EP0758054B1 - 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
EP0758054B1
EP0758054B1 EP95810503A EP95810503A EP0758054B1 EP 0758054 B1 EP0758054 B1 EP 0758054B1 EP 95810503 A EP95810503 A EP 95810503A EP 95810503 A EP95810503 A EP 95810503A EP 0758054 B1 EP0758054 B1 EP 0758054B1
Authority
EP
European Patent Office
Prior art keywords
screw compressor
oil
accordance
connection
partial
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
Application number
EP95810503A
Other languages
German (de)
English (en)
Other versions
EP0758054A1 (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 is about a Screw compressor device for refrigerants with refrigerant-soluble oils, preferably for ammonia polyalkylene glycol soluble therein, with a flow after a screw compressor in a under Oil separator at outlet pressure in a gas stream and is divided into an oil flow and the oil flow via a throttle and an oil inlet in the Screw compressor arrives.
  • Screw compressors roll two helical rotors, main and secondary rotor, in a housing (e.g. EP-A-0 030 619). Enlarged during the suction process the tooth gap between the rotors Gas is sucked in. As the rotors continue to turn closes this gap when crossing the Inlet control edge. The counter wheel engages when turning further into the gap and continuously reduces the enclosed gas space, the gas is compressed until finally reaches the exit control edge and that compressed gas is pushed out.
  • a housing e.g. EP-A-0 030 619
  • Screw compressor 1 becomes one with oil particles penetrated gas stream 30 via a pressure line 2 promoted an oil separator 3. From there the deoiled gas stream 31 in the sense of refrigeration Cycle to a condenser. That in Oil separator 3 separated oil passes through a Line 4 to a water or air-cooled oil cooler 5, in which the heat of compression is dissipated. The oil is from there via a line 6, an oil filter 7 Check valve 8, a solenoid valve 9 and one Oil inlet 10 fed back to the compressor 1, wherein usually the pressure difference between pressure and Suction side on the compressor used for oil delivery becomes.
  • Part of this returned oil is used for the Lubrication of the bearings and in so-called "open" Compressors with the drive shaft facing outwards is performed for the lubrication and cooling of the Shaft seal used.
  • the rotating one Shaft seal is used to drive the compressor drive shaft to seal against the atmosphere.
  • the NH3-soluble oils accumulate due to the Solution behavior according to the given in the oil separator Pressure and temperature conditions with a certain Amount of NH3 at a normal operating point e.g. With approx. 6% NH3 in oil.
  • a normal operating point e.g. With approx. 6% NH3 in oil.
  • the shaft seal and the drive-side bearing will Oil relaxed at suction pressure.
  • the NH3 absorption capacity of oil decreases at a normal operating point e.g. to approx. 3% NH3 in the oil, so that the difference of approx. 3% NH3 inevitably evaporates from the oil. Because of the very large steam volume of NH3 is created by this Evaporation process 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 that do oil intended for lubrication and sealing via a Throttle point 25 relaxed and over one Evaporation container 21 leads, the vapor space via a Line 12 with the suction side 29 of the screw compressor 1 communicates.
  • This "degasses" the oil and can with better lubrication of the shaft seal and be supplied to the drive side bearing, the necessary pressure difference generated by an oil pump 13 becomes.
  • This arrangement has the disadvantage that the Screw compressor during its operation from the Functionality of an oil pump depends. Another Disadvantage is that with the start of such Screw compressor device the oil behind the Throttle point 25 foams and partly as foam the lubrication points.
  • the object of the invention is to address these circumstances improve.
  • This arrangement has the advantage that with one Power failure the lubrication pressure does not collapse during the run-out of the screw compressor, because the pressure difference between final pressure and intermediate pressure if at all slowly after the standstill of the Dismantles screw compressor. In the further there is none Oil pump necessary. In addition, the lubricating oil discharged steam is fed in at intermediate pressure, so that its compression from suction pressure to intermediate pressure and thus the cooling capacity of the cycle is improved.
  • the evaporation tank above to arrange the screw compressor and with check valves emptying the evaporation tank and the supply line in the To prevent standstill, at least the geodesic To have gradients available. If the pressure difference between final pressure and intermediate pressure in the start phase is small, you can also use an oil pump after Provide evaporation containers which, after starting, i.e. at sufficient pressure difference is switched off.
  • the figures are used to improve the lubrication of Bearings and shaft seals on screw compressors for Refrigerant shown with refrigerant-soluble oils.
  • a typical application results for example for Ammonia with soluble polyalkylene glycol.
  • the oil flow returned to the screw compressor before the pressure is reduced to approximately the compressor suction pressure a partial oil flow is withdrawn at an intermediate pressure and is passed over an evaporation tank significant proportions of dissolved refrigerant in one Intermediate pressure connection on the compression path of the Screw compressor can be fed.
  • Corresponding the lubricating properties are more favorable than the rest Partial oil flow at the lubrication connection and the disadvantages of Pressure collapse or foam delivery at one Oil pumps are not required since there is no oil pump with a suitable one Intermediate pressure is necessary.
  • a screw compressor 1 promotes ammonia Gaseous form from a suction line 29 and compresses it, being Polyalkylene glycol injected at an oil inlet 10 the sealing effect between the To improve compression chambers.
  • a throttle point 25 is shown for the resistance of the Nozzles or orifices during injection.
  • the one against Final pressure emerging from the screw compressor 1 Flow 30 is a via a pressure line Oil separator 3 supplied, which has a gas space 3a, from which a gas stream 31 is not shown Condenser is supplied while at the bottom of the Oil separator 3 is an oil supply 3b, from which an oil flow 32 via a line 4 through an oil cooler 5 is performed.
  • the cooled oil flow 32 enters one Line 6 via an oil filter 7, a check valve 8 and a solenoid valve 9 to the throttle point 25 and Oil entry 10.
  • a Branch 11 Before the throttle point 25 is in a Branch 11 is a partial oil flow 35 for the lubrication of Bearings and shaft seals branched and into one Evaporation tank led under the pressure of a Intermediate pressure port 14 on the compression path of the Screw compressor 1 stands.
  • the pressure at entering the branch 11 must therefore be somewhat higher than the pressure in the Intermediate pressure port 14 to be with an aperture 26th to restrict the partial oil flow 35.
  • a Outgassing of ammonia takes place via a line 23 is fed in at the intermediate pressure connection 14.
  • the Outgassing can be by a heater 19, as in 4 and 5 is supported.
  • the degassed partial oil flow enters via a line 15 and Solenoid valve 17 to a lubrication connection 16 and after Running through bearings and shaft seals in one Suction chamber 29 at the compressor inlet back into the gas flow.
  • the evaporation tank 24 is above the Screw compressor 1 arranged and the solenoid valve 17th is closed at a standstill in order to take one under To have gravity supply of oil.
  • FIG. 5 only the circle from partial oil flow 35 is shown Compared to Figure 3 expanded by further components been.
  • a solenoid valve 18 provided that a flow of Prevents oil from the higher areas, and the Partial oil flow 35 is limited by a control valve 20, which, for example, the oil level in the evaporation tank 24 holds constant.
  • a heater 19 favors this Degassing refrigerant.
  • Line 15 bifurcates the solenoid valve 17 in a line 15a, in which a Oil pump 22 with check valve 27 as a starting aid is installed, and in a strand 15b with a Check valve 28 to the shutdown oil pump 22nd to convey past into the lubrication port 16.
  • Such Booster pump 22 could always run when the intermediate pressure for the lubrication is insufficient.
  • the Control valve 20 would correspond to the partial oil flow 35 Track the pumping capacity of the pump 22.
  • Figure 4 shows one compared to Figures 3 and 5 Arrangement in which the branch 11 for the partial oil flow 35 goes in front of the oil cooler 5.
  • the partial oil flow arrives already much hotter via a solenoid valve 18 and a Control valve 20 in the evaporation tank 24.
  • One on Evaporation tank 24 attached heater 19 is therefore only be necessary in exceptional cases.
  • the oil also arrives via a line 15 and Solenoid valve 17 in the lubrication port 16, which Solenoid valve 17 when the oil supply is at a standstill located evaporation container 21.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (11)

