Air compressor

An air compressor system is disclosed that includes a housing sized to enclose an air compressor pump as well as a dryer structured to remove moisture from air that is compressed by the compressor pump. The air compressor pump may be intermittently placed into operation, but the dryer itself is structured in one form to continuously maintain a heat exchanger in a desired temperature range in anticipation of operation of the air compressor pump. The heat exchanger of the dryer can include sufficient thermal mass such that a refrigerant pump of the dryer need not be operated continuously in anticipation of operation of the air compressor pump. While a cooling air flow can be created by operation of the air compressor pump, when the air compressor pump is not operated a cooling fan can be used provide cooling to the heat generating components of the dryer.

TECHNICAL FIELD

The present invention generally relates to air dryers for use with air compressors.

BACKGROUND

The present disclosure relates to air compressor systems and arrangements for removing moisture and other contaminates from compressed air. Compressor systems are often used to provide compressed air for powering machinery, hand, tools, and the like. Air compressors typically compress atmospheric air, which contains moisture. As a result, conventional air compressors generate what is referred to as wet compressed air, wherein the term “wet” refers to the fact that there is typically undesirable amounts of liquid water, water vapor, and other contaminants in the compressed air. Because moisture can cause damage or corrosion in machines and tools, the compressed air supplied to a point of use should be substantially dry. Accordingly, air dryers are generally provided upstream from a point of use in compressed air systems and serve to remove moisture and other contaminates from the compressed air. A refrigerated air dryer operates to remove moisture from the air by cooling the air to cause the moisture vapor in the air to condense, extracting the condensed moisture, and then reheating the air.

Some existing air dryer and air compressor systems have various shortcomings relative to certain applications. Accordingly, there remains a need for further contributions in this area of technology.

SUMMARY

One embodiment of the present invention is a unique air compressor system that includes a dryer and cooling fan. Other embodiments include apparatuses, systems, devices, hardware, methods, and combinations for maintaining temperature of a dryer heat exchanger within a range while providing sufficient cooling for operation of a refrigerant compressor. Further embodiments, forms, features, aspects, benefits, and advantages of the present application shall become apparent from the description and figures provided herewith.

DETAILED DESCRIPTION

The present application discloses various embodiments of an integrated air dryer for compressed air and methods for using and constructing the same. For the purposes of promoting an understanding of the principles of the invention, reference will now be made to the embodiments illustrated in the drawings, and specific language will be used to describe the same. It will nevertheless be understood that no limitation of the scope of the invention is thereby intended. Any alterations and further modifications in the described embodiments, and any further applications of the principles of the invention as described herein, are contemplated as would normally occur to one skilled in the art to which the invention relates having the benefit of the present disclosure.

As shown inFIG. 1, an integrated air dryer system100may include an air compressor subassembly101integrated into a single, fully enclosed assembly with an air dryer104and a refrigeration circuit102. The integrated air dryer system100enables a reliable, convenient, portable, and adaptable source of dry compressed air to be available at any point of use150in a wide range of operating conditions. The integrated air dryer system100may be enclosed in a housing170having vent portions177formed therethrough that enable a flow of ambient air into and out of the system100. The housing170may include openings176to enable fluid connection between the air dryer104within the housing170and a point of use150outside the housing170. Accordingly, ambient air may be drawn into the air compressor subassembly101via a vent portion177, pushed through the air dryer104, where the compressed air exchanges heat with the refrigeration circuit102, and then pushed out of the air dryer104to a point of use150via an opening176. The housing170may have additional openings. By way of non-limiting example, such openings may enable connection to a supply of electrical power, access to control or circuit panels, and access for maintenance of the system100. Further, the housing170may allow additional air flows through the openings to those specifically described herein.

FIG. 2shows a schematic of an integrated air dryer system100according to at least one embodiment according to the present disclosure. As shown inFIG. 2, the integrated air dryer system100may include the refrigeration circuit102in thermal communication with the air dryer104. The air dryer104may include precooling heat exchanger142, an air chiller heat exchanger118(hereinafter referred to as the “chiller118”), and a second condensate separator144fluidly connected in series by a dryer air line105to the point of use150. The air dryer104removes water vapor from the wet compressed air supplied by the air compressor subassembly101, such that the integrated air dryer system100provides dry compressed air to a point of use150. The point of use150may be a reservoir in which dry compressed air may be stored for later use. The air dryer104may include other components for monitoring and regulating the air flow as understood in the art. The integrated air dryer system100may further include the air compressor subassembly101in fluid connection with the air dryer104.

