JP3413399B2 - Electric flow control valve - Google Patents
Electric flow control valveInfo
- Publication number
- JP3413399B2 JP3413399B2 JP2000297869A JP2000297869A JP3413399B2 JP 3413399 B2 JP3413399 B2 JP 3413399B2 JP 2000297869 A JP2000297869 A JP 2000297869A JP 2000297869 A JP2000297869 A JP 2000297869A JP 3413399 B2 JP3413399 B2 JP 3413399B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- valve body
- seat
- rotor
- refrigerant
- 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.)
- Expired - Fee Related
Links
Landscapes
- Electrically Driven Valve-Operating Means (AREA)
- Sliding Valves (AREA)
- Temperature-Responsive Valves (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、ヒートポンプ式冷
凍サイクルの冷媒通過量を調整し、冷凍サイクルの能力
制御を行う電動流量制御弁の改良に係り、特にいずれの
流れ方向の場合においても、冷媒圧力の上昇によって絞
り弁部が開いてしまうことがなく、圧力が上昇しても確
実な制御ができ、かつ、全閉状態まで流量を制御でき、
駆動手段への通電を止めても弁の開度が変化してしまう
ことのない、消費電力量の小さな電動流量制御弁に関す
るものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in an electric flow control valve that adjusts the amount of refrigerant passing through a heat pump type refrigeration cycle to control the capacity of the refrigeration cycle. The throttle valve will not open due to the increase in pressure, reliable control can be performed even if the pressure rises, and the flow rate can be controlled to the fully closed state.
The present invention relates to an electric flow rate control valve with a small amount of power consumption, which does not change the opening of the valve even when the power supply to the drive means is stopped.
【０００２】[0002]
【従来の技術】従来、ステッピングモータと弁軸と一体
化された弁を組み合せてマイコンにより制御する電動流
量制御弁として、各種のものが考案されている。図１４
は、本願出願人が特願平１１−１８４６９１号にて出願
している従来の制御弁の構造であり、以下にその構成を
説明する。従来の制御弁は、密閉ケース１とシャフト２
とロータ３と弁座シート４と圧縮コイルばね５と固定コ
イル６とにより構成される。2. Description of the Related Art Conventionally, various types of electric flow rate control valves have been devised which are combined with a stepping motor and a valve integrated with a valve shaft and controlled by a microcomputer. 14
Is a structure of a conventional control valve filed by the applicant of the present application in Japanese Patent Application No. 11-184691, the structure of which will be described below. The conventional control valve is a closed case 1 and a shaft 2.
The rotor 3, the valve seat 4, the compression coil spring 5, and the fixed coil 6.
【０００３】前記密閉ケース１は、下方を開口させた逆
有底筒状体に形成され、この密閉ケース１上方内面には
凹状に窪ませたストッパー部 １ｂが設けられると共に
上方中心部には軸受部１ａが設けられている。The sealed case 1 is formed as an inverted bottomed cylindrical body having an opening at the bottom, and a stopper portion 1b recessed in a concave shape is provided on the inner surface of the upper side of the sealed case 1 and a bearing is provided in the upper center portion. The part 1a is provided.
【０００４】シャフト２は、上方部分にケースの軸受部
１ａに嵌め込まれる上軸２ａが形成され、中間部分には
ローター３を支える段２ｂと回転を同期させる回り止め
２ｃが形成され、下部には、弁座シート４と接して流量
を制御する弁体部２ｄが形成され、さらに、弁体部２ｄ
の下面には下軸２ｅが形成されている。なお、前記シャ
フト２は樹脂成形によって成形される。また、前記シャ
フト２は、ロータを嵌着させた後、シャフト２の上下端
をそれぞれケースの軸受部１ａと弁座シートの軸穴４ａ
に嵌着させると共にシャフト２の上軸２ａには、前記の
ロータ３並びに弁体部２ｄを下方に押付けるための圧縮
コイルばね５が嵌め込まれ、このシャフト２の１回転未
満にて弁口４ｂの開度を全閉の段階から制御できるよう
になっている。The shaft 2 has an upper shaft 2a which is fitted in the bearing portion 1a of the case in the upper portion, a step 2b supporting the rotor 3 and a detent 2c for synchronizing rotation in the middle portion, and a lower portion in the lower portion. , A valve body portion 2d for controlling the flow rate is formed in contact with the valve seat 4 and further, the valve body portion 2d
A lower shaft 2e is formed on the lower surface of the. The shaft 2 is molded by resin molding. After the rotor is fitted to the shaft 2, the upper and lower ends of the shaft 2 are respectively attached to the bearing portion 1a of the case and the shaft hole 4a of the valve seat.
The compression coil spring 5 for pressing the rotor 3 and the valve body portion 2d downward is fitted to the upper shaft 2a of the shaft 2 and the valve opening 4b is made in less than one rotation of the shaft 2. The opening degree of can be controlled from the fully closed stage.
【０００５】ロータ３は、前述のごとく前記シャフト２
の中間部分に嵌着されるものであり、このロータ３の内
周面には、回転を同期される内部回り止め３ａが設けら
れ、またロータ３の上方外周縁部には、密閉ケースのス
トッパー１ｂに当たる係止片３ｂが設けられている。The rotor 3 has the shaft 2 as described above.
The rotor 3 is provided with an internal rotation stopper 3a whose rotation is synchronized, and an upper outer peripheral edge of the rotor 3 is provided with a stopper of a closed case. A locking piece 3b that hits 1b is provided.
【０００６】圧縮コイルばね５は、シャフト２の上軸２
ａに嵌め込まれ、前記のロータ３を介してシャフト２を
下方に押付け、弁体部２ｄの底面が弁座シート２に気密
的に圧接されるようになっている。The compression coil spring 5 is composed of the upper shaft 2 of the shaft 2.
The shaft 2 is fitted into the a, and the shaft 2 is pressed downward via the rotor 3 so that the bottom surface of the valve body portion 2d is airtightly pressed against the valve seat seat 2.
【０００７】円板状の弁座シート４は、前記密閉ケース
１下端の開口部に気密的に固定されるものであり、この
弁座シート４は、中心部に軸穴４ａが設けられと共に、
第１の通路４ｃに連通する弁口４ｂ並びに第２の通路４
ｄに連通する連通孔４ｅが設けられている。A disc-shaped valve seat 4 is airtightly fixed to the opening at the lower end of the closed case 1. The valve seat 4 has a shaft hole 4a in the center and
The valve opening 4b communicating with the first passage 4c and the second passage 4
A communication hole 4e communicating with d is provided.
【０００８】前記弁体部２ｄの形状は、図１５に示すよ
うに、弁口４ｂを全面覆うのに十分な半径から弁口４ｅ
を開口するのに十分な半径まで変化させたカム板形状に
形成されている。As shown in FIG. 15, the shape of the valve body 2d is from a radius sufficient to cover the entire surface of the valve opening 4b, and the valve opening 4e is formed.
Is formed into a cam plate shape with a radius sufficient to open the.
【０００９】固定コイル６は、前記密閉ケース１の外周
部に固定されている。なお、この固定コイル６の励磁に
よって、前記ロータの回転に伴ってシャフトが回転し、
下端部の弁本体２ｄの１回転未満にて弁口９の開度が制
御できるようになっている。The fixed coil 6 is fixed to the outer peripheral portion of the closed case 1. By the excitation of the fixed coil 6, the shaft rotates with the rotation of the rotor,
The opening degree of the valve opening 9 can be controlled by less than one rotation of the valve body 2d at the lower end.
【００１０】また、図示しないが、弁部の断面形状は渦
巻状に形成してあり、この電動式コントロールバルブの
流量特性は、図１６に示すように、弁部の断面形状を変
化させることにより、弁体部２ｄの回転角度が０゜〜約
２７０゜の範囲で流量を制御できる。つまり、弁体の１
回転未満にて弁口の開度を全閉の段階から制御するよう
にしたものであるから、弁口の開度を全閉の段階から制
御できる。Although not shown, the cross section of the valve section is formed in a spiral shape, and the flow rate characteristic of this electric control valve can be changed by changing the cross section of the valve section as shown in FIG. The flow rate can be controlled within the range of 0 ° to about 270 ° in the rotation angle of the valve body 2d. That is, 1 of the valve body
Since the opening of the valve opening is controlled from the fully closed stage when the rotation is less than the rotation, the opening of the valve opening can be controlled from the fully closed stage.
【００１１】図１７は、特開平８−３１２８２２号公報
に開示された従来の電動流量制御弁の構造であり、以下
にその構成を説明する。図１７に示す電動式コントロー
ルバルブは、バルブ部Ｖと、ステッピングモーター部Ｍ
により構成される。前記バルブ部Ｖは、弁本体１１、軸
部１３、並びに永久磁石２１及びスペーサ２２からなる
ロータ１９で構成される。前記弁本体１１には１次口１
１ａと２次口１１ｂが形成され、これら１次口１１ａと
２次口１１ｂより冷媒等の流体が流入または流出する。
また、弁本体１１は軸部１３をガイドする機能も有し、
垂直方向に当該軸部１３に対するガイド部１１ｇが設け
られる。FIG. 17 shows the structure of a conventional electric flow control valve disclosed in Japanese Patent Application Laid-Open No. 8-32822. The structure will be described below. The electric control valve shown in FIG. 17 has a valve section V and a stepping motor section M.
