JPH08193587A - Rotary type compressor - Google Patents

Abstract

PURPOSE: To smoothly drive a sliding part such as vane and roller by supplying a lubricant directly into a compression chamber while the machine is at a standstill and supplying the lubricant directly into the compression chamber for a certain period from immediately after the start. CONSTITUTION: A lubricating oil 18 in an enclosure casing 1 is in communication with inside a suction pipe 19 via an oil supply pipe 22b, valve mechanism 20, and oil supply pipe 21, and when a compressor is started, the oil 18 gets a high pressure, and the inside of the suction pipe 19 gets a low pressure while the inside of the valve mechanism 20 a middle pressure. By this pressure difference, the oil 18 is led into the suction pipe 19 through the valve mechanism 20 and supplied to a compression chamber 11. A continued operation causes enlargement of the pressure difference, and the direct oil supply is no more conducted. When the compressor stops, the internal pressure of the oil supply pipe 22b drops, followed by a rise of the internal pressure of the suction pipe 19, sinking of the pressure difference to cause lessening smaller than the spring energizing force, separation of the plate 20b from the oil supply pipe 21, and generation of the communication of inside the valve mechanism 20 with the suction pipe 19, and thereby the lubricating oil 18 stagnating in the valve mechanism 20 during the operation flows into the compression chamber 11 by its self-weight so that oil supply is made to all sliding parts.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】本発明は、冷凍サイクル等に使用
する回転式圧縮機に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor used in a refrigeration cycle or the like.

【０００２】[0002]

【従来の技術】従来の回転式圧縮機としては、特開昭６
３−１３４８８８号公報に示されているものがある。以
下、図面を参照しながら上記従来の回転式圧縮機の一例
を説明する。2. Description of the Related Art As a conventional rotary compressor, Japanese Patent Laid-Open No.
There is one disclosed in Japanese Patent Publication No. 3-134888. Hereinafter, an example of the conventional rotary compressor will be described with reference to the drawings.

【０００３】従来の構成を図５、図６に示す。図５、図
６において、１は密閉ケーシング、２は電動機部であ
り、シャフト３を介してシリンダ４，ローラ５，ベーン
６，主軸受７，副軸受８により構成される機械部本体９
と連結している。シャフト３は主軸３ａ，副軸３ｂ，ク
ランク３ｃよりなる。１０はベーン背面に設けられたス
プリングである。A conventional configuration is shown in FIGS. In FIG. 5 and FIG. 6, 1 is a closed casing, 2 is an electric motor part, and a machine part main body 9 composed of a cylinder 4, a roller 5, a vane 6, a main bearing 7, and a sub bearing 8 via a shaft 3.
Connected with. The shaft 3 includes a main shaft 3a, a sub shaft 3b, and a crank 3c. Reference numeral 10 is a spring provided on the back surface of the vane.

【０００４】１１はシリンダ４内で、ローラ５，ベーン
６，主軸受７，副軸受８により構成される圧縮室であ
る。１２はシャフト３と連結する給油機構である。１３
はシリンダ４に固定された吸入管であり、シリンダ４の
吸入通路１４を介して圧縮室１１と連通している。Reference numeral 11 denotes a compression chamber in the cylinder 4, which is constituted by the roller 5, the vane 6, the main bearing 7, and the auxiliary bearing 8. Reference numeral 12 is an oil supply mechanism connected to the shaft 3. Thirteen
Is a suction pipe fixed to the cylinder 4, and communicates with the compression chamber 11 via a suction passage 14 of the cylinder 4.

【０００５】１５は吐出孔であり吐出弁１６を介して密
閉ケーシング１内と連通している。１７は吐出管であり
密閉ケーシング１内に開放している。１８は潤滑油であ
る。また、電動機部２は回転子２ａと固定子２ｂにより
構成され回転子２ａにはバランスウェイト２ｃ，２ｄが
固定されている。A discharge hole 15 communicates with the inside of the closed casing 1 through a discharge valve 16. A discharge pipe 17 is open to the inside of the closed casing 1. Reference numeral 18 is a lubricating oil. The electric motor unit 2 is composed of a rotor 2a and a stator 2b, and balance weights 2c and 2d are fixed to the rotor 2a.

【０００６】冷却システム（図示せず）からの冷媒ガス
は、吸入管１３，吸入通路１４より導かれシリンダ４内
の圧縮室１１に至る。圧縮室１１に至った冷媒ガスは、
シャフト３のクランク３ｃに嵌合されたローラ５とベー
ン６により仕切られた圧縮室１１で、電動機部２の回転
に伴うシャフト３及びローラ５の回転運動により漸次圧
縮される。従って圧縮過程において、高圧室１１ａと低
圧室１１ｂとが存在することになる。Refrigerant gas from a cooling system (not shown) is introduced from a suction pipe 13 and a suction passage 14 to reach a compression chamber 11 in the cylinder 4. The refrigerant gas reaching the compression chamber 11 is
In the compression chamber 11 partitioned by the roller 5 and the vane 6 fitted to the crank 3c of the shaft 3, the shaft 3 and the roller 5 are gradually compressed due to the rotational motion of the electric motor unit 2. Therefore, in the compression process, the high pressure chamber 11a and the low pressure chamber 11b exist.

【０００７】圧縮された冷媒ガスは、副軸受８に備えて
いる吐出孔１５，吐出弁１６を介して密閉ケーシング１
内に一旦吐出された後吐出管１７を介し冷却システムに
吐出される。The compressed refrigerant gas passes through the discharge hole 15 and the discharge valve 16 provided in the auxiliary bearing 8 and the hermetic casing 1
After being once discharged into the inside, it is discharged to the cooling system through the discharge pipe 17.

【０００８】また、潤滑油１８は、給油機構１２により
シャフト３とローラ５，主軸受７，副軸受８等の摺動部
に供給される。シャフト３とローラ５間の摺動部は高圧
であるため、シャフト３とローラ５間の摺動部に供給さ
れた潤滑油１８は、ローラ５と主軸受７，副軸受８間の
隙間を介して、より低圧であるシリンダ４内の圧縮室１
１に差圧により供給される。Lubricating oil 18 is supplied to the sliding portions of shaft 3, roller 5, main bearing 7, auxiliary bearing 8 and the like by oil supply mechanism 12. Since the sliding portion between the shaft 3 and the roller 5 has a high pressure, the lubricating oil 18 supplied to the sliding portion between the shaft 3 and the roller 5 passes through the gap between the roller 5 and the main bearing 7 and the sub bearing 8. The compression chamber 1 in the cylinder 4 that has a lower pressure
1 by differential pressure.

【０００９】さらに、ベーン６はシリンダ４の溝内を往
復運動する際に、密閉ケーシング１内に溜められた潤滑
油１８中に浸り、ベーン６とシリンダ４間の隙間を介し
て、高圧である密閉ケーシング１内からより低圧である
シリンダ４内の圧縮室１１に差圧により供給される。Further, when the vane 6 reciprocates in the groove of the cylinder 4, the vane 6 is immersed in the lubricating oil 18 accumulated in the closed casing 1 and has a high pressure through the gap between the vane 6 and the cylinder 4. The pressure is supplied from the inside of the closed casing 1 to the compression chamber 11 in the cylinder 4, which has a lower pressure, by a differential pressure.

【００１０】[0010]

【発明が解決しようとする課題】しかしながら、上記従
来の回転式圧縮機の構成では、圧縮機が停止中、特に冷
蔵庫における除霜時や圧縮機の起動直後において、冷凍
サイクルから圧縮機の圧縮室１１にガス状態の冷媒でな
く凝縮した液冷媒が戻る場合、圧縮室１１を構成するシ
リンダ４，ローラ５，ベーン６，主軸受７，副軸受８等
の各摺動部に付着している潤滑油１８を除去する可能性
がある。However, in the structure of the conventional rotary compressor described above, the compressor is stopped from the refrigeration cycle to the compression chamber of the compressor while the compressor is stopped, especially when the refrigerator is defrosted or immediately after the compressor is started. When condensed liquid refrigerant returns to 11 instead of the gaseous refrigerant, the lubrication adhered to the sliding parts such as the cylinder 4, the roller 5, the vane 6, the main bearing 7, and the auxiliary bearing 8 that constitute the compression chamber 11. The oil 18 may be removed.

