JP2012031979A - Thrust bearing - Google Patents
Thrust bearing Download PDFInfo
- Publication number
- JP2012031979A JP2012031979A JP2010174144A JP2010174144A JP2012031979A JP 2012031979 A JP2012031979 A JP 2012031979A JP 2010174144 A JP2010174144 A JP 2010174144A JP 2010174144 A JP2010174144 A JP 2010174144A JP 2012031979 A JP2012031979 A JP 2012031979A
- Authority
- JP
- Japan
- Prior art keywords
- sliding surface
- thrust bearing
- lubricating liquid
- opposed
- groove
- 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
Landscapes
- Sliding-Contact Bearings (AREA)
Abstract
Description
本発明は、液体で潤滑されるスラスト軸受に関する。 The present invention relates to a thrust bearing lubricated with a liquid.
スクリュー圧縮機、水中ポンプなどに、水潤滑軸受が用いられる。従来の水潤滑軸受は、セラミックスやカーボン材料、或いはプラスチックスなどの樹脂材料からなる。また特に、水潤滑スラスト軸受の場合には、その摺動面に潤滑水の通り道となる溝（例えばスパイラル溝）が設けられたものが知られている（例えば、特許文献１）。 Water lubricated bearings are used for screw compressors, submersible pumps, and the like. Conventional water-lubricated bearings are made of a resin material such as ceramics, carbon material, or plastics. In particular, in the case of a water-lubricated thrust bearing, it is known that a groove (for example, a spiral groove) serving as a passage for lubricating water is provided on the sliding surface (for example, Patent Document 1).
水潤滑スラスト軸受に用いられるセラミックスやカーボン材料は、水中での摺動特性には優れているが、流体潤滑領域での使用状態ではなく、相手材（支持対象面）と直接接触するため、相手材とのなじみや相手材の耐摩耗性の問題点がある。 Ceramics and carbon materials used in water-lubricated thrust bearings have excellent sliding characteristics in water, but they are not used in the fluid lubrication area, and are in direct contact with the mating material (supported surface). There is a problem of familiarity with the material and wear resistance of the mating material.
また、プラスチックスなどの樹脂材料は、低強度、低ヤング率でありかつ膨潤しやすく変形や摩耗が生じやすいため寿命が短い問題点がある。 In addition, resin materials such as plastics have a problem of short life because they have low strength and low Young's modulus, and are easily swelled and easily deformed and worn.
さらに、摺動面に潤滑水の通り道となる溝を設けていても、摺動面の回転により摺動部の潤滑水が遠心力で外部に排出されてしまうため、焼付が生じる可能性がある。またこの溝がスパイラル溝であっても、スパイラル溝のみでは負荷容量が低い問題点があった。 Furthermore, even if the sliding surface is provided with a groove serving as a passage for lubricating water, the lubricating water in the sliding portion is discharged to the outside by centrifugal force due to rotation of the sliding surface, so that seizure may occur. . Further, even if this groove is a spiral groove, there is a problem that the load capacity is low only by the spiral groove.
本発明は、上述した問題点を解決するために創案されたものである。すなわち、本発明の目的は、潤滑液で潤滑され回転軸のスラスト荷重を支持することができ、遠心力に抗して摺動面に潤滑液を供給することができ、かつ摺動面における負荷容量を高めることができるスラスト軸受を提供することにある。 The present invention has been developed to solve the above-described problems. That is, the object of the present invention is to support the thrust load of the rotating shaft that is lubricated with the lubricating liquid, supply the lubricating liquid to the sliding surface against centrifugal force, and load on the sliding surface. An object of the present invention is to provide a thrust bearing capable of increasing the capacity.
