JPWO2020170344A1

JPWO2020170344A1 - Radial compressor casing and radial compressor

Info

Publication number: JPWO2020170344A1
Application number: JP2021501188A
Authority: JP
Inventors: 保徳渡邊; 良次岡部
Original assignee: Mitsubishi Heavy Industries Engine and Turbocharger Ltd
Current assignee: Mitsubishi Heavy Industries Engine and Turbocharger Ltd
Priority date: 2019-02-20
Filing date: 2019-02-20
Publication date: 2021-11-25
Anticipated expiration: 2039-02-20
Also published as: JP7154372B2; WO2020170344A1

Abstract

スクロール部（７）は、回転軸線（Ｏ）の方向の一方に配置された第一本体部（１１）と、第一本体部（１１）に対して回転軸線（Ｏ）の方向の他方に配置された第二本体部（１２）と、第一本体部（１１）と第二本体部（１２）とを回転軸線（Ｏ）の方向に接合するとともに、スクロール部（７）の流路（ＦＣ）が形成された回転軸線（Ｏ）の方向の範囲内に位置する接合部（１３）と、を有し、第一本体部（１１）には、接合部（１３）よりも径方向の内側に第二本体部（１２）に向かって接合部（１３）を超えて延び、流路（ＦＣ）の内面（７ａ）の一部を形成する環状の凸部（１１ａ）が設けられ、第二本体部（１２）には、流路（ＦＣ）の内面（７ａ）から凹んで凸部（１１ａ）に係合する凹部（１２ａ）が設けられている。The scroll portion (7) is arranged on one side in the direction of the rotation axis (O) and the other side in the direction of the rotation axis (O) with respect to the first main body portion (11). The second main body portion (12), the first main body portion (11), and the second main body portion (12) are joined in the direction of the rotation axis (O), and the flow path (FC) of the scroll portion (7) is joined. ) Is formed with a joint portion (13) located within the range in the direction of the rotation axis (O), and the first main body portion (11) is inside the joint portion (13) in the radial direction. Is provided with an annular convex portion (11a) extending beyond the joint portion (13) toward the second main body portion (12) and forming a part of the inner surface (7a) of the flow path (FC). The main body portion (12) is provided with a concave portion (12a) that is recessed from the inner surface (7a) of the flow path (FC) and engages with the convex portion (11a).

Description

本発明は、ラジアルコンプレッサのケーシング、及びラジアルコンプレッサに関する。 The present invention relates to a casing of a radial compressor and a radial compressor.

コンプレッサの一種としてラジアルコンプレッサが知られている。このラジアルコンプレッサでは、インペラから流出したガスを螺旋状に形成された流路を有するスクロール部に導入し、周方向に案内して吐出するようになっている。スクロール部は、巻き始め側から吐出側に向けて徐々に外形寸法が大きくなっている。 A radial compressor is known as a type of compressor. In this radial compressor, the gas flowing out from the impeller is introduced into a scroll portion having a spirally formed flow path, and is guided in the circumferential direction and discharged. The external dimensions of the scroll portion gradually increase from the winding start side to the discharge side.

ここで、引用文献１、及び引用文献２に記載されたラジアルコンプレッサのように、例えば自動車のターボチャージャに用いられるラジアルコンプレッサのケーシングは、軽量化等のため樹脂製となっている場合がある。 Here, as in the radial compressors described in Cited Document 1 and Cited Document 2, for example, the casing of the radial compressor used in the turbocharger of an automobile may be made of resin for weight reduction or the like.

国際公開第２０１７／１６８７６７号International Publication No. 2017/168767

しかしながら、樹脂はアルミ等の金属と比較して熱伝導率が低いため、特許文献１のコンプレッサのようにケーシングが樹脂製である場合にはケーシングから十分な放熱を行うことが難しい。よって、ケーシングが高温となってケーシングのスクロール部が熱膨張によって大きく変形してしまう可能性がある。またスクロール部には、流路を流通する流体から径方向外側へ向かう圧力が作用する。
特許文献１のコンプレッサでは、ケーシングの第一本体部と第二本体部とを接合することで流路が形成されている。このため、上記の熱膨張や流体の圧力によって、第一本体部と第二本体部との接合部には第一本体部と第二本体部とが離れるように周方向に応力が生じ、接合部に亀裂が生じ、第一本体部と第二本体部との間に隙間が形成されてしまう可能性がある。この結果、コンプレッサの疲労強度が低下する可能性がある。
さらに、第一本体部と第二本体部との隙間に流路内の流体が侵入することで第一本体部と第二本体部とがさらに離れようとして隙間が大きくなり、流体の圧力損失が大きくなってしまう。However, since the resin has a lower thermal conductivity than a metal such as aluminum, it is difficult to sufficiently dissipate heat from the casing when the casing is made of resin as in the compressor of Patent Document 1. Therefore, the casing may become hot and the scroll portion of the casing may be significantly deformed due to thermal expansion. Further, a pressure acting from the fluid flowing through the flow path toward the outside in the radial direction acts on the scroll portion.
In the compressor of Patent Document 1, a flow path is formed by joining the first main body portion and the second main body portion of the casing. Therefore, due to the above-mentioned thermal expansion and fluid pressure, stress is generated in the circumferential direction so that the first main body and the second main body are separated from each other at the joint between the first main body and the second main body, and the joint is joined. There is a possibility that a crack may occur in the portion and a gap may be formed between the first main body portion and the second main body portion. As a result, the fatigue strength of the compressor may decrease.
Further, the fluid in the flow path invades the gap between the first main body and the second main body, so that the first main body and the second main body are further separated from each other and the gap becomes larger, resulting in a pressure loss of the fluid. It gets bigger.

そこで本発明は、疲労強度を向上しつつ、性能向上が可能なラジアルコンプレッサのケーシング、及びラジアルコンプレッサを提供する。 Therefore, the present invention provides a casing of a radial compressor and a radial compressor capable of improving performance while improving fatigue strength.

本発明の第一の態様に係るラジアルコンプレッサのケーシングは、インペラの回転軸線に沿って延びて該回転軸線の方向に開口する筒状をなし、前記インペラに流体を導入する吸気部と、前記吸気部に連通して、前記インペラの外周側で前記回転軸線を中心とした環状に延びる流路を形成する樹脂製のスクロール部と、前記スクロール部の一端に一体に形成されて前記インペラの周方向に沿って延びて開口し、前記流体を前記流路から吐出する吐出部と、を備え、前記スクロール部は、前記回転軸線の方向の一方に配置された第一本体部と、前記第一本体部に対して前記回転軸線の方向の他方に配置された第二本体部と、前記第一本体部と前記第二本体部とを前記回転軸線の方向に接合するとともに、前記流路が形成された前記回転軸線の方向の範囲内に位置する接合部と、を有し、前記第一本体部及び前記第二本体部のうちの一方には、前記接合部よりも前記回転軸線に対する径方向の内側に前記第一本体部及び前記第二本体部のうちの一方から他方に向かって前記接合部を超えて延び、前記流路の内面の一部を形成する前記回転軸線を中心とした環状の凸部が設けられ、前記第一本体部及び前記第二本体部のうちの前記他方には、前記流路の内面から凹んで前記凸部に係合する凹部が設けられている。 The casing of the radial compressor according to the first aspect of the present invention has a tubular shape extending along the rotation axis of the impeller and opening in the direction of the rotation axis, and has an intake portion for introducing a fluid into the impeller and the intake. A resin scroll portion that communicates with the portion and forms an annular flow path centered on the rotation axis on the outer peripheral side of the impeller, and a resin scroll portion integrally formed at one end of the scroll portion in the circumferential direction of the impeller. The scroll portion includes a first main body portion arranged in one direction in the direction of the rotation axis, and the first main body portion, which is provided with a discharge portion extending and opening along the line and discharging the fluid from the flow path. The second main body portion arranged on the other side in the direction of the rotation axis with respect to the portion, the first main body portion and the second main body portion are joined in the direction of the rotation axis, and the flow path is formed. It has a joint located within the range in the direction of the rotation axis, and one of the first main body and the second main body has a radial direction with respect to the rotation axis from the joint. An annular shape centered on the rotation axis that extends inward from one of the first main body and the second main body toward the other beyond the joint and forms a part of the inner surface of the flow path. A convex portion is provided, and the other of the first main body portion and the second main body portion is provided with a concave portion that is recessed from the inner surface of the flow path and engages with the convex portion.

このようなケーシングによれば、接合部を超えて回転軸線の方向に延びてスクロール部の流路の内面を形成する凸部を設けている。このため仮に周方向の応力によって接合部に亀裂が生じたとしても、亀裂をふさぐように凸部が流体の圧力によって径方向外側に押し付けられる。この結果、亀裂の進展速度を低減することができる。また仮に亀裂が生じたとしても、凸部が径方向外側に押し付けられることで亀裂は径方向外側に向かわずに、凸部の根本に回転軸線の方向に向かって進展しようとするため、第一本体部や第二本体部に比べて強度が弱い接合部に亀裂が進展しようとせず、強度の強い第一本体部や第二本体部の内部に向かって進展しようとする。これによっても亀裂の進展速度を低減することができる。
また凸部が流体の圧力によって径方向外側に押し付けられることで、凸部と凹部との隙間が閉じようとするため、この隙間に流体が侵入することを回避できる。よって、流路内の流体の圧力損失を低減することができる。
さらに接合部は、流路が形成された回転軸線の方向の範囲内に位置している。このため、接合部はスクロール部の流路における回転軸線方向の中央の位置に近接して配置されていることになる。この結果、流体の圧力による周方向の応力の影響が大きくなる。しかしこのような場合であっても、上記の凸部によって亀裂の進展を抑えることができるためケーシングの損傷を抑制する効果が得られる。According to such a casing, a convex portion is provided which extends beyond the joint portion in the direction of the rotation axis and forms an inner surface of the flow path of the scroll portion. Therefore, even if a crack is generated in the joint due to the stress in the circumferential direction, the convex portion is pressed outward in the radial direction by the pressure of the fluid so as to close the crack. As a result, the crack growth rate can be reduced. Even if a crack occurs, the convex portion is pressed outward in the radial direction, so that the crack does not go outward in the radial direction but tends to propagate toward the root of the convex portion in the direction of the rotation axis. The crack does not try to grow in the joint part which is weaker than the main body part and the second main body part, but tries to grow toward the inside of the first main body part and the second main body part where the strength is strong. This also makes it possible to reduce the crack growth rate.
Further, since the convex portion is pressed outward in the radial direction by the pressure of the fluid, the gap between the convex portion and the concave portion tends to be closed, so that the fluid can be prevented from entering the gap. Therefore, the pressure loss of the fluid in the flow path can be reduced.
Further, the joint is located within the direction of the rotation axis on which the flow path is formed. Therefore, the joint portion is arranged close to the central position in the flow path of the scroll portion in the direction of the rotation axis. As a result, the influence of the stress in the circumferential direction due to the pressure of the fluid becomes large. However, even in such a case, the protrusions can suppress the growth of cracks, so that the effect of suppressing damage to the casing can be obtained.

