JPH04128585A - Oil feed system for compressor - Google Patents
Oil feed system for compressorInfo
- Publication number
- JPH04128585A JPH04128585A JP24973490A JP24973490A JPH04128585A JP H04128585 A JPH04128585 A JP H04128585A JP 24973490 A JP24973490 A JP 24973490A JP 24973490 A JP24973490 A JP 24973490A JP H04128585 A JPH04128585 A JP H04128585A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- passage
- pressure
- drive shaft
- oil supply
- 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
- 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
- F04C29/021—Control systems for the circulation of the lubricant
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、主に回転数を可変としたスクロールタイプの
圧縮機に適した給油機構に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an oil supply mechanism suitable mainly for a scroll type compressor with variable rotation speed.
（従来の技術）
従来、特開平２−４５６１３６号公報に開示され且つ第
４図に概略示すように、固定スクロール（Ｆ）及び可動
スクロール（０）をもつスクロールタイプの圧縮要素（
Ｃ）を、エンジン等の外部駆動源で１動される駆動軸（
Ｄ）並びにこれに連動されるスイングリンク（Ｓ）を介
して駆動し、前記駆動軸（Ｄ）の内部に油ポンプ（Ｐ）
から延びる給油通路（Ｔ）を設けると共に、前記駆動軸
（Ｄ）の軸端部に、該軸端部からの開放油量を規制する
オリフィス（Ａ）を介装して、該オリフィス（Ａ）で規
制される所定量の油を、前記スイングリンク（Ｓ）と可
動スクロール（０）との間のボス部軸受（Ｒ）や可動ス
クロール（０）のスラスト軸受（Ｂ）並びに圧縮室（Ｅ
）に供給し、前記各軸受（Ｒ）（Ｂ）の潤滑や前記圧縮
室（Ｅ）内のシール等が行えるようにしている。尚、前
記１１縮室（Ｅ）から萬圧の吐出！ （Ｈ）に流出した
油は油戻し通路を介して低圧の油溜（Ｌ）に戻すように
し、ている。(Prior Art) Conventionally, as disclosed in Japanese Patent Application Laid-open No. 2-456136 and schematically shown in FIG. 4, a scroll type compression element (
C) is a drive shaft (
D) and a swing link (S) interlocked therewith, and an oil pump (P) is installed inside the drive shaft (D).
An oil supply passage (T) extending from the drive shaft (D) is provided, and an orifice (A) for regulating the amount of oil released from the shaft end is interposed at the shaft end of the drive shaft (D). A predetermined amount of oil regulated by
) to lubricate the bearings (R) and (B) and seal the inside of the compression chamber (E). In addition, ten thousand pressures are discharged from the 11 contraction chamber (E)! The oil spilled into (H) is returned to the low-pressure oil reservoir (L) via an oil return passage.
（発明が解決しようとする課題）
しかし、以上のものでは、駆動軸（Ｄ）の軸端部かち開
放する油量を単一のオリフィス（Ａ）のみで規制するよ
うにしているから、該オリフィス（Ａ）の口径を、油ポ
ンプ（Ｐ）の汲上げ油量が増大する高速回転時等のよう
に給油通路（Ｔ）内の油圧が高まる高油圧時に対応して
小さく設定していると、逆に低速回転時等の低油圧時、
小さな口径とした前記オリフィス（Ａ）からの開放油量
が減り、各軸受（Ｒ）（Ｂ）で十分な潤滑が行えないと
共に、圧縮室（Ｅ）内のシール性が損なわれ、又、圧縮
室（Ｅ）の注入油量の減少に伴い吐出室（Ｈ）からの戻
し油量が極端に減り、油戻し、通路を介して低圧の油溜
（Ｌ）に吐出ガスが漏れ、性能の低下を招く問題が起こ
る。(Problem to be Solved by the Invention) However, in the above method, the amount of oil released from the shaft end of the drive shaft (D) is regulated by only a single orifice (A). If the diameter of (A) is set small to correspond to high oil pressure when the oil pressure in the oil supply passage (T) increases, such as during high speed rotation when the amount of oil pumped by the oil pump (P) increases, Conversely, when the oil pressure is low such as during low speed rotation,
The amount of oil released from the orifice (A), which has a small diameter, is reduced, making it impossible to provide sufficient lubrication for each bearing (R) and (B), as well as impairing the sealing performance in the compression chamber (E). As the amount of oil injected into the chamber (E) decreases, the amount of oil returned from the discharge chamber (H) decreases dramatically, and the discharge gas leaks into the low-pressure oil reservoir (L) through the oil return and passage, resulting in a decrease in performance. Problems that lead to this occur.
