EP2392886A2 - Orientation insensitive refrigerant distributor tube - Google Patents
Orientation insensitive refrigerant distributor tube Download PDFInfo
- Publication number
- EP2392886A2 EP2392886A2 EP11167680A EP11167680A EP2392886A2 EP 2392886 A2 EP2392886 A2 EP 2392886A2 EP 11167680 A EP11167680 A EP 11167680A EP 11167680 A EP11167680 A EP 11167680A EP 2392886 A2 EP2392886 A2 EP 2392886A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- orifices
- distributor tube
- heat exchanger
- exchanger assembly
- refrigerant
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
- F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D2001/0253—Particular components
- F28D2001/026—Cores
- F28D2001/0273—Cores having special shape, e.g. curved, annular
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/0071—Evaporators
Definitions
- the present disclosure relates to an inlet distributor for an evaporator; more particularly to an inlet distributor having a plurality of orifices arranged along the length of the distributor tube.
- Automotive heat exchangers typically include an inlet header, an outlet header, and a plurality of refrigerant tubes hydraulically connecting the headers for refrigerant flow therebetween. Corrugated fins interconnect adjacent refrigerant tubes to increase the available heat transfer area, as well as to increase the structural integrity of the heat exchanger.
- the coil of the heat exchanger is defined by the refrigerant tubes and interconnecting corrugated fins. To meet the demands of residential and commercial applications, the size of the coil of the heat exchanger has to be increased accordingly, which in turn dramatically increased the lengths of the inlet and outlet headers.
- a typical distributor tube extends the length of the inlet header and includes a plurality of uniformly spaced orifices for distributing the two-phase refrigerant throughout the length of the header.
- the orifices are oriented at a designed angle relative to the center of the cross-section of the refrigerant tube to provide the maximum performance for the coil in a specific application.
- the angle of the orifices is selected based on testing a vertical slab coil design with the refrigerant tube aligned in the opposite direction of gravity.
- Indoor evaporators also have the additional challenge of packaging constraints; the evaporators have to fit within the limited volume offered by the plenums of residential HVAC systems.
- the refrigerant tubes lie in a plane much like that of an automotive heat exchanger, and for maximum efficiency it is preferable that the refrigerant tubes are aligned in the direction of gravity with the inlet header lower than the outlet header.
- two smaller slab coils are assembled into an A-Frame design or a single larger slab coil is bent into an ARC design.
- the A-Frame design or ARC design may need to be installed in various orientations with respect to gravity, in which the refrigerant tubes may not be aligned in the direction of gravity and the inlet header may not be lower than the outlet header.
- the desired distribution of refrigerant flowing through the coil may be adversely affected due to the orientation of the evaporator. There is a long felt need for an evaporator that provides good refrigerant distribution regardless of its orientation.
- the invention relates to a heat exchanger assembly having an inlet header, an outlet header spaced from the inlet header, a plurality of refrigerant tubes hydraulically connecting the inlet header with the outlet header.
- a distributor tube having a plurality of orifices disposed in the inlet header, wherein the orifices are arranged along the distributor tube such that at least one orifice is oriented in the liquid phase of a two-phased refrigerant pressed against the internal surface of the distributor tube regardless of the orientation of the evaporator.
- the orifices may be substantially uniformly spaced along the length of the distributor tube in pairs or groups of four (4).
- one of the orifices may be oriented 90 to 180 degrees apart from the other with respect to the pair's respective point on a central axis.
- Each pair of orifices may be rotated 90 to 180 degrees from the adjacent pair of orifices.
- each of the orifices may be oriented 90 degrees apart from the adjacent orifice with respect to the group's respective point on a central axis.
- Each group of four (4) orifices may be rotated 45 degrees from the adjacent group of four (4) orifices.
- the cylindrical refrigerant distributor tube may have a plurality of orifices spiraled along the tube. With respect to an end view of the central axis, each succeeding orifice may be offset 45 to 180 degrees from the preceding orifice.
