JP4694956B2 - Hermetic compressor - Google Patents

Hermetic compressor Download PDF

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JP4694956B2
JP4694956B2 JP2005353128A JP2005353128A JP4694956B2 JP 4694956 B2 JP4694956 B2 JP 4694956B2 JP 2005353128 A JP2005353128 A JP 2005353128A JP 2005353128 A JP2005353128 A JP 2005353128A JP 4694956 B2 JP4694956 B2 JP 4694956B2
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hermetic compressor
ball
piston
connecting rod
treatment
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JP2007154806A (en
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昌一 中島
博 高安
真一 佐藤
元 紺野
健二 別役
務 野崎
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Hitachi Appliances Inc
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Hitachi Appliances Inc
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Priority to KR1020060122691A priority patent/KR100822508B1/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
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • 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
    • F04B39/0005—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 adaptations of pistons
    • 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
    • F04B39/0005—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 adaptations of pistons
    • F04B39/0022—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 adaptations of pistons piston rods
    • 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
    • F04B39/0094—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 crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2230/00—Manufacture
    • F05B2230/20—Manufacture essentially without removing material
    • F05B2230/22—Manufacture essentially without removing material by sintering
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2230/00—Manufacture
    • F05B2230/90—Coating; Surface treatment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/30—Arrangement of components
    • F05B2250/33—Arrangement of components symmetrical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2280/00—Materials; Properties thereof
    • F05B2280/10—Inorganic materials, e.g. metals
    • F05B2280/107—Alloys
    • F05B2280/1071—Steel alloys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2280/00—Materials; Properties thereof
    • F05B2280/50—Intrinsic material properties or characteristics
    • F05B2280/5007—Hardness

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Description

本発明は、冷蔵庫、エアコン等に用いられる密閉形圧縮機に関し、特に、往復運動するピストンを有する密閉形圧縮機に関する。   The present invention relates to a hermetic compressor used for a refrigerator, an air conditioner, and the like, and more particularly to a hermetic compressor having a reciprocating piston.

従来、圧縮機のピストンとコンロッドにボールジョイント構造としては特開２００３−２１４３４３号公報（特許文献１）のように、窒化処理及び燐酸マンガン処理を球面受け穴（ボール受け穴）やボールの両方もしくは一方に施し、球面に高炭素クロム鋼材を使用した構造が知られている。   Conventionally, as a ball joint structure for a piston and a connecting rod of a compressor, as disclosed in Japanese Patent Application Laid-Open No. 2003-214343 (Patent Document 1), nitriding treatment and manganese phosphate treatment are performed on both spherical receiving holes (ball receiving holes) and balls, or A structure using a high carbon chrome steel material on a spherical surface is known.

特開２００３−２１４３４３号公報JP 2003-214343 A

しかしながら、特許文献１の構造では次のような課題があった。   However, the structure of Patent Document 1 has the following problems.

特許文献１の連結構造では、球面に使用する高炭素クロム鋼材の硬度が高く、加工が難しい。また、ボールジョイント機構、すなわち球面軸受（ボールとボール受け穴）に供給される潤滑油の通路はピストンをシリンダから引き抜く時にはピストンとシリンダの接触部となり、潤滑油の通路となる隙間は狭められる。   In the connection structure of Patent Document 1, the hardness of the high-carbon chromium steel used for the spherical surface is high and processing is difficult. Further, the passage of the lubricating oil supplied to the ball joint mechanism, that is, the spherical bearing (ball and ball receiving hole) becomes a contact portion between the piston and the cylinder when the piston is pulled out from the cylinder, and the gap serving as the passage of the lubricating oil is narrowed.

この隙間を通してでは潤滑油が十分に流れない可能性があり、そのため球面軸受（ボールとボール受け穴）の温度が上昇し、損傷する可能性がある。   Through this gap, there is a possibility that the lubricating oil does not flow sufficiently, so that the temperature of the spherical bearing (ball and ball receiving hole) rises and may be damaged.

また、密閉形圧縮機は、容器、すなわちチャンバが内部機構挿入後に溶接により密閉される。   In the hermetic compressor, the container, that is, the chamber is sealed by welding after the internal mechanism is inserted.

これにより、不可避的に溶接時の溶融飛沫、すなわちスパッタ粒子が容器内に混入・残存する。残存するスパッタ粒子が循環する潤滑油に混入し、摺動部に侵入すると摺動部品の表面を傷つけ、カジリを発生して摩耗や固着に至ることがわかっている。   As a result, inevitably molten droplets at the time of welding, that is, sputtered particles are mixed and remain in the container. It has been found that if the remaining sputtered particles are mixed into the circulating lubricating oil and enter the sliding part, the surface of the sliding part is damaged and galling occurs, leading to wear and sticking.

さらに各摺動面で発生する摩耗粉も潤滑油に混入し、特にボールジョイント部などの狭い摺動部に進入するとスパッタ粒子と同様、摩耗や固着に至り、圧縮機の信頼性を著しく低下させる。   In addition, wear powder generated on each sliding surface is mixed into the lubricating oil, and especially when entering a narrow sliding part such as a ball joint, it leads to wear and sticking like sputtered particles, which significantly reduces the reliability of the compressor. .

本発明は、上記従来の課題を解決しようとするもので、ピストンとロッドを球面軸受により連結し、かつ、潤滑油を十分に供給し、かつ、耐摩耗性の高い材料を使用することで圧縮機の能力及び信頼性を向上することを目的とする。   The present invention is intended to solve the above-described conventional problems. The piston and the rod are connected by a spherical bearing, the lubricant is sufficiently supplied, and the material is compressed by using a material having high wear resistance. The purpose is to improve the capability and reliability of the machine.

本発明は、ピストンに連結されるコンロッドを有し、コンロッドに設けたボールとピストンに設けたボール受け穴とが回動する摺動自在にボールジョイントされ、このボールジョイントの摺動部に潤滑油の供給が行なわれる密閉形圧縮機にあって、ピストン、コンロッドの一方が鉄を主成分とする合金材であり、他方の材料が前記鉄を主成分とする合金材の表面層の硬度よりも高硬度化であることを特徴とする。   The present invention has a connecting rod connected to a piston, and is slidably ball jointed so that a ball provided on the connecting rod and a ball receiving hole provided on the piston rotate. In which the piston and the connecting rod are made of an alloy material mainly composed of iron, and the other material is harder than the hardness of the surface layer of the alloy material composed mainly of iron. It is characterized by high hardness.

本発明によれば、ボールジョイント部の摩耗を低減することができ、信頼性の高い圧縮機とすることができる。   ADVANTAGE OF THE INVENTION According to this invention, wear of a ball joint part can be reduced and it can be set as a reliable compressor.

さらに、本発明を具体的に説明する。   Further, the present invention will be specifically described.

本発明は、ピストン、コンロッドの一方が鉄を主成分とする合金材であり、他方の材料が前記鉄を主成分とする合金材ビッカース硬度において１．５倍以上の硬度であることを特徴とする。   The present invention is characterized in that one of the piston and the connecting rod is an alloy material whose main component is iron, and the other material is 1.5 times or more in the Vickers hardness of the alloy material whose main component is iron. To do.

さらに本発明においては、ボールジョイント部に設けたコンロッドの内部を通る給油口を通して潤滑油を供給し、ピストンとコンロッドの接触面（ボールとボール受け穴）に油膜を形成することで摩擦力を低減し、また効率を向上させ、油膜により該ピストンとコンロッドの固体接触を低減させて摩耗信頼性を向上させることができる。   Furthermore, in the present invention, the lubricating oil is supplied through an oil supply port passing through the inside of the connecting rod provided in the ball joint portion, and the friction force is reduced by forming an oil film on the contact surface (ball and ball receiving hole) of the piston and connecting rod. In addition, the efficiency can be improved and the solid contact between the piston and the connecting rod can be reduced by the oil film, thereby improving the wear reliability.

