JPH07158574A - Oscillation type rotary compressor - Google Patents
Oscillation type rotary compressorInfo
- Publication number
- JPH07158574A JPH07158574A JP5307924A JP30792493A JPH07158574A JP H07158574 A JPH07158574 A JP H07158574A JP 5307924 A JP5307924 A JP 5307924A JP 30792493 A JP30792493 A JP 30792493A JP H07158574 A JPH07158574 A JP H07158574A
- Authority
- JP
- Japan
- Prior art keywords
- piston
- blade portion
- chamber
- cylinder
- blade
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressor (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、主に冷凍装置に使用さ
れる揺動型ロータリー圧縮機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oscillating rotary compressor mainly used in refrigeration equipment.
【０００２】[0002]
【従来の技術】従来、揺動型ロータリー圧縮機として
は、例えば特開平５−２０２８７４号公報に記載されて
いるように、駆動軸の偏心部に挿嵌されるピストンに、
シリンダ室内を吸入室と圧縮室とに区画するためのブレ
ード部を一体的に突設して、このブレード部をシリンダ
に回転可能に配設した支持体の受入溝に揺動可能に支持
することにより、ピストンを公転させながらガス流体を
圧縮するようにしたものが知られている。即ち、従来の
揺動型ロータリー圧縮機は、図３で示したように、軸方
向両側にフロント及びリヤヘッドが対接されるシリンダ
Ａのシリンダ室Ａ１内に、径方向外方に向けて突出する
ブレード部Ｂ１を一体状に設けたピストンＢを、これら
ピストンＢ及びブレード部Ｂ１の上下両端面が前記各ヘ
ッドのフェース面に摺接されるように配設すると共に、
前記シリンダＡの内部に前記各ヘッドに摺接される円柱
状の支持体Ｃを回転可能に支持して、この支持体Ｃに形
成した受入溝Ｃ１に前記ブレード部Ｂ１の先端側を揺動
及び進退出可能に支持させることにより、前記ピストン
Ｂ及びブレード部Ｂ１を介して前記シリンダ室Ａ１の内
部を圧縮室Ｘと吸入室Ｙとに区画する一方、前記ピスト
ンＢに駆動軸の偏心部を挿嵌させて、この駆動軸で前記
ピストンＢを前記シリンダ室Ａ１内で公転駆動させるこ
とにより、前記吸入室Ｙにガス流体を吸入し、また、前
記圧縮室Ｘでガス流体の圧縮を行うようにしている。2. Description of the Related Art Conventionally, as an oscillating rotary compressor, as described in, for example, Japanese Unexamined Patent Publication No. 5-202874, a piston inserted into an eccentric portion of a drive shaft is
To integrally project a blade portion for partitioning the cylinder chamber into a suction chamber and a compression chamber, and swingably support the blade portion in a receiving groove of a support rotatably arranged in the cylinder. It is known that the piston compresses the gas fluid while revolving the piston. That is, as shown in FIG. 3, the conventional oscillating rotary compressor projects radially outward into the cylinder chamber A1 of the cylinder A in which the front and rear heads are axially opposed to each other. The piston B integrally provided with the blade portion B1 is arranged such that the upper and lower end surfaces of the piston B and the blade portion B1 are in sliding contact with the face surfaces of the respective heads.
A cylindrical support C slidably contacting the heads is rotatably supported inside the cylinder A, and a receiving groove C1 formed in the support C swings the tip side of the blade B1. By supporting it so that it can move forward and backward, the interior of the cylinder chamber A1 is divided into a compression chamber X and a suction chamber Y through the piston B and the blade portion B1, while the eccentric portion of the drive shaft is inserted into the piston B. By fitting and driving the piston B to revolve in the cylinder chamber A1 with this drive shaft, the gas fluid is sucked into the suction chamber Y and the gas fluid is compressed in the compression chamber X. ing.
【０００３】また、以上の圧縮機では、前記ピストンＢ
及びブレード部Ｂ１の上下両端面が前記各ヘッドに摺接
されるため、前記ピストンＢ及びブレード部Ｂ１の上下
両端面に潤滑油を供給して潤滑する必要がある。このた
め従来では、前記駆動軸の偏心部と前記ピストンＢの内
周面との間の摺接部位に給油された高圧の潤滑油を、前
記ピストンＢの内周側と前記吸入室Ｙ及び圧縮過程の圧
縮室Ｘとの間、並びに前記吸入室Ｙと圧縮室Ｘとの間の
高低差圧を利用して給油するようにしている。In the above compressor, the piston B is
Since the upper and lower end surfaces of the blade portion B1 are in sliding contact with the heads, it is necessary to supply lubricating oil to the upper and lower end surfaces of the piston B and the blade portion B1 for lubrication. Therefore, conventionally, the high-pressure lubricating oil supplied to the sliding contact portion between the eccentric portion of the drive shaft and the inner peripheral surface of the piston B is compressed to the inner peripheral side of the piston B, the suction chamber Y, and the compression chamber. Oil is supplied using the high and low differential pressures between the compression chamber X and the suction chamber Y and the compression chamber X in the process.
