WO2016088166A1 - ジャーナル軸受 - Google Patents
ジャーナル軸受 Download PDFInfo
- Publication number
- WO2016088166A1 WO2016088166A1 PCT/JP2014/081721 JP2014081721W WO2016088166A1 WO 2016088166 A1 WO2016088166 A1 WO 2016088166A1 JP 2014081721 W JP2014081721 W JP 2014081721W WO 2016088166 A1 WO2016088166 A1 WO 2016088166A1
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- WO
- WIPO (PCT)
- Prior art keywords
- oil supply
- oil
- pad
- journal bearing
- lubricating oil
- Prior art date
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Classifications
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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
- 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
- F16C17/02—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
- 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
- F16C33/105—Conditioning, e.g. metering, cooling, filtering
-
- 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
- F16C33/06—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
- F16C33/1085—Channels or passages to recirculate the liquid in the bearing
Definitions
- the present invention relates to a journal bearing that receives a load of a rotary shaft that is horizontally installed with a plurality of pads.
- the conventional journal bearing has a structure in which a plurality of pads are arranged on the inner diameter side of the lower half carrier ring and a pad stop for restricting movement of each pad in the circumferential direction is provided.
- the pad stop had a function as an oil supply nozzle which discharges lubricating oil in order to form an oil film between the outer peripheral surface of a rotating shaft, and the inner peripheral surface of a pad (for example, refer to patent documents 1).
- the amount of lubricating oil supplied from a plurality of pad stops other than the pad stop located at the rearmost side in the axial rotation direction of the rotating shaft of the lower half carrier ring is the same, and the pad stop It was a structure that did not require adjustment of the amount of oil every time. Moreover, the supply amount of the lubricating oil as a whole bearing is reduced by not providing the oil supply nozzle on the upper half carrier ring side.
- an upstream pad is disposed at an upstream position in the axial rotation direction, and a downstream pad is disposed at a downstream position.
- a sufficient amount of lubricating oil necessary for forming an oil film is supplied to all the pads.
- the oil discharged from the upstream pad flows to the downstream pad as the rotating shaft rotates as carry-over oil.
- the supply amount of lubricating oil becomes excessive by the amount of carry-over oil at the downstream side pad.
- This invention has been made to solve the above-mentioned problems, and by adjusting the amount of lubricating oil supplied according to the arrangement of the pads, it can be reduced by optimizing the amount of lubricating oil supplied to the entire journal bearing,
- the purpose is to reduce bearing loss and downsize the oiling equipment.
- the journal bearing according to the present invention is arranged inside the lower half carrier ring, a carrier ring composed of an upper half carrier ring and a lower half carrier ring arranged on the outer peripheral side of a rotating shaft installed horizontally.
- a first pad and a second pad disposed on the downstream side of the first pad, a first oil supply section for supplying lubricating oil between the rotating shaft and the first pad, and the rotation
- a second oil supply unit that supplies lubricating oil between the shaft and the second pad is provided, and the supply amount of the lubricating oil supplied from the second oil supply unit is supplied from the first oil supply unit. It is characterized by being less than the supply amount of lubricating oil.
- the amount of lubricating oil supplied from the second supply unit is less than the amount of lubricating oil supplied from the first supply unit, so that the first and second supply units
- the amount of lubricating oil to be circulated can be reduced as compared with the case where the amount of lubricating oil supplied from is the same, and the oil supply facility can be made smaller and the loss can be reduced.
- the journal bearing of the present invention is a sliding bearing that is used in a horizontally installed rotating machine in which a bearing load works only downward, and rotatably supports a rotating shaft, and includes an upper half carrier ring and a lower half carrier ring. A plurality of pads that are spaced apart from each other and receive the load of the rotating shaft, and an oil supply nozzle for supplying lubricating oil to each pad. This is called a tilting pad journal bearing.
- the journal bearing of the present invention can be applied to, for example, a rotating electrical machine.
- FIG. 1 is a cross-sectional front view of an essential part perpendicular to the axial direction showing a journal bearing 100 according to Embodiment 1 of the present invention.
- FIG. 2 is a cross-sectional side view of an essential part along the line AA in FIG. 1 along the axial direction of the journal bearing 100.
