JP2018119612A - Motor valve and refrigeration cycle system - Google Patents

Motor valve and refrigeration cycle system Download PDF

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JP2018119612A
JP2018119612A JP2017011528A JP2017011528A JP2018119612A JP 2018119612 A JP2018119612 A JP 2018119612A JP 2017011528 A JP2017011528 A JP 2017011528A JP 2017011528 A JP2017011528 A JP 2017011528A JP 2018119612 A JP2018119612 A JP 2018119612A
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screw member
valve
rotor
male screw
diameter
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JP6691064B2 (en
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大樹 中川
Daiki Nakagawa
大樹 中川
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Saginomiya Seisakusho Inc
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Saginomiya Seisakusho Inc
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F16K31/50—Mechanical actuating means with screw-spindle or internally threaded actuating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/047—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Mechanically-Actuated Valves (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a motor valve capable of appropriately rotating a rotor and having high operability, and a refrigeration cycle system using the motor valve.SOLUTION: A motor valve is configured to convert rotary motion of a rotor stored in an inner periphery of a case into linear motion by screwing a male screw member and a female screw member, and then axially move a valve body stored in a valve body, based on the linear motion, wherein an open hole to which the male screw member is fixed in a penetrated manner is formed, and a bush member configured to transmit rotation of the rotor to the male screw member is provided. The difference between an inner peripheral diameter of the open hole and an outer peripheral diameter of the male screw member is made smaller than smaller one out of the difference between a thread diameter of a male screw of the male screw member and a root diameter of a female screw of the female screw member and the difference between a root diameter of the male screw of the male screw member and a thread diameter of the female screw of the female screw member.SELECTED DRAWING: Figure 2

Description

本発明は、電動弁、および該電動弁を用いた冷凍サイクルシステムに関する。   The present invention relates to a motor-operated valve and a refrigeration cycle system using the motor-operated valve.

従来、パッケージエアコン、ルームエアコン、冷凍機などに用いられる電動弁が知られている（たとえば、特許文献１参照）。この電動弁１００においては、図６に示すように、ステッピングモータが駆動してロータ１０３が回転すると、雌ネジ１３１ａと雄ネジ１２１ａのネジ送り作用により、弁体１１４が中心軸Ｌ方向に移動する。これにより、弁ポート１２１を開閉する調整がなされ、管継手１１１から流入して管継手１１２から流出する冷媒の流量が制御される。   Conventionally, motor-operated valves used for package air conditioners, room air conditioners, refrigerators, and the like are known (for example, see Patent Document 1). In this electric valve 100, as shown in FIG. 6, when the stepping motor is driven and the rotor 103 rotates, the valve body 114 moves in the direction of the central axis L by the screw feeding action of the female screw 131a and the male screw 121a. . Thereby, adjustment which opens and closes the valve port 121 is made, and the flow rate of the refrigerant flowing in from the pipe joint 111 and flowing out from the pipe joint 112 is controlled.

特開２０１２−１７２８３９号公報JP 2012-172839 A

ところで、上述の電動弁１００においては、雄ネジ１２１ａと雌ネジ１３１ａとの間の隙間に起因して電動弁１００の良好な作動性が得られなくなる恐れがあった。   By the way, in the above-mentioned electric valve 100, there was a possibility that good operability of the electric valve 100 could not be obtained due to a gap between the male screw 121a and the female screw 131a.

たとえば、ブッシュ部材１３３の貫通孔１３３ａに弁軸１４１を溶接した際に、図７に示すように、弁軸１４１が軸芯からずれ、偏った位置に固定されることもあり得る。この場合、雄ネジ１２１ａと雌ネジ１３１ａの噛み合いの隙間が大きければ、ロータ１０３が偏った軸を中心に回転するため、電動弁１００の作動性が阻害され、ロータ１０３を高い精度で回転させ難くなる。   For example, when the valve shaft 141 is welded to the through hole 133a of the bush member 133, as shown in FIG. 7, the valve shaft 141 may be displaced from the shaft center and fixed at a biased position. In this case, if the gap between the engagement between the male screw 121a and the female screw 131a is large, the rotor 103 rotates about the biased axis, so that the operability of the motor-operated valve 100 is hindered and it is difficult to rotate the rotor 103 with high accuracy. Become.

本発明の目的は、ロータを適正に回転させることができ、高い作動性を有する電動弁、および該電動弁を用いた冷凍サイクルシステムを提供することである。   An object of the present invention is to provide an electric valve that can appropriately rotate a rotor and has high operability, and a refrigeration cycle system using the electric valve.

