|Publication number||US3887004 A|
|Publication date||3 Jun 1975|
|Filing date||19 Jun 1972|
|Priority date||19 Jun 1972|
|Also published as||CA1014547A, CA1014547A1|
|Publication number||US 3887004 A, US 3887004A, US-A-3887004, US3887004 A, US3887004A|
|Inventors||Theodore A Beck|
|Original Assignee||Hayden Trans Cooler Inc|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (3), Referenced by (41), Classifications (15), Legal Events (4)|
|External Links: USPTO, USPTO Assignment, Espacenet|
United States Patent n9;
1 1 HEAT EXCHANGE APPARATUS  Inventor: Theodore A. Beck, Riverside, Calif.  Assignee: Hayden Trans-Cooler, 1nc., Corona,
 Filed: June 19, 1972  Appl. No.: 263,931
 U.S. Cl. 165/179; 29/l57.3 A; 165/184  Int. Cl... ..F28f 1/42  Field of Search 165/179, 183, 184; 138/38; 60/329, 337
 References Cited UNITED STATES PATENTS 2,212,932 8/1940 Fairlie 165/179 X 2.960.114 11/1960 Himde 165/179 X 3,212,992 10/1965 Salesse et all 165/184 FOREIGN PATENTS OR APPLICATIONS 1,290,700 3/1962 165/169 120.867 1/1909 Germany 165/179 Primary Examiner-Charles J. Myhre Assistant ExaminerTheophil W. Streule Attorney, Agent, or FirmAlbert L. Gabriel  ABSTRACT The present invention relates in general to heat exchangers. and in particular to the type of heat exchanger which includes one or more tubular heat exchange units as a part thereof. More particularly. the present disclosure is directed to an improved tubular heat exchange unit usable in various types of heat exchange apparatus, and including a fluid flow control core which supports a plurality of regularly spaced, generally radially oriented heat exchange fins or splines that are preferably integrally extruded as a part of the core. in a preferred form the core fins have a novel cross-sectional configuration with symmetrical concave sides providing better heat exchange performance by combined improvements in fluid flow and heat gathering and conducing capacities, such cross-sectional fin configuration also providing improvements in assembly and structural integrity. Also disclosed herein are novel longitudinal configuration of the heat exchange fins including a step twisted or joggled configuration, a helically or spirally twisted configuration, and longitudinally segmented fin constructions provided by either annular grooving of the fins or helical grooving of the fins. these fin configurations providing improved heat transfer characteristics by turbulation of fluid conducted between the fins, and causing a circumferential component of fluid flow around the tubular heat exchange unit between cold and hot sides of the overall heat exchange apparatus.
15 Claims, 13 Drawing Figures HEAT EXCHANGE APPARATUS BACKGROUND OF THE INVENTION Heat exchangers are currently employed in a wide variety of fields, and they take a number of different forms. In many fields of heat exchanger usage, such as oil refining plants and industrial refrigeration apparatus, neither space nor weight is at a premium, so the heat exchangers can be large and bulky. and need not be particularly efficient. However, in certain heat ex changer environments it is of particular importance to provide a maximum of heat exchange capacity with a minimum size and weight. An example of such environment is the use of heat exchange apparatus for cooling the oils employed in connection with the operation of motor vehicles, such as transmission fluid used in automatic transmissions and torque converters, engine oil, power steering fluid, hydraulic fluids, and the like, such oils hereinafter being referred to simply as motor vehicle oils. In this motor vehicle environment, during excessive load conditions large amounts of heat must be exchanged from the fluid system into the atmosphere. Nevertheless, there is only minimal space or airflow available in most motor vehicles for placement of heat exchange apparatus for such purposes, and only part of the available space is disposed with good access to the air flow that is necessary for maximum heat exchanging. Accordingly, it is of vital importance in motor vehicle heat exchangers of this type to provide a maximum of heat exchange capacity in heat exchange apparatus of minimum overall dimension.
Similar considerations of high heat exchange capacity in a minimum space also prevail in other environments, as for example with other types of vehicles, in relatively small and compact refrigerations systems such as those found in the home, in restaurants, in computers, and the like.
Most heat exchange apparatus of high capacity with minimum size, such as heat exchange apparatus employed for cooling motor vehicle oils, is of a type having one or more tubular heat exchange units having external fins associated therewith, the oil passing through the tubular units giving up heat to internal fins thereof, the heat being conducted radially outwardly through the walls of the tubular units and thence to the external fins and being removed primarily by radiation and convection from the external fins. Conventional internal turbulating fin structures in such tubular heat exchange units are relatively inefficient, tending to permit laminar fluid flow, and not having particularly good heat gathering capability; and conventional fin constructions also tend to reduce heat transfer by obstructing the flow of fluid through the tubular heat exchange units.
SUMMARY OF THE INVENTION In view of these and other problems in the art, it is an object of the present invention to provide a novel tubular heat exchange unit having a regular annular array of heat transfer fins therein of improved heat exchange characteristics.
Another object of the invention is to provide a tubular heat exchange unit of the character described wherein the heat transfer fins have a novel crosssectional configuration with symmetrical concave sides that are preferably, but not necessarily, of generally parabolic curvature. This concave-sided fin configuration improves heat transfer performance in a number of ways, including increasing the fluid flow channel cross section between the adjacent pairs of fins, reducing pressure drop, adding to the heat collecting surface areas of the fins, provided improved heat transfer characteristics between the inner root portions and outer toe portions of the fins, and adding surface contact area between the outer ends of the fins and the surrounding tubular shell.
