JP3487892B2 - Hermetic compressor - Google Patents
Hermetic compressorInfo
- Publication number
- JP3487892B2 JP3487892B2 JP00566494A JP566494A JP3487892B2 JP 3487892 B2 JP3487892 B2 JP 3487892B2 JP 00566494 A JP00566494 A JP 00566494A JP 566494 A JP566494 A JP 566494A JP 3487892 B2 JP3487892 B2 JP 3487892B2
- Authority
- JP
- Japan
- Prior art keywords
- hole
- connecting rod
- oil
- small end
- piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Description
【０００１】[0001]
【産業上の利用分野】本発明は、冷凍冷蔵装置等に使用
される往復式密閉型圧縮機に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reciprocating hermetic compressor used for a refrigerating machine or the like.
【０００２】[0002]
【従来の技術】冷凍冷蔵装置等に使用される密閉型圧縮
機は密閉容器内に電動圧縮要素が収納されており、密閉
容器内のメンテナンスや修理ができないため、信頼性の
高いものが強く望まれている。なかでも往復型圧縮機の
ピストンピンとコンロッド小端穴との摺動部は圧縮によ
り大きな面圧を受け、厳しい摺動状態にある。そのた
め、ピストンピンとコンロッド小端穴の摺動部の潤滑不
良を防ぎ、信頼性を高める方法が従来から考案されてい
る。コンロッド小端穴への給油方法については、例えば
実公昭４７−１６８３６号公報、またコンロッド小端穴
とピストンピンとの摺動部に設けられた円周溝について
は、例えば特開平２−２７５０７２号公報に示されてい
るような密閉型電動圧縮機がある。2. Description of the Related Art A hermetic compressor used in a refrigerating machine or the like has a highly reliable one because an electric compression element is housed in a hermetic container and maintenance and repair cannot be performed in the hermetic container. It is rare. Above all, the sliding portion between the piston pin of the reciprocating compressor and the small end hole of the connecting rod receives a large surface pressure due to compression, and is in a severe sliding state. Therefore, there has been conventionally devised a method of preventing the lubrication failure of the sliding portion between the piston pin and the small end hole of the connecting rod to improve the reliability. Regarding the method of refueling the connecting rod small end hole, for example, Japanese Utility Model Publication No. 47-16836, and for the circumferential groove provided in the sliding portion between the connecting rod small end hole and the piston pin, see, for example, Japanese Patent Application Laid-Open No. 275072. There is a hermetic electric compressor as shown in.
【０００３】以下、図面を参照しながら、上述した従来
の密閉型電動圧縮機の一例について説明する。An example of the above-mentioned conventional hermetic electric compressor will be described below with reference to the drawings.
【０００４】図６は従来の密閉型電動圧縮機を示す断面
図である。図６において、１は内部をピストン２が往復
動するシリンダである。３はクランク軸４を軸支する軸
受である。前記ピストン２は中空部５と、軸方向と直交
する方向に貫通孔６を有している。７は一端に小端穴８
を他端に大端穴９を有するコンロッドである。１０は前
記コンロッド７内を通り、前記小端穴８と前記大端穴９
とを連通し、かつ前記小端穴８の軸心と前記大端穴９の
軸心とを通る平面上に両端が開口する給油孔であり、１
１は小端穴８とコンロッド７外部とを連通する排油孔で
ある。１２は前記クランク軸４に形成された偏心部であ
る。１３はクランク軸４内に明けられたシャフト給油孔
であり、１４は前記シャフト給油孔１３に交差連通した
偏心部給油孔であり、偏心部１２表面に設けられたオイ
ル溜り１５に開口している。１６はクランク偏心部１２
に固定された給油管であり、前記シャフト給油孔１３に
連通しており、先端は密閉容器（図示せず）底部に貯溜
したオイル１７に浸かっている。前記コンロッド７の小
端穴８はピストン２の中空部５に挿入され、かつ貫通穴
６及び小端穴８にピストンピン１８が挿入されると共
に、偏心部１２が大端穴９に挿入されることにより、ピ
ストン２とクランク軸４が連結されている。１９はピス
トンピン１８表面の円周方向に設けられた円周溝であ
り、２０はピストンピン１８をピストン２に固定するロ
ッキングピンである。FIG. 6 is a sectional view showing a conventional hermetic electric compressor. In FIG. 6, reference numeral 1 is a cylinder in which a piston 2 reciprocates. Reference numeral 3 is a bearing that supports the crankshaft 4. The piston 2 has a hollow portion 5 and a through hole 6 in a direction orthogonal to the axial direction. 7 is a small end hole at one end 8
Is a connecting rod having a large end hole 9 at the other end. 10 passes through the inside of the connecting rod 7, and the small end hole 8 and the large end hole 9 are provided.
An oil supply hole having both ends opened on a plane that communicates with the shaft center of the small end hole 8 and the shaft center of the large end hole 9.
Reference numeral 1 is an oil drain hole that connects the small end hole 8 and the outside of the connecting rod 7. Reference numeral 12 is an eccentric portion formed on the crankshaft 4. Reference numeral 13 is a shaft oil supply hole opened in the crankshaft 4, and 14 is an eccentric part oil supply hole which is in cross communication with the shaft oil supply hole 13, and is open to an oil sump 15 provided on the surface of the eccentric part 12. . 16 is the crank eccentric part 12
Is connected to the shaft oil supply hole 13, and its tip is immersed in oil 17 stored in the bottom of a closed container (not shown). The small end hole 8 of the connecting rod 7 is inserted into the hollow portion 5 of the piston 2, the piston pin 18 is inserted into the through hole 6 and the small end hole 8, and the eccentric portion 12 is inserted into the large end hole 9. As a result, the piston 2 and the crankshaft 4 are connected. Reference numeral 19 is a circumferential groove provided on the surface of the piston pin 18 in the circumferential direction, and 20 is a locking pin for fixing the piston pin 18 to the piston 2.
【０００５】以上のように構成された密閉型圧縮機につ
いて、以下その動作を説明する。クランク軸が回転する
ことにより給油管１６でオイル１７に油圧が発生し、オ
イル１７は給油管１６内及びシャフト給油孔１３を上昇
する。上げられたオイル１７の一部は偏心部給油孔１４
を通ってオイル溜まり１５に流出し、大端穴９と偏心部
１２との摺動部を潤滑する。さらに、オイル溜まり１５
のオイルの一部は給油孔１０を通って小端穴８まで流
れ、ピストンピン１８と小端穴８の摺動部を潤滑し、円
周溝１９を通り、さらに排油孔１１を通ってピストン２
の中空部５に流出する。The operation of the hermetic compressor having the above structure will be described below. As the crankshaft rotates, oil pressure is generated in the oil 17 in the oil supply pipe 16, and the oil 17 rises in the oil supply pipe 16 and the shaft oil supply hole 13. Part of the raised oil 17 is the eccentric part oil supply hole 14
Through the oil reservoir 15 to lubricate the sliding portion between the large end hole 9 and the eccentric portion 12. In addition, the oil sump 15
A part of the oil of the above flows to the small end hole 8 through the oil supply hole 10, lubricates the sliding portion between the piston pin 18 and the small end hole 8, passes through the circumferential groove 19, and further passes through the oil drain hole 11. Piston 2
Flows out into the hollow portion 5 of.
【０００６】図７のａ，ｂ，ｃ，ｄは図６に示すＡ−Ａ
断面における、コンロッド７内の給油孔１０と偏心部１
２内のクランク給油孔１４及びオイル溜り１５の関係を
示す行程図である。図６のクランク軸４の１回転中にお
けるコンロッド７の給油孔１０及び偏心部１２のクラン
ク給油孔１４とオイル溜り１５の関係から明らかなよう
に、常にオイル１７がクランク給油孔１４及びオイル溜
り１５からコンロッド７の給油孔１０に流入可能ではな
く、図７のｃ〜ｄ間、すなわちピストン２が上死点から
下死点に至る間の吸入行程においてのみ流入可能であ
る。この構造により、偏心部１２がコンロッド７の大端
部９から大きな荷重を受ける圧縮行程時は偏心部１２の
オイル溜り１５の無い部分で荷重を受けることになり、
偏心部１２と大端穴９との摺動部に油膜圧力が発生し易
く金属接触による摩耗をしにくくすることができる。Reference characters a, b, c, and d in FIG.