また、ピストン側はボール受け穴の内球面の成形性を良くするために鉄系の焼結材であることが望ましい。一方、コンロッドはボールの外球面の成形・加工および給油口を形成するために焼結材であることが望ましいが、摩耗耐久性を勘案した組み合わせにおいては溶製材も適用することができる。   The piston side is preferably an iron-based sintered material in order to improve the formability of the inner spherical surface of the ball receiving hole. On the other hand, the connecting rod is preferably a sintered material in order to form and process the outer spherical surface of the ball and to form an oil supply port. However, a melted material can also be applied in a combination considering wear durability.

鉄系焼結材はクランクピンからの回転力を往復動として気体を圧縮するためにピストンまたはコンロッドあるいは両方に十分な強度を持たせる必要があり、該鉄系焼結材の密度は６．６ｇ／ｃｍ３以上とする。 The iron-based sintered material needs to have sufficient strength in the piston or connecting rod or both in order to compress the gas by reciprocating the rotational force from the crankpin, and the density of the iron-based sintered material is 6.6 g. / Cm 3 or more.

給油を十分に行い、油膜を有効に形成するために、ボールジョイントの組み合わせに用いる焼結材はさらに高密度としなければならない。   In order to sufficiently supply the oil and effectively form the oil film, the sintered material used for the combination of the ball joints must have a higher density.

原料粉の焼結後に適宜形状を加工し水蒸気処理をすることで内部及び表面の空孔を空孔表面に生成する酸化物膜により封孔し、潤滑油膜が空孔を通して容易に排出されないようにする。水蒸気処理による封孔部の酸化物は、焼結材の強度を向上させるとともに凝着摩耗を防止する効果もある。   After sintering the raw material powder, the shape is appropriately processed and water vapor treated to seal the internal and surface vacancies with the oxide film generated on the vacancy surface, so that the lubricating oil film is not easily discharged through the vacancies To do. The oxide in the sealing portion by the steam treatment has an effect of improving the strength of the sintered material and preventing adhesive wear.

冷媒圧縮の運転条件によっては一時的にボールジョイント部に高い荷重が加わることがあるため、摩擦面に固体接触が生じても同種材同士の接触にならないように、一方の表面を窒化あるいは硫化物化あるいはこれらの混合層として異種材化する。   Depending on the operating conditions of refrigerant compression, a high load may be temporarily applied to the ball joint, so even if solid contact occurs on the friction surface, one surface is nitrided or sulfided to prevent contact between similar materials. Alternatively, these mixed layers are formed into different materials.

摺動部（ボールとボール受け穴）に供給する潤滑油には圧縮機内で使用開始時の馴染み運転や一時的高負荷運転により生成された摩耗粉粒子や、チャンバ密封時のスパッタ粒子が混入する。摩耗粉は軟らかい側の材料において、摺動部（ボールとボール受け穴）表面の加工硬化層が脱落あるいは、脱落した摩耗粉は摺動面の隙間で変形させられるためその硬さは素の材料の１．５倍から２倍となる。   Lubricating oil supplied to the sliding part (ball and ball receiving hole) is mixed with wear powder particles generated during familiar operation or temporary high-load operation in the compressor and sputter particles when the chamber is sealed. . The wear powder is a soft material, and the work hardened layer on the surface of the sliding part (ball and ball receiving hole) falls off, or the fallen wear powder is deformed in the gap of the sliding surface, so its hardness is a raw material 1.5 times to 2 times.

摺動部（ボールとボール受け穴）において、より硬い方の表面硬さを軟らかい側の１．５倍以上にすることにより、硬い方の材料の表面荒れを防止し、摩耗粉が軟らかい材料の表面を変形させながら転動あるいは潤滑油により押し流されて摩擦面外に排出することができる。   In the sliding part (ball and ball receiving hole), by making the surface hardness of the harder one 1.5 times that of the softer side, the surface of the harder material is prevented from roughening and the wear powder is softer. While the surface is deformed, it can be swept away by rolling or lubricating oil and discharged out of the friction surface.

また摩耗粉の排出後には硬い方の材料表面形状に軟らかい方の材料が馴染んで摩耗粉形成・排出前の滑らかな形状に類似した表面に復旧することができる。   In addition, after the wear powder is discharged, the softer material is adapted to the hard material surface shape, and the surface can be restored to a smooth shape before the formation and discharge of the wear powder.

定常運転時の摺動部（ボールとボール受け穴）の隙間は最大１０ミクロンメートル以下にすることが圧縮効率を向上させる上で有効であり、概隙間に生成もしくは潤滑油とともに侵入する粒子の大きさは約１０ミクロン以下となることから、硬い方の材料が転動する粒子により変形・摩耗されないように、表面粒子の大きさに比較して２倍以上の深さまで表面拡散処理の有効深さを確保する。   It is effective to improve the compression efficiency that the gap between the sliding parts (ball and ball receiving hole) during steady operation is 10 microns or less at maximum, and the size of particles generated in the gap or entering with the lubricating oil Since the thickness is about 10 microns or less, the effective depth of the surface diffusion treatment is more than double the size of the surface particles so that the harder material is not deformed or worn by the rolling particles. Secure.

スパッタ粒子はチャンバ溶接時に溶融した鉄製のチャンバ材が空間で再度凝固したもので、ほぼ球形でビッカース硬さは約８００に達するものもある。溶接方法の改善や給油経路にフィルターを設けることもできるが、フィルターは給油効率を下げ潤滑を悪化させる場合もある。したがって、スパッタ粒子によるボールジョイント部の損耗を防止するために、さらに硬い方の硬度を向上させることが有効である。   The sputtered particles are made of iron chamber material melted at the time of chamber welding and solidified again in the space. Some of the sputtered particles are almost spherical and have a Vickers hardness of about 800. Although it is possible to improve the welding method and provide a filter in the oil supply path, the filter may lower the oil supply efficiency and deteriorate the lubrication. Therefore, it is effective to improve the hardness of the harder one in order to prevent wear of the ball joint portion due to the sputtered particles.

鉄系の材料は焼入れにより硬くし、耐摩耗性を向上させることができるが、表面は金属質であり鉄系焼結材と組み合わせた場合に相手材との凝着を起こしやすい。さらに表面を窒化あるいは浸炭することで硬度を増し、さらに非金属化し、相手材との凝着や摩耗粉による変形・摩耗を防止する。非金属化には硫化物処理も有効である。適宜これら拡散処理を組み合わせても良い。拡散処理では、焼入れ後の内部硬度を保つために、拡散処理温度以上の温度で焼き戻しできることが必要である。   Iron-based materials can be hardened by quenching to improve wear resistance, but the surface is metallic, and when combined with an iron-based sintered material, adhesion with the counterpart material is likely to occur. Furthermore, nitriding or carburizing the surface increases the hardness and further makes it non-metallic, preventing deformation and wear due to adhesion with the counterpart material and wear powder. Sulfide treatment is also effective for non-metallization. These diffusion processes may be combined as appropriate. In the diffusion treatment, it is necessary to be able to temper at a temperature equal to or higher than the diffusion treatment temperature in order to maintain the internal hardness after quenching.

本発明の構造に用いる潤滑油は油膜を強固に保持させるために、鉄系焼結材および窒化または浸炭あるいは硫化した表面に良好な吸着力を有するエステル系合成油が有効である。鉱物油とエステル油を混合しても、エステル系の分子が選択的に摺動部表面に付着し固体接触を防止することができる。   As the lubricating oil used in the structure of the present invention, an iron-based sintered material and an ester-based synthetic oil having a good adsorbing force on a nitrided, carburized or sulfided surface are effective in order to hold the oil film firmly. Even if mineral oil and ester oil are mixed, ester-based molecules can selectively adhere to the surface of the sliding portion and solid contact can be prevented.

