US20080190591A1 - Low charge refrigerant flooded evaporator - Google Patents
Low charge refrigerant flooded evaporator Download PDFInfo
- Publication number
- US20080190591A1 US20080190591A1 US11/695,413 US69541307A US2008190591A1 US 20080190591 A1 US20080190591 A1 US 20080190591A1 US 69541307 A US69541307 A US 69541307A US 2008190591 A1 US2008190591 A1 US 2008190591A1
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- United States
- Prior art keywords
- shell
- tubes
- refrigerant
- beads
- evaporator
- 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.)
- Abandoned
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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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
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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
- F28D21/0017—Flooded core heat exchangers
-
- 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
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/1607—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with particular pattern of flow of the heat exchange media, e.g. change of flow direction
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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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
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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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/02—Details of evaporators
- F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
- F25B2339/0242—Evaporators with refrigerant in a vessel in which is situated a heat exchanger having tubular elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2235/00—Means for filling gaps between elements, e.g. between conduits within casings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2275/00—Fastening; Joining
- F28F2275/20—Fastening; Joining with threaded elements
- F28F2275/205—Fastening; Joining with threaded elements with of tie-rods
Definitions
- the present invention relates to shell and tube flooded evaporators for refrigeration applications.
- a shell and tube flooded evaporator is an integral part of a refrigeration system.
- a typical refrigeration system there is an evaporator that cools the process fluid at the expense of boiling the refrigerant that is at a lower saturation temperature and pressure, a compressor that compresses the boiled off refrigerant to an elevated pressure and temperature, a condenser uses a cooling medium to condense the high pressure refrigerant to liquid phase at the expense of heating the cooling medium, and an expansion device that drops down the pressure of the condensed refrigerant back to the low side which then enters the evaporator to repeat the above cycle again.
- This cycle is called the reverse Rankine cycle.
- Such refrigeration systems are found in a variety of installations, such as food processing plants.
- a shell and tube flooded evaporator has a shell with tubes extending through the shell.
- the tubes carry the process fluid.
- the shell of the evaporator is flooded with the refrigerant.
- the liquid refrigerant typically enters the bottom of the shell, contacts the tubes, which tubes carry the hot process fluid.
- the refrigerant vaporizes and exits the shell at the top.
- Refrigerants are typically natural, such as ammonia or propane. Synthetic refrigerants are falling out of favor due to environmental concerns. However, even natural refrigerants have drawbacks; ammonia is toxic and propane is flammable.
- FIG. 1 is a frontal view of an even-pass (four pass) flooded shell and tube evaporator, partially cut away.
- FIG. 2 is a side or end view of the flooded shell and tube evaporator of FIG. 1 .
- FIG. 3 is a frontal view of an odd-pass (three pass) flooded shell and tube evaporator, partially cut away.
- FIG. 4 is a side or end view of the flooded shell and tube evaporator of FIG. 3 .
- FIG. 5 is a cross-sectional view of a tube bundle of the evaporator of FIG. 1 taken at section A-A.
- FIG. 6 is a frontal view of a partially cut away flooded shell and tube evaporator of the present invention.
- FIG. 7 is a detailed cross-sectional view of tubes and filler beads.
- a shell and tube evaporator is shown with a plurality of parallel tubes 6 in horizontal orientation.
- the tubes 6 are received at each end by two end plates 3 (round or rectangular in shape) called tube sheets.
- Each tube sheet 3 has a plurality of parallel holes that are machined at a specific distance with respect to each other according to industry standards, viz., Tubular Exchanger Manufacturers Association, TEMA.
- the tubes are further supported by baffles or tube supports 7 within the span between the tube sheets 3 .
- the distance between the adjacent baffles or tube supports 7 is determined according to industry standards, e.g., Tubular Exchanger Manufacturers Association, TEMA.
- the baffles or tube supports 7 have a hole pattern identical to the tube sheets 3 as shown in FIG. 5 (larger scale).
