JP2008163983A - Bearing device - Google Patents

Bearing device Download PDF

Info

Publication number
JP2008163983A
JP2008163983A JP2006351875A JP2006351875A JP2008163983A JP 2008163983 A JP2008163983 A JP 2008163983A JP 2006351875 A JP2006351875 A JP 2006351875A JP 2006351875 A JP2006351875 A JP 2006351875A JP 2008163983 A JP2008163983 A JP 2008163983A
Authority
JP
Japan
Prior art keywords
inner ring
sleeve
shaft
bearing device
cooling medium
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
Application number
JP2006351875A
Other languages
Japanese (ja)
Inventor
Hiroshi Morishita
比呂志 森下
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Priority to JP2006351875A priority Critical patent/JP2008163983A/en
Publication of JP2008163983A publication Critical patent/JP2008163983A/en
Pending legal-status Critical Current

Links

Images

Landscapes

  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To prevent seizure between a rolling element and an inner ring by increasing the cooling efficiency of the inner ring to reduce a temperature difference between an outer ring and the inner ring. <P>SOLUTION: The bearing device comprises a bearing consisting of the inner ring, the outer ring, and the rolling elements, the inner ring of the bearing being mounted on a shaft directly or via a sleeve. In the inner diameter face of the inner ring, the outer diameter face or the inner diameter face of the sleeve, or the outer diameter face of the shaft, a spiral groove is provided through which cooling medium passes to cool the inner ring or the sleeve. When the shaft is rotated and the cooling medium flows from one end of the spiral groove to the other, the cooling medium receives inertia force with the rotation of the shaft and the cooling medium flows in the direction corresponding to the spiral direction of the spiral groove. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

この発明は、軸受装置、詳しくは、内輪やスリーブの冷却装置を備えた軸受装置に関する。   The present invention relates to a bearing device, and more particularly to a bearing device provided with a cooling device for an inner ring and a sleeve.

ジェットエンジンやガスタービン用の主軸軸受は、高速回転の下で使用される。このため、軸受の内外輪に温度差が生じる。このとき、内輪の温度上昇が大きくなりすぎると、軸受隙間が過小となって、焼付き等が生じる場合がある。このような問題に対し、特許文献１に示すような軸受装置が知られている。   Main shaft bearings for jet engines and gas turbines are used under high speed rotation. For this reason, a temperature difference arises in the inner and outer rings of the bearing. At this time, if the temperature rise of the inner ring becomes too large, the bearing gap becomes too small, and seizure or the like may occur. For such a problem, a bearing device as shown in Patent Document 1 is known.

この軸受装置１は、図４に示すように、内輪２、外輪３、及び転動体４から構成される軸受、及びこの軸受の内輪４を、スリーブ５を介して軸６に取り付けた装置であり、このスリーブ５に油等の冷却媒体を通す冷媒通路７を設けたものである。   As shown in FIG. 4, the bearing device 1 is a device in which an inner ring 2, an outer ring 3, and a rolling element 4, and an inner ring 4 of the bearing are attached to a shaft 6 via a sleeve 5. The sleeve 5 is provided with a refrigerant passage 7 through which a cooling medium such as oil passes.

冷媒通路７に油等の冷却媒体が通るので、スリーブ５やこのスリーブ５に接している内輪２が冷却され、これにより外輪３と内輪２の温度差を小さくし、転動体４と内輪２との焼き付きを防止することができる。   Since a cooling medium such as oil passes through the refrigerant passage 7, the sleeve 5 and the inner ring 2 in contact with the sleeve 5 are cooled, thereby reducing the temperature difference between the outer ring 3 and the inner ring 2, and the rolling element 4 and the inner ring 2. Can be prevented.

特開平０９−３１７７７８号公報JP 09-317778 A

しかしながら、上記の方法では、スリーブ５や内輪２の冷却を十分に行えない場合がある。   However, in the above method, the sleeve 5 and the inner ring 2 may not be sufficiently cooled.

