METHOD AND APPARATUS FOR SECURING TUBES IN A STEAM GENERATOR AGAINST VIBRATION

Abstract

A method of and apparatus for securing tubes within a steam generator against vibration with a metallic anti-vibration bar in a tube bundle. The tube bundle has a plurality of tubes, arranged in rows and columns, with lanes between the tube columns. The method comprises the steps of: inserting the anti-vibration bar in the tube bundle; plastically expanding the wall of the anti-vibration bar from an unexpanded position to an expanded position. In the unexpanded position there are a plurality of gaps between the anti-vibration bar and the tubes of the tube bundle. The gaps decrease in size as the wall of the anti-vibration bar moves from the unexpanded position to the expanded position.

Description

BACKGROUND

1. Field

The disclosed concept pertains generally to a method of securing tubes in a steam generator against vibration, and in particular to a method of securing tubes against vibration with an anti-vibration bar. The disclosed concept also pertains to a steam generator including anti-vibration bars.

2. Background Information

Heat exchangers having tube bundles are commonly employed in pressurized water nuclear reactor systems. A steam generator generally comprises a vertically oriented shell, a tube bundle formed of tubes which each comprise two vertical components that meet at a bend portion, a tube sheet for supporting the tubes at the ends opposite the bend portion, a dividing plate that cooperates with the tube sheet and a hemispheric channel head to form a primary fluid inlet header at one end of the tube bundle and a primary fluid outlet header at the other end of the tube bundle. A primary fluid inlet nozzle is in fluid communication with the primary fluid inlet header and a primary fluid outlet nozzle is in fluid communication with the primary fluid outlet header. The steam generator secondary side comprises a wrapper disposed between the tube bundle and the shell to form an annular chamber made up of the shell on the outside and the wrapper on the inside, and a feedwater ring disposed above the bend portion of the tube bundle.

The primary fluid having been heated by circulation through the reactor core enters the steam generator through the primary fluid inlet nozzle. From the primary fluid inlet nozzle, the primary fluid is conducted through the primary fluid inlet header, through the inside of the tube bundle, out the primary fluid outlet header, through the primary fluid outlet nozzle to the reactor coolant pump for recirculation. At the same time, feedwater is introduced to the steam generator secondary side through a feedwater nozzle which is connected to the feedwater ring inside the steam generator. Upon entering the steam generator, the feedwater mixes with water returning from moisture separators positioned above the tube bundle, referred to as the recirculation stream. This mixture, called the downcomer flow, is conducted down the annular chamber between the shell and the wrapper until the tube sheet near the bottom of the annular chamber causes the water to change direction, passing in heat exchange relationship with the outside of the heat exchanger tubes and up through the inside of the wrapper. While the water is circulating in heat exchange relationship with the tube bundle, heat is transferred from the primary fluid in the tubes to the water surrounding the tubes, causing a portion of the water outside the tubes to be converted to steam. The steam-water mixture then rises and is conducted through a number of moisture separators that separate any entrained water from the steam, and the steam vapor then exits the steam generator and is circulated typically through a turbine generator to generate electricity in a manner well known in the art.

The portion of the steam generator primarily including the bend portion of the heat exchanger tubes and the channel head is typically referred to as the evaporator section. The portion of the steam generator above the tubes that includes the moisture separators is typically referred to as the steam drum. Feedwater enters the steam generator through an inlet nozzle which is disposed in the upper portion of the cylindrical shell. The feedwater is distributed and mixed with water removed by the moisture separators and then flows down the annular channel surrounding the tube bundle.

The heat exchanger tubes are supported at their open ends by conventional means whereby the ends of the tubes are seal welded to the tube sheet which is disposed transverse to the longitudinal axis of the steam generator. A series of tube support plates or grids arranged in an axial spaced relationship to each other are provided along the straight portion of the tubes in order to support the straight section of the tubing. Regarding the tube bundle, various steam generators utilize different heat exchanger tube configurations, for example wherein the bend portion is curved or U-shaped, or wherein the vertical components of the heat exchanger tubes each bend at sharp angles, forming a relatively horizontal shaped bend portion.

