US20090229282A1 - Parallel-flow evaporators with liquid trap for providing better flow distribution - Google Patents
Parallel-flow evaporators with liquid trap for providing better flow distribution Download PDFInfo
- Publication number
- US20090229282A1 US20090229282A1 US11/909,086 US90908605A US2009229282A1 US 20090229282 A1 US20090229282 A1 US 20090229282A1 US 90908605 A US90908605 A US 90908605A US 2009229282 A1 US2009229282 A1 US 2009229282A1
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- United States
- Prior art keywords
- refrigerant
- heat exchanger
- economizer
- liquid trap
- liquid
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- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25C—PRODUCING, WORKING OR HANDLING ICE
- F25C2500/00—Problems to be solved
- F25C2500/02—Geometry problems
Definitions
- This invention relates to a parallel-flow evaporator wherein a liquid trap is positioned upstream of an inlet manifold to provide better flow distribution among parallel channels, improved heat transfer and enhanced system reliability.
- Refrigerant systems are utilized to control the temperature and humidity of air in various indoor environments to be conditioned.
- a refrigerant is compressed in a compressor and delivered to a condenser (or an outdoor heat exchanger in this case).
- heat is exchanged between outside ambient air and the refrigerant.
- the refrigerant passes to an expansion device, at which the refrigerant is expanded to a lower pressure and temperature, and then to an evaporator (or an indoor heat exchanger if the system operates in the cooling mode).
- the evaporator heat is exchanged between the refrigerant and the indoor air, to condition the indoor air.
- the evaporator cools and typically dehumidifies the air that is being supplied to the indoor environment.
- a parallel-flow evaporator One type of evaporator that could be utilized in refrigerant systems is a parallel-flow evaporator.
- Such evaporators have several parallel channels for communicating refrigerant between an inlet manifold and an outlet manifold. Each channel typically has numerous parallel internal paths of various cross-sectional shape separated by internal walls. Corrugated fins are disposed in between the channels for heat transfer enhancement and structural rigidity.
- the channels, manifolds and fins are constructed from similar materials such as aluminum and are attached to each other by furnace brazing.
- parallel-flow evaporators have attracted a lot of attention and interest in the air-conditioning field due to their superior performance, compactness, rigid construction, and enhanced resistance to corrosion.
- Known parallel-flow evaporators typically have inlet and outlet manifolds that are cylindrical in shape.
- the channels are typically made of identical aluminum extrusions that form flat tubes.
- the vapor phase is often separated from the liquid phase. Since the two phases will move independently from each other after separation, the problem of refrigerant maldistribution often arises.
- a parallel-flow evaporator is provided with a liquid trap upstream of its inlet manifold.
- the refrigerant be moving at a speed such that the liquid phase will not separate from the vapor phase, it can flow through the trap, into the manifold, and into the evaporator channels in a generally equal distribution.
- the refrigerant be moving at reduced speed, such that separation of liquid is likely to occur, then the liquid will tend to separate and accumulate in the liquid trap. As the liquid accumulates in the liquid trap, the flow cross-sectional area for the remainder of the refrigerant will become smaller.
- a serpentine path provides by a number of such u-shaped structures is utilized.
- the refrigerant system is provided with an economizer circuit, and the liquid trap is utilized on a line directing the tapped two-phase refrigerant mixture into the economizer heat exchanger.
- This embodiment will provide the benefit and function as with regard to the first disclosed embodiment.
- FIG. 1 is a cross-sectional view of an evaporator incorporating the present invention.
- FIG. 2 shows the FIG. 1 evaporator in a different flow condition.
- FIG. 3 shows another embodiment.
- FIG. 4 shows yet another embodiment.
- a refrigerant system 20 is illustrated in FIG. 1 having a parallel-flow evaporator 22 .
- refrigerant moves from the evaporator 22 downstream to a compressor 24 , a condenser 26 , through an expansion device 28 , and back to the evaporator 22 .
- the refrigerant leaving the expansion device 28 is in a mixed vapor and liquid state.
- the evaporator 22 has a plurality of parallel channels 32 spaced along an inlet manifold 34 .
- the channels 32 and inlet manifold 34 are in fluid communication with each other. Further, the channels 32 are similarly positioned and communicated with an outlet manifold 35 . Fins 30 are disposed between the channels 32 .
