JP3772283B2 - Reciprocating compressor - Google Patents

Reciprocating compressor Download PDF

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Publication number
JP3772283B2
JP3772283B2 JP34584097A JP34584097A JP3772283B2 JP 3772283 B2 JP3772283 B2 JP 3772283B2 JP 34584097 A JP34584097 A JP 34584097A JP 34584097 A JP34584097 A JP 34584097A JP 3772283 B2 JP3772283 B2 JP 3772283B2
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Japan
Prior art keywords
valve
discharge
stopper
portions
fulcrum
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JP34584097A
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JPH11166479A (en
Inventor
壱 田畑
清司 吉井
勝利 榎本
克彦 新井
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Valeo Thermal Systems Japan Corp
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Valeo Thermal Systems Japan Corp
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Priority to JP34584097A priority Critical patent/JP3772283B2/en
Priority to KR1020007000592A priority patent/KR20010022024A/en
Priority to PCT/JP1998/005402 priority patent/WO1999028628A1/en
Publication of JPH11166479A publication Critical patent/JPH11166479A/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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members

Description

【０００１】
【発明の属する技術分野】
この発明は斜板式圧縮機、揺動板式圧縮機等の往復式圧縮機に関する。
【０００２】
【従来の技術】
斜板式圧縮機は、シリンダブロックとシリンダヘッドとの間に配置され、圧縮室と吐出室及び吸入室とを仕切るバルブプレートと、圧縮室の冷媒ガスを吐出室に吐出するための吐出ポートと、吐出ポートを開閉する吐出弁と、弁部の開き量を抑制するストッパプレートとを備える。
【０００３】
図５は従来の斜板式圧縮機のバルブプレートと弁シートとストッパプレートとの関係を示す断面図である。
【０００４】
バルブプレート１０３には、吐出ポート１０３ａが形成されている。
【０００５】
弁シート１２７には吐出ポート１０３ａと対向する舌片状の吐出弁部（弁部）１２７ａが切込み形成されている。
【０００６】
ストッパプレート１２９には、吐出弁部１２７ａに対応するストッパ部１２９ａが切込み形成されている。
【０００７】
吐出弁部１２７ａが２点鎖線で示すように開くと、吐出ポート１０３ａを介して圧縮室と吐出室が連通し、圧縮室から吐出室に高圧の冷媒ガスが流れる。
【０００８】
【発明が解決しようとする課題】
ストッパ部１２９ａは吐出弁部１２７ａが開閉し易いように、固定部１２９ｂに対して所定の角度又は任意の曲率をもった形状に形成されている。
【０００９】
