EP2283284B1 - Kältezyklus und betriebsverfahren dafür - Google Patents

Kältezyklus und betriebsverfahren dafür Download PDF

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Publication number
EP2283284B1
EP2283284B1 EP08773413.3A EP08773413A EP2283284B1 EP 2283284 B1 EP2283284 B1 EP 2283284B1 EP 08773413 A EP08773413 A EP 08773413A EP 2283284 B1 EP2283284 B1 EP 2283284B1
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EP
European Patent Office
Prior art keywords
oil
suction pressure
pressure compressor
oil sump
compressor
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Application number
EP08773413.3A
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English (en)
French (fr)
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EP2283284A1 (de
Inventor
Markus Hafkemeyer
Tobias H. Sienel
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Carrier Corp
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Carrier Corp
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0207—Lubrication with lubrication control systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0269—Hermetic compressors with device for spraying lubricant or with mist lubrication

Definitions

  • the invention relates to a refrigeration cycle and to a method for operating the same.
  • compressors forming one or more sets of compressors are used.
  • the refrigerant circulated through such compressors carries an amount of lubricant, especially machine oil. Normally part of the amount of oil carried by the refrigerant collects in the oil sump of the compressors.
  • Each compressor has a certain oil discharge rate or oil circulation rate depending on its design and operating conditions.
  • the oil circulation rate of a compressor defines the amount of oil that can be transported through the compressor and discharged from the compressor per time unit.
  • FR 1 408 672 shows a compressor for a refrigeration machine comprising a pipe for supplying oil to an oil sump of the compressor.
  • DE 10 44 839 B discloses an arrangement for lubricating friction surfaces of an encapsulated oscillating compressor, in particular for refrigerators, by a capillary extending from the oil sump of the compressor and an oil supply serving injector, which is incorporated in the suction line.
  • the capillary projecting into the oil sump immediately before the suction valve of the compressor is inserted into the suction line such that refrigerant vapor passing the mouth of this capillary triggers an injector-like effect.
  • Another oil recirculation means in a compressor is disclosed in US2956730
  • an oil recirculation arrangement for a refrigeration system comprising low and high suction pressure compressors in series is further disclosed in US2006/0073026 . It would be beneficial to provide a reliable and failure-free operation of refrigeration systems where compressors of different sizes and variable speeds are running.
  • FIG. 1 shows a compressor 2 of arbitrary type for use in a refrigeration cycle.
  • the compressor 2 comprises a housing 4 including a crank case, an inlet port 6, an oil sump 8, a compression element 10, which can be the compression element of a reciprocating compressor including a piston, a piston rod and the like or the compression element of a scroll compressor including scrolls and the like or the compression element of any other type of compressor, a crank shaft 12 for driving the compression element 10, a motor 14 rotating the crank shaft 12 and an outlet port 18.
  • the inlet port 6 is connected a suction conduit, especially a piping, to one or more evaporators connected upstream thereof.
  • the outlet port 18 is connected to a discharge or pressure conduit, especially a piping, to a heat-rejection heat exchanger connected downstream thereof.
  • the inlet port 6 of the compressor attaches to its right-hand side wall and the outlet port 18 is attached to the upper side of the compressor 2.
  • a refrigerant flow 20 of a gaseous refrigerant carrying an amount of oil forms through the inlet port 6, the compression element 10 and the outlet port 18.
  • Part of the oil carried by the gaseous refrigerant is separated on its way to the compression element 10 and falls into the oil sump 8, where it collects.
  • the gaseous refrigerant together with the remaining oil is sucked into the compression element 10, compressed therein and leaves the compressor 2 at the outlet port 18.
  • the oil from the oil sump 8 is taken to lubricate the bearings, pistons and the like and is finally also leaving the compressor 2 to the heat-rejection heat exchanger connected downstream thereof. If more oil is separated than disgorged, the oil level in the oil sump 8 rises.
  • Figure 2 shows a reciprocating compressor 26 for use in a refrigeration cycle.
  • the oil dispersing blade 28 has the function of a slinger. It dips into the oil sump 8 and disperses an amount of oil to form an oil mist in the crank case to be entrained by the refrigerant flow 20, when the oil in the oil sump 8 reaches the predetermined oil sump level 24. This oil mist entrained into the refrigerant gas flow 20 is sucked to the compression chamber and as a result more oil is transported out of the compressor 26 and the oil circulation rate will be increased.
  • the design of the oil dispersing blade 28 will influence the characteristics of the oil circulation rate.
  • the outer radius and the diameter of the oil dispersing blade 28 measured from the crank shaft axis will control the level of the increase of the oil circulation rate. Its shape will give a function of oil circulation rate as a parameter of the oil level.
  • an oil dispersing disc or another feature which is fixed with the crank shaft and rotates with it can be employed.
  • crank shaft 12 itself as a tool which increases the oil circulation rate.
  • the crank shaft 12 When the oil in the oil sump 8 reaches the predetermined oil sump level 24, the crank shaft itself will dip into the oil sump 8 and disperse an amount of oil to form an oil mist to be entrained by the refrigerant flow 20 thereby increasing the oil circulation rate.
  • crankshaft can be placed on the crankshaft to further amplify the oil dispersion if needed.
  • the flow of oil mist within the crank case must be sufficiently high to transport the oil into the suction of the compression element 10. This can be done by appropriately sizing the crankcase as well as the passages which lead from the crankcase to the compression element 10.
  • Figure 3 shows a scroll compressor 44 for use in a refrigeration cycle.
  • crank shaft 12 extends substantially in a vertical direction
  • the inlet port 6 attaches to the left-hand side wall
  • the outlet port 18 attaches to the upper side of the housing 4.
  • a by-pass line 46 extends between an entrainment point 48 positioned at the left-hand side wall of the crank case 4 substantially at the height of the predetermined oil sump level 24 and the inlet port 6 connected with the suction line leading to the compression element 10.
  • the by-pass line 46 can be formed as a bore, as a canal or a pump line and can be internal to the compressor housing or external as shown.
  • Figure 4 shows a reciprocating compressor 52 for use in a refrigeration cycle.
  • Figure 5 shows a first oil circulation rate balancing diagram 64.
  • Figure 6 shows a first multiple compressor refrigeration system 66.
  • Figure 7 shows a second multiple compressor refrigeration system 78 according to the invention.
  • the discharge lines of the lower suction pressure evaporators 84 combine into a common suction line which then divides into three separate suction lines for each of the lower suction pressure compressors 80.
  • the pressure lines of the lower suction pressure compressors 80 combine into a common suction line that divides into three separated suction lines for the medium suction pressure compressors 82.
  • the pressure lines of the medium suction pressure compressors 82 combine into a common pressure line leading to the heat-rejection heat exchanger 70.
  • the discharge lines of the medium suction pressure evaporators 88 combine into a common suction line discharging into the suction line leading to the medium suction pressure compressors 82.
  • the third multiple compressor refrigeration system 92 corresponds to the second multiple compressor refrigeration system 78 with the exception that the two sets of compressors, namely the set of the three lower suction pressure compressors 94 and the set of the three higher suction pressure compressors 96 are not connected in series, but rather in parallel.
  • This diagram 98 shows the oil circulation rate for both the lower suction pressure compressors 94 and the higher suction pressure compressors 96 as a function of increasing oil flow in liters wherein the lower suction pressure compressors 94 are provided with oil circulation rate enhancement features according to the invention therefor allowing for a oil circulation rate adjustment, wherein the higher suction pressure compressors 96 have a nominal oil circulation rate in the range of 0.8 to 1.6 % as depicted in the second oil circulation rate balancing diagram 98.
  • test data for a lower suction pressure reciprocating compressor is shown as a function of the oil sump level.
  • the self-regulating concept of the invention can clearly be seen in this Figure.
  • each lower suction pressure compressor will be able to self-regulate the amount of oil in its sump to achieve a safe level.
  • a closer balance between the required capacity and the delivered capacity can be achieved, which will result in less on/off cycling and lower variations between the desired and actual suction pressure, which will serve to increase the reliability and decrease of energy consumption of the refrigeration system.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (11)

