JP4016535B2

JP4016535B2 - Charge valve

Info

Publication number: JP4016535B2
Application number: JP18941099A
Authority: JP
Inventors: 秀雄原田
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 1999-07-02
Filing date: 1999-07-02
Publication date: 2007-12-05
Anticipated expiration: 2019-07-02
Also published as: JP2001021238A

Description

【０００１】
【発明の属する技術分野】
本発明は、圧力容器の充填口に装着されて高圧流体が逆流することを防止するチャージバルブに関するもので、二酸化炭素を冷媒とする冷凍サイクルのごとく、高圧側の圧力が冷媒の臨界圧力以上となる超臨界冷凍サイクルに適用して有効である。
【０００２】
【従来の技術】
一般的に、チャージバルブでは、内圧が作用した状態ではバルブが閉じるように構成されているとともに、コイルバネ等の弾性手段によりバルブを閉じる向きの力を弁体にさせている。そして、高圧流体を充填するときには、コイルバネの弾性力に対向する力を弁体に作用させてバルブを開いて圧力容器内に高圧流体を充填する。
【０００３】
【発明が解決しようとする課題】
ところで、超臨界冷凍サイクルでは、１００ＭＰａ以上の高圧にて冷媒（二酸化炭素）を高圧配管（高圧容器）内に充填するので、充填する際にコイルバネが全圧縮（密着）してしまい、コイルバネに発生する応力が材料の降伏応力（弾性限界）を越えて永久変形してしまう。
【０００４】
これに対して、コイルバネの線径を拡大する等の手段を施せば、コイルバネに発生する応力が材料の降伏応力（弾性限界）を越えてしまうことを防止できるものの、コイルバネの大型化及びコイルバネの弾性係数が増大するので、チャージバルブを開弁させるに必要な力が大きくなり、冷媒の充填効率及び充填作業が悪化してしまう。
【０００５】
因みに、チャージバルブは、内圧により閉じる構造となっているので、コイルバネの弾性係数が大きくなっても、チャージバルブのシール性は大きく向上しない。したがって、コイルバネの大型化及びコイルバネの弾性係数の増大は、冷媒の充填効率及び充填作業の悪化を招くのみである。
【０００６】
本発明は、上記点に鑑み、コイルバネ等の弾性手段の大型化及びコイルバネの弾性係数の増大を招くことなく、弾性手段が永久変形してしまうことを防止するを目的とする。
【０００７】
本発明は、上記目的を達成するために、請求項１〜５に記載の発明では、充填口（８１０）に固定されて高圧流体が流通する流通路（９１２）が形成されたバルブ本体（９１０）と、バルブ本体（９１０）に対して圧力容器（８００）の外方側に向けて移動することにより流通路（９１２）を閉じ、バルブ本体（９１０）に対して圧力容器（８００）の内方側に向けて移動することにより流通路（９１２）を開く弁体（９２０）と、流通路（９１２）を閉じる向きの弾性力を弁体（９２０）に作用させる弾性手段（９３０）と、弁体（９２０）と一体的に可動してバルブ本体（９１０）と衝突して前記弁体（９２０）が開く向きに移動する際の最大移動量を規制するストッパ手段（９２４）とを有し、バルブ本体（９１０）は、流通路（９１２）が軸方向に延びるように円柱状に形成されており、弁体（９２０）の最大移動量は、弾性手段（９３０）が密着するまで過度に撓むことが防止される移動量であって、バルブ本体（９１０）は、流通路（９１２）が軸方向に延びるように円柱状に形成されており、弁体（９２０）は、流通路（９１２）のうち圧力容器（８００）の内方側端部にて流通路（９１２）を開閉する弁部（９２１）、及び弁部（９２１）から流通路（９１２）に沿って圧力容器（８００）の外方側に向けて延びる作動軸（９２２）を有して形成されており、弾性手段（９３０）は、バルブ本体（９１０）と作動軸（９２２）における圧力容器（８００）の外方側端部にて作動軸（９２２）よりも大きい径に形成された大径部との間に配設されており、さらに、ストッパ手段（９２４）は、作動軸（９２２）においてバルブ本体（９１０）と大径部との間に設けられ、バルブ本体（９１０）における弾性部材（９３０）との接触面に衝突して弁体（９２０）の最大移動量を規制することを特徴とする。
【０００８】
これにより、弾性手段（９３０）が過度に撓むことを防止できるので、弾性手段（９３０）の大型化及び弾性手段（９３０）の弾性係数の増大を招くことなく、弾性手段（９３０）が永久変形してしまうことを防止できる。
【０００９】
請求項２に記載の発明では、高圧側の圧力が冷媒の臨界圧力以上となる超臨界冷凍サイクルに適用され、圧力容器（８００）は、高圧冷媒が充填される高圧配管（８００）であることを特徴とする。
【００１０】
これにより、弾性手段（９３０）が過度に撓むことを防止できるので、弾性手段（９３０）の大型化及び弾性手段（９３０）の弾性係数の増大を招くことなく、弾性手段（９３０）が永久変形してしまうことを防止できる。
【００１１】
請求項３に記載の発明では、ストッパ手段（９２４）は、作動軸（９２２）に一体形成されていることを特徴としている。
請求項４に記載の発明では、ストッパ手段（９２４）は、作動軸（９２２）の外形を打ち出し成形した段付き部であることを特徴とする。
請求項５に記載の発明では、ストッパ手段（９２４）は、作動軸（９２２）に固定された円筒部（９２４ａ）の端部に円盤状のフランジ部（９２４ｂ）を有するハット状の部材であることを特徴とする。
因みに、上記各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示す一例である。
【００１２】
【発明の実施の形態】
（第１実施形態）
本実施形態は、本発明に係るチャージバルブを二酸化炭素を冷媒とする車両用の超臨界冷凍サイクル（以下、サイクルと略す。）に適用したものであり、図１はサイクルの模式図である。
【００１３】
図１中、１００は冷媒を吸入圧縮する圧縮機であり、この圧縮機１００は、電磁クラッチ１１０を介して車両走行用エンジン（図示せず）から駆動力を得て稼動する。２００は圧縮機１００から吐出した冷媒を大気と熱交換して冷却するとともに、内部の圧力が冷媒の臨界圧力を超える放熱器でり、３００は放熱器２００から流出する冷媒を減圧するとともに、放熱器２００出口側の冷媒圧力に基づいて放熱器２００出口側の圧力を制御する圧力制御弁である。そして、放熱器２００から圧力制御弁３００に至る高圧配管（圧力容器）８００には、本実施形態に係るチャージバルブ９００が設けられている。
【００１４】
４００は圧力制御弁３００にて減圧された冷媒を蒸発させて空気を冷却する蒸発器であり、５００はサイクル内の余剰冷媒を貯えるとともに、蒸発器４００から流出する冷媒を気相冷媒と液相冷媒とに分離して気相冷媒を圧縮機１００側に流出させるアキュームレータ（気液分離手段）である。
【００１５】
なお、６００は蒸発器４００にて冷却された空気の温度を検出する温度センサ（温度検出手段）であり、電子制御装置（ＥＣＵ）７００は、温度センサ６００の検出温度に基づいて電磁クラッチ１１０のＯＮ−ＯＦＦを制御している。具体的には、検出温度が３℃以下となったときには、電磁クラッチ１１０をＯＦＦとして圧縮機１００を停止させ、検出温度が４℃以上となったときには、電磁クラッチ１１０をＯＮとして圧縮機１００を稼動させる。
【００１６】
次に、チャージバルブ９００について述べる。
【００１７】
チャージバルブ９００のバルブ本体９１０は、図２（ａ）に示すように、圧力容器をなす高圧配管８００に溶接されて充填口８１０を形成するバルブステム９０１にねじ固定されており、バルブ本体９１０とバルブステム９０１との隙間は、ニトリルゴム製のＯリング９１１により密閉（シール）されている。
【００１８】
そして、バルブ本体９１０は、高圧配管８００の厚み方向が軸方向と一致するように、ステンレス材から略円柱状に形成されているとともに、冷媒の充填時に冷媒が流通する流通孔（流通路）９１２が軸方向に沿って延びるように形成されている。
【００１９】
また、９２０は流通孔９１２を開閉する弁体であり、この弁体９２０は、流通孔９１２のうち高圧配管８００の内方側端部にて流通孔９１２を開閉する略円錐状の弁部９２１、及び弁部９２１から流通孔９１２に沿って高圧配管８００の外方側に向けて延びる作動軸９２２からなるキノコ状のものである。なお、弁部９２１には、流通孔９１２を閉じたときのシール性を確保すべく、ニトリルゴム製のＯリング（弁パッキン）９２３が配設されている。
【００２０】
