JPH07279843A - Displacement control valve for variable displacement compressor - Google Patents
Displacement control valve for variable displacement compressorInfo
- Publication number
- JPH07279843A JPH07279843A JP6070453A JP7045394A JPH07279843A JP H07279843 A JPH07279843 A JP H07279843A JP 6070453 A JP6070453 A JP 6070453A JP 7045394 A JP7045394 A JP 7045394A JP H07279843 A JPH07279843 A JP H07279843A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- valve
- valve body
- compressor
- main 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
Landscapes
- Control Of Positive-Displacement Pumps (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、カークーラに用いられ
る容量可変コンプレッサ用容量制御弁に関するものであ
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a displacement control valve for a variable displacement compressor used in a car cooler.
【０００２】[0002]
【従来の技術】図６において（特公平５−８３７５１
号）、Ａはコンプレッサ、Ｂは該コンプレッサＡの一側
の取付凹部Ｈに固着される高圧の容量制御弁である。コ
ンプレッサＡにおいて、クランクケース１に連続するヘ
ッド部２内には複数個のシリンダ３，３′…が設けら
れ、各シリンダ３，３′…内にはピストン４が摺動自在
に設けられる。クランクケース１からヘッド部２にかけ
て駆動軸５が回動自在に設けられ、該駆動軸５は外端に
設けたプーリ６を介してベルト７によりエンジン（図示
せず）で駆動される。駆動軸５には公知の如くに角度可
変ウオブル板８が設けられ、該ウオブル板８とピストン
４は環状溝８ａとソケット４ａを介して両端に球状結合
端９ａ，９ａを有するピストン桿９により連結され、駆
動軸５によりウオブル板８が傾斜状態において回動する
ことによりピストン桿９乃至ピストン４が往復動作し、
クランクケース１内の圧力Ｐｃとシリンダ３，３′…内
の吸入圧力Ｐｓとの差圧に応じてウオブル板８の取付角
度が自動的に調整され、ウオブル板８の角度変化により
ピストン４のストローク量が変化する。2. Description of the Related Art In FIG.
No.), A is a compressor, and B is a high-pressure capacity control valve fixed to a mounting recess H on one side of the compressor A. In the compressor A, a plurality of cylinders 3, 3 '... Are provided in a head portion 2 continuous with the crankcase 1, and a piston 4 is slidably provided in each cylinder 3, 3'. A drive shaft 5 is rotatably provided from the crankcase 1 to the head portion 2, and the drive shaft 5 is driven by an engine (not shown) by a belt 7 via a pulley 6 provided at an outer end. The drive shaft 5 is provided with a variable angle wobble plate 8 as is known, and the wobble plate 8 and the piston 4 are connected by a piston rod 9 having spherical coupling ends 9a, 9a at both ends via an annular groove 8a and a socket 4a. When the wobble plate 8 is tilted by the drive shaft 5, the piston rod 9 to the piston 4 reciprocate,
The mounting angle of the wobble plate 8 is automatically adjusted according to the pressure difference between the pressure Pc in the crankcase 1 and the suction pressure Ps in the cylinders 3, 3 '... The amount changes.
【０００３】各シリンダ３，３′…には、吸入口Ｓと吐
出口Ｄが設けられ、各吸入口Ｓは内部通路ｓにより、ま
た各吐出口Ｄは内部通路ｄによりそれぞれ相互に連通し
ている。一方のシリンダ３には通路ｓ′，ｄ′を介して
冷凍サイクルを構成する蒸発器１０と凝縮器１１が接続
される。吸入口Ｓにはピストン４の吸入行程において開
くと共に吐出行程において閉じる弁体１２が設けられ、
吐出口Ｄにはピストン４の吐出行程において開くと共に
吸入行程において閉じる弁体１３が設けられる。A suction port S and a discharge port D are provided in each of the cylinders 3, 3 '... The suction port S communicates with an internal passage s, and the discharge port D communicates with an internal passage d. There is. An evaporator 10 and a condenser 11 forming a refrigeration cycle are connected to one cylinder 3 via passages s'and d '. The intake port S is provided with a valve body 12 that opens in the intake stroke of the piston 4 and closes in the discharge stroke.
The discharge port D is provided with a valve body 13 that opens in the discharge stroke of the piston 4 and closes in the suction stroke.
