EP2492615A1 - Machine de réfrigération optimisée pour réaliser des cycles de réfrigération en cascade - Google Patents

Machine de réfrigération optimisée pour réaliser des cycles de réfrigération en cascade Download PDF

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Publication number
EP2492615A1
EP2492615A1 EP11425041A EP11425041A EP2492615A1 EP 2492615 A1 EP2492615 A1 EP 2492615A1 EP 11425041 A EP11425041 A EP 11425041A EP 11425041 A EP11425041 A EP 11425041A EP 2492615 A1 EP2492615 A1 EP 2492615A1
Authority
EP
European Patent Office
Prior art keywords
compressor
heat exchanger
temperature
unit
heat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP11425041A
Other languages
German (de)
English (en)
Inventor
Giuseppe Giovanni Renna
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Thermocold Costruzioni SRL
Original Assignee
Thermocold Costruzioni SRL
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 Thermocold Costruzioni SRL filed Critical Thermocold Costruzioni SRL
Priority to EP11425041A priority Critical patent/EP2492615A1/fr
Priority to PCT/IB2012/050126 priority patent/WO2012114205A1/fr
Publication of EP2492615A1 publication Critical patent/EP2492615A1/fr
Withdrawn legal-status Critical Current

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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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves

Definitions

  • the present invention relates to a machine for carrying out a vapor compression refrigerating cycle apt to provide heat to the user for heating ambients or for the production of sanitary hot water, or for subtracting heat in order to guarantee the ambients to be cooled, which is particularly efficient to work at considerable temperature differences and possibly at particularly low outer temperatures. Moreover the present invention relates to a method for managing the devices constituting the circuit apt to carry out said cycle.
  • Cascade refrigerating cycles can be used both to provide the heat subtracted to the outer environment to the user as useful effect, and to dispose of the heat subtracted to the user in the environment.
  • the first is the typical case of heating ambients during winter and of providing heat for sanitary hot water.
  • the second case relates to the air-conditioning of ambients during summer.
  • the user requires heat for heating water for sanitary use and subtraction of heat for summer air-conditioning of ambients at the same time.
  • the object of the present invention is to provide a machine characterized by an optimized circuit able to operate two cascade refrigerating cycles in order to provide and/or subtract heat to the user and to provide sanitary hot water at the same time.
  • a control logic to manage a machine operating two cascade vapor compression refrigerating cycles.
  • the circuit operating the refrigerating cycle contained in the machine according to the present invention is made up of two units, an inner unit (1) where it is carried out the cycle allowing the production of water for heating, sanitary hot water and cooling water and an outer one (2) where it is carried out the lower cycle which exchanges heat with the outdoor air.
  • the inner unit (1) comprises at least a compressor (11), at least an exchanger able to exchange heat with the outer unit (12), an exchanger serving the users for heating/cooling (13) and a recuperative heat exchanger for heating sanitary hot water (14), a cycle inverting valve (15), a throttling valve (16) and three valves (17, 18 and 19), besides every necessary element to guarantee the correct functioning of machines operating vapor compression cycles, known according to the state of the art and therefore not described in detail.
  • this unit when this unit functions with refrigerating gas R134A, it can reach the condensation temperature of 85°C, beginning from evaporation temperatures up to 15°C, with maximum pressures around 30 bar.
  • the outer unit (2) comprises at least a compressor (21), a heat exchanger (22) able to give and absorb heat from the outdoor air or other heat source, such for example groundwater, superficial water or ground.
  • a heat exchanger can be made up of a battery finned and fanned by means of a fan (28) or a plate-type or a shell and tube exchanger with inverter controlled pump.
  • the outer unit comprises a cycle inverting valve (23), a throttling valve (24), three valves (25, 26, 27) and shares the heat exchanger (12) with the inner unit.
  • this unit can work with gas R410A and can work at very low outer air temperatures, up to -20°C, which imply evaporation temperatures around -25°C and condensation temperatures around 30°C.
  • the working pressure field is between 3 and 20 bar.
  • the refrigerating machine according to the present invention can provide various kinds of cycles, depending on the user temporary needs, useful to provide heat or cold to the user served by the exchanger (13) and heat for the production of sanitary hot water to the recuperative heat exchanger (14).
  • the useful effect required by the user is to provide cold to the exchanger (13).
  • the exchanger (13) functions as evaporator.
  • the heat exchanger (12) functions as condenser for the upper cycle operated by the inner unit (1) and as evaporator for the lower cycle operated by the outer unit (2), which disposes of the heat in the finned battery (22), or plate-type or shell and tube exchanger which in this functioning mode functions as condenser.
  • the rotation speed of the compressor of the inner unit (11) is controlled according to the temperature sensed by the probe (31) shown in figure 2 , arranged at the output of the exchanger (13) and to the evaporation pressure value of the outer unit (2) sensed by the probe (32), remaining around the value needed for maximizing the efficiency of the two units contemporaneous working. This value is approximately around 11.5 bar.
  • the rotation speed of the compressor (11) will be held at its maximum until the set-point for the temperature sensed by the probe (31) at the output of the exchanger (13) will be satisfied, decreased by 25% only in case the evaporation pressure value of the outer unit (2) in the exchanger (12) sensed by the probe (32) excesses the set "set-point" value for such parameter of a 4 bar difference.
  • the set set-point for the temperature of the compressor (11) is reached, it remains off until the value indicated by the readings of the respective probes is not in a predetermined tolerance interval.
  • the compressor (21) of the outer unit (2) which was on with the highest rotation speed, is switched off synchronously with the compressor (11) of the inner unit (1) in order to avoid the problems linked to the pressure differences in conjunction with asynchronous switching offs.
  • the two units provide synchronously the response to the alarm for high condensation pressure of the outer unit in the exchanger (22) as well, which can occur at high outer temperatures and which can be sensed by means of a pressure probe (33) which measures inside the exchanger (22).
  • the rotation speed of the compressor (11) decreases, thus decreasing the thermal power absorbed by the user in order to allow that the heat dissipation at the exchanger (22) lowers again the condensation pressure to acceptable levels.
  • the useful effect is to provide heat only to the exchanger (13) for heating ambients or only to the exchanger (14) for the production of sanitary hot water.
  • the compressor (11) When the set-point is reached, the compressor (11) is switched off, until the value indicated by the readings on the respective probes remains in the preset tolerance interval. When the reading on the probe (31) or (36) goes out of such interval, the compressor (11) is switched on again with rotation speed proportional to the derivative with respect to the time of the temperature reading, that is to the gradient of the temperature curve in the temperature/time graph. If the value of the temperature derivative with respect to the time tends to zero, the compressor (11) is actuated only if it is out of the tolerance interval, at the minimum speed. If the value of the temperature derivative with respect to the time tends to increase, the compressor (11) is actuated at an initial speed which is a fraction of the highest one (ex. 50%) and such speed is increased at preset time intervals according to the derivative of the temperature with respect to time, sensed at constant time intervals.
  • the outer unit (2) in this functioning mode is adjusted so that the evaporation pressure in the inner unit (1) in the exchanger (12), measured by means of the probe (37), is maintained constant.
  • the adjustment occurs at the rotation speeds of the compressor (21) and of the fans (28) initially at the maximum value.
  • the adjustment occurs in the same way as by means of the circulation pump.
  • the evaporation pressure at the exchanger (12) it is firstly reduced the rotation speed of the compressor (21) up to the lower limit of the adjustment field, and subsequently the rotation speed of the fan (28) possibly up to its complete switching off.
  • the modulation after reaching the set value of evaporation pressure, is carried out in differential mode.
  • the fan (28) When the evaporation pressure goes out or under the low limit of the tolerance interval, the fan (28) first and then the compressor (21) are re-activated at constant speed increments but always more frequent. The adjustment occurs according to the derivative with respect to the time of the evaporation pressure at the exchanger (12) sensed at regular time intervals by the probe (37).
  • the functioning mode 3 is activated when the demand on cold at the exchanger (13) for the summer air-conditioning of ambients and on heat at the exchanger (14) for the production of sanitary hot water occurs at the same time.
  • the outer unit (2) remains off and the inner unit (1) works in water/water mode.
  • the exchanger (13) functions as evaporator, and the exchanger (12) is not interested by this cycle, since the inner unit (1) condenses on the recuperative heat exchanger (14) and the outer unit (2) is off.
  • the rotation speed of the compressor (11) of the inner unit (1) is managed in the same way as for the functioning mode 2.
  • the rotation speed is adjusted in fact according to the set set-point for the temperature read by the probe (31), at reaching thereof the compressor (11) being stopped.
  • the compressor (11) is re-activated at speed which varies proportionally to the derivative with respect to the time of the temperature sensed by the probe (31), as stated above.
  • the outer machine can change the functioning cycle as well, thus allowing the exchanger (12) to function alternatively as condenser or evaporator for the inner unit (1), with the clear advantage of carrying out with the same machine a series of different cycles with the lowest number of heat exchangers, valves and other components.
  • the machine according to the present invention allows also to optimize the choice of coolants, thus allowing a control of the working pressures.
  • the choice of the coolant R410A in the first cycle allows also for very low temperatures of outdoor air, approximately up to -25°C, not to go under pressures lower than 1 bar, since the highest condensation temperatures the first cycle has to reach, do not exceed 30°C.
  • the machine according to the present invention can be realized with the functional units, the inner one and outer one, separated.
  • Such embodiment is particularly indicated for applications in places where the outer temperatures can be particularly low, for example lower than -10°C.
  • the components constituting the inner unit (1), and comprising every exchanger where the available thermo-vector fluids are treated are protected against the outer low temperatures and against the fluid freezing danger in the pipes.
  • FIG 3 it is shown by way of example and in a not limiting way, a possible introduction inside the equipment of a building of a machine according to the present invention, with the heat exchanger (13) serving a radiant panels heating device (41) supplied by the accumulation tank (42) and the heat exchanger (14) serving the water distributing equipment for sanitary use supplied by the tank (43) in which it is also stored the heat collected by the solar panels (44).
  • the machine according to the present invention can be realized with the functional units, the inner one and the outer one, enclosed in a sole equipment to be mounted outside, thus reducing at minimum the inner room of the building needed for installation. This embodiment is clearly advantageous in places where the temperatures can be considered constantly higher then -10°C.
  • the device object of the present invention allows to operate efficiently and with a reduced number of components, which are possibly integrated in a sole unit, every refrigerating cycle needed by the summer and winter air-conditioning of ambients and for the production of sanitary hot water. Further it is provided a managing logic of the device object of the present invention which allows to manage simply the two units, which constitute the device, in the various functioning conditions.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP11425041A 2011-02-22 2011-02-22 Machine de réfrigération optimisée pour réaliser des cycles de réfrigération en cascade Withdrawn EP2492615A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP11425041A EP2492615A1 (fr) 2011-02-22 2011-02-22 Machine de réfrigération optimisée pour réaliser des cycles de réfrigération en cascade
PCT/IB2012/050126 WO2012114205A1 (fr) 2011-02-22 2012-01-10 Machine de réfrigération optimisée pour réalisation de cycles de réfrigération en cascade

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11425041A EP2492615A1 (fr) 2011-02-22 2011-02-22 Machine de réfrigération optimisée pour réaliser des cycles de réfrigération en cascade

Publications (1)

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EP2492615A1 true EP2492615A1 (fr) 2012-08-29

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EP11425041A Withdrawn EP2492615A1 (fr) 2011-02-22 2011-02-22 Machine de réfrigération optimisée pour réaliser des cycles de réfrigération en cascade

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EP (1) EP2492615A1 (fr)
WO (1) WO2012114205A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59134469A (ja) * 1983-01-20 1984-08-02 松下電器産業株式会社 冷暖房給湯加熱装置
CN1436980A (zh) * 2003-02-28 2003-08-20 浙江大学 扩大在低温环境下热泵制热能力的方法及装置
WO2010098607A2 (fr) * 2009-02-25 2010-09-02 Kim Sang-Won Système de refroidissement et de chauffage utilisant un échangeur de chaleur en cascade

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000074514A (ja) * 1998-09-03 2000-03-14 Hitachi Ltd 蓄電式空気調和装置及びそれに用いられる冷熱源装置
WO2005052467A1 (fr) * 2003-11-28 2005-06-09 Mitsubishi Denki Kabushiki Kaisha Congelateur et conditionneur d'air
KR100565257B1 (ko) * 2004-10-05 2006-03-30 엘지전자 주식회사 압축기를 이용한 이차냉매사이클 및 이를 구비한 공기조화기
US7240509B2 (en) * 2005-09-14 2007-07-10 Kaori Heat Treatment Co., Ltd. Heating and cooling system
US8136365B2 (en) * 2007-07-02 2012-03-20 Hoshizaki Denki Kabushiki Kaisha Cooling apparatus having a variable speed compressor with speed limited on the basis of a sensed performance parameter
KR20100064751A (ko) * 2008-12-05 2010-06-15 (주)에뜨리 2단 압축 고온수 히트펌프 시스템
KR101639814B1 (ko) * 2009-11-20 2016-07-22 엘지전자 주식회사 냉장 및 냉동 복합 공조시스템

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59134469A (ja) * 1983-01-20 1984-08-02 松下電器産業株式会社 冷暖房給湯加熱装置
CN1436980A (zh) * 2003-02-28 2003-08-20 浙江大学 扩大在低温环境下热泵制热能力的方法及装置
WO2010098607A2 (fr) * 2009-02-25 2010-09-02 Kim Sang-Won Système de refroidissement et de chauffage utilisant un échangeur de chaleur en cascade

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Publication number Publication date
WO2012114205A1 (fr) 2012-08-30

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