JP2010174772A

JP2010174772A - Hermetic compressor

Info

Publication number: JP2010174772A
Application number: JP2009019168A
Authority: JP
Inventors: Hideki Murakami; 秀樹村上; Tsutomu Tsujimoto; 力辻本; Daisuke Funakoshi; 大輔船越; Takashi Morimoto; 敬森本; Noboru Iida; 飯田　　登; Akira Iwashida; 鶸田　　晃; Kiyoshi Sawai; 澤井　　清
Original assignee: Panasonic Corp
Current assignee: Panasonic Corp
Priority date: 2009-01-30
Filing date: 2009-01-30
Publication date: 2010-08-12

Abstract

【課題】固定子の外周が円形形状であっても密閉容器に固定子を焼き嵌めする際の挿入不良を低減させると同時に、吐出されるオイル量の低減と電動機効率低下の抑制と冷凍サイクルの熱交換能力および密閉型圧縮機の効率を同時に向上させること。
【解決手段】密閉容器１の内壁に設けた溝部９の内径円筒部の内径寸法Ａに対して、溝部９を設けていない内径円筒部の内径寸法Ｂを大きくすることで、密閉容器１に固定子２２を挿入する際に、密閉容器１の開口部の内径寸法Ｂが固定子２２の外径寸法よりも大きいため、密閉容器１との接触する軸方向の長さが短くなり、固定子２２をスムーズに挿入できると同時に、吐出されるオイル量の低減と電動機効率低下の抑制と冷凍サイクルの熱交換能力および密閉型圧縮機の効率を同時に向上させることとなる。
【選択図】図１An object of the present invention is to reduce insertion failure when shrink-fitting a stator into a hermetic container even when the outer periphery of the stator is circular, and at the same time, reducing the amount of oil discharged, suppressing reduction in motor efficiency, and reducing the refrigeration cycle. Improving heat exchange capacity and hermetic compressor efficiency at the same time.
The inner diameter dimension B of the inner diameter cylindrical portion where the groove portion 9 is not provided is made larger than the inner diameter dimension A of the inner diameter cylindrical portion of the groove portion 9 provided on the inner wall of the sealed container 1. When the child 22 is inserted, the inner diameter B of the opening of the hermetic container 1 is larger than the outer diameter of the stator 22, so the axial length in contact with the hermetic container 1 is shortened, and the stator 22 Can be inserted smoothly, and at the same time, the amount of oil discharged, the reduction in motor efficiency, the heat exchange capacity of the refrigeration cycle and the efficiency of the hermetic compressor can be improved at the same time.
[Selection] Figure 1

Description

本発明は、空調機、冷凍機、ブロワ、給湯機等に使用される密閉型圧縮機に関するものである。 The present invention relates to a hermetic compressor used for an air conditioner, a refrigerator, a blower, a water heater, and the like.

図１１は、特許文献１および特許文献２に記載された従来の密閉型圧縮機を示すものである。図１１に示すように、密閉容器１の内部に、固定子２２と回転子２４で構成される電動機２とこれによって駆動される圧縮機構部３を配設し、固定子２２の外周が密閉容器１の内壁に焼き嵌めなどで固定されている。圧縮機構部３で圧縮された高温高圧の冷媒ガスが、固定子２２の外周に設けられた切欠部２８及び固定子２２と回転子２４の隙間２６を通過し、密閉容器１上部に設けられた吐出管５から外部冷却回路に吐出されている。固定子２２外周の切欠部２８及び固定子２２内径と回転子２４外径との隙間２６などの電動機２部を通過する冷媒ガスの通路断面積が小さいと電動機２の上部空間７と下部空間８との圧力差が生じ、上部空間７で冷媒ガスから分離されたオイルは密閉容器１内底部に戻りにくくなるとともに、吐出管５から冷媒ガスとともに吐出されるオイル量が多くなっていた。そこで通路断面積を大きくすることによって、吐出されるオイル量を少なくし、圧縮機のオイルレベルの確保と冷凍サイクルの熱交換能力の低下を防止していた。
特開昭６１−２８０７２７号公報特開２００４−１９７６８７号公報 FIG. 11 shows a conventional hermetic compressor described in Patent Literature 1 and Patent Literature 2. As shown in FIG. As shown in FIG. 11, an electric motor 2 including a stator 22 and a rotor 24 and a compression mechanism unit 3 driven by the electric motor 2 are arranged inside the sealed container 1, and the outer periphery of the stator 22 is a sealed container. It is fixed to the inner wall of 1 by shrink fitting. The high-temperature and high-pressure refrigerant gas compressed by the compression mechanism part 3 passes through the notch part 28 provided on the outer periphery of the stator 22 and the gap 26 between the stator 22 and the rotor 24, and is provided at the upper part of the sealed container 1. It is discharged from the discharge pipe 5 to the external cooling circuit. If the cross-sectional area of the refrigerant gas passing through the motor 2 such as the notch 28 on the outer periphery of the stator 22 and the gap 26 between the inner diameter of the stator 22 and the outer diameter of the rotor 24 is small, the upper space 7 and the lower space 8 of the motor 2 are reduced. The oil separated from the refrigerant gas in the upper space 7 is difficult to return to the inner bottom of the sealed container 1 and the amount of oil discharged from the discharge pipe 5 together with the refrigerant gas is large. Therefore, by increasing the cross-sectional area of the passage, the amount of oil discharged is reduced, ensuring the oil level of the compressor and preventing the heat exchange capacity of the refrigeration cycle from being lowered.
Japanese Patent Laid-Open No. 61-280727 Japanese Patent Laid-Open No. 2004-197687

しかしながら、特許文献１に示された構成では、固定子２２切欠部の通路断面積を大きくすることにともない、吐出されるオイル量を少なくすることが可能であるが、一方では固定子２２の切欠を形成したところは、固定子２２の切欠が無い部位より、ヨーク幅が短くなっているため固定子２２の鉄損や磁気抵抗が増加するとともに磁気の飽和などにより電動機の効率が低下してしまうという問題があった。 However, in the configuration shown in Patent Document 1, it is possible to reduce the amount of oil discharged as the passage cross-sectional area of the stator 22 notch is increased, but on the other hand, the notch of the stator 22 is reduced. Is formed, the yoke width is shorter than the portion of the stator 22 where there is no notch, so that the iron loss and magnetic resistance of the stator 22 increase, and the efficiency of the motor decreases due to magnetic saturation and the like. There was a problem.

