Cooling systems and methods incorporating a plural in-series pumped liquid refrigerant trim evaporator cycle

Abstract

Systems and methods relating to a plural in-series pumped liquid refrigerant trim evaporator cycle are described. The cooling systems include a first evaporator coil in thermal communication with an air intake flow to a heat load, and a first liquid refrigerant distribution unit in thermal communication with the first evaporator coil. The cooling systems further include a second evaporator coil disposed in series with the first evaporator coil in the air intake flow and in thermal communication with the air intake flow, and a second liquid refrigerant distribution unit in thermal communication with the second evaporator coil. A trim compression cycle of the second liquid refrigerant distribution unit is configured to further cool the air intake flow through the second evaporator coil when the temperature of the first fluid flowing out of the main compressor of the second liquid refrigerant distribution unit exceeds a predetermined threshold temperature.

Claims

1. A cooling system comprising: a first evaporator in thermal communication with an air intake flow to a heat load; a first liquid refrigerant distribution unit in thermal communication with the first evaporator and a first fluid free-cooled by a fluid cooler; a second evaporator disposed in series with the first evaporator in the air intake flow and in thermal communication with the air intake flow to the heat load; and a second liquid refrigerant distribution unit in thermal communication with the second evaporator and the first fluid free-cooled by the fluid cooler, wherein the first liquid refrigerant distribution unit includes: a third evaporator in fluid communication with the fluid cooler and configured to enable transfer of heat from the first fluid flowing from the fluid cooler to a second fluid; a first main condenser in fluid communication with the first and third evaporators and configured to enable transfer of heat from a third fluid flowing from the first evaporator to the first fluid flowing from the third evaporator; and a first trim condenser in fluid communication with the first main condenser and the third evaporator and configured to enable transfer of heat from the second fluid flowing from the third evaporator to the first fluid flowing from the first main condenser, and wherein a trim compression cycle of the second liquid refrigerant distribution unit is configured to incrementally further cool the air intake flow through the second evaporator when the temperature of the free-cooled first fluid flowing out of the second liquid refrigerant distribution unit exceeds a predetermined temperature.

2. The cooling system according to claim 1, wherein the first evaporator is disposed upstream from the second evaporator in the air intake flow.

3. The cooling system according to claim 2, wherein the predetermined temperature is the maximum temperature needed to bring the temperature of the air intake flow out of the second evaporator down to a desired temperature.

4. The cooling system according to claim 1, wherein the first liquid refrigerant distribution unit further includes: a compressor in fluid communication with a fluid output of the third evaporator and a fluid input of the trim condenser; and an expansion valve in fluid communication with a fluid output of the trim condenser and a fluid input of the third evaporator to form the trim compression cycle.

5. The cooling system according to claim 4, wherein the first liquid refrigerant distribution unit further includes: a fluid receiver in fluid communication with a fluid output of the first main condenser; and a fluid pump in fluid communication with a fluid output of the fluid receiver and a fluid input of the first evaporator.

6. The cooling system according to claim 1, wherein the first fluid is water, the second fluid is a first refrigerant, and the third fluid is a second refrigerant.

7. The cooling system according to claim 1, wherein the second liquid refrigerant distribution unit includes: a fourth evaporator in fluid communication with the fluid cooler and configured to enable transfer of heat from the first fluid flowing from the fluid cooler to a fourth fluid; a second main condenser in fluid communication with the second and fourth evaporators and configured to enable transfer of heat from a fifth fluid flowing from the second evaporator to the first fluid flowing from the fourth evaporator; and a second trim condenser in fluid communication with the second main condenser and the fourth evaporator and configured to enable transfer of heat from the fourth fluid flowing from the fourth evaporator to the first fluid flowing from the second main condenser.

8. The cooling system according to claim 7, wherein the first fluid is a water-based solution, the second fluid is a first refrigerant, and the fourth fluid is a second refrigerant.

9. The cooling system according to claim 7, wherein the second liquid refrigerant distribution unit further includes: a fluid receiver in fluid communication with an output of the second main condenser; and a fluid pump in fluid communication with a fluid output of the fluid receiver and a fluid input of the second evaporator.

