JP2005163775A - Hermetic compressor - Google Patents

Hermetic compressor Download PDF

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JP2005163775A
JP2005163775A JP2004081056A JP2004081056A JP2005163775A JP 2005163775 A JP2005163775 A JP 2005163775A JP 2004081056 A JP2004081056 A JP 2004081056A JP 2004081056 A JP2004081056 A JP 2004081056A JP 2005163775 A JP2005163775 A JP 2005163775A
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oil
oil supply
supply passage
rotary shaft
eccentric
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JP3910600B2 (en
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Kyu Shik Shin
規 植 申
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Samsung Electronics Co Ltd
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Samsung Gwangju Electronics Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
    • F16N7/36—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with feed by pumping action of the member to be lubricated or of a shaft of the machine; Centrifugal lubrication
    • F16N7/366—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with feed by pumping action of the member to be lubricated or of a shaft of the machine; Centrifugal lubrication with feed by pumping action of a vertical shaft of the machine

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hermetic compressor capable of causing sufficient rising force of oil even if a rotary shaft rotates at a low speed to supply oil to each driving part of the rotary shaft smoothly. <P>SOLUTION: An oil supply and guide means provided on the rotary shaft 40 to supply oil in a bottom part of a sealed case to each driving part has a first oil pick-up member 51 provided in a lower part of the rotary shaft 40 to raise oil collected in the sealed case, a first oil supply passage 52 formed in the rotary shaft 40 in an upper part of the first oil pick-up member 51 and being eccentric for the center of the rotary shaft 40, a spiral oil supply channel 54 formed on an outer face of the rotary shaft 40 in an upper part of the first oil supply passage 52 and connected with the first oil supply passage 52, a second oil supply passage 56 formed in an eccentric part 41 of the rotary shaft 40 so as to be connected with the spiral oil supply channel 54, and a second oil pick-up member 53 provided in the first oil supply passage 52 to increase rising force of oil. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は密閉型圧縮機に係り、より詳しくは回転軸の回転を用いて各駆動部分に効果的に給油し得るように給油構造を改善した密閉型圧縮機に関するものである。   The present invention relates to a hermetic compressor, and more particularly to a hermetic compressor having an improved oiling structure so that oil can be effectively supplied to each drive portion by using rotation of a rotating shaft.

一般の密閉型圧縮機に関する技術として、回転軸の回転を用いて圧縮機の各駆動部分に給油する技術が開示されている（例えば、特開２０００−２０５１３０号公報参照）。この圧縮機は、回転軸が回転するとき、密閉ケースの底部に溜まっているオイルを上昇させるためのものであって、回転軸の下部に給油片が設けられ、この給油片の上部の回転軸には、回転軸の中心に対して偏心している給油通路が形成され、給油通路上部の回転軸の外面には、給油通路に連通する給油案内溝が形成されている。また、回転軸上部の偏心部には、ピストン側への給油ができるように、給油案内溝の上端に連通した上側給油通路が形成されている。   As a technique related to a general hermetic compressor, a technique is disclosed in which oil is supplied to each drive portion of the compressor using rotation of a rotating shaft (see, for example, Japanese Patent Laid-Open No. 2000-205130). This compressor is for raising the oil accumulated at the bottom of the hermetic case when the rotary shaft rotates. An oil supply piece is provided at the lower portion of the rotary shaft, and the upper rotary shaft of the oil supply piece is provided. An oil supply passage that is eccentric with respect to the center of the rotation shaft is formed, and an oil supply guide groove that communicates with the oil supply passage is formed on the outer surface of the rotation shaft at the upper portion of the oil supply passage. Further, an upper oil supply passage communicating with the upper end of the oil supply guide groove is formed in the eccentric portion of the upper part of the rotation shaft so that oil supply to the piston side can be performed.

このような密閉型圧縮機は、回転軸が回転するとき、給油片を介してオイルが上昇し、上昇するオイルが偏心状態の給油通路に沿って螺旋状の給油案内溝に供給される。また、給油案内溝に沿って上昇するオイルは回転軸を支持する軸支持部の内面に対する潤滑及び冷却を行いながら、上側偏心部内に形成された上側給油通路に供給され、上側の給油通路のオイルがピストンに供給されて、ピストン側の潤滑を行う。
特開２０００−２０５１３０号公報 In such a hermetic compressor, when the rotary shaft rotates, the oil rises through the oil supply piece, and the rising oil is supplied to the spiral oil supply guide groove along the eccentric oil supply passage. Further, the oil rising along the oil supply guide groove is supplied to the upper oil supply passage formed in the upper eccentric portion while lubricating and cooling the inner surface of the shaft support portion that supports the rotating shaft, and the oil in the upper oil supply passage. Is supplied to the piston to lubricate the piston.
JP 2000-205130 A

ところで、このような従来の密閉型圧縮機は、給油片上側の回転軸内部に形成された給油通路が回転軸の中心に平行に上下直線状に形成されているため、回転軸が低速で回転する場合、給油通路に沿ってオイルが上昇するうちにオイルの上昇力が弱化して螺旋状の給油案内溝側への給油が円滑に行えない欠点があった。 また、従来の圧縮機の給油構造は、回転軸上部の偏心部内に形成された上側給油通路も回転軸に平行に上下直線状に形成される構造であるため、給油過程でオイルの上昇力が弱化してピストン側への給油が円滑でない問題があった。   By the way, in such a conventional hermetic compressor, since the oil supply passage formed inside the rotary shaft on the upper side of the oil supply piece is formed in a straight line in the vertical direction parallel to the center of the rotary shaft, the rotary shaft rotates at a low speed. In this case, there is a drawback that the oil ascending force weakens while the oil rises along the oil supply passage, and the oil supply to the spiral oil supply guide groove cannot be smoothly performed. In addition, the oil supply structure of the conventional compressor is a structure in which the upper oil supply passage formed in the eccentric portion of the upper part of the rotating shaft is also formed in a straight line in the vertical direction parallel to the rotating shaft. There was a problem that the oil supply to the piston side was not smooth due to weakening.

