JP6334302B2 - Fastening jig and rotating body manufacturing method - Google Patents

Fastening jig and rotating body manufacturing method Download PDF

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JP6334302B2
JP6334302B2 JP2014144113A JP2014144113A JP6334302B2 JP 6334302 B2 JP6334302 B2 JP 6334302B2 JP 2014144113 A JP2014144113 A JP 2014144113A JP 2014144113 A JP2014144113 A JP 2014144113A JP 6334302 B2 JP6334302 B2 JP 6334302B2
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fastening
tool
connector
compressor
fastening jig
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JP2016020013A (en
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圭 百瀬
圭 百瀬
健 中野
健 中野
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IHI Rotating Machinery Engineering Co Ltd
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IHI Rotating Machinery Engineering Co Ltd
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Description

本発明は、締結用治具及び回転体の製造方法に関するものである。   The present invention relates to a fastening jig and a method for manufacturing a rotating body.

従来、遠心圧縮機のコンプレッサ翼車を回転軸に螺着締結させるための締結用治具として、締結用治具を回転させるための工具が掛けられる工具掛部と、工具掛部から延びる複数の棒状突起と、を備える締結用治具が知られている（例えば、特許文献１参照。）。コンプレッサ翼車の先端部に、上記棒状突起に対応する複数の穴が形成されており、この穴に棒状突起を挿入するように締結用治具を設置し、工具掛部に工具を掛け回転させることで、コンプレッサ翼車が回転軸に螺着締結される。   Conventionally, as a fastening jig for screwing and fastening a compressor impeller of a centrifugal compressor to a rotating shaft, a tool hanging part on which a tool for rotating the fastening jig is hung, and a plurality of extending parts from the tool hanging part A fastening jig provided with a rod-like protrusion is known (for example, see Patent Document 1). A plurality of holes corresponding to the rod-shaped protrusions are formed at the tip of the compressor wheel, and a fastening jig is installed so that the rod-shaped protrusions are inserted into the holes, and the tool is rotated on the tool hanging portion. As a result, the compressor wheel is screwed to the rotating shaft.

特許第５０６７２０８号公報Japanese Patent No. 5067208

この種の締結用治具においては、大きな締付トルクが作用した場合にも破壊しないように、更に強度を向上することが望まれる。また、締結用治具を切削加工で容易に製作できることも望まれる。そこで、本発明は、強度を向上すると共に加工性が良い締結用治具及びこれを用いた回転体の製造方法を提供することを目的とする。   In this type of fastening jig, it is desired to further improve the strength so as not to break even when a large fastening torque is applied. It is also desirable that the fastening jig can be easily manufactured by cutting. Therefore, an object of the present invention is to provide a fastening jig that improves strength and has good workability, and a method of manufacturing a rotating body using the same.

本発明の締結用治具は、遠心圧縮機のコンプレッサ翼車と工具との間に介在されてコンプレッサ翼車を遠心圧縮機の回転軸に螺着締結するための締結用治具であって、工具が掛けられ回転される工具掛部と、工具掛部から当該工具掛部の回転軸線方向に延在し、コンプレッサ翼車の先端部に設けられた締付用穴に嵌め込まれる連結子と、を備え、連結子は、回転軸線上で当該回転軸線方向に延在し締付用穴の中央に挿入される中央軸部と、中央軸部から工具掛部の回転径方向に突出すると共に回転軸線方向に延在し、締付用穴が備えるトルク伝達溝に係合する凸条部と、を備え、工具掛部と連結子とが切削加工により一体で形成されており、中央軸部と凸条部との接続部の丸みの曲率半径が、連結子の回転軸線方向の長さの１／８よりも大きい。   The fastening jig of the present invention is a fastening jig that is interposed between a compressor impeller and a tool of a centrifugal compressor and screwed and fastened to the rotary shaft of the centrifugal compressor. A tool hanging portion on which a tool is hung and rotated, a connector extending from the tool hanging portion in the rotation axis direction of the tool hanging portion, and fitted into a fastening hole provided at a tip portion of the compressor impeller, The connector extends on the rotation axis in the direction of the rotation axis and is inserted into the center of the fastening hole, and protrudes from the center shaft portion in the radial direction of the tool hook and rotates. A projecting ridge portion extending in the axial direction and engaging with a torque transmission groove provided in the tightening hole, and the tool hook portion and the connector are integrally formed by cutting, and the central shaft portion The radius of curvature of the connecting portion with the ridge is larger than 1/8 of the length of the connector in the rotation axis direction. .

この締結用治具の連結子は、回転軸線上の中央軸部を備え、当該中央軸部から回転径方向に凸条部が突出した構造をなす。回転軸線上に中央軸部が存在する構造により、連結子の断面積を大きくすることができ、回転に対する連結子の強度を向上することができる。また、中央軸部と凸条部との接続部の丸みの曲率半径が、連結子の回転軸線方向の長さの１／８よりも大きいので、長さの１／４以上の直径をもつ通常のエンドミルを用いて１回で上記接続部の丸みを加工することができる。   The connector of the fastening jig includes a central shaft portion on the rotational axis, and has a structure in which a protruding portion protrudes from the central shaft portion in the rotational radial direction. Due to the structure in which the central shaft portion exists on the rotation axis, the cross-sectional area of the connector can be increased, and the strength of the connector against rotation can be improved. In addition, since the radius of curvature of the roundness of the connecting portion between the central shaft portion and the ridge portion is larger than 1/8 of the length in the rotation axis direction of the connector, it usually has a diameter of 1/4 or more of the length. The roundness of the connecting portion can be processed at a time using an end mill.

