JP2004162567A - Control valve for variable displacement compressor - Google Patents

Control valve for variable displacement compressor Download PDF

Info

Publication number
JP2004162567A
JP2004162567A JP2002327909A JP2002327909A JP2004162567A JP 2004162567 A JP2004162567 A JP 2004162567A JP 2002327909 A JP2002327909 A JP 2002327909A JP 2002327909 A JP2002327909 A JP 2002327909A JP 2004162567 A JP2004162567 A JP 2004162567A
Authority
JP
Japan
Prior art keywords
valve
bellows
control valve
variable displacement
displacement compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP2002327909A
Other languages
Japanese (ja)
Inventor
Koji Kainuma
広司 海沼
Naoki Tomaru
直樹 登丸
Masayuki Imai
正幸 今井
Shinsuke Kato
真介 加藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fujikoki Corp
Original Assignee
Fujikoki Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Fujikoki Corp filed Critical Fujikoki Corp
Priority to JP2002327909A priority Critical patent/JP2004162567A/en
Priority to US10/689,699 priority patent/US20040091368A1/en
Priority to KR1020030074265A priority patent/KR20040042817A/en
Priority to EP03026082A priority patent/EP1420163B1/en
Priority to CNB2003101038506A priority patent/CN100368685C/en
Priority to DE60324237T priority patent/DE60324237D1/en
Publication of JP2004162567A publication Critical patent/JP2004162567A/en
Pending legal-status Critical Current

Links

Images

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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—Crankcase pressure
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To enhance accuracy of valve opening-closing operation by minimizing hysteresis in the valve opening-closing operation even if straightness of bellows is slightly inferior. <P>SOLUTION: This control valve has a bellows body 27 held in a bellows case 13 of a sealed structure. A valve opening quantity is changed by transmitting the extension-contraction of the bellows body 27 caused by a change in suction pressure Ps of a variable displacement compressor to a valve element via a valve rod 25 movably supported in the valve lift direction by a valve housing integral with the bellows case. A wear plate member 31 is arranged in a moving side end part of the bellows body 27, and a fitting recessed part 31b is formed in the wear plate member 31. The valve rod 25 is loosely movably fitted to the fitting recessed part 31b. A compression coil spring 30 is interposed between the wear plate member 31 and a lower wear plate member 28 for supporting a nonmoveable side end part of the bellows body 27. <P>COPYRIGHT: (C)2004,JPO