- a residential indoor evaporator may be constructed by using two slab coils in an A-Frame design or a single slab coil bent into an ARC design. Shown in Figs.
- FIGS. 1A-1C are representations of an end view of an A-Frame design or ARC design residential indoor evaporator 10 having an inlet header 12a, an outlet header 12b spaced apart from the inlet header 12a, and a plurality of refrigerant tubes 14 hydraulically connecting the headers 12a, 12b for refrigerant flow.
- An evaporator coil 16, partially shown in Figs. 2 and 3 is defined by the plurality of refrigerant tubes 14 together with external fins 15 interconnecting the adjacent refrigerant tubes 14.
- the evaporator 10 includes a distributor tube 20 in the inlet header 12a, shown in Figs. 2-7 , for improved refrigerant distribution.
- the above mentioned components of the evaporator 10 are typically constructed of a heat conductive material such as aluminum.
- Each of the A-Frame design and ARC design provides an evaporator 10 having at least one apex 18.
- the A-Frame or ARC design can be installed within a HVAC plenum in various orientations with respect to the direction of gravity, in which the apex 18 may be up, down, horizontal, and any other orientation therebetween.
- the inlet header 12a may be located above the outlet header 12b, below the outlet header 12b, or horizontal with the outlet header12b.
- the headers 12a, 12b are typically perpendicular to that of the direction of gravity, but the bottom header may be slightly angled toward the direction of gravity to facilitate condensate drainage.
- a standard angle designed for the orifices 22 of the distribution tube 20 relative to the refrigerant tube 14 may not necessarily work efficiently when used in all the various potential orientations of the evaporator 10. It was found that only certain range of angles of the orifices 22 of the distribution tube 20 relative to the refrigerant tube 14 are acceptable for each of the various evaporator coil 16 orientations. In other words, orifice angles are application specific; therefore, the desired orifice range of angles has to be calculated for each specific orientation of the evaporator 10.
- the liquid phase 24 of a two-phase refrigerant flowing through the distributor tube 20 tends to migrate to the bottom of the interior surface 28 of the distributor tube 20 due to gravity. It is suspected that the liquid phase 24 does not necessary puddle on the bottom or low spot of the distribution tube 20, but instead it is pressed against and rides up a portion of the interior surface 28 of the distributor tube 20 by the flow of refrigerant through the distributor tube 20, thereby forming a liquid refrigerant cross-sectional profile 30 much like a crescent moon with its apex on the bottom.
- the limit would be annular flow where the liquid distributes around the entire peripheral internal surface 28 of the distribution tube 20, but more typically a thicker layer would exist on the bottom.
- the liquid refrigerant cross-sectional profile 30 occupies the interior surface 28 of the distributor tube 20 from 45 to 315 degrees with respect to the opposite direction of gravity being 0 degree. During normal operating conditions, the liquid refrigerant cross-sectional profile 30 occupies the interior surface 28 of the distributor tube 20 from 90 to 270 degrees.
- An aspect of the invention provides a means to transport the liquid phase refrigerant from the distributor tube 20 to the refrigerant tubes 14 for efficient boiling and thus improved heat transfer performance regardless of the orientation of the A-Frame or ARC evaporator coil evaporator.
- This can be achieved by having orifices 22 at angles from 45 to 315 degrees, preferably between 90 to 270 degrees, with respect to the opposite direction of gravity being 0 degree, along the distributor tube 20 to ensure that at least one, but preferably a group, of orifices 22 is substantially oriented within the liquid refrigerant cross-sectional profile 30.
- the refrigerant flowing through the distributor tube 20 will push the liquid phase refrigerant through the orifices 22 and toward the refrigerant tubes.
- Fig. 5 shows a cylindrical refrigerant distributor tube 20 extending along a substantially central axis (A-axis). Pairs of orifices 22 are substantially uniformly spaced along the length of the distributor tube 20, in which each pair of orifices 22 is located about its respective point on the A-axis. Within each pair of orifices 22, one of the orifices 22 may be oriented 90 to 180 degrees apart from the other with respect to the pair's respective point on the A-axis. Furthermore, each pair of orifices 22 may be rotated 90 to 180 degrees from the adjacent pair of orifices 22.