また上記のケーシングでは、前記第一本体部は、前記回転軸線の方向を向く第一対向面を有し、前記第二本体部は、前記第一対向面に面接触する第二対向面を有し、前記第一本体部には、前記第一対向面から前記回転軸線の方向に凹んで前記回転軸線を中心として環状に延びる第一環状凹部が設けられ、前記第二本体部には、前記第一環状凹部が設けられた位置に対応する位置で前記第二対向面から前記回転軸線の方向に凹んで前記回転軸線を中心として環状に延びる第二環状凹部が設けられ、前記接合部は、前記第一環状凹部と前記第二環状凹部とによって形成された空間に配置された樹脂部材であってもよい。 Further, in the casing, the first main body portion has a first facing surface facing the direction of the rotation axis, and the second main body portion has a second facing surface that is in surface contact with the first facing surface. The first main body is provided with a first annular recess that is recessed in the direction of the rotation axis from the first facing surface and extends in an annular shape about the rotation axis, and the second main body is provided with the first annular recess. A second annular recess is provided at a position corresponding to the position where the first annular recess is provided, which is recessed in the direction of the rotation axis from the second facing surface and extends in an annular shape around the rotation axis. It may be a resin member arranged in the space formed by the first annular recess and the second annular recess.

このように樹脂部材を接合部に用いることで、第一本体部と第二本体部とをより強固に接合することができる。さらにダイスライドインジェクションを用いて接合部を設け、第一本体部と第二本体部とを接合することができるため、ケーシングの製造を容易化できる。 By using the resin member for the joint portion in this way, the first main body portion and the second main body portion can be joined more firmly. Further, since the joint portion can be provided by using die slide injection and the first main body portion and the second main body portion can be joined, the manufacturing of the casing can be facilitated.

また上記のケーシングでは、前記凸部は、前記径方向の外側を向く凸部外面を有し、前記凸部外面には前記径方向の外側に突出する横凸部が設けられ、前記第一本体部及び前記第二本体部のうちの前記他方は、前記凸部外面に対向する内面を有し、前記内面には前記径方向の外側に凹むとともに、前記横凸部が係合可能な横凹部が設けられていてもよい。 Further, in the casing, the convex portion has a convex outer surface facing outward in the radial direction, and the outer surface of the convex portion is provided with a lateral convex portion protruding outward in the radial direction, and the first main body is provided. The other of the portion and the second main body portion has an inner surface facing the outer surface of the convex portion, and the inner surface is recessed outward in the radial direction, and the lateral convex portion is engaged with the lateral concave portion. May be provided.

凸部の凸部外面に横凸部が設けられ、凸部外面に対向する内面に横凸部に係合可能な横凹部を設けることで、第一本体部と第二本体部とが回転軸線の方向へ相対移動してしまうことを抑制できる。よって、第一本体部と第二本体部とが、互いに回転軸線の方向の変形を規制し合うことができ、ケーシングの疲労強度を向上しつつ、ケーシングの変形に伴う流体の圧縮効率低下を回避できる。 A lateral convex portion is provided on the outer surface of the convex portion of the convex portion, and a lateral concave portion that can be engaged with the lateral convex portion is provided on the inner surface facing the outer surface of the convex portion. It is possible to suppress the relative movement in the direction of. Therefore, the first main body and the second main body can mutually regulate the deformation in the direction of the rotation axis, and while improving the fatigue strength of the casing, the decrease in the compression efficiency of the fluid due to the deformation of the casing is avoided. can.

また上記のケーシングでは、前記第一本体部と前記第二本体部とのうちの前記他方には前記凸部に対して前記径方向の外側に配置されて前記第一本体部と前記第二本体部とのうちの前記他方から前記一方に向けて突出する外側凸部がさらに設けられ、前記第一本体部と前記第二本体部とのうちの前記一方には、前記外側凸部が係合可能な外側凹部が設けられていてもよい。 Further, in the casing, the first main body portion and the second main body portion are arranged on the other side of the first main body portion and the second main body portion on the outer side in the radial direction with respect to the convex portion. An outer convex portion that protrudes from the other of the portions toward the one is further provided, and the outer convex portion engages with the one of the first main body portion and the second main body portion. Possible outer recesses may be provided.

このように凸部に加えてさらに外側凸部を設けることで、第一本体部と第二本体部とが回転軸線の方向に嵌め合うようにして接合部によって接合される。よって回転軸線に対して径方向に互いに位置ずれしてしまうことを回避でき、組立時、運転時に第一本体部と第二本体部とを確実に同軸上に配置することができる。この結果、流体の圧縮効率の向上が可能である。 By further providing the outer convex portion in addition to the convex portion in this way, the first main body portion and the second main body portion are joined by the joint portion so as to be fitted in the direction of the rotation axis. Therefore, it is possible to prevent the positions of the first main body and the second main body from being displaced from each other in the radial direction with respect to the rotation axis, and the first main body and the second main body can be reliably arranged coaxially during assembly and operation. As a result, it is possible to improve the compression efficiency of the fluid.

また本発明の一態様に係るラジアルコンプレッサのケーシングは、インペラの回転軸線に沿って延びて該回転軸線の方向に開口する筒状をなし、前記インペラに流体を導入する吸気部と、前記吸気部に連通して、前記インペラの外周側で前記回転軸線を中心とした環状に延びる流路を形成する樹脂製のスクロール部と、前記スクロール部の一端に一体に設けられて前記インペラの周方向に沿って延びて開口し、前記流体を前記流路から吐出する吐出部と、を備え、前記スクロール部は、前記回転軸線の方向の一方に配置された第一本体部と、前記第一本体部に対して前記回転軸線の方向の他方に配置された第二本体部と、前記第一本体部と前記第二本体部とを前記回転軸線の方向に接合するとともに、前記流路が形成された前記回転軸線の方向の範囲外に位置する接合部と、を有し、前記第一本体部及び前記第二本体部のうちの一方には、前記接合部よりも前記回転軸線に対する径方向の内側に前記第一本体部及び前記第二本体部のうちの一方から他方に向かって前記接合部を超えて延び、前記流路の内面の一部を形成する前記回転軸線を中心とした環状の凸部が設けられ、前記第一本体部及び前記第二本体部のうちの前記他方には、前記流路の内面から凹んで前記凸部に係合する凹部が設けられ、前記第一本体部は、前記回転軸線の方向を向く第一対向面を有し、前記第二本体部は、前記第一対向面に面接触する第二対向面を有し、前記第一本体部には、前記第一対向面から前記回転軸線の方向に凹んで前記回転軸線を中心として環状に延びる第一環状凹部が設けられ、前記第二本体部には、前記第一環状凹部が設けられた位置に対応する位置で前記第二対向面から前記回転軸線の方向に凹んで前記回転軸線を中心として環状に延びる第二環状凹部が設けられ、前記接合部は、前記第一環状凹部と前記第二環状凹部とによって形成された空間に配置された樹脂部材である。 Further, the casing of the radial compressor according to one aspect of the present invention has a tubular shape extending along the rotation axis of the impeller and opening in the direction of the rotation axis, and has an intake portion for introducing a fluid into the impeller and the intake portion. A resin scroll portion that forms an annular flow path centered on the rotation axis on the outer peripheral side of the impeller, and a resin scroll portion that is integrally provided at one end of the scroll portion and is provided in the circumferential direction of the impeller. The scroll portion includes a first main body portion that extends along the opening and discharges the fluid from the flow path, and the scroll portion has a first main body portion arranged in one direction of the rotation axis and the first main body portion. The second main body portion arranged on the other side in the direction of the rotation axis, the first main body portion and the second main body portion are joined in the direction of the rotation axis, and the flow path is formed. It has a joint portion located outside the range in the direction of the rotation axis, and one of the first main body portion and the second main body portion is inside the joint portion in the radial direction with respect to the rotation axis. An annular protrusion centered on the rotation axis that extends from one of the first main body and the second main body toward the other beyond the joint and forms a part of the inner surface of the flow path. A portion is provided, and the other of the first main body portion and the second main body portion is provided with a concave portion that is recessed from the inner surface of the flow path and engages with the convex portion, and the first main body portion is provided. The second main body portion has a second facing surface that is in surface contact with the first facing surface, and the first main body portion has the first facing surface that faces the direction of the rotation axis. A first annular recess that is recessed in the direction of the rotation axis from one facing surface and extends in an annular shape around the rotation axis is provided, and the second main body portion corresponds to a position where the first annular recess is provided. A second annular recess is provided at a position that is recessed in the direction of the rotation axis from the second facing surface and extends in an annular shape around the rotation axis, and the joint portion is formed by the first annular recess and the second annular recess. It is a resin member arranged in the space formed by.

このようなケーシングによれば、仮に流体の圧力によって生じる周方向の応力によって接合部に亀裂が生じたとしても、亀裂をふさぐように凸部が流体の圧力によって径方向外側に押し付けられることで亀裂の進展速度を低減することができる。また仮に亀裂が生じたとしても、凸部が径方向外側に押し付けられることで亀裂は径方向外側に向かわずに、凸部の根本に回転軸線の方向に向かって進展しようとし、即ち、接合部よりも強度の強い第一本体部や第二本体部の内部に向かって進展しようとする。これによっても亀裂の進展速度を低減することができる。
また凸部が流体の圧力によって径方向外側に押し付けられることで、凸部と凹部との隙間が閉じようとするため、この隙間に流体が侵入することを回避できる。よって、流路内の流体の圧力損失を低減することができる。
さらに接合部は、流路が形成された回転軸線の方向の範囲外に位置している。このため、圧縮された流体からの熱の影響や流体からの圧力の影響が接合部へ及びにくくなり、周方向の応力による接合部での亀裂の発生を抑制することができ、ケーシングの損傷を抑制する効果が得られる。According to such a casing, even if a crack is generated in the joint due to the circumferential stress caused by the pressure of the fluid, the convex portion is pressed outward in the radial direction by the pressure of the fluid so as to close the crack. The progress rate of can be reduced. Even if a crack occurs, the convex portion is pressed outward in the radial direction, so that the crack does not go outward in the radial direction but tries to propagate toward the root of the convex portion in the direction of the rotation axis, that is, the joint portion. It tries to advance toward the inside of the first main body and the second main body, which are stronger than the first main body. This also makes it possible to reduce the crack growth rate.
Further, since the convex portion is pressed outward in the radial direction by the pressure of the fluid, the gap between the convex portion and the concave portion tends to be closed, so that the fluid can be prevented from entering the gap. Therefore, the pressure loss of the fluid in the flow path can be reduced.
Further, the joint is located outside the range in the direction of the rotation axis on which the flow path is formed. For this reason, the influence of heat from the compressed fluid and the influence of pressure from the fluid are less likely to reach the joint, and the occurrence of cracks at the joint due to stress in the circumferential direction can be suppressed, causing damage to the casing. The effect of suppressing is obtained.