Description

【０００１】
【発明の属する技術分野】
この発明は、可変容量型圧縮機用の制御弁に関するものである。
【０００２】
【従来の技術】
可変容量型圧縮機等に設けられる容量制御弁としてベローズ式圧力応動弁を用いることは、特許文献１に示されている。ベローズ式圧力応動弁は、ダイヤフラム式の圧力応動弁に比して、小型で圧力応答ストロークを長く取れると云う利点を有している。
【０００３】
しかし、一般に、ベローズは、構造上高い真直性を得ることが難しく、ベローズが弁リフト方向に対して蛇行していると、ベローズが弁リフト方向に伸縮する際に横方向の力が発生し、この横方向の力が弁棒に伝わることにより、弁開閉動作におけるヒステリシスの増加などを招き、制御不良の要因になって弁開閉精度の低下を招くことになる。
【０００４】
そこで、下記特許文献２に記載のベローズ式圧力応動弁は、圧力感知素子として密閉構造のベローズを有し、前記ベローズの伸縮を弁ハウジングより弁リフト方向に移動可能に支持された弁棒を介してボール弁に伝えることにより開弁量を変化するベローズ式圧力応動弁において、ベローズと弁棒との接続部にベローズと一体の端板とボールとからなる球面継手構造を組み込み、球面接続するようにしている。
【０００５】
【特許文献１】
実公平０２−３７００１号公報
【特許文献２】
特開２０００−８８１３２号公報
【０００６】
【発明が解決しようとする課題】
しかしながら、上記公知例によれば、ベローズの伸縮をボールと下当金部材とからなる球面継手構造を介して弁体に伝える構成となっているために、ベローズの伸縮においてボールと下当金部材と位置ずれを起こすことがあるばかりでなく部品点数が多くなるなどの問題があった。
したがって、本発明の課題は、可変容量型圧縮機用の制御弁において、継手部材の傾動を許容する継手によって位置ずれを発生させず、また、部品点数を少なくすることで組立て工数を少なくした制御弁を提供することにある。
【０００７】
【課題を解決する手段】
本発明は、上記課題を達成するために、下記の手段を講じた。即ち、
請求項１記載の可変容量型圧縮機用の制御弁は、圧力感知素子として密閉構造のベローズケース（１３）に保持されたベローズ本体（２７）を具備し、可変容量型圧縮機の吸入圧力（Ｐｓ）の変動に伴なう前記ベローズ本体（２７）の伸縮をベローズケース（１３）と一体の弁ハウジング（１１）より弁リフト方向に移動可能に支持された弁棒（２５）を介して弁体に伝えることにより開弁量を変化させる可変容量型圧縮機用の制御弁において、前記ベローズ本体（２７）の移動側端部に当金部材（３１）が設けられ、該当金部材（３１）には嵌合凹部（３１ｂ）が形成されると共に該嵌合凹部（３１ｂ）には弁棒（２５）が遊動可能に嵌合され、且つ、上記当金部材（３１）と、前記ベローズ本体（２７）の非移動側端部を支持する下当金部材（２８）との間には圧縮コイルばね（３０）が介装されていることを特徴とする。
【０００８】
請求項２記載の可変容量型圧縮機用の制御弁は、請求項１記載の可変容量型圧縮機用の制御弁において、上記弁棒（２５）の上記嵌合凹部（３１ｂ）に当接する当接端部２５ａの位置は、上記ベローズ本体（２７）の略中央又は該中央より非移動側端部側の位置とされていることを特徴とする。
請求項３記載の可変容量型圧縮機用の制御弁は、請求項１又は請求項２記載の可変容量型圧縮機用の制御弁において、前記ベローズ本体（２７）の非移動側端部の内面側は、下当金部材（２８）により支持され、前記非移動側端部の外面はベローズケース（１３）に設けられた調整ねじ部材（３３）に支持され、更に、その側面はベローズケース（１３）の内面に支持されていることを特徴とする。
【０００９】
請求項４記載の可変容量型圧縮機用の制御弁は、請求項１乃至請求項３記載のいずれかの可変容量型圧縮機用の制御弁において、上記嵌合凹部（３１ｂ）の底部は、上記下当金部材（２８）の中心部に形成されたストッパ面部（２８ａ）と当接可能なストッパ面部（３１ａ）を構成することを特徴とする。
【００１０】
請求項５記載の可変容量型圧縮機用の制御弁は、請求項１又は請求項２記載の可変容量型圧縮機用の制御弁において、前記ベローズ本体（２７）の非移動側端部は、上記当金部材（３１）と略同一形状の下当金部材（２８’）に装着され、該下当金部材（２８’）の側面はベローズケース（１３）に立設された支持筒部（１３’）に支持され、該下当金部材（２８’）の中心部に形成されたストッパ面部（２８’ａ）は調整ねじ部材（３３’）から延設された支持部（３３’ｂ）に支持されていることを特徴とする。
【００１１】
請求項６記載の可変容量型圧縮機用の制御弁は、請求項１乃至請求項５記載のいずれかの可変容量型圧縮機用の制御弁において、上記嵌合凹部（３１ｂ）内にはボール（４０）が内装され、該ボール（４０）に当接させて弁棒（２５”）が遊動可能に嵌合されていることを特徴とする。
【００１２】
【発明の実施の形態】
【実施例１】
以下、本発明の実施の形態について図面を参照して説明する。図１は本発明に係る実施例１の制御弁の縦断面図である。なお、下記説明中、上・下・左・右の表現は、図面中の構成を説明する都合上の表現であり、実際にはこの表現通りの位置関係にあるとは限るものではない。また、図中、矢印は，冷媒の流れ方向を示している。実施例１の制御弁１０は、可変容量型圧縮機（図示省略）のハウジングに形成される制御弁装着孔に冷媒の吐出管からクランク室への冷媒流量の流量制御弁として挿入固定される。
【００１３】
制御弁１０は、筒状の弁ハウジング１１と、弁ハウジング１１の上端に取り付けられたエンドキャップ１２と、弁ハウジング１１の下端にかしめ結合されたベローズケース１３とを有している。
【００１４】
弁ハウジング１１とエンドキャップ１２との組立体は、弁室１４と、弁座部１５により画定される弁ポート１６と、弁ポート１６の一方の側に形成される第１ポート１７と、弁ポート１６の他方の側に弁室１４を隔てて配置されるばね受け座２３と、該ばね受け座２３に形成される第２ポート１８と、弁棒保持孔１９を有している。エンドキャップ１２には第２ポート１８のためのフィルタ２０が一体成形で取り付けられている。
【００１５】
弁室１４内にはボール弁２１が設けられており、ボール弁２１の上下方向（弁リフト方向）の移動によってボール弁２１と弁座部１５との離間量が変化し、弁開度が決まる。弁室１４内のボール受け部材２２と上記ばね受け座２３との間にはボール弁２１を、常時閉弁方向へ付勢する圧縮コイルばね２４が設けられている。
【００１６】
弁棒保持孔１９は、圧縮コイルばね２４の配置部とはボール弁２１を隔てた反対側の弁ハウジング１１部分に、弁座部１５と同芯上に位置するように形成されており、該弁棒保持孔１９には丸棒状の弁棒２５が弁棒保持孔１９の軸線方向である弁リフト方向に移動可能に挿入されている。そして、弁棒２５の下端部はアール状に形成され、後述の当金部材３１の嵌合凹部３１ｂに嵌合される当接端部２５ａを構成している。そして、弁棒２５はボール弁２１を圧縮コイルばね２４のばね力に抗して開弁駆動する。なお、上記弁棒２５の下端部縁部のアール形状に代えて、下端部を半円球形状としてもよい。
【００１７】
ベローズケース１３内には密閉構造のベローズ２６が配置されている。ベローズ２６は、その内部に当金部材３１と下当金部材２８とが具備され、当金部材３１にはベローズ本体２７の上部開口端である閉塞端面２７ａが溶接される。また、下当金部材２８は、ベローズ本体２７下部の肉厚部からなるベローズ本体底部２７ｂ内に配置されて構成される。そして、ベローズ本体２７の内部は真空圧になっている。
【００１８】
ベローズ本体２７の内部には、ベローズ２６を伸張方向に付勢する圧縮コイルばね３０が、下当金部材２８と当金部材３１との間に縮装されて配置されている。また、ベローズ本体２７の移動側端部に設けられる当金部材３１は平面形状が円形の基板部３１ｃと、その中央部が下方（下当金部材２８側）に延設されて形成された径大部３１ｄを介して嵌合凹部３１ｂと、からなり、該嵌合凹部３１ｂの下面がストッパ面部３１ａとして構成される。上記基板部３１ｃの下面は圧縮コイルばね３０の一端を受承し、その上面はベンハウジング１１と当接する。
しかも、嵌合凹部３１ｂの内径は、弁棒に対して当金部材３１が傾動可能となるような大きさに形成される。なお、ベローズ本体２７の閉塞端面２７ａは上記基板部３１ｃに溶接される。また、圧縮コイルバネ３０の一端はベローズ２６の内側で基板部３１ｃの下面で受けている。
【００１９】
一方、ベローズ２６の非移動側端部を支持する下当金部材２８は円盤状の基板部２８ｃとその中心部に当金部材３１側に凸状に延出させて形成させたストッパ面部２８ａとで構成されており、当金部材３１の上記ストッパ面部３１ａと下当金部材２８の上面のストッパ面部２８ａとの当接により、ベローズ２６の最大収縮量が規定されている。また、ストッパ面部２８ａには、通孔２８ｂが穿設されており、下当金部材２８で画定される上下の空間を連通している。なお、基板部２８ｃが圧縮されバネ３０の他端を受ける。
ベローズケース１３にはポート３２が形成されており、ベローズ２６はポート３２からベローズケース１３内に導入される吸込圧力Ｐｓとベローズ内圧との差圧に応じて伸縮する。
【００２０】
ベローズケース１３に形成された下部ネジ孔には調整ねじ部材３３が上下位置調整可能にねじ係合されており、該調整ねじ部材３３の上端面部には、ベローズ本体２７のベローズ本体底部２７ｂが当接して保持されている。
【００２１】
なお、ベローズ本体２７の上部は、当金部材３１と下当金部材２８の間に配置された圧縮コイルばね３６により、上方、即ち、当金部材３１側に付勢され、上方では弁棒２５側の当接端部２５ａと当金部材３１側のストッパ面部３１ａの当接状態が保たれるようになっている。また、符号２７ｃは、ベローズ本体２７がベローズケース１３の肩部に当接して支持されている被支持部である。
【００２２】
弁棒２５と当金部材３１との接続部は、弁棒保持孔１９に挿入されている弁棒２５の下端部を構成するアール形状の当接端部２５ａと、該当接端部２５ａを遊動可能に嵌合する前記嵌合凹部３１ｂとからなり、継手構造を形成している。また、ベローズ２６の伸縮は、前記継手構造を介して弁棒２５及びボール弁２１に伝えられる。
なお、この制御弁１０が可変容量型圧縮機のハウジングに装着された状態において、可変容量型圧縮機のハウジングと弁ハウジング１１との間には、第１ポート１７を挟んでシールリングＳ１，Ｓ２が配置され、クランク室圧力Ｐｃに対する大気圧をシールしており、また、同ハウジングとベローズケース１３との間には、ポート３２の下部位置にシールリングＳ３，Ｓ４が配置され、吸入圧力Ｐｓに対する大気圧をシールしている。
【００２３】
上述の構造による制御弁１０は、可変容量型圧縮機に組込まれた状態において、ベローズ本体２７内の圧縮コイルばね３０の付勢力が、可変容量型圧縮機からポート３２を介して導入される吸入圧力Ｐｓに勝ると、伸張したベローズ本体２７の当金部材３１がエンドキャップ１２側に押圧されることになる。
【００２４】
すると、この当金部材３１により押圧された弁棒２５が、圧縮コイルばね２４のばね力に抗してボール弁２１をエンドキャップ１２側に押圧し、弁ポート１６から離間させて、制御弁１０を開弁させることになる。
【００２５】
上述の継手構造によれば、弁棒２５側の当接端部２５ａとベローズ本体２７側の当金部材３１に形成された嵌合凹部３１ｂとが接続され、当接端部２５ａのアール部と嵌合凹部３１ｂによって、弁棒２５が嵌合凹部３１ｂの底面に揺動可能に当接し、且つ、該当接位置が、ベローズ本体２７の下部位置となるために、ベローズ２６が蛇行したり、ベローズ２６に傾きがあっても上記当接位置の横移動は少ないものとなり、弁棒２５に対する横方向の変位力も小さいものとなる。
【００２６】
これらのことにより、ベローズ２６が蛇行しようとしたり、ベローズ２６に傾き力が作用しても、弁棒２５の下部への作用は少なくなり、弁開閉動作におけるヒステリシスを極小にして高精度な制御特性が得られ、更に、ベローズ２６及び弁棒２５の耐久性が向上する。
しかも、弁棒２５の下端（当接端部２５ａ）位置を、ベローズ２６の伸縮方向（上下方向）のほぼ中央位置か、またはそれよりベローズ本体底部２７ｂ側に設置することにより、ベローズ２６の当金部材３１の基板部３１ｃの側に位置する場合に比べ、弁棒２５へのベローズ２６の傾き力の作用が少なくなり、ヒステリシスを極小にすることができる。
【００２７】
【実施例２】
次に、実施例２について図２を参照しながら説明する。実施例２の説明において、実施例１と同一構成部材については、図２に図１と同一符号を付すことによって説明を省略する。
【００２８】
実施例２の制御弁１０’が実施例１の制御弁１０と相違する点は、当金部材３１’の形状、即ち、嵌合凹部３１’ｂにおける弁棒２５’側の当接端部２５ａを支持する長さを短くした点（第１の点）、そして、ベローズケース１３’、下当金部材２８’、及び、該下当金部材２８’を支持する調整ねじ部材３３’、の各形状（第２の点）にある。
【００２９】
即ち、第１の点については、当金部材３１’において、基板部３１’ｃと嵌合凹部３１’ｂとの間に形成される径大部３１’ｄが実施例１に比べて上下に長く形成され、その長い分だけ嵌合凹部３１’ｂが短くなっている。その結果、弁棒２５に対する当金部材３１’の傾斜自由度が向上することになる。
【００３０】
また、第２の点については、下当金部材２８’は全体として当金部材３１’と略同一形状に形成されると共に、ベローズケース１３’の下部に装着される調整ねじ部材３３’近傍のベローズ室内側に、ベローズ室内に向けて延設して支持筒部１３’ａが形成されており、また、調整ねじ部材３３’は、ストッパ面部２８’ａに当接する位置まで延接部３３’ａを介して支持部３３’ｂが一体的に形成されている。更に、上記延設部３３’ａの周面部は前記支持筒部１３’ａに支持されている。その結果、下当金部材２８’は、支持筒部１３’ａ及び支持部３３’ｂに確実に支持されることになり、ベローズ本体２７の下部の支持が安定する。
さらに、支持部３３’ｂの下当金部材２８’の当接端部をアール部又は球形状にすることで、ベローズ２７の傾きが生じても安定して支持させることができる。
【００３１】