【０００４】容量制御弁Ｂにおいて、弁本体１４の一側
に圧力応動部Ｍが設けられる。圧力応動部Ｍは、本体１
４に固着された下蓋１５に対して圧力応動部材としての
ダイヤフラム１６を挾持した状態で上蓋１７を設けると
共に該上蓋１７にばね箱１８を固着し、ばね箱１８内に
螺着した調整ねじ１９とダイヤフラム１６の上当金２０
に当接するばね受２１との間に調整スプリング２２を設
けて構成する。In the capacity control valve B, a pressure responsive portion M is provided on one side of the valve body 14. The pressure response unit M is the main body 1
The upper lid 17 is provided with the diaphragm 16 as a pressure responsive member being held between the lower lid 15 fixed to the No. 4 and the spring box 18 is fixed to the upper lid 17, and the adjusting screw 19 screwed into the spring box 18 is provided. And a deposit 20 on the diaphragm 16
The adjusting spring 22 is provided between the spring receiver 21 and the spring receiver 21 that contacts the.
【０００５】ダイヤフラム１６の他側には連動杆２３の
当金２４が当接している。連動杆２３は弁本体１４の摺
動孔１４ａを貫通して延長しており、該連動杆２３の一
部と当金２４は受圧室Ｒ1 に位置しており、該受圧室Ｒ
1 には吸入圧力Ｐｓを導入する通路ｓ1 に連通する吸入
圧力導入口１４ｂが形成されている。The metal plate 24 of the interlocking rod 23 is in contact with the other side of the diaphragm 16. Associated rod 23 is extended through the sliding hole 14a of the valve body 14, a portion losses 24 of the associated rod 23 is located in the pressure receiving chamber R 1, receiving chamber R
Suction pressure introducing port 14b communicating with the passageway s 1 for introducing the suction pressure Ps is formed on the 1.
【０００６】摺動孔１４ａを通って延長する連動杆２３
は弁口２５′を通って弁室Ｒ2 に達し、その先端に固着
されたボール弁体Ｖが弁座２５を開閉する。そしてボー
ル弁体Ｖに当接するばね受２６と本体１４に螺着された
調整ねじ２７との間には前記調整スプリング２２に対抗
する調整スプリング２８が設けられている。なお、２９
はシールリングである。Interlocking rod 23 extending through the sliding hole 14a
Reaches the valve chamber R 2 through the valve opening 25 ′, and the ball valve body V fixed to the tip thereof opens and closes the valve seat 25. An adjusting spring 28 that opposes the adjusting spring 22 is provided between the spring receiver 26 that contacts the ball valve body V and the adjusting screw 27 that is screwed to the main body 14. 29
Is a seal ring.
【０００７】弁室Ｒ2 の一次側には吐出圧力供給通路ｄ
1 と連通する吐出圧力導入口１４ｃが設けられ、二次側
にはクランクケース１に対する吐出圧力供給通路ｄ2 と
連通する吐出圧力供給口１４ｄが形成される。クランク
ケース１から吸入口Ｓにかけては、固定オリフィスＣを
介してクランクケース圧力Ｐｃの逃し通路ｃが設けられ
ており、該固定オリフィスＣの口径はピストン４のシー
ルリングを吹抜ける吐出圧力Ｐｄの量に見合って設計さ
れる。A discharge pressure supply passage d is provided on the primary side of the valve chamber R 2.
A discharge pressure introduction port 14c communicating with 1 is provided, and a discharge pressure supply port 14d communicating with the discharge pressure supply passage d 2 for the crankcase 1 is formed on the secondary side. From the crankcase 1 to the suction port S, a relief passage c for the crankcase pressure Pc is provided through a fixed orifice C, and the diameter of the fixed orifice C is the amount of the discharge pressure Pd that blows through the seal ring of the piston 4. Designed to suit.
【０００８】上記構成において、吸入圧力Ｐｓは通路ｓ
1 を介して吸入圧力導入口１４ｂから受圧室Ｒ1 に導入
され、ダイヤフラム１６を介して調整スプリング２２と
対抗している。そして、吸入圧力Ｐｓが低くなるとダイ
ヤフラム１６が連動杆２３を図６において押し下げるよ
うに作動し、弁体Ｖが弁座２５を開いて吐出圧力Ｐｄを
クランクケース１内に導入し、クランクケース内の圧力
Ｐｃを高くしてウオブル板を立てることによりピストン
４のストロークを小さくする。In the above structure, the suction pressure Ps is determined by the passage s.