また本発明の一態様に係るラジアルコンプレッサのケーシングは、インペラの回転軸線に沿って延びて該回転軸線の方向に開口する筒状をなし、前記インペラに流体を導入する吸気部と、
前記吸気部に連通して、前記インペラの外周側で前記回転軸線を中心とした環状に延びる流路を形成する樹脂製のスクロール部と、
前記スクロール部の一端に一体に設けられて前記インペラの周方向に沿って延びて開口し、前記流体を前記流路から吐出する吐出部と、
を備え、
前記スクロール部は、
前記回転軸線の方向の一方に配置された第一本体部と、
前記第一本体部に対して前記回転軸線の方向の他方に配置された第二本体部と、前記第一本体部と前記第二本体部とを前記回転軸線の方向に接合するとともに、前記流路が形成された前記回転軸線の方向の範囲外に位置する接合部と、を有し、前記第一本体部及び前記第二本体部のうちの一方には、前記接合部よりも前記回転軸線に対する径方向の内側に前記第一本体部及び前記第二本体部のうちの一方から他方に向かって前記接合部を超えて延び、前記流路の内面の一部を形成する前記回転軸線を中心とした環状の凸部が設けられ、前記第一本体部及び前記第二本体部のうちの前記他方には、前記流路の内面から凹んで前記凸部に係合する凹部が設けられ、前記凸部は、前記径方向の外側を向く凸部外面を有し、前記凸部外面には前記径方向の外側に突出する横凸部が設けられ、前記第一本体部及び前記第二本体部のうちの前記他方は、前記凸部外面に対向する内面を有し、前記内面には前記径方向の外側に凹むとともに、前記横凸部が係合可能な横凹部が設けられ、前記第一本体部と前記第二本体部とのうちの前記他方には前記凸部に対して前記径方向の外側に配置されて前記第一本体部と前記第二本体部とのうちの前記他方から前記一方に向けて突出する外側凸部がさらに設けられ、前記第一本体部と前記第二本体部とのうちの前記一方には、前記外側凸部が係合可能な外側凹部が設けられている。Further, the casing of the radial compressor according to one aspect of the present invention has a tubular shape extending along the rotation axis of the impeller and opening in the direction of the rotation axis, and has an intake unit for introducing a fluid into the impeller.
A resin scroll portion that communicates with the intake portion and forms an annular flow path centered on the rotation axis on the outer peripheral side of the impeller.
A discharge portion that is integrally provided at one end of the scroll portion and extends and opens along the circumferential direction of the impeller to discharge the fluid from the flow path.
Equipped with
The scroll part is
The first main body portion arranged on one side in the direction of the rotation axis,
The second main body portion arranged on the other side in the direction of the rotation axis with respect to the first main body portion, and the first main body portion and the second main body portion are joined in the direction of the rotation axis, and the flow is described. It has a joint portion located outside the range in the direction of the rotation axis on which the path is formed, and one of the first main body portion and the second main body portion has the rotation axis rather than the joint portion. Centered on the rotation axis that extends from one of the first main body and the second main body toward the other in the radial direction beyond the joint and forms a part of the inner surface of the flow path. An annular convex portion is provided, and the other of the first main body portion and the second main body portion is provided with a concave portion that is recessed from the inner surface of the flow path and engages with the convex portion. The convex portion has a convex outer surface facing outward in the radial direction, and the outer surface of the convex portion is provided with a lateral convex portion protruding outward in the radial direction, and the first main body portion and the second main body portion are provided. The other of the above has an inner surface facing the outer surface of the convex portion, and the inner surface is recessed outward in the radial direction and is provided with a lateral concave portion with which the lateral convex portion can be engaged. The other of the main body and the second main body is arranged on the outer side in the radial direction with respect to the convex portion, and the other of the first main body and the second main body is said to be the same. An outer convex portion that protrudes toward one side is further provided, and one of the first main body portion and the second main body portion is provided with an outer concave portion to which the outer convex portion can engage. ..

このようなケーシングによれば、上記の通り、凸部によって亀裂の進展速度を低減することができるとともに、流路内の流体の圧力損失を低減することができる。さらに、接合部が、流路が形成された回転軸線の方向の範囲外に位置しているため、圧縮された流体からの熱の影響や流体からの圧力の影響が接合部へ及びにくくなる。よって、流体の圧力に起因する周方向の応力による接合部での亀裂の発生を抑制することができ、ケーシングの損傷を抑制する効果が得られる。
さらに、上記のように横凸部によって第一本体部と第二本体部とが、互いに回転軸の方向の変形を規制し合うことができ、ケーシングの疲労強度を向上しつつ、ケーシングの変形に伴う流体の圧縮効率低下を回避できる。また、上記のように外側凸部によって第一本体部と第二本体部とを同軸上に配置でき、流体の圧縮効率の向上が可能である。According to such a casing, as described above, the convex portion can reduce the crack growth rate and reduce the pressure loss of the fluid in the flow path. Further, since the joint is located outside the range in the direction of the rotation axis on which the flow path is formed, the influence of heat from the compressed fluid and the influence of pressure from the fluid are less likely to reach the joint. Therefore, it is possible to suppress the generation of cracks at the joint due to the stress in the circumferential direction caused by the pressure of the fluid, and it is possible to obtain the effect of suppressing the damage to the casing.
Further, as described above, the lateral convex portion allows the first main body portion and the second main body portion to mutually regulate the deformation in the direction of the rotation axis, and while improving the fatigue strength of the casing, the casing is deformed. It is possible to avoid the accompanying decrease in compression efficiency of the fluid. Further, as described above, the first main body portion and the second main body portion can be arranged coaxially by the outer convex portion, and the compression efficiency of the fluid can be improved.

また本発明の一態様に係るラジアルコンプレッサは、インペラと、前記インペラが嵌合して該インペラとともに回転する回転軸と、前記インペラを覆うように設けられた上記のケーシングと、を備えている。 Further, the radial compressor according to one aspect of the present invention includes an impeller, a rotating shaft to which the impeller fits and rotates together with the impeller, and the casing provided so as to cover the impeller.

このようなラジアルコンプレッサでは、上記のケーシングを備えることで、仮に流体の圧力によって生じる周方向の応力によって接合部に亀裂が生じたとしても、凸部によって亀裂の進展速度を低減することができる。また流体の圧力によって凸部と凹部との隙間が閉じようとするため、この隙間に流体が侵入することを回避でき、流路内の流体の圧力損失を低減することができる。 In such a radial compressor, by providing the above-mentioned casing, even if a crack is generated in the joint portion due to the circumferential stress generated by the pressure of the fluid, the crack growth rate can be reduced by the convex portion. Further, since the gap between the convex portion and the concave portion tends to be closed by the pressure of the fluid, it is possible to prevent the fluid from entering the gap and reduce the pressure loss of the fluid in the flow path.

上記のラジアルコンプレッサのケーシング、及びラジアルコンプレッサでは、第一本体部又は第二本体部に凸部を設けたことで、疲労強度を向上しつつ性能向上が可能となる。 In the casing of the radial compressor and the radial compressor described above, by providing the convex portion on the first main body portion or the second main body portion, it is possible to improve the performance while improving the fatigue strength.

本発明の第一実施形態に係るラジアルコンプレッサの全体斜視図である。It is an overall perspective view of the radial compressor which concerns on 1st Embodiment of this invention. 本発明の第一実施形態に係るラジアルコンプレッサのケーシングの要部の縦断面図である。It is a vertical sectional view of the main part of the casing of the radial compressor which concerns on 1st Embodiment of this invention. 本発明の第一実施形態の第一変形例に係るラジアルコンプレッサのケーシングの要部の縦断面図である。It is a vertical sectional view of the main part of the casing of the radial compressor which concerns on the 1st modification of 1st Embodiment of this invention. 本発明の第一実施形態の第二変形例に係るラジアルコンプレッサのケーシングの要部の縦断面図である。It is a vertical sectional view of the main part of the casing of the radial compressor which concerns on the 2nd modification of 1st Embodiment of this invention. 本発明の第二実施形態に係るラジアルコンプレッサのケーシングの要部の縦断面図である。It is a vertical sectional view of the main part of the casing of the radial compressor which concerns on the 2nd Embodiment of this invention. 本発明の第三実施形態に係るラジアルコンプレッサのケーシングの要部の縦断面図である。It is a vertical sectional view of the main part of the casing of the radial compressor which concerns on 3rd Embodiment of this invention. 本発明の第四実施形態に係るラジアルコンプレッサのケーシングの要部の縦断面図である。It is a vertical sectional view of the main part of the casing of the radial compressor which concerns on 4th Embodiment of this invention.

〔第一実施形態〕
以下、本発明の実施形態におけるラジアルコンプレッサ１について説明する。
ラジアルコンプレッサ１（以下、単にコンプレッサ１とする）は、例えば車両に搭載されるターボチャージャ用のコンプレッサである。
図１に示すように、コンプレッサ１は、インペラ２と、インペラ２が嵌合することでインペラ２と一体で回転軸線Ｏを中心として回転する回転軸３と、インペラ２を覆うように設けられたケーシング４とを備えている。[First Embodiment]
Hereinafter, the radial compressor 1 according to the embodiment of the present invention will be described.
The radial compressor 1 (hereinafter, simply referred to as a compressor 1) is, for example, a compressor for a turbocharger mounted on a vehicle.
As shown in FIG. 1, the compressor 1 is provided so as to cover the impeller 2, the rotating shaft 3 that rotates around the rotating axis O integrally with the impeller 2 by fitting the impeller 2, and the impeller 2. It is provided with a casing 4.