- the combination of tube sheets 3 , the tubes 6 , the baffles or tube supports 7 and the tie-rods 9 is also known as tube bundle and is welded to the shell 4 at each end, 19 and 20 , hence isolating the shell side 16 from the tube side 17 .
- the tube side 19 is confined by front and rear heads 1 , 2 .
- the tubes 6 are individually joined to the tube sheets 3 at the corresponding holes in the tube sheets 3 via mechanical means or welding.
- the process fluid such as water or brine or any other fluid to be cooled enters the tube side 17 at the front head 1 (attached to tubes sheets 3 through bolting 5 or welding) via inlet port 10 .
- the heads 1 and 2 could be arranged for multiple pass or single pass configuration.
- the front head 1 and the rear head 2 carry pass partition plates 14 at the corresponding lane 21 on the tube sheets 3 that directs the process fluid in the tubes 6 back and forth through a respective quantity of tubes in each pass until the fluid exits at head 1 via port 11 for even-pass configuration as shown in FIG. 1 and FIG. 2 or at head 2 for odd-pass configuration as shown in FIG. 3 and FIG. 4 via exit port 11 .
- the process fluid entering at inlet port 10 is hot, while the process fluid exiting at outlet port 12 is cooled.
- Low temperature and low pressure liquid or liquid-gas mixture of refrigerant enters the shell side 16 via port 12 .
- the refrigerant travels upwards it extracts heat from the hot fluid in the tubes 6 and progressively evaporates.
- the vapor/liquid ratio increases along the height of the tube bundle.
- the wet vapor exits the shell side 16 via risers 15 and enters the separator 8 and leaves the separator 8 as liquid-free vapor via port 13 .
- the refrigerant vapor is routed to the compressor (not shown), where the refrigerant is compressed. From the compressor, the refrigerant, which is hot, is cooled in the condenser. After leaving the condenser, the pressure of the refrigerant is dropped by an expansion device, wherein the refrigerant reenters the shell 4 at port 12 .
- the tubes 6 are spaced apart from each other, thus creating gaps 31 between the tubes.
- the refrigerant flows through these gaps 31 .
- the tubes are grouped into the sections, with each section representing a pass through the shell.
- section I is the first pass of the process fluid through the shell, from the inlet port 10 and the front head 1 to the rear head 2 .
- Section II is the second pass, from the rear head 2 back to the front head 1 .
- Section III is the third pass, from the front head 1 to the rear head 2 .
- Section IV is the fourth pass, from the rear head 2 to the front head 1 and the outlet port 11 .
- the tubes within a section are separated from each other by a relatively small gap 31 .
- the tubes in adjacent sections are separated from each other by a larger gap, or lane 21 , in order to accommodate the pass partition plates 14 .
- these gaps 31 , 21 which represent the interior volume of the shell, are filled with refrigerant.
- filler beads 35 much of the interior volume of the shell is filled with filler beads 35 (see FIGS. 6 and 7 ).
- the filler beads have a neutral buoyancy when immersed in the refrigerant 33 . This minimizes the possibility of the beads accumulating at the bottom of the shell (if negative buoyancy) or at the top (if positive buoyancy) as assures the even distribution of the filler beads throughout the shell.
- the density of the filler beads 35 could be the same as the density of the refrigerant. Because the refrigerant changes from a liquid state to a vapor state, the density of the refrigerant changes.
- the filler beads can have a neutral buoyancy relative to the liquid refrigerant.
- the filler beads in the preferred embodiment are made of solid plastic.
- the filler beads remain solid and do not turn to liquid inside of the shell.
- the filler beads 35 are spherical, although the beads could be of any shape.
- the filler beads are solid and not hollow. Solid beads are easier to manufacture and easier to match neutral buoyancy with the refrigerant.
- the filler beads 35 are of different sizes. In the preferred embodiment, there are at least three sizes 35 A, 35 B, 35 C (see FIG. 7 ).
- the largest size bead 35 A is small enough to pass through the gaps 31 between adjacent tubes 6 in a section. Thus, the diameter of the largest size bead is less than P-D, where P is the tube pitch and D is the tube outside diameter.
