JPH11166479A - Reciprocating compressor - Google Patents
Reciprocating compressorInfo
- Publication number
- JPH11166479A JPH11166479A JP9345840A JP34584097A JPH11166479A JP H11166479 A JPH11166479 A JP H11166479A JP 9345840 A JP9345840 A JP 9345840A JP 34584097 A JP34584097 A JP 34584097A JP H11166479 A JPH11166479 A JP H11166479A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- discharge
- stopper
- compression
- discharge valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
【０００１】[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。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reciprocating compressor such as a swash plate compressor and a swinging plate compressor.
【０００２】[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。2. Description of the Related Art A swash plate type compressor is disposed between a cylinder block and a cylinder head and separates a compression chamber from a discharge chamber and a suction chamber, and discharges refrigerant gas from the compression chamber to the discharge chamber. Discharge port, a discharge valve for opening and closing the discharge port, and a stopper plate for suppressing the opening amount of the valve portion.
【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。FIG. 5 is a sectional view showing the relationship among a valve plate, a valve seat, and a stopper plate of a conventional swash plate type compressor.
【０００４】バルブプレート１０３には、吐出ポート１
０３ａが形成されている。The valve plate 103 has a discharge port 1
03a is formed.
【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。[0005] A tongue-shaped discharge valve portion (valve portion) 127a facing the discharge port 103a is cut into the valve seat 127.
【０００６】ストッパプレート１２９には、吐出弁部１
２７ａに対応するストッパ部１２９ａが切込み形成され
ている。[0006] The discharge valve portion 1 is provided on the stopper plate 129.
A stopper portion 129a corresponding to 27a is cut and formed.
【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。When the discharge valve portion 127a is opened as shown by a two-dot chain line, the compression chamber and the discharge chamber communicate with each other through the discharge port 103a, and high-pressure refrigerant gas flows from the compression chamber to the discharge chamber.
【０００８】[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。The stopper portion 129a has a fixing portion 129b so that the discharge valve portion 127a can be easily opened and closed.
Is formed in a shape having a predetermined angle or an arbitrary curvature with respect to.
【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。In the case of the above-mentioned shape, the flow of the refrigerant gas is concentrated more on the front end portion where the stopper portion 129a and the discharge valve portion 127a collide than near the boundary between the discharge valve portion 127a and the valve body 127b. The impact force at the time of sitting of 127a increases.
【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。As a result, when the discharge valve portion moves from the position shown by the two-dot chain line as shown by the arrow a and sits down, not only a loud impact sound is generated, but also the valve seat 127 breaks particularly at high speed operation. As a result, there is a problem that durability is reduced.
【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。Further, since the opening degree near the base of the discharge valve portion 127a is small, there is a problem that it is difficult for the refrigerant gas to flow, resulting in excessive compression.
【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１２
９は弁シート１２７との接触面を研磨する。Further, in order to ensure airtightness between the valve seat 127 and the stopper plate 129, the stopper plate 12
9 polishes the contact surface with the valve seat 127.
【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。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 shifted.
【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。As a result, the amount of opening of the discharge valve changes depending on the cylinder, so that the flow of the refrigerant gas changes, causing variations in compression and pulsation.
【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。The present invention has been made in view of such circumstances, and an object of the present invention is to provide a reciprocating compressor having low power consumption, excellent durability, and low pulsation.
【００１６】[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段部が形
成されていることを特徴とする。According to a first aspect of the present invention, there is provided a valve plate disposed between a cylinder block and a cylinder head for partitioning a compression chamber from a high pressure chamber and a low pressure chamber. A discharge port for discharging refrigerant gas from the compression chamber to the high-pressure chamber, a discharge valve for opening and closing the discharge port, and a stopper for suppressing an opening amount of the valve part; In a reciprocating compressor including a stopper having a portion and a fixing portion for fixing the valve body, a step portion is formed between the stopper portion and the fixing portion.
