JPH0419232Y2 - - Google Patents
Info
- Publication number
- JPH0419232Y2 JPH0419232Y2 JP1986047965U JP4796586U JPH0419232Y2 JP H0419232 Y2 JPH0419232 Y2 JP H0419232Y2 JP 1986047965 U JP1986047965 U JP 1986047965U JP 4796586 U JP4796586 U JP 4796586U JP H0419232 Y2 JPH0419232 Y2 JP H0419232Y2
- Authority
- JP
- Japan
- Prior art keywords
- bush
- floating
- cylindrical surface
- effective friction
- bushing
- 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
- 239000012530 fluid Substances 0.000 description 10
- 230000001050 lubricating effect Effects 0.000 description 5
- 239000003921 oil Substances 0.000 description 5
- 230000002159 abnormal effect Effects 0.000 description 4
- 238000005461 lubrication Methods 0.000 description 4
- 239000000314 lubricant Substances 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000010008 shearing Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 239000013535 sea water Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
- F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
-
- 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
- F16C2326/00—Articles relating to transporting
- F16C2326/30—Ships, e.g. propelling shafts and bearings therefor
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
Description
【考案の詳細な説明】
〔産業上の利用分野〕
本考案は、フローテイングブツシユを同一中心
線のまわりに互いに逆方向に同一回転速度で回転
する外部円筒面と内部円筒面との相互間に介装し
同フローテイングブツシユにより内部円筒を外部
円筒内において支承する軸受装置に関し、特に舶
用二重反転プロペラ軸系における船尾管軸受など
に用いて好適のフローテイングブツシユ付き軸受
装置に関する。[Detailed Description of the Invention] [Industrial Application Field] The present invention is a floating bushing that connects an outer cylindrical surface and an inner cylindrical surface that rotate at the same rotational speed in opposite directions around the same center line. The present invention relates to a bearing device with a floating bush that supports an inner cylinder in an outer cylinder by a floating bush, and particularly to a bearing device with a floating bush that is suitable for use in a stern tube bearing in a counter-rotating marine propeller shaft system.
第５，６図に示すように、同一中心線のまわり
に互いに逆方向に同一回転速度で回転する回転軸
（内軸）０１と軸受（外軸）０３とをそなえた軸
系（たとえば、舶用二重反転プロペラ軸系）で
は、回転軸０１を軸受０３内に支承するために、
一般に、回転軸０１の外部円筒面０１ａと軸受０
３の内部円筒面０３ａとの相互間にフローテイン
グブツシユ０２が挿入配置されている。
As shown in Figures 5 and 6, a shaft system (such as a marine In the counter-rotating propeller shaft system), in order to support the rotating shaft 01 in the bearing 03,
Generally, the outer cylindrical surface 01a of the rotating shaft 01 and the bearing 0
A floating bush 02 is inserted and arranged between the inner cylindrical surface 03a of No. 3 and the inner cylindrical surface 03a.
なお、回転軸（内軸）０１は図示しない主機等
により回転駆動されるほか、軸受（外軸）０３
は、図示しないハウジングと一体に設置され、図
示しない駆動源により回転軸０１と逆方向に回転
駆動される。 Note that the rotating shaft (inner shaft) 01 is rotationally driven by a main engine (not shown), etc., and also has a bearing (outer shaft) 03.
is installed integrally with a housing (not shown), and is rotationally driven in a direction opposite to the rotating shaft 01 by a drive source (not shown).
上述のようなフローテイングブツシユ０２付き
の軸受装置においては、回転軸０１とブツシユ０
２との摺動面相互間およびブツシユ０２と軸受０
３との摺動面相互間は、潤滑油あるいは水、海水
などにより潤滑される。 In the bearing device with the floating bush 02 as described above, the rotating shaft 01 and the bush 0
Between the sliding surfaces of 2 and the bush 02 and the bearing 0
The sliding surfaces with 3 are lubricated with lubricating oil, water, seawater, or the like.
