JP2008240962A - Journal bearing device - Google Patents

Journal bearing device Download PDF

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Publication number
JP2008240962A
JP2008240962A JP2007084966A JP2007084966A JP2008240962A JP 2008240962 A JP2008240962 A JP 2008240962A JP 2007084966 A JP2007084966 A JP 2007084966A JP 2007084966 A JP2007084966 A JP 2007084966A JP 2008240962 A JP2008240962 A JP 2008240962A
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Prior art keywords
lower half
pad
bearing
upper half
journal bearing
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JP5197977B2 (en
Inventor
Satoshi Nanba
聡 南波
Makoto Mikami
誠 三上
Kazuma Mukai
一馬 向井
Nobuyuki Takeda
信行 武田
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Toshiba Corp
Toshiba Plant Systems and Services Corp
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Toshiba Corp
Toshiba Plant Systems and Services Corp
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Application filed by Toshiba Corp, Toshiba Plant Systems and Services Corp filed Critical Toshiba Corp
Priority to JP2007084966A priority Critical patent/JP5197977B2/en
Priority to CN2008800098799A priority patent/CN101641525B/en
Priority to PCT/JP2008/000759 priority patent/WO2008126362A1/en
Priority to BRPI0809625-2A priority patent/BRPI0809625B1/en
Priority to KR1020097019403A priority patent/KR20090114460A/en
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    • 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
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02—Sliding-contact 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/02—Sliding-contact 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/08—Attachment of brasses, bushes or linings to the bearing housing
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/108—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid with a plurality of elements forming the bearing surfaces, e.g. bearing pads
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/20—Sliding surface consisting mainly of plastics
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/20—Sliding surface consisting mainly of plastics
    • F16C33/203—Multilayer structures, e.g. sleeves comprising a plastic lining
    • F16C33/205—Multilayer structures, e.g. sleeves comprising a plastic lining with two layers
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/26—Brasses; Bushes; Linings made from wire coils; made from a number of discs, rings, rods, or other members
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/60—Positive connections with threaded parts, e.g. bolt and nut connections

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sliding-Contact Bearings (AREA)
  • Support Of The Bearing (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a journal bearing device sufficiently adoptable as a bearing for a rotation shaft having a large diameter as it is possible to prevent damage and the like of the bearing and the rotation shaft due to inclination of the rotation shaft during operation even in the case of a large load and a low rotation speed. <P>SOLUTION: In the journal bearing device 10, upper half pads 21 are provided for an upper half bearing part 20 for supporting the rotation shaft 50 and lower half pads 31 are provided for the lower half bearing part 30. The plurality of lower half pad 31 are provided along a circumference direction of the lower half bearing part 30 with a predetermined interval and one of the plurality of lower half pads 31 is provided vertically below the rotation shaft 50. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、回転機械における回転軸を支えるジャーナル軸受装置に関する。   The present invention relates to a journal bearing device that supports a rotating shaft in a rotating machine.

回転機械に使用されるジャーナル軸受は、軸受の中心軸と回転軸の中心軸とが平行になるように組み立てられる。しかしながら、回転時には荷重の方向や回転軸の変形などによって、軸受の中心軸と回転軸の中心軸とが平行にならずにずれた状態であるミスアライメントが生じることがある。また、回転荷重が作用すると、例えば、軸受の中心軸と回転軸の中心軸との交点を頂点とする円錐状の振れ回りを生ずることがある。このような運転状態になると軸受の摺動端部に片当りによる損傷（焼付き）が発生する可能性がある。そこで、上記したような回転軸等の損傷を防止するために、これまで様々な技術が報告されている。図１１〜図１３は、従来のジャーナル軸受装置の断面の構造を示す図である。   Journal bearings used in rotating machines are assembled so that the central axis of the bearing and the central axis of the rotating shaft are parallel to each other. However, during rotation, misalignment may occur in which the center axis of the bearing and the center axis of the rotating shaft are not parallel to each other due to the direction of the load or deformation of the rotating shaft. In addition, when a rotational load is applied, for example, a conical swing around the intersection of the center axis of the bearing and the center axis of the rotation shaft may occur. In such an operating state, there is a possibility that damage (seizure) due to a single contact may occur at the sliding end of the bearing. Therefore, various techniques have been reported so far in order to prevent damage to the rotating shaft and the like as described above. 11-13 is a figure which shows the structure of the cross section of the conventional journal bearing apparatus.

図１１に示されたジャーナル軸受装置３００は、背面が凸型の球面の軸受３０１と、この軸受３０１の球面と摺動する、表面が凹型の球面の軸受台３０２を備えている（例えば、特許文献１参照。）。そして、このジャーナル軸受装置３００では、運転中に回転軸３０３が傾いたときに、双方の球面が摺動して回転軸３０３に追従して軸受３０１が自動調芯する。   A journal bearing device 300 shown in FIG. 11 includes a spherical bearing 301 having a convex rear surface and a spherical bearing base 302 having a concave surface that slides on the spherical surface of the bearing 301 (for example, a patent). Reference 1). In the journal bearing device 300, when the rotary shaft 303 is tilted during operation, both spherical surfaces slide and follow the rotary shaft 303 to automatically align the bearing 301.

図１２に示されたジャーナル軸受装置３２０は、回転軸３２３と摺動する軸受３２１の摺動面上に、摺動性に優れた樹脂系複合材料からなる摺動層３２２を備えている（例えば、特許文献２参照。）。この構造にすることで、回転軸３２３の片当りが生じた場合でも、回転軸３２３の摩耗や焼付が防止され、大形軸受としても使用可能となる。また、楕円軸受において、軸受３２１の軸受摺動面上の一部を除く領域に摺動層３２２を設ける技術も開示されている（例えば、特許文献３参照。）。   The journal bearing device 320 shown in FIG. 12 includes a sliding layer 322 made of a resin-based composite material having excellent slidability on the sliding surface of the bearing 321 that slides with the rotating shaft 323 (for example, , See Patent Document 2). By adopting this structure, even when the rotating shaft 323 comes into contact with one piece, the rotating shaft 323 is prevented from being worn or seized, and can be used as a large bearing. In addition, a technique of providing a sliding layer 322 in a region excluding a part on the bearing sliding surface of the bearing 321 in an elliptical bearing is also disclosed (for example, see Patent Document 3).

図１３に示されたジャーナル軸受装置３３０は、従来から自動調芯性に優れる軸受として一般的に使用されているティルティングパッド軸受である（例えば、特許文献４参照。）。ティルティングパッド３３１は、周方向および軸方向に傾斜可能となるように、ピボット３３２などで支持されており、回転軸３３３の傾きに容易に追従できるようになっている。
特開平９−２５９３２号公報 特開平５−３２７９７号公報 特開２００１−１７３６５９号公報 特開２００４−１９７８９０号公報 The journal bearing device 330 shown in FIG. 13 is a tilting pad bearing that has been conventionally used as a bearing that is excellent in automatic alignment (see, for example, Patent Document 4). The tilting pad 331 is supported by a pivot 332 or the like so as to be tiltable in the circumferential direction and the axial direction, and can easily follow the tilt of the rotating shaft 333.
Japanese Patent Laid-Open No. 9-25932 JP-A-5-32797 JP 2001-173659 A JP 2004-197890 A

上記したように、従来のジャーナル軸受装置において、運転時の回転軸の傾きに追従して軸受の損傷を防止する技術が提案されているが、以下のような課題を残している。   As described above, in the conventional journal bearing device, a technique for preventing damage to the bearing by following the inclination of the rotating shaft during operation has been proposed, but the following problems remain.

