Patent Publication Number: US-2020278137-A1

Title: Refrigeration systems and methods related thereto

Description:
RELATED APPLICATION 
     The application claims priority from U.S. Provisional application having Ser. No. 62/586,897 filed on Nov. 16, 2017, which is incorporated herein by reference for all purposes. 
    
    
     FIELD 
     The present teachings and arrangements relate to refrigeration systems. More particularly, the present teachings and arrangements relate to novel systems and process for controlling refrigeration systems (hereinafter also referred to “cooling load controllers”) using a pre-mixing mechanism. 
     BACKGROUND 
     Conventional refrigeration systems require energy to effectively compress a refrigerant. Unfortunately, the energy required to compress the refrigerant comes from an external source, which reduces the efficiency of the refrigeration system and limits the controllability of refrigerant compression. 
     What is, therefore, need are improved systems and processes to efficiently adjust compression in a refrigeration system. 
     SUMMARY 
     To achieve the foregoing, the present teachings provide novel systems and processes for adjusting compression in a refrigeration system. In one aspect, the present arrangements provide a pre-mixing mechanism. An exemplar of such pre-mixing mechanism includes: (i) a complementary chamber; (ii) an actuating chamber that is separate from the complementary chamber; (iii) a complementary chamber input line; (iv) a complementary piston; (v) a complementary chamber output line; (vi) an actuating chamber input line; (vii) an actuating piston; and (viii) an actuating chamber output line. 
     The complementary chamber input line receives and conveys gas and/or vapor resulting from evaporation to the complementary chamber. In a preferred embodiment of the present arrangements, the complementary chamber input line receives and conveys gas and/or vapor resulting from an evaporator serving a cooling load. The complementary chamber input line includes a first complementary chamber inlet and a second complementary chamber inlet. 
     Each of the first and the second complementary chamber inlets is designed to convey gas and/or vapor to two different or opposite ends of the complementary chamber. The complementary chamber, in one embodiment of the present arrangements, is part of a cooling load controller. The complementary piston evacuates the gas and/or the vapor inside the complementary chamber to produce exhaust gas and/or exhaust vapor. The complementary chamber output line directs exhaust gas and/or exhaust vapor from complementary chamber towards a mixing line and includes a first complementary chamber outlet and a second complementary chamber outlet. Each of the first and the second complementary chamber outlets is designed to remove gas and/or vapor from two different or opposite ends of the complementary chamber. 
     The actuating chamber input line receives and conveys gas and/or vapor resulting from heating to the actuating chamber and includes a first actuating chamber inlet and a second actuating chamber inlet. Each of the first and the second actuating chamber inlets is designed to convey gas and/or vapor to two different or opposite ends of the actuating chamber. The actuating piston evacuates the gas and/or the vapor inside the actuating chamber to produce exhaust gas and/or exhaust vapor. The actuating chamber output line directs exhaust gas and/or exhaust vapor from actuating chamber towards the mixing line and includes a first actuating chamber outlet and a second actuating chamber outlet. Each of the first and the second actuating chamber outlets is designed to remove gas and/or vapor from two different or opposite ends of the actuating chamber. In a preferred embodiment of the present arrangements, the complementary piston and the actuating piston are coupled to allow for movement of the complementary piston and the actuating piston in same direction. 
     In an operative state of the pre-mixing mechanism, according to one embodiment of the present arrangements, vapor or gas entering through the first actuating chamber inlet, disposed at a first end of the actuating chamber, pushes the actuating piston away from the first end and evacuates vapor and/or gas inside the actuating chamber. Movement of the actuating piston in a direction away from the first end also allows movement of the complementary piston in the same direction and evacuates vapor and/or gas inside the complementary chamber. Vapor or gas entering through the second actuating chamber inlet, disposed at a second end of the actuating chamber, pushes the actuating piston away from the second end and evacuates vapor and/or gas inside the actuating chamber. Movement of the actuating piston in a direction away from the second end also allows movement of the complementary piston in the same direction, which evacuates vapor and/or gas inside the complementary chamber. 
     The present teachings provide novel systems and processes for adjusting compression in a refrigeration system using a cooling load controller. A cooling load controller, in one embodiment of the present arrangements includes: (i) an energy source; (ii) a pre-mixing mechanism; (iii) a mixing line; and (iv) a condensate line. 
     The cooling load controller may use a refrigerant in the first state (to facilitation discussion, hereinafter also referred to as a “high-pressure fluid” because one attribute of this state of the refrigerant includes its pressure state) and a refrigerant of a second state (to facilitate discussion, hereinafter also referred to as a “low-pressure fluid” because one attribute of this state of the refrigerant includes its pressure state). In a preferred embodiment of the present arrangements, the refrigerant in the first state is a high-pressure refrigerant and refrigerant in the second state is a low-pressure refrigerant. The high-pressure fluid has a pressure that is higher than the low-pressure fluid. 
     The pre-mixing mechanism is designed to evacuate refrigerant in a second state using a force applied by the fluid in the first state to produce exhaust fluid in the first state (hereinafter referred to as a “actuating chamber exhaust fluid”) and exhaust fluid in the second state (hereinafter referred to as a “complementary chamber exhaust fluid”). The pre-mixing mechanism is coupled, on an inlet side of the pre-mixing mechanism, to the energy source and coupled, on an outlet side, to two or more outlets, at least one of which is designed to dispense actuating chamber exhaust fluid and at least another of which is designed to dispense complementary chamber exhaust fluid. 
     The mixing line mixes complementary chamber exhaust fluid and actuating chamber exhaust fluid to produce exhaust fluid in an intermediate state (to facilitate discussion, hereinafter also referred to as an “intermediate pressure fluid” because one attribute of this state of the refrigerant includes its pressure state). Intermediate pressure fluid has a higher pressure than the low-pressure refrigerant and has a lower pressure than the high-pressure refrigerant. 
     The mixing line is coupled, at a receiving end, to the outlets of the pre-mixing mechanism and is configured to be coupled, at a dispensing end, to a condenser for treating the intermediate pressure fluid to produce refrigerant condensate in the intermediate state (to facilitate discussion, hereinafter also referred to as an “intermediate pressure condensate fluid” because one attribute of this state of the refrigerant includes its pressure state). The condensate line conveys a portion of intermediate pressure condensate fluid from condenser to the energy source. In one embodiment of the present arrangements, the energy source is a solar panel capable of energizing intermediate pressure condensate fluid to produce high-pressure fluid. 
     In one embodiment of the present arrangements, cooling load controller includes at least one component chosen from a group comprising a high-pressure intake valve, a regulator, a liquid injection pump, a pneumatic pump, a high-pressure bypass line, and a pressure intake valve. The high-pressure intake valve is disposed between the energy source and the pre-mixing mechanism and is designed to regulate high-pressure fluid before pre-mixing mechanism receives the high-pressure fluid. The regulator valve is disposed between condenser and the energy source and is designed to regulate volume of intermediate pressure condensate fluid conveyed to the energy source. The liquid injection pump that is disposed on the condensate line for pumping intermediate pressure condensate fluid from condenser to the energy source. The pneumatic pump coupled to and drives the liquid injection pump. The high-pressure bypass line is disposed between the energy source and the mixing line and is capable of conveying high-pressure fluid from the energy source to the mixing line. The pressure intake valve is disposed on the high-pressure bypass line and is designed to regulate pressure of high-pressure fluid. 
     In another embodiment of the present arrangements, the cooling load controller includes: (i) a recirculating line for conveying the high-pressure fluid from one or more of the outlets of the pre-mixing mechanism to the condensate line; and (ii) a valve to allow or prevent flow of high-pressure fluid from the one or more of the outlets of the actuating chamber of the pre-mixing mechanism to the condensate line. 
     In another embodiment of the present arrangements, the cooling load controller includes including: (i) a condenser for condensing intermediate pressure fluid to produce intermediate pressure condensate fluid; (ii) an expansion valve coupled, at one end, to the condenser and designed to reduce pressure of intermediate pressure fluid and produce the low-pressure fluid; and (iii) an evaporator coupled to the other end of the expansion valve and designed to increase temperature of low-pressure fluid and produce low-pressure fluid. 
     In another aspect, the present teachings also provide a process of continuous mixing. One such exemplar process includes: (i) receiving, at an actuating chamber, a high-pressure gas and/or a vapor resulting from heating. In a preferred embodiment of the present teachings, step (i) includes a sub-step (a) of performing a first cycle that includes receiving the high-pressure gas and/or vapor at a first actuating chamber inlet; and sub-step (b) carrying out a second cycle that includes receiving the high-pressure gas and/or the vapor at a second actuating chamber inlet. The second cycle is implemented after the performing the first cycle. 