次に、ケーシング４について説明する。
ケーシング４は、インペラ２に例えば空気等のガスＧ（流体）を導入する吸気部５と、インペラ２から流出したガスＧが流通してこのガスＧを吐出する吐出部６と、吸気部５と吐出部６とを連通するスクロール部７とを備えている。Next, the casing 4 will be described.
The casing 4 includes an intake unit 5 that introduces a gas G (fluid) such as air into the impeller 2, a discharge unit 6 through which the gas G flowing out of the impeller 2 flows and discharges the gas G, and an intake unit 5. It is provided with a scroll unit 7 that communicates with the discharge unit 6.

吸気部５は、インペラ２に対して回転軸線Ｏの方向の一方に配置されて回転軸３線の方向に延び、回転軸線Ｏの方向の他方に開口する円筒状をなしている。吸気部５は、インペラ２に向かって回転軸線Ｏの方向の一方からガスＧを吸込み、インペラ２内の流路（不図示）に向けてガスＧを導入する。また、吸気部５の材料は、例えば熱可塑性プラスチック等の樹脂（例えば、ＰＰＳ（ポリフェニレンサルファイド）、ＰＰＡ（ポリフタルアミド）、ＰＡ９Ｔ・ＰＡ４６・ＰＡ６Ｔ（ポリアミド）、ＰＢＴ（ポリブチレンテレフタレート）等）である。 The intake unit 5 is arranged in one direction of the rotation axis O with respect to the impeller 2, extends in the direction of the rotation axis 3, and has a cylindrical shape that opens in the other direction in the direction of the rotation axis O. The intake unit 5 sucks the gas G from one of the directions of the rotation axis O toward the impeller 2, and introduces the gas G toward the flow path (not shown) in the impeller 2. The material of the intake unit 5 is, for example, a resin such as a thermoplastic (for example, PPS (polyphenylene sulfide), PPA (polyphthalamide), PA9T / PA46 / PA6T (polyamide), PBT (polybutylene terephthalate), etc.). be.

スクロール部７は、インペラ２及び吸気部５の外周側に配置されている。このスクロール部７は、インペラ２及び回転軸３の周方向に環状に延びる流路ＦＣを有している。吸気部５から導入されたガスＧは、インペラ２内の流路を流通して圧縮された後にこのスクロール部７の流路ＦＣを流通する。スクロール部７は吸気部５と同様の樹脂によって形成されている。スクロール部７の流路ＦＣは、周方向に直交する断面が円形状をなし、周方向の一方に向かって流路断面積が漸次拡大する。これによりスクロール部７は、周方向の一方に吐出部６に向かって外形寸法が漸次拡大する。スクロール部７は、例えば吸気部５と一体の樹脂の射出成形品となっていてもよいし、吸気部５と別体で製造されて吸気部５と接合されていてもよい。 The scroll portion 7 is arranged on the outer peripheral side of the impeller 2 and the intake portion 5. The scroll portion 7 has a flow path FC extending in an annular shape in the circumferential direction of the impeller 2 and the rotation shaft 3. The gas G introduced from the intake unit 5 flows through the flow path in the impeller 2 and is compressed, and then flows through the flow path FC of the scroll unit 7. The scroll portion 7 is made of the same resin as the intake portion 5. The flow path FC of the scroll portion 7 has a circular cross section orthogonal to the circumferential direction, and the cross-sectional area of the flow path gradually expands toward one of the circumferential directions. As a result, the scroll portion 7 gradually expands in external dimensions toward the discharge portion 6 in one of the circumferential directions. The scroll portion 7 may be, for example, an injection molded product of a resin integrated with the intake portion 5, or may be manufactured separately from the intake portion 5 and joined to the intake portion 5.

吐出部６は、円筒状をなしてスクロール部７の周方向の一方の端部に一体に設けられ、周方向に沿ってスクロール部７の接線方向に延びて開口し、ガスＧを流路ＦＣから吐出する。吐出部６もスクロール部７及び吸気部５と同様の樹脂によって形成されている。吐出部６は、例えばスクロール部７と一体の樹脂の射出成形品となっていてもよいし、スクロール部７と別体で製造されてスクロール部７と接合されていてもよい。 The discharge portion 6 has a cylindrical shape and is integrally provided at one end of the scroll portion 7 in the circumferential direction, extends along the circumferential direction in the tangential direction of the scroll portion 7 and opens, and the gas G is passed through the flow path FC. Discharge from. The discharge portion 6 is also made of the same resin as the scroll portion 7 and the intake portion 5. The discharge unit 6 may be, for example, an injection-molded product of a resin integrated with the scroll unit 7, or may be manufactured separately from the scroll unit 7 and joined to the scroll unit 7.

次に図２を参照してスクロール部７について詳述する。
スクロール部７は、第一本体部１１と、第一本体部１１に対して回転軸線Ｏの方向の他方に配置され、第一本体部１１とともに流路ＦＣの内面７ａを形成する第二本体部１２と、第一本体部１１と第二本体部１２との間に設けられた接合部１３とを有している。Next, the scroll unit 7 will be described in detail with reference to FIG.
The scroll portion 7 is arranged on the other side of the first main body portion 11 and the direction of the rotation axis O with respect to the first main body portion 11, and together with the first main body portion 11, forms the inner surface 7a of the flow path FC. It has a 12 and a joint portion 13 provided between the first main body portion 11 and the second main body portion 12.

第一本体部１１は、回転軸線Ｏを中心とした環状をなしている。第一本体部１１には、第一本体部１１から回転軸線Ｏの方向の他方に突出して延び、流路ＦＣの内面７ａの一部を形成する回転軸線Ｏを中心とした環状の凸部１１ａが設けられている。これにより凸部１１ａは流路ＦＣに接して設けられている。第一本体部１１には凸部１１ａに接して、凸部１１ａよりも径方向外側に回転軸線Ｏの方向の他方を向く第一対向面１１ｂが形成されている。凸部１１ａの径方向外側を向く凸部外面１１ｃは、回転軸線Ｏの方向の他方に向かって径方向内側に向かって傾斜する傾斜面となっている。 The first main body portion 11 has an annular shape centered on the rotation axis O. The first main body portion 11 has an annular convex portion 11a centered on the rotation axis O that protrudes from the first main body portion 11 toward the other side in the direction of the rotation axis O and forms a part of the inner surface 7a of the flow path FC. Is provided. As a result, the convex portion 11a is provided in contact with the flow path FC. The first main body portion 11 is in contact with the convex portion 11a and is formed with a first facing surface 11b that faces the other side in the direction of the rotation axis O on the outer side in the radial direction from the convex portion 11a. The convex outer surface 11c facing the radial outer side of the convex portion 11a is an inclined surface inclined inward in the radial direction toward the other side in the direction of the rotation axis O.

第二本体部１２は、回転軸線Ｏを中心とした環状をなしている。第二本体部１２には流路ＦＣの内面７ａから径方向外側に凹んで、凸部１１ａが挿入されて凸部１１ａに係合する環状の凹部１２ａが設けられている。よって凹部１２ａの径方向内側を向く凹部内面１２ｃは、凸部外面１１ｃに対応して回転軸線Ｏの方向の他方に向かって径方向内側に向かって傾斜する傾斜面となっている。第二本体部１２には、凹部１２ａに接して凹部１２ａよりも径方向外側に、回転軸線Ｏの方向の一方を向く第二対向面１２ｂが形成されている。第二対向面１２ｂは第一対向面１１ｂに回転軸線Ｏの方向に向かい合って面接触して配置されている。 The second main body portion 12 has an annular shape centered on the rotation axis O. The second main body portion 12 is provided with an annular concave portion 12a that is recessed radially outward from the inner surface 7a of the flow path FC and into which the convex portion 11a is inserted and engages with the convex portion 11a. Therefore, the concave inner surface 12c facing the radial inward side of the concave portion 12a is an inclined surface inclined inward in the radial direction toward the other side in the direction of the rotation axis O corresponding to the convex outer surface 11c. The second main body portion 12 is formed with a second facing surface 12b that is in contact with the recess 12a and is radially outward from the recess 12a and faces one side in the direction of the rotation axis O. The second facing surface 12b is arranged in surface contact with the first facing surface 11b so as to face the direction of the rotation axis O.

接合部１３は、凸部１１ａ及び凹部１２ａよりも径方向外側の位置で、第一対向面１１ｂ及び第二対向面１２ｂ上に設けられている。よって接合部１３の径方向内側に、接合部１３に接して凸部１１ａが設けられていることになる。また凸部１１ａは接合部１３を超えて回転軸線Ｏの方向の他方に、第二本体部１２に向かって延びている。接合部１３は、例えば第一対向面１１ｂと第二対向面１２ｂとを回転軸線Ｏの方向に対向させた状態で、第一本体部１１と第二本体部１２とを振動融着や超音波融着等の方法を用いて接合させた結果形成されている。よって接合部１３は第一対向面１１ｂ及び第二対向面１２ｂの全体にわたって回転軸線Ｏを中心とした環状に形成され、第一本体部１１及び第二本体部１２と同じ樹脂材料からなる。 The joint portion 13 is provided on the first facing surface 11b and the second facing surface 12b at a position radially outside the convex portion 11a and the concave portion 12a. Therefore, the convex portion 11a is provided in contact with the joint portion 13 on the inner side in the radial direction of the joint portion 13. Further, the convex portion 11a extends beyond the joint portion 13 toward the second main body portion 12 on the other side in the direction of the rotation axis O. In the joint portion 13, for example, in a state where the first facing surface 11b and the second facing surface 12b face each other in the direction of the rotation axis O, the first main body portion 11 and the second main body portion 12 are subjected to vibration fusion or ultrasonic waves. It is formed as a result of joining using a method such as fusion. Therefore, the joint portion 13 is formed in an annular shape centered on the rotation axis O over the entire first facing surface 11b and the second facing surface 12b, and is made of the same resin material as the first main body portion 11 and the second main body portion 12.

