JP6346754B2 - Bearing support structure and flywheel housing assembly including the same - Google Patents

Bearing support structure and flywheel housing assembly including the same Download PDF

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JP6346754B2
JP6346754B2 JP2014033409A JP2014033409A JP6346754B2 JP 6346754 B2 JP6346754 B2 JP 6346754B2 JP 2014033409 A JP2014033409 A JP 2014033409A JP 2014033409 A JP2014033409 A JP 2014033409A JP 6346754 B2 JP6346754 B2 JP 6346754B2
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support
sleeve member
outer ring
bearing member
flywheel housing
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JP2015158240A (en
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佐藤　元彦
元彦 佐藤
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Aichi Machine Industry Co Ltd
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Aichi Machine Industry Co Ltd
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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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • 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
    • F16C2202/00—Solid materials defined by their properties
    • F16C2202/20—Thermal properties
    • F16C2202/22—Coefficient of expansion
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Description

本発明は、内輪と、外輪と、内輪および外輪の間に配置される複数の転動部材と、を有する軸受部材を支持部材に支持する軸受部材の支持構造に関する。   The present invention relates to a support structure for a bearing member that supports a bearing member having an inner ring, an outer ring, and a plurality of rolling members disposed between the inner ring and the outer ring.

従来、この種の軸受部材の支持構造としては、軸受部材と同じ鉄系の金属材料から構成されるスリーブを軸受部材の外輪に嵌合し、当該スリーブを変速機ケースにボルトにより固定することにより、スリーブを介して軸受部材を変速機ケースに支持する構造が提案されている（例えば、特許文献１参照）。   Conventionally, as a support structure for this type of bearing member, a sleeve made of the same iron-based metal material as the bearing member is fitted to the outer ring of the bearing member, and the sleeve is fixed to the transmission case with bolts. A structure has been proposed in which a bearing member is supported on a transmission case via a sleeve (see, for example, Patent Document 1).

この構造では、鉄系の金属材料からなるスリーブを用いる構成であるため、高い耐摩耗性をもって軸受部材を半径方向および軸線方向に位置決めでき、高い位置決め性を維持できる。   In this structure, since a sleeve made of an iron-based metal material is used, the bearing member can be positioned in the radial direction and the axial direction with high wear resistance, and high positioning performance can be maintained.

特開２０１１−１７４６１８号公報JP 2011-174618 A

ところで、軸受部材を支持する変速機ケースは、軽量化の観点からアルミニウム合金系の金属材料によって構成されることが多い。上述した軸受部材の支持構造では、変速機ケースがアルミニウム合金系の金属材料によって構成されると、スリーブと変速機ケースとの熱膨張率の違いから不都合が生じてしまう。即ち、使用環境温度が低い場合には、変速機ケースがスリーブを介して軸受部材の外輪を圧縮することによって、軸受部材の回転フリクションが増大してしまう。低温時の変速機ケースの収縮を考慮して、外輪と内輪の間の隙間を大きく設定することも考えられるが、低温時以外では当該隙間が必要以上に大きい構成となるため、軸受部材の耐久性が低下してしまう。   By the way, the transmission case that supports the bearing member is often made of an aluminum alloy metal material from the viewpoint of weight reduction. In the bearing member support structure described above, if the transmission case is made of an aluminum alloy-based metal material, inconvenience arises due to the difference in thermal expansion coefficient between the sleeve and the transmission case. In other words, when the use environment temperature is low, the transmission case compresses the outer ring of the bearing member via the sleeve, so that the rotational friction of the bearing member increases. Considering the shrinkage of the transmission case at low temperatures, it is conceivable to set a large gap between the outer ring and the inner ring. The nature will decline.

本発明は、上記に鑑みてなされたものであり、使用環境温度に依らずに適切な状態で軸受部材を支持可能な軸受部材の支持構造を提供することを目的とする。   The present invention has been made in view of the above, and an object of the present invention is to provide a support structure for a bearing member that can support the bearing member in an appropriate state regardless of the operating environment temperature.

本発明の位置決め構造および位置決め方法は、上述の目的を達成するために以下の手段を採った。   The positioning structure and positioning method of the present invention employ the following means in order to achieve the above-described object.

