CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims priority from and the benefit of U.S. Provisional Application No. 63/390,004, entitled “COMPRESSOR SYSTEM FOR HEATING, VENTILATION, AIR CONDITIONING & REFRIGERATION SYSTEM,” filed Inly 18, 2022, which is herein incorporated by reference in its entirety for all purposes.

BACKGROUND

[0002] This section is intended to introduce the reader to various aspects of art that may be related to various aspects of the present disclosure, which are described below. This discussion is believed to be helpful in providing the reader with background information to facilitate a better understanding of the various aspects of the present disclosure. Accordingly, it should be understood that these statements are to be read in this light, and not as admissions of prior art.

[0003] Chiller systems, or vapor compression systems, utilize a working fluid (e.g., a refrigerant) that changes phases between vapor, liquid, and combinations thereof in response to exposure to different temperatures and pressures within components of the chiller system. The chiller system may place the working fluid in a heat exchange relationship with a cooling fluid (e.g., water) and may deliver the cooling fluid to conditioning equipment and/or a conditioned environment serviced by the chiller system. In some embodiments, the chiller system may include an economizer configured to improve an efficiency of the chiller system. For example, a first heat exchanger (e.g., a condenser) may cool the working fluid and direct the cooled working fluid to the economizer, which may separate the working fluid into liquid phase working fluid and vapor phase working fluid. The economizer may direct the liquid phase working fluid to a second heat exchanger (e.g., an evaporator) configured to place the working fluid in the heat exchange relationship with the cooling fluid. The economizer may direct the vapor phase working fluid to a compressor system for pressurization. Unfortunately, existing chiller systems that include economizers may be costly and/or may operate inefficiently.

SUMMARY

[0004] A summary of certain embodiments disclosed herein is set forth below. It should be understood that these aspects are presented merely to provide the reader with a brief summary of these certain embodiments and that these aspects are not intended to limit the scope of this disclosure. Indeed, this disclosure may encompass a variety of aspects that may not be set forth below.

[0005] In one embodiment, a heating, ventilation, air conditioning, and/or refrigeration system configured to circulate a working fluid therethrough includes an economizer system and a compressor system. A first economizer of the economizer system is configured to reduce a first pressure of the working fluid to provide a first vapor working fluid flow, and a second economizer of the economizer system is configured to reduce a second pressure of the working fluid in the second economizer to provide a second vapor working fluid flow. A first compressor stage of the compressor system is configured to receive the second vapor working fluid flow from the second economizer via a second inlet and an additional working fluid flow, separate from the second vapor working fluid flow, via a first inlet. A second compressor stage of the compressor system is configured to receive the first vapor working fluid flow from the first economizer via a third inlet.

[0006] In another embodiment, a vapor compression system for a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system configured to circulate a working fluid therethrough includes a first economizer configured to reduce a first pressure of the working fluid in the first economizer to provide a first vapor working fluid flow, a second economizer configured to reduce a second pressure of the working fluid in the second economizer to provide a second vapor working fluid flow, an evaporator configured to place the working fluid in the evaporator in a heat exchange relationship with a cooling fluid to provide a third vapor working fluid flow, and a compressor system. The compressor system includes a first compressor stage comprising a first inlet and a second inlet, where the first inlet is configured to receive a first working fluid flow, and the second inlet is configured to receive a second working fluid flow, separate from the first working fluid flow, and a second compressor stage comprising a third inlet configured to receive a third working fluid flow, where each of the first working fluid flow, the second working fluid flow, and the third working fluid flow comprises a different one of the first vapor working fluid flow, the second vapor working fluid flow, and the third vapor working fluid flow.

[0007] In another embodiment, a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system configured to circulate a working fluid therethrough includes an economizer system comprising one or more economizers configured to reduce a pressure of the working fluid in the one or more economizers to provide one or more vapor working fluid flows, and a compressor system. The compressor system includes a first compressor stage comprising a first inlet and a second inlet, where the first compressor stage is configured to receive a first vapor working fluid flow of the one or more vapor working fluid flows via the second inlet, and the first compressor stage is configured to receive an additional working fluid flow, separate from the first vapor working fluid flow, via the first inlet, and a second compressor stage comprising a third inlet, where the second compressor stage is configured to receive a second vapor working fluid flow of the one or more vapor working fluid flows via the third inlet.

[0008] Various refinements of the features noted above may exist in relation to various aspects of the present disclosure. Further features may also be incorporated in these various aspects as well. These refinements and additional features may exist individually or in any combination. For instance, various features discussed below in relation to one or more of the illustrated embodiments may be incorporated into any of the above-described aspects of the present disclosure alone or in any combination. The brief summary presented above is intended only to familiarize the reader with certain aspects and contexts of embodiments of the present disclosure without limitation to the claimed subject matter.

DRAWINGS

[0009] Various aspects of this disclosure may be better understood upon reading the following detailed description and upon reference to the drawings in which:

[0010] FIG. 1 is a perspective view of a building that utilizes an embodiment of a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system in a commercial setting, in accordance with an aspect of the present disclosure;

[0011] FIG. 2 is a perspective view of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure;

[0012] FIG. 3 is a schematic of an embodiment of the vapor compression system of FIG. 2, in accordance with an aspect of the present disclosure;

[0013] FIG. 4 is a schematic of an embodiment of the vapor compression system of FIG. 2, in accordance with an aspect of the present disclosure;

[0014] FIG. 5 is a schematic of an embodiment of a vapor compression system that includes an economizer system and a compressor system having a compressor configured to receive separate working fluid flows, in accordance with an aspect of the present disclosure;

[0015] FIG. 6 is a partial cross-sectional side view of an embodiment of a compressor configured to receive separate working fluid flows, in accordance with an aspect of the present disclosure;

[0016] FIG. 7 is a schematic of an embodiment of a compressor system that includes a compressor configured to receive separate working fluid flows, in accordance with an aspect of the present disclosure; [0017] FIG. 8 is a schematic of an embodiment of a compressor system that includes a compressor configured to receive separate working fluid flows, in accordance with an aspect of the present disclosure;

[0018] FIG. 9 is a schematic of an embodiment of a compressor system that includes a compressor configured to receive separate working fluid flows, in accordance with an aspect of the present disclosure;

[0019] FIG. 10 is a schematic of an embodiment of a vapor compression system that includes an economizer system and a compressor system having a compressor configured to receive separate working fluid flows, in accordance with an aspect of the present disclosure;

