JPH07127574A - Closed type compressor - Google Patents
Closed type compressorInfo
- Publication number
- JPH07127574A JPH07127574A JP27662493A JP27662493A JPH07127574A JP H07127574 A JPH07127574 A JP H07127574A JP 27662493 A JP27662493 A JP 27662493A JP 27662493 A JP27662493 A JP 27662493A JP H07127574 A JPH07127574 A JP H07127574A
- Authority
- JP
- Japan
- Prior art keywords
- end hole
- small end
- hole
- piston
- connecting rod
- 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.)
- Granted
Links
Abstract
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 an electrically driven compression element housed in a hermetically sealed container, and maintenance and repair cannot be performed in the hermetically sealed 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４は従来の密閉型電動圧縮機を示す断面
図である。図４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る。１
１は前記クランク軸４に形成された偏心部である。１２
はクランク軸４内に明けられたシャフト給油孔であり、
１３は前記シャフト給油孔１２に交差連通した偏心部給
油孔であり、偏心部１１表面に設けられたオイル溜り１
４に開口している。１５はクランク偏心部１１に固定さ
れた給油管であり、前記シャフト給油孔１２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１６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１７が挿入されると共に、偏心部
１１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。１８はピストンピン１
７表面の円周方向に設けられた円周溝であり、１９はピ
ストンピン１７をピストン２に固定するロッキングピン
である。FIG. 4 is a sectional view showing a conventional hermetic electric compressor. In FIG. 4, 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.
Is an oil supply hole which is open at both ends on a plane which communicates with the shaft center of the small end hole 8 and the shaft center of the large end hole 9. 1
Reference numeral 1 is an eccentric portion formed on the crankshaft 4. 12
Is a shaft oil supply hole opened in the crankshaft 4,
Reference numeral 13 denotes an eccentric part oil supply hole which is in cross communication with the shaft oil supply hole 12, and which is an oil reservoir 1 provided on the surface of the eccentric part 11.
It opens to 4. Reference numeral 15 is an oil supply pipe fixed to the crank eccentric portion 11, communicates with the shaft oil supply hole 12, and its tip is immersed in the oil 16 stored in the bottom portion 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 17 is inserted into the through hole 6 and the small end hole 8, and the eccentric portion 11 is inserted into the large end hole 9. As a result, the piston 2 and the crankshaft 4 are connected. 18 is the piston pin 1
7 is a circumferential groove provided on the surface in the circumferential direction, and 19 is a locking pin for fixing the piston pin 17 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１５でオイル１６に油圧が発生し、オ
イル１６は給油管１５内及びシャフト給油孔１２を上昇
する。上げられたオイル１６の一部は偏心部給油孔１３
を通ってオイル溜まり１４に流出し、大端穴９と偏心部
１１との摺動部を潤滑する。さらに、オイル溜まり１４
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１７と小端穴８の摺動部を潤滑し、円
周溝１８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 16 in the oil supply pipe 15, and the oil 16 rises in the oil supply pipe 15 and the shaft oil supply hole 12. Part of the raised oil 16 is the eccentric part oil supply hole 13
Through the oil reservoir 14 and then lubricates the sliding portion between the large end hole 9 and the eccentric portion 11. In addition, the oil sump 14
A part of the oil flows through the oil supply hole 10 to the small end hole 8, lubricates the sliding portion between the piston pin 17 and the small end hole 8, and flows through the circumferential groove 18 into the hollow portion 5 of the piston 2. To do.
【０００６】図５のａ，ｂ，ｃ，ｄは図４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
１内のクランク給油孔１３及びオイル溜り１４の関係を
示す行程図である。図５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１１のクラン
ク給油孔１３とオイル溜り１４の関係から明らかなよう
に、常にオイル１６がクランク給油孔１３及びオイル溜
り１４からコンロッド７の給油孔１０に流入可能ではな
く、図４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１１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１１の
オイル溜り１４の無い部分で荷重を受けることになり、
偏心部１１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。5A, 5B, 5C and 5D are AA shown in FIG.