図１１に示したジャーナル軸受装置では、軸受に負荷される荷重が大きい場合に、球面間の摩擦力が過大となり、軸受が傾き難くなり追従性が悪くなるという問題がある。そのため、ミスアライメント量が増加すると、回転軸と軸受との片当りが発生し、回転軸と軸受の表面が損傷（焼付）する可能性がある。   The journal bearing device shown in FIG. 11 has a problem that when the load applied to the bearing is large, the frictional force between the spherical surfaces becomes excessive, the bearing becomes difficult to tilt, and the followability is deteriorated. For this reason, when the misalignment amount increases, a contact between the rotating shaft and the bearing may occur, and the surfaces of the rotating shaft and the bearing may be damaged (baked).

また、図１２に示したジャーナル軸受装置では、経年的に軸受側の摩耗が進展し軸受の特性が徐々に低下して、摺動面上における潤滑油膜の形成が困難となる。潤滑油膜が形成されないと、摩擦熱による異常な温度上昇を生じ、樹脂の耐熱温度を超えることで摺動層が劣化し、回転軸と軸受の表面が接触して損傷に至ることがある。また、楕円軸受において、軸受の摺動面上の一部を除く領域に摺動層を設ける場合には、潤滑油が動く領域が広く、潤滑油の攪拌によるエネルギ損失や、ミスアライメントに対するギャップ調整が困難であるなどの問題があった。   In the journal bearing device shown in FIG. 12, wear on the bearing side progresses over time, and the characteristics of the bearing gradually deteriorate, making it difficult to form a lubricating oil film on the sliding surface. If the lubricating oil film is not formed, an abnormal temperature rise due to frictional heat occurs, the sliding layer deteriorates when the heat resistance temperature of the resin is exceeded, and the rotating shaft and the surface of the bearing come into contact with each other and may be damaged. In addition, in the case of an elliptical bearing, when a sliding layer is provided in a region excluding a part on the sliding surface of the bearing, the region in which the lubricating oil moves is wide, and energy loss due to stirring of the lubricating oil and gap adjustment for misalignment are performed. There were problems such as being difficult.

また、図１３に示したジャーナル軸受装置では、例えば大容量バルブ水車発電機のような高荷重で低回転速度用の軸受として使用される場合には、荷重により回転軸の傾きに対する本来の自動調芯性が発揮され難いという問題がある。さらに、摺動面が複数に分割されるため負荷性能が円筒型軸受に比べて悪いこと、十分な潤滑油膜の形成が困難であること、軸受寸法がかなり大きくなること等の問題もある。   Further, in the journal bearing device shown in FIG. 13, when used as a bearing for a high load and a low rotational speed such as a large capacity valve turbine generator, the original automatic adjustment with respect to the inclination of the rotating shaft by the load is performed. There is a problem that the core is difficult to be exhibited. Further, since the sliding surface is divided into a plurality of parts, there are problems such as poor load performance as compared with a cylindrical bearing, difficulty in forming a sufficient lubricating oil film, and a considerably large bearing size.

そこで、本発明は、上記課題を解決するためになされたものであり、大荷重で低回転速度の場合であっても、運転中に発生する回転軸の傾きによる軸受や回転軸の損傷などを防止することができ、大直径化された回転軸の軸受として十分に適用可能なジャーナル軸受装置を提供することを目的とする。   Therefore, the present invention has been made to solve the above-described problems. Even in the case of a large load and a low rotational speed, the bearing or the rotational shaft is damaged due to the inclination of the rotational shaft that occurs during operation. An object of the present invention is to provide a journal bearing device that can be prevented and can be sufficiently applied as a bearing of a rotating shaft having a large diameter.

上記目的を達成するために、本発明のジャーナル軸受装置は、回転軸を支承する軸受の上半軸受に上半パッドを備え、下半軸受に下半パッドを備えるジャーナル軸受装置であって、前記下半軸受の内周面の周方向に沿って所定の間隔をあけて前記下半パッドが複数配設され、該複数の下半パッドのうちの１つが、回転軸の鉛直下方に配設されていることを特徴とする。   In order to achieve the above object, a journal bearing device of the present invention is a journal bearing device in which an upper half pad is provided in an upper half bearing of a bearing that supports a rotating shaft, and a lower half pad is provided in a lower half bearing, A plurality of the lower half pads are arranged at predetermined intervals along the circumferential direction of the inner circumferential surface of the lower half bearing, and one of the plurality of lower half pads is arranged vertically below the rotating shaft. It is characterized by.

また、本発明のジャーナル軸受装置は、回転軸を支承する軸受の上半軸受に上半パッドを備え、下半軸受に下半パッドを備えるジャーナル軸受装置であって、前記下半軸受の内周面の周方向に沿って所定の間隔をあけて前記下半パッドが複数配設されてなるパッド列を、前記回転軸の軸方向に所定の間隔をあけて複数列備え、該各パッド列において複数の下半パッドのうちの１つが、回転軸の鉛直下方に配設されていることを特徴とする。   The journal bearing device of the present invention is a journal bearing device in which an upper half bearing is provided on an upper half bearing of a bearing that supports a rotating shaft, and a lower half pad is provided on a lower half bearing. A plurality of rows of pads arranged with a plurality of lower half pads arranged at predetermined intervals along the circumferential direction of the surface are provided at predetermined intervals in the axial direction of the rotating shaft. One of the plurality of lower half pads is arranged vertically below the rotation axis.

これらのジャーナル軸受装置によれば、上半パッドや下半パッドを軸受の内周面の周方向に複数に分割して設けることができるので、任意の位置に配設可能となる。これによって、回転軸のミスアライメントに追従させ易くなる。   According to these journal bearing devices, the upper half pad and the lower half pad can be divided into a plurality of parts in the circumferential direction of the inner peripheral surface of the bearing, so that they can be arranged at arbitrary positions. This makes it easier to follow the misalignment of the rotating shaft.

本発明のジャーナル軸受装置によれば、大荷重で低回転速度の場合であっても、運転中に発生する回転軸の傾きによる軸受や回転軸の損傷などを防止することができ、大直径化された回転軸の軸受として十分に適用可能である。   According to the journal bearing device of the present invention, even in the case of a large load and a low rotational speed, it is possible to prevent damage to the bearing and the rotary shaft due to the tilt of the rotary shaft that occurs during operation, and to increase the diameter The present invention is sufficiently applicable as a bearing for a rotating shaft.

以下、本発明の一実施の形態について図面を参照して説明する。   Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

（第１の実施の形態）
図１は、本発明に係る第１の実施の形態のジャーナル軸受装置１０における回転軸５０に垂直な断面を示す図である。図２は、本発明に係る第１の実施の形態のジャーナル軸受装置１０における回転軸５０に水平な断面（図１のＡ−Ａ断面）を示す図である。図３は、下半パッド３１と下半軸受部３０の内周面との間にライナ３５を介在させたときの、下半軸受部３０における回転軸５０に水平な断面（軸方向断面）を示す図である。 (First embodiment)
FIG. 1 is a view showing a cross section perpendicular to the rotary shaft 50 in the journal bearing device 10 according to the first embodiment of the present invention. FIG. 2 is a view showing a cross section (cross section AA in FIG. 1) horizontal to the rotating shaft 50 in the journal bearing device 10 according to the first embodiment of the present invention. FIG. 3 shows a horizontal cross section (axial cross section) of the rotary shaft 50 in the lower half bearing portion 30 when the liner 35 is interposed between the lower half pad 31 and the inner peripheral surface of the lower half bearing portion 30. FIG.