The oil supply hole 10 and the eccentric portion 1 in the connecting rod 7 in the cross section
2 is a process diagram showing the relationship between the crank oil supply hole 14 and the oil sump 15 in FIG. As is clear from the relationship between the oil supply hole 10 of the connecting rod 7 and the crank oil supply hole 14 of the eccentric portion 12 and the oil sump 15 during one rotation of the crankshaft 4 shown in FIG. It is not possible to flow into the oil supply hole 10 of the connecting rod 7 from, but only in the suction stroke between the points c and d in FIG. 7, that is, between the top dead center and the bottom dead center of the piston 2. With this structure, the eccentric portion 12 receives a load on the portion of the eccentric portion 12 where the oil reservoir 15 does not exist during a compression stroke in which a large load is applied from the large end portion 9 of the connecting rod 7.
An oil film pressure is likely to be generated at the sliding portion between the eccentric portion 12 and the large end hole 9, so that abrasion due to metal contact can be suppressed.
【０００７】上述した従来の密閉型圧縮機のコンロッド
７の小端穴８への給油方法の他に、小端穴８にＶ溝を設
けたもの、あるいは小端穴８とピストンピンとに給油の
ための溝が何もついていないもの等がある。In addition to the above-described conventional method for supplying oil to the small end hole 8 of the connecting rod 7 of the hermetic compressor, the small end hole 8 is provided with a V groove, or the small end hole 8 and the piston pin are supplied with oil. There are some things that have no groove for it.
【０００８】図８は従来の密閉型電動圧縮機のコンロッ
ド７の小端穴８にＶ溝が設けられたピストン装置の断面
図である。FIG. 8 is a sectional view of a piston device in which a V-groove is provided in a small end hole 8 of a connecting rod 7 of a conventional hermetic electric compressor.
【０００９】図８において、２１は小端穴８との摺動面
に給油のための溝が設けられていないピストンピンであ
る。２２は小端穴８の前記ピストンピン２２との摺動面
上に、前記小端穴８の軸心方向でかつ給油孔１０と直交
する位置に設けられたＶ溝である。In FIG. 8, reference numeral 21 denotes a piston pin having no groove for oil supply on its sliding surface with the small end hole 8. Reference numeral 22 denotes a V groove provided on the sliding surface of the small end hole 8 with respect to the piston pin 22 in the axial direction of the small end hole 8 and at a position orthogonal to the oil supply hole 10.
【００１０】以上のように構成された密閉型圧縮機につ
いて、以下その動作を説明する。コンロッド７の給油孔
１０を通って小端穴８まで流れたオイル１７は、Ｖ溝２
２を通ってピストン２の中空部５に流出すると共にピス
トンピン２１と小端穴８の摺動部を潤滑する。従って、
ピストンピン１７に円周溝１９を設けたものと同様の効
果が得られる。The operation of the hermetic compressor constructed as described above will be described below. The oil 17 flowing to the small end hole 8 through the oil supply hole 10 of the connecting rod 7 is
It flows out into the hollow portion 5 of the piston 2 through 2 and lubricates the sliding portion between the piston pin 21 and the small end hole 8. Therefore,
The same effect as that obtained by providing the piston pin 17 with the circumferential groove 19 can be obtained.
【００１１】図９は従来の密閉型電動圧縮機のコンロッ
ド７の小端穴８とピストンピン２１とに給油のための溝
が何もついていないピストン装置の断面図である。FIG. 9 is a sectional view of a piston device of the conventional hermetic electric compressor in which the small end hole 8 of the connecting rod 7 and the piston pin 21 have no groove for oil supply.
【００１２】図９において、２１は小端穴８との摺動面
に給油のための溝が設けられていないピストンピンであ
り、かつ小端穴８には上述した様な給油のための溝は設
けられていない。In FIG. 9, reference numeral 21 denotes a piston pin in which a groove for oil supply is not provided on the sliding surface with the small end hole 8, and the small end hole 8 has a groove for oil supply as described above. Is not provided.
【００１３】以上のように構成された密閉型圧縮機につ
いて、以下その動作を説明する。コンロッド７の給油孔
１０を通って小端穴８まで流れたオイル１７は、ピスト
ンピン２１と小端穴８の摺動部を潤滑する。この構造に
より、圧縮行程時に荷重を小端穴８で受ける際、小端穴
８とピストンピン２１との摺動部に円周溝１９あるいは
Ｖ溝２２が設けられているものに比べ、それらの溝から
オイル１７が流出しないので、油膜圧力が発生しやす
い。The operation of the hermetic compressor constructed as described above will be described below. The oil 17 flowing to the small end hole 8 through the oil supply hole 10 of the connecting rod 7 lubricates the sliding portion between the piston pin 21 and the small end hole 8. With this structure, when a load is received by the small end hole 8 during the compression stroke, compared with a structure in which the circumferential groove 19 or the V groove 22 is provided in the sliding portion between the small end hole 8 and the piston pin 21, Since the oil 17 does not flow out from the groove, oil film pressure is likely to occur.
【００１４】[0014]
【発明が解決しようとする課題】しかしながら上記従来
の構成のうち、ピストンピンに円周溝が設けられている
もの及び小端穴にＶ溝が設けられたものは、最も荷重が
大きくなる圧縮行程時において、ピストンピンとコンロ
ッドの小端穴との摺動部の荷重のかかる部分には常にコ
ンロッドの給油孔とピストンピンの円周溝叉は小端穴の
Ｖ溝があることになり、摺動部の油膜圧力が発生しにく
く、金属接触によって摺動部が摩耗してしまうという欠
点があった。However, among the above-mentioned conventional constructions, the one in which the piston pin is provided with the circumferential groove and the one in which the small end hole is provided with the V groove have the compression stroke in which the load becomes the largest. At this time, the sliding part between the piston pin and the small end hole of the connecting rod always has the oil supply hole of the connecting rod and the circumferential groove of the piston pin or the V groove of the small end hole. There is a drawback in that the oil film pressure at the part is less likely to be generated and the sliding part is worn by metal contact.
【００１５】また、上記従来の構成のうち、小端穴とピ
ストンピンとに給油のための溝が何もついていないもの
は、給油のための溝がないためにピストンピンと小端穴
との摺動部への給油量が少なくオイルによる冷却効果が
小さいため、摺動部の温度上昇によってオイル粘度の低
下等の潤滑不良が起こりやすいという欠点があった。Further, among the above-mentioned conventional constructions, the small end hole and the piston pin having no groove for lubrication do not have a groove for lubrication, so that the piston pin and the small end hole slide. Since the amount of oil supplied to the portion is small and the cooling effect by the oil is small, there is a drawback that poor lubrication such as a decrease in oil viscosity easily occurs due to an increase in temperature of the sliding portion.
【００１６】また、密閉容器内の冷媒のとけ込んだオイ
ルが摺動部に送られるまでに気化され、摺動部にオイル
と冷媒ガスとが送り込まれオイルが十分に送られず、摺
動部の油膜圧力が発生しにくく、金属接触によって摺動
部が摩耗してしまうという欠点があった。Further, the oil melted in the refrigerant in the closed container is vaporized by the time it is sent to the sliding part, and the oil and the refrigerant gas are sent to the sliding part and the oil is not sufficiently sent. There is a drawback that the oil film pressure is hard to be generated and the sliding portion is worn by metal contact.
【００１７】本発明は従来の課題を解決するもので、ピ
ストンピンとコンロッドの小端穴との摺動部に油膜圧力
を発生し易くすることによって、また冷媒ガスの発生に
よる潤滑不良をなくし、かつ摺動部への十分な給油量を
確保することによって、摺動部の摩耗を防ぎ、信頼性の
高い密閉型圧縮機とすることを目的とする。The present invention solves the conventional problems by making it easy to generate an oil film pressure at the sliding portion between the piston pin and the small end hole of the connecting rod, and eliminating the poor lubrication due to the generation of refrigerant gas, and An object of the present invention is to provide a highly reliable hermetic compressor by preventing the sliding portion from being worn by ensuring a sufficient amount of oil supply to the sliding portion.
【００１８】[0018]
【課題を解決するための手段】この目的を達成するため
本発明の密閉型圧縮機は、ピストンと、一端に小端穴を
他端に大端穴を有するコンロッドと、コンロッド内を通
り、小端穴と大端穴とを連通し、かつ小端穴の軸心と大
端穴の軸心とを通る平面上に両端が開口する給油孔と、
小端穴摺動面とコンロッド外表面を連通する排油孔と、
小端穴に摺動自在に収納され、かつピストンに固定され
たピストンピンと、ピストンが上死点から下死点へ運動
する間に給油孔と排油孔を連通する位置にピストンピン
の円周方向に設けられた半円周状の給油溝とから構成さ
れている。In order to achieve this object, a hermetic compressor of the present invention comprises a piston, a connecting rod having a small end hole at one end and a large end hole at the other end, and a small rod passing through the connecting rod. An oil supply hole that communicates the end hole and the large end hole, and has both ends open on a plane that passes through the axis of the small end hole and the axis of the large end hole,
An oil drain hole that connects the small end hole sliding surface to the connecting rod outer surface,
The piston pin, which is slidably housed in the small end hole and is fixed to the piston, and the circumference of the piston pin at the position where the oil supply hole and the oil discharge hole communicate while the piston moves from top dead center to bottom dead center. And a semicircular oil supply groove provided in the direction.
