WO2008035386A2 - Installation frigorifique a sous-refroidissement regule - Google Patents

Installation frigorifique a sous-refroidissement regule Download PDF

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Publication number
WO2008035386A2
WO2008035386A2 PCT/IT2007/000648 IT2007000648W WO2008035386A2 WO 2008035386 A2 WO2008035386 A2 WO 2008035386A2 IT 2007000648 W IT2007000648 W IT 2007000648W WO 2008035386 A2 WO2008035386 A2 WO 2008035386A2
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerating plant
refrigerating
plant according
exchanger
water
Prior art date
Application number
PCT/IT2007/000648
Other languages
English (en)
Other versions
WO2008035386A3 (fr
Inventor
Giuseppe Giovanni Renna
Original Assignee
Giuseppe Giovanni Renna
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Giuseppe Giovanni Renna filed Critical Giuseppe Giovanni Renna
Publication of WO2008035386A2 publication Critical patent/WO2008035386A2/fr
Publication of WO2008035386A3 publication Critical patent/WO2008035386A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/04—Desuperheaters
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/19—Refrigerant outlet condenser temperature

Definitions

  • a refrigerating plant equipped with controlled subcooling forms the obj ect of the present finding.
  • EER is the ratio between the refrigerating energy provided to the evaporator and the energy absorbed by the compressor.
  • Figure 1 shows the increase of the refrigerant fluid R410A on a pressure - enthalpy diagram (P-H). Similar results can also be obtained with any other refrigerant.
  • the heat taken away from the liquid coming from the condensers ensures that the refrigerant in part evaporates before entering into the second compression stage (in the screw compressors it is in contact with a second suction opening placed at about the midpoint of the rotors). Complete evaporation occurs because the refrigerant is injected in the compressor. During injection, the liquid vaporises, taking away heat: in this manner, the vapour exiting from the first compression stage (point 2) is cooled up to point 3.
  • the economiser on the one hand permits increasing the subcooling, on the other reducing the compression work. It moreover allows limiting the exit temperature of the refrigerant at the end of the compression (point 4): this is very important for the screw compressors which have oil in communication with the high pressure to avoid overly high lubricant temperatures, with consequent cracking phenomena.
  • a second system for increasing the overheating is given by the refrigerating circuit liquid — cold vapour recovery, shown in figure 3.
  • the circuit is simpler than the preceding.
  • the subcooling increase is obtained by cooling the liquid coming from the condenser 14 by means of the cold vapour coming from the evaporator 12, which in turn is overheated.
  • Exchanged enthalpy gradient being equal, the thermal gradient on the cold vapour side is about double that on the liquid.
  • the big disadvantage of the already known applications consists of the fact that the subcooling step has very precise thermal limits, which limit its benefits.
  • said limit consists of the flow rate of refrigerant which must be divided between the first and second compression stage and which must reciprocally exchange heat inside the economiser.
  • said limit consists of the need to limit the overheating of the cold vapour coming from the evaporator.
  • the enthalpy gradient must not be greater than 20 kJ/kg.
  • the obtainable subcooling is therefore only 13 0 C.
  • the technical problem underlying the present invention is therefore that of designing and making a high efficiency refrigerating circuit in which the subcooling step is not subjected to the aforesaid thermal limitations.
  • the finding, object of the present invention resolves this technical problem since it regards a refrigerating plant equipped with controlled subcooling, characterised by the insertion of a heat exchanger on the liquid line, upstream of the thermal expansion valve.
  • a lower-temperature external fluid (figure 4) which can be water, air or another refrigerant.
  • a lower-temperature external fluid (figure 4) which can be water, air or another refrigerant.
  • the objects and advantages obtained by the invention vary slightly according to the different adopted embodiments: air + water hybrid cooling; two-stage heat recovery; low-temperature heat recovery by post-heating; auto-storage of refrigerating energy; controlled subcooling with dedicated refrigerating circuit. Said objects and advantages are clarified in the detailed description of the invention which makes specific reference to tables 1/8 - 8/8 in which several preferred, but absolutely non- limiting embodiments are represented.
  • • Fig. 1 represents the effects of increased subcooling on the performance;
  • Fig. 2 shows a refrigerating circuit with economiser of known type
  • Fig. 3 shows a refrigerating circuit with liquid — cold vapour recovery, still of known type
  • Fig. 4 depicts the insertion of the exchanger on the liquid line
  • Fig. 5 is a hybrid condensation system
  • Fig. 6 shows the power required by the plant and output by the refrigerating groups as a function of the air temperature
  • Fig. 7 shows the EER progression for a normal refrigerating group and a hybrid cooling refrigerating group
  • Fig. 8 is the two-stage heat recovery diagram
  • Fig. 9 shows the energy effects of the two-stage heat recovery
  • Fig. 10 shows the output and efficiency improvements in a heat pump due to the two-stage recovery
  • Fig. 11 depicts the energy loss due to the post-heating
