JP6261818B1 - Rotating electric machine cooling device - Google Patents

Rotating electric machine cooling device Download PDF

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JP6261818B1
JP6261818B1 JP2017517810A JP2017517810A JP6261818B1 JP 6261818 B1 JP6261818 B1 JP 6261818B1 JP 2017517810 A JP2017517810 A JP 2017517810A JP 2017517810 A JP2017517810 A JP 2017517810A JP 6261818 B1 JP6261818 B1 JP 6261818B1
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annular
cylindrical member
flow path
discharge port
supply port
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JPWO2017212556A1 (en
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直哉 佐藤
直哉 佐藤
夏樹 本池
夏樹 本池
加藤　健次
健次 加藤
愛 岡本
愛 岡本
佳樹 岡田
佳樹 岡田
大輔 川口
大輔 川口
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Mitsubishi Electric Corp
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    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K1/00—Details of the magnetic circuit
    • H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
    • H02K1/12—Stationary parts of the magnetic circuit
    • H02K1/20—Stationary parts of the magnetic circuit with channels or ducts for flow of cooling medium
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/20—Casings or enclosures characterised by the shape, form or construction thereof with channels or ducts for flow of cooling medium
    • H02K5/203—Casings or enclosures characterised by the shape, form or construction thereof with channels or ducts for flow of cooling medium specially adapted for liquids, e.g. cooling jackets

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)

Abstract

固定子鉄心１１の外周面１１Ｐに配設された第１の筒状部材１２と、第１の筒状部材１２の外周面１２Ｐと円環状の空隙２３を隔てて配設された第２の筒状部材１３と、第２の筒状部材１３の一端側に設けられた供給口１４から、円環状の空隙２３を通じて第２の筒状部材１３の他端側に設けられた排出口１５へ冷却液１６が通過する冷却流路２０と、を備え、冷却流路２０は、供給口１４に連通する環状の供給口側ヘッダ流路２１と、第１の筒状部材１２の外周面１２Ｐに設けられた円状の環状溝２４と、を有する。The first cylindrical member 12 disposed on the outer peripheral surface 11P of the stator core 11, and the second cylinder disposed with the outer peripheral surface 12P of the first cylindrical member 12 and the annular gap 23 therebetween. Cooling from the supply port 14 provided on one end side of the cylindrical member 13 and the second cylindrical member 13 to the discharge port 15 provided on the other end side of the second cylindrical member 13 through the annular gap 23 A cooling flow path 20 through which the liquid 16 passes. The cooling flow path 20 is provided on the annular supply port side header flow path 21 communicating with the supply port 14 and the outer peripheral surface 12P of the first tubular member 12. And a circular annular groove 24 formed.

Description

本発明は、回転電機を冷却する回転電機冷却装置に関する。   The present invention relates to a rotating electrical machine cooling device that cools a rotating electrical machine.

従来、鋼板が積層された積層鉄心であり、固定子コイルが巻き付けられた固定子鉄心と、固定子鉄心の外周面に接触して設けられたフレームと、冷却液をフレーム内に流すことにより固定子の冷却を行う冷却装置と、を有する回転電機がある（例えば、特許文献１）。特許文献１に記載の回転電機のフレームは、固定子鉄心の外周面に設けられた第１フレームと、第１フレームの外周面に接触して設けられた第２フレームとを有し、第１フレームの第２フレームに接触する面には、円周方向に伸びるように微小な環状の隙間が形成され、第１フレームの第２フレームに接触する面の微小な環状の隙間を冷却液溝となるようにしている。   Conventionally, it is a laminated iron core in which steel plates are laminated, and is fixed by flowing a cooling liquid through the frame, a stator core around which a stator coil is wound, a frame provided in contact with the outer peripheral surface of the stator core There is a rotating electrical machine having a cooling device that cools a child (for example, Patent Document 1). The frame of the rotating electrical machine described in Patent Document 1 includes a first frame provided on the outer peripheral surface of the stator core, and a second frame provided in contact with the outer peripheral surface of the first frame. A minute annular gap is formed on the surface of the frame that contacts the second frame so as to extend in the circumferential direction, and the minute annular gap of the surface that contacts the second frame of the first frame serves as a coolant groove. It is trying to become.

特開２００３−１９９２９１号公報JP 2003-199291 A

しかしながら、特許文献１のような冷却装置を備えた回転電機は、冷却液が冷却液溝の流路を流れるにつれて徐々に温度境界層を発達させるので、冷却能力が低下する。従って、固定子鉄心の軸方向長さが大きくなると冷却液溝の流路が長くなり、必要な冷却能力が得られない、という問題があった。   However, since the rotating electrical machine including the cooling device as in Patent Document 1 gradually develops the temperature boundary layer as the coolant flows through the flow path of the coolant groove, the cooling capacity decreases. Therefore, when the axial length of the stator core is increased, the flow path of the coolant groove is increased, and a necessary cooling capacity cannot be obtained.

本発明は、上記に鑑みてなされたものであって、冷却能力の高い回転電機冷却装置を提供することを目的とする。   This invention is made | formed in view of the above, Comprising: It aims at providing the rotary electric machine cooling device with high cooling capability.

上述した課題を解決し、目的を達成するために、本発明は、固定子鉄心の外周面に配設された第１の筒状部材と、前記第１の筒状部材の外周面と円環状の空隙を隔てて配設された第２の筒状部材と、前記第２の筒状部材の一端側に設けられた供給口から、前記円環状の空隙を通じて前記第２の筒状部材の他端側に設けられた排出口へ冷却液が通過する冷却流路と、を備え、前記冷却流路は、前記供給口に連通する環状の供給口側ヘッダ流路と、
前記排出口に連通する環状の排出口側ヘッダ流路と、前記供給口側ヘッダ流路と前記排出口側ヘッダ流路との間に配置され、前記第１の筒状部材の外周面に設けられ、前記供給口側の環状のヘッダ流路及び前記排出口側の環状のヘッダ流路の溝幅よりも狭い溝幅を有し、且つ複数の独立した円状の環状溝と、を有すると共に、前記供給口側ヘッダ流路内で全周に拡がった冷却液は、前記排出側ヘッダ流路側に向かい前記環状溝の溝方向に直交する軸方向に流れることを特徴とする。 In order to solve the above-described problems and achieve the object, the present invention includes a first cylindrical member disposed on an outer peripheral surface of a stator core, an outer peripheral surface of the first cylindrical member, and an annular shape. A second cylindrical member disposed with a gap therebetween, and a supply port provided on one end side of the second cylindrical member, and the second cylindrical member through the annular gap. A cooling flow path through which the coolant passes to the discharge port provided on the end side, and the cooling flow path is an annular supply port side header flow path communicating with the supply port;
An annular outlet-side header channel communicating with the outlet, and disposed between the supply-port-side header channel and the outlet-side header channel and provided on the outer peripheral surface of the first tubular member A plurality of independent circular annular grooves having a groove width narrower than the groove width of the annular header flow path on the supply port side and the annular header flow path on the discharge port side, and The cooling liquid spreading all around in the supply port side header flow path flows toward the discharge side header flow path side in the axial direction perpendicular to the groove direction of the annular groove.

本発明によれば、冷却能力の高い回転電機冷却装置を提供することができる。   ADVANTAGE OF THE INVENTION According to this invention, a rotary electric machine cooling device with high cooling capability can be provided.

