CA1058156A - Plastic heat exchange tube - Google Patents
Plastic heat exchange tubeInfo
- Publication number
- CA1058156A CA1058156A CA282,263A CA282263A CA1058156A CA 1058156 A CA1058156 A CA 1058156A CA 282263 A CA282263 A CA 282263A CA 1058156 A CA1058156 A CA 1058156A
- Authority
- CA
- Canada
- Prior art keywords
- tube
- center portion
- heat exchange
- channel portion
- spiral
- 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.)
- Expired
Links
Landscapes
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A plastic heat exchange tube for use in combination with large dry and wet/dry type cooling towers. The tube includes a tubular center portion around which an open ended channel portion spirals over substantially the entire length thereof, with the open end in communication with the interior of the center portion. A web portion extends through and preferably integral with the center portion of the tube.
A plastic heat exchange tube for use in combination with large dry and wet/dry type cooling towers. The tube includes a tubular center portion around which an open ended channel portion spirals over substantially the entire length thereof, with the open end in communication with the interior of the center portion. A web portion extends through and preferably integral with the center portion of the tube.
Description
~105~15~; ~
B.~CK~ OIJNI) ~ U~I~IAl~Y Ol: T~IE INVf'N'I'10~
This application is related to Canadian Applicati~n No. 234,377, filed August 28, 1975, for PLASTIC HEAT
EXC~ E TUBE. The prescnt in~ention rclates to a unique plastic heat excilange tubc particularly designed for use in combination with largc dry and wet/d~y type cooling to~ers.
There is a general trend today towards dry and wet/dry cooling due to public opinion factors against ~et cooling in the areas of drift and blo~down discharges, as well as availability of makeup and blol~down water. However, despite their environ-mental advantages, dry and wet/dTy cooling to~;ers have not foundgeneralized employment because of their relatively high initial cost and the likelihood of the metallic finned heat exchange tubes heretofore used therein corroding by chemical action with atmospheric agents.
The present invention is directed to a unique plastic heat exchange tube which may be readily substituted for the heretofore used metallic finned heat exchange tubes. The use of such tubes will significantly reduce the initial cost of the recipient dry and wet/dry towers to the extent that they become com~etitively priced with conventional t~et cooling towers and do not present the corrosion problem which exists in current dry and wet/dry to-~ers.
Despite the kno-~n lo-~ thermal conductivity of plastics, which range in the order of from .2% to 10% of the metals com-monly used in heat exchange tube construction, tubing composed of organic polymers have been used efficientl~ in heat ex-change devices between fluid masses. The heretofore used plastic heat exchange tubes have becn made from thcrmoplastics or other known types of organic polymers and have ta~en the - 1 - ~
1058~5~;
form of hollow filaments of very minute diamcter having very thin and substantially smooth wall surfaces. Such tubes are of substantially smaller size than the metallic heat exchange tubes commonly used in large dry and wet/dry heat exchangers and consequently not readily substituted therefoFe.
It is also known in the prior art to materially increase the thermal conductivity of the plastic tubes by mixing various metallic powders with the plastic material during manufacture.
; As used hereinafter in the specification and claims, the term ~ 10 plastic is intended to include a mixture of plastic and metallic ; powders.
Accordingly, it is a primary object of the present in-vention to provide a heat exchange tube for use in dry and wet~
dry cooling applications which is considerably less expensive ~; to manufacture than heretofore used metallic finned heat ex-change tubes.
: :
Another object is to provide a heat exchange tube for use in dry and wet/dry cooling applications which is non-corro-sive when subjected to the generally encountered environmental ` ~` 20 ~ agents.
A further object of the present invention is to provide a plastic heat exchange tube which has increased heat transfer characteristics over heretofore proposed plastic heat exchange tubes.
A still further object is to provide a plastic heat exchange tube having heat transfer characteristics and struc-tural stability ~hich permits its substitution for metallic heat exchange tubes currently being used in large dry and ~0581S~;
wet/dry cooling towers.
