JP2019218879A - Suction valve structure for reciprocating compressor, and reciprocating compressor - Google Patents

Suction valve structure for reciprocating compressor, and reciprocating compressor Download PDF

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JP2019218879A
JP2019218879A JP2018115093A JP2018115093A JP2019218879A JP 2019218879 A JP2019218879 A JP 2019218879A JP 2018115093 A JP2018115093 A JP 2018115093A JP 2018115093 A JP2018115093 A JP 2018115093A JP 2019218879 A JP2019218879 A JP 2019218879A
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suction valve
suction
arm
root
reciprocating compressor
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JP2018115093A
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勝孝 宇根
Katsutaka Une
勝孝 宇根
鈴木　健太郎
Kentaro Suzuki
健太郎 鈴木
高橋　秀行
Hideyuki Takahashi
秀行 高橋
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Valeo Japan Co Ltd
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Valeo Japan Co Ltd
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Priority to JP2018115093A priority Critical patent/JP2019218879A/en
Priority to EP19180356.8A priority patent/EP3584440A3/en
Publication of JP2019218879A publication Critical patent/JP2019218879A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/0804—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B27/0821—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block component parts, details, e.g. valves, sealings, lubrication
    • F04B27/0839—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block component parts, details, e.g. valves, sealings, lubrication valve means, e.g. valve plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1066—Valve plates

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Check Valves (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

To provide a suction valve structure for a reciprocating compressor capable of securing reliability with respect to a suction valve even if the reciprocating compressor is fast operated while using a lead valve for the suction valve.SOLUTION: A lead valve used for a suction valve 21 of a reciprocating compressor 1 comprises a tongue-like arm part 23. An outer shape of the arm part 23 is formed from a slit part 24 which is provided in a suction valve seat 22, and an inner shape of the arm part 23 is formed from an opening part 25 which is provided in the suction valve seat 22. An outer reference line L2 overlapped with the outer shape and an inner reference line L3 overlapped with the inner shape are inclined so as to cross a centerline L4 of the arm part passing both a center point P2 of a cylinder bore and a center point P3 of a suction port, such that the root side of the arm part 23 becomes wider than the tip side thereof. Further, an inclination angle R1 of the outer reference line L2 from the centerline L4 is larger than an inclination angle R2 of the inner reference line L3 from the centerline L4 by a predetermined value or more.SELECTED DRAWING: Figure 7

Description

この発明は、例えば車両用空調装置の冷凍サイクルに用いられる往復動式圧縮機、特に吸入ポートを開閉する吸入弁にリード弁が用いられた吸入弁構造に関する。   The present invention relates to a reciprocating compressor used in, for example, a refrigeration cycle of a vehicle air conditioner, and more particularly to a suction valve structure using a reed valve as a suction valve for opening and closing a suction port.

往復動式圧縮機において、シリンダボアが形成されたシリンダブロックと、シリンダボア内を往復直線運動するピストンと、シリンダブロックのピストンが挿入される側と反対側に設けられ、作動流体が一時的に収容される吸入室及び吐出室が区画形成されたシリンダヘッドと、シリンダブロックとシリンダヘッドとの間に配された弁板とを備えたものが、例えば特許文献１，２に示されるように、公知となっている。   In a reciprocating compressor, a cylinder block in which a cylinder bore is formed, a piston that reciprocates linearly in the cylinder bore, and a cylinder block are provided on the side opposite to the side where the piston is inserted, and a working fluid is temporarily stored therein. A cylinder head in which a suction chamber and a discharge chamber are formed and a valve plate disposed between the cylinder block and the cylinder head are known, for example, as disclosed in Patent Documents 1 and 2. Has become.

このような構成においては、シリンダボアと吸入室及び吐出室とは、弁板に設けられたポートを介してそれぞれ連通している。それぞれのポートを開閉する弁体（吸入弁、吐出弁）は、例えば特許文献１、２に示されるように、弾性を有し、組み立て性や生産性にも優れた舌状の腕部を有するリード弁が用いられている。吸入弁に舌状の腕部を有するリード弁を用いた場合には、吸入ポートを通過した冷媒ガス等の作動流体は、吸入弁と弁板との狭い隙間を流れるため流路が限られる。   In such a configuration, the cylinder bore communicates with the suction chamber and the discharge chamber via ports provided in the valve plate. A valve body (suction valve, discharge valve) for opening and closing each port has a tongue-shaped arm portion having elasticity and excellent in assemblability and productivity, as shown in Patent Documents 1 and 2, for example. A reed valve is used. When a reed valve having a tongue-shaped arm portion is used as the suction valve, the working fluid such as the refrigerant gas that has passed through the suction port flows through a narrow gap between the suction valve and the valve plate, so that the flow path is limited.

このような作動流体の吸入時における吸入抵抗を低減する手法としては、例えば特許文献２に示されるように、吸入弁の根本側の幅を細くしたり、吸入弁の長手方向の寸法を長くしたりすることで、吸入弁のバネ剛性を低くすることが主流であった。   As a method of reducing the suction resistance at the time of suction of the working fluid, for example, as shown in Patent Document 2, the width of the root side of the suction valve is reduced, or the length of the suction valve in the longitudinal direction is increased. The mainstream has been to lower the spring stiffness of the suction valve.

一方で、近年において、車両用可変容量型の往復動式圧縮機について、必要な能力を得られるようにするために、高速運転させることが望まれている。   On the other hand, in recent years, it has been desired that a variable displacement reciprocating compressor for a vehicle be operated at a high speed in order to obtain necessary performance.

特開２０００−５４９６１号公報JP-A-2000-54961 実用新案登録第２５８７０８５号公報Utility Model Registration No. 2587085

しかしながら、吸入弁に舌状の腕部を有するリード弁を用いた場合に、吸入弁のバネ剛性が低い状態で往復動式圧縮機を高速運転させると、例えば吸入弁が吸入ポートを開く方向に動くときには先端が弁座に当たる速度、ひいては衝撃が大きくなり、吸入弁が吸入ポートを閉じる方向に動くときには先端が弁板に当たる速度、ひいては衝撃が大きくなる。しかも、吸入弁が弁座に当接した後の二次的変形も大きくなる。このため、吸入弁の腕部の先端が割れる等、破損しやすいという不都合が生ずる。   However, when a reed valve having a tongue-shaped arm is used as a suction valve and the reciprocating compressor is operated at a high speed in a state where the spring rigidity of the suction valve is low, for example, the suction valve opens in the direction in which the suction port opens. When moving, the speed at which the tip hits the valve seat, and thus the impact increases, and when the suction valve moves in the direction to close the suction port, the speed at which the tip hits the valve plate, and thus the impact increases. Moreover, the secondary deformation after the suction valve comes into contact with the valve seat also increases. For this reason, there is an inconvenience that the suction valve is easily broken, for example, the tip of the arm is broken.

本発明は、上記課題を解決するためになされたものであって、吸入弁にリード弁を用い、往復動式圧縮機を高速運転しても、吸入弁への信頼性を確保することができる往復動式圧縮機の吸入弁構造及びこの吸入弁構造を用いた往復動式圧縮機を提供することを目的としている。   The present invention has been made in order to solve the above-mentioned problem, and it is possible to ensure the reliability of a suction valve even when a reciprocating compressor is operated at high speed by using a reed valve as a suction valve. An object of the present invention is to provide a suction valve structure of a reciprocating compressor and a reciprocating compressor using the suction valve structure.

