JPH0988857A - Lubricating device of horizontal hermetic compressor - Google Patents

Lubricating device of horizontal hermetic compressor

Info

Publication number
JPH0988857A
JPH0988857A JP24927995A JP24927995A JPH0988857A JP H0988857 A JPH0988857 A JP H0988857A JP 24927995 A JP24927995 A JP 24927995A JP 24927995 A JP24927995 A JP 24927995A JP H0988857 A JPH0988857 A JP H0988857A
Authority
JP
Japan
Prior art keywords
oil
oil tank
compressor
pressure
compression
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP24927995A
Other languages
Japanese (ja)
Inventor
Katsumi Hirooka
勝実 広岡
Original Assignee
Mitsubishi Heavy Ind Ltd
三菱重工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Ind Ltd, 三菱重工業株式会社 filed Critical Mitsubishi Heavy Ind Ltd
Priority to JP24927995A priority Critical patent/JPH0988857A/en
Publication of JPH0988857A publication Critical patent/JPH0988857A/en
Pending legal-status Critical Current

Links

Abstract

PROBLEM TO BE SOLVED: To feed the lubricating oil to the prescribed part to be lubricated without delay in starting a compressor by providing an oil feeding passage to directly connect an oil tank to a sliding part or a rolling part of a compression mechanism in a horizontal compressor provided with an enclosed housing in which the compression mechanism and a motor are and the oil tank. SOLUTION: In a horizontal enclosed compressor in which an enclosed housing 8 is connected to an oil tank 9 by a connection pipe 92, when the compressor is stopped for a long time or after the reversing operation of the liquid, a large volume of the refrigerant is dissolved in the lubricating oil in the oil tank 9. When the compressor is started in this condition, the pressure in the oil tank is also dropped due to the pressure drop in the enclosed housing 8. The foaming phenomenon that the refrigerant dissolved in the lubricating oil is foamed and boils occurs, and the pressure in the oil tank 9 is increased. As a result, the differential pressure is generated between in the oil tank 9 and in the enclosed housing 8, and this differential pressure allows the lubricating oil to be lubricated on a thrust surface 65 through an oil feed pipe 57, an oil feed hole 58, and an oil groove 66.