本発明によれば、回転軸に直交し潤滑液が供給された対向摺動面に沿って相対的に回転し、該回転軸のスラスト荷重を支持するスラスト軸受であって、
前記対向摺動面に対向し、前記対向摺動面の相対的な回転方向に沿って前記対向摺動面との隙間がテーパ状に狭くなる複数のテーパ部と、
該テーパ部に連結して位置し、前記対向摺動面との隙間が一定の複数の平行部と、
前記テーパ部に設けられ、半径方向内端から外端まで延びる複数の溝とを有し、
該溝の中心線上の任意の２点を通る半径方向線と該２点における前記中心線の接線方向線とのなす角度が、外側の角度が内側の角度より大きいスパイラル形状である、ことを特徴とするスラスト軸受が提供される。
According to the present invention, there is provided a thrust bearing that rotates relative to the opposing sliding surface that is orthogonal to the rotating shaft and that is supplied with the lubricating liquid, and that supports the thrust load of the rotating shaft,
A plurality of taper portions facing the opposing sliding surface, wherein a gap between the opposing sliding surface and the opposing sliding surface narrows in a tapered shape along a relative rotation direction of the opposing sliding surface;
A plurality of parallel portions that are connected to the tapered portion and have a constant gap with the opposed sliding surface;
A plurality of grooves provided in the tapered portion and extending from the radially inner end to the outer end;
An angle formed by a radial line passing through any two points on the center line of the groove and a tangential line of the center line at the two points is a spiral shape in which an outer angle is larger than an inner angle. A thrust bearing is provided.
本発明の実施形態によれば、前記対向摺動面は、前記回転軸に固定された円形又は中空円形の回転円板の表面である。 According to an embodiment of the present invention, the opposed sliding surface is a surface of a circular or hollow circular rotating disk fixed to the rotating shaft.
また、本発明の別の実施形態によれば、前記対向摺動面は、固定部材に固定された円形又は中空円形の固定円板の表面である。 According to another embodiment of the present invention, the opposed sliding surface is a surface of a circular or hollow circular fixed disk fixed to a fixed member.
上述した本発明の構成によれば、半径方向内端から外端まで延びる複数の溝がテーパ部に設けられており、該溝の中心線上の任意の２点を通る半径方向線と該２点における前記中心線の接線方向線とのなす角度が、外側の角度が内側の角度より大きいスパイラル形状であるので、対向摺動面に供給された潤滑液が排出されにくく、かつ潤滑液を溝により内方に移動し、溝を介してテーパ部全体に潤滑液を供給することができる。 According to the configuration of the present invention described above, a plurality of grooves extending from the inner end to the outer end in the radial direction are provided in the tapered portion, and the radial line passing through any two points on the center line of the groove and the two points. The angle formed by the tangential direction line of the center line is a spiral shape in which the outer angle is larger than the inner angle, so that the lubricant supplied to the opposed sliding surface is difficult to be discharged, and the lubricant is It can move inward and can supply lubricating liquid to the whole taper part via a groove | channel.
また、複数のテーパ部は対向摺動面の相対的な回転方向に沿って対向摺動面との隙間がテーパ状に狭くなっており、該テーパ部に連結して隙間が一定の複数の平行部が位置しているので、溝を介してテーパ部全体に供給された潤滑液は、テーパ部及び平行部で圧力が上昇し、スラスト荷重を支持する負荷容量を高めることができる。 In addition, the plurality of tapered portions have a narrow gap with the opposing sliding surface along the relative rotational direction of the opposing sliding surface, and are connected to the tapered portion to form a plurality of parallel portions with a constant clearance. Since the portion is positioned, the pressure of the lubricating liquid supplied to the entire tapered portion through the groove increases at the tapered portion and the parallel portion, and the load capacity for supporting the thrust load can be increased.
従って、本発明によれば、対向摺動面に対向する平行部とテーパ部に溝を介して、常に潤滑液を円滑に供給することができる。また潤滑液として低粘度の水を用いても流体潤滑状態を得やすいので、潤滑性能と負荷容量を高めることができ、スラスト軸受の寿命を延ばすことができる。
Therefore, according to the present invention, the lubricating liquid can always be supplied smoothly through the grooves in the parallel portion and the tapered portion that face the opposed sliding surface. Further, even when low viscosity water is used as the lubricating liquid, it is easy to obtain a fluid lubrication state, so that the lubrication performance and load capacity can be increased, and the life of the thrust bearing can be extended.
以下、本発明の好ましい実施形態を添付図面に基づいて詳細に説明する。なお、各図において共通する部分には同一の符号を付し、重複した説明を省略する。 Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. In addition, the same code | symbol is attached | subjected to the common part in each figure, and the overlapping description is abbreviate | omitted.