実施の形態１に係る回転電機冷却装置を示す断面図Sectional drawing which shows the rotary electric machine cooling device which concerns on Embodiment 1. FIG. 実施の形態１に係る回転電機冷却装置の第１の筒状部材の斜視図The perspective view of the 1st cylindrical member of the rotary electric machine cooling device which concerns on Embodiment 1. FIG. 実施の形態１に係る環状溝を設けた第１の筒状部材と第２の筒状部材とから形成される円環状の空隙の断面図Sectional drawing of the annular | circular shaped space | gap formed from the 1st cylindrical member which provided the annular groove which concerns on Embodiment 1, and a 2nd cylindrical member 実施の形態１に係る円環状の空隙と環状溝とに冷却液が通過する様子を示す部分拡大断面図The partial expanded sectional view which shows a mode that a cooling fluid passes the annular space | gap and annular groove which concern on Embodiment 1. FIG. 実施の形態１に係る冷却流路において、円環状の空隙の隙間高さが冷却能力に与える影響を示したグラフThe graph which showed the influence which the clearance gap height of an annular | circular space | gap has on the cooling capacity in the cooling flow path which concerns on Embodiment 1. FIG. 実施の形態１に係る環状溝の幅ｗと深さｈとの比（ｗ／ｈ）が冷却能力に与える影響を示したグラフThe graph which showed the influence which the ratio (w / h) of the width w and the depth h of the annular groove which concerns on Embodiment 1 has on cooling capacity 実施の形態１に係る供給口側ヘッダ流路、円環状の空隙及び排出口側ヘッダ流路の断面図Sectional drawing of the supply port side header flow path which concerns on Embodiment 1, an annular space | gap, and a discharge port side header flow path 図７のVIII−VIII線断面図VIII-VIII sectional view of FIG. 実施の形態１に係る円環状の空隙内の流速比に与える流路断面積比の影響を示したグラフThe graph which showed the influence of the channel cross-sectional area ratio which gives to the flow velocity ratio in the annular | circular shaped space | gap which concerns on Embodiment 1. 実施の形態１に係る回転電機冷却装置の段付き円筒状構造の断面図Sectional drawing of the cylindrical structure with a step of the rotary electric machine cooling device concerning Embodiment 1 実施の形態１に係る変形例の環状溝を設けた第１の筒状部材と第２の筒状部材とから形成される円環状の空隙の断面図Sectional drawing of the annular | circular shaped space | gap formed from the 1st cylindrical member and the 2nd cylindrical member which provided the annular groove of the modification concerning Embodiment 1 実施の形態２に係る回転電機冷却装置を示す断面図Sectional drawing which shows the rotary electric machine cooling device which concerns on Embodiment 2. FIG. 実施の形態１及び実施の形態２と従来の構造における冷却能力について有限体積法による数値解析結果の比較図Comparison diagram of numerical analysis results by finite volume method for cooling capacity in Embodiment 1 and Embodiment 2 and conventional structure 実施の形態３に係る回転電機冷却装置を示す断面図Sectional drawing which shows the rotary electric machine cooling device which concerns on Embodiment 3. FIG.

以下に、本発明の実施の形態に係る回転電機冷却装置を図面に基づいて詳細に説明する。なお、本実施の形態により本発明が限定されるものではない。   Below, the rotating electrical machine cooling device which concerns on embodiment of this invention is demonstrated in detail based on drawing. In addition, this invention is not limited by this Embodiment.

実施の形態１．
図１は、実施の形態１に係る回転電機冷却装置を示す断面図である。回転電機は、固定子コイル１１ａを備えた筒状の固定子鉄心１１と、固定子鉄心１１の内側に回転可能に支持される図示しないロータとを有する。回転電機は、固定子コイル１１ａ及び固定子鉄心１１の発熱を抑える回転電機冷却装置１０を有する。回転電機冷却装置１０は、固定子鉄心１１を冷却する。回転電機冷却装置１０は、第１の筒状部材１２と、第２の筒状部材１３と、冷却流路２０と、を備える。Embodiment 1 FIG.
1 is a cross-sectional view showing a rotating electrical machine cooling apparatus according to Embodiment 1. FIG. The rotating electrical machine includes a cylindrical stator core 11 provided with a stator coil 11 a and a rotor (not shown) that is rotatably supported inside the stator core 11. The rotating electrical machine has a rotating electrical machine cooling device 10 that suppresses heat generation of the stator coil 11 a and the stator core 11. The rotating electrical machine cooling device 10 cools the stator core 11. The rotating electrical machine cooling device 10 includes a first cylindrical member 12, a second cylindrical member 13, and a cooling flow path 20.

第１の筒状部材１２は、固定子鉄心１１の外周面１１Ｐに配置されている。第２の筒状部材１３の一部は、第１の筒状部材１２の外周面１２Ｐの一部と円環状の空隙２３を隔てて配設される。第２の筒状部材１３の一端側１３ＴＦに設けられた供給口１４から、円環状の空隙２３を通じて第２の筒状部材１３の他端側１３ＴＳに設けられた排出口１５へ冷却液１６が通過する。   The first cylindrical member 12 is disposed on the outer peripheral surface 11P of the stator core 11. A part of the second cylindrical member 13 is disposed with a part of the outer peripheral surface 12P of the first cylindrical member 12 and an annular gap 23 therebetween. The coolant 16 flows from the supply port 14 provided on the one end side 13TF of the second cylindrical member 13 to the discharge port 15 provided on the other end side 13TS of the second cylindrical member 13 through the annular gap 23. pass.

冷却流路２０は、供給口１４と接続する円環状の供給口側ヘッダ流路２１と、排出口１５と接続する円環状の排出口側ヘッダ流路２２と、供給口側ヘッダ流路２１と排出口側ヘッダ流路２２とを接続し、かつ冷却液１６が通過する円環状の空隙２３と、第１の筒状部材１２の外周面１２Ｐに設けられた円状の環状溝２４と、を有する。本実施の形態において、環状溝２４は、第１の筒状部材１２の円環状の空隙２３側の面に形成されて、第１の筒状部材１２の円周方向に沿って延びる、互いに独立な複数の環状溝２４を配置している。この複数の環状溝２４は、第１の筒状部材１２の軸Ｚｒ方向と平行な方向に対して直交する方向に延びるが、限定されない。複数の環状溝２４は、第１の筒状部材１２の軸Ｚｒ方向と平行な方向に対して交差する方向に延びてもよい。   The cooling flow path 20 includes an annular supply port side header flow path 21 connected to the supply port 14, an annular discharge port side header flow path 22 connected to the discharge port 15, and a supply port side header flow path 21. An annular gap 23 that connects the outlet-side header flow path 22 and through which the coolant 16 passes, and a circular annular groove 24 provided on the outer peripheral surface 12P of the first tubular member 12. Have. In the present embodiment, the annular groove 24 is formed on the surface of the first cylindrical member 12 on the annular gap 23 side, and extends along the circumferential direction of the first cylindrical member 12. A plurality of annular grooves 24 are arranged. The plurality of annular grooves 24 extend in a direction orthogonal to the direction parallel to the direction of the axis Zr of the first tubular member 12, but are not limited thereto. The plurality of annular grooves 24 may extend in a direction intersecting the direction parallel to the axis Zr direction of the first tubular member 12.

供給口側ヘッダ流路２１は、第２の筒状部材１３に形成され、供給口１４と連通している。排出口側ヘッダ流路２２は、第２の筒状部材１３に形成され、排出口１５と連通している。   The supply port side header flow path 21 is formed in the second cylindrical member 13 and communicates with the supply port 14. The discharge port side header flow path 22 is formed in the second cylindrical member 13 and communicates with the discharge port 15.

円環状の空隙２３は、第１の筒状部材１２と第２の筒状部材１３との間に円筒状に形成された、微小な空隙である。円環状の空隙２３は、第１の筒状部材１２の軸Ｚｒを中心とする円筒状の空隙である。円環状の空隙２３は、第１の筒状部材１２の一端側の供給口側ヘッダ流路２１から他端側の排出口側ヘッダ流路２２に冷却液１６を通過させる。   The annular gap 23 is a minute gap formed in a cylindrical shape between the first cylindrical member 12 and the second cylindrical member 13. The annular gap 23 is a cylindrical gap centered on the axis Zr of the first cylindrical member 12. The annular gap 23 allows the coolant 16 to pass from the supply port side header flow path 21 on one end side of the first cylindrical member 12 to the discharge port side header flow path 22 on the other end side.

環状溝２４は、図１に示すように、第１の筒状部材１２の外周面１２Ｐである円環状の空隙２３側の面に形成されている。複数の環状溝２４は、互いに平行かつ独立の微小な溝群である。つまり環状溝２４は、第１の筒状部材１２の外周面１２Ｐに複数形成されており、第１の筒状部材１２の円周方向に沿って延びている。また、複数の環状溝２４は、第１の筒状部材１２の軸Ｚｒ方向に並んでいる。本実施の形態では、環状溝２４として複数の円状の溝を備えているが、本発明はこれに限定されるものではなく、少なくとも一周する円状の溝を一つ備えるものであってもよい。   As shown in FIG. 1, the annular groove 24 is formed on the surface on the annular gap 23 side that is the outer peripheral surface 12 </ b> P of the first tubular member 12. The plurality of annular grooves 24 are minute groove groups that are parallel and independent of each other. That is, a plurality of annular grooves 24 are formed on the outer peripheral surface 12 </ b> P of the first tubular member 12 and extend along the circumferential direction of the first tubular member 12. The plurality of annular grooves 24 are arranged in the direction of the axis Zr of the first cylindrical member 12. In the present embodiment, a plurality of circular grooves are provided as the annular groove 24. However, the present invention is not limited to this, and the annular groove 24 may be provided with at least one circular groove. Good.