- FIG. 3 is a cross-sectional view of the upstream oil supply nozzle 21a and the downstream oil supply nozzle 31a, which are components of the journal bearing 100, and a plan view showing the discharge ports of the nozzles.
- the journal bearing 100 rotatably supports the rotating shaft 101, and includes a carrier ring 10 having an upper half carrier ring 11 and a lower half carrier ring 12, and a guide disposed radially inside the upper half carrier ring 11.
- An upstream pad 20 (first pad) that receives a load of the rotating shaft 101 and is disposed on the radially inner side of the metal 13 and the lower half carrier ring 12 and a downstream pad 30 (downstream pad)
- the second pad the upstream side oil supply portion 21 (first oil supply portion) for supplying the lubricating oil to the upstream side pad 20 arranged on the upstream side in the rotation direction of the rotating shaft 101, and the downstream side pad 30 are lubricated.
- a downstream oil supply portion 31 (second oil supply portion) for supplying oil is provided, and further, the downstream pad 30 and the guide metal 13 on the upstream side in the rotation direction of the guide metal 13. Between, a guide metal oil supply nozzle 41 for supplying lubricating oil to the guide metal 13.
- the upstream side oil supply unit 21 supplies lubricating oil between the upstream side pad 20 and the rotating shaft 101 to form an oil film, so that the upstream side of the upstream side pad 20, that is, the upstream side pad 20 and the guide metal 13. And a plurality of upstream oil supply nozzles 21a and 21b (first oil supply nozzles) for discharging the lubricating oil.
- the downstream oil supply unit 31 disposed on the downstream side of the upstream oil supply unit 21 supplies the lubricating oil between the downstream pad 30 and the rotating shaft 101 and forms an oil film on the downstream side.
- a plurality of downstream oil supply nozzles 31 a and 31 b (second oil supply nozzles) for discharging lubricating oil are provided on the upstream side of the pad 30, that is, between the upstream pad 20 and the downstream pad 30.
- the upstream oil supply nozzles 21 a and 21 b are arranged at two locations separated from each other.
- the upstream oil supply nozzle 21 a is located between the guide metal 13 and the upstream pad 20 on the upstream side.
- the other upstream oiling nozzle 21 b is disposed near the upstream end of the pad 20, and is disposed in the vicinity of the downstream end of the guide metal 13 near the upstream pad 20. Further, as shown in FIG.
- the downstream oil supply nozzles 31a and 31b are arranged at two positions separated from each other between the upstream pad 20 and the downstream pad 30, for example, the downstream oil supply nozzle 31a
- the other downstream oil supply nozzle 31 b is disposed at the downstream end of the upstream pad 20 close to the downstream pad 30 and is disposed so as to be close to the upstream end of the side pad 30.
- the arrangement of the upstream oil supply nozzles 21a, 21b or the downstream oil supply nozzles 31a, 31b is not limited to the above-described example, and may be an arrangement capable of supplying the lubricating oil to the upstream pad 20 or the downstream pad 30. For example, you may arrange
- lubricating oil is supplied to the oil supply piping part 50 of the journal bearing 100 from the oil supply equipment, and from each nozzle through the piping part which connects each nozzle of the lower half carrier ring 12.
- the lubricating oil discharged to the outer peripheral side of the rotating shaft 101 and discharged from the pad is circulated to the oil supply facility.
- the rotating shaft 101 is rotatably supported by the upstream pad 20 and the downstream pad 30 disposed on the downstream side of the upstream pad 20. At this time, the rotating shaft 101 is not directly supported by the upstream pad 20 and the downstream pad 30 but is supported by an oil film formed between each pad and the rotating shaft 101. Lubricating oil necessary for forming an oil film on the upstream pad 20 or the downstream pad 30 is supplied by the upstream oil supply nozzles 21a and 21b or the downstream oil supply nozzles 31a and 31b.
- the upstream side oil supply nozzle 21 b is configured to discharge the lubricating oil toward the outer peripheral surface side of the rotating shaft 101, and the same applies to the other nozzles.
- the rotating shaft 101 is supported on the upstream pad 20 via lubricating oil (not shown).
