EP3224565B1

EP3224565B1 - Frost tolerant microchannel heat exchanger

Info

Publication number: EP3224565B1
Application number: EP15804285.3A
Authority: EP
Inventors: Arindom Joardar
Original assignee: Carrier Corp
Current assignee: Carrier Corp
Priority date: 2014-11-26
Filing date: 2015-11-20
Publication date: 2023-12-27
Anticipated expiration: 2035-11-20
Also published as: EP3224565A2; RU2017121846A3; RU2693946C2; US20170356700A1; RU2017121846A; CN107003073A; WO2016085817A2; WO2016085817A3

Description

BACKGROUND

This invention relates generally to heat pump and refrigeration applications and, more particularly, to a a heat exchanger, according to claim 1.
Heating, ventilation, air conditioning and refrigeration (HVAC&R) systems include heat exchangers to reject or accept heat between the refrigerant circulating within the system and surroundings. One type of heat exchanger that has become increasingly popular due to its compactness, structural rigidity, and superior performance, is a microchannel or minichannel heat exchanger. A microchannel heat exchanger includes two or more containment forms, such as tubes, through which a cooling or heating fluid (i.e. refrigerant or a glycol solution) is circulated. The tubes typically have a flattened cross-section and multiple parallel flow channels. Fins are typically arranged to extend between the tubes to assist in the transfer of thermal energy between the heating/cooling fluid and the surrounding environment. The fins have a corrugated pattern, incorporate louvers to boost heat transfer, and are typically secured to the tubes via brazing.
Conventional microchannel heat exchangers commonly have substantially identical fins throughout the heat exchanger core. In the heat pump and refrigeration applications, when the microchannel heat exchanger is utilized as an evaporator, moisture present in the airflow provided to the heat exchanger for cooling may condense and then freeze on the external heat exchanger surfaces. The ice or frost formed may block the flow of air through the heat exchanger, thereby reducing the efficiency and functionality of the heat exchanger and HVAC&R system. Microchannel heat exchangers tend to freeze faster than the round tube and plate fin heat exchangers and therefore require more frequent defrosts, reducing useful heat exchanger utilization time and overall performance. Consequently, it is desirable to construct the microchannel heat exchanger with improved frost tolerance and enhanced performance.
WO2013/116178 discloses a a heat exchanger according to the preamble of claim 1.

SUMMARY OF THE INVENTION

A heat exchanger is provided according to the wording of claim 1.
The heat exchanger may be configured such that in use the airflow across the heat exchanger may move from the first slab toward the second slab.
The heat exchanger may be configured such that in use the airflow across the heat exchanger may move from the second slab toward the first slab.
The cross-sectional flow area of the first heat exchange tubes may be smaller than the cross-sectional area of the second heat exchange tubes.
The first heat exchange tubes may include a liquid or liquid-vapor mixture including less than 20% vapor by mass.
The fluid within the second heat exchange tubes may include a vapor or liquid-vapor mixture including at least 50% vapor by mass.
The cross-sectional flow area of the first heat exchange tubes may be larger than the cross-sectional area of the second heat exchange tubes.
The fluid within the second heat exchange tubes may include a liquid or liquid-vapor mixture including less than 20% vapor by mass.
The fluid within the first heat exchange tubes may include a vapor or liquid-vapor mixture including at least 50% vapor by mass.
According to yet another embodiment of the invention, a heat exchanger is provided including a first manifold, a second manifold, and a plurality of heat exchange tube segments fluidly coupling the first and second manifold. The heat exchange tube segments include a bend defining a first slab and a second arranged at an angle to one another. Each of the heat exchange tube segments includes at least a first heat exchange tube and a second heat exchange tube at least partially connected by a web extending there between. The heat exchanger is configured such that in use fluid flowing between the manifolds will flow sequentially through the first heat exchange tubes and the second heat exchange tubes of the heat exchanger such that the fluid within the first heat exchange tubes is a liquid and the fluid within the second heat exchange tubes is a vapor.
The first heat exchange tube and the second heat exchange tube may be asymmetrical such that a cross-sectional flow area of the first heat exchange tube is different than a cross-sectional flow area of the second heat exchange tube.
The cross-sectional flow area of the first heat exchange tubes may be smaller than the cross-sectional area of the second heat exchange tubes.
The heat exchanger may be configured such that in use the airflow across the heat exchanger may move from the first slab toward the second slab.
The heat exchanger may be configured such that in use the airflow across the heat exchanger moves from the second slab toward the first slab.

