EP0076716A1 - Refrigeration installation with multiple motor compressors - Google Patents

Refrigeration installation with multiple motor compressors Download PDF

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Publication number
EP0076716A1
EP0076716A1 EP82401687A EP82401687A EP0076716A1 EP 0076716 A1 EP0076716 A1 EP 0076716A1 EP 82401687 A EP82401687 A EP 82401687A EP 82401687 A EP82401687 A EP 82401687A EP 0076716 A1 EP0076716 A1 EP 0076716A1
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Prior art keywords
points
high pressure
pressure stage
stage
compressors
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German (de)
French (fr)
Inventor
Pierre Deman
Emile Sanzey
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FSB
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    • 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

Definitions

  • the present invention relates to a refrigeration installation with multi-compressors.
  • a known compound refrigeration unit 1 usually comprises, on the one hand, a low pressure moiocompressor 2 which sucks expanded refrigerant gas at the pressure Po from the points of use 3 at a single low evaporation temperature for example -38 ° C., the compresses to the pressure Pm and discharges it into an intermediate bottle 4 where the compressed refrigerant gas is desuperheated, and on the other hand a high pressure motor compressor 5 which sucks desuperheated refrigerant gas from the bottle 4, compresses it to the pressure Pk and discharges it into a condenser 6.
  • the condensed condenser coming from the condenser 6 accumulates in the form of liquid in a tank 7 and passes partly in a coil 8 arranged in the lower zone of the intermediate bottle 4, and partly through a pressure reducer 9 in the bottle 4 where, by evaporation, it desuperheats your vapors of compressed compressed refrigerant by the low pressure compressor 2, and under cools the liquid refrigerant current which borrows the coil 8 to go and relax through the pressure reducer 10 in the points of use 3 at a single low evaporation temperature -38 ° C for example .
  • a refrigeration installation produced according to the invention is a refrigeration installation with multi-compressors having in its refrigeration circuit, at least on the one hand a low pressure stage and a high pressure stage which have their own points of use and whose common suction collectors of the motor compressors are maintained at pressures, equal respectively to the evaporation pressures tl and t2 of the points of use of these two stages, the capacity and the number of the compressors of the low-pressure stage are provided to supply correctly with refrigerant the points of use specific to this stage, and the capacity and the number of compressors of the high pressure stage are determined to supply the points of use of these two stages correctly with refrigerant, the refrigerant gas discharged from the low pressure stage being admitted into the common suction manifold of the high pressure stage at the same time as the expanded refrigerant gas coming from the own points of use of this high pressure stage,
  • the compound refrigeration installation 11 comprises a low pressure stage 12 and a high pressure stage 13 having respectively points of use 14 at an evaporation temperature tl , equal to -38 ° C, and points of use 15 at an evaporation temperature t2, equal to -10 ° C.
  • the low pressure stage 12 comprises two motor compressors 16, 17 whose total capacity is sufficient to supply refrigerant to the points of use 14 while the high pressure stage comprises three motor compressors 18, 19, 20 whose total capacity is determined for supply the refrigeration points 14 and 15 of the two stages 12 and 13 correctly.
  • the common suction manifold 21 of the compressors 16, 17 of the low pressure stage is maintained at a pressure equal to the evaporation pressure - 38 ° C at the points of use 14.
  • the motor compressors 16 and 17 draw in expanded refrigerant gas coming from the points of use 14 and discharge it through their common discharge line 22 and an oil separator 23, into a common suction manifold 24 of the high pressure stage motor compressors 13.
  • the motor compressors 18, 19, 20 from the high pressure stage 13 suck in refrigerant gas being in their suction manifold 24 and discharge it through their common discharge pipe 25 and an oil separator 26, into a condenser 27.
  • the refrigerant gas condensed in the form of liquid passes from the condenser 27 into a reservoir 28 common to the two stages 12 and 13 which feeds under the same high pressure both the points of use 14 and 15 of these two stages.
  • a counter-current exchanger 29 is mounted between these two stages 12 and 13 for firstly under cooling the stream of liquid refrigerant supplying the points of use 14 of the low pressure stage 12 and secondly desuperheating the refrigerant gas discharged by the low pressure stage 12 into the suction manifold 24 of the high pressure stage 13.
  • the superheated expanded refrigerant gas coming from the points of use at evaporation temperature -10 ° C. is not cooled or desuperheated before to be vacuumed and compressed by motor compressors.
  • the casings of the compressors of the motor compressors 16 and 17 of the low pressure stage 12 are connected to each other by a large section pipe 32 whose dual function is to allow the oil to balance in the compressor crankcases and to have the same pressure in these crankcases.
  • the oil recovered by the oil separator 26 as well as gaseous refrigerant entrained by the oil are brought into an oil tank 33, the lower part of which is connected to the casings of the motor-compressors 18, 19, 20 by a pipe 34 and float devices 35, 36, 37 and the upper part is connected to the common suction manifold 24 of the compressors by a pipe 38 and a calibrated valve 39 which creates a pressure drop of approximately one bar for bringing the oil tank 33 to a pressure of one bar higher than the pressure in the casings of the motor compressors 18, 19, 20.
  • the oil in the tank 33 is thus brought under a pressure difference of one bar, in each one. of these casings through devices 35, 36, 37, the float of which maintains the oil at a preset level.
  • the compound refrigeration installation 40 comprises in its refrigeration circuit, on the one hand like that of the first example (FIG. 2) a low pressure stage 41 and a high pressure stage 42 mounted in compound with their own points of use 43, 44 whose evaporation temperatures are respectively -38 ° C and -10 ° C, and on the other hand by a second high pressure stage 45 having its own points of use whose evaporation temperature t3 of the order of -3 ° C to -8 ° C, t3 chosen in this example is equal to -6 ° C.
  • the low pressure stage 41 comprises two motor compressors 47, 48, a common suction manifold 49, an oil separator 50 and a common discharge line 51.
  • the first high pressure stage 42 comprises three motor compressors 52, 53, 54 and a common collector suction 55 which receives both refrigerant gas coming from its own points of use 44 and refrigerant gas discharged from the low pressure stage 41.
  • An exchanger 56 mounted between these two stages 41 for sub-cooling the liquid refrigerant supplying the points of use 43 of the low pressure stage 41 and desuperheating the refrigerant gas discharged from this low pressure stage and the expanded gas coming from the points of use 44 of this first high pressure stage 42 in the common suction manifold 55.
  • the second high pressure stage 45 comprises three motor compressors 57, 58, 59, a common suction manifold 60, independent of the suction manifold 55 of the first high pressure stage 42 and a common discharge line 61 for all the six motor compressors of these two high pressure stages 42 and 45.
  • the suction manifold 55 of the first high pressure stage 42 is maintained at a pressure equal to the evaporation pressure -10 ° C of its points of use 44 while the suction manifold 60 of the second high pressure stage 45 is maintained at a pressure equal to an evaporation pressure -6 ° C of its own points of use 46.
  • the refrigerant gas compressed by the motor compressors of the two high pressure stages 42, 45 is discharged through the common discharge pipe 61 and an oil separator 62 in a condenser 63 common to the three stages 41, 42, 45.
  • the refrigerant in the form of liquid from the condenser 63 accumulates in a reservoir 64 common to these three stages 41, 42, 45 before going to supply the points of use 43, 44, 46 respectively under the same high pressure.
  • a known independent refrigeration plant having points of use at an evaporation temperature of -10 ° C. or a refrigeration plant 11 of the first example illustrated in FIG. 2 can at its points of use 15 also supply points of use at a higher evaporation temperature t3 for example -5 ° C or -6 ° C.
  • a higher evaporation temperature t3 for example -5 ° C or -6 ° C.
  • Evaporation at -5 ° C brings a gain of around twenty percent in refrigeration efficiency at points of use at -5 ° C compared to evaporation at -10 ° C at points of use with valves at constant pressure to maintain -5 ° C evaporation in the evaporator.
  • the casings of the compressors of the low pressure stage 41 are also connected to each other, as in those of the first example, by a pipe of large section 65 so as to have in these crankcases have the same pressure and a preset oil level while in the high pressure stages 42, 45, the crankcases of the motor compressors are connected by float devices and a common line 66 to the lower part of an oil tank 67, the upper part of which is connected to the common suction manifold 55 of the high-pressure first stage motor-compressors 42, through a pipe 68 and a calibrated valve 69 which creates, like that in the first example, a pressure drop of approximately one bar for put the oil tank 67 at a pressure one bar higher than the pressure in the compressor housings.