[0020] FIG. 11 is a schematic of an embodiment of a vapor compression system that includes an economizer system and a compressor system having a compressor configured to receive separate working fluid flows, in accordance with an aspect of the present disclosure;

[0021] FIG. 12 is a schematic of an embodiment of a compressor system that includes a compressor configured to receive separate working fluid flows, in accordance with an aspect of the present disclosure;

[0022] FIG. 13 is a schematic of an embodiment of a vapor compression system that includes an economizer system and a compressor system having a compressor configured to receive separate working fluid flows, in accordance with an aspect of the present disclosure; and

[0023] FIG. 14 is a schematic of an embodiment of a vapor compression system that includes an economizer system and a compressor system having a compressor configured to receive separate working fluid flows, in accordance with an aspect of the present disclosure. DETAILED DESCRIPTION

[0024] One or more specific embodiments will be described below. In an effort to provide a concise description of these embodiments, not all features of an actual implementation are described in the specification. It should be appreciated that in the development of any such actual implementation, as in any engineering or design project, numerous implementation-specific decisions must be made to achieve the developers’ specific goals, such as compliance with system-related and business-related constraints, which may vary from one implementation to another. Moreover, it should be appreciated that such a development effort might be complex and time consuming, but would nevertheless be a routine undertaking of design, fabrication, and manufacture for those of ordinary skill having the benefit of this disclosure.

[0025] When introducing elements of various embodiments of the present disclosure, the articles “a,” “an,” and “the” are intended to mean that there are one or more of the elements. The terms “comprising,” “including,” and “having” are intended to be inclusive and mean that there may be additional elements other than the listed elements. Additionally, it should be understood that references to “one embodiment” or “an embodiment” of the present disclosure are not intended to be interpreted as excluding the existence of additional embodiments that also incorporate the recited features.

[0026] As used herein, the terms “approximately,” “generally,” “substantially,” and so forth, are intended to convey that the property value being described may be within a relatively small range of the property value, as those of ordinary skill would understand. For example, when a property value is described as being “approximately” equal to (or, for example, “substantially similar” to) a given value, this is intended to convey that the property value may be within +/- 5%, within +/- 4%, within +/- 3%, within +/- 2%, within +/- 1%, or even closer, of the given value. Similarly, when a given feature is described as being “substantially parallel” to another feature, “generally perpendicular” to another feature, and so forth, this is intended to convey that the given feature is within +/- 5%, within +/- 4%, within +/- 3%, within +/- 2%, within +/- 1%, or even closer, to having the described nature, such as being parallel to another feature, being perpendicular to another feature, and so forth. Mathematical terms, such as “parallel” and “perpendicular,” should not be rigidly interpreted in a strict mathematical sense, but should instead be interpreted as one of ordinary skill in the art would interpret such terms. For example, one of ordinary skill in the art would understand that two lines that are substantially parallel to each other are parallel to a substantial degree, but may have minor deviation from exactly parallel.

[0027] Embodiments of the present disclosure relate to a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system having a vapor compression system (e.g., a vapor compression circuit). The vapor compression system may include a compressor system configured to pressurize a working fluid within the vapor compression system and to direct the working fluid to a condenser, which may cool and condense the working fluid. The condensed working fluid may be directed to an expansion device, which may reduce a pressure of the working fluid and further cool the working fluid. From the expansion device, the cooled working fluid may be directed to an evaporator, which may place the working fluid in a heat exchange relationship with a cooling fluid to cool the cooling fluid. The compressor system may then receive the working fluid from the evaporator for pressurization to restart the vapor compression cycle.

[0028] In some embodiments, the vapor compression system may include an economizer system configured to receive the working fluid from the condenser. The economizer may include one or more economizers (e.g., economizer stages) configured to separate the working fluid into liquid working fluid and vapor working fluid. The economizers may direct the liquid working fluid to the evaporator and direct the vapor working fluid toward the compressor system for pressurization. In order to improve performance (e.g., efficiency) of the vapor compression system, the compressor system may include multiple compressors or compressor stages, such as individual compressor impellers, that may receive the respective vapor working fluid flow directed by the economizers. As described herein, a single compressor stage receives a vapor working fluid flow and pressurizes the vapor working fluid flow to a higher pressure to provide a pressurized vapor working fluid flow. As an example, each compressor stage may receive a vapor working fluid flow from one of the economizers and increase the pressure of the vapor working fluid flow to a particular pressure that facilitates flow of the vapor working fluid flow through the vapor compression system. For instance, the compressor stage may increase the pressure of the vapor working fluid flow toward the pressure of an additional working fluid flow (e.g., a working fluid flow pressurized by a different compressor or compressor stage) to enable desirable flow (e g., a combined flow) of both the vapor working fluid flow and the additional working fluid flow to another component instead of, for example, causing undesirable back flow of working fluid to the compressor stage, uneven mixture between the working fluid flows, or other flow disruption that hinders flow to the other component. Such flow disruption may be caused by an excessive pressure differential between the vapor working fluid flow and the additional working fluid flow, and the flow disruption may reduce efficient flow of the working fluid to another component and through the vapor compression system. However, increasing a number of compressor stages implemented in the vapor compression system may increase a cost and/or complexity associated with manufacture, installation, and/or operation of the vapor compression system.

[0029] Thus, it is now recognized that improvements are desired for HVAC&R systems having economizer systems. Accordingly, embodiments of the present disclosure are directed to a compressor system that includes a single compressor stage that may receive multiple, separate working fluid flows. For example, the compressor stage may include a first inlet configured to receive a first working fluid flow (e.g., from the evaporator) and a second inlet configured to receive a second working fluid flow (e.g., from an economizer). The compressor stage may pressurize both working fluid flows and discharge the pressurized working fluid flows, such as to the condenser or to another compressor stage. For example, such a compressor stage may be a single stage economized compressor configured to receive a working fluid flow via the first inlet and an additional working fluid flow from an economizer via the second inlet and pressurize both working fluid flows to approximately the same pressure. Indeed, the single stage economized compressor may have multiple inlets configured to receive respective working fluid flows that may be at different intake pressures, and the single stage economized compressor may have a single impeller configured to pressurize each working fluid flow to a common, increased pressure. Such a compressor stage may operate more efficiently to pressurize working fluid flows in comparison to a compressor stage having a single inlet configured to receive a working fluid flow (e.g., a compressor stage dedicated to pressurize vapor working fluid flow from a single one of the economizers). That is, the compressor stage having multiple inlets may be configured to pressurize relatively more working fluid flows, such as to a common pressure. Therefore, the compressor system may utilize a limited number of compressor stages to pressurize vapor working fluid flows (e.g., separate vapor working fluid flows) from the economizer system, such as an economizer system having multiple economizers or economizer stages. Thus, manufacture, installation, and/or operation of the vapor compression system may be improved.