- the discharge holes 210 opened in the upstream oil supply nozzle 21a are opened in the same number as the discharge holes 310 opened in the downstream oil supply nozzle 31a.
- the opening diameter of the discharge hole is formed so that the downstream discharge hole 310 is smaller than the upstream discharge hole 210.
- a discharge hole 210 having a large opening diameter is formed from the downstream oil supply nozzle 31a in which the discharge hole 310 having a small opening diameter is formed.
- a smaller amount of lubricating oil is supplied than the upstream oil supply nozzle 21a.
- the guide metal oil supply nozzle 41 is formed in the same shape as the downstream oil supply nozzle 31a and is supplied with the same amount of lubricating oil.
- the upstream oil supply nozzles 21a and 21b have the same shape and are configured to supply the same amount of lubricating oil. Further, the downstream oil supply nozzles 31a and 31b and the guide metal oil supply nozzle 41 have the same shape, and can supply the same amount of lubricating oil as compared with the upstream oil supply nozzle 21a.
- the amount of lubricating oil to be supplied to the upstream pad 20 or the downstream pad 30 of the journal bearing 100 will be described.
- the amount Q of lubricating oil to be supplied to one pad constituting the journal bearing 100 is calculated by the following equation.
- Q K ⁇ h ⁇ L ⁇ v
- Q Oil amount per pad h: Oil film thickness at pad inlet
- L Effective length of pad
- v Shaft rotational peripheral speed
- K Factor
- the opening diameter of the discharge holes 210 and 310 of the oil supply nozzle is adjusted, the opening diameter of the discharge hole 310 is made smaller than the discharge hole 210, and the upstream oil supply section is made by the amount of carryover oil.
- the lubricating oil supply amount of the downstream side oil supply section 31 is less than that of 21.
- journal bearing 100 As the journal bearing 100, one having a shaft diameter of 500 mm was used. And as a comparative example compared with the journal bearing 100 of Embodiment 1 of this invention, it investigated about what the oil quantity supplied from the five oil supply nozzles arrange
- the upstream side pad 20 and the downstream side pad 30 are each supplied with lubricating oil corresponding to the oil amount Q, and the guide metal 13 is lubricated with Q / 2 from the guide metal oil supply nozzle 41. Oil was supplied. The number and diameter of the discharge holes of the five nozzles in total are the same. When looking at the entire journal bearing, the total supply amount of the lubricating oil of the comparative example is 2.5Q.
- journal bearing 100 the same amount of lubricating oil as that of the comparative example is supplied to the upstream pad 20, and the downstream pad 30 is about 35 than the upstream pad 20.
- % Lubricating oil (the amount of oil corresponding to Q- ⁇ ) was supplied, and (Q- ⁇ ) / 2 lubricating oil was supplied to the guide metal 13 from the guide metal oil supply nozzle 41.
- the above-mentioned supply amount was realized by adjusting the size of the diameter of the discharge hole formed in the nozzle.
- the total supply amount of the lubricating oil according to the first embodiment of the present invention could be reduced by about 20% compared to that of the comparative example.
- the loss of the journal bearing 100 of the first embodiment can be reduced by about 25% compared to that of the comparative example.
- the journal bearing 100 sets the amount of lubricating oil supplied to the downstream pad 30 to carry-over oil more than the amount of lubricating oil supplied to the upstream pad 20. Although it was reduced by a corresponding amount, a sufficient oil film can be formed between each pad and the rotating shaft 101, the temperature of the oil film does not become excessively high, shaft vibration does not occur, A good driving condition could be maintained.
- each oil supply nozzle of the journal bearing 100 is connected to an oil supply facility (not shown) via the oil supply pipe portion 50.
- This oil supply facility is a facility for storing and stirring the lubricating oil and circulating the lubricating oil.
- reducing the amount of lubricating oil supplied is an important condition for downsizing the oil supply equipment. If the oil supply facility can be reduced in size, the energy required for the operation of the facility can be reduced accordingly.
- the supply amount of the lubricating oil in the entire bearing can be reduced by about 20% as compared with the comparative example. Therefore, the required amount of lubricating oil itself can be reduced, and the oil supply equipment necessary for circulation can be reduced in size. Further, by reducing the amount of lubricating oil supplied to the downstream pad 30 and supplying a suitable amount of oil to each pad, bearing loss can be reduced by about 25%.
