JPS61236981A - Four-way reversing valve for reversible refrigerating cycle - Google Patents
Four-way reversing valve for reversible refrigerating cycleInfo
- Publication number
- JPS61236981A JPS61236981A JP60076629A JP7662985A JPS61236981A JP S61236981 A JPS61236981 A JP S61236981A JP 60076629 A JP60076629 A JP 60076629A JP 7662985 A JP7662985 A JP 7662985A JP S61236981 A JPS61236981 A JP S61236981A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- valve
- chamber
- piston
- 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.)
- Granted
Links
Landscapes
- Fluid-Driven Valves (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の目的〕
嵐呈上■皿度光！
本発明は冷暖房兼用型空調機において、冷暖房の切°り
換え操作に用いられる四方逆転弁に関するものである。[Detailed Description of the Invention] [Object of the Invention] Arashi Presentation ■Saradoko! The present invention relates to a four-way reversing valve used for switching between cooling and heating in a dual-purpose air conditioner.
Ｕ回特 ゛
従□来における差圧駆動型の四方逆転弁は、シリンダ状
逆転弁本体内を一対のピストン等により高圧□室と低圧
室と圧力変換室、又は高圧室と２個の圧力変換室め３室
に区分するのがほとんどであり、該圧力変換□室をパイ
ロット三方電磁弁等により切り換え・てピストン乃至は
該ピストンに連結された流路切換量の弁体を移動させる
構成であった。Part U: Conventional differential pressure-driven four-way reversing valves use a pair of pistons, etc. within the cylindrical reversing valve body to convert between a high pressure chamber, a low pressure chamber, and a pressure conversion chamber, or between a high pressure chamber and two pressure conversion chambers. In most cases, the pressure converting chamber is divided into three chambers, and the pressure converting chamber is switched by a pilot three-way solenoid valve, etc., and a piston or a valve body connected to the piston is moved. Ta.
°シようとする四 占
上記従来技術では、逆転四方弁もパイロ−／ ）電磁弁
も構造が複雑であると共に相互の連通用導管の数も多く
て小型化の隘路となっており、また該パイロット電磁弁
の操作による制御は該圧力変換室に対する偵極的な減圧
と積極的な加”圧によるので、微細な電子制御に適して
いない等の欠点があった。In the above-mentioned conventional technology, both the reversing four-way valve and the pyro-magnetic valve have complex structures and a large number of mutually communicating conduits, which is an obstacle to miniaturization. Control by operating a pilot electromagnetic valve involves scouting for pressure reduction and active pressurization of the pressure conversion chamber, which has disadvantages such as being unsuitable for fine electronic control.
本発明は上記した点に着目゛し、逆転弁本体内をピスト
ンにより高圧室と圧力変換室の二車に区分すると共に該
圧力変換室を開閉弁により開閉して差圧又はばねにより
該ピストン乃至は流路切換弁を移動させる構成を採用し
、もって構造の簡略化と小型化を達成し、該開閉弁によ
る該圧力変換★の制御を該圧力変換室から圧縮機の吸入
側に対する一定方向の冷媒流に対する開閉操作とするこ
ぶにより電子方式による微細な制御を可能とし、更には
ばねによるピストン乃至は流路切換弁の移動による暖房
運転から冷房運転への切り換えを迅速化したものである
。The present invention focuses on the above-mentioned points, and divides the inside of the reversing valve body into two parts, a high pressure chamber and a pressure conversion chamber, by a piston, and opens and closes the pressure conversion chamber by an on-off valve, and uses differential pressure or a spring to separate the piston or the pressure conversion chamber. adopts a configuration in which the flow path switching valve is moved, thereby achieving a simpler and more compact structure, and controlling the pressure conversion★ by the on-off valve from the pressure conversion chamber to the suction side of the compressor. The knobs that open and close the refrigerant flow enable fine control by electronic system, and furthermore, the switching from heating operation to cooling operation can be speeded up by moving the piston or flow path switching valve using a spring.
