JPH01296092A - Manufacturing method of parallel flow multi-tubular heat exchanger - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

Detailed Description of the Invention [Field of Industrial Application] The present invention relates to coolers for nuclear power plants, chemical equipment, etc., and particularly relates to a multi-tube heat exchanger in which the shell side fluid flows parallel to the heat transfer tubes, and the multi-tube heat exchanger. Regarding the production method.

[Conventional technology]

The conventional device is as described in Japanese Patent Application Laid-Open No. 57-498.

As a support member for the heat exchanger tubes, a method has been adopted in which a rod is inserted between the heat exchanger tubes to support the heat exchanger tubes.

The rod is fixed to a ring provided on the outer periphery of the heat exchanger tube group by welding or the like. Further, the rods are assembled in a right angle direction or at 60 degrees depending on the arrangement of the heat exchanger tubes.

In this way, rod baffle units are assembled, and a large number of these rod baffle units are provided.

In conventional devices, the gap between the heat exchanger tubes is small, so the rod baffle has a weak rigidity.

In addition, one possible way to prevent this is to increase the pitch of the heat exchanger tubes and increase the rod diameter of the rod baffle, but since increasing the pitch of the heat exchanger tubes increases the flow area of the fluid on the body side. , there were problems such as the flow velocity of the shell-side fluid becoming slow and heat transfer performance decreasing.

[Problem to be solved by the invention]

The above conventional technology does not give sufficient consideration to the rigidity of the rod of the rod baffle of the heat exchanger tube support, and there is a problem that the rigidity of the rod is insufficient when the heat exchanger tube pitch is narrow and the specific gravity of the body side fluid is large. there were.

An object of the present invention is to improve the rigidity and heat transfer performance of heat transfer tube supports for coolers in nuclear power plants, thermal power plants, chemical equipment, etc.

[Means to solve the problem]

In order to achieve the above object, the present invention mainly includes a water chamber, a body, a large number of heat exchanger tubes provided inside the body, and lattice-shaped heat exchanger tube support members provided at multiple locations to support the heat exchanger tubes. A parallel flow type multi-tube heat exchanger in which the body side fluid as a component flows parallel to the heat exchanger tubes, in which a corrugated plate having irregularities in the axial direction of the heat exchanger tubes is provided at any location between the heat exchanger tubes. .

The present invention also provides a body whose main components include a water chamber, a body, a large number of heat exchanger tubes provided inside the body, and lattice-shaped heat exchanger tube support members provided at a plurality of locations to support the heat exchanger tubes. In manufacturing a parallel flow multi-tubular heat exchanger in which the side fluid flows parallel to the heat transfer tubes, a ring-shaped plate is placed at each end of a lattice-like corrugated plate having unevenness in the axial direction of the heat transfer tube between the plates. The two ring-shaped plates are fitted and fixed with a gap provided therebetween, and the two ring-shaped plates are tightened together with bolts to narrow the gap between the rings, thereby compressing the lattice-shaped corrugated plate and enlarging its unevenness. By fixing the heat exchanger tubes together, it can be easily assembled without damaging the heat exchanger tubes.

It is made so that it can be manufactured.

[Effect]

The corrugated plates are arranged perpendicularly to the axial direction of the heat exchanger tubes, and are slightly smaller than the gap between the heat exchanger tubes.

Further, the corrugated plate is provided with a plurality of projections and depressions in the axial direction of the heat exchanger tube.

As a result, the corrugated plate supports the heat exchanger tube in the right angle direction and has rigidity against vibrations caused by the shell-side fluid. Furthermore.

This is because the corrugated plate acts to disrupt the flow of fluid on the body side.

Heat transfer performance can be improved.

〔Example〕

A first embodiment of the present invention will be described below with reference to FIG.

A body side inlet nozzle 2 and a body side outlet nozzle 3 are provided in the body 1,
Tube sheets 4 are placed at both ends of the body 1, and heat exchanger tubes 5 are placed between the two tube sheets. The heat exchanger tubes 5 are supported by heat exchanger tube support members 15 provided at appropriate intervals. The lattice-shaped heat exchanger tube support member 15 is supported by the ring 7. A corrugated plate 6 having irregularities in the axial direction of the heat exchanger tubes is provided at any location between the heat exchanger tubes.