It is introduced into the pressure receiving chamber R 1 from the suction pressure introducing port 14b via 1 and opposes the adjusting spring 22 via the diaphragm 16. When the suction pressure Ps becomes lower, the diaphragm 16 operates so as to push down the interlocking rod 23 in FIG. 6, the valve body V opens the valve seat 25 and introduces the discharge pressure Pd into the crankcase 1, and the inside of the crankcase The stroke of the piston 4 is reduced by raising the pressure Pc and raising the wobble plate.
【０００９】吸入圧力Ｐｓが上昇すると、逆に動作して
クランクケース１内への吐出圧力の供給を遮断する。と
ころで、この容量制御弁の特性は、主に弁の高圧影響と
なり、高吐出圧力時には問題が無いが、低吐出圧力（低
外気温度）時には、図５の実線で示される如くに、吸入
圧力が上昇する傾向となり、蒸発器で充分に水分が取り
にくい為、車内の窓に露が付くという不具合が発生す
る。When the suction pressure Ps rises, the reverse operation is performed to cut off the supply of the discharge pressure into the crankcase 1. By the way, the characteristic of this displacement control valve is mainly affected by the high pressure of the valve, and there is no problem at a high discharge pressure, but at a low discharge pressure (low outside air temperature), the suction pressure is increased as shown by the solid line in FIG. This tends to rise, and it is difficult for the evaporator to take sufficient water, which causes the problem of dew on the windows inside the vehicle.
【００１０】即ち、図６の構造において、制御弁高圧影
響特性は、弁径（有効面積）とダイヤフラム径（有効面
積）によって決定されるものであり、弁の有効面積Ａcm
2 、ダイヤフラムの有効面積Ｆcm2 とした場合におい
て、弁にかかる荷重ＷD とダイヤフラムの下にかかる荷
重ＷF は次式によって示される。That is, in the structure of FIG. 6, the control valve high pressure influence characteristic is determined by the valve diameter (effective area) and the diaphragm diameter (effective area), and the effective area of the valve Acm.
2. When the effective area of the diaphragm is Fcm 2 , the load W D on the valve and the load W F below the diaphragm are shown by the following equations.
【００１１】ＷD ＝（Ｐｄ−Ｐｃ）×Ａcm2 ＷF ＝Ｐｓ×Ｆcm2 従って、Ｐｄ大の場合にはＷD 大であり、低いＰｓで弁
が閉じてバランスするのに対し、Ｐｄ小の場合にはＷD
小なので、Ｐｓを高くしないと弁がバランスしなくな
り、弁の作動特性（Ｐｓ）は図５実線で示される状況と
なる。[0011] W D = (Pd-Pc) Therefore × Acm 2 W F = Ps × Fcm 2, in the case of Pd large is W D large, the valve is closed whereas the balance at a low Ps, Pd small In case of W D
Since it is small, the valve becomes unbalanced unless Ps is increased, and the valve operating characteristic (Ps) is in the situation shown by the solid line in FIG.
【００１２】[0012]
【発明が解決しようとする課題】本発明は上記した点に
着目して為されたものであり、コンプレッサの低吐出圧
力時における吸入圧力の上昇を押さえて前記欠点を解消
するようにしたものである。SUMMARY OF THE INVENTION The present invention has been made by paying attention to the above points, and is intended to eliminate the above-mentioned drawbacks by suppressing an increase in suction pressure at a low discharge pressure of a compressor. is there.
【００１３】[0013]
【課題を解決するための手段】上記の目的を達成するた
め、本発明においては、コンプレッサの吐出側からクラ
ンクケース内に連通する吐出圧力供給通路に介設した主
弁体を該コンプレッサの吸入圧力により制御し、該主弁
体内に形成した均圧連通路内に補正弁体を設け、吐出圧
力とクランクケース内圧力の差圧が設定された補正差圧
以下になると該均圧連通路内の該補正弁体が作動して該
主弁体の高圧影響特性を補正することを特徴とする。In order to achieve the above object, in the present invention, a main valve element provided in a discharge pressure supply passage communicating from the discharge side of the compressor to the inside of the crankcase is provided with a suction pressure of the compressor. The correction valve body is provided in the pressure equalizing communication passage formed in the main valve body, and when the pressure difference between the discharge pressure and the crankcase internal pressure is equal to or less than the set correction differential pressure, the correction valve in the pressure equalizing communication passage is controlled. It is characterized in that the valve element operates to correct the high-pressure influence characteristic of the main valve element.