- Fig. 6 shows a cylindrical refrigerant distributor tube 20 extending along the A-axis.
- Groups of four (4) orifices 22 are substantially uniformly spaced along the length of the distributor tube 20, in which each group of orifices 22 is located about its respective point on the A-axis.
- each of the orifices 22 may be oriented 90 degrees apart from the adjacent orifice 22 with respect to the group's respective point on the A-axis.
- each group of (4) orifices 22 may be rotated 45 degrees from the adjacent group of (4) orifices 22.
- Fig. 7 shows a cylindrical refrigerant distributor tube 20 having a plurality of orifices 22 spiraled along the tube. With respect to an end view of the A-axis, each succeeding orifice 22 may be offset 45 to 180 degrees from the preceding orifice 22.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Details Of Heat-Exchange And Heat-Transfer (AREA)
Abstract
Description
- The present disclosure relates to an inlet distributor for an evaporator; more particularly to an inlet distributor having a plurality of orifices arranged along the length of the distributor tube.
- Residential and commercial air conditioning and heat pump systems are known to employ modified automotive heat exchangers, which are desirable for its proven high heat transfer efficiency, durability, and relatively ease of manufacturability. Automotive heat exchangers typically include an inlet header, an outlet header, and a plurality of refrigerant tubes hydraulically connecting the headers for refrigerant flow therebetween. Corrugated fins interconnect adjacent refrigerant tubes to increase the available heat transfer area, as well as to increase the structural integrity of the heat exchanger. The coil of the heat exchanger is defined by the refrigerant tubes and interconnecting corrugated fins. To meet the demands of residential and commercial applications, the size of the coil of the heat exchanger has to be increased accordingly, which in turn dramatically increased the lengths of the inlet and outlet headers. For a heat exchanger operating in evaporator mode, the increased length of the headers tends to result in refrigerant mal-distribution through the refrigerant tubes. Momentum and gravity effects, due to the large mass differences between the liquid and gas phases, can result in separation of the phases in the inlet header and cause poor refrigerant distribution through the refrigerant tubes. Poor refrigerant distribution degrades evaporator performance and can result in uneven temperature distribution over the coil. To assist in providing uniform refrigerant distribution though the refrigerant tubes, it is known to provide a distributor tube in the inlet header.
- A typical distributor tube extends the length of the inlet header and includes a plurality of uniformly spaced orifices for distributing the two-phase refrigerant throughout the length of the header. The orifices are oriented at a designed angle relative to the center of the cross-section of the refrigerant tube to provide the maximum performance for the coil in a specific application. Typically, the angle of the orifices is selected based on testing a vertical slab coil design with the refrigerant tube aligned in the opposite direction of gravity. Indoor evaporators also have the additional challenge of packaging constraints; the evaporators have to fit within the limited volume offered by the plenums of residential HVAC systems. In a slab coil design, the refrigerant tubes lie in a plane much like that of an automotive heat exchanger, and for maximum efficiency it is preferable that the refrigerant tubes are aligned in the direction of gravity with the inlet header lower than the outlet header. To provide the cooling capacity required within a limited space, two smaller slab coils are assembled into an A-Frame design or a single larger slab coil is bent into an ARC design. The A-Frame design or ARC design may need to be installed in various orientations with respect to gravity, in which the refrigerant tubes may not be aligned in the direction of gravity and the inlet header may not be lower than the outlet header. The desired distribution of refrigerant flowing through the coil may be adversely affected due to the orientation of the evaporator. There is a long felt need for an evaporator that provides good refrigerant distribution regardless of its orientation.
- The invention relates to a heat exchanger assembly having an inlet header, an outlet header spaced from the inlet header, a plurality of refrigerant tubes hydraulically connecting the inlet header with the outlet header. A distributor tube having a plurality of orifices disposed in the inlet header, wherein the orifices are arranged along the distributor tube such that at least one orifice is oriented in the liquid phase of a two-phased refrigerant pressed against the internal surface of the distributor tube regardless of the orientation of the evaporator.