したがって、本発明は、このような問題点を解決するためになされたもので、その目的は、回転軸が低速で回転しても十分なオイルの上昇力を引き起こして、回転軸の各駆動部に円滑に給油し得るようにした密閉型圧縮機を提供することにある。   Accordingly, the present invention has been made to solve such problems, and the object thereof is to cause sufficient oil ascending force even when the rotating shaft rotates at a low speed, so that each drive unit of the rotating shaft Another object of the present invention is to provide a hermetic compressor that can smoothly supply oil.

前記目的を達成するため、本発明は、密閉ケースと、前記密閉ケースに収容されるフレームと、前記フレームに装着される下側の伝動機構部及び上側の圧縮機構部と、前記伝動機構部の回転力を前記圧縮機構部に伝達するため前記フレームに上下方向に設けられ、上部に前記圧縮機構部に連結される偏心部を有する回転軸と、前記密閉ケースの底部のオイルを各駆動部に供給するため前記回転軸に設けられる給油案内手段とを含んでなり、前記給油案内手段は、前記密閉ケース内に溜まったオイルを上昇させるため前記回転軸の下部に設けられる第１オイルピックアップ部材と、前記第１オイルピックアップ部材の上部の前記回転軸内に形成され、前記回転軸の中心に対して偏心している第１給油通路と、前記第１給油通路の上部の前記回転軸の外面に形成され、前記第１給油通路に連結される螺旋状給油溝と、前記螺旋状給油溝に連結されるように前記回転軸の偏心部内に形成される第２給油通路と、オイルの上昇力を増大させるため前記第１給油通路内に設けられる第２オイルピックアップ部材とを含む密閉型圧縮機を提供する。   To achieve the above object, the present invention provides a sealed case, a frame accommodated in the sealed case, a lower transmission mechanism portion and an upper compression mechanism portion mounted on the frame, and a transmission mechanism portion. In order to transmit the rotational force to the compression mechanism, the frame is provided in the vertical direction, and has a rotating shaft having an eccentric portion connected to the compression mechanism at the top, and oil at the bottom of the sealed case is supplied to each drive unit. A first oil pickup member provided at a lower portion of the rotary shaft for raising the oil accumulated in the sealed case; A first oil supply passage formed in the rotary shaft at an upper portion of the first oil pickup member and decentered with respect to a center of the rotary shaft; and the rotation at an upper portion of the first oil supply passage. A helical oil groove formed on the outer surface of the rotary shaft and connected to the helical oil groove, a second oil passage formed in the eccentric portion of the rotary shaft so as to be connected to the helical oil groove, There is provided a hermetic compressor including a second oil pickup member provided in the first oil supply passage in order to increase a rising force.

前記第１給油通路は、下部から上部に行くほど、その中心が前記回転軸の中心から離隔する方向に斜めに形成される。前記第２給油通路は、下部から上部に行くほど、その中心が前記回転軸の中心から離隔する方向に斜めに形成される。前記密閉型圧縮機は、前記フレームの上部と前記回転軸の偏心部下端との間に介在されるベアリングをさらに含み、前記第２給油通路は、前記回転軸の偏心部から前記ベアリングの下部位置の前記回転軸の内部まで形成され、半径方向に形成される連通孔を介して前記螺旋状給油溝に連結される。前記ベアリングは軸方向荷重を支持するスラストベアリングである。前記回転軸の外面には、前記ベアリング側に給油するため、前記螺旋状給油溝の上部から前記ベアリングの位置まで形成されるオイル誘導部が設けられる。前記オイル誘導部は、前記回転軸の外面に上下方向に形成される平面からなる。前記第１オイルピックアップ部材は、下端に外径より小さいオイル流入口が形成された円筒状のオイル案内部と、前記オイル案内部内に収容される螺旋状ブレードとを含む。前記第２オイルピックアップ部材は、前記第１給油通路内に収容される螺旋状ブレードを含む。前記回転軸の偏心部には、前記第２給油通路が偏心部の外面で開放されるように半径方向に補助流路が形成される。   The center of the first oil supply passage is formed obliquely in a direction away from the center of the rotation shaft as it goes from the lower part to the upper part. The center of the second oil supply passage is formed obliquely in a direction away from the center of the rotating shaft as it goes from the lower part to the upper part. The hermetic compressor further includes a bearing interposed between an upper portion of the frame and a lower end of an eccentric portion of the rotating shaft, and the second oil supply passage is located at a lower position of the bearing from the eccentric portion of the rotating shaft. Is formed up to the inside of the rotary shaft, and is connected to the spiral oil supply groove through a communication hole formed in the radial direction. The bearing is a thrust bearing that supports an axial load. The outer surface of the rotating shaft is provided with an oil guiding portion that is formed from the upper portion of the spiral oil supply groove to the position of the bearing in order to supply oil to the bearing side. The oil guiding portion is a flat surface formed in the vertical direction on the outer surface of the rotating shaft. The first oil pickup member includes a cylindrical oil guide part having an oil inlet smaller than an outer diameter formed at a lower end thereof, and a spiral blade accommodated in the oil guide part. The second oil pickup member includes a spiral blade accommodated in the first oil supply passage. In the eccentric part of the rotating shaft, an auxiliary flow path is formed in the radial direction so that the second oil supply passage is opened at the outer surface of the eccentric part.