It is composed of The valve portion V includes a valve body 11, a shaft portion 13, and a rotor 19 including a permanent magnet 21 and a spacer 22. The valve body 11 has a primary port 1
1a and a secondary port 11b are formed, and a fluid such as a refrigerant flows in or out through the primary port 11a and the secondary port 11b.
The valve body 11 also has a function of guiding the shaft portion 13,
A guide portion 11g for the shaft portion 13 is provided in the vertical direction.
【００１２】軸部１３の下部先端には弁部１３ａが形成
されている。この弁部１３ａの断面形状は軸方向に一定
でる。また、弁本体１１の１次口１１ａの上部で、軸部
１３の弁部１３ａが収容されている空間は弁室２０を構
成し、弁室２０の下部は１次口１１ａに通じるととも
に、弁室２０と２次口１１ｂは弁ポート部１１ｃを介し
て連通している。A valve portion 13a is formed at the lower end of the shaft portion 13. The sectional shape of the valve portion 13a is constant in the axial direction. In addition, the space above the primary opening 11a of the valve body 11 in which the valve portion 13a of the shaft portion 13 is housed constitutes the valve chamber 20, and the lower part of the valve chamber 20 leads to the primary opening 11a and The chamber 20 and the secondary port 11b communicate with each other via the valve port portion 11c.
【００１３】軸部１３とロータ１９は一体となって回転
子部３０を構成し、この一体化された回転子部３０が弁
本体１１の上端面１１ｄ上に載置される。尚、１１は永
久磁石、１２はスペーサである。The shaft portion 13 and the rotor 19 are integrated to form a rotor portion 30, and the integrated rotor portion 30 is placed on the upper end surface 11d of the valve body 11. In addition, 11 is a permanent magnet and 12 is a spacer.
【００１４】弁本体１１の外周中央部には段部１１ｅが
形成され、この段部１１ｅ上に下蓋１５がろう付けによ
り固定される。さらに、下蓋１５上にステッピングモー
タ部Ｍの密閉型ケース１６が固定される。また、ケース
１６の外周部には、コイル１７を内蔵したステータ１８
が設けられるとともに、ケース１６内には、軸部１３と
ロータ１９が一体化された回転子部３０が弁本体１１上
に回動自在に設けられる。また、ロータ１９の下部には
段部２２ａが形成され、この段部２２ａがロータ１９に
一体化されたストッパーとして機能する。一方、下蓋１
５には突起１５ａが設けられ、この突起１５ａが下蓋１
５に一体的に設けられた本体側のストッパーとして機能
する。A step portion 11e is formed at the center of the outer periphery of the valve body 11, and the lower lid 15 is fixed to the step portion 11e by brazing. Further, the sealed case 16 of the stepping motor unit M is fixed on the lower lid 15. Further, a stator 18 having a coil 17 built-in is provided on the outer peripheral portion of the case 16.
In addition, a rotor portion 30 in which the shaft portion 13 and the rotor 19 are integrated is rotatably provided on the valve body 11 in the case 16. A step portion 22a is formed in the lower portion of the rotor 19, and the step portion 22a functions as a stopper integrated with the rotor 19. On the other hand, the lower lid 1
5 is provided with a protrusion 15a, and this protrusion 15a is attached to the lower lid 1.
5 functions as a stopper on the main body side that is integrally provided.
【００１５】上記構成において、ステータ１８のコイル
１７に通電すると、永久磁石２１が回転し、永久磁石２
１の回転に応じて軸部１３も回転する。軸部１３が回転
すると、軸部１３の回転角度に応じて弁部１３ａの弁ポ
ート部１ｃに対する角度が変化し、弁ポート部１ｃと、
該弁ポート部１ｃと相対向する該弁部３ａの周面とで形
成される隙間が、該弁部１３ａの前記軸部１３の軸線に
垂直な断面形状に従って、該ロータ１９の回転により変
化するため、冷媒等の流体の流量を制御することができ
る。In the above structure, when the coil 17 of the stator 18 is energized, the permanent magnet 21 rotates and the permanent magnet 2
The shaft portion 13 also rotates in response to the rotation of 1. When the shaft portion 13 rotates, the angle of the valve portion 13a with respect to the valve port portion 1c changes according to the rotation angle of the shaft portion 13, and the valve port portion 1c and
A gap formed between the valve port portion 1c and the peripheral surface of the valve portion 3a facing each other is changed by the rotation of the rotor 19 according to a sectional shape perpendicular to the axis of the shaft portion 13 of the valve portion 13a. Therefore, the flow rate of the fluid such as the refrigerant can be controlled.
【００１６】[0016]
【発明が解決しようとする課題】しかし、図１４に示す
前者の制御弁においては、圧縮コイルばねによって弁体
を弁座シートに押し付けることにより弁体と弁座シート
を密着させて絞り弁機構部を構成しており、ヒートポン
プ式冷凍サイクルの冷暖房の切り替えによる冷媒の流れ
方向の違いによっては、冷媒の圧力が高圧になった場
合、圧縮コイルばねの付勢力不足により弁体が弁座シー
トから離接して開弁してしまうという問題がある。ま
た、高圧の条件においても開弁してしまうことなく安定
的に制御するためには、圧縮コイルばねの付勢力を十分
に大きくしなければならず、それは弁体が回転摺動する
際の摩擦力を増大することとなり、大きな摩擦力に抗し
て回転摺動させるためには、固定コイルおよびロータを
大型化せねばならず、コストアップと大きな電気入力を
必要とし省エネに反するという問題があった。However, in the former control valve shown in FIG. 14, the valve body is pressed against the valve seat seat by the compression coil spring to bring the valve body and the valve seat seat into close contact with each other and the throttle valve mechanism portion. When the pressure of the refrigerant becomes high due to the difference in the flow direction of the refrigerant due to the switching of cooling and heating of the heat pump type refrigeration cycle, the valve element separates from the valve seat seat due to insufficient biasing force of the compression coil spring. There is a problem of opening the valve in contact. Further, in order to stably control the valve without opening it even under a high pressure condition, the urging force of the compression coil spring must be sufficiently large, which is due to friction when the valve body rotates and slides. Since the force is increased, the fixed coil and the rotor must be upsized in order to rotate and slide against a large frictional force, which raises the cost and requires a large electric input, which is a problem against energy saving. It was
【００１７】また、図１７に示す後者の電動式コントロ
ールバルブにおいては、流量を制御する方法が弁ポート
部と相対向する弁部の周面とで形成される隙間を、弁部
の軸線に垂直な断面形状によって制御している為弁口を
全閉にできず、図１８に示す通り、最小流量がゼロとな
らず、かなりの冷媒が常時流れるといった問題があっ
た。つまり、全閉させる為に、弁ポートと弁部を軸線と
垂直方向に密着させなければならないが、それぞれがＲ
面の為密着させるのは構造上非常に困難である。このこ
とは、マルチエアコンでは停止号機に冷媒が流れ冷媒音
や冷媒が不足するといった問題がでる。又、ルームエア
コンでは除湿時に非常に少ない流量を必要とするが、こ
れが大きいと最適な除湿が出来ないという問題がある。In the latter electric control valve shown in FIG. 17, the method of controlling the flow rate is such that the gap formed between the valve port portion and the peripheral surface of the valve portion facing each other is perpendicular to the axis of the valve portion. Since it is controlled by such a cross-sectional shape, the valve port cannot be fully closed, and as shown in FIG. 18, the minimum flow rate does not become zero, and a considerable amount of refrigerant constantly flows. In other words, in order to fully close it, the valve port and valve part must be in close contact with each other in the direction perpendicular to the axis, but
Since it is a surface, it is structurally very difficult to bring them into close contact. This causes a problem that in the multi-air conditioner, the refrigerant flows to the stop unit and the refrigerant noise or the refrigerant is insufficient. Further, the room air conditioner requires a very small flow rate during dehumidification, but if it is large, there is a problem that optimum dehumidification cannot be performed.
【００１８】加えて、流体の流れる方向が弁部の軸線に
対して垂直に流れ、その隙間に沿って流体が流れること
により、流体によって軸部を回転させる力が発生し、永
久磁石の磁力による保持トルクのみでは軸部が回転して
しまうため、制御時最適な位置に停止後コイルに常時通
電してローターが回転しない様にする必要があった。そ
の時当然電気入力が必要となり省エネに反するという問
題もあった。In addition, the flow direction of the fluid flows perpendicularly to the axis of the valve portion, and the fluid flows along the gap, so that a force for rotating the shaft portion is generated by the fluid, and a magnetic force of the permanent magnet is generated. Since only the holding torque causes the shaft to rotate, it is necessary to energize the coil after stopping to an optimum position during control so that the rotor does not rotate. At that time, of course, there was a problem that an electric input was required, which was against energy saving.