上記目的を達成すべく、この発明の往復動式圧縮機の吸入弁構造は、出口端がシリンダボア内に形成される圧縮室に開口し、前記出口端が吸入弁により開閉可能に閉塞される吸入ポート、及び、入口端が前記圧縮室に開口し、出口端が吐出弁により開閉可能に閉塞される吐出ポートを有し、前記吸入弁にリード弁が用いられた往復動式圧縮機において、前記吸入弁は、舌状の腕部を有し、前記腕部の外側形状は、１つの先端部、１対の根本部、前記先端部と前記根本部との間の１対の中間部から成るスリット部を吸入弁シートに設けることで形成され、前記腕部の内側形状は、前記吸入弁シートの前記スリット部の一方の中間部と根本部、他方の中間部と根本部との間に、前記吸入弁シートの周縁近傍から前記シリンダボアの中心点側に向けて延びる長孔状の開口部を設けることで形成され、前記外側形状の前記スリット部の中間部に重なる外側基準線及び前記内側形状の前記開口部の短手方向で向かい合う縁辺に重なる内側基準線を、それぞれ前記シリンダボアの中心点及び前記吸入ポートの中心点の双方を通る腕部の中心線と交差するように傾斜させることにより、前記腕部は付根側の幅が先端側の幅よりも広くなっており、更に、前記外側基準線の傾斜角度が前記内側基準線の傾斜角度よりも所定値以上大きくなっていることを特徴としている（請求項１）。ここで、腕部の付根は、スリット部の一方の根本部と他方の根本部の先端部側とは反対側を通り且つ先端部と平行な基準線上の位置であり、以下に記述する腕部の付根も同様である。また、外側基準線と内側基準線との傾斜角度の差の所定値は、例えば８度である。   In order to achieve the above object, a suction valve structure of a reciprocating compressor according to the present invention has an outlet end opened to a compression chamber formed in a cylinder bore, and the outlet end is opened and closed by a suction valve. A reciprocating compressor in which a port, and an inlet end is open to the compression chamber, and an outlet end is openably and closably closed by a discharge valve, and a reed valve is used for the suction valve. The suction valve has a tongue-shaped arm portion, and the outer shape of the arm portion includes a tip, a pair of roots, and a pair of intermediate portions between the tip and the root. The slit portion is formed in the suction valve seat, and the inner shape of the arm portion is formed between one intermediate portion and the root portion of the slit portion of the suction valve seat, and between the other intermediate portion and the root portion, From the vicinity of the periphery of the suction valve seat to the center point side of the cylinder bore An outer reference line that is formed by providing an elongated slot-shaped opening that extends, and an outer reference line that overlaps the middle portion of the outer shape of the slit portion and an inner reference line that overlaps an edge of the inner shape that is opposed in the short direction of the opening. By inclining so as to intersect with the center line of the arm passing through both the center point of the cylinder bore and the center point of the suction port, the width of the arm at the root is wider than the width at the tip. Further, the inclination angle of the outer reference line is larger than the inclination angle of the inner reference line by a predetermined value or more (claim 1). Here, the root of the arm portion is a position on a reference line passing through the one root portion of the slit portion and the other root portion on the side opposite to the tip portion side and parallel to the tip portion, and is described below. The same applies to the root of. The predetermined value of the difference between the inclination angles of the outer reference line and the inner reference line is, for example, 8 degrees.

このように、吸入弁の腕部の外側形状と内側形状とについて、外側基準線の傾斜角度を内側基準線の傾斜角度よりも所定値以上の大きさとなるように設定することにより、外側形状と内側形状との間の幅が付根側と先端側とで変わらない場合や所定値よりも小さい場合に比し、吸入弁の腕部の付根の剛性を向上させ、吸入弁の腕部がしなり難くなる。これにより、吸入弁にリード弁を用いても吸入ポートの開閉速度を遅くすることができるので、吸入弁の腕部の先端が弁板や弁座に当たる速度、ひいては衝撃を低下させることが可能である。更には、吸入弁の腕部の先端が弁座に接触した後の二次的変形も防止することができる。よって、リード弁の腕部の先端の破損が防止され、往復動式圧縮機の高速運転時でも吸入弁に対する信頼が確保される。また、吸入弁の腕部の先端が弁板や弁座に当たる速度が低下することにより、往復動式圧縮機の騒音も低減することができる。   In this manner, the outer shape and the inner shape of the arm portion of the suction valve are set such that the inclination angle of the outer reference line is larger than or equal to a predetermined value than the inclination angle of the inner reference line, and thus the outer shape and the inner shape are set. Compared with the case where the width between the inner shape and the root side does not change between the root side and the tip side or when the width is smaller than a predetermined value, the rigidity of the root of the arm portion of the suction valve is improved, and the arm portion of the suction valve flexes. It becomes difficult. As a result, even if a reed valve is used as the suction valve, the opening / closing speed of the suction port can be reduced, so that the speed at which the tip of the arm of the suction valve hits the valve plate or valve seat, and hence the impact, can be reduced. is there. Furthermore, secondary deformation after the tip of the arm portion of the suction valve contacts the valve seat can also be prevented. Therefore, damage to the tip of the arm portion of the reed valve is prevented, and the reliability of the suction valve is ensured even during high-speed operation of the reciprocating compressor. Further, the speed at which the tip of the arm of the suction valve contacts the valve plate or the valve seat is reduced, so that the noise of the reciprocating compressor can also be reduced.

また、この発明の往復動式圧縮機の吸入弁構造は、出口端がシリンダボア内に形成される圧縮室に開口し、前記出口端が吸入弁により開閉可能に閉塞される吸入ポート、及び、入口端が前記圧縮室に開口し、出口端が吐出弁により開閉可能に閉塞される吐出ポートを有し、前記吸入弁にリード弁が用いられた往復動式圧縮機において、前記吸入弁は、舌状の腕部を有し、前記腕部の外側形状は、１つの先端部、１対の根本部、前記先端部と前記根本部との間の１対の中間部から成るスリット部を吸入弁シートに設けることで形成され、前記腕部の内側形状は、前記吸入弁シートの前記スリット部の一方の中間部と根本部、他方の中間部と根本部との間に、前記吸入弁シートの周縁近傍から前記シリンダボアの中心点側に向けて延びる長孔状の開口部を設けることで形成され、前記腕部は、前記スリット部の根本部の前記中間部とは反対側の端から前記シリンダボアの中心点及び前記吸入ポートの中心点の双方を通る腕部の中心線までの幅方向寸法と、前記スリット部の双方の根本部の前記中間部とは反対側の端を通る基準線と前記中心線とが交差する位置から前記中心線の前記腕部の先端側の端までの長さ方向寸法とを対比して、前記長さ方向寸法が前記幅方向寸法よりも長いが近似していることを特徴としている（請求項２）。ここで、吸入弁の腕部の幅方向寸法と長さ方向寸法とを対比した場合の数値は、例えば１：１．８以下となる。   In addition, the suction valve structure of the reciprocating compressor of the present invention has a suction port having an outlet end opened to a compression chamber formed in a cylinder bore, and the outlet end being openably closed by a suction valve, and an inlet. In a reciprocating compressor in which an end is open to the compression chamber and an outlet end is openably closed by a discharge valve, and a reed valve is used as the suction valve, the suction valve includes a tongue. The outer shape of the arm portion has a slit portion including one tip portion, a pair of root portions, and a pair of intermediate portions between the tip portion and the root portion. The inner shape of the arm portion is formed by being provided on a seat, and between the middle portion and the root portion of one of the slit portions of the suction valve seat, and the other middle portion and the root portion of the slit portion of the suction valve seat, An elongated hole extending from the vicinity of the peripheral edge toward the center point of the cylinder bore The arm portion is formed by providing a mouth, and the arm portion passes through both the center point of the cylinder bore and the center point of the suction port from an end of the base portion of the slit opposite to the intermediate portion. The width direction dimension up to the center line, and the tip of the arm portion of the center line from the position where the center line intersects with the reference line passing through the end opposite to the intermediate portion of both roots of the slit portion. It is characterized in that the length-wise dimension is longer than the width-wise dimension but is similar to the length-wise dimension up to the side end (claim 2). Here, the numerical value when the width dimension and the length dimension of the arm portion of the suction valve are compared is, for example, 1: 1.8 or less.