本実施形態の接合部１３は、スクロール部７の流路ＦＣにおける回転軸線Ｏの方向の中央位置を通り径方向に延びる仮想線Ｘに沿って配置されている。ただし接合部１３は流路ＦＣが形成された回転軸線Ｏの方向の範囲内に位置していればよく、必ずしも上記の仮想線Ｘに沿って配置されている必要はない。 The joint portion 13 of the present embodiment is arranged along a virtual line X extending in the radial direction through the central position in the direction of the rotation axis O in the flow path FC of the scroll portion 7. However, the joint portion 13 may be located within the range in the direction of the rotation axis O in which the flow path FC is formed, and does not necessarily have to be arranged along the above-mentioned virtual line X.

接合部１３は第一対向面１１ｂと第二対向面１２ｂとの間にのみ設けられているため、凸部１１ａと凹部１２ａとの間には設けられていない。この結果、凸部１１ａと凹部１２ａとは近接、又は接触した状態で互いに接合されていない状態となっている。 Since the joint portion 13 is provided only between the first facing surface 11b and the second facing surface 12b, it is not provided between the convex portion 11a and the concave portion 12a. As a result, the convex portion 11a and the concave portion 12a are in a state of being close to each other or in contact with each other and not joined to each other.

以上説明した本実施形態のコンプレッサ１では、回転軸線Ｏの方向に延びてスクロール部７の流路ＦＣの内面７ａを形成する凸部１１ａを第一本体部１１に設けている。このため、仮に周方向の応力によって接合部１３に亀裂Ｃ（図２参照）が生じたとしても、亀裂Ｃを塞ぐように凸部１１ａがガスＧの圧力によって径方向外側に押し付けられる。この結果、亀裂Ｃの進展速度を低減することができる。 In the compressor 1 of the present embodiment described above, the first main body portion 11 is provided with a convex portion 11a extending in the direction of the rotation axis O to form the inner surface 7a of the flow path FC of the scroll portion 7. Therefore, even if a crack C (see FIG. 2) is generated in the joint portion 13 due to the stress in the circumferential direction, the convex portion 11a is pressed outward in the radial direction by the pressure of the gas G so as to close the crack C. As a result, the growth rate of the crack C can be reduced.

また仮に亀裂Ｃが生じたとしても、凸部１１ａが径方向外側に押し付けられることで亀裂Ｃは径方向外側に向かわずに、凸部１１ａの根本に、接合部１３と凸部１１ａとの間で凸部外面１１ｃに沿って回転軸線の方向の一方に向かって進展しようとする。このため、第一本体部１１や第二本体部１２に比べて強度が弱い接合部１３に亀裂Ｃが生じることがなく、亀裂Ｃは、より強度の強い第一本体部１１や第二本体部１２の内部に向かって進展しようとする。これによっても亀裂Ｃの進展速度を低減することができる。 Even if a crack C is generated, the convex portion 11a is pressed outward in the radial direction so that the crack C does not face the outward direction in the radial direction, and is located at the root of the convex portion 11a between the joint portion 13 and the convex portion 11a. Attempts to travel along the outer surface 11c of the convex portion in one direction of the rotation axis. Therefore, the crack C does not occur in the joint portion 13 whose strength is weaker than that of the first main body portion 11 and the second main body portion 12, and the crack C is the first main body portion 11 and the second main body portion having higher strength. Trying to progress towards the inside of the twelve. This also makes it possible to reduce the growth rate of the crack C.

また凸部１１ａと凹部１２ａとの間は非接合の状態となっているが、凸部１１ａがガスＧの圧力によって径方向外側に向かって凹部１２ａに押し付けられることで、凸部外面１１ｃと凹部内面１２ｃとの隙間が閉じようとする。このため、この隙間にガスＧが侵入することを回避できる。よって、流路ＦＣ内のガスＧの圧力損失を低減することができる。 Further, the convex portion 11a and the concave portion 12a are in a non-bonded state, but the convex portion 11a is pressed against the concave portion 12a in the radial direction by the pressure of the gas G, so that the convex portion outer surface 11c and the concave portion are formed. The gap with the inner surface 12c tries to close. Therefore, it is possible to prevent the gas G from entering this gap. Therefore, the pressure loss of the gas G in the flow path FC can be reduced.

さらに接合部１３は、仮想線Ｘ上に設けられていることで、スクロール部７の流路ＦＣが形成された回転軸線Ｏの方向の範囲内に位置している。このため、接合部１３は流路ＦＣにおける回転軸線Ｏの方向の中央の位置に一致若しくは近接して配置されていることになる。この結果、凸部１１ａが径方向外側に向かって凹部１２ａに押付けられることで、凸部外面１１ｃと凹部内面１２ｃとの隙間が閉じようとする。 Further, since the joint portion 13 is provided on the virtual line X, the joint portion 13 is located within the range in the direction of the rotation axis O in which the flow path FC of the scroll portion 7 is formed. Therefore, the joint portion 13 is arranged at the same position as or close to the central position in the direction of the rotation axis O in the flow path FC. As a result, the convex portion 11a is pressed against the concave portion 12a toward the outer side in the radial direction, so that the gap between the outer surface 11c of the convex portion and the inner surface 12c of the concave portion tends to be closed.

従って本実施形態のコンプレッサ１では、上記のようなケーシング４を備えることで、ケーシング４の疲労強度を向上しつつコンプレッサ１の性能向上が可能となる。 Therefore, in the compressor 1 of the present embodiment, by providing the casing 4 as described above, it is possible to improve the performance of the compressor 1 while improving the fatigue strength of the casing 4.

ここで本実施形態では第二本体部１２に凸部１１ａが設けられ、第一本体部１１に凹部１２ａが設けられていてもよい。また接合部１３は、第一対向面１１ｂ、第二対向面１２ｂ上で、凸部１１ａとは離れた位置まで設けられていてもよい。即ち。接合部１３は凸部外面１１ｃと接していなくともよい。 Here, in the present embodiment, the convex portion 11a may be provided in the second main body portion 12, and the concave portion 12a may be provided in the first main body portion 11. Further, the joint portion 13 may be provided on the first facing surface 11b and the second facing surface 12b up to a position away from the convex portion 11a. That is. The joint portion 13 does not have to be in contact with the convex portion outer surface 11c.

（第一変形例）
次に、図３を参照して本発明の第一実施形態の第一変形例のコンプレッサ１Ａについて説明する。
図３に示すように第一本体部１１には、第一対向面１１ｂから回転軸線Ｏの方向の一方に向かって凹んで回転軸線Ｏを中心として環状に延びる第一環状凹部１１ｄが形成されている。第一環状凹部１１ｄは凸部外面１１ｃに接して形成されている。第一環状凹部１１ｄにおける内面のうち、径方向を向く一対の側底面２１ａ、２１ｂは回転軸線Ｏの方向を向く底面２２に向かって互いに近接するように傾斜している。即ち、側底面２１ａ、２１ｂには型成型時の抜き勾配が設けられている。(First modification)
Next, the compressor 1A of the first modification of the first embodiment of the present invention will be described with reference to FIG.
As shown in FIG. 3, the first main body portion 11 is formed with a first annular recess 11d that is recessed from the first facing surface 11b toward one side in the direction of the rotation axis O and extends in an annular shape about the rotation axis O. There is. The first annular recess 11d is formed in contact with the outer surface 11c of the convex portion. Of the inner surfaces of the first annular recess 11d, the pair of side bottom surfaces 21a and 21b facing in the radial direction are inclined so as to be close to each other toward the bottom surface 22 facing the direction of the rotation axis O. That is, the side bottom surfaces 21a and 21b are provided with a draft at the time of mold molding.

第二本体部１２には、第二対向面１２ｂから回転軸線Ｏの方向の他方に向かって凹んで回転軸線Ｏを中心として環状に延びる第二環状凹部１２ｄが形成されている。第二環状凹部１２ｄの内面のうちの径方向を向く一対の側底面２５ａ、２５ｂのうち径方向内側の側底面２５ａは、凹部１２ａと径方向に離れた位置に設けられている。よって第一環状凹部１１ｄの径方向内側の側底面２１ａよりも径方向外側に設けられている。また、第二環状凹部１２ｄの径方向外側の側底面２５ｂは、第一環状凹部１１ｄの径方向外側の側底面２１ｂと同じ径方向の位置に設けられている。第一環状凹部１１ｄの側底面２１ａ、２１ｂと同様に、第二環状凹部１２ｄの一対の側底面２５ａ、２５ｂは、回転軸線Ｏの方向を向く底面２６に向かって互いに近接するように傾斜している。即ち、側底面２５ａ、２５ｂには成型時の抜き勾配が設けられている。 The second main body portion 12 is formed with a second annular recess 12d that is recessed from the second facing surface 12b toward the other side in the direction of the rotation axis O and extends in an annular shape about the rotation axis O. Of the pair of side bottom surfaces 25a and 25b facing the radial direction on the inner surface of the second annular recess 12d, the side bottom surface 25a on the inner side in the radial direction is provided at a position radially separated from the recess 12a. Therefore, the first annular recess 11d is provided on the outer side in the radial direction with respect to the side bottom surface 21a on the inner side in the radial direction. Further, the radial outer side bottom surface 25b of the second annular recess 12d is provided at the same radial position as the radial outer side bottom surface 21b of the first annular recess 11d. Similar to the side bottom surfaces 21a and 21b of the first annular recess 11d, the pair of side bottom surfaces 25a and 25b of the second annular recess 12d are inclined so as to be close to each other toward the bottom surface 26 facing the direction of the rotation axis O. There is. That is, the side bottom surfaces 25a and 25b are provided with a draft at the time of molding.

接合部２３は、第一環状凹部１１ｄと第二環状凹部１２ｄとによって形成された空間に配置された樹脂部材である。接合部２３の材料には上記のスクロール部７と同様の樹脂材料を用いることができる。接合部２３の外面は、全体にわたって第一本体部１１及び第二本体部１２と接合されている。 The joint portion 23 is a resin member arranged in the space formed by the first annular recess 11d and the second annular recess 12d. As the material of the joint portion 23, the same resin material as the scroll portion 7 can be used. The outer surface of the joint portion 23 is entirely joined to the first main body portion 11 and the second main body portion 12.

以上説明した第一実施形態の第一変形例のコンプレッサ１Ａによれば、第一本体部１１に設けられた凸部１１ａによって亀裂Ｃの進展速度を低減することができるとともに、流路内のガスＧの圧力損失を低減することができる。よってケーシング４Ａの疲労強度を向上しつつコンプレッサ１Ａの性能向上が可能となる。 According to the compressor 1A of the first modification of the first embodiment described above, the growth rate of the crack C can be reduced by the convex portion 11a provided on the first main body portion 11, and the gas in the flow path can be reduced. The pressure loss of G can be reduced. Therefore, it is possible to improve the performance of the compressor 1A while improving the fatigue strength of the casing 4A.