【００１９】[0019]
【課題を解決するための手段】本発明は、筒状ケースの
上部と下部にそれぞれ、弁座と弁体からなる異なった流
量特性を得ることが可能な上流側の絞り弁部と下流側の
絞り弁部を構成させ、ロータの上部と下部には、それぞ
れ決められた範囲内にてロータと一体的に回動できる上
弁体及び下弁体を設け、前記の一方の弁体が冷媒の圧力
によって前記絞り弁部の弁座に当接する時には、他方の
弁体が弁座から離接するごとく設けることにより、冷媒
の上流側の絞り弁部は駆動手段の位置に関係なく全開状
態となり下流側の絞り弁部のみを絞り弁として機能さ
せ、冷媒の流れ方向により自動的に２箇所の絞り弁機構
を使い分け、いずれの流れ方向の場合においても、冷媒
圧力の上昇によって下流側の絞り弁部が開いてしまうこ
とがなく、圧力が上昇しても確実な制御ができる電動流
量制御弁の提供を目的とするものである。SUMMARY OF THE INVENTION According to the present invention, an upstream throttle valve section and a downstream throttle valve section capable of obtaining different flow rate characteristics composed of a valve seat and a valve body are provided at an upper portion and a lower portion of a cylindrical case, respectively. A throttle valve unit is configured, and an upper valve body and a lower valve body that can rotate integrally with the rotor within a predetermined range are provided at the upper and lower portions of the rotor, and one of the valve bodies is a refrigerant When abutting against the valve seat of the throttle valve portion due to pressure, the other valve element is provided so as to separate from and contact the valve seat, so that the throttle valve portion on the upstream side of the refrigerant is fully opened regardless of the position of the driving means and the downstream side. Only the throttle valve section of No. 2 functions as a throttle valve, and two throttle valve mechanisms are automatically used properly according to the flow direction of the refrigerant. In any of the flow directions, the throttle valve section on the downstream side is increased by the increase of the refrigerant pressure. It does not open and the pressure is high It is an object to provide an electric flow control valve can be reliably controlled.
【００２０】すなわち、請求項１記載の電動流量制御弁
は、非磁性体の筒状ケース３１の外周に配置した固定コ
イル３８と内部に配置したロータ３４とにより前記ロー
タ３４と一体的に回動する上弁体３５及び下弁体３６を
ステッピングモーター等の駆動手段によって可逆的に作
動させ、該弁体の回動により２つの絞り弁部の何れかの
開度を制御することにより、ヒートポンプ式冷凍サイク
ルの冷媒通過量を調整し、冷凍サイクルの能力制御を行
う電動流量制御弁であって、前記の筒状ケース３１の上
端部と下端部にそれぞれ上弁座シート３２と下弁座シー
ト３３を設けると共に円筒状のロータ３４の上部と下部
にはロータの端部に離接し且つ一体的に回動可能な上弁
体３５と下弁体３６を設け、前記の上弁体３５と上弁座
シート３２により上流側の絞り弁部４１を構成させ、ま
た下弁体３６と下弁座シート３３により下流側の絞り弁
部４２を構成させ、ヒートポンプ式冷凍サイクルの冷暖
房の切り替えによる冷媒の流れ方向の違いにより、上流
側絞り弁部４１の上弁体３５が上弁座シート３２から離
れると共に下流側の絞り弁部４２の下弁体３６が下弁座
シート３３に当接することにより、上流側の絞り弁部は
駆動手段の位置に関係なく全開状態となり、下流側の絞
り弁部のみを絞り弁として機能させ、冷媒の流れ方向に
より自動的に２箇所の絞り弁機構を使い分け、いずれの
流れ方向の場合においても、冷媒圧力の上昇によって絞
り弁部が開いてしまうことがなく、圧力が上昇しても確
実な制御ができることを特徴とするものである。That is, the electric flow control valve according to the first aspect of the invention is integrally rotated with the rotor 34 by the fixed coil 38 arranged on the outer periphery of the cylindrical case 31 made of a non-magnetic material and the rotor 34 arranged inside. The upper valve body 35 and the lower valve body 36 to be operated are reversibly operated by a driving means such as a stepping motor, and the opening degree of either of the two throttle valve portions is controlled by the rotation of the valve body. An electric flow control valve for adjusting the amount of refrigerant passing through the refrigeration cycle to control the capacity of the refrigeration cycle, wherein an upper valve seat 32 and a lower valve seat 33 are provided at the upper end and the lower end of the cylindrical case 31, respectively. And an upper valve body 35 and a lower valve body 36, which are separated from and in contact with the end of the rotor and are rotatable integrally with each other, are provided on the upper and lower portions of the cylindrical rotor 34. By seat 32 The throttle valve portion 41 on the flow side is configured, and the throttle valve portion 42 on the downstream side is configured by the lower valve body 36 and the lower valve seat seat 33. Due to the difference in the flow direction of the refrigerant due to switching between cooling and heating of the heat pump type refrigeration cycle. , The upstream valve body 35 of the upstream side throttle valve portion 41 is separated from the upper valve seat seat 32, and the lower valve body 36 of the downstream side throttle valve portion 42 abuts the lower valve seat sheet 33, so that the upstream side throttle valve The part is fully opened regardless of the position of the driving means, only the downstream side throttle valve portion functions as a throttle valve, and two throttle valve mechanisms are automatically used properly according to the flow direction of the refrigerant, and in any flow direction Also in the above, the throttle valve portion does not open due to the increase of the refrigerant pressure, and the reliable control can be performed even if the pressure increases.
【００２１】また、請求項２記載の電動流量制御弁は、
前記の上弁体３５並びにに下弁体３６形成される絞り制
御用の溝３５ｄ・３６ｄは、それぞれ溝の形状が異な
り、冷媒の流れ方向の違いによって流量特性が異なるよ
うにしたことを特徴とする請求項１に記載のものであ
る。The electric flow control valve according to claim 2 is
The throttle control grooves 35d and 36d formed in the upper valve body 35 and the lower valve body 36 have different shapes, and the flow rate characteristics are different depending on the flow direction of the refrigerant. According to claim 1,
【００２２】また、請求項３記載の電動流量制御弁は、
前記の上弁体３５及び下弁体３６の外周面にピストンリ
ング４４を設け、前記筒状ケース３１の内周面と上弁体
３５、下弁体３６及び前記ロータ３４の外周面との隙間
に冷媒が流れることを防止したことを特徴とする請求項
１及び請求項２に記載のものである。The electric flow control valve according to claim 3 is
A piston ring 44 is provided on the outer peripheral surfaces of the upper valve body 35 and the lower valve body 36, and a gap between the inner peripheral surface of the cylindrical case 31 and the outer peripheral surfaces of the upper valve body 35, the lower valve body 36 and the rotor 34. The refrigerant according to claim 1 or 2, wherein the refrigerant is prevented from flowing.
【００２３】また、請求項４記載の電動流量制御弁は、
前記の上弁体３５及び下弁体３６が、上弁座シート３２
及び下弁座シート３３の軸穴３２ａ、３３ａに支持され
るシャフト３７に遊嵌状に嵌着されたことを特徴とする
請求項１、請求項２及び請求項３に記載のものである。The electric flow control valve according to claim 4 is
The upper valve body 35 and the lower valve body 36 are the same as the upper valve seat seat 32.
And a shaft 37 supported by the shaft holes 32a, 33a of the lower valve seat 33, and the shaft 37 is loosely fitted to the shaft 37.
【００２４】また、請求項５記載の電動流量制御弁は、
上弁座シート３２及び下弁座シート３３の摺動面で且つ
シャフト３７を中心として弁口３２ｂ・３３ｂとは対極
する位置に、弁口３２ｂ・３３ｂの周りを含めて複数箇
所に弁座シート面より突出させた円板状の当たり面３２
ｃを各々の弁座シートと一体的に設けると共に、前記の
上弁体３５及び下弁体３６の壁面にはそれぞれ連通孔３
５ｇ・３６ｇを設けたことを特徴とする請求項１、請求
項２、請求項３、及び請求項４に記載のものである。The electric flow control valve according to claim 5 is:
At the sliding surface of the upper valve seat 32 and the lower valve seat 33 and at a position opposite to the valve openings 32b and 33b with the shaft 37 as the center, the valve seat seats are provided at a plurality of positions including around the valve openings 32b and 33b. Disc-shaped contact surface 32 protruding from the surface
c is provided integrally with each valve seat, and communication holes 3 are formed in the wall surfaces of the upper valve body 35 and the lower valve body 36, respectively.
5g * 36g is provided, Claim 1, Claim 2, Claim 3, and Claim 4 are characterized by the above-mentioned.
【００２５】また、請求項６記載の電動流量制御弁は、
前記の上弁座シート３２並びに下弁座シート３３に設け
られた弁口３２ｂ・ ３３ｂの周りには、フッ素系樹脂
材等の高滑性樹脂による弁座キャップ４３を配設したこ
とを特徴とする請求項１、請求項２、請求項３、請求項
４及び請求項５に記載のものである。The electric flow control valve according to claim 6 is:
A valve seat cap 43 made of a highly slippery resin such as a fluororesin is disposed around the valve openings 32b and 33b provided in the upper valve seat seat 32 and the lower valve seat seat 33, respectively. According to claim 1, claim 2, claim 3, claim 4 and claim 5.