[0030] Turning now to the drawings, FIG. 1 is a perspective view of an embodiment of an environment for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system 10 in a building 12 for a typical commercial setting. The HVAC&R system 10 may include a vapor compression system 14 (e.g., a chiller, a vapor compression circuit) that supplies a chilled liquid, which may be used to cool the building 12. The HVAC&R system 10 may also include a boiler 16 to supply warm liquid to heat the building 12 and an air distribution system which circulates air through the building 12. The air distribution system can also include an air return duct 18, an air supply duct 20, and/or an air handler 22. In some embodiments, the air handler 22 may include a heat exchanger that is connected to the boiler 16 and the vapor compression system 14 by conduits 24. The heat exchanger in the air handler 22 may receive either heated liquid from the boiler 16 or chilled liquid from the vapor compression system 14, depending on the mode of operation of the HVAC&R system 10. The HVAC&R system 10 is shown with a separate air handler on each floor of building 12, but in other embodiments, the HVAC&R system 10 may include air handlers 22 and/or other components that may be shared between or among floors.

[0031] FIGS. 2 and 3 are embodiments of the vapor compression system 14 that can be used in the HVAC&R system 10. The vapor compression system 14 may circulate a refrigerant through a circuit starting with a compressor 32. The circuit may also include a condenser 34, an expansion valve(s) or device(s) 36, and a liquid chiller or an evaporator 38. The vapor compression system 14 may further include a control panel 40 that has an analog to digital (A/D) converter 42, a microprocessor 44, a non-volatile memory 46, and/or an interface board 48.

[0032] Some examples of fluids that may be used as refrigerants in the vapor compression system 14 are hydrofluorocarbon (HFC) based refrigerants, for example, R- 410A, R-407, R-134a, R-1234ze, R1233zd, hydrofluoro olefin (HFO), "natural" refrigerants like ammonia (NH3), R-717, carbon dioxide (CO2), R-744, or hydrocarbon based refrigerants, water vapor, or any other suitable refrigerant. In some embodiments, the vapor compression system 14 may be configured to efficiently utilize refrigerants having a normal boiling point of about 19 degrees Celsius (66 degrees Fahrenheit) at one atmosphere of pressure, also referred to as low pressure refrigerants, versus a medium pressure refrigerant, such as R-134a. As used herein, "normal boiling point" may refer to a boiling point temperature measured at one atmosphere of pressure.

[0033] In some embodiments, the vapor compression system 14 may use one or more of a variable speed drive (VSDs) 52, a motor 50, the compressor 32, the condenser 34, the expansion valve or device 36, and/or the evaporator 38. The motor 50 may drive the compressor 32 and may be powered by a variable speed drive (VSD) 52. The VSD 52 receives alternating current (AC) power having a particular fixed line voltage and fixed line frequency from an AC power source, and provides power having a variable voltage and frequency to the motor 50. In other embodiments, the motor 50 may be powered directly from an AC or direct current (DC) power source. The motor 50 may include any type of motor that can be powered by a VSD or directly from an AC or DC power source, such as a switched reluctance motor, an induction motor, an electronically commutated permanent magnet motor, or another suitable motor.

[0034] The compressor 32 compresses a refrigerant vapor and delivers the vapor to the condenser 34 through a discharge passage. In some embodiments, the compressor 32 may be a centrifugal compressor. The refrigerant vapor delivered by the compressor 32 to the condenser 34 may transfer heat to a cooling fluid (e.g., water or air) in the condenser 34. The refrigerant vapor may condense to a refrigerant liquid in the condenser 34 as a result of thermal heat transfer with the cooling fluid. The liquid refrigerant from the condenser 34 may flow through the expansion device 36 to the evaporator 38. In the illustrated embodiment of FIG. 3, the condenser 34 is water cooled and includes a tube bundle 54 connected to a cooling tower 56, which supplies the cooling fluid to the condenser 34.

[0035] The liquid refrigerant delivered to the evaporator 38 may absorb heat from another cooling fluid, which may or may not be the same cooling fluid used in the condenser 34. The liquid refrigerant in the evaporator 38 may undergo a phase change from the liquid refrigerant to a refrigerant vapor. As shown in the illustrated embodiment of FIG. 3, the evaporator 38 may include a tube bundle 58 having a supply line 60S and a return line 60R connected to a cooling load 62. The cooling fluid of the evaporator 38 (e g., water, ethylene glycol, calcium chloride brine, sodium chloride brine, or any other suitable fluid) enters the evaporator 38 via return line 60R and exits the evaporator 38 via supply line 60S. The evaporator 38 may reduce the temperature of the cooling fluid in the tube bundle 58 via thermal heat transfer with the refrigerant. The tube bundle 58 in the evaporator 38 can include a plurality of tubes and/or a plurality of tube bundles. In any case, the vapor refrigerant exits the evaporator 38 and returns to the compressor 32 by a suction line to complete the cycle.

[0036] FIG. 4 is a schematic of the vapor compression system 14 with an intermediate circuit 64 incorporated between the condenser 34 and the expansion device 36. The intermediate circuit 64 may have an inlet line 68 that is directly fluidly connected to the condenser 34. In other embodiments, the inlet line 68 may be indirectly fluidly coupled to the condenser 34. As shown in the illustrated embodiment of FIG. 4, the inlet line 68 includes a first expansion device 66 positioned upstream of an intermediate vessel 70, which is incorporated into the vapor compression systems 14 described above to provide efficient operation. In some embodiments, the intermediate vessel 70 may be a flash tank (e.g., a flash intercooler, an economizer). In other embodiments, the intermediate vessel 70 may be configured as a heat exchanger or a “surface economizer.” In the illustrated embodiment of FIG. 4, the intermediate vessel 70 is used as a flash tank, and the first expansion device 66 is configured to lower the pressure of (e.g., expand) the liquid refrigerant received from the condenser 34. During the expansion process, a portion of the liquid may vaporize, and thus, the intermediate vessel 70 may be used to separate the vapor from the liquid received from the first expansion device 66.

