WO2009145278A1 - Système de réfrigération hybride - Google Patents

Système de réfrigération hybride Download PDF

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Publication number
WO2009145278A1
WO2009145278A1 PCT/JP2009/059817 JP2009059817W WO2009145278A1 WO 2009145278 A1 WO2009145278 A1 WO 2009145278A1 JP 2009059817 W JP2009059817 W JP 2009059817W WO 2009145278 A1 WO2009145278 A1 WO 2009145278A1
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Prior art keywords
refrigerant
refrigeration cycle
condenser
compressor
evaporator
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PCT/JP2009/059817
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English (en)
Japanese (ja)
Inventor
繁 小山
ビデュット バラン シャハ
アヌトシュ チャクラボルティ
カンダダイ シュリニヴァッサン
憲 桑原
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国立大学法人九州大学
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Priority to JP2010514541A priority Critical patent/JPWO2009145278A1/ja
Publication of WO2009145278A1 publication Critical patent/WO2009145278A1/fr

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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

Definitions

  • the present invention relates to a hybrid refrigeration system in which a vapor compression refrigeration cycle and an adsorption refrigeration cycle are combined.
  • JP-A-11-63719 Patent Document 1
  • JP-A-11-83235 Patent Document 2
  • JP-A-2005-308355 Patent Document 3
  • a compressor, a condenser, an expander, and Combining a vapor compression refrigeration cycle comprising an evaporator with an adsorption refrigeration cycle having at least a pair of adsorbers that alternately adsorb refrigerant and alternately desorb the adsorbed refrigerant to improve the performance of the adsorption refrigeration cycle Technology is disclosed.
  • Japanese Patent Laid-Open No. 11-63719 Japanese Patent Laid-Open No. 11-83235 JP 2005-308355 A
  • the main focus is on improving the performance of the adsorption refrigeration cycle.
  • the adsorption refrigeration cycle is used. There has been little consideration of using.
  • An object of the present invention is to provide a hybrid refrigeration system that can reduce mechanical work in a vapor compression refrigeration cycle.
  • the hybrid refrigeration system of the present invention includes a vapor compression refrigeration cycle including a compressor, a condenser, an expander, and an evaporator, and at least a pair of adsorbers that alternately adsorb refrigerant and desorb the adsorbed refrigerant alternately.
  • An adsorption refrigeration cycle is combined.
  • the condenser is a concept including a gas cooler.
  • the adsorption refrigeration cycle is combined with the vapor compression refrigeration cycle so as to reduce the compression pressure of the compressor in the vapor compression refrigeration cycle. As a result, the mechanical work in the vapor compression refrigeration cycle can be most effectively reduced.
  • the inventor has two specific types. Proposed invention.
  • the first type of the invention at least a pair of adsorbers that alternately adsorb the refrigerant compressed by the compressor and alternately desorb the adsorbed refrigerant between the compressor and the condenser in the vapor compression refrigeration cycle.
  • the refrigerant is compressed to the intermediate pressure by the compressor, and the refrigerant compressed to the intermediate pressure is increased to a pressure higher than the intermediate pressure by the adsorption refrigeration cycle. If it does in this way, the compression pressure by the compressor in a vapor compression refrigeration cycle can be made lower than before, and the mechanical work in a vapor compression refrigeration cycle can be reduced.
  • an internal heat exchanger for exchanging heat between the refrigerant flow path connecting the evaporator and the compressor and the refrigerant flow path connecting the condenser and the expander may be further provided.
  • an internal heat exchanger is provided, the specific enthalpy between the expander inlet and the evaporator inlet of the vapor compression refrigeration cycle can be lowered by absorbing heat from the refrigerant passing through the condenser. As a result, it is possible to increase the heat flow rate (refrigeration capacity) taken by the refrigerant from the surroundings in the evaporator.
  • the vapor compression refrigeration cycle used in the second type of invention includes a first compressor that compresses the first refrigerant, a first condenser that condenses the first refrigerant compressed by the first compressor, and a first condenser.
  • a first expander that expands the condensed first refrigerant and a first evaporator that evaporates the first refrigerant expanded by the first expander are provided.