These and other objects are realized in accordance with the invention by providing an improved heat e.~c]lange tube for a heat exchanger. The tube comprises an elongated center portion for receiving liquid flow therethrough from an inlet end of the tube to an outlet end, and an open-ended channel portion spiralling in one direction about the center portion along substantially the entire length thereof with the open end of the channel portion in fluid communi-cation with the interior of the center portion. The centerand channel portions are integrally formed from plastic so as to be seamlessly joined to each other along the length, with the height of the channel portion being at least as great as the pitch of the spiral and no greater than two times the pitch, and a web portion extends througl~ the center portion so as to impart longitudinal stability to the tube and to turbulently rotate liquid flowing through the tube outwardly into the channel portion. The web portion has at least two substantially radially extending legs which spiral about the axis of the center portion along substanti-ally the entire length of the center portion.
The web portion permits the channel portion and the center portion to be formed of thinner wall thicknesses which results in increased heat transfer characteristics and a material cost savings in manufacturing the tube.
The web portion also imparts an additional turbulating effect to the liquid passing through the tube to further pre~ent laminar flow and subsequently increase ,,~
105~156 the heat transfer characteTistics of the tube.
BRIEF DESCRIPTION OF THE DRAI~INGS
-Other objects and many of the attendant advantages of the present invention will be readily appreciated as the in-vention becomes better understood by reference to the following detailed description, when considered in connection with the accompanying drawings, in which like reference numerals desig-nate like parts throughout the figures thereof and wherein:
Fig. 1 is a perspective view of a portion of an exem-. ~ ~
10 ~ plary wet/dry cooling tower of a type contemplated for use with the plastic heat exchange tubes of the present invention;
Fig. 2 is an elevational view of the plastic heat ex-change tube of the present invention illustrated in combination with a u~nique mounting arrangement for mounting the tube in a cooling tower of the type shown in Fig. l;
Fig. 3 is a plan view of the plastic heat exchange tube shown in Fig. 2;~
Fig. 4 is an elevational view of the web portion of the ~plastic heat exchange tube shown in Pig. 2; and ;~ 20 Fig. 5 is a sectional view ta~en along line 5-5 in Fig. 3.
~: ~
DESCRIPTION OF THE PREFERRED E~IBODIMENTS
Referring to Figs. 1 and 2, a plastic heat exchange tube 10, constructed in accordance with the present invention~
is shown in combination with a wet/dry cooling tower 12 for purposes of giving an exemplary environmental context to the ;~ invention. It should be understood, however, that the heat exchange tubes of the present invention are intended ~or use in other types of well-known wet/dry and dry cooling arrange-ments, both of the mechanical d~aft and natural draft class.
Referring to Fig. 1, a portion of an exemplary wet/dry cooling tower is indicated generally at 12. Tower 12 includes a housing 13 incorporating a top deck 14 defining a hot water distribution basin 16. Liquid, such as water to be cooled, is pumped into basin 16 thTough distribution pipe 18 and dis-tribution box 19. Positioned immediately below basin 16 is a dry cooling section 22 which includes a plurality of vertically disposed plastic heat exchange tubes 10 constructed in accord-ance with the present invention. Tubes 10 are arranged in a plurality of transversely extending TOWS and mounted between a floor 17 of basin 16 and a horizontal partition deck 26.
Liquid from basin 16 flows downward through tubes 10 for distri-bution over a wet cooling section 30 positioned immediately ~:, therebelow. After descending through fill or pac~ing 32, sup-20~ poTted within wet section 30, the cooled liquid is collected ina cold water collection basin 34 for removal to service.
. , ~
Ambient cooling air is drawn laterally~through the tower by a fan (not shown) rotating in fan stack 36. The air passes successively through openings between inlet louvers 40, which are separately associated with both dry section 22 and wet section 30, and then through the respective dry and wet sections 22 and 30. The exhaust air from dry section 2' and wet section 30 are mixed in plenum area 42 prior to discllarge from the tower via stack 36 to the atmosphere. Movable louver assemblies 44 and 46 may be provided to permit control of the ratio of air ~vs~is~
mix in the plenum area 42 which emanates from the dry and wet sections.