そして、作動軸９２２のうち弁部９２１と反対側には、バルブ本体９１０に接触して流通孔９１２を閉じる向きの弾性力を弁体９２０に作用させる円錐状のコイルバネ（弾性手段）９３０が配設されているとともに、バルブ本体９１０と衝突して弁体９２０が開く向きに移動する際の最大移動量を規制するストッパ９２４が一体形成されている。
【００２１】
なお、９４０は冷媒充填（注入）用の注入窓であり、この注入窓９４０は流通孔９１２に連通している。そして、冷媒充填（封入）時には、充填用外部配管（図示せず）のカプラをバルブステム９０１に装着した状態で、カプラにて作動軸９２２を押圧して、流通孔９１２を開いて注入窓９４０から冷媒を充填する。
【００２２】
次に、チャージバルブ９００の作動及び特徴を述べる。
【００２３】
カプラにより作動軸９２２を高圧配管８００の内方側に向けて（図２のＦの向きに）押圧すると、弁体９２０がバルブ本体９１０に対して高圧配管８００の内方側に向けて移動するので、流通孔９１２（チャージバルブ９００）が開く。
【００２４】
このとき、図３に示すように、ストッパ９２４がバルブ本体９１０と衝突して弁体９２０が開く向きに移動する際の最大移動量を規制されるので、コイルバネ９３０が密着するまで過度に撓むことが防止される。したがって、コイルバネ９３０の大型化及びコイルバネ９３０の弾性係数の増大を招くことなく、コイルバネ９３０が永久変形してしまうことを防止できる。
【００２５】
一方、冷媒の充填が終了し、カプラが外されると、コイルバネ９３０の弾性力により、弁体９２０がバルブ本体９１０に対して高圧配管８００の外方側に向けて移動するので、流通孔９１２（チャージバルブ９００）が閉じる。
【００２６】
（第２実施形態）
本実施形態は、図４に示すように、作動軸９２２をバルブ本体９１０に挿入した後に、作動軸９２２の外径を打ち出し成形する等して段付き部を形成してストッパ９２４を形成したものである。
【００２７】
（第３実施形態）
本実施形態は、図５に示すように、円筒部９２４ａの端部に円盤状のフランジ部９２４ｂを有するようにハット状にプレス成形されたストッパ９２４をカシメ固定等の固定方法により作動軸９２２に固定したものである。
【００２８】
ところで、上述の実施形態では、冷媒として二酸化炭素を用いたが超臨界冷凍サイクルの冷媒はこれに限定されるものではなく、例えば、エチレン、エタン、酸化窒素等でもよい。
【００２９】
また、本発明に係るチャージバルブは、超臨界冷凍サイクルの高圧配管８００に冷媒を充填する場合のみならず、その他の高圧流体を高圧容器に充填する場合にも適用することができる。
【００３０】
また、上述の実施形態では、弾性手段として円錐状のコイルバネ９３０を用いたが、本発明はこれ限定されるものではなく、単純な円筒コイルバネ等のその他のバネ手段であってもよい。
【図面の簡単な説明】
【図１】超臨界冷凍サイクルの模式図である。
【図２】（ａ）は第１実施形態に係るチャージバルブの片側断面図であり、（ｂ）は（ａ）の上面図であり、（ｃ）は（ａ）のＡ−Ａ断面図である。
【図３】バルブが閉じたときの第１実施形態に係るチャージバルブの片側断面図である。
【図４】第２実施形態に係るチャージバルブの片側断面図である。
【図５】第３実施形態に係るチャージバルブの片側断面図である。
【符号の説明】
９１０…バルブ本体、９１２…流通孔（流通路）、９２０…弁体、
９２１…弁部、９２２…作動軸、９２４…ストッパ、
９３０…コイルバネ（弾性手段）。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a charge valve that is attached to a filling port of a pressure vessel to prevent a high-pressure fluid from flowing backward, and the pressure on the high-pressure side is equal to or higher than the critical pressure of the refrigerant, as in a refrigeration cycle using carbon dioxide as a refrigerant. It is effective when applied to the supercritical refrigeration cycle.
[0002]
[Prior art]
In general, the charge valve is configured so that the valve is closed when an internal pressure is applied, and a force in a direction to close the valve is applied to the valve body by an elastic means such as a coil spring. When filling the high pressure fluid, a force opposite to the elastic force of the coil spring is applied to the valve body to open the valve and fill the pressure vessel with the high pressure fluid.
[0003]
[Problems to be solved by the invention]
By the way, in the supercritical refrigeration cycle, since the refrigerant (carbon dioxide) is filled in the high-pressure pipe (high-pressure vessel) at a high pressure of 100 MPa or more, the coil spring is fully compressed (adhered) when filling, and is generated in the coil spring. The resulting stress exceeds the yield stress (elastic limit) of the material and is permanently deformed.
[0004]
On the other hand, if measures such as enlarging the wire diameter of the coil spring can be applied, the stress generated in the coil spring can be prevented from exceeding the yield stress (elastic limit) of the material. Since the elastic modulus increases, the force required to open the charge valve increases, and the refrigerant charging efficiency and the charging operation deteriorate.
[0005]
Incidentally, since the charge valve has a structure that is closed by the internal pressure, the sealing performance of the charge valve is not greatly improved even if the elastic coefficient of the coil spring is increased. Therefore, an increase in the size of the coil spring and an increase in the elastic coefficient of the coil spring only cause deterioration of the refrigerant charging efficiency and the charging operation.
[0006]
In view of the above points, an object of the present invention is to prevent the elastic means from being permanently deformed without increasing the size of the elastic means such as a coil spring and increasing the elastic coefficient of the coil spring.