[0037] Additionally, the intermediate vessel 70 may provide for further expansion of the liquid refrigerant because of a pressure drop experienced by the liquid refrigerant when entering the intermediate vessel 70 (e.g., due to a rapid increase in volume experienced when entering the intermediate vessel 70). The vapor in the intermediate vessel 70 may be drawn by the compressor 32 through a suction line 74 of the compressor 32. For example, the compressor 32 may include a single compressor stage configured to receive and pressurize both the vapor from the evaporator 38 and the vapor from the intermediate vessel 70 to a particular pressure. The liquid that collects in the intermediate vessel 70 may be at a lower enthalpy than the liquid refrigerant exiting the condenser 34 because of the expansion in the expansion device 66 and/or the intermediate vessel 70. The liquid from intermediate vessel 70 may then flow in line 72 through a second expansion device 36 to the evaporator 38.

[0038] It should be appreciated that any of the features described herein may be incorporated with the vapor compression system 14 or any other suitable HVAC&R systems. For example, the present techniques may be incorporated with any HVAC&R system having an economizer, such as the intermediate vessel 70, and a compressor, such as the compressor 32. The discussion below describes the present techniques incorporated with embodiments of the compressor 32 configured as a single stage compressor. However, it should be noted that the systems and methods described herein may be incorporated with other embodiments of the compressor 32 (e.g., multi-stage compressors) and HVAC&R system 10.

[0039] The present disclosure is directed to an HVAC&R system having a compressor system that includes a compressor configured to receive and pressurize separate working fluid flows. For example, the compressor may include a first inlet configured to receive a first working fluid flow, such as from an evaporator and/or from another compressor. The compressor may include a second inlet configured to receive a second working fluid flow, such as from an economizer (e.g., intermediate vessel 70). The compressor may pressurize the first and second working fluid flows and discharge the pressurized working fluid flow (e.g., to a condenser, to another compressor). In this manner, a single compressor of the compressor system may be utilized to pressurize multiple, separate working fluid flows. Thus, the compressor system may include a fewer quantity of compressors as compared to a compressor system having compressor embodiments configured to receive and pressurize a single working fluid flow. As such, the compressor system may pressurize separate working fluid flows, including a working fluid flow received from an economizer, at a reduced cost and/or complexity associated with manufacture, installation, and/or operation of the HVAC&R system.

[0040] With the foregoing in mind, FIG. 5 is a schematic of an embodiment of a vapor compression system or circuit 100 (e.g., of an HVAC&R system) configured to circulate a working fluid. The vapor compression system 100 may include a condenser 102 (e.g., the condenser 34) configured to cool the working fluid and an evaporator 104 (e.g., the evaporator 38) configured to place the working fluid in a heat exchange relationship with a cooling fluid to absorb heat from the cooling fluid. The vapor compression system 100 may also include a compressor system 106 configured to pressurize the working fluid. For example, the compressor system 106 may be configured to receive working fluid from the evaporator 104, pressurize the working fluid, and direct the pressurized working fluid to the condenser 102.

[0041] In the illustrated embodiment, the compressor system 106 includes multiple compressors, such as compressor impellers and/or stages, arranged in a series flow arrangement (e.g., multiple single stage compressors arranged in series) relative to refrigerant flow through the compressor system 106. For example, the compressor system 106 may include a first compressor or compressor stage 110 (e.g., a first single stage compressor configured to pressurize one or more vapor flows to a common, increased pressure) and a second compressor or compressor stage 112 (e.g., a second single stage compressor configured to pressurize one or more vapor flows to a common, increased pressure). The first compressor 110 may receive an intake working fluid flow 113 from the evaporator 104, pressurize the intake working fluid flow 113, and discharge the pressurized intake working fluid flow 113 toward the second compressor 112 as a first pressurized working fluid flow 114. The second compressor 112 may receive the first pressurized working fluid flow 114 and further pressurize the first pressurized working fluid flow 114 for discharge as a second pressurized working fluid flow 115 toward the condenser 102. It should be noted that reference to an element (e.g., a system, component, or the like) directing a fluid (e.g., refrigerant in a vapor or liquid phase) toward another element indicates that the element pressurizes, forces, guides (e.g., via piping, valves, mechanical operation), or the like, the fluid directly or indirectly to the other element.

[0042] The vapor compression system 100 may also include an economizer system 116 (e.g., an intermediate vessel system, a flash tank system) configured to receive refrigerant from the condenser 102. The economizer system 116 may include multiple economizers (e.g., economizer stages) configured to reduce a pressure of the working fluid to vaporize at least a portion of the working fluid to separate the working fluid into liquid working fluid and vapor working fluid. For example, the economizer system 116 may include a first economizer 118, a second economizer 120, and a third economizer 122. The first economizer 118 may receive working fluid from the condenser 102, reduce the pressure of the received working fluid to vaporize a portion of the received working fluid and separate the working fluid into liquid working fluid and vapor working fluid, and direct the liquid working fluid to the second economizer 120. The second economizer 120 may reduce the pressure of the liquid working fluid received from the first economizer 118 to vaporize a portion of the received working fluid to separate the working fluid into liquid working fluid and vapor working fluid and direct the liquid working fluid to the third economizer 122 The third economizer 122 may reduce the pressure of the liquid working fluid received from the second economizer 120 to vaporize a portion of the received working fluid to separate the working fluid into liquid working fluid and vapor working fluid and direct the liquid working fluid to the evaporator 104. Different numbers of economizers may be utilized in such an arrangement in accordance with present embodiments.

[0043] Reducing the pressure of the refrigerant may further reduce a temperature of the refrigerant. Thus, by further reducing the pressure of the refrigerant, the first economizer 118, the second economizer 120, and the third economizer 122 may increase an amount of cooling provided by the vapor compression system 100 to the cooling fluid, thereby increasing efficiency of the vapor compression system 100. In certain embodiments, the economizer system 116 may include a single shell, housing, enclosure, or vessel, and each economizer 118, 120, 122 may include a separate chamber, compartment, or volume within the single shell. Additionally or alternatively, each economizer 118, 120, 122 may include a respective housing and enclosure that may be positioned adjacent to (e.g., coupled to) one another to form the economizer system 116.

