EP3051233B1 - Hybrid compression heat pumping cycles based plants - Google Patents

Hybrid compression heat pumping cycles based plants Download PDF

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EP3051233B1
EP3051233B1 EP15075005.7A EP15075005A EP3051233B1 EP 3051233 B1 EP3051233 B1 EP 3051233B1 EP 15075005 A EP15075005 A EP 15075005A EP 3051233 B1 EP3051233 B1 EP 3051233B1
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coil
pressure
heat
low
compartment
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EP3051233A1 (en
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Mihail-Dan Staicovici
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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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/02—Compression-sorption machines, plants, or systems

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  • the present invention is destined to production of cooling and heating for industrial, agricultural, or household purposes, achieved by plants supplied with sink, heat sink and electrical, or mechanical power sources, on one side, and with sources suffering the useful cooling and heating effects, respectively, on the other side.
  • the deep cooling applications e.g. ((-40) - (-70))°C
  • the compressor of the cooling plant to compress refrigerants with very low densities, or equally, with very high specific volumes. This leads to very high volumes to be compressed, especially to high capacity applications, and ultimately to an important increase of the compressor clearance diagram.
  • ammonia for instance, the most utilized refrigerant in the low temperature applications needed in industry, and of the ammonia compressors.
  • ammonia/water absorption plant For deep cooling applications, the ammonia/water absorption plant is mostly indicated, because it uses absorption instead of mechanical compression in order to handle the high specific volume refrigerants, but, unfortunately, this technology needs quite high temperature heat supply, e.g. (150 - 180)°C and low sink sources, e.g. (15 - 18)°C, which not always are available.
  • WO2013/021323 discloses a hybrid compression based cooling plant incorporating the synergy between two known technologies based compartments, a 1 st compartment of mechanical vapor compression, including a compressor, a low pressure evaporator, a high pressure condenser, an expansion valve and an adequate working fluid and a 2 nd compartment of absorption, including on one side a refrigerant-absorbent mixture loop, consisting of a high pressure generator-rectifier, a low pressure absorber, a pump, an expansion valve and a recovery heat exchanger and on the other side a high pressure condenser, an expansion valve and a low pressure evaporator.
  • the absorber or the condenser of the absorption compartment is thermally coupled to the evaporator of the mechanical vapor compression compartment.
  • the generator-rectifier of the absorption compartment is thermally coupled to the condenser of the mechanical vapor compression compartment.
  • a first object of the present invention is to find a technical solution which is avoiding the compressor operation with high discharge gas temperature in deep cooling and high temperature heating applications.
  • a second object of the present invention is to keep the plants high effectiveness in cooling and heating applications, similar to the COP of TWRC and TTRC methods based plants, achieved in same operation conditions.
  • a third object of the present invention is to enable an absorption plant to run in cooling and heating applications without to depend on the heat and low sink sources availability.
  • the invention provides a hybrid compression based cooling plant according to claims 1 and 3.
  • the invention achieves the first object by introducing a new cooling and heating technology based plants, those with hybrid compression. Similar to the mechanical vapor compression plants, the hybrid compression plants need only two external supplying sources, a sink source and an electrical or mechanical source. Within the frame of hybrid compression plant achievement, the mechanical vapor compression plant, implied classically usually alone in the cooling and heating task fulfilment, is replaced in our case by the synergy between two known technologies based compartments, of mechanical vapor compression and of absorption. These two compartments act together in such a way that the first compartment plays the role of a sink and heat or just heat supplier for the latter, while the latter is performing the useful task of cooling or heating, respectively. According to the cooling or heating hybrid compression plant achievement, the compressor operation with high discharge gas temperatures is avoided this time because it works with much lower compression ratios as compared to those obtained by TWRC and TTRC based plants, therefore with much lower discharge gas temperatures.
  • the invention achieves the second object as low compression ratios lead to diminished specific mechanical work consumption of the compressor, therefore to higher COP in cooling and heating for same operating parameters.
  • the invention achieves the third object because the mechanical vapor compression compartment is running with just the external electrical or mechanical energy input and the external sink source supply, available to most applications, and in this case the hybrid compression plant is capable to provide with internal sink and heat or only with internal heat sources the absorption plant, in order to ensure its operation, that is the cooling or heating task fulfilment, in an independent way of the existence or not of an external heat supply.
  • the hybrid compression cooling plant represented in Figure 1 .
  • the compressor 1 is compressing an adequate refrigerant gas from the evaporator 2 low pressure and temperature p E and T E , respectively, till the condenser 3 high pressure and temperature, p c and T c , respectively, with T c > T E , according to the adiabatic process a-b.
  • the evaporator 2 constant pressure and temperature evaporation process d-a is supplied by a heating source, provided by a 1 st intermediary heat transfer fluid circulated through the evaporator coil 4, while the condenser 3 constant pressure and temperature condensation process b-c is supplied by a cooling source, provided by a 2 nd intermediary heat transfer fluid circulated through condenser coil 5.
  • the refrigerant condensate is expanded from the high condenser pressure p c till the low evaporator pressure p E by means of the expansion valve 6, following the isenthalpic process c-d, in order to close the mechanical vapor compression cycle based compartment.
  • the operation of the single-stage absorption cooling cycle based compartment is secondly described, following the same Figure 1 .