また、具体的な構成として、本発明の締結用治具では、凸条部は、中央軸部から離れる方向に突出する円柱面をなす外側面を備えてもよい。また凸条部は、接続部と外側面との間を繋ぐ接続平面を更に備えてもよい。   Moreover, as a specific configuration, in the fastening jig of the present invention, the ridge portion may include an outer surface forming a cylindrical surface protruding in a direction away from the central shaft portion. Moreover, a protruding item | line part may further be provided with the connection plane which connects between a connection part and an outer surface.

本発明の回転体の製造方法は、回転軸と、回転軸の一端に設けられたタービン翼車と、回転軸の他端に設けられたコンプレッサ翼車と、を備え、遠心圧縮機を含む過給機に内蔵される回転体を製造する製造方法であって、上述の何れかの締結用治具の中央軸部を締付用穴の中央に挿入すると共に凸条部をトルク伝達溝に係合させて、連結子をコンプレッサ翼車の締付用穴に嵌め込む治具嵌込工程と、締結用治具の工具掛部に工具を掛け回転軸線の周りに回転させて、コンプレッサ翼車を回転軸に螺着締結する螺着締結工程と、を備える。   A method of manufacturing a rotating body according to the present invention includes a rotating shaft, a turbine impeller provided at one end of the rotating shaft, and a compressor impeller provided at the other end of the rotating shaft, and includes a centrifugal compressor. A manufacturing method for manufacturing a rotating body incorporated in a feeder, wherein the central shaft portion of any of the above-described fastening jigs is inserted into the center of the fastening hole and the protruding portion is engaged with the torque transmission groove. The jig is inserted into the fastening hole of the compressor impeller, and the tool is put on the tool hook of the fastening jig and rotated around the rotation axis. A screwing and fastening step of screwing and fastening to the rotating shaft.

この製造方法によれば、回転に対する連結子の強度が向上された締結用治具を用いてコンプレッサ翼車が回転軸に螺着締結されるので、締付トルクが大きくなっても締結用治具を破壊することなく螺着締結が可能になる。   According to this manufacturing method, since the compressor wheel is screwed and fastened to the rotating shaft using the fastening jig whose strength of the connector against rotation is improved, the fastening jig can be used even if the tightening torque increases. The screw fastening is possible without destroying.

本発明によれば、強度を向上すると共に加工性が良い締結用治具及びこれを用いた回転体の製造方法を提供することができる。   According to the present invention, it is possible to provide a fastening jig that improves strength and has good workability, and a method for manufacturing a rotating body using the same.

本発明の締結用治具が適用される過給機の一例を示す断面図である。It is sectional drawing which shows an example of the supercharger with which the jig | tool for fastening of this invention is applied. 過給機のコンプレッサ翼車を示す斜視図である。It is a perspective view which shows the compressor impeller of a supercharger. コンプレッサ翼車の先端近傍を示す正面図である。It is a front view which shows the front-end | tip vicinity of a compressor impeller. （ａ）は本実施形態の締結用治具を示す正面図、（ｂ）はその側面図、（ｃ）はその斜視図である。(A) is the front view which shows the jig | tool for fastening of this embodiment, (b) is the side view, (c) is the perspective view. （ａ）は、締結用治具の凸条部近傍の、回転軸線に直交する断面図であり、（ｂ）は、締結用治具の凸条部と締付用穴のトルク伝達溝との、回転軸線に直交する断面図である。(A) is a cross-sectional view perpendicular to the rotation axis in the vicinity of the convex portion of the fastening jig, and (b) is a diagram showing the relationship between the convex portion of the fastening jig and the torque transmission groove of the fastening hole. It is sectional drawing orthogonal to a rotating shaft line. （ａ）〜（ｄ）は、締結用治具の各変形例を示す正面図である。(A)-(d) is a front view which shows each modification of the jig | tool for fastening. （ａ）は、変形例の締結用治具の一つに対応する締付用穴の正面図である。（ｂ）は、締結用治具の変形例の凸条部近傍を示す断面図である。(A) is a front view of the fastening hole corresponding to one of the fastening jigs of a modification. (B) is sectional drawing which shows the convex stripe part vicinity of the modification of the jig | tool for fastening.

以下、図面を参照しながら、本発明の締結用治具が適用される過給機の一例について説明する。   Hereinafter, an example of a supercharger to which the fastening jig of the present invention is applied will be described with reference to the drawings.

図１に示されるように、過給機１は、タービン２とコンプレッサ３（遠心圧縮機）とを備えている。タービン２は、タービンハウジング４と、タービンハウジング４に収納されたタービン翼車６と、を備えている。コンプレッサ３は、コンプレッサハウジング５と、コンプレッサハウジング５に収納されたコンプレッサ翼車７と、を備えている。タービン翼車６は回転軸１４の一端に設けられており、コンプレッサ翼車７は回転軸１４の他端に設けられている。タービンハウジング４とコンプレッサハウジング５との間には、軸受ハウジング１３が設けられている。回転軸１４は、軸受１５を介して軸受ハウジング１３に回転可能に支持されており、回転軸１４、タービン翼車６及びコンプレッサ翼車７を備える回転体１２が一体として回転軸線Ａ周りに回転する。   As shown in FIG. 1, the supercharger 1 includes a turbine 2 and a compressor 3 (centrifugal compressor). The turbine 2 includes a turbine housing 4 and a turbine impeller 6 housed in the turbine housing 4. The compressor 3 includes a compressor housing 5 and a compressor impeller 7 housed in the compressor housing 5. The turbine impeller 6 is provided at one end of the rotating shaft 14, and the compressor impeller 7 is provided at the other end of the rotating shaft 14. A bearing housing 13 is provided between the turbine housing 4 and the compressor housing 5. The rotating shaft 14 is rotatably supported by the bearing housing 13 via the bearing 15, and the rotating body 12 including the rotating shaft 14, the turbine impeller 6 and the compressor impeller 7 rotates around the rotation axis A as a unit. .

