JP2011089507A - Scroll fluid machine - Google Patents

Scroll fluid machine Download PDF

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Publication number
JP2011089507A
JP2011089507A JP2009245752A JP2009245752A JP2011089507A JP 2011089507 A JP2011089507 A JP 2011089507A JP 2009245752 A JP2009245752 A JP 2009245752A JP 2009245752 A JP2009245752 A JP 2009245752A JP 2011089507 A JP2011089507 A JP 2011089507A
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Prior art keywords
housing
scroll
fluid machine
center plate
recess
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JP2009245752A
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Japanese (ja)
Inventor
Yoshihiro Ochiai
芳宏 落合
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Sanden Corp
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Sanden Corp
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Priority to JP2009245752A priority Critical patent/JP2011089507A/en
Priority to CA2775384A priority patent/CA2775384A1/en
Priority to EP10826303.9A priority patent/EP2472114A4/en
Priority to KR1020127007575A priority patent/KR20120049369A/en
Priority to CN2010800432503A priority patent/CN102575671A/en
Priority to US13/497,959 priority patent/US20120237374A1/en
Priority to PCT/JP2010/006250 priority patent/WO2011052166A1/en
Publication of JP2011089507A publication Critical patent/JP2011089507A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a scroll fluid machine which is configured so that the scroll fluid machine has reduced size and weight, and long life achievable by mounting, without increasing the diameter of a barrel, a bearing having a higher load capacity and so that degradation in the performance due to a pressure loss during a high flow-rate operation is suppressed by securi the gas flow path in a center plate with a sufficient cross-sectional area. <P>SOLUTION: The scroll fluid machine is provided with: a first housing which contains a scroll mechanism; a second housing which contains an electric motor; and a center plate which is disposed between both the housings, which contains a motion conversion mechanism for converting rotational motion to orbiting motion, which has mounted thereto a rotation prevention mechanism for preventing the rotation of a movable scroll, and which holds the bearing for supporting a main shaft. At least a part of a fluid path, which connects the insides of the first and second housings through the portion at which the center plate is disposed, is configured to connect an axial recess and a radial recess which are formed in the center plate, the axial recess facing the inside of the second housing and extending in the axial direction, the radial recess being located closer to the first housing side than the bearing and extending in the radial direction. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

本発明は、空調用に用いられる電動スクロール型圧縮機や、車両・ボイラー等の廃熱回収に用いられる発電機を搭載したスクロール型膨張機等のスクロール型流体機械に関する。   The present invention relates to a scroll type fluid machine such as an electric scroll type compressor used for air conditioning and a scroll type expander equipped with a generator used for waste heat recovery of a vehicle, a boiler and the like.

電動モータとスクロール型の圧縮機を同一軸上に配置した電動コンプレッサが知られている。この種の圧縮機は、例えば特許文献１や２に開示されるように、一対の渦巻き体を収容するハウジングと、回転運動を旋回運動に変換する機構部品が取り付けられたセンタープレートと、電動モータを収容するハウジング等から構成されている。このような圧縮機において、冷媒は、電動モータを収容するハウジングに設けられた吸入ポートから吸入された後、電動モータの空隙を通過し、センタープレートに保持される軸受の空隙または軸受を保持する円筒部の外周部の空隙を通り、渦巻き体に取り込まれて一対の渦巻き体を収容するハウジングの吐出ポートから吐出される。   There is known an electric compressor in which an electric motor and a scroll type compressor are arranged on the same axis. For example, as disclosed in Patent Documents 1 and 2, this type of compressor includes a housing that houses a pair of spiral bodies, a center plate to which a mechanical component that converts rotational motion into turning motion, and an electric motor. It is comprised from the housing etc. which accommodate. In such a compressor, the refrigerant is sucked from a suction port provided in a housing that houses the electric motor, and then passes through the gap of the electric motor and holds the bearing gap or the bearing held by the center plate. It passes through the gap in the outer peripheral portion of the cylindrical portion, is taken into the spiral body, and is discharged from the discharge port of the housing that houses the pair of spiral bodies.