On the other hand, the tube side water chamber 8 is provided with a tube side inlet nozzle 9 and a tube side outlet nozzle 10.

FIG. 1(a) is an overall view of the heat exchanger, FIG. 1(b) is a sectional view taken along line A-A of the heat exchanger body, and No. 11!1(Q) is a sectional view of the heat exchanger tube and corrugated plate. FIG. 1(d) shows a bird's-eye view of the heat exchanger tube support member.

During operation of the heat exchanger, cooling water enters through the tube-side inlet nozzle 9, flows through the heat transfer tubes 5, and exits through the tube-side outlet nozzle IO. The fluid to be cooled on the shell side enters through the shell side inlet nozzle 2 and passes through the heat exchanger tube 5.
It flows approximately parallel to the heat transfer tubes on the outside of the tube and exits from the shell side outlet nozzle.

As shown in FIG. 1(c), the corrugated plate has an uneven shape in a direction perpendicular to the flow of the body-side fluid.

Next, the operation of this embodiment will be explained.

The lattice-shaped heat exchanger tube support member 15 is assembled in a lattice shape between the heat exchanger tubes, and supports the heat exchanger tubes 5 in a direction perpendicular to the axis of the heat exchanger tubes. By providing the heat exchanger tube support members 15 at appropriate intervals, damage to the heat exchanger tubes due to vibration caused by the flow of the shell-side fluid is prevented.

Since the corrugated plate has unevenness in the axial direction of the heat transfer tube, the flow of the body-side fluid is disturbed. When the turbulent flow of the fluid is promoted, heat transfer on the surface of the heat exchanger tube is promoted, so that the heat transfer performance of the heat exchanger is improved.

According to this embodiment, the heat transfer performance of the heat exchanger is improved by promoting turbulence in the shell-side fluid.

In this embodiment, the heat exchanger tubes are straight tubes, one pass flow on the shell side, and one bus flow on the tube side, but the same applies even if the heat exchanger tubes are U-shaped tubes.
The number of passes on the ll side and tube side is the same whether it is 2 passes or 4 passes. Further, the arrangement of the heat exchanger tubes can be either a square arrangement or a triangular arrangement.

Next, a second embodiment will be explained with reference to FIG.

The configuration is generally the same as the first embodiment. The difference is that
The heat exchanger tube support member is constituted by a corrugated plate having unevenness in the axial direction of the heat exchanger tubes 5.

Therefore, the points of difference will be explained.

The heat exchanger tubes 5 are supported by lattice-shaped corrugated plates 6 provided at appropriate intervals. The corrugated plate 6 is supported by a ring 7.

FIG. 2(a) is an overall view of the heat exchanger, and FIG. 2(b) is
2(c) is a sectional view of the heat exchanger tube and the corrugated plate, and FIG. 2(d) is a sectional view of the heat exchanger body supported by the corrugated plate. show.

Next, the operation of this embodiment will be explained.

As shown in FIG. 2(c), the heat exchanger tube support member 6 is assembled in a corrugated shape between the heat exchanger tubes.

In the direction perpendicular to the axis of the heat exchanger tube, the heat exchanger tube is supported by contacting adjacent heat exchanger tubes via corrugated plates.

In the axial direction of the heat exchanger tube, that is, in the flow direction of the body side fluid, the heat exchanger tube support member has sufficient rigidity against vibrations caused by the flow of the body side fluid by appropriately providing a waveform shape. There is no risk of damage to the heat transfer tubes due to vibration.

Moreover, since the heat exchanger tube support member has a waveform in a direction perpendicular to the flow of the shell-side fluid, it has the effect of disturbing the flow of the shell-side fluid. When the turbulent flow of the fluid is promoted, the heat transfer effect on the surface of the heat transfer tube is promoted.

Heat transfer performance is improved.