BRIEF DESCRIPTION OF THE DRAWINGS

The subject matter, which is regarded as the invention, 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 invention are apparent from the following detailed description taken in conjunction with the accompanying drawings in which:

FIG. 1 is a schematic diagram of an example of a vapor refrigeration cycle of a refrigeration system;
FIG. 2 is a side view of a microchannel heat exchanger according to an embodiment of the invention prior to a bending operation;
FIG. 3 is a cross-sectional view of a tube segment of a microchannel heat exchanger according to an embodiment of the invention;
FIG. 4 is a cross-sectional view of a tube segment of a microchannel heat exchanger according to an embodiment of the invention;
FIG. 5 is a perspective view of a microchannel heat exchanger according to an embodiment of the invention;
FIG. 6 is a cross-sectional view of a microchannel heat exchanger according to another embodiment of the invention;
FIG. 7 is a cross-sectional view of a microchannel heat exchanger according to yet an embodiment of the invention; and
FIG. 8 is a cross-sectional view of a microchannel heat exchanger according to yet an embodiment of the invention.

The detailed description explains embodiments of the invention, together with advantages and features, by way of example with reference to the drawings.

DETAILED DESCRIPTION

Referring now to FIG. 1, a vapor compression refrigerant cycle 20 of an air conditioning or refrigeration system is schematically illustrated. Exemplary air conditioning or refrigeration systems include, but are not limited to, split, packaged, chiller, rooftop, supermarket, and transport refrigeration systems for example. A refrigerant R is configured to circulate through the vapor compression cycle 20 such that the refrigerant R absorbs heat when evaporated at a low temperature and pressure and releases heat when condensed at a higher temperature and pressure. Within this cycle 20, the refrigerant R flows in a counterclockwise direction as indicated by the arrow. The compressor 22 receives refrigerant vapor from the evaporator 24 and compresses it to a higher temperature and pressure, with the relatively hot vapor then passing to the condenser 26 where it is cooled and condensed to a liquid state by a heat exchange relationship with a cooling medium (not shown) such as air. The liquid refrigerant R then passes from the condenser 26 to an expansion device 28, wherein the refrigerant R is expanded to a low temperature two-phase liquid/vapor state as it passes to the evaporator 24. The low pressure vapor then returns to the compressor 22 where the cycle is repeated. It has to be understood that the refrigeration cycle 20 depicted in FIG. 1 is a simplistic representation of an HVAC&R system, and many enhancements and features known in the art may be included in the schematic. In particular, the heat pump refrigerant cycle includes a four-way valve (not shown) disposed downstream of the compressor with respect to the refrigerant flow that allows reversing the refrigerant flow direction throughout the refrigerant cycle to switch between the cooling and heating mode of operation for the environment to be conditioned.
Referring now to FIG. 2, an example of a heat exchanger 30 configured for use in the vapor compression system 20 is illustrated in more detail. The heat exchanger 30 may be used as either a condenser 24 or an evaporator 28 in the vapor compression system 20. The heat exchanger 30 includes at least a first manifold or header 32, a second manifold or header 34 spaced apart from the first manifold 32, and a plurality of tube segments 36 extending in a spaced, parallel relationship between and connecting the first manifold 32 and the second manifold 34. In the illustrated, non-limiting embodiments, the first header 32 and the second header 34 are oriented generally horizontally and the heat exchange tube segments 36 extend generally vertically between the two headers 32, 34. However, other configurations, such as where the first and second headers 32, 34 are arranged substantially vertically are also within the scope of the invention.
As illustrated in the cross-sections of FIGS. 3 and 4, each of the plurality of tube segments 36 extending between the first manifold 32 and the second manifold 34 is a multiport extruded (MPE) tube segment 36 and includes at least a first heat exchange tube 38 and a second heat exchange tube 40 connected by a web 42 extending at least partially there between. In one embodiment, the web 42 arranged at the outermost tube segments 36 includes a plurality of openings.