Description

【発明の詳細な説明】Detailed Description of the Invention
【0001】[0001]
【発明の属する技術分野】本発明は空気調和機用横型密
閉圧縮機の潤滑装置に関する。
TECHNICAL FIELD The present invention relates to a lubricating device for a horizontal hermetic compressor for an air conditioner.
【0002】[0002]
【従来の技術】図3には、従来の横型スクロール圧縮機
の縦断面図が示されている。図において、密閉ハウジン
グ8の内部はディスチャージカバー31によって高圧側
44と低圧側45とに仕切られている。低圧側45の内
部には、その前方にスクロール型圧縮機構Cが、後方に
電動モータMが配設され、これらは回転軸5を介して互
いに連動連結されている。上記電動モータMはロータM
aとステータMbとからなり、ロータMaは上記回転軸
5に固定され、ステータMbは上記密閉ハウジング8に
固定されている。
2. Description of the Related Art FIG. 3 is a vertical sectional view of a conventional horizontal scroll compressor. In the figure, the inside of the closed housing 8 is partitioned by a discharge cover 31 into a high-voltage side 44 and a low-voltage side 45. Inside the low-pressure side 45, a scroll-type compression mechanism C is arranged in front of the low-pressure side 45, and an electric motor M is arranged in the rear thereof, which are interlockingly connected to each other via a rotary shaft 5. The electric motor M is a rotor M
The rotor Ma is fixed to the rotating shaft 5, and the stator Mb is fixed to the hermetic housing 8.
【0003】上記スクロール型圧縮機構Cは、固定スク
ロール1、旋回スクロール2、同旋回スクロール2の公
転旋回運動を許容し、かつその自転を阻止するオルダム
リンク等の自転阻止機構3、上記固定スクロール1及び
電動モータMが締結されるフレーム6、回転軸5を軸支
する前部軸受71及び後部軸受72等からなる。
The scroll type compression mechanism C allows a fixed scroll 1, an orbiting scroll 2 and a revolving orbiting motion of the orbiting scroll 2 and prevents its rotation from rotating, such as an Oldham link, and the fixed scroll 1. And a frame 6 to which the electric motor M is fastened, a front bearing 71 and a rear bearing 72 that pivotally support the rotary shaft 5, and the like.
【0004】上記固定スクロール1は、端板11とその
内面に立設された渦巻き状ラップ12とを備え、この端
板11の中央部には吐出ポート13が設けられている。
上記旋回スクロール2は、端板21とこれの内面に立設
された渦巻き状ラップ22とを備え、この端板21の外
面に立設されたボス23内にドライブブッシュ54が旋
回軸受73を介して回転自在に嵌装され、このドライブ
ブッシュ54に穿設された孔55内に回転軸5の端部か
ら突出する偏心ピン53が回転自在に嵌合されている。
固定スクロール1と旋回スクロール2とを相互に所定距
離だけ偏心させ、かつ、180度だけ角度をずらせて噛
み合わせることによって複数個の密閉空間24が形成さ
れている。
The fixed scroll 1 has an end plate 11 and a spiral wrap 12 provided upright on the inner surface of the end plate 11, and a discharge port 13 is provided at the center of the end plate 11.
The orbiting scroll 2 is provided with an end plate 21 and a spiral wrap 22 which is erected on the inner surface of the end plate 21, and a drive bush 54 is disposed in a boss 23 which is erected on the outer surface of the end plate 21 via a orbiting bearing 73. An eccentric pin 53 protruding from the end of the rotary shaft 5 is rotatably fitted in a hole 55 formed in the drive bush 54.
A plurality of closed spaces 24 are formed by eccentric the fixed scroll 1 and the orbiting scroll 2 with respect to each other by a predetermined distance and engaging them with each other while shifting the angle by 180 degrees.
【0005】上記フレーム6は密閉ハウジング8に固定
されており、このフレーム6の前面に形成されたスラス
ト面65と旋回スクロール2の背面とが摺接して運転中
に密閉空間24の内圧によって生ずる旋回スクロール2
のスラスト荷重を支持している。また、上記スラスト面
65には油溝66が穿設されている。
The frame 6 is fixed to a hermetically sealed housing 8, and a thrust surface 65 formed on the front surface of the frame 6 and a back surface of the orbiting scroll 2 are in sliding contact with each other to cause a swirl caused by the internal pressure of the hermetically sealed space 24 during operation. Scroll 2
It supports the thrust load of. Further, an oil groove 66 is formed in the thrust surface 65.
【0006】また、上記密閉ハウジング8の下側外部に
は油タンク9が横置きに設置されている。そして同油タ
ンク9内は連結管92によって密閉ハウジング8内と連
通されている。上記回転軸5の後端部には容積型の油ポ
ンプ51が装着されている。同油ポンプ51の吸入口
(図示しない)には吸込管56が接続されており、同吸
入管56の先端は油タンク9内に開口している。また、
同ポンプ51の吐出口(図示しない)は回転軸5に穿設
された給油孔52に連通されている。
An oil tank 9 is horizontally installed outside the lower side of the closed housing 8. The inside of the oil tank 9 is communicated with the inside of the closed housing 8 by a connecting pipe 92. A positive displacement oil pump 51 is attached to the rear end of the rotary shaft 5. A suction pipe 56 is connected to a suction port (not shown) of the oil pump 51, and a tip of the suction pipe 56 is open in the oil tank 9. Also,
A discharge port (not shown) of the pump 51 is communicated with an oil supply hole 52 formed in the rotary shaft 5.
【0007】上記電動モータMを回転駆動すると、回転
軸5、偏心ピン53、ドライブブッシュ54、ボス23
等からなる公転旋回機構を介して旋回スクロール2が駆
動され、同旋回スクロール2は自転阻止機構3によって
自転を阻止されながら公転旋回半径の円軌道上を公転旋
回運動される。すると、冷媒ガスが吸入管82を経て低
圧側45に入り、このガスは通路61を通って低圧室4