【００２６】さらに、請求項７記載の電動流量制御弁
は、前記の上弁体３５及び下弁体３６の間に圧縮コイル
ばね４５を配設したことを特徴とする請求項１、請求項
２、請求項３、請求項４、及び請求項４、請求項５及び
請求項６に記載のものである。Further, in the electric flow control valve according to claim 7, a compression coil spring 45 is disposed between the upper valve body 35 and the lower valve body 36. , Claim 3, claim 4, and claim 4, claim 5, and claim 6.
【００２７】[0027]
【発明の実施の形態】以下、本発明の一実施例を図面に
基づき詳細に説明する。図１は本発明の電動膨張弁の縦
断面図を示し、図２は図１のＡ−Ａ断面図、図３は図１
のＢ−Ｂ断面図、図４は図１のＣ−Ｃ断面図、図５は図
１のＤ−Ｄ断面図の全開状態、図６は図１のＤ−Ｄ断面
図の中間状態、図７は図１のＤ−Ｄ断面図の全閉状態を
示し，図８は本発明の電動膨張弁の流れ方向が逆転した
場合の縦断面図を示すものである。BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the present invention will be described in detail below with reference to the drawings. 1 is a vertical sectional view of an electric expansion valve of the present invention, FIG. 2 is a sectional view taken along the line AA of FIG. 1, and FIG.
4 is a sectional view taken along the line BB, FIG. 4 is a sectional view taken along the line CC of FIG. 1, FIG. 5 is a fully opened state of the sectional view taken along the line DD of FIG. 1, and FIG. 6 is an intermediate state of the sectional view taken along the line DD of FIG. 7 shows a fully closed state of the DD sectional view of FIG. 1, and FIG. 8 shows a vertical sectional view when the flow direction of the electric expansion valve of the present invention is reversed.
【００２８】本発明の電動流量制御弁は筒状ケース３１
と該筒状ケース３１の両端部に気密的に固定される上弁
座シート３２及び下弁座シート３３と円筒状のロータ３
４と該ロータと係合して回動する上弁体３５及び下弁体
３６とシャフト３７と固定コイル３８により構成され
る。The electric flow control valve of the present invention has a cylindrical case 31.
And an upper valve seat 32 and a lower valve seat 33 which are airtightly fixed to both ends of the cylindrical case 31, and the cylindrical rotor 3
4, an upper valve body 35 and a lower valve body 36 that rotate by engaging with the rotor, a shaft 37, and a fixed coil 38.
【００２９】筒状ケース３１は、非磁性金属による両端
面を開口させた円筒形状である。The cylindrical case 31 has a cylindrical shape with both end surfaces made of nonmagnetic metal.
【００３０】上弁座シート３２及び下弁座シート３３は
円板状であり、その中心部にはそれぞれ軸穴３２ａ、３
３ａが設けられるとともに、中心から少し離れた位置に
それぞれ弁口３２ｂ、３３ｂが設けられている。また、
弁体の回転を安定化させるためには必要に応じて、図１
０に示す如く、上弁座シート３２及び下弁座シート３３
の摺動面で且つシャフト３７を中心として弁口３２ｂ・
３３ｂとは対極する位置に、弁口３２ｂ・３３ｂの周り
を含めて複数箇所に弁座シート面より突出させた円板状
の当たり面３２ｃを各々の弁座シートと一体的に設ける
とよい。また、弁座シートの弁口３２ｂ及び３３ｂには
流入出管３９ａ及び３９ｂが気密的に固定されている。The upper valve seat seat 32 and the lower valve seat seat 33 are disc-shaped, and their central portions have shaft holes 32a and 3a, respectively.
3a is provided, and valve openings 32b and 33b are provided at positions slightly apart from the center. Also,
In order to stabilize the rotation of the valve body, as shown in FIG.
0, the upper valve seat seat 32 and the lower valve seat seat 33
Of the valve opening 32b
Disc-shaped abutting surfaces 32c protruding from the valve seat seat surface at a plurality of positions including the periphery of the valve openings 32b and 33b may be provided integrally with each valve seat at a position opposite to 33b. Further, inflow / outflow pipes 39a and 39b are airtightly fixed to the valve openings 32b and 33b of the valve seat.
【００３１】また、上弁座シート３２及び下弁座シート
３３は前記筒状ケース３１の両端部に気密的に固定され
ており、前記の下弁座シート３３にはストッパー４０が
固定されているが、このストッパー４０は、下弁座シー
ト３３に変えて上弁座シート３２側に設けてよいのは言
うまでもない。Further, the upper valve seat seat 32 and the lower valve seat seat 33 are airtightly fixed to both ends of the tubular case 31, and the stopper 40 is fixed to the lower valve seat seat 33. However, needless to say, the stopper 40 may be provided on the upper valve seat 32 side instead of the lower valve seat 33.
【００３２】また、前記の上弁体３５及び下弁体３６の
外周面にはピストンリング４４が設けられており、該ピ
ストンリング４４によって、前記筒状ケース３１の内周
面と上弁体３５、下弁体３６及び前記ロータ３４の外周
面との隙間に冷媒が流れることを防止できるようになっ
ている。つまり、図１に示すごとく冷媒が流入出管３９
ａ→上弁座シート３２の弁口３２ｂ→上弁体３５の連通
孔３５ｂ→ロータ３４の内部→下弁体３６の連通孔３６
ｂ→下弁座シート３３の弁口３３ｂ→流入出管３９ｂへ
と流れる際、冷媒がローター３４の外部を流れないよう
にすることができ、冷媒中に磁性のある異物等が含まれ
ていても、ローター外周部に異物が堆積して回転を阻害
することがなく、信頼性の高い電動流量制御弁を提供す
ることができる。A piston ring 44 is provided on the outer peripheral surfaces of the upper valve body 35 and the lower valve body 36, and the inner peripheral surface of the cylindrical case 31 and the upper valve body 35 are provided by the piston ring 44. It is possible to prevent the refrigerant from flowing into the gap between the lower valve body 36 and the outer peripheral surface of the rotor 34. That is, as shown in FIG.
a → valve opening 32b of the upper valve seat 32 → communication hole 35b of the upper valve body 35 → inside of the rotor 34 → communication hole 36 of the lower valve body 36
b → the valve opening 33b of the lower valve seat 33 → the inflow / outflow pipe 39b, it is possible to prevent the refrigerant from flowing outside the rotor 34, and the refrigerant contains magnetic foreign matter or the like. Also, it is possible to provide a highly reliable electric flow control valve without foreign matter accumulating on the outer peripheral portion of the rotor to hinder rotation.
【００３３】さらに、前述した上弁座シート３２及び下
弁座シート３３の摺動面に、弁口３２ｂ・３３ｂの周り
を含めて複数箇所に円板状の当たり面３２ｃを設けた場
合には、前記の上弁体３５及び下弁体３６の壁面にはそ
れぞれ連通孔３５ｇ・３６ｇが設けられる。なお、この
連通孔３５ｇ・３６ｇを設ける意味は次の通りである。
例えば、図１に示す冷媒の流れの場合においては、下弁
体３６の連通孔３６ｂが当り面３２ｃと接触している状
態においては、冷媒の流れはその当接部において絞ら
れ、下弁体３６の上部と下部には圧力差が発生し、その
圧力差は、下弁体３６全体の大きさに加わることとなっ
て弁体を押し付ける力が大となり、弁体がスムーズに回
転しなくなる。しかし、連通孔３５ｇ・３６ｇがある
と、下弁体３６の上部と下部の圧力差がバランスして弁
体を押し付ける力が小となり、弁体がスムーズに回転で
きるようになる。Further, in the case where the sliding surfaces of the upper valve seat seat 32 and the lower valve seat seat 33 described above are provided with the disk-shaped contact surfaces 32c at a plurality of positions including around the valve openings 32b and 33b, Communication holes 35g and 36g are provided on the wall surfaces of the upper valve body 35 and the lower valve body 36, respectively. The meaning of providing the communication holes 35g and 36g is as follows.
For example, in the case of the flow of the refrigerant shown in FIG. 1, when the communication hole 36b of the lower valve body 36 is in contact with the contact surface 32c, the flow of the refrigerant is throttled at the contact portion, and the lower valve body A pressure difference is generated between the upper part and the lower part of 36, and the pressure difference is added to the entire size of the lower valve body 36, so that the force pressing the valve body is large and the valve body does not rotate smoothly. However, if the communication holes 35g and 36g are provided, the pressure difference between the upper portion and the lower portion of the lower valve body 36 is balanced and the force pressing the valve body is small, so that the valve body can rotate smoothly.
【００３４】円筒状のロータ３４は、その上端部と下端
部には切り欠き部３４ａ、３４ｂ（図２及び図３を参
照）が設けられており、この切り欠き部３４ａ、３４ｂ
は、後述する上弁体３５及び下弁体３６の突出部３５
ｃ、３６ｃと係合するようになっている。The cylindrical rotor 34 is provided with notches 34a, 34b (see FIGS. 2 and 3) at its upper and lower ends, and the notches 34a, 34b are provided.