The oil supply hole 10 and the eccentric portion 1 in the connecting rod 7 in the cross section
3 is a process diagram showing the relationship between the crank oil supply hole 13 and the oil sump 14 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 13 of the eccentric portion 11 and the oil sump 14 during one rotation of the crankshaft 4 in FIG. 5, the oil 16 is constantly kept in the crank oil supply hole 13 and the oil sump 14 It is not possible to flow into the oil supply hole 10 of the connecting rod 7 from the above, but it is possible to flow only during the suction stroke between c and d in FIG. 4, that is, the piston 2 from the top dead center to the bottom dead center. With this structure, the eccentric portion 11 receives a load on the portion of the eccentric portion 11 where the oil reservoir 14 is absent during the 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 in the sliding portion between the eccentric portion 11 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６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. 6 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６において、２０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。２１は小端穴８の前記ピストンピン２１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. 6, reference numeral 20 denotes a piston pin having no groove for oil supply on its sliding surface with the small end hole 8. Reference numeral 21 denotes a V groove provided on the sliding surface of the small end hole 8 with respect to the piston pin 21 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１６は、Ｖ溝２
１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２０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１８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 16 that has flowed through the oil supply hole 10 of the connecting rod 7 to the small end hole 8 is the V groove 2
It flows out through the hollow space 5 of the piston 2 through 1 and lubricates the sliding part between the piston pin 20 and the small end hole 8. Therefore,
The same effect as that of the piston pin 17 provided with the circumferential groove 18 can be obtained.
【００１１】図７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２０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. 7 is a sectional view of a piston device in which a small end hole 8 of a connecting rod 7 and a piston pin 20 of a conventional hermetic electric compressor have no groove for oil supply.
【００１２】図７において、２０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. 7, reference numeral 20 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１６は、ピスト
ンピン２０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２０との摺動部に円周溝１８あるいは
Ｖ溝２１が設けられているものに比べ、それらの溝から
オイル１６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 16 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 20 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 18 or the V groove 21 is provided in the sliding portion between the small end hole 8 and the piston pin 20, Since the oil 16 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る潤滑不良が起こり
やすい。また、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。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 parts is small and the cooling effect of the oil is small, lubrication failure easily occurs due to the temperature rise of the sliding parts. Also, during the compression stroke when the load becomes the largest, there is always the connecting rod oil supply hole in the sliding part between the piston pin and the connecting rod small end hole, and the oil film pressure in the sliding part is generated. However, there is a drawback that the sliding part is worn due to metal contact.
【００１６】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 also securing a sufficient amount of oil supply to the sliding portion. Prevents the sliding parts from wearing,
The purpose is to provide a highly reliable hermetic compressor.
【００１７】[0017]
【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、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
記ピストンピンの前記小端穴との摺動面上に、前記ピス
トンピンの軸心方向で、かつ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連通する位置に設け
られた給油溝とから構成されている。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 passing through the connecting rod. The small end hole and the large end hole are communicated with each other, and an oiling 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 and the small end hole are slidable. On the sliding surface of the piston pin, which is movably accommodated and fixed to the piston, and the small end hole of the piston pin, in the axial direction of the piston pin, and when the piston is below the top dead center. It comprises an oil supply groove provided at a position communicating with the oil supply hole during movement to the dead point.
【００１８】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、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から外れた
位置に両端が開口する給油孔と、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
ンとから構成されている。Further, 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 end hole communicating with the large end hole through the inside of the connecting rod, and the small end hole. An oil supply hole having both ends open at a position deviated from a plane passing through the axis of and the axis of the large end hole, and a piston pin slidably housed in the small end hole and fixed to the piston. It consists of
【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、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から外れた
位置に両端が開口する給油孔と、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、前記ピストンピンの前記小端穴との摺動面上に、
前記ピストンピンの軸心方向で、かつ前記ピストンの１
ストローク中に少なくとも一回は前記給油孔と連通する
位置に設けられた給油溝とから構成されている。Further, 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 end hole communicating with the large end hole through the inside of the connecting rod, and the small end hole. An oil supply hole having both ends open at a position deviated from a plane passing through the axis of and the axis of the large end hole, and a piston pin slidably housed in the small end hole and fixed to the piston. , On the sliding surface of the piston pin with the small end hole,
In the axial direction of the piston pin and in the piston 1
It is composed of an oil supply groove provided at a position communicating with the oil supply hole at least once during the stroke.
【００２０】[0020]
【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
ンの給油溝とが一致して、従来のＶ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。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, during the suction stroke, the oil supply hole of the connecting rod and the oil supply groove of the piston pin are aligned with each other, so that oil can be supplied to the small end hole as in the conventional V groove specification.
