JP4429827B2 - Check valve and gas compression device equipped with check valve - Google Patents

Check valve and gas compression device equipped with check valve Download PDF

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JP4429827B2
JP4429827B2 JP2004198889A JP2004198889A JP4429827B2 JP 4429827 B2 JP4429827 B2 JP 4429827B2 JP 2004198889 A JP2004198889 A JP 2004198889A JP 2004198889 A JP2004198889 A JP 2004198889A JP 4429827 B2 JP4429827 B2 JP 4429827B2
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diameter
refrigerant gas
check valve
stopper
rotor
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JP2006022653A (en
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孝之 岩澤
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Calsonic Kansei Corp
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Description

本発明は、圧縮室へ冷媒ガスを送出する吸入室に連通し、ロータの回転に伴って外部から冷媒ガスが吸入される吸入ポートに設置される逆止弁及びその逆止弁を備えた気体圧縮装置に関する。   The present invention relates to a check valve that communicates with a suction chamber that sends refrigerant gas to a compression chamber and is installed in a suction port through which refrigerant gas is sucked from the outside as the rotor rotates, and a gas including the check valve The present invention relates to a compression device.

住宅用又は車両用の空調システムには、冷媒ガス（例えば代替フロンガス等）を圧縮することにより、空調システム内に設置される空調機器（凝縮器、蒸発器等）への冷媒ガスの循環を実現する気体圧縮機が設けられている。   Refrigerant gas circulation to air conditioning equipment (condenser, evaporator, etc.) installed in the air conditioning system is realized by compressing refrigerant gas (for example, alternative chlorofluorocarbon gas) for residential or vehicle air conditioning systems A gas compressor is provided.

気体圧縮機は、往復動式や回転式等の様々な駆動方式が実現されているが、どのような駆動方式であってもその駆動過程において、圧縮室内に導入された冷媒ガスを圧縮室の容積変動（容積減少）によって圧縮する構造となっている。   Various driving systems such as a reciprocating type and a rotary type are realized in the gas compressor. In any driving system, in the driving process, the refrigerant gas introduced into the compression chamber is supplied to the compression chamber. The structure is compressed by volume fluctuation (volume reduction).

気体圧縮機の圧縮室の端部であって冷媒ガスの上流（吸入）側には、図６に示すように、圧縮室１に連通する冷媒ガスＲの吸入室２と、空調システム内を循環した冷媒ガスＲが供給される吸入ポート３が形成されている。吸入室２と吸入ポート３とは連通されており、吸入ポート３には、供給された冷媒ガスＲの吸入室２への流入を許容するとともに、吸入室２から吸入ポート３への冷媒ガスＲの逆流を阻止するための逆止弁４が設けられている。   As shown in FIG. 6, at the end of the compression chamber of the gas compressor and upstream (intake) of the refrigerant gas, the refrigerant gas R communicates with the compression chamber 1 and circulates in the air conditioning system. A suction port 3 to which the refrigerant gas R is supplied is formed. The suction chamber 2 and the suction port 3 communicate with each other. The suction port 3 allows the supplied refrigerant gas R to flow into the suction chamber 2, and the refrigerant gas R from the suction chamber 2 to the suction port 3. Is provided with a check valve 4 for preventing the reverse flow of the gas.

逆止弁４は、図７に示すように円筒形状を呈するストッパ６と、ストッパ６の下端部に圧接する弁本体７と、弁本体７を上方に付勢するスプリング８と、弁本体７とスプリング８とを収納するケース９とを備えている。   As shown in FIG. 7, the check valve 4 includes a cylindrical stopper 6, a valve body 7 that presses against the lower end of the stopper 6, a spring 8 that biases the valve body 7 upward, and a valve body 7. A case 9 for housing the spring 8 is provided.

ストッパ６の外周下部には、段付き部６ａが形成されており、段付き部６ａは、ケース９の上部開口９ａの周縁部９ｂに当接している。ケース９の上部開口９ａは、ストッパ６の下端部６ｂを内部に嵌入することが可能な円径を備えている。また、ケース９の外周面には、吸入ポート３と吸入室２とを連通させるための複数の開口１０が形成されており、底面には、冷媒ガスＲをケース９の底部から排出するためのガス抜孔９ｃが形成されている。   A stepped portion 6 a is formed at the lower outer periphery of the stopper 6, and the stepped portion 6 a is in contact with the peripheral edge portion 9 b of the upper opening 9 a of the case 9. The upper opening 9a of the case 9 has a circular diameter that allows the lower end 6b of the stopper 6 to be fitted therein. A plurality of openings 10 for communicating the suction port 3 and the suction chamber 2 are formed on the outer peripheral surface of the case 9, and the refrigerant gas R is discharged from the bottom of the case 9 on the bottom surface. A gas vent 9c is formed.

弁本体７は、外径がケース９の内径とほぼ同径を成しており、底部にはスプリング８の上部が収納される凹部７ｂが形成されている。   The valve body 7 has an outer diameter that is substantially the same as the inner diameter of the case 9, and a recess 7 b in which the upper part of the spring 8 is accommodated is formed at the bottom.

