JP3457833B2 - Bearing device - Google Patents
Bearing deviceInfo
- Publication number
- JP3457833B2 JP3457833B2 JP08577297A JP8577297A JP3457833B2 JP 3457833 B2 JP3457833 B2 JP 3457833B2 JP 08577297 A JP08577297 A JP 08577297A JP 8577297 A JP8577297 A JP 8577297A JP 3457833 B2 JP3457833 B2 JP 3457833B2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- shaft
- pedestal
- bearing portion
- thrust force
- 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 - Fee Related
Links
Landscapes
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、軸受け装置に関
し、特にスラスト力を受ける回転軸、例えば舶用のディ
ーゼル機関のクランク回りの主軸受けなどに用いられる
軸受け装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing device, and more particularly to a bearing device used for a rotary shaft which receives a thrust force, for example, a main bearing around a crank of a diesel engine for ships.
【０００２】[0002]
【従来の技術】ディーゼル機関等の主軸受け装置には、
すべり軸受けが用いられることが多い。このようなすべ
り軸受けは、通常、図１０の軸受け装置Ｂに示すよう
に、組立の便宜を図って上下方向に半割りされた軸受け
部材２ａ、２ｂで構成した軸受け部２を台座１上に組み
込むと共に、上方から軸受けキャップ３を組み付けて台
座１に固定する。さらに、該軸受け部２は軸４と接触す
る面である軸受け面５を軸方向に同一内径ｄoに形成
し、外径面６を軸方向に同一外径Ｄoに形成した円筒形
である。さらに、軸受け部２はクランク軸４を回転自在
に支持し、かつ軸４の重量を受けるようになっている。
前記クランク軸４は、図１１及び図１２に示すように押
圧部であるスラストカラー８を設けている構造を取る。2. Description of the Related Art In main bearing devices such as diesel engines,
Sliding bearings are often used. In such a sliding bearing, as shown in a bearing device B in FIG. 10, a bearing portion 2 constituted by bearing members 2a and 2b which are vertically divided in half for the convenience of assembly is usually incorporated on a pedestal 1. At the same time, the bearing cap 3 is assembled from above and fixed to the base 1. Further, the bearing portion 2 has a cylindrical shape in which a bearing surface 5 which is a surface in contact with the shaft 4 is formed to have the same inner diameter do in the axial direction and an outer diameter surface 6 is formed to have the same outer diameter Do in the axial direction. Further, the bearing portion 2 rotatably supports the crankshaft 4 and receives the weight of the shaft 4.
As shown in FIGS. 11 and 12, the crankshaft 4 has a structure in which a thrust collar 8 as a pressing portion is provided.
【０００３】[0003]
【発明が解決しようとする課題】ところで、前述した従
来のこの種の軸受け装置では、以下のような問題があっ
た。例えばディーゼル機関を船舶の主機として運転する
ときに、図１１、及び図１１のＡ視図である図１２から
明らかなように、クランク軸４は推進力の反力であるス
ラスト力Ｔを中心線Ｘ−Ｘに沿った方向に受けるため
に、クランク軸４に設けた押圧部であるスラストカラー
８がスラスト力により軸受け部２（２ａ，２ｂ）又は台
座１を押圧する。そのため、台座１又は軸受け部２（２
ａ，２ｂ）は、矢印Ｃで示すようにスラスト負荷方向に
屈曲してテーパ状に広がり変形した。その結果、クラン
ク軸４と接触する軸受け面５の該軸４に対する相対位置
関係において、符号９で示すように局部的な線、あるい
は点当たり状態を生じ、該局部的な当たり９を生じた部
分に高い面圧が発生し、潤滑油膜の減少、及び軸受け部
２への過大な変形応力が生じた。また、軸受け面５が局
部的に摩耗して軸受け装置を損傷させ、軸受け装置の負
荷能力の低下を招来した。The conventional bearing device of this type described above, however, has the following problems. For example, when the diesel engine is operated as the main engine of a ship, as is apparent from FIG. 11 and FIG. 12 which is a view A of FIG. 11, the crankshaft 4 causes the thrust force T, which is a reaction force of the propulsion force, to be centerline. The thrust collar 8, which is a pressing portion provided on the crankshaft 4, presses the bearing portion 2 (2a, 2b) or the pedestal 1 by the thrust force in order to receive in the direction along XX. Therefore, the base 1 or the bearing 2 (2
a and 2b) were bent in the thrust load direction and expanded and deformed in a taper shape as shown by arrow C. As a result, in the relative positional relationship of the bearing surface 5 in contact with the crankshaft 4 with respect to the shaft 4, a local line or a point contact state is generated as indicated by reference numeral 9, and a portion where the local contact 9 is generated. High surface pressure was generated on the surface of the bearing, and the lubricating oil film was reduced, and excessive deformation stress was applied to the bearing 2. Further, the bearing surface 5 is locally worn to damage the bearing device, resulting in a decrease in the load capacity of the bearing device.