。 占を °するための
上記目的を達成するため、本発明においては、シリンダ
状の逆転弁本体内をピストンにより高圧室と圧力変換室
に区画し、高圧室に圧縮機の吐出管に対する接続口と、
圧縮機の吸入管に対する接続口及び該接続口を挾んで２
個の熱交換器用導管に対する接続口とを設け、吸入管に
対する接続口から２個の熱交換器用導管に対する接続口
にかけて一連の切換用弁シートを設け、該切換用弁シー
トに摺接するスライドバルブを該ピストンに連結し、該
ピストンに高圧室と圧力変換室を連通させ□る均圧孔を
形成する履共に該均圧孔に暖房運転時に烏いて高圧室か
４圧力変換室への流れを遮断する弁体を設け、該ピスト
ンを高圧室方向に常時付勢するばねと暖房運転時におい
てのみ該ピストンを高圧室方向に付勢する補助ばねを設
け、圧力変換室に圧縮機の吸入側に連通ずる圧力逃し孔
を設けると共に該圧力逃し孔に開閉弁を設け、該圧力逃
し孔の径を該均圧孔の径より大きく形成して成る構成を
採用した。. In order to achieve the above-mentioned object of controlling the air pressure, the present invention divides the inside of the cylindrical reversing valve body into a high pressure chamber and a pressure conversion chamber by means of a piston, and the high pressure chamber is provided with a connection port for the discharge pipe of the compressor and a pressure conversion chamber. ,
Connecting port to the suction pipe of the compressor and holding the connecting port 2
A series of switching valve seats are provided from the connection ports for the suction pipes to the connection ports for the two heat exchanger pipes, and a slide valve is provided in sliding contact with the switching valve seats. A pressure equalizing hole is connected to the piston and communicates between the high pressure chamber and the pressure conversion chamber in the piston. At the same time, a pressure equalizing hole is formed in the pressure equalizing hole during heating operation to block the flow to the high pressure chamber or the pressure conversion chamber. A spring that always biases the piston toward the high pressure chamber and an auxiliary spring that biases the piston toward the high pressure chamber only during heating operation are provided, and the pressure conversion chamber is connected to the suction side of the compressor. A configuration was adopted in which a communicating pressure relief hole was provided, an on-off valve was provided in the pressure relief hole, and the diameter of the pressure relief hole was made larger than the diameter of the pressure equalization hole.
夾施■
以下本発明の一実施例について図面と共に説明する。図
面において、１はシリンダ状の逆転弁本体であり、両端
部に栓体２，３が溶接・して固着されている。栓体２に
は圧縮機４の吐出管５が連結され、逆転弁本体１には軸
方向におし）で圧縮機４の吸入管６を挾んで２本の導管
７，１１４連結される。導管７，８は凝縮器又は蒸発器
として逆転的に使用される２個の熱交換器９，１０に連
結される。吸入管６と導管７，８の内端は逆転弁本体１
内に固着される切換用の弁シート１１の３個の通孔１１
ａｓｌｌｂｔｌｌｃに接続され、弁シート１１の内側に
は一連の平滑面ｌｉｄが形成される。Embodiment 1 An embodiment of the present invention will be described below with reference to the drawings. In the drawings, reference numeral 1 denotes a cylindrical reversing valve body, and plugs 2 and 3 are welded and fixed to both ends. A discharge pipe 5 of the compressor 4 is connected to the plug body 2, and two conduits 7, 114 are connected to the reversing valve body 1 with the suction pipe 6 of the compressor 4 sandwiched between them in the axial direction. The conduits 7, 8 are connected to two heat exchangers 9, 10 which are used reciprocally as condensers or evaporators. The inner ends of the suction pipe 6 and conduits 7 and 8 are connected to the reversing valve body 1.
Three through holes 11 of the switching valve seat 11 fixed inside.
asllbtllc, and a series of smooth surfaces lid are formed inside the valve seat 11.
