JP2010156214A - Rotary machine bearing structure - Google Patents

Rotary machine bearing structure Download PDF

Info

Publication number
JP2010156214A
JP2010156214A JP2008333709A JP2008333709A JP2010156214A JP 2010156214 A JP2010156214 A JP 2010156214A JP 2008333709 A JP2008333709 A JP 2008333709A JP 2008333709 A JP2008333709 A JP 2008333709A JP 2010156214 A JP2010156214 A JP 2010156214A
Authority
JP
Japan
Prior art keywords
floating bush
bearing
bush bearing
oil supply
compressor
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
JP2008333709A
Other languages
Japanese (ja)
Inventor
Akihiro Ueda
朗弘 上田
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.)
IHI Corp
Original Assignee
IHI Corp
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 IHI Corp filed Critical IHI Corp
Priority to JP2008333709A priority Critical patent/JP2010156214A/en
Publication of JP2010156214A publication Critical patent/JP2010156214A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/1045—Details of supply of the liquid to the bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Supercharger (AREA)
  • Sliding-Contact Bearings (AREA)
  • Support Of The Bearing (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary machine bearing structure for effectively suppressing the self-exciting vibration of a rotating shaft. <P>SOLUTION: In the rotary machine bearing structure, a compressor side oil-feeding opening 14 is arranged in a position under a compressor side floating bush bearing 12. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、回転機械の軸受構造に関する。   The present invention relates to a bearing structure for a rotary machine.

従来、過給機などの高速回転機械で用いられている軸受構造として、浮動ブッシュ型のすべり軸受け（浮動ブッシュ軸受）を備えたものが知られている（例えば下記特許文献１〜４を参照）。   2. Description of the Related Art Conventionally, as a bearing structure used in a high-speed rotating machine such as a supercharger, a structure having a floating bush type sliding bearing (floating bush bearing) is known (for example, see Patent Documents 1 to 4 below). .

浮動ブッシュ軸受を備えた従来の軸受構造の例を図２に示す。図２の軸受構造において、図２において、回転軸３０の両端には、タービンインペラ３１と、コンプレッサインペラ３２がそれぞれ連結されている。回転軸３０は、ハウジング３３に設けられた円筒穴３４内に配置されたタービン側浮動ブッシュ軸受３９及びコンプレッサ側浮動ブッシュ軸受４０によって回転自在に支承されている。   An example of a conventional bearing structure having a floating bush bearing is shown in FIG. In the bearing structure of FIG. 2, a turbine impeller 31 and a compressor impeller 32 are connected to both ends of the rotating shaft 30 in FIG. 2, respectively. The rotary shaft 30 is rotatably supported by a turbine-side floating bush bearing 39 and a compressor-side floating bush bearing 40 that are disposed in a cylindrical hole 34 provided in the housing 33.

ハウジング３３の円筒穴３４の内面には、タービン側浮動ブッシュ軸受３９に潤滑油を供給するためのタービン側給油口３６と、コンプレッサ側浮動ブッシュ軸受４０に潤滑油を供給するためのコンプレッサ側給油口３７とが、各浮動ブッシュ軸受３９、４０の上方位置に設けられている。各給油口３６、３７は、ハウジング３３に設けられたオイル供給路３５と接続されており、オイル供給源（図示せず）からオイル供給路３６及び各給油口３６、３７を介して各浮動ブッシュ軸受３９、４０に潤滑油３８が供給されるようになっている。   A turbine side oil supply port 36 for supplying lubricating oil to the turbine side floating bush bearing 39 and a compressor side oil supply port for supplying lubricating oil to the compressor side floating bush bearing 40 are formed on the inner surface of the cylindrical hole 34 of the housing 33. 37 is provided above the floating bush bearings 39, 40. The oil supply ports 36 and 37 are connected to an oil supply path 35 provided in the housing 33, and each floating bush is connected from an oil supply source (not shown) via the oil supply path 36 and the oil supply ports 36 and 37. Lubricating oil 38 is supplied to the bearings 39 and 40.

各浮動ブッシュ軸受３９、４０に潤滑油３８が供給されると、軸受３９、４０の内周面及び外周面に潤滑油３８による油膜が形成されるので、回転軸３０は各浮動ブッシュ軸受３９、４０上に浮いた状態で回転する。また、回転軸３０の回転により、油膜を介して回転力が各浮動ブッシュ軸受３９、４０に伝わることで、各浮動ブッシュ軸受３９、４０が回転軸３０に連れられて回転する。   When the lubricating oil 38 is supplied to the floating bush bearings 39, 40, an oil film is formed by the lubricating oil 38 on the inner and outer peripheral surfaces of the bearings 39, 40. Rotates while floating on 40. Further, when the rotary shaft 30 rotates, the rotational force is transmitted to the floating bush bearings 39 and 40 via the oil film, so that the floating bush bearings 39 and 40 are rotated by the rotary shaft 30.