     Another step (ii) includes receiving, at a complementary chamber, the low-pressure gas and/or the vapor resulting from evaporation. In a preferred embodiment of the present teachings, step (ii) includes a sub-step (a) receiving the low-pressure gas and/or vapor, during the first cycle, at a first complementary chamber inlet; and a sub-step (b) of receiving the low-pressure gas and/or the vapor, during the second cycle, at a second complementary chamber inlet. The second cycle is implemented after carrying out the receiving during the first cycle. 
     Next, a step (iii) includes forcing an actuating piston, using high-pressure gas and/or vapor, disposed inside the actuating chamber to be displaced inside the actuating chamber and thereby evacuating the high-pressure gas and/or the vapor present inside the actuating chamber to produce an actuating chamber exhaust gas and/or vapor. In a preferred embodiment of the present teachings, step (iii) includes a sub-step of (a) removing, during the first cycle and using a second actuating chamber outlet, the actuating chamber exhaust gas and/or vapor from the actuating chamber; and a sub-step (b) of removing, during the second cycle and using a first actuating chamber outlet, actuating chamber exhaust gas and/or vapor from the actuating chamber. 
     Another step (iv) includes forcing a complementary piston, that is coupled to the actuating piston and that is disposed inside the complementary chamber, to be displaced inside the complementary chamber and thereby evacuating the low-pressure gas and/or the present inside the complementary chamber to produce a complementary chamber exhaust gas and/or vapor. In a preferred embodiment of the present teachings, step (iv) includes a sub-step (a) of removing, during the first cycle and using a second complementary chamber outlet, complementary chamber exhaust fluid and/or gas from the complementary chamber; and a sub-step (b) removing, during the second cycle and using a first complementary chamber outlet, complementary chamber exhaust fluid and/or gas from the complementary chamber. 
     After step (iv), a step (v) includes mixing, in a mixing line, the actuating chamber exhaust gas and/or vapor with the complementary chamber exhaust gas and/or vapor to produce the intermediate pressure gas and/or vapor. In one embodiment of the present teachings, mixing includes a sub-step (a) of mixing, during the first cycle, the actuating chamber exhaust gas and/or vapor exiting from the second actuating chamber outlet and complementary chamber exhaust fluid and/or gas from the second complementary chamber outlet to form a first intermediate pressure fluid gas and/or vapor; and sub-step (b) mixing, during the second cycle, the actuating chamber exhaust gas and/or vapor exiting from the first actuating chamber outlet and the complementary chamber exhaust fluid and/or gas exiting from the first complementary chamber outlet to form a second intermediate pressure gas and/or vapor. 
     In another aspect, the present teachings also provide a process for controlling cooling load. One such exemplar process includes step (i) of energizing, using an energy source, a refrigerant condensate in an intermediate state to produce a refrigerant in first state (e.g., a high-pressure gas). A step (ii) includes introducing the refrigerant in the first state into a pre-mixing mechanism, which contains a refrigerant in a second state that is circling in a refrigeration cycle. 
     After step (ii), a step (iii) includes evacuating in a first cycle, using the pre-mixing mechanism, low-pressure pressure fluid using a force applied by the high-pressure fluid to produce an exhaust refrigerant in the first state and the exhaust refrigerant in the second state. The pre-mixing mechanism is coupled, on an input side of the pre-mixing mechanism, to the energy source and coupled, on an output side, to two or more outlets, at least one of which is designed to dispense exhaust refrigerant in the first state and at least another of which is designed to dispense exhaust refrigerant in the second state. In a preferred embodiment of the present teachings, the pressure of each of the exhaust refrigerant in the first state and the exhaust refrigerant in the second state equalizes such that each of the exhaust refrigerant in the first state and the exhaust refrigerant in the second state are at an intermediate pressure, which is larger than a pressure of the refrigerant of the second state and less than a pressure of the refrigerant of the first state. 
     Next, a step (iv) includes mixing, using a mixing line, the exhaust refrigerant in the first state and the exhaust refrigerant in the second state to produce an intermediate pressure fluid, and wherein the mixing line is coupled, at a receiving end, to the outlets of the pre-mixing mechanism and is configured to be coupled, at a dispensing end, to condenser for treating the exhaust refrigerant in the intermediate state to produce the refrigerant condensate in the intermediate state. In one embodiment of the present teachings, the exhaust refrigerant in the intermediate state is at an intermediate temperature value between a temperature of the exhaust refrigerant in the first state and a temperature of the exhaust refrigerant in the second state. 
     A step (v) includes conveying, using a condensate line, a portion of the intermediate pressure condensate fluid from condenser to the energy source. 
     In one embodiment of the present teachings, the pre-mixing mechanism includes a actuating chamber and a complementary chamber. The introducing step (ii) includes introducing the refrigerant in the first state into the actuating chamber and the complementary chamber contains the refrigerant in a second state that is circling in a refrigeration cycle. The evacuating step (iii) includes evacuating, in the first cycle, the refrigerant in the second state from the complementary chamber, using a force applied by the refrigerant in the first state in the actuating chamber, to produce an exhaust refrigerant in the first state and the exhaust refrigerant in the second state. 
     The input side of the pre-mixing mechanism may include four or more inlets, at least two of which may be coupled to the energy source. A first of the inlets may be disposed at or near a first end of the actuating chamber and a second of the inlets may be disposed at or near a second end of the actuating chamber, which is opposite to the first end of the actuating chamber. 
     At least two of the inlets on the input side of the pre-mixing mechanism may be coupled to an evaporator of a refrigeration cycle, and a third of the inlets may be disposed at or near a first end of the complementary chamber and a fourth of the inlets may be disposed at or near a second end of the complementary chamber, which is opposite to the first end of the complementary chamber. In this configuration, step (iii) further includes evacuating, in a second cycle, refrigerant in the second state from the complementary chamber, using a force applied by the refrigerant in the first state in the actuating chamber, to produce an exhaust refrigerant in the first state and the exhaust refrigerant in the second state. The refrigerant in the second state enters the complementary chamber through the fourth inlet and the refrigerant in the first state entered the actuating chamber through the second inlet. 
     The systems and processes of operation of the present teachings and arrangements, however, together with additional objects and advantages thereof, will be best understood from the following descriptions of specific embodiments when read in connection with the accompanying figures. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a side-sectional view of a pre-mixing mechanism, according to one embodiment of the present arrangements and that includes an actuating chamber having disposed therein an actuating piston and a complementary chamber having disposed therein a complementary piston, and a coupling shaft that couples the actuating piston and the complementary piston such that displacement of one of the pistons causes displacement of the other. 
         FIG. 2A  shows fluid flow accessing at a first end of actuating chamber to drive the actuating piston, shown in pre-mixing mechanism of  FIG. 1 , from the first end to a second end of the actuating chamber. 
         FIG. 2B  shows fluid flow accessing at the second end of actuating chamber to drive the actuating piston, shown in pre-mixing mechanism of  FIG. 1 , back from the second end to the first end of the actuating chamber. 
         FIG. 3  shows a novel cooling load controller, according to one embodiment of the present arrangements and that is coupled to the refrigeration system, and includes an energy source, a premixing mechanism as shown in  FIGS. 1 and 2A-2B , a mixing line, a condensate line and an injection pump. 
         FIG. 4  shows a Pressure-Enthalpy diagram, according to one embodiment of the present arrangements, of the cooling load controller of  FIG. 3 . 
         FIG. 5  shows the novel cooling load controller of  FIG. 3  and that further includes a pneumatic pump disposed, according to one embodiment of the present arrangements, between the energy source and a condenser which is part of the refrigeration system. 
         FIG. 6  shows the novel cooling load controller of  FIG. 5 , except a transfer pump, according to one embodiment of the present arrangements and used instead of the pneumatic pump and the injection pump, is disposed between the energy source and the condenser of the refrigeration system. 
         FIG. 7  shows the novel cooling load controller of  FIG. 5 , except the pneumatic pump is coupled, according to one embodiment of the present arrangements, to an electrical generator. 
         FIG. 8  shows the novel cooling load controller of  FIG. 3 , and further includes a pressure bypass line between the energy source and the condenser of the refrigeration system. 
         FIG. 9  shows a process flow chart for continuous mixing, according to one embodiment of the present teachings, of a refrigerant using the pre-mixing mechanism shown in  FIG. 1 . 
         FIG. 10  shows a process flow chart for effectively controlling cooling loads, according to one embodiment of the present teachings, of refrigeration system using the pre-mixing mechanism shown in  FIG. 1 . 
     
