JP2019007549A - Motor valve and refrigeration cycle system - Google Patents

Motor valve and refrigeration cycle system Download PDF

Info

Publication number
JP2019007549A
JP2019007549A JP2017123609A JP2017123609A JP2019007549A JP 2019007549 A JP2019007549 A JP 2019007549A JP 2017123609 A JP2017123609 A JP 2017123609A JP 2017123609 A JP2017123609 A JP 2017123609A JP 2019007549 A JP2019007549 A JP 2019007549A
Authority
JP
Japan
Prior art keywords
port
valve
joint pipe
inner diameter
secondary joint
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2017123609A
Other languages
Japanese (ja)
Other versions
JP6740179B2 (en
Inventor
大樹 中川
Daiki Nakagawa
大樹 中川
一也 小林
Kazuya Kobayashi
一也 小林
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Saginomiya Seisakusho Inc
Original Assignee
Saginomiya Seisakusho Inc
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Saginomiya Seisakusho Inc filed Critical Saginomiya Seisakusho Inc
Priority to JP2017123609A priority Critical patent/JP6740179B2/en
Priority to CN201810510173.6A priority patent/CN109114237B/en
Publication of JP2019007549A publication Critical patent/JP2019007549A/en
Application granted granted Critical
Publication of JP6740179B2 publication Critical patent/JP6740179B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/42—Valve seats
    • 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
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/0254—Construction of housing; Use of materials therefor of lift valves with conical shaped valve members
    • 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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
    • 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • 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

Abstract

To reduce noise due to flow of refrigerant at a valve port, in a motor valve configured to open/close the valve port with a needle valve to control a flow rate of refrigerant.SOLUTION: In a valve seat part 1B, formed are a first port 11 having a circular cross section and an inner diameter D1, a second port 12 having an inner diameter D2, a third port 13 having an inner diameter D3, a first taper part 14, and a second taper part 15. The relationship between the inner diameter D3 of a secondary joint pipe 22 side end part of the third port 13 and the inner diameter D4 of the secondary joint pipe 22 satisfies D3=D4. In both of a first flow state that refrigerant flows from a gap between the first port 11 and a needle part 5a to the second port 12, and a second flow state that the refrigerant flows from the secondary joint pipe 22 to the third port 13, the flow of the refrigerant is rectified and then stabilized.SELECTED DRAWING: Figure 2

Description

本発明は、空気調和機等において冷媒の流量を制御する電動弁に関し、特に、ニードル弁に対する弁ポートの形状を改良した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 electric valve that controls the flow rate of a refrigerant in an air conditioner or the like, and more particularly, to an electric valve and a refrigeration cycle system in which the shape of a valve port for a needle valve is improved.

従来、冷凍サイクルシステムにおいて、冷媒の流量を制御する電動弁から発生する、冷媒通過に伴う騒音がしばしば問題となることがある。このような騒音対策を施すようにした電動弁として、例えば特開２０１３−２３４７２６号公報（特許文献１）及び特開２０１２−８２８９６号公報（特許文献２）に開示されたものがある。   Conventionally, in a refrigeration cycle system, noise accompanying the passage of refrigerant, which is generated from an electric valve that controls the flow rate of the refrigerant, often becomes a problem. For example, Japanese Patent Application Laid-Open No. 2013-234726 (Patent Document 1) and Japanese Patent Application Laid-Open No. 2012-82896 (Patent Document 2) have disclosed motor-driven valves that take such noise countermeasures.

特許文献１及び特許文献２の電動弁は、弁ハウジングの側面側から弁室に連通する一次継手管と、弁ハウジングの下部の端部から弁ポートを介して弁室に連通する二次継手管とを有している。そして、冷凍サイクルシステムの例えば暖房運転時には一次継手管から弁室に冷媒が流入し、弁室からニードル弁と弁ポートとの間隙を介して二次継手管に冷媒が流出される。一方、冷房運転時には、二次継手管からニードル弁と弁ポートとの間隙を介して弁室に冷媒が流入し、弁室から一次継手管に冷媒が流出される。   The motor-operated valves of Patent Document 1 and Patent Document 2 include a primary joint pipe that communicates with the valve chamber from the side of the valve housing, and a secondary joint pipe that communicates with the valve chamber from the lower end of the valve housing via the valve port. And have. For example, during heating operation of the refrigeration cycle system, the refrigerant flows from the primary joint pipe into the valve chamber, and the refrigerant flows out from the valve chamber to the secondary joint pipe through the gap between the needle valve and the valve port. On the other hand, during the cooling operation, the refrigerant flows into the valve chamber from the secondary joint pipe through the gap between the needle valve and the valve port, and the refrigerant flows out from the valve chamber to the primary joint pipe.

そして、これら特許文献１及び特許文献２の電動弁は、弁ポートの形状を改良することにより、弁室から二次継手管に冷媒が流出するときの冷媒通過音等を低減するようにしている。   And the electric valve of these patent documents 1 and patent documents 2 is trying to reduce refrigerant passage sound etc. when a refrigerant flows out from a valve room to a secondary joint pipe by improving the shape of a valve port. .

特開２０１３−２３４７２６号公報JP 2013-234726 A 特開２０１２−８２８９６号公報JP 2012-82896 A

特許文献１及び特許文献２の電動弁では、いずれも弁室からニードル弁と弁ポートとの間隙を介して二次継手管に冷媒が流出する状態での騒音を低減する効果が得られるが、二次継手管からニードル弁と弁ポートとの間隙を介して弁室に冷媒が流入する、逆方向の冷媒通過音等に対しては考慮されておらず、改良の余地がある。例えば、二次継手管と弁ポートとの境界部分で径が異なるので、二次継手管から冷媒が流入するときに、縮流が発生して流れの損失が生じるとともに、冷媒通過音等が発生し易くなる。   In the motor-operated valves of Patent Document 1 and Patent Document 2, an effect of reducing noise in a state where the refrigerant flows out from the valve chamber to the secondary joint pipe through the gap between the needle valve and the valve port can be obtained. There is room for improvement because there is no consideration for the refrigerant passing sound in the reverse direction in which the refrigerant flows into the valve chamber from the secondary joint pipe through the gap between the needle valve and the valve port. For example, because the diameter is different at the boundary between the secondary joint pipe and the valve port, when refrigerant flows in from the secondary joint pipe, a contracted flow occurs and a flow loss occurs, and a refrigerant passing sound or the like occurs. It becomes easy to do.

本発明は、冷媒を一次継手管から弁室に流入させて、弁室からニードル弁と弁ポートとの間隙を介して二次継手管に冷媒を流出させる状態と、二次継手管からニードル弁と弁ポートとの間隙を介して弁室に冷媒を流入させる状態との、双方向の流れに対して冷媒通過音等の騒音を低減した電動弁を提供することを課題とする。   The present invention relates to a state in which refrigerant flows into the valve chamber from the primary joint pipe, and flows out from the valve chamber to the secondary joint pipe through a gap between the needle valve and the valve port, and from the secondary joint pipe to the needle valve. It is an object of the present invention to provide a motor-operated valve in which noise such as refrigerant passing sound is reduced with respect to a bidirectional flow in a state where refrigerant flows into the valve chamber through a gap between the valve port and the valve port.

請求項１の電動弁は、一次継手管が連通される弁室と二次継手管とを、ニードル弁で開口面積が増減される弁ポートを介して連通可能とする電動弁であって、前記弁室と前記二次継手管との間に前記弁ポートを有する弁座部を備えるとともに、前記弁ポートに、弁室側の第１ポートと、第１ポートより内径の大きな第２ポートと、前記第１ポートと前記第２ポートとを繋ぐ第１テーパ部と、を備えた電動弁において、前記弁ポートに、前記二次継手管に連通する第３ポートと、前記第２ポートと前記第３ポートとを繋ぐ第２テーパ部とを備え、前記第１ポートの内径Ｄ１と前記第２ポートの内径Ｄ２と前記第３ポートの前記二次継手管側端部の内径Ｄ３と前記二次継手管の内径Ｄ４との関係がＤ１＜Ｄ２＜Ｄ３＝Ｄ４となっていることを特徴とする。   The motor-operated valve according to claim 1 is a motor-operated valve that enables communication between a valve chamber that communicates with a primary joint pipe and a secondary joint pipe via a valve port whose opening area is increased or decreased by a needle valve, A valve seat having the valve port is provided between the valve chamber and the secondary joint pipe, the valve port includes a first port on the valve chamber side, and a second port having a larger inner diameter than the first port, A motor-operated valve comprising: a first taper portion that connects the first port and the second port; a third port that communicates with the secondary joint pipe, the second port, and the second port; A second taper portion connecting the three ports, the inner diameter D1 of the first port, the inner diameter D2 of the second port, the inner diameter D3 of the secondary joint pipe side end portion of the third port, and the secondary joint The relationship with the inner diameter D4 of the tube is D1 <D2 <D3 = D4. To.