上記形状の場合、冷媒ガスの流れは吐出弁部１２７ａと弁本体１２７ｂとの境界付近よりもストッパ部１２９ａと吐出弁部１２７ａとが衝突する先端部に集中してしまい、吐出弁部１２７ａの着座時の衝撃力が大きくなる。
【００１０】
その結果、吐出弁部が２点鎖線で示す位置から矢印ａに示すように移動して着座したとき、大きな衝撃音が発生するばかりか、特に高速運転時には弁シート１２７が折損してしまい、耐久性が低下してしまうという問題があった。
【００１１】
また、吐出弁部１２７ａの根元付近の開度が小さいので、冷媒ガスが流れ難く、過圧縮となってしまうという問題があった。
【００１２】
更に、弁シート１２７とストッパプレート１２９との気密を確保するため、ストッパプレート１２９は弁シート１２７との接触面を研磨する。
【００１３】
しかし、ストッパ部１２９ａの曲率半径が大きいので、研磨によってストッパプレート１２９の厚さが変化すると、弁シート１２７の支点が大きくずれてしまう可能性がある。
【００１４】
その結果、気筒によって吐出弁の開弁量が変わるので、冷媒ガスの流れが変わって圧縮のばらつきが生じ、脈動が発生する。
【００１５】
この発明はこのような事情に鑑みてなされたもので、その課題は消費動力が小さく、耐久性に優れ、しかも脈動が少ない往復式圧縮機を提供することである。
【００１６】
【課題を解決するための手段】
前述の課題を解決するため請求項１記載の発明は、シリンダブロックとシリンダヘッドとの間に配置され、圧縮室と高圧室及び低圧室とを仕切るバルブプレートと、前記圧縮室の冷媒ガスを前記高圧室に吐出するための吐出ポートと、弁本体と弁部とを有し、前記吐出ポートを開閉する吐出弁と、前記弁部の開き量を抑制するストッパ部と前記弁本体を固定する固定部とを有するストッパとを備えた往復式圧縮機において、前記ストッパ部と前記固定部との間に前記弁部の支点を定める段部が形成されていることを特徴とする。
【００１７】
ストッパ部と固定部との間に段部を形成したので、各気筒の弁部のリフトの支点が定まり、リフト量が均一となって圧縮のばらつきがなくなる。また、弁部が開弁したときに弁部にはその支点付近で段部が形成されるので、リフトの支点付近の弁部の開度が増加し、冷媒ガスの流れが良好となる。更に、冷媒ガスが弁部の先端部に集中せず、弁部に加わる衝撃力が緩和される。
【００１８】
請求項２記載の発明は、請求項１に記載の往復式圧縮機において、前記弁部の支点となる、前記固定部の角部は曲線形状であることを特徴とする。
【００１９】
弁部の支点と当接する固定部の角部は曲線形状であるので、弁部の支点に力が集中せず、吐出弁の耐久性が向上する。
【００２０】
【発明の実施の形態】
以下、この発明の実施の形態を図面に基づいて説明する。
【００２１】
図２はこの発明の一実施形態に係る斜板式圧縮機の縦断面図である。
【００２２】
フロント側のシリンダブロック１とリヤ側のシリンダブロック２とは互いに軸方向に対向接合されている。接合されたシリンダブロック１，２の一端にはバルブプレート３、弁シート２７及びストッパプレート（ストッパ）２９を介してフロントヘッド４が固定され、他端にはバルブプレート５、弁シート２８及びストッパプレート３０を介してリヤヘッド６が固定されている。
【００２３】
フロントヘッド４にフロント側のシェル１３が、リヤヘッド６にリヤ側のシェル１４がそれぞれ一体に設けられ、フロントシェル１３とリヤ側シェル１４とがＯリング３８を介して軸方向に互いに嵌合している
フロントヘッド４、シリンダブロック１，２、シェル１３，１４及びリヤヘッド６は通しボルト３９で軸方向に結合されている。
【００２４】
シリンダブロック１，２の中心部には駆動軸７が配設され、この駆動軸７には斜板８が固定され、駆動軸７及び斜板８はベアリング９，１０によって回転可能に支持されている。斜板８は駆動軸７に対して傾いている。
【００２５】
シリンダブロック１，２には複数のシリンダボア１１が設けられている。各シリンダボア１１は駆動軸７に平行であって、駆動軸７を中心とする円周方向に所定間隔おきに配置されている。各シリンダボア１１内にはピストン１２が摺動可能に収容されている。ピストン１２の両方の端面には円板状の突起１５が設けられている。
【００２６】
各シリンダボア１１内のピストン１２の両側には圧縮室２１，２２が形成されている。ピストン１２はほぼ半球体状のシュー１９，２０を介して斜板に連結され、ピストン１２は斜板８の回転に連れてシリンダボア１１内を往復運動する。