一方、発電機を搭載した膨張機においては、吸入ポートと吐出ポートが入れ替わるとともに、冷媒は、上記の圧縮機の場合と全く逆方向に流れる。すなわち、一対の渦巻き体を収容するハウジングの吸入ポートから吸入され、渦巻き体に取り込まれた後、センタープレートに保持される軸受の空隙または軸受を保持するセンタープレートの円筒部の外周部の空隙を通り、発電機の空隙を通過し、発電機を収容するハウジングに設けられた吐出ポートから吐出される。   On the other hand, in an expander equipped with a generator, the suction port and the discharge port are switched, and the refrigerant flows in the opposite direction to that of the compressor described above. That is, after being sucked from the suction port of the housing that houses the pair of spiral bodies and taken into the spiral body, the bearing gap held by the center plate or the gap at the outer periphery of the cylindrical portion of the center plate that holds the bearing As a result, it passes through the gap of the generator and is discharged from a discharge port provided in a housing that houses the generator.

特開２００８−２３２０５７号公報JP 2008-232057 A 特開２００８−３０３８１９号公報JP 2008-303819 A

スクロール型流体機械の小型・軽量化と信頼性の向上を目指した研究開発の過程において、圧縮機の胴径を拡大することなく、負荷容量の大きい主軸用の軸受を採用する必要が生じた。ところが、他部品との関係で制約がある内径寸法を変えることなく軸受けの負荷容量をアップさせるために、軸受の外径を大きくしようとすると、軸受を保持する円筒部の外径寸法と可動渦巻き体のカップリング部の内径寸法が略一致し、主たるガス通路となる空隙を設けることが困難となった。さらに、軸受の空隙のみでは、高流量運転時の圧力損失による性能低下の恐れを解消することは困難であった。   In the course of research and development aimed at reducing the size and weight of scroll-type fluid machines and improving their reliability, it became necessary to adopt bearings for main shafts with a large load capacity without increasing the diameter of the compressor. However, if the outer diameter of the bearing is increased in order to increase the load capacity of the bearing without changing the inner diameter, which is restricted due to the relationship with other parts, the outer diameter of the cylindrical portion holding the bearing and the movable spiral The inner diameter dimensions of the coupling part of the body are substantially the same, and it has become difficult to provide a gap serving as a main gas passage. Furthermore, it was difficult to eliminate the risk of performance degradation due to pressure loss during high flow operation only with the bearing gap.

そこで本発明の課題は、胴体径を拡大することなく、より負荷容量の大きな軸受を組み込むことで小型・軽量化と長寿命化が達成可能であるとともに、センタープレートのガス通路断面積が十分に確保されることで高流量運転時の圧力損失による性能低下が抑制可能なスクロール型流体機械を提供することにある。   Accordingly, an object of the present invention is to achieve a reduction in size, weight and life by incorporating a bearing having a larger load capacity without enlarging the body diameter, and a sufficient gas passage cross-sectional area of the center plate. It is an object of the present invention to provide a scroll type fluid machine capable of suppressing performance degradation due to pressure loss during high flow operation.

上記課題を解決するために、本発明に係るスクロール型流体機械は、固定スクロールと可動スクロールからなるスクロール機構を収容する第一ハウジングと、主軸を回転駆動させる電動モータを収容する第二ハウジングと、両ハウジング間に介在し前記主軸の回転運動を前記可動スクロールの旋回運動に変換する運動変換機構を収容し前記可動スクロールに対し自転阻止機構が取り付けられているとともに前記主軸の軸受を保持するセンタープレートとを備え、前記第二ハウジングの内部と前記第一ハウジングの内部とを前記センタープレートの設置部を介して連通する流体通路を有するスクロール型流体機械であって、前記流体通路の少なくとも一部を、前記センタープレートに形成された、前記第二ハウジングの内部に臨み軸方向に延びる軸方向凹部と、前記軸受よりも前記第一ハウジング側に位置し径方向に延びる径方向凹部とを、連通させることにより形成したことを特徴とするものからなる。   In order to solve the above-described problem, a scroll type fluid machine according to the present invention includes a first housing that houses a scroll mechanism including a fixed scroll and a movable scroll, a second housing that houses an electric motor that rotationally drives the main shaft, A center plate, which is interposed between both housings and accommodates a motion conversion mechanism for converting the rotational motion of the main shaft into the orbiting motion of the movable scroll, has a rotation prevention mechanism attached to the movable scroll, and holds a bearing of the main shaft A scroll type fluid machine having a fluid passage that communicates the inside of the second housing and the inside of the first housing via an installation portion of the center plate, wherein at least a part of the fluid passage is provided. , Formed in the center plate, facing the inside of the second housing and extending in the axial direction The axial recess, a radial recess extending in the radial position in the first housing side than the bearing, consisting of those characterized by being formed by communicating.