  • the adsorption refrigeration cycle includes at least a pair of adsorbers that alternately adsorb the evaporated second refrigerant and alternately desorb the adsorbed second refrigerant, a second condenser that condenses the second refrigerant desorbed from the adsorber, A second expander that expands the second refrigerant condensed by the second condenser and a second evaporator that evaporates the second refrigerant expanded by the second expander are provided.
  • the adsorption refrigeration cycle is combined with the vapor compression refrigeration cycle so as to absorb heat from the first refrigerant passing through the first condenser via the second evaporator.
  • the heat is absorbed from the first refrigerant passing through the first condenser through the second evaporator without increasing the compression pressure of the first compressor of the vapor compression refrigeration cycle.
  • the specific enthalpy between the expander inlet and the evaporator inlet of the refrigeration cycle can be lowered.
  • the heat absorption from the first refrigerant passing through the first condenser can be realized by configuring a heat exchanger between the first condenser and the second evaporator.
  • the heat exchanger can be configured to exchange heat directly between the first condenser and the second evaporator.
  • the heat exchanger may have a structure including a refrigerant circulation path in which a third refrigerant circulates and includes a radiator and is arranged to exchange heat between the first condenser and the second evaporator. it can. If such a heat exchanger is used, a vapor compression refrigeration cycle can be combined so that oil from the first compressor is not mixed into the adsorption refrigeration cycle.
  • FIG. 1 It is a figure which shows the structure of a general vapor compression refrigeration system. It is a figure which shows the structure of the vapor
  • FIG. 2 is a PT (pressure-temperature) diagram of a simple transcritical cycle using carbon dioxide for three different compressor outlet pressures.
  • FIG. 13 is a Ph (pressure-specific enthalpy) diagram corresponding to FIG. FIG.
  • FIG. 3 is a diagram showing a coefficient of performance (COP) as a function of compressor outlet pressure for different gas cooler (condenser) temperatures. It is a figure which shows the performance map of the cooling capacity of the hybrid refrigeration system with respect to different adsorption temperature and desorption pressure. It is a figure which shows the performance map of COP (coefficient of performance) of a hybrid type refrigeration system with respect to different adsorption temperature and desorption pressure. It is a diagram showing a refrigerant amount based on the mass of CO 2 per dry Maxsorb III unit mass for different adsorption temperature and desorption pressure. It is a figure which shows the Ph diagram in adsorption temperature (308K, 313K, and 318K) when there is no internal heat exchanger IHE.
  • COP coefficient of performance
  • FIG. 5 is a diagram showing refrigerant flow rates as a function of desorption pressure with respect to four different compressor discharge pressures (60, 65, 70 and 75 bars) of the hybrid refrigeration system of the first embodiment shown in FIG.
  • FIG. 5 is a diagram showing refrigerant flow rates as a function of desorption pressure with respect to four different compressor discharge pressures (60, 65, 70 and 75 bars) of the hybrid refrigeration system of the first embodiment shown in FIG.
  • FIG. 19 is a table showing performance data of the hybrid refrigeration system showing the Ph diagram of FIG. 18.
  • FIG. 20 is a table showing performance data of a hybrid refrigeration system with an internal heat exchanger (IHE) in the Ph diagram of FIG. 19.
  • IHE internal heat exchanger
  • a general vapor compression refrigeration system includes a compressor 2, a gas cooler (condenser) 3, a receiver 4, an expander 5 and an evaporator 6 as schematically shown in FIG.
  • FIG. 2 shows a configuration of a vapor compression refrigeration system including an internal heat exchanger 7 used in the present embodiment.
  • the internal heat exchanger 7 is used at the outlet of the gas cooler (condenser) 3 and the outlet of the evaporator 6. By exchanging heat between them, the outlet temperature of the gas cooler (condenser) 3 is further reduced, and the evaporator 6 The outlet temperature of the rises more.
  • FIG. 3 shows a general configuration of a single stage adsorption refrigeration cycle 8.
  • the adsorption refrigeration cycle 8 includes a gas cooler (or condenser) 9, an evaporator 10, a pair of adsorbers (absorption / desorption heat exchangers) 11 and 12, and four valves 13 to 16.