請求項２の電動弁は、請求項１に記載の電動弁であって、
Ｄ２−Ｄ１≦Ｄ３−Ｄ２
となっていることを特徴とする。 The motor-driven valve according to claim 2 is the motor-operated valve according to claim 1,
D2-D1 ≦ D3-D2
It is characterized by becoming.

請求項３の電動弁は、請求項１または２のいずれか一項に記載の電動弁であって、前記第３ポートが前記二次継手管の内径部の一部であることを特徴とする。   The motor-operated valve according to claim 3 is the motor-operated valve according to claim 1 or 2, wherein the third port is a part of an inner diameter portion of the secondary joint pipe. .

請求項４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、請求項１乃至３のいずれか一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。   The refrigeration cycle system according to claim 4 is 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. It is used as the expansion valve.

請求項１乃至３の電動弁によれば、第１ポートとニードル弁との隙間から流れる冷媒が第２ポートに流出したとき、第２ポート内で圧力を急激に回復させることがなく、流れを整流化して冷媒の流れを安定化することができ、キャビテーションの破裂を抑制することができる。また、第２ポートから第２テーパ部と第３ポートに流れるときに、流速が減速するので流速音を低減することができる。さらに、二次継手管から冷媒を流したとき、二次継手管から第３ポートへの冷媒の流れが整流化されるので、縮流発生等による流れの損失もなく、冷媒の流れを安定化することができる。したがって、騒音を低減することができる。   According to the electric valve of the first to third aspects, when the refrigerant flowing from the gap between the first port and the needle valve flows out to the second port, the pressure is not rapidly recovered in the second port, The flow of refrigerant can be stabilized by rectification, and cavitation bursting can be suppressed. Moreover, since the flow velocity is reduced when flowing from the second port to the second tapered portion and the third port, the flow velocity sound can be reduced. Furthermore, when the refrigerant flows from the secondary joint pipe, the flow of the refrigerant from the secondary joint pipe to the third port is rectified, so there is no flow loss due to the occurrence of contraction, etc., and the refrigerant flow is stabilized. can do. Therefore, noise can be reduced.

請求項２の電動弁によれば、Ｄ２−Ｄ１≦Ｄ３−Ｄ２となっているので、第２ポートに対して、第２テーパ部から第３ポートにかけて大きく拡径するので、流速の減速効果が高くなり、さらに流速音を低減することができる。   According to the motor-driven valve of claim 2, since D2-D1 ≦ D3-D2, the diameter of the second port is greatly expanded from the second taper portion to the third port. It becomes higher and the flow velocity sound can be further reduced.

請求項３の電動弁によれば、第３ポートが二次継手管の内径部の一部により構成されているので、弁ポートを形成するための加工が容易になる。   According to the motor-driven valve of the third aspect, since the third port is constituted by a part of the inner diameter portion of the secondary joint pipe, the processing for forming the valve port is facilitated.

請求項４の冷凍サイクルシステムによれば、請求項１乃至３と同様な効果が得られる。   According to the refrigeration cycle system of claim 4, the same effects as in claims 1 to 3 can be obtained.

本発明の第１実施形態の電動弁の縦断面図である。It is a longitudinal cross-sectional view of the motor operated valve of 1st Embodiment of this invention. 本発明の第１実施形態の電動弁における弁ポート近傍の要部拡大縦断面図である。It is a principal part expanded longitudinal cross-sectional view of the valve port vicinity in the motor operated valve of 1st Embodiment of this invention. 本発明の第１実施形態の実施形態の電動弁における弁ポートの作用を説明する図である。It is a figure explaining the effect | action of the valve port in the motor operated valve of embodiment of 1st Embodiment of this invention. 本発明の実施形態の電動弁を用いた空気調和機の一例を示す図である。It is a figure which shows an example of the air conditioner using the motor operated valve of embodiment of this invention. 本発明の第２実施形態の電動弁における弁ポート近傍の要部拡大縦断面図である。It is a principal part expansion longitudinal cross-sectional view of the valve port vicinity in the motor operated valve of 2nd Embodiment of this invention. 本発明の第３実施形態の電動弁における弁ポート近傍の要部拡大縦断面図である。It is a principal part expanded longitudinal cross-sectional view of the valve port vicinity in the motor operated valve of 3rd Embodiment of this invention. 本発明の第４実施形態の電動弁における弁ポート近傍の要部拡大縦断面図である。It is a principal part expanded longitudinal cross-sectional view of the valve port vicinity in the motor operated valve of 4th Embodiment of this invention.

次に、本発明の電動弁の実施の形態を図面を参照して説明する。図１は第１実施形態の電動弁の縦断面図、図２は第１実施形態の電動弁における弁ポート近傍の要部拡大縦断面図、図３は第１実施形態の電動弁における弁ポートの作用を説明する図、図４は実施形態の電動弁を用いた空気調和機の一例を示す図である。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。   Next, an embodiment of the motor-operated valve of the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal sectional view of the motor-operated valve according to the first embodiment, FIG. 2 is an enlarged longitudinal sectional view of a main part near the valve port in the motor-operated valve according to the first embodiment, and FIG. 3 is a valve port of the motor-operated valve according to the first embodiment. FIG. 4 is a diagram illustrating an example of an air conditioner using the motor operated valve according to the embodiment. Note that the concept of “upper and lower” in the following description corresponds to the upper and lower sides in the drawing of FIG.

まず、図４に基づいて実施形態に係る空気調和機について説明する。空気調和機は、膨張弁としての実施形態の電動弁１０、室外ユニット１００に搭載された室外熱交換器２０、室内ユニット２００に搭載された室内熱交換器３０、流路切換弁４０、圧縮機５０を有しており、これらの各要素は、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システムを構成している。この冷凍サイクルシステムは本発明の電動弁を適用する冷凍サイクルシステムの一例であり、本発明の電動弁は。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。   First, the air conditioner according to the embodiment will be described with reference to FIG. The air conditioner includes an electric valve 10 as an expansion valve, an outdoor heat exchanger 20 mounted on the outdoor unit 100, an indoor heat exchanger 30 mounted on the indoor unit 200, a flow path switching valve 40, and a compressor. Each of these elements is connected by a conduit as shown in the figure to constitute a heat pump type refrigeration cycle system. This refrigeration cycle system is an example of a refrigeration cycle system to which the electric valve of the present invention is applied, and the electric valve of the present invention. The present invention can also be applied to other systems such as a diaphragm device on the indoor unit side such as a multi air conditioner for buildings.