本発明に係る軸受部材の支持構造の好ましい形態によれば、外輪と、軸部材に嵌合される内輪と、当該外輪および当該内輪の間に配置される複数の転動部材と、を有する軸受部材を、スリーブ部材を介して支持部材に支持する軸受部材の支持構造が構成される。支持部材は、外輪およびスリーブ部材よりも熱膨張率の大きい材料により構成されていると共に、軸部材が挿通される挿通孔を有している。また、挿通孔は、スリーブ部材を介して軸受部材を支持するための支持部を有している。スリーブ部材は、外輪と同じ熱膨張率を有すると共に外輪の外周面に嵌合されるよう構成されており、、スリーブ部材の外周面と支持部の内周面との間に所定の隙間を有した状態で、支持部に取り付け固定される。そして、所定の隙間は、低温時におけるスリーブ部材に対する支持部材の相対熱収縮変形を許容する大きさに設定されている。なお、本発明における「軸受部材」とは、典型的にはボールベアリングがこれに該当するが、ローラベアリングを好適に包含する。また、本発明における「軸受部材と同じ熱膨張率を有する材料」とは、軸受部材を構成する材料と同じ熱膨張率を有する材料、例えば、高炭素クロム軸受鋼の他、軸受部材を構成する材料の熱膨張率に近い熱膨張率を有する材料、例えば、炭素鋼やクロム鋼，鋳鉄，純鉄を含む概念である。さらに、本発明における「相対熱収縮変形」とは、典型的には、スリーブ部材を基準とした支持部材の熱収縮変形として規定される。
According to a preferred embodiment of the support structure for a bearing member according to the present invention, a bearing having an outer ring, an inner ring fitted to the shaft member, and a plurality of rolling members disposed between the outer ring and the inner ring. A support structure for the bearing member that supports the member on the support member via the sleeve member is configured. The support member is made of a material having a larger thermal expansion coefficient than the outer ring and the sleeve member, and has an insertion hole through which the shaft member is inserted. Further, the insertion hole has a support portion for supporting the bearing member via the sleeve member . The sleeve member has the same thermal expansion coefficient as that of the outer ring and is configured to be fitted to the outer peripheral surface of the outer ring, and has a predetermined gap between the outer peripheral surface of the sleeve member and the inner peripheral surface of the support portion. in state, it is fixedly attached to supporting lifting unit. The predetermined gap is set to a size that allows relative thermal contraction deformation of the support member with respect to the sleeve member at a low temperature . The “bearing member” in the present invention typically corresponds to a ball bearing, but preferably includes a roller bearing. Further, the “material having the same thermal expansion coefficient as the bearing member” in the present invention constitutes a bearing member in addition to a material having the same thermal expansion coefficient as the material constituting the bearing member, for example, high carbon chromium bearing steel. It is a concept that includes a material having a thermal expansion coefficient close to that of the material, for example, carbon steel, chromium steel, cast iron, or pure iron. Furthermore, “relative heat shrinkage deformation” in the present invention is typically defined as heat shrinkage deformation of the support member with respect to the sleeve member.

本発明によれば、外輪と同じ熱膨張率を有する材料により構成されたスリーブ部材を外輪に嵌合し、当該スリーブ部材の外周面と取付孔の内周面との間に所定の隙間を有した状態で、当該スリーブ部材を支持部材に取り付け固定することによって、軸受部材を支持部材に支持する構成である。したがって、使用環境温度に応じて、支持部材がスリーブ部材に対して相対熱収縮変形を生じたとしても、当該支持部材の相対熱収縮変形量を所定の隙間によって吸収することができる。これにより、支持部材がスリーブ部材を介して外輪を圧縮することを抑制できる。また、内輪と外輪との間の隙間の変化も生じないため、軸受部材の耐久性が低下することもない。この結果、使用環境温度に依らずに適切な状態で軸受部材を支持することができる。
According to the present invention, a sleeve member made of a material having the same thermal expansion coefficient as that of the outer ring is fitted to the outer ring, and a predetermined gap is provided between the outer peripheral surface of the sleeve member and the inner peripheral surface of the mounting hole. In this state, the bearing member is supported by the support member by attaching and fixing the sleeve member to the support member. Therefore, according to the ambient temperature, the support member even resulted in relative thermal contraction deformation with respect to the sleeve member, it is possible to absorb the relative thermal contraction deformation of the support member by a predetermined gap. Thus, the support member is Ru can be suppressed to compress the outer ring through the sleeve member. In addition, since the gap between the inner ring and the outer ring does not change, the durability of the bearing member does not deteriorate. As a result, the bearing member can be supported in an appropriate state regardless of the use environment temperature.

本発明に係る軸受部材の支持構造の更なる形態によれば、支持部は、挿通孔に段付き状に設けられた凹部として構成されている。
According to a further embodiment of the support structure of the bearing member according to the present invention, the support portion is configured as a recess provided in the stepped shape interpolation hole.

本形態によれば、軸受部材を凹部の底面に突き当てることによって軸部材の軸方向の位置決めを行うことができる。   According to this embodiment, the shaft member can be positioned in the axial direction by abutting the bearing member against the bottom surface of the recess.