また、本発明は、密閉ケースと、前記密閉ケースに収容されるフレームと、前記フレームに装着される下側の伝動機構部及び上側の圧縮機構部と、前記伝動機構部の回転力を前記圧縮機構部に伝達するため前記フレームに上下方向に設けられ、上部に前記圧縮機構部に連結される偏心部を有する回転軸と、前記密閉ケースの底部のオイルを各駆動部に供給するため前記回転軸に設けられる給油案内手段とを含んでなり、前記給油案内手段は、前記密閉ケース内に溜まったオイルを上昇させるため前記回転軸の下部に設けられる第１オイルピックアップ部材と、前記第１オイルピックアップ部材の上部の前記回転軸内に形成され、前記回転軸の中心に対して偏心している第１給油通路と、前記第１給油通路の上部の前記回転軸の外面に形成され、前記第１給油通路に連結される螺旋状給油溝と、前記螺旋状給油溝に連結されるように前記回転軸の偏心部内に形成され、下部から上部に行くほどその中心が前記回転軸の中心から離隔する方向に斜めに形成される第２オイルピックアップ部材とを含む密閉型圧縮機を提供する。   The present invention also provides a sealed case, a frame accommodated in the sealed case, a lower transmission mechanism portion and an upper compression mechanism portion mounted on the frame, and a rotational force of the transmission mechanism portion. A rotary shaft provided in the vertical direction on the frame for transmission to the mechanism part and having an eccentric part connected to the compression mechanism part at the top, and the rotation for supplying oil at the bottom of the sealed case to each drive part Oil supply guide means provided on the shaft, wherein the oil supply guide means is provided with a first oil pickup member provided at a lower portion of the rotating shaft for raising the oil accumulated in the sealed case, and the first oil. A first oil supply passage formed in the rotary shaft above the pickup member and decentered with respect to the center of the rotary shaft, and formed on an outer surface of the rotary shaft above the first oil supply passage. A spiral oil supply groove connected to the first oil supply passage, and an eccentric portion of the rotary shaft so as to be connected to the spiral oil supply groove, the center of the rotary shaft going from the bottom to the top. A hermetic compressor including a second oil pickup member formed obliquely in a direction away from the second oil pickup member.

以上のような本発明による密閉型圧縮機は、回転軸内部の第１給油通路が回転軸の中心に対して偏心している構造で、下部から上部に行くほど回転中心から離隔する方向に斜めに形成され、第２オイルピックアップ部材を収容した構造であるため、回転軸が低速で回転しても、第１給油通路に沿って案内されるオイルの上昇力が増大して、上方向への給油が円滑になされる。
また、本発明は、回転軸上部の第２給油通路が下部から上部に行くほど回転中心から離隔する方向に斜めに形成された構造であるため、回転軸が低速で回転しても第２給油通路に沿って案内されるオイルの上昇力が増大して、上側圧縮機構部側への給油が円滑になされる。
更に、本発明は、回転軸上部の外面のオイル誘導部によりスラストベアリング側に給油されるため、スラストベアリングの潤滑及び冷却が円滑になされる効果がある。 The hermetic compressor according to the present invention as described above has a structure in which the first oil supply passage in the rotating shaft is eccentric with respect to the center of the rotating shaft, and is inclined in a direction away from the rotating center as it goes from the lower part to the upper part. Since the structure is formed and accommodates the second oil pick-up member, even if the rotation shaft rotates at a low speed, the upward force of the oil guided along the first oil supply passage increases, and the oil supply in the upward direction Is made smoothly.
Further, the present invention has a structure in which the second oil supply passage at the upper part of the rotating shaft is formed obliquely in a direction away from the center of rotation as it goes from the lower part to the upper part. Ascending force of the oil guided along the passage is increased, and the oil is smoothly supplied to the upper compression mechanism portion side.
Furthermore, according to the present invention, oil is supplied to the thrust bearing side by the oil guide portion on the outer surface of the upper part of the rotating shaft, so that the thrust bearing is smoothly lubricated and cooled.

以下、本発明の好ましい実施の形態を添付図面に基づいて詳細に説明する。   Preferred embodiments of the present invention will be described below in detail with reference to the accompanying drawings.

図１に示すように、本発明による密閉型圧縮機は、密閉ケース１０の内部に複数の緩衝装置１１を介して設置されるフレーム１２と、該フレーム１２の上側に設けられる圧縮機構部２０と、該圧縮機構部２０の駆動のためにフレーム１２の下側に設けられる伝動機構部３０とを含む。   As shown in FIG. 1, a hermetic compressor according to the present invention includes a frame 12 installed inside a sealed case 10 via a plurality of shock absorbers 11, and a compression mechanism unit 20 provided on the upper side of the frame 12. And a transmission mechanism 30 provided on the lower side of the frame 12 for driving the compression mechanism 20.

この圧縮機は、伝動機構部３０の回転力を圧縮機構部２０に伝達するもので、上下方向に配設され、フレーム１２の軸支持部１３に回転可能に支持される回転軸４０を含む。また、前記回転軸４０は上側の圧縮機構部２０との連結のためのもので、その中心に対して偏心状に形成された偏心部４１を含み、偏心部４１の下端部には、フレーム１２の上部に支持されるように、回転軸４０の外径より大きいベアリング支持部４２を含む。そして、前記ベアリング支持部４２の下面とフレーム１２の上面との間には、回転軸４０の軸方向荷重を支持するとともに回転軸４０の回転を容易にするものとしてスラストベアリング４３が介在される。   This compressor transmits the rotational force of the transmission mechanism 30 to the compression mechanism 20 and includes a rotary shaft 40 that is disposed in the vertical direction and is rotatably supported by the shaft support 13 of the frame 12. The rotary shaft 40 is for connection with the upper compression mechanism portion 20 and includes an eccentric portion 41 formed eccentrically with respect to the center thereof. A bearing support portion 42 that is larger than the outer diameter of the rotating shaft 40 is included. A thrust bearing 43 is interposed between the lower surface of the bearing support portion 42 and the upper surface of the frame 12 to support the axial load of the rotating shaft 40 and facilitate the rotation of the rotating shaft 40.

前述した伝動機構部３０は、回転軸４０の外面に嵌合されて回転軸４０とともに回転する回転子３１と、該回転子３１の外側に固定状態に取り付けられる固定子３２とを含む。そして、圧縮機構部２０は、冷媒の圧縮空間をなすシリンダ２１及びシリンダヘッド２２と、シリンダ２１の内部で進退しながら冷媒の圧縮を行うピストン２３と、一端がピストン２３のピン２４に連結され、他端が回転軸４０の偏心部４１に連結されるコネクティングロッド２５とを含む。このような構成は、伝動機構部３０の動作により回転軸４０が回転するとき、回転軸４０の偏心部４１及びコネクティングロッド２５を介して回転運動を直線往復運動に変換してピストン２３を進退させることにより、冷媒の圧縮を行うようにしたものである。   The transmission mechanism 30 described above includes a rotor 31 that is fitted to the outer surface of the rotating shaft 40 and rotates together with the rotating shaft 40, and a stator 32 that is fixedly attached to the outside of the rotor 31. The compression mechanism 20 includes a cylinder 21 and a cylinder head 22 forming a refrigerant compression space, a piston 23 that compresses the refrigerant while advancing and retreating inside the cylinder 21, and one end connected to a pin 24 of the piston 23. The connecting rod 25 is connected to the eccentric portion 41 of the rotating shaft 40 at the other end. In such a configuration, when the rotating shaft 40 is rotated by the operation of the transmission mechanism 30, the rotational motion is converted into a linear reciprocating motion via the eccentric portion 41 of the rotating shaft 40 and the connecting rod 25, and the piston 23 is advanced and retracted. Thus, the refrigerant is compressed.

