JP6568758B2 - Hermetic compressor and refrigeration cycle apparatus - Google Patents

Hermetic compressor and refrigeration cycle apparatus Download PDF

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JP6568758B2
JP6568758B2 JP2015189880A JP2015189880A JP6568758B2 JP 6568758 B2 JP6568758 B2 JP 6568758B2 JP 2015189880 A JP2015189880 A JP 2015189880A JP 2015189880 A JP2015189880 A JP 2015189880A JP 6568758 B2 JP6568758 B2 JP 6568758B2
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sealed case
case
compressor
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JP2017066890A (en
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平山　卓也
卓也 平山
功 川辺
功 川辺
勝吾 志田
勝吾 志田
昌宏 畑山
昌宏 畑山
木村　茂喜
茂喜 木村
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Toshiba Carrier Corp
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Description

本発明の実施形態は、ガス冷媒等の作動流体を圧縮する密閉型圧縮機及びその密閉型圧縮機を含む冷凍サイクル装置に関する。   Embodiments described herein relate generally to a hermetic compressor that compresses a working fluid such as a gas refrigerant and a refrigeration cycle apparatus including the hermetic compressor.

従来、電動機部と圧縮機構部とを回転軸を介して連結した圧縮機本体を２組設け、２組の圧縮機本体を密閉ケース内に収容した密閉型圧縮機が知られている（下記特許文献１参照）。この密閉型圧縮機では、密閉ケース内に収容された２組の圧縮機本体は、回転軸が一直線上に位置するとともに圧縮機本体が横並びとなるように配置されている。また、各圧縮機本体は、圧縮機構部が密閉ケースの中央側に位置して電動機部が密閉ケースの端部側に位置するように配置されている。さらに、各圧縮機本体は、圧縮機構部に大径部が設けられ、この大径部が密閉ケースに固着されている。電動機部は、回転軸に固定されて回転軸と一体に回転する回転子と、密閉ケースに固定されて回転子の外周部に位置する固定子とを有している。   2. Description of the Related Art Conventionally, a hermetic compressor in which two sets of compressor main bodies in which an electric motor unit and a compression mechanism unit are connected via a rotation shaft is provided and two sets of compressor main bodies are housed in a hermetic case is known (the following patents). Reference 1). In this hermetic compressor, the two sets of compressor main bodies accommodated in the hermetic case are arranged such that the rotating shafts are aligned and the compressor main bodies are arranged side by side. Further, each compressor body is arranged such that the compression mechanism portion is located on the center side of the sealed case and the electric motor portion is located on the end side of the sealed case. Furthermore, each compressor main body is provided with a large-diameter portion in the compression mechanism portion, and the large-diameter portion is fixed to the sealed case. The electric motor unit includes a rotor that is fixed to the rotating shaft and rotates integrally with the rotating shaft, and a stator that is fixed to the hermetic case and located on the outer peripheral portion of the rotor.

実開平２-９４３８９号公報Japanese Utility Model Publication No. 2-94389

特許文献１に記載された密閉型圧縮機においては、圧縮機本体の駆動時には、片持ち状態で支持されている回転子が振れ回りを生じる。この振れ回りは、大径部を介して密閉ケースに伝わり、密閉ケースの両端部が振れ回りを生じる。特に、大径部の密閉ケースへの固着位置から、回転子の圧縮機構部から離れた側の端部までの距離が、２つの圧縮機構部における大径部の密閉ケースへの固着位置間の距離よりも大きいと、密閉ケースの両端部の振れ回りが大きくなり、騒音や、密閉型圧縮機に搭載されている機器の破損等が発生する。   In the hermetic compressor described in Patent Document 1, the rotor supported in a cantilever state swings when the compressor body is driven. This whirling is transmitted to the sealed case through the large diameter portion, and both ends of the sealed case are swung. In particular, the distance from the position where the large-diameter portion is fixed to the sealed case to the end of the rotor away from the compression mechanism portion is between the positions where the two compression mechanism portions are fixed to the large-case sealed case. If the distance is greater than the distance, the swirl of the both ends of the sealed case increases, causing noise and damage to the equipment mounted on the hermetic compressor.

本発明の目的は、密閉ケース内に２組の圧縮機本体を横並びに収容した場合において、密閉ケースの両端部が振れ回りすることを抑制することができる密閉型圧縮機を提供することである。   An object of the present invention is to provide a hermetic compressor that can suppress swinging of both ends of a hermetic case when two sets of compressor bodies are accommodated side by side in the hermetic case. .

実施形態の密閉型圧縮機は、 電動機部と圧縮機構部とを回転軸を介して連結した２組の圧縮機本体が密閉ケース内に収容され、２組の圧縮機本体は回転軸が一直線上に位置するように横並びに配置されるとともに圧縮機構部が密閉ケースの中央側に位置するように配置され、電動機部は回転軸に固定された回転子と密閉ケースに固定された固定子とを有し、圧縮機構部は密閉ケースの内径寸法と略同一の外径寸法を有する大径部を有してこの大径部が密閉ケースに固着された密閉型圧縮機において、圧縮機本体における大径部の密閉ケースへの固着位置から回転子の圧縮機構部から離れた側の端部までの距離“Ｌ１”が、２組の圧縮機本体の固着位置間の距離“Ｌ２”より小さく設定されており、電動機部はブラシレスモータであり、２つのブラシレスモータは固定子のコイル部の仕様を変えることにより磁束量を異ならせ、効率がピークになる回転数が異なるようにされており、固定子に通電用のコイル部が設けられ、密閉ケースの底部に潤滑油が貯留され、密閉ケース内の２組の圧縮機本体の大径部の間の領域に貯留された潤滑油の量が、密閉ケース内の大径部よりケース端部側の２つの領域に貯留された潤滑油の量の合計より多いことを特徴とする。 In the hermetic compressor according to the embodiment, two sets of compressor bodies in which an electric motor unit and a compression mechanism unit are connected via a rotation shaft are accommodated in a sealed case, and the rotation shafts of the two sets of compressor main bodies are in a straight line And the compression mechanism part is arranged at the center side of the sealed case, and the electric motor part includes a rotor fixed to the rotating shaft and a stator fixed to the sealed case. The compression mechanism has a large-diameter portion having an outer diameter that is substantially the same as the inner diameter of the sealed case, and the large-diameter portion is fixed to the sealed case. The distance “L1” from the fixing position of the diameter portion to the sealed case to the end portion on the side away from the rotor compression mechanism is set to be smaller than the distance “L2” between the fixing positions of the two sets of compressor bodies. And the motor part is a brushless motor. The brushless motor changes the amount of magnetic flux by changing the specification of the coil part of the stator, so that the rotation speed at which the efficiency reaches a peak is different . Lubricating oil is stored at the bottom, and the amount of lubricating oil stored in the region between the large diameter portions of the two sets of compressor bodies in the sealed case is 2 on the case end side from the large diameter portion in the sealed case. It is characterized by being greater than the total amount of lubricating oil stored in one region.

