Patent Application
20180106500
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Heating, ventilation, and/or air conditioning (HVAC) systems used in commercial and residential applications often include a heat exchanger configured to promote heat transfer with a fluid carried within the heat exchanger and a fluid and/or airflow that contacts the heat exchanger to provide heating, cooling, and/or otherwise condition interior spaces. Because the amount of heat transfer between fluids affects overall system performance and efficiency, many heat exchangers are often designed for maximum heat transfer efficiency. Additionally, because heat exchangers are becoming more compact and less expensive, attempting to maximize heat transfer in a heat exchanger while reducing the size of a heat exchanger may often produce an undesirable pressure drop across the heat exchanger.
In some embodiments of the disclosure, a heat exchanger is disclosed as comprising: at least one heat exchanger tube, comprising: a first pass; a second pass; a third pass; and a fourth pass; wherein at least a portion of each of the second pass, the third pass, and the fourth pass comprises an elliptical portion.
In other embodiments of the disclosure, an HVAC system is disclosed as comprising: at least one heat exchanger tube, comprising: a first pass; a second pass; a third pass; and a fourth pass; wherein at least a portion of each of the second pass, the third pass, and the fourth pass comprises an elliptical portion.
In yet other embodiments of the disclosure, a method of producing a fin and tube heat exchanger is disclosed as comprising: providing at least one heat exchanger tube in a heat exchanger of the HVAC system, the at least one heat exchanger tube comprising a first pass, a second pass, a third pass, and a fourth pass, wherein at least a portion of each of the second pass, the third pass, and the fourth pass comprises an elliptical portion, and wherein at least one pass comprises a plurality of ribs; generating an airflow; contacting the at least one heat exchanger tube with the airflow; and promoting heat transfer between a fluid passing through an internal passage of the at least one heat exchanger tube and the airflow.
For a more complete understanding of the present disclosure and the advantages thereof, reference is now made to the following brief description, taken in connection with the accompanying drawings and detailed description:
Referring now to
Indoor unit 102 comprises an indoor heat exchanger 108, an indoor fan 110, and an indoor metering device 112. Indoor heat exchanger 108 is a plate fin heat exchanger configured to allow heat exchange between refrigerant carried within internal tubing of the indoor heat exchanger 108 and fluids that contact the indoor heat exchanger 108 but that are kept segregated from the refrigerant. In other embodiments, indoor heat exchanger 108 may comprise a spine fin heat exchanger, a microchannel heat exchanger, or any other suitable type of heat exchanger.
The indoor fan 110 is a centrifugal blower comprising a blower housing, a blower impeller at least partially disposed within the blower housing, and a blower motor configured to selectively rotate the blower impeller. In other embodiments, the indoor fan 110 may comprise a mixed-flow fan and/or any other suitable type of fan. The indoor fan 110 is configured as a modulating and/or variable speed fan capable of being operated at many speeds over one or more ranges of speeds. In other embodiments, the indoor fan 110 may be configured as a multiple speed fan capable of being operated at a plurality of operating speeds by selectively electrically powering different ones of multiple electromagnetic windings of a motor of the indoor fan 110. In yet other embodiments, the indoor fan 110 may be a single speed fan.
The indoor metering device 112 is an electronically controlled motor driven electronic expansion valve (EEV). In alternative embodiments, the indoor metering device 112 may comprise a thermostatic expansion valve, a capillary tube assembly, and/or any other suitable metering device. The indoor metering device 112 may comprise and/or be associated with a refrigerant check valve and/or refrigerant bypass for use when a direction of refrigerant flow through the indoor metering device 112 is such that the indoor metering device 112 is not intended to meter or otherwise substantially restrict flow of the refrigerant through the indoor metering device 112.
Outdoor unit 104 comprises an outdoor heat exchanger 114, a compressor 116, an outdoor fan 118, an outdoor metering device 120, and a reversing valve 122. Outdoor heat exchanger 114 is a spine fin heat exchanger configured to allow heat exchange between refrigerant carried within internal passages of the outdoor heat exchanger 114 and fluids that contact the outdoor heat exchanger 114 but that are kept segregated from the refrigerant. In other embodiments, outdoor heat exchanger 114 may comprise a plate fin heat exchanger, a microchannel heat exchanger, or any other suitable type of heat exchanger.