【００１９】また、ピストンと、一端に小端穴を他端に
大端穴を有するコンロッドと、コンロッド内を通り、小
端穴と大端穴とを連通し、かつ小端穴の軸心と大端穴の
軸心とを通る平面上に両端が開口する給油孔と、給油孔
の断面積より小さな断面積を有し、かつ下端が給油孔に
連通し、上端がコンロッド外表面の上部に開口するコン
ロッド内に設けられた少なくとも１つの冷媒ガス排出孔
と、小端穴に摺動自在に収納され、かつピストンに固定
されたピストンピンとから構成されている。Further, the piston, the connecting rod having a small end hole at one end and the large end hole at the other end, the small end hole and the large end hole are communicated with each other through the connecting rod, and the axial center of the small end hole is formed. It has a lubrication hole with both ends open on a plane that passes through the axial center of the large end hole, and a cross-sectional area smaller than the cross-sectional area of the lubrication hole, the lower end communicates with the lubrication hole, and the upper end is above the outer surface of the connecting rod. It comprises at least one refrigerant gas discharge hole provided in an open connecting rod, and a piston pin slidably accommodated in the small end hole and fixed to the piston.
【００２０】また、ピストンと、一端に小端穴を他端に
大端穴を有するコンロッドと、コンロッド内を通り、小
端穴と大端穴とを連通し、かつ小端穴の軸心と大端穴の
軸心とを通る平面上に両端が開口する給油孔と、給油孔
の断面積より小さな断面積を有し、かつ下端が給油孔に
連通し、上端が下端よりもピストン側でコンロッド外表
面の上部に開口するコンロッド内に設けられた少なくと
も１つの冷媒ガス排出孔と、小端穴に摺動自在に収納さ
れ、かつピストンに固定されたピストンピンとから構成
されている。Further, the piston, the connecting rod having a small end hole at one end and the large end hole at the other end, the small end hole and the large end hole are communicated with each other through the inside of the connecting rod, and the axial center of the small end hole is formed. It has a lubrication hole with both ends open on a plane that passes through the axis of the large end hole, and a cross-sectional area smaller than the cross-sectional area of the lubrication hole, the lower end communicates with the lubrication hole, and the upper end is closer to the piston than the lower end. It is composed of at least one refrigerant gas discharge hole provided in the connecting rod that is open at the upper part of the outer surface of the connecting rod, and a piston pin slidably accommodated in the small end hole and fixed to the piston.
【００２１】また、ピストンと、一端に小端穴を他端に
大端穴を有するコンロッドと、コンロッド内を通り、小
端穴と大端穴とを連通し、かつ小端穴の軸心と大端穴の
軸心とを通る平面上に両端が開口する給油孔と、小端穴
摺動面とコンロッド外表面を連通する排油孔と、給油孔
の断面積より小さな断面積を有し、かつ下端が給油孔に
連通し、上端が下端よりもピストン側でコンロッド外表
面の上部に開口するコンロッド内に設けられた少なくと
も１つの冷媒ガス排出孔と、小端穴に摺動自在に収納さ
れ、かつピストンに固定されたピストンピンと、ピスト
ンが上死点から下死点へ運動する間に給油孔と排油孔を
連通する位置にピストンピンの円周方向に設けられた半
円周状の給油溝とから構成されている。Further, the piston, the connecting rod having a small end hole at one end and the large end hole at the other end, the small end hole and the large end hole are communicated with each other through the inside of the connecting rod, and the axial center of the small end hole is formed. It has an oil supply hole with both ends open on a plane that passes through the axis of the large end hole, an oil discharge hole that connects the sliding surface of the small end hole with the outer surface of the connecting rod, and a cross-sectional area smaller than the cross-sectional area of the oil supply hole. , And at least one refrigerant gas discharge hole provided in the connecting rod whose lower end communicates with the oil supply hole and whose upper end opens to the upper part of the connecting rod outer surface on the piston side with respect to the lower end, and is slidably accommodated in the small end hole. And a semi-circular shape provided in the circumferential direction of the piston pin at the position where the piston pin fixed to the piston communicates with the oil supply hole and the oil discharge hole while the piston moves from the top dead center to the bottom dead center. And the oil supply groove of.
【００２２】[0022]
【作用】本発明の密閉型圧縮機は上記した構成によっ
て、ピストンピンとコンロッドの小端穴との摺動部に大
きな荷重のかかる圧縮行程時には、ピストンピンは給油
溝の無い部分で荷重を受けるので摺動部に油膜圧力を発
生し易く、摺動部の摩耗をしにくくすることができる。
また、吸入行程時にはコンロッドの給油孔とピストンピ
ンの半円周状の給油溝とが一致するので、従来の円周溝
仕様のものと同様に小端穴への給油を行うことができ
る。従って、オイルによる冷却効果が得られ、摺動部の
温度上昇によるオイルの粘度低下等の潤滑不良が防止で
き摺動部の摩耗をしにくくすることができる。In the hermetic compressor of the present invention, the piston pin receives a load at a portion having no oil supply groove during a compression stroke in which a large load is applied to the sliding portion between the piston pin and the small end hole of the connecting rod. The oil film pressure is easily generated in the sliding portion, and the sliding portion is less likely to wear.
Further, since the oil supply hole of the connecting rod and the semicircular oil supply groove of the piston pin coincide with each other during the suction stroke, it is possible to perform oil supply to the small end hole as in the conventional circular groove specification. Therefore, the cooling effect of the oil can be obtained, and the lubrication failure such as the decrease of the viscosity of the oil due to the temperature rise of the sliding portion can be prevented and the sliding portion can be less likely to be worn.
【００２３】また、コンロッドの給油孔内に溜まったオ
イル以外の冷媒ガスが冷媒ガス排出孔から排出されコン
ロッドの小端穴とピストンピンの摺動部に送り込まれる
冷媒ガスの量が低減できコンロッドの小端穴とピストン
ピンの摺動部に油膜圧力が発生し易くなり、小端穴及び
ピストンピンの摺動部を摩耗しにくくすることができ
る。Further, the refrigerant gas other than the oil accumulated in the oil supply hole of the connecting rod is discharged from the refrigerant gas discharge hole, and the amount of the refrigerant gas sent to the small end hole of the connecting rod and the sliding portion of the piston pin can be reduced, so that the connecting rod can be reduced. An oil film pressure is likely to be generated at the sliding portion between the small end hole and the piston pin, and the sliding portion between the small end hole and the piston pin can be less likely to wear.
【００２４】また更に、斜めに設けられた冷媒ガス排出
孔のコンロッド外部への開口部がピストン側に向いてい
ることにより、冷媒ガスが冷媒ガス排出孔から排出され
る際に、冷媒ガス排出孔から漏れるオイルをシリンダー
部や小端穴部に飛ばし、直接シリンダー部や小端穴部へ
の給油を行うことができるので、ピストンとシリンダー
の摺動部や小端穴とピストンピンの摺動部を摩耗しにく
くすることができる。Furthermore, since the opening of the obliquely provided refrigerant gas discharge hole to the outside of the connecting rod faces the piston side, when the refrigerant gas is discharged from the refrigerant gas discharge hole, the refrigerant gas discharge hole is formed. The oil leaking from the cylinder can be sprayed to the cylinder or small end hole to directly supply oil to the cylinder or small end hole, so the sliding part between the piston and cylinder or the sliding part between the small end hole and piston pin. Can be made hard to wear.
【００２５】また更に、圧縮行程中でのピストンピンの
摺動面のオイル中から発生した冷媒ガスが給油孔内に逆
流したときでも、冷媒ガス排出孔から冷媒ガスが排出さ
れ給油時に再び冷媒ガスが摺動部に流れ込まず、安定し
たオイルの供給が行えるので、摺動部の摩耗をしにくく
することができる。Furthermore, even when the refrigerant gas generated from the oil on the sliding surface of the piston pin during the compression stroke flows back into the oil supply hole, the refrigerant gas is discharged from the refrigerant gas discharge hole and again when the oil is supplied. Does not flow into the sliding portion, and stable oil supply can be performed, so that the sliding portion is less likely to wear.