Furthermore, as shown in FIG. 2(d), by assembling the heat exchanger tube support members 6 in a lattice shape, the heat transfer performance is further improved by improving the support rigidity of the heat exchanger tubes and promoting turbulent flow of the body side fluid.

According to this embodiment, since the heat exchanger tube support rigidity can be increased, there is no fear of damage to the heat exchanger tubes due to fluid vibration, and heat transfer performance is improved due to the fluid turbulence promoting effect of the heat exchanger tube support member.

Further, since the heat exchanger tube support member can be made by molding a thin plate using a press or the like, it is possible to freely respond to the selection of the arrangement pitch of the heat exchanger tubes.

Next, another embodiment will be explained with reference to FIG.

The third @ shows a cross section of the heat exchanger tube support member.

The heat exchanger tubes 5 are supported by a corrugated heat exchanger tube support member 6 and a flat heat exchanger tube support member 6A.

The corrugated heat exchanger tube support members 6 and the flat heat exchanger tube support members 6A are arranged alternately.

According to this embodiment, the heat exchanger tube arrangement pitch can be easily achieved with accuracy by assembling the flat heat exchanger tube support members 6A in a lattice shape, and the workability of assembling the heat exchanger tubes is improved.

Another embodiment will be explained with reference to FIG.

FIG. 4 shows a cross section of the heat exchanger tube support member similarly to FIG. 3. The heat exchanger tubes 5 are supported by wavy heat exchanger tube support members 6 and flat heat exchanger tube support members 6A arranged alternately. The heat exchanger tube support members 6 and 6A are each arranged in a lattice shape.

According to this embodiment, since the flat heat exchanger tube support members and the corrugated heat exchanger tube support members are assembled in a lattice shape, the workability of assembling the heat exchanger tube support members is improved.

Another embodiment will be explained with reference to FIG.

FIG. 5 shows an assembled diagram of the heat exchanger tube support member. The heat exchanger tube 5 is supported by a corrugated heat exchanger tube support member 6 and a flat heat exchanger tube support member 6A. The heat exchanger tube support members 6 and 6A are arranged in a grid pattern. The flat heat exchanger tube support members 6A are arranged at appropriate intervals.

According to this embodiment, the flat heat exchanger tube support member 6A can improve the accuracy of the heat exchanger tube arrangement pitch, and the heat exchanger tube support member 6 can improve the heat transfer performance.

Another embodiment will be explained with reference to FIG. 6(a).

FIG. 6 shows a heat exchanger tube support member. The corrugated heat exchanger tube support members 6 arranged between the heat exchanger tubes are fixed by two rings 7A provided at the outermost periphery of the heat exchanger tubes. In the heat exchanger tube support member single item state, the two rings 7A have the following:
A slight gap is provided, and the height of the crest of the waveform is
It is slightly lower than the heat exchanger tube spacing.

The heat exchanger tube support member 11 includes a spacer 12 and a tie rod 1.
3 to be fixed to the tube plate 4.

The assembly and manufacturing procedure of the heat exchanger is performed as follows.

The body 1 is joined to the tube plate 4, and the heat exchanger tube support member is attached. The heat exchanger tube support member is fixed with tie rods 13, and the tube plate 4
A spacer 12 is attached between the heat exchanger tube support member 11 and the heat exchanger tube support member.

It is fixed by tightening the nut 14 at the end of the tie rod. When only the heat exchanger tube support member is installed, a gap remains between the two rings A of the heat exchanger tube support member 11. After inserting the heat exchanger tube into the 0th order and installing all the heat exchanger tubes, remove the tie rod. Tighten the tightening nut. By tightening the tie rods, as shown in FIG. 6(b), the gap between the ring 7A on the outer periphery of the heat exchanger tube support member disappears, and the waveform peaks of the heat exchanger tube support member 6 become larger, so that the heat exchanger tube 5 and the heat exchanger tube support are The gap with member 6 becomes smaller.

After tightening the tie rods, temporarily insert the heat transfer tube into the other tube, and then connect the tube plate and body.