また、本発明による密閉型圧縮機は各駆動部の潤滑及び冷却のためのものであって、密閉ケース１０の底部に所定量のオイルが収容される。そして、回転軸４０には、回転軸４０の回転力を用いて密閉ケース１０の底部に溜まったオイルを上昇させて各駆動部に供給するための給油案内手段が設けられる。   The hermetic compressor according to the present invention is for lubricating and cooling each drive unit, and a predetermined amount of oil is accommodated in the bottom of the hermetic case 10. The rotating shaft 40 is provided with oil supply guide means for raising the oil accumulated at the bottom of the sealed case 10 using the rotational force of the rotating shaft 40 and supplying the oil to each driving unit.

このような給油案内手段は、図２に示すように、回転軸４０の下部に設けられる第１オイルピックアップ部材５１と、該第１オイルピックアップ部材５１の上側の回転軸４０内に形成される第１給油通路５２と、該第１給油通路５２に連結されるように回転軸４０の上部外面に形成される螺旋状給油溝５４と、該螺旋状給油溝５４の上端に連結されるように回転軸４０の偏心部４１内に形成される第２給油通路５６とを含む。   As shown in FIG. 2, such an oil supply guide means includes a first oil pickup member 51 provided in the lower portion of the rotation shaft 40 and a first rotation shaft 40 formed in the upper rotation shaft 40 of the first oil pickup member 51. 1 oil supply passage 52, a spiral oil supply groove 54 formed on the upper outer surface of the rotary shaft 40 so as to be connected to the first oil supply passage 52, and a rotation so as to be connected to the upper end of the spiral oil supply groove 54 And a second oil supply passage 56 formed in the eccentric portion 41 of the shaft 40.

より具体的に、第１オイルピックアップ部材５１は、回転軸４０の下端に結合され、上部から下部に行くほど外径が縮小する円筒状に形成され、オイルに漬かる下端部にその外径より小さいオイル流入口５１ｃが形成されたオイル案内部５１ａと、該オイル案内部５１ａの内部に設けられる螺旋状ブレード５１ｂとからなる。したがって、回転軸４０が回転するにつれて、オイル流入口５１ｃを介して内部に流入したオイルが螺旋状ブレード５１ｂの回転により上昇して第１給油通路５２側に供給される。   More specifically, the first oil pickup member 51 is coupled to the lower end of the rotary shaft 40, is formed in a cylindrical shape whose outer diameter is reduced from the upper part to the lower part, and is smaller than the outer diameter at the lower end part immersed in oil. It comprises an oil guide 51a in which an oil inlet 51c is formed, and a spiral blade 51b provided inside the oil guide 51a. Therefore, as the rotating shaft 40 rotates, the oil that has flowed into the inside through the oil inlet 51c is raised by the rotation of the spiral blade 51b and supplied to the first oil supply passage 52 side.

前記第１給油通路５２は第１オイルピックアップ部材５１の作用により上昇するオイルを案内するためのもので、第１オイルピックアップ部材５１の上部から回転軸４０を支持するフレーム１２の軸支持部１３の下端の上部まで上下方向に長く形成され、回転軸４０の中心に対して偏心状態となるように形成される。また、第１給油通路５２は、下部から上部に行くほどその中心が回転軸４０の中心から離隔する方向に所定角度（θ１）だけ斜めに形成される。そして、第１給油通路５２の上部には、螺旋状給油溝５４の下部と連結されるように回転軸４０の半径方向に連通孔５２ａが形成される。したがって、回転軸４０が回転すると、第１給油通路５２の内部のオイルに作用する遠心力が増大してオイルを円滑に上昇させることができる。   The first oil supply passage 52 is for guiding the oil rising by the action of the first oil pickup member 51, and the shaft support portion 13 of the frame 12 that supports the rotary shaft 40 from above the first oil pickup member 51. It is formed so as to be long in the vertical direction up to the upper end of the lower end, and is formed to be eccentric with respect to the center of the rotating shaft 40. Further, the first oil supply passage 52 is formed so as to be inclined at a predetermined angle (θ1) in a direction in which the center is separated from the center of the rotation shaft 40 as it goes from the lower part to the upper part. A communication hole 52 a is formed in the radial direction of the rotary shaft 40 at the upper portion of the first oil supply passage 52 so as to be connected to the lower portion of the spiral oil supply groove 54. Therefore, when the rotating shaft 40 rotates, the centrifugal force acting on the oil inside the first oil supply passage 52 increases, and the oil can be raised smoothly.

また、第１給油通路５２の内部には、オイルの上昇力をさらに高めるため螺旋ブレード状の第２オイルピックアップ部材５３が設けられる。したがって、回転軸４０が回転するときに発生する遠心力だけでなく第２オイルピックアップ部材５３の作用によりオイルの上昇力が増大するので、オイルが上部の螺旋状給油溝５４まで円滑に案内される。   In addition, a spiral blade-shaped second oil pickup member 53 is provided inside the first oil supply passage 52 in order to further increase the oil lifting force. Therefore, not only the centrifugal force generated when the rotating shaft 40 rotates but also the oil rising force is increased by the action of the second oil pickup member 53, so that the oil is smoothly guided to the upper spiral oil supply groove 54. .

前記螺旋状給油溝５４は、回転軸４０の外面に螺旋状に形成される所定深さの溝からなる。この螺旋状給油溝５４はフレーム１２の軸支持部１３の内面との間にオイル流路が形成することにより、回転軸４０が回転するとき、螺旋状給油溝５４に沿ってオイルの上昇が案内される。また、上昇するオイルにより、回転軸４０の外面と軸支持部１３の内面間の潤滑及び冷却がなされる。   The spiral oil supply groove 54 is a groove having a predetermined depth formed in a spiral shape on the outer surface of the rotating shaft 40. An oil flow path is formed between the spiral oil supply groove 54 and the inner surface of the shaft support portion 13 of the frame 12, so that when the rotary shaft 40 rotates, oil rise is guided along the spiral oil supply groove 54. Is done. Further, the rising oil lubricates and cools the outer surface of the rotating shaft 40 and the inner surface of the shaft support portion 13.