また、特許文献２に示された構成では、外周がほぼ円形になった固定子２２の積厚の一部が１つの密閉容器１に収納される構成であり、固定子２２を挿入する軸方向の長さが短いため固定子２２を所定の位置に到達させるまでの過程で正確に配置固定することが可能であるが、本発明者等は、外周がほぼ円形になった固定子２２の積厚の全長が１つの密閉容器１に収納される構成において、焼き嵌めにて固定する検討を実施したが、以下の問題が発生した。 Further, in the configuration shown in Patent Document 2, a part of the thickness of the stator 22 having a substantially circular outer periphery is stored in one sealed container 1, and the axial direction in which the stator 22 is inserted Since the length of the stator 22 is short, it is possible to accurately place and fix the stator 22 in the process until the stator 22 reaches the predetermined position. In the configuration in which the entire length of the thickness is accommodated in one sealed container 1, a study of fixing by shrink fitting was performed, but the following problems occurred.

固定子２２を密閉容器１に焼き嵌めするには、密閉容器１全体に高周波加熱を行い、密閉容器１を膨張させ密閉容器１の開口部から挿入する。密閉容器１は通常、電縫管などの溶接鋼管や、一端側（底部）側が閉塞された略コップ状の深絞り容器を使用しているが、内径の真円度および円筒度の精度が悪い為、外周が円形の固定子２２の外周と密閉容器１の軸方向全て同一の内径寸法に挿入する際に、密閉容器１の内径と固定子２２の接触する軸方向の長さが長くなり、固定子２２を所定の位置に到達させるまでの過程で正確に配置固定することができないといった挿入不良を招いてしまう課題が有することを把握した。 In order to shrink fit the stator 22 in the sealed container 1, the whole sealed container 1 is heated at high frequency, and the sealed container 1 is expanded and inserted from the opening of the sealed container 1. The sealed container 1 usually uses a welded steel pipe such as an electric resistance welded pipe or a substantially cup-shaped deep-drawn container with one end (bottom) side closed, but the accuracy of roundness and cylindricity of the inner diameter is poor. Therefore, when the outer periphery of the stator 22 having a circular outer periphery and the axial direction of the sealed container 1 are all inserted into the same inner diameter dimension, the axial length of contact between the inner diameter of the sealed container 1 and the stator 22 is increased. It has been found that there is a problem that causes an insertion failure such that the stator 22 cannot be accurately positioned and fixed in the process until the stator 22 reaches a predetermined position.

本発明は、上記従来の問題点に鑑み、固定子の外周が円形形状であっても密閉容器に固定子を焼き嵌めする際の挿入不良を低減させると同時に、吐出されるオイル量の低減と電動機効率低下の抑制と冷凍サイクルの熱交換能力および密閉型圧縮機の効率を同時に向上させることを目的とする。 In view of the above-described conventional problems, the present invention reduces the amount of oil discharged while simultaneously reducing poor insertion when the stator is shrink-fitted in a sealed container even if the outer periphery of the stator is circular. The purpose is to simultaneously improve the efficiency of the refrigeration cycle and the efficiency of the hermetic compressor as well as the suppression of motor efficiency reduction.

前記従来の課題を解決するために、本発明の密閉型圧縮機は、密閉容器の内部に、固定子と回転子で構成される電動機と前記電動機で駆動される圧縮機構部を配設し、固定子の外周が前記密閉容器の内壁に固定される密閉型圧縮機であって、固定子固定部周辺の密閉容器の内壁に円筒軸方向に延びる溝を設けるとともに、密閉容器の内径寸法が円筒軸方向に延びる溝を設けた箇所と円筒軸方向に延びる溝を設けない箇所で異なる寸法としたものである。 In order to solve the above-described conventional problems, the hermetic compressor of the present invention includes an electric motor composed of a stator and a rotor and a compression mechanism driven by the electric motor inside the hermetic container, A hermetic compressor in which the outer periphery of the stator is fixed to the inner wall of the hermetic container, the inner wall of the hermetic container around the stator fixing part is provided with a groove extending in the cylindrical axial direction, and the inner diameter of the hermetic container is cylindrical. The dimensions are different between a place where the groove extending in the axial direction is provided and a place where the groove extending in the cylindrical axis direction is not provided.

この構成により、密閉容器の内壁に設けた溝部の内径円筒部に対して、溝部を設けていない内径円筒部の内径寸法が大きい、すなわち、固定子を挿入する密閉容器の開口部の内径寸法が大きいため、固定子の外周形状が円形であっても固定子を挿入する際の密閉容器との接触する軸方向の長さが短くなり、固定子をスムーズに挿入できる。さらに固定子の外周をほぼ円筒形にすることで、電動機外周に切り欠きを設けている時と比べて、固定子のヨーク幅が均一にできることから、固定子の鉄損や磁気抵抗が増加する要因を排除出来ることで電動機の効率が向上する。さらには、密閉容器内壁に設けた溝部により、電動機外周に切り欠きを設けている時と同等以上の冷媒の通路断面積を確保できることから、吐出されるオイル量を少なくすることが可能となる。よって、密閉容器に対する固定子の挿入不良を低減し、電動機の効率を向上させるとともに吐出されるオイル量を同等に維持することが可能となる。 With this configuration, the inner diameter dimension of the inner diameter cylindrical portion without the groove portion is larger than the inner diameter cylindrical portion of the groove portion provided on the inner wall of the sealed container, that is, the inner diameter size of the opening portion of the sealed container into which the stator is inserted is larger. Therefore, even when the outer peripheral shape of the stator is circular, the axial length of contact with the hermetic container when the stator is inserted is shortened, and the stator can be inserted smoothly. Furthermore, by making the outer periphery of the stator substantially cylindrical, the yoke width of the stator can be made uniform compared with the case where notches are provided on the outer periphery of the motor, so the iron loss and magnetic resistance of the stator increase. The efficiency of the motor is improved by eliminating the factors. Furthermore, since the groove portion provided in the inner wall of the sealed container can ensure a passage cross-sectional area of the refrigerant that is equal to or greater than that in the case where the notch is provided on the outer periphery of the motor, the amount of oil discharged can be reduced. Therefore, it is possible to reduce the poor insertion of the stator into the sealed container, improve the efficiency of the electric motor, and maintain the same amount of oil to be discharged.

本発明の密閉型圧縮機は、固定子の外周が円形形状であっても密閉容器に固定子を焼き嵌めする際の挿入不良を低減させると同時に、吐出されるオイル量の低減と電動機効率低下の抑制と冷凍サイクルの熱交換能力および密閉型圧縮機の効率を同時に向上出来る。さらに圧縮機のオイルレベルを確保できることから高い信頼性も同時に得ることが可能となる。 The hermetic compressor according to the present invention reduces the poor insertion when the stator is shrink-fitted in a hermetic container even when the outer periphery of the stator is circular, and at the same time, reduces the amount of oil discharged and lowers the motor efficiency. And the heat exchange capacity of the refrigeration cycle and the efficiency of the hermetic compressor can be improved at the same time. Furthermore, since the oil level of the compressor can be secured, high reliability can be obtained at the same time.