図１は、本発明によるスラスト軸受の第１実施形態図である。この図において、本発明のスラスト軸受１０は、回転軸１に直交し潤滑液が供給された対向摺動面１１に沿って相対的に回転し、回転軸１のスラスト荷重２を支持するスラスト軸受である。
潤滑液は、好ましくは潤滑水であるが、その他の液体（エマルジョン液、潤滑油）でもよい。また、スラスト軸受１０を潤滑液中で使用するのが好ましいが、対向摺動面１１に向けて潤滑液を連続的又は断続的に供給してもよい。
FIG. 1 is a first embodiment of a thrust bearing according to the present invention. In this figure, a thrust bearing 10 according to the present invention is a thrust bearing that supports the thrust load 2 of the rotating shaft 1 by rotating relatively along the opposed sliding surface 11 that is orthogonal to the rotating shaft 1 and supplied with a lubricating liquid. It is.
The lubricating liquid is preferably lubricating water, but may be other liquid (emulsion liquid, lubricating oil). Although the thrust bearing 10 is preferably used in the lubricating liquid, the lubricating liquid may be supplied continuously or intermittently toward the opposed sliding surface 11.
この例において、スラスト軸受１０は、固定部材４に固定されており、対向摺動面１１は、回転軸１に固定された中空円形の回転円板３の表面（図で右側面）である。なお対向摺動面１１は、スラスト軸受１０の摺動面１０ａと潤滑液を介して近接するが、この図ではその間の隙間を大きく表示している。 In this example, the thrust bearing 10 is fixed to the fixed member 4, and the opposed sliding surface 11 is the surface (right side surface in the drawing) of the hollow circular rotating disk 3 fixed to the rotating shaft 1. The opposing sliding surface 11 is close to the sliding surface 10a of the thrust bearing 10 via the lubricating liquid, but in this figure, the gap between them is shown large.
図２は、図１のＡ−Ａ矢視図であり、図３は、図２のＢ−Ｂ矢視図である。
図２及び図３に示すように、本発明のスラスト軸受１０は、対向摺動面１１に対向する面１０ａに、複数のテーパ部１２、複数の平行部１４及び複数の溝１６を有する。
なお対向摺動面１１は、スラスト軸受１０の摺動面１０ａと潤滑液を介して近接するが、この図ではその間の隙間を大きく表示している。
2 is an AA arrow view of FIG. 1, and FIG. 3 is a BB arrow view of FIG.
As shown in FIGS. 2 and 3, the thrust bearing 10 of the present invention has a plurality of tapered portions 12, a plurality of parallel portions 14, and a plurality of grooves 16 on a surface 10 a facing the opposed sliding surface 11.
The opposing sliding surface 11 is close to the sliding surface 10a of the thrust bearing 10 via the lubricating liquid, but in this figure, the gap between them is shown large.
この例でスラスト軸受１０は、固定部材４（図１参照）に固定された中空円板（中空円形の固定円板）であり、中央に回転軸１（図１参照）が貫通する貫通孔を有する。しかしスラスト軸受１０は、固定部材４に固定された円形の固定円板であってもよい。
スラスト軸受１０は、好ましくはセラミックス、カーボン材、或いは耐腐食性を有する金属からなる。
In this example, the thrust bearing 10 is a hollow disk (hollow circular fixed disk) fixed to the fixing member 4 (see FIG. 1), and has a through-hole through which the rotating shaft 1 (see FIG. 1) passes in the center. Have. However, the thrust bearing 10 may be a circular fixed disk fixed to the fixed member 4.
The thrust bearing 10 is preferably made of a ceramic, a carbon material, or a metal having corrosion resistance.
この例において、テーパ部１２、平行部１４及び溝１６の順で、周方向に等間隔（６０°毎）に６つずつ６組設けられている。しかし、本発明は等間隔に限定されず、不等間隔でもよい。また、テーパ部１２、平行部１４及び溝１６は２組以上であればよい。 In this example, six sets of six taper portions 12, parallel portions 14, and grooves 16 are provided in the order of six at regular intervals (every 60 °) in the circumferential direction. However, the present invention is not limited to equal intervals, and may be irregular intervals. Moreover, the taper part 12, the parallel part 14, and the groove | channel 16 should just be 2 sets or more.