10. The cooling system according to claim 1, wherein the second liquid refrigerant distribution unit includes: a second main condenser in fluid communication with the fluid cooler and configured to enable transfer of heat from the first fluid flowing from the fluid cooler to a fourth fluid flowing through the second main condenser; and a fourth evaporator in fluid communication with the second main condenser and the second evaporator and configured to enable transfer of heat from a fifth fluid flowing from the second evaporator to the fourth fluid flowing from the second main condenser.

11. The cooling system according to claim 10, wherein the second liquid refrigerant distribution unit further includes: an expansion valve in fluid communication with a fluid output of the second main condenser and a fluid input of the third evaporator; and a compressor in fluid communication with a fluid output of the third evaporator and a fluid input of the second main condenser to form a second trim compression cycle.

12. The cooling system according to claim 10, wherein the second liquid refrigerant distribution unit further includes: a fluid receiver in fluid communication with a fluid output of the third evaporator; and a fluid pump in fluid communication with a fluid output of the fluid receiver and a fluid input of the second evaporator.

13. A method of operating a cooling system, comprising: pumping a first refrigerant through a first evaporator coil in thermal communication with an air intake flow to a heat load; pumping a free-cooled fluid through a first liquid refrigerant distribution unit in thermal communication with the first refrigerant flowing through the first evaporator coil; pumping a second refrigerant through a second evaporator coil disposed in series with the first evaporator coil in thermal communication with the air intake flow downstream from the first evaporator coil; pumping a free-cooled fluid through a second liquid refrigerant distribution unit in thermal communication with the second refrigerant flowing through the second evaporator coil; determining whether the temperature of the free-cooled fluid flowing out of a condenser of the second liquid refrigerant distribution unit is greater than a predetermined temperature threshold; turning on a trim compression cycle of the second liquid refrigerant distribution unit if it is determined that the temperature of the free-cooled fluid flowing out of the condenser of the second liquid refrigerant distribution unit is greater than the predetermined temperature threshold; and incrementally increasing a heat load capacity of the trim compression cycle as the wet bulb temperature of the outside environment increases.

14. The method according to claim 13, wherein the predetermined threshold temperature is determined based on the temperature of the free-cooled fluid flowing out of the condenser of the second liquid refrigerant distribution unit that cannot fully condense the second refrigerant back to a liquid.

15. The method according to claim 13, further comprising incrementally changing the heat load capacity of the trim compression cycle of the second liquid refrigerant distribution unit as outside environmental conditions change.

16. A cooling system comprising: a first evaporator in thermal communication with an air intake flow to a heat load; a first liquid refrigerant distribution unit in thermal communication with the first evaporator; a second evaporator disposed in series with the first evaporator in the air intake flow and in thermal communication with the air intake flow to the heat load; a second liquid refrigerant distribution unit in thermal communication with the second evaporator, wherein the first liquid refrigerant distribution unit includes: a third evaporator in fluid communication with the fluid cooler and configured to enable the transfer of heat from the first fluid flowing from the fluid cooler to a second fluid; a first main condenser in fluid communication with the first and third evaporators and configured to enable the transfer of heat from a third fluid flowing from the first evaporator to the first fluid flowing from the third evaporator; and a first trim condenser in fluid communication with the first main condenser and the third evaporator and configured to enable the transfer of heat from the second fluid flowing from the third evaporator to the first fluid flowing from the first main condenser; a fluid cooler for free cooling a first fluid; and a fluid pump for circulating the first fluid through the first and second liquid refrigerant distribution units, wherein a trim compression cycle of the second liquid refrigerant distribution unit is configured to incrementally further cool the air intake flow through the second evaporator when the temperature of the free-cooled first fluid flowing out of a condenser of the second liquid refrigerant distribution unit exceeds a predetermined temperature.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 is a schematic flow diagram of a cooling system using a dual pumped liquid refrigerant system according to embodiments of the present disclosure that includes a primary evaporator and a secondary evaporator in thermal communication with a cooling air flow to a heat load;

(2) FIG. 2 is a schematic flow diagram illustrating the dual pumped liquid refrigerant system according to FIG. 1, where the system includes two individual pumped liquid refrigerant circuits associated with the respective primary and secondary evaporators;

(3) FIG. 3 is a schematic flow diagram of an alternate embodiment of the dual pumped liquid refrigerant system of FIG. 2, which includes a second liquid refrigerant circuit associated with the secondary evaporator having a refrigerant-to-refrigerant heat exchanger in lieu of a water-to-refrigerant heat exchanger of a first liquid refrigerant circuit associated with the primary evaporator; and

(4) FIG. 4 is a flowchart illustrating a method of operating a dual pumped liquid refrigerant system according to embodiments of the present disclosure.