【００１４】[0014]
【作用】コンプレッサの低吐出圧力（低外気温度）時に
おいて、補正弁体が作動して吸入圧力の上昇を阻止す
る。When the compressor has a low discharge pressure (low outside air temperature), the correction valve element operates to prevent the suction pressure from increasing.
【００１５】[0015]
【実施例】図１は本発明にかかる容量可変コンプレッサ
Ａ′の容量制御弁Ｂ′を示し、従来例と同じ構造部分は
同一符号で示されている。容量制御弁Ｂ′において、弁
本体１４の一側に圧力応動部Ｍが設けられる。圧力応動
部Ｍは、弁本体１４に固着された下蓋１５に対して圧力
応動部材としてのダイヤフラム１６を挾持した状態で上
蓋１７を設けると共に該上蓋１７にばね箱１８を固着
し、ばね箱１８内に螺着した調整ねじ１９とダイヤフラ
ム１６の上当金２０に小ボール３０を介して当接するば
ね受２１との間に調整スプリング２２を設けて構成す
る。なお、３１はストッパーである。1 shows a displacement control valve B'of a variable displacement compressor A'according to the present invention, and the same structural parts as those of the conventional example are designated by the same reference numerals. In the capacity control valve B ′, a pressure responsive portion M is provided on one side of the valve body 14. The pressure responsive portion M is provided with an upper lid 17 with a diaphragm 16 serving as a pressure responsive member being held between a lower lid 15 fixed to the valve body 14 and a spring box 18 fixed to the upper lid 17, An adjusting spring 22 is provided between an adjusting screw 19 which is screwed inside and a spring receiver 21 which abuts against an upper metal plate 20 of the diaphragm 16 via a small ball 30. In addition, 31 is a stopper.
【００１６】ダイヤフラム１６の他側には連動杆２３の
当金２４が当接している。連動杆２３は本体１４の摺動
孔１４ａを貫通して延長しており、該連動杆２３の一部
と当金２４は受圧室Ｒ1 に位置して当金２４と本体１４
間に中間スプリング３２を設け、該受圧室Ｒ1 には吸入
圧力Ｐｓを導入する通路に連通する吸入圧力導入口１４
ｂを形成する。The metal plate 24 of the interlocking rod 23 is in contact with the other side of the diaphragm 16. The interlocking rod 23 extends through the sliding hole 14a of the main body 14, and a part of the interlocking rod 23 and the metal plate 24 are located in the pressure receiving chamber R 1 and the metal plate 24 and the metal plate 14 are located.
An intermediate spring 32 is provided between the suction pressure introducing port 14 and the pressure receiving chamber R 1 which communicates with a passage for introducing the suction pressure Ps.
b is formed.
【００１７】摺動孔１４ａを通って延長する連動杆２３
は弁口２５′を通って弁室Ｒ2 に達し、その先端に挿入
されたニードル状主弁体Ｖ1 が弁座２５に接離する。そ
して、主弁体Ｖ1 と弁本体１４に固定されたばね受３３
との間には前記調整スプリング２２に対抗するスプリン
グ２８が設けられている。Interlocking rod 23 extending through the sliding hole 14a
Reaches the valve chamber R 2 through the valve opening 25 ′, and the needle-shaped main valve body V 1 inserted at the tip thereof comes into contact with and separates from the valve seat 25. Then, the spring receiver 33 fixed to the main valve body V 1 and the valve body 14
A spring 28, which opposes the adjusting spring 22, is provided between and.
【００１８】弁室Ｒ2 の一次側には吐出圧力供給通路ｄ
1 と連通する吐出圧力導入口１４ｃが設けられ、二次側
には弁口２５′を介してクランクケース１に対する吐出
圧力供給通路ｄ2 と連通する吐出圧力供給口１４ｄが形
成される。ニードル状主弁体Ｖ1 の内部にはバイパス連
通路３４が貫通して形成されていて常時吐出圧力供給口
１４ｄ側と連通し、該均圧連通路３４の前記吐出圧力導
入口１４ｃ側には筒状部３４′内において圧力室Ｒ3 が
形成され、圧力室Ｒ3 内には高圧用の補正弁体Ｖ2 が摺
動自在に設けられると共に主弁体Ｖ1 との間に設けた補
正スプリング３５により常時開弁方向に付勢され、前記
ばね受３３に該補正弁体Ｖ2 に対する止め輪３６を設け
る。補正弁体Ｖ2 の外端部の外周部において環状凹溝３
７を形成し、該環状凹溝３７を形成する外側のフランジ
状弁部３８が閉弁時において主弁体Ｖ1 の筒状部３４′
の端部における弁座３９と当接する（図３参照）。The discharge pressure supply passage d is provided on the primary side of the valve chamber R 2.
