JP2012021560A - Seal structure for heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an improved seal structure for a heat exchanger in which a variation in interval between flange surfaces owing to a thermal expansion difference between devices along with a temperature change is suppressed or resolved and a variation in interval between flange surfaces which is caused by a flange rotation is suppressed or resolved, to eliminate leakage.SOLUTION: In the seal structure for a heat exchanger, a main container Y1 and a tube plate Y2 are clamped and connected with a seal ring R in between. An annular concave slot m in which the seal ring R is inserted is formed at the tube plate Y2, and an annular ridge j in which the annular concave slot m can be inserted is formed at a flange f of the main container Y1. The seal ring R is wound spirally by a plurality of times, while a metal band whose cross section is wave-like and a band-like expanded graphite are overlapped each other, constituting a spiral part. In an assembled state in which the flange f and the tube plate Y2 are clamped and connected, a spacer L is interposed between the flange f and the tube plate Y2 so that the seal ring R inserted into the annular concave slot m is compressed by a predetermined amount by the annular ridge j.

Description

  The present invention relates to a seal structure used for a heat exchanger such as a fuel oil heater in a thermal power generation facility and a feed water heater in a power plant, that is, a seal structure for a heat exchanger.

  As an example of a heat exchanger, the water supply applied to the heat exchanger applied to the exhaust heat recovery apparatus of the thermal power plant disclosed in Patent Document 1 or the feed water heating system of the power plant disclosed in Patent Document 2 A heater is mentioned. As a conventional example of the heat exchanger seal structure, as disclosed in Patent Document 3, between the tube plate (8) of the body (10) and the water chamber flange (12) of the water chamber (11). There is known one having a seal ring (gasket: 1) interposed. That is, the heat exchanger seal structure is simply expressed by sandwiching an annular seal between a pair of flange surfaces.

  Conventionally, a heat exchanger seal structure generally uses a metal jacket type gasket or a spiral wound gasket (see Patent Document 3) which has a large compression amount and excellent heat resistance. These gaskets exhibit sufficient sealing performance if the initial state is maintained in which the gap between the flange surfaces does not change (the flange is not deformed) from the time of assembly (initial assembly state). However, it has been found that leaks cannot be completely eliminated due to various phenomena (causes) in actual use situations.

  That is, the gap between the pair of flange surfaces may repeatedly increase and decrease due to the difference in thermal expansion between the equipment and its parts accompanying temperature changes, resulting in over-compression and permanent deformation of the gasket. However, it cannot follow it, the tightening pressure gradually decreases, and finally leakage occurs.

  In addition, leakage may occur due to the flange rotation. As shown in FIG. 12, the flange rotation causes each flange 34, 35 or one flange 34 or 35 to undergo a curved deformation (also referred to as rotational deformation) with respect to the gasket G due to a bolt fastening force or fluid pressure. That is. When this occurs, the gap between the flanges 34 and 35 is increased and decreased, which is a disadvantageous phenomenon that leakage occurs. These inconveniences appear more prominent when the flange has a large diameter.

Japanese Patent Laid-Open No. 08-121703 Japanese Patent Laid-Open No. 11-101403 Japanese Patent Laid-Open No. 10-111092

  The object of the present invention is to suppress or eliminate the above-mentioned inconveniences, that is, to suppress or eliminate the change in the spacing between the flange surfaces due to the difference in thermal expansion of the equipment due to temperature change, and to suppress or eliminate the change in the spacing between the flange surfaces due to flange rotation. Therefore, the present invention is to provide a heat exchanger sealing structure which is improved so as not to leak.

The invention according to claim 1 is a first cylindrically-shaped bottom-constituting component Y1 that constitutes a fluid container 4 for internally circulating a fluid to be controlled in temperature, and a first component that is connected and integrated with the first constituent component Y1. 2 component Y2, and a seal ring R interposed between the first component Y1 and the second component Y2, and a flange f formed at an end of the first component Y1; In the heat exchanger seal structure in which the second component Y2 is tightened and connected via the seal ring R,
Either one of the flange f and the second component Y2 is formed with an annular recess groove m into which the seal ring R is fitted and deployed, and either the flange f or the second component Y2 On the other hand, an annular protrusion j that can be fitted into the annular recessed groove m is formed,
The seal ring R is configured to have a structure having a spiral portion u formed by spirally winding a metal strip k having a corrugated cross section and a strip-shaped expanded graphite d in a state of being superposed on each other, and the flange f In the assembled state in which the second component Y2 is tightened and connected, the seal ring R fitted and deployed in the annular recess groove m is compressed by a predetermined amount by the annular protrusion j. Thus, a spacer L interposed between the flange f and the second component Y2 is provided.