冷凍サイクルシステムの流路は流路切換弁４０により暖房モードおよび冷房モードの２通りの流路に切換えられ、暖房モードでは実線の矢印で示すように、圧縮機５０で圧縮された冷媒が流路切換弁４０から室内熱交換器３０に流入され、室内熱交換器３０から流出する冷媒が、管路６０を通って電動弁１０に流入される。そして、この電動弁１０で冷媒が膨張され、室外熱交換器２０、流路切換弁４０、圧縮機５０の順に循環される。冷房モードでは、破線の矢印で示すように、圧縮機５０で圧縮された冷媒が流路切換弁４０から室外熱交換器２０に流入され、室外熱交換器２０から流出する冷媒が電動弁１０で膨張され、管路６０を流れて室内熱交換器３０に流入される。この室内熱交換器３０に流入された冷媒は、流路切換弁４０を介して圧縮機５０に流入される。なお、この図４に示す例では、暖房モード時に、冷媒を電動弁１０の一次継手管２１から二次継手管２２へ流す構成となっているが、配管の接続を逆にして、暖房モード時に、冷媒を二次継手管２２から一次継手管２１へ流す構成としてもよい。   The flow path of the refrigeration cycle system is switched to two flow paths of the heating mode and the cooling mode by the flow path switching valve 40. In the heating mode, the refrigerant compressed by the compressor 50 is flowed as indicated by solid arrows. The refrigerant that flows into the indoor heat exchanger 30 from the switching valve 40 and flows out of the indoor heat exchanger 30 flows into the motor-operated valve 10 through the pipe line 60. Then, the refrigerant is expanded by the electric valve 10 and circulated in the order of the outdoor heat exchanger 20, the flow path switching valve 40, and the compressor 50. In the cooling mode, the refrigerant compressed by the compressor 50 flows into the outdoor heat exchanger 20 from the flow path switching valve 40 and the refrigerant flowing out of the outdoor heat exchanger 20 flows through the motor operated valve 10 as indicated by the dashed arrows. It is expanded, flows through the pipe line 60 and flows into the indoor heat exchanger 30. The refrigerant that has flowed into the indoor heat exchanger 30 flows into the compressor 50 via the flow path switching valve 40. In the example shown in FIG. 4, the refrigerant is configured to flow from the primary joint pipe 21 to the secondary joint pipe 22 in the heating valve 10 during the heating mode. The refrigerant may flow from the secondary joint pipe 22 to the primary joint pipe 21.

電動弁１０は、冷媒の流量を制御する膨張弁（絞り装置）として働き、暖房モードでは、室外熱交換器２０が蒸発器として機能し、室内熱交換器３０が凝縮器として機能し、室内の暖房がなされる。また、冷房モードでは、室外熱交換器２０が凝縮器として機能し、室内熱交換器３０が蒸発器として機能し、室内の冷房がなされる。   The motor-operated valve 10 functions as an expansion valve (throttle device) that controls the flow rate of the refrigerant. In the heating mode, the outdoor heat exchanger 20 functions as an evaporator, the indoor heat exchanger 30 functions as a condenser, Heating is done. In the cooling mode, the outdoor heat exchanger 20 functions as a condenser, the indoor heat exchanger 30 functions as an evaporator, and the room is cooled.

次に、図１及び図２に基づいて第１実施形態の電動弁１０について説明する。この電動弁１０は、ステンレスや真鍮等の金属部材の切削加工等により形成された弁ハウジング１を有しており、弁ハウジング１には弁室１Ａが形成されている。また、この電動弁１０は、弁室１Ａの下部に弁座部１Ｂ（この実施形態では弁ハウジング１の一部）を備えている。また、弁座部１Ｂには第１ポート１１と、第２ポート１２と、第３ポート１３とが形成されている。また、第１ポート１１と第２ポート１２との間に第１テーパ部１４が形成され、第２ポート１２と第３ポート１３との間に第２テーパ部１５が形成されている。これら第１ポート１１、第１テーパ部１４、第２ポート１２、第２テーパ部１５及び第３ポート１３は「弁ポート」を構成している。さらに、弁ハウジング１には、側面側から弁室１Ａに連通する一次継手管２１が取り付けられるとともに、弁室１Ａの軸線Ｘ方向の片側端部に二次継手管２２が取り付けられている。そして、第１ポート１１、第１テーパ部１４、第２ポート１２、第２テーパ部１５及び第３ポート１３を介して、弁室１Ａと二次継手管２２とが導通可能となっている。   Next, based on FIG.1 and FIG.2, the motor operated valve 10 of 1st Embodiment is demonstrated. The electric valve 10 has a valve housing 1 formed by cutting a metal member such as stainless steel or brass, and the valve housing 1 is formed with a valve chamber 1A. The motor-operated valve 10 includes a valve seat portion 1B (a part of the valve housing 1 in this embodiment) below the valve chamber 1A. The valve seat portion 1B is formed with a first port 11, a second port 12, and a third port 13. A first taper portion 14 is formed between the first port 11 and the second port 12, and a second taper portion 15 is formed between the second port 12 and the third port 13. The first port 11, the first tapered portion 14, the second port 12, the second tapered portion 15, and the third port 13 constitute a “valve port”. Further, a primary joint pipe 21 communicating with the valve chamber 1A from the side surface side is attached to the valve housing 1, and a secondary joint pipe 22 is attached to one end portion in the axis X direction of the valve chamber 1A. The valve chamber 1 </ b> A and the secondary joint pipe 22 can be electrically connected via the first port 11, the first tapered portion 14, the second port 12, the second tapered portion 15, and the third port 13.

弁ハウジング１には、上部から弁室１Ａ内に挿通されるように弁ガイド部材２３が圧入及びかしめにより取り付けられており、この弁ガイド部材２３の中心には弁ガイド孔２３ａが形成されている。また、弁ハウジング１の上端部には弁ガイド部材２３の上端外周部を囲うようにリム１ａが形成されており、弁ハウジング１には、リム１ａの外周に嵌合するように円筒状のケース２４が組み付けられている。このケース２４は、リム１ａをかしめるとともに、底部外周をろう付けすることにより弁ハウジング１に固着されている。さらに、ケース２４の上端開口部には固定金具３１を介して支持部材３が取り付けられている。   A valve guide member 23 is attached to the valve housing 1 by press-fitting and caulking so as to be inserted into the valve chamber 1A from above, and a valve guide hole 23a is formed at the center of the valve guide member 23. . A rim 1a is formed at the upper end of the valve housing 1 so as to surround the outer periphery of the upper end of the valve guide member 23. The valve housing 1 has a cylindrical case so as to be fitted to the outer periphery of the rim 1a. 24 is assembled. The case 24 is fixed to the valve housing 1 by caulking the rim 1a and brazing the outer periphery of the bottom. Further, the support member 3 is attached to the upper end opening of the case 24 via a fixing bracket 31.

支持部材３の中心には、第１ポート１１の軸線Ｘと同軸の雌ねじ部３ａとそのネジ孔が形成されるとともに、雌ねじ部３ａのネジ孔の外周よりも径の大きな円筒状のスライド孔３ｂが形成されている。そして、雌ねじ部３ａのネジ孔とスライド孔３ａの中に後述の円柱棒状のロータ軸６２が配設されている。また、スライド孔３ｂには弁ホルダ４が軸線Ｘ方向に摺動可能に嵌合されており、この弁ホルダ４は上部をロータ軸６２に連結されるとともに、下部にニードル弁５を保持している。   At the center of the support member 3, a female screw portion 3a coaxial with the axis X of the first port 11 and its screw hole are formed, and a cylindrical slide hole 3b having a diameter larger than the outer periphery of the screw hole of the female screw portion 3a. Is formed. A cylindrical rod-shaped rotor shaft 62, which will be described later, is disposed in the screw hole and the slide hole 3a of the female screw portion 3a. A valve holder 4 is fitted in the slide hole 3b so as to be slidable in the direction of the axis X. The valve holder 4 is connected to the rotor shaft 62 at the upper part and holds the needle valve 5 at the lower part. Yes.

弁ホルダ４は、筒状の円筒部４１の下端にボス部４２が固着されるとともに、円筒部４１内にバネ受け４３と圧縮コイルバネ４４とワッシャ４５とスペーサ４６とを備えている。ニードル弁５は、ステンレスや真鍮等の金属部材により形成され、下側先端の略楕円体状のニードル部５ａと円柱棒状のロッド部５ｂと上端のフランジ部５ｃとを有している。そして、ニードル弁５は、弁ホルダ４のボス部４２の挿通孔４２ａ内に挿通されるとともに、フランジ部５ｃをボス部４２に当接させて弁ホルダ４に取り付けられている。また、ニードル弁５のロッド部５ｂは弁ガイド部材２３の弁ガイド孔２３ａ内に挿通されている。   The valve holder 4 has a boss portion 42 fixed to the lower end of a cylindrical cylindrical portion 41, and a spring receiver 43, a compression coil spring 44, a washer 45, and a spacer 46 in the cylindrical portion 41. The needle valve 5 is formed of a metal member such as stainless steel or brass, and has a substantially ellipsoidal needle portion 5a at the lower end, a cylindrical rod-shaped rod portion 5b, and an upper flange portion 5c. The needle valve 5 is inserted into the insertion hole 42 a of the boss portion 42 of the valve holder 4 and attached to the valve holder 4 with the flange portion 5 c abutting against the boss portion 42. The rod portion 5 b of the needle valve 5 is inserted into the valve guide hole 23 a of the valve guide member 23.

