JP5702316B2 - Expansion valve - Google Patents

Expansion valve Download PDF

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JP5702316B2
JP5702316B2 JP2012027367A JP2012027367A JP5702316B2 JP 5702316 B2 JP5702316 B2 JP 5702316B2 JP 2012027367 A JP2012027367 A JP 2012027367A JP 2012027367 A JP2012027367 A JP 2012027367A JP 5702316 B2 JP5702316 B2 JP 5702316B2
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valve
port
valve seat
guide member
expansion
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JP2013164125A (en
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関口　英樹
英樹 関口
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Saginomiya Seisakusho Inc
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Saginomiya Seisakusho Inc
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Priority to US13/761,538 priority patent/US9726406B2/en
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Description

本発明は、ヒートポンプ式冷凍サイクル中に設けられ、冷媒の第１の流れ方向に対して該冷媒を絞る機能を果たすとともに、圧力損失を極力小さくして大流量を流せるようにした膨張弁に関する。   The present invention relates to an expansion valve that is provided in a heat pump refrigeration cycle and that functions to throttle the refrigerant in the first flow direction of the refrigerant, and that allows a large flow rate to flow by minimizing pressure loss.

従来、ヒートポンプ式冷凍サイクルの多くは、室外熱交換器側（室外ユニット）に膨張弁が設けられており、この場合、膨張弁で膨張された冷媒は長い管路を介して室内熱交換器に流入される。このため、膨張された冷媒に圧力損失が生じやすく、膨張弁における流量制御がしにくいという問題がある。このことは膨張弁を室内熱交換器側に設けた場合も同様である。   Conventionally, many heat pump refrigeration cycles are provided with an expansion valve on the outdoor heat exchanger side (outdoor unit). In this case, the refrigerant expanded by the expansion valve passes through a long pipe to the indoor heat exchanger. Inflow. For this reason, there is a problem that pressure loss is likely to occur in the expanded refrigerant, and it is difficult to control the flow rate in the expansion valve. This is the same when the expansion valve is provided on the indoor heat exchanger side.

これに対して、特開２００９−２８７９１３号公報（特許文献１）に、ヒートポンプ式冷凍サイクルにおいて、冷房モード時には室内熱交換器側で流量制御を含む絞り機能を発揮し、暖房モード時には室外熱交換器側で絞り機能を発揮できるようにした膨張弁が提案されている。   On the other hand, JP 2009-287913 A (Patent Document 1) discloses that in a heat pump refrigeration cycle, an indoor heat exchanger performs a throttling function including flow control in the cooling mode, and outdoor heat exchange in the heating mode. There has been proposed an expansion valve that can perform a throttle function on the vessel side.

特開２００９−２８７９１３号公報JP 2009-287913 A

特許文献１の膨張弁は、冷媒の第１の流れ方向に対して該冷媒を絞る機能を果たすとともに、第２の流れ方向に対して圧力損失を極力小さくして大流量を流すために、副弁としての弁座部材（２，８）を有しており、この弁座部材（２，８）を弁ハウジング（１，７）内で軸線方向に摺動させる構造となっている。   The expansion valve of Patent Document 1 functions to throttle the refrigerant with respect to the first flow direction of the refrigerant, and to reduce the pressure loss with respect to the second flow direction as much as possible to flow a large flow rate. A valve seat member (2, 8) is provided as a valve, and the valve seat member (2, 8) is slid in the axial direction within the valve housing (1, 7).

しかしながら、この特許文献１の膨張弁では、弁座部材（２）は肉厚の部材であり、この弁座部材（２）自体が重たくなって、第２ポート（１２）から離間するとき動作しにくいという問題がある。これに対して、弁座部材（８）はプレス加工により形成されているので、この弁座部材（８）は軽量になり、第２ポート（７２）から離間するとき容易に動作する。しかしながら、この弁座部材（８）は、弁ポート（８１ａ）もプレス加工により形成されているので、この弁ポート（８１ａ）の径や、形状に精度を出し難く、弁体（５１）との間で弁漏れが生じ易いという問題がある。   However, in the expansion valve of Patent Document 1, the valve seat member (2) is a thick member, and the valve seat member (2) itself becomes heavy and operates when it is separated from the second port (12). There is a problem that it is difficult. On the other hand, since the valve seat member (8) is formed by pressing, the valve seat member (8) is light in weight and easily operates when separated from the second port (72). However, since this valve seat member (8) is also formed by pressing the valve port (81a), it is difficult to obtain accuracy in the diameter and shape of the valve port (81a). There is a problem that valve leakage is likely to occur.

本発明は、ヒートポンプ式冷凍サイクルにおいて、弁ハウジング内で副弁を移動させることにより、冷媒の第１の流れ方向に対して該冷媒を絞る機能を果たすとともに、第２の流れ方向に対して圧力損失を極力小さくして大流量を流せるようにした膨張弁において、副弁を軽量化するとともに、この副弁の弁ポートの精度を高めることを課題とする。   In the heat pump refrigeration cycle, the sub-valve is moved in the valve housing to perform the function of constricting the refrigerant with respect to the first flow direction of the refrigerant and the pressure with respect to the second flow direction. It is an object of the present invention to reduce the weight of a subvalve and to increase the accuracy of the valve port of the subvalve in an expansion valve in which loss can be minimized and a large flow rate can flow.