3を経た後密閉空間24内に吸入される。そして、旋回
スクロール2の公転旋回運動により密閉空間24の容積
が減少するのに伴って、圧縮されながら中央部に至り、
吐出ポート13より逆止弁17を押し開いて高圧室42
から高圧側44に入り、ここから吐出管83を経て外部
に吐出される。
When the electric motor M is driven to rotate, the rotary shaft 5, the eccentric pin 53, the drive bush 54, and the boss 23.
The orbiting scroll 2 is driven via a revolving orbiting mechanism composed of, for example, and the orbiting scroll 2 is revolved on a circular orbit having a revolution revolving radius while being prevented from rotating by a rotation inhibiting mechanism 3. Then, the refrigerant gas enters the low-pressure side 45 through the suction pipe 82, and this gas passes through the passage 61 and enters the low-pressure chamber 4.
After 3 times, it is sucked into the closed space 24. Then, as the volume of the sealed space 24 decreases due to the orbiting motion of the orbiting scroll 2, it reaches the central portion while being compressed,
The check valve 17 is pushed open from the discharge port 13 and the high pressure chamber 42 is opened.
To the high pressure side 44, and is discharged to the outside through the discharge pipe 83.
【0008】これと同時に油ポンプ51が駆動され、油
タンク9内に貯留された潤滑油は吸込管56を通って吸
い上げられ、同油ポンプ51によって付勢されて給油孔
52に吐出される。さらにこの潤滑油は給油孔52内を
前方へ流れた後、途中で分流し後部軸受72、前部軸受
71を潤滑する一方、その主流は偏心ピン53先端の給
油孔52開口から噴出され、偏心ピン53、旋回軸受7
3を潤滑して旋回スクロール2とフレーム6との間に形
成された油溜め室63に入る。
At the same time, the oil pump 51 is driven, the lubricating oil stored in the oil tank 9 is sucked up through the suction pipe 56, is urged by the oil pump 51, and is discharged to the oil supply hole 52. Further, this lubricating oil flows forward in the oil supply hole 52 and then splits midway to lubricate the rear bearing 72 and the front bearing 71, while the main stream is ejected from the opening of the oil supply hole 52 at the tip of the eccentric pin 53, and eccentric. Pin 53, slewing bearing 7
3 is lubricated and enters the oil sump chamber 63 formed between the orbiting scroll 2 and the frame 6.
【0009】さらにこの潤滑油は油溝66を通ってスラ
スト面65、自転阻止機構3等の摺動部を潤滑する。ま
た上記油溜め室63に入った潤滑油の一部は排油孔62
から密閉ハウジング8内底部に滴下する。そして密閉ハ
ウジング8内底部に滴下した潤滑油は連結管92を通っ
て油タンク9内に入りここに貯留される。
Further, the lubricating oil passes through the oil groove 66 and lubricates the sliding portions such as the thrust surface 65 and the rotation preventing mechanism 3. Further, part of the lubricating oil that has entered the oil sump chamber 63 is part of the oil drain hole 62.
To the bottom of the closed housing 8. Then, the lubricating oil dripping on the inner bottom portion of the closed housing 8 passes through the connecting pipe 92 and enters the oil tank 9 where it is stored.
【0010】[0010]
【発明が解決しようとする課題】上記従来の横型密閉圧
縮機においては圧縮機の起動時に、油ポンプ51からの
距離が遠い摺動部、即ち旋回スクロール2の背面とフレ
ーム6前面のスラスト面65との摺動部等への給油に遅
れが生ずる。通常の運転状態における起動時において
は、かかる給油遅れがあっても特段の不具合は発生しな
い。しかしながら、圧縮機の停止期間が長期になったと
きや、液バック運転後の停止時には上記スラスト面65
は冷媒によって油膜が洗い落されて完全なドライ状態に
なり、給油遅れに対し厳しい潤滑状態となっている。
In the above-mentioned conventional horizontal hermetic compressor, when the compressor is started, the sliding portion which is far from the oil pump 51, that is, the thrust face 65 on the rear face of the orbiting scroll 2 and the front face of the frame 6 is used. There will be a delay in the lubrication of the sliding parts such as. At the time of start-up in a normal operating state, no particular trouble occurs even if there is such a delay in refueling. However, when the compressor is stopped for a long period, or when the compressor is stopped after the liquid back operation, the thrust surface 65 is
The oil film is washed off by the refrigerant and becomes a completely dry state, which is a severe lubrication state against a delay in refueling.
【0011】その上、油タンク9内の潤滑油中には多量
の冷媒が溶け込んでいることから、圧縮機の起動時に、
油ポンプ51は発泡した冷媒ガスを吸い込む。このた
め、油ポンプ51のポンプ能力が低下し、上記のような
給油遅れが一層長くなる。
Moreover, since a large amount of refrigerant is dissolved in the lubricating oil in the oil tank 9, when the compressor is started,
The oil pump 51 sucks the foamed refrigerant gas. For this reason, the pumping capacity of the oil pump 51 is reduced, and the above-mentioned oil supply delay becomes longer.
【0012】上記のように、図3に示される従来の圧縮
機にあっては、長期間停止後や液バック運転停止後の再
起動時には、圧縮機構C内の摺動部、特にスラスト面6
5に給油遅れから焼き付きが発生するという問題点を抱
えている。
As described above, in the conventional compressor shown in FIG. 3, when the compressor is restarted after being stopped for a long time or after stopping the liquid back operation, the sliding portion in the compression mechanism C, especially the thrust surface 6