Located within the bend portion of the tubes are a plurality of anti-vibration bars which are typically disposed between each column of the bend portion of the tubes. The anti-vibration bars provide support and do not substantially interfere with the flow of the moisture laden steam. The anti-vibration bars are intended to prevent excessive vibrations of the individual tubes of the entire tube bundle. The vibrations in question are caused by the flow of water and steam past the tubes. These flow-induced vibrations can potentially damage the tubes. It is well known that the bend portion of the tube bundle is more severely affected by the vibrations, and, because of the bend configuration, more difficult to adequately support in order to eliminate the vibrations. While the advent of the anti-vibration bars has materially reduced the magnitude and presence of vibrations, they have not in all cases completely eliminated damage which is caused by vibrations.

The mechanical aspects of the tube bundle are major obstacles to finding a mechanical solution to this problem. The heat exchanger tubes of the tube bundle have dimensional tolerances associated with their outer diameter. There can also be variations caused by ovalization of some tubes as a result of the bending in the bend portion. Furthermore, the spatial relationship between adjacent tubes is a variable, albeit, within design limits. Thus, there is a dimensional tolerance associated with the nominal spacing between the steam generator tubes. Additionally, current anti-vibration bar designs require a small clearance to facilitate assembly, which results in post-assembly gaps.

These gaps are undesirable because they allow vibration of the tubes and relative motion between the tubes and the anti-vibration bars. The relative motion can cause wear and subsequent damage and possibly failure of the tubes. Therefore, it is important to control the spacing between the heat exchanger tubes and the anti-vibration bars for vibration control purposes. Accordingly, it is an object of this invention to decrease the size of the gaps between the anti-vibration bars and the tubes of the steam generator.

SUMMARY

These needs and others are met by the disclosed concept in which the wall of a metallic anti-vibration bar is adapted to plastically expand from an unexpanded position to an expanded position.

In accordance with one aspect of the disclosed concept, a method is provided for securing tubes within a steam generator against vibration with a metallic anti-vibration bar in a tube bundle, wherein the tube bundle has a plurality of tubes, arranged in rows and columns, with lanes between the tube columns. The method comprises the steps of: inserting the anti-vibration bar in the tube bundle; and plastically expanding the wall of the anti-vibration bar from an unexpanded position to an expanded position. In the unexpanded position, there are a plurality of gaps between the anti-vibration bar and the tubes of the tube bundle, the gaps decreasing in size as the wall of the anti-vibration bar moves from the unexpanded position to the expanded position.

As another aspect of the disclosed concept, a steam generator is provided. The steam generator has a primary side for circulating a heated fluid and a secondary side having an axial dimension, for circulating a fluid to be heated by the heated fluid circulating in the primary side. The steam generator comprises: a channel head for receiving the heated fluid; a tube sheet that separates the channel head from the secondary side; a tube bundle having a plurality of tubes, arranged in rows and columns, with lanes between the tube columns, the tube bundle extending from the channel head, through the tube sheet and through at least a portion of the secondary side; and at least one metallic anti-vibration bar disposed within the tube bundle. The wall of the at least one anti-vibration bar is structured to plastically expand from an unexpanded position to an expanded position. In the unexpanded position there are a plurality of gaps between the at least one anti-vibration bar and the tubes of the tube bundle. The gaps decrease in size as the wall of the at least one anti-vibration bar moves from the unexpanded position to the expanded position.

BRIEF DESCRIPTION OF THE DRAWINGS

A full understanding of the disclosed concept can be gained from the following description of the preferred embodiments when read in conjunction with the accompanying drawings in which:

FIG. 1 is a perspective view, partially cut away, of a vertical tube and shell steam generator;

FIG. 2 is a side view of an anti-vibration bar in an unexpanded position in accordance with an exemplary embodiment of the disclosed concept;

FIG. 2A is a side view of an anti-vibration bar in accordance with an alternative embodiment of the disclosed concept;

FIG. 3 is a front view of the anti-vibration bar of FIG. 2;

FIG. 4 is a cross-sectional view of the anti-vibration bar of FIG. 2 situated between two heat exchanger tubes of a steam generator;

