができないという問題がある。  However, in a rotary machine device that generates a relatively large vibration, a large displacement cannot be taken in the damper portion, and its effect is limited. In addition, since a small swell of the thin plate is expected, if a large number of sheets are wound around, the center holding accuracy is poor, and it is difficult to accurately determine or design the damper spring constant during design. There is a problem that the quality of the damper cannot be stabilized at the time of manufacture and assembly.
一方、ゴム製の0リングを用いるダンパー装置は、ゴム材の圧縮永久ひずみのため、ダンピング特性が経時変化するという欠点がある。  On the other hand, a damper device using a rubber 0-ring has a drawback that the damping characteristic changes with time due to compression set of the rubber material.
発明が解決しようとする課題Problems to be solved by the invention
軸受に取り付けるダンパーの変位を大きくすると共に、ダンピング能力を大きくするダンパー装置を提供することを目的とする。  An object of the present invention is to provide a damper device in which the displacement of a damper attached to a bearing is increased and the damping capability is increased.
課題を解決するための手段Means for solving the problem
そこで、板材を用いて、全周で6〜12個の曲げはりを構成させ、これを軸受の外周部に巻き付けるようにし、軸受ハウジングに対し、締代をもたせて、組み立てるようにする。  Therefore, 6 to 12 bending beams are formed on the entire circumference by using a plate material, and these are wound around the outer peripheral portion of the bearing, and the bearing housing is assembled with a tightening allowance.
発明の効果The invention's effect
このように、曲げ変位を大きくすることにより、ダンパーとしての変位が20〜100μmと大きくなる。曲げはりの接点は、軸受外周部側と軸受ハウジング側に交互にできるが、軸受が半径方向に変位するとき、前述の接点では円周方向にわずかなすべりが生ずる。このとき、発生する摩擦により、振動エネルギーが熱エネルギーに変換され、吸収されるため、振動減衰効果が得られる。  Thus, by increasing the bending displacement, the displacement as a damper is increased to 20 to 100 μm. Although the contact point of the bending beam can be alternated between the bearing outer peripheral side and the bearing housing side, when the bearing is displaced in the radial direction, a slight slip occurs in the circumferential direction at the aforementioned contact point. At this time, vibration energy is converted into heat energy and absorbed by the generated friction, so that a vibration damping effect is obtained.
図1〜図4に第一実施例を示す。図において摩擦ダンパー1は多角形状に曲げ加工をし、上下2分割となっている。この摩擦ダンパー1を図3,図4に示すように、ころがり軸受の外周部に巻き付けるように取り付け、軸受ハウジング4の上に入れ、上部カバー3をかぶせボルト5によって、締め付けることにより、摩擦ダンパー1に締付力が与えられ、ころがり軸受2を、軸受ハウジング4の中にしっくりと押さえ込まれる。  1 to 4 show a first embodiment. In the figure, the friction damper 1 is bent into a polygonal shape and divided into two parts. As shown in FIGS. 3 and 4, the friction damper 1 is attached so as to be wound around the outer periphery of the rolling bearing, placed on the bearing housing 4, and the upper cover 3 is tightened with the cover bolt 5, thereby the friction damper 1. A tightening force is applied to the rolling bearing 2 and the rolling bearing 2 is pressed into the bearing housing 4 properly.
摩擦ダンパー1は、多角形をしており、軸受ハウジング4やカバー3の中では、軸受ハウジング4やカバー3に対してはA、A点でころがり軸受2に対しては、B点で接触している。摩擦ダンパー1は、A、AB点を有する曲げはりが全周に複数個構成され、これらがころがり軸受2を全周より押しつけている。The friction damper 1 has a polygonal shape, and in the bearing housing 4 and the cover 3, the bearing housing 4 and the cover 3 are at points A 1 and A 2 at the point B 1 for the rolling bearing 2. In contact. In the friction damper 1, a plurality of bending beams having points A 1 and A 2 B are formed on the entire periphery, and these press the rolling bearing 2 from the entire periphery.
