EP1262722A2 - Installation frigorifique - Google Patents

Installation frigorifique Download PDF

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Publication number
EP1262722A2
EP1262722A2 EP02445030A EP02445030A EP1262722A2 EP 1262722 A2 EP1262722 A2 EP 1262722A2 EP 02445030 A EP02445030 A EP 02445030A EP 02445030 A EP02445030 A EP 02445030A EP 1262722 A2 EP1262722 A2 EP 1262722A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
circuit
primary heat
pump
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Withdrawn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
EP02445030A
Other languages
German (de)
English (en)
Other versions
EP1262722A3 (fr
Inventor
Lennart Asteberg
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.)
INGENJOERSFIRMA LENNART ASTEBERG HANDELSBOLAG
Original Assignee
Ingenjorsfirma Lennart Asteberg AB
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 Ingenjorsfirma Lennart Asteberg AB filed Critical Ingenjorsfirma Lennart Asteberg AB
Publication of EP1262722A2 publication Critical patent/EP1262722A2/fr
Publication of EP1262722A3 publication Critical patent/EP1262722A3/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Withdrawn legal-status Critical Current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
    • 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
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary 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
    • 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
    • F25B2400/06—Several compression cycles arranged in parallel
    • 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
    • F25B2400/22—Refrigeration systems for supermarkets
    • 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

