JPH0368236B2 - - Google Patents
Info
- Publication number
- JPH0368236B2 JPH0368236B2 JP56177055A JP17705581A JPH0368236B2 JP H0368236 B2 JPH0368236 B2 JP H0368236B2 JP 56177055 A JP56177055 A JP 56177055A JP 17705581 A JP17705581 A JP 17705581A JP H0368236 B2 JPH0368236 B2 JP H0368236B2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- chamber
- oil
- oil supply
- supply passage
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 230000006835 compression Effects 0.000 claims description 8
- 238000007906 compression Methods 0.000 claims description 8
- 239000003921 oil Substances 0.000 description 64
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000004140 cleaning Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary-Type Compressors (AREA)
Description
【発明の詳細な説明】
本発明は、互に噛み合う一対のスクリユーロー
タをロータ室で回転せしめて気体を圧縮するスク
リユー圧縮機に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a screw compressor that compresses gas by rotating a pair of screw rotors that mesh with each other in a rotor chamber.
従来この種の冷凍機用スクリユー圧縮機におい
て、ロータ作用空間に潤滑・シール用に液体噴射
を行なう型式のものでは、雄雌ロータへの軸受へ
の給油は、吐出配管中の油分離器で分離した油を
油冷却器にて40〜50℃前後に冷却し、油ポンプを
使つて強制給油する方法が行われている。圧縮機
は冷媒ガスを圧縮するのに伴い、スクリユロータ
の吐出側端面には高い圧力が作用し吸入側端面に
は低い圧力が作用するのでロータにスラスト力が
働く、圧縮機は吸込側軸受室の軸の延長部に軸受
室仕切つた軸封装置を設けて、反軸受側の軸受室
に、軸受に給油する油を分岐供給して吸込側軸端
部を加圧したスラスト力バランス装置を設けて、
ロータに働くスラスト力を小さく軽減し残りの小
さなスラスト力をスラスト軸受にて受けている。
従つて吸込側軸受給油口とバランス装置部に油ポ
ンプから吐出された油圧がかつているので前記バ
ランス装置の軸封部が損傷した場合、高い圧力の
油が軸受側の軸受室に流入し、軸受前後の圧力差
が減少して軸受の供給不足が生ずる。本発明は、
上記欠点を解消し、圧縮機の軸受の信頼性を向上
することである。 Conventionally, in this type of screw compressor for refrigerators, in which liquid is injected into the rotor working space for lubrication and sealing, the oil supply to the male and female rotor bearings is separated by an oil separator in the discharge piping. The method used is to cool the oil in an oil cooler to around 40 to 50 degrees Celsius, and then use an oil pump to forcefully supply the oil. As the compressor compresses the refrigerant gas, high pressure acts on the discharge side end face of the screw rotor and low pressure acts on the suction side end face, so a thrust force acts on the rotor. A shaft sealing device that partitions the bearing chamber is installed on the extension of the shaft, and a thrust force balance device is installed in the bearing chamber on the opposite side of the shaft to supply oil to the bearing in a branched manner to pressurize the shaft end on the suction side. ,
The thrust force acting on the rotor is reduced to a small amount, and the remaining small thrust force is received by the thrust bearing.
Therefore, since the oil pressure discharged from the oil pump is present in the bearing oil supply port on the suction side and the balance device section, if the shaft seal of the balance device is damaged, high pressure oil will flow into the bearing chamber on the bearing side, and the bearing The pressure difference between front and rear decreases, resulting in a shortage of bearing supply. The present invention
It is an object of the present invention to eliminate the above-mentioned drawbacks and improve the reliability of compressor bearings.
本発明は吸込側の反軸受側軸受室への給油通路
の抵抗を吸入側軸受室の給油通路の抵抗より大き
くしたことにより次の如き顕著な効果を有する実
用浄上極めて大なる効果を有するものである。即
ちバランス装置の給油通路に絞りオリフイスを設
けてバランス装置の軸封部の洩れ量が一定値以上
の時でも前記バランス装置の給油通路の抵抗を軸
受に必要最小油量を給油するのに必要な軸受前後
の差圧が生ずるように軸受室の給油通路の抵抗よ
り大きくしたので前記バランス装置の軸封部が損
傷した場合でも軸受前後に必要な差圧が確保され
て軸受に最小油量が確保されて圧縮機の軸受の信
頼性が向上されるものである。 The present invention has the following remarkable effects by making the resistance of the oil supply passage to the bearing chamber on the side opposite to the bearing on the suction side greater than the resistance of the oil supply passage in the bearing chamber on the suction side, which has extremely great effects in terms of practical cleaning. It is. That is, by providing a throttle orifice in the oil supply passage of the balance device, even when the amount of leakage from the shaft seal of the balance device exceeds a certain value, the resistance of the oil supply passage of the balance device is reduced to the level necessary to supply the minimum amount of oil to the bearing. In order to create a differential pressure across the bearing, the resistance is greater than the oil supply passage in the bearing chamber, so even if the shaft seal of the balance device is damaged, the necessary differential pressure is maintained across the bearing, ensuring the minimum amount of oil in the bearing. This improves the reliability of the compressor bearing.
図について説明すれば第１図はスクリユー圧縮
機の側断面図、第２図は第１図のＺ−Ｚ線に沿う
断面図であつて、ケーシング１内のボア１′，
１″にオスロータ４、メスロータ５が設置され、
ガスは吸入口２から圧縮室を経て吐出口３から吐
出される。７はスラスト軸受、８はジヤーナル軸
受を示している。６′はスライドバルブ６から噴
射される油の導入口である。９は駆動軸、９′は
吸入側軸頚を示している。 To explain the figures, FIG. 1 is a side sectional view of the screw compressor, and FIG. 2 is a sectional view taken along the Z-Z line in FIG.
Male rotor 4 and female rotor 5 are installed at 1″,
Gas is discharged from the suction port 2 through the compression chamber and from the discharge port 3. 7 indicates a thrust bearing, and 8 indicates a journal bearing. 6' is an inlet for oil injected from the slide valve 6. 9 is a drive shaft, and 9' is a suction side shaft neck.
第３図は本発明のスクリユー圧縮機の潤滑系統
の説明図、第４図は吸入側の軸受室の拡大図であ
る。潤滑油は矢印ｌで示す如く油ポンプから送ら
れて来て、導入口１１から給油通路１２に入り、
分岐されている給油路１３から吐出側のジヤーナ
ル軸受８に入りついで給油路１６を通つて別のジ
ヤーナル軸受８に入る。油は夫々ジヤーナル軸受
８からスラスト軸受７にゆき軸受室１７に入り、
そこから排油路１８から排出される。又油は図の
右方の給油路１２′から駆動軸９の軸封部９″にゆ
き排油路１９から排出される。 FIG. 3 is an explanatory diagram of the lubrication system of the screw compressor of the present invention, and FIG. 4 is an enlarged view of the bearing chamber on the suction side. Lubricating oil is sent from the oil pump as shown by arrow l, enters the oil supply passage 12 from the inlet 11,
The oil enters the discharge-side journal bearing 8 from the branched oil supply path 13 and then enters another journal bearing 8 through the oil supply path 16. The oil goes from the journal bearing 8 to the thrust bearing 7 and enters the bearing chamber 17, respectively.
From there, the oil is discharged from the drain passage 18. Further, oil passes from the oil supply passage 12' on the right side of the figure to the shaft seal portion 9'' of the drive shaft 9, and is discharged from the oil discharge passage 19.
油は又吸入側の分岐された給油路１４によつ
て、吸入側のジヤーナル軸受８にゆき、給油路２
６を経て他のジヤーナル軸受８に入る。油は第４
図の矢印ａに示す如く、軸受８から軸受側の軸受
室２０に入り、排油路２２を経て圧縮室１０の吸
入口にとじ込み後に開口する開口４０から圧縮室
に導かれる。他の軸受８から軸受室２０に入つた
油は排油路２７に入り、前記の排油路１９中を軸
封部から戻つてくる油と合同油通路２８によつて
とじ込み後の開口４１から圧縮室１０に導入され
る。 The oil also goes to the journal bearing 8 on the suction side via the branched oil supply path 14 on the suction side, and then to the oil supply path 2.
6 and then enters another journal bearing 8. Oil is the fourth
As shown by the arrow a in the figure, the oil enters the bearing chamber 20 on the bearing side from the bearing 8, passes through the oil drain path 22, and is led to the compression chamber through the opening 40 that opens after being locked in the suction port of the compression chamber 10. The oil that has entered the bearing chamber 20 from the other bearing 8 enters the oil drain path 27, and is contained in the oil drain path 19 through the joint oil path 28 with the oil that returns from the shaft sealing portion, and then exits from the opening 41 after being sealed. It is introduced into the compression chamber 10.
更に油は給油路１５から、軸頚９′に設けられ
ているフローテイングシールリング２４の外側の
（即ちシールリング２４を介して軸受側軸受室と
は反対側の）反軸受側軸受室２１に導かれ、前記
の如くバランス作用を行なう。フローテイングシ
ールリング２４はシールリング受２４′と組み合
され、シールリング抑え２３によつて支持されて
いる。 Further, the oil is transferred from the oil supply path 15 to the non-bearing side bearing chamber 21 outside the floating seal ring 24 provided on the shaft neck 9' (that is, on the opposite side of the bearing side bearing chamber via the seal ring 24). guided and performs a balancing action as described above. The floating seal ring 24 is assembled with a seal ring receiver 24' and supported by a seal ring retainer 23.
圧縮室１０内においてはスクリユロータの吐出
側端面には高い圧力がかかり、吸入側端面には低
い圧力がかかるので、ロータは吸入側に押される
のを、この反軸受側軸受室２１内の油圧で右方に
押しかえし、その差の小さなスラスト力をスラス
ト軸受７で受けている。 In the compression chamber 10, high pressure is applied to the discharge side end face of the screw rotor, and low pressure is applied to the suction side end face, so the rotor is pushed toward the suction side by the hydraulic pressure in the bearing chamber 21 on the opposite bearing side. It is pushed back to the right, and the thrust bearing 7 receives the small difference in thrust force.
このフローテイングシールリング２４と軸頚
９′との間の軸封部に損傷が生じた場合、反軸受
側軸受室２１から油はフローテイングシールリン
グ２４と軸頚９′の間の隙間ｃから軸受側軸受室
２０に矢印ｂで示す如く流入し、軸受８の前後の
圧力差が減少し軸受８への給油不足が生じ軸受８
が損傷してしまう惧がある。 If the shaft seal between the floating seal ring 24 and the shaft neck 9' is damaged, the oil will flow from the bearing chamber 21 on the opposite bearing side from the gap c between the floating seal ring 24 and the shaft neck 9'. The oil flows into the bearing chamber 20 on the bearing side as shown by arrow b, and the pressure difference between the front and rear of the bearing 8 decreases, resulting in insufficient oil supply to the bearing 8.
There is a risk that it may be damaged.
そこで本発明は給油路１５に、その室２１への
開口部に、充分径を絞つた絞りオリフイス２５を
設け、給油路１５の抵抗を給油路１４の抵抗より
充分大きくしたものである。そのため反軸受側軸
受室２１に流入する油圧が、それだけ低くなつて
いるので、仮令軸封部に損傷があつて室２１から
油が室２０に流入しても室２０の圧力はそれほど
上がらず、軸受８に必要最小油量を給油するのに
必要な軸受前後の差圧が確保されて、軸受８に給
油不足が生ずることはない。 Therefore, in the present invention, the oil supply passage 15 is provided with a throttle orifice 25 having a sufficiently narrowed diameter at its opening to the chamber 21, so that the resistance of the oil supply passage 15 is made sufficiently larger than the resistance of the oil supply passage 14. Therefore, the oil pressure flowing into the bearing chamber 21 on the opposite bearing side is lowered accordingly, so even if the temporary shaft seal is damaged and oil flows into the chamber 20 from the chamber 21, the pressure in the chamber 20 will not rise that much. The differential pressure required before and after the bearing to supply the minimum required amount of oil to the bearing 8 is ensured, and the bearing 8 will never be under-lubricated.
尚数値の一例を示せば、今ロータの直径170mm、
軸２７の直径50mm、圧縮機の吐出圧力14Kg／cm2、
油ポンプの圧力17Kg／cm2の場合に室２１への圧力
は16.7Kg／cm2位となる。このように圧縮機の寸
法、運転条件によつて最適な抵抗値を選ぶように
する。 To give an example of numerical values, the current rotor diameter is 170 mm,
The diameter of the shaft 27 is 50 mm, the discharge pressure of the compressor is 14 Kg/cm 2 ,
When the pressure of the oil pump is 17 kg/cm 2 , the pressure to the chamber 21 is about 16.7 kg/cm 2 . In this way, the optimum resistance value should be selected depending on the compressor dimensions and operating conditions.
第５図はバランス装置の別な実施態様を示すも
ので、軸頚９′にバランスピストン３０が固定さ
れ、その外周にバランスデイスク３１がケーシン
グ１に固定されている。バランスピストンとバラ
ンスデイスクとの間の隙間ｃが軸封部となつてい
る。軸封部が損傷すれば矢印ｂに示す如く、油が
軸受側の軸受室２０に流入する。第５図において
も第３図、第４図と同じ符号は同じ部品を示し、
その作用は全く同様である。 FIG. 5 shows another embodiment of the balance device, in which a balance piston 30 is fixed to the shaft neck 9', and a balance disk 31 is fixed to the casing 1 on the outer periphery of the balance piston 30. The gap c between the balance piston and the balance disk serves as a shaft seal. If the shaft seal is damaged, oil will flow into the bearing chamber 20 on the bearing side, as shown by arrow b. In Fig. 5, the same symbols as in Figs. 3 and 4 indicate the same parts.
The effect is exactly the same.
この発明はこのように反軸受側軸受室への給油
路の抵抗を軸受側軸受室への給油路の抵抗より大
きくしてあるので、バランス装置の軸封部が損傷
しても軸受の前後に一定の圧力差が確保されて軸
受への給油量が確保されるものである。 In this invention, the resistance of the oil supply path to the bearing chamber on the opposite bearing side is made greater than the resistance of the oil supply path to the bearing chamber on the bearing side, so even if the shaft seal of the balance device is damaged, the resistance of the oil supply path to the bearing chamber on the opposite side of the bearing can be prevented. This ensures a constant pressure difference and the amount of oil supplied to the bearing.
第１図はスクリユー圧縮機の側断面図、第２図
は第１図のＺ−Ｚ線に沿う断面図、第３図は潤滑
系統の説明図、第４図はバランス装置部分の拡大
図、第５図はバランス装置の別実施例の図であ
る。
符号の説明 １…ケーシング、２…吸込口、３
…吐出口、４…オスロータ、５…メロータ、６…
スライドバルブ、７…スラスト軸受、８…ジヤー
ナル軸受、９…駆動軸、１０…圧縮室、１１…油
導入口、１２…給油通路、１３，１４，１５…給
油路、１６…油通路、１７…吐出側軸受室、１
８，１９…排油路、２０…軸受側軸受室、２１…
反軸受側軸受室、２２…排油路、２３…シールリ
ング抑え、２４…フローテイングシールリング、
２５…オリフイス、２６…油通路、２７…排油
路、２８…合同油通路、３０…バランスピスト
ン、３１…バランスデイスク。
Figure 1 is a side sectional view of the screw compressor, Figure 2 is a sectional view taken along the Z-Z line in Figure 1, Figure 3 is an explanatory diagram of the lubrication system, Figure 4 is an enlarged view of the balance device, FIG. 5 is a diagram of another embodiment of the balancing device. Explanation of symbols 1...Casing, 2...Suction port, 3
...Discharge port, 4...Male rotor, 5...Merota, 6...
Slide valve, 7... Thrust bearing, 8... Journal bearing, 9... Drive shaft, 10... Compression chamber, 11... Oil inlet, 12... Oil supply passage, 13, 14, 15... Oil supply passage, 16... Oil passage, 17... Discharge side bearing chamber, 1
8, 19...Drainage path, 20...Bearing side bearing chamber, 21...
Counter-bearing side bearing chamber, 22...Drainage path, 23...Seal ring suppressor, 24...Floating seal ring,
25... Orifice, 26... Oil passage, 27... Oil drain passage, 28... Joint oil passage, 30... Balance piston, 31... Balance disc.
Claims (1)
直径よりも小なる如く互に重なり合つて設けられ
た二個の円筒状ボアの中に、それぞれ前記ボア軸
を中心に回転可能に支えられて互に噛み合う雄ロ
ータと雌ロータとを備え、前記ケーシングには、
前記ボアの両端に前記ボア軸に直角な吸込側端壁
及び吐出側端壁を備え、該吸込側端壁及び吐出側
端壁にはそれぞれ端壁吸込口及び端壁吐出口、さ
らに前記雄、雌ロータを支承する軸受として、吸
込側にジヤーナル軸受を、さらに吐出側にジヤー
ナル軸受とスラスト軸受を設け、ジヤーナル軸受
には軸受給油口を開口し、それぞれ給油通路と接
続し、又前記軸受からの軸端側延長部には軸受室
を形成し、さらに吸込側の軸受室にはスラスト力
バランス用のフローテイングシールリング２４又
はバランスピストン３０を設け、吸込側の軸受室
はフローテイングシールリングをはさんで、ジヤ
ーナル軸受８の側の室２０と、その反対側の室２
１とに分かれ、吸込側のジヤーナル軸受８には給
油通路１４が、又前記の軸受と反対側の室２１に
は給油通路１５が夫々接続され、前記の軸受側の
室２０は吸込口とじ込み後の圧縮室に開口する開
口４０に接続され、又前記の給油通路１４から吸
込側のジヤーナル軸受８に給油された油は、軸受
を潤滑冷却し、軸の外周部を通つて軸受側の室２
０に流入し、前記の如く開口４０によつて吸込口
とじ込み後の圧縮室に戻され、又前記の給油通路
１５より軸受の反対側の室２１に給油された油は
前記のフローテイングシールリング２４又はバラ
ンスピストン３０より漏洩して軸受側の室２０に
入りジヤーナル軸受８よりの油とともに前述の如
く圧縮室に戻るようなスクリユー圧縮機におい
て、前記の吸込側の軸受と反対側の室２１への給
油通路１５の室２１への開口部に、絞りオリフイ
ス２５を設けることによつて、給油通路１５の抵
抗をジヤーナル軸受８への給油通路１４より大き
くしたことを特徴とするスクリユー圧縮機。1 Supported rotatably about the bore axis in two cylindrical bores provided in parallel in the casing and overlapping each other such that the distance between the axes is smaller than the diameter thereof. The casing includes a male rotor and a female rotor that mesh with each other, and the casing includes:
Both ends of the bore are provided with a suction side end wall and a discharge side end wall that are perpendicular to the bore axis, and the suction side end wall and the discharge side end wall each include an end wall suction port and an end wall discharge port, and the male As bearings that support the female rotor, a journal bearing is provided on the suction side, and a journal bearing and a thrust bearing are provided on the discharge side.A bearing oil supply port is opened in the journal bearing, and each is connected to an oil supply passage. A bearing chamber is formed in the extension on the shaft end side, and a floating seal ring 24 or balance piston 30 for thrust force balance is provided in the bearing chamber on the suction side, and the floating seal ring is provided in the bearing chamber on the suction side. The chamber 20 on the side of the journal bearing 8 and the chamber 2 on the opposite side.
A oil supply passage 14 is connected to the journal bearing 8 on the suction side, and an oil supply passage 15 is connected to the chamber 21 on the opposite side of the bearing, and the chamber 20 on the bearing side is connected to the suction side after the suction port is closed. The oil supplied to the journal bearing 8 on the suction side from the oil supply passage 14 lubricates and cools the bearing, and passes through the outer circumference of the shaft to the chamber 2 on the bearing side.
The oil flowing into the chamber 21 on the opposite side of the bearing from the oil supply passage 15 is returned to the compression chamber after the suction port is closed through the opening 40 as described above, and the oil is supplied to the chamber 21 on the opposite side of the bearing from the oil supply passage 15. 24 or in a screw compressor where oil leaks from the balance piston 30 and enters the chamber 20 on the bearing side and returns to the compression chamber together with the oil from the journal bearing 8 as described above, to the chamber 21 on the opposite side from the bearing on the suction side. A screw compressor characterized in that the resistance of the oil supply passage 15 is made greater than that of the oil supply passage 14 to the journal bearing 8 by providing a throttle orifice 25 at the opening of the oil supply passage 15 to the chamber 21.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17705581A JPS5879685A (en) | 1981-11-06 | 1981-11-06 | Screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17705581A JPS5879685A (en) | 1981-11-06 | 1981-11-06 | Screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5879685A JPS5879685A (en) | 1983-05-13 |
| JPH0368236B2 true JPH0368236B2 (en) | 1991-10-25 |
Family
ID=16024337
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17705581A Granted JPS5879685A (en) | 1981-11-06 | 1981-11-06 | Screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5879685A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60249693A (en) * | 1984-05-25 | 1985-12-10 | Ebara Corp | Screw compressor |
| KR100421287B1 (en) * | 2001-10-27 | 2004-03-09 | 엘지전선 주식회사 | An equipped restrictor at supplied oil line of screw compressor |
| CN110905817A (en) * | 2019-11-25 | 2020-03-24 | 珠海格力电器股份有限公司 | Compressor with high lubrication reliability |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6332950Y2 (en) * | 1981-06-05 | 1988-09-02 |
-
1981
- 1981-11-06 JP JP17705581A patent/JPS5879685A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5879685A (en) | 1983-05-13 |
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