一方、前記オリフィス（Ａ）の口径を、油ポンプ（Ｐ）
からの汲上げ油量が減少する低速回転時等のように給油
通路（Ｔ）内の油圧が低くなる低油圧時に対応して大き
く設定すると、高速回転時等の高油圧時に、前記駆動軸
（Ｄ）から開放される油量が過剰になり、圧縮室（Ｅ）
に注入される油量が必要以上に増えて、吐出室（Ｈ）に
流出する油量が油戻し能力を越えて増大し、吐出管を通
じて外部に流出する油量が増えて油溜（Ｌ）の油が減少
し、所謂油上がりの問題が起こる。On the other hand, the diameter of the orifice (A) is changed to that of the oil pump (P).
If the oil pressure in the oil supply passage (T) is set to a large value corresponding to low oil pressure when the oil pressure in the oil supply passage (T) is low, such as during low speed rotation when the amount of oil pumped from the drive shaft (T) decreases, the drive shaft ( The amount of oil released from D) becomes excessive and the compression chamber (E)
The amount of oil injected into the discharge chamber (H) increases more than necessary, and the amount of oil flowing into the discharge chamber (H) increases beyond the oil return capacity, and the amount of oil flowing out through the discharge pipe increases, causing the oil sump (L) to increase. The amount of oil decreases, causing the so-called oil run-up problem.
従って、上記従来例のように一つのオリフィス（Ａ）の
みで給油量を規制していたのでは、高油圧時及び低油圧
時何れも満足する適正な給油を行うことができない問題
がある。Therefore, if the amount of oil supply is regulated by only one orifice (A) as in the conventional example, there is a problem in that it is not possible to supply oil satisfactorily at both high and low oil pressures.
本発明の目的は、低速回転時等の低油圧時と高速回転時
等の高油圧時とで開放油量を変更できるようにし、広い
運転節回にわたり適正な給油が行える圧縮機の給油機構
を提供する点にある。An object of the present invention is to provide a compressor oil supply mechanism that allows the amount of oil released to be changed between low oil pressure, such as during low speed rotation, and high oil pressure, such as high speed rotation, and that enables appropriate oil supply over a wide range of operating intervals. It is in the point of providing.
（課題を解決するための手段）
そこで、本発明では、上記目的を達成するため、圧縮要
素（１）を駆動する駆動軸（２）の内部に、油ポンプ（
３）から延びる給油通路（４）を備え、前記駆動軸（２
）の軸端部から開放する油を給油部に供給するようにし
た圧縮機の給油機構において、前記駆動軸（２）の軸端
部に、前記給油通路（４）に連通ずる油注入主通路（５
）と該主通路（５）を迂回する補助通路（６）とを設け
ると共に、前記駆動軸（２）の軸端部に、前記給油通路
（４）内の油圧変化により変位され、低油圧時、前記補
助通路（６）を給油通路（４）に対し開き、高油圧時、
前記補助通路（６）を給油通路（４）に対し遮断して、
低油圧時の油開放口を高油圧時の油開放口に対し増大さ
せる油圧作動型の油量調節弁（８）を介装した。(Means for Solving the Problem) Therefore, in the present invention, in order to achieve the above object, an oil pump (
a refueling passage (4) extending from the drive shaft (2);
), in which oil released from the shaft end of the compressor is supplied to the oil supply section, an oil injection main passage communicating with the oil supply passage (4) at the shaft end of the drive shaft (2); (5
) and an auxiliary passage (6) that bypasses the main passage (5), and a shaft end of the drive shaft (2) that is displaced by changes in oil pressure in the oil supply passage (4), and is provided with an auxiliary passage (6) that bypasses the main passage (5). , the auxiliary passage (6) is opened to the oil supply passage (4), and when the oil pressure is high,
blocking the auxiliary passage (6) from the oil supply passage (4);
A hydraulically actuated oil amount control valve (8) is installed to increase the oil release port at low oil pressure compared to the oil release port at high oil pressure.