1 and the discharge pressure introducing port 14c communicating is provided on the secondary side discharge pressure supply port 14d communicating with the discharge pressure supply passage d 2 relative to the crank case 1 through the valve port 25 'is formed. A bypass communication passage 34 is formed through the inside of the needle-shaped main valve body V 1 so as to communicate with the discharge pressure supply port 14d side at all times, and a cylinder is provided on the discharge pressure introduction port 14c side of the pressure equalization communication passage 34. A pressure chamber R 3 is formed in the cylindrical portion 34 ′, a high-pressure correction valve body V 2 is slidably provided in the pressure chamber R 3 , and a correction spring is provided between the pressure chamber R 3 and the main valve body V 1. The spring receiver 33 is constantly urged in the valve opening direction by the valve 35 and is provided with a retaining ring 36 for the correction valve body V 2 . The annular groove 3 is formed in the outer peripheral portion of the outer end portion of the correction valve body V 2.
7 is formed, the tubular portion 34 of the main valve body V 1 flanged valve portion 38 of the outer at the time of closing to form the annular groove 37 '
Abutting against the valve seat 39 at the end of the (see FIG. 3).
【００１９】上記構成において、主弁体径：φＤ（有効
面積＝Ａcm2 ）として、Ｐｓ圧力が容量制御弁Ｂ′の設
定圧力以下になると主弁体Ｖ1 が開いてＰｄ圧力がクラ
ンクケース１内に入り、Ｐｓ圧力よりＰｃ圧力が高くな
るのでアンロード運転となる。逆にＰｓ圧力が容量制御
弁Ｂ′の設定圧力以上になると主弁体Ｖ1 が閉じ、Ｐｃ
圧力はＰｓ圧力と同じ圧力になるのでフルロード運転と
なる。In the above structure, when the main valve body diameter is φD (effective area = Acm 2 ), when the Ps pressure becomes equal to or lower than the set pressure of the displacement control valve B ′, the main valve body V 1 opens and the Pd pressure changes to the crankcase 1. Entering inside, the Pc pressure becomes higher than the Ps pressure, so the unloading operation is performed. Conversely when the Ps pressure is above the set pressure of the displacement control valve B 'it closes the main valve body V 1, Pc
Since the pressure is the same as the Ps pressure, full load operation is performed.
【００２０】高圧補正部において、補正弁体径：φＤm
（有効面積＝Ａm cm2 ）補正バネ力Ｗ、補正差圧＝ΔＰ
ｈとすると、補正バネ力Ｗは、次の式を満足する様に設
計する。 Ｗ＝Ａm ×ΔＰｈ この場合において、差圧（Ｐｄ−Ｐｃ圧力）が補正差圧
（ΔＰｈ）以上の場合には、補正弁体Ｖ2 は閉じており
（図１参照）、Ｐｓ圧力は、図５のグラフのＡ−Ｂ間の
主弁体径有効面積（Ａcm2 ）による高圧影響特性を得
る。In the high pressure correction unit, the correction valve body diameter: φDm
(Effective area = Am cm 2 ) Correcting spring force W, Correcting differential pressure = ΔP
When h, the correction spring force W is designed so as to satisfy the following equation. W = Am × ΔPh In this case, when the pressure difference (Pd−Pc pressure) is equal to or higher than the correction pressure difference (ΔPh), the correction valve body V 2 is closed (see FIG. 1), and the Ps pressure is The high pressure influence characteristic by the main valve body diameter effective area (Acm 2 ) between A and B in the graph of 5 is obtained.