【００２１】また、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から外れた位
置に両端が開口するようにコンロッドの給油孔が設けら
れているので、コンロッドの小端穴と大端穴の摺動部の
うち最も大きな荷重のかかるコンロッドの中心線上の部
分に油膜圧力が発生し易く、小端穴及び大端穴の摺動部
が摩耗しにくくすることができる。また更に、オイル溜
りと給油孔との位置関係によっては圧縮行程においても
小端穴への給油が可能となり、更に小端穴の摺動部を摩
耗しにくくすることができる。Further, the connecting rod is lubricated so that the small end hole and the large end hole are communicated with each other and both ends are opened at positions deviated from the plane passing through the axis of the small end hole and the axis of the large end hole. Since the holes are provided, oil film pressure is likely to occur at the part on the center line of the connecting rod where the largest load is applied among the sliding parts of the connecting rod's small end hole and large end hole. It is possible to make the sliding portion less likely to wear. Further, depending on the positional relationship between the oil reservoir and the oil supply hole, oil can be supplied to the small end hole even during the compression stroke, and the sliding portion of the small end hole can be made less likely to wear.
【００２２】また更に、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から外れ
た位置に両端が開口するようにコンロッドの給油孔が設
けられており、かつピストンピンの小端穴との摺動面上
に、ピストンピンの軸心方向で、かつピストンの１スト
ローク中に少なくとも一回は給油孔と連通する位置に給
油溝が設けられているので、ピストンピンの給油溝はピ
ストン軸心上から大きく離れた位置に形成することがで
き、ピストンピンとコンロッドの小端穴との摺動部に油
膜圧力が更に発生し易くなる。また、圧縮行程において
ピストンピン２５に最も荷重のかかる位置が多少ずれて
も、安定して油膜圧力の発生ができる。従って、ピスト
ンピンとコンロッドの小端穴との摺動部の摩耗を安定し
て更にしにくくすることができる。Furthermore, the connecting rod is connected so that the small end hole and the large end hole are communicated with each other, and both ends are opened at positions deviated from the plane passing through the axis of the small end hole and the axis of the large end hole. An oil supply hole is provided, and it is provided on the sliding surface with the small end hole of the piston pin, in the axial direction of the piston pin, and at a position communicating with the oil supply hole at least once during one stroke of the piston. Since the groove is provided, the oil supply groove of the piston pin can be formed at a position far away from the piston axis, and oil film pressure is more likely to occur at the sliding portion between the piston pin and the small end hole of the connecting rod. Become. Further, even if the position where the load is most applied to the piston pin 25 deviates in the compression stroke, the oil film pressure can be stably generated. Therefore, it is possible to stabilize and further prevent abrasion of the sliding portion between the piston pin and the small end hole of the connecting rod.
【００２３】[0023]
【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 will be denoted by the same reference numerals and detailed description thereof will be omitted.
【００２４】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、２２はピストンピ
ンで、２３はピストンピン２２の小端穴８との摺動面上
に、ピストンピン２２の軸心方向で、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と連通する
位置に設けられた給油溝である。FIG. 1 shows a first embodiment of the hermetic compressor of the present invention. In FIG. 1, 22 is a piston pin, 23 is a sliding surface of the piston pin 22 with respect to the small end hole 8, and the piston 2 moves from the top dead center to the bottom dead center in the axial direction of the piston pin 22. It is an oil supply groove provided at a position communicating with the oil supply hole 10 during the operation.
【００２５】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２２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の軸心に対して給油溝２３と反対側に位置す
る。従って、その際ピストンピン２２は給油溝２３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、従来の小端穴８にＶ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とピストン
ピン２２の給油溝２３とが一致して連通し、従来のＶ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。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 22 and the small end hole 8 of the connecting rod 7, the opening portion of the oil supply hole 10 to the small end hole 8 forms an oil supply groove 23 with respect to the axial center of the piston 2. Located on the other side. Therefore, at that time, the piston pin 22 comes into contact with the small end hole 8 of the connecting rod 7 at a portion without the oil supply groove 23 and receives a load at that portion, so that a V groove is provided in the conventional small end hole 8. Compared with the conventional type, the 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 suction stroke, the oil supply hole 10 of the connecting rod 7 and the oil supply groove 23 of the piston pin 22 are aligned and communicate with each other, so that oil can be supplied to the small end hole 8 as in the conventional V groove specification.