前記第２給油通路５６は、下部から上部に行くほどその中心が回転軸４０の中心から離隔する方向に所定角度（θ２）だけ斜めに形成され、下端が回転軸４０の半径方向に形成された連通孔５５を介して螺旋状給油溝５４の上部に連結され、上端が回転軸４０の偏心部４１の上端で開放される。したがって、回転軸４０の回転により生じる遠心力によりオイルの上昇力が増大して、螺旋状給油溝５４に沿って上部まで上昇したオイルがフレーム１２の上側圧縮機構部２０側に円滑に供給される。この際、回転軸４０の偏心部４１には、第２給油通路５６に沿って上昇するオイルが偏心部４１に嵌合されるコネクティングロッド２５側に供給されるように、半径方向に補助流路５７が形成される。   The center of the second oil supply passage 56 is formed obliquely by a predetermined angle (θ2) in a direction away from the center of the rotating shaft 40 as it goes from the lower part to the upper part, and the lower end is formed in the radial direction of the rotating shaft 40. The upper end of the spiral oil supply groove 54 is connected to the upper portion of the helical oil groove 54 through the communication hole 55, and the upper end is opened at the upper end of the eccentric portion 41 of the rotating shaft 40. Therefore, the rising force of the oil is increased by the centrifugal force generated by the rotation of the rotating shaft 40, and the oil rising to the upper portion along the spiral oil supply groove 54 is smoothly supplied to the upper compression mechanism portion 20 side of the frame 12. . At this time, in the eccentric portion 41 of the rotating shaft 40, the oil that rises along the second oil supply passage 56 is supplied to the connecting rod 25 side fitted to the eccentric portion 41 in the radial direction along the auxiliary flow path. 57 is formed.

また、第２給油通路５６は、図３に示すように、回転軸４０の偏心部４１からスラストベアリング４３の下部位置の回転軸４０の内部まで延長されるように形成される。すなわち、第２給油通路５６と螺旋状給油溝５４を連結させる連通孔５５はスラストベアリング４３の下部に位置する。したがって、回転軸４０の外面に形成される螺旋状給油溝５４の上端部がスラストベアリング４３の位置に至ると、螺旋状給油溝５４に沿って上昇したオイルがスラストベアリング４３の隙間を介して半径方向に拡散してそれ以上上昇しないため、連通孔５５をスラストベアリング４３の下部に配置することにより、このような現象を防止する。   Further, as shown in FIG. 3, the second oil supply passage 56 is formed to extend from the eccentric portion 41 of the rotation shaft 40 to the inside of the rotation shaft 40 at a lower position of the thrust bearing 43. That is, the communication hole 55 that connects the second oil supply passage 56 and the helical oil supply groove 54 is positioned below the thrust bearing 43. Therefore, when the upper end portion of the spiral oil supply groove 54 formed on the outer surface of the rotating shaft 40 reaches the position of the thrust bearing 43, the oil rising along the spiral oil supply groove 54 has a radius through the gap of the thrust bearing 43. Since the diffusion in the direction does not increase further, the communication hole 55 is disposed below the thrust bearing 43 to prevent such a phenomenon.

また、回転軸４０の上部外面には、螺旋状給油溝５４に沿って上昇したオイルの一部がスラストベアリング４３側に供給されてスラストベアリング４３の潤滑及び冷却を行うように、螺旋状給油溝５４の上部からスラストベアリング４３の位置まで形成されるオイル誘導部５８が設けられる。この際、オイル誘導部５８は、図４に示すように、フレーム１２の軸支持部１３の内面と回転軸４０の外面との間にオイル流路が形成されるように、回転軸４０の外面に上下方向に形成される平面からなる。   Further, on the outer surface of the upper portion of the rotating shaft 40, a spiral oil supply groove is provided so that a part of the oil rising along the spiral oil supply groove 54 is supplied to the thrust bearing 43 side to lubricate and cool the thrust bearing 43. An oil guide 58 formed from the upper part of 54 to the position of the thrust bearing 43 is provided. At this time, as shown in FIG. 4, the oil guiding portion 58 is formed on the outer surface of the rotating shaft 40 so that an oil flow path is formed between the inner surface of the shaft support portion 13 of the frame 12 and the outer surface of the rotating shaft 40. It consists of a plane formed in the vertical direction.

つぎに、このような密閉型圧縮機の圧縮及び給油動作を説明する。   Next, compression and oil supply operations of such a hermetic compressor will be described.

図１に示すように、下側の伝動機構部３０の動作により回転軸４０が回転すると、回転軸４０の上部の偏心部４１と圧縮機構部２０のコネクティングロッド２５の作用により回転運動が直線往復運動に変換されることにより、ピストン２３が進退する。そして、このようなピストン２３の進退動作により冷媒がシリンダ２１の内部に吸入され、圧縮されてから吐き出される。   As shown in FIG. 1, when the rotary shaft 40 is rotated by the operation of the lower transmission mechanism portion 30, the rotational motion is linearly reciprocated by the action of the eccentric portion 41 on the upper portion of the rotary shaft 40 and the connecting rod 25 of the compression mechanism portion 20. The piston 23 moves forward and backward by being converted into motion. The refrigerant is sucked into the cylinder 21 by such a forward / backward movement of the piston 23 and is discharged after being compressed.

この動作のうちには、回転軸４０に設けられた給油案内手段の作用により、密閉ケースの底部に溜まったオイルが回転軸に沿って上昇しながら各駆動部に給油し、このような給油により、各駆動部の冷却及び潤滑がなされるので、圧縮機が円滑に動作することになる。このような給油動作は具体的につぎのようである。   In this operation, the oil accumulated in the bottom of the sealed case is raised along the rotation shaft by the action of the oil supply guide means provided on the rotation shaft 40, and is supplied to each drive unit. Since each drive unit is cooled and lubricated, the compressor operates smoothly. Such a refueling operation is specifically as follows.