【００２６】[0026]
【実施例】以下、本発明の密閉型圧縮機の第１の実施例
について図面を参照しながら説明する。尚、従来と同一
構成については、同一符号を付して詳細な説明を省略す
る。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the hermetic compressor of the present invention will be described below with reference to the drawings. It should be noted that the same components as those of the related art are denoted by the same reference numerals and detailed description thereof will be omitted.
【００２７】図１は本発明の密閉型圧縮機の第１の実施
例を示すものである。図１において、２３はピストンピ
ンで、２４はピストンピン２３の小端穴８との摺動面上
に、ピストンピン２３の表面に円周方向で、かつピスト
ン２が上死点から下死点へ運動する間に給油孔１０と排
油孔１１を連通する位置に設けられた半円周状の給油溝
である。FIG. 1 shows a first embodiment of the hermetic compressor of the present invention. In FIG. 1, 23 is a piston pin, 24 is a sliding surface with respect to the small end hole 8 of the piston pin 23, the surface of the piston pin 23 is a circumferential direction, and the piston 2 is from a top dead center to a bottom dead center. It is a semicircular oil supply groove provided at a position where the oil supply hole 10 and the oil discharge hole 11 communicate with each other during the movement to.
【００２８】以上のように構成された密閉型圧縮機につ
いて、以下その動作を説明する。ピストンピン２３とコ
ンロッド７の小端穴８との摺動部に大きな荷重のかかる
圧縮行程時には、給油孔１０の小端穴８への開口部はピ
ストン２の軸心に対して半円周状の給油溝２４と反対側
に位置する。従って、その際ピストンピン２３は半円周
状の給油溝２４の無い部分でコンロッド７の小端穴８と
接触し、その部分で荷重を受けることになるので、従来
のピストンピン１８の円周溝が設けられているものに比
べ、摺動部に油膜圧力を発生し易く摺動部の摩耗をしに
くくすることができる。また、吸入行程時には、コンロ
ッド７の給油孔１０と排油孔１１がピストンピン２３の
半円周状の給油溝２４と一致して連通し、従来の円周溝
仕様のものと同様に小端穴８への給油を行うことができ
る。従って、オイルによる冷却効果が得られ、摺動部の
温度上昇によるオイルの粘度低下等の潤滑不良が防止で
き摺動部の摩耗をしにくくすることができる。The operation of the hermetic compressor constructed as described above will be described below. During a compression stroke in which a large load is applied to the sliding portion between the piston pin 23 and the small end hole 8 of the connecting rod 7, the opening of the oil supply hole 10 to the small end hole 8 has a semicircular shape with respect to the axial center of the piston 2. Is located on the opposite side of the oil supply groove 24. Therefore, at that time, the piston pin 23 comes into contact with the small end hole 8 of the connecting rod 7 at a portion without the semicircular oil supply groove 24 and receives a load at that portion. As compared with the case where the groove is provided, the oil film pressure is easily generated in the sliding portion, and the sliding portion is less likely to be worn. Further, during the suction stroke, the oil supply hole 10 and the oil discharge hole 11 of the connecting rod 7 communicate with the semicircular oil supply groove 24 of the piston pin 23 so as to communicate with each other. The hole 8 can be refueled. Therefore, the cooling effect of the oil can be obtained, and the lubrication failure such as the decrease of the viscosity of the oil due to the temperature rise of the sliding portion can be prevented and the sliding portion can be less likely to be worn.
【００２９】以上のように本実施例の密閉型圧縮機は、
ピストンピン２３と、ピストンピン２３の小端穴８との
摺動面上に、ピストンピン２３の表面に円周方向で、か
つピストン２が上死点から下死点へ運動する間に給油孔
１０と排油孔１１とが連通する位置に設けられた半円周
状の給油溝２４で構成しているので、従来のピストンピ
ン１８に円周溝が設けられているものに比べ、圧縮行程
時にはピストンピン２３は半円周状の給油溝２４の無い
部分で荷重を受けるので摺動部に油膜圧力を発生し易
く、摺動部の摩耗をしにくくすることができる。また、
吸入行程時にはコンロッド７の給油孔１０と排油孔１１
とがピストンピン２３の半円周状の給油溝２４と一致し
て、従来の円周溝仕様のものと同様に小端穴８への給油
を行うことができるので、オイルによる冷却効果が得ら
れ、摺動部の温度上昇によるオイルの粘度低下等の潤滑
不良が防止でき摺動部の摩耗をしにくくすることができ
る。As described above, the hermetic compressor of this embodiment is
On the sliding surface between the piston pin 23 and the small end hole 8 of the piston pin 23, the oil supply hole is circumferentially formed on the surface of the piston pin 23 and while the piston 2 moves from the top dead center to the bottom dead center. 10 and the oil drain hole 11 are formed by a semicircular oil supply groove 24 provided at a position where they communicate with each other, the compression stroke is greater than that of the conventional piston pin 18 provided with a circumferential groove. At times, the piston pin 23 receives a load in a portion without the semicircular oil supply groove 24, so that an oil film pressure is likely to be generated in the sliding portion, and the sliding portion is less likely to be worn. Also,
During the intake stroke, the oil supply hole 10 and the oil discharge hole 11 of the connecting rod 7
And the same as the semicircular oil supply groove 24 of the piston pin 23, and the oil can be supplied to the small end hole 8 in the same manner as the conventional circular groove specification, so that the cooling effect by the oil can be obtained. As a result, it is possible to prevent poor lubrication such as a decrease in oil viscosity due to an increase in the temperature of the sliding portion, and it is possible to prevent the sliding portion from wearing.
【００３０】なお、本実施例において半円周状の給油溝
２４としたが、半円周状の給油溝２４は圧縮行程中に半
円周状の給油溝２４と給油孔１０が連通することがな
く、かつ吸入行程時に給油孔１０と排油孔１１が連通す
れば円周上のどの位置にあっても良い。Although the semicircular oil supply groove 24 is used in this embodiment, the semicircular oil supply groove 24 is such that the semicircular oil supply groove 24 and the oil supply hole 10 communicate with each other during the compression stroke. It may be located at any position on the circumference as long as it is not present and the oil supply hole 10 and the oil discharge hole 11 communicate with each other during the suction stroke.
【００３１】次に、本発明の密閉型圧縮機の第２の実施
例について図面を参照しながら説明する。尚、従来例及
び第１の実施例と同一構成については、同一符号を付し
て詳細な説明を省略する。Next, a second embodiment of the hermetic compressor of the present invention will be described with reference to the drawings. The same components as those in the conventional example and the first embodiment are designated by the same reference numerals and detailed description thereof will be omitted.
【００３２】図２は本発明の密閉型圧縮機の第２の実施
例を示すものである。図２において、２５は給油孔の断
面積より小さな断面積を有し、かつ下端が給油孔１０に
連通し、上端がコンロッド７外表面の上部に開口するコ
ンロッド７内に設けられた少なくとも１つの冷媒ガス排
出孔である。FIG. 2 shows a second embodiment of the hermetic compressor of the present invention. In FIG. 2, reference numeral 25 denotes a cross-sectional area smaller than the cross-sectional area of the oil supply hole, the lower end of which communicates with the oil supply hole 10 and the upper end of which is provided in at least one of the connecting rods 7 which is open above the outer surface of the connecting rod 7. It is a refrigerant gas discharge hole.
【００３３】以上のように構成された密閉型圧縮機につ
いて、以下その動作を説明する。オイル１７は給油管１
６により吸い上げられオイル溜まり１５に送られる。送
り込まれ溜まったオイル１７は吸入行程時に給油孔１０
を通りコンロッド７の小端穴８とピストンピン２１の摺
動部に給油される。このとき、オイル１７には冷媒が溶
け込んでおり、小端穴８にオイル１７が到達するまでに
偏心部１２やコンロッド７からの受熱によるオイル１７
の温度上昇や、偏心部給油孔１５やオイル溜まり１６内
などの給油通路内での圧力降下により、オイル１７に溶
け込んだ冷媒が気化し、給油孔１０を通るオイル１７は
気泡が混ざった気泡混入オイルとなる。気泡混入オイル
の冷媒ガスは小端穴８に達するまでに冷媒ガス排出孔２
５より排出される。このとき冷媒ガス排出孔２５は給油
孔１０の断面積より小さい断面積を有し、かつコンロッ
ド７外表面の上部に開口されているため、給油孔１０内
の気泡混入オイルのオイルをあまり排出することなく、
給油孔内の上側を流れている冷媒ガスを排出する。従っ
て、コンロッド７の小端穴８とピストンピン２１の摺動
部に流れ込む冷媒ガスの量が低減できコンロッド７の小
端穴８とピストンピン２１の摺動部に油膜圧力が発生し
易く、小端穴８及びピストンピン２１の摺動部を摩耗し
にくくすることができる。The operation of the hermetic compressor constructed as described above will be described below. Oil 17 is the oil supply pipe 1
It is sucked up by 6 and sent to the oil sump 15. The oil 17 sent in and accumulated is the oil supply hole 10 during the suction stroke.