本発明に係るフライホイールハウジング組立体の好ましい形態によれば、エンジンのクランクシャフトにフライホイールを介して接続される回転軸と、軸受部材を介して当該回転軸を回転可能に支持するフライホイールハウジングと、を備えるフライホイールハウジング組立体が構成される。そして、上述したいずれかの態様の本発明に係る軸受部材の支持構造によって、軸受部材をフライホイールハウジングに支持するよう構成されている。   According to a preferred embodiment of the flywheel housing assembly of the present invention, a rotary shaft connected to the crankshaft of the engine via a flywheel, and a flywheel housing that rotatably supports the rotary shaft via a bearing member. A flywheel housing assembly comprising: And it is comprised so that a bearing member may be supported by a flywheel housing by the support structure of the bearing member which concerns on this invention of the aspect in any one of the aspect mentioned above.

本発明によれば、上述したいずれかの態様の本発明に係る軸受部材の支持構造によって、軸受部材をフライホイールハウジングに支持する構成であるため、本発明に係る軸受部材の支持構造が奏する効果と同様の効果、例えば、使用環境温度に依らずに適切な状態で軸受部材を支持することができる効果などを奏することができる。また、軸受部材が支持する回転軸等が脱落して車両が走行不能な故障となってしまうことがなく、軸受部材の異音による故障検知も容易となる。   According to the present invention, since the bearing member is supported by the flywheel housing by any one of the above-described bearing member support structures according to the present invention, the effect of the bearing member support structure according to the present invention is achieved. The same effects as the above, for example, the effect that the bearing member can be supported in an appropriate state regardless of the use environment temperature can be obtained. In addition, the rotating shaft or the like supported by the bearing member is not dropped and the vehicle cannot run, and the failure detection due to abnormal noise of the bearing member is facilitated.

本発明によれば、使用環境温度に依らずに適切な状態で軸受部材を支持することができる。   According to the present invention, the bearing member can be supported in an appropriate state regardless of the use environment temperature.

本発明の実施の形態に係る玉軸受け６の支持構造を適用したフライホイールハウジング組立体１の構成の概略を示す構成図である。It is a block diagram which shows the outline of a structure of the flywheel housing assembly 1 to which the support structure of the ball bearing 6 which concerns on embodiment of this invention is applied. 本発明の実施の形態に係る玉軸受け６の支持構造の要部を示す拡大図である。It is an enlarged view which shows the principal part of the support structure of the ball bearing 6 which concerns on embodiment of this invention. 低温時における、スリーブ部材３０における円筒部３２の外周面と、支持部２４における円筒凹部２４ａの内周面との間の隙間の状態を示す説明図である。FIG. 4 is an explanatory diagram showing a state of a gap between an outer peripheral surface of a cylindrical portion 32 in a sleeve member 30 and an inner peripheral surface of a cylindrical recess 24a in a support portion 24 at a low temperature.

次に、本発明を実施するための最良の形態を実施例を用いて説明する。   Next, the best mode for carrying out the present invention will be described using examples.

フライホイールハウジング組立体１は、図１に示すように、フライホイールＦＬに接続されるフライホイールダンパー２と、フライホイールダンパー２を軸支する回転軸４と、回転軸４を２つの玉軸受け６，６を介して回転可能に支持するフライホイールハウジング８と、を備える。フライホイールＦＬは、エンジン（図示せず）のクランクシャフトＣＳの軸端面に取り付け固定されている。   As shown in FIG. 1, the flywheel housing assembly 1 includes a flywheel damper 2 connected to the flywheel FL, a rotating shaft 4 that supports the flywheel damper 2, and the rotating shaft 4 with two ball bearings 6. , 6 and a flywheel housing 8 supported rotatably. The flywheel FL is attached and fixed to the shaft end surface of a crankshaft CS of an engine (not shown).

フライホイールダンパー２は、フライホイールＦＬ側に固定される部材２ａと、回転軸４側に固定される部材２ｂと、当該部材を相対回転可能に連結するスプリングＳＰＲと、から構成されており、エンジン（図示せず）の急激なトルク変動を吸収する。   The flywheel damper 2 includes a member 2a that is fixed to the flywheel FL side, a member 2b that is fixed to the rotating shaft 4 side, and a spring SPR that connects the members so as to be relatively rotatable. Absorbs sudden torque fluctuations (not shown).

回転軸４は、フライホイールダンパー２によってトルク変動が吸収されたエンジンの動力を図示しないプロペラシャフトに伝達する伝達軸として構成されている。   The rotating shaft 4 is configured as a transmission shaft that transmits engine power, in which torque fluctuation is absorbed by the flywheel damper 2, to a propeller shaft (not shown).