FIG. 5 is a cross-sectional view of the anti-vibration bar of FIG. 4 in an expanded position situated between the two heat exchanger tubes;

FIG. 6 is a schematic view of a portion of a tube bundle of a steam generator with anti-vibration bars in an unexpanded position situated between heat exchanger tubes in accordance with an alternative embodiment of the disclosed concept;

FIG. 7 is a schematic view of the portion of the tube bundle of FIG. 6 with the anti-vibration bars in an expanded position;

FIG. 8 is a side view of a portion of a steam generator including two anti-vibration bars in a bend portion of a tube bundle in accordance with the disclosed concept;

FIG. 9A is a side view of an anti-vibration bar tree configuration in accordance with the disclosed concept;

FIG. 9B is a side view of another anti-vibration bar tree configuration in accordance with the disclosed concept;

FIG. 9C is a side view of a further anti-vibration bar tree configuration in accordance with the disclosed concept; and

FIG. 9D is a side view of an additional anti-vibration bar tree configuration in accordance with the disclosed concept.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

Referring now to the drawings, FIG. 1 shows a steam generator 2 that utilizes a plurality of heat exchanger tubes 3 which form a tube bundle 4 to provide the heating surface required to transfer heat from the primary fluid to vaporize or boil the secondary fluid. The steam generator 2 comprises a vessel having a vertically oriented tubular shell portion 6 and a top enclosure or dished head 8 enclosing the upper end and a generally hemispherical-shaped channel head 10 enclosing the lower end. The lower shell portion 6 is smaller in diameter than the upper shell portion 12 and a frustoconical-shaped transition 14 connects the upper and lower portions. A tube sheet 16 is attached to the channel head 10 and has a plurality of holes 18 disposed therein to receive ends of the tubes 3. A dividing plate 22 is centrally disposed within the channel head 10 to divide the channel head 10 into two compartments 24 and 26, which serve as headers for the tube bundle 4. Compartment 26 is the primary fluid inlet compartment and has a primary fluid inlet nozzle 27 in fluid communication therewith. Compartment 24 is the primary fluid outlet compartment and has a primary fluid outlet nozzle 28 in fluid communication therewith. Thus, primary fluid, i.e., the reactor coolant, which enters fluid compartment 26 is caused to flow through the tube bundle 4 and out through outlet nozzle 28.

The tube bundle 4 is encircled by a wrapper 30 which forms an annular passage 32 between the wrapper 30 and the shell and transition portions 6 and 14, respectively. The top of the wrapper 30 is covered by a lower deck plate 34 which includes a plurality of openings 36 in fluid communication with a plurality of riser tubes 38. Swirl vanes 40 are disposed within the riser tubes 38 to cause steam flowing therethrough to spin and centrifugally remove some of the moisture contained within the steam as it flows through this primary centrifugal separator. The water separated from the steam in this primary separator is returned to the top surface of the lower deck plate 34. After flowing through the primary centrifugal separator, the steam passes through a secondary separator 42 before reaching a steam outlet nozzle 44 centrally disposed in the dished head 8. The water separated from the steam in the secondary separator 42 is returned to mix with the water returned from the primary separator above the lower deck plate 34.

The feedwater inlet structure of this steam generator 2 includes a feedwater inlet nozzle 46 having a generally horizontal portion called a feedring 48 and discharge nozzles 50 elevated above the feedring 48. Feedwater, which is supplied through the feedwater inlet nozzle 46, passes through the feedwater ring 48, exits through the discharge nozzles 50 and mixes with water which was separated from the steam and is recirculated. The mixture then flows down above the lower deck plate 34 into the annular downcomer passage 32. The water then enters the tube bundle 4 at the lower portion of the wrapper 30 and flows among the tubes 3 and up the tube bundle 4 where it is heated to generate steam.

As previously mentioned, the tube bundle 4 has a plurality of anti-vibration bars (not shown in FIG. 1) located between the tubes 3. As will be discussed below in connection with FIGS. 2 through 9D, the size of the gaps between anti-vibration bars and heat exchanger tubes can be decreased by plastically expanding the walls of anti-vibration bars from unexpanded positions to expanded positions.

