JPH0979409A - Control valve - Google Patents
Control valveInfo
- Publication number
- JPH0979409A JPH0979409A JP7265008A JP26500895A JPH0979409A JP H0979409 A JPH0979409 A JP H0979409A JP 7265008 A JP7265008 A JP 7265008A JP 26500895 A JP26500895 A JP 26500895A JP H0979409 A JPH0979409 A JP H0979409A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- opening
- valve body
- rotor
- control 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
- 230000005540 biological transmission Effects 0.000 claims abstract description 19
- 238000012856 packing Methods 0.000 claims abstract description 11
- 230000002093 peripheral effect Effects 0.000 claims description 8
- 239000000696 magnetic material Substances 0.000 claims description 6
- 239000002184 metal Substances 0.000 claims description 3
- 238000007789 sealing Methods 0.000 claims description 2
- 239000003507 refrigerant Substances 0.000 abstract description 15
- 238000004891 communication Methods 0.000 description 15
- 238000010438 heat treatment Methods 0.000 description 14
- 238000001816 cooling Methods 0.000 description 10
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000007796 conventional method Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000033001 locomotion Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Landscapes
- Electrically Driven Valve-Operating Means (AREA)
- Multiple-Way Valves (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、ヒートポンプ式
冷媒回路における冷房時と暖房時の冷媒の流路を切り換
える四方弁と、膨張弁の機能を果たす電動弁とを複合一
体化した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 control valve in which a four-way valve for switching a refrigerant flow path during cooling and heating in a heat pump type refrigerant circuit and an electric valve functioning as an expansion valve are combined and integrated. Is.
【０００２】[0002]
【従来の技術】先ず最初に図５は、特願平６−２７０３
８１号に開示された従来技術の制御弁Ｚの構造を示す。
制御弁Ｚの構造は、六方弁であり、大きく分けて電動弁
Ａ部、四方弁Ｂ部及び前記電動弁Ａ部と四方弁Ｂ部とを
連結する伝達装置Ｃ部の３つに分けられる。2. Description of the Related Art First, FIG. 5 shows Japanese Patent Application No. 6-2703.
81 shows the structure of a prior art control valve Z disclosed in No. 81.
The structure of the control valve Z is a six-way valve, which is roughly divided into three parts: an electric valve A, a four-way valve B, and a transmission device C that connects the electric valve A and the four-way valve B.
【０００３】第１番目に電動弁Ａ部の構造は、上部を大
径部１ａとした非磁性体からなる円筒状ケース１の下端
部に弁ボディ６が配置されおり、該弁ボディ６は、中央
にチャンバー１７を備えチャンバーの中心上部に推進軸
受７が設けられると共に下部に弁口８が設けられ、チャ
ンバー側部には開口１８が設けられている。又、前記開
口１８には出入口パイプ１９が、又、下部の弁口８下方
の開口２０には出入口パイプ２１が設けられている。First, in the structure of the electrically operated valve A, a valve body 6 is arranged at the lower end of a cylindrical case 1 made of a non-magnetic material having an upper portion having a large diameter portion 1a. A chamber 17 is provided at the center, a propulsion bearing 7 is provided at the upper center of the chamber, a valve port 8 is provided at the lower part, and an opening 18 is provided at the side of the chamber. An inlet / outlet pipe 19 is provided in the opening 18, and an inlet / outlet pipe 21 is provided in the opening 20 below the lower valve port 8.
【０００４】そして、ケース１の下部外周に固定子コイ
ル２が設けられ、前記ケース１の内部には先端部に針状
弁３を備えたねじ軸４の上部と一体的に成形されたモー
タの回転子５が設けられ、このねじ軸４が前記推進軸受
７により直進運動に変換されて弁ボディ６の下部の弁口
８に前記針状弁３を接離させることにより、弁口８の開
口度を制御させるようになっており、回転子５の上半部
内周面には、一箇所だけ中心方向にリブ状の凸部９が突
出状に形成されているものである。A stator coil 2 is provided on the outer periphery of the lower portion of the case 1, and inside the case 1 is a motor integrally formed with the upper portion of a screw shaft 4 having a needle valve 3 at the tip thereof. A rotor 5 is provided, and the screw shaft 4 is converted into a linear motion by the propulsion bearing 7 so that the needle valve 3 is brought into contact with and separated from the valve opening 8 at the lower portion of the valve body 6, thereby opening the valve opening 8. The rib 5 is formed on the inner peripheral surface of the upper half portion of the rotor 5 so as to project in one direction toward the center.
【０００５】第２番目に四方弁Ｂ部の構造は、非磁性体
からなる前記円筒状ケース１上部の大径部１ａの上端
に、図６に示す如く、４つの開口３３、３４、３５、３
６を同心円上でかつ、等間隔に有する金属円板状の弁座
３７が固定され、この弁座３７の下面にプラスチック製
の肉厚円板状の弁体３９が摺動回転可能に配設されたも
のである。The second structure of the four-way valve B is as follows. As shown in FIG. 6, four openings 33, 34, 35 are provided at the upper end of the large diameter portion 1a of the upper portion of the cylindrical case 1 made of a non-magnetic material. Three
A metal disk-shaped valve seat 37 having concentric circles 6 at equal intervals is fixed, and a plastic thick disk-shaped valve body 39 is slidably rotatable on the lower surface of the valve seat 37. It was done.
【０００６】前記弁座３７の４つの開口３３、３４、３
５、３６は、その開口３３を導入口、これと対向位置の
開口３４を導出口、又これらと直交的に配置した開口３
５と３６を通孔としており、それぞれ導入口３３の上面
には導入管４０が、導出口３４には導出管４１が、又通
孔３５と３６には通孔管４２と４３が設けられ、前記導
入口３３の下部にのみパイプによるストッパー４４が少
量突出状に設けられている。The four openings 33, 34, 3 of the valve seat 37
Reference numerals 5 and 36 denote an opening 33 of the opening 33, an outlet 34 of an opening 34 facing the opening 33, and an opening 3 arranged orthogonally to these openings.
5 and 36 are formed as through holes, an introduction pipe 40 is provided on the upper surface of the introduction port 33, a discharge pipe 41 is provided at the discharge port 34, and through-hole pipes 42 and 43 are provided at the through holes 35 and 36, respectively. A stopper 44 made of a pipe is provided in a protruding manner in a small amount only at the lower part of the introduction port 33.
【０００７】又、前記肉厚円板状の弁体３９には、図６
に示す如く、前記弁座３７の導入口３３と通孔３５と対
応する位置に貫通孔４５と４６を設けると共に、その上
半部に両貫通孔４５、４６をつなぐ連通孔４７（図７
（Ａ）参照）を設け、導出口３４及び通孔３６と対応す
る位置に導出口３４及び通孔３６を気密的につなぐ気密
連通孔４８（図７（Ｂ）参照）が設けられ、これら両連
通孔４７、４８の上部は平面円弧状に形成されていて、
隣接する各開口において連通状態が切り換わるようにな
っている。Further, the thick disk-shaped valve body 39 has a structure shown in FIG.