フライホイールハウジング８は、フライホイールダンパー２を収容する収容部２２と、回転軸４を支持する支持部２４と、から構成されており、例えば、アルミニウム合金（ＡＣ２Ａ、熱膨張率：２１．５×１０−６／℃）により形成されている。支持部２４には、図１および図２に示すように、回転軸４の軸線ＣＬと同心状に円筒凹部２４ａが形成されている。また、支持部２４における円筒凹部２４ａの径方向外方部には、ボルト孔２４ｂが形成されている。支持部２４は、本発明における「支持部材」に対応し、円筒凹部２４ａは、本発明における「支持部」および「凹部」に対応する実施構成の一例である。 The flywheel housing 8 includes a housing portion 22 that houses the flywheel damper 2 and a support portion 24 that supports the rotating shaft 4. For example, an aluminum alloy (AC2A, thermal expansion coefficient: 21.5 × 10 −6 / ° C.). As shown in FIGS. 1 and 2, a cylindrical recess 24 a is formed in the support portion 24 concentrically with the axis CL of the rotating shaft 4. Further, a bolt hole 24b is formed in a radially outward portion of the cylindrical recess 24a in the support portion 24. The support portion 24 corresponds to the “support member” in the present invention, and the cylindrical recessed portion 24a is an example of an implementation configuration corresponding to the “support portion” and the “recess portion” in the present invention.

玉軸受け６は、単列アンギュラ玉軸受けを背面組み合わせとし、内輪６２および外輪６４をそれぞれ一体形成した複列アンギュラ玉軸受けとして構成されており、ラジアル荷重と両方向（図１および図２における左右方向）のアキシアル荷重を負荷することができる。内輪６２と外輪６４との間には複数の玉６６が配置されている。玉軸受け６の内輪６２および外輪６４は、例えば、クロム鋼（ＳＣｒ４２０Ｈ、熱膨張率：１２．６×１０−６／℃）により形成されている。 The ball bearing 6 is configured as a double-row angular contact ball bearing in which a single-row angular ball bearing is combined with a back surface and an inner ring 62 and an outer ring 64 are integrally formed, and the radial load and both directions (the left-right direction in FIGS. 1 and 2). Axial load can be applied. A plurality of balls 66 are arranged between the inner ring 62 and the outer ring 64. The inner ring 62 and the outer ring 64 of the ball bearing 6 are made of, for example, chrome steel (SCr420H, coefficient of thermal expansion: 12.6 × 10 −6 / ° C.).

また、玉軸受け６は、スリーブ部材３０を介して、フライホイールハウジング８の支持部２４に支持されている。玉軸受け６は、本発明における「軸受部材」に対応し、玉６６は、本発明における「転動部材」に対応する実施構成の一例である。以下、玉軸受け６をフライホイールハウジング８の支持部２４に支持する支持構造について詳細に説明する。   Further, the ball bearing 6 is supported by the support portion 24 of the flywheel housing 8 via the sleeve member 30. The ball bearing 6 corresponds to a “bearing member” in the present invention, and the ball 66 is an example of an implementation configuration corresponding to a “rolling member” in the present invention. Hereinafter, the support structure for supporting the ball bearing 6 on the support portion 24 of the flywheel housing 8 will be described in detail.

スリーブ部材３０は、玉軸受け６の熱膨張率とほぼ同じ熱膨張率を有する材質、例えば、高炭素クロム軸受鋼（ＳＵＪ２、熱膨張率：１２．８×１０−６／℃）により形成されている。即ち、スリーブ部材３０の熱膨張率は、フライホイールハウジング８の熱膨張率よりも小さい。スリーブ部材３０は、図２に示すように、円筒状に形成された円筒部３２と、円筒部３２の軸方向一端部において、当該円筒部３２から径方向外方に張り出すように円筒部３２に一体形成されたフランジ部３４と、を有する。 The sleeve member 30 is formed of a material having substantially the same thermal expansion coefficient as that of the ball bearing 6, for example, a high carbon chromium bearing steel (SUJ2, thermal expansion coefficient: 12.8 × 10 −6 / ° C.). Yes. That is, the thermal expansion coefficient of the sleeve member 30 is smaller than the thermal expansion coefficient of the flywheel housing 8. As shown in FIG. 2, the sleeve member 30 includes a cylindrical portion 32 that is formed in a cylindrical shape, and a cylindrical portion 32 that protrudes radially outward from the cylindrical portion 32 at one axial end portion of the cylindrical portion 32. And a flange portion 34 integrally formed therewith.

