US3827484A

US3827484A - Liquid metal heat exchanger

Info

Publication number: US3827484A
Application number: US00321507A
Authority: US
Inventors: W Wolowodiuk
Original assignee: Individual
Current assignee: Individual
Priority date: 1970-02-04
Filing date: 1973-01-08
Publication date: 1974-08-06
Anticipated expiration: 1991-08-06

Abstract

A liquid metal heat exchanger in which one of the heat exchange fluids flows alternately radially inward and outward across a series of circular baffles to exchange heat with another heat exchange fluid flowing through a plurality of tubes perpendicular to the baffles in which the first mentioned fluid is not excessively accelerated at any point in its travel across the baffles. The tubes are arranged in concentric circular rows with the spacing between tubes in each row being smaller at larger circles than at comparatively smaller circles.

Description

llnited tates Patent Wolowodiuk Aug. 6, 11974 [54] LIQUlD METAL HEAT EXCHANGER 3,333,630 8/l967 Charcharos 165/[58 2| 11970 B l I65 l6l X [76] Inventor: Walter Wolowodiuk, 51 Evergreen yer ey New Providence 07974 Primary ExaminerAlbert W. Davis, Jr. [22] Filed: Jan. 8, 1973 Attorney, Agent, or Firm.lohn E. Wilson; Marvin A. 21 Appl. No.: 321,507 Nagur Related U.S. Application Data [57] ABSTRACT [63] Continuation-impart of Ser. No. 8,50], Feb. 4, 1970, A q id m tal h at xchanger in which one of the abandoned. heat exchange fluids flows alternately radially inward and outward across a series of circular baffles to ex- [52] U.S. Cl 165/161, 165/158, 165/159, change heat with another heat exchange fluid flowing 122/32 through a plurality of tubes perpendicular to the baf- [51] Int. Cl F28f 9/22 fles in which the first mentioned fluid is not exces- [58] Field of Search 165/ 159, 160, 161, 157, sively accelerated at any point in its travel across the 165/158; 122/32-34 baffles. The tubes are arranged in concentric circular rows with the spacing between tubes in each row [56] References Cited being smaller at larger circles than at comparatively UNITED STATES PATENTS Smaller clrcles- 2,930,592 3/1960 Long et al 165/161 X 4 Claims, 3 Drawing Figures 34 p if 27 r -44 J2 kW/f LIQUID METAL HEAT EXCHANGER CROSS-REFERENCE TO A RELATED APPLICATION This application is a continuation-in-part of US. Pat. application Ser. No. 8,501 filed on Feb. 4, 1970, now abandoned in the name of Walter Wolowodiuk.

BACKGROUND OF THE INVENTION The invention described herein was made in the course of or under a contract with the U. S. Atomic Energy Commission.

In the development of nuclear power plants in which the reactor is cooled by liquid metal, it is necessary to use heat exchangers in which the heat is transferred from the liquid metal. If the heat exchanger is a socalled intermediate heat exchanger, the heat is transferred to another stream of liquid metal. If the heat exchanger is a steam generator or a superheater, the heat is transferred to water or steam. In either case, the liquid metal in moving through the heat exchanger can induce high vibration if it is made to change velocity abruptly. The vibration and the high heat densities and thermal gradients which appear in different regions of the heat exchangers necessitate a skillful design if the heat exchanger is to operate safely over an extended period.

SUMMARY OF THE INVENTION It is an object of the present invention to overcome drawbacks found in the prior art such as those discussed above. Accordingly, a heat exchanger which is supplied heat by a stream of flowing liquid metal comprises a plurality of tubes arranged in concentric circles and which pass through a series of annular baffles which cause the liquid metal to flow alternately radially inward and radially outward across the tubes, the tubes being arranged so that the total of the areas between the tubes on any of the circles is approximately the same.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an elevation view partly in section showing a preferred embodiment of the present invention;

FIG. 2 is a plan view of a quadrant of the tube bundle of the present invention; and

FIG. 3 is a view taken substantially along the line 3-3 of FIG. 1.