請求項１の膨張弁は、シリンダ状の主弁室を構成する弁ハウジングと、該主弁室に連通する第１ポート及び該主弁室の軸方向端部に連通する第２ポートと、前記主弁室内に該主弁室の軸方向に移動可能に配置されて、主弁室と前記第２ポートとの間に弁ポートを有する副弁と、前記副弁に対する前記軸方向の移動により前記弁ポートを開閉する弁体とを備え、冷媒を前記第１ポートから前記第２ポートへ流すとき、該第１ポートと第２ポートの差圧により前記副弁を前記第２ポートの周囲に着座させて該第２ポートを閉状態とするとともに、前記弁体により前記弁ポートへ流れる冷媒を絞り、冷媒を逆方向に流すとき、前記第２ポートと第１ポートの差圧により前記副弁を前記第２ポートから離間して該第２ポートを全開状態とするようにした膨張弁において、前記副弁を、前記弁ハウジングの内周面に摺接するガイド部材であって金属板のプレス加工により形成されたガイド部材と、前記弁ポートを有し前記ガイド部材の中央に配置された弁座部材であって金属材の切削加工により形成された弁座部材とで構成し、前記ガイド部材は、前記主弁室の軸に直角に交差する円盤部と、該円盤部の中央に形成された嵌合孔と、該円盤部の周囲に立設された複数のガイド板とを有し、前記弁座部材は、円盤状のフランジ部と、該フランジ部の上部に形成された円環状の環状ボス部とを有し、前記弁座部材の環状ボス部が前記ガイド部材の嵌合孔内に挿通され、前記環状ボス部の端部を外周側に広げるようにかしめることで、前記フランジ部と前記円盤部とが密着して結合され、かつ、前記円盤部の端部と前記フランジ部の端部との接合部分に溶接が施され、前記ガイド部材と前記弁座部材とが固着されていることを特徴とする。 The expansion valve according to claim 1 includes a valve housing constituting a cylindrical main valve chamber, a first port communicating with the main valve chamber, a second port communicating with an axial end of the main valve chamber, A sub-valve disposed in the main valve chamber so as to be movable in the axial direction of the main valve chamber, and having a valve port between the main valve chamber and the second port, and the axial movement with respect to the sub-valve A valve body that opens and closes the valve port, and when the refrigerant flows from the first port to the second port, the sub-valve is seated around the second port due to a differential pressure between the first port and the second port. When the second port is closed, the refrigerant flowing to the valve port is throttled by the valve body, and when the refrigerant flows in the reverse direction, the sub-valve is controlled by the differential pressure between the second port and the first port. Keep away from the second port and fully open the second port In the expansion valve, the sub-valve is a guide member that is slidably contacted with the inner peripheral surface of the valve housing and is formed by pressing a metal plate, and has the valve port and is arranged at the center of the guide member A valve seat member formed by cutting a metal material, and the guide member includes a disk portion perpendicular to the axis of the main valve chamber, and a center of the disk portion. It has a formed fitting holes, and a plurality of guide plates erected around the circular plate portion, the valve seat member includes a disk-shaped flange portion, formed in the upper portion of the flange portion An annular annular boss portion, and the annular boss portion of the valve seat member is inserted into the fitting hole of the guide member, and the end portion of the annular boss portion is caulked so as to spread outward. , and the flange portion and the disc portion are bonded in close contact, and the Welding the ends of the panel portion to the joint portion between the end portion of the flange portion is subjected, characterized in that said guide member and the valve seat member is fixed.

請求項２の膨張弁は、請求項１に記載の膨張弁であって、前記ガイド板の前記軸方向と平行な側縁におけるプレス加工によるバリが内側に形成され、かつ、前記スポット溶接が施される箇所の前記円盤部の前記フランジ部と反対側の縁にプレス加工によるダレ面がくるようにしたことを特徴とする。 An expansion valve according to a second aspect is the expansion valve according to the first aspect , wherein a burr formed by pressing at a side edge parallel to the axial direction of the guide plate is formed inside, and the spot welding is performed. A sag surface is formed by pressing at the edge of the disk portion opposite to the flange portion.

請求項１の膨張弁によれば、副弁において、ガイド部材が金属盤のプレス加工で形成されているので副弁自体を軽量にすることができ、かつ、弁座部材は切削加工で形成されているので、弁ポートを精度高く形成することができ、弁漏れを防止して信頼性の高い膨張弁が得られる。   According to the expansion valve of the first aspect, in the auxiliary valve, the guide member is formed by pressing a metal disc, so that the auxiliary valve itself can be reduced in weight, and the valve seat member is formed by cutting. Therefore, the valve port can be formed with high accuracy, and a highly reliable expansion valve can be obtained by preventing valve leakage.

さらに、ガイド部材の嵌合孔内に挿通された環状ボス部のかしめにより弁座部材に対するガイド部材の芯出しを行うことができ、ガイド部材の中心に弁座部材を保持することができる。 Furthermore, the guide member can be centered with respect to the valve seat member by caulking the annular boss portion inserted into the fitting hole of the guide member, and the valve seat member can be held at the center of the guide member.

請求項２の膨張弁によれば、請求項１の効果に加えて、弁ハウジングの内周面と線接触するガイド板の側縁の接触部分にプレス加工のバリがないので、副弁が容易に摺動し、安定した動作が得られる。また、円盤部のダレ面はフランジ部と反対側にあり、すなわちスポット溶接をする前の状態で、円盤部におけるプレス加工のバリはフランジ部側にあり、このバリをフランジ部の外側に来るようにすれば、スポット溶接時に、このバリが溶融する。これにより、円盤部とフランジ部とが隙間なく密着するので、より確実にスポット溶接を行うことができる。 According to the expansion valve of the second aspect, in addition to the effect of the first aspect, since there is no burr of press working at the contact portion of the side edge of the guide plate that makes line contact with the inner peripheral surface of the valve housing, the auxiliary valve is easy. Stable operation can be obtained. In addition, the sag surface of the disk part is on the opposite side of the flange part, that is, in the state before spot welding, the burrs of the press work in the disk part are on the flange part side so that this burr comes outside the flange part. In this case, this burr is melted during spot welding. Thereby, since a disk part and a flange part closely_contact | adhere without gap, spot welding can be performed more reliably.

本発明の実施形態の膨張弁の絞り状態の縦断面図である。It is a longitudinal cross-sectional view of the throttle state of the expansion valve of the embodiment of the present invention. 同膨張弁の全開状態の縦断面図である。It is a longitudinal cross-sectional view of the fully open state of the expansion valve. 本発明の実施形態における副弁の平面図及び縦断面図である。It is the top view and longitudinal cross-sectional view of a subvalve in embodiment of this invention. 本発明の実施形態における副弁のガイド部材と弁座部材の組立前の斜視図である。It is a perspective view before the assembly of the guide member and valve seat member of the sub valve in the embodiment of the present invention. 本発明の実施形態における副弁の組立状態の斜視図である。It is a perspective view of the assembly state of the subvalve in the embodiment of the present invention. 本発明の実施形態における副弁の他の例を示す図である。It is a figure which shows the other example of the subvalve in embodiment of this invention. 本発明の実施形態の膨張弁を備えたヒートポンプ式冷凍サイクルを示す図である。It is a figure which shows the heat pump type | mold refrigerating cycle provided with the expansion valve of embodiment of this invention.