As shown inFIG. 2, the air compressor subassembly101may include an air compressor108fluidly connected to an air cooler186, which is further fluidly connected to a first condensate separator145. The first condensate separator145may be fluidly connected to the air dryer104to enable a flow of compressed air to be dried. The air compressor108includes a drive motor. The air compressor108may be a single compressor or a plurality of compressors arranged in parallel and/or series to generate a flow of compressed air at a desired flow rate and pressure. The air cooler186may be an air-to-air heat exchanger or radiator. The first condensate separator145removes liquid water that coalesces as the compressed air from the air compressor108passes through the air cooler186. Without the first condensate separator145, liquid water may enter the air dryer104, which may reduce the efficiency of the heat exchange process in the chiller118. The first condensate separator145may be further connected to a drain line107a, which is in fluid communication with a condensate drain160. The drain line107aremoves the collected liquid water and other contaminates from the air compressor subassembly101.

The air compressor subassembly101may further include a cooling fan182adjacent the air cooler186. The cooling fan182may provide a cooling flow of air across the air cooler186to cool the compressed air exiting the air compressor108and thereby facilitate condensation of water vapor out of the compressed air flow prior to the first condensate separator145and subsequently the air dryer104. The cooling fan182may be configured to operate only when the air compressor108is operating and generating a flow of compressed air through the air cooler186. The cooling flow generated by the cooling fan182may be directed across a condenser114of the refrigeration circuit102as described further herein to provide cooling flow for the refrigeration circuit102. The cooling flow generated by the cooling fan182may further provide cooling for the motor of the air compressor108.

The refrigeration circuit102may include a refrigerant loop103containing a fluid, such as a refrigerant, fluidly coupling a refrigerant compressor112, the condenser114, an expander116, and the chiller118. The refrigerant compressor112, condenser114, and expander116may be similar to components of a conventional vapor-compression refrigeration system. The chiller118acts as an evaporator in the refrigeration cycle formed by the refrigeration cycle102, transferring thermal energy as heat from the air dryer104into the refrigeration circuit102when the air compressor subassembly101is operating. The transferred heat is expelled from the refrigeration circuit102in the condenser114as part of the refrigeration cycle. When the air compressor subassembly101is not operating (e.g., due to low demand for compressed air), no compressed air flows through the chiller118and, therefore, little or no heat is transferred from the air dryer104to the refrigeration circuit102. Additional heat, referred to herein as “internal heat,” may be generated within the refrigeration circuit102itself, for instance by operation of the refrigerant compressor112, and transferred to the fluid flowing within the refrigerant loop103. This internal heat may also be expelled from the refrigeration circuit102in the condenser114as part of the refrigeration cycle.

To improve heat transfer from the condenser114, air flow may be generated over the condenser114. As noted, the cooling fan182of the air compressor subassembly101may provide such flow when the air compressor108is operating. However, the refrigeration circuit102may be operated independent of the air compressor subassembly101. Consequently, a cooling flow may be advantageous to dissipate the internal heat generated by the operation of the refrigeration circuit102itself. The refrigeration circuit102may include a condenser fan180disposed external to the refrigerant loop103, which draws ambient air across the condenser114, thereby dissipating heat from the refrigerant flowing therethrough.

As shown in one embodiment illustrated inFIG. 3, the integrated air dryer100may thus include three air flow paths, a first flow path A, a second flow path B, and a third flow path C. The first flow path A may flow into the system100from the environment, drawn by the cooling fan182, across the air cooler186, and across the condenser114. The second flow path B may flow into the system100from the environment, drawn by the condenser fan180, and across the condenser114. The third flow path C may flow from within the system100to environment, such that the third flow path C may be comprised of air flow from the first flow path A and/or the second flow path B. As will be understood by one skilled in the art having the benefit of the present disclosure, the condenser fan180and the cooling fan182may be configured to either push or draw air flows. Consequently, the position of the condenser fan180and the cooling fan182relative to the condenser114and the air cooler186(and other components of the system100), whether upstream or downstream, may be different than as depicted inFIG. 3. All such configurations are within the scope of the disclosure. For example, in alternative embodiments, the condenser fan180may direct the second flow path B directly across the refrigerant compressor112without first flowing across the condenser114, thereby providing a separate cooling effect directly to the refrigerant compressor112. Accordingly, the cooling effect resulting from the second flow path B may include convective heat transfer from the refrigerant compressor212.