  • activated carbon for example, Maxsorb III (trademark)
  • the refrigerant is adsorbed by one of the adsorbers 11 and 12, and desorption is caused in the adsorber in which the refrigerant is first adsorbed in the evaporation process.
  • the adsorbers 11 and 12 alternately repeat adsorption and desorption by alternately cooling and heating.
  • the refrigerant (CO 2 ) evaporates at the evaporation temperature in the evaporator 10 and is adsorbed by the adsorber (Bed 1) 12. Adsorption continues until the refrigerant concentration of the adsorbent becomes high. Cooling water is used to remove the heat of adsorption.
  • the adsorber (Bed2) 11 functioning as a desorber is heated to a desorption temperature by driving heat input (exhaust heat or a heat source from a renewable energy source).
  • the refrigerant desorbed from the adsorber (Bed2) 11 is cooled (or condensed) by the gas cooler (or condenser) 9.
  • the heat of condensation in the condenser 9 is removed by the cooling water.
  • the driving time for suction / desorption continues for 240 to 600 seconds, and the condensed refrigerant liquid returns to the evaporator 10 according to a prescribed cycle.
  • the time for closing all valves 13 to 16 is introduced for about 30 seconds so that no evaporation occurs.
  • the complete reverse cycle then continues with all valves in the reverse mode.
  • FIG. 4 shows a schematic configuration of the first embodiment of the present invention in which the vapor compression refrigeration cycle of FIG. 1 and the adsorption refrigeration cycle of FIG. 3 are combined.
  • members similar to those shown in FIGS. 1 and 3 are given the same reference numerals as those shown in FIGS. 1 and 2 plus 100.
  • the hybrid refrigeration system of the first embodiment shown in FIG. 4 alternately adsorbs and adsorbs the refrigerant compressed by the compressor 102 between the compressor 102 and the condenser 103 in the vapor compression refrigeration cycle 101.
  • the adsorption refrigeration cycle 108 is combined so that at least a pair of adsorbers 111 and 112 and 111 'and 112' for alternately desorbing the refrigerant are located.
  • the adsorbers 111 and 111 ′ and the adsorbers 112 and 112 ′ alternately perform adsorption and desorption operations.
  • the batch operation of the adsorption cycle has two time intervals called the switching period and the operation period.
  • suction and desorption are performed to maintain compression pressure and gas cooler (or condenser) pressure.
  • a water-cooled or air-cooled gas cooler (or condenser) cools the fluid desorbed from a designated desorber (the one of the adsorbers 111 to 112 ′ that is desorbing), and the fluid that has become the supercooled liquid is then expanded into the expander 105.
  • the refrigeration cycle is completed.
  • the function of the adsorber (including the adsorbent) that has been desorbed is restored by switching that switches the direction of the external heat source.
  • external cooling is also switched to the designated adsorbers, and similarly, the compressor 102 and condenser 103 are also switched to their respective adsorbers and desorbers (adsorbers performing desorption).
  • the heated desorber (desorbing adsorber) and the condenser 103 are also switched to their respective adsorbers and desorbers (adsorbers performing desorption).
  • FIG. 5 shows the refrigeration cycle w2 of the embodiment of FIG.
  • symbols with numerals 1 to 4 are added in circles, but these symbols are enclosed in parentheses in the specification because of restrictions on characters that can be used in the specification. Describe using the characters “(1) to (4)” with numbers. Also in the drawings after FIG. 4, when a symbol with a number is added in a circle, similarly for these symbols, use the characters (1) to (4). Describe. FIG. 4 shows an evaporation end point (1), an intermediate compression end point (2) ′, a compression end point (2) ”, a gas cooler (or condenser) outlet (3), an evaporator shown in the refrigeration cycle of FIG.
  • the compressor 102 compresses the refrigerant to an intermediate pressure [(1) ⁇ ( 2) ′] Then, without increasing the compression pressure of the compressor 102 to (2), the refrigerant compressed to the intermediate pressure is increased to a pressure higher than the intermediate pressure by the adsorption refrigeration cycle 108 [(2) ′ ⁇ ( 2) ”]. If it does in this way, the compression pressure by the compressor 102 in the vapor compression refrigeration cycle 101 can be made an intermediate pressure lower than before, and the mechanical work (power) in the vapor compression refrigeration cycle 101 is reduced. be able to.