【００１１】従って、圧縮機の起動時、密閉ケーシング
１内の圧力が上昇し、差圧により各摺動部に隙間を介し
て潤滑油１８が供給されるまでの間、摺動部の潤滑油が
不足状態で運転される。そのため、摺動部、特にベーン
６とローラ５との摺動部の摩耗が促進されるという長期
耐久信頼性面から改善を要する点があった。Therefore, when the compressor is started, the pressure in the closed casing 1 rises, and until the lubricating oil 18 is supplied to each sliding portion through the gap due to the differential pressure, the lubricating oil in the sliding portion is supplied. Is operated in a shortage condition. Therefore, there is a point that improvement is required from the viewpoint of long-term durability and reliability, in which abrasion of the sliding portion, particularly the sliding portion between the vane 6 and the roller 5 is promoted.

【００１２】また、圧縮室１１を構成する各摺動部の摩
耗は摺動部の加工精度及び潤滑油１８にてシールされて
いる各シール部のシール性を低下させ、長期的にみて圧
縮機の効率に影響を及ぼす可能性があった。Further, the wear of each sliding portion constituting the compression chamber 11 deteriorates the processing accuracy of the sliding portion and the sealing performance of each sealing portion sealed by the lubricating oil 18, and in the long term, the compressor is improved. Could affect the efficiency of the.

【００１３】また、圧縮機の運転状態や、冷媒及び潤滑
油１８の種類によっては、冷媒が密閉ケーシング１内で
凝縮して液冷媒となり、密閉ケーシング１底部に滞留す
る。特に非相溶性の潤滑油１８を使用した場合、その比
重が液冷媒の比重よりも小さいため密閉ケーシング１底
部に溜まり易く給油機構１２あるいはベーン６駆動によ
り各摺動部に導かれ潤滑油１８を除去し摩耗を促進させ
る。Further, depending on the operating condition of the compressor and the types of the refrigerant and the lubricating oil 18, the refrigerant condenses in the closed casing 1 to become a liquid refrigerant and stays at the bottom of the closed casing 1. In particular, when an incompatible lubricating oil 18 is used, its specific gravity is smaller than that of the liquid refrigerant, so that the lubricating oil 18 is easily accumulated in the bottom portion of the closed casing 1 and is guided to each sliding portion by the oil supply mechanism 12 or the vane 6 to drive the lubricating oil 18 Removes and promotes wear.

【００１４】また、圧縮機起動後の密閉ケーシング１内
の圧力は、起動後の初期においては上昇を続けるが、冷
凍サイクルの運転状態等によっては、その後密閉ケーシ
ング１内の圧力が低下し摺動部への給油が不充分となり
摩耗を促進する可能性がある。The pressure in the closed casing 1 after the compressor starts up continues to rise in the initial stage after the start up, but the pressure in the closed casing 1 then drops and slides depending on the operating conditions of the refrigeration cycle. There is a possibility that lubrication to parts will be insufficient and wear will be promoted.

【００１５】本発明は上記課題を解決するもので、圧縮
機の運転停止中や、起動直後に冷凍サイクルから圧縮室
に液冷媒が戻ってきても、圧縮機の停止中に圧縮室内に
直接潤滑油を供給し、かつ圧縮機起動直後から一定時間
圧縮室内に直接潤滑油を供給することによって、圧縮室
を構成するベーンやローラ等の摺動部を円滑に駆動させ
ることにより耐摩耗性を向上させ耐久信頼性を確保し、
同時に潤滑油による各シール部のシール性を維持させる
ことにより圧縮機の効率の低下を防止することを目的と
するものである。The present invention solves the above-mentioned problems. Even if the liquid refrigerant returns from the refrigeration cycle to the compression chamber immediately after the operation of the compressor is stopped or immediately after startup, the compressor is directly lubricated while the liquid refrigerant is stopped. By supplying oil and directly supplying lubricating oil into the compression chamber for a certain period of time immediately after starting the compressor, wear resistance is improved by smoothly driving the sliding parts of the compression chamber, such as vanes and rollers. To ensure durability and reliability,
At the same time, it is an object of the invention to prevent the efficiency of the compressor from being lowered by maintaining the sealing property of each seal portion by the lubricating oil.

【００１６】[0016]

【課題を解決するための手段】この目的を達成するため
に本発明の回転式圧縮機は、一端が密閉ケーシング外に
連通し、他端がシリンダに設けられた吸入通路に連通し
た吸入パイプと、密閉ケーシング内に収納され吸入パイ
プ、低圧室、吸入通路のいずれかより重力方向上方に配
設されたバルブ機構と、一端がバルブ機構より重力方向
下方に配設された吸入パイプ、低圧室、吸入通路のいず
れかに連通し、他端がバルブ機構の下部に連通した給油
管と、一端がバルブ機構の上部に連通し、他端が密閉ケ
ーシング内に溜められた潤滑油中に開口した給油路と、
バルブ機構の重力方向下方に配設されたタンクと、一端
がバルブ機構の下部に連通し他端がタンク内に連通した
排液管と、一端がタンク内に連通し、他端がバルブ機構
の上部に連通した均圧管と、バルブ機構に連通した排液
管の開口端に配設され潤滑油より比重が大きく且つ液冷
媒より比重が小さい材料にて形成されたフロートから構
成された均圧機構とから構成されている。To achieve this object, a rotary compressor according to the present invention comprises a suction pipe having one end communicating with the outside of a hermetic casing and the other end communicating with a suction passage provided in a cylinder. A valve mechanism which is housed in a closed casing and is disposed above the suction pipe, the low pressure chamber, or the suction passage in the direction of gravity, and an intake pipe whose one end is disposed below the valve mechanism in the direction of gravity, the low pressure chamber, An oil supply pipe that communicates with one of the suction passages and the other end communicates with the lower part of the valve mechanism, and one end communicates with the upper part of the valve mechanism, and the other end opens into the lubricating oil accumulated in the closed casing. Road,
A tank disposed below the valve mechanism in the direction of gravity, a drain pipe having one end communicating with the lower portion of the valve mechanism and the other end communicating with the tank, one end communicating with the tank, and the other end of the valve mechanism. A pressure equalizing mechanism that is composed of a pressure equalizing pipe that communicates with the upper portion, and a float that is disposed at the open end of a drainage pipe that communicates with the valve mechanism and that is made of a material that has a specific gravity greater than that of lubricating oil and less than that of a liquid refrigerant. It consists of and.

【００１７】また、密閉ケーシング内の圧力変動を配慮
し、給油路を形成する給油管に逆止弁機構を備えた構成
としている。Further, in consideration of the pressure fluctuation in the closed casing, the oil supply pipe forming the oil supply passage is provided with a check valve mechanism.

【００１８】[0018]

【作用】本発明の回転式圧縮機は上記構成において圧縮
機の運転停止中や圧縮機起動直後に冷凍サイクルから圧
縮室に液冷媒が戻ってきても、バルブ機構を介して圧縮
機の停止中に圧縮室内に直接潤滑油を供給し、かつ圧縮
機起動直後から一定時間圧縮室内に直接潤滑油を供給す
ることができる。そのため、圧縮室を構成する各摺動部
が潤滑油不足の状態で圧縮機が起動することを防止で
き、圧縮室を構成する各摺動部等の耐摩耗性を向上さ
せ、同時に各シール部のシール性を維持させ圧縮機の効
率の低下を防止することができる。In the rotary compressor of the present invention having the above-described structure, even when the liquid refrigerant returns from the refrigeration cycle to the compression chamber immediately after the compressor is stopped or immediately after the compressor is started, the compressor is stopped through the valve mechanism. It is possible to directly supply the lubricating oil into the compression chamber and to directly supply the lubricating oil into the compression chamber for a certain period of time immediately after the compressor is started. Therefore, it is possible to prevent the compressor from starting when each sliding part that constitutes the compression chamber is insufficient in lubricating oil, improve the wear resistance of each sliding part that configures the compression chamber, and at the same time to seal each seal part. It is possible to maintain the sealability of the compressor and prevent the efficiency of the compressor from lowering.