【０００４】即ち、吸入室Ｙは勿論、前記圧縮室Ｘにお
いても、該圧縮室Ｘでガス流体が所定圧力に圧縮される
以前の段階までは前記ピストンＢの内周面側の圧力との
間に高低差圧が生ずるし、また、吸入室Ｙと圧縮室Ｘと
の間にも高低差圧が生ずるのであって、これらの高低差
圧を利用し、前記ピストンＢと前記偏心部との間を潤滑
した後の高圧潤滑油を、図３の実線矢印イで示すよう
に、前記ピストンＢの内周側から前記圧縮室Ｘ及び吸入
室Ｙへと前記ピストンＢの上下両端面を経て導入させた
り、前記圧縮室Ｘから吸入室Ｙへと前記ブレード部Ｂ１
の上下両端面を経て導入させることにより、前記ピスト
ンＢ及びブレード部Ｂ１の上下両端面を潤滑するように
している。That is, not only in the suction chamber Y but also in the compression chamber X, between the pressure on the inner peripheral surface side of the piston B until the stage before the gas fluid is compressed to a predetermined pressure in the compression chamber X. A high-low differential pressure is generated between the intake chamber Y and the compression chamber X, and the high-low differential pressure is generated between the suction chamber Y and the compression chamber X. As shown by the solid arrow A in FIG. 3, the high-pressure lubricating oil after lubricating the oil is introduced from the inner peripheral side of the piston B into the compression chamber X and the suction chamber Y through the upper and lower end surfaces of the piston B. Or the blade portion B1 from the compression chamber X to the suction chamber Y.
The upper and lower end surfaces of the piston B and the blade portion B1 are lubricated by being introduced through the upper and lower end surfaces of the.
【０００５】[0005]
【発明が解決しようとする課題】ところが、従来では前
記したように、前記フロントヘッド及びリヤヘッドと、
これらヘッドのフェース面に摺接する前記ピストンＢ及
びブレード部Ｂ１の上下端面との給油は、高低差圧を利
用し、前記フェース面との隙間を介して給油するように
していたため、図３に示す斜線で囲んだ部分Ｄ，Ｅ、即
ち、前記ピストンＢにおけるブレード部突設基部の上下
両端面部分Ｄと、前記支持体Ｃの受入溝Ｃ１に介入して
いる前記ブレード部Ｂ１の突出先端側上下両端面部分Ｅ
とには高低差圧が発生し難いことから、潤滑油の流れが
生じず、これら部分Ｄ，Ｅにおいては潤滑不良が生じ、
従って、前記ピストンＢ及びブレード部Ｂ１の前記フェ
ース面との摺接部を確実に潤滑することができず信頼性
が低くなる問題があった。However, in the prior art, as described above, the front head and the rear head,
The piston B and the upper and lower end surfaces of the blade portion B1 that are in sliding contact with the face surface of these heads are supplied with oil through a clearance between the piston B and the upper and lower end surfaces of the blade portion B1. The portions D and E surrounded by diagonal lines, that is, the upper and lower end surface portions D of the protruding base portion of the blade portion of the piston B, and the protruding tip side upper and lower sides of the blade portion B1 intervening in the receiving groove C1 of the support C Both ends E
Since a high and low differential pressure is unlikely to occur in and, a flow of lubricating oil does not occur, and a lubrication failure occurs in these portions D and E.
Therefore, there is a problem that the sliding contact portion of the piston B and the blade portion B1 with the face surface cannot be reliably lubricated, and the reliability is lowered.
【０００６】本発明の目的は、ピストン及びブレード部
の上下両端面における全面を確実に潤滑でき、信頼性を
向上することができる揺動型ロータリー圧縮機を提供す
ることにある。An object of the present invention is to provide an oscillating rotary compressor capable of reliably lubricating the entire upper and lower end surfaces of the piston and the blade portion and improving reliability.
【０００７】[0007]
【課題を解決するための手段】上記目的を達成するた
め、請求項１記載の発明は、シリンダ１のシリンダ室１
１に、駆動軸３の偏心部３１に挿嵌するピストン２を公
転可能に内装し、このピストン２に、前記シリンダ室１
１を圧縮室Ｘと吸入室Ｙとに区画するブレード部２１を
一体的に突設して、このブレード部２１を前記シリンダ
１に回転可能に配設した支持体４の受入溝４１に揺動可
能に支持した揺動型ロータリー圧縮機において、前記ブ
レード部２１及びピストン２の前記ブレード部突設部に
おける上下端面のうち少なくとも一方に、一端が前記ピ
ストン２の内周面に開放し、他端が前記ブレード部２１
の突出側先端部に開放する油溝２２を形成したのであ
る。In order to achieve the above object, the invention according to claim 1 provides a cylinder chamber 1 of a cylinder 1.
1, a piston 2 which is fitted into the eccentric portion 31 of the drive shaft 3 is revolvably mounted inside, and the piston 2 has the cylinder chamber
1. A blade portion 21 that divides 1 into a compression chamber X and a suction chamber Y is integrally projectingly provided, and the blade portion 21 swings in a receiving groove 41 of a support body 4 rotatably arranged in the cylinder 1. In an oscillating rotary compressor that is supported so that at least one of the upper and lower end surfaces of the blade portion 21 and the protruding portion of the blade portion of the piston 2 has one end open to the inner peripheral surface of the piston 2 and the other end. Is the blade portion 21
The oil groove 22 is formed at the tip of the protruding side.
【０００８】また、請求項２記載の発明は、前記支持体
４の受入溝４１における前記ブレード部２１の背面側
に、閉鎖された高圧室１５を形成したのである。Further, in the second aspect of the present invention, the closed high pressure chamber 15 is formed on the rear surface side of the blade portion 21 in the receiving groove 41 of the support body 4.