上記部品（６〜９）を有する逆止弁４が組み立てられると、弁本体７とスプリング８とが収納された状態で、ケース９の上部開口９ａにストッパ６の下端部６ｂが嵌入され、スプリング８の付勢力により上方に押し上げられる弁本体７が、ストッパ６の下端部６ｂに圧接した状態となる。   When the check valve 4 having the above components (6 to 9) is assembled, the lower end portion 6b of the stopper 6 is fitted into the upper opening 9a of the case 9 in a state where the valve body 7 and the spring 8 are accommodated, and the spring The valve body 7 pushed upward by the urging force 8 is brought into pressure contact with the lower end portion 6 b of the stopper 6.

吸入ポート３に設置された逆止弁４において、吸入室２の内部圧力が冷媒ガスＲの供給圧よりも高いときや、冷媒ガスＲの供給圧が吸入室２との内部圧力よりも高いが、その圧力差がスプリング８の付勢力よりも小さいときには、図８（ａ）に示すように、弁本体７がスプリング８の付勢力によりストッパ６に突き当てられることによって、吸入室２と吸入ポート３との連通が閉塞され、吸入室２から吸入ポート３への冷媒ガスＲの逆流が防止される。   In the check valve 4 installed in the suction port 3, when the internal pressure of the suction chamber 2 is higher than the supply pressure of the refrigerant gas R, or the supply pressure of the refrigerant gas R is higher than the internal pressure with the suction chamber 2. When the pressure difference is smaller than the biasing force of the spring 8, the valve body 7 is abutted against the stopper 6 by the biasing force of the spring 8, as shown in FIG. 3 is blocked, and the backflow of the refrigerant gas R from the suction chamber 2 to the suction port 3 is prevented.

一方、冷媒ガスＲの供給圧が吸入室２との内部圧力よりも高く、さらにその圧力差がスプリング８の付勢力よりも大きい場合には、図８（ｂ）に示すように、弁本体７がスプリング８の付勢力に対抗して下方に押し下げられ、弁本体７の上面７ｃがケース９の開口１０の上端部１０ａよりも下方まで変位することによって、吸入ポート３と吸入室２とが連通し、吸入ポート３に供給された冷媒ガスＲが吸入室２に流入する。
特開２００２−２５７０４６号公報 On the other hand, when the supply pressure of the refrigerant gas R is higher than the internal pressure with the suction chamber 2 and the pressure difference is larger than the urging force of the spring 8, as shown in FIG. Is pushed downward against the urging force of the spring 8, and the upper surface 7c of the valve body 7 is displaced below the upper end portion 10a of the opening 10 of the case 9, whereby the suction port 3 and the suction chamber 2 communicate with each other. Then, the refrigerant gas R supplied to the suction port 3 flows into the suction chamber 2.
JP 2002-257046 A

しかしながら、ストッパ６は、図７に示すように、一定の口径を備える筒状体により構成されているため、吸入ポート３を経て気体圧縮機本体に吸入される冷却ガスＲの流量は、ロータの回転速度に比例して増大する。このため、ロータを高速に回転させた場合、本来必要とされる冷媒ガスＲの吸入量以上の冷媒ガスＲが気体圧縮機に吸入されてしまい、エネルギー効率の観点から無駄なエネルギー消費をもたらすおそれがあった。一方、無駄なエネルギー消費を低減させるために、ストッパ６の口径を小さくすると、ロータを低速で回転させた場合に冷媒ガスＲを気体圧縮機へ十分に吸入させることが困難となり、気体圧縮機による冷却能力が低下してしまうおそれがあった。   However, as shown in FIG. 7, the stopper 6 is formed of a cylindrical body having a constant diameter, so that the flow rate of the cooling gas R sucked into the gas compressor body through the suction port 3 is the rotor flow rate. It increases in proportion to the rotation speed. For this reason, when the rotor is rotated at a high speed, the refrigerant gas R that is larger than the amount of refrigerant gas R that is originally required may be sucked into the gas compressor, resulting in unnecessary energy consumption from the viewpoint of energy efficiency. was there. On the other hand, if the diameter of the stopper 6 is reduced in order to reduce wasteful energy consumption, it becomes difficult to sufficiently suck the refrigerant gas R into the gas compressor when the rotor is rotated at a low speed. There was a possibility that cooling capacity might fall.

本発明は、上記問題に鑑みてなされたものであり、ロータの回転速度に応じて適切な流量の冷媒ガスを吸入することが可能な逆止弁及びその逆止弁を備えた気体圧縮機を提供することを課題とする。   The present invention has been made in view of the above problems, and provides a check valve capable of sucking an appropriate flow rate of refrigerant gas in accordance with the rotational speed of a rotor, and a gas compressor including the check valve. The issue is to provide.