【０００４】しかも、従来はこれらの局部当たり９に対
処するためには、なじみ運転をした後に、軸と接触する
面（軸受け面）５を目視により確認し、該軸受け面５を
軸の中心線とのアラインメント調整を行い、さらには手
作業による当たり付けを行っていたので、このような作
業が煩雑で、軸受け装置の価格も高価となった。In addition, conventionally, in order to deal with these 9 points per local area, after the running-in operation, the surface (bearing surface) 5 that comes into contact with the shaft is visually confirmed, and the bearing surface 5 is used as the center line of the shaft. Since the alignment adjustment with and the hitting by hand were performed, such work is complicated and the price of the bearing device becomes expensive.
【０００５】本発明の目的は、かかる従来の問題点を解
決するためになされたもので、軸受け部又は台座がスラ
スト力を受けても、軸と接触する面に局部当たりが発生
するのを防止した軸受け装置を提供することにある。The object of the present invention is to solve the above-mentioned problems of the prior art. Even if the bearing portion or the pedestal receives a thrust force, it is possible to prevent local contact from occurring on the surface in contact with the shaft. The present invention is to provide a bearing device.
【０００６】[0006]
【課題を解決するための手段】本発明は、前述の技術的
課題を解決するために、請求項１記載の発明において
は、軸線方向にスラスト力を受ける軸と、前記軸を支持
するための台座と、前記軸と台座の間に設置される軸受
け部と、前記軸と一体又は軸に固定され、軸が受けたス
ラスト力により軸受け部又は台座を押す押圧部とからな
る軸受け装置において、前記軸と接触する軸受け部の、
前記押圧部側端面内径をｄ1、他端側端面内径をｄ2とし
た場合に、ｄ1からｄ2に向けて（ｄ1＞ｄ2）となるよう
に、前記両端面間の軸受け面をテーパ状に加工するとと
もに、前記軸受け部が上下方向に半割りされ、下側の軸
受け部に傾きを設けて前記テーパ形状を形成させたこと
を特徴とする。In order to solve the above-mentioned technical problems, the present invention provides a shaft for receiving a thrust force in an axial direction and a shaft for supporting the shaft. a pedestal, and a bearing portion which is disposed between the shaft and the base, fixed to the shaft and integral or axis, in a bearing apparatus comprising a pressing part pressing the bearing unit or the base by the thrust force the shaft is received, the Of the bearing part that contacts the shaft,
The inner diameter of the end surface on the pressing portion side is d1, and the inner diameter of the end surface on the other end side is d2.
In case of, it becomes (d1> d2) from d1 to d2
In addition, the bearing surface between the both end surfaces is processed into a taper shape, and the bearing portion is vertically divided into halves.
It is characterized in that the receiving portion is inclined to form the tapered shape .
【０００７】請求項２記載の発明は、軸線方向にスラス
ト力を受ける軸と、前記軸を支持するための台座と、前
記軸と台座の間に設置される軸受け部と、前記軸と一体
又は軸に固定され、軸が受けたスラスト力により軸受け
部又は台座を押す押圧部とからなる軸受け装置におい
て、前記軸受け部の前記台座と接触する外径面を、押圧
部（スラストカラー）側外径をＤ1、他端側外径をＤ2と
した場合に、Ｄ1からＤ2に向けて次第に外径を増して
（Ｄ1＜Ｄ2）となるようにテーパ状に加工するととも
に、前記軸の運転時に、前記押圧部からのスラスト力に
より変形した軸受け部と軸受け部の軸と接触する面が軸
と平行に沿う形状となるように前記テーバ形状を設定し
たことを特徴とする。According to a second aspect of the present invention, a shaft that receives a thrust force in the axial direction, a pedestal for supporting the shaft, a bearing portion installed between the shaft and the pedestal, and the shaft are integral with or In a bearing device fixed to a shaft and comprising a bearing portion or a pressing portion that pushes the pedestal by the thrust force received by the shaft, the outer diameter surface of the bearing portion that contacts the pedestal is pressed.
The outer diameter on the part (thrust collar) side is D1, and the outer diameter on the other end side is D2.
If you do, gradually increase the outer diameter from D1 to D2
It is machined into a taper shape so that (D1 <D2) and the thrust force from the pressing part is applied when the shaft is in operation.
The more deformed bearing and the surface of the bearing that contacts the shaft is the shaft.
Set the above-mentioned taper shape so that it will be parallel to
Characterized in that was.