そこで、この発明は、内輪の冷却効率を上げ、外輪と内輪との温度差を小さくし、転動体と内輪との焼き付きを防止することを目的とする。   Accordingly, an object of the present invention is to increase the cooling efficiency of the inner ring, reduce the temperature difference between the outer ring and the inner ring, and prevent seizure between the rolling elements and the inner ring.

この発明は、内輪、外輪、及び転動体から構成される軸受、及びこの軸受の内輪を、直接、又はスリーブを介して軸に取り付けた軸受装置において、上記内輪の内径面、上記スリーブの外径面若しくは内径面、又は上記軸の外径面に、上記の内輪やスリーブを冷却するための冷却媒体を通すための螺旋溝を設け、上記軸を回転させ、かつ、上記冷却媒体を上記螺旋溝の一方の端から他方の端に向かって流すとき、上記軸の回転によって上記冷却媒体が受ける慣性力と、上記冷却媒体の流れ方向と一致するように、上記螺旋溝の螺旋方向を設けることを特徴とする。   The present invention relates to a bearing including an inner ring, an outer ring, and rolling elements, and a bearing device in which the inner ring of the bearing is attached to a shaft directly or via a sleeve, and the inner diameter surface of the inner ring and the outer diameter of the sleeve. A spiral groove for passing a cooling medium for cooling the inner ring and the sleeve is provided on the surface or the inner diameter surface or the outer diameter surface of the shaft, the shaft is rotated, and the cooling medium is supplied to the spiral groove. Providing a spiral direction of the spiral groove so that the inertial force received by the cooling medium by the rotation of the shaft coincides with the flow direction of the cooling medium when flowing from one end to the other end. Features.

この発明にかかる軸受装置は、内輪の内径面、スリーブの外径面若しくは内径面、又は軸の外径面に、冷却媒体を通すための螺旋溝を設け、軸を回転させ、かつ、冷却媒体を螺旋溝の一方の端から他方の端に向かって流すとき、軸の回転によって冷却媒体が受ける慣性力と、冷却媒体の流れ方向と一致するように、螺旋溝の螺旋方向を設けるので、内輪全体の冷却を効率よく行うことができ、回転によって生じる内輪の高温化を抑制することができる。これにより、外輪と内輪との温度差を小さくすることを、効率よくでき、転動体と内輪との焼き付きを防止することができる。   In the bearing device according to the present invention, a spiral groove for passing a cooling medium is provided on the inner diameter surface of the inner ring, the outer diameter surface or inner diameter surface of the sleeve, or the outer diameter surface of the shaft, the shaft is rotated, and the cooling medium Since the spiral direction of the spiral groove is provided so that the inertial force received by the cooling medium by the rotation of the shaft and the flow direction of the cooling medium coincide with each other when flowing from one end of the spiral groove toward the other end. The entire cooling can be performed efficiently, and the high temperature of the inner ring caused by the rotation can be suppressed. Thereby, it is possible to efficiently reduce the temperature difference between the outer ring and the inner ring, and seizure between the rolling element and the inner ring can be prevented.

この発明にかかる軸受装置は、内輪、外輪、及び転動体から構成される軸受、及びこの軸受の内輪を、直接、又はスリーブを介して軸に取り付けた装置である。以下、この発明について、図１〜図３を用いて説明する。   The bearing device according to the present invention is a device comprising an inner ring, an outer ring, and rolling elements, and an apparatus in which the inner ring of this bearing is attached to a shaft directly or via a sleeve. The present invention will be described below with reference to FIGS.

［第１の軸受装置（軸受装置１１ａ）］
この発明にかかる第１の軸受装置である軸受装置１１ａは内輪１２ａ、外輪１３、及び転動体１４から構成される軸受、及びこの軸受の内輪１２ａを、スリーブ１５を介して軸１６に取り付けた装置である。 [First Bearing Device (Bearing Device 11a)]
A bearing device 11a, which is a first bearing device according to the present invention, is a bearing composed of an inner ring 12a, an outer ring 13, and a rolling element 14, and a device in which the inner ring 12a of this bearing is attached to a shaft 16 via a sleeve 15. It is.