- According to one aspect of the invention, the orifices may be substantially uniformly spaced along the length of the distributor tube in pairs or groups of four (4). Within each pair of orifices, one of the orifices may be oriented 90 to 180 degrees apart from the other with respect to the pair's respective point on a central axis. Each pair of orifices may be rotated 90 to 180 degrees from the adjacent pair of orifices. For groups of four (4) orifices, each of the orifices may be oriented 90 degrees apart from the adjacent orifice with respect to the group's respective point on a central axis. Each group of four (4) orifices may be rotated 45 degrees from the adjacent group of four (4) orifices.
- In another aspect of the invention, the cylindrical refrigerant distributor tube may have a plurality of orifices spiraled along the tube. With respect to an end view of the central axis, each succeeding orifice may be offset 45 to 180 degrees from the preceding orifice.
- The above configurations of orifices on the distributor tube provide that at least one of the orifices will be located within the liquid phase of the two-phase refrigerant flowing through the distributor tube regardless of the final orientations of the evaporator coil. This provides at least the advantage of improved refrigerant distribution through the refrigerant tube of the heat exchanger assembly resulting in improved heat transfer efficiency.
- This invention will be further described with reference to the accompanying drawings in which:
-
Figs. 1 A-C show representative end views of an A-type coil or bent coil design evaporator. -
Fig. 2 shows a distributor tube in an inlet header of an evaporator, in which the orifices of the distributor tube are oriented in a direction opposite that of the direction of gravity. -
Fig. 3 shows a distributor tube in an inlet header of an evaporator, in which the orifices of the distributor tube are oriented in the direction of gravity. -
Fig. 4 shows a cross-section of the inlet header having a distributor tube with the liquid phase of refrigerant pressed-up against the interior surface of the distributor tube. -
Fig. 5 shows a refrigerant distributor tube having groups of two (2) orifices along the length of the distributor tube, wherein the orifices in each group are oriented 180 degrees apart from each other and the groups of two (2) orifices are rotated 90 degrees apart from each other. -
Fig. 6 shows a refrigerant distributor tube having groups of four (4) orifices along the length of the distributor tube, wherein the orifices in each group are oriented 90 degrees apart from each other. -
Fig. 7 shows a refrigerant distributor tube having a plurality of orifices spiraled along the tube at an exemplary 90 degrees between adjacent orifices. - For a typical slab coil design evaporator, the desired angle of the orifices of a distributor tube is selected based on testing of a vertical slab coil in which the refrigerant tubes are aligned in the direction of gravity with the inlet header lower than the outlet header. To accommodate the packaging constraints required for residential applications, a residential indoor evaporator may be constructed by using two slab coils in an A-Frame design or a single slab coil bent into an ARC design. Shown in
Figs. 1A-1C are representations of an end view of an A-Frame design or ARC design residentialindoor evaporator 10 having aninlet header 12a, anoutlet header 12b spaced apart from theinlet header 12a, and a plurality ofrefrigerant tubes 14 hydraulically connecting theheaders evaporator coil 16, partially shown inFigs. 2 and3 , is defined by the plurality ofrefrigerant tubes 14 together withexternal fins 15 interconnecting theadjacent refrigerant tubes 14. Theevaporator 10 includes adistributor tube 20 in theinlet header 12a, shown inFigs. 2-7 , for improved refrigerant distribution. The above mentioned components of theevaporator 10 are typically constructed of a heat conductive material such as aluminum. - Each of the A-Frame design and ARC design provides an
evaporator 10 having at least oneapex 18. The A-Frame or ARC design can be installed within a HVAC plenum in various orientations with respect to the direction of gravity, in which theapex 18 may be up, down, horizontal, and any other orientation therebetween. With these varieties of possible orientations, theinlet header 12a may be located above theoutlet header 12b, below theoutlet header 12b, or horizontal with the outlet header12b. Theheaders - A standard angle designed for the