次に、本発明の膨張弁の実施形態を図面を参照して説明する。図７は実施形態の膨張弁を設けたヒートポンプ式冷凍サイクルを示す図であり、先ず、図７に基づいて実施形態に係るヒートポンプ式冷凍サイクルについて説明ずる。図７において、符号１０1 ，１０2 は本発明の実施形態の第１の膨張弁及び第２の膨張弁であり、第１の膨張弁１０1 は室外ユニット１００に搭載され、第２の膨張弁１０2 は室内ユニット２００に搭載されている。膨張弁１０1 ，１０2 、室外熱交換器２０、室内熱交換器３０、流路切換弁４０、及び圧縮機５０は、それぞれ導管によって図示のように接続され、ヒートポンプ式の冷凍サイクルを構成している。 Next, an embodiment of the expansion valve of the present invention will be described with reference to the drawings. FIG. 7 is a view showing a heat pump refrigeration cycle provided with the expansion valve of the embodiment. First, the heat pump refrigeration cycle according to the embodiment will be described based on FIG. 7, reference numeral 10 1, 10 2 is the first expansion valve and the second expansion valve embodiments of the present invention, the first expansion valve 10 1 is mounted on the outdoor unit 100, a second expansion the valve 10 2 is mounted in the indoor unit 200. The expansion valves 10 1 and 10 2 , the outdoor heat exchanger 20, the indoor heat exchanger 30, the flow path switching valve 40, and the compressor 50 are respectively connected by conduits as shown in the figure, and constitute a heat pump type refrigeration cycle. ing.

冷凍サイクルの流路は流路切換弁４０により「冷房モード」および「暖房モード」の２通りの流路に切換えられる。冷房モードでは、圧縮機５０で圧縮された冷媒は流路切換弁４０から室外熱交換器２０に流入され、第１の膨張弁１０1 を介して管路ａを流れて第２の膨張弁１０2 に流入される。そして、この第２の膨張弁１０2 で冷媒が膨張され、室内熱交換機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。暖房モードでは、圧縮機５０で圧縮された冷媒は流路切換弁４０から室内熱交換器３０に流入され、第２の膨張弁１０2 、管路ａを通って第１の膨張弁１０1 に流入される。そして、この第１の膨張弁１０1 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。 The flow path of the refrigeration cycle is switched to two flow paths of “cooling mode” and “heating mode” by the flow path switching valve 40. 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, flows through the pipe line a via the first expansion valve 101, and the second expansion valve 10. Inflow into 2 . Then, the refrigerant is expanded by the second expansion valve 102 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 heating mode, the refrigerant compressed by the compressor 50 flows into the indoor heat exchanger 30 from the flow path switching valve 40, passes through the second expansion valve 10 2 , the pipe line a, and enters the first expansion valve 10 1 . Inflow. Then, the refrigerant is expanded by the first expansion valve 101 and circulated in the order of the outdoor heat exchanger 20, the flow path switching valve 40, and the compressor 50.

ここで、膨張弁１０1 ，１０2 は冷媒の流量を制御しない全開状態と、冷媒の流量を制御する絞り状態とをとり、全開状態では継手管１２から冷媒が流入して継手管１１から流出する。また、絞り状態では継手管１１から冷媒が流入して継手管１２から流出する。すなわち、冷房モードにおいては第１の膨張弁１０1 は全開状態で第２の膨張弁１０2 が絞り状態となり、また、暖房モードにおいては、第２の膨張弁１０2 が全開状態で第１の膨張弁１０1 が絞り状態となる。また、冷房モード及び暖房モードのいずれのモードでも、第１の膨張弁１０1 と第２の膨張弁１０2 を接続する管路ａでは冷媒の流れは大流量となり、絞り機能を持つ膨張弁手前での圧力損失を低減することができ、運転能力が向上する。 Here, the expansion valves 10 1 and 10 2 take a fully open state in which the refrigerant flow rate is not controlled and a throttle state in which the refrigerant flow rate is controlled. In the fully open state, the refrigerant flows in from the joint pipe 12 and flows out from the joint pipe 11. To do. In the throttled state, the refrigerant flows in from the joint pipe 11 and flows out from the joint pipe 12. That is, in the cooling mode 1 first expansion valve 10 is in a state the second expansion valve 10 2 is squeezed with the fully open state, and in the heating mode, the second expansion valve 10 2 are first in the fully open state expansion valve 10 1 is squeezed state. Also, in either mode of cooling mode and heating mode, the first expansion valve 10 1 and the second conduit refrigerant flow in a connecting the expansion valve 10 2 becomes the large flow rate, the expansion valve before having a stop function Pressure loss can be reduced, and the driving ability is improved.

次に、実施形態の膨張弁１０1 ，１０2 について説明する。図１は実施形態の膨張弁の絞り状態の縦断面図、図２は同膨張弁の全開状態の縦断面図、図３は実施形態における副弁の平面図（図３(A) ）及び縦断面図（図３(B) ）、図４は副弁のガイド部材と弁座部材の組立前の斜視図、図５は副弁の組立状態の斜視図である。なお、膨張弁１０1 ，１０2 の符号の添え字は、第１の膨張弁と第２の膨張弁とを区別するものであるが、以下の説明において両者を区別しない場合など添え字は適宜省略する。 Next, the expansion valves 10 1 and 10 2 of the embodiment will be described. 1 is a longitudinal sectional view of the expansion valve of the embodiment in a throttled state, FIG. 2 is a longitudinal sectional view of the expansion valve in a fully opened state, and FIG. 3 is a plan view of the auxiliary valve in the embodiment (FIG. 3A) and a longitudinal section. FIG. 3 is a perspective view of the auxiliary valve guide member and the valve seat member before assembly, and FIG. 5 is an assembled perspective view of the auxiliary valve. The subscripts of the reference numerals of the expansion valves 10 1 and 10 2 distinguish the first expansion valve and the second expansion valve. Omitted.