図１に示すように、ジャーナル軸受装置１０は、上半パッド２１を内周面に備える上半軸受部２０および下半パッド３１を内周面に備える下半軸受部３０とからなるジャーナル軸受本体４０を備え、上半パッド２１および下半パッド３１で回転軸５０を支承する構成になっている。上半軸受部２０は、ジャーナル軸受本体４０の中心を通る水平面でジャーナル軸受本体４０を２分割したしたときの上半分の軸受部であり、下半軸受部３０は、その下半分の軸受部である。   As shown in FIG. 1, the journal bearing device 10 includes a journal bearing body including an upper half bearing portion 20 having an upper half pad 21 on the inner peripheral surface and a lower half bearing portion 30 having a lower half pad 31 on the inner peripheral surface. 40, and the rotary shaft 50 is supported by the upper half pad 21 and the lower half pad 31. The upper half bearing portion 20 is an upper half bearing portion when the journal bearing main body 40 is divided into two by a horizontal plane passing through the center of the journal bearing main body 40, and the lower half bearing portion 30 is a lower half bearing portion. is there.

図１および図２に示すように、上半パッド２１は、上半軸受部２０の内周面に周方向に沿って所定の間隔をあけて配設され、下半パッド３１は、下半軸受部３０の内周面に周方向に沿って所定の間隔をあけて配設される。すなわち、上半パッド２１および下半パッド３１は、それぞれ分割した状態で周方向に沿って配設される。また、上半パッド２１および下半パッド３１は、着脱可能に上半軸受部２０や下半軸受部３０の内周面に配設されている。複数配置された下半パッド３１のうちの１つは、回転軸５０の鉛直下方に配置される。また、上半パッド２１および下半パッド３１は、特に半径方向荷重が顕著に作用する内周面に配置することが好ましい。このように上半パッド２１および下半パッド３１を配置することで、回転軸５０が大荷重で低回転速度の場合において、重力方向荷重Ｗが大きく増大して回転するときにおいても、十分な負荷容量を確保することができる。なお、ここでいう負荷容量とは、その軸受で支持可能な最大荷重のことを言う。   As shown in FIGS. 1 and 2, the upper half pad 21 is disposed on the inner circumferential surface of the upper half bearing portion 20 at a predetermined interval along the circumferential direction, and the lower half pad 31 is a lower half bearing. Arranged on the inner circumferential surface of the portion 30 at a predetermined interval along the circumferential direction. That is, the upper half pad 21 and the lower half pad 31 are arranged along the circumferential direction in a divided state. The upper half pad 21 and the lower half pad 31 are detachably disposed on the inner peripheral surface of the upper half bearing portion 20 and the lower half bearing portion 30. One of the plurality of lower half pads 31 is disposed vertically below the rotation shaft 50. Moreover, it is preferable to arrange | position the upper half pad 21 and the lower half pad 31 on the internal peripheral surface where radial direction load acts notably. By arranging the upper half pad 21 and the lower half pad 31 in this manner, even when the rotating shaft 50 is rotated with a large load and a low rotational speed, a sufficient load can be obtained even when the gravity direction load W is greatly increased. Capacity can be secured. The load capacity here means the maximum load that can be supported by the bearing.

上半パッド２１および下半パッド３１の曲率半径は、回転する回転軸５０の表面との間に油膜を形成するために、回転軸５０の半径よりも若干大きな曲率を有している。   The curvature radii of the upper half pad 21 and the lower half pad 31 have a slightly larger curvature than the radius of the rotating shaft 50 in order to form an oil film between the rotating shaft 50 and the surface of the rotating rotating shaft 50.

下半軸受部３０に設けられる各下半パッド３１間の所定の間隔は、その下半パッド３１間に形成される間隙を潤滑油が流動可能な程度であることが好ましく、潤滑油の粘度等や使用される温度条件等に基づいて適宜設定される。   The predetermined interval between the lower half pads 31 provided in the lower half bearing portion 30 is preferably such that the lubricating oil can flow through the gap formed between the lower half pads 31, and the viscosity of the lubricating oil, etc. It is set as appropriate based on the temperature conditions used.

また、上半パッド２１および下半パッド３１は、基材２１ｂ、３１ｂの表面に、熱可塑性樹脂材料や、セラミックス繊維、二硫化モリブデンおよび黒鉛等からなる粒子の少なくとも１種を含有した熱可塑性樹脂材料で形成された表面層２１ａ、３１ａを備えて構成される。基材２１ｂ、３１ｂは、普通鋼やステンレス鋼などの鋼材で構成される。表面層２１ａ、３１ａを構成する樹脂として、具体的には、ポリテトラフロオロエチレン（ＰＴＦＥ）樹脂、ポリエテルエテルケトン（ＰＥＥＫ）樹脂、ポリイミド（ＰＩ）樹脂などが挙げられる。また、セラミックス繊維や二硫化モリブデンや黒鉛等からなる粒子を含有した熱可塑性樹脂材料として、具体的には、上記した樹脂と同様に、ポリテトラフロオロエチレン（ＰＴＦＥ）樹脂、ポリエテルエテルケトン（ＰＥＥＫ）樹脂、ポリイミド（ＰＩ）樹脂などが挙げられる。熱可塑性樹脂材料に含有される材料の含有率、すなわち、含有される材料を含めた樹脂の重量に対する含有される材料の重量の割合は、１０〜２０重量％であることが好ましい。この範囲が好ましいのは、１０重量％未満の場合には、含有した材料の効果が顕著に現れないためであり、２０重量％を超える場合には、それ以上含有しても量に比例した効果が期待できないからである。ここで、セラミックス繊維を含有する場合には、機械的強度や耐摩耗性能が向上し、二硫化モリブデンや黒鉛等からなる粒子を含有する場合には、摩擦係数が低減する。   The upper half pad 21 and the lower half pad 31 are thermoplastic resins containing at least one kind of particles made of a thermoplastic resin material, ceramic fibers, molybdenum disulfide, graphite, or the like on the surfaces of the base materials 21b and 31b. It is configured to include surface layers 21a and 31a formed of a material. The base materials 21b and 31b are made of steel materials such as ordinary steel and stainless steel. Specific examples of the resin constituting the surface layers 21a and 31a include polytetrafluoroethylene (PTFE) resin, polyetheretherketone (PEEK) resin, and polyimide (PI) resin. In addition, as a thermoplastic resin material containing particles made of ceramic fibers, molybdenum disulfide, graphite, or the like, specifically, as with the above-described resin, polytetrafluoroethylene (PTFE) resin, polyetheretherketone ( PEEK resin, polyimide (PI) resin and the like. The content of the material contained in the thermoplastic resin material, that is, the ratio of the weight of the material contained to the weight of the resin including the contained material is preferably 10 to 20% by weight. This range is preferable because when the content is less than 10% by weight, the effect of the contained material does not appear remarkably, and when it exceeds 20% by weight, the effect is proportional to the amount even if the content is more than 10% by weight. This is because it cannot be expected. Here, when the ceramic fiber is contained, the mechanical strength and wear resistance are improved, and when the particle is made of molybdenum disulfide, graphite, or the like, the friction coefficient is reduced.

このように、上半パッド２１や下半パッド３１の表面を樹脂材料で形成することで、従来用いられていた軟金属材料を表面に用いる場合よりも摩擦係数が大幅に低減する。これによって、例えば、組立て作業の際、下半パッド３１上における回転軸５０の軸方向の移動を容易にすることができる。特に、回転軸５０の鉛直下方に配置された下半パッド３１によって、回転軸５０の鉛直下方側の面を支持することができるので、回転軸５０の軸方向の移動を容易にすることができる。また、表面を樹脂材料で形成することで、優れた耐摩耗性を有するので、回転軸５０の始動時において、油膜厚さが薄いあるいは油膜が形成されていない状態でも、回転軸の表面とパッド表面との接触や回転軸５０との片当り等による、回転軸５０やパッドの摺動面の局所摩耗や損傷発生を、オイルリフタを用いることなく抑制することができる。   Thus, by forming the surfaces of the upper half pad 21 and the lower half pad 31 from a resin material, the friction coefficient is greatly reduced as compared with the case where a conventionally used soft metal material is used for the surface. Thereby, for example, the axial movement of the rotary shaft 50 on the lower half pad 31 can be facilitated during the assembly work. In particular, since the lower half pad 31 disposed vertically below the rotation shaft 50 can support the vertically lower surface of the rotation shaft 50, the movement of the rotation shaft 50 in the axial direction can be facilitated. . Further, since the surface is made of a resin material, it has excellent wear resistance. Therefore, when the rotating shaft 50 is started, the surface of the rotating shaft and the pad can be used even when the oil film is thin or no oil film is formed. Local wear or damage on the sliding surface of the rotating shaft 50 or the pad due to contact with the surface or contact with the rotating shaft 50 can be suppressed without using an oil lifter.