【００２６】以上のように本実施例の密閉型圧縮機は、
ピストン２と、一端に小端穴８を他端に大端穴９を有す
るコンロッド７と、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１０と、前記小端穴８に摺動自在に収納さ
れ、かつ前記ピストン２に固定されたピストンピン２２
と、前記ピストンピン２２の前記小端穴８との摺動面上
に、前記ピストンピン２２の軸心方向で、かつ前記ピス
トン２が上死点から下死点へ運動する間に前記給油孔１
０と連通する位置に設けられた給油溝２３とから構成さ
れているので、従来の小端穴８にＶ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２２は給油溝
２３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
ピストンピン２２の給油溝２３とが一致して、従来のＶ
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。As described above, the hermetic compressor of this embodiment is
The piston 2, a connecting rod 7 having a small end hole 8 at one end and a large end hole 9 at the other end, and the small end hole 8 and the large end hole 9 communicate with each other through the inside of the connecting rod 7, An oil supply hole 10 having both ends opened on a plane that passes through the axis of the end hole 8 and the axis of the large end hole 9, and is slidably housed in the small end hole 8 and fixed to the piston 2. Piston pin 22
And on the sliding surface of the piston pin 22 with the small end hole 8, the oil supply hole in the axial direction of the piston pin 22 and while the piston 2 moves from the top dead center to the bottom dead center. 1
Since the piston pin 22 does not have the oil supply groove 23 at the time of the compression stroke, the piston pin 22 does not have the oil supply groove 23 in the compression stroke, as compared with the conventional small end hole 8 having the V groove. Since the load is applied to the portion, the oil film pressure is easily generated in the sliding portion, and the sliding portion is less likely to be worn. Further, during the intake stroke, the oil supply hole 10 of the connecting rod 7 and the oil supply groove 23 of the piston pin 22 are aligned with each other, and the conventional V
Oil can be supplied to the small end hole 8 as in the case of the groove type.
【００２７】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.
【００２８】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、２４はコンロッド
７内を通り、小端穴８と大端穴９とを連通し、かつ小端
穴８の軸心と大端穴９の軸心とを通る平面上から外れた
位置に両端が開口する給油孔である。FIG. 2 shows a second embodiment of the hermetic compressor of the present invention. In FIG. 2, 24 passes through the connecting rod 7, communicates the small end hole 8 and the large end hole 9, and deviates from the plane passing through the axis of the small end hole 8 and the axis of the large end hole 9. It is an oil supply hole with both ends open at the position.
【００２９】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。圧縮行程でコンロッド
７の小端穴８及び大端穴９が、それぞれピストンピン２
０及び偏心部１１から最も荷重を受ける部分はコンロッ
ド７の中心線上付近である。本実施例のコンロッド７の
給油孔２４はコンロッド７内を通り、小端穴８と大端穴
９とを連通し、かつ小端穴８の軸心と大端穴９の軸心と
を通る平面上から外れた位置に両端が開口しているの
で、従来の給油孔１０がコンロッド７の中心線上に設け
られたものに比べ、コンロッド７の小端穴８と大端穴９
の摺動部のうち最も大きな荷重のかかるコンロッド７の
中心線上の部分に油膜圧力が発生し易く、小端穴８及び
大端穴９の摺動部を摩耗しにくくすることができる。ま
た更に、オイル溜り１４と給油孔２３との位置関係によ
っては吸入行程のみならず圧縮行程においても大端穴９
に油膜圧力が発生しやすい状態のまま小端穴８への給油
が可能となり、更に小端穴８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. During the compression stroke, the small end hole 8 and the large end hole 9 of the connecting rod 7 are
The portion that receives the most load from 0 and the eccentric portion 11 is near the center line of the connecting rod 7. The oil supply hole 24 of the connecting rod 7 of the present embodiment passes through the connecting rod 7, connects the small end hole 8 and the large end hole 9 and passes through the axis of the small end hole 8 and the axis of the large end hole 9. Since both ends are open at positions deviated from the plane, the small end hole 8 and the large end hole 9 of the connecting rod 7 are different from those in which the conventional oil supply hole 10 is provided on the center line of the connecting rod 7.
The oil film pressure is likely to be generated in the portion on the center line of the connecting rod 7 to which the largest load is applied among the sliding portions of, and the sliding portions of the small end hole 8 and the large end hole 9 can be made less likely to wear. Furthermore, depending on the positional relationship between the oil sump 14 and the oil supply hole 23, the large end hole 9 may be used not only in the suction stroke but also in the compression stroke.
It is possible to supply oil to the small end hole 8 while the oil film pressure is likely to be generated, and it is possible to make the sliding portion of the small end hole 8 less likely to wear.
