JP6596052B2 - Flow path switching valve - Google Patents

Flow path switching valve Download PDF

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JP6596052B2
JP6596052B2 JP2017189298A JP2017189298A JP6596052B2 JP 6596052 B2 JP6596052 B2 JP 6596052B2 JP 2017189298 A JP2017189298 A JP 2017189298A JP 2017189298 A JP2017189298 A JP 2017189298A JP 6596052 B2 JP6596052 B2 JP 6596052B2
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main valve
port
valve seat
valve body
pair
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JP2019065896A (en
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健資 田渕
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Fujikoki Corp
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Fujikoki Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/0655—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with flat slides
    • 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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/30—Details
    • 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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/30—Details
    • F16K3/314—Forms or constructions of slides; Attachment of the slide to the spindle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Sliding Valves (AREA)

Description

本発明は、弁体を移動させることにより流路の切り換えを行う流路切換弁に係り、例えば、ヒートポンプ式冷暖房システム等において流路切換を行うのに好適な流路切換弁に関する。   The present invention relates to a flow path switching valve that switches flow paths by moving a valve body, and more particularly to a flow path switching valve that is suitable for performing flow path switching in a heat pump air conditioning system or the like.

一般に、ルームエアコン、カーエアコン等のヒートポンプ式冷暖房システムは、圧縮機、室外熱交換器、室内熱交換器、及び膨張弁等に加えて、流路（流れ方向）切換手段としての流路切換弁を備えている。   Generally, a heat pump type air conditioning system such as a room air conditioner or a car air conditioner has a flow path switching valve as a flow path (flow direction) switching means in addition to a compressor, an outdoor heat exchanger, an indoor heat exchanger, an expansion valve, and the like. It has.

この種の流路切換弁としては、四方切換弁がよく知られているが、それに代えて六方切換弁を用いることが考えられている。   As this type of flow path switching valve, a four-way switching valve is well known, but it is considered to use a six-way switching valve instead.

以下に六方切換弁を備えたヒートポンプ式冷暖房システムの一例を図７（Ａ）、（Ｂ）を参照しながら簡単に説明する。図示例のヒートポンプ式冷暖房システム１００は、運転モード（冷房運転と暖房運転）の切り換えを六方切換弁１８０で行うようになっており、基本的には、圧縮機１１０、室外熱交換器１２０、室内熱交換器１３０、冷房用膨張弁１５０、及び暖房用膨張弁１６０を備え、それらの間に６個のポートｐＡ、ｐＢ、ｐＣ、ｐＤ、ｐＥ、ｐＦを有する六方切換弁１８０が配在されている。   Hereinafter, an example of a heat pump type air conditioning system having a six-way switching valve will be briefly described with reference to FIGS. 7 (A) and 7 (B). The heat pump type air conditioning system 100 in the illustrated example is configured to perform switching between operation modes (cooling operation and heating operation) by a six-way switching valve 180. Basically, the compressor 110, the outdoor heat exchanger 120, the indoor A heat exchanger 130, a cooling expansion valve 150, and a heating expansion valve 160 are provided, and a six-way switching valve 180 having six ports pA, pB, pC, pD, pE, and pF is disposed therebetween. Yes.

前記各機器間は導管（パイプ）等で形成される流路で接続されており、冷房運転モードが選択されたときには、図７（Ａ）に示される如くに、圧縮機１１０から吐出された高温高圧の冷媒は、六方切換弁１８０のポートｐＡからポートｐＢを介して室外熱交換器１２０に導かれ、ここで室外空気と熱交換して凝縮し、高圧の気液二相又は液冷媒となって冷房用膨張弁１５０に導入される。この冷房用膨張弁１５０により高圧の冷媒が減圧され、減圧された低圧の冷媒は、六方切換弁１８０のポートｐＥからポートｐＦを介して室内熱交換器１３０に導入され、ここで室内空気と熱交換（冷房）して蒸発し、室内熱交換器１３０からは低温低圧の冷媒が六方切換弁１８０のポートｐＣからポートｐＤを介して圧縮機１１０の吸入側に戻される。   The devices are connected by a flow path formed by a conduit (pipe) or the like, and when the cooling operation mode is selected, the high temperature discharged from the compressor 110 as shown in FIG. The high-pressure refrigerant is guided from the port pA of the six-way switching valve 180 to the outdoor heat exchanger 120 through the port pB, where it is condensed by exchanging heat with the outdoor air to become a high-pressure gas-liquid two-phase or liquid refrigerant. And introduced into the cooling expansion valve 150. The high-pressure refrigerant is depressurized by the cooling expansion valve 150, and the depressurized low-pressure refrigerant is introduced from the port pE of the six-way switching valve 180 to the indoor heat exchanger 130 through the port pF. The refrigerant exchanges (cools) and evaporates, and the low-temperature and low-pressure refrigerant is returned from the indoor heat exchanger 130 from the port pC of the six-way switching valve 180 to the suction side of the compressor 110 via the port pD.

それに対し、暖房運転モードが選択されたときには、図７（Ｂ）に示される如くに、圧縮機１１０から吐出された高温高圧の冷媒は、六方切換弁１８０のポートｐＡからポートｐＦを介して室内熱交換器１３０に導かれ、ここで室内空気と熱交換（暖房）して凝縮し、高圧の気液二相又は液冷媒となって暖房用膨張弁１６０に導入される。この暖房用膨張弁１６０により高圧の冷媒が減圧され、減圧された低圧の冷媒は、六方切換弁１８０のポートｐＣからポートｐＢを介して室外熱交換器１２０に導入され、ここで室外空気と熱交換して蒸発し、室外熱交換器１２０からは低温低圧の冷媒が六方切換弁１８０のポートｐＥからポートｐＤを介して圧縮機１１０の吸入側に戻される。   On the other hand, when the heating operation mode is selected, as shown in FIG. 7B, the high-temperature and high-pressure refrigerant discharged from the compressor 110 passes through the port pA of the six-way switching valve 180 through the port pF. It is led to the heat exchanger 130, where it is condensed by exchanging heat with room air (heating) and becomes a high-pressure gas-liquid two-phase or liquid refrigerant and introduced into the heating expansion valve 160. The high-pressure refrigerant is depressurized by the heating expansion valve 160, and the depressurized low-pressure refrigerant is introduced from the port pC of the six-way switching valve 180 to the outdoor heat exchanger 120 through the port pB. The refrigerant is evaporated and evaporated, and the low-temperature and low-pressure refrigerant is returned from the outdoor heat exchanger 120 from the port pE of the six-way switching valve 180 to the suction side of the compressor 110 via the port pD.

前記した如くのヒートポンプ式冷暖房システム等に組み込まれる六方切換弁（流路切換弁）として、特許文献１に所載の如くの、スライド式のものが知られている。このスライド式の六方切換弁は、スライド式主弁体を内蔵する弁本体（主弁ハウジング）と電磁式のパイロット弁（四方パイロット弁）とを有し、主弁ハウジングに、前記ポートｐＡ〜ｐＦが設けられるとともに、スライド式主弁体が左右方向に摺動可能に配在されている。主弁ハウジングにおけるスライド式主弁体の左右には、パイロット弁を介して圧縮機吐出側及び圧縮機吸入側に接続される、それぞれスライド式主弁体に結合された左右一対のピストン型パッキンにより画成される二つの作動室が設けられ、この二つの作動室への高圧流体（冷媒）の導入・排出を前記パイロット弁で選択的に行い、この二つの作動室の圧力差を利用して前記スライド式主弁体を左右方向に摺動させることで前記流路切換を行うようにされている。   As a six-way switching valve (flow path switching valve) incorporated in the heat pump type air conditioning system as described above, a sliding type as described in Patent Document 1 is known. This slide type six-way switching valve has a valve body (main valve housing) incorporating a slide type main valve body and an electromagnetic pilot valve (four-way pilot valve), and the ports pA to pF are provided in the main valve housing. Is provided, and a slide type main valve body is arranged to be slidable in the left-right direction. The left and right sides of the slide type main valve body in the main valve housing are connected to a compressor discharge side and a compressor suction side via a pilot valve by a pair of left and right piston type packings respectively coupled to the slide type main valve body. Two working chambers are defined, and high pressure fluid (refrigerant) is selectively introduced into and discharged from the two working chambers by the pilot valve, and the pressure difference between the two working chambers is utilized. The flow path switching is performed by sliding the sliding main valve body in the left-right direction.

特開平８−１７０８６４号公報JP-A-8-170864

前記した如くの従来の流路切換弁においては、次のような解決すべき課題がある。   The conventional flow path switching valve as described above has the following problems to be solved.

すなわち、特許文献１に所載のスライド式の六方切換弁（流路切換弁）では、前記６個のポートｐＡ〜ｐＦのうち５個のポートｐＢ〜ｐＦが軸線方向に並んで設けられているので、前記５個のポートｐＢ〜ｐＦが設けられる主弁座やスライド式主弁体が（軸線方向で）長くなり、スライド式主弁体が摺動自在に対接せしめられる主弁座の弁シート面やスライド式主弁体のシール面の面精度（平面度）の確保が難しく、初期漏れや耐久劣化による漏れ（弁漏れ）が増加するおそれがある。   That is, in the slide type six-way switching valve (flow path switching valve) described in Patent Document 1, five ports pB to pF among the six ports pA to pF are provided side by side in the axial direction. Therefore, the main valve seat and the slide type main valve body provided with the five ports pB to pF become longer (in the axial direction), and the main valve seat valve is slidably brought into contact with the slide type main valve body. It is difficult to ensure the surface accuracy (flatness) of the seat surface and the sealing surface of the slide type main valve body, and there is a risk that leakage due to initial leakage or durability deterioration (valve leakage) increases.

また、内容積が比較的小さな主弁ハウジング内において高圧流体（冷媒）が内壁面等に衝突するとともに、その流れ方向がクランク状に大きく変わるので、圧力損失が大きくなる嫌いがある。   In addition, the high pressure fluid (refrigerant) collides with the inner wall surface or the like in the main valve housing having a relatively small internal volume, and the flow direction is greatly changed in a crank shape.

上記に加えて、従来の流路切換弁、特に、前記したヒートポンプ式冷暖房システムに使用される流路切換弁では、主弁ハウジング内において高温高圧の冷媒（ポートｐＡからポートｐＢ、ポートｐＡからポートｐＦへ流れる冷媒）と低温低圧の冷媒（ポートｐＣからポートｐＤ、ポートｐＥからポートｐＤへ流れる冷媒）とが近接した状態で流される。詳しくは、高温高圧の冷媒と低温低圧の冷媒とが、冷房運転時には主弁座を介して隣接するポートｐＢとポートｐＣとに流され、暖房運転時には主弁座を介して隣接するポートｐＦとポートｐＣとに流されるが、その各ポートが設けられる主弁座は、一般に熱伝導率の高い金属で作製されているので、それらの間の熱交換量（つまり、熱損失）が大きくなって、システムの効率が悪くなるという問題もある。   In addition to the above, in the conventional flow path switching valve, in particular, the flow path switching valve used in the heat pump air conditioning system described above, a high-temperature and high-pressure refrigerant (port pA to port pB, port pA to port) in the main valve housing. The refrigerant that flows to pF) and the low-temperature and low-pressure refrigerant (the refrigerant that flows from port pC to port pD and from port pE to port pD) flow in close proximity. Specifically, the high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant are caused to flow to the adjacent ports pB and pC via the main valve seat during the cooling operation, and to the adjacent port pF via the main valve seat during the heating operation. Although the main valve seat provided with each port is generally made of a metal having high thermal conductivity, the amount of heat exchange between them (ie, heat loss) becomes large. There is also a problem that the efficiency of the system deteriorates.

本発明は、上記事情に鑑みてなされたもので、その目的とするところは、弁漏れし難くできるとともに、圧力損失を効果的に抑えることのできる流路切換弁を提供することにある。   The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a flow path switching valve that can prevent valve leakage and can effectively suppress pressure loss.