第１の実施形態における、断面で示した密閉型圧縮機を含む冷凍サイクル装置の構成図である。It is a block diagram of the refrigerating-cycle apparatus containing the hermetic type compressor shown in the cross section in 1st Embodiment. モータの磁束量が異なる場合にモータ回転数とモータ効率との関係を示すグラフである。It is a graph which shows the relationship between motor rotation speed and motor efficiency when the amount of magnetic flux of a motor differs. 第２の実施形態における、断面で示した密閉型圧縮機を含む冷凍サイクル装置の構成図である。It is a block diagram of the refrigerating-cycle apparatus containing the hermetic type compressor shown in the cross section in 2nd Embodiment.

（第１の実施形態）
第１の実施形態について、図１及び図２に基づいて説明する。図１は冷凍サイクル装置１を示しており、この冷凍サイクル装置１は、密閉型圧縮機２と、密閉型圧縮機２に接続された放熱器３と、放熱器３に接続された膨張装置４と、膨張装置４に接続された蒸発器５と、蒸発器５に接続されたアキュムレータ６とを有し、アキュムレータ６が密閉型圧縮機２に接続されている。密閉型圧縮機２では作動流体であるガス冷媒が圧縮されて高温高圧になり、放熱器３では高温高圧のガス冷媒から放熱されて液化される。膨張装置４では冷媒が減圧され、蒸発器５では減圧された液冷媒が気化されてガス冷媒になる。アキュムレータ６では、ガス冷媒中に含まれる液冷媒が分離され、ガス冷媒のみが密閉型圧縮機２に供給されるようになっている。 (First embodiment)
1st Embodiment is described based on FIG.1 and FIG.2. FIG. 1 shows a refrigeration cycle apparatus 1, which includes a hermetic compressor 2, a radiator 3 connected to the hermetic compressor 2, and an expansion device 4 connected to the radiator 3. And an evaporator 5 connected to the expansion device 4 and an accumulator 6 connected to the evaporator 5, and the accumulator 6 is connected to the hermetic compressor 2. In the hermetic compressor 2, the gas refrigerant, which is a working fluid, is compressed to a high temperature and high pressure, and in the radiator 3, heat is radiated from the high temperature and pressure gas refrigerant and liquefied. In the expansion device 4, the refrigerant is decompressed, and in the evaporator 5, the decompressed liquid refrigerant is vaporized to become a gas refrigerant. In the accumulator 6, the liquid refrigerant contained in the gas refrigerant is separated, and only the gas refrigerant is supplied to the hermetic compressor 2.

この冷凍サイクル装置１では、冷媒がガス冷媒と液冷媒とに相変化しながら循環し、その過程で放熱と吸熱とが行われ、これらの放熱と吸熱とを利用して暖房、冷房、加熱、冷却等が行われる。   In this refrigeration cycle apparatus 1, the refrigerant circulates while changing phase between a gas refrigerant and a liquid refrigerant, and in the process, heat dissipation and heat absorption are performed, and using these heat dissipation and heat absorption, heating, cooling, heating, Cooling is performed.

密閉型圧縮機２は、略円筒状に形成されて気密状態とされる密閉ケース７を有し、この密閉ケース７は長手方向である円筒の軸方向を横向きにして配置されている。密閉ケース７内には、電動機部８と圧縮機構部９とを回転軸１０を介して連結した２組の圧縮機本体１１ａ，１１ｂが収容されている。２組の圧縮機本体１１ａ、１１ｂは、回転軸１０が一直線上に位置するように横並びに配置されるとともに、各圧縮機本体１１ａ，１１ｂの圧縮機構部９が密閉ケース７の中央側に位置し、電動機部８が密閉ケース７の端部側に位置するように配置されている。また、密閉ケース７内の底部には、潤滑油１２が貯留されている。   The hermetic compressor 2 has a hermetic case 7 that is formed in a substantially cylindrical shape and is in an airtight state. The hermetic case 7 is arranged with the axial direction of the cylinder, which is the longitudinal direction, being laterally oriented. In the sealed case 7, two sets of compressor bodies 11 a and 11 b are accommodated in which the electric motor unit 8 and the compression mechanism unit 9 are connected via the rotation shaft 10. The two sets of compressor bodies 11a and 11b are arranged side by side so that the rotary shaft 10 is positioned in a straight line, and the compression mechanism 9 of each compressor body 11a and 11b is located on the center side of the sealed case 7. However, the electric motor unit 8 is arranged so as to be located on the end side of the sealed case 7. A lubricating oil 12 is stored at the bottom of the sealed case 7.

電動機部８は、回転軸１０に固定された回転子１３と、回転子１３の外周を囲む位置に配置されて密閉ケース７の内周面に固定された固定子１４とを有するブラシレスモータとされている。回転子１３には永久磁石１５が内包され、固定子１４には通電用のコイル部１６が設けられている。   The electric motor unit 8 is a brushless motor having a rotor 13 fixed to the rotary shaft 10 and a stator 14 arranged at a position surrounding the outer periphery of the rotor 13 and fixed to the inner peripheral surface of the sealed case 7. ing. The rotor 13 includes a permanent magnet 15, and the stator 14 is provided with a coil portion 16 for energization.

圧縮機構部９は、一対のシリンダ１７と、一対のシリンダ１７の間に配置されてシリンダ１７の一端側を閉塞する仕切板１８と、各シリンダ１７の他端側を閉塞するとともに回転軸１０を回転可能に軸支する一対の軸受１９とを有し、両端を仕切板１８と軸受１９とにより閉塞された各シリンダ１７の内部にはシリンダ室２０が形成されている。シリンダ室２０には回転軸１０が挿通され、回転軸１０のシリンダ室２０内に位置する部分に偏心部２１が設けられている。偏心部２１にはローラ２２が嵌合され、ローラ２２の外周面には摺動可能なブレード２３の先端部が当接され、ブレード２３の先端部がローラ２２の外周面に当接されることによりシリンダ室２０内が吸込室と圧縮室とに区画されている。吸込室は低圧のガス冷媒が吸込まれる領域であり、圧縮室は吸込まれたガス冷媒が圧縮される領域であり、吸込室にはこの吸込室に向けてガス冷媒が流れる吸込管２４が接続されている。   The compression mechanism unit 9 is disposed between the pair of cylinders 17, the partition plate 18 that is disposed between the pair of cylinders 17 and closes one end side of the cylinders 17, closes the other end side of each cylinder 17, and rotates the rotating shaft 10. A cylinder chamber 20 is formed inside each cylinder 17 having a pair of bearings 19 that are rotatably supported and closed at both ends by a partition plate 18 and a bearing 19. The rotating shaft 10 is inserted into the cylinder chamber 20, and an eccentric portion 21 is provided at a portion of the rotating shaft 10 located in the cylinder chamber 20. A roller 22 is fitted to the eccentric portion 21, and the tip of the slidable blade 23 is brought into contact with the outer peripheral surface of the roller 22, and the tip of the blade 23 is brought into contact with the outer peripheral surface of the roller 22. Thus, the cylinder chamber 20 is divided into a suction chamber and a compression chamber. The suction chamber is a region where low-pressure gas refrigerant is sucked, the compression chamber is a region where the sucked gas refrigerant is compressed, and a suction pipe 24 through which the gas refrigerant flows toward the suction chamber is connected to the suction chamber Has been.