円筒部３２の内周面は、玉軸受け６の外輪６４の外周面に対して、所定の締り嵌めで嵌合するように形成されている。円筒部３２の外周面は、フライホイールハウジング８の支持部２４の円筒凹部２４ａの内周面に対して、所定の隙間を有する大きさに形成されている。また、フランジ部３４には、ボルトＢＬＴを挿通可能なボルト挿通孔３４ａが形成されている。   The inner peripheral surface of the cylindrical portion 32 is formed so as to be fitted to the outer peripheral surface of the outer ring 64 of the ball bearing 6 with a predetermined interference fit. The outer peripheral surface of the cylindrical portion 32 is formed in a size having a predetermined gap with respect to the inner peripheral surface of the cylindrical concave portion 24 a of the support portion 24 of the flywheel housing 8. The flange portion 34 is formed with a bolt insertion hole 34a into which the bolt BLT can be inserted.

スリーブ部材３０は、図２に示すように、ボルトＢＬＴによってフランジ部３４がフライホイールハウジング８の支持部２４に締め付けられることによって、支持部２４に取り付け固定される。このとき、スリーブ部材３０の円筒部３２は、円筒部３２の外周面と支持部２４の円筒凹部２４ａの内周面との間に所定の隙間をもって、円筒凹部２４ａ内に挿通された状態となる。   As shown in FIG. 2, the sleeve member 30 is attached and fixed to the support portion 24 by fastening the flange portion 34 to the support portion 24 of the flywheel housing 8 with bolts BLT. At this time, the cylindrical portion 32 of the sleeve member 30 is inserted into the cylindrical concave portion 24a with a predetermined gap between the outer peripheral surface of the cylindrical portion 32 and the inner peripheral surface of the cylindrical concave portion 24a of the support portion 24. .

このとき、玉軸受け６の内輪６２の内周面には、回転軸４が圧入嵌合されている。スリーブ部材３０が支持部２４に取り付け固定されることによって、円筒部３２の外周面と円筒凹部２４ａの内周面との間に所定の隙間を有した状態で、スリーブ部材３０が玉軸受け６を支持部２４に支持する構成は、本発明における「スリーブ部材の外周面と支持部の内周面との間に所定の隙間を有した状態で、スリーブ部材を支持部材に取り付け固定することによって、軸受部材を前記支持部材に支持する」に対応する実施構成の一例である。   At this time, the rotary shaft 4 is press-fitted to the inner peripheral surface of the inner ring 62 of the ball bearing 6. By attaching and fixing the sleeve member 30 to the support portion 24, the sleeve member 30 holds the ball bearing 6 in a state where a predetermined gap is provided between the outer peripheral surface of the cylindrical portion 32 and the inner peripheral surface of the cylindrical concave portion 24a. The structure to be supported by the support portion 24 is the "fixing the sleeve member to the support member in a state having a predetermined gap between the outer peripheral surface of the sleeve member and the inner peripheral surface of the support portion in the present invention. It is an example of the implementation structure corresponding to "a bearing member is supported by the said support member."

なお、スリーブ部材３０の円筒部３２の外周面と、フライホイールハウジング８の支持部２４の円筒凹部２４ａの内周面との間に設定される所定の隙間は、本実施の形態では、支持部２４におけるスリーブ部材３０に対する支持部２４の相対熱収縮変形が大きい場合でも、支持部２４が、スリーブ部材３０を介して外輪６４を圧縮することがない大きさに設定されている。   The predetermined gap set between the outer peripheral surface of the cylindrical portion 32 of the sleeve member 30 and the inner peripheral surface of the cylindrical concave portion 24a of the support portion 24 of the flywheel housing 8 is the support portion in the present embodiment. Even when the relative heat shrinkage deformation of the support portion 24 with respect to the sleeve member 30 at 24 is large, the support portion 24 is set to a size that does not compress the outer ring 64 via the sleeve member 30.

具体的には、当該所定の隙間は、組付け時温度（常温）に対し、フライホイールハウジング組立体１の使用環境温度のうち最も低温（極低温）となったときの、スリーブ部材３０に対する支持部２４の相対熱収縮変形量以上の大きさに設定されている。   Specifically, the predetermined gap is supported to the sleeve member 30 when the flywheel housing assembly 1 is at the lowest temperature (extremely low temperature) in relation to the assembly temperature (normal temperature). The size is set to be equal to or greater than the amount of relative heat shrinkage deformation of the portion 24.

