Patent Application
20200278137
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.
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.
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.
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
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
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
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
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.
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.
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.
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 feet3 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.
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
The pre-mixing mechanism shown in Table 1 may be used in a cooling load controller (e.g., cooling load controller 360 of
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
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 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.
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.
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.
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.
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
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.
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
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.
A liquid injection pump (e.g., injection pump 370 of
The present teachings also provide processes for continuously mixing a fluid.
Next, a step 904 is carried out. This step includes receiving, at a complementary chamber (e.g., complementary chamber 102 off
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
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
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
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
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
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.
Process 1000 begins with a step 1002 that involves energizing, using an energy source (e.g., energy source 362 of
Next, a step 1004 includes evacuating, using a pre-mixing mechanism (e.g., pre-mixing mechanism 100 of
Step 1006 includes mixing, using a mixing line (e.g., mixing line 134 of
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.
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.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/US18/61401 | 11/16/2018 | WO | 00 |
| Number | Date | Country | |
|---|---|---|---|
| 62586897 | Nov 2017 | US |