As shown in FIG. 7, through holes 45 and 46 are provided at positions corresponding to the inlet 33 and the through hole 35 of the valve seat 37, and a communication hole 47 connecting both through holes 45 and 46 to the upper half portion thereof (FIG. 7).
(See (A)), and an airtight communication hole 48 (see FIG. 7B) that airtightly connects the outlet 34 and the through hole 36 is provided at a position corresponding to the outlet 34 and the through hole 36. The upper portions of the communication holes 47 and 48 are formed in a plane arc shape,
The communication state is switched at each adjacent opening.
【０００８】又、肉厚円板状の弁体３９には、図５に示
す如く、その上面中心に孔２２が設けられ、この孔２２
に運転時冷媒の圧力により弁体３９を弁座３７に押圧す
る圧力よりも弱い圧力の圧縮コイルばね２３が設けら
れ、反対側の弁体３９の下面中心にはボス２４を設け、
その中心部に多数の内歯２５が形成されている。Further, as shown in FIG. 5, the thick disc-shaped valve body 39 is provided with a hole 22 at the center of its upper surface.
Is provided with a compression coil spring 23 having a pressure weaker than the pressure for pressing the valve body 39 against the valve seat 37 by the pressure of the refrigerant during operation, and the boss 24 is provided at the center of the lower surface of the valve body 39 on the opposite side.
A large number of inner teeth 25 are formed at the center thereof.
【０００９】第３番目に伝達装置Ｃ部は、図５に示す如
く、前記電動弁Ａ部の回転子５と四方弁Ｂ部の弁体２９
との間の前記非磁性体からなる円筒状ケース１の中間部
に設けられ、電動弁Ａ部の弁口８が全開直前の位置と全
閉直前の位置において、回転を伝えるようにしたもので
ある。Thirdly, as shown in FIG. 5, the transmission device C portion includes the rotor 5 of the motor-operated valve A portion and the valve element 29 of the four-way valve B portion.
Is provided in the intermediate portion of the cylindrical case 1 made of the non-magnetic material between and and the valve opening 8 of the motor-operated valve A portion transmits rotation at a position immediately before full opening and a position immediately before full closing. is there.
【００１０】即ち、円筒状ケース１内にガイドブッシュ
２６をかしめ固定し、このガイドブッシュ２６の中心
に、上部に鍔２７を有する連結棒２８を気密的、かつ回
転自在に支持し、この連結棒２８の上端部には前記弁体
３９下面中心の内歯２５と噛み合う外歯２９が形成さ
れ、この内歯２５と外歯２９とにより係合手段３０を形
成している。That is, a guide bush 26 is caulked and fixed in the cylindrical case 1, and a connecting rod 28 having a flange 27 at an upper portion is air-tightly and rotatably supported at the center of the guide bush 26. External teeth 29 meshing with the internal teeth 25 at the center of the lower surface of the valve body 39 are formed at the upper end of the valve body 39, and the engagement means 30 is formed by the internal teeth 25 and the external teeth 29.
【００１１】また、上記の連結棒２８の下方は、ガイド
ブッシュ２６を貫通し、上下に突出片１４、１５を有す
るコイルによる遅延伝達手段１６が設けられている。即
ち、連結棒２８の下端は前記回転子５の上半部内面にま
で延び、その先端にフランジ１１を備えている。Below the connecting rod 28, a delay transmission means 16 is provided, which penetrates the guide bush 26 and has a coil having projecting pieces 14, 15 on the upper and lower sides. That is, the lower end of the connecting rod 28 extends to the inner surface of the upper half of the rotor 5, and the flange 11 is provided at the tip thereof.
【００１２】そして、連結棒２８のガイドブッシュ２６
より少し下方に、垂下状のストッパー片１３ａを外方先
端に備えたストッパー１３を固定し、このストッパー１
３と下端のフランジ１１との間に、図５および図１０、
図１１に示す如く、所定長さのコイルの上下端を上方の
突出片１４と下方の突出片１５として接線方向にほぼ平
行的に延長させた遅延伝達手段１６を回転可能に設け、
この遅延伝達手段１６の上方の突出片１４の先端が前記
ストッパー片１３ａと当接可能となっており、下方の突
出片１５の先端が前記回転子５の上半部内面に形成され
た内向きの凸部９と当接可能となっている。The guide bush 26 of the connecting rod 28
A stopper 13 having a hanging stopper piece 13a at its outer tip is fixed to a slightly lower position.
3 and the flange 11 at the lower end,
As shown in FIG. 11, a delay transmission means 16 having rotatably provided upper and lower ends of a coil of a predetermined length as an upper protruding piece 14 and a lower protruding piece 15 is extended substantially parallel to the tangential direction,
The tip of the upper projecting piece 14 of the delay transmission means 16 can be brought into contact with the stopper piece 13a, and the tip of the lower projecting piece 15 faces inwardly formed on the inner surface of the upper half of the rotor 5. Can be brought into contact with the convex portion 9.
【００１３】引き続いて、従来技術の制御弁の作用（作
動）について説明する。図５に示す如く、電動弁Ａ部の
針状弁３が閉弁状態で、図７、図８に示す如く、四方弁
Ｂ部の弁体３９における貫通孔４５と４６が弁座３７の
導入孔３３と通孔３５に対応して暖房状態となっている
時は、図１０、図１１（Ａ）に示す如く、平面的にみ
て、回転子５の凸部９の一側面（上面）が遅延伝達手段
１６の下方の突出片１５の外面（下面）に、また、上方
の突出片１４の外面（上面）がストッパー片１３ａの外
側（下面）に当接して、上下の突出片１４、１５を凸部
９とストッパー片１３ａにより挟んだ状態となってい
る。Next, the operation (operation) of the conventional control valve will be described. As shown in FIG. 5, the needle valve 3 of the motor-operated valve A is closed, and as shown in FIGS. 7 and 8, the through holes 45 and 46 in the valve body 39 of the four-way valve B are introduced into the valve seat 37. When the heating state is provided corresponding to the holes 33 and the through holes 35, one side surface (upper surface) of the convex portion 9 of the rotor 5 is viewed in plan as shown in FIGS. 10 and 11A. The outer surface (lower surface) of the lower projecting piece 15 of the delay transmission means 16 and the outer surface (upper surface) of the upper projecting piece 14 contact the outer surface (lower surface) of the stopper piece 13a, so that the upper and lower projecting pieces 14, 15 are contacted. Is sandwiched between the convex portion 9 and the stopper piece 13a.