封孔処理は供給する潤滑油の油膜を保持するために必須である。が、不可避的に残存する空孔に潤滑油が充填されるようにしておくことにより、摩耗が発生し空孔が表面に露呈した場合でも充填された潤滑油が摩耗部の金属接触を防止し、摩耗を防止することができる。   The sealing treatment is essential for retaining the oil film of the lubricating oil to be supplied. However, by unavoidably leaving the remaining holes filled with lubricating oil, even when wear occurs and the holes are exposed on the surface, the filled lubricating oil prevents metal contact of the worn parts. , Can prevent wear.

さらに本発明は、ピストンとコンロッドの連結構造を有する圧縮機において、連結構造（ボールとボール受け穴）が脱落しないボールジョイント機構とし、さらにコンロッド内部から潤滑油を供給する構造とするものである。   Furthermore, the present invention is a compressor having a connecting structure of a piston and a connecting rod, wherein the connecting structure (ball and ball receiving hole) is a ball joint mechanism that does not drop off, and further, a lubricating oil is supplied from the inside of the connecting rod.

本発明によれば、冷媒自体では摩耗防止の効果が発揮できないイソブタン冷媒やＲ１３４ａ等の非塩素冷媒の圧縮に際して有効な密閉形圧縮機となる。   According to the present invention, an airtight compressor is effective when compressing non-chlorine refrigerants such as isobutane refrigerant and R134a that cannot exhibit the effect of preventing wear by the refrigerant itself.

上述の構成により、潤滑性の優れたボールジョイント機構を構成でき、密閉形圧縮機の性能及び信頼性を向上させることが出来る。   With the above configuration, a ball joint mechanism with excellent lubricity can be configured, and the performance and reliability of the hermetic compressor can be improved.

以下、本発明の実施形態をそれぞれ図に基づいて説明する。   Embodiments of the present invention will be described below with reference to the drawings.

図１には、密閉容器内の軸受１ａとフレーム１ｂと一体に成形された圧縮要素のシリンダ１内を、コンロッド２によりクランクシャフト７ａに結合されたピストン４が往復動して圧縮要素を構成する本発明を適用したレシプロ式密閉形圧縮機が示されている。   In FIG. 1, a piston 4 coupled to a crankshaft 7a by a connecting rod 2 reciprocates in a cylinder 1 of a compression element formed integrally with a bearing 1a and a frame 1b in an airtight container to constitute a compression element. A reciprocating hermetic compressor to which the present invention is applied is shown.

フレーム１ａの下部には、電動要素である電動機を構成するステータ５およびロータ６が取り付けられている。ロータ６のロータシャフト７の回転中心より偏心した位置に、クランクシャフト７ａがある。   A stator 5 and a rotor 6 constituting an electric motor as an electric element are attached to the lower part of the frame 1a. The crankshaft 7 a is located at a position eccentric from the rotation center of the rotor shaft 7 of the rotor 6.

このロータシャフト７は、フレーム１の軸受け部１ａに貫通して取り付けられている。このロータシャフト７とロータ６とは直結していて、ロータシャフト７の回転（時計回りに回転するものとする）によって、コンロッド２を介し、ピストン４を往復動させる。   The rotor shaft 7 is attached so as to penetrate the bearing portion 1 a of the frame 1. The rotor shaft 7 and the rotor 6 are directly connected to each other, and the piston 4 is reciprocated through the connecting rod 2 by the rotation of the rotor shaft 7 (which rotates clockwise).

ロータシャフト７のクランクシャフト７ａ、コンロッド２を含めてクランク機構と言う。   The crankshaft including the crankshaft 7a of the rotor shaft 7 and the connecting rod 2 is referred to as a crank mechanism.

圧縮要素のピストンについて図２、図３、図４を用いて詳細に説明する。   The piston of the compression element will be described in detail with reference to FIGS.

図２はピストン４をロータシャフト７から見た内部側を示す図であり、ボール受け部（内球面）４ａを有している。図３は図２のＡ−Ａ断面図である。図４は図２のＢ−Ｂ断面である。   FIG. 2 is a view showing the internal side of the piston 4 as viewed from the rotor shaft 7, and has a ball receiving portion (inner spherical surface) 4a. 3 is a cross-sectional view taken along the line AA in FIG. FIG. 4 is a BB cross section of FIG.

ピストンのボール受け部（内球面）４ａはＡ−Ａ断面ではコンロッド２のボール（外球面）２ａの先端から１８０度以上の角度で包む形状であるが、Ｂ−Ｂ断面では１８０度以下の角度でのみコンロッド２のボール（外球面）２ａを包む形状である。   The ball receiving portion (inner sphere) 4a of the piston is shaped to wrap at an angle of 180 degrees or more from the tip of the ball (outer sphere) 2a of the connecting rod 2 in the AA section, but in the BB section, an angle of 180 degrees or less. It is a shape that encloses the ball (outer spherical surface) 2a of the connecting rod 2 only at.

従って、Ｂ−Ｂ断面ではＡ−Ａ断面よりも摺動面積が少ないボールジョイント構造となり、潤滑油の通る経路が短いため、潤滑油が流れやすく、充分に潤滑油が供給できる構造となる。   Therefore, the ball joint structure having a smaller sliding area than the AA cross section in the BB cross section and the path through which the lubricating oil passes are short, so that the lubricating oil can easily flow and the lubricating oil can be sufficiently supplied.

コンロッドについて図５を用いて説明する。   The connecting rod will be described with reference to FIG.

図５はコンロッド２の斜視図である。コンロッド２はピストン４のボール受け部（内球面）４ａに挿入されるボール（外球面）２ａと、クランクシャフト７ａが挿入されるクランク軸受部２ｂと、ボール（外球面）２ａとクランク軸受部２ｂを繋ぐロッド部２ｃから構成されている。   FIG. 5 is a perspective view of the connecting rod 2. The connecting rod 2 includes a ball (outer spherical surface) 2a inserted into the ball receiving portion (inner spherical surface) 4a of the piston 4, a crank bearing portion 2b into which the crankshaft 7a is inserted, a ball (outer spherical surface) 2a, and the crank bearing portion 2b. It is comprised from the rod part 2c which connects.

給油孔２ｄは、ボール（外球面）２ａ及びロッド部２ｃの内部を貫通するように設けられる。潤滑油は、この給油孔２ｄを流れてクランク軸受部２ｂからボール（外球面）２ａの摺動部に供給される。   The oil supply hole 2d is provided so as to penetrate the inside of the ball (outer spherical surface) 2a and the rod portion 2c. Lubricating oil flows through the oil supply hole 2d and is supplied from the crank bearing portion 2b to the sliding portion of the ball (outer spherical surface) 2a.

また、ボール（外球面）２ａはピストン４のボール受け部（内球面）４ａと同様、球面の一部を切り欠いた構造となっている。従って潤滑油の通る経路が短く、潤滑油が流れやすく、充分に潤滑油が供給できる構造となる。   Further, the ball (outer spherical surface) 2 a has a structure in which a part of the spherical surface is cut out in the same manner as the ball receiving portion (inner spherical surface) 4 a of the piston 4. Accordingly, the route through which the lubricating oil passes is short, the lubricating oil can easily flow, and the lubricating oil can be sufficiently supplied.

回り止めについて図６、図７、及び図８を用いて説明する。   The rotation stopper will be described with reference to FIGS. 6, 7, and 8. FIG.

図６は回り止めを示す斜視図である。図７は回り止めをボールジョイント構造に組み立てた状態の斜視図である。図８（ａ）はボールジョイント構造として組み立てられた回り止めをクランク軸受部側から見た図である。図８（ｂ）は見方を変えた図７と同等なる斜視図である。   FIG. 6 is a perspective view showing a detent. FIG. 7 is a perspective view of a state in which the rotation stopper is assembled into a ball joint structure. FIG. 8A is a view of the rotation stopper assembled as a ball joint structure as seen from the crank bearing portion side. FIG. 8B is a perspective view equivalent to FIG.