[0044] It should be noted that components of the vapor compression system 100 may be described as being positioned or arranged upstream or downstream of one another. As described herein, upstream and downstream may refer to the positioning of the components with respect to a sequential flow of refrigerant through the vapor compression system 100, such as from the compressor system 106 (e.g., from the first compressor 110 to the second compressor 112), to the condenser 102, to the economizer system 116, and to the evaporator 104 and/or back to the compressor system 106. For example, upstream may refer to positioning (e.g., a preceding position) in a direction opposite the direction of refrigerant flow through the vapor compression system 100, and downstream may refer to positioning (e.g., a proceeding position) in a direction of refrigerant flow through the vapor compression system 100.

[0045] Each compressor 110, 112 may be configured to receive vapor working fluid from the economizer system 116. For instance, the first economizer 118 and the second economizer 120 may discharge a first vapor working fluid flow 124 and a second vapor working fluid flow 126, respectively, to the second compressor 112 for pressurization. The third economizer 122 may discharge a third vapor working fluid flow 128 to the first compressor 110 for pressurization. The first compressor 110 may include a first inlet 130 configured to receive the intake working fluid flow 113 from the evaporator 104 and a second inlet 132, separate from the first inlet 130, configured to receive the third vapor working fluid flow 128 from the third economizer 122. Thus, the first compressor 110 may receive the intake working fluid flow 113 and the third vapor working fluid flow 128 as separate working fluid flows for pressurization and discharge as the first pressurized working fluid flow 114. The second compressor 112 may include a third inlet 134 configured to receive the first pressurized working fluid flow 114 from the first compressor 110 and the second vapor working fluid flow 126 from the second economizer 120. As an example, the second vapor working fluid flow 126 may combine with the first pressurized working fluid flow 114 as a combined working fluid flow 135, and the combined working fluid flow 135 (e.g., the combined second vapor working fluid flow 126 and the first pressurized working fluid flow 114) may be directed to the second compressor 112 via the third inlet 134. The second compressor 112 may also include a fourth inlet 136, separate from the third inlet 134, configured to receive the first vapor working fluid flow 124 from the first economizer 118. As such, the second compressor 112 may receive the first vapor working fluid flow 124 and the combined working fluid flow 135 as separate working fluid flows for pressurization and discharge as the second pressurized working fluid flow 115. In this manner, each compressor 110, 112 may include multiple inlets configured to receive separate working fluid flows, such as working fluid flows at different pressures.

[0046] The illustrated embodiment of the compressors 110, 112 configured to receive separate working fluid flows may limit a quantity of compressors utilized by the compressor system 106 to pressurize working fluid from the economizer system 116. For example, at least one of the compressors 110, 112 may receive multiple vapor working fluid flows directly from the economizer system 116. Thus, a fewer quantity of compressors may be utilized to pressurize the vapor working fluid flows from the economizer system 116 as compared to a compressor system that includes individual compressors dedicated to receiving and pressurizing each respective vapor working fluid flow from the economizer system 116. As such, a cost and/or complexity associated with manufacture and/or operation of the illustrated compressor system 106 may be reduced.

[0047] Although the compressor system 106 of the illustrated vapor compression system 100 includes two compressors 110, 112 configured to receive the vapor working fluid flows 124, 126, 128 from the economizer system 116, the compressor system 106 may have any suitable number of compressors 110, 112 in additional or alternative HVAC&R systems. For example, the number of compressors 110, 112 utilized in the compressor system 106 may be based on the number of economizers 118, 120, 122 of the economizer system 116. For instance, three compressors may be utilized to pressurize vapor working fluid flow from an economizer system 116 having five economizers, seven compressors may be utilized to pressurize vapor working fluid flow from an economizer system 116 having seven economizers, and so forth. In such embodiments, each compressor may receive multiple (e.g., two) separate working fluid flows for pressurization.

[0048] FIG. 6 is a partial cross-sectional side view of an embodiment of a compressor 160 (e.g., a compressor impeller system, a single stage economized compressor), such as the compressor 110 and/or the compressor 112. The compressor 160 may include a housing 162 (e.g., a compressor housing) in which an impeller 164 may be disposed. A first working fluid flow 166 (e.g., the intake working fluid flow 113, the first pressurized working fluid flow 114, the second vapor working fluid 126, the combined working fluid flow 135, a main suction flow) may enter the housing 162 at a suction inlet 168 (e.g., a first inlet) and be directed toward the impeller 164. The compressor impeller 164 may be fixedly coupled to a shaft 170, which may rotate (e.g., via a motor) during operation of the compressor 160 to drive corresponding rotation of the impeller 164. The impeller 164 driven into rotation may impart mechanical energy into the first working fluid flow 166. The first working fluid flow 166 may exit the impeller 164, through a diffuser passage 172 (e.g., a pressure recovery portion) of the compressor 160, and toward a volute 174 of the compressor 160. From the volute 174, the first working fluid flow 166 may be directed toward a condenser (e.g., the condenser 102) and/or toward another compressor.

[0049] The compressor 160 may also be configured to receive a second working fluid flow 176 (e.g., the first vapor working fluid flow 124, the third vapor working fluid flow 128) from an economizer 178 (e.g., the first economizer 118, the third economizer 122). To this end, the compressor 160 includes an economizer inlet 180 (e.g., a second inlet) fluidly coupled to the economizer 178. The economizer inlet 180 may direct the second working fluid flow 176 into the housing 162 to combine with the first working fluid flow 166. For example, the housing 162 may include an opening 182 through which the second working fluid flow 176 may be directed to flow toward the first working fluid flow 166. The first working fluid flow 166 and the second working fluid flow 176 may combine at a flow junction 183 within the housing 162. For instance, the flow junction 183 may be positioned between the diffuser passage 172 and the impeller 164.

[0050] The initial pressure of the first working fluid flow 166 at the suction inlet 168 may be different from the initial pressure of the second working fluid flow 176 at the economizer inlet 180. In other words, the working fluid flows 166, 176 received by the compressor 160 may initially be at different pressures. For example, the initial pressure of the first working fluid flow 166 may be less than the initial pressure of the second working fluid flow 176. However, the compressor 160 may partially pressurize the first working fluid flow 166 via the impeller 164 toward the initial pressure of the second working fluid flow 176 prior to flow of the first working fluid flow 166 reaching the flow junction 183. Thus, at the flow junction 183, the partially pressurized first working fluid flow 166 and the received second working fluid flow 176 may have substantially similar pressures. The similar pressures of the working fluid flows 166, 176 at the flow junction 183 may facilitate directing of the working fluid flows 166, 176 toward the diffuser passage 172 instead of, for example, in back flow directions toward the suction inlet 168 and/or the economizer inlet 180 as a result of a pressure differential between the first working fluid flow 166 and the second working fluid flow 176 at the flow junction 183. In this manner, the compressor 160 may readily direct each of the first working fluid flow 166 and the second working fluid flow 176 toward the volute 174 for discharge. The compressor 160 may further pressurize the working fluid flow 166, 176 directed downstream of the flow junction 183 and through the diffuser passage 172, such as to a common increased pressure, for discharge.