【０００８】なお、本発明の主たる構成要素を詳細に説
明すると、
（軸）本発明における軸には、内燃機関のクランク軸、
工作機械の主軸、大型タービン軸など、軸の種類は問わ
ない。
（軸受け部）本発明において、軸受け部はすべり軸受け
であり、軸の回転中に軸と接触する面（軸受け面）で軸
を回転自在に支えるものであり、組み込みを容易にする
ために二つ割りに形成しても又一体型としてもよい。ま
た、軸受け部の構成材料には軸よりも軟らかくて摩擦抵
抗の少ない材料、例えばホワイトメタル、ケルメット、
りん青銅、砲金などの金属、あるいは多孔質の焼結合
金、自己潤滑性のある合成樹脂、例えばフッ素樹脂など
多くのものを例示することができる。
（台座）本発明における台座は、軸受け部を支持するも
のであれば、その種類を問わない。そのために、台座は
軸受けを直立状態に取り付けるペデスタル軸受け、壁に
取り付けるブラケット形軸受け、天井から吊り下げるよ
うに構成するハンガー形軸受けなどに適用される台座を
含むものである。The main components of the present invention will be described in detail. (Shaft) The shaft in the present invention includes a crankshaft of an internal combustion engine,
The type of shaft, such as the main shaft of a machine tool or large turbine shaft, does not matter. (Bearing portion) In the present invention, the bearing portion is a sliding bearing, and rotatably supports the shaft by a surface (bearing surface) that comes into contact with the shaft during rotation of the shaft. It may be formed or integrated. Further, the material of the bearing portion is softer than the shaft and has less friction resistance, such as white metal, kelmet,
Examples thereof include metals such as phosphor bronze and gun metal, porous sintered alloys, self-lubricating synthetic resins such as fluororesins, and the like. (Pedestal) The pedestal in the present invention may be of any type as long as it supports the bearing. Therefore, the pedestal includes a pedestal bearing for mounting the bearing in an upright state, a bracket type bearing for mounting on a wall, a hanger type bearing configured to be suspended from the ceiling, and the like.
【０００９】請求項１記載の発明によれば、軸受け部の
軸と接触する面、すなわち軸と摺動する軸受け面を、ス
ラスト力付加による軸受け部の変形や傾きに対応して予
めテーパ状に加工してあるから、スラスト力が軸受け部
にかかりスラスト負荷方向に屈曲してしても、前記予備
テーパによって相殺され、軸と摺動する軸受け面は軸と
平行面を維持する事が出来、この結果軸受け面の軸に対
する局部的な線或いは点当たりが生じることはなくま
た、軸受け面が局部的に摩耗することなく均一な面圧維
持が図られ、負荷能力を増加させる。According to the first aspect of the invention, the surface of the bearing portion that contacts the shaft, that is, the bearing surface that slides with the shaft, is tapered in advance in response to deformation or inclination of the bearing portion due to the thrust force. Since it has been processed, even if the thrust force is applied to the bearing portion and bent in the thrust load direction, it is offset by the preliminary taper, and the bearing surface that slides with the shaft can be maintained parallel to the shaft, As a result, a local line or point contact with the shaft of the bearing surface does not occur, the bearing surface is not locally worn, and a uniform surface pressure is maintained to increase the load capacity.
【００１０】また請求項２記載の発明によれば、前記軸
受け部の前記台座と接触する面を、スラスト力付加によ
る台座の変形や傾きに対応して予めテーパ状に加工して
あるから、スラスト力が軸受け部や台座にかかり台座が
スラスト負荷方向に屈曲してしても、前記予備テーパに
よって相殺され、軸と摺動する軸受け面は軸と平行面を
維持する事が出来、この結果軸受け面の軸に対する局部
的な線或いは点当たりが生じることはなく、また、軸受
け面が局部的に摩耗することなく均一な面圧維持が図ら
れ、負荷能力を増加させるとともに軸受け部が台座から
脱落することはない。Further, according to the second aspect of the present invention, the surface of the bearing portion contacting the pedestal is preliminarily processed into a taper shape corresponding to the deformation or inclination of the pedestal due to the thrust force applied. Even if the force is applied to the bearing part and the pedestal and the pedestal bends in the thrust load direction, it is offset by the preliminary taper, and the bearing surface that slides with the shaft can maintain a parallel surface with the shaft. There is no local line or point contact with the shaft of the surface, and even bearing pressure is maintained without local wear of the bearing surface, increasing the load capacity and the bearing part falling off from the pedestal. There is nothing to do.
