This disclosure relates generally to heat exchangers and, more particularly, to a heat exchanger configured for use as an outdoor heat exchanger in residential air conditioning and heat pump applications.
In recent years, much interest and design effort has been focused on the efficient operation of heat exchangers of refrigerant systems, particularly condensers and evaporators. A relatively recent advancement in heat exchanger technology includes the development and application of parallel flow (such as microchannel, minichannel, brazed-plate, plate-fin, or plate-and frame) heat exchangers as condensers and evaporators.
According to an embodiment, a heat exchanger is provided including a first header and a second header and a plurality of heat exchange tube arranged in spaced parallel relationship and fluidly coupling the first and second header. A flow restricting element defining a first volume and a second volume is positioned within one of the first and second header. The heat exchanger has a multi-pass configuration such that a first portion of the plurality of heat exchange tubes are coupled to the first volume and form a first fluid pass of the heat exchanger and a second portion of the plurality of heat exchange tubes are coupled to the second volume and form a second fluid pass of the heat exchanger. During operation, the heat transfer fluid conveyed through the first volume has a first saturation temperature and the heat transfer fluid conveyed through the second volume has a different second saturation temperature.
In addition to one or more of the features described above, or as an alternative, in further embodiments a difference between the second saturation temperature and the first saturation temperature exceeds normal temperature variation within the at least one of the first header and second header.
In addition to one or more of the features described above, or as an alternative, in further embodiments the flow restricting element imparts a pressure drop on the heat transfer fluid conveyed there through during operation causing the first saturation temperature and the second saturation temperature to be different.
In addition to one or more of the features described above, or as an alternative, in further embodiments the pressure drop is between about 3 psi and about 12 psi.
In addition to one or more of the features described above, or as an alternative, in further embodiments the pressure drop is about 6 psi.
In addition to one or more of the features described above, or as an alternative, in further embodiments the flow restricting element comprises an orifice.
In addition to one or more of the features described above, or as an alternative, in further embodiments a cross-sectional area of the orifice is between about 3% and about 30% of a cross-sectional area of the at least one of the first header and the second header in which it is disposed.
In addition to one or more of the features described above, or as an alternative, in further embodiments a distributor fluidly coupled to the orifice is arranged within the second volume and is adjacent at least the second portion of the plurality of heat exchange tubes.
In addition to one or more of the features described above, or as an alternative, in further embodiments a porous insert is positioned within the second volume adjacent at least the second portion of the plurality of heat exchange tubes. The porous insert is configured to restrict a fluid flow path between the first fluid pass and the second fluid pass.
In addition to one or more of the features described above, or as an alternative, in further embodiments the flow restricting element comprises a flow control valve. The flow control valve is movable to adjust a parameter of a fluid flow path between the first fluid pass and the second fluid pass.
In addition to one or more of the features described above, or as an alternative, in further embodiments the plurality of heat exchange tubes are microchannel tubes.
In addition to one or more of the features described above, or as an alternative, in further embodiments the first header comprises one or more partitions disposed therein and defining two or more discrete fluid volumes.
In addition to one or more of the features described above, or as an alternative, in further embodiments the first header comprises two baffles forming three first header volumes and the second header comprises two flow restricting elements forming a first, second, and third second header volume.
In addition to one or more of the features described above, or as an alternative, in further embodiments during operation, a heat transfer fluid conveyed through the first volume has a first saturation temperature and the heat transfer fluid conveyed through the third volume has a third saturation temperature. The first saturation temperature and the third saturation temperature are different.
In addition to one or more of the features described above, or as an alternative, in further embodiments the second saturation temperature and the third saturation temperature are generally identical.
In addition to one or more of the features described above, or as an alternative, in further embodiments the second saturation temperature and the third saturation temperature are distinct.
The subject matter, which is regarded as the present disclosure, is particularly pointed out and distinctly claimed in the claims at the conclusion of the specification. The foregoing and other features, and advantages of the present disclosure are apparent from the following detailed description taken in conjunction with the accompanying drawings in which:
a are various cross-sectional view of a header of a heat exchanger of the outdoor coil unit according to another embodiment
The detailed description explains embodiments of the present disclosure, together with advantages and features, by way of example with reference to the drawings.
Microchannel heat exchangers as outdoor coil units are being considered for use in residential heat pump and air conditioning applications. Due to regulatory efficiency requirements, sound constraints, and a non-optimized heat exchanger design, the size of the outdoor heat exchanger is typically large. As a result, the heat pump and air conditioning systems incur higher costs and have a higher refrigerant charge. Current legislation limits the amount of charge of refrigerant systems, and heat exchangers in particular, containing most low global warming potential refrigerants (currently classified as A2L substances).