DESCRIPTION OF THE PREFERRED EMBODIMENT In FIG. 1, a heat exchanger indicated generally as consists of an outer shell 12 of generally cylindrical shape having a curved bottom 14 with a primary outlet 16 located at the center of the bottom. The heat exchanger 10 has a neck 18 which is of a diameter smaller than that of the outer shell 12 and which extends up from a flange 19 which is secured to the top of the shell 12. Besides the outer shell 12, the heat exchanger 10 has an inner shell 20 which is generally cylindrical. Extending down into the shell 20 is a cylindrical tube or center pipe 22, open at the top to function as the secondary liquid inlet, terminating in a flow guide assembly 22(a) almost touching a tube sheet 24 which is jointed at its periphery to the top of the shell 20. The space between the lower end of the assembly 22(a) and the tube sheet 24 is large enough to accommodate thermal expansion of the former. Guides (not shown) may be relied upon to maintain center pipe 22 in a vertical direction.

The tube sheet 24 is curved, i.e., it is concave downward and completely closes off the inner shell 20 at the bottom thereof. The top of the inner shell 20 is joined to the periphery of an annular concave upward tube sheet 26 which extends upward and inward to the vertical collar portion 27 which extends up to the flange 19.

The outer shell 12 is provided with a primary inlet 32 which opens into the space above the upper tube sheet 26 and below the flange 19 while a secondary outlet 34 in the neck 18 communicates with the annular space between the neck 18 and the center pipe 22.

A tube bundle 36 which is illustrated in phantom in FIG. 1 is positioned in the annular space between the center pipe 22 and the shell 20. The tube bundle 36 consists of vertically extending tubes 38 some of which are shown in FIG. 2 and all of which are shown in FIG. 3. The tubes 38 are arranged in circular rows which are radially spaced equally apart. The circumferential pitch of the tubes 38, that is, the space between them, decreases as the radius increases for a purpose to be later described.

The annular tube bundle 36 tenninates at the upper end in the upper tube sheet 26 and at the lower end in the lower tube sheet 24. Thus, primary fluid entering through the primary inlet 32 fills the space above the upper tube sheet 26 and enters into the tubes 38 through the tube sheet 26, passes down through the tube bundle 36 and immerges from the tube sheet 34 into the cavity below the tube sheet 24. Thereafter, the primary liquid leaves the heat exchanger 10 through the primary outlet 16. Single-headed arrows indicate this flow in FIG. 1.

The flow guide assembly 22(a) at the lower end of pipe 22 includes a plurality of flow guides 42, the function of which will be described hereinafter. The tube bundle 36 is supported by a plurality of flow baffles 44 and that alternate along the axis of the heat exchanger 10. Each of the

flow baffles

44 and 45 engages every tube 38 of the tube bundle 36 such that every tube 38 is supported at its intersection with each of the baffles. Baffles 44 may consist of scalloped rings which are mechanically welded together. An expansion loop, as understood in the art, is provided in the region designated by double arrow (a) with a support 46 located in the middle of the expansion loop.

Secondary liquid metal enters heat exchanger 10 through the center pipe 22 and flows downward through it to exit at its bottom being directed outward by the flow guides 42 of the flow guide assembly 22(a). Thus, the secondary liquid metal flows out into the annular space between the center pipe 22 and the inner shell 20 to flow upward between and in contact with the tubes 38 and then through the annular collar portion 27 and out of the heat exchanger 10 through the secondary outlet 34.

The flow baffles 44 differ from the flow baffles 45 in that the flow baffles 44 contact at their inner edges the center pipe 22 and extend outward to a circle spaced from the inner shell 20. The flow baffles 45 contact at their outer peripheries the inner shell 20 and extend inward to a circle spaced from the center pipe 22. These two types of

flow baffles

44 and 45 are alternately spaced so that secondary fluid when flowing upward in the annular space between the center pipe 22 and the inner shell will flow alternately inward and outward as it makes its way through the tube bundle 36. This arrangement allows for an effective transfer of heat between the primary and secondary fluid.

One problem in heat exchangers of this type is that the secondary fluid will experience acceleration forces as it moves radially over the tube 38. The acceleration forces are caused primarily because as the secondary fluid flows radially, it encounters varying resistance to flow as it moves between adjacent tubes 38. This is so because if the tubes are uniformly spaced as is common in heat exchangers, there will be progressively more spaces and thus more area for the fluid to move through as the fluid moves radially outward. Thus, the resistance to flow will become less as the fluid moves outward and more as it moves inward. The result is acceleration forces on the fluid and consequently, vibration will develop in the heat exchanger.