そして、各摺動面相互間には、摺動面の相対運
動により流体動圧が発生し、流体潤滑膜が厚く形
成されるようになつている。 Fluid dynamic pressure is generated between each sliding surface due to the relative movement of the sliding surfaces, and a thick fluid lubricating film is formed.
ところで、フローテイングブツシユ０２の内外
面に形成される流体潤滑膜の厚さは、主として同
ブツシユ０２の回転数により規定され、このブツ
シユ０２の回転数は、ブツシユ０２の内外面にそ
れぞれ作用する潤滑流体の粘性剪断力の釣合いに
よつて決定される。
By the way, the thickness of the fluid lubricant film formed on the inner and outer surfaces of the floating bush 02 is mainly determined by the rotation speed of the floating bush 02, and the rotation speed of the bush 02 acts on the inner and outer surfaces of the bush 02, respectively. It is determined by the balance of viscous shear forces in the lubricating fluid.
一般に、フローテイングブツシユ０２は、回転
軸（内軸）０１と軸受（外軸）０３との間におい
てほぼ静止した状態となるのが最も理想的である
が、上述した従来のフローテイングブツシユ０２
付き軸受装置では、ブツシユ０２の外周面積が同
ブツシユ０２の内周面積よりも大きいため、ブツ
シユ０２の内外面に作用する潤滑流体の粘性剪断
力は外面側の方が大きくなる。 Generally, it is most ideal for the floating bush 02 to be in a nearly stationary state between the rotating shaft (inner shaft) 01 and the bearing (outer shaft) 03, but the above-mentioned conventional floating bush 02
In the bearing device, since the outer peripheral area of the bush 02 is larger than the inner peripheral area of the bush 02, the viscous shearing force of the lubricating fluid acting on the inner and outer surfaces of the bush 02 is larger on the outer surface side.
したがつて、フローテイングブツシユ０２は、
軸受（外軸）０３と同方向に回転するようにな
り、このブツシユ０２の内面と回転軸（内軸）０
１の外部円筒面０１ａとは互いに逆方向に回転す
るため。ブツシユ０２の内側において、流体力学
的な動圧発生能力が低下し流体潤滑膜の厚さが薄
くなり、摺動面の直接接触を生じるようになる。 Therefore, floating bush 02 is
It now rotates in the same direction as the bearing (outer shaft) 03, and the inner surface of this bushing 02 and the rotating shaft (inner shaft) 0
This is because the external cylindrical surface 01a of No. 1 rotates in opposite directions. Inside the bush 02, the hydrodynamic ability to generate dynamic pressure decreases, the thickness of the fluid lubricant film becomes thinner, and direct contact between sliding surfaces occurs.
この結果、軸受装置において、軸受の焼付きあ
るいは異常摩耗などの損傷が発生する恐れがあ
る。 As a result, damage such as seizure or abnormal wear of the bearing may occur in the bearing device.
本考案は、このような問題点の解決をはかろう
とするもので、フローテイングブツシユをほぼ静
止した状態に保持できるようにして、軸受の焼付
きや異常摩耗の発生等を確実に防止した、フロー
テイングブツシユ付き軸受装置を提供することを
目的とする。 The present invention attempts to solve these problems by making it possible to hold the floating bush in a nearly stationary state, thereby reliably preventing bearing seizing and abnormal wear. , an object of the present invention is to provide a bearing device with a floating bush.
このため、本考案のフローテイングブツシユ付
き軸受装置では、同一中心線のまわりに互いに逆
方向に同一回転速度で回転する外部円筒面と内部
円筒面との相互間にフローテイングブツシユをそ
なえ、同ブツシユの外面の有効摩擦幅が同ブツシ
ユの内面の有効摩擦幅よりも小さく形成され、同
ブツシユの外面と内面とが次の３つの条件を満た
すように形成されたことを特徴としている。
Therefore, in the bearing device with a floating bushing of the present invention, a floating bushing is provided between an outer cylindrical surface and an inner cylindrical surface that rotate at the same rotational speed in opposite directions around the same center line, The brush is characterized in that the effective friction width of the outer surface of the bush is smaller than the effective friction width of the inner surface of the bush, and the outer and inner surfaces of the bush are formed to satisfy the following three conditions.