タービンハウジング４には、排気ガス流入口８及び排気ガス流出口１０が設けられている。内燃機関（図示せず）から排出された排気ガスが、排気ガス流入口８を通じてタービンハウジング４内に流入し、タービン翼車６を回転させ、その後、排気ガス流出口１０を通じてタービンハウジング４外に流出する。   The turbine housing 4 is provided with an exhaust gas inlet 8 and an exhaust gas outlet 10. Exhaust gas discharged from an internal combustion engine (not shown) flows into the turbine housing 4 through the exhaust gas inlet 8 to rotate the turbine impeller 6, and then to the outside of the turbine housing 4 through the exhaust gas outlet 10. leak.

コンプレッサハウジング５には、吸入口９及び吐出口１１が設けられている。上記のようにタービン翼車６が回転すると、回転軸１４を介してコンプレッサ翼車７が回転する。回転するコンプレッサ翼車７は、吸入口９を通じて外部の空気を吸入し、圧縮して吐出口１１から吐出する。吐出口１１から吐出された圧縮空気は、前述の内燃機関に供給される。   The compressor housing 5 is provided with a suction port 9 and a discharge port 11. When the turbine impeller 6 rotates as described above, the compressor impeller 7 rotates via the rotating shaft 14. The rotating compressor wheel 7 sucks external air through the suction port 9, compresses it, and discharges it from the discharge port 11. The compressed air discharged from the discharge port 11 is supplied to the internal combustion engine described above.

続いて、回転体１２について更に説明する。前述のとおり、回転体１２は、タービン翼車６と、回転軸１４と、コンプレッサ翼車７と、を備え、過給機１に内蔵されている。なお、回転体１２は、回転軸１４に取り付けられ軸受ハウジング１３のスラスト軸受１３ａに係合するカラー１８等も備えている。タービン翼車６は回転軸１４の一端に溶接されることで、タービン翼車６と回転軸１４とは一体物として形成されている。   Subsequently, the rotating body 12 will be further described. As described above, the rotating body 12 includes the turbine impeller 6, the rotating shaft 14, and the compressor impeller 7, and is built in the supercharger 1. The rotating body 12 also includes a collar 18 that is attached to the rotating shaft 14 and that engages with the thrust bearing 13 a of the bearing housing 13. The turbine impeller 6 is welded to one end of the rotating shaft 14 so that the turbine impeller 6 and the rotating shaft 14 are formed as a single body.

図２に示されるコンプレッサ翼車７は、例えばアルミ合金製であり、回転軸１４に取り付けられるハブ１６と、当該ハブ１６の外周面に回転周方向に複数配設されたブレード１７と、を備えている。コンプレッサ翼車７は中実構造をなす。具体的には、コンプレッサ翼車７の後端部には盲螺子穴７ｂ（図１参照）が設けられており、当該盲螺子穴７ｂに回転軸１４の他端が螺合されることで、コンプレッサ翼車７が回転軸１４に取り付けられている。回転軸１４はハブ１６を貫通せず、盲螺子穴７ｂよりも先端側ではハブ１６は中実である。この中実構造によれば、回転軸をコンプレッサ翼車の中空部に貫通させる構造に比較して、コンプレッサ翼車７の強度が高められる。   The compressor wheel 7 shown in FIG. 2 is made of, for example, an aluminum alloy, and includes a hub 16 attached to the rotating shaft 14 and a plurality of blades 17 disposed on the outer peripheral surface of the hub 16 in the rotating circumferential direction. ing. The compressor wheel 7 has a solid structure. Specifically, a blind screw hole 7b (see FIG. 1) is provided at the rear end portion of the compressor wheel 7, and the other end of the rotary shaft 14 is screwed into the blind screw hole 7b. A compressor impeller 7 is attached to the rotary shaft 14. The rotating shaft 14 does not penetrate the hub 16, and the hub 16 is solid on the tip side of the blind screw hole 7b. According to this solid structure, the strength of the compressor impeller 7 can be increased as compared with a structure in which the rotary shaft is passed through the hollow portion of the compressor impeller.

回転体１２の製造時やメンテナンス時において、コンプレッサ翼車７を回転軸１４に螺着締結する際には、回転軸１４に対してコンプレッサ翼車７自体を回転させる必要がある。具体的には、コンプレッサ翼車７の先端部７ａの中央には、締付用穴２１が設けられている。コンプレッサ翼車７を回転軸１４に螺着締結する際には、締付用穴２１に締結用治具３０（図４参照）を挿入し、当該締結用治具３０に工具（例えば六角レンチ）を掛け、回転軸１４に対してコンプレッサ翼車７を回転させる。   When the compressor impeller 7 is screwed and fastened to the rotating shaft 14 during manufacture of the rotating body 12 or during maintenance, the compressor impeller 7 itself needs to be rotated with respect to the rotating shaft 14. Specifically, a tightening hole 21 is provided in the center of the tip portion 7 a of the compressor impeller 7. When the compressor impeller 7 is screwed and fastened to the rotary shaft 14, a fastening jig 30 (see FIG. 4) is inserted into the fastening hole 21, and a tool (for example, a hexagon wrench) is inserted into the fastening jig 30. And the compressor wheel 7 is rotated with respect to the rotating shaft 14.