なお、上半パッド２１の表面層２１ａは、回転軸５０を構成する材料よりも硬度が小さく、すなわち柔らかく、形成された油膜圧力に耐え、摩耗耐力のある軟金属材料で構成されてもよい。この軟金属材料として、例えばホワイトメタル等が挙げられる。このように軟金属材料を表面層として使用する場合には、従来の軸受パッドの製造方法を適用することができることから製造コストの削減を図ることができる。また、下半パッド３１においても、半径方向荷重が小さい内周面に配置される場合には、下半パッド３１の表面層３１ａをホワイトメタル等の軟金属材料で構成することも可能である。   The surface layer 21a of the upper half pad 21 may be made of a soft metal material having a hardness smaller than that of the material constituting the rotary shaft 50, that is, soft, withstanding the formed oil film pressure and having wear resistance. Examples of the soft metal material include white metal. Thus, when using a soft metal material as a surface layer, since the manufacturing method of the conventional bearing pad can be applied, reduction of manufacturing cost can be aimed at. Further, when the lower half pad 31 is also disposed on the inner peripheral surface having a small radial load, the surface layer 31a of the lower half pad 31 can be made of a soft metal material such as white metal.

ここで、ジャーナル軸受本体４０の中心軸と回転軸５０の中心軸とが平行にならずにずれた状態であるミスアライメントが生じた場合には、ジャーナル軸受本体４０の中心軸と回転軸５０の中心軸との交点を頂点とする円錐状の振れ回りを生ずることがある。このような状態を回避するために、所定の上半パッド２１の背面と上半軸受部２０の内周面との間、および／または所定の下半パッド３１の背面と下半軸受部３０の内周面との間に、薄板として機能するライナ３５を介在させてそれぞれのパッド２１、３１を固定し、軸受ギャップを調整するようにしてもよい。これにより、軸受の剛性が増し、上記した振れ回りを抑制することができる。また、上半パッド２１や下半パッド３１は、軸受部に着脱可能に固定されているので、上半パッド２１や下半パッド３１の配設位置を移動したり、パッド数を増減して、上記した振れ回りを抑制してもよい。ライナは、例えば、普通鋼やステンレス鋼などの鋼材からなる薄板や箔などで構成される。   Here, when misalignment occurs in which the center axis of the journal bearing body 40 and the center axis of the rotating shaft 50 are not parallel to each other and are shifted, the center axis of the journal bearing body 40 and the rotating shaft 50 are not aligned. There may be a conical swing around the intersection with the central axis. In order to avoid such a state, between the back surface of the predetermined upper half pad 21 and the inner peripheral surface of the upper half bearing portion 20 and / or the back surface of the predetermined lower half pad 31 and the lower half bearing portion 30. A liner 35 functioning as a thin plate may be interposed between the inner peripheral surface and the pads 21 and 31 may be fixed to adjust the bearing gap. Thereby, the rigidity of the bearing is increased and the above-described swinging can be suppressed. Further, since the upper half pad 21 and the lower half pad 31 are detachably fixed to the bearing portion, the arrangement positions of the upper half pad 21 and the lower half pad 31 are moved, the number of pads is increased or decreased, The above whirling may be suppressed. The liner is made of, for example, a thin plate or foil made of steel such as ordinary steel or stainless steel.

ここでは、下半パッド３１の背面と下半軸受部３０の内周面との間に、ライナ３５を介在させて固定する場合を一例として説明する。図３に示すように、下半パッド３１は、固定部材３６を下半軸受部３０の外周側から、例えばネジ３７によって固定することによって、下半軸受部３０の内周面に固定される。下半パッド３１の背面と下半軸受部３０の内周面との間に、薄板を介在させる場合には、まず、固定部材３６を外し、下半パッド３１の背面と下半軸受部３０の内周面との間にライナ３５を挿入する。続いて、固定部材３６をネジ３７によって固定する。なお、上記したライナ３５の装着は、回転軸５０がリフトアップされた状態、すなわちジャーナル軸受本体４０に回転軸５０の荷重がかかっていない状態で行なわれる。また、下半パッド３１の固定方法は、上記した方法に限定されるものではなく、下半パッド３１を下半軸受部３０の内周面に固定できる方法であれば特に問わない。上半パッド２１についても、下半パッド３１と同様の方法で固定される。   Here, a case where the liner 35 is interposed and fixed between the back surface of the lower half pad 31 and the inner peripheral surface of the lower half bearing portion 30 will be described as an example. As shown in FIG. 3, the lower half pad 31 is fixed to the inner peripheral surface of the lower half bearing portion 30 by fixing the fixing member 36 from the outer peripheral side of the lower half bearing portion 30 with, for example, screws 37. When a thin plate is interposed between the back surface of the lower half pad 31 and the inner peripheral surface of the lower half bearing portion 30, first, the fixing member 36 is removed, and the back surface of the lower half pad 31 and the lower half bearing portion 30 are removed. The liner 35 is inserted between the inner peripheral surface. Subsequently, the fixing member 36 is fixed by screws 37. The above-described liner 35 is mounted in a state where the rotary shaft 50 is lifted up, that is, in a state where the journal bearing body 40 is not loaded with the rotary shaft 50. Further, the fixing method of the lower half pad 31 is not limited to the above-described method, and any method can be used as long as it can fix the lower half pad 31 to the inner peripheral surface of the lower half bearing portion 30. The upper half pad 21 is also fixed in the same manner as the lower half pad 31.

次に、回転軸５０と下半パッド３１と間に形成される油膜の圧力分布について説明する。   Next, the pressure distribution of the oil film formed between the rotating shaft 50 and the lower half pad 31 will be described.

図４および図５は、油膜圧力分布６０の偏芯角θに対応して下半パッド３１を設けた場合のジャーナル軸受装置１０における回転軸５０に垂直な断面を示す図である。なお、潤滑油は、例えば、上半軸受部２０の頂上部かつ２つの上半パッド２１間からジャーナル軸受本体４０内に供給される。   4 and 5 are views showing a cross section perpendicular to the rotating shaft 50 in the journal bearing device 10 when the lower half pad 31 is provided corresponding to the eccentric angle θ of the oil film pressure distribution 60. The lubricating oil is supplied into the journal bearing body 40 from the top of the upper half bearing portion 20 and between the two upper half pads 21, for example.

通常、ジャーナル軸受装置１０では、回転軸５０の回転時にジャーナル軸受装置１０と回転軸５０の間に潤滑油による油膜が形成されることにより回転軸５０の潤滑が保たれるとともにジャーナル軸受装置１０で回転軸の荷重が支持されている。そして、その油膜圧力分布６０、換言すると油膜圧力がピーク値を示す領域は、静止荷重時に対して偏芯角θほど回転軸５０の回転方向６５にシフトしている。   Normally, in the journal bearing device 10, when the rotating shaft 50 rotates, an oil film is formed between the journal bearing device 10 and the rotating shaft 50, so that lubrication of the rotating shaft 50 is maintained and at the journal bearing device 10. The load on the rotating shaft is supported. The oil film pressure distribution 60, in other words, the region where the oil film pressure exhibits a peak value is shifted in the rotational direction 65 of the rotary shaft 50 by an eccentric angle θ with respect to the static load.