また、本発明の他の目的とするところは、ヒートポンプ式冷暖房システム等の高温高圧の流体と低温低圧の流体が流される環境で使用される場合において、熱損失を低減し得てヒートポンプ式冷暖房システムの効率を向上させることのできる流路切換弁を提供することにある。   Another object of the present invention is to reduce heat loss when used in an environment where a high-temperature and high-pressure fluid and a low-temperature and low-pressure fluid flow, such as a heat pump type air conditioning system. It is in providing the flow-path switching valve which can improve the efficiency of this.

前記の目的を達成すべく、本発明に係る流路切換弁は、基本的には、ピストン及び主弁室が配在された筒状の主弁ハウジング、複数のポートが開口せしめられた弁シート面を持つ主弁座、前記主弁室内に軸線方向に移動可能に配在されるとともに、前記弁シート面に摺動自在に対接せしめられたスライド式の主弁体、及び前記ピストンの往復移動に伴って前記主弁体を移動させるための連結体を備え、前記主弁室内で前記連結体を介して前記主弁体を移動させることにより、連通するポート間が切り換えられるようにされ、前記主弁ハウジングの軸線に対して反対側にそれぞれ複数のポートが開口せしめられるとともに、前記主弁体は、前記複数のポート間を選択的に連通させるＵターン通路がそれぞれに設けられた一対のスライド弁体が前記主弁座の弁シート面に対して直交する方向で背面合わせの状態で配在されて構成されており、前記連結体は、前記主弁座の弁シート面に対して平行に且つ前記主弁座の弁シート面に対して直交する方向で相互に離れて配置された一対の支持板部を有する一枚又は複数枚の板材からなり、前記一対の支持板部の各々に、前記一対のスライド弁体の各々が前記ピストンの往復移動に伴って移動するように連結、嵌合、もしくは係合せしめられており、前記連結体における前記支持板部と前記ピストンとの間に延在する接続板部に、別途の開口が形成されていることを特徴としている。 In order to achieve the above object, a flow path switching valve according to the present invention basically includes a cylindrical main valve housing in which a piston and a main valve chamber are arranged, and a valve seat in which a plurality of ports are opened. A main valve seat having a surface, a slidable main valve body slidably disposed in the main valve chamber and slidably brought into contact with the valve seat surface, and reciprocation of the piston It is provided with a connecting body for moving the main valve body with movement, and the main valve body is moved through the connecting body in the main valve chamber, so that the ports that communicate with each other are switched. A plurality of ports are opened on opposite sides of the axis of the main valve housing, and the main valve body is provided with a pair of U-turn passages that selectively communicate between the ports. Slide valve body in front The main valve seat is arranged in a back-to-back state in a direction orthogonal to the valve seat surface of the main valve seat, and the connecting body is parallel to the valve seat surface of the main valve seat and the main valve It is composed of one or a plurality of plate members having a pair of support plate portions arranged away from each other in a direction orthogonal to the valve seat surface of the seat, and each of the pair of support plate portions includes the pair of slides. Each of the valve bodies is connected, fitted, or engaged so as to move with the reciprocating movement of the piston, and a connection plate extending between the support plate portion and the piston in the connection body A separate opening is formed in the part .

好ましい態様では、前記一対の支持板部の各々に、前記一対のスライド弁体の各々が前記ピストンの往復移動に伴って軸線方向に一体的に移動自在に押動されるとともに、前記主弁座の弁シート面に対して直交する方向に摺動自在に嵌合せしめられる開口が形成される。   In a preferred aspect, each of the pair of slide valve bodies is pushed by each of the pair of support plate portions so as to be integrally movable in the axial direction along with the reciprocating movement of the piston, and the main valve seat. An opening that is slidably fitted in a direction perpendicular to the valve seat surface is formed.

他の好ましい態様では、前記一対の支持板部の各々は、前記一対のスライド弁体の各々における前記弁シート面寄りの部位で該一対のスライド弁体の各々に連結、嵌合、もしくは係合する。   In another preferred embodiment, each of the pair of support plate portions is connected to, fitted to, or engaged with each of the pair of slide valve bodies at a portion near the valve seat surface in each of the pair of slide valve bodies. To do.

別の好ましい態様では、前記連結体は、それぞれが前記支持板部を有する、逆向きに配置された同一寸法及び同一形状の一対の板材で構成される。   In another preferred embodiment, the coupling body is composed of a pair of plate materials having the same size and the same shape, each having the support plate portion, arranged in opposite directions.

更に好ましい態様では、前記一対の板材には、該一対の板材を相互に位置合わせするための突き合わせ段部が設けられる。   In a more preferred embodiment, the pair of plate members is provided with a butting step portion for aligning the pair of plate members with each other.

別の好ましい態様では、前記連結体は、前記一対の支持板部を有する一枚の板材で構成される。   In another preferable aspect, the connection body is constituted by a single plate member having the pair of support plate portions.

本発明に係る六方切換弁では、主弁ハウジングの軸線に対して反対側にそれぞれ複数のポートが開口せしめられ、主弁体は、前記複数のポートを選択的に連通させるＵターン通路がそれぞれに設けられた一対のスライド弁体が主弁座の弁シート面に対して直交する方向で背面合わせの状態で配在されて構成されており、主弁室内で主弁体を移動させることにより、連通するポート間が切り換えられるようにされている。そのため、従来のスライド式主弁体を使用した流路切換弁と比べて、ポートが設けられる主弁座や主弁体を（軸線方向で）短くできるので、主弁座の弁シート面や主弁体のシール面の面精度（平面度）が確保しやすくなり、弁漏れを抑えられるとともに、流体（例えば高圧流体（冷媒））がＵターン通路を介して流されるので、圧力損失を低減することもできる。   In the six-way switching valve according to the present invention, a plurality of ports are opened on the opposite side to the axis of the main valve housing, and the main valve body has U-turn passages for selectively communicating the plurality of ports. A pair of provided slide valve bodies are arranged in a back-to-back state in a direction orthogonal to the valve seat surface of the main valve seat, and by moving the main valve body in the main valve chamber, The communication ports can be switched. For this reason, the main valve seat and the main valve body provided with the port can be shortened (in the axial direction) as compared with the flow path switching valve using the conventional slide type main valve body. The surface accuracy (flatness) of the sealing surface of the valve body is easily ensured, valve leakage is suppressed, and fluid (for example, high-pressure fluid (refrigerant)) is flowed through the U-turn passage, thereby reducing pressure loss. You can also

上記に加えて、本発明に係る流路切換弁をヒートポンプ式冷暖房システム等の、高温高圧の冷媒と低温低圧の冷媒が流される環境で使用する場合、高温高圧の冷媒が流されるＵターン通路と低温低圧の冷媒が流されるＵターン通路が、例えば金属製の主弁座を介することなく比較的大きく離されて設けられるので、高温高圧の冷媒と低温低圧の冷媒とが金属製の主弁座を介して近接した状態で流される従来のものに比べて、それらの間の熱交換量（つまり、熱損失）を大幅に低減でき、そのため、システムの効率を向上できるという効果も得られる。   In addition to the above, when the flow path switching valve according to the present invention is used in an environment in which a high-temperature and high-pressure refrigerant and a low-temperature and low-pressure refrigerant are flowed, such as a heat pump air conditioning system, Since the U-turn passage through which the low-temperature and low-pressure refrigerant flows is provided with a relatively large distance without using, for example, a metal main valve seat, the high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant are made of metal. Compared with the conventional one that flows in close proximity via the heat exchanger, the amount of heat exchange (that is, heat loss) between them can be greatly reduced, so that the efficiency of the system can be improved.

また、本発明に係る流路切換弁では、連結体が、主弁座の弁シート面に対して平行に且つ前記主弁座の弁シート面に対して直交する方向（弁シート面の高さ方向）に離れて配置された一対の支持板部を有し、その一対の支持板部の各々に、一対のスライド弁体の各々がピストンの往復移動に伴って移動するように連結、嵌合、もしくは係合せしめられる。そのため、例えば連結体が主弁座の弁シート面に対して平行に配置された一枚の板材から構成される従来の流路切換弁と比べて、主弁体（詳しくは、主弁体を構成する各スライド弁体）を弁シート面に近い位置で押すことができ、主弁体の傾きを抑えてスムーズに移動（スライド）させられるので、これによっても、弁漏れを抑えられるとともに、摺動抵抗を抑えられるので、動作性を高めることができる。   In the flow path switching valve according to the present invention, the connecting body is parallel to the valve seat surface of the main valve seat and orthogonal to the valve seat surface of the main valve seat (height of the valve seat surface). A pair of support plate portions that are arranged apart from each other in the direction), and connected and fitted to each of the pair of support plate portions so that each of the pair of slide valve bodies moves in accordance with the reciprocating movement of the piston. Or engaged. Therefore, for example, compared with a conventional flow path switching valve in which a connecting body is formed of a single plate member arranged in parallel to the valve seat surface of the main valve seat, the main valve body (specifically, the main valve body is Each slide valve body) can be pushed at a position close to the valve seat surface, and the main valve body can be smoothly moved (slid) while suppressing the inclination of the main valve body. Since the dynamic resistance can be suppressed, the operability can be improved.

また、本発明に係る流路切換弁では、主弁体を構成する各スライド弁体は、弁シート面に対して上下動できるように各支持板部に支持されているので、シール性を確保しやすいといった利点もある。   Further, in the flow path switching valve according to the present invention, each slide valve body constituting the main valve body is supported by each support plate portion so as to be able to move up and down with respect to the valve seat surface. There is an advantage that it is easy to do.

上記した以外の、課題、構成、及び作用効果は、以下の実施形態により明らかにされる。   Problems, configurations, and operational effects other than those described above will be clarified by the following embodiments.

本発明に係る流路切換弁（六方切換弁）の一実施形態の第１連通状態（冷房運転時）を示す縦断面図。The longitudinal cross-sectional view which shows the 1st communication state (at the time of air_conditionaing | cooling operation) of one Embodiment of the flow-path switching valve (hexagonal switching valve) which concerns on this invention. 本発明に係る流路切換弁（六方切換弁）の一実施形態の第２連通状態（暖房運転時）を示す縦断面図。The longitudinal cross-sectional view which shows the 2nd communication state (at the time of heating operation) of one Embodiment of the flow-path switching valve (hexagonal switching valve) which concerns on this invention. 図１のＵ−Ｕ矢視線に従う断面図。FIG. 3 is a cross-sectional view taken along the line U-U in FIG. 1. 図１に示される六方切換弁の要部を拡大して示す要部拡大縦断面図。The principal part expansion longitudinal cross-sectional view which expands and shows the principal part of the six-way switching valve shown by FIG. 本発明に係る流路切換弁（六方切換弁）の一実施形態の連結体を構成する一対の連結板を示す図であり、（Ａ）は縦断面図、（Ｂ）は側面図、（Ｃ）は上面図。It is a figure which shows a pair of connection board which comprises the connection body of one Embodiment of the flow-path switching valve (hexagonal switching valve) which concerns on this invention, (A) is a longitudinal cross-sectional view, (B) is a side view, (C ) Is a top view. 本発明に係る流路切換弁（六方切換弁）に使用される四方パイロット弁を拡大して示す図であり、（Ａ）は第１連通状態（冷房運転時）（通電ＯＦＦ時）、（Ｂ）は第２連通状態（暖房運転時）（通電ＯＮ時）をそれぞれ示す縦断面図。It is a figure which expands and shows the four-way pilot valve used for the flow-path switching valve (6-way switching valve) which concerns on this invention, (A) is a 1st communication state (at the time of air_conditionaing | cooling operation) (at the time of electricity supply OFF), (B ) Is a longitudinal sectional view showing a second communication state (at the time of heating operation) (when energization is ON). 流路切換弁として六方切換弁が使用されたヒートポンプ式冷暖房システムの一例における、（Ａ）は冷房運転時、（Ｂ）は暖房運転時をそれぞれ示す概略構成図。In an example of a heat pump type air conditioning system in which a six-way switching valve is used as a flow path switching valve, (A) is a schematic configuration diagram illustrating a cooling operation, and (B) is a schematic configuration diagram illustrating a heating operation.