環状溝２４の形状は、断面が図１に示すように四角形であってもよいし、Ｖ字型であってもよいし、Ｕ字型であってもよいし、その他の形状であってもよい。   The shape of the annular groove 24 may be a quadrangle as shown in FIG. 1, a V shape, a U shape, or other shapes. Good.

冷却流路２０は、供給口１４に供給された冷却液１６が、供給口側ヘッダ流路２１、円環状の空隙２３、及び排出口側ヘッダ流路２２を通り、排出口１５から排出される。冷却液１６は、冷却流路２０を通過する時に、第１の筒状部材１２と熱交換を行い、第１の筒状部材１２を冷却する。これにより、発熱源である固定子鉄心１１で発生した熱で加熱された第１の筒状部材１２を冷却し、回転電機の過熱を抑制する。   In the cooling channel 20, the coolant 16 supplied to the supply port 14 passes through the supply port side header channel 21, the annular gap 23, and the discharge port side header channel 22 and is discharged from the discharge port 15. . When the coolant 16 passes through the cooling flow path 20, the coolant 16 exchanges heat with the first tubular member 12 to cool the first tubular member 12. Thereby, the 1st cylindrical member 12 heated with the heat which generate | occur | produced in the stator core 11 which is a heat generating source is cooled, and the overheating of a rotary electric machine is suppressed.

第１の筒状部材１２は、第２の筒状部材１３と対向する面の軸Ｚｒ方向の両側に、各々シール部材２５であるＯリングを取り付けるための溝２６が形成されている。溝２６には、シール部材２５が配置されている。シール部材２５は、第１の筒状部材１２と第２の筒状部材１３との隙間をシールしている。つまり、回転電機は、第１の筒状部材１２と第２の筒状部材１３との間の隙間であって、冷却流路２０の円環状の空隙２３が設けられている領域の軸Ｚｒ方向における両側にシール部材２５が設けられている。本構造により、回転電機は、円環状の空隙２３を流れる冷却液１６の液漏れを抑制できる。また、冷却流路２０は、排出口１５と供給口１４とが、図示しない循環ラインに接続される。循環ラインは、冷却液１６を冷却する冷却設備が配置されている。冷却液１６は、冷却流路２０を流れることで回転電機の熱を吸収して、回転電機を冷却する。加熱された冷却液１６は、冷却設備で冷却される。冷却液１６は、循環ラインと冷却流路２０とを繰り返し循環することで、冷却と加熱とが繰り返される。   The first cylindrical member 12 has grooves 26 for attaching O-rings, which are seal members 25, on both sides in the axis Zr direction of the surface facing the second cylindrical member 13. A seal member 25 is disposed in the groove 26. The seal member 25 seals the gap between the first tubular member 12 and the second tubular member 13. That is, the rotating electrical machine is a gap between the first cylindrical member 12 and the second cylindrical member 13 and is in the direction of the axis Zr in the region where the annular gap 23 of the cooling channel 20 is provided. Seal members 25 are provided on both sides of the. With this structure, the rotating electrical machine can suppress the leakage of the coolant 16 flowing through the annular gap 23. Moreover, the cooling flow path 20 has the discharge port 15 and the supply port 14 connected to a circulation line (not shown). A cooling facility for cooling the coolant 16 is arranged in the circulation line. The coolant 16 absorbs the heat of the rotating electrical machine by flowing through the cooling flow path 20 and cools the rotating electrical machine. The heated coolant 16 is cooled by a cooling facility. The cooling liquid 16 is repeatedly circulated through the circulation line and the cooling flow path 20 to repeat cooling and heating.

図２は、実施の形態１に係る回転電機冷却装置の第１の筒状部材の斜視図である。図３は、実施の形態１に係る環状溝を設けた第１の筒状部材と第２の筒状部材とから形成される円環状の空隙の断面図である。図３は、円環状の空隙２３及び環状溝２４を拡大した断面を示す。図２及び図３を用いて冷却流路２０を流れる冷却液１６の流れを説明する。図３に示すように、環状溝２４は、第１の筒状部材１２の円筒外周面を基準とする第１の基準面４１（図１参照）からの窪んだ溝により形成される。ここで、円環状の空隙２３の隙間高さ、すなわち第１の筒状部材１２の径方向における距離をδ、環状溝２４の幅、すなわち第１の筒状部材１２の軸Ｚｒ方向における距離をｗ、環状溝２４の深さ、すなわち第１の筒状部材１２の径方向における距離をｈ、環状溝２４のピッチ、すなわち第１の筒状部材１２の軸Ｚｒ方向における距離をｐとする。   FIG. 2 is a perspective view of a first cylindrical member of the rotating electrical machine cooling apparatus according to the first embodiment. FIG. 3 is a cross-sectional view of an annular gap formed by the first cylindrical member and the second cylindrical member provided with the annular groove according to the first embodiment. FIG. 3 shows an enlarged cross section of the annular gap 23 and the annular groove 24. The flow of the coolant 16 flowing through the cooling flow path 20 will be described with reference to FIGS. As shown in FIG. 3, the annular groove 24 is formed by a recessed groove from a first reference surface 41 (see FIG. 1) based on the cylindrical outer peripheral surface of the first cylindrical member 12. Here, the clearance height of the annular gap 23, that is, the distance in the radial direction of the first cylindrical member 12 is δ, the width of the annular groove 24, that is, the distance in the axis Zr direction of the first cylindrical member 12. w, the depth of the annular groove 24, that is, the distance in the radial direction of the first cylindrical member 12, and the pitch of the annular groove 24, that is, the distance of the first cylindrical member 12 in the axis Zr direction is p.

図２及び図３に示すように、供給口１４より供給された冷却液１６は、供給口側ヘッダ流路２１を流れることで、第１の筒状部材１２の円周方向３１に流れ、供給口側ヘッダ流路２１の円周方向の全周に広がる。供給口側ヘッダ流路２１内において全周に広がった冷却液１６は、円環状の空隙２３では第１の筒状部材１２の軸方向３２に流れる。そして、排出口側ヘッダ流路２２では再び円周方向３３から集められるように流れ、排出口１５から排出される。   As shown in FIGS. 2 and 3, the coolant 16 supplied from the supply port 14 flows in the circumferential direction 31 of the first cylindrical member 12 by flowing through the supply port side header flow path 21, and is supplied. The mouth-side header channel 21 spreads over the entire circumference in the circumferential direction. The coolant 16 that has spread all around in the supply port side header flow path 21 flows in the axial direction 32 of the first tubular member 12 in the annular gap 23. Then, in the discharge port side header flow path 22, the flow again collects from the circumferential direction 33 and is discharged from the discharge port 15.

図４は、実施の形態１に係る円環状の空隙と環状溝とに冷却液が通過する様子を示す部分拡大断面図である。図４に示すように、隙間高さδの円環状の空隙２３を通過する冷却液１６には、第１の筒状部材１２の面に膜状の温度境界層５１があり、流れに沿って、当該層の厚さが大きくなり、発達する。温度境界層５１の厚さが大きいと熱伝達率が低下し、冷却性能が低下する。ここで、一定間隔毎に設けられた複数の独立した環状溝２４を横切って流れる際、発達した温度境界層５１が分断され、環状溝２４を通過後、第１の筒状部材１２の面に厚さ０から温度境界層５２が再生される。環状溝２４の通過前後で温度境界層の厚さが小さくなるため、熱伝達率が上昇し、冷却性能が向上する。   FIG. 4 is a partially enlarged cross-sectional view showing a state in which the coolant passes through the annular gap and the annular groove according to the first embodiment. As shown in FIG. 4, the coolant 16 passing through the annular gap 23 having a gap height δ has a film-like temperature boundary layer 51 on the surface of the first cylindrical member 12, and is along the flow. , The thickness of the layer increases and develops. When the thickness of the temperature boundary layer 51 is large, the heat transfer coefficient is lowered and the cooling performance is lowered. Here, when flowing across a plurality of independent annular grooves 24 provided at regular intervals, the developed temperature boundary layer 51 is divided, and after passing through the annular groove 24, the surface of the first tubular member 12 is formed. From the thickness 0, the temperature boundary layer 52 is regenerated. Since the thickness of the temperature boundary layer is reduced before and after passing through the annular groove 24, the heat transfer rate is increased and the cooling performance is improved.