- FIG. 4 is a cross-sectional view of the upstream oil supply nozzle 22a and the downstream oil supply nozzle 31a constituting the journal bearing 100 according to Embodiment 2 of the present invention, and a plan view showing the discharge holes 220 and 310 of each nozzle.
- a discharge hole 220 is formed in the upstream oil supply nozzle 22 a that supplies lubricating oil to the upstream pad 20.
- 25 discharge holes 220 are provided in one upstream-side oil supply nozzle 22a.
- the downstream oil supply nozzle 31a is provided with 17 discharge holes 310 having the same diameter as the discharge holes 220 at 17 places smaller than the upstream oil supply nozzle 22a.
- the number of openings of the upstream oil supply nozzle 22a that requires a large amount of oil is increased according to the amount of supply of the lubricating oil, and less oil.
- the discharge amount can be adjusted by a method of reducing the numerical aperture of the downstream-side oil supply nozzle 31a that requires an amount.
- the diameter of the discharge holes shown in the first embodiment is adjusted. Needless to say, it is possible to use a combination of techniques.
- FIG. 5 is a cross-sectional side view of an essential part perpendicular to the axial direction of the journal bearing 100.
- the upstream side oil supply section 21 has been shown to include two nozzles, the upstream side oil supply nozzles 21a and 21b.
- another upstream side oil supply portion 21 is provided. It shows that the oil supply nozzle 21c is added.
- the upstream pad 20 has three upstream oil supply nozzles 21a, 21b, which are spaced apart from each other.
- the lubricating oil is supplied from 21c, and the downstream pad 30 is supplied from two downstream oil supply nozzles 31a and 31b that are spaced apart from each other, and the downstream pad 30 is more
- the number of nozzles is one less than that of the upstream pad 20.
- the upstream side oil supply nozzles 21a, 21b, 21c, the downstream side oil supply nozzles 31a, 31b, and the guide metal oil supply nozzle 41 have the same nozzle shape (number of openings, opening diameter), the number of nozzles that supply oil per pad. If the number of nozzles is large, the amount of oil supplied is large. Conversely, if the number of nozzles is small, the amount of oil supplied is also small.
- the oil quantity (Q1) equivalent to three nozzles is supplied from the upstream oil supply nozzles 21a, 21b, 21c, and the downstream oil supply nozzles 31a, An oil amount (Q2) for two nozzles can be supplied from 31b, and an oil supply amount close to the verification experiment shown in the first embodiment described above can be realized. Further, in this case, since all the nozzle shapes are the same, the effect that the types of nozzles can be reduced is also obtained.
- three nozzles for supplying oil to the upstream pad 20 and two nozzles for supplying oil to the downstream pad 30 are used.
- two nozzles for supplying oil to the upstream pad 20 and two downstream pads 30 are used.
- FIG. 6 is a cross-sectional side view of an essential part perpendicular to the axial direction of the journal bearing 100.
- the upstream side oil supply unit 21 has shown an example in which two nozzles are formed in the downstream side oil supply unit 31 respectively.
- the upstream side oil supply unit 21 has one It is comprised by the upstream oil supply nozzle 21a, and the downstream oil supply part 31 shows the example comprised by one downstream oil supply nozzle 31a.
- journal bearing 100 of the present invention when the amount of lubricant supplied to the upstream pad 20 is compared with the amount of lubricant supplied to the downstream pad 30, the amount supplied to the downstream pad 30 is carried.
- This is a configuration that reduces the amount of excess oil. Therefore, it is necessary to adjust the oil supply amount of the upstream oil supply nozzle 21a and the downstream oil supply nozzle 31a according to the oil supply amount of each pad.
- each of the nozzles shown in FIG. This can be realized by adjusting the opening diameter, adjusting the numerical aperture of each nozzle shown in FIG. 4 of Embodiment 2, or adjusting them in combination.