  1. Kältekreislauf (78), umfassend mindestens einen Verdichter mit niedrigerem Saugdruck (80), mindestens einen Verdichter mit höherem Saugdruck (82), wobei der mindestens eine Verdichter mit niedrigerem Saugdruck (80) und der mindestens eine Verdichter mit höherem Saugdruck (82) in Reihe verbunden sind, einen wärmeabgebenden Wärmetauscher (70), bevorzugt einen Sammelbehälter (72), mindestens einen Verdampfer mit niedrigerem Saugdruck (84), der eine Expansionseinrichtung (86) aufweist, die stromaufwärts davon verbunden ist, mindestens einen Verdampfer mit höherem Saugdruck (88), der eine Expansionseinrichtung (90) aufweist, die stromaufwärts davon verbunden ist, und Leitungen, durch die ein Kältemittel zirkuliert,
    wobei der mindestens eine Verdichter mit niedrigerem Saugdruck (80) Folgendes umfasst:
    eine Einlassöffnung (6),
    ein Verdichtungselement (10),
    eine Auslassöffnung (18),
    wobei in Betrieb ein Kältemittelstrom (20) eines gasförmigen Kältemittels, das eine Menge von Öl befördert, durch die Einlassöffnung (6), das Verdichtungselement (10) und die Auslassöffnung (18) zirkuliert,
    einen Ölsumpf (8), in dem sich ein Teil des durch das gasförmige Kältemittel beförderten Öls sammelt,
    dadurch gekennzeichnet, dass
    der mindestens eine Verdichter mit niedrigerem Saugdruck (80) ferner ein Merkmal zur Verbesserung der Ölzirkulationsrate (16) umfasst, das so konfiguriert ist, dass es Öl aus dem Ölsumpf (8) zu dem Kältemittelstrom (20) und somit zu dem stromabwärts verbundenen Verdichter mit höherem Saugdruck (82) leitet, wenn das Öl in dem Ölsumpf (8) einen vorbestimmten Ölsumpfstand (24) übersteigt;
    dass der Verdichter mit niedrigerem Saugdruck (80) und der Verdichter mit höherem Saugdruck (82) derart konfiguriert sind, dass, wenn der Ölsumpfstand (8) des Verdichters mit niedrigerem Saugdruck (80) geringer als sein vorbestimmter Ölsumpfstand (24) ist, seine Ölzirkulationsrate stets geringer als die Ölzirkulationsrate des Verdichters mit höherem Saugdruck (82) ist;
    und dass der Verdichter mit niedrigerem Saugdruck (80) und der Verdichter mit höherem Saugdruck (82) derart konfiguriert sind, dass, wenn der Ölsumpfstand (8) des Verdichters mit niedrigerem Saugdruck (80) seinen vorbestimmten Ölsumpfstand (24) übersteigt, seine Ölzirkulationsrate stets höher als die Ölzirkulationsrate des Verdichters mit höherem Saugdruck (82) ist.
  2. Kältekreislauf (78) nach Anspruch 1, umfassend Verdichter (80), die unterschiedliche Größen aufweisen.
  3. Kältekreislauf (78) nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das Merkmal zur Verbesserung der Ölzirkulationsrate durch die Kurbelwelle (12) ausgebildet ist, die drehbar durch einen Motor (14) angetrieben ist, wobei die Kurbelwelle (12) so konfiguriert ist, dass sie in den Ölsumpf (8) eintaucht und eine Menge von Öl dispergiert, um einen Ölnebel zu bilden, der durch den Kältemittelstrom (20) mitgenommen wird, wenn das Öl in dem Ölsumpf (8) den vorbestimmten Ölsumpfstand (24) erreicht.
  4. Kältekreislauf (78) nach Anspruch 1, 2 oder 3, dadurch gekennzeichnet, dass das Merkmal zur Verbesserung der Ölzirkulationsrate durch ein Öldispersionselement (28) ausgebildet ist, insbesondere eine Schaufel oder eine Scheibe, die an der Kurbelwelle (12) befestigt ist und drehbar durch einen Motor (14) angetrieben ist, wobei das Öldispersionselement (28) so konfiguriert ist, dass es in den Ölsumpf (8) eintaucht und eine Menge von Öl dispergiert, um einen Ölnebel zu bilden, der durch den Kältemittelstrom (20) mitgenommen wird, wenn das Öl in dem Ölsumpf (8) den vorbestimmten Ölsumpfstand (24) erreicht.