【００１４】この状態においては、弁座３７と弁体３９
の位置関係が図８に示す如く、四方弁Ｂ部の弁座３７の
導入口３３の下面に突出状に設けたストッパー４４は、
弁体３９の貫通孔４５と対応した位置にある。従って、
図７（Ａ）に示す如く、連通孔４７により導入口３３と
通孔３５とが連通された状態になり、図９で示すよう
に、圧縮機Ｆの吐出口から出た冷媒は、導入管４０→導
入口３３→連通孔４７→通孔管４２を経て室内熱交換器
Ｅに入り、制御弁Ａの出入口パイプ１９→弁口８→出入
口パイプ２１を経て、室外熱交換器Ｄを通り、図６
（Ｂ）に示す如く、通孔管４３→通孔３６→気密連通孔
４８→導出口３４→導出管４１を経て圧縮機Ｆに戻る。In this state, the valve seat 37 and the valve body 39
As shown in FIG. 8, the stopper 44 provided in a protruding shape on the lower surface of the inlet 33 of the valve seat 37 of the four-way valve B is
It is at a position corresponding to the through hole 45 of the valve body 39. Therefore,
As shown in FIG. 7A, the introduction port 33 and the through hole 35 are in communication with each other through the communication hole 47. As shown in FIG. 9, the refrigerant discharged from the discharge port of the compressor F is introduced into the introduction pipe. 40 → Inlet 33 → Communication hole 47 → Enter the indoor heat exchanger E through the through hole pipe 42, pass through the inlet / outlet pipe 19 of the control valve A → Valve 8 → Inlet / outlet pipe 21 and the outdoor heat exchanger D, Figure 6
As shown in (B), the flow returns to the compressor F via the through-hole pipe 43 → the through-hole 36 → the airtight communication hole 48 → the outlet 34 → the outlet pipe 41.
【００１５】この暖房状態において、電動弁Ａの固定子
コイル２に閉弁方向に回転するように通電されると、図
１０、図１１（Ａ）に示すモータの回転子５は上面から
みて矢印の如く左方向に一回転し、回転子５の凸部９が
遅延伝達手段１６の下方の突出片１５から離れ、約１周
回転したところで図１１（Ｂ）のように下方の突出片１
５の内側（上面）に当たる。When the stator coil 2 of the motor-operated valve A is energized so as to rotate in the valve closing direction in this heating state, the rotor 5 of the motor shown in FIGS. As shown in FIG. 11 (B), when the protrusion 9 of the rotor 5 is separated from the lower protruding piece 15 of the delay transmission means 16 and rotated about one turn, the lower protruding piece 1 is rotated as shown in FIG.
5 inside (upper surface).
【００１６】続いて回転子５が回転すると、前記遅延伝
達手段１６下方の突出片１５が回転子５の凸部９に押さ
れて上方の突出片１４と共に左方向に回動し、やがて、
図１１（Ｃ）のように上方の突出片１４が前記スッパー
片１３ａの後面（上面）と当接するまで回転子５が回転
する。上記図１１（Ａ）〜（Ｃ）間の回転子５の約２回
転の間は遅延伝達手段１６におけるコイルの空転によ
り、連結棒２８には伝わらない。従って、この間、ねじ
軸４による針状弁３の上下作用により弁口８の開口面積
を変化させることができ、最適絞り度の位置で、暖房運
転が可能となる。Subsequently, when the rotor 5 rotates, the projecting piece 15 below the delay transmission means 16 is pushed by the convex portion 9 of the rotor 5 and rotates leftward with the projecting piece 14 above.
As shown in FIG. 11C, the rotor 5 rotates until the upper protruding piece 14 contacts the rear surface (upper surface) of the sputter piece 13a. During about two rotations of the rotor 5 shown in FIGS. 11 (A) to 11 (C), it is not transmitted to the connecting rod 28 due to idling of the coil in the delay transmission means 16. Therefore, during this period, the opening area of the valve port 8 can be changed by the vertical action of the needle valve 3 by the screw shaft 4, and the heating operation can be performed at the position of the optimum throttle degree.
【００１７】次に、冷房運転に切り換えたい時は、図１
１（Ｃ）の状態から回転子５を、さらに左方向に回転さ
せると上方の突出片１４により連結棒２８と一体的に固
定されたストッパー片１３ａを押しつつ、図１１（Ｄ）
の状態まで回転するので、連結棒２８は回転を始め、上
部の四方弁Ｂ部の弁体３６に回転を伝える。これによ
り、弁体３９が図８の状態から図９の状態まで９０°回
転し、冷房運転に切り換わる。Next, when it is desired to switch to the cooling operation, FIG.
When the rotor 5 is further rotated leftward from the state of 1 (C), the upper protruding piece 14 pushes the stopper piece 13a integrally fixed to the connecting rod 28, and FIG.
Since the connection rod 28 starts rotating, the rotation is transmitted to the valve body 36 of the upper four-way valve B portion. As a result, the valve element 39 rotates 90 ° from the state shown in FIG. 8 to the state shown in FIG. 9 and switches to the cooling operation.
【００１８】この暖房運転から冷房運転に切り換える
際、弁体３９を９０°回転させるが、この時、弁体３９
における連通孔４７の貫通孔４５側の内縁外端部に当接
していたストッパー４４が連通孔４７の貫通孔４６側の
内縁外端部に図９の如く当接することにより確実に停止
する。When switching from the heating operation to the cooling operation, the valve body 39 is rotated by 90 degrees.
The stopper 44, which was in contact with the inner edge outer end portion of the communication hole 47 on the side of the through hole 45, comes into contact with the inner edge outer end portion of the communication hole 47 on the side of the through hole 46 as shown in FIG.
【００１９】この弁体３９の切り換えにより、気密連通
孔４８は導出孔３４と通孔３５の間を気密的に連通させ
ることになるため、圧縮機Ｆの吐出口から出た冷媒は、
導入管４０→導入口３３→連通孔４７→通孔３６→導孔
管４３を経て室外熱交換器Ｄに入り、制御弁の出入口パ
イプ２１→弁口８→出入口パイプ１９を経て室内熱交換
器Ｅを通り、通孔管４２→通孔３５→連通孔４８→導出
口３４→導出管４１を経て圧縮機Ｆに戻る。The switching of the valve body 39 causes the airtight communication hole 48 to airtightly communicate between the outlet hole 34 and the communication hole 35, so that the refrigerant discharged from the discharge port of the compressor F is
Introducing pipe 40 → Introducing port 33 → Communicating hole 47 → Passing hole 36 → Introducing into the outdoor heat exchanger D via the guiding pipe 43, through the inlet / outlet pipe 21 of the control valve → Valve 8 → Inlet / outlet pipe 19, the indoor heat exchanger After passing through E, it returns to the compressor F through the through hole pipe 42, the through hole 35, the communication hole 48, the outlet 34, and the outlet pipe 41.