実施例２によれば、上記構成、即ち、前記ベローズ本体２７の非移動側端部は、上記当金部材３１’と略同一形状の下当金部材２８’に装着され、該下当金部材２８’はベローズケース１３’の底部に当接して支持されると共に、その側面はベローズケース１３’に立設された支持筒部１３’ａに支持され、更に、該下当金部材２８’の中心部に形成されたストッパ面部２８’ａは調整ねじ部材３３’から延設された支持部３３’ｂに支持されていることにより、ベローズ本体２７の下部を安定的な支持状態とし、上部はベローズ本体２７の蛇行・傾きに対して、弁棒２５はその下部の比較的フレキシブルな継手構造により、左右に偏心力を受けることなく、安定的な上下動を実現させることができる。
【００３２】
【実施例３】
次に、実施例３の制御弁１０”について図３を参照しながら説明する。実施例３の説明において、実施例１と同一構成部材については、図３に図１と同一符号を付すことによって説明を省略する。
【００３３】
実施例３の制御弁１０”において、実施例１の制御弁１０の構成、即ち、圧力感知素子として密閉構造のベローズケース１３に保持されたベローズ本体２７を具備し、可変容量型圧縮機の吸入圧力Ｐｓの変動に伴なう前記ベローズ本体２７の伸縮をベローズケース１３と一体の弁ハウジング１１より弁リフト方向に移動可能に支持された弁棒２５を介してボール弁２１に伝えることにより開弁量を変化させる可変容量型圧縮機用の制御弁において、ベローズ本体２７の移動側端部に当金部材３１が設けられ、該当金部材３１には嵌合凹部３１ｂが形成されると共に該嵌合凹部３１ｂには弁棒２５が遊動可能に嵌合され、且つ、上記当金部材３１と、前記ベローズ本体２７の非移動側端部を支持する下当金部材２８との間には圧縮コイルばね３０が介装されている点、及び、前記ベローズ本体２７の非移動側端部の内面側は、下当金部材２８により支持され、前記非移動側端部の外面はベローズケース１３に設けられた調整ねじ部材３３に支持され、更に、その側面はベローズケース１３の内面に支持されている点、及び、上記嵌合凹部３１ｂの底部は、上記下当金部材２８の中心部に形成されたストッパ面部２８ａと当接可能なストッパ面部３１ａを構成することは、実施例１と同じである。
【００３４】
実施例３においては、 上記嵌合凹部３１ｂ内にはボール４０が遊転可能に内装され、該ボール４０に当接させて弁棒２５”が遊動可能に嵌合されている。この弁棒２５”の長さは、実施例１の弁棒２５の長さよりも、ボール４０の直径ぶんだけ短く形成されている。実施例３によれば、部品点数は多くなるものの、円滑な制御弁の作動が可能となる。
なお、図２に示す実施例２においても嵌合凹部３１’ｂ内にボール４０を遊転可能に内装し、弁棒２５’の当接端部２５ａと当接させても良い。
【００３５】
【発明の効果】
以上の説明から理解される如く、本発明による可変容量型圧縮機用の制御弁によれば、ベローズの真直度が多少悪くても、弁開閉動作におけるヒステリシスを極小にし、弁開閉動作の精度を高めることができる。
【図面の簡単な説明】
【図１】本発明に係る実施例１の制御弁の縦断面図。
【図２】本発明に係る実施例２の制御弁の縦断面図。
【図３】本発明に係る実施例３の制御弁の縦断面図。
【符号の説明】
Ｐｃ・・クランク室圧力 Ｐｓ・・吸入圧力（圧縮機吸入圧力）
Ｐｄ・・吐出圧力
１０，１０’，１０”・・制御弁 １１・・弁ハウジング
１２・・エンドキャップ
１３，１３’・・ベローズケース １３’ａ・・支持筒部 １４・・弁室
１５・・弁座部 １６・・弁ポート １７・・第１ポート
１８・・第２ポート １９・・弁棒保持孔 ２０・・フィルタ
２１・・ボール弁（弁体） ２２・・ボール受け部材 ２３・・ばね受け座
２４・・圧縮コイルばね
２５，２５’，２５”・・弁棒 ２５ａ・・当接端部 ２５ｂ・・当接周面
２６・・ベローズ ２７・・ベローズ本体
２７ａ・・閉塞端面 ２７ｂ・・ベローズ本体底部 ２７ｃ・・被支持部
２８，２８’・・下当金部材 ２８ａ，２８’ａ・・ストッパ面部
２８ｂ・・通孔 ２８ｃ・・当接部
３０・・圧縮コイルばね ３１，３１’・・当金部材
３１ａ・・ストッパ面部 ３１ｂ，３１’ｂ・・嵌合凹部
３１ｃ，３１’ｃ・・基板部 ３１ｄ，３１’ｄ・・径大部
３２・・ポート ３３，３３’・・調整ねじ部材
３３’ａ・・延接部 ３３’ｂ・・支持部 ３６・・圧縮コイルばね
４０・・ボール[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a control valve for a variable displacement compressor.
[0002]
[Prior art]
The use of a bellows-type pressure-responsive valve as a displacement control valve provided in a variable displacement compressor or the like is disclosed in Patent Document 1. The bellows type pressure responsive valve has an advantage that it is small in size and can have a long pressure response stroke as compared with a diaphragm type pressure responsive valve.
[0003]
However, in general, it is difficult for the bellows to obtain high straightness due to its structure.If the bellows meanders in the valve lift direction, a lateral force is generated when the bellows expands and contracts in the valve lift direction. The transmission of this lateral force to the valve stem causes an increase in hysteresis in the valve opening / closing operation and the like, which causes a control failure and lowers the valve opening / closing accuracy.
[0004]
Therefore, the bellows-type pressure responsive valve described in Patent Document 2 below has a bellows having a closed structure as a pressure sensing element, and the expansion and contraction of the bellows is performed via a valve rod supported to be movable in a valve lift direction from a valve housing. In a bellows-type pressure-responsive valve that changes the valve opening by transmitting it to a ball valve, a spherical joint structure consisting of an end plate and a ball integrated with the bellows is incorporated at the connection between the bellows and the valve rod, and the spherical connection is made. I have to.
[0005]
[Patent Document 1]
Japanese Utility Model Publication No. 02-37001 [Patent Document 2]
JP 2000-88132 A
[Problems to be solved by the invention]
However, according to the above-described known example, since the expansion and contraction of the bellows is transmitted to the valve body via the spherical joint structure including the ball and the lower metal member, the ball and the lower metal member are used in the expansion and contraction of the bellows. In addition, there is a problem that not only the positional deviation may occur but also the number of parts increases.
Accordingly, an object of the present invention is to provide a control valve for a variable displacement compressor in which a displacement that does not occur due to a joint that allows the joint member to be tilted does not occur and the number of parts is reduced to reduce the number of assembly steps. It is to provide a valve.
[0007]
[Means to solve the problem]
The present invention takes the following measures to achieve the above object. That is,
The control valve for a variable displacement compressor according to the first aspect includes a bellows body (27) held as a pressure sensing element in a closed bellows case (13), and a suction pressure of the variable displacement compressor (13). The expansion and contraction of the bellows body (27) accompanying the fluctuation of Ps) is performed via a valve rod (25) supported so as to be movable in a valve lift direction from a valve housing (11) integral with the bellows case (13). In a control valve for a variable displacement compressor that changes a valve opening amount by transmitting it to a body, a contact member (31) is provided at a moving-side end of the bellows body (27), and the corresponding metal member (31) is provided. A fitting recess (31b) is formed in the fitting recess (31b), and a valve stem (25) is movably fitted in the fitting recess (31b). The fitting member (31) and the bellows body ( 27) Lower support that supports the non-moving side end Between the wood (28), characterized in that the compression coil spring (30) is interposed.
[0008]
The control valve for a variable displacement compressor according to the second aspect is the control valve for a variable displacement compressor according to the first aspect, which is in contact with the fitting recess (31b) of the valve rod (25). The position of the contact end portion 25a is substantially at the center of the bellows main body (27) or at a position closer to the non-movable side end portion than the center.