本発明の電動弁は、
ケースの内周に収容されたロータの回転運動を、雄ネジ部材と雌ネジ部材とのネジ螺合により直線運動に変換し、この直線運動に基づいて弁本体内に収容された弁体を軸方向に移動させる電動弁であって、
前記雄ネジ部材が貫通して固定される貫通孔が形成され、前記ロータの回転を前記雄ネジ部材に伝達するブッシュ部材を備え、
前記貫通孔の内周径と前記雄ネジ部材の外周径との差が、
前記雄ネジ部材の雄ネジの山径と前記雌ネジ部材の雌ネジの谷径との差と、前記雄ネジ部材の雄ネジの谷径と前記雌ネジ部材の雌ネジの山径との差のうちいずれか小さい方よりも小さいことを特徴とする。 The motor operated valve of the present invention is
The rotational motion of the rotor accommodated in the inner periphery of the case is converted into linear motion by screwing the male screw member and the female screw member, and the valve body accommodated in the valve body is pivoted based on this linear motion. A motorized valve that moves in a direction,
A through hole is formed through which the male screw member is fixed, and includes a bush member that transmits the rotation of the rotor to the male screw member.
The difference between the inner diameter of the through hole and the outer diameter of the male screw member is
The difference between the male thread crest diameter of the male screw member and the female thread trough diameter of the female screw member, and the difference between the male thread trough diameter of the male screw member and female thread crest diameter of the female screw member. It is characterized by being smaller than any one of them.

このように、ブッシュ部材の貫通孔と雄ネジ部材の間の隙間を狭くすることにより、ロータ回転時にロータが軸芯に対して偏芯することを抑制することができる。よって、ロータを適正に回転させることができ、高い作動性を有する電動弁を提供することができる。   In this way, by narrowing the gap between the through hole of the bush member and the male screw member, the rotor can be prevented from being eccentric with respect to the shaft center when the rotor rotates. Therefore, a rotor can be rotated appropriately and the motor operated valve which has high operativity can be provided.

また、本発明の電動弁は、
前記ケースの内周径と前記ロータの外周径との差が、
前記雄ネジ部材の雄ネジの山径と前記雌ネジ部材の雌ネジの谷径との差と、前記雄ネジ部材の雄ネジの谷径と前記雌ネジ部材の雌ネジの山径との差のうちいずれか大きい方よりも大きいことを特徴とする。 Moreover, the motor operated valve of the present invention is
The difference between the inner diameter of the case and the outer diameter of the rotor is
The difference between the male thread crest diameter of the male screw member and the female thread trough diameter of the female screw member, and the difference between the male thread trough diameter of the male screw member and female thread crest diameter of the female screw member. It is characterized by being larger than any one of them.

このように、ケースとロータの間の隙間の間隔を広げることにより、ロータ回転時にロータがケースの内側に接触し、ロータがケースの内周面に摺動することを防止することができる。   In this way, by widening the gap between the case and the rotor, it is possible to prevent the rotor from coming into contact with the inside of the case when the rotor rotates and the rotor from sliding on the inner peripheral surface of the case.

また、本発明の電動弁は、
前記雌ネジ部材が樹脂で形成されていることを特徴とする。
これにより、雌ネジ部材の摩擦係数を低くすることができ、耐久性を向上させることができる。 Moreover, the motor operated valve of the present invention is
The female screw member is made of resin.
Thereby, the friction coefficient of a female screw member can be made low and durability can be improved.

また、本発明の冷凍サイクルシステムは、
圧縮機、凝縮器、膨張弁、および蒸発器等を含む冷凍サイクルシステムであって、上述の電動弁を前記膨張弁として用いることを特徴とする。 In addition, the refrigeration cycle system of the present invention,
A refrigeration cycle system including a compressor, a condenser, an expansion valve, an evaporator, and the like, wherein the above-described electric valve is used as the expansion valve.

本発明に係る発明によれば、ロータを適正に回転させることができ、高い作動性を有する電動弁、および該電動弁を用いた冷凍サイクルシステムを提供することができる。   ADVANTAGE OF THE INVENTION According to the invention which concerns on this invention, a rotor can be rotated appropriately and the electrically operated valve which has high operativity, and the refrigerating cycle system using this electrically operated valve can be provided.

実施の形態に係る電動弁の断面図である。It is sectional drawing of the motor operated valve which concerns on embodiment. 実施の形態に係る電動弁のネジ結合部分の拡大断面図である。It is an expanded sectional view of the screw joint part of the motor operated valve concerning an embodiment. 実施の形態に係るブッシュ部材の弁軸の間の隙間の拡大断面図である。It is an expanded sectional view of the crevice between the valve shafts of the bush member concerning an embodiment. 実施の形態に係るケースとロータの間の隙間の拡大断面図である。It is an expanded sectional view of the crevice between a case and a rotor concerning an embodiment. 電動弁において、回転軸の軸芯が傾斜した状態を示す図である。In a motor operated valve, it is a figure which shows the state in which the axial center of the rotating shaft inclined. 従来の電動弁の断面図である。It is sectional drawing of the conventional motor operated valve. 電動弁において、弁軸が軸芯からずれてブッシュ部材に固定された状態を説明する断面図である。In a motor operated valve, it is sectional drawing explaining the state from which the valve shaft shifted | deviated from the axial center and was fixed to the bush member.

