EP1637819A2 - Installation frigorifique - Google Patents

Installation frigorifique Download PDF

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Publication number
EP1637819A2
EP1637819A2 EP05445051A EP05445051A EP1637819A2 EP 1637819 A2 EP1637819 A2 EP 1637819A2 EP 05445051 A EP05445051 A EP 05445051A EP 05445051 A EP05445051 A EP 05445051A EP 1637819 A2 EP1637819 A2 EP 1637819A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat
pump
circuit
pressure side
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Withdrawn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
EP05445051A
Other languages
German (de)
English (en)
Other versions
EP1637819A3 (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.)
Ingenjorsfirma Lennart Asteberg HB
Original Assignee
Ingenjorsfirma Lennart Asteberg HB
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 HB filed Critical Ingenjorsfirma Lennart Asteberg HB
Publication of EP1637819A2 publication Critical patent/EP1637819A2/fr
Publication of EP1637819A3 publication Critical patent/EP1637819A3/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Withdrawn legal-status Critical Current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
    • 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
    • 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 a plant of the kind defined in the preamble of the accompanying claim 1.
  • a plant of this kind is earlier known from EP-A-02445030.6.
  • This earlier known plant comprises a refrigerant circuit that includes a first pump for driving refrigerant through a heat consumer, at least two secondary heat exchangers that are connected in parallel across circuit conducting portions that connect to the heat consumer, wherein the secondary heat exchangers are adapted to cool a respective heat emitting unit through which refrigerant flows and which is associated with at least one cooling/chilling plant such as a refrigerator or freezer.
  • the refrigerant circuit includes a primary heat exchanger which functions to emit heat from the environmental surroundings, preferably to atmospheric air.
  • the secondary heat exchangers are connected in the circuit, between the heat consumer and the primary heat exchanger.
  • the primary heat exchanger includes a second pump which drives refrigerant in a pre-determined direction through the primary heat exchanger.
  • the first pump is adapted to drive the refrigerant in a pre-determined direction through the heat consumer.
  • the first pump and the second pump are adapted to drive the refrigerant in mutually opposite directions, such that the circuit on a low pressure side from which the pumps pump refrigerant and the circuit on a high pressure side to which the pumps pump refrigerant, a pressure difference sensor detects the pressure difference between the low pressure side and the high pressure side of the circuit, and wherein the first pump is controlled to satisfy the heat requirement of the heat consumer.
  • the pump of the primary heat exchanger is controlled by the pressure difference sensor, meaning that the flow of refrigerant passing the primary heat exchanger varies. Consequently, there is a danger that the refrigerant flowing through the channels of this heat exchanger will change from a turbulent flow to a laminar flow, therewith resulting in a significant change in the Reynold's number and thus in the transfer of heat from the refrigerant to the heat-exchanger channels/conductors through which the refrigerant flows. This problem need not normally occur, provided that the refrigerant cooler is dimensioned correctly.
  • the refrigerant cooler/ heat exchanger installed in the plant is initially much too small, in other words has relatively small heat exchanging surfaces
  • this worsening of the heat transfer between the refrigerant and the heat exchanger pipe can have a significant influence and cause the capacity of the refrigerant cooler/ heat exchanger to decrease.
  • the fans (or blowers) of the heat exchanging arrangement can consume a relatively large amount of energy when the heat exchanging surfaces of the heat exchanger are meagre, and vice versa. When the heat exchanger has meagre dimensions, this can mean that the amount of energy supplied to the fans/blowers of the heat exchanger must be increased, something that is, of course, undesirable.
  • an object of the present invention is to avoid the indicated problem, either completely or partially, in a plant of the described earlier known kind.
  • the present invention basically involves driving the pump of the primary heat exchanger so as to deliver a generally constant flow rate; establishing a shunt line between the low pressure side and the high pressure side; providing a flow regulating device for controlling the flow through the shunt line; and providing a pressure difference sensor for controlling the flow regulating device such as to maintain a generally constant pressure difference between the low pressure side and the high pressure side.