上記課題を解決するために、本発明に係る逆止弁は、圧縮室へ冷媒ガスを送出する吸入室に連通し、ロータの回転に伴って外部から冷媒ガスが吸入される吸入ポートに設置される逆止弁であって、該逆止弁が、前記外部に連通するストッパと、該ストッパに圧接することにより前記冷媒ガスの吸入室への吸入及び逆流を防止し、前記ストッパから離反することによって前記冷媒ガスの前記吸入室への流入を許容する弁本体とを有し、前記ストッパの内部には、該ストッパの中部から前記外部側端部にかけて口径が拡大されて傾斜面が形成された拡径空間が設けられ、該拡径空間には、前記ロータの回転速度に応じて前記傾斜面を摺動して前記拡径空間における前記冷媒ガスの流入孔内径を変更することが可能な径可変部材が設けられることを特徴とする。   In order to solve the above-described problems, a check valve according to the present invention communicates with a suction chamber that sends refrigerant gas to a compression chamber, and is installed in a suction port through which refrigerant gas is sucked from the outside as the rotor rotates. The check valve is configured to prevent the refrigerant gas from being sucked into and sucked into the suction chamber by being in pressure contact with the stopper, and separated from the stopper. And a valve body that allows the refrigerant gas to flow into the suction chamber, and the inside of the stopper has an inclined surface with an enlarged diameter from a middle portion of the stopper to the outer end portion. A diameter-expanding space is provided, and the diameter-expanded space is a diameter capable of changing the inside diameter of the refrigerant gas inflow hole in the diameter-expanding space by sliding on the inclined surface according to the rotational speed of the rotor. That a variable member is provided. And butterflies.

また、前記径可変部材は、環状部材が複数に分割された環片部材と、該環片部材の中心部に周方向に向かって延設された孔部に挿入される棒状弾性バネとを有し、前記孔部に前記棒状弾性バネが挿入されて前記複数の環片部材によって環形状を形成する前記径可変部材が、前記棒状弾性バネの弾性力により径方向に広がろうとする拡径力と、前記ロータの回転に伴って吸入される前記冷媒ガスにより前記環片部材の上面に加えられる吸入圧力との強弱関係に応じて前記流入孔内径が拡狭することを特徴とする。 Moreover, the diameter varying member, the ring-shaped member and a ring piece member that is divided into a plurality, and a rod-shaped elastic springs which are inserted into a hole portion extending in the center portion toward the peripheral direction of the ring piece member The diameter-variable member in which the rod-shaped elastic spring is inserted into the hole and the ring- shaped member is formed into an annular shape by the plurality of ring piece members is expanded in diameter by the elastic force of the rod-shaped elastic spring. The inner diameter of the inflow hole is increased or decreased in accordance with a strength relationship between a force and a suction pressure applied to the upper surface of the ring piece member by the refrigerant gas sucked as the rotor rotates.

さらに、上述した逆止弁を備えた気体圧縮装置も本発明に該当する。   Furthermore, the gas compression apparatus provided with the above-described check valve also corresponds to the present invention.

本発明に係る逆止弁及び該逆止弁を備えた気体圧縮装置によれば、ロータの回転速度が低速である場合には、径可変部材の内径を大きくしてロータの回転速度に応じて吸入される冷媒ガスの吸入量の増減率を高くすることができ、ロータの回転速度が中速になった場合には、回転速度に応じて径可変部材の内径を増減させることによって、ロータの回転に最適な冷媒ガスの吸入量を維持することができ、さらに、ロータの回転速度が高速になった場合には、径可変部材の内径を小さくして冷媒ガスの吸入量の増減率を低くすることができるので、ロータの回転速度に応じて必要とされる冷媒ガスの吸入量を調整することができ、無駄なエネルギー消費を防止することが可能となる。   According to the check valve and the gas compression apparatus including the check valve according to the present invention, when the rotational speed of the rotor is low, the inner diameter of the variable diameter member is increased to correspond to the rotational speed of the rotor. The rate of increase / decrease in the amount of refrigerant gas sucked in can be increased, and when the rotational speed of the rotor becomes medium, the inner diameter of the variable diameter member is increased / decreased according to the rotational speed. The refrigerant gas suction amount optimal for rotation can be maintained. Further, when the rotational speed of the rotor becomes high, the inner diameter of the variable diameter member is reduced to reduce the rate of change in the refrigerant gas suction amount. Therefore, it is possible to adjust the refrigerant gas suction amount required according to the rotational speed of the rotor, and to prevent wasteful energy consumption.

以下、本発明に係る逆止弁を備えた気体圧縮装置について図面を用いて説明する。   Hereinafter, a gas compression apparatus provided with a check valve according to the present invention will be described with reference to the drawings.

図１は、本発明に係る逆止弁を備えた気体圧縮機であって、車両用の空調システムに用いられるロータリコンプレッサ２０を示した側方断面図である。   FIG. 1 is a side sectional view showing a rotary compressor 20 used in an air conditioning system for a vehicle, which is a gas compressor provided with a check valve according to the present invention.