【００２０】この冷房運転、即ち、図１１（Ｄ）の状態
で最適絞り度を得ようとする時は、針状弁３が閉弁方向
に回転するように固定子コイル２に通電する。それによ
り、前記とは逆の原理にて、モータの回転子５は遅延伝
達手段とは接触することなく上面から見て矢印とは逆の
右方向に一回転し、回転子の凸部９が遅延伝達手段１６
の下方の突出片１５の反対側に当たる。続いて回転子５
が回転すると、遅延伝達手段１６の下方の突出片１５が
ロータースリーブの凸部９に押されて右方向に回転し、
やがて上方の突出片１４が前記ストッパー片１３と当接
するまで、回転子５が回転する。この間ねじ軸４による
針状弁３の上下作用により弁口８の開口面積を変化させ
ることができ、最適絞り度の位置で冷房運転が可能とな
る。In this cooling operation, that is, in order to obtain the optimum throttle degree in the state of FIG. 11D, the stator coil 2 is energized so that the needle valve 3 rotates in the valve closing direction. As a result, on the principle opposite to the above, the rotor 5 of the motor does not make contact with the delay transmission means but makes one full rotation in the right direction opposite to the arrow when viewed from the top, and the convex portion 9 of the rotor is Delay transmission means 16
It hits the opposite side of the protruding piece 15 below. Then rotor 5
When is rotated, the protruding piece 15 below the delay transmission means 16 is pushed by the convex portion 9 of the rotor sleeve and rotated to the right,
The rotor 5 rotates until the upper protruding piece 14 comes into contact with the stopper piece 13. During this time, the opening area of the valve opening 8 can be changed by the vertical movement of the needle valve 3 by the screw shaft 4, and the cooling operation can be performed at the position of the optimum throttling degree.
【００２１】再び暖房運転に切り換えたい時は、針状弁
３が更に閉弁方向に回転するように固定子コイル２に通
電すると、遅延伝達手段１６の上方の突出片１４がスト
ッパー片１３ａと当接し連結棒２８が図１１において反
時計方向に回転し、弁体３９は図９の状態から図８の状
態に９０°回動して暖房運転に切り換わる。When it is desired to switch to the heating operation again, when the stator coil 2 is energized so that the needle valve 3 further rotates in the valve closing direction, the protruding piece 14 above the delay transmission means 16 contacts the stopper piece 13a. The connecting rod 28 rotates in the counterclockwise direction in FIG. 11, and the valve body 39 rotates 90 ° from the state of FIG. 9 to the state of FIG. 8 to switch to the heating operation.
【００２２】[0022]
【発明が解決しようとする課題】前述した従来技術で
は、弁口８の内径を大口径（例えば、φ３ｍｍ→φ６ｍ
ｍ）にし、かつ、大流量高差圧の冷媒を流量制御（絞り
制御）する場合には、回転子５の上部と下部に高差圧が
作用し、針状弁３の受圧面積と圧力差に比例して増大す
る作動抵抗力により以下のような問題点があった。 針状弁３を開閉弁させるのに大型のモータ（固定子コ
イル２や回転子５など）が必要であり、配管スペースに
無駄が生じた。 大型モータは、部品コストを高くした。 大型のモータを駆動させると、消費電力がアップし、
エアコンの運転コストを高くした。In the above-mentioned conventional technique, the inner diameter of the valve opening 8 is set to a large diameter (for example, φ3 mm → φ6 m).
m) and controlling the flow rate (throttle control) of the refrigerant having a large flow rate and high differential pressure, the high differential pressure acts on the upper and lower parts of the rotor 5, and the pressure receiving area of the needle valve 3 and the pressure difference. There was the following problem due to the operating resistance force that increases in proportion to. A large motor (such as the stator coil 2 and the rotor 5) is required to open and close the needle valve 3, resulting in waste of piping space. Large motors have increased component costs. Driving a large motor increases power consumption,
Increased the operating cost of the air conditioner.
【００２３】[0023]
【問題点を解決するための手段】本発明の制御弁は、膨
張弁の機能を果たす電動弁Ａ部と、冷房時と暖房時の冷
媒の流路を切り換える機能を果たす四方弁Ｂ部からなる
従来の制御弁において、回転子５と一体化された弁体５
１の外周面におねじ５２と円筒状のシール部５３及び弁
部５５のを設けると共に中心部に均圧孔５６を設けるこ
とにより、回転子５を回転させ上下動させるときに圧力
差によって発生する作動抵抗力をなくすことにより、小
さな駆動力（小型モータ）で大流量の冷媒の流量制御
（絞り制御）可能とすることを特徴とするものである。The control valve of the present invention comprises an electrically operated valve A section which functions as an expansion valve, and a four-way valve B section which functions to switch the flow path of the refrigerant during cooling and heating. In the conventional control valve, the valve body 5 integrated with the rotor 5
By providing the screw 52, the cylindrical seal portion 53, and the valve portion 55 on the outer peripheral surface of No. 1 and providing the pressure equalizing hole 56 in the central portion, the pressure difference is generated when the rotor 5 is rotated and moved up and down. It is characterized in that the flow rate control (throttle control) of a large flow rate of refrigerant can be performed with a small driving force (small motor) by eliminating the operating resistance force.
【００２４】すなわち、本発明に係る制御弁は、非磁性
体からなるケース１外周部の固定子コイル２への通電に
よるケース１内の回転子５の回転により、この回転子５
の中心下方に一体的に設けられたおねじを介しておねじ
の下端に設けられた弁を上下動させ、ケース１の下端に
設けた弁ボディ６下部の弁口８の開度を制御する電動弁
Ａ部と、少なくとも３つの開口を同心円上に設けた金属
円板状の弁座３７を前記ケース１の上端に設け、この弁
座３７の下面を摺動回転して前記３つの開口の少くとも
２つを気密的に連通させ、他の１つの開口は開放状態と
する弁体３９とからなる四方弁Ｂ部と、前記電動弁Ａ部
の回転子５と四方弁Ｂ部の弁体３９との間に設けた、電
動弁Ａ部の弁口８が全開直前の位置と全閉直前の位置に
おいて回転を伝える伝達装置Ｃ部とにより構成され、前
記電動弁Ａ部の回転子５の回転力を利用して、電動弁Ａ
部の弁口８の絞り開閉と四方弁Ｂ部の弁体３９の回転に
よる流路切換とを連動して行なう制御弁において、前記
回転子５の中心部には弁体５１を一体的に設け、該弁体
５１の外周部にはおねじ５２と円筒状のシール部５３及
び弁部５５のを設けると共に中心部に均圧孔５６を設け
て前記ケース１内に形成しているチャンバー６２と前記
弁口８の下に形成している開口２０とを連通させ、前記
弁ボディ６には、中央上部にめねじ６０を有する推進軸
受７を設けると共に、その下方に前記弁体５１のシール
部５３を気密シールするパッキン６１を設けた制御弁で
ある。That is, in the control valve according to the present invention, the rotor 5 in the case 1 is rotated by energization of the stator coil 2 at the outer peripheral portion of the case 1 made of a non-magnetic material.