回り止めについて説明する前に、コンロッドのボール（外球面）と、ピストンのボール受け部（内球面）について説明を加える。   Before explaining the rotation stopper, the connecting rod ball (outer spherical surface) and the piston ball receiving portion (inner spherical surface) will be described.

ボール（外球面）２ａは、コンロッド２の長手方向に沿うように形成された一対の平坦面２ｅを対称に有する。   The ball (outer spherical surface) 2 a has a pair of flat surfaces 2 e formed symmetrically along the longitudinal direction of the connecting rod 2.

ボール受け穴（内球面）４ａは、両平坦面２ｃ間の厚み幅と同等ないし幾分大き目に形成された一対の挿入用切欠開口４ｂを有する。挿入用切欠開口４ｂの幅はＬである。ピストン４は、一対の挿入用切欠開口４ｂの外側に概ね半円形状をした一対の保持窪４ｃを有する。   The ball receiving hole (inner spherical surface) 4a has a pair of notch openings 4b for insertion formed to be equal to or somewhat larger than the thickness width between the two flat surfaces 2c. The width of the insertion notch opening 4b is L. The piston 4 has a pair of holding recesses 4c having a substantially semicircular shape outside the pair of insertion cutout openings 4b.

ピストン４は、ボール受け穴（内球面）４ａが形成される手前にボール受け穴（内球面）４ａよりも大きな円形穴４ｆを有する。つまり、ボール受け穴（内球面）４ａは、円形穴４ｆの中央底部に落ち込むように形成される。   The piston 4 has a circular hole 4f larger than the ball receiving hole (inner spherical surface) 4a before the ball receiving hole (inner spherical surface) 4a is formed. That is, the ball receiving hole (inner spherical surface) 4a is formed so as to drop into the center bottom of the circular hole 4f.

油溜部４ｄは、ボール受け穴（内球面）４ａの中央の底に形成される。この油溜部４ｄには、給油孔２ｄを流れて供給される潤滑油が溜まる。ここに溜まる潤滑油により、ボール受け穴（内球面）４ａとボール（外球面）２ａとの摺動面が良く潤され、円滑な回転が行われる。   The oil reservoir 4d is formed at the bottom at the center of the ball receiving hole (inner spherical surface) 4a. Lubricating oil supplied through the oil supply hole 2d is stored in the oil reservoir 4d. The lubricating oil accumulated here moisturizes the sliding surface between the ball receiving hole (inner spherical surface) 4a and the ball (outer spherical surface) 2a, and smooth rotation is performed.

ボール受け穴（内球面）４ａにボール（外球面）２ａを挿入し、ボール（外球面）２ａを平坦面２ｃが挿入用切欠開口４ｂに来るように回すことにより、ボール受け穴（内球面）４ａとボール（外球面）２ａが円滑に滑るように結合するボールジョイントの抜け止めが行なわれる。   The ball (outer spherical surface) 2a is inserted into the ball receiving hole (inner spherical surface) 4a, and the ball (outer spherical surface) 2a is turned so that the flat surface 2c comes to the insertion notch opening 4b. The ball joint that joins the ball 4a and the ball (outer spherical surface) 2a so as to smoothly slide is prevented.

回り止め１０は、ボールジョイントされたボール（外球面）２ａがボール受け穴（内球面）４ａから脱落しないように、ボール（外球面）２ａの回り止めを行なう。   The rotation stopper 10 prevents rotation of the ball (outer spherical surface) 2a so that the ball-joined ball (outer spherical surface) 2a does not fall off from the ball receiving hole (inner spherical surface) 4a.

この回り止め１０は、ピストン４に設けられた一対の保持窪４ｃに挿入される一対の嵌め込み脚１０ａと、一対の嵌め込み脚１０ａに架け渡される連結部１０ｂとを有する。一対の嵌め込み脚１０ａは、平坦板部１０ａ１と、この平坦板部１０ａ１の両端側から外側に折れて円弧を描きながら互いに近づくように延在する二つの円弧部１０ａ２とを有する。   The detent 10 has a pair of fitting legs 10a inserted into a pair of holding recesses 4c provided on the piston 4, and a connecting portion 10b spanning the pair of fitting legs 10a. The pair of fitting legs 10a includes a flat plate portion 10a1 and two arc portions 10a2 extending outward from both ends of the flat plate portion 10a1 so as to approach each other while drawing an arc.

さらに平坦板部１０ａ１の中央には、内向きに凹むように設けられ、ボール（外球面）２ａの平坦面２ｃに接合する凹部１０ａ３を有する。回り止め１０は、鋼板を折り曲げて形成する。鋼板や燐青銅板を含むバネ性の金属板を用いて作られる。   Further, the center of the flat plate portion 10a1 is provided with a concave portion 10a3 which is provided so as to be recessed inward and joined to the flat surface 2c of the ball (outer spherical surface) 2a. The rotation stopper 10 is formed by bending a steel plate. It is made using spring metal plates including steel plates and phosphor bronze plates.

回り止め１０は、図７、図８に示すように、ピストン４に取り付けられる。ピストン４の円形穴４ｆから挿入された回り止め１０は、嵌め込み脚１０ａが保持窪４ｃに挿入されて保持される。嵌め込み脚１０ａは、二つの円弧部１０ａ２が弾性を利用して撓むように保持窪４ｃに嵌るので、容易に外れない。   The detent 10 is attached to the piston 4 as shown in FIGS. The rotation stopper 10 inserted from the circular hole 4f of the piston 4 is held by inserting the fitting leg 10a into the holding recess 4c. The fitting leg 10a is not easily detached because it fits into the holding recess 4c so that the two arc portions 10a2 bend using elasticity.

この弾性を有する円弧部１０ａ２が設けられた回り止め１０を用いることにより、ピストン４のボール受け穴（内球面）４ａ及びコンロッド２のボール（外球面）を変形させることなくボールジョイント構造を組み立てることが可能となり、摺動性に優れたボールジョイント構造となる。   Assembling the ball joint structure without deforming the ball receiving hole (inner spherical surface) 4a of the piston 4 and the ball (outer spherical surface) of the connecting rod 2 by using the rotation stopper 10 provided with the arc portion 10a2 having elasticity. And a ball joint structure with excellent slidability.

回り止め１０がピストン４に取り付けた状態では、平坦板部１０ａ１の凹部１０ａ３が、ボール（外球面）２ａの平坦面２ｃに接合している。このため、ボール（外球面）２ａは、平坦面２ｃと凹部１０ａ３との接合を解除する方向の回動は阻止される。この回動阻止により、ボール（外球面）２ａとボール受け穴（内球面）４ａが結合するボールジョイントは脱落しないよう保たれるのである。   In a state where the rotation stopper 10 is attached to the piston 4, the concave portion 10a3 of the flat plate portion 10a1 is joined to the flat surface 2c of the ball (outer spherical surface) 2a. For this reason, the ball (outer spherical surface) 2a is prevented from rotating in the direction in which the joining of the flat surface 2c and the recess 10a3 is released. By preventing the rotation, the ball joint where the ball (outer spherical surface) 2a and the ball receiving hole (inner spherical surface) 4a are coupled is kept from falling off.

ボール受け穴（内球面）４ａに対するボール（外球面）２ａの回動は、コンロロッド２のロッド部２ｃが首振るような揺動の回動作動になる。   The rotation of the ball (outer spherical surface) 2a with respect to the ball receiving hole (inner spherical surface) 4a is a swinging rotation operation in which the rod portion 2c of the stove rod 2 swings.

