JP2004100687A - Reciprocating compressor - Google Patents

Reciprocating compressor Download PDF

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Publication number
JP2004100687A
JP2004100687A JP2003073246A JP2003073246A JP2004100687A JP 2004100687 A JP2004100687 A JP 2004100687A JP 2003073246 A JP2003073246 A JP 2003073246A JP 2003073246 A JP2003073246 A JP 2003073246A JP 2004100687 A JP2004100687 A JP 2004100687A
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JP
Japan
Prior art keywords
piston
reciprocating compressor
suction
discharge
compression space
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Pending
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JP2003073246A
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Japanese (ja)
Inventor
Byung-Jik Kim
キム　ビュン−ジク
Hyon-Sok Kim
キム　ヒョン−ソク
Dong-Han Kim
キム　ドン−ハン
Jin-Sung Park
パーク　ジン−スン
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LG Electronics Inc
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LG Electronics Inc
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Publication of JP2004100687A publication Critical patent/JP2004100687A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0016—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons with valve arranged in the piston

Abstract

<P>PROBLEM TO BE SOLVED: To provide a reciprocating compressor capable of reducing noise by the buffer action of lubricating oil while allowing the smooth operation of an intake valve by reducing contact area between a piston and the intake valve. <P>SOLUTION: This reciprocating compressor is provided with a piston 142 connected to a reciprocating motor 30, reciprocated in a compression space P of a cylinder 141 and formed therein with an intake passage F communicating with the compression space P; the intake valve 143 mounted to the end face of the piston 142 to regulate the intake of gas by opening/closing the intake passage F of the piston 142; a discharge valve assembly 70 mounted to the discharge side of the cylinder 141 to regulate the discharge of gas by opening/closing the compression space P; and an adhesion preventive part formed at a contact part between the end face of the piston and the intake valve 143 to reduce the contact area between the piston 142 and the intake valve 143 and to minimize the adhesion of lubricating oil. <P>COPYRIGHT: (C)2004,JPO

Description

【０００１】
【発明の属する技術分野】
本発明は往復動式圧縮機に関し、より詳細には、ピストンと吸入バルブとの接触面積を低減し、吸入バルブの動作を円滑にし得る往復動式圧縮機に関する。
【０００２】
【従来の技術】
一般に、冷凍サイクル装置を構成する圧縮機は、増発器から流入する低温、低圧状態の冷媒ガスを圧縮して高温・高圧の状態で吐出する機器である。
圧縮機は、流体を圧縮する方式によって回転式圧縮機、往復動式圧縮機、スクロール圧縮機等に分類することができる。
【０００３】
特に、往復動式圧縮機は、ピストンが線形に動きながら流体を吸入、圧縮するものであって、駆動モータの回転運動をピストンの往復運動に変換して流体を吸入、圧縮する方式のものと、駆動モータが直線往復運動しながらピストンを往復運動させ、流体を吸入、圧縮する方式のものとに大別される。
【０００４】