A plastic heat exchange tube 10 formed in accordance with the present invention is illustrated in Figs. 2 - 5. Tube 10 includes a tubular center portion 50 around which an open ended channel portion 52 spirals over substantially the entire length thereof. Channel portion 52 includes an open end 54 which is in fluid communication with the interior of center portion 50 such that liquid passing through the center portion 50 is free to enter and exit channel portion 52 over substantially the entire length thereof. The center portion 50 and channel portion 52 are lntegrally formed so that there are no seams extending spirally along the tube.
An integrally formed web portion 56 extends through the center portion 50. Web portion 56 includes a center core section 58, extending through the longitudinal center axis of the tube 10, from which three rib sections 60 extend radially outward toward and are connected to the inner surface of center portion 50. As best seen in Figs. 3 and 4, the rib sections 60 spiral in the same direction as the channel portion 52 as they extend longitudinally through the center portion 50.
A preferred form of heat exchange tube constructed in accordance with the present invention has a center portion 50 with an outside diameter of 1" and a channel portion 52 with an outer diameter of 2". The channel portion 52 is defined by side walls 62 and 64 and a curved end wall 66, as seen in Fig.
5. The thickness of walls 62, 64, and 66 is .03 inches. The side walls 62 and 64 taper towards one another as they extend outward from center portion 50 such that they are spaced .06 inches apart where they meet the end wall 66 and .10 inches apart where they intersect the center portion 50.
105~156 The height of each channcl portion 52 is thus seen to be 1/2". According to the preferred form o~ the invention, the pitch of the channel portion spiral is 1/3". The height to pitch ratio is thus 1.5 to 1. For reasons hereinafter discussed, this configuration is the most advantageous, considering all pertinent factors.
According to the invention the height to pitch ratio can be varied within limits, however, and still retain substan-tial, although lesser, advantages. It has been found that a height to pitch ratio as low as 1 to 1 and as high as 2 to 1 ~ will still produce substantial advantages.
; The rib sections 60 are .03 inches in thickness and make a complete spiral over each foot of tube length. They are three in number, as will be noted, and spiral in the same direc-tion as the channel portion 52.
Referring to Fig. 2, a unique manner of supporting the tubes lO between floor 17 and a partition deck 26 is shown.
:
A top socket and nozzle member 70 is provided to extend through a cooperating opening 71 in floor 17 and perform the dual ; 20 function of directing the liquid to be cooled from basin 16 into tube 10 and supporting the tube 10 from floor 17. Top socket ` ~ 70 includes an upstanding hollow neck portion 72 having slotted openings 74 formed about the upper portion thereof to receive the liquid from basin 16 therethrough and direct it into the tube 10. Socket 70 additionally includes a base portion 76 ~`:
having a spiral cavity 78 formed therein for receipt of the upper section of the channel portion 52 therein. The socket 70 is preferably formed from a plastic material and split verti-cally into two parts which may be bonded together after the ,. d ~ 058156 channel portion 52 is properly seated in the cavity 78. An annular flange S0 is formed about the base portion 76 for se-curing socket 70 to floor 17 via a rubber grommet 82 wedged thereinbetween. A lower socket 84 is provided for securing the lower end of tube 10 to the partition deck 26. Lower socket 84 is formed from a plastic material with an upper cavity 86 for receipt of the center portion 50 and the web portion 56 therein and a lower cavity 88 for receipt of a conventional spray nozzle ~ assembly 90 therein. Upper and lower flanges 92 and 94 are ; 10 provided for sandwiching partition deck 26 therebetween as socket 84 is forced through a cooperating opening 96 in the deck 26.
In operation, liquid to be cooled passes from the basin 16 through slots 74 in socket 70 and down into the heat exchange tubes 10. As the liquid enters each tube 10, the bulk of it initially seeks to descend in the center portion 50 while a portion of it initially finds its way into the channel portion 52 and seeksto descend spirally therein.