複数（この例で６）のテーパ部１２は、対向摺動面１１に対向し、対向摺動面１１の相対的な回転方向５（この例で回転軸１の回転方向）に沿って対向摺動面１１との隙間がテーパ状に狭くなっている。この例でテーパ部１２の周方向角度は約４０°（図中θ１）である。またテーパ部１２の軸方向距離（図中のＣ）は、約０．０２ｍｍである。なおテーパ部１２の角度と長さは、任意であり、対向摺動面１１との間に流体潤滑状態が得られるように設定するのがよい。 A plurality of (six in this example) taper portions 12 are opposed to the opposing sliding surface 11, and are opposed to each other along the relative rotational direction 5 of the opposing sliding surface 11 (the rotational direction of the rotary shaft 1 in this example). A gap with the moving surface 11 is tapered and narrowed. In this example, the circumferential angle of the tapered portion 12 is about 40 ° (θ1 in the figure). The axial distance (C in the figure) of the taper portion 12 is about 0.02 mm. The angle and length of the taper portion 12 are arbitrary, and are preferably set so that a fluid lubrication state is obtained between the taper portion 12 and the opposed sliding surface 11.
複数（この例で６）の平行部１４は、各テーパ部１２に連結して位置し、対向摺動面１１との隙間が一定になっている。この例で平行部１４の周方向角度は約２０°（図中θ２）である。なお平行部１４の大きさは、任意であり、対向摺動面１１との間に発生する液圧によりスラスト荷重を支持する所望の負荷容量が得られるように設定するのがよい。 A plurality (six in this example) of parallel portions 14 are connected to the respective tapered portions 12 and have a constant gap with the opposed sliding surface 11. In this example, the circumferential angle of the parallel portion 14 is about 20 ° (θ2 in the figure). In addition, the magnitude | size of the parallel part 14 is arbitrary and it is good to set so that the desired load capacity which supports a thrust load with the hydraulic pressure which generate | occur | produces between the opposing sliding surfaces 11 may be obtained.
複数（この例で６）の溝１６は、テーパ部１２に設けられ、半径方向内端から外端まで延びる。
また、溝１６は、対向摺動面１１の相対的な回転方向５（この例で回転軸１の回転方向）の上流側への傾き、すなわち半径方向に対する溝の傾きが、外側が大きく内側が小さいスパイラル形状になっている。
溝１６の断面形状とスパイラル形状は、対向摺動面１１に供給された潤滑液が排出されにくく、かつ潤滑液を溝１６により内方に移動し、溝１６を介してテーパ部全体に潤滑液を供給できるように設定するのがよい。
A plurality of (six in this example) grooves 16 are provided in the tapered portion 12 and extend from the radially inner end to the outer end.
Further, the groove 16 has an inclination toward the upstream side in the relative rotation direction 5 (in this example, the rotation direction of the rotary shaft 1) of the opposed sliding surface 11, that is, the inclination of the groove with respect to the radial direction is large on the outside and on the inside. It has a small spiral shape.
The cross-sectional shape and spiral shape of the groove 16 are such that the lubricating liquid supplied to the opposed sliding surface 11 is difficult to be discharged, and the lubricating liquid is moved inward by the groove 16, and the lubricating liquid is applied to the entire tapered portion via the groove 16. It is good to set so that can be supplied.
図４は、図２における溝１６のスパイラル形状の説明図である。この図において、溝１６の周方向幅の中心線をＤＥとする。
上述した「半径方向に対する溝の傾き」とは、中心線ＤＥ上の任意の点Ｆを通る半径方向線Ｇと任意の点Ｆにおける溝１６の接線方向線Ｈとのなす角度αを意味する。
従って、「この傾きが、外側が大きく内側が小さい」とは、中心線ＤＥ上の任意の２点Ｆ１、Ｆ２を通る半径方向線Ｇ１、Ｇ２と任意の２点Ｆ１、Ｆ２における中心線ＤＥの接線方向線Ｈ１、Ｈ２とのなす角度α１、α２が、外側の角度α１が内側の角度α２より大きいことを意味する。
FIG. 4 is an explanatory diagram of the spiral shape of the groove 16 in FIG. In this figure, the center line of the circumferential width of the groove 16 is set to DE.
The above-mentioned “slope of the groove with respect to the radial direction” means an angle α formed by the radial line G passing through the arbitrary point F on the center line DE and the tangential line H of the groove 16 at the arbitrary point F.
Therefore, “this inclination is large on the outside and small on the inside” means that the radial lines G1 and G2 passing through any two points F1 and F2 on the center line DE and the center line DE at any two points F1 and F2 The angles α1 and α2 formed by the tangential direction lines H1 and H2 mean that the outer angle α1 is larger than the inner angle α2.
