JP2014206149A5

JP2014206149A5 -

Info

Publication number: JP2014206149A5
Application number: JP2013085688A
Authority: JP
Filing date: 2013-04-16
Publication date: 2015-10-29

Description

回転軸にかかる荷重は、主に、冷媒圧力による荷重すなわち圧縮室の吸入側圧縮室と吐出側圧縮室の圧力差による圧縮荷重と、回転軸および電動機要素の回転子の回転に伴う遠心力による荷重である。回転軸が一周するうち、圧縮荷重を受けるのは、吸入側圧縮室のある特定の範囲であり、ベーンの位置を起点（０°）として偏心軸部が１８０°回動する位置までの範囲、すなわち０°〜１８０°の範囲である。これに対し、遠心力の荷重の方向は、回転軸と、回転軸に連結された回転子の偏心荷重方向によって決定され、回転子側の偏心荷重は、一般にバランスウェイトで吸収されるようになっている。また、回転軸の偏心荷重の方向は、回転軸の偏心軸部の偏心方向であり、回転軸側から見ればほぼ一定であり、回転軸の回転に追随し回転する。 Load applied to the rotating shaft is primarily due to the centrifugal force caused by rotation of the rotor of the compressive load due to the pressure difference between the load i.e. the discharge side compression chamber and the suction side compression chamber of the compression chamber by the refrigerant pressure, the rotation shaft and the electric motor element It is a load. While the rotation shaft makes one round, the compression load is received in a specific range of the suction side compression chamber, and the range from the vane position to the starting point (0 °) to the position where the eccentric shaft portion rotates 180 °, That is, it is in the range of 0 ° to 180 °. On the other hand, the direction of centrifugal force load is determined by the rotating shaft and the eccentric load direction of the rotor connected to the rotating shaft, and the eccentric load on the rotor side is generally absorbed by the balance weight. ing. The direction of the eccentric load of the rotating shaft is the eccentric direction of the eccentric shaft portion of the rotating shaft, and is substantially constant when viewed from the rotating shaft side, and rotates following the rotation of the rotating shaft.

本発明に係るロータリー式密閉型圧縮機は、密閉容器内に電動要素と、電動要素に回転軸で連結された圧縮要素とを収納し、圧縮要素は、回転軸上に一体化された偏芯軸部と、偏芯軸部が挿入されるリング状のシリンダーと、偏心軸部に勘合しシリンダーに収納されるローリングピストンと、回転軸を支持し、シリンダーの軸方向両端の開口を閉塞する主軸受および副軸受とを備え、冷媒圧力による荷重を支持しない主軸受の内周面の部位と、遠心力による荷重を支持しない回転軸の外周面の部位とに、それぞれ給油溝を設けたものである。 Rotary hermetic compressor according to the present invention, houses a motor element in a sealed container, a compression element coupled with the rotary shaft electrodeposition dynamic elements, compression elements, integrated on the rotating shaft polarized a core shaft portion, and a ring-shaped cylinder eccentric shaft portion is inserted, a rolling piston which is accommodated in and fitted to the eccentric shaft part cylinder, supports the rotary shaft, the opening of the axial ends of the cylinder closed fort The main bearing and the sub-bearing are provided , and oil supply grooves are provided respectively on the inner peripheral surface portion of the main bearing that does not support the load due to the refrigerant pressure and on the outer peripheral surface portion of the rotary shaft that does not support the load due to the centrifugal force . Is.

本発明に係るロータリー式密閉型圧縮機においては、冷媒圧力による荷重を支持しない主軸受の内周面の部位と、遠心力による荷重を支持しない回転軸の外周面の部位とに、それぞれ給油溝を設けたので、荷重を受ける方向には給油溝が形成されない。このため、油膜が途切れることがなく、信頼性が向上する。 In a rotary hermetic compressor assembly according to the present invention, a portion of the inner peripheral surface of the main bearing which does not support the load by the refrigerant pressure, to the region of the outer circumferential surface of the rotary shaft, not supporting a load by centrifugal force, respectively oil groove Therefore, the oil supply groove is not formed in the direction of receiving the load. For this reason, the oil film is not interrupted and the reliability is improved.

Claims

An electric element in a sealed container, a compression element coupled with the rotating shaft before Symbol electromotive element housed,
The compression element is
An eccentric shaft integrated on the rotating shaft;
A ring-shaped cylinder into which the eccentric shaft portion is inserted;
A rolling piston that fits into the eccentric shaft and is housed in the cylinder;
Supporting the rotary shaft, the opening of the axial ends of said cylinder and a main bearing and a sub-bearing is closed infarction,
And the site of the inner peripheral surface of said main bearing which does not support the load by the refrigerant pressure, to the region of the outer circumferential surface of the rotary shaft, not supporting a load by centrifugal force, a rotary sealing, characterized in that a respective oil supply groove Mold compressor.

The oil supply groove in the portion of the inner peripheral surface of the main bearing that does not support the load due to the refrigerant pressure is disposed below the sliding portion between the rotating shaft and the main bearing, and the rotation that does not support the load due to the centrifugal force The oil supply groove in the portion of the outer peripheral surface of the shaft is disposed at the upper part of the sliding portion between the rotating shaft and the main bearing,
Rotary hermetic compressor according to claim 1, wherein the main bearing side of the oil supply groove and the oil supply groove and an annular groove connecting the said rotation shaft side is kicked set on the outer circumferential surface of the rotary shaft.

The oil supply groove in the portion of the inner peripheral surface of the main bearing that does not support the load due to the refrigerant pressure is disposed below the sliding portion between the rotating shaft and the main bearing, and the rotation that does not support the load due to the centrifugal force The oil supply groove in the portion of the outer peripheral surface of the shaft is disposed at the upper part of the sliding portion between the rotating shaft and the main bearing,
Rotary hermetic compressor according to claim 1, wherein the main bearing side of the oil supply groove and the oil supply groove and an annular groove connecting the said rotation shaft side is kicked set on the inner peripheral surface of said main bearing .

The oil supply groove in the portion of the inner peripheral surface of the main bearing that does not support the load due to the refrigerant pressure is disposed below the sliding portion between the rotating shaft and the main bearing, and the rotation that does not support the load due to the centrifugal force The oil supply groove in the portion of the outer peripheral surface of the shaft is disposed at the upper part of the sliding portion between the rotating shaft and the main bearing,
An outer peripheral surface of the rotary shaft portion serving as between the main bearing side of the oil supply groove and the oil supply groove of the rotary shaft side, a stepped portion serving as a relief for forming the oil supply groove on the rotary shaft set vignetting The rotary hermetic compressor according to claim 1, wherein

The oil supply groove in the portion of the inner peripheral surface of the main bearing that does not support the load due to the refrigerant pressure is disposed below the sliding portion between the rotating shaft and the main bearing, and the rotation that does not support the load due to the centrifugal force The oil supply groove in the portion of the outer peripheral surface of the shaft is disposed at the upper part of the sliding portion between the rotating shaft and the main bearing,
An inner peripheral surface of the main bearing portion to be between the main bearing side of the oil supply groove and the oil supply groove of the rotary shaft side, a stepped portion serving as a relief for forming the oil supply groove to the main bearing is set 2. The rotary hermetic compressor according to claim 1, wherein the rotary hermetic compressor is provided.

A vane is provided which is slidably inserted into the cylinder and has one end abutting on the outer peripheral surface of the rolling piston and defining the inside of the cylinder into a suction side compression chamber and a discharge side compression chamber. The rotary hermetic compressor according to any one of claims 1 to 5.