本発明のスクロール型流体機械によれば、第一ハウジングの内部と第二ハウジングの内部とをセンタープレートを介して連通する流体通路の少なくとも一部が、センタープレートに形成された軸方向凹部と径方向凹部とを連通させることにより形成されているので、ガス通路の断面積を十分に確保することができ、高流量運転時の圧力損失による性能低下を効果的に抑制することができる。また、流体通路は主軸に対して軸方向に延びる軸方向凹部と径方向に延びる径方向凹部との連通により形成されるので、ガス通路を簡便な加工によって形成することが可能である。   According to the scroll type fluid machine of the present invention, at least part of the fluid passage that connects the inside of the first housing and the inside of the second housing via the center plate has an axial recess and a diameter formed in the center plate. Since it is formed by communicating with the directional recess, a sufficient cross-sectional area of the gas passage can be ensured, and performance degradation due to pressure loss during high flow rate operation can be effectively suppressed. Further, since the fluid passage is formed by communication between an axial recess extending in the axial direction with respect to the main shaft and a radial recess extending in the radial direction, the gas passage can be formed by simple processing.

本発明のスクロール型流体機械において、前記軸方向凹部が周方向に複数形成されていることが好ましい。このように軸方向凹部を形成することにより、負荷容量の大きな軸受を組み込んだ場合にも、流体通路の断面積を確保しやすくなる。   In the scroll fluid machine of the present invention, it is preferable that a plurality of the axial recesses are formed in the circumferential direction. By forming the axial recess in this manner, it becomes easy to ensure the cross-sectional area of the fluid passage even when a bearing having a large load capacity is incorporated.

また、前記軸方向凹部は、その内面の一部が、前記第二ハウジングの内部側に向けてテーパ状に広がる面に形成されていることが好ましい。軸方向凹部をこのような形状とすることにより、センタープレートの強度を確保しつつ加工の容易化を図ることができる。   Moreover, it is preferable that a part of the inner surface of the axial recess is formed on a surface that extends in a tapered shape toward the inner side of the second housing. By forming the axial recess in such a shape, it is possible to facilitate the processing while ensuring the strength of the center plate.

本発明のスクロール型流体機械において、前記径方向凹部が周方向に環状に延びる凹部に形成されていることが好ましい。径方向凹部をこのような形状とすることにより、加工の容易化を図ることができる。   In the scroll type fluid machine of the present invention, it is preferable that the radial recess is formed in a recess extending in an annular shape in the circumferential direction. By making the radial recess into such a shape, the processing can be facilitated.

また、前記径方向凹部は、その内面の一部が、前記第一ハウジングの内部から前記第二ハウジングの内部側に向けてテーパ状に広がる面に形成されていることが好ましい。径方向凹部をこのような形状とすることにより、センタープレートの強度を確保しつつ加工の容易化を図ることができる。   Moreover, it is preferable that a part of the inner surface of the radial recess is formed on a surface that extends in a tapered shape from the inside of the first housing toward the inside of the second housing. By forming the radial concave portion in such a shape, it is possible to facilitate the processing while ensuring the strength of the center plate.

本発明のスクロール型流体機械においては、前記軸方向凹部が、前記センタープレートの素形材の製造時に設けられていることが好ましい。センタープレートの素形材を製造するのと同時に軸方向凹部を設けることで、センタープレートの製造工程を簡素化することが可能となる。さらに、前記センタープレートの素形材が鋳造によって製造され、前記軸方向凹部が型を用いて形成されていることが好ましい。また、前記径方向凹部が中子を用いて形成されていてもよい。このような製造工程を採用することにより、センタープレートをより効率的に製造することが可能となる。   In the scroll type fluid machine of the present invention, it is preferable that the axial recess is provided at the time of manufacturing the shape member of the center plate. It is possible to simplify the manufacturing process of the center plate by providing the axial recess at the same time as manufacturing the shaped member of the center plate. Furthermore, it is preferable that the shape material of the center plate is manufactured by casting, and the axial recess is formed using a mold. Moreover, the said radial direction recessed part may be formed using the core. By employing such a manufacturing process, the center plate can be manufactured more efficiently.