図４に示すように、回転軸５０の鉛直下方に配設されている下半パッド３１を、回転軸５０の回転方向に、１０〜１５度（偏芯角θ＝１０〜１５度）程度移動させる。なお、この移動範囲（偏芯角）は、回転軸５０と各パッド２１、３１との間隙量によって大きく変わるため、このジャーナル軸受本体４０が適用される機器によって最適な位置に調整することが望ましい。   As shown in FIG. 4, the lower half pad 31 disposed vertically below the rotation shaft 50 is moved by about 10 to 15 degrees (eccentric angle θ = 10 to 15 degrees) in the rotation direction of the rotation shaft 50. Let Since this moving range (eccentric angle) varies greatly depending on the amount of gap between the rotating shaft 50 and each pad 21, 31, it is desirable to adjust it to the optimum position depending on the equipment to which this journal bearing body 40 is applied. .

このような調整によって偏芯角が大きくなった場合には、図５に示すように、回転軸５０の鉛直下方に配設されている下半パッド３１を、回転軸５０の回転方向に延設してもよい。この場合には、回転軸５０の鉛直下方に配設されている下半パッド３１の表面の面積が増加することになり、油膜圧力分布を広範囲に亘らせることができる。   When the eccentric angle is increased by such adjustment, as shown in FIG. 5, the lower half pad 31 disposed vertically below the rotation shaft 50 is extended in the rotation direction of the rotation shaft 50. May be. In this case, the area of the surface of the lower half pad 31 disposed vertically below the rotation shaft 50 increases, and the oil film pressure distribution can be spread over a wide range.

上記したように、油膜圧力分布６０に対応させて、下半パッド３１の配設位置やサイズを適宜に変更することで、回転軸５０と下半パッド３１との間に油膜を十分に形成することができ、負荷容量を増加することができる。   As described above, an oil film is sufficiently formed between the rotary shaft 50 and the lower half pad 31 by appropriately changing the arrangement position and size of the lower half pad 31 corresponding to the oil film pressure distribution 60. And the load capacity can be increased.

上記した第１の実施の形態のジャーナル軸受装置１０によれば、上半パッド２１や下半パッド３１をジャーナル軸受本体４０の内周面の周方向に複数に分割して設けることにより、任意の位置に配設可能となり、回転軸５０のミスアライメントに追従させ易くなる。また、上半パッド２１や下半パッド３１を、特に重力方向に荷重Ｗが顕著に作用する内周面に選択的に配置することができる。さらに、複数に分割して設けられた上半パッド２１および／または下半パッド３１のうちの所定のパッドの背面と軸受部の内周面との間にライナ３５を挿入することで、局所的にパッドの厚さを調整することができる。これによって、軸受ギャップの調整等を容易に行なうことができる。   According to the journal bearing device 10 of the first embodiment described above, the upper half pad 21 and the lower half pad 31 are divided into a plurality of parts in the circumferential direction of the inner peripheral surface of the journal bearing body 40, thereby providing an arbitrary It becomes possible to arrange at the position, and it becomes easy to follow the misalignment of the rotating shaft 50. Further, the upper half pad 21 and the lower half pad 31 can be selectively disposed on the inner peripheral surface where the load W acts remarkably in the gravity direction. Furthermore, by inserting the liner 35 between the back surface of a predetermined pad of the upper half pad 21 and / or the lower half pad 31 provided in a divided manner and the inner peripheral surface of the bearing portion, The pad thickness can be adjusted. This makes it possible to easily adjust the bearing gap.

また、上半パッド２１や下半パッド３１をジャーナル軸受本体４０の内周面の周方向に所定の間隔をあけて複数に分割して設けることにより、潤滑油の流れとして、パッド間の間隙を流動する潤滑油が主としてパッド上に供給される流れとなる。ここで、パッド間を流動する潤滑油は、パッド上を流れる潤滑油よりも低温であることから、常時低温の潤滑油をパッド上に供給することが可能となる。このように、低温の潤滑油を、上半パッド２１および下半パッド３１上、すなわち上半パッド２１および下半パッド３１と回転軸５０との間に供給することができるので、各パッドおよびジャーナル軸受本体４０の冷却が促進され、負荷容量を増加させることができる。   Further, the upper half pad 21 and the lower half pad 31 are divided into a plurality at predetermined intervals in the circumferential direction of the inner peripheral surface of the journal bearing body 40, so that a gap between the pads is generated as a flow of the lubricating oil. The flowing lubricating oil is mainly supplied onto the pad. Here, since the lubricating oil flowing between the pads is at a lower temperature than the lubricating oil flowing on the pads, it is possible to always supply a low-temperature lubricating oil onto the pads. Thus, since the low temperature lubricating oil can be supplied on the upper half pad 21 and the lower half pad 31, that is, between the upper half pad 21 and the lower half pad 31 and the rotating shaft 50, each pad and journal Cooling of the bearing body 40 is promoted, and the load capacity can be increased.

また、上半パッド２１や下半パッド３１は、任意のサイズに作製することが可能であり、そのパッドをジャーナル軸受本体４０の内周面の周方向に配設することができる。そのため、回転軸５０の直径が大きくなっても、ジャーナル軸受本体４０の製造限界に関係なくジャーナル軸受装置１０を製造することができる。さらに、油膜圧力分布の偏芯角を考慮して、パッドの配設位置や個々のパッドの表面の面積を任意に設定することができるので、油膜圧力分布を広範囲に亘らせることができる。これによって、油膜を十分に形成することができるので、負荷容量を増加することができる。また、上半パッド２１や下半パッド３１は、ジャーナル軸受本体４０の内周面に、パッドの背面を直接当接させて固定されるため、ジャーナル軸受本体４０の剛性が増加し、大荷重にも対応することができる。   Further, the upper half pad 21 and the lower half pad 31 can be produced in an arbitrary size, and the pads can be arranged in the circumferential direction of the inner peripheral surface of the journal bearing body 40. Therefore, the journal bearing device 10 can be manufactured regardless of the manufacturing limit of the journal bearing body 40 even if the diameter of the rotary shaft 50 is increased. Furthermore, since the eccentric position of the oil film pressure distribution can be taken into account, the arrangement position of the pads and the area of the surface of each pad can be set arbitrarily, so that the oil film pressure distribution can be spread over a wide range. As a result, the oil film can be sufficiently formed, and the load capacity can be increased. Further, since the upper half pad 21 and the lower half pad 31 are fixed to the inner peripheral surface of the journal bearing main body 40 by directly contacting the back surface of the pad, the rigidity of the journal bearing main body 40 increases and a large load is applied. Can also respond.

（第２の実施の形態）
図６は、本発明に係る第２の実施の形態のジャーナル軸受装置１００における回転軸５０に垂直な断面を示す図である。図７は、本発明に係る第２の実施の形態のジャーナル軸受装置１００における回転軸５０に水平な断面（図６のＢ−Ｂ断面）を示す図である。図８は、下半軸受部３０を上方（回転軸５０側）から見たときの下半軸受部３０における潤滑油の流れの様子を示す図である。図９は、ジャーナル軸受本体４０の内周面に配設された上半パッド２１および下半パッド３１を回転軸５０側から見たときの形状の一例を示す平面図である。図１０は、図９のＣ−Ｃ断面を示す図である。なお、第１の実施の形態のジャーナル軸受装置１０と同一の構成部分には同一の符号を付して重複する説明を省略または簡略する。 (Second Embodiment)
FIG. 6 is a view showing a cross section perpendicular to the rotating shaft 50 in the journal bearing device 100 according to the second embodiment of the present invention. FIG. 7 is a view showing a cross section (cross section BB in FIG. 6) horizontal to the rotary shaft 50 in the journal bearing device 100 according to the second embodiment of the present invention. FIG. 8 is a diagram illustrating the flow of the lubricating oil in the lower half bearing portion 30 when the lower half bearing portion 30 is viewed from above (rotating shaft 50 side). FIG. 9 is a plan view showing an example of the shape of the upper half pad 21 and the lower half pad 31 disposed on the inner peripheral surface of the journal bearing body 40 when viewed from the rotating shaft 50 side. FIG. 10 is a view showing a CC cross section of FIG. In addition, the same code | symbol is attached | subjected to the component same as the journal bearing apparatus 10 of 1st Embodiment, and the overlapping description is abbreviate | omitted or simplified.