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

Abstract

The installation has a low-pressure stage (12) and at least one high-pressure stage (13) mounted in a compound arrangement comprising on the one hand utilisation points (14, 15), specific to each of these stages and having evaporation temperatures which are respectively different, and on the other hand a refrigerating circuit feeding all these utilisation points with liquid refrigerant under the same high pressure, coming from a condensed refrigerant reservoir (28) which is common to these stages. <IMAGE>

Description

La présente invention concerne une installation frigorifique à multimotocompresseurs.The present invention relates to a refrigeration installation with multi-compressors.

Pour obtenir une basse température inférieure à -35°C environ, il est connu de subdiviser dans une centrale frigorifique, la compression en deux étages pour éviter des inconvénients d'un rapport de compression élevé dans un fonctionnement à un seul étage. Ces inconvénients sont aussi bien d'ordre thermodynamique que d'ordre constructif. En effet une chaleur de surchauffe élevée risque de conduire à une décomposition du médium de graissage et une grande différence de pression risque de compromettre l'étanchéité des clapets des motocompresseurs de la centrale. Cependant dans des centrales frigorifiques compounds ou à étages en cascade connues, existent fréquemment des points d'utilisation à une seule basse température d'évaporation. Dans une installation frigorifique à points d'utilisation à températures différentes d'évaporation réalisée selon des solutions connues, une telle centrale frigorifique compound est associée à d'autres centrales à circuits frigorifiques indépendants donnant respectivement des températures d'évaporation demandées. Il existe ainsi dans cette installation autant de circuits frigorifiques que de centrales associées et l'installation frigorifique réalisée selon ces solutions connues s'avère onéreuse aussi bien en coût de construction qu'en celui de fonctionnement.To obtain a low temperature below about -35 ° C, it is known to subdivide in a refrigeration plant, the compression into two stages to avoid the disadvantages of a high compression ratio in a single stage operation. These drawbacks are both thermodynamic and constructive. In fact, a high superheating heat risks leading to a breakdown of the lubrication medium and a large pressure difference risks compromising the tightness of the valves of the central compressors. However, in compound refrigeration plants or with known cascade stages, there are frequently points of use at a single low evaporation temperature. In a refrigeration installation with points of use at different evaporation temperatures carried out according to known solutions, such a compound refrigeration plant is associated with other plants with independent refrigeration circuits respectively giving requested evaporation temperatures. There are thus in this installation as many refrigeration circuits as associated plants and the refrigeration installation produced according to these known solutions proves to be expensive both in construction cost and in operating cost.