In the presently preferred form of the invention the fins are integrally extruded with an inner tubular core body, the fins extending generally radially outwardly from this tubular core body and having their outer ends seated in metal-to-metal heat-exchange contact with the tubular outer shell of the tubular heat exchange unit. In assembling the flow control core consisting of the tubular core body and its fins to the outer tubular shell, the tubular core body is expanded radially outwardly to a much greater extent than the clearance to be taken up between the outer ends of the fins and the outer shell, and such outward expansion involves a unique cooperation of varying work hardening from the as extruded" condition of the flow control core with the configuration of tubular core body and fins, wherein the tubular core body becomes a generally rigid internal supporting structure, the fins are hardest in their inner root portions where they are thinnest and need strengthening, and become softer radially outwardly to soft outer toe portions that are thereby made formable for intimate mating with the outer tubular shell, the hard internal supporting tube structure maintaining outward compression of the flow control core against the outer tubular shell for good structural integrity and heat conducting interfaces.
Another important feature of the present invention is the provision of novel longitudinal configurations of the heat exchange fins. One such longitudinal configuration is a step-twisted or joggled configuration wherein the fins are maintained in parallel relationship to each other, while they are stepped or joggled in a succession of alternate longitudinal portions which are preferably generally parallel to the axis of the tubular heat exchange unit and twisted portions which are inclined at a substantial angle to the axis and are generally helical; such step twisted or joggled fin configurations reducing the tendency for laminar flow and intro ducing turbulation into the fluid, as well as rotating the fluid circumferentially about the tubular heat exchange unit between cold and hot sides thereof.
Another novel longitudinal configuration of the fins is the segmentation thereof by either a series of annular longitudinally spaced grooves, or a single spiral or helical groove, such segmentations being applicable to either straight or joggled or spirally twisted fins, and adding additional turbulation and in the case of the spiral groove circumferential movement of the fluid. An important aspect of such longitudinally interrupted fins is that the grooves which provide the interruptions, while removing side surface areas from the fins, add the end surface areas of the fin segments so that overall surface area is not substantially reduced.
Other objects, aspects and advantages of the present invention will be apparent from the following description taken in connection with the accompanying drawings, wherein:
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an elevational view illustrating heat exchange apparatus of one type which is particularly suitable for use with the present invention.
FIG. 2 is an enlarged cross-sectional view taken on the line 2-2 in FIG. 1 illustrating one form of tubular heat exchange unit according to the invention.
FIG. 3 is a side elevational view, partly in axial section, showing a form of the invention wherein the core fins in the tubular heat exchange unit have a joggled or stepped twist configuration.
FIG. 4 is a view similar to FIG. 3 illustrating a form of the invention wherein the core fins are longitudinally interrupted by a series of longitudinally spaced annular grooves.
FIG. 5 is a view similar to FIGS. 3 and 4, but illustrating a flow control core of the tubular heat exchange unit which has longitudinaly arranged core fins that are generally parallel to the axis of the unit.
FIG. 6 is a view similar to FIGS. 3, 4, and 5, but illustrating longitudinal interruption of the core fins by a helical groove which provides a series of longitudinally spaced grooves in each of the fins.
FIG. 7 is a view similar to FIGS. 3 to 6, but illustrat ing a core body having helically twisted fins.
FIG. 8 is an end elevational view illustrating a heat exchange unit similar to that shown in FIG. 2, but with the addition of an inner fin structure disposed within the tubular core body.
FIG. 9 is an end elevational view illustrating a modified flow control core having generally flat-sided fins.
FIG. 10 is a view similar to FIG. 9, but illustrating a flow control core of generally inverted construction wherein the tubular core body is on the outside and the integral fins extend generally radially inwardly therefrom.
FIG. 11 illustrates heat exchange apparatus embodying the invention which has a spiral finned outer shell.
FIG. 12 is a transverse section, with portions shown in elevation, illustrating heat exchange apparatus wherein a bundle' of tubular heat exchange units according to the invention is enclosed within an outer heat exchanger shell.
FIG. 13 illustrates an expansion method step used in making a tubular heat exchange unit according to the invention and securing the same within finned heat exchange apparatus.
DETAILED DESCRIPTION FIG. 1 illustrates heat exchange apparatus 10 of a general type that is currently widely employed in heat exchange systems for cooling motor vehicle oils. Such heat exchange systems employing heat exchange apparatus of the general type shown in FIG. 1 are described in US. Pat. No. 3,3l5,464, issued Apr. 25, I967 to Perez M. Hayden for Heat-Exchange System. The heat exchange apparatus 10 represents typical heat exchange apparatus in which the present invention may be employed, although it is to be understood that the present invention is adaptable for any type of heat exchange apparatus which utilizes tubular heat exchange members therein. It is also to be understood that while the present invention is particularly useful in heat exchange apparatus that is employed for cooling motor vehicle oils under circumstances of excessive heat production, nevertheless the invention is suitable for any heat exchange purpose involving the transfer of heat from one fluid to another.
The heat exchange apparatus of FIG. 1 includes a plurality of tubular heat exchange units 12 according to the present invention, these heat exchange units 12 being four in number in the apparatus 10, and being arranged in a generally parallel, regularly spaced planar array. The tubular heat exchange units 12 are maintained in this array by engagement thereof through spaced apertures in a series of parallel fins 14 that are disposed normal to the axes of the tubular heat exchange units 12. The fins l4 serve not only as supporting structures, but they are in heat exchange relationship with the outer surfaces of the tubular heat exchange units 12, and thereby add considerable additional heat exchange area to the outer surfaces of the tubular heat exchange units 12 so as to increase the overall heat exchange efficiency of the apparatus 10.