[0051] In certain embodiments, the impeller 164 may include blades 184 that, during rotation of the impeller 164, may force the first working fluid flow 166 through the housing 162, through the diffuser passage 172, and to the volute 174. The impeller 164 may also include a shroud 186 that may be integral to the blades 184 to enclose and cover the blades 184 (e.g., to shield a portion, such as a tip 185, of the blades 184 from the housing 162). The first working fluid flow 166 may be directed through the impeller 164 within the shroud 186 toward the diffuser passage 172. In the illustrated embodiment, the second working fluid flow 176 is directed through the housing 162 and along a passage 188 that extends between the shroud 186 and the housing 162 toward the diffuser passage 172 to enable the second working fluid flow 176 to combine with the first working fluid flow 166 (e.g., the partially pressurized first working fluid that is at approximately the same pressure as that of the second working fluid flow 176) at the flow junction 183. The shroud 186 may block contact between the second working fluid flow 176 and the first working fluid flow 166 within the shroud 186. For example, the first working fluid flow 166 and the second working fluid flow 176 may combine with one another downstream of the tip 185 of the blades 184 with respect to flow through the compressor 160 and toward the diffuser passage 172. However, in additional or alternative embodiments, the impeller 164 may not include the shroud 186 and/or may include a shroud 186 that exposes a portion of the blades 184, such as the tip 185, to the housing 162. In such embodiments, the first working fluid flow 166 and the second working fluid flow 176 may combine with one another upstream of the tip 185 of the blades 184 with respect to flow of the working fluid through the compressor 160 and toward the diffuser passage 172. In any case, the suction inlet 168 and the economizer inlet 180 may enable the compressor 160 to receive separate working fluid flows for pressurization and discharge.

[0052] FIG. 7 is a schematic of an embodiment of the compressor system 106 having the first compressor 110, which may include a first compressor impeller 210, and the second compressor 112, which may include a second compressor impeller 212. The first compressor impeller 210 and the second compressor impeller 212 may be coupled to a common shaft 214. For example, the compressor system 106 may include a double- ended (e.g., a double-ended two single stage compressor) configuration in which the first compressor impeller 210 is coupled at a first end 216 of the shaft 214 and the second compressor impeller 212 is coupled at a second end 218, opposite the first end 216, of the shaft 214. Thus, rotation of the shaft 214 via a motor 220 may drive rotation of each of the first compressor impeller 210 and the second compressor impeller 212.

[0053] The first compressor 110 may receive the intake working fluid flow 113, such as from the evaporator 104, via the first inlet 130 (e.g., a suction inlet), and pressurize the intake working fluid flow 113. The first compressor 1 10 may also receive the third vapor working fluid flow 128 from the third economizer 122 via the second inlet 132 (e.g., an economizer inlet), and the intake working fluid flow 113 (e.g., a partially pressurized intake working fluid flow 113) and the third vapor working fluid flow 128 may combine and flow toward a first volute 224. The first compressor 110 may discharge the intake working fluid flow 113 and the third vapor working fluid flow 128 from the first volute 224 toward the second compressor 112 as the first pressurized working fluid flow 114.

[0054] The second compressor 112 may receive the first pressurized working fluid flow 114 via the third inlet 134 (e.g., a suction inlet). The second compressor 112 may additionally or alternatively receive the second vapor working fluid flow 126 from the second economizer 120 via the third inlet 134. The second compressor 112 may pressurize the first pressurized working fluid flow 114 and/or the second vapor working fluid flow 126 (e.g., as the combined working fluid flow 135) and direct the first pressurized working fluid flow 114 and/or the second vapor working fluid flow 126 (e.g., the combined working fluid flow 135) toward a second volute 226. The second compressor 112 may further receive the first vapor working fluid 124 from the first economizer 118 via the fourth inlet 136 (e.g., an economizer inlet). The first vapor working fluid 124 may combine with the first pressurized working fluid flow 114 and/or the second vapor working fluid flow 126 (e.g., the first pressurized working fluid flow 114 and/or the second vapor working fluid flow 126 partially pressurized by the second compressor 112, the combined working fluid flow 135) and flow toward the second volute 226. The second compressor 112 may then discharge the combination of the first pressurized working fluid flow 114, the first vapor working fluid flow 124, and/or the second vapor working fluid flow 126 as the second pressurized working fluid flow 115 toward the condenser 102.

[0055] In the illustrated embodiment, the first compressor 110 and the second compressor 112 are oriented in opposite directions of one another. For example, the first inlet 130 of the first compressor 110 and the third inlet 134 of the second compressor 112 face away from one another. For this reason, rotation of the shaft 214, as caused by operation of the motor 220, may drive the first compressor impeller 210 to rotate in a first rotational direction 228 (e.g., a clockwise rotation) and the second compressor impeller 212 to rotate in a second rotational direction 230 (e.g., a counterclockwise rotation), opposite the first rotational direction 228. In additional or alternative embodiments, the first compressor 110 and the second compressor 112 may be oriented in opposite directions of one another such that the first inlet 130 of the first compressor 110 and the third inlet 134 of the second compressor 112 face toward one another. In further embodiments, the first compressor 110 and the second compressor 112 may be oriented in the same direction (e.g., the first inlet 130 and the third inlet 134 face the same direction).

[0056] FIG. 8 is a schematic of an embodiment of the compressor system 106 having the first compressor 110 and the second compressor 112. For example, the first compressor 110 may receive and pressurize the intake working fluid flow 113 (e.g., from the evaporator 104) and/or the third vapor working fluid flow 128 (e.g., from the third economizer 122) to discharge the intake working fluid flow 113 and/or the third vapor working fluid flow 128 as the first pressurized working fluid flow 114 toward the second compressor 112. The second compressor 112 may receive and pressurize the first pressurized working fluid flow 114, the first vapor working fluid flow 124 (e.g., from the first economizer 118), and/or the second vapor working fluid flow 126 (e.g., from the second economizer 120) to discharge the first pressurized working fluid flow 114, the first vapor working fluid flow 124, and/or the second vapor working fluid flow 126 as the second pressurized working fluid flow 115 toward the condenser 102.