【００１１】[0011]
【発明の実施の形態】以下、本発明の軸受け装置を図に
示される実施形態について更に詳細に説明する。但し、
この実施形態に記載されている構成部品の寸法、材質、
形状、その相対的配置等は特定的な記載がない限りは、
この発明の範囲をそれに限定する趣旨ではなく、単なる
説明例にすぎない。図面には本発明の実施形態に係る軸
受け装置が符号Ｂで示されている。そして、図１は本発
明の第１実施形態の正面図を示し、図２は図１のＹ−Ｙ
線断面である。図３は軸の停止時における軸受け装置の
縦断面、図４は軸の回転時にスラスト力を受けた状態の
同縦断面を示す。また、図５は図３のＡ方向から視た軸
の停止時の軸受け装置の横断面、図６は軸の回転時にス
ラスト力を受けた状態の同横断面を示す。BEST MODE FOR CARRYING OUT THE INVENTION The bearing device of the present invention will be described below in more detail with reference to the embodiments shown in the drawings. However,
The dimensions, materials, and components of the components described in this embodiment
Unless otherwise specified in terms of shape, relative arrangement, etc.
The scope of the present invention is not intended to be limited thereto, but is merely an illustrative example. In the drawings, the bearing device according to the embodiment of the present invention is indicated by reference numeral B. 1 shows a front view of the first embodiment of the present invention, and FIG. 2 shows YY of FIG.
It is a line cross section. FIG. 3 shows a vertical cross section of the bearing device when the shaft is stopped, and FIG. 4 shows the same vertical cross section in a state in which a thrust force is applied when the shaft rotates. 5 shows a cross section of the bearing device when the shaft is stopped as viewed from the direction A of FIG. 3, and FIG. 6 shows the same cross section in a state in which a thrust force is applied when the shaft rotates.
【００１２】前記夫々の図において軸受け装置Ｂは、軸
線Ｘ−Ｘに沿った方向にスラスト力Ｔを受ける軸４と、
前記軸４を支えるための台座１と、前記軸４と台座１の
間に設置される軸受け部２と、前記軸４と一体又は軸４
に固定され、軸４が受けたスラスト力Ｔにより軸受け部
２又は台座１を押すスラストカラー（押圧部）８とから
なる。そして、舶用ディーゼル機関のクランク軸回りの
軸受け装置として適用した場合を図９に基づいて説明す
ると、オイルパン１１に台板軸受け台である台座１を立
設し、図１に示すように台座１に軸受けキャップ３をボ
ルト１５及びナット１６で固定することにより軸受け部
２を組み込むと共に、軸受け部２にクランク軸４を回転
自在に支持する。また、クランク軸４には押圧部である
スラストカラー８が軸４と一体又は軸４に固定されてい
る。In each of the above figures, the bearing device B comprises a shaft 4 which receives a thrust force T in a direction along the axis XX,
A pedestal 1 for supporting the shaft 4, a bearing portion 2 installed between the shaft 4 and the pedestal 1, and an integral part of the shaft 4 or the shaft 4.
And a thrust collar (pressing portion) 8 that presses the bearing portion 2 or the pedestal 1 by the thrust force T received by the shaft 4. A case of application as a bearing device around a crankshaft of a marine diesel engine will be described with reference to FIG. 9. A pedestal 1, which is a base plate bearing pedestal, is erected on an oil pan 11, and as shown in FIG. The bearing cap 2 is assembled by fixing the bearing cap 3 with the bolt 15 and the nut 16, and the crankshaft 4 is rotatably supported by the bearing unit 2. A thrust collar 8 that is a pressing portion is fixed to the crankshaft 4 either integrally with the shaft 4 or on the shaft 4.
【００１３】前記軸受け部２は組立に便利なように上下
方向に半割りされた軸受け部材２ａ、２ｂで構成され
る。また、軸受け部材２ａ、２ｂのうち、台座１側に取
り付けられた軸受け部材２ａを、機関の運転時に軸受け
装置Ｂに加わる荷重及びスラスト力付加による台座１の
傾き、及び軸受け部２の軸と接触する面（軸受け面）５
のテーパ形状の広がり変形を予め計算解析にて求めてお
き、図２に示すようにクランク軸４と接触する面、すな
わち軸受け面５をテーパ状に加工して、運転時に生ずる
軸４と軸受け面５との相対傾きを無くしている。６は外
径面である。The bearing portion 2 is composed of bearing members 2a and 2b which are vertically divided in half for convenience of assembly. Further, of the bearing members 2a and 2b, the bearing member 2a attached to the pedestal 1 side is brought into contact with the shaft of the bearing portion 2 and the inclination of the pedestal 1 due to the load and thrust force applied to the bearing device B during engine operation. Surface (bearing surface) 5
The spread deformation of the taper shape is previously obtained by calculation analysis, and as shown in FIG. 2, the surface contacting the crankshaft 4, that is, the bearing surface 5 is processed into a taper shape, and the shaft 4 and the bearing surface generated during operation are The relative inclination with 5 is eliminated. 6 is an outer diameter surface.