【００２７】
図３はバルブプレートと弁シートとストッパプレートとを示す分解斜視図、図４（ａ）はバルブプレートと弁シートとストッパプレートとを重ねたときのストッパプレートの一部分の平面図、図４（ｂ）は図４（ａ）の４Ｂ−４Ｂ線に沿う断面図、図１は図４（ａ）の１Ａ−１Ａ線に沿う断面図であり、図１（ａ）は開弁時の状態を、図１（ｂ）は閉弁時の状態をそれぞれ示す図である。
【００２８】
ほぼ円板状のバルブプレート３，５には、圧縮室２１，２２の冷媒ガスを吐出室（高圧室）２４へ吐出するための吐出ポート３ａ，５ａ、吸入時に吸入弁部２７ｄ，２８ｄを圧縮室２１，２２へ逃がす吸入弁部逃がし孔３ｂ，５ｂ及び通しボルト３９を挿入するためのボルト通し孔３ｃ，５ｃがそれぞれ設けられている。
【００２９】
吸入弁部逃がし孔３ｂ，５ｂは吸入弁部２７ｄ，２８ｄを介して吸入ポート２９ｄ，３０ｄに隣接し、吸入時に吸入弁部２７ｄ，２８ｄが開いたときに吸入ポート２９ｄ，３０ｄと連通する。
【００３０】
ほぼ円板状の弁シート２７，２８には、舌片状の吐出弁部（弁部）２７ａ，２８ａ及び舌片状の吸入弁部２７ｄ，２８ｄがそれぞれ切込み形成されているとともに、ボルト通し孔２７ｃ，２８ｃが形成されている。
【００３１】
吐出弁部２７ａ，２８ａがリフトするとき支点となる部分には、図１に示すように、段部２９ｆ，３０ｆが形成され、吐出弁部２７ａ，２８ａの支点付近の弁開度を大きくとれるようにしている。
【００３２】
ほぼ円板状のストッパプレート２９，３０には、吐出弁部２７ａ，２８ａの開き量又は変形量を抑制する溝状のストッパ部２９ａ，３０ａ、吸入室（低圧室）２３の冷媒ガスを圧縮室２１，２２に吸入させるための吸入ポート２９ｄ，３０ｄ及びボルト通し孔２９ｃ，３０ｃがそれぞれ形成されている。
【００３３】
また、ストッパプレート２９，３０には、ストッパ部２９ａ，３０ａの長手方向に沿う吐出用孔２９ｂ，３０ｂが形成されている。
【００３４】
更に、吐出弁部２７ａ，２８ａの支点となる、ストッパプレート２９，３０の角部Ｐは曲線形状に形成されている。
【００３５】
バルブプレート３，５と弁シート２７，２８とストッパプレート２９，３０とを重ねたときには、吐出ポート３ａ，５ａと吐出弁部２７ａ，２８ａとが対向し、バルブプレート３，５の吐出ポート３ａ，５ａ及びストッパプレート２９，３０の吐出用孔２９ｂ，３０ｂを介して、圧縮室２１，２２と吐出室２４とが連通する（図４参照）。
【００３６】
なお、吐出弁部２７ａ，２８ａに連なる弁本体２７ｅ，２８ｅはストッパプレート２９，３０の固定部２９ｅ，３０ｅとバルブプレート３，５とによって固定されている。
【００３７】
次にこの実施形態の斜板式圧縮機の動作を説明する。
【００３８】
駆動軸７が回転すると、斜板８も一体に回転する。斜板８の回転によりピストン１２がシリンダボア１１内を往復運動する。ピストン１２がバルブプレート３に最も近付いた位置（ピストン１２が圧縮室２１側で上死点に位置するとき）から、斜板８が１／２回転すると、ピストン１２がバルブプレート５側へ移動し、圧縮室２１側では吸入行程が完了し、圧縮室２２では圧縮行程、吐出行程が終了する。この状態から斜板８が更に１／２回転すると、逆に圧縮室２２で吸入工程が完了し、圧縮室２１側で圧縮行程、吐出行程が終了する。
【００３９】
吸入行程では吸入弁部２７ｄ，２８ｄが吸入弁部逃がし孔３ｂ，５ｂ側へ弾性変形し、吸入ポート２９ｄ，３０ｄ及び吸入弁部逃がし孔３ｂ，５ｂを通じて圧縮室２１，２２へ低圧の冷媒ガスが流入する。
【００４０】
圧縮行程では圧縮室２１，２２内で圧縮された冷媒ガスによって吐出弁部２７ａ，２８ａが吐出室側へ弾性変形し、吐出ポート３ａ，５ａ及び吐出用孔２９ｂ，３０ｂを通じて圧縮室２１，２２から吐出室２４へ高圧の冷媒ガスが吐出される。
【００４１】
この実施形態の斜板式圧縮機によれば、段部２９ｆ，３０ｆによって吐出弁部２７ａ，２８ａがリフトするときの支点が定められているので、各気筒の吐出弁部２７ａ，２８ａのリフト量が均一となって圧縮のばらつきがなくなり、圧縮のばらつきに起因する脈動が低減する。
【００４２】
また、吐出弁部２７ａ，２８ａが開弁したとき、吐出弁部２７ａ，２８ａの支点付近には冷媒ガスの吐出圧によって段部２７ｆ，２８ｆが形成され、吐出弁部２７ａ，２８ａの弁開度が増加するので、冷媒ガスの流れが良好となり、過圧縮が低減され、消費動力が小さくなる。
