JPH0893769A - Journal bearing device - Google Patents
Journal bearing deviceInfo
- Publication number
- JPH0893769A JPH0893769A JP6231949A JP23194994A JPH0893769A JP H0893769 A JPH0893769 A JP H0893769A JP 6231949 A JP6231949 A JP 6231949A JP 23194994 A JP23194994 A JP 23194994A JP H0893769 A JPH0893769 A JP H0893769A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- dam
- upper half
- rotary shaft
- discharge hole
- 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.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- 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
- F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
-
- 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
- F16C33/1045—Details of supply of the liquid to the bearing
-
- 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
- F16C17/022—Sliding-contact bearings for exclusively rotary movement for radial load only with a pair of essentially semicircular bearing sleeves
-
- 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
- F16C17/24—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
- Motor Or Generator Frames (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明はジャーナル軸受装置に
係り、特にタービンや電動機等のように比較的高速な回
転軸に使用するジャーナル軸受装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a journal bearing device, and more particularly to a journal bearing device used for a relatively high speed rotating shaft such as a turbine or an electric motor.
【０００２】[0002]
【従来の技術】大型のタービンやタービン発電機、電動
機等の高速回転機の回転軸は通常ジャーナル軸受によっ
て支持されており、このジャーナル軸受には、円筒軸受
およびティルティングパッド軸受等が採用されている。
近年特に多く使用されているティルティングパッドジャ
ーナル軸受は、大きな制振力を有するとともに高い安定
性を備えており、他の軸受と比較したとき自励振動に対
してきわめて高い安定性を有している反面、負荷容量が
小さいため高荷重、高面圧な回転機の軸受にはあまり使
用されていない。2. Description of the Related Art The rotating shaft of a high-speed rotating machine such as a large turbine, a turbine generator or an electric motor is usually supported by a journal bearing, and a cylindrical bearing and a tilting pad bearing are adopted as the journal bearing. There is.
Tilt pad journal bearings, which have been widely used in recent years, have a large damping force and high stability, and have extremely high stability against self-excited vibration when compared to other bearings. On the other hand, since it has a small load capacity, it is not often used for bearings of rotating machines with high load and high surface pressure.
【０００３】従来、このような回転機には、真円型の二
円弧軸受や楕円（偏心形二円弧）軸受が使用されている
が、ティルティングパッド軸受とは逆に高荷重、高面圧
には優れているが、オイルウィップやオイルホワールな
どの自励振動に対する安定性に若干の難がある。Conventionally, such a rotating machine has used a true circular two-circle bearing or an elliptical (eccentric two-circle) bearing. Contrary to the tilting pad bearing, a high load and a high surface pressure are used. However, there is some difficulty in stability against self-excited vibration such as oil whip and oil whirl.
【０００４】図４は従来のジャーナル装置に用いられる
二円弧形の軸受の断面を示し、符号１は軸受上半部を、
符号２は軸受下半部をそれぞれ示している。この種のジ
ャーナル軸受では、一般に回転軸の偏心率が大きいほど
軸系は安定となることが知られている（例えば日本機械
学会編・すべり軸受の静特性および動特性資料集）。FIG. 4 shows a cross section of a two-arc bearing used in a conventional journal device, and reference numeral 1 denotes the upper half of the bearing.
Reference numeral 2 indicates the lower half of the bearing. In this type of journal bearing, it is generally known that the greater the eccentricity of the rotating shaft, the more stable the shaft system (for example, the static and dynamic characteristics data collection of slide bearings edited by the Japan Society of Mechanical Engineers).
【０００５】[0005]
【発明が解決しようとする課題】従来のジャーナル軸受
装置では回転軸の偏心率は、通常０．８〜０．９程度に
設計されているが、実際の運転時に計算通りの値が得ら
れず、偏心率が小さい状態で回転して不安定となる不具
合が発生する可能性がある。In the conventional journal bearing device, the eccentricity of the rotary shaft is usually designed to be about 0.8 to 0.9, but the calculated value cannot be obtained during actual operation. However, there is a possibility that a problem may occur in which the eccentricity rotates and becomes unstable.