ころがり軸受2のインナーレース回転軸4が嵌合されており、回転軸4に作用する力によって、摩擦ダンパー1の曲げはりが弾性変形し、ころがり軸受2が、半径方向に変位する。摩擦ダンパー1のばね定数を小さく設計できるため、回転軸4を柔軟に支持する。摩擦ダンパー1が変形するとき、曲げはりは、周方向にも、長さの変化があり、前述の接点A、A、B点において、わずかなすべりが生じ、これが、振動エネルギーを吸収する。いわゆるダンピング効果が得られる。The inner race rotating shaft 4 of the rolling bearing 2 is fitted, and the bending beam of the friction damper 1 is elastically deformed by the force acting on the rotating shaft 4, and the rolling bearing 2 is displaced in the radial direction. Since the spring constant of the friction damper 1 can be designed to be small, the rotating shaft 4 is supported flexibly. When the friction damper 1 is deformed, the length of the bending beam also changes in the circumferential direction, and a slight slip occurs at the aforementioned points of contact A 1 , A 2 and B, which absorbs vibration energy. . A so-called damping effect is obtained.
図1〜図4の実施例においては、軸受ハウジング3、4が上下2ツ割れとなっており、摩擦ダンパー1の装着性から、上下2ツ割れとしている。  In the embodiment shown in FIGS. 1 to 4, the bearing housings 3 and 4 are divided into two upper and lower parts.
図5は、本発明の第二実施例で、周方向に1ヶ所カットされているが、1体形の摩擦ダンパー101となっている。使い方は、図3の第一実施例と同じて、予め軸受2に取り付けておき、軸受ハウジング4に入れ、カバー2をかぶせボルト5で、これを締め付けて、組み立てられる。  FIG. 5 shows a second embodiment of the present invention, in which one place is cut in the circumferential direction, but a one-piece friction damper 101 is formed. The usage is the same as in the first embodiment of FIG. 3, which is assembled to the bearing 2 in advance, put in the bearing housing 4, and the cover 2 is covered with the bolt 5 to tighten it.
図5に第三実施例摩擦ダンパー201を示す。曲げはりは、周全体から、半径方向にばね力を加えるためのものであり、周方向に分割してもその機能や効果は変わらない。このため、組立性あるいは、部品としての製作性あるいは在庫管理などを考慮した互換性などの観点から、周方向の分割数などを、自由に選ぶことができる。  FIG. 5 shows a friction damper 201 according to the third embodiment. The bending beam is for applying a spring force in the radial direction from the entire circumference, and its function and effect are not changed even if it is divided in the circumferential direction. For this reason, the number of divisions in the circumferential direction and the like can be freely selected from the viewpoints of assemblability, compatibility as a result of manufacturability as parts, inventory management, and the like.
図7は第四実施例を示すもので、摩擦ダンパー301は、花形をしたウェーブ状曲げはりにしたものである。曲げはりとしてのばね特性を選定することによって、多角形摩擦ダンパーと機能や作用効果は全く同じである。  FIG. 7 shows a fourth embodiment, in which the friction damper 301 is a flower-like wave bending beam. By selecting the spring characteristics as a bending beam, the functions and effects of the polygonal friction damper are exactly the same.
図8は第五実施例を示すもので、摩擦ダンパー401は、リング状のダンパーに対し、外側と内側に突起を交互に設け、連続した曲げはりを構成させるものである。大径用の摩擦ダンパーでは、板曲げより簡単に製作できるというメリットがある。  FIG. 8 shows a fifth embodiment. A friction damper 401 is provided with a protrusion on the outer side and an inner side of a ring-shaped damper alternately to form a continuous bending beam. Large diameter friction dampers have the advantage of being easier to manufacture than plate bending.
図9,図10は第六実施例を示すもので、片持ちはり形の摩擦ダンパー501である。帯状薄板に図9に示すような切り込みを入れ、これを軸受の外周に巻き付けると図10のように片持ちはりが構成されるので、これを軸受2と共に、軸受ハウジング4に装着して使用される。片持ちはりであるためばね定数が小さく、装着性が良いというメリットがある。  9 and 10 show a sixth embodiment, which is a cantilevered friction damper 501. FIG. When a notch as shown in FIG. 9 is made in the belt-shaped thin plate and wound around the outer periphery of the bearing, a cantilever is formed as shown in FIG. 10, and this is used by being mounted on the bearing housing 4 together with the bearing 2. The Since it is a cantilever, it has the advantage of a small spring constant and good mounting properties.