回り止めの他の実施例ついて、図９、図１０を引用して述べる。   Another embodiment of the detent will be described with reference to FIGS.

この回り止め１０は、図１０に示すように、連結部１０ｂに係止爪１０ｃを設けたところが特徴である。他は先に述べた回り止めと共通の構成を有する。   As shown in FIG. 10, this detent 10 is characterized in that a locking claw 10c is provided on the connecting portion 10b. Others have the same configuration as the above-described detent.

ピストン４は、図９に示すように、円形穴４ｆに環状の止め溝４ｇを設けたところが特徴である。他は先に述べたピストンと共通の構成を有する。   As shown in FIG. 9, the piston 4 is characterized in that an annular retaining groove 4g is provided in a circular hole 4f. Others have the same configuration as the piston described above.

係止爪１０ｃが止め溝４ｇに係合することにより、回り止め１０は、円形穴４ｆから外れなくなる。二つの円弧部１０ａ２の弾性による保持に、係止爪１０ｃの係止が加わるので、回り止め１０は、より確実に保持される。   When the locking claw 10c is engaged with the stop groove 4g, the rotation stopper 10 does not come off from the circular hole 4f. Since the locking claw 10c is locked in addition to the elastic holding of the two arc portions 10a2, the detent 10 is more reliably held.

潤滑油の供給に関する他の実施例ついて、図１１を引用して述べる。   Another embodiment relating to the supply of lubricating oil will be described with reference to FIG.

クランクシャフト７ａは、軸方向に延在する潤滑油の油流通孔１１０と、外周に貫通する油流出孔１１１を有する。また、クランク軸受部２ｂは、摺動面に環状の油受溝１１２を有する。この油受溝１１２に給油孔２ｄが連通するように形成されている。   The crankshaft 7a has an oil flow hole 110 for lubricating oil extending in the axial direction and an oil outflow hole 111 penetrating the outer periphery. The crank bearing 2b has an annular oil receiving groove 112 on the sliding surface. The oil receiving groove 112 is formed so as to communicate with the oil supply hole 2d.

クランク軸受部２ｂには、油流通孔１１０を流れる潤滑油が油流出孔１１１、油受溝１１２を経由して供給され、クランク軸受部２ｂとクランクシャフト７ａの摺動面を潤す。油受溝１１２内の潤滑油は、給油孔２ｄにも注がれるので、ボール受け穴（内球面）４ａとボール（外球面）２ａとの摺動面も潤す。   Lubricating oil flowing through the oil circulation hole 110 is supplied to the crank bearing portion 2b via the oil outflow hole 111 and the oil receiving groove 112 to moisten the sliding surfaces of the crank bearing portion 2b and the crankshaft 7a. Since the lubricating oil in the oil receiving groove 112 is also poured into the oil supply hole 2d, the sliding surface between the ball receiving hole (inner spherical surface) 4a and the ball (outer spherical surface) 2a is also moistened.

油溜めになる油受溝１１２がクランク軸受部２ｂに設けられているので、クランク軸受部２ｂとクランクシャフト７ａの摺動面に潤滑油の供給が良く行われる。また、油溜めになる油受溝１１２に給油孔２ｄが連通しているので、ボール受け穴（内球面）４ａとボール（外球面）２ａとの摺動面に潤滑油の供給が良く行われる。   Since the oil receiving groove 112 serving as an oil reservoir is provided in the crank bearing portion 2b, the lubricating oil is often supplied to the sliding surfaces of the crank bearing portion 2b and the crankshaft 7a. Further, since the oil supply hole 2d communicates with the oil receiving groove 112 serving as an oil reservoir, the lubricating oil is often supplied to the sliding surface between the ball receiving hole (inner spherical surface) 4a and the ball (outer spherical surface) 2a. .

次に充分に潤滑油が供給される構造に適したボールジョイント部の信頼性を確保するための材料について説明する。   Next, the material for ensuring the reliability of the ball joint part suitable for the structure to which the lubricating oil is sufficiently supplied will be described.

図１２にピストン４及びコンロッド２に使用する材料について、リングオンブロック摩擦試験機により摺動試験を行った結果を示す。   FIG. 12 shows the results of a sliding test performed on a material used for the piston 4 and the connecting rod 2 using a ring-on-block friction tester.

本試験は潤滑油中で、摺動速度は１．０１ｍ／ｓとし、試験負荷は１２３．５Ｎとした。本試験結果から、コンロッド２の材料には封孔処理せず、ピストン４の材料のみ水蒸気処理を施して封孔した焼結材４を使用したものは摩耗量が多いことが確認された。   In this test, the sliding speed was 1.01 m / s and the test load was 123.5 N in lubricating oil. From the result of this test, it was confirmed that the material of the connecting rod 2 was not sealed, but only the material of the piston 4 was steam-treated and sealed using the sintered material 4 that had a large amount of wear.

これは、封孔処理されていないため、油膜が形成されないためである。一方、空孔の無い鋳鉄や両方に封孔処理を施した焼結材を用いた場合、コンロッド２の材料の摩耗が少なくなる傾向があり、必要とする限界摩耗量をコンロッド２の材料で満足させることができた。   This is because the oil film is not formed because the sealing treatment is not performed. On the other hand, when cast iron without voids or a sintered material in which both are sealed, there is a tendency that the wear of the material of the connecting rod 2 tends to decrease, and the required amount of wear is satisfied with the material of the connecting rod 2 I was able to.

しかし、ピストン４の材料の摩耗が増加することも認められる。焼結材同士の場合、コンロッド２の材料に窒化した焼結材４ＳＮと窒化しないピストン４の材料の焼結材８Ｓを組み合わせたものは窒化したコンロッド２の材料で摩耗限界を下回ったが、窒化していないピストン４の材料の摩耗を増やす結果となった。   However, it is also observed that the wear of the material of the piston 4 increases. In the case of the sintered materials, the combination of the sintered material 4SN nitrided to the material of the connecting rod 2 and the sintered material 8S of the material of the piston 4 that is not nitrided is less than the wear limit by the material of the connecting rod 2 that is nitrided. As a result, the wear of the material of the piston 4 which has not been increased is increased.

両方に窒化をした場合はどちらも摩耗が増大してしまった。金型鋼に後述の熱処理（処理条件１０３）を施し表面を硬くした相手材Ａ３と焼結材８Ｓではコンロッド２の材料とピストン４の材料ともに耐摩耗性が向上し、摩耗限界を下回った。これら試験や試行検討より、組み合わせる材料表面の硬さの比が耐摩耗性向上に大きく影響していることを見出した。   When both were nitrided, the wear increased in both cases. In the counterpart material A3 and the sintered material 8S, which were subjected to the heat treatment described later (processing condition 103) on the mold steel and the surface thereof was hardened, the wear resistance of both the material of the connecting rod 2 and the material of the piston 4 was improved and was below the wear limit. From these tests and trial studies, it was found that the ratio of the hardness of the surface of the material to be combined has a great influence on the improvement of wear resistance.

図１３は焼結材の表面硬さ測定結果を示す。焼結材４ＳＮと焼結材８Ｓの表面硬さの比は約１．４倍であり、この硬さ比を高くすることで図１２に示す摩耗限界値を満足できることが推測できる。   FIG. 13 shows the measurement results of the surface hardness of the sintered material. The ratio of the surface hardness between the sintered material 4SN and the sintered material 8S is about 1.4 times, and it can be estimated that the wear limit value shown in FIG. 12 can be satisfied by increasing the hardness ratio.

Figure 0004694956
Figure 0004694956

表１は、本発明の実施例に係るもので、金型鋼焼入れ窒化材の処理条件と硬さ測定結果をまとめたものである。   Table 1 relates to the embodiment of the present invention, and summarizes the processing conditions and hardness measurement results of the die steel hardened nitride material.