  • the main process is (i) the heat load on the evaporator 106 maintained at a constant temperature (5 ° C.) and a constant pressure (39.8 bar). Then, the CO 2 liquid refrigerant evaporates [(4) ⁇ (1)], and (ii) the vaporized CO 2 liquid refrigerant is pressurized from the evaporation pressure to the compression pressure (intermediate pressure) through the compressor 102 [ (1) ⁇ (2) ′]. (iii) The compressed CO 2 vapor is thermally compressed by desorption in the adsorption refrigeration cycle 108. (iv) Gas cooler (or condenser) pressure undergoes isobaric heat release process by gas cooler (or condenser) [(2) ” ⁇ (3)], (v) and adiabatic expansion process [(3) ⁇ ( 4)].
  • FIG. 6 is a diagram showing a configuration of the second embodiment of the present invention as a modification of the first embodiment shown in FIG.
  • FIG. 6 the same members as those of the first embodiment shown in FIG.
  • FIG. 7 shows the refrigeration cycle of the embodiment shown in FIG.
  • FIG. 6 shows the evaporation end point (1), intermediate compression end point (2) ′, compression end point (2) ”, gas cooler (or condenser) outlet (3), evaporator shown in the refrigeration cycle of FIG.
  • the same symbol [(1) to (4) ′] is attached to the position corresponding to the inlet (4) ′.
  • the refrigerant flow path FP1 connecting the evaporator 106 and the compressor 102 and the condensation are provided.
  • the internal heat exchanger 107 which performs heat exchange between the refrigerant
  • the internal heat exchanger 107 is the gas cooler (or condenser) 103. Used between the outlet and the outlet of the evaporator 106, the heat exchange between them lowers the outlet temperature of the gas cooler (or condenser) 103 and further increases the outlet temperature of the evaporator 106. This increases the coefficient of performance (COP) of the system.
  • COP coefficient of performance
  • the specific enthalpy (h) of the expander inlet (3) ′ and the evaporator inlet (4) ′ of the vapor compression refrigeration cycle 101 ′ is absorbed by absorbing heat from the refrigerant passing through the condenser 103, Compared with the case where the internal heat exchanger 107 is not provided, the internal heat exchanger 107 can be lowered (reduced), and as a result, without increasing the compression pressure by the compressor 102 [without increasing the pressure to (2)], the evaporator 106 can generate refrigerant.
  • the heat flow (refrigeration capacity) taken away from the surroundings can be increased, that is, the mechanical work in the vapor compression refrigeration cycle 101 'can be reduced also by this embodiment.
  • FIG. 8 shows the configuration of the third embodiment of the hybrid refrigeration system of the present invention.
  • the number of 100 is added to the number of the reference numerals shown in FIGS. 4 and 6 to the same members as those of the first embodiment shown in FIG. A number of symbols are attached.
  • the adsorption refrigeration cycle since the refrigerant of the vapor compression refrigeration cycle 101 and the adsorption refrigeration cycle 108 are common, the adsorption refrigeration cycle unless a filter device is installed in the refrigerant flow path. Contaminants such as machine oil that are likely to be contained in the refrigerant at 108 pass through the adsorbers (211 and 212, 211 'and 212').
  • the adsorbers (211 and 212, 211 'and 212') become contaminated, it becomes necessary to clean them regularly. Therefore, in the third embodiment, a configuration is adopted in which the adsorbers (211 and 212, 211 ′ and 212 ′) are protected from dirt.
  • the refrigerant used in the vapor compression refrigeration cycle 201 is different from the refrigerant used in the adsorption refrigeration cycle 208, and heat exchange is performed between both cycles.
  • the vapor compression refrigeration cycle 201 used in the third embodiment includes a first compressor 202 that compresses the first refrigerant, a first condenser 203 that condenses the first refrigerant compressed by the first compressor 202, A first expander 205 that expands the first refrigerant condensed by the first condenser 203 and a first evaporator 206 that evaporates the first refrigerant expanded by the first expander 205 are provided.
  • the adsorption refrigeration cycle 208 includes at least a pair of adsorbers (211 and 212, 211 'and 212') that alternately adsorb the evaporated second refrigerant and alternately desorb the adsorbed second refrigerant, and desorb from the adsorber.