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present teaching and arrangements. It will be apparent, however, to one skilled in the art that the present teaching and arrangements may be practiced without limitation to some or all of these specific details. In other instances, well-known process steps have not been described in detail in order to not unnecessarily obscure the present teachings and arrangements. 
     The present arrangements relate to novel systems and methods of creating a more efficient refrigeration system (e.g., refrigeration cycle for an air conditioner). Conventional refrigeration systems use external energy to power a compressor, which uses a substantial amount of energy to compress a refrigerant (herein after also referred to as a “fluid,” which may be a liquid, vapor, and/or gas). A typical compressor, by way of example, may use between about 0.3 kilowatts (“kw”) and about 0.84 kw per refrigerant ton. The term “refrigerant ton” is unit of power and refers to the cooling capacity or heat absorption rate of an air conditioning system to convert one ton of water into ice at the same temperature in 24 hours. The present arrangements, however, do not require external power to induce cooling of the same amount and thereby offer significant energy and monetary savings for operating a refrigeration system. 
     The present arrangements substitute the compressor with a novel pre-mixing mechanism that receives low pressure gas from a refrigeration cycle and high-pressure gas from a cooling load controller (e.g., cooling load controller  360  of  FIG. 3 ). The high-pressure gas from the cooling load controller has a higher pressure than the low-pressure fluid from the refrigeration cycle. An energy source, preferably a renewable one, energizes the cooling load controller to generate the high-pressure gas. Both gases are exhausted from the pre-mixing mechanism and are mixed to create an intermediate pressure gas, which has a higher pressure than the gas from the refrigeration cycle and has a lower pressure than the high-pressure gas resulting from being energized from the energy source. A portion of the intermediate pressure gas may be introduced back into the cooling load controller. Another portion of intermediate pressure gas may also be introduced back into the refrigeration cycle as a pressurized gas. In other words, the pre-mixing mechanism may allow for refrigerant pressurization in a refrigeration cycle without the typical high energy requirements of a compressor. In a preferred embodiment, the pre-mixing mechanism receives high-pressure gas and low-pressure gas and exhausts a intermediate pressure gas. The present teachings recognize, however, that pre-mixing mechanism may be used with fluids of a different state (e.g., a liquid) and/or a mixture of different states (e.g., a mixture of fluid and gas). The pre-mixing mechanism functions in a substantially similar manger, regardless of the state of the fluid. 
       FIG. 1  shows a pre-mixing mechanism  100 , according to one embodiment of the present arrangements and that includes a complementary chamber  102  and an actuating chamber  104 . A complementary piston  112  is disposed within complementary chamber  102  and an actuating piston  126  is disposed within actuating chamber  104 . Complementary piston  112  and actuating piston  126  are coupled together by a coupling shaft  113  such that any movement by one piston realizes a corresponding movement by the other piston in the same direction. As will be explained in greater detail below, movement of each piston within its respective chamber allows for receiving fluid and dispensing or exhausting fluid. 
     Each of a complementary chamber input line  106  and a complementary chamber output line  114  provide fluidic communication with complementary chamber  102 . Complementary chamber  102  includes a first complementary chamber inlet  108  and a second complementary chamber inlet  110 , each of which couple complementary chamber input line  106  to complementary chamber  102 . A low-pressure fluid, resulting from an evaporator (e.g., evaporator  352  of  FIG. 3 ) that is part of a refrigeration cycle and that is received by complementary chamber input line  106 , is conveyed, using first complementary chamber inlet  108  and/or second complementary chamber inlet  110 , to complementary chamber  102 . 
     First complementary chamber inlet  108  is coupled to a first complementary chamber inlet valve  152  and second complementary chamber inlet  110  is coupled to a second complementary chamber inlet valve  154 . First complementary chamber inlet valve  152  and second complementary chamber inlet valve  154  control fluid flow from complementary chamber input line  106  into complementary chamber  102 . In the case of low-pressure fluid resulting from an evaporator (e.g., evaporator  352  of  FIG. 3 ), first complementary chamber inlet valve  152  and second complementary chamber inlet valve  154  control fluid flow from entering into complementary chamber  102 . 
     Complementary chamber  102  includes a first complementary chamber outlet  116  and second complementary chamber outlet  118 , each of which couple complementary chamber  102  to complementary chamber output line  114 . First complementary chamber outlet  116  and second complementary chamber outlet  118  exhaust the intermediate pressure fluid (hereinafter the “complementary chamber exhaust fluid”), present inside complementary chamber  102 , to complementary chamber output line  114 . Complementary chamber output line  114  exhausts the complementary chamber exhaust fluid to mixing line  134 . 
     First complementary chamber outlet  116  is coupled to a first complementary chamber outlet valve  156  and second complementary chamber outlet  118  is coupled to a second complementary chamber outlet valve  158 . First complementary chamber outlet valve  156  and second complementary chamber outlet valve  158  control complementary chamber exhaust fluid flow from complementary chamber  102  to complementary chamber output line  114 . 
     As shown in  FIG. 1 , each of actuating chamber input line  120  and an actuating chamber output line  128  provide fluidic communication with actuating chamber  104 . Actuating chamber  104  includes a first actuating chamber inlet  122  and a second actuating chamber inlet  124 , each of which couple actuating chamber input line  120  to actuating chamber  104 . A high-pressure fluid, resulting from energizing the fluid at an energy source (e.g., energy source  362  of  FIG. 3 ) that is part of the cooling load controller and that is received by actuating chamber input line  120 , is conveyed, using first actuating chamber inlet  122  and second actuating chamber inlet  124 , to actuating chamber  104 . 
     First actuating chamber inlet  122  is coupled to a first actuating chamber inlet valve  144  and second actuating chamber inlet  124  is coupled to a second actuating chamber inlet valve  146 . First actuating chamber inlet valve  144  and second actuating chamber inlet valve  146  control fluid flow from actuating chamber input line  120  into actuating chamber  104 . In the case of high-pressure fluid resulting from an evaporator energy source, first actuating chamber inlet valve  144  and second actuating chamber inlet valve  146  control fluid flow from entering into actuating chamber  104 . 
     Actuating chamber  104  includes a first actuating chamber outlet  130  and a second actuating chamber outlet  132 , each of which couple actuating chamber  104  to actuating chamber output line  128 . First actuating chamber output  130  and a second actuating chamber output  132  exhaust intermediate pressure (hereinafter the “actuating chamber exhaust fluid”), present inside actuating chamber  104 , to actuating chamber output line  128 . Actuating chamber output line  128  exhausts the actuating chamber exhaust fluid to mixing line  134 . 
     First actuating chamber outlet  130  is coupled to a first actuating chamber outlet valve  148  and second actuating chamber outlet  132  is coupled to a second actuating chamber outlet valve  150 . First actuating chamber outlet valve  148  and second actuating chamber outlet valve  150  control actuating chamber exhaust fluid flow from actuating chamber  104  to actuating chamber outlet line  128 . 
     In a one embodiment of the present arrangements, first complementary chamber inlet  108  and first complementary chamber outlet  116  are disposed on opposing or different ends of complementary chamber  102  than second complementary chamber inlet  110  and second actuating chamber outlet  118 . In other words, first complementary chamber inlet  108  and first complementary chamber outlet  116  are disposed proximate to first complementary chamber end  140 . Second complementary chamber inlet  110  and second actuating chamber outlet  118  are disposed proximate to second complementary chamber end  142 . 
     Similarly, first actuating chamber inlet  122  and second actuating chamber inlet  124  are disposed on opposing or different ends of actuating chamber  104 . Similarly, first actuating chamber outlet  130  and second actuating chamber outlet  132  disposed on opposing or different ends of actuating chamber  104 . By way of example, first actuating chamber inlet  122  and first actuating chamber outlet  130  are disposed proximate to first complementary chamber end  136 . Second actuating chamber inlet  146  and second actuating chamber outlet  140  are disposed proximate to second actuating chamber end  138 . 