図１及び図２に示すように、膨張弁１０は、弁ハウジング１を有し、弁ハウジング１には円筒シリンダ状の主弁室１Ａを形成する本体部１ａと、本体部１ａの下端から下方に延びる筒状部１ｂを有している。弁ハウジング１には、主弁室１Ａの片側内周面に継手管１１が取り付けられ、この継手管１１の端部は主弁室１Ａに開口する第１ポート１１ａとなっている。また、筒状部１ｂ内の主弁室１Ａ側にはステンレス製の弁座リング３が取り付けられるとともに、この筒状部１ｂの下端部に継手管１２が取り付けられている。弁座リング３の内側は第２ポート３ａとなっている。   As shown in FIGS. 1 and 2, the expansion valve 10 includes a valve housing 1. The valve housing 1 includes a main body 1 a that forms a cylindrical cylinder-shaped main valve chamber 1 </ b> A, and a lower portion from the lower end of the main body 1 a. It has the cylindrical part 1b extended to. A joint pipe 11 is attached to the valve housing 1 on the inner peripheral surface on one side of the main valve chamber 1A, and the end of the joint pipe 11 serves as a first port 11a that opens to the main valve chamber 1A. Further, a stainless steel valve seat ring 3 is attached to the main valve chamber 1A side in the tubular portion 1b, and a joint pipe 12 is attached to a lower end portion of the tubular portion 1b. The inside of the valve seat ring 3 is a second port 3a.

主弁室１Ａ内には、副弁２が配設されている。図３に示すように、副弁２はガイド部材２１と弁座部材２２とで構成されている。ガイド部材２１は円盤部２１ａと３つのガイド板２１１，２１２，２１３とで構成されている。また、弁座部材２２は円盤部２１ａの中央に固着されており、この弁座部材２２の中央には弁ポート２２ａが形成されている。   A sub valve 2 is disposed in the main valve chamber 1A. As shown in FIG. 3, the auxiliary valve 2 includes a guide member 21 and a valve seat member 22. The guide member 21 includes a disk portion 21a and three guide plates 211, 212, and 213. The valve seat member 22 is fixed to the center of the disk portion 21a, and a valve port 22a is formed at the center of the valve seat member 22.

弁ハウジング１の上部には固定金具４１によって支持部材４が固着されている。支持部材４には軸Ｌ方向に長いガイド孔４２が形成され、ガイド孔４２に連通する均圧孔４３が形成されている。また、固定金具４１には均圧孔４４が形成されている。ガイド孔４２には円筒状の弁ホルダ５が軸Ｌ方向に摺動可能に挿通されている。これにより、弁ホルダ５は支持部材４を介して弁ハウジング１に対して軸Ｌ方向に移動可能に支持されている。   A support member 4 is fixed to the upper portion of the valve housing 1 by a fixing bracket 41. A long guide hole 42 is formed in the support member 4 in the direction of the axis L, and a pressure equalizing hole 43 communicating with the guide hole 42 is formed. Further, a pressure equalizing hole 44 is formed in the fixing bracket 41. A cylindrical valve holder 5 is inserted into the guide hole 42 so as to be slidable in the direction of the axis L. Thereby, the valve holder 5 is supported via the support member 4 so as to be movable in the direction of the axis L with respect to the valve housing 1.

弁ホルダ５は主弁室１Ａと同軸に取り付けられ、この弁ホルダ５の下端部には端部がニードル状でステンレス製の弁体５１が固着されている。弁体５１は、弁ホルダ５と共に軸Ｌ方向に移動することにより、弁ポート２２ａの開口面積を増減し、第１ポート１１ａから第２ポート３ａへ流れる流体の流量を制御して冷媒を絞る機能を果たす。なお、弁体５１は、図１に示すように最降下した全閉位置と、図２に示すように最上昇した全開位置との間で移動可能になっている。   The valve holder 5 is attached coaxially to the main valve chamber 1A, and a stainless steel valve body 51 having a needle-like end is fixed to the lower end portion of the valve holder 5. The valve body 51 moves in the direction of the axis L together with the valve holder 5 to increase or decrease the opening area of the valve port 22a and control the flow rate of the fluid flowing from the first port 11a to the second port 3a to throttle the refrigerant. Fulfill. In addition, the valve body 51 is movable between a fully closed position that is lowered as shown in FIG. 1 and a fully opened position that is raised as shown in FIG.

また、弁ホルダ５は、ステッピングモータ６のロータ軸６１に係合している。すなわち、ロータ軸６１の下端部にはフランジ部６１ａが一体形成され、このフランジ部６１ａが弁ホルダ５の上端部と共にワッシャ５２を挟み込み、このロータ軸６１の下端部が弁ホルダ５の上端部で回転可能に係合している。この係合により、弁ホルダ５がロータ軸６１によって回転可能に吊り下げた状態で支持されている。また、弁ホルダ５内には、バネ受け５３が軸Ｌ方向に移動可能に設けられ、バネ受け５３と弁体５１との間には圧縮コイルバネ５４が所定の荷重を与えられた状態で取り付けられている。これにより、バネ受け５３は、上側に付勢され、ロータ軸６１の下端部に当接係合している。   The valve holder 5 is engaged with the rotor shaft 61 of the stepping motor 6. That is, a flange portion 61 a is integrally formed at the lower end portion of the rotor shaft 61, and the flange portion 61 a sandwiches the washer 52 together with the upper end portion of the valve holder 5, and the lower end portion of the rotor shaft 61 is the upper end portion of the valve holder 5. It is rotatably engaged. By this engagement, the valve holder 5 is supported in a state of being rotatably suspended by the rotor shaft 61. A spring receiver 53 is provided in the valve holder 5 so as to be movable in the direction of the axis L, and a compression coil spring 54 is attached between the spring receiver 53 and the valve body 51 with a predetermined load applied. ing. As a result, the spring receiver 53 is biased upward and is in contact with and engaged with the lower end portion of the rotor shaft 61.

ロータ軸６１には雄ねじ部６１ｂが形成されており、この雄ねじ部６１ｂは支持部材４に形成された雌ねじ部４ａに螺合している。これにより、ロータ軸６１は回転に伴って軸Ｌ線方向に移動する。   The rotor shaft 61 is formed with a male screw portion 61 b, and the male screw portion 61 b is screwed into a female screw portion 4 a formed on the support member 4. As a result, the rotor shaft 61 moves in the direction of the axis L along with the rotation.