The compressor 116 is a multiple speed scroll type compressor configured to selectively pump refrigerant at a plurality of mass flow rates. In alternative embodiments, the compressor 116 may comprise a modulating compressor capable of operation over one or more speed ranges, the compressor 116 may comprise a reciprocating type compressor, the compressor 116 may be a single speed compressor, and/or the compressor 116 may comprise any other suitable refrigerant compressor and/or refrigerant pump.
The outdoor fan 118 is an axial fan comprising a fan blade assembly and fan motor configured to selectively rotate the fan blade assembly. In other embodiments, the outdoor fan 118 may comprise a mixed-flow fan, a centrifugal blower, and/or any other suitable type of fan and/or blower. The outdoor fan 118 is configured as a modulating and/or variable speed fan capable of being operated at many speeds over one or more ranges of speeds. In other embodiments, the outdoor fan 118 may be configured as a multiple speed fan capable of being operated at a plurality of operating speeds by selectively electrically powering different ones of multiple electromagnetic windings of a motor of the outdoor fan 118. In yet other embodiments, the outdoor fan 118 may be a single speed fan.
The outdoor metering device 120 is a thermostatic expansion valve. In alternative embodiments, the outdoor metering device 120 may comprise an electronically controlled motor driven EEV, a capillary tube assembly, and/or any other suitable metering device. The outdoor metering device 120 may comprise and/or be associated with a refrigerant check valve and/or refrigerant bypass for use when a direction of refrigerant flow through the outdoor metering device 120 is such that the outdoor metering device 120 is not intended to meter or otherwise substantially restrict flow of the refrigerant through the outdoor metering device 120.
The reversing valve 122 is a so-called four-way reversing valve. The reversing valve 122 may be selectively controlled to alter a flowpath of refrigerant in the HVAC system 100 as described in greater detail below. The reversing valve 122 may comprise an electrical solenoid or other device configured to selectively move a component of the reversing valve 122 between operational positions.
The system controller 106 may comprise a touchscreen interface for displaying information and for receiving user inputs. The system controller 106 may display information related to the operation of the HVAC system 100 and may receive user inputs related to operation of the HVAC system 100. However, the system controller 106 may further be operable to display information and receive user inputs tangentially and/or unrelated to operation of the HVAC system 100. In some embodiments, the system controller 106 may comprise a temperature sensor and may further be configured to control heating and/or cooling of zones associated with the HVAC system 100. In some embodiments, the system controller 106 may be configured as a thermostat for controlling supply of conditioned air to zones associated with the HVAC system 100.
In some embodiments, the system controller 106 may selectively communicate with an indoor controller 124 of the indoor unit 102, with an outdoor controller 126 of the outdoor unit 104, and/or with other components of the HVAC system 100. In some embodiments, the system controller 106 may be configured for selective bidirectional communication over a communication bus 128. In some embodiments, portions of the communication bus 128 may comprise a three-wire connection suitable for communicating messages between the system controller 106 and one or more of the HVAC system 100 components configured for interfacing with the communication bus 128. Still further, the system controller 106 may be configured to selectively communicate with HVAC system 100 components and/or other device 130 via a communication network 132. In some embodiments, the communication network 132 may comprise a telephone network and the other device 130 may comprise a telephone. In some embodiments, the communication network 132 may comprise the Internet and the other device 130 may comprise a so-called smartphone and/or other Internet enabled mobile telecommunication device.
The indoor controller 124 may be carried by the indoor unit 102 and may be configured to receive information inputs, transmit information outputs, and otherwise communicate with the system controller 106, the outdoor controller 126, and/or any other device via the communication bus 128 and/or any other suitable medium of communication. In some embodiments, the indoor controller 124 may be configured to communicate with an indoor personality module 134, receive information related to a speed of the indoor fan 110, transmit a control output to an electric heat relay, transmit information regarding an indoor fan 110 volumetric flow-rate, communicate with and/or otherwise affect control over an air cleaner 136, and communicate with an indoor EEV controller 138. In some embodiments, the indoor controller 124 may be configured to communicate with an indoor fan controller 142 and/or otherwise affect control over operation of the indoor fan 110. In some embodiments, the indoor personality module 134, or any other suitable information storage device, may comprise information related to the identification and/or operation of the indoor unit 102 and/or a position of the outdoor metering device 120.