（作用）
低油圧時、油量調節弁（８）により補助通路（６）が開
かれ、油注入主通路（５）と補助通路（６）との２つの
経路を介して油が開放され、油圧の減少を補って必要油
量を確保できると共に、高油圧時、前記油量調節弁（８
）により補助通路（６）が遮断され、油注入主通路（５
）のみを介して油が開放され、開放油量を抑制して過剰
給油を防止できる。(Function) When the oil pressure is low, the auxiliary passage (6) is opened by the oil amount control valve (8), and oil is released through two paths: the oil injection main passage (5) and the auxiliary passage (6). It is possible to compensate for the decrease in oil pressure and secure the required oil amount, and when the oil pressure is high, the oil amount adjustment valve (8)
), the auxiliary passage (6) is blocked off, and the main oil injection passage (5
), the oil is released only through the valve, and the amount of oil released can be suppressed to prevent over-lubrication.
（実施例）
第３図に示すものは、横型開放タイプのスクロール圧縮
機であって、横形ケーシング（９）の内部に、固定スク
ロール（１１）と可動スクロール（１２）とをもつ圧縮
要素（１）を内装しており、駆動軸（２）の−側を前記
ケーシング（９）の外部に突出させて、その突出端にエ
ンジン等の外部駆動源に接続されるブー！Ｊ（２０）を
取り付け、２０〜７０Ｈｚ程度の可変速範囲内で運転を
行うようにしている。(Embodiment) The one shown in FIG. 3 is a horizontal open type scroll compressor, in which a compression element (1) having a fixed scroll (11) and a movable scroll (12) is provided inside a horizontal casing (9). ), the - side of the drive shaft (2) projects outside the casing (9), and the projecting end is connected to an external drive source such as an engine. J (20) is installed, and the engine is operated within a variable speed range of about 20 to 70 Hz.
前記駆動軸（２）の回転は、軸端部に一体化するカウン
タウェイト（２１）、及びその端面に突設するドライブ
ビン（２２）に嵌合すれ且つリミットビン（２３）によ
り一定範囲の揺動を可能にしたスイングリンク（２４）
を介して可動スクロール（１２）に伝達される。又、可
動スクロール（１２）の自転は、該スクロールとハウジ
ング（９０）とに係合するキー（図示せず）をもつオル
ダムリング（２５）により阻止される。全体の回転バラ
ンスは、駆動軸（２）に結合するバランスウェイト（２
６）により保持される。The rotation of the drive shaft (2) is controlled by a counterweight (21) integrated at the end of the shaft, a drive bin (22) protruding from the end face of the drive shaft, and a limit bin (23). Swing link that enables movement (24)
It is transmitted to the movable scroll (12) via the movable scroll (12). Rotation of the movable scroll (12) is also prevented by an Oldham ring (25) having a key (not shown) that engages the scroll and the housing (90). The overall rotational balance is determined by the balance weight (2) connected to the drive shaft (2).
6).
こうし、で、前記可動スクロール（１２）を固定スクロ
ール（１１）に対し公転駆動させ、吸入管（９１）から
ケーシング（９）の内部に取込む低圧ガスを、各スクロ
ール（１１）（１２）間に画成する圧縮室（１３）で圧
縮し、高圧ガスを、吐出穴（１４）から吐出室（１５）
に開放して油分離器（１６）を通過させた後、吐出管（
９２）から外部に取出すようにしている。In this way, the movable scroll (12) is driven to revolve relative to the fixed scroll (11), and the low pressure gas taken into the inside of the casing (9) from the suction pipe (91) is transferred to each scroll (11) (12). The high-pressure gas is compressed in the compression chamber (13) defined between the two, and is passed from the discharge hole (14) to the discharge chamber (15).
After opening to the oil separator (16) and passing through the oil separator (16), the discharge pipe (
92) to the outside.
一方、前記駆動軸（２）の軸心には油ポンプ（３）から
延びる給油通路（４）を備え、主軸受（４１）に給油す
ると共に、軸端部から開放する油を、可動スクロール（
１２）とスイングリンク（２４）との間のボス部軸受（
４２）に供給し、更に、該ボス部軸受（４２）を給油し
た後の油を可動スクロール（１２）のスラスト軸受（４
３）及び圧縮室（１３）側に跳ね上げ、各部で潤滑及び
シールを行うようにしている。吐出室（１５）に流出し
た油は油戻し管（４４）を介して底部油溜（９３）に戻
すようにしている。尚、給油通路（４）における反圧線
要素側通路（４０）は、図示しないが、駆動軸（２）の
開放側に介装する主軸受やメカニカルシールに連通させ
ている。On the other hand, the axial center of the drive shaft (2) is provided with an oil supply passage (4) extending from an oil pump (3) to supply oil to the main bearing (41) and to supply oil released from the shaft end to the movable scroll (
12) and the swing link (24).