図５は、本発明によるスラスト軸受の第２実施形態図である。この図において、本発明のスラスト軸受１０は、回転軸１に直交し潤滑液が供給された対向摺動面１１に沿って相対的に回転し、回転軸１のスラスト荷重２を支持するスラスト軸受である。 FIG. 5 is a diagram showing a second embodiment of a thrust bearing according to the present invention. In this figure, a thrust bearing 10 according to the present invention is a thrust bearing that supports the thrust load 2 of the rotating shaft 1 by rotating relatively along the opposed sliding surface 11 that is orthogonal to the rotating shaft 1 and supplied with a lubricating liquid. It is.
この例において、対向摺動面１１は、固定部材４に固定された中空円形の固定円板６の表面（図で左側面）である。なお、固定円板６は固定部材４と一体であってもよい。 In this example, the opposed sliding surface 11 is the surface (left side surface in the figure) of the hollow circular fixed disk 6 fixed to the fixed member 4. The fixed disk 6 may be integrated with the fixed member 4.
図６は、図５のＡ−Ａ矢視図であり、図７は、図６のＢ−Ｂ矢視図である。
図６及び図７に示すように、本発明のスラスト軸受１０は、対向摺動面１１に対向する面１０ａに、複数のテーパ部１２、複数の平行部１４及び複数の溝１６を有する。
6 is an AA arrow view of FIG. 5, and FIG. 7 is a BB arrow view of FIG.
As shown in FIGS. 6 and 7, the thrust bearing 10 of the present invention has a plurality of tapered portions 12, a plurality of parallel portions 14, and a plurality of grooves 16 on a surface 10 a facing the opposed sliding surface 11.
この例でスラスト軸受１０は、回転軸１に固定された中空円板（中空円形の固定円板）であり、中央に回転軸１が貫通する貫通孔を有する。しかしスラスト軸受１０は、回転軸１に固定された円形の回転円板であってもよい。 In this example, the thrust bearing 10 is a hollow disk (hollow circular fixed disk) fixed to the rotary shaft 1 and has a through-hole through which the rotary shaft 1 passes. However, the thrust bearing 10 may be a circular rotating disk fixed to the rotating shaft 1.
この例において、テーパ部１２は、対向摺動面１１に対向し、対向摺動面１１の相対的な回転方向５（この例で回転軸１の反回転方向）に沿って対向摺動面１１との隙間がテーパ状に狭くなっている。
また溝１６は、対向摺動面１１の相対的な回転方向５（この例で回転軸１の反回転方向）の上流側への傾き、すなわち半径方向に対する溝の傾きが、外側が大きく内側が小さいスパイラル形状になっている。
In this example, the tapered portion 12 faces the opposing sliding surface 11 and faces the opposing sliding surface 11 along the relative rotational direction 5 of the opposing sliding surface 11 (in this example, the counter-rotating direction of the rotary shaft 1). The gap is narrowed in a tapered shape.
Further, the groove 16 has an inclination toward the upstream side in the relative rotation direction 5 (in this example, the counter-rotation direction of the rotating shaft 1) of the opposed sliding surface 11, that is, the inclination of the groove with respect to the radial direction is large on the outside and on the inside. It has a small spiral shape.
すなわち図４に示したように、溝１６の中心線ＤＥ上の任意の２点Ｆ１、Ｆ２を通る半径方向線Ｇ１、Ｇ２とその２点Ｆ１、Ｆ２における中心線ＤＥの接線方向線Ｈ１、Ｈ２とのなす角度α１、α２が、外側の角度α１が内側の角度α２より大きいスパイラル形状になっている。
その他の構成は、第１実施形態と同様である。
That is, as shown in FIG. 4, radial direction lines G1 and G2 passing through arbitrary two points F1 and F2 on the center line DE of the groove 16 and tangential direction lines H1 and H2 of the center line DE at the two points F1 and F2. Are formed in a spiral shape in which the outer angle α1 is larger than the inner angle α2.
Other configurations are the same as those of the first embodiment.
