KR20100005097A - A method and system for rejecting heat in an absorption chiller - Google Patents

Abstract

A method and system for rejecting heat from a hot water source (30) capable of being used for heating in a simultaneous heating and cooling absorption chiller (10) includes a bypass loop (80) configured in parallel with a heat exchanger (26) used to increase a temperature of hot water (30) passing through the heat exchanger (26). The bypass loop (80) is connected to an inlet (84) and an outlet (90) of the heat exchanger (26) and is configured to receive at least a portion of the hot water (30) flowing to the heat exchanger (26). The bypass loop (80) includes a radiator (100) positioned inside a portion of a cooling water loop (32), and the radiator (100) is configured to reject or transfer heat from the hot water (30) to cooling water in the cooling water loop (32). The system further includes a valve (82) for controlling a flow of hot water (30) through the bypass loop (80) as a function of a temperature of the hot water (30) at the outlet (90) of the heat exchanger (26).

Description

A METHOD AND SYSTEM FOR REJECTING HEAT IN AN ABSORPTION CHILLER}

The present invention relates to an absorption chiller system. More specifically, the present invention relates to a method and system for heat rejection from a hot water source in an absorption chiller capable of simultaneous heating and cooling.

The simultaneous HVAC absorber chiller may be configured to provide heating and cooling to the building using a hot water source and a chilled water source, respectively. The absorption chiller may include a heat exchanger configured to receive the hot water to raise the temperature of the hot water. Buildings may have heating and cooling needs that change frequently. There may be a period during which the building does not require any heating, so the absorption chiller does not have a heating requirement during that period. In these cases, if there is a cooling requirement, the absorption chiller is still in operation, and a pump that delivers hot water to the heat exchanger may continue to circulate the hot water through the heat exchanger. In part due to the energy from the pump and the frictional heat inside the piping of the heat exchanger, the temperature of the hot water may rise. If the building does not have a heating load to consume energy from the hot water, the hot water may be raised to an undesirable temperature.

When the hot water temperature at the outlet of the heat exchanger rises above a predetermined level, there is a need for a system and method for dissipating heat from a hot water supply.

The present invention provides a method and system for radiating heat from a hot water source that can be used for heating in an absorber, a generator, a heat exchanger, a condenser, an evaporator, and a simultaneous air-conditioning absorption chiller having a cooling water loop through the absorber and the condenser. It is about. The system includes a bypass loop configured in parallel with the heat exchanger and connected to the inlet and the outlet of the heat exchanger. The bypass loop is configured to receive at least a portion of the hot water flowing to the heat exchanger and includes a radiator located inside a portion of the cooling water loop. Hot water guided into the bypass loop flows through the radiator such that heat from the hot water is transferred to the cooling water in the cooling water loop. The system also includes a valve for controlling the flow of hot water through the bypass loop.

1 is a schematic diagram of an exemplary embodiment of a simultaneous heating and cooling absorption chiller, which includes a bypass loop configured for heat dissipation from a heat exchanger and a hot water supply to the heat exchanger.

FIG. 2 is a schematic diagram of a portion of the heat exchanger and bypass loop of FIG. 1. FIG.

3 is another schematic diagram of the heat exchanger and bypass loop of FIGS. 1 and 2 and a valve configured to regulate the flow through the bypass loop.

4 is a schematic diagram of a portion of the cooler of FIG. 1 including an absorber, a condenser, a coolant loop, and a bypass loop, the cooler including a heat radiating radiator passing through the piping of the coolant loop.

5 is a schematic diagram of a control system for controlling the operation of the absorption chiller of FIG. 1.

1 is a schematic diagram of an absorption chiller system 10, wherein the absorption chiller system 10 includes an evaporator 12, an absorber 14, a high stage generator 16, a low stage generator 18, a condenser 20, a high temperature. Solution heat exchanger 22, low temperature solution heat exchanger 24, and auxiliary heat exchanger 26. In the exemplary embodiment of FIG. 1, the chiller system 10 is a dual effect absorption chiller with simultaneous heating and cooling capability, and the system 10 can be used to supply heating and cooling to a building. In addition, the methods and systems described herein for dissipating heat in the chiller system 10 may be applied to any type of absorption chiller having simultaneous air conditioning performance, including, but not limited to, single effect or triple effect absorption chillers. It may be.