【００４３】
更に、冷媒ガスの流れがストッパ部１２９ａと吐出弁部１２７ａとが衝突する先端部に集中しないので、吐出弁部２７ａ，２８ａに加わる衝撃力が緩和され、騒音が低減されるとともに、耐久性が向上する。
【００４４】
吐出弁部２７ａ，２８ａの支点となる、ストッパプレート２９，３０の角部Ｐは曲線形状に形成されているので、吐出弁部２７ａ，２８ａの支点に力が集中せず、吐出弁部２７ａ，２８ａの耐久性が向上する。
【００４５】
なお、上記実施形態においては、本願発明をシェル付きの斜板式圧縮機を用いて説明したが、シェルを持たない構造のものにも適用することができる。
【００４６】
【発明の効果】
以上に説明したように請求項１記載の発明の往復式圧縮機によれば、ストッパ部と固定部との間に弁部の支点を定める段部を形成したので、各気筒の弁部のリフトの支点が定まり、リフト量が均一となって圧縮のばらつきがなくなり、圧縮のばらつきに起因する脈動をなくすことができる。また、弁部が開弁したときに弁部にはその支点付近で段部が形成されるので、支点付近での弁部の開度を増加させることができ、冷媒ガスの流れが良好となり、過圧縮が低減し、消費動力が小さくなる。更に、冷媒ガスが弁部の先端部に集中せず、弁部に加わる衝撃力が緩和されるので、騒音が低減されるとともに、耐久性が向上する。
【００４７】
請求項２記載の発明の往復式圧縮機によれば、弁部の支点と当接する固定部の角部は曲線形状であるので、弁部の支点に力が集中せず、吐出弁の耐久性が向上する。
【図面の簡単な説明】
【図１】図１は図４（ａ）の１Ａ−１Ａ線に沿う断面図であり、図１（ａ）は開弁時の状態を、図１（ｂ）は閉弁時の状態をそれぞれ示す図である。
【図２】図２はこの発明の一実施形態に係る斜板式圧縮機の縦断面図である。
【図３】図３はバルブプレートと弁シートとストッパプレートとを示す分解斜視図である。
【図４】図４（ａ）はバルブプレートと弁シートとストッパプレートとを重ねたときのストッパプレートの一部分の平面図、図４（ｂ）は図４（ａ）の４Ｂ−４Ｂ線に沿う断面図である。
【図５】図５は従来の斜板式圧縮機のバルブプレートと弁シートとストッパプレートとの関係を示す断面図である。
【符号の説明】
１，２ シリンダブロック
３，５ バルブプレート
３ａ，５ａ 吐出ポート
４，６ シリンダヘッド
２１，２２ 圧縮室
２３ 吸入室（低圧室）
２４ 吐出室（高圧室）
２７ａ，２８ａ 吐出弁部（弁部）
２７ｅ，２８ｅ 弁本体
２９，３０ ストッパプレート
２９ａ，３０ａ ストッパ部
２９ｅ，３０ｅ 固定部
２９ｆ，３０ｆ 段部[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a reciprocating compressor such as a swash plate compressor and a swing plate compressor.
[0002]
[Prior art]
The swash plate compressor is disposed between a cylinder block and a cylinder head, and partitions a compression chamber, a discharge chamber, and a suction chamber, a discharge port for discharging refrigerant gas in the compression chamber to the discharge chamber, A discharge valve that opens and closes the discharge port and a stopper plate that suppresses the opening amount of the valve portion are provided.
[0003]
FIG. 5 is a cross-sectional view showing the relationship among a valve plate, a valve seat, and a stopper plate of a conventional swash plate compressor.