さらに、圧縮機構部９の各軸受１９には、圧縮室で圧縮されたガス冷媒が吐出される吐出ポート２５と、この吐出ポート２５を開閉する吐出弁２６と、吐出ポート２５から吐出されたガス冷媒が流入する吐出マフラ２７とが設けられている。なお、各軸受１９に設けられた吐出マフラ２７は図示しない連通路により連通され、電動機部８側に位置する一方の吐出マフラ２７にはマフラ出口２８が設けられ、吐出マフラ２７内のガス冷媒がマフラ出口２８を通って密閉ケース７内に流出するようになっている。密閉ケース７には、密閉ケース７内のガス冷媒が吐出される吐出管２９の一端が接続され、吐出管２９の他端は放熱器３に接続されている。   Further, each bearing 19 of the compression mechanism section 9 has a discharge port 25 through which the gas refrigerant compressed in the compression chamber is discharged, a discharge valve 26 that opens and closes the discharge port 25, and a gas discharged from the discharge port 25. A discharge muffler 27 into which the refrigerant flows is provided. A discharge muffler 27 provided in each bearing 19 is communicated by a communication passage (not shown), and one discharge muffler 27 located on the motor unit 8 side is provided with a muffler outlet 28, and the gas refrigerant in the discharge muffler 27 is exchanged. It flows out into the sealed case 7 through the muffler outlet 28. One end of a discharge pipe 29 through which the gas refrigerant in the sealed case 7 is discharged is connected to the sealed case 7, and the other end of the discharge pipe 29 is connected to the radiator 3.

ここで、圧縮機構部９には、密閉ケース７の内径寸法と略同一の外径寸法を有する大径部３０が設けられ、この大径部３０が密閉ケース７にスポット溶接により固着されている。大径部３０の密閉ケース７への固着位置３１から回転子１３の圧縮機構部９から離れた側の端部までの距離“Ｌ１”が、圧縮機本体１１ａの大径部３０の固着位置３１と圧縮機本体１１ｂの大径部３０の固着位置３１との間の距離“Ｌ２”より小さく設定されている。なお、大径部３０は、その上部側が圧力損失を生じる状態でガス冷媒が通過可能なように構成され、その下部側は潤滑油１２が通過可能なように構成されている。   Here, the compression mechanism portion 9 is provided with a large diameter portion 30 having an outer diameter dimension substantially the same as the inner diameter dimension of the sealed case 7, and the large diameter portion 30 is fixed to the sealed case 7 by spot welding. . The distance “L1” from the fixing position 31 of the large-diameter portion 30 to the sealed case 7 to the end of the rotor 13 on the side away from the compression mechanism portion 9 is the fixing position 31 of the large-diameter portion 30 of the compressor body 11a. And a distance “L2” between the fixing position 31 of the large-diameter portion 30 of the compressor body 11b. The large-diameter portion 30 is configured such that a gas refrigerant can pass through the upper side of the large-diameter portion 30 with pressure loss, and the lubricating oil 12 is configured to pass through the lower side thereof.

密閉ケース７内に貯留されている潤滑油１２の量は、２組の圧縮機本体１１ａ、１１ｂの２つの大径部３０の間の領域Ｘに貯留された潤滑油の量が、密閉ケース７内の各大径部３０よりケース端部側の２つの領域Ｙ、Ｚに貯留された潤滑油の量の合計より多くなっている。   The amount of the lubricating oil 12 stored in the sealed case 7 is equal to the amount of the lubricating oil stored in the region X between the two large diameter portions 30 of the two sets of compressor bodies 11a and 11b. It is larger than the total amount of lubricating oil stored in the two regions Y and Z on the case end side from each large-diameter portion 30 inside.

また、領域Ｘに貯留されている潤滑油の油面の面積が、領域Ｙ、Ｚに貯留されている潤滑油の油面の面積より大きくなっている。   Further, the area of the lubricating oil stored in the region X is larger than the area of the lubricating oil stored in the regions Y and Z.

各圧縮機本体１１ａ、１１ｂに設けられている２つの電動機部８は上述したようにブラシレスモータであり、２つの電動機部８は磁束量が異なるように設けられている。２つの電動機部８の磁束量は、コイルの巻き数や線径を変えることにより変えられている。   The two electric motor parts 8 provided in each compressor main body 11a, 11b are brushless motors as described above, and the two electric motor parts 8 are provided so as to have different magnetic flux amounts. The amount of magnetic flux of the two electric motor units 8 is changed by changing the number of turns of the coil and the wire diameter.

この密閉型圧縮機２には、いずれか一方の圧縮機本体１１ａ、１１ｂのみを運転するように切替える切替手段が設けられている。いずれか一方の圧縮機本体１１ａ、１１ｂのみを運転する場合には、磁束量の大きな電動機部８を有する一方の圧縮機本体１１ａが運転されるように設定されている。   The hermetic compressor 2 is provided with switching means for switching to operate only one of the compressor bodies 11a and 11b. When only one of the compressor main bodies 11a and 11b is operated, it is set so that one compressor main body 11a having the motor unit 8 having a large amount of magnetic flux is operated.

圧縮機本体１１ａ、１１ｂに設けられている圧縮機構部９のシリンダ室２０の排除容積が異なり、磁束量の大きな電動機部８を有する一方の圧縮機本体１１ａのシリンダ室２０の排除容積が、他方の圧縮機本体１１ｂのシリンダ室２０の排除容積より小さく形成されている。   The displacement volume of the cylinder chamber 20 of the compression mechanism section 9 provided in the compressor bodies 11a and 11b is different, and the displacement volume of the cylinder chamber 20 of one compressor body 11a having the motor section 8 having a large magnetic flux amount is the other. It is formed smaller than the excluded volume of the cylinder chamber 20 of the compressor main body 11b.

また、２つの圧縮機本体１１ａ、１１ｂに設けられている圧縮機構部９の吐出弁２６のばね定数が異なり、磁束量が大きな電動機部８を有する一方の圧縮機本体１１ａの吐出弁２６のばね定数が、他方の圧縮機本体１１ｂの吐出弁２６のばね乗数より小さく設定されている。   Further, the spring constant of the discharge valve 26 of the compression mechanism section 9 provided in the two compressor bodies 11a and 11b is different, and the spring of the discharge valve 26 of the one compressor body 11a having the motor section 8 having a large amount of magnetic flux. The constant is set smaller than the spring multiplier of the discharge valve 26 of the other compressor body 11b.