逆転弁本体１内において、弁シート１１と栓体３間にお
いてピストン１２枠（摺動自在に設けられ、逆転弁本体
１内を高圧室Ｒ１と圧力変換室Ｒ２に区画する。ピスト
ン１２と栓体３間には圧縮ばね１３が設けられ、ピスト
ン１２は高圧室Ｒ，力方向常時付勢されている。ピスト
ン１２には高圧室Ｒ４と圧力変換室Ｒ２を常、時連通さ
せる均圧孔１２ａが形成され、栓体３には該均圧孔１２
ａよりも径の大きい圧力逃し孔３ａが形成されると共に
該圧力逃し孔、３ ａには吸入管６に至る導管１４が連
結される。均圧孔１２ａの圧力変換室側の端部に弁シー
）１２ｂと弁室１２ｃが設けられ、弁室１２ｃ内におい
てボール状の弁体１２ｄがシけら 、れる・ ・
弁室１２ｃの外壁１２ｅにはリング状の衝合子１２ｆが
摺動自在に構台され、該衝合４子１２ｆは−同じく外Ｈ
ｊｌ１２ｅに捲装された復帰用補助圧縮ばね１２ｇによ
り栓体３方向に突出するように付勢されるもので、該衝
合子１２． ｆの開口１２ｆ、によりボール状の弁体１
２ｄが一部突出した状態で支持されている。Inside the reversing valve body 1, a piston 12 frame (slidably provided between the valve seat 11 and the plug body 3 divides the inside of the reversing valve body 1 into a high pressure chamber R1 and a pressure conversion chamber R2. The piston 12 and the plug body A compression spring 13 is provided between the piston 12 and the high pressure chamber R, and the piston 12 is always biased in the force direction. The pressure equalizing hole 12 is formed in the plug body 3.
A pressure relief hole 3a having a larger diameter than the pressure relief hole 3a is formed, and a conduit 14 leading to the suction pipe 6 is connected to the pressure relief hole 3a. A valve seat 12b and a valve chamber 12c are provided at the end of the pressure conversion chamber side of the pressure equalization hole 12a, and a ball-shaped valve body 12d is disposed within the valve chamber 12c. A ring-shaped abutment 12f is slidably mounted on a pedestal, and the four abutments 12f are also located outside H.
jl12e is biased to protrude in the direction of the stopper 3 by a return auxiliary compression spring 12g wound around the abutment 12. The ball-shaped valve body 1 is opened by the opening 12f of f.
2d is supported in a partially protruding state.
栓体３にプライン４．ヤ管１５を介して電磁開閉弁１６
が５付設され、そのプランジャ１７の先端に設し才たボ
ール弁１８が圧力逃し孔３ａの途中に設けた弁シー）３
ｂに接離して該圧力逃し孔３ａを開閉する。即〉、圧力
逃し孔３ａは栓体３の外周部分、において圧力変換室Ｒ
２から弁室３Ｃに達する通孔３ ａ４ と、弁室３Ｃか
ら栓体３の中心部分を通る通孔３ａｚからの放射方向の
通孔３ａ、から成り、該通孔３ａ、の弁室３ｃ側端部に
弁シート３ｂが設けられ、通孔３ａ、に前記導管１４が
接続される。プランジャ１７と吸引鉄心１９間には圧縮
ばね２０が設けられてボール弁１８は弁シー）３ｂに当
接する方向に付勢される。Pline 4 on the plug body 3. Electromagnetic on-off valve 16 via Yapipe 15
5 is attached, and a ball valve 18 provided at the tip of the plunger 17 is provided in the middle of the pressure relief hole 3a) 3
b to open and close the pressure relief hole 3a. Immediately, the pressure relief hole 3a is connected to the pressure conversion chamber R at the outer peripheral portion of the plug body 3.