このロータリコンプレッサ２０は、図１に示すように、フロントサイドブロック２１、リヤサイドブロック２２、シリンダ２３、ロータ２４及びロータ２４に備えられたベーン２５を有しており、シリンダ２３、ロータ２４、ベーン２５に囲まれて形成された複数の圧縮室１の各容積が、ロータ２４の回転にしたがって縮小されることによって、圧縮室１内の冷媒ガスＲが圧縮される構造となっている。   As shown in FIG. 1, the rotary compressor 20 includes a front side block 21, a rear side block 22, a cylinder 23, a rotor 24, and a vane 25 provided in the rotor 24, and the cylinder 23, the rotor 24, and the vane 25. The refrigerant gas R in the compression chamber 1 is compressed by reducing the volume of each of the plurality of compression chambers 1 surrounded by the rotation of the rotor 24.

フロントサイドブロック２１には、吸入室２に導入された冷媒ガスＲを吸入行程において圧縮室１へ導入する吸入口（図示せず）が形成されている。また、シリンダ２３には、冷媒ガスＲの吐出行程において圧縮された冷媒ガスＲが圧縮室１から排出される吐出孔（図示せず）が形成され、この吐出孔には吐出弁（図示せず）が設けられている。   The front side block 21 is formed with a suction port (not shown) through which the refrigerant gas R introduced into the suction chamber 2 is introduced into the compression chamber 1 in the suction stroke. Further, a discharge hole (not shown) through which the refrigerant gas R compressed in the discharge stroke of the refrigerant gas R is discharged from the compression chamber 1 is formed in the cylinder 23, and a discharge valve (not shown) is formed in the discharge hole. ) Is provided.

リヤサイドブロック２２には、シリンダ２３の吐出弁から吐出された冷媒ガスＲの流路となる吐出口が形成され、さらにこのリヤサイドブロック２２の外側には、吐出口から吐出された冷媒ガスＲの混入冷凍機油Ｌを冷媒ガスＲから分離するための分離機金網２７を備えたサイクロンブロック２８が取り付けられている。   The rear side block 22 is formed with a discharge port serving as a flow path for the refrigerant gas R discharged from the discharge valve of the cylinder 23. Further, outside the rear side block 22, the refrigerant gas R discharged from the discharge port is mixed. A cyclone block 28 having a separator wire mesh 27 for separating the refrigerating machine oil L from the refrigerant gas R is attached.

フロントサイドブロック２１、リヤサイドブロック２２、シリンダ２３、ロータ２４、シャフト２９は圧縮機本体３０を構成し、この圧縮機本体３０とサイクロンブロック２８は、フロントヘッド３１及びケース３２によって覆われている。   The front side block 21, the rear side block 22, the cylinder 23, the rotor 24, and the shaft 29 constitute a compressor body 30, and the compressor body 30 and the cyclone block 28 are covered with a front head 31 and a case 32.

ロータ２４には、図示しない電動機から、動力伝達ベルト３４、動力伝達機構３５、及びフロントサイドブロック２１とリヤサイドブロック２２とに軸支されたシャフト２９を介して回転力が与えられる。動力伝達機構３５は、動力伝達ベルト３４が巻き掛けられ、ラジアルベアリングを介してフロントヘッド３１に支持されたプーリ３６、及びシャフト２９とプーリ３６とを連結する連結板３７を備えている。   A rotational force is applied to the rotor 24 from an electric motor (not shown) through a power transmission belt 34, a power transmission mechanism 35, and a shaft 29 that is pivotally supported by the front side block 21 and the rear side block 22. The power transmission mechanism 35 includes a pulley 36 around which a power transmission belt 34 is wound and supported by the front head 31 via a radial bearing, and a connecting plate 37 that connects the shaft 29 and the pulley 36.

一方、フロントヘッド３１とフロントサイドブロック２１との間には、フロントサイドブロック２１の吸入口に通じ、圧縮室１に対して冷媒ガスＲの上流側となる吸入室２が形成されている。フロントヘッド３１には、このコンプレッサ２０の外部すなわち空調システムのエバポレータから冷媒ガスＲが供給される吸入ポート３Ａが形成され、ケース３２にはコンプレッサ２０の外部すなわち空調システムのコンデンサに、圧縮されて高温・高圧となった冷媒ガスＲを吐出する吐出ポート４０が形成されている。   On the other hand, a suction chamber 2 is formed between the front head 31 and the front side block 21, leading to the suction port of the front side block 21 and upstream of the refrigerant gas R with respect to the compression chamber 1. The front head 31 is formed with a suction port 3A to which the refrigerant gas R is supplied from the outside of the compressor 20, that is, an evaporator of the air conditioning system, and the case 32 is compressed by the outside of the compressor 20, that is, a condenser of the air conditioning system. A discharge port 40 for discharging the refrigerant gas R having a high pressure is formed.

吸入ポート３Ａには、逆止弁４１が配設されており、吸入ポート３Ａは逆止弁４１を介して吸入室２と連通する構造となっている。   The suction port 3A is provided with a check valve 41, and the suction port 3A communicates with the suction chamber 2 through the check valve 41.

逆止弁４１は、図２に示すように、上部開口の口径Ｒ１が中部の口径Ｒ２に比べて幅広に形成されるストッパ４２と、ストッパ４２の下端部に圧接する弁本体４３と、弁本体４３を上方に付勢するスプリング４４と、弁本体４３とスプリング４４とを収納するケース４５とを備えている。   As shown in FIG. 2, the check valve 41 includes a stopper 42 whose upper opening diameter R1 is wider than the middle diameter R2, a valve main body 43 that presses against the lower end of the stopper 42, and a valve main body. A spring 44 that urges 43 upward, and a case 45 that houses the valve main body 43 and the spring 44 are provided.