[0007]
In order to achieve the above object, according to the present invention, in the inventions of claims 1 to 5 , a valve body (910) formed with a flow passage (912) fixed to the filling port (810) and through which a high-pressure fluid flows. ) And the valve body (910) toward the outer side of the pressure vessel (800) to close the flow passage (912), and the valve body (910) to the inside of the pressure vessel (800). A valve body (920) that opens the flow passage (912) by moving toward the side, and an elastic means (930) that applies an elastic force to the valve body (920) to close the flow passage (912); valve (920) and integrally with the movable possess a stopper means (924) for restricting the maximum movement amount when colliding with the valve body (910) moves in the direction of the valve body (920) is opened The valve body (910) is connected to the flow passage (91 2) is formed in a cylindrical shape so as to extend in the axial direction, and the maximum movement amount of the valve body (920) is a movement amount that prevents excessive bending until the elastic means (930) comes into close contact. The valve body (910) is formed in a cylindrical shape so that the flow passage (912) extends in the axial direction, and the valve body (920) is formed in the pressure vessel (800) of the flow passage (912). A valve portion (921) for opening and closing the flow passage (912) at the side end, and an operating shaft extending from the valve portion (921) along the flow passage (912) toward the outer side of the pressure vessel (800). The elastic means (930) is formed from the operating shaft (922) at the outer end of the pressure vessel (800) in the valve body (910) and the operating shaft (922). Is disposed between the large-diameter portion formed with a large diameter, and The upper means (924) is provided between the valve main body (910) and the large diameter portion on the operating shaft (922), and collides with the contact surface of the valve main body (910) with the elastic member (930). The maximum movement amount of the body (920) is regulated .
[0008]
As a result, it is possible to prevent the elastic means (930) from being bent excessively, so that the elastic means (930) is made permanent without increasing the size of the elastic means (930) and increasing the elastic coefficient of the elastic means (930). Deformation can be prevented.
[0009]
In the second aspect of the present invention , the pressure vessel (800) is a high-pressure pipe (800) filled with a high-pressure refrigerant, which is applied to a supercritical refrigeration cycle in which the pressure on the high-pressure side is equal to or higher than the critical pressure of the refrigerant. It is characterized by.
[0010]
As a result, it is possible to prevent the elastic means (930) from being bent excessively, so that the elastic means (930) is made permanent without increasing the size of the elastic means (930) and increasing the elastic coefficient of the elastic means (930). Deformation can be prevented.
[0011]
The invention according to claim 3 is characterized in that the stopper means (924) is integrally formed with the operating shaft (922).
The invention according to claim 4 is characterized in that the stopper means (924) is a stepped portion formed by punching out the outer shape of the operating shaft (922).
In the invention described in claim 5, the stopper means (924) is a hat-like member having a disk-like flange portion (924b) at the end of the cylindrical portion (924a) fixed to the operating shaft (922). It is characterized by that.
Incidentally, the reference numerals in parentheses of each means described above are an example showing the correspondence with the specific means described in the embodiments described later.