Referring to FIGS. 2 and 3, a generally V-shaped anti-vibration bar 100 in accordance with one embodiment of the disclosed concept is shown. As seen, two chambers 102,104 are disposed within the anti-vibration bar 100 between the ends. The anti-vibration bar 100 may be made by any suitable mechanism known in the art (e.g., without limitation, a weldment of a tube that has been plastically compressed). Schematically shown, the chambers 102,104 terminate at an end 110 that is sealed. The end 110 may be sealed by any suitable mechanism known in the art (e.g., without limitation, being welded shut). The other end of the anti-vibration bar 100 includes a coupling assembly (schematically shown as 106) which may remain on the anti-vibration bar 100 while the steam generator (not shown) is in operation. The coupling assembly 106 may be, for example and without limitation, a quick connect pressure fitting. The coupling assembly 106 is adapted to be removably coupled to a pressure source 108 which may be, for example and without limitation, a hydraulic or pneumatic pressure source.

During fabrication of the anti-vibration bar 100, the bend region may become sealed. FIG. 2A shows an alternative embodiment of the disclosed concept in which a generally V-shaped anti-vibration bar 100′, similar to the anti-vibration bar 100 shown in FIGS. 2 and 3, is adapted to be coupled to two pressure sources 108′, one at each end of the anti-vibration bar 100′.

Referring to FIG. 4, the chambers 102,104 are oval shaped. However, it is within the scope of the disclosed concept for the chambers to be other shapes (e.g., without limitation, round or rectangular shaped). Additionally, although the anti-vibration bar 100 has two chambers 102,104, it is within the scope of the disclosed concept for an anti-vibration bar (not shown) to have one chamber or more than two chambers. The anti-vibration bar 100 is inserted into the tube bundle of a steam generator (not shown). FIG. 4 shows the anti-vibration bar 100 located between two heat exchanger tubes 150 of a steam generator (not shown) after it has been inserted. As seen, the anti-vibration bar 100 has a thickness 152 that is smaller than a distance 154 between the heat exchanger tubes 150. In other words, there is a gap between the heat exchanger tubes 150 and the anti-vibration bar 100.

FIG. 4 shows the wall of the anti-vibration bar 100 in an unexpanded position 103. As seen the anti-vibration bar 100 is substantially flattened in the unexpanded position 103. Referring to FIGS. 2 through 5, the pressure sources 108,108′ plastically expand the walls of the anti-vibration bars 100,100′. The pressure source 108 plastically expands the wall of the anti-vibration bar 100 from the unexpanded position 103 to an expanded position 103′, seen in FIG. 5. Referring to FIG. 2A, the pressure sources 108′ likewise plastically expand the wall of the anti-vibration bar 100′. The pressure sources 108,108′ are removed before the steam generator (not shown) is placed into service. The pressure required to plastically expand the wall of any given anti-vibration bar varies depending on many factors such as material, size, and tube pitch. However, the pressure has to be sufficient to plastically expand the material so that the expanded section does not return to the original geometry once the pressure is removed. If a pneumatic pressure source is employed, the pressure required to plastically expand the wall of the anti-vibration bar 100,100′ is preferably less than 1,000 psi, more preferably being less than 500 psi. In other words, the expansion has to be irreversible rather than an elastic expansion. Regarding material, the anti-vibration bar 100 is metallic and may be made of any material suitable for plastically expanding the wall from the unexpanded position 103 to the expanded position 103′ in a steam generator (e.g., without limitation, stainless steel).

As the wall of the anti-vibration bar 100 is plastically expanded to the expanded position 103′, the gaps between the heat exchanger tubes 150 and the anti-vibration bar 100 are decreased in size. This elimination of space between the heat exchanger tubes 150 and the anti-vibration bar 100 reduces vibrations which, in turn, advantageously reduces wear and damage of the heat exchanger tubes 150 during the operation of the steam generator (not shown). As seen in FIG. 5, there is a substantially tangential contact between the anti-vibration bar 100 and the heat exchanger tubes 150.