ストッパ４２の内周上部は、中部から上部に沿って口径が拡大されて傾斜面４８が形成される拡径空間４９を備えており、この拡径空間４９には、後述する口径可変部材５０が設けられている。ストッパ４２の外周下部には、段付き部４２ａが形成されており、段付き部４２ａは、ケース４５上部開口４５ａの周縁部４５ｂに当接する。   The inner peripheral upper portion of the stopper 42 is provided with a diameter expansion space 49 in which the diameter is enlarged from the middle portion to the upper portion to form an inclined surface 48, and a diameter variable member 50 described later is provided in the diameter expansion space 49. Is provided. A stepped portion 42 a is formed at the lower outer periphery of the stopper 42, and the stepped portion 42 a abuts on the peripheral edge 45 b of the case 45 upper opening 45 a.

ケース４５の上部開口４５ａはストッパ４２の下端部４２ａを内部に嵌入することが可能な内径を備えている。また、ケース４５の外周面には、吸入ポート３Ａと吸入室２とを連通させるための複数の開口４６が形成されており、底面には、冷媒ガスＲをケース４５の底部から排出するためのガス抜孔４５ｃが形成されている。   The upper opening 45a of the case 45 has an inner diameter that allows the lower end portion 42a of the stopper 42 to be fitted therein. A plurality of openings 46 for communicating the suction port 3A and the suction chamber 2 are formed on the outer peripheral surface of the case 45, and the bottom surface of the case 45 is used for discharging the refrigerant gas R from the bottom of the case 45. A gas vent 45c is formed.

弁本体４３は、外径がケース４５の内径とほぼ同径を成しており、底部には、スプリング４４の上部が収納される凹部４３ｂが形成されている。各部品からなる逆止弁４１を組み立てると、逆止弁４１は、弁本体４３とスプリング４４とが収納された状態で、ケース４５の上部開口４５ａにストッパ４２の下端部４２ａが嵌入され、スプリング４４の付勢力によって上方に押し上げられる弁本体４３が、ストッパ４２の下端部４２ｂに圧接した状態となる。   The valve main body 43 has an outer diameter that is substantially the same as the inner diameter of the case 45, and a recess 43 b in which the upper portion of the spring 44 is accommodated is formed at the bottom. When the check valve 41 made up of each part is assembled, the check valve 41 is inserted into the upper opening 45a of the case 45 with the lower end portion 42a of the stopper 42 in a state where the valve main body 43 and the spring 44 are accommodated. The valve body 43 pushed upward by the urging force 44 is brought into pressure contact with the lower end portion 42 b of the stopper 42.

径可変部材５０は、図３（ａ）（ｂ）に示すように、円環状部材が４分割された環片部材５１によって構成されており、環片部材５１は、図３（ｃ）（ｄ）に示すように、互いに平行な水平面を形成する上面５２ａ及び下面５２ｂと、上面５２ａ及び下面５２ｂに直行する内面５２ｃと、ストッパ４２の傾斜面４８を摺動する外面２５ｄとを有している。 環片部材５１の両端面５３ａ、５３ｂには、環片部材５１の略中心部を周方向に延設された孔部５４が形成されており、孔部５４には、弾性棒状バネ５５が挿入される。弾性棒状バネ５５が、隣接する環片部材５１の孔部５４に挿入されて４つの環片部材５１で円環形状が形成されると、環片部材５１は弾性棒状バネ５５の弾性力によって、円環形状の径方向へ広がろうとする（拡径力が生じる）ため、径可変部材５０の内径が拡大する。 Diameter varying member 50, as shown in FIG. 3 (a) (b), is configured annular member by 4 divided ring plate assembly 51, the ring piece member 51, FIG. 3 (c) (d ), An upper surface 52a and a lower surface 52b forming horizontal planes parallel to each other, an inner surface 52c perpendicular to the upper surface 52a and the lower surface 52b, and an outer surface 25d sliding on the inclined surface 48 of the stopper 42. . Both end faces 53a of the ring piece member 51, the 53b, the ring piece has a substantially central portion of the member 51 hole 54 which extends in the circumferential direction is formed, the hole portion 54, the elastic rod-shaped spring 55 inserted Is done. When the elastic rod-shaped spring 55 is inserted into the hole 54 of the adjacent ring piece member 51 to form an annular shape by the four ring piece members 51, the ring piece member 51 is caused by the elastic force of the elastic rod-shaped spring 55. When to spread the radial direction of the annular shape (diameter force is generated), so to expand the inner diameter of the diameter varying member 50.