【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、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。Since the step portion is formed between the stopper portion and the fixed portion, the fulcrum of the lift of the valve portion of each cylinder is determined, the lift amount becomes uniform, and there is no variation in compression. Further, the opening degree of the valve portion near the fulcrum of the lift increases, and the flow of the refrigerant gas becomes good. Further, the refrigerant gas does not concentrate on the tip of the valve, and the impact force applied to the valve is reduced.
【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。According to a second aspect of the present invention, in the reciprocating compressor according to the first aspect, a corner of the fixed portion, which is a fulcrum of the valve portion, has a curved shape.
【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。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】[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。Embodiments of the present invention will be described below with reference to the drawings.
【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。FIG. 2 is a longitudinal sectional view of a swash plate type compressor according to one embodiment of the present invention.
【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。The cylinder block 1 on the front side and the cylinder block 2 on the rear side 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】フロントヘッド４にフロント側のシェル１
３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１
３，１４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。The front side shell 1 is attached to the front head 4.
3, a rear shell 6 is provided integrally with the rear head 6, and a front shell 13 and a rear shell 14 are provided.
The front head 4, the cylinder blocks 1 and 2, and the shell 1 are fitted to each other in the axial direction via an O-ring 38.
3, 14 and the rear head 6 are axially connected by through bolts 39.
【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。A drive shaft 7 is provided 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. The swash plate 8 is inclined with respect to the drive shaft 7.
【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。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 a circumferential direction around the drive shaft 7. Each cylinder bore 11
A piston 12 is slidably accommodated therein. Disc-shaped projections 15 are provided on both end faces of the piston 12.
【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１
２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。Compression chambers 21 and 22 are formed on both sides of the piston 12 in each cylinder bore 11. Piston 1
2 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】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。FIG. 3 is an exploded perspective view showing a valve plate, a valve seat, and a stopper plate. FIG. 4A is a plan view of a part of the stopper plate when the valve plate, the valve seat, and the stopper plate are stacked. 4 (b) is FIG.
FIG. 1A is a cross-sectional view taken along line 4B-4B, and FIG.
1A is a cross-sectional view taken along the line 1A-1A of FIG. 1. FIG. 1A shows a state at the time of valve opening, and FIG. 1B shows a state at the time of valve closing.
【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。The substantially disk-shaped valve plates 3 and 5 include:
Discharge ports 3a and 5a for discharging refrigerant gas from the compression chambers 21 and 22 to the discharge chamber (high-pressure chamber) 24, and suction valve release holes 3b for releasing the suction valve portions 27d and 28d to the compression chambers 21 and 22 during suction. 5b and bolt through holes 3c, 5c for inserting the through bolt 39 are provided respectively.
【００２９】吸入弁部逃がし孔３ｂ，５ｂは吸入弁部２
７ｄ，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。The suction valve escape holes 3b, 5b are
It is adjacent to the suction ports 29d, 30d via 7d, 28d, and communicates with the suction ports 29d, 30d when the suction valve portions 27d, 28d open during suction.
【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。The substantially disc-shaped valve seats 27 and 28 are formed with cut-outs formed by tongue-shaped discharge valve portions (valve portions) 27a and 28a and tongue-shaped suction valve portions 27d and 28d, respectively. Bolt through holes 27c and 28c are formed.
【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。As shown in FIG. 1, a step portion 29f, a fulcrum when the discharge valve portions 27a, 28a are lifted, is provided.
30f is formed so that the valve opening degree near the fulcrum of the discharge valve portions 27a and 28a can be increased.
【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２９
ｃ，３０ｃがそれぞれ形成されている。A substantially disk-shaped stopper plate 29, 30
Are provided with groove-shaped stopper portions 29a and 30a for suppressing the opening amounts or deformation amounts of the discharge valve portions 27a and 28a, and a suction port for sucking the refrigerant gas in the suction chamber (low-pressure chamber) 23 into the compression chambers 21 and 22. 29d, 30d and bolt through hole 29
c, 30c are respectively formed.
【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２
９ｂ，３０ｂが形成されている。Further, the stopper plates 29 and 30 have
Discharge hole 2 along the longitudinal direction of stopper portions 29a, 30a
9b and 30b are formed.