【００１４】上記のように軸と接触する面（軸受け面）
５をテーパ状に加工するために、軸受け部２の内径は図
２に示すように両端面においてそれぞれｄ1、ｄ2（ｄ1
＞ｄ2）であり、両端面間の距離（軸受け幅）Ｌは、テ
ーパ形状（ｄ1−ｄ2）／２Ｌ＝１．８〜６．０×１０-4
（rad）、軸受け外径は同一外径Ｄoで加工してある。ま
た、軸受け部２の両端面に面取り７を施してある。As described above, the surface that contacts the shaft (bearing surface)
In order to machine 5 into a tapered shape, the inner diameter of the bearing 2 is d1 and d2 (d1
> D2), and the distance (bearing width) L between both end surfaces is tapered (d1-d2) /2L=1.8 to 6.0 × 10 −4
(Rad), the bearing outer diameter is machined to have the same outer diameter Do. Further, chamfers 7 are provided on both end surfaces of the bearing portion 2.
【００１５】なお、テーパ形状を本実施形態において前
記の値に設定したのは、舶用内燃機関の主軸受け装置が
運転時にスラスト力を受けた場合の傾きを調査したとこ
ろ表１の通りの結果が得られたことに基づく。よって、
スラスト力Ｔを受ける軸受け部２は０〜６．０×１０ー4
（rad）の範囲内で傾き、軸４と軸受け面５の局部的当
たりによる局部面圧の上昇を引き起こすことが分かった
ので、本実施形態ではかかる局部的当たりによる面圧の
上昇を軽減するために、軸受け部２のテーパ形状を、前
記傾きと同程度に形成してある。しかしながら、前記の
テーパ度は本発明の必須事項ではなく、本発明に係る軸
受け装置を適用する機関、装置等により適宜実施しうる
選択的事項であることは言うまでもない。The taper shape is set to the above value in the present embodiment. When the main bearing of the marine internal combustion engine receives a thrust force during operation, the inclination shown in Table 1 is obtained. Based on what was obtained. Therefore,
Bearing unit 2 which receives the thrust force T is 0 to 6.0 × 10 -4
It has been found that the inclination in the range of (rad) causes the local surface pressure to increase due to the local contact between the shaft 4 and the bearing surface 5. Therefore, in the present embodiment, in order to reduce the increase in the surface pressure due to the local contact. In addition, the tapered shape of the bearing 2 is formed to the same extent as the inclination. However, it goes without saying that the above-mentioned taper degree is not an essential item of the present invention, but is an optional item that can be appropriately implemented by an engine, a device or the like to which the bearing device of the present invention is applied.
【００１６】[0016]
【表１】 [Table 1]
【００１７】さらに、クランク軸４は後端にスクリュー
１２が取り付けられており（図９参照）、クランク軸４
に形成されるアーム１３を連結するクランクピン１４に
摺動可能に組み込まれた図示しないコネクティングロッ
ドを介してピストンに連設される。そして、クランク軸
４は、シリンダ内をシリンダ中心線Ｆに沿って往復動す
るピストンの運動を受けて回転するようになっている。Further, the crankshaft 4 has a screw 12 attached to its rear end (see FIG. 9).
Is connected to the piston through a connecting rod (not shown) slidably incorporated in a crank pin 14 connecting the arm 13 formed in the above. The crankshaft 4 is adapted to rotate in response to the movement of the piston that reciprocates in the cylinder along the cylinder center line F.
【００１８】次に、本発明の実施の形態にかかる軸受け
装置の作用を図３〜図６に基づいて説明する。図３及び
図５に示すディーゼル機関の停止時では、軸受け部２の
うち台座１側に固定された軸受け部材２ａの軸４と接触
する面、すなわち軸受け面５には、前記したように予め
計算され解析された軸受け面に生じる傾きに対応して、
テーパ状に加工されている。Next, the operation of the bearing device according to the embodiment of the present invention will be described with reference to FIGS. When the diesel engine shown in FIGS. 3 and 5 is stopped, the surface of the bearing portion 2 that is in contact with the shaft 4 of the bearing member 2a fixed to the pedestal 1 side, that is, the bearing surface 5, is calculated in advance as described above. Corresponding to the tilt that occurs in the bearing surface analyzed and analyzed,
It is processed into a taper shape.