In the present invention, this problem is overcome by placing all of the tubes 38 on concentric circles as shown best perhaps in FIG. 3. Thus, the tubes 38 are all positioned in rows which lie on one of a number of

concentric circles

50, 52, 54, 56 or 58. FIG. 3 shows only five circumferential rows of tubes. This is for the sake of simplicity and in all probability, in practice, there would be more rows of tubes, as indicated in FIG. 2.

As shown in FIG. 3, the tubes 38 on the circular row 50 are separated by a distance 60 between adjacent tubes. Similarily, adjacent tubes in row 52 are separated by a distance 62, adjacent tubes in row 54 are separated by a distance 64, adjacent tubes in row 56 are separated by a distance 66 and adjacent tubes in row 58 are separated by a distance 68. The distance 68 is less than the distance 66 which is less than the distance 64, which is less than the distance 62, which is less than the distance 60. Furthermore, the

distances

60, 62, 64, 66 and 68 are chosen so that the sum of the distances between all of the tubes on any one of the

circles

50, 52, 54, 56 or 58 is the same as the sum of the distances between tubes on any other of those circles. Since the

flow baffles

44 and 45 are parallel, this means that the sum of the areas between tubes on any of the concentric circles will be the same and therefore, the total resistance to flow at any circle as to any fluid moving radially over the circles will be the same. The elimination of excessive acceleration greatly reduces vibration which would otherwise be inclined by the flowing fluid.

The use of curved tube sheets instead of the customary flat tube sheets reduces the minimum allowable thickness of the metal so that the construction is more economical and thermal stresses are minimized. Any

vibration which does occur in the present invention is handled because of the annular construction of the

baffles

44 and 45 which allows them to support each tube at many points along its length.

The foregoing describes but one embodiment of the present invention, other embodiments being possible without exceeding the scope of the present invention as defined in the following claims.

I claim:

I. A heat exchanger where liquid metal flows over tubes which contain another flowing heat exchange fluid comprising:

a. a shell;

b. a pipe extending down into said shell and forming a central passageway surrounded by and communicating at one of its ends with an annular passageway between said pipe and said shell forming a double pass for said liquid metal;

0. an annularly arranged tube bundle having a plurality of tubes extending through said annular passageway for carrying a single pass of said other heat exchange liquid, said tubes being arranged in a number of concentric circles with the distance between adjacent tubes on each circle being chosen so that the sum of the distances between adjacent tubes will be substantially equal at each circle; and

d. annular baffles for supporting said tubes, said baffles being parallel to each other and axially spaced and encircling said tube bundle and being of two types, one of said types of baffles extending outwardly from said pipe to a circle spaced inwardly from said shell, the other of said types extending inwardly from said shell to a circle spaced outwardly from said pipes, said types being alternately spaced so that they direct said liquid metal alternately radially inward and radially outward across said tubes as said liquid metal passes along the length of said passageway, said arrangement of tubes being such as to assure a substantially constant velocity of said liquid metal across each of said baffles.

2. The heat exchanger of claim 1 in which said tube bundle at each of its ends is provided with curved tube sheets to support and seal the ends of said tubes.

3. The heat exchanger of claim 2 in which flow vanes are provided at the exit of said pipe for directing said liquid metal into the entrance of said annular passageway to insure smooth flow conditions.

4. The heat exchanger of claim 3 in which the passageways are vertically disposed and the other heat exchange fluid makes a single pass downward through said tube sheets.

Claims

1. A heat exchanger where liquid metal flows over tubes which contain another flowing heat exchange fluid comprising: a. a shell; b. a pipe extending down into said shell and forming a central passageway surrounded by and communicating at one of its ends with an annular passageway between said pipe and said shell forming a double pass for said liquid metal; c. an annularly arranged tube bundle having a plurality of tubes extending through said annular passageway for carrying a single pass of said other heat exchange liquid, said tubes being arranged in a number of concentric circles with the distance between adjacent tubes on each circle being chosen so that the sum of the distances between adjacent tubes will be substantially equal at each circle; and d. annular baffles for supporting said tubes, said baffles being parallel to each other and axially spaced and encircling said tube bundle and being of two types, one of said types of baffles extending outwardly from said pipe to a circle spaced inwardly from said shell, the other of said types extending inwardly from said shell to a circle spaced outwardly from said pipes, said types being alternately spaced so that they direct said liquid metal alternately radially inward and radially outward across said tubes as said liquid metal passes along The length of said passageway, said arrangement of tubes being such as to assure a substantially constant velocity of said liquid metal across each of said baffles.