また、前記径方向凹部は、機械加工により形成することも可能である。とくに径方向凹部が周方向に環状に延びる凹部に形成される場合には、機械加工を比較的容易に行うことができる。   The radial recess can be formed by machining. In particular, when the radial recess is formed in a recess extending annularly in the circumferential direction, machining can be performed relatively easily.

本発明のスクロール型流体機械において、前記センタープレートは、前記第一ハウジングおよび第二ハウジングのいずれかと一体に形成されていてもよい。センタープレートと第一または第二ハウジングとが一体形成されることで構成部品点数を低減させ、スクロール型流体機械の組み立て工程を簡素化することが可能となる。   In the scroll fluid machine of the present invention, the center plate may be formed integrally with either the first housing or the second housing. Since the center plate and the first or second housing are integrally formed, the number of components can be reduced, and the assembly process of the scroll fluid machine can be simplified.

本発明のスクロール型流体機械は、圧縮機または膨張機として構成されることが可能である。すなわち、本発明のスクロール型流体機械においては、主軸の回転方向に応じて、圧縮機または膨張機としての機能が発揮される。とくに圧縮機として構成される場合には、吐出弁を設けることが好ましい。   The scroll type fluid machine of the present invention can be configured as a compressor or an expander. That is, in the scroll type fluid machine of the present invention, a function as a compressor or an expander is exhibited according to the rotation direction of the main shaft. In particular, when configured as a compressor, it is preferable to provide a discharge valve.

本発明のスクロール型流体機械は、車両に搭載される流体機械として好適に利用可能である。車両に搭載される流体機械は、小型化および軽量化の要請が特に強いので、本発明のスクロール型流体機械の技術的特徴がより効果的に発揮され得る。   The scroll type fluid machine of the present invention can be suitably used as a fluid machine mounted on a vehicle. Since a fluid machine mounted on a vehicle is particularly demanded to be reduced in size and weight, the technical features of the scroll type fluid machine of the present invention can be more effectively exhibited.

本発明に係るスクロール型流体機械によれば、簡便な加工によって形成される流体通路の断面積を十分に確保することができ、高流量運転時の圧力損失による性能低下を効果的に抑制することができる。その結果、負荷容量の大きな軸受を組み込んだ場合にも胴体径を拡大する必要がなくなり、流体機械の小型・軽量化と長寿命化を達成可能である。また、センタープレートの流体通路断面積が十分に確保されることで高流量運転時の圧力損失による性能低下を抑制可能である。   According to the scroll type fluid machine according to the present invention, it is possible to sufficiently secure the cross-sectional area of the fluid passage formed by simple processing, and effectively suppress the performance deterioration due to the pressure loss during the high flow rate operation. Can do. As a result, even when a bearing having a large load capacity is incorporated, it is not necessary to enlarge the body diameter, and the fluid machine can be reduced in size, weight and life. In addition, a sufficient fluid passage cross-sectional area of the center plate can be ensured to suppress performance degradation due to pressure loss during high flow rate operation.

本発明の一実施態様に係るスクロール型圧縮機の縦断面図である。It is a longitudinal cross-sectional view of the scroll compressor which concerns on one embodiment of this invention. 図１のＡの部分近傍を拡大した部分拡大縦断面図である。FIG. 2 is a partially enlarged longitudinal sectional view in which the vicinity of a portion A in FIG. 1 is enlarged.

以下に、本発明の望ましい実施の形態を、図面を参照して説明する。
図１は、本発明の一実施態様に係るスクロール型圧縮機の縦断面図である。圧縮機１は、固定スクロール２と可動スクロール３を収容する第一ハウジング４と、主軸５の回転運動を可動スクロール３の旋回運動に変換するクランク機構６、および可動スクロールの自転を阻止する自転阻止機構７が取り付けられているセンタープレート８と、電動モータ９を収容する第二ハウジング１０から構成されており、電動モータ９と圧縮機１は同一軸上に配置されている。センタープレート８の電動モータ９側の面には、主軸５の軸受１１を保持する円筒状の軸受保持部１２が取り付けられ、軸受保持部１２よりも径方向外側には、複数の放射状に形成されたリブ（図示略）が設けられ、隣接するリブの間には主軸５の軸方向に延びる複数の軸方向凹部１３が、第二ハウジング１０の内部側に向けてテーパ状に広がる内面を有するように形成されている。 Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view of a scroll compressor according to an embodiment of the present invention. The compressor 1 includes a first housing 4 that accommodates the fixed scroll 2 and the movable scroll 3, a crank mechanism 6 that converts the rotational motion of the main shaft 5 into the turning motion of the movable scroll 3, and the rotation prevention that prevents the rotation of the movable scroll. It is comprised from the center plate 8 to which the mechanism 7 is attached, and the 2nd housing 10 which accommodates the electric motor 9, and the electric motor 9 and the compressor 1 are arrange | positioned on the same axis | shaft. A cylindrical bearing holding portion 12 that holds the bearing 11 of the main shaft 5 is attached to the surface of the center plate 8 on the electric motor 9 side, and a plurality of radial shapes are formed radially outward from the bearing holding portion 12. Ribs (not shown) are provided, and between the adjacent ribs, a plurality of axial recesses 13 extending in the axial direction of the main shaft 5 have an inner surface that extends in a tapered shape toward the inner side of the second housing 10. Is formed.