5 has a problem that seizure occurs due to delay in refueling.
【0013】本発明の目的は、圧縮機の起動時に遅滞な
く潤滑油を所要潤滑部に送給することにより、特に潤滑
油中に多量の冷媒が溶け込んでいる場合においても給油
遅れを最少限に短縮して摺動部、転動部の焼付き等の事
故の発生を防止することである。
An object of the present invention is to supply lubricating oil to a required lubrication section without delay at the time of starting the compressor, thereby minimizing the oil supply delay even when a large amount of refrigerant is dissolved in the lubricating oil. Shorten the length to prevent accidents such as seizure of sliding parts and rolling parts.
【0014】[0014]
【課題を解決するための手段】本発明は上記問題点を解
決するもので、その要旨とする第1の手段は、横置きの
密閉ハウジング内に、圧縮機構及び同圧縮機構に略水平
に配置された回転軸を介して連結される圧縮機構駆動用
のモータを収納し、上記回転軸により駆動される油ポン
プと、上記密閉ハウジングの下方に設置され上記油ポン
プの吸込口と吸込管を介して連通されるとともに上記密
閉ハウジング内と連結管を介して連通される油タンクと
を備えた横型圧縮機の潤滑装置において、上記油タンク
と上記圧縮機構の摺動部あるいは転動部とを直接接続す
る給油通路を設けたことにある。
DISCLOSURE OF THE INVENTION The present invention is to solve the above-mentioned problems, and the first means, which is the gist of the present invention, is to arrange a compression mechanism and a substantially horizontal position in the compression mechanism in a horizontally sealed housing. A motor for driving a compression mechanism, which is connected via a rotary shaft, is housed, and an oil pump driven by the rotary shaft, and a suction port and a suction pipe of the oil pump installed below the hermetically sealed housing are installed. In a lubrication device for a horizontal compressor having an oil tank communicated with the inside of the hermetic housing through a connecting pipe, the oil tank and the sliding portion or rolling portion of the compression mechanism are directly connected to each other. This is because the oil supply passage to be connected is provided.
【0015】上記手段によれば圧縮機の起動時、密閉ハ
ウジング内の圧力が降下し、これにつれて油タンク内の
圧力が降下すると、長期間停止後や液バック運転後の停
止後の起動の場合には、油タンク中の潤滑油中に多量の
冷媒が溶け込んでいるので、この冷媒が泡状となって沸
騰する発泡現象(フォーミング現象)が発生し、油タン
ク内の圧力が上昇する。
According to the above means, when the compressor starts, the pressure in the hermetically sealed housing drops, and the pressure in the oil tank drops accordingly. In the case of starting after the stop for a long period of time or after the stop after the liquid back operation. Since a large amount of the refrigerant is dissolved in the lubricating oil in the oil tank, a foaming phenomenon (foaming phenomenon) in which the refrigerant becomes a bubble and boil occurs, and the pressure in the oil tank rises.
【0016】この結果、油タンク内の圧力と密閉ハウジ
ング内の圧力との間に圧力差が生じる。この圧力差によ
って油タンク内の潤滑油は同油タンクと密閉ハウジング
とを直接接続する給油通路を通って圧縮機構内の摺動部
及び転動部に迅速に送り込まれることとなり、従来のも
ののような起動時の給油遅れの発生は無い。
As a result, a pressure difference occurs between the pressure inside the oil tank and the pressure inside the closed housing. Due to this pressure difference, the lubricating oil in the oil tank is quickly sent to the sliding parts and rolling parts in the compression mechanism through the oil supply passage that directly connects the oil tank and the closed housing. There is no delay in refueling at startup.
【0017】また、本発明の第2の手段は、上記第1の
手段において上記連結管内に上記密閉ハウジング内の圧
力が一定圧力よりも降下したとき、上記連結管路を遮断
する逆止弁機構を設けたことにある。
The second means of the present invention is the check valve mechanism according to the first means, which shuts off the connecting pipe when the pressure in the closed housing in the connecting pipe falls below a certain pressure. Has been established.
【0018】上記手段によれば、圧縮機の起動時におい
て密閉ハウジング内の圧力が降下し、これによって逆止
弁機構が閉じ、油タンク内の圧力と密閉ハウジング内の
圧力との間に圧力差が生ずる。この圧力差によって上記
第1の手段と同様に油タンク内の潤滑油は給油通路を通
って直接圧縮機構内の摺動部に強制的に送り込まれる。
これと同時に、上記圧力差によって油タンク内の潤滑油
は吸込管を通って油ポンプ内に強制的に送り込まれる。
According to the above means, when the compressor is started, the pressure in the hermetically-closed housing is lowered, whereby the check valve mechanism is closed, and the pressure difference between the pressure in the oil tank and the pressure in the hermetically-sealed housing is reduced. Occurs. Due to this pressure difference, the lubricating oil in the oil tank is forcibly sent directly to the sliding portion in the compression mechanism through the oil supply passage as in the case of the first means.
At the same time, the pressure difference causes the lubricating oil in the oil tank to be forced into the oil pump through the suction pipe.
【0019】この場合は、逆止弁機構により強制的に上
記圧力差を生ぜしめるので、上記第1の手段よりもさら
に迅速かつ確実に給油を行うことができる。尚、上記逆