  • Fig. 12 shows the application of the controlled subcooling in direct expansion, to recover the post-heating heat
  • Fig. 13 represents the energy advantages of the system as a function of the temperature downstream of the post-heating
  • Fig. 14 shows the auto-storage of the refrigerating energy due to the use of controlled subcooling
  • Fig. 15 represents the production of refrigerating energy with the system, object of the present invention
  • Fig. 17 represents the subcooling controlled by a refrigerating circuit in summer functioning.
  • a refrigerating plant is the object of the present finding, equipped with controlled subcooling comprising at least one compressor 11, an evaporator 12, a thermal expansion valve 13 and a condenser 14 and characterised by the introduction, in the refrigeration cycle, of a heat exchanger 15 on the liquid line, upstream of the thermal expansion valve 13.
  • the refrigerant liquid is cooled by a lower- temperature external fluid.
  • a first embodiment provides for the use, as external refrigerant fluid, of tap water (or groundwater or water from other low- temperature heat reservoir) which is generally found at 15 0 C, in addition to air.
  • Figure 5 shows the functioning diagram.
  • the exchanger 15 is of liquid- water type.
  • the calibration valve 16 placed on the tap water line is commanded by a microprocessor to regulate the power and to optimise the efficiency.
  • the name of hybrid cooling arises from the fact that air is normally used, but in certain favourable conditions, depending on several factors, in order to increase output and efficiency, diminish costs or reduce noise, the air cooling is supplemented with the water cooling.
  • Figure 6 better specifies the specific and innovative characteristics of the solution. The figure reports the outside air temperature on the x-axis and the refrigerating power required by the plant and that provided by various refrigerating groups on the y-axis. The power required by the plant increases as the outside air temperature increases. Generally, the refrigerating group is chosen to satisfy the power required by the plant in nominal conditions (for example 35 0 C air temperature).
  • the normal refrigerating group GF is selected. If, however, the air temperature increases, the plant requires more and the refrigerating group outputs less. There is an imbalance which prevents keeping the plant's thermo-hygrometric conditions under control; it would then be necessary to choose the oversized refrigerating group GF.
  • the cooling takes place only with air up to a certain temperature (3O 0 C in the example), after which the water cooling valve is also opened, and the subcooling is increased, exactly following the plant's requirement curve.
  • the size of the refrigerating group is even less than the normal selection size.
  • the opening of the water cooling can also be commanded based on efficiency, as shown in figure 7.
  • the valve Over a certain air temperature, the valve is opened, improving the efficiency with respect to a normal refrigerating group which is only cooled with air, in greater percentages the higher the outside air temperature. This characteristic leads to a considerable diminution both of consumptions and of the environmental impact of the refrigerating group.
  • the water cooling can be directed to reduce the noise produced by the refrigerating group. In fact, it is possible to make the fans 17 rotate more slowly, taking advantage of a greater condensation temperature, making up for the diminution of power and efficiency thanks to the hybrid cooling.
  • a second embodiment provides for a two-stage heat recovery.
  • the heat recovery occurs at only one temperature level, either by employing all of the condensation heat in a refrigerant - water exchanger parallel to the refrigerant - air exchanger, or by employing only the superheat of the refrigerant in the so-called desuperheater 18.
  • the exchanger 15 can be employed on the liquid line to carry out a two-stage recovery, one with lower temperature in the liquid exchanger and one with higher temperature in the desuperheater.
  • the diagram is shown in figure 8 for the specific case of water for sanitary use, but said recovery can also be adopted in all cases in which there is a sufficiently low temperature level of the fluid to be heated. This leads to an improvement of the functioning conditions, both in summer (functioning as refrigerator) and in winter (functioning as heat pump).
  • Figure 9 shows the thermal and refrigerating energy requirement of a plant, the electric power consumption as a function of the recovery water requirement in the case of a refrigerating group with total recovery, refrigerating group with partial recovery and two-stage refrigerating group.
  • the electric power consumption of the two-stage recovery system is always better than the other two in every condition. This is explainable thanks to the clear energy efficiency improvement from the subcooling.
  • the low temperature dashed line of the air indicates that the recovery by the desuperheater was not sufficient, so that it is necessary to carry out an external supplementation (in the figure, supplementing with a heating element is assumed).
  • a third embodiment of the invention defined heat recovery by post-heating, is the version of the two-stage heat recovery in direct expansion.
  • the loss is due to the fact that the air is brought to a level of enthalpy lower than that of insertion (point C) to then be heated up to point D.