第１の発明は、密閉容器の内部に、固定子と回転子で構成される電動機と前記電動機で駆動される圧縮機構部を配設し、固定子の外周が密閉容器の内壁に固定される密閉型圧縮機であって、固定子固定部周辺の密閉容器の内壁に円筒軸方向に延びる溝を設けるとともに、密閉容器の内径寸法が円筒軸方向に延びる溝を設けた箇所と円筒軸方向に延びる溝を設けない箇所で異なる寸法となることで、密閉容器に固定子を挿入する際に密閉容器の開口部の内径寸法が大きいため、密閉容器との接触する軸方向の長さが短くなり、固定子をスムーズに挿入できる効果が得られる。また、密閉容器内壁の溝部により吐出された冷媒ガスが下部空間から上部空間に移動する時の流速を遅くする事が出来る。よって、上部空間と下部空間の圧力差が小さくなり、上部空間に溜ったオイルが自重により密閉容器内のオイル溜りに戻りやすくなり、圧縮機のオイルレベルが確保される。さらに、上部空間のオイルが少なくなるため、吐出冷媒とともに巻き上げられるオイルも少なくなって、圧縮機本体から吐出されるオイル量も低減され、冷凍サイクルの熱交換能力の低下を防止することができる。 In the first invention, an electric motor composed of a stator and a rotor and a compression mechanism portion driven by the electric motor are disposed inside the sealed container, and the outer periphery of the stator is fixed to the inner wall of the sealed container. In the hermetic compressor, a groove extending in the cylindrical axial direction is provided on the inner wall of the sealed container around the stator fixing portion, and a position in which the inner diameter of the sealed container is provided with a groove extending in the cylindrical axial direction and in the cylindrical axial direction. Since the inner diameter of the opening of the sealed container is large when the stator is inserted into the sealed container, the axial length in contact with the sealed container is shortened by having different dimensions at the location where the extending groove is not provided. The effect that the stator can be inserted smoothly is obtained. Moreover, the flow rate when the refrigerant gas discharged by the groove part of the inner wall of the sealed container moves from the lower space to the upper space can be reduced. Therefore, the pressure difference between the upper space and the lower space is reduced, and the oil accumulated in the upper space is easily returned to the oil sump in the sealed container by its own weight, and the oil level of the compressor is secured. Furthermore, since the oil in the upper space is reduced, the amount of oil that is rolled up with the discharged refrigerant is reduced, the amount of oil discharged from the compressor body is reduced, and the heat exchange capacity of the refrigeration cycle can be prevented from being lowered.

第２の発明は、特に、第１の発明の密閉型圧縮機において、密閉容器の内壁に設けた溝部の内径円筒部に対して、溝部を設けていない内径円筒部の内径寸法が密閉容器の内径真円度測定値よりも大きい寸法にすることで、密閉容器に固定子を挿入する際に、密閉容器の開口部の内径寸法が大きいため、密閉容器との接触する軸方向の長さが短くなり、固定子をスムーズに挿入できる。さらに、溝部を設けていない内径円筒部の内径寸法を最低限の大きさに出来ることから、圧縮機構部の体格を最小限の寸法で構成できる事から、材料費の抑制をする事が出来る。 In particular, the second aspect of the invention is the hermetic compressor according to the first aspect of the invention, in which the inner diameter dimension of the inner diameter cylindrical portion not provided with the groove portion is smaller than the inner diameter cylindrical portion of the groove portion provided on the inner wall of the sealed container. Since the inner diameter of the opening of the sealed container is large when the stator is inserted into the sealed container by making the dimension larger than the inner diameter roundness measurement value, the axial length in contact with the sealed container is small. Shorter and the stator can be inserted smoothly. Furthermore, since the inner diameter dimension of the inner diameter cylindrical part not provided with the groove part can be made the minimum size, the physique of the compression mechanism part can be configured with the minimum dimension, so that the material cost can be suppressed.

第３の発明は、特に、第１〜２の発明の密閉型圧縮機において、固定子固定部周辺に設けた密閉容器の内壁に円筒軸方向に延びる溝部の断面積を、固定子の積厚寸法と同等以上の長さの密閉容器の円筒軸方向に形成し、かつ固定子の上下部に開口することにより、密閉容器の溝部を流れる冷媒ガスの流速が乱れる事無く上部空間に通過することができ圧縮機本体から吐出されるオイル量が低減され、冷凍サイクルの熱交換能力の低下を防止することができる。 In a third aspect of the invention, in particular, in the hermetic compressors of the first and second aspects of the invention, the cross-sectional area of the groove portion extending in the cylindrical axial direction on the inner wall of the hermetic container provided around the stator fixing portion is determined by the thickness of the stator. By forming it in the cylindrical axis direction of a sealed container with a length equal to or greater than the size and opening the upper and lower parts of the stator, the flow rate of the refrigerant gas flowing through the groove of the sealed container can pass through the upper space without being disturbed. Therefore, the amount of oil discharged from the compressor body is reduced, and a decrease in the heat exchange capacity of the refrigeration cycle can be prevented.

第４の発明は、特に、第１〜３の発明の密閉型圧縮機において、溝を複数個設けることで、冷媒ガスの通路断面積を大きくすることが可能となる。これによって、上部空間と下部空間の圧力差を小さくすることができ、圧縮機本体から吐出されるオイル量が低減され、冷凍サイクルの熱交換能力の低下を防止することができる。 In the fourth aspect of the invention, in particular, in the hermetic compressors of the first to third aspects, the passage sectional area of the refrigerant gas can be increased by providing a plurality of grooves. As a result, the pressure difference between the upper space and the lower space can be reduced, the amount of oil discharged from the compressor body can be reduced, and a reduction in the heat exchange capacity of the refrigeration cycle can be prevented.

第５の発明は、特に、第１〜４の発明の密閉型圧縮機において、溝部を斜めに設けることで、冷媒ガスの通過距離を長くすることが可能となる。よって、固定子の高さが低い場合においても、冷媒ガスが固定子と密閉容器の間を通過する時の流速を十分に遅くすることが可能となり、上部空間と下部空間の圧力差を小さく出来ることから、吐出されるオイル量が低減され、冷凍サイクルの熱交換能力の低下を防止することができる。 In the fifth aspect of the invention, in particular, in the hermetic compressors of the first to fourth aspects of the invention, it is possible to increase the passage distance of the refrigerant gas by providing the groove portion obliquely. Therefore, even when the height of the stator is low, it is possible to sufficiently slow down the flow rate when the refrigerant gas passes between the stator and the sealed container, and the pressure difference between the upper space and the lower space can be reduced. For this reason, the amount of oil discharged is reduced, and a decrease in the heat exchange capacity of the refrigeration cycle can be prevented.