42), and the boss bearing (42) is then supplied to the thrust bearing (42) of the movable scroll (12).
3) and the compression chamber (13) side, and lubricates and seals each part. The oil spilled into the discharge chamber (15) is returned to the bottom oil sump (93) via an oil return pipe (44). Although not shown, the counterpressure line element side passage (40) in the oil supply passage (4) communicates with a main bearing and a mechanical seal interposed on the open side of the drive shaft (2).
前記油ポンプ（３）は、油室を構成する環状偏心溝（３
１）をもち、キー（３２）により駆動軸（２）に一体化
されるロータ（３３）と、バネ（３４）を介して前記偏
心溝（３１）に頭部を当接させるベーン（３５）とを備
えた定容積式のものであり、油溜（９３）から油吸入路
（３６）を介し、て−回転毎に定量づつ汲上げる油を油
吐出路（３７）から環状溝（３８）及び連通路（３９）
を経て給油通路（４）に導くようにしている。The oil pump (3) has an annular eccentric groove (3) constituting an oil chamber.
a rotor (33) that is integrated with the drive shaft (2) by a key (32); and a vane (35) whose head abuts against the eccentric groove (31) via a spring (34). The oil is pumped up in a fixed amount at each rotation from the oil sump (93) through the oil suction path (36), and the oil is pumped up from the oil discharge path (37) to the annular groove (38). and communication path (39)
It is designed to lead to the oil supply passageway (4) through the passageway.
以上の構成で、第１図及び第２図に明示するように、前
記駆動軸（２）の軸端部軸心上に、前記給油通路（４）
に連続する第１凹部（４５）と第２凹部（４６）とを段
付き杖に設けると共に、前記第１凹部（４５）のネジ（
４７）に螺合される取付部（５１）と、前記第２凹部（
４６）との間に環状隙間（４８）を空ける多角形外面を
もつ本体部（５２）とを備えたホルダー（５０）を設け
て、該ホルダー（５０）の内部軸心上に、後述する油量
調節弁（８）の弁孔（５３）及びバネ収容孔（５４）並
びに、前記駆動軸（２）が高速回転等されて給油通路（
４）内の油圧が高くなる高油圧時に対応した油量を軸端
部に開放する比較的小さな口径をもつ油注入主通路（５
）をそれぞれ開口する。更に、前記本体部（５２）の基
部外周部に、前記弁孔（５３）を環状隙間（４８）に連
通させる複数の連通穴（５５）を開口して、前記弁孔（
５３）とこの連通穴（５５）及び環状隙間（４８）とで
、前記油注入主通路（５）を迂回する補助通路（６）を
形成する。尚、（４９）は、スイングリンク（２４）の
底面側に油を受は渡すガイド筒である。With the above configuration, as clearly shown in FIGS. 1 and 2, the oil supply passage (4) is located on the axis of the shaft end of the drive shaft (2).
The stepped cane is provided with a first recess (45) and a second recess (46) that are continuous with each other, and the first recess (45) has a screw (
47), and a mounting portion (51) that is screwed into the second recess (
46) and a main body (52) having a polygonal outer surface with an annular gap (48) therebetween. The oil supply passage (
4) A main oil injection passage (5) with a relatively small diameter that releases the amount of oil corresponding to the high oil pressure in the shaft end.
) respectively. Furthermore, a plurality of communication holes (55) are opened in the outer periphery of the base of the main body (52) to communicate the valve hole (53) with the annular gap (48).
53), this communication hole (55), and the annular gap (48) form an auxiliary passage (6) that bypasses the oil injection main passage (5). Note that (49) is a guide cylinder that receives and passes oil to the bottom side of the swing link (24).