The valve chamber 3c side of the through hole 3a is composed of a through hole 3a4 reaching the valve chamber 3C from the valve chamber 3C, and a radial through hole 3a from the through hole 3az passing through the center part of the plug body 3 from the valve chamber 3C. A valve seat 3b is provided at the end, and the conduit 14 is connected to the through hole 3a. A compression spring 20 is provided between the plunger 17 and the suction core 19, and the ball valve 18 is biased in the direction of contacting the valve seat 3b.
弁シート１１上には連通用内腔２１ａを有するスライド
バルブ２１が設けられ、該スライドバルブ２１は連結杆
２２によりピストン１２に連結される。スライドバルブ
２１は移動によりその内腔２１ａを介して弁シート１１
における吸入管６に対する通孔１１ａをその両側の熱交
換器用導管７．８に対する通孔１１ｂｓｌｌｃに対して
択一的に連通させる。A slide valve 21 having a communication bore 21a is provided on the valve seat 11, and the slide valve 21 is connected to the piston 12 by a connecting rod 22. The slide valve 21 moves to the valve seat 11 through its inner cavity 21a.
The through hole 11a for the suction pipe 6 is alternatively communicated with the through hole 11bsllc for the heat exchanger conduit 7.8 on both sides thereof.
上記構成において、第１図は冷房運転状態を示す、即ち
、電磁開閉弁１６は無通電状態にあってプランジ中１７
がばね２０により押されてボール弁１８が圧力逃し孔３
ａを閉じるので、均圧孔１２ａにより高圧室Ｒ，と圧力
変換室Ｒ３は同圧力となり、従ってピストン１２はばね
１３により弁シ”−）１１に当接する迄押し動かされ、
スライドバルブ２１は通孔１１ａを通孔１１ｃに対して
連通させるので、冷媒は圧縮機４−吐出管５−ａｌｔ管
７−室外熱交換器９−絞り手段２３−室内熱交換器１０
−導管８→吸入管６−圧縮機４の経路で循環する。In the above configuration, FIG. 1 shows the cooling operation state, that is, the electromagnetic on-off valve 16 is in a non-energized state and the plunger 17 is in a plunging state.
is pushed by the spring 20 and the ball valve 18 closes to the pressure relief hole 3.
a is closed, the high pressure chamber R and the pressure conversion chamber R3 have the same pressure due to the pressure equalization hole 12a, and therefore the piston 12 is pushed by the spring 13 until it comes into contact with the valve seat 11.
Since the slide valve 21 allows the through hole 11a to communicate with the through hole 11c, the refrigerant flows through the compressor 4 - the discharge pipe 5 - the alt pipe 7 - the outdoor heat exchanger 9 - the throttle means 23 - the indoor heat exchanger 10
It circulates along the route of - conduit 8 -> suction pipe 6 - compressor 4.
次に電磁開閉弁１６に通電すると共に圧縮機４を起動す
ると、プランジャ１７が吸引されてニードル弁体１８が
圧力逃し孔３ａを開き、圧力変換室Ｒ２内を圧縮機４の
吸入側の低圧に連通させる。Next, when the electromagnetic on-off valve 16 is energized and the compressor 4 is started, the plunger 17 is attracted, the needle valve body 18 opens the pressure relief hole 3a, and the inside of the pressure conversion chamber R2 is changed to the low pressure on the suction side of the compressor 4. communicate.
これにより、圧力変換室Ｒ２においては冷媒が圧力逃し
孔３ａより吸入側へ逃げると同時に高圧室Ｒ＋より均圧
孔１２ａを介して冷媒が供給され、この際において圧力
逃し孔３ａの径が均圧孔１２ａの径よりも大であって冷
媒の供給量よりも排出量が大きいので圧力変換室Ｒ２は
低圧となり、室Ｒ１，Ｒ１間には圧縮ばね１３の弾力に
打ち勝つ差圧が発生し、第２図に示される如くにピスト
ン１２乃至スライドバルブ２１は栓体３方向に移動を開
始する。As a result, in the pressure conversion chamber R2, the refrigerant escapes from the pressure relief hole 3a to the suction side, and at the same time, the refrigerant is supplied from the high pressure chamber R+ through the pressure equalization hole 12a, and at this time, the diameter of the pressure relief hole 3a becomes equal to the pressure. Since the diameter of the hole 12a is larger and the amount of refrigerant discharged is larger than the amount of refrigerant supplied, the pressure conversion chamber R2 becomes low pressure, and a pressure difference that overcomes the elasticity of the compression spring 13 is generated between the chambers R1 and R1. As shown in FIG. 2, the piston 12 to the slide valve 21 start moving in the direction of the stopper 3.
上記移動により、ピストン１２が栓体３に接近すると、
弁体１２ｄ乃至衝合子１２ｆが栓体３に当接し、復帰用
補助ばね１２ｇを圧縮すると共に′弁体１２ｄが弁シー
ト１２ｂに当接して均圧孔１２ａを閉止した状態で停止
す！、この状態に蓄いて、スライドバルブ２１は通孔１
１ａを通孔１１ｂに対して連通させるので、冷媒は圧縮
機４−４出管５−導管８−室外熱交換器１〇二絞り手段
２ ：４−の経路で循環して暖房運転となる。When the piston 12 approaches the stopper 3 due to the above movement,
The valve body 12d to the abutment 12f come into contact with the stopper 3, compressing the return auxiliary spring 12g, and stop with the valve body 12d coming into contact with the valve seat 12b and closing the pressure equalizing hole 12a! , in this state, the slide valve 21 opens through hole 1.
Since the through hole 1a is communicated with the through hole 11b, the refrigerant is circulated through the route of the compressor 4, the outlet pipe 5, the conduit 8, the outdoor heat exchanger 10, the throttle means 2, and 4, resulting in heating operation.
暖房運転時において、サーモスタットにより圧縮機４が
停止すると、高圧−と低圧側は徐＝にバランスして行き
、最高作動圧力差になるとピストンは１縮ばね１３と補
助圧縮ばね１２ｇの弾撥力により比較的迅速に移動を開
始する。During heating operation, when the compressor 4 is stopped by the thermostat, the high pressure and low pressure sides gradually become balanced, and when the maximum operating pressure difference is reached, the piston is moved by the elastic force of the first compression spring 13 and the auxiliary compression spring 12g. Start moving relatively quickly.
このように暖房運転時において、冷房状態に迅速に切り
換えた後、除霜開始信号により除霜運転を行なう。In this way, during the heating operation, after quickly switching to the cooling state, the defrosting operation is performed in response to the defrosting start signal.
第４図の実施例においては、栓体３においてピストン１
２の均圧孔１２ａに対向するニードル状の弁体１２ｄ′
が設けられ、前記したと同様にピストン１２が栓体３に
接近した際において、該ニードル状の弁体１２ｄ′が弁
シート１２ｂに当接して閉止する。また０、前記衝合子
１２ｆに代えて栓体３に対し補助ばね１２ｇを圧縮する
突子１２ｆ′が設けられている。In the embodiment shown in FIG. 4, the piston 1 is
A needle-shaped valve body 12d' facing the pressure equalizing hole 12a of No. 2
is provided, and when the piston 12 approaches the stopper 3, the needle-shaped valve element 12d' comes into contact with the valve seat 12b and closes. Further, in place of the abutment 12f, a protrusion 12f' that compresses the auxiliary spring 12g against the plug body 3 is provided.