  • the refrigerant-absorbent working combination is covering the solution loop consisting of a low-pressure absorber 7, a high-pressure generator rectifier 8, which is generating almost pure refrigerant vapor, a pump 9, pumping the rich refrigerant-absorbent solution pressure from that of the absorber 7 low pressure value till that of the generator-rectifier 8 high pressure value, an expansion valve 10, decreasing the poor refrigerant-absorbent solution pressure from that of the generator-rectifier 8 high value till that of the absorber 7 low value and a recovery heat exchanger 11, which is subcooling the poor solution coming of the generator-rectifier 8 by means of the rich solution superheating, coming of absorber 7.
  • the absorber 7 absorption process is supplied by a cooling source, provided by the 1 st intermediary heat transfer fluid circulated through absorber coil 12, while the generator-rectifier 8 generation process is supplied by a heating source, provided by the 2 nd intermediary heat transfer fluid circulated through the generator-rectifier coil 13.
  • T M is the temperature of the coabsorbent cycle mixing point M, which in our case is slightly higher than the evaporator 2 temperature T E , that is T E ⁇ T M .
  • the absorbent exiting the generator-rectifier 8 has a temperature T GO , which is slightly higher or equal to the external sink source temperature, T ss and slightly lower than the condenser 3 temperature, T c , that is T ss ⁇ T GO ⁇ T c .
  • T GO the external sink source temperature
  • T c the condenser 3 temperature
  • the refrigerant condensate is subcooled in a recovery way in the subcooler 16, it is expanded in the expansion valve 17 from the condenser 14 high pressure till the absorber 7 low pressure, it enters the low pressure absorption plant evaporator 18, where it is producing the useful effect of cooling the source to be cooled 19, the non-evaporated refrigerant enters the absorber 7 and the refrigerant vapor it is exiting the evaporator 18 by means of the pipe 20, it is superheated in the subcooler 16 and it is absorbed in the low pressure absorber 7, in order to close the absorption cycle compartment.
  • the source 19 is cooled till a temperature close to that of absorption plant evaporator 18 or desorber inlet, TDI, noted like this according to the coabsorbent technology.
  • the heat released by absorber 7 and condenser 14 of the absorption plant compartment is taken over by the evaporator 2 by means of the 1 st intermediary heat transfer fluid which is covering a closed loop consisting of the evaporator coil 4, pipe 21, pump 22, absorber coil 12, pipe 23, condenser coil 15, and pipe 24, in order to close the absorber 7 and condenser 14 internal sink source circuit.
  • the heat supplied to the generator-rectifier 8 is provided by the condenser 3 by means of the 2 nd intermediary heat transfer fluid which is covering a closed loop consisting of the condenser coil 5, pipe 25, pump 26, generator-rectifier coil 13, pipe 27 and the heat exchanger 28, in which coil 29 and the 2 nd intermediary heat transfer fluid is cooled finally till a temperature close to the sink source temperature T ss by means of the external sink source 30, in order to close the generator-rectifier 8 heating circuit and the hybrid compression plant operation.
  • the generator-rectifier 8 benefits of a compressor 31 mounted on the pipe 32, which is sucking its generated-rectified refrigerant, it compresses it from the generation process intermediary pressure, higher than the low pressure of the absorber 7 and evaporator 18 absorption compartment bottom, till the high pressure of the condenser 14, and it delivers it to the condenser 14, in order to be cooled and condensed till the temperature T M , with T M > T E .
  • the hybrid operation which the generator-rectifier 8 is provided with, benefits, in fact, to a certain extent the hybrid compression plant behavior, because the absorption compartment generation takes place to lower generation temperature, comparatively, and for that two positive consequences hold true, firstly the generator-rectifier 8 consumes less rectification heat during the generation-rectification process, and secondly, the mechanical vapor compression burden decreases as the compression ratio of the compressor 1 diminishes correspondingly, because T c , hence p c , decrease, comparatively, with good effects on COP increase and its clearance diagram decrease.
  • the absorption compartment operates not with just the single-stage absorption cooling cycle construction, but with a double-effect absorption cooling cycle structure, based on a thermal cascade of two single-stage absorption cooling subcycles subcompartments, consisting of the 2 nd subcycle subcompartment, labeled with index "2", operating to higher generation temperature and numbered identically as to the absorption cooling cycle construction of Figure 1 and the 1 st subcycle subcompartment, labeled with index "1" and operating to lower generation temperature due to the recovery of its generator-rectifier of the heat released by the absorber 7 of the 2 nd subcycle subcompartment.
  • the refrigerant-absorbent working combination of the 1 st absorption subcycle subcompartment is covering the solution loop consisting of a low pressure absorber 33, a high pressure generator-rectifier 34, generating almost pure refrigerant vapor, a pump 35, pumping the rich refrigerant-absorbent solution from the absorber 33 low pressure, equal to absorber 7 low pressure, till the generator-rectifier 34 high pressure, equal to the generator-rectifier 8 high pressure, an expansion valve 36, decreasing the poor refrigerant-absorbent solution pressure from that of the generator-rectifier 34 high value till that of the absorber 33 low value and a recovery heat exchanger 37, which is subcooling the poor solution coming of the generator-rectifier 34 by means of the rich solution superheating, coming of absorber 33.
  • the absorber 33 absorption process is supplied by a cooling source, provided by the 1 st intermediary heat transfer fluid circulated through absorber coil 38, while the generator-rectifier 34 generation process is supplied by a heating source, provided by a 3 rd intermediary heat transfer fluid circulated through the generator-rectifier coil 39.
