JP2021165576A - Radial foil bearing - Google Patents

Radial foil bearing Download PDF

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JP2021165576A
JP2021165576A JP2020068962A JP2020068962A JP2021165576A JP 2021165576 A JP2021165576 A JP 2021165576A JP 2020068962 A JP2020068962 A JP 2020068962A JP 2020068962 A JP2020068962 A JP 2020068962A JP 2021165576 A JP2021165576 A JP 2021165576A
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plate
foil
shaped member
radial
circumferential direction
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直陸 大森
Naomichi Omori
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IHI Corp
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IHI Corp
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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
    • F16C43/00—Assembling bearings
    • F16C43/02—Assembling 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/026—Sliding-contact bearings for exclusively rotary movement for radial load only with helical grooves in the bearing surface to generate hydrodynamic pressure, e.g. herringbone grooves
    • 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
    • F16C2226/70—Positive connections with complementary interlocking parts
    • F16C2226/74—Positive connections with complementary interlocking parts with snap-fit, e.g. by clips
    • 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
    • F16C2326/00—Articles relating to transporting

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Support Of The Bearing (AREA)
  • Mounting Of Bearings Or Others (AREA)

Abstract

To provide a new top foil support structure having a damping capacity.SOLUTION: A radial foil bearing 3 includes: a bearing housing 12 having an insertion hole 12a; a top foil 9 disposed at the inner side of the insertion hole 12a; and a foil structure 10 disposed between the top foil 9 and the bearing housing 12. The foil structure 10 has areas (plate spring parts 10b) in each of which a gap between the foil structure 10 and the bearing housing 12 increases and a gap between the foil structure 10 and the top foil 9 decreases toward a center part as seen in a circumferential direction of the insertion hole 12a.SELECTED DRAWING: Figure 2

Description

本開示は、ラジアルフォイル軸受に関するものである。 The present disclosure relates to radial foil bearings.

従来、高速回転体用の軸受として、回転軸に外挿されて用いられるラジアル軸受が知られている。このようなラジアル軸受としては、軸受面を形成する薄板状のトップフォイルと、このトップフォイルを弾性的に支持するバックフォイルと、前記トップフォイル及び前記バックフォイルを収容する円筒状の軸受ハウジングと、を備えたラジアルフォイル軸受がよく知られている。ラジアルフォイル軸受のバックフォイルとしては、薄板を波板状に成形したバンプフォイルが主として用いられている（特許文献１参照）。 Conventionally, as a bearing for a high-speed rotating body, a radial bearing used by extrapolating to a rotating shaft is known. Such radial bearings include a thin plate-shaped top foil forming a bearing surface, a back foil that elastically supports the top foil, a cylindrical bearing housing that accommodates the top foil and the back foil, and the like. Radial foil bearings with are well known. As the back foil of the radial foil bearing, a bump foil obtained by molding a thin plate into a corrugated plate shape is mainly used (see Patent Document 1).

このようなラジアルフォイル軸受では、フォイルの摩擦（フォイル間の摩擦や、フォイルと軸受ハウジング間の摩擦）などによってエネルギー散逸を引き起こすことで、流体潤滑膜の膜圧変動を減衰させ、回転軸の軸振動（自励振動）を抑制し、該軸振動を収まり易くすることができる。 In such a radial foil bearing, the friction between the foils (friction between the foils and the friction between the foil and the bearing housing) causes energy dissipation to attenuate the fluctuation of the film pressure of the fluid lubricating film, and the axis of the rotating shaft. Vibration (self-excited vibration) can be suppressed and the shaft vibration can be easily contained.

特許第５６６４７８９号公報Japanese Patent No. 5664789

しかしながら、バンプフォイルの高さに製作誤差があると、設計通りの性能が得られない可能性がある。 However, if there is a manufacturing error in the height of the bump foil, the performance as designed may not be obtained.

本開示は、減衰能力を有する新たなトップフォイルの支持構造を提供する。 The present disclosure provides a new top foil support structure with damping capability.

上記の課題を解決するために、本開示のラジアルフォイル軸受は、挿通孔を有する軸受ハウジングと、前記挿通孔の内側に配置されたトップフォイルと、前記トップフォイルと前記軸受ハウジングとの間に介在するフォイル構造体と、を備え、前記フォイル構造体は、前記挿通孔の周方向の中央部に向かって、前記軸受ハウジングとの間隔が増大すると共に前記トップフォイルとの間隔が減少する領域を有する。 In order to solve the above problems, the radial foil bearing of the present disclosure is interposed between a bearing housing having an insertion hole, a top foil arranged inside the insertion hole, and the top foil and the bearing housing. The foil structure comprises a region in which the distance from the bearing housing increases and the distance from the top foil decreases toward the central portion in the circumferential direction of the insertion hole. ..

また、本開示においては、前記フォイル構造体は、前記挿通孔の周方向の中央部において、前記挿通孔が延びる軸方向における前記軸受ハウジングの端面に形成された嵌合溝に嵌合する嵌合部を有してもよい。 Further, in the present disclosure, the foil structure is fitted into a fitting groove formed in an end face of the bearing housing in the axial direction in which the insertion hole extends at the central portion in the circumferential direction of the insertion hole. It may have a part.

また、本開示においては、前記フォイル構造体は、前記挿通孔の径方向において重なった複数の板状部材によって形成されていてもよい。 Further, in the present disclosure, the foil structure may be formed of a plurality of plate-shaped members overlapping in the radial direction of the insertion hole.

また、本開示においては、前記複数の板状部材の少なくとも一つは、前記挿通孔の周方向における長さが異なっていてもよい。 Further, in the present disclosure, at least one of the plurality of plate-shaped members may have different lengths in the circumferential direction of the insertion hole.

また、本開示においては、前記複数の板状部材の少なくとも一つは、スリットによって形成された爪部を備えてもよい。 Further, in the present disclosure, at least one of the plurality of plate-shaped members may include a claw portion formed by a slit.

また、本開示においては、前記複数の板状部材のうち、前記挿通孔の径方向で重なる板状部材は、前記スリットのパターンが互いに異なってもよい。 Further, in the present disclosure, among the plurality of plate-shaped members, the plate-shaped members overlapping in the radial direction of the insertion holes may have different slit patterns.

本開示によれば、減衰能力を有する新たなトップフォイルの支持構造を提供できる。 According to the present disclosure, it is possible to provide a new top foil support structure having damping capability.

本開示のラジアルフォイル軸受が適用されるターボ機械の一例を示す側面図である。It is a side view which shows an example of the turbo machine to which the radial foil bearing of this disclosure is applied. 本開示の第１実施形態に係るラジアルフォイル軸受を示す正面図である。It is a front view which shows the radial foil bearing which concerns on 1st Embodiment of this disclosure. 本開示の第１実施形態に係るトップフォイルを展開した平面図である。It is a top view which developed the top foil which concerns on 1st Embodiment of this disclosure. 本開示の第１実施形態に係るラジアルフォイル軸受の要部の拡大斜視図である。It is an enlarged perspective view of the main part of the radial foil bearing which concerns on 1st Embodiment of this disclosure. 本開示の第２実施形態に係るラジアルフォイル軸受を示す正面図である。It is a front view which shows the radial foil bearing which concerns on 2nd Embodiment of this disclosure. 本開示の第２実施形態に係るラジアルフォイル軸受の要部の拡大斜視図である。It is an enlarged perspective view of the main part of the radial foil bearing which concerns on 2nd Embodiment of this disclosure. 本開示の第２実施形態の一変形例に係るラジアルフォイル軸受を示す正面図である。It is a front view which shows the radial foil bearing which concerns on one modification of the 2nd Embodiment of this disclosure. 本開示の第２実施形態の一変形例に係るラジアルフォイル軸受の要部の拡大斜視図である。It is an enlarged perspective view of the main part of the radial foil bearing which concerns on one modification of the 2nd Embodiment of this disclosure. 本開示の第２実施形態の一変形例に係るラジアルフォイル軸受を示す正面図である。It is a front view which shows the radial foil bearing which concerns on one modification of the 2nd Embodiment of this disclosure. 本開示の第２実施形態の一変形例に係るラジアルフォイル軸受の要部の拡大斜視図である。It is an enlarged perspective view of the main part of the radial foil bearing which concerns on one modification of the 2nd Embodiment of this disclosure. 本開示の第２実施形態の一変形例に係るフォイル構造体を平坦化して径方向から視た平面図である。It is a top view which flattened the foil structure which concerns on one modification of 2nd Embodiment of this disclosure and was seen from the radial direction. 本開示の第３実施形態に係るラジアルフォイル軸受を示す正面図である。It is a front view which shows the radial foil bearing which concerns on 3rd Embodiment of this disclosure. 本開示の第３実施形態に係るラジアルフォイル軸受の要部の拡大斜視図である。It is an enlarged perspective view of the main part of the radial foil bearing which concerns on 3rd Embodiment of this disclosure. 本開示の第３実施形態の一変形例に係るラジアルフォイル軸受の要部の拡大斜視図である。It is an enlarged perspective view of the main part of the radial foil bearing which concerns on one modification of the 3rd Embodiment of this disclosure. 本開示の第４実施形態に係るラジアルフォイル軸受を示す正面図である。It is a front view which shows the radial foil bearing which concerns on 4th Embodiment of this disclosure. 本開示の第４実施形態に係るラジアルフォイル軸受の要部の拡大斜視図である。It is an enlarged perspective view of the main part of the radial foil bearing which concerns on 4th Embodiment of this disclosure. 本開示の第４実施形態に係る板状部材を形成するフォイル片（パターンＡのスリットが形成されている）を平坦化して径方向から視た平面図である。It is a top view which flattened the foil piece (where the slit of the pattern A is formed) which forms the plate-like member which concerns on 4th Embodiment of this disclosure, and viewed from the radial direction. 本開示の第４実施形態に係る板状部材を形成するフォイル片（パターンＢのスリットが形成されている）を平坦化して径方向から視た平面図である。It is a top view which flattened the foil piece (where the slit of the pattern B is formed) which forms the plate-like member which concerns on 4th Embodiment of this disclosure, and viewed from the radial direction. 本開示の第４実施形態に係る板状部材を形成するフォイル片（パターンＣのスリットが形成されている）を平坦化して径方向から視た平面図である。It is a top view which flattened the foil piece (where the slit of the pattern C is formed) which forms the plate-like member which concerns on 4th Embodiment of this disclosure, and viewed from the radial direction. 本開示の第４実施形態に係る板状部材を形成するフォイル片（パターンＤのスリットが形成されている）を平坦化して径方向から視た平面図である。It is a top view which flattened the foil piece (where the slit of the pattern D is formed) which forms the plate-like member which concerns on 4th Embodiment of this disclosure, and viewed from the radial direction. 本開示の第４実施形態に係る板状部材を形成するフォイル片（パターンＥのスリットが形成されている）を平坦化して径方向から視た平面図である。It is a top view which flattened the foil piece (where the slit of the pattern E is formed) which forms the plate-like member which concerns on 4th Embodiment of this disclosure, and viewed from the radial direction. 本開示の第４実施形態に係る板状部材を形成するフォイル片（パターンＦのスリットが形成されている）を平坦化して径方向から視た平面図である。It is a top view which flattened the foil piece (where the slit of the pattern F is formed) which forms the plate-like member which concerns on 4th Embodiment of this disclosure, and viewed from the radial direction. 本開示の第４実施形態に係るフォイル構造体の２層目と３層目のスリットのパターンの組み合わせ例を示す図である。It is a figure which shows the combination example of the slit pattern of the 2nd layer and the 3rd layer of the foil structure which concerns on 4th Embodiment of this disclosure. 本開示の第４実施形態の一変形例に係るラジアルフォイル軸受を示す正面図である。It is a front view which shows the radial foil bearing which concerns on one modification of 4th Embodiment of this disclosure. 本開示の第４実施形態の一変形例に係るラジアルフォイル軸受の要部の拡大斜視図である。It is an enlarged perspective view of the main part of the radial foil bearing which concerns on one modification of 4th Embodiment of this disclosure.

