JP7499587B2 - Motor-operated valve and refrigeration cycle system - Google Patents

Motor-operated valve and refrigeration cycle system Download PDF

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JP7499587B2
JP7499587B2 JP2020047604A JP2020047604A JP7499587B2 JP 7499587 B2 JP7499587 B2 JP 7499587B2 JP 2020047604 A JP2020047604 A JP 2020047604A JP 2020047604 A JP2020047604 A JP 2020047604A JP 7499587 B2 JP7499587 B2 JP 7499587B2
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rolling bearing
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剛 竹田
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Saginomiya Seisakusho Inc
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Description

本発明は、冷凍サイクルシステムなどに使用する電動弁及び冷凍サイクルシステムに関する。 The present invention relates to an electrically operated valve for use in a refrigeration cycle system and a refrigeration cycle system.

従来、ステッピングモータなどの回転駆動部によってロータ軸などの回転軸を回転駆動し、この回転軸の回転運動をねじ送り機構によって直線運動に変換し、弁を開閉する電動弁が利用されている（例えば、特許文献１，２等を参照）。この種の電動弁では、弁体の供回りと、弁体の弁座部への過度の押付けと、を抑制して、弁の着座による耐久性を向上させるために、弁体とねじ送り機構との間に、軸受と、弁ばねと、が内蔵された弁ホルダが設けられている。このような弁ホルダに内蔵される軸受には、転がり軸受と、滑り軸受の２種類があるが、転がり軸受の方が、回転負荷が小さく、回転駆動部の必要な出力が小さくて済む高効率な電動弁となる。 Conventionally, motorized valves have been used in which a rotary shaft such as a rotor shaft is rotated by a rotary drive unit such as a stepping motor, and the rotary motion of the rotary shaft is converted to linear motion by a screw feed mechanism to open and close the valve (see, for example, Patent Documents 1 and 2). In this type of motorized valve, a valve holder incorporating a bearing and a valve spring is provided between the valve body and the screw feed mechanism to suppress the co-rotation of the valve body and excessive pressing of the valve body against the valve seat and to improve durability due to the seating of the valve. There are two types of bearings that are incorporated in such valve holders: rolling bearings and sliding bearings. Rolling bearings have a smaller rotation load and require less output from the rotary drive unit, resulting in a highly efficient motorized valve.

特許第６４７２６３７号公報Patent No. 6472637 中国実用新案登録第２０８５１９２８４号公報China Utility Model Registration No. 208519284

しかしながら、特許文献１，２に開示されたような従来の電動弁にあっては、弁漏れを低減させるために、弁体と弁座とが同軸上に位置した状態で着座させる必要があるが、部品製造時における部品の寸法公差、組立時における組立公差などに起因する寸法誤差のばらつきにより、図１１に示すように、弁体９５と弁座９６（弁ポート９７）の芯ずれが生じて弁漏れの可能性を排除することが困難であるという問題があった。すなわち、特許文献１の構造では、図１１に示すように、弁軸９１の先端とバネ受け９２とは、弁ばね９３の荷重を受けて互いに当接しており、さらに弁ばね９３の下端は、弁ガイド９４に固着された弁体９５と直接当接しているので、弁体９５が着座した時に弁体９５の軸心Ｌ´と弁座部９６の弁ポート９７の軸心Ｌとのずれを補正しにくく、弁漏れが生じやすい。また、特許文献２の構造では、転がり軸受がねじ軸と弁体の収容溝との間に、径方向のわずかな隙間で収容され、径方向の自由度が殆ど無いため、弁体の軸心を弁座の軸心に合わせるように補正することができないため、弁漏れが生じやすい。 However, in conventional motor-operated valves such as those disclosed in Patent Documents 1 and 2, in order to reduce valve leakage, the valve body and the valve seat must be seated coaxially, but due to variations in dimensional errors caused by dimensional tolerances of parts during part manufacturing and assembly tolerances during assembly, the valve body 95 and the valve seat 96 (valve port 97) may be misaligned as shown in Fig. 11, making it difficult to eliminate the possibility of valve leakage. That is, in the structure of Patent Document 1, as shown in Fig. 11, the tip of the valve shaft 91 and the spring receiver 92 abut against each other under the load of the valve spring 93, and the lower end of the valve spring 93 abuts directly against the valve body 95 fixed to the valve guide 94. Therefore, when the valve body 95 is seated, it is difficult to correct the misalignment between the axis L' of the valve body 95 and the axis L of the valve port 97 of the valve seat portion 96, and valve leakage is likely to occur. Furthermore, in the structure of Patent Document 2, the rolling bearing is accommodated between the screw shaft and the accommodation groove of the valve disc with a small radial gap, and since there is almost no radial freedom, it is not possible to correct the axis of the valve disc to align with the axis of the valve seat, which makes the valve prone to leakage.

本発明の目的は、高効率化を図りつつ、弁漏れを抑制することができる電動弁及び冷凍サイクルシステムを提供することである。 The object of the present invention is to provide an electric valve and a refrigeration cycle system that can suppress valve leakage while achieving high efficiency.

本発明の電動弁は、弁室及び弁座部を構成する弁本体と、前記弁座部と軸線方向で接離して弁ポートの開度を変更する弁体と、回転軸を進退駆動させる駆動部と、前記弁体と前記回転軸とに亘る弁ホルダと、弁閉方向に弁体を付勢する弁ばねと、を備えた電動弁であって、前記弁体及び前記回転軸の少なくとも一方は、前記弁ホルダに回転自在に挿通される軸部を有し、前記軸部と前記弁ホルダとの間に転がり軸受を備え、前記転がり軸受と、前記軸部及び前記弁ホルダの少なくとも一方と、の間には、径方向の隙間が設けられており、前記軸部と前記弁ホルダとは、前記径方向に相対変位可能に接続され、前記転がり軸受は、前記軸部及び前記弁ホルダの少なくとも一方に対し、前記軸線方向に移動可能な隙間を介して設けられていることを特徴とする。 The electric valve of the present invention is an electric valve comprising a valve body constituting a valve chamber and a valve seat portion, a valve body that moves axially toward and away from the valve seat portion to change the opening degree of the valve port, a drive portion that drives a rotating shaft back and forth, a valve holder that spans the valve body and the rotating shaft, and a valve spring that biases the valve body in a valve closing direction, wherein at least one of the valve body and the rotating shaft has a shaft portion that is rotatably inserted into the valve holder, a rolling bearing is provided between the shaft portion and the valve holder, a radial gap is provided between the rolling bearing and at least one of the shaft portion and the valve holder, the shaft portion and the valve holder are connected so as to be able to displace relative to each other in the radial direction , and the rolling bearing is provided relative to at least one of the shaft portion and the valve holder via a gap that is movable in the axial direction .

このような本発明によれば、弁体又は回転軸の軸部と弁ホルダとを相対回転可能に接続する軸受に転がり軸受を用いるので、高効率とすることができる。さらに、転がり軸受と、軸部及び弁ホルダの少なくとも一方と、の間には、径方向の隙間が設けられており、軸部と弁ホルダとは、径方向に相対変位可能に接続されているので、弁体が弁座部に着座する際、軸部と弁ホルダとは隙間の範囲内だけ径方向に相対変位し、弁座部に対して同軸上に弁体を着座させることができ、弁漏れを低減させることができる。 According to the present invention, a rolling bearing is used to connect the valve body or the shaft of the rotating shaft to the valve holder so that they can rotate relative to each other, which can achieve high efficiency. Furthermore, a radial gap is provided between the rolling bearing and at least one of the shaft and the valve holder, and the shaft and the valve holder are connected so that they can be displaced relative to each other in the radial direction. Therefore, when the valve body sits on the valve seat, the shaft and the valve holder are displaced relative to each other in the radial direction only within the range of the gap, and the valve body can be seated coaxially with the valve seat, thereby reducing valve leakage.