次に、本発明の実施の形態に係る玉軸受け６の支持構造の作用について説明する。図３は、低温時における、スリーブ部材３０の円筒部３２の外周面と、支持部２４の円筒凹部２４ａの内周面との間の隙間の状態を示す説明図である。フライホイール組立体１の使用環境温度が常温、例えば、２０℃の場合には、図２に示すように、スリーブ部材３０の円筒部３２の外周面と、支持部２４の円筒凹部２４ａの内周面との間には、フライホイールハウジング組立体１を組み立てた際に設定された所定の隙間が形成されている。しかしながら、玉軸受け６は、スリーブ部材３０を介して支持部２４に支持される構成であるため、内輪６２および外輪６４と玉６６との間の隙間、即ち、ラジアル隙間は適正に維持されている。これにより、良好な作動性が確保される。   Next, the effect | action of the support structure of the ball bearing 6 which concerns on embodiment of this invention is demonstrated. FIG. 3 is an explanatory diagram showing a state of a gap between the outer peripheral surface of the cylindrical portion 32 of the sleeve member 30 and the inner peripheral surface of the cylindrical concave portion 24a of the support portion 24 at a low temperature. When the operating environment temperature of the flywheel assembly 1 is normal temperature, for example, 20 ° C., as shown in FIG. 2, the outer peripheral surface of the cylindrical portion 32 of the sleeve member 30 and the inner periphery of the cylindrical concave portion 24a of the support portion 24 are used. A predetermined gap that is set when the flywheel housing assembly 1 is assembled is formed between the surfaces. However, since the ball bearing 6 is supported by the support portion 24 via the sleeve member 30, the gap between the inner ring 62 and the outer ring 64 and the ball 66, that is, the radial gap is properly maintained. . Thereby, good operability is ensured.

一方、フライホイール組立体１の使用環境温度が極低温、例えば、―４０℃になると、支持部２４やスリーブ部材３０，玉軸受け６などに熱収縮変形が生じる。本実施の形態では、支持部２４が、スリーブ部材３０および玉軸受け６の外輪６４よりも熱膨張率が大きなアルミニウム合金製であるため、支持部２４はスリーブ部材３０および外輪６４よりも大きな熱収縮変形を生ずる。   On the other hand, when the operating environment temperature of the flywheel assembly 1 is extremely low, for example, −40 ° C., heat shrinkage deformation occurs in the support portion 24, the sleeve member 30, the ball bearing 6, and the like. In the present embodiment, since the support portion 24 is made of an aluminum alloy having a larger coefficient of thermal expansion than the sleeve member 30 and the outer ring 64 of the ball bearing 6, the support portion 24 has a larger thermal contraction than the sleeve member 30 and the outer ring 64. Cause deformation.

しかしながら、フライホイールハウジング組立体１を組み立てた際に設定した所定の隙間が、スリーブ部材３０に対する支持部２４の相対熱収縮変形量以上の大きさに設定されているため、図３に示すように、所定の隙間が当該熱収縮変形を吸収する。これにより、支持部２４が、スリーブ部材３０を介して外輪６４を圧縮することがなく、内輪６２、外輪６４およびスリーブ部材３０は熱膨張率がほぼ同じであるため、ラジアル隙間は適正に維持されるため、玉軸受け６の転がり抵抗が増加することがない。この結果、低温時においても良好な作動性が確保される。   However, since the predetermined gap set when the flywheel housing assembly 1 is assembled is set to a size equal to or greater than the amount of relative heat shrinkage deformation of the support portion 24 with respect to the sleeve member 30, as shown in FIG. The predetermined gap absorbs the heat shrink deformation. As a result, the support portion 24 does not compress the outer ring 64 via the sleeve member 30, and the inner ring 62, the outer ring 64, and the sleeve member 30 have substantially the same coefficient of thermal expansion, so that the radial gap is properly maintained. Therefore, the rolling resistance of the ball bearing 6 does not increase. As a result, good operability is ensured even at low temperatures.

なお、フライホイール組立体１の使用環境温度が高温、例えば、１４０℃になると、支持部２４が、スリーブ部材３０および玉軸受け６よりも大きな膨張変形を生じ、所定の隙間がフライホイールハウジング組立体１を組み立てた際に設定したときよりも大きくなる。しかしながら、玉軸受け６は、スリーブ部材３０を介して支持部２４に支持される構成であり、内輪６２、外輪６４およびスリーブ部材３０は熱膨張率がほぼ同じであるため、ラジアル隙間は適正に維持される。これにより、スリーブ部材３０と外輪６４との間のガタに基づく騒音の発生を防止できる。また、内輪６２と外輪６４との間の隙間の変化が生じないため、玉軸受け６の耐久性が低下することもない。この結果、高温時においても良好な作動性が確保される。  Note that when the operating environment temperature of the flywheel assembly 1 is high, for example, 140 ° C., the support portion 24 undergoes a larger expansion deformation than the sleeve member 30 and the ball bearing 6, and a predetermined gap is formed in the flywheel housing assembly. It becomes larger than when it is set when 1 is assembled. However, since the ball bearing 6 is supported by the support portion 24 via the sleeve member 30 and the inner ring 62, the outer ring 64, and the sleeve member 30 have substantially the same thermal expansion coefficient, the radial gap is properly maintained. Is done. Thereby, generation | occurrence | production of the noise based on the backlash between the sleeve member 30 and the outer ring | wheel 64 can be prevented. Further, since the gap between the inner ring 62 and the outer ring 64 does not change, the durability of the ball bearing 6 does not deteriorate. As a result, good operability is ensured even at high temperatures.