一方、センタープレート８の第一ハウジング４側の面には、主軸５と垂直方向に延びる径方向凹部１４が、センタープレート８の全周にわたって環状に延びる凹部として形成されている。径方向凹部１４の内面は、第一ハウジング４の内部から第二ハウジング１０の内部側（電動モータ９側）に向けて、主軸５と平行な方向にテーパ状に広がるように形成されている。   On the other hand, on the surface of the center plate 8 on the first housing 4 side, a radial recess 14 extending in a direction perpendicular to the main shaft 5 is formed as a recess extending in an annular shape over the entire circumference of the center plate 8. The inner surface of the radial recess 14 is formed so as to taper in a direction parallel to the main shaft 5 from the inside of the first housing 4 toward the inside of the second housing 10 (the electric motor 9 side).

このように形成された径方向凹部１４と複数の軸方向凹部１３とが、互いに連通することによって、被圧縮流体としての冷媒ガスが流通するための流体通路が形成されている。吸入ポート１５から吸入された冷媒ガスは、電動モータ９の隙間を通ってセンタープレート９の手前まで運ばれた後、主として軸方向凹部１３と径方向凹部１４を経由して可動スクロール３に取り込まれ、可動スクロール３と固定スクロール２からなる圧縮機構により圧縮された後に、吐出孔１６および吐出室１７を経由して吐出ポート１８から吐出される。圧縮機１の冷凍回路は、このような経路をなすように構成されている。従来は軸受１１の空隙や軸受保持部１２の外周側の空隙を流通していた冷媒ガスが、径方向凹部と軸方向凹部１３からなる流体通路の内部を流通できるようになり、冷媒ガスの通路断面積が十分に確保されるので、高流量運転時の圧力損失の低減が図られる。   The thus formed radial recess 14 and the plurality of axial recesses 13 communicate with each other to form a fluid passage through which refrigerant gas as a fluid to be compressed flows. The refrigerant gas sucked from the suction port 15 is carried to the front of the center plate 9 through the gap of the electric motor 9 and then taken into the movable scroll 3 mainly through the axial recess 13 and the radial recess 14. After being compressed by a compression mechanism comprising the movable scroll 3 and the fixed scroll 2, it is discharged from the discharge port 18 via the discharge hole 16 and the discharge chamber 17. The refrigeration circuit of the compressor 1 is configured to form such a path. Conventionally, the refrigerant gas that has circulated through the gap of the bearing 11 and the gap on the outer peripheral side of the bearing holding portion 12 can circulate inside the fluid passage composed of the radial recess 13 and the axial recess 13. Since a sufficient cross-sectional area is ensured, pressure loss during high flow operation can be reduced.

図２は、図１のＡの部分近傍を拡大した部分拡大縦断面図である。以下、図２を参照しながら軸方向凹部１３と径方向凹部１４の好ましいサイズおよび形状について説明する。   FIG. 2 is a partially enlarged vertical sectional view in which the vicinity of the portion A in FIG. 1 is enlarged. Hereinafter, preferred sizes and shapes of the axial recess 13 and the radial recess 14 will be described with reference to FIG.

軸方向凹部１３と径方向凹部１４の重複する領域の軸方向長さａは、２〜９ｍｍであることが好ましい。長さａが大きいほど圧力損失は低減されるが、あまり大き過ぎるとセンタープレート９の強度が弱くなる。   The axial length a of the region where the axial recess 13 and the radial recess 14 overlap is preferably 2 to 9 mm. As the length a is larger, the pressure loss is reduced. However, if the length a is too large, the strength of the center plate 9 is weakened.