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Abstract
Description
このように、従来のジャーナル軸受では、上流側、下流側の各パッドに同量の潤滑油を供給していたため、安定した稼動のためには、軸受全体として必要となる潤滑油供給量が多くなってしまうものであり、各パッドに対し適正な量の潤滑油を供給することが難しいものであった。
この発明の上記以外の目的、特徴、観点および効果は、図面を参照する以下のこの発明の詳細な説明から、さらに明らかになるであろう。
以下、この発明の実施の形態1によるジャーナル軸受について、図1ないし図3を用いて説明する。各図において、同一、または相当部材、部位については同一符号を付して説明する。
本発明のジャーナル軸受は、軸受荷重が下方にのみ働く水平に設置された回転機械に用いられ、回転軸を回転可能に支持する滑り軸受であって、上半部キャリアリングおよび下半部キャリアリングよりなるキャリアリングと、その下半部キャリアリングの半径方向内側に、間隔を空けて配置され、回転軸の荷重を受ける複数のパッドと、各パッドに潤滑油を供給するための給油ノズルを備えた構成であり、ティルティングパッドジャーナル軸受と呼ばれる。本発明のジャーナル軸受は、例えば、回転電機に適用することが可能である。
20に近い、ガイドメタル13の下流側端部の近傍に配置されている。
また、図1に示すように、下流側給油ノズル31a、31bは、上流側パッド20と下流側パッド30の間の、互いに離間した二カ所に配置され、例えば、下流側給油ノズル31aは、下流側パッド30の上流側端部に近接するように配置され、もう一つの下流側給油ノズル31bは、下流側パッド
30に近い、上流側パッド20の下流側端部に配置されている。
また、図1に示すように、潤滑油は、給油設備からジャーナル軸受100の給油配管部50に供給されており、下半部キャリアリング12の各ノズルを繋ぐ配管部を介して、各ノズルから回転軸101外周側へ吐出され、パッド上から排出された潤滑油は、給油設備へと循環される。
また、図3に示すように、上流側給油ノズル21aに開口された吐出孔
210は、下流側給油ノズル31aに開口された吐出孔310と同じ数だけ開口されている。そして吐出孔の開口径は、下流側の吐出孔310の方が、上流側の吐出孔210よりも小さくなるように形成されている。
ジャーナル軸受100に設けられる複数の給油ノズルには、ほぼ均等の油圧がかかるため、開口径が小さい吐出孔310が形成された下流側給油ノズル31aからは、開口径が大きい吐出孔210が形成された上流側給油ノズル21aよりも少ない量の潤滑油が供給される。なお、ガイドメタル用給油ノズル41は、下流側給油ノズル31aと同形状に形成され、同量の潤滑油が供給される。
なお、上流側給油ノズル21aと21bは、同形状であり、同量の潤滑油を供給する構成である。また、下流側給油ノズル31a、31bおよびガイドメタル用給油ノズル41は、同形状であり、同量の、上流側給油ノズル
21aよりも少ない潤滑油を供給することができる。
30に供給すべき潤滑油の油量について説明する。
ジャーナル軸受100を構成するパッド一枚に供給すべき潤滑油の油量Qは下記式で計算される。
Q=K×h×L×v
Q:パッド一枚当たりの給油量
h:パッド入口の油膜厚さ
L:パッドの有効長
v:軸の回転周速
K:係数
そして、下流側給油部31の下流側給油ノズル31a、31bから下流側パッド30に供給される油量Q2は、上流側パッド20から下流側パッド
30に流れ込むキャリーオーバー油の量(α)を、一枚のパッドに供給すべき油量Qから差し引いた量(Q-α)となる(Q2=Q-α)。具体的には、給油ノズルの吐出孔210、310の開口径の大きさを調節し、吐出孔
210よりも吐出孔310の開口径を小さくして、キャリーオーバー油の量だけ、上流側給油部21よりも下流側給油部31の潤滑油供給量が少なくなる構成としている。
ジャーナル軸受100は、軸径500mmのものを用いた。そして、本発明の実施の形態1のジャーナル軸受100と対比させる比較例としては、ジャーナル軸受100に配置された5つの給油ノズルから供給される油量が同量であるものについて調査を行った。
比較例のジャーナル軸受100では、上流側パッド20、下流側パッド
30には、それぞれ油量Qに相当する潤滑油が供給され、ガイドメタル13にはガイドメタル用給油ノズル41からQ/2の潤滑油が供給された。計5つのノズルの吐出孔の数と径は同じである。ジャーナル軸受全体としてみると、比較例の潤滑油の総供給量は2.5Qとなる。