以下、図面を参照して本開示のラジアルフォイル軸受を詳しく説明する。 Hereinafter, the radial foil bearing of the present disclosure will be described in detail with reference to the drawings.

図１は、本開示のラジアルフォイル軸受が適用されるターボ機械の一例を示す側面図である。
図１中、符号１は回転軸（シャフト）、符号２は回転軸の軸方向の一方側の先端に設けられたインペラ、符号３は本開示に係るラジアルフォイル軸受である。なお、図１では省略してラジアルフォイル軸受を一つしか記載していないが、通常は回転軸１の軸方向にラジアルフォイル軸受が二つ設けられている。したがって、本開示においてもラジアルフォイル軸受３が二つ設けられている。 FIG. 1 is a side view showing an example of a turbomachine to which the radial foil bearing of the present disclosure is applied.
In FIG. 1, reference numeral 1 is a rotating shaft (shaft), reference numeral 2 is an impeller provided at one end of the rotating shaft in the axial direction, and reference numeral 3 is a radial foil bearing according to the present disclosure. Although only one radial foil bearing is omitted in FIG. 1, two radial foil bearings are usually provided in the axial direction of the rotating shaft 1. Therefore, also in the present disclosure, two radial foil bearings 3 are provided.

回転軸１には、ラジアルフォイル軸受３が外挿（挿通）されている。回転軸１のインペラ２とラジアルフォイル軸受３との間には、スラストカラー４が設けられている。このスラストカラー４の軸方向両側には、スラスト軸受５が配置（挿通）されている。インペラ２は、静止側となるハウジング６内に配置されており、ハウジング６との間にチップクリアランス７を有している。 A radial foil bearing 3 is extrapolated (inserted) into the rotating shaft 1. A thrust collar 4 is provided between the impeller 2 of the rotating shaft 1 and the radial foil bearing 3. Thrust bearings 5 are arranged (inserted) on both sides of the thrust collar 4 in the axial direction. The impeller 2 is arranged in the housing 6 on the stationary side, and has a tip clearance 7 with the housing 6.

（第１実施形態）
図２は、本開示の第１実施形態に係るラジアルフォイル軸受３を示す正面図である。
ラジアルフォイル軸受３は、回転軸１に外挿されて、該回転軸１を支持する軸受である。ラジアルフォイル軸受３は、トップフォイル９と、フォイル構造体１０と、軸受ハウジング１２と、を備える。軸受ハウジング１２は、回転軸１が挿通される挿通孔１２ａを有する。 (First Embodiment)
FIG. 2 is a front view showing the radial foil bearing 3 according to the first embodiment of the present disclosure.
The radial foil bearing 3 is a bearing that is extrapolated to the rotating shaft 1 and supports the rotating shaft 1. The radial foil bearing 3 includes a top foil 9, a foil structure 10, and a bearing housing 12. The bearing housing 12 has an insertion hole 12a through which the rotating shaft 1 is inserted.

なお、以下の説明においては、挿通孔１２ａを基準に各部材の位置関係を説明することがある。具体的に、「軸方向」とは、挿通孔１２ａが延びる方向（回転軸１が挿通される方向）を言う。また、「径方向」とは、挿通孔１２ａの径方向を言う。また、「周方向」とは、挿通孔１２ａの内周面に沿った周方向を言う。 In the following description, the positional relationship of each member may be described with reference to the insertion hole 12a. Specifically, the "axial direction" refers to the direction in which the insertion hole 12a extends (the direction in which the rotation shaft 1 is inserted). Further, the "diameter direction" means the radial direction of the insertion hole 12a. The "circumferential direction" refers to the circumferential direction along the inner peripheral surface of the insertion hole 12a.

軸受ハウジング１２は、径方向におけるラジアルフォイル軸受３の最外部を構成する円筒状の部材である。軸受ハウジング１２には、挿通孔１２ａが形成されている。挿通孔１２ａには、フォイル構造体１０、トップフォイル９が収容されている。具体的に、フォイル構造体１０は挿通孔１２ａの内周面に支持され、トップフォイル９はフォイル構造体１０に支持されている。つまり、フォイル構造体１０は、トップフォイル９と軸受ハウジング１２との間に介在している。なお、本開示の軸受ハウジング１２は、挿通孔１２ａを備える円筒状の部材である。しかし、挿通孔１２ａを有すれば、軸受ハウジング１２は、円筒状以外の部材（例えば角柱状の部材）であってもよい。 The bearing housing 12 is a cylindrical member that constitutes the outermost part of the radial foil bearing 3 in the radial direction. An insertion hole 12a is formed in the bearing housing 12. The foil structure 10 and the top foil 9 are housed in the insertion hole 12a. Specifically, the foil structure 10 is supported by the inner peripheral surface of the insertion hole 12a, and the top foil 9 is supported by the foil structure 10. That is, the foil structure 10 is interposed between the top foil 9 and the bearing housing 12. The bearing housing 12 of the present disclosure is a cylindrical member provided with an insertion hole 12a. However, if the bearing housing 12 has an insertion hole 12a, the bearing housing 12 may be a member other than a cylindrical member (for example, a prismatic member).

図３は、本開示の第１実施形態に係るトップフォイル９を展開した平面図である。
トップフォイル９は、図３に示すように、周方向を長辺とし、軸方向を短辺とする矩形状の金属箔である。このトップフォイル９は、図２に示すように、円筒状に巻かれて、回転軸１の周面に対向して配置されている。 FIG. 3 is a plan view of the top foil 9 according to the first embodiment of the present disclosure.
As shown in FIG. 3, the top foil 9 is a rectangular metal foil having a long side in the circumferential direction and a short side in the axial direction. As shown in FIG. 2, the top foil 9 is wound in a cylindrical shape and arranged so as to face the peripheral surface of the rotating shaft 1.

トップフォイル９の長辺方向における一方の短辺（端部，第１端）には、図３に示すように、長辺方向の一方側に突出する一つの凸部２１ａと、凸部２１ａの短辺方向両側に形成された二つの凹部２２ａとを有してなる第１の凹凸部２３ａが形成されている。すなわち、トップフォイル９の長辺方向における一方の短辺は、長辺方向の一方側に突出する一つの凸部２１ａと、凸部２１ａの短辺方向両側に延接する段差とを備える。 On one short side (end, first end) of the top foil 9 in the long side direction, as shown in FIG. 3, one convex portion 21a protruding to one side in the long side direction and the convex portion 21a A first uneven portion 23a having two recesses 22a formed on both sides in the short side direction is formed. That is, one short side of the top foil 9 in the long side direction includes one convex portion 21a protruding to one side in the long side direction and a step extending to both sides of the convex portion 21a in the short side direction.

また、トップフォイル９の当該一方の短辺と反対の他方の短辺（長辺方向における他方側に位置する短辺（端部，第２端））には、短辺方向において離隔する二つの凸部２１ｂと、当該二つの凸部２１ｂの間に位置する一つの凹部２２ｂと、を有してなる第２の凹凸部２３ｂが形成されている。あるいは、トップフォイル９の長辺方向の他方側に位置する短辺には、長辺方向の一方側に窪む凹部２２ｂと、凹部２２ｂの短辺方向両側に位置する段差とを備える。 Further, the other short side of the top foil 9 opposite to the one short side (the short side located on the other side in the long side direction (end, second end)) has two separated sides in the short side direction. A second concave-convex portion 23b having a convex portion 21b and one concave portion 22b located between the two convex portions 21b is formed. Alternatively, the short side of the top foil 9 located on the other side in the long side direction is provided with a recess 22b recessed on one side in the long side direction and a step located on both sides of the recess 22b in the short side direction.

第２の凹凸部２３ｂの凹部２２ｂは、第１の凹凸部２３ａの凸部２１ａに対応して形成されている。また、第１の凹凸部２３ａの凹部２２ａは、第２の凹凸部２３ｂの凸部２１ｂに対応して形成されている。つまり、凹部２２ｂの短辺方向の間隔の最少が、凸部２１ａの短辺方向の幅の最大より大きい。本開示の凹部２２ｂの長辺方向の間隔と、凸部２１ａの長辺方向の間隔は、長辺方向において一定である。 The concave portion 22b of the second uneven portion 23b is formed corresponding to the convex portion 21a of the first uneven portion 23a. Further, the concave portion 22a of the first uneven portion 23a is formed corresponding to the convex portion 21b of the second uneven portion 23b. That is, the minimum distance in the short side direction of the concave portion 22b is larger than the maximum width in the short side direction of the convex portion 21a. The distance between the concave portion 22b of the present disclosure in the long side direction and the distance between the convex portion 21a in the long side direction are constant in the long side direction.

第２の凹凸部２３ｂの凹部２２ｂは、第１の凹凸部２３ａと第２の凹凸部２３ｂとが重なるようにトップフォイル９を円筒状に巻いた際、凹部２２ｂ内を凸部２１ａが通り抜けるように形成されている。同様に、第１の凹凸部２３ａの凹部２２ａは、トップフォイル９を円筒状に巻いた際、該凹部２２ａ内を凸部２１ｂがそれぞれ通り抜けるように形成されている。つまり、トップフォイル９は、第１端（一方の短辺）から周方向一方側に延伸する部位（凸部２１ａ）と、第２端（他方の短辺）から周方向他方側に延伸する部位（凸部２１ｂ）が、軸方向に交差している。 The concave portion 22b of the second uneven portion 23b is such that when the top foil 9 is wound in a cylindrical shape so that the first uneven portion 23a and the second uneven portion 23b overlap, the concave portion 21a passes through the concave portion 22b. Is formed in. Similarly, the concave portion 22a of the first uneven portion 23a is formed so that the convex portion 21b passes through the concave portion 22a when the top foil 9 is wound in a cylindrical shape. That is, the top foil 9 has a portion extending from the first end (one short side) to one side in the circumferential direction (convex portion 21a) and a portion extending from the second end (the other short side) to the other side in the circumferential direction. (Convex portions 21b) intersect in the axial direction.

凹部２２ｂ、２２ａを通り抜けた凸部２１ａ、２１ｂ（トップフォイル９の両端）は、図２に示すように、それぞれ軸受ハウジング１２側に引き出される。すなわち、挿通孔１２ａの内周側に配されたトップフォイル９を軸方向から見ると、凸部２１ａと凸部２１ｂが交差している。また、トップフォイル９の凸部２１ａは、軸方向において、２つの凸部２１ｂの間に位置する。軸受ハウジング１２には、挿通孔１２ａの内周面に、凸部２１ａ、２１ｂが挿入される通し溝１４が形成されている。通し溝１４は、軸受ハウジング１２の軸方向の一方の端面１２ｂから他方の端面１２ｂまで軸方向に沿って形成されている。 The convex portions 21a and 21b (both ends of the top foil 9) that have passed through the concave portions 22b and 22a are pulled out to the bearing housing 12 side, respectively, as shown in FIG. That is, when the top foil 9 arranged on the inner peripheral side of the insertion hole 12a is viewed from the axial direction, the convex portion 21a and the convex portion 21b intersect. Further, the convex portion 21a of the top foil 9 is located between the two convex portions 21b in the axial direction. The bearing housing 12 is formed with a through groove 14 into which the convex portions 21a and 21b are inserted on the inner peripheral surface of the insertion hole 12a. The through groove 14 is formed along the axial direction from one end surface 12b in the axial direction of the bearing housing 12 to the other end surface 12b.