The control valve for a variable displacement compressor according to claim 3 is the control valve for a variable displacement compressor according to claim 1 or 2, wherein an inner surface of a non-moving-side end of the bellows body (27). The side is supported by a lower abutment member (28), the outer surface of the non-moving side end is supported by an adjusting screw member (33) provided on the bellows case (13), and the side surface thereof is a bellows case ( 13) It is supported on the inner surface.
[0009]
A control valve for a variable displacement compressor according to claim 4 is the control valve for a variable displacement compressor according to any one of claims 1 to 3, wherein a bottom of the fitting recess (31b) is: The present invention is characterized in that a stopper surface portion (31a) which can be brought into contact with a stopper surface portion (28a) formed at the center of the lower abutment member (28) is characterized.
[0010]
The control valve for a variable displacement compressor according to claim 5 is the control valve for a variable displacement compressor according to claim 1 or 2, wherein the non-moving-side end of the bellows body (27) is: The lower support member (28 ') is attached to a lower support member (28') having substantially the same shape as the above-described support member (31), and a side surface of the lower support member (28 ') is supported by a support cylinder ( 13 '), and a stopper surface portion (28'a) formed at the center of the lower abutment member (28') extends from the adjusting screw member (33 ') to a support portion (33'b). It is characterized by being supported by.
[0011]
A control valve for a variable displacement compressor according to claim 6 is the control valve for a variable displacement compressor according to any one of claims 1 to 5, wherein a ball is provided in the fitting recess (31b). (40) is provided therein, and the valve stem (25 ") is fitted movably in contact with the ball (40).
[0012]
BEST MODE FOR CARRYING OUT THE INVENTION
Embodiment 1
Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal sectional view of a control valve according to a first embodiment of the present invention. In the following description, the expressions “up”, “down”, “left” and “right” are expressions for the sake of convenience in describing the configuration in the drawings, and are not necessarily limited to the actual positional relationship. Also, in the figure, arrows indicate the flow direction of the refrigerant. The control valve 10 of the first embodiment is inserted and fixed in a control valve mounting hole formed in a housing of a variable displacement compressor (not shown) as a flow control valve of a refrigerant flow from a refrigerant discharge pipe to a crank chamber.
[0013]
The control valve 10 has a cylindrical valve housing 11, an end cap 12 attached to an upper end of the valve housing 11, and a bellows case 13 which is caulked to a lower end of the valve housing 11.
[0014]
An assembly of the valve housing 11 and the end cap 12 includes a valve chamber 14, a valve port 16 defined by a valve seat 15, a first port 17 formed on one side of the valve port 16, and a valve port. The spring receiving seat 23 has a second port 18 formed in the other side of the valve chamber 14 and the valve port holding hole 19. A filter 20 for the second port 18 is attached to the end cap 12 by integral molding.
[0015]
A ball valve 21 is provided in the valve chamber 14, and the vertical distance (valve lift direction) of the ball valve 21 changes the amount of separation between the ball valve 21 and the valve seat 15 to determine the valve opening. . A compression coil spring 24 is provided between the ball receiving member 22 and the spring receiving seat 23 in the valve chamber 14 to constantly bias the ball valve 21 in the valve closing direction.
[0016]
The valve stem holding hole 19 is formed in the portion of the valve housing 11 opposite to the portion where the compression coil spring 24 is disposed and separated from the ball valve 21 so as to be located coaxially with the valve seat portion 15. A round rod-shaped valve stem 25 is inserted into the valve stem holding hole 19 so as to be movable in the valve lift direction which is the axial direction of the valve stem holding hole 19. The lower end portion of the valve stem 25 is formed in a round shape, and constitutes a contact end portion 25a to be fitted into a fitting concave portion 31b of the contact member 31 described later. Then, the valve stem 25 drives the ball valve 21 to open the valve against the spring force of the compression coil spring 24. Note that, instead of the round shape of the lower end edge portion of the valve stem 25, the lower end portion may have a semicircular spherical shape.
[0017]
A bellows 26 having a closed structure is arranged in the bellows case 13. The bellows 26 has an abutment member 31 and a lower abutment member 28 therein, and a closed end surface 27 a which is an upper open end of the bellows main body 27 is welded to the abutment member 31. In addition, the lower abutment member 28 is disposed and configured in a bellows main body bottom portion 27b formed of a thick portion below the bellows main body 27. The inside of the bellows body 27 is at a vacuum pressure.
[0018]
Inside the bellows body 27, a compression coil spring 30 for urging the bellows 26 in the extension direction is compressed and arranged between the lower abutment member 28 and the abutment member 31. The abutting member 31 provided at the moving-side end of the bellows main body 27 has a circular base portion 31c having a circular planar shape, and a central portion extending downward (toward the lower abutting member 28). The fitting recess 31b is formed via the large portion 31d, and the lower surface of the fitting recess 31b is configured as a stopper surface 31a. The lower surface of the substrate portion 31c receives one end of the compression coil spring 30, and the upper surface thereof contacts the ben housing 11.
Moreover, the inner diameter of the fitting recess 31b is formed in such a size that the abutment member 31 can tilt with respect to the valve stem. The closed end surface 27a of the bellows main body 27 is welded to the substrate 31c. One end of the compression coil spring 30 is received inside the bellows 26 on the lower surface of the substrate 31c.