【００３０】以上のように本実施例の密閉型圧縮機は、
ピストン２と、一端に小端穴８を他端に大端穴９を有す
るコンロッド７と、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から外れた位
置に両端が開口する給油孔２４と、前記小端穴８に摺動
自在に収納され、かつ前記ピストン２に固定されたピス
トンピン２０とから構成されているので、従来の給油孔
１０がコンロッド７の中心線上に設けられたものに比
べ、コンロッド７の小端穴８と大端穴９の摺動部のうち
最も大きな荷重のかかるコンロッド７の中心線上の部分
に油膜圧力が発生し易く、小端穴８及び大端穴９の摺動
部が摩耗しにくくすることができる。また更に、オイル
溜り１４と給油孔２４との位置関係によっては圧縮行程
においても小端穴８への給油が可能となり、更に小端穴
８の摺動部が摩耗しにくくすることができる。As described above, the hermetic compressor of this embodiment is
The piston 2, a connecting rod 7 having a small end hole 8 at one end and a large end hole 9 at the other end, and the small end hole 8 and the large end hole 9 communicate with each other through the inside of the connecting rod 7, An oil supply hole 24 having both ends open at a position deviated from a plane passing through the axis of the end hole 8 and the axis of the large end hole 9, and the piston is slidably housed in the small end hole 8 and the piston. Since it is composed of the piston pin 20 fixed to 2, the sliding of the small end hole 8 and the large end hole 9 of the connecting rod 7 in comparison with the conventional oil supply hole 10 provided on the center line of the connecting rod 7. The oil film pressure is likely to be generated in the portion on the center line of the connecting rod 7 to which the largest load is applied, and the sliding portions of the small end hole 8 and the large end hole 9 are less likely to wear. Further, depending on the positional relationship between the oil reservoir 14 and the oil supply hole 24, oil can be supplied to the small end hole 8 even during the compression stroke, and the sliding portion of the small end hole 8 can be made less likely to wear.
【００３１】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.
【００３２】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、２５はピストンピ
ンであり、２６はコンロッド７内を通り、小端穴８と大
端穴９とを連通し、かつ小端穴８の軸心と大端穴９の軸
心とを通る平面上から外れた位置に両端が開口する給油
孔である。２７はピストンピン２５の小端穴８との摺動
面上に、ピストンピン２５の軸心方向で、かつピストン
２の１ストローク中に少なくとも一回は給油孔２６と連
通する位置に設けられた給油溝である。FIG. 3 shows a third embodiment of the hermetic compressor of the present invention. In FIG. 3, reference numeral 25 is a piston pin, 26 is a rod passing through the connecting rod 7, connecting the small end hole 8 and the large end hole 9 to each other, and connecting the axis of the small end hole 8 to the axis of the large end hole 9. It is an oil supply hole whose both ends open at positions deviated from the plane passing through. Numeral 27 is provided on the sliding surface of the piston pin 25 with respect to the small end hole 8 in the axial direction of the piston pin 25 and at a position communicating with the oil supply hole 26 at least once during one stroke of the piston 2. It is a refueling groove.
【００３３】以上のように構成された密閉型圧縮機は第
１及び第２の実施例での効果に加えて、ピストンピン２
５の給油溝２７はピストン２の軸心から更に離れた位
置、すなわち圧縮行程において最も荷重のかかる部分か
ら離れた位置に形成することができるので、圧縮行程に
おいてピストンピン２とコンロッド７の小端穴８との摺
動部に油膜圧力が更に発生し易くなる。また、圧縮行程
においてピストンピン２５に最も荷重のかかる位置が多
少ずれても、安定して油膜圧力の発生ができる。従っ
て、安定して小端穴８の摺動部が更に摩耗しにくくする
ことができる。In addition to the effects of the first and second embodiments, the hermetic compressor constructed as above has the piston pin 2
5 can be formed at a position further away from the axial center of the piston 2, that is, at a position farthest from the most loaded portion in the compression stroke, so that the small end of the piston pin 2 and the connecting rod 7 in the compression stroke can be formed. The oil film pressure is more likely to be generated in the sliding portion with the hole 8. Further, even if the position where the load is most applied to the piston pin 25 deviates in the compression stroke, the oil film pressure can be stably generated. Therefore, the sliding portion of the small end hole 8 can be made more stable and less likely to wear.