【００２１】Ｐｄ圧力を降下させ、差圧（Ｐｄ−Ｐｃ圧
力）が補正差圧（ΔＰｈ）より小さくなると、補正弁体
Ｖ2 が補正スプリング３５の力により作動して補正弁体
Ｖ2が止め輪３６に当接する事により、補正スプリング
力及び補正弁の高圧影響が主弁体Ｖ1 に加わり、主弁体
Ｖ1 の特性に補正動作を行い（図４参照）、図５のグラ
フにおけるＢ−Ｃ間のフラットな特性を得る。When the Pd pressure is lowered and the differential pressure (Pd-Pc pressure) becomes smaller than the correction differential pressure (ΔPh), the correction valve body V 2 is actuated by the force of the correction spring 35 and the correction valve body V 2 is stopped. by abutting the wheel 36, joined the high-pressure effect of the correction spring force and the correction valve in the main valve body V 1, to perform correction operation characteristic of the main valve body V 1 (see FIG. 4), B in the graph of FIG. 5 Obtain flat characteristics between −C.
【００２２】補正スプリング力、補正弁体径を変える事
により任意のＰｓ圧力特性が得られる。但し、主弁体径
有効面積（Ａcm2 ）による高圧影響特性より大きくする
事は出来ない。Arbitrary Ps pressure characteristics can be obtained by changing the correction spring force and the correction valve body diameter. However, it cannot be made larger than the high-pressure influence characteristics due to the effective area of the main valve body diameter (Acm 2 ).
【００２３】[0023]
【発明の効果】本発明は上記した如くに、コンプレッサ
の吐出側からクランクケース内に連通する吐出圧力供給
通路に介設した主弁体を該コンプレッサの吸入圧力によ
り制御し、該主弁体内に形成した均圧連通路内に補正弁
体を設け、吐出圧力とクランクケース内圧力の差圧が設
定された補正差圧以下になると該均圧連通路内の該補正
弁体が作動して該主弁体の高圧影響特性を補正するもの
であるから、コンプレッサの低吐出圧力時における吸入
圧力の上昇を阻止し、蒸発器が充分に機能しないことに
よる窓における結露等の不都合を効果的に解消すること
が出来る。As described above, according to the present invention, the main valve body provided in the discharge pressure supply passage communicating from the discharge side of the compressor into the crankcase is controlled by the suction pressure of the compressor, and A correction valve element is provided in the formed pressure equalizing communication passage, and when the pressure difference between the discharge pressure and the crankcase internal pressure becomes less than or equal to the set correction pressure difference, the correction valve element in the pressure equalizing communication passage operates and the main valve Since it corrects the high-pressure influence characteristics of the body, it prevents the rise of suction pressure at low discharge pressure of the compressor and effectively eliminates the inconvenience such as dew condensation in the window due to the evaporator not functioning sufficiently. Can be done.
【図１】本発明一実施例についての説明図である。FIG. 1 is an explanatory diagram of an embodiment of the present invention.
【図２】容量制御弁の断面図である。FIG. 2 is a sectional view of a capacity control valve.
【図３】同上の要部の拡大断面図である。FIG. 3 is an enlarged cross-sectional view of a main part of the above.
【図４】図３の作動状態の断面図である。FIG. 4 is a sectional view of the operating state of FIG.
【図５】主弁高圧影響特性を示すグラフである。FIG. 5 is a graph showing a main valve high pressure influence characteristic.
【図６】従来例の説明図である。FIG. 6 is an explanatory diagram of a conventional example.