La présente invention ayant pour but d'éviter ces inconvénients, permet de réaliser une installation frigorifique à multimotocompresseurs, économique à points d'utilisation à températures différentes d'évaporation présentant un bon fonctionnement mécanique et un excellent rendement frigorifique. Selon l'invention une installation frigorifique à multimotocompresseurs, ayant un étage basse pression et au moins un étage haute pression, montés en compound comprend d'une part des points d'utilisation, propres à chacun de ces étages et à températures d'évaporation respectivement différentes, et d'autre part un circuit frigorifique alimentant l'ensemble de ces points d'utilisation, en réfrigérant liquide sous une même haute pression, issu d'un réservoir de réfrigérant condensé, commun à ces étages.The aim of the present invention is to avoid these drawbacks, which makes it possible to produce a multi-compressor refrigeration installation, economical at points of use at different evaporation temperatures, exhibiting good mechanical operation and excellent refrigeration efficiency. According to the invention a refrigeration installation with multi-compressor, having a stage low pressure and at least one high pressure stage, mounted as a compound comprises, on the one hand, points of use, specific to each of these stages and at respectively different evaporation temperatures, and on the other hand a refrigeration circuit supplying the all of these points of use, in liquid refrigerant under the same high pressure, coming from a condensed refrigerant tank, common to these stages.

Pour mieux faire comprendre l'invention, on décrit ci-après à titre indicatif un certain nombre d'exemples de réalisation illustrés par des dessins ci-annexés dont :

  • -la figure 1 représente un schéma d'une centrale frigorifique compound connue,
  • -la figure 2 représente une vue schématique d'un premier exemple de réalisation selon l'invention, d'une installation frigorifique compound, à points d'utilisation à températures différentes d'évaporation, et
  • -la figure 3 représente une vue schématique d'un deuxième exemple de réalisation selon l'invention d'une installation frigorifique compound à points d'utilisation à températures différentes d'évaporation.
To make the invention easier to understand, a certain number of embodiments are illustrated below by way of illustration, illustrated by the appended drawings, of which:
  • FIG. 1 represents a diagram of a known compound refrigeration plant,
  • FIG. 2 represents a schematic view of a first exemplary embodiment according to the invention, of a compound refrigeration installation, at points of use at different evaporation temperatures, and
  • FIG. 3 represents a schematic view of a second exemplary embodiment according to the invention of a compound refrigeration installation with points of use at different evaporation temperatures.

Une centrale frigorifique compound 1 connue comprend habituellement, d'une part un moiocompresseur basse pression 2 qui aspire du gaz réfrigérant détendu à la pression Po des points d'utilisation 3 à une seule basse température d'évaporation par exemple -38°C, le comprime jusqu'à la pression Pm et le refoule dans une bouteille intermédiaire 4 où le gaz refrigérant comprimé se désurchauffe, et d'autre part un motocompresseur haute pression 5 qui aspire du gaz réfrigérant désurchauffé de la bouteille 4, le comprime à la pression Pk et le refoule dans un condenseur 6. Le réfrigérant condensé venant du condenseur 6 s'accumule sous forme de liquide dans un réservoir 7 et passe en partie dans un serpentin 8 disposé dans la zone inférieure de la bouteille intermédiaire 4, et en partie à travers un détendeur 9 dans la bouteille 4 où, par évaporation, il désurchauffe tes vapeurs de réfrigérant comprimé refoulé par le motocompresseur basse pression 2, et sous refroidit le courant de réfrigérant liquide qui emprunte le serpentin 8 pour aller se détendre à travers le détendeur 10 dans les points d'utilisation 3 à une seule basse température d'évaporation -38°C par exemple.A known compound refrigeration unit 1 usually comprises, on the one hand, a low pressure moiocompressor 2 which sucks expanded refrigerant gas at the pressure Po from the points of use 3 at a single low evaporation temperature for example -38 ° C., the compresses to the pressure Pm and discharges it into an intermediate bottle 4 where the compressed refrigerant gas is desuperheated, and on the other hand a high pressure motor compressor 5 which sucks desuperheated refrigerant gas from the bottle 4, compresses it to the pressure Pk and discharges it into a condenser 6. The condensed condenser coming from the condenser 6 accumulates in the form of liquid in a tank 7 and passes partly in a coil 8 arranged in the lower zone of the intermediate bottle 4, and partly through a pressure reducer 9 in the bottle 4 where, by evaporation, it desuperheats your vapors of compressed compressed refrigerant by the low pressure compressor 2, and under cools the liquid refrigerant current which borrows the coil 8 to go and relax through the pressure reducer 10 in the points of use 3 at a single low evaporation temperature -38 ° C for example .

Selon une technique connue, pour réaliser une installation frigorifique à points d'utilisation à deux températures différentes d'évaporation par exemple -38°C et -10°C, on associe une centrale frigorifique compound 1 ci-dessus avec une autre centrale à circuit frigorifique indépendant, de type connu, non représentée donnant du froid à une seule température d'évaporation -lO°C. Un des grands inconvénients de cette solution connue est déjà rappelée dans un paragraphe précédent.According to a known technique, in order to produce a refrigeration installation with points of use at two different evaporation temperatures, for example -38 ° C and -10 ° C, a compound refrigeration plant 1 above is combined with another circuit plant independent refrigerator, of known type, not shown giving cold at a single evaporation temperature -10 ° C. One of the great drawbacks of this known solution is already recalled in a previous paragraph.