Microchannel heat exchangers have a small internal volume and therefore store less refrigerant charge than conventional round tube plate fin heat exchangers. Although a lower refrigerant charge is generally beneficial, the smaller internal volume of microchannel heat exchangers makes them extremely sensitive to overcharge or undercharge situations, which could result in refrigerant charge imbalance, degrade refrigerant system performance, and cause nuisance shutdowns. In addition, the refrigerant charge contained in the manifolds of the microchannel heat exchanger, particularly when the heat exchanger operates as a condenser, is significant, such as about half of the total heat exchanger charge. As a result, the refrigerant charge reduction potential of the heat exchanger is limited.
Referring now to
Disposed in contact with a surface of the heat exchanger 22 is a fan assembly 26 configured to draw ambient air radially inward, through the heat exchanger 22, after which the air is discharged upwardly through an opening 28. In an embodiment, the unit 20 includes a floor pan 29 configured to hold the heat exchanger 22 in place.
With reference now to
In the non-limiting embodiments illustrated in the FIGS., the headers 30, 32 comprise hollow, closed end cylinders having a circular cross-section. However, headers 30, 32 having other configurations, such as elliptical, semi-elliptical, square, rectangular, hexagonal, octagonal, or other cross-sections for example, are within the scope of the disclosure. The heat exchanger 22 may be used as either a condenser or an evaporator in a vapor compression system, such as a heat pump system or air conditioning system for example.
The heat exchanger 22 can be any type of heat exchanger, such as a round tube plate fin (RTPF) type heat exchanger or a microchannel heat exchanger for example. Referring now to
A plurality of heat transfer fins 50 (
The heat exchanger 22 may be configured with a single or multi-pass flow configuration. To form a multi-pass flow configuration, at least one of the first manifold 30 and the second manifold 32 includes two or more fluidly distinct sections or chambers. In one embodiment, the fluidly distinct sections are formed by coupling separate manifolds together to form the first or second manifold 30, 32. Alternatively, a baffle or divider plate (not shown) known to a person of ordinary skill in the art may be arranged within at least one of the first header 30 and the second header 32 to define a plurality of fluidly distinct sections therein.
In the illustrated, non liming embodiment of
Although embodiments where the heat exchange tubes 34 are divided into two or three groups are illustrated, a heat exchanger having any number of passes and therefore any number groups of heat exchange tubes 34 is within the scope of the disclosure. A length of the plurality of sections of the headers 30, 32 and the number of tubes 34 within the distinct groups 34a, 34b, 34c may, but need not be substantially identical. In one embodiment, the sections of the headers 30, 32 are formed arranging a baffle plate or other divider 80 at a desired location within the headers 30, 32.
The direction of fluid flow through the heat exchanger 22, as illustrated by the arrows, depends on the mode in which the outdoor unit 20 is being operated. For example, when the heat exchanger 22 illustrated in
As the heat transfer fluid flows sequentially through the second and first groups 34b, 34a of heat exchanger tubes 34, or alternatively, through the second and third groups 34b, 34c of heat exchanger tubes 34, heat from an adjacent flow of air A, is transferred to the heat transfer fluid. As a result, a substantially vaporized heat transfer fluid is provided at the outlets 60. Alternatively, heat transfer fluid is configured to flow in a reverse direction through the heat exchanger 22, indicated by a second set of arrows, when operated as a condenser. The configuration of the heat exchanger 22 illustrated and described herein is intended as an example only, and other types of heat exchangers 22 having any number of passes are within the scope of the disclosure.
Referring now to
Alternatively, or in addition, the flow restricting element 90 may include a longitudinally elongated distributor 84 (
In another embodiment, the fluid restricting element 90 positioned within the header 32 between the first volume associated with the first pass and the second volume associated with the second pass of the heat exchanger 22 includes an insert 86 configured to reduce the inner volume thereof. The insert 86 can be formed from a metal or non-metal material, such as a foam, mesh, woven wire or thread, or a sintered metal for example, and can have a uniform or non-uniform porosity. The insert 86 may have at least one of a size and shape generally complementary to an interior of the header 32. A porosity of the insert 86 may be configured to change, such as uniformly for example, along the length of the header 32 in the direction of the heat transfer fluid flow. In an embodiment, the insert 86 is formed with a plurality of pockets or cavities (not shown), each cavity being configured to receive or accommodate one of the heat exchange tubes 34 extending into the header 32.
The insert 86 may be integrally formed with the header 32, or alternatively, may be a separate removable sub-assembly inserted into the inner volume thereof, such as supported on plates mounted therein for example. In addition, the porous insert 86 may be combined with any of the previously described flow restricting elements 90. For example, a distributor 84 may be inserted into the insert 86.
In yet another embodiment,illustrated in
In conventional systems it is desirable to maintain a constant pressure throughout a fluid flow path of a heat exchanger to ensure even distribution of the liquid and gas phases of the fluid throughout the various passes. However, with respect to the heat exchanger 22 described herein, the various methods for restricting the fluid flow within a volume of the header create a pressure drop exceeding normal pressure variation within the header 32 between the first and second passes of the heat exchanger 22. In one embodiment, the pressure drop between the first and second passes is between about 3 pounds per square inch (psi) and about 12 psi, such as 6 psi for example.