センタープレート９の可動スクロール３側端面と径方向凹部１４のテーパ状内面とのなす角度ｂは、２０〜６０°であることが好ましい。角度ｂをこの範囲に設定することにより、径方向凹部１４の加工作業の容易化が図られる。   The angle b formed by the end surface on the movable scroll 3 side of the center plate 9 and the tapered inner surface of the radial recess 14 is preferably 20 to 60 °. By setting the angle b in this range, the processing operation of the radial recess 14 can be facilitated.

軸方向凹部１３のテーパ状内面と軸方向のなす角度ｃ（ｅ）は、１〜４°であることが好ましい。角度ｃをこの範囲に設定することにより、第二ハウジング１０の内部から軸方向凹部１３に流入する冷媒ガスの流動性の向上およびの径方向凹部１４の加工作業の容易化が図られる。   The angle c (e) formed between the tapered inner surface of the axial recess 13 and the axial direction is preferably 1 to 4 °. By setting the angle c within this range, it is possible to improve the fluidity of the refrigerant gas flowing from the inside of the second housing 10 into the axial recess 13 and to facilitate the processing of the radial recess 14.

径方向凹部１４の径方向深さｄは、３〜９ｍｍであることが好ましい。深さｄをこの範囲に設定することにより、軸方向凹部１３から径方向凹部１４を経由して第一ハウジング４の内部に流入する冷媒ガスの流動性の向上およびの径方向凹部１４の加工作業の容易化が図られる。   The radial depth d of the radial recess 14 is preferably 3 to 9 mm. By setting the depth d in this range, the fluidity of the refrigerant gas flowing into the first housing 4 from the axial recess 13 via the radial recess 14 is improved, and the radial recess 14 is processed. Is facilitated.

本発明に係るスクロール型流体機械は、小型化および軽量化の要請が強い車両用の圧縮機等として好適に利用可能である。   The scroll type fluid machine according to the present invention can be suitably used as a compressor or the like for a vehicle that is strongly demanded to be reduced in size and weight.

１ 圧縮機
２ 固定スクロール
３ 可動スクロール
４ 第一ハウジング
５ 主軸
６ クランク機構
７ 自転阻止機構
８ センタープレート
９ 電動モータ
１０ 第二ハウジング
１１ 軸受
１２ 軸受保持部
１３ 軸方向凹部
１４ 径方向凹部
１５ 吸入ポート
１６ 吐出孔
１７ 吐出室
１８ 吐出ポート
ａ 軸方向凹部と径方向凹部の重複領域の軸方向長さ
ｂ センタープレートの可動スクロール側端面と径方向凹部のテーパ状内面とのなす角度
ｃ、ｅ 軸方向凹部のテーパ状内面と軸方向のなす角度
ｄ 径方向凹部の径方向深さ DESCRIPTION OF SYMBOLS 1 Compressor 2 Fixed scroll 3 Movable scroll 4 First housing 5 Main shaft 6 Crank mechanism 7 Rotation prevention mechanism 8 Center plate 9 Electric motor 10 Second housing 11 Bearing 12 Bearing holding portion 13 Axial recess 14 Radial recess 15 Suction port 16 Discharge hole 17 Discharge chamber 18 Discharge port a Axial length b of overlapping region of axial recess and radial recess b Angle c, e formed by movable scroll side end surface of center plate and tapered inner surface of radial recess The angle between the taper-shaped inner surface and the axial direction d The radial depth of the radial recess

Claims (9)