フォイル構造体１０は、トップフォイル９と軸受ハウジング１２との間に配置されている。フォイル構造体１０は、本開示では、挿通孔１２ａの内周面に沿って配置された３つの板状部材１０Ａによって構成されている。３つの板状部材１０Ａは、展開形状が略矩形状であり、軸方向から見たとき、図２に示すように、全体として略円筒状になるよう湾曲している。本開示では、板状部材１０Ａの３つが全て同じ形状・寸法に形成されている。したがって、これら板状部材１０Ａは、挿通孔１２ａの内周面を周方向において略３分割して配置されている。 The foil structure 10 is arranged between the top foil 9 and the bearing housing 12. In the present disclosure, the foil structure 10 is composed of three plate-shaped members 10A arranged along the inner peripheral surface of the insertion hole 12a. The three plate-shaped members 10A have a substantially rectangular unfolded shape, and are curved so as to be substantially cylindrical as a whole as shown in FIG. 2 when viewed from the axial direction. In the present disclosure, all three of the plate-shaped members 10A are formed in the same shape and dimensions. Therefore, these plate-shaped members 10A are arranged by substantially dividing the inner peripheral surface of the insertion hole 12a into three in the circumferential direction.

板状部材１０Ａは、板状部材１０Ａの周方向の中央部に向かって、軸受ハウジング１２との径方向の間隔が増大すると共にトップフォイル９との間隔が減少する領域（板バネ部１０ｂ）と、板状部材１０Ａの周方向の中央部において、板バネ部１０ｂよりも径方向外側に窪む（突出する）嵌合部１０ｃと、を有する。板バネ部１０ｂは、板状部材１０Ａの周方向の両端部において、挿通孔１２ａの内周面に接すると共にトップフォイル９から離隔している。また、板バネ部１０ｂは、板状部材１０Ａの周方向の中央部において、挿通孔１２ａの内周面から離隔すると共に、トップフォイル９に接している。 The plate-shaped member 10A has a region (leaf spring portion 10b) in which the radial distance from the bearing housing 12 increases and the distance from the top foil 9 decreases toward the central portion in the circumferential direction of the plate-shaped member 10A. The plate-shaped member 10A has a fitting portion 10c that is recessed (protruding) radially outward from the leaf spring portion 10b at the central portion in the circumferential direction. The leaf spring portions 10b are in contact with the inner peripheral surface of the insertion hole 12a and separated from the top foil 9 at both ends of the plate-shaped member 10A in the circumferential direction. Further, the leaf spring portion 10b is separated from the inner peripheral surface of the insertion hole 12a at the central portion in the circumferential direction of the plate-shaped member 10A and is in contact with the top foil 9.

嵌合部１０ｃは、トップフォイル９から離隔している。嵌合部１０ｃは、板状部材１０Ａの周方向両端の間の周方向位置（本開示では周方向における板状部材１０Ａの中央位置）に形成されている。軸受ハウジング１２の軸方向両側の端面１２ｂには、図２に示すようにそれぞれ、挿通孔１２ａの内周縁から径方向外側に向かって延びる一対の嵌合溝１５が形成されている。本開示の嵌合溝１５は、軸受ハウジング１２の端面１２ｂを、その周方向にほぼ３分割する位置に、それぞれ形成されている。そして、これら嵌合溝１５には、上述した板状部材１０Ａの嵌合部１０ｃが嵌合している。なお、図中、嵌合溝１５と嵌合部１０ｃとの間には隙間が設けられているが、この隙間は、各部材を明瞭に区別するために設けられたもので、実装置においては、各部材はそれぞれ当接している（以下の図においても同様）。 The fitting portion 10c is separated from the top foil 9. The fitting portion 10c is formed at a circumferential position between both ends of the plate-shaped member 10A in the circumferential direction (in the present disclosure, a central position of the plate-shaped member 10A in the circumferential direction). As shown in FIG. 2, a pair of fitting grooves 15 extending radially outward from the inner peripheral edge of the insertion hole 12a are formed on the end faces 12b on both sides of the bearing housing 12 in the axial direction. The fitting grooves 15 of the present disclosure are formed at positions where the end surface 12b of the bearing housing 12 is substantially divided into three in the circumferential direction. Then, the fitting portion 10c of the plate-shaped member 10A described above is fitted in these fitting grooves 15. In the drawing, a gap is provided between the fitting groove 15 and the fitting portion 10c, but this gap is provided to clearly distinguish each member, and in an actual device, the gap is provided. , Each member is in contact with each other (the same applies to the following figure).

本開示では、３つの嵌合溝１５のうちの２つの嵌合溝１５の間に、通し溝１４が配置されている。また、嵌合溝１５の一つは、通し溝１４と径方向において対向している。嵌合溝１５を形成するには、エンドミルによる切削加工等が適宜選択できる。また、嵌合溝１５は、軸受ハウジング１２の内周縁から外周縁まで貫通して形成されていなくてもよい。 In the present disclosure, a through groove 14 is arranged between two fitting grooves 15 out of the three fitting grooves 15. Further, one of the fitting grooves 15 faces the through groove 14 in the radial direction. In order to form the fitting groove 15, cutting with an end mill or the like can be appropriately selected. Further, the fitting groove 15 may not be formed so as to penetrate from the inner peripheral edge to the outer peripheral edge of the bearing housing 12.

図４は、本開示の第１実施形態に係るラジアルフォイル軸受３の要部の拡大斜視図である。
図４に示すように、板状部材１０Ａには、それぞれの周方向両端の間の周方向位置（軸受ハウジング１２の周方向に沿う方向の中央部）の両側周縁部に、嵌合部１０ｃが形成されている。つまり、板状部材１０Ａは、軸方向において対向する位置に、２つの嵌合部１０ｃを有している。あるいは、板状部材１０Ａは、軸方向の両側の端縁に、それぞれ嵌合部１０ｃを有している。 FIG. 4 is an enlarged perspective view of a main part of the radial foil bearing 3 according to the first embodiment of the present disclosure.
As shown in FIG. 4, the plate-shaped member 10A has fitting portions 10c on both side peripheral portions of the circumferential position (central portion in the direction along the circumferential direction of the bearing housing 12) between both ends in the circumferential direction. It is formed. That is, the plate-shaped member 10A has two fitting portions 10c at positions facing each other in the axial direction. Alternatively, the plate-shaped member 10A has fitting portions 10c at both end edges in the axial direction.

また、板状部材１０Ａは、軸方向の両側の端縁に形成された２つの嵌合部１０ｃの間に、孔部１０ｄを有している。孔部１０ｄは、嵌合部１０ｃの周方向幅以上の周方向幅を有し、軸方向に延伸している。また、孔部１０ｄの軸方向幅は、嵌合部１０ｃの軸方向幅よりも大きい。つまり、板状部材１０Ａの周方向両端の間の周方向位置には、軸方向に延伸する孔部１０ｄ（スリット）を有する。あるいは、板状部材１０Ａの２つの板バネ部１０ｂが、孔部１０ｄ（スリット）により分断され、板状部材１０Ａの両側周縁部の２つの嵌合部１０ｃによって接続されているとも言える。 Further, the plate-shaped member 10A has a hole portion 10d between two fitting portions 10c formed on both end edges in the axial direction. The hole portion 10d has a circumferential width equal to or larger than the circumferential width of the fitting portion 10c and extends in the axial direction. Further, the axial width of the hole portion 10d is larger than the axial width of the fitting portion 10c. That is, the plate-shaped member 10A has a hole portion 10d (slit) extending in the axial direction at a position in the circumferential direction between both ends in the circumferential direction. Alternatively, it can be said that the two leaf spring portions 10b of the plate-shaped member 10A are separated by the hole portion 10d (slit) and connected by the two fitting portions 10c on both side peripheral portions of the plate-shaped member 10A.

嵌合部１０ｃは、軸受ハウジング１２の嵌合溝１５に対し径方向に挿入され、周方向における嵌合溝１５の両側面に対向して配置される。嵌合部１０ｃは、板バネ部１０ｂから挿通孔１２ａの径方向の外側に向かって曲げられ、且つ、もう一つの板バネ部１０ｂに向かって径方向の内側に曲げ返されている。具体的に、嵌合部１０ｃは、板バネ部１０ｂから径方向の外側に向かって延伸する延伸部と、もう一つの板バネ部１０ｂに向かって径方向の内側に延伸する返し部、周方向に延伸し、延伸部と返し部とを接続する接続部と、を有する略Ｕ字状に形成されている。これら延伸部、接続部、返し部は、板バネ部１０ｂからこの順序で周方向に連続的にたどることができる。なお、本開示の嵌合部１０ｃでは、周方向に延伸する接続部を設けたが、接続部を介さずに、例えば、延伸部と返し部とを略Ｖ字状に接続して形成することも可能である。 The fitting portion 10c is inserted in the fitting groove 15 of the bearing housing 12 in the radial direction and is arranged so as to face both side surfaces of the fitting groove 15 in the circumferential direction. The fitting portion 10c is bent outward from the leaf spring portion 10b in the radial direction of the insertion hole 12a, and is bent back inward in the radial direction toward the other leaf spring portion 10b. Specifically, the fitting portion 10c includes a stretched portion extending radially outward from the leaf spring portion 10b, a return portion extending radially inward toward the other leaf spring portion 10b, and a circumferential direction. It is formed in a substantially U shape having a connecting portion that stretches to and connects the stretched portion and the return portion. These extending portions, connecting portions, and return portions can be continuously traced in the circumferential direction from the leaf spring portion 10b in this order. In the fitting portion 10c of the present disclosure, a connecting portion extending in the circumferential direction is provided, but for example, the extending portion and the return portion are connected in a substantially V shape without passing through the connecting portion. Is also possible.

図２に戻り、板状部材１０Ａは、嵌合部１０ｃを除く部分（板バネ部１０ｂ）がもとは平板形状であり、軸受ハウジング１２の挿通孔１２ａに沿わせるために湾曲している。つまり、板状部材１０Ａは、湾曲形状からもとの平板形状に戻ろうとするバネ反力によって、トップフォイル９を径方向内側に押し上げ、回転軸１の締め付け状態を作り出している。なお、バネの効き始めを調整するため、板バネ部１０ｂは、完全なる平板形状では無く、初めから若干のＲ（湾曲形状）を有していても良い。 Returning to FIG. 2, the plate-shaped member 10A originally has a flat plate shape except for the fitting portion 10c (leaf spring portion 10b), and is curved so as to follow the insertion hole 12a of the bearing housing 12. That is, the plate-shaped member 10A pushes up the top foil 9 inward in the radial direction by the spring reaction force that tries to return from the curved shape to the original flat plate shape, and creates a tightened state of the rotating shaft 1. In order to adjust the starting effect of the spring, the leaf spring portion 10b may have a slight R (curved shape) from the beginning instead of a perfect flat plate shape.

つまり、板状部材１０Ａは、軸受ハウジング１２の挿通孔１２ａよりも大きな曲率半径を有している。これにより、板状部材１０Ａは、軸受ハウジング１２の挿通孔１２ａには密着せず、板状部材１０Ａの周方向中央部が挿通孔１２ａの内周面から浮き上がった状態となる。この板状部材１０Ａの浮きが、ラジアルフォイル軸受３が荷重を受けた際の吸収代となる。また、板状部材１０Ａは、周方向の両端部のみが挿通孔１２ａの内周面に接している。つまり、板状部材１０Ａは、挿通孔１２ａの周方向の中央部に向かって、軸受ハウジング１２との径方向の間隔が増大すると共にトップフォイル９との径方向の間隔が減少する領域（板バネ部１０ｂ）を有する。 That is, the plate-shaped member 10A has a radius of curvature larger than that of the insertion hole 12a of the bearing housing 12. As a result, the plate-shaped member 10A does not come into close contact with the insertion hole 12a of the bearing housing 12, and the central portion of the plate-shaped member 10A in the circumferential direction is raised from the inner peripheral surface of the insertion hole 12a. The floating of the plate-shaped member 10A serves as an absorption allowance when the radial foil bearing 3 receives a load. Further, in the plate-shaped member 10A, only both ends in the circumferential direction are in contact with the inner peripheral surface of the insertion hole 12a. That is, the plate-shaped member 10A has a region (leaf spring) in which the radial distance from the bearing housing 12 increases and the radial distance from the top foil 9 decreases toward the central portion in the circumferential direction of the insertion hole 12a. It has a part 10b).