このように、吸入弁の腕部の長さ方向寸法を幅方向寸法より長いが近似させることにより、吸入弁の腕部の長さ方向寸法と幅方向寸法との長さの差が大きい場合に比し、吸入弁の腕部の付根の剛性を向上させ、吸入弁の腕部がしなり難くなる。これにより、吸入弁にリード弁を用いても吸入ポートの開閉速度を遅くすることができるので、吸入弁の腕部の先端が弁板や弁座に当たる速度、ひいては衝撃も低下することが可能である。更には、吸入弁の腕部の先端が弁座に接触した後の二次的変形も防止することができる。よって、吸入弁の腕部の先端の破損が防止され、往復動式圧縮機の高速運転時でも吸入弁に対する信頼が確保される。また、吸入弁の腕部の先端が弁板や弁座に当たる速度が低下することにより、往復動式圧縮機の騒音も低減することができる。   As described above, by approximating the length dimension of the arm portion of the suction valve to be longer than the width direction dimension, when the difference between the length dimension and the width dimension of the arm portion of the suction valve is large, In comparison, the rigidity of the base of the arm portion of the suction valve is improved, and the arm portion of the suction valve is less likely to bend. As a result, even if a reed valve is used as the suction valve, the opening / closing speed of the suction port can be reduced, so that the speed at which the tip of the arm of the suction valve hits the valve plate or valve seat and, consequently, the impact can be reduced. is there. Furthermore, secondary deformation after the tip of the arm portion of the suction valve contacts the valve seat can also be prevented. Therefore, damage to the distal end of the arm portion of the suction valve is prevented, and the reliability of the suction valve is ensured even during high-speed operation of the reciprocating compressor. Further, the speed at which the tip of the arm of the suction valve contacts the valve plate or the valve seat is reduced, so that the noise of the reciprocating compressor can also be reduced.

請求項３に記載の往復動式圧縮機の吸入弁構造において、前記スリット部は、前記先端部及び前記中間部の短手方向の隙間の幅が所定の数値にて一定又は略一定に形成され、前記根本部が円形状に形成されることにより、前記根本部の隙間の幅が前記先端部及び前記中間部の短手方向の隙間の幅よりも大きいことを特徴としている。ここで、所定の数値とは、例えば２ｍｍである。もっとも、スリット部の中間部では短手方向の溝幅を例えば２ｍｍで一定としつつ、先端部では短手方向の溝幅を例えば２ｍｍで一定とする場合のみならず、１．６ｍｍから１．７ｍｍの範囲で一定としても良い。この場合にはスリット部の中間部と先端部との境界部位では幅が変位することもあるので、一定又は略一定としている。   4. The suction valve structure of the reciprocating compressor according to claim 3, wherein the slit portion is formed such that a width of a gap in the short direction between the front end portion and the intermediate portion is constant or substantially constant at a predetermined numerical value. Since the root is formed in a circular shape, the width of the gap at the root is larger than the width of the gap in the short direction between the distal end and the intermediate part. Here, the predetermined numerical value is, for example, 2 mm. Of course, not only when the width of the groove in the short direction is constant at, for example, 2 mm at the middle portion of the slit portion, but also at the tip portion, the width of the groove in the short direction is constant at, for example, 2 mm, but also from 1.6 mm to 1.7 mm. May be constant within the range. In this case, the width may be displaced at the boundary portion between the intermediate portion and the distal end portion of the slit portion, so that the width is constant or substantially constant.

これにより、スリット部の先端部及び中間部の短手方向の溝幅を所定の数値の幅で一定又は略一定にすることにより、スリット部の短手方向の溝幅が大きい場合に比し、スリット部によるデッドボリュームを削減することができるので、圧縮機の性能の向上が図られる。また、前記根本部が円形状に形成されることにより、根本部にせん断加工で発生したバリを取る作業が容易となり、バレル研磨などの機械加工により確実にバリを取る作業を行うことが可能である。さらに、スリット部の根本部を円形状にすることにより、根本部が角を有する形状とする場合とは異なり、吸入弁の腕部がしなっても根本部に割れが生ずるのを防止することができる。   Thereby, by making the groove width in the short direction of the leading end portion and the intermediate portion of the slit portion constant or substantially constant at a predetermined numerical value width, compared to the case where the groove width in the short direction of the slit portion is large, Since the dead volume due to the slit portion can be reduced, the performance of the compressor is improved. In addition, since the root portion is formed in a circular shape, it is easy to remove burrs generated by shearing the root portion, and it is possible to reliably remove burrs by mechanical processing such as barrel polishing. is there. Furthermore, unlike the case where the root portion has a corner, by forming the root portion of the slit portion into a circular shape, it is possible to prevent the root portion from being cracked even when the arm portion of the suction valve is bent. Can be.

請求項４に記載の往復動式圧縮機の吸入弁構造において、前記腕部は、前記スリット部の双方の根本部の前記中間部とは反対側の端を通る基準線と前記中心線とが交差する位置が前記シリンダボアの中心に近接していることを特徴としている。   5. The suction valve structure of the reciprocating compressor according to claim 4, wherein the arm portion has a reference line and a center line passing through opposite ends of both root portions of the slit portion opposite to the intermediate portion. 6. The crossing position is close to the center of the cylinder bore.

これにより、吸入弁の腕部の付根の位置を従来よりもシリンダボアの中心に寄せることができるので、吸入弁の腕部の長さ方向の寸法を短くして、吸入弁の腕部の剛性を更に上げて、往復動式圧縮機の高速運転時における吸入弁への信頼性をより一層高めることができる。   As a result, the position of the root of the arm of the suction valve can be closer to the center of the cylinder bore than before, so that the length in the length direction of the arm of the suction valve is shortened, and the rigidity of the arm of the suction valve is reduced. Furthermore, the reliability of the suction valve during high-speed operation of the reciprocating compressor can be further improved.

請求項５に記載の往復動式圧縮機は、請求項１から請求項４のいずれかに記載の吸入弁構造を有することを特徴としている。往復動式圧縮機は、例えば車両用空調装置の冷凍サイクルに用いられる。   A reciprocating compressor according to a fifth aspect has the suction valve structure according to any one of the first to fourth aspects. The reciprocating compressor is used, for example, in a refrigeration cycle of a vehicle air conditioner.

以上に述べたように、本発明によれば、吸入弁の腕部の付根の剛性を向上させ、吸入弁の腕部がしなり難くなることにより、吸入弁にリード弁を用いても吸入ポートの開閉速度を遅くすることができる。このため、吸入弁の腕部の先端が弁板や弁座に当たる速度、ひいては衝撃も低下させることが可能となる。更には、吸入弁の腕部の先端が弁座に接触した後の二次的変形も防止することができる。よって、吸入弁の腕部の先端の破損が防止され、往復動式圧縮機の高速運転時でも吸入弁に対する信頼を確保することができる。そして、吸入弁の腕部の先端が弁板や弁座に当たる速度が低下するので、往復動式圧縮機の騒音の低減も図ることができる。   As described above, according to the present invention, the rigidity of the base of the arm portion of the suction valve is improved, and the arm portion of the suction valve becomes difficult to bend. Opening and closing speed can be reduced. Therefore, it is possible to reduce the speed at which the tip of the arm portion of the suction valve hits the valve plate or the valve seat, and furthermore, the impact. Furthermore, secondary deformation after the tip of the arm of the suction valve comes into contact with the valve seat can also be prevented. Therefore, damage to the tip of the arm portion of the suction valve is prevented, and reliability of the suction valve can be ensured even during high-speed operation of the reciprocating compressor. Since the speed at which the tip of the arm portion of the suction valve contacts the valve plate or the valve seat decreases, the noise of the reciprocating compressor can be reduced.