       FIGS. 2A and 2B  show the two cycles of pre-mixing mechanism  200 . In a first cycle, pre-mixing mechanism  200  is configured to allow actuating piston  126  and complementary piston  112  to move, within actuating chamber  104  and complementary chamber, respectively, away from a first end, and towards a second end. In a second cycle, pre-mixing mechanism  200  is configured to move actuating piston  126  and complementary piston  112  away from the second end, and towards the first end. Piston movement during each cycle, facilitates, at actuating chamber  104 , receipt of high-pressure fluid and exhaustion of actuating chamber exhaust fluid and facilitates, and at complementary chamber  102 , receipt low-pressure fluid and exhaustion of complementary chamber exhaust fluid. 
       FIG. 2A  shows a first cycle, according to one embodiment of the present arrangements, of pre-mixing mechanism  200  that facilitates actuating piston  126  to moves away from first actuating chamber end  136 , and towards second actuating chamber end  138 . 
     In the first cycle, first actuating chamber inlet valve  144  is open to provide a fluidic flow path from actuating chamber input line  120  to first actuating chamber inlet  122 . First actuating chamber outlet valve  148  is closed to prevent removal of high-pressure fluid through first actuating chamber outlet  130 . In this configuration, high-pressure fluid, received from actuating chamber input line  120 , accumulates in a portion of actuating chamber  104  defined between first actuating chamber end  136  and actuating piston  126 . 
     Second actuating chamber inlet valve  146  is closed, which prevents high-pressure fluid from entering actuating chamber  104  through second actuating chamber inlet  124 . Second actuating chamber outlet valve  150  is open, which provides an exhaust fluid flow path from actuating chamber  104  to actuating chamber output line  128 . 
     During the first cycle of pre-mixing mechanism  200 , the portion of actuating chamber  104 , defined between first actuating chamber end  136  and actuating piston  126 , receives high-pressure fluid. Additionally, high-pressure fluid within actuating chamber  104 , between actuating piston  126  and second actuating chamber end  138 , transitions an intermediate pressure fluid. The high-pressure fluid exerts a force against actuating piston  126  and intermediate pressure fluid exerts a force on opposing side actuating piston  126 . The force from the high-pressure fluid, which is greater than the force from the intermediate pressure fluid, causes actuating piston  126  to move away from first actuating chamber end  136  and towards second actuating chamber end  138 . As actuating piston  126  moves towards second actuating chamber end  138 , intermediate pressure fluid within actuating chamber  104 , between actuating piston  126  and second actuating chamber end  138 , is exhausted through second actuating chamber outlet valve  150 . 
     As discussed above, complementary piston  112 , which is coupled to actuating piston  126 , moves away from first complementary chamber end  140 , and towards second complementary chamber end  142 . To facilitates movement of complementary piston  112  towards a second complementary chamber end  142 , first complementary chamber inlet valve  152  is open and first complementary outlet valve  156  is closed. First complementary chamber inlet  108  may receive low-pressure fluid from complementary chamber input line  106 . This low-pressure fluid is held within complementary chamber  102 , between first complementary chamber end  140  and complementary piston  112 . 
     Moreover, second complementary chamber inlet valve  154  is closed and second complementary chamber outlet valve  158  is open. In this configuration, complementary chamber exhaust fluid in complementary chamber  102 , between complementary piston  112  and second complementary chamber end  142 , may egress to complementary chamber output line  114 . The exhausted fluids from actuating chamber  104  and complementary chamber  102  are mixed together in mixing line  134 . 
       FIG. 2B  shows a second cycle of pre-mixing mechanism  200 , according one embodiment of the present arrangements, in which actuating piston  126  moves away from second actuating chamber end  138  and towards first actuating chamber end  136 . Complementary piston  112 , which is coupled to actuating piston  126 , moves away from second complementary chamber end  142 , and towards first complementary chamber end  140 . 
     During the second cycle, second actuating chamber inlet valve  146  is open and second actuating chamber outlet valve  150  is closed. High-pressure fluid, conveyed to actuating chamber  104  from second actuating chamber inlet  124 , pushes actuating piston  126  towards first actuating chamber end  136  and away from second actuating chamber end  138 . First actuating chamber inlet valve  144  is closed and first actuating chamber outlet valve  148  is open. High-pressure fluid in actuating chamber  104  from the first cycle, held between actuating piston  126  and first actuating chamber end  136 , is exhausted to actuating chamber outlet line  128 , via first actuating chamber outlet  130 . 
     In regard to complementary chamber  102 , second complementary chamber inlet valve  154  is open and second complementary chamber outlet valve  158  is closed. First complementary chamber inlet valve  152  is closed and first complementary chamber outlet valve  156  is open. 
     Movement of actuating piston  126  causes a corresponding movement of complementary piston  112  towards first complementary chamber end  140 . A portion of complementary chamber  102 , between second complementary chamber end  142  and complementary piston  112 , receives low-pressure fluid from complementary chamber input line  106 . Movement of complementary piston  112  also exhausts complementary chamber exhaust fluid present in complementary chamber  102 , between complementary piston  112  and first complementary chamber end  140 , from complementary chamber  102 . The complementary chamber exhaust fluid is conveyed, through first complementary chamber outlet  116 , to complementary chamber output line  114 . The complementary chamber exhaust fluid, from complementary chamber output line  114 , and the actuating chamber exhaust fluid, from actuating chamber output line  128 , are mixed together in mixing line  134  to create an intermediate pressure exhaust. 
     Opening and closing of inlet valves and outlet valves are controlled, in one embodiment of the present arrangements, using a programmable logic controller (“PLC”). Each valve is communicatively coupled to the PCL and receives instructions from when to open and close. By way of example, during the first cycle, first actuating chamber inlet valve  144 , second actuating chamber outlet valve  150 , first complementary camber inlet valve  152 , and second complementary chamber outlet valve  158  are instructed to remain open. In addition, the PLC instructs second actuating chamber inlet valve  146 , first actuating chamber outlet valve  148 , second complementary camber inlet valve  154 , and first complementary chamber outlet valve  156  to remain open. During a second cycle, the PLC instructs the valves that were open during the first cycle to close and instructs the valves that were closed to open. This process of opening and closing continues with each successive cycle. 
       FIGS. 1, 2A, and 2B  show a pre-mixing mechanism  100 , according to one embodiment of the present arrangements and including actuating chamber  104  having an internal volume that is substantially the same as that of complementary chamber  102 . This ensures that an equal volume of, both, complementary chamber exhaust fluid and the actuating chamber exhaust fluid are discharged from pre-mixing mechanism  100 . The present teachings, however, are not so limited. Rather, the internal volume of complementary chamber  102  may be different than the internal volume of actuating chamber  104 . In one embodiment of the present arrangements, the internal volume of complementary chamber  102  is twice as large as the internal volume of actuating chamber  104 . In another embodiment of the present arrangements, the internal volume of actuating chamber  102  is four times as large as the internal volume of actuating chamber  104 . 
     Tables 1-6 shows fluid characteristics of high-pressure fluid and low-pressure fluid within a computer simulated cooling load controller  360  in which the complementary chamber receives a low-pressure fluid that is about 60 degrees Fahrenheit (and about 57 pounds per square inch gauge (“psig”)) and the actuating chamber receives a high-pressure fluid that is about 110 degrees Fahrenheit (or about 145 psig) and has a volumetric flow rate of about 5 feet 3  per minutes. Table 1 shows values for heat absorption and volumetric flow rate for a situation when the internal volume of the complementary chamber is same as the internal volume of the actuating chamber (i.e., a 1:1 ratio) and for another situation when the internal volume of the complementary chamber is twice the volume as the internal volume of the actuating chamber (i.e., a 1:2 ratio). In the 1:2 ratio scenario, pre-mixing mechanism  300  exhausts twice the volume of complementary chamber exhaust fluid than the exhausted volume of actuating chamber exhaust fluid. 
     