【０００６】このような場合の対策として、図４および
図５（Ｂ）に示すように軸受下半部２の周面中央部に１
〜数mmの深さを有して供給溝３および排出溝４に通ずる
中央溝５を形成し、軸受上半部１の周面には図５（Ａ）
のように溝６が形成されていて、図６のように中央溝５
のない場合の圧力分布ａを圧力分布ｂのようにして負圧
容量を低下させたり、軸受端部を削落して軸受幅を狭め
ることによって負荷容量を低減させるようにして偏心率
を大きくし、安定化を図るようにしているが、これによ
る場合、溝幅や削り幅を大きくしすぎると偏心率が大き
くなりすぎて膜厚が薄くなり、軸受メタルの焼損をきた
す可能性が生じる。As a countermeasure against such a case, as shown in FIG. 4 and FIG.
A central groove 5 having a depth of ˜several millimeters and communicating with the supply groove 3 and the discharge groove 4 is formed, and the peripheral surface of the upper half portion 1 of the bearing is formed as shown in FIG.
The groove 6 is formed as shown in FIG.
When there is no pressure distribution a, the negative pressure capacity is reduced to a pressure distribution b, or the bearing capacity is reduced by narrowing the bearing end to reduce the bearing capacity to increase the eccentricity. Although it is attempted to stabilize it, in this case, if the groove width or the cut width is too large, the eccentricity becomes too large and the film thickness becomes thin, which may cause the bearing metal to be burned.
【０００７】なお上記の安定問題とは直接関係はない
が、多くの大形の実機においては軸受隙間内の温度を低
減させるため上半部周面に逃げ溝と呼ばれる冷却用の溝
を加工したものがあり、この溝の深さは軸受隙間の５〜
６倍程度と相当に深く、かつ潤滑剤の供給溝および排出
溝に連なっているので圧力は発生しない。Although not directly related to the above stability problem, in many large-sized actual machines, a cooling groove called an escape groove is formed on the upper half peripheral surface in order to reduce the temperature in the bearing gap. The depth of this groove is 5 to the bearing clearance.
No pressure is generated because it is about 6 times deeper and is connected to the lubricant supply groove and the lubricant discharge groove.
【０００８】この発明は、上述した事情を考慮したもの
で、回転軸の不安定な振動を制振するとともに、軸受の
焼損を確実に防止することができるようにしたジャーナ
ル軸受装置を提供することを目的とする。The present invention has been made in view of the above circumstances, and provides a journal bearing device capable of damping unstable vibrations of a rotating shaft and reliably preventing burnout of a bearing. With the goal.
【０００９】[0009]
【課題を解決するための手段】上記目的を達成するた
め、この発明に係るジャーナル軸受装置は請求項１に記
載したように、円筒形軸受面を有する軸受において、こ
の軸受の上半部軸受面に周方向の周溝を形成し、この周
溝の回転方向下流側にダムを設けたものである。In order to achieve the above object, a journal bearing device according to the present invention is a bearing having a cylindrical bearing surface. A circumferential groove is formed in the circumferential direction, and a dam is provided on the downstream side of the circumferential groove in the rotation direction.
【００１０】請求項２では、前記ダムの手前側に排出孔
またはポケットを設け、これにより排出される潤滑剤を
導く配管に調整弁を介装し、その吐出孔に高圧の潤滑剤
を供給するようにしたものであり、請求項３は、上半部
軸受面の周溝の複数箇所に吐出孔を設けるとともに軸受
外にポンプと流量または圧力を調整する調整弁を設け、
これら吐出孔に高圧の潤滑剤を供給するようにしたもの
である。そして請求項４は、軸受の下半部軸受面の中央
部に上半部軸受面に形成されたダム付きの周縁と同様な
周溝、ダム、および排出孔、調整弁を設けたことにあ
る。According to a second aspect of the present invention, a discharge hole or pocket is provided on the front side of the dam, a regulating valve is provided in a pipe for guiding the lubricant discharged by the dam, and a high-pressure lubricant is supplied to the discharge hole. According to a third aspect of the present invention, the discharge holes are provided at a plurality of positions in the circumferential groove of the upper half bearing surface, and the pump and the adjusting valve for adjusting the flow rate or the pressure are provided outside the bearing.