次に、このような構成からなるラジアルフォイル軸受３の作用について説明する。
回転軸１が停止した状態では、トップフォイル９はフォイル構造体１０（３つの板状部材１０Ａ）によって回転軸１側に付勢されることで回転軸１に密着している。 Next, the operation of the radial foil bearing 3 having such a configuration will be described.
When the rotating shaft 1 is stopped, the top foil 9 is brought into close contact with the rotating shaft 1 by being urged toward the rotating shaft 1 by the foil structure 10 (three plate-shaped members 10A).

そして、回転軸１を図２中の矢印Ｐ方向に始動させると、最初は低速で回転を始め、その後徐々に加速して高速で回転する。すると、図２中矢印Ｑで示すように、トップフォイル９の一端側から周囲流体が引き入れられ、トップフォイル９と回転軸１との間に流入する。これにより、トップフォイル９と回転軸１との間に流体潤滑膜が形成される。 Then, when the rotation shaft 1 is started in the direction of the arrow P in FIG. 2, the rotation starts at a low speed at first, and then gradually accelerates and rotates at a high speed. Then, as shown by the arrow Q in FIG. 2, the ambient fluid is drawn in from one end side of the top foil 9 and flows into the space between the top foil 9 and the rotating shaft 1. As a result, a fluid lubricating film is formed between the top foil 9 and the rotating shaft 1.

この流体潤滑膜の膜圧は、トップフォイル９に作用し、該トップフォイル９に接する板状部材１０Ａの周方向中央部を押圧する。すると、板状部材１０Ａの周方向中央部における挿通孔１２ａの内周面に対する浮きが、当該押圧の吸収代となり、板状部材１０Ａが径方向外側に変形する。そうすると、板状部材１０Ａの周方向両端部が、軸受ハウジング１２上をその周方向に動こうとする。すなわち、板状部材１０Ａは、トップフォイル９を弾性的に支持するため、トップフォイル９から荷重を受けた際には径方向及び周方向に変形することで、トップフォイル９の撓みを許容し、これを支持する。 The film pressure of the fluid lubricating film acts on the top foil 9 and presses the central portion in the circumferential direction of the plate-shaped member 10A in contact with the top foil 9. Then, the floating of the insertion hole 12a at the central portion in the circumferential direction of the plate-shaped member 10A with respect to the inner peripheral surface serves as an absorption allowance for the pressing, and the plate-shaped member 10A is deformed radially outward. Then, both ends of the plate-shaped member 10A in the circumferential direction tend to move on the bearing housing 12 in the circumferential direction. That is, since the plate-shaped member 10A elastically supports the top foil 9, when it receives a load from the top foil 9, it deforms in the radial direction and the circumferential direction to allow the top foil 9 to bend. I support this.

ここで、図２に示すように、軸受ハウジング１２の嵌合溝１５には、板状部材１０Ａの嵌合部１０ｃが嵌合している。これにより、周方向における板状部材１０Ａの回転が抑制される。したがって、板状部材１０Ａの周方向両端部は、嵌合部１０ｃが嵌合している嵌合溝１５を挟み周方向両側に変形する（動く）。 Here, as shown in FIG. 2, the fitting portion 10c of the plate-shaped member 10A is fitted in the fitting groove 15 of the bearing housing 12. As a result, the rotation of the plate-shaped member 10A in the circumferential direction is suppressed. Therefore, both ends in the circumferential direction of the plate-shaped member 10A are deformed (moved) on both sides in the circumferential direction with the fitting groove 15 into which the fitting portion 10c is fitted.

また、嵌合部１０ｃは、軸方向において対向する位置に２つ設けられ、軸受ハウジング１２と軸方向において対向している。つまり、一対の嵌合部１０ｃは、軸受ハウジング１２に対する板状部材１０Ａの軸方向の移動を抑制している。よって、軸受ハウジング１２からの板状部材１０Ａの脱落が抑制される。 Further, two fitting portions 10c are provided at positions facing each other in the axial direction, and face the bearing housing 12 in the axial direction. That is, the pair of fitting portions 10c suppresses the axial movement of the plate-shaped member 10A with respect to the bearing housing 12. Therefore, the plate-shaped member 10A is suppressed from falling off from the bearing housing 12.

板状部材１０Ａは、トップフォイル９から荷重を受ける際、トップフォイル９と共に撓むが、このとき板状部材１０Ａの周方向両端部と軸受ハウジング１２の挿通孔１２ａとの間で「滑り」が生じる。すなわち、回転軸１の軸振動により流体潤滑膜に圧力変動が生じると、トップフォイル９に圧力変動が伝達し、当該「滑り」が生じる。この「滑り」が摩擦によるエネルギー散逸を引き起こし、膜圧変動を減衰させるので、回転軸１の軸振動が抑制される。 When the plate-shaped member 10A receives a load from the top foil 9, it bends together with the top foil 9. At this time, "slip" occurs between both ends of the plate-shaped member 10A in the circumferential direction and the insertion holes 12a of the bearing housing 12. Occurs. That is, when the pressure fluctuation occurs in the fluid lubricating film due to the shaft vibration of the rotating shaft 1, the pressure fluctuation is transmitted to the top foil 9, and the "slip" occurs. This "slip" causes energy dissipation due to friction and attenuates the fluctuation of the film pressure, so that the axial vibration of the rotating shaft 1 is suppressed.

回転軸１の軸振動による変動荷重（負荷と除荷の繰り返し）が板状部材１０Ａに作用し、例えば荷重が除荷側になったとき、板状部材１０Ａの周方向中央部は、軸受ハウジング１２の挿通孔１２ａの内周面から浮き上がる。ここで、板状部材１０Ａの嵌合部１０ｃが、軸受ハウジング１２の嵌合溝１５に当接している場合、嵌合部１０ｃと嵌合溝１５との間で「滑り」が生じ、これが摩擦によるエネルギー散逸を引き起こし、減衰として寄与する。なお、荷重が負荷側になったときも同様である。板状部材１０Ａを制振合金製とすれば、さらに減衰効果が高まる。 When a fluctuating load (repeated load and unloading) due to shaft vibration of the rotating shaft 1 acts on the plate-shaped member 10A, for example, when the load is on the unloading side, the central portion of the plate-shaped member 10A in the circumferential direction is the bearing housing. It rises from the inner peripheral surface of the insertion hole 12a of 12. Here, when the fitting portion 10c of the plate-shaped member 10A is in contact with the fitting groove 15 of the bearing housing 12, "slip" occurs between the fitting portion 10c and the fitting groove 15, which causes friction. Causes energy dissipation due to, and contributes as attenuation. The same applies when the load is on the load side. If the plate-shaped member 10A is made of a vibration damping alloy, the damping effect is further enhanced.

また、上述したトップフォイル９の支持構造（フォイル構造体１０）において、従来のバンプフォイルの高さに対応するのは板バネ部１０ｂの厚さであり、板厚の誤差は極めて少なく（プレス加工の１／１００程度）、製作時の個体差によって回転軸１の締め付け状態が変化し難くなる。また、強い外乱が作用した場合には、板バネ部１０ｂが軸受ハウジング１２に完全に密着状態（挿通孔１２ａの内周面との隙間が無くなった状態）となることにより、軸変位が増大するのを抑制することができる。なお、このような外乱が作用した場合でも板状部材１０Ａの周方向中央部の嵌合部１０ｃが軸受ハウジング１２の嵌合溝１５に差し込まれているので、板状部材１０Ａが定位置からずれることは無い。 Further, in the above-mentioned support structure of the top foil 9 (foil structure 10), the thickness of the leaf spring portion 10b corresponds to the height of the conventional bump foil, and the error in the plate thickness is extremely small (press working). The tightening state of the rotating shaft 1 is less likely to change due to individual differences during production. Further, when a strong disturbance acts, the leaf spring portion 10b is completely in close contact with the bearing housing 12 (a state in which there is no gap between the insertion hole 12a and the inner peripheral surface), so that the axial displacement increases. Can be suppressed. Even when such a disturbance acts, the fitting portion 10c at the center of the plate-shaped member 10A in the circumferential direction is inserted into the fitting groove 15 of the bearing housing 12, so that the plate-shaped member 10A is displaced from the fixed position. There is no such thing.

このように、上述のラジアルフォイル軸受３によれば、挿通孔１２ａを有する軸受ハウジング１２と、挿通孔１２ａの内側に配置されたトップフォイル９と、トップフォイル９と軸受ハウジング１２との間に介在するフォイル構造体１０と、を備え、フォイル構造体１０は、挿通孔１２ａの周方向の中央部に向かって、軸受ハウジング１２との間隔が増大すると共にトップフォイル９との間隔が減少する領域（板バネ部１０ｂ）を有する、という構成を採用することによって、減衰能力を有する新たなトップフォイル９の支持構造を提供できる。 As described above, according to the above-mentioned radial foil bearing 3, the bearing housing 12 having the insertion hole 12a, the top foil 9 arranged inside the insertion hole 12a, and the top foil 9 and the bearing housing 12 are interposed. The foil structure 10 is provided with a foil structure (10), and the foil structure (10) has an area (a region) in which the distance from the bearing housing (12) increases and the distance from the top foil (9) decreases toward the central portion of the insertion hole (12a) in the circumferential direction. By adopting the configuration of having the leaf spring portion 10b), it is possible to provide a support structure of a new top foil 9 having a damping ability.

（第２実施形態）
次に、本開示の第２実施形態について説明する。以下の説明において、上述の実施形態と同一又は同等の構成については同一の符号を付し、その説明を簡略若しくは省略する。 (Second Embodiment)
Next, a second embodiment of the present disclosure will be described. In the following description, the same or equivalent configurations as those in the above-described embodiment are designated by the same reference numerals, and the description thereof will be simplified or omitted.

図５は、本開示の第２実施形態に係るラジアルフォイル軸受３を示す正面図である。図６は、本開示の第２実施形態に係るラジアルフォイル軸受３の要部の拡大斜視図である。
これらの図に示すように、第２実施形態のラジアルフォイル軸受３は、フォイル構造体１０が、挿通孔１２ａの径方向において重なった複数の板状部材１０Ａ〜１０Ｃによって形成されている点で、上記実施形態と異なる。 FIG. 5 is a front view showing the radial foil bearing 3 according to the second embodiment of the present disclosure. FIG. 6 is an enlarged perspective view of a main part of the radial foil bearing 3 according to the second embodiment of the present disclosure.
As shown in these figures, in the radial foil bearing 3 of the second embodiment, the foil structure 10 is formed by a plurality of plate-shaped members 10A to 10C overlapping in the radial direction of the insertion hole 12a. It is different from the above embodiment.

図５及び図６に示すように、板状部材１０Ａは、上記実施形態と同一の構成を有する。この板状部材１０Ａの径方向外側には、２枚の板状部材１０Ｂ，１０Ｃが重なって配置されている。板状部材１０Ｂ，１０Ｃは、展開形状が略矩形状であり、軸方向から見たとき、図５に示すように、全体として略円筒状になるよう湾曲している。本開示では、板状部材１０Ａ〜１０Ｃの周方向における長さが全て同じ寸法に形成されている。したがって、これら板状部材１０Ａ〜１０Ｃは、挿通孔１２ａの内周面を周方向において略３分割して配置されている。 As shown in FIGS. 5 and 6, the plate-shaped member 10A has the same configuration as that of the above embodiment. Two plate-shaped members 10B and 10C are arranged so as to overlap each other on the radial outer side of the plate-shaped member 10A. The plate-shaped members 10B and 10C have a substantially rectangular unfolded shape, and are curved so as to be substantially cylindrical as a whole as shown in FIG. 5 when viewed from the axial direction. In the present disclosure, the plate-shaped members 10A to 10C are all formed to have the same length in the circumferential direction. Therefore, these plate-shaped members 10A to 10C are arranged by substantially dividing the inner peripheral surface of the insertion hole 12a into three in the circumferential direction.