- one type of flooded evaporator has gaps between tubes of 3/16 inches.
- the largest size filler bead 35 A is less than 3/16 inches.
- the intermediate size beads 35 B and the smallest size beads 35 C are sized relative to the largest size beads so as to fit within the spaces of the adjacent largest size beads 35 A.
- the filler beads 35 displace refrigerant inside of the shell 4 .
- the filler beads are located in the gaps 31 , 21 between the tubes.
- the filler beads have the same isothermic state as the refrigerant and consequently are thermally inert.
- the amount of filler beads inside the shell depends on how efficient the evaporator is to be. For example, filler beads can displace 10% of the volume inside of the shell, thus reducing the volume of refrigerant. Higher evaporator efficiencies can be achieved by using more filler beads. It is believed that up to one half to two thirds of the shell volume can be taken up by filler beads 35 . As described below, it is desirable not to overfill the shell with beads to the extent that the beads are immobile. It is desired if the beads can move inside of the shell.
- the filler beads 35 can be put into an evaporator before the evaporator's initial operation.
- an evaporator can be retrofitted with the filler beads. If retrofitted, the beads will quickly reach the same temperature as the refrigerant.
- the refrigerant 33 flows through the spaces 37 between the filler beads 35 and consequently through the gaps 31 between the tubes.
- the filler beads form a structure similar to sponges, with voids formed by the filler beads.
- the filler beads channel the refrigerant through the spaces or gaps between the beads.
- the filler beads 35 move and disperse the refrigerant resulting in enhanced heat exchange and refrigerant distribution.
- the filler beads contact and scrub the outside diameter of the tubes 6 . This is useful in dislodging bubbles 39 that are formed on the outside of tubes 6 as the refrigerant boils. A bubble 39 on a tube decreases the heat exchange at that particular location on the tube. Dislodging the bubble increases the heat exchange.
- An evaporator equipped with the filler beads is more efficient and utilizes less refrigerant than prior art evaporators.
- the size of the evaporator can be reduced, saving material costs and also floor space.
- the evaporator requires a lower charge of refrigerant for the same heat exchange capacity when compared to the prior art. The requirement of less refrigerant results in a savings in startup and maintenance cost. In addition, any accidental release of refrigerant is less dangerous as there is less refrigerant to release.
Abstract
A flooded evaporator has a plurality of tubes extending through a shell. Process fluid flows through the tubes and refrigerant flows inside of the shell through gaps between the tubes. Filler beads are located in the gaps between the tubes, thus displacing some of the refrigerant and requiring a lower refrigerant charge. The refrigerant flows through the spaces between the filler beads. The filler beads move thereby dispersing the refrigerant and dislodging bubbles from the outside of the tubes, resulting in an increase in efficiency of heat exchange.
Description
- This application claims the benefit of U.S. provisional application Ser. No. 60/900,139, filed Feb. 8, 2007.
- The present invention relates to shell and tube flooded evaporators for refrigeration applications.
- A shell and tube flooded evaporator is an integral part of a refrigeration system. In a typical refrigeration system there is an evaporator that cools the process fluid at the expense of boiling the refrigerant that is at a lower saturation temperature and pressure, a compressor that compresses the boiled off refrigerant to an elevated pressure and temperature, a condenser uses a cooling medium to condense the high pressure refrigerant to liquid phase at the expense of heating the cooling medium, and an expansion device that drops down the pressure of the condensed refrigerant back to the low side which then enters the evaporator to repeat the above cycle again. This cycle is called the reverse Rankine cycle.
- Such refrigeration systems are found in a variety of installations, such as food processing plants.
- A shell and tube flooded evaporator has a shell with tubes extending through the shell. The tubes carry the process fluid. The shell of the evaporator is flooded with the refrigerant. The liquid refrigerant typically enters the bottom of the shell, contacts the tubes, which tubes carry the hot process fluid. The refrigerant vaporizes and exits the shell at the top.