以上説明した本発明の実施の形態に係る玉軸受け６の支持構造によれば、スリーブ部材３０を玉軸受け６の内輪６２および外輪６４とほぼ同じ熱膨張率を有する材質により構成し、スリーブ部材３０の円筒部３２の外周面と、支持部２４の円筒凹部２４ａの内周面との間に所定の隙間を有した状態で、当該スリーブ部材３０が玉軸受け６を支持部２４に支持する構成であるため、フライホイールハウジング組立体１の使用環境温度に依らずに、玉軸受け６のラジアル隙間を適正に維持することができる。これにより、フライホイールハウジング組立体１の使用環境温度に依らずに、玉軸受け６の良好な作動性を確保することができる。   According to the support structure for the ball bearing 6 according to the embodiment of the present invention described above, the sleeve member 30 is made of a material having substantially the same thermal expansion coefficient as the inner ring 62 and the outer ring 64 of the ball bearing 6, and the sleeve member 30. The sleeve member 30 supports the ball bearing 6 on the support portion 24 with a predetermined gap between the outer peripheral surface of the cylindrical portion 32 and the inner peripheral surface of the cylindrical recess 24 a of the support portion 24. Therefore, the radial gap of the ball bearing 6 can be properly maintained regardless of the operating environment temperature of the flywheel housing assembly 1. Thereby, good operability of the ball bearing 6 can be ensured irrespective of the operating environment temperature of the flywheel housing assembly 1.

本実施形態では、所定の隙間は、フライホイールハウジング組立体１の使用環境温度のうち最も低温（極低温）となったときの、スリーブ部材３０に対する支持部２４の相対熱収縮変形量以上の大きさに設定する構成としたが、当該極低温時における相対熱収縮変形量とほぼ等しい設定としたり、小さい設定としても構わない。なお、所定の隙間を常温時に対する極低温時における相対熱収縮変形量よりも小さい設定とした場合でも、所定の隙間によって当該相対熱収縮変形量の一部を吸収することができるため、支持部材２４がスリーブ部材３０を介して外輪６４を圧縮することを抑制できる。   In the present embodiment, the predetermined gap is larger than the relative thermal contraction deformation amount of the support portion 24 with respect to the sleeve member 30 when the flywheel housing assembly 1 is at the lowest temperature (extremely low temperature) of the use environment temperature. However, it may be set to be substantially equal to the relative heat shrinkage deformation amount at the extremely low temperature or may be set to a small setting. Note that even when the predetermined gap is set to be smaller than the relative heat shrinkage deformation amount at an extremely low temperature with respect to the normal temperature, a part of the relative heat shrinkage deformation amount can be absorbed by the predetermined gap, so that the support member It can suppress that 24 compresses the outer ring | wheel 64 via the sleeve member 30. FIG.

本実施形態では、フライホイールハウジング８は、スリーブ部材３０よりも熱膨張率が大きいアルミニウム合金製としたが、フライホイールハウジング８は、スリーブ部材３０と同じ熱膨張率を有する材質で構成するものとしても構わない。フライホイールハウジング８の支持部２４およびスリーブ部材３０の形状によっては、フライホイールハウジング８とスリーブ部材３０とが同じ熱膨張率であっても熱変形量に違いが生じる場合があるため、当該場合に有効なものとなる。   In this embodiment, the flywheel housing 8 is made of an aluminum alloy having a thermal expansion coefficient larger than that of the sleeve member 30. However, the flywheel housing 8 is made of a material having the same thermal expansion coefficient as that of the sleeve member 30. It doesn't matter. Depending on the shape of the support 24 and the sleeve member 30 of the flywheel housing 8, there may be a difference in the amount of thermal deformation even if the flywheel housing 8 and the sleeve member 30 have the same thermal expansion coefficient. It becomes effective.

また、フライホイールハウジング８は、スリーブ部材３０よりも熱膨張率が小さい材質で構成するものとしても構わない。この場合、所定の隙間は、フライホイールハウジング組立体１の使用環境温度のうち最も高温（例えば、１４０℃）となったときのスリーブ部材３０に対する支持部２４の相対熱膨張変形量以上の大きさに設定することが望ましい。   The flywheel housing 8 may be made of a material having a smaller coefficient of thermal expansion than the sleeve member 30. In this case, the predetermined gap is not less than the amount of relative thermal expansion deformation of the support portion 24 with respect to the sleeve member 30 when the flywheel housing assembly 1 reaches the highest temperature (for example, 140 ° C.). It is desirable to set to.