弁ホルダ４において、圧縮コイルバネ４４はバネ受け４３とニードル弁５のフランジ部５ｃとの間には所定の荷重を与えられた状態で取り付けられており、弁ホルダ４は、バネ受け４４をスペーサ４６の下端部に当接するとともに、円筒部４１の上端部でワッシャ４５を介してスペーサ４６上端部を押さえつけている。そして、ロータ軸６２のフランジ部６２ｂは、ワッシャ４５とスペーサ４６との間に係合されて、ワッシャ４５により抜け止めがなされている。これにより、ニードル弁５は弁ホルダ４を介してロータ軸６２に連結されるとともに、ロッド部５ｂにガイドされて軸線Ｘ方向に移動可能となっている。   In the valve holder 4, the compression coil spring 44 is attached between the spring receiver 43 and the flange portion 5 c of the needle valve 5 with a predetermined load applied. The valve holder 4 attaches the spring receiver 44 to the spacer 46. The upper end portion of the spacer 46 is pressed by the upper end portion of the cylindrical portion 41 via the washer 45. The flange portion 62 b of the rotor shaft 62 is engaged between the washer 45 and the spacer 46, and is prevented from coming off by the washer 45. Thereby, the needle valve 5 is connected to the rotor shaft 62 via the valve holder 4 and is movable in the direction of the axis X while being guided by the rod portion 5b.

弁ハウジング１の上端には密閉ケース２５が溶接等によって気密に固定されている。密閉ケース２５内には、外周部を多極に着磁されたマグネットロータ６１と、ロータ軸マグネットロータ６１の中心に固着された前記ロータ軸６２とが設けられている。ロータ軸６２の上端部は、密閉ケース２５の天井部に設けられた円筒状のガイド２６内に回転可能に嵌合されている。また、ロータ軸６２には雄ねじ部６２ａが形成されており、この雄ねじ部６２ａは支持部材３に形成された雌ねじ部３ａに螺合している。密閉ケース２５の外周にはステータコイル６３が配設されており、マグネットロータ６１、ロータ軸６２及びステータコイル６３はステッピングモータ６を構成している。そして、ステータコイル６３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６１が回転されてロータ軸６２が回転する。なお、ガイド２６の外周にはマグネットロータ６１に対する回転ストッパ機構２７が設けられている。   A sealing case 25 is fixed to the upper end of the valve housing 1 in an airtight manner by welding or the like. In the sealed case 25, there are provided a magnet rotor 61 whose outer peripheral portion is magnetized in multiple poles, and the rotor shaft 62 fixed to the center of the rotor shaft magnet rotor 61. An upper end portion of the rotor shaft 62 is rotatably fitted in a cylindrical guide 26 provided on the ceiling portion of the sealed case 25. Further, the rotor shaft 62 is formed with a male screw portion 62 a, and this male screw portion 62 a is screwed into a female screw portion 3 a formed on the support member 3. A stator coil 63 is disposed on the outer periphery of the sealed case 25, and the magnet rotor 61, the rotor shaft 62, and the stator coil 63 constitute the stepping motor 6. When a pulse signal is given to the stator coil 63, the magnet rotor 61 is rotated according to the number of pulses, and the rotor shaft 62 is rotated. A rotation stopper mechanism 27 for the magnet rotor 61 is provided on the outer periphery of the guide 26.

以上の構成により実施形態の電動弁は以下のように動作する。まず、図１の弁開度制御状態で、ステッピングモータ６の駆動により、マグネットロータ６１及びロータ軸６２が回転し、ロータ軸６２の雄ねじ部６２ａと支持部材３の雌ねじ部３ａとのねじ送り機構により、ロータ軸６２は軸線Ｘ方向に移動する。この回転に伴うロータ軸６２の軸線Ｘ方向移動によって弁ホルダ４と共にニードル弁５が軸線Ｘ方向に移動する。そして、ニードル弁５は、ニードル部５ａの部分で第１ポート１１の開口面積を増減し、一次継手管２１から二次継手管２２へ、あるいは二次継手管２２から一次継手管２１へ流れる冷媒の流量が制御される。なお、一次継手管２１から二次継手管２２へ冷媒が流れる場合を「第１の流れ」、二次継手管２２から一次継手管２１へ冷媒が流れる場合を「第２の流れ」という。   With the above configuration, the motor-operated valve of the embodiment operates as follows. First, in the valve opening control state of FIG. 1, the magnet rotor 61 and the rotor shaft 62 are rotated by driving the stepping motor 6, and a screw feeding mechanism between the male screw portion 62 a of the rotor shaft 62 and the female screw portion 3 a of the support member 3. Thus, the rotor shaft 62 moves in the axis X direction. The needle valve 5 moves in the direction of the axis X together with the valve holder 4 by the movement of the rotor shaft 62 in the direction of the axis X accompanying this rotation. The needle valve 5 increases or decreases the opening area of the first port 11 at the needle portion 5a, and the refrigerant flows from the primary joint pipe 21 to the secondary joint pipe 22 or from the secondary joint pipe 22 to the primary joint pipe 21. The flow rate is controlled. The case where the refrigerant flows from the primary joint pipe 21 to the secondary joint pipe 22 is referred to as “first flow”, and the case where the refrigerant flows from the secondary joint pipe 22 to the primary joint pipe 21 is referred to as “second flow”.

第１ポート１１、第２ポート１２及び第３ポート１３は、軸線Ｘを中心とする円柱の側面の形状をしており、図２に示すように、第１ポート１１の内径Ｄ１はニードル部５ａの外周に合わせた寸法である。また、第２ポート１２の内径Ｄ２は第１ポート１１の内径Ｄ１より僅かに大きな寸法である。第３ポート１３の二次継手管２２側端部の内径Ｄ３は第２ポート１２の内径Ｄ２より大きな寸法で、かつ、二次継手管２２の内径Ｄ４と同寸となっている。なお、図２において各径Ｄ１〜Ｄ４には直径を示す「φ」を付記してある。第１ポート１１の長さＬ１は内径Ｄ１に比して小さな寸法であり、第１テーパ部１４と第２ポート１２とを合わせた長さＬ２は第１ポート１１の長さＬ１より大きな寸法となっている。第２テーパ部１５と第３ポート１３とを合わせた長さＬ３は第１テーパ部１４と第２ポート１２とを合わせた長さＬ２より大きな寸法となっている。   The first port 11, the second port 12, and the third port 13 have a cylindrical side surface shape centered on the axis X, and as shown in FIG. 2, the inner diameter D1 of the first port 11 is the needle portion 5a. It is the dimension according to the outer periphery. The inner diameter D2 of the second port 12 is slightly larger than the inner diameter D1 of the first port 11. The inner diameter D3 of the end of the third port 13 on the secondary joint pipe 22 side is larger than the inner diameter D2 of the second port 12 and the same dimension as the inner diameter D4 of the secondary joint pipe 22. In FIG. 2, “φ” indicating the diameter is appended to each of the diameters D1 to D4. The length L1 of the first port 11 is smaller than the inner diameter D1, and the combined length L2 of the first tapered portion 14 and the second port 12 is larger than the length L1 of the first port 11. It has become. The combined length L3 of the second tapered portion 15 and the third port 13 is larger than the combined length L2 of the first tapered portion 14 and the second port 12.