Une installation frigorifique réalisée selon l'invention, à points d'utilisation à températures différentes d'évaporation par exemple à deux basses températures d'évaporation tl et t2 avec tl inférieure à t2, est une installation frigorifique à multimotocompresseurs ayant dans son circuit frigorifique, au moins d'une part un étage basse pression et un étage haute pression qui ont leurs propres points d'utilisation et dont les collecteurs communs d'aspiration des motocompresseurs sont maintenus à des pressions, égales respectivement aux pressions d'évaporation tl et t2 des points d'utilisation de ces deux étages, la capacité et le nombre des motocompresseurs de l'étage basse pression sont prévus pour alimenter correctement en réfrigérant les points d'utilisation propres à cet étage, et la capacité et le nombre de motocompresseurs de l'étage haute pression sont déterminés pour alimenter correctement en réfrigérant les points d'utilisation de ces deux étages, le gaz réfrigérant refoulé de l'étage basse pression étant admis dans le collecteur commun d'aspiration de l'étage haute pression en même temps que le gaz réfrigérant détendu venant des points d'utilisation propres de cet étage haute pression, et d'autre part des dispositifs pour assurer un sous refroidissement du réfrigérant liquide alimentant les points d'utilisation de l'étage basse pression et une désurchauffe du gaz réfrigérant refoulé de l'étage basse pression pour que l'entrée de ce dernier dans le collecteur commun d'aspiration de l'étage haute pression maintienne la température du mélange gazeux qui s'y trouve à un niveau de désurchauffe souhaité.A refrigeration installation produced according to the invention, at points of use at different evaporation temperatures, for example at two low evaporation temperatures tl and t2 with tl less than t2, is a refrigeration installation with multi-compressors having in its refrigeration circuit, at least on the one hand a low pressure stage and a high pressure stage which have their own points of use and whose common suction collectors of the motor compressors are maintained at pressures, equal respectively to the evaporation pressures tl and t2 of the points of use of these two stages, the capacity and the number of the compressors of the low-pressure stage are provided to supply correctly with refrigerant the points of use specific to this stage, and the capacity and the number of compressors of the high pressure stage are determined to supply the points of use of these two stages correctly with refrigerant, the refrigerant gas discharged from the low pressure stage being admitted into the common suction manifold of the high pressure stage at the same time as the expanded refrigerant gas coming from the own points of use of this high pressure stage, and on the other hand devices for ensuring a sub-cooling of the liquid refrigerant supplying the points of use of the low pressure stage and a desuperheating of the refrigerant gas discharged from the low pressure stage so that the entry of the latter into the common suction manifold of the high pressure stage maintains the temperature of the gas mixture therein at a desired level of desuperheating.

Dans un premier exemple de réalisation de l'invention, illustré dans la figure 2, l'installation frigorifique compound 11 comprend un étage basse pression 12 et un étage haute pression 13 ayant respectivement des points d'utilisation 14 à une température d'évaporation tl, égale à -38°C, et des points d'utilisation 15 à une température d'évaporation t2, égale à -10°C.In a first embodiment of the invention, illustrated in FIG. 2, the compound refrigeration installation 11 comprises a low pressure stage 12 and a high pressure stage 13 having respectively points of use 14 at an evaporation temperature tl , equal to -38 ° C, and points of use 15 at an evaporation temperature t2, equal to -10 ° C.

L'étage basse pression 12 comprend deux motocompresseurs 16, 17 dont la capacité totale est suffisante pour alimenter en réfrigérant les points d'utilisation 14 tandis que l'étage haute pression comporte trois motocompresseurs 18, 19, 20 dont la capacité totale est déterminée pour alimenter correctement en réfrigérant les points d'utilisation 14 et 15 des deux étages 12 et 13. Le collecteur commun d'aspiration 21 des motocompresseurs 16, 17 de l'étage basse pression est maintenu à une pression égale à la pression d'évaporation -38°C des points d'utilisation 14. Les motocompresseurs 16 et 17 aspirent du gaz réfrigérant détendu venant des points d'utilisation 14 et le refoulent à travers leur conduite commune de refoulement 22 et un déshuileur 23, dans un collecteur commun d'aspiration 24 des motocompresseurs de l'étage haute pression 13. Le collecteur d'aspiration 24, maintenu à une pression égale à la pression d'évaporation -10°C des points d'utilisation 15, reçoit à la fois du gaz réfrigérant détendu venant de ces points d'utilisation 15 et du gaz réfrigérant refoulé de l'étage basse pression 12. Les motocompresseurs 18, 19, 20 de l'étage haute pression 13 aspirent du gaz réfrigérant se trouvant dans leur collecteur d'aspiration 24 et le refoulent à travers leur conduite commune de refoulement 25 et un déshuileur 26, dans un condenseur 27. Le gaz réfrigérant condensé sous forme de liquide passe du condenseur 27 dans un réservoir 28 commun aux deux étages 12 et 13 lequel alimente sous une même haute pression à la fois les points d'utilisation 14 et 15 de ces deux étages. Un échangeur 29 à contre courant est monté entre ces deux étages 12 et 13 pour d'une part sous refroidir le courant de réfrigérant liquide alimentant les points d'utilisation 14 de l'étage basse pression 12 et d'autre part désurchauffer le-gaz réfrigérant refoulé par l'étage basse pression 12 dans le collecteur d'aspiration 24 de l'étage haute pression 13. Dans cet échangeur 29, une partie du liquide réfrigérant venant du réservoir 28 traversant un détendeur 30 est injecté à contre courant dans le corps de l'échangeur 29 pour sous refroidir le courant de réfrigérant liquide allant de ce réservoir 28 aux points d'utilisation 14 à température d'évaporation -38°C tandis que le réfrigérant détendu dans le corps de l'échangeur 29 est injecté à travers une vanne 31 dans le courant de gaz réfrigérant refoulé par l'étage basse pression 12 et le désurchauffe à un niveau choisi avant son entrée dans le collecteur commun d'aspiration 24 de l'étage haute pression 13.The low pressure stage 12 comprises two motor compressors 16, 17 whose total capacity is sufficient to supply refrigerant to the points of use 14 while the high pressure stage comprises three motor compressors 18, 19, 20 whose total capacity is determined for supply the refrigeration points 14 and 15 of the two stages 12 and 13 correctly. The common suction manifold 21 of the compressors 16, 17 of the low pressure stage is maintained at a pressure equal to the evaporation pressure - 38 ° C at the points of use 14. The motor compressors 16 and 17 draw in expanded refrigerant gas coming from the points of use 14 and discharge it through their common discharge line 22 and an oil separator 23, into a common suction manifold 24 of the high pressure stage motor compressors 13. The suction manifold 24, maintained at a pressure equal to the evaporation pressure -10 ° C at the points of use 15, receives both ref gas rigorous relaxed coming from these points of use 15 and from the refrigerant gas discharged from the low pressure stage 12. The motor compressors 18, 19, 20 from the high pressure stage 13 suck in refrigerant gas being in their suction manifold 24 and discharge it through their common discharge pipe 25 and an oil separator 26, into a condenser 27. The refrigerant gas condensed in the form of liquid passes from the condenser 27 into a reservoir 28 common to the two stages 12 and 13 which feeds under the same high pressure both the points of use 14 and 15 of these two stages. A counter-current exchanger 29 is mounted between these two stages 12 and 13 for firstly under cooling the stream of liquid refrigerant supplying the points of use 14 of the low pressure stage 12 and secondly desuperheating the refrigerant gas discharged by the low pressure stage 12 into the suction manifold 24 of the high pressure stage 13. In this exchanger 29, part of the coolant coming from the reservoir 28 passing through a pressure reducer 30 is injected against the current into the body of the exchanger 29 in order to sub cool the current of liquid refrigerant going from this reservoir 28 to the points of use 14 at evaporation temperature -38 ° C while the expanded refrigerant in the body of the exchanger 29 is injected through a valve 31 into the stream of refrigerant gas discharged by the low pressure stage 12 and the desuperheating at a selected level before entering the common suction manifold 24 of the high pressure stage 13.