【００３４】以上のように本実施例の密閉型圧縮機は、
ピストン２と、一端に小端穴８を他端に大端穴９を有す
るコンロッド７と、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から外れた位
置に両端が開口する給油孔２６と、前記小端穴８に摺動
自在に収納され、かつ前記ピストン２に固定されたピス
トンピン２５と、前記ピストンピン２５の前記小端穴８
との摺動面上に、前記ピストンピン２５の軸心方向で、
かつ前記ピストン２の１ストローク中に少なくとも一回
は前記給油孔２６と連通する位置に設けられた給油溝２
７とから構成されているので、第１及び第２の実施例で
の効果に加えて、ピストンピン２４の給油溝２５は圧縮
行程において最も荷重のかかる部分から更に離れた位置
に形成することができるので、ピストンピン２４と小端
穴８との摺動部に油膜圧力が更に発生し易くなり、また
安定して油膜圧力の発生ができる。また、圧縮行程にお
いてピストンピン２５に最も荷重のかかる位置が多少ず
れても、安定して油膜圧力の発生ができる。従って、安
定して小端穴８の摺動部が更に摩耗しにくくすることが
できる。As described above, the hermetic compressor of this embodiment is
The piston 2, a connecting rod 7 having a small end hole 8 at one end and a large end hole 9 at the other end, and the small end hole 8 and the large end hole 9 communicate with each other through the inside of the connecting rod 7, An oil supply hole 26 having both ends open at positions deviated from a plane passing through the axis of the end hole 8 and the axis of the large end hole 9, and the piston is slidably housed in the small end hole 8 and the piston. 2 and the small end hole 8 of the piston pin 25.
On the sliding surface of and in the axial direction of the piston pin 25,
Further, the oil supply groove 2 provided at a position communicating with the oil supply hole 26 at least once during one stroke of the piston 2.
In addition to the effects of the first and second embodiments, the oil supply groove 25 of the piston pin 24 can be formed at a position further away from the most loaded portion in the compression stroke. Therefore, the oil film pressure is more likely to be generated in the sliding portion between the piston pin 24 and the small end hole 8, and the oil film pressure can be stably generated. Further, even if the position where the load is most applied to the piston pin 25 deviates in the compression stroke, the oil film pressure can be stably generated. Therefore, the sliding portion of the small end hole 8 can be made more stable and less likely to wear.
【００３５】[0035]
【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、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
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、前記ピストンピンの前記小端穴との摺
動面上に、前記ピストンピンの軸心方向で、かつ前記ピ
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
連通する位置に設けられた給油溝とから構成されている
ので、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給油溝と
が一致して、従来のＶ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。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 passing through the connecting rod. And an oil supply hole having both ends open on a plane passing through the axis of the small end hole and the axis of the large end hole, and the piston is slidably housed in the small end hole and attached to the piston. On the sliding surface of the fixed piston pin and the small end hole of the piston pin, the oil supply hole in the axial direction of the piston pin and while the piston moves from the top dead center to the bottom dead center. Since it is composed of an oil supply groove that is provided in a position that communicates with the piston pin, the piston pin receives a load at the part without the oil supply groove during the compression stroke, so oil film pressure is likely to be generated in the sliding part and wear of the sliding part Can be difficult to do. Further, during the suction stroke, the oil supply hole of the connecting rod and the oil supply groove of the piston pin are aligned with each other, so that oil can be supplied to the small end hole as in the conventional V groove specification.
【００３６】また本発明は、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、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から
外れた位置に両端が開口する給油孔と、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
トンピンとから構成されているので、コンロッドの小端
穴と大端穴の摺動部のうち最も大きな荷重のかかるコン
ロッドの中心線上の部分に油膜圧力が発生し易く、小端
穴及び大端穴の摺動部が摩耗しにくくすることができ
る。また更に、オイル溜りと給油孔との位置関係によっ
ては圧縮行程においても小端穴への給油が可能となり、
更に小端穴の摺動部が摩耗しにくくすることができる。Further, according to the present invention, a piston, a connecting rod having a small end hole at one end and a large end hole at the other end, the connecting rod passing through the connecting rod, the small end hole and the large end hole are communicated with each other, and An oil supply hole having both ends opened at a position deviated from a plane passing through the axis of the small end hole and the axis of the large end hole, and slidably housed in the small end hole and fixed to the piston. Since it is composed of a piston pin, the oil film pressure is likely to be generated on the part of the sliding part of the small end hole and the large end hole of the connecting rod on the center line of the connecting rod to which the largest load is applied. It is possible to make the sliding portion of the hole less likely to wear. Furthermore, depending on the positional relationship between the oil sump and the oil supply hole, it is possible to supply oil to the small end hole even during the compression stroke.