  The invention according to claim 2 is the heat exchanger seal structure according to claim 1, wherein the flange f, the second component Y2, and the spacer L have the same or substantially the same hardness. It is characterized by being formed.

  According to a third aspect of the present invention, in the heat exchanger sealing structure according to the first or second aspect, only the metal band k is swirled a plurality of times at the radially inner end and / or radially outer end of the spiral portion u. It is characterized by being wound into a shape.

  The invention according to claim 4 is the heat exchanger seal structure according to any one of claims 1 to 3, wherein the seal ring R is disposed on the inner diameter side of the spiral part u and the thickness of the spiral part u. The protrusion prevention ring r having a thickness smaller than a value obtained by subtracting the predetermined amount from the above is integrally provided.

  According to a fifth aspect of the present invention, in the heat exchanger seal structure according to any one of the first to fourth aspects, the means 7 for tightening and connecting the flange f and the second component Y2 includes: It is a plurality of bolts arranged across the outer peripheral portions, and the spacer L is configured in a ring shape fitted for each appropriate bolt 7 of the plurality of bolts 7. It is what.

  The invention according to claim 6 is the heat exchanger seal structure according to any one of claims 1 to 5, wherein a seal member h for short-circuiting the inner peripheral ends of the seal ring R is provided. It is characterized by.

  The invention according to claim 7 is the heat exchanger seal structure according to any one of claims 1 to 6, wherein the fluid container 4 is a fuel oil heater for fuel in a thermal power generation facility. It is characterized by.

  According to the first aspect of the present invention, the seal ring having a spiral wound gasket structure inserted and arranged in the annular recessed groove is forcibly sandwiched and compressed between the annular recessed groove and the annular protrusion, and the first component The second component is connected to the second component by a spacer. Accordingly, since the seal ring is sandwiched and interposed by a spacer structure disposed between the flange and the second component, the first component and the second component are locally deformed or the above-described flange rotation is performed. Will not occur. And since it is the connection structure excellent in the rigidity, the distortion resulting from the thermal expansion difference of each part accompanying a temperature change will also be suppressed. As a result, it is possible to suppress or eliminate the change in the gap between the flange surfaces due to the difference in thermal expansion of the equipment due to the temperature change, and to suppress or eliminate the change in the gap between the flange faces due to the flange rotation so that no leakage occurs. A heat exchanger sealing structure can be provided.

  According to the invention of claim 2, the flange, the second component, and the spacer have the same or substantially the same hardness. If the spacer is harder than the flange or the second component, the flange or the second component may be damaged by the spacer, and if the flange or the second component is replaced or repaired, enormous costs are incurred. In addition, when the flange or the second component is harder than the spacer, the spacer is likely to be abnormally deformed, which may cause early deterioration of the sealing performance of the spiral portion. On the other hand, the seal structure according to the third aspect of the present invention has an advantage that a good sealing function can be exhibited without incurring any of them and without increasing the cost.

  The invention according to claim 3 has the following effects. That is, in the structure in which the seal ring is forcibly sandwiched and compressed between the annular recessed groove and the annular protrusion, the radial direction of both of them is set so that the annular recessed groove and the annular protrusion are smoothly fitted during assembly. Is set to have a certain gap. Therefore, when a seal ring having only a spiral portion in which a metal strip and strip-shaped expanded graphite are overlapped and wound is used, the inner and outer ends of the annular ridge are positioned in the expanded graphite portion due to the presence of the gap. The ring may be compressed, and if that happens, relatively soft expanded graphite will protrude into the gap with a metal band, and there will be no particular problem if it is seen as the surface pressure of the entire seal ring. There is a risk that the seal surface pressure slightly decreases at the end. On the other hand, in the seal structure according to the invention of claim 3, a portion where no expanded graphite exists is obtained by winding only a metal strip in a spiral shape at the inner diameter end part and / or outer diameter end part of the spiral part. Since it is intentionally provided, the inner and outer ends of the annular ridge are not located in the expanded graphite portion even when forcedly compressed by the annular recessed groove and the annular ridge, and the metal strip is advantageous in strength and rigidity. Will be located in the part. Therefore, there is no fear that the above-mentioned “expanded graphite is squeezed out into the gap with a metal band”, and there is an advantage that the desired surface pressure is maintained and the sealing performance can be further improved.