従来の浮動ブッシュ軸受の課題として、回転軸の自励振動が挙げられる。この自励振動は、回転軸と軸受との隙間にある油膜の挙動や軸心の振れ等に応じて生じ、騒音、軸受損傷の原因となっている。   A problem with conventional floating bush bearings is the self-excited vibration of the rotating shaft. This self-excited vibration is generated according to the behavior of the oil film in the gap between the rotating shaft and the bearing, the shaft center shake, etc., and causes noise and bearing damage.

特開２００２−１３８８４６号公報JP 2002-138846 A 特開２００６−１７７４８７号公報JP 2006-177487 A 特開２００２−２１３２４８号公報JP 2002-213248 A 特開平１１−３３６７４４号公報JP 11-336744 A

しかしながら、従来の回転機械の軸受構造では、自励振動を充分に抑えることは難しかった。   However, it has been difficult to sufficiently suppress the self-excited vibration in the conventional rotating machine bearing structure.

本発明は、上記の問題に鑑みてなされたものであり、回転軸の自励振動を効果的に抑えることができる回転機械の軸受構造を提供することを課題とする。   This invention is made in view of said problem, and makes it a subject to provide the bearing structure of the rotary machine which can suppress the self-excited vibration of a rotating shaft effectively.

上記の問題を解決するため、本発明の回転機械の軸受構造は、以下の技術的手段を採用する。   In order to solve the above problem, the following technical means is adopted in the bearing structure of the rotary machine of the present invention.

（１）本発明は、回転機械において回転軸心がほぼ水平な回転体の回転軸と該回転軸を囲む静止部との間に、前記回転軸心方向に離間して配置された第１浮動ブッシュ軸受及び第２浮動ブッシュ軸受と、前記静止部において前記第１浮動ブッシュ軸受に対向する位置に設けられ該第１浮動ブッシュ軸受に潤滑油を供給するための第１給油口と、前記静止部において前記第２浮動ブッシュ軸受に対向する位置に設けられ該第２浮動ブッシュ軸受に潤滑油を供給するための第２給油口と、を備え、前記回転体の重心が前記第１浮動ブッシュ軸受を基準として前記第２浮動ブッシュ軸受とは反対側の位置にある、回転機械の軸受構造において、前記第１給油口は前記第１浮動ブッシュ軸受の上方位置に配置され、前記第２給油口は前記第２浮動ブッシュ軸受の下方位置に配置されている、ことを特徴とする回転機械の軸受構造。 (1) In the rotary machine, the first floating unit is disposed so as to be spaced apart in the direction of the rotation axis between the rotation axis of the rotating body whose rotation axis is substantially horizontal and the stationary portion surrounding the rotation axis. A bush bearing and a second floating bush bearing; a first oil supply port provided at a position facing the first floating bush bearing in the stationary portion; and supplying the lubricating oil to the first floating bush bearing; and the stationary portion And a second oil supply port provided at a position facing the second floating bush bearing for supplying lubricating oil to the second floating bush bearing, and the center of gravity of the rotating body includes the first floating bush bearing. In the bearing structure of the rotating machine, which is at a position opposite to the second floating bush bearing as a reference, the first oil supply port is disposed above the first floating bush bearing, and the second oil supply port is Second floating book Bearing structure of a rotary machine which is disposed at a lower position of the Interview bearing, that said.

（２）また、上記の回転機械の軸受構造において、前記回転体は、前記回転軸と、該回転軸の一端に連結されたタービンインペラと、前記回転軸の他端に連結されたコンプレッサインペラとからなり、前記第１浮動ブッシュ軸受は、前記タービンインペラ側に配置されたタービン側浮動ブッシュ軸受であり、前記第２浮動ブッシュ軸受は、前記コンプレッサインペラ側に配置されたコンプレッサ側浮動ブッシュ軸受である。 (2) In the bearing structure of the rotating machine, the rotating body includes the rotating shaft, a turbine impeller connected to one end of the rotating shaft, and a compressor impeller connected to the other end of the rotating shaft. The first floating bush bearing is a turbine side floating bush bearing disposed on the turbine impeller side, and the second floating bush bearing is a compressor side floating bush bearing disposed on the compressor impeller side. .