orifices 22 of thedistribution tube 20 relative to therefrigerant tube 14 may not necessarily work efficiently when used in all the various potential orientations of theevaporator 10. It was found that only certain range of angles of theorifices 22 of thedistribution tube 20 relative to therefrigerant tube 14 are acceptable for each of thevarious evaporator coil 16 orientations. In other words, orifice angles are application specific; therefore, the desired orifice range of angles has to be calculated for each specific orientation of theevaporator 10. - With reference to
Figs. 2-4 , it is believed that theliquid phase 24 of a two-phase refrigerant flowing through thedistributor tube 20 tends to migrate to the bottom of theinterior surface 28 of thedistributor tube 20 due to gravity. It is suspected that theliquid phase 24 does not necessary puddle on the bottom or low spot of thedistribution tube 20, but instead it is pressed against and rides up a portion of theinterior surface 28 of thedistributor tube 20 by the flow of refrigerant through thedistributor tube 20, thereby forming a liquid refrigerantcross-sectional profile 30 much like a crescent moon with its apex on the bottom. The limit would be annular flow where the liquid distributes around the entire peripheralinternal surface 28 of thedistribution tube 20, but more typically a thicker layer would exist on the bottom. - It was found that if the
orifices 22 were facing in a direction other than between 45 to 315 degrees with respect to the opposite direction of gravity being 0 degree, mostly vapor phase refrigerant tend to exits theorifices 22 migrating toward therefrigerant tubes 14. This is undesirable because optimal heat transfer efficiency is obtained when the refrigerant entering the refrigerant tubes is in a substantially liquid phase. - With reference to
Fig. 3 , it was surprisingly found that when theorifices 22 are oriented substantially in the direction of gravity, the pressure and momentum of the refrigerant flowing through thedistributor tube 20 pushes the liquid phase refrigerant out of thedistributor tube 20 through theorifices 22 toward the refrigerant tubes. The refrigerant remains substantially in liquid phase until it reaches therefrigerant tubes 14, at which point the liquid phase refrigerant starts to absorb heat and vaporizes, thereby providing optimum heat transfer and even temperature distribution across theevaporator coil 16. With reference toFig. 4 , during periods of high refrigerant flow, the liquidrefrigerant cross-sectional profile 30 occupies theinterior surface 28 of thedistributor tube 20 from 45 to 315 degrees with respect to the opposite direction of gravity being 0 degree. During normal operating conditions, the liquid refrigerantcross-sectional profile 30 occupies theinterior surface 28 of thedistributor tube 20 from 90 to 270 degrees. - An aspect of the invention provides a means to transport the liquid phase refrigerant from the
distributor tube 20 to therefrigerant tubes 14 for efficient boiling and thus improved heat transfer performance regardless of the orientation of the A-Frame or ARC evaporator coil evaporator. This can be achieved by havingorifices 22 at angles from 45 to 315 degrees, preferably between 90 to 270 degrees, with respect to the opposite direction of gravity being 0 degree, along thedistributor tube 20 to ensure that at least one, but preferably a group, oforifices 22 is substantially oriented within the liquid refrigerantcross-sectional profile 30. By having one or more orifices within theliquid profile 30, the refrigerant flowing through thedistributor tube 20 will push the liquid phase refrigerant through theorifices 22 and toward the refrigerant tubes. -
Fig. 5 shows a cylindricalrefrigerant distributor tube 20 extending along a substantially central axis (A-axis). Pairs oforifices 22 are substantially uniformly spaced along the length of thedistributor tube 20, in which each pair oforifices 22 is located about its respective point on the A-axis. Within each pair oforifices 22, one of theorifices 22 may be oriented 90 to 180 degrees apart from the other with respect to the pair's respective point on the A-axis. Furthermore, each pair oforifices 22 may be rotated 90 to 180 degrees from the adjacent pair oforifices 22. -