  As in the invention of claim 4, it may be a seal ring equipped with a protrusion preventing ring inside the spiral portion, and a further improvement in sealing performance can be expected. Also, when disassembling the seal structure, if the spiral part sticks to the flange etc. (sticks) and cannot be removed easily, it can be peeled off by hooking a tool on the protrusion prevention ring. There is also an accompanying effect that the handleability is excellent.

  According to the invention of claim 5, the connecting structure can be realized at low cost and with high productivity by using a bolt with a simple structure, and if the spacer is a ring-shaped one interposed by the bolt, any additional parts or special parts can be obtained. There is an advantage that an assembling method and a reliable sealing structure with a spacer can be provided without any trouble.

  As in the sixth aspect of the invention, a seal ring provided with a seal member for short-circuiting the inner peripheral ends is also useful depending on the situation of the equipment used or for sealing the internal structure. Furthermore, the heat exchanger seal structure according to the present invention is very suitable for a fuel oil heater as defined in claim 7.

Schematic diagram showing schematic configuration of thermal power generation equipment Front view showing a fuel oil heater (heat exchanger) (a) is a side view in the Z direction of the fuel oil heater of FIG. 2, and (b) is a cross-sectional view taken along the line II of FIG. Expanded sectional view of the main part showing the heat exchanger seal structure (Examples 1 and 2) (A) is sectional drawing of the principal part which shows a 1st seal structure, (b) is sectional drawing of the principal part which shows a 2nd seal structure. The 1st seal ring is shown, (a) is a front view, (b) is an AA line sectional view. The 2nd seal ring is shown, (a) is a front view, (b) is a BB line sectional view. The arrangement state of the spacer is shown, (a) is the first seal ring side, (b) is the second seal ring side. (A) is a principal part expanded sectional view of the seal structure for heat exchangers (Examples 3 and 4), (b) is a sectional view of the principal part showing the seal structure. The 3rd seal ring is shown, (a) is a front view, (b) is a CC line sectional view. The 4th seal ring is shown, (a) is a front view, (b) is a DD line sectional view. Sectional view of the main part of a conventional seal structure showing flange rotation

  Embodiments of a heat exchanger seal structure according to the present invention will be described below with reference to the drawings when applied to a thermal power generation facility.

Examples 1 and 2
FIG. 1 shows a schematic diagram of a thermal power generation facility. The fuel oil (heavy oil, etc.) carried by the tanker F is first transferred to the storage tank Q, where a necessary amount is stored. The fuel oil discharged from the storage tank Q is heated (heated) to a temperature suitable for combustion by a fuel oil heater (an example of a heat exchanger) H, and the heated fuel oil is supplied to the boiler V and combusted. The generator E is moved by the turbine T driven by the pressure to generate electric power.

  As shown in FIGS. 2 and 4, the fuel oil heater H includes a main container 1 formed in a bottomed cylindrical shape, an auxiliary container 2, and a tube plate 3 interposed between the two and 1 and 2. And a fluid container 4 having a capsule shape (long cylindrical container shape) having an axis P. The main container 1 and the tube sheet 3 are bolted together with a first seal ring 5 interposed therebetween, and the auxiliary container 2 and the tube sheet 3 are interposed a second seal ring 6 therebetween. Bolts are connected in a state where

  The main container 1 is a steel plate container main body 1H, heated fluid supply / discharge ports 1a and 1b, flanges formed on the opening side (flange forming the opening) 1F, curved from the opening side end to the bottom. A vertical partition wall 1d extending toward the side wall 1c is provided. The vertical partition wall 1d exists as a vertical wall extending from the opening side end to the vicinity of the bottom 1c. As shown in FIG. 3B, the internal space of the main container 1 is divided into a low temperature chamber 1e and a high temperature chamber 1f. The low temperature chamber 1e and the high temperature chamber 1f communicate with each other at the bottom 1c side end. A large number of heating heat pipes (not shown) are accommodated in both the chambers 1e and 1f.

