JP3298189B2 - Multi-tube heat exchanger - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a preferred structure of a multitubular heat exchanger.

[0002]

2. Description of the Related Art As an example of this type of heat exchanger, there is known a double-tube type heat exchanger disclosed in Japanese Utility Model Publication No. 56-32769.

FIG. 7 shows this heat exchanger. 101a,
Reference numerals 101b denote left and right tube sheets to which both end portions of a large number of outer tubes 102 are fixed by welding or tube expansion. 103 is a U-shaped heat transfer tube, and the open end of each U-shaped heat transfer tube 103 is U-shaped.
They are connected by a letter pent 104. The tube sheet 10
The curved portions of the U-shaped heat transfer tube 103 and the U-shaped pent 104 are covered by side covers 105a and 105b having peripheral walls on both outer surfaces of both ends of 1a and 101b. Then, the partition plate 106 integrally formed on the inner surfaces of the side covers 105a and 105b is
By making contact with 1a and 101b, the curved portion of the U-shaped heat transfer tube 103 and the U-shaped pent 104 are partitioned one by one to form a meandering double tube structure. The outer pipe inlet 108 is provided at one end of the side covers 105a and 105b,
09 are formed at the other ends, respectively.

The U-shaped heat transfer tube 103 penetrating at one end of the side covers 105a and 105b is extended outward to form an inner tube inlet 110, and the U-shaped heat transfer tube 1 penetrating at the other end.
03 is extended outward to form an inner tube outlet 111.

[0005] The cooling medium flows from the inner tube inlet 110 and reaches the inner tube outlet 111 through the plurality of U-shaped heat transfer tubes 103 and the U-shaped pent 104. On the other hand, the medium to be cooled flows from the outer tube inlet 108 and reaches the outer tube outlet 109 via the outer peripheral wall surfaces of the plurality of U-shaped heat transfer tubes 103 while performing heat exchange with the cooling medium.

[0006] As this type of heat exchanger, Japanese Utility Model Laid-Open No.
A shell-and-tube type disclosed in Japanese Patent Publication No. 55895/95 is also known. This conventional heat exchanger is shown in FIGS. 112 is a cylindrical body, 11
Reference numeral 3 denotes a heat transfer tube, and 114 denotes a baffle plate of a circular plate-like member.
A hole 116 having a predetermined diameter larger than the diameter of the hole 116 is provided. Reference numeral 117 denotes a tube sheet having a hole 118 into which the end of the heat transfer tube 113 is inserted and fixed.

A plurality of baffle plates 114 are arranged inside the body 112 along the axial direction with the missing circles 115 shifted by a predetermined angle in the circumferential direction, and are held in parallel at predetermined intervals by a spacing member (not shown). Have been. Both ends of the heat transfer tube 113 are fixed by the tube plate 117 and inserted and held in the holes 116 of the baffle plate 114, and the heat transfer tubes 113 meander as shown by the arrow 119 in FIG. The cooling medium and the cooling medium flowing in the heat transfer tube 113 perform heat exchange.

[0008]

However, the heat exchanger disclosed in Japanese Utility Model Publication No. 56-32769 has a double pipe structure and a U-shaped pipe.
Compared to a shell-and-tube type used with the same performance, the volume and weight of the heat exchanger are increased, and the cost is increased due to an increase in the number of parts. Further, when a cooling medium containing foreign matter such as seawater is used for the fluid flowing in the U-shaped heat transfer tube 103 and the U-shaped pent 104, maintenance for the foreign matter is required, and the use of the fluid containing the foreign matter in this structure is required. Will not be possible and will be limited by the environment in which it is used. Further, since the U-shaped pent 103 is used, there is a problem that the assembling process requires time and the assembling efficiency is low.

In the heat exchanger disclosed in Japanese Utility Model Application Laid-Open No. 60-55895, the number of parts such as outer tubes is reduced by using a shell-and-tube type, thereby reducing the size, weight, and cost. At the same time, a structure that does not use a U-shaped tube enables the use of a fluid that requires maintenance for foreign substances. However, in this configuration, it is necessary to pass through the heat transfer tubes through a large number of holes formed in each of the baffle plate and the tube plate and to fix the heat transfer tubes.