図11,図12,図13は第七実施例の説明図である。図11は、摩擦ダンパー601の展開図である。この摩擦ダンパー601は、軸方向に複数の曲げはりを構成させるもので、曲げはり形のばね、曲げはりの接点で、はりの変形に伴う微小なすべりを利用して、ダンピング効果を得るもので、これまでに述べてきた摩擦ダンパーと機能や作用、効果は全く同じである。曲げはりの寸法選定が容易であり、設計しやすく、目標性能に対する最適化が得やすいというメリットがある。  11, 12 and 13 are explanatory views of the seventh embodiment. FIG. 11 is a development view of the friction damper 601. This friction damper 601 constitutes a plurality of bending beams in the axial direction, and is a bending beam spring and a contact point of the bending beam, and obtains a damping effect by utilizing a minute slip accompanying deformation of the beam. The functions, functions, and effects are the same as the friction dampers described so far. There are advantages in that it is easy to select the dimensions of the bending beam, it is easy to design, and it is easy to optimize the target performance.
図14,図15は、第八実施例の説明図で、摩擦ダンパー701は、図1,図2に示す2分割多角形であるが、対象とする軸受はすべり軸受702である。すべり軸受においても、用途によって外部ダンパーの必要なものがあり、すべり軸受702の外周部に2列に装着されている。すべり軸受702は、概して軸受巾が広いため、2列に用いるのが一般的である。FIGS. 14 and 15 are explanatory views of the eighth embodiment. The friction damper 701 is a two-part polygon shown in FIGS. 1 and 2, but the target bearing is a sliding bearing 702. Some slide bearings also require external dampers depending on the application, and are mounted in two rows on the outer periphery of the slide bearing 702. Since the plain bearing 702 has a generally wide bearing width, it is generally used in two rows.
本発明の第一実施例に係わる摩擦ダンパーの正面図である。It is a front view of the friction damper concerning the 1st example of the present invention. 本発明の第一実施例に係わる摩擦ダンパーの図1の横断面図である。It is a cross-sectional view of FIG. 1 of the friction damper according to the first embodiment of the present invention. 本発明の第一実施例に係わる摩擦ダンパーをころがり軸受と共に軸受ハウジングに装着した説明図である。It is explanatory drawing which attached the friction damper concerning the 1st Example of this invention to the bearing housing with the rolling bearing. 本発明の第一実施例に係わる摩擦ダンパーをころがり軸受と共に軸受ハウジングに装着した図3の横断面図である。FIG. 4 is a cross-sectional view of FIG. 3 in which the friction damper according to the first embodiment of the present invention is mounted on the bearing housing together with the rolling bearing. 本発明の第二実施例に係わる摩擦ダンパーである。It is a friction damper concerning the 2nd example of the present invention. 本発明の第三実施例に係わる摩擦ダンパーである。It is a friction damper concerning the 3rd example of the present invention. 本発明の第四実施例に係わる摩擦ダンパーである。It is a friction damper concerning the 4th example of the present invention. 本発明の第五実施例に係わる摩擦ダンパーである。It is a friction damper concerning the 5th example of the present invention. 本発明の第六実施例に係わる摩擦ダンパーである。It is a friction damper concerning the 6th example of the present invention. 本発明の第六実施例に係わる摩擦ダンパーで、ころがり軸受に取り付けたときの形状を示すものである。The friction damper concerning a 6th example of the present invention shows the shape when attached to a rolling bearing. 本発明の第七実施例に係わる摩擦ダンパーで、摩擦ダンパー材の展開図である。FIG. 11 is a development view of a friction damper material in a friction damper according to a seventh embodiment of the present invention. 本発明の第七実施例に係わる摩擦ダンパーで、ころがり軸受と共に軸受ハウジングに装着した正面図である。It is a front view with which the friction damper concerning 7th Example of this invention was mounted | worn with the rolling bearing and the bearing housing. 本発明の第七実施例に係わる摩擦ダンパーをころがり軸受と共に軸受ハウジングに装着した図12の横断面図である。FIG. 13 is a cross-sectional view of FIG. 12 in which the friction damper according to the seventh embodiment of the present invention is mounted on the bearing housing together with the rolling bearing. 本発明の第八実施例に係わる摩擦ダンパーで、すべり軸受と共に軸受ハウジングに装着したところの正面図である。