[0019]
On the other hand, the lower abutment member 28 supporting the non-moving-side end of the bellows 26 has a disc-shaped substrate portion 28c and a stopper surface portion 28a formed at the center thereof so as to protrude toward the abutment member 31 side. The maximum contraction amount of the bellows 26 is defined by the contact between the stopper surface 31a of the contact member 31 and the stopper surface 28a on the upper surface of the lower contact member 28. Further, a through hole 28b is formed in the stopper surface portion 28a, and communicates with the upper and lower spaces defined by the lower abutment member 28. The substrate 28c is compressed and receives the other end of the spring 30.
A port 32 is formed in the bellows case 13, and the bellows 26 expands and contracts according to a pressure difference between the suction pressure Ps introduced into the bellows case 13 from the port 32 and the bellows internal pressure.
[0020]
An adjusting screw member 33 is screw-engaged with a lower screw hole formed in the bellows case 13 so as to be able to adjust the vertical position, and a bottom surface 27b of the bellows main body 27 of the bellows main body 27 contacts the upper end surface of the adjusting screw member 33. Held in contact.
[0021]
The upper part of the bellows main body 27 is urged upward, that is, toward the contact member 31 by a compression coil spring 36 disposed between the contact member 31 and the lower contact member 28, and the valve stem 25 is located upward. The contact state between the contact end portion 25a on the side and the stopper surface 31a on the contact member 31 is maintained. Reference numeral 27c denotes a supported portion in which the bellows body 27 is supported in contact with the shoulder of the bellows case 13.
[0022]
The connecting portion between the valve stem 25 and the abutment member 31 moves between a rounded abutting end portion 25a constituting the lower end portion of the valve stem 25 inserted into the valve stem holding hole 19 and the corresponding abutting end portion 25a. The fitting recess 31b fits as much as possible to form a joint structure. The expansion and contraction of the bellows 26 is transmitted to the valve stem 25 and the ball valve 21 via the joint structure.
When the control valve 10 is mounted on the housing of the variable displacement compressor, the seal rings S1 and S2 are disposed between the housing of the variable displacement compressor and the valve housing 11 with the first port 17 interposed therebetween. Are arranged to seal the atmospheric pressure with respect to the crank chamber pressure Pc. Further, between the housing and the bellows case 13, seal rings S3 and S4 are arranged at a lower position of the port 32, so that the suction pressure Ps is reduced. Atmospheric pressure is sealed.
[0023]
In the control valve 10 having the above-described structure, when the control valve 10 is incorporated in the variable displacement compressor, the urging force of the compression coil spring 30 in the bellows body 27 is introduced through the port 32 from the variable displacement compressor. When the pressure Ps is exceeded, the contact member 31 of the extended bellows body 27 is pressed toward the end cap 12.
[0024]
Then, the valve rod 25 pressed by the abutment member 31 presses the ball valve 21 toward the end cap 12 against the spring force of the compression coil spring 24, and separates the ball valve 21 from the valve port 16. Will be opened.
[0025]
According to the above-described joint structure, the contact end portion 25a on the valve stem 25 side is connected to the fitting concave portion 31b formed in the contact member 31 on the bellows main body 27 side, and the round portion of the contact end portion 25a is connected. The fitting recess 31b allows the valve stem 25 to swingably contact the bottom surface of the fitting recess 31b, and the corresponding contact position is a lower position of the bellows main body 27. Even if the 26 has an inclination, the lateral movement of the contact position is small, and the lateral displacement force on the valve stem 25 is also small.
[0026]
As a result, even if the bellows 26 meanders or a tilting force acts on the bellows 26, the action on the lower part of the valve rod 25 is reduced, and the hysteresis in the valve opening / closing operation is minimized to achieve high-precision control characteristics. , And the durability of the bellows 26 and the valve stem 25 is further improved.
In addition, the lower end (abutting end portion 25a) of the valve stem 25 is located substantially at the center of the bellows 26 in the expansion / contraction direction (vertical direction) or at the lower side of the bellows body bottom portion 27b. Compared to the case where the metal member 31 is located on the side of the substrate portion 31c, the effect of the inclination force of the bellows 26 on the valve stem 25 is reduced, and the hysteresis can be minimized.
[0027]
Embodiment 2
Next, a second embodiment will be described with reference to FIG. In the description of the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals in FIG.
[0028]
The control valve 10 'of the second embodiment differs from the control valve 10 of the first embodiment in the shape of the abutment member 31', that is, the contact end 25a of the fitting recess 31'b on the valve rod 25 'side. , And the length of the bellows case 13 ′, the lower support member 28 ′, and the adjusting screw member 33 ′ supporting the lower support member 28 ′. In shape (second point).
[0029]
That is, as for the first point, in the metal member 31 ′, the large-diameter portion 31 ′ d formed between the substrate portion 31 ′ c and the fitting concave portion 31 ′ b is vertically higher than in the first embodiment. It is formed long, and the fitting recess 31′b is shortened by the length. As a result, the degree of freedom of inclination of the abutment member 31 ′ with respect to the valve stem 25 is improved.
[0030]