An interior flow passage of each heat exchange tube 38,40 may be divided by interior walls into a plurality of discrete flow channels 44a, 44b that extend over the length of the tube segments 36 and establish fluid communication between the respective first and second manifolds 32, 34. The interior flow passages of the first heat exchange tubes 38 may be divided into a different number of discrete flow channels 44 than the interior flow passages of the second heat exchange tubes 40. The flow channels 44a, 44b may have any shape cross-section, such as a circular cross-section, a rectangular cross-section, a trapezoidal cross-section, a triangular cross-section, or another non-circular cross-section for example. The plurality of heat exchange tube segments 36 including the discrete flow channels 44a, 44b may be formed using known techniques, such as extrusion for example.
Each first heat exchange tube 38 and second heat exchange tube 40 has a respective leading edge 46a, 46b, a trailing edge 48a, 48b, a first surface 50a, 50b, and a second surface 52a, 52b (FIG. 3). The leading edge 46a, 46b of each heat exchange tube 38, 40 is upstream of its respective trailing edge 48a, 48b with respect to an airflow A through the heat exchanger 30.
The first heat exchange tubes 38 and the second heat exchanger tubes 40 are substantially different or asymmetric. In the illustrated, non-limiting embodiment, the second heat exchange tubes 40 are wider and have a greater number of discrete flow channels 44 than the first heat exchange tube 38, resulting in a larger cross-sectional flow area. Although the second heat exchange tube 40, as illustrated in FIG. 3, is wider than the first heat exchange tube 38, other configurations, such as where the plurality of first heat exchange tubes 38 have a greater cross-sectional flow area than the plurality of second heat exchange tubes 40 for example, are within the scope of the invention. The ratio of asymmetry between the first heat exchange tubes 38 and the second heat exchanger tubes 40 may depend on any of a variety of parameters of the heat exchanger, such as capacity,
Referring now to FIG. 5, each tube segment 36 of the heat exchanger 30 includes at least one bend 60, such that the heat exchanger 30 has a multi-pass configuration relative to the airflow A. The bend 60 is generally formed about an axis extending substantially perpendicular to the longitudinal axis or the discrete flow channels 44a, 44b of the tube segments 36. In the illustrated embodiment, the bend 60 is a ribbon fold; however other types of bends are within the scope of the invention. In the illustrated, non-limiting embodiment, the bend 60 is formed at an approximate midpoint of the tube segments 36 between the opposing first and second manifolds 32, 34.
The bend 60 at least partially defines a first section or slab 62 and a second section or slab 64 of the plurality of tube segments 36. As shown in the FIG., the bend 60 can be formed such that the first slab is positioned at an obtuse angle with respect to the second slab 64. Alternatively, or in addition, the bend 60 can also be formed such that the first slab 62 is arranged at either an acute angle or substantially parallel to the second slab 64. The bend 60 allows for the formation of a heat exchanger 30 having a conventional A-coil or V-coil shape. In embodiments where the first slab 62 and the second slab 64 are arranged substantially parallel, the lengths of the first slab 62 and the second slab 64 may vary to offset the position of the first manifold 32 relative to the second manifold 34. Alternatively, the free ends of the first slab 62 and the second slab 64 may angle or flare away from one another to accommodate the manifolds 32, 34.
As previously stated, the heat exchanger 30 includes a multi-pass configuration as a result of the bend 60 formed therein. In one embodiment, illustrated in FIG. 6, the heat exchanger 30 is configured such that both the first heat exchanger tube 38 and the second heat exchanger tube 40 of a tube segment 36 within the first slab 62 define a first pass relative to an airflow A. Similarly, both the first heat exchanger tube 38 and the second heat exchanger tube 40 within the second slab 64 of the same tube segment 36 define a subsequent pass relative to the airflow. Although in the illustrated FIG., the fluid or refrigerant has a counter flow orientation relative to the direction of the airflow, other embodiments where the refrigerant has a parallel flow orientation are also within the scope of the invention.