止弁機構は、好ましくは球状の弁体からなる球形弁型式
とする。これにより、逆止弁機構の構造が簡単かつコン
パクトになる。
In this case, since the check valve mechanism forcibly causes the pressure difference, the fuel can be supplied more quickly and reliably than the first means. The check valve mechanism is preferably a spherical valve type including a spherical valve body. This makes the structure of the check valve mechanism simple and compact.
【0020】[0020]
【発明の実施の形態】以下図面を参照して本発明の実施
形態について詳細に説明する。図1には本発明の実施形
態に係る空気調和装置用横型密閉圧縮機の断面図が示さ
れている。
BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the drawings. FIG. 1 shows a cross-sectional view of a horizontal hermetic compressor for an air conditioner according to an embodiment of the present invention.
【0021】図1において、Cはスクロール型圧縮機
構、1は同圧縮機構Cの固定スクロール、2は旋回スク
ロール、3は自転阻止機構である。Mは圧縮機構C駆動
用の電動モータ、5は上記圧縮機構Cと電動モータMと
を連結する回転軸、8は密閉ハウジング、6はフレーム
である。
In FIG. 1, C is a scroll type compression mechanism, 1 is a fixed scroll of the compression mechanism C, 2 is an orbiting scroll, and 3 is a rotation preventing mechanism. M is an electric motor for driving the compression mechanism C, 5 is a rotary shaft that connects the compression mechanism C and the electric motor M, 8 is a hermetic housing, and 6 is a frame.
【0022】51は上記回転軸5の軸端部に装備された
油ポンプ、9は潤滑油タンク、56は上記油ポンプ51
の吸込口と潤滑油タンク9とを接続する吸込管である。
92は密閉ハウジング8の下部と油タンク9とを接続す
る連結管である。66は上記フレーム6の端面即ちスラ
スト面65の旋回スクロール2と摺接する部位に刻設さ
れた油溝である。
Reference numeral 51 is an oil pump mounted on the shaft end of the rotary shaft 5, 9 is a lubricating oil tank, and 56 is the oil pump 51.
Is a suction pipe that connects the suction port of and the lubricating oil tank 9.
Reference numeral 92 is a connecting pipe that connects the lower portion of the closed housing 8 and the oil tank 9. Reference numeral 66 denotes an oil groove formed on the end surface of the frame 6, that is, the thrust surface 65, which is in sliding contact with the orbiting scroll 2.
【0023】58はフレーム6に穿設された給油孔であ
り、その一端は、フレーム6の前面に形成された上記ス
ラスト面65に刻設された油溝66部に開口され、他端
は密閉ハウジング8の外側に延長されて、油タンク9に
追設された給油管57に接続されている。同給油管57
の他端は油タンク9内に開口されている。
Reference numeral 58 is an oil supply hole formed in the frame 6, one end of which is opened in an oil groove 66 formed in the thrust surface 65 formed on the front surface of the frame 6, and the other end is hermetically sealed. It is extended to the outside of the housing 8 and is connected to an oil supply pipe 57 additionally provided in the oil tank 9. Same refueling pipe 57
The other end of is open in the oil tank 9.
【0024】その他の構成は図3に示される従来のもの
と同様であり、これと同一の部材には同一の符号を附し
て示す。
The other structure is the same as that of the conventional one shown in FIG. 3, and the same members as those shown in FIG.
【0025】上記のように構成された圧縮機において、
長期間停止時や液バック運転後の停止時には油タンク9
内の潤滑油中には多量の冷媒が溶け込んでいるが、この
状態で圧縮機Cを起動すると密閉ハウジング8内の圧力
降下により、同ハウジング8に連通された油タンク9内
の圧力も降下する。これにより、潤滑油中に溶け込んだ
冷媒が泡状になって沸騰する所謂発泡現象(フォーミン
グ現象)が生じ、油タンク9内圧力が上昇する。この結
果、油タンク9内と密閉ハウジング8内とに圧力差が生
じ、この圧力差によって油タンク9内の潤滑油は給油管
57、給油孔58を通り、油溝66を経てスラスト面6
5に送り込まれ、これを潤滑する。このように、長期間
停止時、液バック停止時等の潤滑油中に多量の冷媒が溶
け込んだ状態からの起動時においても、スラスト面65
には充分な量の潤滑油が迅速に供給されることとなり、
焼付きの発生が防止される。
In the compressor configured as described above,
Oil tank 9 when stopped for a long time or after a liquid back operation
A large amount of refrigerant is dissolved in the lubricating oil inside, but when the compressor C is started in this state, the pressure in the sealed housing 8 drops, so that the pressure in the oil tank 9 communicating with the housing 8 also drops. . As a result, a so-called foaming phenomenon (foaming phenomenon) occurs in which the refrigerant dissolved in the lubricating oil becomes a bubble and boils, and the internal pressure of the oil tank 9 rises. As a result, a pressure difference is generated between the inside of the oil tank 9 and the inside of the closed housing 8, and this pressure difference causes the lubricating oil in the oil tank 9 to pass through the oil supply pipe 57, the oil supply hole 58, the oil groove 66, and the thrust surface 6
It is sent to No. 5, and it is lubricated. As described above, even when the engine is started from a state in which a large amount of the refrigerant is dissolved in the lubricating oil, such as when the liquid is stopped for a long period of time or when the liquid bag is stopped, the thrust surface 65 is
Will be quickly supplied with a sufficient amount of lubricating oil,