図９は、従来の往復動式圧縮機の内部を示す縦断面図で、図１０は、図９におけるピストンと吸入バルブとの取り付けを示す分解斜視図で、図１１は、図９における吸入行程を示す縦断面図で、図１２は、図９における圧縮行程を示す縦断面図である。
【０００５】
図示するように、従来の往復動式圧縮機は、ガス吸入管ＳＰ及びガス吐出管ＤＰを有するケース１０と、ケース１０の内部に弾力的に設けられるフレームユニット２０と、フレームユニット２０に固定され、可動子３３が直線往復運動する往復動式モータ３０と、往復動式モータ３０の可動子３３に連結され、かつ、フレームユニット２０により支持される圧縮ユニット４０と、往復動式モータ３０の可動子３３を運動方向に付勢し、共振運動を誘導する共振スプリングユニット５０とから構成される。
【０００６】
圧縮ユニット４０は、前方フレーム２１に一体形成されるシリンダ４１と、往復動式モータ３０の可動子３３に連結されてシリンダ４１の圧縮空間Ｐで往復運動をするピストン４２と、ピストン４２の先端に設けられて該ピストン４２の吸入流路Ｆを開閉し、ガスの吸入を調節する吸入バルブ４３と、シリンダ４１の吐出側に設けられて圧縮空間Ｐを開閉し、ガスの吐出を調節する吐出バルブ組立体７０とから構成されている。
【０００７】
吐出バルブ組立体７０は、シリンダ４１の圧縮空間Ｐをカバーする吐出カバー７１と、吐出カバー７１の内部に配備され、圧縮空間Ｐを弾力的に開閉する吐出バルブ７２とからなる。
【０００８】
吸入バルブ４３は円形の薄板状に形成されており、その中には、切開溝４３ａが設けられる。吸入バルブ４３は、切開溝４３ａにより固定部４３ｂと開閉部４３ｃとに分けられる。吸入バルブ４３は、ピストンの端面４６に面接触するボルトＢによってピストンの端面４６に固定される。
【０００９】
上記のように構成された従来の往復動式圧縮機の作用について説明する。
往復動式モータ３０の駆動力によってピストン４２がシリンダ４１の内部で往復動することにより圧縮空間Ｐの体積を変化させながらガスを圧縮空間Ｐに吸入、圧縮する。
【００１０】
ガスの圧力が所定圧力以上になると、吐出バルブ組立体７０の吐出カバー７２が開かれて圧縮ガスが吐出され、この一連の過程が繰り返し実施される。
ピストン４２が下死点／位置ａに達すると、圧力差により吐出バルブ組立体７０の吐出バルブ７２がシリンダ４１の圧縮空間Ｐを閉鎖すると同時に、ピストン４２に取り付けられた吸入バルブ４３の開閉部４３ｃが湾曲し、吸入流路Ｆを開放する。この時、ガスがピストン４２の吸入流路Ｆを通じてシリンダ４２の圧縮空間Ｐ内に吸入される。
【００１１】
次いで、ピストン４２が上死点ｂに達すると、吸入バルブ４３が元の状態に復帰してピストン４２の吸入流路Ｆを閉鎖し、圧縮空間Ｐに吸入されたガスを圧縮する。ガスの圧力が所定圧力以上となると、吐出バルブ組立体７０の吐出カバー７２が開放されて圧縮ガスを吐出する。
【００１２】
通常、ピストンの往復運動を円滑にするために、吸入バルブ４３とピストン端面４６との間に潤滑油が供給される。従来の往復動式圧縮機では、その潤滑油の粘性のために、吸入バルブ４３がピストンの端面４６に一時的に付着することがある。
【００１３】
【発明が解決しようとする課題】
吸入バルブ４３がピストンの端面４６に付着すると、吸入流路Ｆが正常状態より遅れて開放されるのみならず、より大きく開かれることにより、圧縮機の圧縮効率を低減するという問題がある。
【００１４】
本発明は、このような従来の課題に鑑みてなされたもので、ピストンの端面と吸入バルブの接触面積を低減して、潤滑油による粘着力を弱めることによって、吸入バルブを円滑に動作するとともに、潤滑油の緩衝作用によって騷音を低減し得る往復動式圧縮機を提供することを目的とする。
【００１５】
【課題を解決するための手段】
このような目的を達成するため、本発明に係る往復動式圧縮機は、往復動式モータに連結されてシリンダの圧縮空間で往復運動し、内部には、前記圧縮空間と連通する吸入流路が形成されたピストンと、前記ピストンの端面に装着されてそのピストンの吸入流路を開閉し、ガスの吸入を調節する吸入バルブと、前記シリンダの吐出側に装着されて圧縮空間を開閉し、ガスの吐出を調節する吐出バルブ組立体と、前記ピストンと前記吸入バルブの接触面積を低減し、潤滑油の粘着を最小化するように、前記ピストンの端面と前記吸入バルブとの接触部分に形成された粘着防止部とを具備する。
【００１６】
【発明の実施の形態】
以下、添付図面を参照して、本発明の実施形態をより詳細に説明する。
図１は、本発明の一実施形態による往復動式圧縮機の内部を示した縦断面図で、図２は、図１の往復動圧縮機のピストンと吸入バルブとの取り付けを示す分解斜視図で、図３は、図１の往復動圧縮機のピストンの端面を示す正面図で、図４は、図１の往復動圧縮機の吸入行程を示す縦断面図で、図５は、図１の往復動圧縮機の圧縮行程を示す縦断面図である。
【００１７】
図示するように、本発明の往復動圧縮機は、ガス吸入管ＳＰ及びガス吐出管ＤＰを有するケース１０と、ケース１０の内部に弾力的に設置されるフレームユニット２０と、フレームユニット２０に固定されて可動子（図示せず）が直線往復運動する往復動式モータ３０と、往復動式モータ３０の可動子に連結され、かつ、フレームユニット２０により支持される圧縮ユニット１４０と、往復動式モータ３０の可動子を運動方向に付勢し、共振運動を誘導する共振スプリングユニット５０とから構成される。
【００１８】
圧縮ユニット１４０は、フレームユニット２０に一体形成されるシリンダ１４１と、往復動式モータ３０の可動子に連結されてシリンダ１４１の圧縮空間Ｐで往復運動するピストン１４２と、ピストン１４２の先端に装着されてそのピストン１４２の吸入流路Ｆを開閉することによってガスの吸入を調節する吸入バルブ１４３と、シリンダ１４１の吐出側に装着されて圧縮空間Ｐを開閉することによって圧縮ガスの吐出を調節する吐出バルブ組立体１７０とから形成されている。
【００１９】
ピストン１４２は、所定長さを有し、シリンダ１４１の内部に挿入されるヘッド部１４５と、ヘッド部１４５の一方の端部に設けられて圧縮空間Ｐを形成するピストン端面１４６と、ヘッド部１４５の他方には前記可動子に連結するようにその長手方向に直交するように所定面積を有して形成された連結部１４７とで構成される。
【００２０】
ガスが流れる吸入流路Ｆが、ヘッド部１４５の内部からピストン端面１４６に達するまで形成される。