（ａ）は、本発明に係る吸入弁構造を備えた往復動式圧縮機の一部を示す断面図であり、（ｂ）は、往復動式圧縮機の吸入弁等の拡大断面図である。(A) is a sectional view showing a part of a reciprocating compressor having a suction valve structure according to the present invention, and (b) is an enlarged sectional view of a suction valve and the like of the reciprocating compressor. . （ａ）は、弁板のシリンダブロック側の端面を示す図であり、（ｂ）は、弁板のシリンダブロック側の端面に重ね合わせる吸入弁シートを示す図である。(A) is a figure which shows the cylinder block side end surface of a valve plate, (b) is a figure which shows the suction valve seat superimposed on the cylinder block side end surface of a valve plate. 弁板に吸入弁シートを重ね合わせた状態を示す図である。It is a figure showing the state where the suction valve seat was superimposed on the valve plate. （ａ）は、弁板のシリンダヘッド側の端面を示す図であり、（ｂ）は、弁板のシリンダヘッド側の端面に重ね合わせる吐出弁シートを示す図である。(A) is a figure which shows the cylinder head side end surface of a valve plate, (b) is a figure which shows the discharge valve sheet superimposed on the cylinder head side end surface of a valve plate. 弁板に吐出弁シートを重ね合わせた状態を示す図である。It is a figure showing the state where the discharge valve sheet was overlapped on the valve plate. 吸入弁シートに形成されて吸入弁として用いられるリード弁の腕部の領域を示した図である。FIG. 5 is a diagram illustrating a region of an arm portion of a reed valve formed on a suction valve seat and used as a suction valve. 吸入弁の腕部は、付根側の幅が先端側の幅よりも広くなっていること、しかも、外側基準線の中心線からの傾斜角度が内側基準線の中心線からの傾斜角度よりも８度以上大きくなっていることを示した図である。The arm of the suction valve has a width on the root side wider than a width on the tip side, and the angle of inclination of the outer reference line from the center line is 8 degrees smaller than the angle of inclination of the inner reference line from the center line. It is the figure which showed that it became larger than degree. 吸入弁の腕部の長さ方向寸法は幅方向寸法よりもその長いが両寸法の比率は１．８：１以下であることを示した図である。It is a figure showing that the length dimension of the arm portion of the suction valve is longer than the width dimension, but the ratio of both dimensions is 1.8: 1 or less.

以下、この発明の実施形態について添付図面を参照しながら説明する。
本発明が適用される往復動式圧縮機の一例として、冷媒を作動流体とする車両用空調装置の冷凍サイクルに用いられる、斜板式又はピストン型とも称される往復動式圧縮機が図１に示されている。 Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
As an example of a reciprocating compressor to which the present invention is applied, a reciprocating compressor, also called a swash plate type or a piston type, used in a refrigeration cycle of a vehicle air conditioner using a refrigerant as a working fluid is shown in FIG. It is shown.

この往復動式圧縮機１は、シリンダブロック２と、このシリンダブロック２ のリア側に弁板３を介して組み付けられたシリンダヘッド４と、シリンダブロック２のフロント側を覆うように組付けられ、シリンダブロック２のフロント側でクランク室５を画成するフロントハウジング６とを有して構成されている。これらフロントハウジング６、シリンダブロック２、弁板３、及び、シリンダヘッド４は、図示しない締結ボルトにより軸方向に締結されて圧縮機のハウジング７を構成している。   The reciprocating compressor 1 is assembled so as to cover a cylinder block 2, a cylinder head 4 mounted on a rear side of the cylinder block 2 via a valve plate 3, and a front side of the cylinder block 2. And a front housing 6 defining a crank chamber 5 on the front side of the cylinder block 2. The front housing 6, the cylinder block 2, the valve plate 3, and the cylinder head 4 are fastened in the axial direction by fastening bolts (not shown) to form a housing 7 of the compressor.

クランク室５に配される駆動軸８は、フロントハウジング６及びシリンダブロック２にベアリング９（シリンダブロック側のみ図示）を介して回転自在に保持されている。この駆動軸８は、この実施形態では、フロントハウジング６から突出して図示しない走行用エンジンにベルト及びプーリを介して接続され、走行用エンジンの動力が伝達されて回転するようになっている。   The drive shaft 8 arranged in the crank chamber 5 is rotatably held by the front housing 6 and the cylinder block 2 via bearings 9 (only the cylinder block side is shown). In this embodiment, the drive shaft 8 protrudes from the front housing 6 and is connected to a traveling engine (not shown) via a belt and a pulley, so that the power of the traveling engine is transmitted to rotate.

シリンダブロック２には、前記ベアリング９が収容される支持孔１１と、この支持孔１１を中心とする円周上に等間隔に配された複数のシリンダボア１２とが形成されている。それぞれのシリンダボア１２には、片頭ピストン１３が往復摺動可能に挿入されている。   The cylinder block 2 is formed with a support hole 11 for accommodating the bearing 9 and a plurality of cylinder bores 12 arranged at equal intervals on a circumference centered on the support hole 11. A single-headed piston 13 is inserted into each of the cylinder bores 12 so as to be able to slide back and forth.

クランク室５には、駆動軸８の回転に同期して回転する斜板１４が駆動軸８上にヒンジボール１５を介して設けられている。この斜板１４の周縁部分には、前後に設けられた一対のシュー１６を介して片頭ピストン１３の係合部１３ａが係留されている。   In the crank chamber 5, a swash plate 14 that rotates in synchronization with the rotation of the drive shaft 8 is provided on the drive shaft 8 via a hinge ball 15. An engaging portion 13a of the single-headed piston 13 is moored at a peripheral portion of the swash plate 14 via a pair of shoes 16 provided at the front and rear.

したがって、駆動軸８が回転すると、これに伴って斜板１４が回転し、この斜板１４の回転運動がシュー１６を介して片頭ピストン１３の往復直線運動に変換され、シリンダボア１２内において片頭ピストン１３と弁板３との間に形成される圧縮室１７の容積を変化させるようになっている。   Accordingly, when the drive shaft 8 rotates, the swash plate 14 rotates with the rotation of the drive shaft 8, and the rotational motion of the swash plate 14 is converted into the reciprocating linear motion of the single-head piston 13 via the shoe 16, and the single-head piston The volume of the compression chamber 17 formed between the valve 13 and the valve plate 3 is changed.

前記弁板３には、それぞれのシリンダボア１２に対応して吸入ポート２０及び吐出ポート３０が形成されている。更に、弁板３の吸入ポート２０の周囲に環状溝２８を形成することで、吸入弁２１が着座する弁座２７が吸入ポート２０の開口周縁に円環状に形成され、弁板３の吐出ポート３０の周囲に環状溝３８を形成することで、吐出弁が着座する弁座３７が吐出ポート３０の開口周縁に円環状に形成されている。   The valve plate 3 is formed with a suction port 20 and a discharge port 30 corresponding to each cylinder bore 12. Further, by forming an annular groove 28 around the suction port 20 of the valve plate 3, the valve seat 27 on which the suction valve 21 is seated is formed in an annular shape around the opening edge of the suction port 20, and the discharge port of the valve plate 3 is formed. By forming the annular groove 38 around the periphery of the discharge port 30, the valve seat 37 on which the discharge valve is seated is formed in an annular shape around the opening edge of the discharge port 30.