Is a protruding portion 35 of an upper valve body 35 and a lower valve body 36, which will be described later.
It is adapted to engage with c and 36c.
【００３５】上弁体３５及び下弁体３６は円柱形状であ
り、その中心部には軸孔３５ａ、３６ａが設けられ、ま
た、上弁体３５及び下弁体３６のロータ３４側は、該ロ
ータの内径と嵌合できるように段付形状とするととも
に、図２及び図３に示すように前記ロータの切り欠き部
３４ａ、３４ｂと対応する突出部３５ｃ、３６ｃが設け
られている。The upper valve body 35 and the lower valve body 36 have a cylindrical shape, and shaft holes 35a and 36a are provided in the center thereof, and the rotor 34 side of the upper valve body 35 and the lower valve body 36 is It has a stepped shape so that it can be fitted into the inner diameter of the rotor, and as shown in FIGS. 2 and 3, projections 35c and 36c corresponding to the notches 34a and 34b of the rotor are provided.
【００３６】また、上弁体３５及び下弁体３６は、上下
の弁座シートの弁口３２ｂ、３３ｂに対応する位置に、
図４図、５及び図１１に示すように回転方向に伴い断面
積が徐変する溝３５ｄ、３６ｄが設けられており、この
溝の断面積が最大となる位置３５ｅ、３６ｅには連通孔
３５ｂ、３６ｂが設けられ、図１に示すごとく、冷媒が
流入出管３９ｂ→下弁座シート３３の弁口３３ｂ→下弁
体３６の連通孔３６ｂ→ロータ３４の内部→上弁体３５
の連通孔３５ｂ→上弁座シート３２の弁口３２ｂ→流入
出管３９ａへと流れるようになっている。The upper valve body 35 and the lower valve body 36 are located at positions corresponding to the valve openings 32b and 33b of the upper and lower valve seats, respectively.
As shown in FIGS. 4, 5 and 11, grooves 35d and 36d whose cross-sectional areas gradually change with the rotation direction are provided, and communication holes 35b are provided at positions 35e and 36e where the cross-sectional areas of these grooves are maximum. , 36b are provided, and as shown in FIG. 1, the refrigerant flows in / out pipe 39b → valve port 33b of the lower valve seat 33 → communication hole 36b of the lower valve body 36 → inside the rotor 34 → upper valve body 35.
The communication hole 35b → the valve opening 32b of the upper valve seat 32 → the inflow / outflow pipe 39a.
【００３７】また、図５に示すように、下弁体３６に
は、前述した下弁座シートのストッパー４０に対応させ
て係止片３６ｆが設けられており、この係止片３６ｆが
ストッパー４０に当接することにより、ロータ３４と上
弁体及び下弁体が回転する際の回転端位置を規制するよ
うになっている。Further, as shown in FIG. 5, the lower valve body 36 is provided with a locking piece 36f corresponding to the stopper 40 of the above-mentioned lower valve seat, and this locking piece 36f is provided with the stopper 40f. When the rotor 34 and the upper valve body and the lower valve body rotate, the rotation end position of the rotor 34 is regulated.
【００３８】また、本発明は、上述した電動流量制御弁
の構成において、上弁体３５と上弁座シート３２により
上流側の絞り弁部４１を構成させ、また下弁体３６と下
弁座シート３３により下流側の絞り弁部４２を構成させ
ている。なお、前記の絞り制御部において、上弁体３５
と下弁体３６に形成される絞り制御用の溝３５ｄ・３６
ｄの形状を異なったものとすることにより、冷媒の流れ
方向の違いによって流量特性を異なったものにすること
ができる。Further, according to the present invention, in the structure of the electric flow control valve described above, the upstream valve body 35 and the upper valve seat seat 32 constitute the upstream throttle valve portion 41, and the lower valve body 36 and the lower valve seat. The seat 33 constitutes the throttle valve portion 42 on the downstream side. In the throttle control unit, the upper valve body 35
And grooves 35d and 36 for controlling the throttle formed in the lower valve body 36
By making the shape of d different, the flow rate characteristics can be made different depending on the difference in the flow direction of the refrigerant.
【００３９】シャフト３７は、ロータ３４と上弁体３５
及び下弁体３６の回転軸であり、シャフト３７の両端部
がそれぞれ上弁座シート３２及び下弁座シート３３の軸
穴３２ａ、３３ａに軸支されるとともに、上弁体及び下
弁体の軸孔３５ａ、３６ａを貫通するようになってい
る。なお、前記のシャフト３７は必ずしも必要とするも
のでなく、必要に応じて適宜選択すればよい。The shaft 37 includes a rotor 34 and an upper valve body 35.
And the rotation axis of the lower valve body 36, and both ends of the shaft 37 are axially supported by the shaft holes 32a and 33a of the upper valve seat seat 32 and the lower valve seat seat 33, respectively. The shaft holes 35a and 36a are penetrated. The shaft 37 is not always necessary and may be appropriately selected as needed.
【００４０】図８は、図１の電動流量制御弁に対して、
ヒートポンプ式冷凍サイクルの冷暖房の切り替えにより
冷媒の流れ方向が逆転した場合の状態を示す図であり、
この状態ではロータ３４と上弁体３５は上方の上弁座シ
ート３２に押し付けられていが、図１の状態と同じ作用
効果を奏するのは言うまでもない。FIG. 8 shows the electric flow control valve of FIG.
It is a diagram showing a state when the flow direction of the refrigerant is reversed by switching the heating and cooling of the heat pump type refrigeration cycle,
In this state, the rotor 34 and the upper valve body 35 are pressed against the upper upper valve seat seat 32, but it goes without saying that the same operational effect as the state of FIG. 1 is exerted.
【００４１】また、上述の施例においては、上弁体３５
及び下弁体３６がロータ３４とは別部品で構成されてい
るが、これらを一体的に形成しても同じ作用効果が得ら
れるのは言うまでもない。In the above embodiment, the upper valve body 35
The lower valve element 36 and the lower valve element 36 are formed as separate parts from the rotor 34, but it goes without saying that the same effect can be obtained by integrally forming them.
【００４２】[0042]
【他の実施例】図１２は、本発明の電動流量制御弁にお
ける弁口部分に弁座キャップ４３及び圧縮コイルばね４
５を取付けた状態を示す部分縦断面図である。この実施
例においては、図１に示した実施例との相違点のみを以
下に説明する。[Other Embodiments] FIG. 12 shows a valve seat cap 43 and a compression coil spring 4 at the valve opening portion of the electric flow control valve of the present invention.
5 is a partial vertical cross-sectional view showing a state in which 5 is attached. FIG. In this embodiment, only the differences from the embodiment shown in FIG. 1 will be described below.
【００４３】弁座キャップ４３は、フッ素系樹脂材等の
高滑性樹脂により成形されたものであり、図１３に示す
ように、該弁座キャップ４３は、上弁座シート３２に設
けられた弁口３２ｂ並びに下弁座シート３３に設けられ
た弁口３３ｂの周りに、弁座キャップ押さえ４６を介し
て上弁座シート３２並びに下弁座シート３３にスポット
溶接等によって固定されている。この弁座キャップ４３
によって、上下の弁体３５、３６が小さなトルクでも回
転できるようになっている。The valve seat cap 43 is formed of a highly slippery resin such as a fluorine resin material. As shown in FIG. 13, the valve seat cap 43 is provided on the upper valve seat 32. It is fixed to the upper valve seat 32 and the lower valve seat 33 by spot welding or the like around the valve opening 32b and the valve opening 33b provided in the lower valve seat 33 via a valve seat cap retainer 46. This valve seat cap 43
Thus, the upper and lower valve bodies 35, 36 can rotate even with a small torque.
【００４４】また、ストッパー４０が弁座キャップ押え
４６に設けられている。A stopper 40 is provided on the valve seat cap retainer 46.
【００４５】圧縮コイルばね４５は、前記の上弁体３５
及び下弁体３６の間に配設されており、圧縮コイルばね
４５が上弁体３５と下弁体３６との間に配設されること
により、上弁体３５及び下弁体３６はそれぞれ上弁座シ
ート３２及び下弁座シート３３に押しつけるように付勢
されているため、冷媒が流れていない時でも弁体が回転
してしまうことがない、操作の容易な電動流量制御弁を
提供することができる。The compression coil spring 45 is the upper valve body 35.
And the lower valve body 36, and the compression coil spring 45 is disposed between the upper valve body 35 and the lower valve body 36, so that the upper valve body 35 and the lower valve body 36 respectively Since the valve body is biased so as to be pressed against the upper valve seat seat 32 and the lower valve seat seat 33, the valve body does not rotate even when the refrigerant does not flow, and an electric flow control valve that is easy to operate is provided. can do.