【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。Further, the corners P of the stopper plates 29, 30 which are fulcrums of the discharge valve portions 27a, 28a are formed in a curved shape.
【００３５】バルブプレート３，５と弁シート２７，２
８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，３０
ｂを介して、圧縮室２１，２２と吐出室２４とが連通す
る（図４参照）。Valve plates 3 and 5 and valve seats 27 and 2
8 and the stopper plates 29, 30
The discharge ports 3a, 5a face the discharge valve portions 27a, 28a, and the discharge ports 3a, 5a of the valve plates 3, 5 and the discharge holes 29b, 30 of the stopper plates 29, 30.
The compression chambers 21 and 22 communicate with the discharge chamber 24 via b (see FIG. 4).
【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。The valve bodies 27e and 28e connected to the discharge valve portions 27a and 28a are fixed by fixing portions 29e and 30e of the stopper plates 29 and 30 and the valve plates 3 and 5, respectively.
【００３７】次にこの実施形態の斜板式圧縮機の動作を
説明する。Next, the operation of the swash plate type compressor of this embodiment will be described.
【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。When the drive shaft 7 rotates, the swash plate 8 also rotates integrally. The rotation of the swash plate 8 causes the piston 12 to reciprocate in the cylinder bore 11. When the swash plate 8 makes a half turn from the position where the piston 12 comes 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. In the compression chamber 21, the suction stroke is completed, and in the compression chamber 22, the compression stroke and the discharge stroke are completed. When the swash plate 8 further rotates by か ら from this state, the suction process is completed in the compression chamber 22, and the compression stroke and the discharge stroke are completed in the compression chamber 21.
【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。In the suction stroke, the suction valve portions 27d and 28d are elastically deformed toward the suction valve release holes 3b and 5b, and the low pressure is applied to the compression chambers 21 and 22 through the suction ports 29d and 30d and the suction valve release holes 3b and 5b. Refrigerant gas flows in.
【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２
９ｂ，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。In the compression stroke, the discharge valves 27a, 28a are elastically deformed toward the discharge chambers by the refrigerant gas compressed in the compression chambers 21, 22, and the discharge ports 3a, 5a and the discharge holes 2a are formed.
9b, 30b to the discharge chamber 24 from the compression chambers 21, 22.
High-pressure refrigerant gas is discharged to the
【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。According to the swash plate type compressor of this embodiment, since the fulcrum when the discharge valve portions 27a, 28a are lifted by the step portions 29f, 30f is determined, the discharge valve portions 27a, 28a of each cylinder are determined. The lift amount becomes uniform, and there is no variation in compression, and pulsation due to the variation in compression is reduced.
【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。When the discharge valve portions 27a and 28a are opened, steps 27f and 28f are formed near the fulcrum of the discharge valve portions 27a and 28a by the discharge pressure of the refrigerant gas. Since the valve opening increases, the flow of the refrigerant gas becomes good, overcompression is reduced, and power consumption is reduced.
【００４３】更に、冷媒ガスの流れがストッパ部１２９
ａ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。Further, the flow of the refrigerant gas is controlled by the stopper 129.
Since the a and the discharge valve portion 127a do not concentrate on the tip portion where they collide, the impact force applied to the discharge valve portions 27a and 28a is reduced, noise is reduced, and durability is improved.
【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。Since the corners P of the stopper plates 29, 30 serving as fulcrums of the discharge valve parts 27a, 28a are formed in a curved shape, force is not concentrated on the fulcrum of the discharge valve parts 27a, 28a. The durability of the portions 27a and 28a is improved.
【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。In the above embodiment, the present invention has been described using a swash plate type compressor with a shell, but the present invention can also be applied to a structure without a shell.
【００４６】[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、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、リフトの支点近傍の弁部の開度が増加
するので、冷媒ガスの流れが良好となり、過圧縮が低減
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。As described above, according to the reciprocating compressor of the first aspect of the present invention, the fulcrum of the lift of the valve portion of each cylinder is determined, the lift amount becomes uniform, and there is no variation in compression. In addition, it is possible to eliminate the pulsation caused by the variation in compression. In addition, since the opening degree of the valve portion near the fulcrum of the lift increases, the flow of the refrigerant gas becomes good, overcompression is reduced, and power consumption is reduced. Further, since the refrigerant gas does not concentrate on the tip of the valve portion and the impact force applied to the valve portion is reduced, noise is reduced and durability is improved.