  As shown in FIGS. 2 and 3 (a), the auxiliary container 2 includes a steel plate main body 2H, an inlet pipe 2a, an outlet pipe 2b, a curved side wall 2c as a bottom, a vertical partition wall 2d, and a flange 2F. Is a bottomed cylindrical member having a structure in which the main container 1 is shortened. The vertical partition wall 2d is formed over the entire length in the axis P direction, and divides the inside into an inlet chamber 2e that communicates with the inlet pipe 2a and an outlet chamber 2f that communicates with the outlet pipe 2b. . Further, as shown in FIG. 4, a vertical partition wall 3d is also formed on the tube plate 3, and the internal space is divided into right and left, and accordingly, the low temperature chamber 1e and the inlet chamber 2e, and the high temperature chamber 1f and the outlet chamber are divided. Each s of 2f communicates with each other.

  Low-temperature (normal temperature) fuel oil e entering from the inlet pipe 2a passes through one of the inlet chamber 2e and the tube plate 3 and enters the low-temperature chamber 1e toward the bottom 1c while being heated by a number of heat pipes (not shown). move on. That is, it proceeds on the forward path w1 (portion indicated by the broken arrow) including the inlet chamber 2e and the low temperature chamber 1e. Next, the bottom 1c portion enters the high temperature chamber 1f as indicated by the arrow a, proceeds while being heated by a number of heat pipes (not shown), and enters the outlet chamber 2f through the other inside of the tube plate 3. That is, it proceeds on the return path w2 (the portion indicated by the two-dot broken line arrow) including the high temperature chamber 1f, the outlet chamber 2f, and the like. Then, the fuel oil e sufficiently heated by the low temperature chamber 1e and the high temperature chamber 1f goes out from the outlet pipe 2b. This is the heating (heating) action of the fuel oil in the fuel oil heater H. Next, the seal structure will be described.

  The heat exchanger seal structure is a first seal portion S1 according to the first embodiment formed over the main container 1 and the tube plate 3, and a second embodiment formed over the auxiliary container 2 and the tube plate 3. The second seal portion S2 is pointed to both. First, the first seal part S1 will be described.

  As shown in FIGS. 4 and 5A, the first seal portion S1 includes a first flange 1F (an example of a flange f) and a tube of the main container 1 (an example of a bottomed cylindrical first component Y1). A state in which the plate 3 (an example of the second constituent element Y2) and a first seal ring 5 (an example of the seal ring R) interposed between the plates 1F and 3 are sandwiched between the first seal ring 5 The first flange 1F and the tube sheet 3 are connected by tightening using a plurality of bolts 7.

  A first annular recess groove 8 (an example of an annular recess groove m) in which the first seal ring 5 is fitted and deployed is formed on the first side circumferential surface 3a of the tube plate 3, and the first annular recess groove 8 A first annular protrusion 9 (an example of an annular protrusion j) that can be fitted is formed on the side peripheral surface 10 of the first flange 1F. The first annular recess groove 8 is a circumferential groove having a rectangular cross section having a seal surface 8s that contacts the first seal ring 5 as a bottom surface, and the first annular protrusion 9 is a first seal. The cross section having a seal surface 9s abutting on the ring 5 as a top surface is a circular strip having a rectangular shape. The diameter of the first annular protrusion 9 is set so that it enters the first annular recess groove 8 in a state where a slight gap (several millimeters: for example, 1 to 3 mm) is formed both inside and outside the diameter. Has been made.

  As shown in FIGS. 5A, 6A, and 6B, the first seal ring 5 is a state in which a metal band k having a corrugated cross section and a band-shaped expanded graphite d that is a filler material are polymerized with each other. Are formed in a flat cylindrical shape having a spiral portion u wound in a spiral shape and a protrusion prevention ring r that is integrally provided inside the spiral portion u. . The thickness of the protrusion prevention ring r is set to a value smaller than a value obtained by subtracting a predetermined amount described later from the thickness of the spiral portion u. For example, when the thickness of the spiral portion u is 4.5 mm and the thickness of the protrusion prevention ring r is 3.0 m, the predetermined amount t exceeds 0 and less than 1.5 mm (0 <t <1. 5).

  In the assembled state (state shown in FIG. 5A) in which the first flange 1F and the tube plate 3 are tightened and connected by a plurality of bolts 7 provided at equal angles with respect to the axis P, the first annular recess is provided. A spacer 15 (spacer) interposed between the first flange 1F and the tube plate 3 so that the first seal ring 5 fitted and deployed in the groove 8 is compressed by a predetermined amount by the first annular protrusion 9. L) is equipped. As an example, as shown in FIG. 8A, the spacer 15 made of carbon steel is an appropriate one of 40 bolts 7, for example, three in the circumferential direction, one is skipped, and the three are skipped in this order. Thus, it is configured in a ring shape that is fitted to 12 bolts 7 in total.