このような構成において、２つの圧縮機本体１１ａ、１１ｂの各電動機部８に通電されることにより各回転軸１０が中心線回りに回転し、各回転軸１０の回転により各圧縮機構部９が駆動され、各圧縮機構部９においてガス冷媒が圧縮される。一方の圧縮機本体１１ａと他方の圧縮機本体１１ｂとの動作とは同じであるので、以下の説明では一方の圧縮機本体１１ａの動作についてのみ説明する。   In such a configuration, when the electric motor parts 8 of the two compressor bodies 11a and 11b are energized, the rotary shafts 10 rotate around the center line, and the rotation of the rotary shafts 10 causes the compression mechanism parts 9 to rotate. The gas refrigerant is compressed in each compression mechanism 9 by being driven. Since the operation of one compressor body 11a and the other compressor body 11b is the same, only the operation of one compressor body 11a will be described in the following description.

圧縮されたガス冷媒の圧力が設定圧に達すると、吐出弁２６が開弁され、圧縮されたガス冷媒が吐出ポート２５から吐出されて吐出マフラ２７内に流入する。密閉ケース７の中央寄りに位置する一方の吐出マフラ２７内に流入したガス冷媒は連通路を通って他方の吐出マフラ２７内に流入し、他方の吐出マフラ２７に設けられているマフラ出口２８を通って密閉ケース７内における大径部３０よりケース端部側の領域Ｙに流出する。そして、領域Ｙに流出したガス冷媒は、大径部３０を通過して密閉ケース７内の２つの大径部３０の間の領域Ｘに流入し、領域Ｘに流入したガス冷媒は、吐出管２９を通って放熱器３側に吐出され、放熱器３内に流入する。放熱器３内に流入した冷媒ガスは、膨張装置４、蒸発器５を順に経由して再び密閉型圧縮機２へと循環することにより、冷凍サイクルが実行される。   When the pressure of the compressed gas refrigerant reaches the set pressure, the discharge valve 26 is opened, and the compressed gas refrigerant is discharged from the discharge port 25 and flows into the discharge muffler 27. The gas refrigerant that has flowed into one discharge muffler 27 located near the center of the sealed case 7 flows into the other discharge muffler 27 through the communication path, and passes through a muffler outlet 28 provided on the other discharge muffler 27. It flows out from the large diameter portion 30 in the sealed case 7 to the region Y on the case end side. The gas refrigerant that has flowed out into the region Y passes through the large-diameter portion 30 and flows into the region X between the two large-diameter portions 30 in the sealed case 7, and the gas refrigerant that has flowed into the region X is discharged from the discharge pipe. 29 is discharged to the radiator 3 side and flows into the radiator 3. The refrigerant gas that has flowed into the radiator 3 circulates again to the hermetic compressor 2 through the expansion device 4 and the evaporator 5 in order, thereby executing a refrigeration cycle.

ここで、各圧縮機本体１１ａ、１１ｂにおける大径部３０の固着位置３１から回転子１３の圧縮機構部９から離れた側の端部までの距離“Ｌ１”が、２つの大径部３０の固着位置３１間の距離“Ｌ２”より小さく設定されている。そして、大径部３０の固着位置３１から回転子１３の圧縮機構部９から離れた側の端部までの距離“Ｌ１”が小さいことにより、各回転子１３に生じる振れ回りが固着位置３１を通じて密閉ケース７に伝わった場合に、密閉ケース７のケース端部側を振れ回りさせる力が小さくなる。さらに、２つの固着位置３１間の距離“Ｌ２”が大きくなるので、固着位置３１間の重量が増大し、密閉ケース７の振れ回りによる振動量を低減させることができる。従って、圧縮機構部９の駆動時における密閉ケース７の両端部の振れ回りを抑制することができる。さらに、吐出管２９が２つの大径部３０間に設けられているので、密閉ケース７の両端部の振れ回りによる吐出管２９の振動を抑制することができ、吐出管２９の配管設計を容易にすることができる。   Here, the distance “L1” from the fixing position 31 of the large-diameter portion 30 in each compressor main body 11a, 11b to the end portion on the side away from the compression mechanism portion 9 of the rotor 13 is the distance between the two large-diameter portions 30. The distance between the fixing positions 31 is set to be smaller than “L2”. Further, since the distance “L1” from the fixing position 31 of the large-diameter portion 30 to the end portion of the rotor 13 on the side away from the compression mechanism portion 9 is small, the whirling generated in each rotor 13 passes through the fixing position 31. When transmitted to the sealed case 7, the force for swinging the case end side of the sealed case 7 is reduced. Furthermore, since the distance “L2” between the two fixing positions 31 is increased, the weight between the fixing positions 31 is increased, and the amount of vibration due to the swinging of the sealed case 7 can be reduced. Therefore, it is possible to suppress the swinging of both ends of the sealed case 7 when the compression mechanism unit 9 is driven. Furthermore, since the discharge pipe 29 is provided between the two large diameter portions 30, vibration of the discharge pipe 29 due to the swinging of both ends of the sealed case 7 can be suppressed, and the piping design of the discharge pipe 29 is easy. Can be.

密閉ケース７内に貯留されている潤滑油１２の量は、領域Ｘに貯留された潤滑油１２の量が、２つの領域Ｙ、Ｚに貯留された潤滑油１２の量の合計より多くなっている。   The amount of the lubricating oil 12 stored in the sealed case 7 is such that the amount of the lubricating oil 12 stored in the region X is larger than the total amount of the lubricating oil 12 stored in the two regions Y and Z. Yes.

ここで、電動機部８はコイル部１６からの発熱により高温になり易く、この電動機部８が位置している領域である密閉ケース７内の大径部３０よりケース端部側の領域に貯留されている潤滑油１２は、電動機部８により加熱されて粘度の低下や油性の劣化が生じ易い。一方、２つの大径部３０の間の領域に貯留されている潤滑油１２は、大径部３０により電動機部８と隔絶されていることや、圧縮機構部９に吸込まれる低圧低温のガス冷媒により冷やされること等により、加熱されにくくなっている。このため、加熱されにくい２つの大径部３０の間の領域に貯留された潤滑油１２の量を、加熱され易い密閉ケース７内の大径部３０よりケース端部側の２つの領域に貯留された潤滑油１２の量の合計より多くすることにより、密閉ケース７内の潤滑油１２が全体として温度上昇することを抑制することができ、潤滑油１２の潤滑性能を維持することかできる。   Here, the electric motor unit 8 is likely to become high temperature due to heat generated from the coil unit 16, and is stored in a region closer to the case end than the large-diameter portion 30 in the sealed case 7 where the electric motor unit 8 is located. The lubricating oil 12 being heated is easily heated by the electric motor unit 8 to cause a decrease in viscosity or deterioration in oiliness. On the other hand, the lubricating oil 12 stored in the region between the two large-diameter portions 30 is isolated from the electric motor portion 8 by the large-diameter portion 30 and the low-pressure low-temperature gas sucked into the compression mechanism portion 9. It is difficult to be heated by being cooled by a refrigerant. For this reason, the amount of the lubricating oil 12 stored in the region between the two large-diameter portions 30 that are difficult to be heated is stored in the two regions closer to the case end than the large-diameter portion 30 in the sealed case 7 that is easily heated. By increasing the total amount of the lubricating oil 12, the temperature of the lubricating oil 12 in the sealed case 7 can be prevented from rising as a whole, and the lubricating performance of the lubricating oil 12 can be maintained.

