EP0758054A1 - Système de circulation d'huile pour un compresseur à vis - Google Patents

Système de circulation d'huile pour un compresseur à vis Download PDF

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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
Application number
EP95810503A
Other languages
German (de)
English (en)
Other versions
EP0758054B1 (fr
Inventor
Ferdinand Baur
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sulzer Escher Wyss GmbH
Original Assignee
Sulzer Escher Wyss GmbH
Escher Wyss GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Sulzer Escher Wyss GmbH, Escher Wyss GmbH filed Critical Sulzer Escher Wyss GmbH
Priority to EP95810503A priority Critical patent/EP0758054B1/fr
Priority to DE59509083T priority patent/DE59509083D1/de
Priority to US08/692,684 priority patent/US5765392A/en
Publication of EP0758054A1 publication Critical patent/EP0758054A1/fr
Application granted granted Critical
Publication of EP0758054B1 publication Critical patent/EP0758054B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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)
EP95810503A 1995-08-09 1995-08-09 Système de circulation d'huile pour un compresseur à vis Expired - Lifetime EP0758054B1 (fr)

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)

* Cited by examiner, † Cited by third party
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)

* Cited by examiner, † Cited by third party
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)

* Cited by examiner, † Cited by third party
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)

* Cited by examiner, † Cited by third party
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

Patent Citations (4)

* Cited by examiner, † Cited by third party
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)

* Cited by examiner, † Cited by third party
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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