図６および図７に示すように、ジャーナル軸受装置１００は、第１の実施の形態のジャーナル軸受装置１０における、上半軸受部２０の内周面に周方向に沿って所定の間隔をあけて配設された複数の上半パッド２１からなるパッド列および下半軸受部３０の内周面に周方向に沿って所定の間隔をあけて配設された複数の下半パッド３１からなるパッド列を、軸方向に所定の間隔をあけてそれぞれ２列備えている。また、下半軸受部３０における各パッド列において複数の下半パッド３１のうちの１つが、回転軸５０の鉛直下方に配設されている。なお、パット列は、軸方向に所定の間隔をあけて３列以上設けてもよい。   As shown in FIGS. 6 and 7, the journal bearing device 100 has a predetermined interval along the circumferential direction on the inner peripheral surface of the upper half bearing portion 20 in the journal bearing device 10 of the first embodiment. A pad row made up of a plurality of upper half pads 21 and a pad row made up of a plurality of lower half pads 31 arranged at predetermined intervals along the circumferential direction on the inner peripheral surface of the lower half bearing portion 30. Are provided in two rows at predetermined intervals in the axial direction. In addition, one of the plurality of lower half pads 31 in each pad row in the lower half bearing portion 30 is disposed vertically below the rotary shaft 50. Note that three or more pad rows may be provided at predetermined intervals in the axial direction.

また、ここでは、上半軸受部２０における上半パッド２１のパッド列と、下半軸受部３０における下半パッド３１のパッド列とが、円周方向に直列、すなわち同一円周上に一列に備えられた一例を示しているが、この配設構成に限られるものではない。例えば、円周方向に並列、すなわち、上半軸受部２０における上半パッド２１のパッド列と下半軸受部３０における下半パッド３１のパッド列とが、同一円周上に配設されない構成であってもよい。さらに、上半軸受部２０および下半軸受部３０において、軸方向に複数のパッド列を設ける場合、各パッド列のパッド数が異なる配設構成であってもよい。具体的には、例えば、一方の下半パッド３１のパッド列におけるパッド数が３つで、それに所定の間隔をあけて隣接する他方の下半パッド３１のパッド列におけるパッド数が２つであってもよい。このように、上半軸受部２０および下半軸受部３０の内周面に複数に分割して配設されるパッドの配設構成は、例えばミスアライメント等に対応して適宜に設定することができる。   Here, the pad row of the upper half pad 21 in the upper half bearing portion 20 and the pad row of the lower half pad 31 in the lower half bearing portion 30 are serially arranged in the circumferential direction, that is, in a row on the same circumference. Although an example provided is shown, it is not limited to this arrangement configuration. For example, in a configuration parallel to the circumferential direction, that is, the pad row of the upper half pad 21 in the upper half bearing portion 20 and the pad row of the lower half pad 31 in the lower half bearing portion 30 are not arranged on the same circumference. There may be. Furthermore, in the upper half bearing portion 20 and the lower half bearing portion 30, when a plurality of pad rows are provided in the axial direction, an arrangement configuration in which the number of pads in each pad row is different may be employed. Specifically, for example, the number of pads in the pad row of one lower half pad 31 is three, and the number of pads in the pad row of the other lower half pad 31 adjacent to it at a predetermined interval is two. May be. As described above, the arrangement of the pads arranged in a plurality of portions on the inner peripheral surfaces of the upper half bearing portion 20 and the lower half bearing portion 30 can be appropriately set corresponding to, for example, misalignment. it can.

また、軸方向に設けられたパット列間の所定の間隔は、そのパット列間に形成される間隙を潤滑油が流動可能な程度であることが好ましく、潤滑油の粘度等や使用される温度条件等に基づいて適宜設定される。   The predetermined interval between the pad rows provided in the axial direction is preferably such that the lubricating oil can flow through the gap formed between the pad rows, and the viscosity of the lubricating oil and the temperature used It is set appropriately based on conditions and the like.

また、ジャーナル軸受本体４０の中心軸と回転軸５０の中心軸とが平行にならずにずれた状態であるミスアライメントが生じた場合には、第１の実施の形態のジャーナル軸受装置１０の場合と同様に、所定の上半パッド２１の背面と上半軸受部２０の内周面との間、および／または所定の下半パッド３１の背面と下半軸受部３０の内周面との間に、薄板として機能するライナを介在させてそれぞれのパッド２１、３１を固定し、軸受ギャップを調整するようにしてもよい。ジャーナル軸受装置１００においては、軸方向にパットを複数列設けることができるので、例えば、各列毎に異なる軸受ギャップの調整をすることができる。   Further, in the case of misalignment in which the center axis of the journal bearing body 40 and the center axis of the rotary shaft 50 are not parallel but shifted, the journal bearing device 10 according to the first embodiment is used. Similarly, between the back surface of the predetermined upper half pad 21 and the inner peripheral surface of the upper half bearing portion 20 and / or between the rear surface of the predetermined lower half pad 31 and the inner peripheral surface of the lower half bearing portion 30. In addition, a liner functioning as a thin plate may be interposed to fix the pads 21 and 31 to adjust the bearing gap. In the journal bearing device 100, since a plurality of rows of pads can be provided in the axial direction, for example, a different bearing gap can be adjusted for each row.

次に、ジャーナル軸受装置１００の下半軸受部３０における潤滑油の流れの様子を、図８を参照して説明する。   Next, the flow of the lubricating oil in the lower half bearing portion 30 of the journal bearing device 100 will be described with reference to FIG.

図８では、図の縦方向に、下半軸受部３０の内周面に周方向に沿って所定の間隔をあけて配設された下半パッド３１の２つのパット列を平面的に示している。したがって、例えば、回転軸５０の鉛直下方に配設される下半パッド３１は、図８に示された下半パッド３１のうちの上から２番の下半パッド３１となる。なお、潤滑油は、例えば、上半軸受部２０の頂上部かつパッド列間からジャーナル軸受本体４０内に供給される。   In FIG. 8, two pad rows of the lower half pads 31 arranged in the longitudinal direction of the figure on the inner circumferential surface of the lower half bearing portion 30 at a predetermined interval along the circumferential direction are shown in plan view. Yes. Therefore, for example, the lower half pad 31 disposed vertically below the rotation shaft 50 is the second lower half pad 31 from the top of the lower half pads 31 shown in FIG. The lubricating oil is supplied into the journal bearing body 40 from the top of the upper half bearing portion 20 and between the pad rows, for example.