以下、本発明の実施形態を図面を参照しながら説明する。   Embodiments of the present invention will be described below with reference to the drawings.

図１及び図２は、本発明に係る流路切換弁としての六方切換弁の一実施形態を示す縦断面図であり、図１は、第１連通状態（冷房運転時）、図２は、第２連通状態（暖房運転時）を示す図である。図３は、図１のＵ−Ｕ矢視線に従う断面図である。   1 and 2 are longitudinal sectional views showing an embodiment of a six-way switching valve as a flow path switching valve according to the present invention. FIG. 1 shows a first communication state (during cooling operation), and FIG. It is a figure which shows a 2nd communication state (at the time of heating operation). 3 is a cross-sectional view taken along the line U-U in FIG.

なお、本明細書において、上下、左右、前後等の位置、方向を表わす記述は、説明が煩瑣になるのを避けるために図面に従って便宜上付けたものであり、実際にヒートポンプ式冷暖房システム等に組み込まれた状態での位置、方向を指すとは限らない。   In the present specification, descriptions indicating positions, directions such as up and down, left and right, and front and rear are provided for the sake of convenience in accordance with the drawings in order to avoid complicated explanation, and are actually incorporated in a heat pump type air conditioning system or the like. It does not necessarily indicate the position and direction in the state of being pressed.

また、各図において、部材間に形成される隙間や部材間の離隔距離等は、発明の理解を容易にするため、また、作図上の便宜を図るため、各構成部材の寸法に比べて大きくあるいは小さく描かれている場合がある。   In each drawing, the gap formed between the members, the separation distance between the members, etc. are larger than the dimensions of each constituent member for easy understanding of the invention and for convenience of drawing. Or it may be drawn small.

図示実施形態の六方切換弁１は、例えば前述した図７（Ａ）、（Ｂ）に示されるヒートポンプ式冷暖房システム１００における六方切換弁１８０として用いられるスライド式のもので、基本的に、シリンダ型の六方弁本体１０と、パイロット弁としての単一の電磁式四方パイロット弁９０とを備える。なお、本実施形態の六方切換弁１に備えられている６個のポートは、上記六方切換弁１８０の各ポートｐＡ〜ｐＦに対応させて同一の符号が付されている。   The six-way switching valve 1 of the illustrated embodiment is a slide type used as the six-way switching valve 180 in the heat pump type air conditioning system 100 shown in FIGS. 7A and 7B, for example, and is basically a cylinder type. 6-way valve main body 10 and a single electromagnetic four-way pilot valve 90 as a pilot valve. The six ports provided in the six-way switching valve 1 of the present embodiment are assigned the same reference numerals corresponding to the ports pA to pF of the six-way switching valve 180.

［六方弁本体１０の構成］
六方弁本体１０は、真鍮あるいはステンレス等の金属製とされた筒状の主弁ハウジング１１を有し、この主弁ハウジング１１に、一端側（上端側）から順次、第１作動室３１、第１ピストン２１、主弁室１２、第２ピストン２２、及び第２作動室３２が配在されている。前記第１及び第２ピストン２１、２２にはいずれにも、主弁ハウジング１１を気密的に仕切るべく、主弁ハウジング１１の内周面にその外周部が圧接するばね付きパッキンが取り付けられている。 [Configuration of the hexagonal valve body 10]
The six-way valve body 10 has a cylindrical main valve housing 11 made of a metal such as brass or stainless steel. The main valve housing 11 is provided with a first working chamber 31 and a first one in order from one end side (upper end side). 1 piston 21, the main valve chamber 12, the 2nd piston 22, and the 2nd working chamber 32 are arranged. Each of the first and second pistons 21 and 22 is provided with a spring-loaded packing whose outer peripheral portion is in pressure contact with the inner peripheral surface of the main valve housing 11 in order to hermetically partition the main valve housing 11. .

主弁ハウジング１１の上端には、容量可変の第１作動室３１を画成する第１ピストン２１の上方向への移動を阻止するストッパを兼ねる傘状の上端側蓋部材１１Ａが気密的に固着され、主弁ハウジング１１の下端には、容量可変の第２作動室３２を画成する第２ピストン２２の下方向への移動を阻止するストッパを兼ねる逆立傘状の下端側蓋部材１１Ｂが気密的に固着されている。上端側蓋部材１１Ａ及び下端側蓋部材１１Ｂには、第１作動室３１及び第２作動室３２に高圧流体（冷媒）を導入・排出するためのポートｐ１１、ｐ１２がそれぞれ取り付けられている。   At the upper end of the main valve housing 11, an umbrella-shaped upper end side lid member 11 </ b> A that also serves as a stopper that prevents the upward movement of the first piston 21 that defines the first working chamber 31 with variable capacity is fixed in an airtight manner. At the lower end of the main valve housing 11, there is an inverted umbrella-shaped lower end side lid member 11B that also serves as a stopper that prevents the second piston 22 that moves downward from the second piston 22 that defines the variable capacity second working chamber 32. Airtightly fixed. Ports p11 and p12 for introducing and discharging a high-pressure fluid (refrigerant) to the first working chamber 31 and the second working chamber 32 are respectively attached to the upper end side lid member 11A and the lower end side lid member 11B.

前記主弁ハウジング１１（の主弁室１２）には、合計で６個のポートが設けられている。   A total of six ports are provided in the main valve housing 11 (the main valve chamber 12 thereof).

詳しくは、前記主弁室１２の左部中央には、その表面（右面）が平坦な弁シート面とされた例えば金属製の第１主弁座（弁シート）１３がろう付け等により主弁ハウジング１１（の内周）に気密的に固着され、その第１主弁座１３の弁シート面に、左方に向けて延びる管継手からなる３個のポート（上端側から順次、ポートｐＢ、ポートｐＡ、ポートｐＦ）が縦並びで（軸線Ｏ方向に並んで）略等間隔に開口せしめられている。   Specifically, in the center of the left portion of the main valve chamber 12, a first main valve seat (valve seat) 13 made of, for example, metal, whose surface (right surface) is a flat valve seat surface is brazed or the like. Three ports (ports pB, sequentially from the upper end side), which are formed of pipe joints that are airtightly fixed to the housing 11 (the inner periphery thereof) and that extend to the left on the valve seat surface of the first main valve seat 13. Ports pA and pF) are opened at substantially equal intervals in a line (in the direction of the axis O).

また、前記主弁室１２の右部中央（第１主弁座１３に対向する位置、言い換えれば、軸線Ｏに対して第１主弁座１３の反対側の位置）には、その表面（左面）が平坦な弁シート面とされた例えば金属製の第２主弁座（弁シート）１４がろう付け等により主弁ハウジング１１（の内周）に気密的に固着され、その第２主弁座１４の弁シート面に、右方に向けて延びる管継手からなる３個のポート（上端側から順次、ポートｐＣ、ポートｐＤ、ポートｐＥ）が縦並びで（軸線Ｏ方向に並んで）略等間隔に開口せしめられている。   Further, at the center of the right portion of the main valve chamber 12 (a position facing the first main valve seat 13, in other words, a position opposite to the first main valve seat 13 with respect to the axis O), its surface (left surface) ) Is a flat valve seat surface, for example, a metal second main valve seat (valve seat) 14 is hermetically fixed to the main valve housing 11 (inner periphery) by brazing or the like, and the second main valve On the valve seat surface of the seat 14, three ports (ports pC, port pD, and port pE in order from the upper end side) are arranged vertically (lined up in the direction of the axis O). It is opened at equal intervals.

第１主弁座１３に設けられた各ポート（ポートｐＢ、ポートｐＡ、ポートｐＦ）と第２主弁座１４に設けられた各ポート（ポートｐＣ、ポートｐＤ、ポートｐＥ）とは、対向する位置（軸線Ｏに対して反対側）に設定されるとともに、本例では、第１主弁座１３及び第２主弁座１４に設けられた各ポートｐＡ〜ｐＦの口径は略同径に設定されている。   Each port (port pB, port pA, port pF) provided in the first main valve seat 13 and each port (port pC, port pD, port pE) provided in the second main valve seat 14 are opposed to each other. In addition to being set to a position (opposite side with respect to the axis O), in this example, the diameters of the ports pA to pF provided in the first main valve seat 13 and the second main valve seat 14 are set to substantially the same diameter. Has been.

前記主弁室１２内には、両側面（左面及び右面）が前記第１主弁座１３及び第２主弁座１４の弁シート面にそれぞれ摺動自在に対接せしめられる、レーストラック形の環状シール面を持つ断面矩形状のスライド式の主弁体１５が軸線Ｏ方向（上下方向）に移動可能に配在されている。   In the main valve chamber 12, racetrack-shaped, both side surfaces (left surface and right surface) are slidably brought into contact with the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14, respectively. A sliding main valve element 15 having a rectangular cross section having an annular sealing surface is disposed so as to be movable in the direction of the axis O (vertical direction).

前記主弁体１５は、例えば合成樹脂製とされ、第１主弁座１３側（左側）の第１スライド弁体１５Ａと、第２主弁座１４側（右側）の第２スライド弁体１５Ｂとが、背面合わせの状態で配在されて構成されている。   The main valve body 15 is made of, for example, synthetic resin, and the first slide valve body 15A on the first main valve seat 13 side (left side) and the second slide valve body 15B on the second main valve seat 14 side (right side). Are arranged in a back-to-back state.

第１スライド弁体１５Ａの左面側（第２スライド弁体１５Ｂ側とは反対側）には、第１主弁座１３の弁シート面に開口する３個のポートのうちの隣り合う２個のポート（ポートｐＢとポートｐＡ、あるいは、ポートｐＡとポートｐＦ）を選択的に連通させ得るような大きさの椀状窪みからなる第１Ｕターン通路（連通路）１６Ａが開設されている。また、第２スライド弁体１５Ｂの右面側（第１スライド弁体１５Ａ側とは反対側）には、第２主弁座１４の弁シート面に開口する３個のポートのうちの隣り合う２個のポート（ポートｐＣとポートｐＤ、あるいは、ポートｐＤとポートｐＥ）を選択的に連通させ得るような大きさの椀状窪みからなる第２Ｕターン通路（連通路）１６Ｂが開設されている。   On the left surface side of the first slide valve body 15A (on the opposite side to the second slide valve body 15B side), two adjacent ports among the three ports that open to the valve seat surface of the first main valve seat 13 are provided. A first U-turn passage (communication passage) 16A having a bowl-shaped depression having a size capable of selectively communicating ports (port pB and port pA, or port pA and port pF) is provided. Further, on the right surface side of the second slide valve body 15B (on the side opposite to the first slide valve body 15A side), two adjacent two of the three ports opened in the valve seat surface of the second main valve seat 14 are provided. A second U-turn passage (communication passage) 16B made of a bowl-shaped depression having a size capable of selectively communicating the ports (port pC and port pD, or port pD and port pE) is provided.