【００１９】また、密閉ケーシング内で冷媒が凝縮して
密閉ケーシング底部に液冷媒として滞留し、その液冷媒
をバルブ機構内に吸入しても、均圧機構によりバルブ機
構内に滞留することなくすみやかにタンクに排出できる
ため、圧縮室には液冷媒が流入せず、潤滑油のみを供給
することができる。したがって、圧縮室を構成する各摺
動部等の耐摩耗性を向上させ同時に、各シール部のシー
ル性を維持し圧縮機の効率の低下を防止することができ
る。Further, even if the refrigerant condenses in the closed casing and stays as a liquid refrigerant at the bottom of the closed casing and the liquid refrigerant is sucked into the valve mechanism, the pressure equalizing mechanism prevents the refrigerant from staying in the valve mechanism. Since it can be discharged to the tank, the liquid refrigerant does not flow into the compression chamber, and only the lubricating oil can be supplied. Therefore, it is possible to improve the wear resistance of each sliding portion that constitutes the compression chamber, and at the same time, maintain the sealing performance of each sealing portion and prevent the efficiency of the compressor from being lowered.

【００２０】また、逆止弁機構を給油管内に備えた給油
路を備えたものであるから、圧縮機の運転中において、
一旦上昇した密閉ケーシング内の圧力がその後に低下し
ても、バルブ機構内の潤滑油が密閉ケーシング内に流出
することを防止できる。そのため、いかなる圧力状態で
圧縮機が運転されても、圧縮機の運転中において、バル
ブ機構に確実に潤滑油を溜め、その潤滑油を圧縮機の停
止中に圧縮室内に供給することにより、ベーンやローラ
等の摺動部を円滑に潤滑させた状態で圧縮機を起動させ
ることができる。Further, since the oil supply passage having the check valve mechanism in the oil supply pipe is provided, the
Even if the pressure in the hermetically-sealed casing that has risen once decreases thereafter, the lubricating oil in the valve mechanism can be prevented from flowing out into the hermetically-sealed casing. Therefore, no matter what pressure the compressor is operating under, the lubricating oil is reliably accumulated in the valve mechanism during the operation of the compressor, and the lubricating oil is supplied into the compression chamber while the compressor is stopped. The compressor can be started in a state where the sliding parts such as rollers and rollers are smoothly lubricated.

【００２１】[0021]

【実施例】以下、本発明による回転式圧縮機の第１の実
施例について、図面を参照しながら説明する。なお、従
来と同一構成部については、同一符号を付して詳細な説
明を省略する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the rotary compressor according to the present invention will be described below with reference to the drawings. The same components as those of the related art will be designated by the same reference numerals and detailed description thereof will be omitted.

【００２２】図１は本発明の第１の実施例による回転式
圧縮機の要部断面図である。図２は同実施例の回転式圧
縮機の縦断面図である。FIG. 1 is a sectional view of a main part of a rotary compressor according to a first embodiment of the present invention. FIG. 2 is a vertical sectional view of the rotary compressor of the same embodiment.

【００２３】図１、図２において、１４はシリンダ４に
設けられた吸入通路、１９は一端が密閉ケーシング１外
に連通し、他端が吸入通路１４に連通した吸入パイプ、
２０は密閉ケーシング１内に収納され吸入パイプ１９の
重力方向上方に配設されたバルブ機構である。In FIGS. 1 and 2, 14 is a suction passage provided in the cylinder 4, 19 is a suction pipe having one end communicating with the outside of the closed casing 1 and the other end communicating with the suction passage 14,
Reference numeral 20 denotes a valve mechanism housed in the closed casing 1 and arranged above the suction pipe 19 in the direction of gravity.

【００２４】２１は一端が吸入パイプ１９の重力方向上
方に連通し、他端がバルブ機構２０の下部に連通した給
油管であり、２２は一端がバルブ機構２０の上部に連通
し、他端が密閉ケーシング１内に溜められた潤滑油１８
中に開口した給油路で給油管２２ｂで構成している。Reference numeral 21 denotes an oil supply pipe having one end communicating with the suction pipe 19 above the gravity direction and the other end communicating with the lower portion of the valve mechanism 20, and 22 has one end communicating with the upper portion of the valve mechanism 20 and the other end. Lubricating oil 18 stored in the closed casing 1
An oil supply passage opened to the inside is configured by an oil supply pipe 22b.

【００２５】２３はバルブ機構２０の重力方向下方に配
設されたタンクである。２４は一端がバルブ機構２０の
下部に連通し他端がタンク２３上部に連通した排液管で
ある。Reference numeral 23 is a tank disposed below the valve mechanism 20 in the direction of gravity. Reference numeral 24 is a drain pipe having one end communicating with the lower portion of the valve mechanism 20 and the other end communicating with the upper portion of the tank 23.

【００２６】２５は一端がタンク２３上部に連通し、他
端がバルブ機構２０の上方部に連通した均圧管であり、
２６はバルブ機構２０に連通した排液管２４の上方開口
端２４ａに配設され潤滑油より比重が大きく且つ液冷媒
より比重が小さい材料にて形成されたフロート２６ａで
構成された均圧機構である。Reference numeral 25 is a pressure equalizing pipe, one end of which communicates with an upper portion of the tank 23 and the other end of which communicates with an upper portion of the valve mechanism 20,
Reference numeral 26 denotes a pressure equalizing mechanism which is disposed at the upper opening end 24a of the drainage pipe 24 communicating with the valve mechanism 20 and is composed of a float 26a made of a material having a specific gravity higher than that of the lubricating oil and lower than that of the liquid refrigerant. is there.

【００２７】バルブ機構２０は、ホルダー２０ａ，プレ
ート２０ｂ，バネ２０ｃとから構成されている。バネ２
０ｃはプレート２０ｂをホルダー２０ａ上部の給油管２
２ｂの開口部２２ａに付勢するように配設されている。The valve mechanism 20 comprises a holder 20a, a plate 20b and a spring 20c. Spring 2
0c refers to the plate 20b and the oil supply pipe 2 above the holder 20a.
It is arranged so as to urge the opening 22a of 2b.

【００２８】以上のように構成された回転式圧縮機にお
いて、以下その動作を説明する。まず、圧縮機の起動直
後において、蒸発器に滞留していた液冷媒が圧縮機に吸
い込まれることがある。圧縮機に液冷媒が吸い込まれる
と、まず、吸入パイプ１９内を液冷媒が流れ、シリンダ
４に設けられた吸入通路１４を介して圧縮室１１に導か
れ、シリンダ４，ローラ５，ベーン６，主軸受７，副軸
受８等の各摺動部に付着している潤滑油１８を除去して
しまう可能性がある。The operation of the rotary compressor configured as described above will be described below. First, immediately after the start of the compressor, the liquid refrigerant that has accumulated in the evaporator may be sucked into the compressor. When the liquid refrigerant is sucked into the compressor, first, the liquid refrigerant flows in the suction pipe 19 and is guided to the compression chamber 11 via the suction passage 14 provided in the cylinder 4, and the cylinder 4, the roller 5, the vane 6, The lubricating oil 18 adhering to the sliding parts of the main bearing 7, the sub bearing 8, etc. may be removed.

【００２９】しかしながら、まず圧縮機起動前において
は、プレート２０ｂはバネ２０ｃによりホルダー２０ａ
上部の給油管２２ｂの開口部２２ａに付勢されているた
め、プレート２０ｂと給油管２１とは接触シールせず隙
間が保たれている。その後圧縮機が起動すると、吸入パ
イプ１９内及び給油管２１内の圧力は低下し、密閉ケー
シング１内の圧力より低くなる。However, first, before starting the compressor, the plate 20b is held by the spring 20c in the holder 20a.
Since the opening 20a of the upper oil supply pipe 22b is biased, the plate 20b and the oil supply pipe 21 are not contact-sealed with each other, but a gap is maintained. After that, when the compressor is activated, the pressure in the suction pipe 19 and the pressure in the oil supply pipe 21 decrease, and become lower than the pressure in the closed casing 1.