上記内輪１２ａ、外輪１３、及び転動体１４から構成される軸受は、ジェットエンジンやガスタービン用の主軸軸受として、高速回転下で使用することができれば、転がり軸受、玉軸受等、任意の軸受を用いることができる。   If the bearing comprised from the said inner ring | wheel 12a, the outer ring | wheel 13, and the rolling element 14 can be used under high-speed rotation as a main shaft bearing for jet engines and gas turbines, it will be arbitrary bearings, such as a rolling bearing and a ball bearing. Can be used.

図１（ａ）に示す軸受装置は、内輪１２ａを、スリーブ１５を介して軸１６に取り付けた装置である。このとき、内輪１２ａはスリーブ１５に嵌合して取り付けられ、スリーブ１５は軸１６に嵌合して取り付けられる。そして、このスリーブ１５の内径面には、図１（ｂ）に示すように、螺旋溝１７ａが設けられる。そして、この螺旋溝１７ａには、内輪１２ａ及びスリーブ１５を冷却するための冷却媒体が通される。   The bearing device shown in FIG. 1A is a device in which an inner ring 12 a is attached to a shaft 16 via a sleeve 15. At this time, the inner ring 12 a is fitted and attached to the sleeve 15, and the sleeve 15 is fitted and attached to the shaft 16. A spiral groove 17a is provided on the inner diameter surface of the sleeve 15 as shown in FIG. A cooling medium for cooling the inner ring 12a and the sleeve 15 is passed through the spiral groove 17a.

上記の冷却媒体とは、上記螺旋溝１７ａを通ることにより、周囲の、特にスリーブ１５や内輪１２ａの熱を奪う媒体であり、具体例としては、油や空気をあげることができる。また、上記油としては、一般的に潤滑用に用いられる潤滑油等をあげることができる。   The cooling medium is a medium that removes heat from the surroundings, particularly the sleeve 15 and the inner ring 12a, by passing through the spiral groove 17a. Specific examples thereof include oil and air. Moreover, as said oil, the lubricating oil etc. which are generally used for lubrication can be mention | raise | lifted.

また、図１（ａ）に示すように、軸１６をＡ方向（図１（ａ）の右側から見て反時計回り）に回転させ、かつ、上記冷却媒体を螺旋溝の一方の端から他方の端に向かって流すとき、具体的には、上記冷却媒体を媒体入口１８ａから入れ、螺旋溝１７ａを通し、媒体出口１８ｂから回収したとき、軸１６の回転によって冷却媒体が受ける慣性力と、冷却媒体の流れ方向と一致するように、螺旋溝１７ａの螺旋方向を設ける。このような螺旋方向を採用することにより、冷却媒体がよりスムーズに螺旋溝１７ａ内を流れることができ、内輪１２ａの冷却効率をより向上させることができる。   Further, as shown in FIG. 1A, the shaft 16 is rotated in the A direction (counterclockwise when viewed from the right side of FIG. 1A), and the cooling medium is moved from one end of the spiral groove to the other. Specifically, the inertial force received by the cooling medium by the rotation of the shaft 16 when the cooling medium is inserted from the medium inlet 18a, passed through the spiral groove 17a and recovered from the medium outlet 18b, The spiral direction of the spiral groove 17a is provided so as to coincide with the flow direction of the cooling medium. By adopting such a spiral direction, the cooling medium can flow through the spiral groove 17a more smoothly, and the cooling efficiency of the inner ring 12a can be further improved.