  • the invention enables a constant flow of refrigerant to be maintained through the primary heat exchanger, therewith retaining the turbulence of the refrigerant in the exchanger; while, at the same time, maintaining a constant pressure difference between the high pressure and the low pressure side and allowing a variable flow of refrigerant to the condenser.
  • the present invention avails itself of the advantage that a pump that is constructed to run at a fixed speed normally occurs a lower cost that a pump which is designed to be driven at a variable speed.
  • the condensing pressure of the individual refrigerating plants is controlled by a valve that regulates the refrigerant flow through the condenser.
  • the valve is controlled by the condensing pressure or by the temperature of the exiting refrigerant.
  • the condensing pressure can be controlled by controlling the effective cooling surface in the condenser. This takes place on the refrigerant side (the Freon side) of the system.
  • the thermostat located on the outlet side of the second primary heat exchanger controls activation of the fans/blowers that drive ambient air through said second primary heat exchanger so as to satisfy cooling requirements.
  • the plant comprises a circulation circuit 10 that contains a liquid, such as a glycol/aqueous mixture.
  • the circuit includes a heat consumer, which is represented by a heat exchanger 11 and which transfers heat from the circuit 10 to a heat recovery circuit 14 through which fluid passes.
  • the circuit 10 also includes a primary heat exchanger 20 with which excess heat is emitted to the surroundings, for instance to ambient air.
  • the circuit 10 further includes a pump 12 (P2) which drives the refrigerant in the circuit 10 through the heat exchanger 11.
  • a pump 21 (P1) which drives the refrigerant in the circuit 10 in a chosen direction through the heat exchanger 20.
  • the pumps 12, 21 operate in mutually opposite directions and therefore define therebetween a low pressure part 10a in the circuit 10.
  • the circuits 10, 14 may be connected to one another directly, therewith enabling the heat exchanger to be eliminated.
  • the remaining part 10b of the circuit receives refrigerant from the two heat exchangers 11, 12 and therewith forms the high pressure part of the circuit 10.
  • Heat exchangers 31, 32, 33 are connected in parallel between the circuit parts 10a, 10b and are through passed by the refrigerant in the circuit 10 as a result of the pressure difference therebetween.
  • the heat exchangers 31-33 are connected at different distances around the circuit parts.
  • the heat exchanger 33 that lies nearest the heat exchanger 11 receives refrigerant of high temperature that defines the condensing temperature of the condenser 53.
  • the next heat exchanger 32 in line may possibly also receive from the heat exchanger 11 refrigerant of elevated temperature, and may also possibly receive a sub-flow of refrigerant from heat exchanger 20, these sub-flows defining the temperature level of the condenser 52.
  • the heat exchanger 31 located closest to the heat exchanger will, of course, be supplied with refrigerant at the temperature defined by the thermostat 23 that controls the fan or blower 26.
  • the heat exchangers 31-33 will, in this order, primarily be supplied with relatively cold refrigerant from the heat exchanger 20, and that the heat exchangers 33-31 will primarily be supplied with relatively warm refrigerant from the heat exchanger 11, and that the division of refrigerant from both of said sources will be set automatically in accordance with demand/supply of heat via the circuit 14.
  • the pump 21 is driven at a pre-set constant speed, so as to deliver a generally constant flow of refrigerant to the heat exchanger 20.
  • a pressure difference sensor 22 (GP1) is provided between the circuit parts 10a, 10b.
  • Extending between the circuit parts 10a, 10b is a shunt line 60 which includes a flow regulating device, for instance a throttle valve 61, which is controlled by the pressure difference sensor 22 so as to establish a pre-set constant pressure difference between the circuit parts 10a, 10b.
  • the shunt line 60 connects with the low pressure side 10 immediately downstream of the heat exchanger 20.
  • a temperature sensor which controls a fan/blower 26 that regulates the flow of ambient air through the heat exchanger 20 so as to set the surface temperature of the refrigerant from the heat exchanger 20 to a pre-chosen value.
  • the pump 12 (P2) is controlled by 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 connected between the pump 12 and the heat exchanger 11 so as to restrict the temperature of the refrigerant passing to the heat exchanger 11 in an upward sense. In this case none of the delivered heat is passed to the heat exchanger 11?. It will be seen that refrigerant exiting from the heat exchanger 11 first flows through the 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 the refrigerating plant (the heat pump) 43 has to operate at a relatively high condensing temperature, i.e.
  • the refrigerating plants 41-43 are able to operate at different condensing temperatures, wherein heat is supplied to the heat recovery circuit 14 from the refrigerating plants 43,42,41 that lie closest to the first heat exchanger in that order.
  • the invention achieves a constant flow of refrigerant through the heat exchanger 20 while, at the same time, maintaining a constant pressure difference from the circuit parts 10a, 10b and a variable flow of refrigerant to the condensers.
  • the refrigerating plants 41, 42, 43 that lie closes to the second heat exchanger 20, which dumps heat to the ambient air, are able to operate at a high degree of efficiency, i.e. a relatively low condenser temperature, to the extent that the heat emitted from the condensers 53, 52, 51 is not required to deliver heat to the recovery circuit.
  • the flow of refrigerant through heat exchangers 31, 32, 33 of the circuit 10 is self-adjusting and is controlled by the constant flow generated by the pump 21, the flow shunted through the shunt line 60 and the control valve 61 (which is steered by the pressure difference sensor to create a constant pressure difference between the circuit parts 10a, 10b), and the flow generated by the pump P2 (which, in turn, is controlled by temperature sensor 13 of the recovery circuit), wherein the refrigerating plants 41-43 are able to operate at different condensing temperatures so as to prioritize a high efficiency in respect of given refrigerating plants in a selected order on the one hand, and high heat emission from other refrigerating plants on the other hand?.
  • the mutual distance of the heat exchangers 31-33 from respective heat exchangers 11, 20 is significant to the temperature level at which the corresponding condensers 51-53 can operate.
  • the plant provides a manner of controlling the refrigerant in the circuit 10 so that only those refrigerating plants from which surplus heat can be utilized will operate at a high condensing temperature and therewith require higher energy consumption.
  • the distribution of energy to the heat recovery circuit and to the ambient air can be made continuous.
  • a shunt line 80 between the outlet sides of the pumps 21 and a valve 81, normally closed, in the line 80.
  • a valve 81 can be opened should one of the pumps 21, 12 malfunction.
  • the two pumps 12, 21 function as a reserve for one another, therewith enhancing the operational reliability of the plant.
  • the condensing pressure in respective refrigerating plants is controlled by a valve 70 in the supply line to said condenser heat exchangers 31-33.
  • This valve 70 is controlled by the condensing pressure (not shown) of the plant or by the temperature of the return flow from respective heat exchangers 31-33. Because the flow through the heat exchangers 31-33 is self-regulating no special control valves are required, which is beneficial due to the fact that control valves normally cause pressure drops that must be overcome with the aid of the pumps, i.e. the pump driving energy.
  • Each such parallel-connected heat exchangers 31-33 cools a respective condenser 51-53 belonging to a refrigerating plant 41-43.
  • a single refrigerating plant 41' may have a condenser unit that includes 3 series-connected units 51'-53' which operate as hot gas coolers, actually as condensers and condensate-supercoolers respectively, and which are arranged in heat-exchanging relationship with a respective heat exchanger 31-33 at different temperature levels.
  • the refrigeration plant 41' may include an oil cooler 54' which forms a further secondary unit 34 in the heat recovery circuit.
  • the alternative shown in figure 2 also includes a heat pump circuit that may have a drying filter 55 and a refrigerant viewing glass 56 between the condenser 32 and the supercooler 33.
  • the heat pump circuit also includes an evaporator 59 and an expansion valve 60.
  • heat exchangers 31-34 may be coupled in series, in a temperature order, in the heat recovery circuit 10 (figure 1) optionally together with further units.
  • a pressure difference sensor 22 controls the pump 21 of the heat exchanger 20.
  • the pump 12 of the heat exchanger 11 is controlled by the heat requirement of the recovery circuit 14.
  • the cooling effect of the heat exchanger 20 is controlled by a thermostat 33 on the outlet side of said exchanger 20.

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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)
  • Air Conditioning Control Device (AREA)
EP05445051A 2004-09-10 2005-06-22 Installation frigorifique Withdrawn EP1637819A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE0402168A SE527635C2 (sv) 2004-09-10 2004-09-10 Kylmaskinanläggning

Publications (2)

Publication Number Publication Date
EP1637819A2 true EP1637819A2 (fr) 2006-03-22
EP1637819A3 EP1637819A3 (fr) 2006-12-27

Family

ID=33308746

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05445051A Withdrawn EP1637819A3 (fr) 2004-09-10 2005-06-22 Installation frigorifique

Country Status (2)

Country Link
EP (1) EP1637819A3 (fr)
SE (1) SE527635C2 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8924311B2 (en) 2009-10-15 2014-12-30 World's Fresh Waters Pte. Ltd. Method and system for processing glacial water
US9010261B2 (en) 2010-02-11 2015-04-21 Allen Szydlowski Method and system for a towed vessel suitable for transporting liquids
US9017123B2 (en) 2009-10-15 2015-04-28 Allen Szydlowski Method and system for a towed vessel suitable for transporting liquids
US9371114B2 (en) 2009-10-15 2016-06-21 Allen Szydlowski Method and system for a towed vessel suitable for transporting liquids
US9521858B2 (en) 2005-10-21 2016-12-20 Allen Szydlowski Method and system for recovering and preparing glacial water
US11584483B2 (en) 2010-02-11 2023-02-21 Allen Szydlowski System for a very large bag (VLB) for transporting liquids powered by solar arrays

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1262722A2 (fr) 2001-05-31 2002-12-04 Ingenjörsfirma Lennart Asteberg AB Installation frigorifique

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001019519A1 (fr) * 1999-09-16 2001-03-22 Mirai Electronics Ab Systeme de chambre d'essais climatiques, et procede de fonctionnement correspondant

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1262722A2 (fr) 2001-05-31 2002-12-04 Ingenjörsfirma Lennart Asteberg AB Installation frigorifique

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9521858B2 (en) 2005-10-21 2016-12-20 Allen Szydlowski Method and system for recovering and preparing glacial water
US8924311B2 (en) 2009-10-15 2014-12-30 World's Fresh Waters Pte. Ltd. Method and system for processing glacial water
US9017123B2 (en) 2009-10-15 2015-04-28 Allen Szydlowski Method and system for a towed vessel suitable for transporting liquids
US9371114B2 (en) 2009-10-15 2016-06-21 Allen Szydlowski Method and system for a towed vessel suitable for transporting liquids
US10399642B2 (en) 2009-10-15 2019-09-03 World's Fresh Waters Pte. Ltd Method and system for processing glacial water
US10435118B2 (en) 2009-10-15 2019-10-08 Allen Szydlowski Method and system for a towed vessel suitable for transporting liquids
US10953956B2 (en) 2009-10-15 2021-03-23 Allen Szydlowski Method and system for a towed vessel suitable for transporting liquids
US9010261B2 (en) 2010-02-11 2015-04-21 Allen Szydlowski Method and system for a towed vessel suitable for transporting liquids
US11584483B2 (en) 2010-02-11 2023-02-21 Allen Szydlowski System for a very large bag (VLB) for transporting liquids powered by solar arrays

Also Published As

Publication number Publication date
SE527635C2 (sv) 2006-04-25
EP1637819A3 (fr) 2006-12-27
SE0402168L (sv) 2006-03-11
SE0402168D0 (sv) 2004-09-10

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