Through the small end hole 8 of the connecting rod 7 and the sliding portion of the piston pin 21. At this time, the refrigerant has melted into the oil 17, and the oil 17 due to the heat received from the eccentric portion 12 and the connecting rod 7 before the oil 17 reaches the small end hole 8.
Due to the temperature rise of the oil and the pressure drop in the oil supply passages such as the eccentric part oil supply hole 15 and the oil sump 16, the refrigerant dissolved in the oil 17 is vaporized, and the oil 17 passing through the oil supply hole 10 is mixed with bubbles. It becomes oil. By the time the refrigerant gas of the air-blended oil reaches the small end hole 8, the refrigerant gas discharge hole 2
It is discharged from 5. At this time, since the refrigerant gas discharge hole 25 has a cross-sectional area smaller than the cross-sectional area of the oil supply hole 10 and is opened at the upper part of the outer surface of the connecting rod 7, the oil of the air bubble-mixed oil in the oil supply hole 10 is discharged much. Without
The refrigerant gas flowing in the upper side of the oil supply hole is discharged. Therefore, the amount of the refrigerant gas flowing into the sliding portion between the small end hole 8 of the connecting rod 7 and the piston pin 21 can be reduced, and the oil film pressure is easily generated in the sliding portion between the small end hole 8 of the connecting rod 7 and the piston pin 21. It is possible to make the sliding portions of the end hole 8 and the piston pin 21 less likely to wear.
【００３４】以上のように本実施例の密閉型圧縮機は、
給油孔の断面積より小さな断面積を有し、かつ下端が給
油孔１０に連通し、上端がコンロッド７外表面の上部に
開口するコンロッド７内に設けられた少なくとも１つの
冷媒ガス排出孔２５で構成されているので、給油孔１０
内の気泡混入オイルのオイルをあまり排出することな
く、給油孔内の上側を流れている冷媒ガスを排出する。
従って、コンロッド７の小端穴８とピストンピン２１の
摺動部に流れ込む冷媒ガスの量が低減できコンロッド７
の小端穴８とピストンピン２１の摺動部に油膜圧力が発
生し易く、小端穴８及びピストンピン２１の摺動部を摩
耗しにくくすることができる。As described above, the hermetic compressor of this embodiment is
At least one refrigerant gas discharge hole 25 provided in the connecting rod 7 having a cross-sectional area smaller than that of the oil supply hole, the lower end communicating with the oil supply hole 10, and the upper end opening to the upper part of the outer surface of the connecting rod 7. Since it is configured, the oil supply hole 10
The refrigerant gas flowing in the upper side of the oil supply hole is discharged without discharging much of the oil mixed with bubbles inside.
Therefore, the amount of the refrigerant gas flowing into the small end hole 8 of the connecting rod 7 and the sliding portion of the piston pin 21 can be reduced, and the connecting rod 7 can be reduced.
The oil film pressure is easily generated in the sliding portion between the small end hole 8 and the piston pin 21, and the sliding portion between the small end hole 8 and the piston pin 21 can be less likely to wear.
【００３５】なお、本実施例において冷媒ガス排出孔２
５は１つとしたが、冷媒ガス排出孔２５は複数個として
もよい。In this embodiment, the refrigerant gas discharge hole 2
Although the number 5 is one, the refrigerant gas discharge holes 25 may be plural.
【００３６】次に、本発明の密閉型圧縮機の第３の実施
例について図面を参照しながら説明する。尚、従来例、
第１及び第２の実施例と同一構成については、同一符号
を付して詳細な説明を省略する。Next, a third embodiment of the hermetic compressor of the present invention will be described with reference to the drawings. Incidentally, the conventional example,
The same components as those in the first and second embodiments are designated by the same reference numerals and detailed description thereof will be omitted.
【００３７】図３は本発明の密閉型圧縮機の第３の実施
例を示すものである。図３において、２６は給油孔１０
の断面積より小さな断面積を有し、かつ下端が給油孔１
０に連通し、上端が下端よりもピストン２側でコンロッ
ド７外表面の上部に開口するコンロッド７内に設けられ
た少なくとも１つの冷媒ガス排出孔である。FIG. 3 shows a third embodiment of the hermetic compressor of the present invention. In FIG. 3, reference numeral 26 is an oil supply hole 10.
Has a smaller cross-sectional area than the cross-sectional area of the
And at least one refrigerant gas discharge hole provided in the connecting rod 7 which communicates with 0 and whose upper end is open to the upper part of the outer surface of the connecting rod 7 on the piston 2 side with respect to the lower end.
【００３８】以上のように構成された密閉型圧縮機につ
いて、以下その動作を説明する。オイル１７は給油管１
６により吸い上げられオイル溜まり１５に送られる。送
り込まれ溜まったオイル１７は吸入行程時に給油孔１０
を通りコンロッド７の小端穴８とピストンピン２１の摺
動部に給油される。このとき、オイル１７には冷媒が溶
け込んでおり、小端穴８にオイル１７が到達するまでに
偏心部１２やコンロッド７からの受熱によるオイル１７
の温度上昇や、偏心部給油孔１５やオイル溜まり１６内
などの給油通路内での圧力降下により、オイル１７に溶
け込んだ冷媒が気化し、給油孔１０を通るオイル１７は
気泡が混ざった気泡混入オイルとなる。気泡混入オイル
の冷媒ガスは小端穴８に達するまでに冷媒ガス排出孔２
６より排出される。このとき冷媒ガス排出孔２６は給油
孔１０の断面積より小さい断面積を有し、かつ下端が給
油孔１０に連通し、上端が下端よりもピストン２側でコ
ンロッド７外表面の上部に開口されているため、給油孔
１０内の気泡混入オイルの冷媒ガスと一緒に排出される
少量のオイル１７を吸入行程時に発生する慣性力により
飛ばし、シリンダー１や小端穴８部に供給する。従っ
て、コンロッド７の小端穴８とピストンピン２１の摺動
部に流れ込む冷媒ガスの量が低減できるとともに、シリ
ンダー１部や小端穴８部にオイルを直接供給することが
でき、小端穴８とピストンピン２１の摺動部、及びシリ
ンダー１とピストン２の摺動部に油膜圧力が発生し易
く、摺動部の摩耗をしにくくすることができる。The operation of the hermetic compressor constructed as described above will be described below. Oil 17 is the oil supply pipe 1
It is sucked up by 6 and sent to the oil sump 15. The oil 17 sent in and accumulated is the oil supply hole 10 during the suction stroke.
Through the small end hole 8 of the connecting rod 7 and the sliding portion of the piston pin 21. At this time, the refrigerant has melted into the oil 17, and the oil 17 due to the heat received from the eccentric portion 12 and the connecting rod 7 before the oil 17 reaches the small end hole 8.
Due to the temperature rise of the oil and the pressure drop in the oil supply passages such as the eccentric part oil supply hole 15 and the oil sump 16, the refrigerant dissolved in the oil 17 is vaporized, and the oil 17 passing through the oil supply hole 10 is mixed with bubbles. It becomes oil. By the time the refrigerant gas of the air-blended oil reaches the small end hole 8, the refrigerant gas discharge hole 2
It is discharged from 6. At this time, the refrigerant gas discharge hole 26 has a cross-sectional area smaller than the cross-sectional area of the oil supply hole 10, the lower end communicates with the oil supply hole 10, and the upper end is opened above the outer surface of the connecting rod 7 closer to the piston 2 than the lower end. Therefore, a small amount of oil 17 discharged together with the refrigerant gas of the air-blended oil in the oil supply hole 10 is blown off by the inertial force generated during the suction stroke, and is supplied to the cylinder 1 and the small end hole 8. Therefore, the amount of the refrigerant gas flowing into the small end hole 8 of the connecting rod 7 and the sliding portion of the piston pin 21 can be reduced, and oil can be directly supplied to the cylinder 1 part and the small end hole 8 part. The oil film pressure is likely to be generated in the sliding portion between 8 and the piston pin 21 and the sliding portion between the cylinder 1 and the piston 2, so that the sliding portion can be less likely to wear.