[0012]
DETAILED DESCRIPTION OF THE INVENTION
(First embodiment)
In the present embodiment, the charge valve according to the present invention is applied to a supercritical refrigeration cycle (hereinafter abbreviated as a cycle) for vehicles using carbon dioxide as a refrigerant, and FIG. 1 is a schematic diagram of the cycle.
[0013]
In FIG. 1, reference numeral 100 denotes a compressor that sucks and compresses refrigerant, and the compressor 100 operates by obtaining driving force from a vehicle travel engine (not shown) via an electromagnetic clutch 110. 200 is a heat radiator that cools the refrigerant discharged from the compressor 100 by exchanging heat with the atmosphere, and 300 is a radiator in which the internal pressure exceeds the critical pressure of the refrigerant. It is a pressure control valve that controls the pressure on the outlet side of the radiator 200 based on the refrigerant pressure on the outlet side of the radiator 200. The high-pressure pipe (pressure vessel) 800 extending from the radiator 200 to the pressure control valve 300 is provided with the charge valve 900 according to this embodiment.
[0014]
Reference numeral 400 denotes an evaporator that evaporates the refrigerant decompressed by the pressure control valve 300 and cools the air. Reference numeral 500 stores excess refrigerant in the cycle and converts the refrigerant flowing out of the evaporator 400 into a gas phase refrigerant and a liquid phase. It is an accumulator (gas-liquid separation means) that separates the refrigerant into refrigerant and flows out the gas-phase refrigerant to the compressor 100 side.
[0015]
Incidentally, 600 is a temperature sensor for detecting the temperature of air that has been hand-cooled evaporator 40 0 (temperature detecting means), an electronic control unit (ECU) 700, the electromagnetic clutch 110 based on the temperature detected by the temperature sensor 600 ON-OFF is controlled. Specifically, when the detected temperature becomes 3 ° C. or lower, the electromagnetic clutch 110 is turned off and the compressor 100 is stopped. When the detected temperature becomes 4 ° C. or higher, the electromagnetic clutch 110 is turned on and the compressor 100 is turned off. Make it work.
[0016]
Next, the charge valve 900 will be described.
[0017]
As shown in FIG. 2A, the valve body 910 of the charge valve 900 is screwed to a valve stem 901 that is welded to a high-pressure pipe 800 forming a pressure vessel to form a filling port 810. The gap with the valve stem 901 is sealed (sealed) by an O-ring 911 made of nitrile rubber.
[0018]
The valve body 910 is formed in a substantially cylindrical shape from a stainless material so that the thickness direction of the high-pressure pipe 800 coincides with the axial direction, and a circulation hole (flow passage) 912 through which the refrigerant flows when the refrigerant is charged. Is formed so as to extend along the axial direction.
[0019]
Reference numeral 920 denotes a valve body that opens and closes the flow hole 912. The valve body 920 is a substantially conical valve portion 921 that opens and closes the flow hole 912 at the inner end of the high-pressure pipe 800 in the flow hole 912. , and also to a is from the working axis 922 mushroom's made extending outward side of the high-pressure pipe 800 from a valve portion 921 along the flow hole 912. The valve portion 921 is provided with an O-ring (valve packing) 923 made of nitrile rubber in order to ensure sealing performance when the flow hole 912 is closed.
[0020]
A conical coil spring (elastic means) 930 is provided on the opposite side of the operating shaft 922 from the valve portion 921 to apply an elastic force to the valve body 920 so as to contact the valve body 910 and close the flow hole 912. A stopper 924 that restricts the maximum amount of movement when the valve body 920 moves in the opening direction by colliding with the valve body 910 is integrally formed.