A high-pressure lubricant is supplied to these discharge holes. Further, claim 4 is that a peripheral groove, a dam, a discharge hole, and a regulating valve similar to the peripheral edge with a dam formed on the upper half bearing surface are provided in the center of the lower half bearing surface of the bearing. .
【００１１】[0011]
【作用】調整弁が閉じられていれば、軸受上半部に潤滑
剤の流れがダムによりせき止められることによって溝内
に圧力が発生し、回転軸は前記の圧力によって下半部方
向へ押され、回転軸の偏心率が増加するとともに回転軸
の振動が抑制される。When the adjusting valve is closed, the flow of the lubricant in the upper half of the bearing is dammed by the dam to generate pressure in the groove, and the rotary shaft is pushed toward the lower half by the above pressure. The eccentricity of the rotary shaft increases, and the vibration of the rotary shaft is suppressed.
【００１２】排出孔に連なる配管中の調整弁で流量を制
御するようにすれば、溝内に発生する圧力の大きさを調
整することができる。なお調整弁を全開にすればダム効
果はなくなり、従来の逃げ溝と同じ作用となる。The amount of pressure generated in the groove can be adjusted by controlling the flow rate with the adjusting valve in the pipe connected to the discharge hole. The dam effect disappears when the adjustment valve is fully opened, and the function is the same as the conventional escape groove.
【００１３】一方、軸受外に設けたポンプによって昇圧
した高圧の潤滑剤を吐出孔から供給すれば、軸受上半部
に静圧効果を持たせ、回転軸を下半部に押しつけて前記
と同様に回転軸の偏心率を増加させるとともに回転軸の
振動を抑制する。On the other hand, if a high-pressure lubricant pressurized by a pump provided outside the bearing is supplied from the discharge hole, a static pressure effect is given to the upper half of the bearing, and the rotary shaft is pressed against the lower half so that the same as above. The eccentricity of the rotating shaft is increased and the vibration of the rotating shaft is suppressed.
【００１４】配管に調整弁を設けた場合は、これを全開
にすれば従来と同様に中央溝となって負荷容量は低下す
るが、調整弁を閉じるにしたがってダム効果が生じ、圧
力が発生して負荷容量が回復して行く。When the adjusting valve is provided in the pipe, if it is fully opened, it becomes a central groove to reduce the load capacity as in the conventional case, but as the adjusting valve is closed, a dam effect is produced and pressure is generated. The load capacity will recover.
【００１５】[0015]
【実施例】以下、この発明の実施例を図面について説明
する。図１は本発明によるジャーナル軸受装置の一実施
例の断面を示し、図２（Ａ）はジャーナル軸受装置の上
半部１０、図２（Ｂ）はジャーナル軸受装置の下半部１
１の軸受面をそれぞれ示す展開図である。Embodiments of the present invention will be described below with reference to the drawings. 1 shows a cross section of an embodiment of a journal bearing device according to the present invention. FIG. 2 (A) is an upper half part 10 of the journal bearing device, and FIG. 2 (B) is a lower half part 1 of the journal bearing device.
It is a development view showing each bearing surface of 1.