       
         
           
               
               
               
             
               
                 TABLE 1 
               
             
            
               
                   
               
               
                   
                 Heat Absorption Rate 
                 Volumetric Flow Rate 
               
               
                 Cooling Load Controller 
                 (BTU/h) 
                 (Feet 3  per Minute) 
               
               
                 Refrigerant: R-134a 
                 (Approximate) 
                 (Approximate) 
               
            
           
           
               
               
               
               
               
            
               
                 Pre-mixing Mechanism 
                 1:1 Ratio 
                 1:2 Ratio 
                 1:1 Ratio 
                 1:2 Ratio 
               
               
                   
               
            
           
           
               
               
               
               
               
            
               
                 Complementary Chamber 
                 50,500 
                 100,999 
                 5 
                 10 
               
               
                 (60° F. Saturated gas 
               
               
                 (57 psig)) 
               
               
                 Actuating Chamber 
                 121,103 
                 121,103 
                 5 
                 5 
               
               
                 (110° F. Saturated gas 
               
               
                 (145 psig)) 
                   
               
               
                 Total 
                 176,603 
                 222,102 
                 10 
                 15 
               
               
                   
               
            
           
         
       
     
     As shown in Table 1, increasing the internal volume of complementary chamber  102 , relative to actuating chamber  102 , increases the volumetric fluid flow rate of the fluid flowing through a refrigeration system (e.g., refrigeration system  350  of  FIG. 3 ) from 5 feet 3  per minute to 10 feet 3  per minute. An increase in the volumetric fluid flow rate of the complementary chamber fluid results in an increase in heat absorption rate by the refrigeration system from about 176,603 British thermal units per hour (“btu/h”) to about 222,102 btu/h. In other words, an evaporator (e.g., evaporator  352  of  FIG. 3 ) of the refrigeration system is capable of absorbing more heat over a given time period when the refrigerant is cycling at a higher volumetric flow rate. 
     The pre-mixing mechanism shown in Table 1 may be used in a cooling load controller (e.g., cooling load controller  360  of  FIG. 3 ), to control a refrigeration system (e.g., refrigeration system  350  of  FIG. 3 ). As shown in Table 2, the incoming heat absorption rate of a combined system of the cooling load controller and a refrigeration system is substantially similar to the outgoing heat absorption rate. In other words, the heat absorbed by the fluid, from the renewable energy source and the evaporator, is substantially the same as the heat dispensed by the fluid in the condenser. Moreover, Table 2 shows that using a cooling load controller having a 1:1 ratio in pre-mixing mechanism provides a heat recovery of about 40%. Heat recovery percentage, which is a ratio of a value of an evaporator&#39;s heat absorption rate to a value of an energy source&#39;s heat absorption rate, refers to a percentage of heat, or energy, that may be absorbed by the fluid in refrigeration system to cool an area surrounding the evaporator. A cooling load controller having a 1:2 ratio in pre-mixing mechanism provides a heat recovery of about 81%. A 1:2 ratio provides significant heat recovery within a refrigeration system. As will be discussed in greater detail below, a 1:2 ratio pre-mixing mechanism, results in a higher fluid flow rate through the evaporator of the refrigeration system. The higher fluid flow rate allows the fluid to absorb more than about twice the heat than a 1:1 ratio pre-mixing mechanism. 
     
       
         
           
               
               
               
             
               
                 TABLE 2 
               
             
            
               
                   
               
               
                   
                 Heat Absorption 
                 Heat Absorption 
               
               
                 Cooling load controller 
                 Rate In 
                 Rate Out 
               
               
                 coupled to 
                 (btu/h) (Approximate) 
                 (btu/h) (Approximate) 
               
            
           
           
               
               
               
               
               
            
               
                 refrigeration cycle 
                 1:1 Ratio 
                 1:2 Ratio 
                 1:1 Ratio 
                 1:2 Ratio 
               
               
                   
               
            
           
           
               
               
               
               
               
            
               
                 Energy Source 
                 78,647 
                 78,647 
                   
                   
               
               
                 Condenser 
                   
                   
                 110,493 
                 142,337 
               
               
                 Evaporator 
                 31,845 
                 63,690 
               
               
                 Heat Recovery 
                 40% 
                 81% 
               
               
                   
               
            
           
         
       
     
       FIG. 3  shows a cooling load controller  360 , according to one embodiment of the present arrangements and that includes a pre-mixing mechanism  300  and a mixing line  334  for controlling the cooling load of a refrigeration system  350 . Pre-mixing mechanism  300  and mixing line  334  are substantially similar to pre-mixing mechanism  100  of  FIG. 1 . In addition to pre-mixing mechanism  300 , cooling load controller  360  includes an energy source  362 , a mixing line  334 , a condensate line  364 , and an injection pump  370 . Refrigeration system  350 , in one embodiment of the present arrangements includes a condenser  354 , an expansion valve  356 , and an evaporator  352 . 
     Pre-mixing mechanism  300  receives a high-pressure fluid from energy source  362  and low-pressure fluid from evaporator  352 . More particularly, energy source  362  energizes a fluid to create the high-pressure fluid. The high-pressure fluid is transferred to an actuating chamber (e.g., actuating chamber  104  of  FIG. 1 ) of pre-mixing mechanism  300 . Evaporator  352  dispenses low-pressure fluid to a complementary chamber (e.g., complementary chamber  102  of  FIG. 1 ) of pre-mixing mechanism  300 . The high-pressure fluid, and the low-pressure fluid, may have other fluid characteristics in addition to fluid pressure. By way of example, each of the high-pressure fluid, and the low-pressure fluid have associated therewith at least one fluid characteristic value chosen from a group comprising temperature value, volumetric flow rate value, mass flow rate value, and/or heat absorption rate value (e.g., btu/h). 
     Table 3 provides exemplar characteristic values, according to one embodiment of the present arrangements, used in a cooling load controller simulation of a high-pressure fluid that is conveyed from energy source  362  to the actuating chamber of pre-mixing mechanism  300 . 
     
       
         
           
               
             
               
                 TABLE 3  
               
             
            
               
                   
               
               
                 High-pressure Gas Characteristic Values Entering Pre-Mixing Mechanism 300 
               
            
           
           
               
               
               
            
               
                   
                 Refrigerant R-410a 
                 Refrigerant R-134a 
               
            
           
           
               
               
               
               
               
               
            
               
                   
                 Chamber 
                 General Range 
                 Preferred Range 
                 General Range 
                 Preferred Range 
               
               
                   
                 Ratio 
                 (Approximate) 
                 (Approximate) 
                 (Approximate) 
                 (Approximate) 
               
               
                   
                   
               
            
           
           
               
               
               
               
               
               
            
               
                 Temperature 
                 1:1 
                 100-160  
                 120-140 
                 100-160 
                 120-140 
               
               
                 (Fahrenheit) 
               
               
                   
                 1:2 
               
               
                 Pressure 
                 1:1 
                 123-300  
                 170-228 
                 320-694 
                 422-546 
               
               
                 (psig) 
               
               
                   
                 1:2 
               
               
                 Heat 
                 1:1 
                 72,000-264,000 
                 142,000-200,000 
                 220,000-525,000 
                 300,000-435,000 
               
               
                 Absorption 
               
               
                 Rate (btu/h) 
               
               
                   
                 1:2 
               
               
                 Volumetric 
                 1:1 
                 1-10 
                 4-6 
                  1-10 
                 4-6 
               
               
                 Flow Rate 
               
               
                 (Feet 3  per 
               
               
                 minute 
               
               
                 (“ft 3 /min”)) 
               
               
                   
                 1:2 
               
               
                   
               
            
           
         
       
     
     Table 4 provides characteristic values, according to one embodiment of the present arrangements, used in a cooling load controller simulation of a low-pressure fluid that is conveyed from evaporator  352  to the complementary chamber of pre-mixing mechanism  300 . 
     