【００１９】いま、機関が運転を始めると、軸（クラン
ク軸）４は推進力の反力であるスラスト力Ｔを受け、さ
らに該軸４と一体又は軸に固定された押圧部８が台座１
を押圧し、図４及び図６に示すように台座１は矢印Ｃで
示すように傾いて広がり、変形する。そのため台座１に
取り付けられた軸受け部２ａも台座１の変形に伴って軸
方向にテーパ状に広がる。しかし、予め台座１の傾きに
よるテーパ形状の広がりに対応して、軸受け部２の軸４
と接触する面５にテーパ面加工されているために、スラ
スト力Ｔを受けても、軸受け部２の軸４と接触する面
（軸受け面）５が軸４と平行に沿う形状となる。このた
め、軸４と接触する面５に局部当たりが発生せず、該面
５の全体が有効に作用する。Now, when the engine starts to operate, the shaft (crankshaft) 4 receives a thrust force T which is a reaction force of the propulsion force, and a pressing portion 8 which is integral with or fixed to the shaft 4 is mounted on the pedestal 1
4 is pressed, the pedestal 1 is inclined and expanded as shown by an arrow C, and is deformed. Therefore, the bearing portion 2a attached to the pedestal 1 also expands in a taper shape in the axial direction as the pedestal 1 is deformed. However, the shaft 4 of the bearing portion 2 is previously corresponding to the spread of the tapered shape due to the inclination of the pedestal 1.
Since the surface 5 that comes into contact with is tapered, the surface (bearing surface) 5 that comes into contact with the shaft 4 of the bearing portion 2 has a shape that is parallel to the shaft 4 even if it receives a thrust force T. Therefore, no local contact occurs on the surface 5 that contacts the shaft 4, and the entire surface 5 effectively works.
【００２０】さらに、図７は本発明の第２実施形態の軸
受け部２の形状を示す縦断面、図８は図３のＡ方向から
視た軸停止時の軸受け装置の横断面図である。図７より
明らかな如く前記実施形態とは逆に、前記軸受け部は、
前記台座と接触する外径面をテーパ状に加工するととも
に、前記テーパがスラストカラー（押圧部）から遠ざか
る方向に拡径されるテーパ形状をなす。すなわち、具体
的には軸受け部２の台座１と接触する面を押圧部（スラ
ストカラー）８側ではＤ1、他端側ではＤ2とした場合
に、Ｄ1からＤ2に向けて次第に直径を増すように（Ｄ1
＜Ｄ2）テーパ状に加工される。そして台座１は軸受け
部２取り付け穴を平行円筒形状とする。Further, FIG. 7 is a vertical sectional view showing the shape of the bearing portion 2 of the second embodiment of the present invention, and FIG. 8 is a transverse sectional view of the bearing device when the shaft is stopped as seen from the direction A in FIG. As is clear from FIG. 7, contrary to the embodiment, the bearing portion is
The outer diameter surface that comes into contact with the pedestal is machined into a tapered shape, and the tapered shape is such that the taper is expanded in the direction away from the thrust collar (pressing portion). That is, specifically, when the surface of the bearing portion 2 in contact with the pedestal 1 is D1 on the pressing portion (thrust collar) 8 side and D2 on the other end side, the diameter gradually increases from D1 to D2. (D1
<D2) It is processed into a taper shape. Then, the pedestal 1 has a bearing 2 mounting hole having a parallel cylindrical shape.
【００２１】かかる構成において、軸受け部２を前記台
座１の取り付け穴に圧入すると図８、即ち図５と同様に
軸受け部２の内径側がテーパ状になり、この実施の形態
によれば、第１実施形態と同様に機関が運転を始める
と、図６に示すように、軸４には推進力の反力であるス
ラスト力Ｔが軸４に設けたスラストカラー（押圧部）８
を介して軸受け部２にかかる。そのために、台座１や軸
受け部２は傾いて広がり変形する。そして、第１の実施
の形態と同様に軸受け部２ａは軸方向に広がり、軸受け
部２の軸４と接触する面５が軸と平行に沿う形状とな
る。In such a structure, when the bearing portion 2 is press-fitted into the mounting hole of the pedestal 1, the inner diameter side of the bearing portion 2 is tapered as in the case of FIG. 8, that is, FIG. When the engine starts to operate as in the embodiment, as shown in FIG. 6, a thrust collar (pressing portion) 8 provided on the shaft 4 is a thrust force T which is a reaction force of the propulsive force on the shaft 4.
To the bearing unit 2 via. Therefore, the pedestal 1 and the bearing portion 2 are tilted and expanded. Then, similarly to the first embodiment, the bearing portion 2a expands in the axial direction, and the surface 5 of the bearing portion 2 that comes into contact with the shaft 4 has a shape parallel to the axis.
【００２２】さらに、外径面６がテーパ状に加工されて
いるために、軸受け部２と台座１間が圧入状態になり、
スラスト力Ｔが作用して軸受け部２が変形しても、軸受
け部２が台座１から脱落することが防止される。Further, since the outer diameter surface 6 is tapered, the space between the bearing 2 and the base 1 is press-fitted,
Even if the bearing portion 2 is deformed by the thrust force T, the bearing portion 2 is prevented from falling off the pedestal 1.
