EP0593495B1 - Dispositif frigorifique - Google Patents

Dispositif frigorifique Download PDF

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Publication number
EP0593495B1
EP0593495B1 EP92909704A EP92909704A EP0593495B1 EP 0593495 B1 EP0593495 B1 EP 0593495B1 EP 92909704 A EP92909704 A EP 92909704A EP 92909704 A EP92909704 A EP 92909704A EP 0593495 B1 EP0593495 B1 EP 0593495B1
Authority
EP
European Patent Office
Prior art keywords
compressor
oil
coolant
refrigerant
bearings
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
EP92909704A
Other languages
German (de)
English (en)
Other versions
EP0593495A1 (fr
Inventor
Klaus Hossner
Adalbert Stenzel
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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 Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP0593495A1 publication Critical patent/EP0593495A1/fr
Application granted granted Critical
Publication of EP0593495B1 publication Critical patent/EP0593495B1/fr
Anticipated expiration legal-status Critical
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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
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid

Definitions

  • the invention relates to a cooling device according to the preamble of patent claim 1.
  • Refrigeration and air conditioning systems essentially comprise an evaporator in which heat is extracted from the environment by vaporizing the refrigerant, a compressor which increases the pressure of the evaporated refrigerant from a suction pressure to an outlet pressure, and a condenser in which that is under the outlet pressure evaporated refrigerant is liquefied with the release of heat.
  • the oil injected into the compressor is cooled depending on an end temperature resulting at the pressure outlet of the compressor. Cooling can be done by refrigerant injection, or by cooling with water or air in a heat exchanger, e.g. a plate heat exchanger. In the latter case, a large amount of oil injection requires large and expensive heat exchangers.
  • the temperature of the injected oil is essentially determined by the fact that its viscosity is high enough to ensure lubrication of the bearing points. If the oil temperature rises, the viscosity of the oil drops and the lubrication of the bearing points of the rotors is at risk. However, lower oil viscosities or higher oil temperatures would also be permissible for the above-mentioned seal of the column, which requires the largest amount of oil injection.
  • the object of the invention is to cool the oil used for bearing lubrication in a simple and economical manner, regardless of the total amount of oil injected into the compressor.
  • a cooling device essentially comprises a screw compressor 1, a condenser 2 and an evaporator 3, which are connected in a closed refrigerant circuit by lines 4. Furthermore, there is a check valve 5 in the refrigerant circuit, which is arranged directly at the pressure outlet of the compressor, an oil separator 6, which is arranged behind the check valve 5 and in front of the condenser 2, and an expansion element 7, which is located between the condenser 2 and the evaporator 3 in the refrigerant circuit.
  • a first temperature sensor 8 senses the temperature at the bearing points of the compressor 1 and is connected to a control unit 11 via an electrical line 9.
  • a second Temperature sensor 12 senses the temperature in the pressure outlet area of the compressor 1 and is also connected to the control unit 11 via an electrical line 13.
  • a main oil line 14 extends from the oil separator 6 and leads into the compression space of the compressor 1 via a solenoid valve 15.
  • a bearing oil line 16 is branched off from the main oil line 14 and leads into a heat exchanger 17 and from there to the bearing points of the compressor 1.
  • part of the refrigerant is branched off from the line 4 of the refrigerant circuit via a line 18, fed to a solenoid valve 20 which can be controlled by the control unit 11 via an electrical line 19, and passes from there via an injection nozzle 21 into the heat exchanger 17, from which it is fed to a point 22 of the compressor 1 at which the suction process of the compressor 1 caused by the rotors is completed.
  • the cooling device operates as follows: The refrigerant evaporated in the evaporator 3 is drawn in on the suction side of the compressor 1 and is compressed therein. Oil is injected into the compression chamber of the compressor via the main oil line 14 and the solenoid valve 15. The oil is entrained by the refrigerant to be compressed, and the resulting oil-refrigerant mixture is compressed in the compressed state Check valve 5 fed to the oil separator 6. In the oil separator 6, the oil is separated from the refrigerant and, since it is under increased pressure, is injected back into the compressor 1 via the main oil line 14 and the solenoid valve 15 at a point of the compressor which is at a lower pressure. The oil is separated from the refrigerant so as not to adversely affect the heat transfer of the refrigerant within the refrigerant circuit and also to implement a closed main oil circuit.
  • the control unit 11 opens the magnetic valve 20 via the electrical line 19 and coolant in a liquid state Form injected into the heat exchanger 17 via the line 18 and the injector 21.
  • the oil branched off from the main oil line 14 via the bearing oil line 16 is cooled for cooling the bearing points by the refrigerant branched off behind the condenser 2, heat being supplied to the coolant and heat being removed from the oil used for lubricating the bearing points.
  • the refrigerant evaporated in the heat exchanger 17 is fed to the suction side of the compressor, advantageously to a point 22 at which the suction process of the compressor 1 is completed.
  • the injection at this point 22 of the compressor 1 is necessary because otherwise the cooling capacity of the compressor, ie the amount of heat absorbed by the environment in the evaporator 3 for evaporating the refrigerant, decreases because the refrigerant branched off for cooling the oil used for bearing lubrication does not transfer heat contributes in the evaporator 3. Furthermore, when the refrigerant is injected at the point 22 of the compressor 1, there is the advantage that the refrigerant coming from the heat exchanger 17 meets the partially compressed, warmer refrigerant in the compressor 1 and thereby cools the latter, which leads to an advantageous lower compression end temperature.
  • the second temperature sensor 12 located in the pressure outlet area of the compressor 1 opens the solenoid valve 20 via the electrical line 13 through the control unit 11 and more refrigerant is injected into the heat exchanger 17 by means of the injection nozzle 21. than is necessary for cooling the oil used for bearing lubrication.
  • the temperature sensor 12 or a further temperature sensor (not shown) in the pressure outlet region of the compressor 1 via the control unit 11 switches off the compressor.
  • the main advantage of the controllable cooling of the oil used to lubricate the compressor bearing points according to the invention is that, despite the use of an oil with a low basic viscosity, a sufficient operating viscosity of the oil used for the bearing lubrication is achieved. Since the main oil flow in the main oil line, which is intended for injection into the compressor, remains uncooled, it is prevented that the compression end temperature does not drop to critical values and thus no refrigerant in the oil separator condenses into the oil. In addition, the cost of oil cooling is significantly reduced by the bearing oil cooling according to the invention and thus the economy is increased.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Encapsulation Of And Coatings For Semiconductor Or Solid State Devices (AREA)
  • Sampling And Sample Adjustment (AREA)
  • Surgical Instruments (AREA)