【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。According to the reciprocating compressor according to the second aspect of the present invention, since the corner of the fixed portion abutting on the fulcrum of the valve is curved, the force is not concentrated on the fulcrum of the valve and the discharge valve Durability is improved.
【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。FIG. 1 is a 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.
【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。FIG. 2 is a longitudinal sectional view of a swash plate type compressor according to one embodiment of the present invention.
【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。FIG. 3 is an exploded perspective view showing a valve plate, a valve seat, and a stopper plate.
【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。FIG. 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. It is sectional drawing.
【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。FIG. 5 is a cross-sectional view showing a relationship between a valve plate, a valve seat, and a stopper plate of the conventional swash plate compressor.
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 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 section (valve section) 27e , 28e Valve body 29, 30 Stopper plate 29a, 30a Stopper portion 29e, 30e Fixing portion 29f, 30f Step portion
───────────────────────────────────────────────────── フロントページの続き (72)発明者 新井 克彦 埼玉県大里郡江南町大字千代字東原39番地 株式会社ゼクセル江南工場内 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Katsuhiko Arai 39, Higashihara, Chiyo, Odai-gun, Osato-gun, Saitama
Claims (2)
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段部が形成されて
いることを特徴とする往復式圧縮機。1. A valve plate disposed between a cylinder block and a cylinder head and separating a compression chamber from a high-pressure chamber and a low-pressure chamber; and a discharge port for discharging refrigerant gas in the compression chamber to the high-pressure chamber. A reciprocating valve having a valve body and a valve portion, a discharge valve for opening and closing the discharge port, and a stopper having a stopper portion for suppressing an opening amount of the valve portion and a fixing portion for fixing the valve body. A reciprocating compressor, wherein a step portion is formed between the stopper portion and the fixed portion.
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。2. The reciprocating compressor according to claim 1, wherein a corner portion of the fixed portion, which is a fulcrum of the valve portion, has a curved shape.
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 true JPH11166479A (en) | 1999-06-22 |
| JP3772283B2 JP3772283B2 (en) | 2006-05-10 |
Family
ID=18379348
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP34584097A Expired - Fee Related JP3772283B2 (en) | 1997-12-01 | 1997-12-01 | Reciprocating compressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP3772283B2 (en) |
| KR (1) | KR20010022024A (en) |
| WO (1) | WO1999028628A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014207791A1 (en) * | 2013-06-24 | 2014-12-31 | 株式会社日立産機システム | Fluid machine |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5450206U (en) * | 1977-09-14 | 1979-04-07 | ||
| JPS5777769U (en) * | 1980-10-29 | 1982-05-13 | ||
| JP2587085Y2 (en) * | 1992-05-06 | 1998-12-14 | 株式会社豊田自動織機製作所 | Suction reed valve mechanism of piston type compressor |
-
1997
- 1997-12-01 JP JP34584097A patent/JP3772283B2/en not_active Expired - Fee Related
-
1998
- 1998-12-01 KR KR1020007000592A patent/KR20010022024A/en active IP Right Grant
- 1998-12-01 WO PCT/JP1998/005402 patent/WO1999028628A1/en active IP Right Grant
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014207791A1 (en) * | 2013-06-24 | 2014-12-31 | 株式会社日立産機システム | Fluid machine |
| JP6039073B2 (en) * | 2013-06-24 | 2016-12-07 | 株式会社日立産機システム | Fluid machinery |
| US9964107B2 (en) | 2013-06-24 | 2018-05-08 | Hitachi Industrial Equipment Systems Co., Ltd. | Fluid machine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3772283B2 (en) | 2006-05-10 |
| KR20010022024A (en) | 2001-03-15 |
| WO1999028628A1 (en) | 1999-06-10 |
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