第６の発明は、特に、第４の発明の密閉型圧縮機において、密閉容器の溝を固定子のスロット数と同一数またはスロット数の約数におけるどちらか一方の整数に１を除くｎ倍数の溝を設けることにより、密閉容器に固定子を焼き嵌め等で固着させた場合の固定子にかかる密閉容器の収縮時の応力を均等化させ、固定子における鉄損の分布の偏りを抑制することができ周方向における磁束密度の安定化を図る事ができるため、電動機の効率向上が出来る。 In particular, the sixth aspect of the invention is the hermetic compressor according to the fourth aspect of the invention, wherein the groove of the hermetic container has the same number as the number of slots of the stator or a multiple of the divisor of the number of slots except for one multiple of n. By providing the groove, the stress at the time of shrinkage of the closed container applied to the stator when the stator is fixed to the closed container by shrink fitting or the like is equalized, and the distribution of iron loss distribution in the stator is suppressed. Since the magnetic flux density in the circumferential direction can be stabilized, the efficiency of the electric motor can be improved.

第７の発明は、特に、第１〜４および６のいずれかの発明の密閉型圧縮機において、電動機の巻線形態が集中巻の構成の場合に、密閉容器の溝部を固定子のティース部の背面に設けたることにより、密閉容器に固定子を焼き嵌め等で固着させた場合の固定子にかかる密閉容器の収縮時の応力による鉄損の増加がヨーク部の背面に設けた時よりも抑制することができ電動機の効率向上が出来る。 In a seventh aspect of the invention, in particular, in the hermetic compressor according to any one of the first to fourth and sixth aspects of the invention, when the winding form of the electric motor is a concentrated winding configuration, the groove portion of the hermetic container is replaced with the teeth portion of the stator. When the stator is fixed to the sealed container by shrink fitting, the increase in iron loss due to the stress at the time of contraction of the sealed container applied to the stator is larger than that provided at the back of the yoke part. The efficiency of the electric motor can be improved.

第８の発明は、特に、第１〜７の発明の密閉型圧縮機において、固定子の外周をほぼ円筒形にすることにより、電動機の効率を向上することが出来る。また、密閉容器の溝部により固定子と密閉容器の間の通路断面積が確保されるため、電動機の切り欠きがあった時と同等のオイル吐出量にすることが出来る。よって、電動機の効率の向上によって圧縮機本体の効率が向上するとともに、吐出されるオイル量が低減され冷凍サイクルの熱交換能力の低下を防止することができる。 In the eighth aspect of the invention, in particular, in the hermetic compressors of the first to seventh aspects of the invention, the efficiency of the electric motor can be improved by making the outer periphery of the stator substantially cylindrical. Further, since the cross-sectional area of the passage between the stator and the hermetic container is ensured by the groove portion of the hermetic container, the oil discharge amount can be equal to that when the motor is notched. Therefore, the efficiency of the compressor body can be improved by improving the efficiency of the electric motor, and the amount of oil discharged can be reduced to prevent the heat exchange capacity of the refrigeration cycle from being lowered.

以下、本発明の実施の形態について、図面を参照しながら説明する。なお、この実施の形態によって本発明が限定されるものではない。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

（実施の形態１）
図１は、本発明の第１の実施の形態における密閉型圧縮機の縦断面図であり、図２は、本発明の第１の実施形態における電動機部の上部空間から見た横断面図である。 (Embodiment 1)
FIG. 1 is a longitudinal sectional view of a hermetic compressor according to a first embodiment of the present invention, and FIG. 2 is a transverse sectional view seen from an upper space of an electric motor section according to the first embodiment of the present invention. is there.

図１において、本実施の形態の密閉型圧縮機は、底部にオイルの貯溜されたオイル溜り６を有する密閉容器１で、この容器内には上側に電動機２が、下側に圧縮機構部３がそれぞれ収納されている。電動機２は回転軸３１に装着された回転子２４と、外周に切欠部２８を形成した固定子２２とで構成されている。圧縮機構部３は、シリンダ３０と、回転軸
３１の偏芯部３１ａによりシリンダ３０内を回転するピストン３２とこのピストン３２に接してシリンダ３０内を吸入室と圧縮室とに分けるベーン（図示せず）とシリンダ３０の開口を封じる上軸受部３４と下軸受部３５と、この上軸受部３４に取り付けられた吐出弁（図示せず）と、この吐出弁を覆うカップマフラー３７とで構成されており、回転子２４からの駆動によりシリンダ３０内をピストン３２が回転し冷媒が圧縮される構造となっている。また、密閉容器１の内壁に設けた溝部９の内径円筒部の内径寸法Ａに対して、溝部９を設けていない内径円筒部の内径寸法Ｂを大きくする構成としている。密閉容器１は、電縫管などの溶接鋼管や、一端側（底部）側が閉塞された略コップ状の深絞り容器を使用しているため、内径寸法Ｂは密閉容器１の内径真円度測定値よりも大きい寸法にすることが望ましい。 In FIG. 1, the hermetic compressor of the present embodiment is a hermetic container 1 having an oil reservoir 6 in which oil is stored at the bottom, in which an electric motor 2 is located on the upper side and a compression mechanism part 3 on the lower side. Is stored. The electric motor 2 includes a rotor 24 mounted on a rotating shaft 31 and a stator 22 having a notch 28 formed on the outer periphery. The compression mechanism unit 3 includes a cylinder 30, a piston 32 that rotates in the cylinder 30 by the eccentric portion 31 a of the rotating shaft 31, and a vane (not shown) that divides the inside of the cylinder 30 into a suction chamber and a compression chamber in contact with the piston 32. 2), an upper bearing portion 34 and a lower bearing portion 35 that seal the opening of the cylinder 30, a discharge valve (not shown) attached to the upper bearing portion 34, and a cup muffler 37 that covers the discharge valve. The piston 24 rotates in the cylinder 30 by driving from the rotor 24 and the refrigerant is compressed. Further, the inner diameter dimension B of the inner diameter cylindrical portion not provided with the groove portion 9 is made larger than the inner diameter dimension A of the inner diameter cylindrical portion of the groove portion 9 provided on the inner wall of the sealed container 1. Since the sealed container 1 uses a welded steel pipe such as an electric resistance welded pipe or a substantially cup-shaped deep-drawn container with one end (bottom) side closed, the inner diameter dimension B is the inner diameter roundness measurement of the sealed container 1. It is desirable to make the dimension larger than the value.