板状部材１０Ｂ，１０Ｃは、それぞれの周方向の中央部に向かって、軸受ハウジング１２との径方向の間隔が増大すると共にトップフォイル９との間隔が減少する領域を有する。つまり、板状部材１０Ｂ，１０Ｃも板状部材１０Ａと同様に、軸受ハウジング１２の挿通孔１２ａよりも大きな曲率半径を有している。これにより、板状部材１０Ｂ，１０Ｃにおいても周方向中央部が挿通孔１２ａの内周面から浮き上がった状態で設置される。なお、板状部材１０Ａ〜１０Ｃのうち、最外周に配置された板状部材１０Ｃは、その周方向両端部が挿通孔１２ａの内周面に接している。 The plate-shaped members 10B and 10C have a region in which the radial distance from the bearing housing 12 increases and the distance from the top foil 9 decreases toward the central portion in the circumferential direction. That is, the plate-shaped members 10B and 10C also have a radius of curvature larger than the insertion hole 12a of the bearing housing 12 like the plate-shaped member 10A. As a result, even in the plate-shaped members 10B and 10C, the central portion in the circumferential direction is installed in a state of being raised from the inner peripheral surface of the insertion hole 12a. Of the plate-shaped members 10A to 10C, the plate-shaped members 10C arranged on the outermost circumference are in contact with the inner peripheral surface of the insertion hole 12a at both ends in the circumferential direction.

図６に示すように、板状部材１０Ｂ，１０Ｃには、それぞれの周方向両端の間の周方向位置（挿通孔１２ａの周方向に沿う方向の中央部）の両側周縁部に、切欠１０ｅが形成されている。つまり、板状部材１０Ｂ，１０Ｃの周方向に沿った縁部の周方向両端の間の周方向位置には、軸方向に凹みが存在する。 As shown in FIG. 6, the plate-shaped members 10B and 10C have notches 10e at the peripheral edges on both sides of the circumferential position (the central portion in the direction along the circumferential direction of the insertion hole 12a) between both ends in the circumferential direction. It is formed. That is, there is an axial dent at the circumferential position between both ends in the circumferential direction of the edge portion of the plate-shaped members 10B and 10C along the circumferential direction.

切欠１０ｅは、軸受ハウジング１２の嵌合溝１５に対応する位置、すなわち嵌合溝１５と径方向において重なる位置に形成されている。また、切欠１０ｅの幅が嵌合溝１５の幅と同じに形成されている。板状部材１０Ａの嵌合部１０ｃは、板状部材１０Ｂ，１０Ｃの切欠１０ｅを径方向に通過し、軸受ハウジング１２の嵌合溝１５に嵌合している。 The notch 10e is formed at a position corresponding to the fitting groove 15 of the bearing housing 12, that is, a position overlapping the fitting groove 15 in the radial direction. Further, the width of the notch 10e is formed to be the same as the width of the fitting groove 15. The fitting portion 10c of the plate-shaped member 10A passes through the notches 10e of the plate-shaped members 10B and 10C in the radial direction and is fitted into the fitting groove 15 of the bearing housing 12.

次に、このような構成からなるラジアルフォイル軸受３の作用について説明する。 Next, the operation of the radial foil bearing 3 having such a configuration will be described.

図６に示すように、板状部材１０Ｂ，１０Ｃには、軸方向の端縁に形成された切欠１０ｅに、板状部材１０Ａの嵌合部１０ｃが挿通されている。嵌合部１０ｃは、軸受ハウジング１２の端面１２ｂに形成された嵌合溝１５に嵌合しており、この嵌合部１０ｃが切欠１０ｅに挿通されることで、周方向における板状部材１０Ｂ，１０Ｃの回転が抑制される。したがって、板状部材１０Ｂ，１０Ｃの周方向両端部は、嵌合部１０ｃが挿通されている切欠１０ｅを挟み周方向両側に変形する（動く）。 As shown in FIG. 6, in the plate-shaped members 10B and 10C, the fitting portion 10c of the plate-shaped member 10A is inserted into the notch 10e formed at the end edge in the axial direction. The fitting portion 10c is fitted in the fitting groove 15 formed in the end surface 12b of the bearing housing 12, and the fitting portion 10c is inserted into the notch 10e so that the plate-shaped member 10B in the circumferential direction, The rotation of 10C is suppressed. Therefore, both ends of the plate-shaped members 10B and 10C in the circumferential direction are deformed (moved) to both sides in the circumferential direction with the notch 10e through which the fitting portion 10c is inserted.

嵌合部１０ｃは、軸方向において対向する位置に２つ設けられ、軸受ハウジング１２と軸方向において対向すると共に、板状部材１０Ｂ，１０Ｃとも軸方向において対向している。つまり、嵌合部１０ｃは、軸受ハウジング１２に対する板状部材１０Ａの軸方向の移動を抑制すると共に、板状部材１０Ｂ，１０Ｃの軸方向の移動も抑制している。よって、軸受ハウジング１２からの板状部材１０Ｂ，１０Ｃの脱落が抑制される。 Two fitting portions 10c are provided at positions facing each other in the axial direction, facing the bearing housing 12 in the axial direction, and also facing the plate-shaped members 10B and 10C in the axial direction. That is, the fitting portion 10c suppresses the axial movement of the plate-shaped member 10A with respect to the bearing housing 12, and also suppresses the axial movement of the plate-shaped members 10B and 10C. Therefore, the plate-shaped members 10B and 10C are suppressed from falling off from the bearing housing 12.

板状部材１０Ｂ，１０Ｃは、トップフォイル９から荷重を受ける際、トップフォイル９および板状部材１０Ａと共に撓むが、このときトップフォイル９、板状部材１０Ａ、板状部材１０Ｂ、板状部材１０Ｃ、軸受ハウジング１２の間で「滑り」が生じる。すなわち、フォイル構造体１０が複数の板状部材１０Ａ〜１０Ｃから形成されていると、回転軸１が振動した際、板状部材１０Ａ〜１０Ｃ同士の接触部でも「滑り」による摩擦エネルギーの散逸が引き起こされるので、振動を減衰させる効果が高くなる。
このように、上記構成の第２実施形態によれば、上述した第１実施形態の作用効果に加えて、フォイル構造体１０における接触面積を増やし、摩擦による減衰効果をさらに高めることができる。 When the plate-shaped members 10B and 10C receive a load from the top foil 9, they bend together with the top foil 9 and the plate-shaped member 10A. At this time, the top foil 9, the plate-shaped member 10A, the plate-shaped member 10B, and the plate-shaped member 10C , "Slip" occurs between the bearing housings 12. That is, when the foil structure 10 is formed of a plurality of plate-shaped members 10A to 10C, when the rotating shaft 1 vibrates, frictional energy is dissipated due to "sliding" even at the contact portion between the plate-shaped members 10A to 10C. Since it is caused, the effect of attenuating vibration is enhanced.
As described above, according to the second embodiment of the above configuration, in addition to the action and effect of the first embodiment described above, the contact area in the foil structure 10 can be increased, and the damping effect due to friction can be further enhanced.

上記第２実施形態のラジアルフォイル軸受３は、下記図７及び図８に示すような構成を採用してもよい。 The radial foil bearing 3 of the second embodiment may adopt the configuration shown in FIGS. 7 and 8 below.

図７は、本開示の第２実施形態の一変形例に係るラジアルフォイル軸受３を示す正面図である。図８は、本開示の第２実施形態の一変形例に係るラジアルフォイル軸受３の要部の拡大斜視図である。
図７及び図８に示す板状部材１０Ｂ，１０Ｃは、板状部材１０Ａと同様の構成となっており、板バネ部１０ｂと、嵌合部１０ｃとを備えている。 FIG. 7 is a front view showing a radial foil bearing 3 according to a modification of the second embodiment of the present disclosure. FIG. 8 is an enlarged perspective view of a main part of the radial foil bearing 3 according to a modification of the second embodiment of the present disclosure.
The plate-shaped members 10B and 10C shown in FIGS. 7 and 8 have the same configuration as the plate-shaped member 10A, and include a leaf spring portion 10b and a fitting portion 10c.

板状部材１０Ａに形成された嵌合部１０ｃは、板状部材１０Ｂの嵌合部１０ｃの内側の空間に嵌合している。また、板状部材１０Ｂに形成された嵌合部１０ｃは、板状部材１０Ｃの嵌合部１０ｃの内側の空間に嵌合している。つまり、嵌合部１０ｃの周方向における寸法が、板状部材１０Ａ、板状部材１０Ｂ、板状部材１０Ｃの順に大きくなっている。また、嵌合部１０ｃの径方向における寸法が、板状部材１０Ａ、板状部材１０Ｂ、板状部材１０Ｃの順に大きくなっている。なお、板状部材１０Ｃの嵌合部１０ｃは、軸受ハウジング１２の嵌合溝１５に嵌合している。図中、板状部材１０Ａ〜１０Ｃの嵌合部１０ｃの間には隙間が設けられているが、この隙間は、各部材を明瞭に区別するために設けられたもので、実装置においては、各部材はそれぞれ当接している。 The fitting portion 10c formed on the plate-shaped member 10A is fitted in the space inside the fitting portion 10c of the plate-shaped member 10B. Further, the fitting portion 10c formed on the plate-shaped member 10B is fitted in the space inside the fitting portion 10c of the plate-shaped member 10C. That is, the dimensions of the fitting portion 10c in the circumferential direction increase in the order of the plate-shaped member 10A, the plate-shaped member 10B, and the plate-shaped member 10C. Further, the radial dimension of the fitting portion 10c increases in the order of the plate-shaped member 10A, the plate-shaped member 10B, and the plate-shaped member 10C. The fitting portion 10c of the plate-shaped member 10C is fitted in the fitting groove 15 of the bearing housing 12. In the figure, a gap is provided between the fitting portions 10c of the plate-shaped members 10A to 10C, but this gap is provided to clearly distinguish each member, and in an actual device, the gap is provided. Each member is in contact with each other.

上記構成によれば、上述した第２実施形態の作用効果に加えて、トップフォイル９が回転軸１の軸振動による変動荷重が受け、フォイル構造体１０が共に撓んだときに、板状部材１０Ａ〜１０Ｃの嵌合部１０ｃの間でも「滑り」が生じ、これが摩擦によるエネルギー散逸を引き起こし、減衰として寄与する。
このように、上述のラジアルフォイル軸受３によれば、フォイル構造体１０における接触面積を増やし、摩擦による減衰効果をさらに高めることができる。 According to the above configuration, in addition to the effects of the second embodiment described above, when the top foil 9 receives a fluctuating load due to the shaft vibration of the rotating shaft 1 and the foil structure 10 bends together, the plate-shaped member “Slip” also occurs between the fitting portions 10c of the 10A to 10C, which causes energy dissipation due to friction and contributes as damping.
As described above, according to the radial foil bearing 3 described above, the contact area in the foil structure 10 can be increased, and the damping effect due to friction can be further enhanced.

また、上記第２実施形態のラジアルフォイル軸受３は、下記図９及び図１０に示すような構成を採用してもよい。 Further, the radial foil bearing 3 of the second embodiment may adopt the configuration as shown in FIGS. 9 and 10 below.

図９は、本開示の第２実施形態の一変形例に係るラジアルフォイル軸受３を示す正面図である。図１０は、本開示の第２実施形態の一変形例に係るラジアルフォイル軸受３の要部の拡大斜視図である。
図９及び図１０に示す複数の板状部材１０Ａ〜１０Ｃの少なくとも一つ（板状部材１０Ｂ，１０Ｃ）は、挿通孔１２ａの周方向における長さが異なっている。 FIG. 9 is a front view showing a radial foil bearing 3 according to a modification of the second embodiment of the present disclosure. FIG. 10 is an enlarged perspective view of a main part of the radial foil bearing 3 according to a modification of the second embodiment of the present disclosure.
At least one of the plurality of plate-shaped members 10A to 10C shown in FIGS. 9 and 10 (plate-shaped members 10B and 10C) has different lengths of the insertion holes 12a in the circumferential direction.