The chiller system 10 is configured to provide cooling to the building by lowering the temperature of the cold water source 28 passing through the evaporator 12. At the same time, the system 10 can provide heating to the building by raising the temperature of the hot water source 30 passing through the auxiliary heat exchanger 26. As commonly used as absorption chillers, system 10 also includes a coolant loop 32 for flowing water from the cooling tower through absorber 14 and condenser 20 such that the coolant is used for heat removal. do.

As is known in the art, absorption chiller systems, such as system 10, are configured to use refrigerants such as water and absorbent solutions such as lithium bromide to provide cooling and / or heating effects. Although a chiller system 10 using lithium bromide and water is described, other combinations (eg, water as absorbent and ammonia as refrigerant) may optionally be used in system 10.

The evaporator 12 is configured to receive a refrigerant in liquid form (ie, water) from the condenser 20 and to store water in the evaporator sump 34. Using the refrigerant pump 36, the evaporator 12 is from a sump 34, to a sprayer 38 located on top of the evaporator 12, or to a dripper system in the evaporator 12. Pump water. Due to the cold water 28 running through the tube inside the evaporator 12, the water from the sprayer 38 vaporizes and the cold water 28 drops in temperature. As shown, system 10 is a closed loop system and is maintained in a vacuum such that water from sprayer 38 boils at low temperatures. The refrigerant (water), now in the vaporized state, proceeds to the absorber 14 via an eliminator 40, at which point water is sprayed through the sprayer 42 at the top of the absorber 14 Is absorbed by the concentrated lithium bromide solution. The diluted lithium bromide solution is delivered to the high stage generator 16 using a solution pump 44. The hot and cold solution heat exchangers 22, 24 which transfer the lithium bromide solution to the low stage generator 18 and from the low stage generator 18 raise the temperature of the diluted lithium bromide solution flowing to the generator 16. Therefore, the efficiency of the generator 16 is increased.

The exhaust gas is fed to the high stage generator 16 to boil the water from the lithium bromide solution, thereby producing steam. In the exemplary embodiment of FIG. 1, the exhaust gas is supplied from a microturbine or other type of prime mover. An advantage of the system 10 is that the system utilizes waste heat from another part used in the building. Other types of heat sources may be used to supply thermal energy to generator 16. For example, in other embodiments, generator 16 may be directly ignited, steam ignited, or driven with hot water. The steam produced by the generator 16 can then be directed to the low stage generator 18 and to the auxiliary heat exchanger 26. In addition, steam from generator 16 may also remain in overflow piping 46.

Steam from the high stage generator 16 flows to the tube side of the low stage generator 18. The lithium bromide solution from the high stage generator 16 flows through the heat exchanger 22 and then to the shell side of the low stage generator 18. The lithium bromide solution in generator 18 boils off additional steam due to the transferred heat from the steam on the tube side of generator 18. Thereafter, additional steam at the shell side of the generator 18 proceeds to the condenser 20 through an eliminator 48 located between the generator 18 and the condenser 20. In the condenser 20, the coolant 32 flows through the tube side of the condenser 20. As steam from generator 18 enters the shell side of condenser 20, steam condenses and the condensate is recycled back to evaporator 12.

Steam in the tube side of the generator 18 condenses and this condensate, with the condensate from the condenser 20, is recycled back to the evaporator 12. Lithium bromide from generator 18, which is again high concentration, flows through heat exchanger 24 and is recycled back to absorber 14. As the concentrated lithium bromide is sprayed into the absorber 14 to absorb the water from the evaporator 12, the circulation is repeated.

In the exemplary embodiment of FIG. 1, since the system 10 is a simultaneous HVAC absorber, the system 10 also includes an auxiliary heat exchanger 26 that may be used for heating. Steam from the high stage generator 16 proceeds to the shell side of the auxiliary heat exchanger 26, where the steam condenses and transfers heat to the hot water source 30 flowing through the tube side of the heat exchanger 26. . After the steam has condensed, the liquid condensate is recycled back to the generator 16, where the liquid condensate may be reabsorbed by the lithium bromide solution in the generator 16.