  • Gas cooler (or second condenser) 223 for condensing the second refrigerant, the second expander 221 and the second expander for expanding the second refrigerant cooled (or condensed) by the gas cooler (or second condenser) 223
  • a second evaporator 222 is provided for evaporating the second refrigerant expanded by 221.
  • the 1st condenser 203 and the 2nd evaporator 222 are comprised as one unit so that a heat exchanger may be comprised between both.
  • this heat exchanger can exchange heat directly between the first condenser 202 and the second evaporator 222, or can exchange heat by arranging a circulation path containing another refrigerant between them.
  • its configuration is arbitrary.
  • the adsorption refrigeration cycle 208 is combined with the vapor compression refrigeration cycle 201 so as to absorb heat from the first refrigerant passing through the first condenser 203 via the second evaporator 222.
  • FIG. 9 shows the refrigeration cycle of the embodiment of FIG.
  • FIG. 9 shows the evaporation end point (1) (5), compression end point (2) ′ (6), condensation end point (3) ′ (7), and expansion end point (4) shown in the refrigeration cycle of FIG.
  • the same symbol [(1) to (8)] is attached to the position corresponding to) ′ (8).
  • heat is absorbed from the first refrigerant passing through the first condenser 206 via the second evaporator 222 without increasing the compression pressure of the first compressor 202 of the vapor compression refrigeration cycle 201.
  • the specific enthalpy of the expander inlet (3) ′ and the evaporator inlet (4) ′ of the vapor compression refrigeration cycle 201 can be reduced (to a small value).
  • the refrigerant is surrounded by the first evaporator 206 without increasing the compression pressure (compression work) of the first compressor 202 as in the first and second embodiments.
  • the heat flow (refrigeration capacity) deprived from can be increased.
  • FIG. 10 shows a fourth embodiment as a modification of the third embodiment shown in FIG.
  • the same number as that of the third embodiment shown in FIG. 8 is obtained by adding 100 to the number of reference numerals attached in FIG. 8.
  • symbol is attached
  • the 1st condenser 203 and the 2nd evaporator 222 are comprised as one unit so that a heat exchanger may be comprised between both.
  • the heat exchanger that performs heat exchange between the first condenser 203 and the second evaporator 222 includes a radiator 324, and includes the first condenser 303 and the second condenser 303.
  • the structure is provided with a refrigerant circulation path 328 in which the third refrigerant circulates and is arranged so as to exchange heat with the evaporator 310.
  • the adsorbers 311 and 312 have a structure that is regenerated by the exhaust heat of the engine 327 of the automobile. Valves 326 and 329 are arranged between the engine 327 and the pair of adsorbers 311 and 312 for alternately connecting the engine 327 and the radiator 325 to the adsorbers 311 and 312 at the time of desorption.
  • the first evaporator 306 is used to generate cooling capacity, and the second evaporator 310 prevents the adsorbers 311 and 312 from being mixed with oil. Used to operate the adsorber.
  • the condenser 309 is used to dissipate the heat absorbed by the second evaporator 310 to the outside.
  • FIG. 11 shows experimental data of adsorption isotherms of the adsorbent used in the adsorber.
  • the paper ⁇ S. Himeno, T. Komatsu and S. Fujita, High-pressure adsorption equilibria of methane and carbon dioxide on several activated carbons, J. Chem. Eng. Data 50 (2005), 369-376 ''
  • Maxsorb III TM the results of measurement in a temperature range of 273 to 348 K and a pressure of up to 4 MPa are described.
  • FIG. 11 shows the relationship of the amount of adsorption with respect to the pressure change at various adsorption temperatures. From FIG. 11, it can be seen that the maximum amount of CO 2 adsorbed is 1.5 kg per 1 kg of Maxsorb III.
  • the adsorption capacity defined by the maximum isothermal adsorption per gram of adsorbent is “F. Dreisbach, R. Staudt and JU Keller, J High-pressure adsorption Data of Methane, Nitrogen, Carbon Dioxide and their Binary and Ternary Mixtures on Activated. Carbon. Adsorption 5 (1999), 215-227., ⁇ A. Kapoor and RT Yang, Kinetic Separation of Methane-Carbon Dioxide Mixture by Adsorption on Molecular Sieve Carbon. Chem. Eng.