径可変部材５０が、図３（ｂ）に示すようにストッパ４２の拡径空間４９に設置された場合であって、ロータ２４の回転が停止して冷媒ガスＲの吸入が行われない場合又はロータ２４の回転速度が低速であって冷媒ガスＲの吸入流速が遅い場合には、弾性棒状バネ５５の弾性力によって各環片部材５１の内径（冷媒ガスの流入孔内径）が径方向に広がって外面５２ｄが傾斜面４８に摺動し、各環片部材５１が、拡径空間４９を上昇してストッパ４２の上端部に形成される規制枠５６に環片部材５１の上面５２ａ外周縁部を当接させてストッパ４２の上部に停止する。この場合、図３（ａ）に示すように、各環片部材５１が径方向に広がって径可変部材５０の内径（流入孔内径）が大きくなる（内径Ｌ１）ので、ストッパ４２を通過する冷媒ガスＲの吸入量を多くすることが可能となる。 When the diameter variable member 50 is installed in the diameter expansion space 49 of the stopper 42 as shown in FIG. 3B, the rotation of the rotor 24 stops and the refrigerant gas R is not sucked. When the rotation speed of the rotor 24 is low and the suction flow rate of the refrigerant gas R is low, the inner diameter (inner diameter of the refrigerant gas inflow hole) of each ring piece member 51 is expanded in the radial direction by the elastic force of the elastic rod-shaped spring 55. the outer surface 52d slides on the inclined surface 48 Te, each ring piece member 51, the diameter space 49 rises top 52a the outer peripheral edge portion of the upper ring piece to the regulating frame 56 which is formed in the part member 51 of the stopper 42 To stop at the top of the stopper 42. In this case, as shown in FIG. 3A, each ring piece member 51 expands in the radial direction and the inner diameter (inlet hole inner diameter) of the diameter variable member 50 increases (inner diameter L1). It becomes possible to increase the intake amount of the gas R.

一方で、ロータ２４の回転速度が高速であって冷媒ガスＲの吸入流速が早い場合には、環片部材５１の上面５２ａに冷媒ガスＲが当たって、環片部材５１を下方へ押し下げようとする。冷媒ガスＲが環片部材５１を押し下げようとする圧力（吸入圧力）が、弾性棒状バネ５５の弾性力が各環片部材５１を上昇させようとする力よりも強い場合には、図３（ｄ）に示すように、ストッパ４２の上部に停止していた環片部材５１がストッパ４２の中部へと押し下げられる。この場合、図３（ｂ）に示すように、各環片部材５１が互いに近づき間隔を狭めようとするため、径可変部材５０の内径が狭まり（内径Ｌ２）、ストッパ４２を通過する冷媒ガスＲの吸入量が制限される。 On the other hand, when the rotation speed of the rotor 24 is inspiratory flow rate of the refrigerant gas R a fast is fast, hit refrigerant gas R to the upper surface 52a of the ring piece member 51, and will push down the ring piece member 51 downward To do. When the refrigerant gas R is the pressure to be push down the ring piece member 51 (suction pressure) is stronger than the force elastic force of the elastic rod-shaped spring 55 attempts to increase the respective ring piece member 51, FIG. 3 ( As shown in d), the ring piece member 51 stopped at the top of the stopper 42 is pushed down to the middle of the stopper 42. In this case, as shown in FIG. 3B, the ring piece members 51 approach each other and try to narrow the interval, so that the inner diameter of the diameter variable member 50 is reduced (inner diameter L <b> 2), and the refrigerant gas R that passes through the stopper 42. The amount of inhalation is limited.

図４はロータ２４の回転速度と冷媒ガスＲの吸入量との関係を示したグラフであり、ロータ２４の回転速度Ａは、径可変部材５０がストッパ４２内を下降し始めるときの回転速度を示し、回転速度Ｂは、径可変部材５０がストッパ４２の最下部へ下降して停止する回転速度を示している。   FIG. 4 is a graph showing the relationship between the rotational speed of the rotor 24 and the intake amount of the refrigerant gas R. The rotational speed A of the rotor 24 is the rotational speed at which the variable diameter member 50 starts to descend in the stopper 42. The rotation speed B indicates the rotation speed at which the diameter variable member 50 descends to the bottom of the stopper 42 and stops.

ロータ２４の回転速度が０〜Ａである場合（回転速度が低速度である場合）には、径可変部材５０がストッパ４２の上部に位置して内径Ｌ１を維持するため、ロータ２４の回転速度に対応する冷媒ガスＲの吸入量の増加率を従来のストッパ６を通る冷媒ガスＲの吸入量の増減率と同程度にすることができる。   When the rotation speed of the rotor 24 is 0 to A (when the rotation speed is low), the diameter variable member 50 is positioned above the stopper 42 and maintains the inner diameter L1, so the rotation speed of the rotor 24 is increased. The increase rate of the suction amount of the refrigerant gas R corresponding to the above can be made the same as the increase / decrease rate of the suction amount of the refrigerant gas R passing through the conventional stopper 6.

ロータ２４の回転速度がＡ〜Ｂの間である場合（回転速度が中速度である場合）には、径可変部材５０が回転速度に比例して下降するので、径可変部材５０の内径（流入孔内径）がロータの回転速度に応じて連続的に増減し、回転速度に応じて適切に冷媒ガスの吸入量増減率を変化させることができる。   When the rotational speed of the rotor 24 is between A and B (when the rotational speed is a medium speed), the diameter variable member 50 descends in proportion to the rotational speed. It is possible to continuously increase / decrease the hole inner diameter) according to the rotational speed of the rotor, and to appropriately change the refrigerant gas suction amount increase / decrease rate according to the rotational speed.