また、密閉ケース７内の２つの大径部３０の間の領域Ｘに貯留されている潤滑油１２の油面の面積が、密閉ケース７内の大径部３０よりケース端部側の領域Ｙ、Ｚに貯留されている潤滑油の油面の面積より大きく設定されている。ここで、密閉ケース７内の潤滑油１２の油面の高さは、圧縮機本体１１ａ、１１ｂの運転停止時には一定となっている。一方、圧縮機本体１１ａ、１１ｂの運転時には、圧縮機構部９で圧縮されたガス冷媒が、領域Ｙ、Ｚに流入し、その後、大径部３０を通過して領域Ｘに流入する。そして、ガス冷媒が大径部３０を通過する際に圧力損失が生じ、運転中における領域Ｙ、Ｚのガス冷媒の圧力は、運転中における領域Ｘのガス冷媒の圧力より高くなる。このガス冷媒の圧力差により、領域Ｙ、Ｚでは潤滑油１２の油面が低くなり、領域Ｘでは潤滑油１２の油面が高くなる。   Further, the area of the oil surface of the lubricating oil 12 stored in the region X between the two large diameter portions 30 in the sealed case 7 is the region Y on the case end side of the large diameter portion 30 in the sealed case 7. , Z is set larger than the area of the oil surface of the lubricating oil stored in Z. Here, the height of the oil surface of the lubricating oil 12 in the sealed case 7 is constant when the compressor main bodies 11a and 11b are stopped. On the other hand, during the operation of the compressor main bodies 11a and 11b, the gas refrigerant compressed by the compression mechanism unit 9 flows into the regions Y and Z, and then passes through the large diameter portion 30 and flows into the region X. And when a gas refrigerant passes the large diameter part 30, a pressure loss arises and the pressure of the gas refrigerant of the area | regions Y and Z during driving | operation becomes higher than the pressure of the gas refrigerant of the area | region X in driving | operation. Due to the pressure difference of the gas refrigerant, the oil level of the lubricating oil 12 becomes lower in the regions Y and Z, and the oil level of the lubricating oil 12 becomes higher in the region X.

そして、このような運転時と運転停止時とにおける潤滑油１２の油面高さの変動は、潤滑油１２の油面の面積が大きいほど小さくなり、油面の面積が小さいほど大きくなる。従って、２つの大径部３０の間の領域Ｘでは、潤滑油１２の油面の面積を大きくすることにより運転時における潤滑油１２の油面の上昇を抑制することができ、潤滑油１２の油面が上昇したために潤滑油１２が吐出管２９から密閉ケース７外に排出され易くなるという事態の発生を抑制することができる。一方、大径部３０よりケース端部側の領域Ｙ、Ｚでは、潤滑油１２の油面の面積を小さくすることにより運転時における潤滑油１２の油面の下降を促進することができ、回転する回転子１３が潤滑油１２に浸漬して回転負荷が増大するという事態の発生を抑制することができる。   And the fluctuation | variation of the oil surface height of the lubricating oil 12 at the time of such an operation | movement and a driving | operation stop becomes so small that the area of the oil surface of the lubricating oil 12 is large, and becomes so large that the area of an oil surface is small. Therefore, in the region X between the two large-diameter portions 30, an increase in the oil level of the lubricating oil 12 can be suppressed by increasing the area of the lubricating oil 12 so that the lubricating oil 12 Occurrence of a situation in which the lubricating oil 12 is easily discharged from the discharge pipe 29 to the outside of the sealed case 7 because the oil level has risen can be suppressed. On the other hand, in the regions Y and Z closer to the case end than the large-diameter portion 30, the lowering of the oil level of the lubricating oil 12 can be promoted by reducing the area of the lubricating oil 12. The occurrence of a situation in which the rotating rotor 13 is immersed in the lubricating oil 12 and the rotational load increases can be suppressed.

つぎに、２つの圧縮機本体１１ａ、１１ｂに設けられているブラシレスモータである電動機部８は、一方の圧縮機本体１１ａの電動機部８の磁束量が、他方の圧縮機本体１１ｂの電動機部８の磁束量より大きく設定されている。電動機部８の磁束量が異なる場合、それらの電動機部８の回転数とモータ効率との関係は図２に示すようになり、モータ効率がピークになる場合の回転数が異なる。従って、２つの電動機部８を効率がピークとなるように駆動させた場合において、２つの電動機部８は回転数が異なるため、共振による振動や騒音の増大を抑制することができる。   Next, in the electric motor unit 8 which is a brushless motor provided in the two compressor main bodies 11a and 11b, the magnetic flux amount of the electric motor unit 8 of one compressor main body 11a is the same as the electric motor unit 8 of the other compressor main body 11b. Is set larger than the amount of magnetic flux. When the amount of magnetic flux of the motor unit 8 is different, the relationship between the number of rotations of the motor unit 8 and the motor efficiency is as shown in FIG. 2, and the number of rotations when the motor efficiency reaches a peak is different. Therefore, when the two electric motor parts 8 are driven so that the efficiency reaches a peak, the two electric motor parts 8 have different rotation speeds, so that an increase in vibration and noise due to resonance can be suppressed.

ここで、２つの電動機部８の磁束量は、コイルの巻き数や線径を変える等のコイル部１６の仕様を変えることにより変えられている。このため、磁束量が異なる電動機部８であっても固定子１４の本体部や固定子１４の各種部品を共用することができ、電動機部８のコスト低減や製造性の向上を図ることができる。   Here, the amount of magnetic flux of the two motor units 8 is changed by changing the specifications of the coil unit 16 such as changing the number of turns of the coil and the wire diameter. For this reason, even if it is the electric motor part 8 from which the amount of magnetic flux differs, the various parts of the main-body part of the stator 14 and the stator 14 can be shared, and the cost reduction of the electric motor part 8 and improvement of manufacturability can be aimed at. .

また、この密閉型圧縮機２は、いずれか一方の圧縮機本体１１ａ、１１ｂのみを運転するように切替える切替手段を備えており、この切替時には、磁束量の大きな電動機部８を有する一方の圧縮機本体１１ａが運転されるように設定されている。このため、低回転数域でのモータ効率を高めることができ、より低能力域での効率が向上し、部分負荷特性の良い密閉型圧縮機２を得ることができる。   The hermetic compressor 2 is provided with a switching means for switching so that only one of the compressor bodies 11a and 11b is operated. At the time of this switching, one of the compressors having the motor unit 8 having a large amount of magnetic flux. The machine main body 11a is set to operate. For this reason, the motor efficiency in the low rotation speed region can be increased, the efficiency in the lower capacity region can be improved, and the hermetic compressor 2 with good partial load characteristics can be obtained.