In at least one embodiment of the present disclosure, the first flow path A will only be generated when the air compressor subassembly101, including the air compressor108, is operating. Similarly, the second flow path B will only be generated when the air compressor subassembly101, including the air compressor108, is not operating, but the refrigeration circuit102, including the refrigerant compressor112, is operating. The third flow path C may be generated under either condition. By using the first flow path A to provide cooling to both the air cooler186and the refrigeration circuit102, via the condenser114, the heat transfer processes within the integrated air dryer system100may be improved while consuming less power.

In at least one embodiment, a flow capacity of the condenser fan180may be selected such that the resulting cooling effect across the condenser114is large enough to dissipate heat generated in the refrigerant compressor112under conditions when the air compressor subassembly101is not operating and no compressed air flows through the air dryer104. Conversely, the flow capacity of the condenser fan180need not be so large as to provide the cooling required to adequately dissipate heat transferred to the refrigeration circuit102from the air dryer104when the air compressor108is operating because this degree of cooling may be generated solely by the cooling fan182of the air compressor subassembly101. Consequently, the condenser fan180may have relatively low flow capacity, power consumption, and cost compared to the cooling and/or condenser fans of conventional integrated air dryers. Thus, the condenser fan180may mitigate the risk of the refrigerant compressor112overheating while consuming less electrical power and being less costly than a conventional air dryer cooling fans.

In operation when the air compressor subassembly101is operating, the air compressor subassembly101introduces relatively wet compressed air at a first temperature TAinto the dryer air line105of the air dryer104. The wet compressed air passes through precooling heat exchanger142via a precooling path142a, expels heat to a reheating path142bwithin the precooling heat exchanger142, and is cooled to a second temperature TBlower than the first temperature TA, at which point some water may begin to condense from vapor to liquid. The wet compressed air then flows through the chiller118via an air path118a, expels heat to a refrigerant path118b, which is a portion of the refrigeration cycle102, and is cooled to a third temperature TCbelow the second temperature TBsuch that water further condenses from vapor to liquid. The wet compressed air then flows through the second condensate separator144where the condensed liquid water is separated to yield dry compressed air. The dry compressed air then flows through the reheating path142bof the precooling heat exchanger142, where heat is exchanged with the incoming wet compressed air in the precooling path142aand is heated to a fourth temperature TDhigher than the third temperature TC. Raising the temperature of the dry compressed air to the fourth temperature TDinhibits the formation of condensation on the outside of downstream plumbing. Downstream of the precooling heat exchanger142, the dry compressed air at the fourth temperature D is available at the point of use150.

The second condensate separator144may include a drain line107b, which is in fluid communication with the condensate drain160, including one or more one-way valves164and a strainer166. The second condensate separator144may separate liquid water from the compressed air by vortex action. Alternatively, the second condensate separator144may use coalescing action or another method to remove liquid from the compressed air, such as by having the air flow through a demister pad. The drain line107removes the collected liquid water and other contaminates from the system100. Other condensate separators are known and may be used, as desired.

In a conventional air dryer, when the air compressor is not active and no compressed air is flowing through the evaporator, the refrigerant in the refrigeration cycle may become exceedingly cold due to the lack of heat transfer from the air dryer. Under conditions when the air compressor is not operating and no compressed air flows through the evaporator, continued operation of the refrigeration cycle may result in refrigerant temperatures below the freezing point of water and the formation of ice within the evaporator, which may damage the system, causing blockages, rupture of the evaporator, and/or inefficient heat transfer. Ice may form particularly when a conventional integrated air dryer system is operated at low ambient temperatures, making evaporator operation below the freezing point more likely. Though the formation of ice in the system may be mitigated by cycling the refrigerant compressor on and off based on demands for compressed air, and subsequent operation of the air compressor, frequent cycling without cooling air flow can cause excessive over-heating and potentially premature failure of refrigerant compressor. Unlike such conventional air dryers, the integrated air dryer system100prevents operation below the freezing point, and thereby the formation of ice, and further reduces the need to cycle the refrigerant compressor112frequently, thereby preventing over-heating.