The tubular heat exchange units 12 are interconnected by means of a series of U-shaped end fittings 16 so that the tubular heat exchange units 12 are arranged for serial flow of fluid therethrough between open ends 18 and 20 which are adapted to be connected into the heat exchange system.
FIG. 2 illustrates a presently preferred crosssectional arrangement for a tubular heat exchange unit 12 according to the present invention. The heat exchange unit 12 includes two principal structural components, a tubular flow control core 22 and a tubular outer shell 38. Both of these components 22 are preferably extrusions, and they may be extruded from any material having good heat transfer characteristics, as for example aluminum. copper or other heat conducting metal.
The flow control core 22 includes a tubular core body 24 which serves as an inner tube member for the heat exchange unit 12. Integrally extruded with the core body 24 are a plurality of regularly spaced, generally radially outwardly extending core fins or splines 26. For illustrative purposes 18 of these regularly spaced core fins 26 have been shown in FIG. 2. However, any desired number of these core fins 26 may be provided without departing from the present invention. Thus, for example, flow control cores 22 may be provided with 12 fins, l8 fins, 22 fins, or other desired number of fins. Since most of the useful heat transfer area of heat exchange unit 12 exposed to the fluid that flows therethrough is in the side surfaces of the core fins 26, what is desired is a maximum of such core fin side surface heat transfer area, while at the same time maintaining a maximum flow conduit cross section between adjacent fins 26. In other words, what is desired is the best possible combination of heat transfer area and minimum pressure drop in the tubular heat exchange unit 12. With present extrusion techniques, the presently preferred number of core fins 26 is about 22, which allows the fins to be relatively long in the radial direction, while at the same time being relatively narrow in the circumferential direction, so as to provide an excellent combination of large heat transfer area and low pressure drop. However, if extrusion die manufacturing techniques materially improve over those currently available, then the tongue ratio" (arealwidth of the fins could be increased to allow an increase in the number of fins without the fins being shortened to the point of losing performance.
Nevertheless. the optimum number of fins will depend upon the viscosity. specific heat and conductivity of the heat exchange fluid, as these factors will determine the frictional losses and the heat transfer characteristics in relation to any particular number of the fins 26.
Still referring to FIG. 2 of the drawings, each of core fins 26 commences at a root portion 28 proximate the core body 24 and terminates in a toe portion having a free end surface 32 that is preferably arcuately complementary to the curvature of the inside of the tubular shell 38 within which the flow control core 22 is en gaged. Each core fin 26 is symmetrical about its radial axis, and in the preferred cross-sectional form of the invention as shown in FIG. 2., each core fin 26 has symmetrical side surfaces 34 which are concave in the general radial direction, the core fin being relatively thin at its root portion 28, and thickening at a non-uniform, progressively increasing rate from the root portion 28 to the free end surface 32. The preferred form of this concave curvature of the side surfaces 34 is parabolic.
The symmetrical concave side surface configuration for the core fins 26 provides a number of advantages over core fins that have parallel straight sides or radially outwardly flaring straight sides. One advantage is that the concave side surfaces 34 provide a substantial increase in the cross sections of the fluid flow channels 36 between adjacent fins 26, Without losing any heat collecting or transferring capacity of the fins. In fact, a second advantage of the concave side surfaces 34 of the fins 26 is that the increased surface area provided thereby and the flaring at the toe portion 30 actually provide increased efficiency in heat collection and transfer to the free end surfaces 32 of the fins 26. Another advantage of the concave side configuration for the core fins 26 is that when the flow control core 22 is expanded outwardly against the tubular outer shell 38 as hereinafter described in detail, the concavities in the sides of the core fins 26 accommodate some bulging in the fins. Another factor of improvement caused by the concave sides is that the resulting circumferential widths of the free end surfaces 32 of the fins 26 are greater, providing increased heat flow contact surface areas between the outer surfaces of the fins 26 and the inner surface of the tubular shell 38. Not only does this added circumferential width at the fin ends 32 increase the heat transfer, but it also tends to stabilize the generally radial orientation of the fins against buckling or distortion as the flow control core 22 is expanded outwardly against the tubular shell 38.
FIG. 13 illustrates a presently preferred method of making heat exchange apparatus embodying the present invention. FIG. 13 illustrates a fragmentary section of heat exchange apparatus like the apparatus 10 shown in FIG. 1, taken axially of one of the tubular heat exchange units 12 of the invention. Prior to the method step that is in progress in FIG. 13, the parallel fins 14 were assembled over the tubular shell 38 of heat exchange unit 12, and the tubular shell 38 was expanded outwardly against the fins 14 to provide secure mechanical interconnection between the shell 38 and fins 14. Such outward expansion of the tubular shell 38 against the fins 14 is by conventional means, as for example by passing an expander mandrel axially through the tubular shell 38. Such outward expansion of the tubular shell 38 causes work hardening in the shell 38 so 6 that shell 38 is illustrated in FIG. 13 is substantially harder than in the as received condition thereof.
In making heat exchange apparatus like the apparatus 10 shown in FIG. I, normally all of the tubular shells 38 will be assembled with the fins 14 by the aforesaid expansion of the shells 38, and at least one end of each of the shells 38 (i.e., each of the four in the apparatus 10 of FIG. 1) will be left open for insertion of a respective flow control core section 22 therein. Thus, for example, in the apparatus 10 of FIG. 1, the U-shaped end fittings 16 may all be absent when the cores 22 are inserted in the respective tubular shells 38, or if desired the two end fittings 16 at the left-hand side of the apparatus 10 as shown may be installed, and the single central fitting 16 may still be unconnected, so that all of the four flow control cores 22 can be inserted from the right-hand ends of the tubular shells 38. For ease of assembly, it is preferred to provide some clearance between the free end surfaces 32 of the core fins 26 and the inner surface of the tubular shell 38. For example, for a typical flow control core 22 having an OD. of approximately 11/16 inch, it is desirable to have a clearance of approximately 0.005 inch between the thin ends 32 and the inner surface of shell 38. With present extrusion techniques it is difficult to establish such clearance with the desired uniformity, so that it is preferred to either roll or draw the flow control cores 22 to the desired size. Such rolling or drawing provides a configuration of the free end surfaces 32 of the core fins 26 which is more nearly accurately complementary to the inner surface of tubular shell 38, for better mating therebetween and hence better heat transfer characteristics.