弁ハウジング１の上端には、ステッピングモータ６のケース６２が溶接等によって気密に固定されている。ケース６２内には、外周部を多極に着磁されたマグネットロータ６３が回転可能に設けられ、このマグネットロータ６３にはロータ軸６１が固着されている。なお、ケース６２の天井部にはマグネットロータ６３の回転を規制する回転ストッパ機構６４が設けられている。   A case 62 of the stepping motor 6 is airtightly fixed to the upper end of the valve housing 1 by welding or the like. In the case 62, a magnet rotor 63 whose outer periphery is magnetized in multiple poles is rotatably provided, and a rotor shaft 61 is fixed to the magnet rotor 63. A rotation stopper mechanism 64 that restricts the rotation of the magnet rotor 63 is provided on the ceiling of the case 62.

また、ケース６２の外周には、ステータコイル６５が配設されており、ステッピングモータ６は、ステータコイル６５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６３を回転させる。そして、このマグネットロータ６３の回転によってマグネットロータ６３と一体のロータ軸６１が回転し、この回転に伴うロータ軸６１の軸Ｌ方向移動によって弁ホルダ５と共に弁体５１が軸Ｌ方向に移動する。   A stator coil 65 is disposed on the outer periphery of the case 62, and the stepping motor 6 rotates the magnet rotor 63 according to the number of pulses when a pulse signal is given to the stator coil 65. Then, the rotor shaft 61 integral with the magnet rotor 63 is rotated by the rotation of the magnet rotor 63, and the valve body 51 is moved in the axis L direction together with the valve holder 5 by the movement of the rotor shaft 61 in the axis L direction accompanying the rotation.

以上の構成により、実施形態の膨張弁１０は以下のように動作する。図１は継手管１１（第１ポート１１ａ）側から高圧冷媒が流入されて、冷媒流量が制御され、継手管１２（弁座リング３の第２ポート３ａ）から膨張された冷媒が流出する状態を示している。この場合、第１ポート１１ａ及び主弁室１Ａ内が高圧で第２ポート３ａ側が低圧となるため、その冷媒圧力の差圧により、副弁２は第２ポート３ａの周囲の副弁座３１に着座して、この第２ポート３ａを閉状態とする。そして、弁体５１の軸Ｌ方向位置をステッピングモータ６で制御することにより、主弁室１Ａから弁体５１と弁ポート２２ａとの間を介して流れる冷媒流量が制御される。   With the above configuration, the expansion valve 10 of the embodiment operates as follows. FIG. 1 shows a state in which high-pressure refrigerant is introduced from the joint pipe 11 (first port 11a) side, the refrigerant flow rate is controlled, and the expanded refrigerant flows out from the joint pipe 12 (second port 3a of the valve seat ring 3). Is shown. In this case, since the inside of the first port 11a and the main valve chamber 1A is high pressure and the second port 3a side is low pressure, the sub valve 2 is connected to the sub valve seat 31 around the second port 3a due to the differential pressure of the refrigerant pressure. Sit down and close the second port 3a. Then, by controlling the position of the valve body 51 in the axis L direction by the stepping motor 6, the flow rate of the refrigerant flowing from the main valve chamber 1A through the valve body 51 and the valve port 22a is controlled.

一方、圧縮機５０を停止するとともに流路切換弁４０を切り換える。このとき、ステッピングモータ６で制御して、弁体５１を副弁２から離間する方向（上方）に移動し、再び圧縮機５０を駆動する。これにより、継手管１２（第２ポート３ａ）側から高圧冷媒を流入して、継手管１１（第１ポート１１ａ）から冷媒を流出する状態とすると、第２ポート３ａが高圧で主弁室１Ａ及び第１ポート１１ａ側が低圧となる。そして、冷媒圧力の差圧により副弁２は副弁座３１から離間し、図２の状態になる。すなわち、第２ポート３ａは全開状態となる。これにより、第２ポート３ａと主弁室１Ａを介して第１ポート１１ａに冷媒が解放されて流通するようになる。   On the other hand, the compressor 50 is stopped and the flow path switching valve 40 is switched. At this time, it is controlled by the stepping motor 6, the valve body 51 is moved in the direction (upward) away from the sub-valve 2, and the compressor 50 is driven again. Accordingly, when the high pressure refrigerant flows in from the joint pipe 12 (second port 3a) side and the refrigerant flows out from the joint pipe 11 (first port 11a), the second port 3a is at a high pressure and the main valve chamber 1A. And the 1st port 11a side becomes a low voltage | pressure. Then, the sub valve 2 is separated from the sub valve seat 31 by the differential pressure of the refrigerant pressure, and the state shown in FIG. That is, the second port 3a is fully opened. As a result, the refrigerant is released and circulated to the first port 11a via the second port 3a and the main valve chamber 1A.

次に、副弁２の詳細について説明する。図４に示すように、副弁２のガイド部材２１は、ステンレス板のプレス加工により形成されており、主弁室１Ａの軸Ｌに直角に交差する円盤部２１ａと、この円盤部２１ａの周囲３箇所に立設された３つのガイド板２１１，２１２，２１３とを一体にして構成されている。各ガイド板２１１，２１２，２１３は平板状（フラット）であり、円盤部２１ａに対して軸Ｌと平行な方向にＬ形に立設されている。また、円盤部２１ａの中央には略円形の嵌合孔２１ｂが形成されている。   Next, details of the auxiliary valve 2 will be described. As shown in FIG. 4, the guide member 21 of the auxiliary valve 2 is formed by pressing a stainless steel plate, and includes a disk portion 21a that intersects the axis L of the main valve chamber 1A at a right angle, and the periphery of the disk portion 21a. Three guide plates 211, 212, and 213 provided upright at three locations are integrally formed. Each guide plate 211, 212, 213 has a flat plate shape (flat), and is erected in an L shape in a direction parallel to the axis L with respect to the disk portion 21a. A substantially circular fitting hole 21b is formed at the center of the disk portion 21a.