In some embodiments, the indoor EEV controller 138 may be configured to receive information regarding temperatures and pressures of the refrigerant in the indoor unit 102. More specifically, the indoor EEV controller 138 may be configured to receive information regarding temperatures and pressures of refrigerant entering, exiting, and/or within the indoor heat exchanger 108. Further, the indoor EEV controller 138 may be configured to communicate with the indoor metering device 112 and/or otherwise affect control over the indoor metering device 112.
The outdoor controller 126 may be carried by the outdoor unit 104 and may be configured to receive information inputs, transmit information outputs, and otherwise communicate with the system controller 106, the indoor controller 124, and/or any other device via the communication bus 128 and/or any other suitable medium of communication. In some embodiments, the outdoor controller 126 may be configured to communicate with an outdoor personality module 140 that may comprise information related to the identification and/or operation of the outdoor unit 104. In some embodiments, the outdoor controller 126 may be configured to receive information related to an ambient temperature associated with the outdoor unit 104, information related to a temperature of the outdoor heat exchanger 114, and/or information related to refrigerant temperatures and/or pressures of refrigerant entering, exiting, and/or within the outdoor heat exchanger 114 and/or the compressor 116. In some embodiments, the outdoor controller 126 may be configured to transmit information related to monitoring, communicating with, and/or otherwise affecting control over the outdoor fan 118, a compressor sump heater, a solenoid of the reversing valve 122, a relay associated with adjusting and/or monitoring a refrigerant charge of the HVAC system 100, a position of the indoor metering device 112, and/or a position of the outdoor metering device 120. The outdoor controller 126 may further be configured to communicate with a compressor drive controller 144 that is configured to electrically power and/or control the compressor 116.
The HVAC system 100 is shown configured for operating in a so-called cooling mode in which heat is absorbed by refrigerant at the indoor heat exchanger 108 and heat is rejected from the refrigerant at the outdoor heat exchanger 114. In some embodiments, the compressor 116 may be operated to compress refrigerant and pump the relatively high temperature and high pressure compressed refrigerant from the compressor 116 to the outdoor heat exchanger 114 through the reversing valve 122 and to the outdoor heat exchanger 114. As the refrigerant is passed through the outdoor heat exchanger 114, the outdoor fan 118 may be operated to move air into contact with the outdoor heat exchanger 114, thereby transferring heat from the refrigerant to the air surrounding the outdoor heat exchanger 114. The refrigerant may primarily comprise liquid phase refrigerant and the refrigerant may be pumped from the outdoor heat exchanger 114 to the indoor metering device 112 through and/or around the outdoor metering device 120 which does not substantially impede flow of the refrigerant in the cooling mode. The indoor metering device 112 may meter passage of the refrigerant through the indoor metering device 112 so that the refrigerant downstream of the indoor metering device 112 is at a lower pressure than the refrigerant upstream of the indoor metering device 112. The pressure differential across the indoor metering device 112 allows the refrigerant downstream of the indoor metering device 112 to expand and/or at least partially convert to a gaseous phase. The gaseous phase refrigerant may enter the indoor heat exchanger 108. As the refrigerant is passed through the indoor heat exchanger 108, the indoor fan 110 may be operated to move air into contact with the indoor heat exchanger 108, thereby transferring heat to the refrigerant from the air surrounding the indoor heat exchanger 108. The refrigerant may thereafter reenter the compressor 116 after passing through the reversing valve 122.
To operate the HVAC system 100 in the so-called heating mode, the reversing valve 122 may be controlled to alter the flowpath of the refrigerant, the indoor metering device 112 may be disabled and/or bypassed, and the outdoor metering device 120 may be enabled. In the heating mode, refrigerant may flow from the compressor 116 to the indoor heat exchanger 108 through the reversing valve 122, the refrigerant may be substantially unaffected by the indoor metering device 112, the refrigerant may experience a pressure differential across the outdoor metering device 120, the refrigerant may pass through the outdoor heat exchanger 114, and the refrigerant may reenter the compressor 116 after passing through the reversing valve 122. Most generally, operation of the HVAC system 100 in the heating mode reverses the roles of the indoor heat exchanger 108 and the outdoor heat exchanger 114 as compared to their operation in the cooling mode.