- the channels 32 , fins 30 , inlet manifold 34 , and outlet manifold 35 are typically attached to each other by furnace brazing. As is known, air is passed over the fins 30 and channels 32 to be conditioned. Due to heat transfer interaction with air supplied to a conditioned space, refrigerant evaporates inside the channels 32 .
- the velocity of the refrigerant approaching the inlet manifold 34 may cause liquid refrigerant to separate from the vapor. This can result in a poor distribution of the two refrigerant phases among the channels 32 . As shown in FIG. 1 , the refrigerant is moving at an adequate velocity, and little or no separation of refrigerant phases occurs.
- a tube 36 leading into the inlet manifold 34 is positioned downstream of a liquid trap 38 .
- the liquid trap 38 generally extends vertically in a u-shape. Thus, any liquid that tends to separate will collect in the liquid trap 38 .
- the refrigerant velocity is insufficiently low in comparison to the FIG. 1 condition to prevent phase separation, and a certain quantity of liquid refrigerant 40 has collected in the trap 38 .
- the cross-sectional area 42 remaining for the flow of refrigerant decreases significantly. This in turn increases the velocity of the refrigerant passing to the inlet manifold 34 .
- the vapor refrigerant will tend to carry its liquid phase to the channels 32 in a homogeneous manner to ensure generally equal distribution. In effect, a jetting zone is created to increase velocity and limit additional phase separation.
- the present invention self-regulates the velocity of the refrigerant and ensures that other than the initial separation of a small quantity of liquid refrigerant 40 , the remaining liquid refrigerant will tend not to separate form the vapor phase resulting in homogeneous flow conditions in the inlet manifold 34 .
- the inlet manifold 34 should be of an appropriate cross-sectional area and length to sustain this flow homogeneity.
- the liquid trap 38 should be positioned in close proximity to the inlet manifold 34 .
- the liquid trap 38 should be located within 5 inches from the entrance to the inlet manifold 34 and extend vertically beneath it. Consequently, the evaporator performance is improved. This will also result in no liquid refrigerant in the evaporator outlet manifold 35 and system reliability enhancement.
- liquid trap 38 is shown in its simplest configuration, other arrangements (such as multiple u-shape segments connected together, local flow impedances, etc.) are also feasible.
- FIG. 3 Another embodiment 100 shown in FIG. 3 has a plurality of serial u-shaped traps 102 upstream of the portion 104 leading into the inlet manifold 34 .
- Each liquid trap 102 can collect small amount of liquid refrigerant, increasing velocity of the vapor phase and promoting homogeneous conditions at the entrance of the inlet manifold 34 .
- FIG. 4 Another refrigerant system embodiment 110 is illustrated in FIG. 4 .
- a compressor 112 delivers a compressed refrigerant to a condenser 114 .
- a line 116 is tapped off of a main refrigerant flow line 126 , and passed through an economizer expansion device 118 .
- a liquid trap 120 regulates the refrigerant passing through an inlet 122 , to an economizer heat exchanger 124 .
- the liquid trap 120 will provide the function and will operate as described with regard to the FIG. 1 and FIG. 2 embodiments.
- the economizer heat exchanger 124 is structured to have adjacent channels such that heat is exchanged between the refrigerant in the tap line 116 and the refrigerant in the main flow line 126 .
- the main flow line 126 delivers refrigerant to an outlet 128 and passes it through a main expansion device 130 to an evaporator 132 .
- the present invention can utilize the liquid trap with both the economizer heat exchanger 124 , and the evaporator 132 .
- the refrigerant returns from the evaporator 132 back to the compressor 112 .
- a line 134 downstream of the economizer heat exchanger 124 returns the tapped refrigerant back to an intermediate compression point in the compressor 112 .
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A parallel-flow evaporator has a liquid trap for regulating velocity of refrigerant delivered to an evaporator from an expansion device. In its simplest configuration, the liquid trap is a u-shaped pipe positioned vertically and connected to an inlet manifold of the evaporator. By providing a liquid trap, a small amount of liquid refrigerant separates from the vapor phase at certain conditions. This separated liquid will tend to collect in the trap, and reduce a flow cross-sectional area of the line leading to the inlet manifold of the evaporator. As this cross-sectional area decreases, the velocity of the refrigerant passing through the line will increase. In this sense, as a small amount of liquid phase separates out, it will ensure that the velocity of the remaining refrigerant will increase such that further separation will be significantly reduced or entirely avoided. As a result, homogeneous refrigerant flow is provided to the evaporator, resulting in its performance enhancement and system reliability improvement.