【００３９】以上のように本実施例の密閉型圧縮機は、
給油孔１０の断面積より小さな断面積を有し、かつ下端
が給油孔１０に連通し、上端が下端よりもピストン２側
でコンロッド７外表面の上部に開口するコンロッド７内
に設けられた少なくとも１つの冷媒ガス排出孔２６で構
成されているので、コンロッド７の小端穴８とピストン
ピン２１の摺動部に流れ込む冷媒ガスの量が低減できる
とともに、シリンダー１部や小端穴８部にオイルを直接
供給することができ、小端穴８とピストンピン２１の摺
動部、及びシリンダー１とピストン２の摺動部に油膜圧
力が発生し易く、摺動部の摩耗をしにくくすることがで
きる。As described above, the hermetic compressor of this embodiment is
At least provided in the connecting rod 7 having a cross-sectional area smaller than that of the oil supply hole 10, a lower end communicating with the oil supply hole 10, and an upper end opening to an upper portion of the outer surface of the connecting rod 7 on the piston 2 side from the lower end. Since it is composed of one refrigerant gas discharge hole 26, the amount of refrigerant gas flowing into the small end hole 8 of the connecting rod 7 and the sliding portion of the piston pin 21 can be reduced, and at the same time, in the cylinder 1 part and the small end hole 8 part. Oil can be directly supplied, oil film pressure is likely to be generated in the sliding portion between the small end hole 8 and the piston pin 21, and the sliding portion between the cylinder 1 and the piston 2, and abrasion of the sliding portion is less likely to occur. You can
【００４０】次に、本発明の密閉型圧縮機の第４の実施
例について図面を参照しながら説明する。尚、従来例、
第１、第２及び第３の実施例と同一構成については、同
一符号を付して詳細な説明を省略する。Next, a fourth embodiment of the hermetic compressor of the present invention will be described with reference to the drawings. Incidentally, the conventional example,
The same components as those of the first, second and third embodiments are designated by the same reference numerals and detailed description thereof will be omitted.
【００４１】図４は本発明の密閉型圧縮機の第４の実施
例を示すもので、図５は図４のＢ−Ｂ断面図である。FIG. 4 shows a fourth embodiment of the hermetic compressor of the present invention, and FIG. 5 is a sectional view taken along line BB of FIG.
【００４２】図４、図５において、２７は給油孔１０の
断面積より小さな断面積を有し、かつ下端が給油孔１０
に連通し、上端が下端よりもピストン２側でコンロッド
７外表面の上部に開口するコンロッド７内に設けられた
少なくとも１つの冷媒ガス排出孔で、２８はピストンピ
ンで、２９はピストンピン２８の小端穴８との摺動面上
に、ピストンピン２８の表面に円周方向で、かつピスト
ン２が上死点から下死点へ運動する間に給油孔１０と排
油孔１１を連通する位置に設けられた半円周状の給油溝
である。In FIGS. 4 and 5, 27 has a cross-sectional area smaller than the cross-sectional area of the oil supply hole 10, and the lower end has the oil-supply hole 10 at its lower end.
And at least one refrigerant gas discharge hole provided in the connecting rod 7 whose upper end is open to the upper part of the outer surface of the connecting rod 7 on the piston 2 side with respect to the lower end, 28 is a piston pin, and 29 is a piston pin 28. The oil supply hole 10 and the oil discharge hole 11 are communicated with each other on the sliding surface with the small end hole 8 on the surface of the piston pin 28 in the circumferential direction and while the piston 2 moves from the top dead center to the bottom dead center. It is a semicircular oil supply groove provided at a position.
【００４３】以上のように構成された密閉型圧縮機は第
１及び第３の実施例での効果に加えて、圧縮行程中での
ピストンピン２８の摺動面のオイル１６中から発生した
冷媒ガスが給油孔１０内に逆流したときでも冷媒ガスが
冷媒ガス排出孔２７から排出することができる。従っ
て、吸入行程時の給油時に、ピストンピン２８の摺動面
から発生した冷媒ガスが給油孔１０から再び摺動部に流
れ込むことを低減でき、安定したオイルの供給を行うこ
とができる。In addition to the effects of the first and third embodiments, the hermetic compressor constructed as described above has a refrigerant generated from the oil 16 on the sliding surface of the piston pin 28 during the compression stroke. Even when the gas flows back into the oil supply hole 10, the refrigerant gas can be discharged from the refrigerant gas discharge hole 27. Therefore, during refueling during the suction stroke, the refrigerant gas generated from the sliding surface of the piston pin 28 can be prevented from flowing into the sliding portion from the refueling hole 10 again, and stable oil supply can be performed.
【００４４】以上のように本実施例の密閉型圧縮機は、
給油孔１０の断面積より小さな断面積を有し、かつ下端
が給油孔１０に連通し、上端が下端よりもピストン２側
でコンロッド７外表面の上部に開口するコンロッド７内
に設けられた少なくとも１つの冷媒ガス排出孔２７と、
ピストンピン２８と、ピストンピン２８の小端穴８との
摺動面上に、ピストンピン２８の表面に円周方向で、か
つピストン２が上死点から下死点へ運動する間に給油孔
１０と排油孔１１を連通する位置に設けられた半円周状
の給油溝２９で構成しているので、第１及び第３の実施
例での効果に加えて、圧縮行程中でのピストンピン２８
の摺動面のオイル１６中から発生した冷媒ガスが給油孔
１０内に逆流したときでも冷媒ガスを冷媒ガス排出孔２
７から排出することができる。従って、吸入行程時の給
油時に、ピストンピン２８の摺動面から発生した冷媒ガ
スが給油孔１０から再び摺動部に流れ込むことを低減で
き、安定したオイルの供給を行うことができる。As described above, the hermetic compressor of this embodiment is
At least provided in the connecting rod 7 having a cross-sectional area smaller than that of the oil supply hole 10, a lower end communicating with the oil supply hole 10, and an upper end opening to an upper portion of the outer surface of the connecting rod 7 on the piston 2 side from the lower end. One refrigerant gas discharge hole 27,
On the sliding surface between the piston pin 28 and the small end hole 8 of the piston pin 28, an oil supply hole is formed on the surface of the piston pin 28 in the circumferential direction and while the piston 2 moves from the top dead center to the bottom dead center. 10 and the oil drain hole 11 are formed by a semicircular oil supply groove 29 provided at a position communicating with each other, the piston in the compression stroke is obtained in addition to the effects of the first and third embodiments. Pin 28
Even when the refrigerant gas generated from the oil 16 on the sliding surface of the refrigerant flows back into the oil supply hole 10, the refrigerant gas is discharged through the refrigerant gas discharge hole 2
It can be discharged from 7. Therefore, during refueling during the suction stroke, the refrigerant gas generated from the sliding surface of the piston pin 28 can be prevented from flowing into the sliding portion from the refueling hole 10 again, and stable oil supply can be performed.
【００４５】[0045]
【発明の効果】以上説明したように本発明は、ピストン
と、一端に小端穴を他端に大端穴を有するコンロッド
と、コンロッド内を通り、小端穴と大端穴とを連通し、
かつ小端穴の軸心と大端穴の軸心とを通る平面上に両端
が開口する給油孔と、小端穴摺動面とコンロッド外表面
を連通する排油孔と、小端穴に摺動自在に収納され、か
つピストンに固定されたピストンピンと、ピストンが上
死点から下死点へ運動する間に給油孔と排油孔を連通す
る位置にピストンピンの円周方向に設けられた半円周状
の給油溝とで構成されているので、ピストンピンとコン
ロッドの小端穴との摺動部に大きな荷重のかかる圧縮行
程時には、ピストンピンは給油溝の無い部分で荷重を受
けるので摺動部に油膜圧力を発生し易く、摺動部の摩耗
をしにくくすることができる。また、吸入行程時にはコ
ンロッドの給油孔とピストンピンの半円周状の給油溝と
が一致するので、従来の円周溝仕様のものと同様に小端
穴への給油を行うことができる。従って、オイルによる
冷却効果が得られ、摺動部の温度上昇によるオイルの粘
度低下等の潤滑不良が防止でき摺動部の摩耗をしにくく
することができる。As described above, according to the present invention, the piston, the connecting rod having the small end hole at one end and the large end hole at the other end, the small end hole and the large end hole are communicated with each other through the connecting rod. ,
In addition, an oil supply hole with both ends open on a plane that passes through the axis of the small end hole and the axis of the large end hole, an oil drain hole that connects the sliding surface of the small end hole with the outer surface of the connecting rod, and the small end hole A piston pin, which is slidably housed and fixed to the piston, is provided in the circumferential direction of the piston pin at a position that connects the oil supply hole and the oil discharge hole while the piston moves from top dead center to bottom dead center. Since it is configured with a semicircular oil supply groove, the piston pin receives the load in the part without the oil supply groove during the compression stroke in which a large load is applied to the sliding part between the piston pin and the small end hole of the connecting rod. The oil film pressure is easily generated in the sliding portion, and the sliding portion is less likely to wear. Further, since the oil supply hole of the connecting rod and the semicircular oil supply groove of the piston pin coincide with each other during the suction stroke, it is possible to perform oil supply to the small end hole as in the conventional circular groove specification. Therefore, the cooling effect of the oil can be obtained, and the lubrication failure such as the decrease of the viscosity of the oil due to the temperature rise of the sliding portion can be prevented and the sliding portion can be less likely to be worn.