Fig. 6 shows a cylindricalrefrigerant distributor tube 20 extending along the A-axis. Groups of four (4)orifices 22 are substantially uniformly spaced along the length of thedistributor tube 20, in which each group oforifices 22 is located about its respective point on the A-axis. Within each group of four (4)orifices 22, each of theorifices 22 may be oriented 90 degrees apart from theadjacent orifice 22 with respect to the group's respective point on the A-axis. Furthermore, each group of (4)orifices 22 may be rotated 45 degrees from the adjacent group of (4)orifices 22. -
Fig. 7 shows a cylindricalrefrigerant distributor tube 20 having a plurality oforifices 22 spiraled along the tube. With respect to an end view of the A-axis, each succeedingorifice 22 may be offset 45 to 180 degrees from the precedingorifice 22. - With the above configurations of
orifices 22 on thedistributor tube 20 or any configuration that provides at least oneorifice 22 in the desired direction regardless of the orientation of theevaporator 10 would improve the distribution of refrigerant though therefrigerant tubes 14. Therefore, if theevaporator coil 16 is positioned in any one of the various possible orientations, at least one of theorifices 22 would be located within the liquid refrigerantcross-sectional profile 30. - While this invention has been described in terms of the preferred embodiments thereof, it is not intended to be so limited, but rather only to the extent set forth in the claims that follow.
Claims (15)
- A heat exchanger assembly (10) for use with a two-phase refrigerant, comprising;
an inlet header (12a);
an outlet header (12b) spaced from said inlet header (12a);
a plurality of refrigerant tubes (14) hydraulically connecting said inlet header (12a) to said outlet header (12b);
a distributor tube (20) having a plurality of orifices (22) disposed in said inlet header (12a), wherein said orifices (22) are arranged along said distributor tube (20) such that at least one orifice (22) is oriented in the liquid phase (24) of the refrigerant pressed against said internal surface of said distributor tube (20) regardless of orientation of said heat exchanger assembly (10). - A heat exchanger assembly (10) of claim 1, wherein each of said plurality of orifices (22) is randomly positioned along said distributor tube (20).
- A heat exchanger assembly (10) of claim 1, wherein said plurality of orifices (22) is spirally positioned along said distributor tube (20) about a substantially center axis.
- A heat exchanger assembly (10) of claim 3, wherein each of said plurality of orifices (22) is off-set 45 to 180 degrees from adjacent said orifices (22), preferably 90 degrees from adjacent orifices (22).
- A heat exchanger assembly (10) of claim 3, wherein each of said plurality of orifices (22) is off-set 90 degrees or 180 degrees from adjacent orifices (22).
- A heat exchanger assembly (10) of claim 1,
wherein said distributor tube (20) extends along a substantially center axis and includes pairs of said orifices (22) spaced along said distributor tube (20);
wherein each of said pairs of orifices (22) is located about a respective point on said center axis. - A heat exchanger assembly (10) of claim 6, wherein said pair of orifices (22) includes one orifice that is 90 to 180 degrees apart from the other orifice.
- A heat exchanger assembly (10) of claim 6, wherein said pair of orifices (22) includes one orifice that is 90 degrees from the other orifice.
- A heat exchanger assembly (10) of claim 8, wherein each of said pairs of orifices (22) is 90 degrees rotated from adjacent said pairs of orifices (22).
- A heat exchanger assembly (10) of claim 8, wherein each of said pairs of orifices (22) is 180 degrees rotated from adjacent said pairs of orifices (22).
- A heat exchanger assembly (10) of claim 6, wherein said pair of orifices (22) includes one orifice that is 180 degrees from the other orifice.
- A heat exchanger assembly (10) of claim 11, wherein each of said pairs of orifices (22) is 90 degrees rotated from adjacent said pairs of orifices (22).