Because of the low pitch, and relatively high height to pitch ratio, however, the liquid which initially enters the channel portion 52 tends to turbulently tumble in and out of the channel portion while continuing spiral movement. At the same time the liquid which initially starts down the center portion 50 is turbulently rotated outwardly into the channel portion 52 by the spiral, three rib 60 web portion 56 spiralling in the same direction but at a pitch of approximately 1 foot.
Subsequently, it too tumbles into and out of the channel portion 52 while continuing spiral movement.
The combination of channel portion 52 depth ~i.e., height), low pitch spiral configuration, a height to pitch ratio ilO58~5~ .
of approximately 1.5 to 1, and three rib web portion 56 produces substantially non-laminar liquid flo~ hile maintaining a high incidence of fluid contact with the tube 10 wall. The ambient air dra~n through the dry section 22 cools the liquid passing through the tubes 10. The cooled liquid leaving tube 10 is directed through nozzle 90 and sprayed over the wet section 30.
The ambient air drawn through the wet section 30 further cools the liquid as it descends therethrough for collection in basin 34.
It should be understood, of course, that the foregoing disclosure relates to only a preferred embodiment of the inven-tion and that numerous modifications or alterations may be made therein without departing from the true spirit and the scope of : the invention as set forth in the appended claims.
B.~CK~ OIJNI) ~ U~I~IAl~Y Ol: T~IE INVf'N'I'10~
This application is related to Canadian Applicati~n No. 234,377, filed August 28, 1975, for PLASTIC HEAT
EXC~ E TUBE. The prescnt in~ention rclates to a unique plastic heat excilange tubc particularly designed for use in combination with largc dry and wet/d~y type cooling to~ers.
There is a general trend today towards dry and wet/dry cooling due to public opinion factors against ~et cooling in the areas of drift and blo~down discharges, as well as availability of makeup and blol~down water. However, despite their environ-mental advantages, dry and wet/dTy cooling to~;ers have not foundgeneralized employment because of their relatively high initial cost and the likelihood of the metallic finned heat exchange tubes heretofore used therein corroding by chemical action with atmospheric agents.
The present invention is directed to a unique plastic heat exchange tube which may be readily substituted for the heretofore used metallic finned heat exchange tubes. The use of such tubes will significantly reduce the initial cost of the recipient dry and wet/dry towers to the extent that they become com~etitively priced with conventional t~et cooling towers and do not present the corrosion problem which exists in current dry and wet/dry to-~ers.
Despite the kno-~n lo-~ thermal conductivity of plastics, which range in the order of from .2% to 10% of the metals com-monly used in heat exchange tube construction, tubing composed of organic polymers have been used efficientl~ in heat ex-change devices between fluid masses. The heretofore used plastic heat exchange tubes have becn made from thcrmoplastics or other known types of organic polymers and have ta~en the - 1 - ~
1058~5~;
form of hollow filaments of very minute diamcter having very thin and substantially smooth wall surfaces. Such tubes are of substantially smaller size than the metallic heat exchange tubes commonly used in large dry and wet/dry heat exchangers and consequently not readily substituted therefoFe.
It is also known in the prior art to materially increase the thermal conductivity of the plastic tubes by mixing various metallic powders with the plastic material during manufacture.
; As used hereinafter in the specification and claims, the term ~ 10 plastic is intended to include a mixture of plastic and metallic ; powders.
Accordingly, it is a primary object of the present in-vention to provide a heat exchange tube for use in dry and wet~
dry cooling applications which is considerably less expensive ~; to manufacture than heretofore used metallic finned heat ex-change tubes.
: :
Another object is to provide a heat exchange tube for use in dry and wet/dry cooling applications which is non-corro-sive when subjected to the generally encountered environmental ` ~` 20 ~ agents.
A further object of the present invention is to provide a plastic heat exchange tube which has increased heat transfer characteristics over heretofore proposed plastic heat exchange tubes.
A still further object is to provide a plastic heat exchange tube having heat transfer characteristics and struc-tural stability ~hich permits its substitution for metallic heat exchange tubes currently being used in large dry and ~0581S~;
wet/dry cooling towers.