【００３０】給油路２２を形成する給油管２２ｂ内は密
閉ケーシング１内と同じ圧力であるため、給油管２２ｂ
内の圧力がバルブ機構２０内の圧力よりも高くなり圧力
差が生じる。圧縮機の起動初期においてはこの圧力差は
小さいが、プレート２０ｂを給油管２２ｂの開口部２２
ａに付勢するバネ２０ｃの付勢力より僅かに大きくな
る。そのため、プレート２０ｂは給油管２２ｂの開口部
２２ａから離れるが、圧力差がバネ２０ｃの付勢力に対
して十分大きくないため、プレート２０ｂは給油管２１
に押しつけられず、バルブ機構２０と給油管２１は連通
している。Since the inside of the oil supply pipe 22b forming the oil supply passage 22 has the same pressure as the inside of the closed casing 1, the oil supply pipe 22b is formed.
The internal pressure becomes higher than the internal pressure of the valve mechanism 20, and a pressure difference occurs. Although this pressure difference is small in the initial stage of starting the compressor, the plate 20b is connected to the opening 22 of the oil supply pipe 22b.
It is slightly larger than the biasing force of the spring 20c that biases a. Therefore, the plate 20b moves away from the opening 22a of the oil supply pipe 22b, but since the pressure difference is not sufficiently large with respect to the urging force of the spring 20c, the plate 20b has the oil supply pipe 21b.
The valve mechanism 20 and the oil supply pipe 21 communicate with each other without being pressed against.

【００３１】したがって、密閉ケーシング１内の潤滑油
１８と吸入パイプ１９内は、給油管２２ｂ、バルブ機構
２０、給油管２１を介して連通しているが、潤滑油１８
は高圧、吸入パイプ１９内は低圧でバルブ機構２０内は
その中間の圧力となる。そのため、この圧力差により潤
滑油１８がバルブ機構２０を介して吸入パイプ１９内に
導かれ、圧縮室１１に供給される。Therefore, the lubricating oil 18 in the closed casing 1 and the suction pipe 19 are communicated with each other through the oil supply pipe 22b, the valve mechanism 20, and the oil supply pipe 21.
Is high pressure, the suction pipe 19 has a low pressure, and the valve mechanism 20 has an intermediate pressure. Therefore, due to this pressure difference, the lubricating oil 18 is guided into the suction pipe 19 via the valve mechanism 20 and is supplied to the compression chamber 11.

【００３２】また、圧縮機の運転状態、また冷媒や潤滑
油１８の種類によっては、圧縮機の停止中や運転中にお
いて、冷媒ガスが密閉ケーシング１内で凝縮して液冷媒
となり、密閉ケーシング１内底部に滞留する。特に非相
溶性の潤滑油１８を使用した場合には、潤滑油１８の比
重は液冷媒の比重よりも小さく滞留しやすい。Further, depending on the operating condition of the compressor and the types of the refrigerant and the lubricating oil 18, the refrigerant gas is condensed in the closed casing 1 to become a liquid refrigerant during the stop or operation of the compressor, and the closed casing 1 Remains on the inner bottom. In particular, when the incompatible lubricating oil 18 is used, the specific gravity of the lubricating oil 18 is smaller than the specific gravity of the liquid refrigerant and tends to stay.

【００３３】その場合、圧縮機が運転中において、密閉
ケーシング１内とバルブ機構２０内の圧力差が大きくな
り、プレート２０ｂが給油管２１上部を閉鎖するととも
に密閉ケーシング１内底部に滞留している液冷媒が、潤
滑油１８と共に給油管２２ｂを介してバルブ機構２０内
に流入する。しかし、均圧機構２６を構成するフロート
２６ａは液冷媒より比重が小さい材料にて形成されてい
るため均圧機構２６の入口側であるバルブ機構２０内と
出口側であるタンク２３内は均圧管２５により常に圧力
を均一に保持する機能をもつため、フロート２６ａが開
き、液冷媒がタンク２３に流出し、給油管２１内に流れ
込むことはない。In this case, when the compressor is in operation, the pressure difference between the closed casing 1 and the valve mechanism 20 becomes large, and the plate 20b closes the upper part of the oil supply pipe 21 and stays at the inner bottom of the closed casing 1. The liquid refrigerant flows into the valve mechanism 20 together with the lubricating oil 18 via the oil supply pipe 22b. However, since the float 26a constituting the pressure equalizing mechanism 26 is made of a material having a smaller specific gravity than the liquid refrigerant, the pressure equalizing pipe is provided inside the valve mechanism 20 on the inlet side and the tank 23 on the outlet side of the pressure equalizing mechanism 26. Since 25 has a function of always maintaining a uniform pressure, the float 26a is opened, and the liquid refrigerant does not flow into the tank 23 and flow into the oil supply pipe 21.

【００３４】なお、潤滑油１８のみがバルブ機構２０内
に流入した際には、フロート２６ａは潤滑油１８より比
重の大きな材料にて形成されているので、排液管開口部
２４ａは閉じたままであり、潤滑油１８がタンク２３に
流出することはなく、バルブ機構２０内に溜まる。When only the lubricating oil 18 flows into the valve mechanism 20, since the float 26a is made of a material having a larger specific gravity than the lubricating oil 18, the drain pipe opening 24a remains closed. Therefore, the lubricating oil 18 does not flow out into the tank 23, but collects in the valve mechanism 20.

【００３５】さらに圧縮機の運転が継続して、密閉ケー
シング１内の圧力が更に上昇し、吸入パイプ１９内との
圧力差が大きくなり、バネ２０ｃの付勢力より圧力差が
十分大きくなると、プレート２０ｂが給油管２１に接触
するまでバネ２０ｃが縮む。そのため、プレート２０ｂ
と給油管２１とが接触シールしバルブ機構２０内と給油
管２１とは連通しなくなり、バルブ機構２０から吸入パ
イプ１９を介して行われていた圧縮室１１への直接給油
は行われなくなる。しかし、バルブ機構２０内にはそれ
まで給油管２２ｂを介して流入していた潤滑油１８が溜
まったままとなる。When the operation of the compressor is further continued and the pressure inside the closed casing 1 further rises, the pressure difference between the inside of the suction pipe 19 becomes large, and the pressure difference becomes sufficiently larger than the biasing force of the spring 20c, the plate The spring 20c contracts until 20b contacts the oil supply pipe 21. Therefore, the plate 20b
And the oil supply pipe 21 are in contact with each other and the valve mechanism 20 and the oil supply pipe 21 do not communicate with each other, and the direct oil supply from the valve mechanism 20 to the compression chamber 11 via the suction pipe 19 is not performed. However, the lubricating oil 18 that has flowed in through the oil supply pipe 22b until then remains in the valve mechanism 20.

【００３６】そして、バルブ機構２０、吸入パイプ１９
を介して行われていた圧縮室１１への直接給油は行われ
なくなった後は、従来のローラ５と主軸受７，副軸受８
間の隙間及びベーン６とシリンダ４の溝間の隙間を介し
て圧縮室１１内に給油される。Then, the valve mechanism 20 and the suction pipe 19
After the direct oil supply to the compression chamber 11 which has been performed via the oil is no longer performed, the conventional roller 5, the main bearing 7, and the auxiliary bearing 8 are used.
Oil is supplied into the compression chamber 11 through a gap therebetween and a gap between the vane 6 and the groove of the cylinder 4.

【００３７】したがって、圧縮機の起動直後に冷凍サイ
クルから液冷媒が戻ってきても、起動と同時に圧縮室１
１に直接給油を行うことにより、圧縮室１１を構成する
シリンダ４，ローラ５，ベーン６，主軸受７，副軸受８
等の各摺動部において、液冷媒により付着している潤滑
油１８が除去される状態で摺動することが防止できる。Therefore, even if the liquid refrigerant returns from the refrigeration cycle immediately after the compressor is started, the compression chamber 1
By directly supplying oil to the cylinder 1, the cylinder 4, the roller 5, the vane 6, the main bearing 7, and the auxiliary bearing 8 which form the compression chamber 11 are formed.
It is possible to prevent the sliding of each of the sliding parts such as the above while the lubricating oil 18 adhering to the liquid refrigerant is removed.