  5. Kältekreislauf (78) nach Anspruch 1, dadurch gekennzeichnet, dass das Merkmal zur Verbesserung der Ölzirkulationsrate durch eine Umgehungsleitung (46, 54) ausgebildet ist, die sich zwischen dem Ölsumpf (8) im Wesentlichen in einer Höhe des vorbestimmten Ölsumpfstands (24) und dem Kältemittelstrom (20) an einer Position vor dem Verdichtungselement (10) innerhalb oder außerhalb des Verdichtergehäuses erstreckt.
  6. Kältekreislauf (78) nach Anspruch 5, dadurch gekennzeichnet, dass ein Ejektor zum Transportieren von Öl aus dem Ölsumpf (8) zu dem Kältemittelstrom (20) bereitgestellt ist.
  7. Kältekreislauf (78) nach Anspruch 5, dadurch gekennzeichnet, dass Öl durch Mitnahme durch statischen Druck aus dem Ölsumpf (8) zu dem Kältemittelstrom (20) transportiert wird.
  8. Kältekreislauf (78) nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass sich die Umgehungsleitung (46) zwischen dem Ölsumpf (8) auf der Höhe des vorbestimmten Ölsumpfstands (24) und der Einlassöffnung (6) erstreckt.
  9. Kältekreislauf (78) nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass sich die Umgehungsleitung (46) zwischen dem Ölsumpf (8) auf der Höhe des vorbestimmten Ölsumpfstands (24) und einer Saugleitung, die mit der Einlassöffnung verbunden ist, erstreckt.
  10. Kältekreislauf (78) nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass sich die Umgehungsleitung (54) zwischen dem Ölsumpf (8) auf der Höhe des vorbestimmten Ölsumpfstands (24) und einer Verdichtungselement-Saugleitung (58) oder einem Verdichtungselement-Saugabschnitt erstreckt.
  11. Verfahren zum Betreiben eines Kältekreislaufs (78), umfassend:
    Bereitstellen von mindestens einem Verdichter mit niedrigerem Saugdruck (80) und mindestens einem Verdichter mit höherem Saugdruck (82), die in Reihe verbunden und derart konfiguriert sind, dass, wenn der Ölsumpfstand des Verdichters mit niedrigerem Saugdruck (80) geringer als sein vorbestimmter Ölsumpfstand (24) ist, seine Ölzirkulationsrate stets niedriger als die Ölzirkulationsrate des Verdichters mit höherem Saugdruck (82) ist und dass, wenn der Ölsumpfstand des Verdichters mit niedrigerem Saugdruck (80) seinen vorbestimmten Ölsumpfstand übersteigt, seine Ölzirkulationsrate stets höher als die Ölzirkulationsrate des Verdichters mit höherem Saugdruck (82) ist,
    Betreiben eines Verdichtungselements (10) jedes Verdichters (80, 82) derart, dass ein Kältemittelstrom (20) eines gasförmigen Kältemittels, das eine Menge von Öl befördert, durch eine Einlassöffnung (6), das Verdichtungselement (10) und eine Auslassöffnung (18) jedes Verdichters (80, 82) zirkuliert und dass sich ein Teil des durch das gasförmige Kältemittel beförderten Öls in einem Ölsumpf (8) jedes Verdichters (80, 82) sammelt,
    Leiten von Öl aus dem Ölsumpf (8) in dem Verdichter mit niedrigerem Saugdruck (80) zu dem Kältemittelstrom (20) und somit zu dem stromabwärts verbundenen Verdichter mit höherem Saugdruck (82), wenn das Öl in dem Ölsumpf (8) einen vorbestimmten Ölsumpfstand (24) übersteigt, und dadurch Erreichen eines selbstregulierenden Ausgleichs von Öl zwischen dem Verdichter mit niedrigerem Saugdruck (80) und dem Verdichter mit höherem Saugdruck (82).
EP08773413.3A 2008-06-12 2008-06-12 Kältezyklus und betriebsverfahren dafür Active EP2283284B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2008/004734 WO2009149726A1 (en) 2008-06-12 2008-06-12 Compressor for a refrigeration cycle, refrigeration cycle and method for operating the same