[0004]
A discharge port 103 a is formed in the valve plate 103.
[0005]
A tongue-shaped discharge valve portion (valve portion) 127a facing the discharge port 103a is cut and formed in the valve seat 127.
[0006]
A stopper portion 129a corresponding to the discharge valve portion 127a is cut in the stopper plate 129.
[0007]
When the discharge valve portion 127a is opened as indicated by a two-dot chain line, the compression chamber and the discharge chamber communicate with each other via the discharge port 103a, and high-pressure refrigerant gas flows from the compression chamber to the discharge chamber.
[0008]
[Problems to be solved by the invention]
The stopper portion 129a is formed in a shape having a predetermined angle or an arbitrary curvature with respect to the fixed portion 129b so that the discharge valve portion 127a can be easily opened and closed.
[0009]
In the case of the above shape, the flow of the refrigerant gas is concentrated at the tip portion where the stopper portion 129a and the discharge valve portion 127a collide rather than near the boundary between the discharge valve portion 127a and the valve main body 127b, and the seating of the discharge valve portion 127a. The impact force at the time increases.
[0010]
As a result, when the discharge valve part is moved and seated from the position indicated by the two-dot chain line as shown by the arrow a, not only a large impact sound is generated, but the valve seat 127 is broken particularly during high-speed operation, resulting in durability. There was a problem that the performance would be lowered.
[0011]
Further, since the opening near the base of the discharge valve portion 127a is small, there is a problem that the refrigerant gas hardly flows and is overcompressed.
[0012]
Furthermore, in order to ensure airtightness between the valve seat 127 and the stopper plate 129, the stopper plate 129 polishes the contact surface with the valve seat 127.
[0013]
However, since the radius of curvature of the stopper portion 129a is large, if the thickness of the stopper plate 129 changes due to polishing, the fulcrum of the valve seat 127 may be greatly displaced.
[0014]
As a result, the opening amount of the discharge valve varies depending on the cylinder, so that the flow of the refrigerant gas changes, causing variations in compression, and pulsation occurs.
[0015]
The present invention has been made in view of such circumstances, and its object is to provide a reciprocating compressor that consumes little power, has excellent durability, and has little pulsation.
[0016]
[Means for Solving the Problems]
In order to solve the above-mentioned problem, the invention according to claim 1 is arranged between the cylinder block and the cylinder head, and partitions the compression chamber, the high-pressure chamber and the low-pressure chamber, and the refrigerant gas in the compression chamber. A discharge port for discharging into the high-pressure chamber, a valve body and a valve portion, a discharge valve for opening and closing the discharge port, a stopper portion for suppressing an opening amount of the valve portion, and a fixing for fixing the valve body In the reciprocating compressor provided with a stopper having a portion, a step portion for defining a fulcrum of the valve portion is formed between the stopper portion and the fixed portion.
[0017]
Since the step portion is formed between the stopper portion and the fixed portion, the lift fulcrum of the valve portion of each cylinder is determined, the lift amount becomes uniform, and the variation in compression is eliminated. Further, when the valve portion is opened, a step portion is formed in the vicinity of the fulcrum of the valve portion, so that the opening degree of the valve portion near the fulcrum of the lift is increased and the flow of the refrigerant gas is improved. Furthermore, the refrigerant gas does not concentrate on the tip of the valve portion, and the impact force applied to the valve portion is alleviated.
[0018]
According to a second aspect of the present invention, in the reciprocating compressor according to the first aspect, a corner portion of the fixed portion serving as a fulcrum of the valve portion has a curved shape.
[0019]
Since the corner portion of the fixed portion that contacts the fulcrum of the valve portion has a curved shape, the force is not concentrated on the fulcrum of the valve portion, and the durability of the discharge valve is improved.
[0020]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[0021]
FIG. 2 is a longitudinal sectional view of a swash plate compressor according to an embodiment of the present invention.