板状部材１０Ｂは、板状部材１０Ａよりも周方向における長さが短い。また、板状部材１０Ｃは、板状部材１０Ｂよりも周方向における長さが短い。つまり、周方向における寸法が、板状部材１０Ａ、板状部材１０Ｂ、板状部材１０Ｃの順に短くなっている。板状部材１０Ａの周方向両端部は、挿通孔１２ａの内周面に接触している。また、板状部材１０Ｂの周方向両端部も、挿通孔１２ａの内周面に接触している。また、板状部材１０Ｃの周方向両端部も、挿通孔１２ａの内周面に接触している。 The plate-shaped member 10B has a shorter length in the circumferential direction than the plate-shaped member 10A. Further, the plate-shaped member 10C has a shorter length in the circumferential direction than the plate-shaped member 10B. That is, the dimensions in the circumferential direction are shortened in the order of the plate-shaped member 10A, the plate-shaped member 10B, and the plate-shaped member 10C. Both ends of the plate-shaped member 10A in the circumferential direction are in contact with the inner peripheral surface of the insertion hole 12a. Further, both ends of the plate-shaped member 10B in the circumferential direction are also in contact with the inner peripheral surface of the insertion hole 12a. Further, both ends of the plate-shaped member 10C in the circumferential direction are also in contact with the inner peripheral surface of the insertion hole 12a.

上記構成によれば、上述した第２実施形態の作用効果に加えて、トップフォイル９が回転軸１の軸振動による変動荷重が受け、フォイル構造体１０が共に撓んだときに、板状部材１０Ａ〜１０Ｃのそれぞれの周方向両端部と挿通孔１２ａの内周面との間でも「滑り」が生じ、これが摩擦によるエネルギー散逸を引き起こし、減衰として寄与する。
このように、上述のラジアルフォイル軸受３によれば、フォイル構造体１０における接触面積を増やし、摩擦による減衰効果をさらに高めることができる。 According to the above configuration, in addition to the effects of the second embodiment described above, when the top foil 9 receives a fluctuating load due to the shaft vibration of the rotating shaft 1 and the foil structure 10 bends together, the plate-shaped member “Slip” also occurs between both ends of the 10A to 10C in the circumferential direction and the inner peripheral surface of the insertion hole 12a, which causes energy dissipation due to friction and contributes as damping.
As described above, according to the radial foil bearing 3 described above, the contact area in the foil structure 10 can be increased, and the damping effect due to friction can be further enhanced.

さらに、図９及び図１０に示す第２実施形態の一変形例は、下記図１１に示すような構成を採用してもよい。 Further, in one modification of the second embodiment shown in FIGS. 9 and 10, the configuration as shown in FIG. 11 below may be adopted.

図１１は、本開示の第２実施形態の一変形例に係るフォイル構造体１０を平坦化して径方向から視た平面図である。
図１１に示す複数の板状部材１０Ａ〜１０Ｃの少なくとも一つ（板状部材１０Ｂ，１０Ｃ）は、周方向両端部の端辺の形状が異なっている。 FIG. 11 is a plan view of the foil structure 10 according to a modification of the second embodiment of the present disclosure, which is flattened and viewed from the radial direction.
At least one of the plurality of plate-shaped members 10A to 10C shown in FIG. 11 (plate-shaped members 10B and 10C) has different shapes at both ends in the circumferential direction.

板状部材１０Ａの周方向両端部の端辺１０Ａ１は、軸方向に沿った直線形状になっている。一方、板状部材１０Ｂの周方向両端部の端辺１０Ｂ１は、板状部材１０Ａの周方向両端部の間の周方向位置で、軸方向中央部において周方向に延伸されている。また、板状部材１０Ｃの周方向両端部の端辺１０Ｃ１は、板状部材１０Ｂの周方向両端部の間の周方向位置で、軸方向中央部において周方向に延伸されている。 The end sides 10A1 at both ends of the plate-shaped member 10A in the circumferential direction have a linear shape along the axial direction. On the other hand, the end sides 10B1 of both ends in the circumferential direction of the plate-shaped member 10B are extended in the circumferential direction at the central portion in the axial direction at the circumferential position between the both ends in the circumferential direction of the plate-shaped member 10A. Further, the end sides 10C1 of both ends in the circumferential direction of the plate-shaped member 10C are extended in the circumferential direction at the central portion in the axial direction at the circumferential position between the both ends in the circumferential direction of the plate-shaped member 10B.

上記構成によれば、上述した第２実施形態の一変形例の作用効果に加えて、板状部材１０Ａ〜１０Ｃが挿通孔１２ａの内周面に強く押し付けられたとき、荷重を支える面積（板状部材１０Ａ〜１０Ｃが重なっている領域）が広くなり、より強い外乱に耐えられるようになる。 According to the above configuration, in addition to the action and effect of one modification of the second embodiment described above, when the plate-shaped members 10A to 10C are strongly pressed against the inner peripheral surface of the insertion hole 12a, the area that supports the load (plate). The area where the shape members 10A to 10C overlap) becomes wider, and it becomes possible to withstand a stronger disturbance.

（第３実施形態）
次に、本開示の第３実施形態について説明する。以下の説明において、上述の実施形態と同一又は同等の構成については同一の符号を付し、その説明を簡略若しくは省略する。 (Third Embodiment)
Next, a third embodiment of the present disclosure will be described. In the following description, the same or equivalent configurations as those in the above-described embodiment are designated by the same reference numerals, and the description thereof will be simplified or omitted.

図１２は、本開示の第３実施形態に係るラジアルフォイル軸受３を示す正面図である。図１３は、本開示の第３実施形態に係るラジアルフォイル軸受３の要部の拡大斜視図である。
これらの図に示すように、第３実施形態のラジアルフォイル軸受３は、フォイル構造体１０が、嵌合部１０ｃとして一対の折り曲げ部１７を有する点で、上記実施形態と異なる。 FIG. 12 is a front view showing the radial foil bearing 3 according to the third embodiment of the present disclosure. FIG. 13 is an enlarged perspective view of a main part of the radial foil bearing 3 according to the third embodiment of the present disclosure.
As shown in these figures, the radial foil bearing 3 of the third embodiment is different from the above embodiment in that the foil structure 10 has a pair of bent portions 17 as fitting portions 10c.

板状部材１０Ａには、それぞれの周方向両端の間の周方向位置（挿通孔１２ａの周方向に沿う方向の中央部）の両側周縁部に、一対の折り曲げ部１７が形成されている。つまり、板状部材１０Ａは、軸方向において対向する位置に、２つの一対の折り曲げ部１７を有している。あるいは、板状部材１０Ａは、軸方向の両側の端縁に、それぞれ一対の折り曲げ部１７を有している。 The plate-shaped member 10A is formed with a pair of bent portions 17 on both side peripheral portions at a circumferential position (central portion in a direction along the circumferential direction of the insertion hole 12a) between both ends in the circumferential direction. That is, the plate-shaped member 10A has two pairs of bent portions 17 at positions facing each other in the axial direction. Alternatively, the plate-shaped member 10A has a pair of bent portions 17 at both end edges in the axial direction.

図１３に示すように、板状部材１０Ａには、一対の折り曲げ部１７を径方向外側に向かって切り起こすための切込み１０ｆが形成されている。つまり、板状部材１０Ａの周方向に沿った縁部の周方向両端の間の周方向位置には、軸方向に凹みが存在する。一対の折り曲げ部１７は、周方向において離隔している。一対の折り曲げ部１７は、軸方向における幅が一定の矩形板状に形成されている。また、一対の折り曲げ部１７は、板状部材１０Ａの平坦部（板バネ部）に対して径方向外側に向かって略９０°に曲げられている。 As shown in FIG. 13, the plate-shaped member 10A is formed with a notch 10f for cutting up the pair of bent portions 17 in the radial direction outward. That is, there is an axial dent at the circumferential position between both ends in the circumferential direction of the edge portion along the circumferential direction of the plate-shaped member 10A. The pair of bent portions 17 are separated in the circumferential direction. The pair of bent portions 17 are formed in a rectangular plate shape having a constant width in the axial direction. Further, the pair of bent portions 17 are bent at approximately 90 ° in the radial direction with respect to the flat portion (leaf spring portion) of the plate-shaped member 10A.

一対の折り曲げ部１７は、図１２に示すように、軸受ハウジング１２の嵌合溝１５に嵌合している。板状部材１０Ａが挿通孔１２ａへの装着によって湾曲すると、一対の折り曲げ部１７は、周方向両側に広がり、嵌合溝１５の周方向の両側面に当接する。これにより、一対の折り曲げ部１７と嵌合溝１５との間に摩擦力が発現し、板状部材１０Ａが軸受ハウジング１２に保持される。 As shown in FIG. 12, the pair of bent portions 17 are fitted in the fitting groove 15 of the bearing housing 12. When the plate-shaped member 10A is curved by being attached to the insertion hole 12a, the pair of bent portions 17 spreads on both sides in the circumferential direction and abuts on both side surfaces in the circumferential direction of the fitting groove 15. As a result, a frictional force is generated between the pair of bent portions 17 and the fitting groove 15, and the plate-shaped member 10A is held by the bearing housing 12.

次に、このような構成からなるラジアルフォイル軸受３の作用について説明する。 Next, the operation of the radial foil bearing 3 having such a configuration will be described.

回転軸１の軸振動による変動荷重（負荷と除荷の繰り返し）が板状部材１０Ａに作用し、例えば荷重が除荷側になったとき、板状部材１０Ａは、軸受ハウジング１２の挿通孔１２ａの内周面から浮き上がる。ここで、板状部材１０Ａの一対の折り曲げ部１７は、軸受ハウジング１２の嵌合溝１５の周方向の両側面に当接しているため、一対の折り曲げ部１７と嵌合溝１５との間で「滑り」が生じ、これが摩擦によるエネルギー散逸を引き起こし、減衰として寄与する。図１２に示すように、板状部材１０Ａが挿通孔１２ａへの装着によって湾曲し、一対の折り曲げ部１７が周方向両側に広がり、嵌合溝１５の周方向の両側面に押し付けられているので、一対の折り曲げ部１７の嵌合溝１５の周方向の両側面への接触力が弱まることが無く、確実に摩擦減衰効果が発揮される。なお、荷重が負荷側になったときも同様である。
このように、上記構成の第３実施形態によれば、上述した第１実施形態の作用効果に加えて、嵌合部１０ｃの摩擦による減衰効果をさらに高めることができる。 When a fluctuating load (repeated load and unloading) due to shaft vibration of the rotating shaft 1 acts on the plate-shaped member 10A, for example, when the load is on the unloading side, the plate-shaped member 10A has an insertion hole 12a of the bearing housing 12. It rises from the inner peripheral surface of. Here, since the pair of bent portions 17 of the plate-shaped member 10A are in contact with both side surfaces of the fitting groove 15 of the bearing housing 12 in the circumferential direction, between the pair of bent portions 17 and the fitting groove 15. "Slip" occurs, which causes energy dissipation due to friction and contributes as damping. As shown in FIG. 12, the plate-shaped member 10A is curved by being attached to the insertion hole 12a, and the pair of bent portions 17 spread on both sides in the circumferential direction and are pressed against both side surfaces in the circumferential direction of the fitting groove 15. The contact force of the pair of bent portions 17 on both side surfaces in the circumferential direction of the fitting grooves 15 is not weakened, and the friction damping effect is surely exhibited. The same applies when the load is on the load side.
As described above, according to the third embodiment of the above configuration, in addition to the action and effect of the first embodiment described above, the damping effect due to the friction of the fitting portion 10c can be further enhanced.

上記第３実施形態のラジアルフォイル軸受３は、下記図１４に示すような構成を採用してもよい。 The radial foil bearing 3 of the third embodiment may adopt the configuration as shown in FIG. 14 below.