These and other objects are realized in accordance with the invention by providing an improved heat e.~c]lange tube for a heat exchanger. The tube comprises an elongated center portion for receiving liquid flow therethrough from an inlet end of the tube to an outlet end, and an open-ended channel portion spiralling in one direction about the center portion along substantially the entire length thereof with the open end of the channel portion in fluid communi-cation with the interior of the center portion. The centerand channel portions are integrally formed from plastic so as to be seamlessly joined to each other along the length, with the height of the channel portion being at least as great as the pitch of the spiral and no greater than two times the pitch, and a web portion extends througl~ the center portion so as to impart longitudinal stability to the tube and to turbulently rotate liquid flowing through the tube outwardly into the channel portion. The web portion has at least two substantially radially extending legs which spiral about the axis of the center portion along substanti-ally the entire length of the center portion.
The web portion permits the channel portion and the center portion to be formed of thinner wall thicknesses which results in increased heat transfer characteristics and a material cost savings in manufacturing the tube.
The web portion also imparts an additional turbulating effect to the liquid passing through the tube to further pre~ent laminar flow and subsequently increase ,,~
105~156 the heat transfer characteTistics of the tube.
BRIEF DESCRIPTION OF THE DRAI~INGS
-Other objects and many of the attendant advantages of the present invention will be readily appreciated as the in-vention becomes better understood by reference to the following detailed description, when considered in connection with the accompanying drawings, in which like reference numerals desig-nate like parts throughout the figures thereof and wherein:
Fig. 1 is a perspective view of a portion of an exem-. ~ ~
10 ~ plary wet/dry cooling tower of a type contemplated for use with the plastic heat exchange tubes of the present invention;
Fig. 2 is an elevational view of the plastic heat ex-change tube of the present invention illustrated in combination with a u~nique mounting arrangement for mounting the tube in a cooling tower of the type shown in Fig. l;
Fig. 3 is a plan view of the plastic heat exchange tube shown in Fig. 2;~
Fig. 4 is an elevational view of the web portion of the ~plastic heat exchange tube shown in Pig. 2; and ;~ 20 Fig. 5 is a sectional view ta~en along line 5-5 in Fig. 3.
~: ~
DESCRIPTION OF THE PREFERRED E~IBODIMENTS
Referring to Figs. 1 and 2, a plastic heat exchange tube 10, constructed in accordance with the present invention~
is shown in combination with a wet/dry cooling tower 12 for purposes of giving an exemplary environmental context to the ;~ invention. It should be understood, however, that the heat exchange tubes of the present invention are intended ~or use in other types of well-known wet/dry and dry cooling arrange-ments, both of the mechanical d~aft and natural draft class.
Referring to Fig. 1, a portion of an exemplary wet/dry cooling tower is indicated generally at 12. Tower 12 includes a housing 13 incorporating a top deck 14 defining a hot water distribution basin 16. Liquid, such as water to be cooled, is pumped into basin 16 thTough distribution pipe 18 and dis-tribution box 19. Positioned immediately below basin 16 is a dry cooling section 22 which includes a plurality of vertically disposed plastic heat exchange tubes 10 constructed in accord-ance with the present invention. Tubes 10 are arranged in a plurality of transversely extending TOWS and mounted between a floor 17 of basin 16 and a horizontal partition deck 26.
Liquid from basin 16 flows downward through tubes 10 for distri-bution over a wet cooling section 30 positioned immediately ~:, therebelow. After descending through fill or pac~ing 32, sup-20~ poTted within wet section 30, the cooled liquid is collected ina cold water collection basin 34 for removal to service.
. , ~
Ambient cooling air is drawn laterally~through the tower by a fan (not shown) rotating in fan stack 36. The air passes successively through openings between inlet louvers 40, which are separately associated with both dry section 22 and wet section 30, and then through the respective dry and wet sections 22 and 30. The exhaust air from dry section 2' and wet section 30 are mixed in plenum area 42 prior to discllarge from the tower via stack 36 to the atmosphere. Movable louver assemblies 44 and 46 may be provided to permit control of the ratio of air ~vs~is~
mix in the plenum area 42 which emanates from the dry and wet sections.