また、２つの圧縮機本体１１ａ、１１ｂに設けられている圧縮機構部９のシリンダ室２０の排除容積が異なり、磁束量の大きな電動機部８を有する一方の圧縮機本体１１ａのシリンダ室２０の排除容積が、他方の圧縮機本体１１ｂのシリンダ室２０の排除容積より小さく形成されている。このため、低能力域での効率がさらに向上し、より一層部分負荷特性の良い密閉型圧縮機２を得ることができる。   Further, the displacement volume of the cylinder chamber 20 of the compression mechanism section 9 provided in the two compressor bodies 11a and 11b is different, and the displacement of the cylinder chamber 20 of the one compressor body 11a having the electric motor section 8 having a large magnetic flux amount. The volume is smaller than the excluded volume of the cylinder chamber 20 of the other compressor body 11b. For this reason, the efficiency in a low capacity range further improves, and the hermetic compressor 2 with better partial load characteristics can be obtained.

また、２つの圧縮機本体１１ａ、１１ｂに設けられている圧縮機構部９の吐出弁２６のばね定数が異なり、磁束量が大きな電動機部８を有する一方の圧縮機本体１１ａの吐出弁２６のばね定数が、他方の圧縮機本体１１ｂの吐出弁２６のばね乗数より小さく設定されている。このため、一方の圧縮機本体１１ａでは過圧縮損失を低減することができ、特に、低回転数域のモータ効率をより高めることができる。一方、高回転数域でモータ効率が良い磁束量の小さな圧縮機構部９を用いる圧縮機本体１１ｂでは、吐出弁２６のバネ定数を大きくすることにより吐出弁２６の応答性を向上させることができ、高回転時のモータ効率を高めることができるとともに、高回転時における吐出弁２６の信頼性を向上させることができる。   Further, the spring constant of the discharge valve 26 of the compression mechanism section 9 provided in the two compressor bodies 11a and 11b is different, and the spring of the discharge valve 26 of the one compressor body 11a having the motor section 8 having a large amount of magnetic flux. The constant is set smaller than the spring multiplier of the discharge valve 26 of the other compressor body 11b. For this reason, in one compressor main body 11a, an overcompression loss can be reduced, and in particular, motor efficiency in a low rotation speed region can be further increased. On the other hand, in the compressor main body 11b using the compression mechanism unit 9 having a small magnetic flux and high motor efficiency in a high rotational speed range, the response of the discharge valve 26 can be improved by increasing the spring constant of the discharge valve 26. The motor efficiency at the time of high rotation can be increased, and the reliability of the discharge valve 26 at the time of high rotation can be improved.

（第２の実施形態）
第２の実施形態について、図３に基づいて説明する。なお、第１の実施形態で説明した構成要素と同じ構成要素には同じ符号を付け、重複する説明は省略する。 (Second Embodiment)
A second embodiment will be described with reference to FIG. In addition, the same code | symbol is attached | subjected to the same component as the component demonstrated in 1st Embodiment, and the overlapping description is abbreviate | omitted.

図３は冷凍サイクル装置１Ａを示しており、この冷凍サイクル装置１Ａは、密閉型圧縮機２Ａと、密閉型圧縮機２Ａに接続された放熱器３と、放熱器３に接続された膨張装置４と、膨張装置４に接続された蒸発器５と、蒸発器５に接続されたアキュムレータ６とを有し、アキュムレータ６が密閉型圧縮機２Ａに接続されている。第２の実施形態の密閉型圧縮機２Ａは、略円筒状に形成されて横向きに配置される密閉ケース７を有し、この密閉ケース７内に、２組の圧縮機本体１１ａ、１１ｂが収容され、圧縮機本体１１ａ、１１ｂは、電動機部８と圧縮機構部９と回転軸１０とを有している。また、２組の圧縮機本体１１ａ、１１ｂは、回転軸１０が一直線上に位置するように横並びに配置されるとともに、圧縮機構部９が密閉ケース７の中央側に位置して電動機部８が密閉ケース７の端部側に位置するように配置されている。   FIG. 3 shows a refrigeration cycle apparatus 1A. The refrigeration cycle apparatus 1A includes a hermetic compressor 2A, a radiator 3 connected to the hermetic compressor 2A, and an expansion device 4 connected to the radiator 3. And an evaporator 5 connected to the expansion device 4 and an accumulator 6 connected to the evaporator 5, and the accumulator 6 is connected to the hermetic compressor 2A. The hermetic compressor 2A of the second embodiment has a hermetic case 7 that is formed in a substantially cylindrical shape and is disposed sideways, and two sets of compressor bodies 11a and 11b are accommodated in the hermetic case 7. The compressor main bodies 11 a and 11 b have an electric motor unit 8, a compression mechanism unit 9, and a rotating shaft 10. The two sets of compressor bodies 11a and 11b are arranged side by side so that the rotary shaft 10 is positioned in a straight line, and the compression mechanism section 9 is positioned on the center side of the sealed case 7 so that the motor section 8 It arrange | positions so that it may be located in the edge part side of the airtight case 7. FIG.

このように、第２の実施形態の密閉型圧縮機２Ａと第１の実施形態の密閉型圧縮機２との基本的な構成は同じであり、異なる点は、第１の実施形態の密閉型圧縮機２では密閉ケース７内に圧縮機構部９で圧縮された後の高圧のガス冷媒が流入するのに対し、第２の実施形態の密閉型圧縮機２Ａでは密閉ケース７内に圧縮機構部９で圧縮される前の低圧のガス冷媒が流入する点である。   Thus, the basic configuration of the hermetic compressor 2A of the second embodiment and the hermetic compressor 2 of the first embodiment is the same, and the difference is that the hermetic type of the first embodiment. In the compressor 2, the high-pressure gas refrigerant after being compressed by the compression mechanism unit 9 flows into the sealed case 7, whereas in the sealed compressor 2 </ b> A of the second embodiment, the compression mechanism unit is placed in the sealed case 7. 9 is that the low-pressure gas refrigerant before being compressed flows in.

密閉ケース７の外周部には、低圧のガス冷媒を密閉ケース７内に流入させる流入管３２と、密閉ケース７内に流入した低圧のガス冷媒を圧縮機構部９の吸込室に吸込むための吸込管３３と、吸込室に吸込まれた後に圧縮室で圧縮されて高圧になったガス冷媒を吐出する吐出管３４とが設けられている。吐出管３４から吐出された高圧のガス冷媒が放熱器３内に流入し、放熱器３内に流入した冷媒ガスが、膨張装置４、蒸発器５、アキュムレータ６を順に経由して再び密閉型圧縮機２の密閉ケース７内へと循環することにより、冷凍サイクルが実行される。   The outer periphery of the sealed case 7 has an inflow pipe 32 through which low-pressure gas refrigerant flows into the sealed case 7, and a suction for sucking the low-pressure gas refrigerant flowing into the sealed case 7 into the suction chamber of the compression mechanism unit 9. A pipe 33 and a discharge pipe 34 for discharging a gas refrigerant that has been sucked into the suction chamber and then compressed in the compression chamber to a high pressure are provided. The high-pressure gas refrigerant discharged from the discharge pipe 34 flows into the radiator 3, and the refrigerant gas flowing into the radiator 3 passes through the expansion device 4, the evaporator 5, and the accumulator 6 in order, and is again sealed. A refrigeration cycle is performed by circulating into the sealed case 7 of the machine 2.