The valve provided at the lower end of the screw is moved up and down via the male screw integrally provided below the center of the case to control the opening of the valve opening 8 below the valve body 6 provided at the lower end of the case 1. A motor-operated valve A portion and a metal disk-shaped valve seat 37 in which at least three openings are concentrically provided are provided at the upper end of the case 1, and the lower surface of the valve seat 37 is slidably rotated to allow the three openings to be opened. A four-way valve B section consisting of a valve body 39 in which at least two are communicated in an airtight manner and the other one opening is in an open state, a rotor 5 of the electric valve A section and a valve body of the four-way valve B section. The valve opening 8 of the motor-operated valve A portion, which is provided between the motor-operated valve A portion 39 and the motor-operated valve A portion, is constituted by a transmission device C portion that transmits rotation at a position immediately before fully opening and a position immediately before fully closing. Motorized valve A using rotational force
In a control valve that interlocks opening and closing of the valve port 8 of the section and switching of the flow path by rotation of the valve body 39 of the four-way valve B, a valve body 51 is integrally provided at the center of the rotor 5. A male screw 52, a cylindrical seal portion 53, and a valve portion 55 are provided on the outer peripheral portion of the valve body 51, and a pressure equalizing hole 56 is provided in the central portion to form a chamber 62 in the case 1 and the chamber 62. The valve body 6 is provided with a propulsion bearing 7 having an internal thread 60 at the upper center thereof, which is communicated with an opening 20 formed below the valve opening 8, and a sealing portion 53 of the valve body 51 is provided below the propulsion bearing 7. Is a control valve provided with a packing 61 that hermetically seals.
【００２５】[0025]
【発明の実施の形態】本発明の一実施例を図１、図２に
基づき詳細に説明する。なお、従来技術の制御弁Ｚと同
じ部品については同一の符号を用いている。本発明の制
御弁は、図１に示す如く、伝達装置Ｃ部及び四方弁Ｂ部
については、従来技術の制御弁と構造が同一のため従来
技術と重複ので詳細な説明は省略する。BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the present invention will be described in detail with reference to FIGS. Note that the same reference numerals are used for the same components as the control valve Z of the related art. In the control valve of the present invention, as shown in FIG. 1, the transmission device C portion and the four-way valve B portion have the same structure as the control valve of the prior art, and thus the description is omitted because it is the same as that of the prior art.
【００２６】本発明の制御弁の電動弁Ａ部の構造は、ケ
ース１と固定子コイル２と回転子５および回転子に固着
された弁体５１と弁ボテディ６とにより構成されてい
る。前記弁ボディ６は、上部を大径部１ａとした非磁性
体からなる円筒状ケース１の下端部に取り付けられるも
のであり、図２に示すように、該弁ボディ６の中央上部
には、めねじ６０を有する推進軸受７を固定保持してい
る軸受座部５７が設けられ、その下方に弾性体でできて
いるリング状のパッキン６１をはめ込むためのパッキン
溝５８が設けられ、続いて内径φＤ１を有するガイド部
５９、チャンバー１７、内径φＤ２を有する弁口８が設
けられるとともに、チャンバー１７の側部には開口１８
が設けられている。又、弁口８の下部には開口２０が設
けられており、さらに、開口１８には出入口パイプ１９
を、開口２０には出入口パイプ２１が取り付けられてい
る。The structure of the motor-operated valve A portion of the control valve of the present invention comprises a case 1, a stator coil 2, a rotor 5, a valve body 51 fixed to the rotor, and a valve body 6. The valve body 6 is attached to the lower end of the cylindrical case 1 made of a non-magnetic material with the upper portion having a large diameter portion 1a. As shown in FIG. A bearing seat 57 for fixing and holding the propulsion bearing 7 having an internal thread 60 is provided, and a packing groove 58 for fitting a ring-shaped packing 61 made of an elastic body is provided below the bearing seat 57, followed by an inner diameter. A guide portion 59 having φD1, a chamber 17 and a valve port 8 having an inner diameter φD2 are provided, and an opening 18 is provided at a side portion of the chamber 17.
Is provided. Further, an opening 20 is provided in the lower portion of the valve opening 8, and the opening 18 has an inlet / outlet pipe 19
An inlet / outlet pipe 21 is attached to the opening 20.
【００２７】一方、ケース１の下部外周には固定子コイ
ル２が設けられ、該ケース１内にはチャンバー６２が形
成されている。又、前記チャンバー６２内に配置された
回転子５の中心部には弁体５１が一体的に設けられてお
り、該弁体５１の外周には、上から順に前記めねじ６０
と螺合するおねじ５２、前記ガイド部５９の内径φＤ１
より小さい外径で前記パッキン６１とにより気密保持す
る円筒状のシール部５３、同じく前記ガイド部５９の内
径φＤ１より小さい内径φＤ３を有する小径部５４及び
前記弁口８の内径φＤ２より小さい外径で弁口８と接離
することにより弁口８の開口度を制御するストレート円
筒状の弁部５５が形成されている。又、前記弁体５１の
中心部には、前記チャンバー６２と前記開口２０とを連
通する内径φＤ４を有する均圧孔５６が形成されてい
る。On the other hand, a stator coil 2 is provided on the outer periphery of the lower part of the case 1, and a chamber 62 is formed in the case 1. Further, a valve body 51 is integrally provided at the center of the rotor 5 arranged in the chamber 62, and the female screw 60 is sequentially provided on the outer periphery of the valve body 51 from the top.
Male thread 52 to be screwed with, inner diameter φD1 of the guide portion 59
A cylindrical seal portion 53 having a smaller outer diameter and airtightly held by the packing 61, a small diameter portion 54 having an inner diameter φD3 smaller than the inner diameter φD1 of the guide portion 59, and an outer diameter smaller than the inner diameter φD2 of the valve opening 8 are also provided. A straight cylindrical valve portion 55 that controls the opening degree of the valve opening 8 by coming into contact with and separating from the valve opening 8 is formed. In addition, a pressure equalizing hole 56 having an inner diameter φD4 that connects the chamber 62 and the opening 20 is formed in the center of the valve body 51.