【００２３】[0023]
【発明の効果】以上説明したように請求項１記載の発明
によれば、軸受け部の軸と接触する面である軸受け面を
予めテーパ状に加工したので、
１）軸受け装置がスラスト力で軸方向へ傾いたり、スラ
スト力の付加方向に対してテーパ状に変形して広がるよ
うなことがあっても、軸と接触する面（軸受け面）が軸
の中心線に沿って平行になり、該面に局部当たりによる
過大な面圧が発生するのが防止される。しかも、該面全
体で軸を支持するから軸受け装置の負荷能力が向上し、
軸受け装置の信頼性が向上する。
２）そのうえ、従来のようになじみ運転や、軸受け面の
当たりを目視して確認し、軸受け装置の軸との煩雑なア
ラインメント調整をすることが不必要となる。このため
に、軸受け装置のコスト低減にも寄与するところが大で
ある。
３）さらに、請求項２記載の発明によれば、軸受け部の
台座と接触する面をテーパ状に加工することによって、
軸受け部がスラスト力の十分抗することができ、軸受け
部が台座から脱落することはない。As described above, according to the first aspect of the present invention, the bearing surface, which is the surface of the bearing portion that comes into contact with the shaft, is previously processed into a tapered shape. Even if it tilts in the direction or is deformed and spreads in a tapered shape in the direction in which the thrust force is applied, the surface in contact with the shaft (bearing surface) becomes parallel along the center line of the shaft, Excessive surface pressure due to local contact with the surface is prevented. Moreover, since the shaft is supported by the entire surface, the load capacity of the bearing device is improved,
The reliability of the bearing device is improved. 2) In addition, it is unnecessary to perform familiar operation as in the past and visually check the contact of the bearing surface to perform complicated alignment adjustment with the shaft of the bearing device. Therefore, it greatly contributes to the cost reduction of the bearing device. 3) Further, according to the invention described in claim 2, by processing the surface of the bearing portion in contact with the pedestal into a tapered shape,
The bearing portion can sufficiently resist the thrust force, and the bearing portion does not fall off the pedestal.
【図１】本発明の第１の実施形態である軸受け装置の正
面図である。FIG. 1 is a front view of a bearing device according to a first embodiment of the present invention.
【図２】図１のＹ−Ｙ線による断面図である。FIG. 2 is a sectional view taken along line YY of FIG.
【図３】軸停止時における軸受け装置の縦断面図であ
る。FIG. 3 is a vertical sectional view of the bearing device when the shaft is stopped.
【図４】軸回転時にスラスト力を受けた状態の図３の縦
断面である。FIG. 4 is a vertical cross section of FIG. 3 in a state in which a thrust force is applied during shaft rotation.
【図５】図３のＡ方向から視た軸停止時の軸受け装置の
横断面図である。5 is a cross-sectional view of the bearing device when the shaft is stopped as viewed from the direction A in FIG.
【図６】軸回転時にスラスト力を受けた状態の図５の横
断面である。FIG. 6 is a transverse cross section of FIG. 5 in a state in which a thrust force is applied when the shaft rotates.
【図７】本発明の第２の実施形態の軸受け部の縦断面で
ある。FIG. 7 is a vertical cross section of a bearing portion according to a second embodiment of the present invention.
【図８】図７の軸受部を組込んだ図５の対応図である。8 is a corresponding view of FIG. 5 in which the bearing portion of FIG. 7 is incorporated.
【図９】本発明の軸受け装置を備える舶用ディーゼル機
関の部分側面図である。FIG. 9 is a partial side view of a marine diesel engine including the bearing device of the present invention.
【図１０】従来の軸受け装置の縦断面図である。FIG. 10 is a vertical sectional view of a conventional bearing device.
【図１１】軸停止時における従来の軸受け装置の縦断面
図である。FIG. 11 is a vertical cross-sectional view of a conventional bearing device when the shaft is stopped.
【図１２】軸回転時にスラスト力を受けた状態の図１１
の縦断面である。FIG. 12 is a view showing a state in which a thrust force is applied during shaft rotation
Is a vertical cross section.