また、シリンダヘッド４には、圧縮室１７に供給する作動流体を収容する吸入室１８と、圧縮室１７から吐出した作動流体を収容する吐出室１９とが画設されている。この例において、吸入室１８は、シリンダヘッド４の中央部分に形成され、吐出室１９は吸入室１８の周囲に環状に形成されている。   The cylinder head 4 is provided with a suction chamber 18 for containing a working fluid supplied to the compression chamber 17 and a discharge chamber 19 for containing a working fluid discharged from the compression chamber 17. In this example, the suction chamber 18 is formed at the center of the cylinder head 4, and the discharge chamber 19 is formed annularly around the suction chamber 18.

吸入室１８は、後述する吸入弁２１によって開閉される前記吸入ポート２０を介して圧縮室１７に連通可能となっている。また、吐出室１９は、後述する吐出弁３１によって開閉される前記吐出ポート３０を介して圧縮室１７に連通可能となっている。   The suction chamber 18 can communicate with the compression chamber 17 via the suction port 20 which is opened and closed by a suction valve 21 described later. Further, the discharge chamber 19 can communicate with the compression chamber 17 via the discharge port 30 which is opened and closed by a discharge valve 31 described later.

弁板３とシリンダブロック２との間には、弁板３のシリンダブロック側の端面に重ね合わせて取り付けられ、吸入弁２１が形成された吸入弁シート２２と、この吸入弁シート２２に重ね合わせられ、弁板３とシリンダブロック２との間に挟持固定されるガスケット２６とが設けられている。   Between the valve plate 3 and the cylinder block 2, a suction valve seat 22 on which a suction valve 21 is formed, which is attached to the end surface of the valve plate 3 on the cylinder block side, and a superposition on the suction valve seat 22. And a gasket 26 sandwiched and fixed between the valve plate 3 and the cylinder block 2.

また、弁板３とシリンダヘッド４との間には、弁板３のシリンダヘッド側の端面に重ね合わせて取り付けられ、吐出弁３１が形成された吐出弁シート３２と、この吐出弁シート３２に重ね合わせられ、弁板３とシリンダヘッド４との間に挟持固定されると共に、吐出弁３１と対向する部位にリテーナ３５が一体に形成されたガスケット３６とが設けられている。   Further, between the valve plate 3 and the cylinder head 4, a discharge valve seat 32 on which a discharge valve 31 is formed, which is mounted on the cylinder head side end surface of the valve plate 3, A gasket 36, which is superposed and fixed between the valve plate 3 and the cylinder head 4 and is fixed to the discharge valve 31, is provided with a retainer 35 integrally therewith.

前記シリンダブロック２、ガスケット２６、吸入弁シート２２、弁板３、吐出弁シート３２、ガスケット３６、及びシリンダヘッド４は、図示しない位置決めピンによって位置決めされ、前記ハウジング７の構成部材を締結する前記締結ボルトにより圧接された状態で固定されている。   The cylinder block 2, the gasket 26, the suction valve seat 22, the valve plate 3, the discharge valve seat 32, the gasket 36, and the cylinder head 4 are positioned by positioning pins (not shown), and fasten the components of the housing 7. It is fixed in a state of being pressed by bolts.

なお、吸入室１８は、吐出室１９を貫通するように径方向に延設された吸入通路を介して外部冷媒回路の低圧側（蒸発器の出口側）に接続される図示しない吸入口と連通し、吐出室１９は、ガスケット３４や弁板３、吸入弁シート２２、ガスケット２３、及びシリンダブロック２に形成された通路を介してシリンダブロック２の周壁部に形成された吐出空間４１に連通している。この吐出空間４１は、シリンダブロック２とこれに取り付けられたカバー４２とによって画成され、カバー４２に形成された吐出口４３を介して外部冷媒回路の高圧側（放熱器の入口側）に接続されている。   The suction chamber 18 communicates with a suction port (not shown) connected to the low-pressure side (outlet side of the evaporator) of the external refrigerant circuit via a suction passage extending radially through the discharge chamber 19. The discharge chamber 19 communicates with the gasket 34, the valve plate 3, the suction valve seat 22, the gasket 23, and a discharge space 41 formed in a peripheral wall of the cylinder block 2 through a passage formed in the cylinder block 2. ing. The discharge space 41 is defined by the cylinder block 2 and a cover 42 attached to the cylinder block 2, and is connected to a high pressure side (an inlet side of a radiator) of an external refrigerant circuit via a discharge port 43 formed in the cover 42. Have been.

吸入弁シート２２は、図２（ａ）に示される弁板３のシリンダブロック側の端面に重ね合わせて取り付けられ、図２（ｂ）に示されるように、前記吸入ポート２０を開閉する複数の吸入弁２１の集合体からなるもので、この吸入弁シート２２には、シリンダボア１２の数に合わせて吸入弁２１が周方向に所定の間隔で形成され、また、締結ボルトを挿通するための通孔や図示しない位置決めピンを挿通するための通孔等が形成されている。また、それぞれの吸入弁２１の基端部には、前記吐出ポート３０との干渉を避ける開口部２５が形成されている。   The suction valve seat 22 is attached to the cylinder block side end surface of the valve plate 3 shown in FIG. 2A so as to overlap with each other, and as shown in FIG. The suction valve 21 is formed of a set of suction valves 21, and the suction valves 21 are formed at predetermined intervals in the circumferential direction in accordance with the number of the cylinder bores 12. Holes, through holes for inserting positioning pins (not shown), and the like are formed. At the base end of each suction valve 21, an opening 25 is formed to avoid interference with the discharge port 30.

それぞれの吸入弁２１は、吸入弁シート２２の一部で構成されているもので、この実施形態ではリード弁が用いられている。吸入弁２１は、腕部２３の先端の部位を弁板３の吸入ポート２０の周囲に形成された弁座２７に着座するシート部としている。吸入弁２１のより詳細な構造については後述する。   Each of the suction valves 21 is constituted by a part of a suction valve seat 22, and in this embodiment, a reed valve is used. The suction valve 21 has a distal end portion of the arm portion 23 as a seat portion seated on a valve seat 27 formed around the suction port 20 of the valve plate 3. A more detailed structure of the suction valve 21 will be described later.

なお、吸入弁シート２２とシリンダブロック２との間に介在されるガスケット２６は、シリンダボア１２との干渉を避ける開口部がシリンダボア１２の数に合わせて周方向に所定の間隔で形成され、また、締結ボルトを挿通するための通孔や位置決めピンを挿通するための通孔等が形成されている。   In the gasket 26 interposed between the suction valve seat 22 and the cylinder block 2, openings for avoiding interference with the cylinder bore 12 are formed at predetermined circumferential intervals in accordance with the number of the cylinder bores 12, and A through hole for inserting a fastening bolt, a through hole for inserting a positioning pin, and the like are formed.

吐出弁シート３２は、図４（ａ）に示される弁板３のシリンダヘッド側の端面に重ね合わせて取り付けられ、図４（ｂ）に示されるように、吐出ポート３０を開閉する複数の吐出弁３１の集合体によって構成される。吐出弁３１は、シリンダボア１２の数に合わせて周方向に所定の間隔で形成されている。また、吐出弁シート３２には、吸入ポート２０との干渉を避ける開口部３９と、位置決めピンを挿通するための図示しない通孔等が形成されている。   The discharge valve sheet 32 is attached to the cylinder head side end surface of the valve plate 3 shown in FIG. 4A so as to overlap with the plurality of discharge ports for opening and closing the discharge port 30 as shown in FIG. 4B. It is constituted by an assembly of valves 31. The discharge valves 31 are formed at predetermined intervals in the circumferential direction in accordance with the number of the cylinder bores 12. The discharge valve seat 32 has an opening 39 for avoiding interference with the suction port 20, and a not-shown through hole for inserting a positioning pin.