【００１６】軸受上半部１０の軸受面には、一端にダム
１２を有する周溝１３が形成され、このダム１２の手前
近傍位置には排出孔１４が設けられ、この排出孔１４に
連なる配管１５中には流量の調整弁１６が設けられてい
る。A circumferential groove 13 having a dam 12 at one end is formed on the bearing surface of the upper half 10 of the bearing, and a discharge hole 14 is provided in the vicinity of the front of the dam 12, and a pipe connecting to the discharge hole 14 is formed. A flow rate adjusting valve 16 is provided in the valve 15.
【００１７】上記周溝１３内には複数個の吐出孔１７，
１７が形成されており、この吐出孔１７，１７に連なる
配管１８中には流量または圧力の調整弁１９を介してポ
ンプ２０が設けられている。A plurality of discharge holes 17 are provided in the circumferential groove 13.
17 is formed, and a pump 20 is provided in a pipe 18 connected to the discharge holes 17, 17 via a flow rate or pressure adjusting valve 19.
【００１８】一方、軸受下半部１１の軸受面には、一端
にダム２１を有する中央溝２２が周方向に形成され、こ
のダム２１の手前近傍位置には排出孔２３が設けられ、
この排出孔２３に連なる配管２４中に流量の調整弁２５
が設けられている。On the other hand, on the bearing surface of the lower half 11 of the bearing, a central groove 22 having a dam 21 at one end is formed in the circumferential direction, and a discharge hole 23 is provided in the vicinity of the front of the dam 21.
A flow rate adjusting valve 25 is provided in a pipe 24 connected to the discharge hole 23.
Is provided.
【００１９】上記のような円筒形のジャーナル軸受は、
回転軸２６の偏心率が０．８〜０．９程度になるように
設計されるが、軸受隙間の潤滑剤の温度上昇の見積り誤
差などによって実際に上記偏心率が得られないこともあ
る。また、ジャーナル軸受の回転軸の偏心率が誤差範囲
にあったとしても外乱の影響により不安定を生じる可能
性がある。The cylindrical journal bearing as described above is
Although the eccentricity of the rotating shaft 26 is designed to be about 0.8 to 0.9, the eccentricity may not be actually obtained due to an estimation error of the temperature rise of the lubricant in the bearing gap. Further, even if the eccentricity of the rotary shaft of the journal bearing is within the error range, instability may occur due to the influence of disturbance.
【００２０】この点に関しジャーナル軸受装置は軸受上
半部１０の周溝１３の端部にダム１２を設けることによ
り図３（Ａ）、（Ｂ）に示すように軸受上半部１０に圧
力Ｐを発生させ、回転軸２６の振れ回りを抑制する回転
軸２６の不安定な振動を抑制する手段を構成する一方、
回転軸２６の下半部１１への偏心を増して安定性が高め
られる。但しダム効果が顕著で軸受上半部１０での圧力
が過大になると、回転軸２６の振れ回りが抑制されて安
定ではあるが潤滑膜が薄くなり、膜破断を生じ、破損を
発生する可能性がある。In this respect, in the journal bearing device, by providing the dam 12 at the end of the circumferential groove 13 of the bearing upper half portion 10, the pressure P is applied to the bearing upper half portion 10 as shown in FIGS. 3 (A) and 3 (B). And a means for suppressing unstable vibration of the rotary shaft 26 for suppressing whirling of the rotary shaft 26.
The eccentricity of the lower half portion 11 of the rotary shaft 26 is increased to improve the stability. However, when the dam effect is remarkable and the pressure in the upper half 10 of the bearing becomes excessive, whirling of the rotating shaft 26 is suppressed and the lubricating film becomes thin, although stable, and film breakage may occur, causing damage. There is.
【００２１】それ故、ダム１２の手前側に排出孔１４お
よび流量を調整する調整弁１６を設けていることにより
潤滑剤の流れをせき止める抵抗を与え、ダム効果による
発生圧力を制御することによって膜破断が生じないよう
な適切な偏心率を回転軸２６に与え、軸系を安定に維持
することができ、軸受焼損防止手段を構成している。Therefore, by providing the discharge hole 14 and the adjusting valve 16 for adjusting the flow rate on the front side of the dam 12, a resistance for stopping the flow of the lubricant is given and the pressure generated by the dam effect is controlled to control the film. An appropriate eccentricity that does not cause breakage is given to the rotary shaft 26, the shaft system can be stably maintained, and a bearing burnout prevention unit is configured.