【０００９】[0009]
【作用】請求項１記載の発明では、前記ピストン２のブ
レード部突設基部における上下両端面のうち少なくとも
一方に、一端が前記ピストン２の内周面に開放し、他端
が前記ブレード部２１の突出先端側に開放する前記油溝
２２を形成したから、前記ピストン２の内周側に給油さ
れた潤滑油が、その公転駆動時に前記ピストン２に作用
する遠心力により、前記油溝２２を流れて前記ブレード
部２１の突出先端側へと強制的に案内されると共に、こ
のとき前記油溝２２を流れる潤滑油は、前記ピストン２
の公転駆動によりこの油溝２２から前記ピストン２のブ
レード部突設基部における上下端面及び前記ブレード部
２１の上下端面に給油されるのである。従って、前記ピ
ストン２及びブレード部２１の上下端面全体が前記ピス
トン２内周面と圧縮室Ｘ、吸入室Ｙとの間に生じる差圧
を利用した差圧給油と相俟って、確実に潤滑でき、その
信頼性を向上できるのである。According to the first aspect of the present invention, at least one of the upper and lower end surfaces of the protruding portion of the blade portion of the piston 2 has one end open to the inner peripheral surface of the piston 2 and the other end is the blade portion 21. Since the oil groove 22 that opens to the protruding tip side of the piston 2 is formed, the lubricating oil supplied to the inner peripheral side of the piston 2 can move the oil groove 22 by the centrifugal force that acts on the piston 2 during its revolution drive. The lubricating oil that flows and is forcibly guided to the protruding tip side of the blade portion 21 and at this time the lubricating oil that flows in the oil groove 22 is the piston 2
By revolving drive, oil is supplied from the oil groove 22 to the upper and lower end surfaces of the protruding base of the blade portion of the piston 2 and the upper and lower end surfaces of the blade portion 21. Therefore, the entire upper and lower end surfaces of the piston 2 and the blade portion 21 are reliably lubricated together with the differential pressure oil supply utilizing the differential pressure generated between the inner peripheral surface of the piston 2 and the compression chamber X and the suction chamber Y. Yes, it can improve its reliability.
【００１０】また、請求項２記載の発明では、前記支持
体４の受入溝４１における前記ブレード部２１の背面側
に、前記油溝２２を介して前記ピストン２の内周部側に
連通する高圧室１５を形成したから、前記ピストン２の
公転駆動時に、前記油溝２２から高圧室１５内に導入さ
れた潤滑油を、該高圧室１５に充満させられ、従って、
この高圧室１５に対し低圧状態に保持される前記吸入室
Ｙ側に、前記シリンダ１内に支持された前記支持体４の
吸入室側外周部や前記ブレード部２１の吸入室側壁部に
沿って差圧により流通させられると共に、前記圧縮室Ｘ
側においては、その内部で圧縮されるガス流体が前記高
圧室１５の内部圧力と同等となるまでは、この高圧室１
５内の潤滑油を、その差圧により前記支持体４の圧縮室
側外周部や前記ブレード部２１の圧縮室側壁部に沿って
前記圧縮室Ｘへと流通させられるのである。この結果、
前記支持体４の外周部及び上下端面、さらに、前記受入
溝４１に対しても、潤滑を有効にできるのである。Further, in the second aspect of the present invention, the high pressure that communicates with the rear surface side of the blade portion 21 in the receiving groove 41 of the support body 4 through the oil groove 22 to the inner peripheral side of the piston 2. Since the chamber 15 is formed, the lubricating oil introduced from the oil groove 22 into the high pressure chamber 15 is filled in the high pressure chamber 15 when the piston 2 is revolved, and therefore,
On the suction chamber Y side which is maintained at a low pressure with respect to the high pressure chamber 15, along the suction chamber side outer peripheral portion of the support body 4 supported in the cylinder 1 and the suction chamber side wall portion of the blade portion 21. It is circulated by a differential pressure and the compression chamber X
On the side, until the gas fluid compressed therein becomes equal to the internal pressure of the high pressure chamber 15, this high pressure chamber 1
The lubricating oil in 5 is circulated to the compression chamber X along the outer peripheral portion of the support 4 on the compression chamber side and the side wall of the compression chamber of the blade portion 21 due to the pressure difference. As a result,
It is possible to effectively lubricate the outer peripheral portion and the upper and lower end surfaces of the support body 4, and also the receiving groove 41.
【００１１】[0011]
【実施例】図１及び図２は揺動型ロータリー圧縮機の圧
縮要素部分のみを示しており、この圧縮要素は、フロン
ト及びリヤヘッド（図示せず）のフェース面で閉鎖され
るシリンダ１のシリンダ室１１内に、径方向外方に向け
て突出するブレード部２１を一体状に設けたピストン２
を、これらピストン２及びブレード部２１の上下両端面
が前記各ヘッドのフェース面に摺接されるように配設す
ると共に、前記ピストン２内に駆動軸３の偏心部３１を
挿嵌させて、該駆動軸３の回転に伴い前記ピストン２
を、その外周面を前記シリンダ室１１の内壁面に接触さ
せながら公転駆動させるようになす一方、前記シリンダ
１に設けた吐出口１２と吸入孔１３との中間部位には、
前記シリンダ室１１の内部と連通する円形状の支持孔１
４を形成し、この支持孔１４に前記各ヘッドに摺接され
る支持体４を回転可能に支持して、この支持体４に設け
た受入溝４１に前記ブレード部２１の先端側を揺動及び
進退出可能に支持させている。尚、前記支持体４は、半
円柱形状とされた２つの部材４Ａ，４Ｂで形成してお
り、前記各部材４Ａ，４Ｂのフラットな対向面間を前記
受入溝４１として、該受入溝４１に前記ブレード部２１
の先端側を挿入させている。1 and 2 show only the compression element portion of an oscillating rotary compressor, which is a cylinder of cylinder 1 which is closed by the face surfaces of front and rear heads (not shown). A piston 2 in which a blade portion 21 that projects radially outward is integrally provided in the chamber 11.