According to this embodiment, the gap between the heat exchanger tube support plate 6 and the heat exchanger tube is large when the heat exchanger tube is inserted, so one assembly can be performed without damaging the heat exchanger tube, and after the heat exchanger tube is assembled, the gap between the heat exchanger tube support plate 6 and the heat exchanger tube is large. Since the gap between the heat exchanger tubes becomes smaller, the supporting force of the heat exchanger tubes increases, and damage to the heat exchanger tubes due to vibration of the heat exchanger tubes caused by the fluid can be prevented.

〔Effect of the invention〕

According to the present invention, in a multi-tubular heat exchanger in which the shell side fluid flows in parallel with the heat exchanger tubes, the support rigidity of the heat exchanger tubes is increased, damage to the heat exchanger tubes due to fluid vibration is prevented, and turbulence of the shell side fluid is promoted. Heat transfer performance is improved.

[Brief explanation of the drawing]

FIG. 1 shows an embodiment of the present invention, FIG. 1(a) is an overall view of a shell-and-tube heat exchanger, and FIG. 1(b) is an A of FIG. 1(a).
-A sectional view, FIG. 1(c) is a BB sectional view of FIG. 1(b), FIG. 1(d) is a detailed view of the heat exchanger tube support member in FIG. 1(C), The figure shows another embodiment, similar to figure 1.
Figure (a) is an overall view of the heat exchanger, Figure 2 (b) is a sectional view of the body, Figure 2 (Q) is a sectional view of the heat exchanger tubes and corrugated plates, and Figure 2 (d) is the heat exchanger tube support. 3 is a cross-sectional view of a heat transfer tube support member in another embodiment, FIG. 4 is a cross-sectional view of a heat transfer tube support member in another embodiment, and FIG. 5 is a cross-sectional view of a heat transfer tube support member in another embodiment. FIG. 6 is an assembled view of the heat transfer tube support member, and FIG. 6A is a cross-sectional view of the heat exchanger tube support member before tightening, and FIG. 6B is a cross-sectional view of the heat transfer tube support member after tightening.

Claims (1)

[Claims] 1. Main components include a water chamber, a body, a large number of heat exchanger tubes provided inside the body, and lattice-shaped heat exchanger tube support members provided at multiple locations to support the heat exchanger tubes. A parallel flow type multi-tube heat exchanger in which a body side fluid flows parallel to the heat exchanger tubes, characterized in that a corrugated plate having irregularities in the axial direction of the heat exchanger tubes is provided at any location between the heat exchanger tubes. Flow type multi-tubular heat exchanger. 2. The body-side fluid is transmitted, the main components of which are a water chamber, a body, a large number of heat exchanger tubes provided inside the body, and lattice-shaped heat exchanger tube support members provided at multiple locations to support the heat exchanger tubes. A parallel flow type multi-tube heat exchanger that flows in parallel with the heat exchanger tubes, wherein the lattice-shaped heat exchanger tube support member is composed of a corrugated plate having unevenness in the axial direction of the heat exchanger tubes. type heat exchanger. 3. The parallel flow type multi-tubular heat exchanger according to item 2, wherein a part of the lattice constituting the lattice-shaped heat exchanger tube support member is composed of a flat plate. 4. The body-side fluid is transmitted, the main components of which are a water chamber, a body, a large number of heat exchanger tubes provided inside the body, and lattice-shaped heat exchanger tube support members provided at multiple locations to support the heat exchanger tubes. In manufacturing a parallel flow type multi-tubular heat exchanger that flows parallel to the heat transfer tubes, ring-shaped plates are provided at each end of a lattice-like corrugated plate having unevenness in the axial direction of the heat transfer tubes, and a gap is provided between the plates. The two ring-shaped plates are fitted and fixed in this manner, and the two ring-shaped plates are tightened with bolts to narrow the gap between the rings, thereby compressing the lattice-shaped corrugated plate and enlarging its unevenness. A method for manufacturing a parallel flow multi-tube heat exchanger characterized by fixing heat tubes to each other.