  • the absorbent exiting the absorber 33 is cooled till is cooled till a temperature T M 1 , which is the internal sink temperature of the 1 st absorption subcycle subcompartment and according to the hybrid compression plant achievement is much lower than the external sink temperature T ss and T M 2 , that is T ss >> T M 2 >> T M 1 , but slightly higher than the evaporator 2 temperature, T E , that is T E ⁇ T M 1 .
  • the absorbent exiting the generator-rectifier 34 has a temperature T GO 1 , which is slightly lower than the internal sink temperature, T M 2 , of the 2 nd absorption subcycle compartment, T GO 1 ⁇ T M 2 .
  • T M 2 internal sink temperature
  • T GO 1 the internal sink temperature
  • T M 2 the internal sink temperature
  • T GO 1 the internal sink temperature
  • T M 2 the internal sink temperature
  • T GO 1 the refrigerant vapor coming of the generator-rectifier 34 is condensed in the high pressure condenser 40 and cooled till the same temperature T M 1 by the 1 st intermediary heat transfer fluid circulated through the condenser coil 41.
  • the refrigerant condensate is subcooled in a recovery way in the subcooler 42, it is expanded in the expansion valve 43 from the condenser 40 high pressure till the absorber 33 low pressure, it enters the low pressure absorption plant evaporator 44, where it is producing the useful effect of cooling the source to be cooled 45, the non-evaporated refrigerant enters the absorber 33 and the refrigerant vapor is exiting the evaporator 44 by means of the pipe 46, it is superheated in the subcooler 42 and it is absorbed in the low pressure absorber 33, in order to close the absorption cycle compartment.
  • the source 45 is cooled till a temperature close to that of evaporator 44, T DI .
  • the heat released by absorber 33 and condenser 40 is taken over by the evaporator 2 by means of the 1 st intermediary heat transfer fluid which is covering a closed loop consisting of the evaporator coil 4, pipe 21, pump 22, absorber coil 38, pipe 23, condenser coil 15, condenser coil 41 and pipe 24.
  • the heat released by the absorber 7 is supplied to the generator-rectifier 34 by the 3 rd intermediary heat transfer fluid which is covering a closed loop consisting of the absorber coil 12, pump 47, pipe 48, generator-rectifier coil 39 and pipe 49, in order to close the hybrid compression plant operation.
  • the hybrid compression heating plant represented in Figure 4
  • the single-stage mechanical vapor compression cycle based compartment is the same as all similar compartments described in Figures 1-3 .
  • the absorption cycle based compartment is different and will be described next, following the same Figure 4 .
  • this compartment bases on an Osenbrück cycle construction and operation, consisting, on one side, of a refrigerant-absorbent solution loop which includes a low pressure desorber 50, a high pressure resorber 51, a pump 52, pumping the absorbent from the desorber 50 low pressure till the resorber 51 high pressure, an expansion valve 53, decreasing the absorbent pressure from that of the resorber 51 high value till that of the desorber 50 low value and a recovery heat exchanger 54, superheating the poor absorbent prior to enter the resorber 51 through the subcooling of the rich absorbent prior to enter the desorber 50, and, on the other side, a compressor 55, mounted on the pipe 56 and sucking the low pressure vapor desorbed by the desorber 50 and compressing it till the resorber 51 high pressure, where it is resorbed.
  • a refrigerant-absorbent solution loop which includes a low pressure desorber 50, a high pressure resorber 51,
  • the useful resorption process heat release is supplied by a cooling source, provided by a 1 st intermediary heat transfer fluid circulated through the resorber coil 57, while the desorber 50 desorption process is supplied by a heating source, provided by a 2 nd intermediary heat transfer fluid circulated through the desorber coil 58.
  • the desorber 50 absorbent outlet temperature T DO is smaller than the condenser temperature, T C , that is T C > T DO
  • the heating useful effect temperature, T h,u is lower than the resorber 51 absorbent actual inlet temperature, T RI . that is T RI > T h,u .
  • the condenser 3 condensing heat is supplying the desorber 50 by means of the 2 nd intermediary heat transfer fluid which is covering a closed loop consisting of the condenser coil 5, pipe 59, pump 60, desorber coil 58 and pipe 61, in order to close the desorber 50 heating loop.
  • the evaporator 2 is supplied with heat from a depleted or low grade heat source by means of a 3 rd intermediary heat transfer fluid which is covering a closed loop consisting of the evaporator coil 4, pipe 62, heat exchanger 63, heat exchanger coil 64, pump 65, pipe 66, enabling the low grade heat source 67 to supply with heat the coil 64, in order to close the evaporator 2 heating loop.
  • the evaporator temperature T E is smaller than the low grade source temperature, T ss , that is T E ⁇ T ss .
  • the usefully heated fluid loop is supplied with heat coming from the resorber 51, by means of the 1 st intermediary heat transfer fluid which is covering a closed loop consisting of the resorber coil 57, pipe 68, heat exchanger 69, enabling the resorber heat to be transferred from heat exchanger coil 70 to the usefully heated fluid 71, and pump 72 mounted on the pipe 73, in order to close the resorber 51 heating loop.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Description

  • The present invention is destined to production of cooling and heating for industrial, agricultural, or household purposes, achieved by plants supplied with sink, heat sink and electrical, or mechanical power sources, on one side, and with sources suffering the useful cooling and heating effects, respectively, on the other side.