[0022]
The front-side cylinder block 1 and the rear-side cylinder block 2 are joined to each other in the axial direction. The front head 4 is fixed to one end of the joined cylinder blocks 1 and 2 via a valve plate 3, a valve seat 27 and a stopper plate (stopper) 29, and the other end is a valve plate 5, a valve seat 28 and a stopper plate. The rear head 6 is fixed via 30.
[0023]
A front side shell 13 and a rear side shell 14 are integrally provided on the front head 4 and the rear head 6, respectively. The front shell 13 and the rear side shell 14 are fitted together in an axial direction via an O-ring 38. The front head 4, the cylinder blocks 1 and 2, the shells 13 and 14, and the rear head 6 are coupled in the axial direction by through bolts 39.
[0024]
A drive shaft 7 is disposed at the center of the cylinder blocks 1 and 2, and a swash plate 8 is fixed to the drive shaft 7. The drive shaft 7 and the swash plate 8 are rotatably supported by bearings 9 and 10. Yes. The swash plate 8 is inclined with respect to the drive shaft 7.
[0025]
The cylinder blocks 1 and 2 are provided with a plurality of cylinder bores 11. The cylinder bores 11 are parallel to the drive shaft 7 and are arranged at predetermined intervals in the circumferential direction around the drive shaft 7. A piston 12 is slidably accommodated in each cylinder bore 11. Disc-shaped projections 15 are provided on both end faces of the piston 12.
[0026]
Compression chambers 21 and 22 are formed on both sides of the piston 12 in each cylinder bore 11. The piston 12 is connected to the swash plate via substantially hemispherical shoes 19 and 20, and the piston 12 reciprocates in the cylinder bore 11 as the swash plate 8 rotates.
[0027]
3 is an exploded perspective view showing the valve plate, the valve seat, and the stopper plate. FIG. 4A is a plan view of a portion of the stopper plate when the valve plate, the valve seat, and the stopper plate are overlapped, and FIG. ) Is a cross-sectional view taken along line 4B-4B of FIG. 4A, FIG. 1 is a cross-sectional view taken along line 1A-1A of FIG. 4A, and FIG. FIG.1 (b) is a figure which respectively shows the state at the time of valve closing.
[0028]
The substantially disc-shaped valve plates 3 and 5 compress the discharge ports 3a and 5a for discharging the refrigerant gas in the compression chambers 21 and 22 to the discharge chamber (high pressure chamber) 24, and the suction valve portions 27d and 28d at the time of suction. Suction valve part relief holes 3b and 5b for escape to the chambers 21 and 22 and bolt through holes 3c and 5c for inserting through bolts 39 are provided, respectively.
[0029]
The suction valve part relief holes 3b and 5b are adjacent to the suction ports 29d and 30d through the suction valve parts 27d and 28d, and communicate with the suction ports 29d and 30d when the suction valve parts 27d and 28d are opened during suction.
[0030]
The substantially disc-shaped valve seats 27 and 28 are provided with tongue-shaped discharge valve portions (valve portions) 27a and 28a and tongue-shaped suction valve portions 27d and 28d, respectively, and are provided with bolt through holes. 27c and 28c are formed.
[0031]
As shown in FIG. 1, step portions 29f and 30f are formed at portions that serve as fulcrums when the discharge valve portions 27a and 28a are lifted, so that the valve opening near the fulcrums of the discharge valve portions 27a and 28a can be increased. I have to.
[0032]
The substantially disc-shaped stopper plates 29 and 30 are provided with groove-shaped stopper portions 29a and 30a for suppressing the opening amount or deformation amount of the discharge valve portions 27a and 28a, and the refrigerant gas in the suction chamber (low pressure chamber) 23 is compressed. Suction ports 29d and 30d and bolt through-holes 29c and 30c are respectively formed for suctioning to 21 and 22.
[0033]
The stopper plates 29 and 30 are formed with ejection holes 29b and 30b along the longitudinal direction of the stopper portions 29a and 30a.
[0034]
Further, the corner portions P of the stopper plates 29 and 30 serving as fulcrums of the discharge valve portions 27a and 28a are formed in a curved shape.