吐出バルブ組立体１７０は、シリンダ１４１の圧縮空間Ｐを覆う吐出カバー１７１と、吐出カバー１７１の内部に配設され、圧縮空間Ｐを弾力的に開閉する吐出バルブ１７２とからなる。
【００２１】
吸入バルブ１４３は円形の薄板状に形成され、その中間には、切開溝１４３ａが設けられる。吸入バルブ１４３は、その切開溝１４３ａにより固定部１４３ｂと開閉部１４３ｃとに分けられる。吸入バルブ１４３は、ピストン端面１４６に面接触された状態で、ボルトＢによってピストンの端面１４６に固定される。
【００２２】
即ち、吸入行程時には、圧力差によって吸入バルブ１４３が吸入流路Ｆを開放し、また圧縮行程時には、圧力差によって吸入バルブ１４３が吸入流路Ｆを遮断するように構成される。
【００２３】
本発明では、吸入バルブ１４３との接触面積を低減し、潤滑油の粘性による付着作用を最小化するように、ピストンの端面１４６と吸入バルブ１４３の接触部とに粘着防止部が形成される。
前記粘着防止部を形成する場合において、ピストン端面１４６と吸入バルブ１４３との接触部の一方または両方に粘着防止部を形成することができる。
【００２４】
本発明の一実施形態に係る往復動式圧縮機では、図１〜図５に示すように粘着防止部として、ピストン端面１４６に所定深さで設けられた粘着防止溝１４６ａが形成されている。
粘着防止溝１４６ａの深さは、潤滑油の粘性に影響を与えない範囲内で決められるが、約２０〜２００μｍ程度と微細に形成することが望ましい。
【００２５】
さらに、粘着防止溝１４６ａに流入した潤滑油が、吸入流路Ｆ側に流入しないように、ピストンの端面１４６に位置する吸入流路Ｆの端部に、流入防止突条１４６ｂが突出形成される。
吸入バルブ１４３によって吸入流路Ｆが選択的に開閉できるように流入防止突条１４６ｂは、ピストン端面１４６と同一な垂直面上に配置される。
【００２６】
図６は、本発明の他の実施例に係る往復動式圧縮機の一部を示した縦断面図で、図７は、図６の往復動圧縮機のピストンと吸入バルブとの取り付けを示した分解斜視図である。
【００２７】
図示するように、本発明の他の実施例に係る往復動式圧縮機では、粘着防止のために、ピストンの端面１４６に所定深さで設けられた粘着防止溝１５６ａが形成されている。粘着防止溝１５６ａは、ピストンの端面１４６の上端一部に形成されている。
【００２８】
これは、吸入行程時に吸入バルブ１４３が吸入流路Ｆを適時に開放し、また圧縮行程時には吸入バルブ１４３がガスが漏れないように吸入流路Ｆを気密に遮断し得るようにするためである。
【００２９】
粘着防止溝１５６ａの深さは、潤滑油の粘性に影響を与えない範囲内で決められるが、概ね２０〜２００μｍ程度と微細に形成することが望ましい。さらに、粘着防止溝１５６ａに流入した潤滑油が、吸入流路Ｆ側に流入しないように、ピストンの端面１４６に位置した吸入流路Ｆの端部にガス逆流防止突条１５６ｂが突出形成される。
吸入バルブ１４３によって吸入流路Ｆが選択的に開閉されるようにガス逆流防止突条１５６ｂは、ピストン端面１４６と同一な垂直面上に位置される。
【００３０】
図８は、本発明の更に他の実施形態に係る往復動式圧縮機を示すものである。図示するように、本発明の他の実施形態では、粘着防止溝１６６ａが吸入バルブ１４３に形成されている。
【００３１】
粘着防止溝１６６ａも約２０〜２００μｍ程度と微細に形成されることが望ましい。
以下、本発明の一実施形態に係る往復動式圧縮機の作用について説明する。
【００３２】
往復動式モータ３０の駆動力によってピストン１４２がシリンダ１４１の内部で往復運動し、圧縮空間Ｐの体積を変化させながらガスを圧縮空間Ｐに吸入、圧縮する。ガスの圧力が所定圧力以上となると、吐出バルブ組立体１７０が開かれ、圧縮ガスを吐出する。こうした一連の過程が繰り返し実施される。
【００３３】
すなわち、ピストン１４２が下死点ａに達すると、圧力差により吐出バルブ組立体１７０がシリンダ１４１の圧縮空間Ｐを閉じると同時に、ピストン１４２に取り付けられた吸入バルブ１４３の開閉部１４３ｃが湾曲して吸入流路Ｆが開放される。この時、ピストン１４２の吸入流路Ｆを通じてガスがシリンダ１４２の圧縮空間Ｐの内部に吸入される。
【００３４】
本発明では、ピストン１４２の端面１４６に粘着防止溝１４６ａが形成されているため、その分だけ吸入バルブ１４３とピストンの端面１４６との接触面積が低減される。
すなわち、潤滑油の粘着力は、接触面積に比例するので吸入バルブ１４３は、潤滑油の粘着力に影響されず、適時に吸入流路Ｆを開放することができる。
【００３５】
次いで、ピストン１４２が上死点ｂに達すると、吸入バルブ１４３が元の状態に復帰しながらピストン１４２の吸入流路Ｆが閉鎖し、圧縮空間Ｐに吸入されているガスを圧縮する。ガスの圧力が所定圧力以上になると、吐出バルブ組立体１７０の吐出カバー１７２が開かれて圧縮されたガスを吐出する。
【００３６】
上述したように、吸入行程から圧縮行程に転じる時、湾曲していた吸入バルブ１４３の開閉部１４３ｃは元の状態に復帰する。この時、粘着防止溝１４６ａに溜まっている潤滑油によって緩衝される。即ち、潤滑油によって吸入バルブ１４３の開閉部１４３ｃとピストン端面１４６との接触面積が減少し、チャタリング（Ｃｈａｔｔｅｒｉｎｇ）騷音を与える少なくすることができる。
【００３７】
【発明の効果】
以上説明したように、本発明によると潤滑油の粘着力を少なくし、吸入バルブ１４３が適時に開かれるため、圧縮性能を高め、製品の信頼性を向上し得るとの効果を奏する。
また、本発明によれば、潤滑油の緩衝作用によって、ピストン１４２と吸入バルブ１４３との接触により発生するチャタリング騷音を低減し得るという効果を奏する。
【図面の簡単な説明】
【図１】本発明の一実施形態に係る往復動式圧縮機の内部を示した縦断面図である。
【図２】図１の往復動式圧縮機におけるピストンと吸入バルブとの取り付けを示す分解斜視図である。
【図３】図１の往復動式圧縮機におけるピストンの端面を示す正面図である。
【図４】図１の往復動式圧縮機における吸入行程を示す縦断面図である。
【図５】図１の往復動式圧縮機における圧縮行程を示す縦断面図である。
【図６】本発明の他の実施形態に係る往復動式圧縮機の一部を図示した縦断面図である。
【図７】図６の往復動式圧縮機におけるピストンと吸入バルブとの取り付けを示した分解斜視図である。
【図８】本発明の更に他の実施形態に係る往復動式圧縮機の一部を図示した縦断面図である。