In another embodiment, as illustrated in FIGS. 7 and 8, the first heat exchanger tube 38 and the second heat exchanger tube 40 within the same first slab 62 or second slab 64 are configured as different passes within the refrigerant flow path of the heat exchanger 30. For example, as shown in FIG. 7, the heat exchanger 30 may be configured such that refrigerant flows sequentially through the first heat exchanger tube 38 of both the first slab 62 and the second slab 64 prior to flowing through the second heat exchanger tube 40 of the second slab 64 and the first slab 62. However, other flow configurations such as where the refrigerant flows through the second heat exchanger tubes 40 before flowing the first heat exchanger tubes 38, as shown in FIG. 8, is within the scope of the invention. In addition, the refrigerant may enter the heat exchanger 30 at the same slab as the airflow, as shown in the embodiments of FIGS. 7 and 8, or alternatively, may enter the heat exchanger at a different slab as the airflow.
Depending on the direction of the airflow A relative to the heat exchanger 30 and which slab the refrigerant is configured as an inlet to the heat exchanger 30, the flow through the first heat exchanger tube 38 has a first configuration and the flow through the second heat exchanger tube 40 has a second configuration, different from the first configuration. As shown in the illustrated, non-limiting embodiment of FIG. 7, with the airflow A flowing from the first slab 62 toward the second slab 64, the flow within the first heat exchanger tube 38 is parallel to the direction of the airflow A, and the flow within the second heat exchanger tube 40 is counter to the airflow A. In embodiments where the refrigerant is first provided to the second heat exchanger tubes 40, as shown in FIG. 8, the flow within the second heat exchanger tubes 40 is parallel to the direction of the airflow A, and the flow within the first heat exchanger tubes 38 is counter to the airflow A.
To minimize the formation of frost on the heat exchanger 30, the flow path of the refrigerant through the heat exchanger 30 may be configured such that the liquid or two phase portion of the refrigerant flows through the heat exchanger tube having a smaller cross-sectional flow area and the vapor portion of the refrigerant flows through the heat exchanger tube having a larger cross-sectional flow area. For example, in the embodiment illustrated in FIG. 8, the second heat exchanger tube 40 has a smaller cross-sectional flow area than the first heat exchanger tube 38. The airflow is configured to flow from the first slab 62 to the second slab 64, and the liquid or two-phase refrigerant is input to the second heat exchanger tubes 40 of the first slab 62. By the time the refrigerant reaches first heat exchange tubes 38 of the first slab 62, the refrigerant is a superheated vapor which is at a higher temperature than the saturation temperature. As a result, the amount of heat transfer that occurs between the airflow A and first heat exchange tubes 38 of the first slab 62 is limited. In such embodiments, the liquid or liquid vapor mixture within the second heat exchange tubes 40 is less than 20% vapor by mass and the vapor or liquid-vapor mixture within the first heat exchanger tubes 38 is at least 50% vapor by mass.
In other embodiments, refrigerant may be provided to the first heat exchange tubes 38 then the second heat exchange tubes 40, as shown in FIG. 7. In such embodiments, first heat exchanger tubes 38 may have a cross-sectional flow area smaller than that of the second heat exchanger tubes 40 such that the liquid or liquid vapor mixture within the first heat exchange tubes 38 is less than 20% vapor by mass and the vapor or liquid-vapor mixture within the second heat exchanger tubes 40 is at least 50% vapor by mass.
Presence of superheated vapor and reducing the amount of heat transfer between an airflow A and a fluid R in the pass of the refrigerant where the airflow initially contacts the heat exchanger leads to reduced rate of frost accumulation and improved frost tolerance.. As a result, the formation of frost, and therefore a number of defrost cycles required to maintain the operational efficiency of the heat exchanger 30 are reduced. Because the operational efficiency of the heat exchanger 30 is improved (due to a lower number of defrost cycles and increased heat transfer in the second slab), the size of the heat exchanger 30 required for a desired application may also be reduced. Alternatively, size of other components, such as a compressor may be reduced, which in turn would cause even higher evaporation temperature and further reduction of defrost cycles as well as the system performance boost.
While the present invention 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 invention as defined by the claims. 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. In particular, similar principals and ratios may be extended to the rooftops applications and vertical package units.