       
         
           
               
             
               
                 TABLE 4 
               
             
            
               
                   
               
               
                 Low-pressure Gas Characteristic Values Entering Pre-Mixing Mechanism 300 
               
            
           
           
               
               
               
            
               
                   
                 Refrigerant R-134a 
                 Refrigerant R-410a 
               
            
           
           
               
               
               
               
               
               
            
               
                   
                 Chamber 
                 General Range 
                 Preferred Range 
                 General Range 
                 Preferred Range 
               
               
                   
                 Ratio 
                 (Approximate) 
                 (Approximate) 
                 (Approximate) 
                 (Approximate) 
               
               
                   
                   
               
            
           
           
               
               
               
               
               
               
            
               
                 Temperature 
                 1:1 
                 10-70  
                 40-60 
                 10-70  
                 40-60 
               
               
                 (Fahrenheit) 
                 1:2 
               
               
                 Pressure 
                 1:1 
                 10-70  
                 35-50 
                 60-200 
                 115-170 
               
               
                 (psig) 
                 1:2 
               
               
                 Heat Absorption 
                 1:1 
                 18,000-65,000  
                 30,000-45,000 
                 45,000-135,000 
                 80,000-115,00 
               
               
                 Rate (btu/h) 
                 1:2 
                 32,000-130,000 
                 60,000-90,000 
                 90,000-270,000 
                 160,000-230,000 
               
               
                 Volumetric Flow 
                 1:1 
                 1-10 
                 4-6 
                 1-10 
                 4-6 
               
               
                 Rate (ft 3 /min) 
                 1:2 
                 2-20 
                  8-12 
                 2-20 
                  8-12 
               
               
                   
               
            
           
         
       
     
     Mixing line  334 , at a receiving end of pre-mixing mechanism  300 , receives and mixes the actuating chamber exhaust fluid and the complementary chamber exhaust fluid to form an intermediate pressure fluid. While the complementary chamber exhaust fluid and an actuating chamber exhaust fluid are at the same pressure, the present arrangements recognize that this pressure is not the only characteristic associated with each exhaust fluid. Table 5 provides characteristic values, according to one embodiment of the present arrangements, used in a cooling load controller simulation of an intermediate pressure fluid that is conveyed from pre-mixing mechanism  300  to condenser  354 . 
     
       
         
           
               
             
               
                 TABLE 5 
               
             
            
               
                   
               
               
                 Intermediate Pressure Gas Characteristic Values Entering Condenser 354 
               
            
           
           
               
               
               
            
               
                   
                 Refrigerant R-134a 
                 Refrigerant R-410a 
               
            
           
           
               
               
               
               
               
               
            
               
                   
                 Chamber 
                 General Range 
                 Preferred Range 
                 General Range 
                 Preferred Range 
               
               
                   
                 Ratio 
                 (Approximate) 
                 (Approximate) 
                 (Approximate) 
                 (Approximate) 
               
               
                   
                   
               
            
           
           
               
               
               
               
               
               
            
               
                 Temperature 
                 1:1 
                 85-140 
                 105-125 
                  80-140 
                 105-125 
               
               
                 (Fahrenheit) 
               
               
                   
                 1:2 
                 75-130 
                 105-125 
                  80-140 
                 105-125 
               
               
                 Pressure 
                 1:1 
                 65-185 
                 100-140 
                 190-450 
                 270-360 
               
               
                 (psig) 
                 1:2 
                 50-145 
                 100-140 
                 190-450 
                 270-360 
               
               
                 Heat 
                 1:1 
                 90,000-330,000 
                 170,000-245,000 
                 265,000-670,000 
                 380,000-550,000 
               
               
                 Absorption 
               
               
                 Rate (btu/h) 
               
               
                   
                 1:2 
                 110,000-395,000  
                 200,000-290,000 
                 310,000-805,000 
                 460,000-665,000 
               
               
                 Volumetric 
                 1:1 
                 2-20 
                  8-12 
                  2-20 
                  8-12 
               
               
                 Flow Rate 
               
               
                 (ft 3 /min) 
               
               
                   
                 1:2 
                 3-30 
                 12-18 
                  3-30 
                 12-18 
               
               
                   
               
            
           
         
       
     
     Mixing line  334 , at a dispensing end, is coupled to condenser  354 , which removes heat from the intermediate pressure fluid (hereinafter also referred to as a “intermediate pressure condensate fluid”). The intermediate pressure condensate fluid may be conveyed to energy source  362  and/or expansion valve  356 . Intermediate pressure condensate fluid transferred to expansion valve  356  cycles through refrigeration system  350  and is converted to a low-pressure fluid as it exits from evaporator  352 . Intermediate pressure condensate fluid is conveyed, through condensate line  364 , via injection pump  370 , to energy source  362 . Table 6 provides characteristic values, according to one embodiment of the present arrangements, used in a cooling load controller simulation of an intermediate pressure condensate fluid that is conveyed, from condenser, to evaporator  352  and/or injection pump  370 . 
     
       
         
           
               
             
               
                 TABLE 6 
               
             
            
               
                   
               
               
                 Intermediate Pressure Condensate Fluid Characteristic Values Exiting Condenser 354 
               
            
           
           
               
               
               
            
               
                   
                 Refrigerant R-134a 
                 Refrigerant R-410a 
               
            
           
           
               
               
               
               
               
               
            
               
                   
                 Chamber 
                 General Range 
                 Preferred Range 
                 General Range 
                 Preferred Range 
               
               
                   
                 Ratio 
                 (Approximate) 
                 (Approximate) 
                 (Approximate) 
                 (Approximate) 
               
               
                   
                   
               
            
           
           
               
               
               
               
               
               
            
               
                 Temperature 
                 1:1 
                 60-140 
                 80-105 
                 60-125 
                  85-110 
               
               
                 (Fahrenheit) 
               
               
                   
                 1:2 
                 55-130 
                 75-105 
                 50-110 
                 220-300 
               
               
                 Pressure 
                 1:1 
                 60-175 
                 90-130 
                 180-440  
                 260-350 
               
               
                 (psig) 
               
               
                   
                 1:2 
                 50-140 
                 80-130 
                 150-360  
                 220-300 
               
               
                 Heat 
                 1:1 
                 35,000-150,000 
                 65,000-105,000 
                 85,000-450,000 
                 240,000-300,000 
               
               
                 Absorption 
               
               
                 Rate btu/h) 
               
               
                   
                 1:2 
                 45,000-180,000 
                 75,000-125,000 
                 95,000-510,000 
                 180,000-310,000 
               
               
                 Volumetric 
                 1:1 
                 2-20 
                 8-12 
                 2-20 
                  8-12 
               
               
                 Flow Rate 
               
               
                 (ft 3 /min) 
               
               
                   
                 1:2 
                 3-30 
                 12-18  
                 3-30 
                 12-18 
               
               
                   
               
            
           
         
       
     