本発明は上記した如くに、シリンダ状の逆転弁本尿内を
ピストンにより高圧室と圧力変換室に区画し、・高圧室
に圧縮機の吐出管に対する接続口と、圧縮機の吸入管に
対す゛る接続口及び該接続口を挾んで２゛□個の一熱交
換器用導管に対する接続口とを設け、吸入管に対する接
続口から２個の熱交換器用導管に対する接続口にかけて
一連の切換用弁シートを設け、該切換用弁シートに摺接
するスライドバルブを該ピストンに連結し、該ピストン
に高圧室と圧力変換室を連通させる均圧孔を形成すると
共に該均圧孔に暖房運転時において高圧室から圧力変換
室への流れを遮断する弁体を設け、該ピストンを高圧室
方向に常時付勢するばねと暖房運転時においてのみ該ピ
ストンを高圧室方向に付勢する補助ばねを設け、圧力変
換室に圧縮機の吸入側に連通ずる圧力逃し孔を設けると
共に該圧力逃し孔に開閉弁を設け、該圧力逃し孔の径を
該均圧孔の径より大きく形成して成るものであるから、
構造を大巾に簡略化して作動を安定させると共に小型化
を達成でき、また電子方式により微細な制御を行なうこ
とができる。As described above, the present invention divides the interior of a cylindrical reversing valve into a high pressure chamber and a pressure conversion chamber by means of a piston, and the high pressure chamber has a connection port for the discharge pipe of the compressor and a connection port for the suction pipe of the compressor. A series of switching valve seats are provided from the connection port for the suction pipe to the connection ports for the two heat exchanger conduits. A slide valve that is in sliding contact with the switching valve seat is connected to the piston, and a pressure equalization hole is formed in the piston to communicate the high pressure chamber and the pressure conversion chamber. A valve body is provided to shut off the flow from the air to the pressure conversion chamber, and a spring that constantly biases the piston toward the high pressure chamber and an auxiliary spring that biases the piston toward the high pressure chamber only during heating operation are provided. A pressure relief hole communicating with the suction side of the compressor is provided in the chamber, an on-off valve is provided in the pressure relief hole, and the diameter of the pressure relief hole is formed to be larger than the diameter of the pressure equalization hole.
The structure can be greatly simplified, operation can be stabilized, miniaturization can be achieved, and fine control can be performed by electronic means.
特に本発明においては、暖房運転時においてのみ作動す
る復帰用補助ばねを設けているので、暖房運転から冷房
運転への切り換えを迅速化し得ると共に冷房運転から暖
房運転への切り換えも迅速化し得ることができ、冷房運
転から暖房運転へ移行した際において直ちに弁体により
均圧孔を閉止するので、冷媒の漏れを最小限に止めるこ
とができる。In particular, in the present invention, since an auxiliary return spring is provided that operates only during heating operation, it is possible to speed up the switching from heating operation to cooling operation, and also to speed up the switching from cooling operation to heating operation. Since the pressure equalizing hole is immediately closed by the valve body when the cooling operation shifts to the heating operation, leakage of refrigerant can be minimized.
第１図は本発明の一実施例について冷房運転状態を示す
断面図、第２図は同上の冷房運転から暖房運転への移行
途中における作動状態図、第３図は同上における暖房運
転状態を示す断面図、第４図は弁体の他の実施例の詳細
図である。
１・・・逆転弁本体、Ｒ＋・・・高圧室、Ｒ２・・・圧
力変換室、４・・・圧縮機、５・・・吐出管、６・・・
吸入管、９．１０・・・熱交換器、１１・・・切換用の
弁シート、１２・・・ピストン、１２ ａ−・・均圧孔
、３ａ・・・圧力逃し孔、１２ｄ・・・弁体、１２ｇ・
・・補助ばね、１３・・・圧縮ばね、１８・”開閉弁。Fig. 1 is a sectional view showing the cooling operation state of an embodiment of the present invention, Fig. 2 is an operation state diagram during the transition from cooling operation to heating operation in the same example, and Fig. 3 shows the heating operation state in the same example. The sectional view, FIG. 4, is a detailed view of another embodiment of the valve body. 1...Reversing valve body, R+...High pressure chamber, R2...Pressure conversion chamber, 4...Compressor, 5...Discharge pipe, 6...
Suction pipe, 9.10...Heat exchanger, 11...Switching valve seat, 12...Piston, 12a...Pressure equalization hole, 3a...Pressure relief hole, 12d... Valve body, 12g・
...Auxiliary spring, 13...Compression spring, 18.''Opening/closing valve.
Claims (1)
力変換室に区画し、高圧室に圧縮機の吐出管に対する接
続口と、圧縮機の吸入管に対する接続口及び該接続口を
挾んで２個の熱交換器用導管に対する接続口とを設け、
吸入管に対する接続口から２個の熱交換器用導管に対す
る接続口にかけて一連の切換用弁シートを設け、該切換
用弁シートに摺接するスライドバルブを該ピストンに連
結し、該ピストンに高圧室と圧力変換室を連通させる均
圧孔を形成すると共に該均圧孔に暖房運転時において高
圧室から圧力変換室への流れを遮断する弁体を設け、該
ピストンを高圧室方向に常時付勢するばねと暖房運転時
においてのみ該ピストンを高圧室方向に付勢する補助ば
ねを設け、圧力変換室に圧縮機の吸入側に連通する圧力
逃し孔を設けると共に該圧力逃し孔に開閉弁を設け、該
圧力逃し孔の径を該均圧孔の径より大きく形成して成る
ことを特徴とする可逆冷凍サイクル用四方逆転弁。The cylindrical reversing valve body is divided into a high pressure chamber and a pressure conversion chamber by a piston, and the high pressure chamber has a connection port for the discharge pipe of the compressor, a connection port for the suction pipe of the compressor, and two ports sandwiching the connection port. and a connection port for the heat exchanger conduit,
A series of switching valve seats is provided from the connection port for the suction pipe to the connection port for the two heat exchanger conduits, and a slide valve in sliding contact with the switching valve seat is connected to the piston. A pressure equalization hole is formed that communicates the conversion chamber, and a valve body is provided in the pressure equalization hole to block the flow from the high pressure chamber to the pressure conversion chamber during heating operation, and a spring that constantly biases the piston in the direction of the high pressure chamber. and an auxiliary spring that biases the piston toward the high pressure chamber only during heating operation, a pressure relief hole communicating with the suction side of the compressor is provided in the pressure conversion chamber, and an on-off valve is provided in the pressure relief hole. A four-way reversing valve for a reversible refrigeration cycle, characterized in that the diameter of the pressure relief hole is larger than the diameter of the pressure equalization hole.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60076629A JPS61236981A (en) | 1985-04-12 | 1985-04-12 | Four-way reversing valve for reversible refrigerating cycle |
| US06/794,851 US4644760A (en) | 1984-11-05 | 1985-11-04 | Reversible four-way valve for reversible refrigerating cycle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60076629A JPS61236981A (en) | 1985-04-12 | 1985-04-12 | Four-way reversing valve for reversible refrigerating cycle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61236981A true JPS61236981A (en) | 1986-10-22 |
| JPH0559309B2 JPH0559309B2 (en) | 1993-08-30 |
Family
ID=13610657
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60076629A Granted JPS61236981A (en) | 1984-11-05 | 1985-04-12 | Four-way reversing valve for reversible refrigerating cycle |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61236981A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5259233A (en) * | 1991-04-24 | 1993-11-09 | American Air Liquide | Counterflow valve |
| WO2009152402A3 (en) * | 2008-06-13 | 2010-04-08 | Carrier Corporation | Four-way reversing valve |
-
1985
- 1985-04-12 JP JP60076629A patent/JPS61236981A/en active Granted
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5259233A (en) * | 1991-04-24 | 1993-11-09 | American Air Liquide | Counterflow valve |
| WO2009152402A3 (en) * | 2008-06-13 | 2010-04-08 | Carrier Corporation | Four-way reversing valve |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0559309B2 (en) | 1993-08-30 |
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