Il en résulte que le gaz détendu venant des points d'utilisation 15 propres à l'étage haute pression est également désurchauffé. Dans une comparaison entre deux installations frigorifiques de capacité équivalente dont l'une est une installation réalisée selon une technique connue consistant en un regroupement côte à côte d'une centrale compound à points d'utilisation à une température d'évaporation -38°C et d'une centrale à circuit frigorifique indépendant à points d'utilisation à température d'évaporation -10°C, et l'autre est une installation 11 réalisée selon l'invention décrite dans un paragraphe précédent, on remarque que grâce à une désurchauffe volontaire du gaz détendu venant des points d'utilisation 15 de l'étage haute pression 13 et du gaz refoulé de l'étage basse pression 12 de l'installation 11 une appréciable économie d'énergie dépensée est réalisée dans la production du froid dans ces points d'utilisation à températures d'évaporation -38°C et -10°C. En effet à cause de l'indépendance des circuits frigorifiques dans l'installation réalisée, selon la technique connue, le gaz réfrigérant détendu surchauffé venant des points d'utilisation à température d'évaporation -10°C n'est pas refroidi ou désurchauffé avant d'être aspiré et comprimé par des motocompresseurs.As a result, the expanded gas from the points of use 15 specific to the high pressure stage is also desuperheated. In a comparison between two refrigeration installations of equivalent capacity, one of which is an installation produced according to a known technique consisting of a side-by-side grouping of a compound power station with points of use at an evaporation temperature -38 ° C and of a power station with independent refrigeration circuit at points of use at evaporation temperature -10 ° C, and the other is an installation 11 produced according to the invention described in a previous paragraph, it is noted that thanks to a voluntary desuperheating expanded gas coming from the points of use 15 of the high pressure stage 13 and gas discharged from the low pressure stage 12 of the installation 11 an appreciable saving of energy expended is achieved in the production of cold in these points of use at evaporation temperatures -38 ° C and -10 ° C. Indeed, because of the independence of the refrigeration circuits in the installation carried out, according to the known technique, the superheated expanded refrigerant gas coming from the points of use at evaporation temperature -10 ° C. is not cooled or desuperheated before to be vacuumed and compressed by motor compressors.

Pour obtenir un bon fonctionnement mécanique par un graissage correct des motocompresseurs, dans l'installation 11 illustrée à la figure 2, les carters des compresseurs des motocompresseurs 16 et 17 de l'étage basse pression 12 sont reliés entre eux par une conduite de grosse section 32 dont la double fonction est de permettre à l'huile de s'équilibrer dans les carters des compresseurs et d'avoir dans ces carters une même pression. Dans l'étage haute pression 13 de l'installation 11, l'huile recupérée par le déshuileur 26 ainsi que du réfrigérant gazeux entraîné par l'huile sont amenés dans un réservoir d'huile 33 dont la partie inférieure est reliée aux carters des motocompresseurs 18, 19, 20 par une conduite 34 et des dispositifs à flotteur 35, 36, 37 et la partie supérieure est reliée au collecteur commun d'aspiration 24 des motocompresseurs par une conduite 38 et un clapet taré 39 qui crée une perte de charge de un bar environ pour mettre le réservoir d'huile 33 à une pression de un bar supérieure à la pression dans des carters des motocompresseurs 18, 19, 20. L'huile du réservoir 33 est ainsi amenée sous une différence de pression de un bar, dans chacun. de ces carters à travers des dispositifs 35, 36, 37 dont le flotteur assure un maintien de l'huile à un niveau préréglé.To obtain good mechanical operation by correct lubrication of the motor compressors, in the installation 11 illustrated in FIG. 2, the casings of the compressors of the motor compressors 16 and 17 of the low pressure stage 12 are connected to each other by a large section pipe 32 whose dual function is to allow the oil to balance in the compressor crankcases and to have the same pressure in these crankcases. In the high pressure stage 13 of the installation 11, the oil recovered by the oil separator 26 as well as gaseous refrigerant entrained by the oil are brought into an oil tank 33, the lower part of which is connected to the casings of the motor-compressors 18, 19, 20 by a pipe 34 and float devices 35, 36, 37 and the upper part is connected to the common suction manifold 24 of the compressors by a pipe 38 and a calibrated valve 39 which creates a pressure drop of approximately one bar for bringing the oil tank 33 to a pressure of one bar higher than the pressure in the casings of the motor compressors 18, 19, 20. The oil in the tank 33 is thus brought under a pressure difference of one bar, in each one. of these casings through devices 35, 36, 37, the float of which maintains the oil at a preset level.