Ａ′ コンプレッサ Ｂ′ 容量制御弁 Ｐｄ コンプレッサの吐出圧力 Ｐｓ コンプレッサの吸入圧力 Ｐｃ コンプレッサのクランクケース内圧力 ｄ1 ，ｄ2 吐出圧力供給通路 Ｒ1 受圧室 Ｒ2 弁室 Ｒ3 圧力室 Ｖ1 主弁体 Ｖ2 補正弁体 １４ 弁本体 １４ｃ 吐出圧力導入口 １４ｄ 吐出圧力供給口 １６ 圧力応動部材 ２２ 調整スプリング ２３ 連動杆 ２５′ 弁口 ２８ スプリング ３４ 均圧連通路 ３５ 補正スプリングA'Compressor B'Volume control valve Pd Compressor discharge pressure Ps Compressor suction pressure Pc Compressor crankcase pressure d 1 , d 2 Discharge pressure supply passage R 1 Pressure receiving chamber R 2 Valve chamber R 3 Pressure chamber V 1 Main valve Body V 2 Compensation valve body 14 Valve body 14c Discharge pressure introduction port 14d Discharge pressure supply port 16 Pressure response member 22 Adjusting spring 23 Interlocking rod 25 'Valve port 28 Spring 34 Pressure equalizing communication passage 35 Correction spring
───────────────────────────────────────────────────── フロントページの続き (72)発明者 金子 守男 埼玉県狭山市笹井535 株式会社鷺宮製作 所狭山事業所内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Morio Kaneko 535 Sasai, Sayama City, Saitama Prefecture Saginomiya Works Sayama Plant
Claims (2)
ス内に連通する吐出圧力供給通路に介設した主弁体を該
コンプレッサの吸入圧力により制御し、該主弁体内に形
成した均圧連通路内に補正弁体を設け、吐出圧力とクラ
ンクケース内圧力の差圧が設定された補正差圧以下にな
ると該均圧連通路内の該補正弁体が作動して該主弁体の
高圧影響特性を補正することを特徴とする容量可変コン
プレッサ用容量制御弁。1. A main valve body provided in a discharge pressure supply passage communicating from a discharge side of a compressor into a crankcase is controlled by a suction pressure of the compressor, and is corrected in a pressure equalizing communication passage formed in the main valve body. A valve element is provided, and when the differential pressure between the discharge pressure and the crankcase internal pressure becomes less than or equal to the set correction differential pressure, the correction valve element in the pressure equalizing communication passage operates to correct the high pressure influence characteristic of the main valve element. This is a capacity control valve for variable capacity compressors.
の吸入圧力を圧力応動部材を介して調整スプリングと対
抗させ、コンプレッサの吐出圧力供給通路における吐出
圧力導入口、弁室，弁口及び吐出圧力供給口を順次に該
弁本体に形成し、該弁室内に該弁口を開閉する主弁体を
設け、主弁体と該圧力応動部材間に該弁口を通って連動
杆を設けると共に該主弁体に対して該調整スプリングに
対抗するスプリングを設け、該主弁体内を貫通して形成
した均圧連通路の圧力室において補正弁体を摺動自在に
設け、該補正弁体は補正スプリングにより該吐出圧力導
入口に向けた開弁方向に常時付勢されて成ることを特徴
とする請求項１に記載の容量可変コンプレッサ用容量制
御弁。2. The suction pressure of the compressor introduced into the pressure receiving chamber of the valve body is opposed to the adjusting spring through the pressure responsive member, and the discharge pressure introducing port, the valve chamber, the valve opening and the discharge pressure in the discharge pressure supply passage of the compressor. Supply ports are sequentially formed in the valve body, a main valve body for opening and closing the valve port is provided in the valve chamber, and an interlocking rod is provided between the main valve body and the pressure responsive member through the valve port. A spring that opposes the adjusting spring is provided for the main valve body, and a correction valve body is slidably provided in a pressure chamber of a pressure equalizing communication passage formed through the main valve body. 2. The displacement control valve for a variable displacement compressor according to claim 1, wherein the displacement control valve is constantly urged in a valve opening direction toward the discharge pressure introducing port.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07045394A JP3383403B2 (en) | 1994-04-08 | 1994-04-08 | Displacement control valve for variable displacement compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07045394A JP3383403B2 (en) | 1994-04-08 | 1994-04-08 | Displacement control valve for variable displacement compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07279843A true JPH07279843A (en) | 1995-10-27 |
| JP3383403B2 JP3383403B2 (en) | 2003-03-04 |
Family
ID=13431950
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP07045394A Expired - Fee Related JP3383403B2 (en) | 1994-04-08 | 1994-04-08 | Displacement control valve for variable displacement compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3383403B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006152934A (en) * | 2004-11-30 | 2006-06-15 | Fuji Koki Corp | Pressure regulating valve |
| JP2008286204A (en) * | 2008-07-14 | 2008-11-27 | Tgk Co Ltd | Pressure control valve |
| CN109915341A (en) * | 2017-12-12 | 2019-06-21 | 朱君忠 | Compressor controller |
-
1994
- 1994-04-08 JP JP07045394A patent/JP3383403B2/en not_active Expired - Fee Related
Cited By (4)
| 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 |
| JP2008286204A (en) * | 2008-07-14 | 2008-11-27 | Tgk Co Ltd | Pressure control valve |
| CN109915341A (en) * | 2017-12-12 | 2019-06-21 | 朱君忠 | Compressor controller |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3383403B2 (en) | 2003-03-04 |
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