Description
- This invention relates to a parallel-flow evaporator wherein a liquid trap is positioned upstream of an inlet manifold to provide better flow distribution among parallel channels, improved heat transfer and enhanced system reliability.
- Refrigerant systems are utilized to control the temperature and humidity of air in various indoor environments to be conditioned. In a typical refrigerant system operating in the cooling mode, a refrigerant is compressed in a compressor and delivered to a condenser (or an outdoor heat exchanger in this case). In the condenser, heat is exchanged between outside ambient air and the refrigerant. From the condenser, the refrigerant passes to an expansion device, at which the refrigerant is expanded to a lower pressure and temperature, and then to an evaporator (or an indoor heat exchanger if the system operates in the cooling mode). In the evaporator, heat is exchanged between the refrigerant and the indoor air, to condition the indoor air. When the refrigerant system is operating in the cooling mode, the evaporator cools and typically dehumidifies the air that is being supplied to the indoor environment.
- One type of evaporator that could be utilized in refrigerant systems is a parallel-flow evaporator. Such evaporators have several parallel channels for communicating refrigerant between an inlet manifold and an outlet manifold. Each channel typically has numerous parallel internal paths of various cross-sectional shape separated by internal walls. Corrugated fins are disposed in between the channels for heat transfer enhancement and structural rigidity. Usually, the channels, manifolds and fins are constructed from similar materials such as aluminum and are attached to each other by furnace brazing. Recently, parallel-flow evaporators have attracted a lot of attention and interest in the air-conditioning field due to their superior performance, compactness, rigid construction, and enhanced resistance to corrosion. However, one concern with parallel-flow evaporators is maldistribution of the refrigerant among their channels. The maldistribution problem in the parallel-flow evaporators is typically caused by the liquid phase separating from the vapor in the inlet manifold due to gravity combined with insufficient refrigerant velocity, and thus manifests itself in unequal amounts of vapor and liquid refrigerant passing through the evaporator channels. Additional phenomena effecting maldistribution can be attributed to different distances the refrigerant must flow to reach various channels and to exit them, unequal pressure impedances and variations in the heat transfer rates between the channels, etc.
- Known parallel-flow evaporators typically have inlet and outlet manifolds that are cylindrical in shape. The channels are typically made of identical aluminum extrusions that form flat tubes. As the two-phase refrigerant enters the inlet manifold, the vapor phase is often separated from the liquid phase. Since the two phases will move independently from each other after separation, the problem of refrigerant maldistribution often arises.
- When such maldistribution occurs, the heat exchanger performance drops significantly, frequently resulting in liquid refrigerant leaving the outlet manifold. This liquid refrigerant can cause serious reliability problems and permanent compressor damage. Obviously, this is undesirable.
- In a disclosed embodiment of this invention, a parallel-flow evaporator is provided with a liquid trap upstream of its inlet manifold. In this manner, should the refrigerant be moving at a speed such that the liquid phase will not separate from the vapor phase, it can flow through the trap, into the manifold, and into the evaporator channels in a generally equal distribution. However, should the refrigerant be moving at reduced speed, such that separation of liquid is likely to occur, then the liquid will tend to separate and accumulate in the liquid trap. As the liquid accumulates in the liquid trap, the flow cross-sectional area for the remainder of the refrigerant will become smaller. Since the flow cross-sectional area becomes smaller, then the refrigerant velocity will increase, creating a jetting effect that will carry droplets of liquid into the inlet manifold and will limit further phase separation. This phenomenon will be self-regulating, to ensure that an adequate refrigerant velocity will be maintained such that the refrigerant liquid will tend not to separate from the vapor.
- In one embodiment, rather than having a single u-shaped trap, a serpentine path provides by a number of such u-shaped structures is utilized.