[0010] It has been generally known that it is conventionally advantageous in terms of heat exchange performance that a heat exchanger has a cooling medium inside a heat transfer tube and a medium to be cooled outside the heat transfer tube in counterflow. In the heat exchanger disclosed in Japanese Utility Model Publication No. 56-32769, the heat exchange performance is exhibited by using a counter flow, but in the heat exchanger disclosed in Japanese Utility Model Publication No. 60-55895. The mainstream of the heat transfer tubes is the cross flow, and the heat exchange performance is not sufficiently exhibited.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a low-cost heat exchanger structure that can sufficiently exhibit heat exchange performance and improve assembly efficiency.

[0012]

According to the present invention, as a means for solving the above-mentioned problems, a plurality of heat transfer tubes through which a cooling medium flows are arranged between tube sheets provided at both end portions of a cylindrical body. And
In the multi-tube heat exchanger cooled medium cooled by the cooling medium through the heat transfer tubes flows the tubular body together when the partitions are parallel to the cylindrical body in the axial direction of the cylindrical body
To promote heat transfer between the cooling medium and the medium to be cooled.
A plurality of heat transfer tube groups in which a baffle plate to be advanced and a plurality of the heat transfer tubes are integrated are arranged in parallel in the cylinder at predetermined intervals, and the medium to be cooled is provided at an end of the baffle plate of the heat transfer tube group. A multi-tube heat exchanger, characterized in that a communication port through which heat is passed is provided, and the medium to be cooled flows in a meandering manner in the cylindrical body along the heat transfer tubes of the heat transfer tube group.

[0013]

According to the present invention, a heat transfer tube and a baffle plate parallel to the axial direction of the heat transfer tube are integrated, and a plurality of heat transfer tube groups are arranged in parallel to form a heat transfer tube and a baffle plate. In addition to simplifying the attaching process and improving the assembling efficiency, heat exchange between the cooling medium flowing inside the heat transfer tube and the medium to be cooled flowing outside the heat transfer tube is performed extremely efficiently.

[0014]

Next, a multi-tube heat exchanger according to the present invention will be described with reference to an embodiment shown in the drawings. First Embodiment FIGS. 1, 2 and 3 show a first embodiment of the present invention. FIG. 1 is a sectional view of a heat exchanger, and FIG. 2 is a sectional view taken along the line A--A in FIG. FIG. 3 and FIG. 3 show cross-sectional views taken along arrows BB in FIG.

The heat exchanger is shown in FIG. 1 and FIG.
A body 1 forming a cylinder, tube plates 3a, 3b separating a cooling medium passage from a cooling medium passage, side covers 4a, 4b forming a refrigerant chamber between the tube plates 3a, 3b, and the refrigerant chamber And a plurality of heat transfer tube portions 2 serving as passages for the cooling medium.

The body 1 has a hollow cylindrical shape, and a cooling medium inlet 6 is provided at one upper end of the body 1, and a cooling medium inlet is provided at the lower other end of the body 1. An outlet 7 is provided. The tube sheets 3a and 3b are disk-shaped members having a plurality of holes into which the ends of the heat transfer tube portion 2 can be inserted. The side cover 4a is provided with a coolant outlet 8, and the side cover 4b is provided with a coolant inlet 9. Also, the side covers 4a, 4
The partition plates 5a, 5b integrally formed on the inner surface of the b. make the partition plates 5a, 5b contact the left and right tube plates 3a, 3b via a sealing member such as a packing (not shown), thereby forming a flow path for the refrigerant. Stipulates.

In this embodiment, FIGS. 2 and 3
As shown in the figure, a plurality of heat transfer tube sections 2 having a perfect circular cross section,
The baffle plate portions 10 of the plate-like members are integrally formed as a substantially plate-like heat transfer tube group by extrusion or the like so as to be alternately arranged. A plurality of the heat transfer tube groups are arranged in the body 1 at predetermined intervals in the normal direction of the body 1. The first heat transfer tube group 11, the third heat transfer tube group 13, the fifth heat transfer tube group 15, and the sixth heat transfer tube group 16 have, at both ends of the baffle plate portion 10, elongated holes 1 through which a medium to be cooled passes.
7, the second heat transfer tube group 12 has a long hole portion 17 through which the medium to be cooled passes only at the end of the baffle plate portion 10 on the first refrigerant chamber 18 side, and the fourth heat transfer tube group 14 Only the end of the baffle plate 10 on the refrigerant chamber 21 side has an elongated hole 17 through which the medium to be cooled passes.