DETAILED DESCRIPTION

(5) The dual pumped liquid refrigerant system of the present disclosure includes circuits that are intended to operate either alone or in series. The primary circuit implements a free cooling water-cooled pumped refrigerant process with an in-series trim refrigerant circuit that is capable of trimming the entering condenser process water. The refrigerant trim process is only energized when the outside environmental conditions (e.g., wet bulb conditions) cannot fully condense the refrigerant back to a liquid at a given condenser setpoint.

(6) The secondary circuit is a similar circuit to the primary circuit. It is intended to provide supplemental trim cooling when the primary circuit cannot sufficiently handle the load on its own. The dual circuits can also be operated in a non-compression primary and back-up compression secondary operation for greater overall combined system efficiencies. When operating the circuits in tandem, the effective compressor load is reduced by more than 50-70%.

(7) Additionally, because the refrigerant circuits are in series, the “lift” of the compressor is greatly reduced, which enables the compressor to operate at a highly efficient kw per ton. This reduction in kw per ton can be at least ten times more efficient than an air-cooled system plant, and at least four times more efficient than a compressor operating on a traditional water-cooled plant. The process heat that is generated by this cycle is intended to be transported and rejected to the atmosphere using a fluid cooler, cooling tower 3000, or other heat rejection apparatus.

(8) FIG. 1 illustrates a dual pumped liquid refrigerant system 1000 according to embodiments of the present disclosure that includes a primary evaporator 331′ and a secondary evaporator 332′ in direct contact with cooling air flowing through a fresh air intake 101 to a heat load 50′ that is downstream of an air handling unit (AHU) 52. The dual pumped liquid refrigerant system 1000 is suitable for low wet bulb environments.

(9) The flow of cooling air is directed to the air handling unit 52 from the fresh air intake 101 through cooling air conduits 1001, 1002, and 1003. The first cooling air conduit 1001 provides fluid communication between the fresh air intake 101 to a secondary evaporator coil 332′. Upon flowing through the secondary evaporator coil 332′, the cooling air is directed through second air flow conduit 1002 to primary evaporator coil 331′ to provide fluid communication between the primary and secondary evaporator coils 331′ and 332′, respectively. Upon flowing through the primary evaporator coil 331′, the cooling air is directed through third air flow conduit 1003 to provide fluid communication with the air handling unit 52 and the heat load 50′.

(10) The primary evaporator coil 331′ is in fluid communication with a primary liquid refrigerant pumped circuit or distribution unit 2111 via liquid refrigerant supply header 201′ and liquid refrigerant return header 251′.

(11) Similarly, the secondary evaporator coil 332′ is in fluid communication with a secondary liquid refrigerant pumped circuit or distribution unit 2122 via liquid refrigerant supply header 202′ and liquid refrigerant return header 252′.

(12) The primary and secondary liquid refrigerant pumped circuits or distribution units 2111 and 2122, are each supplied cooling water via a common cooling water supply header 3100. Upon transferring heat from the primary and secondary liquid refrigerant pumped circuits or distribution units 2111 and 2122, the cooling water is discharged to a cooling tower 3000 via a common cooling water return header 3110. Via the fluid communication between the cooling air flowing through the air conduits 1001, 1002, and 1003 from the fresh air intake 101, the primary and secondary evaporator coils 331′ and 332′, and the primary and secondary liquid refrigerant pumped circuit or distribution units 2111 and 2122, the cooling air flowing through the air conduits 1001, 1002 and 1003 from the fresh air intake 101 is thereby in thermal communication with the cooling tower 3000.

(13) The heat removal from the cooling air flowing through the air conduits 1001, 1002, and 1003 is rejected to the environment via the cooling tower 3000. Cooling fluid pumps 3001 and 3002 are disposed in the common cooling water return header 3110 to provide forced circulation flow of the cooling fluid, generally water, from the cooling tower 3000 to the primary and secondary liquid refrigerant pumped circuit or distribution units 2111 and 2122, respectively.