  1. Installation de compresseur à vis pour des fluides frigorigènes avec des huiles solubles dans des fluides frigorigènes, de préférence pour de l'ammoniaque avec du polyalkylèneglycol soluble dans celui-ci, où un flux de convoyage (30), en aval d'un compresseur à vis (1), dans un séparateur d'huile (3) soumis à une pression de sortie, est divisé en un flux de gaz (31) et un flux d'huile (32) et où le flux d'huile (32) arrive par un emplacement d'étranglement (25) et une entrée d'huile (10) dans le compresseur à vis (1), caractérisée en ce qu'il est dérivé en amont de l'emplacement d'étranglement (25) par un branchement (11) un flux d'huile partiel (35) pour le graissage de paliers et/ou de garnitures d'étanchéité d'arbre, qui est guidé à travers un récipient d'évaporation (24) qui est relié, côté gaz, par un conduit (23) à un raccord de pression intermédiaire (14) sur le chemin de compression du compresseur à vis (1) pour amener le flux d'huile partiel (35) sous une pression correspondant à la pression intermédiaire à un raccord de graissage (16) au compresseur à vis.
  2. Installation de compresseur à vis selon la revendication 1, caractérisée en ce que le récipient d'évaporation (24) est disposé géodésiquement au-dessus des emplacements de graissage au compresseur à vis (1) pour tirer profit d'une pente pour la pression de graissage.
  3. Installation de compresseur à vis selon la revendication 2, caractérisée en ce qu'il est disposé entre le réservoir d'évaporation (24) et le raccord de graissage (16) une vanne d'arrêt (17) pour empêcher, lors d'un arrêt, un écoulement d'huile du réservoir d'évaporation (24).
  4. Installation de compresseur à vis selon l'une des revendications 1 à 3, caractérisée en ce qu'il est disposé dans le branchement (11) une vanne d'arrêt (18) pour, lors d'un arrêt, empêcher un reflux de l'huile.
  5. Installation de compresseur à vis selon l'une des revendications 1 à 4, caractérisée en ce qu'il est disposé au récipient d'évaporation (24), pour soutenir la puissance d'évaporation, une installation de chauffage (19) qui, lors d'un arrêt, empêche un enrichissement de l'huile en fluide frigorigène.
  6. Installation de compresseur à vis selon l'une des revendications 1 à 5, caractérisée en ce qu'il est prévu dans le branchement (11) un organe d'étranglement (26) pour limiter le flux d'huile partiel (35).
  7. Installation de compresseur à vis selon la revendication 6, caractérisée en ce qu'il est prévu dans le branchement (11) comme organe d'étranglement une vanne de réglage (20) pour régler, conformément à une valeur de consigne prédéterminée, le flux d'huile partiel (35) dans le branchement (11).
  8. Installation de compresseur à vis selon l'une des revendications 1 à 7, caractérisée en ce que sont prévus entre le récipient d'évaporation (24) et le raccord de graissage (16) deux conduits de liaison parallèles (15a, 15b) dont l'un (15a) présente une pompe de convoyage (22) avec une vanne d'arrêt (27) et l'autre (15b) une vanne d'arrêt (28) pour, lors du démarrage du compresseur à vis (1), soutenir le convoyage de l'huile dans le raccord de graissage (16).
  9. Installation de compresseur à vis selon l'une des revendications 1 à 8, caractérisée en ce que le compresseur à vis, comme raccord intermédiaire (14), présente un raccord économique tel que prévu pour une introduction intermédiaire d'un flux de gaz partiel lors d'une détente multiple du flux de gaz (31).
  10. Installation de compresseur à vis selon l'une des revendications 1 à 8, caractérisée en ce que le raccord de pression intermédiaire (14), sur toute la zone de rendement, notamment aussi dans le cas d'une charge partielle extrême, ne présente pas de liaison à l'enceinte d'aspiration afin de maintenir une pression intermédiaire requise pour le graissage.
  11. Installation de compresseur à vis selon l'une des revendications 1 à 8, où le compresseur à vis présente notamment une garniture d'étanchéité d'arbre et possède un palier côté entraínement au côté d'aspiration.
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 EP0758054A1 (fr) 1997-02-12
EP0758054B1 true 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