それぞれの吐出弁３１は、吐出弁シート３２の一部で構成されているもので、この実施形態では、外方に向けて放射状に延出した腕部３３を有するリード弁として形成され、腕部３３の先端の部位を弁板３の吐出ポート３０の周囲に形成された弁座３７に着座するシート部としている。   Each discharge valve 31 is constituted by a part of the discharge valve seat 32, and in this embodiment, is formed as a reed valve having an arm portion 33 extending radially outward, The distal end portion of 33 is a seat portion that sits on a valve seat 37 formed around the discharge port 30 of the valve plate 3.

なお、吐出弁シート３２とシリンダヘッド４との間に介在されるガスケット３６は、吸入ポート２０との干渉を避ける開口部がシリンダボアの数に合わせて周方向に所定の間隔で形成され、また、締結ボルトを挿通するための通孔や位置決めピンを挿通するための通孔等が形成され、吐出弁３１と対峙する箇所に、吐出弁３１の腕部３３の付根側から先端側にかけて徐々に離れるようにリテーナ３５が一体に形成されている。   In the gasket 36 interposed between the discharge valve seat 32 and the cylinder head 4, openings for avoiding interference with the suction port 20 are formed at predetermined circumferential intervals in accordance with the number of cylinder bores. A through hole for inserting a fastening bolt, a through hole for inserting a positioning pin, and the like are formed, and gradually separate from a root side to a tip side of the arm portion 33 of the discharge valve 31 at a position facing the discharge valve 31. Thus, the retainer 35 is formed integrally.

したがって、吸入行程時においては、吸入弁２１によって開閉される吸入ポート２０を介して吸入室１８から圧縮室１７に冷媒を吸引し、圧縮行程時においては、吐出弁３１によって開閉される吐出ポート３０を介して圧縮された冷媒を圧縮室１７から吐出室１９へ吐出するようにしている。   Therefore, during the suction stroke, refrigerant is sucked from the suction chamber 18 into the compression chamber 17 via the suction port 20 opened and closed by the suction valve 21, and during the compression stroke, the discharge port 30 opened and closed by the discharge valve 31 The compressed refrigerant is discharged from the compression chamber 17 to the discharge chamber 19 through the compression chamber 17.

ところで、吸入弁２１は、特に図６から図８に示されるように、外側形状と内側形状とで舌状を成す腕部２３を有して構成されている、   Incidentally, the suction valve 21 is configured to have a tongue-shaped arm portion 23 with an outer shape and an inner shape, as shown in particular in FIGS. 6 to 8.

腕部２３の外側形状は、先端部２４ａ、１対の根本部２４ｃと２４ｃ、先端部２４ａと根本部２４ｃとの間の１対の中間部２４ｂと２４ｂから成るＵ字状のスリット部２４を吸入弁シート２２に設けることで形成されている。   The outer shape of the arm portion 23 includes a U-shaped slit portion 24 including a tip portion 24a, a pair of root portions 24c and 24c, and a pair of intermediate portions 24b and 24b between the tip portion 24a and the root portion 24c. It is formed by providing the suction valve seat 22.

スリット部２４の１対の中間部２４ｂと２４ｂは、短手方向の隙間の幅Ｈ１が例えば２ｍｍの幅にて一定に形成されており、更にこの実施形態では直線状に延びている。スリット部２４の先端部２４ａは、この実施形態では短手方向の隙間の幅Ｈ２が例えば１．６ｍｍから１．７ｍｍの幅にて一定に形成されている。中間部２４ｂと先端部２４ａとの境界部位では、短手方向の一方の隙間の幅が一方の隙間の幅に成るように徐々に拡がり或いは狭まっている。１対の根本部２４ｃと２４ｃは、円形状に形成されることで、かかる根本部２４ｃの円形状の溝の中心点Ｐ１を通る隙間の幅Ｈ３が上記した先端部２４ａ及び中間部の短手方向の隙間の幅Ｈ１、Ｈ２のいずれよりも大きくなっている。   In the pair of intermediate portions 24b and 24b of the slit portion 24, the width H1 of the gap in the short direction is formed to be constant at a width of, for example, 2 mm, and further extends linearly in this embodiment. In this embodiment, the distal end portion 24a of the slit portion 24 is formed such that the width H2 of the gap in the short direction is constant, for example, from 1.6 mm to 1.7 mm. At the boundary portion between the intermediate portion 24b and the tip portion 24a, the width of one gap in the short direction gradually expands or narrows so as to be equal to the width of one gap. The pair of roots 24c and 24c are formed in a circular shape so that the width H3 of the gap passing through the center point P1 of the circular groove of the root 24c is shorter than the width of the tip 24a and the intermediate part. The width of the gap in the direction is larger than both of the widths H1 and H2.

腕部２３の内側形状は、吸入弁シート２２のスリット部２４の一方の中間部２４ｂ、根本部２４ｃと他方の中間部２４ｂ、根本部２４ｃとの間に、吸入弁シート２２の周縁近傍からシリンダボア１２の中心点Ｐ２側に向けて延びる長孔状の開口部２５を設けることで形成されている。   The inner shape of the arm portion 23 is such that the cylinder bore extends from the vicinity of the peripheral edge of the suction valve seat 22 between the intermediate portion 24b and the root portion 24c of the slit portion 24 of the suction valve seat 22 and the other intermediate portion 24b and the root portion 24c. It is formed by providing a slot-like opening 25 extending toward the center point P2 side of the twelve.

このような吸入弁２１の腕部２３において、スリット部２４の１対の根本部２４ｃと２４ｃの、１対の中間部２４ｂと２４ｂが先端部２４ａに向けて延びる方向とは反対側の端を通る腕部の幅方向の基準線Ｌ１の位置が、吸入弁２１の付根になり、付根とはシリンダボア１２の中心点Ｐ２を間にして反対側の端が先端となる。   In the arm 23 of the suction valve 21, the end of the pair of roots 24 c and 24 c of the slit 24 opposite to the direction in which the pair of intermediate portions 24 b and 24 b extends toward the tip 24 a is formed. The position of the reference line L1 in the width direction of the passing arm portion is the root of the suction valve 21, and the end on the opposite side of the center point P2 of the cylinder bore 12 is the tip.

そして、腕部２３の外側形状のうちスリット部２４の中間部２４ｂに重なる腕部の外側基準線Ｌ２及び、腕部２３の内側形状のうち開口部２５の短手方向で向かい合う縁辺に重なる腕部の内側基準線Ｌ３は、それぞれシリンダボア１２の中心点Ｐ２及び吸入ポート２０の中心点Ｐ３の双方を通る腕部の中心線Ｌ４と交差するように傾斜している。なお、腕部の中心線Ｌ４は、この実施形態では吐出ポート３０の中心点Ｐ４も通っている。   The outer reference line L2 of the arm portion overlapping the middle portion 24b of the slit portion 24 in the outer shape of the arm portion 23, and the arm portion overlapping the edge of the inner shape of the arm portion 23 facing the opening portion 25 in the short direction. Are inclined so as to intersect with the center line L4 of the arm passing through both the center point P2 of the cylinder bore 12 and the center point P3 of the suction port 20, respectively. The center line L4 of the arm also passes through the center point P4 of the discharge port 30 in this embodiment.