Referring now to
In addition to the components of HVAC system 100 described above, in this embodiment, each HVAC system 100 further comprises a ventilator 146, a prefilter 148, a humidifier 150, and a bypass duct 152. The ventilator 146 may be operated to selectively exhaust circulating air to the environment and/or introduce environmental air into the circulating air. The prefilter 148 may generally comprise a filter media selected to catch and/or retain relatively large particulate matter prior to air exiting the prefilter 148 and entering the air cleaner 136. The humidifier 150 may be operated to adjust a humidity of the circulating air. The bypass duct 152 may be utilized to regulate air pressures within the ducts that form the circulating air flowpaths. In some embodiments, air flow through the bypass duct 152 may be regulated by a bypass damper 154 while air flow delivered to the zones 226, 228, 230, 232, 234, and 236 may be regulated by zone dampers 156.
Still further, each HVAC system 100 may further comprise a zone thermostat 158 and a zone sensor 160. In some embodiments, a zone thermostat 158 may communicate with the system controller 106 and may allow a user to control a temperature, humidity, and/or other environmental setting for the zone in which the zone thermostat 158 is located. Further, the zone thermostat 158 may communicate with the system controller 106 to provide temperature, humidity, and/or other environmental feedback regarding the zone in which the zone thermostat 158 is located. In some embodiments, a zone sensor 160 may communicate with the system controller 106 to provide temperature, humidity, and/or other environmental feedback regarding the zone in which the zone sensor 160 is located.
While HVAC systems 100 are shown as a so-called split system comprising an indoor unit 102 located separately from the outdoor unit 104, alternative embodiments of an HVAC system 100 may comprise a so-called package system in which one or more of the components of the indoor unit 102 and one or more of the components of the outdoor unit 104 are carried together in a common housing or package. The HVAC system 100 is shown as a so-called ducted system where the indoor unit 102 is located remote from the conditioned zones, thereby requiring air ducts to route the circulating air. However, in alternative embodiments, an HVAC system 100 may be configured as a non-ducted system in which the indoor unit 102 and/or multiple indoor units 102 associated with an outdoor unit 104 is located substantially in the space and/or zone to be conditioned by the respective indoor units 102, thereby not requiring air ducts to route the air conditioned by the indoor units 102.
Furthermore, the system controllers 106 may be configured for bidirectional communication with each other and may further be configured so that a user may, using any of the system controllers 106, monitor and/or control any of the HVAC system 100 components regardless of which zones the components may be associated. Further, each system controller 106, each zone thermostat 158, and each zone sensor 160 may comprise a humidity sensor. As such, it will be appreciated that structure 250 is equipped with a plurality of humidity sensors in a plurality of different locations. In some embodiments, a user may effectively select which of the plurality of humidity sensors is used to control operation of one or more of the HVAC systems 100. In some embodiments, the HVAC systems 100 may further comprise a furnace 170 configured to burn fuel such as, but not limited to, natural gas, heating oil, propane, and/or any other suitable fuel, to generate heat and/or provide heated air to at least one zone 226, 228, 230, 232, 234, 236 conditioned by an HVAC system 100.
Referring now to
In operation, at least one burner of the burner box 174 may be configured to receive and combust an air-fuel mixture. In some cases, additional burners may be utilized to increase an overall heating capacity. The one or more heat exchanger tubes 177 of the primary heat exchanger 176 may be configured to receive hot gases produced by at least partially combusting the air-fuel mixture from the burner box 174 and/or each of the burners associated with the burner box 174. In some embodiments, each heat exchanger tube 177 may receive the hot gases produced by at least partially combusting the air-fuel mixture from an associated and/or dedicated burner of the burner box 174, so that multiple parallel air-fuel mixture flow paths may be formed through the heat exchanger tubes 177 of the primary heat exchanger 176. However, in other embodiments, the burners may feed at least one manifold configured to distribute the hot gases to a plurality of heat exchanger tubes 177 of the primary heat exchanger 176. Further, the flow of the hot gases produced from at least partially combusting the air-fuel mixture may be provided by the draft inducer system 184 before ejecting the hot gases through the exhaust 186.
