EP0858559B1 - Compresseurs en spirale - Google Patents

Compresseurs en spirale Download PDF

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Publication number
EP0858559B1
EP0858559B1 EP96935148A EP96935148A EP0858559B1 EP 0858559 B1 EP0858559 B1 EP 0858559B1 EP 96935148 A EP96935148 A EP 96935148A EP 96935148 A EP96935148 A EP 96935148A EP 0858559 B1 EP0858559 B1 EP 0858559B1
Authority
EP
European Patent Office
Prior art keywords
chamber
compressor
economiser
pressure
scroll
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
EP96935148A
Other languages
German (de)
English (en)
Other versions
EP0858559A1 (fr
Inventor
Terence William Thomas Young
John Michael Roll
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.)
J&E Hall Ltd
Daikin Applied Americas Inc
Original Assignee
J&E Hall Ltd
AAF McQuay Inc
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
Priority claimed from GBGB9522516.5A external-priority patent/GB9522516D0/en
Priority claimed from GBGB9522517.3A external-priority patent/GB9522517D0/en
Priority claimed from GBGB9611261.0A external-priority patent/GB9611261D0/en
Application filed by J&E Hall Ltd, AAF McQuay Inc filed Critical J&E Hall Ltd
Priority claimed from PCT/GB1996/002677 external-priority patent/WO1997016647A1/fr
Publication of EP0858559A1 publication Critical patent/EP0858559A1/fr
Application granted granted Critical
Publication of EP0858559B1 publication Critical patent/EP0858559B1/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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
    • 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
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more pumps
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators

Definitions

  • This invention relates to a gas compressor of the kind using two intermeshed involute scrolls one of which remains stationary and the and the other of which orbits (but does not rotate) about the first scroll.
  • two gas chambers are first opened on diametrically opposite sides of the intermeshed scrolls, these chambers then grow in size until they are closed as "C" shaped pumping chambers which progress symmetrically on diametrically opposite sides of the centre of the stationary scroll towards that centre reducing in volume as they so progress.
  • the gas trapped in each chamber when it first closed has been compressed to a higher pressure and is released from the chamber to the exhaust duct of the compressor.
  • a compressor of this type will herein be referred to as a "scroll compressor” and a pair of gas chambers of one or more scroll compressors ganged together as described in the following paragraph will be referred to as "a scroll compressor arrangement of the kind specified”.
  • the compressor For operating a scroll compressor in accordance with the method of this invention it is necessary for the compressor to have at least two "C"-shaped pumping chambers of variable volume, each of which receives fluid to be compressed from a primary inlet when the respective pumping chamber has a first volume at least close to its maximum volume and each of which discharges compressed fluid from an outlet when the respective pumping chamber has a second volume which is less than said first volume, one of said pumping chambers having a secondary inlet open to the said one chamber when it has a third volume intermediate the first and second volumes after said chamber is closed off from its primary inlet but before the said one chamber opens to its outlet.
  • the invention seeks to improve the efficiency of a scroll compressor arrangement of the kind specified particularly in its application to refrigeration.
  • the method of the invention may be practised using two separate scroll compressors one of which provides the first "C"-shaped pumping chamber and the other compressor of which provides the second "C”-shaped pumping chamber.
  • the invention may also be applied to a composite compressor arrangement where the at least two "C"-shaped chambers of varying volume are provided in a common casing.
  • US-A-4 696 627 discloses a gas compressor according to the preamble of claim 1.
  • GB-A-1 501 474 describes a gas compressor in which the outlet of a first non-C-shaped pumping chamber is fed to a secondary inlet of a second non-C-shaped pumping chamber.
  • a gas compressor according to claim 1 is provided.
  • this aspect of the invention can be seen as a way of utilising a prior art economiser port of one of a pair of pumping chambers to improve performance without the need for any economiser vessel or system-derived side load.
  • the secondary inlet need not be in a fixed position in the said one pumping chamber and both pumping chambers in a scroll compressor arrangement of the kind specified can have such secondary inlets.
  • a method of impriving the efficiency of a pair of scroll refrigeration compressors according to claim 2 is provided.
  • the delivery pressure of the first scroll compressor is reduced to the intermediate pressure of the second scroll compressor so that the operational pressure ratio of the first scroll compressor is reduced with resulting improvements in both volumetric and isentropic efficiency.
  • refrigerant gas is entered into the second scroll compressor, via the intermediate port, during the compression of the low pressure suction gas in the second scroll compressor.
  • the invention is expected to offer advantages even over a conventional two-stage system.
  • a conventional two-stage system to operate efficiently there must be a considerable difference in the swept volumes of the two stages unless there is a considerable system side load.
  • both scroll compressors may be (but by the same token, if preferred, need not be) of the same swept volume.
  • a more flexible installation may be designed, with the option of shutting down one scroll compressor completely if system demand falls below 50% (in a two-compressor installation).
  • an alternating lead and lag compressor sequence may be operated if required.
  • the total compressor displacement required is greatly reduced when compared to a conventional two-stage system.
  • the system may be further refined by the use of an economiser facility (e.g. with a conventional economiser vessel or heat exchanger). Greater performance can be achieved in this mode.
  • an economiser facility e.g. with a conventional economiser vessel or heat exchanger. Greater performance can be achieved in this mode.
  • Figures 1 to 4 illustrate piston-in-cylinder pumping chambers for easier understanding of the inventive concept.
  • Figure 1 shows a prior art refrigeration multi-compressor system having two compressors with pumping chambers 10A and 10B, respectively, each having a primary inlet 11a, 11b, a secondary inlet (or economiser port) 12a, 12b and an outlet 13a, 13b.
  • the two primary inlets communicate with a common suction line 14 leading from the evaporator 16 of the system and the two outlets communicate with a common high pressure delivery line 15 leading to the upstream end of the condenser 17 of the system.
  • the expansion valve is shown at 18.
  • the intermediate ports 12a and 12b are connected to a vapour outlet 19a of an economiser vessel 19.
  • FIG. 2 shows a compressor arrangement in accordance with the invention.
  • the outlet 13a of chamber 10A is now connected to the intermediate inlet 12b of chamber 10B.
  • Both inlets 11a and 11b remain connected to a common suction line 14 but only outlet 13b now feeds the delivery line 15.
  • the intermediate port 12a is not used and this is the arrangement shown in Figure 2.
  • FIG. 3 shows a further compressor arrangement connected in accordance with the invention but with the addition of an economiser vessel 19.
  • the vapour outlet 19a from this economiser vessel is returned to the intermediate port 12a.
  • FIG. 4 shows a still further compressor arrangement connected in accordance with the invention but now with two economiser vessels 19A, 19B connected.
  • the vapour outlet from the first economiser vessel 19A operating at the higher saturation pressure, is returned to the intermediate port 12b, where it mixes with the flow from the discharge port 13a as it enters chamber 10B.
  • the vapour outlet from the second economiser vessel 19B is returned to the intermediate port 12a and flows into chamber 10A.
  • Unloading of the compressors 10A, 10B shown schematically in Figures 2, 3 and 4 can be undertaken in the normal way except that it is anticipated that the compression process in chamber 10A, pumping into the economiser port 12b, would be unloaded before the compression process in chamber 10B.
  • Figure 5 shows the diagram for a standard economised scroll compressor machine.
  • compression of a non-economised machine would normally progress along line 1-3, but when economiser flow is introduced at an intermediate pressure Pe then, provided the temperature of this gas from the economiser vessel is lower than the temperature of the gas in the "C"-shaped chamber at this point then the temperature within the compressor will fall to point 4, compression will then continue to point 5 to achieve the delivery pressure Pd. Desuperheating and condensing of the gas will then take place as shown by line to 5 to 6.
  • the liquid would pass through an expansion device where the pressure would be reduced to suction pressure Ps at point 10.