The pressure drop between the first pass and the second pass of the heat exchanger 22 results in different saturation temperatures due to the hydraulic resistance created by the flow restricting element 90. As a result of this difference in saturation temperature, which exceeds normal saturation temperature variation within a header 32, the time required for frost to accumulate on the heat exchange tubes 34 of the portion of the heat exchanger 22 having a different saturation temperature increases, resulting in a longer frost-defrost cycle of the outdoor unit 20. The pressure drop between consecutive passes of the heat exchanger 22 may be optimized to achieve a desired saturation temperature difference, based not only on the heat exchanger 22 configuration, but also specific operating conditions.
The heating seasonal performance factor (HSPF) of the heat exchanger 22 is determined by the frost-defrost cycle time. An increase in the saturation pressure difference and frost-defrost cycle time, similarly results in an increased HSPF. As a result of this increase in HSPF, the size of the heat exchanger 22 may be optimized, resulting in both cost and space savings.
Embodiment 1: A heat exchanger, comprising:
Embodiment 2: The heat exchanger according to embodiment 1, wherein a difference between the second saturation temperature and the first saturation temperature exceeds normal temperature variation within the at least one of the first header and second header.
Embodiment 3: The heat exchanger according to embodiment 1, wherein the flow restricting element imparts a pressure drop on the heat transfer fluid conveyed there through during operation, causing the first saturation temperature and the second saturation temperature to be different.
Embodiment 4: The heat exchanger according to embodiment 3, wherein the pressure drop is between about 3 psi and about 12 psi.
Embodiment 5: The heat exchanger according to embodiment 3 or embodiment 4, wherein the pressure drop is about 6 psi.
Embodiment 6: The heat exchanger according to embodiment 3, wherein the flow restricting element comprises an orifice.
Embodiment 7: The heat exchanger according to embodiment 6, wherein a cross-sectional area of the orifice is between about 3% and about 30% of a cross-sectional area of the at least one of the first header and the second header in which it is disposed.
Embodiment 8: The heat exchanger according to embodiment 6 or embodiment 7, wherein a distributor fluidly coupled to the orifice is arranged within the second volume and is adjacent at least the second portion of the plurality of heat exchange tubes.
Embodiment 9: The heat exchanger according to any of the preceding embodiments, further comprising a porous insert positioned within the second volume adjacent at least the second portion of the plurality of heat exchange tubes, the porous insert being configured to restrict a fluid flow path between the first fluid pass and the second fluid pass.
Embodiment 10: The heat exchanger according to any of the preceding embodiments, wherein the flow restricting element comprises a flow control valve, the flow control valve being movable to adjust a parameter of a fluid flow path between the first fluid pass and the second fluid pass.
Embodiment 11: The heat exchanger according to any of the preceding embodiments, wherein the plurality of heat exchange tubes are microchannel tubes.
Embodiment 12: The heat exchanger according to any of the preceding embodiments, wherein the first header comprises one or more partitions disposed therein and defining two or more discrete fluid volumes.
Embodiment 13: The heat exchanger according to any of the preceding embodiments, wherein the first header comprises two baffles forming three first header inner volumes and the second header comprises two flow restricting elements forming a first, second, and third second header volume.
Embodiment 14: The heat exchanger according to embodiment 13, wherein during operation a heat transfer fluid conveyed through the first volume has a first saturation temperature and the heat transfer fluid conveyed through the third volume has a third saturation temperature, wherein the first saturation temperature and the third saturation temperature are different.
Embodiment 15: The heat exchanger according to embodiment 14, wherein the second saturation temperature and the third saturation temperature are generally identical.
Embodiment 16: The heat exchanger according to embodiment 14, wherein the second saturation temperature and the third saturation temperature are distinct.
While the present disclosure has been particularly shown and described with reference to the exemplary embodiments as illustrated in the drawing, it will be recognized by those skilled in the art that various modifications may be made without departing from the scope of the present disclosure. Therefore, it is intended that the present disclosure not be limited to the particular embodiment(s) disclosed as, but that the disclosure will include all embodiments falling within the scope of the appended claims.
This application is a divisional of U.S. patent application Ser. No. 15/365,131, filed Nov. 30, 2016, which claims the benefit of U.S. provisional application Ser. No. 62/260,963 filed Nov. 30, 2015, the contents of which are incorporated by reference in its entirety herein.
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Number | Date | Country | |
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20210341227 A1 | Nov 2021 | US |
Number | Date | Country | |
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62260963 | Nov 2015 | US |
Number | Date | Country | |
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Parent | 15365131 | Nov 2016 | US |
Child | 17375661 | US |