- Refrigerants are typically natural, such as ammonia or propane. Synthetic refrigerants are falling out of favor due to environmental concerns. However, even natural refrigerants have drawbacks; ammonia is toxic and propane is flammable.
- It is desirable to design an evaporator that has a higher efficiency than found in the prior art. A more efficient evaporator would use less refrigerant, thus minimizing any danger from an accidental refrigerant release. In addition, a more efficient evaporator would be physically smaller, taking up a smaller footprint on a factory or plant floor, thus saving money.
-
FIG. 1 is a frontal view of an even-pass (four pass) flooded shell and tube evaporator, partially cut away. -
FIG. 2 is a side or end view of the flooded shell and tube evaporator ofFIG. 1 . -
FIG. 3 is a frontal view of an odd-pass (three pass) flooded shell and tube evaporator, partially cut away. -
FIG. 4 is a side or end view of the flooded shell and tube evaporator ofFIG. 3 . -
FIG. 5 is a cross-sectional view of a tube bundle of the evaporator ofFIG. 1 taken at section A-A. -
FIG. 6 is a frontal view of a partially cut away flooded shell and tube evaporator of the present invention. -
FIG. 7 is a detailed cross-sectional view of tubes and filler beads. - In
FIGS. 1 and 2 , a shell and tube evaporator is shown with a plurality ofparallel tubes 6 in horizontal orientation. Thetubes 6 are received at each end by two end plates 3 (round or rectangular in shape) called tube sheets. Eachtube sheet 3 has a plurality of parallel holes that are machined at a specific distance with respect to each other according to industry standards, viz., Tubular Exchanger Manufacturers Association, TEMA. The tubes are further supported by baffles or tube supports 7 within the span between thetube sheets 3. The distance between the adjacent baffles ortube supports 7 is determined according to industry standards, e.g., Tubular Exchanger Manufacturers Association, TEMA. The baffles or tube supports 7 have a hole pattern identical to thetube sheets 3 as shown inFIG. 5 (larger scale). The combination oftube sheets 3, thetubes 6, the baffles or tube supports 7 and the tie-rods 9 is also known as tube bundle and is welded to theshell 4 at each end, 19 and 20, hence isolating theshell side 16 from thetube side 17. At the ends, thetube side 19 is confined by front andrear heads tubes 6 are individually joined to thetube sheets 3 at the corresponding holes in thetube sheets 3 via mechanical means or welding. - The process fluid such as water or brine or any other fluid to be cooled enters the
tube side 17 at the front head 1 (attached totubes sheets 3 through bolting 5 or welding) viainlet port 10. Depending upon the nature of the application, theheads front head 1 and therear head 2 carrypass partition plates 14 at thecorresponding lane 21 on thetube sheets 3 that directs the process fluid in thetubes 6 back and forth through a respective quantity of tubes in each pass until the fluid exits athead 1 viaport 11 for even-pass configuration as shown inFIG. 1 andFIG. 2 or athead 2 for odd-pass configuration as shown inFIG. 3 andFIG. 4 viaexit port 11. The process fluid entering atinlet port 10 is hot, while the process fluid exiting atoutlet port 12 is cooled. - Low temperature and low pressure liquid or liquid-gas mixture of refrigerant enters the
shell side 16 viaport 12. As the refrigerant travels upwards it extracts heat from the hot fluid in thetubes 6 and progressively evaporates. The vapor/liquid ratio increases along the height of the tube bundle. The wet vapor exits theshell side 16 viarisers 15 and enters theseparator 8 and leaves theseparator 8 as liquid-free vapor viaport 13. - From the
separator 8, the refrigerant vapor is routed to the compressor (not shown), where the refrigerant is compressed. From the compressor, the refrigerant, which is hot, is cooled in the condenser. After leaving the condenser, the pressure of the refrigerant is dropped by an expansion device, wherein the refrigerant reenters theshell 4 atport 12. - As shown in