第１テーパ部１４及び第２テーパ部１５は、軸線Ｘを中心とする円錐台の側面の形状をしており、第１テーパ部１４の内側面は第１ポート１１から第２ポート１２にかけて内径が拡大する形状、第２テーパ部１５の内側面は第２ポート１２から第３ポート１３にかけて内径が拡大する形状をしている。そして、第１テーパ部１４の開き角度であるテーパ角θ１は、第２テーパ部１５の開き角度であるテーパ角θ２よりも大きい開き角度となっている。なお、これらの寸法及び角度は図２に図示のものには限定されるものではない。   The first taper portion 14 and the second taper portion 15 have a shape of a truncated cone centering on the axis X, and the inner side surface of the first taper portion 14 has an inner diameter from the first port 11 to the second port 12. The inner surface of the second tapered portion 15 has a shape in which the inner diameter increases from the second port 12 to the third port 13. The taper angle θ1 that is the opening angle of the first taper portion 14 is larger than the taper angle θ2 that is the opening angle of the second taper portion 15. These dimensions and angles are not limited to those shown in FIG.

図３（Ａ）に示すように、第１の流れのときは、ニードル部５ａと第１ポート１１の隙間を通った冷媒は、第１テーパ部１４、第２ポート１２、第２テーパ部１５及び第３ポート１３を通って二次継手管２２へ流れる。このとき、ニードル部５ａと第１ポート１１の隙間は最も狭い箇所であり、ここで流速は最大になるが、第１ポート１１の長さＬ１は可能な限り短くなっており、この隙間を通った冷媒の流れは、第１テーパ部１４に倣って直ぐに第２ポート１２の内壁に沿う形で流れる。第２ポート１２の内径Ｄ２は第１ポート１１の内径Ｄ１より僅かに大きいだけであり、第１ポート１１から第２ポート１２に流れる間に、圧力を急激に回復させることがない。また、第２ポート１２の長さは長いので、冷媒の流れは第２ポート１２で整流化される。したがって、キャビテーションの破裂を抑制することができるとともに、冷媒の流れを安定化することができる。   As shown in FIG. 3A, during the first flow, the refrigerant passing through the gap between the needle portion 5a and the first port 11 is the first taper portion 14, the second port 12, and the second taper portion 15. And flows to the secondary joint pipe 22 through the third port 13. At this time, the gap between the needle portion 5a and the first port 11 is the narrowest part, and the flow velocity is maximized here, but the length L1 of the first port 11 is as short as possible and passes through this gap. The flow of the refrigerant immediately follows the first tapered portion 14 and flows along the inner wall of the second port 12. The inner diameter D2 of the second port 12 is only slightly larger than the inner diameter D1 of the first port 11, and the pressure is not rapidly recovered while flowing from the first port 11 to the second port 12. Further, since the length of the second port 12 is long, the flow of the refrigerant is rectified at the second port 12. Therefore, rupture of cavitation can be suppressed and the flow of the refrigerant can be stabilized.

第２ポート１２を通った冷媒の流れは、第２テーパ部１５に倣って圧力を回復すなわち高くしながら第３ポート１３に流れる。この第３ポート１３の二次継手管２２側端部の内径Ｄ３は第２ポート１２の内径Ｄ２より大きいので、第２テーパ部１５に倣って流れる間に流速が減速される。すなわち、第２ポート１２である程度、整流化しながら、直ぐに流速を減速するので、流速音が低減する。さらに、第２テーパ部１５を通って減速された冷媒の流れは、第３ポート１３に流れるが、冷媒の流れは第２ポート１２ですでに整流されているので、この第３ポート１３内では、冷媒の流れは乱れにくく、キャビテーションの破裂を抑制することができる。   The refrigerant flowing through the second port 12 flows to the third port 13 while recovering, that is, increasing the pressure following the second tapered portion 15. Since the inner diameter D3 of the end of the third port 13 on the secondary joint pipe 22 side is larger than the inner diameter D2 of the second port 12, the flow velocity is reduced while flowing along the second tapered portion 15. That is, since the flow velocity is immediately reduced while rectifying to some extent at the second port 12, the flow velocity sound is reduced. Furthermore, the flow of the refrigerant decelerated through the second tapered portion 15 flows to the third port 13, but since the flow of the refrigerant has already been rectified in the second port 12, The flow of the refrigerant is hardly disturbed, and the cavitation burst can be suppressed.

このように、第２ポート１２である程度、整流化し、第２テーパ部１５を介して第３ポート１３に流すことで、第２テーパ部１５で整流化を保ったまま流速を減速することができる。これにより、第３ポート１３における流れの乱れを低減してキャビテーションの破裂を抑制でき、かつ、第２テーパ部１５で流速を減速して流速音を低減できる。   Thus, the flow rate can be reduced while maintaining rectification in the second taper portion 15 by rectifying to some extent at the second port 12 and flowing to the third port 13 via the second taper portion 15. . Thereby, the turbulence of the cavitation can be suppressed by reducing the turbulence of the flow at the third port 13, and the flow velocity sound can be reduced by decelerating the flow velocity at the second tapered portion 15.

一方、図３（Ｂ）に示すように、第２の流れのときは、二次継手管２２から流入する冷媒は、第３ポート１３を通って、第２テーパ部１５に倣って第２ポート１２の内壁に沿う形で流れ、さらに、第１テーパ部１４に倣って第１ポート１１へと流れる。そして、ニードル部５ａと第１ポート１１の隙間を通って、弁室に流れる。そして、二次継手管２２の内径と第３ポート１３の二次継手管２２側端部の内径が同寸となっているので、冷媒は二次継手管２２及び第３ポート１３から第２テーパ部１５に抵抗無く流れる。したがって、冷媒の流れが整流化されるので、縮流発生等による流れの損失もなく、冷媒の流れを安定化することができる。   On the other hand, as shown in FIG. 3B, during the second flow, the refrigerant flowing from the secondary joint pipe 22 passes through the third port 13 and follows the second taper portion 15 to follow the second port. 12 flows along the inner wall of 12, and further flows to the first port 11 following the first tapered portion 14. Then, it flows through the gap between the needle portion 5a and the first port 11 and flows into the valve chamber. Since the inner diameter of the secondary joint pipe 22 and the inner diameter of the end of the third port 13 on the side of the secondary joint pipe 22 are the same, the refrigerant is supplied from the secondary joint pipe 22 and the third port 13 to the second taper. It flows to the part 15 without resistance. Therefore, since the flow of the refrigerant is rectified, the flow of the refrigerant can be stabilized without any flow loss due to the occurrence of contraction.

実施形態における電動弁１０は、一次継手管２１と二次継手管２２との圧力差が高い場合に、流速音の低減効果が高いものであり、第１ポート１１、第２ポート１２、第３ポート１３、第１テーパ部１４、第２テーパ部１５、及び二次継手管２２の各部の寸法及び角度は以下の条件を満たすように設定されている。   The motor-operated valve 10 according to the embodiment has a high effect of reducing flow velocity sound when the pressure difference between the primary joint pipe 21 and the secondary joint pipe 22 is high. The first port 11, the second port 12, and the third port The size and angle of each part of the port 13, the first tapered portion 14, the second tapered portion 15, and the secondary joint pipe 22 are set so as to satisfy the following conditions.

以下に、一次継手管２１と二次継手管２２との圧力差が高い場合に、流速音の低減効果が高い実施形態の各部の寸法及び角度の条件を示す。第１ポート１１の内径Ｄ１は、
１mm≦Ｄ１≦４．５mm
であり、第２ポート１２の内径Ｄ２は、
１．１５mm≦Ｄ２≦４．９mm
であり、第３ポート１３の内径Ｄ３と二次継手管２２の内径Ｄ４は、
４．６mm≦Ｄ３＝Ｄ４≦６．３５mm
である。 Below, when the pressure difference of the primary joint pipe | tube 21 and the secondary joint pipe | tube 22 is high, the conditions of the dimension and angle of each part of embodiment with a high reduction effect of a flow velocity sound are shown. The inner diameter D1 of the first port 11 is
1mm ≦ D1 ≦ 4.5mm
The inner diameter D2 of the second port 12 is
1.15mm ≦ D2 ≦ 4.9mm
The inner diameter D3 of the third port 13 and the inner diameter D4 of the secondary joint pipe 22 are
4.6 mm ≦ D3 = D4 ≦ 6.35 mm
It is.