上述したように、本発明のスラスト軸受１０は、セラミックス、カーボン材、又は耐腐食性を有する金属からなり、対向摺動面１１に対向する面をテーパ部１２と平行部１４からなるすべり軸受特有のダム付テーパランド型とし、さらに直線状の溝ではなく、曲率を持たせた溝１６を形成することで外部から潤滑水を取り入れるようになっている。
溝の形状は、半円状やＶ型、凹型などである。この構成により、回転によって外部から内部へ潤滑液を引き込む作用がある。
As described above, the thrust bearing 10 of the present invention is made of ceramics, carbon material, or metal having corrosion resistance, and has a surface opposed to the opposed sliding surface 11 that is unique to the slide bearing having the tapered portion 12 and the parallel portion 14. The tapered land type with a dam is used, and a groove 16 having a curvature is formed instead of a linear groove so that lubricating water is taken in from the outside.
The shape of the groove is semicircular, V-shaped, concave, or the like. With this configuration, the lubricating liquid is drawn from the outside to the inside by rotation.
上述したように本発明の構成によれば、半径方向内端から外端まで延びる複数の溝１６がテーパ部１２に設けられており、溝１６の中心線ＤＥ上の任意の２点Ｆ１、Ｆ２を通る半径方向線Ｇ１、Ｇ２と２点Ｆ１、Ｆ２における中心線ＤＥの接線方向線Ｈ１、Ｈ２とのなす角度α１、α２が、外側の角度α１が内側の角度α２より大きいスパイラル形状であるので、対向摺動面１１に供給された潤滑液が排出されにくく、かつ潤滑液を溝１６により内方に移動し、溝１６を介してテーパ部１２の全体に潤滑液を供給することができる。 As described above, according to the configuration of the present invention, the plurality of grooves 16 extending from the inner end to the outer end in the radial direction are provided in the taper portion 12, and two arbitrary points F1 and F2 on the center line DE of the groove 16 are provided. Since the angles α1 and α2 formed by the radial lines G1 and G2 passing through and the tangential direction lines H1 and H2 of the center line DE at the two points F1 and F2 are spiral shapes, the outer angle α1 is larger than the inner angle α2. The lubricating liquid supplied to the opposed sliding surface 11 is difficult to be discharged, and the lubricating liquid can be moved inward by the groove 16, and the lubricating liquid can be supplied to the entire tapered portion 12 through the groove 16.
また、複数のテーパ部１２は対向摺動面１１の相対的な回転方向５に沿って対向摺動面１１との隙間がテーパ状に狭くなっており、テーパ部１２に連結して隙間が一定の複数の平行部１４が位置しているので、溝１６を介してテーパ部１２の全体に供給された潤滑液は、テーパ部１２及び平行部１４で圧力が上昇し、スラスト荷重を支持する負荷容量を高めることができる。 Further, the gap between the plurality of tapered portions 12 and the opposing sliding surface 11 is narrowed in a taper shape along the relative rotational direction 5 of the opposing sliding surface 11 and is connected to the tapered portion 12 so that the gap is constant. Since the plurality of parallel portions 14 are positioned, the lubricating liquid supplied to the entire taper portion 12 through the groove 16 increases in pressure at the taper portion 12 and the parallel portion 14 and supports the thrust load. Capacity can be increased.
従って、本発明によれな、対向摺動面１１に対向する平行部１４とテーパ部１２に溝１６を介して、常に潤滑液を円滑に供給することができる。また潤滑液として低粘度の水を用いても流体潤滑状態を得やすいので、潤滑性能と負荷容量を高めることができ、スラスト軸受の寿命を延ばすことができる。 Therefore, according to the present invention, the lubricating liquid can always be smoothly supplied to the parallel portion 14 and the tapered portion 12 facing the opposed sliding surface 11 via the groove 16. Further, even when low viscosity water is used as the lubricating liquid, it is easy to obtain a fluid lubrication state, so that the lubrication performance and load capacity can be increased, and the life of the thrust bearing can be extended.
なお、本発明は上述した実施形態に限定されず、特許請求の範囲の記載によって示され、さらに特許請求の範囲の記載と均等の意味および範囲内でのすべての変更を含むものである。 In addition, this invention is not limited to embodiment mentioned above, is shown by description of a claim, and also includes all the changes within the meaning and range equivalent to description of a claim.