[0057] In the illustrated embodiment, the first compressor 110 and the second compressor 112 are oriented in the same direction. For example, each of the first inlet 130 and the second inlet 134 may face a common direction, such as in a direction 250. Orientation of the compressors 110, 112 in the same direction may enable rotation of the shaft 214, as caused by operation of the motor 220, to drive rotation of the compressor impellers 210, 212 in the same rotational direction, such as the first rotational direction 228. [0058] The compressors 110, 112 are positioned at a common end 252 (e.g., the first end 216) of the shaft 214 in the illustrated embodiment. As an example, the common end 252 may include a drive end of the shaft 214, or an end of the shaft 214 that may receive a significant radial load or force (e.g., a force imparted perpendicularly to a rotational axis of the shaft 214). As another example, the common end 252 may include a nondrive end, opposite the drive end, of the shaft 214, such as for an overhung (e.g., double overhung, an overhung two single stage) configuration of the compressor system 106. Moreover, although the compressors 110, 112 are oriented such that the first inlet 130 and the third inlet 134 face away from the motor 220 in the illustrated embodiment, the compressors 110, 112 may be oriented such that the first inlet 130 and the third inlet 134 face toward the motor 220 in alternative embodiments.

[0059] FIG. 9 is a schematic of an embodiment of the compressor system 106 having the first compressor 110 and the second compressor 112. In the illustrated embodiment, the compressor impellers 210, 212 are coupled to different shafts. For example, the first compressor impeller 210 may be coupled to a first shaft 280 driven by a first motor 282, and the second compressor impeller 212 may be coupled to a second shaft 284 driven by a second motor 286. In this manner, operation of the first motor 282 may rotate the first shaft 280 to drive rotation of the first compressor impeller 210, but the first motor 282 may not directly drive rotation of the second compressor impeller 212 via the second shaft 284, and operation of the second motor 286 may rotate the second shaft 284 to drive rotation of the second compressor impeller 212, but the second motor 286 may not directly drive rotation of the first compressor impeller 210 via the first shaft 280. In this manner, the compressors 110, 112 (e.g., a rotational speed of the compressor impellers 210, 212) may be controlled independently of one another. However, operation of the compressors 110, 112 may be generally similar as that described above in which the first compressor 110 may receive and pressurize the intake working fluid flow 113 and/or the third vapor working fluid flow 128 to discharge the intake working fluid flow 113 and/or the third vapor working fluid flow 128 as the first pressurized working fluid flow 114 toward the second compressor 112. Moreover, the second compressor 112 may receive and pressurize the first pressurized working fluid flow 114, the first vapor working fluid flow 124, and/or the second vapor working fluid flow 126 (e.g., the combined working fluid flow 135 and the first vapor working fluid flow 124) to discharge the first pressurized working fluid flow 114, the first vapor working fluid flow 124, and/or the second vapor working fluid flow 126 as the second pressurized working fluid flow 115 toward the condenser 102.

[0060] The compressors 110, 112 may be oriented such that the first inlet 130 and the third inlet 134 face the same direction, such as the direction 250. In alternative embodiments, the compressors 110, 112 may be oriented in different directions, such as an arrangement in which the first inlet 130 and the third inlet 134 face opposite directions, an arrangement in which the first inlet 130 and the third inlet 134 face crosswise to one another, and so forth. Indeed, the shafts 280, 284 may be arranged in any suitable manner to orient the compressors 110, 112 in corresponding directions.

[0061] In the embodiments described above, the compressors 110, 112 are positioned in a series flow arrangement in which the working fluid may be directed from the first compressor 110 to the second compressor 112. In additional or alternative embodiments, the compressors 110, 112 may be positioned in a parallel flow arrangement in which the working fluid may be directed to one of the compressors 110, 112 and not the other of the compressors 110, 112 before being directed to the condenser 102. For example, each of the first compressor 110 and the second compressor 112 may directly discharge respective working fluid flows to the condenser 102.

[0062] FIG. 10 is a schematic of an embodiment of the vapor compression system 100 in which the first compressor 110 and the second compressor 112 are in a parallel flow arrangement. The first compressor 110 may receive and pressurize the intake working fluid flow 113 (e g., from the evaporator 104 via the first inlet 130) and/or the third vapor working fluid flow 128 (e.g., from the third economizer 122 via the second inlet 132) to provide the first pressurized working fluid flow 114. However, the first compressor 110 may discharge the first pressurized working fluid flow 114 to the condenser 102 instead of to the second compressor 112. Thus, the first pressurized working fluid flow 114 may bypass flow through the second compressor 112 to flow directly from the first compressor 110 to the condenser 102. The second compressor 112 may receive and pressurize the first vapor working fluid flow 124 (e.g., via the fourth inlet 136) and/or the second vapor working fluid flow 126 (e.g., via the third inlet 134) to discharge the first vapor working fluid flow 124 and/or the second vapor working fluid flow 126 as the second pressurized working fluid flow 115 to the condenser 102. For example, the first pressurized working fluid flow 114 and the second pressurized working fluid flow 115 may combine and flow to the condenser 102 via a common inlet 320 of the condenser 102. In additional or alternative embodiments, the first pressurized working fluid flow 114 and the second pressurized working fluid flow 115 may flow to the condenser 102 as separate fluid flows, such as via different inlets of the condenser 102. In the parallel flow arrangement, the first compressor 110 and the second compressor 112 may be coupled to a common shaft or to separate shafts.

[0063] In addition to or as an alternative to the embodiment of the compressors 110, 112 (e.g., as represented by the compressor 160) having multiple inlets configured to receive separate working fluid flows, the vapor compression system 100 may also include a compressor embodiment having a single inlet configured to receive a single working fluid flow. For example, FIG. 11 is a schematic of an embodiment of the vapor compression system 100 having the first compressor 110 and a third compressor 350. The first compressor 110 may receive separate working fluid flows, such as the intake working fluid flow 113 via the first inlet 130 and the second vapor working fluid flow 126 via the second inlet 132. The first compressor 110 may pressurize the intake working fluid flow 113 and/or the second vapor working fluid flow 126 to provide the first pressurized working fluid flow 114.