【００４６】また、ピストンと、一端に小端穴を他端に
大端穴を有するコンロッドと、コンロッド内を通り、小
端穴と大端穴とを連通し、かつ小端穴の軸心と大端穴の
軸心とを通る平面上に両端が開口する給油孔と、給油孔
の断面積より小さな断面積を有し、かつ下端が給油孔に
連通し、上端がコンロッド外表面の上部に開口するコン
ロッド内に設けられた少なくとも１つの冷媒ガス排出孔
と、小端穴に摺動自在に収納され、かつピストンに固定
されたピストンピンとから構成されているので、コンロ
ッドの給油孔内に溜まったオイル以外の冷媒ガスが冷媒
ガス排出孔から排出されコンロッドの小端穴とピストン
ピンの摺動部に送り込まれる冷媒ガスの量が低減できコ
ンロッドの小端穴とピストンピンの摺動部に油膜圧力が
発生し易くなり、小端穴及びピストンピンの摺動部を摩
耗しにくくすることができる。Further, the piston, the connecting rod having a small end hole at one end and the large end hole at the other end, the small end hole and the large end hole are communicated with each other through the connecting rod, and the axial center of the small end hole is formed. It has a lubrication hole with both ends open on a plane that passes through the axial center of the large end hole, and a cross-sectional area smaller than the cross-sectional area of the lubrication hole, the lower end communicates with the lubrication hole, and the upper end is above the outer surface of the connecting rod. Since it is composed of at least one refrigerant gas discharge hole provided in the opening connecting rod and a piston pin slidably accommodated in the small end hole and fixed to the piston, it is accumulated in the oil supply hole of the connecting rod. The refrigerant gas other than oil is discharged from the refrigerant gas discharge hole and the amount of refrigerant gas sent to the sliding part of the connecting rod's small end hole and piston pin can be reduced, and an oil film is formed on the sliding part of the connecting rod's small end hole and piston pin. Pressure is more likely to occur, It can be difficult to abrade the sliding portions of the end hole and the piston pin.
【００４７】また、ピストンと、一端に小端穴を他端に
大端穴を有するコンロッドと、コンロッド内を通り、小
端穴と大端穴とを連通し、かつ小端穴の軸心と大端穴の
軸心とを通る平面上に両端が開口する給油孔と、給油孔
の断面積より小さな断面積を有し、かつ下端が給油孔に
連通し、上端が下端よりもピストン側でコンロッド外表
面の上部に開口するコンロッド内に設けられた少なくと
も１つの冷媒ガス排出孔と、小端穴に摺動自在に収納さ
れ、かつピストンに固定されたピストンピンとから構成
されているので、冷媒ガスが冷媒ガス排出孔から排出さ
れる際に、冷媒ガス排出孔から漏れるオイルをシリンダ
ー部や小端穴部に飛ばし、直接シリンダー部や小端穴部
への給油を行うことができるので、ピストンとシリンダ
ーの摺動部や小端穴とピストンピンの摺動部を摩耗しに
くくすることができる。Further, the piston, the connecting rod having a small end hole at one end and the large end hole at the other end, the small end hole and the large end hole are communicated with each other through the connecting rod, and the axial center of the small end hole is formed. It has a lubrication hole with both ends open on a plane that passes through the axis of the large end hole, and a cross-sectional area smaller than the cross-sectional area of the lubrication hole, the lower end communicates with the lubrication hole, and the upper end is closer to the piston than the lower end. Since it is composed of at least one refrigerant gas discharge hole provided in the connecting rod that is open above the outer surface of the connecting rod, and a piston pin slidably accommodated in the small end hole and fixed to the piston, When the gas is discharged from the refrigerant gas discharge hole, the oil leaking from the refrigerant gas discharge hole can be blown to the cylinder part or the small end hole part to directly supply oil to the cylinder part or the small end hole part. And cylinder sliding parts and small ends It can be difficult to abrade the sliding portions of the piston pin and.
【００４８】また、ピストンと、一端に小端穴を他端に
大端穴を有するコンロッドと、コンロッド内を通り、小
端穴と大端穴とを連通し、かつ小端穴の軸心と大端穴の
軸心とを通る平面上に両端が開口する給油孔と、小端穴
摺動面とコンロッド外表面を連通する排油孔と、給油孔
の断面積より小さな断面積を有し、かつ下端が給油孔に
連通し、上端が下端よりもピストン側でコンロッド外表
面の上部に開口するコンロッド内に設けられた少なくと
も１つの冷媒ガス排出孔と、小端穴に摺動自在に収納さ
れ、かつピストンに固定されたピストンピンと、ピスト
ンが上死点から下死点へ運動する間に給油孔と排油孔を
連通する位置にピストンピンの円周方向に設けられた半
円周状の給油溝とから構成されているので、第１と第２
の実施例の効果に加えて圧縮行程中でのピストンピンの
摺動面のオイル中から発生した冷媒ガスが給油孔内に逆
流したときでも、冷媒ガス排出孔から冷媒ガスが排出さ
れ給油時に再び冷媒ガスが摺動部に流れ込まず、安定し
たオイルの供給が行えるので、摺動部の摩耗をしにくく
することができる。Further, the piston, the connecting rod having a small end hole at one end and the large end hole at the other end, the small end hole and the large end hole are communicated with each other through the connecting rod, and the axial center of the small end hole is formed. It has an oil supply hole with both ends open on a plane that passes through the axis of the large end hole, an oil discharge hole that connects the sliding surface of the small end hole with the outer surface of the connecting rod, and a cross-sectional area smaller than the cross-sectional area of the oil supply hole. , And at least one refrigerant gas discharge hole provided in the connecting rod whose lower end communicates with the oil supply hole and whose upper end opens to the upper part of the connecting rod outer surface on the piston side with respect to the lower end, and is slidably accommodated in the small end hole. And a semi-circular shape provided in the circumferential direction of the piston pin at the position where the piston pin fixed to the piston communicates with the oil supply hole and the oil discharge hole while the piston moves from the top dead center to the bottom dead center. Since it is configured with the oil supply groove of
In addition to the effects of the embodiment, even when the refrigerant gas generated from the oil on the sliding surface of the piston pin during the compression stroke flows back into the oil supply hole, the refrigerant gas is discharged from the refrigerant gas discharge hole and again when refueling. Refrigerant gas does not flow into the sliding portion, and stable oil supply can be performed, so that the sliding portion is less likely to wear.
【図１】本発明の第１の実施例を示す密閉型圧縮機のピ
ストン装置の断面図FIG. 1 is a sectional view of a piston device for a hermetic compressor showing a first embodiment of the present invention.
【図２】本発明の第２の実施例を示す密閉型圧縮機のピ
ストン装置の側面断面図FIG. 2 is a side sectional view of a piston device for a hermetic compressor showing a second embodiment of the present invention.
【図３】本発明の第３の実施例を示す密閉型圧縮機のピ
ストン装置の側面断面図FIG. 3 is a side sectional view of a piston device of a hermetic compressor showing a third embodiment of the present invention.
【図４】本発明の第４の実施例を示す密閉型圧縮機のピ
ストン装置の側面断面図FIG. 4 is a side sectional view of a piston device for a hermetic compressor showing a fourth embodiment of the present invention.
【図５】図４のＢ−Ｂ断面図5 is a sectional view taken along line BB of FIG.
【図６】従来の密閉型圧縮機のピストン装置の側面断面
図FIG. 6 is a side sectional view of a piston device of a conventional hermetic compressor.