【００２２】また、ジャーナル軸受装置は、軸受外にポ
ンプ２０を設置し、潤滑剤を高圧に昇圧して軸受上半部
１０に供給するようになっており、この静圧効果を利用
したものでは、調整弁１６を全閉にしても十分な偏心率
が得られない場合にポンプ２０を起動し、調整弁１９で
通常流量を調整して静圧をかけ、安定化を図る。また前
記実施例によって十分であっても、軸受上半部１０で潤
滑剤の冷却が不足する場合、調整弁１６を適度に開けた
うえで上記の静圧をかけ、圧力の発生と冷却との双方の
効果を持たせることができる。Further, in the journal bearing device, a pump 20 is installed outside the bearing, and the lubricant is pressurized to a high pressure and supplied to the upper half 10 of the bearing. When the eccentricity is not sufficiently obtained even when the adjusting valve 16 is fully closed, the pump 20 is started, and the adjusting valve 19 adjusts the normal flow rate to apply static pressure to stabilize the eccentricity. Further, even if the above embodiment is sufficient, when the cooling of the lubricant is insufficient in the upper half portion 10 of the bearing, the above-mentioned static pressure is applied after the adjustment valve 16 is appropriately opened to generate the pressure and cool the same. It can have both effects.
【００２３】また、このジャーナル軸受装置には、従来
の軸受下半部１１の中央溝（図５（Ｂ）の５）によって
軸受負荷容量が低下し過ぎ、回転軸２６の偏心率が過大
になった場合にこれを回避する対策がとられている。Further, in this journal bearing device, the bearing load capacity is excessively reduced by the central groove (5 in FIG. 5B) of the conventional bearing lower half portion 11, and the eccentricity of the rotary shaft 26 becomes excessive. If this happens, measures are taken to avoid this.
【００２４】図５（Ｂ）に示す従来の中央溝５は供給溝
３と排出溝４に連通していて溝部に殆んど圧力が発生し
なかったのに対し、このジャーナル軸受装置において
は、図２（Ｂ）にみられるように中央溝２２を供給溝２
８に連通させずに排出溝２９のみに連通させ、途中にダ
ム２１を設け、このダム２１の手前側に排出孔２３およ
び流量の調整弁２５を設けることにより、調整弁２５の
全開時は従来と変らないが、調整弁２５を閉めて行くこ
とによって徐々に圧力が発生し、軸受負荷容量が増して
回転軸を浮上させる。したがって調整弁２５の開度制御
により安定で十分な膜厚を得ることができる。The conventional center groove 5 shown in FIG. 5 (B) communicates with the supply groove 3 and the discharge groove 4 and almost no pressure is generated in the groove portion, whereas in this journal bearing device, As shown in FIG. 2 (B), the central groove 22 is connected to the supply groove 2
8 is communicated with only the discharge groove 29 without being communicated with 8, and a dam 21 is provided on the way, and a discharge hole 23 and a flow rate adjusting valve 25 are provided on the front side of the dam 21, so that when the adjusting valve 25 is fully opened, However, the pressure is gradually generated by closing the adjusting valve 25, the bearing load capacity is increased, and the rotary shaft is levitated. Therefore, a stable and sufficient film thickness can be obtained by controlling the opening degree of the adjusting valve 25.