- In another disclosed embodiment, the refrigerant system is provided with an economizer circuit, and the liquid trap is utilized on a line directing the tapped two-phase refrigerant mixture into the economizer heat exchanger. This embodiment will provide the benefit and function as with regard to the first disclosed embodiment.
- These and other features of the present invention can be best understood from the following specification and drawings, the following of which is a brief description.
-
FIG. 1 is a cross-sectional view of an evaporator incorporating the present invention. -
FIG. 2 shows theFIG. 1 evaporator in a different flow condition. -
FIG. 3 shows another embodiment. -
FIG. 4 shows yet another embodiment. - A
refrigerant system 20 is illustrated inFIG. 1 having a parallel-flow evaporator 22. As is known, refrigerant moves from the evaporator 22 downstream to acompressor 24, acondenser 26, through anexpansion device 28, and back to the evaporator 22. The refrigerant leaving theexpansion device 28 is in a mixed vapor and liquid state. The evaporator 22 has a plurality ofparallel channels 32 spaced along aninlet manifold 34. Thechannels 32 andinlet manifold 34 are in fluid communication with each other. Further, thechannels 32 are similarly positioned and communicated with anoutlet manifold 35. Fins 30 are disposed between thechannels 32. Thechannels 32,fins 30,inlet manifold 34, andoutlet manifold 35 are typically attached to each other by furnace brazing. As is known, air is passed over thefins 30 andchannels 32 to be conditioned. Due to heat transfer interaction with air supplied to a conditioned space, refrigerant evaporates inside thechannels 32. - As mentioned above, should the velocity of the refrigerant approaching the
inlet manifold 34 be insufficiently low, it may cause liquid refrigerant to separate from the vapor. This can result in a poor distribution of the two refrigerant phases among thechannels 32. As shown inFIG. 1 , the refrigerant is moving at an adequate velocity, and little or no separation of refrigerant phases occurs. - A
tube 36 leading into theinlet manifold 34 is positioned downstream of aliquid trap 38. As illustrated, theliquid trap 38 generally extends vertically in a u-shape. Thus, any liquid that tends to separate will collect in theliquid trap 38. - As shown in
FIG. 2 , the refrigerant velocity is insufficiently low in comparison to theFIG. 1 condition to prevent phase separation, and a certain quantity ofliquid refrigerant 40 has collected in thetrap 38. As a result, thecross-sectional area 42 remaining for the flow of refrigerant decreases significantly. This in turn increases the velocity of the refrigerant passing to theinlet manifold 34. As the velocity of the refrigerant flow increases, the vapor refrigerant will tend to carry its liquid phase to thechannels 32 in a homogeneous manner to ensure generally equal distribution. In effect, a jetting zone is created to increase velocity and limit additional phase separation. Thus, by including theliquid trap 38 upstream of theheader 34, the present invention self-regulates the velocity of the refrigerant and ensures that other than the initial separation of a small quantity ofliquid refrigerant 40, the remaining liquid refrigerant will tend not to separate form the vapor phase resulting in homogeneous flow conditions in theinlet manifold 34. Of course, theinlet manifold 34 should be of an appropriate cross-sectional area and length to sustain this flow homogeneity. Also, theliquid trap 38 should be positioned in close proximity to theinlet manifold 34. Preferably, theliquid trap 38 should be located within 5 inches from the entrance to theinlet manifold 34 and extend vertically beneath it. Consequently, the evaporator performance is improved. This will also result in no liquid refrigerant in theevaporator outlet manifold 35 and system reliability enhancement. - While this invention is disclosed in a conventional evaporator, other heat exchangers, for instance economizer heat exchangers (or so-called brazed plate heat exchangers) also performing an evaporator function, may equally benefit from this invention.