(Q-α)/2の潤滑油が供給された。具体的には、ノズルに形成する吐出孔の径の大きさを調整し、上記の供給量をそれぞれ実現した。ジャーナル軸受全体としてみると、本発明の実施の形態1の潤滑油の総供給量は、比較例のものよりも約20%減とすることができた。また、このとき、実施の形態1のジャーナル軸受100の損失は、比較例のものよりも約25%減とすることが可能となった。
100は、下流側パッド30に供給する潤滑油の量を、上流側パッド20に供給される潤滑油量よりもキャリーオーバー油に相当する分だけ少なくしていたが、各パッドと回転軸101の間に十分な油膜を形成することができ、油膜の温度が過度に高くなることはなく、軸の振動なども発生せず、良好な運転状態を維持することができた。
以下、この発明の実施の形態2のジャーナル軸受100について、図4に基づいて説明する。図4は、本発明の実施の形態2に係るジャーナル軸受
100を構成する上流側給油ノズル22a、下流側給油ノズル31aの断面図、および各ノズルの吐出孔220、310を示す平面図である。図4において、上流側パッド20に潤滑油を供給する上流側給油ノズル22aには、吐出孔220が形成されている。図4の例では、吐出孔220は、一つの上流側給油ノズル22aに、25カ所設けられている。これに対し、下流側給油ノズル31aは、吐出孔220と同径の吐出孔310が、上流側給油ノズル22aよりも少ない17カ所に設けられている。
なお、この実施の形態2で示したように、吐出量に適合するようにノズルの吐出孔の数を調整する手法に加え、実施の形態1において示した、吐出孔の径の大きさを調整する手法を併用することも可能であることは言うまでもない。
以下、この発明の実施の形態3のジャーナル軸受100について図5に基づいて説明する。図5は、ジャーナル軸受100の軸方向に垂直な要部断面側面図である。上述の実施の形態1では、上流側給油部21は、上流側給油ノズル21a、21bの二つのノズルを含む構成であることを示したが、この実施の形態3では、さらにもう一つの上流側給油ノズル21cが追加された構成であることを示している。図5に示すように、上流側パッド20には、互いに離間して配置された3つの上流側給油ノズル21a、21b、
21cから潤滑油が給油される構成であり、下流側パッド30には、互いに離間して配置された2つの下流側給油ノズル31a、31bから給油する構成であり、下流側パッド30の方が、上流側パッド20よりもノズル本数が一本少なくなっている。上流側給油ノズル21a、21b、21c、下流側給油ノズル31a、31b、ガイドメタル用給油ノズル41のノズル形状(開口数、開口径)を同じとする場合、パッド一枚につき給油を行うノズルの本数が多いと供給される油量が多く、逆に、ノズル本数が少ないと供給される油量も少なくなる。
31bからノズル2本分の油量(Q2)を供給することができ、上述の実施の形態1において示した検証実験に近い給油量を実現することが可能である。
また、この場合、全てのノズル形状が同じであるため、ノズルの種類を低減できるという効果も得られる。
以下、この発明の実施の形態4のジャーナル軸受100について図6に基づいて説明する。図6は、ジャーナル軸受100の軸方向に垂直な要部断面側面図である。上述の実施の形態1では、上流側給油部21は、下流側給油部31にそれぞれ二つのノズルを形成した例を示したが、この実施の形態4では、上流側給油部21は、一つの上流側給油ノズル21aによって構成され、下流側給油部31は、一つの下流側給油ノズル31aによって構成された例を示す。
21a、下流側給油ノズル31aの給油量を調整する必要があり、具体的には、実施の形態1の図3で示した各ノズルの開口径の調整、または、実施の形態2の図4で示した各ノズルの開口数の調整、あるいはそれらを組み合わせた調整によって実現することが可能である。
Claims (8)
- 水平に設置された回転軸の外周側に配置された上半部キャリアリングおよび下半部キャリアリングよりなるキャリアリング、
上記下半部キャリアリングの内側に配置された第一のパッドと上記第一のパッドの下流側に配置された第二のパッド、
上記回転軸と上記第一のパッドとの間に潤滑油を供給する第一の給油部、および、上記回転軸と上記第二のパッドとの間に潤滑油を供給する第二の給油部を備え、
上記第二の給油部から供給される潤滑油の供給量は、上記第一の給油部から供給される潤滑油の供給量よりも少ないことを特徴とするジャーナル軸受。 - 上記第二の給油部を構成し、潤滑油を吐出する第二の給油ノズルに開口された吐出孔の径は、上記第一の給油部を構成し、潤滑油を吐出する第一の給油ノズルに開口された吐出孔の径よりも小さいことを特徴とする請求項1記載のジャーナル軸受。