Referring to FIG. 13, after the flow control core 22 is slidably inserted into tubular shell 38, the core 22 is then expanded radially outwardly into compressive engagement with the shell 38 by any conventional means, as for example by one or more passes of a mandrel 40 axially through the tubular core body 24 of the flow control core 22, the mandrel 40 having a bead or bug 42 thereon which causes the expansion. It is preferred to expand the core body 24 outwardly much more than the amount of the clearance between the end surfaces 32 of the fins and the shells 38 in order to provide a preferred combination of work hardening in strategic portions of the core 22 and intimate mating between the free end surfaces 32 of the core fins and the shell 38. For example, with an initial clearance of about 5/1000 inch between the fin end surfaces 32 and the shell 38, it is desirable to apply approximately three times this amount or about l5/l000 inch of radial expansion to the tubular core body 24. This expansion step is illustrated in FIG. 13, the flow control core 22 being expanded from left to right by the mandrel bead This relatively large amount of radial expansion of the core body 24 relative to the initial clearance causes a considerable amount of work hardening of the tubular core body 24 from its initially soft as extruded" condition, so that the internal supporting tubular core body 24 becomes quite hard, and serves as a stable internal supporting structure for the core fins 26. This expansion also causes a considerable amount of work hardening in the actual fins 26, but such work hardening is greatest proximate the root portions 28 of the fins, and decreases outwardly through the fins to a minimum of work hardening proximate the toe portions 30 of the fins, and particularly at the free end surfaces 32 of the fins. Thus, the relatively thin root portions 28 of the fins are substantially strengthened by work hardening, while the thicker toe portions 30 which inherently have greater structural strength remain softer, and the soft free end surface portions 32 of the fins are formable against the tubular shell 38 for excellent mating contact therewith and consequent good thermal flow characteristics therebetween. Generally the tubular shell 38 will be harder from its aforesaid work hardening than the free end surfaces 32 of the fins 26, and with the relatively hard inner core body 24 and the relatively hard outer tubular shell 38, there will be good permanent radial loading on the fins 26 under all operative conditions of the heat exchange apparatus.
For the example given, with an initial clearance between the O.D. of the flow control core 22 and the ID. of tubular shell 38 of about 0.005 inch, and with an expansion of the tubular core body 24 of about 0.0l inch, it is found in practice that the outer tubular shell 38 will be further expanded outwardly approximately another 0.001 inch, which serves to further secure the structural connection between the shell 38 and the fins 14 and thereby provide a stronger overall heat exchange apparatus.
After a flow control core 22 is thus inserted and expanded into each of the tubular shells 38 of the heat exchange apparatus 10, then the end fitting connections of the apparatus may be completed.
While the flow control cores 22 will normally only be used in straight sections of the outer tubular shells 38, it is to be understood that an assembled tubular heat exchange unit 12, including both the flow control core 22 and the tubular outer shell 38, may be bent as desired for a particular heat exchange installation, provided the are of the bend is sufficiently large to avoid crimping or collapsing of the assembly.
In addition to the forming of the free end surfaces 32 of the core fins 26 against the inner surface of tubular shell 38, the outward pressurization of the fins against the shell 38 described in detail hereinabove results in the outer ends of the fins actually slightly sinking into the material of tubular shell 38, which is a factor in the excellent heat flow characteristics of the interface between the fins 26 and the tubular shell 38.
lf desired the core 22 may be secured within the tubular shell 38 by furnace brazing as an alternative to the aforesaid preferred expansion technique.
The central passage within tubular core body 24 may either be blocked off against the flow of fluid therethrough so as to force all of the fluid to flow through the flow channels 36, or left open so that fluid will flow both through the flow channels 36 and through the center of core body 24. If there is an unlimited flow of fluid available, then the maximum heat exchange capacity of a tubular heat exchange unit 12 will be achieved by having the center of core body 24 open and passing fluid through both the flow channels 36 and the center of core body 24. However, without a large fluid flow availability the tubular heat exchange unit 12 will be more efficient if the center of core body 24 is blocked off and the fluid is thereby required to flow through the channels 36. An alternative arrangement is to provide valve means within core body 24 which permits the flow of fluid through core body 24 according to the temperature and/or viscosity of the fluid, such alternative being the subject matter of another patent application concurrently filed by the present applicant and entitled Heat Exchange Valve System."
FIG. 3 illustrates a tubular heat exchange unit [20 having a flow control core 22a which includes a tubular body 24a and core fins 26a. This flow control core 220 preferably, but not necessarily, has a cross-sectional configuration like that illustrated in FIG. 2 and described in detail in connection therewith. In the heat exchange unit 120 the core fins 260 are provided with a stepped twist or joggle, while nevertheless being maintained parallel to each other. Thus, each of the core fins 26a is formed to a series of alternating longitudinal portions 44 which are generally parallel to the axis of the core 220 and twisted portions 46 which are inclined at a substantial angle relative to the axis of core 22a so as to be generally helically disposed. The transitions from longitudinal portions 44 to twisted portions 46 and from twisted portions 46 back to longitudinal portions 44 are preferably sharply defined direct angle bends 48 in the core fins 26a. The step twisted or joggled core fins 26a provide step twisted or joggled flow channels 50 therebetween, and each of these channels as it extends longitudinally along the flow control core 22a progresses circumferentially around the flow control core 220, preferably at least l.