  • W is the adsorption volume
  • W 0 is the maximum adsorption volume to the micropores
  • K is a Langmuir constant that is an adsorption index when the adsorption amount is very small
  • P is the pressure.
  • K can be expressed as a function of temperature as follows:
  • R is a gas constant
  • T is an equilibrium temperature
  • K 0 is a coefficient
  • ⁇ H ads is an adsorption heat. Langmuir's adsorption isotherm model was confirmed to agree with the experimental data within ⁇ 5%.
  • FIG. 12 shows a PT (pressure-temperature) diagram of a simple transcritical cycle using carbon dioxide for three different compressor outlet pressures.
  • the Ph (pressure-specific enthalpy) diagram that coincides with this is as shown in FIG.
  • Transcritical CO 2 cycle consists of (a) isoenthalpy compression process (1-2 or 1-2 'or 1-2 "), (b) isobaric heat release process (2-3 or 2'-3' or 2" -3 "), (c) Adiabatic expansion process (3-4 or 3'-5 or 3" -6), (d) Isobaric evaporation process (4-1 or 5-1 or 6-1) Is shown.
  • FIG. 13 is a PT (pressure-temperature) diagram of a vapor compression refrigeration cycle. 13 A represents the cycle 1-2-3-4-1, B represents the cycle 1-2'-3'-5-1, and C represents the cycle 1-2 "-3"- 6-1.
  • FIGS. 14A to 14C show cycles 1-2-3-4-1 and cycle 1-2'- shown in the PT and Ph diagrams of the vapor compression refrigeration cycle of FIGS. 3′-5-1 and cycle 1-2 ′′ -3 ′′ -6-1 are shown.
  • vapor compression is the analysis result of the general vapor compression refrigeration cycle of FIG. 1
  • IHE-use vapor compression is the result of the vapor compression refrigeration cycle having the internal heat exchanger of FIG. 2. It is an analysis result.
  • 15 and 16 show the performance maps of the cooling capacity and COP (coefficient of performance) of the hybrid refrigeration system for different adsorption temperatures (308K, 313K and 318K) and desorption pressure, respectively.
  • 15 and 16 A shows the analysis result of the hybrid refrigeration system of the first embodiment shown in FIG. 4, and B shows the hybrid refrigeration system of the second embodiment shown in FIG. An analysis result is shown.
  • the COP (coefficient of performance) is close to 8.0, which is about twice that of the vapor compression refrigeration cycle for the optimum condition of a gas cooler (condenser) temperature of 35 ° C.
  • FIG. 16 shows that when an internal heat exchanger (IHE) is added, the COP (coefficient of performance) is 10 or more depending on the gas cooler (condenser) temperature and the desorption pressure.
  • IHE internal heat exchanger
  • FIG. 17 shows the amount of refrigerant based on the mass of CO 2 per unit mass of dry Maxsorb III for different adsorption temperatures (308K, 313K and 318K) and desorption pressure.
  • 17, A shows the analysis result of the hybrid refrigeration system of the first embodiment shown in FIG. 4, and B shows the analysis result of the hybrid refrigeration system of the second embodiment shown in FIG. Show. From this analysis, the amount of Maxsorb III for the required cooling capacity can be easily estimated.
  • the Ph diagrams at the adsorption temperatures (308K, 313K, and 318K) when there is no internal heat exchanger IHE (FIG. 18) and when there is (FIG. 19) are shown in FIGS.
  • FIGS. 20A and 20B and FIG. 21 show the four different compressor discharge pressures (60, 65, 70 and 75 bars) of the hybrid refrigeration system of the first embodiment shown in FIG.
  • the cooling capacity, COP (coefficient of performance) and refrigerant flow are shown as a function of desorption pressure.
  • FIG. 22 shows a vapor compression process, a thermal compression process (adsorption-preheating-desorption-precooling) and an expansion process.
  • the compressor outlet pressure is 60 bar and the gas cooler temperature is 35.degree.
  • FIG. 25 and FIG. 25 shows performance data of the hybrid refrigeration system of FIG. 16
  • FIG. 26 shows performance data of the hybrid refrigeration system with an internal heat exchanger (IHE) of FIG.