上記軸受装置１１ａには、転動体１４の周囲に潤滑剤を供給するため、媒体入口１８ａのほか、必要に応じて、潤滑剤供給口１９を設ける。上記冷却媒体として潤滑用の油を用いる場合は、これを潤滑油としても併用することができるが、空気を用いると、別途、潤滑油を供給する必要が生じる。このような場合に、上記潤滑剤供給口１９から潤滑油を供給することができる。   In addition to the medium inlet 18a, the bearing device 11a is provided with a lubricant supply port 19 as needed in order to supply the lubricant around the rolling elements 14. When lubricating oil is used as the cooling medium, it can be used together as lubricating oil. However, when air is used, it is necessary to supply lubricating oil separately. In such a case, lubricating oil can be supplied from the lubricant supply port 19.

［第２の軸受装置（軸受装置１１ｂ）］
次に、第２の軸受装置である軸受装置１１ｂについて説明する。
上記の軸受装置１１ａは、スリーブ１５の内径面に螺旋溝１７ａを設けたが、他の実施形態として、上記の軸受装置１１ａにおいて、このスリーブを用いず、内輪を直接、軸１６に取り付けた装置があげられる。これは、図２（ａ）（ｂ）に示すように、内輪１２ｂを用い、この内輪１２ｂを軸１６に嵌合して取り付け、この内輪１２ｂの内径面に螺旋溝１７ｂを設けた装置である。内輪１２ａ及びスリーブ１５の代わりに、螺旋溝１７ｂを設けた内輪１２ｂを用いる以外の構成は、軸受装置１１ａの場合と同様である。そして、その作用・効果も、軸受装置１１ａの場合と同様である。さらに、螺旋溝１７ｂの螺旋方向、及びその効果も螺旋溝１７ａの場合と同様である。 [Second Bearing Device (Bearing Device 11b)]
Next, the bearing device 11b as the second bearing device will be described.
The above-described bearing device 11a is provided with the spiral groove 17a on the inner diameter surface of the sleeve 15. However, as another embodiment, in the above-described bearing device 11a, the inner ring is directly attached to the shaft 16 without using this sleeve. Can be given. As shown in FIGS. 2 (a) and 2 (b), this is an apparatus using an inner ring 12b, fitting the inner ring 12b to a shaft 16 and attaching it, and providing a spiral groove 17b on the inner diameter surface of the inner ring 12b. . The configuration other than using the inner ring 12b provided with the spiral groove 17b instead of the inner ring 12a and the sleeve 15 is the same as that of the bearing device 11a. The operation and effect are the same as in the case of the bearing device 11a. Further, the spiral direction of the spiral groove 17b and the effect thereof are the same as those of the spiral groove 17a.

［第３の軸受装置］
次に、第３の軸受装置について説明する。
上記の軸受装置１１ａは、スリーブ１５の内径面に螺旋溝１７ａを設け、また、上記の軸受装置１１ｂは、内輪内径面に螺旋溝１７ｂを設けたが、他の実施形態として、上記軸受装置１１ａ又は軸受装置１１ｂにおいて、これらの螺旋溝１７ａ，１７ｂを設けず、その代わりに、図３に示すように、軸１６の外径面であって、スリーブ１５や内輪１２ｂと接する部分に、螺旋溝１７ｃを設ける装置があげられる。それ以外の構成、作用及び効果は、軸受装置１１ａや軸受装置１１ｂの場合と同様である。さらに、螺旋溝１７ｃの螺旋方向、及びその効果も螺旋溝１７ａ，１７ｂの場合と同様である。 [Third bearing device]
Next, the third bearing device will be described.
The bearing device 11a is provided with the spiral groove 17a on the inner diameter surface of the sleeve 15, and the bearing device 11b is provided with the spiral groove 17b on the inner ring inner surface. However, as another embodiment, the bearing device 11a is provided. Alternatively, in the bearing device 11b, these spiral grooves 17a and 17b are not provided. Instead, as shown in FIG. 3, the spiral grooves are formed on the outer diameter surface of the shaft 16 and in contact with the sleeve 15 and the inner ring 12b. An apparatus for providing 17c is used. Other configurations, operations, and effects are the same as those of the bearing device 11a and the bearing device 11b. Further, the spiral direction of the spiral groove 17c and the effect thereof are the same as those of the spiral grooves 17a and 17b.