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US (1) US5765392A (fr)
EP (1) EP0758054B1 (fr)
DE (1) DE59509083D1 (fr)

Families Citing this family (21)

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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
US8858192B2 (en) * 2009-03-16 2014-10-14 Daikin Industries, Ltd. Screw compressor
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
EP2920469A2 (fr) 2012-09-27 2015-09-23 Vilter Manufacturing Llc Appareil et procédé pour améliorer le rendement de compresseur
US10487833B2 (en) 2013-12-18 2019-11-26 Carrier Corporation Method of improving compressor bearing reliability
CN105829715B (zh) * 2013-12-18 2019-07-09 开利公司 压缩机组件和用于可移动部件的润滑系统
DE102014101113A1 (de) * 2014-01-30 2015-07-30 Pfeiffer Vacuum Gmbh Vakuumpumpe
EP3387258B1 (fr) * 2015-12-11 2020-02-12 Atlas Copco Airpower Procédé de régulation de l'injection de liquide d'un compresseur, compresseur à injection de liquide et élément compresseur à injection de liquide
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
EP3814695A1 (fr) 2018-06-26 2021-05-05 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

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Also Published As

Publication number Publication date
US5765392A (en) 1998-06-16
DE59509083D1 (de) 2001-04-12
EP0758054A1 (fr) 1997-02-12

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