(14) Turning now to FIG. 2, primary and secondary liquid refrigerant pumped circuits or distribution units 2111 and 2122 include primary evaporator coil 331′ and secondary evaporator coil 332′ that are supplied and return liquid refrigerant via first liquid refrigerant assist cycle supply headers 201′ and 202′ and first liquid refrigerant assist cycle return headers 251′ and 252′, respectively, from first and second liquid refrigerant assist circuits 2001′ and 2002′, respectively.

(15) First liquid refrigerant assist cycle return headers 251′ and 252′ return to main condensers 2691 and 2692, respectively, through which the at least partially vaporized liquid refrigerant is condensed and returned to the liquid receivers 255′ and 256′ via evaporator to liquid receiver supply lines 253′ and 254′. A minimum level of liquid refrigerant is maintained in the receivers 255′ and 256′. Liquid refrigerant in the receivers 255′ and 256′ is in fluid communication with the suction side of liquid refrigerant pumps 257′ and 258′ and is discharged as a pumped liquid via the liquid refrigerant pumps 257′ and 258′ to the primary evaporator 331′ and secondary evaporator 332′ via the liquid refrigerant assist cycle supply headers 201′ and 202′, respectively. To ensure minimum recirculation flow in the receivers 255′ and 256′, at least the receiver 255′ may include a bypass control valve 259′ that provides fluid communication between the liquid refrigerant assist cycle supply header 201′ on the discharge side of liquid refrigerant pump 257′ and the receiver 255′.

(16) The main condensers 2691 and 2692 are in thermal and fluid communication with trim condensers 2693 and 2694, and with evaporators 2701 and 2702, respectively, in the following manner. Cooling water supplied from the common cooling water supply header 3100 is supplied in series via cooling water supply to evaporator conduit lines 3101 and 3102 first to evaporators 2701 and 2702, then to main condensers 2691 and 2692 via evaporator to main condenser cooling water conduit lines 3103 and 3104, then to trim condensers 2693 and 2694 via main condenser to trim condenser cooling water conduit lines 3105 and 3106, and then from trim condensers 2693 and 2694 back to cooling water return header 3110 via trim condenser to return header cooling water conduit lines 3107 and 3108, respectively.

(17) In each of the primary and secondary liquid refrigerant pumped circuit or distribution units 2111 and 2122, a second liquid refrigerant is in thermal and fluid communication with the respective evaporators 2701 and 2702 and with the respective trim condensers 2693 and 2694 in the following manner. When the trim condensers 2693 and 2694 are in operation, the second liquid refrigerant, in an at least partially vaporized state, is transported from the evaporators 2701 and 2702 at the refrigerant outlet to the suction of trim condenser compressors 2655 and 2666 via evaporator to trim condenser compressor second liquid refrigerant conduit lines 2653 and 2664, respectively.

(18) The second liquid refrigerant is discharged from the trim condenser compressors 2655 and 2666 as a high pressure gas and transported from the trim condenser compressors 2655 and 2666 to the trim condensers 2693 and 2694 via trim condenser compressor to trim condenser second refrigerant conduit lines 2657 and 2668, respectively. Upon transferring heat in the trim condensers 2693 and 2694 to the cooling water flowing through the trim condensers via the cooling water conduit lines 3105, 3106, 3107, and 3108 back to the cooling water return header 3110, the high pressure gas is condensed in the trim condensers 2693 and 2694 and transported as a liquid refrigerant from the trim condensers 2693 and 2694 to the refrigerant inlet of evaporators 2701 and 2702 via trim condenser to evaporator liquid refrigerant lines 2801 and 2802, respectively.

(19) As shown in the primary liquid refrigerant distribution unit 2111 of FIG. 2, a temperature switch or sensor TS 2605 may be disposed in evaporator to trim condenser compressor conduit line 2653 and may be used to control a liquid refrigerant expansion valve 2803 disposed in trim condenser to evaporator conduit line 2801 to control the flow of cold gas to the evaporator 2701. Similarly, as shown in the secondary liquid refrigerant distribution unit 2122, a pressure and temperature sensor PT 2606 may be disposed in the evaporator to trim condenser compressor conduit line 2664 and may be used to control a liquid refrigerant expansion valve 2804 disposed in trim condenser to evaporator conduit line 2802 to control the flow of cold gas to the evaporator 2702.