【００２５】[0025]
【発明の効果】以上のようにこの発明によれば、軸受上
半部にダムを有する周溝とこのダムの手前側に排出孔お
よび排出量調整用調整弁を設けたことにより、ダム効果
による圧力の発生を制御するとともに回転軸に適切な偏
心率を与えることができ、かつ上半部で潤滑剤の冷却を
十分に行なうことができる。As described above, according to the present invention, by providing the circumferential groove having the dam in the upper half of the bearing and the discharge hole and the discharge adjusting valve on the front side of the dam, the dam effect can be obtained. The generation of pressure can be controlled, an appropriate eccentricity can be given to the rotating shaft, and the lubricant can be sufficiently cooled in the upper half portion.
【００２６】また軸受下半部の中央溝にダムを設けると
ともにダムの手前側に排出孔および排出量を調整する調
整弁を設けることにより回転軸の過大な偏心を防ぎ、安
全な膜厚を与えることができる。Further, a dam is provided in the central groove of the lower half of the bearing, and a discharge hole and a regulating valve for regulating the discharge amount are provided on the front side of the dam to prevent excessive eccentricity of the rotary shaft and provide a safe film thickness. be able to.
【図１】この発明に係るジャーナル軸受装置の一実施例
を示す断面図。FIG. 1 is a sectional view showing an embodiment of a journal bearing device according to the present invention.
【図２】（Ａ）はジャーナル軸受装置の軸受上半部の軸
受面の展開図、（Ｂ）は軸受下半部の軸受面の展開図。FIG. 2A is a development view of a bearing surface in an upper half portion of the bearing of the journal bearing device, and FIG. 2B is a development view of a bearing surface in a lower half portion of the bearing.
【図３】（Ａ）はジャーナル軸受装置のダム部の構造
図、（Ｂ）はその圧力分布を示すグラフ。3A is a structural diagram of a dam portion of a journal bearing device, and FIG. 3B is a graph showing a pressure distribution thereof.
【図４】従来のジャーナル軸受装置の断面図。FIG. 4 is a sectional view of a conventional journal bearing device.
【図５】（Ａ）は従来のジャーナル軸受装置の上半部の
軸受面の展開図、（Ｂ）は同下半部の軸受面の展開図。5A is a development view of a bearing surface of an upper half portion of a conventional journal bearing device, and FIG. 5B is a development view of a bearing surface of the lower half portion thereof.
【図６】従来の中央溝と圧力分布図。FIG. 6 is a conventional center groove and pressure distribution diagram.
【符号の説明】 １，１０ 軸受上半部 ２，１１ 軸受下半部 ３，２８ 供給溝 ４，２９ 排出溝 ５，２２ 中央溝 ６ 溝 １２，２１ ダム １３ 周溝 １４，２３ 排出孔 １６，１９，２５ 調整弁 １７ 吐出孔 ２０ ポンプ ２６ 回転軸[Explanation of symbols] 1,10 bearing upper half 2,11 bearing lower half 3,28 supply groove 4,29 discharge groove 5,22 central groove 6 groove 12,21 dam 13 circumferential groove 14,23 discharge hole 16, 19, 25 Adjustment valve 17 Discharge hole 20 Pump 26 Rotating shaft
Claims (4)
の軸受の上半部軸受面に周方向の周溝を形成し、この周
溝の回転方向下流側にダムを設けたことを特徴とするジ
ャーナル軸受装置。1. A bearing having a cylindrical bearing surface, wherein a circumferential circumferential groove is formed on the upper half bearing surface of the bearing, and a dam is provided on the downstream side of the circumferential groove in the rotational direction. Journal bearing device.
トを設け、これにより排出される潤滑剤を導く配管に調
整弁を介装し、その吐出孔に高圧の潤滑剤を供給するよ
うにした請求項１に記載のジャーナル軸受装置。2. A discharge hole or pocket is provided on the front side of the dam, a regulating valve is provided in a pipe for guiding the lubricant discharged by this, and a high-pressure lubricant is supplied to the discharge hole. The journal bearing device according to claim 1.