これにより、吸入弁２１の腕部２３は付根側の幅が先端側の幅よりも広くなっている。更には、外側基準線Ｌ２の中心線Ｌ４からの傾斜角度Ｒ１が内側基準線Ｌ３の中心線Ｌ４からの傾斜角度Ｒ２よりも所定値以上大きくなっている。この傾斜角度の差の所定値は、８度以上であることが望ましい。   Accordingly, the width of the arm portion 23 of the suction valve 21 on the root side is wider than the width on the tip side. Furthermore, the inclination angle R1 of the outer reference line L2 from the center line L4 is larger than the inclination angle R2 of the inner reference line L3 from the center line L4 by a predetermined value or more. It is desirable that the predetermined value of the difference between the inclination angles is 8 degrees or more.

また、スリット部２４の根本部２４ｃの中間部２４ｂとは反対側の端から前記中心線Ｌ４までの腕部の幅方向寸法Ｗ１と、前記腕部の幅方向の基準線Ｌ１と前記中心線Ｌ４とが交差する位置Ｃ１から前記中心線Ｌ４の腕部２３の先端側の端までの腕部の長さ方向寸法Ｗ２とを対比して、長さ方向寸法Ｗ２が幅方向寸法Ｗ１よりも大きいが近似したものとなっている。腕部２３の幅方向寸法Ｗ１と長さ方向寸法Ｗ２との対比は、１：１．８以下であることが望ましい。これに伴い、腕部２３の付根の位置は、前記シリンダボアの中心点Ｐ２よりも吐出ポート３０側であるが当該シリンダボアの中心点Ｐ２に近接、すなわちシリンダボアの中心Ｐ２に従来の吸入弁よりも寄ったものとなっている。   Further, a width direction dimension W1 of the arm from the end opposite to the intermediate portion 24b of the root portion 24c of the slit portion 24 to the center line L4, a reference line L1 in the width direction of the arm and the center line L4 The length dimension W2 is larger than the width dimension W1 in comparison with the length dimension W2 of the arm from the position C1 where the intersection C1 intersects with the end of the arm 23 on the center line L4. It is an approximation. It is desirable that the contrast between the width dimension W1 and the length dimension W2 of the arm portion 23 is 1: 1.8 or less. Accordingly, the position of the root of the arm 23 is closer to the discharge port 30 than the center point P2 of the cylinder bore, but closer to the center point P2 of the cylinder bore, that is, closer to the center P2 of the cylinder bore than the conventional suction valve. It has become.

このように、吸入弁２１の腕部２３の外側形状と内側形状とについて、外側基準線Ｌ２の傾斜角度Ｒ１を内側基準線Ｌ３の傾斜角度Ｒ２よりも８度以上の大きさとなるように設定することにより、外側形状と内側形状との間の幅が付根側と先端側とで変わらない場合や、腕部２３の付根側が先端側よりも広がっていても傾斜角度Ｒ１とＲ２との差が８度よりも小さい場合に比し、吸入弁２１の腕部２３の付根の剛性を向上させ、腕部２３をしなり難くすることが可能となる。   In this manner, the outer shape and the inner shape of the arm portion 23 of the suction valve 21 are set such that the inclination angle R1 of the outer reference line L2 is at least 8 degrees greater than the inclination angle R2 of the inner reference line L3. Thereby, even if the width between the outer shape and the inner shape does not change between the root side and the distal end side, or the difference between the inclination angles R1 and R2 is 8 even if the root side of the arm portion 23 is wider than the distal side. The rigidity of the base of the arm 23 of the suction valve 21 can be improved as compared with the case where the degree is smaller than the degree, and the arm 23 can be made hard to bend.

そして、吸入弁２１の腕部２３の長さ方向寸法Ｗ２と幅方向寸法Ｗ１とを、１．８：１以下に設定して、吸入弁２１の腕部２３の長さ方向寸法Ｗ２を幅方向寸法Ｗ１より長いが近似させるようにした。これによっても、腕部２３の長さ方向寸法Ｗ２と幅方向寸法Ｗ１との長さの対比が１．８：１よりも大きい場合に比し、吸入弁２１の腕部２３の付根の剛性を向上させ、腕部２３をしなり難くすることが可能となる。   Then, the length dimension W2 and the width dimension W1 of the arm 23 of the suction valve 21 are set to 1.8: 1 or less, and the length dimension W2 of the arm 23 of the suction valve 21 is set in the width direction. It is longer than the dimension W1, but is approximated. Also in this case, the rigidity of the root of the arm portion 23 of the suction valve 21 can be reduced as compared with the case where the length ratio of the length direction W2 and the width direction W1 of the arm portion 23 is greater than 1.8: 1. This makes it possible to make the arm portion 23 hard to bend.

これらのことから、本発明の吸入弁２１の構造を適用することにより、吸入弁としてリード弁を用いても吸入ポート２０の開閉速度を遅くすることができるので、吸入弁２１の腕部２３の先端が弁板３や弁座２７に当たる速度、ひいては衝撃を低下させることが可能である。更には、吸入弁２１の腕部２３の先端が弁座２７に接触した後の二次的変形も防止することができる。よって、吸入弁２１の腕部２３の先端の割れ等の破損が防止され、往復動式圧縮機１の高速運転時でも吸入弁２１に対する信頼を確保することが可能になる。   From these facts, by applying the structure of the suction valve 21 of the present invention, the opening and closing speed of the suction port 20 can be reduced even when a reed valve is used as the suction valve. It is possible to reduce the speed at which the tip hits the valve plate 3 and the valve seat 27, and thus the impact. Furthermore, secondary deformation after the tip of the arm 23 of the suction valve 21 contacts the valve seat 27 can also be prevented. Therefore, breakage of the distal end of the arm portion 23 of the suction valve 21 such as a crack is prevented, and reliability of the suction valve 21 can be ensured even during high-speed operation of the reciprocating compressor 1.

１ 往復動式圧縮機
１２ シリンダボア
１７ 圧縮室
１８ 吸入室
１９ 吐出室
２０ 吸入ポート
２１ 吸入弁
２２ 吸入弁シート
２３ 腕部
２４ スリット部
２４ａ 先端部
２４ｂ 中間部
２４ｃ 根本部
２５ 開口部
３０ 吐出ポート
３１ 吐出弁
Ｐ２ シリンダボアの中心点
Ｐ３ 吸入ポートの中心点
Ｌ１ 腕部の幅方向の基準線(腕部の付根)
Ｌ２ 腕部の外側基準線
Ｌ３ 腕部の内側基準線
Ｌ４ 腕部の中心線
Ｒ１ 外側基準線の中心線からの傾斜角度
Ｒ２ 内側基準線の中心線からの傾斜角度
Ｗ１ 腕部の幅方向の寸法
Ｗ２ 腕部の長さ方向の寸法
Ｈ１ スリット部の中間部の短手方向の隙間の幅
Ｈ２ スリット部の先端部の短手方向の隙間の幅
Ｈ３ スリット部の根本部の円形状の溝の中心を通る隙間の幅 DESCRIPTION OF SYMBOLS 1 Reciprocating compressor 12 Cylinder bore 17 Compression chamber 18 Suction chamber 19 Discharge chamber 20 Suction port 21 Suction valve 22 Suction valve seat 23 Arm part 24 Slit part 24a Tip part 24b Intermediate part 24c Root part 25 Opening 30 Discharge port 31 Discharge Valve P2 Center point of cylinder bore P3 Center point of suction port L1 Reference line in width direction of arm (root of arm)
L2 Outer reference line of arm L3 Inner reference line of arm L4 Center line of arm R1 Angle of inclination from center line of outer reference line R2 Angle of inclination from center line of inner reference line W1 Dimension of arm in width direction W2 Length dimension of the arm in the length direction H1 Width of the gap in the short direction at the middle of the slit H2 Width of the gap in the short direction at the tip of the slit H3 Center of the circular groove at the root of the slit The width of the gap through