表１は相手材として、より硬さ比を大きくするためにＪＩＳにおけるＳＫＤ１１相当の冷間金型鋼を用い、熱処理及び窒化処理を実施した相手材Ａ１、Ａ３、Ａ４の表面層および内部の硬さ測定結果を示す。   Table 1 shows the surface layer and internal hardness of the counterpart materials A1, A3, and A4 that were subjected to heat treatment and nitriding treatment using a cold die steel equivalent to SKD11 in JIS to increase the hardness ratio as the counterpart material. The measurement results are shown.

焼き戻し温度を高くすることにより表面硬度は高くなり、さらに窒化処理の温度を低くすることにより表層および内部ともに高硬度化することがわかる。この最高高度の材料（相手材Ａ４）を用いると、硬さの比を約３倍とすることができ、図１１に示す通り、コンロッド２の材料とピストン４の材料の双方で摩耗を抑制できることがわかる。   It can be seen that increasing the tempering temperature increases the surface hardness, and further decreasing the nitriding temperature increases the hardness of both the surface layer and the interior. By using this highest-grade material (partner material A4), the hardness ratio can be increased by about 3 times, and wear can be suppressed by both the material of the connecting rod 2 and the material of the piston 4 as shown in FIG. I understand.

相手材を硬くすることは、同時に加工しにくくしてしまうため、加工性に鑑みて相手材の検討を実施した。表１の相手材Ａ１、Ａ３、Ａ４に加え、ＪＩＳにおけるＳＣＭ４１５材（肌焼鋼）を用い窒化と高周波焼入れにより図１４に示す相手材Ｂ６、Ｂ８を作成した。   Since hardening the mating material makes it difficult to process at the same time, the mating material was examined in view of workability. In addition to the mating materials A1, A3, and A4 in Table 1, mating materials B6 and B8 shown in FIG. 14 were prepared by nitriding and induction quenching using SCM415 material (skin-hardened steel) in JIS.

図１５に図１２と同様の試験条件で焼結材８Ｓと組み合わせた摩耗試験の結果を示す。   FIG. 15 shows the result of a wear test combined with the sintered material 8S under the same test conditions as FIG.

この結果から表面層の硬さの比が１．５倍以上であれば、定常の摩耗に関しては所望の耐久性が得られることがわかった。   From this result, it was found that if the hardness ratio of the surface layer is 1.5 times or more, desired durability can be obtained with respect to steady wear.

さらに、相手材Ｂ６、Ｂ８を用い、それぞれ焼結材８Ｓと組み合わせ、図１２と同様のリングオンブロック摩擦試験機により再度摺動試験を行った。再試験は平均粒径１０ミクロンメートルに調整した軟鋼溶接時の溶接スパッタを混入させた潤滑油中で、摺動速度は１．０１ｍ／ｓとし、試験負荷は１２３．５Ｎとし短時間の試験を行った。   Further, the mating materials B6 and B8 were used, respectively, combined with the sintered material 8S, and the sliding test was performed again with the same ring-on-block friction tester as in FIG. The retest was conducted in a lubricating oil mixed with weld spatter during mild steel welding adjusted to an average particle size of 10 microns, with a sliding speed of 1.01 m / s and a test load of 123.5 N. went.

試験後に摩擦面を観察した結果、相手材Ｂ６の表面にはスパッタ粒子による傷、すなわちアブレッシブ摩耗痕が観察されたが、相手材Ｂ８の表面にはアブレッシブ摩耗痕はほとんど観察されなかった。   As a result of observing the friction surface after the test, scratches due to sputtered particles, that is, abrasive wear marks, were observed on the surface of the counterpart material B6, but almost no abrasive wear marks were observed on the surface of the counterpart material B8.

以上の結果により、ピストン４の材料として焼結材に水蒸気処理で封孔を行ったもの、及びコンロッド２の材料として焼結材に水蒸気処理で封孔した後に窒化したもの及び金型鋼を焼入れし、高温焼き戻し後に焼き戻し温度以下で窒化を行ったものを使用することとした。   Based on the above results, the piston 4 is made of a sintered material that has been sealed by steam treatment, and the connecting rod 2 is made of a sintered material that has been sealed by steam treatment. Then, it was decided to use a material that was nitrided at a temperature lower than the tempering temperature after tempering at a high temperature.

〔実施形態１〕
ピストン４の材料として水蒸気処理による封孔処理を施したＦｅ−Ｃｕ（１〜２％）−Ｃ（０．７〜１．０％）の焼結材を使用し、コンロッド２の材料として鉄系合金を用いた圧縮機を製作した。 [Embodiment 1]
A sintered material of Fe-Cu (1-2%)-C (0.7-1.0%) subjected to sealing treatment by steam treatment is used as the material of the piston 4, and iron-based material is used as the material of the connecting rod 2. A compressor using an alloy was manufactured.

この鉄系合金は溶製材でありＣｒ（１１〜１３重量％）−Ｍｏ（０．８〜１．２重量％）−Ｍｎ（０．３〜０．６重量％）−Ｃ（０．６〜１．６重量％）と他不可避的元素を含む残部鉄の鉄基合金を１０１０℃〜１０４０℃で焼入れ後、５２０℃２時間の焼き戻しを２回行い、４８０℃の塩浴中で９０分窒化処理を施した。   This iron-based alloy is a melting material, Cr (11 to 13% by weight) -Mo (0.8 to 1.2% by weight) -Mn (0.3 to 0.6% by weight) -C (0.6 to 1.6% by weight) and the remaining iron-based alloy containing other inevitable elements were quenched at 1010 ° C. to 1040 ° C., tempered twice at 520 ° C. for 2 hours, and then in a salt bath at 480 ° C. for 90 minutes. Nitriding treatment was performed.

この密閉形圧縮機を装備した冷凍サイクルに冷媒としてイソブタン、潤滑油としてエステル油を封入し、運転回転数毎分４９００回転、吐出圧力１．６ＭＰａで３０日間運転したところ、ボールジョイント構造部に摩耗が発生せず、良好な摺動性を維持できる結果を得た。   The refrigeration cycle equipped with this hermetic compressor was filled with isobutane as a refrigerant and ester oil as a lubricating oil, and operated at 4900 rpm and a discharge pressure of 1.6 MPa for 30 days. Was obtained, and good slidability was maintained.

さらに吐出圧力を２．０ＭＰａまで高めた同様の試験を実施したところ、ボールジョイント構造部に異常摩耗が発生することなく、良好な特性が維持できた。   Further, when a similar test was performed with the discharge pressure increased to 2.0 MPa, it was possible to maintain good characteristics without causing abnormal wear in the ball joint structure.

また、溶接によるスパッタ粒子を管理上限の１０倍を潤滑油に添加した圧縮機を製作し同様の条件で５日間運転したところ、回転が止まることはなく安定に運転することができ、摩擦面に微細な擦り傷が観察される以外に異常な摩耗はなかった。   In addition, when a compressor in which 10 times the control upper limit of welding sputter particles was added to the lubricating oil was manufactured and operated under the same conditions for 5 days, it could be operated stably without stopping rotation, and the friction surface There was no abnormal wear other than the observation of fine scratches.

上述したように、本発明の各実施例を適用すると、ボールジョイント構造のボール受け部（内球面）４ａおよびボール（外球面）２ａに異常磨耗が発生しないため、密閉形圧縮機の長期信頼性が確保され、また、密閉形圧縮機の動作時における摺動損失の低減により密閉形圧縮機の効率を向上することができる。   As described above, when each embodiment of the present invention is applied, since abnormal wear does not occur in the ball receiving portion (inner spherical surface) 4a and the ball (outer spherical surface) 2a of the ball joint structure, the long-term reliability of the hermetic compressor In addition, the efficiency of the hermetic compressor can be improved by reducing the sliding loss during the operation of the hermetic compressor.