一方、第２スライド弁体１５Ｂの左面（第１スライド弁体１５Ａに対向する面）には、該第２スライド弁体１５Ｂの外形とほぼ同形の筒状部１５ｂが（左向きに）延設され、第１スライド弁体１５Ａの右面（第２スライド弁体１５Ｂに対向する面）には、該第１スライド弁体１５Ａの外形（言い換えれば、第２スライド弁体１５Ｂの外形）より若干小さい筒状の嵌合凸部１５ａが（右向きに）突設されている。前記嵌合凸部１５ａが前記筒状部１５ｂに（間にＯリング１８を挟んで）摺動自在に内嵌されることにより、第１スライド弁体１５Ａと第２スライド弁体１５Ｂとは、左右方向（軸線Ｏに対して垂直な方向であって第１主弁座１３に設けられた各ポート（ポートｐＢ、ポートｐＡ、ポートｐＦ）と第２主弁座１４に設けられた各ポート（ポートｐＣ、ポートｐＤ、ポートｐＥ）とが対向する方向）に相互に若干の移動自在、かつ、上下方向（軸線Ｏ方向）に一体的に移動自在とされている。   On the other hand, on the left surface of the second slide valve body 15B (the surface facing the first slide valve body 15A), a cylindrical portion 15b having substantially the same shape as the outer shape of the second slide valve body 15B is extended (toward the left). On the right surface of the first slide valve body 15A (the surface facing the second slide valve body 15B), a cylinder slightly smaller than the outer shape of the first slide valve body 15A (in other words, the outer shape of the second slide valve body 15B). A fitting projection 15a having a shape protrudes (toward the right). When the fitting convex portion 15a is slidably fitted into the cylindrical portion 15b (with an O-ring 18 interposed therebetween), the first slide valve body 15A and the second slide valve body 15B are: Left and right direction (directions perpendicular to the axis O and provided in the first main valve seat 13 (port pB, port pA, port pF) and ports provided in the second main valve seat 14 ( Port pC, port pD, and port pE) are slightly movable with respect to each other) and can be integrally moved in the vertical direction (axis O direction).

なお、第１スライド弁体１５Ａの嵌合凸部１５ａと第２スライド弁体１５Ｂの筒状部１５ｂとの配置関係は逆でも良い。つまり、第１スライド弁体１５Ａに筒状部を設け、第２スライド弁体１５Ｂに嵌合凸部を設け、第１スライド弁体１５Ａの筒状部に第２スライド弁体１５Ｂの嵌合凸部を内嵌して、当該第１スライド弁体１５Ａと第２スライド弁体１５Ｂとを一体としても良い。   The arrangement relationship between the fitting convex portion 15a of the first slide valve body 15A and the cylindrical portion 15b of the second slide valve body 15B may be reversed. That is, the first slide valve body 15A is provided with a cylindrical portion, the second slide valve body 15B is provided with a fitting projection, and the first slide valve body 15A is fitted with a fitting projection of the second slide valve body 15B. The first slide valve body 15 </ b> A and the second slide valve body 15 </ b> B may be integrated with each other by internal fitting.

また、図示例では、第１スライド弁体１５Ａの右面（における嵌合凸部１５ａより内側の部分）と第２スライド弁体１５Ｂの左面（における嵌合凸部１５ａより内側の部分）との間に、若干の隙間が形成されるとともに、第１スライド弁体１５Ａ（における第１Ｕターン通路１６Ａの底部）に、第１Ｕターン通路１６Ａと前記隙間とを連通する横孔からなる連通孔１６ａが設けられており、前記嵌合凸部１５ａと前記筒状部１５ｂとの間に（具体的には、嵌合凸部１５ａの外周に設けられた環状溝に）、シール部材としてのＯリング１８が介装されている。   In the illustrated example, between the right surface of the first slide valve body 15A (the portion inside the fitting convex portion 15a) and the left surface of the second slide valve body 15B (the portion inside the fitting convex portion 15a). In addition, a slight gap is formed, and a communication hole 16a including a lateral hole that connects the first U-turn passage 16A and the gap is provided in the first slide valve body 15A (the bottom of the first U-turn passage 16A). An O-ring 18 as a seal member is provided between the fitting convex portion 15a and the cylindrical portion 15b (specifically, in an annular groove provided on the outer periphery of the fitting convex portion 15a). It is intervened.

そのため、前記隙間を含む前記Ｏリング１８より内側の部分は、ポート（吐出側高圧ポート）ｐＡから第１Ｕターン通路１６Ａ及び連通孔１６ａを介して高圧流体（冷媒）が導入される圧力室１７とされている。この圧力室１７と主弁室１２とは、その間に配在された前記Ｏリング１８によりシール（封止）されている。   Therefore, the portion inside the O-ring 18 including the gap includes a pressure chamber 17 into which high-pressure fluid (refrigerant) is introduced from the port (discharge side high-pressure port) pA via the first U-turn passage 16A and the communication hole 16a. Has been. The pressure chamber 17 and the main valve chamber 12 are sealed (sealed) by the O-ring 18 disposed therebetween.

ここでは、図１〜図３とともに図４を参照すればよく分かるように、左右方向（軸線Ｏに対して垂直な方向）で視て、第１スライド弁体１５Ａにおける圧力室１７側（右面側）の受圧面積Ｓｂは第１主弁座１３側（左面側）の受圧面積Ｓａより大きくされる。   Here, as can be understood by referring to FIG. 4 together with FIGS. 1 to 3, the pressure chamber 17 side (right surface side) of the first slide valve body 15 </ b> A when viewed in the left-right direction (direction perpendicular to the axis O). ) Is larger than the pressure receiving area Sa on the first main valve seat 13 side (left surface side).

より詳しくは、左右方向に対して垂直な平面に対する前記圧力室１７の投影面積であって、前記圧力室１７内に導入された高圧冷媒によって第１スライド弁体１５Ａ（の右面）が左方向の圧力を受ける面の投影面積（受圧面積Ｓｂ）が、左右方向に対して垂直な平面に対する前記第１主弁座１３側の環状シール面の投影面積であって、ポート（環状シール面の内側）を流れる高圧冷媒によって第１スライド弁体１５Ａ（の左面）が右方向の圧力を受ける面の投影面積（受圧面積Ｓａ）より大きくされている。   More specifically, it is a projected area of the pressure chamber 17 with respect to a plane perpendicular to the left-right direction, and the first slide valve body 15A (the right surface thereof) is moved leftward by the high-pressure refrigerant introduced into the pressure chamber 17. The projected area (pressure-receiving area Sb) of the pressure receiving surface is the projected area of the annular seal surface on the first main valve seat 13 side with respect to a plane perpendicular to the left-right direction, and is a port (inside the annular seal surface). The first slide valve body 15A (the left surface thereof) is made larger than the projected area (pressure receiving area Sa) of the surface that receives the pressure in the right direction by the high-pressure refrigerant flowing through.

これにより、ポート（吐出側高圧ポート）ｐＡを介して第１Ｕターン通路１６Ａに高圧冷媒が導入され、該第１Ｕターン通路１６Ａに導入された高圧冷媒の一部が前記連通孔１６ａを介して圧力室１７に充填されたときに、圧力室１７（の高圧冷媒）から受ける圧力（より詳細には、圧力室１７（の高圧冷媒）から受ける圧力と第２Ｕターン通路１６Ｂを流れる冷媒（低圧冷媒）から受ける圧力との差圧）によって、第２スライド弁体１５Ｂの右面（の環状シール面）が第２主弁座１４の弁シート面に押し付けられるとともに、圧力室１７（の高圧冷媒）から受ける圧力と第１Ｕターン通路１６Ａを流れる冷媒（高圧冷媒）から受ける圧力との差圧によって、第１スライド弁体１５Ａの左面（の環状シール面）が第１主弁座１３の弁シート面に押し付けられるようになっている。   As a result, the high-pressure refrigerant is introduced into the first U-turn passage 16A via the port (discharge side high-pressure port) pA, and a part of the high-pressure refrigerant introduced into the first U-turn passage 16A is pressurized via the communication hole 16a. The pressure received from the pressure chamber 17 (high-pressure refrigerant thereof) when the chamber 17 is filled (more specifically, the pressure received from the pressure chamber 17 (high-pressure refrigerant thereof) and the refrigerant flowing through the second U-turn passage 16B (low-pressure refrigerant) The right surface (the annular seal surface) of the second slide valve body 15B is pressed against the valve seat surface of the second main valve seat 14 and received from the pressure chamber 17 (the high-pressure refrigerant). Due to the pressure difference between the pressure and the pressure received from the refrigerant (high-pressure refrigerant) flowing through the first U-turn passage 16A, the left surface (the annular seal surface) of the first slide valve body 15A is the valve seat surface of the first main valve seat 13. Which is pressed against way.

なお、本例では、第１スライド弁体１５Ａの第１Ｕターン通路１６Ａ及び第２スライド弁体１５Ｂの第２Ｕターン通路１６Ｂの略中央に、形状保持のための補強ピン１５ｃ、１５ｄが前後方向に向けて架設されている。   In this example, reinforcing pins 15c and 15d for maintaining the shape are provided in the front-rear direction at the approximate center of the first U-turn passage 16A of the first slide valve body 15A and the second U-turn passage 16B of the second slide valve body 15B. It is erected toward.

また、本例では、主弁体１５（を構成する第１スライド弁体１５Ａ及び第２スライド弁体１５Ｂ）の外周面（上下面及び前後面）に、後述する連結体２５の連結板２５Ａ、２５Ｂの矩形開口２５ｄ（の上下の端縁部）に嵌合せしめられる窪み面１５ｅが形成されている。   In this example, the connection plate 25A of the connection body 25 described later is provided on the outer peripheral surfaces (upper and lower surfaces and front and rear surfaces) of the main valve body 15 (the first slide valve body 15A and the second slide valve body 15B). A recessed surface 15e is formed to be fitted into the rectangular opening 25d (upper and lower edge portions) of 25B.

前記主弁体１５は、前述のように、第１スライド弁体１５Ａと第２スライド弁体１５Ｂとが一体となって軸線Ｏ方向に移動せしめられ、図１に示される如くの、ポートｐＦを開きかつポートｐＢとポートｐＡとを第１スライド弁体１５Ａの第１Ｕターン通路１６Ａを介して連通させるとともに、ポートｐＥを開きかつポートｐＣとポートｐＤとを第２スライド弁体１５Ｂの第２Ｕターン通路１６Ｂを介して連通させる冷房位置（上端位置）と、図２に示される如くの、ポートｐＢを開きかつポートｐＡとポートｐＦとを第１スライド弁体１５Ａの第１Ｕターン通路１６Ａを介して連通させるとともに、ポートｐＣを開きかつポートｐＤとポートｐＥとを第２スライド弁体１５Ｂの第２Ｕターン通路１６Ｂを介して連通させる暖房位置（下端位置）とを選択的にとり得るようにされている。   As described above, the first valve body 15A and the second slide valve body 15B are integrally moved in the direction of the axis O, and the main valve body 15 has a port pF as shown in FIG. The port pB and the port pA are opened and communicated via the first U-turn passage 16A of the first slide valve body 15A, the port pE is opened, and the port pC and the port pD are connected to the second U-turn of the second slide valve body 15B. The cooling position (upper end position) communicating with the passage 16B, and the port pB is opened and the ports pA and pF are opened via the first U-turn passage 16A of the first slide valve body 15A as shown in FIG. A heating position (lower end position) that opens the port pC and allows the port pD and the port pE to communicate with each other via the second U-turn passage 16B of the second slide valve body 15B. ) It is a to obtain selective to take.

主弁体１５の第１スライド弁体１５Ａは、移動時以外は３個のポートのうちの２個のポート（ポートｐＢとポートｐＡ、あるいは、ポートｐＡとポートｐＦ）の真上に位置し、主弁体１５の第２スライド弁体１５Ｂは、移動時以外は３個のポートのうちの２個のポート（ポートｐＣとポートｐＤ、あるいは、ポートｐＤとポートｐＥ）の真上に位置し、このときは、第１スライド弁体１５Ａと第２スライド弁体１５Ｂとの間に設けられた圧力室１７（に導入された高圧冷媒）からの圧力や圧縮コイルばね１９の付勢力によりそれぞれ左右に押圧されて第１主弁座１３及び第２主弁座１４の弁シート面に圧接せしめられている。   The first slide valve body 15A of the main valve body 15 is located directly above two of the three ports (port pB and port pA, or port pA and port pF) except during movement, The second slide valve body 15B of the main valve body 15 is located directly above two of the three ports (port pC and port pD, or port pD and port pE) except during movement, At this time, the pressure from the pressure chamber 17 (high-pressure refrigerant introduced into the pressure chamber 17) provided between the first slide valve body 15A and the second slide valve body 15B and the urging force of the compression coil spring 19 are changed to the left and right respectively. The pressure seats are pressed against the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14.