図５は、実施の形態１に係る冷却流路において、円環状の空隙の隙間高さが冷却能力に与える影響を示したグラフである。図５は、円環状の空隙２３の隙間高さδが冷却能力に与える影響について、計算で得られた結果の一例を示す。温度は、供給口側ヘッダ流路２１及び排出口側ヘッダ流路２２及び円環状の空隙２３を円周方向に分割し、各分割流路間の流量及び圧力のバランス計算を行い、得られた各分割流路の流量から流速を算出し、流速から熱伝達率の計算式を用いて温度を算出した。   FIG. 5 is a graph showing the influence of the gap height of the annular gap on the cooling capacity in the cooling flow path according to the first embodiment. FIG. 5 shows an example of a result obtained by calculation regarding the influence of the gap height δ of the annular gap 23 on the cooling capacity. The temperature was obtained by dividing the supply port side header flow channel 21, the discharge port side header flow channel 22 and the annular gap 23 in the circumferential direction, and calculating the balance between the flow rate and pressure between the divided flow channels. The flow rate was calculated from the flow rate of each divided flow path, and the temperature was calculated from the flow rate using a formula for calculating the heat transfer coefficient.

図５においては、冷却能力を縦軸とすると共に、隙間高さδ（ｍｍ）を横軸とした。ここで、隙間高さδ（ｍｍ）は、円環状の空隙２３の幅であり、固定子鉄心１１の軸方向と垂直な方向における円環状の空隙２３の距離である。冷却能力（Ｗ／Ｋ）は、回転電機発熱量（Ｗ）／固定子鉄心温度上昇値（Ｋ）によって求められる比率であると、ここでは定義する。図５は、円環状の空隙２３の隙間高さδが１．０ｍｍのとき、回転電機の発熱量を固定子鉄心１１の温度上昇値で除算した値を１００としたときの関係を示している。図５の結果によれば、固定子鉄心１１の軸方向と垂直な方向の幅である隙間高さδが１．０ｍｍ以下のときに高い冷却性能を発揮することが確認された。また、隙間高さδが０．５ｍｍ以下のときにさらに高い冷却性能が発揮された。これらの結果から、円環状の空隙２３の隙間高さδは、同心円の径方向の距離が１．０ｍｍ以下、より好ましくは０．５ｍｍ以下の値とすることで、冷却性能が発揮することが確認された。   In FIG. 5, the vertical axis is the cooling capacity, and the horizontal axis is the gap height δ (mm). Here, the gap height δ (mm) is the width of the annular gap 23 and is the distance of the annular gap 23 in the direction perpendicular to the axial direction of the stator core 11. The cooling capacity (W / K) is defined here as a ratio determined by the amount of heat generated by the rotating electrical machine (W) / the stator core temperature rise value (K). FIG. 5 shows the relationship when the value obtained by dividing the heat generation amount of the rotating electrical machine by the temperature rise value of the stator core 11 is 100 when the gap height δ of the annular gap 23 is 1.0 mm. . According to the result of FIG. 5, it was confirmed that high cooling performance is exhibited when the gap height δ, which is the width in the direction perpendicular to the axial direction of the stator core 11, is 1.0 mm or less. Further, when the gap height δ was 0.5 mm or less, higher cooling performance was exhibited. From these results, the clearance height δ of the annular gap 23 can exhibit cooling performance when the radial distance of the concentric circles is 1.0 mm or less, more preferably 0.5 mm or less. confirmed.

図６は、実施の形態１に係る環状溝の幅ｗと深さｈとの比（ｗ／ｈ）が冷却能力に与える影響を示したグラフである。図６では、環状溝２４の幅ｗと深さｈとの比（ｗ／ｈ）について、有限体積法による数値解析で得られた結果の一例を示す。図６に示すように、環状溝２４の幅ｗと深さｈとの比（ｗ／ｈ）が１０、かつ環状溝２４の深さｈと円環状の空隙２３の隙間高さδとの比（ｈ／δ）が１．０のときにおいて、回転電機発熱量を固定子鉄心１１の温度上昇値で除算した値を１００としたときの関係を示している。   FIG. 6 is a graph showing the effect of the ratio (w / h) between the width w and the depth h of the annular groove according to the first embodiment on the cooling capacity. FIG. 6 shows an example of the result obtained by numerical analysis by the finite volume method with respect to the ratio (w / h) between the width w and the depth h of the annular groove 24. As shown in FIG. 6, the ratio (w / h) between the width w and the depth h of the annular groove 24 is 10, and the ratio between the depth h of the annular groove 24 and the gap height δ of the annular gap 23. When (h / δ) is 1.0, the relationship when the value obtained by dividing the amount of heat generated by the rotating electrical machine by the temperature rise value of the stator core 11 is 100 is shown.

図６によれば、環状溝２４の幅ｗと深さｈとの比（ｗ／ｈ）が５から１０の間の条件が５≦（ｗ／ｈ）≦１０で、かつ環状溝２４の深さｈと隙間高さδの比（ｈ／δ）が１．０から１．８の間の条件、すなわち１．０≦（ｈ／δ）≦１．８において、高い冷却効果を発揮することが確認された。   According to FIG. 6, the condition that the ratio (w / h) of the width w to the depth h of the annular groove 24 is 5 to 10 is 5 ≦ (w / h) ≦ 10, and the depth of the annular groove 24 is High cooling effect is exhibited under the condition that the ratio of the height h to the gap height δ (h / δ) is 1.0 to 1.8, that is, 1.0 ≦ (h / δ) ≦ 1.8. Was confirmed.

よって、環状溝２４の幅ｗと深さｈとの比（ｗ／ｈ）が５から１０の間の範囲において、環状溝２４の深さｈと隙間高さδとの比（ｈ／δ）を１．０から１．８の間の範囲とすることで、高い冷却性能が発揮されることが確認された。   Therefore, in the range where the ratio (w / h) between the width w and the depth h of the annular groove 24 is between 5 and 10, the ratio (h / δ) between the depth h of the annular groove 24 and the gap height δ. It was confirmed that a high cooling performance is exhibited by setting the value between 1.0 and 1.8.

図７は、実施の形態１に係る供給口側ヘッダ流路、円環状の空隙及び排出口側ヘッダ流路の断面図である。図８は、図７のVIII−VIII線断面図である。図７において、供給口側ヘッダ流路２１又は排出口側ヘッダ流路２２の断面積をＡとし、図８において、円環状の空隙２３の断面積をＢとする。断面積Ａは、図７中の網掛け部分の面積である。断面積Ｂは、図８中の白抜き部分の面積である。   FIG. 7 is a cross-sectional view of the supply port side header flow path, the annular gap, and the discharge port side header flow path according to the first embodiment. 8 is a cross-sectional view taken along line VIII-VIII in FIG. In FIG. 7, the cross-sectional area of the supply port side header flow path 21 or the discharge port side header flow path 22 is A, and in FIG. The cross-sectional area A is the area of the shaded portion in FIG. The cross-sectional area B is the area of the white portion in FIG.

図９は、実施の形態１において、円環状の空隙内の流速比に与える流路断面積比の影響を示したグラフである。円環状の空隙２３内の流速比に与える流路断面積比（Ａ／Ｂ）の影響について図５と同様の計算方法によって得られた結果の一例を示したものである。ここで、円環状の空隙２３内の流速比とは、円周方向に生じる流速分布の最大流速を最小流速で除算した値である。   FIG. 9 is a graph showing the influence of the channel cross-sectional area ratio on the flow velocity ratio in the annular gap in the first embodiment. FIG. 6 shows an example of a result obtained by the same calculation method as in FIG. 5 with respect to the influence of the channel cross-sectional area ratio (A / B) on the flow rate ratio in the annular gap 23. FIG. Here, the flow rate ratio in the annular gap 23 is a value obtained by dividing the maximum flow rate of the flow rate distribution generated in the circumferential direction by the minimum flow rate.