以下、図面を参照して、本発明の実施の形態に係る電動弁について説明する。図１は、実施の形態に係る電動弁２を示した断面図である。なお、本明細書において、「上」あるいは「下」とは図１の状態で規定したものである。すなわち、ロータ４は弁体１７より上方に位置している。
この電動弁２では、非磁性体の金属により筒状のカップ形状をなすケース６０の開口側の下方に、弁本体３０が溶接などにより一体的に接続されている。 Hereinafter, an electric valve according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view showing an electric valve 2 according to an embodiment. In the present specification, “upper” or “lower” is defined in the state of FIG. That is, the rotor 4 is positioned above the valve body 17.
In the motor-operated valve 2, the valve body 30 is integrally connected by welding or the like below the opening side of the case 60 having a cylindrical cup shape made of a non-magnetic metal.

ここで、弁本体３０は、ステンレス等の金属から成り、内部に弁室１１を有している。また、弁本体３０には、弁室１１に直接連通するステンレス製や銅製の第１の管継手１２が固定装着されている。さらに、弁本体３０の下方内側には、断面円形の弁ポート１６ａが形成された弁座部材１６が組み込まれている。弁座部材１６には、弁ポート１６ａを介して弁室１１に連通するステンレス製や銅製の第２の管継手１５が固定装着されている。   Here, the valve body 30 is made of a metal such as stainless steel and has the valve chamber 11 therein. The valve body 30 is fixedly mounted with a first pipe joint 12 made of stainless steel or copper that directly communicates with the valve chamber 11. Further, a valve seat member 16 in which a valve port 16a having a circular cross section is formed is incorporated in the lower inside of the valve body 30. A second pipe joint 15 made of stainless steel or copper that communicates with the valve chamber 11 via the valve port 16a is fixedly mounted on the valve seat member 16.

ケース６０の内周には、回転可能なロータ４が収容され、ロータ４の軸芯部分には、ブッシュ部材３３を介して弁軸４１が配置されている。ブッシュ部材３３で結合されたこの弁軸４１とロータ４とは、回転しながら上下方向に一体的に移動する。なお、この弁軸４１の中間部付近の外周面には雄ネジ４１ａが形成されている。本実施の形態では、弁軸４１が雄ネジ部材として機能している。   The rotatable rotor 4 is accommodated in the inner periphery of the case 60, and the valve shaft 41 is disposed on the shaft core portion of the rotor 4 via the bush member 33. The valve shaft 41 and the rotor 4 coupled by the bush member 33 move integrally in the vertical direction while rotating. A male screw 41 a is formed on the outer peripheral surface near the middle portion of the valve shaft 41. In the present embodiment, the valve shaft 41 functions as a male screw member.

ここで、ブッシュ部材３３は、ステンレス等の金属から成り、中央に弁軸４１が貫通する貫通孔３３ａが形成された円筒状の部材である。ロータ４は、磁性粉を含有するポリフェニレンサルファイド（ＰＰＳ）等の樹脂材料やフェライト磁石等の磁性を有する素材で形成されている。また、ブッシュ部材３３は、ロータ４にインサート成形により固定されている。なお、弁軸４１は、ブッシュ部材３３の貫通孔３３ａに弁軸４１を貫通させて溶接４１ｃすることにより、ブッシュ部材３３に固定される。このように、ロータ４とブッシュ部材３３、ブッシュ部材３３と弁軸４１がそれぞれ固定されることにより、ロータ４の回転が弁軸４１に伝達される。   Here, the bush member 33 is a cylindrical member made of a metal such as stainless steel and having a through-hole 33a through which the valve shaft 41 passes in the center. The rotor 4 is formed of a resin material such as polyphenylene sulfide (PPS) containing magnetic powder, or a magnetic material such as a ferrite magnet. The bush member 33 is fixed to the rotor 4 by insert molding. The valve shaft 41 is fixed to the bush member 33 by passing the valve shaft 41 through the through hole 33a of the bush member 33 and welding 41c. Thus, the rotation of the rotor 4 is transmitted to the valve shaft 41 by fixing the rotor 4 and the bush member 33, and the bush member 33 and the valve shaft 41, respectively.

ケース６０の外周には、図示しないヨーク、ボビン、およびコイルなどからなるステータが配置され、ロータ４とステータとでステッピングモータが構成されている。
ケース６０の天井面にはガイド支持体５２が固定されている。ガイド支持体５２は、円筒部５３と、円筒部５３の上端側に形成された傘状部５４とを有し、全体をプレス加工により一体成形されている。傘状部５４はケース６０の頂部内側と略同形状に成形されている。 On the outer periphery of the case 60, a stator including a yoke, a bobbin, and a coil (not shown) is arranged, and the rotor 4 and the stator constitute a stepping motor.
A guide support 52 is fixed to the ceiling surface of the case 60. The guide support body 52 has a cylindrical portion 53 and an umbrella-shaped portion 54 formed on the upper end side of the cylindrical portion 53, and the whole is integrally formed by pressing. The umbrella-shaped portion 54 is formed in substantially the same shape as the inside of the top portion of the case 60.