  • Firstly, a recent author research, see Staicovici, 2014, has shown that the coefficient of performance, in short COP, of cooling and heating plants based on mechanical vapor compression can be greatly improved if the discharge gas superheating were capitalized on using essentially two methods, i.e. the Thermal-to-Work Recovery Compression, in short TWRC, and the Thermal-to-Thermal Recovery Compression, in short TTRC. The application of these two methods leads to an increase of the deep, industrial cooling COP by 50 to 100 percent, and more, and that of heat pumps up to 30 percent, as compared to the COP of the existing heat pumping equipment. In spite of this outstanding effectiveness increase, the two methods, already applied by some big compressor manufacturers, are confronted with a real problem, that of compressor operation with high discharge gas temperature, especially in the deep cooling and higher temperature heating, e.g. (150 - 180)°C, which causes greasing oil premature decay, mechanical stress, etc.
  • Secondly, the deep cooling applications, e.g. ((-40) - (-70))°C, and lower, mostly desired in the food industry, for example, are requiring the compressor of the cooling plant to compress refrigerants with very low densities, or equally, with very high specific volumes. This leads to very high volumes to be compressed, especially to high capacity applications, and ultimately to an important increase of the compressor clearance diagram. It is the case of ammonia, for instance, the most utilized refrigerant in the low temperature applications needed in industry, and of the ammonia compressors. For deep cooling applications, the ammonia/water absorption plant is mostly indicated, because it uses absorption instead of mechanical compression in order to handle the high specific volume refrigerants, but, unfortunately, this technology needs quite high temperature heat supply, e.g. (150 - 180)°C and low sink sources, e.g. (15 - 18)°C, which not always are available. The document WO2013/021323 discloses a hybrid compression based cooling plant incorporating the synergy between two known technologies based compartments, a 1st compartment of mechanical vapor compression, including a compressor, a low pressure evaporator, a high pressure condenser, an expansion valve and an adequate working fluid and a 2nd compartment of absorption, including on one side a refrigerant-absorbent mixture loop, consisting of a high pressure generator-rectifier, a low pressure absorber, a pump, an expansion valve and a recovery heat exchanger and on the other side a high pressure condenser, an expansion valve and a low pressure evaporator. By means of a first intermediary heat transfer circuit the absorber or the condenser of the absorption compartment is thermally coupled to the evaporator of the mechanical vapor compression compartment. By means of a 2nd intermediary heat transfer circuit the generator-rectifier of the absorption compartment is thermally coupled to the condenser of the mechanical vapor compression compartment.
  • A first object of the present invention is to find a technical solution which is avoiding the compressor operation with high discharge gas temperature in deep cooling and high temperature heating applications.
  • A second object of the present invention is to keep the plants high effectiveness in cooling and heating applications, similar to the COP of TWRC and TTRC methods based plants, achieved in same operation conditions.
  • A third object of the present invention is to enable an absorption plant to run in cooling and heating applications without to depend on the heat and low sink sources availability.
  • In order to achieve the objects set out above, the invention provides a hybrid compression based cooling plant according to claims 1 and 3.
  • The invention achieves the first object by introducing a new cooling and heating technology based plants, those with hybrid compression. Similar to the mechanical vapor compression plants, the hybrid compression plants need only two external supplying sources, a sink source and an electrical or mechanical source. Within the frame of hybrid compression plant achievement, the mechanical vapor compression plant, implied classically usually alone in the cooling and heating task fulfilment, is replaced in our case by the synergy between two known technologies based compartments, of mechanical vapor compression and of absorption. These two compartments act together in such a way that the first compartment plays the role of a sink and heat or just heat supplier for the latter, while the latter is performing the useful task of cooling or heating, respectively. According to the cooling or heating hybrid compression plant achievement, the compressor operation with high discharge gas temperatures is avoided this time because it works with much lower compression ratios as compared to those obtained by TWRC and TTRC based plants, therefore with much lower discharge gas temperatures.
  • The invention achieves the second object as low compression ratios lead to diminished specific mechanical work consumption of the compressor, therefore to higher COP in cooling and heating for same operating parameters.
  • The invention achieves the third object because the mechanical vapor compression compartment is running with just the external electrical or mechanical energy input and the external sink source supply, available to most applications, and in this case the hybrid compression plant is capable to provide with internal sink and heat or only with internal heat sources the absorption plant, in order to ensure its operation, that is the cooling or heating task fulfilment, in an independent way of the existence or not of an external heat supply.
    • According to present invention, the hybrid compression running in cooling and heating mode benefits of a compressor operation with much lower discharge gas temperatures, avoiding in this way the greasing oil premature decay, compressor premature wear, mechanical stress, etc.;
    • According to present invention, the hybrid compression plant benefits of an operation with higher COP in cooling and heating mode, as compared to the classic equipment, saving primary energy and protecting the environment;
    • According to present invention, the hybrid compression plant benefits of an independent operation of its absorption compartment with respect to the existence or not of an external heat supply;
    • According to present invention, the hybrid compression plant is mostly indicated to be employed in deep cooling applications, for using its absorption based compartment instead of a mechanical vapor compression unit in order to handle low temperature-high specific volume refrigerants the compressor clearance diagram results small, even in high capacity achievements;
    • According to present invention, given the hybrid compression plant is capable to provide the absorption compartment with internal low sink and heat temperature sources, e.g. (0 - (-35))°C and (30 - 45)°C, respectively, in order to ensure its operation, the plant absorption equipment results with diminished complexity, that is its rectification device can be very small, or even can be eliminated from the scheme, in case of deep cooling and volatile absorbent, e.g. ammonia-water, applications.