According to at least one embodiment of the present disclosure, the chiller118includes greater thermal capacitance than a conventional chiller/evaporator. The chiller118includes two thermal capacitances (in some embodiments, the chiller118may include more or fewer thermal capacitances), a wall thermal capacitance and a storage thermal capacitance. The wall thermal capacitance includes the thermal capacitance inherent in the mass of the chiller118, including the walls defining the air path118a, the refrigerant path118b, and the surrounding structure needed to give the chiller118structural integrity. The storage thermal capacitance of the chiller118includes additional mass selected to provide a predetermined thermal capacity. The predetermined thermal capacity may be determine from the design and operational parameters of the system100. Such parameters may include the anticipated flow rates through the refrigeration circuit102and the air dryer104, the wall thermal capacitance of the chiller118sized to enable sufficient heat transfer at the given flow rates, the anticipated ambient conditions in which the system will operate, the anticipated duty cycle of the air circuit, and the desired duty cycle of the refrigerant compressor. Accordingly, the storage thermal capacitance of the chiller118may be engineered to provide sufficient cooling of the wet compressed air flowing through the chiller118for a predetermine period of time under conditions when the refrigerant compressor112is not operating.

In at least one embodiment, the chiller118may include one of more plates190disposed adjacent the air path118aand the refrigerant path118b, as shown inFIG. 4. The plates190may be selected to provide a predetermined storage thermal capacitance that enables the refrigerant compressor112to operate less frequently, whereby the storage thermal capacitance may enable cooling for a predetermined period of time. The plates190may be a material with a high thermal capacitance, including but not limited to a ceramic or a metal, such as aluminum. Alternatively, the walls defining the air path118aand the refrigerant path118bwithin the chiller118may be thicker than conventional heat exchangers, thereby increasing the thermal capacitance of the chiller118. The walls defining the fluid flow paths of a conventional heat exchanger may have a thickness sufficient to give the heat exchanger adequate structural integrity, where such a wall thickness provides a conventional wall thermal capacitance. In contrast, the walls defining the air path118aand the refrigerant path118bwithin the chiller118may be thicker than required for the structural integrity of the chiller, such that the additional wall thickness beyond that needed for structural integrity (i.e., the conventional wall thermal capacitance) defines an additional predetermined storage thermal capacitance. Consequently, the increased storage thermal capacitance of the chiller118enables the refrigeration circuit102to cool the compressed air flowing through the air dryer104without frequently cycling the refrigerant compressor112.

For example, in operation the refrigerant compressor112may be activated and the refrigeration circuit102may operate until the temperature of the chiller118reaches a low temperature limit TL. Upon reaching the low temperature limit TL, the refrigerant compressor112may be switched off, but the chiller118continues to cool the compressed air in the air dryer104as heat is transferred to the relatively cool storage thermal capacitance of the chiller118. With the refrigerant compressor112switched off, the temperature of the chiller118gradually rises until it reaches a high temperature limit TH. Moreover, if the air compressor108is switched off and compressed air is not flowing through the chiller118, the temperature of the chiller118may rise more gradually, thereby further delaying the need to cycle on the refrigerant compressor112. Once the chiller118reaches the high temperature limit TH, the refrigerant compressor112is switched on and operates until the temperature of the chiller118reaches the low temperature limit TLagain.

In at least one embodiment, the low temperature limit TLmay be about 2° C., and the high temperature limit THmay be about 5° C. Accordingly, the temperature of the chiller118does not reach the freezing point, and ice formation may be prevented. Alternatively, the low and high temperature limits TL, THmay be selected in concert with the predetermined storage thermal capacitance of the chiller118to ensure that the refrigerant compressor112is not cycled on and off too frequently, which can lead to overheating and potentially failure of the refrigerant compressor112. For example, excessive temperatures in the refrigerant compressor motor windings may cause electrical failures as insulation within the compressor brings to breakdown or mechanical failures as lubricants begin to breakdown at elevated temperature. To protect against overheating, a predetermined safety limit may be set for the temperature of the refrigerant compressor112, such that the safety limit is less than a failure temperature for the refrigerant compressor112. Accordingly, the low and high temperature limits TL, THand the predetermined storage thermal capacitance of the chiller118may be selected to ensure the refrigerant compressor112operates below the safety limit. In at least one alternative embodiment, the low and high temperature limits TL, THand the storage thermal capacitance of the chiller118may be selected to ensure that the refrigerant compressor112cycles no more frequently than once every 6 minutes or 10 cycles per hour. Consequently, the refrigerant compressor112and the refrigeration circuit102may operate independently of the air dryer104, and the duty cycle of the refrigerant compressor112may be reduced accordingly.