図３〜図５を参照しながら、締付用穴２１と締結用治具３０について説明する。図３は、コンプレッサ翼車７の先端部７ａ近傍を示す正面図である。締付用穴２１は、先端部７ａの中央に形成された主穴部２２と、主穴部２２の周縁部に等間隔に形成された複数（本例では４つ）のトルク伝達溝２３とを備えている。主穴部２２の内側面２２ａは、回転軸線Ａを軸とする円柱面をなす。トルク伝達溝２３は、内側面２２ａから径方向外側に窪むように形成されたＵ溝であり、後述する締結用治具３０からの締付トルクを伝達する。トルク伝達溝２３の内側面２３ａは、回転軸線Ａ方向に延びると共に主穴部２２よりも小さい曲率半径の円柱面をなしている。このように締付用穴２１の内側面は２種類の円柱面で構成されているので、締付用穴２１は２種類のドリルのみで形成することができる。なお、トルク伝達溝２３の内側面２３ａを構成する円柱面の中心軸は、主穴部２２の内側面２２ａを構成する円柱面よりも僅かに内側に位置している。   The fastening hole 21 and the fastening jig 30 will be described with reference to FIGS. FIG. 3 is a front view showing the vicinity of the tip 7 a of the compressor impeller 7. The tightening hole 21 includes a main hole portion 22 formed in the center of the tip end portion 7a, and a plurality (four in this example) of torque transmission grooves 23 formed at equal intervals on the peripheral edge portion of the main hole portion 22. It has. The inner side surface 22a of the main hole portion 22 forms a cylindrical surface with the rotation axis A as an axis. The torque transmission groove 23 is a U groove formed so as to be recessed radially outward from the inner side surface 22a, and transmits a tightening torque from a fastening jig 30 described later. The inner side surface 23 a of the torque transmission groove 23 extends in the direction of the rotation axis A and forms a cylindrical surface having a smaller radius of curvature than the main hole portion 22. Thus, since the inner surface of the fastening hole 21 is composed of two types of cylindrical surfaces, the fastening hole 21 can be formed with only two types of drills. The central axis of the cylindrical surface constituting the inner side surface 23 a of the torque transmission groove 23 is located slightly inside the cylindrical surface constituting the inner side surface 22 a of the main hole 22.

一方、締結用治具３０は、コンプレッサ翼車７と工具との間に介在されて使用される。図４（ａ）は締結用治具３０を示す正面図、図４（ｂ）はその側面図、図４（ｃ）はその斜視図である。図に示されるように、締結用治具３０は、工具が掛けられる工具掛部３９と、工具掛部から回転軸線Ｘ方向に延在し締付用穴２１に嵌め込まれる連結子３１と、を備えている。工具掛部３９と連結子３１とは、切削加工により一体で形成されている。工具掛部３９は略正六角柱をなし、例えば六角レンチ等の締結用の工具を掛けられるようになっている。工具掛部３９は、上記工具が掛けられ回転軸線Ｘ周りに回転される。以下の説明において、単に「回転周方向」、「回転径方向」等と言う場合には、回転軸線Ｘ周りの回転に対応するものとする。   On the other hand, the fastening jig 30 is used by being interposed between the compressor impeller 7 and the tool. 4A is a front view showing the fastening jig 30, FIG. 4B is a side view thereof, and FIG. 4C is a perspective view thereof. As shown in the figure, the fastening jig 30 includes a tool hanging portion 39 on which a tool is hung, and a connector 31 that extends from the tool hanging portion in the rotation axis X direction and is fitted into the tightening hole 21. I have. The tool hook 39 and the connector 31 are integrally formed by cutting. The tool hanging portion 39 has a substantially regular hexagonal column, and can be used for hanging a fastening tool such as a hexagon wrench. The tool hanging portion 39 is rotated around the rotation axis X with the tool hung thereon. In the following description, the terms “rotational circumferential direction”, “rotational radial direction”, and the like simply correspond to rotation around the rotation axis X.

連結子３１は、中央軸部３２と、中央軸部３２の周囲に形成された凸条部３３とを備えている。中央軸部３２は、回転軸線Ｘ上で当該回転軸線Ｘ方向に工具掛部３９から延在しており、締付用穴２１の主穴部２２の中央に挿入される。中央軸部３２は円柱形状をなしており、中央軸部３２の外側面３２ａは円柱面をなす。凸条部３３は、中央軸部３２から工具掛部３９の回転径方向に突出している。凸条部３３は、回転軸線Ｘ方向に延在し、締付用穴２１のトルク伝達溝２３に係合する。凸条部３３の外側面３３ａは、中央軸部３２よりも小さい曲率半径をもつ円柱面をなしている。   The connector 31 includes a central shaft portion 32 and a protruding strip portion 33 formed around the central shaft portion 32. The central shaft portion 32 extends from the tool hook portion 39 in the direction of the rotational axis X on the rotational axis X, and is inserted into the center of the main hole portion 22 of the fastening hole 21. The central shaft portion 32 has a cylindrical shape, and the outer surface 32a of the central shaft portion 32 forms a cylindrical surface. The protruding portion 33 protrudes from the central shaft portion 32 in the rotational radial direction of the tool hook portion 39. The ridge 33 extends in the rotation axis X direction and engages with the torque transmission groove 23 of the tightening hole 21. The outer surface 33 a of the ridge 33 forms a cylindrical surface having a smaller radius of curvature than the central shaft portion 32.