【図９】従来の往復動式圧縮機の内部を示した縦断面図である。
【図１０】図９の往復動式圧縮機におけるピストンと吸入バルブの取り付けを示す分解斜視図である。
【図１１】図９の往復動式圧縮機における吸入行程を示す縦断面図である。
【図１２】図９の往復動式圧縮機における圧縮行程を示す縦断面図である。
【符号の説明】
１４０…圧縮ユニット
１４１…シリンダ
１４２…ピストン
１４３…吸入バルブ
１４３ａ…切開溝
１４３ｂ…固定部
１４３ｃ…開閉部
１４５…ヘッド部
１４６…ピストンの端面
１４６ａ…粘着防止溝
１５６ａ…粘着防止溝[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a reciprocating compressor, and more particularly, to a reciprocating compressor capable of reducing the contact area between a piston and a suction valve and smoothing the operation of the suction valve.
[0002]
[Prior art]
Generally, a compressor that constitutes a refrigeration cycle apparatus is a device that compresses a low-temperature, low-pressure refrigerant gas flowing from an expander and discharges the refrigerant gas at a high-temperature, high-pressure state.
Compressors can be classified into rotary compressors, reciprocating compressors, scroll compressors, and the like according to the method of compressing a fluid.
[0003]
In particular, a reciprocating compressor is a type that sucks and compresses fluid while a piston moves linearly, and a type that sucks and compresses fluid by converting the rotational motion of a drive motor into reciprocating motion of a piston. The driving motor is roughly classified into a method in which a piston reciprocates while a driving motor linearly reciprocates to suck and compress a fluid.
[0004]
FIG. 9 is a longitudinal sectional view showing the inside of a conventional reciprocating compressor, FIG. 10 is an exploded perspective view showing attachment of a piston and a suction valve in FIG. 9, and FIG. 11 is a suction stroke in FIG. FIG. 12 is a longitudinal sectional view showing a compression stroke in FIG.
[0005]
As shown in the figure, a conventional reciprocating compressor includes a case 10 having a gas suction pipe SP and a gas discharge pipe DP, a frame unit 20 elastically provided inside the case 10, and a frame unit 20 fixed to the frame unit 20. A reciprocating motor 30 in which the mover 33 linearly reciprocates; a compression unit 40 connected to the mover 33 of the reciprocating motor 30 and supported by the frame unit 20; And a resonance spring unit 50 that urges the child 33 in the movement direction and induces a resonance movement.
[0006]
The compression unit 40 includes a cylinder 41 integrally formed with the front frame 21, a piston 42 connected to the mover 33 of the reciprocating motor 30 and reciprocating in the compression space P of the cylinder 41, and A suction valve 43 provided to open and close the suction flow path F of the piston 42 to adjust the suction of gas, and a discharge valve provided at the discharge side of the cylinder 41 to open and close the compression space P to adjust the discharge of gas. And an assembly 70.