FIG. 10 is a front view of a friction damper according to an eighth embodiment of the present invention, which is mounted on a bearing housing together with a slide bearing. 本発明の第八実施例に係わる摩擦ダンパーで、すべり軸受と共に軸受ハウジングに装着した図14の横断面図である。FIG. 15 is a cross-sectional view of FIG. 14 in which the friction damper according to the eighth embodiment of the present invention is mounted on a bearing housing together with a slide bearing. 従来より、ころがり軸受などに用いられる薄板を利用したダンパーの図である。It is the figure of the damper using the thin plate conventionally used for a rolling bearing etc. 従来より、ころがり軸受などに用いられる薄板を利用したダンパーの図で、図16のダンパーをころがり軸受に取り付けた形状を示すものである。It is a figure of the damper using the thin plate conventionally used for a rolling bearing etc., and shows the shape which attached the damper of FIG. 16 to the rolling bearing. 従来より、ころがり軸受に用いられる薄板を利用したダンパーのもうひとつの例の図である。It is a figure of another example of the damper using the thin plate conventionally used for a rolling bearing. 従来より、ころがり軸受に用いられる薄板を利用したダンパーのもうひとつの例の図で、ころがり軸受に取り付けたときの形状を示した図である。It is the figure of another example of the damper using the thin plate used for a rolling bearing conventionally, and is the figure which showed the shape when attached to a rolling bearing.
符号の説明Explanation of symbols
1.摩擦ダンパー
2.ころがり軸受
3.軸受カバー
4.軸受ハウジング
5.ボルト
6.回転軸
摩擦ダンパーの軸受カバー、あるいは軸受ハウジングとの接点
B 摩擦ダンパーのころがり軸受との接点
101.第二実施例の摩擦ダンパー
201.第三実施例の摩擦ダンパー
301.第四実施例の摩擦ダンパー
401.第五実施例の摩擦ダンパー
501.第六実施例の摩擦ダンパー
601.第七実施例の摩擦ダンパー
602.第七実施例説明図におけるころがり軸受
603.軸受カバー
604.軸受ハウジング
701.第八実施例説明図の摩擦ダンパー
702.第八実施例説明図のすべり軸受
703.軸受カバー
704.軸受ハウジング
705.ボルト
706.回転軸
1001.従来よりころがり軸受などに用いられる、薄板を利用したダンパーの説明図の凹凸を設けたダンパー
1011.従来よりころがり軸受などに用いられる薄板を利用した説明図におけるダンパーである。
1. Friction damper 2. 2. Rolling bearings 3. Bearing cover 4. Bearing housing Bolt 6. Rotating shaft A 1 A 2 Contact with the bearing cover or bearing housing of the friction damper B Contact with the rolling bearing of the friction damper 101. Friction damper 201 of the second embodiment. Friction damper 301 of the third embodiment. Friction damper 401 of the fourth embodiment 401. Friction damper 501 of the fifth embodiment. Friction damper 601 of the sixth embodiment. Friction damper 602 of the seventh embodiment. Rolling bearing 603 in the explanatory diagram of the seventh embodiment. Bearing cover 604. Bearing housing 701. Friction damper 702. Sliding bearing 703 of the eighth embodiment explanatory drawing 703. Bearing cover 704. Bearing housing 705. Bolt 706. Rotating shaft 1001. Damper 1011.. Provided with irregularities in the explanatory diagram of a damper using a thin plate, which is conventionally used for a rolling bearing or the like. It is a damper in explanatory drawing using the thin plate conventionally used for a rolling bearing etc.

Claims (6)

  1. 板を全周で6以上12個以下の角を有する多角形状にし、外周が円形をした軸受に巻きつけるように装着し、これを内周が円形をした軸受ハウジングに締め代をもたせて組み込み、該多角形の外周側の陵が軸受ハウジング接触し、多角形状部材辺の内側中間点が軸受と接触して、それぞれの辺が、曲げはりを構成し、軸受を弾性支持することを特徴とした回転軸受用の摩擦ダンパー装置。  The plate is made into a polygonal shape having 6 to 12 corners on the entire circumference, and is mounted so as to be wound around a bearing having a circular outer periphery, and this is incorporated into a bearing housing having a circular inner periphery with a tightening margin, The outer periphery of the polygon is in contact with the bearing housing, the inner middle point of the side of the polygonal member is in contact with the bearing, and each side constitutes a bending beam and elastically supports the bearing. Friction damper device for rotary bearings.