固定スクロールと可動スクロールからなるスクロール機構を収容する第一ハウジングと、主軸を回転駆動させる電動モータを収容する第二ハウジングと、両ハウジング間に介在し前記主軸の回転運動を前記可動スクロールの旋回運動に変換する運動変換機構を収容し前記可動スクロールに対し自転阻止機構が取り付けられているとともに前記主軸の軸受を保持するセンタープレートとを備え、前記第二ハウジングの内部と前記第一ハウジングの内部とを前記センタープレートの設置部を介して連通する流体通路を有するスクロール型流体機械であって、前記流体通路の少なくとも一部を、前記センタープレートに形成された、前記第二ハウジングの内部に臨み軸方向に延びる軸方向凹部と、前記軸受よりも前記第一ハウジング側に位置し径方向に延びる径方向凹部とを、連通させることにより形成したことを特徴とするスクロール型流体機械。   A first housing that houses a scroll mechanism composed of a fixed scroll and a movable scroll, a second housing that houses an electric motor that rotationally drives the main shaft, and a rotational motion of the main shaft that is interposed between both housings. And a center plate for holding a rotation bearing for the movable scroll and holding a bearing of the main shaft, and an inside of the second housing, an inside of the first housing, A scroll type fluid machine having a fluid passage communicating with the center plate through an installation portion of the center plate, wherein at least a part of the fluid passage faces the inside of the second housing formed in the center plate. An axial recess extending in the direction, and a radial direction located closer to the first housing than the bearing A radial recess extending scroll-type fluid machine characterized by being formed by communicating. 前記軸方向凹部が周方向に複数形成されている、請求項１に記載のスクロール型流体機械。   The scroll type fluid machine according to claim 1, wherein a plurality of the axial recesses are formed in the circumferential direction. 前記軸方向凹部の内面の一部が、前記第二ハウジングの内部側に向けてテーパ状に広がる面に形成されている、請求項１または２に記載のスクロール型流体機械。   3. The scroll type fluid machine according to claim 1, wherein a part of an inner surface of the axial recess is formed on a surface extending in a tapered shape toward the inner side of the second housing. 前記径方向凹部が周方向に環状に延びる凹部に形成されている、請求項１〜３のいずれかに記載のスクロール型流体機械。   The scroll type fluid machine according to any one of claims 1 to 3, wherein the radial recess is formed in a recess extending annularly in a circumferential direction. 前記径方向凹部の内面の一部が、前記第一ハウジングの内部から前記第二ハウジングの内部側に向けてテーパ状に広がる面に形成されている、請求項１〜４のいずれかに記載のスクロール型流体機械。   5. The part according to claim 1, wherein a part of the inner surface of the radial recess is formed on a surface that extends in a tapered shape from the inside of the first housing toward the inside of the second housing. Scroll type fluid machine. 前記軸方向凹部が、前記センタープレートの素形材の製造時に設けられている、請求項１〜５のいずれかに記載のスクロール型流体機械。   The scroll type fluid machine according to any one of claims 1 to 5, wherein the axial recess is provided at the time of manufacturing the shape member of the center plate. 前記センタープレートの素形材が鋳造によって製造され、前記軸方向凹部が型を用いて形成されている、請求項６に記載のスクロール型流体機械。   The scroll type fluid machine according to claim 6, wherein the shape member of the center plate is manufactured by casting, and the axial recess is formed by using a mold. 前記径方向凹部が機械加工により形成されている、請求項１〜７のいずれかに記載のスクロール型流体機械。   The scroll type fluid machine according to any one of claims 1 to 7, wherein the radial recess is formed by machining. 前記センタープレートが、前記第一ハウジングおよび第二ハウジングのいずれかと一体に形成されている、請求項１〜８のいずれかに記載のスクロール型流体機械。
The scroll type fluid machine according to any one of claims 1 to 8, wherein the center plate is formed integrally with either the first housing or the second housing.
JP2009245752A 2009-10-26 2009-10-26 Scroll fluid machine Pending JP2011089507A (en)

Priority Applications (7)

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JP2009245752A JP2011089507A (en) 2009-10-26 2009-10-26 Scroll fluid machine
CA2775384A CA2775384A1 (en) 2009-10-26 2010-10-21 Scroll-type fluid machiner
EP10826303.9A EP2472114A4 (en) 2009-10-26 2010-10-21 Scroll fluid machine
KR1020127007575A KR20120049369A (en) 2009-10-26 2010-10-21 Scroll fluid machine
CN2010800432503A CN102575671A (en) 2009-10-26 2010-10-21 Scroll fluid machine
US13/497,959 US20120237374A1 (en) 2009-10-26 2010-10-21 Scroll-Type Fluid Machiner
PCT/JP2010/006250 WO2011052166A1 (en) 2009-10-26 2010-10-21 Scroll fluid machine

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US20120237374A1 (en) 2012-09-20
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EP2472114A1 (en) 2012-07-04
KR20120049369A (en) 2012-05-16
CN102575671A (en) 2012-07-11

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