The step twisted or joggled flow channels 50 have several important advantages. One advantage is that each direction change imposed upon the fluid flowing through the channels 50 causes a reduced film thickness of the fluid proximate the fin surfaces, thereby improving the heat transfer characteristics. Additionally, each direction change causes a turbulence in the fluid, which further increases the heat transfer characteristics. The sharper and more direct the change in direction of the fluid flow at the angle bends 48, the more effective the film thickness reduction and turbulation, and accordingly the better the heat transfer characteristics. Also, the channels between the twisted fin portions 46 are narrower than those between the straight fin portions 44, whereby the fluid flow in the twisted channels will have increased velocity and reduced pressure (according to Bernoulis principle), which causes a further turbulation, tending to create fluid vortices when the fluid is suddenly subjected to speed reduction, pressure increase and direction change as it enters the straight channels from the twisted channels.
Another important advantage of the step twisted or joggled fin construction as shown in H6. 3 is that it conducts the fluid peripherally around the tubular heat exchange unit 12a from one side to the other in a heat exchange apparatus such as the apparatus 10 that embodies a heat exchange unit 120. Heat exchange apparatus such as apparatus 10 is typically disposed in an airstream which enters through one flat side of the apparatus l0 and leaves through the other, so that the side through which the airstream enters becomes colder than the side from which the air-stream leaves. The stepped twist or joggled arrangement of the core fins 26a thus causes the fluid in the tubular heat exchange unit 12a to rotate around the unit 12a between the cold and hot sides of the overall heat exchange apparatus, producing maximum heat transfer efficiency.
FIG. 4 illustrates a tubular heat exchange unit 12b that is similar to the heat exchange unit 12a shown in P10. 3, but which has annular grooves cut in the core fins thereof by saw or knife cutting or the like for further turbulation of the fluid passing generally axially through the heat exchange unit 12b. Thus, the unit 12b includes flow control core 22b having step twisted or joggled core fins 26b which are parallel and which each include a series of alternate longitudinal portions 44b and twisted portions 46b. The core fins 26b are longitudinally interrupted by a series of longitudinally spaced annular grooves 52 which may extend into the core fins 26b to any desired depth. Preferably, the annular grooves 52 are cut approximately through the entire depth of the core fins 26b to the tubular core body 24b, but if desired the depth of the cut may be either less or more. Some or all of the grooves 52 may be unequally cut, if desired, to an extent providing some communicating passages between the flow control channels defined between adjacent core fins 26b and the bore within the tubular body 24b.
As the fluid passes through a channel defined between either a pair of longitudinal fin portions 44b or a pair of twisted fin portions 46b, the velocity and viscosity of the fluid tend to make its flow become laminar; but before substantial laminar characteristics of flow can be established, the fluid reaches a groove 52 and becomes turbulated to disturb such laminar flow. In this manner, the fluid flow is repeatedly disturbed as the fluid progresses both axially and circumferentially through the heat exchange unit 12b, and optimized heat exchange characteristics are obtained by maintaining a balance of turbulent and laminar flow.
It will be noted that in FIG. 4 the grooves 52 are shown as being cut proximate the angle bends of the step twisted or joggled fins. This provides opposite end faces 54 and 56 on the discrete core fin segments which are proximate the change of direction of flow of the fluid for good turbulating effect of both upstream and downstream faces. The sharp, knife-like corners of the fin segments which face upstream scavenge some of the central fluid flow from each channel and divert it into the next channel and against the fin sides, thereby assuring repeated fin surface contact of all portions of the fluid.
However, if desired the grooves 52 may alternatively be cut through the longitudinal centers of the longitudinal portions 44b and the twisted portions 46b of the core fins 26b; or the grooves 52 may be longitudinally spaced at other intervals.
Satisfactory turbulating results have been achieved with the grooves 52 cut from about 0.020 inch to about V4 inch in axial width, with their centers axially spaced from about V4 inch to about I inch. However, it is preferred to have the axial width of each groove 52 approximately equal to the average core fin thickness, which provides a substantial turbulating gap, without any substantial loss in heat transfer surface area of the fins since the surface area of the added faces 54 and 56 substantially completely compensates for the loss in side surface area of the fins. If the grooves 52 were made substantially wider in the axial direction of the unit 12b, then heat transfer surface of the fins would be sacrificed; while on the other hand, if the grooves 52 were made substantially narrower in the axial direction of the unit 12b, then turbulation would be decreased. Because of the importance of having a maximum amount of heat transfer surface area in the fins, and since the heat transfer area is actually increased by the grooves 52 if they are narrower than the average fin thickness, and heat transfer surface area is not reduced until the width of the grooves 52 becomes greater than the average thickness of the fins, it is preferred according to the invention to provide grooves 52 which are not substantially wider in the axial direction than the average fin thickness.
The stepped type of twist is shown in FIGS. 3 and 4 can be provided by taking an untwisted flow control core 22 such as that shown in FIG. 5 and, before insertion thereof in the outer shell 38, gripping the core 22 at spaced axial locations corresponding to the longitudinal portions 44 of the fins as shown in FIG. 3 and applying the required twisting forces to twist the core 22 until the fins acquire the desired amount of twist, such as the twist of the fin portions 46 as shown in FIG. 3. Gripping force for such twisting action, and definition of discrete angle bends 48, may be achieved by engaging a series of gripping lugs between adjacent core fins proximate the longitudinal portions 44 thereof as shown in FIG. 3, such lugs having substantially the same axial length of the longitudinal fin portions 44 as shown in FIG. 3.