  • IHE internal heat exchanger
  • the hybrid refrigeration system of the present invention is not only highly efficient but also provides a high refrigeration effect and can eliminate problems caused by compressors and valves. Therefore, the hybrid refrigeration system of the present invention can be sufficiently applied to an automobile air conditioning system and a heat pump system.
  • a compressor that compresses the refrigerant, a condenser that condenses the refrigerant compressed by the compressor, an expander that expands the refrigerant condensed by the condenser, and the refrigerant that is expanded by the expander At least adsorbs the refrigerant compressed by the compressor and desorbs the adsorbed refrigerant alternately between the compressor and the condenser in a vapor compression refrigeration cycle comprising an evaporator for evaporating at least An adsorption refrigeration cycle having a pair of adsorbers is provided, the refrigerant is compressed to an intermediate pressure by the compressor, and the refrigerant compressed to the intermediate pressure is increased to a pressure higher than the intermediate pressure by the adsorption refrigeration cycle.
  • a hybrid refrigeration system characterized by:
  • a first compressor that compresses the first refrigerant, a first condenser that condenses the first refrigerant compressed by the first compressor, and expands the first refrigerant condensed by the first condenser.
  • a vapor compression refrigeration cycle comprising: a first expander that causes the first refrigerant to evaporate the first refrigerant expanded by the first expander; At least a pair of adsorbers that alternately adsorb the evaporated second refrigerant and alternately desorb the adsorbed second refrigerant, a second condenser that condenses the second refrigerant desorbed from the adsorber, and the second An adsorption refrigeration cycle comprising a second expander that expands the second refrigerant condensed by the condenser and a second evaporator that evaporates the second refrigerant expanded by the second expander;
  • the hybrid refrigeration system wherein the adsorption refrigeration cycle is combined with the vapor compression refrigeration cycle so as to absorb heat from the first ref
  • the heat exchanger includes a refrigerant circulation path in which a third refrigerant circulates and includes a radiator and is arranged to exchange heat between the first condenser and the second evaporator.
  • the hybrid refrigeration system according to (3) above.
  • the adsorption refrigeration cycle is combined with the vapor compression refrigeration cycle so as to reduce the compression pressure of the compressor in the vapor compression refrigeration cycle.
  • the amount of work can be reduced.

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Abstract

L'invention porte sur un système de réfrigération hybride configuré de telle sorte qu'une charge de travail mécanique dans un cycle de réfrigération à compression de vapeur est réduite. Un système de réfrigération hybride est formé par une combinaison d'un cycle de réfrigération à compression de vapeur (101) ayant un compresseur (102), un condenseur (103), un détendeur (105) et un évaporateur (106), et d'un cycle de réfrigération à adsorption (108) ayant au moins une paire d'adsorbeurs (111-112') pour adsorber alternativement un fluide frigorigène et pour désorber alternativement le fluide frigorigène adsorbé. Le cycle de réfrigération à adsorption (108) est combiné au cycle de réfrigération à compression de vapeur (101) de telle sorte que la pression de compression du compresseur (102) dans le cycle de réfrigération à compression de vapeur (101) est réduite.
PCT/JP2009/059817 2008-05-28 2009-05-28 Système de réfrigération hybride WO2009145278A1 (fr)

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CN103453689A (zh) * 2012-05-30 2013-12-18 财团法人工业技术研究院 复合式制冷系统及其控制方法
CN106403361A (zh) * 2015-10-18 2017-02-15 李华玉 第五类热驱动压缩‑吸收式热泵
WO2017103939A1 (fr) 2015-12-18 2017-06-22 Bry-Air [Asia] Pvt. Ltd. Dispositifs à cycle hybride de compression-adsorption de vapeur et leur procédé de mise en œuvre
WO2019069598A1 (fr) * 2017-10-06 2019-04-11 株式会社デンソー Adsorbeur et réfrigérateur à adsorption
JP2019070509A (ja) * 2017-10-06 2019-05-09 株式会社デンソー 吸着器および吸着式冷凍機
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JP2019070509A (ja) * 2017-10-06 2019-05-09 株式会社デンソー 吸着器および吸着式冷凍機

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