図９に示すように、流路断面積比（Ａ／Ｂ）が０．２の場合に流速比が概ね１になることが確認された。流速比を１に近づけることで回転電機を円周方向に均一かつ効率的に冷却することができる。なお、円環状の空隙２３の隙間高さδは、δ＝１．００ｍｍ（図９中の菱形黒印）及びδ＝０．１５ｍｍ（図９中の×印）とした。   As shown in FIG. 9, it was confirmed that the flow rate ratio was approximately 1 when the channel cross-sectional area ratio (A / B) was 0.2. By making the flow rate ratio close to 1, the rotating electrical machine can be cooled uniformly and efficiently in the circumferential direction. The clearance height δ of the annular gap 23 was set to δ = 1.00 mm (diamond black mark in FIG. 9) and δ = 0.15 mm (x mark in FIG. 9).

実施の形態１において、第１の筒状部材１２と第２の筒状部材１３との一部を段加工して段付き円筒状構造を形成している。図１０は、実施の形態１に係る回転電機冷却装置の段付き円筒状構造の断面図である。図１０に示すように、段付き円筒状構造は、突出段付部１２Ａと、切欠部１３Ａとを有している。突出段付部１２Ａは、第１の筒状部材１２の排出口１５側に形成されて、軸Ｚｒ方向と直交する外周方向で円周方向にわたって段加工して第２の筒状部材１３側に突出する。切欠部１３Ａは、第２の筒状部材１３の排出口１５側に形成される。切欠部１３Ａは、第２の筒状部材１３の円周方向にわたって切欠き加工される。回転電機を組み立てる際には、突出段付部１２Ａの内側端面１２Ｂと、切欠部１３Ａの軸Ｚｒ方向の外側端面１３Ｂとを接触させてから固定することにより、段付き円筒状構造が形成される。   In the first embodiment, a part of the first cylindrical member 12 and the second cylindrical member 13 is stepped to form a stepped cylindrical structure. FIG. 10 is a cross-sectional view of the stepped cylindrical structure of the rotating electrical machine cooling apparatus according to the first embodiment. As shown in FIG. 10, the stepped cylindrical structure has a protruding stepped portion 12A and a cutout portion 13A. The projecting stepped portion 12A is formed on the discharge port 15 side of the first cylindrical member 12, and is stepped in the circumferential direction in the outer circumferential direction orthogonal to the axis Zr direction on the second cylindrical member 13 side. Protruding. The cutout portion 13A is formed on the discharge port 15 side of the second cylindrical member 13. The cutout portion 13 </ b> A is cutout in the circumferential direction of the second cylindrical member 13. When assembling the rotating electrical machine, a stepped cylindrical structure is formed by contacting and fixing the inner end surface 12B of the protruding stepped portion 12A and the outer end surface 13B of the cutout portion 13A in the axis Zr direction. .

すなわち、第１の筒状部材１２の突出段付部１２Ａの内側端面１２Ｂと、第２の筒状部材１３の切欠部１３Ａの外側端面１３Ｂとを接触させてから固定することにより、排出口側ヘッダ流路２２の流路を形成する際における位置決めを容易にすることが可能となる。従って、回転電機は組立性が良好な構造となるので、組立作業の簡素化を図ることができる。   That is, by fixing the inner end surface 12B of the protruding stepped portion 12A of the first cylindrical member 12 and the outer end surface 13B of the cutout portion 13A of the second cylindrical member 13, the outlet side Positioning when forming the flow path of the header flow path 22 can be facilitated. Therefore, the rotating electric machine has a structure with good assemblability, and the assembling work can be simplified.

実施の形態１に係る冷却流路２０は、環状溝２４のピッチｐが均等となるが、環状溝２４のピッチｐは不均等であってもよい。また、供給口側ヘッダ流路２１の断面積及び排出口側ヘッダ流路２２の断面積は等しくなくてもよい。   In the cooling channel 20 according to the first embodiment, the pitch p of the annular groove 24 is equal, but the pitch p of the annular groove 24 may be unequal. Moreover, the cross-sectional area of the supply port side header flow path 21 and the cross-sectional area of the discharge port side header flow path 22 may not be equal.

実施の形態１に係る冷却流路２０は、円環状の空隙２３の隙間高さδを円筒の軸Ｚｒ方向に一定の値としたが、隙間高さはこれに限定されるものではない。円環状の空隙２３は、軸Ｚｒ方向に隙間高さδが異なる位置を有してもよい。また、円筒の軸Ｚｒ方向に沿って不等の値を持つテーパ構造又は段付構造となるようにしてもよい。   In the cooling channel 20 according to the first embodiment, the gap height δ of the annular gap 23 is set to a constant value in the direction of the axis Zr of the cylinder, but the gap height is not limited to this. The annular gap 23 may have a position where the gap height δ differs in the direction of the axis Zr. Moreover, you may make it become a taper structure or a stepped structure which has an unequal value along the axis Zr direction of a cylinder.

実施の形態１に係る回転電機冷却装置１０の冷却流路２０は、供給口１４と排出口１５とに各々連通する円環状の供給口側ヘッダ流路２１及び排出口側ヘッダ流路２２と、供給口側ヘッダ流路２１及び排出口側ヘッダ流路２２を結び、冷却液１６が通過する円環状の空隙２３と、第１の筒状部材１２の円環状の空隙２３面に形成されて、第１の筒状部材１２の軸Ｚｒ方向に対して垂直で独立な複数の環状溝２４と、を有する。本構造により、供給された冷却液１６は、供給口側ヘッダ流路２１において第１の筒状部材１２の円周方向３１に流れる。供給口側ヘッダ流路２１内の全周に広がった冷却液１６は、円環状の空隙２３では第１の筒状部材１２の軸方向３２に流れる。そして、排出口側ヘッダ流路２２では再び円周方向３３に流れ、排出口１５から排出される。   The cooling flow path 20 of the rotating electrical machine cooling device 10 according to the first embodiment includes an annular supply port side header flow path 21 and a discharge port side header flow path 22 that communicate with the supply port 14 and the discharge port 15, respectively. The supply port side header flow path 21 and the discharge port side header flow path 22 are connected to each other and formed in an annular gap 23 through which the coolant 16 passes and an annular gap 23 surface of the first cylindrical member 12. A plurality of annular grooves 24 that are perpendicular to the axis Zr direction of the first cylindrical member 12 and independent. With this structure, the supplied coolant 16 flows in the circumferential direction 31 of the first cylindrical member 12 in the supply port side header flow path 21. The coolant 16 that has spread all around the supply port side header flow path 21 flows in the axial direction 32 of the first tubular member 12 through the annular gap 23. Then, it flows again in the circumferential direction 33 in the discharge port side header flow path 22 and is discharged from the discharge port 15.

円環状の空隙２３を通過する冷却液１６は、一定間隔に設けられた複数の独立した環状溝２４を横切って流れる際に、各環状溝２４で温度境界層５１，５２の発達が抑制され、熱伝達率が上昇するので冷却性能が向上する。また、流路形状が単純であるので、圧力損失の増加を抑制できる上、加工コストの増加を抑制できる。従って、実施の形態１に係る回転電機冷却装置１０の冷却流路２０によれば、圧力損失及び加工コストの増加を抑えながら、冷却能力の高い冷却ができる回転電機冷却装置１０を提供することができる。固定子鉄心１１の軸Ｚｒ方向の長さが大きくなり、円環状の空隙２３の流路が長くなった場合も、複数の独立した環状溝２４により温度境界層５１，５２の発達が抑制されるので、冷却能力を向上させることができる。   When the coolant 16 passing through the annular gap 23 flows across a plurality of independent annular grooves 24 provided at regular intervals, the development of the temperature boundary layers 51 and 52 is suppressed in each annular groove 24, Since the heat transfer rate is increased, the cooling performance is improved. Moreover, since the flow path shape is simple, an increase in pressure loss can be suppressed, and an increase in processing cost can be suppressed. Therefore, according to the cooling flow path 20 of the rotating electrical machine cooling device 10 according to the first embodiment, it is possible to provide the rotating electrical machine cooling device 10 capable of cooling with high cooling capacity while suppressing an increase in pressure loss and processing cost. it can. Even when the length of the stator core 11 in the axis Zr direction increases and the flow path of the annular gap 23 becomes longer, the development of the temperature boundary layers 51 and 52 is suppressed by the plurality of independent annular grooves 24. Therefore, the cooling capacity can be improved.