[0021]
Reference numeral 940 denotes an injection window for filling (injecting) the refrigerant, and the injection window 940 communicates with the flow hole 912. When filling (filling) the refrigerant, with the coupler of the external pipe for filling (not shown) attached to the valve stem 901, the operating shaft 922 is pressed by the coupler to open the flow hole 912 and the injection window 940. Fill with refrigerant.
[0022]
Next, the operation and characteristics of the charge valve 900 will be described.
[0023]
When the operating shaft 922 is pressed toward the inner side of the high-pressure pipe 800 by the coupler (in the direction of F in FIG. 2), the valve body 920 moves toward the inner side of the high-pressure pipe 800 with respect to the valve body 910. Therefore, the flow hole 912 (charge valve 900) is opened.
[0024]
At this time, as shown in FIG. 3, the maximum amount of movement when the stopper 924 collides with the valve body 910 and moves in the direction in which the valve body 920 opens is restricted, so that the coil spring 930 bends excessively until it comes into close contact. It is prevented. Therefore, it is possible to prevent the coil spring 930 from being permanently deformed without increasing the size of the coil spring 930 and increasing the elastic coefficient of the coil spring 930.
[0025]
On the other hand, when the charging of the refrigerant is completed and the coupler is removed, the valve body 920 moves toward the outer side of the high-pressure pipe 800 with respect to the valve main body 910 by the elastic force of the coil spring 930. (Charge valve 900) closes.
[0026]
(Second Embodiment)
In this embodiment, as shown in FIG. 4, after the operating shaft 922 is inserted into the valve body 910, the outer diameter of the operating shaft 922 is stamped and formed to form a stepped portion to form the stopper 924. It is.
[0027]
(Third embodiment)
In this embodiment, as shown in FIG. 5, a stopper 924 press-molded in a hat shape so as to have a disc-shaped flange portion 924b at the end of a cylindrical portion 924a is attached to the operating shaft 922 by a fixing method such as caulking. It is fixed.
[0028]
By the way, in the above-mentioned embodiment, although carbon dioxide was used as a refrigerant | coolant, the refrigerant | coolant of a supercritical refrigerating cycle is not limited to this, For example, ethylene, ethane, nitric oxide etc. may be sufficient.
[0029]
Further, the charge valve according to the present invention can be applied not only when the high-pressure pipe 800 of the supercritical refrigeration cycle is filled with the refrigerant but also when filling the high-pressure vessel with other high-pressure fluid.
[0030]
In the above-described embodiment, the conical coil spring 930 is used as the elastic means. However, the present invention is not limited to this, and other spring means such as a simple cylindrical coil spring may be used.
[Brief description of the drawings]
FIG. 1 is a schematic diagram of a supercritical refrigeration cycle.
2A is a half sectional view of the charge valve according to the first embodiment, FIG. 2B is a top view of FIG. 2A, and FIG. 2C is a sectional view taken along line AA in FIG. is there.
FIG. 3 is a half sectional view of the charge valve according to the first embodiment when the valve is closed.
FIG. 4 is a half sectional view of a charge valve according to a second embodiment.
FIG. 5 is a half sectional view of a charge valve according to a third embodiment.
[Explanation of symbols]
910 ... Valve body, 912 ... Flow hole (flow passage), 920 ... Valve body,
921 ... Valve unit, 922 ... Operating shaft, 924 ... Stopper,
930: Coil spring (elastic means).