  With the above configuration, in the first seal portion S1, the assembled state tightened with the plurality of bolts 7 is an assembled state in which the spacer 15 is included, and the first annular recessed groove 8 The first seal ring 5 positioned inside is forcibly centered by the seal surface 8s of the first annular recess groove 8 and the seal surface 9s of the first annular protrusion 9 where the spiral portions u are close to each other. It is compressed by a predetermined amount in the direction.

  Next, as shown in FIG. 4 and FIG. 5B, the second seal portion S <b> 2 includes the second flange 2 </ b> F (an example of the flange f) of the auxiliary container 2 (an example of the bottomed cylindrical first component Y <b> 1). ) And the tube plate 3 (an example of the second component Y2), and a second seal ring 6 (an example of the seal ring R) interposed between the two 2F and 3; The second flange 2F and the tube sheet 3 are connected by being tightened using a plurality of bolts 11 while being sandwiched.

  A second annular recessed groove 12 (an example of the annular recessed groove m) for fitting and deploying the second seal ring 6 is formed on the second side peripheral surface 3b of the tube plate 3, and the second annular recessed groove 12 is formed in the second annular recessed groove 12. The 2nd annular protrusion 13 (an example of the annular protrusion j) which can be fitted is formed in the side peripheral surface 14 of the 2nd flange 2F, respectively. The second annular recess groove 12 is a circumferential groove having a rectangular cross section having a seal surface 12s abutting against the second seal ring 6 as a bottom surface, and the second annular protrusion 13 is a second seal. The cross section having a seal surface 13s abutting on the ring 6 as a top surface is a circular strip having a rectangular shape. The diameter of the second annular protrusion 13 enters the second annular recessed groove 12 in a state in which some gaps c1 and c2 (about several millimeters: for example, 1 to 3 mm) are formed on both the outer side and the inner side. Dimension setting is made. The same applies to the case of the first seal ring 5.

  As shown in FIGS. 5B and 7, the second seal ring 6 is a spiral formed by winding a metal strip k having a corrugated cross section and a strip-shaped expanded graphite d into a spiral shape a plurality of times. It is configured in a flat cylindrical shape having a protrusion u (reinforcing ring) r and a seal member h, which are integrally provided inside the diameter u of the spiral portion u. The thickness of the protrusion prevention ring r is set to a value smaller than a value obtained by subtracting a predetermined amount described later from the thickness of the spiral portion u. For example, when the thickness of the spiral portion u is 4.5 mm and the thickness of the protrusion prevention ring r is 2.7 m, the predetermined amount t exceeds 0 and less than 1.8 mm (0 <t <1. 8).

  The seal member h connects the inner peripheral ends of the second seal ring 6, that is, the inner peripheral ends of the protrusion prevention ring r, and is made of a pipe that passes through the axis P and is a single vertical end. The short-circuit member 17 and a plurality of horizontal short-circuit members 18 made of pipe are welded and integrated. The vertical short-circuit member 17 is arranged and set so as to overlap the vertical partition wall 3d when viewed in the direction of the axis P, and the inside of the protrusion prevention ring r can be made to correspond to the forward path w1 and the backward path w2. Yes. The pipes constituting the vertical short-circuit member 17 and the horizontal short-circuit member 18 are made of metal such as stainless steel and can exhibit a sealing function by being compressed and deformed in the same manner as the spiral portion u in the assembled state. In addition, although illustration is abbreviate | omitted, the groove | channel for letting the sealing member h of the 2nd seal ring 6 and the 4th seal ring 20 mentioned later pass is formed in each flange f.

  In the assembled state (state shown in FIG. 5 (b)) in which the second flange 2F and the tube sheet 3 are tightened and connected by a plurality of bolts 11 provided at equal angles with respect to the axis P, the second annular recess is provided. A spacer 16 (spacer) interposed between the second flange 2F and the tube plate 3 so that the second seal ring 6 fitted and deployed in the groove 12 is compressed by a predetermined amount by the second annular protrusion 13. L) is equipped. As shown in FIG. 8 (b), the spacers 16 are appropriately connected to 12 bolts 11 in the order of three of the 44 bolts 11 in an appropriate order, that is, in the circumferential direction. It is configured in a ring shape to be fitted.