(1) r2／r1＝1.2〜1.3 ただし、 r1は上記ブツシユの内径 r2は上記ブツシユの最大外径。(1) r 2 / r 1 = 1.2 to 1.3, where r 1 is the inner diameter of the bush, and r 2 is the maximum outer diameter of the bush.
(2) C2／C1＝１，０〜1.8
ただし、
C1は上記ブツシユの内面と上記内部円筒面
とすき間
C2は上記ブツシユの外面と上記外部円筒面
との最小すき間。(2) C 2 /C 1 = 1,0 to 1.8, where C 1 is the gap between the inner surface of the bush and the inner cylindrical surface, and C 2 is the minimum gap between the outer surface of the bush and the outer cylindrical surface.
(3) L1／L2＝1.2〜2.0 ただし、 L1は上記ブツシユの内面の有効摩擦幅 L2は上記ブツシユの外面の有効摩擦幅。(3) L 1 /L 2 = 1.2 to 2.0, where L 1 is the effective friction width on the inner surface of the bushing, and L 2 is the effective friction width on the outer surface of the bushing.
上述の本考案のフローテイングブツシユ付き軸
受装置では、フローテイングブツシユは、その外
面の有効摩擦幅を内面の有効摩擦幅よりも小さく
形成されているため、上記ブツシユの内外面に作
用する潤滑流体の粘性剪断力が釣合うようにな
り、上記ブツシユは、外部円筒面と内部円筒面と
の相互間でほぼ静止する。
In the bearing device with a floating bush of the present invention described above, the floating bush has an effective friction width on its outer surface that is smaller than an effective friction width on its inner surface, so that the lubrication acting on the inner and outer surfaces of the bush is smaller. The viscous shear forces of the fluid become balanced and the bush becomes substantially stationary between the outer and inner cylindrical surfaces.
以下、図面により本考案の一実施例としてのフ
ローテイングブツシユ付き軸受装置について説明
すると、第１図はそのフローテイングブツシユの
縦断面図、第２図はそのフローテイングブツシユ
の変形例を示す縦断面図、第３図はそのフローテ
イングブツシユの他の変形例を示す縦断面図、第
４図は、そのフローテイングブツシユの内外面の
有効摩擦幅比（L1／L2）と、同ブツシユの回転
数と軸回転数との比（Nb／No）との関係を示す
グラフである。
Below, a bearing device with a floating bushing as an embodiment of the present invention will be explained with reference to the drawings. Fig. 1 is a longitudinal sectional view of the floating bushing, and Fig. 2 is a modification of the floating bushing. 3 is a longitudinal sectional view showing another modification of the floating bushing, and FIG. 4 is a longitudinal sectional view showing the effective friction width ratio (L 1 /L 2 ) of the inner and outer surfaces of the floating bushing. It is a graph showing the relationship between the rotation speed of the same bush and the ratio of the shaft rotation speed (Nb/No).
第１〜３図に示すフローテイングブツシユ１
２，２２，３２は、いずれも従来と同様、同一中
心線のまわりに互いに逆方向に同一回転速度で回
転する外部円筒面と内部円筒面との相互間に配設
されるものである。 Floating bush 1 shown in Figures 1 to 3
2, 22, and 32 are all disposed between an outer cylindrical surface and an inner cylindrical surface that rotate at the same rotational speed in opposite directions around the same center line, as in the conventional case.
第１図に示すフローテイングブツシユ１２にお
いては、同ブツシユ１２の外面の軸方向両端部に
切り欠き部１２ａ，１２ａが形成されており、ブ
ツシユ１２の外面の有効摩擦幅L2が同ブツシユ
１２の内面の有効摩擦幅L1よりも小さく形成さ
れている。 In the floating bush 12 shown in FIG. 1, notches 12a, 12a are formed at both axial ends of the outer surface of the bush 12, and the effective friction width L2 of the outer surface of the bush 12 is It is formed smaller than the effective friction width L 1 of the inner surface of.