In some embodiments, each heat exchanger tube 177 of the primary heat exchanger 176 may comprise a plurality of U-shaped bends, so that each heat exchanger tube 177 passes multiple times across an interior space 188 of the furnace 170. The interior space 188 of the furnace 170 may be configured to receive an incoming airflow 190 generated by a blower of the furnace 170 and/or the indoor fan 110 of the indoor unit 102 of
Referring now to
The first pass 202 generally comprises a substantially straight, round tube that extends from the inlet 201 to the first bend 203. The first pass 202 also generally comprises no additional enhancements and/or features on the tube surface that are configured to enhance heat transfer. In some embodiments, providing no enhancements and/or features to the substantially round tube may substantially reduce the likelihood of and/or altogether prevent flame impingement. The first bend 203, the second bend 205, and the third bend 207 also generally comprise substantially round tubes that are bent (i.e. via a mandrel and/or other tubing bending apparatus) to form 180 degree U-shaped bends. Each of the bends 203, 205, 207 further comprises no additional enhancements and/or features on the tube surface that are configured to enhance heat transfer. However, in some embodiments, the process of forming the bends 203, 205, 207 may result in a series of crimps, ripples, and/or consecutively compressed sections on an inner portion of the bends 203, 205, 207 that may provide enhanced heat transfer properties as compared to substantially smooth bends 203, 205, 207 having no crimps, ripples, and/or consecutively compressed sections.
However, each of the second pass 204, the third pass 206, and the fourth pass 208 may comprise features that further enhance heat transfer. Each of the second pass 204, the third pass 206, and the fourth pass 208 comprises an elliptical portion 210, a transition 209 disposed at each end of the elliptical portion 210, and a plurality of ribs 212. Each of the transitions 209 comprises a portion of a pass 204, 206, 208 that comprises a round shape on a first end and gradually and/or progressively transitions to an elliptical shape complementary to and/or substantially similar to the elliptical portions 210 on a second end that is adjacent to and/or abuts the elliptical portions 210 of each pass 204, 206, 208. Accordingly, the transitions 209 of the second pass 204 comprise a complementary elliptical shape on the ends of the transitions 209 adjacent to the elliptical portion 210 of the second pass 204 and gradually transition to a complementary round shape at the ends adjacent to the bends 203, 205. The transitions 209 of the third pass 206 comprise a complementary elliptical shape on the ends of the transitions 209 adjacent to the elliptical portion 210 of the third pass 206 and comprise a complementary round shape at the ends adjacent to the bends 205, 207. Additionally, the transitions 209 of the fourth pass 208 comprise a complementary elliptical shape on the ends of the transitions 209 adjacent to the elliptical portion 210 of the fourth pass 208 and comprise a complementary round shape at the ends adjacent to the third bend 207 and the outlet 211.
The elliptical portions 210 of each of the passes 204, 206, 208 generally comprise a longitudinal axis 214 and a lateral axis 216. The longitudinal axis 214 may be associated with a major (larger) diameter of the elliptical portions 210, while the lateral axis 216 may be associated with a minor (smaller) diameter of the elliptical portions 210. Accordingly, the geometries of the elliptical portions 210 may be parameterized by comprising a major diameter and a minor diameter, caused by a so-called “flattening” of the original round shape of the passes 204, 206, 208. As such, in some embodiments, the elliptical portions 210 may comprise at least about a 10% reduction of the minor diameter along the lateral axis 216 as compared to the original diameter of the round tube. However, in other embodiments, the elliptical portions 210 may comprise at least about a 15% reduction, at least about a 20% reduction, at least about a 25% reduction, at least about a 30% reduction, at least about a 33% reduction, at least about a 35% reduction, at least about a 40% reduction, and/or at least about a 50% of the minor diameter. For example, a round heat exchanger tube having a 1.5 inch diameter may comprise a 2.0 inch major diameter along the longitudinal axis 214 and a 1.0 inch minor diameter along the lateral axis 216. Accordingly, the reduction in minor diameter is (1−(1.0/1.5))×100=33% reduction in minor diameter.