As shown inFIG. 2, the integrated air dryer system100may include a controller130capable of operating upon a change in temperature, the controller130in communication with the chiller118. In some embodiments the controller130can be an analog device that senses temperature and provides a switching function, such as switching an electrical device on and off. In at least one embodiment, the controller130may he a thermostatic switch. In at least one embodiment, the thermostatic switch may respond to changes in temperature with a hysteresis response. In such an embodiment, the thermostatic switch may include hysteresis about a center point temperature to enable the low and high temperature limits TL, TH. In certain embodiments, the system100may include a temperature sensor (not shown) in thermal communication with the chiller118and in communication with a controller130. The controller130may monitor the output of the temperature sensor and activate or deactivate the refrigerant compressor112according to the low and high temperature limits TL, THas described herein. The controller130may comprise digital circuitry, analog circuitry, or a hybrid combination of both of these types. Also, the controller130can be programmable, an integrated state machine, or a hybrid combination thereof. The controller130can include one or more Arithmetic Logic Units (ALUs), Central Processing Units (CPUs), memories, limiters, conditioners, filters, format converters, or the like which are not shown to preserve clarity. In one form, the controller130is of a programmable variety that executes algorithms and processes data in accordance with operating logic that is defined by programming instructions (such as software or firmware). Alternatively or additionally, operating logic for the controller130can be at least partially defined by hardwired logic or other hardware. It should be appreciated that controller130can be exclusively dedicated to monitor the temperature of the chiller118or may further be used in the regulation/control/activation of one or more other subsystems or aspects of the integrated air dryer system100.

The temperature sensor may be any suitable type of sensor that enables communication with the controller130and control of the refrigerant compressor112, including but not limited to a thermocouple, a resistive temperature device (RTD), a thermistor, an infrared radiator, a bimetallic device, a liquid expansion device, a molecular change-of-state device, and a silicon diode. In at least one embodiment, the functions of the temperature sensor and controller130may be performed by a thermostatic switch.

As shown inFIG. 5, the refrigeration circuit102and the air dryer104may packaged as an air dryer subassembly200to facilitate integration with the air compressor subassembly101and incorporation into the integrated air dryer system100. The air dryer subassembly200may include a base172upon which the refrigeration circuit102and the air dryer104are disposed. The base172may be configured to support the weight of the air dryer subassembly200and facilitate integration with the air compressor subassembly101. The base172may be made of any suitable material, including but not limited to metal, such as steel. To reduce the space, and thus cost, required to package the air dryer subassembly200into the integrated air dryer system100, the chiller118, the precooling heat exchanger142, and the second condensate separator144may be arranged in an interconnected exchanger subassembly140as shown inFIGS. 5 and 6. The exchanger subassembly140may include an inlet air connection fitting146, an outlet air connection fitting148, and a precooler manifold147, each in fluid communication with the precooling heat exchanger142of the air dryer104. The exchanger subassembly140may further include an inlet refrigerant connection fitting136, an outlet refrigerant connection fitting138, and a chiller manifold137, each in fluid communication with the chiller118of the refrigeration circuit102.

Referring toFIG. 2, the refrigeration circuit102may include a refrigerant dryer120disposed between the condenser114and the expander116and configured to remove contaminants, such as water, from the refrigerant. The refrigeration circuit102may further include a pressure relief valve122operatively coupled to a pressure relief line123and the refrigerant compressor112, and a hot gas bypass valve124operatively coupled to a bypass line125, though one or more of these components may be omitted in certain embodiments. The pressure relief valve122and the pressure relief line123may selectively fluidly couple a compression chamber of the refrigerant compressor112to the refrigerant loop103downstream of the condenser114. The pressure relief valve122may prevent damage to the refrigerant compressor112and other components of the refrigeration circuit102due to over-pressurization by opening when the pressure of the refrigerant in the pressure relief line123reaches a threshold value. The hot gas bypass valve124may facilitate control of the pressure within the chiller118via a pressure equalization line127under partial flow operation at moderate and high ambient temperature conditions. Whether a given embodiment includes the hot gas bypass valve124may be determined by the selected thermal capacitance of the chiller118and the low and high temperature limits.