Is arranged so that the upper and lower end surfaces of the piston 2 and the blade portion 21 are in sliding contact with the face surfaces of the respective heads, and the eccentric portion 31 of the drive shaft 3 is inserted into the piston 2, As the drive shaft 3 rotates, the piston 2
Is revolved while its outer peripheral surface is in contact with the inner wall surface of the cylinder chamber 11, and at an intermediate portion between the discharge port 12 and the suction hole 13 provided in the cylinder 1,
A circular support hole 1 communicating with the inside of the cylinder chamber 11.
4, a support body 4 slidably contacting the heads is rotatably supported in the support hole 14, and a tip end side of the blade portion 21 is swung in a receiving groove 41 provided in the support body 4. In addition, they are supported so that they can move in and out. The support body 4 is formed of two semi-cylindrical members 4A and 4B, and the flat facing surfaces of the members 4A and 4B are used as the receiving groove 41, and the receiving groove 41 is formed in the receiving groove 41. The blade portion 21
The tip side of is inserted.
【００１２】そして、前記ピストン２の公転駆動時に、
その外周面が前記シリンダ室１１の内壁面に接触される
接点と、前記ブレード部２１におけるピストン２の公転
方向前方側壁面とで囲まれる前記シリンダ室１１の内部
空間を前記吸入孔１３に連通する吸入室Ｙとなし、か
つ、前記接点と前記ブレード部２２における前記ピスト
ン２の公転方向後方側壁面とで囲まれる前記シリンダ室
１１の内部空間を前記吐出口１２に連通する圧縮室Ｘと
して、前記駆動軸３の駆動に伴い前記ピストン２の接点
を前記シリンダ室１１の内壁面に沿って接触させながら
移動させることにより、前記吸入孔１３から前記吸入室
Ｙ内にガスを吸入し、また、前記圧縮室Ｘ内でガスを圧
縮して前記吐出口１２から吐出し、これらガスの吸入と
圧縮とを繰り返すようにしている。When the piston 2 is revolved,
An inner space of the cylinder chamber 11, which is surrounded by a contact point whose outer peripheral surface contacts the inner wall surface of the cylinder chamber 11 and a front side wall surface of the blade portion 21 in the revolution direction of the piston 2, communicates with the suction hole 13. The internal space of the cylinder chamber 11 which is not the suction chamber Y and which is surrounded by the contact point and the rear side wall surface of the blade portion 22 in the revolution direction of the piston 2 serves as the compression chamber X communicating with the discharge port 12. When the drive shaft 3 is driven, the contact point of the piston 2 is moved along the inner wall surface of the cylinder chamber 11 while being brought into contact therewith, thereby sucking gas from the suction hole 13 into the suction chamber Y, and The gas is compressed in the compression chamber X and discharged from the discharge port 12, and suction and compression of these gases are repeated.
【００１３】また、前記駆動軸３の軸心内部には給油ポ
ンプに連通する給油通路３２を形成すると共に、前記駆
動軸３の偏心部３１に前記給油通路３２から径方向外方
に延びる分岐通路３３を設けて、前記給油通路３２に汲
上げられた高圧の潤滑油を前記分岐通路３３を介して前
記ピストン２の内周面と前記偏心部３１の外周面との摺
接部位に給油するようにしている。Further, an oil supply passage 32 communicating with an oil supply pump is formed inside the shaft center of the drive shaft 3, and a branch passage extending radially outward from the oil supply passage 32 is formed in the eccentric portion 31 of the drive shaft 3. 33 is provided so that the high-pressure lubricating oil pumped up to the oil supply passage 32 is supplied to the sliding contact portion between the inner peripheral surface of the piston 2 and the outer peripheral surface of the eccentric portion 31 via the branch passage 33. I have to.
【００１４】また、前記ピストン２の内周部側は、該ピ
ストン２の公転駆動時、前記給油ポンプで汲上げられた
高圧潤滑油が給油されて高圧となるのであり、従って、
このピストン２の内周部側と前記吸入室Ｙとの間には、
常に所定の高低差圧が発生するし、また、前記圧縮室Ｘ
側においては、該圧縮室Ｘでガス流体が前記ピストン２
の内周側の圧力と同等圧力に圧縮されるまでは、前記内
周部側との間に所定の高低差圧が発生することになる。
この結果、前記ピストン２の内周部に給油される高圧潤
滑油は、図１，２の実線矢印イで示すように、前記ピス
トン２の内周部側から前記圧縮室Ｘ及び吸入室Ｙへと前
記ピストン２の上下両端面を経て導入され、これら圧縮
室Ｘ及び吸入室Ｙへと潤滑油が導入されるとき、前記ピ
ストン２の公転駆動に伴いその上下両端面に給油され
る。Further, the inner peripheral side of the piston 2 is supplied with high pressure lubricating oil pumped by the oil supply pump to have a high pressure when the piston 2 revolves.
Between the inner peripheral side of the piston 2 and the suction chamber Y,
A predetermined high and low differential pressure is always generated, and the compression chamber X
On the side, the gas fluid is transferred to the piston 2 in the compression chamber X.
Until it is compressed to a pressure equal to the pressure on the inner peripheral side, a predetermined pressure difference between the inner peripheral side and the inner peripheral side is generated.
As a result, the high-pressure lubricating oil supplied to the inner peripheral portion of the piston 2 flows from the inner peripheral portion side of the piston 2 to the compression chamber X and the suction chamber Y as shown by the solid arrow A in FIGS. When the lubricating oil is introduced into the compression chamber X and the suction chamber Y through the upper and lower end surfaces of the piston 2, the upper and lower end surfaces of the piston 2 are refueled as the piston 2 revolves.