- A heat exchanger assembly (10) of claim 1,
wherein said distributor tube (20) extends along a substantially center axis and includes groups of 4 orifices (22) spaced along said distributor tube (20). - A heat exchanger assembly (10) of claim 13,
wherein each orifice within said group of 4 orifices (22) is 90 degrees from said adjacent orifices (22). - A heat exchanger assembly (10) of claim 14,
wherein each group of 4 orifices (22) is 45 degrees rotated from adjacent group of 4 orifices (22).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US35012310P | 2010-06-01 | 2010-06-01 | |
US13/114,405 US20110290465A1 (en) | 2010-06-01 | 2011-05-24 | Orientation insensitive refrigerant distributor tube |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2392886A2 true EP2392886A2 (en) | 2011-12-07 |
EP2392886A3 EP2392886A3 (en) | 2014-07-02 |
EP2392886B1 EP2392886B1 (en) | 2016-08-24 |
Family
ID=44583632
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11167680.5A Not-in-force EP2392886B1 (en) | 2010-06-01 | 2011-05-26 | Orientation insensitive refrigerant distributor tube |
Country Status (5)
Country | Link |
---|---|
US (1) | US20110290465A1 (en) |
EP (1) | EP2392886B1 (en) |
KR (1) | KR20110132273A (en) |
CN (1) | CN202216453U (en) |
BR (1) | BRPI1102318A8 (en) |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014124312A1 (en) * | 2013-02-08 | 2014-08-14 | Trane International Inc. | Microchannel heat exchanger |
WO2018100301A1 (en) | 2016-11-30 | 2018-06-07 | Valeo Systemes Thermiques | Device for mixing a refrigerant fluid inside a collector box of a heat exchanger |
WO2018100307A1 (en) | 2016-11-30 | 2018-06-07 | Valeo Systemes Thermiques | Device for distributing a refrigerant fluid inside a collector box of a heat exchanger |
WO2018100304A1 (en) | 2016-11-30 | 2018-06-07 | Valeo Systemes Thermiques | Device for distributing a coolant inside a collecting box of a heat exchanger |
WO2018100303A1 (en) | 2016-11-30 | 2018-06-07 | Valeo Systemes Thermiques | Box for collecting a refrigerant fluid, comprising at least one device for the angular positioning of a pipe |
WO2018100300A1 (en) | 2016-11-30 | 2018-06-07 | Valeo Systemes Thermiques | Device for distributing a refrigerant inside a collector box of a heat exchanger |
EP2784428B1 (en) | 2013-03-25 | 2019-02-20 | LG Electronics Inc. | Heat exchanger |
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- 2011-05-30 BR BRPI1102318A patent/BRPI1102318A8/en not_active Application Discontinuation
- 2011-05-30 CN CN2011202584714U patent/CN202216453U/en not_active Expired - Fee Related
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WO2019121699A1 (en) | 2017-12-19 | 2019-06-27 | Valeo Systemes Thermiques | Refrigerant fluid distribution device intended to be accommodated in a header of a heat exchanger |
WO2019121557A1 (en) | 2017-12-19 | 2019-06-27 | Valeo Systemes Thermiques | Header of a heat exchanger provided with a member for retention and/or angular positioning of a device for distribution of a refrigerant fluid |
WO2019121565A1 (en) | 2017-12-19 | 2019-06-27 | Valeo Systemes Thermiques | Header box of a heat exchanger accommodating a device for distribution of a cooling fluid, which device is retained by means of a centring unit |
US11441851B2 (en) | 2017-12-19 | 2022-09-13 | Valeo Systemes Thermiques | Refrigerant fluid distribution device intended to be accommodated in a header of a heat exchanger |
US11774193B2 (en) | 2017-12-19 | 2023-10-03 | Valeo Systemes Thermiques | Header of a heat exchanger provided with a member for retention and/or angular positioning of a device for distribution of a refrigerant fluid |
Also Published As
Publication number | Publication date |
---|---|
BRPI1102318A8 (en) | 2017-10-24 |
EP2392886A3 (en) | 2014-07-02 |
CN202216453U (en) | 2012-05-09 |
US20110290465A1 (en) | 2011-12-01 |
KR20110132273A (en) | 2011-12-07 |
EP2392886B1 (en) | 2016-08-24 |
BRPI1102318A2 (en) | 2012-11-20 |
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