  • the loss is given by the value ⁇ H. There is even loss if the heating from C to D is made by means of a heat recovery by the desuperheater 18. If said recovery is not carried out, the loss substantially doubles (since the necessary heat must be generated). In figure 11, it is seen that the air in point C has a substantially low temperature, so that the subcooling can be increased. Hence, it is possible to recover the post-cooling heat by subcooling. In this manner, the refrigerating output of the system is improved and the loss cancelled.
  • Figure 12 shows how a direct expansion air conditioner can be constructed. If desired, if the post-heating required is high, it is also possible to use the recovery by desuperheater 18, or employ this heat to produce hot sanitary water. The energy savings is quite significant.
  • Figure 13 shows the electric power consumption necessary to bring the air from 28°C with 50% relative humidity up to saturation and then heat it up to the temperature reported on the x-axis.
  • the comparison was made by considering one traditional system with heat recovery by post-heating, and one with electric post-heating. As seen, the system of the invention gives clearly better results.
  • the electric post-heating system rapidly increases consumption due to the energy absorbed by the heating element.
  • the traditional system with hot gas post-heating by desuperheater maintains constant consumption while there is the possibility to employ the desuperheater heat, after which also in this case a heating element must be used.
  • the invention instead, decreases the required power.
  • a fourth embodiment of the invention certainly the most interesting application, is the auto-storage of refrigerating energy.
  • the power increase of the subcooling is utilised to increase the possible refrigerating energy in the hydraulic store 19 (fig.14).
  • There is an over 10-times increase of the stored energy because one can employ the over 3O 0 C thermal gradient as opposed to a 3 0 C thermal gradient (from 7 to 10 0 C).
  • Figure 14 better illustrates the functioning. In normal functioning, pump Pl of the hydraulic plant is in function, pump P2 of the exchanger is turned off, the valve V has path B closed and path A open.
  • the entire water flow rate passes through the hydraulic store 19 before heading towards the plant.
  • the store is by-passed, closing path A of the valve V and opening path B.
  • the pump P2 starts, which feeds the exchanger 15 with water cooled to 7°C for the controlled subcooling.
  • the obtainable increase is greater than 40%, electrical consumption being equal.
  • the temperature of the water store can be restored. Therefore, there is an energy production at different times from that of maximum consumption.
  • the water store substantially works as an energy store. Since the thermal gradient obtainable on the subcooling exchanger is about 35°C (7°C - 42°C), the storable energy is about 40 kWh for every 1000 litres of water.
  • the refrigerating group of the present invention gives at most 100% of instantaneous power, while the remaining part is obtained from the increase of the subcooling through the store.
  • the cold store is restored shortly before the starting of the plant.
  • the system works as an ice storage system, with the unquestionable advantage of requiring neither glycol water nor working at low temperatures with low efficiency.
  • the consumptions are reduced during the preparation of the store.
  • the hydraulic circuit also results considerably simplified.
  • the fifth and final embodiment of the invention provides for a controlled subcooling with dedicated refrigerating circuit. It is the most complex and least applicable system and can give rather good results in a heat pump.
  • the additional subcooling is obtained through a second refrigerating circuit.
  • the exchanger of the subcooling 35 (fig. 17) is on one side the evaporator 22 of the second circuit.
  • the second circuit condenses at the same temperature of the first, but evaporates to a higher temperature.
  • the second compressor 21 is smaller with respect to the increase of power provided to the first compressor, since it evaporates at higher temperature.
  • the overall efficiency is increased because the second circuit works with an improved EER.
  • Figure 17 shows the system in summer functioning.
  • the condenser 24 of the second circuit can also be used for the heat recovery. This appears very interesting if a CO 2 refrigeration cycle is used for the production of high temperature sanitary water. In this case, the production would also increase the refrigerating output and efficiency. The heat pump functioning seems more interesting. Both condensers work to produce hot water and condense at the same temperature, but the evaporation in the second circuit occurs at a much higher temperature, which clearly improves the overall COP, particularly with lower outside air temperatures.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention concerne une installation frigorifique à sous-refroidissement régulé, obtenue par insertion d'un échangeur de chaleur sur la conduite de liquide afin d'augmenter le sous-refroidissement. L'échangeur peut réaliser un échange de chaleur au moyen d'eau, d'air ou d'un autre fluide frigorigène. Les avantages obtenus varient en fonction de la solution adoptée : refroidissement hybride air + eau; récupération de chaleur en deux étapes; récupération de chaleur à basse température par post-chauffage; auto-stockage d'énergie frigorifique; sous-refroidissement régulé à circuit frigorifique spécialisé.
PCT/IT2007/000648 2006-09-20 2007-09-18 Installation frigorifique a sous-refroidissement regule WO2008035386A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITBA2006A000054 2006-09-20
ITBA20060054 ITBA20060054A1 (it) 2006-09-20 2006-09-20 Impianto frigorifero dotato di sottoraffreddamento controllato