Regarding the second point, the lower abutment member 28 'is formed to have substantially the same shape as the abutment member 31' as a whole, and the vicinity of the adjustment screw member 33 'attached to the lower portion of the bellows case 13'. A support cylindrical portion 13'a is formed on the inner side of the bellows extending toward the bellows chamber, and the adjusting screw member 33 'extends to a position where it comes into contact with the stopper surface portion 28'a. The support part 33'b is integrally formed through "a". Further, the peripheral surface of the extending portion 33'a is supported by the support cylinder 13'a. As a result, the lower abutment member 28 'is reliably supported by the support cylinder 13'a and the support 33'b, and the lower support of the bellows main body 27 is stabilized.
Further, by forming the contact end of the lower abutment member 28 'of the support portion 33'b into a round shape or a spherical shape, the bellows 27 can be stably supported even if it is inclined.
[0031]
According to the second embodiment, the above configuration, that is, the non-moving-side end of the bellows main body 27 is attached to the lower support member 28 ′ having substantially the same shape as the lower support member 31 ′. 28 'is in contact with and supported by the bottom of the bellows case 13', and its side surface is supported by a support cylinder 13'a erected on the bellows case 13 '. The stopper surface portion 28'a formed at the center portion is supported by a support portion 33'b extending from the adjusting screw member 33 ', so that the lower portion of the bellows main body 27 is stably supported, and the upper portion is With respect to the meandering / tilting of the bellows body 27, the valve rod 25 can realize a stable vertical movement without receiving an eccentric force on the left and right due to the relatively flexible joint structure at the lower part thereof.
[0032]
Embodiment 3
Next, a control valve 10 ″ of the third embodiment will be described with reference to FIG. 3. In the description of the third embodiment, the same components as those of the first embodiment are denoted by the same reference numerals in FIG. Description is omitted.
[0033]
In the control valve 10 "of the third embodiment, the structure of the control valve 10 of the first embodiment, that is, the bellows body 27 held as a pressure sensing element in the bellows case 13 having a closed structure is provided, and the suction of the variable displacement compressor is performed. The valve is opened by transmitting the expansion and contraction of the bellows main body 27 accompanying the fluctuation of the pressure Ps to the ball valve 21 via the valve rod 25 supported movably in the valve lift direction from the valve housing 11 integral with the bellows case 13. In the control valve for the variable displacement compressor that changes the amount, a contact member 31 is provided at the moving-side end of the bellows body 27, and a fitting recess 31b is formed in the corresponding metal member 31 and the fitting member 31 is formed. A valve rod 25 is movably fitted into the concave portion 31b, and a compression coil spring is provided between the abutment member 31 and the lower abutment member 28 supporting the non-moving-side end of the bellows body 27. 3 And the inner surface of the non-moving end of the bellows body 27 is supported by a lower abutment member 28, and the outer surface of the non-moving end is provided in the bellows case 13. A point supported by the adjusting screw member 33, and a side surface thereof is supported by the inner surface of the bellows case 13, and a bottom portion of the fitting concave portion 31b is a stopper formed at the center of the lower abutment member 28. The configuration of the stopper surface portion 31a that can contact the surface portion 28a is the same as that of the first embodiment.
[0034]
In the third embodiment, a ball 40 is rotatably mounted in the fitting recess 31b, and a valve stem 25 "is movably fitted in contact with the ball 40. The valve stem 25" The length is formed shorter than the length of the valve stem 25 of the first embodiment by the diameter of the ball 40. According to the third embodiment, although the number of parts is increased, the control valve can be operated smoothly.
In the second embodiment shown in FIG. 2, the ball 40 may be freely rotatably provided in the fitting recess 31'b and may be brought into contact with the contact end 25a of the valve rod 25 '.
[0035]
【The invention's effect】
As can be understood from the above description, according to the control valve for a variable displacement compressor according to the present invention, even if the straightness of the bellows is somewhat poor, the hysteresis in the valve opening / closing operation is minimized, and the accuracy of the valve opening / closing operation is improved. Can be enhanced.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a control valve according to a first embodiment of the present invention.
FIG. 2 is a longitudinal sectional view of a control valve according to a second embodiment of the present invention.
FIG. 3 is a longitudinal sectional view of a control valve according to a third embodiment of the present invention.
[Explanation of symbols]
Pc ... Crank chamber pressure Ps ... Suction pressure (compressor suction pressure)
Pd ··· Discharge pressure 10, 10 ', 10 ”··· Control valve 11 ··· Valve housing 12 ··· End cap 13, 13' ··· Bellows case 13'a ··· Support cylinder part 14 ··· Valve chamber 15 ··· Valve seat 16 Valve port 17 First port 18 Second port 19 Valve rod holding hole 20 Filter 21 Ball valve (valve element) 22 Ball receiving member 23 Spring Receiving seat 24-Compression coil spring 25, 25 ', 25 "-Valve stem 25a-Contact end 25b-Contact peripheral surface 26-Bellows 27-Bellows main body 27a-Closed end surface 27b- Bellows body bottom 27c Supported parts 28, 28 'Lower support member 28a, 28'a Stopper face 28b Through hole 28c Contact part 30, Compression coil spring 31, 31'・ Abutment member 31a ・ ・ Stopper surface 31b, 3 1'b Fitting recesses 31c, 31'c Board part 31d, 31'd Large diameter part 32 Port 33, 33 'Adjusting screw member 33'a Extension part 33' b support 36 compression coil spring 40 ball