また、第２図に示すフローテイングブツシユ２
２においては、同ブツシユ２２の軸方向中央部に
給油穴２２ｂが穿設され、この給油穴２２ｂの近
傍に切り欠き部２２ａが形成されて、ブツシユ２
２の外面の有効摩擦幅L2（＝l1＋l2，l1l2）が同
ブツシユ２２の内面の有効摩擦幅L1よりも小さ
く形成されている。 In addition, floating bush 2 shown in Fig. 2
In No. 2, an oil supply hole 22b is bored in the axial center of the bush 22, and a notch 22a is formed near this oil supply hole 22b.
The effective friction width L 2 (=l 1 +l 2 , l 1 l 2 ) on the outer surface of the bush 22 is smaller than the effective friction width L 1 on the inner surface of the bush 22.
さらに、第３図に示すフローテイングブツシユ
３２においては、同ブツシユ３２の軸方向中央位
置よりもやや離れた位置（第３図において右方向
寄りの位置）に給油穴３２ｂが穿設され、この給
油穴３２ｂの近傍に切り欠き部３２ａが形成され
て、ブツシユ３２の外面の有効摩擦幅L2（＝l3＋
l4，l3＞l4）が同ブツシユ３２の内面の有効摩擦
幅L1よりも小さく形成されている。 Furthermore, in the floating bush 32 shown in FIG. 3, a refueling hole 32b is drilled at a position slightly away from the axial center position of the bush 32 (a position closer to the right in FIG. 3). A notch 32a is formed near the oil supply hole 32b, and the effective friction width L 2 (=l 3 +
l 4 , l 3 >l 4 ) is smaller than the effective friction width L 1 of the inner surface of the bush 32.
ところで、互いに逆方向に同一回転速度で回転
する内部円筒面と外部円筒面とにより、フローテ
イングブツシユ１２（または２２，３２）の内面
および外面がそれぞれ受ける潤滑流体の粘性剪断
力に基づくモーメントT1とT2とは、近似的に次
式に示すような関係にある。 By the way, the moment T based on the viscous shearing force of the lubricating fluid that is applied to the inner and outer surfaces of the floating bushing 12 (or 22, 32) by the inner and outer cylindrical surfaces that rotate in opposite directions at the same rotational speed. 1 and T 2 have a relationship approximately as shown in the following equation.
T1＝T2
ただし、
ここで、
π：円周率（3.141592）
μ：潤滑流体粘度
r1：フローテイングブツシユ１２（または２
２，３２）の内径
r2：フローテイングブツシユ１２（または２
２，３２）の最大外径
C1：フローテイングブツシユ１２（または２
２，３２）の内面と内部円筒面とのすき間
C2：フローテイングブツシユ１２（または２
２，３２）の外面との外部円筒面との最小すき間
L1：フローテイングブツシユ１２（または２
２，３２）の内面の有効摩擦幅
L2：フローテイングブツシユ１２（または２
２，３２）の外面の有効摩擦幅
N1：フローテイングブツシユ１２（または２
２，３２）の内部円筒面に対する相対回転数差
N2：フローテイングブツシユ１２（または２
２，３２）の外部円筒面に対する相対回転数差
n1：フローテイングブツシユ１２（または２
２，３２）の内部円筒面に対する偏心率
n2：フローテイングブツシユ１２（または２
２，３２）の外部円筒面に対する偏心率
また、フローテイングブツシユ１２（または２
２，３２）において切り欠き部１２ａ（または２
２ａ，３２ａ）を形成した場合に、同フローテイ
ングブツシユ１２（または２２，３２）が、強度
上あるいは潤滑上の点で支障をきたさないように
するためには、その形状の実用的な条件範囲とし
て次のような値が設定される。 T 1 = T 2 However, Here, π: Pi (3.141592) μ: Lubricating fluid viscosity r 1 : Floating bush 12 (or 2
2, 32) inner diameter r 2 :Floating bush 12 (or 2)
2, 32) maximum outer diameter C 1 : Floating bush 12 (or 2
Gap C 2 between the inner surface of the floating bush 12 (or 2) and the internal cylindrical surface
Minimum clearance L 1 between the outer surface of floating bush 12 (or 2) and the outer cylindrical surface of floating bush 12 (or 2
Effective friction width L 2 on the inner surface of floating bush 12 (or 2)
Effective friction width N 1 of the outer surface of floating bush 12 (or 2)
2, 32) relative rotational speed difference with respect to the internal cylindrical surface N 2 : Floating bush 12 (or 2
2, 32) relative rotational speed difference with respect to the external cylindrical surface n 1 : Floating bush 12 (or 2
Eccentricity n 2 with respect to the internal cylindrical surface of floating bush 12 (or 2)
2, 32) with respect to the external cylindrical surface.