[0007]
The discharge valve assembly 70 includes a discharge cover 71 that covers the compression space P of the cylinder 41, and a discharge valve 72 that is provided inside the discharge cover 71 and that elastically opens and closes the compression space P.
[0008]
The suction valve 43 is formed in a circular thin plate shape, and a cutout groove 43a is provided therein. The suction valve 43 is divided into a fixed portion 43b and an opening / closing portion 43c by an incision groove 43a. The suction valve 43 is fixed to the piston end surface 46 by a bolt B that comes into surface contact with the piston end surface 46.
[0009]
The operation of the conventional reciprocating compressor configured as described above will be described.
The piston 42 reciprocates inside the cylinder 41 by the driving force of the reciprocating motor 30, thereby changing the volume of the compression space P and sucking and compressing gas into the compression space P.
[0010]
When the pressure of the gas becomes equal to or higher than the predetermined pressure, the discharge cover 72 of the discharge valve assembly 70 is opened to discharge the compressed gas, and this series of processes is repeatedly performed.
When the piston 42 reaches the bottom dead center / position a, the pressure difference causes the discharge valve 72 of the discharge valve assembly 70 to close the compression space P of the cylinder 41, and at the same time, the opening / closing portion 43c of the suction valve 43 attached to the piston 42. Is curved, and the suction passage F is opened. At this time, the gas is sucked into the compression space P of the cylinder 42 through the suction passage F of the piston 42.
[0011]
Next, when the piston 42 reaches the top dead center b, the suction valve 43 returns to the original state, closes the suction passage F of the piston 42, and compresses the gas sucked into the compression space P. When the gas pressure exceeds a predetermined pressure, the discharge cover 72 of the discharge valve assembly 70 is opened to discharge the compressed gas.
[0012]
Usually, lubricating oil is supplied between the suction valve 43 and the piston end surface 46 in order to smooth the reciprocating motion of the piston. In a conventional reciprocating compressor, the suction valve 43 may temporarily adhere to the end face 46 of the piston due to the viscosity of the lubricating oil.
[0013]
[Problems to be solved by the invention]
If the suction valve 43 adheres to the end face 46 of the piston, there is a problem that not only the suction flow path F is opened later than the normal state, but also the compression efficiency of the compressor is reduced by opening the suction flow path F more widely.
[0014]
The present invention has been made in view of such a conventional problem, and reduces the contact area between the end face of the piston and the suction valve to reduce the adhesive force of the lubricating oil, thereby allowing the suction valve to operate smoothly. It is another object of the present invention to provide a reciprocating compressor capable of reducing noise by a lubricating oil buffering action.
[0015]
[Means for Solving the Problems]
In order to achieve such an object, the reciprocating compressor according to the present invention is connected to a reciprocating motor and reciprocates in a compression space of a cylinder. Formed with a piston, mounted on an end face of the piston to open and close a suction flow path of the piston, and a suction valve for adjusting gas suction, and mounted on a discharge side of the cylinder to open and close a compression space, A discharge valve assembly for controlling the discharge of gas, and a contact area between the end face of the piston and the suction valve so as to reduce a contact area between the piston and the suction valve and minimize sticking of lubricating oil. And a provided anti-adhesion part.
[0016]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described in more detail with reference to the accompanying drawings.
FIG. 1 is a longitudinal sectional view showing the inside of a reciprocating compressor according to an embodiment of the present invention, and FIG. 2 is an exploded perspective view showing attachment of a piston and a suction valve of the reciprocating compressor of FIG. 3 is a front view showing an end face of a piston of the reciprocating compressor shown in FIG. 1, FIG. 4 is a longitudinal sectional view showing a suction stroke of the reciprocating compressor shown in FIG. 1, and FIG. It is a longitudinal cross-sectional view which shows the compression stroke of the reciprocating compressor of FIG.
[0017]
As shown in the drawing, a reciprocating compressor of the present invention includes a case 10 having a gas suction pipe SP and a gas discharge pipe DP, a frame unit 20 resiliently installed inside the case 10, and fixed to the frame unit 20. A reciprocating motor 30 in which a movable element (not shown) linearly reciprocates; a compression unit 140 connected to the movable element of the reciprocating motor 30 and supported by the frame unit 20; And a resonance spring unit 50 that urges the mover of the motor 30 in the direction of movement and induces resonance movement.
[0018]
The compression unit 140 includes a cylinder 141 integrally formed with the frame unit 20, a piston 142 connected to a movable element of the reciprocating motor 30 and reciprocating in a compression space P of the cylinder 141, and mounted on a tip of the piston 142. A suction valve 143 for adjusting the suction of gas by opening and closing the suction passage F of the piston 142, and a discharge valve mounted on the discharge side of the cylinder 141 to adjust the discharge of compressed gas by opening and closing the compression space P. And a valve assembly 170.
[0019]
The piston 142 has a predetermined length, a head part 145 inserted into the cylinder 141, a piston end face 146 provided at one end of the head part 145 to form a compression space P, and a head part 145. And a connecting portion 147 formed to have a predetermined area perpendicular to the longitudinal direction so as to be connected to the mover.