  8 (a) and 8 (b) show only the arrangement state of the bolts 7 and 11, and the bolt 7 in which the spacers 15 and 16 are externally fitted (fitted) and the spacers 15 and 16 are externally fitted (fitted). Bolts 7 that are not mounted are drawn respectively. The number of spacers 15 and 16 should be small in terms of cost and labor for assembly / disassembly, but in reality, more than half of the total number of bolts 7 are installed from the viewpoint of the function of maintaining surface pressure and spacing. It is considered desirable. The first flange 1F, the spacer 15, the tube plate 3, the spacer 16, and the second flange 2F are set to have the same or substantially the same hardness within the range of, for example, a Brinell hardness HB120 or less. desirable.

  In a large heat exchanger such as a fuel oil heater having a fluid container 4 with a diameter of about 2 m, it is often difficult to realize a small or slight modification as a very large modification. In addition, with the passage of time, the seal ring is strongly pressed and stuck to the seal surface of each component, so it cannot be removed easily, and frequent seal replacement work is not easy. May also affect performance. Therefore, the improvement of the leak and the improvement of the durability have a great merit in practical use.

[Examples 3 and 4]
Now, a heat exchanger seal structure applied to the fuel oil heater H having different specifications from those used in the first and second embodiments may be used. That is, as shown in FIG. 9A, a fuel oil heater H having a structure in which the main container 21 and the auxiliary container 22 have the same inner diameter and outer diameter and the same flanges 21F and 22F, The third seal portion S3 according to the third embodiment configured across the main container 21 and the tube plate 23, and the fourth seal portion S4 according to the fourth embodiment configured across the auxiliary container 22 and the tube plate 23 will be described. To do.

  First, as shown in FIGS. 9 and 10, the third seal portion S3 includes a third flange 21F (an example of the flanged f) of the main container 21 (an example of the bottomed cylindrical first component Y1) and a tube sheet. 23 (an example of the second component Y2) and a third seal ring 19 (an example of the seal ring R) interposed between the two components 21F and 23, with the third seal ring 19 being sandwiched The third flange 21 </ b> F and the tube plate 23 are connected by tightening using a plurality of bolts and nuts 29.

  A third annular recess groove 24 (an example of an annular recess groove m) for fitting and deploying the third seal ring 19 is formed in the first side peripheral surface 23a of the tube plate 23, and the third annular recess groove 24 is formed in the third annular recess groove 24. A third annular protrusion 25 (an example of the annular protrusion j) that can be fitted is formed on the side peripheral surface 26 of the third flange 21F. The third annular recess groove 24 is a circumferential groove having a rectangular cross section having a seal surface 24s abutting against the third seal ring 19 as a bottom surface, and the third annular protrusion 25 is a third seal. The cross section having a seal surface 25s abutting on the ring 19 as a top surface is a circular strip having a rectangular shape. The diameter of the third annular protrusion 24 enters the third annular recess groove 25 in a state in which some gaps c1 and c2 (about several millimeters: for example, 1 to 3 mm) are formed both inside and outside the diameter. Is set (see FIG. 9B).

  As shown in FIGS. 10A and 10B, the third seal ring 19 is formed by spirally winding a metal band k having a corrugated section and a band-shaped expanded graphite d in a state of being polymerized with each other. It has a flat cylindrical shape having a spiral portion u. At the radially inner end and the radially outer end of the spiral portion u, an inner metal portion 27 and an outer metal portion 28 are formed, in which only the metal band k is spirally wound a plurality of times. As the portion of only the metal band k, the inner and outer ends of the spiral portion u are set to about 7 to 13 turns. 8-10 turns are preferred for both the radially inner end and the radially outer end.

  In the assembled state (state shown in FIG. 9A) in which the third flange 21F and the tube plate 23 are tightened and connected by a plurality of bolts 29 provided at equal angles with respect to the axis P, the third annular recess is provided. The third seal ring 19 that is fitted and deployed so as to come into contact with the seal surface (bottom surface) 24s of the groove 24 is compressed by a predetermined amount by the seal surface (top surface) 25s of the third annular protrusion 25. A spacer 30 (spacer L) interposed between the third flange 21F and the tube plate 23 is provided. Although illustration is omitted, 48 bolts and nuts 29 are provided for each equal angle with respect to the shaft center P, and the flat cylindrical spacer 30 is connected to the bolts and nuts 29 for each skip, that is, 24 bolts. -The nut 29 is fitted.