2, 32), the notch 12a (or 2
2a, 32a), in order to ensure that the floating bush 12 (or 22, 32) does not pose any problems in terms of strength or lubrication, the practical conditions of its shape must be met. The following values are set as the range.
r2／r1＝1.2〜1.3 ……(3)
C2／C1＝1.0〜1.8 ……(4)
n1，n2＝0.85〜0.95 ……(5)
これらの条件(3)〜(5)に基づいて(1)，(2)式を解
き、フローテイングブツシユ１２（または２２，
３２）の内外面の有効摩擦幅比L1／L2と、フロ
ーテイングブツシユ１２（または２２，３２）の
回転数Nbと外部円筒面または内部円筒面の回転
数Noとの比Nb／Noとの関係を求めたものを第
４図のグラフに示す。ただし、このグラフにおい
て、破線p1，p2はr2／r1＝1.2の場合を示し、C1，
C2，n1，n2の値により上記関係を表す曲線はこれ
らの破線p1，p2間に存在する。また、実線p3，p4
はr2／r1＝1.3の場合を示し、C1，C2，n1，n2の値
により上記関係を表す曲線はこれらの実線p3，p4
間に存在する。 r 2 / r 1 = 1.2 to 1.3 ... (3) C 2 / C 1 = 1.0 to 1.8 ... (4) n 1 , n 2 = 0.85 to 0.95 ... (5) These conditions (3) to ( Solve equations (1) and (2) based on 5) and calculate floating bush 12 (or 22,
32) effective friction width ratio L 1 /L 2 of the inner and outer surfaces and the ratio Nb / No of the rotation speed Nb of the floating bush 12 (or 22, 32) and the rotation speed No of the outer cylindrical surface or the inner cylindrical surface The graph in Figure 4 shows the relationship between However, in this graph, the broken lines p 1 and p 2 indicate the case where r 2 /r 1 = 1.2, and C 1 ,
A curve expressing the above relationship based on the values of C 2 , n 1 , and n 2 exists between these broken lines p 1 and p 2 . Also, solid lines p 3 , p 4
indicates the case of r 2 /r 1 = 1.3, and the curve representing the above relationship by the values of C 1 , C 2 , n 1 , n 2 is the solid line p 3 , p 4
exists between.
第４図から明らかなように、強度上あるいは潤
滑上の条件(3)〜(5)を満たしながら、フローテイン
グブツシユ１２（または２２，３２）の回転数
Nb（つまりNb／No＝０）とするためには、フロ
ーテイングブツシユ１２（または２２，３２）の
内外面の有効摩擦幅比L1／L2が、
L1／L2＝1.2〜2.0 ……(6)
を満たすように、フローテイングブツシユ１２
（または２２，３２）を形成する。 As is clear from Fig. 4, the number of rotations of the floating bush 12 (or 22, 32) is
In order to obtain Nb (that is, Nb/No=0), the effective friction width ratio L 1 /L 2 of the inner and outer surfaces of the floating bush 12 (or 22, 32) must be L 1 /L 2 = 1.2 to 2.0. ……(6) Floating bush 12
(or 22, 32).