前記回転軸４０とともに第１オイルピックアップ部材５１が回転すると、密閉ケース１０の底部に溜まったオイルは第１オイルピックアップ部材５１のオイル流入口５１ｃを介してその内部に流入し、流入したオイルは第１オイルピックアップ部材５１の内部の螺旋状ブレード５１ｂの作用により上部の第１給油通路５２に供給される。   When the first oil pickup member 51 rotates together with the rotary shaft 40, the oil accumulated at the bottom of the sealed case 10 flows into the inside through the oil inlet 51c of the first oil pickup member 51, and the oil that has flowed in 1 is supplied to the upper first oil supply passage 52 by the action of the spiral blade 51 b inside the oil pickup member 51.

前記第１給油通路５２に供給されたオイルは、第１給油通路５２が回転軸４０の中心から偏心状態にかつ所定角度（θ１）だけ傾いているだけでなく、第１給油通路５２の内部に第２オイルピックアップ部材５３が設けられているため、回転軸４０が低速で回転しても、オイルの上昇力が増大して上部の螺旋状給油溝５４側に円滑に案内される。この際、第１給油通路５２に沿って上昇したオイルは第１給油通路５２の上部の連通孔５２ａを介して螺旋状給油溝５４に供給される。   The oil supplied to the first oil supply passage 52 is not only the first oil supply passage 52 being eccentric from the center of the rotary shaft 40 and inclined by a predetermined angle (θ1), but also inside the first oil supply passage 52. Since the second oil pickup member 53 is provided, even if the rotary shaft 40 rotates at a low speed, the oil rising force increases and is smoothly guided to the upper spiral oil supply groove 54 side. At this time, the oil that has risen along the first oil supply passage 52 is supplied to the spiral oil supply groove 54 via the communication hole 52 a in the upper part of the first oil supply passage 52.

前記螺旋状給油溝５４に供給されたオイルは螺旋状給油溝５４の作用により上昇しながら回転軸４０の外面と軸支持部１３の内面間の潤滑及び冷却を行う。つづいて、オイルは螺旋状給油溝５４により上側に案内された後、半径方向の連通孔５５を介して第２給油通路５６に供給され、第２給油通路５６に沿って上昇して圧縮機構部２０の各駆動部に供給される。この際、第１給油通路５６が所定角度（θ２）だけ斜めに形成されているため、回転軸４０が低速で回転しても、遠心力によりオイルの上昇力が増大して圧縮機構部２０側に円滑に給油される。また、螺旋状給油溝５４の上部まで案内されたオイルの一部はオイル誘導部５８を介してスラストベアリング４３側にも供給されるので、スラストベアリング４３の潤滑及び冷却が効率良くなされる。   The oil supplied to the helical oil supply groove 54 is lubricated and cooled between the outer surface of the rotating shaft 40 and the inner surface of the shaft support portion 13 while being raised by the action of the helical oil supply groove 54. Subsequently, after the oil is guided upward by the spiral oil supply groove 54, the oil is supplied to the second oil supply passage 56 through the communication hole 55 in the radial direction, and rises along the second oil supply passage 56 to be compressed. Supplied to 20 drive units. At this time, since the first oil supply passage 56 is formed obliquely by a predetermined angle (θ2), even if the rotary shaft 40 rotates at a low speed, the oil rising force increases due to the centrifugal force, and the compression mechanism unit 20 side Smoothly lubricated. Further, since a part of the oil guided to the upper part of the spiral oil supply groove 54 is also supplied to the thrust bearing 43 side through the oil guiding portion 58, the thrust bearing 43 is lubricated and cooled efficiently.

本発明による密閉型圧縮機の構成を示す断面図である。It is sectional drawing which shows the structure of the hermetic type compressor by this invention. 本発明による密閉型圧縮機の回転軸に設けられた給油案内手段の構成を示す部分断面側面図である。It is a fragmentary sectional side view which shows the structure of the oil supply guide means provided in the rotating shaft of the hermetic type compressor by this invention. 本発明による密閉型圧縮機の回転軸の上側の第２給油通路とオイル誘導部の構成を示す断面図である。It is sectional drawing which shows the structure of the 2nd oil supply path above the rotating shaft of the hermetic compressor by this invention, and an oil guide part. 図３の線IV−IV’についての断面図である。FIG. 4 is a cross-sectional view taken along line IV-IV ′ in FIG. 3.

符号の説明Explanation of symbols

１０ 密閉ケース
１１ 緩衝装置
１２ フレーム
１３ 軸支持部
２０ 圧縮機構部
２１ シリンダ
２２ シリンダヘッド
２３ ピストン
２４ ピン
２５ コネクティングロッド
３０ 伝動機構部
３１ 回転子
３２ 固定子
４０ 回転軸
４１ 偏心部
４２ ベアリング支持部
４３ スラストベアリング
５１ 第１オイルピックアップ部材
５１ａ オイル案内部
５１ｂ 螺旋状ブレード
５１ｃ オイル流入口
５２ 第１給油通路
５２ａ 連通孔
５３ 第２オイルピックアップ部材
５４ 螺旋状給油溝
５５ 連通孔
５６ 第２給油通路 DESCRIPTION OF SYMBOLS 10 Sealing case 11 Shock absorber 12 Frame 13 Shaft support part 20 Compression mechanism part 21 Cylinder 22 Cylinder head 23 Piston 24 Pin 25 Connecting rod 30 Transmission mechanism part 31 Rotor 32 Stator 40 Rotating shaft 41 Eccentric part 42 Bearing support part 43 Thrust Bearing 51 First oil pickup member 51a Oil guide portion 51b Spiral blade 51c Oil inlet 52 First oil supply passage 52a Communication hole 53 Second oil pickup member 54 Spiral oil supply groove 55 Communication hole 56 Second oil supply passage

Claims (13)