第１ピストン２１と第２ピストン２２とは、連結体２５により一体移動可能に連結されており、この連結体２５に、前記主弁体１５の第１スライド弁体１５Ａと第２スライド弁体１５Ｂとが左右方向に若干の摺動自在かつ前後方向及び上下方向での移動はほぼ阻止された状態で嵌合せしめられて支持されている。   The first piston 21 and the second piston 22 are connected to each other by a connecting body 25 so as to be integrally movable. The first sliding valve body 15A and the second slide valve body 15B of the main valve body 15 are connected to the connecting body 25. Are supported by being fitted in a state in which they are slightly slidable in the left-right direction and are substantially prevented from moving in the front-rear direction and the up-down direction.

前記連結体２５は、本例では、例えばプレス成形等で作製された、同一寸法及び同一形状の一対の板材で構成されており、各板材が、左右方向に直交するように（言い換えれば、第１主弁座１３及び第２主弁座１４の弁シート面に平行となるように）配置されるとともに、それら一対の板材が、左右方向（弁シート面に直交する方向）で相互に離れて対向配置されている。なお、以下、左側（第１スライド弁体１５Ａ側）に配置される板材を連結板２５Ａ、右側（第２スライド弁体１５Ｂ側）に配置される板材を連結板２５Ｂと称する。   In this example, the connecting body 25 is composed of a pair of plate materials having the same dimensions and the same shape, for example, produced by press molding or the like, so that each plate material is orthogonal to the left-right direction (in other words, the first The first and second main valve seats 13 and 14 are arranged so as to be parallel to the valve seat surfaces, and the pair of plate members are separated from each other in the left-right direction (direction perpendicular to the valve seat surface). Opposed. Hereinafter, the plate material arranged on the left side (first slide valve body 15A side) is referred to as a connection plate 25A, and the plate material arranged on the right side (second slide valve body 15B side) is referred to as a connection plate 25B.

より詳しくは、図１〜図３とともに図５を参照すればよく分かるように、各連結板２５Ａ、２５Ｂは、その中心から左右方向に延びる中心線（対称線）に対して対称な縦長矩形状の板材で構成されている。各連結板２５Ａ、２５Ｂの（上下方向の）中央部は、前記主弁体１５（の第１スライド弁体１５Ａ、第２スライド弁体１５Ｂ）を軸線Ｏ方向に一体的に移動自在に係合支持するための支持板部２５ａとされ、この支持板部２５ａ（つまり、連結板２５Ａ、２５Ｂの中央部）に、主弁体１５の第１スライド弁体１５Ａ、第２スライド弁体１５Ｂが左右側から摺動自在に嵌合せしめられる例えば角部が丸み付け（Ｒ付け）された矩形開口２５ｄが形成されている。主弁体１５の第１スライド弁体１５Ａ、第２スライド弁体１５Ｂは、第１及び第２ピストン２１、２２の往復移動に伴って前記連結体２５の各連結板２５Ａ、２５Ｂの矩形開口２５ｄ部分に押動されて冷房位置（上端位置）と暖房位置（下端位置）との間を行き来するようにされている。本例では、各連結板２５Ａ、２５Ｂの矩形開口２５ｄ部分が、主弁体１５の第１スライド弁体１５Ａ、第２スライド弁体１５Ｂにおける第１主弁座１３、第２主弁座１４の弁シート面寄りの部位を押動するように、前記各連結板２５Ａ、２５Ｂ（の支持板部２５ａ）が（左右方向で）離間配置される。   More specifically, as can be understood by referring to FIG. 5 together with FIG. 1 to FIG. It is composed of a plate material. The central portions (in the vertical direction) of the connecting plates 25A and 25B engage the main valve body 15 (the first slide valve body 15A and the second slide valve body 15B) so as to be movable integrally in the axis O direction. A support plate portion 25a for supporting the first slide valve body 15A and the second slide valve body 15B of the main valve body 15 is provided on the support plate portion 25a (that is, the central portion of the connecting plates 25A and 25B). For example, a rectangular opening 25d with rounded corners (R-attached) that is slidably fitted from the side is formed. The first slide valve body 15A and the second slide valve body 15B of the main valve body 15 are rectangular openings 25d of the connection plates 25A and 25B of the connection body 25 as the first and second pistons 21 and 22 reciprocate. By being pushed by the part, it goes back and forth between the cooling position (upper position) and the heating position (lower position). In this example, the rectangular openings 25d of the connecting plates 25A and 25B are formed on the first main valve seat 13 and the second main valve seat 14 of the first slide valve body 15A and the second slide valve body 15B of the main valve body 15, respectively. The connecting plates 25A and 25B (support plate portions 25a thereof) are spaced apart (in the left-right direction) so as to push the portion near the valve seat surface.

各連結板２５Ａ、２５Ｂにおける前記支持板部２５ａの上下は、第１ピストン２１又は第２ピストン２２まで延在する接続板部２５ｂとされ、この接続板部２５ｂ（言い換えれば、矩形開口２５ｄの上下）に、より詳しくは、主弁体１５が冷房位置（上端位置）をとるときに第１主弁座１３の下側のポートｐＦと第２主弁座１４の下側のポートｐＥの略真横に位置する部位に（ポートｐＦ、ｐＥと略同径の）円形開口２５ｅが形成されるとともに、主弁体１５が暖房位置（下端位置）をとるときに第１主弁座１３の上側のポートｐＢと第２主弁座１４の上側のポートｐＣの略真横に位置する部位に（ポートｐＢ、ｐＣと略同径の）円形開口２５ｅが形成されている。   The upper and lower sides of the support plate portion 25a in each of the connecting plates 25A and 25B are connection plate portions 25b extending to the first piston 21 or the second piston 22, and this connection plate portion 25b (in other words, the upper and lower sides of the rectangular opening 25d). More specifically, when the main valve body 15 assumes the cooling position (upper end position), the port pF on the lower side of the first main valve seat 13 and the port pE on the lower side of the second main valve seat 14 are substantially directly beside. A circular opening 25e (having substantially the same diameter as the ports pF and pE) is formed at a position located at the top of the first main valve seat 13 when the main valve body 15 takes the heating position (lower end position). A circular opening 25e (substantially the same diameter as the ports pB and pC) is formed in a portion located substantially beside the port pC on the upper side of the pB and the second main valve seat 14.

また、各連結板２５Ａ、２５Ｂ（の接続板部２５ｂ）の上下の端部は、対向配置される連結板２５Ｂ、２５Ａ側に向けて略９０°折り曲げられて形成された取付脚部２５ｃとされ、その取付脚部２５ｃに、当該連結板２５Ａ、２５Ｂを第１ピストン２１又は第２ピストン２２に連結するボルト３０を挿通するためのねじ穴２９が螺設されている（特に、図５（Ｃ）参照）。   Further, the upper and lower ends of each of the connecting plates 25A and 25B (the connecting plate portion 25b) are mounting leg portions 25c formed by being bent approximately 90 ° toward the opposingly arranged connecting plates 25B and 25A. The mounting leg 25c is screwed with a screw hole 29 for inserting a bolt 30 for connecting the connecting plates 25A and 25B to the first piston 21 or the second piston 22 (particularly, FIG. )reference).

また、本例では、組立性を考慮して（後で詳述）、各連結板２５Ａ、２５Ｂの取付脚部２５ｃの端部に、対向配置される連結板２５Ｂ、２５Ａに対して当該連結板２５Ａ、２５Ｂ（の左右方向及び前後方向の位置）を当接させて位置合わせする（すなわち、一対の連結板２５Ａ、２５Ｂを相互に位置合わせする）ための突き合わせ段部２５ｆが形成されている（特に、図５（Ｃ）参照）。   Further, in this example, in consideration of assemblability (described in detail later), the connection plate is connected to the connection plates 25B and 25A that are arranged opposite to the end portions of the mounting legs 25c of the connection plates 25A and 25B. Abutting step portion 25f is formed for aligning (ie, aligning the pair of connecting plates 25A and 25B with each other) by bringing 25A and 25B (the positions in the left and right direction and the front and rear direction) into contact with each other. In particular, see FIG.

本例では、前記したように、各連結板２５Ａ、２５Ｂは、同一寸法及び同一形状の板材で構成されているので、２枚の連結板２５Ａ、２５Ｂを左右方向で対向して配置するとともに、前記突き合わせ段部２５ｆを介して逆向きで（詳しくは、上下逆さまにして）組み合わせて（相互に位置合わせした状態で）配置し、各連結板２５Ａ、２５Ｂにおける支持板部２５ａの矩形開口２５ｄに前記主弁体１５の第１スライド弁体１５Ａ及び第２スライド弁体１５Ｂを（それぞれ左右方向から）配置する。そして、ボルト３０を介して各取付脚部２５ｃを前記第１ピストン２１又は第２ピストン２２に固定することで、前記主弁体１５の第１スライド弁体１５Ａと第２スライド弁体１５Ｂとが、左右方向に若干の摺動自在かつ前後方向及び上下方向での移動はほぼ阻止された状態で当該連結体２５に嵌合せしめられる。   In this example, as described above, each of the connecting plates 25A and 25B is composed of a plate material having the same dimensions and the same shape, so that the two connecting plates 25A and 25B are arranged facing each other in the left-right direction, Arranged in a reverse direction (specifically, upside down) through the abutting step portion 25f (in a state where they are aligned with each other) and arranged in a rectangular opening 25d of the support plate portion 25a in each of the connection plates 25A and 25B. The first slide valve body 15A and the second slide valve body 15B of the main valve body 15 are disposed (from the left and right directions, respectively). Then, by fixing each mounting leg portion 25c to the first piston 21 or the second piston 22 via the bolt 30, the first slide valve body 15A and the second slide valve body 15B of the main valve body 15 are connected. The connector 25 is fitted in the connecting body 25 in a state in which it is slightly slidable in the left-right direction and is substantially prevented from moving in the front-rear direction and the up-down direction.

連結体２５（の一対の連結板２５Ａ、２５Ｂ）に嵌合されて支持された主弁体１５は、第１及び第２ピストン２１、２２の往復移動に伴って前記連結体２５の連結板２５Ａ、２５Ｂにおける矩形開口２５ｄの上端縁部又は下端縁部に押動されて（ここでは、主弁体１５の第１スライド弁体１５Ａ及び第２スライド弁体１５Ｂの上下面が押圧されて）冷房位置（上端位置）と暖房位置（下端位置）との間を行き来するようにされている。   The main valve body 15 fitted and supported by the connecting body 25 (a pair of connecting plates 25A and 25B) is connected to the connecting plate 25A of the connecting body 25 as the first and second pistons 21 and 22 reciprocate. , 25B is pushed by the upper edge or the lower edge of the rectangular opening 25d (here, the upper and lower surfaces of the first slide valve body 15A and the second slide valve body 15B of the main valve body 15 are pressed) It moves between the position (upper position) and the heating position (lower position).

［六方弁本体１０の動作］
次に、上記した如くの構成を有する六方弁本体１０の動作を説明する。 [Operation of the hexagonal valve body 10]
Next, the operation of the six-way valve body 10 having the configuration as described above will be described.