Next, the heat exchanger of the present embodiment will be described in assembling order. The projecting end of the heat transfer tube portion 2 of each of the heat transfer tube groups 11 to 16 is inserted into a hole formed in the tube sheets 3a and 3b. Insert. Each of the heat transfer tube groups 11 to 16 and the tube sheets 3a and 3b are fixed by brazing or the like. Next, the body 1, the side cover 4a and the O-ring 29 are engaged, and the heat transfer tube groups 11 to 16 and the tube sheets 3a and 3b assembled therein are inserted therein. At this time, the tube sheet 3a is airtightly held by the pressing force of the O-ring 29. Finally, the side covers 4b of the first refrigerant chamber 18 and the third refrigerant chamber 20 are attached by bolting or brazing.

The means for engaging the side covers 4a, 4b is not limited to this. For example, the side covers 4a, 4b
And the tube sheets 3a and 3b may be engaged with each other.

Therefore, according to this embodiment, the actual opening time is 60─5.
It is not necessary to penetrate the heat transfer tubes one by one with respect to the baffle plate as in the prior art disclosed in Japanese Patent No. 5895, and the heat transfer tubes and the baffle plate are integrally formed, so that a plurality of baffle plates The work of inserting the heat transfer tubes can be omitted, and the improvement of assembly efficiency can be achieved.

Next, the flows of the cooling medium and the medium to be cooled will be described with reference to the arrows in FIGS. In the arrows of FIG. 1, the solid line indicates the flow of the medium to be cooled, and the broken line indicates the flow of the cooling medium.

First, the cooling medium is introduced into the first refrigerant chamber 18 through the cooling medium inlet 9. The flow path of the cooling medium flowing into the first refrigerant chamber 18 is defined by the partition plate 5b and the tube plate 3b, and the first heat transfer tube group 11 and the second heat transfer tube group 1
The second refrigerant passes through the second heat transfer tube portion 2 and flows into the second refrigerant chamber 19. The flow path of the cooling medium flowing into the second refrigerant chamber 19 is defined by the partition plate 5 a and the tube sheet 3 a, and is passed through the third heat transfer tube group 13 and the fourth heat transfer tube group 14.
Flows into Thereafter, the cooling medium flows into the fourth refrigerant chamber 21 via the fifth heat transfer tube group 15 and the sixth heat transfer tube group 16, and is guided to the cooling medium outlet 8.

On the other hand, the cooling medium flowing into the cooling medium inlet 6 is separated from the medium flowing through the first passage 22 and the first heat transfer tube group 1.
The flow is divided into the medium flowing through the second passage 23 through the long hole 17 formed at the end of the first refrigerant chamber 19. The medium to be cooled flowing through the first passage 22 forms a flow toward the first refrigerant chamber 18 while contacting the outer surface of the first heat transfer tube group 11. The medium to be cooled flowing through the second passage 23 also forms a flow toward the first refrigerant chamber 18 like the medium to be cooled flowing through the first passage 22. Further, the first heat transfer tube group 11
The medium flowing through the first passage 22 merges with the medium flowing through the second passage 23 through the elongated hole portion 17 formed at the end of the refrigerant chamber 18 side, and then the first heat transfer tube 12 of the second heat transfer tube group 12 Refrigerant chamber 18
It flows into the third passage 24 through the elongated hole 17 formed in the side end.