環状溝２４の窪みの形状は、実施の形態１のような断面矩形状に限定されず、断面三角形状、又は断面半円形状とすることもできる。また、環状溝２４の窪みは、これらの形状を混合したものとすることもできる。環状溝２４の深さｈも一定とせず、異なる深さとするようにしてもよい。例えば、冷却能力の低下しやすい下流側の環状溝２４を上流側の環状溝２４に比べて深くしてもよい。   The shape of the recess of the annular groove 24 is not limited to the rectangular cross section as in the first embodiment, but may be a triangular cross section or a semicircular cross section. Further, the recess of the annular groove 24 may be a mixture of these shapes. The depth h of the annular groove 24 is not constant and may be different. For example, the downstream annular groove 24 where the cooling capacity tends to decrease may be deeper than the upstream annular groove 24.

環状溝２４同士の溝間のピッチｐが均等配置又は不均等配置となるようにしてもよい。さらに、予め発熱分布の傾向を求め、傾向を求めた発熱分布に対応するように、環状溝２４のピッチｐを変化させるようにして冷却してもよい。   The pitch p between the grooves of the annular grooves 24 may be arranged uniformly or non-uniformly. Furthermore, the tendency of the heat generation distribution may be obtained in advance, and cooling may be performed by changing the pitch p of the annular groove 24 so as to correspond to the heat generation distribution for which the tendency has been obtained.

図１１は、実施の形態１に係る変形例の環状溝を設けた第１の筒状部材と第２の筒状部材とから形成される円環状の空隙の断面図である。図１１に示すように、変形例では、第１の筒状部材１２の円環状の空隙２３側の面に形成される複数の環状溝２４のピッチｐを供給口１４側よりも排出口１５側で狭くなるように変更するようにしている。本変形例では、冷却液１６の供給口側ヘッダ流路２１側からの環状溝２４の配置のピッチｐを、最初の供給口１４側の領域では相対的に間隔を広いピッチｐ1とし、排出口１５側の領域では相対的に間隔を狭いピッチｐ3とし、中央の領域ではピッチｐ1とピッチｐ３との中間のピッチｐ2とすることで、冷却液１６が環状溝２４を横切って流れる際の温度境界層の発達の抑制の頻度を異ならせている。従って、供給口１４側の領域では熱伝達率は低く、排出口１５側の領域は熱伝達率が高く、中央の領域では熱伝達率は中間程度となる。FIG. 11 is a cross-sectional view of an annular gap formed by a first cylindrical member and a second cylindrical member provided with an annular groove according to a modification of the first embodiment. As shown in FIG. 11, in the modification, the pitch p of the plurality of annular grooves 24 formed on the surface of the first cylindrical member 12 on the annular gap 23 side is set to the outlet 15 side than the supply port 14 side. It changes so that it may become narrow. In this modification, the pitch p of the arrangement of the annular grooves 24 from the supply port side header flow path 21 side of the coolant 16 is set to a pitch p 1 having a relatively wide interval in the first supply port 14 side region. In the region on the outlet 15 side, the pitch p 3 is relatively narrow, and in the center region, the pitch p 2 is intermediate between the pitch p 1 and the pitch p 3 so that the coolant 16 crosses the annular groove 24. The frequency of suppression of the development of the temperature boundary layer during flow is varied. Accordingly, the heat transfer rate is low in the region on the supply port 14 side, the heat transfer rate is high in the region on the discharge port 15 side, and the heat transfer rate is intermediate in the central region.

例えば、本実施の形態を用いない場合、供給口１４側から排出口１５側に向かって冷却液１６の温度が上がるのに伴って熱伝導率が低下し、供給口１４側に比べて排出口１５側で固定子鉄心１１の熱が冷却されにくいとする。このような場合に、供給口１４側に比べて排出口１５側で環状溝２４のピッチｐを狭くすることによって、固定子鉄心１１の熱が冷却されにくい排出口１５側の熱伝導率が高くなり、排出口１５側の固定子鉄心１１の冷却を促進することができる。このように、冷却性能を領域毎に制御することもできる。   For example, when this embodiment is not used, as the temperature of the coolant 16 increases from the supply port 14 side toward the discharge port 15 side, the thermal conductivity decreases, and the discharge port becomes smaller than the supply port 14 side. It is assumed that the heat of the stator core 11 is hardly cooled on the 15th side. In such a case, by reducing the pitch p of the annular groove 24 on the discharge port 15 side compared to the supply port 14 side, the heat conductivity on the discharge port 15 side where the heat of the stator core 11 is difficult to be cooled is high. Thus, cooling of the stator core 11 on the discharge port 15 side can be promoted. In this way, the cooling performance can be controlled for each region.

尚、本実施の形態では、環状溝２４は円状に連続して一周する溝とした。環状溝２４が円状に一部断続している場合、その断続する箇所において温度境界層の厚さが大きいままとなるため、本実施の形態の効果が十分得られない。   In the present embodiment, the annular groove 24 is a groove that continuously makes a circle. When the annular groove 24 is partially interrupted in a circular shape, the thickness of the temperature boundary layer remains large at the intermittent location, so that the effect of the present embodiment cannot be sufficiently obtained.

また、本実施の形態では、環状溝２４は円状に連続して一周する溝としたが、環状溝２４が螺旋状に設けられている場合、冷却液１６の流路が螺旋状の溝に沿って螺旋状に変化してしまう。そのため、圧力損失が大きくなり、冷却ポンプの負荷が大きくなってしまう。また、螺旋状の溝を形成するためには、加工コストが高くなる。   Further, in the present embodiment, the annular groove 24 is a groove that continuously makes a circle, but when the annular groove 24 is provided in a spiral shape, the flow path of the coolant 16 is a spiral groove. It changes spirally along. As a result, the pressure loss increases and the load on the cooling pump increases. Moreover, in order to form a spiral groove, processing cost becomes high.

本実施の形態に係る回転電機冷却装置１０によれば、円状に連続して一周する環状溝２４を備えたので、圧力損失及び加工コストの増加を抑制しながら冷却性能を向上する効果が得られる。   According to the rotating electrical machine cooling apparatus 10 according to the present embodiment, since the annular groove 24 that continuously makes a circle is provided, an effect of improving the cooling performance while suppressing an increase in pressure loss and processing cost is obtained. It is done.

実施の形態２．
図１２は、実施の形態２に係る回転電機冷却装置を示す断面図である。図１２に示すように、実施の形態２に係る回転電機冷却装置１０ａは、第２の筒状部材１３の両端部に供給口側ヘッダ流路２１及び排出口側ヘッダ流路２２を形成するものである。第１の筒状部材１２は、強度を確保するため、肉厚をある程度大きくする必要がある。例えば図１に示すように、実施の形態１の第１の筒状部材１２においては、強度確保の関係から供給口側ヘッダ流路２１及び排出口側ヘッダ流路２２を形成するには、溝加工深さ限界である第２の基準面４２よりも供給口側ヘッダ流路２１及び排出口側ヘッダ流路２２を深く加工することができない。Embodiment 2. FIG.
FIG. 12 is a cross-sectional view showing the rotating electrical machine cooling apparatus according to the second embodiment. As shown in FIG. 12, the rotating electrical machine cooling device 10 a according to Embodiment 2 forms a supply port side header flow path 21 and a discharge port side header flow path 22 at both ends of the second tubular member 13. It is. The first tubular member 12 needs to have a certain thickness to ensure strength. For example, as shown in FIG. 1, in the first tubular member 12 of the first embodiment, a groove is formed to form the supply port side header flow path 21 and the discharge port side header flow path 22 from the relationship of ensuring strength. The supply port side header flow path 21 and the discharge port side header flow path 22 cannot be processed deeper than the second reference surface 42 that is the processing depth limit.