In the embodiment shown in FIG. 1, the chiller system 10 includes an overflow piping 46 connected between the high stage generator 16 and the absorber 14. The overflow piping 46 used in connection with the steam trap 50 can be used to recycle excess absorbent solution in the generator 16, which may accumulate back into the absorber 14 under certain operating conditions. . As also shown in FIG. 1, the system 10 includes a liquid level sensor 52 for monitoring the level of refrigerant in the evaporator sump 34 to control the operation of the refrigerant pump 36. Overflow piping 46, steam trap 50, and sensor 52 are not required for chiller system 10, but may be used to improve operation of system 10, particularly under low cooling or heating loads.

As shown in FIG. 1, the system 10 includes three main valves-a diverter valve 70 (also referred to as CVl), a heat exchanger control valve used to control the operation of the system 10. 72 (also referred to as CV2) and a low stage generator control valve (also referred to as CV3). The valve 70 (CVl) is configured to adjust the amount of exhaust gas supplied to the high stage generator 16 based on the heating and / or cooling requirements in the system 10. Valve 72 (CV2) is configured to regulate the amount of liquid condensate in heat exchanger 26 that is recycled back to generator 16 as a function of heating demand. Valve 74 (CV3) regulates the amount of liquid condensate in low stage generator 8 that is recycled back to evaporator 12 based on conditions inside high stage generator 16 and heating and / or cooling needs. It is configured to. The system 10 also includes a bypass loop 80 and a valve 82 configured in parallel with the heat exchanger 26, both of which are described in more detail below. Additional valves, not specifically shown in FIG. 1 or not described herein, are included in system 10.

FIG. 2 is a schematic diagram of the heat exchanger 26 from FIG. 1. The heat exchanger 26 is used to raise the temperature of the hot water 30 passing through the heat exchanger 26 via the heat exchanger inlet 84 and the heat exchanger outlet 90. In one embodiment, heat exchanger 26 may be a shell and tube type heat exchanger, in which case hot water 30a entering through inlet 84 may pass multiple tubes 86 inside heat exchanger 26. Is guided through. Steam from generator 16 enters shell side of heat exchanger 26 through piping 88. Thereby, heat from the steam is transferred to the warm water 30, which condenses outside of the tube 86 to form liquid condensate. Generally speaking, when steam from generator 16 enters the shell side of heat exchanger 26 and hot water 30 is passing through the tube side, the outlet temperature of hot water 30b at outlet 90 ( T _{HE OUT} is the inlet temperature T _HE of the warm water 30a at the inlet 84. _IN )

Valve 72 (CV2) is configured to regulate the amount of heat that can be transferred to hot water 30. When CV2 is open, liquid condensate (which was steam from generator 16) is guided to flow out of heat exchanger 26 and back through generator 92 to generator 16. In contrast, when CV2 is closed, liquid condensate accumulates inside the heat exchanger 26. The heating capacity of the heat exchanger 26 is a function of the amount of condensate inside the heat exchanger 26. As the condensate accumulates inside the heat exchanger 26, less steam is entering the heat exchanger 26 and thus less heat is transferred to the warm water 30. If CV2 is closed over a period of time, the condensate may eventually occupy all of the space inside heat exchanger 26 such that heat exchanger 26 may not be able to heat any of the hot water 30. In summary, the heating capacity of the heat exchanger 26 is partly a function of the position or condition of CV2.

CV2 is the set point temperature (T _HE ) for hot water (30) _SET The outlet temperature T _HE of the hot water 30b by controlling the amount of condensate inside the heat exchanger 26 based on _PT ). _OUT ). For example, during a heating request, the set point temperature T _{HE SET PT} ) may be 175 ° F (79.4 ° C). Thus, CV2 is T _{HE It} is positioned and adjusted as necessary to maintain _OUT at essentially 175 ° F (79.4 ° C). Since the system 10 is a simultaneous air conditioning absorption chiller, the system 10 may not work in some cases where there is a cooling requirement but no heating requirement. (This includes cases where the heating and cooling needs in the system 10 vary frequently.) Under these conditions, hot water 30 continues through the heat exchanger 26, even if the building does not require any heating. It may also be pumped.

Set point temperature for hot water outlet (T _{HE SET PT} ) is adjusted to reflect changes in heating needs. When there is no heating requirement, the controller 112 of the system 10 (described below with reference to FIG. 5) will T _HE to supply less heat to the generator 16. _{SET The PT} may be lowered and the diverter valve 70 (CVl) may be adjusted. Less heat produces less steam and transfers less heat to hot water 30. The controller may also close CV2 to reduce the heating capacity of heat exchanger 26 by accumulating liquid condensate inside heat exchanger 26. Despite these adjustments, as the pump continues to circulate the hot water 30 through the heat exchanger 26, the residual energy and frictional heat from the pump are at the outlet temperature T _{HE. OUT} ) is the set point temperature (T _{HE) SET PT} ) may rise higher than. If this hot water energy is not consumed by the building heating load, the outlet temperature (T _{HE) OUT} ) may eventually reach undesirable high temperatures.