The occurrence of seizure is prevented.
【0026】図2には本発明の実施の第2形態が示され
ている。この実施形態においては、密閉ハウジング8と
油タンク9との油戻し用の連結管92に逆止弁機構10
0が設けられている。
FIG. 2 shows a second embodiment of the present invention. In this embodiment, the check valve mechanism 10 is attached to the connecting pipe 92 for returning the oil between the closed housing 8 and the oil tank 9.
0 is provided.
【0027】即ち図2において、上記逆止弁機構100
は、弁座102と多数の透孔が穿設されたリテーナ10
3との間の弁室106内に球状の弁体101を挿入して
構成され、上記連結管92の密閉ハウジング8側開口部
近傍に設けられている。尚、上記逆止弁機構100は連
結管路92中の任意の部位に装備できる。上記の構成以
外は図1に示される第1形態と同一である。
That is, referring to FIG. 2, the check valve mechanism 100 is shown.
Is a retainer 10 having a valve seat 102 and a large number of through holes.
3 is formed by inserting the spherical valve element 101 into the valve chamber 106 between the valve chamber 3 and the valve chamber 106, and is provided near the opening of the connecting pipe 92 on the hermetic housing 8 side. It should be noted that the check valve mechanism 100 can be installed in any portion of the connecting conduit 92. Except for the above configuration, it is the same as the first embodiment shown in FIG.
【0028】図2に示される逆止弁機構100を備えた
圧縮機Cを長時間停止した後、これを起動すると、油ポ
ンプ51が回転するとともに、密閉ハウジング8内のガ
スが圧縮機構Cの密閉空間24内に吸入されるので、密
閉ハウジング8内の圧力は下降し始める。
When the compressor C having the check valve mechanism 100 shown in FIG. 2 is stopped for a long time and then started, the oil pump 51 is rotated and the gas in the hermetic housing 8 is compressed by the compression mechanism C. Since the air is sucked into the closed space 24, the pressure in the closed housing 8 starts to drop.
【0029】一方、油タンク9内の圧力は圧縮機構Cの
停止中と変わらないため、密閉ハウジング8内の圧力と
油タンク9内の圧力との間に圧力差が生じる。この圧力
差により、油タンク9内のガスが連結管92内を通って
密閉ハウジング8内に逆流し、このガス流れによって逆
止弁機構100の弁体101が持ち上げられて弁座10
2のガス通路104を閉止する。これによって、密閉ハ
ウジング8内の圧力と油タンク9内の圧力との圧力差が
増大し、この圧力差によって油タンク9内の潤滑油は給
油管57及び給油孔58を通り、さらに油溝66を経て
スラスト面65に送り込まれる。
On the other hand, since the pressure in the oil tank 9 is the same as when the compression mechanism C is stopped, there is a pressure difference between the pressure in the closed housing 8 and the pressure in the oil tank 9. Due to this pressure difference, the gas in the oil tank 9 flows back into the closed housing 8 through the inside of the connecting pipe 92, and the valve body 101 of the check valve mechanism 100 is lifted by this gas flow and the valve seat 10 is opened.
The second gas passage 104 is closed. As a result, the pressure difference between the pressure in the closed housing 8 and the pressure in the oil tank 9 increases, and the pressure difference causes the lubricating oil in the oil tank 9 to pass through the oil supply pipe 57 and the oil supply hole 58 and further to the oil groove 66. Then, it is sent to the thrust surface 65 via.
【0030】図1に示される第1形態においては、密閉
ハウジング8内と油タンク9内の間で自然に発生する圧
力差によってスラスト面65に給油したが、この実施形
態においては、起動時に上記の作用によって連結管を閉
塞し、強制的に上記圧力差を生ぜしめるので、第1形態
よりもさらに迅速かつ確実に給油を行うことができる。
In the first embodiment shown in FIG. 1, the thrust surface 65 is refueled by the pressure difference that naturally occurs between the closed housing 8 and the oil tank 9. By the action of the above, the connecting pipe is closed and the pressure difference is forcibly produced, so that the fuel can be supplied more quickly and surely than in the first embodiment.
【0031】上記逆止弁機構100は、上記の他に次の
ような油ポンプの能力低下防止作用をなす。即ち、上記
油タンク9と密閉ハウジング8との圧力差によって、油
タンク9内に貯留されている潤滑油はこの中に多量の冷
媒が溶け込んでいても、吸込管56を通って油ポンプ5
1内に強制的に送り込まれ、油ポンプ51によって付勢
されて所要潤滑個所に供給される。従って、起動時にお
いても油ポンプ51は確実に作動し、能力の低下は無
い。
In addition to the above, the check valve mechanism 100 has the following function of preventing the deterioration of the capacity of the oil pump. That is, due to the pressure difference between the oil tank 9 and the closed housing 8, the lubricating oil stored in the oil tank 9 passes through the suction pipe 56 and the oil pump 5 even if a large amount of refrigerant is dissolved therein.
It is forcibly sent into the inside of No. 1 and is urged by the oil pump 51 to be supplied to the required lubrication point. Therefore, the oil pump 51 operates reliably even at the time of start-up, and there is no reduction in capacity.
【0032】さらに、油タンク9内の潤滑油の量が少な
くなることによって、その内部の圧力が低下すると、逆
止弁機構100の弁体101はその自重によって落下し
てガス通路104を開き、リテーナ103上に保持され
る。これによって密閉ハウジング8内の底部に滴下した
潤滑油が逆止弁機構100の弁座102の連通口10
4、リテーナ103の多数の穴105を通り、連結管9
2を経て油タンク9内に入り、この内部に貯留される。