- Further, although the
liquid trap 38 is shown in its simplest configuration, other arrangements (such as multiple u-shape segments connected together, local flow impedances, etc.) are also feasible. - Another
embodiment 100 shown inFIG. 3 has a plurality of serialu-shaped traps 102 upstream of theportion 104 leading into theinlet manifold 34. Eachliquid trap 102 can collect small amount of liquid refrigerant, increasing velocity of the vapor phase and promoting homogeneous conditions at the entrance of theinlet manifold 34. - Another
refrigerant system embodiment 110 is illustrated inFIG. 4 . In this embodiment, acompressor 112 delivers a compressed refrigerant to acondenser 114. Aline 116 is tapped off of a mainrefrigerant flow line 126, and passed through aneconomizer expansion device 118. Aliquid trap 120 regulates the refrigerant passing through aninlet 122, to aneconomizer heat exchanger 124. Theliquid trap 120 will provide the function and will operate as described with regard to theFIG. 1 andFIG. 2 embodiments. It should be understood that theeconomizer heat exchanger 124 is structured to have adjacent channels such that heat is exchanged between the refrigerant in thetap line 116 and the refrigerant in themain flow line 126. Themain flow line 126 delivers refrigerant to anoutlet 128 and passes it through amain expansion device 130 to anevaporator 132. The present invention can utilize the liquid trap with both theeconomizer heat exchanger 124, and theevaporator 132. The refrigerant returns from theevaporator 132 back to thecompressor 112. Aline 134 downstream of theeconomizer heat exchanger 124 returns the tapped refrigerant back to an intermediate compression point in thecompressor 112. - It has to be pointed out that although all inlet manifolds are shown in a horizontal configuration, the maldistribution phenomenon is more pronounced in a vertical orientation. In such circumstances, the benefits of the present invention become even more pronounced.
- Although a preferred embodiment of this invention has been disclosed, a worker of ordinary skill in this art would recognize that certain modifications would come within the scope of this invention. For that reason, the following claims should be studied to determine the true scope and content of this invention.
Claims (15)
1. A refrigerant system comprising:
a compressor delivering a compressed refrigerant to a condenser, refrigerant passing from said condenser to an expansion device, and from said expansion device to an evaporator, said evaporator comprising an inlet manifold, outlet manifold, a plurality of channels receiving refrigerant from said inlet manifold and delivering it to said outlet manifold, and fins disposed between said channels; and
a line connecting said expansion device and said evaporator, said line being provided with a liquid trap to collect liquid separated out of a vapor refrigerant passing from said expansion device to said evaporator.
2. The refrigerant system as set forth in claim 1 , wherein said liquid trap extends vertically beneath said inlet manifold.
3. The refrigerant system as set forth in claim 1 , wherein said liquid trap is generally provided by a u-shape downwardly extending portion of said line.
4. The refrigerant system as set forth in claim 1 , wherein said liquid trap is positioned within 5 inches from said inlet manifold.
5. The refrigerant system as set forth in claim 1 , wherein said refrigerant system is also provided with an economizer circuit, said economizer circuit having an economizer heat exchanger, and said economizer heat exchanger being provided with a tap line connecting a main flow line through an economizer expansion device, and then into said economizer heat exchanger, said tap line being returned to an intermediate compression point in said compressor downstream of said economizer heat exchanger, and a liquid trap to collect liquid separated out of a vapor refrigerant passing from said economizer expansion device to said economizer heat exchanger.
6. The refrigerant system as set forth in claim 1 , wherein said liquid trap includes a plurality of serially spaced u-shaped liquid trap portions.
7. A method of operating a refrigerant system comprising the steps of:
providing an evaporator having a plurality of tubes receiving refrigerant from an inlet manifold, and delivering said refrigerant to an outlet manifold, and from said outlet manifold to compressor, said compressor delivering the refrigerant to a condenser, and said refrigerant passing from said condenser to an expansion device, and then back to said evaporator, and providing a fluid line connecting said expansion device to said evaporator, said fluid line being provided with a liquid trap to capture liquid that has separated from a vapor refrigerant; and
passing refrigerant through said refrigerant system and such that liquid trap self-regulates a velocity of refrigerant as the liquid separates from the vapor refrigerant to deliver refrigerant into said inlet manifold in a predominantly homogeneous state.
8. The method as set forth in claim 7 , wherein the refrigerant system further being provided with an economizer circuit, said economizer circuit including an economizer heat exchanger, and tapping refrigerant and passing the tapped refrigerant through an economizer expansion device into said economizer heat exchanger, and a liquid trap provided to capture liquid that has separated from a vapor passing from said economizer expansion device into said economizer heat exchanger, and further including the steps of passing refrigerant through said economizer expansion device, and to said economizer heat exchanger, such that said liquid trap self-regulates a velocity of refrigerant as the liquid separates from the vapor refrigerant to deliver refrigerant into said economizer heat exchanger in a predominantly homogeneously state.