Nevertheless, a tubular heat exchange unit 12 as shown in FIG. 5, including a flow control core 22 having generally straight core fins 26 and intermediate flow channels 36 which are generally parallel to the axis of the heat exchange unit 12, will have good heat exchange characteristics with a cross-sectional configuration generally as shown in FIG. 2.
Referring now to FIG. 6 of the drawings, a tubular heat exchange unit 12: is illustrated which embodies a generally untwisted or straight flow control core 22c having tubular core body 240 and core fins 26c. In this form of the invention a helical groove 58 is provided in the core fins 26c, as by saw or knife cutting or the like, such helical groove 58 separating each of the core fins 260 into a series of discrete core fins sections having end faces 60 and 62. The angular inclines and sharp leading corners of the faces 62 resulting from the helical type groove 58 tend to deflect and swirl the fluid streams in vortexlike movements proximate the groove for good turbulation. The angular faces also tend to circulate the fluid circumferentially as it progresses axially through the heat exchange unit 120, shifting the centers of the fluid streams into contact with fin surfaces and moving the fluid between cold and hot sides of heat exchange apparatus embodying this type of heat exchange unit 12c.
The spiral frequency or number of spirals per inch of the groove 58 is important to the heat transfer capability, and is preferably about the same as the spacing between adjacent grooves 52 in the form shown in FIG. 4. Accordingly, a suitable lead" for the groove 58 is about inch between groove centers for a particular fin, with leads between /4 inch and 1 inch operating satisfactorily, for a flow control core 220 that is roughly 34 inch in diameter. However, an increase in the spiral frequency will generally be desirable to accommodate an increase in the number of fins. As with the grooves 52 of FIG. 4, groove widths for the helical or spiral grooves 58 may be a width from about 0.020 inch to about A inch, but it is preferred that the width be approximately the same as the average thickness of the fins 26c, and not be substantially greater than the average thickness of the fins 260. The helical groove 58 preferably extends radially inwardly through the entire radial depth of the core fins 26c.
While the helical groove form a flow control core has been shown in FIG. 6 with generally straight fins 26c,
it is to be understood that the helical groove may be ap plied to a flow control core according to the invention which has step twisted or joggled core fins like those shown in FIG. 3, or which has helically twisted fins like the fins 26d illlustrated in FIG. 7 which figure illustrates a tubular heat exchange unit 12d having flow control core 24d comprising tubular core body 2411 and the helically twisted fins 26d extending generally radially therefrom. Similarly, the annular type grooves like those shown in FIG. 4 in connection with the step twisted or joggled core fins may alternatively be applied to straight core fins like those shown in FIG. or to helically twisted core fins like those shown in FIG. 7.
If desired, further heat exchange capacity can be provided in tubular heat exchange units according to the present invention by incorporating within the tubular core body a small inner fin structure 64 as shown in FIG. 8, and allowing the fluid to pass through the core body. Such fluid flow may, if desired, be controlled by valve means in the core body 24 which regulates the flow according to the temperature and/or viscosity of the fluid, as shown and described in said concurrently filed application for Heat Exchange Valve System." The inner fin structure 64 shown in FIG. 8 may be formed of a multifolded strip of metal, and fin constructions similar to this are disclosed in the aforesaid Hayden U.S. Pat. No. 3,3l5,464, and also in US. Pat. No. 2,797,554, issued July 2, I957 to W. J. Donovan for Heat Exchanger in Refrigeration System" and US. Pat. No. 3,197,975, issued Aug. 3, 1965 to C. Boling for Refrigeration System and Heat Exchangers. If desired, the inner fin structure 64 may be supported in its operative position by a central core 65 which is shown as a rod, but may be a small tube.
FIG. 9 illustrates a tubular heat exchange unit according to the present invention wherein the flow control core 66 has a tubular core body 68 with integral core fins 70 which expand radially outwardly from the core body 68 to the outer shell 38 with generally flat, radially oriented sides 72.
FIG. illustrates a tubular heat exchange unit which is generally inverted or inside out from the other forms of the invention disclosed herein, having a flow control core 74 that consists of an outer tubular core body 76 having integral inwardly extending fins 78 therein, the core body 76 and fins 78 preferably being formed together by extrusion. The inner tubular shell 80 may be a separately extruded tube that is inserted inside the inner ends of the fins 78 and then expanded outwardly against the fins 78. If desired, such outward expansion of the inner shell 80 may be sufficient to cause an overall outward expansion of the outer tubular core body 76 for securing the latter in a series of fins such as the fins 14 shown in FIGS. I and 13.
FIG. 11 illustrates heat exchange apparatus generally designated 82 comprising a spiral finned outer shell 84 commonly referred to as Wolverine tubing, with a flow control core 22 of the present invention fitted therein. The core 22 is preferably expanded outwardly into intimate heat transfer engagement with the inner tubular surface of the shell 84 generally in the manner illustrated in FIG. 13. Heat exchange apparatus 82 of this type is particularly useful for small heat exchange requirements wherein a plurality of tubular heat exchange units such as the arrangement in FIG. 1 is not required.