この際、前記軸部と前記弁ホルダとは、前記軸線方向に移動可能な前記隙間を介して前記軸線方向に相対変位可能に接続されていることが好ましい。 In this case, it is preferable that the shaft portion and the valve holder are connected to each other so as to be relatively displaceable in the axial direction via the gap that is movable in the axial direction .

以上のような構成では、弁閉時に、弁ばねの収縮により弁体へ適切な押し付け荷重を与えるため、回転軸は弁体を着座位置よりもさらに下降させようとするが、弁体が弁座部に着座する際、軸部と弁ホルダとが、軸線方向に相対変位することによって、軸部と弁ホルダが軸線方向の隙間分自由となるため、弁体に力が加わらない。これにより、回転軸の軸線と弁座（弁口）の軸線とがずれていても、軸部と弁ホルダとが、大きな摺動抵抗なしに径方向及び軸線方向に相対変位することが可能になるため、弁座部に対して同軸上に弁体を着座させることができ、弁漏れを低減させることができる。 In the above configuration, when the valve is closed, the valve spring contracts to apply an appropriate pressure load to the valve disc, so the rotating shaft tries to lower the valve disc further than the seated position. However, when the valve disc seats on the valve seat, the shaft and the valve holder are displaced relative to each other in the axial direction, which allows the shaft and the valve holder to move freely by an axial gap, so no force is applied to the valve disc. As a result, even if the axis of the rotating shaft and the axis of the valve seat (valve orifice) are misaligned, the shaft and the valve holder can be displaced relative to each other in the radial and axial directions without significant sliding resistance, so the valve disc can be seated coaxially with the valve seat, reducing valve leakage.

また、前記軸部は、前記弁体のロッド軸であることが好ましい。また、前記軸部は、前記回転軸の先端部であることが好ましい。 The shaft portion is preferably the rod shaft of the valve body. The shaft portion is preferably the tip of the rotating shaft.

本発明の冷凍サイクルシステムは、圧縮機と、凝縮器と、膨張弁と、蒸発器と、を含む冷凍サイクルシステムであって、前記いずれかの電動弁が、前記膨張弁として用いられていることを特徴とする。 The refrigeration cycle system of the present invention is a refrigeration cycle system including a compressor, a condenser, an expansion valve, and an evaporator, and is characterized in that any one of the motor-operated valves is used as the expansion valve.

このような本発明によれば、上記したように、本発明の電動弁は、高効率化を図りつつ、弁漏れを抑制することができるので、運転時に、省エネであり、且つ、不具合が生じ難い冷凍サイクルシステムとすることができる。 As described above, the motor-operated valve of the present invention is highly efficient while suppressing valve leakage, resulting in a refrigeration cycle system that is energy-efficient and less prone to malfunctions during operation.

本発明の電動弁および冷凍サイクルシステムによれば、高効率化を図りつつ、弁漏れを抑制することができる。 The motor-operated valve and refrigeration cycle system of the present invention can suppress valve leakage while achieving high efficiency.

本発明の第１実施形態に係る電動弁を示す縦断面図である。1 is a vertical cross-sectional view showing a motor-operated valve according to a first embodiment of the present invention. 前記電動弁の弁開時における要部を示す縦断面図である。2 is a vertical cross-sectional view showing a main part of the motor-operated valve when the valve is open. FIG. 前記電動弁の弁体と弁座との当接時における要部を示す縦断面図である。4 is a longitudinal sectional view showing a main part of the motor-operated valve when a valve body and a valve seat are in contact with each other; FIG. 前記電動弁の着座時における要部を示す縦断面図である。3 is a vertical cross-sectional view showing a main part of the motor-operated valve when seated. FIG. 本発明の第２実施形態に係る電動弁の要部を示す縦断面図である。FIG. 6 is a vertical cross-sectional view showing a main portion of a motor-operated valve according to a second embodiment of the present invention. 本発明の第３実施形態に係る電動弁の弁開時における要部を示す縦断面図である。FIG. 11 is a vertical cross-sectional view showing a main part of a motor-operated valve according to a third embodiment of the present invention when the valve is open. 前記第３実施形態の電動弁の弁体と弁座との当接時における要部を示す縦断面図である。FIG. 11 is a longitudinal sectional view showing a main part of the motor-operated valve of the third embodiment when the valve body and the valve seat are in contact with each other. 前記第３実施形態の前記電動弁の着座時における要部を示す縦断面図である。FIG. 11 is a vertical cross-sectional view showing a main part of the motor-operated valve according to the third embodiment when the motor-operated valve is seated. 本発明の第４実施形態に係る電動弁の要部を示す縦断面図である。FIG. 10 is a vertical cross-sectional view showing a main portion of a motor-operated valve according to a fourth embodiment of the present invention. 本発明の冷凍サイクルシステムの一例を示す図である。FIG. 1 is a diagram showing an example of a refrigeration cycle system of the present invention. 従来の電動弁の要部を示す縦断面図である。FIG. 1 is a vertical cross-sectional view showing a main portion of a conventional motor-operated valve.

本発明の第１実施形態に係る電動弁を図１～図４に基づいて説明する。図１に示すように、本実施形態の電動弁１０は、弁本体１と、弁体２と、弁ホルダ６と、駆動部としてのステッピングモータ３と、を備えている。なお、以下の説明における「上下」の概念は図１の図面における上下に対応する。 The motor-operated valve according to the first embodiment of the present invention will be described with reference to Figs. 1 to 4. As shown in Fig. 1, the motor-operated valve 10 of this embodiment comprises a valve body 1, a valve element 2, a valve holder 6, and a stepping motor 3 as a drive unit. Note that the concept of "upper and lower" in the following description corresponds to the upper and lower in the drawing of Fig. 1.

弁本体１は、筒状の弁ハウジング部材１Ａと、弁ハウジング部材１Ａの上端開口部に固定される支持部材５と、を有している。 The valve body 1 has a cylindrical valve housing member 1A and a support member 5 that is fixed to the upper end opening of the valve housing member 1A.

弁ハウジング部材１Ａは、その内部に略円筒状の弁室１Ｃが形成され、側面側から弁室１Ｃに連通する第１の継手管１１が取り付けられている。また、弁ハウジング部材１Ａには、底面側から略円筒状の弁座部材１５が挿入され、ろう付けにより固定される弁座部材１５によって弁座部１３が構成されている。弁座部１３には、弁口である弁ポート１４が形成されている。さらに、弁ハウジング部材１Ａの底面側には、弁座部材１５の内側面の下端部となだらかに連続するように、第２の継手管１２が、弁ハウジング部材１Ａの底部にろう付けにより固定されている。第１の継手管１１から流体としての冷媒が流入した場合には、弁室１Ｃを介して弁ポート１４を通過した冷媒が第２の継手管１２から流出される。また、第２の継手管１２から冷媒が流入した場合には、弁ポート１４を介して弁室１Ｃを通過した冷媒が第１の継手管１１から流出される。 The valve housing member 1A has a substantially cylindrical valve chamber 1C formed therein, and a first joint tube 11 is attached to the side surface of the valve housing member 1A, which communicates with the valve chamber 1C. A substantially cylindrical valve seat member 15 is inserted into the valve housing member 1A from the bottom surface side, and the valve seat member 15 is fixed by brazing to form a valve seat portion 13. A valve port 14, which is a valve opening, is formed in the valve seat portion 13. Furthermore, a second joint tube 12 is fixed to the bottom of the valve housing member 1A by brazing on the bottom surface side of the valve housing member 1A so as to be smoothly continuous with the lower end of the inner surface of the valve seat member 15. When a refrigerant as a fluid flows in from the first joint tube 11, the refrigerant that has passed through the valve port 14 via the valve chamber 1C flows out from the second joint tube 12. When a refrigerant flows in from the second joint tube 12, the refrigerant that has passed through the valve chamber 1C via the valve port 14 flows out from the first joint tube 11.

支持部材５は、弁ハウジング部材１Ａの上端開口部に固定金具４１を介して溶接固定されている。この支持部材５の上側の中心には、弁ポート１４等の軸線Ｌと同軸に形成された雌ねじ部５ａが設けられており、下方に雌ねじ部５ａの外周よりも径の大きな円筒状のガイド孔５ｃが形成されている。 The support member 5 is welded to the upper end opening of the valve housing member 1A via a fixing bracket 41. A female threaded portion 5a is provided at the center of the upper side of the support member 5, which is formed coaxially with the axis L of the valve port 14, etc., and a cylindrical guide hole 5c with a diameter larger than the outer periphery of the female threaded portion 5a is formed below.

弁体２は、下側先端にニードル部２１が設けられた軸部としてのロッド軸２２を有している。ロッド軸２２は、上部の縮径部２２ａと下部の拡径部２２ｂとから成り、その上端部には、フランジ部２３が形成されている。ロッド軸２２の外周面側には、転がり軸受８（後述）が配設され、ロッド軸２２の上端部が拡大されたフランジ部２３によって転がり軸受８が抜け止めされている。 The valve body 2 has a rod shaft 22 as a shaft portion with a needle portion 21 at the lower end. The rod shaft 22 consists of an upper reduced diameter portion 22a and a lower expanded diameter portion 22b, and a flange portion 23 is formed at its upper end. A rolling bearing 8 (described later) is disposed on the outer peripheral surface side of the rod shaft 22, and the rolling bearing 8 is prevented from coming off by the expanded flange portion 23 at the upper end of the rod shaft 22.

ステッピングモータ３は、キャン４と、キャン４内に設けられたマグネットロータ３１と、ロータ軸３２と、不図示のステータコイルと、ステッピングモータ３の回転ストッパ機構７と、を有している。 The stepping motor 3 has a can 4, a magnet rotor 31 provided in the can 4, a rotor shaft 32, a stator coil (not shown), and a rotation stopper mechanism 7 for the stepping motor 3.

キャン４は、弁ハウジング１Ａの上端に溶接などによって気密に固定され、支持部材５、後述するマグネットロータ３１及び回転ストッパ機構７を収納している。マグネットロータ３１は、その外周部が多極に着磁されており、その中心にロータ軸３２が固定されている。ロータ軸３２は、その下端部が、弁ホルダ６及び転がり軸受８を介して、弁体２のロッド軸２２と連結されている。また、ロータ軸３２は、その中間部の上側表面に雄ねじ部３２ａが形成されている。この雄ねじ部３２ａは、支持部材５の雌ねじ部５ａに螺合され、これらの雄ねじ部３２ａ及び雌ねじ部５ａによって、駆動部のねじ送り機構１６が構成されている。ねじ送り機構１６は、ステッピングモータ３の回転運動をロータ軸３２直線運動に変換し、これにより弁体２が軸線Ｌ方向に進退駆動されるようになっている。ステータコイルは、キャン４の外周に配設されており、このステータコイルにパルス信号が与えられることにより、そのパルス数に応じてマグネットロータ３１が回転されてロータ軸３２が回転するようになっている。 The can 4 is fixed airtightly to the upper end of the valve housing 1A by welding or the like, and houses the support member 5, the magnet rotor 31 described later, and the rotation stopper mechanism 7. The magnet rotor 31 has its outer periphery magnetized with multiple poles, and the rotor shaft 32 is fixed to its center. The rotor shaft 32 has its lower end connected to the rod shaft 22 of the valve body 2 via the valve holder 6 and the rolling bearing 8. The rotor shaft 32 also has a male thread 32a formed on the upper surface of its middle part. This male thread 32a is screwed into the female thread 5a of the support member 5, and these male thread 32a and female thread 5a form the screw feed mechanism 16 of the drive unit. The screw feed mechanism 16 converts the rotational motion of the stepping motor 3 into linear motion of the rotor shaft 32, so that the valve body 2 is driven forward and backward in the axis L direction. The stator coil is arranged on the outer periphery of the can 4, and when a pulse signal is given to this stator coil, the magnet rotor 31 rotates according to the number of pulses, causing the rotor shaft 32 to rotate.

ステッピングモータ３の回転ストッパ機構７は、キャン４の天井部にガイド支持体７Ａが固定され、ガイド支持体７Ａには、キャン４の天井部の中心から軸心に沿って垂下された円筒状のガイド７６と、ガイド７６の外周に固定された螺旋ガイド７７と、螺旋ガイド７７にガイドされて回転かつ上下動可能な可動スライダ７８と、を備えている。可動スライダ７８には、径方向外側に突出した爪部７８ａが設けられ、マグネットロータ３１には、上方に延びて爪部７８ａと当接する延長部３１ａが設けられ、マグネットロータ３１が回転すると、延長部３１ａが爪部７８ａを押すことで、可動スライダ７８が螺旋ガイド７７に倣って回転かつ上下するようになっている。また、円筒状のガイド７６内部にはロータ軸３２の上部をガイドする筒部材７Ｂが嵌合されている。 The rotation stopper mechanism 7 of the stepping motor 3 has a guide support 7A fixed to the ceiling of the can 4, and the guide support 7A has a cylindrical guide 76 that hangs down from the center of the ceiling of the can 4 along the axis, a screw guide 77 fixed to the outer periphery of the guide 76, and a movable slider 78 that can rotate and move up and down guided by the screw guide 77. The movable slider 78 has a claw portion 78a that protrudes radially outward, and the magnet rotor 31 has an extension portion 31a that extends upward and abuts against the claw portion 78a. When the magnet rotor 31 rotates, the extension portion 31a presses the claw portion 78a, causing the movable slider 78 to rotate and move up and down following the screw guide 77. In addition, a tube member 7B that guides the upper part of the rotor shaft 32 is fitted inside the cylindrical guide 76.

螺旋ガイド７７には、マグネットロータ３１の最上端位置を規定する上端ストッパ７７ａと、マグネットロータ３１の最下端位置を規定する下端ストッパ７７ｂと、が形成されている。マグネットロータ３１の正回転に伴って下降した可動スライダ７８が下端ストッパ７７ｂに当接すると、この当接した位置で可動スライダ７８が回転不能となり、これによりマグネットロータ３１の回転が規制され、弁体２の下降も停止される。一方、マグネットロータ３１の逆回転に伴って上昇した可動スライダ７８が上端ストッパ７７ａに当接すると、この当接した位置で可動スライダ７８が回転不能となり、これによりマグネットロータ３１の回転が規制され、弁体２の上昇も停止される。 The spiral guide 77 is formed with an upper end stopper 77a that determines the uppermost position of the magnet rotor 31, and a lower end stopper 77b that determines the lowermost position of the magnet rotor 31. When the movable slider 78, which has descended in association with the forward rotation of the magnet rotor 31, abuts against the lower end stopper 77b, the movable slider 78 becomes unable to rotate at this abutting position, thereby restricting the rotation of the magnet rotor 31 and stopping the descent of the valve body 2. On the other hand, when the movable slider 78, which has ascended in association with the reverse rotation of the magnet rotor 31, abuts against the upper end stopper 77a, the movable slider 78 becomes unable to rotate at this abutting position, thereby restricting the rotation of the magnet rotor 31 and stopping the ascent of the valve body 2.

図２に示すように、弁ホルダ６は、筒状のホルダ本体６１の上面部中央に、ロータ軸３２の下側先端部を挿通させる挿通孔６１ａを有し、ロータ軸３２の下側先端部と相対回転可能に係合されている。また、ロータ軸３２の下側先端部には、鍔部３２ｂが設けられており、ホルダ本体６１内から抜けないようになっている。ロータ軸３２の鍔部３２ｂの下面には弁ばね９の上端が当接されている。転がり軸受８は、弁体２のロッド軸２２の縮径部２２ａの外周面側に配設されるリング状の第１部材８１と、複数個の転動部材としての鋼球８ａを介して接続されるリング状の第２部材８２と、を有したベアリングによって構成されている。この転がり軸受８は、第２部材８２が弁ばね９で付勢され、第２部材８２の下端部がホルダ本体６１の下端部（圧入部材６３）に当接するようになっている。弁ホルダ６は、ホルダ本体６１の下面中央に挿通孔６１ｂを有し、弁体２のロッド軸２２の拡径部２２ｂが挿通孔６１ｂに挿通されている。また、挿通孔６１ｂには、図１に示すように、リング状の圧入部材６３が圧入され、この圧入部材６３によって弁ホルダ６からの弁体２及び転がり軸受８の抜け止めがされている。なお、ここでは、ホルダ本体６１の下端部を圧入部材６３を圧入したものを例示したが、これに代わりホルダ本体６１の下端部にリング状の部材（止め輪等）を溶接や、かしめ等で固定してもよく、転がり軸受８の抜け止めが可能な構造であればこれらに限らない。 2, the valve holder 6 has an insertion hole 61a in the center of the upper surface of the cylindrical holder body 61 through which the lower end of the rotor shaft 32 is inserted, and is engaged with the lower end of the rotor shaft 32 so as to be rotatable relative to the rotor shaft 32. A flange 32b is provided at the lower end of the rotor shaft 32 so as not to come out of the holder body 61. The upper end of the valve spring 9 abuts against the lower surface of the flange 32b of the rotor shaft 32. The rolling bearing 8 is composed of a bearing having a ring-shaped first member 81 arranged on the outer peripheral surface side of the reduced diameter portion 22a of the rod shaft 22 of the valve body 2, and a ring-shaped second member 82 connected via a plurality of steel balls 8a as rolling members. In this rolling bearing 8, the second member 82 is biased by the valve spring 9, and the lower end of the second member 82 abuts against the lower end of the holder body 61 (press-in member 63). The valve holder 6 has an insertion hole 61b in the center of the bottom surface of the holder body 61, and the enlarged diameter portion 22b of the rod shaft 22 of the valve body 2 is inserted into the insertion hole 61b. In addition, as shown in FIG. 1, a ring-shaped press-in member 63 is pressed into the insertion hole 61b, and this press-in member 63 prevents the valve body 2 and the rolling bearing 8 from coming out of the valve holder 6. Note that here, an example in which the press-in member 63 is pressed into the bottom end of the holder body 61 is shown, but instead, a ring-shaped member (such as a retaining ring) may be fixed to the bottom end of the holder body 61 by welding or crimping, and is not limited to these as long as the structure is capable of preventing the rolling bearing 8 from coming out.

さらに、転がり軸受８内側の第１部材８１と、弁体２におけるロッド軸２２の縮径部２２ａとの間には、ロッド軸２２の径方向の隙間Ｃ１が設けられている。また、転がり軸受８の下側面と、弁体２におけるロッド軸２２の拡径部２２ｂとの間には、軸線方向Ｌの隙間Ｃ２が設けられている。 Furthermore, a gap C1 is provided in the radial direction of the rod shaft 22 between the first member 81 inside the rolling bearing 8 and the reduced diameter portion 22a of the rod shaft 22 in the valve body 2. A gap C2 is provided in the axial direction L between the lower surface of the rolling bearing 8 and the expanded diameter portion 22b of the rod shaft 22 in the valve body 2.

図２に示すように、弁開時においては、弁体２の軸線Ｌ´の位置は、例えば、弁座部１３の軸線Ｌの位置よりも左側にずれている。着座状態にするために、ステッピングモータ３の駆動によって弁体２が下降し、図３に示すように、ニードル部２１が弁座部１３に当接したときは、まだ弁体２の軸線Ｌ´は弁座部１３（弁ポート１４）の軸線Ｌの位置よりも左側にずれた状態で、ニードル部２１の左側が弁座部１３の左側に片当たりしている。この時、弁体２の弁座１３との当接部には矢印のような力（径方向には右方向の力、軸線Ｌ方向には上方向の力）が働く。さらにロータ軸３２が下降すると、弁体２は弁ホルダ６に対し相対的に軸線Ｌ方向で隙間Ｃ２を縮めるように上側に変位しながら、径方向のずれを正すように、径方向の隙間Ｃ１がある右側に変位し、回転ストッパ機構７が働いた着座時においては、図４に示すように、弁体２は、弁開時と比較して弁ホルダ６に対して相対的に右上に移動し、弁体２と弁ポート１４とが同軸上に位置することで、ニードル部２１は弁ポート１４の上端開口部（弁座部１３）の全周に着座する。 As shown in Figure 2, when the valve is open, the position of the axis L' of the valve disc 2 is, for example, shifted to the left of the position of the axis L of the valve seat 13. To achieve a seated state, the valve disc 2 is lowered by driving the stepping motor 3, and when the needle portion 21 abuts against the valve seat 13 as shown in Figure 3, the axis L' of the valve disc 2 is still shifted to the left of the position of the axis L of the valve seat 13 (valve port 14), and the left side of the needle portion 21 is abutting against the left side of the valve seat 13. At this time, forces as shown by the arrows (a force to the right in the radial direction and an upward force in the axial direction L) act on the abutment portion of the valve disc 2 with the valve seat 13. When the rotor shaft 32 further descends, the valve body 2 is displaced upward relative to the valve holder 6 in the direction of the axis L to reduce the gap C2, while displacing to the right where the radial gap C1 is located to correct the radial misalignment. When the rotation stopper mechanism 7 is activated and the valve body 2 is seated, as shown in FIG. 4, the valve body 2 moves upward and to the right relative to the valve holder 6 compared to when the valve is open, and the valve body 2 and the valve port 14 are positioned coaxially, so that the needle portion 21 is seated on the entire circumference of the upper end opening (valve seat portion 13) of the valve port 14.

以上の本実施形態によれば、弁体２のロッド軸２２と弁ホルダ６とを相対回転可能に接続する軸受に転がり軸受８を用いるので、弁閉時における弁体２の供回りを抑制でき、弁体２と弁座１３との間の摺動抵抗による回転負荷が小さくなるため、高効率な作動とすることができる。さらに、転がり軸受８と、弁体２のロッド軸２２と、の間には、径方向の隙間Ｃ１が設けられており、ロッド軸２２と弁ホルダ６とは、径方向に相対変位可能に接続されているので、弁体２が弁座部１３に着座する際、ロッド軸２２と弁ホルダ６のホルダ本体６１とは隙間Ｃ１の範囲内だけ径方向に相対変位し、弁座部１３に対して同軸上に弁体２を着座させることができ、弁漏れを低減させることができる。 According to the above embodiment, the rolling bearing 8 is used as the bearing that connects the rod shaft 22 of the valve body 2 and the valve holder 6 so that they can rotate relative to each other, so that the co-rotation of the valve body 2 when the valve is closed can be suppressed, and the rotation load due to the sliding resistance between the valve body 2 and the valve seat 13 can be reduced, resulting in highly efficient operation. Furthermore, a radial gap C1 is provided between the rolling bearing 8 and the rod shaft 22 of the valve body 2, and the rod shaft 22 and the valve holder 6 are connected so that they can be displaced relative to each other in the radial direction. Therefore, when the valve body 2 seats on the valve seat portion 13, the rod shaft 22 and the holder body 61 of the valve holder 6 are displaced relative to each other in the radial direction only within the range of the gap C1, and the valve body 2 can be seated coaxially with the valve seat portion 13, thereby reducing valve leakage.

また、転がり軸受８と、弁体２のロッド軸２２と、の間には、軸線Ｌ方向に隙間Ｃ２が設けられているので、弁体２が弁座と当接後にロータ軸３２がさらに下降するとき、弁体２が着座部１３に着座する際、ロッド軸２２と弁ホルダ６とが、軸線Ｌ方向に相対変位することによって、ロッド軸２２のフランジ部２３の下面と転がり軸受８の第１部材８１の上面が離れて、弁体２が軸線Ｌ方向の隙間分だけ自由となるため、ロータ軸３２の軸線Ｌ´と弁ポート１４の軸線Ｌとがずれていても、ロッド軸２２と弁ホルダ６とが、径方向及び軸線Ｌ方向に相対変位することによって、弁座部１３に対して同軸上に弁体２を着座させることができ、弁漏れを低減させることができる。 なお、軸線Ｌ´が、軸線Ｌに対して図示とは逆の右側に傾斜している場合は、弁体２は、弁体２が着座部１３に着座する際、隙間Ｃ１，Ｃ２がある左上の位置に変位する。 In addition, a gap C2 is provided in the axial direction L between the rolling bearing 8 and the rod shaft 22 of the valve body 2. Therefore, when the rotor shaft 32 descends further after the valve body 2 abuts against the valve seat, and the valve body 2 seats on the seating portion 13, the rod shaft 22 and the valve holder 6 are displaced relative to each other in the axial direction L, causing the lower surface of the flange portion 23 of the rod shaft 22 to separate from the upper surface of the first member 81 of the rolling bearing 8, and the valve body 2 is free by the amount of the gap in the axial direction L. Therefore, even if the axis L' of the rotor shaft 32 and the axis L of the valve port 14 are misaligned, the rod shaft 22 and the valve holder 6 are displaced relative to each other in the radial and axial directions L, allowing the valve body 2 to be seated coaxially with the valve seat portion 13, thereby reducing valve leakage. If the axis L' is inclined to the right with respect to the axis L, opposite to the illustration, the valve body 2 will be displaced to the upper left position where there are gaps C1 and C2 when the valve body 2 sits on the seating portion 13.

次に、図５に基づき、本発明の第２実施形態に係る電動弁について説明する。本実施形態の電動弁は、第１実施形態の電動弁１０と同様に、弁本体１と、弁体２と、弁ホルダ６と、駆動部としてのステッピングモータ３と、を備えている。本実施形態の電動弁では、弁ホルダ６の一部構成が第１実施形態の電動弁１０と相違している。以下、相違点について詳しく説明する。 Next, a motor-operated valve according to a second embodiment of the present invention will be described with reference to FIG. 5. The motor-operated valve of this embodiment, like the motor-operated valve 10 of the first embodiment, comprises a valve body 1, a valve element 2, a valve holder 6, and a stepping motor 3 as a drive unit. In the motor-operated valve of this embodiment, a portion of the configuration of the valve holder 6 differs from that of the motor-operated valve 10 of the first embodiment. The differences will be described in detail below.

本実施形態の電動弁では、ロータ軸３２の下端部に鍔部３２ｂがなく、弁ホルダ６のホルダ本体６１の上側の挿通孔６１ａもなく、ロータ軸３２の下端部と、ホルダ本体６１の上面の中心部とが一体的に連結され、ホルダ本体６１の円筒内部の天井面に弁ばね９の上端 が当接している点が第１実施形態の電動弁１０と相違している。なお、ロータ軸３２とホルダ本体６１とは、一体的に連結されたものに限らず、別体で形成されて適宜な取り付け手段によって取り付けられていてもよい。 The motor-operated valve of this embodiment differs from the motor-operated valve 10 of the first embodiment in that there is no flange 32b at the lower end of the rotor shaft 32, there is no insertion hole 61a on the upper side of the holder body 61 of the valve holder 6, the lower end of the rotor shaft 32 and the center of the upper surface of the holder body 61 are integrally connected, and the upper end of the valve spring 9 abuts against the ceiling surface inside the cylinder of the holder body 61. Note that the rotor shaft 32 and the holder body 61 are not limited to being integrally connected, and may be formed separately and attached by appropriate attachment means.

以上の本実施形態の電動弁においても、弁体２の軸心と弁座部１３の軸線とのずれに対する補正については第１実施形態と同様な効果が得られる。これに加え、弁ホルダ６においては、ロータ軸３２の下端部と弁ホルダ６のホルダ本体６１とが一体的に形成されているので、第１実施形態の電動弁１０よりも、構成の簡易化を図ることができる。 In the motor-operated valve of this embodiment, the same effect as in the first embodiment can be obtained with respect to the correction of the misalignment between the axis of the valve body 2 and the axis of the valve seat portion 13. In addition, in the valve holder 6, the lower end of the rotor shaft 32 and the holder body 61 of the valve holder 6 are integrally formed, so that the configuration can be simplified compared to the motor-operated valve 10 of the first embodiment.

次に、図６～図８に基づき、本発明の第３実施形態に係る電動弁について説明する。本実施形態の電動弁は、第１実施形態の電動弁１０と同様に、弁本体１と、弁体２と、弁ホルダ６と、駆動部としてのステッピングモータ３と、を備えている。本実施形態の電動弁では、弁体２、弁ホルダ６、ロータ軸３２の構成が第１実施形態の電動弁１０と相違している。以下、相違点について詳しく説明する。 Next, a motor-operated valve according to a third embodiment of the present invention will be described with reference to Figures 6 to 8. The motor-operated valve of this embodiment, like the motor-operated valve 10 of the first embodiment, comprises a valve body 1, a valve element 2, a valve holder 6, and a stepping motor 3 as a drive unit. In the motor-operated valve of this embodiment, the configurations of the valve element 2, the valve holder 6, and the rotor shaft 32 differ from those of the motor-operated valve 10 of the first embodiment. The differences will be described in detail below.

本実施形態の電動弁において、図６に示すように、転がり軸受８は、ホルダ本体６１内において、軸部としてのロータ軸３２の下側先端部における下側鍔部３２ｂと上側鍔部３２ｄとの間の縮径部３２ｃの外周部に、第１部材８１が取り付けられている。また、転がり軸受８の第２部材８２とホルダ本体６１の内側面との間に、ロータ軸３２の径方向の隙間Ｃ１が設けられている。さらに、ホルダ本体６１の内側面中間部には、リング状の突出部６４が設けられており、この突出部６４と転がり軸受８の下面との間には、軸線Ｌ方向の隙間Ｃ２が設けられている。また、突出部６４の下面には弁ばね９の上端が当接している。 In the motor-operated valve of this embodiment, as shown in FIG. 6, the rolling bearing 8 is attached to the outer periphery of the reduced diameter portion 32c between the lower flange 32b and the upper flange 32d at the lower end of the rotor shaft 32 as the shaft portion in the holder body 61, with the first member 81. In addition, a gap C1 in the radial direction of the rotor shaft 32 is provided between the second member 82 of the rolling bearing 8 and the inner surface of the holder body 61. Furthermore, a ring-shaped protrusion 64 is provided at the middle part of the inner surface of the holder body 61, and a gap C2 in the axial direction is provided between this protrusion 64 and the lower surface of the rolling bearing 8. In addition, the upper end of the valve spring 9 abuts against the lower surface of the protrusion 64.

図６に示すように、弁開時においては、ロータ軸３２の軸線Ｌ´の位置は、例えば、弁座部１３の軸線Ｌの位置よりも左側にずれている。着座状態にするために、ステッピングモータ３の駆動によって弁体２が下降し、図７に示すように、ニードル部２１が弁座部１３に当接したときは、まだ弁体２の軸線Ｌ´は弁座部１３（弁ポート１４）の軸線Ｌの位置よりも左側にずれた状態で、ニードル部２１の左側が弁座部１３の左側に片当たりしている。この時、弁体２の弁座１３との当接部には矢印のような力（径方向には右方向の力、軸線Ｌ方向には上方向の力）が働くとともに、弁ホルダ６には矢印のような径方向に右側の力が働く。さらにロータ軸３２が下降すると、弁体２と弁ばね９によって軸線Ｌ方向に支持されたホルダ本体６１の天井面と転がり軸受８の第２部材８２の上端面とが離れ、ロータ軸３２及び転がり軸受８に対し相対的に弁体２及び弁ホルダ６が径方向の右方向に、軸線Ｌ方向の上方向に移動することで、ホルダ本体６１が、軸線Ｌ方向で隙間Ｃ２を縮めるように上側に変位しながら、弁体２の軸線Ｌ´と弁座１３の軸線Ｌの径方向のずれが無くなるように、径方向の隙間Ｃ２がある右側に変位し、回転ストッパ機構７が働いた着座時においては、図８に示すように、ロータ軸３２の下端部は、弁開時と比較して弁ホルダ６に対して相対的に左下に移動し、弁体２と弁ポート１４とが同軸上に位置している。 As shown in Figure 6, when the valve is open, the position of the axis L' of the rotor shaft 32 is, for example, shifted to the left of the position of the axis L of the valve seat 13. To achieve a seated state, the valve body 2 is lowered by driving the stepping motor 3, and as shown in Figure 7, when the needle portion 21 abuts against the valve seat 13, the axis L' of the valve body 2 is still shifted to the left of the position of the axis L of the valve seat 13 (valve port 14), and the left side of the needle portion 21 is abutting against the left side of the valve seat 13. At this time, a force as shown by the arrows (a force to the right in the radial direction and an upward force in the axial direction L) acts on the abutment portion of the valve body 2 with the valve seat 13, and a force to the right in the radial direction as shown by the arrows acts on the valve holder 6. When the rotor shaft 32 further descends, the ceiling surface of the holder body 61 supported in the axial direction L by the valve body 2 and the valve spring 9 separates from the upper end surface of the second member 82 of the rolling bearing 8, and the valve body 2 and the valve holder 6 move radially to the right and upward in the axial direction L relative to the rotor shaft 32 and the rolling bearing 8. As a result, the holder body 61 displaces upward to reduce the gap C2 in the axial direction L, and displaces to the right where the radial gap C2 is located so that the radial misalignment between the axis L' of the valve body 2 and the axis L of the valve seat 13 is eliminated. When the rotation stopper mechanism 7 is activated and the valve seat is seated, as shown in FIG. 8, the lower end of the rotor shaft 32 moves downward and left relative to the valve holder 6 compared to when the valve is open, and the valve body 2 and the valve port 14 are coaxially positioned.

以上の本実施形態によれば、ロータ軸３２と弁ホルダ６とを相対回転可能に接続する軸受に転がり軸受８を用いるので、弁閉時における弁体２の供回りを抑制でき、弁体２と弁座１３との間の摺動抵抗による回転負荷が小さくなるため、高効率な作動とすることができる。さらに、転がり軸受８と、ロータ軸３２の縮径部３２ｃと、の間には、径方向の隙間Ｃ１が設けられており、ロータ軸３２と弁ホルダ６とは、径方向に相対変位可能に接続されているので、弁体２が着座部１３に着座する際、ロータ軸３２と弁ホルダ６のホルダ本体６１とは隙間Ｃ１の範囲内だけ径方向に相対変位し、弁座部１３に対して同軸上に弁体２を着座させることができ、弁漏れを低減させることができる。 According to the above embodiment, the rolling bearing 8 is used as the bearing that connects the rotor shaft 32 and the valve holder 6 so that they can rotate relative to each other, so that the co-rotation of the valve body 2 when the valve is closed can be suppressed, and the rotation load due to the sliding resistance between the valve body 2 and the valve seat 13 can be reduced, resulting in highly efficient operation. Furthermore, a radial gap C1 is provided between the rolling bearing 8 and the reduced diameter portion 32c of the rotor shaft 32, and the rotor shaft 32 and the valve holder 6 are connected so that they can be displaced relative to each other in the radial direction. Therefore, when the valve body 2 seats on the seating portion 13, the rotor shaft 32 and the holder body 61 of the valve holder 6 are displaced relative to each other in the radial direction only within the range of the gap C1, and the valve body 2 can be seated coaxially with the valve seat portion 13, thereby reducing valve leakage.

また、弁体２と弁座部１３との当接後、さらにロータ軸３２が下降して、弁体２が弁座部１３に着座する際、ロータ軸３２の軸線Ｌ´と弁ポート１４の軸線Ｌとがずれていても、ロータ軸３２と弁ホルダ６とが、径方向及び軸線Ｌ方向に相対変位することによって、弁座部１３に対して同軸上に弁体２を着座させることができ、ニードル部２１が弁ポート１４の上部開口端（弁座部１３）の全周に当接して弁漏れを低減させることができる。なお、軸線Ｌ´が、軸線Ｌに対して図示とは逆の右側にずれている場合は、ロータ軸３２は、弁体２が着座部１３に着座する際、隙間Ｃ１，Ｃ２がある右下の位置に変位する。なお、図６～図８の実施形態では、転がり軸受８の第１部材８１とロータ軸３２との取付状態として、第１部材８１とロータ軸３２の下側鍔部３２ｂ及び上側鍔部３２ｄとの間において、ロータ軸３２の軸線Ｌ´方向に隙間を設けたものを例示したが、転がり軸受８の第１部材８１とロータ軸３２の下側鍔部３２ｂ及び上側鍔部３２ｄとの間に軸線Ｌ´方向に隙間が無くとも、ホルダ本体６１の突出部６４と転がり軸受８の下面との間には、軸線Ｌ方向の隙間が設けられていることから、上述の効果が得られることは自明である。 Furthermore, even if the axis L' of the rotor shaft 32 is misaligned with the axis L of the valve port 14 when the rotor shaft 32 further descends and the valve disc 2 seats on the valve seat 13 after the valve disc 2 abuts against the valve seat 13, the rotor shaft 32 and the valve holder 6 are displaced relative to each other in the radial and axial L directions, so that the valve disc 2 can be seated coaxially on the valve seat 13, and the needle portion 21 abuts against the entire circumference of the upper opening end (valve seat 13) of the valve port 14, thereby reducing valve leakage. Note that if the axis L' is misaligned to the right, opposite to the illustration, the rotor shaft 32 will be displaced to the lower right where there are gaps C1 and C2 when the valve disc 2 seats on the seat 13. In the embodiment of Figures 6 to 8, the mounting state between the first member 81 of the rolling bearing 8 and the rotor shaft 32 is illustrated as being such that a gap is provided in the direction of the axis L' of the rotor shaft 32 between the first member 81 and the lower flange 32b and upper flange 32d of the rotor shaft 32. However, even if there is no gap in the direction of the axis L' between the first member 81 of the rolling bearing 8 and the lower flange 32b and upper flange 32d of the rotor shaft 32, it is self-evident that the above-mentioned effect can be obtained because a gap is provided in the direction of the axis L between the protrusion 64 of the holder body 61 and the underside of the rolling bearing 8.

次に、図９に基づき、本発明の第３実施形態に係る電動弁について説明する。本実施形態の電動弁は、第１実施形態の電動弁１０と同様に、弁本体１と、弁体２と、弁ホルダ６と、駆動部としてのステッピングモータ３と、を備えている。本実施形態の電動弁では、弁ホルダ６の一部構成が第１実施形態の電動弁１０と相違している。以下、相違点について詳しく説明する。 Next, a motor-operated valve according to a third embodiment of the present invention will be described with reference to FIG. 9. The motor-operated valve of this embodiment, like the motor-operated valve 10 of the first embodiment, comprises a valve body 1, a valve element 2, a valve holder 6, and a stepping motor 3 as a drive unit. In the motor-operated valve of this embodiment, a portion of the configuration of the valve holder 6 differs from that of the motor-operated valve 10 of the first embodiment. The differences will be described in detail below.

本実施形態の電動弁では、ロータ軸３２の下端部に鍔部３２ｂがなく、弁ホルダ６のホルダ本体６１の上側の挿通孔６１ａもなく、ロータ軸３２の下端部と、ホルダ本体６１の上面の中心部とが一体的に形成されており、さらに、弁体２のロッド軸２２の下側の大部分が、ホルダ本体６１の外部に位置して設けられている。転がり軸受８は、その第２部材８２がホルダ本体６１の内側に固定されている。弁ばね９は、弁体２のニードル部２１とロッド軸２２の途中に挿通したリング状のばね受部材２ａとの間に圧縮状態で設けられ、ばね受２ａに対して弁体２が下向きに付勢されている。弁体２のロッド軸２２は、転がり軸受８の第１部材８１に挿通され、弁体２は軸線方向Ｌに沿って変位可能に支持されている。さらに、ロッド軸２２の径方向の隙間Ｃ１は、ロッド軸２２と転がり軸受８の第１部材８１との間に設けられている。また、ロッド軸２２の軸線Ｌ方向の隙間Ｃ２は、転がり軸受８の下面とばね受２ａの上面との間に設けられている。なお、ばね受部材２ａは、弁体２と別部材とせずに、一体的に形成してもよい。 In the motor-operated valve of this embodiment, there is no flange 32b at the lower end of the rotor shaft 32, and there is no through hole 61a on the upper side of the holder body 61 of the valve holder 6. The lower end of the rotor shaft 32 and the center of the upper surface of the holder body 61 are integrally formed, and further, most of the lower side of the rod shaft 22 of the valve body 2 is located outside the holder body 61. The second member 82 of the rolling bearing 8 is fixed to the inside of the holder body 61. The valve spring 9 is provided in a compressed state between the needle portion 21 of the valve body 2 and the ring-shaped spring bearing member 2a inserted halfway through the rod shaft 22, and the valve body 2 is biased downward against the spring bearing 2a. The rod shaft 22 of the valve body 2 is inserted into the first member 81 of the rolling bearing 8, and the valve body 2 is supported so as to be displaceable along the axial direction L. Furthermore, the radial gap C1 of the rod shaft 22 is provided between the rod shaft 22 and the first member 81 of the rolling bearing 8. Furthermore, the axial gap C2 of the rod shaft 22 is provided between the lower surface of the rolling bearing 8 and the upper surface of the spring bearing 2a. The spring bearing member 2a may be formed integrally with the valve body 2 instead of being a separate member.

以上の本実施形態の電動弁においても、弁体２の軸心と弁座部１３の軸線のずれに対する補正については第１実施形態と同様な効果が得られる。これに加え、弁ホルダ６においては、第２実施形態の電動弁と同様、ロータ軸３２の下端部と弁ホルダ６のホルダ本体６１とが一体的に形成されていることで、第１実施形態の電動弁１０よりも、この部分の構成の簡易化を図ることができる。 In the motor-operated valve of this embodiment, the same effect as in the first embodiment can be obtained with respect to the correction of the misalignment between the axis of the valve body 2 and the axis of the valve seat portion 13. In addition, in the valve holder 6, as in the motor-operated valve of the second embodiment, the lower end of the rotor shaft 32 and the holder body 61 of the valve holder 6 are integrally formed, so that the configuration of this part can be simplified compared to the motor-operated valve 10 of the first embodiment.

次に、本発明の冷凍サイクルシステムを図８に基づいて説明する。図８は、本発明の冷凍サイクルシステムの一例を示す図である。図８において、符号１００は前記各実施形態の電動弁１０を用いた膨張弁であり、２００は室外ユニットに搭載された室外熱交換器、３００は室内ユニットに搭載された室内熱交換器、４００は四方弁を構成する流路切換弁、５００は圧縮機である。電動弁１００、室外熱交換器２００、室内熱交換器３００、流路切換弁４００、および圧縮機５００は、それぞれ導管によって図示のように接続され、ヒートポンプ式の冷凍サイクルを構成している。なお、アキュムレータ、圧力センサ、温度センサ等は図示を省略してある。 Next, the refrigeration cycle system of the present invention will be described with reference to FIG. 8. FIG. 8 is a diagram showing an example of the refrigeration cycle system of the present invention. In FIG. 8, reference numeral 100 denotes an expansion valve using the motor-operated valve 10 of each of the above-mentioned embodiments, 200 denotes an outdoor heat exchanger mounted on an outdoor unit, 300 denotes an indoor heat exchanger mounted on an indoor unit, 400 denotes a flow path switching valve constituting a four-way valve, and 500 denotes a compressor. The motor-operated valve 100, the outdoor heat exchanger 200, the indoor heat exchanger 300, the flow path switching valve 400, and the compressor 500 are each connected by a conduit as shown in the figure, constituting a heat pump type refrigeration cycle. Note that an accumulator, a pressure sensor, a temperature sensor, etc. are omitted from the illustration.

冷凍サイクルの流路は、流路切換弁４００により冷房運転時の流路と暖房運転時の流路の２通りに切換えられる。冷房運転時には、図８に実線の矢印で示したように、圧縮機５００で圧縮された冷媒は流路切換弁４００から室外熱交換器２００に流入され、この室外熱交換器２００は凝縮器として機能し、室外熱交換器２００から流出された液冷媒は膨張弁１００を介して室内熱交換器３００に流入され、この室内熱交換器３００は蒸発器として機能する。 The flow path of the refrigeration cycle is switched between two paths, one for cooling operation and the other for heating operation, by the flow path switching valve 400. During cooling operation, as shown by the solid arrows in Figure 8, the refrigerant compressed by the compressor 500 flows from the flow path switching valve 400 into the outdoor heat exchanger 200, which functions as a condenser, and the liquid refrigerant flowing out of the outdoor heat exchanger 200 flows into the indoor heat exchanger 300 via the expansion valve 100, which functions as an evaporator.

一方、暖房運転時には、図８に破線の矢印で示したように、圧縮機５００で圧縮された冷媒は流路切換弁４００から室内熱交換器３００、膨張弁１００、室外熱交換器２００、流路切換弁４００、そして、圧縮機５００の順に循環され、室内熱交換器３００が凝縮器として機能し、室外熱交換器２００が蒸発器として機能する。膨張弁１００は、冷房運転時に室外熱交換器２００から流入する液冷媒、または暖房運転時に室内熱交換器３００から流入する液冷媒を、それぞれ減圧膨張し、さらにその冷媒の流量を制御する。なお、図７においては、冷房運転時に室外熱交換器２００から液冷媒が膨張弁１００の第１の継手管１０１に流入し、暖房運転時には、室内熱交換器３００からの液冷媒が膨張弁１００の第２の継手管１０２に流入するように冷凍サイクルに膨張弁１００を設けているが、これに限らず、冷房運転時に室外熱交換器２００からの液冷媒が膨張弁１００の第２の継手管１０２に流入し、暖房運転時には室内熱交換器３００からの液冷媒が膨張弁１００の第１の継手管１０１に流入するように膨張弁１００を冷凍サイクルに設けてもよい。 On the other hand, during heating operation, as shown by the dashed arrows in Figure 8, the refrigerant compressed by the compressor 500 is circulated from the flow path switching valve 400 to the indoor heat exchanger 300, the expansion valve 100, the outdoor heat exchanger 200, the flow path switching valve 400, and then the compressor 500, with the indoor heat exchanger 300 functioning as a condenser and the outdoor heat exchanger 200 functioning as an evaporator. The expansion valve 100 reduces the pressure and expands the liquid refrigerant flowing in from the outdoor heat exchanger 200 during cooling operation, or the liquid refrigerant flowing in from the indoor heat exchanger 300 during heating operation, and further controls the flow rate of the refrigerant. In FIG. 7, the expansion valve 100 is provided in the refrigeration cycle so that liquid refrigerant from the outdoor heat exchanger 200 flows into the first joint pipe 101 of the expansion valve 100 during cooling operation, and liquid refrigerant from the indoor heat exchanger 300 flows into the second joint pipe 102 of the expansion valve 100 during heating operation. However, this is not limited to this, and the expansion valve 100 may be provided in the refrigeration cycle so that liquid refrigerant from the outdoor heat exchanger 200 flows into the second joint pipe 102 of the expansion valve 100 during cooling operation, and liquid refrigerant from the indoor heat exchanger 300 flows into the first joint pipe 101 of the expansion valve 100 during heating operation.

以上の本発明の冷凍サイクルシステムによれば、上記したように、本実施形態の電動弁１０は、高効率化を図りつつ、弁漏れを抑制することができるので、運転時に、省エネであり、且つ、不具合が生じ難い冷凍サイクルシステムとすることができる。 According to the refrigeration cycle system of the present invention, as described above, the motor-operated valve 10 of this embodiment can suppress valve leakage while achieving high efficiency, resulting in a refrigeration cycle system that is energy-efficient and less prone to malfunctions during operation.

以上、図面を参照して、本発明を実施するための形態を第１～３実施形態に基づいて詳述してきたが、具体的な構成は、これらの実施形態に限らず、本発明の要旨を逸脱しない程度の設計的変更は、本発明に含まれる。 The above describes in detail the first to third embodiments of the present invention with reference to the drawings, but the specific configuration is not limited to these embodiments, and design changes that do not deviate from the gist of the present invention are included in the present invention.

例えば、上記した第１～３実施形態では、電動弁１０を、冷凍サイクルシステムの膨張弁として使用したが、これに限定されず、例えば、ビル用のマルチエアコン等の室内機側の絞り装置等、他のシステムにも適用することができる。 For example, in the first to third embodiments described above, the motor-operated valve 10 is used as an expansion valve in a refrigeration cycle system, but the present invention is not limited to this and can also be applied to other systems, such as a throttling device on the indoor unit side of a multi-air conditioner for a building.

１０ 電動弁
Ｃ１，Ｃ２ 隙間
１ 弁本体
１Ａ 弁ハウジング部材
１Ｃ 弁室
２ 弁体
２ａ ばね受部材
２１ ニードル部
２２ ロッド軸（軸部）
３ ステッピングモータ（駆動部）
６ 弁ホルダ
６１ ホルダ本体
６２ ばね受
８ 転がり軸受
８１ 第１部材
８２ 第２部材
８ａ 鋼球（転動部材）
９ 弁ばね
１３ 弁座部
１４ 弁ポート
３２ ロータ軸（回転軸、軸部）
１００ 膨張弁
２００ 室外熱交換器（凝縮器、蒸発器）
３００ 室内熱交換器（凝縮器、蒸発器）
４００ 流路切換弁
５００ 圧縮機 Reference Signs List 10 Motor-operated valve C1, C2 Gap 1 Valve body 1A Valve housing member 1C Valve chamber 2 Valve body 2a Spring receiving member 21 Needle portion 22 Rod shaft (shaft portion)
3 Stepping motor (drive unit)
6 Valve holder 61 Holder body 62 Spring bearing 8 Rolling bearing 81 First member 82 Second member 8a Steel ball (rolling member)
9 Valve spring 13 Valve seat portion 14 Valve port 32 Rotor shaft (rotating shaft, shaft portion)
100 Expansion valve 200 Outdoor heat exchanger (condenser, evaporator)
300 Indoor heat exchanger (condenser, evaporator)
400 Flow path switching valve 500 Compressor

Claims (4)

弁室及び弁座部を構成する弁本体と、前記弁座部と軸線方向で接離して弁ポートの開度を変更する弁体と、回転軸を進退駆動させる駆動部と、前記弁体と前記回転軸とに亘る弁ホルダと、弁閉方向に弁体を付勢する弁ばねと、を備えた電動弁であって、
前記弁体及び前記回転軸の少なくとも一方は、前記弁ホルダに回転自在に挿通される軸部を有し、前記軸部と前記弁ホルダとの間に転がり軸受を備え、
前記転がり軸受と、前記軸部及び前記弁ホルダの少なくとも一方と、の間には、径方向の隙間が設けられており、前記軸部と前記弁ホルダとは、前記径方向に相対変位可能に接続され、
前記転がり軸受は、前記軸部及び前記弁ホルダの少なくとも一方に対し、前記軸線方向に移動可能な隙間を介して設けられ、
前記軸部と前記弁ホルダとは、前記軸線方向に移動可能な前記隙間を介して前記軸線方向に相対変位可能に接続されていることを特徴とする電動弁。 An electrically operated valve comprising: a valve body that defines a valve chamber and a valve seat; a valve disc that moves axially toward and away from the valve seat to change an opening degree of a valve port; a drive unit that drives a rotary shaft to move forward and backward; a valve holder that spans between the valve disc and the rotary shaft; and a valve spring that biases the valve disc in a valve closing direction,
At least one of the valve body and the rotating shaft has a shaft portion rotatably inserted into the valve holder, and a rolling bearing is provided between the shaft portion and the valve holder,
A radial gap is provided between the rolling bearing and at least one of the shaft portion and the valve holder, and the shaft portion and the valve holder are connected to be relatively displaceable in the radial direction,
The rolling bearing is provided with respect to at least one of the shaft portion and the valve holder via a gap that allows the rolling bearing to move in the axial direction ,
The motor-operated valve, characterized in that the shaft portion and the valve holder are connected to each other so as to be capable of relative displacement in the axial direction via the gap that is movable in the axial direction. 前記軸部は、前記弁体のロッド軸であることを特徴とする請求項１に記載の電動弁。 2. The motor-operated valve according to claim 1 , wherein the shaft portion is a rod shaft of the valve body. 前記軸部は、前記回転軸の先端部であることを特徴とする請求項１に記載の電動弁。 2. The motor-operated valve according to claim 1 , wherein the shaft portion is a tip end portion of the rotating shaft. 圧縮機と、凝縮器と、膨張弁と、蒸発器と、を含む冷凍サイクルシステムであって、請求項１～３のいずれか１項に記載の電動弁が、前記膨張弁として用いられていることを特徴とする冷凍サイクルシステム。 A refrigeration cycle system including a compressor, a condenser, an expansion valve, and an evaporator, wherein the motor-operated valve according to any one of claims 1 to 3 is used as the expansion valve.
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Citations (2)

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Publication number Priority date Publication date Assignee Title
JP2012172839A (en) 2011-02-24 2012-09-10 Fuji Koki Corp Motor-operated valve
JP2013224708A (en) 2012-04-23 2013-10-31 Saginomiya Seisakusho Inc Motor-operated valve

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012172839A (en) 2011-02-24 2012-09-10 Fuji Koki Corp Motor-operated valve
JP2013224708A (en) 2012-04-23 2013-10-31 Saginomiya Seisakusho Inc Motor-operated valve

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