【００１５】しかして、図１に示した実施例は、以上の
構成において、前記ピストン２の前記ブレード部突設部
における上下両端面と、前記ブレード部２１の上下両端
面とに、一端が前記ピストン２の内周面に開放され、か
つ、他端が前記ブレード部２１の突出先端側に開放され
る直線状の油溝２２をそれぞれ形成したのである。Therefore, in the embodiment shown in FIG. 1, in the above-mentioned structure, one end is formed on each of the upper and lower end surfaces of the blade portion projecting portion of the piston 2 and the upper and lower end surfaces of the blade portion 21. A linear oil groove 22 is formed so as to be opened to the inner peripheral surface of the piston 2 and open at the other end to the protruding tip side of the blade portion 21.
【００１６】従って、前記駆動軸３の給油通路３２に汲
上げられて前記分岐通路３３からピストン２と前記偏心
部３１との摺接部位に給油された後の潤滑油は、図１の
実線矢印ハで示すように、前記ピストン２の公転駆動時
に発生する遠心力で前記各油溝２２に沿って前記ブレー
ド部２１の突出先端側へと強制的に案内され、これら各
油溝２２を流れる潤滑油が前記ピストン２の公転駆動に
より、前記油溝２２から、前記ピストン２のブレード部
突設基部における上下両端面と、前記ブレード部２１に
おける上下両端面とに給油されるのである。Therefore, the lubricating oil after being pumped up to the oil supply passage 32 of the drive shaft 3 and supplied from the branch passage 33 to the sliding contact portion between the piston 2 and the eccentric portion 31 is a solid arrow in FIG. As shown by C, the centrifugal force generated when the piston 2 revolves is forcibly guided along the oil grooves 22 toward the protruding tip side of the blade portion 21, and the lubrication flowing in the oil grooves 22 is performed. The oil is supplied from the oil groove 22 to the upper and lower end surfaces of the protruding base portion of the blade portion of the piston 2 and the upper and lower end surfaces of the blade portion 21 by the revolution of the piston 2.
【００１７】この結果、前記ピストン２及びブレード部
２１の上下両端面全体を確実に潤滑できるようになり、
信頼性に優れたものとなし得るのである。尚、前述した
図１の実施例においては、前記支持体４の受入溝４１に
おける前記ブレード部２１の突出先端側を開放したが、
前記シリンダ１の外部側に対し閉鎖させてもよく、何れ
の場合でも、前記ピストン２及びブレード部２１の上下
両端面全体を確実に潤滑できるのである。As a result, the entire upper and lower end surfaces of the piston 2 and the blade portion 21 can be reliably lubricated,
It can be made highly reliable. In the embodiment of FIG. 1 described above, the protruding tip side of the blade portion 21 in the receiving groove 41 of the support 4 is opened.
It may be closed to the outside of the cylinder 1, and in any case, the entire upper and lower end surfaces of the piston 2 and the blade portion 21 can be reliably lubricated.
【００１８】また、図２に示した実施例は、前記シリン
ダ１における前記支持孔１４のブレード部突出先端側と
なる外方位置に、前記支持体４を構成する２つの部材４
Ａ，４Ｂ間に形成される受入溝４１と連続し、かつ、前
記ブレード部２１に設けた前記油溝２２を介して前記ピ
ストン２の内周部側に連通する高圧室１５を、前記シリ
ンダ１の外部側に対し閉鎖状に形成したものである。Further, in the embodiment shown in FIG. 2, the two members 4 constituting the support body 4 are provided at the outer position of the support hole 14 of the cylinder 1 on the tip side of the protruding blade portion.
The high pressure chamber 15 which is continuous with the receiving groove 41 formed between A and 4B and communicates with the inner peripheral side of the piston 2 through the oil groove 22 provided in the blade portion 21 is connected to the cylinder 1 It is formed in a closed shape with respect to the outer side of.
【００１９】以上の構成とするときは、前記ピストン２
の公転駆動時で、そのブレード部２１が前記高圧室１５
に対し進出方向に公転されるとき、前記ピストン２の遠
心力により、該ピストン２の内周部に給油された高圧の
潤滑油が前記油溝２２を介して前記高圧室１５へと導入
されて充満することになり、このため、図２の点線矢印
ロで示したように、前記ブレード部２１の移動に伴い前
記高圧室１５内の潤滑油が、差圧で前記支持孔１４に支
持された前記支持体４の吸入室側外周部や前記ブレード
部２１の吸入室側壁部に沿って前記吸入室Ｙ側へ流れ
る。また一方、前記圧縮室Ｘ側においては、その内部で
圧縮されるガス流体が前記高圧室１５の内部圧力と同圧
以上となるまでは、この高圧室１５内の潤滑油が差圧に
より前記支持体４の圧縮室側外周部や前記ブレード部２
１の圧縮室側壁部に沿って前記圧縮室Ｘへと流れるので
あり、従って、前記高圧室１４から圧縮室Ｘ及び吸入室
Ｙへの差圧による油流れにより、前記支持体４の外周部
や上下端面及び受入溝４１に給油でき、前記支持体４の
外周部及び上下端面、さらに、前記ブレード部２１が摺
動する前記受入溝４１の潤滑も有効に行うことができる
のである。In the case of the above construction, the piston 2
When the orbital drive of the
On the other hand, when the piston 2 is revolved in the advancing direction, the centrifugal force of the piston 2 causes the high-pressure lubricating oil supplied to the inner peripheral portion of the piston 2 to be introduced into the high-pressure chamber 15 via the oil groove 22. Therefore, as shown by the dotted arrow B in FIG. 2, the lubricating oil in the high pressure chamber 15 is supported in the support hole 14 by the differential pressure as the blade portion 21 moves. It flows to the suction chamber Y side along the suction chamber side outer peripheral portion of the support body 4 and the suction chamber side wall portion of the blade portion 21. On the other hand, on the compression chamber X side, until the gas fluid compressed therein has a pressure equal to or higher than the internal pressure of the high pressure chamber 15, the lubricating oil in the high pressure chamber 15 is supported by the differential pressure. The outer peripheral portion of the body 4 on the compression chamber side and the blade portion 2
1 flows to the compression chamber X along the side wall of the compression chamber 1. Therefore, the oil flow due to the differential pressure from the high pressure chamber 14 to the compression chamber X and the suction chamber Y causes the outer peripheral portion of the support 4 and the like. Oil can be supplied to the upper and lower end surfaces and the receiving groove 41, and the outer peripheral portion and the upper and lower end surfaces of the support body 4 and the receiving groove 41 on which the blade portion 21 slides can be effectively lubricated.