FIG. 12 illustrates a further type of heat exchange apparatus 86 within which tubular heat exchange units I2 according to the present invention may be employed. The apparatus 86 includes a tubular outer shell 88 within which a bundle of the heat exchange units 12 is contained, the outer shell 88 having inlet and outlet conduits 90 and 92 for circulation of one fluid about the outsides of the tubular heat exchange units 12 through the interstitial flow channels 94; while the ends of the heat exchange units 12 communicate with respective headers (not shown) for passage of another fluid through the heat exchange units 12. Heat exchange apparatus of this general type is illustrated in the aforesaid Donovan US. Pat. No. 2,797,554.
In general, tubular heat exchange units 12 according to the present invention will provide improved heat exchange performance in any type of heat exchange apparatus which employs tubular heat exchange members therein, such as the apparatus 10 shown in FIG. 1, apparatus similar to that of FIG. 1 but with a plurality of the tubular heat exchange units arranged for parallel flow between end headers, the apparatus 82 shown in FIG. 11, the apparatus 86 shown in FIG. 12, or other heat exchange apparatus.
While the instant invention has been shown and described herein in what are conceived to be the most practical and preferred embodiments, it is recognized that departures may be made therefrom within the scope of the invention. I claim:
1. A tubular heat exchange conduit which comprises an elongated central tubular core, a plurality of elongated, generally longitudinally arranged, circumferentially spaced heat transfer fins extending generally radially outwardlly from said core, both sides of each of said fins being concavely curved in the general radial direction throughout substantially their entire radial width, with their outer edges being thicker than inner portions thereof and an elongated, tubular shell peripherally engaged about and in heat conducting abutting relationship with the outer edges of said fins, said core, fins and shell defining a plurality of fluid flow channels between adjacent pairs of the fins.
2. A tubular heat exchange unit as defined in claim 1, wherein said concave fin sides are of generally parabolic curvature.
3. A tubular heat exchange unit as defined in claim 1, wherein the rate of curvature of said concave fin sides increases progressively from the root portions to the toe portions of the fins, so that the thickness of the fins increases at greater than a linear rate from said root portions,
4. A tubular heat exchange unit as defined in claim 1, wherein said tubular core is compsed of a heat conducting metal that is hardest proximate said tubular core and is progressively softer from said core radially outwardly through said fins to the outer edges of the fins.
5. A tubular heat exchange unit as defined in claim 4, wherein said shell is composed of heat conducting metal that is harder than the outer edge portions of said fins that are in contact therewith.
6. A tubular heat exchange unit as defined in claim 1, which includes a series of external fins arranged over said shell with their planes generally normal to the axis of the tubular unit, said shell being generally radially outwardly stressed by said extrusion core and fins against said external fins.
7. A tubular heat exchange unit as defined in claim 1, wherein said shell has spiral external fin means externally formed thereon.
8. A tubular heat exchange unit as defined in claim I, which includes an elongated inner fin structure disposed within said tubular core 9. A tubular heat exchange unit as defined in claim 1, having grooves segmenting said fins throughout substantially their entire height, said groove means comprising a series of longitudinally spaced, generally circumferentially arranged grooves in the fins.
13. A tubular heat exchange unit as defined in claim 12, wherein said groove means comprises a generally spirally arranged groove in the fins.
14. A tubular heat exchange unit as defined in claim 12, wherein said groove means comprises a series of longitudinally spaced, generally transverse grooves in the fins, the widths of said grooves being not substantially greater in the longitudinal direction of the fins than the average fin thickness.
15. A tubular heat exchange unit as defined in claim 14, wherein the widths of said grooves are substantially the same in the longitudinal direction of the fins as the average fin thickness.
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US2212932 *||28 Oct 1938||27 Aug 1940||Fairlie Andrew Miller||Filling material for reaction spaces|
|US2960114 *||26 Apr 1957||15 Nov 1960||Bell & Gossett Co||Innerfinned heat transfer tubes|
|US3212992 *||17 Mar 1961||19 Oct 1965||Commissariat Energie Atomique||Nuclear fuel element casing|
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US4154296 *||1 Aug 1977||15 May 1979||American Standard Inc.||Inner finned heat exchanger tube|
|US4168618 *||7 Jul 1978||25 Sep 1979||Wieland-Werke Aktiengesellschaft||Y and T-finned tubes and methods and apparatus for their making|
|US4175416 *||11 Jan 1978||27 Nov 1979||Hitachi, Ltd.||Apparatus for manufacturing heat transfer tubes|