さらに、接合部２３に樹脂部材を用いることで、第一本体部１１と第二本体部１２とをより強固に接合することができる。さらに、例えばダイスライドインジェクションを用いて接合部２３を設け、第一本体部１１と第二本体部１２とを接合することができる。具体的には、第一本体部１１と第二本体部１２を成型した後にダイスライドを行って第一環状凹部１１ｄと第二環状凹部１２ｄとを回転軸線Ｏの方向に対向させ、接合部２３の樹脂材料を第一環状凹部１１ｄと第二環状凹部１２ｄとの間の空間に充填することで、容易にケーシング４Ａを製造できる。 Further, by using a resin member for the joint portion 23, the first main body portion 11 and the second main body portion 12 can be joined more firmly. Further, the joining portion 23 can be provided by using, for example, die slide injection, and the first main body portion 11 and the second main body portion 12 can be joined. Specifically, after molding the first main body portion 11 and the second main body portion 12, a die slide is performed so that the first annular recess 11d and the second annular recess 12d face each other in the direction of the rotation axis O, and the joint portion 23 By filling the space between the first annular recess 11d and the second annular recess 12d with the resin material of the above, the casing 4A can be easily manufactured.

（第二変形例）
次に、図４を参照して本発明の第一実施形態の第二変形例のコンプレッサ１Ｂについて説明する。
第二変形例では、第一変形例とは第二環状凹部３２ｄの形状が異なっている。図４に示すように第二環状凹部３２ｄの径方向内側の側底面は、凸部外面１１ｃである。これにより接合部３３は凸部外面１１ｃに接して第一本体部１１と第二本体部１２との間にわたって設けられている。接合部３３の外面は、全体にわたって第一本体部１１及び第二本体部１２と接合されている。(Second modification)
Next, the compressor 1B of the second modification of the first embodiment of the present invention will be described with reference to FIG.
In the second modification, the shape of the second annular recess 32d is different from that of the first modification. As shown in FIG. 4, the radial inner side bottom surface of the second annular recess 32d is the convex outer surface 11c. As a result, the joint portion 33 is provided in contact with the outer surface 11c of the convex portion and extends between the first main body portion 11 and the second main body portion 12. The outer surface of the joint portion 33 is entirely joined to the first main body portion 11 and the second main body portion 12.

本変形例においても、接合部３３の樹脂材料を第一環状凹部１１ｄと第二環状凹部３２ｄとの間の空間に充填したことで、第一本体部１１と第二本体部１２とをより強固に接合することができ、かつ、例えばダイスライドインジェクションを用いて容易にケーシング４Ｂを製造できる。 Also in this modification, the resin material of the joint portion 33 is filled in the space between the first annular recess 11d and the second annular recess 32d to make the first main body 11 and the second main body 12 stronger. The casing 4B can be easily manufactured by using, for example, die slide injection.

〔第二実施形態〕
次に、図５を参照して本発明の第二実施形態のコンプレッサ１Ｃについて説明する。以下に説明する第二実施形態においては、第一実施形態と同一部分に同一符号を付して説明するとともに、重複説明を省略する。
本実施形態では、第一実施形態の第二変形例と比較して、接合部４３の位置が異なっている。[Second Embodiment]
Next, the compressor 1C of the second embodiment of the present invention will be described with reference to FIG. In the second embodiment described below, the same parts as those in the first embodiment will be described with the same reference numerals, and duplicate description will be omitted.
In the present embodiment, the position of the joint portion 43 is different from that of the second modification of the first embodiment.

第一本体部４１の第一対向面４１ｂ、及び第二本体部４２の第二対向面４２ｂは、流路の回転軸線Ｏの方向の中央位置を通る仮想線Ｘよりも回転軸線Ｏの方向の一方側に配置されている。そして第一対向面４１ｂ及び第二対向面４２ｂは、流路ＦＣが形成された回転軸線Ｏの方向の範囲外に配置されている。
さらに、第一環状凹部４１ｄ及び第二環状凹部４２ｄも、流路ＦＣが形成された回転軸線Ｏの方向の範囲外に配置されている。よって、接合部４３も流路ＦＣが形成された回転軸線Ｏの方向の範囲外に配置されている。The first facing surface 41b of the first main body 41 and the second facing surface 42b of the second main body 42 are in the direction of the rotation axis O rather than the virtual line X passing through the central position in the direction of the rotation axis O of the flow path. It is located on one side. The first facing surface 41b and the second facing surface 42b are arranged outside the range in the direction of the rotation axis O in which the flow path FC is formed.
Further, the first annular recess 41d and the second annular recess 42d are also arranged outside the range in the direction of the rotation axis O in which the flow path FC is formed. Therefore, the joint portion 43 is also arranged outside the range in the direction of the rotation axis O in which the flow path FC is formed.

以上説明した本実施形態のコンプレッサ１Ｃでは、第一本体部４１に設けられた凸部４１ａによって亀裂の進展速度を低減することができるとともに、流路ＦＣ内のガスＧの圧力損失を低減することができる。よって、ケーシング４Ｃの疲労強度を向上しつつ、コンプレッサ１Ｃの性能向上が可能となる。 In the compressor 1C of the present embodiment described above, the convex portion 41a provided on the first main body portion 41 can reduce the crack growth rate and reduce the pressure loss of the gas G in the flow path FC. Can be done. Therefore, it is possible to improve the performance of the compressor 1C while improving the fatigue strength of the casing 4C.

さらに接合部４３は、流路ＦＣが形成された回転軸線Ｏの方向の範囲外に位置している。このため、圧縮されたガスＧからの熱の影響やガスＧからの圧力の影響が接合部４３へ及びにくくなり、周方向の応力による接合部４３での亀裂Ｃの発生を抑制することができる。よってケーシング４Ｃの損傷を抑制する効果が得られる。 Further, the joint portion 43 is located outside the range in the direction of the rotation axis O in which the flow path FC is formed. Therefore, the influence of heat from the compressed gas G and the influence of the pressure from the gas G are less likely to reach the joint portion 43, and the generation of cracks C at the joint portion 43 due to stress in the circumferential direction can be suppressed. .. Therefore, the effect of suppressing damage to the casing 4C can be obtained.

〔第三実施形態〕
次に、図６を参照して本発明の第三実施形態のコンプレッサ１Ｄについて説明する。以下に説明する第三実施形態においては、第一実施形態及び第二実施形態と同一部分に同一符号を付して説明するとともに、重複説明を省略する。[Third Embodiment]
Next, the compressor 1D according to the third embodiment of the present invention will be described with reference to FIG. In the third embodiment described below, the same parts as those in the first embodiment and the second embodiment will be described with the same reference numerals, and duplicate description will be omitted.

第一実施形態及び第二実施形態とは逆に凸部５２ａが第二本体部５２に設けられ、凸部５２ａが挿入されて凸部５２ａに係合する凹部５１ａが第一本体部５１に設けられている。 Contrary to the first embodiment and the second embodiment, the convex portion 52a is provided in the second main body portion 52, and the concave portion 51a into which the convex portion 52a is inserted and engages with the convex portion 52a is provided in the first main body portion 51. Has been done.

さらに凸部５２ａにおける径方向外側を向く面である凸部外面５２ｃには、径方向外側に突出する横凸部５２ｆが設けられている。この横凸部５２ｆは、回転軸線Ｏを中心とした環状に設けられてもよいし、周方向に間隔をあけて複数設けられてもよい。 Further, the convex outer surface 52c, which is a surface of the convex portion 52a facing outward in the radial direction, is provided with a lateral convex portion 52f protruding outward in the radial direction. The laterally convex portions 52f may be provided in an annular shape centered on the rotation axis O, or may be provided in plurality at intervals in the circumferential direction.

また凹部５１ａにおける径方向内側を向く凹部内面５１ｃには、径方向外側に凹むとともに横凸部５２ｆが挿入されて係合する横凹部５１ｆが設けられている。横凹部５１ｆは回転軸線Ｏを中心とした環状をなしてもよいし、周方向に間隔をあけて複数設けられていてもよい。 Further, the concave inner surface 51c of the concave portion 51a facing inward in the radial direction is provided with a horizontal concave portion 51f that is recessed outward in the radial direction and the lateral convex portion 52f is inserted and engaged with the concave portion 51a. The lateral recesses 51f may form an annular shape centered on the rotation axis O, or may be provided in plurality at intervals in the circumferential direction.

第二本体部５２には、凸部５２ａに加えて、凸部５２ａと径方向に間隔をあけて凸部５２ａに対して径方向外側に配置され、第二本体部５２の第二対向面５２ｂから回転軸線Ｏの一方、即ち、第一本体部５１に向けて突出する外側凸部５２ｅが設けられている。第二対向面５２ｂは、凸部５２ａに接して凸部５２ａよりも径方向外側に配置されて回転軸線Ｏの方向の一方を向く面である。外側凸部５２ｅの径方向外側を向く面は、回転軸線Ｏの方向に延びる第一本体部５１と第二本体部５２との分割面Ｄとなっている。 In addition to the convex portion 52a, the second main body portion 52 is arranged radially outward with respect to the convex portion 52a at a radial distance from the convex portion 52a, and the second facing surface 52b of the second main body portion 52b. An outer convex portion 52e projecting from one of the rotation axis O, that is, toward the first main body portion 51 is provided. The second facing surface 52b is a surface that is in contact with the convex portion 52a and is arranged radially outside the convex portion 52a and faces one side in the direction of the rotation axis O. The surface of the outer convex portion 52e facing outward in the radial direction is a dividing surface D of the first main body portion 51 and the second main body portion 52 extending in the direction of the rotation axis O.

第一本体部５１には、外側凸部５２ｅが挿入されて係合可能に、第二対向面５２ｂに対向する第一対向面５１ｂから回転軸線Ｏの方向の一方に凹む外側凹部５１ｅが設けられている。 The first main body portion 51 is provided with an outer concave portion 51e that is recessed in one direction in the direction of the rotation axis O from the first facing surface 51b facing the second facing surface 52b so that the outer convex portion 52e can be inserted and engaged. ing.