以上のように構成された密閉型圧縮機において、図２に示すように、固定子２２の外周が密閉容器１の内壁に固定されている。密閉容器１内の空間が、電動機２を挟んで上部空間７と下部空間８の大きく二つに分離されている。密閉容器１の内壁に円筒軸方向に延びるように設けた溝部９の断面積を、固定子２２の積厚寸法と同等以上の長さの密閉容器１の円筒軸方向に形成し、溝部９を、固定子上部空間７と下部空間８の両方に開口する構成としている。 In the hermetic compressor configured as described above, the outer periphery of the stator 22 is fixed to the inner wall of the hermetic container 1 as shown in FIG. The space in the sealed container 1 is largely divided into an upper space 7 and a lower space 8 with the electric motor 2 interposed therebetween. The cross-sectional area of the groove 9 provided to extend in the cylindrical axis direction on the inner wall of the sealed container 1 is formed in the cylindrical axis direction of the sealed container 1 having a length equal to or greater than the stacking dimension of the stator 22, and the groove 9 is formed. The stator is open to both the upper space 7 and the lower space 8.

図１において、高圧に圧縮された冷媒は、カップマフラー３７より密閉容器１内に吐出され、固定子２２と密閉容器１内壁で形成された切欠部２８と、固定子２２と密閉容器１の内壁で形成された溝部９および、電動機２のエアギャップ２６を通って、電動機２の上部空間７に送り出され、冷媒吐出管５から密閉容器１の外に吐出される。矢印は、冷媒の流れを示す。 In FIG. 1, the refrigerant compressed to a high pressure is discharged from the cup muffler 37 into the sealed container 1, and a notch 28 formed by the stator 22 and the inner wall of the sealed container 1, and the inner wall of the stator 22 and the sealed container 1. And the air gap 26 of the electric motor 2 through the groove 9 and the air gap 26 of the electric motor 2, and is discharged from the refrigerant discharge pipe 5 to the outside of the sealed container 1. Arrows indicate the refrigerant flow.

以上のように、本実施の形態においては、密閉容器１の内壁に設けた溝部９の内径円筒部の内径寸法Ａに対して、溝部９を設けていない内径円筒部の内径寸法Ｂを大きくすることで、密閉容器１に固定子２２を挿入する際に、密閉容器１の開口部の内径寸法Ｂが固定子２２の外径寸法よりも大きいため、密閉容器１との接触する軸方向の長さが短くなり、固定子２２をスムーズに挿入できる効果が得られる。さらに、溝部９を設けることで、冷媒の通路断面積が増加し、吐出された冷媒ガスが下部空間８から上部空間７に移動する時の流速が遅くなるため、上部空間７と下部空間８の圧力差が減少する。よって、冷媒から分離されたオイルが自重により、上部空間７から下部空間８のオイル溜り６に戻りやすくなるため、圧縮機のオイルレベルが確保できる。また、上部空間のオイルが少なくなるため、吐出冷媒とともに巻き上げられるオイルも少なくなって、圧縮機本体から吐出されるオイル量も減少し、冷凍サイクルの熱交換能力の低下を防止することができる。 As described above, in the present embodiment, the inner diameter dimension B of the inner diameter cylindrical portion not provided with the groove portion 9 is made larger than the inner diameter dimension A of the inner diameter cylindrical portion of the groove portion 9 provided on the inner wall of the sealed container 1. Thus, when the stator 22 is inserted into the hermetic container 1, the inner diameter dimension B of the opening of the hermetic container 1 is larger than the outer diameter dimension of the stator 22. Thus, the effect that the stator 22 can be inserted smoothly is obtained. Furthermore, the provision of the groove 9 increases the cross-sectional area of the refrigerant passage, and the flow rate when the discharged refrigerant gas moves from the lower space 8 to the upper space 7 is reduced. Therefore, the upper space 7 and the lower space 8 Pressure difference decreases. Therefore, the oil separated from the refrigerant easily returns from the upper space 7 to the oil sump 6 in the lower space 8 due to its own weight, so that the oil level of the compressor can be secured. Further, since the oil in the upper space is reduced, the amount of oil that is rolled up with the discharged refrigerant is reduced, the amount of oil discharged from the compressor body is reduced, and the heat exchange capacity of the refrigeration cycle can be prevented from being lowered.

また、密閉容器１の内壁に設けた溝部９の内径円筒部の内径寸法Ａに対して、溝部９を設けていない内径円筒部の内径寸法Ｂが密閉容器の内径真円度測定値よりも大きい寸法にすることで、密閉容器１に固定子２２を挿入する際に、密閉容器１の開口部の内径寸法が大きいため、密閉容器１との接触する軸方向の長さが短くなり、固定子２２をスムーズに挿入できる。さらに、溝部９を設けていない内径円筒部の内径寸法を最低限の大きさに出来ることから、圧縮機構部の体格を最小限の寸法で構成できる事から、材料費の抑制をする事が出来る。 Further, the inner diameter dimension B of the inner diameter cylindrical portion without the groove portion 9 is larger than the inner diameter roundness measurement value of the sealed container with respect to the inner diameter size A of the inner diameter cylindrical portion of the groove portion 9 provided on the inner wall of the sealed container 1. With the dimensions, when the stator 22 is inserted into the sealed container 1, since the inner diameter of the opening of the sealed container 1 is large, the axial length in contact with the sealed container 1 is shortened, and the stator 22 can be inserted smoothly. Furthermore, since the inner diameter dimension of the inner diameter cylindrical part not provided with the groove part 9 can be made the minimum size, the physique of the compression mechanism part can be configured with the minimum dimension, and the material cost can be suppressed. .

また、固定子固定部周辺に設けた密閉容器１の内壁に円筒軸方向に延びる溝部９の断面積を、固定子２２の積厚寸法と同等以上の長さの密閉容器１の円筒軸方向に形成し、かつ固定子２２の上下部に開口することにより、密閉容器１の溝部９を流れる冷媒ガスの流速が乱れる事無く上部空間に通過することができ圧縮機本体から吐出されるオイル量が低減され、冷凍サイクルの熱交換能力の低下を防止することができる。 Further, the cross-sectional area of the groove portion 9 extending in the cylindrical axial direction on the inner wall of the hermetic container 1 provided around the stator fixing portion is set in the cylindrical axial direction of the hermetic container 1 having a length equal to or larger than the thickness of the stator 22. By forming and opening the upper and lower portions of the stator 22, the flow rate of the refrigerant gas flowing through the groove portion 9 of the sealed container 1 can pass through the upper space without being disturbed, and the amount of oil discharged from the compressor body is reduced. It is possible to prevent a decrease in the heat exchange capacity of the refrigeration cycle.