  2. 多角形をした板材を周方向に2分割あるいは複数個に分割した請求項1の回転軸受用の摩擦ダンパー装置。  The friction damper device for a rotary bearing according to claim 1, wherein the polygonal plate material is divided into two or a plurality of parts in the circumferential direction.
  3. 軸受の外周部に板材を巻き付けるようにして曲げはりを構成し、弾性支持する摩擦ダンパー装置において、板部の形状を全周にわたり6個以上12個の波形にしたこと。  In a friction damper device that is formed by bending a plate material around the outer periphery of the bearing and elastically supports it, the shape of the plate portion is made from 6 to 12 corrugations over the entire circumference.
  4. 軸受の外周部に板材を巻き付けるように取り付け、曲げはりを構成させて軸受を弾性支持する摩擦ダンパー装置において、板材に対し、軸受あるいは軸受ハウジングとの接点となる部分に、内周と外周にそれぞれ全周で6〜12個の起点を設けたこと。  In a friction damper device that is mounted so that a plate material is wound around the outer peripheral portion of the bearing and is configured to bend a beam to elastically support the bearing. 6-12 starting points were provided on the entire circumference.
  5. 帯状薄板に切り込みを入れるなどして、これを軸受の外周に巻き付けたとき、形状される部材が、曲げはりとなり、軸受ハウジングとの間でばねを構成し、弾性支持する請求項1の摩擦ダンパー装置。  2. The friction damper according to claim 1, wherein when the belt-like thin plate is cut and wound around the outer periphery of the bearing, the shaped member becomes a bending beam, constitutes a spring with the bearing housing, and is elastically supported. apparatus.
  6. 帯状薄板で、一文字の中心部材に対し、両側に6〜12個の舌を設けた、いわゆる百足状部材とし、中心部材を軸受外周に巻き付け、軸受ハウジングに装着したとき、舌部の先端が軸受ハウジングとの間接点となり、曲げはりを構成し、このばね力により軸受を弾性支持するようにした請求項1の摩擦ダンパー装置。  It is a strip-shaped thin plate that has 6 to 12 tongues on both sides with respect to the center member of a single letter. When the center member is wound around the outer periphery of the bearing and mounted on the bearing housing, the tip of the tongue is the bearing. 2. The friction damper device according to claim 1, wherein the friction damper device is a contact between the housing and a bending beam, and the bearing is elastically supported by the spring force.
JP2007201310A 2007-07-03 2007-07-03 Friction damper device Pending JP2009014193A (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012011568A1 (en) 2010-07-23 2012-01-26 日産自動車株式会社 Engine automatic stop device and automatic stop method
CN102635567A (en) * 2012-03-29 2012-08-15 苏州立德泵技术研究院有限公司 Octagonal closed-type bearing bracket connected with shell
CN107461156A (en) * 2017-10-06 2017-12-12 西南石油大学 Rock bit roll-slide combined bearing
CN108916218A (en) * 2017-01-23 2018-11-30 宁波高新区起兴机电有限公司 A kind of bumper and absorbing shock ring for compressor of air conditioner deep groove ball bearing

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012011568A1 (en) 2010-07-23 2012-01-26 日産自動車株式会社 Engine automatic stop device and automatic stop method
CN102635567A (en) * 2012-03-29 2012-08-15 苏州立德泵技术研究院有限公司 Octagonal closed-type bearing bracket connected with shell
CN108916218A (en) * 2017-01-23 2018-11-30 宁波高新区起兴机电有限公司 A kind of bumper and absorbing shock ring for compressor of air conditioner deep groove ball bearing
CN108916220A (en) * 2017-01-23 2018-11-30 宁波高新区起兴机电有限公司 A kind of dedicated deep groove ball bearing shock ring of compressor of air conditioner
CN108916220B (en) * 2017-01-23 2020-04-03 郑梦兰 Dedicated deep groove ball bearing damping ring of air condition compressor
CN107461156A (en) * 2017-10-06 2017-12-12 西南石油大学 Rock bit roll-slide combined bearing

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