上述の構成により、本考案の一実施例としての
フローテイングブツシユ付き軸受装置では、フロ
ーテイングブツシユ１２（または２２，３２）
が、強度上あるいは潤滑上で支障をきたすことな
く、同一中心線のまわりに互いに逆方向に同一回
転速度で回転する外部円筒面と内部円筒面との相
互間において、静止状態に保持されるようになる
ので、フローテイングブツシユ１２（または２
２，３２）の内外面の、それぞれ、内部円筒面お
よび外部円筒面との相対すべり速度は等しくな
る。 With the above-described configuration, in the bearing device with a floating bush as an embodiment of the present invention, the floating bush 12 (or 22, 32)
is maintained in a stationary state between an outer cylindrical surface and an inner cylindrical surface that rotate at the same rotational speed in opposite directions around the same center line without causing problems in terms of strength or lubrication. Therefore, floating bush 12 (or 2
The relative sliding speeds of the inner and outer surfaces of 2 and 32) with respect to the inner and outer cylindrical surfaces are equal, respectively.
したがつて、フローテイングブツシユ１２（ま
たは２２，３２）の内外面側において、それぞれ
流体力学的な流体潤滑膜を良好な状態で形成する
こが可能となり、軸受の焼付きや異常摩耗などの
損傷の発生を確実に防止できるのである。 Therefore, it is possible to form a hydrodynamic fluid lubricant film in good condition on the inner and outer surfaces of the floating bushing 12 (or 22, 32), thereby preventing bearing seizure and abnormal wear. This makes it possible to reliably prevent damage from occurring.
以上詳述したように、本考案のフローテイング
ブツシユ付き軸受装置によれば、同一中心線のま
わりに互いに逆方向に同一回転速度で回転する外
部円筒面と内部円筒面との相互間にフローテイン
グブツシユをそなえ、同ブツシユの外面の有効摩
擦幅が同ブツシユの内面の有効摩擦幅よりも小さ
く形成され、同ブツシユの外面と内面とが次の３
つの条件、すなわち、
(1) r2／r1＝1.2〜1.3
ただし、
r1は上記ブツシユの内径
r2は上記ブツシユの最大外径
(2) C2／C1＝１，０〜1.8
ただし、
C1は上記ブツシユの内面と上記内部円筒面
とのすき間
C2は上記ブツシユの外面と上記外部円筒面
との最小すき間
(3) L1／L2＝1.2〜2.0
ただし、
L1は上記ブツシユの内面の有効摩擦幅
L2は上記ブツシユの外面の有効摩擦幅
を満たすように形成されるという簡素な構成で、
フローテイングブツシユは、強度上あるいは潤滑
上で支障をきたすことなく、静止状態に保持され
るようになり、これにより、軸受の焼付きや異常
摩耗等の損傷の発生を確実に回避できるのであ
る。
As described in detail above, according to the bearing device with a floating bush of the present invention, there is a flow between the outer cylindrical surface and the inner cylindrical surface that rotate at the same rotational speed in opposite directions around the same center line. The bushing is provided with a sliding bush, the effective friction width of the outer surface of the bushing is smaller than the effective friction width of the inner surface of the bushing, and the outer surface and inner surface of the bushing are formed in the following three types.
Two conditions, namely: (1) r 2 / r 1 = 1.2 to 1.3, where r 1 is the inner diameter of the bush, r 2 is the maximum outer diameter of the bush (2) C 2 / C 1 = 1,0 to 1.8, but , C 1 is the gap between the inner surface of the bush and the inner cylindrical surface, C 2 is the minimum gap between the outer surface of the bush and the outer cylindrical surface (3) L 1 /L 2 = 1.2 to 2.0 However, L 1 is the above It has a simple structure in which the effective friction width L 2 of the inner surface of the bush is formed to satisfy the effective friction width of the outer surface of the bush.
Floating bushes can now be held stationary without compromising strength or lubrication, thereby reliably avoiding damage such as bearing seizure or abnormal wear. .