このガイド部材２１のプレス加工時にはプレスは２度に分けて行い、ガイド板２１１，２１２，２１３の部分は図３及び図４に示す矢印Ｐ１の方向からプレスしている。また、ガイド板２１１，２１２，２１３以外の円盤部２１ａの端部の部分は、図４に示す矢印Ｐ２の方向からプレスしている。   When the guide member 21 is pressed, the pressing is performed twice, and the portions of the guide plates 211, 212, and 213 are pressed from the direction of the arrow P1 shown in FIGS. Moreover, the part of the edge part of the disc part 21a other than the guide plates 211, 212, and 213 is pressed from the direction of the arrow P2 shown in FIG.

副弁２の弁座部材２２は、ステンレスの切削加工により形成されており、下部に円錐台状の副弁部２２１と、この副弁部２２１の外周に形成された円盤状のフランジ部２２２と、上部に形成された円環状の環状ボス部２２３を一体にして構成されている。環状ボス部２２３は端部にいくに従って肉薄になるように形成されている。   The valve seat member 22 of the sub-valve 2 is formed by cutting stainless steel, and has a frustoconical sub-valve portion 221 at the bottom and a disc-shaped flange portion 222 formed on the outer periphery of the sub-valve portion 221. The annular annular boss portion 223 formed on the upper portion is integrally formed. The annular boss 223 is formed so as to become thinner toward the end.

以上の構成により、副弁２は以下のように組み付ける。弁座部材２２の環状ボス部２２３をガイド部材２１の嵌合孔２１ｂ内に挿通し、フランジ部２２２を円盤部２１ａの裏面に突き当てた状態で環状ボス部２２３の端部を外周側に広げるようにかしめる。これによりガイド部材２１と弁座部材２２が結合される。そして、ガイド部材２１の円盤部２１ａの端部と、弁座部材２２のフランジ部２２２の端部との接合部分（図３(A) に円弧状破線で示す接合部分）にスポット溶接を施す。   With the above configuration, the auxiliary valve 2 is assembled as follows. The annular boss portion 223 of the valve seat member 22 is inserted into the fitting hole 21b of the guide member 21, and the end portion of the annular boss portion 223 is widened to the outer peripheral side with the flange portion 222 abutting against the back surface of the disk portion 21a. Caulking like so. Thereby, the guide member 21 and the valve seat member 22 are combined. Then, spot welding is performed on a joint portion (joint portion indicated by an arc-shaped broken line in FIG. 3A) between the end portion of the disc portion 21a of the guide member 21 and the end portion of the flange portion 222 of the valve seat member 22.

かしめのみでガイド部材２１と弁座部材２２を結合する場合、環状ボス部２２３のかしめが甘いと、ガイド部材２１が弁座部材２２から脱落してしまう。逆にかしめが強すぎるとガイド部材２１が変形してしまい、弁ハウジングとの所定のクリアランスを確保できなくなる。その結果、最悪の場合、副弁２が弁ハウジング１内でロックしてしまう虞がある。また、スポット溶接のみでガイド部材２１と弁座部材２２を結合する場合、ガイド部材２１と弁座部材２２との間のクリアランスにより、ガイド部材２１の中心に弁座部材２２を保持することは困難である。そのため、前述のように環状ボス部２２３のかしめにより弁座部材２２に対するガイド部材２１の芯出しを行った後、スポット溶接を行うことにより、ガイド部材２１と弁座部材２２とを確実に固着することができるだけでなく、ガイド部材２１の中心に弁座部材２２を保持することができる。   When the guide member 21 and the valve seat member 22 are coupled only by caulking, the guide member 21 falls off the valve seat member 22 if the annular boss portion 223 is not caulked. Conversely, if the caulking is too strong, the guide member 21 is deformed and a predetermined clearance from the valve housing cannot be secured. As a result, in the worst case, the secondary valve 2 may be locked in the valve housing 1. Further, when the guide member 21 and the valve seat member 22 are coupled only by spot welding, it is difficult to hold the valve seat member 22 at the center of the guide member 21 due to the clearance between the guide member 21 and the valve seat member 22. It is. Therefore, after the guide member 21 is centered with respect to the valve seat member 22 by caulking the annular boss portion 223 as described above, the guide member 21 and the valve seat member 22 are securely fixed by spot welding. In addition, the valve seat member 22 can be held at the center of the guide member 21.

なお、図４に二点鎖線の円で囲った拡大断面図に示すように、円盤部２１ａの端部にはプレス時のダレ面とバリが形成されているが、前記のように矢印Ｐ２の方向からプレスしているので、ダレ面は弁座部材２２のフランジ部２２２と反対側にでき、バリはフランジ部２２２側にできる。円盤部２１ａはフランジ部２２２より径が僅かに大きくなるように形成されており、バリをフランジ部２２２の外に出すことにより、スポット溶接時に、このバリ部分が溶融する。これにより、円盤部２１ａとフランジ部２２２とを隙間無く密着させることができ、より確実にスポット溶接することができる。   In addition, as shown in the enlarged sectional view surrounded by a two-dot chain line circle in FIG. 4, a sag surface and a burr at the time of pressing are formed at the end of the disk portion 21a. Since pressing is performed from the direction, the sagging surface can be on the side opposite to the flange portion 222 of the valve seat member 22 and the burr can be on the flange portion 222 side. The disk portion 21a is formed to have a diameter slightly larger than that of the flange portion 222, and the burr portion is melted at the time of spot welding by taking the burr out of the flange portion 222. Thereby, the disk part 21a and the flange part 222 can be closely_contact | adhered without gap, and spot welding can be performed more reliably.

副弁２のガイド板２１１，２１２，２１３は平板状（フラット）であり、各ガイド板２１１，２１２，２１３の軸Ｌと平行な両端の縁が本体部１ａの内周面１ａ１（図３(A) 参照）に対して線接触で摺接し、主弁室１Ａ内で軸Ｌ方向に摺動可能となっている。また、ガイド板２１１，２１２，２１３は平板状であるので、ガイド板２１１，２１２，２１３と内周面１ａ１との間には間隙ができ、このガイド板２１１，２１２，２１３と内周面１ａ１との間にゴミ等が噛むことがなく、副弁２の摺動動作を安定した動作とすることができる。   The guide plates 211, 212, and 213 of the auxiliary valve 2 are flat (flat), and the edges of both ends parallel to the axis L of each guide plate 211, 212, and 213 are the inner peripheral surface 1a1 (FIG. A) is slidable in line contact with respect to the reference), and is slidable in the direction of the axis L in the main valve chamber 1A. Further, since the guide plates 211, 212, and 213 are flat, a gap is formed between the guide plates 211, 212, and 213 and the inner peripheral surface 1a1, and the guide plates 211, 212, and 213 and the inner peripheral surface 1a1 are formed. The sub-valve 2 can be operated in a stable manner without causing dust or the like to bite between them.