また、第１テーパ部１４のテーパ角θ１は、
６０°≦θ１≦１５０°
の範囲であり、第２テーパ部１５のテーパ角θ２は、
２０°≦θ２≦９０°
の範囲である。 The taper angle θ1 of the first taper portion 14 is
60 ° ≦ θ1 ≦ 150 °
The taper angle θ2 of the second taper portion 15 is
20 ° ≦ θ2 ≦ 90 °
Range.

また、第１ポート１１の長さＬ１は、
０．１mm≦Ｌ１≦０．５mm
であり、このＬ１は短いほど騒音が低下する。第１テーパ部１４と第２ポート１２の長さＬ２は、
０．６mm≦Ｌ２≦２．０mm
であり、これらの長さＬ１，Ｌ２に組み合わせは、Ｌ１＋Ｌ２が、
０．７mm≦Ｌ１＋Ｌ２≦２．５mm
となる条件により設定されている。また、第１ポート１１の長さＬ１と、第１テーパ部１４と第２ポート１２の長さＬ２と、第２テーパ部１５と第３ポート１３の長さＬ３の総和Ｌ１＋Ｌ２＋Ｌ３は、
７mm≦Ｌ１＋Ｌ２＋Ｌ３≦１２mm
である。 The length L1 of the first port 11 is
0.1mm ≦ L1 ≦ 0.5mm
The noise becomes lower as the L1 is shorter. The length L2 of the first tapered portion 14 and the second port 12 is
0.6mm ≦ L2 ≦ 2.0mm
The combination of these lengths L1 and L2 is L1 + L2,
0.7mm ≦ L1 + L2 ≦ 2.5mm
Is set according to the conditions. Further, the total length L1 + L2 + L3 of the length L1 of the first port 11, the length L2 of the first tapered portion 14 and the second port 12, and the length L3 of the second tapered portion 15 and the third port 13 is:
7mm ≦ L1 + L2 + L3 ≦ 12mm
It is.

また、第１テーパ部１４と第２ポート１２の長さＬ２と、第１ポート１１の長さＬ１の比Ｌ２／Ｌ１は、
１．２≦Ｌ２／Ｌ１≦８．５
の範囲であり、第２テーパ部１５と第３ポート１３の長さＬ３と、第１テーパ部１４と第２ポート１２の長さＬ２の比Ｌ３／Ｌ２は、
３≦Ｌ３／Ｌ２≦１５
の範囲であり、第２ポート１２の内径Ｄ２と第１ポート１１の内径Ｄ１の寸法比Ｄ２／Ｄ１は、
１．０３≦Ｄ２／Ｄ１≦１．５
の範囲であり、第３ポート１３の内径Ｄ３と第２ポート１２の内径Ｄ２の寸法比Ｄ３／Ｄ２は、
１．０２≦Ｄ３／Ｄ２≦５．５２
の範囲である。 Further, the ratio L2 / L1 of the length L2 of the first tapered portion 14 and the second port 12 and the length L1 of the first port 11 is:
1.2 ≦ L2 / L1 ≦ 8.5
The ratio L3 / L2 of the length L3 of the second taper portion 15 and the third port 13 and the length L2 of the first taper portion 14 and the second port 12 is:
3 ≦ L3 / L2 ≦ 15
The dimension ratio D2 / D1 between the inner diameter D2 of the second port 12 and the inner diameter D1 of the first port 11 is
1.03 ≦ D2 / D1 ≦ 1.5
The dimension ratio D3 / D2 between the inner diameter D3 of the third port 13 and the inner diameter D2 of the second port 12 is
1.02 ≦ D3 / D2 ≦ 5.52
Range.

以上のように、各寸法及び角度の範囲を示したが、この範囲内の値は、Ｄ１＜Ｄ２＜Ｄ３＝Ｄ４の条件を満たすような組み合わせの値である。   As described above, the range of each dimension and angle is shown, but the value within this range is a combination value that satisfies the condition of D1 <D2 <D3 = D4.

図５は本発明の第２実施形態の電動弁における弁ポート近傍の要部拡大縦断面図である。なお、以下の各実施形態において第１実施形態と同様な要素には図１乃至図４と同符号を付記して重複する説明は適宜省略する。また、以下の各実施形態における電動弁の全体構成は第１実施形態と同様であり、図４の空気調和機の冷凍サイクルシステムに用いられるものである。   FIG. 5 is an enlarged vertical cross-sectional view of the main part in the vicinity of the valve port in the electric valve according to the second embodiment of the present invention. In the following embodiments, the same elements as those in the first embodiment are denoted by the same reference numerals as those in FIGS. The overall configuration of the motor-operated valve in each of the following embodiments is the same as that of the first embodiment, and is used in the refrigeration cycle system of the air conditioner of FIG.

図５の第２実施形態では、弁座部１Ｂの弁ポートは、第１ポート１１と、第２ポート１２と、第３ポート１３′と、第１テーパ部１４と、第２テーパ部１５とで構成されている。また、弁ハウジング１には、弁室１Ａの軸線Ｘ方向の片側端部に二次継手管２２′が取り付けられている。この二次継手管２２′は第１実施形態の二次継手管２２より僅かに長くされて、弁ハウジング１側の端部は第２テーパ部１５の周囲を囲うようにして、弁ハウジング１に埋設されている。そして、二次継手管２２′の内径部の一部が弁座部１Ｂにおける第３ポート１３′となっており、この第３ポート１３′は第２テーパ部１５へ連続している。   In the second embodiment of FIG. 5, the valve port of the valve seat portion 1 </ b> B includes the first port 11, the second port 12, the third port 13 ′, the first taper portion 14, and the second taper portion 15. It consists of Further, a secondary joint pipe 22 ′ is attached to the valve housing 1 at one end portion in the axis X direction of the valve chamber 1 </ b> A. The secondary joint pipe 22 ′ is slightly longer than the secondary joint pipe 22 of the first embodiment, and the end on the valve housing 1 side surrounds the second taper portion 15, so that the valve housing 1 Buried. A part of the inner diameter portion of the secondary joint pipe 22 ′ is a third port 13 ′ in the valve seat portion 1 </ b> B, and the third port 13 ′ is continuous to the second taper portion 15.

この第２実施形態でも、各部位の寸法及び角度は第１実施形態（図２）と同様である。すなわち、第１ポート１１から二次継手管２２′まで通じる弁座部１Ｂの弁ポートの形状は第１実施形態と同様である。したがって、第１の流れ及び第２の流れのいずれの場合も、第１実施形態同様な作用効果が得られる。   Also in the second embodiment, the size and angle of each part are the same as those in the first embodiment (FIG. 2). That is, the shape of the valve port of the valve seat portion 1B leading from the first port 11 to the secondary joint pipe 22 ′ is the same as that of the first embodiment. Therefore, in both cases of the first flow and the second flow, the same effects as those of the first embodiment can be obtained.

図６は本発明の第３実施形態の電動弁における弁ポート近傍の要部拡大縦断面図である。この第３実施形態では、弁座部１Ｂにおける弁ポートは第１実施形態と同様であり、第１ポート１１と、第２ポート１２と、第３ポート１３と、第１テーパ部１４と、第２テーパ部１５で構成されている。また、弁ハウジング１には、弁室１Ａの軸線Ｘ方向の片側端部に二次継手管２２″が取り付けられている。この二次継手管２２″は第１実施形態の二次継手管２２より僅かに長くされるとともに、端部を拡径されており、この拡径部分が第３ポート１３の周囲を囲うようにして、弁ハウジング１に埋設されている。そして、二次継手管２２″の内径Ｄ４と、第３ポート１３の二次継手管２２″側端部の内径Ｄ３は同寸となっている。   FIG. 6 is an enlarged vertical cross-sectional view of a main part in the vicinity of a valve port in an electric valve according to a third embodiment of the present invention. In the third embodiment, the valve port in the valve seat portion 1B is the same as that of the first embodiment, and the first port 11, the second port 12, the third port 13, the first tapered portion 14, It is composed of two taper portions 15. Further, a secondary joint pipe 22 "is attached to one end portion of the valve chamber 1A in the axis X direction of the valve housing 1. This secondary joint pipe 22" is the secondary joint pipe 22 of the first embodiment. The diameter of the end portion is increased, and the diameter-enlarged portion is embedded in the valve housing 1 so as to surround the third port 13. The inner diameter D4 of the secondary joint pipe 22 ″ and the inner diameter D3 of the third port 13 on the side of the secondary joint pipe 22 ″ are the same size.