Publications (2)

Publication Number Publication Date
EP2283284A1 EP2283284A1 (de) 2011-02-16
EP2283284B1 true EP2283284B1 (de) 2018-09-12

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US (1) US20110081254A1 (de)
EP (1) EP2283284B1 (de)
CN (1) CN101999064A (de)
DK (1) DK2283284T3 (de)
WO (1) WO2009149726A1 (de)

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CN103282729B (zh) * 2011-01-14 2015-09-30 开利公司 制冷系统和用于操作制冷系统的方法
FR2981739B1 (fr) 2011-10-20 2018-03-02 Danfoss Commercial Compressors Compresseur frigorifique
US9689386B2 (en) 2012-07-31 2017-06-27 Bitzer Kuehlmaschinenbau Gmbh Method of active oil management for multiple scroll compressors
US10634137B2 (en) * 2012-07-31 2020-04-28 Bitzer Kuehlmaschinenbau Gmbh Suction header arrangement for oil management in multiple-compressor systems
US9476414B2 (en) 2013-08-08 2016-10-25 Emerson Climate Technologies, Inc. Variable capacity reciprocating compressor
EP3066402B1 (de) 2013-11-04 2018-10-31 Carrier Corporation Kältekreislauf mit öltrennung
US9939179B2 (en) 2015-12-08 2018-04-10 Bitzer Kuehlmaschinenbau Gmbh Cascading oil distribution system
US10760831B2 (en) * 2016-01-22 2020-09-01 Bitzer Kuehlmaschinenbau Gmbh Oil distribution in multiple-compressor systems utilizing variable speed
CN107747544B (zh) * 2017-11-07 2019-07-09 苏州英华特涡旋技术有限公司 一种带均油管的压缩机、并联式压缩机组及均油方法

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Also Published As

Publication number Publication date
CN101999064A (zh) 2011-03-30
EP2283284A1 (de) 2011-02-16
DK2283284T3 (en) 2019-01-07
US20110081254A1 (en) 2011-04-07
WO2009149726A1 (en) 2009-12-17

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