【００２０】[0020]
【発明の効果】以上説明したように、請求項１記載の発
明によれば、シリンダ１のシリンダ室１１内に、駆動軸
３の偏心部３１に挿嵌するピストン２を公転可能に内装
し、このピストン２に、前記シリンダ室１１を圧縮室Ｘ
と吸入室Ｙとに区画するブレード部２１を一体的に突設
して、このブレード部２１を前記シリンダ１に回転可能
に設けた支持体４の受入溝４１に揺動可能に支持した揺
動型ロータリー圧縮機において、前記ピストン２とその
ブレード部２１における上下端面のうち少なくとも一方
に、一端が前記ピストン２の内周面に開放し、他端が前
記ブレード部２１の突出側先端部に開放する油溝２２を
形成したから、前記ピストン２の内周側に給油された潤
滑油を、その公転駆動時に前記ピストン２に作用する遠
心力により、前記油溝２２を介して前記ブレード部２１
の突出先端側へと強制的に案内でき、このとき前記油溝
２２を流れる潤滑油によって、前記ピストン２のブレー
ド部突設基部における上下端面及び前記ブレード部２１
の上下端面に給油できるのである。従って、前記ピスト
ン２及びブレード部２１の上下端面全体が前記ピストン
２内周面と圧縮室Ｘ、吸入室Ｙとの間に生じる差圧を利
用した差圧給油と相俟って、確実に潤滑でき、その信頼
性を向上できるのである。As described above, according to the first aspect of the invention, the piston 2 inserted into the eccentric portion 31 of the drive shaft 3 is revolvably mounted in the cylinder chamber 11 of the cylinder 1. The piston 2 is provided with the cylinder chamber 11 and the compression chamber X.
And a suction chamber Y, a blade portion 21 is integrally projectingly provided, and the blade portion 21 is swingably supported in a receiving groove 41 of a support body 4 rotatably provided in the cylinder 1. -Type rotary compressor, at least one of the upper and lower end surfaces of the piston 2 and its blade portion 21 has one end opened to the inner peripheral surface of the piston 2 and the other end opened to the protruding side tip portion of the blade portion 21. Since the oil groove 22 is formed, the lubricating oil supplied to the inner peripheral side of the piston 2 is moved through the oil groove 22 by the centrifugal force that acts on the piston 2 when it is revolved.
Of the piston 2 can be forcibly guided to the protruding tip side of the piston 2, and the lubricating oil flowing in the oil groove 22 at this time allows the upper and lower end surfaces of the protruding base portion of the blade portion of the piston 2 and the blade portion 21.
The upper and lower end surfaces of the can be refueled. Therefore, the entire upper and lower end surfaces of the piston 2 and the blade portion 21 are reliably lubricated together with the differential pressure oil supply utilizing the differential pressure generated between the inner peripheral surface of the piston 2 and the compression chamber X and the suction chamber Y. Yes, it can improve its reliability.
【００２１】また、請求項２記載の発明では、前記支持
体４の受入溝４１における前記ブレード部２１の背面側
に、前記油溝２２を介して前記ピストン２の内部側に連
通する高圧室１５を閉鎖状に形成したから、前記ピスト
ン２の公転駆動時に、前記油溝２２から高圧室１５内に
導入された潤滑油を、該高圧室１５に充満させられ、従
って、この高圧室１５に対し低圧状態に保持される前記
吸入室Ｙ側に、前記シリンダ１内に支持された前記支持
体４の吸入室側外周部や前記ブレード部２１の吸入室側
壁部に沿って差圧により流通できると共に、前記圧縮室
Ｘ側においては、その内部で圧縮されるガス流体が前記
高圧室１５の内部圧力と同等となるまでは、この高圧室
１５内の潤滑油を、その差圧により前記支持体４の圧縮
室側外周部や前記ブレード部２１の圧縮室側壁部に沿っ
て前記圧縮室Ｘへと流通できるのである。この結果、前
記支持体４の外周部及び上下端面、さらに、前記受入溝
４１に対しても、潤滑を有効にできるのである。According to the second aspect of the present invention, the high pressure chamber 15 communicating with the back side of the blade portion 21 in the receiving groove 41 of the support 4 and the inside of the piston 2 through the oil groove 22. Is closed, the lubricating oil introduced from the oil groove 22 into the high pressure chamber 15 is filled in the high pressure chamber 15 when the piston 2 is revolved. On the side of the suction chamber Y that is maintained at a low pressure, it can flow by a differential pressure along the suction chamber side outer periphery of the support body 4 supported in the cylinder 1 and the suction chamber side wall of the blade portion 21. On the side of the compression chamber X, until the gas fluid compressed therein becomes equal to the internal pressure of the high-pressure chamber 15, the lubricating oil in the high-pressure chamber 15 is moved to the support 4 by the differential pressure. The outer periphery of the compression chamber and the above Than it can flow into the compression chamber X along a compression chamber side wall of the blade section 21. As a result, it is possible to effectively lubricate the outer peripheral portion and the upper and lower end surfaces of the support body 4 as well as the receiving groove 41.