Definitions

  • the invention relates to plant of the kind defined in the preamble of Claim 1.
  • refrigerator condensers The energy delivered by refrigerator condensers is often a heating source of interest with respect to heating processes and/or for property heating purposes (heating of apartment buildings or premises, tap water heating systems). This applies in particular to those refrigerating machines that are at work year-round. Examples of such refrigerators are refrigerators for food stores, industrial kitchens, refrigeration, cold-storage and freeze houses and also industrial processes.
  • a heat recovery plant is often installed, when there is a need for such energy at a reasonable distance from the heat sources.
  • One drawback with such heat recovery is that it is almost always necessary to recover the thermal energy at a temperature level which is higher than the temperature level of the ambient air; refrigerator condensers are normally cooled by ambient air.
  • This desideratum can be satisfied in a heat recovery system of the kind indicated, by allowing the system circuit to transport surplus heat from the condensers of the refrigerating machines via an environmentally acceptable refrigerant or coolant, for instance by a glycol/water mixture.
  • a refrigerant circuit will include a heat exchanger that delivers surplus heat to the ambient air, this type of system being designated an indirect system in the art.
  • a refrigerating plant will often consist of a plurality of refrigerating machines/refrigerating systems each having its own compressor, expansion valve, etc.
  • the machines often share a common refrigerant circuit. This means that all refrigerating machines operate at the same temperature of condensation, since they are cooled by the circuit coolant.
  • a system which lacks heat recovery can operate at a low coolant temperature of about 15°C, wherewith the machines will have a low driving energy requirement.
  • the requirement for recovered energy will vary from 0 and upwards. Because it is necessary to increase the energy input of all refrigerating machines connecting with the refrigerant circuit, merely to recover perhaps some few kilowatt hours, it may be that the increase in driving energy requirement for the compressors of the refrigerating machines will sometimes exceed the useful energy that can be recovered with the heat recovery circuit.
  • an object of the present invention is to provide plant with which the indicated drawback is eliminated either fully or partially.
  • the invention resides in coolant circuit that includes two primary heat exchangers with associated pumps which operate in opposite directions in the circuit, so as to form a circuit high-pressure side and a circuit low-pressure side.
  • a number of secondary heat exchangers are connected in parallel between the high and the low pressure sides, and are therewith connected at different distances from the primary heat exchangers.
  • Each secondary heat exchanger cools a condenser belonging to a refrigerating or freezing machine through which a refrigerant flows.
  • One primary heat exchanger dumps surplus heat into the environment (e.g. into the ambient air).
  • the other primary heat exchanger delivers heat to a heat recovery circuit.
  • the pump associated with said one primary heat exchanger is guided by the heat requirement of the heat recovering circuit.
  • the pump which is associated with said other primary heat exchanger is controlled by a pressure difference sensor which senses the pressure between the high and the low pressure sides of the refrigerant circuit, such as to maintain a chosen pressure difference.
  • Located on the outlet side of said other primary heat exchanger is a thermostat which maintains the refrigerant, or coolant, leaving said other primary heat exchanger at a chosen temperature level.
  • the refrigeration machines that are primarily intended to contribute heat to the heat recovery circuit are placed closest to the first primary heat exchanger in a given order.
  • Those secondary heat exchangers that lie nearest the second primary heat exchanger will be kept at the chosen lower temperature level, since these heat exchangers receive refrigerant chiefly directly from the second primary heat exchanger, meaning that the corresponding refrigeration machines obtain a low temperature of condensation and a relatively higher efficiency.
  • one single refrigeration machine may, of course, be utilised fundamentally for forming two or more heat sources which are coupled in series in the circulation circuit of the refrigeration machine via respective heat exchange units, and cooled at different temperature levels.
  • These heat sources may include condenser units belonging to one single heat pump and, in addition, a hot gas cooler and/or a condensate supercooler, or combinations thereof.
  • Certain types of heat pumps will also include a heat exchanger for cooling oil circulating in the compressor part of the heat pump.
  • This oil cooler may also be used as a heat-exchange unit connected-up in the heat recovery circuit. This enables heat to be delivered from one single refrigeration machine to two or more secondary heat exchangers at different temperature levels. However, for the sake of simplicity, the invention will be described primarily with reference to the simple case in which each secondary heat exchanger delivers heat from an affiliated refrigeration machine via its condenser unit.
  • this pump will compensate for an increasing rate of flow through the first primary heat exchanger, by lowering its speed of rotation.
  • speed of the pump of the second primary heat exchanger it is possible to control continuously the distribution between recovered energy and energy dumped into the environment between 0-100%.
  • the pressure of condensation of the individual refrigeration machines is controlled conventionally, internally in the refrigeration machine, by a self-acting valve, which regulates the flow rate of refrigerant to the condenser.
  • the valve is controlled by the pressure of condensation of the condenser.
  • the pressure of condensation can be controlled by controlling the effective cooling surface area in the condenser. This is achieved on the refrigerant side ("the freon side") of the system.
  • the thermostat located on the outlet side of the second primary heat exchanger controls the activation of the blowers (fans) that drive ambient air through the second primary heat exchanger to satisfy the refrigerating or cooling requirement.
  • the plant includes a circulation circuit 10, which contains a liquid, such as a glycol/water mixture.
  • the circuit includes a first primary heat exchanger 11 which transfers heat from the circuit 10 to a heat recovery circuit 14 through which a fluid flows.
  • the circuit 10 also includes a second primary heat exchanger 20, which delivers surplus heat to the environment, for instance to the ambient air.
  • the circuit 10 further includes a pump 12 (P2), which drives the refrigerant in the circuit 10 through the heat exchanger 11.
  • the primary heat exchanger 20 has an associated pump 21 (P1), which drives the circuit refrigerant through the primary heat exchanger 20 in a chosen direction.
  • the pumps 12, 21 operate in mutually opposite directions and therefore define therebetween a low pressure part 10a in the circuit 10.
  • the remaining part 10b of the circuit receives flow from the two heat exchangers 11, 20 and forms the high pressure part of the circulation circuit 10.
  • the heat exchangers 31, 32, 33 are connected in parallel between the circuit parts 10a, 10b and circuit refrigerant will flow therethrough due to the difference of pressure therebetween.
  • Secondary heat exchangers 31-33 are coupled at different distances along the circuit parts.
  • the secondary heat exchanger 33 that lies nearest to the primary heat exchanger 11 receives refrigerant of high temperature that defines the temperature of condensation for the condenser 53.
  • the secondary heat exchanger 32 next in line may possibly also receive from the heat primary exchanger 11 refrigerant of elevated temperature, and may possibly also receive a sub-flow of refrigerant from the primary heat exchanger 20, these sub-flows defining the temperature level on the condenser 52.
  • the secondary heat exchanger 31 nearest the second primary heat exchanger 20 will normally be supplied with refrigerant having the temperature defined by the thermostat 23 that controls the blower 20.
  • the secondary heat exchangers 31-33 in this order, will be provided primarily with relatively cold refrigerant from the primary heat exchanger 20, and that the secondary heat exchangers 33-31 will primarily be supplied with relatively hot refrigerant from the primary heat exchanger 11, and that the refrigerant distribution from these two sources will be set automatically in relation to the demand/supply of heat via the circuit 14.
  • GP1 Located between the circuit parts 10a, 10b is a pressure difference sensor 22 (GP1) which controls the pump 21.
  • GP3 Located on the outlet side of the primary heat exchanger 20 is a temperature sensor (GP3), which controls a blower (fan) 26 that regulates the rate of flow of the ambient air through the primary heat exchanger 20, so that the refrigerant output temperature from the primary heat exchanger 20 will be set to a pre-chosen value.
  • the pump 12 (P2) is controlled in keeping with the heat recovery requirement, wherewith the recovery circuit 14 may include a temperature sensor 13 (GT1) that controls the pump P2.
  • a temperature sensor 16 (GT2) may be coupled between the pump 12 and the first primary heat exchanger 11 to limit the refrigerant temperature to said heat exchanger 11 in an upward direction, in those instances when there is no market for the heat delivered to the heat exchanger 11. It can be seen that refrigerant exiting from the primary heat exchanger 11 first flows through the secondary heat exchanger 33, which thus cools the condenser 53 at a temperature level which is normally relatively high (depending on the return temperature of the recovery circuit). This means that although the refrigerating machine (the heat pump) 43 will operate at a relatively high temperature of condensation, i.e.
  • refrigerant leaving the primary heat exchanger 20 has the temperature defined by the sensor 23 and passes through the secondary heat exchanger 31 which cools an associated condenser 51 at this temperature and gives the associated refrigeration machine (the heat pump) a relatively high efficiency.
  • the refrigeration machines 41-43 can operate at different temperatures of condensation, wherewith the heat supply to the heat recovery circuit 14 will consist of heat from those refrigeration machines 43, 42, 41 that lie, in turn, nearest the first primary heat exchanger. Because the pump P1 is controlled by a difference pressure transmitter 22, there is established a constant driven pressure to the secondary heat exchangers 31, 32, 33. This causes the pump 21 to slow down automatically when the pump 12 belonging to the first primary heat exchanger 11 begins to deliver a rate of flow that satisfies the heat requirement of the recovery circuit 14.
  • those refrigeration machines 41, 42, 43 that lie nearest to the second primary heat exchanger or circuit cooler 20 that dumps heat into the ambient air can operate at a high efficiency, i.e. a relatively low temperature of condensation, to the extent in which heat delivered from the condensers 53, 52, 51 is not required for supplying heat to the recovery circuit.
  • the rates of flow through the secondary heat exchangers 31, 32, 33 are self-setting and controlled by the pump 21 and its associated pressure difference sensor on the one hand, and by the pump P2 and the temperature sensor 13 of the recovery circuit on the other hand, wherewith the refrigeration machines 41-43 can operate at different temperatures of condensation for prioritising high efficiency in the case of certain refrigeration machines on the one hand, and a high heat emission from other refrigeration machines.
  • the relative distances of respective secondary heat exchangers 31-33 from respective primary heat exchangers 11, 20 is significant in respect of the temperature level at which the corresponding condensers 51-53 can operate.
  • the invention thus provides a method of controlling the refrigerant in the circuit 10 so that only those refrigeration machines from which surplus heat can be utilised will work at high temperatures of condensation and therewith require relatively higher energy inputs.
  • the distribution of energy to the heat recovery circuit and to the ambient air can be made continuous, i.e. smooth.
  • the two pumps 12, 21 constitute a reserve one for the other, therewith enhancing the reliability of the plant in operation. Because the rates of flow through the secondary heat exchangers 31-33 are self-regulating, no separate control valves are required, which affords certain advantages since control valves normally cause drops in pressure that must be overcome with the aid of the pumps, i.e. with the pump driving energy.
  • a refrigerant circuit 10 includes a first primary heat exchanger 11, which delivers heat to a recovery circuit 14, and a second primary heat exchanger 20 which pumps heat into the ambient air.
  • Each primary heat exchanger 11, 20 has an associated pump 12, 21 which pumps circuit liquid in opposite directions, so that the circuit will obtain a low pressure side 10a and high pressure side 10b, between which a number of secondary heat exchangers 31-33 are coupled in parallel at different distances apart.
  • Each such parallel-coupled heat exchanger 31-33 cools a refrigerating machine 41-43 belonging to respective condensers 51-53.
  • one single refrigeration machine 41' can include a condenser unit which has three series-coupled units 51'-53' that function as a hot gas cooler, actually a condenser and condensate supercooler respectively, and are arranged in heat-exchange relationship with a respective secondary heat exchanger 31-33 at different temperature levels.
  • the refrigeration machine 41' may include an oil cooler 54', which forms a further secondary unit 34 in the heat recovery circuit.
  • Fig. 2 also shows that the heat pump circuit may include a drying filter 55 and an inspection glass/?/56 for the refrigerant, between the condenser 32 and the supercooler 33.
  • the heat pump circuit also includes an evaporator 59 and an expansion valve 60. It will be understood that the heat exchangers 31-34 may be coupled in series, in temperature order, in the heat recovery circuit 10 (Fig. 1), possibly together with further units.
  • a pressure difference sensor 22 controls the pump 21 of the primary heat exchanger 20.
  • the pump 12 of the heat exchanger 11 is controlled by the heat requirement of the recovery circuit 14.
  • the refrigerating effect of the primary heat exchanger 20 is controlled by a thermostat 23 on the outlet side of said primary heat exchanger 20.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Other Air-Conditioning Systems (AREA)
EP02445030A 2001-05-31 2002-03-11 Installation frigorifique Withdrawn EP1262722A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0101916 2001-05-31
SE0101916A SE517594C2 (sv) 2001-05-31 2001-05-31 Anläggning för värmeåtervinning från ett flertal kylmaskinerier

Publications (2)

Publication Number Publication Date
EP1262722A2 true EP1262722A2 (fr) 2002-12-04
EP1262722A3 EP1262722A3 (fr) 2003-10-15

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP02445030A Withdrawn EP1262722A3 (fr) 2001-05-31 2002-03-11 Installation frigorifique

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EP (1) EP1262722A3 (fr)
SE (1) SE517594C2 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1637819A2 (fr) 2004-09-10 2006-03-22 Ingenjörsfirma Lennart Asteberg Handelsbolag Installation frigorifique
BG65811B1 (bg) * 2004-02-09 2009-12-31 "Солкав България" Оод Инсталация за нагряване и охлаждане
ITFI20130244A1 (it) * 2013-10-16 2015-04-17 Frigel Firenze S P A "unita' frigorifera multistadio per la refrigerazione di un fluido di processo"
WO2015071511A1 (fr) * 2013-11-18 2015-05-21 Ávila Chillida Vicente Système de réfrigération industriel
US9816739B2 (en) 2011-09-02 2017-11-14 Carrier Corporation Refrigeration system and refrigeration method providing heat recovery
EP3076110B1 (fr) * 2015-03-30 2019-02-27 Viessmann Werke GmbH & Co. KG Systeme fluidique et procede de commande d'un systeme fluidique
IT202000016504A1 (it) * 2020-07-08 2022-01-08 Carel Ind Spa Impianto di refrigerazione con circuito di raffreddamento

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE0300172D0 (sv) * 2003-01-24 2003-01-24 Pettersson Mikael Frikyla
CN104776665A (zh) * 2015-04-02 2015-07-15 南京祥源动力供应有限公司 一种自动控制的节能型冷却供水系统

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3910345A (en) * 1974-04-22 1975-10-07 James J Whalen Heating and cooling system
EP0887599A1 (fr) * 1996-12-27 1998-12-30 Daikin Industries, Limited Appareil de refrigeration et son procede de fabrication
US6205795B1 (en) * 1999-05-21 2001-03-27 Thomas J. Backman Series secondary cooling system

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3910345A (en) * 1974-04-22 1975-10-07 James J Whalen Heating and cooling system
EP0887599A1 (fr) * 1996-12-27 1998-12-30 Daikin Industries, Limited Appareil de refrigeration et son procede de fabrication
US6205795B1 (en) * 1999-05-21 2001-03-27 Thomas J. Backman Series secondary cooling system

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BG65811B1 (bg) * 2004-02-09 2009-12-31 "Солкав България" Оод Инсталация за нагряване и охлаждане
EP1637819A2 (fr) 2004-09-10 2006-03-22 Ingenjörsfirma Lennart Asteberg Handelsbolag Installation frigorifique
EP1637819A3 (fr) * 2004-09-10 2006-12-27 Ingenjörsfirma Lennart Asteberg Handelsbolag Installation frigorifique
US9816739B2 (en) 2011-09-02 2017-11-14 Carrier Corporation Refrigeration system and refrigeration method providing heat recovery
ITFI20130244A1 (it) * 2013-10-16 2015-04-17 Frigel Firenze S P A "unita' frigorifera multistadio per la refrigerazione di un fluido di processo"
WO2015071511A1 (fr) * 2013-11-18 2015-05-21 Ávila Chillida Vicente Système de réfrigération industriel
EP3076110B1 (fr) * 2015-03-30 2019-02-27 Viessmann Werke GmbH & Co. KG Systeme fluidique et procede de commande d'un systeme fluidique
IT202000016504A1 (it) * 2020-07-08 2022-01-08 Carel Ind Spa Impianto di refrigerazione con circuito di raffreddamento
WO2022009106A1 (fr) * 2020-07-08 2022-01-13 Carel Industries S.p.A. Installation de réfrigération avec circuit de refroidissement

Also Published As

Publication number Publication date
SE0101916L (sv) 2002-06-25
SE517594C2 (sv) 2002-06-25
EP1262722A3 (fr) 2003-10-15
SE0101916D0 (sv) 2001-05-31

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