Dans un deuxième exemple de réalisation de l'invention, schématiquement illustré à la figure 3, l'installation frigorifique compound 40 comprend dans son circuit frigorifique, d'une part comme celle du premier exemple (figure 2) un étage basse pression 41 et un étage haute pression 42 montés en compound avec leurs points d'utilisation propres 43, 44 dont les températures d'évaporation sont respectivement -38°C et -10°C, et d'autre part par un deuxième étage haute pression 45 ayant ses propres points d'utilisation dont la température d'évaporation t3 de l'ordre de -3°C à -8°C, t3 choisie dans cet exemple est égale à -6°C. L'étage basse pression 41 comprend deux motocompresseurs 47, 48, un collecteur commun d'aspiration 49, un déshuileur 50 et une conduite commune de refoulement 51. Le premier étage haute pression 42 comprend trois motocompresseurs 52, 53, 54 et un collecteur commun d'aspiration 55 qui reçoit à la fois du gaz réfrigérant venant de ses propres points d'utilisation 44 et du gaz réfrigérant refoulé de J'étage basse pression 41. Un échangeur 56 monté entre ces deux étages 41 pour sous refroidir le réfrigérant liquide alimentant les points d'utilisation 43 de l'étage basse pression 41 et désurchauffer le gaz réfrigérant refoulé de cet étage basse pression et du gaz détendu venant des points d'utilisation 44 de ce premier étage haute pression 42 dans le collecteur commun d'aspiration 55. Le deuxième étage haute pression 45 comprend trois motocompresseurs 57, 58, 59, un collecteur commun d'aspiration 60, indépendant du collecteur d'aspiration 55 du premier étage haute pression 42 et une conduite commune de refoulement 61 pour l'ensemble des six motocompresseurs de ces deux étages haute pression 42 et 45.In a second embodiment of the invention, schematically illustrated in FIG. 3, the compound refrigeration installation 40 comprises in its refrigeration circuit, on the one hand like that of the first example (FIG. 2) a low pressure stage 41 and a high pressure stage 42 mounted in compound with their own points of use 43, 44 whose evaporation temperatures are respectively -38 ° C and -10 ° C, and on the other hand by a second high pressure stage 45 having its own points of use whose evaporation temperature t3 of the order of -3 ° C to -8 ° C, t3 chosen in this example is equal to -6 ° C. The low pressure stage 41 comprises two motor compressors 47, 48, a common suction manifold 49, an oil separator 50 and a common discharge line 51. The first high pressure stage 42 comprises three motor compressors 52, 53, 54 and a common collector suction 55 which receives both refrigerant gas coming from its own points of use 44 and refrigerant gas discharged from the low pressure stage 41. An exchanger 56 mounted between these two stages 41 for sub-cooling the liquid refrigerant supplying the points of use 43 of the low pressure stage 41 and desuperheating the refrigerant gas discharged from this low pressure stage and the expanded gas coming from the points of use 44 of this first high pressure stage 42 in the common suction manifold 55. The second high pressure stage 45 comprises three motor compressors 57, 58, 59, a common suction manifold 60, independent of the suction manifold 55 of the first high pressure stage 42 and a common discharge line 61 for all the six motor compressors of these two high pressure stages 42 and 45.

Le collecteur d'aspiration 55 du premier étage haute pression 42 est maintenu à une pression égale à la pression d'évaporation -10°C de ses points d'utilisation 44 tandis que le collecteur d'aspiration 60 du deuxième étage haute pression 45 est maintenu à une pression égale à une pression d'évaporation -6°C de ses propres points d'utilisation 46. Le gaz réfrigérant comprimé par les motocompresseurs des deux étages haute pression 42, 45 est refoulé à travers la conduite commune de refoulement 61 et un déshuileur 62 dans un condenseur 63 commun aux trois étages 41, 42, 45.The suction manifold 55 of the first high pressure stage 42 is maintained at a pressure equal to the evaporation pressure -10 ° C of its points of use 44 while the suction manifold 60 of the second high pressure stage 45 is maintained at a pressure equal to an evaporation pressure -6 ° C of its own points of use 46. The refrigerant gas compressed by the motor compressors of the two high pressure stages 42, 45 is discharged through the common discharge pipe 61 and an oil separator 62 in a condenser 63 common to the three stages 41, 42, 45.

Le réfrigérant sous forme de liquide issu du condenseur 63 s'accumule dans un réservoir 64 commun à ces trois étages 41, 42, 45 avant d'aller alimenter sous une même haute pression respectivement les points d'utilisation 43, 44, 46.The refrigerant in the form of liquid from the condenser 63 accumulates in a reservoir 64 common to these three stages 41, 42, 45 before going to supply the points of use 43, 44, 46 respectively under the same high pressure.