[0020]
A suction flow path F through which gas flows is formed from inside the head portion 145 to the piston end surface 146.
The discharge valve assembly 170 includes a discharge cover 171 that covers the compression space P of the cylinder 141, and a discharge valve 172 that is disposed inside the discharge cover 171 and that elastically opens and closes the compression space P.
[0021]
The suction valve 143 is formed in a circular thin plate shape, and an incision groove 143a is provided in the middle thereof. The suction valve 143 is divided into a fixed portion 143b and an opening / closing portion 143c by the cut groove 143a. The suction valve 143 is fixed to the piston end surface 146 by bolts B in a state of being in surface contact with the piston end surface 146.
[0022]
That is, during the suction stroke, the suction valve 143 opens the suction passage F due to the pressure difference, and during the compression stroke, the suction valve 143 shuts off the suction passage F due to the pressure difference.
[0023]
In the present invention, an anti-adhesion part is formed between the end face 146 of the piston and the contact part of the suction valve 143 so as to reduce the contact area with the suction valve 143 and minimize the adhesion effect due to the viscosity of the lubricating oil.
When forming the anti-adhesion portion, the anti-adhesion portion can be formed on one or both of the contact portions between the piston end surface 146 and the suction valve 143.
[0024]
In the reciprocating compressor according to one embodiment of the present invention, as shown in FIGS. 1 to 5, an anti-adhesion groove 146 a provided at a predetermined depth on the piston end surface 146 is formed as an anti-adhesion portion.
The depth of the anti-adhesion groove 146a is determined within a range that does not affect the viscosity of the lubricating oil, but is desirably formed as fine as about 20 to 200 μm.
[0025]
Further, an inflow prevention ridge 146b is formed at an end of the suction passage F located at the end face 146 of the piston so that the lubricating oil flowing into the anti-adhesion groove 146a does not flow into the suction passage F. .
The inflow prevention ridge 146 b is arranged on the same vertical plane as the piston end surface 146 so that the suction flow path F can be selectively opened and closed by the suction valve 143.
[0026]
FIG. 6 is a longitudinal sectional view showing a part of a reciprocating compressor according to another embodiment of the present invention, and FIG. 7 shows attachment of a piston and a suction valve of the reciprocating compressor of FIG. FIG.
[0027]
As shown in the drawing, in a reciprocating compressor according to another embodiment of the present invention, an anti-adhesion groove 156a provided at a predetermined depth on an end surface 146 of the piston is formed to prevent adhesion. The anti-adhesion groove 156a is formed at a part of the upper end of the end surface 146 of the piston.
[0028]
This is because the suction valve 143 can open the suction passage F in a timely manner during the suction stroke, and the suction valve F 143 can airtightly shut off the suction passage F during the compression stroke so that gas does not leak. .
[0029]
The depth of the anti-adhesion groove 156a is determined within a range that does not affect the viscosity of the lubricating oil, but is desirably formed to be as fine as about 20 to 200 μm. Further, a gas backflow prevention ridge 156b is formed at an end of the suction passage F located on the end face 146 of the piston so as to prevent the lubricating oil flowing into the anti-adhesion groove 156a from flowing into the suction passage F. .
The gas backflow prevention ridge 156b is located on the same vertical plane as the piston end surface 146 so that the suction flow path F is selectively opened and closed by the suction valve 143.
[0030]
FIG. 8 shows a reciprocating compressor according to still another embodiment of the present invention. As shown, in another embodiment of the present invention, an anti-adhesion groove 166a is formed in the suction valve 143.
[0031]
It is desirable that the anti-adhesion groove 166a is also formed as fine as about 20 to 200 μm.
Hereinafter, the operation of the reciprocating compressor according to one embodiment of the present invention will be described.
[0032]
The piston 142 reciprocates inside the cylinder 141 by the driving force of the reciprocating motor 30, and sucks and compresses gas into the compression space P while changing the volume of the compression space P. When the gas pressure exceeds a predetermined pressure, the discharge valve assembly 170 is opened to discharge the compressed gas. Such a series of processes is repeatedly performed.
[0033]
That is, when the piston 142 reaches the bottom dead center a, the pressure difference causes the discharge valve assembly 170 to close the compression space P of the cylinder 141, and at the same time, the opening / closing portion 143c of the suction valve 143 attached to the piston 142 curves. The suction passage F is opened. At this time, gas is sucked into the compression space P of the cylinder 142 through the suction passage F of the piston 142.
[0034]
In the present invention, since the anti-adhesion groove 146a is formed on the end face 146 of the piston 142, the contact area between the suction valve 143 and the end face 146 of the piston is reduced by that much.
That is, since the adhesive force of the lubricating oil is proportional to the contact area, the suction valve 143 can open the suction flow path F at an appropriate time without being affected by the adhesive force of the lubricating oil.