  • The invention is described by the following figures which represent examples of invention achievements:
    • Figure 1- Representation in the p-h and log p-1/T diagrams of a hybrid compression cooling plant using a single-stage mechanical vapor compression cycle based compartment and a single-stage absorption cooling cycle based compartment;
    • Figure 2 - Representation in the p-h and log p-1/T diagrams of a hybrid compression cooling plant using a single-stage mechanical vapor compression cycle based compartment and a single-stage hybrid absorption cooling cycle based compartment;
    • Figure 3 - Representation in the p-h and log p-1/T diagrams of a hybrid compression cooling plant using a single-stage mechanical vapor compression cycle based compartment and a double-effect absorption cooling cycle based compartment;
    • Figure 4 - Representation in the p-h and log p-1/T diagrams of a hybrid compression heating plant using a single-stage mechanical vapor compression cycle based compartment and an Osenbrück cycle based compartment.
  • Firstly, the hybrid compression cooling plant, represented in Figure 1, will be described. We begin with the operation of the single-stage mechanical vapor compression cycle based compartment, working in cogeneration of cooling and heating. The compressor 1 is compressing an adequate refrigerant gas from the evaporator 2 low pressure and temperature pE and TE, respectively, till the condenser 3 high pressure and temperature, pc and Tc, respectively, with Tc > TE, according to the adiabatic process a-b. The evaporator 2 constant pressure and temperature evaporation process d-a is supplied by a heating source, provided by a 1st intermediary heat transfer fluid circulated through the evaporator coil 4, while the condenser 3 constant pressure and temperature condensation process b-c is supplied by a cooling source, provided by a 2nd intermediary heat transfer fluid circulated through condenser coil 5. The refrigerant condensate is expanded from the high condenser pressure pc till the low evaporator pressure pE by means of the expansion valve 6, following the isenthalpic process c-d, in order to close the mechanical vapor compression cycle based compartment. The operation of the single-stage absorption cooling cycle based compartment is secondly described, following the same Figure 1. The refrigerant-absorbent working combination is covering the solution loop consisting of a low-pressure absorber 7, a high-pressure generator rectifier 8, which is generating almost pure refrigerant vapor, a pump 9, pumping the rich refrigerant-absorbent solution pressure from that of the absorber 7 low pressure value till that of the generator-rectifier 8 high pressure value, an expansion valve 10, decreasing the poor refrigerant-absorbent solution pressure from that of the generator-rectifier 8 high value till that of the absorber 7 low value and a recovery heat exchanger 11, which is subcooling the poor solution coming of the generator-rectifier 8 by means of the rich solution superheating, coming of absorber 7. The absorber 7 absorption process is supplied by a cooling source, provided by the 1st intermediary heat transfer fluid circulated through absorber coil 12, while the generator-rectifier 8 generation process is supplied by a heating source, provided by the 2nd intermediary heat transfer fluid circulated through the generator-rectifier coil 13. The absorbent exiting the absorber 7 is cooled till a temperature TM, which is the cycle internal sink temperature and according to the hybrid compression plant achievement is much lower than the external sink temperature Tss , that is Tss ≫ TM , Within the frame of the coabsorbent technology, including the absorption technology as a particular case, Staicovici, 2014, TM is the temperature of the coabsorbent cycle mixing point M, which in our case is slightly higher than the evaporator 2 temperature TE, that is TE < TM. The absorbent exiting the generator-rectifier 8 has a temperature TGO, which is slightly higher or equal to the external sink source temperature, Tss and slightly lower than the condenser 3 temperature, Tc, that is Tss ≤ TGO < Tc. The refrigerant vapor coming of the generator-rectifier 8 is condensed in the high pressure absorption plant condenser 14 and cooled till the same temperature TM by the 1st intermediary heat transfer fluid circulated through the absorption plant condenser coil 15. The refrigerant condensate is subcooled in a recovery way in the subcooler 16, it is expanded in the expansion valve 17 from the condenser 14 high pressure till the absorber 7 low pressure, it enters the low pressure absorption plant evaporator 18, where it is producing the useful effect of cooling the source to be cooled 19, the non-evaporated refrigerant enters the absorber 7 and the refrigerant vapor it is exiting the evaporator 18 by means of the pipe 20, it is superheated in the subcooler 16 and it is absorbed in the low pressure absorber 7, in order to close the absorption cycle compartment. The source 19 is cooled till a temperature close to that of absorption plant evaporator 18 or desorber inlet, TDI, noted like this according to the coabsorbent technology. The heat released by absorber 7 and condenser 14 of the absorption plant compartment is taken over by the evaporator 2 by means of the 1st intermediary heat transfer fluid which is covering a closed loop consisting of the evaporator coil 4, pipe 21, pump 22, absorber coil 12, pipe 23, condenser coil 15, and pipe 24, in order to close the absorber 7 and condenser 14 internal sink source circuit. The heat supplied to the generator-rectifier 8 is provided by the condenser 3 by means of the 2nd intermediary heat transfer fluid which is covering a closed loop consisting of the condenser coil 5, pipe 25, pump 26, generator-rectifier coil 13, pipe 27 and the heat exchanger 28, in which coil 29 and the 2nd intermediary heat transfer fluid is cooled finally till a temperature close to the sink source temperature Tss by means of the external sink source 30, in order to close the generator-rectifier 8 heating circuit and the hybrid compression plant operation.