Claims

A heat exchanger (30) comprising:
a first manifold (32);

a second manifold (34) separated from the first manifold;

a plurality of heat exchange tube segments (36) arranged in spaced parallel relationship and fluidly coupling the first manifold and the second manifold, the plurality of heat exchange tube segments including a bend (60) defining a first slab (62) and a second slab (64) of the heat exchange tube segments, the first slab being arranged at an angle to the second slab, each of the plurality of heat exchange tube segments including at least a first heat exchange tube (38) and a second heat exchange tube (40) at least partially connected by a web (42) extending there between, the first heat exchange tube and the second heat exchange tube being asymmetrical such that a cross-sectional flow area of the first heat exchange tube is different than a cross-sectional flow area of the second heat exchange tube;
characterised in that:
the heat exchanger is configured such that in use a fluid flowing between the manifolds will flow sequentially through heat exchange tubes, such that the fluid provided to the heat exchange tubes having the smaller cross section is at least partially liquid and the fluid provided to the heat exchange tubes having the larger cross section is a vapor.
The heat exchanger according to claim 1, wherein the heat exchanger is configured such that in use an airflow across the heat exchanger moves from the first slab toward the second slab.
The heat exchanger according to claim 1, wherein the heat exchanger is configured such that in use an airflow across the heat exchanger moves from the second slab toward the first slab.
The heat exchanger according to claim 1, wherein the cross-sectional flow area of the first heat exchange tubes is smaller than the cross-sectional area of the second heat exchange tubes.
The heat exchanger according to claim 4, wherein the fluid within the first heat exchange tubes includes a liquid or liquid-vapor mixture including less than 20% vapor by mass.
The heat exchanger according to claim 4, wherein the fluid within the second heat exchange tubes includes a vapor or liquid-vapor mixture including at least 50% vapor by mass.
The heat exchanger according to claim 1, wherein the cross-sectional flow area of the first heat exchange tubes is larger than the cross-sectional area of the second heat exchange tubes.
The heat exchanger according to claim 7, wherein the fluid within the second heat exchange tubes includes a liquid or liquid-vapor mixture including less than 20% vapor by mass.
The heat exchanger according to claim 7, wherein the fluid within the first heat exchange tubes includes a vapor or liquid-vapor mixture including at least 50% vapor by mass.
A heat exchanger according to claim 1 comprising:
a plurality of heat exchange tube segments arranged in spaced parallel relationship and fluidly coupling the first manifold and the second manifold, the plurality of heat exchange tube segments including a bend defining a first section of the heat exchanger tube segments and a second section of the heat exchange tube segments, the first section being arranged at an angle to the second section, each of the plurality of tube segments including at least a first heat exchange tube and a second heat exchange tube at least partially connected by a web extending there between;

wherein the first heat exchanger tubes and the second heat exchanger tubes are configured as different passes within a fluid flowpath, wherein the heat exchanger is configured such that in use an airflow enters the heat exchanger adjacent a portion of the first heat exchange tubes, and the fluid provided to the portion of the first heat exchanger tubes has a temperature above a saturation temperature.
The heat exchanger according to claim 10, wherein the first heat exchange tube and the second heat exchange tube are asymmetrical such that a cross-sectional flow area of the first heat exchange tube is different than a cross-sectional flow area of the second heat exchange tube.
The heat exchanger according to claim 11, wherein the cross-sectional flow area of the first heat exchange tubes is smaller than the cross-sectional area of the second heat exchange tubes.
The heat exchanger according to claim 10, wherein the heat exchanger is configured such that in use an airflow across the heat exchanger moves from the first slab toward the second slab.
The heat exchanger according to claim 10, wherein the heat exchanger is configured such that in use an airflow across the heat exchanger moves from the second slab toward the first slab.