(20) Thus, cooling water is supplied in series to the evaporators 2701 and 2702, to the main condensers 2691 and 2692, and to the trim condensers 2693 and 2694. The system 1000 may be operated in various modes depending upon the heat load presented by the fresh air at fresh air intake 101. That is, operation may range from the minimum operational state of the primary evaporator 331′ in operation with the liquid receiver 255′ and main condenser 2691. If conditions warrant, the trim condenser 2693 may be placed into operation in conjunction with operation of the trim condenser compressor 2655.

(21) Again, if conditions warrant, the secondary evaporator 332′ may be placed into operation with the same operational sequence applied. If the heat load decreases, the cooling operation may be reduced in the opposite sequence beginning with reduction of the secondary evaporator 332′ cooling followed by reduction of the primary evaporator 331′ cooling or even beginning with reduction of the primary evaporator 331′ cooling.

(22) In the exemplary embodiments of FIGS. 1 and 2, the primary liquid refrigerant distribution unit 2111 and the secondary liquid refrigerant distribution unit 2122 are functionally mirror images or duplicates of each other. That is to say, although the capacity and sizing of the secondary evaporation coil 332′ and secondary liquid refrigerant distribution unit 2122 are generally the same as the capacity and sizing of the primary evaporation coil 331′ and primary liquid refrigerant distribution unit 2111, respectively, the capacity and sizing may differ one from the other, depending on the particular design requirements or choices. The first liquid refrigerant assist circuit 2001′ is dedicated to, and in fluid communication with, the first evaporation coil 331′, while the second liquid refrigerant assist circuit 2002′ is dedicated to, and in fluid communication with, the second evaporation coil 332′.

(23) Accordingly, the first and second evaporation coils 331′ and 332′ are in fluid communication with the first and second liquid refrigerant assist circuits 2001′ and 2002′ via first liquid refrigerant assist cycle supply headers 201′, 202′ and first liquid refrigerant assist cycle return headers 251′, 252′, respectively.

(24) For some environments, the primary liquid refrigerant distribution unit 2111 may not include the evaporator 2701, the expansion valve 2803, the compressor 2655, or the trim condenser 2693. That is, the main condenser 2691 may be in direct fluid communication with the common cooling water supply header 3100 and the cooling water return header 3110 so that cooling water flows from the common cooling water supply header 3100, through the main condenser 2691, and back to the cooling water return header 3110.

(25) FIG. 3 is a schematic flow diagram that is similar to the schematic of FIG. 2. The differences are in the secondary circuit. The secondary cooling circuit possesses a refrigerant-to-refrigerant heat exchanger in lieu of the water-to-refrigerant heat exchanger. This is more beneficial in high wet bulb environments. This is a cooling system that exhibits greatly improved cooling production to power use ratios over a broad spectrum of environmental conditions and system loading.

(26) FIG. 3 indicates two cycles: the first cycle is a plural water-to-refrigerant pumped solution which is best utilized in low to moderate wet bulb conditions (below 24° C. wet bulb). The cycle illustrated in FIG. 3 is optimized for use in environments that incur higher wet bulb spikes. Under both systems illustrated in FIGS. 2 and 3, the cycles enable a heat absorption process that is performed in steps or stages. The primary heat absorption is performed at the primary evaporator. In some embodiments, depending on the environment and the desired cooling requirements (e.g., ultimate discharge air temperature), the primary evaporator cycle can absorb as much as 50%-70% of the incoming present cooling load at approximately 10% of the power use that would normally be required in a compressor cycle.

(27) The balance of the load can be cooled by either utilizing the primary trim compressor (on the primary evaporator circuit) or by staging further cooling downstream at the secondary evaporator circuit. The resultant load that remains to be cooled in the secondary circuit (if there is any) can be handled at a greatly reduced capacity. By staging the heat rejection process utilizing a pumped refrigerant circuit as a primary means of cooling, the power to cooling capacity ratio is effectively reduced by as much as 90% for the primary or initial stage of cooling, and the further (secondary staged) or incremental cooling reduces the total power required by as much as 77% as compared to a conventional chiller plant system to cool fresh air intake systems, thereby optimizing effects of latent heat of vaporization so as to supplant traditional compressed refrigerant cooling systems for many applications.