【図１】本発明にかかる揺動型ロータリー圧縮機のピス
トンを示す斜視図である。FIG. 1 is a perspective view showing a piston of an oscillating rotary compressor according to the present invention.
【図２】同圧縮機の要部を示す平面図である。FIG. 2 is a plan view showing a main part of the compressor.
【図３】従来のピストンを示す斜視図である。FIG. 3 is a perspective view showing a conventional piston.
１ シリンダ １１ シリンダ室 １３ 吸入孔 １５ 高圧室 ２ ピストン ２１ ブレード部 ２２ 油溝 ３ 駆動軸 ３１ 偏心部 ４ 支持体 ４１ 受入溝 Ｘ 圧縮室 Ｙ 吸入室 1 Cylinder 11 Cylinder chamber 13 Suction hole 15 High pressure chamber 2 Piston 21 Blade part 22 Oil groove 3 Drive shaft 31 Eccentric part 4 Support 41 Receiving groove X Compression chamber Y Suction chamber
Claims (2)
に、駆動軸（３）の偏心部（３１）に挿嵌するピストン
（２）を公転可能に内装し、このピストン（２）に、前
記シリンダ室（１１）を圧縮室（Ｘ）と吸入室（Ｙ）と
に区画するブレード部（２１）を一体的に突設して、こ
のブレード部（２１）を前記シリンダ（１）に回転可能
に配設した支持体（４）の受入溝（４１）に揺動可能に
支持した揺動型ロータリー圧縮機であって、前記ブレー
ド部（２１）及びピストン（２）の前記ブレード部（２
１）突設部における上下端面の少なくとも一方に、一端
が前記ピストン（２）の内周面に開放し、他端が前記ブ
レード部（２１）の突出先端部に開放する油溝（２２）
を形成していることを特徴とする揺動型ロータリー圧縮
機。1. A cylinder chamber (11) of a cylinder (1)
A piston (2) which is fitted into the eccentric part (31) of the drive shaft (3) is revolvably installed inside, and the cylinder chamber (11) is provided in the compression chamber (X) and the suction chamber in the piston (2). A blade portion (21) that is partitioned into (Y) and a blade portion (21) are integrally projected, and the blade portion (21) is rotatably disposed in the cylinder (1). ) Is swingably supported by the blade portion (21) and the blade portion (2) of the piston (2).
1) An oil groove (22) whose one end opens to the inner peripheral surface of the piston (2) and the other end opens to the protruding tip of the blade part (21) on at least one of the upper and lower end faces of the protruding part.
An oscillating rotary compressor, characterized in that
ブレード部（２１）の背面側に、閉鎖された高圧室（１
５）を形成している請求項１記載の揺動型ロータリー圧
縮機。2. A closed high-pressure chamber (1) on the rear side of the blade (21) in the receiving groove (41) of the support (4).
5) The oscillating rotary compressor according to claim 1, which forms 5).
Priority Applications (12)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30792493A JP3473067B2 (en) | 1993-12-08 | 1993-12-08 | Swing type rotary compressor |
| SG1996004083A SG43887A1 (en) | 1993-12-08 | 1994-12-01 | A swing type rotary compressor |
| EP95902284A EP0683321B1 (en) | 1993-12-08 | 1994-12-01 | Swinging rotary compressor |
| DK95902284T DK0683321T3 (en) | 1993-12-08 | 1994-12-01 | Swing type rotary compressor |
| DE69427186T DE69427186T2 (en) | 1993-12-08 | 1994-12-01 | SWINGING ROTATIONAL COMPRESSOR |
| KR1019950703289A KR100322269B1 (en) | 1993-12-08 | 1994-12-01 | Oscillating Rotary Compressor |
| CN94191130A CN1041453C (en) | 1993-12-08 | 1994-12-01 | Swinging rotary compressor |
| US08/500,847 US5577903A (en) | 1993-12-08 | 1994-12-01 | Rotary compressor |
| ES95902284T ES2158069T3 (en) | 1993-12-08 | 1994-12-01 | OSCILLATING ROTARY COMPRESSOR. |
| PCT/JP1994/002020 WO1995016136A1 (en) | 1993-12-08 | 1994-12-01 | Swinging rotary compressor |
| MYPI94003243A MY119158A (en) | 1993-12-08 | 1994-12-06 | Rotary compressor |
| TW086201162U TW378721U (en) | 1993-12-08 | 1994-12-07 | A swing type rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30792493A JP3473067B2 (en) | 1993-12-08 | 1993-12-08 | Swing type rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07158574A true JPH07158574A (en) | 1995-06-20 |
| JP3473067B2 JP3473067B2 (en) | 2003-12-02 |
Family
ID=17974812
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP30792493A Expired - Fee Related JP3473067B2 (en) | 1993-12-08 | 1993-12-08 | Swing type rotary compressor |
Country Status (10)
| Country | Link |
|---|---|
| EP (1) | EP0683321B1 (en) |
| JP (1) | JP3473067B2 (en) |
| KR (1) | KR100322269B1 (en) |
| CN (1) | CN1041453C (en) |
| DE (1) | DE69427186T2 (en) |
| DK (1) | DK0683321T3 (en) |
| ES (1) | ES2158069T3 (en) |
| MY (1) | MY119158A (en) |
| SG (1) | SG43887A1 (en) |
| WO (1) | WO1995016136A1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6336336B1 (en) | 2000-03-20 | 2002-01-08 | Hitachi, Ltd. | Rotary piston compressor and refrigerating equipment |