回転体の重心が第１浮動ブッシュ軸受（タービン側浮動ブッシュ軸受）を基準として第２浮動ブッシュ軸受（コンプレッサ側浮動ブッシュ軸受）とは反対側の位置にある場合、
回転軸による第２浮動ブッシュ軸受の内周部に作用する荷重は鉛直上向きになる。従来の軸受構造では、第２給油口が第２浮動ブッシュ軸受の上方位置に設けられていたため、給油圧力による第２浮動ブッシュ軸受内周部に作用する荷重は、鉛直下向きとなり、回転軸による第２浮動ブッシュ軸受内周部に鉛直上向きに作用する荷重と反対方向となる。このため、第２浮動ブッシュ軸受の内周部に全体として作用する荷重が小さくなり、第２浮動ブッシュ軸受の内周面及び外周面の油膜において負荷能力を生み出す動圧が十分に発生せず、自励振動が生じやすくなる。 When the center of gravity of the rotating body is at a position opposite to the second floating bush bearing (compressor side floating bush bearing) with respect to the first floating bush bearing (turbine side floating bush bearing),
The load acting on the inner peripheral portion of the second floating bush bearing by the rotating shaft is vertically upward. In the conventional bearing structure, since the second oil supply port is provided at the upper position of the second floating bush bearing, the load acting on the inner periphery of the second floating bush bearing due to the oil supply pressure is vertically downward, and the second oil supply port is rotated by the rotating shaft. 2 The direction is opposite to the load acting vertically upward on the inner periphery of the floating bush bearing. For this reason, the load acting on the inner peripheral portion of the second floating bush bearing as a whole is reduced, and the dynamic pressure that generates load capacity is not sufficiently generated in the oil film on the inner peripheral surface and the outer peripheral surface of the second floating bush bearing, Self-excited vibration is likely to occur.

そこで、本発明では、第２給油口を、第２浮動ブッシュ軸受（コンプレッサ側浮動ブッシュ軸受）の下方位置に配置するものとした。この構成により、給油圧力による第２浮動ブッシュ軸受内周部に作用する荷重は鉛直上向きになる。この荷重方向は、回転軸による第２浮動ブッシュ軸受の内周部に作用する荷重の方向と同じであるため、第２浮動ブッシュ軸受の内周部に全体として作用する荷重を大きくすることができる。これにより、第２浮動ブッシュ軸受の内周面及び外周面の油膜において負荷能力を生み出す動圧が十分に発生するので、自励振動を効果的に抑制し、騒音、軸受損傷を低減できる。   Therefore, in the present invention, the second oil supply port is disposed below the second floating bush bearing (compressor side floating bush bearing). With this configuration, the load acting on the inner peripheral portion of the second floating bush bearing due to the oil supply pressure is vertically upward. Since this load direction is the same as the direction of the load acting on the inner peripheral portion of the second floating bush bearing by the rotating shaft, the load acting as a whole on the inner peripheral portion of the second floating bush bearing can be increased. . As a result, sufficient dynamic pressure for generating load capacity is generated in the oil film on the inner peripheral surface and the outer peripheral surface of the second floating bush bearing, so that self-excited vibration can be effectively suppressed and noise and bearing damage can be reduced.

以下、本発明の好ましい実施形態を添付図面に基づいて詳細に説明する。   Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

図１は、本発明の軸受構造を備えた回転機械の一例としての過給機１の概略構成を示す断面図である。以下では、本発明の軸受構造を過給機１に適用した例を説明するが、本発明はこれに限られず、過給機１以外の回転機械においても同様に適用することが可能である。   FIG. 1 is a cross-sectional view showing a schematic configuration of a supercharger 1 as an example of a rotary machine having a bearing structure of the present invention. Below, although the example which applied the bearing structure of this invention to the supercharger 1 is demonstrated, this invention is not restricted to this, It is possible to apply similarly also in rotary machines other than the supercharger 1. FIG.

図１において、過給機１は、回転体である過給機ロータ２を有する。この過給機ロータ２は、回転軸５と、回転軸５の一端に連結されたタービンインペラ３と、回転軸５の他端に連結されたコンプレッサインペラ４とからなる。図１に示すように、回転軸５の回転軸心５ａは、従来の過給器の回転軸の軸心と同様に、ほぼ水平に設定されている。   In FIG. 1, a supercharger 1 has a supercharger rotor 2 that is a rotating body. The supercharger rotor 2 includes a rotating shaft 5, a turbine impeller 3 connected to one end of the rotating shaft 5, and a compressor impeller 4 connected to the other end of the rotating shaft 5. As shown in FIG. 1, the rotation axis 5 a of the rotation shaft 5 is set substantially horizontal, like the rotation axis of the conventional supercharger.

タービンインペラ３は図示しないタービンハウジング内に収容されており、コンプレッサインペラ４は図示しないコンプレッサハウジング内に収容されている。タービンハウジング内に内燃機関からの排気ガスが導入されると、タービンインペラ３が回転させられ、その回転駆動力が回転軸５を介してコンプレッサインペラ４に伝えられることでコンプレッサインペラ４が回転させられ、導入された空気がコンプレッサインペラ４によって圧縮されて内燃機関に供給されるようになっている。   The turbine impeller 3 is housed in a turbine housing (not shown), and the compressor impeller 4 is housed in a compressor housing (not shown). When the exhaust gas from the internal combustion engine is introduced into the turbine housing, the turbine impeller 3 is rotated, and the rotational driving force is transmitted to the compressor impeller 4 through the rotating shaft 5, whereby the compressor impeller 4 is rotated. The introduced air is compressed by the compressor impeller 4 and supplied to the internal combustion engine.

回転軸５は、静止部であるハウジング１０に設けられた軸受支承用の円筒穴６内に配置されている。ハウジング１０と回転軸５との間に、回転軸心５ａ方向に離間して、第１浮動ブッシュ軸受であるタービン側浮動ブッシュ軸受１１と、第２浮動ブッシュ軸受であるコンプレッサ側浮動ブッシュ軸受１２が配置されている。   The rotating shaft 5 is disposed in a cylindrical hole 6 for bearing support provided in a housing 10 which is a stationary part. A turbine side floating bush bearing 11 as a first floating bush bearing and a compressor side floating bush bearing 12 as a second floating bush bearing are separated between the housing 10 and the rotation shaft 5 in the direction of the rotation axis 5a. Has been placed.

各浮動ブッシュ軸受１１、１２はリング状に形成されている。また、各浮動ブッシュ軸受１１、１２には、浮動ブッシュ軸受１１、１２をその半径方向に貫通する貫通孔１１ａ、１２ａが周方向に離間して複数設けられている。各浮動ブッシュ軸受１１、１２の外周面と円筒穴６の内周面との間、及び、各浮動ブッシュ軸受１１、１２の内周面と回転軸５の外周面との間には、それぞれ僅かな隙間が形成されるようになっている。   Each floating bush bearing 11, 12 is formed in a ring shape. Each of the floating bush bearings 11 and 12 is provided with a plurality of through-holes 11a and 12a that penetrate the floating bush bearings 11 and 12 in the radial direction and are spaced apart in the circumferential direction. Between the outer peripheral surface of each floating bush bearing 11, 12 and the inner peripheral surface of the cylindrical hole 6, and between the inner peripheral surface of each floating bush bearing 11, 12 and the outer peripheral surface of the rotating shaft 5, a little Gaps are formed.

図１において、各浮動ブッシュ軸受１１、１２の軸方向の移動を制限するための手段は、図示されていないが、例えば、各浮動ブッシュ軸受１１、１２に隣接した位置にリング状の止め部材を配置したり、浮動ブッシュ軸受１１、１２間に中間スリーブを配置したりするなど、公知の手段で各浮動ブッシュ軸受１１、１２の軸方向の移動を制限してよい。   In FIG. 1, means for restricting the axial movement of the floating bush bearings 11 and 12 is not shown. For example, a ring-shaped stop member is provided at a position adjacent to the floating bush bearings 11 and 12. The movement of the floating bush bearings 11 and 12 in the axial direction may be limited by a known means such as disposing them or arranging an intermediate sleeve between the floating bush bearings 11 and 12.

ハウジング５に形成された円筒穴６の内面には、タービン側浮動ブッシュ軸受１１に潤滑油９を供給するための第１給油口であるタービン側給油口１３と、コンプレッサ側浮動ブッシュ軸受１２に潤滑油９を供給するための第２給油口であるコンプレッサ側給油口１４とが設けられている。   The inner surface of the cylindrical hole 6 formed in the housing 5 lubricates the turbine side oil supply port 13 which is a first oil supply port for supplying the lubricating oil 9 to the turbine side floating bush bearing 11 and the compressor side floating bush bearing 12. The compressor side oil supply port 14 which is the 2nd oil supply port for supplying the oil 9 is provided.