第１〜４図は本考案の一実施例としてのフロー
テイングブツシユ付き軸受装置を示すもので、第
１図はそのフローテイングブツシユの縦断面図、
第２図はそのフローテイングブツシユの変形例を
示す縦断面図、第３図はそのフローテイングブツ
シユの他の変形例を示す縦断面図、第４図は、そ
のフローテイングブツシユの内外面の有効摩擦幅
比（L1／L2）と、同ブツシユの回転数と軸回転
数との比（Nb／No）との関係を示すグラフであ
り、第５，６図は従来のフローテイングブツシユ
付き軸受装置を示すもので、第５図はその縦断面
図、第６図は第５図の−矢視断面図である。
１２……フローテイングブツシユ、１２ａ……
切り欠き部、２２……フローテイングブツシユ、
２２ａ……切り欠き部、２２ｂ……給油穴、３２
……フローテイングブツシユ、３２ａ……切り欠
き部、３２ｂ……給油穴。
1 to 4 show a bearing device with a floating bushing as an embodiment of the present invention, and Fig. 1 is a vertical sectional view of the floating bushing;
Fig. 2 is a vertical sectional view showing a modification of the floating bush, Fig. 3 is a longitudinal sectional view showing another variation of the floating bush, and Fig. 4 is an internal view of the floating bush. This is a graph showing the relationship between the effective friction width ratio of the outer surface (L 1 /L 2 ) and the ratio of the rotation speed of the bush to the shaft rotation speed (Nb / No). 5 is a longitudinal cross-sectional view thereof, and FIG. 6 is a cross-sectional view taken along the - arrow in FIG. 5. 12...Floating bush, 12a...
Notch part, 22...floating button,
22a... Notch, 22b... Oil supply hole, 32
...Floating bush, 32a...Notch, 32b...Oil supply hole.
Claims (1)
速度で回転する外部円筒面と内部円筒面との相互
間にフローテイングブツシユをそなえ、同ブツシ
ユの外面の有効摩擦幅が同ブツシユの内面の有効
摩擦幅よりも小さく形成され、同ブツシユの外面
と内面とが次の３つの条件を満たすように形成さ
れたことを特徴とする、フローテイングブツシユ
付き軸受装置。 (1) r2／r1＝1.2〜1.3 ただし、 r1は上記ブツシユの内径 r2は上記ブツシユの最大外径。 (2) C2／C1＝１，０〜1.8 ただし、 C1は上記ブツシユの内面と上記内部 円筒
面とのすき間 C2は上記ブツシユの外面と上記外部 円筒
面との最小すき間。 (3) L1／L2＝1.2〜2.0 ただし、 L1は上記ブツシユの内面の有効摩擦幅 L2は上記ブツシユの外面の有効摩擦幅。[Claims for Utility Model Registration] A floating bush is provided between an outer cylindrical surface and an inner cylindrical surface that rotate at the same rotational speed in opposite directions around the same center line, and the effective friction of the outer surface of the bush is provided. A bearing device with a floating bush, characterized in that the width is smaller than the effective friction width of the inner surface of the bush, and the outer and inner surfaces of the bush are formed to satisfy the following three conditions. (1) r 2 / r 1 = 1.2 to 1.3, where r 1 is the inner diameter of the bush, and r 2 is the maximum outer diameter of the bush. (2) C 2 /C 1 = 1,0 to 1.8, where C 1 is the gap between the inner surface of the bush and the inner cylindrical surface, and C 2 is the minimum gap between the outer surface of the bush and the outer cylindrical surface. (3) L 1 /L 2 = 1.2 to 2.0, where L 1 is the effective friction width on the inner surface of the bushing, and L 2 is the effective friction width on the outer surface of the bushing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1986047965U JPH0419232Y2 (en) | 1986-03-31 | 1986-03-31 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1986047965U JPH0419232Y2 (en) | 1986-03-31 | 1986-03-31 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62163324U JPS62163324U (en) | 1987-10-17 |
| JPH0419232Y2 true JPH0419232Y2 (en) | 1992-04-30 |
Family
ID=30869059
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1986047965U Expired JPH0419232Y2 (en) | 1986-03-31 | 1986-03-31 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0419232Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE112019002201T5 (en) | 2018-04-27 | 2021-01-07 | Ihi Corporation | Bearings and turbochargers |
-
1986
- 1986-03-31 JP JP1986047965U patent/JPH0419232Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62163324U (en) | 1987-10-17 |
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