[0035]
When the valve plates 3, 5, the valve seats 27, 28 and the stopper plates 29, 30 are overlapped, the discharge ports 3 a, 5 a and the discharge valve portions 27 a, 28 a face each other, and the discharge ports 3 a, The compression chambers 21 and 22 communicate with the discharge chamber 24 through the discharge holes 29b and 30b of the stopper plate 29 and 30 (see FIG. 4).
[0036]
The valve bodies 27e, 28e connected to the discharge valve portions 27a, 28a are fixed by the fixing portions 29e, 30e of the stopper plates 29, 30 and the valve plates 3, 5.
[0037]
Next, the operation of the swash plate compressor of this embodiment will be described.
[0038]
When the drive shaft 7 rotates, the swash plate 8 also rotates together. The piston 12 reciprocates in the cylinder bore 11 by the rotation of the swash plate 8. When the swash plate 8 rotates 1/2 from the position where the piston 12 is closest to the valve plate 3 (when the piston 12 is located at the top dead center on the compression chamber 21 side), the piston 12 moves to the valve plate 5 side. The suction stroke is completed on the compression chamber 21 side, and the compression stroke and the discharge stroke are completed on the compression chamber 22. When the swash plate 8 further makes a half turn from this state, the suction process is completed in the compression chamber 22 and the compression stroke and the discharge stroke are completed on the compression chamber 21 side.
[0039]
In the suction stroke, the suction valve portions 27d and 28d are elastically deformed toward the suction valve portion relief holes 3b and 5b, and low-pressure refrigerant gas is supplied to the compression chambers 21 and 22 through the suction ports 29d and 30d and the suction valve portion relief holes 3b and 5b. Inflow.
[0040]
In the compression stroke, the discharge valve portions 27a and 28a are elastically deformed to the discharge chamber side by the refrigerant gas compressed in the compression chambers 21 and 22, and are discharged from the compression chambers 21 and 22 through the discharge ports 3a and 5a and the discharge holes 29b and 30b. A high-pressure refrigerant gas is discharged into the discharge chamber 24.
[0041]
According to the swash plate compressor of this embodiment, since the fulcrum when the discharge valve portions 27a and 28a are lifted is determined by the step portions 29f and 30f, the lift amount of the discharge valve portions 27a and 28a of each cylinder is determined. It becomes uniform and there is no variation in compression, and the pulsation caused by the variation in compression is reduced.
[0042]
Further, when the discharge valve portions 27a and 28a are opened, step portions 27f and 28f are formed near the fulcrum of the discharge valve portions 27a and 28a by the discharge pressure of the refrigerant gas, and the valve opening degree of the discharge valve portions 27a and 28a. Therefore, the flow of the refrigerant gas becomes good, the overcompression is reduced, and the power consumption is reduced.
[0043]
Furthermore, since the flow of the refrigerant gas does not concentrate on the tip portion where the stopper portion 129a and the discharge valve portion 127a collide, the impact force applied to the discharge valve portions 27a and 28a is alleviated, noise is reduced, and durability is improved. improves.
[0044]
Since the corner portions P of the stopper plates 29, 30 serving as fulcrums of the discharge valve portions 27a, 28a are formed in a curved shape, the force does not concentrate on the fulcrums of the discharge valve portions 27a, 28a, and the discharge valve portions 27a, The durability of 28a is improved.
[0045]
In the above embodiment, the present invention has been described using a swash plate compressor with a shell, but the present invention can also be applied to a structure without a shell.
[0046]
【The invention's effect】
As described above, according to the reciprocating compressor of the first aspect of the present invention, since the step portion that defines the fulcrum of the valve portion is formed between the stopper portion and the fixed portion, the lift of the valve portion of each cylinder The fulcrum is fixed, the lift amount becomes uniform, and there is no variation in compression, and the pulsation caused by the variation in compression can be eliminated. Further, when the valve portion is opened, a step portion is formed in the vicinity of the fulcrum of the valve portion, so that the opening of the valve portion near the fulcrum can be increased, and the flow of the refrigerant gas becomes good. Over compression is reduced and power consumption is reduced. Furthermore, since the refrigerant gas does not concentrate on the tip of the valve portion and the impact force applied to the valve portion is alleviated, noise is reduced and durability is improved.