9. A heat exchanger and fluid line system comprising:
a fluid line leading into an inlet manifold;
a liquid trap on said fluid line; and
a heat exchanger having a plurality of channels receiving a fluid from said inlet manifold.
10. The heat exchanger and fluid line system as set forth in claim 9 , wherein said heat exchanger is a refrigerant system evaporator.
11. The heat exchanger and fluid line system as set forth in claim 9 , wherein said heat exchanger is a refrigerant system economizer heat exchanger.
12. The heat exchanger and fluid line system as set forth in claim 9 , wherein said liquid trap extends vertically beneath said inlet manifold.
13. The heat exchanger and fluid line system as set forth in claim 9 , wherein said liquid trap is generally provided by a u-shape downwardly extending portion of said line.
14. The heat exchanger and fluid line system as set forth in claim 9 , wherein said liquid trap is positioned within 5 inches from said inlet manifold.
15. The heat exchanger and fluid line system as set forth in claim 9 , wherein said liquid trap is provided by a plurality of serially spaced u-shaped structures.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/US2005/018349 WO2006127001A2 (en) | 2005-05-24 | 2005-05-24 | Parallel-flow evaporators with liquid trap for providing better flow distribution |
Publications (1)
Publication Number | Publication Date |
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US20090229282A1 true US20090229282A1 (en) | 2009-09-17 |
Family
ID=37452484
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US11/909,086 Abandoned US20090229282A1 (en) | 2005-05-24 | 2005-05-24 | Parallel-flow evaporators with liquid trap for providing better flow distribution |
Country Status (10)
Country | Link |
---|---|
US (1) | US20090229282A1 (en) |
EP (1) | EP1883771A4 (en) |
JP (1) | JP2008542677A (en) |
CN (1) | CN100554833C (en) |
AU (1) | AU2005332040B2 (en) |
BR (1) | BRPI0520260A2 (en) |
CA (1) | CA2604466A1 (en) |
HK (1) | HK1120600A1 (en) |
MX (1) | MX2007012510A (en) |
WO (1) | WO2006127001A2 (en) |
Cited By (6)
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US20110042047A1 (en) * | 2008-05-14 | 2011-02-24 | Carrier Corporation | Heat exchanger drip tube |
US20120210744A1 (en) * | 2011-02-22 | 2012-08-23 | Colmac Coil Manufacturing, Inc. | Refrigerant distributor |
US20130256423A1 (en) * | 2011-11-18 | 2013-10-03 | Richard G. Lord | Heating System Including A Refrigerant Boiler |
US20140158332A1 (en) * | 2009-01-25 | 2014-06-12 | Alcoil Usa Llc | Heat exchanger |
CN103900164A (en) * | 2014-03-31 | 2014-07-02 | 华南理工大学 | Air-conditioning outdoor unit capable of reducing refrigerant charge and method implemented by air-conditioning outdoor unit |
US20170234597A1 (en) * | 2009-05-12 | 2017-08-17 | Reflect Scientific, Inc | Extremely fast freezing, low-temperature blast freezer |
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CN104315758B (en) * | 2014-10-20 | 2016-09-07 | 广东美的制冷设备有限公司 | Air-conditioner and parallel-flow evaporator thereof |
JP6997048B2 (en) * | 2018-07-30 | 2022-01-17 | ダイハツ工業株式会社 | Vehicle air conditioner |
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JPS56153776U (en) * | 1980-04-17 | 1981-11-17 | ||
JPS56146961A (en) * | 1980-04-17 | 1981-11-14 | Mitsubishi Electric Corp | Cooler |
JPH0579725A (en) * | 1991-09-18 | 1993-03-30 | Nippondenso Co Ltd | Multiple path type evaporator |
JPH06307737A (en) * | 1993-04-23 | 1994-11-01 | Nippondenso Co Ltd | Refrigerant vaporizer |
JPH07190520A (en) * | 1993-12-27 | 1995-07-28 | Kobe Steel Ltd | Freezer |