【００３８】また、圧縮機の運転状態、また冷媒や潤滑
油の種類によって、圧縮機の停止中や運転中において、
冷媒ガスが密閉ケーシング１内で凝縮して液冷媒とな
り、密閉ケーシング１内底部に滞留した際でも、潤滑油
１８と共に給油管２２ｂを介してバルブ機構２０内に流
入した液冷媒は、タンク２３に流出し、給油管２１内に
流れ込むことはない。Further, depending on the operating condition of the compressor, the type of refrigerant or lubricating oil, the compressor may be stopped or operating,
Even when the refrigerant gas is condensed in the closed casing 1 to become a liquid refrigerant and stays at the bottom of the closed casing 1, the liquid refrigerant flowing into the valve mechanism 20 through the oil supply pipe 22b together with the lubricating oil 18 is stored in the tank 23. It does not flow out and flow into the oil supply pipe 21.

【００３９】また、圧縮室１１内に過多の潤滑油１８が
供給されオイル圧縮を引き起こすこともなく、圧縮機か
ら冷凍サイクルへ流出する潤滑油量が増大することもな
い。Further, the excessive amount of lubricating oil 18 is not supplied to the compression chamber 11 to cause oil compression, and the amount of lubricating oil flowing from the compressor to the refrigeration cycle does not increase.

【００４０】なお、給油管２２ｂ、バルブ機構２０を介
して圧縮室１１内へ直接給油を行う時間は、バネ２０ｃ
の付勢力を変えることによって調整できることは言うま
でもない。The time during which oil is directly supplied into the compression chamber 11 via the oil supply pipe 22b and the valve mechanism 20 is the spring 20c.
Needless to say, it can be adjusted by changing the urging force of.

【００４１】さらに時間が経過して圧縮機が停止する
と、圧縮機内部は時間経過と共に均圧状態になる。すな
わち、給油管２２ｂ内の圧力が徐々に低下し、吸入パイ
プ１９内の圧力が徐々に上昇することにより、その圧力
差が次第に小さくなる。したがって、圧力差がバネ２０
ｃの付勢力より小さくなり、プレート２０ｂが給油管２
１から離れ、バルブ機構２０内と吸入パイプ１９とが給
油管２１を介して連通する。When the compressor is stopped after a further lapse of time, the pressure inside the compressor becomes equalized with the lapse of time. That is, the pressure in the oil supply pipe 22b gradually decreases and the pressure in the suction pipe 19 gradually increases, so that the pressure difference gradually decreases. Therefore, the pressure difference is
It becomes smaller than the urging force of c and the plate 20b becomes
1, the inside of the valve mechanism 20 and the suction pipe 19 communicate with each other via the oil supply pipe 21.

【００４２】そして、圧縮機の運転中にバルブ機構２０
内に溜まっていた潤滑油１８がその自重により給油管２
１、吸入パイプ１９内を介して圧縮室１１内に流入し、
圧縮室１１を構成するシリンダ４，ローラ５，ベーン
６，主軸受７，副軸受８等の各摺動部に供給される。な
お、本実施例において、吸入パイプ１９が圧縮室１１に
対して重力方向上方となるよう傾斜している方がより効
果的であることは言うまでもない。The valve mechanism 20 is operated while the compressor is operating.
The lubricating oil 18 accumulated inside the oil supply pipe 2 due to its own weight.
1, flow into the compression chamber 11 through the suction pipe 19,
It is supplied to each sliding portion such as the cylinder 4, the roller 5, the vane 6, the main bearing 7, the auxiliary bearing 8 and the like which form the compression chamber 11. Needless to say, in this embodiment, it is more effective if the suction pipe 19 is inclined so as to be upward with respect to the compression chamber 11 in the direction of gravity.

【００４３】したがって、圧縮機の運転停止中に、冷凍
サイクルから圧縮機の圧縮室１１に液冷媒が戻ってきて
も、バルブ機構２０内に溜まっていた潤滑油１８を直接
圧縮室１１に供給することができ、圧縮室１１を構成す
るシリンダ４，ローラ５，ベーン６，主軸受７，副軸受
８等の各摺動部において、潤滑油が液冷媒によって除去
されることを防止できる。そのため、圧縮機の起動直前
から圧縮室１１内には十分な潤滑油１８が供給されてお
り、圧縮室１１を構成する各摺動部が潤滑油不足状態で
起動することを防止できる。Therefore, even if the liquid refrigerant returns from the refrigeration cycle to the compression chamber 11 of the compressor while the compressor is stopped, the lubricating oil 18 accumulated in the valve mechanism 20 is directly supplied to the compression chamber 11. Therefore, it is possible to prevent the lubricating oil from being removed by the liquid refrigerant in each of the sliding parts such as the cylinder 4, the roller 5, the vane 6, the main bearing 7, the auxiliary bearing 8 that constitute the compression chamber 11. Therefore, sufficient lubricating oil 18 has been supplied into the compression chamber 11 immediately before the compressor is started, and it is possible to prevent the sliding portions forming the compression chamber 11 from starting in a lubricating oil shortage state.

【００４４】以上本実施例の回転式圧縮機は、上記構成
からわかるように、従来の方式にあらたにバルブ機構お
よび均圧機構を設けた構造になっているため圧縮機の起
動直後や圧縮機の運転停止中に冷凍サイクルから圧縮室
に液冷媒が戻ってきても圧縮機の起動直後から一定時間
及び圧縮機の運転停止中に、圧縮室内に直接潤滑油を供
給できる。As can be seen from the above structure, the rotary compressor of this embodiment has a structure in which a valve mechanism and a pressure equalizing mechanism are newly provided in the conventional system. Even if the liquid refrigerant returns from the refrigeration cycle to the compression chamber during the suspension of operation, the lubricating oil can be directly supplied into the compression chamber for a certain period of time immediately after the compressor is started and during the suspension of the compressor.

【００４５】また、圧縮機の運転状態、また冷媒や潤滑
油の種類によって圧縮機の停止中や運転中において、冷
媒ガスが密閉ケーシング内で凝縮して液冷媒となり、密
閉ケーシング内下部に滞留した場合でも潤滑油とともに
給油管を介してバルブ機構内に流入した液冷媒はタンク
に流出し、給油管内及び圧縮室に流れ込むことなく圧縮
機の起動と同時に各摺動部に常に潤滑油を確保すること
ができかつ圧縮機の起動前から圧縮室内に十分な潤滑油
を供給することができるため、圧縮室を構成する各摺動
部の耐摩耗性を改善でき、耐久信頼性を向上することが
でき、同時に摺動部の加工精度及び潤滑油にてシールさ
れている各シール部のシール性の低下を防止でき、圧縮
機の効率の低下を防止することができる。Further, depending on the operating condition of the compressor, and also during stop or operation of the compressor depending on the types of refrigerant and lubricating oil, the refrigerant gas condenses in the hermetic casing to become liquid refrigerant and stays in the lower part of the hermetic casing. Even when the lubricating oil flows into the valve mechanism through the oil supply pipe together with the lubricating oil, the liquid refrigerant flows out into the tank and does not flow into the oil supply pipe and the compression chamber, so that the lubricating oil is always secured in each sliding part at the same time when the compressor starts up. Since it is possible to supply sufficient lubricating oil into the compression chamber before the compressor is started, it is possible to improve the wear resistance of each sliding part that constitutes the compression chamber and improve the durability and reliability. At the same time, it is possible to prevent the processing accuracy of the sliding portion and the sealing performance of each sealing portion sealed by the lubricating oil from being lowered, and to prevent the efficiency of the compressor from being lowered.