又、前記ホルダー（５０）内の弁孔（５３）に、−側を
前記給油通路（４）に臨ませ、他側にテーバ形の着座部
（８１）を形成して該着座部を前記バネ収容孔（５４）
の開口縁部に臨ませた油量調節弁（８）を摺動自由に介
装して、該調節弁（８）の内部軸心上に、前記給油通路
（４）に連続する連続穴（８２）と、前記駆動軸（２）
が低速回転等されて給油通路（４）内の油圧が低くなる
低油圧時に対応した油量を設定し、前記主通路（５）よ
りも口径を大きくした規制通路（８３）とを開口すると
共に、前記着座部（８１）の頂部に、前記バネ収容孔（
５４）に納めるコイルスプリングから成る弾性体（７）
を付与させる。こうして、低速回転される低油圧時、第
１図に示すように、弾性体（７）の付勢力が前記調節弁
（８）に付与される油圧力に勝り、着座部（８１）を離
間させて補助通路（６）を給油通路（４）に対し開き、
又、高速回転される高油圧時、第２図に示すように、前
記調節弁（８）に付与される油圧力が弾性体（７）の付
勢力に勝り、着座部（８１）を着座させて補助通路（６
）を給油通路（４）に対し遮断し、これにより低油圧時
の油開放口を高油圧時の油開放口に対し増大させる。前
記着座部（８１）の着座は、約４０Ｈｚ程度の回転数に
見合う油圧で行われるようにしている。Further, a valve hole (53) in the holder (50) is formed with a - side facing the oil supply passage (4) and a tapered seating part (81) on the other side, and the seating part is connected to the spring. Accommodation hole (54)
An oil flow control valve (8) facing the opening edge of the oil supply passageway (4) is slidably interposed therein, and a continuous hole ( 82) and the drive shaft (2)
The amount of oil corresponding to low oil pressure is set when the oil supply passage (4) is rotated at a low speed, etc. and the oil pressure in the oil supply passage (4) is low, and a regulation passage (83) having a larger diameter than the main passage (5) is opened. , the spring accommodation hole (
Elastic body (7) consisting of a coil spring housed in 54)
be granted. In this way, when the oil pressure is low due to low speed rotation, the biasing force of the elastic body (7) overcomes the hydraulic pressure applied to the control valve (8), as shown in FIG. 1, and the seating portion (81) is separated. to open the auxiliary passage (6) to the oil supply passage (4),
Furthermore, when the oil pressure is high during high-speed rotation, the hydraulic pressure applied to the control valve (8) overcomes the biasing force of the elastic body (7), causing the seating portion (81) to be seated, as shown in FIG. Auxiliary passage (6
) is shut off from the oil supply passage (4), thereby increasing the number of oil release ports during low oil pressure compared to the oil release port during high oil pressure. Seating of the seating portion (81) is performed using oil pressure corresponding to a rotational speed of about 40 Hz.
以上の構成により、２０〜４０Ｈｚの範囲Ｉ低速回転さ
れる低油圧時、第１図に示すように、軸端部には油注入
主通路（５）と補助通路（６）との２つの経路を介して
油が開放され、油圧力ご減少を補って必要油量を確保す
ることができる。With the above configuration, when the oil pressure is low and is rotated at a low speed in the range I of 20 to 40 Hz, as shown in FIG. Oil is released through the valve, making it possible to compensate for the decrease in hydraulic pressure and secure the required amount of oil.
しかも、このとき開放される油量は、低油圧時に対応し
た口径をもつ規制通路（８３）で規制される適正な値と
なるから、該低油圧時に適合した避退な給油が行える。Furthermore, since the amount of oil released at this time is an appropriate value regulated by the regulation passage (83) having a diameter corresponding to the low oil pressure, it is possible to carry out evacuation oil supply suitable for the low oil pressure.
一方、４０〜７０Ｈｚの範囲で高速回転される高油圧時
、第２図に示すように、軸端部には油注入主通路（５）
のみを介して油が開放され、開放油量を抑制して過剰給
油を防止することができる。しかも、このとき開放され
る油量は、前記主通路（５）を高油圧時に対応した口径
にしていることにより適正な値となるから、該高油圧時
に適合した最適な給油が行える。On the other hand, when the oil pressure is high and is rotated at high speed in the range of 40 to 70 Hz, as shown in Figure 2, the main oil injection passage (5) is installed at the end of the shaft.
The oil is released only through the valve, and the amount of released oil can be suppressed to prevent over-lubrication. Furthermore, the amount of oil released at this time becomes an appropriate value by making the main passage (5) have a diameter suitable for high oil pressure, so that optimal oil supply suitable for the high oil pressure can be performed.