主弁ハウジング１１内に配在された主弁体１５が暖房位置（下端位置）（図２に示される如くの第２連通状態）にあるときにおいて、後述する四方パイロット弁９０を介して、第２作動室３２を吐出側高圧ポートであるポートｐＡに連通させるとともに、第１作動室３１を吸入側低圧ポートであるポートｐＤに連通させると、第２作動室３２に高温高圧の冷媒が導入されるとともに、第１作動室３１から高温高圧の冷媒が排出される。そのため、主弁室１２の他端側（下端側）の第２作動室３２の圧力が主弁室１２の一端側（上端側）の第１作動室３１の圧力より高くなり、図１に示される如くに、第１、第２ピストン２１、２２及び主弁体１５が上方に移動して第１ピストン２１が上端側蓋部材１１Ａに接当係止され、主弁体１５が冷房位置（上端位置）（図１に示される如くの第１連通状態）をとる。   When the main valve body 15 disposed in the main valve housing 11 is in the heating position (lower end position) (second communication state as shown in FIG. 2), the first valve body 15 is disposed via the four-way pilot valve 90 described later. When the second working chamber 32 is connected to the port pA that is the discharge-side high-pressure port and the first working chamber 31 is connected to the port pD that is the suction-side low-pressure port, the high-temperature and high-pressure refrigerant is introduced into the second working chamber 32. At the same time, the high-temperature and high-pressure refrigerant is discharged from the first working chamber 31. Therefore, the pressure in the second working chamber 32 on the other end side (lower end side) of the main valve chamber 12 becomes higher than the pressure in the first working chamber 31 on one end side (upper end side) of the main valve chamber 12, and is shown in FIG. As shown, the first and second pistons 21 and 22 and the main valve body 15 are moved upward, the first piston 21 is contacted and locked to the upper end side lid member 11A, and the main valve body 15 is moved to the cooling position (upper end). Position) (first communication state as shown in FIG. 1).

これにより、ポートｐＡとポートｐＢとが（第１Ｕターン通路１６Ａを介して）連通せしめられ、ポートｐＣとポートｐＤとが（第２Ｕターン通路１６Ｂを介して）連通せしめられ、ポートｐＥとポートｐＦとが（主弁室１２を介して）連通せしめられるので、図７（Ａ）、（Ｂ）に示される如くのヒートポンプ式冷暖房システム１００において、冷房運転が行われる。   Thereby, the port pA and the port pB are communicated (via the first U-turn passage 16A), and the port pC and the port pD are communicated (via the second U-turn passage 16B), and the port pE and the port pF are communicated. Are communicated (via the main valve chamber 12), so that the cooling operation is performed in the heat pump type air conditioning system 100 as shown in FIGS. 7A and 7B.

主弁体１５が冷房位置（上端位置）（図１に示される如くの第１連通状態）にあるときにおいて、後述する四方パイロット弁９０を介して、第１作動室３１を吐出側高圧ポートであるポートｐＡに連通させるとともに、第２作動室３２を吸入側低圧ポートであるポートｐＤに連通させると、第１作動室３１に高温高圧の冷媒が導入されるとともに、第２作動室３２から高温高圧の冷媒が排出される。そのため、主弁室１２の一端側（上端側）の第１作動室３１の圧力が主弁室１２の他端側（下端側）の第２作動室３２の圧力より高くなり、図２に示される如くに、第１、第２ピストン２１、２２及び主弁体１５が下方に移動して第２ピストン２２が下端側蓋部材１１Ｂに接当係止され、主弁体１５が暖房位置（下端位置）（図２に示される如くの第２連通状態）をとる。   When the main valve body 15 is in the cooling position (upper end position) (first communication state as shown in FIG. 1), the first working chamber 31 is connected to the discharge-side high-pressure port via a four-way pilot valve 90 described later. When the second working chamber 32 is communicated with a port pA and the second working chamber 32 is communicated with a port pD which is a suction side low pressure port, a high-temperature and high-pressure refrigerant is introduced into the first working chamber 31 and the second working chamber 32 has a high temperature. High pressure refrigerant is discharged. Therefore, the pressure in the first working chamber 31 on one end side (upper end side) of the main valve chamber 12 becomes higher than the pressure in the second working chamber 32 on the other end side (lower end side) of the main valve chamber 12, and is shown in FIG. As shown, the first and second pistons 21 and 22 and the main valve body 15 are moved downward and the second piston 22 is contacted and locked to the lower end side lid member 11B, and the main valve body 15 is moved to the heating position (lower end). Position) (second communication state as shown in FIG. 2).

これにより、ポートｐＡとポートｐＦとが（第１Ｕターン通路１６Ａを介して）連通せしめられ、ポートｐＥとポートｐＤとが（第２Ｕターン通路１６Ｂを介して）連通せしめられ、ポートｐＣとポートｐＢとが（主弁室１２を介して）連通せしめられるので、図７（Ａ）、（Ｂ）に示される如くのヒートポンプ式冷暖房システム１００において、暖房運転が行われる。   Thereby, the port pA and the port pF are communicated (via the first U-turn passage 16A), and the port pE and the port pD are communicated (via the second U-turn passage 16B), and the port pC and the port pB are communicated. Are communicated (via the main valve chamber 12), so that the heating operation is performed in the heat pump air conditioning system 100 as shown in FIGS. 7 (A) and 7 (B).

［四方パイロット弁９０の構成］
パイロット弁としての四方パイロット弁９０は、その構造自体はよく知られているもので、図６（Ａ）、（Ｂ）に拡大図示されている如くに、基端側（左端側）外周に電磁コイル９１が外嵌固定された円筒状のストレートパイプからなる弁ケース９２を有し、該弁ケース９２に、基端側から順次、吸引子９５、圧縮コイルばね９６、プランジャ９７が直列的に配在されている。 [Configuration of the four-way pilot valve 90]
The structure of the four-way pilot valve 90 as a pilot valve is well known. As shown in enlarged views in FIGS. 6 (A) and 6 (B), an electromagnetic wave is provided on the outer periphery of the base end side (left end side). A valve case 92 is formed of a cylindrical straight pipe to which a coil 91 is fitted and fixed. A suction element 95, a compression coil spring 96, and a plunger 97 are arranged in series on the valve case 92 in this order from the base end side. Be present.

弁ケース９２の左端部は、吸引子９５の鍔状部（外周段丘部）に溶接等により密封接合されており、吸引子９５は、通電励磁用の電磁コイル９１の外周を覆うカバーケース９１Ａにボルト９２Ｂにより締結固定されている。   The left end portion of the valve case 92 is hermetically joined to the flange portion (outer peripheral terrace) of the attractor 95 by welding or the like, and the attractor 95 is attached to a cover case 91A that covers the outer periphery of the electromagnetic coil 91 for energization excitation. The bolt 92B is fastened and fixed.

一方、弁ケース９２の右端開口部には、高圧冷媒を導入するための細管挿着口（高圧導入ポートａ）を有するフィルタ付き蓋部材９８が溶接、ろう付け、かしめ等により気密的に取着されており、蓋部材９８とプランジャ９７と弁ケース９２とで囲まれる領域が弁室９９となっている。弁室９９には、蓋部材９８の細管挿着口（高圧導入ポートａ）に気密的に挿着された可撓性を有する高圧細管＃ａを介して前記ポート（吐出側高圧ポート）ｐＡから高温高圧の冷媒が導入されるようになっている。   On the other hand, a lid member 98 with a filter having a narrow tube insertion port (high pressure introduction port a) for introducing a high pressure refrigerant is hermetically attached to the right end opening of the valve case 92 by welding, brazing, caulking, or the like. A region surrounded by the lid member 98, the plunger 97, and the valve case 92 is a valve chamber 99. The valve chamber 99 is connected to the port (discharge-side high-pressure port) pA through a flexible high-pressure thin tube #a that is airtightly inserted into the thin tube insertion port (high-pressure introduction port a) of the lid member 98. A high-temperature and high-pressure refrigerant is introduced.

また、弁ケース９２におけるプランジャ９７と蓋部材９８との間には、その内端面が平坦な弁シート面とされた弁座９３がろう付け等により気密的に接合されており、この弁座９３の弁シート面（内端面）には、先端側（右端側）から順次、前記した六方弁本体１０の第１作動室３１に細管＃ｂを介して接続されるポートｂ、ポート（吸入側低圧ポート）ｐＤに細管＃ｃを介して接続されるポートｃ、第２作動室３２に細管＃ｄを介して接続されるポートｄが弁ケース９２の長手方向（左右方向）に沿って所定間隔をあけて横並びに開口せしめられている。   Further, between the plunger 97 and the lid member 98 in the valve case 92, a valve seat 93 whose inner end surface is a flat valve seat surface is airtightly joined by brazing or the like. In the valve seat surface (inner end surface), the port b and the port (suction side low pressure) are connected to the first working chamber 31 of the above-described hexagonal valve body 10 through the thin tube #b sequentially from the front end side (right end side). Port) port c connected to pD via narrow tube #c, and port d connected to second working chamber 32 via thin tube #d are spaced apart along the longitudinal direction (left-right direction) of valve case 92. Open and open side by side.

吸引子９５に対向配置されたプランジャ９７は、基本的には円柱状とされ、弁ケース９２内を軸方向（弁ケース９２の中心線Ｌに沿う方向）に摺動自在に配在されている。そのプランジャ９７の吸引子９５側とは反対側の端部には、弁体９４をその自由端側で厚み方向に摺動可能に保持する弁体ホルダ９４Ａがその基端部を取付具９４Ｂと共に圧入、かしめ等により取付固定されている。この弁体ホルダ９４Ａには、弁体９４を弁座９３に押し付ける方向（厚み方向）に付勢する板ばね９４Ｃが取り付けられている。弁体９４は、弁座９３の弁シート面に開口するポートｂ、ｃ、ｄ間の連通状態を切り換えるべく、当該弁座９３の弁シート面に対接せしめられた状態で、弁座９３の弁シート面をプランジャ９７の左右方向の移動に伴って摺動するようになっている。   The plunger 97 disposed to face the suction element 95 is basically cylindrical, and is slidably disposed in the valve case 92 in an axial direction (a direction along the center line L of the valve case 92). . At the end of the plunger 97 opposite to the suction element 95 side, a valve body holder 94A for holding the valve body 94 so as to be slidable in the thickness direction on its free end side has its base end together with the fixture 94B. It is fixed by press fitting or caulking. A leaf spring 94C for urging the valve body 94 in a direction (thickness direction) to press the valve body 94 against the valve seat 93 is attached to the valve body holder 94A. The valve body 94 is in contact with the valve seat surface of the valve seat 93 in order to switch the communication state between the ports b, c, and d opened on the valve seat surface of the valve seat 93. The valve seat surface slides as the plunger 97 moves in the left-right direction.

また、弁体９４には、弁座９３の弁シート面に開口する３個のポートｂ〜ｄのうちの隣り合うポートｂ−ｃ間、ｃ−ｄ間を選択的に連通させ得るような大きさの凹部９４ａが設けられている。   Further, the valve body 94 is large enough to selectively communicate between the adjacent ports bc and cd among the three ports b to d opened on the valve seat surface of the valve seat 93. A recess 94a is provided.

また、圧縮コイルばね９６は、吸引子９５とプランジャ９７との間に縮装されてプランジャ９７を吸引子９５から引き離す方向（図では、右方）に付勢するようになっているが、本例では、弁座９３（の左端部）が、プランジャ９７の右方への移動を阻止するストッパとされている。なお、このストッパの構成としては、その他の構成を採用し得ることは言うまでも無い。   The compression coil spring 96 is compressed between the suction element 95 and the plunger 97 and urges the plunger 97 in a direction (rightward in the drawing) to separate the plunger 97 from the suction element 95. In the example, the valve seat 93 (the left end portion thereof) is a stopper that prevents the plunger 97 from moving to the right. It goes without saying that other configurations can be adopted as the configuration of the stopper.