| JP2008121577A (en) * | 2006-11-13 | 2008-05-29 | Daikin Ind Ltd | Rotary fluid machine |
| JP2010025103A (en) * | 2008-06-16 | 2010-02-04 | Daikin Ind Ltd | Rotary compressor |
| JP2013139720A (en) * | 2011-12-28 | 2013-07-18 | Daikin Industries Ltd | Rotary compressor |
| JP2014077415A (en) * | 2012-10-11 | 2014-05-01 | Toshiba Carrier Corp | Hermetic type compressor and refrigeration cycle device |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1997024415A1 (en) | 1995-12-28 | 1997-07-10 | Daikin Industries, Ltd. | Refrigerating machine oil and refrigerator using same |
| JP3731127B2 (en) * | 2004-01-22 | 2006-01-05 | ダイキン工業株式会社 | Swing compressor |
| CN101328891B (en) * | 2008-07-22 | 2012-08-08 | 温岭市鑫磊空压机有限公司 | Dual rotors translation type rotary compressing device |
| KR101499976B1 (en) * | 2008-07-22 | 2015-03-10 | 엘지전자 주식회사 | compressor |
| CN102788017B (en) * | 2012-07-03 | 2015-04-08 | 邵阳学院 | Portable inflator |
| CN104595195B (en) * | 2014-12-04 | 2016-06-29 | 广东美芝制冷设备有限公司 | Low backpressure rotary compressor |
| JP6256643B2 (en) * | 2016-02-23 | 2018-01-10 | ダイキン工業株式会社 | Swing piston compressor |
| JP6520999B2 (en) * | 2017-07-31 | 2019-05-29 | ダイキン工業株式会社 | Production control system and production control method |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR698476A (en) * | 1928-11-27 | 1931-01-31 | Thomson Houston Comp Francaise | Improvements to rotary pumps |
| FR937086A (en) * | 1946-10-07 | 1948-08-06 | Rotary compressor | |
| GB729281A (en) * | 1952-11-22 | 1955-05-04 | Vadim Stephane Makaroff | Improvements in rotary fluid motors, compressors, pumps and the like |
| DE1428140A1 (en) * | 1964-03-11 | 1969-11-20 | Inpaco Trust Reg | Compressor with eccentrically moving rotary piston |
| JPS48113011U (en) * | 1972-03-28 | 1973-12-25 | ||
| JP2576235B2 (en) * | 1989-08-10 | 1997-01-29 | ダイキン工業株式会社 | Rotary compressor |
| JP3178559B2 (en) * | 1991-09-24 | 2001-06-18 | ダイキン工業株式会社 | Rotary compressor |
| JP2776134B2 (en) * | 1992-04-28 | 1998-07-16 | ダイキン工業株式会社 | Rotary compressor |
| JP2768114B2 (en) * | 1992-03-04 | 1998-06-25 | ダイキン工業株式会社 | Rotary compressor |
| JP2770648B2 (en) * | 1992-05-11 | 1998-07-02 | ダイキン工業株式会社 | Rotary compressor |
-
1993
- 1993-12-08 JP JP30792493A patent/JP3473067B2/en not_active Expired - Fee Related
-
1994
- 1994-12-01 DK DK95902284T patent/DK0683321T3/en active
- 1994-12-01 WO PCT/JP1994/002020 patent/WO1995016136A1/en active IP Right Grant
- 1994-12-01 KR KR1019950703289A patent/KR100322269B1/en not_active IP Right Cessation
- 1994-12-01 CN CN94191130A patent/CN1041453C/en not_active Expired - Fee Related
- 1994-12-01 SG SG1996004083A patent/SG43887A1/en unknown
- 1994-12-01 DE DE69427186T patent/DE69427186T2/en not_active Expired - Lifetime
- 1994-12-01 EP EP95902284A patent/EP0683321B1/en not_active Expired - Lifetime
- 1994-12-01 ES ES95902284T patent/ES2158069T3/en not_active Expired - Lifetime
- 1994-12-06 MY MYPI94003243A patent/MY119158A/en unknown
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6336336B1 (en) | 2000-03-20 | 2002-01-08 | Hitachi, Ltd. | Rotary piston compressor and refrigerating equipment |
| JP2008121577A (en) * | 2006-11-13 | 2008-05-29 | Daikin Ind Ltd | Rotary fluid machine |
| JP2010025103A (en) * | 2008-06-16 | 2010-02-04 | Daikin Ind Ltd | Rotary compressor |
| JP2013139720A (en) * | 2011-12-28 | 2013-07-18 | Daikin Industries Ltd | Rotary compressor |
| JP2014077415A (en) * | 2012-10-11 | 2014-05-01 | Toshiba Carrier Corp | Hermetic type compressor and refrigeration cycle device |
Also Published As
| Publication number | Publication date |
|---|---|
| SG43887A1 (en) | 1997-11-14 |
| DK0683321T3 (en) | 2001-05-28 |
| EP0683321B1 (en) | 2001-05-09 |
| ES2158069T3 (en) | 2001-09-01 |
| MY119158A (en) | 2005-04-30 |
| CN1041453C (en) | 1998-12-30 |
| WO1995016136A1 (en) | 1995-06-15 |
| JP3473067B2 (en) | 2003-12-02 |
| EP0683321A1 (en) | 1995-11-22 |
| CN1117755A (en) | 1996-02-28 |
| KR960701306A (en) | 1996-02-24 |
| EP0683321A4 (en) | 1996-05-15 |
| DE69427186T2 (en) | 2001-09-20 |
| DE69427186D1 (en) | 2001-06-13 |
| KR100322269B1 (en) | 2002-06-20 |
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