ここで、圧縮機構部９には、密閉ケース７の内径寸法と略同一の外径寸法を有する大径部３５が設けられており、この大径部３５が密閉ケース７にスポット溶接により固着されている。大径部３５の密閉ケース７への固着位置３６から回転子１３の圧縮機構部９から離れた側の端部までの距離“Ｌ１”が、圧縮機本体１１ａ、１１ｂの２つの大径部３５の固着位置３６間の距離“Ｌ２”より小さく設定されている。そして、密閉ケース７内の２つの大径部３５の間の領域Ｘ空間容積が、密閉ケース７内の大径部３５よりケース端部側の２つの領域Ｙ、Ｚの合計の空間容積より大きく設定されている。また、流入管３２、吸込管３３、吐出管３４は、密閉ケース７内の２つの大径部３５の間の領域Ｘに連通されている。   Here, the compression mechanism portion 9 is provided with a large diameter portion 35 having an outer diameter dimension substantially the same as the inner diameter dimension of the sealed case 7, and the large diameter portion 35 is fixed to the sealed case 7 by spot welding. ing. The distance “L1” from the fixing position 36 of the large-diameter portion 35 to the sealed case 7 to the end of the rotor 13 on the side away from the compression mechanism portion 9 is the two large-diameter portions 35 of the compressor bodies 11a and 11b. Is set to be smaller than the distance “L2” between the fixing positions 36. The region X space volume between the two large diameter portions 35 in the sealed case 7 is larger than the total space volume of the two regions Y and Z on the case end side from the large diameter portion 35 in the sealed case 7. Is set. Further, the inflow pipe 32, the suction pipe 33, and the discharge pipe 34 are communicated with a region X between the two large diameter portions 35 in the sealed case 7.

このような構成において、２つの圧縮機本体１１ａ、１１ｂの各電動機部８に通電されることにより各回転軸１０が中心線回りに回転し、各回転軸１０の回転により各圧縮機構部９が駆動され、密閉ケース７内の低圧のガス冷媒が吸込管３３を経由して各圧縮機構部９の吸込室に吸込まれ、圧縮室で圧縮される。圧縮されたガス冷媒は、吐出ポート２５、吐出マフラ２７を経由して吐出管３４から吐出されて放熱器３内に流入し、放熱器３内に流入した冷媒ガスが、膨張装置４、蒸発器５、アキュムレータ６を順に経由して流入管３２から密閉ケース７内へと循環し、冷凍サイクルが実行される。なお、流入管３２から密閉ケース７内に流入するガス冷媒は、密閉ケース７内における２つの大径部３５の間の領域に流入する。   In such a configuration, when the electric motor parts 8 of the two compressor bodies 11a and 11b are energized, the rotary shafts 10 rotate around the center line, and the rotation of the rotary shafts 10 causes the compression mechanism parts 9 to rotate. Driven, the low-pressure gas refrigerant in the sealed case 7 is sucked into the suction chambers of the compression mechanism portions 9 via the suction pipes 33 and compressed in the compression chambers. The compressed gas refrigerant is discharged from the discharge pipe 34 via the discharge port 25 and the discharge muffler 27 and flows into the radiator 3, and the refrigerant gas flowing into the radiator 3 becomes the expansion device 4 and the evaporator. 5. The refrigerant is circulated from the inflow pipe 32 into the sealed case 7 through the accumulator 6 in order, and the refrigeration cycle is executed. Note that the gas refrigerant flowing into the sealed case 7 from the inflow pipe 32 flows into a region between the two large diameter portions 35 in the sealed case 7.

この密閉型圧縮機２Ａは、第１の実施形態の密閉型圧縮機２と同様に、各圧縮機本体１１ａ、１１ｂにおける大径部３５の固着位置３６から回転子１３の圧縮機構部９から離れた側の端部までの距離“Ｌ１”が、２つの大径部３５の固着位置３６間の距離“Ｌ２”より小さく設定されている。これにより、大径部３５の固着位置３６から回転子１３の圧縮機構部９から離れた側の端部までの距離“Ｌ１”が小さくなるとともに、２つの固着位置３６間の距離“Ｌ２”が大きくなる。従って、第１の実施形態と同様に、圧縮機構部９の駆動時における密閉ケース７の両端部の振れ回りを抑制することができる。また、密閉ケース７の両端部の振れ回りによる吐出管３４の振動を抑制することができ、吐出管３４の配管設計を容易にすることができる。   The hermetic compressor 2A is separated from the compression mechanism portion 9 of the rotor 13 from the fixing position 36 of the large-diameter portion 35 in each compressor main body 11a, 11b, similarly to the hermetic compressor 2 of the first embodiment. The distance “L1” to the end on the other side is set smaller than the distance “L2” between the fixing positions 36 of the two large diameter portions 35. As a result, the distance “L1” from the fixing position 36 of the large-diameter portion 35 to the end of the rotor 13 on the side away from the compression mechanism 9 is reduced, and the distance “L2” between the two fixing positions 36 is reduced. growing. Therefore, as in the first embodiment, it is possible to suppress the swinging of both ends of the sealed case 7 when the compression mechanism unit 9 is driven. Further, the vibration of the discharge pipe 34 due to the swinging of both ends of the sealed case 7 can be suppressed, and the piping design of the discharge pipe 34 can be facilitated.

さらに、密閉ケース７内の２つの大径部３５の間の領域Ｘの空間容積が大きく形成されており、吸込管３３は、密閉ケース７内の２つの大径部３５の間の領域Ｘに連通させて設けられている。このため、密閉ケース７内のガス冷媒が吸込管３３を経由して吸込室に吸込まれる際の脈動を低減させることができ、騒音や振動の少ない密閉型圧縮機２を得ることができる。   Further, the space volume of the region X between the two large diameter portions 35 in the sealed case 7 is formed large, and the suction pipe 33 is located in the region X between the two large diameter portions 35 in the sealed case 7. It is provided in communication. For this reason, the pulsation when the gas refrigerant in the sealed case 7 is sucked into the suction chamber via the suction pipe 33 can be reduced, and the hermetic compressor 2 with less noise and vibration can be obtained.

以上、本発明のいくつかの実施形態を説明したが、これらの実施形態は、例として提示したものであり、発明の範囲を限定することは意図していない。これらの実施形態は、その他の様々な形態で実施されることが可能であり、発明の要旨を逸脱しない範囲で、種々の省略、置き換え、変更を行うことができる。これら実施形態やその変形は、発明の範囲や要旨に含まれると同様に、特許請求の範囲に記載された発明とその均等の範囲に含まれるものである。   As mentioned above, although some embodiment of this invention was described, these embodiment is shown as an example and is not intending limiting the range of invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. These embodiments and their modifications are included in the scope and gist of the invention, and are also included in the invention described in the claims and the equivalents thereof.