その上、−本の給油通路（４）に対して、その軸端部の
開放口を低油圧時と高油圧時とで変更するだけの構成で
あるため、前記給油通路（４）自体を途中で分岐させた
り又は複数本構成とし、その内の一つの通路を開閉して
油量調節するものに比べ、構成を簡単にできるのである
。Moreover, since the opening of the shaft end of the - oil supply passage (4) is simply changed between low oil pressure and high oil pressure, the oil supply passage (4) itself is The structure can be simplified compared to a system in which the oil amount is adjusted by opening or closing one of the passages, which is divided into branches or has a plurality of passages.
又、前記油量調節弁（８）を駆動軸（２）の軸心上に配
置したから、該駆動軸（２）の回転バランスを狂わせる
ことがなく、カウンタウェイト（２１）やバランスウェ
イト（２６）等のバランス設計をやり直す煩わしさも排
除できるのである。In addition, since the oil amount control valve (8) is arranged on the axis of the drive shaft (2), the rotational balance of the drive shaft (2) is not disturbed, and the counterweight (21) and balance weight (26) ) etc., the trouble of having to redo the balance design can also be eliminated.
（発明の効果）
以Ｊ１本発明によれば、低油圧時、油注入主通路（５）
と補助通路（６）との２つの経路を介して駆動軸（２）
の軸端部に油を開放でき、油圧力の減少を補って必要油
量を確保でき、給油部の潤滑やシールを良好に行うこと
ができると共に、品油圧時、補助通路（６）を遮断して
油注入主通路（５）のみを介して油を開放でき、開放油
量を抑制して過剰給油を防止でき、油上がりの問題を回
避することができ、低油圧時及び高油圧時双方について
適正な給油が行えるのである。(Effect of the invention) According to the present invention, when the oil pressure is low, the oil injection main passage (5)
and the auxiliary passage (6) through the drive shaft (2).
The oil can be released to the end of the shaft, making up for the decrease in oil pressure and securing the required amount of oil, ensuring good lubrication and sealing of the oil supply part, and blocking the auxiliary passage (6) when the oil pressure is high. The oil can be released only through the oil injection main passage (5), and the amount of oil released can be suppressed to prevent excessive oil supply, and the problem of oil leakage can be avoided. This allows for proper refueling.
第１図は本発明に係る給油機構の低油圧時における要部
断面図、第２図は同高油圧時における要部断面図、第３
図は同全体構成を示す断面図、第４図は従来例の断面図
である。
（１）・・・・圧縮要素
（２）・・・・駆動軸
（３）・・・・油ポンプ
（４）・・・・給油通路
（５）・・・・油注入主通路
（６）・・・・補助通路
（８）・・・・油量調節弁FIG. 1 is a sectional view of the main parts of the oil supply mechanism according to the present invention when the oil pressure is low, FIG. 2 is a sectional view of the main parts when the oil pressure is high, and FIG.
The figure is a cross-sectional view showing the overall configuration, and FIG. 4 is a cross-sectional view of a conventional example. (1)...Compression element (2)...Drive shaft (3)...Oil pump (4)...Oil supply passage (5)...Oil injection main passage (6) ... Auxiliary passage (8) ... Oil flow control valve
Claims (1)
、油ポンプ（３）から延びる給油通路（４）を備え、前
記駆動軸（２）の軸端部から開放する油を給油部に供給
するようにした圧縮機の給油機構において、前記駆動軸
（２）の軸端部に、前記給油通路（４）に連通する油注
入主通路（５）と該主通路（５）を迂回する補助通路（
６）とを設けると共に、前記駆動軸（２）の軸端部に、
前記給油通路（４）内の油圧変化により変位され、低油
圧時、前記補助通路（６）を給油通路（４）に対し開き
、高油圧時、前記補助通路（６）を給油通路（４）に対
し遮断して、低油圧時の油開放口を高油圧時の油開放口
に対し増大させる油圧作動型の油量調節弁（８）を介装
したことを特徴とする圧縮機の給油機構。(1) An oil supply passage (4) extending from an oil pump (3) is provided inside the drive shaft (2) that drives the compression element (1), and oil is supplied from the shaft end of the drive shaft (2). In a compressor oil supply mechanism configured to supply oil to an oil supply section, an oil injection main passage (5) communicating with the oil supply passage (4) and an oil injection main passage (5) are provided at the shaft end of the drive shaft (2). Auxiliary passage to bypass (
6), and at the shaft end of the drive shaft (2),