【００２８】[0028]
【作用】本発明の制御弁の回転子５が上下動する際に、
圧力差によって回転子５に加わる作動抵抗力を、いかに
無くすことができるかについて説明する。ここで、開口
１８での内圧を圧力Ｐ1 、開口部２０での内圧をＰ2 と
すると、圧力損失がほとんどなく開口１８と連通してい
るチャンバー１７の内圧はＰ1 となり、さらに、同じく
圧力損失がほとんどなく均圧孔５６と連通しているチャ
ンバー６２の内圧はＰ2 となる。次ぎに、各室の内圧に
よって回転子５に加わる力は、それぞれ以下のようにな
る。チャンバー６２内において回転子５に加わる下向き
の力Ｒ1 は、 Ｒ1 ＝１／４×π・（Ｄ12−Ｄ42）・Ｐ2 となり、チャンバー１７内において回転子５に加わる上
向きの力Ｒ2 は、 Ｒ2 ＝１／４×π・（Ｄ12−Ｄ32）・Ｐ1 となり、チャンバー１７内において回転子５に加わる下
向きの力Ｒ3 は、 Ｒ3 ＝１／４×π・（Ｄ22−Ｄ32）・Ｐ1 となり、開口２０内において回転子５に加わる上向きの
力Ｒ4 は、 Ｒ4 ＝１／４×π・（Ｄ22−Ｄ42）・Ｐ2 となる。よって、圧力差によって回転子５に発生する作
動抵抗力Ｒ（下向きの力を＋とする）は、 Ｒ＝Ｒ1 −Ｒ2 ＋Ｒ3 −Ｒ4 ＝１／４×π・（Ｄ12−Ｄ22）・（Ｐ2 −Ｐ1 ） となり、ここで、Ｄ1 ＝Ｄ2 とすると、Ｒ＝０となり、
弁口８の内径φＤ2 や圧力差（Ｐ2 −Ｐ1 ）が、いくら
大きくなっても、弁口８の内径φＤ2 をガイド部５９の
内径φＤ1 と等しく設計すれば、均圧孔５６とパッキン
シールの働きにより圧力差によって回転子５に発生する
作動抵抗力Ｒがゼロとなり、大きなモータは不要とな
る。When the rotor 5 of the control valve of the present invention moves up and down,
How the operation resistance force applied to the rotor 5 due to the pressure difference can be eliminated will be described. Here, if the internal pressure at the opening 18 is P1 and the internal pressure at the opening 20 is P2, there is almost no pressure loss, and the internal pressure of the chamber 17 communicating with the opening 18 is P1. Instead, the internal pressure of the chamber 62 communicating with the pressure equalizing hole 56 becomes P2. Next, the forces applied to the rotor 5 by the internal pressure of each chamber are as follows. The downward force R1 applied to the rotor 5 in the chamber 62 is R1 = 1/4 × π · (D1 2 −D4 2 ) · P2, and the upward force R2 applied to the rotor 5 in the chamber 17 is R2. = 1/4 × π · (D1 2 −D3 2 ) · P1 and the downward force R3 applied to the rotor 5 in the chamber 17 is R3 = 1/4 × π · (D2 2 −D3 2 ) · P1. Thus, the upward force R4 applied to the rotor 5 in the opening 20 is R4 = 1 / 4.multidot..pi..multidot..multidot..multidot..multidot..multidot. (D2 2 -D4 2 ) .multidot.P2. Therefore, the operating resistance force R (the downward force is +) generated in the rotor 5 due to the pressure difference is R = R1 −R2 + R3 −R4 = 1/4 × π · (D1 2 −D2 2 ) · ( P2-P1), where D1 = D2, R = 0,
No matter how large the inner diameter φD2 or the pressure difference (P2-P1) of the valve opening 8, if the inner diameter φD2 of the valve opening 8 is designed to be equal to the inner diameter φD1 of the guide portion 59, the pressure equalizing hole 56 and the packing seal function. As a result, the operating resistance force R generated in the rotor 5 due to the pressure difference becomes zero, and a large motor is unnecessary.
【００２９】なお、上述の実施例では、おねじ５２及び
めねじ６０が上側で、シール部５３及びパッキン６１が
下側となる取付関係で説明したが、その取付関係が上下
逆に取り付いても同様な効果が得られることは明白であ
る。In the above embodiment, the male screw 52 and the female screw 60 are on the upper side, and the seal portion 53 and the packing 61 are on the lower side, but the mounting relation is upside down. Obviously, the same effect can be obtained.
【００３０】さらに、上述の実施例では、弁部５５の外
周形状をストレート状として説明したが、図３に示すよ
うに、様々な流量特性（回転子５の回転位置＜ステップ
数＞と流量との関係）の弁を設計するために弁部５５の
外周形状をテーパー面６３を形成させたり、弁部５５の
側面の一部にスリット６４を設けたりするが、この場合
においても同様な効果が得られる。Further, in the above embodiment, the outer peripheral shape of the valve portion 55 is described as a straight shape, but as shown in FIG. 3, various flow rate characteristics (rotational position of rotor 5 <step number> and flow rate) are obtained. In order to design the valve, the outer peripheral shape of the valve portion 55 is formed with a tapered surface 63, or a slit 64 is provided on a part of the side surface of the valve portion 55. In this case, the same effect is obtained. can get.
【００３１】[0031]
【発明の効果】本発明の制御弁は、膨張弁の機能を果た
す電動弁Ａ部と、冷房時と暖房時の冷媒の流路を切り換
える機能を果たす四方弁Ｂ部からなる従来の制御弁にお
いて、回転子５と一体化された弁体５１の外周部にシー
ル部５３を形成するとともに、中心部に均圧孔５６を形
成することにより、回転子５を回転させ上下動させると
きに冷媒の圧力差によって発生する作動抵抗力をなくす
ことを可能とするものである。The control valve of the present invention is a conventional control valve comprising an electrically operated valve A portion which functions as an expansion valve and a four-way valve B portion which functions to switch the flow path of the refrigerant during cooling and heating. By forming the seal portion 53 in the outer peripheral portion of the valve body 51 integrated with the rotor 5 and forming the pressure equalizing hole 56 in the central portion, the refrigerant is prevented when the rotor 5 is rotated and moved up and down. It is possible to eliminate the operation resistance force generated by the pressure difference.
【００３１】したがって、大流量高差圧の冷媒を流量制
御（絞り制御）する場合でも下述のような効果が得られ
る。 大型のモータ（固定子コイル２や回転子５など）は不
要となり、配管スペースに無駄が生じない。 小型モータにより、部品コストを安くできる。 小型モータにより駆動時の消費電力がダウンし、エア
コンの運転コストを安くすることができる。Therefore, even in the case of controlling the flow rate (throttle control) of a refrigerant having a large flow rate and high differential pressure, the following effects can be obtained. A large motor (such as the stator coil 2 and the rotor 5) is unnecessary, and the piping space is not wasted. A small motor can reduce the cost of parts. The small motor reduces the power consumption during driving, and the operating cost of the air conditioner can be reduced.
【図１】 本発明の制御弁の一実施例の暖房状態におけ
る縦断面図。FIG. 1 is a vertical cross-sectional view of an embodiment of a control valve of the present invention in a heating state.
【図２】 本発明の制御弁の電動弁Ａ部拡大縦断面図。FIG. 2 is an enlarged vertical sectional view of a motor-operated valve A portion of the control valve of the present invention.
【図３】 本発明の制御弁の他の実施例の弁口近傍拡大
図で、（Ａ）は弁部形状をテーパー状とした例の拡大
図、（Ｂ）は弁部にスリットを設けた例の拡大図。FIG. 3 is an enlarged view of the vicinity of a valve opening of another embodiment of the control valve of the present invention, (A) is an enlarged view of an example in which the valve portion has a tapered shape, and (B) is a slit provided in the valve portion. An enlarged view of the example.
【図４】 制御弁を用いた冷凍サイクル図であり、実線
矢印は暖房運転時の冷媒の流れを示す。FIG. 4 is a refrigeration cycle diagram using a control valve, and solid arrows indicate the flow of refrigerant during heating operation.