The medium to be cooled which has flowed into the third passage 24 passes through the medium flowing through the third passage 24 and the slot 17 formed at the end of the third heat transfer tube group 13 on the third refrigerant chamber 20 side. Through the fourth passage 25 to the medium flowing through the fourth passage 25. Third passage 24
Forms a flow toward the second refrigerant chamber 19 side. The medium to be cooled flowing through the fourth passage 25 is also the same as the medium to be cooled flowing through the third passage 24, in the second refrigerant chamber 1.
A flow toward the side 9 is formed. Further, the third heat transfer tube group 13
The medium flowing in the third passage 24 merges with the medium flowing in the fourth passage 25 through the elongated hole 17 formed at the end of the second heat transfer tube group 14 on the side of the second refrigerant chamber 19. The fifth passage 2 is formed through an elongated hole 17 formed at the end of the second refrigerant chamber 19 side.
6 will flow.

Further, the medium to be cooled which has flowed into the fifth passage 26 is mixed with the medium flowing through the fifth passage 26 and the fifth heat transfer tube group 15.
And a medium flowing through the sixth passage 27 through the long hole portion 17 formed at the end of the fourth refrigerant chamber 21 and the end of the sixth heat transfer tube group 16 at the end of the fourth refrigerant chamber 21. The flow is divided into the medium flowing through the seventh passage 28 via the long hole 17. Fifth passage 2
The cooling medium flowing through the sixth, sixth and seventh passages 27 and 28 together form a flow toward the third refrigerant chamber 20. Further, an elongated hole 17 drilled at the end of the fifth heat transfer tube group 15 on the third refrigerant chamber 20 side and the third refrigerant chamber 20 of the sixth heat transfer tube group 16 are provided.
The fifth passage 26 is formed through the long hole 17 formed in the side end.
The medium flowing through the sixth passage 27 merges with the medium flowing through the seventh passage 28, and is thereafter guided to the cooling medium outlet 7.

That is, the medium to be cooled is the heat transfer tube groups 11 to 1
6 and flowing while contacting the outer peripheral wall surface of heat transfer tube section 2
Then, heat exchange with the cooling medium is performed. In addition, baffles
The medium to be cooled and the cooling medium in the heat transfer tube section 2 also pass through the plate section 10.
Heat exchange takes place with the body. At this time, the flow of the cooling medium and the medium to be cooled is dominated by the most advantageous counterflow in the heat exchange, so that the performance of the heat exchange can be improved.

[Second Embodiment] FIG. 4 shows a second embodiment of the present invention.
It is a figure showing the section composition of the heat exchanger concerning an example.

In the second embodiment, similarly to the first embodiment described above, the body 1, the tube sheets 3a and 3b for separating the cooling medium passage and the cooling medium passage, and the tube sheets 3a and 3b It comprises side covers 4a and 4b forming a refrigerant chamber, partition plates 5a and 5b for dividing the refrigerant chamber, and a plurality of heat transfer pipes 2 serving as passages for a cooling medium.

However, in this embodiment, all the heat transfer tube groups 11 to 16 have the elongated holes 17 at both ends of the baffle plate portion 10 for allowing the medium to be cooled to pass. Further, in the third passage and the fifth passage, a partition wall 30 is provided so as to divide each passage into two along the axial direction of the body 1.

According to the first embodiment, the flow of the cooling medium and the medium to be cooled is dominated by the most advantageous counterflow in the heat exchange. The medium to be cooled flowing through 24 does not form a counterflow.
Similarly, the cooling medium flowing through the fourth heat transfer tube group 14 and the fifth passage 2
The medium to be cooled flowing through 6 does not form a counterflow.

However, according to the second embodiment, the flow of the cooling medium indicated by the dashed line and the flow of the medium to be cooled indicated by the solid line are all counterflows, so that the heat exchange can be further improved.

As for the variation of the shape of the heat transfer tube groups 11 to 16, for example, in the case of extrusion molding, FIG.
As shown in (a), the same effect can be obtained even when the cross-sectional shape of the heat transfer tube portion 2 is a semicircular shape.

Similarly, in the extrusion molding, the heat dissipating fins 31 as shown in FIG.
, The heat exchange performance is further improved. In the case of press working, as shown in FIG. 5C, the upper and lower portions are formed by press working, and the heat transfer tube groups 11 to 16 can be obtained by this joining. At this time, the long hole portion 17 can be formed at the same time in the pressing process.