【００４６】また、圧縮機の運転が続くと圧縮室内への
給油は、従来のローラと主軸受，副軸受間の隙間及びベ
ーンとシリンダの溝間の隙間を介しての供給となる。そ
のため、圧縮室内に過多の潤滑油が供給されオイル圧縮
を引き起こすこともなく、また圧縮機から冷凍サイクル
へ流出する潤滑油量が増大することもない。When the compressor continues to be operated, oil is supplied into the compression chamber through the gap between the conventional roller and the main bearing and the sub bearing, and the gap between the vane and the groove of the cylinder. Therefore, neither excessive amount of lubricating oil is supplied into the compression chamber to cause oil compression, nor does the amount of lubricating oil flowing from the compressor to the refrigeration cycle increase.

【００４７】なお、本実施例では、給油管が吸入パイプ
に連通しているが、給油管がシリンダ内の低圧室や吸入
通路等の、圧縮機の起動により圧力が低下する箇所に連
通していれば同様の効果が得られることは言うまでもな
い。また、圧縮機の運転停止中にプレートが給油路の開
口部に接触していなくても、プレートが給油管と接触シ
ールしていなければ良いことは言うまでもない。また、
本実施例では、バルブ機構は、ホルダー、プレート、バ
ネとから構成されているが、他の構成であっても同様の
効果が得られることは言うまでもない。In this embodiment, the oil supply pipe communicates with the suction pipe, but the oil supply pipe communicates with a low pressure chamber in the cylinder, a suction passage, or the like, where the pressure decreases due to activation of the compressor. Needless to say, the same effect can be obtained. Needless to say, even if the plate is not in contact with the opening of the oil supply passage while the compressor is stopped, the plate need not be in contact with and sealed by the oil supply pipe. Also,
In the present embodiment, the valve mechanism is composed of the holder, the plate and the spring, but it goes without saying that the same effect can be obtained with other configurations.

【００４８】次に、本発明の回転式圧縮機の第２の実施
例について、図面を参照しながら説明する。なお、第１
の実施例と同一構成については、同一符号を付して詳細
な説明は省略する。Next, a second embodiment of the rotary compressor of the present invention will be described with reference to the drawings. The first
The same configurations as those of the embodiment are given the same reference numerals and detailed description thereof will be omitted.

【００４９】図３は本発明の第２の実施例による回転式
圧縮機の要部断面図である。図４は同実施例の回転式圧
縮機の縦断面図である。図３、図４において、２７は逆
止弁機構であり、給油路２２を形成する給油管２２ｂ内
に配設されている。FIG. 3 is a sectional view of the essential parts of a rotary compressor according to the second embodiment of the present invention. FIG. 4 is a vertical sectional view of the rotary compressor of the same embodiment. In FIG. 3 and FIG. 4, 27 is a check valve mechanism, which is arranged in the oil supply pipe 22 b forming the oil supply passage 22.

【００５０】逆止弁機構２７は、弁体２７ａ、弁２７
ｂ、スプリング２７ｃとから構成されている。スプリン
グ２７ｃは弁２７ｂを弁体２７ａ下部のシート面２７ｄ
に付勢するように配設されている。なお、図３中の矢印
は、潤滑油１８の流れ方向を示しており、流れの上流側
が密閉ケーシング１内の下部に滞留している潤滑油１８
側であり、下流側がバルブ機構２０側である。The check valve mechanism 27 includes a valve body 27a and a valve 27.
b and a spring 27c. The spring 27c connects the valve 27b to the seat surface 27d below the valve body 27a.
It is arranged so as to bias. The arrows in FIG. 3 indicate the flow direction of the lubricating oil 18, and the lubricating oil 18 whose upstream side of the flow stays in the lower portion of the closed casing 1 is shown.
And the downstream side is the valve mechanism 20 side.

【００５１】以上のように構成された回転式圧縮機にお
いて、以下その動作を説明する。まず、圧縮機起動前
は、弁２７ｂはスプリング２７ｃにより弁体２７ａ下部
のシート面２７ｄに付勢され接触シールされている。そ
の後圧縮機が起動すると吸入パイプ１９内、給油管２１
内及びバルブ機構２０内の圧力は低下し、密閉ケーシン
グ１内の圧力より低くなり、圧力差が生じる。この圧力
差がスプリング２７ｃの付勢力より大きくなると弁２７
ｂはシート面２７ｄから離れる。The operation of the rotary compressor having the above structure will be described below. First, before the compressor is activated, the valve 27b is urged by the spring 27c against the seat surface 27d below the valve body 27a to be contact-sealed. After that, when the compressor starts, the suction pipe 19 and the oil supply pipe 21
The pressure inside and inside the valve mechanism 20 decreases and becomes lower than the pressure inside the closed casing 1, resulting in a pressure difference. When this pressure difference becomes larger than the biasing force of the spring 27c, the valve 27
b is separated from the seat surface 27d.

【００５２】したがって、密閉ケーシング１内の潤滑油
１８と吸入パイプ１９内は、給油管２２ｂ、逆止弁機構
２７、バルブ機構２０、給油管２１を介して連通し、潤
滑油１８は高圧、吸入パイプ１９内は低圧、バルブ機構
２０内はその中間の圧力となる。そのため、この圧力差
により潤滑油１８がバルブ機構２０を介して吸入パイプ
１９内に導かれ、圧縮室１１に供給される。Therefore, the lubricating oil 18 inside the closed casing 1 and the inside of the suction pipe 19 communicate with each other through the oil supply pipe 22b, the check valve mechanism 27, the valve mechanism 20 and the oil supply pipe 21. The pipe 19 has a low pressure, and the valve mechanism 20 has an intermediate pressure. Therefore, due to this pressure difference, the lubricating oil 18 is guided into the suction pipe 19 via the valve mechanism 20 and is supplied to the compression chamber 11.

【００５３】さらに圧縮機の運転が継続して、密閉ケー
シング１内の圧力が更に上昇し、吸入パイプ１９内との
圧力差が大きくなり、バルブ機構２０内のバネ２０ｃの
付勢力より圧力差が十分大きくなると、プレート２０ｂ
が給油管２１に接触するまでバネ２０ｃが縮む。そのた
め、プレート２０ｂと給油管２１とが接触シールし、バ
ルブ機構２０内と給油管２１とは連通しなくなり、バル
ブ機構２０、吸入パイプ１９を介して行われていた圧縮
室１１への直接給油は停止する。しかし、バルブ機構２
０内にはそれまで給油管２２ｂを介して流入していた潤
滑油１８が溜まったままとなる。Further, as the compressor continues to operate, the pressure inside the closed casing 1 further rises, the pressure difference between the inside of the suction pipe 19 becomes large, and the pressure difference becomes greater than the biasing force of the spring 20c inside the valve mechanism 20. When it is large enough, the plate 20b
The spring 20c contracts until it contacts the oil supply pipe 21. Therefore, the plate 20b and the oil supply pipe 21 are contact-sealed with each other, the communication between the inside of the valve mechanism 20 and the oil supply pipe 21 is lost, and direct oil supply to the compression chamber 11 performed via the valve mechanism 20 and the suction pipe 19 is not performed. Stop. However, the valve mechanism 2
The lubricating oil 18 that has flowed in through 0 through the oil supply pipe 22b remains accumulated in 0.

【００５４】そして、バルブ機構２０内と給油管２１内
が連通しなくなると、バルブ機構２０内と密閉ケーシン
グ１内との圧力差はなくなり、その結果、弁２７ｂはス
プリング２７ｃの付勢力により弁体２７ａ下部のシート
面２７ｄに付勢され、接触シールされる。When the inside of the valve mechanism 20 and the inside of the oil supply pipe 21 are no longer communicated with each other, the pressure difference between the inside of the valve mechanism 20 and the inside of the closed casing 1 disappears, and as a result, the valve 27b is moved by the urging force of the spring 27c. The seat surface 27d at the lower part of 27a is urged and contact-sealed.

【００５５】そのため、バルブ機構２０内は、吸入管２
１及び密閉ケーシング１内とは連通せず、高圧の状態で
維持される。Therefore, the inside of the valve mechanism 20 includes the suction pipe 2
1 and the inside of the closed casing 1 do not communicate with each other and are maintained in a high pressure state.