  • Secondly, concerning the hybrid compression cooling plant represented in Figure 2, its construction and operation are identical to those of the hybrid compression cooling plant represented in Figure 1, except those concerning the absorption compartment generator-rectifier 8 which is provided with a hybrid construction and operation. Indeed, in this case, the generator-rectifier 8 benefits of a compressor 31 mounted on the pipe 32, which is sucking its generated-rectified refrigerant, it compresses it from the generation process intermediary pressure, higher than the low pressure of the absorber 7 and evaporator 18 absorption compartment bottom, till the high pressure of the condenser 14, and it delivers it to the condenser 14, in order to be cooled and condensed till the temperature TM, with TM > TE. In spite of an additional electrical or mechanical power consumed by the compressor 31, the hybrid operation, which the generator-rectifier 8 is provided with, benefits, in fact, to a certain extent the hybrid compression plant behavior, because the absorption compartment generation takes place to lower generation temperature, comparatively, and for that two positive consequences hold true, firstly the generator-rectifier 8 consumes less rectification heat during the generation-rectification process, and secondly, the mechanical vapor compression burden decreases as the compression ratio of the compressor 1 diminishes correspondingly, because Tc, hence pc , decrease, comparatively, with good effects on COP increase and its clearance diagram decrease.
  • Thirdly, concerning the hybrid compression cooling plant represented in Figure 3, although its construction and operation are principally the same as those of the hybrid compression plant represented in Figure 1, there are however comparative differences with respect to the absorption compartment structure. Indeed, this time the absorption compartment operates not with just the single-stage absorption cooling cycle construction, but with a double-effect absorption cooling cycle structure, based on a thermal cascade of two single-stage absorption cooling subcycles subcompartments, consisting of the 2nd subcycle subcompartment, labeled with index "2", operating to higher generation temperature and numbered identically as to the absorption cooling cycle construction of Figure 1 and the 1st subcycle subcompartment, labeled with index "1" and operating to lower generation temperature due to the recovery of its generator-rectifier of the heat released by the absorber 7 of the 2nd subcycle subcompartment. The differences in construction and operation of the hybrid compression plant represented in Figure 3 are described next. In the graphical representation of the absorption subcycles construction, forming the thermal cascade, 7 items are overlapping, which reason for these have been over-numbered, for the sake of clarity and simplicity of the layout. The refrigerant-absorbent working combination of the 1st absorption subcycle subcompartment is covering the solution loop consisting of a low pressure absorber 33, a high pressure generator-rectifier 34, generating almost pure refrigerant vapor, a pump 35, pumping the rich refrigerant-absorbent solution from the absorber 33 low pressure, equal to absorber 7 low pressure, till the generator-rectifier 34 high pressure, equal to the generator-rectifier 8 high pressure, an expansion valve 36, decreasing the poor refrigerant-absorbent solution pressure from that of the generator-rectifier 34 high value till that of the absorber 33 low value and a recovery heat exchanger 37, which is subcooling the poor solution coming of the generator-rectifier 34 by means of the rich solution superheating, coming of absorber 33. The absorber 33 absorption process is supplied by a cooling source, provided by the 1st intermediary heat transfer fluid circulated through absorber coil 38, while the generator-rectifier 34 generation process is supplied by a heating source, provided by a 3rd intermediary heat transfer fluid circulated through the generator-rectifier coil 39. The absorbent exiting the absorber 33 is cooled till is cooled till a temperature T M1, which is the internal sink temperature of the 1st absorption subcycle subcompartment and according to the hybrid compression plant achievement is much lower than the external sink temperature Tss and T M2 , that is Tss >> T M2 >> T M1 , but slightly higher than the evaporator 2 temperature, TE, that is TE < T M1 . The absorbent exiting the generator-rectifier 34 has a temperature T GO1, which is slightly lower than the internal sink temperature, T M2 , of the 2nd absorption subcycle compartment, T GO1 < T M2 . The refrigerant vapor coming of the generator-rectifier 34 is condensed in the high pressure condenser 40 and cooled till the same temperature T M1 by the 1st intermediary heat transfer fluid circulated through the condenser coil 41. The refrigerant condensate is subcooled in a recovery way in the subcooler 42, it is expanded in the expansion valve 43 from the condenser 40 high pressure till the absorber 33 low pressure, it enters the low pressure absorption plant evaporator 44, where it is producing the useful effect of cooling the source to be cooled 45, the non-evaporated refrigerant enters the absorber 33 and the refrigerant vapor is exiting the evaporator 44 by means of the pipe 46, it is superheated in the subcooler 42 and it is absorbed in the low pressure absorber 33, in order to close the absorption cycle compartment. The source 45 is cooled till a temperature close to that of evaporator 44, TDI. The heat released by absorber 33 and condenser 40 is taken over by the evaporator 2 by means of the 1st intermediary heat transfer fluid which is covering a closed loop consisting of the evaporator coil 4, pipe 21, pump 22, absorber coil 38, pipe 23, condenser coil 15, condenser coil 41 and pipe 24. The heat released by the absorber 7 is supplied to the generator-rectifier 34 by the 3rd intermediary heat transfer fluid which is covering a closed loop consisting of the absorber coil 12, pump 47, pipe 48, generator-rectifier coil 39 and pipe 49, in order to close the hybrid compression plant operation.