本実施形態では、フライホイールハウジング組立体１における回転軸４を回転可能に支持する玉軸受け６の支持に適用する構成としたが、これに限らず、軸受部材を支持する必要がある装置や機構に適用可能である。   In the present embodiment, the structure is applied to support of the ball bearing 6 that rotatably supports the rotating shaft 4 in the flywheel housing assembly 1, but is not limited to this, and an apparatus or mechanism that needs to support the bearing member It is applicable to.

本実施形態は、本発明を実施するための形態の一例を示すものである。したがって、本発明は、本実施形態の構成に限定されるものではない。   This embodiment shows an example for carrying out the present invention. Therefore, the present invention is not limited to the configuration of the present embodiment.

１ フライホイールハウジング組立体
２ フライホイールダンパー
２ａ フライホイールＦＬ側に固定される部材
２ｂ 回転軸４側に固定される部材
４ 回転軸
６ 玉軸受け
８ フライホイールハウジング
２２ 収容部
２４ 支持部
２４ａ 円筒凹部
２４ｂ ボルト孔
３０ スリーブ部材
３２ 円筒部
３４ フランジ部
３４ａ ボルト挿通孔
６２ 内輪
６４ 外輪
６６ 玉
ＦＬ フライホイール
ＳＰＲ スプリング
ＣＳ クランクシャフト
ＢＬＴ ボルト DESCRIPTION OF SYMBOLS 1 Flywheel housing assembly 2 Flywheel damper 2a The member fixed to the flywheel FL side 2b The member fixed to the rotating shaft 4 side 4 Rotating shaft 6 Ball bearing 8 Flywheel housing 22 Accommodating part 24 Supporting part 24a Cylindrical recessed part 24b Bolt hole 30 Sleeve member 32 Cylindrical part 34 Flange part 34a Bolt insertion hole 62 Inner ring 64 Outer ring 66 Ball FL Flywheel SPR Spring CS Crankshaft BLT Bolt

Claims (3)

外輪と、軸部材に嵌合される内輪と、前記外輪および前記内輪の間に配置される複数の転動部材と、を有する軸受部材を、スリーブ部材を介して支持部材に支持する軸受部材の支持構造であって、
前記支持部材は、前記外輪および前記スリーブ部材よりも熱膨張率の大きい材料により構成されていると共に、前記軸部材が挿通される挿通孔を有しており、
前記挿通孔は、前記スリーブ部材を介して前記軸受部材を支持するための支持部を有しており、
前記スリーブ部材は、前記外輪と同じ熱膨張率を有すると共に前記外輪の外周面に嵌合されるよう構成されており、前記スリーブ部材の外周面と前記支持部の内周面との間に所定の隙間を有した状態で前記支持部に取り付け固定され、
前記所定の隙間は、低温時における前記スリーブ部材に対する前記支持部材の相対熱収縮変形を許容する大きさに設定されている
軸受部材の支持構造。 A bearing member for supporting a bearing member having an outer ring, an inner ring fitted to a shaft member, and a plurality of rolling members disposed between the outer ring and the inner ring on a support member via a sleeve member A support structure,
The support member is made of a material having a larger coefficient of thermal expansion than the outer ring and the sleeve member, and has an insertion hole through which the shaft member is inserted.
The insertion hole has a support part for supporting the bearing member via the sleeve member ,
The sleeve member has the same coefficient of thermal expansion as the outer ring and is configured to be fitted to the outer peripheral surface of the outer ring, and a predetermined gap is provided between the outer peripheral surface of the sleeve member and the inner peripheral surface of the support portion. fixedly attached to the front Symbol support portion in a state of having a gap,
The bearing member support structure , wherein the predetermined gap is set to a size that allows relative heat shrinkage deformation of the support member with respect to the sleeve member at a low temperature . 前記支持部は、前記挿通孔に段付き状に設けられた凹部として構成されている請求項１に記載の軸受部材の支持構造。 The support portion, the support structure of the bearing member according to claim 1 that is configured as a recess provided in the stepped shape to the interpolation hole. エンジンのクランクシャフトにフライホイールを介して接続される回転軸と、軸受部材を介して前記回転軸を回転可能に支持するフライホイールハウジングと、を備えるフライホイールハウジング組立体であって、
前記請求項１または２に記載の軸受部材の支持構造によって、前記軸受部材を前記フライホイールハウジングに支持するよう構成されているフライホイールハウジング組立体。 A flywheel housing assembly comprising: a rotary shaft connected to a crankshaft of an engine via a flywheel; and a flywheel housing rotatably supporting the rotary shaft via a bearing member,
Claim 1 or the support structure of the bearing member according to 2, flywheel housing assembly is configured to support the bearing member to the flywheel housing.
JP2014033409A 2014-02-24 2014-02-24 Bearing support structure and flywheel housing assembly including the same Expired - Fee Related JP6346754B2 (en)

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