Further, when the internal pressure of the oil tank 9 decreases due to the decrease in the amount of lubricating oil in the oil tank 9, the valve body 101 of the check valve mechanism 100 falls by its own weight and opens the gas passage 104, It is held on the retainer 103. As a result, the lubricating oil that has dripped at the bottom of the closed housing 8 will not allow the communication port 10 of the valve seat 102 of the check valve mechanism 100.
4, passing through many holes 105 of retainer 103, connecting pipe 9
After passing through 2, the oil enters the oil tank 9 and is stored therein.
【0033】[0033]
【発明の効果】本発明は以上のように構成されており、
請求項1の発明によれば、圧縮機の起動時において、油
タンク内の潤滑油中に溶け込んだ冷媒の発泡現象(フォ
ーミング現象)の発生に伴う油タンク内の圧力上昇によ
って、油タンク内と密閉ハウジング内との間に圧力差が
生じ、これによって油タンク内の潤滑油は給油通路を通
って直接圧縮機構内の摺動部及び転動部に送り込まれ
る。
The present invention is configured as described above.
According to the first aspect of the present invention, when the compressor is activated, the pressure in the oil tank increases due to the pressure increase in the oil tank caused by the foaming phenomenon (forming phenomenon) of the refrigerant dissolved in the lubricating oil in the oil tank. A pressure difference is generated between the inside of the closed housing and the lubricating oil in the oil tank is directly sent to the sliding portion and the rolling portion in the compression mechanism through the oil supply passage.
【0034】この結果、圧縮機の長期間停止後や液バッ
ク運転後の停止後等冷媒によってスラスト面その他圧縮
機構内の摺動部、転動部の油膜が洗い落されて完全なド
ライ状態になっていても、圧縮機の起動時、迅速に潤滑
油を上記摺動部及び転動部に送り込むことができるの
で、焼き付き等の事故を未然に防止することができる。
As a result, after the compressor has been stopped for a long period of time or after stopping after the liquid back operation, the thrust surface and other oil films on the sliding parts and rolling parts in the compression mechanism are washed off by the refrigerant to be completely dry. Even if it is, the lubricating oil can be quickly sent to the sliding portion and the rolling portion when the compressor is started, so that an accident such as seizure can be prevented.
【0035】また、請求項2の発明によれば、圧縮機の
起動時において、逆止弁機構が閉じることにより生ずる
油タンク内と密閉ハウジング内の間の圧力差によって油
タンク内の潤滑油は給油通路を通って直接圧縮機構の摺
動部及び転動部に送り込まれると同時に、上記圧力差に
よって吸込管を通って油ポンプ内へも強制的に送り込ま
れる。上記圧力差は、逆止弁機構で連結管を閉止するこ
とにより強制的に発生せしめられているため、請求項1
の場合よりも大きな圧力差を得ることができ、さらに確
実かつ迅速な給油が実現できる。
Further, according to the second aspect of the present invention, when the compressor is started, the pressure difference between the oil tank inside and the closed housing caused by the closing of the check valve mechanism prevents the lubricating oil inside the oil tank. At the same time as being sent directly to the sliding part and rolling part of the compression mechanism through the oil supply passage, it is forcibly sent into the oil pump through the suction pipe due to the pressure difference. The pressure difference is forcibly generated by closing the connecting pipe with a check valve mechanism.
It is possible to obtain a larger pressure difference than in the above case, and it is possible to realize reliable and quick refueling.
【0036】さらに加えて、圧縮機の長期間停止後や、
液バック運転後の停止後など潤滑油中に多量の冷媒が溶
け込んでいても、この潤滑油を油ポンプに送り込むこと
ができ、ポンプ能力の低下を防止することができる。こ
れにより、給油遅れのさらなる短縮が実現でき上記効果
を相乗的に一層確実にすることができる。
In addition, after the compressor has been stopped for a long time,
Even if a large amount of refrigerant is dissolved in the lubricating oil such as after the stop after the liquid back operation, the lubricating oil can be sent to the oil pump, and the deterioration of the pump performance can be prevented. As a result, the delay of refueling can be further shortened and the above effects can be synergistically ensured.
【図面の簡単な説明】[Brief description of drawings]
【図1】本発明の実施の第1形態に係る横型密閉圧縮機
の縦断面図。
FIG. 1 is a vertical cross-sectional view of a horizontal hermetic compressor according to a first embodiment of the present invention.
【図2】本発明の実施の第2形態の要部を示す部分断面
図。
FIG. 2 is a partial sectional view showing a main part of a second embodiment of the present invention.
【図3】従来の横型密閉圧縮機の縦断面図。FIG. 3 is a vertical sectional view of a conventional horizontal hermetic compressor.
【符号の説明】[Explanation of symbols]
C 圧縮機構 M 電動モータ 5 回転軸 8 密閉ハウジング 9 油タンク 51 油ポンプ 52 給油孔 56 吸込管 57 給油管 58 給油孔 92 連結管 100 逆止弁機構 C compression mechanism M electric motor 5 rotating shaft 8 hermetic housing 9 oil tank 51 oil pump 52 oil supply hole 56 suction pipe 57 oil supply pipe 58 oil supply hole 92 connecting pipe 100 check valve mechanism