Furthermore, the sliding portion of the small end hole can be made less likely to wear.
【００３７】また更に本発明は、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、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
から外れた位置に両端が開口する給油孔と、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、前記ピストンピンの前記小端穴との摺
動面上に、前記ピストンピンの軸心方向で、かつ前記ピ
ストンの１ストローク中に少なくとも一回は前記給油孔
と連通する位置に設けられた給油溝とから構成されてい
るので、第１及び第２の実施例での効果に加えて、ピス
トンピンの給油溝は圧縮行程において最も荷重のかかる
部分から離れた位置に形成することができるので、ピス
トンピンと小端穴との摺動部に油膜圧力が更に発生し易
くなり、また圧縮行程においてピストンピンに最も荷重
のかかる位置が多少ずれても、安定して油膜圧力の発生
ができる。従って、安定して小端穴の摺動部が更に摩耗
しにくくすることができる。Further, according to the present invention, 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 An oil supply hole whose both ends open at positions deviated from a plane passing through the axis of the small end hole and the axis of the large end hole, and slidably accommodated in the small end hole and fixed to the piston. On the sliding surface between the piston pin and the small end hole of the piston pin, in the axial direction of the piston pin, and at a position communicating with the oil supply hole at least once during one stroke of the piston. In addition to the effects of the first and second embodiments, the oil supply groove of the piston pin should be formed at a position farthest from the most loaded portion in the compression stroke. Since it can be done, piston pin and small end hole Oil film pressure is further easily generated in the sliding portion of, also be slightly deviated most load consuming located on the piston pin during the compression stroke can occur in stable oil film pressure. Therefore, the sliding portion of the small end hole can be made more stable and less likely to wear.
【図面の簡単な説明】[Brief description of drawings]
【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
ストン装置の断面図FIG. 2 is a sectional view of a piston device of 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
ストン装置の断面図FIG. 3 is a sectional view of a piston device of a hermetic compressor showing a third embodiment of the present invention.
【図４】従来の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 of a conventional hermetic compressor.
【図５】図４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5 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６】従来の密閉型圧縮機のピストン装置の断面図FIG. 6 is a sectional view of a piston device of a conventional hermetic compressor.
【図７】従来の密閉型圧縮機の別のピストン装置の断面
図FIG. 7 is a sectional view of another piston device of the conventional hermetic compressor.
【符号の説明】 ２ ピストン ７ コンロッド ８ 小端穴 ９ 大端穴 １０ 給油孔 ２０ ピストンピン ２２ ピストンピン ２３ 給油溝 ２４ 給油孔 ２５ ピストンピン ２６ 給油孔 ２７ 給油溝[Explanation of symbols] 2 Piston 7 Connecting rod 8 Small end hole 9 Large end hole 10 Oil supply hole 20 Piston pin 22 Piston pin 23 Oil supply groove 24 Oil supply hole 25 Piston pin 26 Oil supply hole 27 Oil supply groove
Claims (3)
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、前記ピストンピ
ンの前記小端穴との摺動面上に、前記ピストンピンの軸
心方向で、かつ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連通する位置に設けられた給油溝
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. And a piston pin fixed to the piston and slidably housed in the small end hole. Provided on the sliding surface with the small end hole in the axial direction of the piston pin and at a position communicating with the oil supply hole while the piston moves from the top dead center to the bottom dead center. Hermetic compressor consisting of a 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から外れた位置に
両端が開口する給油孔と、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. An oil supply hole having both ends open at a position deviated from a plane passing through the axis of and the axis of the large end hole, and a piston pin slidably housed in the small end hole and fixed to the piston. A hermetic compressor consisting of.