【図５】 従来技術の制御弁の暖房状態における縦断面
図。FIG. 5 is a vertical cross-sectional view of a conventional control valve in a heating state.
【図６】 従来技術の制御弁の弁座と弁体との分解斜視
図で、（Ａ）は弁座の斜視図、（Ｂ）は弁体の斜視図。6A and 6B are exploded perspective views of a valve seat and a valve body of a conventional control valve, FIG. 6A is a perspective view of the valve seat, and FIG. 6B is a perspective view of the valve body.
【図７】 従来技術の制御弁の弁座と弁体とを組み合わ
せた状態における断面図で、（Ａ）は図６のＡ−Ａ断面
図、（Ｂ）は図６のＢ−Ｂ断面図。7A and 7B are cross-sectional views in a state in which a valve seat and a valve body of a control valve of a conventional technology are combined, FIG. 7A being a cross-sectional view taken along the line AA of FIG. 6 and FIG. .
【図８】 従来技術の制御弁の暖房時における弁座と弁
体の位置関係を示す平面図。FIG. 8 is a plan view showing the positional relationship between the valve seat and the valve element during heating of the control valve of the related art.
【図９】 従来技術の制御弁の冷房時における弁座と弁
体の位置関係を示す平面図。FIG. 9 is a plan view showing a positional relationship between a valve seat and a valve body during cooling of a control valve according to a conventional technique.
【図１０】 従来技術の制御弁の遅延連結手段の一部切
欠斜視図。10 is a partially cutaway perspective view of a prior art control valve delay coupling means. FIG.
【図１１】 冷・暖切換時における従来技術の制御弁の
遅延連結手段の作動状態を説明するための平面図であ
り、（Ａ）は暖房時、（Ｂ）〜（Ｃ）は弁口の絞り時、
（Ｄ）は冷房時の状態を示す平面図。FIG. 11 is a plan view for explaining an operating state of the delay coupling means of the conventional control valve at the time of switching between cold and warm, in which (A) is for heating and (B) to (C) are for valve opening. When squeezing
(D) is a plan view showing a state during cooling.
Ａ 電動弁 Ｂ 四方弁 Ｃ
伝達装置 Ｄ 室外側熱交換器 Ｅ 室内側熱交換器 Ｆ
圧縮機 Ｚ 制御弁 Ｒ 作動抵抗力 Ｒ1 、Ｒ2 、Ｒ3 、Ｒ4 力 Ｐ1 、Ｐ2 内圧 φＤ1 、φＤ2 φＤ3 、φ
Ｄ4 内径 １ ケース ２ 固定子コイル ３
針状弁 ４ ねじ軸 ５ 回転子 ６
弁ボディ ７ 推進軸受 ８ 弁口 ９
凸部 １０ 蓋 １１ フランジ部 １３ａ ストッパー片 １３ ストッパー １
４ 上方の突出片 １５ 下方の突出片 １６ 遅延伝達手段 １
７ チャンバー １８ 開口 １９ パイプ ２
０ 開口 ２１ パイプ ２２ 孔 ２
３ 圧縮コイルばね ２４ ボス ２５ 内歯 ２
６ ガイドブッシュ ２７ 鍔 ２８ 連結棒 ２
９ 外歯 ３０ 係合手段 ３１ 弁本体 ３
２ 円筒状のケース ３３ 開口（導入口） ３４ 開口（導出口） ３
５ 開口（通孔） ３６ 開口（通孔） ３７ 弁座 ３
８ 圧縮コイルばね ３９ 弁体 ４０ 導入管 ４
１ 導出管 ４２ 通孔管 ４３ 通孔管 ４
４ 弁体ストッパー ４５ 貫通孔 ４６ 貫通孔 ４
７ 連通孔 ４８ 連通孔 ５１ 弁体 ５２ おねじ ５
３ シール部 ５４ 小径部 ５５ 弁部 ５
６ 均圧孔 ５７ 軸受座部 ５８ パッキン溝 ５
９ ガイド部 ６０ めねじ ６１ パッキン ６
２ チャンバー ６３ テーパー面 ６４ スリットA Motorized valve B Four-way valve C
Transmission device D Outdoor heat exchanger E Indoor heat exchanger F
Compressor Z Control valve R Operating resistance force R1, R2, R3, R4 force P1, P2 Internal pressure φD1, φD2 φD3, φ
D4 Inner diameter 1 Case 2 Stator coil 3
Needle valve 4 Screw shaft 5 Rotor 6
Valve body 7 Propulsion bearing 8 Valve mouth 9
Convex part 10 Lid 11 Flange part 13a Stopper piece 13 Stopper 1
4 Upper protruding piece 15 Lower protruding piece 16 Delay transmission means 1
7 Chamber 18 Opening 19 Pipe 2
0 opening 21 pipe 22 hole 2
3 Compression coil spring 24 Boss 25 Internal tooth 2
6 Guide bush 27 Tsuba 28 Connecting rod 2
9 External Teeth 30 Engaging Means 31 Valve Body 3
2 Cylindrical case 33 Opening (inlet) 34 Opening (outlet) 3
5 Opening (through hole) 36 Opening (through hole) 37 Valve seat 3
8 compression coil spring 39 valve body 40 introduction pipe 4
1 Outlet pipe 42 Through-hole pipe 43 Through-hole pipe 4
4 Valve body stopper 45 Through hole 46 Through hole 4
7 Communication hole 48 Communication hole 51 Valve body 52 Male thread 5
3 Seal part 54 Small diameter part 55 Valve part 5
6 Pressure equalizing hole 57 Bearing seat 58 Packing groove 5
9 Guide part 60 Female thread 61 Packing 6
2 Chamber 63 Tapered surface 64 Slit
Claims (3)
コイル２への通電によるケース１内の回転子５の回転に
より、この回転子５の中心下方に一体的に設けられたお
ねじを介しておねじの下端に設けられた弁部を上下動さ
せ、ケース１の下端に設けた弁ボディ６下部の弁口８の
開度を制御する電動弁Ａ部と、 少なくとも３つの開口を同心円上に設けた金属円板状の
弁座３７を前記ケース１の上端に設け、この弁座３７の
下面を摺動回転して前記３つの開口の少くとも２つを気
密的に連通させ、他の１つの開口は開放状態とする弁体
３９とからなる四方弁Ｂ部と、 前記電動弁Ａ部の回転子５と四方弁Ｂ部の弁体３９との
間に設けた、電動弁Ａ部の弁口８が全開直前の位置と全
閉直前の位置において回転を伝える伝達装置Ｃ部とによ
り構成され、 前記電動弁Ａ部の回転子５の回転力を利用して、電動弁
Ａ部の弁口８の絞り開閉と四方弁Ｂ部の弁体３９の回転
による流路切換とを連動して行なう制御弁において、 前記回転子５の中心部には弁体５１を一体的に設け、該
弁体５１の外周部にはおねじ５２と円筒状のシール部５
３及び弁部５５のを設けると共に中心部に均圧孔５６を
設けて前記ケース１内に形成しているチャンバー６２と
前記弁口８の下に形成している開口２０とを連通させ、 前記弁ボディ６には、中央上部にめねじ６０を有する推
進軸受７を設けると共に、その下方に前記弁体５１のシ
ール部５３を気密シールするパッキン６１を設けたこと
を特徴とする制御弁。1. A male screw integrally provided below the center of the rotor 5 by the rotation of a rotor 5 in the case 1 by energizing a stator coil 2 at the outer peripheral portion of the case 1 made of a non-magnetic material. A valve section provided at the lower end of the screw is moved up and down through an electric valve A section for controlling the opening of the valve opening 8 at the lower part of the valve body 6 provided at the lower end of the case 1, and at least three openings are provided. A metal disc-shaped valve seat 37 provided concentrically is provided at the upper end of the case 1, and the lower surface of the valve seat 37 is slidably rotated to airtightly connect at least two of the three openings, The other one opening is a four-way valve B part including a valve body 39 that is in an open state, and the motor-operated valve A provided between the rotor 5 of the motor-operated valve A part and the valve body 39 of the four-way valve B part. The valve port 8 of the section is constituted by a transmission device C section that transmits rotation at a position immediately before fully opening and a position immediately before fully closing. Using the rotational force of the rotor 5 of the motor-operated valve A, the opening / closing of the valve opening 8 of the motor-operated valve A and the switching of the flow path by the rotation of the valve body 39 of the four-way valve B are performed in conjunction with each other. In the control valve, a valve body 51 is integrally provided at the center of the rotor 5, and a male screw 52 and a cylindrical seal portion 5 are provided on the outer periphery of the valve body 51.