弁軸４１のブッシュ部材３３より下方には、後述するように弁軸４１との間でネジ結合Ａを構成するとともに弁軸４１の傾きを抑制する機能を有する弁軸ホルダ６が、弁本体３０に対して相対的に回転不能に固定されている。   Below the bush member 33 of the valve shaft 41, a valve shaft holder 6 that has a function of forming a screw coupling A with the valve shaft 41 and suppressing the inclination of the valve shaft 41 as will be described later. It is fixed to be relatively non-rotatable.

弁軸ホルダ６は、たとえば、ポリフェニレンサルファイド（ＰＰＳ）等の樹脂材料で形成されており、摩擦係数を低減させるため添加剤が含有されている。添加材としては、ポリテトラフルオロエチレン（ＰＴＦＥ）等のフッ素系樹脂やカーボンファイバー等が用いられる。   The valve shaft holder 6 is made of, for example, a resin material such as polyphenylene sulfide (PPS), and contains an additive for reducing the friction coefficient. As the additive, fluorine resin such as polytetrafluoroethylene (PTFE), carbon fiber, or the like is used.

この弁軸ホルダ６は、上部側の筒状小径部６ａと下部側の筒状大径部６ｂと弁本体３０の内周部側に収容される嵌合部６ｃとリング状のフランジ部６ｆとからなる。そして、弁軸ホルダ６のフランジ部６ｆは、弁本体３０の上端に溶接などで固定されている。また、弁軸ホルダ６の内部には、後述する弁ガイド１８を収容する収容室６ｈが形成されている。   The valve shaft holder 6 includes an upper cylindrical small diameter portion 6a, a lower cylindrical large diameter portion 6b, a fitting portion 6c accommodated on the inner peripheral side of the valve body 30, and a ring-shaped flange portion 6f. Consists of. The flange portion 6f of the valve shaft holder 6 is fixed to the upper end of the valve body 30 by welding or the like. A housing chamber 6h for housing a valve guide 18 (to be described later) is formed inside the valve shaft holder 6.

また、この弁軸ホルダ６の筒状小径部６ａの上部開口部６ｇから所定の深さまで下方に向かって雌ネジ６ｄが形成されている。このため、本実施の形態では、弁軸ホルダ６が雌ネジ部材として機能している。そして、弁軸４１の外周に形成された雄ネジ４１ａと、弁軸ホルダ６の筒状小径部６ａの内周に形成された雌ネジ６ｄとにより、ネジ結合Ａが構成されている。   A female screw 6d is formed downward from the upper opening 6g of the cylindrical small diameter portion 6a of the valve shaft holder 6 to a predetermined depth. For this reason, in this embodiment, the valve shaft holder 6 functions as a female screw member. The male screw 41a formed on the outer periphery of the valve shaft 41 and the female screw 6d formed on the inner periphery of the cylindrical small diameter portion 6a of the valve shaft holder 6 constitute a screw coupling A.

さらに、弁軸ホルダ６の筒状大径部６ｂの側面には、均圧孔５１が穿設され、この均圧孔５１により、筒状大径部６ｂ内の弁軸ホルダ室８３と、ロータ収容室６７（第２の背圧室）との間が連通している。このように均圧孔５１を設けることにより、ケース６０のロータ４を収容する空間と、弁軸ホルダ６内の空間とを連通することにより、弁軸ホルダ６の移動動作をスムーズに行うことができる。   Further, a pressure equalizing hole 51 is formed in a side surface of the cylindrical large diameter portion 6b of the valve shaft holder 6, and the pressure equalizing hole 51 allows the valve shaft holder chamber 83 in the cylindrical large diameter portion 6b and the rotor to be formed. The accommodation chamber 67 (second back pressure chamber) communicates with it. By providing the pressure equalizing hole 51 as described above, the movement of the valve shaft holder 6 can be smoothly performed by communicating the space in which the rotor 4 of the case 60 is accommodated with the space in the valve shaft holder 6. it can.

また、弁軸４１の下方には、筒状の弁ガイド１８が弁軸ホルダ６の収容室６ｈに対して摺動可能に配置されている。この弁ガイド１８は天井部２１側がプレス成形により略直角に折り曲げられている。そして、この天井部２１には貫通孔１８ａが形成されている。また、弁軸４１の下方には、さらに鍔部４１ｂが形成されている。   Further, a cylindrical valve guide 18 is disposed below the valve shaft 41 so as to be slidable with respect to the storage chamber 6 h of the valve shaft holder 6. The valve guide 18 is bent at a substantially right angle on the ceiling 21 side by press molding. A through hole 18 a is formed in the ceiling portion 21. A flange 41 b is further formed below the valve shaft 41.