中央軸部３２と凸条部３３との接続部３４には、丸め加工（アール加工）が施されている。この丸み（アール）の曲率半径Ｒは、連結子３１の回転軸線Ｘ方向の長さＬの１／８よりも大きくなっている。具体的には、図５（ａ）に示されるように、凸条部３３近傍の、回転軸線Ｘに直交する断面形状を考える。この断面上では、中央軸部３２は、外側面３２ａに対応して円弧をなす輪郭線３２ｂを含み、凸条部３３は、外側面３３ａに対応して円弧をなす円弧輪郭線３３ｂを含む。なお、円弧輪郭線３３ｂは、中央軸部３２から離れる方向に突出する円弧である。そして、中央軸部３２の輪郭線３２ｂと凸条部３３の円弧輪郭線３３ｂとが、接続部３４の輪郭線３４ｂで接続されている。この輪郭線３４ｂは、輪郭線３２ｂ及び円弧輪郭線３３ｂとは逆方向に湾曲した円弧である。そして、接続部３４の輪郭線３４ｂの曲率半径Ｒが連結子３１の回転軸線Ｘ方向の長さＬ（図４（ｂ）参照）の１／８よりも大きい。なお、曲率半径Ｒが回転軸線Ｘ方向の長さの１／６を超えると、曲率半径Ｒがコンプレッサ翼車７の締付用穴２１と干渉する可能性が高まるので、曲率半径Ｒは回転軸線Ｘ方向の長さの１／６以下が望ましい。   The connecting portion 34 between the central shaft portion 32 and the ridge portion 33 is rounded (rounded). The curvature radius R of the roundness (R) is larger than 1/8 of the length L of the connector 31 in the rotation axis X direction. Specifically, as shown in FIG. 5A, a cross-sectional shape in the vicinity of the ridge 33 and orthogonal to the rotation axis X is considered. On this cross section, the central shaft portion 32 includes a contour line 32b that forms an arc corresponding to the outer surface 32a, and the ridge portion 33 includes an arc contour line 33b that forms an arc corresponding to the outer surface 33a. The arc contour line 33 b is an arc projecting in a direction away from the central shaft portion 32. Then, the contour line 32 b of the central shaft portion 32 and the arc contour line 33 b of the ridge portion 33 are connected by the contour line 34 b of the connection portion 34. The contour line 34b is an arc curved in the opposite direction to the contour line 32b and the arc contour line 33b. And the curvature radius R of the outline 34b of the connection part 34 is larger than 1/8 of the length L (refer FIG.4 (b)) of the rotation axis X direction of the connector 31. FIG. If the curvature radius R exceeds 1/6 of the length in the direction of the rotation axis X, the possibility that the curvature radius R interferes with the fastening hole 21 of the compressor wheel 7 increases. 1/6 or less of the length in the X direction is desirable.

また、図５（ｂ）に示されるように、締付用穴２１に連結子３１が嵌め込まれた状態を考える。このとき、凸条部３３はトルク伝達溝２３に対して、ほとんど隙間なく嵌め込まれるようになっている。これにより、締結用治具３０を回転軸線Ｘ周りに（矢印Ｗ方向に）回転させたとき、締付トルクが凸条部３３からトルク伝達溝２３に伝達される。これに対して、中央軸部３２の外側面３２ａと主穴部２２の内側面２２ａとは、間隙Ｆを空けて対面する。間隙Ｆの寸法は、接続部３４の回転径方向の寸法に対応している。   Further, as shown in FIG. 5B, a state where the connector 31 is fitted in the tightening hole 21 is considered. At this time, the ridge 33 is fitted into the torque transmission groove 23 with almost no gap. Thus, when the fastening jig 30 is rotated around the rotation axis X (in the direction of the arrow W), the fastening torque is transmitted from the ridge 33 to the torque transmission groove 23. On the other hand, the outer side surface 32a of the central shaft portion 32 and the inner side surface 22a of the main hole portion 22 face each other with a gap F therebetween. The dimension of the gap F corresponds to the dimension of the connecting portion 34 in the rotational radial direction.

なお、連結子３１の断面積を更に大きくするためには、上記のような間隙Ｆを空けないことも考えられる。すなわち、連結子が締付用穴にほぼ隙間なく挿入されるように、連結子を締付用穴２１とほぼ同じ断面形状に形成することも考えられる。しかしながらこの場合、中央軸部と凸条部との接続部を角にするか、又は接続部の丸みを極端に小さくする必要がある。そしてこの場合、エンドミルによる切削加工が不可能となり、例えば放電加工等によって接続部を加工することが必要になってしまう。その結果、連結子の加工性が低下してしまうので、連結子を締付用穴２１とほぼ同じ形状に形成する構成は、加工性向上に反する。   In order to further increase the cross-sectional area of the connector 31, it is conceivable that the gap F as described above is not provided. In other words, it is conceivable that the connector is formed in substantially the same cross-sectional shape as that of the tightening hole 21 so that the connector is inserted into the tightening hole with almost no gap. However, in this case, it is necessary to make the connecting portion between the central shaft portion and the ridge portion a corner or make the roundness of the connecting portion extremely small. In this case, cutting by an end mill becomes impossible, and it becomes necessary to process the connecting portion by, for example, electric discharge machining. As a result, since the workability of the connector is lowered, the configuration in which the connector is formed in substantially the same shape as the fastening hole 21 is contrary to the improvement of workability.