[0064] The third compressor 350 may be configured to receive a single working fluid flow. For instance, the third compressor 350 may include a fifth inlet 352, which may receive the first pressurized working fluid flow 114. Thus, the first compressor 110 and the third compressor 350 may be in a series flow arrangement in which the third compressor 350 is positioned downstream of the first compressor 110 with respect to a flow of the working fluid through the compressor system 106. In some embodiments, the first vapor working fluid flow 124 directed by the first economizer 118 may combine with the first pressurized working fluid flow 114 as a combined working fluid flow 354, and the third compressor 350 may receive and pressurize the combined working fluid flow 354 to provide the second pressurized working fluid flow 115 for discharge toward the condenser 102. However, the third compressor 350 may not include an inlet in addition to the fifth inlet 352 and therefore may not receive separate working fluid flows (e.g., the third vapor working fluid flow 128 from the third economizer 122 that would otherwise be incorporated in the economizer system 116).

[0065] FIG. 12 is a schematic of an embodiment of the compressor system 106 having the first compressor 110 and the third compressor 350. The first compressor 110 may receive and pressurize the intake working fluid flow 113 and/or the second vapor working fluid flow 126 for discharge toward the third compressor 350 as the first pressurized working fluid flow 114. The third compressor 350 may receive and pressurize the first pressurized working fluid flow 114 and/or the first vapor working fluid flow 124 (e.g., the combined working fluid flow 354) via the fifth inlet 352 for discharge toward the condenser 102 as the second pressurized working fluid flow 115. As an example, the third compressor 350 may include a third compressor impeller 380, which may impart mechanical energy into the first pressurized working fluid flow 114 and/or the first vapor working fluid flow 124 (e.g., the combined working fluid flow 354) to direct the first pressurized working fluid flow 114 and/or the first vapor working fluid flow 124 to a third volute 382. The third compressor 350 may discharge the first pressurized working fluid flow 114 and/or the first vapor working fluid flow 124 from the third volute 382 toward the condenser 102 as the second pressurized working fluid flow 1 15 [0066] In the illustrated embodiment, the first compressor impeller 210 and the third compressor impeller 380 are coupled to different shafts. For example, the first compressor impeller 210 may be coupled to the first shaft 280 driven by the first motor 282, and the third compressor impeller 380 may be coupled to the second shaft 284 driven by the second motor 286. Therefore, operation of the motors 282, 286 may cause respective rotations of the compressors 110, 350 (e.g., rotation of the respective impellers 210, 380). In additional or alternative embodiments, the first compressor impeller 210 and the third compressor impeller 380 may be coupled to a common shaft (e.g., the shaft 214) driven by a single motor (e g., the motor 220), such as at opposite ends of the shaft and/or at a common end of the shaft. Thus, operation of the motor may cause rotation of both compressors 110, 350.

[0067] FIG. 13 is a schematic of an embodiment of the compressor system 106 having the first compressor 110 and the third compressor 350 in a series flow arrangement. In the illustrated embodiment, the first compressor 110 is positioned downstream of the third compressor 350 with respect to a flow of the working fluid through the compressor system 106. As an example, the third compressor 350 may receive the intake working fluid flow 113 from the evaporator 104 via the fifth inlet 352, pressurize the intake working fluid flow 113, and discharge the pressurized intake working fluid flow 113 toward the first compressor 110 as the first pressurized working fluid flow 114. The first compressor 110 may receive the pressurized intake working fluid flow 113 (e.g., the first pressurized working fluid flow 114) and/or the second vapor working fluid flow 126 (e.g., a combined working fluid flow 117) via the first inlet 130. The first compressor 110 may also receive the first vapor working fluid flow 124 via the second inlet 132. The first compressor 110 may pressurize the intake working fluid flow 113, the first vapor working fluid flow 124, and/or the second vapor working fluid flow 126 and discharge the pressurized working fluid flows to the condenser 102 as the second pressurized working fluid flow 115. [0068] FIG. 14 is a schematic of an embodiment of the compressor system 106 having the first compressor 110 and the third compressor 350 in a parallel flow arrangement. For example, the first compressor 110 may receive and pressurize the intake working fluid flow 113 and/or the second vapor working fluid flow 126 to provide the first pressurized working fluid flow 114. The first compressor 110 may then discharge the first pressurized working fluid flow 114 to the condenser 102 and bypass the third compressor 350. The third compressor 350 may receive and pressurize the first vapor working fluid flow 124 to discharge the pressurized first vapor working fluid flow 124 as the second pressurized working fluid flow 1 15 to the condenser 102 and bypass the first compressor 110. In additional or alternative embodiments, the third compressor 350 may receive and pressurize the intake working fluid flow 113 to discharge to the condenser 102 and bypass the first compressor 110, and the first compressor 110 may receive and pressurize the second vapor working fluid flow 126 and/or the first vapor working fluid flow 124 to discharge to the condenser 102 and bypass the third compressor 350. In any of these embodiments, the first compressor 110 and the third compressor 350 may be coupled to a common shaft or to separate shafts.

[0069] While only certain features and embodiments of the present disclosure have been illustrated and described, many modifications and changes may occur to those skilled in the art (e.g., variations in sizes, dimensions, structures, shapes and proportions of the various elements, values of parameters (e.g., temperatures, pressures, etc.), mounting arrangements, use of materials, colors, orientations, etc.) without materially departing from the novel teachings and advantages of the subject matter recited in the claims. The order or sequence of any process or method steps may be varied or resequenced according to alternative embodiments. It is, therefore, to be noted that the appended claims are intended to cover all such modifications and changes as fall within the true spirit of the present disclosure. Furthermore, in an effort to provide a concise description of the exemplary embodiments, all features of an actual implementation may not have been described (i.e., those unrelated to the presently contemplated best mode of carrying out the present disclosure, or those unrelated to enabling the claimed embodiments). It should be appreciated that in the development of any such actual implementation, as in any engineering or design project, numerous implementation specific decisions may be made. Such a development effort might be complex and time consuming, but would nevertheless be a routine undertaking of design, fabrication, and manufacture for those of ordinary skill having the benefit of this disclosure, without undue experimentation.

[0070] The techniques presented and claimed herein are referenced and applied to material objects and concrete examples of a practical nature that demonstrably improve the present technical field and, as such, are not abstract, intangible or purely theoretical. Further, if any claims appended to the end of this specification contain one or more elements designated as “means for [perform]ing [a function], ..” or “step for [perform]ing [a function]...”, it is intended that such elements are to be interpreted under 35 U.S.C. 112(f). However, for any claims containing elements designated in any other manner, it is intended that such elements are not to be interpreted under 35 U.S.C. 112(f).