Displaced by changes in oil pressure in the oil supply passage (4), when the oil pressure is low, the auxiliary passage (6) is opened to the oil supply passage (4), and when the oil pressure is high, the auxiliary passage (6) is opened to the oil supply passage (4). A compressor oil supply mechanism characterized by being equipped with a hydraulically operated oil flow control valve (8) that shuts off the oil pressure and increases the oil release port at low oil pressure compared to the oil release port at high oil pressure. .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2249734A JP2674292B2 (en) | 1990-09-18 | 1990-09-18 | Oil supply mechanism for compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2249734A JP2674292B2 (en) | 1990-09-18 | 1990-09-18 | Oil supply mechanism for compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04128585A true JPH04128585A (en) | 1992-04-30 |
| JP2674292B2 JP2674292B2 (en) | 1997-11-12 |
Family
ID=17197413
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2249734A Expired - Fee Related JP2674292B2 (en) | 1990-09-18 | 1990-09-18 | Oil supply mechanism for compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2674292B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2390874A (en) * | 2002-06-03 | 2004-01-21 | Kobe Steel Ltd | Oil cooled compressor restricts cooling oil flow depending on outlet pressure |
| EP1369590A3 (en) * | 2002-06-05 | 2004-04-28 | Sanyo Electric Co., Ltd. | Two-stage rotary type compressor |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5975589U (en) * | 1982-11-12 | 1984-05-22 | トキコ株式会社 | scroll compressor |
| JPS6210487A (en) * | 1985-07-05 | 1987-01-19 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| JPH01219383A (en) * | 1988-02-26 | 1989-09-01 | Matsushita Refrig Co Ltd | Compressor |
| JPH025787A (en) * | 1988-06-22 | 1990-01-10 | Mitsubishi Electric Corp | Scroll compressor |
| JPH0245686A (en) * | 1988-08-03 | 1990-02-15 | Daikin Ind Ltd | Horizontal open compressor |
-
1990
- 1990-09-18 JP JP2249734A patent/JP2674292B2/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5975589U (en) * | 1982-11-12 | 1984-05-22 | トキコ株式会社 | scroll compressor |
| JPS6210487A (en) * | 1985-07-05 | 1987-01-19 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| JPH01219383A (en) * | 1988-02-26 | 1989-09-01 | Matsushita Refrig Co Ltd | Compressor |
| JPH025787A (en) * | 1988-06-22 | 1990-01-10 | Mitsubishi Electric Corp | Scroll compressor |
| JPH0245686A (en) * | 1988-08-03 | 1990-02-15 | Daikin Ind Ltd | Horizontal open compressor |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2390874A (en) * | 2002-06-03 | 2004-01-21 | Kobe Steel Ltd | Oil cooled compressor restricts cooling oil flow depending on outlet pressure |
| GB2390874B (en) * | 2002-06-03 | 2004-06-02 | Kobe Steel Ltd | Oil-cooled compressor |
| US7094037B2 (en) | 2002-06-03 | 2006-08-22 | Kobe Steel, Ltd. | Oil-cooled compressor |
| EP1369590A3 (en) * | 2002-06-05 | 2004-04-28 | Sanyo Electric Co., Ltd. | Two-stage rotary type compressor |
| US7131821B2 (en) | 2002-06-05 | 2006-11-07 | Sanyo Electric Co., Ltd. | Internal intermediate pressure multistage compression type rotary compressor, manufacturing method thereof and displacement ratio setting method |
| CN100347452C (en) * | 2002-06-05 | 2007-11-07 | 三洋电机株式会社 | Rotary compressor and method for manufacturing same and removal volumetric proportions setting method |
| US7520733B2 (en) | 2002-06-05 | 2009-04-21 | Sanyo Electric Co., Ltd. | Multistage compression type rotary compressor |
| US7600986B2 (en) | 2002-06-05 | 2009-10-13 | Sanyo Electric Co., Ltd. | Filtering device for multistage compression type rotary compressor |
| US7798787B2 (en) | 2002-06-05 | 2010-09-21 | Sanyo Electric Co., Ltd. | Internal intermediate pressure multistage compression type rotary compressor, manufacturing method thereof and displacement ratio setting method |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2674292B2 (en) | 1997-11-12 |
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