タービン側給油口１３は、円筒穴６の内面においてタービン側浮動ブッシュ軸受１１に対向する位置に設けられ、タービン側浮動ブッシュ軸受１１の上方位置に配置されている。コンプレッサ側給油口１４は、円筒穴６の内面においてコンプレッサ側浮動ブッシュ軸受１２に対向する位置に設けられ、コンプレッサ側浮動ブッシュ軸受１２の下方位置に配置されている。   The turbine-side oil supply port 13 is provided at a position facing the turbine-side floating bush bearing 11 on the inner surface of the cylindrical hole 6, and is disposed above the turbine-side floating bush bearing 11. The compressor side oil supply port 14 is provided at a position facing the compressor side floating bush bearing 12 on the inner surface of the cylindrical hole 6, and is disposed at a position below the compressor side floating bush bearing 12.

各給油口１３、１４は、ハウジング１０に設けられたオイル供給路７と接続されており、オイル供給源（図示せず）からオイル供給路７及び各給油口１３、１４を介して各浮動ブッシュ軸受１１、１２に潤滑油９が供給されるようになっている。各浮動ブッシュを通過した潤滑油９は、オイル排出路８から排出されるようになっている。   Each oil supply port 13, 14 is connected to an oil supply path 7 provided in the housing 10, and each floating bush from an oil supply source (not shown) via the oil supply path 7 and each oil supply port 13, 14. Lubricating oil 9 is supplied to the bearings 11 and 12. The lubricating oil 9 that has passed through each floating bush is discharged from the oil discharge path 8.

上記の構成において、各浮動ブッシュ軸受１１、１２に潤滑油９が供給されると、潤滑油９が貫通孔１１ａ、１２ａを通るなどして各浮動ブッシュ軸受１１、１２の内周面及び外周面の両方に供給され、両面において潤滑油９による油膜が形成されるので、回転軸５は浮動ブッシュ軸受１１、１２上に浮いた状態で回転する。また、回転軸５の回転により、油膜を介して回転力が各浮動ブッシュ軸受１１、１２に伝わることで、各浮動ブッシュ軸受１１、１２が回転軸５に連れられて回転する。   In the above configuration, when the lubricating oil 9 is supplied to the floating bush bearings 11 and 12, the lubricating oil 9 passes through the through holes 11a and 12a so that the inner and outer peripheral surfaces of the floating bush bearings 11 and 12 are provided. Since the oil film is formed by the lubricating oil 9 on both sides, the rotating shaft 5 rotates while floating on the floating bush bearings 11 and 12. Further, the rotational force is transmitted to the floating bush bearings 11 and 12 through the oil film by the rotation of the rotary shaft 5, whereby the floating bush bearings 11 and 12 are rotated by the rotary shaft 5.

ここで、一般に、タービンインペラ３には耐熱性が要求されることから鉄系の材質が使用され、コンプレッサインペラ４にはアルミニウム合金等の材質（鉄系の材質に比べ比重が小さい）が使用されることが多い。このため、設計によっては回転体である過給機ロータ２の重心Ｇが、タービン側浮動ブッシュ軸受１１を基準としてコンプレッサ側浮動ブッシュ軸受１２とは反対側の位置、すなわち、タービン側浮動ブッシュ軸受１１よりもタービンインペラ３側の位置になることがある。図１の過給機ロータ２においても、過給機ロータ２の重心Ｇはタービン側浮動ブッシュ軸受１１よりもタービンインペラ３側の位置となっているものとする。   In general, the turbine impeller 3 is made of an iron-based material because heat resistance is required, and the compressor impeller 4 is made of a material such as an aluminum alloy (specific gravity is smaller than that of an iron-based material). Often. For this reason, the center of gravity G of the supercharger rotor 2 which is a rotating body depending on the design is located on the opposite side of the compressor side floating bush bearing 12 with respect to the turbine side floating bush bearing 11, that is, the turbine side floating bush bearing 11. The position may be closer to the turbine impeller 3 side. Also in the supercharger rotor 2 of FIG. 1, it is assumed that the center of gravity G of the supercharger rotor 2 is located on the turbine impeller 3 side of the turbine side floating bush bearing 11.

本発明者による研究の結果、従来の軸受構造では、過給機ロータ２の重心Ｇがタービン側浮動ブッシュ軸受１１よりもタービンインペラ３側の位置となっている場合、以下に述べるように、自励振動が生じやすくなることが明らかとなった。   As a result of research by the present inventor, in the conventional bearing structure, when the center of gravity G of the turbocharger rotor 2 is located on the turbine impeller 3 side of the turbine side floating bush bearing 11, as described below, It became clear that excitation vibration is likely to occur.

従来の軸受構造の場合、図２を参照して説明したように、コンプレッサ側給油口３７はコンプレッサ側浮動ブッシュ軸受４０の上方位置に設けられているため、給油圧力によるコンプレッサ側浮動ブッシュ軸受４０内周部に作用する荷重は、鉛直下向きとなる。   In the case of the conventional bearing structure, as described with reference to FIG. 2, the compressor-side oil supply port 37 is provided above the compressor-side floating bush bearing 40. The load acting on the periphery is vertically downward.

ところが、図２に示すように、過給機ロータの重心Ｇがタービン側浮動ブッシュ軸受１１よりもタービンインペラ３１側の位置となっている場合、回転軸３０によるコンプレッサ側浮動ブッシュ軸受４０の内周部に作用する荷重は鉛直上向きとなり、給油圧力による荷重方向と反対方向となる。このため、コンプレッサ側浮動ブッシュ軸受４０の内周部に全体として作用する荷重が小さくなり、コンプレッサ側浮動ブッシュ軸受４０の内周面及び外周面の油膜において負荷能力を生み出す動圧が十分に発生せず、自励振動が生じやすくなる。   However, as shown in FIG. 2, when the center of gravity G of the turbocharger rotor is located on the turbine impeller 31 side of the turbine side floating bush bearing 11, the inner periphery of the compressor side floating bush bearing 40 by the rotating shaft 30. The load acting on the part is vertically upward, and is opposite to the load direction due to the oil supply pressure. For this reason, the load acting as a whole on the inner peripheral portion of the compressor side floating bush bearing 40 is reduced, and a sufficient dynamic pressure for generating load capacity is generated in the oil film on the inner peripheral surface and the outer peripheral surface of the compressor side floating bush bearing 40. Therefore, self-excited vibration is likely to occur.

そこで、本発明では、図１に示すように、コンプレッサ側給油口１４を、コンプレッサ側浮動ブッシュ軸受１２の下方位置に配置する構成とした。この構成により、給油圧力によるコンプレッサ側浮動ブッシュ軸受１２内周部に作用する荷重は鉛直上向きになる。この荷重方向は、回転軸５によるコンプレッサ側浮動ブッシュ軸受１２の内周部に作用する荷重の方向と同じであるため、コンプレッサ側浮動ブッシュ軸受１２の内周部に全体として作用する荷重を大きくすることができる。これにより、コンプレッサ側浮動ブッシュ軸受１２の内周面及び外周面の油膜において負荷能力を生み出す動圧が十分に発生するので、自励振動を効果的に抑制し、騒音、軸受損傷を低減できる。   Therefore, in the present invention, as shown in FIG. 1, the compressor-side oil supply port 14 is arranged below the compressor-side floating bush bearing 12. With this configuration, the load acting on the inner peripheral portion of the compressor side floating bush bearing 12 due to the oil supply pressure is vertically upward. This load direction is the same as the direction of the load acting on the inner peripheral portion of the compressor-side floating bush bearing 12 by the rotating shaft 5, so that the load acting on the inner peripheral portion of the compressor-side floating bush bearing 12 as a whole is increased. be able to. As a result, sufficient dynamic pressure is generated in the oil film on the inner and outer peripheral surfaces of the compressor-side floating bush bearing 12 to generate load capacity, so that self-excited vibration can be effectively suppressed, and noise and bearing damage can be reduced.

また、従来の軸受構造では、回転軸３０によるコンプレッサ側浮動ブッシュ軸受４０の内周部に作用する鉛直上向きの力によって、コンプレッサ側浮動ブッシュ軸受４０が上方に持ち上げられることで、コンプレッサ側給油口３７が塞がれ、給油が阻害されるという事態も起こりかねない。これに対し、本発明の軸受構造では、コンプレッサ側給油口１４がコンプレッサ側浮動ブッシュ軸受１２の下方位置に配置されているので、そのような事態の発生を未然に防止できる利点もある。   Further, in the conventional bearing structure, the compressor-side floating bush bearing 40 is lifted upward by the vertically upward force acting on the inner peripheral portion of the compressor-side floating bush bearing 40 by the rotating shaft 30, so that the compressor-side oil supply port 37. May be blocked and refueling will be hindered. On the other hand, in the bearing structure of the present invention, since the compressor-side oil supply port 14 is disposed below the compressor-side floating bush bearing 12, there is an advantage that such a situation can be prevented in advance.

なお、上記において、本発明の実施形態について説明を行ったが、上記に開示された本発明の実施の形態は、あくまで例示であって、本発明の範囲はこれら発明の実施の形態に限定されない。本発明の範囲は、特許請求の範囲の記載によって示され、さらに特許請求の範囲の記載と均等の意味および範囲内でのすべての変更を含むものである。   Although the embodiments of the present invention have been described above, the embodiments of the present invention disclosed above are merely examples, and the scope of the present invention is not limited to these embodiments. . The scope of the present invention is indicated by the description of the scope of claims, and further includes meanings equivalent to the description of the scope of claims and all modifications within the scope.

本発明の軸受構造を備えた回転機械の一例としての過給機の概略構成を示す断面図である。It is sectional drawing which shows schematic structure of the supercharger as an example of the rotary machine provided with the bearing structure of this invention. 浮動ブッシュ軸受を備えた従来の軸受構造の例を示す図である。It is a figure which shows the example of the conventional bearing structure provided with the floating bush bearing.

符号の説明Explanation of symbols

１ 過給機（回転機械）
２ 過給機ロータ（回転体）
３ タービンインペラ
４ コンプレッサインペラ
５ 回転軸
５ａ 回転軸心
６ 円筒穴
７ オイル供給路
８ オイル排出路
９ 潤滑油
１０ ハウジング（静止部）
１１ タービン側浮動ブッシュ軸受
１１ａ 貫通孔
１２ コンプレッサ側浮動ブッシュ軸受
１２ａ 貫通孔
１３ タービン側給油口
１４ コンプレッサ側給油口
Ｇ 重心 1 Supercharger (Rotating machine)
2 Supercharger rotor (rotating body)
3 Turbine impeller 4 Compressor impeller 5 Rotating shaft 5a Rotating shaft center 6 Cylindrical hole 7 Oil supply path 8 Oil discharge path 9 Lubricating oil 10 Housing (stationary part)
11 Turbine side floating bush bearing 11a Through hole 12 Compressor side floating bush bearing 12a Through hole 13 Turbine side oil supply port 14 Compressor side oil supply port G Center of gravity

Claims (2)

回転機械において回転軸心がほぼ水平な回転体の回転軸と該回転軸を囲む静止部との間に、前記回転軸心方向に離間して配置された第１浮動ブッシュ軸受及び第２浮動ブッシュ軸受と、
前記静止部において前記第１浮動ブッシュ軸受に対向する位置に設けられ該第１浮動ブッシュ軸受に潤滑油を供給するための第１給油口と、
前記静止部において前記第２浮動ブッシュ軸受に対向する位置に設けられ該第２浮動ブッシュ軸受に潤滑油を供給するための第２給油口と、を備え、
前記回転体の重心が前記第１浮動ブッシュ軸受を基準として前記第２浮動ブッシュ軸受とは反対側の位置にある、回転機械の軸受構造において、
前記第１給油口は前記第１浮動ブッシュ軸受の上方位置に配置され、前記第２給油口は前記第２浮動ブッシュ軸受の下方位置に配置されている、ことを特徴とする回転機械の軸受構造。 A first floating bush bearing and a second floating bush that are spaced apart in the direction of the rotation axis between a rotation axis of a rotating body whose rotation axis is substantially horizontal in the rotating machine and a stationary part surrounding the rotation axis. A bearing,
A first oil supply port provided at a position facing the first floating bush bearing in the stationary portion for supplying lubricating oil to the first floating bush bearing;
A second oil supply port provided at a position facing the second floating bush bearing in the stationary portion and for supplying lubricating oil to the second floating bush bearing;
In the bearing structure of the rotating machine, the center of gravity of the rotating body is at a position opposite to the second floating bush bearing with respect to the first floating bush bearing.
A bearing structure for a rotary machine, wherein the first oil supply port is disposed at an upper position of the first floating bush bearing, and the second oil supply port is disposed at a lower position of the second floating bush bearing. . 前記回転体は、前記回転軸と、該回転軸の一端に連結されたタービンインペラと、前記回転軸の他端に連結されたコンプレッサインペラとからなり、
前記第１浮動ブッシュ軸受は、前記タービンインペラ側に配置されたタービン側浮動ブッシュ軸受であり、
前記第２浮動ブッシュ軸受は、前記コンプレッサインペラ側に配置されたコンプレッサ側浮動ブッシュ軸受である、請求項１記載の回転機械の軸受構造。 The rotating body includes the rotating shaft, a turbine impeller connected to one end of the rotating shaft, and a compressor impeller connected to the other end of the rotating shaft,
The first floating bush bearing is a turbine side floating bush bearing disposed on the turbine impeller side,
The bearing structure for a rotary machine according to claim 1, wherein the second floating bush bearing is a compressor side floating bush bearing disposed on the compressor impeller side.
JP2008333709A 2008-12-26 2008-12-26 Rotary machine bearing structure Pending JP2010156214A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2008333709A JP2010156214A (en) 2008-12-26 2008-12-26 Rotary machine bearing structure