また、図３に示すように、密閉容器１内の下側に電動機２が、上側に圧縮機構部３が収納されている場合も同等の効果が得られるものである。 In addition, as shown in FIG. 3, the same effect can be obtained when the electric motor 2 is stored in the lower side of the sealed container 1 and the compression mechanism unit 3 is stored in the upper side.

また、図２に示すように、溝部９を複数個設けることで、冷媒ガスの通路断面積をさらに大きくすることができるため、上部空間７と下部空間８の圧力差を小さくすることが可能となる。 In addition, as shown in FIG. 2, by providing a plurality of grooves 9, the refrigerant gas passage cross-sectional area can be further increased, so that the pressure difference between the upper space 7 and the lower space 8 can be reduced. Become.

また、図４に示すように溝部９を斜めに設けることで、冷媒ガスの通過距離を長くすることが可能となる。これによって、固定子２２の高さが低い場合でも、溝９を通過する時に十分に冷媒の流速を遅くすることが可能となり、上部空間７と下部空間８の圧力差を小さくすることが可能となる。 Moreover, as shown in FIG. 4, it is possible to lengthen the passage distance of the refrigerant gas by providing the grooves 9 obliquely. As a result, even when the height of the stator 22 is low, the flow rate of the refrigerant can be sufficiently slowed when passing through the groove 9, and the pressure difference between the upper space 7 and the lower space 8 can be reduced. Become.

また、図５に示すように溝部９が密閉容器１の円周方向の幅より、径方向の深さを小さくすることで、吐出管５から冷媒ガスとともに吐出されるオイル量を低減したまま、密閉容器１の外周を大きくせずにコンパクトな密閉型圧縮機を提供することができる。 In addition, as shown in FIG. 5, the groove 9 has a radial depth smaller than the circumferential width of the sealed container 1, thereby reducing the amount of oil discharged together with the refrigerant gas from the discharge pipe 5. A compact hermetic compressor can be provided without enlarging the outer periphery of the hermetic container 1.

（実施の形態２）
図６は本発明第２の実施の形態における密閉型圧縮機の縦断面図であり、図７は、本発明第２の実施形態における電動機部の上部空間から見た横断面図である。 (Embodiment 2)
FIG. 6 is a longitudinal sectional view of a hermetic compressor according to the second embodiment of the present invention, and FIG. 7 is a transverse sectional view seen from the upper space of the electric motor section according to the second embodiment of the present invention.

図６において圧縮機は、底部にオイルの貯溜されたオイル溜り６を有する密閉容器１で、この容器内には上側に電動機２が、下側に圧縮機構部３がそれぞれ収納されている。電動機２は回転軸３１に装着された回転子２４と、固定子２２とで構成されている。固定子２２の外周が密閉容器１の内壁に固定され、密閉容器１内の空間が、電動機２を挟んで上部空間７と下部空間８の大きく二つに分離されており、密閉容器１の内壁に設けた溝９が、上部空間７と下部空間８の両方に開口する構成としている。圧縮機構部３は、シリンダ３０と、回転軸３１の偏芯部３１ａによりシリンダ３０内を回転するピストン３２とこのピストン３２に接してシリンダ３０内を吸入室と圧縮室とに分けるベーン（図示せず）とシリンダ３０の開口を封じる上軸受部３４と下軸受部３５と、この上軸受部３４に取り付けられた吐出弁（図示せず）と、この吐出弁を覆うカップマフラー３７とで構成されており、回転子２４からの駆動によりシリンダ３０内をピストン３２が回転し冷媒が圧縮される構造となっている。また、密閉容器１の内壁に設けた溝部９の内径円筒部の内径寸法Ａに対して、溝部９を設けていない内径円筒部の内径寸法Ｂを大きくする構成としている。密閉容器１は、電縫管などの溶接鋼管や、一端側（底部）側が閉塞された略コップ状の深絞り容器を使用しているため、内径寸法Ｂは密閉容器１の内径真円度測定値よりも大きい寸法にすることが望ましい。 In FIG. 6, the compressor is a sealed container 1 having an oil reservoir 6 in which oil is stored at the bottom, and an electric motor 2 is accommodated in the upper part and a compression mechanism part 3 is accommodated in the lower part. The electric motor 2 includes a rotor 24 attached to a rotary shaft 31 and a stator 22. The outer periphery of the stator 22 is fixed to the inner wall of the hermetic container 1, and the space in the hermetic container 1 is separated into two parts, an upper space 7 and a lower space 8, with the electric motor 2 interposed therebetween. The groove 9 provided in the opening is configured to open to both the upper space 7 and the lower space 8. The compression mechanism unit 3 includes a cylinder 30, a piston 32 that rotates in the cylinder 30 by the eccentric portion 31 a of the rotating shaft 31, and a vane (not shown) that divides the inside of the cylinder 30 into a suction chamber and a compression chamber in contact with the piston 32. 2), an upper bearing portion 34 and a lower bearing portion 35 that seal the opening of the cylinder 30, a discharge valve (not shown) attached to the upper bearing portion 34, and a cup muffler 37 that covers the discharge valve. The piston 24 rotates in the cylinder 30 by driving from the rotor 24 and the refrigerant is compressed. Further, the inner diameter dimension B of the inner diameter cylindrical portion not provided with the groove portion 9 is made larger than the inner diameter dimension A of the inner diameter cylindrical portion of the groove portion 9 provided on the inner wall of the sealed container 1. Since the sealed container 1 uses a welded steel pipe such as an electric resistance welded pipe or a substantially cup-shaped deep-drawn container with one end (bottom) side closed, the inner diameter dimension B is the inner diameter roundness measurement of the sealed container 1. It is desirable to make the dimension larger than the value.

圧縮された冷媒は、カップマフラー３７より密閉容器１内に吐出され、固定子２２と密閉容器１内壁で形成された溝部９と電動機２のエアギャップ２６を通って、電動機２の上部へ送り出され、冷媒吐出管５から密閉容器１の外に吐出される。矢印は、冷媒の流れを示す。また、図７に示すように、固定子２２の外周形状は、ほぼ円筒形の構成をしている。 The compressed refrigerant is discharged from the cup muffler 37 into the hermetic container 1, and is sent to the upper part of the electric motor 2 through the groove portion 9 formed by the stator 22 and the inner wall of the hermetic container 1 and the air gap 26 of the electric motor 2. The refrigerant is discharged from the refrigerant discharge pipe 5 to the outside of the sealed container 1. Arrows indicate the refrigerant flow. Further, as shown in FIG. 7, the outer peripheral shape of the stator 22 has a substantially cylindrical configuration.