【００５６】その後、更に圧縮機の運転が継続し冷凍サ
イクルの運転状態等によっては、密閉ケーシング１内の
圧力がそれまでの圧力よりも低下することがある。その
時には、バルブ機構２０内の方が密閉ケーシング１内よ
りも圧力が高い状態となり、逆止弁機構２７によりバル
ブ機構２０内と密閉ケーシング１内とは連通しない。After that, the pressure in the closed casing 1 may be lower than the pressure up to that point, depending on the operation state of the refrigeration cycle, etc. of the compressor. At that time, the pressure inside the valve mechanism 20 is higher than that inside the closed casing 1, and the check valve mechanism 27 does not allow communication between the inside of the valve mechanism 20 and the inside of the closed casing 1.

【００５７】そのため、一旦バルブ機構２０内に溜まっ
た潤滑油１８は、圧縮機運転中はそのままバルブ機構２
０内に滞留したままとなる。Therefore, the lubricating oil 18 once stored in the valve mechanism 20 remains as it is during operation of the compressor.
It stays in 0.

【００５８】さらに時間が経過して圧縮機が停止する
と、圧縮機内部は時間経過と共に均圧状態になる。すな
わち、給油管２１内の圧力が徐々に上昇し、バルブ機構
２０内との圧力差が次第に小さくなり、圧力差がバネ２
０ｃの付勢力より小さくなり、プレート２０ｂが給油管
２１から離れ、バルブ機構２０内と吸入パイプ１９とが
給油管２１を介して連通する。When the compressor is stopped after a further lapse of time, the interior of the compressor becomes in a pressure equalizing state with the lapse of time. That is, the pressure inside the oil supply pipe 21 gradually rises, the pressure difference between the inside of the valve mechanism 20 gradually decreases, and the pressure difference becomes equal to that of the spring 2.
The force becomes smaller than the urging force of 0c, the plate 20b separates from the oil supply pipe 21, and the inside of the valve mechanism 20 communicates with the suction pipe 19 via the oil supply pipe 21.

【００５９】そして、圧縮機の運転中にバルブ機構２０
内に溜まっていた潤滑油１８がその自重により給油管２
１、吸入パイプ１９内を介して圧縮室１１内に流入し、
圧縮室１１を構成するシリンダ４，ローラ５，ベーン
６，主軸受７，副軸受８等の各摺動部に供給される。Then, the valve mechanism 20 is operated during the operation of the compressor.
The lubricating oil 18 accumulated inside the oil supply pipe 2 due to its own weight.
1, flow into the compression chamber 11 through the suction pipe 19,
It is supplied to each sliding portion such as the cylinder 4, the roller 5, the vane 6, the main bearing 7, the auxiliary bearing 8 and the like which form the compression chamber 11.

【００６０】以上のように本実施例の回転式圧縮機は、
給油路を形成する給油管に逆止弁機構を備えた構成であ
るから、圧縮機の運転中において、一旦上昇した密閉ケ
ーシング内の圧力がその後に低下しても、バルブ機構内
の潤滑油が密閉ケーシング内に流出することを防止でき
る。そのため、いかなる圧力状態で圧縮機が運転されて
も、圧縮機運転中において、バルブ機構に確実に潤滑油
を溜め、その潤滑油を圧縮機停止中に圧縮室内に供給す
ることにより、圧縮室を構成するベーンやローラ等の摺
動部が潤滑油不足の状態で圧縮機が起動することを防止
できる。As described above, the rotary compressor of this embodiment is
Since the oil supply pipe forming the oil supply passage is provided with a check valve mechanism, even if the pressure in the closed casing that has once risen during the operation of the compressor decreases thereafter, the lubricating oil in the valve mechanism will It can be prevented from flowing out into the closed casing. Therefore, no matter what pressure the compressor is operated under, the lubricating oil is reliably accumulated in the valve mechanism during the operation of the compressor, and the lubricating oil is supplied into the compression chamber while the compressor is stopped, so that the compression chamber is maintained. It is possible to prevent the compressor from starting when the sliding portions such as the vanes and the rollers that are formed have insufficient lubricating oil.

【００６１】なお、本実施例では、逆止弁機構は、弁
体、弁、スプリングとから構成されているが、他の構成
であっても同様の効果が得られることは言うまでもな
い。In the present embodiment, the check valve mechanism is composed of the valve body, the valve and the spring, but it goes without saying that the same effect can be obtained with other configurations.

【００６２】[0062]

【発明の効果】本発明は上記説明からわかるように、一
端が密閉ケーシング外に連通し、他端がシリンダに設け
られた吸入通路に連通した吸入パイプと、密閉ケーシン
グ内に収納され吸入パイプ、低圧室、吸入通路のいずれ
かより重力方向上方に配設されたバルブ機構と、一端が
バルブ機構より重力方向下方に配設された吸入パイプ、
低圧室、吸入通路のいずれかに連通し、他端がバルブ機
構の下部に連通した給油管と、一端がバルブ機構の上部
に連通し、他端が密閉ケーシング内に溜められた潤滑油
中に開口した給油路を形成する給油管と、バルブ機構の
重力方向下方に配設されたタンクと、一端がバルブ機構
の下部に連通し、他端がタンク内に連通した排液管と、
一端がタンク内に連通し他端がバルブ機構の上部に連通
した均圧管と、バルブ機構に連通した排液管の開口端に
配設され潤滑油より比重が大きく、かつ液冷媒より比重
が小さい材料にて形成されたフロートで構成した均圧機
構を備えたものであるから、圧縮機の起動直後や圧縮機
の停止中に冷凍サイクルから圧縮室に液冷媒が戻ってき
ても、圧縮機の起動直後から一定時間及び圧縮機の運転
停止中に、圧縮室内に直接潤滑油を供給できる。As can be seen from the above description, the present invention has a suction pipe having one end communicating with the outside of the closed casing and the other end communicating with a suction passage provided in the cylinder, and a suction pipe housed in the closed casing. A valve mechanism disposed above the low-pressure chamber or the suction passage in the direction of gravity, and a suction pipe whose one end is disposed below the valve mechanism in the direction of gravity.
An oil supply pipe that communicates with either the low-pressure chamber or the suction passage and the other end communicates with the lower part of the valve mechanism, and one end communicates with the upper part of the valve mechanism, and the other end with the lubricating oil stored in the closed casing. An oil supply pipe forming an open oil supply passage, a tank disposed below the valve mechanism in the direction of gravity, a drain pipe having one end communicating with the lower portion of the valve mechanism and the other end communicating with the tank,
The pressure equalizing pipe, one end of which communicates with the inside of the tank and the other end of which communicates with the upper part of the valve mechanism, and the drain pipe, which communicates with the valve mechanism, are disposed at the open ends of the pressure equalizing pipe, and have a specific gravity higher than that of the lubricating oil and lower than that of the liquid refrigerant. Since it is equipped with a pressure equalizing mechanism composed of a float formed of material, even if the liquid refrigerant returns from the refrigeration cycle to the compression chamber immediately after the compressor is started or while the compressor is stopped, The lubricating oil can be directly supplied into the compression chamber for a certain period of time immediately after the start-up and while the compressor is stopped.

【００６３】また、圧縮機の運転状態、また冷媒や潤滑
油の種類によって、圧縮機の運転停止中や運転中におい
て、冷媒ガスが密閉ケーシング内で凝縮して液冷媒とな
り、密閉ケーシング内下部に滞留したときでも、潤滑油
とともに給油路を介してバルブ機構内に流入した液冷媒
は、タンクに流出し、給油管内及び圧縮室に流れ込むこ
とはない。Further, depending on the operating condition of the compressor and the types of the refrigerant and the lubricating oil, the refrigerant gas is condensed in the closed casing to become a liquid refrigerant during the stoppage or the operation of the compressor, and the refrigerant gas is formed in the lower part of the closed casing. Even when accumulated, the liquid refrigerant that has flowed into the valve mechanism together with the lubricating oil through the oil supply passage flows out into the tank and does not flow into the oil supply pipe or the compression chamber.