  • Figure 6 shows the pressure enthalpy diagram for a simple scroll compressor system operating in accordance with the method of the invention.
  • the compression process would normally progress along dashed line 1-4.
  • the compression process is divided into two "C"-shaped compression chambers such that the first compression chamber compresses over the entire required pressure range from suction pressure to delivery pressure, whereas the second compression chamber compresses over a reduced compression ratio (and thus with higher efficiency and reduced temperature) from suction pressure Ps to the pressure Pe at the economiser port of the first chamber, as shown by line 1-3.
  • the gas from this second "C"-shaped chamber is fed via the economiser port of the first chamber, into the first "C"-shaped chamber, where the two compression gas streams are combined.
  • the compression process in the first chamber progresses along line 1-2, which is less efficient than that achieved in the second chamber due to the gas leakage effects from the higher pressure ultimately achieved in this compression chamber.
  • the combined gas streams will then be further compressed in the first compression chamber to the final delivery pressure Pd at point 5.
  • the cycle continues with desuperheating and condensing taking place between 5 and 6, the pressure then being dropped from 6 to 7 and the liquid boiled off in the evaporator from 7 to 1.
  • the benefits are not shown by an increase in enthalpy change in the evaporator, but rather by an increase in mass flow through the evaporator together with an improvement in coefficient of performance (C.O.P.), which can not be represented in Figure 6.
  • Figure 7 also shows a further scroll compressor system operating in the manner of the invention, but with the addition of economising of the low compression ratio chamber.
  • the two gas flows are combined in the first "C"-shaped compression chamber from points 2 and 3, like the non-economised arrangement discussed above and compressed together to the final delivery pressure Pd at point 5.
  • the second "C"-shaped compression chamber combines the economising effect described previously.
  • desuperheating and condensing of the gas takes place between 5 and 6.
  • the liquid is then dropped in pressure to Pel at point 7 in the economiser vessel, where some liquid is boiled off and returned to the economiser port of the second compression chamber. This evaporation cools the remaining liquid in the economiser to point 8.
  • FIG. 7 again shows an open-flooded economiser vessel but it is equally possible to accomplish this economiser liquid cooling in an indirect heat exchanger where the liquid that is cooled is retained at the higher condensing pressure.
  • the beneficial effect of economising can be seen by the increase in enthalpy change in the evaporator shown by line 9-1 in this diagram when compared with line 7-1 of Figure 6.
  • Figure 8 shows another economised system operating in accordance with the method of the invention as shown in Figure 7, but with the addition of means for providing economising to the first "C"-shaped compression chamber.
  • This system operates similarly to that previously described (for Figure 7) except that after the gas from the second "C"-shaped compression chamber has been fed to the first compression chamber further economising is introduced in one of two possible ways. Either additional high pressure economiser flow is also introduced at the pressure where the two compression chambers are combined, from an additional economiser vessel, or alternatively economiser flow from the second high pressure economiser operating at pressure Pem is introduced at a later stage either by pressure regulation or an additional later economiser port into the first compression chamber. In this instance the beneficial effect of additional economising can be seen by the increase in enthalpy change in the evaporator shown by line 12-1 in this diagram when compared with 9-1 of Figure 7.
  • Prior art design single stage multi-scroll compressor systems combine the delivery ports from each of the scroll compressors into a common delivery line while the suction ports of the compressors are connected to a common suction line.
  • the suction line remains open to the suction ports of all the scroll compressors but the delivery ports of at least two of the compressors are now separated.
  • the first compressor can be piped up externally in the conventional fashion with the delivery connected to the condenser.
  • delivery gas from the second scroll compressor is taken to an economiser port provided on the first scroll compressor (the conventionally connected scroll compressor). If required, the economiser connection of the second scroll compressor may be used to provide a conventional economiser facility.
  • Unloading of scroll compressors connected in this way can be accomplished in the normal manner by unloading both compressor processes together.
  • the compression process pumping into the economiser port should be unloaded first, followed by unloading of the remaining compression process.
  • the or each economiser port need not be in a fixed position in the compressor casing, but may be capable of moving within the casing to maintain an optimum part-load economiser position.
  • Figure 9 shows twelve views of the intermeshing scrolls which create the pumping chambers of a scroll compressor, the stationary scroll being shown cross hatched at 20 and the orbiting scroll being shown unshaded at 21.
  • the twelve views represent three complete orbits of the two scrolls, one relative to the other, the four views in the upper row representing positions 90° apart during the first orbit, the second row representing four positions 90° apart during the second orbit and the bottom row, scroll positions at 90° intervals during the third orbit.
  • the inlet of the compressor opening to the outer periphery of the scrolls 20,21 there is no chamber available for filling with gas from the inlet in the first view in the top row but that two such chambers do begin to open between the first and the second views in the upper row.
  • the arrows 22,23 at the top and bottom of the second and third views in the upper row indicate gas at inlet pressure flowing into expanding chambers 24,25. (Shown dotted)
  • the third view in the upper row shows the development of two "C"-shaped chambers 24,25 which continue to expand and fill with gas from the inlet, whereas the last view in the upper row shows these chambers at maximum volume but now closed against further ingress of gas at inlet pressure.
  • the two "C"-shaped chambers 24,25 reduce in size as the orbital motion between the scrolls causes these pumping chambers to spiral in towards the centre of the stationary scroll 20.
  • the lowest row shows stages during the third orbit when the two chambers reach their minimum volume and discharge their compressed contents to the outlet of the compressor located in the centre of the stationary scroll.
  • chambers 24 and 25 can be isolated from each other during the compression process so that the discharge of gas at pressure Pe from one chamber can be fed to the economiser port of the other chamber, the invention could be practised with just two C-shaped chambers.
  • the pressure Pe shown in Figures 6 to 8 is in the range 30% to 70% of Pd, the delivery pressure from the compressor.
  • the compressor arrangement can be switched between standard operation and operation in accordance with this invention.