Claims

A charge that is provided in a filling port (810) of a pressure vessel (800) filled with a high-pressure fluid and prevents the high-pressure fluid filled in the pressure vessel (800) from flowing backward from the filling port (810). A valve,
A valve body (910) fixed to the filling port (810) and having a flow passage (912) through which a high-pressure fluid flows;
The flow passage (912) is closed by moving toward the outer side of the pressure vessel (800) with respect to the valve body (910), and the pressure vessel (800) with respect to the valve body (910). A valve body (920) that opens the flow passage (912) by moving toward the inward side of
Elastic means (930) for applying an elastic force in a direction to close the flow passage (912) to the valve body (920);
Stopper means (924) that moves integrally with the valve body (920) and restricts the maximum amount of movement when the valve body (920) moves in the opening direction by colliding with the valve body (910). Yes, and
The maximum movement amount of the valve body (920) is a movement amount that is prevented from being bent excessively until the elastic means (930) is in close contact,
The valve body (910) is formed in a cylindrical shape so that the flow passage (912) extends in the axial direction,
The valve body (920) includes a valve portion (921) for opening and closing the flow passage (912) at an inner side end portion of the pressure vessel (800) in the flow passage (912), and the valve portion ( 921) and an operating shaft (922) extending toward the outer side of the pressure vessel (800) along the flow path (912).
The elastic means (930) is formed at a larger diameter than the operating shaft (922) at the outer end of the pressure vessel (800) in the valve body (910) and the operating shaft (922). It is arranged between the large diameter part,
Further, the stopper means (924) is provided between the valve main body (910) and the large diameter portion of the operating shaft (922), and is connected to the elastic member (930) of the valve main body (910). A charge valve characterized by restricting the maximum amount of movement of the valve element (920) by colliding with a contact surface .

Applied to supercritical refrigeration cycles where the pressure on the high pressure side is above the critical pressure of the refrigerant,
The charge valve according to claim 1, wherein the pressure vessel (800) is a high-pressure pipe (800) filled with a high-pressure refrigerant .

The charge valve according to claim 1 or 2, wherein the stopper means (924) is integrally formed with the operating shaft (922).

The charge valve according to claim 1 or 2, wherein the stopper means (924) is a stepped portion formed by punching out the outer shape of the operating shaft (922).

The stopper means (924) is a hat-shaped member having a disc-shaped flange portion (924b) at an end portion of a cylindrical portion (924a) fixed to the operating shaft (922). The charge valve according to 1 or 2.