この第３実施形態でも、弁ポートの各部位の寸法及び角度は第１実施形態（図２）と同様である。すなわち、第１ポート１１から第３ポート１３まで通じる弁ポートの形状は第１実施形態と同様である。また、第３ポート１３と二次継手管２２″の内径部との間に僅かに溝が形成されているが、この溝の部分では、冷媒はリング状の渦となるだけであり、冷媒の流れには影響しない。したがって、第１の流れ及び第２の流れのいずれの場合も、第１実施形態同様な作用効果が得られる。   Also in the third embodiment, the size and angle of each part of the valve port are the same as those in the first embodiment (FIG. 2). That is, the shape of the valve port leading from the first port 11 to the third port 13 is the same as in the first embodiment. In addition, a slight groove is formed between the third port 13 and the inner diameter portion of the secondary joint pipe 22 ″. In this groove portion, the refrigerant only forms a ring-shaped vortex. Therefore, in both cases of the first flow and the second flow, the same effect as the first embodiment can be obtained.

図７は本発明の第４実施形態の電動弁における弁ポート近傍の要部拡大縦断面図である。この第４実施形態では、弁座部１Ｂの弁ポートは、第１ポート１１と、第２ポート１２と、第３ポート１３″と、第１テーパ部１４と、第２テーパ部１５′とで構成されている。二次継手管２２′は第２実施形態と同様である。第３ポート１３″は僅かにテーパ状であり、この第３ポート１３″の開き角度であるテーパ角θ３は適宜設定されている。また、第２テーパ部１５′の開き角度であるテーパ角θ２′は第１実施形態における第２テーパ部１５のテーパ角θ２より僅かに小さく設定されている。そして、二次継手管２２′の内径Ｄ４と、第３ポート１３″の二次継手管２２′側端部の内径Ｄ３は同寸となっている。   FIG. 7 is an enlarged vertical cross-sectional view of a main part in the vicinity of a valve port in an electric valve according to a fourth embodiment of the present invention. In the fourth embodiment, the valve port of the valve seat portion 1B includes the first port 11, the second port 12, the third port 13 ″, the first taper portion 14, and the second taper portion 15 ′. The secondary joint pipe 22 'is the same as in the second embodiment. The third port 13 "is slightly tapered, and the taper angle θ3, which is the opening angle of the third port 13", is appropriately set. The taper angle θ2 ′, which is the opening angle of the second taper portion 15 ′, is set slightly smaller than the taper angle θ2 of the second taper portion 15 in the first embodiment. The inner diameter D4 of the joint pipe 22 ′ and the inner diameter D3 of the end of the third port 13 ″ on the secondary joint pipe 22 ′ side are the same.

この第４実施形態でも、弁ポートの各部位の寸法及び角度は第１実施形態（図２）と略同様である。すなわち、第１ポート１１から第３ポート１３″まで通じる弁ポートの形状は第１実施形態と同様である。また、第３ポート１３″と二次継手管２２′の内径部との間に僅かに角度がついているが、微小な角度であり、冷媒の流れには影響しない。したがって、第１の流れ及び第２の流れのいずれの場合も、第１実施形態同様な作用効果が得られる。   Also in the fourth embodiment, the size and angle of each part of the valve port are substantially the same as those in the first embodiment (FIG. 2). That is, the shape of the valve port leading from the first port 11 to the third port 13 ″ is the same as in the first embodiment. Further, a slight gap is formed between the third port 13 ″ and the inner diameter portion of the secondary joint pipe 22 ′. Is angled, but it is a very small angle and does not affect the flow of the refrigerant. Therefore, in both cases of the first flow and the second flow, the same effects as those of the first embodiment can be obtained.

以上の実施形態では、弁ポートを形成する弁座部１Ｂを弁ハウジング１の一部（及び二次継手２２′の一部）としているが、弁座部材等の別の部材に弁ポートを形成したものでもよい。   In the above embodiment, the valve seat portion 1B forming the valve port is a part of the valve housing 1 (and a part of the secondary joint 22 '), but the valve port is formed in another member such as a valve seat member. You may have done.

以上、本発明の実施の形態について図面を参照して詳述してきたが、具体的な構成はこれらの実施の形態に限られるものではなく、本発明の要旨を逸脱しない範囲の設計の変更等があっても本発明に含まれる。   As described above, the embodiments of the present invention have been described in detail with reference to the drawings. However, the specific configuration is not limited to these embodiments, and the design can be changed without departing from the scope of the present invention. Is included in the present invention.

１ 弁ハウジング
１Ａ 弁室
１Ｂ 弁座部
１１ 第１ポート（弁ポートの一部）
１２ 第２ポート（弁ポートの一部）
１３ 第３ポート（弁ポートの一部）
１４ 第１テーパ部（弁ポートの一部）
１５ 第２テーパ部（弁ポートの一部）
２１ 一次継手管
２２ 二次継手管
２３ 弁ガイド部材
３ 支持部材
３ａ 雌ねじ部
３ｂ スライド孔
４ 弁ホルダ
５ ニードル弁
５ａ ニードル部
５ｂ ロッド部
６ ステッピングモータ
６１ マグネットロータ
６２ ロータ軸
６２ａ 雄ねじ部
６３ ステータコイル
４ 弁ホルダ
Ｘ 軸線
１３′ 第３ポート
２２′ 二次継手管
２２″ 二次継手管
１５′ 第２テーパ部
１３″ 第３ポート
１０ 電動弁
２０ 室外熱交換器
３０ 室内熱交換器
４０ 流路切換弁
５０ 圧縮機 1 Valve Housing 1A Valve Chamber 1B Valve Seat 11 First Port (Part of Valve Port)
12 Second port (part of valve port)
13 Third port (part of valve port)
14 1st taper part (part of valve port)
15 Second taper part (part of valve port)
21 Primary joint pipe 22 Secondary joint pipe 23 Valve guide member 3 Support member 3a Female thread part 3b Slide hole 4 Valve holder 5 Needle valve 5a Needle part 5b Rod part 6 Stepping motor 61 Magnet rotor 62 Rotor shaft 62a Male thread part 63 Stator coil 4 Valve holder X Axis 13 'Third port 22' Secondary joint pipe 22 "Secondary joint pipe 15 'Second taper part 13" Third port 10 Electric valve 20 Outdoor heat exchanger 30 Indoor heat exchanger 40 Channel switching valve 50 compressor

Claims (4)