さらに、この副弁２のガイド部材２１をプレス加工するとき、ガイド板２１１，２１２，２１３の部分は、図３に示す矢印Ｐ１の方向からプレスするので、内側がバリ面となり、線接触する部分はダレ面となる。したがって、副弁２の摺動動作を安定した動作とすることができる。   Furthermore, when the guide member 21 of the sub-valve 2 is pressed, the portions of the guide plates 211, 212, and 213 are pressed from the direction of the arrow P1 shown in FIG. Becomes sagging. Therefore, the sliding operation of the auxiliary valve 2 can be made stable.

また、副弁２において、ガイド部材２１は薄板状のステンレス板で形成された軽量な部材であるので、例えば特許文献１の副弁（弁座部材２）の全体を切削加工で形成する従来に比べて、軽量化することができ、図１の状態から図２の状態に移行するとき、副弁２が容易に持ち上がり、安定した動作が得られる。さらに、弁座部材２２は切削加工により形成されているので、弁ポート２２ａを精度高く形成することができ、弁漏れを防止して信頼性の高い膨張弁が得られる。   In the auxiliary valve 2, since the guide member 21 is a lightweight member formed of a thin plate-like stainless steel plate, for example, the entire auxiliary valve (valve seat member 2) of Patent Document 1 is formed by cutting. In comparison, the weight can be reduced, and when the state shown in FIG. 1 is shifted to the state shown in FIG. 2, the auxiliary valve 2 is easily lifted and a stable operation can be obtained. Further, since the valve seat member 22 is formed by cutting, the valve port 22a can be formed with high accuracy, and a highly reliable expansion valve can be obtained by preventing valve leakage.

なお、当該膨張弁の組立時に、弁座リング３は弁ハウジング１の筒状部１ｂ内に内側から圧入され、この筒状部１ｂに対して、リング状のろう材を継手管１２に嵌め込んだ状態で継手管１２が挿通される。継手管１１も同様なろう材を嵌め込んだ状態で本体部１ａに挿通される。そして、組み付けたアセンブリを、ろう付け装置のフラックス無炉中にて加熱することで、継手管１１，１２が弁ハウジング１に対してろう付けされる。ここで、ろう付け装置の雰囲気条件によっては、溶け出したろう材の流れる量を制御するのが困難な場合があり、ろう材が弁座リングの第２ポートを通って副弁座に流れ出すと、弁座リングと副弁との当接面にろう材が付着して形状を不均一にするので弁漏れが生じる虞がある。しかしながら、この実施形態の弁座リング３は第２ポート３ａの継手管１２側内周に溝３２を形成している。したがって、継手管１２の周囲から弁座リング３側に流れ出したろう材は溝３２に溜まり、弁座３１に達することがない。   When the expansion valve is assembled, the valve seat ring 3 is press-fitted into the tubular portion 1b of the valve housing 1 from the inside, and a ring-shaped brazing material is fitted into the joint pipe 12 with respect to the tubular portion 1b. In this state, the joint pipe 12 is inserted. The joint pipe 11 is also inserted into the main body 1a with a similar brazing material fitted therein. And the joint pipes 11 and 12 are brazed with respect to the valve housing 1 by heating the assembled assembly in the flux furnace of a brazing apparatus. Here, depending on the atmospheric conditions of the brazing device, it may be difficult to control the amount of the molten brazing material flowing, and when the brazing material flows out to the secondary valve seat through the second port of the valve seat ring, Since the brazing material adheres to the contact surface between the valve seat ring and the sub-valve and makes the shape non-uniform, there is a risk of valve leakage. However, the valve seat ring 3 of this embodiment has a groove 32 formed on the inner periphery of the second port 3a on the side of the joint pipe 12. Accordingly, the brazing material that has flowed out from the periphery of the joint pipe 12 toward the valve seat ring 3 is accumulated in the groove 32 and does not reach the valve seat 31.

以上の実施形態では、副弁２は、ガイド板２１１，２１２，２１３が平板状である場合について説明したが、図６(A) に示すように、内側に湾曲した曲面状のガイド板７１１，７１２，７１３を持つ副弁２′でもよい。なお、図６にといて前記実施形態（図３）と同様あるいは対応する要素は同符号を付記して説明は省略する。ガイド板７１１，７１２，７１３は、弁ハウジング１の内周面１ａ１と逆方向に湾曲している。このように、本体部１ａの内周面１ａ１とガイド板７１１，７１２，７１３との間に間隙ができればよい。この場合も、プレス加工によるバリは内側に形成する。   In the above embodiment, the auxiliary valve 2 has been described with respect to the case where the guide plates 211, 212, and 213 have a flat plate shape. However, as shown in FIG. 6 (A), the curved guide plate 711 that is curved inward. A secondary valve 2 ′ having 712 and 713 may be used. In FIG. 6, the same or corresponding elements as those in the embodiment (FIG. 3) are denoted by the same reference numerals, and the description thereof is omitted. The guide plates 711, 712, and 713 are curved in the direction opposite to the inner peripheral surface 1a1 of the valve housing 1. In this way, it is sufficient if there are gaps between the inner peripheral surface 1a1 of the main body 1a and the guide plates 711, 712, 713. Also in this case, the burr | flash by press work is formed inside.