However, the disclosed concept is not limited to situations where the gaps are merely decreased in size, resulting in less space or a tangential contact. For example and without limitation, it is also within the scope of the disclosed concept for gaps to be eliminated such that a residual preload is created between the anti-vibration bar 100 and the heat exchanger tubes 150 of the tube bundle when the wall of the anti-vibration bar 100 is in the expanded position 103′. In this manner, the elastic rebound of the heat exchanger tubes 150 exceeds the rebound of the chambers 102,104, resulting in more than a tangential contact between the anti-vibration bar 100 and the heat exchanger tubes 150.

Referring to FIGS. 6 and 7, an alternative embodiment of the disclosed concept is provided. Schematically shown, a plurality of linear anti-vibration bars 200 are located between a plurality of heat exchanger tubes 250. Unlike the anti-vibration bars 100,100′, each anti-vibration bar 200 is an individual tube, distinct from the heat exchanger tubes 250, that is plastically compressed, becoming substantially flattened, and sealed at one end before being inserted into the tube bundle of the steam generator (not shown). Furthermore, unlike the anti-vibration bars 100,100′, which are generally V-shaped, the anti-vibration bars 200 are generally linear, being located along a longitudinal axis between the ends.

Schematically shown, one end of each anti-vibration bar 200 includes a coupling assembly 206 which may be any suitable assembly known in the art (e.g., without limitation, a quick connect pressure fitting). The coupling assembly 206 may be left on while the steam generator (not shown) is in operation. Furthermore, the coupling assembly 206 is adapted to be removably coupled to a pressure source 212 which may be, for example and without limitation, a hydraulic or pneumatic pressure source. Schematically shown, the anti-vibration bars 200 have opposite ends 214 that are sealed. The ends 214 may be sealed by any suitable mechanism known in the art (e.g., without limitation, being welded shut). The anti-vibration bars are substantially flattened in unexpanded positions 203, seen in FIG. 6, and the pressure source 212 plastically expands the walls to expanded positions 203′, seen in FIG. 7. If a pneumatic pressure source is employed, the pressure required to plastically expand the walls of the anti-vibration bars 200 is preferably less than 1,000 psi, more preferably being less than 500 psi. Furthermore, the pressure source 212 is removed before the steam generator (not shown) is placed into service.

When the walls of the anti-vibration bars 200 are in the unexpanded positions 203, the heat exchanger tubes 250 have a distance 216 between any given pair of adjacent columns that is greater than a thickness 218 of the anti-vibration bars 200. In other words, there is a gap between the heat exchanger tubes 250 and the anti-vibration bars 200 when the walls of the anti-vibration bars 200 are in the unexpanded positions 203. As the walls of the anti-vibration bars 200 plastically expand from the unexpanded positions 203 to the expanded positions 203′, the size of the gaps decreases. This elimination of space between the heat exchanger tubes 250 and the anti-vibration bars 200 reduces vibration of the heat exchanger tubes 250 which, in turn, advantageously reduces wear and damage of the heat exchanger tubes 250 during operation of the steam generator (not shown).

It is also within the scope of the disclosed concept for gaps to be eliminated such that a residual preload is created between the anti-vibration bars 200 and the heat exchanger tubes 250. FIG. 7 shows the contact between the anti-vibration bars 200 and the heat exchanger tubes 250 when the walls of the anti-vibration bars 200 are in the expanded positions 203′. As seen, the anti-vibration bars 200 become partially sinuous such that more than a tangential contact is created with the heat exchanger tubes 250 of the tube bundle.

Continuing to refer to FIGS. 6 and 7, the exemplary heat exchanger tubes 250 have a triangular pitch. Seen in FIG. 6, any two adjacent heat exchanger tubes 250 have an equal distance 220 between their centers. The disclosed concept however, is not limited to arrangements wherein the heat exchanger tubes 250 have a triangular pitch (e.g., without limitation, the disclosed concept may be employed with heat exchanger tubes (not shown) that have a square pitch or a rotated square pitch (e.g., diamond shape)).