本発明の実施例に係るもので、密閉形圧縮機の縦断面図。1 is a longitudinal sectional view of a hermetic compressor according to an embodiment of the present invention. 本発明の実施例に係るもので、ピストン内側構造を示す図。The figure which concerns on the Example of this invention and shows a piston inner side structure. 本発明の実施例に係るもので、図１のＡ−Ａ断面図。1. It concerns on the Example of this invention, and is AA sectional drawing of FIG. 本発明の実施例に係るもので、図１のＢ−Ｂ断面図。1. It concerns on the Example of this invention, and is BB sectional drawing of FIG. 本発明の実施例に係るもので、コンロッドの斜視図。The perspective view of a connecting rod which concerns on the Example of this invention. 本発明の実施例に係るもので、回り止めの斜視図。The perspective view of a detent according to the embodiment of the present invention. 本発明の実施例に係るもので、ピストンとコンロッドの組立状態を示す図。The figure which concerns on the Example of this invention and shows the assembly state of a piston and a connecting rod. 本発明の実施例に係るもので、ピストンとコンロッドの組立状態について回り止めを加えて示した図。The figure which concerns on the Example of this invention and added the rotation stop about the assembly state of a piston and a connecting rod. 本発明の他の実施例に係るもので、ピストンとコンロッドと回り止めとの関係を示す断面図。Sectional drawing which concerns on the other Example of this invention, and shows the relationship between a piston, a connecting rod, and a rotation stopper. 本発明の他の実施例に係るもので、回り止めの斜視図。The perspective view of a detent according to another embodiment of the present invention. 本発明の他の実施例に係るもので、クランクシャフトとクランク軸受部の断面図。The sectional view of a crankshaft and a crank bearing according to another embodiment of the present invention. 本発明の実施例に係るもので、ピストン材料とコンロッド材料の磨耗試験結果を示す図。The figure which concerns on the Example of this invention and shows the abrasion test result of piston material and a connecting rod material. 本発明の実施例に係るもので、焼結材の硬さ測定結果を示す図。The figure which concerns on the Example of this invention and shows the hardness measurement result of a sintered material. 本発明の実施例に係るもので、各種鋼材の硬さ測定結果を示す図。The figure which concerns on the Example of this invention and shows the hardness measurement result of various steel materials. 本発明の実施例に係るもので、ピストン材料及びコンロッド材料の摩耗試験結果を示す図。The figure which concerns on the Example of this invention and shows the abrasion test result of piston material and a connecting rod material.

符号の説明Explanation of symbols

１…シリンダ、４…ピストン、２…コンロッド、２ａ…ボール、４ａ…ボール受け穴。   1 ... Cylinder, 4 ... Piston, 2 ... Connecting rod, 2a ... Ball, 4a ... Ball receiving hole.

Claims (17)