実施の形態２においては、第２の筒状部材１３の内面側に、供給口１４と排出口１５とに連通する円環状の供給口側ヘッダ流路２１及び排出口側ヘッダ流路２２を設けて、ヘッダ用の供給流路を形成する。ヘッダ用の供給流路を形成する構造により、円環状の空隙２３に形成される環状溝２４の加工面を第２の基準面４２の近くに形成することができる。これにより、発熱源である固定子鉄心１１と円環状の空隙２３との間における熱伝導の距離Ｌが小さくなるので、冷却性能が向上する。従って、円環状の空隙２３と発熱源との距離Ｌが接近するので、冷却液１６と発熱源との間の熱抵抗が減少し、冷却性能の向上を図ることができる。   In the second embodiment, an annular supply port side header flow path 21 and discharge port side header flow path 22 communicating with the supply port 14 and the discharge port 15 are provided on the inner surface side of the second cylindrical member 13. Thus, a header supply channel is formed. The processed surface of the annular groove 24 formed in the annular gap 23 can be formed near the second reference surface 42 by the structure that forms the supply flow path for the header. As a result, the distance L of heat conduction between the stator core 11 serving as a heat generation source and the annular gap 23 is reduced, so that the cooling performance is improved. Therefore, since the distance L between the annular gap 23 and the heat generation source approaches, the thermal resistance between the coolant 16 and the heat generation source decreases, and the cooling performance can be improved.

図１３は、実施の形態１及び実施の形態２と従来の構造とにおける冷却能力について、有限体積法を用いて数値解析した結果の比較図である。なお、従来の構造は、環状溝２４を有さない。図１３に示すように、実施の形態１は、従来の構造よりも回転電機を効率よく冷却でき、圧力の損失及び加工コストの増加を抑制できる。また、実施の形態２は熱伝導の距離Ｌを小さくすることができ、実施の形態１よりもさらに冷却能力の向上を図ることができる。   FIG. 13 is a comparison diagram of the results of numerical analysis using the finite volume method for the cooling capacity in the first and second embodiments and the conventional structure. The conventional structure does not have the annular groove 24. As shown in FIG. 13, the first embodiment can cool the rotating electrical machine more efficiently than the conventional structure, and can suppress pressure loss and processing cost increase. In the second embodiment, the heat conduction distance L can be reduced, and the cooling capacity can be further improved as compared with the first embodiment.

実施の形態３．
図１４は、実施の形態３に係る回転電機冷却装置を示す断面図である。図１４に示すように、実施の形態３に係る回転電機冷却装置１０ｂは、第１の筒状部材１２と第２の筒状部材１３との一部を加工して第１及び第２の段付き円筒状構造を形成している。第１の段付き円筒状構造は、突出段付部１２Ａと、切欠部１３Ａとを有する。突出段付部１２Ａは、第１の筒状部材１２に形成され、排出口１５側の内側端面１２Ｂである外周側面が第２の筒状部材１３側に突出して形成される。すなわち、突出段付部１２Ａは、円周方向にわたって、軸Ｚｒ方向と直交する方向、すなわち第１の筒状部材１２の径方向に沿って、第２の基準面４２から突出する。切欠部１３Ａは、第２の筒状部材１３に形成され、排出口１５側の外側端面１３Ｂである内周側面に凹みが形成される。そして、第１の筒状部材１２の突出段付部１２Ａの排出口１５側の内側端面１２Ｂの外周側面と、第２の筒状部材１３の切欠部１３Ａの排出口１５側の外側端面１３Ｂである内周側面と、が排出口側ヘッダ流路２２を介して対向するように固定される。突出段付部１２Ａ及び切欠部１３Ａが、円周方向にわたって切欠き加工される回転電機が組み立てられる際には、突出段付部１２Ａの内側端面１２Ｂの外周側面と、軸Ｚｒ方向における切欠部１３Ａの外側端面１３Ｂである内周側面と、を排出口１５の径よりも離して対向させて組み合わせる。組立後、排出口側ヘッダ流路２２が形成される。Embodiment 3 FIG.
FIG. 14 is a cross-sectional view showing the rotating electrical machine cooling apparatus according to the third embodiment. As shown in FIG. 14, the rotating electrical machine cooling apparatus 10b according to the third embodiment processes a part of the first cylindrical member 12 and the second cylindrical member 13 to produce first and second stages. A cylindrical structure is formed. The first stepped cylindrical structure has a protruding stepped portion 12A and a cutout portion 13A. The protruding stepped portion 12A is formed in the first cylindrical member 12, and the outer peripheral side surface which is the inner end surface 12B on the discharge port 15 side is formed to protrude toward the second cylindrical member 13 side. That is, the protruding stepped portion 12A protrudes from the second reference surface 42 along the direction orthogonal to the axis Zr direction, that is, the radial direction of the first cylindrical member 12 over the circumferential direction. The cutout portion 13A is formed in the second cylindrical member 13, and a recess is formed on the inner peripheral side surface that is the outer end surface 13B on the discharge port 15 side. Then, the outer peripheral side surface of the inner end surface 12B on the discharge port 15 side of the protruding stepped portion 12A of the first cylindrical member 12 and the outer end surface 13B of the cutout portion 13A of the second cylindrical member 13 on the discharge port 15 side. It fixes so that a certain inner peripheral side may oppose via the discharge port side header flow path 22. FIG. When a rotating electrical machine in which the protruding stepped portion 12A and the cutout portion 13A are cut out in the circumferential direction is assembled, the outer peripheral side surface of the inner end surface 12B of the protruding stepped portion 12A and the cutout portion 13A in the axis Zr direction. The inner peripheral side surface, which is the outer end surface 13B, is combined with the inner peripheral side surface facing away from the diameter of the discharge port 15. After the assembly, the discharge port side header flow path 22 is formed.

よって、排出口１５の径は、突出段付部１２Ａの内側端面１２Ｂである外周側面と、切欠部１３Ａの外側端面１３Ｂである内周側面と、の間の距離よりも短いものとなる。   Therefore, the diameter of the discharge port 15 is shorter than the distance between the outer peripheral side surface that is the inner end surface 12B of the protruding stepped portion 12A and the inner peripheral side surface that is the outer end surface 13B of the notch 13A.

また、第２の段付き円筒状構造は、第２突出段付部１３Ｃと、切欠部１２Ｃとを有する。第２突出段付部１３Ｃは、第２の筒状部材１３の供給口１４に形成され、供給口１４側の内側端面１３Ｄである外周側面に凹みが形成される。第２突出段付部１３Ｃは、軸Ｚｒ方向と直交する内周方向に円周方向にわたって、第２の基準面４２側へ突出する。切欠部１２Ｃは、第１の筒状部材１２の供給口１４側の内周側面１２Ｄが円周方向にわたって形成される。回転電機が組み立てられる際には、第２突出段付部１３Ｃの供給口１４側の内側端面１３Ｄの外周側面と、切欠部１２Ｃの軸Ｚｒ方向の供給口１４側の内周側面１２Ｄとを離して、供給側の扁平な供給口側ヘッダ流路２１が形成される。これにより、軸Ｚｒ方向における供給口側ヘッダ流路２１の長さを大きくした扁平の流路が形成されている。   The second stepped cylindrical structure includes a second protruding stepped portion 13C and a notch 12C. The second protruding stepped portion 13C is formed in the supply port 14 of the second cylindrical member 13, and a recess is formed in the outer peripheral side surface that is the inner end surface 13D on the supply port 14 side. The second protruding stepped portion 13C protrudes toward the second reference surface 42 over the circumferential direction in the inner circumferential direction orthogonal to the axis Zr direction. In the cutout portion 12C, an inner peripheral side surface 12D on the supply port 14 side of the first cylindrical member 12 is formed over the circumferential direction. When the rotating electrical machine is assembled, the outer peripheral side surface of the inner end surface 13D on the supply port 14 side of the second protruding stepped portion 13C is separated from the inner peripheral side surface 12D on the supply port 14 side in the axis Zr direction of the notch portion 12C. Thus, a flat supply port side header flow path 21 on the supply side is formed. Thereby, the flat flow path which enlarged the length of the supply port side header flow path 21 in the axis Zr direction is formed.