Une centrale frigorifique indépendante connue ayant des points d'utilisation à une température d'évaporation -10°C ou une installation frigorifique 11 du premier exemple illustré dans la figure 2 peut au niveau de ses points d'utilisation 15 alimenter également des points d'utilisation à une température d'évaporation t3 plus élevée par exemple -5°C ou -6°C. En effet, d'après les courbes normales de rendement d'un compresseur frigorifique, une évaporation à -5°C par exemple par rapport à celle à -10°C amène, pour une même température de condensation, une appréciable augmentation de production calorifique de l'ordre d'une vingtaine de pourcents et seulement une relativement faible augmentation de l'énergie consommée de l'ordre d'une dizaine de pourcents. Une évaporation à -5°C apporte un gain d'une vingtaine de pourcents en rendement frigorifique sur des points d'utilisation à -5°C par rapport à une évaporation à -10°C sur des points d'utilisation comportant des vannes à pression constante pour maintenir dans l'évaporateur une évaporation -5°C.A known independent refrigeration plant having points of use at an evaporation temperature of -10 ° C. or a refrigeration plant 11 of the first example illustrated in FIG. 2 can at its points of use 15 also supply points of use at a higher evaporation temperature t3 for example -5 ° C or -6 ° C. Indeed, according to the normal efficiency curves of a refrigeration compressor, an evaporation at -5 ° C for example compared to that at -10 ° C brings, for the same condensation temperature, an appreciable increase in calorific production of the order of twenty percent and only a relatively small increase in the energy consumed of the order of ten percent. Evaporation at -5 ° C brings a gain of around twenty percent in refrigeration efficiency at points of use at -5 ° C compared to evaporation at -10 ° C at points of use with valves at constant pressure to maintain -5 ° C evaporation in the evaporator.

Pour obtenir un graissage correct des motocompresseurs dans l'installation frigorifique 40, les carters des compresseurs de l'étage basse pression 41 sont également reliés entre eux, comme dans ceux du premier exemple, par une conduite de grosse section 65 de manière à avoir dans ces carters une même pression et un niveau prérèglé d'huile tandis que dans les étages haute pression 42, 45, les carters des motocompresseurs sont reliés par des dispositifs à flotteur et une conduite commune 66 à la partie inférieure d'un réservoir d'huile 67 dont la partie supérieure est branchée au collecteur commun d'aspiration 55 des motocompresseurs du premier étage haute pression 42, à travers une conduite 68 et un clapet taré 69 qui crée comme celui dans le premier exemple une perte de charge de un bar environ pour mettre le réservoir d'huile 67 à une pression de un bar supérieure à la pression dans des carters des compresseurs.To obtain correct lubrication of the motor compressors in the refrigeration installation 40, the casings of the compressors of the low pressure stage 41 are also connected to each other, as in those of the first example, by a pipe of large section 65 so as to have in these crankcases have the same pressure and a preset oil level while in the high pressure stages 42, 45, the crankcases of the motor compressors are connected by float devices and a common line 66 to the lower part of an oil tank 67, the upper part of which is connected to the common suction manifold 55 of the high-pressure first stage motor-compressors 42, through a pipe 68 and a calibrated valve 69 which creates, like that in the first example, a pressure drop of approximately one bar for put the oil tank 67 at a pressure one bar higher than the pressure in the compressor housings.

Claims (6)