１ 回転軸、２ スラスト荷重、３ 回転円板、
４ 固定部材、５ 相対的な回転方向、６ 固定円板、
１０ スラスト軸受、１０ａ 摺動面、１１ 対向摺動面、
１２ テーパ部、１４ 平行部、１６ 溝
1 rotating shaft, 2 thrust load, 3 rotating disc,
4 fixed members, 5 relative rotational directions, 6 fixed disks,
10 Thrust bearing, 10a Sliding surface, 11 Opposing sliding surface,
12 taper part, 14 parallel part, 16 groove
Claims (3)
前記対向摺動面に対向し、前記対向摺動面の相対的な回転方向に沿って前記対向摺動面との隙間がテーパ状に狭くなる複数のテーパ部と、
該テーパ部に連結して位置し、前記対向摺動面との隙間が一定の複数の平行部と、
前記テーパ部に設けられ、半径方向内端から外端まで延びる複数の溝とを有し、
該溝の中心線上の任意の２点を通る半径方向線と該２点における前記中心線の接線方向線とのなす角度が、外側の角度が内側の角度より大きいスパイラル形状である、ことを特徴とするスラスト軸受。 A thrust bearing that is orthogonal to the rotation axis and relatively rotates along an opposing sliding surface to which a lubricating liquid is supplied, and supports a thrust load of the rotation axis;
A plurality of taper portions facing the opposing sliding surface, wherein a gap between the opposing sliding surface and the opposing sliding surface narrows in a tapered shape along a relative rotation direction of the opposing sliding surface;
A plurality of parallel portions that are connected to the tapered portion and have a constant gap with the opposed sliding surface;
A plurality of grooves provided in the tapered portion and extending from the radially inner end to the outer end;
An angle formed by a radial line passing through any two points on the center line of the groove and a tangential line of the center line at the two points is a spiral shape in which an outer angle is larger than an inner angle. And thrust bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010174144A JP2012031979A (en) | 2010-08-03 | 2010-08-03 | Thrust bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010174144A JP2012031979A (en) | 2010-08-03 | 2010-08-03 | Thrust bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2012031979A true JP2012031979A (en) | 2012-02-16 |
Family
ID=45845621
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2010174144A Pending JP2012031979A (en) | 2010-08-03 | 2010-08-03 | Thrust bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2012031979A (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103644138A (en) * | 2013-11-01 | 2014-03-19 | 丹东通博泵业有限公司 | Magnetic pump sliding bearing and application |
| JP2014077475A (en) * | 2012-10-10 | 2014-05-01 | Ihi Corp | Bearing structure and water injection type air compression device |
| JP2017026046A (en) * | 2015-07-23 | 2017-02-02 | 大豊工業株式会社 | Washer |
| KR20180061904A (en) * | 2016-11-30 | 2018-06-08 | 평화오일씰공업주식회사 | Oil film bearing |
| US10200670B2 (en) | 2011-09-30 | 2019-02-05 | Carl Zeiss Optotechnik GmbH | Method and apparatus for determining the 3D coordinates of an object |
| CN109654124A (en) * | 2018-12-19 | 2019-04-19 | 中国科学院长春应用化学研究所 | Active spoil disposal sand water lubriucated bearing |
| US10704593B2 (en) | 2016-09-29 | 2020-07-07 | Ihi Corporation | Bearing structure and turbocharger |
| JP2020180701A (en) * | 2019-04-25 | 2020-11-05 | フロイデンベルグ−エヌオーケー ジェネラル パートナーシップＦｒｅｕｄｅｎｂｅｒｇ−Ｎｏｋ Ｇｅｎｅｒａｌ Ｐａｒｔｎｅｒｓｈｉｐ | Fluid dynamic pressure thrust washer comprising pump function for sparse lubrication applications |
| WO2021073344A1 (en) * | 2019-10-14 | 2021-04-22 | 天津深之蓝海洋设备科技有限公司 | Thrust block, motor, and underwater booster |
| US11898457B2 (en) | 2020-11-17 | 2024-02-13 | Ihi Corporation | Bearing and turbocharger |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01307723A (en) * | 1988-06-06 | 1989-12-12 | Ricoh Co Ltd | Holding structure for rotating polygon mirror |
| JPH08189525A (en) * | 1995-01-10 | 1996-07-23 | Hitachi Ltd | Dynamic pressure bearing spindle motor |
| JP2004293684A (en) * | 2003-03-27 | 2004-10-21 | Nok Corp | Thrust bearing |
-
2010
- 2010-08-03 JP JP2010174144A patent/JP2012031979A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01307723A (en) * | 1988-06-06 | 1989-12-12 | Ricoh Co Ltd | Holding structure for rotating polygon mirror |