密閉ケースと、前記密閉ケースに収容されるフレームと、前記フレームに装着される下側の伝動機構部及び上側の圧縮機構部と、前記伝動機構部の回転力を前記圧縮機構部に伝達するため前記フレームに上下方向に設けられ、上部に前記圧縮機構部に連結される偏心部を有する回転軸と、前記密閉ケースの底部のオイルを各駆動部に供給するため前記回転軸に設けられる給油案内手段とを有して、
前記給油案内手段は、前記密閉ケース内に溜まったオイルを上昇させるため前記回転軸の下部に設けられる第１オイルピックアップ部材と、前記第１オイルピックアップ部材の上部の前記回転軸内に形成され、前記回転軸の中心に対して偏心している第１給油通路と、前記第１給油通路の上部の前記回転軸の外面に形成され、前記第１給油通路に連結される螺旋状給油溝と、前記螺旋状給油溝に連結されるように前記回転軸の偏心部内に形成される第２給油通路と、オイルの上昇力を増大させるため前記第１給油通路内に設けられる第２オイルピックアップ部材とを有することを特徴とする密閉型圧縮機。 A sealing case, a frame housed in the sealing case, a lower transmission mechanism portion and an upper compression mechanism portion mounted on the frame, and a rotational force of the transmission mechanism portion to transmit the rotational force to the compression mechanism portion A rotation shaft provided in the vertical direction on the frame and having an eccentric portion connected to the compression mechanism portion on the upper portion, and an oil supply guide provided on the rotation shaft for supplying oil at the bottom of the sealed case to each drive portion Having means,
The oil supply guide means is formed in the rotary shaft at the top of the first oil pickup member, and a first oil pickup member provided at the lower portion of the rotary shaft for raising the oil accumulated in the sealed case, A first oil supply passage that is eccentric with respect to a center of the rotation shaft, a helical oil supply groove that is formed on an outer surface of the rotation shaft at an upper portion of the first oil supply passage, and is connected to the first oil supply passage; A second oil supply passage formed in the eccentric portion of the rotary shaft so as to be connected to the helical oil supply groove, and a second oil pickup member provided in the first oil supply passage to increase the oil lifting force. A hermetic compressor characterized by having. 前記第１給油通路は、下部から上部に行くほどその中心が前記回転軸の中心から離隔する方向に斜めに形成されることを特徴とする請求項１に記載の密閉型圧縮機。   2. The hermetic compressor according to claim 1, wherein a center of the first oil supply passage is inclined in a direction away from the center of the rotating shaft as it goes from the lower part to the upper part. 前記第２給油通路は、下部から上部に行くほどその中心が前記回転軸の中心から離隔する方向に斜めに形成されることを特徴とする請求項１に記載の密閉型圧縮機。   2. The hermetic compressor according to claim 1, wherein a center of the second oil supply passage is formed obliquely in a direction away from the center of the rotation shaft as it goes from the lower part to the upper part. 前記フレームの上部と前記回転軸の偏心部下端との間に介在されるベアリングをさらに含み、
前記第２給油通路は、前記回転軸の偏心部から前記ベアリングの下部位置の前記回転軸の内部まで形成され、半径方向に形成される連通孔を介して前記螺旋状給油溝に連結されることを特徴とする請求項１に記載の密閉型圧縮機。 A bearing interposed between the upper part of the frame and the lower end of the eccentric part of the rotary shaft;
The second oil supply passage is formed from an eccentric portion of the rotary shaft to the inside of the rotary shaft at a lower position of the bearing, and is connected to the spiral oil supply groove through a communication hole formed in a radial direction. The hermetic compressor according to claim 1. 前記ベアリングは軸方向荷重を支持するスラストベアリングであることを特徴とする請求項４に記載の密閉型圧縮機。   The hermetic compressor according to claim 4, wherein the bearing is a thrust bearing that supports an axial load. 前記回転軸の外面には、前記ベアリング側に給油するため、前記螺旋状給油溝の上部から前記ベアリングの位置まで形成されるオイル誘導部が設けられることを特徴とする請求項４に記載の密閉型圧縮機。   5. The hermetic seal according to claim 4, wherein an oil guide portion formed from an upper portion of the spiral oil supply groove to a position of the bearing is provided on an outer surface of the rotating shaft to supply oil to the bearing side. Mold compressor. 前記オイル誘導部は、前記回転軸の外面に上下方向に形成される平面からなることを特徴とする請求項６に記載の密閉型圧縮機。   The hermetic compressor according to claim 6, wherein the oil guide portion is a flat surface formed on an outer surface of the rotating shaft in a vertical direction. 前記第１オイルピックアップ部材は、下端に外径より小さいオイル流入口が形成された円筒状のオイル案内部と、前記オイル案内部内に収容される螺旋状ブレードとを有することを特徴とする請求項１に記載の密閉型圧縮機。   The first oil pickup member includes a cylindrical oil guide part having an oil inlet smaller than an outer diameter formed at a lower end thereof, and a spiral blade accommodated in the oil guide part. The hermetic compressor according to 1. 前記第２オイルピックアップ部材は、前記第１給油通路内に収容される螺旋状ブレードを有することを特徴とする請求項１に記載の密閉型圧縮機。   2. The hermetic compressor according to claim 1, wherein the second oil pickup member has a spiral blade accommodated in the first oil supply passage. 前記回転軸の偏心部には、前記第２給油通路が前記偏心部の外面で開放されるように半径方向に補助流路が形成されることを特徴とする請求項１に記載の密閉型圧縮機。   2. The hermetic compression according to claim 1, wherein an auxiliary flow path is formed in a radial direction in the eccentric portion of the rotating shaft so that the second oil supply passage is opened at an outer surface of the eccentric portion. Machine. 密閉ケースと、前記密閉ケースに収容されるフレームと、前記フレームに装着される下側の伝動機構部及び上側の圧縮機構部と、前記伝動機構部の回転力を前記圧縮機構部に伝達するため前記フレームに上下方向に設けられ、上部に前記圧縮機構部に連結される偏心部を有する回転軸と、前記密閉ケースの底部のオイルを各駆動部に供給するため前記回転軸に設けられる給油案内手段とを有して、
前記給油案内手段は、前記密閉ケース内に溜まったオイルを上昇させるため前記回転軸の下部に設けられる第１オイルピックアップ部材と、前記第１オイルピックアップ部材の上部の前記回転軸内に形成され、前記回転軸の中心に対して偏心してなる第１給油通路と、前記第１給油通路の上部の前記回転軸の外面に形成され、前記第１給油通路に連結される螺旋状給油溝と、前記螺旋状給油溝に連結されるように前記回転軸の偏心部内に形成され、下部から上部に行くほど中心が前記回転軸の中心から離隔する方向に斜めに形成される第２オイルピックアップ部材とを有することを特徴とする密閉型圧縮機。 A sealing case, a frame housed in the sealing case, a lower transmission mechanism portion and an upper compression mechanism portion mounted on the frame, and a rotational force of the transmission mechanism portion to transmit the rotational force to the compression mechanism portion A rotation shaft provided in the vertical direction on the frame and having an eccentric portion connected to the compression mechanism portion on the upper portion, and an oil supply guide provided on the rotation shaft for supplying oil at the bottom of the sealed case to each drive portion Having means,
The oil supply guide means is formed in a first oil pickup member provided at a lower portion of the rotary shaft for raising oil accumulated in the sealed case, and in the rotary shaft at an upper portion of the first oil pickup member, A first oil supply passage that is eccentric with respect to the center of the rotation shaft, a spiral oil supply groove that is formed on an outer surface of the rotation shaft at an upper portion of the first oil supply passage, and is connected to the first oil supply passage; A second oil pickup member formed in the eccentric portion of the rotating shaft so as to be connected to the spiral oil supply groove, and formed so that the center is inclined in a direction away from the center of the rotating shaft from the bottom to the top. A hermetic compressor characterized by having. 前記フレームの上部と前記回転軸の偏心部下端との間に介在されるスラストベアリングをさらに含み、
前記第２給油通路は、前記回転軸の偏心部から前記スラストベアリングの下部位置の前記回転軸の内部まで形成され、半径方向に形成される連通孔を介して前記螺旋状給油溝に連結されることを特徴とする請求項１１に記載の密閉型圧縮機。 A thrust bearing interposed between the upper part of the frame and the lower end of the eccentric part of the rotary shaft;
The second oil supply passage is formed from an eccentric portion of the rotary shaft to the inside of the rotary shaft at a lower position of the thrust bearing, and is connected to the spiral oil supply groove through a communication hole formed in a radial direction. The hermetic compressor according to claim 11. 前記回転軸の外面には、前記スラストベアリング側に給油するため、前記螺旋状給油溝の上部から前記スラストベアリングの位置まで形成される平面状のオイル誘導部が設けられることを特徴とする請求項１２に記載の密閉型圧縮機。   The planar oil guide part formed from the upper part of the spiral oil supply groove to the position of the thrust bearing is provided on the outer surface of the rotating shaft to supply oil to the thrust bearing side. 12. The hermetic compressor according to 12.
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007292019A (en) * 2006-04-27 2007-11-08 Matsushita Electric Ind Co Ltd Hermetic compressor
EP4006343A1 (en) 2020-11-27 2022-06-01 LG Electronics Inc. Hermetic compressor