A plastic heat exchange tube 10 formed in accordance with the present invention is illustrated in Figs. 2 - 5. Tube 10 includes a tubular center portion 50 around which an open ended channel portion 52 spirals over substantially the entire length thereof. Channel portion 52 includes an open end 54 which is in fluid communication with the interior of center portion 50 such that liquid passing through the center portion 50 is free to enter and exit channel portion 52 over substantially the entire length thereof. The center portion 50 and channel portion 52 are lntegrally formed so that there are no seams extending spirally along the tube.
An integrally formed web portion 56 extends through the center portion 50. Web portion 56 includes a center core section 58, extending through the longitudinal center axis of the tube 10, from which three rib sections 60 extend radially outward toward and are connected to the inner surface of center portion 50. As best seen in Figs. 3 and 4, the rib sections 60 spiral in the same direction as the channel portion 52 as they extend longitudinally through the center portion 50.
A preferred form of heat exchange tube constructed in accordance with the present invention has a center portion 50 with an outside diameter of 1" and a channel portion 52 with an outer diameter of 2". The channel portion 52 is defined by side walls 62 and 64 and a curved end wall 66, as seen in Fig.
5. The thickness of walls 62, 64, and 66 is .03 inches. The side walls 62 and 64 taper towards one another as they extend outward from center portion 50 such that they are spaced .06 inches apart where they meet the end wall 66 and .10 inches apart where they intersect the center portion 50.
105~156 The height of each channcl portion 52 is thus seen to be 1/2". According to the preferred form o~ the invention, the pitch of the channel portion spiral is 1/3". The height to pitch ratio is thus 1.5 to 1. For reasons hereinafter discussed, this configuration is the most advantageous, considering all pertinent factors.
According to the invention the height to pitch ratio can be varied within limits, however, and still retain substan-tial, although lesser, advantages. It has been found that a height to pitch ratio as low as 1 to 1 and as high as 2 to 1 ~ will still produce substantial advantages.
; The rib sections 60 are .03 inches in thickness and make a complete spiral over each foot of tube length. They are three in number, as will be noted, and spiral in the same direc-tion as the channel portion 52.
Referring to Fig. 2, a unique manner of supporting the tubes lO between floor 17 and a partition deck 26 is shown.
:
A top socket and nozzle member 70 is provided to extend through a cooperating opening 71 in floor 17 and perform the dual ; 20 function of directing the liquid to be cooled from basin 16 into tube 10 and supporting the tube 10 from floor 17. Top socket ` ~ 70 includes an upstanding hollow neck portion 72 having slotted openings 74 formed about the upper portion thereof to receive the liquid from basin 16 therethrough and direct it into the tube 10. Socket 70 additionally includes a base portion 76 ~`:
having a spiral cavity 78 formed therein for receipt of the upper section of the channel portion 52 therein. The socket 70 is preferably formed from a plastic material and split verti-cally into two parts which may be bonded together after the ,. d ~ 058156 channel portion 52 is properly seated in the cavity 78. An annular flange S0 is formed about the base portion 76 for se-curing socket 70 to floor 17 via a rubber grommet 82 wedged thereinbetween. A lower socket 84 is provided for securing the lower end of tube 10 to the partition deck 26. Lower socket 84 is formed from a plastic material with an upper cavity 86 for receipt of the center portion 50 and the web portion 56 therein and a lower cavity 88 for receipt of a conventional spray nozzle ~ assembly 90 therein. Upper and lower flanges 92 and 94 are ; 10 provided for sandwiching partition deck 26 therebetween as socket 84 is forced through a cooperating opening 96 in the deck 26.
In operation, liquid to be cooled passes from the basin 16 through slots 74 in socket 70 and down into the heat exchange tubes 10. As the liquid enters each tube 10, the bulk of it initially seeks to descend in the center portion 50 while a portion of it initially finds its way into the channel portion 52 and seeksto descend spirally therein.