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から外れた位置に
両端が開口する給油孔と、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、
前記ピストンピンの前記小端穴との摺動面上に、前記ピ
ストンピンの軸心方向で、かつ前記ピストンの１ストロ
ーク中に少なくとも一回は前記給油孔と連通する位置に
設けられた給油溝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. An oil supply hole having both ends open at a position deviated from a plane passing through the axis of and the axis of the large end hole, and a piston pin slidably housed in the small end hole and fixed to the piston. ,
An oil supply groove provided on the sliding surface of the piston pin with the small end hole, in the axial direction of the piston pin, and at a position communicating with the oil supply hole at least once during one stroke of the piston. A hermetic compressor consisting of
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27662493A JP2783381B2 (en) | 1993-11-05 | 1993-11-05 | Hermetic compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27662493A JP2783381B2 (en) | 1993-11-05 | 1993-11-05 | Hermetic compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07127574A true JPH07127574A (en) | 1995-05-16 |
| JP2783381B2 JP2783381B2 (en) | 1998-08-06 |
Family
ID=17572038
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP27662493A Expired - Fee Related JP2783381B2 (en) | 1993-11-05 | 1993-11-05 | Hermetic compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2783381B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6399250B1 (en) | 1998-11-25 | 2002-06-04 | Samsung Display Devices Co., Ltd. | Negative material for rechargeable lithium battery and method of preparing the same |
| JP2007526958A (en) * | 2003-07-07 | 2007-09-20 | フレイ、ベルンハルト | Eccentric drive mechanism for a volumetrically acting pump or motor |
| KR100871129B1 (en) * | 2002-10-31 | 2008-12-03 | 엘지전자 주식회사 | Oil supplying structure of connectingrod in hermetic compressor |
| JP2019173614A (en) * | 2018-03-28 | 2019-10-10 | 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 including the same |
| WO2020177507A1 (en) * | 2019-03-01 | 2020-09-10 | 安徽美芝制冷设备有限公司 | Pump body assembly for reciprocating-type compressor, and reciprocating-type compressor |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2013122240A (en) | 2011-11-11 | 2013-06-20 | Panasonic Corp | Refrigerant compressor |
-
1993
- 1993-11-05 JP JP27662493A patent/JP2783381B2/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6399250B1 (en) | 1998-11-25 | 2002-06-04 | Samsung Display Devices Co., Ltd. | Negative material for rechargeable lithium battery and method of preparing the same |
| KR100871129B1 (en) * | 2002-10-31 | 2008-12-03 | 엘지전자 주식회사 | Oil supplying structure of connectingrod in hermetic compressor |
| JP2007526958A (en) * | 2003-07-07 | 2007-09-20 | フレイ、ベルンハルト | Eccentric drive mechanism for a volumetrically acting pump or motor |
| JP2019173614A (en) * | 2018-03-28 | 2019-10-10 | 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 including the same |
| CN110318980A (en) * | 2018-03-28 | 2019-10-11 | 日立环球生活方案株式会社 | Compressor and equipment with the compressor |
| CN110318980B (en) * | 2018-03-28 | 2020-10-30 | 日立环球生活方案株式会社 | Compressor and equipment with same |
| WO2020177507A1 (en) * | 2019-03-01 | 2020-09-10 | 安徽美芝制冷设备有限公司 | Pump body assembly for reciprocating-type compressor, and reciprocating-type compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2783381B2 (en) | 1998-08-06 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5118263A (en) | Hermetic refrigeration compressor | |
| JPH07127574A (en) | Closed type compressor | |
| US5046930A (en) | Connecting rod cooling and lubrication | |
| JP3487892B2 (en) | Hermetic compressor | |
| JP3488676B2 (en) | Hermetic compressor | |
| JP3872146B2 (en) | Hermetic compressor | |
| JP2001027177A (en) | Variable displacement swash plate type compressor | |
| JP2013122240A (en) | Refrigerant compressor | |
| JPH07247960A (en) | Enclosed type compressor | |
| JPH07259738A (en) | Hermetic type compressor | |
| JP3725208B2 (en) | Hermetic compressor | |
| KR100227420B1 (en) | Compressor | |
| JPH0742669A (en) | Reciprocating compressor | |
| KR0115480Y1 (en) | Lubricating structure of a hermetic compressor | |
| JP2002202057A (en) | Piston installing structure and reciprocating compressor | |
| JP2720598B2 (en) | Scroll compressor | |
| JP2003293953A (en) | Reciprocating hermetic motor compressor | |
| KR100296102B1 (en) | Structure for supplying oil of compressor | |
| KR200163927Y1 (en) | Piston lubrication apparatus of a compressor | |
| JPH09112427A (en) | Hermetic compressor | |
| JPS6111514Y2 (en) | ||
| KR100296101B1 (en) | Structure for cooling of closed compress | |
| KR200230846Y1 (en) | Piston pin of closed compressor | |
| JPH08159030A (en) | Enclosed compressor | |
| JP2001173562A (en) | Closed motor-driven compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |