EP0758054A1 - Système de circulation d'huile pour un compresseur à vis - Google Patents
Système de circulation d'huile pour un compresseur à vis Download PDFInfo
- Publication number
- EP0758054A1 EP0758054A1 EP95810503A EP95810503A EP0758054A1 EP 0758054 A1 EP0758054 A1 EP 0758054A1 EP 95810503 A EP95810503 A EP 95810503A EP 95810503 A EP95810503 A EP 95810503A EP 0758054 A1 EP0758054 A1 EP 0758054A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- screw compressor
- oil
- lubrication
- connection
- pressure
- 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
- 238000005461 lubrication Methods 0.000 claims abstract description 30
- 230000006835 compression Effects 0.000 claims abstract description 11
- 238000007906 compression Methods 0.000 claims abstract description 11
- 239000003921 oil Substances 0.000 claims description 97
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 claims description 34
- 238000001704 evaporation Methods 0.000 claims description 24
- 230000008020 evaporation Effects 0.000 claims description 24
- 229910021529 ammonia Inorganic materials 0.000 claims description 6
- 239000003507 refrigerant Substances 0.000 claims description 6
- 229920001515 polyalkylene glycol Polymers 0.000 claims description 5
- 238000010438 heat treatment Methods 0.000 claims description 4
- 229910000069 nitrogen hydride Inorganic materials 0.000 description 11
- 238000005057 refrigeration Methods 0.000 description 8
- 239000006260 foam Substances 0.000 description 4
- 230000001050 lubricating effect Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000002480 mineral oil Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000007872 degassing Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000004090 dissolution Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 238000010943 off-gassing Methods 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
Images
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
- F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
-
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S418/00—Rotary expansible chamber devices
- Y10S418/01—Non-working fluid separation
Definitions
- the invention relates to a screw compressor device for refrigerants with refrigerant-soluble oils, preferably for ammonia with polyalkylene glycol soluble therein, a feed stream downstream of a screw compressor being divided into a gas stream and an oil stream in an oil separator under outlet pressure, and the oil stream via a throttle point and an oil inlet gets into the screw compressor.
- a relatively large amount of oil is injected into the gas flow to be pumped in the compression chamber in order to achieve a better seal and thereby an improvement in the degree of delivery and to dissipate part of the heat of compression with the oil.
- This oil must be separated from the gas flow on the pressure side of the compressor by an oil separator, because otherwise it would undesirably burden the refrigeration cycle.
- a gas stream 30 interspersed with oil particles is conveyed via a pressure line 2 to an oil separator 3. From there, the deoiled gas stream 3l is led to a condenser in the sense of the refrigeration cycle.
- the oil separated in the oil separator 3 passes via a line 4 to a water- or air-cooled oil cooler 5, in which the heat of compression is removed. From there, the oil is fed back to the compressor 1 via a line 6, an oil filter 7, a check valve 8, a solenoid valve 9 and an oil inlet 10, the pressure difference between the pressure and suction sides on the compressor being generally used for the oil delivery.
- a part of this returned oil is used for the lubrication of the bearings and for so-called "open" compressors, in which the drive shaft is led outwards, for the lubrication and cooling of the shaft seal.
- the rotating shaft seal is used to seal the compressor drive shaft against the atmosphere.
- the NH3-soluble oils accumulate due to the dissolution behavior according to the pressure and temperature conditions given in the oil separator with a certain amount of NH3, at a normal operating point, for example with approx. 6% NH3 in the oil.
- a normal operating point for example with approx. 6% NH3 in the oil.
- the NH3 absorption capacity of the oil decreases, for example to about 3% NH3 in the oil at a normal operating point, so that the difference of approximately 3% NH3 inevitably evaporates from the oil. Due to the very large steam volume of NH3, this evaporation process creates a large volume of oil foam (at a normal operating point approx.
- FIG. 2 shows a known device for refrigerant-soluble oils on screw compressors, which relaxes the oil provided for lubrication and sealing via a throttle point 25 and passes through an evaporation tank 21, the steam chamber of which is connected via a line 12 to the suction side 29 of the screw compressor 1.
- the oil is "degassed" and can be supplied to the shaft seal and the drive-side bearing with a better lubricating effect, the necessary pressure difference being generated by an oil pump 13.
- This arrangement has the disadvantage that the screw compressor depends on the functionality of an oil pump during its operation. Another disadvantage is that with the start of such a screw compressor device, the oil foams up behind the throttle point 25 and reaches the lubrication points in part as foam.
- the object of the invention is to improve these circumstances.
- This object is achieved in that a partial oil flow for the lubrication of bearings and / or shaft seals is branched off in front of the throttle point, which is led through an evaporation tank which is connected on the gas side via a line to an intermediate pressure connection on the compression path of the screw compressor to supply the partial oil flow with a pressure corresponding to the intermediate pressure to a lubrication connection on the screw compressor.
- This arrangement has the advantage that the lubrication pressure does not collapse in the event of a power failure during the run-down of the screw compressor, since the pressure difference between final pressure and intermediate pressure slowly, if at all, then slowly decreases after the screw compressor has come to a standstill. Furthermore, no oil pump is necessary. In addition, the steam discharged from the lubricating oil is fed in at intermediate pressure, so that it does not have to be compressed from suction pressure to intermediate pressure, thus improving the cooling capacity of the cycle.
- the figures show an improvement in the lubrication of bearings and shaft seals on screw compressors for refrigerants with refrigerant-soluble oils.
- a typical application arises, for example, for ammonia with polyalkylene glycol soluble therein.
- a partial oil flow at an intermediate pressure is removed and passed through an evaporation tank, substantial portions of dissolved refrigerant can be fed in at an intermediate pressure connection on the compression path of the screw compressor.
- the lubricating properties of the remaining partial oil flow at the lubrication connection are correspondingly more favorable, and the disadvantages of pressure collapse or foam delivery are eliminated with an oil pump, since no oil pump is necessary with the appropriate intermediate pressure.
- a screw compressor 1 conveys ammonia in gaseous form from a suction line 29 and compresses it, polyalkylene glycol being injected at an oil inlet 10 in order to improve the sealing effect between the compression chambers.
- a throttle point 25 is symbolically shown for the resistance of the nozzles or orifices during injection.
- the flow 30 emerging from the screw compressor 1 against a final pressure is fed via a pressure line to an oil separator 3, which has a gas space 3a, from which a gas flow 31 is fed to a condenser (not shown), while there is an oil supply 3b at the bottom of the oil separator 3 which an oil flow 32 is passed through a line 4 through an oil cooler 5.
- the cooled oil flow 32 arrives in a line 6 via an oil filter 7, a check valve 8 and a solenoid valve 9 to the throttle point 25 and the oil inlet 10.
- a partial oil flow 35 is branched off in a branch 11 for the lubrication of bearings and shaft seals and led into an evaporation tank, which is under the pressure of an intermediate pressure connection 14 on the compression path of the screw compressor 1.
- the pressure at the inlet into the branch 11 must therefore be somewhat higher than the pressure in the Intermediate pressure port 14 to restrict the partial oil flow 35 with an orifice 26.
- ammonia is outgassed by the dwell time in the tank and by vacuum zones at the edges of the orifice 26, which ammonia is fed in via a line 23 at the intermediate pressure connection 14.
- the outgassing can be supported by a heating device 19, as shown in FIGS. 4 and 5.
- the degassed partial oil flow passes through a line 15 and a solenoid valve 17 to a lubrication connection 16 and after passing through bearings and shaft seals in a suction chamber 29 at the compressor inlet back into the gas flow.
- a so-called economizer connection on the screw compressor 1 is used as the intermediate pressure connection.
- the evaporation tank 24 is arranged above the screw compressor 1 and the solenoid valve 17 is closed at a standstill in order to have a supply of oil under gravity at the start.
- FIG. 5 only the circuit of the partial oil flow 35 has been expanded by further components compared to FIG. 3.
- a solenoid valve 18 is provided, which prevents oil from flowing back from the higher areas when it is at a standstill, and the partial oil flow 35 is limited by a control valve 20 which, for example, keeps the oil level in the evaporation tank 24 constant.
- a heating device 19 promotes the degassing of refrigerant.
- the line 15 bifurcates into a line 15a, in which an oil pump 22 with a check valve 27 is installed as a starting aid, and into a line 15b with a check valve 28, in order to convey past the shutdown oil pump 22 into the lubrication connection 16 .
- Such a booster pump 22 could always run when the intermediate pressure is insufficient for lubrication.
- the control valve 20 would track the partial oil flow 35 according to the pumping capacity of the pump 22.
- FIG. 4 shows, compared to FIGS. 3 and 5, an arrangement in which the branch 11 for the partial oil flow 35 goes away in front of the oil cooler 5.
- the partial oil flow reaches the evaporation tank 24 much hotter via a solenoid valve 18 and a control valve 20.
- a heating device 19 attached to the evaporation tank 24 will therefore only be necessary in exceptional cases.
- the oil also reaches the lubrication connection 16 via a line 15 and a solenoid valve 17, the solenoid valve 17 holding the oil supply in the higher-level evaporation tank 21 at a standstill.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP95810503A EP0758054B1 (fr) | 1995-08-09 | 1995-08-09 | Système de circulation d'huile pour un compresseur à vis |
DE59509083T DE59509083D1 (de) | 1995-08-09 | 1995-08-09 | Schmiersystem für Schraubenverdichtern |
US08/692,684 US5765392A (en) | 1995-08-09 | 1996-08-06 | Screw compressor apparatus for refrigerants with oils soluble in refrigerants |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP95810503A EP0758054B1 (fr) | 1995-08-09 | 1995-08-09 | Système de circulation d'huile pour un compresseur à vis |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0758054A1 true EP0758054A1 (fr) | 1997-02-12 |
EP0758054B1 EP0758054B1 (fr) | 2001-03-07 |
Family
ID=8221782
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP95810503A Expired - Lifetime EP0758054B1 (fr) | 1995-08-09 | 1995-08-09 | Système de circulation d'huile pour un compresseur à vis |
Country Status (3)
Country | Link |
---|---|
US (1) | US5765392A (fr) |
EP (1) | EP0758054B1 (fr) |
DE (1) | DE59509083D1 (fr) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101858349B (zh) * | 2009-04-08 | 2012-06-13 | 同方人工环境有限公司 | 一种螺杆式制冷压缩机满液式机组的供油回路 |
WO2015094465A1 (fr) * | 2013-12-18 | 2015-06-25 | Carrier Corporation | Procédé d'amélioration de la fiabilité de paliers de compresseur |
WO2015094464A1 (fr) * | 2013-12-18 | 2015-06-25 | Carrier Corporation | Dispositif de renforcement de la viscosité de lubrifiant d'un compresseur à fluide frigorigène |
Families Citing this family (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3637786B2 (ja) | 1998-09-17 | 2005-04-13 | 株式会社日立製作所 | ブライン冷却装置 |
US6688857B1 (en) * | 1998-10-28 | 2004-02-10 | Ewan Choroszylow | Compressor and dehydrator system |
US6116046A (en) * | 1999-03-05 | 2000-09-12 | American Standard Inc. | Refrigeration chiller with assured start-up lubricant supply |
NL1013332C2 (nl) * | 1999-10-18 | 2001-04-19 | Grasso Products B V | Asafdichting voor een pomp of compressor, in het bijzonder voor gebruik in compressoren voor koelinrichtingen. |
JP3985023B2 (ja) | 2001-03-19 | 2007-10-03 | 彰三 勝倉 | ポンプ装置 |
US6767524B2 (en) * | 2001-11-15 | 2004-07-27 | Bernard Zimmern | Process to produce nearly oil free compressed ammonia and system to implement it |
US6674046B2 (en) * | 2002-02-11 | 2004-01-06 | Illinois Tool Works Inc. | Screw air compressor for a welder |
US7011183B2 (en) * | 2002-03-14 | 2006-03-14 | Vilter Manufacturing Llc | Suction oil injection for rotary compressor |
US7165949B2 (en) * | 2004-06-03 | 2007-01-23 | Hamilton Sundstrand Corporation | Cavitation noise reduction system for a rotary screw vacuum pump |
CN102356240B (zh) * | 2009-03-16 | 2015-03-11 | 大金工业株式会社 | 螺杆式压缩机 |
EP2920469A2 (fr) | 2012-09-27 | 2015-09-23 | Vilter Manufacturing Llc | Appareil et procédé pour améliorer le rendement de compresseur |
DE102014101113A1 (de) * | 2014-01-30 | 2015-07-30 | Pfeiffer Vacuum Gmbh | Vakuumpumpe |
JP6686144B2 (ja) * | 2015-12-11 | 2020-04-22 | アトラス コプコ エアーパワー, ナームローゼ フェンノートシャップATLAS COPCO AIRPOWER, naamloze vennootschap | 圧縮機の液体噴射を調整する方法、液体噴射式圧縮機及び液体噴射式圧縮機要素 |
JP2018003720A (ja) * | 2016-07-04 | 2018-01-11 | 株式会社日立産機システム | 圧縮機 |
CA3016521A1 (fr) * | 2017-09-06 | 2019-03-06 | Joy Global Surface Mining Inc | Systeme de lubrification destine a un compresseur |
WO2020002961A1 (fr) | 2018-06-26 | 2020-01-02 | Carrier Corporation | Procédé amélioré de lubrification pour compresseurs de réfrigération |
WO2021106145A1 (fr) * | 2019-11-28 | 2021-06-03 | 株式会社前川製作所 | Système d'alimentation en huile pour compresseur |
AU2021202410A1 (en) | 2020-04-21 | 2021-11-11 | Joy Global Surface Mining Inc | Lubrication system for a compressor |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2801408A1 (de) * | 1978-01-13 | 1979-07-19 | Linde Ag | Verfahren und vorrichtung zum kuehlen eines in einem kaeltekreislauf angeordneten verdichters der drehkolbenbauart |
EP0030275A1 (fr) * | 1979-12-05 | 1981-06-17 | Karl Prof. Dr.-Ing. Bammert | Compresseur, en particulier compresseur à vis avec circuit de lubrification |
EP0030619A1 (fr) * | 1979-12-05 | 1981-06-24 | Karl Prof. Dr.-Ing. Bammert | Compresseur à rotor, en particulier compresseur à vis avec alimentation en lubrifiant et drainage du lubrifiant des paliers |
WO1983003641A1 (fr) * | 1982-04-13 | 1983-10-27 | Glanvall, Rune | Compresseur du type hermetique |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SU1079968A1 (ru) * | 1980-04-23 | 1984-03-15 | Всесоюзный Научно-Исследовательский Институт Холодильной Промышленности | Холодильна машина |
US4497185A (en) * | 1983-09-26 | 1985-02-05 | Dunham-Bush, Inc. | Oil atomizing compressor working fluid cooling system for gas/vapor/helical screw rotary compressors |
-
1995
- 1995-08-09 DE DE59509083T patent/DE59509083D1/de not_active Expired - Fee Related
- 1995-08-09 EP EP95810503A patent/EP0758054B1/fr not_active Expired - Lifetime
-
1996
- 1996-08-06 US US08/692,684 patent/US5765392A/en not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2801408A1 (de) * | 1978-01-13 | 1979-07-19 | Linde Ag | Verfahren und vorrichtung zum kuehlen eines in einem kaeltekreislauf angeordneten verdichters der drehkolbenbauart |
EP0030275A1 (fr) * | 1979-12-05 | 1981-06-17 | Karl Prof. Dr.-Ing. Bammert | Compresseur, en particulier compresseur à vis avec circuit de lubrification |
EP0030619A1 (fr) * | 1979-12-05 | 1981-06-24 | Karl Prof. Dr.-Ing. Bammert | Compresseur à rotor, en particulier compresseur à vis avec alimentation en lubrifiant et drainage du lubrifiant des paliers |
WO1983003641A1 (fr) * | 1982-04-13 | 1983-10-27 | Glanvall, Rune | Compresseur du type hermetique |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101858349B (zh) * | 2009-04-08 | 2012-06-13 | 同方人工环境有限公司 | 一种螺杆式制冷压缩机满液式机组的供油回路 |
WO2015094465A1 (fr) * | 2013-12-18 | 2015-06-25 | Carrier Corporation | Procédé d'amélioration de la fiabilité de paliers de compresseur |
WO2015094464A1 (fr) * | 2013-12-18 | 2015-06-25 | Carrier Corporation | Dispositif de renforcement de la viscosité de lubrifiant d'un compresseur à fluide frigorigène |
US10288069B2 (en) | 2013-12-18 | 2019-05-14 | Carrier Corporation | Refrigerant compressor lubricant viscosity enhancement |
US10487833B2 (en) | 2013-12-18 | 2019-11-26 | Carrier Corporation | Method of improving compressor bearing reliability |
Also Published As
Publication number | Publication date |
---|---|
EP0758054B1 (fr) | 2001-03-07 |
US5765392A (en) | 1998-06-16 |
DE59509083D1 (de) | 2001-04-12 |
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