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JP2002048484A (en) * | 2000-07-31 | 2002-02-15 | Kyoritsu Reinetsu Kk | Refrigerant circulating route of natural circulation type heat pump |
JP4249380B2 (en) * | 2000-08-17 | 2009-04-02 | 三菱電機株式会社 | Air conditioner |
JP3906830B2 (en) * | 2003-09-17 | 2007-04-18 | 三菱電機株式会社 | Natural circulation cooling device and heat exchange method using natural circulation cooling device |
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2005
- 2005-05-24 US US11/909,086 patent/US20090229282A1/en not_active Abandoned
- 2005-05-24 BR BRPI0520260-4A patent/BRPI0520260A2/en not_active IP Right Cessation
- 2005-05-24 MX MX2007012510A patent/MX2007012510A/en active IP Right Grant
- 2005-05-24 JP JP2008513439A patent/JP2008542677A/en not_active Ceased
- 2005-05-24 CA CA002604466A patent/CA2604466A1/en not_active Abandoned
- 2005-05-24 EP EP05753677A patent/EP1883771A4/en not_active Withdrawn
- 2005-05-24 CN CNB200580049875XA patent/CN100554833C/en not_active Expired - Fee Related
- 2005-05-24 WO PCT/US2005/018349 patent/WO2006127001A2/en active Application Filing
- 2005-05-24 AU AU2005332040A patent/AU2005332040B2/en not_active Ceased
-
2008
- 2008-11-06 HK HK08112196.9A patent/HK1120600A1/en not_active IP Right Cessation
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US3528260A (en) * | 1968-08-30 | 1970-09-15 | Gen Motors Corp | Refrigeration apparatus with components connected by chlorinated polyethylene hoses |
US4290266A (en) * | 1979-09-04 | 1981-09-22 | Twite Terrance M | Electrical power generating system |
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US5901782A (en) * | 1994-10-24 | 1999-05-11 | Modine Manufacturing Co. | High efficiency, small volume evaporator for a refrigerant |
US5937670A (en) * | 1997-10-09 | 1999-08-17 | International Comfort Products Corporation (Usa) | Charge balance device |
US6817205B1 (en) * | 2003-10-24 | 2004-11-16 | Carrier Corporation | Dual reversing valves for economized heat pump |
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US20110042047A1 (en) * | 2008-05-14 | 2011-02-24 | Carrier Corporation | Heat exchanger drip tube |
US20140158332A1 (en) * | 2009-01-25 | 2014-06-12 | Alcoil Usa Llc | Heat exchanger |
US20170234597A1 (en) * | 2009-05-12 | 2017-08-17 | Reflect Scientific, Inc | Extremely fast freezing, low-temperature blast freezer |
US10188098B2 (en) * | 2009-05-12 | 2019-01-29 | Reflect Scientific Inc. | Extremely fast freezing, low-temperature blast freezer |
US20120210744A1 (en) * | 2011-02-22 | 2012-08-23 | Colmac Coil Manufacturing, Inc. | Refrigerant distributor |
US8783057B2 (en) * | 2011-02-22 | 2014-07-22 | Colmac Coil Manufacturing, Inc. | Refrigerant distributor |
US20130256423A1 (en) * | 2011-11-18 | 2013-10-03 | Richard G. Lord | Heating System Including A Refrigerant Boiler |
US11029040B2 (en) | 2011-11-18 | 2021-06-08 | Carrier Corporation | Heating system including a refrigerant boiler |
CN103900164A (en) * | 2014-03-31 | 2014-07-02 | 华南理工大学 | Air-conditioning outdoor unit capable of reducing refrigerant charge and method implemented by air-conditioning outdoor unit |
Also Published As
Publication number | Publication date |
---|---|
MX2007012510A (en) | 2007-11-09 |
HK1120600A1 (en) | 2009-04-03 |
EP1883771A4 (en) | 2011-12-21 |
WO2006127001A3 (en) | 2007-01-18 |
AU2005332040A1 (en) | 2006-11-30 |
CA2604466A1 (en) | 2006-11-30 |
EP1883771A2 (en) | 2008-02-06 |
CN100554833C (en) | 2009-10-28 |
JP2008542677A (en) | 2008-11-27 |
AU2005332040B2 (en) | 2009-07-02 |
WO2006127001A2 (en) | 2006-11-30 |
CN101180506A (en) | 2008-05-14 |
BRPI0520260A2 (en) | 2009-09-15 |
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