Bypass loop 80 has an outlet temperature T _{HE When OUT} ) rises above a predetermined level, it may be used for heat dissipation (ie, transfer of heat) from hot water 30. The bypass loop 80 includes a first flow path 96, a second flow path 98 and a heat rejection radiator 100 (see FIG. 4). As shown in FIGS. 1 and 2, the bypass loop 80 is configured parallel to the heat exchanger 26 and receives a portion of the hot water 30a entering the inlet 84 of the heat exchanger 26. It is configured to. As shown in FIG. 2, the first flow path 96 is connected to the inlet 84 of the heat exchanger 26, and the second flow path 98 is connected to the outlet 90. (This is further described in Figures 3 and 4).

3 is a schematic diagram of a heat exchanger 26, a portion of the bypass loop 80, and a valve 82. The first flow path 96 transfers the hot water 30 from the heat exchanger inlet 84 to the heat radiating radiator 100 (see FIG. 4), and the second flow path 98 transfers the hot water 30 to the heat radiating radiator 100. ) To the heat exchanger outlet 90. In the exemplary embodiment shown in FIG. 3, the first flow path 96 includes two sections of piping—first piping section 96a and second piping section 96b. The second flow path 98 is similarly formed from the piping of at least one section.

The valve 82 is located between the first piping section 96a and the second piping section 96b and is configured to regulate the flow of the hot water 30 through the bypass loop 80. In one embodiment, the valve 82 is a solenoid valve. Other types of flow valves or similar flow regulators may be used. As described above, the flow path 96 is configured to receive a portion of the warm water 30 passing through the inlet 84. When solenoid valve 82 is actuated, water 30 is allowed to flow through radiator 100 to radiator 100. When valve 82 is closed, all hot water 30 flows through tube 86 of heat exchanger 26.

4 is a schematic diagram of a portion of absorber 14, condenser 20, coolant loop 32, and bypass loop 80, all of which are also shown in FIG. 1. As described above with reference to FIG. 1, the coolant loop 32 is configured to circulate water from the cooling tower through the absorber 14 and the condenser 20. The coolant loop 32 includes a cross-over piping 32a between the absorber 14 and the condenser 20. As shown in FIG. 4, the bypass loop 80 includes a first flow path 96 (particularly a second section 96b), a second flow path 98, a first flow path 96 and a second flow path. And a heat dissipation radiator 100 positioned between the 98.

The heat dissipation radiator 100 is designed to be located inside the crossover pipe 32a and includes a radiator inlet 102 and a radiator outlet 104. The hot water 30 from the heat exchanger inlet 84 passes from the first flow path 96 through the heat radiating radiator 100 and then passes through the second flow path 98 to the heat exchanger outlet 90. During operation of the system 10, coolant is circulating through the crossover pipe 32a. As the hot water 30 flows through the radiator 100, heat is transferred from the hot water 30 to the coolant in the cross pipe 32a. As such, the temperature of the hot water 30 at the outlet 104 of the radiator 100 is lower than the temperature of the hot water 30 at the inlet 102.

In the embodiment shown in FIG. 4, the heat dissipation radiator 100 is one U-shaped tubing, the diameter of which is significantly smaller than the diameter of the crossover tubing 32a. An advantage of the embodiment of FIG. 4 is that the standard piece tubing may be curved to form a U-shaped or hairpin shape. In other embodiments, the tubing may be curved in various ways as long as the tubing is configured to be positioned inside the crossover tubing 32a.

By storing the heat radiating radiator 100 inside the crossover pipe 32a, the system 100 does not require an additional heat exchanger configured to radiate heat from the hot water 30. Instead, the chiller system 10 has a hot water outlet temperature T _{HE. Use} an existing cooling source (ie coolant loop 32) for heat dissipation with _OUT ) rising above a predetermined level. In addition, the bypass loop 80 does not increase the footprint of the chiller system 10 because the heat dissipation radiator 100 is not housed in the crossover pipe 32a.

In a preferred embodiment, the radiator 100 maximizes the length L of the radiator 100 inside the cross piping 32a to maximize the amount of heat transferred from the radiator 100 to the coolant inside the cross piping 32a. It is configured to. In some embodiments, the radiator 100 may only remain in the crossover piping 32a, and in other embodiments, part of the radiator 100 may be a water box of the absorber 14 and / or the condenser 20. box).

5 is a schematic diagram of a control system 110 for controlling the operation of a chiller system 10 including a bypass loop 80. System 110 includes a controller 112, an input 114 to controller 112, and an output 116. Control system 110 includes additional inputs and outputs not included in FIG. 5 for clarity.

Input 114 is cooling request 118, heating request 120, T _{HE OUT} , T _{HE SET PT} , T _{ABS OUT} , T _{G2 OUT} , T _{G2 SET PT} . Because the chiller system 10 is configured for simultaneous air conditioning, the system 10 can have both cooling demands and heating demands at the same time. Usually, the system 10 may be operating under cooling or heating requirements. In addition, the system 10 may experience frequent fluctuations in cooling and / or heating needs. Based on the cooling request 118 and the heating request 120, the controller 112 controls the position of the valve 70 (CV1) that supplies heat (ie, waste gas) to the generator 16. As long as the overall demand (heating and cooling) does not exceed the maximum value, the controller 112 may not be required to specify the heating priority or cooling priority. However, if the overall demand is greater than the maximum value, the controller 12 may operate at least in part as a function of whether the system 10 has a heating priority or a cooling priority. In either case, when the overall demand is at or above the maximum value, control valve 70 (CVl) is fully open and controller 112 provides valve 72 to provide the required heating and / or cooling. , 74).

Since valve 72 (CV2) is configured to regulate the flow of condensate present in heat exchanger 26, valve 72 transfers heat to hot water 30 passing through heat exchanger 26. Control the power of 26. The position of the valve 72 (CV2) is determined by the temperature T _HE of the hot water 30b at the outlet 90. Partially controlled as a function of _OUT ). Temperature (T _{HE OUT} ) is the set point temperature T _HE for hot water, which may for example be generally set to 175 ° F (79.4 ° C) _{SET PT} ). Thus, as shown in FIG. 5, T _{HE OUT} and T _{HE SET} All _PTs are input to the controller 112.

As described above and shown in FIGS. 2 to 4, the temperature T _HE of the hot water 30 at the outlet 90 of the heat exchanger 26. _{If OUT} ) is too high, bypass loop 80 is configured to guide at least a portion of hot water 30 back from heat exchanger 26 to heat radiating radiator 100. As described above, the controller 112 may set the setpoint temperature T _{HE. SET} Temperature T _HE based on _PT ) Adjust CV2 to control _OUT ). Thus, the radiator radiator 100 has a temperature T _{HE OUT} ) is the set point temperature (T _{HE) SET It} is not normally used until it is higher than a predetermined value that is larger than _PT ). The valve 82 controls the flow of hot water 30 to the radiator 100 and is controlled by the controller 112. T _{HE When OUT} rises above a predetermined value, controller 112 opens valve 82 so that water 30 can flow through radiator 100. The predetermined value is the set point temperature (T _{HE). SET PT} ) and the sum of the limit values. For example, T _{HE SET If PT} is 175 ° F (79.4 ° C) and the limit value is 10 degrees, controller 112 is T _HE. Open valve 82 when _OUT is greater than 185 ° F (85 ° C). After this, the valve 82 is T _HE It may be closed when _OUT drops to a temperature less than or equal to a predetermined value. Control system 110 is T _HE At least one temperature sensor located around the outlet 90 of the heat exchanger 26 to measure _OUT .

As shown in FIG. 5, the input 114 is also T _G2 , which is the temperature of the liquid condensate present on the tube side of the generator 18. T _ABS which is the temperature of _OUT and the absorption solution (ie lithium bromide) present in the absorber 14 Contains _OUT T _{G2 OUT} And T _{ABS OUT} is T _HE by the controller 112 to determine the position of the valve 74 (CV3). _It can also be monitored with _OUT . As described above, the valve 72 (CV2) is the outlet temperature T _HE of the hot water 30. _OUT ) and to control the amount of heating provided by the heat exchanger 26. However, in some cases (eg low external ambient temperature), the outlet temperature of the hot water 30, even if the valve 72 (CV2) is fully open (ie to maximize the heating capacity of the heat exchanger 26). (T _{HE OUT} ) is the setpoint temperature (T _{HE) SET PT} ). In this case, the outlet temperature T _HE Raise _OUT ) and make it T _{HE SET} To get closer to _PT , T _{G2 OUT} , T _{ABS OUT} and T _{HE The} valve 74 CV3 may be adjusted based on _OUT . In addition, as shown in Figure 5, input 114 is T _{ABS OUT} and T _HE Set point temperature T _G2 for condensate present in low stage generator 18, which may be a function of _{OUT SET} Referred to as _PT ). Condensate Set Point Temperature (T _{G2) SET PT} ) is calculated by the controller 112 as a function of the input 114 to the controller 112 and thus T _{G2 SET PT} changes depending on the state inside the system 10. Controller 112 determines T _G2 to determine how to regulate valve 74. _OUT to T _{G2 SET} Compare with _PT . The control system 110 includes at least one temperature sensor at the outlet of the absorber 14 to measure the temperature T _{ABS OUT} of the absorbent solution and the temperature of the steam condensate T _G2. At least one sensor at the outlet of generator 18 to measure _OUT ).

As described herein and shown in FIGS. 1-4, the bypass loop 80 including the radiator 100 is used when the building does not have heating requirements and the outlet temperature of the hot water 30 is undesirably high. It may be used in the chiller system 10 to radiate or transfer heat from the warm water 30. The bypass loop 80 is designed such that existing piping 32a of the cooling water loop 32 in the system 10 may be used to radiate heat from the hot water 30 to the cooling water passing through the piping 32a. By this, the bypass loop 80 does not increase the footprint of the absorption chiller system 10. In addition, by using an existing cooling water loop, the bypass loop 80 does not require an additional heat exchanger dedicated to removing heat from the hot water 30.

In the exemplary embodiment shown and described above, the heat dissipation radiator 100 is a single piece of tubing having a U-shape and is located within the cross piping 32a. Additional designs for the radiator 100 may be used in the system 10. For example, in other embodiments, the heat dissipation radiator 100 may be located inside the piping of the coolant loop 32 at other locations within the system 10. Bypass loop 80 may be added to an existing cooler system, or may be included in the design of a new cooler.

Although the present invention has been described in connection with preferred embodiments, those 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.

Claims (22)

