WO2004111558A1 - Systeme de pompe a chaleur et procede de regulation d'un tel systeme - Google Patents

Systeme de pompe a chaleur et procede de regulation d'un tel systeme Download PDF

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Publication number
WO2004111558A1
WO2004111558A1 PCT/SE2003/000961 SE0300961W WO2004111558A1 WO 2004111558 A1 WO2004111558 A1 WO 2004111558A1 SE 0300961 W SE0300961 W SE 0300961W WO 2004111558 A1 WO2004111558 A1 WO 2004111558A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat pump
refrigerant
evaporator
heating means
temperature
Prior art date
Application number
PCT/SE2003/000961
Other languages
English (en)
Inventor
Jan TEDSJÖ
Timo HEIKKILÄ
Original Assignee
Strateg Trade 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 Strateg Trade Ab filed Critical Strateg Trade Ab
Priority to AU2003239003A priority Critical patent/AU2003239003A1/en
Priority to PCT/SE2003/000961 priority patent/WO2004111558A1/fr
Publication of WO2004111558A1 publication Critical patent/WO2004111558A1/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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/19—Pressures
    • F25B2700/197—Pressures of the evaporator
    • 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

Definitions

  • the invention relates to a heat pump system and a method for controlling such a system to improve the operating range of the system, particularly at low temperatures.
  • Heat pumps are commonly use for energy saving purposes for a wide range of applications, e.g. for heating ventilation air or water in a building.
  • a conventional heat pump will have a reduced capacity for delivering heat as the temperature of the source drops. The capacity will begin to reduce when the said temperature drops below approximately +7 0 C and will for all practical purposes cease at approximately -7°C.
  • the invention aims to solve the above problems by providing means allowing heat pump systems to be used over a wider range of temperatures with a maintained capacity for delivering heat.
  • the invention relates to a heat pump system provided with a compressor means, a condenser, a pressure reduction means, an evaporator, a refrigerant, a refrigerant circulating conduit connecting said compressor means, said condenser, said pressure reduction means and said evaporator, and an electronic control unit.
  • the heat pump system is further provided with at least one controllable heating means for heating said refrigerant, which heating means is located between a first position downstream of the condenser and a second position upstream of the compressor means.
  • An ambient medium such as air or water passes through the evaporator to allow the refrigerant to absorb heat.
  • air to be used for heating purposes is forced through the condenser by a fan. This will be described in further detail below.
  • controllable heating means is positioned in a low pressure section of the heat pump system, which section includes the evaporator and the refrigerant circulating conduit leading up to the compressor.
  • the pressure reduction means may be a separate expansion valve placed before the evaporator, or be integrated in the evaporator, in the form of capillary tubes. In the latter case the evaporator is considered to be a part of the low pressure section , even though it also functions as a pressure reduction means.
  • controllable heating means is positioned in the evaporator.
  • the heating means may either be placed in or adjacent one or more conduits in the evaporator.
  • the term adjacent includes various arrangements of the heating means.
  • the heating means may for instance be placed alongside, or parallel, to one or more conduits, as well as around the conduits, either concentric or s a helical coil.
  • the conduits may be coiled around the heating means.
  • the heating means can also be arranged as a heat exchanger, such as a coaxial or plate heat exchanger, through which the refrigerant and the heated liquid passes, separated from the ambient medium.
  • the heating means is preferably arranged adjacent and parallel to the conduits.
  • controllable heating means may instead, or additionally, be positioned in or adjacent the refrigerant circulating conduit leading up to the compressor.
  • controllable heating means may instead, or additionally, be positioned adjacent and immediately upstream of the evaporator, or in or adjacent the refrigerant circulating conduit downstream of the condenser.
  • the controllable heating means may comprise a tank filled with a suitable liquid, which tank is provided with an immersion heater. The conduit may pass through said tank to be heated to a desired temperature.
  • the tank may be arranged as a heat exchanger, such as a coaxial or plate heat exchanger, through which the refrigerant and the heated liquid passes.
  • a liquid for use in such a tank may be an alcohol, such as methanol, or a similar suitable liquid.
  • the liquid should preferably have suitable anti-freezing properties.
  • the heating means is preferably an electric heater, but other sources of heat, such as a liquid or gas heat exchanger, may also be used depending on availability.
  • controllable heating means is actuated when the temperature of a medium used to heat the evaporator drops below a predetermined value.
  • the medium may be either air, water or any other suitable source for heating the evaporator.
  • the arrangement may be applied to any combination of air/air, air/water, water/air or water/water for the evaporator and condenser. Any suitable refrigerant may be used in the system, although media such as 407c or 410a are preferred due to the relatively high pressure used in the system according to the invention.
  • a temperature sensor is provided to determine the temperature of said medium.
  • the controllable heating means may be typically actuated when the temperature of said medium drops below +7°C.
  • controllable heating means is actuated gradually to maintain an evaporation temperature of the refrigerant at a predetermined value.
  • a temperature sensor may be provided to determine the evaporation temperature of said refrigerant.
  • the controllable heating means is actuated gradually to maintain an evaporation pressure of the refrigerant at a predetermined level.
  • a pressure sensor may be provided to determine the evaporation pressure of said refrigerant.
  • the invention further relates to a method for controlling a heat pump system provided with a compressor means, a condenser, a pressure reduction means, an evaporator, a refrigerant, a refrigerant circulating conduit connecting said compressor means, said condenser, said pressure reduction means and said evaporator, and an electronic control unit.
  • the method involves heating a section of the heat pump system by means of at least one controllable heating means for heating said refrigerant, which heating means can be located between a first position downstream of the condenser and a second position upstream of the compressor means, when at least one predetermined condition is fulfilled.
  • the method involves actuating the controllable heating means when the temperature of a medium used to heat the evaporator drops below a predetermined value
  • the method involves controlling the heating means in relation to the temperature of said medium. Consequently, the amount of heat supplied by the heating means is a function of the temperature of the medium.
  • the controllable heating means may be actuated to maintain an evaporation temperature of the refrigerant at said predetermined value and/or to maintain an evaporation pressure of the refrigerant at a predetermined level.
  • the controllable heating means is used to heat the evaporator in order to maintain a pressure and temperature in the evaporator at a level that is equivalent to a predetermined minimum ambient temperature at which the heat pump will remain operational without losing capacity to deliver heat. Consequently the heat pump can maintain its capacity to supply heat, not only at relatively low temperatures where a conventional heat pump has a reduced capacity (from +7 0 C to about -7°C) but also at sub-zero temperatures where such heat pumps may cease to operate altogether.
  • Figure 1 shows a shows a diagram illustrating a heat pump system according to one embodiment of the invention
  • Figure 2 shows a diagram illustrating a heat pump system according to an alternative embodiment of the invention
  • Figure 3 shows a diagram illustrating a heat pump system according to a further alternative embodiment of the invention. MODES FOR CARRYING OUTTHE INVENTION
  • Figure 1 shows a heat pump system provided with a compressor 1 , a condenser 2, an expansion valve 3, an evaporator 4.
  • the component parts are connected by a refrigerant circulating conduit containing a refrigerant.
  • the compressor 1 is provided with an upstream pressure switch 5 in a low pressure section of the circulating conduit, and a downstream pressure switch 6 in a high pressure section of the circulating conduit.
  • the pressure switches 5, 6 are used to regulate the compressor, so that a relatively constant, high pressure is delivered.
  • a typical absolute pressure in the high pressure section is 19-20 bar, preferably 19,2-19,5 bar.
  • the absolute pressure is 4-5 bar, preferably 4,2 bar.
  • the refrigerant flows to the evaporator 4 via an expansion valve 3.
  • the expansion valve 3 is connected to a bulb 9 located downstream of the evaporator 4 and is controlled to maintain a constant pressure drop over the evaporator 4 located in the low pressure section of the circulating conduit.
  • the evaporator 4 contains a heat exchanging arrangement in the form of tubes or coils 10, in which heat is transferred from an air flow supplied by a fan 11. In this case ambient, outside air supplied by the fan 11 passes through the evaporator 4, in which heat is transferred from the air flow to the refrigerant.
  • the refrigerant is then returned to the compressor 1 to close the circulating conduit, while the air is returned to the atmosphere as indicated by the arrow A 2 .
  • the heat pump system is also provided with a controllable heating means for allowing heating of said refrigerant as it passes through the evaporator 4.
  • the heating means is an electrical heater 12 placed adjacent the tubes 10 in the evaporator 4 and controlled by an electronic control unit ECU. Although the following text refers to "an electrical heater 12", the heating means is actually arranged to distribute heat evenly through the entire evaporator 4.
  • the control unit ECU is connected to a triac device 14 that is used to supply a pulsed electrical power to all resistor elements of the electrical heater 12. By pulsing the electrical power to the electrical heater it is possible to control the temperature of the evaporator accurately.
  • the control unit ECU is connected to an electronic pressure switch 15, generating a signal representing the pressure of the refrigerant as it leaves the evaporator 4, an evaporation sensor 16, giving the temperature in the evaporator 4, and an ambient air temperature sensor 17, giving the temperature of the medium used to heat the evaporator.
  • the control unit ECU is arranged to control the supply of heat to the evaporator 4.
  • the triac device 14 may of course be integrated in the control unit ECU. Alternative means for controlling the electrical power to the heater may also be used.
  • the controllable heating means is actuated when the temperature of ambient air sensed by the sensor 17 drops below a set limit.
  • This limit can be set to a suitable value preferably, but not necessarily, within the range 0°C to -6°C. In the current embodiment, the limit is set at -3 0 C to -4 0 C to maintain a desired temperature in the heated air supplied by the condenser.
  • the control unit ECU will then transmit a signal to the triac device 14, so that pulses of electrical power is supplied to the heater 12.
  • the feedback signals from the pressure and temperature sensors 15, 16 in the evaporator 4 are then used to maintain a pressure and temperature in the evaporator 4 at a level that is equivalent to an ambient temperature of about +7°C.
  • the electrical heater 12 is controlled constantly as long as the ambient temperature is below the set limit. As the ambient temperature drops, the triac device 14 is controlled to increase the amount of electrical power to the heating means 12.
  • the number of electrical heaters associated with the tubes or coils in the evaporator, as well as the rated output of each heater, is determined by the climate at the location of the installation. By a suitable dimensioning of the electrical heaters the heat pump arrangement may remain fully operational at ambient temperatures of -20°C and below.
  • a suitable temperature for actuating the electrical heater may be selected depending on a number of different factors, such as the type of refrigerant used, the compression ratio and the desired temperature of the air leaving the condenser. However, for the current embodiment the capacity of the heat pump system to deliver heat will start to decrease at about +7 0 C. However, the heat pump will continue to operate satisfactorily as the temperature drops below O 0 C and may be operated down to about -6 0 C, although at a reduced efficiency. As stated above, a suitable temperature for actuating the heating means for the current embodiment is -3°C to -4°C.
  • Figure 2 shows a preferred, alternative embodiment of the heat pump system as shown in Figure 1.
  • each of the electrical heaters are preferably arranged adjacent and parallel to a capillary tube, due to their relatively small cross-section. This arrangement will also give a more even and a better controllable heat transfer to the refrigerant.
  • the control of the electrical heaters 12 is performed in the same way as described for the embodiment of Figure 1.
  • FIG. 3 shows an alternative embodiment of the invention as shown in
  • FIG 2 although the general principle may also be applied to the embodiment sown in Figure 1.
  • a heating vessel 19 provided with an immersion heater 20 is arranged around the refrigerant conduit at a suitable location between the evaporator 4 and the compressor 1.
  • the control unit ECU will control the electrical power supplied by the triac device 14 to the immersion heater 20 based on the input signals from the pressure sensor 15 and the temperature sensor 16 in the evaporator 4 and the ambient air sensor 17.
  • control unit may be provided with a matrix, or look-up table for a more accurate control of the immersion heater.
  • the time lag is dependent on the temperature and flow rate of the incoming refrigerant, as well as the power rating of the heating means 20.
  • a further temperature sensor may be provided in the heating vessel 19 or on/in the refrigerant conduit, to provide the control unit with a feedback signal.
  • An alternative version of the above embodiment is indicated with dotted lines in Figure 3.
  • the condenser 2 is provided with a temperature sensor 21 for the heated air leaving the condenser. Should the temperature of the delivered heated air drops from a desired temperature, of say +40 0 C, to minimum set limit temperature, of say +20 0 C, the electronic control unit ECU transmits a signal to a solenoid valve 22.
  • the solenoid valve 22 is placed in a conduit 23 connecting the refrigerant conduit in the heating vessel 19 with the refrigerant conduit immediately upstream of the evaporator 4.
  • the conduit 23 is further provided with a non-return valve 24, preventing flow in the direction of the heating vessel 19.
  • a non-return valve 24 preventing flow in the direction of the heating vessel 19.
  • a bypass conduit provided with a fluid switching valve (not shown) may be provided.
  • a fluid switching valve (not shown) may be provided.
  • said valve is actuated and the refrigerant is taken past the heating vessel, directly to a section of the conduit upstream of the compressor.
  • Figure 4 shows an alternative embodiment of the heat pump arrangement of Figure 3.
  • the main difference between these embodiments is that the heating vessel 19 is arranged immediately upstream of the evaporator 4, instead of being located between the evaporator 4 and the condenser 2. Otherwise, the function of the arrangement shown in Figure 4 is the same as that of Figure 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Central Heating Systems (AREA)

Abstract

L'invention se rapporte à un système de pompe à chaleur comportant un moyen compresseur (1), un condenseur (2), un moyen de réduction de la pression (13, 18), un évaporateur (4), un fluide caloporteur, une conduite de circulation du fluide caloporteur raccordée audit moyen compresseur, audit condenseur, audit moyen de réduction de la pression et audit évaporateur, et une unité de commande (ECU). Ce système de pompe à chaleur comporte au moins un moyen de chauffage réglable (12, 20) conçu pour chauffer ledit fluide caloporteur, ledit moyen de chauffage étant situé entre une première position en aval du moyen condenseur (2) et une seconde position en amont du moyen compresseur (1).
PCT/SE2003/000961 2003-06-13 2003-06-13 Systeme de pompe a chaleur et procede de regulation d'un tel systeme WO2004111558A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU2003239003A AU2003239003A1 (en) 2003-06-13 2003-06-13 Heat pump system and a method for controlling such a system
PCT/SE2003/000961 WO2004111558A1 (fr) 2003-06-13 2003-06-13 Systeme de pompe a chaleur et procede de regulation d'un tel systeme

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/SE2003/000961 WO2004111558A1 (fr) 2003-06-13 2003-06-13 Systeme de pompe a chaleur et procede de regulation d'un tel systeme

Publications (1)

Publication Number Publication Date
WO2004111558A1 true WO2004111558A1 (fr) 2004-12-23

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PCT/SE2003/000961 WO2004111558A1 (fr) 2003-06-13 2003-06-13 Systeme de pompe a chaleur et procede de regulation d'un tel systeme

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AU (1) AU2003239003A1 (fr)
WO (1) WO2004111558A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017133728A (ja) * 2016-01-26 2017-08-03 伸和コントロールズ株式会社 温度制御装置
US10488089B2 (en) 2016-10-05 2019-11-26 Johnson Controls Technology Company Parallel capillary expansion tube systems and methods
US10656110B2 (en) 2016-01-26 2020-05-19 Shinwa Controls Co., Ltd. Temperature control system, temperature control device and refrigeration device

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3082610A (en) * 1959-02-24 1963-03-26 Marlo Coil Company Method and apparatus for controlling pressure entering refrigerant flow device
GB1500152A (en) * 1974-07-24 1978-02-08 Alsthom Cgee Air conditioning system for use in a building
EP0210337A2 (fr) * 1985-07-25 1987-02-04 Dornier Gmbh Evaporateur assisté par une structure capillaire
US4785639A (en) * 1986-05-20 1988-11-22 Sundstrand Corporation Cooling system for operation in low temperature environments
DE3739461A1 (de) * 1987-11-21 1989-06-01 Stiebel Eltron Gmbh & Co Kg Heizungsanlage eines gebaeudes
US5473907A (en) * 1994-11-22 1995-12-12 Briggs; Floyd Heat pump with supplementary heat
WO2001075379A1 (fr) * 2000-03-29 2001-10-11 Eversave Ab Procede et appareil ameliorant le rendement d'une pompe a chaleur a air

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3082610A (en) * 1959-02-24 1963-03-26 Marlo Coil Company Method and apparatus for controlling pressure entering refrigerant flow device
GB1500152A (en) * 1974-07-24 1978-02-08 Alsthom Cgee Air conditioning system for use in a building
EP0210337A2 (fr) * 1985-07-25 1987-02-04 Dornier Gmbh Evaporateur assisté par une structure capillaire
US4785639A (en) * 1986-05-20 1988-11-22 Sundstrand Corporation Cooling system for operation in low temperature environments
DE3739461A1 (de) * 1987-11-21 1989-06-01 Stiebel Eltron Gmbh & Co Kg Heizungsanlage eines gebaeudes
US5473907A (en) * 1994-11-22 1995-12-12 Briggs; Floyd Heat pump with supplementary heat
WO2001075379A1 (fr) * 2000-03-29 2001-10-11 Eversave Ab Procede et appareil ameliorant le rendement d'une pompe a chaleur a air

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017133728A (ja) * 2016-01-26 2017-08-03 伸和コントロールズ株式会社 温度制御装置
US10656110B2 (en) 2016-01-26 2020-05-19 Shinwa Controls Co., Ltd. Temperature control system, temperature control device and refrigeration device
US10488089B2 (en) 2016-10-05 2019-11-26 Johnson Controls Technology Company Parallel capillary expansion tube systems and methods
US10502468B2 (en) 2016-10-05 2019-12-10 Johnson Controls Technology Company Parallel capillary expansion tube systems and methods

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