図１４は、本開示の第３実施形態の一変形例に係るラジアルフォイル軸受３の要部の拡大斜視図である。
図１４に示す板状部材１０Ａには、周方向において離隔した２つの切込み１０ｆから、それぞれ径方向外側に向かって切り起こされた一対の折り曲げ部１７が形成されている。つまり、板状部材１０Ａの周方向に沿った縁部の周方向両端の間の周方向位置には、軸方向に２つ凹みが存在する。 FIG. 14 is an enlarged perspective view of a main part of the radial foil bearing 3 according to a modification of the third embodiment of the present disclosure.
The plate-shaped member 10A shown in FIG. 14 is formed with a pair of bent portions 17 which are cut and raised outward in the radial direction from two notches 10f separated in the circumferential direction. That is, there are two dents in the axial direction at the circumferential position between both ends in the circumferential direction of the edge portion along the circumferential direction of the plate-shaped member 10A.

２つの凹み（切込み１０ｆ）の間には、凸部１８が形成されている。一対の折り曲げ部１７は、凸部１８の周方向両側に接続されている。つまり、一対の折り曲げ部１７は、凸部１８から周方向両側に延伸した部分を、径方向外側に折り曲げて形成されている。このような構成によれば、図１３に示すように一対の折り曲げ部１７の長さが、その間の切込み１０ｆの周方向における寸法に制限されることがない。対して、図１４に示す構成によれば、一対の折り曲げ部１７が周方向において離隔する寸法を広げることなく、一対の折り曲げ部１７を長く形成できる。これにより、嵌合溝１５を周方向に大きくすることなく、また、一対の折り曲げ部１７を長くし嵌合溝１５に嵌合させ易くすることができる。 A convex portion 18 is formed between the two recesses (cuts 10f). The pair of bent portions 17 are connected to both sides of the convex portion 18 in the circumferential direction. That is, the pair of bent portions 17 are formed by bending the portions extending from the convex portions 18 on both sides in the circumferential direction outward in the radial direction. According to such a configuration, as shown in FIG. 13, the length of the pair of bent portions 17 is not limited to the dimension of the notch 10f between them in the circumferential direction. On the other hand, according to the configuration shown in FIG. 14, the pair of bent portions 17 can be formed long without widening the dimension in which the pair of bent portions 17 are separated in the circumferential direction. As a result, the fitting groove 15 can be made longer in the circumferential direction, and the pair of bent portions 17 can be lengthened to facilitate fitting in the fitting groove 15.

（第４実施形態）
次に、本開示の第４実施形態について説明する。以下の説明において、上述の実施形態と同一又は同等の構成については同一の符号を付し、その説明を簡略若しくは省略する。 (Fourth Embodiment)
Next, a fourth embodiment of the present disclosure will be described. In the following description, the same or equivalent configurations as those in the above-described embodiment are designated by the same reference numerals, and the description thereof will be simplified or omitted.

図１５は、本開示の第４実施形態に係るラジアルフォイル軸受３を示す正面図である。図１６は、本開示の第４実施形態に係るラジアルフォイル軸受３の要部の拡大斜視図である。
これらの図に示すように、第４実施形態のラジアルフォイル軸受３は、フォイル構造体１０が、径方向において重なった複数の板状部材１０Ａ〜１０Ｃによって形成されており、複数の板状部材１０Ａ〜１０Ｃの少なくとも一つ（板状部材１０Ｂ，１０Ｃ）は、径方向外側に向かって切り起こされた爪部１０ｇを有する点で、上記実施形態と異なる。 FIG. 15 is a front view showing the radial foil bearing 3 according to the fourth embodiment of the present disclosure. FIG. 16 is an enlarged perspective view of a main part of the radial foil bearing 3 according to the fourth embodiment of the present disclosure.
As shown in these figures, in the radial foil bearing 3 of the fourth embodiment, the foil structure 10 is formed by a plurality of plate-shaped members 10A to 10C overlapping in the radial direction, and the plurality of plate-shaped members 10A are formed. At least one of 10C (plate-shaped members 10B, 10C) is different from the above embodiment in that it has a claw portion 10g cut up outward in the radial direction.

図１６に示すように、板状部材１０Ａは、上記第２実施形態の一変形例（図１４参照）と同一の構成を有する。この板状部材１０Ａの径方向外側には、２枚の板状部材１０Ｂ，１０Ｃが重なって配置されている。板状部材１０Ｂ，１０Ｃは、上記第２実施形態（図６参照）と同様の切欠１０ｅを有する。つまり、板状部材１０Ｂ，１０Ｃには、それぞれの周方向両端の間の周方向位置（挿通孔１２ａの周方向に沿う方向の中央部）の両側周縁部に、切欠１０ｅが形成されている。板状部材１０Ａの嵌合部１０ｃ（一対の折り曲げ部１７）は、板状部材１０Ｂ，１０Ｃの切欠１０ｅを径方向に通過し、軸受ハウジング１２の嵌合溝１５に嵌合している。 As shown in FIG. 16, the plate-shaped member 10A has the same configuration as one modification (see FIG. 14) of the second embodiment. Two plate-shaped members 10B and 10C are arranged so as to overlap each other on the radial outer side of the plate-shaped member 10A. The plate-shaped members 10B and 10C have the same notch 10e as in the second embodiment (see FIG. 6). That is, the plate-shaped members 10B and 10C are formed with notches 10e at the peripheral edges on both sides of the circumferential position (the central portion in the direction along the circumferential direction of the insertion hole 12a) between both ends in the circumferential direction. The fitting portion 10c (pair of bent portions 17) of the plate-shaped member 10A passes through the notches 10e of the plate-shaped members 10B and 10C in the radial direction and is fitted into the fitting groove 15 of the bearing housing 12.

図１７〜図２２は、本開示の第４実施形態に係る板状部材１０Ｂ，１０Ｃを形成するフォイル片１０ａを平坦化して径方向から視た平面図である。
これらの図に示すように、板状部材１０Ｂ，１０Ｃを形成するフォイル片１０ａには、所定パターンのスリット２０（切込み）が形成されている。このフォイル片１０ａを湾曲させると、スリット２０によって隔離した部分が径方向外側に切り起こされて爪部１０ｇとなる。 17 to 22 are plan views of the foil pieces 10a forming the plate-shaped members 10B and 10C according to the fourth embodiment of the present disclosure, which are flattened and viewed from the radial direction.
As shown in these figures, slits 20 (cuts) having a predetermined pattern are formed in the foil pieces 10a forming the plate-shaped members 10B and 10C. When the foil piece 10a is curved, the portion separated by the slit 20 is cut up radially outward to form a claw portion 10g.

図１７に示すスリット２０（パターンＡ）は、フォイル片１０ａの軸方向中央部に、Ｈ字状スリットが形成されると共に、該Ｈ字状スリットの周方向両側に、一対のＵ字状スリットが形成されている。
図１８に示すスリット２０（パターンＢ）は、フォイル片１０ａの軸方向中央部に、一対のＵ字状スリットが形成されると共に、フォイル片１０ａの４つのコーナー部に、Ｌ字状スリットが形成されている。 In the slit 20 (pattern A) shown in FIG. 17, an H-shaped slit is formed in the axial center portion of the foil piece 10a, and a pair of U-shaped slits are formed on both sides of the H-shaped slit in the circumferential direction. It is formed.
In the slit 20 (pattern B) shown in FIG. 18, a pair of U-shaped slits are formed in the axial center portion of the foil piece 10a, and L-shaped slits are formed in the four corner portions of the foil piece 10a. Has been done.

図１９に示すスリット２０（パターンＣ）は、フォイル片１０ａの４つのコーナー部に、フォイル片１０ａの中央部に向かって延びる一対の傾斜スリットが形成されている。
図２０に示すスリット２０（パターンＤ）は、フォイル片１０ａの軸方向中央部に、一対のＵ字状スリットが形成されると共に、該一対のＵ字状スリットの周方向両側に、一対のＵ字状スリットが形成されている。 In the slit 20 (pattern C) shown in FIG. 19, a pair of inclined slits extending toward the center of the foil piece 10a are formed at the four corners of the foil piece 10a.
In the slit 20 (pattern D) shown in FIG. 20, a pair of U-shaped slits are formed in the axial center portion of the foil piece 10a, and a pair of U-shaped slits are formed on both sides of the pair of U-shaped slits in the circumferential direction. A character slit is formed.

図２１に示すスリット２０（パターンＥ）は、フォイル片１０ａの軸方向中央部に、Ｈ字状スリットが形成されると共に、該Ｈ字状スリットの周方向両側に、一対のＨ字状スリットが形成されている。
図２２に示すスリット２０（パターンＦ）は、フォイル片１０ａの４つのコーナー部に、Ｔ字状スリットが形成されている。 In the slit 20 (pattern E) shown in FIG. 21, an H-shaped slit is formed in the axial center portion of the foil piece 10a, and a pair of H-shaped slits are formed on both sides of the H-shaped slit in the circumferential direction. It is formed.
In the slit 20 (pattern F) shown in FIG. 22, T-shaped slits are formed at the four corners of the foil piece 10a.

図２３は、本開示の第４実施形態に係るフォイル構造体１０の２層目（板状部材１０Ｂ）と３層目（板状部材１０Ｃ）のスリット２０のパターン（Ａ〜Ｆ）の組み合わせ例を示す図である。
図２３に示すように、板状部材１０Ｂ，１０Ｃのスリット２０のパターン（Ａ〜Ｆ）は、互いに異なっている。つまり、２層目（板状部材１０Ｂ）と３層目（板状部材１０Ｃ）を重ねたときに互いの爪部１０ｇが干渉しないよう、各層の切込み位置は違えてある。 FIG. 23 shows a combination example of the slit 20 patterns (A to F) of the second layer (plate-shaped member 10B) and the third layer (plate-shaped member 10C) of the foil structure 10 according to the fourth embodiment of the present disclosure. It is a figure which shows.
As shown in FIG. 23, the patterns (A to F) of the slits 20 of the plate-shaped members 10B and 10C are different from each other. That is, the cut positions of the respective layers are different so that the claw portions 10g do not interfere with each other when the second layer (plate-shaped member 10B) and the third layer (plate-shaped member 10C) are overlapped.

次に、このような構成からなるラジアルフォイル軸受３の作用について説明する。 Next, the operation of the radial foil bearing 3 having such a configuration will be described.

２層目（板状部材１０Ｂ）と３層目（板状部材１０Ｃ）にスリット２０を入れ、板状部材１０Ｂ，１０Ｃを湾曲させると、スリット２０によって離隔した部分が、径方向外側（湾曲面の接線方向）へ飛び出し、２層目（板状部材１０Ｂ）の爪部１０ｇは３層目（板状部材１０Ｃ）に接し、３層目（板状部材１０Ｃ）の爪部１０ｇは軸受ハウジング１２の挿通孔１２ａの内壁面に接する。 When slits 20 are inserted in the second layer (plate-shaped member 10B) and the third layer (plate-shaped member 10C) and the plate-shaped members 10B and 10C are curved, the portions separated by the slits 20 are radially outward (curved surface). The claw portion 10g of the second layer (plate-shaped member 10B) is in contact with the third layer (plate-shaped member 10C), and the claw portion 10g of the third layer (plate-shaped member 10C) is the bearing housing 12. In contact with the inner wall surface of the insertion hole 12a.

このように板状部材１０Ｂ，１０Ｃが爪部１０ｇを有していると、回転軸１が振動した際、爪部１０ｇの接触部でも「滑り」による摩擦エネルギーの散逸が引き起こされるので、振動を減衰させる効果が高くなる。
このように、上記構成の第４実施形態によれば、上述した実施形態の作用効果に加えて、フォイル構造体１０における接触面積を増やし、摩擦による減衰効果をさらに高めることができる。 When the plate-shaped members 10B and 10C have the claw portion 10g in this way, when the rotating shaft 1 vibrates, the frictional energy is dissipated due to "sliding" even at the contact portion of the claw portion 10g. The effect of damping is high.
As described above, according to the fourth embodiment of the above configuration, in addition to the action and effect of the above-described embodiment, the contact area in the foil structure 10 can be increased, and the damping effect due to friction can be further enhanced.