１…冷凍サイクル装置、１Ａ…冷凍サイクル装置、２…密閉型圧縮機、２Ａ…密閉型圧縮機、３…放熱器、４…膨張装置、５…蒸発器、７…密閉ケース、８…電動機部、９…圧縮機構部、１０…回転軸、１１ａ、１１ｂ…圧縮機本体、１３…回転子、１４…固定子、３０…大径部、３１…固着位置、３３…吸込管、３５…大径部、３６…固着位置   DESCRIPTION OF SYMBOLS 1 ... Refrigeration cycle apparatus, 1A ... Refrigeration cycle apparatus, 2 ... Sealed compressor, 2A ... Sealed compressor, 3 ... Radiator, 4 ... Expansion device, 5 ... Evaporator, 7 ... Sealed case, 8 ... Electric motor part DESCRIPTION OF SYMBOLS 9 ... Compression mechanism part, 10 ... Rotary shaft, 11a, 11b ... Compressor main body, 13 ... Rotor, 14 ... Stator, 30 ... Large diameter part, 31 ... Adhering position, 33 ... Suction pipe, 35 ... Large diameter Part, 36 ... fixing position

Claims (4)

電動機部と圧縮機構部とを回転軸を介して連結した２組の圧縮機本体が密閉ケース内に収容され、２組の前記圧縮機本体は前記回転軸が一直線上に位置するように横並びに配置されるとともに前記圧縮機構部が前記密閉ケースの中央側に位置するように配置され、前記電動機部は前記回転軸に固定された回転子と前記密閉ケースに固定された固定子とを有し、前記圧縮機構部は前記密閉ケースの内径寸法と略同一の外径寸法を有する大径部を有してこの大径部が前記密閉ケースに固着された密閉型圧縮機において、
前記圧縮機本体における前記大径部の前記密閉ケースへの固着位置から前記回転子の前記圧縮機構部から離れた側の端部までの距離“Ｌ１”が、２組の前記圧縮機本体の前記固着位置間の距離“Ｌ２”より小さく設定されており、
前記電動機部はブラシレスモータであり、２つの前記ブラシレスモータは前記固定子のコイル部の仕様を変えることにより磁束量を異ならせ、効率がピークになる回転数が異なるようにされており、
前記固定子に通電用のコイル部が設けられ、前記密閉ケースの底部に潤滑油が貯留され、前記密閉ケース内の２組の前記圧縮機本体の前記大径部の間の領域に貯留された潤滑油の量が、前記密閉ケース内の前記大径部よりケース端部側の２つの領域に貯留された潤滑油の量の合計より多いことを特徴とする密閉型圧縮機。 Two sets of compressor main bodies in which the electric motor unit and the compression mechanism unit are connected via a rotating shaft are accommodated in a sealed case, and the two sets of compressor main bodies are arranged side by side so that the rotating shafts are positioned in a straight line. And the compression mechanism portion is disposed so as to be positioned on the center side of the hermetic case, and the electric motor portion includes a rotor fixed to the rotating shaft and a stator fixed to the hermetic case. In the hermetic compressor, the compression mechanism portion has a large diameter portion having an outer diameter dimension substantially the same as the inner diameter dimension of the sealed case, and the large diameter portion is fixed to the sealed case.
The distance “L1” from the position where the large-diameter portion of the compressor main body is fixed to the sealed case to the end of the rotor on the side away from the compression mechanism portion is the two sets of the compressor main bodies. It is set smaller than the distance “L2” between the fixing positions,
The electric motor part is a brushless motor, and the two brushless motors have different magnetic flux amounts by changing the specifications of the coil part of the stator, so that the rotational speed at which the efficiency reaches a peak is different .
The energizing coil portion is provided in the stator, the lubricating oil is stored in the bottom portion of the hermetic case, and is stored in the region between the large diameter portions of the two sets of the compressor main bodies in the hermetic case. The hermetic compressor characterized in that the amount of lubricating oil is larger than the total amount of lubricating oil stored in two regions closer to the case end than the large diameter portion in the sealed case . 前記圧縮機構部で圧縮された作動流体が前記密閉ケース内の前記大径部よりケース端部側の領域に吐出された後に前記大径部を通過して前記密閉ケース内の２組の前記圧縮機本体の前記大径部の間の領域に流入し、前記密閉ケース内の２つの前記大径部の間の領域内の作動流体が吐出管から吐出されるように設けられ、
前記密閉ケース内の２つの前記大径部の間の領域に貯留されている潤滑油の油面の面積が、前記密閉ケース内の前記大径部よりケース端部側の領域に貯留されている潤滑油の油面の面積より大きいことを特徴とする請求項１記載の密閉型圧縮機。 After the working fluid compressed by the compression mechanism portion is discharged to a region on the case end side from the large diameter portion in the sealed case, the two sets of compression in the sealed case pass through the large diameter portion. It flows into the region between the large diameter portions of the machine body, and is provided so that the working fluid in the region between the two large diameter portions in the sealed case is discharged from the discharge pipe,
The area of the oil surface of the lubricating oil stored in the region between the two large-diameter portions in the sealed case is stored in the region closer to the case end than the large-diameter portion in the sealed case. 2. The hermetic compressor according to claim 1, wherein the hermetic compressor has a larger area than the surface of the lubricating oil. 前記密閉ケース内の２つの前記大径部の間の領域に圧縮前の作動流体が流入し、この作動流体を前記圧縮機構部に導く吸込管が前記密閉ケース内の２つの前記大径部の間の領域に連通して設けられ、前記密閉ケース内の２つの前記大径部の間の領域の空間容積が、前記密閉ケース内の前記大径部よりケース端部側の２つの領域の合計の空間容積より大きいことを特徴とする請求項１記載の密閉型圧縮機。 The working fluid before compression flows into a region between the two large-diameter portions in the sealed case, and a suction pipe that guides the working fluid to the compression mechanism portion is provided between the two large-diameter portions in the sealed case. The space volume of the region between the two large diameter portions in the sealed case is a total of the two regions on the case end side from the large diameter portion in the sealed case. The hermetic compressor according to claim 1 , wherein the hermetic compressor is larger than the space volume. 請求項１ないし３のいずか一項に記載の密閉型圧縮機と、前記密閉型圧縮機に接続される放熱器と、前記放熱器に接続される膨張装置と、前記膨張装置と前記密閉型圧縮機との間に接続される蒸発器とを備えることを特徴とする冷凍サイクル装置。
Wherein the hermetic compressor according to an item Izuka of claims 1 to 3, a radiator connected to the hermetic compressor, an expansion device connected to the radiator, and the expansion device sealed A refrigerating cycle device comprising: an evaporator connected to the compressor.
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