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005116449A1 (en) * 2004-05-28 2005-12-08 Matsushita Electric Industrial Co., Ltd. Hermetically sealed compressor
JP4158746B2 (en) * 2004-06-28 2008-10-01 松下電器産業株式会社 Electric compressor
CN1888435B (en) * 2005-06-29 2010-06-02 乐金电子(天津)电器有限公司 Working oil supply structure for geared compressor
KR101161124B1 (en) * 2005-10-07 2012-06-28 삼성전자 주식회사 Variable capacity compressor
WO2008142822A1 (en) * 2007-05-16 2008-11-27 Panasonic Corporation Expander-integrated compressor and refrigeration cycle device with the same
BRPI0800686A2 (en) * 2008-01-21 2009-09-08 Whirlpool Sa oil pump for a refrigeration compressor
KR20110054813A (en) * 2009-11-18 2011-05-25 엘지전자 주식회사 Compressor
BRPI1009161B8 (en) * 2010-12-06 2022-02-01 Embraco Ind De Compressores E Solucoes Em Refrigeracao Ltda Crankshaft for a reciprocating refrigeration compressor
JP6015055B2 (en) * 2012-03-27 2016-10-26 株式会社富士通ゼネラル Rotary compressor
KR101910656B1 (en) 2012-04-25 2018-10-23 삼성전자주식회사 Hermetic reciprocating compressor
KR101483519B1 (en) 2012-05-15 2015-01-16 삼성전자 주식회사 Hermetic reciprocating compressor
CN102953961A (en) * 2012-11-29 2013-03-06 广州万宝集团压缩机有限公司 Refrigerator compressor and lubricating-oil supplying device
CN105041618A (en) * 2015-08-27 2015-11-11 黄石东贝电器股份有限公司 Novel crankshaft of refrigeration compressor
KR102377778B1 (en) 2017-07-19 2022-03-23 삼성전자주식회사 Hermetic compressor
EP4092271A1 (en) * 2020-01-17 2022-11-23 Nidec Global Appliance Brasil Ltda. System for transporting lubricating oil in a compressor
CN113175617A (en) * 2021-03-29 2021-07-27 杭州罗松贸易有限公司 Self-lubricating device for textile machine and using method thereof
CN217652875U (en) * 2021-10-25 2022-10-25 思科普有限责任公司 Encapsulated refrigerant compressor
CN114992091B (en) * 2022-07-12 2023-11-17 珠海格力电器股份有限公司 Reciprocating piston compressor and refrigerator

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0629527B2 (en) * 1987-05-29 1994-04-20 川崎重工業株式会社 Lubricator for vertical axis engine
IT245317Y1 (en) * 1998-07-01 2002-03-20 Zanussi Elettromecc PERFECTED HERMETIC MOTOR-COMPRESSOR GROUP
JP4759862B2 (en) * 2001-07-16 2011-08-31 パナソニック株式会社 Hermetic electric compressor

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007292019A (en) * 2006-04-27 2007-11-08 Matsushita Electric Ind Co Ltd Hermetic compressor
EP4006343A1 (en) 2020-11-27 2022-06-01 LG Electronics Inc. Hermetic compressor
KR20220075122A (en) 2020-11-27 2022-06-07 엘지전자 주식회사 Hermetic compressor
KR102461070B1 (en) 2020-11-27 2022-11-01 엘지전자 주식회사 Hermetic compressor

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