  • In a fourth place, the hybrid compression heating plant, represented in Figure 4, will be described. The single-stage mechanical vapor compression cycle based compartment is the same as all similar compartments described in Figures 1-3. The absorption cycle based compartment is different and will be described next, following the same Figure 4. Thermodynamically, this compartment bases on an Osenbrück cycle construction and operation, consisting, on one side, of a refrigerant-absorbent solution loop which includes a low pressure desorber 50, a high pressure resorber 51, a pump 52, pumping the absorbent from the desorber 50 low pressure till the resorber 51 high pressure, an expansion valve 53, decreasing the absorbent pressure from that of the resorber 51 high value till that of the desorber 50 low value and a recovery heat exchanger 54, superheating the poor absorbent prior to enter the resorber 51 through the subcooling of the rich absorbent prior to enter the desorber 50, and, on the other side, a compressor 55, mounted on the pipe 56 and sucking the low pressure vapor desorbed by the desorber 50 and compressing it till the resorber 51 high pressure, where it is resorbed. In our case, the useful resorption process heat release is supplied by a cooling source, provided by a 1st intermediary heat transfer fluid circulated through the resorber coil 57, while the desorber 50 desorption process is supplied by a heating source, provided by a 2nd intermediary heat transfer fluid circulated through the desorber coil 58. The desorber 50 absorbent outlet temperature TDO is smaller than the condenser temperature, TC, that is TC > TDO, while the heating useful effect temperature, Th,u , is lower than the resorber 51 absorbent actual inlet temperature, TRI. that is TRI > Th,u. The condenser 3 condensing heat is supplying the desorber 50 by means of the 2nd intermediary heat transfer fluid which is covering a closed loop consisting of the condenser coil 5, pipe 59, pump 60, desorber coil 58 and pipe 61, in order to close the desorber 50 heating loop. The evaporator 2 is supplied with heat from a depleted or low grade heat source by means of a 3rd intermediary heat transfer fluid which is covering a closed loop consisting of the evaporator coil 4, pipe 62, heat exchanger 63, heat exchanger coil 64, pump 65, pipe 66, enabling the low grade heat source 67 to supply with heat the coil 64, in order to close the evaporator 2 heating loop.
  • The evaporator temperature TE is smaller than the low grade source temperature, Tss, that is TE < Tss. Finally, the usefully heated fluid loop is supplied with heat coming from the resorber 51, by means of the 1st intermediary heat transfer fluid which is covering a closed loop consisting of the resorber coil 57, pipe 68, heat exchanger 69, enabling the resorber heat to be transferred from heat exchanger coil 70 to the usefully heated fluid 71, and pump 72 mounted on the pipe 73, in order to close the resorber 51 heating loop.
    • REFERENCES
    1. 1. Staicovici M. D., 2014, Coabsorbent and Thermal Heat Recovery Compression Heat Pumping Technologies. Berlin-Heidelberg: Springer Verlag, 2014.

Claims (3)

  1. Hybrid compression based cooling plant, incorporating the synergy between two known technologies based compartments, including
    1. a 1st compartment of mechanical vapor compression, including
    • a first compressor (1),
    • a first low-pressure evaporator (2),
    • a first high-pressure condenser (3),
    • a first expansion valve (6) and
    • an adequate working fluid and
    2. a 2nd compartment of absorption, including
    - on one side a refrigerant-absorbent mixture loop, including
    • a high-pressure generator-rectifier (8),
    • a low-pressure absorber (7),
    • a first pump (9),
    • a second expansion valve (10) and
    • a recovery heat exchanger (11) and
    - on the other side including
    • a second high-pressure condenser (14),
    • a refrigerant condensate subcooler (16),
    • a third expansion valve (17) and
    • a second low-pressure evaporator (18),
    wherein
    the 1st compartment further comprising for operation two external supplying sources, a sink source (30) and an electrical or mechanical source, is being capable to accomplish simultaneously two tasks, a first task, of being the internal sink source provider for the 2nd compartment, by taking over at the same time the heat released by the low-pressure absorber (7) and by the second high-pressure condenser (14) of the absorption compartment by means of the first low-pressure evaporator (2) of the mechanical vapor compression compartment, with the help of a 1st intermediary heat transfer fluid, covering a first closed loop, consisting of
    • a first low-pressure evaporator coil (4), releasing to the first low-pressure evaporator (2) the heat rejected by the first low-pressure absorber (7) and by the second high-pressure condenser (14),
    • a low-pressure absorber coil (12), taking over the heat released by the low-pressure absorber (7),
    • a second high-pressure condenser coil (15), serially connected with said low-pressure absorber coil (12) and taking over the heat released by the second high-pressure condenser (14),
    • a second pump (22), to pump the 1st intermediary heat transfer fluid in the first closed loop,
    • a first pipe (21), interconnecting said first low-pressure evaporator coil (4), said second pump (22) and said low-pressure absorber coil (12),
    • a second pipe (23), interconnecting said low-pressure absorber coil (12) and said second high-pressure condenser coil (15), and
    • a third pipe (24), interconnecting said second high-pressure condenser coil (15) and said first low-pressure evaporator coil (4), and
    a second task, of being the internal heat source provider for the high-pressure generator-rectifier (8) of the absorption compartment by means of the first high-pressure condenser (3) of the mechanical vapor compression compartment, with the help of a 2nd intermediary heat transfer fluid, covering a second closed loop consisting of
    • a first high-pressure condenser coil (5), taking over the heat released by the first high-pressure condenser (3) in order to be released to the generator-rectifier (8) and finally to a heat exchanger (28),
    • a generator-rectifier coil (13), serially connected with said first condenser coil (5) and taking over the part of the heat released by the first high-pressure condenser (3) in order to supply with heat source the high-pressure generator-rectifier (8),
    • the heat exchanger (28), enabling the final part of the heat released by the first high-pressure condenser (3) be released to the said sink source (30) by means of its primary coil (29) of the heat exchanger (28),
    • a third pump (26), to pump the 2nd intermediary heat transfer fluid in the second closed loop,
    • a fourth pipe (25), interconnecting said first high-pressure condenser coil (5), third pump (26) and the said generator-rectifier coil (13),
    • and a fifth pipe (27), interconnecting said generator-rectifier coil (13), said primary coil (29) and said first high-pressure condenser coil (5),
    in such a way that the 2nd compartment performs the useful task of cooling independently of the existence of an external heat source.