密閉容器と、この密閉容器内に収納される圧縮要素、電動要素、及び前記電動要素の回転力を圧縮要素に伝えるクランク機構とを備え、
前記圧縮要素は、シリンダと、このシリンダ内を往復動するピストンとを有し、
前記クランク機構は、前記ピストンに連結されるコンロッドを有し、
前記コンロッドに設けたボールと前記ピストンに設けたボール受け穴とが回動するように摺動自在にボールジョイントされ、このボールジョイントの摺動部に潤滑油の供給が行なわれる密閉形圧縮機にあって、
前記ボールは、前記コンロッドの長手方向に沿うように形成された一対の平坦面を対称に有し、
前記ボール受け穴は、前記両平坦面間の厚み幅と同等ないし幾分大き目に形成された一対の挿入用切欠開口を有し、
前記ボール受け穴に挿入した前記ボールを前記平坦面が挿入用切欠開口に来るように回してボールジョイントの抜け止めをなし、
前記ピストンは、前記一対の挿入用切欠開口の外側に概ね半円形状をした一対の保持窪を有し、
前記ボール受け穴に挿入した前記ボールが抜ける方向に回るのを阻止する回り止めを備え、
前記回り止めは、前記一対の保持窪に挿入される一対の嵌め込み脚と、前記一対の嵌め込み脚に架け渡される連結部とを有し、
前記ピストン、前記コンロッドの一方が鉄を主成分とする合金材であり、
他方の材料は、前記鉄を主成分とする合金材の表面層の硬度に対してビッカース硬度において１．５倍以上の硬度であることを特徴とする密閉形圧縮機。 An airtight container, a compression element housed in the airtight container, an electric element, and a crank mechanism that transmits the rotational force of the electric element to the compression element;
The compression element has a cylinder and a piston that reciprocates in the cylinder,
The crank mechanism has a connecting rod connected to the piston,
A hermetic compressor in which a ball provided on the connecting rod and a ball receiving hole provided on the piston are slidably ball jointed so that the ball joint hole rotates, and lubricating oil is supplied to the sliding portion of the ball joint. There,
The ball has a pair of flat surfaces symmetrically formed along the longitudinal direction of the connecting rod,
The ball receiving hole has a pair of notch openings for insertion formed to be equal to or somewhat larger than the thickness width between the two flat surfaces,
Turn the ball inserted into the ball receiving hole so that the flat surface comes to the insertion notch opening to prevent the ball joint from coming off,
The piston has a pair of holding recesses that are generally semicircular on the outside of the pair of insertion cutout openings,
A detent that prevents the ball inserted into the ball receiving hole from rotating in the direction of withdrawal;
The detent has a pair of fitting legs that are inserted into the pair of holding recesses, and a connecting portion that spans the pair of fitting legs,
One of the piston and the connecting rod is an alloy material mainly composed of iron,
The other material is a hermetic compressor having a Vickers hardness of 1.5 times or more with respect to the hardness of the surface layer of the alloy material containing iron as a main component. 請求項１記載の密閉形圧縮機において、
前記一対の嵌め込み脚は、平坦板部と、この平坦板部の両端側から外側に折れて円弧を描きながら互いに近づくように延在する二つの円弧部を有することを特徴とする密閉形圧縮機。 The hermetic compressor according to claim 1, wherein
The pair of fitting legs have a flat plate portion and two arc portions extending outward from both ends of the flat plate portion so as to approach each other while drawing an arc. . 請求項２記載の密閉形圧縮機において、
前記嵌め込み脚は、平坦板部の中央に内向きに凹むように設けられ、かつ前記ボールの平坦面に接合する凹部を有することを特徴とする密閉形圧縮機。 The hermetic compressor according to claim 2, wherein
The hermetic compressor is characterized in that the fitting leg is provided so as to be recessed inwardly in the center of the flat plate portion and has a concave portion joined to the flat surface of the ball. 請求項１記載の密閉形圧縮機において、
前記回り止めの連結部は、前記ピストンに設けた止め溝に係止める係止爪を有することを特徴とする密閉形圧縮機。 The hermetic compressor according to claim 1, wherein
The hermetic compressor is characterized in that the connecting portion of the rotation stopper has a locking claw that is locked in a locking groove provided in the piston. 請求項１記載の密閉形圧縮機において、
前記回り止めは、鋼板を含む金属板で形成されることを特徴とする密閉形圧縮機。 The hermetic compressor according to claim 1, wherein
The said rotation stopper is formed with the metal plate containing a steel plate, The hermetic compressor characterized by the above-mentioned. 密閉容器と、この密閉容器内に収納される圧縮要素、電動要素、及び前記電動要素の回転力を圧縮要素に伝えるクランク機構とを備え、
前記圧縮要素は、シリンダと、このシリンダ内を往復動するピストンとを有し、
前記クランク機構は、前記ピストンに連結されるコンロッドを有し、
前記コンロッドに設けたボールと前記ピストンに設けたボール受け穴とが回動するように摺動自在にボールジョイントされ、このボールジョイントの摺動部に潤滑油の供給が行なわれる密閉形圧縮機にあって、
前記コンロッドは、前記ボールの反対側に設けたクランク軸受を有し、
前記クランク機構は、電動要素側に設けたクランクシャフトと、前記ボールの反対側になる前記コンロッドの端に設けられ、かつ前記クランクシャフトを回動自在に支持するクランク軸受とを有し
前記クランク軸受は、摺動面に環状の油受溝を有し、
前記コンロッドは、前記油受溝から前記ボールの摺動部側に抜ける給油孔を有し、
前記ピストン、前記コンロッドの一方が鉄を主成分とする合金材であり、
他方の材料は、前記鉄を主成分とする合金材の表面層の硬度に対してビッカース硬度において１．５倍以上の硬度であることを特徴とする密閉形圧縮機。 An airtight container, a compression element housed in the airtight container, an electric element, and a crank mechanism that transmits the rotational force of the electric element to the compression element;
The compression element has a cylinder and a piston that reciprocates in the cylinder,
The crank mechanism has a connecting rod connected to the piston,
A hermetic compressor in which a ball provided in the connecting rod and a ball receiving hole provided in the piston are slidably ball-jointed so that a lubricant is supplied to the sliding portion of the ball joint. There,
The connecting rod has a crank bearing provided on the opposite side of the ball,
The crank mechanism includes a crankshaft provided on the electric element side, and a crank bearing provided at an end of the connecting rod on the opposite side of the ball and rotatably supporting the crankshaft. Has an annular oil receiving groove on the sliding surface,
The connecting rod has an oil supply hole extending from the oil receiving groove to the sliding portion side of the ball,
One of the piston and the connecting rod is an alloy material mainly composed of iron,
The other material is a hermetic compressor having a Vickers hardness of 1.5 times or more with respect to the hardness of the surface layer of the alloy material containing iron as a main component. 請求項１−６の何れかに記載の密閉形圧縮機にあって、
前記鉄を主成分とする合金材は焼結材であり、該焼結材の密度は６．６ｇ／ｃｍ３以上であることを特徴とする密閉形圧縮機。 In the hermetic compressor according to any one of claims 1 to 6,
2. The hermetic compressor according to claim 1, wherein the iron-based alloy material is a sintered material, and the density of the sintered material is 6.6 g / cm 3 or more. 請求項１−６の何れかに記載の密閉形圧縮機にあって、
前記鉄を主成分とする合金材は焼結材であり、前記焼結材は酸化膜により封孔処理されていることを特徴とする密閉形圧縮機。 In the hermetic compressor according to any one of claims 1 to 6,
The hermetic compressor, wherein the iron-based alloy material is a sintered material, and the sintered material is sealed with an oxide film. 請求項１−６の何れかに記載の密閉形圧縮機にあって、
前記鉄を主成分とする合金材は焼結材であり、前記焼結材は酸化膜により封孔処理され、
前記封孔処理は、前記ピストンあるいは前記コンロッドの成形、切削加工後に水蒸気処理により前記焼結材に残存する空孔の封孔処理であることを特徴とする密閉形圧縮機。 In the hermetic compressor according to any one of claims 1 to 6,
The iron-based alloy material is a sintered material, and the sintered material is sealed with an oxide film,
The hermetic compressor is a hermetic compressor in which pores remaining in the sintered material are subjected to steam treatment after molding or cutting of the piston or the connecting rod. 請求項１−６の何れかに記載の密閉形圧縮機にあって、
前記他方の材料は、表面部もしくは前記摺動部が窒化処理あるいは炭化処理、浸炭処理、浸硫窒化処理のいずれかの表面拡散処理が施されていることを特徴とする密閉形圧縮機。 In the hermetic compressor according to any one of claims 1 to 6,
The hermetic compressor is characterized in that the other material is subjected to a surface diffusion treatment of any one of nitriding treatment, carbonization treatment, carburizing treatment, and nitrosulphurizing treatment on the surface portion or the sliding portion. 請求項１−６の何れかに記載の密閉形圧縮機にあって、
前記他方の材料は、表面部もしくは前記摺動部が窒化処理あるいは炭化処理、浸炭処理、浸硫窒化処理のいずれかの表面拡散処理が施され、
前記表面拡散処理により形成された窒化物層もしくは硫化物層、または硫化物と窒化物の混合層は表面硬化層であり、前記１．５倍以上の硬度となる範囲が最表面から少なくとも深さ２０ミクロンメートル以上であることを特徴とする密閉形圧縮機。 In the hermetic compressor according to any one of claims 1 to 6,
The other material is subjected to any surface diffusion treatment of nitriding treatment or carbonizing treatment, carburizing treatment, nitronitriding treatment on the surface portion or the sliding portion,
The nitride layer or sulfide layer formed by the surface diffusion treatment or the mixed layer of sulfide and nitride is a hardened surface layer, and the range where the hardness is 1.5 times or more is at least the depth from the outermost surface. A hermetic compressor characterized by being 20 microns or more. 請求項１−６の何れかに記載の密閉形圧縮機にあって、
前記他方の材料は、表面部もしくは前記摺動部が窒化処理あるいは炭化処理、浸炭処理、浸硫窒化処理のいずれかの表面拡散処理が施され、
前記表面拡散処理は、材料の焼き戻し温度以下で行う窒化処理であることを特徴とする密閉形圧縮機。 In the hermetic compressor according to any one of claims 1 to 6,
The other material is subjected to any surface diffusion treatment of nitriding treatment or carbonizing treatment, carburizing treatment, nitronitriding treatment on the surface portion or the sliding portion,
The hermetic compressor is characterized in that the surface diffusion treatment is a nitriding treatment performed at a temperature lower than the tempering temperature of the material. 請求項１−６の何れかに記載の密閉形圧縮機にあって、
前記潤滑油は、エステル系潤滑油またはエステル系潤滑油と鉱油を混合した潤滑油であることを特徴とする密閉形圧縮機。 In the hermetic compressor according to any one of claims 1 to 6,
The above-mentioned lubricating oil is an ester-type lubricating oil or a lubricating oil obtained by mixing an ester-based lubricating oil and mineral oil. 請求項１−６の何れかに記載の密閉形圧縮機にあって、
前記鉄を主成分とする合金材は焼結材であり、
エステル系潤滑油またはエステル系潤滑油と鉱油を混合した潤滑油が前記焼結材に残存する空孔に充填・含浸していることを特徴とする密閉形圧縮機。 In the hermetic compressor according to any one of claims 1 to 6,
The iron-based alloy material is a sintered material,
A hermetic compressor characterized in that an ester-based lubricant or a lubricant obtained by mixing an ester-based lubricant and a mineral oil fills and impregnates pores remaining in the sintered material. 請求項１−６の何れかに記載の密閉形圧縮機にあって、
前記シリンダで圧縮する冷媒をイソブタンとしたことを特徴とする密閉形圧縮機。 In the hermetic compressor according to any one of claims 1 to 6,
A hermetic compressor, wherein the refrigerant compressed by the cylinder is isobutane. 請求項１−６の何れかに記載の密閉形圧縮機にあって、
前記シリンダで圧縮する冷媒に、エステル系潤滑油と相溶性を持つＲ１３４ａなどの非塩素系冷媒を用いることを特徴とする密閉形圧縮機。 In the hermetic compressor according to any one of claims 1 to 6,
A hermetic compressor characterized in that a non-chlorine refrigerant such as R134a having compatibility with an ester lubricant is used as the refrigerant compressed by the cylinder. 請求項１−６の何れかに記載の圧縮機にあって、
前記コンロッドを縦に貫通して前記ボールの摺動部側に抜ける給油孔を有することを特徴とする密閉形圧縮機。 In the compressor in any one of Claims 1-6,
A hermetic compressor having an oil supply hole that vertically penetrates the connecting rod and exits to the sliding portion side of the ball.
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