１ 台座 ２ 軸受け部 ４ 軸（クランク軸） ５ 軸と接触する面（軸受け面） ６ 台座と接触する面（外径面） ８ 押圧部（スラストカラー） Ｂ 軸受け装置 Ｔ スラスト力 Ｘ−Ｘ 軸の中心線 1 pedestal 2 Bearing part 4 axes (crankshaft) 5 Surface that contacts the shaft (bearing surface) 6 Surface that contacts the pedestal (outer diameter surface) 8 Pressing part (thrust color) B bearing device T thrust force XX axis center line
フロントページの続き (56)参考文献 特開 昭62−242123（ＪＰ，Ａ) 特開 平７−279967（ＪＰ，Ａ) 特開 平２−278011（ＪＰ，Ａ) 特開 平５−272531（ＪＰ，Ａ) 実開 昭57−40715（ＪＰ，Ｕ) 実開 昭62−93420（ＪＰ，Ｕ) 実開 平２−94451（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F16C 9/02 F16C 33/02 F16C 23/02 Continuation of the front page (56) Reference JP 62-242123 (JP, A) JP 7-279967 (JP, A) JP 2-278011 (JP, A) JP 5-272531 (JP , A) Actually developed 57-40715 (JP, U) Actually developed 62-93420 (JP, U) Actually developed 2-94451 (JP, U) (58) Fields investigated (Int.Cl. 7 , DB) Name) F16C 9/02 F16C 33/02 F16C 23/02
Claims (2)
記軸を支持するための台座と、前記軸と台座の間に設置
される軸受け部と、前記軸と一体又は軸に固定され、軸
が受けたスラスト力により軸受け部又は台座を押す押圧
部とからなる軸受け装置において、前記軸と接触する軸受け部の、前記押圧部側端面内径を
ｄ1、他端側端面内径をｄ2とした場合に、ｄ1からｄ2に
向けて（ｄ1＞ｄ2）となるように、前記両端面間の軸受
け面をテーパ状に 加工するとともに、前記軸受け部が上
下方向に半割りされ、下側の軸受け部に傾きを設けて前
記テーパ形状を形成させたことを特徴とする軸受け装
置。1. A shaft for receiving a thrust force in an axial direction, a pedestal for supporting the shaft, a bearing portion installed between the shaft and the pedestal, and a shaft integral with or fixed to the shaft, In the bearing device including a bearing portion or a pressing portion that pushes the pedestal by the thrust force received by the bearing portion, the inner diameter of the end surface of the bearing portion of the bearing portion that contacts the shaft is
If d1 and the inner diameter of the end face on the other end side are d2, change from d1 to d2
Bearing between the both end faces so that (d1> d2)
The bearing surface is machined into a tapered shape and the bearing is
It is divided in half in the downward direction, and the lower bearing is tilted
A bearing device having a tapered shape .
記軸を支持するための台座と、前記軸と台座の間に設置
される軸受け部と、前記軸と一体又は軸に固定され、軸
が受けたスラスト力により軸受け部又は台座を押す押圧
部とからなる軸受け装置において、 前記軸受け部の前記台座と接触する外径面を、押圧部
（スラストカラー）側外径をＤ1、他端側外径をＤ2とし
た場合に、Ｄ1からＤ2に向けて次第に外径を増して（Ｄ
1＜Ｄ2）となるようにテーパ状に加工するとともに、前
記軸の運転時に、前記押圧部からのスラスト力により変
形した軸受け部と軸受け部の軸と接触する面が軸と平行
に沿う形状となるように前記テーバ形状を設定したこと
を特徴とする軸受け装置。2. A shaft that receives a thrust force in the axial direction, a pedestal for supporting the shaft, a bearing portion installed between the shaft and the pedestal, and a shaft that is integral with or fixed to the shaft, In a bearing device comprising a bearing portion or a pressing portion that pushes the pedestal by the thrust force received by the bearing portion, an outer diameter surface of the bearing portion that contacts the pedestal is
The outer diameter on the (thrust collar) side is D1, and the outer diameter on the other end side is D2.
The outer diameter gradually increases from D1 to D2 (D
With processed into 1 <D2) and so as to taper, before
When the spindle is in operation, it changes due to the thrust force from the pressing part.
The shaped bearing and the surface of the bearing that contacts the shaft are parallel to the shaft
The bearing device is characterized in that the taper shape is set so as to follow the shape .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP08577297A JP3457833B2 (en) | 1997-03-19 | 1997-03-19 | Bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP08577297A JP3457833B2 (en) | 1997-03-19 | 1997-03-19 | Bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH10259819A JPH10259819A (en) | 1998-09-29 |
| JP3457833B2 true JP3457833B2 (en) | 2003-10-20 |
Family
ID=13868177
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP08577297A Expired - Fee Related JP3457833B2 (en) | 1997-03-19 | 1997-03-19 | Bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3457833B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108413483B (en) * | 2017-07-18 | 2023-08-15 | 奥克斯空调股份有限公司 | Air conditioner fan blade bearing seat assembly and air conditioner indoor unit |
| CN108413484B (en) * | 2017-07-18 | 2023-08-15 | 奥克斯空调股份有限公司 | Air conditioner fan blade bearing seat assembly and air conditioner indoor unit |
-
1997
- 1997-03-19 JP JP08577297A patent/JP3457833B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH10259819A (en) | 1998-09-29 |
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