| JPH08189525A (en) * | 1995-01-10 | 1996-07-23 | Hitachi Ltd | Dynamic pressure bearing spindle motor |
| JP2004293684A (en) * | 2003-03-27 | 2004-10-21 | Nok Corp | Thrust bearing |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10200670B2 (en) | 2011-09-30 | 2019-02-05 | Carl Zeiss Optotechnik GmbH | Method and apparatus for determining the 3D coordinates of an object |
| JP2014077475A (en) * | 2012-10-10 | 2014-05-01 | Ihi Corp | Bearing structure and water injection type air compression device |
| CN103644138A (en) * | 2013-11-01 | 2014-03-19 | 丹东通博泵业有限公司 | Magnetic pump sliding bearing and application |
| CN103644138B (en) * | 2013-11-01 | 2015-11-11 | 丹东通博泵业有限公司 | Magnetic Drive Pump Sliding Bearing and application |
| JP2017026046A (en) * | 2015-07-23 | 2017-02-02 | 大豊工業株式会社 | Washer |
| US10704593B2 (en) | 2016-09-29 | 2020-07-07 | Ihi Corporation | Bearing structure and turbocharger |
| KR20180061904A (en) * | 2016-11-30 | 2018-06-08 | 평화오일씰공업주식회사 | Oil film bearing |
| CN109654124A (en) * | 2018-12-19 | 2019-04-19 | 中国科学院长春应用化学研究所 | Active spoil disposal sand water lubriucated bearing |
| JP2020180701A (en) * | 2019-04-25 | 2020-11-05 | フロイデンベルグ−エヌオーケー ジェネラル パートナーシップＦｒｅｕｄｅｎｂｅｒｇ−Ｎｏｋ Ｇｅｎｅｒａｌ Ｐａｒｔｎｅｒｓｈｉｐ | Fluid dynamic pressure thrust washer comprising pump function for sparse lubrication applications |
| JP7301785B2 (en) | 2019-04-25 | 2023-07-03 | フロイデンベルグ－エヌオーケー ジェネラル パートナーシップ | Fluid dynamic thrust washer with pump function for sparse lubrication applications |
| WO2021073344A1 (en) * | 2019-10-14 | 2021-04-22 | 天津深之蓝海洋设备科技有限公司 | Thrust block, motor, and underwater booster |
| US11898457B2 (en) | 2020-11-17 | 2024-02-13 | Ihi Corporation | Bearing and turbocharger |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP2012031979A (en) | Thrust bearing | |
| WO2016104535A1 (en) | Sliding bearing and pump | |
| EP2634441A1 (en) | Spiral-grooved thrust bearing | |
| JP6312346B2 (en) | Journal bearing, rotating machine | |
| CN102272467B (en) | Improved journal bearing design | |
| JP5863422B2 (en) | Thrust bearing and rotating machine | |
| US9739310B2 (en) | Tilt pad bearing with through-pivot lubrication | |
| EP2213892A2 (en) | Separator for bearing assemblies with cyclic loads | |
| CN101809299A (en) | Hydrodynamic axial bearing | |
| CN101696728B (en) | Liquid lubricated end face seal structure with cross-scale surface texture characteristic | |
| JP2014533342A (en) | Fluid dynamic pressure thrust bearing | |
| US20050135714A1 (en) | Grooves on both the moving and the stationary mating fluid dynamic bearing surfaces for performance enhancement | |
| EA035325B1 (en) | Hybrid dynamic pressure gas radial bearing | |
| WO2014164576A1 (en) | Bearing with axial variation | |
| JP5761560B2 (en) | Thrust support device | |
| CN1860305B (en) | Ball bearing | |
| JP5635245B2 (en) | Structure of thrust bearing for water lubrication | |
| JP2015158212A (en) | thrust bearing | |
| US9188157B2 (en) | Axial sliding bearing | |
| CN110382890B (en) | Rolling bearing and bearing structure provided with same | |
| US9903412B2 (en) | Tapered roller bearing | |
| US10774876B1 (en) | Hydrodynamic thrust washers with pumping features for sparse lubrication applications | |
| US11703079B2 (en) | Bearing element with a smooth continuous profile | |
| KR102629312B1 (en) | Journal bearings with improved efficiency | |
| JP6077746B2 (en) | Thrust plain bearing |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20130625 |
|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20140127 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20140129 |
|
| A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20140529 |