Claims (4)

  1. Dispositif de refroidissement pour un compresseur à piston rotatif (1), notamment un compresseur à vis faisant partie d'un circuit de réfrigérant conjointement avec un condenseur (2) et un évaporateur (3), un flux partiel (18) du réfrigérant de l'installation frigorifique et une huile (16) servant à la lubrification des paliers ainsi qu'au refroidissement et à l'étanchement du compresseur à vis pouvant être injectés dans le compresseur à vis, huile pour le refroidissement de laquelle on utilise un flux dérivé de réfrigérant qui est lui-même ensuite à nouveau amené au compresseur à vis, caractérisé en ce que seule la partie de l'huile servant à la lubrification des paliers du compresseur à vis (1) est refroidie par le flux dérivé de réfrigérant, en fonction de la température de l'huile qui est détectée au niveau des paliers.
  2. Dispositif selon la revendication 1, caractérisé en ce que le flux dérivé de réfrigérant peut en outre être régulé en fonction d'une température finale de compression s'obtenant à la suite de la compression.
  3. Dispositif selon la revendication 1 ou 2, caractérisé en ce que le flux dérivé de réfrigérant est amené au côté aspiration du compresseur à vis (1).
  4. Dispositif selon l'une des revendications précédentes, caractérisé en ce que le flux dérivé de réfrigérant est amené au compresseur à vis (1) en un point (22) où le processus d'aspiration du compresseur à vis (1) est achevé.
EP92909704A 1991-07-11 1992-05-13 Dispositif frigorifique Expired - Lifetime EP0593495B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4122889 1991-07-11
DE4122889A DE4122889C1 (fr) 1991-07-11 1991-07-11
PCT/EP1992/001045 WO1993001413A1 (fr) 1991-07-11 1992-05-13 Dispositif frigorifique