3 and the valve portion 55, and a pressure equalizing hole 56 is provided in the central portion to communicate the chamber 62 formed in the case 1 and the opening 20 formed under the valve opening 8 with each other, The control valve is characterized in that the valve body 6 is provided with a propulsion bearing 7 having an internal thread 60 at the upper center thereof, and a packing 61 for hermetically sealing the seal portion 53 of the valve body 51 is provided below the propulsion bearing 7.
ねじ６０と、弁体５１のシール部５３及び弁ボディ６の
パッキン６１の取付関係が、上下逆に取り付いているこ
とを特徴とする請求項１記載の制御弁。2. The male screw 52 of the valve body 51, the female screw 60 of the propulsion bearing 7, the seal portion 53 of the valve body 51, and the packing 61 of the valve body 6 are attached upside down. The control valve according to claim 1.
周にテーパー面６３を形成させるか、あるいは、弁部５
５の側面の一部にスリット６４を設けたことを特徴とす
る請求項１およびに請求項２記載の制御弁。3. A tapered surface 63 is formed on the outer periphery of a valve portion 55 formed at the lower end of the valve body 51, or the valve portion 5 is formed.
The control valve according to claim 1 or 2, wherein a slit 64 is provided on a part of a side surface of the control valve 5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP26500895A JP3150885B2 (en) | 1995-09-18 | 1995-09-18 | Control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP26500895A JP3150885B2 (en) | 1995-09-18 | 1995-09-18 | Control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0979409A true JPH0979409A (en) | 1997-03-25 |
| JP3150885B2 JP3150885B2 (en) | 2001-03-26 |
Family
ID=17411301
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP26500895A Expired - Fee Related JP3150885B2 (en) | 1995-09-18 | 1995-09-18 | Control valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3150885B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011075016A (en) * | 2009-09-30 | 2011-04-14 | Daikin Industries Ltd | Composite valve and refrigerating device |
| CN103868289A (en) * | 2012-12-11 | 2014-06-18 | 浙江三花股份有限公司 | Electronic expansion valve |
| CN104180567A (en) * | 2013-05-22 | 2014-12-03 | 浙江三花股份有限公司 | Electronic expansion valve |
| US9890869B2 (en) | 2012-12-11 | 2018-02-13 | Zhejiang Sanhua Climate And Appliance Controls Group Co., Ltd | Electronic expansion valve |
| WO2020034423A1 (en) * | 2018-08-17 | 2020-02-20 | 浙江盾安禾田金属有限公司 | Electronic expansion valve |
-
1995
- 1995-09-18 JP JP26500895A patent/JP3150885B2/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011075016A (en) * | 2009-09-30 | 2011-04-14 | Daikin Industries Ltd | Composite valve and refrigerating device |
| CN103868289A (en) * | 2012-12-11 | 2014-06-18 | 浙江三花股份有限公司 | Electronic expansion valve |
| US9890869B2 (en) | 2012-12-11 | 2018-02-13 | Zhejiang Sanhua Climate And Appliance Controls Group Co., Ltd | Electronic expansion valve |
| CN104180567A (en) * | 2013-05-22 | 2014-12-03 | 浙江三花股份有限公司 | Electronic expansion valve |
| CN104180567B (en) * | 2013-05-22 | 2017-08-25 | 浙江三花智能控制股份有限公司 | A kind of electric expansion valve |
| WO2020034423A1 (en) * | 2018-08-17 | 2020-02-20 | 浙江盾安禾田金属有限公司 | Electronic expansion valve |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3150885B2 (en) | 2001-03-26 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP4180786B2 (en) | Electric switching valve and refrigeration cycle apparatus for refrigeration / refrigerator | |
| KR100285613B1 (en) | 4-way selector valve for air conditioners | |
| JPS63134894A (en) | Scroll compressor | |
| JP2002147896A (en) | Motor flow control valve | |
| JPH10281321A (en) | Control valve | |
| JP3150885B2 (en) | Control valve | |
| JPH08247328A (en) | Four way valve used for air conditioner | |
| JP2000320711A (en) | Electric control valve | |
| JPH1030741A (en) | Control valve | |
| JPH08312821A (en) | Sealed type flow rate regulating valve | |
| JP2001343076A (en) | Control valve | |
| JP2711516B2 (en) | Control valve | |
| JP2000310348A (en) | Electric operated selector valve | |
| JP2004125096A (en) | Electrical rotation type channel change valve and freezing cycle device for freezer/refrigerator | |
| JP3136086B2 (en) | Control valve | |
| JP3327670B2 (en) | Fluid compressors and air conditioners | |
| JPH0821556A (en) | Motor-driven flow control valve | |
| JPH0972447A (en) | Control valve | |
| CN113294527A (en) | Electric valve and refrigeration cycle system | |
| JP2000081257A (en) | Flow passage switching device for working medium for cooling and heating device | |
| KR0130152Y1 (en) | Four-way valve for airconditioner refrigerant direction converting | |
| JP2005207574A (en) | Refrigerant flow control valve and air-conditioner | |
| JP2001153491A (en) | Motor operated selector valve and refrigerating cycle equipment | |
| JP2006183802A (en) | Flow passage switching valve, compressor with flow passage switching valve and air conditioner | |
| JPH0132389B2 (en) |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |