EP2156108A1 - Procédé et système pour réguler la température dans un refroidisseur par absorption - Google Patents

Procédé et système pour réguler la température dans un refroidisseur par absorption

Info

Publication number
EP2156108A1
EP2156108A1 EP07755341A EP07755341A EP2156108A1 EP 2156108 A1 EP2156108 A1 EP 2156108A1 EP 07755341 A EP07755341 A EP 07755341A EP 07755341 A EP07755341 A EP 07755341A EP 2156108 A1 EP2156108 A1 EP 2156108A1
Authority
EP
European Patent Office
Prior art keywords
temperature
heat exchanger
stage generator
refrigerant
hot water
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Withdrawn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
EP07755341A
Other languages
German (de)
English (en)
Inventor
Lynn M. Rog
Sung-Han Jung
Timothy C. Wagner
Jin Sang Ryu
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.)
Carrier Corp
Original Assignee
UTC Power Corp
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 UTC Power Corp filed Critical UTC Power Corp
Publication of EP2156108A1 publication Critical patent/EP2156108A1/fr
Withdrawn legal-status Critical Current

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
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption 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
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
    • F25B15/02—Sorption machines, plants or systems, operating continuously, e.g. absorption type without inert gas
    • 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
    • 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
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B41/28—Disposition of valves, e.g. of on-off valves or flow control valves specially adapted for sorption cycles
    • 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
    • F25B49/04—Arrangement or mounting of control or safety devices for sorption 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2507—Flow-diverting valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/62—Absorption based systems

Definitions

  • the present disclosure relates to an absorption chiller system. More particularly, the present disclosure relates to a method and system for controlling an outlet temperature of a hot water source capable of being used for heating in a simultaneous heating and cooling absorption chiller.
  • a simultaneous heating and cooling absorption chiller may be configured for providing heating and cooling to a building using, respectively, a hot water source and a chilled water source.
  • the absorption chiller may include a heat exchanger configured for receiving the hot water and thereby increasing a temperature of the hot water to a set point temperature.
  • the heat exchanger utilizes steam produced by a generator of the absorption chiller to transfer heat to the hot water source passing through the heat exchanger.
  • An outside ambient air temperature may affect operating conditions inside the absorption chiller. More specifically, a low ambient air temperature may reduce pressure inside the generator, which impacts a temperature of the steam produced by the generator. In some cases, a low ambient air temperature may impact an ability of the heat exchanger to increase the hot water temperature to the set point temperature.
  • the present disclosure relates to a method and system for controlling a simultaneous heating and cooling absorption chiller having an absorber, a high stage generator, a low stage generator, a heat exchanger, a condenser, and an evaporator.
  • the system includes a first flow passage for delivering refrigerant in vaporized form from the high stage generator to the low stage generator, and a second flow passage for delivering refrigerant in vaporized form from the high stage generator to the heat exchanger.
  • a first valve is configured for controlling an amount of refrigerant in liquid form flowing from the low stage generator to the evaporator.
  • A. second valve is configured for controlling an amount of refrigerant in liquid form flowing from the heat exchanger back to the high stage generator.
  • the system further includes a controller for controlling operation of the first and second valves as a function of a temperature of at least one of a hot water source, the refrigerant in liquid form and an absorbent solution.
  • FIG. 1 is a schematic diagram of an exemplary embodiment of a simultaneous heating and cooling absorption chiller, which includes a high stage generator, a low stage generator, and a heat exchanger configured for increasing a temperature of a hot water source flowing through the heat exchanger.
  • FIG. 2 is a schematic diagram of the heat exchanger of FIG. 1, including a control valve for regulating a flow of condensate from the heat exchanger.
  • FIG. 3 is a schematic diagram of a portion of the chiller of FIG. 1, including a low stage generator, a condenser and a cooling water loop.
  • FIG. 4 is a schematic diagram of a control system for controlling operation of the absorption chiller of FIG. 1.
  • FIG. 1 is a schematic diagram of absorption chiller system 10, which includes evaporator 12, absorber 14, high stage generator 16, low stage generator 18, condenser 20, high temperature solution heat exchanger 22, low temperature solution heat exchanger 24, and auxiliary heat exchanger 26.
  • chiller system 10 is a double-effect absorption chiller with simultaneous heating and cooling capabilities, and as such, system 10 may be used to supply heating and cooling to a building. It is recognized that the method and system described herein for controlling a temperature of a hot water source in chiller system 10 may also apply to any type of absorption chiller having simultaneous heating and cooling capabilities, including, but not limited to, a single-effect or a triple-effect absorption chiller.
  • Chiller system 10 is configured to provide cooling to a building by decreasing a temperature of chilled water source 28, which passes through evaporator 12.
  • System 10 is able to simultaneously provide heating to the building by increasing a temperature of hot water source 30, which passes through auxiliary heat exchanger 26.
  • system 10 also includes cooling water loop 32 for flowing water from a cooling tower through absorber 14 and condenser 20 such that the cooling water is used for heat removal.
  • absorption chiller systems like system 10, are configured to use an absorbent solution, such as lithium bromide, and a refrigerant, such as water, to provide a cooling and/or a heating effect.
  • an absorbent solution such as lithium bromide
  • a refrigerant such as water
  • chiller system 10 is described using lithium bromide and water, it is recognized that other combinations (for example, water as the absorbent and ammonia as the refrigerant) may alternatively be used in system 10.
  • Evaporator 12 is configured to receive refrigerant in liquid form (i.e. water) from condenser 20 and store the water in evaporator sump 34.
  • evaporator 12 pumps water from sump 34 to sprayer 38, located at a top of evaporator 12, or to a dripper system in evaporator 12.
  • system 10 is a closed loop system and maintained in a vacuum such that water from sprayer 38 boils at a lower temperature.
  • the refrigerant (water), now in vaporized form, travels to absorber 14 through eliminator 40, at which point the water is absorbed by a concentrated lithium bromide solution being sprayed through sprayer 42 at a top of absorber 14.
  • a diluted lithium bromide solution then is delivered to high stage generator 16 using solution pump 44.
  • Exhaust gas is supplied to high stage generator 16 to boil water from the lithium bromide solution, thus generating steam.
  • exhaust gas is supplied from a microturbine or another type of prime mover.
  • a benefit of system 10 is that it utilizes waste heat from another component used in the building. It is recognized that other types of heat sources may be used for supplying heat energy to generator 16.
  • generator 16 may be direct-fired, steam fired or hot-water driven. Steam generated by generator 16 may then be directed to low stage generator 18 and to auxiliary heat exchanger 26. Moreover, steam from generator 16 may also reside in overflow piping 46.
  • Lithium bromide solution from high stage generator 16 flows through heat exchanger 22 and then flows to a shell side of low stage generator 18.
  • the lithium bromide solution in generator 18 then boils off additional steam due to transferred heat from the steam on the tube side of generator 18.
  • the additional steam on the shell side of generator 18 then travels to condenser 20 through eliminator 48 located between generator 18 and condenser 20.
  • cooling water 32 flows through a tube side of condenser 20.
  • the steam from generator 18 enters the shell side of condenser 20 the steam condenses and the condensate is recycled back to evaporator 12.
  • system 10 in the exemplary embodiment of FIG. 1, is a simultaneous heating and cooling absorption chiller, system 10 also includes auxiliary heat exchanger 26, which may be used for heating.
  • chiller system 10 includes overflow piping 46 connected between high stage generator 16 and absorber 14. Overflow piping 46, used in conjunction with steam trap 50, may be used to recycle excess absorbent solution in generator 16, which may accumulate under certain operating conditions, back to absorber 14. As also shown in FIG.
  • system 10 includes liquid level sensors 52 for monitoring a level of refrigerant in evaporator sump 34 to control operation of refrigerant pump 36. It is recognized that overflow piping 46, steam trap 50 and sensors 52 are not required in chiller system 10, but may be used for improving operation of system 10, particularly under a low cooling or heating load.
  • system 10 includes three main valves that are used to control operation of system 10 - diverter valve 70 (also referred to as CVl), heat exchanger control valve 72 (also referred to as CV2), and low stage generator control valve (also referred to as CV3).
  • Valve 70 (CVl) is configured to regulate an amount of exhaust gas supplied to high stage generator 16 based on the heating and/or cooling demands on system 10.
  • Valve 72 (C V2) is configured to regulate an amount of liquid condensate in heat exchanger 26 recycled back to generator 16, as a function of the heating demand.
  • Valve 74 (C V3) is configured to regulate an amount of liquid condensate in low stage generator 18 recycled back to evaporator 12, based on the heating and/or cooling demands and the conditions inside high stage generator 16.
  • System 10 also includes bypass loop 80, configured in parallel with heat exchanger 26, and valve 82, both of which are described in further detail below. It is recognized that bypass loop 80 and valve 82 are not required in chiller system 10, but may be used for improving operation of system 10, particularly in an absence of a heating demand. It is recognized that additional valves not specifically shown in FIG. 1 or described herein are included in system 10. [0020] FIG.
  • Heat exchanger 26 is used to increase a temperature of hot water 30 passing through heat exchanger 26 via heat exchanger inlet 84 and heat exchanger outlet 90.
  • heat exchanger 26 may be a shell and tube type heat exchanger, in which case hot water 30a entering through inlet 84 is directed through multiple tubes 86 inside heat exchanger 26.
  • Steam from generator 16 enters a shell side of heat exchanger 26 through piping 88. As such, heat from the steam is transferred to hot water 30 and the steam condenses on the outside of tubes 86 to form a liquid condensate.
  • an outlet temperature T HE OUT of hot water 30b at outlet 90 is greater than an inlet temperature T HE I N of hot water 30a at inlet 84.
  • Valve 72 is configured to regulate an amount of heat transferable to hot water 30. If CV2 is open, the liquid condensate (which was steam from generator 16) is directed to flow out of heat exchanger 26 and back to generator 16 through piping 92. Conversely, if CV2 is closed, the liquid condensate builds up inside heat exchanger 26.
  • a heating capacity of heat exchanger 26 is a function of an amount of condensate inside heat exchanger 26. As condensate accumulates inside heat exchanger 26, less steam is entering heat exchanger 26; consequently, there is less heat transfer to hot water 30.
  • the condensate eventually may occupy all of the space inside heat exchanger 26 such that heat exchanger 26 is not capable of providing any heating to hot water 30.
  • the heating capacity of heat exchanger 26 is a function, in part, of the position or state of CV2.
  • CV2 controls the outlet temperature T HE OUT of hot water 30b by controlling an amount of condensate inside heat exchanger 26, based on a set point temperature T HE SET PT for hot water 30.
  • the set point temperature TH E S ET PT may be equal to 175°F. Therefore, CV2 is positioned and adjusted as necessary so that T HE OUT remains essentially equal to 175 0 F.
  • system 10 is a simultaneous heating and cooling absorption chiller, system 10 may be operating in some cases when there is a cooling demand, but no heating demand. (This includes those scenarios in which the heating and cooling demands on system 10 are frequently fluctuating.) Under those conditions, hot water 30 may continue to be pumped through heat exchanger 26, even though the building is not requesting any heating.
  • the set point temperature T HE SET PT for the hot water outlet is adjusted to reflect changes in the heating demand.
  • controller 112 of system 10 may decrease T HE S E T P T and adjust diverter valve 70 (CVl) to supply less heat to generator 16. Less heat results in a generation of less steam and less heat transfer to hot water 30.
  • the controller may also close CV2 in order to the decrease the heating capacity of heat exchanger 26 by accumulating liquid condensate inside heat exchanger 26.
  • Bypass loop 80 may be used to reject (i.e. transfer) heat from hot water 30 when outlet temperature T HE OUT rises above a predetermined level.
  • Bypass loop 80 is configured in parallel with heat exchanger 26, and includes first flow passage 96, second flow passage 98 and a heat rejection radiator (not shown). As shown in FIG.
  • first flow passage 96 is connected to inlet 84 of heat exchanger 26 and second flow passage 98 is connected to outlet 90 so that at least a portion of hot water 30 may flow through bypass loop 80.
  • the heat rejection radiator of bypass loop 80 is designed to be located inside piping of cooling water loop 32 (see FIG. 1). When water 30 flows through the heat rejection radiator, heat from water 30 is transferred to cooling water circulating through cooling water loop 32. Valve 82 (see FIG. 1) is located within first flow passage 96, and is configured to regulate a flow of hot water 30 through bypass loop 80. In alternative embodiments, instead of using the heat rejection radiator, heat may be transferred or rejected from hot water 30 using other devices or methods.
  • Bypass loop 80 maybe used in those scenarios where system 10 does not have a heating demand and the outlet temperature T HE O UT rises to an undesirable value.
  • operation of chiller system 10 also includes those scenarios in which the building has a heating demand and system 10 may have difficulty maintaining the outlet temperature T HE O UT at the set point T HE SET PT - AS described above, valve 72 (CV2) may be used to control an amount of heating provided by system 10 by controlling the flow of condensate out of heat exchanger 26.
  • FIG. 3 is a schematic diagram of a portion of chiller system 10 of FIG.
  • cooling water loop 32 is configured to contain cooling water from a cooling tower. Cooling water loop 32 passes through absorber 14 (see FIG. 1) and then through condenser 20. The cooling water is then recycled back to the cooling tower.
  • low stage generator 18 is configured to receive steam from high stage generator 16 (via piping 122), which flows to the tube side of low stage generator 18. Lithium bromide solution from high stage generator 16 flows through piping 124 to the shell side of low stage generator 18.
  • a temperature of the cooling water at the inlet of cooling water loop 32 may be approximately 85°F and a temperature at the outlet of cooling water loop 32 (an outlet of condenser 20) may be approximately 95°F. Because the cooling tower is exposed to ambient air, the inlet temperature of the cooling water is directly affected by an outside ambient air temperature. A lower cooling water temperature impacts the condensation process inside condenser 20.
  • an internal pressure inside condenser 20 directly correlates to a temperature of the cooling water. When the cooling water is at a lower temperature, it results in a lower pressure inside condenser 20. (Note that chiller system 10 is in a vacuum and all components within system 10 are at low pressures. Any pressure differentials described herein are relative.)
  • a lower pressure inside condenser 20 results in a lower pressure within other components of chiller system 10, such as high stage generator 16 and low stage generator 18. If chiller system 10 only had a cooling demand, lower pressure conditions inside system 10 may not be problematic. However, a lower pressure inside high stage generator 16 causes steam from the lithium bromide solution to boil at a lower temperature. The lower temperature steam then travels from high stage generator 16 to heat exchanger 26 (see FlG. 1). Since the temperature of the steam is lower, the steam transfers less heat to hot water 30 passing through heat exchanger 26. In that case, it may not be possible for the outlet temperature T HE OUT to reach the set point temperature T HE S E T PT (for example, 175 0 F). [0030] Control valve 74 (see FIG.
  • control valve 74 which is located at an outlet of low stage generator 18, may be used to control the pressure inside high stage generator 16.
  • control valve 74 may indirectly control the outlet temperature T HE OUT of hot water 30.
  • control valve 74 (CV3) is fully open, condensate from the tube side of generator 18 is able to freely flow through piping 128, and ultimately through piping 130 back to evaporator 12. In that case, there is essentially no change in pressure between high stage generator 16 and condenser 20. As mentioned above, when the pressure in condenser 20 is low, the pressure in generator 16 is also low. Conversely, when control valve 74 (CV3) is closed at least partially, the flow of condensate through piping 128 is limited by an orifice created by partially closing valve 74.
  • controller 112 controls a position of valve 74 in order to maintain the outlet temperature T HE OUT of hot water 30 essentially equal to the set point temperature T HE SET PT - Controller 112 may control valve 74 based on various parameters within system 10, as explained below.
  • an input parameter to controller 112 is a temperature T G2 ou ⁇ of the liquid condensate (refrigerant) at an outlet of low stage generator 18.
  • At least one temperature sensor located upstream of valve 74, in or around piping 128, may be used for measuring T G2 OU T-
  • FIG. 4 is a schematic diagram of control system 110 for controlling operation of chiller system 10.
  • System 110 includes controller 112, inputs 114 to controller 112 and outputs 116. It is recognized that control system 110 includes additional inputs and outputs that are not included in FIG. 4 for clarity.
  • Inputs 114 include cooling demand 118, heating demand 120, THE OUT, THE SET
  • chiller system 10 may have a cooling demand and a heating demand at the same time. At other times, system 10 may be operating under either a cooling demand or a heating demand. Moreover, system 10 may experience frequent fluctuations in the cooling and/or the heating demand. Based on cooling demand 118 and heating demand 120, controller 112 controls a position of valve 70 (CVl), which supplies heat (i.e. waste gas) to generator 16. So long as the total demand (heating plus cooling) does not exceed a maximum value, controller 112 may not be required to designate a heating priority or a cooling priority.
  • CVl position of valve 70
  • controller 12 may operate as a function, at least in part, of whether system 10 has a heating priority or a cooling priority. In either case, when the total demand is at or above a maximum value, control valve 70 (CVl) is fully open and controller 112 adjusts valves 72 and 74 to provide the required heating and/or cooling.
  • CVl control valve 70
  • valve 72 (CV2) is configured to regulate a flow of condensate exiting heat exchanger 26, valve 72 controls an ability of heat exchanger 26 to transfer heat to hot water 30 passing through heat exchanger 26.
  • a position of valve 72 (C V2) is controlled, in part, as a function of the temperature TH E OU T of hot water 30b at outlet 90. Temperature THE OUT is compared to a set point temperature THE SET PT for the hot water, which may be, for example, commonly set at 175°F.
  • TH E OU T and T H E S ET P T are both inputs to controller 112.
  • bypass loop 80 is configured to redirect at least a portion of hot water 30 from heat exchanger 26 to the heat rejection radiator if the temperature T H E out of hot water 30 at outlet 90 of heat exchanger 26 is too high.
  • controller 112 adjusts CV2 to control temperature T HE O U T , based on the set point temperature T H E S E T PT- Therefore, the heat rejection radiator is usually not used until temperature T H E O UT is above a predetermined value that is greater than the set point temperature THE SE T P T- Valve 82 controls a flow of hot water 30 to the radiator, and is controlled by controller 112.
  • controller 112 opens valve 82 so that water 30 is able to flow through bypass loop 80.
  • the predetermined value is equal to a sum of the set point temperature T H ⁇ SET PT and a marginal value. For example, if T HE SET PT is equal to 175°F and the marginal value is equal to ten degrees, controller 112 opens valve 82 if THE OUT is greater than 185°F. Valve 82 may then be closed when T HE OUT decreases to a temperature that is less than or equal to the predetermined value.
  • Control system 110 includes at least one temperature sensor located around outlet 90 of heat exchanger 26 for measuring THE OUT- [0036]
  • Inputs 114 also include TQ 2 OUT , which, as mentioned above, is a temperature of the liquid condensate (refrigerant) exiting a tube side of generator 18, and T A B S O U T , which is a temperature of the absorbent solution (i.e. lithium bromide) exiting absorber 14.
  • TG 2 O UT and T ABS OUT may be monitored, along with T HE OUT , by controller 112 to determine a position of valve 74 (CV3).
  • valve 72 (CV2) is used to control the outlet temperature T HE OUT of hot water 30, and consequently control an amount of heating provided by heat exchanger 26.
  • the outlet temperature TH E OU T of hot water 30 may be less than the set point temperature T HE SET PT -
  • adjustments may be made to valve 74 (CV3), based on TG 2 OUT, TABS OUT, and THE OUT, to increase the outlet temperature THE OUT and bring it closer to T HE SE TPT-
  • inputs 114 may also include a set point temperature for liquid condensate exiting low stage generator 18 (referred to as T G2 SET PT -)
  • T G2 SET PT The condensate set point temperature TQ 2 SE T PT is calculated by controller 112 as a function of inputs 114 to controller 112, and thus T G2 SET PT varies depending on conditions inside system 10.
  • the set point temperature T G2 SET PT may be determined using an algorithm described below.
  • Control system 110 includes at least one temperature sensor at an outlet of absorber 14 for measuring the temperature of the absorbent solution T ABS OUT , and at least one sensor at an outlet of generator 18 for measuring the temperature of the steam condensate, T G2 O U T - [0037]
  • Controller 112 includes a control algorithm that determines when and how valve 74 (CV3) is adjusted.
  • Inputs 114 to controller 112 include the set point temperature TG 2 S ET P T for steam condensate at an outlet of low stage generator 18 and an actual temperature T G2 O U T of the steam condensate at the outlet of generator 18.
  • Controller 112 controls a position of valve 74 so that TG2 OUT is essentially equal to T G2 SET PT (assuming a tolerance range). Valve 74 is opened or closed (incrementally) based on a difference between TG 2 SET PT and TG 2 OUT- IfTG 2 OUT is greater than TQ 2 SET PT, then controller 112 starts opening valve 74 until TG 2 OUT decreases to T G2 SET PT - On me other hand, if TQ 2 OUT is less than TG 2 SET PT, then controller 112 starts closing valve 74 until TQ 2 OUT increases to TG 2 SET PT- [0038]
  • the control algorithm includes three equations to calculate the set point temperature TQ 2 S E T PT of the condensate (liquid refrigerant) exiting low stage generator 18.
  • the set point temperature TG 2 SET PT is a function of the temperature of the lithium bromide solution exiting absorber 14 (TA BS OUT ), the actual outlet temperature of water 30 exiting heat exchanger 26 (THE OUT), an d a valve position feedback percentage for valve 72 (referred to as VFcv2), which is expressed as a decimal value.
  • VFcv2 valve position feedback percentage for valve 72
  • Equation 2 IF (T ABS O UT + G2 factor A) > (TH E O UT + G2 factor B), THEN
  • G2 factor A is a constant value ranging between 80 and
  • G2 factor B is a constant value ranging between 2 and 30.
  • valve 74 (CV3) is incrementally opened until TG 2 OUT is equal to TG 2 SET PT- If TG 2 OUT is less than TG 2 SET PT, then valve 74 (CV3) is incrementally closed until T G2 O U T is equal to TG 2 SET PT-
  • Chiller system 10 is described above using lithium bromide as the absorbent solution and water as the refrigerant. As mentioned above, other combinations, such as ammonia and water, may also be used in system 10. In those embodiments, the control method described herein may also be used to control the outlet temperature T HE O U T of hot water 30 by controlling valve 74. It is recognized that Equations 1-3 may vary depending on the absorbent solution and refrigerant. For example, in a system using ammonia and water, the ranges for G2 factor A and G2 factor B may be different than the ranges provided above. [0045] In the exemplary embodiment shown in FIGS. 1-3, valves 72 and 74 are bellows type valves. It is recognized that other types of valves for regulating fluid flow may be used in system 10. In a preferred embodiment, controller 112 includes a proportional integral derivative (PID) function and a limiter for controlling a position and rate motion of valves 72 and 74.
  • PID proportional integral derivative
  • the set point temperature TH E S ET P T for hot water 30 may be determined by a user based, in part, on the building conditions and the heating demand. Thus, the user may input the hot water set point THE SET PT into control system 110 and change THE SET PT as necessary or as desired.
  • the set point temperature T G2 SET PT for the condensate exiting low stage generator 18 is calculated by controller 112, based on other inputs 114, such as TA BS OUT and T H E OUT-
  • the set point temperature T G 2 S ET P T of the condensate may fluctuate frequently based on conditions in chiller system 10.
  • Control system 110 then uses a comparison between T G2 OUT and T G2 SE T PT to adjust valve 74, in order to maintain the outlet temperature THE O UT essentially equal to the set point temperature TH E SET P T for hot water 30.
  • chiller system 10 is a double-effect absorption chiller. It is recognized that this control method may be used in other types of absorption chillers, such as a single-effect or a triple-effect absorption chiller. The control method described herein may be used to control a hot water temperature in those other systems by monitoring and controlling pressure and/or temperature inside the absorption chiller in similar locations as compared to what was shown and described above for chiller system 10.
  • the present invention has been described with reference to preferred embodiments, workers skilled in the art will recognize that changes may be made in form and detail without departing from the spirit and scope of the invention.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Abstract

L'invention concerne un procédé et un système pour réguler la température d'une source d'eau chaude qui peuvent être utilisés pour le chauffage pour un refroidisseur par absorption comprenant une première soupape pour réguler une quantité de réfrigérant liquide sortant d'un générateur de bas étage dans le refroidisseur par absorption, afin de réguler une pression dans un générateur de haut étage configuré pour produire de la vapeur d'eau. Une seconde soupape régule une quantité de réfrigérant liquide sortant d'un échangeur de chaleur dans le refroidisseur par absorption, afin de réguler une capacité de chauffage de l'échangeur de chaleur. Un régulateur régule le fonctionnement des première et seconde soupapes en fonction de la température de la source d'eau chaude et/ou du réfrigérant liquide et/ou d'une solution d'absorbant.
EP07755341A 2007-04-13 2007-04-13 Procédé et système pour réguler la température dans un refroidisseur par absorption Withdrawn EP2156108A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2007/009034 WO2008127229A1 (fr) 2007-04-13 2007-04-13 Procédé et système pour réguler la température dans un refroidisseur par absorption

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EP2156108A1 true EP2156108A1 (fr) 2010-02-24

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EP07755341A Withdrawn EP2156108A1 (fr) 2007-04-13 2007-04-13 Procédé et système pour réguler la température dans un refroidisseur par absorption

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EP (1) EP2156108A1 (fr)
KR (1) KR20100063680A (fr)
CN (1) CN101730825A (fr)
WO (1) WO2008127229A1 (fr)

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CN101806517B (zh) * 2010-02-26 2011-12-28 清华大学 一种以高温烟气和热水为驱动热源的地温能供热制冷机组
US9250002B2 (en) 2011-02-28 2016-02-02 Carrier Corporation System and method for controlling an absorption chiller configured to simultaneously produce cooling and heating
JP5646385B2 (ja) * 2011-03-30 2014-12-24 三洋電機株式会社 吸収式冷凍機
CN105423592B (zh) * 2015-12-23 2018-02-02 双良节能系统股份有限公司 双工况直燃双效型溴化锂吸收式热泵机组
CN105627652B (zh) * 2016-01-14 2018-02-02 山东奇威特太阳能科技有限公司 燃气热泵工质浓度控制方法
CN113669956B (zh) * 2021-08-02 2023-01-20 北京工业大学 可调节发生器及其控制方法

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JP3285099B2 (ja) * 1992-11-04 2002-05-27 大阪瓦斯株式会社 吸収式冷凍機
JP3128501B2 (ja) * 1996-02-07 2001-01-29 リンナイ株式会社 吸収式空調装置
JP4721783B2 (ja) * 2005-06-24 2011-07-13 三洋電機株式会社 吸収冷温水機の運転制御方法

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See references of WO2008127229A1 *

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KR20100063680A (ko) 2010-06-11
WO2008127229A1 (fr) 2008-10-23
CN101730825A (zh) 2010-06-09

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