［第４の軸受装置］
次に、第４の軸受装置について説明する。
上記の軸受装置１１ａは、スリーブ内径面に螺旋溝１７ａを設けたが、他の実施形態として、上記軸受装置１１ａにおいて、スリーブ１５の内径面に螺旋溝１７ａを設けず、その代わりに、スリーブ１５の外径面又は内輪１２ａの内径面に螺旋溝を設ける装置があげられる（図示せず）。それ以外の構成、作用及び効果は、軸受装置１１ａの場合と同様である。さらに、上記螺旋溝の螺旋方向、及びその効果も螺旋溝１７ａ〜１７ｃの場合と同様である。 [Fourth bearing device]
Next, the fourth bearing device will be described.
The bearing device 11a is provided with the spiral groove 17a on the sleeve inner diameter surface. However, as another embodiment, the bearing device 11a does not have the spiral groove 17a on the inner diameter surface of the sleeve 15, and instead the sleeve 15 And an inner diameter surface of the inner ring 12a are provided with a spiral groove (not shown). Other configurations, operations, and effects are the same as those of the bearing device 11a. Further, the spiral direction of the spiral groove and the effect thereof are the same as those of the spiral grooves 17a to 17c.

［第１〜第４の軸受装置］
上記したような第１〜第４の軸受装置は、ジェットエンジンやガスタービン等の高速回転が要求される装置の主軸用の軸受装置として用いることができる。 [First to fourth bearing devices]
The first to fourth bearing devices as described above can be used as a bearing device for a main shaft of a device that requires high-speed rotation, such as a jet engine or a gas turbine.

（ａ）第１の軸受装置の構造を示す断面図、（ｂ）（ａ）のスリーブのみを示す断面図(A) Cross-sectional view showing structure of first bearing device, (b) Cross-sectional view showing only sleeve of (a) （ａ）第２の軸受装置の構造を示す断面図、（ｂ）（ａ）の内輪のみを示す断面図(A) Cross-sectional view showing structure of second bearing device, (b) Cross-sectional view showing only inner ring of (a) 第３の軸受装置の軸を示す斜視図The perspective view which shows the axis | shaft of a 3rd bearing apparatus. 従来の軸受装置の構造を示す断面図Sectional view showing the structure of a conventional bearing device

符号の説明Explanation of symbols

１ 軸受装置
２ 内輪
３ 外輪
４ 転動体
５ スリーブ
６ 軸
７ 冷媒通路
１１ａ、１１ｂ 軸受装置
１２ａ，１２ｂ 内輪
１３ 外輪
１４ 転動体
１５ スリーブ
１６ 軸
１７ａ，１７ｂ，１７ｃ 螺旋溝
１８ａ 媒体入口
１８ｂ 媒体出口
１９ 潤滑剤供給口 DESCRIPTION OF SYMBOLS 1 Bearing apparatus 2 Inner ring 3 Outer ring 4 Rolling element 5 Sleeve 6 Shaft 7 Refrigerant passage 11a, 11b Bearing apparatus 12a, 12b Inner ring 13 Outer ring 14 Rolling element 15 Sleeve 16 Shaft 17a, 17b, 17c Spiral groove 18a Medium inlet 18b Medium outlet 19 Lubrication Agent supply port

Claims (2)