(28) FIG. 3 illustrates an alternate embodiment of the dual-pumped liquid refrigerant system 1000 of FIGS. 1 and 2 that includes circuits that are intended to operate either alone or in series. The dual-pumped liquid refrigerant system 1000′ differs from dual-pumped liquid refrigerant-system 1000 in that the secondary liquid refrigerant pumped circuit or distribution unit 2122 is replaced by secondary liquid refrigerant pumped circuit or distribution unit 212′.

(29) Cooling water is supplied to secondary liquid refrigerant pumped circuit or distribution unit 212′ via the cooling tower 3000 and the common cooling water supply header 3100 and common cooling water return header 3110.

(30) Generally speaking, although the capacity and sizing of the second evaporation coil 332′ and second liquid refrigerant distribution unit 212′ are the same as the capacity and sizing of the first evaporation coil 331′ and first liquid refrigerant distribution unit 2111, the capacity and sizing may differ one from the other, depending on the particular design requirements or choices. The first liquid refrigerant assist circuit 2001′ is dedicated to, and in fluid communication with, the first evaporation coil 331′, while second liquid refrigerant assist circuit 2012′ is dedicated to, and in fluid communication with, the second evaporation coil 332′.

(31) Accordingly, the first and second evaporation coils 331′ and 332′ are again in fluid communication with the first and second liquid refrigerant assist circuits 2001′ and 2012′ via first liquid refrigerant assist cycle supply headers 201′ and 202′ and first liquid refrigerant assist cycle return headers 251′ and 252′, respectively.

(32) As liquid refrigerant is supplied to first and second evaporation coils 331′ and 332′ via the first liquid refrigerant assist cycle supply headers 201′ and 202′, the liquid refrigerant is at least partially vaporized by transfer of heat from the first and second evaporation coils 331′ and 332′ such that at least partially vaporized refrigerant in the form of a gas or a gas and liquid refrigerant mixture is returned via liquid refrigerant assist circuit return headers 251′ and 252′ to evaporators 2701 and 262′, included within first and second liquid refrigerant assist circuits 2001′ and 2012′, respectively.

(33) As the process for transferring heat from the primary evaporator 331′ to the cooling tower 3000 via first liquid refrigerant distribution unit 2111 is the same as described above with respect to FIGS. 1 and 2, the following description is generally directed to describing the process for transferring heat from the secondary evaporator 332′ to the cooling tower 3000 via secondary liquid refrigerant distribution unit 2122.

(34) Accordingly, within the evaporator 262′, heat is transferred from the gas or gas and liquid refrigerant mixture such that condensation of the liquid refrigerant occurs within the evaporator 262′ and liquid refrigerant is discharged via evaporator to liquid receiver supply line 254′ to liquid receiver 256′. The liquid refrigerant receiver 256′ is operated to maintain a supply of liquid refrigerant on the suction side of liquid refrigerant pump 258′, which discharges liquid refrigerant into the liquid refrigerant assist cycle supply header 202′ to supply liquid refrigerant again to the evaporation coil 332′.

(35) Thus, the liquid refrigerant distribution unit 212′ is in thermal communication with the fresh air intake air flow through the second and third air conduits 1002 and 1003 and the secondary evaporation coil 332′, and is configured to circulate a second fluid, i.e., the first liquid refrigerant flowing in the first liquid refrigerant assist cycle supply header 202′ and first liquid refrigerant assist circuit return header 252′, thereby enabling heat transfer from the intake air flow at 101 to the first liquid refrigerant.

(36) The circulation or flow of a first liquid refrigerant from the evaporators 2701 and 262′ to the evaporator coils 331′ and 332′ via the liquid refrigerant pumps 257′ and 258′ and the liquid receivers 255′ and 256′, and back to the main condenser 2691 and evaporator 262′ as a gas or a gas and liquid refrigerant mixture, define first liquid refrigerant circuits 2001′ and 2012′, respectively.

(37) Heat is transferred within the evaporator 262′ from the condensation side represented by the flow of the gas or gas and liquid refrigerant mixture in the liquid refrigerant assist circuit return header 252′ to the liquid refrigerant assist cycle supply header 202′, to the trim evaporation side of the evaporator 262′. The trim evaporation side is represented by the flow to the evaporator 262′ of a second liquid refrigerant flowing in the second liquid refrigerant circuit or trim compressor circuit 2004′ of the second liquid refrigerant distribution unit 212′.