【００６４】そのため、圧縮室を構成する各摺動部にお
いて、圧縮機の起動と同時に常に潤滑油を確保すること
ができ、且つ圧縮機の起動前から圧縮室内に十分な潤滑
油を供給することができるため、圧縮室を構成する各摺
動部の摩耗を防止でき圧縮機の耐久信頼性が向上し、同
時に圧縮室を構成する各摺動部の摩耗を防止することに
より、摺動部の加工精度及び潤滑油にてシールされてい
る各シール部のシール性の低下が防止でき、圧縮機の効
率の低下を防止することができる。Therefore, the lubricating oil can be always ensured at the same time when the compressor is started in each sliding portion forming the compression chamber, and sufficient lubricating oil can be supplied into the compression chamber before the start of the compressor. Therefore, it is possible to prevent wear of the sliding parts that make up the compression chamber, improve the durability reliability of the compressor, and at the same time prevent wear of the sliding parts that make up the compression chamber, It is possible to prevent deterioration of the processing accuracy and the sealing property of each seal portion sealed by the lubricating oil, and prevent the efficiency of the compressor from decreasing.

【００６５】また、圧縮機の運転が続くと、圧縮室内へ
の給油は、従来のローラと主軸受，副軸受間の隙間及び
ベーンとシリンダの溝間の隙間を介してなされるが、圧
力変動にも影響されないため圧縮室内に過多の潤滑油が
供給されオイル圧縮を引き起こすこともなく、また圧縮
機から冷凍サイクルへ流出する潤滑油量が増大すること
もない。When the compressor continues to be operated, oil is supplied into the compression chamber through the gap between the conventional roller and the main bearing and the sub bearing and the gap between the vane and the groove of the cylinder. Therefore, the excessive amount of lubricating oil supplied to the compression chamber does not cause oil compression, and the amount of lubricating oil flowing from the compressor to the refrigeration cycle does not increase.

【００６６】また、逆止弁機構を備えた給油路を備えた
ものであるから、圧縮機の運転中において、一旦上昇し
た密閉ケーシング内の圧力がその後に低下しても、バル
ブ機構内の潤滑油が密閉ケーシング内に流出することを
防止できる。したがって、いかなる圧力状態で圧縮機が
運転されても、圧縮機運転中においてバルブ機構に確実
に潤滑油を溜め、その潤滑油を圧縮機の運転停止中に圧
縮室内に供給することにより、圧縮室を構成するベーン
やローラ等の摺動部が潤滑油不足なく円滑な状態で圧縮
機を起動させることができる。Further, since the oil supply passage provided with the check valve mechanism is provided, even if the pressure in the closed casing which once rises during the operation of the compressor decreases thereafter, lubrication in the valve mechanism is performed. It is possible to prevent oil from flowing out into the closed casing. Therefore, no matter what pressure the compressor is operated under, the lubricating oil is reliably accumulated in the valve mechanism during operation of the compressor, and the lubricating oil is supplied into the compression chamber while the compressor is not operating. It is possible to start the compressor in a smooth state in which the sliding parts such as the vanes and rollers that make up the above are smooth without lack of lubricating oil.

【図面の簡単な説明】[Brief description of drawings]

【図１】本発明による第１の実施例を示す回転式圧縮機
の要部断面図FIG. 1 is a sectional view of a main part of a rotary compressor showing a first embodiment according to the present invention.

【図２】同実施例の回転式圧縮機の縦断面図FIG. 2 is a vertical cross-sectional view of the rotary compressor of the same embodiment.

【図３】本発明による第２の実施例を示す回転式圧縮機
の要部断面図FIG. 3 is a sectional view of an essential part of a rotary compressor showing a second embodiment according to the present invention.

【図４】同実施例の回転式圧縮機の縦断面図FIG. 4 is a vertical cross-sectional view of the rotary compressor of the same embodiment.

【図５】従来の回転式圧縮機の縦断面図FIG. 5 is a vertical sectional view of a conventional rotary compressor.

【図６】図５のＡ−Ａ線断面図6 is a sectional view taken along line AA of FIG.

【符号の説明】[Explanation of symbols]

１ 密閉ケーシング ４ シリンダ ６ ベーン １１ 圧縮室 １１ａ 高圧室 １１ｂ 低圧室 １４ 吸入通路 １８ 潤滑油 １９ 吸入パイプ ２０ バルブ機構 ２１ 給油管 ２２ 給油路 ２２ａ 給油管開口部 ２２ｂ 給油管 ２３ タンク ２４ 排液管 ２４ａ 排液管の開口端 ２５ 均圧管 ２６ 均圧機構 ２６ａ フロート ２７ 逆止弁機構 ２７ａ 弁体 ２７ｂ 弁 ２７ｃ スプリング ２７ｄ シート面 1 Closed Casing 4 Cylinder 6 Vane 11 Compression Chamber 11a High Pressure Chamber 11b Low Pressure Chamber 14 Suction Passage 18 Lubricating Oil 19 Suction Pipe 20 Valve Mechanism 21 Oil Supply Pipe 22 Oil Supply Path 22a Oil Supply Pipe Opening 22b Oil Supply Pipe 23 Tank 24 Drainage Pipe 24a Discharge Open end of liquid pipe 25 Pressure equalizing pipe 26 Pressure equalizing mechanism 26a Float 27 Check valve mechanism 27a Valve body 27b Valve 27c Spring 27d Seat surface

Claims (2)

【特許請求の範囲】[Claims] 【請求項１】 密閉ケーシングと、前記密閉ケーシング
内に配設された圧縮要素を構成するシリンダと、前記シ
リンダ内をローラとベーンで分割形成する低圧室と高圧
室と、一端が前記密閉ケーシング外に連通し、他端が前
記シリンダに形成された吸入通路に連通した吸入パイプ
と、前記密閉ケーシング内に収納され前記吸入パイプ、
前記低圧室、前記吸入通路のいずれかより重力方向上方
に配設されたバルブ機構と、一端が前記バルブ機構より
重力方向下方に配設された前記吸入パイプ、前記低圧
室、前記吸入通路のいずれかに連通し他端が前記バルブ
機構の下部に連通した給油管と、一端が前記バルブ機構
上部に連通し他端が前記密閉ケーシング内に溜められた
潤滑油中に開口した給油路を形成する給油管と、前記バ
ルブ機構の重力方向下方に配設されたタンクと、一端が
前記バルブ機構の下部に連通し他端が前記タンク内に連
通した排液管と、一端が前記タンク内に連通し他端が前
記バルブ機構の上部に連通した均圧管と、前記バルブ機
構に連通した前記排液管の開口端に配設され潤滑油より
比重が大きく且つ液冷媒より比重が小さい材料にて形成
されたフロートで構成する均圧機構とからなる回転式圧
縮機。1. A hermetic casing, a cylinder constituting a compression element disposed in the hermetic casing, a low pressure chamber and a high pressure chamber in which the interior of the cylinder is divided by rollers and vanes, and one end of which is outside the hermetic casing. A suction pipe, the other end of which is in communication with a suction passage formed in the cylinder, and the suction pipe housed in the closed casing,
Any one of the low pressure chamber and the valve mechanism arranged above the suction passage in the gravity direction, and the suction pipe whose one end is arranged below the valve mechanism in the gravity direction, the low pressure chamber, and the suction passage. An oil supply pipe communicating with the crab and the other end communicating with the lower part of the valve mechanism, and an oil supply passage having one end communicating with the upper part of the valve mechanism and the other end opening into the lubricating oil accumulated in the closed casing. An oil supply pipe, a tank disposed below the valve mechanism in the direction of gravity, a drain pipe having one end communicating with the lower portion of the valve mechanism and the other end communicating with the tank, and one end communicating with the tank. And the other end of the pressure equalizing pipe that communicates with the upper portion of the valve mechanism, and a material that is disposed at the open end of the drainage pipe that communicates with the valve mechanism and that has a specific gravity higher than that of the lubricating oil and lower than that of the liquid refrigerant. With a float Rotary compressor comprising a pressure equalization mechanism. 【請求項２】 給油路を形成する給油管に逆止弁機構を
備えた請求項１記載の回転式圧縮機。2. A rotary compressor according to claim 1, wherein the oil supply pipe forming the oil supply passage is provided with a check valve mechanism.