FIG. 5 , thetubes 6 are spaced apart from each other, thus creatinggaps 31 between the tubes. The refrigerant flows through thesegaps 31. The tubes are grouped into the sections, with each section representing a pass through the shell. Thus, section I is the first pass of the process fluid through the shell, from theinlet port 10 and thefront head 1 to therear head 2. Section II is the second pass, from therear head 2 back to thefront head 1. Section III is the third pass, from thefront head 1 to therear head 2. Section IV is the fourth pass, from therear head 2 to thefront head 1 and theoutlet port 11. The tubes within a section are separated from each other by a relativelysmall gap 31. The tubes in adjacent sections are separated from each other by a larger gap, orlane 21, in order to accommodate thepass partition plates 14. In a prior art evaporator, thesegaps - In the present invention, much of the interior volume of the shell is filled with filler beads 35 (see
FIGS. 6 and 7 ). The filler beads have a neutral buoyancy when immersed in therefrigerant 33. This minimizes the possibility of the beads accumulating at the bottom of the shell (if negative buoyancy) or at the top (if positive buoyancy) as assures the even distribution of the filler beads throughout the shell. For example, the density of thefiller beads 35 could be the same as the density of the refrigerant. Because the refrigerant changes from a liquid state to a vapor state, the density of the refrigerant changes. The filler beads can have a neutral buoyancy relative to the liquid refrigerant. - The filler beads in the preferred embodiment are made of solid plastic. The filler beads remain solid and do not turn to liquid inside of the shell. In the preferred embodiment, the
filler beads 35 are spherical, although the beads could be of any shape. In the preferred embodiment, the filler beads are solid and not hollow. Solid beads are easier to manufacture and easier to match neutral buoyancy with the refrigerant. Thefiller beads 35 are of different sizes. In the preferred embodiment, there are at least threesizes FIG. 7 ). Thelargest size bead 35A is small enough to pass through thegaps 31 betweenadjacent tubes 6 in a section. Thus, the diameter of the largest size bead is less than P-D, where P is the tube pitch and D is the tube outside diameter. As an example, one type of flooded evaporator has gaps between tubes of 3/16 inches. Thus, the largestsize filler bead 35A is less than 3/16 inches. When several of thelargest size beads 35A are located so as to contact one another, there are spaces between the beads. Theintermediate size beads 35B and thesmallest size beads 35C are sized relative to the largest size beads so as to fit within the spaces of the adjacentlargest size beads 35A. - The
filler beads 35 displace refrigerant inside of theshell 4. The filler beads are located in thegaps filler beads 35. As described below, it is desirable not to overfill the shell with beads to the extent that the beads are immobile. It is desired if the beads can move inside of the shell. - The
filler beads 35 can be put into an evaporator before the evaporator's initial operation. Alternatively, an evaporator can be retrofitted with the filler beads. If retrofitted, the beads will quickly reach the same temperature as the refrigerant. - In operation, the refrigerant 33 (see
FIG. 6 ) flows through thespaces 37 between thefiller beads 35 and consequently through thegaps 31 between the tubes. The filler beads form a structure similar to sponges, with voids formed by the filler beads. Thus, the filler beads channel the refrigerant through the spaces or gaps between the beads. Thefiller beads 35 move and disperse the refrigerant resulting in enhanced heat exchange and refrigerant distribution. In addition, the filler beads contact and scrub the outside diameter of thetubes 6. This is useful in dislodgingbubbles 39 that are formed on the outside oftubes 6 as the refrigerant boils. Abubble 39 on a tube decreases the heat exchange at that particular location on the tube. Dislodging the bubble increases the heat exchange. - An evaporator equipped with the filler beads is more efficient and utilizes less refrigerant than prior art evaporators. As a more efficient heat exchanger, the size of the evaporator can be reduced, saving material costs and also floor space. The evaporator requires a lower charge of refrigerant for the same heat exchange capacity when compared to the prior art. The requirement of less refrigerant results in a savings in startup and maintenance cost. In addition, any accidental release of refrigerant is less dangerous as there is less refrigerant to release.