1. Installation frigorifique à multimotocompresseurs ayant un étage basse pression (12, 41) et au moins un étage haute pression (13, 42) montés en compound, caractérisée en ce qu'elle comprend d'une part des points d'utilisation (14, 15, 43, 44, 46), propres à chacun de ces étages et à températures d'évaporation respectivement différentes (tl, t2, t3), et d'autre part un circuit frigorifique alimentant l'ensemble de ces points d'utilisation en réfrigérant liquide sous une même haute pression, issu d'un réservoir de réfrigérant condensé (28, 64), commun à ces étages.1. Refrigeration installation with multi-compressors having a low pressure stage (12, 41) and at least one high pressure stage (13, 42) mounted as a compound, characterized in that it comprises, on the one hand, points of use (14 , 15, 43, 44, 46), specific to each of these stages and with respectively different evaporation temperatures (tl, t2, t3), and on the other hand a refrigeration circuit supplying all of these points of use in liquid refrigerant under the same high pressure, coming from a condensed refrigerant tank (28, 64), common to these stages. 2. Installation selon la revendication l, caractérisée en ce qu'elle comprend un circuit frigorifique ayant dans l'étage basse pression (12, 41) un collecteur commun d'aspiration (21, 49) des motocompresseurs (16, 17, 47, 48) recevant du gaz réfrigérant détendu venant des points d'utilisation (14, 43) de cet étage, et maintenu à une pression égale à la pression d'évaporation -38°C de ces points d'utilisation (14, 43) et dans l'étage haute pression (13, 42), un collecteur commun d'aspiration (24, 55) des motocompresseurs (18, 19, 20, 52, 53, 54), recevant à la fois du gaz réfrigérant détendu venant des points d'utilisation (15, 44) de cet étage (13, 42) et du gaz réfrigérant refoulé de l'étage basse pression (12, 41), et maintenu à une pression égale à la pression d'évaporation -10°C de ces points d'utilisation (15, 44).2. Installation according to claim l, characterized in that it comprises a refrigeration circuit having in the low pressure stage (12, 41) a common suction manifold (21, 49) of the compressors (16, 17, 47, 48) receiving expanded refrigerant gas coming from the points of use (14, 43) of this stage, and maintained at a pressure equal to the evaporation pressure -38 ° C of these points of use (14, 43) and in the high pressure stage (13, 42), a common suction manifold (24, 55) of the motor compressors (18, 19, 20, 52, 53, 54), receiving both expanded refrigerant gas coming from the points of use (15, 44) of this stage (13, 42) and of the refrigerant gas discharged from the low pressure stage (12, 41), and maintained at a pressure equal to the evaporation pressure -10 ° C these points of use (15, 44). 3. Installation selon l'une des revendications 1 et 2, caractérisée en ce qu'elle comprend dans son circuit frigorifique un deuxième étage haute pression (45) ayant avec le premier étage haute pression (42) une conduite commune de refoulement (61) pour les motocompresseurs (52, 53, 54, 57, 58, 59) un condenseur commun (63), un réservoir commun pour réfrigérant condensé (64) qui alimente sous une même haute pression en réfrigérant liquide l'ensemble des points d'utilisation (43, 44, 46) de l'étage basse pression (41) et des deux étages haute pression (42, 45), et un collecteur commun d'aspiration (60) pour les motocompresseurs du deuxième étage haute pression (45) recevant du gaz réfrigérant détendu des points d'utilisation (46) de cet étage (45) et maintenu à une pression égale à la pression d'évaporation t3 de ces derniers points d'utilisation (46).3. Installation according to one of claims 1 and 2, characterized in that it comprises in its refrigeration circuit a second high pressure stage (45) having with the first high pressure stage (42) a common discharge pipe (61) for motor compressors (52, 53, 54, 57, 58, 59) a common condenser (63), a common tank for condensed refrigerant (64) which supplies all the points of use under a same high pressure with liquid refrigerant (43, 44, 46) of the low pressure stage (41) and of the two high pressure stages (42, 45), and a common suction manifold (60) for the motor compressors of the second high pressure stage (45) receiving refrigerant gas expanded from the points of use (46) of this stage (45) and maintained at a pressure equal to the evaporation pressure t3 of these latter points of use (46). 4. Installation selon la revendication 3, caractérisée en ce qu'elle comprend un circuit frigorifique ayant dans le deuxième étage haute pression (45) des points d'utilisation (46) ayant une température d'évaporation de l'ordre de -3°C à -8°C.4. Installation according to claim 3, characterized in that it comprises a refrigeration circuit having in the second high pressure stage (45) points of use (46) having an evaporation temperature of the order of -3 ° C at -8 ° C. 5. Installation selon l'une des revendications 1 à 4, caractérisée en ce qu'elle comprend dans son circuit frigorifique un réservoir d'huile (33, 67) alimentant en huile les carters des motocompresseurs à travers des dispositifs à flotteurs (35, 36, 37) et un clapet taré (39, 69) créant une différence de pression entre ce réservoir d'huile (33, 67) et les carters de ces motocompresseurs.5. Installation according to one of claims 1 to 4, characterized in that it comprises in its refrigerating circuit an oil tank (33, 67) supplying oil to the casings of the motor compressors through float devices (35, 36, 37) and a calibrated valve (39, 69) creating a pressure difference between this oil tank (33, 67) and the casings of these motor-compressors. 6. Installation selon l'une des revendications 1 à 5, caractérisée en ce qu'elle comprend dans son circuit frigorifique un échangeur (29, 56) à contre courant pour sous refroidir le courant de réfrigérant liquide alimentant les points d'utilisation (14, 43) et désurchauffer le gaz réfrigérant refoulé de l'étage basse pression (12, 41) dans le collecteur d'aspiration (24, 55) de l'étage haute pression (13, 42) et du gaz détendu venant des points d'utilisation (15, 44) de cet étage haute pression (13, 42) dans ce collecteur d'aspiration (24, 55).6. Installation according to one of claims 1 to 5, characterized in that it comprises in its refrigerating circuit an exchanger (29, 56) against the current to sub cool the current of liquid refrigerant supplying the points of use (14 , 43) and desuperheat the refrigerant gas discharged from the low pressure stage (12, 41) in the suction manifold (24, 55) of the high pressure stage (13, 42) and the expanded gas coming from the points d use (15, 44) of this high pressure stage (13, 42) in this suction manifold (24, 55).
EP82401687A 1981-09-25 1982-09-16 Refrigeration installation with multiple motor compressors Withdrawn EP0076716A1 (en)

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FR8118136 1981-09-25
FR8118136A FR2513747A1 (en) 1981-09-25 1981-09-25 MULTIMOTOCOMPRESSOR REFRIGERATION SYSTEM

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EP1050723A2 (en) * 1999-05-05 2000-11-08 Linde Aktiengesellschaft Refrigeration system and method for operating a refrigeration system
WO2006022829A1 (en) * 2004-08-09 2006-03-02 Carrier Corporation Co2 refrigeration circuit with sub-cooling of the liquid refrigerant against the receiver flash gas and method for operating the same
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EP2021703A2 (en) * 2006-06-01 2009-02-11 Carrier Corporation Multi-stage compressor unit for a refrigeration system
EP3064866A1 (en) * 2015-03-04 2016-09-07 Heatcraft Refrigeration Products LLC Modulated oversized compressor configuration for flash gas bypass in a carbon dioxide refrigeration system

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Cited By (14)

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Publication number Priority date Publication date Assignee Title
FR2557962A1 (en) * 1984-01-11 1985-07-12 Copeland Corp TWO-STAGE, FLEXIBLE OPERATION AND HIGH EFFICIENCY REFRIGERATION DEVICE
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WO2007016944A1 (en) * 2005-08-08 2007-02-15 Carrier Corporation Refrigeration system comprising multiple refrigeration consumer devices
EP2021703A2 (en) * 2006-06-01 2009-02-11 Carrier Corporation Multi-stage compressor unit for a refrigeration system
EP2021703A4 (en) * 2006-06-01 2012-02-15 Carrier Corp Multi-stage compressor unit for a refrigeration system
EP3064866A1 (en) * 2015-03-04 2016-09-07 Heatcraft Refrigeration Products LLC Modulated oversized compressor configuration for flash gas bypass in a carbon dioxide refrigeration system
CN105937815A (en) * 2015-03-04 2016-09-14 西克制冷产品有限责任公司 Modulated oversized compressors configuration for flash gas bypass in a carbon dioxide refrigeration system
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ES8308627A1 (en) 1983-09-16
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ES515937A0 (en) 1983-09-16

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