Further, the heat transfer tube groups 11 to 16 can be formed by forming the heat transfer tube 2 and the baffle plate 10 separately and fixing them as shown in FIG. Further, in each heat transfer tube group, it is also possible to use a pipe 32 as shown in FIG. That is, a heat transfer tube group slightly shorter than the entire length of the heat transfer tube groups 11 to 16 is integrally formed, and the heat transfer tube portion 2 of the heat transfer tube group is formed.
By fixing the pipes to the pipes, the gaps between the pipes 32 can serve as the elongated holes 17. At this time,
The size of the long hole can be adjusted by adjusting the length of the pipe 32.

The same applies when the flow path of the cooling medium and the medium to be cooled is reversed, that is, when the medium to be cooled flows inside the heat transfer tube section 2 and the cooling medium flows outside the heat transfer tube section 2. An effect can be obtained.

[0036]

According to the present invention, the heat transfer tube and the baffle plate extending in the axial direction of the heat transfer tube are integrated, and the heat transfer tube group is arranged in plural rows in parallel, thereby simplifying the assembly process. As a result, the efficiency of assembly can be improved, and the flow of the cooling medium and the flow of the medium to be cooled become parallel flows, thereby improving the heat exchange performance.

[Brief description of the drawings]

FIG. 1 is a sectional configuration diagram of a heat exchanger showing a first embodiment of the present invention.

FIG. 2 is a sectional view taken along the line AA in FIG. 1;

FIG. 3 is a sectional view taken along the line BB in FIG. 1;

FIG. 4 is a sectional configuration diagram of a heat exchanger showing a second embodiment of the present invention.

5 (a), (b), (c), and (d) are side views showing variations in the shape of the heat transfer tube group.

FIG. 6 is a top view showing another example of the long hole portion in the heat transfer tube bank.

FIG. 7 is a cross-sectional configuration diagram showing a conventional double-pipe heat exchanger.

FIG. 8 is a sectional view showing a conventional shell and tube heat exchanger.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Body which forms a cylindrical body 2 ... Heat transfer tube part 3a, 3b ... Tube plate 10 ... Baffle plate part 11-16 ... Heat transfer tube group 17 ... Long hole which forms a communication port Department

Claims (3)

(57) [Claims] 1. A plurality of heat transfer tubes through which a cooling medium flows between tube plates provided at both end portions of a cylindrical body, and a cooling medium cooled by the cooling medium through the heat transfer tubes. in There multitubular heat exchanger flowing through the tube body, the tube body the parallel to the axial direction of the cylinder divider Rutotomoni, before
The heat transfer between the cooling medium and the medium to be cooled is promoted.
A plurality of heat transfer tube groups in which a baffle plate to be made and a plurality of the heat transfer tubes are integrated are arranged in parallel in the cylinder at predetermined intervals, and the medium to be cooled is placed at an end of the baffle plate of the heat transfer tube group. A multi-tube heat exchanger having a communication port through which the cooling medium flows in a meandering manner in the cylinder along the heat transfer tubes of the heat transfer tube group. 2. The cooling medium passing through the heat transfer tubes and the medium to be cooled passing outside the heat transfer tubes flow at the ends of the baffle plate of the heat transfer tube group so as to flow in directions opposite to each other. The multi-tube heat exchanger according to claim 1, wherein a communication port is provided. 3. A cooling system in which a plurality of heat transfer tubes through which a medium to be cooled flows are arranged between tube sheets provided at both end portions of a cylindrical body, and heat exchanges with the medium to be cooled through the heat transfer tubes. In a multi-tube heat exchanger in which a medium flows through the cylinder, the cylinder is partitioned in parallel with the axial direction of the cylinder , and
Promoting heat transfer between the cooling medium and the medium to be cooled.
A plurality of heat transfer tube groups in which a baffle plate and a plurality of the heat transfer tubes are integrated are arranged in parallel in the cylinder at predetermined intervals, and the cooling medium passes through an end of the baffle plate of the heat transfer tube group. A multi-tubular heat exchanger, wherein a communication port is provided to allow the cooling medium to flow through the cylinder in a steerable shape along the heat transfer tubes of the heat transfer tube group.