In some embodiments, the longitudinal axis 214 may be aligned with a primary direction of the incoming airflow 190. The elliptical portions 210 of the second pass 204 and the third pass 206 may not overlap in a downstream direction with respect to the primary direction of the incoming airflow 190. Additionally, the elliptical portions 210 of the third pass 206 and the fourth pass 208 may not overlap in a downstream direction with respect to the primary direction of the incoming airflow 190, which may also reduce a pressure drop across the passes 202, 204, 206, 208 of the heat exchanger tube 200. However, in some embodiments, the passes 204, 206, 208 may partially overlap in a downstream direction with respect to the primary direction of the incoming airflow 190. Additionally, by reducing the minor diameter of the elliptical portions 210 along the lateral axis 216, the elliptical portion 210 may provide less resistance to the incoming airflow 190. As such, the incoming airflow 190 may experience a reduced pressure drop as compared to a round tube. In some embodiments, each elliptical portion 210 of the passes 204, 206, 208 may comprise substantially similar reductions in minor diameter. However, in alternative embodiments, each elliptical portion 210 of the passes 204, 206, 208 may comprise substantially different reductions in minor diameter.
In this embodiment, the elliptical portion 210 of the third pass 206 and the fourth pass 208 may comprise a substantially similar reductions in the minor diameter, and the third pass 206 and the fourth pass 208 may comprise a greater reduction in their minor diameters with respect to the reduction in minor diameter of the elliptical portion 210 of the second pass 204. Thus, the fourth pass 208 and the third pass 206 comprise a more elliptical shape than the second pass 204, such that the pressure drop is significantly reduced across the fourth pass 208 and third pass 206 as compared to the second pass 204 and the first pass 202. In one exemplary embodiment, the first pass 202 may comprise a 1.5 inch diameter round tube, the elliptical portion 210 of the second pass 204 may comprise a 0.91 inch minor diameter and a 2.43 inch major diameter, and the elliptical portions 210 of the fourth pass 208 and the third pass 206 may comprise a 0.75 inch minor diameter and a 2.56 inch major diameter. Accordingly, the reduction in minor diameter of the elliptical portion 210 of the second pass 204 is 39.3%, while the reduction in minor diameter of the elliptical portion 210 of the fourth pass 208 and the third pass 206 is 50.0%.
Still referring to
The ribs 212 generally comprise linear indentions that comprise a radius 217. Accordingly, in some embodiments, the ribs 212 may comprise substantially similar radii. In this embodiment, the ribs 212 comprise a radius of about 0.125 inches. However, in other embodiments, the ribs may comprise different radiused ribs 212 in each of the passes 204, 206, 208. Because ribs 212 disposed oppositely protrude into the internal passage of the heat exchanger tube 200, the cross-sectional area of the heat exchanger tube 200 is greatly reduced at the apex of the opposing ribs 212. In this embodiment, the internal passage between ribs 212 of the second pass 204 may comprise a minor diameter of about 0.42 inches, while the internal passages between ribs 212 of the third pass 206 and the fourth pass 208 may comprise a minor diameter of about 0.25 inches. Alternatively, the ribs 212 may be alternating, still providing a reduction in the overall heat exchanger tube 200 cross sectional area in passes 204, 206, 208. In some embodiments, the cross sectional area of the heat exchanger tube 200 may result in at least about a 95%, at least about an 85%, at least about a 75%, at least about a 65%, at least about a 50%, at least about a 35%, at least about a 30%, at least about a 25%, at least about a 20%, at least about a 15%, at least about a 10%, and/or at least about a 5% reduction in overall cross sectional area of the heat exchanger tube 200. However, opposing ribs 212 and/or adjacently disposed alternating ribs 212 may even contact one another in certain embodiments. Accordingly, it is an object of the ribs 212 of the heat exchanger tube 200 to increase velocity through the internal passage of the heat exchanger tube 200 while increasing heat transfer and maintaining a manageable pressure drop though the heat exchanger tube 200.