The disclosed concept has been described in association with generally V-shaped anti-vibration bars 100,100′ that have chambers (see for example chambers 102,104) along the edges, and linear anti-vibration bars 200 that are plastically compressed tubes that are substantially flat when the walls are in the unexpanded positions 203. However, the disclosed concept may be employed with alternative configurations of anti-vibration bars (e.g., without limitation, FIGS. 8 through 9D). FIG. 8 shows two anti-vibration bars 302,304 located in a bend portion 306 of a tube and shell steam generator 300. As seen, the anti-vibration bars 302,304 are generally V-shaped, the first anti-vibration bar 302 having an angle 310 and the second anti-vibration bar 304 having an angle 312.

The walls of the anti-vibration bars 302,304 are structured to plastically expand between unexpanded positions and expanded positions. The anti-vibration bars 302,304 may have chambers (not shown) similar to the chambers 102,104 of the anti-vibration bar 100. It is also within the scope of the disclosed concept for the anti-vibration bars 302,304 to be individual tubes that have been bent to be generally V-shaped and plastically compressed to be substantially flat, before being placed into the steam generator 300. In this manner, when the walls are plastically expanded, gaps between the anti-vibration bars 302,304 and the heat exchanger tubes 308 are advantageously decreased in size. The heat exchanger tubes 308 generally have a U-shaped curvature in the bend portion 306 of the steam generator 300. The disclosed concept also applies to other steam generators (not shown). For example and without limitation, steam generators wherein the heat exchanger tubes each bend at sharp angles in the bend portion, forming a relatively horizontal shaped bend portion.

FIGS. 9A through 9D show a few of the many alternative, non-limiting configurations of anti-vibration bars 400,420,440,460, which may be employed in the tube bundle of a steam generator (not shown). The walls of the anti-vibration bars 400,420,440,460 are structured to plastically expand between unexpanded positions and expanded positions. As the walls of the anti-vibration bars 400,420,440,460 expand, the size of the gaps between anti-vibration bars 400,420,440,460 and the surrounding heat exchanger tubes (not shown) advantageously decrease in size.

The anti-vibration bars 400,420,440,460 are each weldments of numerous bars and have at least one sealed end and at least another end that is coupled to a pressure source (not shown). The individual bars that make up the anti-vibration bars 400,420,440,460 may have one or more chambers (not shown) similar to the chambers 102,104 of the anti-vibration bar 100. The individual bars that make up the anti-vibration bars 400,420,440,460 may also be tubes that are plastically compressed and/or bent before being placed into a given steam generator (not shown).

The foregoing description of the invention has been presented for purposes of illustration and description. It is not intended to be exhaustive or to limit the invention to the precise form disclosed, and other modifications and variations may be possible in light of the above teachings. The embodiments were chosen and described in order to best explain the principles of the invention and its practical application to thereby enable others skilled in the art to best utilize the invention in various embodiments and various modifications as are suited to the particular use contemplated. It is intended that the appended claims be construed to include other alternative embodiments of the invention except insofar as limited by the prior art.

As employed herein, the statement that two or more parts or components are “coupled” together shall mean that the parts are joined or operate together either directly or through one or more intermediate parts or components.

Claims

1. A method of securing tubes within a steam generator against vibration with a metallic anti-vibration bar in a tube bundle, wherein the tube bundle has a plurality of tubes, arranged in rows and columns, with lanes between the tube columns, the method comprising the steps of: inserting the anti-vibration bar in the tube bundle;plastically expanding the wall of the anti-vibration bar from an unexpanded position to an expanded position;wherein in the unexpanded position there are a plurality of gaps between the anti-vibration bar and the tubes of the tube bundle, the gaps decreasing in size as the wall of the anti-vibration bar moves from the unexpanded position to the expanded position; andwherein in the unexpanded position the anti-vibration bar is substantially flattened.

2. The method of claim 1 wherein a residual preload is created between the anti-vibration bar and the tubes of the tube bundle when the wall of the anti-vibration bar is in the expanded position; and wherein more than a tangential contact is created between the anti-vibration bar and the tubes in the tube bundle when the wall of the anti-vibration bar is in the expanded position.

3. The method of claim 1 wherein the anti-vibration bar is another tube, the another tube having a first end that is sealed and a second end that is coupled to a pressure source, the another tube being disposed in a longitudinal axis situated between the first end and the second end; wherein the pressure source plastically expands the wall of the another tube from the unexpanded position to the expanded position.