一次継手管が連通される弁室と二次継手管とを、ニードル弁で開口面積が増減される弁ポートを介して連通可能とする電動弁であって、前記弁室と前記二次継手管との間に前記弁ポートを有する弁座部を備えるとともに、前記弁ポートに、弁室側の第１ポートと、第１ポートより内径の大きな第２ポートと、前記第１ポートと前記第２ポートとを繋ぐ第１テーパ部と、を備えた電動弁において、
前記弁ポートに、前記二次継手管に連通する第３ポートと、前記第２ポートと前記第３ポートとを繋ぐ第２テーパ部とを備え、前記第１ポートの内径Ｄ１と前記第２ポートの内径Ｄ２と前記第３ポートの前記二次継手管側端部の内径Ｄ３と前記二次継手管の内径Ｄ４との関係がＤ１＜Ｄ２＜Ｄ３＝Ｄ４となっていることを特徴とする電動弁。 An electric valve that enables communication between a valve chamber to which a primary joint pipe is communicated and a secondary joint pipe through a valve port whose opening area is increased or decreased by a needle valve, the valve chamber and the secondary joint pipe A valve seat having the valve port between the first port on the valve chamber side, a second port having a larger inner diameter than the first port, the first port, and the second port. A motor-operated valve including a first taper portion connecting the port;
The valve port includes a third port that communicates with the secondary joint pipe, and a second tapered portion that connects the second port and the third port, and the inner diameter D1 of the first port and the second port The relationship between the inner diameter D2 of the second port, the inner diameter D3 of the end portion on the secondary joint pipe side of the third port, and the inner diameter D4 of the secondary joint pipe is D1 <D2 <D3 = D4. valve. 請求項１に記載の電動弁であって、
Ｄ２−Ｄ１≦Ｄ３−Ｄ２
となっていることを特徴とする電動弁。 The electric valve according to claim 1,
D2-D1 ≦ D3-D2
The motor-operated valve characterized by becoming. 前記第３ポートが前記二次継手管の内径部の一部であることを特徴とする請求項１または２に記載の電動弁。   The motor-operated valve according to claim 1 or 2, wherein the third port is a part of an inner diameter portion of the secondary joint pipe. 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乃至３のいずれか一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. A refrigeration cycle system characterized by that.
JP2017123609A 2017-06-23 2017-06-23 Motorized valve and refrigeration cycle system Active JP6740179B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2017123609A JP6740179B2 (en) 2017-06-23 2017-06-23 Motorized valve and refrigeration cycle system
CN201810510173.6A CN109114237B (en) 2017-06-23 2018-05-24 Electric valve and refrigeration cycle system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2017123609A JP6740179B2 (en) 2017-06-23 2017-06-23 Motorized valve and refrigeration cycle system

Publications (2)

Publication Number Publication Date
JP2019007549A true JP2019007549A (en) 2019-01-17
JP6740179B2 JP6740179B2 (en) 2020-08-12

Family

ID=64822496

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2017123609A Active JP6740179B2 (en) 2017-06-23 2017-06-23 Motorized valve and refrigeration cycle system

Country Status (2)

Country Link
JP (1) JP6740179B2 (en)
CN (1) CN109114237B (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020184076A1 (en) * 2019-03-08 2020-09-17 株式会社不二工機 Flow-rate adjusting valve
WO2020189736A1 (en) * 2019-03-20 2020-09-24 株式会社不二工機 Electric valve
JP2021124154A (en) * 2020-02-04 2021-08-30 株式会社鷺宮製作所 Motor-operated valve and refrigeration cycle system
JP2021124153A (en) * 2020-02-04 2021-08-30 株式会社鷺宮製作所 Motor-operated valve and refrigeration cycle system
JP2022090042A (en) * 2020-01-28 2022-06-16 株式会社不二工機 Motor valve

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7365188B2 (en) * 2019-10-10 2023-10-19 株式会社鷺宮製作所 control valve
JP7199335B2 (en) * 2019-10-25 2023-01-05 株式会社鷺宮製作所 Electric valve and refrigeration cycle system
JP7362569B2 (en) * 2020-08-20 2023-10-17 株式会社鷺宮製作所 Electric valve and refrigeration cycle system
CN117905889A (en) * 2020-08-20 2024-04-19 株式会社鹭宫制作所 Flow control valve and refrigeration cycle system
WO2022057421A1 (en) * 2020-09-18 2022-03-24 广东美的制冷设备有限公司 Electronic expansion valve, refrigerant circulation pipeline, and air conditioner system
US11892211B2 (en) * 2021-05-23 2024-02-06 Copeland Lp Compressor flow restrictor

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005221095A (en) * 2004-02-03 2005-08-18 Mitsubishi Electric Corp Electronic expansion valve and air conditioner
JP2015143543A (en) * 2014-01-31 2015-08-06 株式会社鷺宮製作所 control valve
JP2017089864A (en) * 2015-11-17 2017-05-25 株式会社不二工機 Flow regulating valve
JP2017115989A (en) * 2015-12-24 2017-06-29 株式会社鷺宮製作所 Electric operated valve
JP2019007550A (en) * 2017-06-23 2019-01-17 株式会社鷺宮製作所 Motor valve and refrigeration cycle system

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006284088A (en) * 2005-03-31 2006-10-19 Daikin Ind Ltd Expansion valve and refrigerating device
CN101294761B (en) * 2008-06-17 2010-09-29 邓永林 Thermal expansion valve
JP2010019406A (en) * 2008-07-14 2010-01-28 Fuji Koki Corp Motor-driven valve
JP5696093B2 (en) * 2012-05-10 2015-04-08 株式会社鷺宮製作所 Motorized valve
CN104930241B (en) * 2014-03-19 2018-09-28 浙江三花智能控制股份有限公司 Electric expansion valve
CN105972233A (en) * 2016-07-20 2016-09-28 珠海格力电器股份有限公司 Expansion valve, refrigerant cycle system and air conditioner

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005221095A (en) * 2004-02-03 2005-08-18 Mitsubishi Electric Corp Electronic expansion valve and air conditioner
JP2015143543A (en) * 2014-01-31 2015-08-06 株式会社鷺宮製作所 control valve
JP2017089864A (en) * 2015-11-17 2017-05-25 株式会社不二工機 Flow regulating valve
JP2017115989A (en) * 2015-12-24 2017-06-29 株式会社鷺宮製作所 Electric operated valve
JP2019007550A (en) * 2017-06-23 2019-01-17 株式会社鷺宮製作所 Motor valve and refrigeration cycle system

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020184076A1 (en) * 2019-03-08 2020-09-17 株式会社不二工機 Flow-rate adjusting valve
WO2020189736A1 (en) * 2019-03-20 2020-09-24 株式会社不二工機 Electric valve
JPWO2020189736A1 (en) * 2019-03-20 2020-09-24
JP7133880B2 (en) 2019-03-20 2022-09-09 株式会社不二工機 electric valve
JP2022090042A (en) * 2020-01-28 2022-06-16 株式会社不二工機 Motor valve
JP7374522B2 (en) 2020-01-28 2023-11-07 株式会社不二工機 electric valve
JP2021124154A (en) * 2020-02-04 2021-08-30 株式会社鷺宮製作所 Motor-operated valve and refrigeration cycle system
JP2021124153A (en) * 2020-02-04 2021-08-30 株式会社鷺宮製作所 Motor-operated valve and refrigeration cycle system
JP7299177B2 (en) 2020-02-04 2023-06-27 株式会社鷺宮製作所 Electric valve and refrigeration cycle system
JP7299178B2 (en) 2020-02-04 2023-06-27 株式会社鷺宮製作所 Electric valve and refrigeration cycle system

Also Published As

Publication number Publication date
CN109114237B (en) 2020-09-18
CN109114237A (en) 2019-01-01
JP6740179B2 (en) 2020-08-12

Similar Documents

Publication Publication Date Title
JP6740179B2 (en) Motorized valve and refrigeration cycle system
JP6738775B2 (en) Motorized valve and refrigeration cycle system
JP6479648B2 (en) Motorized valve
JP6659624B2 (en) Motorized valve and refrigeration cycle system
JP5696093B2 (en) Motorized valve
JP5395775B2 (en) Motorized valve
JP5480753B2 (en) Motorized valve
JP2019044880A (en) Motor valve and refrigeration cycle system
JP2020034141A (en) Motor-operated valve and refrigeration cycle system
JP7123020B2 (en) Electric valve and refrigeration cycle system
CN107356024A (en) Electric expansion valve
JP7199335B2 (en) Electric valve and refrigeration cycle system
JP2019070449A (en) Motor valve and refrigeration cycle system
JP7341280B2 (en) Electric valve and refrigeration cycle system
JP7317191B2 (en) Electric valve and refrigeration cycle system
JP7299178B2 (en) Electric valve and refrigeration cycle system
JP7299177B2 (en) Electric valve and refrigeration cycle system
JP7361628B2 (en) Electric valve and refrigeration cycle system
JP2022021471A (en) Electrically-operated valve and refrigeration cycle system

Legal Events

Date Code Title Description
RD04 Notification of resignation of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7424

Effective date: 20180119

A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20190111

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20191015

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20191029

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20191217

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20200114

A601 Written request for extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A601

Effective date: 20200305

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20200512

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20200714

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20200722

R150 Certificate of patent or registration of utility model

Ref document number: 6740179

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150