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

Claims (3)

  1. Compresseur de gaz ayant au moins deux chambres de pompage en forme de "C" (24, 25) de volume variable, chacune d'entre elles recevant un fluide à comprimer d'une entrée primaire (5) lorsque la chambre de pompage respective (24, 25) a un premier volume au moins proche de son volume maximal et chacune d'entre elles déchargeant du fluide comprimé par une sortie lorsque la chambre de pompage respective (24, 25) a un deuxième volume qui est inférieur audit premier volume, l'une (25) desdites chambres de pompage ayant une entrée secondaire (I) débouchant vers ladite première chambre (25) lorsqu'elle a un troisième volume intermédiaire entre les premier et deuxième volumes après que ladite chambre (25) a été coupée de son entrée primaire (S), mais avant que ladite première chambre s'ouvre vers sa sortie (D), caractérisé en ce que la sortie de l'autre chambre de pompage (24) est acheminée à l'entrée secondaire (I) de ladite première chambre de pompage (25), et deux compresseurs à volutes séparés (B, A) sont utilisés, un premier (B) formant la chambre en forme de C (25) et le second (A) formant l'autre chambre en forme de C (24).
  2. Procédé pour améliorer l'efficacité d'une paire de premier (A) et second (B) compresseurs de réfrigération à volutes, dont au moins le second (B) comprend un orifice intermédiaire (1), caractérisé en ce que la décharge du premier compresseur à volutes (A) est introduite dans l'orifice intermédiaire (1) du second compresseur à volutes à une pression correspondant à l'orifice intermédiaire (1) dans le processus de compression se produisant dans le second compresseur à volutes (B) .
  3. Procédé selon la revendication 2, caractérisé en ce que la pression de décharge du premier compresseur à volutes (A) se situe dans la plage de 30% à 70% de la pression de décharge du second compresseur à volutes (B).
EP96935148A 1995-11-02 1996-11-01 Compresseurs en spirale Expired - Lifetime EP0858559B1 (fr)

Applications Claiming Priority (9)

Application Number Priority Date Filing Date Title
GB9522517 1995-11-02
GB9522516 1995-11-02
GBGB9522516.5A GB9522516D0 (en) 1995-11-02 1995-11-02 Improvements in and relating to single screw compressors
GBGB9522517.3A GB9522517D0 (en) 1995-11-02 1995-11-02 Improved compressor arrangement
GBGB9611261.0A GB9611261D0 (en) 1996-05-30 1996-05-30 Improvements in and relating to scroll compressors
GB9611261 1996-05-30
WOPCT/GB96/02677 1996-11-01
PCT/GB1996/002677 WO1997016647A1 (fr) 1995-11-02 1996-11-01 Agencement de compresseur ameliore et son procede de fonctionnement
PCT/GB1996/002679 WO1997016649A1 (fr) 1995-11-02 1996-11-01 Compresseurs en spirale

Publications (2)

Publication Number Publication Date
EP0858559A1 EP0858559A1 (fr) 1998-08-19
EP0858559B1 true EP0858559B1 (fr) 2002-01-30

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP96935148A Expired - Lifetime EP0858559B1 (fr) 1995-11-02 1996-11-01 Compresseurs en spirale

Country Status (2)

Country Link
EP (1) EP0858559B1 (fr)
WO (1) WO1997016649A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10145587B2 (en) 2014-12-11 2018-12-04 Angelantoni Test Technologies S.R.L. Refrigeration device

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1501474A (en) * 1975-07-16 1978-02-15 Uniscrew Ltd Rotary compressors
JPS58124084A (ja) * 1982-01-21 1983-07-23 Toshiba Corp スクロ−ル形圧縮機
US4431388A (en) * 1982-03-05 1984-02-14 The Trane Company Controlled suction unloading in a scroll compressor
US4696627A (en) * 1985-08-15 1987-09-29 Nippondenso Co., Ltd. Scroll compressor
JPS6248979A (ja) * 1985-08-27 1987-03-03 Hitachi Ltd スクロ−ル圧縮機

Also Published As

Publication number Publication date
EP0858559A1 (fr) 1998-08-19
WO1997016649A1 (fr) 1997-05-09

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