|US4179911 *||7 Jul 1978||25 Dec 1979||Wieland-Werke Aktiengesellschaft||Y and T-finned tubes and methods and apparatus for their making|
|US4337824 *||24 Oct 1980||6 Jul 1982||Amtrol||Double wall heat exchanger|
|US4353234 *||14 Dec 1978||12 Oct 1982||Carrier Corporation||Heat transfer surface and method of manufacture|
|US4419802 *||11 Sep 1980||13 Dec 1983||Riese W A||Method of forming a heat exchanger tube|
|US4527624 *||18 Jun 1984||9 Jul 1985||Sanyo Electric Co., Ltd.||Cooling device for refrigerator|
|US4546819 *||10 Feb 1984||15 Oct 1985||Amtrol Inc.||Double wall heat exchanger|
|US4991643 *||23 Aug 1989||12 Feb 1991||Hayden, Inc.||Heat exchanger with internal bypass valve|
|US5098514 *||17 Aug 1990||24 Mar 1992||Kurt Held||Double band press with heatable or coolable parts and method for their fabrication|
|US5214928 *||2 Apr 1991||1 Jun 1993||Omega Enterprises, Inc.||Refrigeration apparatus and methods|
|US5613368 *||16 Nov 1995||25 Mar 1997||Omega Enterprises, Inc.||Refrigeration apparatus and methods|
|US5765596 *||16 Jun 1995||16 Jun 1998||Hps Merrimac||Ceramic heat exchanger|
|US6434972||20 Sep 2000||20 Aug 2002||Behr Gmbh & Co.||Air conditioner with internal heat exchanger and method of making same|
|US6751983 *||18 Sep 2000||22 Jun 2004||Behr Gmbh & Co.||Air conditioning unit with an inner heat transfer unit|
|US6819561||2 Oct 2002||16 Nov 2004||Satcon Technology Corporation||Finned-tube heat exchangers and cold plates, self-cooling electronic component systems using same, and methods for cooling electronic components using same|
|US6883601 *||23 Oct 2001||26 Apr 2005||Eaton Fluid Power Gmbh||Air conditioner with internal heat exchanger and heat exchanger tube therefor|
|US7059390 *||3 May 2005||13 Jun 2006||Abb Oy||Cooling element|
|US7191824||21 Nov 2003||20 Mar 2007||Dana Canada Corporation||Tubular charge air cooler|
|US8550147 *||14 Aug 2009||8 Oct 2013||Clear Vision Associates, Llc||Windshield washer fluid heater and system|
|US8925620||27 Dec 2011||6 Jan 2015||Tsm Corporation||Windshield washer fluid heater|
|US9149847 *||4 Jan 2005||6 Oct 2015||Halla Visteon Climate Control Corporation||Indented tube for a heat exchanger|
|US20050109493 *||21 Nov 2003||26 May 2005||Wu Alan K.||Tubular charge air cooler|
|US20050142049 *||31 Dec 2003||30 Jun 2005||Amsden Jeffrey M.||Multi-tubular reactors with monolithic catalysts|
|US20050274505 *||3 May 2005||15 Dec 2005||Risto Laurila||Cooling element|
|US20070235163 *||4 Jan 2005||11 Oct 2007||Holden Jerry L||Indented Tube for a Heat Exchanger|
|US20090242184 *||31 Jan 2007||1 Oct 2009||Shi Mechanical & Equipment Inc.||Spiral Tube Fin Heat Exchanger|
|US20090308051 *||17 Dec 2009||Gea Rainey Corporation||Heat exchanger tube and air-to-air intercooler|
|US20100037415 *||18 Feb 2010||Lansinger Jere R||Windshield washer fluid heater and system|
|US20150219405 *||5 Feb 2014||6 Aug 2015||Lennox Industries Inc.||Cladded brazed alloy tube for system components|
|CN104154791A *||1 Aug 2014||19 Nov 2014||兰州交通大学||Streamline constant-amplitude parabolic corrugated fin for elliptical tube and fin heat exchanger|
|DE19944951A1 *||20 Sep 1999||22 Mar 2001||Behr Gmbh & Co||Air conditioning system has refrigerant circuit in which concentric tubular heat exchangers are inserted and wound in radial spiral or meandering form|
|DE19944951B4 *||20 Sep 1999||10 Jun 2010||Behr Gmbh & Co. Kg||Klimaanlage mit innerem Wärmeübertrager|
|DE102011100683A1 *||6 May 2011||8 Nov 2012||GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware)||Wärmetauscher für eine Kraftfahrzeug-Klimaanlage|
|DE102013020469A1 *||6 Dec 2013||11 Jun 2015||Webasto SE||Wärmeübertrager und Verfahren zum Herstellen eines Wärmeübertragers|
|EP2313295A2 *||18 Aug 2009||27 Apr 2011||Jere R. Lansinger||Windshield washer fluid heater and system|
|EP2313295A4 *||18 Aug 2009||23 Apr 2014||Jere R Lansinger||Windshield washer fluid heater and system|
|WO1991002936A1 *||16 Aug 1990||7 Mar 1991||Hayden Inc||Heat exchanger with internal bypass valve|
|WO1996024811A1 *||7 Feb 1996||15 Aug 1996||Equion Corp||Heat exchanger|
|WO2012167279A1 *||4 Jun 2012||6 Dec 2012||Holtec International, Inc.||Vertical bundle air-cooled heat exchnager, method of manufacturing the same, and power generation plant implementing the same|
|U.S. Classification||165/179, 165/DIG.520, 29/890.49, 29/890.47, 165/184|
|International Classification||F28F13/12, F28F1/42|
|Cooperative Classification||Y10S165/52, F28F1/42, F28F13/12, F28F1/40, F28F1/32, F28F2255/16|
|European Classification||F28F1/42, F28F13/12|
|8 Jul 1988||AS17||Release by secured party|
Owner name: CONNECTICUT BANK AND TRUST COMPANY, N.A.
Effective date: 19861024
Owner name: HAYDEN, INC., 1531 POMONA ROAD, CORONA, CA A CORP.
|8 Jul 1988||AS||Assignment|
Owner name: HAYDEN, INC., 1531 POMONA ROAD, CORONA, CA A CORP
Free format text: RELEASED BY SECURED PARTY;ASSIGNOR:CONNECTICUT BANK AND TRUST COMPANY, N.A.;REEL/FRAME:004907/0221
Effective date: 19861024
Owner name: HAYDEN, INC.,CALIFORNIA
|29 Oct 1985||AS||Assignment|
Owner name: CONNECTICUT BANK AND TRUST COMPANY, N.A., THE, 900
Free format text: SECURITY INTEREST;ASSIGNOR:HAYDEN, INC.;REEL/FRAME:004473/0803
Effective date: 19851023
|29 Oct 1985||AS06||Security interest|
Owner name: CONNECTICUT BANK AND TRUST COMPANY, N.A., THE, 900
Owner name: HAYDEN, INC.
Effective date: 19851023