また、上記第４実施形態のラジアルフォイル軸受３は、下記図２４に示すような構成を採用してもよい。 Further, the radial foil bearing 3 of the fourth embodiment may adopt the configuration as shown in FIG. 24 below.

図２４は、本開示の第４実施形態の一変形例に係るラジアルフォイル軸受３を示す正面図である。
図２４に示す板状部材１０Ｂ，１０Ｃは、板状部材１０Ａと同様に、一対の折り曲げ部１７（嵌合部１０ｃ）を備えている。 FIG. 24 is a front view showing a radial foil bearing 3 according to a modification of the fourth embodiment of the present disclosure.
The plate-shaped members 10B and 10C shown in FIG. 24 include a pair of bent portions 17 (fitting portions 10c), similarly to the plate-shaped members 10A.

板状部材１０Ａに形成された一対の折り曲げ部１７は、板状部材１０Ｂの一対の折り曲げ部１７の内側の空間に嵌合している。また、板状部材１０Ｂに形成された一対の折り曲げ部１７は、板状部材１０Ｃの一対の折り曲げ部１７の内側の空間に嵌合している。つまり、一対の折り曲げ部１７の周方向における寸法（隙間）が、板状部材１０Ａ、板状部材１０Ｂ、板状部材１０Ｃの順に大きくなっている。なお、板状部材１０Ｃの一対の折り曲げ部１７は、軸受ハウジング１２の嵌合溝１５に嵌合している。図中、板状部材１０Ａ〜１０Ｃの一対の折り曲げ部１７の間には隙間が設けられているが、この隙間は、各部材を明瞭に区別するために設けられたもので、実装置においては、各部材はそれぞれ当接している。 The pair of bent portions 17 formed on the plate-shaped member 10A are fitted in the space inside the pair of bent portions 17 of the plate-shaped member 10B. Further, the pair of bent portions 17 formed on the plate-shaped member 10B are fitted in the space inside the pair of bent portions 17 of the plate-shaped member 10C. That is, the dimensions (gap) of the pair of bent portions 17 in the circumferential direction increase in the order of the plate-shaped member 10A, the plate-shaped member 10B, and the plate-shaped member 10C. The pair of bent portions 17 of the plate-shaped member 10C are fitted in the fitting groove 15 of the bearing housing 12. In the figure, a gap is provided between the pair of bent portions 17 of the plate-shaped members 10A to 10C, but this gap is provided to clearly distinguish each member, and in an actual device, the gap is provided. , Each member is in contact with each other.

上記構成によれば、上述した第４実施形態の作用効果に加えて、トップフォイル９が回転軸１の軸振動による変動荷重が受け、フォイル構造体１０が共に撓んだときに、板状部材１０Ａ〜１０Ｃの一対の折り曲げ部１７（嵌合部１０ｃ）の間でも「滑り」が生じ、これが摩擦によるエネルギー散逸を引き起こし、減衰として寄与する。
このように、上述のラジアルフォイル軸受３によれば、フォイル構造体１０における接触面積を増やし、摩擦による減衰効果をさらに高めることができる。 According to the above configuration, in addition to the effects of the fourth embodiment described above, when the top foil 9 receives a fluctuating load due to the shaft vibration of the rotating shaft 1 and the foil structure 10 bends together, the plate-shaped member “Slip” also occurs between the pair of bent portions 17 (fitting portions 10c) of the 10A to 10C, which causes energy dissipation due to friction and contributes as damping.
As described above, according to the radial foil bearing 3 described above, the contact area in the foil structure 10 can be increased, and the damping effect due to friction can be further enhanced.

さらに、図２４に示す第４実施形態の一変形例は、下記図２５に示すような構成を採用してもよい。 Further, as one modification of the fourth embodiment shown in FIG. 24, the configuration as shown in FIG. 25 below may be adopted.

図２５は、本開示の第４実施形態の一変形例に係るラジアルフォイル軸受３の要部の拡大斜視図である。
図２４に示す板状部材１０Ｂ，１０Ｃは、板状部材１０Ａ（図１４参照）と同様に、周方向において離隔した２つの切込み１０ｆから、それぞれ径方向外側に向かって切り起こされた一対の折り曲げ部１７（嵌合部１０ｃ）を備えている。 FIG. 25 is an enlarged perspective view of a main part of the radial foil bearing 3 according to a modification of the fourth embodiment of the present disclosure.
Similar to the plate-shaped member 10A (see FIG. 14), the plate-shaped members 10B and 10C shown in FIG. 24 are a pair of bends that are cut and raised outward in the radial direction from two notches 10f separated in the circumferential direction. A portion 17 (fitting portion 10c) is provided.

板状部材１０Ｃに形成された一対の折り曲げ部１７は、板状部材１０Ｂの一対の折り曲げ部１７の内側の空間に嵌合している。また、板状部材１０Ｂに形成された一対の折り曲げ部１７は、板状部材１０Ａの一対の折り曲げ部１７の内側の空間に嵌合している。つまり、一対の折り曲げ部１７の周方向における寸法（隙間）が、板状部材１０Ａ、板状部材１０Ｂ、板状部材１０Ｃの順に小さくなっている。なお、板状部材１０Ａの一対の折り曲げ部１７は、軸受ハウジング１２の嵌合溝１５に嵌合している。 The pair of bent portions 17 formed on the plate-shaped member 10C are fitted in the space inside the pair of bent portions 17 of the plate-shaped member 10B. Further, the pair of bent portions 17 formed on the plate-shaped member 10B are fitted in the space inside the pair of bent portions 17 of the plate-shaped member 10A. That is, the dimensions (gap) of the pair of bent portions 17 in the circumferential direction are reduced in the order of the plate-shaped member 10A, the plate-shaped member 10B, and the plate-shaped member 10C. The pair of bent portions 17 of the plate-shaped member 10A are fitted in the fitting groove 15 of the bearing housing 12.

上記構成によれば、上述した第４実施形態の一変形例と同様に、トップフォイル９が回転軸１の軸振動による変動荷重が受け、フォイル構造体１０が共に撓んだときに、板状部材１０Ａ〜１０Ｃの一対の折り曲げ部１７（嵌合部１０ｃ）の間でも「滑り」が生じ、これが摩擦によるエネルギー散逸を引き起こし、減衰として寄与する。
このように、上述のラジアルフォイル軸受３によれば、フォイル構造体１０における接触面積を増やし、摩擦による減衰効果をさらに高めることができる。 According to the above configuration, as in the case of one modification of the fourth embodiment described above, when the top foil 9 receives a fluctuating load due to the shaft vibration of the rotating shaft 1 and the foil structure 10 bends together, the top foil 9 has a plate shape. “Slip” also occurs between the pair of bent portions 17 (fitting portions 10c) of the members 10A to 10C, which causes energy dissipation due to friction and contributes as damping.
As described above, according to the radial foil bearing 3 described above, the contact area in the foil structure 10 can be increased, and the damping effect due to friction can be further enhanced.

以上、図面を参照しながら本開示の好適な実施形態について説明したが、本開示は上記実施形態に限定されるものではない。上述した実施形態において示した各構成部材の諸形状や組み合わせ等は一例であって、本開示の主旨から逸脱しない範囲において設計要求等に基づき種々変更可能である。 Although the preferred embodiments of the present disclosure have been described above with reference to the drawings, the present disclosure is not limited to the above embodiments. The various shapes and combinations of the constituent members shown in the above-described embodiment are examples, and can be variously changed based on the design requirements and the like without departing from the gist of the present disclosure.

例えば、上記各実施形態及び各変形例の構成の置換、組み合わせは適宜行うことができる。 For example, the configurations of the above-described embodiments and modifications can be replaced or combined as appropriate.

３ ラジアルフォイル軸受
９ トップフォイル
１０ フォイル構造体
１０Ａ 板状部材
１０ｂ 板バネ部
１０Ｂ 板状部材
１０ｃ 嵌合部
１０Ｃ 板状部材
１０ｇ 爪部
１２ 軸受ハウジング
１２ａ 挿通孔
１２ｂ 端面
１５ 嵌合溝
２０ スリット
Ａ パターン
Ｂ パターン
Ｃ パターン
Ｄ パターン
Ｅ パターン
Ｆ パターン 3 Radial foil bearing 9 Top foil 10 Foil structure 10A Plate member 10b Plate spring part 10B Plate member 10c Fitting part 10C Plate member 10g Claw part 12 Bearing housing 12a Insertion hole 12b End face 15 Fitting groove 20 Slit A pattern B pattern C pattern D pattern E pattern F pattern

Claims (6)

挿通孔を有する軸受ハウジングと、
前記挿通孔の内側に配置されたトップフォイルと、
前記トップフォイルと前記軸受ハウジングとの間に介在するフォイル構造体と、を備え、
前記フォイル構造体は、前記挿通孔の周方向の中央部に向かって、前記軸受ハウジングとの間隔が増大すると共に前記トップフォイルとの間隔が減少する領域を有する、ラジアルフォイル軸受。 Bearing housing with insertion holes and
With the top foil arranged inside the insertion hole,
A foil structure interposed between the top foil and the bearing housing is provided.
The foil structure is a radial foil bearing having a region in which the distance from the bearing housing increases and the distance from the top foil decreases toward the central portion in the circumferential direction of the insertion hole. 前記フォイル構造体は、前記挿通孔の周方向の中央部において、前記挿通孔が延びる軸方向における前記軸受ハウジングの端面に形成された嵌合溝に嵌合する嵌合部を有する、請求項１に記載のラジアルフォイル軸受。 The foil structure has a fitting portion that fits into a fitting groove formed in an end face of the bearing housing in the axial direction in which the insertion hole extends at a central portion in the circumferential direction of the insertion hole. Radial foil bearings described in. 前記フォイル構造体は、前記挿通孔の径方向において重なった複数の板状部材によって形成されている、請求項１または２に記載のラジアルフォイル軸受。 The radial foil bearing according to claim 1 or 2, wherein the foil structure is formed of a plurality of plate-shaped members overlapping in the radial direction of the insertion hole. 前記複数の板状部材の少なくとも一つは、前記挿通孔の周方向における長さが異なる、請求項３に記載のラジアルフォイル軸受。 The radial foil bearing according to claim 3, wherein at least one of the plurality of plate-shaped members has different lengths in the circumferential direction of the insertion hole. 前記複数の板状部材の少なくとも一つは、スリットによって形成された爪部を備える、請求項３または４に記載のラジアルフォイル軸受。 The radial foil bearing according to claim 3 or 4, wherein at least one of the plurality of plate-shaped members includes a claw portion formed by a slit. 前記複数の板状部材のうち、前記挿通孔の径方向で重なる板状部材は、前記スリットのパターンが互いに異なる、請求項５に記載のラジアルフォイル軸受。 The radial foil bearing according to claim 5, wherein among the plurality of plate-shaped members, the plate-shaped members overlapping in the radial direction of the insertion holes have different slit patterns.
JP2020068962A 2020-04-07 2020-04-07 Radial foil bearing Pending JP2021165576A (en)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006057828A (en) * 2004-12-02 2006-03-02 Kawasaki Heavy Ind Ltd Top foil locking mechanism
DE102017204761A1 (en) * 2017-03-22 2018-09-27 Robert Bosch Gmbh Aerodynamic radial bearing
JP2019157889A (en) * 2018-03-07 2019-09-19 株式会社Ihi Radial foil bearing
WO2020035208A1 (en) * 2018-08-15 2020-02-20 Robert Bosch Gmbh Air bearing, bearing unit and compressor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006057828A (en) * 2004-12-02 2006-03-02 Kawasaki Heavy Ind Ltd Top foil locking mechanism
DE102017204761A1 (en) * 2017-03-22 2018-09-27 Robert Bosch Gmbh Aerodynamic radial bearing
JP2019157889A (en) * 2018-03-07 2019-09-19 株式会社Ihi Radial foil bearing
WO2020035208A1 (en) * 2018-08-15 2020-02-20 Robert Bosch Gmbh Air bearing, bearing unit and compressor

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