Claims (6)

圧力感知素子として密閉構造のベローズケースに保持されたベローズ本体を具備し、可変容量型圧縮機の吸入圧力の変動に伴なう前記ベローズ本体の伸縮をベローズケースと一体の弁ハウジングより弁リフト方向に移動可能に支持された弁棒を介して弁体に伝えることにより開弁量を変化させる可変容量型圧縮機用の制御弁において、
前記ベローズ本体の移動側端部に当金部材が設けられ、該当金部材には嵌合凹部が形成されると共に該嵌合凹部には弁棒が遊動可能に嵌合され、且つ、上記当金部材と、前記ベローズ本体の非移動側端部を支持する下当金部材との間には圧縮コイルばねが介装されていることを特徴とする可変容量型圧縮機用の制御弁。The bellows body held as a pressure sensing element in a bellows case having a closed structure is provided. A control valve for a variable displacement compressor that changes a valve opening amount by transmitting it to a valve body via a valve rod movably supported by
An abutment member is provided at a moving-side end of the bellows body, a fitting concave portion is formed in the corresponding gold member, and a valve stem is movably fitted in the fitting concave portion. A control valve for a variable displacement compressor, characterized in that a compression coil spring is interposed between the member and a lower abutment member that supports a non-moving end of the bellows body. 上記弁棒の上記嵌合凹部に当接する当接端部の位置は、上記ベローズ本体の略中央又は該中央より非移動側端部側の位置とされていることを特徴とする請求項１記載の可変容量型圧縮機用の制御弁。The position of the contact end of the valve stem that abuts the fitting recess is substantially at the center of the bellows body or at a position closer to the non-moving end than the center. Control valve for variable displacement compressor. 前記ベローズ本体の非移動側端部の内面側は、下当金部材により支持され、前記非移動側端部の外面はベローズケースに設けられた調整ねじ部材に支持され、更に、その側面はベローズケースの内面に支持されていることを特徴とする請求項１又は２記載の可変容量型圧縮機用の制御弁。The inner surface side of the non-moving side end of the bellows body is supported by a lower abutment member, the outer surface of the non-moving side end is supported by an adjusting screw member provided on a bellows case, and the side surface is further provided with a bellows. 3. The control valve for a variable displacement compressor according to claim 1, wherein the control valve is supported on an inner surface of the case. 上記嵌合凹部の底部は、上記下当金部材の中心部に形成されたストッパ面部と当接可能なストッパ面部を構成することを特徴とする請求項１乃至請求項３記載のいずれかの可変容量型圧縮機用の制御弁。The variable portion according to any one of claims 1 to 3, wherein a bottom portion of the fitting recess forms a stopper surface portion that can contact a stopper surface portion formed at a center portion of the lower abutment member. Control valve for displacement compressor. 前記ベローズ本体の非移動側端部は、上記当金部材と略同一形状の下当金部材に装着され、該下当金部材の側面はベローズケースに立設された支持筒部に支持され、該下当金部材の中心部に形成されたストッパ面部は調整ねじ部材から延設された支持部に支持されていることを特徴とする請求項１又は請求項２記載の可変容量型圧縮機用の制御弁。The non-moving-side end of the bellows body is attached to a lower support member having substantially the same shape as the above-mentioned support member, and the side surface of the lower support member is supported by a support cylinder portion erected on the bellows case, 3. The variable displacement compressor according to claim 1, wherein a stopper surface portion formed at a center portion of the lower metal member is supported by a support portion extending from the adjusting screw member. Control valve. 上記嵌合凹部内にはボールが内装され、該ボールに当接させて弁棒が遊動可能に嵌合されていることを特徴とする請求項１乃至請求項５記載のいずれかの可変容量型圧縮機用の制御弁。The variable displacement type according to any one of claims 1 to 5, wherein a ball is provided inside the fitting recess, and a valve stem is loosely fitted in contact with the ball. Control valve for compressor.
JP2002327909A 2002-11-12 2002-11-12 Control valve for variable displacement compressor Pending JP2004162567A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP2002327909A JP2004162567A (en) 2002-11-12 2002-11-12 Control valve for variable displacement compressor
US10/689,699 US20040091368A1 (en) 2002-11-12 2003-10-22 Control valve for variable capacity compressor
KR1020030074265A KR20040042817A (en) 2002-11-12 2003-10-23 Control valve for variable capacity compressors
EP03026082A EP1420163B1 (en) 2002-11-12 2003-11-12 Control valve for variable capacity compressor
CNB2003101038506A CN100368685C (en) 2002-11-12 2003-11-12 Control valve for variable capacity compressor
DE60324237T DE60324237D1 (en) 2002-11-12 2003-11-12 Control valve for a compressor of variable displacement