接合部５３は、流路ＦＣの回転軸線Ｏの方向の中央位置を通る仮想線Ｘよりも回転軸線Ｏの方向の他方側に配置され、流路ＦＣが形成された回転軸線Ｏの方向の範囲外に配置されている。接合部５３の外面は、全体にわたって第一本体部５１及び第二本体部５２と接合されている。 The joint portion 53 is arranged on the other side in the direction of the rotation axis O from the virtual line X passing through the central position in the direction of the rotation axis O of the flow path FC, and is a range in the direction of the rotation axis O in which the flow path FC is formed. It is located outside. The outer surface of the joint portion 53 is entirely joined to the first main body portion 51 and the second main body portion 52.

ここで、第一本体部５１と第二本体部５２とは、分割面Ｄで径方向に対向している。第一本体部５１には、回転軸線Ｏの方向の他方を向く端面に開口するとともに、上記分割面Ｄから径方向外側に凹む回転軸線Ｏを中心とした環状をなす第一環状凹部５１ｄが設けられている。また第二本体部５２には、回転軸線Ｏの方向の他方を向く端面に開口するとともに、上記分割面Ｄから径方向内側に凹む回転軸線Ｏを中心とした環状をなす第二環状凹部５２ｄが設けられている。第一環状凹部５１ｄと第二環状凹部５２ｄとは、回転軸線Ｏの方向に同じ位置に設けられている。また、第一環状凹部５１ｄ及び第二環状凹部５２ｄは流路ＦＣが形成された回転軸線Ｏの方向の範囲外に位置している。 Here, the first main body portion 51 and the second main body portion 52 face each other in the radial direction on the dividing surface D. The first main body 51 is provided with a first annular recess 51d that opens at the end surface facing the other in the direction of the rotation axis O and forms an annular shape centered on the rotation axis O that is concave outward in the radial direction from the divided surface D. Has been done. Further, the second main body portion 52 has a second annular recess 52d that opens at the end surface facing the other side in the direction of the rotation axis O and forms an annular shape centered on the rotation axis O that is concave inward in the radial direction from the divided surface D. It is provided. The first annular recess 51d and the second annular recess 52d are provided at the same position in the direction of the rotation axis O. Further, the first annular recess 51d and the second annular recess 52d are located outside the range in the direction of the rotation axis O in which the flow path FC is formed.

そして接合部５３は、第一環状凹部５１ｄと第二環状凹部５２ｄとによって形成された空間に配置されている。よって接合部５３も流路ＦＣが形成された回転軸線Ｏの方向の範囲外に位置している。 The joint portion 53 is arranged in the space formed by the first annular recess 51d and the second annular recess 52d. Therefore, the joint portion 53 is also located outside the range in the direction of the rotation axis O in which the flow path FC is formed.

以上説明した本実施形態のコンプレッサ１Ｄでは、上記の通り、凸部５２ａによって亀裂の進展速度を低減することができるとともに、流路ＦＣ内のガスＧの圧力損失を低減することができる。さらに、接合部５３が、流路ＦＣが形成された回転軸線Ｏの方向の範囲外に位置しているため、圧縮されたガスＧからの熱の影響やガスＧからの圧力の影響が接合部５３へ及びにくくなる。よって、周方向の応力による接合部５３での亀裂の発生を抑制することができ、ケーシング４Ｄの損傷を抑制する効果が得られる。 In the compressor 1D of the present embodiment described above, as described above, the protrusion 52a can reduce the crack growth rate and reduce the pressure loss of the gas G in the flow path FC. Further, since the joint portion 53 is located outside the range in the direction of the rotation axis O in which the flow path FC is formed, the influence of heat from the compressed gas G and the influence of the pressure from the gas G are the joint portion. It becomes difficult to reach 53. Therefore, it is possible to suppress the occurrence of cracks at the joint portion 53 due to stress in the circumferential direction, and it is possible to obtain the effect of suppressing damage to the casing 4D.

また、凸部５２ａに加えてさらに外側凸部５２ｅを設けることで、第一本体部５１と第二本体部５２とが回転軸線Ｏの方向に嵌め合うようにして、接合部５３によって接合される。よって回転軸線Ｏに対して互いに位置ずれしてしまうことを回避でき、組立時、運転時に第一本体部５１と第二本体部５２とを同軸上に配置することができる。即ち、同軸度を向上できる。この結果、ガスＧの圧縮効率の向上が可能である。 Further, by further providing the outer convex portion 52e in addition to the convex portion 52a, the first main body portion 51 and the second main body portion 52 are joined by the joining portion 53 so as to be fitted in the direction of the rotation axis O. .. Therefore, it is possible to avoid misalignment with respect to the rotation axis O, and the first main body 51 and the second main body 52 can be arranged coaxially during assembly and operation. That is, the coaxiality can be improved. As a result, it is possible to improve the compression efficiency of the gas G.

凸部外面５２ｃに横凸部５２ｆが設けられ、凸部外面５２ｃに対向する凹部内面５１ｃには横凸部５２ｆに係合可能な横凹部５１ｆを設けることで、第一本体部５１と第二本体部５２とが回転軸線Ｏの方向へ相対移動してしまうことを抑制できる。よって、第一本体部５１と第二本体部５２とが、互いに回転軸線Ｏの方向の変形を規制し合うことができ、ケーシング４Ｄの疲労強度を向上しつつ、ケーシング４Ｄの変形に伴うガスＧの圧縮効率低下を回避できる。特に第一本体部５１と第二本体部５２とのいずれか一方が高温となりやすく熱変形量が大きいような場合であっても、第一本体部５１と第二本体部５２とのうちの熱変形量の小さい方が熱変形量の大きい方の変形を抑制することができる。よってケーシング４Ｄの疲労強度を向上しつつ、ケーシング４Ｄの変形に伴うガスＧの圧縮効率低下を回避できる。 The convex portion outer surface 52c is provided with the lateral convex portion 52f, and the concave inner surface 51c facing the convex portion outer surface 52c is provided with the lateral concave portion 51f that can be engaged with the lateral convex portion 52f. It is possible to prevent the main body portion 52 and the main body portion 52 from moving relative to each other in the direction of the rotation axis O. Therefore, the first main body 51 and the second main body 52 can mutually regulate the deformation in the direction of the rotation axis O, and while improving the fatigue strength of the casing 4D, the gas G accompanying the deformation of the casing 4D. It is possible to avoid a decrease in compression efficiency. In particular, even when either one of the first main body 51 and the second main body 52 tends to have a high temperature and the amount of thermal deformation is large, the heat of the first main body 51 and the second main body 52 is high. The smaller the amount of deformation, the more the deformation of the larger amount of thermal deformation can be suppressed. Therefore, while improving the fatigue strength of the casing 4D, it is possible to avoid a decrease in the compression efficiency of the gas G due to the deformation of the casing 4D.

本実施形態では、外側凸部５２ｅ（外側凹部５１ｅ）、及び横凸部５２ｆ（横凹部５１ｆ）のうちのいずれか一方のみが設けられていてもよい。 In the present embodiment, only one of the outer convex portion 52e (outer concave portion 51e) and the lateral convex portion 52f (lateral concave portion 51f) may be provided.

〔第四実施形態〕
次に、図７を参照して本発明の第四実施形態のコンプレッサ１Ｅについて説明する。以下に説明する第四実施形態においては、第一実施形態から第三実施形態と同一部分に同一符号を付して説明するとともに、重複説明を省略する。本実施形態では、接合部６３の位置が第三実施形態とは異なっている。[Fourth Embodiment]
Next, the compressor 1E according to the fourth embodiment of the present invention will be described with reference to FIG. 7. In the fourth embodiment described below, the same parts as those of the first to third embodiments will be described with the same reference numerals, and duplicate description will be omitted. In the present embodiment, the position of the joint portion 63 is different from that of the third embodiment.

図７に示すように例えば、第一本体部６１には、外側凹部５１ｅから回転軸線Ｏの方向の一方に凹む第一環状凹部６１ｄが設けられている。第二本体部６２には、外側凸部５２ｅから回転軸線Ｏの方向の他方に凹むとともに、回転軸線Ｏを中心として環状をなす第二環状凹部６２ｄが設けられている。第一環状凹部６１ｄと第二環状凹部６２ｄとは径方向に同じ位置に設けられている。第一環状凹部６１ｄ及び第二環状凹部６２ｄは、流路ＦＣが形成された回転軸線Ｏの方向の範囲内に位置している。 As shown in FIG. 7, for example, the first main body 61 is provided with a first annular recess 61d that is recessed in one direction from the outer recess 51e in the direction of the rotation axis O. The second main body portion 62 is provided with a second annular recess 62d that is recessed from the outer convex portion 52e to the other side in the direction of the rotation axis O and forms an annular shape with the rotation axis O as the center. The first annular recess 61d and the second annular recess 62d are provided at the same position in the radial direction. The first annular recess 61d and the second annular recess 62d are located within the range in the direction of the rotation axis O in which the flow path FC is formed.

そして接合部６３は、第一環状凹部６１ｄと第二環状凹部６２ｄとによって形成された空間に配置されている。よって接合部６３も流路ＦＣが形成された回転軸線Ｏの方向の範囲内に位置している。 The joint portion 63 is arranged in the space formed by the first annular recess 61d and the second annular recess 62d. Therefore, the joint portion 63 is also located within the range in the direction of the rotation axis O in which the flow path FC is formed.

以上説明した本実施形態のコンプレッサ１Ｅによれば、接合部６３が流路ＦＣが形成された回転軸線Ｏの方向の範囲内に位置している。このため、接合部６３は流路ＦＣにおける回転軸線Ｏの方向の中央の位置（仮想線Ｘ）に近接して配置されていることになる。この結果、ガスＧの圧力による周方向の応力の影響が大きくなるが、このような場合であっても上記の凸部５２ａによって亀裂の進展を抑えることができるためケーシング４Ｅの損傷を抑制する効果が得られる。 According to the compressor 1E of the present embodiment described above, the joint portion 63 is located within the range in the direction of the rotation axis O in which the flow path FC is formed. Therefore, the joint portion 63 is arranged close to the central position (virtual line X) in the direction of the rotation axis O in the flow path FC. As a result, the influence of the stress in the circumferential direction due to the pressure of the gas G becomes large, but even in such a case, the protrusion 52a can suppress the growth of cracks, so that the effect of suppressing damage to the casing 4E is achieved. Is obtained.

本実施形態では接合部６３の位置は上記の場合に限定されず、接合部６３が少なくとも流路ＦＣが形成された回転軸線Ｏの方向の範囲内に位置していればよい。 In the present embodiment, the position of the joint portion 63 is not limited to the above case, and the joint portion 63 may be located at least within the range in the direction of the rotation axis O in which the flow path FC is formed.