以上の構成を備える締結用治具３０による作用効果は次の通りである。締結用治具３０の連結子３１は、回転軸線Ｘ上の中央軸部３２を備え、当該中央軸部３２から回転径方向に凸条部３３が突出した構造をなす。回転軸線Ｘ上に中央軸部３２が存在する構造によって、連結子３１の断面積を大きくすることができ、回転に対する連結子３１の強度を向上することができる。また、中央軸部３２と凸条部３３との接続部３４の丸みの曲率半径Ｒが、連結子３１の回転軸線Ｘ方向の長さＬの１／８よりも大きいので、長さＬの１／４以上の直径をもつ通常のエンドミルを用いて、１回で接続部３４の丸みを加工することができる。その結果、特殊な工具を用いることなく通常のエンドミルを用いた切削加工で連結子３１を削り出すことができるので、締結用治具３０の加工性が良い。また、接続部３４に丸め加工を施すことにより、締付トルクが作用したときの接続部３４への応力集中も低減できる。   The effect by the fastening jig | tool 30 provided with the above structure is as follows. The connector 31 of the fastening jig 30 includes a central shaft portion 32 on the rotational axis X, and has a structure in which a protruding strip portion 33 projects from the central shaft portion 32 in the rotational radial direction. Due to the structure in which the central shaft portion 32 exists on the rotation axis X, the cross-sectional area of the connector 31 can be increased, and the strength of the connector 31 against rotation can be improved. Further, since the radius of curvature R of the roundness of the connecting portion 34 between the central shaft portion 32 and the ridge portion 33 is larger than 1/8 of the length L of the connector 31 in the rotation axis X direction, Using a normal end mill having a diameter of / 4 or more, the roundness of the connecting portion 34 can be processed at a time. As a result, since the connector 31 can be cut out by cutting using a normal end mill without using a special tool, the workability of the fastening jig 30 is good. Further, by rounding the connection portion 34, stress concentration on the connection portion 34 when a tightening torque is applied can be reduced.

締結用治具３０を用いた回転体１２の製造方法は次の通りである。一端にタービン翼車６が設けられている回転軸１４の他端側にカラー１８等を装着した後、回転軸１４の他端の雄螺子部１４ａ（図１参照）に、コンプレッサ翼車７の盲螺子穴７ｂ（図１参照）を螺合させる。その後、コンプレッサ翼車７の先端部７ａの締付用穴２１（図２参照）に締結用治具３０の連結子３１を嵌め込む（治具嵌込工程）。その状態から、締結用治具３０の工具掛部３９に六角レンチ等の工具を掛け、回転軸線Ｘ周りに回転させ、規定の締付トルクを付与することでコンプレッサ翼車７を回転軸１４に螺着締結する（螺着締結工程）。その後、締結用治具３０はコンプレッサ翼車７の先端部７ａから除去される。   The manufacturing method of the rotating body 12 using the fastening jig 30 is as follows. After the collar 18 or the like is attached to the other end of the rotating shaft 14 provided with the turbine impeller 6 at one end, the male screw portion 14a (see FIG. 1) at the other end of the rotating shaft 14 is attached to the compressor impeller 7. The blind screw hole 7b (see FIG. 1) is screwed. Thereafter, the connector 31 of the fastening jig 30 is fitted into the fastening hole 21 (see FIG. 2) of the tip 7a of the compressor impeller 7 (jig fitting process). From that state, a tool such as a hexagon wrench is hung on the tool hook 39 of the fastening jig 30, rotated around the rotation axis X, and a predetermined tightening torque is applied to the compressor wheel 7 to the rotation shaft 14. Screw fastening (screw fastening process). Thereafter, the fastening jig 30 is removed from the front end portion 7 a of the compressor impeller 7.

この製造方法によれば、回転に対する連結子３１の強度が向上された締結用治具３０を用いてコンプレッサ翼車７を回転軸１４に螺着締結するので、締付トルクが大きくなっても締結用治具３０を破壊することなく螺着締結が可能になる。   According to this manufacturing method, since the compressor impeller 7 is screwed and fastened to the rotary shaft 14 using the fastening jig 30 with improved strength of the connector 31 against rotation, the fastening is achieved even if the tightening torque increases. Screw fastening can be performed without destroying the jig 30 for use.

以下、図６及び図７を参照しながら、締結用治具３０の変形例を説明する。以下に説明する各締結用治具の変形例によっても、締結用治具３０と同様の作用効果を奏することができる。なお、各変形例において締結用治具３０と同一又は同等の構成については図面に同一の符号を付して重複する説明を省略する。また、図６（ａ）〜（ｄ）は、変形例に係る締結用治具の正面図（回転軸線Ｘ方向から見た図）のみを示し側面図及び斜視図は省略するが、各締結用治具の連結子の長さは、すべてＬに等しいものとする。   Hereinafter, a modification of the fastening jig 30 will be described with reference to FIGS. 6 and 7. Effects similar to those of the fastening jig 30 can also be achieved by modifications of the fastening jigs described below. In addition, about the structure which is the same as that of the jig | tool 30 for fastening in each modification, the same code | symbol is attached | subjected to drawing, and the overlapping description is abbreviate | omitted. 6 (a) to 6 (d) show only a front view (a view seen from the direction of the rotation axis X) of the fastening jig according to the modification, and a side view and a perspective view are omitted, but for each fastening. The lengths of the connector of the jig are all equal to L.