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2002327909A JP2004162567A (en) 2002-11-12 2002-11-12 Control valve for variable displacement compressor

Publications (1)

Publication Number Publication Date
JP2004162567A true JP2004162567A (en) 2004-06-10

Family

ID=32171351

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2002327909A Pending JP2004162567A (en) 2002-11-12 2002-11-12 Control valve for variable displacement compressor

Country Status (6)

Country Link
US (1) US20040091368A1 (en)
EP (1) EP1420163B1 (en)
JP (1) JP2004162567A (en)
KR (1) KR20040042817A (en)
CN (1) CN100368685C (en)
DE (1) DE60324237D1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006152934A (en) * 2004-11-30 2006-06-15 Fuji Koki Corp Pressure regulating valve
KR20200101259A (en) 2019-02-19 2020-08-27 가부시기가이샤 후지고오키 Valve device

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1884830B (en) * 2005-06-24 2010-09-29 上海三电贝洱汽车空调有限公司 Compressor control valve
JP4608395B2 (en) * 2005-08-23 2011-01-12 株式会社鷺宮製作所 Valve device and manufacturing method thereof
KR100890207B1 (en) * 2006-09-06 2009-03-25 주식회사 퍼시픽콘트롤즈 Variable capacity control valve
KR100942907B1 (en) * 2008-05-29 2010-02-16 영신기전공업(주) Control valve of capacity variable type compressors
CN101762130B (en) * 2008-12-24 2013-12-18 上海三电贝洱汽车空调有限公司 Control valve
JP5699259B2 (en) * 2011-01-07 2015-04-08 株式会社テージーケー Control valve for variable capacity compressor
CN102818068B (en) * 2011-06-08 2016-02-17 浙江三花股份有限公司 The electric expansion valve of a kind of valve body parts and this valve body parts of use
KR101462418B1 (en) * 2011-12-02 2014-11-19 주식회사 퍼시픽콘트롤즈 A Variable Capacity Control Valve
WO2017145798A1 (en) * 2016-02-22 2017-08-31 株式会社豊田自動織機 Volume-variable swash plate compressor
KR20200092519A (en) 2019-01-24 2020-08-04 주식회사 지에이티 Control valve for variable capacity type compressor and assembling methd thereof
EP3951170A4 (en) * 2019-04-03 2022-11-23 Eagle Industry Co., Ltd. Capacity control valve
CN113646530A (en) * 2019-04-03 2021-11-12 伊格尔工业股份有限公司 Capacity control valve
JP7451064B2 (en) 2019-04-24 2024-03-18 イーグル工業株式会社 capacity control valve
KR102093076B1 (en) 2019-10-14 2020-03-25 주식회사 지에이티 Control valve for variable-capacity compressor
KR102301578B1 (en) 2020-03-18 2021-09-14 주식회사 지에이티 Control valve for variable-capacity compressor, and assembly method for same
KR102565101B1 (en) 2021-07-23 2023-08-14 주식회사 지에이티 Control valve for variable capacity type compressor and assembling methd thereof

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5913175A (en) * 1982-07-09 1984-01-23 Matsushita Refrig Co Fluid control valve
JP3355002B2 (en) * 1993-10-15 2002-12-09 株式会社豊田自動織機 Control valve for variable displacement compressor
JP3432995B2 (en) * 1996-04-01 2003-08-04 株式会社豊田自動織機 Control valve for variable displacement compressor
JP4051134B2 (en) * 1998-06-12 2008-02-20 サンデン株式会社 Capacity control valve mechanism of variable capacity compressor
JP3435077B2 (en) * 1998-09-16 2003-08-11 株式会社鷺宮製作所 Bellows pressure operated valve
JP2001020857A (en) * 1999-07-05 2001-01-23 Toyota Autom Loom Works Ltd Control valve for variable displacement type compressor
JP4205826B2 (en) * 1999-11-30 2009-01-07 株式会社不二工機 Control valve for variable displacement compressor
JP2001153043A (en) * 1999-12-01 2001-06-05 Sanden Corp Variable displacement type swash plate compressor
JP2002089442A (en) * 2000-09-08 2002-03-27 Toyota Industries Corp Control valve for variable displacement compressor
JP2002221153A (en) * 2001-01-23 2002-08-09 Toyota Industries Corp Control valve for variable displacement type compressor
JP4829419B2 (en) * 2001-04-06 2011-12-07 株式会社不二工機 Control valve for variable displacement compressor
JP3982237B2 (en) * 2001-11-06 2007-09-26 株式会社豊田自動織機 Variable capacity compressor, air conditioner equipped with the variable capacity compressor, and control method in variable capacity compressor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006152934A (en) * 2004-11-30 2006-06-15 Fuji Koki Corp Pressure regulating valve
JP4644475B2 (en) * 2004-11-30 2011-03-02 株式会社不二工機 Pressure regulating valve
KR20200101259A (en) 2019-02-19 2020-08-27 가부시기가이샤 후지고오키 Valve device

Also Published As

Publication number Publication date
KR20040042817A (en) 2004-05-20
EP1420163B1 (en) 2008-10-22
CN100368685C (en) 2008-02-13
CN1499078A (en) 2004-05-26
EP1420163A2 (en) 2004-05-19
DE60324237D1 (en) 2008-12-04
US20040091368A1 (en) 2004-05-13
EP1420163A3 (en) 2005-08-24

Similar Documents

Publication Publication Date Title
JP2004162567A (en) Control valve for variable displacement compressor
JP5553514B2 (en) Control valve for variable displacement compressor
JP5222447B2 (en) Variable capacity compressor
WO2000015990A1 (en) Bellows type pressure responding valve
JP4051134B2 (en) Capacity control valve mechanism of variable capacity compressor
JP2000018172A (en) Capacity control valve mechanism of capacity variable compressor
JP4113425B2 (en) Piezoelectric element driven metal diaphragm type control valve
JP2002122070A (en) Control valve for variable displacement compressor
JP2004197652A (en) Control valve for variable displacement compressor
JP2012102782A (en) Diaphragm device
US20070068578A1 (en) Direct acting pressure reducing valve
JP3826583B2 (en) Control valve
KR102237210B1 (en) Thermal expansion valve
JP2024021648A (en) Pressure reduction valve
JP2001003872A (en) Small pump
CN111577907B (en) Valve device
JP4644475B2 (en) Pressure regulating valve
JP2024021649A (en) Pressure reduction valve
JP2013029241A (en) Expansion valve
JP2000009033A (en) Volume control valve for variable displacement compressor
KR100757507B1 (en) Displacement control valve for variable displacement compressor
JPH06173852A (en) Oscillating swash plate type variable displacement compressor
JP5269391B2 (en) Control valve for variable displacement compressor
KR20040010100A (en) A control valve
JP2012241726A (en) Pressure control valve

Legal Events

Date Code Title Description
RD03 Notification of appointment of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7423

Effective date: 20041119

A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20051013

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20080401

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20080331

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20080602

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20081209

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20090407