[0035]
Next, when the piston 142 reaches the top dead center b, the suction valve F returns to the original state, the suction passage F of the piston 142 closes, and the gas sucked into the compression space P is compressed. When the pressure of the gas exceeds a predetermined pressure, the discharge cover 172 of the discharge valve assembly 170 is opened to discharge the compressed gas.
[0036]
As described above, when switching from the suction stroke to the compression stroke, the opening / closing portion 143c of the curved suction valve 143 returns to the original state. At this time, it is buffered by the lubricating oil stored in the anti-adhesion groove 146a. That is, the contact area between the opening / closing portion 143c of the suction valve 143 and the piston end surface 146 is reduced by the lubricating oil, and chattering noise can be reduced.
[0037]
【The invention's effect】
As described above, according to the present invention, the adhesive force of the lubricating oil is reduced and the suction valve 143 is opened in a timely manner, so that the compression performance is improved and the reliability of the product can be improved.
Further, according to the present invention, the chattering noise generated by the contact between the piston 142 and the suction valve 143 can be reduced by the lubricating oil buffering effect.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view showing the inside of a reciprocating compressor according to one embodiment of the present invention.
FIG. 2 is an exploded perspective view showing attachment of a piston and a suction valve in the reciprocating compressor of FIG.
FIG. 3 is a front view showing an end face of a piston in the reciprocating compressor of FIG. 1;
FIG. 4 is a longitudinal sectional view showing a suction stroke in the reciprocating compressor of FIG.
FIG. 5 is a longitudinal sectional view showing a compression stroke in the reciprocating compressor of FIG.
FIG. 6 is a longitudinal sectional view illustrating a part of a reciprocating compressor according to another embodiment of the present invention.
FIG. 7 is an exploded perspective view showing attachment of a piston and a suction valve in the reciprocating compressor of FIG. 6;
FIG. 8 is a longitudinal sectional view illustrating a part of a reciprocating compressor according to still another embodiment of the present invention.
FIG. 9 is a longitudinal sectional view showing the inside of a conventional reciprocating compressor.
FIG. 10 is an exploded perspective view showing attachment of a piston and a suction valve in the reciprocating compressor of FIG. 9;
FIG. 11 is a longitudinal sectional view showing a suction stroke in the reciprocating compressor of FIG. 9;
FIG. 12 is a longitudinal sectional view showing a compression stroke in the reciprocating compressor of FIG. 9;
[Explanation of symbols]
140 compression unit 141 cylinder 142 piston 143 suction valve 143a incision groove 143b fixing part 143c opening / closing part 145 head part 146 piston end surface 146a anti-adhesion groove 156a anti-adhesion groove

Claims (7)

往復動式モータに連結されてシリンダの圧縮空間で往復運動をする、かつ内部に前記圧縮空間と連通する吸入流路が形成されたピストンと、前記ピストンの端面に装着されてそのピストンの吸入流路を開閉することによってガスの吸入を調節する吸入バルブと、
前記シリンダの吐出側に装着されて圧縮空間を開閉することによってガスの吐出を調節する吐出バルブ組立体と、
前記ピストンと前記吸入バルブとの接触面積を低減し、潤滑油の粘着を最小化できるように前記ピストン端面と前記吸入バルブとの接触部分に形成された粘着防止部を含む往復動式圧縮機。A piston connected to a reciprocating motor and reciprocating in a compression space of a cylinder and having a suction flow passage formed therein and communicating with the compression space; and a suction flow of the piston mounted on an end face of the piston. An intake valve that regulates gas intake by opening and closing a path;
A discharge valve assembly mounted on the discharge side of the cylinder to control gas discharge by opening and closing a compression space;
A reciprocating compressor including an anti-adhesion portion formed at a contact portion between the piston end surface and the suction valve so as to reduce a contact area between the piston and the suction valve and minimize adhesion of lubricating oil. 前記粘着防止部は、ピストンの端面に形成されていることを特徴とする請求項１記載の往復動式圧縮機。The reciprocating compressor according to claim 1, wherein the anti-adhesion portion is formed on an end surface of the piston. 前記粘着防止部は、溝であることを特徴とする請求項２記載の往復動式圧縮機。The reciprocating compressor according to claim 2, wherein the anti-adhesion portion is a groove. 前記粘着防止部は、深さ２０〜２００μｍの溝であることを特徴とする請求項３記載の往復動式圧縮機。The reciprocating compressor according to claim 3, wherein the anti-adhesion portion is a groove having a depth of 20 to 200 μm. 前記ピストンの前面に位置する吸入流路の端部には、ガス逆流防止のための突条が形成されていることを特徴とする請求項１記載の往復動式圧縮機。2. The reciprocating compressor according to claim 1, wherein a ridge for preventing gas backflow is formed at an end of the suction flow path located in front of the piston. 前記粘着防止部は、前記吸入バルブに形成されていることを特徴とする請求項５記載の往復動式圧縮機。The reciprocating compressor according to claim 5, wherein the anti-adhesion portion is formed on the suction valve. 前記粘着防止部は、溝であることを特徴とする請求項６記載の往復動式圧縮機。The reciprocating compressor according to claim 6, wherein the anti-adhesion portion is a groove.