また、以上の実施形態では、副弁２，２′は、ガイド板が３枚の場合について説明したが、図６(B) に示すように、ガイド板８１１，８１２，８１３，８１４の４枚のガイド板を持つ副弁２″でもよい。このガイド板の枚数は３枚または４枚がよい。ガイド板の枚数が多くなると、本体部１ａの内周面１ａ１との間隙が狭くはり、ゴミ噛みが生じる可能性が高くなる。また、継手管１１と干渉するという問題も生じる。この４枚のガイド板も図６(A) に示すような、弁ハウジング１の内周面１ａ１と逆方向に湾曲した形状でもよい。この場合も、プレス加工によるバリは内側に形成する。   In the above embodiment, the sub-valve 2 and 2 ′ have been described with respect to the case where there are three guide plates. However, as shown in FIG. 6 (B), four guide plates 811, 812, 813 and 814 are used. The number of guide plates may be three or four. As the number of guide plates increases, the gap between the main body 1a and the inner peripheral surface 1a1 becomes narrower, and dust is generated. There is also a high possibility of biting, and there is also a problem of interference with the joint pipe 11. These four guide plates are also in the opposite direction to the inner peripheral surface 1a1 of the valve housing 1 as shown in FIG. In this case as well, the burr formed by pressing is formed inside.

１ 弁ハウジング
１Ａ 主弁室
１ａ 本体部
１ａ１ 内周面
１ｂ 筒状部
１１ 継手管
１１ａ 第１ポート
１２ 継手管
２ 副弁
２１ ガイド部材
２２ 弁座部材
２１ａ 円盤部
２１ｂ 嵌合孔
２１１，２１２，２１３ ガイド板
２２ａ 弁ポート２２ａ
２２１ 副弁部
２２２ フランジ部
２２３ 環状ボス部
３ 弁座リング
３ａ 第２ポート
３１ 副弁座
５ 弁ホルダ
５１ 弁体
６ ステッピングモータ
Ｌ 軸 DESCRIPTION OF SYMBOLS 1 Valve housing 1A Main valve chamber 1a Main-body part 1a1 Inner peripheral surface 1b Tubular part 11 Joint pipe 11a 1st port 12 Joint pipe 2 Subvalve 21 Guide member 22 Valve seat member 21a Disk part 21b Fitting hole 211,212,213 Guide plate 22a Valve port 22a
221 Sub valve portion 222 Flange portion 223 Annular boss portion 3 Valve seat ring 3a Second port 31 Sub valve seat 5 Valve holder 51 Valve body 6 Stepping motor L shaft

Claims (2)

シリンダ状の主弁室を構成する弁ハウジングと、該主弁室に連通する第１ポート及び該主弁室の軸方向端部に連通する第２ポートと、前記主弁室内に該主弁室の軸方向に移動可能に配置されて、主弁室と前記第２ポートとの間に弁ポートを有する副弁と、前記副弁に対する前記軸方向の移動により前記弁ポートを開閉する弁体とを備え、
冷媒を前記第１ポートから前記第２ポートへ流すとき、該第１ポートと第２ポートの差圧により前記副弁を前記第２ポートの周囲に着座させて該第２ポートを閉状態とするとともに、前記弁体により前記弁ポートへ流れる冷媒を絞り、冷媒を逆方向に流すとき、前記第２ポートと第１ポートの差圧により前記副弁を前記第２ポートから離間して該第２ポートを全開状態とするようにした膨張弁において、
前記副弁を、前記弁ハウジングの内周面に摺接するガイド部材であって金属板のプレス加工により形成されたガイド部材と、前記弁ポートを有し前記ガイド部材の中央に配置された弁座部材であって金属材の切削加工により形成された弁座部材とで構成し、
前記ガイド部材は、前記主弁室の軸に直角に交差する円盤部と、該円盤部の中央に形成された嵌合孔と、該円盤部の周囲に立設された複数のガイド板とを有し、
前記弁座部材は、円盤状のフランジ部と、該フランジ部の上部に形成された円環状の環状ボス部とを有し、
前記弁座部材の環状ボス部が前記ガイド部材の嵌合孔内に挿通され、前記環状ボス部の端部を外周側に広げるようにかしめることで、前記フランジ部と前記円盤部とが密着して結合され、かつ、前記円盤部の端部と前記フランジ部の端部との接合部分に溶接が施され、前記ガイド部材と前記弁座部材とが固着されていることを特徴とする膨張弁。 A valve housing constituting a cylindrical main valve chamber; a first port communicating with the main valve chamber; a second port communicating with an axial end of the main valve chamber; and the main valve chamber within the main valve chamber An auxiliary valve having a valve port between the main valve chamber and the second port, and a valve element that opens and closes the valve port by the axial movement relative to the auxiliary valve; With
When the refrigerant flows from the first port to the second port, the sub-valve is seated around the second port by the pressure difference between the first port and the second port to close the second port. In addition, when the refrigerant flowing to the valve port is throttled by the valve body and the refrigerant flows in the reverse direction, the second valve is separated from the second port by the differential pressure between the second port and the first port. In the expansion valve in which the port is fully open,
A guide member that is slidably in contact with the inner peripheral surface of the valve housing, the sub-valve being formed by pressing a metal plate, and a valve seat that has the valve port and is arranged at the center of the guide member It is composed of a valve seat member formed by cutting a metal material,
The guide member includes a disk portion intersecting at a right angle to the axis of said main valve chamber, and a fitting hole formed at the center of the circular platen, and a plurality of guide plates erected around the circular plate portion Have
The valve seat member has a disk-shaped flange portion and an annular annular boss portion formed on the upper portion of the flange portion ,
An annular boss portion of the valve seat member is inserted into a fitting hole of the guide member, and the flange portion and the disc portion are in close contact with each other by caulking the end portion of the annular boss portion so as to spread outward. expansion and coupled and welded joint portion between the end portion of the flange portion and the end portion of the disk portion is subjected, characterized in that said guide member and the valve seat member is fixed valve. 前記ガイド板の前記軸方向と平行な側縁におけるプレス加工によるバリが内側に形成され、かつ、前記スポット溶接が施された箇所の前記円盤部の前記フランジ部と反対側の縁にプレス加工によるダレ面がくるようにしたことを特徴とする請求項１に記載の膨張弁。 A burr formed by pressing at a side edge parallel to the axial direction of the guide plate is formed on the inner side, and the edge opposite to the flange portion of the disk portion at the spot-welded portion is formed by pressing. 2. The expansion valve according to claim 1 , wherein a sag surface is provided.
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