さらに、ロータ２４の回転速度がＢ以上になった場合には、径可変部材５０の内径（流入孔内径）が内径Ｌ２に固定されるので、ロータ２４の回転速度に対応する冷媒ガスＲの吸入量の増減率を内径Ｌ１の場合に比べて制限することが可能となる。   Further, when the rotational speed of the rotor 24 is equal to or higher than B, the inner diameter (inflow hole inner diameter) of the diameter variable member 50 is fixed to the inner diameter L2, so that the suction of the refrigerant gas R corresponding to the rotational speed of the rotor 24 is performed. It becomes possible to limit the rate of increase / decrease in the amount compared to the case of the inner diameter L1.

このように、本発明に係る吸入ポート３Ａを備えた気体圧縮装置２０を用いることによって、ロータ２４の回転速度が低速である場合には、径可変部材５０の内径を大きくして冷媒ガスＲの流入量の増減率を高くすることができる。また、ロータ２４の回転速度が中速になった場合には、回転速度に応じて径可変部材５０の内径を増減させることによって、ロータ２４の回転に最適な冷媒ガスの流入量を維持することができる。さらに、ロータ２４の回転速度が高速になった場合には、径可変部材５０の内径を小さくして冷媒ガスＲの吸入量の増減率を低くすることができる。   As described above, by using the gas compression device 20 including the suction port 3A according to the present invention, when the rotational speed of the rotor 24 is low, the inner diameter of the variable diameter member 50 is increased to increase the refrigerant gas R. Increase / decrease rate of the inflow amount can be increased. Further, when the rotational speed of the rotor 24 becomes medium speed, the flow rate of the refrigerant gas optimal for the rotation of the rotor 24 is maintained by increasing or decreasing the inner diameter of the diameter variable member 50 according to the rotational speed. Can do. Further, when the rotational speed of the rotor 24 is increased, the inner diameter of the diameter variable member 50 can be reduced to reduce the rate of increase or decrease in the intake amount of the refrigerant gas R.

このように本発明に係る径可変部材５０を用いることによって、ロータ２４の回転速度に応じて必要とされる冷媒ガスＲの吸入量を調整することができるので、無駄なエネルギー消費を防止することが可能となる。   As described above, by using the diameter variable member 50 according to the present invention, it is possible to adjust the suction amount of the refrigerant gas R according to the rotational speed of the rotor 24, thereby preventing wasteful energy consumption. Is possible.

また、ロータ２４の回転速度に応じて径可変部材５０の内径が変更するので、ロータ２４の低速回転時であっても十分な冷媒ガスを吸入すること可能であり、気体圧縮機２０において十分な冷却能力を確保することができる。   Further, since the inner diameter of the diameter variable member 50 is changed according to the rotational speed of the rotor 24, it is possible to suck a sufficient amount of refrigerant gas even when the rotor 24 rotates at a low speed. Cooling capacity can be secured.

なお、本発明に係る径可変部材５０の構造は、上述したものに限定されるものはなく、上記実施の形態に示した効果と同様の効果を奏するものであるならば形状、構造等に変更を加えたものであっても本発明に含まれるものである。例えば、図５に示すように、環片部材５１の下方にバネ５８を設置して、バネ５８の付勢力によって径可変部材５０が上昇して内径が拡大され、冷媒ガスＲの流圧によりバネ５８が押し下げられて径可変部材５０の内径が小さくなる構造であっても良い。 In addition, the structure of the diameter variable member 50 according to the present invention is not limited to the above-described structure, and can be changed to a shape, a structure, or the like as long as the same effect as the effect described in the above embodiment is achieved. Even if it adds, it is included in this invention. For example, as shown in FIG. 5, a spring 58 is installed below the ring piece member 51, the diameter variable member 50 is raised by the urging force of the spring 58 and the inner diameter is enlarged, and the spring is driven by the flow pressure of the refrigerant gas R. The structure may be such that the inner diameter of the diameter variable member 50 is reduced by pushing down 58.