A system for use in a simultaneous air-conditioning absorption chiller having an absorber, a generator, a heat exchanger, a condenser, an evaporator, and a cooling water loop passing through the absorber and the condenser, Parallel to the heat exchanger, connected to the inlet and the outlet of the heat exchanger, configured to receive at least a portion of the hot water flowing to the heat exchanger, located inside a portion of the coolant loop and configured to transfer heat from the hot water to the coolant in the coolant loop A bypass loop containing a radiator, A valve for controlling the flow of hot water through the bypass loop; System for use in simultaneous HVAC absorption chillers. The method of claim 1, The valve is a solenoid valve System for use in simultaneous HVAC absorption chillers. The method of claim 2, The solenoid valve is operated when the temperature of the hot water at the outlet of the heat exchanger is higher than the predetermined temperature. System for use in simultaneous HVAC absorption chillers. The method of claim 1, The valve operates as a function of the difference between the temperature of the hot water at the outlet of the heat exchanger and the predetermined temperature. System for use in simultaneous HVAC absorption chillers. The method of claim 1, The radiator is a heat exchanger with a coolant loop System for use in simultaneous HVAC absorption chillers. The method of claim 5, Heat exchanger can be inserted into the coolant loop System for use in simultaneous HVAC absorption chillers. The method of claim 1, Bypass loop is A first flow passage connected to the inlet of the heat exchanger and configured to deliver hot water to the inlet of the radiator, And a second flow path connected to the outlet of the heat exchanger and configured to transfer hot water from the outlet of the radiator to the outlet of the heat exchanger. System for use in simultaneous HVAC absorption chillers. The method of claim 7, wherein The valve is located in the first flow path System for use in simultaneous HVAC absorption chillers. The method of claim 1, Further comprising a sensor for measuring the temperature of the hot water at the outlet of the heat exchanger System for use in simultaneous HVAC absorption chillers. System for controlling the temperature of hot water source in the simultaneous air-conditioning absorption chiller, With absorption cooler, A heat dissipation loop configured in parallel with the heat exchanger, A sensor for measuring the temperature of the hot water at the outlet of the heat exchanger, A valve for regulating the flow of hot water through the heat dissipation loop, The absorption chiller, An evaporator configured to receive a refrigerant in liquid form and to vaporize a portion of the refrigerant, An absorber configured to receive the absorbent solution and to receive the refrigerant in vaporized form from the evaporator such that the absorbent solution absorbs the refrigerant to form a diluted absorbent solution; A generator configured to receive the dilute absorption solution and the heat source so that the refrigerant is vaporized from the dilute absorption solution; A heat exchanger configured to receive at least a portion of the vaporized refrigerant from the generator, the heat exchanger configured to use the vaporized refrigerant to raise the temperature of the hot water passing through the heat exchanger, A condenser configured to receive a refrigerant in vaporized form and form a condensate that is recycled back to the evaporator, A coolant loop through the absorber and the condenser, The heat dissipation loop, A radiator located inside the coolant loop and configured to lower the temperature of the hot water delivered to the heat exchanger when there is no heating requirement; A first flow passage connected to the inlet of the heat exchanger and configured to direct a portion of the hot water to the radiator, A second flow path connected to the outlet of the heat exchanger and configured to direct hot water from the radiator to the outlet of the heat exchanger, System for controlling the temperature of hot water supply in a simultaneous air-conditioning absorption chiller. The method of claim 10, The position of the valve is a function of the difference between the temperature of the hot water supply at the outlet of the heat exchanger and the predetermined temperature. System for controlling the temperature of hot water supply in a simultaneous air-conditioning absorption chiller. The method of claim 11, The predetermined temperature is the sum of the set point and the limit value of the outlet temperature of the hot water source. System for controlling the temperature of hot water supply in a simultaneous air-conditioning absorption chiller. The method of claim 10, The valve is a solenoid valve System for controlling the temperature of hot water supply in a simultaneous air-conditioning absorption chiller. The method of claim 10, And a controller configured to receive a signal from the sensor and to control the valve as a function of the temperature of the hot water supply at the outlet of the heat exchanger. System for controlling the temperature of hot water supply in a simultaneous air-conditioning absorption chiller. The method of claim 10, The coolant loop includes cross piping between the absorber and the condenser, The radiator is a section of pipe that has a diameter smaller than the diameter of the cross pipe. System for controlling the temperature of hot water supply in a simultaneous air-conditioning absorption chiller. The method of claim 15, The radiator is U-shaped System for controlling the temperature of hot water supply in a simultaneous air-conditioning absorption chiller. A method of radiating heat from a hot water source that can be used for heating in a simultaneous HVAC absorber. Removing a portion of the hot water from the inlet of the auxiliary heat exchanger, The step of flowing hot water through the heat radiating radiator, where the heat radiating radiator is located inside the crossover piping between the absorber and the condenser, and the crossover piping directs the coolant so that the hot water discharged from the radiating radiator is at a lower temperature than the hot water entering the radiating radiator. Flowing hot water through a heat radiating radiator, configured to convey; Directing the hot water from the heat radiating radiator to the outlet of the auxiliary heat exchanger; Controlling the flow of water through the heat radiating radiator as a function of the outlet temperature of the water discharged from the outlet of the secondary heat exchanger; A method of radiating heat from a hot water source in a simultaneous HVAC absorber. The method of claim 17, Controlling the flow of water through the heat radiating radiator includes a solenoid valve A method of radiating heat from a hot water source in a simultaneous HVAC absorber. The method of claim 17, Controlling the flow of water through the heat dissipation radiator includes preventing water from flowing through the heat dissipation radiator when the outlet temperature of the water is lower than a predetermined value. A method of radiating heat from a hot water source in a simultaneous HVAC absorber. The method of claim 17, Controlling the flow of water through the heat dissipation radiator includes flowing water through the heat dissipation radiator if the outlet temperature of the water is higher than a predetermined value. A method of radiating heat from a hot water source in a simultaneous HVAC absorber. The method of claim 17, Sensing the temperature of the hot water discharged from the outlet of the auxiliary heat exchanger; A method of radiating heat from a hot water source in a simultaneous HVAC absorber. The method of claim 17, The radiator radiator is a U-shaped pipe A method of radiating heat from a hot water source in a simultaneous HVAC absorber.

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