- The foregoing disclosure and showings made in the drawings are merely illustrative of the principles of this invention and are not to be interpreted in a limiting sense.
Claims (7)
1. A flooded shell and tube evaporator, comprising:
a) a shell having an inlet and an outlet and having a first and second end;
b) a plurality of tubes located in the shell and extending between the first and second ends, the tubes forming a path through the shell, the path comprising at least one pass through the shell;
c) gaps between the tubes;
d) refrigerant located in the shell;
e) filler beads located inside of the shell, the filler beads located in the gaps, the filler beads being smaller than the gaps so as to be able to move through the gaps, the filler beads having a neutral buoyancy relative to the refrigerant.
2. The evaporator of claim 1 wherein the filler beads comprise three sizes.
3. The evaporator of claim 1 wherein the filler beads are made of plastic.
4. The evaporator of claim 1 wherein the filler beads are spherical.
5. A method of heat exchange in a flooded shell and tube evaporator, comprising the steps of:
a) providing filler beads inside of the shell and amongst the tubes;
b) flowing a process fluid through the tubes in the evaporator;
c) flowing a refrigerant through the shell and through the spaces between the filler beads and through gaps between the tubes.
6. The method of claim 5 further comprising the steps of allowing the beads to move as the refrigerant is flowed, wherein the beads disperse the exchange of heat between the tubes and the refrigerant and the beads contact the tubes and dislodge bubbles on the tubes.
7. The method of claim 5 wherein the step of providing filler beads inside of the shell and amongst the tubes further comprises the step of providing filler beads with a neutral buoyancy with respect to the refrigerant.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US11/695,413 US20080190591A1 (en) | 2007-02-08 | 2007-04-02 | Low charge refrigerant flooded evaporator |
Applications Claiming Priority (2)
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US90013907P | 2007-02-08 | 2007-02-08 | |
US11/695,413 US20080190591A1 (en) | 2007-02-08 | 2007-04-02 | Low charge refrigerant flooded evaporator |
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US20080190591A1 true US20080190591A1 (en) | 2008-08-14 |
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ID=39684840
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US11/695,413 Abandoned US20080190591A1 (en) | 2007-02-08 | 2007-04-02 | Low charge refrigerant flooded evaporator |
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Cited By (10)
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US20090165497A1 (en) * | 2007-12-31 | 2009-07-02 | Johnson Controls Technology Company | Heat exchanger |
CN102410673A (en) * | 2012-01-04 | 2012-04-11 | 天津商业大学 | High-pressure working medium condenser/evaporator |
WO2012107645A1 (en) | 2011-02-09 | 2012-08-16 | Vahterus Oy | Device for separating droplets |
WO2013049219A1 (en) | 2011-09-26 | 2013-04-04 | Ingersoll Rand Company | Refrigerant evaporator |
US20140223936A1 (en) * | 2011-09-26 | 2014-08-14 | Trane International Inc. | Refrigerant management in hvac systems |
JP2015502518A (en) * | 2011-12-20 | 2015-01-22 | コノコフィリップス カンパニー | Internal baffle for sloshing suppression in core heat exchanger in shell |
CN105546881A (en) * | 2015-12-07 | 2016-05-04 | 上海交通大学 | Bubble flow guide full-liquid type shell tube evaporator |
US20160201519A1 (en) * | 2015-01-14 | 2016-07-14 | Ford Global Technologies, Llc | Heat exchanger for a rankine cycle in a vehicle |
US9746256B2 (en) * | 2011-11-18 | 2017-08-29 | Carrier Corporation | Shell and tube heat exchanger with a vapor port |
US9849404B2 (en) | 2012-04-04 | 2017-12-26 | Vahterus Oy | Apparatus for vapourising a medium and separating droplets as well as for condensing the medium |
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US20090165497A1 (en) * | 2007-12-31 | 2009-07-02 | Johnson Controls Technology Company | Heat exchanger |
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