JP2003073246A 2002-09-07 2003-03-18 Reciprocating compressor Pending JP2004100687A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006057634A (en) * 2004-08-16 2006-03-02 Lg Electronics Inc Refrigerant suction guide structure for reciprocating compressor
KR101179076B1 (en) * 2005-05-06 2012-09-03 엘지전자 주식회사 Structure for reducing noise of piston in reciprocating compressor
JP2015010611A (en) * 2013-06-28 2015-01-19 エルジー エレクトロニクス インコーポレイティド Linear compressor

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20050056601A (en) * 2003-12-10 2005-06-16 엘지전자 주식회사 A reciprocating compressor
JP5073989B2 (en) * 2005-11-14 2012-11-14 エルジー エレクトロニクス インコーポレイティド Linear compressor
CN203835658U (en) 2013-06-28 2014-09-17 Lg电子株式会社 Linear compressor
CN104251193A (en) 2013-06-28 2014-12-31 Lg电子株式会社 Linear compressor
CN203906210U (en) 2013-06-28 2014-10-29 Lg电子株式会社 Linear compressor
CN104251196B (en) 2013-06-28 2016-10-05 Lg电子株式会社 Linearkompressor
CN104251191B (en) 2013-06-28 2017-05-03 Lg电子株式会社 Linear compressor
JP6580450B2 (en) * 2015-10-23 2019-09-25 住友重機械工業株式会社 Valve structure, non-lubricated linear compressor, and cryogenic refrigerator
CN117231470A (en) * 2023-11-13 2023-12-15 瑞纳智能设备股份有限公司 Gas bearing device of compressor and compressor

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE653720C (en) * 1936-10-01 1937-12-01 Robert Bosch Akt Ges Compressor valve, especially for refrigeration machines
DE2162031A1 (en) * 1971-12-10 1973-06-14 Auergesellschaft Gmbh DIAPHRAGM PUMP
JPS5612074A (en) * 1979-07-09 1981-02-05 Hitachi Ltd Valve seat for full-enclose type motor-driven compressor
JPS57195883A (en) * 1981-05-26 1982-12-01 Honda Motor Co Ltd Compressor
US4580604A (en) * 1983-06-23 1986-04-08 Mitsubishi Denki Kabushiki Kaisha Discharging valve device for a compressor
JPH0196479A (en) * 1987-10-05 1989-04-14 Toyota Autom Loom Works Ltd Valve device for compressor
KR910007990Y1 (en) * 1989-06-22 1991-10-10 박춘식 Shock-absorber
US5078582A (en) * 1990-01-16 1992-01-07 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Reciprocatory piston type compressor having a noise and vibration suppressed discharge valve mechanism
CN2105573U (en) * 1991-08-05 1992-05-27 高信泉 Reciprocating double-cylinder compression engine
US5203686A (en) * 1991-11-04 1993-04-20 General Electric Company Rotary compressor with span type discharge valve
US5163819A (en) * 1992-02-07 1992-11-17 General Motors Corporation Asymmetrical suction porting for swash plate compressor
JPH062654A (en) * 1992-06-18 1994-01-11 Nippondenso Co Ltd Compressor
JPH06101644A (en) * 1992-09-21 1994-04-12 Sanden Corp Delivery valve for gas compressor
KR200154567Y1 (en) * 1995-06-03 1999-08-16 윤종용 A discharge valve device of a compressor
JP3301895B2 (en) * 1995-09-05 2002-07-15 三洋電機株式会社 Hermetic compressor
CN2289077Y (en) * 1996-11-14 1998-08-26 陈启明 Piston for air compressor
DE19706066A1 (en) * 1997-02-17 1997-11-20 Hans Dipl Ing Unger Compressor providing compressed air in vehicle
DE19732808A1 (en) * 1997-07-30 1999-02-04 Knf Neuberger Gmbh Method for evacuating the sterilisation chamber of a steam sterilisation unit - with the medium used during evacuation cooled along its flow path in such a way that it is in or is converted into a liquid state in the delivery unit
KR100480086B1 (en) * 1998-01-12 2005-06-08 엘지전자 주식회사 Suction loss reduction structure of linear compressor
JP2000186670A (en) * 1998-12-22 2000-07-04 Tokico Ltd Reciprocating compressor

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006057634A (en) * 2004-08-16 2006-03-02 Lg Electronics Inc Refrigerant suction guide structure for reciprocating compressor
KR101179076B1 (en) * 2005-05-06 2012-09-03 엘지전자 주식회사 Structure for reducing noise of piston in reciprocating compressor
JP2015010611A (en) * 2013-06-28 2015-01-19 エルジー エレクトロニクス インコーポレイティド Linear compressor
US10634127B2 (en) 2013-06-28 2020-04-28 Lg Electronics Inc. Linear compressor

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US20040047750A1 (en) 2004-03-11
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DE10312355A1 (en) 2004-03-18
CN1480648A (en) 2004-03-10
KR20040022787A (en) 2004-03-18
BR0300317B1 (en) 2013-01-08

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