Because of the low pitch, and relatively high height to pitch ratio, however, the liquid which initially enters the channel portion 52 tends to turbulently tumble in and out of the channel portion while continuing spiral movement. At the same time the liquid which initially starts down the center portion 50 is turbulently rotated outwardly into the channel portion 52 by the spiral, three rib 60 web portion 56 spiralling in the same direction but at a pitch of approximately 1 foot.
Subsequently, it too tumbles into and out of the channel portion 52 while continuing spiral movement.
The combination of channel portion 52 depth ~i.e., height), low pitch spiral configuration, a height to pitch ratio ilO58~5~ .
of approximately 1.5 to 1, and three rib web portion 56 produces substantially non-laminar liquid flo~ hile maintaining a high incidence of fluid contact with the tube 10 wall. The ambient air dra~n through the dry section 22 cools the liquid passing through the tubes 10. The cooled liquid leaving tube 10 is directed through nozzle 90 and sprayed over the wet section 30.
The ambient air drawn through the wet section 30 further cools the liquid as it descends therethrough for collection in basin 34.
It should be understood, of course, that the foregoing disclosure relates to only a preferred embodiment of the inven-tion and that numerous modifications or alterations may be made therein without departing from the true spirit and the scope of : the invention as set forth in the appended claims.
Claims (3)
1. In a heat exchanger, the improvement in a heat exchange tube, comprising:
a. an elongated center portion for receiving liquid flow therethrough from an inlet end of the tube to an outlet end, b. an open-ended channel portion spiralling in one direction about said center portion along substantially the entire length thereof with the open end of said channel portion in fluid communication with the interior of said center portion, c. said center and channel portions being integrally formed from plastic so as to be seamlessly joined to each other along said length, d. the height of said channel portion being at least as great as the pitch of the spiral and no greater than two times the pitch, and e. a web portion extending through said center portion so as to impart longitudinal stability to the tube and to turbulently rotate liquid flowing through the tube outwardly into said channel portion, f. said web portion having at least two substantially radially extending legs, g. said radially extending legs spiraling about the axis of said center portion along substantially the entire length of said center portion.
a. an elongated center portion for receiving liquid flow therethrough from an inlet end of the tube to an outlet end, b. an open-ended channel portion spiralling in one direction about said center portion along substantially the entire length thereof with the open end of said channel portion in fluid communication with the interior of said center portion, c. said center and channel portions being integrally formed from plastic so as to be seamlessly joined to each other along said length, d. the height of said channel portion being at least as great as the pitch of the spiral and no greater than two times the pitch, and e. a web portion extending through said center portion so as to impart longitudinal stability to the tube and to turbulently rotate liquid flowing through the tube outwardly into said channel portion, f. said web portion having at least two substantially radially extending legs, g. said radially extending legs spiraling about the axis of said center portion along substantially the entire length of said center portion.
2. The improvement in the heat exchange tube of Claim 1 further characterized in that:
.
a. The height of said channel portion is approximately one and one-half times the pitch of the spiral of said channel portion.
.
a. The height of said channel portion is approximately one and one-half times the pitch of the spiral of said channel portion.
3. The improvement in the heat exchange tube of Claim 1 further characterized in that:
a. said radially extending legs spiral about the axis of said center portion in said one direction whereby they rotate liquid flowing through the tube in said one direction, b. The pitch of said ribs as they spiral along the length of said center portion being no greater than one foot.
a. said radially extending legs spiral about the axis of said center portion in said one direction whereby they rotate liquid flowing through the tube in said one direction, b. The pitch of said ribs as they spiral along the length of said center portion being no greater than one foot.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US05/757,194 US4132264A (en) | 1974-12-20 | 1977-01-06 | Plastic heat exchange tube |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1058156A true CA1058156A (en) | 1979-07-10 |
Family
ID=25046789
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA282,263A Expired CA1058156A (en) | 1977-01-06 | 1977-07-07 | Plastic heat exchange tube |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1058156A (en) |
-
1977
- 1977-07-07 CA CA282,263A patent/CA1058156A/en not_active Expired
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