  Note that a fourth seal portion S4, which will be described later, is basically the same as the third seal portion S3, and FIG. 9B showing the relationship between the first component Y1 and the second component Y2 is representative. As for the third seal portion S3. In the third and fourth seal portions S3 and S4, the main container 21, the tube plate 23, and the auxiliary container 22 are fastened (tightened) at once using a common bolt / nut 29. It is structured.

  The fourth seal portion S4 having the fourth seal ring 20 (an example of the seal ring R) has a fourth annular recess groove 31 (an example of the annular recess groove m) equivalent to the third annular recess groove 24. A fourth annular ridge 32 (equivalent to the third annular ridge 25) is formed on the fourth flange 22F (an example of the flange f) of the auxiliary container 22 (an example of the bottomed cylindrical first component Y1). The third seal portion S3 is the same as the third seal portion S3 except that an example of the annular protrusion j is formed on the tube plate 23 (an example of the second component Y2). Accordingly, parts having the same parts and functions are denoted by the same reference numerals as those in the third embodiment, and the description thereof is made.

  11A and 11B, the fourth seal ring 20 is formed of a single vertical short-circuit member 17 made of a metal pipe and a pair of horizontal short-circuit members 18 made of a metal pipe inside the third seal ring 29. , 18 and a swirl portion u having both sides (both sides circumferential surfaces) of an expanded graphite sheet material (expanded graphite tape) 33 is laminated. The point is also different.

[Another Example]
For example, a structure in which a seal ring R is interposed between the main container 1 and the auxiliary container 2 (an example of the second component Y2), or between a plate-like tube plate without holes and the main container 1 or the auxiliary container Alternatively, the seal ring R may be interposed. Further, a seal ring having a structure in which a protrusion prevention ring (reinforcing ring) is provided outside the spiral portion is also possible. The spacer L may be a single large-diameter ring having holes corresponding to the plurality of bolts 7.

4 Fluid container 7 Tightening connection means (bolts)
L Spacer R Seal ring Y1 1st component Y2 2nd component d Expanded graphite f Flange h Reinforcement member j Annular ridge k Metal band m Annular groove r Reinforcement ring u Spiral part

Claims (7)

A bottomed cylindrical first component that constitutes a fluid container for internally circulating a fluid to be temperature controlled, a second component that is connected and integrated with the first component, and the first component A seal ring interposed between the second component and a flange formed at an end of the first component and the second component are tightened with the seal ring interposed A heat exchanger seal structure connected,
Either one of the flange and the second component is formed with an annular recess groove into which the seal ring is fitted and deployed, and the other of the flange and the second component is formed with the annular recess. An annular ridge that can be fitted into the groove is formed,
The seal ring is configured to have a structure having a spiral portion formed by winding a metal strip having a corrugated cross-section and a strip-shaped expanded graphite in a state of being spirally wound a plurality of times, and the flange and the second configuration. In the assembled state in which the element is tightened and connected, the flange and the second portion are arranged such that the seal ring fitted and deployed in the annular recess groove is compressed by a predetermined amount by the annular protrusion. A heat exchanger seal structure equipped with a spacer interposed between components.   The seal structure for a heat exchanger according to claim 1, wherein the flange, the second component, and the spacer are formed to have the same or substantially the same hardness.   3. The heat exchanger sealing structure according to claim 1, wherein only the metal band is wound in a spiral shape at a radially inner end and / or a radially outer end of the spiral portion.   The seal ring is configured to be integrally provided with a protrusion prevention ring having a thickness smaller than a value obtained by subtracting the predetermined amount from the thickness of the spiral portion on the inner side of the spiral portion. The seal structure for a heat exchanger according to any one of claims 1 to 3.   The means for tightening and connecting the flange and the second component is a plurality of bolts arranged across their outer peripheral portions, and the spacer is provided for each appropriate bolt of the plurality of bolts. The heat exchanger seal structure according to any one of claims 1 to 4, wherein the heat exchanger seal structure is formed in a ring-like shape to be fitted.   The seal structure for a heat exchanger according to any one of claims 1 to 5, wherein a seal member that short-circuits the inner peripheral ends of the seal ring is provided.   The heat exchanger seal structure according to any one of claims 1 to 6, wherein the fluid container is of a fuel oil heater for fuel in a thermal power generation facility.

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