図６（ａ）に示される締結用治具５０は、中央軸部３２の周囲に５つの凸条部３３を等間隔で設けたものである。なお、この場合、コンプレッサ翼車７の先端部７ａには、図７（ａ）に示されるように、５つのトルク伝達溝２３を備える締付用穴５９が設けられる。この例のように、凸条部３３の数は４つに限られず、５つ以上としてもよく、３つ以下としてもよい。凸条部３３が増加することにより、締付トルクが周方向に分散される。但し、図７（ａ）に示されるように、トルク伝達溝２３同士の間の部分の肉厚Ｐが小さくなりすぎると、当該部分の強度が低下する。従って、締付トルクの分散と肉厚Ｐの確保とを両立する観点から、凸条部３３の数は４つ又は５つとすることができる。   The fastening jig 50 shown in FIG. 6A is provided with five protruding strips 33 at equal intervals around the central shaft portion 32. In this case, the front end portion 7a of the compressor impeller 7 is provided with a tightening hole 59 including five torque transmission grooves 23 as shown in FIG. As in this example, the number of ridges 33 is not limited to four, and may be five or more, or three or less. By increasing the ridge 33, the tightening torque is distributed in the circumferential direction. However, as shown in FIG. 7A, when the thickness P of the portion between the torque transmission grooves 23 becomes too small, the strength of the portion decreases. Therefore, from the viewpoint of achieving both the dispersion of the tightening torque and the securing of the wall thickness P, the number of the ridge portions 33 can be four or five.

また、中央軸部は円柱に限られず、図６（ｂ）に示される締結用治具６０のように、四角柱の中央軸部６２を採用してもよい。この形状によれば、中央軸部６２の断面積を大きくすることができ、回転に対する連結子の強度を高めることができる。また、締結用治具６０では、中央軸部６２の四角柱の４側面の各中心に凸条部３３を設けているが、図６（ｃ）に示される締結用治具７０のように、中央軸部６２の四角柱の４つの角の位置に凸条部３３を設けてもよい。   Further, the central shaft portion is not limited to a cylinder, and a square shaft central shaft portion 62 may be employed as in the fastening jig 60 shown in FIG. According to this shape, the cross-sectional area of the central shaft portion 62 can be increased, and the strength of the connector against rotation can be increased. Further, in the fastening jig 60, the protruding strips 33 are provided at the centers of the four side surfaces of the quadrangular column of the central shaft part 62. However, like the fastening jig 70 shown in FIG. The ridges 33 may be provided at the positions of the four corners of the quadrangular column of the central shaft portion 62.

また、図６（ｄ）に示される締結用治具８０のように、凸条部３３に対して回転周方向に幅を伸長させた凸条部８３を備えてもよい。この締結用治具８０の構成によれば、締付トルクに対する凸条部８３の強度が向上する。但し、締結用治具８０に対応する締付用穴を形成するためには、ドリルだけでは足りずエンドミルを必要とするので、締結用治具８０よりも、締結用治具３０を採用した方が締付用穴の加工性がよい。   Moreover, you may provide the protruding item | line part 83 which extended the width | variety to the rotation circumferential direction with respect to the protruding item | line part 33 like the fastening jig | tool 80 shown by FIG.6 (d). According to the configuration of the fastening jig 80, the strength of the convex portion 83 with respect to the fastening torque is improved. However, in order to form a fastening hole corresponding to the fastening jig 80, a drill alone is not sufficient, and an end mill is required. Therefore, the fastening jig 30 is used rather than the fastening jig 80. However, workability of the tightening hole is good.

また、図７（ｂ）に示される締結用治具１３０のように、凸条部３３に対して回転径方向に長さを伸長させた凸条部１３３を備えてもよい。図７（ｂ）は、回転軸線Ｘに直交する断面における凸条部１３３と締付用穴１２１のトルク伝達溝１２３との断面図である。凸条部１３３は、凸条部３３に比べて、直方体１３５の分だけ回転径方向に伸長されている。すなわち、凸条部１３３は、凸条部３３に加えて、接続部３４と外側面（円柱面）３３ａとの間を繋ぐ接続平面１３５ａを更に備えている。接続平面１３５ａは、直方体１３５の側面に対応する平面である。   Moreover, you may provide the protruding item | line part 133 which extended the length to the rotation radial direction with respect to the protruding item | line part 33 like the fastening jig | tool 130 shown by FIG.7 (b). FIG. 7B is a cross-sectional view of the ridge 133 and the torque transmission groove 123 of the tightening hole 121 in a cross section orthogonal to the rotation axis X. The ridge 133 is extended in the rotational radial direction by the amount of the rectangular parallelepiped 135 compared to the ridge 33. In other words, in addition to the ridge 33, the ridge 133 further includes a connection plane 135a that connects the connection 34 and the outer surface (cylindrical surface) 33a. The connection plane 135a is a plane corresponding to the side surface of the rectangular parallelepiped 135.

これに対応して、トルク伝達溝１２３も、接続平面１３５ａに対面する平面部１２５ａの分だけ伸長されており、トルク伝達溝１２３はトルク伝達溝２３に比較して深くなっている。この構成によれば、凸条部３３と比較して、接続平面１３５ａの分だけトルク伝達溝１２３との接触面積が増加するので、締付トルクに起因して凸条部及びトルク伝達溝に作用する応力が低減する。但し、締結用治具１３０に対応する締付用穴１２１を形成するためには、ドリルだけでは足りずエンドミルを必要とするので、締結用治具１３０よりも、締結用治具３０を採用した方が締付用穴の加工性がよい。   Correspondingly, the torque transmission groove 123 is also extended by the flat portion 125 a facing the connection flat surface 135 a, and the torque transmission groove 123 is deeper than the torque transmission groove 23. According to this configuration, the contact area with the torque transmission groove 123 is increased by the amount of the connection plane 135a as compared with the ridge portion 33, so that it acts on the ridge portion and the torque transmission groove due to the tightening torque. Reducing stress. However, in order to form the fastening hole 121 corresponding to the fastening jig 130, an end mill is required because the drill alone is not sufficient, so the fastening jig 30 is used rather than the fastening jig 130. The better the workability of the tightening hole.