Publications (2)

Publication Number Publication Date
EP0593495A1 EP0593495A1 (fr) 1994-04-27
EP0593495B1 true EP0593495B1 (fr) 1995-01-18

Family

ID=6435868

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92909704A Expired - Lifetime EP0593495B1 (fr) 1991-07-11 1992-05-13 Dispositif frigorifique

Country Status (7)

Country Link
US (1) US5433590A (fr)
EP (1) EP0593495B1 (fr)
AT (1) ATE117409T1 (fr)
DE (1) DE4122889C1 (fr)
DK (1) DK0593495T3 (fr)
ES (1) ES2067334T3 (fr)
WO (1) WO1993001413A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6082982A (en) * 1997-11-17 2000-07-04 Uop Llc Flooded compressor with improved oil reclamation
CN1283254A (zh) * 1997-12-30 2001-02-07 爱特里尔斯布时股份公司 冷却装置
US6067804A (en) * 1999-08-06 2000-05-30 American Standard Inc. Thermosiphonic oil cooler for refrigeration chiller
DE19963170A1 (de) * 1999-12-27 2001-06-28 Leybold Vakuum Gmbh Vakuumpumpe mit Wellendichtmitteln
EP1571337B1 (fr) * 2004-03-05 2007-11-28 Corac Group plc Compresseur sans huile pour gaz à plusieurs étages
SE0402006L (sv) * 2004-08-12 2005-10-18 Peter Blomkvist Värmepump
US8590324B2 (en) 2009-05-15 2013-11-26 Emerson Climate Technologies, Inc. Compressor and oil-cooling system
EP2766676B1 (fr) * 2011-09-16 2018-03-21 Danfoss A/S Circuits de refroidissement et de sous-refroidissement de moteur pour compresseur
EP2573429B1 (fr) * 2011-09-22 2014-04-23 Moventas Gears Oy Procédé de contrôle d'une pompe de lubrification d'une unité d'engrenage et unité d'engrenage
EP2573388B1 (fr) * 2011-09-22 2018-11-07 Moventas Gears Oy Procédé de contrôle d'une pompe de lubrification d'une unité d'engrenage et unité d'engrenage

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3176913A (en) * 1960-07-22 1965-04-06 Linde Eismasch Ag Rotary compressor arrangement
US3710590A (en) * 1971-07-19 1973-01-16 Vilter Manufacturing Corp Refrigerant cooled oil system for a rotary screw compressor
US3759348A (en) * 1971-11-08 1973-09-18 Maekawa Seisakusho Kk Method of compressing chlorine gas
SE360168B (fr) * 1971-12-22 1973-09-17 Stal Refrigeration Ab
DE2801408A1 (de) * 1978-01-13 1979-07-19 Linde Ag Verfahren und vorrichtung zum kuehlen eines in einem kaeltekreislauf angeordneten verdichters der drehkolbenbauart
FR2620205A1 (fr) * 1987-09-04 1989-03-10 Zimmern Bernard Compresseur hermetique pour refrigeration avec moteur refroidi par gaz d'economiseur
JPH0784955B2 (ja) * 1989-04-26 1995-09-13 ダイキン工業株式会社 スクリュー冷凍機

Also Published As

Publication number Publication date
ES2067334T3 (es) 1995-03-16
DE4122889C1 (fr) 1992-12-17
EP0593495A1 (fr) 1994-04-27
WO1993001413A1 (fr) 1993-01-21
ATE117409T1 (de) 1995-02-15
US5433590A (en) 1995-07-18
DK0593495T3 (da) 1995-04-10

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