     Using injection pump  370 , intermediate pressure condensate fluid is pumped from the condensate line  362  to energy source  362 , which energizes (i.e., heat is added to the intermediate pressure condensate fluid having a fixed volume) to again create a high-pressure fluid. In one embodiment of the present arrangements, injection pump  370  increases the pressure of intermediate pressure condensate fluid to match the pressure of high-pressure fluid within energy source  362 . In another embodiment of the present arrangements, injection pump  370  regulates the amount of fluid entering energy source  362  to ensure there is always fully saturated gas and some remaining liquid entering energy source  362 . 
     Energy source may be any energy source that adds energy to a fluid. By way of example, energy source may be one source chosen from a group comprising solar array, geothermal energy, exhaust heat from data centers, exhaust heat from condensers, waste heat from energy generation, electricity generation using fossil fuels, exhaust from a generator, engine exhaust, and waste heat from industrial processes. In one preferred embodiment of the present arrangements, energy source  362  is a solar array. 
     Cooling load controller  360 , in a preferred embodiment of the present arrangements, also includes a high-pressure intake valve  366  disposed between energy source  362  and pre-mixing mechanism  300 . High-pressure intake valve  366  regulates the pressure of the high-pressure fluid before pre-mixing mechanism  300  receives the high-pressure fluid. Cooling load controller  360 , in another preferred embodiment of the present arrangements, includes a regulator valve  368  disposed between condenser  354  and energy source  362 . Regulator valve  368  regulates the volume of intermediate pressure condensate fluid conveyed to energy source  362 . 
       FIG. 4  shows a Pressure-Enthalpy (“P-E”) diagram, according to one embodiment of the present arrangements, of a refrigeration system  400  that incorporates a cooling load controller  460 , and not a compressor. Refrigeration system  400  and cooling load controller  460  is substantially similar to their counterpart refrigeration system  300  and cooling load controller  300  of  FIG. 3  (i.e., premixing mechanism  400 , evaporator  452 , condenser  454 , expansion valve  456 , energy source  462 , and injection pump  470  are substantially similar to premixing mechanism  300 , evaporator  352 , condenser  354 , expansion valve  356 , energy source  362 , and injection pump  370  of  FIG. 3 ), respectively. 
     In this embodiment, energy source  462  receives and transfers heat to a high-pressure fluid. The temperature and pressure of high-pressure fluid remain relatively unchanged. The evaporator  452  receives and transfers heat to a low-pressure fluid. Similar to energy source  462 , temperature and pressure of the intermediate pressure fluid remain relatively unchanged. The high-pressure fluid from energy source  462  is transferred to actuating chamber  104  of pre-mixing mechanism  400 . The portion of intermediate pressure fluid from evaporator  452  is transferred to complementary chamber  402  of premixing mechanism  400 . 
     As previously explained above in relation to  FIGS. 2A and 2B , the exhaust fluids from pre-mixing mechanism  400  mix to create an intermediate pressure fluid, which has a pressure that is greater than the low-pressure fluid and less than the high-pressure fluid. Specifically, pressure of the fluid, cycling within a refrigeration system, is increased, using the high-pressure fluid from energy source  462 , without a compressor. A condenser extracts heat from intermediate pressure fluid to create an intermediate pressure condensate fluid. In addition, the temperature of intermediate pressure fluid is reduced as heat is lost from intermediate pressure fluid to the surrounding environment. 
     A portion of intermediate pressure condensate fluid is conveyed to injection pump  472 , which increases fluid pressure to create a high-pressure fluid. Another portion of intermediate pressure condensate fluid is conveyed to expansion valve  456 , which reduces fluid pressure to create a low-pressure fluid. The cycle continues again with the high-pressure fluid being conveyed to energy source  462  and low-pressure fluid being conveyed to evaporator  452 . 
       FIG. 5  shows a cooling load controller  560 , according to another embodiment of the present arrangements and that includes a pneumatic pump  572  disposed between and communicatively coupled to energy source  562  and to condenser  554 . Cooling load controller  560  of  FIG. 5  is substantially similar to cooling load controller  360  of  FIG. 3 . In other words, energy source  562 , pre-mixing mechanism  500 , mixing line  534 , condensate line  564 , and injection pump  570  of  FIG. 5  are substantially similar to their counterparts of  FIG. 3 , i.e., energy source  362 , pre-mixing mechanism  300 , mixing line  334 , condensate line  364 , and injection pump  370 . 
     As shown, pneumatic pump  572  is coupled to and powers injection pump  570  during its normal operation. In one embodiment of the present arrangements, fluid flow through pneumatic pump  572  generates electricity, which is used to power injection pump  570 . In another embodiment of the present arrangements, pneumatic pump  572  is mechanically coupled to injection pump  572  using a rotating driveshaft. In this embodiment, fluid flow through pneumatic pump  572  rotates the driveshaft. Injection pump  570 , coupled to the driveshaft, operates to pump a portion of intermediate pressure fluid from condenser  554  to energy source  562 . 
     Cooling load controller  560 , as shown in  FIG. 5 , allows a high-pressure fluid to be conveyed to pre-mixing mechanism  500 , or injection pump  570 , or a combination of both. To that end, cooling load controller  560  is capable of controlling the refrigeration cycle to a high degree of precision by adjusting the fluid flow through pre-mixing mechanism  500  and/or liquid injection pump  570 . 
       FIG. 6  shows a cooling load controller  660 , according to another embodiment of the present arrangements and that includes a transfer pump  674  disposed between and communicatively coupled to energy source  662  and condenser  654 . Cooling load controller  660  is substantially similar to cooling load controller  560  of  FIG. 5  (i.e., each of energy source  662 , pre-mixing mechanism  600 , mixing line  634 , and condensate line  664  of  FIG. 6  are substantially similar to each of energy source  562 , pre-mixing mechanism  500 , mixing line  534 , and condensate line  564  of  FIG. 5 , respectively). In this embodiment, however, transfer pump  674  is used instead of injection pump  570  and pneumatic pump  572  of  FIG. 5 . The structure of transfer pump  674  is substantially similar to that of pre-mixing mechanism  600 . Transfer pump  674  has first piston disposed with a first chamber and a second disposed within second chamber. The first piston and second piston are coupled (e.g., through a shaft) and move in a same direction during a first cycle and a second cycle. Moreover, transfer pump  674  operates in a substantially similar manner as pre-mixing mechanism  600 . Transfer pump  674 , in the first chamber, receives high pressure fluid from energy source  662 , which displaces the first piston from one end of the first chamber to a second end. During this displacement, intermediate pressure fluid exhausts to mixing line  634 . The second chamber of transfer pump  674  receives intermediate pressure condensate fluid from condenser  654  and exhausts high pressure fluid to energy source  662 . 
       FIG. 7  shows a cooling load controller  760 , according to an alternate embodiment of the present arrangements and that is substantially similar to cooling load controller  560  of  FIG. 5 , except for at least one difference that is described below. Cooling load controller  760 , for example, includes an electricity generator  776  coupled to pneumatic pump  772 . Electricity generator  776  may generate either alternating current or direct current, depending on the application it is used in. During an operative state of cooling load controller  760 , high pressure fluid from energy source  762  is pumped through the pneumatic pump  772 . Fluid flow through pneumatic pump  772  drives electricity generator  776  into an operable configuration. When electricity generator  776  is in an operable configuration, it generates an electric current, which may be used to power supplemental devices. By way of example, electricity generator  776  produces DC current that is used to power a condenser fan to facilitate faster removal of heat from fluid flowing through the condenser. Energy supplied by electricity generator  776  may reduce and/or eliminate external energy used to operate cooling load controller  760  components. 
     Using cooling load controller  760 , high pressure fluid may be transmitted to pre-mixing mechanism  700 , or electricity generator  776 , or a combination of both. To that end, cooling load controller  760  is capable of controlling a refrigeration system to a high degree of precision by adjusting the fluid flow through pre-mixing mechanism  700  and/or electricity generator  776 . 
       FIG. 8  shows a cooling load controller  860 , according to yet another embodiment of the present arrangements and that is substantially similar to cooling load controller  360  of  FIG. 3 , except of at least one difference that is described hereinafter. Cooling load controller  860 , for example, includes a pressure bypass line  878 . The configuration shown in  FIG. 8  allows cooling load controller to bypass refrigeration system  850  when refrigeration system  850  is not needed. Pressure bypass line  878  transmits high pressure fluid from energy source  862  to condenser  854 . The fluid condensate is then transmitted back to energy source  862  to complete the cycle. 
     A liquid injection pump (e.g., injection pump  370  of  FIG. 3 ), electricity generator (e.g., electricity generator  776  of  FIG. 6 ) and pressure bypass valve  878  may be installed into cooling load controller, individually or in combination, depending on the requirements of the cooling load controller. To that end, the cooling load controller may be modified, using the above-mentioned components, to adjust the efficiency of the refrigeration cycle. 