以上のように、本実施の形態においては、密閉容器１の内壁に設けた溝部９の内径円筒部に対して、溝部９を設けていない内径円筒部の内径寸法Ｂを大きくすることで、密閉容器１に固定子２２を挿入する際に、密閉容器１の開口部の内径寸法Ｂが固定子２２の外径寸法よりも大きいため、密閉容器１との接触する軸方向の長さが短くなり、固定子２２をスムーズに挿入できる効果が得られる。さらに、固定子２２の外周をほぼ円筒形にすることで、電動機外周に切り欠きを設けている時と比べて、固定子２２のヨーク幅が均一にできることから、固定子２２の鉄損や磁気抵抗が増加する要因を排除出来ることで電動機２
の効率が向上する。 As described above, in the present embodiment, the inner diameter dimension B of the inner diameter cylindrical portion not provided with the groove portion 9 is increased with respect to the inner diameter cylindrical portion of the groove portion 9 provided on the inner wall of the sealed container 1. When the stator 22 is inserted into the container 1, since the inner diameter B of the opening of the sealed container 1 is larger than the outer diameter of the stator 22, the axial length in contact with the sealed container 1 is shortened. The effect that the stator 22 can be inserted smoothly is obtained. Further, by making the outer periphery of the stator 22 substantially cylindrical, the yoke width of the stator 22 can be made uniform as compared with the case where notches are provided on the outer periphery of the electric motor. Electric motor 2 by eliminating the cause of increased resistance
Increases efficiency.

また、密閉容器１内壁に設けた溝部９により、電動機２の外周に切り欠きを設けている時と同様の冷媒の通路断面積を確保できることから、吐出されるオイル量を少なくすることが出来る。よって、電動機２の効率を向上させ、同時に吐出されるオイル量を電動機１の切り欠きがあった時と同等に維持することが可能となる。 Further, the groove 9 provided on the inner wall of the sealed container 1 can secure the same passage cross-sectional area of the refrigerant as when the notch is provided on the outer periphery of the electric motor 2, so that the amount of oil discharged can be reduced. Therefore, it is possible to improve the efficiency of the electric motor 2 and maintain the amount of oil discharged at the same time as when the electric motor 1 is notched.

（実施の形態３）
図８ないし図１０は本発明第３の実施の形態における電動機部の横断面図である。なお、前述の実施の形態と同一構成要素には同一の符号を付与して説明を省略する。 (Embodiment 3)
8 to 10 are cross-sectional views of the electric motor unit according to the third embodiment of the present invention. In addition, the same code | symbol is provided to the same component as above-mentioned embodiment, and description is abbreviate | omitted.

図８において、電動機２の固定子２２に設けられたティース４２と、スロット４４を有する。ティース４２には、固定子２２との間に図示しない絶縁フィルム、インシュレータ等の絶縁物を介して直接巻線４６が施されている。また、固定子２２は、各ティース間を連結する略環状のヨーク４８を有しており、固定子２２の外周はほぼ円筒形の構成をしている。回転子２４は、固定子２２の内側に、固定子２２と同心円状に、回転自在に保持されており、回転子２４は、永久磁石が埋設されている埋め込み磁石型回転子を示している。また、軸孔５２には圧縮機構部３の回転軸３１が挿入されている。一方、密閉容器１の円周方向の内壁には、固定子２２と同一数の溝部９を等間隔設けており、固定子２２のティース４２部背面に溝部９の中心が対向するように構成している。 In FIG. 8, a tooth 42 provided on the stator 22 of the electric motor 2 and a slot 44 are provided. A winding 46 is directly provided between the teeth 42 and the stator 22 via an insulating material such as an insulating film or an insulator (not shown). The stator 22 has a substantially annular yoke 48 for connecting the teeth, and the outer periphery of the stator 22 has a substantially cylindrical configuration. The rotor 24 is rotatably held concentrically with the stator 22 inside the stator 22, and the rotor 24 is an embedded magnet type rotor in which a permanent magnet is embedded. Further, the rotation shaft 31 of the compression mechanism unit 3 is inserted into the shaft hole 52. On the other hand, the same number of groove portions 9 as the stator 22 are provided at equal intervals on the inner wall in the circumferential direction of the hermetic container 1, and the center of the groove portion 9 faces the back surface of the teeth 42 portion of the stator 22. ing.

また、図９においては、密閉容器１の円周方向における内壁の溝部９を固定子２２のスロット４４数（２４スロット）の約数における整数の１つである２の２倍である４箇所に溝部９を等間隔設けており、固定子２２のティース４２部背面に６つおきに溝部９の中心が対向するように構成している。 Further, in FIG. 9, the groove portion 9 on the inner wall in the circumferential direction of the hermetic container 1 is provided at four locations that are two times 2 which is one of the integers of the number of slots 44 (24 slots) of the stator 22. The groove portions 9 are provided at equal intervals, and the center of the groove portions 9 is opposed to the back surface of the teeth 42 portion of the stator 22 every sixth.

また、図１０は密閉容器１の溝部９をヨーク４８部の背面に対向させた場合の構成を示している。 FIG. 10 shows a configuration when the groove portion 9 of the sealed container 1 is opposed to the back surface of the yoke 48 portion.

以上のように、本実施の形態においては、密閉容器１の内壁に設けた溝部９が、１つの固定子２２のティース４２部の背面に設けることにより、密閉容器１に固定子２２を焼き嵌め等で固着させた場合の固定子２２にかかる密閉容器１の収縮時の応力による鉄損の増加をヨーク４８部の背面に設けた時よりも抑制する事ができる。それは、ヨーク４８部の背面よりティース４２部の背面における固定子２２の剛性が高いためである。固定子２２の電磁鋼板は、圧縮応力により鉄損を増加させる性質を持っていることは公知であり、密閉容器１の収縮時における圧縮応力の少ないティース４２部背面に溝部９を配置する事で、電動機２の効率向上が出来る。また、密閉容器１の溝部９を固定子２２のスロット数と同一数またはスロット数の約数におけるどちらか一方の整数に１を除くｎ倍数の溝部９を設けることにより、固定子２２と密閉容器１の横断面における上下左右の対称性が保たれる事から、固定子２２にかかる応力が少なくなり、密閉容器１に固定子２２を焼き嵌め等で固着させた場合の固定子２２にかかる密閉容器１の収縮時の応力を均等化させ、固定子２２における鉄損の分布の偏りを抑制することができ周方向における磁束密度の安定化を図る事ができるため、電動機２の効率向上が出来る。 As described above, in the present embodiment, the groove portion 9 provided on the inner wall of the sealed container 1 is provided on the back surface of the tooth 42 portion of one stator 22, so that the stator 22 is shrink-fitted into the sealed container 1. Thus, the increase in iron loss due to the stress at the time of contraction of the sealed container 1 applied to the stator 22 when the stator 22 is fixed can be suppressed more than when it is provided on the back surface of the yoke 48 part. This is because the rigidity of the stator 22 on the back surface of the tooth 42 portion is higher than that on the back surface of the yoke 48 portion. It is known that the magnetic steel sheet of the stator 22 has the property of increasing iron loss due to compressive stress. By arranging the groove 9 on the back surface of the tooth 42 portion where the compressive stress is small when the sealed container 1 is contracted. The efficiency of the electric motor 2 can be improved. Further, the groove portion 9 of the hermetic container 1 is provided with the n-fold multiple of the groove portion 9 excluding 1 in either the same number as the number of slots of the stator 22 or a divisor of the number of slots. Since the vertical and horizontal symmetry in the cross section of 1 is maintained, the stress applied to the stator 22 is reduced, and the sealing applied to the stator 22 when the stator 22 is fixed to the sealed container 1 by shrink fitting or the like. Since the stress at the time of contraction of the container 1 can be equalized, the uneven distribution of iron loss in the stator 22 can be suppressed, and the magnetic flux density in the circumferential direction can be stabilized. Therefore, the efficiency of the electric motor 2 can be improved. .