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2008333709A JP2010156214A (en) 2008-12-26 2008-12-26 Rotary machine bearing structure

Publications (1)

Publication Number Publication Date
JP2010156214A true JP2010156214A (en) 2010-07-15

Family

ID=42574310

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2008333709A Pending JP2010156214A (en) 2008-12-26 2008-12-26 Rotary machine bearing structure

Country Status (1)

Country Link
JP (1) JP2010156214A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104989461A (en) * 2015-07-13 2015-10-21 湖南天雁机械有限责任公司 Full-floating bearing turbocharger rotor system
US10465747B2 (en) 2015-07-21 2019-11-05 Ihi Corporation Bearing structure and turbocharger

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004324460A (en) * 2003-04-22 2004-11-18 Hitachi Ltd Turbomachine
JP2008128042A (en) * 2006-11-17 2008-06-05 Toyota Motor Corp Bearing structure of turbocharger
JP2008267463A (en) * 2007-04-18 2008-11-06 Toyota Motor Corp Floating bearing structure

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004324460A (en) * 2003-04-22 2004-11-18 Hitachi Ltd Turbomachine
JP2008128042A (en) * 2006-11-17 2008-06-05 Toyota Motor Corp Bearing structure of turbocharger
JP2008267463A (en) * 2007-04-18 2008-11-06 Toyota Motor Corp Floating bearing structure

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104989461A (en) * 2015-07-13 2015-10-21 湖南天雁机械有限责任公司 Full-floating bearing turbocharger rotor system
US10465747B2 (en) 2015-07-21 2019-11-05 Ihi Corporation Bearing structure and turbocharger

Similar Documents

Publication Publication Date Title
US9599119B2 (en) Bearing device for turbocharger
WO2007148390A1 (en) Bearing structure for rotating machine, rotating machine, method of producing bearing structure, and method of producing rotating machine
KR20150074036A (en) Fluid film hydrodynamic flexure pivot tilting pad semi-floating ring journal bearing with compliant dampers
JP2007071165A (en) Bearing structure for electric supercharger
JP2013011251A5 (en)
JP2015516054A (en) Axial bearing device
JP2007046642A (en) Supercharger and fully floating bearing
JP2011153668A (en) Bearing device
US20140147066A1 (en) Bearing arrangement for a shaft of a turbine wheel
JP2017186964A (en) Bearing mechanism for turbo charger
JP2017501340A (en) Bearing device for exhaust gas turbocharger and exhaust gas turbocharger
JP2010156214A (en) Rotary machine bearing structure
JP2014034879A (en) Supercharger and bearing
JP2009156333A (en) Bearing device of rotary machine
JP2012036855A (en) Turbocharger using rolling bearing
US20180156273A1 (en) Bearing bushing and corresponding charger device
JP5829397B2 (en) Bearing method and apparatus for rotating shaft of turbocharger
WO2017150500A1 (en) Journal bearing and rotary machine
JP6512296B2 (en) Bearing structure and turbocharger
JP4572682B2 (en) Bearing structure of rotating machine, rotating machine, manufacturing method of bearing structure, and manufacturing method of rotating machine
JP4877405B2 (en) Bearing structure of rotating machine, rotating machine, method of manufacturing bearing structure, method of manufacturing rotating machine
JP2009041745A (en) Thrust sliding bearing device
JP5995735B2 (en) Turbocharger bearing structure and turbocharger including the same
JP2008291810A (en) Turbocharger
JP2008215086A (en) Bearing structure of turbocharger

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20111026

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20121001

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20121031

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20130402