     The present teachings also provide processes for continuously mixing a fluid.  FIG. 9  shows a process flow chart  900 , according to one embodiment of the present teachings, for effectively controlling cooling loads of a refrigeration system using a novel pre-mixing mechanism design (e.g., pre-mixing mechanism  100  of  FIG. 1 ). Process  900  begins with a step  902  that involves receiving, at an actuating chamber (e.g., actuating chamber  104  off  FIG. 1 ), a high-pressure fluid resulting from heating a fluid at an energy source. Receiving step  902  may be performed in a first cycle and/or a second cycle. In the first cycle, high-pressure fluid may be received at a first actuating chamber inlet (e.g., first actuating chamber inlet  122  of  FIG. 1 ) and not a second actuating chamber inlet (e.g., second actuating chamber inlet  124  of  FIG. 1 ). More particularly, a first actuating chamber inlet valve (e.g., first actuating chamber inlet valve  144  of  FIG. 1 ) is, preferably, opened to allow receipt of the high-pressure fluid and, at this stage, second actuating chamber inlet valve (e.g., second actuating chamber inlet valve  146  of  FIG. 1 ) is closed. In the second cycle, which may be carried out after the first cycle, the first actuating chamber inlet valve is closed, but the second actuating chamber inlet valve is open. Thus, in the second cycle, the high-pressure fluid is received at the second actuating chamber inlet but not at the first actuating chamber inlet. 
     Next, a step  904  is carried out. This step includes receiving, at a complementary chamber (e.g., complementary chamber  102  off  FIG. 1 ), low-pressure fluid resulting from evaporation at an evaporator (e.g., evaporator  352  of  FIG. 3 ). Step  904  preferably includes a first cycle and a second cycle. In the first cycle, a first complementary chamber inlet valve (e.g., first complementary chamber inlet valve  152  of  FIG. 1 ) is open, but a second complementary chamber inlet valve (e.g., second complementary chamber inlet valve  154  of  FIG. 1 ) is closed. In this configuration, the low-pressure fluid is received at first complementary chamber inlet (e.g., first complementary chamber inlet  108  of  FIG. 1 ) but is prevented from entering the complementary chamber at the second complementary chamber inlet. 
     In the second cycle of step  904 , which is after the first cycle, the second complementary chamber inlet valve is open, but the first complementary chamber inlet valve is closed. In this configuration, the low-pressure fluid is received at second complementary chamber inlet, but the first complementary chamber inlet valve prevents low-pressure fluid from entering the complementary chamber at the second complementary chamber inlet. 
     Process  900  then proceeds to step  906 , which involves using the high-pressure fluid to displace an actuating piston (e.g., actuating piston  126  of  FIG. 1 ) disposed inside the actuating chamber. In other words, the pressure of the high-pressure fluid displaces the actuating piston from one end of the actuating chamber to another end of the actuating chamber. Step  906  preferably includes a first cycle and a second cycle, which is carried out after the first cycle. 
     In the first cycle of step  906 , the actuating piston moves away from a first actuating chamber end (e.g., first actuating chamber end  136  of  FIG. 2A ) and towards a second actuating chamber end (e.g., second actuating chamber end  138  of  FIG. 2A ). A second actuating chamber outlet valve (e.g., second actuating chamber outlet valve  150  of  FIG. 2A ) is open to enable evacuation of high-pressure fluid held in the actuating chamber from a previous cycle. In this configuration, a first actuating chamber outlet valve (e.g., first actuating chamber outlet valve  148  of  FIG. 2A ) is closed. With the opening of the second actuating chamber outlet valve, the high-pressure fluid is now in fluidic communication, by way of a mixing line (e.g., mixing line  134  of  FIG. 2A ), with the low-pressure fluid of the complementary chamber. As explained below, in step  908 , low-pressure fluid in complementary chamber is also in fluidic communication with the mixing line and thus with the high-pressure fluid. The pressures of high-pressure fluid and that of the low-pressure fluid equalize to form an intermediate pressure fluid. Thus, the high-pressure fluid evacuates from a second actuating chamber outlet (e.g., second actuating chamber outlet  132 ) as actuating chamber exhaust fluid. 
     In the second cycle of step  906 , which is carried out after the first cycle, the actuating piston moves away from the second actuating chamber end and towards the first actuating chamber end. The first actuating chamber outlet valve is closed. The second actuating chamber outlet valve is open to enable fluidic communication between the actuating chamber and the mixing line. The pressure of high-pressure fluid and that of the low-pressure fluid, in the complementary chamber, equalizes to create an intermediate pressure fluid. The intermediate pressure fluid evacuates from a second actuating chamber outlet (e.g., second actuating chamber outlet  132  of  FIG. 2B ) as actuating chamber exhaust fluid. 
     Next, a step  908  includes forcing displacement of a complementary piston (e.g., complementary piston  112 ) disposed within the complementary chamber. In one preferred implementation of this step, the displacement of an actuating piston, which is coupled to a complementary piston, forces displacement of the complementary piston. Regardless of what enables displacement of the complementary piston, in this step, complementary piston displaces from one end of the complementary chamber to another end of the complementary chamber. In a first cycle of step  908 , which occurs simultaneously with the first cycle of step  906 , complementary piston moves away from a first complementary chamber end (e.g., first complementary chamber end  140  of  FIG. 2A ) and towards a second complementary chamber end (e.g., second complementary chamber end  142  of  FIG. 2A ). To enable evacuation of low-pressure fluid, held in the actuating chamber from a previous cycle, a second complementary chamber outlet valve (e.g., second complementary chamber outlet valve  158  of  FIG. 2A ) is open. At this stage, a first complementary chamber outlet valve (e.g., first complementary chamber outlet valve  156  of  FIG. 2A ) is closed. An open second complementary chamber outlet valve creates a fluidic pathway, via the mixing line, between the low-pressure fluid and the high-pressure fluid of the actuating chamber. The pressure of high-pressure fluid and that of the low-pressure fluid equalize to become an intermediate pressure fluid. Thus, the intermediate pressure fluid evacuates from a second actuating chamber outlet (e.g., second complementary chamber outlet  118 ) as complementary chamber exhaust fluid. 
     In the second cycle of step  908 , which is carried out after the first cycle, the complementary piston moves away from the second complementary chamber end and towards the first complementary chamber end. At this stage, the second actuating chamber outlet valve is closed. The first complementary chamber outlet valve is open to enable fluidic communication between the complementary chamber and the mixing line. The pressure of the low-pressure fluid equalizes with that of the high-pressure fluid in the actuating chamber to become an intermediate pressure fluid. The intermediate pressure fluid evacuates from a second complementary chamber outlet (e.g., second complementary chamber outlet  118  of  FIG. 2B ) as complementary chamber exhaust fluid. 
     Then, a step  910  includes mixing, in the mixing line, the actuating chamber exhaust fluid with the complementary chamber exhaust fluid to produce an intermediate pressure fluid. In a preferred embodiment of the present arrangements, intermediate pressure fluid has a higher pressure than the low-pressure fluid that is received from an evaporator of a refrigeration system. 
       FIG. 10  shows a process flow chart  1000 , according to one embodiment of the present teachings, for operation of the novel mixing mechanism shown in  FIG. 1 . 
     Process  1000  begins with a step  1002  that involves energizing, using an energy source (e.g., energy source  362  of  FIG. 3 ), an intermediate pressure condensate fluid to produce a high-pressure fluid. In a preferred embodiment of the present teachings, high-pressure fluid is a gas. 
     Next, a step  1004  includes evacuating, using a pre-mixing mechanism (e.g., pre-mixing mechanism  100  of  FIG. 1 ), a low-pressure fluid using a force applied by the high-pressure fluid to produce an actuating chamber exhaust fluid and complementary chamber exhaust fluid, each of which may have an intermediate pressure. The pre-mixing mechanism may be coupled, on an inlet side of the pre-mixing mechanism, to the energy source. The pre-mixing mechanism may be coupled, on an outlet side, to two or more outlets (e.g., first and second actuating chamber outputs  130  and  132 , respectively, and first and second complementary chamber outlets  116  and  118 , respectively of  FIG. 1 ). At least one of these outlets is designed to dispense the intermediate pressure exhaust. 
     Step  1006  includes mixing, using a mixing line (e.g., mixing line  134  of  FIG. 1 ), the exhaust refrigerant in the state and the exhaust refrigerant in the second state to produce the exhaust refrigerant in an intermediate state. The mixing line is coupled, at a receiving end, to the outlets of the pre-mixing mechanism and is configured to be coupled, at a dispensing end, to a condenser for treating exhaust refrigerant in the intermediate state to produce a refrigerant condensate in the intermediate state. 
     Then, a step  1008  includes conveying, using a condensate line, a portion of the refrigerant condensate in the intermediate state from condenser to the energy source. 
     Although illustrative embodiments of the present teachings and arrangements are shown and described in terms of controlling fluid within a sewer system, other modifications, changes, and substitutions are intended. Accordingly, it is appropriate that the disclosure be construed broadly and, in a manner, consistent with the scope of the disclosure, as set forth in the following claims.