【図７】図６に示すＡ−Ａ断面における給油孔とクラン
ク給油孔及びオイル溜りの関係を示す行程図FIG. 7 is a process diagram showing the relationship between the oil supply hole, the crank oil supply hole, and the oil sump in the AA cross section shown in FIG.
【図８】従来の密閉型圧縮機の別のピストン装置の断面
図FIG. 8 is a sectional view of another piston device of the conventional hermetic compressor.
【図９】従来の密閉型圧縮機の別のピストン装置の断面
図FIG. 9 is a sectional view of another piston device of the conventional hermetic compressor.
２ ピストン ７ コンロッド ８ 小端穴 ９ 大端穴 １０ 給油孔 １１ 排油孔 ２１ ピストンピン ２３ ピストンピン ２４ 半円周状の給油溝 ２５ 冷媒ガス排出孔 ２６ 冷媒ガス排出孔 ２７ 冷媒ガス排出孔 ２８ ピストンピン ２９ 半円周状の円周溝 2 pistons 7 connecting rod 8 small end holes 9 Large end hole 10 Lubrication hole 11 Oil drain hole 21 piston pin 23 Piston pin 24 Semi-circular lubrication groove 25 Refrigerant gas discharge hole 26 Refrigerant gas discharge hole 27 Refrigerant gas discharge hole 28 Piston Pin 29 semicircular circumferential groove
フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F04B 39/02 F04B 27/02 F04B 27/04 Front page continuation (58) Fields surveyed (Int.Cl. 7 , DB name) F04B 39/02 F04B 27/02 F04B 27/04
Claims (4)
穴を有するコンロッドと、前記コンロッド内を通り、前
記小端穴と前記大端穴とを連通し、かつ前記小端穴の軸
心と前記大端穴の軸心とを通る平面上に両端が開口する
給油孔と、前記小端穴摺動面と前記コンロッド外表面を
連通する排油孔と、前記小端穴に摺動自在に収納され、
かつ前記ピストンに固定されたピストンピンと、前記ピ
ストンが上死点から下死点へ運動する間に前記給油孔と
前記排油孔を連通する位置に前記ピストンピンの円周方
向に設けられた半円周状の給油溝とからなる密閉型圧縮
機。1. A piston, a connecting rod having a small end hole at one end and a large end hole at the other end, a small end hole communicating with the large end hole through the connecting rod, and the small end hole. To the small end hole, an oil supply hole having both ends open on a plane passing through the shaft center of the large end hole and the shaft end of the large end hole, an oil drain hole communicating the small end hole sliding surface with the connecting rod outer surface, and the small end hole. It is slidably stored,
And a piston pin fixed to the piston, and a semicircle provided in the circumferential direction of the piston pin at a position communicating the oil supply hole and the oil discharge hole while the piston moves from the top dead center to the bottom dead center. A hermetic compressor consisting of a circumferential oil supply groove.
穴を有するコンロッドと、前記コンロッド内を通り、前
記小端穴と前記大端穴とを連通し、かつ前記小端穴の軸
心と前記大端穴の軸心とを通る平面上に両端が開口する
給油孔と、前記給油孔の断面積より小さな断面積を有
し、かつ下端が前記給油孔に連通し、上端が前記コンロ
ッド外表面の上部に開口する前記コンロッド内に設けら
れた少なくとも１つの冷媒ガス排出孔と、前記小端穴に
摺動自在に収納され、かつ前記ピストンに固定されたピ
ストンピンとからなる密閉型圧縮機。2. A piston, a connecting rod having a small end hole at one end and a large end hole at the other end, a small end hole communicating with the large end hole through the inside of the connecting rod, and the small end hole. Has a cross-sectional area smaller than the cross-sectional area of the oil-filling hole and has a lower end communicating with the oil-filling hole and an upper end. Is a hermetic seal including at least one refrigerant gas discharge hole provided in the connecting rod that opens to the upper part of the outer surface of the connecting rod, and a piston pin slidably accommodated in the small end hole and fixed to the piston. Type compressor.
穴を有するコンロッドと、前記コンロッド内を通り、前
記小端穴と前記大端穴とを連通し、かつ前記小端穴の軸
心と前記大端穴の軸心とを通る平面上に両端が開口する
給油孔と、前記給油孔の断面積より小さな断面積を有
し、かつ下端が前記給油孔に連通し、上端が下端よりも
前記ピストン側で前記コンロッド外表面の上部に開口す
る前記コンロッド内に設けられた少なくとも１つの冷媒
ガス排出孔と、前記小端穴に摺動自在に収納され、かつ
前記ピストンに固定されたピストンピンとからなる密閉
型圧縮機。3. A piston, a connecting rod having a small end hole at one end and a large end hole at the other end, and the small end hole and the large end hole communicating with each other through the inside of the connecting rod, and the small end hole. Has a cross-sectional area smaller than the cross-sectional area of the oil-filling hole and has a lower end communicating with the oil-filling hole and an upper end. Is at least one refrigerant gas discharge hole provided in the connecting rod that is open to the upper part of the outer surface of the connecting rod on the piston side from the lower end, and is slidably accommodated in the small end hole and fixed to the piston. Hermetic compressor consisting of the piston pin
穴を有するコンロッドと、前記コンロッド内を通り、前
記小端穴と前記大端穴とを連通し、かつ前記小端穴の軸
心と前記大端穴の軸心とを通る平面上に両端が開口する
給油孔と、前記小端穴摺動面と前記コンロッド外表面を
連通する排油孔と、前記給油孔の断面積より小さな断面
積を有し、かつ下端が前記給油孔に連通し、上端が下端
よりも前記ピストン側で前記コンロッド外表面の上部に
開口する前記コンロッド内に設けられた少なくとも１つ
の冷媒ガス排出孔と、前記小端穴に摺動自在に収納さ
れ、かつ前記ピストンに固定されたピストンピンと、前
記ピストンが上死点から下死点へ運動する間に前記給油
孔と前記排油孔を連通する位置に前記ピストンピンの円
周方向に設けられた半円周状の給油溝とからなる密閉型
圧縮機。4. A piston, a connecting rod having a small end hole at one end and a large end hole at the other end, a small end hole passing through the connecting rod to communicate the small end hole with the large end hole, and the small end hole. An oil supply hole having both ends opened on a plane passing through the axis of the small end hole and the axis of the large end hole, an oil discharge hole communicating the sliding surface of the small end hole with the outer surface of the connecting rod, and a disconnection of the oil supply hole. At least one refrigerant gas discharge having a cross-sectional area smaller than the area, the lower end communicating with the oil supply hole, and the upper end opening in the upper part of the connecting rod outer surface on the piston side with respect to the lower end. A hole, a piston pin slidably accommodated in the small end hole, and fixed to the piston, and the oil supply hole and the oil discharge hole are communicated with each other while the piston moves from the top dead center to the bottom dead center. Half of the piston pin in the circumferential direction A hermetic compressor consisting of a circumferential oil supply groove.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP00566494A JP3487892B2 (en) | 1994-01-24 | 1994-01-24 | Hermetic compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP00566494A JP3487892B2 (en) | 1994-01-24 | 1994-01-24 | Hermetic compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07208337A JPH07208337A (en) | 1995-08-08 |
| JP3487892B2 true JP3487892B2 (en) | 2004-01-19 |
Family
ID=11617379
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP00566494A Expired - Fee Related JP3487892B2 (en) | 1994-01-24 | 1994-01-24 | Hermetic compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3487892B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100487777B1 (en) * | 2002-08-30 | 2005-05-06 | 엘지전자 주식회사 | A connecting structure of piston and connecting rod for hermetic compressor |
| JP4652125B2 (en) * | 2005-05-19 | 2011-03-16 | 日立アプライアンス株式会社 | Hermetic compressor |
| KR100708551B1 (en) * | 2005-07-19 | 2007-04-18 | 삼성광주전자 주식회사 | Hermetic type compressor |
| JP5626041B2 (en) * | 2011-03-10 | 2014-11-19 | パナソニック株式会社 | Reciprocating compressor |
| JP6893487B2 (en) * | 2018-03-28 | 2021-06-23 | 日立グローバルライフソリューションズ株式会社 | Compressor and equipment with it |
| CN108443113A (en) * | 2018-04-16 | 2018-08-24 | 安庆市星杰环保设备科技有限公司 | A kind of oil-free air compressor connecting rod with stuffing hole |
-
1994
- 1994-01-24 JP JP00566494A patent/JP3487892B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH07208337A (en) | 1995-08-08 |
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