以上のように、本発明の密閉型圧縮機は、固定子の外周が円形形状であっても密閉容器に固定子を焼き嵌めする際の挿入不良を低減させると同時に、電動機の効率を向上させ、冷媒ガスとともに吐出されるオイル量を低減することで、冷凍サイクルの熱交換能力の向上と圧縮機本体の効率の向上が得られる。さらに圧縮機のオイルレベルを確保できることから高い信頼性も同時に得ることが可能となり、ＨＦＣ系冷媒やＨＣＦＣ系冷媒を用いた
エアーコンディショナー用圧縮機のほかに、自然冷媒ＣＯ_２を用いたエアーコンディショナーやヒートポンプ式給湯機などの用途にも適用できる。 As described above, the hermetic compressor of the present invention reduces the poor insertion when the stator is shrink-fitted in the hermetic container even when the outer periphery of the stator is circular, and at the same time improves the efficiency of the electric motor. By reducing the amount of oil discharged together with the refrigerant gas, it is possible to improve the heat exchange capacity of the refrigeration cycle and improve the efficiency of the compressor body. Furthermore, since the oil level of the compressor can be secured, high reliability can be obtained at the same time. In addition to the compressor for the air conditioner using the HFC refrigerant or the HCFC refrigerant, the air conditioner using the natural refrigerant CO ₂ It can also be applied to uses such as heat pump water heaters.

本発明の実施の形態１における密閉型圧縮機の縦断面図1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention. 本発明の実施の形態１における密閉型圧縮機の横断面図1 is a cross-sectional view of a hermetic compressor according to Embodiment 1 of the present invention. 本発明の実施の形態１における密閉型圧縮機の他の構成を示す縦断面図The longitudinal cross-sectional view which shows the other structure of the hermetic compressor in Embodiment 1 of this invention 本発明の実施の形態１における密閉型圧縮機の要部を示す拡大側面図The expanded side view which shows the principal part of the hermetic compressor in Embodiment 1 of this invention. 本発明の実施の形態１における密閉型圧縮機の要部を示す拡大平面図The enlarged plan view which shows the principal part of the hermetic compressor in Embodiment 1 of this invention. 本発明の実施の形態２における密閉型圧縮機の縦断面図Vertical sectional view of a hermetic compressor according to Embodiment 2 of the present invention 本発明の実施の形態２における密閉型圧縮機の横断面図Cross-sectional view of hermetic compressor in embodiment 2 of the present invention 本発明の実施の形態３における密閉型圧縮機の横断面図Cross-sectional view of hermetic compressor according to Embodiment 3 of the present invention 本発明の実施の形態３における密閉型圧縮機の横断面図Cross-sectional view of hermetic compressor according to Embodiment 3 of the present invention 本発明の実施の形態３における密閉型圧縮機の横断面図Cross-sectional view of hermetic compressor according to Embodiment 3 of the present invention 従来の密閉型圧縮機を示す縦断面図Longitudinal sectional view showing a conventional hermetic compressor

１密閉容器
２電動機
２２固定子
２４回転子
２６エアギャップ
２８切欠部
３圧縮機構部
３０シリンダ
３１回転軸
３１ａ偏芯部
３２ピストン
３４上軸受部
３５下軸受部
３７カップマフラー
４上シェル
５冷媒吐出管
６オイル溜り
７上部空間
８下部空間
９溝部
４２ティース
４４スロット
４６ヨーク
４８巻線
５２軸孔 DESCRIPTION OF SYMBOLS 1 Airtight container 2 Electric motor 22 Stator 24 Rotor 26 Air gap 28 Notch part 3 Compression mechanism part 30 Cylinder 31 Rotating shaft 31a Eccentric part 32 Piston 34 Upper bearing part 35 Lower bearing part 37 Cup muffler 4 Upper shell 5 Refrigerant discharge pipe 6 Oil reservoir 7 Upper space 8 Lower space 9 Groove 42 Teeth 44 Slot 46 Yoke 48 Winding 52 Shaft hole

Claims

A hermetic compressor in which an electric motor composed of a stator and a rotor and a compression mechanism driven by the electric motor are arranged inside the hermetic container, and an outer periphery of the stator is fixed to an inner wall of the hermetic container A groove extending in the cylindrical axis direction is provided on the inner wall of the sealed container around the stator fixing portion, and the inner diameter dimension of the sealed container extends in the cylindrical axis direction and a portion provided with the groove extending in the cylindrical axis direction. A hermetic compressor characterized by having different dimensions where no groove is provided.

2. The inner diameter dimension of the sealed container is characterized in that the portion where the groove extending in the cylindrical axis direction is not provided is made larger than the roundness measurement value than the portion where the groove extending in the cylindrical axis direction is provided. Hermetic compressor.

A cross-sectional area of a groove extending in the cylindrical axial direction on the inner wall of the hermetic container provided around the stator fixing part is formed in the cylindrical axial direction of the hermetic container with a length equal to or greater than the thickness of the stator, and the fixing The hermetic compressor according to claim 1, wherein the hermetic compressor opens at the upper and lower portions of the child.

The hermetic compressor according to any one of claims 1 to 3, wherein a plurality of grooves are provided.

The hermetic compressor according to any one of claims 1 to 4, wherein the grooves are provided obliquely.

The groove of an airtight container is provided with the groove | channel of the n multiple except 1 in the integer of either the same number as the slot number of a stator, or the divisor of a slot number at equal intervals. Hermetic compressor.

The hermetic compressor according to any one of claims 1 to 4 and 6, wherein a groove of the hermetic container is provided on a back surface of the teeth portion of the stator.

The hermetic compressor according to any one of claims 1 to 7, wherein the outer peripheral shape of the stator is circular.