図８に示すように、パット列間の間隙１１０を流れる潤滑油が主流１２０となり、この主流１２０から、各下半パッド３１上および各パット列の各下半パッド３１の間隙に分流する。また、各パット列の各下半パッド３１の間隙に分流した潤滑油も、下半パッド３１上に流入する。主流１２０を流れる潤滑油は、下半パッド３１上を流れる潤滑油よりも低温であるため、常時低温の潤滑油を下半パッド３１上に供給することが可能となる。なお、上半パッド２１においても、下半パッド３１の場合と同様の潤滑油の流れとなる。このように、低温の潤滑油を、上半パッド２１および下半パッド３１上、すなわち上半パッド２１および下半パッド３１と回転軸５０との間に供給することができるので、各パッドおよびジャーナル軸受本体４０の冷却が促進され、負荷容量を増加させることができる。   As shown in FIG. 8, the lubricating oil flowing through the gap 110 between the pad rows becomes the main flow 120, and is divided from the main flow 120 into the gaps between the lower half pads 31 and the lower half pads 31 of each pad row. In addition, the lubricating oil that has been split into the gaps between the lower half pads 31 of each pad row also flows onto the lower half pads 31. Since the lubricating oil flowing in the main flow 120 is at a lower temperature than the lubricating oil flowing on the lower half pad 31, it is possible to always supply a low-temperature lubricating oil onto the lower half pad 31. The upper half pad 21 also has the same lubricating oil flow as that of the lower half pad 31. Thus, since the low temperature lubricating oil can be supplied on the upper half pad 21 and the lower half pad 31, that is, between the upper half pad 21 and the lower half pad 31 and the rotating shaft 50, each pad and journal Cooling of the bearing body 40 is promoted, and the load capacity can be increased.

また、上半パッド２１および下半パッド３１の形状の一例を図９および図１０を参照して説明する。   An example of the shape of the upper half pad 21 and the lower half pad 31 will be described with reference to FIGS.

図９および図１０に示すように、上記した上半パッド２１および下半パッド３１において、潤滑油１２１が上半パッド２１および下半パッド３１上に流入する側の端縁を傾斜面１５０で構成している。この傾斜面は、上半パッド２１および下半パッド３１の外側に向かって下方傾斜している。このように潤滑油１２１が流入する側の端縁を傾斜面１５０で構成することにより、潤滑油１２１は、上半パッド２１および下半パッド３１上にスムーズに導くことができる。なお、この上半パッド２１および下半パッド３１の構成を、前述した第１の実施の形態のジャーナル軸受装置１０の上半パッド２１および下半パッド３１に備えてもよい。   As shown in FIGS. 9 and 10, in the upper half pad 21 and the lower half pad 31 described above, the edge on the side where the lubricating oil 121 flows into the upper half pad 21 and the lower half pad 31 is constituted by the inclined surface 150. is doing. This inclined surface is inclined downward toward the outside of the upper half pad 21 and the lower half pad 31. By configuring the edge on the side into which the lubricating oil 121 flows in this way with the inclined surface 150, the lubricating oil 121 can be smoothly guided onto the upper half pad 21 and the lower half pad 31. The configurations of the upper half pad 21 and the lower half pad 31 may be provided in the upper half pad 21 and the lower half pad 31 of the journal bearing device 10 according to the first embodiment described above.

上記した第２の実施の形態のジャーナル軸受装置１００によれば、上半軸受部２０の内周面に周方向に沿って所定の間隔をあけて配設された複数の上半パッド２１からなるパッド列および下半軸受部３０の内周面に周方向に沿って所定の間隔をあけて配設された複数の下半パッド３１からなるパッド列を、回転軸５０の軸方向に所定の間隔をあけて複数列備えることで、軸受ギャップの調整等を容易にかつ適確に行なうことができる。   According to the journal bearing device 100 of the above-described second embodiment, the journal bearing device 100 includes a plurality of upper half pads 21 disposed on the inner circumferential surface of the upper half bearing portion 20 at a predetermined interval along the circumferential direction. A pad row composed of a plurality of lower half pads 31 arranged at predetermined intervals along the circumferential direction on the inner peripheral surface of the pad row and the lower half bearing portion 30 is set at a predetermined interval in the axial direction of the rotary shaft 50. By providing a plurality of rows with a gap, adjustment of the bearing gap and the like can be performed easily and accurately.

また、パット列間の間隙１１０を流れる低温の潤滑油が主流１２０となり、この主流１２０から分流して、上半パッド２１や下半パッド３１上に低温の潤滑油を導くことができるので、パッドや軸受の冷却を効率よく行なうことができる。これによって、ジャーナル軸受装置１００の負荷容量の増加等を図ることができる。さらに、潤滑油が上半パッド２１および下半パッド３１上に流入する側の端縁を傾斜面１５０で構成することで、潤滑油が上半パッド２１および下半パッド３１上にスムーズに導かれようになり、上記したパッドの冷却効率をさらに向上させることができる。   Further, the low-temperature lubricating oil flowing through the gap 110 between the pad rows becomes the main flow 120, and the low-temperature lubricating oil can be guided to the upper half pad 21 and the lower half pad 31 by being diverted from the main flow 120. And cooling of the bearing can be performed efficiently. Thereby, an increase in the load capacity of the journal bearing device 100 can be achieved. Further, the end surface on the side where the lubricant flows into the upper half pad 21 and the lower half pad 31 is formed by the inclined surface 150, so that the lubricant is smoothly guided onto the upper half pad 21 and the lower half pad 31. As a result, the cooling efficiency of the pad can be further improved.

また、上半パッド２１や下半パッド３１は、任意のサイズに作製することが可能であり、そのパッドをジャーナル軸受本体４０の内周面の周方向に配設することができる。そのため、回転軸５０の直径が大きくなっても、ジャーナル軸受本体４０の製造限界に関係なくジャーナル軸受装置１００を製造することができる。さらに、油膜圧力分布の偏芯角を考慮して、パッドの配設位置や個々のパッドの表面の面積を任意に設定することができるので、油膜圧力分布を広範囲に亘らせることができる。これによって、油膜を十分に形成することができるので、負荷容量を増加することができる。また、上半パッド２１や下半パッド３１は、ジャーナル軸受本体４０の内周面に、パッドの背面を直接当接させて固定されるため、ジャーナル軸受本体４０の剛性が増し、大荷重にも対応することができる。   Further, the upper half pad 21 and the lower half pad 31 can be produced in an arbitrary size, and the pads can be arranged in the circumferential direction of the inner peripheral surface of the journal bearing body 40. Therefore, even if the diameter of the rotating shaft 50 increases, the journal bearing device 100 can be manufactured regardless of the manufacturing limit of the journal bearing body 40. Furthermore, since the eccentric position of the oil film pressure distribution can be taken into account, the arrangement position of the pads and the area of the surface of each pad can be set arbitrarily, so that the oil film pressure distribution can be spread over a wide range. As a result, the oil film can be sufficiently formed, and the load capacity can be increased. Further, since the upper half pad 21 and the lower half pad 31 are fixed to the inner peripheral surface of the journal bearing body 40 by directly contacting the back surface of the pad, the rigidity of the journal bearing body 40 is increased, and a large load is also applied. Can respond.

以上、本発明を実施の形態により具体的に説明したが、本発明はこれらの実施の形態にのみ限定されるものではなく、その要旨を逸脱しない範囲で種々変更可能である。   Although the present invention has been specifically described above with reference to the embodiments, the present invention is not limited to these embodiments, and various modifications can be made without departing from the scope of the invention.