なお、上記四方パイロット弁９０は、取付具９２Ａを介して六方弁本体１０の背面側等の適宜の箇所に取付けられる。また、上記四方パイロット弁９０では、吸入側低圧ポートであるポートｐＤに細管＃ｃを接続しているが、中圧冷媒が流されるポートｐＣに細管＃ｃを接続してもよい。   The four-way pilot valve 90 is attached to an appropriate location such as the back side of the six-way valve body 10 via a fixture 92A. In the four-way pilot valve 90, the narrow tube #c is connected to the port pD that is the suction side low-pressure port, but the thin tube #c may be connected to the port pC through which the medium-pressure refrigerant flows.

［四方パイロット弁９０の動作］
上記した如くの構成とされた四方パイロット弁９０においては、電磁コイル９１への通電ＯＦＦ時には、図１及び図６（Ａ）に示される如くに、プランジャ９７は圧縮コイルばね９６の付勢力により、その右端が弁座９３に接当する位置まで押し動かされている。この状態では、弁体９４がポートｂとポートｃ上に位置し、その凹部９４ａによりポートｂとポートｃが連通するとともに、ポートｄと弁室９９とが連通するので、ポート（吐出側高圧ポート）ｐＡに流入する高圧流体が高圧細管＃ａ→弁室９９→ポートｄ→細管＃ｄ→ポートｐ１２を介して第２作動室３２に導入されるとともに、第１作動室３１の高圧流体がポートｐ１１→細管＃ｂ→ポートｂ→凹部９４ａ→ポートｃ→細管＃ｃ→ポート（吸入側低圧ポート）ｐＤへと流れて排出される。 [Operation of four-way pilot valve 90]
In the four-way pilot valve 90 configured as described above, when the energization of the electromagnetic coil 91 is turned off, as shown in FIGS. 1 and 6A, the plunger 97 is caused by the urging force of the compression coil spring 96. The right end is pushed and moved to a position where it contacts the valve seat 93. In this state, the valve element 94 is positioned on the port b and the port c, and the port b and the port c communicate with each other by the recess 94a, and the port d and the valve chamber 99 communicate with each other. ) The high-pressure fluid flowing into pA is introduced into the second working chamber 32 via the high-pressure narrow tube # a → the valve chamber 99 → the port d → the narrow tube # d → the port p12, and the high-pressure fluid in the first working chamber 31 is ported P11 → Narrow tube # b → Port b → Recess 94a → Port c → Narrow tube # c → Port (suction side low pressure port) pD is discharged.

それに対し、電磁コイル９１への通電をＯＮにすると、図２及び図６（Ｂ）に示される如くに、プランジャ９７は吸引子９５の吸引力により、その左端が吸引子９５に接当する位置まで（圧縮コイルばね９６の付勢力に抗して）引き寄せられる。このときには、弁体９４がポートｃとポートｄ上に位置し、その凹部９４ａによりポートｃとポートｄが連通するとともに、ポートｂと弁室９９とが連通するので、ポート（吐出側高圧ポート）ｐＡに流入する高圧流体が高圧細管＃ａ→弁室９９→ポートｂ→細管＃ｂ→ポートｐ１１を介して第１作動室３１に導入されるとともに、第２作動室３２の高圧流体がポートｐ１２→細管＃ｄ→ポートｄ→凹部９４ａ→ポートｃ→細管＃ｃ→ポート（吸入側低圧ポート）ｐＤへと流れて排出される。   On the other hand, when energization to the electromagnetic coil 91 is turned ON, the plunger 97 is positioned at the left end of the plunger 97 in contact with the suction element 95 by the suction force of the suction element 95 as shown in FIGS. (Against the biasing force of the compression coil spring 96). At this time, the valve element 94 is positioned on the port c and the port d, and the port c and the port d communicate with each other by the recess 94a, and the port b and the valve chamber 99 communicate with each other. The high-pressure fluid flowing into pA is introduced into the first working chamber 31 via the high-pressure narrow tube # a → valve chamber 99 → port b → thin tube # b → port p11, and the high-pressure fluid in the second working chamber 32 is port p12. → Narrow tube # d → Port d → Recess 94a → Port c → Narrow tube # c → Port (suction side low pressure port) pD is discharged.

したがって、電磁コイル９１への通電をＯＦＦにすると、六方弁本体１０の主弁体１５が暖房位置（第２連通状態）から冷房位置（第１連通状態）に移行し、前記した如くの流路切換が行われる一方、電磁コイル９１への通電をＯＮにすると、六方弁本体１０の主弁体１５が冷房位置（第１連通状態）から暖房位置（第２連通状態）に移行し、前記した如くの流路切換が行われる。   Therefore, when energization to the electromagnetic coil 91 is turned off, the main valve body 15 of the six-way valve body 10 shifts from the heating position (second communication state) to the cooling position (first communication state), and the flow path as described above. On the other hand, when energization to the electromagnetic coil 91 is turned on, the main valve body 15 of the six-way valve body 10 shifts from the cooling position (first communication state) to the heating position (second communication state), as described above. The flow path is switched as described above.

このように、本実施形態の六方切換弁１では、電磁式四方パイロット弁９０への通電をＯＮ／ＯＦＦで切り換えることで、六方切換弁１内を流通する高圧流体（高圧部分であるポートｐＡを流れる流体）と低圧流体（低圧部分であるポートｐＤを流れる流体）との差圧を利用して六方弁本体１０を構成する主弁体１５を主弁室１２内で移動させることにより、主弁ハウジング１１に合計で６個設けられたポート間の連通状態が切り換えられ、図７（Ａ）、（Ｂ）に示される如くのヒートポンプ式冷暖房システム１００において、暖房運転から冷房運転への切り換え、及び、冷房運転から暖房運転への切り換えを行うことができる。   Thus, in the six-way switching valve 1 of the present embodiment, the high-pressure fluid (the port pA that is the high-pressure portion is circulated) through the six-way switching valve 1 by switching the energization to the electromagnetic four-way pilot valve 90 by ON / OFF. The main valve body 15 constituting the six-way valve body 10 is moved in the main valve chamber 12 by using the differential pressure between the fluid flowing) and the low-pressure fluid (fluid flowing through the port pD which is the low-pressure portion). The communication state between the six ports provided in total in the housing 11 is switched, and in the heat pump air conditioning system 100 as shown in FIGS. 7A and 7B, switching from the heating operation to the cooling operation, and Switching from the cooling operation to the heating operation can be performed.

［六方切換弁（流路切換弁）１の作用効果］
以上の説明から理解されるように、本実施形態の六方切換弁１においては、主弁室１２に、ポートｐＢ、ポートｐＡ、及びポートｐＦが軸線Ｏ方向に並んで開口せしめられるとともに、ポートｐＢ、ポートｐＡ、及びポートｐＦとは軸線Ｏに対して反対側に、ポートｐＣ、ポートｐＤ、及びポートｐＥが軸線Ｏ方向に並んで開口せしめられ、主弁体１５は、前記３個のポート（ポートｐＢ、ポートｐＡ、及びポートｐＦ、並びに、ポートｐＣ、ポートｐＤ、及びポートｐＥ）を選択的に連通させる第１及び第２Ｕターン通路１６Ａ、１６Ｂがそれぞれに設けられた一対の第１及び第２スライド弁体１５Ａ、１５Ｂが主弁座（第１主弁座１３及び第２主弁座１４）の弁シート面に対して直交する方向で背面合わせの状態で配在されて構成されており、主弁室１２内で主弁体１５を移動させることにより、連通するポート間が切り換えられるようにされている。そのため、従来のスライド式主弁体を使用した流路切換弁と比べて、ポートが設けられる主弁座（第１主弁座１３及び第２主弁座１４）や主弁体１５を（軸線Ｏ方向で）短くできるので、主弁座（第１主弁座１３及び第２主弁座１４）の弁シート面や主弁体１５のシール面の面精度（平面度）が確保しやすくなり、弁漏れを抑えられるとともに、流体（例えば高圧流体（冷媒））が第１Ｕターン通路１６Ａを介して流されるので、圧力損失を低減することもできる。 [Effects of the six-way switching valve (channel switching valve) 1]
As understood from the above description, in the six-way switching valve 1 of the present embodiment, the port pB, the port pA, and the port pF are opened in the main valve chamber 12 along the axis O direction, and the port pB , Port pA, and port pF on the opposite side to the axis O, the port pC, port pD, and port pE are opened side by side in the direction of the axis O, and the main valve body 15 includes the three ports ( A pair of first and second U-turn passages 16A and 16B, which selectively connect the port pB, the port pA and the port pF, and the port pC, the port pD and the port pE), respectively. Two slide valve bodies 15A and 15B are arranged and arranged in a back-to-back state in a direction orthogonal to the valve seat surface of the main valve seat (the first main valve seat 13 and the second main valve seat 14). Ri, by moving the main valve body 15 in main valve chamber 12, is adapted between port communicating is switched. Therefore, the main valve seat (the first main valve seat 13 and the second main valve seat 14) provided with the port and the main valve body 15 (axis line) are compared with the flow path switching valve using the conventional slide type main valve body. Since it can be shortened (in the O direction), it becomes easy to ensure the surface accuracy (flatness) of the valve seat surface of the main valve seat (the first main valve seat 13 and the second main valve seat 14) and the seal surface of the main valve body 15. In addition to suppressing valve leakage, a fluid (for example, high-pressure fluid (refrigerant)) is caused to flow through the first U-turn passage 16A, so that pressure loss can be reduced.

また、本実施形態では、六方弁本体１０内を流れる流体（例えば低圧冷媒）が第２Ｕターン通路１６Ｂを介して流されるとともに、流体（例えば中圧冷媒）が主弁室１２内を左右方向に（ストレート状に）流されるので、これによっても、圧力損失を低減することが可能となる。   Further, in the present embodiment, fluid (for example, low-pressure refrigerant) flowing in the six-way valve body 10 is flowed through the second U-turn passage 16B, and fluid (for example, medium-pressure refrigerant) is moved in the main valve chamber 12 in the left-right direction. As a result, the pressure loss can be reduced.

上記に加えて、本実施形態の六方切換弁１をヒートポンプ式冷暖房システム等の、高温高圧の冷媒と低温低圧の冷媒が流される環境で使用する場合、高温高圧の冷媒が流される第１Ｕターン通路１６Ａと低温低圧の冷媒が流される第２Ｕターン通路１６Ｂが、例えば金属製の主弁座を介することなく比較的大きく離されて設けられるので、高温高圧の冷媒と低温低圧の冷媒とが金属製の主弁座を介して近接した状態で流される従来のものに比べて、それらの間の熱交換量（つまり、熱損失）を大幅に低減でき、そのため、システムの効率を向上できるという効果も得られる。   In addition to the above, when the six-way switching valve 1 of the present embodiment is used in an environment in which a high-temperature and high-pressure refrigerant and a low-temperature and low-pressure refrigerant flow, such as a heat pump type air conditioning system, the first U-turn passage through which the high-temperature and high-pressure refrigerant flows. 16A and the second U-turn passage 16B through which the low-temperature and low-pressure refrigerant flows are provided relatively apart from each other without a metal main valve seat, for example, so that the high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant are made of metal. Compared to the conventional one that flows in close proximity through the main valve seat, the amount of heat exchange between them (ie heat loss) can be greatly reduced, and the system efficiency can be improved. can get.