[0047]
According to the reciprocating compressor of the second aspect of the present invention, the corner portion of the fixed portion that comes into contact with the fulcrum of the valve portion has a curved shape, so that the force does not concentrate on the fulcrum of the valve portion, and the durability of the discharge valve Will improve.
[Brief description of the drawings]
1 is a cross-sectional view taken along line 1A-1A in FIG. 4 (a), FIG. 1 (a) shows a state when the valve is opened, and FIG. 1 (b) shows a state when the valve is closed. FIG.
FIG. 2 is a longitudinal sectional view of a swash plate compressor according to an embodiment of the present invention.
FIG. 3 is an exploded perspective view showing a valve plate, a valve seat, and a stopper plate.
4A is a plan view of a part of the stopper plate when the valve plate, the valve seat, and the stopper plate are overlapped, and FIG. 4B is along the line 4B-4B in FIG. 4A. It is sectional drawing.
FIG. 5 is a cross-sectional view showing a relationship among a valve plate, a valve seat, and a stopper plate of a conventional swash plate compressor.
[Explanation of symbols]
1, 2 Cylinder block 3, 5 Valve plate 3a, 5a Discharge port 4, 6 Cylinder head 21, 22 Compression chamber 23 Suction chamber (low pressure chamber)
24 Discharge chamber (high pressure chamber)
27a, 28a Discharge valve part (valve part)
27e, 28e Valve body 29, 30 Stopper plate 29a, 30a Stopper part 29e, 30e Fixing part 29f, 30f Step part

Claims (2)

シリンダブロックとシリンダヘッドとの間に配置され、圧縮室と高圧室及び低圧室とを仕切るバルブプレートと、前記圧縮室の冷媒ガスを前記高圧室に吐出するための吐出ポートと、弁本体と弁部とを有し、前記吐出ポートを開閉する吐出弁と、前記弁部の開き量を抑制するストッパ部と前記弁本体を固定する固定部とを有するストッパとを備えた往復式圧縮機において、前記ストッパ部と前記固定部との間に前記弁部の支点を定める段部が形成されていることを特徴とする往復式圧縮機。A valve plate disposed between the cylinder block and the cylinder head and partitioning the compression chamber from the high pressure chamber and the low pressure chamber; a discharge port for discharging refrigerant gas in the compression chamber to the high pressure chamber; a valve body and a valve; A reciprocating compressor including a discharge valve that opens and closes the discharge port, a stopper having a stopper portion that suppresses an opening amount of the valve portion, and a fixing portion that fixes the valve body. A reciprocating compressor characterized in that a step portion for defining a fulcrum of the valve portion is formed between the stopper portion and the fixed portion. 前記弁部の支点となる、前記固定部の角部は曲線形状であることを特徴とする請求項１に記載の往復式圧縮機。The reciprocating compressor according to claim 1, wherein a corner portion of the fixed portion serving as a fulcrum of the valve portion has a curved shape.
JP34584097A 1997-12-01 1997-12-01 Reciprocating compressor Expired - Fee Related JP3772283B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP34584097A JP3772283B2 (en) 1997-12-01 1997-12-01 Reciprocating compressor
KR1020007000592A KR20010022024A (en) 1997-12-01 1998-12-01 Reciprocating compressor
PCT/JP1998/005402 WO1999028628A1 (en) 1997-12-01 1998-12-01 Reciprocating compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP34584097A JP3772283B2 (en) 1997-12-01 1997-12-01 Reciprocating compressor

Publications (2)

Publication Number Publication Date
JPH11166479A JPH11166479A (en) 1999-06-22
JP3772283B2 true JP3772283B2 (en) 2006-05-10

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JP34584097A Expired - Fee Related JP3772283B2 (en) 1997-12-01 1997-12-01 Reciprocating compressor

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KR (1) KR20010022024A (en)
WO (1) WO1999028628A1 (en)

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KR101824554B1 (en) * 2013-06-24 2018-02-01 가부시키가이샤 히다치 산키시스템 Fluid machine

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JPS5450206U (en) * 1977-09-14 1979-04-07
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WO1999028628A1 (en) 1999-06-10
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