Publications (2)

Publication Number Publication Date
WO2008035386A2 true WO2008035386A2 (fr) 2008-03-27
WO2008035386A3 WO2008035386A3 (fr) 2008-05-29

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010056556A1 (fr) * 2008-11-12 2010-05-20 Johnson Controls Technology Company Échangeur à chaleur à plusieurs étages
WO2010081249A1 (fr) * 2009-01-13 2010-07-22 Enrique Luis Aparicio Bernat Système d'amélioration universel autonome et compact, utile pour augmenter la capacité et l'efficacité de systèmes de réfrigération ou d'air conditionné
GB2495149A (en) * 2011-09-30 2013-04-03 Arctic Circle Ltd Refrigeration Apparatus With Subcooler
CN107003044A (zh) * 2014-11-14 2017-08-01 开利公司 利用热能存储的节能循环
FR3063539A1 (fr) * 2017-03-03 2018-09-07 Electricite De France Installation frigorifique
WO2020251480A1 (fr) * 2019-06-14 2020-12-17 Maxeff Teknoloji̇ Anoni̇m Şi̇rketi̇ Machine de chauffage-refroidissement à source d'eau dotée d'unité de refroidissement de fluide frigorigène refroidissant à l'aide d'une source de refroidissement externe et procédé de chauffage-refroidissement

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3976123A (en) * 1975-05-27 1976-08-24 Davies Thomas D Refrigeration system for controlled heating using rejected heat of an air conditioner
US4373346A (en) * 1981-03-25 1983-02-15 Hebert Thomas H Precool/subcool system and condenser therefor
GB2168136A (en) * 1984-12-05 1986-06-11 Yutaka Takahashi Air-conditioning hot-water supply device
US4599870A (en) * 1981-03-25 1986-07-15 Hebert Theodore M Thermosyphon heat recovery
US4964279A (en) * 1989-06-07 1990-10-23 Baltimore Aircoil Company Cooling system with supplemental thermal storage
US5095712A (en) * 1991-05-03 1992-03-17 Carrier Corporation Economizer control with variable capacity
US20020033024A1 (en) * 1998-10-08 2002-03-21 Hebert Thomas H. Utilization of harvest and/or melt water from an ice machine for a refrigerant subcool/precool system and method therefor
WO2003014637A2 (fr) * 2001-08-09 2003-02-20 Albert Robert Lowes Installation de refrigeration
US20040031278A1 (en) * 2002-08-13 2004-02-19 Delaware Capital Formation, Inc. Cooling device with subcooling system
US20060201188A1 (en) * 2005-03-14 2006-09-14 York International Corporation HVAC system with powered subcooler

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3976123A (en) * 1975-05-27 1976-08-24 Davies Thomas D Refrigeration system for controlled heating using rejected heat of an air conditioner
US4373346A (en) * 1981-03-25 1983-02-15 Hebert Thomas H Precool/subcool system and condenser therefor
US4599870A (en) * 1981-03-25 1986-07-15 Hebert Theodore M Thermosyphon heat recovery
GB2168136A (en) * 1984-12-05 1986-06-11 Yutaka Takahashi Air-conditioning hot-water supply device
US4964279A (en) * 1989-06-07 1990-10-23 Baltimore Aircoil Company Cooling system with supplemental thermal storage
US5095712A (en) * 1991-05-03 1992-03-17 Carrier Corporation Economizer control with variable capacity
US20020033024A1 (en) * 1998-10-08 2002-03-21 Hebert Thomas H. Utilization of harvest and/or melt water from an ice machine for a refrigerant subcool/precool system and method therefor
WO2003014637A2 (fr) * 2001-08-09 2003-02-20 Albert Robert Lowes Installation de refrigeration
US20040031278A1 (en) * 2002-08-13 2004-02-19 Delaware Capital Formation, Inc. Cooling device with subcooling system
US20060201188A1 (en) * 2005-03-14 2006-09-14 York International Corporation HVAC system with powered subcooler

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010056556A1 (fr) * 2008-11-12 2010-05-20 Johnson Controls Technology Company Échangeur à chaleur à plusieurs étages
WO2010081249A1 (fr) * 2009-01-13 2010-07-22 Enrique Luis Aparicio Bernat Système d'amélioration universel autonome et compact, utile pour augmenter la capacité et l'efficacité de systèmes de réfrigération ou d'air conditionné
GB2495149A (en) * 2011-09-30 2013-04-03 Arctic Circle Ltd Refrigeration Apparatus With Subcooler
CN107003044A (zh) * 2014-11-14 2017-08-01 开利公司 利用热能存储的节能循环
FR3063539A1 (fr) * 2017-03-03 2018-09-07 Electricite De France Installation frigorifique
WO2020251480A1 (fr) * 2019-06-14 2020-12-17 Maxeff Teknoloji̇ Anoni̇m Şi̇rketi̇ Machine de chauffage-refroidissement à source d'eau dotée d'unité de refroidissement de fluide frigorigène refroidissant à l'aide d'une source de refroidissement externe et procédé de chauffage-refroidissement

Also Published As

Publication number Publication date
ITBA20060054A1 (it) 2008-03-21
WO2008035386A3 (fr) 2008-05-29

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