In this embodiment, the passes 204, 206, 208 may comprise a substantially similar number of ribs 212. However, in other embodiments, the passes 204, 206, 208 may comprise a different number of ribs 212. Additionally, in this embodiment, the ribs 212 may be disposed at substantially similar locations along a length of each of the elliptical portions 210 of the passes 204, 206, 208. However, in some embodiments, the ribs 212 may be disposed at different locations along the length of each of the elliptical portions 210 of the passes 204, 206, 208. Accordingly, it is an object of the heat exchanger tube 200 to provide enhanced heat transfer while also controlling the pressure drop of the incoming airflow 190 across the heat exchanger tube 200.
It will be appreciated that in some embodiments, the heat exchanger tube 200 and/or the features of the passes 204, 206, 208 of the heat exchanger tube 200 may be used in the indoor heat exchanger 108 and/or the outdoor heat exchanger 114. Further, the heat exchanger tube 200 may comprise a plurality of thin, plate-like fins disposed along the tubes. Still further, adjacently disposed heat exchanger tubes 200 may not overlap one another in the downstream direction with respect to a primary airflow direction across the heat exchanger tube 200. Additionally, the heat exchanger tube 200 may comprise elliptical portions 210 comprising fins and be void of fins on portions of the heat exchanger tube 200 where the ribs 212 are disposed. Further, in embodiments disclosed herein, the heat exchanger tube 200 may only comprise a second pass 204 and/or third pass 206 comprising an elliptical portion 210 and a plurality of ribs 212. Additionally, in some embodiments, the heat exchanger tube 200 may further comprise a plurality of second passes 204 and/or third passes 206. For example, in the case of a non-condensing furnace 170, 180, the heat exchanger tube 200 may comprise four passes, where the first pass 202 comprises no ribs 212, and each of the second pass 204, the third pass 206, and the fourth pass 208 comprise ribs 212. However, in other embodiments of a non-condensing furnace 170, 180 having four passes, only the third pass 206 and the fourth pass 208 may comprise ribs 212. Further, in some embodiments, a plurality of second passes 204, third passes 206, and/or fourth passes 208 may be connected between two headers such that fluid flows through the internal passages of the passes 204, 206, 208 in parallel. Accordingly, it will be appreciated that the features and/or geometries of the heat exchanger tube 200 described herein may be applied to any tube of a heat exchanger comprising multiple passes.
Referring now to
Referring now to
At least one embodiment is disclosed and variations, combinations, and/or modifications of the embodiment(s) and/or features of the embodiment(s) made by a person having ordinary skill in the art are within the scope of the disclosure. Alternative embodiments that result from combining, integrating, and/or omitting features of the embodiment(s) are also within the scope of the disclosure. Where numerical ranges or limitations are expressly stated, such express ranges or limitations should be understood to include iterative ranges or limitations of like magnitude falling within the expressly stated ranges or limitations (e.g., from about 1 to about 10 includes, 2, 3, 4, etc.; greater than 0.10 includes 0.11, 0.12, 0.13, etc.). For example, whenever a numerical range with a lower limit, Rl, and an upper limit, Ru, is disclosed, any number falling within the range is specifically disclosed. In particular, the following numbers within the range are specifically disclosed: R=Rl+k*(Ru−Rl), wherein k is a variable ranging from 1 percent to 100 percent with a 1 percent increment, i.e., k is 1 percent, 2 percent, 3 percent, 4 percent, 5 percent, . . . , 50 percent, 51 percent, 52 percent, . . . , 95 percent, 96 percent, 97 percent, 98 percent, 99 percent, or 100 percent. Unless otherwise stated, the term “about” shall mean plus or minus 10 percent of the subsequent value. Moreover, any numerical range defined by two R numbers as defined in the above is also specifically disclosed. Use of the term “optionally” with respect to any element of a claim means that the element is required, or alternatively, the element is not required, both alternatives being within the scope of the claim. Use of broader terms such as comprises, includes, and having should be understood to provide support for narrower terms such as consisting of, consisting essentially of, and comprised substantially of. Accordingly, the scope of protection is not limited by the description set out above but is defined by the claims that follow, that scope including all equivalents of the subject matter of the claims. Each and every claim is incorporated as further disclosure into the specification and the claims are embodiment(s) of the present invention.