(38) The trim evaporation side is also represented by the second liquid refrigerant circuit 2004′, in which a second liquid refrigerant is circulated from the evaporator 262′ to the condenser 270′ such that the second refrigerant is received in liquid form from the condenser 270′ via the second refrigerant condenser to the evaporator supply line 274′. The second refrigerant in liquid form is then evaporated in the evaporator 262′ via the transfer of heat from the first liquid refrigerant circuit 2012′ side of the evaporator 262′.

(39) The at least partially evaporated second refrigerant, evaporated via a trimming method, flows or circulates from the evaporator 262′ to the suction side of trim compressor 266′ via evaporator to compressor suction connection line 264′. The trim compressor 266′ compresses the at least partially evaporated second refrigerant to a high pressure gas. For example, the compressed high pressure gas may have a pressure range of approximately 135-140 psia (pounds per square inch absolute).

(40) The high pressure second refrigerant gas circulates from the discharge side of compressor 266′ to the condenser side of condenser 270′ via compressor discharge to condenser connection line 268′. Heat is transferred from the condenser side of condenser 270′ to the water side of the condenser 270′. Cooling water supplied from the common cooling water supply header 3100 is supplied to the water side of condenser 270′ via cooling water supply to condenser conduit line 3101′. The cooling water is then returned from condenser 270′ back to cooling water return header 3110 via condenser to return header cooling water conduit line 3202′.

(41) Cooling the intake air occurs by sequentially and incrementally operating the primary evaporator cooling coil 331′ and the secondary evaporator cooling coil 332′ in the same manner as the sequential and incremental operation of primary evaporator cooling coil 331′ and secondary evaporator cooling coil 332′ described above with respect to FIG. 2.

(42) Those skilled in the art will recognize and understand that the secondary liquid refrigerant pumped circuit or distribution unit 212′ for cooling of the fresh air intake via secondary evaporator 332′ may be operated in an incremental manner in conjunction with the operation of the primary liquid refrigerant pumped circuit or distribution unit 2111 for cooling the fresh air intake via primary evaporator 331′ as described above.

(43) FIG. 4 is a flowchart illustrating a method of operating a dual pumped liquid refrigerant system according to embodiments of the present disclosure. In step 402, a first refrigerant is pumped through a first evaporator coil in thermal communication with an air intake flow to a heat load. In step 404, a free-cooled fluid is pumped through a first liquid refrigerant distribution unit in thermal communication with the first refrigerant flowing through the first evaporator coil. In step 406, a second refrigerant is pumped through a second evaporator coil disposed in series with the first evaporator coil and in thermal communication with the air intake flow downstream from the first evaporator coil. In step 408, a free-cooled fluid is pumped through a second liquid refrigerant distribution unit in thermal communication with the second refrigerant flowing through the second evaporator coil.

(44) Next, in step 410, it is determined whether the temperature of the free-cooled fluid flowing out of the main condenser of the second liquid refrigerant distribution unit is greater than a predetermined threshold temperature. The predetermined threshold temperature may be determined based upon the temperature of the free-cooled fluid flowing out of the main condenser needed to fully condense the refrigerant flowing through the second evaporator coil back to a liquid. If, in step 410, it is determined that the temperature of the free-cooled fluid flowing out of the main condenser of the second liquid refrigerant distribution unit is not greater than the predetermined threshold temperature, then the method returns to step 402. Otherwise, a trim compression cycle of the second liquid refrigerant distribution unit is turned on, in step 412, and the heat load capacity of the trim compression cycle of the second liquid refrigerant distribution unit is incrementally changed based on changes in the temperature of the free-cooled fluid flowing out of the main condenser of the second liquid refrigerant distribution unit, in step 414. Then, the method returns to step 402.

(45) In some cases, the trim compression cycle of the first liquid refrigerant distribution unit may be turned on and incrementally controlled based on the outside environmental conditions, e.g., the wet bulb temperature, if a component of the second liquid refrigerant distribution unit fails or the trim compression cycle of the second liquid refrigerant distribution unit is unable to cool the air intake flow to a desired temperature because of the outside environmental conditions.

(46) Other applications for the in series pumped liquid refrigerant trim evaporator cycle or system include turbine inlet air cooling, laboratory system cooling, and electronics cooling, among many others.