内輪、外輪、及び転動体から構成される軸受、及びこの軸受の内輪を、直接、又はスリーブを介して軸に取り付けた軸受装置において、
上記内輪の内径面、上記スリーブの外径面若しくは内径面、又は上記軸の外径面に、上記の内輪やスリーブを冷却するための冷却媒体を通すための螺旋溝を設け、
上記軸を回転させ、かつ、上記冷却媒体を上記螺旋溝の一方の端から他方の端に向かって流すとき、上記軸の回転によって上記冷却媒体が受ける慣性力と、上記冷却媒体の流れ方向と一致するように、上記螺旋溝の螺旋方向を設けることを特徴とする軸受装置。 In a bearing composed of an inner ring, an outer ring, and rolling elements, and a bearing device in which the inner ring of this bearing is attached to the shaft directly or via a sleeve,
Provided on the inner diameter surface of the inner ring, the outer diameter surface or inner diameter surface of the sleeve, or the outer diameter surface of the shaft is a spiral groove for passing a cooling medium for cooling the inner ring or sleeve;
When the shaft is rotated and the cooling medium flows from one end of the spiral groove toward the other end, the inertial force received by the cooling medium by the rotation of the shaft, and the flow direction of the cooling medium, A bearing device, wherein a spiral direction of the spiral groove is provided so as to coincide with each other. 上記冷却媒体は、油又は空気であることを特徴とする請求項１に記載の軸受装置。
The bearing device according to claim 1, wherein the cooling medium is oil or air.
JP2006351875A 2006-12-27 2006-12-27 Bearing device Pending JP2008163983A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2006351875A JP2008163983A (en) 2006-12-27 2006-12-27 Bearing device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006351875A JP2008163983A (en) 2006-12-27 2006-12-27 Bearing device

Publications (1)

Publication Number Publication Date
JP2008163983A true JP2008163983A (en) 2008-07-17

Family

ID=39693738

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2006351875A Pending JP2008163983A (en) 2006-12-27 2006-12-27 Bearing device

Country Status (1)

Country Link
JP (1) JP2008163983A (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010190344A (en) * 2009-02-19 2010-09-02 Sii Micro Precision Kk Rolling bearing device
JP2011106593A (en) * 2009-11-18 2011-06-02 Mitsubishi Heavy Industries Food & Packaging Machinery Co Ltd Dew condensation preventing device for bearing of rotary joint
CN103161830A (en) * 2013-04-07 2013-06-19 四川皇龙智能破碎技术股份有限公司 High-temperature-resistance bearing base

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010190344A (en) * 2009-02-19 2010-09-02 Sii Micro Precision Kk Rolling bearing device
JP2011106593A (en) * 2009-11-18 2011-06-02 Mitsubishi Heavy Industries Food & Packaging Machinery Co Ltd Dew condensation preventing device for bearing of rotary joint
CN103161830A (en) * 2013-04-07 2013-06-19 四川皇龙智能破碎技术股份有限公司 High-temperature-resistance bearing base

Similar Documents

Publication Publication Date Title
JP4800111B2 (en) Electric motor
US9366295B2 (en) Rolling bearing assembly
JP2007309101A (en) Cooling structure of supercharger with electric motor
JP2012193709A (en) Bearing structure of turbocharger
JP2009264526A (en) Bearing arrangement of supercharger
JPWO2009107493A1 (en) Rotary table device with cooling structure, rotary bearing with cooling structure
JP2007024256A (en) Lubricating device of rolling bearing
JP2007023858A (en) Bearing structure for turbocharger
JP2016109269A (en) Tilting pad bearing
JP2009063015A (en) Tilting pad type journal bearing
US20110236193A1 (en) Turbocharger bearing lubrication
JP2007009702A (en) Bearing device for turbocharger, and turbocharger
JP4367628B2 (en) Electric motor integrated turbocharger
JP2014062557A (en) Bearing device
JP2007321950A (en) Cylindrical roller bearing
JP2008163983A (en) Bearing device
JP2009287678A (en) Roller bearing and bearing structure
JP2010138753A (en) Bearing device for supercharger
JP2010156367A (en) Lubricating and cooling structure for antifriction bearing
JP2007071356A (en) Turbocharger rotation supporting device
JP2009270613A (en) Bearing structure of turbocharger
JP2018063018A (en) Bearing device of supercharger
JP2007024258A (en) Lubricating device of rolling bearing
JP2011106493A (en) Rolling bearing device
JP2008240946A (en) Lubricating device for rolling bearing