  2. Hybrid compression based cooling plant, according to claim 1, wherein the first compartment of mechanical vapor compression is provided with thermal-to-work recovery compression (TWRC) or thermal-to-thermal recovery compression (TTRC) type or is a hybrid compression based heating plant type.
  3. Hybrid compression based heating plant, incorporating the synergy between two known technologies based compartments, including
    1. a 1st compartment of mechanical vapor compression, including
    • a first compressor (1),
    • a first low-pressure evaporator (2),
    • a first high-pressure condenser (3),
    • a first expansion valve (6) and
    • an adequate working fluid and
    2. a 2nd compartment of absorption, as for example of Osenbrück type, including
    - on one side a refrigerant-absorbent mixture loop, including
    • a high-pressure resorber (51), including a resorber coil (57),
    • a low-pressure desorber (50),
    • a first pump (52),
    • a second expansion valve (53) and
    • a first recovery heat exchanger (54) and
    - on the other side
    • a second compressor (55) on a fifth pipe (56),
    wherein
    the 1st compartment further comprising for operation two external supplying sources, a heat-sink source (67) and an electrical or mechanical source, is being capable to accomplish simultaneously two tasks, a first task, of extracting heat by a second heat exchanger (63) from said heat-sink source (67) by means of a second heat exchanger coil (64) by means of a 3rd intermediary heat transfer fluid which is covering subsequently a closed loop consisting of
    • a first low-pressure evaporator coil (4), releasing the extracted heat from the said heat-sink source (67) to the first low-pressure evaporator (2),
    • a second pump (65), to pump the 3rd intermediary heat transfer fluid in the closed loop,
    • a first pipe (62), connecting said first low-pressure evaporator coil (4) with said heat exchanger coil (64), and
    • a second pipe (66), connecting the said heat exchanger coil (64) with said first low-pressure evaporator coil (4), and
    a second task, of upgrading the heat extracted from said heat-sink source (67) for being the 2nd compartment heat source by means of a 2nd intermediary heat transfer fluid, covering a closed loop consisting of
    • a first high-pressure condenser coil (5), taking over the heat released by the said first high-pressure condenser (3) for supplying the desorber (50) by means of a desorber coil (58),
    • a third pump (60), to pump the 2nd intermediary heat transfer fluid in the said closed loop,
    • a third pipe (59), connecting said first high-pressure condenser coil (5) with said third pump (60), and
    • a fourth pipe (61), connecting said desorber coil (58) with said first high-pressure condenser coil (5),
    in such a way that the 2nd compartment is enabled to perform the useful task by
    - firstly, supplying said high-pressure resorber (51) with refrigerant coming from said desorber (50), with the help of the second compressor (55), and
    - secondly, to extract the heat coming from the high-pressure resorber (51) with said resorber coil (57), by means of a 1st intermediary heat transfer fluid, covering a closed loop consisting of said resorber coil (57), and of
    • a third heat exchanger (69) with a third heat exchanger coil (70), enabling the high-pressure resorber (51) to transfer the heat from the said third heat exchanger coil (70) to a usefully heated fluid (71),
    • a fourth pump (72), to pump the 1st intermediary heat transfer fluid in the closed loop,
    • a sixth pipe (73), connecting said third heat exchanger coil (70) with said resorber coil (57), and
    • a seventh pipe (68), connecting said resorber coil (57) with the third heat exchanger coil (70).
EP15075005.7A 2015-01-29 2015-01-29 Hybrid compression heat pumping cycles based plants Active EP3051233B1 (en)

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Publication number Priority date Publication date Assignee Title
EP4177540A1 (en) * 2021-11-08 2023-05-10 Mihail-Dan Staicovici Mother & father hybrid compression for working and heating

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WO2018067818A1 (en) * 2016-10-05 2018-04-12 Johnson Controls Technology Company Heat pump for a hvac&r system

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AU533300B2 (en) * 1980-04-17 1983-11-17 Matsushita Electric Industrial Co., Ltd. Compressor control in compression absorption hybrid refrigeration plant
ITTO20110732A1 (en) * 2011-08-05 2013-02-06 Innovation Factory S C A R L HEAT PUMP SYSTEM AND METHOD OF COOLING AND / OR HEATING ACTIVATED THROUGH THIS SYSTEM
DE102013210177A1 (en) * 2013-05-31 2014-12-04 Siemens Aktiengesellschaft Cooling system and cooling process for use in high-temperature environments

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