【００４６】次に、図１及び図１２に示す本発明の電動
流量制御弁の作動について説明する。図５〜図７は、図
１のＤ−Ｄ断面に相当し、電動流量制御弁の全開（図
５），中間（図６），全閉（図７）と弁開度が変化する
様子を示す。それぞれの図は、下弁体３５と下弁座シー
ト３３の弁口３３ｂとの位置関係を示すものである。下
弁体３６の連通口３６ｂから流入する冷媒は、弁体の回
転に伴い断面積が徐変する溝３６ｄを通って下弁座シー
ト３３の弁口３３ｂに流入するものであるが、冷媒の流
量は下弁座シート３３の弁口３３ｂと当接している位置
における、溝３６ｄの断面積の大きさにより絞られるよ
うになっている。つまり、ロータ３４の回転によって回
転する下弁体３６の回転位置により冷媒通過量を調整
し、冷凍サイクルの能力制御を行うことができる。Next, the operation of the electric flow control valve of the present invention shown in FIGS. 1 and 12 will be described. FIGS. 5 to 7 correspond to the D-D cross section of FIG. 1, and show how the valve opening changes when the electric flow control valve is fully opened (FIG. 5), intermediate (FIG. 6), and fully closed (FIG. 7). Show. Each drawing shows the positional relationship between the lower valve body 35 and the valve opening 33b of the lower valve seat seat 33. The refrigerant flowing from the communication port 36b of the lower valve body 36 flows into the valve port 33b of the lower valve seat 33 through the groove 36d whose cross-sectional area gradually changes as the valve body rotates. The flow rate is restricted by the size of the cross-sectional area of the groove 36d at the position in contact with the valve opening 33b of the lower valve seat 33. That is, the refrigerant passage amount can be adjusted by the rotational position of the lower valve body 36 rotated by the rotation of the rotor 34, and the refrigeration cycle capacity control can be performed.
【００４７】上述のごとく構成された本発明の電動流量
制御弁は、ヒートポンプ式冷凍サイクルの冷暖房の切り
替えによる冷媒の流れ方向の違いにより、上流側の絞り
弁部４１の上弁体３５が上弁座シート３２面から離れる
ことにより上流側の絞り弁部４１は駆動手段の位置に関
係なく全開状態となり下流側の絞り弁部４２のみが絞り
弁として機能するため、冷媒の流れ方向により自動的に
２箇所の絞り弁機構を使い分け、いずれの流れ方向の場
合においても、冷媒圧力の上昇によって絞り弁部が開い
てしまうことがなく、圧力が上昇しても確実な制御がで
きる。In the electric flow rate control valve of the present invention constructed as described above, the upper valve body 35 of the upstream side throttle valve portion 41 is the upper valve due to the difference in the flow direction of the refrigerant due to the switching of cooling and heating of the heat pump type refrigeration cycle. By separating from the seat seat 32 surface, the upstream side throttle valve portion 41 is fully opened regardless of the position of the driving means, and only the downstream side throttle valve portion 42 functions as a throttle valve, so that it automatically changes depending on the flow direction of the refrigerant. Two throttle valve mechanisms are used properly, and in any flow direction, the throttle valve portion does not open due to the increase in the refrigerant pressure, and reliable control can be performed even if the pressure increases.
【００４８】また、下流側となる絞り弁部４２の下弁体
３６は、ロータ３４と係合して回転すると共に冷媒の流
れにより回転軸に対して垂直面に設けた弁座に押付けら
れ、下弁体３６の１回転未満にて弁口の開度を全閉の段
階から制御できるため、図９の流量特性図に示す如く、
最小流量をゼロとすることができる。Further, the lower valve body 36 of the throttle valve portion 42 on the downstream side is engaged with the rotor 34 to rotate, and is pressed against a valve seat provided on a surface vertical to the rotation axis by the flow of the refrigerant, Since the opening of the valve opening can be controlled from the fully closed stage with the lower valve body 36 less than one rotation, as shown in the flow rate characteristic diagram of FIG.
The minimum flow rate can be zero.
【００４９】さらに、冷媒の流れによる圧力差によって
下流側の下弁体３６が下弁座シート３３に押し付けられ
ることによって前記の下弁体３６をその位置に保持する
摩擦力が働くため、弁体を回転させない力はロータ３４
の磁力による保持トルクと積算され、弁体を回転位置制
御して最適な位置に停止させた後にコイルへの通電を止
めても弁体が回転してしまうことがないようにしてあ
る。Further, since the lower valve body 36 on the downstream side is pressed against the lower valve seat seat 33 by the pressure difference due to the flow of the refrigerant, a frictional force for holding the lower valve body 36 at that position works, so that the valve body The force that does not rotate the rotor is
The holding torque due to the magnetic force of (1) is integrated so that the valve body will not rotate even if the energization of the coil is stopped after controlling the rotational position of the valve body to stop it at the optimum position.
【００５０】[0050]
【発明の効果】以上のように、請求項１に記載の発明に
おいては、冷媒の流れ方向により自動的に２箇所の絞り
弁機構を使い分け、いずれの流れ方向の場合において
も、冷媒圧力の上昇によって絞り弁部が開いてしまうこ
とがなく、圧力が上昇しても確実な制御ができる。As described above, according to the first aspect of the invention, two throttle valve mechanisms are automatically used according to the flow direction of the refrigerant, and the refrigerant pressure rises in either direction. As a result, the throttle valve portion does not open, and reliable control can be performed even if the pressure rises.
【００５１】また、２箇所に設けられた弁体のうち下流
側に位置する弁体を冷媒の流れにより回転軸に対して垂
直面に設けた弁座面に押付け、回転摺動して弁口の開度
を調整して流量を制御することにより、弁体の１回転未
満にて弁口の開度を全閉の段階から制御して、最小流量
をゼロとすることができるため、マルチエアコンやルー
ムエアコンにおいて最適な制御ができる。Of the valve elements provided at the two positions, the valve element located on the downstream side is pressed by the flow of the refrigerant against the valve seat surface provided on the surface vertical to the rotation axis, and rotationally slides to open the valve opening. By controlling the flow rate by adjusting the opening degree of the valve body, the opening degree of the valve opening can be controlled from the fully closed stage in less than one rotation of the valve body, and the minimum flow rate can be set to zero. Optimal control is possible for room air conditioners.
【００５２】また、冷媒の流れによる圧力差によって下
流側の弁体が弁座シート面に押し付けられることによ
り、弁体を回転位置制御して最適な位置に停止させた後
にコイルへの通電を止めても弁体が回転してしまうこと
がなく、消費電力量を低減することができる。Further, since the valve element on the downstream side is pressed against the valve seat seat surface by the pressure difference due to the flow of the refrigerant, the valve element is stopped in the optimum position by controlling the rotational position of the valve element and then energizing the coil is stopped. However, the valve body does not rotate, and the power consumption can be reduced.
【００５３】また、請求項２に記載の発明においては、
上弁体３５と下弁体３６に形成される絞り制御用の溝３
５ｄ・３６ｄの形状を異なったものとすることにより、
例えば暖房運転と冷房運転では流量特性を異なったもの
にすることができ、きめの細かい空調制御が行なえる。Further, in the invention described in claim 2,
Groove 3 for throttle control formed in the upper valve body 35 and the lower valve body 36
By making the shapes of 5d and 36d different,
For example, the heating operation and the cooling operation can have different flow rate characteristics, and fine air conditioning control can be performed.
【００５４】また、請求項３に記載の発明によれば、上
弁体３５及び下弁体３６の外周部には、ピストンリング
４４がそれぞれ配設されているため、図１に示すごとく
冷媒が流入出管３９ａ→上弁座シート３２の弁口３２ｂ
→上弁体３５の連通孔３５ｂ→ロータ３４の内部→下弁
体３６の連通孔３６ｂ→下弁座シート３３の弁口３３ｂ
→流入出管３９ｂへと流れる際、冷媒がローター３４の
外部を流れないようにすることができ、冷媒中に磁性の
ある異物等が含まれていても、ローター外周部に異物が
堆積して回転を阻害することがなく、信頼性の高い電動
流量制御弁を提供することができる。Further, according to the invention described in claim 3, since the piston rings 44 are arranged on the outer peripheral portions of the upper valve body 35 and the lower valve body 36, respectively, the refrigerant as shown in FIG. Inlet / outlet pipe 39a → valve port 32b of the upper valve seat 32
→ Communication hole 35b of the upper valve body 35 → Inside of the rotor 34 → Communication hole 36b of the lower valve body 36 → Valve port 33b of the lower valve seat 33
→ When the refrigerant flows to the inflow / outflow pipe 39b, the refrigerant can be prevented from flowing outside the rotor 34, and even if the refrigerant contains magnetic foreign matters, the foreign matters are accumulated on the outer peripheral portion of the rotor. It is possible to provide a highly reliable electric flow control valve that does not hinder rotation.
【００５５】また、請求項４に記載の発明によれば、上
弁体３５及び下弁体３６がシャフト３７によって支持さ
れているため、回転作動が安定し信頼性の高い電動流量
制御弁を提供することができる。Further, according to the invention described in claim 4, since the upper valve body 35 and the lower valve body 36 are supported by the shaft 37, an electric flow rate control valve having stable rotation operation and high reliability is provided. can do.
【００５６】また、請求項５に記載の発明によれば、弁
口３２ｂ・３３ｂとは対極する位置の複数箇所に円板状
の当たり面３２ｃを設けると共に上弁体３５及び下弁体
３６の壁面にはそれぞれ連通孔３５ｇ・３６ｇを設けた
ものであるから、下弁体３６の連通孔３６ｂが当り面３
２ｃと接触している状態においても弁体をスムーズに回
転させることができる。According to the fifth aspect of the invention, disk-shaped contact surfaces 32c are provided at a plurality of positions opposite to the valve openings 32b and 33b, and the upper valve body 35 and the lower valve body 36 are provided. Since the communication holes 35g and 36g are provided on the wall surface, respectively, the communication hole 36b of the lower valve body 36 contacts the contact surface 3
The valve body can be smoothly rotated even in the state of being in contact with 2c.
【００５７】また、請求項６に記載の発明によれば、弁
口３２ｂ及び３３ｂの周りにはフッ素系樹脂材等の高滑
性樹脂による弁座キャップ４３が固定されているため、
弁体は小さなトルクでも回転できるようなり、駆動手段
を小型化し、安価な電動流量制御弁を提供することがで
きる。According to the sixth aspect of the invention, the valve seat cap 43 made of a highly slippery resin such as a fluororesin is fixed around the valve openings 32b and 33b.
The valve body can be rotated even with a small torque, the drive means can be downsized, and an inexpensive electric flow control valve can be provided.
【００５８】さらに、請求項７に記載の発明によれば、
圧縮コイルばね４５が上弁体３５と下弁体３６との間に
配設されることにより、上弁体３５及び下弁体３６はそ
れぞれ上弁座シート３２及び下弁座シート３３に押しつ
けるように付勢されているため、冷媒が流れていない時
でも弁体が回転してしまうことがない、操作の容易な電
動流量制御弁を提供することができる。Further, according to the invention of claim 7,
Since the compression coil spring 45 is disposed between the upper valve body 35 and the lower valve body 36, the upper valve body 35 and the lower valve body 36 press the upper valve seat seat 32 and the lower valve seat seat 33, respectively. Since the valve body is biased to, the valve body does not rotate even when the refrigerant does not flow, and it is possible to provide an electric flow control valve that is easy to operate.
【図１】 本発明の実施例を示す縦断面図。FIG. 1 is a vertical sectional view showing an embodiment of the present invention.
【図２】 図１のＡ−Ａ断面図。2 is a sectional view taken along line AA of FIG.
【図３】 図１のＢ−Ｂ断面図。3 is a sectional view taken along line BB of FIG.
【図４】 図１のＣ−Ｃ断面図。FIG. 4 is a sectional view taken along line CC of FIG.
【図５】 図１のＤ−Ｄ断面図（全開状態）。5 is a cross-sectional view taken along the line DD of FIG. 1 (fully opened state).
【図６】 図１のＤ−Ｄ断面図（中間状態）。6 is a cross-sectional view taken along line DD of FIG. 1 (intermediate state).
【図７】 図１のＤ−Ｄ断面図（全閉状態）。7 is a cross-sectional view taken along line DD of FIG. 1 (fully closed state).
【図８】 図１に対し冷媒の流れ方向が逆転した場合の
図。FIG. 8 is a diagram when the flow direction of the refrigerant is reversed with respect to FIG.
【図９】 本発明に係る電動流量制御弁の流量特性図。FIG. 9 is a flow rate characteristic diagram of the electric flow control valve according to the present invention.
【図１０】 本発明の下弁座シートの斜視図。FIG. 10 is a perspective view of the lower valve seat of the present invention.
【図１１】 本発明の下弁体の斜視図。FIG. 11 is a perspective view of a lower valve body of the present invention.
【図１２】 本発明の他の実施例を示す縦断面図。FIG. 12 is a vertical sectional view showing another embodiment of the present invention.
【図１３】 弁口部分に弁座キャップ４３を取付ける状
態を示す分解斜視図。FIG. 13 is an exploded perspective view showing a state in which a valve seat cap 43 is attached to a valve opening portion.
【図１４】 従来の電動流量制御弁の縦断面図。FIG. 14 is a vertical sectional view of a conventional electric flow control valve.
【図１５】 図１４のＢ−Ｂ断面図。15 is a cross-sectional view taken along the line BB of FIG.
【図１６】 図１４に示す電動流量制御弁の流量特性
図。16 is a flow rate characteristic diagram of the electric flow rate control valve shown in FIG.
【図１７】 従来の他の電動流量制御弁の縦断面図。FIG. 17 is a vertical cross-sectional view of another conventional electric flow control valve.
【図１８】 図１７に示す電動流量制御弁の流量特性
図。FIG. 18 is a flow characteristic diagram of the electric flow control valve shown in FIG.
３１ 筒状ケース、 ３２ 上弁座シー
ト、３３ 下弁座シート、 ３２ａ、３３
ａ 軸穴、３２ｂ、３３ｂ 弁口、 ３２
ｃ、３３ｃ 当り面、３４ ロータ、
３４ａ、３４ｂ 切り欠き部、３５ 上弁体、
３６ 下弁体、３５ａ、３６ａ 軸
孔、 ３５ｂ、３６ｂ 連通孔、３５ｃ、３
６ｃ 突出部、 ３５ｄ、３６ｄ 溝、３５
ｅ、３６ｅ 溝の断面積が最大となる位置、３６ｆ 係
止片、 ３７ シャフト、３８ 固
定コイル、 ３９ａ、３９ｂ 流入出管、
４０ ストッパー、 ４１ 上流側の絞
り弁部、４２ 下流側の絞り弁部。 ４３ 弁
座キャップ
４４ ピストンリング ４５ 圧縮コイル
ばね
４６ 弁座キャップ押さえ31 cylindrical case, 32 upper valve seat seat, 33 lower valve seat seat, 32a, 33
a shaft hole, 32b, 33b valve opening, 32
c, 33c contact surface, 34 rotor,
34a, 34b Notch, 35 Upper valve body,
36 lower valve body, 35a, 36a shaft hole, 35b, 36b communication hole, 35c, 3
6c Projection part, 35d, 36d Groove, 35
e, 36e Position where groove cross-sectional area is maximum, 36f Locking piece, 37 Shaft, 38 Fixed coil, 39a, 39b Inlet / outlet pipe,
40 stopper, 41 upstream throttle valve section, 42 downstream throttle valve section 43 valve seat cap 44 piston ring 45 compression coil spring 46 valve seat cap retainer
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ // Ｆ２５Ｂ 13/00 ３７１ Ｆ２５Ｂ 13/00 ３７１ (58)調査した分野(Int.Cl.7，ＤＢ名) F25B 41/04 F16K 3/06 F16K 3/08 F06K 31/04 F16K 31/68 F25B 13/00 371 F25B 41/06 ─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. 7 identification code FI // F25B 13/00 371 F25B 13/00 371 (58) Fields investigated (Int.Cl. 7 , DB name) F25B 41/04 F16K 3/06 F16K 3/08 F06K 31/04 F16K 31/68 F25B 13/00 371 F25B 41/06
Claims (7)
置した固定コイル（３８）と内部に配置したロータ（３
４）とにより前記ロータ（３４）と一体的に回動する上
弁体（３５）及び下弁体（３６）をステッピングモータ
ー等の駆動手段によって可逆的に作動させ、該弁体の回
動により２つの絞り弁部の何れかの開度を制御すること
により、ヒートポンプ式冷凍サイクルの冷媒通過量を調
整し、冷凍サイクルの能力制御を行う電動流量制御弁で
あって、 前記の筒状ケース（３１）の上端部と下端部にそれぞれ
上弁座シート（３２）と下弁座シート（３３）を設ける
と共に円筒状のロータ（３）の上部と下部にはロータの
端部に離接し且つ一体的に回動可能な上弁体３５と下弁
体（３６）を設け、前記の上弁体３５と上弁座シート
（３２）により上流側の絞り弁部（４１）を構成させ、
また下弁体（３６）と下弁座シート（３３）により下流
側の絞り弁部（４２）を構成させ、 ヒートポンプ式冷凍サイクルの冷暖房の切り替えによる
冷媒の流れ方向の違いにより、上流側絞り弁部（４１）
の上弁体（３５）が上弁座シート（３２）から離れると
共に下流側の絞り弁部（４２）の下弁体（３６）が下弁
座シート（３３）に当接することにより、上流側の絞り
弁部は駆動手段の位置に関係なく全開状態となり、下流
側の絞り弁部のみを絞り弁として機能させ、冷媒の流れ
方向により自動的に２箇所の絞り弁機構を使い分け、い
ずれの流れ方向の場合においても、冷媒圧力の上昇によ
って下流側の絞り弁部が開いてしまうことがなく、圧力
が上昇しても確実な制御ができることを特徴とする電動
流量制御弁。1. A fixed coil (38) arranged on the outer periphery of a non-magnetic cylindrical case (31) and a rotor (3) arranged inside.
4) causes the upper valve body (35) and the lower valve body (36) that rotate integrally with the rotor (34) to be reversibly operated by a driving means such as a stepping motor, and the valve body rotates. An electric flow rate control valve for adjusting the refrigerant passage amount of a heat pump type refrigeration cycle to control the capacity of the refrigeration cycle by controlling the opening of one of the two throttle valve sections, the tubular case ( An upper valve seat (32) and a lower valve seat (33) are provided at the upper end and the lower end of (31), respectively, and the upper and lower parts of the cylindrical rotor (3) are separated from and in contact with the end of the rotor and integrated. Provided with a vertically rotatable upper valve body 35 and a lower valve body (36), and the upstream valve body 35 and the upper valve seat seat (32) constitute an upstream throttle valve portion (41),
The lower valve body (36) and the lower valve seat (33) constitute a downstream throttle valve section (42). Due to the difference in the flow direction of the refrigerant due to the switching of cooling and heating of the heat pump type refrigeration cycle, the upstream throttle valve (42) Division (41)
The upper valve body (35) separates from the upper valve seat seat (32), and the lower valve body (36) of the downstream throttle valve portion (42) abuts the lower valve seat seat (33). The throttle valve section is fully opened regardless of the position of the driving means, only the downstream throttle valve section functions as a throttle valve, and two throttle valve mechanisms are automatically used according to the flow direction of the refrigerant, whichever flow Even in the case of the directional control, the electric flow control valve is characterized in that the throttle valve unit on the downstream side does not open due to the increase of the refrigerant pressure, and the reliable control can be performed even if the pressure increases.
６）形成される絞り制御用の溝（３５ｄ）・（３６ｄ）
は、それぞれ溝の形状が異なり、冷媒の流れ方向の違い
によって流量特性が異なるようにしたことを特徴とする
請求項１に記載の電動流量制御弁。2. The upper valve body (35) and the lower valve body (3)
6) Formed throttle control grooves (35d) and (36d)
The electric flow control valve according to claim 1, wherein the groove has a different shape, and the flow rate characteristics are different depending on the flow direction of the refrigerant.
の外周面にピストンリング（４４）を設け、前記筒状ケ
ース（３１）の内周面と上弁体（３５）、下弁体（３
６）及び前記ロータ（３４）の外周面との隙間に冷媒が
流れることを防止したことを特徴とする請求項１及び請
求項２に記載の電動流量制御弁。3. The upper valve body (35) and the lower valve body (36).
A piston ring (44) is provided on the outer peripheral surface of the cylindrical case (31), the upper valve body (35) and the lower valve body (3).
6) The electric flow control valve according to claim 1 or 2, wherein the refrigerant is prevented from flowing into a gap between the rotor and the outer peripheral surface of the rotor (34).
が、上弁座シート（３２）及び下弁座シート（３３）の
軸穴（３２ａ）、（３３ａ）に支持されるシャフト（３
７）に遊嵌状に嵌着されたことを特徴とする請求項１、
請求項２及び請求項３に記載の電動流量制御弁。4. The upper valve body (35) and the lower valve body (36).
Is supported by the shaft holes (32a), (33a) of the upper valve seat seat (32) and the lower valve seat seat (33).
7. It is loosely fitted in 7).
The electric flow control valve according to claim 2 or 3.
（３３）の摺動面で且つシャフト３７を中心として弁口
(３２ｂ)・(３３ｂ)とは対極する位置に、弁口(３２ｂ)
・(３３ｂ)の周りを含めて複数箇所に弁座シート面より
突出させた円板状の当たり面（３２ｃ）を各々の弁座シ
ートと一体的に設けると共に、前記の上弁体（３５）及
び下弁体（３６）の壁面にはそれぞれ連通孔（３５ｇ）
・（３６ｇ）を設けたことを特徴とする請求項１、請求
項２、請求項３、及び請求項４に記載の電動流量制御
弁。5. A valve opening on the sliding surface of the upper valve seat seat (32) and the lower valve seat seat (33) and centered on the shaft 37.
At the position opposite to (32b) and (33b), the valve port (32b)
· Disc-shaped contact surfaces (32c) protruding from the valve seat seat surface are provided integrally with each valve seat at a plurality of locations including around (33b), and the upper valve body (35) is also provided. And a communication hole (35g) on the wall surface of the lower valve body (36), respectively.
-(36g) was provided, The electric flow control valve of Claim 1, Claim 2, Claim 3, and Claim 4 characterized by the above-mentioned.
シート（３３）に設けられた弁口(３２ｂ)・ (３３ｂ)
の周りには、フッ素系樹脂材等の高滑性樹脂による弁座
キャップ（４３）を配設したことを特徴とする請求項
１、請求項２、請求項３、請求項４及び請求項５に記載
の電動流量制御弁。6. Valve openings (32b), (33b) provided in the upper valve seat seat (32) and the lower valve seat seat (33).
A valve seat cap (43) made of a highly slippery resin such as a fluororesin is provided around the valve seat, claim 1, claim 2, claim 3, claim 4, and claim 5. The electric flow control valve described in.
の間に圧縮コイルばね（４５）を配設したことを特徴と
する請求項１、請求項２、請求項３、請求項４、及び請
求項４、請求項５及び請求項６に記載の電動流量制御
弁。7. The upper valve body (35) and the lower valve body (36).
An electric motor according to claim 1, claim 2, claim 3, claim 4, claim 4, claim 5 or claim 6, characterized in that a compression coil spring (45) is disposed between the two. Flow control valve.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000297869A JP3413399B2 (en) | 2000-06-26 | 2000-09-29 | Electric flow control valve |
| CN 00136878 CN1214199C (en) | 2000-06-26 | 2000-12-29 | Electric flow control valve |
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000190762 | 2000-06-26 | ||
| JP2000258287 | 2000-08-29 | ||
| JP2000-190762 | 2000-08-29 | ||
| JP2000-258287 | 2000-08-29 | ||
| JP2000297869A JP3413399B2 (en) | 2000-06-26 | 2000-09-29 | Electric flow control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2002147896A JP2002147896A (en) | 2002-05-22 |
| JP3413399B2 true JP3413399B2 (en) | 2003-06-03 |
Family
ID=27343843
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000297869A Expired - Fee Related JP3413399B2 (en) | 2000-06-26 | 2000-09-29 | Electric flow control valve |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3413399B2 (en) |
| CN (1) | CN1214199C (en) |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002295694A (en) * | 2001-03-29 | 2002-10-09 | Fuji Koki Corp | Motor-operated valve |
| JP2004263725A (en) | 2003-02-14 | 2004-09-24 | Saginomiya Seisakusho Inc | Electrically driven control valve |
| JP2004293732A (en) * | 2003-03-28 | 2004-10-21 | Pacific Ind Co Ltd | Control valve |
| FI116580B (en) * | 2004-07-23 | 2005-12-30 | Kytoelae Instrumenttitehdas | flow controller |
| JP2006038193A (en) * | 2004-07-30 | 2006-02-09 | Saginomiya Seisakusho Inc | Electric control valve |
| ITPD20050312A1 (en) * | 2005-10-20 | 2007-04-21 | Carel Spa | PERFECT VALVE STRUCTURE FOR FLUID FLOW RATE ADJUSTMENT IN PARTICULAR REFRIGERATORS |
| JP2012047327A (en) * | 2010-08-30 | 2012-03-08 | Rinnai Corp | Flow rate adjusting device |
| CN103353194B (en) * | 2013-07-01 | 2016-06-08 | 新奥科技发展有限公司 | A kind of refrigeration plant controls system and control method |
| CN104879515A (en) * | 2014-02-28 | 2015-09-02 | 北京谊安医疗***股份有限公司 | Flow control valve and respirator provided with same |
| CN107327614A (en) * | 2017-09-03 | 2017-11-07 | 江苏中科机械有限公司 | Rotate self-cleaning fluted disc switching valve |
| CN110005854A (en) * | 2018-01-04 | 2019-07-12 | 浙江三花智能控制股份有限公司 | Valve gear |
| CN110005832A (en) * | 2018-01-04 | 2019-07-12 | 浙江三花智能控制股份有限公司 | Valve gear |
| CN110005833A (en) * | 2018-01-04 | 2019-07-12 | 浙江三花智能控制股份有限公司 | Valve gear |
| JP6737380B1 (en) * | 2019-06-11 | 2020-08-05 | 株式会社デンソー | Valve device |
| JP7099421B2 (en) * | 2019-09-10 | 2022-07-12 | 株式会社デンソー | Valve device, fluid circulation circuit |
| JP7392619B2 (en) * | 2020-09-29 | 2023-12-06 | 株式会社デンソー | valve device |
| CN114688754A (en) * | 2020-12-31 | 2022-07-01 | 浙江三花智能控制股份有限公司 | Refrigerating system and electrically operated valve |
-
2000
- 2000-09-29 JP JP2000297869A patent/JP3413399B2/en not_active Expired - Fee Related
- 2000-12-29 CN CN 00136878 patent/CN1214199C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN1331393A (en) | 2002-01-16 |
| JP2002147896A (en) | 2002-05-22 |
| CN1214199C (en) | 2005-08-10 |
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