ここで、弁軸４１は、弁ガイド１８に対して回転可能、かつ径方向に変位可能となるように弁ガイド１８の貫通孔１８ａに遊貫状態で挿入されており、鍔部４１ｂは、弁ガイド１８に対して回転可能、かつ、径方向に変位可能となるように弁ガイド１８内に配置されている。また、弁軸４１は貫通孔１８ａを挿通し、鍔部４１ｂの上面が、弁ガイド１８の天井部２１に対向するように配置されている。なお、鍔部４１ｂが弁ガイド１８の貫通孔１８ａより大径であることにより、弁軸４１の抜け止めがなされている。   Here, the valve shaft 41 is inserted into the through hole 18a of the valve guide 18 so as to be rotatable with respect to the valve guide 18 and displaceable in the radial direction. It arrange | positions in the valve guide 18 so that it can rotate with respect to the guide 18 and it can displace to radial direction. In addition, the valve shaft 41 is inserted through the through hole 18 a and is arranged so that the upper surface of the flange portion 41 b faces the ceiling portion 21 of the valve guide 18. The flange 41b is larger in diameter than the through hole 18a of the valve guide 18 so that the valve shaft 41 is prevented from coming off.

弁軸４１と弁ガイド１８とが互いに径方向に移動可能であることにより、弁軸ホルダ６および弁軸４１の配置位置に関して、さほど高度な同芯取付精度を求められることなく、弁ガイド１８および弁体１７との同芯性が得られる。   Since the valve shaft 41 and the valve guide 18 are movable in the radial direction with respect to each other, the valve guide 18 and the valve guide 18 and the valve shaft 41 are not required to have a high degree of concentric mounting accuracy with respect to the arrangement positions of the valve shaft holder 6 and the valve shaft 41. Concentricity with the valve body 17 is obtained.

弁ガイド１８の天井部２１と弁軸４１の鍔部４１ｂとの間には、中央部には貫通孔が形成されたワッシャ７０が設置されている。ワッシャ７０は、高滑性表面の金属製ワッシャ、フッ素樹脂等の高滑性樹脂ワッシャあるいは高滑性樹脂コーティングの金属製ワッシャ、高滑性樹脂を含有する各種樹脂ワッシャなどであることが好ましい。
さらに、弁ガイド１８内には、圧縮された弁バネ２７とバネ受け３５とが収容されている。 Between the ceiling portion 21 of the valve guide 18 and the flange portion 41b of the valve shaft 41, a washer 70 having a through-hole formed at the center is installed. The washer 70 is preferably a metal washer having a highly slippery surface, a highly slippery resin washer such as a fluororesin, a metal washer having a highly slippery resin coating, or various resin washers containing a highly slippery resin.
Further, a compressed valve spring 27 and a spring receiver 35 are accommodated in the valve guide 18.

次に、本発明の要点となる電動弁２を構成する部品の寸法関係について説明する。図２は、実施の形態に係る電動弁２のネジ結合Ａ部分の拡大断面図である。図２に示すように、結合Ａ部分における弁軸４１の外周には、雄ネジ４１ａが形成され、弁軸ホルダ６の筒状小径部６ａの内周には、雌ネジ６ｄが形成されている。なお、雌ネジ６ｄの内径は、雄ネジ４１ａの外径よりも大きくなるように設計されており、雄ネジ４１ａのネジ山４１ｍ、ネジ谷４１ｖと雌ネジ６ｄのネジ山６ｍ、ネジ谷６ｖとの間には、それぞれ径方向にクリアランス６６が形成されている。   Next, the dimensional relationship of the parts constituting the motor-operated valve 2 that is the main point of the present invention will be described. FIG. 2 is an enlarged cross-sectional view of a screw coupling A portion of the electric valve 2 according to the embodiment. As shown in FIG. 2, a male screw 41a is formed on the outer periphery of the valve shaft 41 in the coupling A portion, and a female screw 6d is formed on the inner periphery of the cylindrical small diameter portion 6a of the valve shaft holder 6. . The inner diameter of the female screw 6d is designed to be larger than the outer diameter of the male screw 41a. Clearances 66 are formed in the radial direction between the two.

また、図３は、実施の形態に係る電動弁２において、図１の円Ｂ内に示された部分の拡大断面図である。図３に示すように、貫通孔３３ａに貫通する部分の弁軸４１の外周４１ｏにネジは形成されておらず、ブッシュ部材３３の貫通孔３３ａの内周３３ｉと弁軸４１の外周４１ｏとの間には隙間３４が存在する。この隙間３４は、クリアランス６６よりも狭く形成されている。すなわち、貫通孔３３ａの内周径と弁軸４１（雄ネジ部材）の外周径との差は、以下の（１）、（２）に示す差のうちいずれか小さい方よりも小さくなるように形成されている。   FIG. 3 is an enlarged cross-sectional view of a portion shown in a circle B in FIG. 1 in the motor-operated valve 2 according to the embodiment. As shown in FIG. 3, no screw is formed on the outer periphery 41 o of the valve shaft 41 in the portion that penetrates the through hole 33 a, and the inner periphery 33 i of the through hole 33 a of the bush member 33 and the outer periphery 41 o of the valve shaft 41 are There is a gap 34 between them. The gap 34 is formed narrower than the clearance 66. That is, the difference between the inner peripheral diameter of the through-hole 33a and the outer peripheral diameter of the valve shaft 41 (male screw member) is made smaller than the smaller one of the differences shown in (1) and (2) below. Is formed.

（１）弁軸４１（雄ネジ部材）の雄ネジ４１ａの山径（ネジ山４１ｍの外周径）と弁軸ホルダ６（雌ネジ部材）の雌ネジ６ｄの谷径（ネジ谷６ｖの内周径）との差
（２）弁軸４１（雄ネジ部材）の雄ネジ４１ａの谷径（ネジ谷４１ｖの外周径）と弁軸ホルダ６（雌ネジ部材）の雌ネジ６ｄの山径（ネジ山６ｍの内周径）との差
さらに、図４は、実施の形態に係る電動弁２において、図１の円Ｃ内に示された部分の拡大断面図である。図４に示すように、電動弁２において、ケース６０の内周６０ｉとロータ４の外周４ｏの間には、クリアランス６６よりも広い隙間６８が存在する。すなわち、ケース６０の内周径とロータ４の外周径との差は、上述の（１）、（２）に示す差のうちいずれか大きい方よりも大きくなるように形成されている。 (1) The diameter of the male thread 41a (the outer diameter of the thread 41m) of the valve shaft 41 (male thread member) and the root diameter of the female thread 6d of the valve shaft holder 6 (female thread member) (the inner circumference of the thread valley 6v) (2) The root diameter of the male screw 41a (the outer peripheral diameter of the screw trough 41v) of the valve shaft 41 (male screw member) and the mountain diameter (screw) of the female screw 6d of the valve shaft holder 6 (female screw member) Further, FIG. 4 is an enlarged cross-sectional view of a portion shown in a circle C in FIG. 1 in the motor-operated valve 2 according to the embodiment. As shown in FIG. 4, in the motor operated valve 2, a gap 68 wider than the clearance 66 exists between the inner periphery 60 i of the case 60 and the outer periphery 4 o of the rotor 4. That is, the difference between the inner peripheral diameter of the case 60 and the outer peripheral diameter of the rotor 4 is formed to be larger than the larger one of the differences shown in the above (1) and (2).

この実施の形態に係る電動弁２によれば、ブッシュ部材３３の貫通孔３３ａと弁軸４１の間の隙間３４を、雄ネジ４１ａと雌ネジ６ｄとの間のクリアランス６６よりも狭くすることにより、ロータ４の回転時にロータ４が軸芯に対して偏芯することを抑制することができる。よって、ロータ４を適正に回転させることができ、高い作動性を有する電動弁２を提供することができる。   According to the motor-operated valve 2 according to this embodiment, the gap 34 between the through hole 33a of the bush member 33 and the valve shaft 41 is made narrower than the clearance 66 between the male screw 41a and the female screw 6d. The rotor 4 can be prevented from being eccentric with respect to the axis when the rotor 4 rotates. Therefore, the rotor 4 can be rotated appropriately and the motor-operated valve 2 having high operability can be provided.

なお、上述したように、弁軸ホルダ６（雌ネジ部材）は、ポリフェニレンサルファイド（ＰＰＳ）等の樹脂で形成されているため、摩擦係数が低く耐久性に優れている。一方、一般に射出成形により成形される樹脂製の部品は、射出成形によるヒケや反り等の寸法変形や、線膨張、膨潤等の樹脂成形特有の寸法変化を考慮すると、精密な成形は困難である場合が多い。   As described above, since the valve shaft holder 6 (female screw member) is made of resin such as polyphenylene sulfide (PPS), it has a low coefficient of friction and excellent durability. On the other hand, in general, resin parts molded by injection molding are difficult to accurately mold in consideration of dimensional deformation such as sink and warp due to injection molding, and dimensional changes peculiar to resin molding such as linear expansion and swelling. There are many cases.

このため、樹脂製の弁軸ホルダ６を採用した場合には、雄ネジ４１ａと雌ネジ６ｄの噛み合いに生じるクリアランス６６が大きくなりやすくなる傾向がある。クリアランス６６が大きくなると、図５に示すように、ロータ４だけでなく弁軸４１（雄ネジ部材）までもが偏った軸を中心に回転するおそれがある。   For this reason, when the resin valve shaft holder 6 is employed, the clearance 66 generated when the male screw 41a and the female screw 6d are engaged with each other tends to increase. If the clearance 66 becomes large, as shown in FIG. 5, there is a possibility that not only the rotor 4 but also the valve shaft 41 (male screw member) rotates around a biased shaft.

しかしながら、ブッシュ部材３３の貫通孔３３ａと弁軸４１の間の隙間３４を、雄ネジ４１ａと雌ネジ６ｄとの間のクリアランス６６よりも狭くすることにより、ロータ４が偏心することを抑制できる。このため、電動弁２において弁軸ホルダ６（雌ネジ部材）を樹脂製とした場合における、作動性に対する影響を低減することができる効果は顕著なものとなる。   However, by making the gap 34 between the through hole 33a of the bush member 33 and the valve shaft 41 smaller than the clearance 66 between the male screw 41a and the female screw 6d, the rotor 4 can be prevented from being eccentric. For this reason, the effect which can reduce the influence with respect to operativity in the case where the valve shaft holder 6 (female screw member) is made of resin in the motor-operated valve 2 becomes remarkable.

また、実施の形態に係る電動弁２によれば、ケース６０の内周とロータ４の外周の間の隙間６８を広げ、クリアランス６６よりも大きくすることにより、ロータ４の回転時にロータ４がケース６０の内側に接触し、ロータ４がケース６０の内周面に摺動することを防止することができる。したがって、ロータ４を高い精度で適正に回転させることができる。   In addition, according to the motor-operated valve 2 according to the embodiment, the gap 4 between the inner periphery of the case 60 and the outer periphery of the rotor 4 is widened to be larger than the clearance 66, so that the rotor 4 is in the case when the rotor 4 rotates. It is possible to prevent the rotor 4 from sliding on the inner peripheral surface of the case 60 by contacting the inside of the rotor 60. Therefore, the rotor 4 can be appropriately rotated with high accuracy.

ここで、樹脂製の弁軸ホルダ６を採用した場合、雄ネジ４１ａと雌ネジ６ｄとの間のクリアランス６６が大きくなることで、図５に示すように、回転軸の軸芯が傾斜し、ロータ４がケース６０と接触して（円Ｆ内参照）、ロータ４の回転が阻害されることも考えられる。   Here, when the resin valve shaft holder 6 is employed, the clearance 66 between the male screw 41a and the female screw 6d is increased, so that the axis of the rotating shaft is inclined as shown in FIG. It is also conceivable that the rotor 4 comes into contact with the case 60 (refer to the inside of the circle F) and the rotation of the rotor 4 is inhibited.

しかしながら、ケース６０の内周とロータ４の外周の間の隙間６８（図４参照）を広げ、隙間６８をクリアランス６６よりも大きくすることにより、弁軸ホルダ６（雌ネジ部材）を樹脂製とした場合であってもロータ４がケース６０と接触しないようにすることができる。   However, by opening a gap 68 (see FIG. 4) between the inner periphery of the case 60 and the outer periphery of the rotor 4 and making the gap 68 larger than the clearance 66, the valve shaft holder 6 (female screw member) is made of resin. Even in this case, the rotor 4 can be prevented from contacting the case 60.

なお、ロータ４とケース６０との隙間６８の間隔は、過剰に広くする必要性がない。このため、ロータ４とケース６０との隙間６８を広げても、隙間６８を所定の間隔以下に維持することができれば、ロータ４とコイルとのエアギャップを小さく抑えることができ、トルクの減少を低減することができる。   Note that the gap 68 between the rotor 4 and the case 60 need not be excessively wide. For this reason, even if the gap 68 between the rotor 4 and the case 60 is widened, if the gap 68 can be maintained at a predetermined distance or less, the air gap between the rotor 4 and the coil can be kept small, and the torque can be reduced. Can be reduced.

また、本実施の形態の電動弁２においては、ブッシュ部材３３がロータ４とは別々の部材である場合を例に説明しているが、ロータ４とブッシュ部材３３は、一つの部材として形成されていてもよい。この場合においても、ロータ４の回転は弁軸４１に伝達される。   In the motor-operated valve 2 of the present embodiment, the case where the bush member 33 is a separate member from the rotor 4 is described as an example. However, the rotor 4 and the bush member 33 are formed as one member. It may be. Even in this case, the rotation of the rotor 4 is transmitted to the valve shaft 41.

また、本実施の形態の電動弁２においては、弁軸ホルダ６（雌ネジ部材）が樹脂で形成されている場合を例に説明しているが、弁軸ホルダ６は、金属で形成されていてもよい。弁軸ホルダ６が金属製であっても、雄ネジ４１ａと雌ネジ６ｄとの間のクリアランス６６が大きければ、ブッシュ部材３３の貫通孔３３ａと弁軸４１の間の隙間３４を狭くすることにより、ロータ回転時にロータ４が軸芯に対して偏芯することを抑制することができる。   Further, in the motor-operated valve 2 of the present embodiment, the case where the valve shaft holder 6 (female screw member) is formed of resin is described as an example, but the valve shaft holder 6 is formed of metal. May be. Even if the valve shaft holder 6 is made of metal, if the clearance 66 between the male screw 41a and the female screw 6d is large, the gap 34 between the through hole 33a of the bush member 33 and the valve shaft 41 is narrowed. The rotor 4 can be prevented from being eccentric with respect to the axis when the rotor rotates.

なお、本実施の形態の電動弁２は、たとえば、圧縮機、凝縮器、膨張弁、および蒸発器等から成る冷凍サイクルシステムにおいて、凝縮器と蒸発器との間に設けられる膨張弁として用いられる。   The motor-operated valve 2 of the present embodiment is used as an expansion valve provided between the condenser and the evaporator, for example, in a refrigeration cycle system including a compressor, a condenser, an expansion valve, and an evaporator. .

２ 電動弁
４ ロータ
４ｏ ロータの外周
６ 弁軸ホルダ
６ａ 筒状小径部
６ｄ 雌ネジ
６ｍ 雌ネジのネジ山
６ｖ 雌ネジのネジ谷
１７ 弁体
３３ ブッシュ部材
３３ａ 貫通孔
３３ｉ 貫通孔の内周
３４ 隙間
４１ 弁軸
４１ａ 雄ネジ
４１ｃ 溶接
４１ｍ 雄ネジのネジ山
４１ｏ 弁軸の外周
４１ｖ 雄ネジのネジ谷
６０ ケース
６０ｉ ケースの内周
６６ クリアランス
６８ 隙間 2 Motorized valve 4 Rotor 4o Rotor outer periphery 6 Valve shaft holder 6a Tubular small diameter portion 6d Female screw 6m Female screw thread 6v Female screw thread trough 17 Valve element 33 Bush member 33a Through hole 33i Through hole 34 Clearance 41 Valve shaft 41a Male screw 41c Welding 41m Male screw thread 41o Valve shaft outer periphery 41v Male screw thread valley 60 Case 60i Case inner periphery 66 Clearance 68 Clearance

Claims (4)

ケースの内周に収容されたロータの回転運動を、雄ネジ部材と雌ネジ部材とのネジ螺合により直線運動に変換し、この直線運動に基づいて弁本体内に収容された弁体を軸方向に移動させる電動弁であって、
前記雄ネジ部材が貫通して固定される貫通孔が形成され、前記ロータの回転を前記雄ネジ部材に伝達するブッシュ部材を備え、
前記貫通孔の内周径と前記雄ネジ部材の外周径との差が、
前記雄ネジ部材の雄ネジの山径と前記雌ネジ部材の雌ネジの谷径との差と、前記雄ネジ部材の雄ネジの谷径と前記雌ネジ部材の雌ネジの山径との差のうちいずれか小さい方よりも小さいことを特徴とする電動弁。 The rotational motion of the rotor accommodated in the inner periphery of the case is converted into linear motion by screwing the male screw member and the female screw member, and the valve body accommodated in the valve body is pivoted based on this linear motion. A motorized valve that moves in a direction,
A through hole is formed through which the male screw member is fixed, and includes a bush member that transmits the rotation of the rotor to the male screw member.
The difference between the inner diameter of the through hole and the outer diameter of the male screw member is
The difference between the male thread crest diameter of the male screw member and the female thread trough diameter of the female screw member, and the difference between the male thread trough diameter of the male screw member and female thread crest diameter of the female screw member. The motor-operated valve characterized by being smaller than any one of them. 前記ケースの内周径と前記ロータの外周径との差が、
前記雄ネジ部材の雄ネジの山径と前記雌ネジ部材の雌ネジの谷径との差と、前記雄ネジ部材の雄ネジの谷径と前記雌ネジ部材の雌ネジの山径との差のうちいずれか大きい方よりも大きいことを特徴とする請求項１記載の電動弁。 The difference between the inner diameter of the case and the outer diameter of the rotor is
The difference between the male thread crest diameter of the male screw member and the female thread trough diameter of the female screw member, and the difference between the male thread trough diameter of the male screw member and female thread crest diameter of the female screw member. The motor-operated valve according to claim 1, wherein the motor-operated valve is larger than any one of them. 前記雌ネジ部材は、樹脂で形成されていることを特徴とする請求項１または２記載の電動弁。   The motor-operated valve according to claim 1 or 2, wherein the female screw member is made of resin. 圧縮機、凝縮器、膨張弁、および蒸発器等を含む冷凍サイクルシステムであって、請求項１〜３の何れか一項に記載の電動弁を前記膨張弁として用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, an evaporator, and the like, wherein the motor-operated valve according to any one of claims 1 to 3 is used as the expansion valve. system.
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