出孔を設けるとともに軸受外にポンプと流量または圧力
を調整する調整弁を設け、これら吐出孔に高圧の潤滑剤
を供給するようにした請求項１に記載のジャーナル軸受
装置。3. A discharge hole is provided at a plurality of positions in the circumferential groove of the upper half bearing surface, a pump and a regulating valve for adjusting the flow rate or pressure are provided outside the bearing, and a high-pressure lubricant is supplied to these discharge holes. The journal bearing device according to claim 1, configured as described above.
部軸受面に形成されたダム付きの周縁と同様な周溝、ダ
ム、および排出孔、調整弁を設けた請求項２に記載のジ
ャーナル軸受装置。4. A peripheral groove, a dam, a discharge hole, and a regulating valve similar to the peripheral edge with a dam formed on the upper half bearing surface are provided at the center of the lower half bearing surface of the bearing. Journal bearing device according to.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6231949A JPH0893769A (en) | 1994-09-28 | 1994-09-28 | Journal bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6231949A JPH0893769A (en) | 1994-09-28 | 1994-09-28 | Journal bearing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0893769A true JPH0893769A (en) | 1996-04-09 |
Family
ID=16931597
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6231949A Pending JPH0893769A (en) | 1994-09-28 | 1994-09-28 | Journal bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0893769A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100548831B1 (en) * | 1997-03-19 | 2006-06-21 | 가부시끼가이샤 히다치 세이사꾸쇼 | Multiplexing Control Device and Its Recovery Method |
| EP2103823A2 (en) | 2008-03-19 | 2009-09-23 | Hitachi Ltd. | Journal bearing device |
| JP2010116953A (en) * | 2008-11-12 | 2010-05-27 | Hitachi Ltd | Journal bearing device |
| DE102006010698B4 (en) * | 2006-03-08 | 2012-03-29 | Federal-Mogul Wiesbaden Gmbh | Bearing shell and bearing |
| EP2824338A1 (en) | 2013-07-09 | 2015-01-14 | Mitsubishi Hitachi Power Systems, Ltd. | Hydro dynamic bearing device |
| CN110520640A (en) * | 2017-03-24 | 2019-11-29 | 江森自控科技公司 | Pressure dam bearing |
| WO2023247816A1 (en) * | 2022-06-22 | 2023-12-28 | Wärtsilä Finland Oy | Bearing shell, main bearing for a piston engine and piston engine |
-
1994
- 1994-09-28 JP JP6231949A patent/JPH0893769A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100548831B1 (en) * | 1997-03-19 | 2006-06-21 | 가부시끼가이샤 히다치 세이사꾸쇼 | Multiplexing Control Device and Its Recovery Method |
| DE102006010698B4 (en) * | 2006-03-08 | 2012-03-29 | Federal-Mogul Wiesbaden Gmbh | Bearing shell and bearing |
| EP2103823A2 (en) | 2008-03-19 | 2009-09-23 | Hitachi Ltd. | Journal bearing device |
| US8147145B2 (en) | 2008-03-19 | 2012-04-03 | Hitachi, Ltd. | Journal bearing device |
| JP2010116953A (en) * | 2008-11-12 | 2010-05-27 | Hitachi Ltd | Journal bearing device |
| EP2824338A1 (en) | 2013-07-09 | 2015-01-14 | Mitsubishi Hitachi Power Systems, Ltd. | Hydro dynamic bearing device |
| US9255604B2 (en) | 2013-07-09 | 2016-02-09 | Mitsubishi Hitachi Power Systems, Ltd. | Hydro dynamic bearing device |
| US10323688B2 (en) | 2013-07-09 | 2019-06-18 | Mitsubishi Hitachi Power Systems, Ltd. | Hydro dynamic bearing device |
| CN110520640A (en) * | 2017-03-24 | 2019-11-29 | 江森自控科技公司 | Pressure dam bearing |
| WO2023247816A1 (en) * | 2022-06-22 | 2023-12-28 | Wärtsilä Finland Oy | Bearing shell, main bearing for a piston engine and piston engine |
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