Claims (2)

    【特許請求の範囲】[Claims]
  1. 【請求項1】 横置きの密閉ハウジング内に、圧縮機構
    及び同圧縮機構に略水平に配置された回転軸を介して連
    結される圧縮機構駆動用のモータを収納し;上記回転軸
    により駆動される油ポンプと、上記密閉ハウジングの下
    方に設置され上記ポンプの吸込口と吸込管を介して連通
    されるとともに上記密閉ハウジング内と連結管を介して
    連通される油タンクとを備えた横型圧縮機において、上
    記油タンクと上記圧縮機構の摺動部あるいは転動部とを
    直接接続する給油通路を設けたことを特徴とする横型密
    閉圧縮機の潤滑装置。
    1. A compression mechanism and a motor for driving a compression mechanism, which is connected to the compression mechanism via a rotary shaft arranged substantially horizontally, are housed in a horizontally sealed housing; and the motor is driven by the rotary shaft. Horizontal compressor provided with an oil pump, and an oil tank installed below the hermetic housing and communicating with the suction port of the pump via a suction pipe and with the interior of the hermetic housing via a connecting pipe. 3. A lubrication device for a horizontal hermetic compressor, characterized in that an oil supply passage for directly connecting the oil tank and the sliding portion or rolling portion of the compression mechanism is provided.
  2. 【請求項2】 上記連結管内に、上記密閉ハウジング内
    の圧力が一定圧力よりも降下したとき上記連結管路を遮
    断する逆止弁機構を設けた請求項1記載の横型密閉圧縮
    機の潤滑装置。
    2. The lubricating device for a horizontal hermetic compressor according to claim 1, wherein a check valve mechanism is provided in the connecting pipe to shut off the connecting pipe when the pressure in the hermetic housing falls below a certain pressure. .
JP24927995A 1995-09-27 1995-09-27 Lubricating device of horizontal hermetic compressor Pending JPH0988857A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP24927995A JPH0988857A (en) 1995-09-27 1995-09-27 Lubricating device of horizontal hermetic compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP24927995A JPH0988857A (en) 1995-09-27 1995-09-27 Lubricating device of horizontal hermetic compressor

Publications (1)

Publication Number Publication Date
JPH0988857A true JPH0988857A (en) 1997-03-31

Family

ID=17190606

Family Applications (1)

Application Number Title Priority Date Filing Date
JP24927995A Pending JPH0988857A (en) 1995-09-27 1995-09-27 Lubricating device of horizontal hermetic compressor

Country Status (1)

Country Link
JP (1) JPH0988857A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003500611A (en) * 1999-06-01 2003-01-07 エルジー エレクトロニクス インコーポレイテッド Vacuum compression prevention device for scroll compressor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003500611A (en) * 1999-06-01 2003-01-07 エルジー エレクトロニクス インコーポレイテッド Vacuum compression prevention device for scroll compressor

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