4. The method of claim 3 wherein the first end is welded shut.

5. The method of claim 3 wherein the pressure source is a hydraulic or pneumatic pressure source and the second end includes a coupling assembly, the hydraulic or pneumatic pressure source being removably coupled to the coupling assembly.

6. The method of claim 5 wherein the pressure source is a hydraulic pressure source and the hydraulic pressure source is removed before the steam generator is placed into service.

7. The method of claim 5 wherein the pressure source is a pneumatic pressure source, the pneumatic pressure source being removed before the steam generator is placed into service, and wherein the pressure required to plastically expand the wall of the another tube is less than 500 psi.

8. The method of claim 1 wherein the anti-vibration bar has a first end, a second end, and a first chamber disposed within the anti-vibration bar between the first end and the second end, the first end being coupled to a pressure source, the pressure source plastically expanding the wall of the first chamber from the unexpanded position to the expanded position.

9. The method of claim 8 wherein the anti-vibration bar has a second chamber disposed within the anti-vibration bar between the first end and the second end, the pressure source plastically expanding the wall of the second chamber from the unexpanded position to the expanded position.

10. The method of claim 9 wherein the first chamber and the second chamber are each either round shaped or oval shaped.

11. The method of claim 9 wherein the pressure source is a hydraulic pressure source and the first end includes a coupling assembly, the hydraulic pressure source being removably coupled to the coupling assembly.

12. A steam generator having a primary side for circulating a heated fluid and a secondary side having an axial dimension, for circulating a fluid to be heated by the heated fluid circulating in the primary side, comprising: a channel head for receiving the heated fluid;a tube sheet that separates the channel head from the secondary side;a tube bundle having a plurality of tubes, arranged in rows and columns, with lanes between the tube columns, the tube bundle extending from the channel head, through the tube sheet and through at least a portion of the secondary side;at least one metallic anti-vibration bar disposed within the tube bundle;wherein the wall of the at least one anti-vibration bar is structured to plastically expand from an unexpanded position to an expanded position;wherein in the unexpanded position there are a plurality of gaps between the at least one anti-vibration bar and the tubes of the tube bundle, the gaps decreasing in size as the wall of the at least one anti-vibration bar moves from the unexpanded position to the expanded position; andwherein in the unexpanded position the at least one anti-vibration bar is substantially flattened.

13. The steam generator of claim 12 wherein more than a tangential contact is created between the at least one anti-vibration bar and the tubes of the tube bundle when the at least one anti-vibration bar is in the expanded position; and wherein a residual preload is created between the at least one anti-vibration bar and the tubes of the tube bundle when the wall of the at least one anti-vibration bar is in the expanded position.

14. The steam generator of claim 12 wherein the at least one anti-vibration bar is another tube, the another tube having a first end that is sealed and a second end that is adapted to be coupled to a pressure source, the another tube being disposed in a longitudinal axis situated between the first end and the second end; wherein the pressure source plastically expands the wall of the another tube from the unexpanded position to the expanded position.

15. The steam generator of claim 14 wherein the first end is welded shut.

16. The steam generator of claim 14 wherein the pressure source is a pneumatic pressure source, the pneumatic pressure source being removed before the steam generator is placed into service, and wherein the pressure required to plastically expand the wall of the another tube is less than 500 psi.

17. The steam generator of claim 12 wherein the at least one anti-vibration bar has a first end, a second end, and a first chamber disposed within the at least one anti-vibration bar between the first end and the second end, the first end being adapted to be coupled to a pressure source, the pressure source being structured to plastically expand the wall of the first chamber from the unexpanded position to the expanded position.

18. The steam generator of claim 17 wherein the at least one anti-vibration bar has a second chamber disposed within the at least one anti-vibration bar between the first end and the second end, the pressure source being structured to plastically expand the wall of the second chamber from the unexpanded position to the expanded position.

19. The steam generator of claim 18 wherein the first chamber and the second chamber are each either round shaped or oval shaped.

20. The steam generator of claim 18 wherein the pressure source is a hydraulic or pneumatic pressure source and the first end includes a coupling assembly.