In one aspect of the present disclosure, the integrated air dryer system100may be used in a method300to prevent both the formation of ice within the refrigeration circuit102and over-heating of the refrigerant compressor112as shown inFIG. 7. The method300may include a step310of monitoring a temperature of the chiller118. The method300may include the step320of switching on the refrigerant compressor112when the temperature of the chiller118rises above the prescribed high temperature limit TH. The method300may further include the step330of switching off the refrigerant compressor112when the temperature of the chiller118falls below the prescribed low temperature limit TL. The method300may further include the step340of switching on the condenser fan180under conditions when the refrigerant compressor112is switched on and the air compressor108is switched off, whether due to sufficient pressure in the dryer air line105or otherwise. In at least one embodiment of the method300, the steps310,320,330, or340may be repeated as necessary to monitor and control the system100as described herein.

FIG. 8shows an alternative embodiment of an integrated air dryer system300. As shown inFIG. 8, the integrated air dryer system300may be position on a stable surface1and enclosed by the housing170. The housing170includes openings, which may provide inlets and/or outlets, that enable the flow of ambient air into and out of the system300. The integrated air dryer system300may include the air compressor108, which is driven by a compressor motor109, disposed near the stable surface1and near an opening disposed near the bottom of the housing170adjacent the air compressor108to enable a supply of air to be compressed by the air compressor108. The integrated air dryer system300may include the air dryer subassembly200, including the condenser114, disposed at or near an opening through another side of the housing170, thereby enabling the first flow path A into the housing170and through the air dryer subassembly200. The integrated air dryer system300may further include cooling fan182positioned at or near the top of the housing170adjacent an opening that enables the third flow path C through the air cooler186and out of the housing170. The system300may include a shroud184disposed between the cooling fan182and the air cooler186to funnel the third flow path C from the cooling fan182through the air cooler186. The first flow path A and the third flow path C may be generated by the cooling fan182and/or the condenser fan180of the air dryer subassembly200. As shown inFIG. 8, the system300may include a compressed air line152through which compressed air flows through the system300. The compressed air line152connects an output of the air compressor108to the air cooler186to the exchanger subassembly140of the air dryer subassembly200to a point of use150outside of the housing170via an opening.

In operation, the air compressor subassembly101of the integrated air dryer system100may be intermittently activated as needed to provide the desired supply or flow of compressed air. Though packaged together within the housing170and thermally connected via the chiller118, the refrigeration circuit102may operate independent of the air compressor subassembly101. The controller130may monitor the temperature of the chiller118, whereby the refrigeration circuit102, and specifically the refrigerant compressor112, may be activated to maintain the chiller118in a desired temperature range in anticipation of operation of the air compressor subassembly101. The chiller118may include sufficient thermal mass such that the refrigerant compressor112need not be operated continuously or frequently in anticipation of operation of the air compressor108. While a cooling air flow across the refrigeration circuit102can be created by operation of the air compressor subassembly101, and specifically the cooling fan182, when the air compressor subassembly101is not operated the condenser fan180can be used to provide cooling to the internal heat generating components of the refrigeration circuit102, including the refrigerant compressor112. Consequently, the condenser fan180may be sized to provide only enough cooling to dissipate such internal heat. Thus, some embodiments of the integrated air dryer100may include both the chiller118having sufficient thermal mass such that the refrigerant compressor112need not be operated continuously or frequently in anticipation of operation of the air compressor108and having the condenser fan180, which can be used to provide cooling to the internal heat generating components of the refrigeration circuit102under conditions when the air compressor subassembly101is not operating.

As will be understood by one skilled in the art having the benefit of the present disclosure, the terms used to identify the components of the integrated air dryer systems disclosed herein may be similarly described by other terms unless explicitly provided to the contrary. For example, the integrated air dryer system100may be referred to as an air compressor unit, the air dryer subassembly200may be referred to as an integrated air dryer or, simply, a dryer, the housing170may be referred to as an air compressor unit enclosure, the air cooler186may be referred to as a compressor cooler. Such difference in terms does not alter the structure or operation of the integrated air dryer system.

Further, in describing representative embodiments, the disclosure may have presented a method and/or process as a particular sequence of steps. However, to the extent that the method or process does not rely on the particular order of steps set forth herein, the method or process should not be limited to the particular sequence of steps described. Other sequences of steps may be possible and are therefore contemplated by the inventor. Therefore, the particular order of the steps disclosed herein should not be construed as limitations of the present disclosure. Such sequences may be varied and still remain within the scope of the present disclosure.