本発明に係る吸入ポートを備えた気体圧縮機を示した断面図である。It is sectional drawing which showed the gas compressor provided with the suction port which concerns on this invention. 図１に示した逆止弁の展開側面図である。FIG. 2 is a developed side view of the check valve shown in FIG. 1. 図２に示すストッパと径可変部材とを示した図であり、（ａ）は内径が拡大したときの径可変部材を示した平面図であり、（ｂ）は内径が狭くなったときの径可変部材を示した平面図であり、（ｃ）は（ａ）のＡ−Ａ線を矢印方向から見た断面図であり、（ｄ）は（ｂ）のＢ−Ｂ線を矢印方向から見た断面図である。It is the figure which showed the stopper and diameter variable member which are shown in FIG. 2, (a) is a top view which showed the diameter variable member when an internal diameter expands, (b) is a diameter when an internal diameter becomes narrow. It is the top view which showed the variable member, (c) is sectional drawing which looked at the AA line of (a) from the arrow direction, (d) is the BB line of (b) seen from the arrow direction. FIG. ロータの回転速度と冷媒ガスの吸入量との関係を示したグラフである。6 is a graph showing the relationship between the rotational speed of the rotor and the amount of refrigerant gas sucked. 他のストッパと径可変部材とを示した図であり、（ａ）は径可変部材を示した平面図であり、（ｂ）は（ａ）のＣ−Ｃ線を矢印方向から見た断面図であり、It is the figure which showed the other stopper and the diameter variable member, (a) is a top view which showed the diameter variable member, (b) is sectional drawing which looked at CC line of (a) from the arrow direction And 従来の気体圧縮機における逆止弁を示した断面図である。It is sectional drawing which showed the non-return valve in the conventional gas compressor. 従来の逆止弁を示した展開側面図である。It is the expansion | deployment side view which showed the conventional check valve. 従来の逆止弁の駆動状況を示した断面図であって、（ａ）は弁本体の閉塞時を示し、（ｂ）は弁本体の開放時を示したものである。It is sectional drawing which showed the drive condition of the conventional non-return valve, Comprising: (a) shows the time of closing of a valve main body, (b) shows the time of opening of a valve main body.

符号の説明Explanation of symbols

１ 圧縮室
２ 吸入室
３、３Ａ 吸入ポート
６、４２ ストッパ
７、４３ 弁本体
２４ ロータ
４８ 傾斜面
４９ 拡径空間
５０ 径可変部材 DESCRIPTION OF SYMBOLS 1 Compression chamber 2 Suction chamber 3, 3A Suction port 6, 42 Stopper 7, 43 Valve main body 24 Rotor 48 Inclined surface 49 Expanded space 50 Diameter variable member

Claims (3)

圧縮室へ冷媒ガスを送出する吸入室に連通し、ロータの回転に伴って外部から冷媒ガスが吸入される吸入ポートに設置される逆止弁であって、
該逆止弁は、前記外部に連通するストッパと、該ストッパに圧接することにより前記冷媒ガスの吸入室への吸入及び逆流を防止し、前記ストッパから離反することによって前記冷媒ガスの前記吸入室への流入を許容する弁本体とを有し、
前記ストッパの内部には、該ストッパの中部から前記外部側端部にかけて口径が拡大されて傾斜面が形成された拡径空間が設けられ、
該拡径空間には、前記ロータの回転速度に応じて前記傾斜面を摺動して前記拡径空間における前記冷媒ガスの流入孔内径を変更することが可能な径可変部材が設けられること
を特徴とする逆止弁。 A check valve that communicates with a suction chamber that sends refrigerant gas to the compression chamber, and that is installed at a suction port through which refrigerant gas is sucked from the outside as the rotor rotates;
The check valve includes a stopper communicating with the outside, and prevents suction and backflow of the refrigerant gas into the suction chamber by being in pressure contact with the stopper, and the suction chamber of the refrigerant gas is separated from the stopper. A valve body that allows inflow to
Inside the stopper, there is provided an enlarged space in which the diameter is enlarged from the middle part of the stopper to the outer side end part to form an inclined surface,
The diameter-expanding space is provided with a variable diameter member capable of changing the inside diameter of the refrigerant gas inflow hole in the diameter-expanding space by sliding on the inclined surface according to the rotational speed of the rotor. Characteristic check valve. 前記径可変部材は、環状部材が複数に分割された環片部材と、該環片部材の中心部に周方向に向かって延設された孔部に挿入される棒状弾性バネとを有し、
前記孔部に前記棒状弾性バネが挿入されて前記複数の環片部材によって環形状を形成する前記径可変部材が、前記棒状弾性バネの弾性力により径方向に広がろうとする拡径力と、前記ロータの回転に伴って吸入される前記冷媒ガスにより前記環片部材の上面に加えられる吸入圧力との強弱関係に応じて前記流入孔内径が拡狭することを特徴とする請求項１に記載の逆止弁。 The diameter varying member includes the ring-shaped member and a ring piece member that is divided into a plurality, and a rod-shaped elastic springs which are inserted into a hole portion extending in the center portion toward the peripheral direction of the ring piece member ,
A diameter force said diameter varying member which forms a ring shape by the plurality of ring pieces member the rod-shaped elastic spring is inserted into the hole portion, when you to spread radially by the elastic force of the rod-shaped elastic springs, The inflow hole inner diameter expands or contracts according to a strength relationship with a suction pressure applied to the upper surface of the ring piece member by the refrigerant gas sucked as the rotor rotates. Check valve. 請求項１又は請求項２に記載の逆止弁を備えたことを特徴とする気体圧縮装置。   A gas compression apparatus comprising the check valve according to claim 1.
JP2004198889A 2004-07-06 2004-07-06 Check valve and gas compression device equipped with check valve Expired - Fee Related JP4429827B2 (en)

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JP5029526B2 (en) * 2008-07-22 2012-09-19 株式会社豊田自動織機 Refrigerant gas suction amount control device for rotary compressor
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