以上、本発明の実施形態について図面を参照して詳述したが、各実施形態における各構成及びそれらの組み合わせ等は一例であり、本発明の趣旨から逸脱しない範囲内で、構成の付加、省略、置換、およびその他の変更が可能である。また、本発明は実施形態によって限定されることはなく、請求の範囲によってのみ限定される。 Although the embodiments of the present invention have been described in detail with reference to the drawings, the configurations and combinations thereof in each embodiment are examples, and the configurations may be added or omitted within a range not deviating from the gist of the present invention. , Replacements, and other changes are possible. Further, the present invention is not limited to the embodiments, but is limited only to the claims.

例えば、スクロール部７、吸気部５、吐出部６の材料は、互いに同じでなくともよい。また、少なくともスクロール部７が樹脂製であればよい。ここで「樹脂製」とは純粋に樹脂のみで製造されるものだけでなく、フィラー等の樹脂以外の材料を含んだ樹脂によって製造されるものも含む。吸気部５や吐出部６はアルミ等の金属、炭素繊維、金属フィラ―を含んだ複合材等で形成してもよい。 For example, the materials of the scroll portion 7, the intake portion 5, and the discharge portion 6 do not have to be the same. Further, at least the scroll portion 7 may be made of resin. Here, "made of resin" includes not only those manufactured purely of resin but also those manufactured of resin containing a material other than resin such as filler. The intake portion 5 and the discharge portion 6 may be formed of a metal such as aluminum, a carbon fiber, a composite material containing a metal filler, or the like.

上記のラジアルコンプレッサのケーシング、及びラジアルコンプレッサによれば、疲労強度を向上しつつ、性能向上が可能である。 According to the casing of the radial compressor and the radial compressor described above, it is possible to improve the performance while improving the fatigue strength.

１、１Ｂ、１Ｃ、１Ｄ、１Ｅコンプレッサ
２インペラ
３回転軸
４、４Ｂ、４Ｃ、４Ｄ、４Ｅケーシング
５吸気部
６吐出部
７スクロール部
７ａ内面
１１、４１、５１、６１第一本体部
１１ａ、４１ａ、５２ａ凸部
１１ｂ、４１ｂ、５１ｂ第一対向面
１１ｃ、５２ｃ凸部外面
１１ｄ、４１ｄ、５１ｄ、６１ｄ第一環状凹部
１２、４２、５２、６２第二本体部
１２ａ、５１ａ凹部
１２ｂ、４２ｂ、５２ｂ第二対向面
１２ｃ、５１ｃ凹部内面
１２ｄ、３２ｄ、４２ｄ、５２ｄ、６２ｄ第二環状凹部
１３、２３、３３、４３、５３、６３接合部
２１ａ、２１ｂ、２５ａ、２５ｂ側底面
２２、２６底面
５１ｅ外側凹部
５１ｆ横凹部
５２ｅ外側凸部
５２ｆ横凸部
６１第一本体部
６２第二本体部
Ｘ仮想線
Ｇガス
Ｏ回転軸線
ＦＣ流路
Ｃ亀裂
Ｄ分割面1,1B, 1C, 1D, 1E compressor
2 impeller
3 rotating shaft
4, 4B, 4C, 4D, 4E casing
5 Intake unit
6 Discharge section
7 Scroll part
7a inner surface
11, 41, 51, 61 First body
11a, 41a, 52a Convex part
11b, 41b, 51b First facing surface
11c, 52c Convex outer surface
11d, 41d, 51d, 61d First annular recess 12, 42, 52, 62 Second main body
12a, 51a concave
12b, 42b, 52b Second facing surface
12c, 51c Inner surface of recess
12d, 32d, 42d, 52d, 62d Second annular recess
13, 23, 33, 43, 53, 63 joints
21a, 21b, 25a, 25b Side bottom surface 22, 26 Bottom surface 51e Outer concave portion 51f Lateral concave portion 52e Outer convex portion 52f Lateral convex portion 61 First main body portion 62 Second main body portion X Virtual line
G gas
O Rotating axis FC Flow path C Crack D Dividing surface

Claims

A cylindrical shape that extends along the rotation axis of the impeller and opens in the direction of the rotation axis, and an intake unit that introduces a fluid into the impeller.
A resin scroll portion that communicates with the intake portion and forms an annular flow path centered on the rotation axis on the outer peripheral side of the impeller.
A discharge portion that is integrally formed at one end of the scroll portion, extends and opens along the circumferential direction of the impeller, and discharges the fluid from the flow path.
Equipped with
The scroll part is
The first main body portion arranged on one side in the direction of the rotation axis,
A second main body portion arranged on the other side in the direction of the rotation axis with respect to the first main body portion,
The first main body portion and the second main body portion are joined in the direction of the rotation axis, and the joint portion located within the range in the direction of the rotation axis in which the flow path is formed and the joint portion.
Have,
One of the first main body and the second main body has one of the first main body and the second main body inside the joint portion in the radial direction with respect to the rotation axis from one of the first main body to the other. An annular convex portion centered on the rotation axis extending toward the joint portion and forming a part of the inner surface of the flow path is provided.
A casing of a radial compressor in which a concave portion recessed from the inner surface of the flow path and engaged with the convex portion is provided on the other side of the first main body portion and the second main body portion.

The first main body portion has a first facing surface facing the direction of the rotation axis.
The second main body portion has a second facing surface that comes into surface contact with the first facing surface.
The first main body is provided with a first annular recess that is recessed in the direction of the rotation axis from the first facing surface and extends in an annular shape around the rotation axis.
The second main body portion has a second annular recess that is recessed in the direction of the rotation axis from the second facing surface at a position corresponding to the position where the first annular recess is provided and extends in an annular shape around the rotation axis. Is provided,
The casing of the radial compressor according to claim 1, wherein the joint is a resin member arranged in a space formed by the first annular recess and the second annular recess.

The convex portion has a convex outer surface facing outward in the radial direction.
The outer surface of the convex portion is provided with a lateral convex portion that protrudes outward in the radial direction.
The other of the first main body and the second main body has an inner surface facing the outer surface of the convex portion.
The casing of the radial compressor according to claim 1 or 2, wherein the inner surface is recessed outward in the radial direction and is provided with a lateral recess with which the lateral convex portion can be engaged.

The other of the first main body and the second main body is arranged on the outer side in the radial direction with respect to the convex portion, and the first main body and the second main body are the same. Further, an outer convex portion protruding from the other toward the one is provided.
The radial according to any one of claims 1 to 3, wherein an outer concave portion with which the outer convex portion can be engaged is provided on one of the first main body portion and the second main body portion. Compressor casing.

A cylindrical shape that extends along the rotation axis of the impeller and opens in the direction of the rotation axis, and an intake unit that introduces a fluid into the impeller.
A resin scroll portion that communicates with the intake portion and forms an annular flow path centered on the rotation axis on the outer peripheral side of the impeller.
A discharge portion that is integrally provided at one end of the scroll portion and extends and opens along the circumferential direction of the impeller to discharge the fluid from the flow path.
Equipped with
The scroll part is
The first main body portion arranged on one side in the direction of the rotation axis,
A second main body portion arranged on the other side in the direction of the rotation axis with respect to the first main body portion,
The first main body portion and the second main body portion are joined in the direction of the rotation axis, and the joint portion located outside the range of the rotation axis direction in which the flow path is formed and the joint portion.
Have,
One of the first main body and the second main body has one of the first main body and the second main body inside the joint portion in the radial direction with respect to the rotation axis from one of the first main body to the other. An annular convex portion centered on the rotation axis extending toward the joint portion and forming a part of the inner surface of the flow path is provided.
The other of the first main body and the second main body is provided with a concave portion that is recessed from the inner surface of the flow path and engages with the convex portion.
The first main body portion has a first facing surface facing the direction of the rotation axis.
The second main body portion has a second facing surface that comes into surface contact with the first facing surface.
The first main body is provided with a first annular recess that is recessed in the direction of the rotation axis from the first facing surface and extends in an annular shape around the rotation axis.
The second main body portion has a second annular recess that is recessed in the direction of the rotation axis from the second facing surface at a position corresponding to the position where the first annular recess is provided and extends in an annular shape around the rotation axis. Is provided,
The joint portion is a casing of a radial compressor which is a resin member arranged in a space formed by the first annular recess and the second annular recess.

A cylindrical shape that extends along the rotation axis of the impeller and opens in the direction of the rotation axis, and an intake unit that introduces a fluid into the impeller.
A resin scroll portion that communicates with the intake portion and forms an annular flow path centered on the rotation axis on the outer peripheral side of the impeller.
A discharge portion that is integrally provided at one end of the scroll portion and extends and opens along the circumferential direction of the impeller to discharge the fluid from the flow path.
Equipped with
The scroll part is
The first main body portion arranged on one side in the direction of the rotation axis,
A second main body portion arranged on the other side in the direction of the rotation axis with respect to the first main body portion,
The first main body portion and the second main body portion are joined in the direction of the rotation axis, and the joint portion located outside the range of the rotation axis direction in which the flow path is formed and the joint portion.
Have,
One of the first main body and the second main body has one of the first main body and the second main body inside the joint portion in the radial direction with respect to the rotation axis from one of the first main body to the other. An annular convex portion centered on the rotation axis extending toward the joint portion and forming a part of the inner surface of the flow path is provided.
The other of the first main body and the second main body is provided with a concave portion that is recessed from the inner surface of the flow path and engages with the convex portion.
The convex portion has a convex outer surface facing outward in the radial direction.
The outer surface of the convex portion is provided with a lateral convex portion that protrudes outward in the radial direction.
The other of the first main body and the second main body has an inner surface facing the outer surface of the convex portion.
The inner surface is recessed outward in the radial direction and is provided with a lateral recess with which the lateral convex portion can be engaged.
The other of the first main body and the second main body is arranged on the outer side in the radial direction with respect to the convex portion, and the first main body and the second main body are the same. Further, an outer convex portion protruding from the other toward the one is provided.
A casing of a radial compressor in which an outer concave portion with which the outer convex portion can be engaged is provided on one of the first main body portion and the second main body portion.

With an impeller,
A rotating shaft to which the impeller fits and rotates with the impeller,
The casing according to any one of claims 1 to 6, which is provided so as to cover the impeller.
Radial compressor equipped with.