本発明に係る第１の実施の形態のジャーナル軸受装置における回転軸に垂直な断面を示す図。The figure which shows a cross section perpendicular | vertical to the rotating shaft in the journal bearing apparatus of 1st Embodiment concerning this invention. 本発明に係る第１の実施の形態のジャーナル軸受装置における回転軸に水平な断面（図１のＡ−Ａ断面）を示す図。The figure which shows the cross section (AA cross section of FIG. 1) horizontal to the rotating shaft in the journal bearing apparatus of 1st Embodiment which concerns on this invention. 下半パッドと下半軸受部の内周面との間にライナを介在させたときの、下半軸受部における回転軸に水平な断面を示す図。The figure which shows a horizontal cross section to the rotating shaft in a lower half bearing part when a liner is interposed between the lower half pad and the inner peripheral surface of a lower half bearing part. 油膜圧力分布の偏芯角θに対応して下半パッドを設けた場合のジャーナル軸受装置における回転軸に垂直な断面を示す図。The figure which shows a cross section perpendicular | vertical to the rotating shaft in the journal bearing apparatus when the lower half pad is provided corresponding to the eccentric angle (theta) of oil film pressure distribution. 油膜圧力分布の偏芯角θに対応して下半パッドを設けた場合のジャーナル軸受装置における回転軸に垂直な断面を示す図。The figure which shows a cross section perpendicular | vertical to the rotating shaft in the journal bearing apparatus when the lower half pad is provided corresponding to the eccentric angle (theta) of oil film pressure distribution. 本発明に係る第２の実施の形態のジャーナル軸受装置における回転軸に垂直な断面を示す図。The figure which shows a cross section perpendicular | vertical to the rotating shaft in the journal bearing apparatus of 2nd Embodiment which concerns on this invention. 本発明に係る第２の実施の形態のジャーナル軸受装置における回転軸に水平な断面（図６のＢ−Ｂ断面）を示す図。The figure which shows a cross section (BB cross section of FIG. 6) horizontal to the rotating shaft in the journal bearing apparatus of 2nd Embodiment which concerns on this invention. 下半軸受部を上方から見たときの下半軸受部における潤滑油の流れの様子を示す図。The figure which shows the mode of the flow of the lubricating oil in a lower half bearing part when a lower half bearing part is seen from upper direction. ジャーナル軸受本体の内周面に配設された上半パッドおよび下半パッドを回転軸側から見たときの形状の一例を示す平面図。The top view which shows an example of a shape when the upper half pad and lower half pad which were arrange | positioned at the internal peripheral surface of a journal bearing main body are seen from the rotating shaft side. 図９のＣ−Ｃ断面を示す図。The figure which shows CC cross section of FIG. 従来のジャーナル軸受装置の断面の構造を示す図。The figure which shows the structure of the cross section of the conventional journal bearing apparatus. 従来のジャーナル軸受装置の断面の構造を示す図。The figure which shows the structure of the cross section of the conventional journal bearing apparatus. 従来のジャーナル軸受装置の断面の構造を示す図。The figure which shows the structure of the cross section of the conventional journal bearing apparatus.

符号の説明Explanation of symbols

１０…ジャーナル軸受装置、２０…上半軸受部、２１…上半パッド、２１ａ、３１ａ…表面層、２１ｂ、３１ｂ…基材、３０…下半軸受部、３１…下半パッド、３１ａ…、３１ｂ…、３５…ライナ、４０…ジャーナル軸受本体、５０…回転軸、Ｗ…重力方向荷重。   DESCRIPTION OF SYMBOLS 10 ... Journal bearing apparatus, 20 ... Upper half bearing part, 21 ... Upper half pad, 21a, 31a ... Surface layer, 21b, 31b ... Base material, 30 ... Lower half bearing part, 31 ... Lower half pad, 31a ..., 31b ..., 35 ... liner, 40 ... journal bearing body, 50 ... rotating shaft, W ... gravity direction load.

Claims (10)

回転軸を支承する軸受の上半軸受に上半パッドを備え、下半軸受に下半パッドを備えるジャーナル軸受装置であって、
前記下半軸受の内周面の周方向に沿って所定の間隔をあけて前記下半パッドが複数配設され、該複数の下半パッドのうちの１つが、回転軸の鉛直下方に配設されていることを特徴とするジャーナル軸受装置。 A journal bearing device having an upper half pad on an upper half bearing and a lower half pad on a lower half bearing, each bearing a rotary shaft.
A plurality of the lower half pads are arranged at predetermined intervals along the circumferential direction of the inner peripheral surface of the lower half bearing, and one of the plurality of lower half pads is arranged vertically below the rotating shaft. A journal bearing device characterized by that. 回転軸を支承する軸受の上半軸受に上半パッドを備え、下半軸受に下半パッドを備えるジャーナル軸受装置であって、
前記下半軸受の内周面の周方向に沿って所定の間隔をあけて前記下半パッドが複数配設されてなるパッド列を、前記回転軸の軸方向に所定の間隔をあけて複数列備え、該各パッド列において複数の下半パッドのうちの１つが、回転軸の鉛直下方に配設されていることを特徴とするジャーナル軸受装置。 A journal bearing device having an upper half pad on an upper half bearing and a lower half pad on a lower half bearing, each bearing a rotary shaft.
A plurality of rows of pad rows in which a plurality of lower half pads are arranged at predetermined intervals along the circumferential direction of the inner peripheral surface of the lower half bearing are arranged at predetermined intervals in the axial direction of the rotary shaft. A journal bearing device, wherein one of a plurality of lower half pads in each pad row is disposed vertically below the rotation shaft. 少なくとも前記下半パッドの表面が、熱可塑性樹脂材料で形成されていることを特徴とする請求項１または２記載のジャーナル軸受装置。   The journal bearing device according to claim 1, wherein at least a surface of the lower half pad is formed of a thermoplastic resin material. 少なくとも前記下半パッドの表面が、セラミックス繊維、二硫化モリブデン粒子または黒鉛粒子のうち少なくとも１種を含有した熱可塑性樹脂材料で形成されていることを特徴とする請求項１または２記載のジャーナル軸受装置。   3. The journal bearing according to claim 1, wherein at least a surface of the lower half pad is formed of a thermoplastic resin material containing at least one of ceramic fibers, molybdenum disulfide particles or graphite particles. apparatus. 前記上半パッドの表面が、軟金属材料で形成されていることを特徴とする請求項１乃至４のいずれか１項記載のジャーナル軸受装置。   5. The journal bearing device according to claim 1, wherein a surface of the upper half pad is formed of a soft metal material. 前記上半パッドおよび前記下半パッドが、着脱可能に設けられていることを特徴とする請求項１乃至５のいずれか１項記載のジャーナル軸受装置。   The journal bearing device according to any one of claims 1 to 5, wherein the upper half pad and the lower half pad are detachably provided. 所定の前記上半パッドと上半軸受の内周面との間に、薄板を介在させて前記上半パッドを固定可能なことを特徴とする請求項１乃至６のいずれか１項記載のジャーナル軸受装置。   The journal according to any one of claims 1 to 6, wherein the upper half pad can be fixed with a thin plate interposed between the predetermined upper half pad and an inner peripheral surface of the upper half bearing. Bearing device. 所定の前記下半パッドと下半軸受の内周面との間に、薄板を介在させて前記下半パッドを固定可能なことを特徴とする請求項１乃至７のいずれか１項記載のジャーナル軸受装置。   The journal according to any one of claims 1 to 7, wherein the lower half pad can be fixed with a thin plate interposed between the predetermined lower half pad and an inner peripheral surface of the lower half bearing. Bearing device. 前記上半パッドにおいて、少なくとも、前記上半パッドの表面上に潤滑油を流入させる側の端縁が傾斜面で構成されていることを特徴とする請求項１乃至８のいずれか１項記載のジャーナル軸受装置。   9. The upper half pad according to any one of claims 1 to 8, wherein at least an edge on a side where lubricating oil is allowed to flow onto the surface of the upper half pad is formed by an inclined surface. Journal bearing device. 前記下半パッドにおいて、少なくとも、前記下半パッドの表面上に潤滑油を流入させる側の端縁が傾斜面で構成されていることを特徴とする請求項１乃至９のいずれか１項記載のジャーナル軸受装置。   10. The lower half pad according to claim 1, wherein at least an edge on a side where lubricating oil is allowed to flow onto the surface of the lower half pad is formed by an inclined surface. 11. Journal bearing device.
JP2007084966A 2007-03-28 2007-03-28 Journal bearing device Expired - Fee Related JP5197977B2 (en)

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