実施の形態３の回転電機冷却装置１０ｂは、実施の形態２と同様に、円環状の空隙２３を溝加工深さ限界の第２の基準面４２近くに形成できるので、固定子鉄心１１と円環状の空隙２３間との熱伝導の距離Ｌが小さくなり冷却性が向上する。また、実施の形態２とは異なり、供給口側ヘッダ流路２１を設ける際、第２の筒状部材１３の内面側を溝加工する必要がないので、加工コストが低減できる。   In the rotating electrical machine cooling apparatus 10b according to the third embodiment, the annular gap 23 can be formed near the second reference plane 42 at the groove processing depth limit as in the second embodiment. The distance L of heat conduction between the annular gaps 23 is reduced, and the cooling performance is improved. Further, unlike the second embodiment, when the supply port side header flow path 21 is provided, it is not necessary to groove the inner surface side of the second cylindrical member 13, so that the processing cost can be reduced.

以上の実施の形態に示した構成は、本発明の内容の一例を示すものであり、別の公知の技術と組み合わせることも可能であるし、本発明の要旨を逸脱しない範囲で、構成の一部を省略、変更することも可能である。   The configuration described in the above embodiment shows an example of the contents of the present invention, and can be combined with another known technique, and can be combined with other configurations without departing from the gist of the present invention. It is also possible to omit or change the part.

１０ 回転電機冷却装置、１１ 固定子鉄心、１２ 第１の筒状部材、１３ 第２の筒状部材、１４ 供給口、１５ 排出口、１６ 冷却液、２０ 冷却流路、２１ 供給口側ヘッダ流路、２２ 排出口側ヘッダ流路、２３ 円環状の空隙、２４ 環状溝、３１，３３ 円周方向、３２ 軸方向、４１ 第１の基準面、４２ 第２の基準面。   DESCRIPTION OF SYMBOLS 10 Rotating electrical machine cooling device, 11 Stator core, 12 1st cylindrical member, 13 2nd cylindrical member, 14 Supply port, 15 Discharge port, 16 Coolant, 20 Cooling flow path, 21 Supply port side header flow Path, 22 outlet-side header flow path, 23 annular gap, 24 annular groove, 31, 33 circumferential direction, 32 axial direction, 41 first reference plane, 42 second reference plane.

Claims (10)

固定子鉄心の外周面に配設された第１の筒状部材と、
前記第１の筒状部材の外周面と円環状の空隙を隔てて配設された第２の筒状部材と、
前記第２の筒状部材の一端側に設けられた供給口から、前記円環状の空隙を通じて前記第２の筒状部材の他端側に設けられた排出口へ冷却液が通過する冷却流路と、を備え、
前記冷却流路は、前記供給口に連通する環状の供給口側ヘッダ流路と、
前記排出口に連通する環状の排出口側ヘッダ流路と、
前記供給口側ヘッダ流路と前記排出口側ヘッダ流路との間に配置され、前記第１の筒状部材の外周面に設けられ、前記供給口側の環状のヘッダ流路及び前記排出口側の環状のヘッダ流路の溝幅よりも狭い溝幅を有し、且つ複数の独立した円状の環状溝と、を有すると共に、
前記供給口側ヘッダ流路内で全周に拡がった冷却液は、前記排出側ヘッダ流路側に向かい前記環状溝の溝方向に直交する軸方向に流れることを特徴とする回転電機冷却装置。 A first tubular member disposed on the outer peripheral surface of the stator core;
A second cylindrical member disposed with an outer circumferential surface of the first cylindrical member and an annular gap therebetween;
A cooling channel through which a coolant passes from a supply port provided on one end side of the second cylindrical member to a discharge port provided on the other end side of the second cylindrical member through the annular gap. And comprising
The cooling flow path is an annular supply port side header flow path communicating with the supply port;
An annular outlet-side header channel communicating with the outlet;
Arranged between the supply port side header flow path and the discharge port side header flow path, provided on the outer peripheral surface of the first tubular member , the supply port side annular header flow path and the discharge port A groove width that is narrower than the groove width of the annular header channel on the side, and a plurality of independent circular annular grooves, and
The rotating electrical machine cooling device according to claim 1, wherein the coolant that has spread over the entire circumference in the supply-portion-side header flow path flows in the axial direction perpendicular to the groove direction of the annular groove toward the discharge-side header flow path. 前記環状溝は、複数設けられることを特徴とする請求項１に記載の回転電機冷却装置。   The rotating electrical machine cooling device according to claim 1, wherein a plurality of the annular grooves are provided. 前記円環状の空隙は、前記固定子鉄心の軸方向と垂直な方向の幅が１．０ｍｍ以下であることを特徴とする請求項１又は２に記載の回転電機冷却装置。   The rotating electrical machine cooling device according to claim 1 or 2, wherein the annular gap has a width in a direction perpendicular to an axial direction of the stator core of 1.0 mm or less. 複数の前記環状溝同士の溝間のピッチは均等であることを特徴とする請求項１から３のいずれか１項に記載の回転電機冷却装置。   The rotating electrical machine cooling device according to any one of claims 1 to 3, wherein pitches between the plurality of annular grooves are uniform. 複数の前記環状溝同士の溝間のピッチは不均等であることを特徴とする請求項１から３のいずれか１項に記載の回転電機冷却装置。   4. The rotating electrical machine cooling device according to claim 1, wherein pitches between the plurality of annular grooves are not uniform. 5. 固定子鉄心の外周面に配設された第１の筒状部材と、
前記第１の筒状部材の外周面と円環状の空隙を隔てて配設された第２の筒状部材と、
前記第２の筒状部材の一端側に設けられた供給口から、前記円環状の空隙を通じて前記第２の筒状部材の他端側に設けられた排出口へ冷却液が通過する冷却流路と、を備え、
前記冷却流路は、前記供給口に連通する環状の供給口側ヘッダ流路と、
前記排出口に連通する環状の排出口側ヘッダ流路と、
前記第１の筒状部材の外周面に設けられた円状の環状溝と、を有し、
複数の前記環状溝同士の溝間のピッチは不均等であると共に、
前記溝間のピッチは、前記供給口側よりも前記排出口側で狭いことを特徴とする回転電機冷却装置。 A first tubular member disposed on the outer peripheral surface of the stator core;
A second cylindrical member disposed with an outer circumferential surface of the first cylindrical member and an annular gap therebetween;
A cooling channel through which a coolant passes from a supply port provided on one end side of the second cylindrical member to a discharge port provided on the other end side of the second cylindrical member through the annular gap. And comprising
The cooling flow path is an annular supply port side header flow path communicating with the supply port;
An annular outlet-side header channel communicating with the outlet;
A circular annular groove provided on the outer peripheral surface of the first tubular member,
The pitch between the plurality of annular grooves is unequal,
The rotating electrical machine cooling device according to claim 1, wherein a pitch between the grooves is narrower on the discharge port side than on the supply port side. 前記環状溝は、複数設けられることを特徴とする請求項６に記載の回転電機冷却装置。   The rotating electrical machine cooling device according to claim 6, wherein a plurality of the annular grooves are provided. 前記円環状の空隙は、前記固定子鉄心の軸方向と垂直な方向の幅が１．０ｍｍ以下であることを特徴とする請求項６又は７に記載の回転電機冷却装置。   The rotating electrical machine cooling device according to claim 6 or 7, wherein the annular gap has a width in a direction perpendicular to an axial direction of the stator core of 1.0 mm or less. 前記第１の筒状部材は、前記排出口側の外周側面が前記第２の筒状部材側に突出して形成された突出段付部を有し、
前記第２の筒状部材は、前記排出口側の内周側面が凹んだ切欠部を有し、
前記排出口側の前記外周側面と、前記排出口側の前記内周側面とが前記排出口側ヘッダ流路を介して対向するように固定されたことを特徴とする請求項１又は６に記載の回転電機冷却装置。 The first cylindrical member has a protruding stepped portion formed by projecting an outer peripheral side surface on the discharge port side toward the second cylindrical member side,
The second cylindrical member has a notch portion in which an inner peripheral side surface on the discharge port side is recessed,
The said outer peripheral side surface by the said discharge port side and the said inner peripheral side surface by the said discharge port side were fixed so that it might oppose through the said discharge port side header flow path. Rotating electric machine cooling device. 前記排出口の径は、前記排出口側の外周側面と前記排出口側の内周側面との間の距離よりも短いことを特徴とする請求項９に記載の回転電機冷却装置。   The rotating electrical machine cooling device according to claim 9, wherein a diameter of the discharge port is shorter than a distance between an outer peripheral side surface on the discharge port side and an inner peripheral side surface on the discharge port side.
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