以上、本発明の実施形態について説明したが、本発明は、上記実施形態に限られるものではなく、各請求項に記載した要旨を変更しない範囲で変形したものであってもよい。例えば、実施形態及び各変形例に係る締結用治具の各構成要素は、適宜組み合わせて採用してもよい。   As mentioned above, although embodiment of this invention was described, this invention is not restricted to the said embodiment, You may change in the range which does not change the summary described in each claim. For example, each component of the fastening jig according to the embodiment and each modification may be appropriately combined and employed.

１ 過給機
３ コンプレッサ（遠心圧縮機）
６ タービン翼車
７ コンプレッサ翼車
７ａ 先端部
１２ 回転体
１４ 回転軸
２１ 締付用穴
２３ トルク伝達溝
３０、５０、６０、７０、８０、１３０ 締結用治具
３１ 連結子
３２，６２ 中央軸部
３３，８３，１３３ 凸条部
３３ａ 外側面
３４ 接続部
１３５ａ 接続平面
３９ 工具掛部
Ｘ 回転軸線
1 Supercharger 3 Compressor (centrifugal compressor)
6 Turbine impeller 7 Compressor impeller 7a Tip 12 Rotating body 14 Rotating shaft 21 Tightening hole 23 Torque transmission grooves 30, 50, 60, 70, 80, 130 Fastening jig 31 Connector 32, 62 Central shaft 33, 83, 133 ridge 33a outer side 34 connection 135a connection plane 39 tool hook X rotation axis

Claims (4)

遠心圧縮機のコンプレッサ翼車と工具との間に介在されて前記コンプレッサ翼車を前記遠心圧縮機の回転軸に螺着締結するための締結用治具であって、
前記工具が掛けられ回転される工具掛部と、
前記工具掛部から当該工具掛部の回転軸線方向に延在し、前記コンプレッサ翼車の先端部に設けられた締付用穴に嵌め込まれる連結子と、を備え、
前記連結子は、
前記回転軸線上で当該回転軸線方向に延在し前記締付用穴の中央に挿入される中央軸部と、
前記中央軸部から前記工具掛部の回転径方向に突出すると共に前記回転軸線方向に延在し、前記締付用穴が備えるトルク伝達溝に係合する凸条部と、を備え、
前記工具掛部と前記連結子とが切削加工により一体で形成されており、
前記中央軸部と前記凸条部との接続部の丸みの曲率半径が、前記連結子の前記回転軸線方向の長さの１／８よりも大きい、締結用治具。 A fastening jig interposed between a compressor impeller of a centrifugal compressor and a tool for screwing and fastening the compressor impeller to a rotary shaft of the centrifugal compressor,
A tool hanging portion on which the tool is hung and rotated;
A connector that extends from the tool hook in the direction of the axis of rotation of the tool hook and is fitted into a tightening hole provided at a tip of the compressor wheel,
The connector is
A central shaft portion extending in the rotational axis direction on the rotational axis and inserted into the center of the fastening hole;
A protruding portion that protrudes from the central shaft portion in the radial direction of the tool hanging portion and extends in the rotational axis direction, and engages with a torque transmission groove provided in the tightening hole, and
The tool hanging portion and the connector are integrally formed by cutting,
A fastening jig in which a radius of curvature of a connection portion between the central shaft portion and the ridge portion is larger than 1/8 of a length of the connector in the rotation axis direction. 前記凸条部は、前記中央軸部から離れる方向に突出する円柱面をなす外側面を備える請求項１に記載の締結用治具。   The fastening jig according to claim 1, wherein the protruding portion includes an outer surface that forms a cylindrical surface protruding in a direction away from the central shaft portion. 前記凸条部は、前記接続部と前記外側面との間を繋ぐ接続平面を更に備える請求項２に記載の締結用治具。   The fastening jig according to claim 2, wherein the protruding portion further includes a connection plane that connects the connection portion and the outer surface. 回転軸と、前記回転軸の一端に設けられたタービン翼車と、前記回転軸の他端に設けられたコンプレッサ翼車と、を備え、前記遠心圧縮機を含む過給機に内蔵される回転体を製造する製造方法であって、
請求項１〜３の何れか１項に記載の締結用治具の前記中央軸部を前記締付用穴の中央に挿入すると共に前記凸条部を前記トルク伝達溝に係合させて、前記連結子を前記コンプレッサ翼車の前記締付用穴に嵌め込む治具嵌込工程と、
前記締結用治具の前記工具掛部に工具を掛け前記回転軸線の周りに回転させて、前記コンプレッサ翼車を前記回転軸に螺着締結する螺着締結工程と、を備える回転体の製造方法。 A rotating shaft, a turbine impeller provided at one end of the rotating shaft, and a compressor impeller provided at the other end of the rotating shaft, the rotation built in a turbocharger including the centrifugal compressor A manufacturing method for manufacturing a body,
The center shaft portion of the fastening jig according to any one of claims 1 to 3 is inserted into the center of the tightening hole and the protruding portion is engaged with the torque transmission groove, A jig fitting step for fitting a connector into the fastening hole of the compressor wheel,
A method of manufacturing a rotating body, comprising: a screwing and fastening step in which a tool is put on the tool hanging portion of the fastening jig and rotated around the rotation axis, and the compressor impeller is screwed and fastened to the rotation shaft. .
JP2014144113A 2014-07-14 2014-07-14 Fastening jig and rotating body manufacturing method Expired - Fee Related JP6334302B2 (en)

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