また、本実施形態の六方切換弁１では、連結体２５が、主弁座（第１主弁座１３及び第２主弁座１４）の弁シート面に対して平行に且つ前記主弁座（第１主弁座１３及び第２主弁座１４）の弁シート面に対して直交する方向（弁シート面の高さ方向）に離れて配置された一対の支持板部２５ａを有し、その一対の支持板部２５ａの各々に、一対の第１及び第２スライド弁体１５Ａ、１５Ｂの各々がピストン２１、２２の往復移動に伴って移動するように連結、嵌合、もしくは係合せしめられる。そのため、例えば連結体が主弁座の弁シート面に対して平行に配置された一枚の板材から構成される従来の流路切換弁と比べて、主弁体１５（詳しくは、主弁体１５を構成する各第１及び第２スライド弁体１５Ａ、１５Ｂ）を弁シート面に近い位置で押すことができ、主弁体１５の傾きを抑えてスムーズに移動（スライド）させられるので、これによっても、弁漏れを抑えられるとともに、摺動抵抗を抑えられるので、動作性を高めることができる。   Further, in the six-way switching valve 1 of the present embodiment, the connecting body 25 is parallel to the valve seat surface of the main valve seat (the first main valve seat 13 and the second main valve seat 14) and the main valve seat ( The first main valve seat 13 and the second main valve seat 14) have a pair of support plate portions 25a arranged away from each other in the direction orthogonal to the valve seat surface (the height direction of the valve seat surface), Each of the pair of first and second slide valve bodies 15A and 15B is connected to, fitted to, or engaged with each of the pair of support plate portions 25a so as to move as the pistons 21 and 22 reciprocate. . Therefore, the main valve body 15 (specifically, the main valve body in detail) is compared with a conventional flow path switching valve in which, for example, the connecting body is formed of a single plate member arranged parallel to the valve seat surface of the main valve seat. 15 can be pushed at a position close to the valve seat surface, and the main valve body 15 can be smoothly moved (slid) while suppressing the inclination of the main valve body 15. Therefore, valve leakage can be suppressed and sliding resistance can be suppressed, so that the operability can be improved.

また、本実施形態の六方切換弁１では、主弁体１５を構成する各第１及び第２スライド弁体１５Ａ、１５Ｂは、弁シート面に対して上下動できるように各支持板部２５ａに支持されているので、シール性を確保しやすいといった利点もある。   Further, in the six-way switching valve 1 of the present embodiment, the first and second slide valve bodies 15A and 15B constituting the main valve body 15 are attached to the support plate portions 25a so as to move up and down with respect to the valve seat surface. Since it is supported, there is also an advantage that it is easy to ensure sealing performance.

なお、上記実施形態では、主弁ハウジング１１の軸線Ｏに対して反対側にそれぞれ３個ずつ合計６個のポートｐＡ〜ｐＦが開口せしめられた六方切換弁を例示して説明したが、主弁ハウジング１１（の主弁室１２）に設けられるポートの数や位置、主弁ハウジング１１の構成や形状、主弁ハウジング１１（の主弁室１２）内に配在される主弁体１５の構成や形状等は、図示例に限られないことは勿論である。   In the above embodiment, a six-way switching valve in which a total of six ports pA to pF are opened on the opposite side to the axis O of the main valve housing 11 has been described as an example. The number and position of ports provided in the housing 11 (the main valve chamber 12), the configuration and shape of the main valve housing 11, and the configuration of the main valve body 15 disposed in the main valve housing 11 (the main valve chamber 12) Needless to say, the shape and the like are not limited to the illustrated examples.

また、上記実施形態では、連結体２５として、それぞれが矩形開口２５ｄ付きの支持板部２５ａを有する、同一寸法及び同一形状の一対の板材で構成される例を説明したが、前記連結体２５は、例えば一枚の板材を折り曲げ等して、左右方向で離間して対向配置された一対の支持板部２５ａ等を形成するようにしてもよい。また、上記実施形態では、連結体２５を構成する各連結板２５Ａ、２５Ｂにおける接続板部２５ｂが、支持板部２５ａと同様に（左右方向で）離間して配置されているが、各連結板２５Ａ、２５Ｂにおける接続板部２５ｂの一部もしくは全部を相互に近づく方向に変形させて対接させてもよいことは当然である。   Moreover, although the said embodiment demonstrated the example comprised with a pair of board | plate material of the same dimension and the same shape which each has the support plate part 25a with the rectangular opening 25d as the connection body 25, the said connection body 25 is the following. For example, a pair of support plate portions 25a and the like may be formed by bending a single plate material and facing each other in the left-right direction. Moreover, in the said embodiment, although the connection plate part 25b in each connection plate 25A, 25B which comprises the connection body 25 is spaced apart similarly to the support plate part 25a (in the left-right direction), each connection plate Of course, part or all of the connecting plate portion 25b in 25A and 25B may be deformed in a direction approaching each other and brought into contact with each other.

また、上記実施形態の六方切換弁１では、四方パイロット弁９０を用いて主弁室１２内で主弁体１５を駆動する構成について説明したが、例えば四方パイロット弁９０に代えてモータを用いて主弁室１２内で主弁体１５を駆動する構成でも良い。   In the six-way switching valve 1 of the above embodiment, the configuration in which the main valve body 15 is driven in the main valve chamber 12 using the four-way pilot valve 90 has been described. For example, instead of the four-way pilot valve 90, a motor is used. The main valve body 15 may be driven in the main valve chamber 12.

また、本実施形態の六方切換弁１は、ヒートポンプ式冷暖房システムのみならず、他のシステム、装置、機器類にも組み込めることは勿論である。   Of course, the six-way switching valve 1 of the present embodiment can be incorporated not only in the heat pump air conditioning system but also in other systems, devices, and devices.

１ 六方切換弁（流路切換弁）
１０ 六方弁本体
１１ 主弁ハウジング
１１Ａ 上端側蓋部材
１１Ｂ 下端側蓋部材
１２ 主弁室
１３ 第１主弁座（弁シート）
１４ 第２主弁座（弁シート）
１５ 主弁体
１５Ａ 第１スライド弁体
１５Ｂ 第２スライド弁体
１５ａ 第１スライド弁体の嵌合凸部
１５ｂ 第２スライド弁体の筒状部
１６Ａ 第１Ｕターン通路（連通路）
１６Ｂ 第２Ｕターン通路（連通路）
１６ａ 連通孔
１７ 圧力室
１８ Ｏリング
２１ 第１ピストン
２２ 第２ピストン
２５ 連結体
２５Ａ、２５Ｂ 一対の連結板（板材）
２５ａ 支持板部
２５ｂ 接続板部
２５ｃ 取付脚部
２５ｄ 矩形開口
２５ｅ 円形開口
２５ｆ 突き合わせ段部
３１ 第１作動室
３２ 第２作動室
９０ 四方パイロット弁
ｐＡ、ｐＢ、ｐＣ、ｐＤ、ｐＥ、ｐＦ ポート 1 Six-way switching valve (channel switching valve)
10 6-way valve body 11 Main valve housing 11A Upper end side lid member 11B Lower end side lid member 12 Main valve chamber 13 First main valve seat (valve seat)
14 Second main valve seat (valve seat)
15 Main valve body 15A 1st slide valve body 15B 2nd slide valve body 15a Fitting convex part 15b of 1st slide valve body Cylindrical part 16A of 2nd slide valve body 1st U turn path (communication path)
16B 2nd U-turn passage (communication passage)
16a Communication hole 17 Pressure chamber 18 O-ring 21 1st piston 22 2nd piston 25 Connection body 25A, 25B A pair of connection plate (plate material)
25a Support plate portion 25b Connection plate portion 25c Mounting leg portion 25d Rectangular opening 25e Circular opening 25f Butting step portion 31 First working chamber 32 Second working chamber 90 Four-way pilot valve pA, pB, pC, pD, pE, pF port

Claims (6)

ピストン及び主弁室が配在された筒状の主弁ハウジング、複数のポートが開口せしめられた弁シート面を持つ主弁座、前記主弁室内に軸線方向に移動可能に配在されるとともに、前記弁シート面に摺動自在に対接せしめられたスライド式の主弁体、及び前記ピストンの往復移動に伴って前記主弁体を移動させるための連結体を備え、前記主弁室内で前記連結体を介して前記主弁体を移動させることにより、連通するポート間が切り換えられるようにされた流路切換弁であって、
前記主弁ハウジングの軸線に対して反対側にそれぞれ複数のポートが開口せしめられるとともに、前記主弁体は、前記複数のポート間を選択的に連通させるＵターン通路がそれぞれに設けられた一対のスライド弁体が前記主弁座の弁シート面に対して直交する方向で背面合わせの状態で配在されて構成されており、
前記連結体は、前記主弁座の弁シート面に対して平行に且つ前記主弁座の弁シート面に対して直交する方向で相互に離れて配置された一対の支持板部を有する一枚又は複数枚の板材からなり、前記一対の支持板部の各々に、前記一対のスライド弁体の各々が前記ピストンの往復移動に伴って移動するように連結、嵌合、もしくは係合せしめられており、
前記連結体における前記支持板部と前記ピストンとの間に延在する接続板部に、別途の開口が形成されていることを特徴とする流路切換弁。 A cylindrical main valve housing in which a piston and a main valve chamber are arranged, a main valve seat having a valve seat surface in which a plurality of ports are opened, and an axially movable arrangement in the main valve chamber A slidable main valve body that is slidably brought into contact with the valve seat surface, and a connecting body for moving the main valve body in accordance with the reciprocating movement of the piston. A flow path switching valve adapted to switch between communicating ports by moving the main valve body through the connecting body,
A plurality of ports are opened on opposite sides of the axis of the main valve housing, and the main valve body is provided with a pair of U-turn passages that selectively communicate between the ports. The slide valve body is arranged in a back-to-back state in a direction orthogonal to the valve seat surface of the main valve seat,
The connecting body has a pair of support plate portions arranged in parallel to the valve seat surface of the main valve seat and separated from each other in a direction perpendicular to the valve seat surface of the main valve seat. Alternatively, each of the pair of support plate portions is connected, fitted, or engaged with each of the pair of slide valve bodies so as to move along with the reciprocating movement of the piston. And
A flow path switching valve , wherein a separate opening is formed in a connection plate portion extending between the support plate portion and the piston in the coupling body . 前記一対の支持板部の各々に、前記一対のスライド弁体の各々が前記ピストンの往復移動に伴って軸線方向に一体的に移動自在に押動されるとともに、前記主弁座の弁シート面に対して直交する方向に摺動自在に嵌合せしめられる開口が形成されていることを特徴とする請求項１に記載の流路切換弁。   Each of the pair of slide valve bodies is pushed by the pair of support plate portions so as to be integrally movable in the axial direction along with the reciprocation of the piston, and the valve seat surface of the main valve seat The flow path switching valve according to claim 1, wherein an opening that is slidably fitted in a direction orthogonal to is formed. 前記一対の支持板部の各々は、前記一対のスライド弁体の各々における前記弁シート面寄りの部位で該一対のスライド弁体の各々に連結、嵌合、もしくは係合していることを特徴とする請求項１又は２に記載の流路切換弁。   Each of the pair of support plate portions is connected to, fitted to, or engaged with each of the pair of slide valve bodies at a portion close to the valve seat surface in each of the pair of slide valve bodies. The flow path switching valve according to claim 1 or 2. 前記連結体は、それぞれが前記支持板部を有する、逆向きに配置された同一寸法及び同一形状の一対の板材で構成されることを特徴とする請求項１から３のいずれか一項に記載の流路切換弁。 The coupling body, each having the supporting plate portion, wherein that it is composed of a pair of plates of the same size and same shape arranged opposite the preceding claims, characterized in any one of 3 Flow path switching valve. 前記一対の板材には、該一対の板材を相互に位置合わせするための突き合わせ段部が設けられていることを特徴とする請求項４に記載の流路切換弁。 5. The flow path switching valve according to claim 4 , wherein the pair of plate members is provided with a butting step portion for aligning the pair of plate members with each other. 前記連結体は、前記一対の支持板部を有する一枚の板材で構成されることを特徴とする請求項１から３のいずれか一項に記載の流路切換弁。 The flow path switching valve according to any one of claims 1 to 3 , wherein the coupling body is configured by a single plate member having the pair of support plate portions.
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