- 上記第二の給油部を構成し、潤滑油を吐出する第二の給油ノズルに開口された吐出孔の数は、上記第一の給油部を構成し、潤滑油を吐出する第一の給油ノズルに開口された吐出孔の数よりも少ないことを特徴とする請求項1または請求項2記載のジャーナル軸受。
- 上記第一の給油部を構成し、潤滑油を吐出する第一の給油ノズルの数よりも、上記第二の給油部を構成し、潤滑油を吐出する第二の給油ノズルの数が少ないことを特徴とする請求項1から3のいずれか一項記載のジャーナル軸受。
- 上記第一の給油部を構成し、潤滑油を吐出する第一の給油ノズルは、互いに離間した二カ所に設けられ、
上記第二の給油部を構成し、潤滑油を吐出する第二の給油ノズルは、互いに離間した二カ所に設けられたことを特徴とする請求項1から3のいずれか一項記載のジャーナル軸受。 - 上記第一の給油部を構成し、潤滑油を吐出する第一の給油ノズルは、互いに離間した三カ所に設けられ、
上記第二の給油部を構成し、潤滑油を吐出する第二の給油ノズルは、互いに離間した二カ所に設けられたことを特徴とする請求項1から4のいずれか一項記載のジャーナル軸受。 - 上記第一の給油部を構成し、潤滑油を吐出する第一の給油ノズルは、一カ所に設けられ、
上記第二の給油部を構成し、潤滑油を吐出する第二の給油ノズルは、一カ所に設けられたことを特徴とする請求項1から3のいずれか一項記載のジャーナル軸受。 - 回転電機に用いることを特徴とする請求項1から7のいずれか一項記載のジャーナル軸受。
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Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11125241A (ja) * | 1997-10-20 | 1999-05-11 | Mitsubishi Heavy Ind Ltd | ジャーナル軸受 |
JP2000274432A (ja) * | 1999-03-19 | 2000-10-03 | Toshiba Corp | パッド型ジャーナル軸受 |
JP2002147455A (ja) * | 2000-11-07 | 2002-05-22 | Mitsubishi Heavy Ind Ltd | 軸受装置、及び、タービン |
WO2010097990A1 (ja) * | 2009-02-27 | 2010-09-02 | 三菱重工業株式会社 | ジャーナル軸受 |
Family Cites Families (5)
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US2459826A (en) * | 1941-09-30 | 1949-01-25 | Cincinnati Milling Machine Co | Fluid pressure bearing |
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US6050727A (en) * | 1997-04-09 | 2000-04-18 | Pioneer Motor Bearing Company | Hydrostatically supported tilting pad journal bearing improvements |
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11125241A (ja) * | 1997-10-20 | 1999-05-11 | Mitsubishi Heavy Ind Ltd | ジャーナル軸受 |
JP2000274432A (ja) * | 1999-03-19 | 2000-10-03 | Toshiba Corp | パッド型ジャーナル軸受 |
JP2002147455A (ja) * | 2000-11-07 | 2002-05-22 | Mitsubishi Heavy Ind Ltd | 軸受装置、及び、タービン |
WO2010097990A1 (ja) * | 2009-02-27 | 2010-09-02 | 三菱重工業株式会社 | ジャーナル軸受 |
Non-Patent Citations (1)
Title |
---|
See also references of EP3228883A4 * |
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