Claims (5)

出口端がシリンダボア内に形成される圧縮室に開口し、前記出口端が吸入弁により開閉可能に閉塞される吸入ポート、及び、入口端が前記圧縮室に開口し、出口端が吐出弁により開閉可能に閉塞される吐出ポートを有し、前記吸入弁にリード弁が用いられた往復動式圧縮機において、
前記吸入弁は、舌状の腕部を有し、前記腕部の外側形状は、１つの先端部、１対の根本部、前記先端部と前記根本部との間の１対の中間部から成るスリット部を吸入弁シートに設けることで形成され、前記腕部の内側形状は、前記吸入弁シートの前記スリット部の一方の中間部と根本部、他方の中間部と根本部との間に、前記吸入弁シートの周縁近傍から前記シリンダボアの中心点側に向けて延びる長孔状の開口部を設けることで形成され、
前記外側形状の前記スリット部の中間部に重なる外側基準線及び前記内側形状の前記開口部の短手方向で向かい合う縁辺に重なる内側基準線を、それぞれ前記シリンダボアの中心点及び前記吸入ポートの中心点の双方を通る腕部の中心線と交差するように傾斜させることにより、前記腕部は付根側の幅が先端側の幅よりも広くなっており、
更に、前記外側基準線の傾斜角度が前記内側基準線の傾斜角度よりも所定値以上大きくなっていることを特徴とする往復動式圧縮機の吸入弁構造。 An outlet end opens into a compression chamber formed in the cylinder bore, a suction port whose outlet end is opened and closed by a suction valve, and an inlet end opens into the compression chamber and an outlet end opens and closes by a discharge valve. In a reciprocating compressor having a discharge port that is closed as possible, and a reed valve is used as the suction valve,
The suction valve has a tongue-shaped arm portion, and the outer shape of the arm portion is formed from one tip, a pair of roots, and a pair of intermediate portions between the tip and the root. Is formed by providing a slit portion formed in the suction valve seat, and the inner shape of the arm portion is formed between one intermediate portion and the root portion of the slit portion of the suction valve seat, and between the other intermediate portion and the root portion. , Formed by providing a slot-shaped opening extending from the vicinity of the peripheral edge of the suction valve seat toward the center point of the cylinder bore,
A center point of the cylinder bore and a center point of the suction port are defined as an outer reference line overlapping the middle portion of the slit portion of the outer shape and an inner reference line overlapping the edge of the inner shape facing the opening in the short direction. By inclining so as to intersect with the center line of the arm that passes through both, the width of the arm at the base is wider than the width at the tip,
Further, the inclination angle of the outer reference line is larger than the inclination angle of the inner reference line by a predetermined value or more. 入出口端がシリンダボア内に形成される圧縮室に開口し、前記出口端が吸入弁により開閉可能に閉塞される吸入ポート、及び、入口端が前記圧縮室に開口し、出口端が吐出弁により開閉可能に閉塞される吐出ポートを有し、前記吸入弁にリード弁が用いられた往復動式圧縮機において、
前記吸入弁は、舌状の腕部を有し、前記腕部の外側形状は、１つの先端部、１対の根本部、前記先端部と前記根本部との間の１対の中間部から成るスリット部を吸入弁シートに設けることで形成され、前記腕部の内側形状は、前記吸入弁シートの前記スリット部の一方の中間部と根本部、他方の中間部と根本部との間に、前記吸入弁シートの周縁近傍から前記シリンダボアの中心点側に向けて延びる長孔状の開口部を設けることで形成され、
前記腕部は、前記スリット部の根本部の前記中間部とは反対側の端から前記シリンダボアの中心点及び前記吸入ポートの中心点の双方を通る腕部の中心線までの幅方向寸法と、前記スリット部の双方の根本部の前記中間部とは反対側の端を通る基準線と前記中心線とが交差する位置から前記中心線の前記腕部の先端側の端までの長さ方向寸法とを対比して、前記長さ方向寸法が前記幅方向寸法よりも長いが近似していることを特徴とする往復動式圧縮機の吸入弁構造。 An inlet / outlet end opens to a compression chamber formed in the cylinder bore, a suction port whose outlet end is openably closed by a suction valve, and an inlet end opens to the compression chamber, and an outlet end is opened by a discharge valve. In a reciprocating compressor having a discharge port that is openably and closably closed, wherein a reed valve is used as the suction valve,
The suction valve has a tongue-shaped arm portion, and the outer shape of the arm portion is formed from one tip, a pair of roots, and a pair of intermediate portions between the tip and the root. Is formed by providing a slit portion formed in the suction valve seat, and the inner shape of the arm portion is formed between one intermediate portion and the root portion of the slit portion of the suction valve seat, and between the other intermediate portion and the root portion. , Formed by providing a slot-shaped opening extending from the vicinity of the peripheral edge of the suction valve seat toward the center point of the cylinder bore,
The arm portion has a width direction dimension from an end of the root portion of the slit portion opposite to the intermediate portion to a center line of the arm portion passing through both the center point of the cylinder bore and the center point of the suction port, The length dimension from the position where the reference line passing through the end opposite to the intermediate part of both roots of the slit part and the center line intersects to the end of the center line on the tip side of the arm part Wherein the length dimension is longer than, but approximated to, the width dimension of the reciprocating compressor. 前記スリット部は、前記先端部及び前記中間部の短手方向の隙間の幅が所定の数値にて一定又は略一定に形成され、前記根本部が円形状に形成されることにより、前記根本部の隙間の幅が前記先端部及び前記中間部の短手方向の隙間の幅よりも大きいことを特徴とする請求項１又は請求項２に記載の往復動式圧縮機の吸入弁構造。   The slit portion is formed such that a width of a gap in the lateral direction between the tip portion and the intermediate portion is formed to be constant or substantially constant at a predetermined numerical value, and the root portion is formed in a circular shape, whereby the root portion is formed. 3. The suction valve structure of a reciprocating compressor according to claim 1, wherein the width of the gap is larger than the width of the gap in the short direction between the front end portion and the intermediate portion. 4. 前記腕部は、前記スリット部の双方の根本部の前記中間部とは反対側の端を通る基準線と前記中心線とが交差する位置が前記シリンダボアの中心点に近接していることを特徴とする請求項１から請求項３のいずれかに記載の往復動式圧縮機の吸入弁構造。   The arm portion is characterized in that a position where a reference line passing through an end opposite to the intermediate portion of both root portions of the slit portion and the center line intersects is close to a center point of the cylinder bore. The suction valve structure for a reciprocating compressor according to any one of claims 1 to 3. 請求項１から請求項４のいずれかに記載の吸入弁構造を有することを特徴とする往復動式圧縮機。   A reciprocating compressor having the suction valve structure according to any one of claims 1 to 4.
JP2018115093A 2018-06-18 2018-06-18 Suction valve structure for reciprocating compressor, and reciprocating compressor Withdrawn JP2019218879A (en)

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EP19180356.8A EP3584440A3 (en) 2018-06-18 2019-06-14 Reciprocating compressor suction valve structure and reciprocating compressor

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JPWO2007029366A1 (en) * 2005-09-07 2009-03-12 株式会社ヴァレオサーマルシステムズ Reciprocating compressor
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